POWER TRANSFER APPARATUS

Abstract: A power transfer unit coupling two otherwise separate hydraulic systems for bidirectional transfer of hydraulic power therebetween without transfer of fluid between the two systems. The unit comprises power transfer apparatus characterised in that it comprises a first variable displacement fluid pump-­ motor unit (50) having associated high and low pressure fluid ports (34,36) for connection to a first pressure fluid source (14), and a first rotary shaft (66) the first unit (50) being operable to convert energy between pressurised fluid flow and mechanical rotation of the first shaft (66); a second fixed displacement fluid pump-motor unit (68) also having associated high and low pressure fluid ports (42,44) for connection to a second pressure fluid source (14′) and a second rotary shaft (80), the second unit (68) being operable to convert energy between pressurised fluid flow and mechanical rotation of the second shaft (80), the first and second shafts (66,80) being mechanically interconnected for common rotation to transmit power between the first and second units (50,68) without mixture of their respective fluids; and control means (32) for adjusting the displacement of the first unit (50), the control means (32) being responsive to the pressures of the high pressure ports (34,42) of both the first and second units (50,68) and being operable to maintain the pressure differential therebetween below a preselected level whenever the first and second shafts (50,68) are rotating.

Description: The field of the present invention is reversible hydraulic motor-pump units. More particularly, the present invention relates to power transfer units in which two reversible hydraulic motor-pump units are coupled for torque transfer between them. Each one of the motor-pump units is associated with a separate hydraulic system having its own main high-pressure pump and fluid reservoir. By means of the power transfer unit, hydraulic power may be borrowed from one system for conversion into mechanical power by one of the motor-pump units, and then converted by the other motor-pump unit into hydraulic power which is supplied to the other of the two hydraulic systems. It is conventional in modern aircraft to provide a plurality of separate hydraulic systems by which the various control functions of the aircraft may be performed. For example, the hydraulic systems of the aircraft may be used to move and selectively position control surfaces such as the slats or flaps of the wing, and to raise and lower the aircraft landing gear. In order to improve the level of flight safety, the hydraulic systems may be in redundant relationship with respect to performing some control functions. In order to provide such plural and partially redundant hydraulic systems while also minimising the weight required for such systems, it is common to provide hydraulic power transfer units between the systems. These conventional hydraulic power transfer units provide for borrowing of hydraulic power from one system in order to meet a need in a coupled system which is beyond the supply capability of the primary high-pressure pump of that system which is borrowing power. Additionally, it is necessary that the hydraulic power transfer units prevent transfer of fluid between the coupled systems to ensure that a failure of one system does not incapacitate a coupled system. However, it is recognised in the field that conventional hydraulic power transfer units have several shortcomings. Among the shortcomings is a tendency for conventional units to operate too frequently. That is, a relatively low level of hydraulic pressure differential between two coupled hydraulic systems will result in conventional power transfer units operating in order to minimise the pressure differential between the coupled systems. Such overly frequent operation results in increased wear and shortened service life for conventional power transfer units. Another recognised shortcoming of conventional power transfer units is the possibility of failure of one portion of the power transfer unit resulting failure of both of the coupled systems due to fluid leakage between the two systems. Those conventional power transfer units which provide for bi-directional transfer of power between coupled hydraulic systems have in many cases also employed relatively complex electro-hydraulic control systems. Such complexity is undesirable because it provides additional opportunities for failure of the power transfer unit. The necessity of providing electrical power to such units is also a disadvantage. In view of the above, it is a primary object of the present invention to provide a hydraulic power transfer unit which will not operate until a predetermined pressure differential exists between the two hydraulic system which are coupled by the power transfer unit. An additional object of the present invention is to provide a power transfer unit of this kind which once operating will maintain a pressure differential between the coupled hydraulic systems which is lower than the predetermined pressure differential necessary to begin operation of the power transfer unit. