Power transmission

A hydraulic control system comprising a hydraulic actuator having opposed openings adapted to alternately function as inlets and outlets for moving the element of the actuator in opposite directions and a variable displacement pump with loading sensing control for supplying fluid to said actuator. A pair of meter-in valves are provided to which the fluid from the pump is supplied and a pilot controller alternately supplies fluid at pilot pressure to a meter-in valve for controlling the displacement of movement of the meter-in valve and the direction and velocity of the actuator. Alternately pilot pressure from the pilot controller is applied simultaneously to both of the meter-in valves in conjunction with the venting of one of two load drop check valves to provide a regenerative mode. A line extends from the meter-in valve to its respective opening of the actuator and a meter-out valve is associated with each line of the actuator for controlling the flow out of the actuator when that line to the actuator does not have pressure fluid from the pump applied thereto. Each meter-out valve is pilot operated by the pilot pressure from the controller. In a modified form, utilizing a single actuator, the hydraulic control system includes a single meter-in valve associated with one opening of the actuator.

This invention relates to power transmission and particularly to hydraulic 
circuits for actuators such as are found in earth moving equipment 
including excavators and cranes. 
BACKGROUND AND SUMMARY OF THE INVENTION 
This invention relates to hydraulic systems for controlling a plurality of 
actuators such as hydraulic cylinders which are found, for example, in 
earth moving equipment such as excavators and cranes. In such a system, it 
is conventional to provide a pilot operated control valve for each 
actuator which is controlled by a manually operated controller through a 
pilot hydraulic circuit. The control valve functions to supply hydraulic 
fluid to the actuator to control the speed and direction of operation of 
the actuator. In addition, the control valve for each actuator controls 
the flow of hydraulic fluid out of the actuator. It is also common to 
provide counterbalance valves or fixed restrictions to control overrunning 
loads. 
In the copending U.S. application of Robert H. Breeden et al, Ser. No. 
024,058, filed Mar. 26, 1979, now U.S. Pat. No. 4,201,052, having a common 
assignee with the present application, there is disclosed and claimed a 
hydraulic system for accurately controlling the position and speed of 
operation of the actuators; which system is simple and easy to make and 
maintain; which system is unaffected by change of load pressure of various 
portions of the system or other actuators served by the same source; which 
system may not use flow from the pressure source in the case of 
overrunning loads on the actuators; wherein the control valves may be 
mounted adjacent the actuator for preventing loss of control of the load 
in case of malfunction in the hydraulic lines to the actuator; wherein the 
valves which control flow out of the actuator function to control the 
velocity in the case of energy generating loads, wherein the valve that 
controls flow into the actuator controls the velocity in the case of 
energy absorbing loads; wherein the valve system for each actuator can be 
mounted on its respective actuator and incorporates means for preventing 
uncontrolled lowering of the load in case of pressure failure due to 
breaking of the lines to the valve system; wherein the timing of operation 
of the valve controlling flow into the actuator and out of the actuator 
can be designed to accommodate the specific nature of the particular load. 
It is an object of the present invention to provide a dual acting hydraulic 
control system having dual meter-in valves for controlling dual-acting 
hydraulic actuators. 
Another object of the present invention is to provide a dual acting 
hydraulic control system having dual meter-in valves for providing control 
of dual-acting hydraulic actuators in a regenerative mode. 
A further object of the present invention is to provide a single acting 
hydraulic control system for controlling single acting hydraulic 
actuators. 
The present invention comprises a hydraulic control system for use with a 
hydraulic actuator, a pilot controller, and a pump. The actuator includes 
a movable element and a pair of openings adapted to function alternately 
as inlets or outlets for moving the element in opposite directions. The 
pilot controller supplies fluid to the system at pilot pressure and the 
pump supplies fluid at pump pressure to the actuator. The control system 
includes a line adapted for connection to each of the openings and a 
meter-out valve associated with each of the lines for controlling fluid 
flow from the actuator. The meter-out valves are each selectively pilot 
operated by pilot pressure from the pilot controller. A meter-in valve is 
positioned in each of the lines for controlling fluid flow from the pump 
to the actuator with each of the meter-in valves being selectively 
operable by pilot pressure from the pilot controller. 
