proveme paratus.
Year: 1896

page_text: Date of Application (in United Kingdom), 17th June, 1896
Complete Specification Left, 17th Mar., 1897-Accepted, 1st May, 1897
PROVISIONAL SPECIFICATION.
proveme
paratus.
We LA SOCIÉTÉ MILLOCHAU, BERNAUD ET CIE., of Nanterre (Seine)-France,
Mineral Oil Merchants do hereby declare the nature of this invention to be as
follows:-
This invention relates to apparatus for automatically and continuously lubricating
engines and machinery, shafting, etc. The apparatus is adapted to work at any
distance, is of simple construction, contains no part liable to get out of gear break
or wear and needs no supervision; it can be placed in any position and may work
while the machine to be lubricated is not in motion. The same size of apparatus
may be used for lubricating engines of any kind or power and it may work
continuously for a period only limited by the capacity of the oil or grease
reservoir from which it is supplied, while the rate of flow of the lubricating
material through the ducts is capable of infinite variation. The regularity with
which the minimum of lubricating material is uninterruptedly supplied to the parts
enables a considerable economy to be obtained as compared with the means
ordinarily employed and avoids accidents by dispensing with the services of
attendants.
The invention may be carried into effect in various ways to suit the nature of
the case and an example of the apparatus is represented in the accompanying
drawings in which Figure 1 is a part sectional elevation and Figure 2 a plan partly
in section of the lubricating apparatus.
The apparatus comprises two distinct parts, viz. (1) the oil or grease pump a
with its suction valve box b and delivery valve boxes c; (2) the motor cylinder d
with its distribution valve gear. Both of these parts may be mounted upon the
same frame.
The oil or grease pump cylinder a may have either a double acting piston or a
plunger e as shewn. The valves are contained in ordinary valve boxes and are each
provided with a stem or with guide wings and may be either cylindro-conical or
ogival headed at one or at both ends, as shewn at f Figure 1, for the purpose of
facilitating the passage of the oil or grease. The working cylinder d has a double
acting piston h (Figure 2) whose rod may extend in both directions through
stuffing boxes i the part k of the piston rod being connected to the pump piston e
by a screw connection for example, as represented in Figure 1. The working
piston may be operated either by means of a liquid under pressure by compressed
gas or by steam pressure. On the backward stroke of the pump piston the oil or
grease is drawn into the pump cylinder through the inlet valve 6 and on the
forward stroke it is delivered through the valves c and pipes g to the points to be
lubricated. The forward stroke should be exceedingly slow so as to obtain the

page_text: greatest possible economy of lubricating material, and will vary according to the
size, nature, and number of the parts to be lubricated. It will be in all cases very
slow as compared with that of the piston of a steam engine. However slow its
motion may be it is necessary that the action of the actuating fluid be reversed
precisely at the moment when the piston arrives at the end of its stroke. This
necessitates the use of special distribution gear such as represented in the drawing
in which the actuating fluid is admitted by pipe 7 and is distributed to the front or
rear end of the cylinder by a four-way cock m. When the fluid is admitted to the
front end of the cylinder the other end is in communication with the exhaust pipe n
and by turning the cock ninety degrees the reverse effect takes place, the operating
fluid passing to the rear end of the cylinder and its front end being placed in com-
munication with the exhaust. For the purpose of rotating it ninety degrees at each
end of the stroke of the working piston, a small crank or a toothed segment o for
example is fixed to the plug of the cock as shewn in Figure 1 and is coupled by a
connecting rod or geared by a rack q, as represented in Figure 1, with a sleeve p
which is free to slide in guides rr and is prevented from turning by a feathers sliding
in a guide t, the guides rr being slotted to give passage to rack q and feather s when
placing the sleeve p in position. The sleeve p is provided at mid-length with an
internal division u centrally apertured for the passage of a rod v carrying spiral springs
which bear against opposite sides of the division u. The springs may be alternately
compressed by means of collars a y on rod v, the extent to which each of the
springs may be compressed being greater than the common stroke of the pistons.
During the return stroke of the pump piston the arm 1 fixed to piston rod k carries
the rod attached thereto back with it and causes collar to compress the adjacent
spring against the partition u, the effect of which would be to slide the sheath p
longitudinally were it not held stationary by a bolt 2 (Figure 2) pressed by a
spring 4 into engagement with a notch in the sheath. The spring continues to be
compressed throughout the entire stroke of the pistons however slow it may be
until on arriving at the end of the backward stroke the apex of the inclined faces
of a cam 3 carried by collar and which moves in a slot in the sheath p forces
back the bolt 2 and so releases the sheath which is thereupon caused to slide
backwards and rotate the distribution cock m through ninety degrees. On the
forward stroke the same movements take place in inverse direction and at the end
of the stroke the sheath is forced forward by the other spiral spring and the bolt 2
again falls into engagement with the sheath. 5 and 6 are collars fixed on the
sheath p and acting as stops to limit the movement of the latter by abutting
against the bearings r r. The adjustment of the distribution valve gear and
the setting of the collars a y in position may be effected by turning a knob 7
screwed on the end of rod v.
In lubricating the moving parts of a machine the pressure at the delivery of the
pump cylinder should be relatively weak as before mentioned, however great may
be the pressure of the fluid employed for actuating the lubricator and this is
ensured by means of a throttle valve z having a truncated conical plug whose mean
diameter is greater than that of the cylindrical bore 8 of the cock casing and
which is hollowed symmetrically at opposite sides as shewn in Figure 1 so that by
suitably adjusting it, only the smallest quantity of oil or grease may be allowed to
pass, thus producing in the flow pipes the exact pressure required which may be
indicated on a gauge fixed at 9. The part 10 (Figure 2) of the plug has a mark
parallel to its axis which when the plug is turned comes successively opposite to
divisions marked upon the face 11 thus enabling the plug to be returned to the
exact position previously occupied. The gauge serves not only to indicate the
pressure at the delivery but also as a means of ascertaining the working of
the lubricator. For lubricating the slide valves and cylinders of a steam engine,
the boiler steam may be used for actuating the lubricator, the relative diameters
of the working pump pistons being such that there will always be an excess of
pressure per unit of surface upon the pump piston which is more than sufficient and
which is reduced to the minimum by means of the throttle regulator z.

