55TH CONGRESS, > HOUSE OF BEPKESENTATIVES. ( DOCUMENT 

3d Session. J \ No. 500.

DEPARTMENT OF THE INTERIOR

WATER-SUPPLY

AND

IEEIGATION PAPEES

OF THE

UNITED STATES GEOLOGICAL SURVEY

]STo

TESTS OF PUMPS AND WATER LIFTS. HOOD

WASHINGTON

GOVERNMENT PRINTING OFFICE 

1898
UNITED STATES GEOLOGICAL STJBVEY

CHARLES D. WALCOTT, DIRECTOR

NEW TESTS

CERTAIN PUMPS AND WATER LIFTS 

USED IN IRRIGATION

OZZSTI POUTER HOOD

WASHINGTON

GOVERNMENT PRINTING OFFICE

1898
CONTENTS.

Page.

Letter of transmittal..........-..........._............................... 9

Introduction -----------------._____.__.._.._...._-..---.-___-....-....._. 11

Definitions -.,...- .................._.-___..-___...___.--_._-.--._-.-._-. 11

Suction ----------.----....--_-----.-_..-_____--_-.--.__________.__.-_.____ 14-

Upstroke -...-...---..----..--.-_._--.__--.__........-_._-._..____.--..___. 18

Downstroke---------.------._-----... .................................... 19

Valves .-.-..---.....-.--.._..____ .____.__.._.._...__..__.__..__.__._.-. 19

Piston and rod....-....--._._--.....___....__....____-_._.._.__..._....._..-- 23

Piston speed....__...-.----_.._.._..._.____._.,.__-..__..___......._...... 25

Discharge ... _._._.__..-.-._____._-._____...__.____..___..__..._.._-_.....-. 28

Efficiency of pumps...-...._._..__-_________._____._....__.__-_....-..-_.. 29

Mark pump....... ---.._.----.---_..__.__...__-..._......_-_...-...._-. 30

Frizell pump ......................................................... 43

Van Voorhis pump...-........----........-..............---...---.--. 54

Cook pump............................................................ 60

Summary .............._................................_.....'...-.... 64

Resistance to rotation offered by various crank-driven pumps.............. 65

Various water lifts._..-.--.-..-..-.--....-------...--....-....-.--..----.-- 73

Bucket lifts........................................................... 74

Seaman bucket lift -.--.---..---.--.-.--.-..---_-.---_-----.--..--- 74

Lifting by animal power.--....-.........-.....__...--...-.-...---..-- 78

Some Indian devices.-----.--_.._----.-.-..--....-...--.._..--.-.- 80

An American device. ---....---..-..-..-.----.--..--.------.---..-- 87

5
ILLUSTRATIONS.

PLATE I. At view of link-belt water elevator; B, view of Boyce water lift. 74 

FIG. 1. Vertical sections of bucket pump __--__-.-.---------.--___-----... 12

2. Vertical sections of piston and plunger pumps _.-___._-._--_-_.._.. 12

3. Vertical sections of plunger and double-acting pumps............. 13

4. Diagrammatic representation of pump problem ................... 14

5. Dynamometer diagrams of pump-rod stresses..--....--_.-.-.-.-.. 16

6. Dynamometer diagrams of pump-rod stresses ....-_-......--...... 17

7. Dynamometer diagram of pump-rod stresses from an 8-inch, pump

having large clack valvesr piston speed, 40 feet per minute...... 20

8. Dynamometer diagram of pump-rod stresses from a 6-inch pump

having multiple small valves; piston speed, 40 feet per minute... 20

9. Clack valves..................................................... 21

10. Dynamometer diagram of pump-rod stresses, showing late closing

of suction valve..._--__.______.__-__-._-_._._-__..--__--_-.---- 23

11. Diagram illustrating relation between piston speed and pull......_ 26

12. Dynamometer diagram of pump-rod stresses, showing excessive

initial shock due to late closing of discharge valve .............. 27

13. Dynamometer diagram of pump-rod stresses, showing excessive

discharge _._.................----............-....--...---...-. 29

14. Vertical section of 8-inch brass cylinder with disk valves _..-.....- 30

15. Discharge curve of 8-inch Mark pump............................. 31

16. Varying-efficiency curve of 8-inch Mark pump, showing effect of

varying height of lift and speed..______.___.....__..-.--..._.._. 31

17. Variation of efficiency with varying height of lift of 8-inch Mark

pump at speed of 15 strokes per minute.,....................... 32

18. Vertical section of a brass-lined cylinder of small Mark pump..... 33

19. Discharge curve of 4-inch Mark pump....--.-.--..---....---..... 32

20. Varying-efficiency curves of 4-inch Mark pump, showing effect of

varying height of lift and speed. ................................ 33

21. Variation of efficiency with varying height of lift of 4-inch Mark

pump at speed of 20 strokes per minute......................... 34

22. Discharge curve for 4-inch Mark pump at a total lift of 38 feet and

at various suction lifts ..........._. --.---.-..-....---.------._ 35

23. Vertical section of piston pump with valve chamber surrounding

cylinder .........._................._.............-..--..-.-.-. 43

24. Discharge curve of 6-inch Frizell pump........................... 44

25. Varying-efficiency curves of 6-inch Frizell pump, showing effect of

varying height of lift and speed.......--...._.....--..-..--..... 44

26. Variation of efficiency with varying height of lift of 6-inch Frizell

pump at speed of 20 strokes per minute. ..........^.............. 45

27. Vertical section of Frizell cylinder with butterfly valve............ 48

28. Discharge curve of 4-inch Frizell pump..-.-..-..-.......-....---. 48

29. Varying-efficiency curves of 4-inch Frizell pump, showing effect of

varying height of lift and speed......................._......_ 49

7
8 ILLUSTRATIONS.

Page. 

FIG. 30. Variation of efficiency with varying height of lift of 4-inch Frizell

pump at speed of 20 strokes per minute ...........--.-..-.---.- 50

31. Efficiency of 4-inch pump used as a force pump..---.--.-_...-.__. 53

32. Vertical section of pump designed for slow speeds and low lifts.... 54

33. Varying-discharge curves of 8-inch Van Voorhis pump, showing

effect of varying lift and speed ____._.__------_-_-.---.---_...--. 55

34. Varying-efficiency curves of 8-inch Van Voorhis pump, showing

effect of varying lift and speed......----..,... .-.-...-.._.------ 56

35. Variation of efficiency with varying height of lift of Van Voorhis

pump at speed of 15 strokes per minute..-..---...------.-.----- 57

36. Vertical section of Cook cylinder ___..-....__.--_--_-_-.. .__..----- 61

37. Discharge curve for 4-inch Cook deep-well pump ._.__-.--._..----. 63

38. Varying-efficiency curves of 4-inch Cook pump, showing effect of

varying lift and speed __.............-...._----.......--...---.. 62

39. Diagram of resistance to rotation of crank driving a single-cylinder

lift pump ............ ...................... .................... 66

40. Dynamometer diagram of actual resistance at various positions of

crank......_..._.............. _._ _.____.__-..---_-------.----. 66

41. Method of counterbalancing a windmill pump..-.....-...--....-. 67

42. Diagram of resistance to rotation of a shaft carrying two cranks

driving a duplex pump...................---._...-....-....-.-- 68

43. Diagram of resistance to rotation of a shaft carrying three cranks

driving a triplex pump..............-.,....-.--.---.--.....--.- 68

44. Gould triplex power pump....... ................................ 69

45. Gould triplex pump and horsepower combined _.................... 70

46. Discharge of Gould 4-iiich by 8-inch triplex pump ................ 70

47. Varying-efficiency curves of Gould triplex pump, showing effect of

varying speed, and at two different lifts ...--.--.---...-....---. 71

48. Dynamometer diagram of uniformity of resistance afforded by triplex pump -__._____.___..__._._._._.-____._-.-_ ..-........-._. 7i

49. Vertical section of bucket of water elevator.......... ............ 74

50. Dynamometer diagram of uniformity of resistance afforded by

Seaman bucket lift...-._..-........----...--..._....:.. ....... 75

51. Discharge per bucket of Seaman bucket lift at various speeds...... 75

52. Total discharge of Seaman bucket lift at various speeds........... 76

53. Efficiency curve of Seaman bucket at lift of 18.8 feet............... 76

54. Plan and vertical section of Stoney water lift...-.....-.-.--.....- 81

55. End elevation of Stoney water lift.......--..------. ............. 82

56. Whim used with Stoney water lift............'--......-.-.....-... 83

57. Construction of Boy ce water lift................-....---.----.--.. 87

58. Construction of Boyce water lift.............._._................. 88
LETTER OF TRANSMITTAL.

DEPARTMENT OF THE INTERIOR, 

UNITED STATES GEOLOGICAL SURVEY,

DIVISION OF HYDROGRAPHY,

Washington, January 24, 1898.

SIR: I have the honor to transmit herewith a paper entitled New 

Tests of Certain Pumps and Water Lifts Used in Irrigation, by Ozni 

P. Hood, professor of mechanics and engineering at the State Agricultural College, Manhattan, Kansas, and to recommend that it be 

published in the series of Water-Supply and Irrigation Papers. The 

facts herein briefly set forth represent a large body of original experimental work by Professor Hood and assistants, begun in the summer 

of 1896 and but recently brought to a finish.

While the water lifts have had their origin in the needs of irrigation, devices for pumping have not; with them, indeed, there is 

no special adaptation to irrigation use. Economy of power must be 

the essence of such adaptation; time is not, for ample time can be 

taken to secure the full supply. But with existing designs, as, for 

example, the deep-mine varieties, the aim usually has been rather to 

attain rapidity of delivery, even at the cost of wasteful expenditure 

of power. Among appliances for irrigation, pumps, of whatever kind, 

are but in a trial stage. Their wide use and the extension of irrigation possibilities that would result can come only through adaptations 

in design especially economical of power. It should not be left to 

come by gradual evolution through chance suggestions of practice, 

but should be deliberately brought about by engineers. Professor 

Hood's experimental determinations of efficiencies and of the little 

sources of frictional loss have contributed data which will be useful 

for this purpose.

Very respectfully, F. H. NEWELL,

Hydrographer in Charge. 

Hon. CHARLES D. WALCOTT,

Director United States Geological Survey.

9

NEW TESTS OF CERTAIN PUMPS AND WATER LIFTS 

USED IN IRRIGATION,

By O. P. HOOD.

INTRODUCTION.

The necessity of raising water for irrigation and other purposes has 

been met by a great variety of water-lifting devices. By far the most 

familiar of these is the reciprocating pump, ranging in capacity from 

the simple mechanism for cisterns to the large engines used for public 

water supply. In order that one may know what it is reasonable to 

expect from the many forms of pumps, and be able to make an intelligent selection, it is necessary first to become acquainted with some of 

the problems connected with their design and operation. In this 

paper it is the author's purpose to state certain of these problems, to 

give the results of new tests of irrigation pumps and machinery, and 

to offer notes on several other water lifts in less common use.

DEFINITIONS.

Of reciprocating pumps there are many forms, and among them there 

are essential differences. The names commonly used to designate 

these diverse forms are not in every case self-explanatory; in some 

cases they may be even misleading. Among these common designations are bucket pump, lift pump, suction pump, combined suction 

and lift pump, piston pump, plunger pump, and force pump. Common to all these forms is a backward and forward moving piston 

or plunger. When all the effective work is done while the piston is 

moving either in one direction or the other the pump is single-acting. 

When the effective work is distributed between the two motions the 

pump is double-acting. It is to this alternating movement that the 

term "reciprocating" applies. Generally speaking, in all reciprocating pumps there are three essential parts the suction pipe below, the 

discharge pipe above, and, intermediate in position between these two, 

the pump cylinder, in which a piston reciprocates.

11
12 TESTS OP PUMPS AND WATEE LIFTS. [NO. 14.

A B

FIG. 1. Vertical sections of bucket pump. A, ordinary form; B, with stuffing box.

FIG. 2. Vertical sections of piston and plunger pumps. A, piston pnmp; B, plunger pump.
DEFINITIONS. 13

A bucket pump is one in which the reciprocating piston has a valvecovered opening through it. Such a pump is shown diagrammatically 

in fig. 1, A. Between the incoming water and the piston is another 

valve-covered opening.

If the pump parts are so placed that the suction valve comes below 

the normal water level, it is called a lift pump. If, on the other hand, 

the suction lift is relatively great and the delivery pipe short, it is 

called a suction pump. Most pumps, however, by reason of the more 

even proportioning of these parts, are called combined suction and

A- B

FIG. 3. Vertical sections of plunger and double-acting pumps. A, plunger pump with large 

valve openings; B, double-acting pump.

lift pumps. Fig. 1, B, shows a pump in which the pump rod is carried through a stuffing box, whereby it is rendered unnecessary for 

the delivery pipe to follow the pump rod. A piston pump is one in 

which the piston carries no valve, the discharge valve being otherwise placed, as in fig. 2, 'A. Fig. 2, B, shows a plunger pump, a 

solid plunger, packed on the outside, replacing the piston, which is 

packed on the inside. Fig. 3, A, indicates one of several methods of 

obtaining large valve openings. Fig. 3, B, shows a double-acting 

pump, serving as a suction and force pump and acting in either direction of movement of the piston. For irrigation the type most in favor 

is that shown in fig 1, A, operated as a simple lift pump.
14 TESTS OP PUMPS AND WATER LIFTS. [NO. 14.

SUCTION.

Whenever, within a closed vessel, the normal air pressure is by any 

means diminished, there results what is commonly called suction.

Suction is here but a manifestation of 

superior pressure on the part of the 

external air. This atmospheric pressure, though varying continually, is, 

at sea level, about 14.7 pounds per 

square inch. A column of water about 

34 feet in height exerts an equal pressure. Hence, to raise the piston, shown 

in fig. 4, it is necessary not only to lift 

the column of water, L, already above 

the piston, but to overcome as well the 

atmospheric pressure, equivalent to an 

additional column of water, B, 34 feet 

in height; or to overcome, in total, a 

pressure equivalent to the weight of a 

column of water, L+B.

But with the raising of the piston 

conditions for suction, so called, are 

thereby at the same time established, 

i. e., the water surface in the pump 

tube below the piston is relieved of 

pressure, whereas outside the tube 

the atmospheric pressure continues, 

undisturbed, upon the surrounding 

water surface. It results that, by 

reason of this pressure without, water 

is forced upward in the pump tube; 

and it continues to follow the piston to 

a balancing height, which at sea level, 

as stated, is 34 feet. If the lift of the 

piston is short of this height the rising water will bear upward against the 

under side of the piston with a pressure equivalent to the weight of so 

much of the column as remains, or 

B S; less, however, such force as 

may be used up in overcoming the 

various resistances during motion. 

As the piston lift does in fact always

FIG. 4-Diagrammatic representation of gfop short of this maximum, the rempump problem. T-, n

nant of pressure, B S, serves as a

head of water for effecting flow into the suction pipe and for filling 

the cylinder. Though the theoretical limit to the height of suction is
HOOD.] SUCTION. 15

about 34 feet, a practical limit is reached at from 25 to 30 feet, depending on the perfection of packing, the tightness of joints, and the 

piston speed. If, however, the piston speed be too great, the head 

of water (B S) may not be able to produce a flow sufficiently rapid 

to follow it, and in consequence there will be incomplete filling of 

the cylinder during the period of the upstroke.

The water will encounter resistances to flow in the suction pipe, such 

as those involved in friction against its sides, in lifting the suction 

valve, and in passing through the reduced valve opening, all of which 

resistances will tend to diminish its velocity of entry into the cylinder. The less the height of the suction lift the greater will be the 

head left for overcoming these resistances, thereby admitting of a 

more rapid rate of filling and a higher piston speed. Again, by 

enlarging the suction pipe and thereby reducing the sum of the frictional resistances the flow will be increased. It follows that in practice many pumps have suction pipes of larger diameter than their 

discharge pipes.

The height of suction lift limits the possible piston speed. To show 

this, a 4-inch by 14-inch pump was arranged to discharge water at a 

total height of 38 feet, the cylinder being placed successively at various heights in the pipe, from the natural water level- up to the limit 

of suction. The suction and delivery pipes were each 2 inches in 

diameter. The various speed limits reached under these varied conditions are shown in fig. 22 (p. 35), in the progressive diminution of 

discharge due to incomplete filling of the cylinder. The upstroke of 

the piston may be more rapid than the suction uprise of the water following it, in which case there will be separation of the piston from 

the following water. This separation may under certain conditions 

lead to a shock. The separation will begin, if at all, with the beginning of the upstroke; but the acceleration of the upstroke has a diminishing rate, while the speed of the following water may have an 

increasing rate. If the water overtake the piston about midway of 

its rise, the meeting will be without perceptible shock; if near the 

end of its stroke, the shock may be considerable. If, on the other 

hand, the piston has time to complete the upstroke and accomplish a 

part of its return, the shock may be severe.

It is these recurring shocks which produce what is called pounding. 

This action is shown in the accompanying diagrams, figs. 5 to 8, 

which exhibit the pull on the pump rod at various stages of its stroke. 

In fig. 5, A, the line a?, from A to B, represents th# length of the 

stroke, the direction AB the upstroke, the direction BA the downstroke. Vertical distances above the line x represent the pull in the 

pump rod. Thus, when the piston has reached the point C on the 

upstroke, the pull in the rod is represented by the line CD, and when 

it has reached the point E the stress is EF. On the return stroke the 

stress at E is EG, and at C it is CH. The figures here referred to are
16 TESTS OF PUMPS AND WATER LIFTS. I . 14.

from card diagrams, automatically drawn by a specially devised dynamometer, which was introduced into the pump rod of pumps in opertion, so that they record actual practice. The diagram shown in fig. 

5, A, gives the results of the test of a 4-inch pump having a total lift 

of 38 feet, a 7-inch suction lift, 2-inch suction and delivery pipes, and 

a speed of thirty 14-inch strokes per minute, or an average piston speed 

of 70 feet per minute. The height of the line ab shows the pull necessary merely to support the column of water.

At the starting point, A, of the upstroke, the delivery valve closed, 

and the sudden pull on the rod which resulted is shown by the long 

vertical line. The depression immediately following is due to the 

spring of the pump rod and connections upon receiving the first 

large stress. The upward movement of the water column having 

become accelerated, a continually lessening pull is required to produce its discharge, as shown by the rapidly falling upper line. 

The suction valve closes at B, and the weight of piston and 

rod still produces a small tension in the rod. With 

excessive friction, or at high speed, this reOL - 

A B

FIG. 5. Dynamometer diagrams of pump-rod stresses. A, general; B, with suction lift of 30.8

feet, 30 strokes per minute.

turn-stroke line frequently falls in part below the zero line, showing 

compression in the pump rod.

In fig. 5, B, the pump was given a suction lift of 30.8 feet, with the 

same total lift and speed, however, as in fig. 5, A. The pull on the 

pump rod is seen to be very differently varied. On the upstroke this 

pull is much less, having only a small body of water to accelerate in 

addition to the weight of the atmosphere which it has to lift. The 

load remains nearly constant throughout the upstroke, the piston not 

being aided in its upward movement, toward the end, by the momentum of a rising column of water, as in fig. 5, A. On the return stroke 

the downward thrust is aided by the weight of the water in the delivery pipe as well as by the atmospheric pressure, and is resisted only 

by friction in the cylinder until the piston reaches the point 0, where 

it encounters the slowly rising column of water. The blow of the 

piston against the rising water momentarily relieves the rod of tension, as shown by the drop in the vertical line in the diagram at x. 

This opposing pressure is at once dimished, however, by the opening 

of the piston valve. At y the suction valve closes and remains closed 

until opened at w on the upstroke.

If the piston speed had been slower the cylinder would have more 

nearly filled, as shown by the card (fig. 6, A) taken at 10 strokes
HOOD.] SUCTION. 17

per minute, under which conditions the cylinder had become more 

than half filled before the shock of meeting. In fig. 6, B, the suetion 

lift was 24.7 feet, and at a speed of 30 strokes per minute the cylinder had filled to the point x. In fig. 6, C, at a speed of 20 strokes, 

the rising water overtook the more slowly rising piston during the 

upstroke at the point z. In fig. 6, D, the speed was but 15 strokes 

per minute. In this case the following water overtook the piston 

near the middle of its upstroke, when the difference of speeds was 

not great, and the diagram in consequence shows at a but slightly 

reduced tension.

It is characteristic of this condition of high suction lift that with 

the same speed the upstroke of the pump starts more easily than 

when the cylinder is full, and that pounding may occur at any point 

in the last three-fourths of the stroke the nearer its end the more

y\

QL,

C D

FIG. 6. Dynamometer diagrams of pump-rod stresses. A, suction lift of 30.8 feet, 10 strokes 

per minute; B, suction lift of 34.07 feet, 30 strokes per minute; C, suction lift of 24.07 feet, 30 

strokes per minute; D, suction lift of 34.07 feet, 15 strokes per minute.

severe. A sudden change or reversal of stress in the rod produces 

disastrous pounding and limits the speed of the pump. It should not 

be forgotten in this connection that it is weakening of suction head, 

as it might be called, that is the real cause of pounding, and that the 

difficulty may arise from undue frictional resistance to flow as well 

as from excessive suction lift.

It has been a common practice, in order to prevent an intake of 

sand where the suction pipe is itself the well and not merely a pipe 

suspended in an open well, to have the whole intake at the foot of the 

suction pipe through a screen. To the use of the screen there are 

objections of a serious nature, and the difficulty which is met by its 

use is best avoided entirely by resorting to the open well. However, 

if the screen is to be used at all, the total area of its perforations 

should be at least double the cross-section area of the suction pipe. 

Even then the screen openings will in- time become clogged to such 

extent as greatly to increase the resistance. Not infrequently in a 

IRK 14 2
18 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

pump with a screen intake failure to fill is wholly due to a clogged 

condition of the screen.

The introduction of elbows in the suction pipe is to be avoided 

wherever possible. The resistance to flow which they offer is considerable. Again, pipes of the smaller sizes are commonly cut with the 

rolling cutter, which raises a burr on the inside edge, thereby seriously 

reducing the entrance diameter. It is worth while to remove this 

burr. The following table shows the reduced cross-section area of a 

number of sizes of pipe cut with this tool:

Reduction of cross-section areas of pipes of various size cut with the rolling cutter. 

\ Diameter of pipe.

Hnch.

Per cent.

87

f-inch.

Per cent. 

77-83

1-inch.

Per cent. 

83-90

li-inch.

Per cent. 

80-88

IJ-inch.

Per cent. 

85

2-inch.

Per cent. 

90

2i-inch.

Per cent. 

95

Wherever, as sometimes happens, it becomes necessary to .extend 

the suction pipe horizontally for any distance, such horizontal section 

should be given a larger diameter than that used in vertical sections. 

The larger volume of water which the head (B S, fig. 4, p. 14) must 

move, together with the added friction of the increased length of pipe 

and of the necessary turns, reduces the velocity of the incoming water 

and fixes a lower limit to the possible piston speed.

UPSTROKE.

On the upstroke the pump simultaneously performs two distinct 

operations: It lifts directly the column of water L (fig. 4, p. 14) 

and the atmospheric column above it. By thus completely relieving 

of load the column of water below, it establishes the conditions under 

which that lower column is driven upward by the atmospheric pressure without. The resistances to upward movement above the delivery valve offered by the water are its hydraulic pressure, its inertia, 

and its friction. The hydraulic pressure depends on the height H, 

and is about 0.433 pound per square inch of piston area for each foot 

of height of water. If the discharge pipe is smaller than the cylinder, 

the velocity of the discharging water will be correspondingly greater. 

If the velocity be doubled, the frictional resistances, varying as the 

velocity squared, will be increased four times. Furthermore, water 

encounters resistance in making entrance into a pipe; wherefore it is 

desirable, when practicable, that the discharge pipe should have the 

same size as the cylinder. If the pump rod be carried through a stuffing box its friction therein will be considerable. There will be frictional loss also at the necessary turns in the delivery pipe, which loss 

may, however, be minimized by giving to these turns a long radius.

During the upstroke there is acceleration of speed at the outset and
HOOD.] STROKES AND VALVES. 19

retardation toward the close, the rate of acceleration diminishing 

toward the center of the stroke, and the rate of retardation increasing 

from that point toward the close of the stroke. The upward start of 

the water column is thus, in effect, somewhat abrupt, and in abruptly 

overcoming the inertia of this water column a pull is exerted upon 

the pump rod much in excess of that due to the weight of the water 

alone. This inertia resistance also varies as the velocity squared, 

and becomes a destructive resistance in fast-running pumps.

DOWNSTROKE.

At the finish of the upstroke the suction valve below closes, and 

the column of water above it remains at rest until the downstroke 

has been completed and another upstroke begun. During the descent 

of the piston through this stationary column of water the piston 

valve, or delivery valve, as it is called, is opened thereby. The resistances encountered on the downstroke are the frictional resistance of 

the piston packing and of the column of still water through which 

the piston has to be forced. It will be apparent that no useful work 

is accomplished on the downstroke; that all, on the other hand, is 

accomplished on the upstroke. In rising, the piston lifts B+L, and 

in turn is pressed upon from below by B S, the difference between 

these forces being that force necessary to be applied to the rod and 

equal to H, fig. 4, p. 14. It is therefore evident that the force to be 

exerted is measured by the total height of the water lift and is independent of the relation of the suction lift to the direct lift.

VALVES.

There are two common forms of valves the clack valve, which 

opens on a hinge, and the disk valve, which rises bodily on guides 

either at its circumference or along a central spindle. Valves of 

whatever variety should open and close readily, and should afford, 

when open, a water way as large and as direct as practicable. To open 

readily they must not be too heavy; on the other hand, for quick 

closing weight is an advantage. Also, to give free and large water 

passage they must have considerable amplitude of movement; yet, 

again, for quick closing such amplitude of movement is a disadvantage. Thus it appears that of necessity valve design is a matter of 

compromise among opposing conditions and requirements.

Some of the conditions which bear upon valve design are brought 

out in the following diagrams. Fig. 7 is the record made by an 8-inch 

pump having large clack valves, the smallest valve-opening area 

being 70 per cent of the cylinder cross-section area, and even this is 

an unusually large valve opening. These valves were in fact so large 

that, in the experiments, at only 25 strokes per minute they did not 

close until from 7 to 8 per cent of the stroke had been made. On
20 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

the return stroke the lower valve did not close until the piston had 

had time to travel from. B to C (fig. 7), during which time, of course, 

water was escaping. This delay in closing and the consequent loss 

of water occurred at the very moderate piston speed of about 40 feet

FIG. 7. Dynamometer diagram of pump-rod stresses from an 8-inch pump having large clack 

valves. Piston speed, 40 feet per minute.

per minute. Its diagrammatic record exhibits the main defect in 

large clack valves.

Fig. 8 is the record made by a 6-inch pump using eight small clack 

valves for delivery valves, having a 14-inch stroke, and operated at a 

speed of 55 strokes per minute. The aggregate area of the valve 

openings was 15 per cent in excess of the cylinder cross-section 

area, yet at this high piston speed of more than 125 feet per 

minute the delay in the closing of these valves, as shown at A, 

was very small, being only about 2 per cent of the time interval 

of the whole stroke. The efficiency of this pump was 

very high. Thus there is seen to be decided advantage 

in the substitution, wherever practicable, of several 

small valve openings for a single large one. 

Valve lift is thereby minimized and quick closing secured, and without reduction in the aggregate area of 

valve opening.

That the discharge area 

around the edge of a clack 

valve shall equal that of the valve-seat opening, the valve must 

rise at its outer edge to a height equal to at least half the diameter 

of the valve opening. The diameter, in inches, of a clack-valve 

opening should not exceed 100 divided by the speed of the pump 

in strokes per minute. For example, a pump making 25 strokes 

per minute should have a clack-valve opening not exceeding in

FIG. 8. Dynamometer diagram of pump-rod stresses 

from a 6-inch pump having multiple small valves. 

Piston speed, 40 feet per minute.
HOOD.] VALVES. 21

diameter ^g^0-, or 4 inches. Thus the clack valve is limited in use 

either to small pumps, to pumps of low speed, or to pumps of such 

design that they admit of the introduction of several small valves in 

substitution for a single large one.

With multiple valves the valve area should be equal to at least 50 

per cent of the cylinder cross-section area. A modification 1 of the 

usual clack valve is presented in fig. 9, A, as an illustration of the 

manner in which some of the objections to this valve may be overcome. This modification consists in mounting upon the back of the 

large clack a second clack, covering a valve opening in the first. The 

tendency of the current of water to open widely the larger clack is in 

part overcome by the yielding of the smaller clack. It is claimed 

that higher speeds may thus be attained; also that the modification 

can readily be introduced into any large single clack already in use.

The advantages of the clack valve are its simplicity and its high 

efficiency at low speed. Being usually cut out of leather, as shown

FIG. 9. Clack valves: A, vertical section of double clack valve; B, leather suction valve.

in fig. 9, B, it is self-packing when closed and is self-hinged. It 

should be cut from a solid piece of leather, of uniform thickness and 

without soft spots. The width of the hinge should equal half the 

valve diameter, and the leather should be placed with the hair side 

to the seat. A metal disk slightly larger than the valve opening 

should be attached to the back of the valve, both to add to its stiffness 

and to give it weight.

Clack valves should have a small angle of lift in pumps running 

more than 15 strokes per minute. The resistance to flow through 

clack valves has been determined for the following angular openings:

Resistance to flow through clack valves.

Degrees of lift.

15°

Per ct. 

64

20°

Per ct. 

53

25°

Per ct. 

32

30°

Per ct. 

21

40°

Per ct. 

10
22 TESTS OP PUMPS AND WATER LIFTS. [NO. 14

If, for high speed, the valve lift be limited to about 30 degrees, or 

to an opening that, at its outer edge, is equal to half the valve diameter, the disadvantage of obstruction to flow will be about balanced 

by the advantage gained of quick closing.

A modification in form is the butterfly valve, in which the hinge is 

along a diameter line across the center of the leather disk, so that, 

instead of opening as one piece from a single point at the edge, it 

opens upward in two halves, back to back, like the wings of a butterfly, 

and is in effect a double valve. Fig. 27 (p. 48) shows such valves.

The disk valve is commonly but a circular metal plate, with one 

face adapted to fit a valve seat, and designed for a straight lift, within 

guides, either as shown in fig. 14 (p. 30), or in fig. 23 (p. 43). As a rule 

its vertical range is limited mechanically, but occasionally, as in fig. 23, 

the disk is merely weighted, and control of its range is left to the 

velocity of the incoming water, to which the weighting has been or 

can from time to time be adjusted. For low speeds, of about 20 

strokes per minute, large disk valves work well, but for higher speeds 

the valves should be smaller. A valve of more that 5 inches diameter would be considered large. For quick-running pumps multiple 

valves from 3 to 4 inches in diameter are best.

In irrigation pumps the valve lift should not exceed 1$ inches. At 

that lift, and at a speed of 30 strokes per minute, about one-eleventh 

of a second is required for the drop-return of the valve disk, which 

involves a sacrifice of about 7 per cent of the stroke length. It is well 

to limit the valve diameter to four times the valve lift; and in the 

case of irrigation pumps, to 6 inches as a maximum.

The area between the edge of the disk and the cylinder walls 

should not be less than the valve-seat area. Where the cylinder is 

not enlarged into a valve chamber the valve area can not exceed 

about 40 per cent of the cylinder area, because of the necessary grids 

and lap of valves. It follows that the piston speed should fall well 

within 100 feet per minute; that is, in a pump with disk valves of 

this kind, having a 40 per cent valve opening and a 24-inch stroke, a 

speed of 25 strokes per minute should be considered high. This is a 

piston speed of 100 feet per minute.

In irrigation pumps the velocity of water through valves should 

not exceed 250 feet per minute. The speed of the piston at its maximum rate will be 1.57 times that at its average rate. In other words, 

when the average piston speed is 100 feet per minute there will be a 

maximum rate at about the middle of the stroke of 157 feet per minute; and this also will be the velocity of the water in the cylinder 

immediately ahead of the piston, but the water has to be forced 

through a contracted valve opening, and it must in consequence take 

on there a correspondingly increased velocity. If the valve opening 

be 40 per cent of that of the cylinder cross section, as above stated, 

the increase of velocity over that in the cylinder will then be from
HOOD.) PISTON AND ROD. 23

157 feet per minute to 392 feet per minute. Hence an average piston 

speed of 100 feet per minute would be excessive. Experience with 

pumps of this class has shown that the best running speed is 60 feet 

per minute. It is found that beyond this speed the resistance offered 

by disk valves -rapidly reduces the pump efficiency.

If the disk be weighted merely, and not limited in movement 

mechanically, it may be drawn up so far into the cylinder by the 

high velocity of the entering water that very late closing will result. 

The speed of the pump shown in fig. 27 (p. 48) is restricted thus to 50 

strokes per minute. Fig. 10 gives the record of this pump when running at 55 strokes per minute. The suction valve was drawn up into 

the cylinder by the high speed of the water, and did not return to its 

seat until after half the downstroke had been completed. Seating at 

this late stage produced serious pounding. 

! For lifts exceeding 100 feet ball valves become desirable, because of

FIG. 10. Dynamometer diagram of pump-rod stresses, showing late closing of suction valve.

the increased pressure. The ball should be solid and should fit into 

a metal seat. This form of valve is used in deep-well pumps, where, 

in order to secure greater strength of parts, it becomes necessary to 

reduce the valve area to a smaller percentage of the cylinder crosssection area.

PISTON AND ROD.

The piston of a pump is usually packed by means of cup leathers 

held between disks in the piston. Cup leathers can not well be 

homemade, as special appliances are necessary for their manufacture, and they had best be bought of dealers. The cup leather should 

not exceed three-fourths of an inch in width on the wearing surface. 

The water pressure holds the leather against the walls of the cylinder 

with considerable friction. This friction amounts, approximately, in

DWH pounds to o , D being the cylinder diameter in inches, W the

o

width of the cup leather in inches, and H the lift of water in feet.
24 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

In a 6-inch cylinder, with a 20-foot lift, the piston friction will be

about 30 pounds, or 12 per cent of the weight of the water lifted.

i The piston friction, regarded thus as a percentage, is, approxi- "W

mately, -^. To show the amount of this piston friction, reference is

made to fig. 6, A. This diagram is from a pump having a 4-inch 

cylinder, a 14-inch stroke, and running at 10 strokes per minute. 

The suction lift was 30.8 feet, and the total lift was 38 feet. There 

was about 8 feet of water above the piston. The height y represents 

the pull on the rod due to the lifting of the 8 feet of water, the atmospheric pressure, and the weight of piston and rod, and to the overcoming of the friction of the cup leather.

The piston, once having left the water behind, is beyond the influence of the suction valve. The line y' represents the pull due to the 

load of nearly 8 feet of water, the atmospheric pressure, and the 

weight of piston and rod; but it does not represent in this case the 

friction of the piston, which, on the downstroke, tends rather to 

reduce the pull on the rod and to produce compression. The difference between y and y', therefore, represents twice the combined piston and water friction in the delivery pipe. At this speed the water 

friction in a straight pipe is very small, and the difference is almost 

entirely due to piston friction. In this case it amounts to 30 per cent 

of y. The piston friction was, therefore, 15 per cent of the whole 

work done, equivalent to about 18 per cent of the weight of water. 

The pump leather was three-fourths inch wide. By the above formula

W 

 yr- would give 18f per cent. The width of the packing leather is said

to influence the friction very little in heavy hydraulic work, but it 

seems to be important with the lighter pressures of ordinary pumping, 

s Piston friction is a large factor in the problem, varying nearly 

directly as the lift and inversely as the cylinder diameter. The tendency is to render the efficiency of the larger cylinders the higher. 

Since a single leather has been found insufficient for the prevention 

of leakage in pumps working in deep wells, two, or sometimes even 

three, are used. Where these leathers can not readily be procured 

they can be made by soaking good harness leather until pliable and 

then bolting it into a wooden form. To make the form, a board about 

three-fourths inch thick, having in it a hole of the same diameter as 

the pump cylinder, is nailed to a stiff backboard, and a cylindrical 

block, three-eighths of an inch less in diameter, is bolted concentrically within the circular opening. The bolts should be long enough so 

that the wet and pliable leather, laid over the hole, can be drawn 

down by the bolts and block, forcing tlie leather into position. The 

wrinkled edge of the leather can then be trimmed off, and when the 

whole is dry, removed and brought to a thin and even edge with 

a sharp knife. The friction of the piston leather should not be so
HOOD.] PISTON SPEED. 25

great that on the downstroke the piston will not return by its weight 

alone.

Metal rods joined by screw couplings are commonly used in such 

pumps. By using a large rod a differential action is obtained in the 

delivery, rendering more uniform the work between the upstroke and 

the downstroke. A stiff rod is necessary where water is delivered 

on the downstroke. Wooden rods, because of their elasticity, frequently give less trouble at connections than metal rods, and where 

delivery pipes are large enough they are sometimes preferred.

PISTON SPEED.

Four factors tend to limit the piston speed: First, the excessive 

initial shock of lift on the upstroke; second, the tardy closing of 

valves; third, incomplete filling of the cylinder; fourth, the rapid 

lowering of general pump efficiency as the speed is increased.

To give to a body of water rapid motion necessitates a greater 

expenditure of energy than would be necessary simply to balance its 

static pressure. The acceleration of motion of the water is greatest 

at the beginning of the upstroke, and, as the rotative speed of the 

crank increases, the acceleration and the force necessary to produce 

it also increases. In practice the quantitative importance of this first 

stress is found to be largely a matter of pump design. If the rod is 

short and the pump connections and frame very rigid, the stresses 

will increase to a high limit earlier than when the machine has a 

certain lack of rigidity. The yielding of windmill towers to the 

various shocks of pump operation is in those structures a means of 

keeping down, this stress. The extension and the elasticity of the 

pump rod also tend to soften the shock of starting the water column. 

The spring of parts is, therefore, in some degree, rather an advantage than otherwise, and the incorporation of a stiff spring into 

the pump rod would be advantageous.

In some of the pumps tested the pump rod had a length of about 40 

feet and the machinery was placed upon an unusually rigid floor. 

Fig. 11 shows the maximum stress for a number of pumps tested 

from this floor. The horizontal distances represent average piston 

speed in feet per minute. With the pump piston at rest, the pump 

rod supported a certain constant load. With the pump piston in 

motion, this load no longer remained constant, but varied, being 

greater at the beginning of the stroke and at the end usually less; 

and this variation was found to increase as the speed increased. In 

fig. 11 distances above the base line exhibit this increase of stress. 

Vertical distances represent the maximum load while running, 

expressed in percentages of the quiet load. For example, in the test 

of one 4-inch pump it appeared that at a speed of 40 feet per minute 

the maximum load on the rod was 175 per cent of the quiet load, 

while at a speed of 80 feet per minute it was about 200 per cent. In
26 TESTS OP PUMPS AND WATER LIFTS. {NO. 14.

the test of another 4-inch pump, at these same speeds the corresponding percentages were 200 per cent and 400 per cent. At piston speeds 

of 70 feet per minute the initial stress may be equivalent to from two 

and one-half to five times the weight of the water. The percentages 

are greatest where loads are light. Where the parts are not of ample 

proportions, or where they are loosely assembled, the shocks due to 

this initial stress soon destroy the machine.

The stresses shown in fig. 11 may in large part be due to the late 

closing of valves. In fig. 12, delayed and sudden application of the 

load after the piston had acquired a high speed, at one-tenth of its 

upward stroke, produced a much more severe shock than would have

Average piston speed, in feet per minute.

PIG. 11. Diagram illustrating relation between piston speed and pull.

been felt if the valve had closed earlier. The effect of this slow 

closing of large valves is shown by the upper line in fig. 11. In the 

case of the lower valve it produces a blow on the under side of the 

piston, and frequently the shock of this blow is such as to jar a spray 

at each stroke from the upper surface of the water in the delivery 

pipe.

Incomplete filling of the cylinder limits piston speed, as shown in 

figs. 5, B (p. 16), to 6, D (p. 17). There is no advantage to be gained 

in running faster than the cylinder can fill. The upward tendency 

of the water into the cylinder depends rather upon other forces which 

we have called "head." We have seen that "suction" is the name

1 Per cent of hydraulic pressure on the piston, representing maximum pull on the pump rod.
HOOD.] PISTON SPEED. 27

for an appearance rather than for an actual fact. The piston merely 

relieves the lower water column of load, and this column rises really 

under impulse from other agencies. It becomes the business, then, 

of the piston to keep the load that had held it down out of its way. 

Incomplete filling reduces the maximum stress nearly to that of a 

constant load, and indeed during the first part of the upstroke it 

results in more quiet running; but on the downstroke, on the other 

hand, with water and piston moving in opposite directions, it produces serious pounding.

Longer strokes admit of a much more rapid piston speed. This 

speed is limited by the number of times per minute the valves can 

open and close without serious shock and by the clear valve area. 

William Barr, in discussing steam pumps, says of the action of these 

valves: "The area of clear way through a set of valves in a water 

end should be not less than 40 per cent of the plunger area for speeds

FlG. 12. Dynamometer diagram of pump-rod stresses, showing excessive initial shock due to 

late closing of discharge valve.

of 100 feet per minute, 50 per cent for 125 feet, 60 per cent for 150 

feet, 75 per cent for 175 feet, and 100 per cent for 200 feet per 

minute." With the usual windmill speeds, not exceeding 30 strokes 

per minute, a stroke of 2 feet would give a piston speed of 120 feet 

per minute, and should be possible with pumps having 50 per cent of 

clear valve area. Steam pumps, as stated by Barr, have a low efficiency as compared with some of the best forms of irrigation pumps; 

and while the above speed is possible, the valve area for high efficiency should be larger still. It is impossible accurately to set limits 

to pump speed, because it depends upon valve design and upon length 

of stroke, which in turn vary greatly in different forms of pumps.

The individual peculiarities of various makes are well brought out 

in fig. 11. The 4-inch Frizell pump, which gave the lowest maximum 

stress, and therefore made record of smooth running, had a valve 

area of but 27 per cent, while the 8-inch Van Voorhis pump, which
28 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

had 97 per cent of valve area and a short stroke, was noisy. In 

general it may be said of a reciprocating pump that a speed of 100 

feet per minute is about all that should be expected. The following 

table shows the highest piston speed employed in the test of a number of irrigation cylinders. For a regular working speed it would be 

excessive

Speeds of piston in irrigation cylinders.

No. of fig. 

herein.

18

27

23

14

32

Diameter, 

in inches.

4

4

6

8

8

Stroke, in 

inches.

14.00

23.70

14.11

13.95

10.00

Speed, in 

feet per 

minute.

114

198

141

90

216

Weisbach says: "Usually the velocity of the piston is not over 78 

feet per minute, the common valve ranging between 40 and 60 feet, 

though piston velocities of 196 feet sometimes occur." In some highclass pumping engines speeds of 480 feet have been obtained.

While it is possible to run at a high speed, it may not, for practical 

reasons, be desirable to do so. By referring to the diagrams showing 

the efficiencies of pumps of various design it is seen that all are more 

efficient at slow speeds. A fall in efficiency of about 15 per cent up 

to 30 strokes per minute is to be expected, even in a good pump. A 

large pump run slowly will, therefore, work with small power and to 

better advantage than a smaller pump at a higher speed. For the 

very best results in connection with a windmill a higher gearing than 

the usual 3 to 1 would be advisable, the limiting factor being the 

increased expense of the larger size of pump thus made necessary.

DISCHARGE.

The discharge of a pump per stroke is measured by the capacity of 

the cylinder within the stroke length, less, however, the amount by 

which the cylinder may have failed to fill on the upstroke, and less, 

as well, those losses on the downstroke which will result from backslip of water past the tardily closing valve and from leakage through 

the valve after closing. The discharge of various cylinders tested is 

given in diagrams accompanying the description of each. Keuleaux 

gives the discharge, in per cent of the geometrical displacement, as 

92 per cent at a speed ranging from 27 to 40 strokes per minute, 95 

per cent at 50 strokes, and 98 per cent at 60 strokes. At slow speed 

the leakage reduces the discharge by an amount ranging from 1 to 5 

per cent. This loss diminishes, as a percentage, with increase of 

speed, but with high speed the loss from slow closing of valves 

rises and soon outweighs it. Weisbach states the loss to be from 5
HOOD.] EFFICIENCY OF PUMPS. 29

to 15 per cent, which seems excessive for such cylinders as have been 

tested by the writer.

Where the velocity of water is high, owing either to a high piston 

speed or to a small pipe, the discharge per stroke may ev^n exceed 

the cylinder capacity per stroke. The momentum of the rising water 

may be sufficient to hold the valves open for a brief interval after the 

completion of the upstroke, and thus for a moment to continue intake 

after the beginning of the downstroke. The paradoxical character of 

this effect is brought out by the discharge curves in figs. 19 (p. 32) and 

22 (p. 35), and by the stress diagram, fig. 13. This stress diagram is a 

record from the work of the pump shown in fig. 18 (p. 32), and indicates that the tension on the rod in that pump, under the conditions 

imposed, was relieved by the momentum of the rising column of 

water before the end of the stroke had been reached, and that this momentum impulse continued effective until the lower valve had closed, 

at A (fig. 13), on the return stroke. This same effect may be observed 

when the suction pipe is carried to a considerable horizontal distance, 

increasing the weight of the moving water. Unless a suction chamber is put. on in such 

cases, the suction pipe 

should increase in area 

directly as the length increases. Fig. 19 shows 

an example of the discharge being increased 

by a more rigid setting.

EFFICIENCY OF PUMPS.

The efficiency of a 

pump is that percentage 

of the effort expended 

which is returned in useful work as water lifted.

FIG. 13. Dynamometer diagram of pump-rod stresses, 

showing excessive discharge.

Efficiency will vary with the design, speed, and adaptation to the 

particular use. In small steam pumps the useful work done will 

account for only about 50 per cent of the power developed by the 

steam. Weisbach states the efficiency to be, "in well-designed 

pumps, working under favorable conditions, 80 per cent; in pumps 

of average perfection, 75 per cent; and in ordinary pumps, 70 per 

cent, and sometimes 65 per cent only." Mr. William O. Weber 1 gives 

the efficiency of reciprocating pumps as follows:

Efficiency of reciprocating pumps.

Lift (feet). . ........ 10

30

15

45

20

55

35

61

30

66

35

68

40

71

50

75

60

77

80

83

100

85

130

87

160

90

300

89

340

88

?<8fl

8fi

1 Trans. Am. Soc. Mech. Eng., TO! 7, p. 598.
30 TESTS OP PUMPS AND WATER LIFTS. [NO. 14,

To determine the usual range of efficiency for such pumps as are 

offered for irrigation purposes, and to determine what room there may 

be in them for improvement, the author has made something more 

than 1,000 measurements of various designs. The process by which 

were obtained the stress diagrams previously referred to affords a 

method for determining the amount of work, useful and otherwise, 

performed by the pump. By weighing the water discharged at various 

speeds and lifts a rating curve for each pump was obtained; and the 

useful work was determined by multiplying the weight of water discharged by the total lift. The 

diagrams show only the work 

actually performed by the pump 

rod, and therefore do not exhibit 

the ineffectual effort of the 

mechanism which transmitted 

power to the rod. The efficiencies are those of the pump cylinder and the pipes alone. They 

seem to show that some forms 

of the irrigation pumps tested 

here compare very favorably 

with those tested by others. 

Each pump has a particular 

sphere to which it is best adapted. No great increase of efficiency over the best now to be 

had is to be expected in any new 

form. Many of those now in 

the market could be much improved. The pumps represented in the drawings are typical, 

and by noting their performance, as shown in the following 

diagrams, the general range of 

efficiency of other pumps may 

often be closely approximated. 

The efficiency is seen to rise with increase of lift and to fall with 

increase of speed. The maximum efficiency is reached at lifts lower 

than those of Weber's table. Certain pumps may be expected to 

have an efficiency above 80 per cent at the usual speeds and at moderate lifts. Efficiency with such will but slightly increase, if at all, at 

lifts of more than 50 feet.

MARK PUMP.

Fig. 14 shows an 8-inch brass cylinder having disk valves with 

limited movement. It is made by the Mark Manufacturing Company, 

of Chicago, Illinois, and is specially designed for irrigation work.

FIG. 14. Vertical section of 8-inch brass cylinder 

with disk valves.
HOOD.] MARK PUMP. 31

discharged stroke. Poundsper 

W to»»\> 

4» IV) OJcp

__ 6£ OMETfi '/CAL DISPLA

k -^^

r£MEN\

^

 _ ^^ -

^I

10 15 20 25 30 35 40

Speed, in strokes per minute. Stroke, 13.94 inches.

FIG. 15. Discharge curve of 8-inch Mark pump.

100

80

70

60

a 50

10 15 20 25 30

Speed, in strokes per minute. Stroke, 13.94 inches.

35 40

PIG. 16. Varying-efficiency curve of 8-inch Mark pump, showing effect of varying height of lift 

and speed. (The line for 11.8 lift has been placed 10 per cent too high in the column 35-40. It 

should curve downward at the end and not cross the line 21.8.)
32 TESTS OF PUMPS AND WATEE LIFTS. [NO. 14.

The lower valve is limited in movement by a cross attached to a pendent spindle on the valve disk. This valve is leather faced and has a 

clear opening of 36 per cent of the piston area. The upper valve area

100

90

80

 § 70

I 60

50

4-0

30 5 IO 15 20 25 30

Weight of lift, in feet.

FIG. 17. Variation of efficiency with varying height of 

lift of 8-inch Mark pump at speed of 15 strokes per 

minute.

is 34.7 percent, the area between the edge of 

the disk and the cylinder walls is 53 per cent,

340

ST 3

(0 15 EO Z5 30 35 4-0

Strokes per minute. Stroke, 13.91 inches.

50

FIG. 19. Discharge curve of 4-inch Mark pump.