In one embodiment of the present invention the actuator includes a head end 
and a rod end associated with each of the pair of openings and each of the 
lines adapted to be connected therewith having a load drop check valve 
associated with the head end and rod end, respectively. A means for 
venting the load drop check valve associated with the rod end and means 
for simultaneously opening the meter-in valves provide control of fluid 
flow to the actuator in a regenerative mode. 
Another embodiment of the invention comprises a hydraulic control system 
for use with a hydraulic actuator having a movable element and an opening 
adapted to function alternately as an outlet and an inlet for moving the 
element. A pilot controller controls a supply of fluid at pilot pressure 
and a pump supplies fluid at pump pressure to the actuator. The hydraulic 
control system comprising a single line adapted for connection to the 
opening of the actuator and a single meter-out valve associated with the 
line for controlling flow from the opening. The meter-out valve being 
pilot operated by pilot pressure from the pilot controller. A single 
meter-in valve is positioned in the line for controlling fluid flow from 
the pump to the actuator with the meter-in valve being operable by pilot 
pressure from the pilot controller. 
These and other objects, advantages, and details of the invention may be 
had from the following drawings and description taken together with the 
accompanying claims.

DETAILED DESCRIPTION 
Referring to FIG. 1 and FIG. 1a, the hydraulic system embodying the 
invention comprises an actuator 20, herein shown as a hydraulic cylinder 
having a movable rod 21, a head end 21a, a rod end 21b, and a pair of 
openings A and B associated with head end 21a and rod end 21b, 
respectively. Rod 21 is moved in opposite directions by hydraulic fluid 
supplied from a variable displacement pump system 22, FIG. 1a, which has 
load sensing control in accordance with conventional construction. The 
hydraulic system further includes a manually operated controller 23 that 
directs a pilot pressure to a valve system 24 for controlling the 
direction of movement of the actuator, as presently described. Fluid from 
the pump 22 is directed to the pump pressure lines P and passages 26 and 
26a to a pair of meter-in valves 27a, 27b, that function to direct and 
control the flow of hydraulic fluid to one or the other end 21a, 21b, of 
the actuator 20. Each meter-in valve 27a, 27b is pilot pressure controlled 
by controller 23 movable to direct pilot pressure through lines C1 or C2 
to passages 28 or 29 and passages 30a or 31a to one or the other of the 
meter-in valves. Depending upon which of the meter-in valves is actuated, 
hydraulic fluid passes through passages, 32, 33 to one or the other end of 
the actuator 20. 
The hydraulic system further includes a meter-out valve 34, 35 associated 
with each end of the actuator in passages 32, 33 for controlling the flow 
of fluid from the end of the actuator to which hydraulic fluid is not 
flowing from the pump to a tank passage 36, as presently described. 
The hydraulic system further includes spring loaded poppet valves 37, 38 in 
the lines 32, 33 and spring loaded anti-cavitation valves 39, 40 which are 
adapted to open the lines 32, 33 to the tank passage 36. In addition, 
spring loaded poppet valves 41,42 are associated with each meter-out 
valves 34, 35 as presently described. A bleed line 47 having an orifice 49 
extends from passage 36 to meter-out valves 34, 35 and to the pilot 
control lines 28, 29 through check valves 77. 
The system also includes a back pressure valve 44, FIG. 1a, associated with 
the return or tank line. Back pressure valve 44 functions to minimize 
cavitation when an over-running or a lowering load tends to drive the 
actuator down. A charge pump relief valve 45 is provided to take excess 
flow above the inlet requirements of the pump 22 and apply it to the back 
pressure valve 44 to augment the fluid available to the actuator. 
Referring to FIG. 2, each meter-in valve 27a, 27b comprises a bore 50 in 
which a spool 51 is positioned and in the absence of pilot pressure 
maintained in a neutral position by springs 52. The spool 51 normally 
blocks the flow from the pressure passages 26a, 26b to the passages 32, 
33. When pilot pressure is applied to either passages 30a or 31a, the 
meter-in spool 51 of the respective meter-in valve is moved in the 
direction of the pressure until a force balance exists among the pilot 
pressure, the spring load and the flow forces. The direction of movement 
determines which of the passages 32, 33 is provided with fluid under 
pressure from passage 26a or 26b. 