page_text: The invention may be employed for machinery generally including hydraulic
engines, compressed air engines, electrical machines, cylinders of steam haminers,
rolling mills, etc. etc. and more particularly for large marine and stationary engines.
all the movable parts of which may be lubricated by means of flexible piping, as
well as to locomotives.
Dated this 17th dex of Lune 1806
We, LA SOCIÉTÉ MILLOCHAU, BERNAUD ET CIE. of Nanterre (Seine)
France, Mineral Oil Merchants, do hereby declare the nature of this invention
and in what manner the same is to be performed to be particularly described aud
ascertained in and by the following statement:-
This invention relates to apparatus for automatically and continuously lubricating
engines and machinery, shafting, etc. The apparatus is adapted to work at any
distance from the parts to be lubricated, is of simple construction, can be fixed at
small expense, contains no part liable to get out of gear, break, or wear, and needs
no supervision; it can be placed in any position and may operate while the machine
to be lubricated is not in motion. The same size of apparatus may be used for
lubricating engines of any kind or power and it may work continuously for a period
only limited by the capacity of the oil or grease reservoir from which it is supplied,
while the rate of flow of the lubricating material through the ducts is capable of
infinite variation. The regularity with which the minimum of lubricating material
is uninterruptedly supplied to the parts enables a considerable economy to be
obtained as compared with the meaus ordinarily employed and avoids accidents by
dispensing with the services of attendants.
The invention may be carried into effect in various ways to suit the nature of
the case and an example of the apparatus is represented in the drawings
accompanying our Provisional Specification in which Figure 1 is a part sectional
elevation and Figure 2 a plan partly in section of the lubricating apparatus.
The apparatus comprises two distinct parts, viz. :-(1) the oil or grease pump a
with its suction valve box 6 and delivery valve boxes c; (2) the motor cylinder d
with its distribution valve gear. Both of these parts may be mounted upon the
same frame.
The oil or grease pump cylinder a may have either a double acting piston or a
plungere as shewn. The valves are contained in ordinary valve boxes and are each
provided with a stem or with guide wings and may be either cylindro-conical or
ogival headed at one or at both ends, as shewn at f Figure 1, for the purpose of
facilitating the passage of the oil or grease.
When the pump piston is drawn inwards by the working piston, a vacuum
is created in the pump cylinder a, the delivery valve or valves close and the
admission valve opens to admit oil or grease into the cylinder a, and when the pump
cylinder is moved outwards by the working piston the motion of the valves is
reversed and the oil or grease is expelled through the pipes g to the parts to be
lubricated.
The working cylinder d has a double acting piston h (Figure 2) whose rod may
extend in both directions through stuffing boxes i the part of the piston rod being
connected to the pump piston e by a screw couuection for example, as represented