FIG. 18. Vertical section of a 

brass-lined cylinder of small 

Mark pump. and the area between the edge of the disk and

the valve seat is slightly in excess of the valve

area. The weight of the pump is 145^ pounds; of the piston and rod

alone, 67-| pounds. The pump rod was a three-fourths-inch pipe, and
HOOD.] MARK PUMP. 33

the delivery pipe was 6-inch. This pump is typical of the best design 

of those having large disk valves. It shows a very high efficiency at 

slow speeds, but a rapidly falling efficiency as the speed increases. 

Fig. 15 shows the discharge to be about 96 per cent of the geometrical 

displacement of the piston at a speed of 25 strokes per minute, but

60

7O

60

50

40

30

20

90

70

60

50

30

20

\

/£./?'

10 30 40 50- 10 20

Strokes per minute. Stroke, 13.91 Inches.

30 40 50

FIG. 20. Varying-efficiency curves of 4-inch Mark pump, showing effect of varying height of lift 

and speed. (The lines for 17.83 and 84 should not cross. The diagram is erroneous in this 

respect. The correct figures for these curves are given on pages 37,38.)

also shows that it has a falling rate beyond that speed. The efficiency 

is high for strokes fewer than 20 per minute, and at lifts exceeding 

10 feet. Fig. 16 shows the efficiency curves at five lifts, from 6| to 

feet.

IRK, 14 3
34 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

In fig. 17 the heavy vertical lines show the*range of efficiency at 

varying speeds at each lift, and the irregular line joining those points 

represents the efficiencies at a speed of 15 strokes per minute. It 

would seem from this diagram that a considerable increase of efficiency 

at a higher lift is not to be expected.

Fig. 18 gives a section of a brass-lined cylinder of the same make, 

which is typical of the better-made small pumps that provide for a 

suction and discharge pipe of less diameter than the cylinder. It has 

a 14-inch stroke, with a metal disk-valve carried in the piston. The 

upper valve area is 30 per cent of the cylinder area. The lower metal 

valve seats on a rubber ring. The lower valve area is 18 per cent. 

The suction and delivery pipes are 2-inch.

Fig. 19 shows two discharge curves of this pump. When rigidly

90

80

70

£

I 60

|

50

1 

£

4-0 

3O 

20

VL

10 15 20 Z5

Height of lift, in feet.

30 35

FIG. 21. Variation of efficiency with varying height of lift of 4-inch 

Mark pump at speed of 30 strokes per minute.

held, so that the rapidly moving water could not jar the pump and 

pipe, the discharge was greater than when simply suspended in the 

well, as usual. The discharge is greater than the geometrical displacement of the piston at speeds above 38 strokes per minute, owing 

to the high velocity of the water in a small pipe. The efficiencies at 

six different lifts are given in the tables, and in the diagram, fig. 20. 

The rapidly lowering efficiency shows the effect of small connections 

and of small valve area.

From fig. 21 the maximum efficiency seems to be reached at about 

a 25-foot lift. This pump was used in an interesting test which brought 

out the effect of varying the suction lift. The total lift suction and 

direct together was 38 feet. The cylinder was placed at different 

heights in the pipe, giving different heights of suction, ranging from
HOOD.] MAEK PUMP. 35

nothing to 30| feet. Fig. 22 shows the effect on the discharge of the 

varying suction lift. In all cases, as the speed increases, the tendency

ETR/CAL D/SPL ACEMt'NT

75'

30.85

10 15 20 25 30 35

Speed, in strokes per minute.

40 45 50 55

FIG. 22 Discharge curve for 4-inch Mark pump at a total lift of 38 feet and at various suction

lifts.

is to increase the discharge; but when the lift gets to be so great that 

the atmospheric pressure is unequal to the filling of the cylinder the 

discharge curve rapidly falls. This maximum rise of the curve is seen
36 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

to occur earlier with each successive increase in the suction lift. 

Figs. 5, B to 6, D (pp. 16, 17) give diagrams of stresses in the pumprod, and may be compared with fig. 5, A, which is typical of normal 

conditions. The tables present the results of suction tests.

Discharge of 8-inch Mark pump stroke, 13.94 inches.

Speed, i

10.................. .................

10...... .............................

15......................................

15 .... ......... .-..__.

30......-.... .......................

20.......... ............................

25

25.......... ............. .. . ..

30...... . ........... .... .......

30... ...... .......... ...... ..........

35 ...... . . ... . . .

35... ...... . .. ............

40.. ........... ...... ...... ..........

40.... ......................... ...- .

Discharge for 

15 strokes; 

lift, 6.5 feet.

367*

369*

Qfifll

368

368

365*

365

365

358

358

Qlfii

348

337*

352

Discharge for 

15 strokes; 

lift, 11.8 feet.

371

 WSQ

368*

363*

369*

367

369*

370*

367

361*

358

356*

359

357

Discharge for 

15 strokes; 

lift, 26. 5 feet.

356

QKK]

3KRL

357*

358

358*

355J

358}

351*

351f

Plotted 

average discharge per 

stroke.

24.30

24.30

24.30

24 266

24

23.60

23.20

1 Strokes per minute.

Figures from efficiency tests of 8-inch Mark pump; stroke, 13.94 inches.

LIFT, 6.5 FEET.

Speed.

10 

10 .........................

15... ...... ........ ..... in

20.... ..........................

20

25

25 ..

30... ...... ....... ...... ...

30 .................... .......

35 ...... .....................

35 

35.. ............. .............

35 . - - 

35 ...... - . 

40

40..... ... ... _ .

Discharge 

per 

stroke.

Pounds. 

24 300

24 300

24 300

24.300

24 300

24.300

24 266

24.266

24

24

23.600 *i fino

23.600

23 600

23.600

23.200

23.200

Footpounds 

of useful 

work.

leir QK

1W Q1

157.95

TK7 QK

157.95

157.95

157.73

157.73

156 iufi

153.40

153 40

153.40

153.40

153.40

150.80

150.80

Average 

pull on 

the rod.

Pounds. 

184.72

17Q fil

200

191.52

200

200.16

213.36

220 32

244.04

253 52

284 72

271.16

289.80

259.32

266 94

325.38

320.04

Footpounds 

of work 

given to 

the rod.

214.28

208.38

233 36

223 16

232 36

233 50

 M7 KO

255.57

383.08

392 93

330.38

314. l»K

336.17

300.81

309.65

377.44

371.25

Mechanical efficiency.

Per cent. 

73.7 if\ i

67.9

71.1

67 9

67.8

63.7

61.3

55.1

53.2

46.4

48.7

45.6

50.9

49.5

39.7

40.5

Maximum 

tension 

on the 

rod.

Pounds. 

312

648

664

738

Minimum 

tension 

on the 

rod.

Pounds.

72

 72

80

108

LIFT, 11.8 FEET.

10....--. .............. ......

10 ........ ....... .. .......

15 ... .. .

15 

20 .

30

25

25 _ .. .....

30. ...... ....... ... ....

30... . 

35 

35... . 

40

40 

34.30

34.30

34.30

24.30

24.30

24.30

24 266

34 266

24

24

23.60

33.60

23.20

23.20

286 74

286 74

386.74

386 74

286.74

286 74

286.34

286.34

283.20

283.30

278.48

278.48

373.76

373.76

293.60

390.60

397

398.05

308.50

305.55

311.95

311.95

328.95

335.45

346.80

346.80

384.60

395.30

340.58

337.10

344.53

345.74

357.86

354.44

385.06

385.06

381.58

389.12

402 39

403.39

446.14

458.55

84.3

85

83.3

83.9

80.3

80.8

74.3

74.3

74.2

73.8

69.3

69.3

61.3

59.4

480

650

700

1,140

70

 35

50

 100
HOOD.] MARK PUMP. ' 37

Figures from efficiency tests of 8-inch Mark pump; stroke, 13.94 inches Cont'd.

LIFT, 16.75 FEET.

Speed.

10......... ................. ....

10...... ..................... ...

15..............................

15... ......................... ..

20..............................

20..... ........................ .

25

25

30...... ...... ............ ......

30..... .........................

35...... ...... .................. in

40..............................

Discharge peistroke.

Pounds. 

24.30 24 '30

24.30

24.30

24.30

24.30

24. 266

24.266

24.00

24.00

23.60

23.20

23.20

Footpounds 

of useful 

work.

407 03

407.03

407.03

407.03

407.03

407.03

406.47

406.47

402.00

402.00

395.30

388.60

388.60

Average 

pull on 

the rod.

Pounds. 

436 22

419. 85

435.90

429.45

445.50

441.97

458.32

467.92

477 52

529.72

555.30

558.45

564.82

Footpounds 

of work 

given to 

the rod.

494 68

487 45

506.08

498. 16

516. 78

512. 66

531.66

543.79

552.93

619.48

644.15

647.80

655.30

Mechanical efficiency.

Per cent. 

82.3 sf; i

80.4

81.7

78.7

79.5

76.4

74.8

72.5

63.9

61.3

59.9

59.3

Maximum 

tension 

on the 

rod.

Pounds. 

585

900

1,170

1,245

Minimum 

tension 

on the 

rod.

Pounds. 

60

0

 150

150

LIFT, 21.8 FEET.

10...... ............ ...........

10.......... ........ ............

15 ......... .......... .

15 .............. .. _ ... .

30

20. ....... ...................

25 - - -. . 

25

30 -- - . .., 

30 - - 

30~~ - - . -

35. ... ......... ...........

35. . 

24.300

34.300

24.300

34.300

34.300

34.300

34.266

34.366

24.000

34.000

24.000

23.600

23.600

529.74

529.74

529 74

529 74

529.74

529.74

529.01

529.01

523.30

523 30

523 20

514.48

514. 48

536.18

536.18

539.47

539.47

549.30

546.00

582.34

583.65

595.35

595.35

585.52

684.15

707.17

607.67

607.67

611.40

611.40

622.54

618.80

659.87

661.47

674. 73

674.73

663.59

775.37

811.46

87.1

87.1

86.6

86.6

85.1

85.6

80.2

79.9

77.5

77.5

78.8

69.8

67.5

825

960

997.5

1,387.5

75

75

-57.5

 165

LIFT, 26.5 FEET.

10 .. ......... .......

10 - . . -.. 

15.-.. . .. ... ...........

15 . , .

20.. ...... ................. .... .

20 

25 - -- . -

25 - . .... .......

30.... ....... .............. .....

30...-. ............ .............

24.300

24.300

24.300

24.300

24,300

24.300

24.266

24 266

24.000

24.000

643.95

643.95

643.95

643.95

643. 95

643.95

643.06

643.06

630 00

630.00

684. 15

680.85

677.62

674.33

694.05

697.35

720.37

740.77

786. 15

801.67

775.37

771.83

767.97

764.23

786. 59

790.33

816. 42

839.44

890.97

908.56

83.5

83.6

83.8

84.2

81.8

81.4

78.7

76.6

71.3

69.9

997.5

1,275

45.0

 37.5

Discharge of 4-inch Mark pump at various speeds and lifts.

Speed.

10.... ... ......................... .*.... 

10.-....-.. ............ ................

15. ............. . ..--_ ........

15... ............ ........ .......

20. ............ ........ ...... 

20 . ...... ......... .......... .......

35.----.-. ..........................

25

30----... .........................

30..... ...................................

35..-..-. ... ....... ................ ....

35. ...... ............ ........ ..........

40 ....... ...... .......... ...,. .

40........................................

45------.-.. .... ................... ....

45-..-.-.-. ...... ...... ._ . . 

50. ........... ...............

50......................... ..............

Discharge, in pounds, for 50 strokes for lift:

6.17 feet.

309.5 

306.5 

306 

306 

306 

305.5 

303 

305.5 

308 

306 

309 

309 

306 

306.5 

300 

301

12.17 feet.

311 

309.5 

312 

309 

310.5 

310.5 

310.5 

308 

308 

307 

308.5 

308.5 

309.5 

308.5 

312 

310.5 

314.5 

313.5

24.2 feet.

304 

303.5 

305 

305.5 

308 

308.5 

309 

308.5 

312.5 

309.5 

310 

311 

311.5 

309 

321 

328.5

30.17 feet.

307 

307.5 

309 

308 

307 

308 

307 

309.5 

309 

307 

307 

308.5 

311 

313

Average 

discharge, 

in pounds, 

per stroke by discharge 

curve.

6.146

6.148

6.152

6. 156

6.16

6.17

6.192

6.24

6.28
38 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Discharge of 4-inch Mark pump at various lifts and speeds; pump cylinder

heavily weighted.

Speed.

10...... ......

10............

11

15- , ------

20-. ,- ..

20.. .......

25 -----

25 - 

30.- - 

Discharge, in pounds, 

for 50 strokes for lift:

30.17 feet.

308.5 

308.5 

311.5 

312 

311.5 

312 

312 

310.5 

313

36.3 feet.

305.5 

303.5 

308.5 

307 

308.5 

307.5 

308 

309 

309.5

Average 

discharge, 

in pounds, 

per stroke by discharge 

curve.

6.16

6.192

0.196

6.198

6.304

Speed.

30-.-. ------

35---.-.-.-.

OK

40

40-...-.-...

45

45 -- 

50..--..-.-.

50..-- ---

Discharge, in pounds, 

for 50 strokes for lift:

30. 17 feet.

311.5 

311 

31 1 ^

314. 5

317 

333 

338 

339.5 

341

36.3 feet.

310 

310.5 

310.5 

331 

316 

. 338 

329 

331.5 

337

Average 

discharge, 

in pounds, 

per stroke by discharge 

curve.

-

6.33

6.34

6.584

6.744

Figures from efficiency tests of 4-inch Mark pump; stroke\ 13.91 inches.

LIFT, 6.17 FEET.

Speed.

10... --. ... ..,-.. . ___

10 ....... ... .. ...... ....... ......

15. . . ...

15...... ...... -- . _ _ ._..

20...... ....... .. _.. __.-._.

20

20 .. .-...- ...........

25

25. .. _ _._ ... . ......

25......... ... ... ....... .......

30

30 . _-_ .._ ., . ,. .. .-

35... ....... ...... . . ..... .

35 -. . . . . ......

40 . 

40

45 _, . ..

45 

48 _ __ . .. . .

Discharge 

per 

stroke.

Pounds. 

6.146

6 146

6.148

6.148

6.152

6.152

6.153

6.156

6. 156

6.156

6.16

6.16

6.17

6.17

6.192

6.193

6.34

6.24

6.27

Footpounds 

of useful 

work.

37.92

37 09

37.94

37.94

37.96

37.96

37.96

37.98

37.98

37.98

38.01

38.01

38.07

38.07

38.21

38.21

38.5

38.5

38.69

Average 

pull on 

rod.

Pounds. 

60.58

60.58

59.62

59.68

60.58

59.23

72 44

71.47

75

82.37

83.97

86.86

86.86

88.5

89.42

117.4

131.8

173.3

Footpounds 

of'work 

given 

to rod.

70.21

 69.46

70.21

69.1

69.17

70.21

68.65

83.95

82.84

78.13

95.47

97.33

100.7

100.7

102.5

103.6

136.1

152.8

200.9

Mechanical efficiency.

Per cent. 

54

54 6

54

54.9

54.8

54

55.3

45.2

45.8

43.6

39.8

39

37.8

37.8

37.2

36.8

28.2

25.2

19.2

Maximum 

ptill on 

rod.

Pounds. 

81

107

133

158

159

294

LIFT, 12.17 FEET.

10 .. ..... ............

10...... -- .. _.. . ... ...

15----......... ... . ............

15 . .... .....................

30. ..................................

20 ............ . .... .....

25. .................... .. ____-

^>. ................ ......................

30.... .................................. ..

30........ . ........ ....... ...

35 .

35.. . ______ ....... .................. -..

40 . ._. ....

40....... . . . ........

45. ... .. .. . .......

45-.,.-... ........ ................_.-.

50... ....... ... . .

50- ... .

6.146

6.146

6.148

6.148

6.152

6 152

6. 156

6.156

6.16

6.16

6.17

6.17

6.192

6.193

6.84

6.34

6.38

6.28

74.8

74.8

74.82

74 82

74.87

74.87

74.93

74.93

74.97

74.97

75.09

75.09

75.3

75.3

75.94

75.94

76.4

76.4

93

93.6

97.7

97.7

110.7

113.6

120 2

134.3

136.6

139.1

140.1

146.5

150

166.7

165. 4

187

183.7

107.8

107.3

113.4

113.4

138.3

131.7

140

139.3

144.1

146.7

161.3

162.4

169.8

173.8

193.2

191.7

216.8

211.7

69.3

69.6

65.9

65.9

56.8

53.5

53.7

53

51

46.5

46.2

44.4

43.3

39.3

39.6

35.2

36.1

117

159

147

223

255

300

366

372
HOOD.] MARK PUMP. 39 

Figures from efficiency tests of 4-inch Mark pump; stroke, 13.91 inches Continued.

LIFT, 17.83 FEET.

Speed.

10 .- .._ ...... ._ ., 

10........................................

15.... ...... ............ ................

15..... ........"........................

20............... ......................

20...... ............... ................

25........................................

25 .........................................

30... .....................................

30.... ....................................

35.......... ..............................

35... .............. .......................

40......... ...............................

40-... ...... ..............................

45...........

45........ ................................

50........................................

50... .....................................

Dis 

charge 

per 

stroke.

Pounds. 

6.146

6.146

6.148

6.148

6.152

6.152

6.156

6.156

6.16

6.16

6.17

6.17

6.192

6.192

6.24

6.24

6.28

6.28

Footpounds 

of useful 

work.

109.6

109.6

109.6

109.6

109.7

109.7

109.8

109.8

109.8

109.8

110

110

110.4

110.4

111.3

111.3

112

112

Average 

pull on 

rod.

Pounds. 

119.5

121.5

126.1

130.5

139

135.7

137

148.7

162.9

175.1

183.5

175.6

184.3

189.4

211.8

213.7

239.5

257.5

Footpounds 

of work 

given 

to rod.

139

140.9

146.1

151.3

161.1

157.3

158.8

172.4

188.8

202.9

212.6

208.3

213.6

219.6

245.5

248.7

277.6

298.4

Mechanical efficiency.

Per cent. 

79.1

77.8

75

72.4

68

69.7

69.1

63.7

58.1

54.1

51.7

53.8

51.7

50.3

45.-3

44.9

40.3

37.5

Maximum 

pull on 

rod.

Pounds. 

210

225

264

270

375

411

432

420

489

555

684

LIFT, 242 FEET.

10........................................

10.........................................

10........ .............................

15........... .............................

15.... ....................................

20 ................... ...... ...........

20. ....................................

25........................................

25

30.....-. ......... ......... ..........

30. ...... ....... .. ... 

35. ....................................

35. ....................................

40....-... ............................

40... . ........................... ....

45.... .. ............ ..................

45.... ........ .........................

45...... . . ...,. ......

45 . .. ...__. _ __ .__._..

50........................................

50. ....................................

6.146

6.146

6.146

6.148

6.148

6.152

6.152

6.156

6.156

6.16

6.16

6.17

6.17

6.192

6.192

6.24

6.24

6.24

6.24

6.28

> 6.28

148.7

148.7

148.7

148.8

148.8

148.9

148.9

149

149

1.49.1

149.1

149.3

149.3

149.8

149.8

151

151

151

151

152

152

150

157.2

147.4

156.5

156.5

161.1

161.1

177.3

174.7

188.8

191.4

215.3

200.4

262.7

244.6

243.6

242.4

275.8

257.5

267.2

274.7

173.8

182.2

170.8

181.4

181.4

186.7

186.7

205.5

203.5

218.8

221.8

249.5

232.3

304.4

283.5

382.3

281

319.6

298.4

309.5

318.4

85.5

81.6

87

82

82

79.7

79.7

72.5

73.6

68.1

67.2

59.8

64.2

49.2

52.8

53.5

53.7

47.2

50.6

49

47.7

noo

234

225

255

258

385

285

348

345

447

471

558

501

720

669

665

640

760

775

775

LIFT, 30.17 F.EET.

10.-.... - - -.....

10.......... ............................ ~\&...... ..................................

ti>...... ..................................

20............................... ........

20

26 ...... ..............................

25

30 ...................................

30.... ...... ............ ..................

35........................................

35. ................................. ......

40........................................

40........................................

45....

45........................................

6 146

6.146

6.148

6.148

6.152

6.152

6.156

6.156

6.16

6.16

6.17

6.17

6.192

6.192

6.24

6.24

185.4

185.4

185.5

185.5

185.6

185.6

185.7

185.7

185.8

185.8

186.1

186.1

186.8

186.8

188.2

188.2

195.6

191.3

198.9

200

206.7

206.7

208.9

211

235.9

234.8

255.4

257.6

260.8

265.1

283.4

288.8

226.7

221.7

230.5

231

239.6

239.6

242

244.6

273.4

272.2

296

298.5

302.3

307.3

328.5

334.7

81.7

83.6

80.4

80

77.4

77.4

76.7

75.9

67.9

68.2

62.8

62.3

61.8

60.8

57.3

56.3

300

305

360

345

380

390

410

410

535

535

650

675

675

700

830

320
40 TESTS OP PUMPS AND WATEE LIFTS. [NO. 14.

Figures from efficiency tests of 4-inch Mark pump; stroke, 13,91 inches Continued.

LIFT, 30.17 FEET. 

[Pump heavily weighted.]

Speed.

10......... ........................... .

10... - -- - 

15... ............................... ...

15. - - - - - 

20.... - . .- - -- - 

20 ------------------------------------

25......... ...... ........ -__.__ . .

25... . -. -.-. . --.. ..

30--..--------------. ------------

30- -. - - .-- .

35 ....

35. - - - 

40 . .-. . --. .-. ------

40-.- --..--- --- - -... .

4&.. ......................................

4&.... ....................................

^..... ...................................

Discharge 

per 

stroke.

Pounds. 

6.16

6.16

6.193

6.192

6.196

6.196

6.198

6.198

6.204

6.204

6.23

6.23

6.34

6.34

6.58

0.58

6.744

Footpounds 

of useful 

work.

185.8

185.8

186.8

186.8

186.9

186.9

187

187

187.2

187.2

187.9

187.9

191.2

191.2

197.6

197.6

203.5

Average 

pull on 

rod.

Pounds. 

195. 9

194.8

204.3

203.2

316.3

213

222.8

220.6

240.3

245.7

248.9

254.3

281.2

285.5

318.7

314.1

356.8

Footpounds 

of work 

given 

to rod.

227

225 8

236.8

2a5.6

250.7

246.9

258.2

255.7

278.5

284.7

288.5

294.7

326

330.9

369.4

364

413.6

Mechanical efficiency.

Per cent. 

81.8

82.3

78.8

79.3

74.5

75.7

72 4

72.7

67.2

65.7

65.1

63.7

58.6

57.8

53.7

54.5

49.2

Maximum 

pull on 

rod.

Pounds. 

315

305

350

350

410

415

490

480

575

595

620

615

730

755

880

845

1,000

LIFT, 36.3 FEET. 

[Pump heavily weighted.]

10. .- .... -. . _._---... ....

10.....---- -- ------ ------ -. 

15....,.. - -- -.-. -

15. -.-- ----------

20

20 - ..- - .- -- . 

25

25

30-... ---------------------- -----

30. .. . ........ . ... - .

35 . ..... ...... ......

35.-..---.---.. ----------------

40 - - -- ... ---. ...

40.. .. ........ -..... . 

45 ....

45. ---------------------------- -----

50 .. .- - - 

50. .......................................

50

50--.. ----------------------- ----

50....-_- ----------------

6.16

6.16

6.192

6.192

6.196

6. 196

6.198

6.198

6.204

6.204

6.23

6.23

6.34

6.34

6.584

6. 584

6.744

6.744

6.744

6.744

£.744

233.6

223.6

224.8

224 8

224.9

224.9

335

225

225.2

2^5 3

226 1

226.1

230.2

230.3

239

239

244.5

244.8

244.8

244.8

244.8

244.6

245. 6

253.3

356.5

263

25Q 7

272 7

273.8

387.7

396.3

307.9

306.9

335.8

360.5

367

418 5

391. 6

403.4

403. 4

409.9

283.5

284.7

293.5

297.3

304.8

301

316.1

317.3

333.5

343.4

356.9

355. 7

389.3

398

417.9

435. 3

485

453.9

467.6

467.6

475.1

78.9

78.5

76.5

75.6

73.8

74.7

71.1

70.9

67.5

65.5

63.3

63. 6

59.1

57.8

57.2

54.9

50.4

53.9

52.3

52.3

51.5

355

350

<u f\

440

465

465

560

vtn

680

700

760

760

875

925

925

985

1,035

1,000

1,050

1,065

.1,000

Plotted averages of discharge per stroke, suction test of 4-inch Mark pump.

Discharge, in pounds, per stroke.

Speed.

10-....... ...........

15 - -. --.. .......

20--- - ---

25 ...

30..... ..... . ......

35. . - - 

40- . ... 

45. --. ...

50. .--- -

Total lift, 

38 feet; 

suction lift, 

30.85 feet.

185.5

172.5

79.5

25.5

7.5

Total lift, 

37.96 feet; 

suction lift, 

24.77 feet.

6.11

6.154

6.15

6.996

5.730

Total lift, 

38 feet; 

suction lift, 

18.77 feet.

