JPH01364A - power transmission device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a reversible fluid pressure motor pump device, particularly to a
Regarding a power transmission device in which reverse fluid pressure motor pump devices are connected via a torque conversion device, each motor pump device is linked to a fluid pressure system that serves as a high pressure pump and a fluid tank, and the Pressure power is delivered from - of the two-flow pressure system by one of the two-motor pump devices and converted into mechanical power by the other motor-pump device,
Next, the other motor pump device converts the power into hydraulic power and supplies it to the rest of the two-fluid system.

BACKGROUND OF THE INVENTION Modern aircraft have traditionally been equipped with multiple separate hydraulic systems for performing various control functions of the aircraft.

For example, in aircraft, hydraulic systems are used to move control surfaces such as yellow slats or flaps to selectively control or lower landing gear. In order to improve cruising safety of airplanes, it is necessary to use a hydraulic system that can smoothly perform control functions. To accommodate multiple hydraulic systems and to minimize the bulk of the hydraulic systems, power transmission units are typically disposed between the systems. This power transmission device obtains hydraulic power from one of the hydraulic systems, and can also satisfy the condition that the supply capacity C3 is larger than the supply capacity C3 of the high-pressure pump of the hydraulic system that is sending out the power. Furthermore, the movement of fluid between the hydraulic systems connected to each other via the power transmission unit is suppressed, so that even if one hydraulic system fails, pressure fluid can be delivered by the other hydraulic system. It is composed of

(Problems to be Solved by the Invention) However, conventional power transmission devices have several drawbacks. In particular, the power transmission device operates frequently and has poor durability.In other words, when the flow pressure difference between the two connected two-flow pressure systems is relatively small, the power transmission device described above can handle the flow pressure difference. This causes the power transmission device to operate more frequently, leading to faster wear and tear on the power transmission device and shortening its service life. Further, the power transmission device described in L has a problem that if one of the power transmission devices fails, fluid leaks between the two fluid pressure systems, causing both fluid pressure systems to malfunction.

In addition, it transfers power bi-directionally between hydraulic systems.”
- The conventional power transmission units mentioned above often employ relatively complicated electronic/fluid control systems (1-1 dynamic gradient transmission, which is more prone to failure due to its complexity). The device also required a power supply, which posed a safety problem.

Therefore, it is an object of the present invention to provide a power transmission device that does not operate until the fluid pressure difference between two fluid pressure systems connected to each other via a power transmission unit reaches a predetermined level. Another object of the present invention is to provide a power transmission device that, once activated, maintains the flow IE Z:: between two fluid pressure systems below a predetermined fluid pressure differential necessary to initiate operation of the power transmission unit.

Another object of the present invention is to provide a power transmission device in which leakage of fluid between two hydraulic systems connected via a power transmission unit is reliably prevented.

Still another object of the present invention is to provide a power transmission device that utilizes fluid from one of two hydraulic systems connected through a power transmission unit in the other system under complete hydraulic control.

(Means for Solving the Problems) According to the present invention, there is provided a power transmission device including a first reversible motor pump device of variable displacement type and a second reversible motor pump device of fixed displacement Iit type. The valley motor pump device includes a high-pressure and low-pressure inlet/output I-J section and an input/output shaft, and is configured such that mechanical power is input to and output from the motor pump device through the shaft. [And the 11th
A second motor pump device connects each input and output shaft:
The direction of rotation is determined by each motor-pump device operating as a pump or a motor. Each of the H motor pump units is associated with a separate fluid supply having a respective high pressure pump to supply relatively high pressure fluid from each high pressure pump to the high pressure inlet/output section I-1 of the motor pump unit and to the low pressure of the motor pump unit. Entrance/exit [
, provided to supply a relatively low pressure fluid to one part,
Furthermore, a fluid control device delays the start of operation of a power transmission unit for transmitting power in one direction between two fluid pressure systems in accordance with the high pressures of two fluid supply sources until the fluid pressure difference between the systems reaches a predetermined level. Once the power transmission between the two fluid pressure systems is started, the fluid control device converts the fluid pressure difference between the two fluid pressure systems into a predetermined fluid pressure difference necessary to start operation of the power transmission device. is configured to maintain it at a lower level, thereby meeting the objective described above.

(Function) The power transmission device of the present invention configured as described above does not operate until the fluid pressure ratio of the two-flow pressure system of the power transmission unit reaches a predetermined level, so the drive frequency is reduced and power supply is not required. It is possible to achieve fluid control without

(Example) FIG. 1 shows a pair of r7. A hydraulic system 10 is shown having a symmetrical configuration in which the symmetrical components on the right in FIG. This is what is shown.

Referring now to the configuration on the left side of FIG. 1, tank 12 contains reservoir fluid +4, which is conveyed from tank 12 via conduit 18 to injection pump 16. Infusion pump 16 delivers compressed fluid to an intermediate pressure level via conduit 20 to main high pressure pump 22; The load 24 may be any type of motor or actuator selectively driven by high pressure fluid under control of an L-motor or automatic device. Fluid pressure 1. During operation of the IQ, the compressed fluid absorption or consumption characteristics of the load 24 are determined by the actuator introducing fluid from the conduit 26;
It varies greatly depending on the number and size of the equipment of the motor "50M. Relatively low pressure fluid is discharged from the load 24 via conduit z8, and the conduit 2811 body is connected to the conduit 20 between the infusion pump 16 and the main high-pressure pump 22. Conduit 28 is in communication with tank 12 through safety valve 30, which limits the pressure within conduit 20.28 to approximately 150% of the design discharge pressure of infusion pump 16.