page_text: in Figure 1. The working piston may be operated either by means of a liquid
under pressure by compressed gas or by steam pressure. On the backward stroke
of the pump piston the oil or grease is drawn into the pamp cylinder through the
inlet valve and on the forward stroke it is delivered through the valve cand
pipes g to the points to be lubricated. The forward stroke should be exceedingly
slow so as to obtain the greatest possible economy of lubricating material and will
vary according to the size nature and number of the parts to be lubricated. It will
in all cases be very slow as compared with that of the piston of a steam engine.
However slow its motion may be it is necessary that the action of the actuating
fluid be reversed precisely at the moment when the piston arrives at the end of its
stroke. This necessitates the use of special distribution gear such as represented
in the drawing in which the actuating fluid is admitted by pipe 7 and is distributed
to the front or rear end of the cylinder by a four-way cock m. When the fluid is
admitted to the front end of the cylinder the other end is in communication with
the exhaust pipe x and by turning the cock 90° the reverse effect takes place, the
operating fluid. passing to the rear end of the cylinder and its front end being
placed in communication with the exhaust. For the purpose of rotating it 90° at
each eml of the stroke of the working piston, a small crank or a toothed segment o
for example is fixed to the plug of the cock, as shewn in Figure 1, and is coupled
by a connecting rod or geared by a rack g, as represented in Figure 1, with
a sleeve which is free to slide in guides rand is prevented from turning by a
feather a sliding in a guide t, the guides r r being slotted to give passage to rack y
and feathers when placing the sleeve p in position. The sleeve p is provided at
mid-length with an internal division a centrally apertured for the passage of a rod v
carrying spiral springs which bear against opposite sides of the division . The
springs may be alternately compressed by means of collars a y on rod v, the extent
to which each of the springs may be compressed being greater than the common
stroke of the pistons. During the return stroke of the pump piston the arm 1 fixed
to piston rod k carries the rod v attached thereto back with it and causes collar a to
-compress the adjacent spring against the partition x, the effect of which would be
to slide the sheath p longitudinally were it not held stationary by a bolt 2 (Figure 2)
pressed by a spring 4 into engagement with a notch in the sheath. The spring
continues to be compressed throughout the entire stroke of the pistons however
slow it may be until on arriving at the end of the hackward stroke the apex of the
inclined faces of a cam 3 carried by collar and which moves in a slot in the
sheath p forces back the bolt 2 and so releases the sheath which is thereupon caused
to slide backwards and rotate the distribution cock m through 90°. On the forward
stroke the same movements take place in inverse direction the collar y compressing
the other spiral spring until at the end of the stroke the cam carried by the collar y
releases the locking bolt at that end, whereupon the sheath is forced forward by
the other spiral spring and the bolt 2 again falls into engagement with the sheath.
5 and 6 are collars fixed on the sheath p and acting as stops to limit the movement
of the latter by abutting against the bearings r r. The adjustment of the
distribution valve gear and the setting of collars a y in position may be effected by
turning a knob 7 screwed on the end of rod v.
In lubricating the moving parts of a machine the pressure at the delivery of the
pump cylinder should be relatively weak as before mentioned, however great may
be the pressure of the fluid employed for actuating the lubricator and this is
ensured by means of a throttle valve having a truncated conical plug whose mean
diameter is greater than that of the cylindrical bore 8 of the cock casing and which
is hollowed symmetrically at opposite sides, as shewn in Figure 1, so that by
suitably adjusting it, only the smallest quantity of oil or grease may be allowed to
pass, thus producing in the flow pipes the exact pressure required which may be
indicated on a gauge fixed at 9. The part 10 (Figure 2) of the plug has a mark
parallel to its axis which when the plug is turned comes successively opposite to
divisions marked upon the face 11 thus enabling the plug to be returned to the
exact position previously occupied. The gauge serves not only to indicate the

page_text: pressure at the delivery but also as a means of ascertaining the working of
the lubricator.
For lubricating the slide valves and cylinders of a steam engine, the boiler steam
may be used for actuating the lubricator, the relative diameters of the working
pump pistons being such that there will always be an excess of pressure per unit of
surface upon the pump piston which is more than sufficient and which is reduced to
the minimum by means of the throttle regulator z.
The invention may be employed for machinery generally including hydraulic
engines, compressed air engines, electrical machines, cylinders of steam hammers,
rolling mills, etc. etc. and more particularly for large marine and stationary engines,
all the movable parts of which may be lubricated by means of flexible piping, as
well as locomotives.
Having now particularly described and ascertained the nature of the said inven-
tion and in what manner the same is to be performed we declare that what we
claim is :-
1. In a lubricating apparatus the herein described means of actuating the
distribution valve of the working cylinder in such manner that the sudden reversal
of the valve is exactly timed with regard to the motion of the piston however slow,
the said means consisting essentially of a spring-actuated reciprocating part geared
or coupled with the distribution cock, mechanism for locking said reciprocating
part in either of its extreme positions, springs adapted to be compressed by the
motion of the working piston, and means such as described for effecting the release
of the locking mechanism and permitting the action of the springs at the proper
moment substantially as specified.
2. The herein described system of distribution valve gear comprising a sheath p
having an internal division u and fitted to slide in guides, locking bolts engaging
with the sheath, a rod r rigidly connected to the piston rod k and passing through
spiral springs (one at either side of division u within the sheath) and provided with
collars y for compressing the springs carrying cams for releasing the locking
bolts, collars 5, 6, on sheath p to limit its motion, and rack q in gear with the
distribution cock, all combined and arranged substantially as herein before described
and illustrated in the drawings and for the purpose specified.
ינות
101 1 x 1007
A. M. & WM. CLARK,
53, Chancery Lane, London, Chartered Patent Agents.