6.21

6.226

6.23

6.234

6.256

6.46

6.024

Total lift, 

37.96 feet; 

suction lift, 

12. 77 feet.

6.16

6.168

6.176

6.184

6.192

6.2

6.266

6.754

6.78

Total lift, 

37. 92 feet; 

suction lift, 

6. 73 feet.

6.13

6.16

6.168

6. 174

6.178

6.184

6.250

6.56

6.68

Total lift, 

37.93 feet; 

suction lift, 

0.6 foot.

6.14

6.15

6.156

6.16

6.164

6.184

6.34

6 1Rft

6.706
HOOD.] MARK PUMP. 41

Discharges of 4-inch Mark pump at various suction lifts and speeds.

Speed.

10. ........... ........... .....

10 . 

15............................

15. ................... ........

20.... ........................

20............................

25

25

30............................

30.. ..........................

35 ........................ ....

35 ......................... ...

40.... .................... ....

40............................

45

45

50 ........................ ....

50............................

Discharge, in pounds, for 50 strokes.

Total lift, 

38 feet; 

suction 

lift, 30.85 

feet.

185.5

173.5

79.5

25.5

7.5

Total lift, 

37.96 feet; 

suction 

lift, 24.77 

feet.

306 

305 

310.5 

305 

308.5 

306.5 

299.5 

300 

290 

283.5

Total lift, 

38 feet; 

suction 

lift, 18.77 

feet.

311.5 

309.5 

311 

312 

313.5 

310 

313 

311 

312.5 

313 

323 

323 

301.5 

301

Total lift, 

37.96 feet; 

suction 

lift, 12.77 

feet.

308.5 

307.5 

306.5 

309.5 

307.5 

310 

310.5 

309 

308 

309 

311 

309 

312.5 

314 

H37.5 

338 

340 

338

Total lift, 

37.92 feet, 

suction 

lift, 6.73 

feet.

306.5 

306.5 

307.5 

306.5 

309 

309.5 

308.5 

308.5 

309 

309 

309.5 

309 

312.5

328

334

Total lift, 

38. 08 feet; 

suction 

lift, 0.6 

foot.

306.5 

307.5 

307 

308 

308.5 

307 

307 

309.5 

308 

307 

311.5 

307 

318.5 

318.5

331.5 

339

Figures from suction test of J^vnjQh, Maria pump. 

TOTAL LIFT, 38.08 FEET; SUCTION" LIFT, 0.6 FOOT.

Speed.

10. ................................... ....

10. ...................................... .

15............. ....................... ....

15 ...........,.........................

20.... ....................................

20

20....... ............................. ....

25........................................

25-- ............... .............. ...

30...... ..................................

30 .................................. ......

35 .

35 

40 

40.........................................

45 .

45

50. ........ .... .... 

50 .... ........... ............. ........

Discharge 

per 

stroke.

Pounds. 

6.14

6.14

6.15

6.15

6.156

6.156

6.156

6.16

6.16

6.164

6.164

6.184

6.184

6.34

6.34

6.556

6.556

6.706

6.706

Footpounds 

of useful 

work.

233.8

233.8

234 2

234 2

235 4

235.4

235.4

235.5

235.5

235 7

235.7

235.6

235.6

241.4

241.4

249.6

249.6

255.4

255.4

Average 

pull on 

rod.

Pounds.

OKO O

356.6

357 7

357.7

263 1

267.5

264 2

275.1

276.1

297.8

316.3

322.8

340.2

a59.3

368

394

390.7

415.6

418.8

Footpounds 

of work 

given to 

rod.

293.6

297 4

398.6

398.6

3f>A Q

310

306.2

318.8

320

345.2

366.6

374.2

394.3

416.4

426.5

456.6

452.8

481.7

485.4

Mechanical efficiency.

Per cent.

70 R

78.6

78.4

78.4

76.8

75.6

76.5

73.5

73.3

68

64

63.9

59.7

57.9

56.6

54.6

55.1

53

52.6

Maximum 

pull on 

rod.

Pounds. 

350

370 <wn

400

460

470

470

530

530

710

760

780

860

910

920

990

1,000

1,030

1,030

TOTAL LIFT, 37.93 FEET; SUCTION LIFT, 6.73 FEET.

10 ................................ 

10 

15 ....... . . .. -

15... ............ .. .... .. ...

^. .......................................

20

25

^&.... .................................. ..

30...... ..... ................... ..........

30.. .. ... . ............

35 _ . .......... ......

35 ........ ........... .. . . 

40

40 . .. __.__._._. ...... ...... - 

45........................................

45 ......... .. .... . .

60 . . 

80 ... 

6.13

6.13

6.16

6.16

6.168

6.168

6.174

6.174

6.178

6.178

6.184

6.184

6.25

6.25

6.56

6.56

6.68

6.68

232.4

232.4

233.6

233.6

233.9

233.9

234.1

234.1

234.2

234.2

234.5

234.5

237

237

248.8

248.8

253.3

253.3

245.1

243.5

256.5

355.5

366.4

270.7

287.1

292.6

302.2

315.2

332.2

332.2

359.9

381.5

422.4

404.1

468.8

473

384

282.3

297.3

396.1

308.7

313.8

332.8

339.1

350.2

365.3

385.1

385.1

416.9

442.1

489.6

468.3

543.3

547.1

81.8

82.3

78.5

78.9

75.7

74.5

70.3

69

66.9

64.1

60.9

60.9

56.8

53.6

50.8

53.1

46.6

46.3

380

375

435

435

490

505

585

630

660

720

785

800

870

950

1,005

960

1,160

1,050
42 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Figures from suction test of 4-inch Mark pump Continued.

TOTAL LIFT, 37.96 FEET; SUCTION LIFT, 12.77 FEET.

Speed.

10 ............. ........................

10. .................................. .....

15............. .........................

15 ........ ............ ... ..... .

20-................. ........... ......

20

25 .. . ...... -- .. ..

25........ . ...... ..... ......

30-.... ..............................

30 ............. ............ ...........

35. . . . ....... . 

35.. ............ ......................

 40. .... ...-....... .........

45 . . ......... ..............

45...... ..............................

45............ .........................

45...... ..................................

50..-..- . . ....... ......

50. .................... ............

Discharge 

per

stroke.

Pounds. 

6.16

6.16

6.168

6.168

6.176

6.176

6.184

6.184

6.192

6.192

6.2

6.2

6.266

6.754

6.754

6.754

6.754

6.78

6.78

Footpounds 

of useful 

work.

233.8

233.8

234

234

213.8

213.8

234.7

234 7

235

235

235.4

235.4

237.9

256 4

256.4

256.4

256.4

257.4

257.4

Average 

pull en 

rod.

Pounds. 

254.4

252 2

256

260 4

263.1

264.2

277.3

282.8

301.3

299.1

319.6

318.5

394.6

414.1

407.6

439.1

430.4

431.8

443.7

Footpounds 

of work 

given to 

rod.

294.8

292.3

296.7

301.8

304.9

306.2

321.4

327.7

349.2

346.7

370.4

369.1

457.3

480

472.4

508.9

498.9

500.5

514.3

Mechanical efficiency.

Per cent. 

79.3

80

78.9

77.5

76.8

76.5

73

71.6

67.3

67.8

63.5

63.7

52

53.4

54.2

50.3

51.4

51.4

50

Maxi- - 

mum 

pull on 

rod.

Pounds. 

370

380

410

410

460

440

560

560

650

640

715

705

915

885

885

1,000

TOTAL LIFT, 38 FEET; SUCTION LIFT, 18.77 FEET.

10. ...... ........................... 

10 ..... ............. ....... .

15. . . .. ...... ..........

15 ........ _. .

20 . .. . . ..... .

20 ...... ....... .................

25-....-..... ......... ... ......

25

30 . . . 

30 . -. --....... __..... .

30 .............. ...... ...... ..........

35 ...- ... . ....... ...........

35 . ........ ...... ...... .

40. ...... ......... . .... 

40

40 . ........ .................

40 ...... ..... ... .................

6.21

6.21

6 226

6 226

6.23

6 23

6.234

6.234

6.256

6.256

6.256

6.46

6.46

6.024

6.024

6.024

6.024

236

236

236.6

236.6

236.7

236.7

236.9

236.9

237.7

237.7

237.7

245.5

245.5

225.7

225.7

225.7

225.7

239.1

241.2

254 4

250

268.5

264.1

271.7

271.7

302.2

302.2

303.8

350.2

340.5

365.7

355.9

364.6

364.6

277.1

279.6

294.8

289.8

311.2

306.1

314.9

314.9

350.2

350.2

352.1

405.9

394.7

423.9

422.1

422.6

432.6

85.1

84.4

80.2

81.6

76

77.3

75.2

75.2

67.8

67.8

67.5

60.4

62.2

54

55.5

54.1

54.1

310

325

385

465

440

485

490

550

555

570

725

765

830

870

TOTAL LIFT, 37.96 FEET; SUCTION LIFT, 24.77 FEET.

10...... . ... .......... ..... . ..

10.... ... .. .......... ..... .

15. ...... ...... ...... ..................

15 ......... .. . . ..

20. . .. .. ............

20

20

20 . .... .- ..............

20

25. ...... ._....._ 

25

25

25

25 ...... ................ ............

30 ....................................

30. ...... .- ...... ........

6.11

6.11

6.154

6.154

6.15

6.15

6.15

6.15

6.15

5.996

5.996

5.996

5.996

5.996

5.73

5.73

231.9

231.9

233.6

233.6

233.5

233.5

233.5

233.5

233.5

227.6

227.6

227.6

227.6

227.6

213.7

213.7

240.1

241.2

250

248.9

258.7

268.4

269.5

273.8

259.8

291.7

291.5

286

287.1

292.8

279.5

270.7

278.3

279.6

289.8

288.5

299.9

311.1

312.3

317.4

301.1

338

337.8

331.5

332.8

339.3

323.9

313.8

83.3

82.9

80.6

80.9

77.8

75

74.7

73.5

77.5

67.3

67.3

68.6

68.4

67

65.9

68.1

290

285

310

305

345

365

370

375

345

425

500

415

525

405

585

475

TOTAL LIFT, 38 FEET; SUCTION LIFT, 30.85 FEET.

10 ....... ..............................

10. ............ ................

15 ............. ....... ................

15.......... ..............................

20

20

25... ..................... .... ..

25 ........ ........................ ....

30.... .................................

30 ...... .......... . ._._._. ....._.

3.71

3.71

3.45

3.45

1.59

1.59

.516

.516

.14

.14

141

141

131.1

131.1

60.4

60.4

19.6

19.6

5.32

5.32

178.3

178.3

165.2

175

116.8

125

96

102.6

109.8

81.1

206.6

206.6

191.5

202.8

135.4

144.9

113.9

118.9

127.2

94

68.2

68.2

68.4

64.6

44.6

41.7

17.21

16.4

4.1

5.6

265

265

265

265

270

270

270

275

285

295
HOOD.] EFFICIENCY OF PUMPS. 43

FRIZELL PUMP.

Fig. 23 represents a piston pump having a valve chamber surrounding the cylinder, and containing eight small clack discharge valves.

PIG. 23. Vertical section of piston pump with valve chamber surrounding cylinder.

The suction valve is a heavy disk valve, playing in a special suction 

chamber, guided at its circumference, and not limited in its rise. It
44 TESTS OP PUMPS AND WATER LIFTS. [NO. 14.

is arranged to withdraw through the cylinder if necessary. On the 

upstroke water is drawn into the cylinder through the suction valve;

12.6

10 15 20 45 50 

FIG. 24. Discharge curve of 6-inch Frizell pump.

35 30 30 40

Strokes per minute. Stroke, 14.11 inches.

on the downstroke this water is forced through the delivery valves 

into the space above the piston, and is lifted on the next upstroke.

so1

10 .20 25 30 35 4O

Strokes per minute. Stroke, 14.11 inches.

FIG. 35. Varying-efflciency curves of 6-inch Frizell pump, showing effect of varying height of

lift and speed.

The suction-valve area is 59£ per cent, of the cylinder area; the cylinder diameter, 5.74 inches; the upper valve seat area, 29.7 inches, or
HOOD.] FRIZELL PUMP. 45

3.8 inches more than the cylinder area; the weight of the pump, 270 

pounds, and the weight of piston, rod, etc., 62 pounds. This pump 

was designed especially for irrigation purposes, and is known as the 

"Frizell" pump. It is remarkable for its sustained efficiency at high 

speeds. So far as tested the speed was limited only by the ability of 

connections to stand the work. Fig. 24 gives the discharge per stroke, 

which reaches a maximum of 95^ per cent of the geometrical displacement. Fig. 25 shows efficiency curves for five lifts. The small dif100

. <cO

CDO

-4O

10 IS ZQ

Height of lift, In feet.

25" 30 35

FIG. 26. Variation of efficiency with varying height of lift of 6-inch 

Frizell pump at speed of 20 strokes per minute.

ference of efficiency at different speeds is due to the employment of 

large valve areas and small quick-closing valves. Fig. 26 shows that 

efficiency varies with the lift, being at its best probably at about 25 

feet. The tables present the details of the tests.

Discharge of 6-inch Frizell pump at various lifts and speeds.

Speed.

10.......... . .. 

10....... . ............................

15........ ............................

15- .......... ........ .................

20 ...... ..........................

20 

25. --.. 

25 

30. .. . ... ............ .......

30-.. ......... ........ ...........

35. ...... 

35. ..... .... .. ..... ................

40....... ...... .. ........ .. . .

40 

45 

45 

50. ......

50-.-.... 

50...... .. .. ........... .........

55 .. 

55.. . . .. .......... ........

60............................. ..........

60. ...................................

Discharge in 

30 strokes, lift 

7.66 feet.

070

377 077

379

OWtV

0701

QQO

375

379

374

371

379

376*

374

373

377f-378

380-379

371f-374

363

371 -370

373

371 -371

Discharge in 

30 strokes, lift 

13.66 feet.

367

371

07-1

QTQl

372i oirn

370

366i

369

371

365

370

365*

3ft!vX

367

373

364

364

359

361

357

Discharge in 

30 strokes, lift 

33.75 feet.

OfVrt*

070

380

383£

001 I

380

383

OQ1 i

3T6

377i 3741

070

374.1

376

373

370J

369

Plotted averages 

per stroke.

13.50

1*> Kfi

-lo Krf

13.55

13.53

13.47

13 44

13 40

1 O oft

13.30

12.23
46 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Figures from efficiency tests of 6-inch Frizell pump; stroke, 19.^ inches.

LIFT, 7.66 FEET.

Speed.

10.-..... ....................

10..............................

15.-........... ..............

15 .

20....... ....................

^d...... ........................

35 ...........................

35

dO.... ..........................

30 . . 

m..-. ....................... ...

35. ............................ ffi..... .........................

40-.-.-----.- .. ......... ...

^>.... ..........................

45 .....,.... ........

50 -- - - . 

50--. ........ .... . .....

55. . 

55 

60-.- .... ..........

60 .

Discharge 

per 

stroke.

Pounds. 

12.50

12.60

12.56

13.56

12.57

19 W

13.55

13.55

12 52

12.52

12.47

12.47

12.44

13.44

12.40

13.40

12.36

12.36

12.30

12.30

12 33

12 33

Footpounds 

of useful 

work.

95.75

95.75

Oft 91

96.38

96.38

96.13

Oft 13

nt; on

Q?i on

95.52

95.52

Q^ 9Q

95.39

94.98

94.98

94.68

94.68

94 33

94.33

93 60

93.60

Average 

pull on 

rod.

Pounds. 

106.37

111.70

134 45 127! 65

124 45

133.40

133.35

132.88

133.40

131.30

131.30

135.53

135.53

135.53

135.53

124.45

136.56

138.16

138.16

138.16

138.16

139.36

Footpounds 

of work 

given to 

rod.

134.11

131.36

146.35

icn to

146 35

145.13

143.88

144 50

145 12

143.65

142.65

147.61

147.61

147.61

147. 61

146 35

148.84

150.72

150.73

150.72

150.72

152

Mechanical efficiency.

Per cent. 

77.1

72.8

66.4

64 1

65.7

66.3

66.8

66.5

66

67.2

66.9

64 7

64.5

64.5

64.3

64 9

63.6

63.8

62.5

62.5

63.1

61.5

Maximum 

tension 

on rod.

Pounds.

800

Minimum 

tension 

on rod.

Pounds.

-30

LIFT, 13.66 FEET.

10 . ... . .. --

10...... .... ... ......

15 -- 

15 ....

2Q....... .......................

20.... ..........................

35

35 - . --------

30 

30 . 

35 ..... ......................

35 - - ..

^.... ..........................

4Jd.... ..........................

4A........ ......................

to........... ........... .......

&d. ......................... ....

50 

55 _.

55. 

60 _. .. - 

60 ...... .--.... ......

13.50

13.50

12.56

12.56

12.57

12.57

12.55

13.55

12.53

12.52

12 47

12.47

12.44

13.44

13.40

13.40

12.36

12.36

12.30

12.30

13.33

13 33

158.35

158.35

11Q

159

159.14

110 14.

158.98

IRQ QQ

158.50

158 50

157.86

157. 86

157.49

157.49

156.98

156. 98

1KC KQ

156.58

155.73

155. 72 ~\<a 7n

154. 70

191.45

193.80

186.95

187 ft!.

181.40

189.35

107 on

188.55

193.80

191.45

m d.<\

191.45

189.35

M AR

190.65

185. 10

187. 70

194.44

188.55

188.55

192.80

180.35

225 15

336.70

230 35

330 79

213.33

233 67

330 15

331 74

336.73

335 15

335.15

335 15

233 67

335.15

334 21

217. 68

219. 15.

338 66

331 74

331 74

236.73

233.67

70.3

69.8

72.1

72

74.6

71.4

72 2

ri. r

69.9

TO. 3

70.1

TO.l

70. 7

69.9

70 

73 1

75.9

68.4

70. 3

70.2

68.2

69.4

300

310

750

750

850

65

40

75

 80

 70

LIFT, 33.66 FEET.

10 

10 

1^

15 .-- ----- --------

20 

30- .... .-- 

35

25 

30 - . 

30 - .- .

35 

35.---.-- ----. -- , 

dfi

40 

45 . ......

45 -

50... ...... . -- - 

50 

55 

55.. ....... . 

60

60

T> Kf\

12.50

T> Hft

13.56

12.57

13.57

13.55

12.55

12.53

12 53

12.47

13.47

J3 44

Li 44

13.40

12.40

12.36

12.36

13.30

12.30

12 32

13.33

383.35

ODO OK

384.61

384.61

OOA Ql

284.84

384 38

384.38

283.70

383.70

283.56

382.56

381.89

381 89

280.98

380.98

380.08

380. 0&

378. 73

278.72

376.90

376.90

377.50

279.65

277.50

377.50

277.50

382 70

380.60

383 70

384.80

391.10

295.35

295.35

391.10

291. 10

284.80

294.40

395.35

293.10

391.10

290.35

396.20

336.34

338.87

336.34

336.34

336.34

332.35

339.98

332.35

334.93

343.33

347.33

347.33

343.33

343.33

332.12

346.13

347.33

343.39

343.33

341.34

348.33

86.7

80.6

86 4

87.2

87.3

87.3

85.6

86.2

85.3

84.4

82.6

81.3

81

83.3

81.8

84.6

80.9

80.6

81.1

81.4

81.1

79.4

410

500

770

930

925

1,050

60

_ 35

85

 50

-100

 100
HOOD.] FRIZELL PUMP. 47

Figiires from efficiency tests of 6-inch Frizell pump; stroke, 19.1 inches Continued.

LIFT, 33.75 FEET.

Speed.

IQ, .............................

W.... ..........................

^5. ......................... ....

^5...... ........................

20.............. ................

20 ... -.. 

35..............................

25...... ........................

m. .............................

30...... ........................

35...... ................ ........

35.................. ............

40...... ........ ................

40... ....................... ....

45...... ................... .....

45.... ...... ... ............... ..

50. ..........................

50 ...... ...... ...............

Discharge 

per

stroke.

Pounds. 

12.50

12.50

12.56

12.56

12.57

12.57

12.55

12.55

12 52

12 52

12.47

12.47

12.44

12.44

13.40

13.40

12.36

12.36

Footpounds 

of useful 

work.

409.38

409.38

411.34

411.34

433.06

433.06

431.41

431.41

430 43

490 43

408.39

408.39

407.41

407.41

406.10

406.10

404.79

404.79

Average 

pull on 

rod.

Pounds. 

435.38

431 35 AA\ fin

444.90

440 40

441 60

439

435 38

425.85

431.35

434.43

424.43

430.80

435.03

425.30

419.47

425.30

425.30

Footpounds 

of work 

given to 

rod.

513

507. 15

519.33

533.30

tXf 01

591.33

504.50

513

500.90

507.15

499.13

499.12

506.63

510.43

500.04

493.39

500 04

500.04

Mechanical efficiency.

Per cent. 

81.3

80 7

79.2

78.6

81.5

81.7

83.5

83.1

83.9

83.9

81.8

81.8

81.3

79.8

81.1

83.9

80.9

80.9

Maximum 

tension 

on rod.

Pounds.

730

1,050

1,037.5

1,360

Minimum 

tension 

on rod.

Pounds.

-30

-97.5 -90

-fiO

LIFT, 37.75 FEET.

10....... . ... ...

10.......- - ..... ......

15 .........................

15- ... ...........

20

9Q

35

2&....... .......................

30...... . . . . .-....

30............ ..................

35...... . .. ..... ..........

35..............................

40--...........,--.....-.......

40..............................

45 .................. .........

13.50

13.50

13.56

13.56

13.57

13.57

13.55

13.55

13 53

13.53

13.47

13 47

13.44

13.44

13.40

471.87

471.87

474 14

474. 14

474. 52

474 53

473. 76

473.76

473.63

473.63

470. 74

470. 74

469.61

469.61

468.10

484.35

484 87

478. 73

475.50

476.63

479. 77

493.53

486.32

483

495.75

492 52

483

489.38

486.33

486.33

573.97

566. 68

562.97

559.19

560 40

564.21

579.30

561.79

568

583

WQ 9,(\

568

575. 51

571.79

571.79

82 2

 83.2

85.3

84.7

84 6

84.1

81.7

84.8

83.3

81

81.3

82.8

81.6

82.3

81.9

750

1,030

1,005

0

 67.5

 67.5
48 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

In the smaller size of this same make, fig. 27, a single butterfly valve 

in the piston replaces the several small clack valves. The cylinder is

FIG. 27. Vertical section of Frizell cylinder with butterfly valve.

brass-lined, is 3.73 inches in diameter, and has a 24-inch stroke. The 

valve area in the piston is 27.4 per cent of the cylinder area; the sueI 9.3

S3

9.1

ceoft £Tf}/cs L o/sPLACE, we/vr

10 15 30 35 30 35

Strokes per minute. Stroke, 23.7 inches.

4-O 4-5 50

FIG. 28. Discharge curve of 4r-inch Frizell pump.

tion valve, 56 per cent; the weight of the pump, 57^ pounds, and the 

weight of piston, rod, etc., 39^- pounds. Fig. 28 shows a discharge
HOOD.] FRIZELL PUMP. 49

attaining to 100 per cent at speeds ranging from 25 to 40 strokes per 

minute. Fig. 29 shows the efficiency at six different lifts. The sustained efficiency of this pump is noticeable. In fig. 30 increase of 

efficiency with increase of lift appears. This pump is much used in 

Kansas for irrigation.

15 30 25 30 35

Strokes per minute. Stroke, 23.7 inches.

FIG, 39. Varying-efficiency curves of 4-inch Frizell pump, showing effect of varying height of

" *tf t and speed. 

IRE- 14 4
50 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

80

* 60

gso

30

tO 15 20 25 30 35

Height o£ lift, in feet.

FIG. 30. Variation of efficiency with varying height of lift of 4-inch Frizell pump at speed of 20

strokes per minute.

Discharges of 4-inch Frizell pump at various lifts and speeds; stroke, 23,7 inches.

Speed.

10_... ....... .....

10..-.--- ..................

15.---.-.---.-....-........-..

15. . ...... _ . .._......

20. ....................... ....

20--.-..-...-.......--...-....

35---.----...---.....-.......

25 .........................

30.--....--.. .-...

30...........................

35.-.--.-------.-.

35 ....... .................

40.--.,--.----..-...-.--..

40 

45 

45. . ... 

50... . ....... ..........

50... . ..._. .. ___._.

55. - . .......... .

56.....-..--......... ----.

Discharge 

for 50 

strokes; 

lift, 34.3 

feet.

Pounds.

4fSO

465

467

466

473

467

467

Discharge 

for 50 

strokes; 

lift, 34.8 

feet.

Pounds. 

451 5

457 5

463 5

464

464 5

ifii

At& ^

463 5

469

465

468

4(53.5

466.5

466.5

463.5

465

449.5

Discharge 

for 50 

strokes; 

lift, 37.8 

feet.

Pounds. 

462

AfiZ

466

468

467

468

467

467.5

467

4A7

468

466.5

466

467

467.5

4A7 H

443

Discharge 

for 30 

strokes; 

lift, 13.75 

feet.