Referring to FIG. 4, each meter-out valve 34, 35 is of identical 
construction and, for purposes of clarity, only valve 34 is described. The 
meter-out valve 34 includes a bore 60 in which a poppet 61 is positioned. 
The poppet 61 includes one or more passages 64 extending from an area 63 
within the poppet to the tank passage 36. A stem 65 normally closes the 
connection between the chamber 63 and passages 64 under the action of a 
spring 66. The pressure in area or chamber 63 equalizes with the pressure 
in line 32 and the resulting force unbalance keeps poppet 61 seated. The 
valve further includes a piston 67 surrounding the stem 65 yieldingly 
urged by a spring 68 to the left as viewed in FIG. 4. The pilot line 28 
from the controller 23 extends through a passage 69 to a chamber 70 that 
acts against the piston 67. When pilot pressure is applied to passage 28, 
the piston 67 is moved to the left as viewed in FIG. 4 moving the stem 65 
to the left permitting chamber 63 to be vented to tank passage 36 via 
passage 64. The resulting force unbalance causes poppet 61 to move to the 
left connecting line 32 to passage 36. 
It can thus be seen that the same pilot pressure which functions to 
determine the direction of opening of a meter-in valve also functions to 
determine and control the opening of the appropriate meter-out valve so 
that the fluid in the actuator can return to the tank line. 
Referring to FIG. 3, each of the meter-out valves has associated therewith 
a spring loaded pilot spool 71 which functions when the load pressure in 
passage 32 exceeds a predetermined value to open a flow path from the load 
through a control orifice 62 to the tank passage 36 through an 
intermediate passage 73. This bleed flow reduces the pressure and closing 
force on the left end of the poppet valve 61 permitting the valve 61 to 
move to the left and allowing flow from passage 32 to the return or tank 
line 36. In order to prevent overshoot when the pressure rises rapidly, an 
orifice 72 and associated chamber 72a are provided so that there is a 
delay in the pressure build-up to the left of poppet valve 71. As a 
result, poppet valves 71 and 61 will open sooner and thereby control the 
rate of pressure rise and minimize overshoot. 
Referring to FIGS. 1 and 1a, in the case of an energy absorbing load, when 
the controller 23 is moved to operate the actuator 20 in a predetermined 
direction, pilot pressure applied through line 28 and passages, 31a moves 
the spool of the respective meter-in valve to the right causing hydraulic 
fluid under pressure to flow through passage 33 opening poppet valve 38 
and continuing to opening B associated with rod end 21b of actuator 20. 
The same pilot pressure is applied to the meter-out valve 34 permitting 
the flow of fluid out of opening A associated with head end 21a of the 
actuator 20 to the return or tank passage 36. 
Referring to FIGS. 1 and 1a, when the controller 23 is moved to operate the 
actuator, for example, for an overrunning or lowering a load, the 
controller 23 is moved to C1 so that pilot pressure is applied to passage 
31a and to passage 28. The meter-out valve 34 opens before the respective 
meter-in valve 27a under the influence of pilot pressure. The load on the 
actuator forces hydraulic fluid through the opening A of the actuator past 
the meter-out valve 34 to the return or tank passage 36. At the same time, 
the poppet valve 40 is opened permitting return of some of the fluid to 
the other end of the actuator through opening B thereby avoiding 
cavitation. Thus, the fluid is supplied to the other end of the actuator 
without opening the meter-in valve 27b and without utilizing fluid from 
the pump. 
To achieve a float position, the controller 23 is bypassed and pilot 
pressure is applied to both pilot pressure lines 28, 29. This is achieved, 
for example, by the use of solenoid operated valves which bypass 
controller 23 when energized and apply the fluid from pilot pump directly 
to lines 28, 29 causing both meter-out valves 34 and 35 to open and 
thereby permit both ends of the actuator to be connected to tank pressure. 
In this situation, the meter-out valves function in a manner that the stem 
of each is fully shifted permitting fluid to flow back and forth between 
opposed ends of the cylinder. 
In the modified form of the hydraulic system shown in FIG. 1b taken in 
conjunction with FIG. 1, a remote controlled circuit is provided wherein 
the system may be operated in the normal fashion as described above with 
reference to FIGS. 1 and 1a or in a regenerative mode as presently 
described. In the regenerative mode fluid from the rod end 21b of actuator 
20 is permitted to flow to the head end 21a via line 33, vented load drop 
check valve 38a, presently described, meter-in valve 27b, and to pump 
pressure lines P wherein the fluid flow from rod end 21b joins fluid flow 
from the pump to head end 21a. 
In the modified circuit three remote controlled two-position valves, such 
as solenoid operated valves, are provided to control the flow of pilot 
pressure to meter-in valves 27a, 27b and meter-out valves 34, 35, shown in 
FIG. 1. In addition a fourth remote controlled two-position valve is 
provided to vent a modified load drop check valve 38a, FIG. 1b., as 
described below. 
A first of the two-position valves 75a, is connected to a remote hydraulic 
pilot controller through lines C1, C2 which provide fluid flow at pilot 
pressure thereto. First valve 75a is connected to a second valve 75b and a 
third valve 75c of the two-position valves through control pressure lines 
C1 and C2, respectively. Second and third valves 75b, 75c are in turn 
connected through lines C1 and C2 to passages 28, 30, 30a and 29, 31, 31a, 
respectively, of the hydraulic control system of FIG. 1. The fourth 
two-position or on-off valve 75d is connected between check valve 38a and 
tank. 
The modified load check valve 38a, FIG. 1b, includes an orifice 76 and a 
passage 78 connected to on-off valve 75d. The orifice 76 provides a means 
of limiting the amount of flow being vented to the tank. 
In normal operation on-off valve 75d, is closed in the spring offset 
position and valves 75a, 75b, and 75c are also in the spring offset 
position permitting control pressure flow in the manner heretofore 
described with regard to the arrangement of FIGS. 1 and 1a. 
When a regenerative function is desired valves 75a, 75b, 75c and 75d are 
energized. On-off valve 75d vents load drop check valve 38a to tank, 
control pressure to both meter-out valves 34, 35, FIG. 1, is shut-off, and 
at the same time control pressure applied simultaneously opens both 
meter-in valves 27a and 27b. The opening of check valve 38a and meter-in 
valves 27a and 27b with meter-out valve 34 and 35 being closed permit 
fluid flow in the regenerative mode as described above. Thus, this circuit 
arrangement permits operation in the normal mode or in the regenerative 
mode, the latter being used where a more rapid movement of the actuator 
element 21 is desired. 
Where the pressure in the return from end A of the actuator is excessive, 
the pilot spool 71 functions to permit the poppet valve 61 to open and 
thereby compensate for the increased pressure as well as permit additional 
flow to the actuator 20 through opening of the poppet valve 40 extending 
to the passage which extends to the other end of the actuator. 
By varying the spring forces and the areas on the meter-in valves 27a, 27b 
and the meter-out valves 34, 35, the timing between these valves can be 
controlled. Thus, for example, if the timing is adjusted so that the 
meter-out valve leads the meter-in valve, the respective meter-in valve 
will control flow and speed in the case where the actuator is being 
driven. In such an arrangement with an overhauling load, the 
load-generated pressure will result in the meter-out valve controlling 
flow and speed. In such a situation, the anti-cavitation check valves 39, 
40 will permit fluid to flow to the supply side of the actuator so that no 
pump flow is needed to fill the actuator in an overhauling load mode or 
condition. 
With this knowledge of independent control of the meter-out and meter-in 
valves, varying metering arrangements can be made to accommodate the type 
of loading situation encountered by the particular actuator. Thus, where 
there are primarily energy absorbing or driving loads, the spring and 
areas of the meter-out valve can be controlled so that the meter-out valve 
opens quickly before the meter-in valve opens. In the case of primarily 
overrunning loads, the meter-out valve can be caused to open gradually but 
much sooner than the meter-in valve so that the meter-out valve is the 
primary control. 