The right-hand symmetrical part and the left-hand symmetrical part of the hydraulic system 10 are connected via a power transmission unit 32 .

The power transmission unit 32 has a first high pressure input/output a*+<34
and a first low-pressure inlet/outlet section 36.
4.36 are in communication with conduit 26.20 via conduit 38.40, respectively. Similarly, the power transmission unit 32 has an ’ is communicated with.

During operation of the hydraulic system lO, all infusion pumps 16.1
6. The high pressure pump 22.22' is activated to supply high pressure fluid ( ) to the load 24.24' through the conduit 26.26' at the same design pressure. On the other hand, if the f1 load 24.24' exceeds the pumping capacity of the main high pressure pump 22.22', the flow pressure in conduit 26.26' will fall below the design pressure of the hydraulic system. At this time, the power transmission unit 32 is actuated to transfer the fluid pressure from the other symmetrical part of the fluid pressure system, so to speak.
For example, if the injection pump 16 or the high-pressure pump 22 goes out of order, one of the symmetrical parts becomes unusable and is fully operational to the load despite a reduction in speed or power consumption. Fluid power is transferred from the other symmetrical part via the power transmission unit 32 to continue operation.

Referring to FIG. 2, the power transmission unit 32 includes a first motor pump assembly 50 of the variable displacement I11 type using an axially tilted piston swashplate.

A plurality of openings 54 extending in the axial direction are formed in the rotary body 52 of the motor pump device 50, and an identical plunger device 56 that reciprocates in the axial direction is inserted into each opening 1-1 portion 54. A shoe member 58 is integrally sunk into the plunger device 56, and the shoe member 58 itself is slidably engaged with a rotary swash plate 60 whose angle varies from I to IJ.

Further, the rotating body portion 52 is pivotally supported on bearings 62 and 64 via a shaft portion 66 of the motor pump device 50.

The power transmission unit 32 further includes a fixed discharge T-shaped second motor pump device 68 arranged at a certain angle with respect to the axial direction, and the second motor pump device 68 is rotatable. A plurality of openings 72 extending in the axial direction are formed in the body portion 70, and the same plunger member 74 that reciprocates in the axial direction is inserted into each opening L] portion 72, respectively. The body 70 is pivotally supported by a pair of bearing members 76 and 78 spaced apart in the axial direction, and is rotatably driven by a drive shaft member 80 having a single-gouge joint J'4 for constant speed transmission at each end. be done. That is, since the chest 70 and the socket member 82 are drivingly connected via the universal joint, these components are all connected so that they can rotate together. The socket member 82 is driveably connected to the shaft portion 66 of the first motor pump device 50 and is provided with a number of radially outwardly extending drive arms 84 equal to the number of openings 72 . Each plunger member 74 is drivably connected to the - of the drive arm 84 via a connecting rod 86, and at this time, the spherical end of each connecting rod 86 is connected to the - of the drive arm 84 and the - of the plunger member 74, respectively. Ru. Further, a radially outer and axially extending surface 88 of the socket member 82 abuts a pair of sealing members 90, 92 to form a sealing surface. "And the second motor pump device 6
8 contains a casing for receiving and supporting the components of the hydraulic system, only a part of which is shown in FIG. This casing reliably prevents fluid movement between the first motor pump device 50 and the second motor pump device 68. be done.

It will be seen from FIG. 2 that when high pressure fluid is supplied to conduit 38, 46, each motor-pump device 50, 68 begins to operate as a motor, driving the motor-pump devices in unison. On the other hand, the motor-pump device 50.68 is connected to perform a reverse operation and has a large static friction force, so that within a predetermined range of the flow IF in the conduit 38.46, the motor-pump device 50. A static torque balance of .68 is taken. On the other hand, when the fluid pressure difference between the conduits 38, 46 exceeds the predetermined range indicated by -1-, one of the motor pump devices 50, 68 operates as a motor, that is, in motor mode;
The other motor operating as a pump, ie operating in pump mode, drives the pump device. In this case, the motor pump device in motor mode introduces high pressure fluid in conduit 38.46 and delivers fluid through conduit 40.4FI. while the motor pump device operating in bomb mode introduces low pressure fluid via conduit 40.48;
Fluid is delivered via conduit 46.38. Here, the static torque f balance between each motor pump device 50.68 is the rotary swash plate 60.
It will be determined depending on the turning position of.

Also, the speed and torque versus pressure characteristics of the power transmission unit 32 during operation are determined according to this pivot position.

For controlling the pivoting position of the swashplate 60, an elongated control arm 94 is attached to the swashplate 60 and has an annular portion 96,98 formed at its outer end.

Within the annulus 96.98 is a control plunger 100, +02
are inserted with their opposite ends precisely spaced apart, and the opposite ends of each control plunger 100.102 form the actuating part of the control device 104, +06. The configuration of each controller 104, 106 is substantially the same except for the difference in effective fluid pressure area. Each control device 104.1
06 is an annular movable spring seat member 1 that connects to the rear wall of the control device.
Compression springs 108 and +10 are arranged between 12 and 114.
is included. The spring seat members +12.114 are respectively connected to the annulus 1!6.118 ``1'' of the control device, the radially inwardly extending annulus and the control plunger 100, +02 ``1''.
'4 can be engaged with collar members 120, +22 extending radially outward. Thus, when the control arm 94 is in the body II- position, each spring seat member +12, +14 abuts the annulus +16, +18 and the collar member 120, 122, respectively. Further, in the rest position of the control arm 94, the rotating swash plate 6o is mounted at a certain angle with respect to a plane perpendicular to the shaft portion 66. In this case, in the illustrated rest position, the first motor-pump device 50 causes the shaft part 66 to
The rotation of can give a predetermined characteristic representing a predetermined effective fluid displacement=tb and static and dynamic torque, convection pressure, and operating speed.

Next, referring also to FIG. 3, the power transmission unit 32 includes a control valve device 124. Control valve device +24
A stepped opening 128 is formed inside the housing 126 . A pair of sleeve members 130 and 132 are inserted into the opening 128, and the sleeve members 130 and 132 are inserted into the opening 128.
．． A plunger member 134 and a spool valve member 136 are inserted into the inner body of 132, respectively. In FIG. 1, at the left end of the control valve device 124, there is a chamber 13g in which the sleeve member 130, the plunger member 134, and the housing 126 together receive the compression spring 140 and the spring seat member +42.
is divided. Further, at the left end of the control valve device 124, the spring seat member +42 abuts against the plunger member 134. Via the opening L1 section 144, the chamber 138 is communicated with the high pressure conduit 146 and further with the conduit 46 of the second motor pump device 68. Similarly, at the right end of the control valve device +24,
housing! 26 and the cap member 148 together define a chamber +50, and a compression spring +52 is disposed within the chamber 150 between the cap member 148 and the spring seat member 154. The spring seat member 154 contacts the right end of the spool valve member 136 and the spool valve member 13
When 6- is displaced, the other end comes into contact with plunger member +34. The housing +26 is provided with 11 open Li portions 156, +58 which communicate separately with the interior of each of the first and second motor pump devices 50, 68 via conduits +60, +62. An opening +64 formed in the housing 126 communicates with the high pressure conduit 38 of the first motor pump device 50 via a conduit +66.

Inside the housing 126, however, sleeve members +30, 132 cooperate to define an annular chamber 168 which communicates with openings 164, +66. The end of the sleeve member 130 is provided with a radially extending notch 170 that abuts the sleeve member +32. Through notch 170, fluid is transferred from conduit 166 to chamber 172 defined between plunger member 134 and spool valve member 136.
will be communicated to. Housing +26 also has a passageway 174 in communication with annular chamber 168 and chamber 150. The end of the spool valve member 136 thus receives fluid from the high pressure conduit 38 of the first motor pump arrangement 50 via a conduit +66.

Similarly, sleeve member 132 cooperates with housing +26 to define an annular chamber +76 that communicates with opening 158 and conduit 162. The opening +28 also includes an annular chamber 180 surrounding the sleeve member 130 and an annular chamber 1.
76 is provided.

Annular chamber 180 has openings 156, +58 and conduits! 6
It is matched with a similar annular chamber +80 in communication with 0.

1) According to the above-described configuration, the spool valve member 136 is slidably inserted in the sleeve member +32 in a sealed state. The spool valve member 136 of this section has a pair of lands +84 and +86 spaced apart in the axial direction, and the central part of the land parts 184 and 186 is the spool valve member!
radially extending slot-shaped channel formed in 36 +8
8, +90. The groove portion extending in the axial direction of the spool valve member 136 is the land portion +8
4.186 and extends between 1 and 1 in sleeve member 132.
A gap extending in one radial direction is formed.

The flow path 194 is connected to the annular chamber + through a sleeve member 132 that extends radially outwardly from a groove in the spool valve member +36.
It connects to 76. The slot-shaped channels 188.190 are narrowly formed in the circumferential direction.
The axial end of 190 is positively and sealingly mated with the axial end of land +84.186. Slot-shaped channel 1
88.190 radially outwardly of the housing 12
6 and the spool valve member +36 cooperate to open the annular chamber 2.
00.202 is divided. Annular chamber 200 is in communication with controller 106 via opening 204 and conduit 206 . Similarly, the annular chamber 202 is open.
g and a conduit 21G to the control device 106.

The configuration of the control device 104 , 106 allows the conduit 206 to open to the rest of the control device 104 and to a chamber 212 defined by the control plunger 100 . Conduit 210 also opens into a chamber 214 defined by the rest of control device 106 and control plunger 102 .

1 [Also, the sleeve member 130 is the plunger member +3
4 defines an annular chamber 216 which itself communicates with the annular chamber 180 via a radially extending channel 2+8. Similarly, plunger member +34 cooperates with sleeve member 130 to open annular chamber 2.
20, and the annular chamber 220 communicates with the annular chamber +82 via the annular chamber 220 of the upper radially extending flow path. A plurality of grooves 224 are provided between both ends of the plunger member 134, spaced apart along the longitudinal direction thereof, extending in the 16 radial direction, and continuous in the circumferential direction,
Groove 224 cooperates with sleeve member 130 to define a labyrinth seal.

Next, the operation of the fluid pressure system 10 and the power transmission unit 32 having the above-mentioned configuration will be explained. When all pumps 16, 16' and high pressure pumps 22,22' are in operation, conduits 26,26' are introduced with high pressure fluid at a substantially equal pressure according to the design of the hydraulic system 10. Ru. As the fluid absorption of the load 24.24' changes as the load is switched on and off, the flow rate and fluid pressure within the conduit 26,26' changes. Fluid is returned from negative A: 24.24' via conduit 28.28' to conduit 20.20' between infusion pump 16, +6' and high pressure pump 22.22'. The safety valve 30.30' reduces the flow pressure in the conduit 20.20' to approximately 150° below the design output pressure of the injection pump 16.16'.
%. Therefore, the fluid pressure in conduit 40.48 communicating with power transmission unit 32 is
, +6' and the safety pressure of the safety valve 30.30".

Although the pressure in conduit 26.26' may rise up to substantially the design pressure level of hydraulic system 10, motor pump device 50.68 is capable of controlling fluid pressure changes in conduit 26.26' within a predetermined range. However it doesn't work. This is because the motor-pump devices 50.68 are connected via shaft parts 66.80 which are arranged to drive in opposite directions. Even if the rotational torque generated by one of the motor-pump devices 50, 68 is greater than the counter-rotational torque generated by the other motor-pump device, the torque difference will be greater than the static friction force, i.e. the level required to start the power transmission unit. Never. On the other hand, the motor pump device 50
．． Even if 68 is in a static state, the control device ! 04.106 is effectively activated and the motor pump device 50.68 starts operating at step 4B.

For example, when the load 24 exceeds the pumping capacity of the high pressure pump 22, the fluid pressure in the conduit 26 will be lower than the fluid pressure in the conduit 26', but the fluid pressure difference will prevent the motor pump device 50, 68 from starting operation. . The relatively low fluid pressure in conduit 26 is communicated via conduit 38 with first high pressure inlet/outlet Dffi<34, which in turn is communicated via conduit 166 to notch 17G, and into flow path 174. is in communication with chamber 150 via conduit 26', while relatively high pressure fluid from conduit 26' is transferred via conduit 46 to second high pressure inlet/outlet section 42, and then via conduit 146 to chamber 183 at the left end of control valve arrangement 124. Therefore, -f Yani/Ha1
Due to the pressure difference between 38 and 172, the plunger member +34
Effectively, the spool valve member 136 is moved slightly to the right (in FIG. 2) against the compression spring 52. By moving the spool valve member 136 in the right direction, the land portion 18
6 is moved to the right with respect to the slot-shaped channel +90 extending in the radial direction of 11, and the chamber 172
High pressure fluid is delivered to conduit 210 via section 208 which is also in communication with pipe 90 . Control device +06 via conduit 210
The high pressure fluid in communication with the chamber 214 acts operatively within the chamber 214 to move the control plunger 102 to the right.

Similarly, the land portion 184 of the spool valve i material 136 is moved slightly to the right with respect to the slotted channel 188, so that the chamber 212 of the control device +04
lTI section 204, annular chamber 200, slotted channel 188, channel 194, annular chamber 176, opening 15
8, communicates with the caning of the first motor pump device 50 via a flow path defined by a conduit 162. Therefore,
The fluid within chamber 212 of controller 104 is brought to a low pressure by infusion pump 16 and safety valve 30 . When the force acting on the control plunger +02 becomes greater than the compression spring 108, the control arm 94
It is moved to the right by 1t.

To further explain the first motor pump device 50 in detail, when the control arm 94 is moved to the right as described above, the rotary swash plate 60 moves from its body resting position 1 to the first motor pump device. It is moved to a position where the discharge iIt of 50 is decreased. As a result, the resistive torque produced by the first motor-pump arrangement 50 is reduced and the drive torque produced by the second motor-pump arrangement 68 remains at its previous level. Therefore, the power transmission unit 32 is HF-prepared to start operating the second motor pump device 68, which operates as a motor for driving the motor pump device 50 in the pump mode. conduit 2
When the pressure difference between 6.26 and 6.26 reaches a predetermined level and becomes larger than the starting torque of the first and second motor pump devices 50.68, the second motor pump device 68 turns off the first motor pump device 68. The device 50 is started to be driven and the fluid is transferred to the conduit 4.
0 to conduit 38 and serves to maintain the pressure level within conduit 26 at approximately the design pressure level. When the motor-pumping device 50.68 of the power transmission unit 32 is started to operate, the j! J tube 26.26
The pressure difference between the two is maintained to be less than the pressure difference required to start operation of the power transmission unit. Therefore, during operation of the power transmission unit, the control valve device 124 adjusts the position of the control arm 94 so that the first motor pump device 5
A displacement of 0 is ranged between a reduced displacement position and a displacement corresponding to the rest position of the rotating swash plate 60 and control arm 94.

On the other hand, if the load 24' has a pump capacity n1 of the pump 22' and the fluid pressure in the conduit 26' is lower than the fluid pressure in the conduit 26, high pressure will be applied in the chamber 172 of the control valve arrangement 124 rather than in the chamber 138. Therefore, the plunger member +34 is moved slightly to the left in the opposite direction to the compression spring 140, and the spool valve member 13G is moved by the compression spring 152 acting through the spring seat member 154, following the movement of the plunger member +34. This leftward movement of spool valve member 136 establishes communication between chamber 150 and opening 204 and via conduit 206 to controller +04.

This leftward movement of spool valve member 136 also causes conduit 210 to open from controller 106 and axially flow between the groove of spool valve member 136 and sleeve member 132 via section 208 and slotted passageway 190. tX11 extending to
! 12 and fluid is communicated to conduit +6 via flow path 194.
2 and further to the casing of the first motor pump device 50 . As a result, the control arm 94
It is moved to the left in the opposite direction to the compression spring 110 of the control device 106 in response to the 10,000 4f weight and the spring force. control arm 9
4 is thus moved, - the rotating swash plate 60 is swiveled and the effective displacement fIt and the static torque of the first motor pump device 50 are increased so that the first motor pump device 50
operates as a motor.

When the effective discharge IIt of the first motor pump device 5G increases as described above, the first motor pump device 50
The effective torque input to and output from the motor increases. - The resisting torque produced by the motor-pump device 68 of the force tube 2 is reduced by the effective low flow pressure in the conduits 46 and 26'. conduit 26
．． When the pressure difference between 26° and 26° reaches a predetermined level greater than the starting torque determined according to the static friction force within the power transmission unit 32, the power transmission unit 32 starts operating and the first motor pump device 50 operates as a motor. Then, the second motor pump device 68 in pump mode is driven. The second motor pump device 68 therefore introduces fluid through conduit 48 and through conduit 46 and through conduit 26' to load 24'.
supply the necessary compressed fluid. During operation of the power transmission unit, the control valve arrangement 124 is connected to the control arm 94 and the rotating swash plate 6.
0 position can be adjusted from its maximum displacement position to the rest position described above.

1- From the above, when the power transmission unit operates and one of the motor pump devices 5G and 68 drives the other,
It will be appreciated that the control arm 94 and swashplate 60 are adjusted between a rest position and one of maximum and minimum displacement positions depending on the direction of operation of the power transmission unit. That is, when the power transmission unit is activated and power is transmitted from the left symmetrical portion to the right symmetrical portion of the hydraulic system of FIG. 1, the swash plate 60 is positioned between the maximum displacement position and the rest position.

On the other hand, when the power transmission unit 32 is activated and power is transmitted from the right-hand symmetrical part to the left-hand symmetrical part of the hydraulic system of FIG. and the body IL position.

At this time, if the load condition of one of the loads 24.24' is reduced and the high-pressure pump 22.22' can satisfy the design pressure condition of the hydraulic system 10, the control arm 94
And the rotating swash plate 60 is adjusted to the rest position. As a result, the operation of the power transmission unit 32 is such that the torque difference between the two motor pump devices is smaller than the sum of the effective kinetic friction torque within the power transmission unit 32 and the resistance torque of the power transmission unit 32 operating in the pump mode. When this body 11 state is reached, the operation of the motor pump device 5G, 68 of the power transmission unit 322 is terminated. 94 and rotating swashplate 60 are moved away from the rest position so that the fluid pressure level in conduit 26.26' changes dynamically in response to changes in the effective fluid pressure required by load 24.24-. The motor pump device of the power transmission unit 32 is again prepared for operation.

It will be understood by those skilled in the art that the present invention is not limited to the illustrated embodiments, but encompasses design modifications that fall within the spirit of the claims.

For example, although the illustrated embodiment has been described above as a configuration in which fluid pressure systems with equal design operating pressures are interconnected, fluid pressure systems with unequal design operating pressures may be interconnected, and if necessary, the components may be The dimensions and pressure-responsive area can also be varied.

(Effects of the Invention) -1- According to the power transmission device of the present invention configured as described above, the driving frequency is greatly reduced, so the durability is significantly improved and the power supply is reduced. Because there is no such thing, it can achieve unique effects such as improving safety.

[Brief explanation of drawings]

FIG. 1 is a simplified configuration diagram of a power transmission device according to the present invention, FIG. 2 is a sectional view of a main part of the same power transmission device, and FIG. 3 is an enlarged sectional view of the same portion. 10... Fluid pressure system, 12... Tank, 14, Fluid, 16.16 - Injection bomb 2, 18... Conduit, 2
0.20゛... Conduit, 22.22゛... High pressure pump, 24.24'... Load, 26.26... Conduit, 28.28゛... Conduit, 30.30'. ... safety valve, 32 ... power transmission unit, 34 ... entrance/exit section,
36... Entrance/exit part, 38... Conduit, 40... Conduit, 42... Entrance/exit part, 44... Entrance/exit 11 part, 46...
... Conduit, 48 ... Conduit, 50 ... Motor pump device, 52 ... Rotating body, 54 ... Opening, 56 ...
- Plunger device, 58... unit member, 60...
Rotating swash plate, 62. 64... Bearing, 66... Shaft part, 68... Motor pump device, 70... Body part, 72... Opening part, 74... Plunger member, 7
6.78... Bearing member, 80... Drive socket member, 82... Socket member, 84... Drive arm, 86... Connection rond, 88... Surface part, 90.9
2... Sealing member, 94... Control arm, 96.98
... Annular part, +00.102 ... Control plunger,
+04.106...control device, +08.110...
Compression spring, +12.1!4... spring seat member, 116,
+18-... Annular part, 120. 122... Collar member, 124... Control valve device, +26... Housing, +28... Opening part, +30, +32... Sleeve member, 134... ...Plunger member, +36...Spool valve member, 138...Chamber, +40...Compression spring, 142...Spring seat member, 144...Opening part,
146... Conduit, 148... Cap member, +50
...Chamber, 152...Compression spring, 154...
Spring seat member, +56.158...opening, 160,]
62... Conduit, +64... Open L part, +66...
Conduit, 16g... Annular chamber, 170... Notch, 172... Chamber, 174... Channel, 176...
・Annular chamber, 178...flow path, 180, +82・
...Annular chamber, 184,! 86...Land part, +
88, +90... Slot-shaped channel, 194... Channel, 200.202... Annular channel l<, 204...
Opening, 206... Conduit, 208... Opening, 21
0... Conduit, 212.214... Chamber, 216
...Annular chamber<, 21g...Flow path, 220...
- Annular chamber, 222...channel, 224...groove.

Claims (23)

[Claims] (1) A first variable displacement reversible motor pump device having a first high-pressure inlet/outlet section, a first low-pressure inlet/outlet section, and a first rotating shaft section for inputting and outputting mechanical power; a second reversible motor pump device with a fixed displacement having an inlet/outlet portion, a second low pressure inlet/outlet portion, and a second shaft portion for inputting/outputting mechanical power; Input/output high pressure fluid at high pressure inlet/outlet part
A first fluid supply source device that inputs and outputs low-pressure fluid at the low-pressure inlet and outlet portion of the device, and a second fluid supply source device that is communicated with the second motor pump device and inputs and outputs high-pressure fluid at the second high-pressure inlet and outlet portion, and A second fluid supply source device that inputs and outputs low-pressure fluid and the first and second fluid source devices are separated from each other in a sealed state to prevent communication of pressure fluid between the first and second fluid source devices. a hermetic separation device communicating with both the first and second high pressure inlet/outlet portions to prevent rotation of the first shaft of the first motor pump device in response to a fluid pressure difference between the first and second high pressure inlet/outlet portions; a fluid pressure-responsive control device capable of changing the effective discharge amount per unit, and the first and second shafts are
The first motor pump device and the second motor pump device are connected with a reverse torque so as to be able to transmit rotational power between the first motor pump device and the second motor pump device.
and the direction of rotation of the second shaft is determined by driving one of the motor pump devices, one of the motor pump devices being operated as a pump and the other as a motor to exchange fluid between the first and second fluid source devices. A power transmission device that transmits fluid power without causing any damage and maintains a difference between a first and second fluid supply source device at a predetermined level. (2) The first motor pump device includes a movable member that can change the effective displacement amount, and the fluid pressure responsive control device includes a first motor pump device that displaces the movable member to a first position of the effective displacement amount. and the first fluid supply source device and a second fluid source device that is larger than the first fluid source device, reducing the effective discharge amount inversely to the first pressing device. 2. The power transmission device according to claim 1, further comprising a first pressure responsive device for moving the movable member to the second position. (3) The control device includes a second pressing device that displaces the movable member to the first position of the effective discharge amount, and a second fluid source device that supplies the first fluid source device and the second fluid source device. and a second pressure-responsive device that moves the movable member to a third position that increases the effective discharge amount inversely to the second pressing device in response to a fluid pressure difference with the source device. A power transmission device according to claim 2, comprising: (4) The power transmission device according to claim 3, wherein the control device includes a stop device that faces each of the first and second pressing devices at the first position of the movable member. (5) The first and second pressure-responsive devices of the control device include a first housing having an opening therein, and a first variable displacement chamber that is movably inserted into the opening in a sealed state to define a first variable displacement chamber. 5. The power transmission device according to claim 4, wherein the power transmission device includes a first plunger member. (6) The second pressure-responsive device of the control device includes a second housing having an opening therein, and a second housing that is movably inserted in the opening in a sealed state and that is movable in a direction opposite to the first plunger member. a second plunger member that defines a variable displacement chamber, the second plunger member including a second plunger member that cooperates with the movable member to move the movable member to a third position where the effective displacement is increased. 6. The power transmission device according to claim 5, comprising a cooperating portion and a third cooperating portion cooperating with the stop device. (7) The control device is configured to cause one of the first and second variable displacement chambers to communicate with the high pressure fluid of the first fluid source device, and to simultaneously control the first and second variable displacement chambers in response to movement of the valve device in one of the two directions. a valve device communicating with the other of the second variable displacement chamber to receive the low-pressure fluid of the first fluid source device; and first and second pressure responsive valves arranged sealingly separated from each other and facing each other. a pressure-responsive device having a surface, the pressure-responsive device being coupled to the valve device to move the valve device in two directions; a first communication device for moving the pressure responsive member and the valve device in a direction to communicate the second variable displacement chamber with the high pressure fluid;
a second pressure-responsive surface in communication with the high-pressure fluid of the second fluid source device and a second pressure-responsive member and a valve arrangement in communication with the high-pressure fluid in a second of two directions; 2 communication devices and a pressing device for displacing the pressure responsive member and the valve device to a central position in which high pressure fluid is not supplied to either the first or second variable displacement chamber. The power transmission device according to scope item 6. (8) The pressure-responsive member of the control device has a first
, an elongate plunger member forming a second pressure-responsive surface, and the control device includes an elongated plunger member that surrounds the plunger member between its ends in close proximity to the first pressure-responsive surface and communicates with the plunger member. a second annular drain chamber surrounding and communicating with the plunger member spaced from the first annular drain chamber between ends thereof and proximate the second pressure responsive surface; a first flow path device that communicates the first annular drain chamber with the low pressure fluid of the first fluid source device; and a second flow path device that communicates the second annular drain chamber with the low pressure fluid of the second fluid source device. A first pressure-responsive surface, first and second annular drain chambers, and a sealing separation device for sealingly separating the second pressure-responsive surface from other parts. The power transmission device according to item 7. (9) The sealed separation device includes a plunger member that is sealed and slidably inserted into the opening formed in the control device, and the plunger member has a plunger member that extends in a radial direction and is continuous in a circumferential direction. 9. The power transmission device according to claim 8, wherein a plurality of grooves spaced apart in the direction are formed and a labyrinth seal is formed within the opening. (10) A first variable displacement reversible motor pump device having a first high-pressure inlet/outlet section, a first low-pressure inlet/outlet section, and a first rotating shaft section for inputting and outputting mechanical power; a second reversible motor pump device with a fixed displacement having an inlet/outlet portion, a second low pressure inlet/outlet portion, and a second shaft portion for inputting/outputting mechanical power; A first fluid supply source device that inputs and outputs high-pressure fluid at a high-pressure inlet/outlet portion and inputs/outputs low-pressure fluid at a first low-pressure inlet/outlet portion; A second fluid supply source device that inputs and outputs fluid and inputs and outputs low-pressure fluid at a second low-pressure inlet and outlet portion, and a first and second fluid source device that are sealed and separated from each other to supply the first and second fluids. a sealing separation device that prevents the supply of pressurized fluid pressure between the supply source devices; and a sealing separation device that communicates with both the first and second high-pressure inlet/outlet portions, and a first and second high-pressure inlet/outlet portion depending on a fluid pressure difference between the first and second high-pressure inlet/outlet portions. a fluid pressure responsive control device capable of changing the effective discharge amount per rotation of the first shaft of the first motor pump device, the fluid pressure responsive control device including:
control members that move in opposite directions from a rest position to increase or decrease the effective displacement of the first motor-pump device relative to the respective rest displacement; first and second fluid-pressure-responsive plunger members disposed opposite each other to move the control member in opposite directions from the rest position; first and second elastic members arranged to face each other so as not to move beyond the first and second elastic members;
moved from the central position to a rest position with one of the variable displacement cavities in communication with the high pressure fluid of the first fluid source device and the other variable displacement cavity with the low pressure fluid of the first fluid source device. the control member is movable from one to the other in opposite directions;
a spool valve with a closed central portion; a pressure responsive plunger member that is linked to the spool valve and moves the spool valve to form opposing and sealingly separated pressure responsive surfaces; 1. first and second flow path devices communicating with a second fluid supply source device; first and second elastic devices facing each other that press and displace the plunger member to a central position where the spool valve member is located; A power transmission device that includes (11) Claim 10, wherein the first motor pump device is formed as an axial piston rotating swash plate type, and the second motor pump device is formed as an axial piston type inclined with respect to the axial direction. power transmission device. (12) The power transmission device according to claim 11, wherein the control member is a pivot lever pivotably attached to the rotating swash plate of the first motor pump device. (13) providing a variable displacement first reversible motor pump device having a first high-pressure inlet/outlet section, a first low-pressure inlet/outlet section, and a first rotating shaft section for inputting and outputting mechanical power; providing a second reversible motor pump device with a fixed displacement having two high-pressure inlet/outlet sections, a second low-pressure inlet/outlet section, and a second shaft section for inputting and outputting mechanical power;
and a second shaft to the first motor pump device and the second shaft.
a step of connecting the first motor pump device with the first motor pump device with opposite torque so as to be able to transmit rotational power;
communicating with the fluid pressure system of the first high pressure inlet/outlet section to input/output high pressure fluid at a design pressure level and inputting/outputting low pressure fluid at the first low pressure inlet/outlet section; communicating with a fluid pressure system to input/output high pressure fluid at a design pressure level at a second high pressure inlet/outlet and input/output low pressure fluid at a second low pressure inlet/outlet;
and the second motor pump device are hermetically separated from each other and the first
and preventing fluid pressure communication between the second motor pump device and the first motor pump device in communication with both the first and second high pressure inlet/outlet portions.
and providing a fluid pressure responsive control device that selectively changes the effective discharge amount per revolution of the first shaft of the first motor pump device in response to the fluid pressure difference between the second high pressure inlet and outlet portions. A method for driving a power transmission device that bidirectionally transmits power between separate first and second hydraulic systems. (14) When the first and second motor pump devices connected to each other are not in operation, the first fluid pressure system responds to the fluid pressure difference between the second fluid pressure system and the first fluid pressure system, which is larger than the second fluid pressure system.
increasing the effective displacement of the motor-pumping device, and increasing the effective displacement of the first motor-pumping device according to the fluid pressure difference between the first fluid pressure system and a second fluid pressure system that is greater than the first fluid pressure system. 14. A method of power transmission according to claim 13, comprising a step of decreasing. (15) The first motor-pump device operates as a motor or a pump by increasing the driving static torque or decreasing the resisting static torque of the first motor-pump device. The power transmission method described in item 13. (16) Detect one of the first and second fluid pressure systems that is lower than the design fluid pressure, and when the fluid pressure of the first fluid pressure system is low, reduce the resistance static torque of the first motor pump device. 16. The power transmission method according to claim 15, comprising the step of increasing the static drive torque of the first motor pump device when the fluid pressure of the second fluid pressure system is low. (17) Two separate hydraulic systems are connected via a power transmission unit such that hydraulic power can be transmitted bidirectionally between the two systems without fluid transmission between each system, and each system is connected to the first and second hydraulic systems. a first motor-pumping device of variable displacement is torque transmittably coupled to a second motor-pumping device of fixed displacement to provide a rest displacement; Each of the motor pump devices is sealed and separated from and in fluid communication with one of the two hydraulic systems, and a predetermined static starting torque necessary for starting the operation of the first and second motor pump devices to which the power transmission unit is connected. In the power transmission device, the predetermined static starting torque is given by the difference between the driving torque and the resistance torque when the first and second motor pump devices are connected. When the motor-pumping device is in a static state, the effective displacement and resistance torque of the first motor-pumping device are reduced relative to the rest displacement in response to the low pressure of the hydraulic system, and the first motor-pumping device is operated as a pump. a second motor pump device, and in response to low pressure of a fluid pressure system connected to the second motor pump device, the driving torque is increased relative to the rest displacement amount according to the effective displacement of the first motor pump device. A method for driving a power transmission device comprising the steps of: operating a first motor pump device as a pump and driving the first motor pump device. (18) Setting a predetermined fluid pressure difference between the fluid pressure systems necessary for static startup, and selectively changing the effective displacement of the first motor pump device above and below the idle displacement of the connected first and second motor pump devices. 18. The method according to claim 17, comprising the step of starting operation of the motor pump device. (19) During operation of the motor pump devices connected to each other,
controlling the effective displacement of the first motor-pumping device between a rest displacement and a low displacement when the first motor-pumping device is operating as a pump; 19. The method of claim 18, further comprising the step of controlling the effective displacement of the first motor-pump device between a rest displacement and a high displacement when the first motor-pump device is in operation. (20) Two fluid pressure systems that are fluidly separate are connected via a power transmission unit, and each fluid pressure system has a design fluid pressure level that allows mechanical power to be transmitted bidirectionally between the fluid pressure systems. and each hydraulic system has a variable displacement first motor pump device in communication with one of the two hydraulic systems and a fixed displacement second motor pump device in communication with the other of the two hydraulic systems. First,
In a method for driving a power transmission device in which second motor pump devices are connected to each other so as to apply torque in opposite directions, mechanical power is transmitted between the motor pump devices, and fluid is transmitted between two fluid pressure systems, the control device The effective fluid discharge amount of the first motor pump device is selectively changed according to the fluid pressure difference between the two fluid pressure systems by continuously operating the first motor pump device.
a step of operating the motor pump devices as a pump or a motor, a step of maintaining the mutually connected motor pump devices in a static state while the flow pressure difference is smaller than a predetermined value, and a step of starting the operation of the mutually connected motor pump devices. a motor pump starting step of transmitting fluid power to the fluid pressure system whose fluid pressure is lower than each design fluid pressure level by setting the fluid pressure difference between the two fluid pressure systems to a predetermined value; and a motor pump device connected to each other. A method for driving a power transmission device comprising the step of maintaining a fluid pressure difference between a motor pump device at a level lower than a predetermined value by transmitting fluid power through a power transmission unit during operation. (21) A process of applying fluid pressure to the motor pump device corresponding to the ratio of static friction force and static torque convection pressure to a starting torque level necessary for starting the operation of the connected motor pump device, and variable discharge during operation of the motor pump device. setting the effective displacement of the first motor-pumping device of the quantity to a resting value so that a starting torque value is not obtained at a fluid pressure difference less than a predetermined value; 21. The method of claim 20, wherein the motor pump device is kept inactive while the fluid pressure difference is less than a predetermined value. (22) In the motor pump starting step, the effective displacement of the first motor pump device is increased from the rest value according to the fluid pressure difference in the first fluid pressure system which is higher than the second fluid pressure system, and the static drive torque convection pressure is increased. a step of increasing the ratio and operating the second motor as a motor that drives the pump device by the fluid pressure difference to a predetermined value; A patent comprising the steps of: reducing the effective displacement of a motor pump device from a rest value and reducing the ratio of static resistance torque to fluid pressure to cause the pump to operate as a pump driven by a second motor pump device with a fluid pressure difference. A driving method according to claim 21. (23) When the motor-pump device is started to operate, it gives a dynamic torque-to-hydraulic pressure ratio to the static torque-to-hydraulic pressure ratio for the connected motor-pump device, even when the fluid pressure difference between the two fluid pressure systems is low. continuing operation of the pumping device; and returning the effective displacement of the first motor-pumping device from a value increased or decreased during operation of the connected motor-pumping devices with a flow pressure difference less than a predetermined flow pressure difference to a rest value. and maintaining the fluid pressure difference between the two fluid pressure systems at a level lower than a predetermined level.
Driving method described in section.