Pounds. 

375.5

375.5

275.5

375.5

378

fWVQ R

378.5

379.5

379.5

379.5

281

281

OQA K

280.5

OQA

977 *t

379

171

Discharge 

for 30 

strokes; 

lift, 6.54 

feet.

Pounds.

274

nrfty

278.5

00 1

281.5

280

280

379

OQA

381

380.5

OQA

oon

379

379

353

367

Plotted 

average 

discharge 

per stroke.

9

1£»Q

9 OK

9

QAO

9

OQQ

9.334

9 34

9 An

9.333

9 911
HOOD.] FRIZELL PUMP. 51

Figures from efficiency tests of 4-inch Frizell pump; stroke, 23.7 inches. 

LIFT, 6.54 FEET.

Speed.

10.. .......................... ..

10...........-.. .............

IS. ................. ...... ......

15...... .. .... .........

ao...... ........................

30

25

25..............................

30.......-..........-... ....

30........... ............... ....

35..............................

35...... ...... ............ ...

40...... ........ ........... .....

40.............. ........ .... ....

45......... .....................

45...... ..................... ...

50...... ........ ............ ....

50...... ...__.._......._.... ....

55...... ........................

55...... .................... ....

Discharge 

per

stroke.

Pounds.

9

1CQ

9.168

9.2592

9.2593

9.2724

9.2724

9.31

9.31

9.327

9.327

9 34

9.34

9.35

9.35

9.33

9.33

9.25

9.25

8.66

8.66

Footpounds 

of useful 

work.

<M Clf;

59.96

60.56

60.56

60 64

60.64

60.89

60.89

61.00

61.00

61.08

61.08

61.18

61.18

61.04

61.04

60.53

60.53

56.68

56.68

Average 

pull on 

rod.

Pounds. 

79.38

79.99

70 1<;

78.96

84.31

83.75

77.91

76 04

76.66

77 Q1

75.82

77.08

75.00

75.00

76.23

76.65

75.82

78.75

75.82

75.41

Footpounds 

of work 

given 

to rod.

1KC W

158.01

156.33

1SK QA.

161. 51

165.41

153.81

150.18

151.40

153.87

149. 74

152.23

148. 11

148.11

150.55

151.38

149. 74

155.50

149.44

148.90

Mechanical efficiency.

Per cent.

OO O

37.9

38.7

38.8

36 4

<?fi ft

39.6

4/1 ^

40.2

3Q Q

40 7

40.0

41.2

41.2

40.5

40 3

40.4

39.9

37.8-

38.0

Maximum

tension 

on rod.

Pounds. 

120

135

177

195

201

253.5

249

322

Minimum 

tension 

on rod.

Pounds. 

33

9

9

6

 15

 30

 24

-30

LIFT, 12.75 FEET.

10... ...........................

10....... ...... .................

15 ...... --....- -..-. 

15......... ....... ......... .. ...

20....... ........ ...... ......

20.... ..........................

25....... ....................

25

30... _ ...-- .. .- 

30

35 -.. ......................

35...... .................... ....

40. ..........................

40 - .-..... .. ....

45. .......................... ...

45.-.. ......................

50...... ........ .............

Kf)

55..............................

9.168

9.168

9.26C

9.260

9.270

9.270

9.310

9.310

9.327

9.337

9.340

9.340

9.350

9.350

9.330

9.330

9.250

9.250

5.700

116. 89

116.89

118.05

118.05

118 22

118 23

118. 70

118. 70

118.91

118. 91

119.08

119.08

119, 17

119. 17

118.99

118.99

117. 99

117.99

73.67

89.63

87.07

QJ. on

98.20

97.17

QP; 77

97 22

96.60

94.63

97.80

95 22

96.45

109.85

100.70

99.57

101.40

95.77

96.90

99.30

177 00

m Q7

187 43

193.11

191. 91

189.24

192.00

190.78

186.88

184.82

188.09

190.78

216.95

198.88

196.66

200.26

189.24

191.54

196.11

66

68

63

61

61

62

62

62

63

63

63

63

54

59

60

59

62

62

37

175

250

325

350

375

30

11.5

 11.5

 95

- 75

LIFT, 18.8 FEET.

10....................... ....

10........ ........ ..............

15....... .... ........... .....

15_... .......... ................

20.......... ....................

^d. ................ .............

^&.. ............................

35.-. .............. ..........

30.................. . .

30..............................

35_.._ .__.-. ....................

35.... ....... ................

40........ ......................

40 ................ ..........

45. ................ . ........... .

45 ..........................

50........ ......................

50 -- -. 

55..............................

55..............................

58......... .....................

58....... .......................

9.168

9.168

9.260

9.260

9.270

9.270

9.310

9.310

9.327

9.327

9.340

9.340

9.350

9.350

9.330

9.330

9.250

9.250

5.700

5.700

5.430

5.430

172.36

172.36

174.07

, 174. 07

174.32

174.32

175. 03

175.03

175.35

175.35

175.59

175.59

175.86

175. 86

175.45

175.45

173. 98

173.98

107. 16

107. 16

102.14

102.14

126.75

130.33

135 21

133.50

139.05

136.89

148. 32

143.83

139. 47

139.47

141.90

145.33

146.64

151.68

150.42

138.57

154.62

151.36

150.42

156.32

159. 72

156.33

250.33

237.65

267.04

263.66

274 62

270.35

392.93

383 09

275.45

275.45

380 25

387.00

389.61

399.56

397.08

378.67

305.37

299.49

397.08

308.75

315.36

308.75

69

72

65

69

63

64

60

62

63

63

64

61

61

58

59

63

56

58

36

34

32

33

180

340

288

336

360

405

450

450

36

24

3

6

 9

 30

 120

-120
52 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Figures from efficiency tests of 4-inch Frizell pump; stroke, 33.7 inches Continued.

LIFT, 24.8 FEET.

Speed.

10. .. .................... 

10.. ...... ................... ...

15............. ..............

15 ............. ..............

20 ...........................

20- ..........................

25

25

30......... ..................

30 ...... ....... ........

35............ ..................

35........, ..................

40.... _ ... ..........

40..............................

45.... ..........................

45..............................

50... ...........................

Discharge 

per 

stroke

Pounds. 9ifi«

9.168

Q 9fift

9 9tfif\

9.270

9.270

9.310

9.310

9.327

9.327

9.340

9.340

9.350

9.350

9.330

9.330

9.250

Footpounds 

of useful 

work.

227.36

227.36

229.65

229 65

229 89

229 89

230.89

230.89

231.11

231.11

231.63

231.63

231.88

231.88

231.38

231.38

229.40

Average 

pull on 

rod.

Pounds. 

149.28

147 48

161.28

155.01

155.82

-IKC aa

156. 66

154.14

154 14

152.46

IE! 11

162.48

157.59

158.73

161.10

158.73

153.99

Footpounds 

of work 

given 

to rod.

294 82

291 27

fyfff an

306.06

307.74

309.40

WO tf\

304 34

304.32

301.10

304.42

319.23

311.24

312.65

319.00

312.65

304.13

Mechanical efficiency.

Per cent. 

77.1

78.0

72.3

75.3

74.7

74.3

74.6

75.8

75.8

76.7

76.8

72.5

74.4

74.1

72.5

74.0

75.4

Maximum, 

tension 

on rod.

Pounds.

348

398

471

Minimum 

tension 

on rod.

Pounds.

3fi

 24

 36

LIFT, 30.75 FEET.

10+........ .......... ..........

10+. ........................

10.... ..........................

10. ...... . ..... ........

15 ..........................

15 ...........................

20.... ................. .........

20

25

25. .......... ........

30 ......... ,. . .

30 ...........................

35 ..........................

35... ......... ..................

40. ..........................

40 . -.. ......... .

45... ......... . .......

45

SO......... .....................

9.168

9.168

9.168

9.168

9 9K

9.26

9 97

9.27

9.31

9.31

9.327

9.327

9.34

9 m

9.35

9.35

9.33

9 33

q 35

280.89

280.89

280.89

280.89

284.72

284.72

285 12

285.12

286.29

286.29

286.81

286.81

287.20

287.20

287.65

287.65

286.98

286.98

284.58

176.45

175.05

176.00

167.60

176.55

176.55

179.25

181. 15

180.65

184.85

180.15

177.35

190.15

185.90

197. 45

198 60

199.70

193.25

188.70

348 50

345 70

347 80

331.00

348 70

348 70

354.00

357.80

356.80

365.10

355.80

350.30

375.60

367.20

390.00

392.20

394.40

381.70

373. 70

80.5

81.2

80 7

84.8

81.6

81.6

80.5

79.3

80 2

78.1

80.6

81.8

76.4

78.2

73.7

73.3

72.7

75.1

76.3

250

240

280

370

425

490

540

590

15

40

40

0

0

25

 5

_ 135

LIFT, 37.6 FEET.

10 . . .. . 

10. ... .............

15- .... .......... ......... ....

15 ............... ...........

20..............................

2U. .............................

25.... ----.... ..r......... ......

25

SO. 

30............ .............. ....

35..............................

35.............................

40................ ..............

48.... ........ .......... ........

48.... ..........................

9.168

9 1ftR

9.26

Q 9P,

9.27

9.27

9.31

9.31

9.327

9.327

9.34

9.34

9.35

9.33

9.33

344.61

344 61

348.14

348 14

348.64

348.64

350.06

350.06

350.70

350.70

351.18

351.18

351.73

350.91

350.91

208 32

208 32

213.30

211.56

214. 98

220.74

220 74

218.94

224 16

225 18

224 34

231.00

231.66

229.56

234.30

411.35

411.35

421.26

417 84

424.58

435.93

435.93

432.40

442.70

444.73

443.07

456.22

457.36

453.38

462.89

83

83

82

83

82

80

80

81

79.4

78

79

77

76

77

75

275

360

410

50

36

0

This pump was arranged as a force pump, as shown in fig. 1 (p. 12), 

and tested at three different lifts, as shown in fig. 31. At a lift of 

about 24 feet the efficiency is seen to be reduced from about 75 per 

cent to about 52 per cent upon the addition of a stuffing box and two 

turns in the discharge pipe. This drop in the efficiency exhibits the 

harmful effect of added complications. The gland was carefully 

made, and as lightly packed as possible, to prevent leakage. Adding
HOOD.] PEIZELL PUMP. 53

this reduction of about 20 per cent to the efficiencies found for the two 

high lifts of 47 and 70 feet, respectively, the efficiency of the pump

10 15 20 25 30 35

Strokes per minute. Stroke, 23.7 inches.

40 45

Fia. 31. Efficiency of 4-inch pump used as a force pump.

when used as a simple lift pump, as in the first trials, is brought up 

to the neighborhood of 80 per cent.

Figures from efficiency tests of 4-inch Frizell pump, used as a force pump with a 

stuffing box; stroke, 23.7 inches.

LIFT, 24.3 FEET.

Speed.

10-. ....................... ....

10 . .. 

15---..-.-. ..................

15 

30.. ............. ......,.. 

20...... ........................

25

25

30..............................

30-- . 

35. .... ...... ...... 

35 

40 . 

40...... ........................

45.............................

45... ........... ............

Discharge 

per 

stroke.

Pounds. 

9.168

9.168

9.360

9.260

9.270

9.270

9.310

9.310

9.327

9.327

9.340

9.340

9.350

9.350

9.330

9.330

Footpounds 

of useful 

work.

222 48

222.48

225.02

225.02

225 26

225.26

226 32

226 82

226.60

226.60

227 12

227.12

229:55

229.55

234.69

224.69

Average 

pull on 

rod.

Pounds. 

221 08

225 52

223 32

218.88

217.76

218. 88

211.08

217. 76

217. 56

216.60

221 08

220.96

217.68

215.44

215.44

213.44

Footpounds 

of work 

given to 

rod.

436.63

445 40

441.06

432 28

430 07

432.28

416.88

430 07

429.56

427.78

436.63

448.56

449.08

425.47

425.47

431.82

Mechanical efficiency.

Per cent. 

51.2

50

53.2

54 4

52.3

52 1

54.2

52.6

52

52.9

52 1

50.6

51.1

53.9

52.8

52.3

Maximum 

tension 

on rod.

Pounds. 

280

308

376

520

Minimum 

tension 

on rod.

Pounds. 

24

-32

_ 33

- 88

Frizell 4-inch pump; §trolce, 23.7 indies; used as a force pump and delivering water 

against air pressure equivalent to the lift noted.

LIFT, 47.37 FEET.

Speed.

10, .... .. ............ ........

10 ........ ..

15. ...... .... 

15 

20...... .................. ......

20.......... ....................

25

25.............. . ....... .....

30.. ...... .... . .....

30.. .......... ... ...... ......

35 .. .. 

35 

40,.. ....... ............. ....

40 ............ .......

45 ...... ......... .........

45 

Discharge 

per 

stroke.

Pounds. 

9.168

9.168

9.26

9.26

9.27

9.27

9.31

9.31

9.327

9.327

9.34

9.34

9.35

9.35

9.33

9.33

Footpound s 

of useful 

work.

434 29

434 29

438.60

438 60

439 21

439.21

441 01

441.01

441 82

441.82

442.44

442.44

442.90

442.90

441.96

441.96

Average 

pull on 

rod.

Pounds. 

348 60

369.60

376.20

360.30

361.32

360

366.66

360

378.30

383.58

380.33

380

385.44

385.32

402.24

413.32

Footpounds 

of work 

given to 

rod.

695. 78

729.96

734.66

m PM

713.61

711

724.16

711

747. 14

757.48

751.15

750.50

761.23

761

794.34

816.30

Mechanical efficiency.

Per cent. 

62.4

59.4

59.7

61.6

61.5

61.7

fin o

62

no 1

58.3

58.9

58.9

58.1

58.2

56.9

54.1

Maximum 

tension 

on rod.

Pounds.

444

636

756

Minimum 

tension 

on rod.

Pounds.

 18

 108

 90
54 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Frizell 4-inch pump; stroke, 23.II indies; used as a force pump and delivering water

against air pressure equivalent to the lift noted Continued.

LIFT, 70.5 FEET.

Speed.

10.-..........-. ............

10............. ........ ......

IK

1^

20..-....-...---- --. ......

20...... ........................

25

2.^..... ..................... ....

30.. ........................ ....

30. ....................... ......

S&....... .......................

35. .............................

40

40............... ...... - . ....

45. .....-.....--.. ..............

45

Discharge 

per 

stroke..

Pounds. 

9.168

9.163

9 9R

9.36

9.27

9.27

9.31

9.31

9.327

9.327

9.34

9.34

9.a<5

9.35

9.33

9.33

Footpounds 

of useful 

work.

646.34

646.34

652.83

652.83

653.54

653.54

656.36

656. 36

657. 55

657.55

658.47

658.47

659.18

659.18

657. 77

657.77

Average 

pull on 

rod.

Pounds. 

495. 75

510

515. 33

514. 50

508. a5

513. 22

536.25

534.15

532.13

527.85

521.53

515.33

533.13

516. 66

535. 60

525.60

Footpounds 

of work 

given to 

rod.

895. 77

1,007

1, 101. 11

1,016.22

1,003.90

1,013.62

1,059.09

1,054.96

1,050.95

1,042.50

1,030.02

1,101.11

1,050.96

1,020.32

1,038.06

1,038.06

Mechanical efficiency.

Per cent. 

72 1

64.5

1Q 9

64.2

65

64.4

61.9

62 2

62.5

63

63.8

59.8

63.7

64.6

63.3

63.3

Maximum 

tension 

on rod.

Pounds.

780

835

Minimum 

tension 

on rod.

Pounds.

-75

 165

VAN VOORHIS PUMP.

Fig. 32 is a pump specially designed for slow speeds and low lifts, 

yet capable of running at high speeds. It is locally known in KanFIQ. 32. Vertical section of pump designed for slow speeds and low lifts.
HOOD.] VAN VOORHIS PUMP. 55

sas as the Van Voorhis pump. The piston is replaced by a hollow 

plunger the upper opening of which is covered by a large clack valve. 

The plunger is packed with a suitable cup leather on the outside.

210 10 2O 30 4O 5O 6O 70 80

Strokes per minute. Stroke, 10.02 inches.

PiG. 33. Varying-discharge curves of 8-inch Van Voorhis pump, showing effect of varying lift

and speed.

The suction valve also is a large clack valve. The valve area is very 

great, being 70 per cent for the lower valve and 94 per cent for the 

upper valve in an 8-inch pump. The weight of the pump was 146 

pounds, and of the plunger, rod, etc., 101.5 pounds. This design has
56 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

many advantages for very slow running, which, however, quickly 

disappear when a moderate piston speed is reached. The discharge

so

90

ao

70

60

50

90

70

SO

5'

3O ^O "SO 6O IO

Strokes per minute. Stroke, 10.02 inches.

82.04

3O 4.0 SO

FIG. 34. Varying-efflciency curves of 8-inch Van Voorhis pump, showing effect of varying lift

and speed.

curves, shown in fig. 33, and varying for each lift, give the results for 

the large valves. Fig. 34 shows the efficiencies for six different lifts, 

and fig. 35 the change of efficiency with increase of lift.
HOOD.] VAN VOOEHIS PUMP, 57

100

i eo

 s 

I 80

I

£

to

60

10 15 20 « 30 35

Height of lift, in feet.

PlG. 35. Variation of efficiency with varying height of lift of Van Voorhis pump at speed of

15 strokes per minute.

Discharge of Van Voorhis 8-inch pump at 5-foot lift; stroke, 10.02 inches.

Speed.

10............

15............

20............

25............

30............

35............

40............

45............

47............

Discharge 

in 20

strokes.

Pounds.

348.5

344.5

832

315

301

296

289

281

373

Discharge 

in 20 

strokes.

Pounds.

348.5

346

328

315.5

296

294

290

291

Plotted 

average; 

discharge 

per stroke.

Pounds. 

17.55

17.05

16.50

15.97

15.42

14.85

14.30

13.77

13.55

Speed.

<»ft

55...........

60 ...........

65...........

68...........

70........... i<\

80...........

85...........

Discharge 

in 20 

strokes.

Pounds. 

262

249

244

227

220

222

221 5

213

315.5

Discharge 

in 20 

strokes.

Pounds. 

259.5

253

241.5

235

238

219.5

220

215

208.5

Plotted 

average; 

discharge 

per stroke

Pounds. 

13.35

10 DA

12.35

11.60

11.35

11.05

10.90

10.67

10.55

Discharge of Van Voorhis 8-inch pump at various lifts and speeds.

Discharge, in pounds, for 20 strokes for lift:

10......................................

10.........................................

15............................... ... .

15.................................. ...

20...................................... .

20............................... .........

25

25..............................

30............................... . ..... .

30 .............. ...... . ..

35................................ . ....

35.........................................

40............... ....... .. .

40............................... ..... ..

45...................................... ..

45.........................................

50..............................

50.........................................

55.........................................

55.........................................

60.........................................

60.........................................

11.83 feet.

320.5

Qia 1

QOQ

325.5

326.5

322.5

309.5

308.5

294

301.5

290

290.5

275.5

270.5

272.5

267.5

357.5

249.5

247.5

239

232.5

223.5

16. 83 feet.

328

332.5

329.5

328

320.5

321

on« i

310.5

297

301

284.5

286

356

275

243

251

27.12 feet.

0531

ooo t

329.5

326

317.5

315

300

300.5

288.5

286

285

284

33.04 feet.

QfW*

OAQ

010

317.5

OQQ

303.5

293

290.5 9on

282.5

37.21 feet.

31 Q

Q1Q

OAQ

°/K>

9OQ

296

280.5

268.5
58 TESTS OP PUMPS AND WATER LIFTS. [NO. 14.

Plotted average discharge per stroke.

Speed.

10...-.-- . ........... ......

15.................. ..........

20. ........................ ...

25...........................

30.. ......... ............ .....

35. .................... ....

40......... ....... ............

45............................

50...........................

55 _ ,. .. .

60...... ......................

Discharge, in pounds, per stroke for lift:

11.83 feet.

15. 975 

16.1 

16.05 

15. 575 

15 

14.425 

13. a5 

13.275 

12.7 

12.125 

11.55

16. 83 feet.

16.525

16.45 

16 

15.425 

14.85 

14.3 

13.725 

13. 175 

13.6 

12.05 

11.5

22 feet.

16.562 

16. 412 

15.887 

15. 275 

14. 675 

14.1 

13.48V 

12. 912 

12.3

27.12 feet.

16.6 

16. 375 

15. 775 

15.125 

14.5 

13.9 

13.35 

12. 65 

12

32. 04 feet.

15.55 

15.7 

15.2 

14.575 

14 

13.35

37.21 feet.

15.8 

15.935

15.45 

14.85 

14.25

Figures from efficiency tests of 8-inch Van Voorhis pump; stroke, 10.02 inches.

LIFT, 4.875 FEET.

Speed.

8 ..... .

8..... .....

35-. -

40

40. . 

54 

54.. 

54. .. 

54.. . 

charge

stroke.

Pounds.

17.65

17.65

14.85

14.30

14.30

12.80

12.80

12.80

12.80

Footpounds 

of

useful 

work.

86.04

86.04

73.39

69.71

69.71

62.40

62.40

63.40

63.40

Average 

pull on

rod.

Pounds.

130

135.50

140.95

147.65

151

158.30

156.65

155.30

157. 70

Footpounds 

work

given to 

rod

108.55

104 79

117.68

133 28

126

132. 18

131.63

139.67

131.69

Mechanical efficiency.

Per cent.

79.20

82.10

62

56

55.30

47.20

47.40

48.20

47.30

Maximum

tension

on the 

rod.

Pounds.

235

515

780

675

Minimum 

tension

on the 

rod.

Pounds.

+ 85

+ 20

- 50

 35

Stroke

finished

at closure of

the 

upper

valve.

Per cent.

4

5

5

11

11

11

11

Stroke

finished

at closure of

the 

lower

valve.

Per cent.

12

16

16

21

21

21

31

LIFT, 5.166 FEET.

IK

16.------.

17 

20 

33

26.. .......

29 . .

36. . 

36 .

43 . 43 i

46.. ....... 43 i

49.........

54. ....... .

54_.... ....

58--.....

65.. .......

72 

84.........

85 

90 . 

100 . 

17.05

16.95

16.85

16.50

16.20

15.85

15.50

14.75

14.75

14

13.90

13.65

13.90

13.35

12.80

13.80

12.35

11.60

11.05

10.55

10.50

10.40

10

88.09

87.57

86.96

85.35

83.70

81.89

80.08

76.30

76.30

72.33

71.81

70.52

71.81

68.97

66.13

66.13

63.81

59.93

55.35

54.51

54.24

53.73

50

154 30

150.80

148.65

. 150

145.70

153.30

150

150

151.30

167. 75

147.65

154.30

147.65

150

153.30

153.30

164.04

179.46

194.33

385.30

336.16

364.12

283 72

138.84

125.90

124.12

135.25

131.66

138

135 35

135. 25

126.33

140 07 190 os

128.67

133 38

135 25

138

128

136.89

149.84

162 25

238.23

188.64

220 37

236.90

67.60

69.55

70

68

68.80

63.97

63.92

60.80

60.30

51.60

58.20

54.80

58.30

55

51.60

51.60

46.60

40

34

22 80

27.80

24.70

21.10

385

380

490

550

575

fivi

876

600

1,300

1,500

1,200

1,560

40

50.

0

0

15

0

- 72

0

 75

 150

 160

-135

.6

.9

2

4

4

6

6

7

5

5

10

10

12

12

17

20

21

20

23

2

3

5

6

6

9

11

15

15

16

17

19

17

30

31

22

23

27

37
HOOD.] VAN VOORHTS PUMP. 59

Figures from efficiency tests of 8-inch Van Voorhis pump; stroke, 10.02 indies 

Continued.

LIFT, 11.83 FEET.

Speed.

10... .....................................

10... . ........... ................. ........

15........................................

15........................................

ao. .......................................

20

25........................................

30. .................... ................

SO............ ............................

35........................................

35........................................

40........................................

40........................................

45.......................... ............

45 ................................. ....

50. .......................................

60... .....................................

55.................... ....................

55..................... ................

60........................................

60.................. ... ...............

Discharge pei* 

stroke.

Pounds.

11 Q71

15. 975

16.1

16.1

16.05

16.05

15.575

15

15

14.425

14. 425

13.85

13.85

13. 275

13. 275

12.7

12 7

12.125

12.135

11.55

11.55

Footpounds 

of 

useful 

work.

188.9

188.9

190.4

190.4

189.8

189.8

184.3

177.4

177.4

170.6

170.6

163.8

163.8

157

157

150.2

150.2

143.4

143.4

136.6

136.6

Average 

pull on 

rod.

Pounds. 

381 i

381 1

276

269.9

274

273.7

272.5

272.4

266.2

264.6

266.9

272.2

366.9

274. 5

368.4

369.1

285.4

303.9

303.9

308.5

303.2

Footpounds 

of work 

given 

to rod.

235.8

235.8

330.2

225 4

228.8

228.5

226.9

237 4

322.3

221

233.9

337.3

332.8

329 2

324 1

324.7

238.2

253.7

253 7

257.6

259.5

Mechanical efficiency.