As shown in FIGS. 1 and 1a, a check valve 77 is provided in a branch 78 of 
each pilot line 28, 29 adjacent each meter-out valve 34, 35. The valves 77 
allow fluid to bleed from the high tank pressure in passage 36, which 
fluid is relatively warm, and to circulate through pilot lines 28, 29 back 
to the controller 23 and the fluid reservoir when no pilot pressure is 
applied to the pilot lines 28, 29. When pilot pressure is applied to a 
pilot line, the respective check valve 77 closes isolating the pilot 
pressure from the tank pressure. 
As further shown in FIGS. 1 and 1a, provision is made for sensing the 
maximum load pressure in one of a series of valve systems 24 controlling a 
plurality of actuators and applying that higher pressure to the load 
sensitive variable displacement pump 22. Each valve system 24 includes a 
line 79 extending to a shuttle valve 80 that receives load pressure from 
an adjacent actuator through line 81. Shuttle valve 80 senses which of the 
two pressures is greater and shifts to apply the same to a shuttle valve 
82 through line 83. A line 84 extends from passage 32 to shuttle valve 82. 
Shuttle valve 82 senses which of the pressures is greater and shifts to 
apply the higher pressure to pump 22. Thus, each valve system in 
succession incorporates shuttle valves 80, 82 which compare the load 
pressure therein with the load pressure of an adjacent valve system and 
transmit the higher pressure to the adjacent valve system in succession 
and finally apply the highest load pressure to pump 22. 
The provision of the load sensing system and the two load drop check valves 
37, 38 provide for venting of the meter-in valves in neutral so that no 
orifices are required in the load sensing lines which would result in a 
horsepower loss during operation which would permit flow from the load 
during build up of pressure in the sensing lines. In addition, there will 
be no cylinder drift if other actuators are in operation. Further, the 
load drop check valves 37, 38 eliminate the need for close tolerances 
between the spool 51 and the bore 50. 
In practice, the various components of valve assembly 24 are preferably 
made as a part of a valve which is mounted directly on actuator 20 so that 
the need for long flow lines from the valve assembly to the actuator is 
obviated. 
Although the system has been described in connection with a variable 
displacement pump with load sensing control, the system can also be 
utilized with a fixed displacement pump having a load sensing variable 
relief valve. In such an arrangement, the pressure from line 81a is 
applied to the variable relief valve associated with the fixed 
displacement pump rather than the variable displacement pump with load 
sensing control. It will be apparent to those skilled in the art that many 
changes may be made to the described invention without departing from the 
spirit and scope thereof and of the appended claims. 
An example of such changes is in the form of the invention shown in FIGS. 5 
and 5a. The hydraulic control system of FIG. 1 is modified for use with a 
single acting hydraulic actuator 20a shown as a hydraulic cylinder having 
a rod 21a. Rod 21a is moved only in one direction by hydraulic fluid 
supplied from pump system 22, FIG. 5a, and may be moved in the opposite 
direction mechanically or by gravity. 
In the modified single acting hydraulic system, as shown, only the elements 
of the right half of the double acting system shown in FIG. 1 are utilized 
to control actuator 20a. 
In the case of an energy absorbing load, when controller 23, FIG. 5a, is 
moved to operate the actuator 20a, the controller 23 is moved to C1 so 
that the pilot pressure is applied through passage 28 and passage 31a. The 
applied pilot pressure moves the spool of the meter-in valve 27b to the 
right, as viewed in FIG. 5, causing hydraulic fluid under pressure to flow 
through passage 33 opening poppet valve 38 and continuing to inlet B of 
actuator 20a. 
When the controller 23 is moved to operate the actuator for a lowering 
load, the controller is moved to C2 so that pilot pressure is applied to 
passage 29 and the meter-out valve 35 opens. The load on the actuator 
forces hydraulic fluid through opening B past the meter-out valve 35 to 
tank passage 36. 
When large actuators are required, for example, in large fork lift trucks 
and off-highway equipment having a large double acting cylinder and high 
area ratios exist, an appropriately sized large volume single acting 
system may be used to control the head end of the cylinder and an 
appropriately sized small volume single acting system may be used to 
control the rod end of the cylinder. 
When, in the interest of safety, an absolute load lock is required and no 
piping is allowed between the head end and the rod end of a cylinder 
subject to overrunning loads in both directions, a pair of single acting 
systems may be placed at each end of the cylinder.