Per cent.

8(1 H

80.5

QO ff

84 5

82.9

83

81.2

78

79.8

77 2

76.5

72

73.5

68.5

70

66.8

63

56.5

56.5

53

52.6

Maximum 

tension 

on rod.

Pounds. 

417

432

427

437

475

500

525

660

720

750

780

1,080

895

1,070

1,015

1,135

1,265

1,410

1,380

1,357

1,433

LIFT, 16.83 FEET.

10.. ................................ ..

10. .......................................

15 ...................... ^. .......... .....

IS........................................

20.... .................. ......... ......

30 ................................. __..

25 .. . .-.

35.......................................

30 ........... ......... . .... ....-

30 . ..._ . . 

35 ........ ........ ..... . .--

35. .................................... ...

40 . ._._._..._.... ...... ......

40....... .. . . ......

40............. ...........................

40. ........ ..... ..... .......

45.......--........ .... ............ ....

45... .................... . . .... .

60 .................. ....... .....

60 

55. ........................... .........

55 . _ .- . .. .

60 .. _... . . 

60.... ...... ........................... 

16. 525

16.525

16.45

16.45

16

16

15.425

15.435

14.85

14.85

14.3

14.3

13.725

13.725

13. 725

13. 725

13. 175

13. 175

12.6

12.6

12.05

12.05

11.5

11.5

278.1

278.1

276.8

276.8

369.3

269.3

259.6

359.6

249.9

249.9

240.6

240.6

231

231

231

231

231.7

231.7

212

212

203.8

203.8

193.5

193.5

395.8

396.6

394.7

391.2

386.6

387.3

383.8

380

375.3

374.6

374.2

373.5

370.4

375. 3

372.3

374.2

391

405.9

404.8

405.9

404.7

404.7

436.4

410.4

330.5

331.3

329.6

326.6

323 8

323.4

330.5

317.3

313.4

312.8

312.5

311.9

309.3

313.4

310.9

317.8

326.5

338.9

338

338.9

337.9

337.9

356.1

343.7

84.1

83.9

84.1

84.7

83.4

83.2

81

81.8

79.7

79. 9

77

77.1

74.7

73.7

74.3

73 7

67.9

65.4

63.7

63.5

60

60

54.3

56.4

565

565

595

590

650

650

710

710

875

940

1,000

1,030

1,050

1,070

1,010

1,224

1,309

1,245

1,395

1,372

1,330

1,515

1,447

LIFT, 22 FEET.

10........................................

10.... ...... ................... ...........

15 ...... ........ ._. 

15 ........................... ............

20

30 .....................................

35

25 .......... .................... .. .....

30. ................................... ....

30................. .......................

35 ........................................

35 ....................... ........ ........

40 .............. _...... ... . 

40 .............. ...... ........ ............

4K

45.....................-. ..............

50. ............................ ......--

50................................ .....

16.562

16. 563

16.412

16.412

15.887

15.887

15.275

15.375

14.675

14.676

14.1

14.1

13.487

13.487

12.912

12. 912

12.3

12.3

364.3

364.3

361

361

349.5

349.5

336

322.8

322.8

310.2

310.2

296.7

296.7

384

384

270.6

370.6

510.8

510.1

504.7

510.8

497.7

492.2

486.8

480.7

483.9

482.2

474.6

468.4

501.5

513.8

505.3

505.3

531.6

533.2

426.5

425.9

4S1.4

426.5

415.6

411

406.5

401.4

404

402.7

396.3

391.2

418.8

429

421.9

431.9

443.9

445.3

85.4

85.5

85.6

84.6

84.1

85

82.6

83.7

79.9

80.1

78.2

79.3

70.8

69.1

67.3

67.3

60.9

60.7

730

715

770

740

855

890

945

1,035

1,140

1,215

1,160

1,380

1,507

1,403

1,402

1,687

1,650
60 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Figures from efficiency tests of 8'inch Van Voorhis pump; stroke 10.0% inches 

Continued.

LIFT, 27.12 FEET.

Speed.

10 .................................... ....

10......-... .................... ......

16... . _. ..... . . ......

15 ...... ........... ...... .. _ ..

20.......... ...... ........................

20..-. ...... . . . . . .......

25

25 .. .........................

30 .... ...... ...... ...... ...... ... ..

30,... ......... ...........................

85................ ........................

85..... ...................................

Discharge 

per 

stroke.

Pounds. 

16.6

16.6

16. 375

16. 375

15. 775

15.775

15.125

15.125

14.5

14.5

13.9

13.9

Foot 

pounds 

of 

useful 

work.

450.2

450.2

444.1

444.1

427.8

427.8

410.2

410.2

393.2

393.2

367

367

Average 

pull on 

rod.

Pounds. 

646 3

646.5

642.5

640.9

634.7

638.2

617.3

619.9

619.9

615.7

611.5

600

Foot 

pounds 

of work 

given 

to rod.

539.7

539.8

536.5

535.1

530

532.9

515.4

517.7

517.7

514.1

510.6

501

Mechanical efficiency.

Per cent. 

83.4

83.4

82.7

83

80.7

80.3

79.5

79.2

75.96

76.4

71.8

73.3

Maximum 

tension 

on rod.

Pounds. 

832

900

969

975

1.027

1,035

1,207

1,170

1,395

1,380

1,500

1,447

LIFT, 32.04 FEET.

10............. ........... ........ ....

10........ ........ ........................

15 . .. . ......... .... ......

15. ........... ...... . .. 

20... . ... . ...... ............ ..........

20 ... .. .. .. 

25...........-....... ..... .... .... 

35................. ............. ..........

30 ...... .............. ....... ......

80 ................. ....... ..

S&.... ....................................

35...... ..................................

15.55

15.55

15.7

15.7

15.2

15.3

14. 575

14.575

14

14

13.35

13.35

498.2

498.3

503

503

487

487

467

467

448.5

448.5

427.7

427.7

760.4

760.4

753.5

746.5

734.9

721

725.6

718.9

724.5

712.1

706.2

696.3

634.9

634.9

629.3

623.3

613.6

602

605.9

600.2

604.9

594.5

589.6

581.4

78.4

78.4

79.9

80.7

79.3

80.9

77

77.8

74.1

75.4

72.5

73.5

1,057

1,080

1,132

1,110

1,252

1,350

1,330

1,440

1,455

1,447

1,567

1,567

LIFT, 37.21 FEET.

10. ............................. ....... 

10 .......... ...... .....,... ...... .......

15 .... ......... ............. ..........

16.... ..... .. . . 

20...... ..................... ....... ......

20 ...... . ........ . 

25 ...... .......... .......... ..........

25

30.............. .... ... ......

30 ................. ........ ..........

15.8

15.8

15.925

15.925

15.45

15.45

14.85

14.85

14.25

14.25

587.9

587.9

592.5

592.5

574.9

574.9

553.5

553.5

530.2

530.2

868

865.7

867.2

864.5

857.3

859.1

845.5

847.8

825.7

823.1

724.8

722.8

724.1

721.8

715.9

717.3

704.5

707.9

689.5

.687.3

81.1

81.3

81.8

82

80.3

80.1

78.3

78

76.9

77.1

1,177

1,177

1,185

1,185

1,230

1,260

1,305

1,380

1,380

1,380

COOK PUMP.

The Cook cylinder, made by the Cook Well Company, of St. Louis, 

Missouri, has been developed especially for deep-well pumping, and 

the 4-inch size is shown in fig. 36. The design admits of the withdrawal of both the piston and the suction-valve device for inspection, 

or repair. The actual diameter is 3.75 inches. Though furnished 

with double packing leathers and having a valve area of 21 per cent 

of the cylinder area, its efficiency in deep wells is notable. Both valves 

are rubber disks, guided by a central stem. The cylinder is brass 

lined and highly polished, and friction is thus greatly reduced. However, on account of the high pressures with which this pump deals, 

double cup leathers for packing are required, by which, on the other 

hand, friction is increased. Built especially for high lifts, it is not to
HOOD.] COOK PUMP. 61

be expected that it will develop a high efficiency at the low lifts 

prevailing in irrigation work.

In testing this pump it was first operated in an open well with a 

34.8-foot lift. The efficiency varied from about 78 to 58 per cent at

FIG. 36. Vertical section of Cook cylinder.

speeds of 12 to 40 2-foot strokes per minute. The pump was then 

provided with a stuffing box, carefully made and packed, and was 

made to deliver water against an air pressure equivalent to the 

previous total lift of 34.8 feet.
62 TESTS OP PUMPS AND WATER LIFTS. [NO. 14.

The mean pull on the pump rod was found to be increased about 

30 pounds by the friction in the stuffing box, and the efficiency, in

15 20 25 3O 35 40

Strokes per minute. Stroke, 24 inches.

PIG. 37. Discharge curve for 4-inch Cook deep-well pump.

consequence, lowered from the 78 to 58 per cent of the previous test 

to 67 to 53 per cent. At the higher lifts tried the same method was

roo

so

70

60

SO

10 15 ZQ 25 30 35

Strokes per minute. Stroke, 24 inches.

PIG. 38. Varying-efflciency curves of 4-inch Cookpump, showing effect of varying lift and speed.

followed, and the efficiency, at an 82.5-foot lift and at speeds ranging 

from. 15 to 35 strokes per minute, was found to range from 81 to 72
HOOD.] COOK PUMP. 63

per cent. Allowing for the increase of friction resulting from the 

addition of a stuffing box, the efficiency of the pump in an open well 

and at the same depth would probably be 85 to 77 per cent. Fig. 37 

gives the discharge curve, and fig. 38 the efficiency curves, at differing lifts, for this pump, fitted with the packed stuffing box and rod. 

There are exhibited a quick action of the valves, a remarkably low 

maximum stress, and slight compression in the pump rod at speeds 

above 20 strokes per minute.

There is here seen to be marked advantage in the special adaptation 

of parts to special conditions.

Discharge of 4-inch Cook pump; stroke, 24- inches.

Speed.

13...... . ........ ...............

12-.-.- --- .

12

15... ......................

15--------------... ----------

15-. . --------.--- 

15- - 

20 . -

20 .... -

20-.-....---. ......... .....

Experimental discharge 

per 50 

strokes.

Pounds. 

465

464

467

469

471

468

468

468

461

467

Plotted 

average discharge 

per 

stroke.

Pounds. 

9.3

9.38

9.32

Speed.

20.. .......................

25

25----... .......... ----------

30

30---.... . ....

35 . .

35.-...-. .. .... -------

40...... ....... . .. 

40

Experimental 

discharge 

per 50 

strokes.

Pounds. 

465

457

460

460

460

458

456

456

460

Plotted 

average discharge 

per 

stroke.

Pounds.

9.2

9.18

9.16

9.14

Figures from efficiency tests ofJ^-incli Cook pump; stroke, ?4 inches. 

LIFT, 34.8 FEET; OPEN WELL.

Speed.

12 ....... _ ....................

12....... .......... ....................

15.-- .- .- ... .- - 

15... . ... .................. ......

W. .......................................

2O...... ..................................

25

25

30.. . . .. - - 

30.. . .. . .......... . .......

35 .- -.- 

35..- _ . _. ...... ........

40.-- - . ---.. 

m....... .................................

Discharge 

per 

stroke.

Pounds. 

9 3

9.3

9 38

9.38

9.32

9.32

9.2

9.2

9.18

9.18

9 Hi

9.16

9.14

9.14

Footpounds 

of useful 

work.

323.6

333.6

326.4

326.4

324.3

324.3

320 1

320.1

319.5

319.5

318.8

318.8

318.1

318.1

Average 

pull 

on rod.

Pounds. 

207.6

213.9

205.3

203.9

215.9

212 5

225 6

235.6

246.3

243.1

257.6

253 4

273

270.1

Footpounds 

of work 

given to 

rod.

415.6

428.1

410.9

408.2

433 1

425.4

451.6

451.6

493

486.6

STi fi

507.3

546.4

540.7

Mechanical 

efficiency.

Per cent.

*yry Q

75.6

7Q i

79.9

75

76.2

70.8

70.8

64.8

65.6

61.8

62.8

58 2

58.8

Maximum 

pull on 

rod.

Pounds. 

280

285

315

305

350

335

385

410

510

525

W!

635

650

650

LIFT, 34.8 FEET, USING STUFFING BOX.

13 -. .........................

-12. .......................................

15. .................................... ...

15. ............................... ........

20 -. . .. . ...... 

20

25...... - .-- . - 

25

30...-- .......... ........... .

30 _- ....... ........ .................. 

35.... . _ .. . __.

35 ........................................

9

0

9.3

9.38

9.38

9.32

9.32

9.2

9.3

9.18

9.18

9.16

9.16

333.6

323.6

326.4

326.4

324.3

324.3

320.1

320.1

319.5

319.5

318.8

318.8

243.1

332 7

251.4

251 4

264 5

9fjQ 4.

250

359.1

366.7

379 2

297.2

300

486.5

465.7

503.2

503.2

529

521.3

. 500.4

518.6

533.8

558.8

594.9

600.4

66.5

fid fi

64.8

64.8

61.2

62 2

63.9

61.7

59.8

57.1

53.5

53

315

310

350

375

400

415

420

435

565

560

650

675
64 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Figures from efficiency tests of 4-inch Cook pump; stroke, $4. inches Continued. 

LIFT, 48 FEET, USING STUFFING BOX.

Speed.

12. ................................... ....

12........................................

15..-..-.-..-.-.-............--.-........

15..-.. ................ ........... ........

m. .......... .............................

20 ........................................

25...-.-...- ..........................

25

30................ ................ ........

30...... -.. _-_-__-_.

35--.....-----.- --.. -...-. .

35..... ...................................

Dis

charge peistroke .

Pounds.

9 q

Q Q

9.38

9.38

9.33

9.33

9.3

9.3

9.18

9.18

9.16

9.16

Foot 

pounds 

of useful 

work.

116 1

446.4

450.3

450 2

447.4

447.4

441.6

441.6

440.6

440.6

439.7

439 7

Average 

pull 

on rod.

Pounds. 

284.8

288 1

295.4

298.6

303 2

309.2

327.3

304.9

332.7

316.2

335.7

331.9

Foot 

pounds 

of work 

given to 

rod.

570.1

576. 7

591.2

597.7

605

618 9

655.1

610.3

645.9

633.8

651.9

664.4

Mechanical 

efficiency.

Percent. 

78.3

77.4

76.1

^ q

73.9

72.3

67.4

73.3

68.2

69.6

67.4

66.1

Maximum 

pull on 

rod.

Pounds. 

380

375

400

us;

460

490

515

490

565

545

640

655

LIFT, 71 FEET, USING STUFFING BOX.

15.. ........... ....... . .............

l^. .......................................

ZQ. ................................... ....

ZQ. .......................................

25

^&... ............................... ......

30.- .......... ................ ...... .

30 ---..... .............

9.38

9.38

9.32

9.32

9.2

9.2

9.18

9.18

666

666

661.7

661.7

653.2

653.2

651.8

651.8

416.6

389.3

-433.9

421.4

431.3

428.1

439

454.7

834

779.2

868.4

843.4

863.2

856.8

858.6

910.2

79.8

85.4

76.2

78.4

75.6

76.2

75.9

71.6

565

520

585

595

625

630

750

765

LIFT, 82.5 FEET, USING STUFFING BOX.

IK

15 - --..... . _ .....

20.-- --- -.-... --------- ............ 2f\. .......................................

25

25. .......................................

30.. .........-.... .......... ........

30 ..-... - . .. . ..

35--....--....--..---......--...-.. ..

35- - . .......... ..

9.38

9.38

9.33

9.33

9.2

9.2

9.18

9.18

9.16

9.16

773.9

773.9

705

705

759

759

757.3

757.3

755. 7

755.7

475

488.2

478.5

485.3

489.6

488.9

509.7

518. 7

539.2

523.7

950.7

977.1

957.7

971.5

980

978.5

1,020

1,038

1,059

1,048

81.4

79.2

80.3

79.1

77.4

77.5

74.2

72,9

71.3

72.1

59C

59C

705

70C

78C

825

83C

84C

815

1,000

SUMMARY.

To pump large quantities of water with small power economically, 

it is necessary that the pump speed l>e slow, preferably below 20 

strokes per minute; that the pump itself be large and of long stroke, 

and that the valve area be at least 30 per cent of the cylinder crosssection area.

For the more rapid-running pumps the valve area should be still 

larger.

The efficiency of pumps rightly called good pumps may vary from 

20 to 85 per cent, depending on the lift and the piston speed.

A fall of 25 per cent in the efficiency of a pump in the usual range 

of windmill speed is not uncommon.

A pump having a variation of only 5 per cent is possible.

For wells about 20 feet deep there is no need for using a pump of 

less than 75 per cent efficiency for average speeds.

Two pumps may compare very favorably at a certain lift, and much 

less favorably at some other lift not greatly different.
HOOD.] RESISTANCE OFFERED BY CRANK-DRIVEN PUMPS. 65

A pump having an efficiency of over 80 per cent at piston speeds up 

to 100 feet per minute is possible at a 20-foot lift.

Some pumps can be run at a piston speed of 180 feet per minute 

and maintain an efficiency above 70 per cent for lifts above 20 feet.

A pump with very large clack valves, on a very low lift, may give 

an efficiency from 80 per cent at slow speed to 50 per cent at a piston 

speed of 80 feet per minute.

Pumps at slow speed and at high speed alike discharge a little less 

water per stroke than at medium speed perhaps from 1 to 2 per 

cent.

A pump with small delivery pipe may at high speed deliver a considerably larger amount of water than that computed from the cylinder capacity.

With pumps having an ample supply of water the speed may be 

limited by failure of the lower valve if its movement is not limited.

Valves of limited movement are preferable for fast speeds.

The addition of a stuffing box to any form of pump may seriously 

reduce the efficiency.

The initial stress on the upstroke at the higher speeds is the 

destructive element in windmill operation. The use of a device for 

reducing this stress is well worth consideration. At piston speeds of 

only 70 feet per minute this sudden jerk may be equivalent to two or 

three times the weight of the column of water lifted.

A method of pump testing is possible which would determine the 

behavior of valves and give the measure of the resistances at various 

stages of the stroke in such manner as to admit of quantitative statement.

RESISTANCE TO ROTATION OFFERED BY VARIOUS CRANKDRIVEN PUMPS.

The resistance offered to any driving mechanism by a single-cylinder pump varies greatly at different stages of the pump stroke. If 

connection with the pump be through the usual crank, the resistance 

offered by the crank will be slight at each dead center. Piston and 

rod, if of sufficient weight, will afford some motive power on the downstroke. The useful work is done during the upstroke, and the larger 

portion of it during the first part of the upstroke, excepting when the 

speed is very slow. In fig. 39 horizontal distances represent positions of the crank in its circular course during a single revolution. 

The position in each case is located from the lower dead center as an 

initial point. The heights of the vertical lines represent the resisting 

moment at that point. Neglecting the effect of angularity of the connecting rod, the smooth sinusoidal curve represents the resistances to 

turning, assuming the load to be uniform on the upstroke and to be 

diminished to about one-eighth on the downstroke. This diminished 

load is the weight of the piston, rod, etc. The shaded area above 

IRR 14 5
66 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

the zero line represents the work done in raising the piston, rod, and 

water; and that below the line, from 180° to 360°, represents the work 

returned by the falling piston and rod on the downstroke. The outside line and the heavier-shaded portion show the actual resisting 

moments, as computed from the diagram, fig. 40, from the work of 

an 8-inch pump at a lift of 22 feet and a speed of 25 strokes per minute. The additional work required for acceleration of the water, etc.,

FIG. 39. Diagram of resistance to rotation of crank driving a single-cylinder lift pump.

is shown by the heavier-shaded area. This great variation in the turning resistance renders it impossible, without considerable loss of efficiency, effectively to use certain forms of motors.

If a horse be used to operate a pump of this kind, by means of a 

sweep or other suitable turning device, during a stroke of the pump, 

he will meet with resistances such as shown by the vertical lines in 

fig. 39. The pump must not be so large that the maximum moment

900 

7 5O 

600

*5O 

300

 50

!o v % %i t. lo to «* ?u

 P) 1C ts O) O <\l <r CD

Position of crank from lower center.

FIG. 40. Dynamometer diagram of actual resistance at various positions of crank.

can not be reached and overcome at a point somewhere between 50° 

and 90° of the revolution. Even then, for at least half the time, the 

horse will be doing no work at all, and for 60 per cent of the time he 

will be loaded below the average. The line AB gives the average 

resistance. Furthermore, i t appears that the maximum load reaches to 

more than three and one-half times that of the average load. This 

fault may be remedied in part by the use of a fly wheel of moderate
HOOD.] EESISTANCE OFFERED BY CEANK-DRIVEN PUMPS. 67

weight. The unevenness of loading will continue to be so considerable, however, as to render the work of the horse laborious; whereas 

with equalized load he could do even a larger amount of work with 

comparative ease. A windmill encounters the same difficulty, as may 

be seen from the ineffectual efforts it makes in light winds to pass

W/NOMILL PLATFORM

FIG. 41 . Method of counterbalancing a windmill pump.

this point of maximum load. It becomes apparent, too, that if the 

load were evenly distributed the mill would find the light wind power 

sufficient for light" running. By the use of a counterweight a partial 

distribution at least can be effected.

A modification of the horse-power sweep sometimes to be seen is 

a wooden spring bar so attached as to offer a spring resistance during
68 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

the light-pull interval and to assist correspondingly on the heavy 

pull. It has decided merit. As applied to the pump rod of a windmill the modification might take the form of a weight encircling the 

rod and given a direction of motion opposite to that of the rod by 

means of pulleys, as shown in fig. 41. This device should be attached 

to back-geared mills only, and should have its range of action fixed 

so high in the tower as to leave the pump rod free to act in compression without bending. The counterweight should equal one-half that 

of the load on the piston and should range as low in the tower as 

practicable. 

Differential pumps equalize the work between the upstroke and

FIG. 42. Diagram of resistance to rotation of a shaft carrying two cranks driving a duplex

pump.

the downstroke by employing a very large piston rod. If the crosssection area of the piston rod be one-half that of the cylinder, onehalf of the cylinder capacity will be discharged on the upstroke and 

the remaining half by displacement on the downstroke. Work is 

thus equalized between the upstroke and the downstroke. Since, 

however, the work required on the downstroke, which has now become 

in fact a down thrust, necessitates the use of stiff rods in order to 

avoid eompressive bending, there is disadvantage in the practice 

where long rods are required, as in deep wells or for windmills with

: 360*

FIG. 43. Dia,gram of resistance to rotation of a shaft carrying three cranks driving a triplex

 pump.

high towers. For such long thrust rods guides must be provided at 

frequent intervals to preserve the alignment and insure direct action, 

and frictional resistance is thus introduced.

Again, there will be enlargement of the pump rod for a short distance only at the water surface in the discharge pipe. This enlargement is partially withdrawn from the water on the upstroke, thereby 

vacating a space to be filled and thus reducing the discharge, and it 

is lowered into the water on the downstroke, thereby forcing upward 

an equal volume, of water by displacement and thus compensating 

for the previous loss. Yet it does not effect an equalization of work
HOOD.] RESISTANCE OFFERED BY CRANK-DRIVEN PUMPS. 69

between the two strokes. The full cylinder capacity is lifted on the 

upstroke nearly to the full height of the discharge, and on the downstroke but half of this is displaced from the height of the discharge 

opening, requiring little work on the downstroke. It is evidently a 

mistake to regard this device as an equalizer of work. The enlargement, to be fully effective, should continue down to the piston.

Compound pumps having four valves and discharging on both the 

upstroke and the downstroke, or two cylinder pumps in which one 

cylinder makes an upstroke during the downstroke of the other, would 

produce a resistance diagram such as shown in fig. 42. This diagram

FIG. 44. Gould triplex power pump.

represents the crank resistance of a pump discharging the same quantity of water per revolution of the crank as the pump represented in 

fig. 39 (p. 66). The curve below the zero line exhibits the effect of the 

weight of piston and rod, and the curve above the resistance due to 

lifting piston, rod, and water. The shaded portions show the resistances at each point in the revolution, the piston weights balancing 

each other. In this double-cylinder form the maximum resistance is 

about 1.6 times the average resistance, as against 3^ times with the
70 TESTS OP PUMPS AND WATER LIFTS. [NO. 14,

single-cylinder form. At two points in each rotation the resistance 

will be zero, but it does not fall below zero, as with the single-cylinder form. A pump of this kind can be more easily driven by horse 

power than one with a single cylinder, but it is, on the other hand,

FIG. 45. Gould triplex pump and horsepower combined.

too irregular in action to admit of any considerable speed. With a 

single large cylinder counterweighed as above described the resistances are as shown in fig. 42 (p. 68) and the efficiency is greater than 

with two small cylinders.

Fig. 43 (p. 68) shows the resistances in a three-cylinder pump 

arranged to discharge the same quantity per revolution as did the

40 60 14-0 70 80 90 IOO MO 120 

m Revolutions per minute.

FIG. 46. Discharge of Gould 4-inch by 8-inch triplex pump.

two-cylinder and the one-cylinder forms. The three pistons are 

driven from three crank elbows in the shaft set at 120° each to 

each, as shown in fig. 44 (p. 69). The resistance offered by this
HOOD.] RESISTANCE OFFERED BY CRANK-DRIVEN PUMPS. 71

device is very uniform, as appears from the shaded portion of 

the diagram. The maximum resistance is but 6 per cent above 

the average resistance, and a moderate fly wheel renders the motion 

entirely steady.

Such pumps admit of the best use of any constant power, as that of 

a horse or a small engine. In Gould's triplex pump (fig. 44), a horse 

will encounter a nearly uniform resistance and can work to the best 

advantage. A 4 by 8 inch pump of this make was tested by tho

" " 10 20 30 40 50 60 70 80 90 100 119 IZO 190 MO ISO 160 170 ISO

Revolutions per minute. Stroke, 8 inches.

PIG. 47. Varying-efflciency curves of Gould triplex pump, showing effect of varying speed, and

at two different lifts.

author at three different lifts. The crank shaft is arranged to be run 

by a pulley belted from any source of power, or by means of the 

encircling internal master wheel and the vertical shaft carrying 

bevel gears, as in fig. 45, and operated by means of a horse attached 

to a sweep on the master wheel. The very uniform resistance of this 

kind of pump, as shown by the diagram, fig. 48, which represents the 

belt pull or resistance while at work, has opened a large field for it

2f Revolutions of Triplex Pump

Speed 44-per minute

FIG. 48. Dynamometer diagram showing uniformity of resistance afforded by triplex pump.

in connection with various motors. While not so efficient as a singlecylinder pump of equal capacity, yet it applies energy so effectively 

as to render it the more advantageous form for many uses. The 

efficiency of the one tested is seen to be about 60 per cent not 

greater than that of many homemade water lifts. Its durability and 

compactness, however, entitle it to very favorable consideration in 

comparison with any such homemade device.
72 TESTS OF PUMPS AND WATER LIFTS [NO. 14.

Discharges of Gould triplex pump. 

LIFT, 19.75 FEET.

Speed, in revolutions per minute.

30 ... .........

30. ............. ....

36...... ...... ......

47--... ....... ......

58.. .............. ..

56..................

67. . 

60. ............ .....

65 ........ 

70.... ... .......

74...... ...... ......

Discharge 

per minute by 

experiment.

Pounds. 

331

331

353

476

539

581

644

628

672

728

771

Average discharge 

per minute by discharge 

curve.

Pounds. 

308

308

373

490

542

583

595

625

678

730

772

Average discharge 

per revolution.

Pounds. 

10.2

10.2

10.3

10.4

10.4

10.4

10.4

10.4

10.4

10.4

10.4

Speed, in revolutions per minute.

75 .... ...........

79.... ...... ... .....

83 . -. 

90.... _.. - .....

99.... ......... .....

111. ............ ....

114 . .

114 

133..... ........ ....

156....... ..........

166.8. ....... .......

Discharge 

per minute by experiment.

Pounds.

784

816

876

947

1,035

1,175

1,208

1,213

1,390

1,630

1,720

Average discharge 

per minute by discharge 

curve.

Pounds.

783

825

857

941

1,035

1,161

1,192

1,192

1,390

1,631

1,745

Average discharge 

per revolution.

Pounds. 

10.4

10.4

10.4

10.4

10.4

10.4

10.4

10.4

10.4

10.4

10.4

LIFT, 38.55 FEET.

40..... .............

45 .......

416

482 

827

416 

468 

803

10.4 

10. 4 

10.4

84 . ......

90...... ....... .....

898 

964

853 

941

10.4 

10.4

Figures from efficiency test of Gould triplex pump 4 by 8 inches. 

LIFT, 19.75 FEET.

Speed, in revolutions per minute.

25.9 --. ... --. --. ...... ......... 

9^. ....................................................

29.5 - -- .- -.- . ..

32.8-................. .................... ..........

40.5 

43.8 - - 

43.8..- .. . . . - . 

46.9.. - . . 

48 

49.6 

51.8 -- -- . . 

58.8. .... 

58.8 

60.6............. ....... . . 

68.2............... ...... . .. ..... .........

"18.2....... ........................................ ....

76....... ..............................................

78.2........................ ......................... ..

79.8.. - - 

81.1. . . . ...... . . .

85.7. .... .... . . .. ......... ......

95.3 - . 

98.3...... . ..... .................... 

100. -. .. .. . .-.- - 

100

101 . - 

105.3... ....... - .-.-. -- 

180 - -. ... - 

135 . -- - 

157.9 

171 A.

YS1.4:.. ...................... ............ ..............

Discharge 

per minute.

Pounds. 

265

376

303

338

430

455

455

487

500

515

540

607

612

639

712

764

794

815

825

848

895

997

1,036

1,047

1,047

1,055

1,100

1,255

1,305

1,650

1,790

1,790

Footpounds of 

useful 

work per 

minute.

5,234

5,451

5,984

6,675

8,295

8,986

8,986

9,618

9,875

10, 171

10,665

11,988

12,087

12,630

14,063

15,086

15,681

16,096

16,392

16,748

17,666

19,690

20,363

20,678

20,678

30,836

21, 725

24,786

35,773

33,587

35,853

35,352

Footpounds of 

work given 

to putnp 

per 

minute.

9,715

10,370

11,429

13,383

16,008

17,569

16,588

17,213

19,405

18,133

20,260

22,410

21 953

22,' 771

26,391

30,330

29,063

29,809

33,309

33,072

35,743

37,750

39,710

40,175

40,413

39,430

42,409

51,698

55,302

78,199

86,142

87,937

Mechanical efficiency.

Per cent. 

53.8

52.5

53.3

50.2

51.8

51.1

54.1

55.8

VI Q

56.1

52.6

53.5

55

55.4

53.2

49.7

53.9

54

48.9

52.2

51.8

53.1

51

51.4

51.1

52.8

51.2

47.9

46.7

41.6

41

40.2
HOOD.] VARIOUS WATER LIFTS. 73

Figures from efficiency test of Qould triplex pump Jfby 8 inches Continued.

LIFT, 38.55 FEET.

Speed, in revolutions per minute.

43.1............ ........... .- . ... 

44.8............ ........... .............................

50.8...................................................

57.7 ........ ........................................

59.4....... ....................................... ......

61.2....................................................

65.2.. .............................................. ....

83.3... ..._ . ...... ...__.. . ... . .

90.9.............................. . ................ ....

93.3 ........ ................ ...... ...... - .-. 

92.3-.... .......... ....................................

107.1................... .................... ........

Discharge 

per minute.

Pounds. 

439

465

530

600

618

640

675

sro

950

965

965

1,120

Footpounds of 

useful 

work per 

minute.

16,923

17,925

20,431

23,130

23,824

24,672

26,022

33,538

36,622

37,201

37,201

43,176

Footpounds of 

work given 

to pump 

per 

minute.

25.801

27,167

31,765

35,144

37,177

39,027

41,058

52,978

57,212

58,517

60,065

69,324

Mechanical efficiency.

Per cent. 

65.6

65.9

64.3

65.8

64

63.2

63.3

63.3

64

63.5

61.9

62.2

VARIOUS WATER LIFTS.

On tlie Western plains devices for raising water other than the 

reciprocating pumps are not common. The centrifugal pump, which, 

if driven at a high and uniform speed, has an efficiency of about 66 

per cent at a lift of about 16 feet, has its field limited to tracts where 

water is to be found at comparatively shallow depths and to applications where motive power giving uniform and high speed may be 

economically employed. It is not well adapted to horse or windmill 

power.

Early forms of water lifts are mentioned and illustrated by Weisbach. While these are of interest, they are not likely to be used by 

American farmers, who are impatient of slow and laborious methods. 

The following statements are abstracted from Mechanics of Pumping Machinery, by Weisbach and Hermann:

Men, bailing with buckets holding about one-third of a cubic foot 

each, can lift 15 buckets per minute,. 3 to 4 feet high, for a length of 

time daily equivalent to six hours of steady labor. This amounts to 

about 390,000 foot-pounds per day, or a quantity of water sufficient 

to cover an acre one-half inch deep. With deeper wells the sweep or 

weighted lever will yield about the same result in foot-pounds daily 

per man. At a crank handle an ordinary laborer can exert a force of 

15 pounds in steady work, or can labor steadily at a rate of approximately 3,300 foot-pounds per minute. This is about the best manner 

of employing human labor. From a 10-foot well a man with a winch 

and bucket, properly proportioned, can cover an acre with one-half 

inch of water in a day. Approximately the same can be done with a 

hand pump suitably proportioned to the lift. The Dutch scoop, which 

consists of a long-handled scoop shovel suspended from an overhead 

support by a rope and swung by three men, will lift water 3£ feet and 

throw it 6^ feet horizontally. One man working thus alone can do
74 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

about as much work as by the bailing method, but three men working 

together on a single scoop will do more than five men bailing separately.

BUCKET LIFTS.

A very old device for raising water consists of a vertical rope or chain 

carrying buckets, the chain running on a power-driven sprocket wheel 

at the top and maintained in proper position by a loose sprocket suspended in its lower loop. The modern development of the sprocket 

wheel and of the cast-link belt, in which links may be had specially 

adapted to receive sheet-metal buckets, has brought the bucket lift

FIG. 49. Vertical section of bucket of water elevator.

into renewed use. A modern form is shown in PL I, A. (See also 

fig. 49.) Its great advantages are uniformity of resistance and steady 

delivery. Its disadvantages are: large size for a given capacity, 

necessity imposed for using a large well, and difficulty in securing 

a perfect delivery. The buckets must be so made that in dipping 

into the water air will not be entrapped, and so that when delivering 

air may again readily enter. It has so far not been found practicable 

entirely to prevent loss from spilling of a portion of the water lifted. 

Furthermore, for emptying, the lift has to exceed somewhat the height 

of the discharge point. From these two inherent defects results a 

noticeable failure in efficiency.

SEAMAN BUCKET LIFT.

A lift designed for irrigation work, and made by Seaman & 

Schuske, of St. Joseph, Missouri, was tested, and the result appears
U. S. GEOLOGICAL SURVEY WATER-SUPPLY PAPER NO. 14 PL.

A VIEW OF LINK-BELT WATER ELEVATOR.

.B.-VIEW OF BOYCE WATER LIFT.

HOOD.] BUCKET LIFTS. 75

in fig. 50. This device consists of a series of galvanized-iron buckets, 

riveted to lugs carried on a common link belt. The sprocket chains, 

at each side of the bucket, are carried on two sprocket wheels. Each 

bucket is provided with a clay-ball valve, carried in a wire cage 

at the bottom of the bucket. The leather clack valve is a very old 

form for this use. With the rise of the bucket the valve of whatever design covers a circular aperture in the bucket bottom, and

15 -Buckets. Sea man Bucket Lift.

^\f\^\<wy^^

Zero /ine

Speed 35 buckets per mm.

FIG. 50. Dynamometer diagram showing uniformity of resistance afforded by Seaman bucket

lift.

opens in turn with the descent into water, thus obviating the possibility of entrapping air. In the pendent loop of the chain two sprocket 

wheels on a shaft run without bearings. A gear on the main sprocket 

shaft is driven by a pinion, the power for which may be derived from 

any source.

The uniformity of the resistance offered by this lift is shown in fig. 

50, taken from a recording dynamometer when the device was delivering about 300 pounds of water per minute, from a depth of 18.8 feet.

40 SO 70 eo 9O 100 MO UO I3O I4O ISO I6O I7O 180 190

Buckets discharged per minute.

FIG. 51. Discharge per bucket of Seaman bucket lift at various speeds.

Fig. 51 gives the discharge per bucket at various speeds, and fig. 52 

the total discharge. The efficiency, as shown in fig. 53, is about 60 

per cent at the favorable speed of 100 buckets per minute. A peculiar drop appears in the discharge record at speeds ranging from 100 

to 130 buckets per minute. At very slow speed the discharge is less, 

due to leakage around the valve, and due, further, to failure of the 

buckets to empty into the discharge chute. At higher speed the 

valve loss becomes small, but the buckets soon pass the discharge
76 TESTS OF PUMPS AND WATER. LIFTS. [NO. 14.

chute before fully emptying. At still higher speed centrifugal force 

aids greatly in discharging the bucket and temporarily increases the 

discharge. As speed still further increases, however, swaying of the 

chain causes loss, by slopping, from the rising buckets.

7

30 40 50 60 70 80 90 100 110 120 130 I4O ISO 160 ~ 170 180 190'

Buckets discharged per minute.

FIG. 52. Total discharge of Seaman bucket lift at various speeds.

This pump has been successfully used in connection with a windmill. It can be recommended wherever a large open well is available, 

and where the depth to water is moderate, say from 20 to 35 feet. It

"30 4,0 SO 60 70 60 90- 100 110 120 130 140 ISO 160 170 180 190

Buckets discharged per minute.

FIG. 53. Efficiency curve of Seaman bucket at lift of 18.8 feet.

is best adapted to small powers of from 1 to 5 horsepower. The 

power necessary to operate such a pump is about double that represented by the useful work done, in water raised and discharged.
HOOD.] BUCKET LIFTS. 77

Discharges of Seaman bucket lift at various speeds.

Speed, in buckets 

per minute.

38.................

44.. ............ ._

48.. ............. .,

58.................

68....:. .......

73.. ..............

75.................

77.................

78.................

81.............. .

85.................

87...............

90.................

91.................

92............ .

94.................

94.................

95.................

97.............. .

97.................

98.................

99................

99....... .

103.................

104.................

104................

106..............

106. ............ ....

106.................

108..... ............

111. ............. ...

1U... ..............

112............... .

115..... ............

115. ............... .

116. ............ ....

116.................

Discharge 

per minute by experiment.

Pounds. 

315

389

423

555

651

750

768

805

803

841

866

918

923

937

963

974

993

1,114

1,025

1,044

1,014

1,094

1,084

1,108

1,107

1,146

1 123

1,127

1,114

1,140

1,149

1,161

1,151

1,170

1,175

1,200

1,175

Average discharge 

per minute by 

discharge 

curve.

Pounds. 

310

385

433

558

682

743

770

793

804

841

889

912

948

960

972

996

996

1,008

1,032

1,032

1,044

1,056

1,056

1,092

1,114

1,114

1,127

1,127

1,127

1,138

1,151

1,151

1,155

1,175

1,175

1,185

1,185

Average discharge 

per 

bucket.

Pounds. 

8.158

8.75

9.02

9.62

10.03

10.17

10.26

10.3

10.31

10.38

10.45

10.48

10.53

10.55

10.56

10.59

10.59

10.61

10.63

10.63

10.65

10.66

10.66

10.70

10.71

10.71

10.63

10.63

10.63

10.53

10.37

10.37

10.31

10.22

10.22

10.2]

10.21

Speed, in buckets 

per minute.

117 ....... .........

118 

119...... ..........

121 .... .

122.--......---...

122

123 

124 . 

125

126 - -----

126 

138- . 

128 ----------

130 

130 .

131 .

133. 

134 

134

134 .. 

136 . _ 

138-...... -..

139.......... ......

141. 

144 

145 - 

149 ...... ...... 

160 

158.. 

178 ....

185 .

186 

186 

186 ..... ...

187 .- 

187-..... ......

191-... ........

Discharge 

per minute by experiment.

Pounds. 

1,191

1,205

1 223

1? 247

1,286

1,290

1,295

1,281

1,317

1,348

1,379

1,358

1,351

1,380

1,367

1 427

1,412

1,404

1,420

1,442

1,437

1,362

1,477

1,490

1,534

1,461

1,559

1,561

1,618

1,685

1,745

1,752

1,697

1,720

1,757

1 752

1,779

Average discharge 

per minute by discharge 

curve.

Pounds. 

1,193

1,205

1,218

1 254

1,273

1,273

1,290

1,307

1 321

1,335

1,335

1,360

1,360

1,382

1,382

1,395

1,415

1,426

1,426

1,426

1,447

1,465

1,475

1,492

1,513

1,520

1,548

1,556

1,610

1,718

1,750

1,755

1,755

1,755

1,758

1,758

1,779

Average discharge 

per 

bucket.

Pounds. 

10.19

10.21

10.23

10.31

10.43

10.43

10.48

10.54

10.57

10.59

10.59

10.62

10.62

10.63

10.63

10.64

10.64

10.64

10.64

10.64

10.64

10.61

10.61

10.58

10.5

10.48

10.4

10.37

10.12

9.65

9.46

9.42

9.42

9.42

9.4

9.4

9.31

Figures from efficiency tests of Seaman bucket lift. 

USEFUL LIFT, 18.8 FEET.

Speed, in buckets per minute.

35.3 - - -. - 

1Q 7

48A. .................................... ....

50...... ............................... ......

S0.i. ........................................

54... . - .

57.1 

57.1...... ...... ...... . . ._. -.

60

63.1 - - 

65.2 - - - 

69.7...... . 

70.6 . ...... ........ ......

71.4 .. . ... .

73 

n.... .......................................

rr...... .....................................

77.9 . _ ......

78.9 .... . 

S3.3.. .......................................

84.5 ...... ...............................

Discharge 

per 

minute.

Pounds. 

275

330

440

4fiO

465

508

547

547

KOJ

621

648

705

713

724

743

757

Kftl

815

870

884

Footpounds 

of useful 

work per 

minute.

5,170

6,270

8 272

8,648

8,835

9,652

10,393

10,393

11,116

U 7OQ

12,312

13,395

13,547

13,756

14,117

14,383

15,086

15,115

15 322

16,356

16.619

Footpounds 

of work 

given to 

machine 

per minute.

12,675

13,564

17 nos

17,245

17,883

17,931

9O W7

20,025

9fi QO1

22 132

22,488

25 218

24 143

24^859

35 825

25,644

27,388

26 422

27,563

28,740

28.319

Mechanical efficiency.

Per cent. 

40.8

46.2

48.6

50.1

49.4

53.8

51.3

51.9

53.1

53.3

54.7

53.1

56.1

55.3

54 6

56

IK

57.2

55.6

56.9

58.6

Lift.

Feet. 

18.8

19

18.8

18.8

19

19

19

19

19

19

19

19

19

19

19

19

19

18.8

18.8

18.8

18.8
78 TESTS OF PUMPS AND WATER LIFTS. [NO. 14,

Figures from efficiency tests of Seaman bucket lift Continued. 

USEFUL, LIFT, 18.8 FEET Continued.

Speed, in buckets per minute.

89.5.-...----------. .....................

90. .-- - -_-.... . ..

94.4....... ---.-. ....--.. .. -........

95.9...... ................................

98.3........... ..............................

98.3.... ......... .......-...... ...........

100.......-. ..............................

101.7-...- ............................... im.i. ................................... .... in.i.... ....................................

117.6--.-. ................ ..............

117.6...... .................................

117.6...... -. ... ........ ...........

IgSA...... ..................................

1225

127.6. ...... . __....._.._. . .

130. - ___.._.

134.8--..-..--..-.- ....................

136 - . 

136.4--.. . . .. .._....

136.4 -- .- _ 

137.9 .. . ..

139.5 .

143

143... . . . . . .. ........

1446

146.3 . - . 

150. ..

151.9......- . ......... ........

154. . . . .. .. ...... 

160... . . .. - .

171.4.. ....... ........ ... . 

171.4. ..... ,. . ........ ...... ......

171.5-.....-- ......... .. ...... 

184.6... _.... ._..._ _ 

187.5..-..-. ............... ..... . .

Discharge 

per 

minute.

Pounds. 

943

948

1,000

1,030

1 048

1^048

1,068

1,090

1,133

1 153

1 300

1^300

1 300

1 384

l'384

1,355

1,383

1 435

1^448

1 450

l'450

l',463

1,480

1,505

1,505

1,516

1,530

1,556

1,570

1,584

1,623

1,685

1,685

1,687

1,748

1,760

Footpounds 

of useful 

work per 

minute.

17, 898

17 833

18,800

1Q 17fi

19,912

19,702

20,078

20,492

2i; 300

21,657

32 800

32,560

32,560

24,139

24,139

25 474

26^258

26,978

27,512

27,260

27,360

27,797

27,824

38,595

28,595

38,804

39,070

29,564

39,830

30,096

30,818

32,015

32,015

31, 715

33,212

33,440

Footpounds 

of work 

given to 

machine 

per minute.

30,937

30,721

32,235

32,415

32 124

32,014

33,674

32,630

35,529

38,076

37 236

40J60

39,211

40,623

39,453

42,633

41,503

43,386

43,607

46,750

44,405

42,816

44,809

43,584

44,442

44,198

45,058

44,541

52,101

45,003

48,075

47,638

47,436

52,199

51,996

53,337

Mechanical efficiency.

Per cent.

w s

58

58.3

59.1

61.9

61.5

59.6

63.8

59.9

56.8

61.2

56.1

59.4

61.1

59.7

63.2

63.1

63

58.3

61.3

64.9

63.1

65.6

64.3

65.1

64.5

57.2

66.8

64.1

67.2

67.5

60.7

63.8

62.7

Lift.

Feet. 

19

18.8

18.8

18.8

19

18.8

18.8

18.8

18.8

18.8

19

18.8

18.8

18.8

18.8

18.8

19

18.8

19

18.8

18.8

19

18.8

19

19

19

19

19

19

19

19

19

19

18.8

19

19

SAME USING TWO VALVES IN EACH BUCKET.

96 . - 

100 - - 

100

102.5.. .. . . .

103.4... . ---- ----------

111.1 ............ .... . 

115.4-- 

122 5

125 

130.4--- . .. ......

133.3 - - . - - 

142.8 .-. . 

142.8 - . 

142.8- - - -. 

151.9.....-. .... .... .... ..... .... ....

162.1 - - -- - 

169--- .... .. ...... .... . 

184.6 

187.5 .... .. ...... .......

1,032

1,069

1,069

1,098

1,108

1,152

1,178

1,283

1,323

1,383

1,430

1,505

1,505

1,505

1,570

1,634

1,673

1,749

1,760

19,401

20,204

20,078

20,642

20,941

21,657

32 190

24,130

34,872

26,138

26,838

28,294

38,294

38,444

29,516

30,719

31,452

32,881

33,088

35,447

36,738

36,604

37,205

37,109

39,361

40,960

42,151

42,830

44,058

45,895

50,222

50, 770

48,856

50,724

54,713

54,839

63,934

63,337

54.7

55

54.8

55.4

56.4

55

54.1

57.2

58

59.3

58.4

56.3

55.7

58.1

58.2

56.1

57.2

52.2

52.2

18.8

18.9

18.8

18.8

18.9

18.8

18.8

18.8

18.8

18.9

18.9

18.8

18.8

18.9

18.8

18.8

18.8

18.8

18.8

LIFTING BY ANIMAL POWER.

It is somewhat surprising that horses are not more used for lifting 

water. In small operations, or where a farmer is experimenting with 

a view to irrigation, horse power would seem to be the resource readiest to hand. It is but little recognized how much work may be got
HOOD.] LIFTING BY ANIMAL POWER. 79

from a horse if a suitable device be provided. Farm horses, like their 

masters, work especially hard during special seasons. Their rate is 

higher then than it could be if they were worked continuously. If 

the following estimates at first sight appear low, it should be understood that they are made on the assumption of a uniform daily rate. 

It is assumed that a good work team of two horses will pull 300 pounds 

steadily during a day of eight hours. In plowing, this effort is frequently doubled. For horses worked continuously at a straight-away 

pull, 125 pounds each for medium-weight horses is good average work. 

For occasional short periods a horse can throw one-third of his weight 

into his effort, but he can not do so at frequently recurring intervals. 

The maximum load for a horse, if recurring at short intervals, should 

not exceed double the average fair load, and the more frequently it 

recurs the less it should be. The natural gait of a work horse is 

about 3 feet per second. If loaded to pull 125 pounds at this gait, his 

work would be equivalent to 22,500 foot-pounds per minute, or about 

two-thirds of a horsepower. 

If a horse could be worked steadily at some device the' efficiency of

3 3 which would be 66 per cent, he could lift, in a ten-hour day, ^- acreLi

feet of water, L being the height of lift in feet. In many cases the 

lift will be about 15 feet, giving an output per horse of 0.22 acre-foot, 

and if the depth of irrigation be 3 inches, accompanied with the usual 

waste, the water for about three-fourths of an acre per day could 

easily be supplied by two horses. With storage and with intervals of 

ten days between irrigations a team, of two horses could care for from 

5 to 7 acres. While to the enthusiast these figures will not appear 

large, they are large enough to justify the use of horses in small undertakings. The assumed efficiency of 66 per cent is, in fact, low rather 

than high, and a device for the utilization of horsepower that shall 

attain to this percentage ought to be possible of achievement by 

mechanical skill.

The foregoing is a statement of what it is possible to do with horses 

if suitable machinery be provided; but the majority of existing devices 

will not do so well as this. As shown by the stress diagram for a 

single-cylinder pump (fig. 39, p. 66), the maximum stress is more than 

three and one-half times what would be the average stress. As the 

maximum effort of a horse should not rise to more than double his 

average effort, and as the average resistance in the single-cylinder 

pump is 28 per cent of the maximum resistance, the actual average 

load put on the horse can equal only 28 per cent of twice his average 

effort, or 56 per cent of his possible average effort. In order to get 

full work out of a horse, therefore, it would be necessary, at some 

period of each pump stroke, for him to make an effort more than 

three and one-half times his most efficient average effort. This would 

be too great irregularity of exertion.
80 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

A horse can not do full work on an unbalanced single-cylinder 

pump. It is imperative that recourse be had to some device which 

will more nearly equalize his efforts. The use of a sweep, by reason 

of the circular course a horse has to follow, involves a loss of 20 per 

cent of efficiency, as compared with the possible efficiency in a straightaway pull. At each point of his actual course he will be pulling at an 

angle with his most effective course, which at any point will always 

be a tangent to the circular path. Tests of the usual sweep horsepower show an efficiency of about 80 per cent.

A horse can deliver to a pumping device, through the medium of 

a sweep, 80 per cent of 80 per cent, or 64 per cent of his best effort. 

If the pumping device have an efficiency of 60 per cent, such as 

shown by the bucket lift, the water actually lifted will represent 80 x 

80 X 60 per cent, or 38.4 per cent straight-away average effort of the 

horse. In the operation of a bucket lift of this kind,

8640 

L P'

in which L is the total lift of water in feet, and p the number of 

pounds discharged per minute for each horse employed.

To determine the proper speed for the bucket lift, let S be the. length 

of sweep in feet, L the lift of water in feet, I b d the dimensions,, 

respectively, of the buckets used in inches, and n the number of 

buckets emptied during one revolution of the sweep; then, for each 

horse

10,4008

Omitting from consideration what might be done by overtaxing the 

horse, a larger output than this is to be looked for only through 

increase of efficiency in the mechanism of either the sweep or the 

pump. This low efficiency, in which but 38 per cent of the power 

expended by the horse appears as returned in useful work, lies at the 

root of the nonuse of horsepower for these light water-lifting operations. As already stated, the difficulty does not to the writer appear 

insuperable.

SOME INDIAN DEVICES.

Among devices employed in India for raising water from wells by 

animal power a number have been tested as to their mechanical efficiencies, and have been reported upon to the Madras government in 

Bulletin No. 32 of the department of land records and agriculture, 

under the title, Experiments with Water Lifts. The following copious 

extracts from this interesting report, together with figs. 54, 55, and 56, 

which are selected reproductions from its plates, show what may 

be accomplished with these rude devices of the Indian farmer, to 

whom the cost of modern machinery is, as a rule, prohibitive.
HOOD.] SOME INDIAN DEVICES. 81

The experiments conducted by the committee had the following objects in 

view: The determination of 

(1) The quantity of water and the effective height it was lifted in a given time 

by bullocks of known weight, and working in a way that did not unduly fatigue 

them.

(3) The quantity of work actually obtained from the animals in the same 

time.

PLAN

PIG. 54. Plan and vertical section of Stoney water lift.

(3) The quantity of work which might have been obtained from the animals in 

the same time had the working of the lifts been continuous.

The first quantity divided by the second gives the mechanical efficiency of the 

water lift, and the first quantity divided by the third gives its absolute efficiency 

as a machine for utilizing animal power in a given way.

(4) The quantity of work represented in water lifted per hour divided by the 

weight of the bullocks in pounds. 

IKR 14 6
TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

j i. ,n*n rfn. ill ifn rm . L

FIG. 55. End elevation of Stoney water lift.
HOOD.] SOME INDIAN DEVICES. 83

This yields a constant which, on the assumption that the animals employed in 

working the various lifts are all equally strained, enables a comparison to be 

made between very different types of water lift and very different methods of 

applying animal power. In some lifts only the draft of the animals is utilized. 

In others, as for instance the ordinary single mhote, both draft and weight are 

utilized, whilst in a third class only the animals' weight is made use of, as in Mr. 

Subba Rao's oscillating platform; and between such very different methods the 

constants yielded by (4) seems to be the best method of making comparisons of 

the actual value of different machines for lifting water. It must be remembered

| $%$%$$$%!, \

FIG. 56. Whim used with Stoney water lift.

that though the mechanical efficiency of a water lift may be high, yet the mode 

of getting the work out of the animals employed may be bad, and the actual value 

of the constants yielded by (4) depends on the assumption that the strength of 

animals is proportional to their weight, which is probably roughly true for animals in good working condition and in the prime of life, and on the accuracy 

with which it is possible to estimate whether two animals working in different 

ways are exerting themselves to their full working capacity. The figures therefore obtained are only to be taken as offering a rough method of comparing the 

different lifts, and as a guide in estimating their probable value as machines for 

lifting water.
84 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

Stoney's water lift. The principal feature in this lift is the employment of 

buckets of wrought iron, suspended in a stirrup by two adjustable pivots 

attached to the bucket very slightly above the center of gravity of the bucket 

when full of water. The mouth of the bucket is inclined as shown in the drawing, and the lower ends of the stirrup are turned outward and encircle steel 

wires which are suspended in the well from screw eyebolts attached to the framing above. The wires are fastened by some convenient means to the bottom of 

the well and act as guides to the bucket, ascending and descending, and prevent it 

from either turning round or swaying to and fro, and thus striking either the sides 

of the well or the second bucket. On the bucket being lowered into the water it 

turns horizontally and rapidly fills with water, and on being drawn up assumes 

a vertical position and rises steadily out of the water, till the discharging level is 

reached, when the upper side of the inclined mouth comes into contact with an 

iron bar fixed across the framing of the lift, and the stirrup, continuing its 

upward motion, causes the bucket to revolve about the point of contact of the 

bucket with the iron rod, and thus discharge its contents into the delivery trough. 

The lift was worked by carrying the ropes which hold the buckets over guide 

pulleys to a whim turned by either a pair of bullocks or a single bullock. Two 

buckets were attached and the ropes arranged so that as one bucket ascended the 

other descended, and the dead weight of the buckets was balanced. The whim 

consisted of a drum built of wood and carried by an iron spindle on the top of a 

post firmly built into the ground. The bullocks worked at the end of a long 

arm, the circumference swept out by which was 3.85 times the circumference of 

the drum. The whim is worked alternately in one direction and the other, the 

cattle being made to turn round while the biicket is discharging its contents. 

The lift was provided with two sets of buckets of a nominal capacity of 30 and 25 

gallons (English), respectively. In the following table is exhibited the data 

regarding their capacity:

TABLE I.

No. 1.....

No. 2--- 

No. I.,...

No. 2.-.-

Weight, 

empty.

Pounds. 

101

yo

68

67

Weight 

of water 

when full.

Pounds. 

296

295 

245

Weight of 

water delivered by 

buckets.

Pounds. 

280

280 

330

*5oU

The capacity of the lift was tested by working it with a single Nellore bullock 

weighing 1,146 pounds on three different days, but owing to insufficiency of water 

in the well no test could be continued for more than two hours forty-two minutes. 

In Table II the results obtained are shown:

TABLE II.

Date.

July 16, 1895.... '

July 17, 1895 _-.....{ 

July 18, 1895.. ..... {

Time 

started.

8-37 

9-37 

2-04 

3-04 

4-04 

3-00 

3-00 

3-29 4-29

Time 

stopped.

9-37 

10-07 

3-04 

4-04 

4-46 3-W 

3-51 

4-29 

5-29

Number 

of 

buckets 

raised.

a 88 

a 51 

a 91 

a 86 

a 63 

a 85 

a 73 

6167 ')79

Lift at beginning.

Ft. in.

22 0

anoi

22 2

22 2

Lift at 

end.

Ft. in.

23 3

23 <H

23 4

Mean 

lift.

22.625

23.24

22.87

22.75

Gallons 

raised 

per hour.

2,594

2,489

2,391

1,886

Footpounds of useful Work 

done.

586,900

575,500

546,900

429,060

a30-gallon buckets. b 25-gallon buckets.
HOOD.] SOME INDIAN DEVICES. 85

The mechanical efficiency of the lift when just moving is 83.6 per cent, and at 

the ordinary working speed, 79 per cent. It was found that the speed at which 

the bullock walked when exerting a draft of 92 pounds was, as the mean of a number of observations, 3.64 feet per second, and that in 162 minutes he raised 240 

buckets of water, lifting each bucket 23 feet. Walking at this speed vrithout 

stopping, which without doubt the animal could have easily done, he could have 

lifted 401 buckets, so that he was only usefully employed for 59.7 per cent of the 

time. The absolute efficiency of the lift was therefore 79 by 59.7 per cent or 47.2 

per cent. This calculation neglects to take into account the extra pull which is 

necessary to tilt the bucket to make it discharge, which was found to amount to 

122 pounds and which was exerted through about 3 feet. This quantity would 

only affect the result very slightly and the decrease in efficiency would diminish 

as the height to which the water has to be raised increases.

A device of this kind is among the possibilities of home manufacture in any American community. The results given were obtained 

from actual trial and could be duplicated here by the use of horses.

A device called an improved single mhote was also tested and 

described. A water carrier holding 31 gallons was provided, at its 

bottom opening, with a large leather pipe. This carrier or bucket 

was suspended by a rope from a pulley, and the free end of the leather 

discharge pipe was separately suspended and held up by a second rope 

passing over a pulley below the bucket pulley at the ground surface. 

The discharge end of the leather pipe was ordinarily held above the 

bucket, and in this position permitted no discharge. Upon the ascent 

of the bucket and its upturned discharge pipe or leather tube the tube 

would be drawn out along the ground by its controlling rope and discharge effected as soon as the bucket passed above the ground surface. The two ropes were connected in such manner that they were 

operated together, the pull being exerted by bullocks descending an 

inclined plane which had been excavated below the ground level.

The improvement on the ordinary single mhote is effected by attaching a rope 

to the draft rope and carrying it on to the large drum of a kind of windlass 

erected at the end of the inclined plane and at a considerable height above the 

level of the end of the run. Cords wound round two smaller drums, one on each 

side of the large drum, carry weights, which it was found almost balanced the 

weight of the empty bucket, so that at the end of a lift, as soon as the bucket was 

empty, the draft rope automatically rose in the air and the bullocks were able to 

turn round and walk up the inclined plane in a natural, easy manner instead 

of being forced backward, as is the common plan. The improvement effected 

is undoubtedly a very great one, as not only is the weight of the empty bucket 

practically balanced, but the animals are also spared the cramped and unnatural 

backward walk up a steep incline, which probably tires them more than their 

exertions in drawing the bucket out of the well. The experiments made on this 

lift were not very extensive, but the following results were obtained and are 

worthy of record. The mhote was worked by two bullocks weighing 732 pounds 

and 616 pounds, respectively, or in the aggregate 1,348 pounds. The bucket, 

which was of iron and fitted with a leathern discharge trunk, weighed 43 pounds 

and when full held 31 gallons of water, but the mean quantity lifted, as measured 

into a tank, was 24.2 gallons per lift, the rest being spilt or lost by leakage. With 

the bullocks employed the rate of working was 90 lifts per hour, and the height of 

the lift being 23 feet, the total quantity of work usefully done amounted to 500,940
86 TESTS OF PUMPS AND WATER LIFTS. [NO. 14.

foot-pounds per hour. The draft exerted by the bullocks down the inclined plane 

was found to be 383 pounds. The useful work done in a single lift was 24 x 10 X 23 

or 5,570 foot-pounds, whilst the bullocks exerted a pull of 383 pounds through 25f 

feet, the bucket having to be raised an extra 2-J- feet to enable it to discharge its 

contents, and the work done is equal to 9,760 foot-pounds. The bullocks then had 

to return up a gradient of 1 in 5,28 feet, in doing which they expended 6,510 footpounds of energy in lifting their own weight against the action of gravity. The 

total amount of work done by them in a single lift was, therefore, 16,570 footpounds and the useful outturn 5,570 foot-pounds, so that the efficiency of this 

method of lifting water is not greater than 34.3 per cent. As compared with the 

ordinary single mhote, the great advantage which this lift possesses is that it 

allows the bullocks to turn round at the bottom of the inclined plane and ascend 

walking forward instead of backward, an advantage which it would be difficult 

to express numerically, but the balancing of the bucket diminishes the draft by 

about 40 pounds and increases the efficiency of the lift by about 6.3 per cent, not, 

perhaps, a very large amount, but still by no means a negligible quantity.

A see-saw lift described is unique, and might be developed into a 

practical device:

In this form of water lift the bullock is made to walk along a platform supported 

on a roller, and by his weight it is caused to oscillate up and down. Two ropes 

are attached to one end of the platform and wound round two small drums forming part of a windlass, round the large drum of which a rope working an ordinary 

single mhote is passed. The platform is not supported in the middle, but at some 

distance therefrom, so that the working end of the platform greatly preponderates 

and the bullock has to walk to the free end of the platform to tilt the longer segment up and lower the bucket into the well. The platform is 24 feet long and the 

supporting roller is fixed 15 feet 3f inches from the working end. It was not possible to weigh the platform, and calculations of its weight, based upon the quantity of timber used in it, can only be approximate. It was, however, carefully 

measured up, and assuming that the teak wood, of which it was constructed, 

weighed 45 pounds per cubic foot, the weights of the two sections are 1,450 pounds 

and 850 pounds. To diminish the shock when the free end falls and the bucket 

is lowered into the water, 230 pounds of iron rails are fastened underneath the 

platform by a short chain, so that just before this end of the platform reaches its 

lowest position the rails rest on the ground and their weight ceases to act, and the 

platform comes to rest more gently than would be the case if the velocity of 

descent continued to accelerate to the very end. The rapes from the platform 

were wound round drums, the circumference of which was 3 feet 2^ inches as 

measured by unwinding one coil of the rope, and the mhote rope was worked from 

a drum 7 feet 10 inches in circumference so that the motion of the working end of 

the platform was multiplied 2,44 times. With the bucket empty and the platform 

horizontal the load at the free end could be varied from 160 pounds to 362 pounds 

without disturbing the equilibrium, whilst with a load of 247 pounds in the bucket, 

equal to 24.7 gallons of water, the platform remained horizontal, though the load 

at the working end varied between 584 pounds and 275 pounds. Taking the mean 

between the two extreme values to be the actual weight required to balance the 

platform, it is possible by taking moments about the center to determine the only 

force acting on the platform which was not measured, viz, the weight of the 

empty bucket and ropes acting with a lineage of 2.44 to 1. With the bucket 

unloaded, the weight works out as 65.4 pounds and when loaded 62 pounds, a 

remarkably close agreement.

The lift was worked during the trial by a bullock weighing 700 pounds and a 

man weighing 117 pounds, The rate of working was 81 lifts per hour from a well 

18 feet 1 inch deep. The average quantity of water brought up by the bucket, as 

measured into a tank, was 23.5 gallons, and the useful work done per hour
HOOD.] AN AMERICAN DEVICE. 87

amounted to 344,210 foot-pounds. The bullock and the man together were much 

heavier than was really necessary, and they did not use the full length of the platform, so that it is difficult to estimate the work done by them in working the lift, 

but the mechanical efficiency of the lift on the day of trial can-be ascertained by 

multiplying the fall of the front end of the platform by the force required to set 

it in steady motion when lifting a bucket full of water. The total height the 

bucket had to rise to discharge its contents was 22 feet, and the end of the platform therefore fell 9 feet and the work done was 584 x 9 = 5,256 foot-pounds. To 

raise the platform back to its initial position the free end then falls 5.18 feet and" 

the load on it is 362 pounds, and the work done is equal to 1,875 foot-pounds. The 

total work, therefore, done in a single lift is 7,131 foot-pounds, and the useful 

work given to the water is 4,245 foot-pounds, so that the mechanical efficiency, 

when just working, is 59.6 per cent; at the normal rate of working it is much 

lower, probably not more than 50 per cent.

FIG. 57. Construction of Boyce water lift.

The conclusion reached by the engineer, Mr. A. Chatterton, who 

made the tests, was that '' the most efficient way of utilizing animal 

power is to make the animal raise himself against the action of gravity, and then, in some way, convert the potential energy stored in the 

animal's body into work."

AN AMERICAN DEVICE.

An American water lift, devised by Mr. A. Boyee, of Augusta, 

Oklahoma, was exhibited at Garden, Kansas, in 1896. Figs. 57, 58, 

and PL I, B (p. 74), show its construction and general mode of operation. Its very considerable merit lies in the readiness with which it 

may be constructed on the farm, and in its cheapness. The general 

plan of the device may be described as follows:

The running gear of an ordinary farm wagon, with the two wheels 

of one side removed, has its axles fixed radially to a circular track, 

the diameter of which is made to exceed slightly the total height of 

the water lift. The axles are bolted to beams which extend to the 

center of the circular track, where they are pivoted to a low post.
88 TESTS OP PUMPS AND WATER LIFTS. [NO. 14.

Horses hitched in the usual manner draw this two-wheeled device 

around the circle. A vertical post, rigidly braced on the wagon frame

and extending to a height somewhat above the backs of the 

horses, carries at its upper end a 

vertical pin, to which ropes are attached by means of a loose link 

and extended to a lifting device 

at the well. As the wagon travels 

around the track, the framework, 

as a whole, acts as a crank, the 

throw of which is equal to the 

height of lift of the water. The 

ropes extend horizontally from the 

top of the traveling post to the 

well framework, so that the horses 

pass beneath them. By simple 

multiplication of ropes more than 

one well may be drawn upon. 

Where, however, there is but a 

single well, a counterbalance upon 

the wagon must be used to prevent 

overturning. In the well is a 

bucket, hung at either side on gimbals, attached a little above its 

center of gravity when full, so as 

barely to insure stability. In the 

bottom of the bucket two large 

clack valves admit of the ingress 

of water. The supporting ropes, 

one on each side, pass through 

pulley blocks over head and thence 

horizontally to the crank link on 

the wagon post. These pulley 

blocks hang from the ends of a 

short beam, pivoted at its center so 

that it may always maintain a position normal to the continually 

changing direction of the ropes.

The mechanism for emptying 

the bucket is designed to receive 

its full discharge and at the same 

time to avoid shock. A swinging

FIG. 58. Construction of Boyce water lift. , ,. -, -, , » ,

trough is suspended at four points,

by rods, from the framework overhead. As the bucket reaches the 

summit of its rise it encounters a cross rod, on a tilting lever, as shown
HOOD.] AN AMERICAN DEVICE. 89

in fig. 58. The tilting of this lever draws forward the trough supports by means of an adjustable connecting rod and swings one end 

of the trough under the tilting bucket. The bucket is prevented from 

tilting too far by a bail on the tilting lever.

This device is simple and very direct in operation. If applied to a 

single well, it has the fault of being single-acting, and horses can not 

be worked to their full capacity without overstrain. The resistances 

for one revolution would be, practically, as shown in the diagram, 

fig. 39 (p. 66). To render this work more nearly uniform three or 

more wells should be drawn upon at the same time. Three wells 

placed at the points of an equilateral triangle, with the sweep operating at its center, could be served nearly as easily as one. The 

mechanism is so direct acting that an efficiency of at least 80 per cent 

could be expected, as with the similar device of Mr. Stoney.

In the case of a single well the full weight of the loaded bucket will 

come upon the horses at that moment when their direction of pull 

falls in line with the rope. If a team of two horses can pull 400 

pounds for a short distance, the weight of bucket and water may be 

80 per cent of that amount. A 50-gallon oil barrel makes a good 

bucket. The barrel will weigh, when wet, about 70 pounds, and 

when three-fifths full will have the weight given above.

If three wells be used the resistance will be so uniform that an 

average pull of 200 pounds, for two horses working in a circle, may 

be taken as a basis for determining the proper dimensions for the 

buckets. If the machine has frictional resistances of but 20 per cent 

the water in each bucket may weigh 160 pounds, and in one revolution 

480 pounds, or about 57 gallons, can be discharged. The number of 

revolutions per minute will depend upon the size of the circle described

57 by the horses, and will be =- if the diameter of the circle is made Li

equal to the height of the lift. The gallons discharged per minute

QQ-( O £* "1

will be =r- , and the acre-feet, per day of ten hours, -^-. A mechan- LJ Li

ical advantage may be secured by attaching the crank post to the 

sweep at a point nearer to the center than the point to which the 

horses are attached. It will thus describe a smaller circle. In consequence larger buckets may be used.

This device is adaptable to any number of horses and to any number 

of wells. Mr. Boyce makes the statement that, "using two buckets 

drawing from one well, one bucket ascending as the other descends, 

I can raise 200 gallons per minute from a well 27 feet deep, with a 

small team of [two] horses." While this is heavy work for two horses, 

and probably could not be maintained continuously for ten hours, it 

shows what could be done on occasion. No accurate tests of efficiency 

have been made, so far as I know.

A device of this kind is well worth the attention of beginners in 

irrigation who wish to avoid a large initial outlay for machinery.

INDEX.

Animal power, water-lifting by... -... 78-89 

Barr, William, cited on clear valve area. 27 

Boyce water lift, description of.......... 87-89

figures showing form of. ...... 74, 87, 88

Bucket lifts, forms and efficiency of----- 74-78

Bucket pump, essential features of _.-... 13 

figure of................................ 12

Butterfly valve, form of..__... , 33 

Clack valves, features of 19

figure of..._-__.-_--..__--. ------ 31

table showing resistance to flow

through.._.____.._... 31

Cook pump, discharge curve of... 63

efficiency of.-........................... 60-64

vertical section of cylinder of........ 61

Counterbalance for windmill pump, form

of.... .............................. 67

Discharge of pumps, amount of .......... 38-39

Disk valve, figure of...................... 30,43

form of ___..._--._.._.-._.-- __.-_- 32 

Double-acting pump, features of......... 11

Dynamometer diagrams showing pumprod stresses.............. 16,17,30,33,27,39

Efficiency of pumps, data concerning...- 39-65 

Elbows in suction pipe, objections to use

of..................................... 18

Frizell pump, discharge curves of........ 44,48

efficiency of............................ 43-54

valve areaof--_ ._.'.__.._.... 27

vertical section of.--.-.._........... 48

Gould triples power pump, diagram

showing discharge of........_._. 70

efficiency of...-........................ 71-73

flguresof............................... 69,70

Indian water lifts, description of...-___ 80-87 

Lift pump and suction pump, distinguishing features of.-.-..-__......---.. 13

Link-belt water elevator, view of __.... 74

Mhote for lifting water, description of... 85-86

Mark pump, diagram of cylinder of... _ 30

discharge curves of... ._... 31,32,35

efficiency of ........................... 30-42

Newell, P. H., letter of transmittal by... 9 

Piston and rod, features of...... ..... 23-25

Pistonpump, figured -..._ ..-.. 12 

Piston speed, limits of................. 15,25-28

Piston speed and pull, diagram showing

relations between. .__.-.-.. 36 

Piston speed in irrigation cylinders, table

showing. . .-.. ......... 28

Plunger pump, figured..-.------. .--- 13

"Pounding," cause of. ... ....-._- 15

diagrams showiug. .....--- . 16,17,30

Pump (bucket,) features of .....----.. 13

Page. 

Pump (bucket), figured ... .... .... 12

(double-acting),features of.-...-_-. 11 

(double-acting), figured......__..... 13

(piston), figured. . .......---.. 13

(plunger), figured.__......---_... 13

(reciprocating), features of...----.... 11

(single-acting), features of............ 11

Pump-rod stresses, dynamometer diagrams showing........-- 16,17,20,33,37,39

Pumps, efficiency of..._..._.__.__ 29-65 

Reciprocating pumps, diagram showing

efficiency of.......................... '39

features of.-.-...-.__.__..._... 11 

Resistance to rotation in crank-driven

pumps, data concerning ............ 65-73

Reuleaus, cited on relation between

pump discharge and piston speed.. 38 

Rotation in crank-driven pumps, resistance to.........._.__.._...... 65-73

Screen in suction pipe, objections to use

of............. ..................... 17

Seaman bucket lift, tests of ...__...... 74-78

See-saw water lift, description of ........ 86-87

Single-acting pump, features of __. - _. 11

Speed of piston, limits of _...--...--..-.-- 15,35

Stoney water lift, description of ...-. 84-85

figures showing form of ........... 81,83,83

Suction, conditions for. .-....--.-.--- 14

Suction pump and lift pump, distinguishing features of . ....... 13

Valve (butterfly), form of-. ....-- .. 32

(clack), features of......... . 19

(clack), figured----.....--.... .--... 31

(clack), table showing resistance to 

flow through. ...... ....... 31

(disk),form of --.--- - ----- 33

(disk), figured-..--.--- .- - -, 30,43 

Valves, forms and functions of. __,....- 19-33

Van Voorhis pump, discharge curves of 55 

efficiency of.-...... .-.---.- ----- 54-60

valve areaof....................... 37-38

vertical section of............ . 54

Water lifts, forms and features of. .... 73-89

use of animal power on... ..... 78-89

Weber, W. O., cited on efficiency of reciprocating pumps.......... .... 29

Weisbach, cited on loss of water from

high piston speed ... ....... 28-39

cited on piston and valve speed.. 28 

Weisbach and Hermann, cited on effi. 

ciency of various forms of water 

lifts ............ - - - - 73-74

Windmill pump, method of counterbalancing . . -- - 67

91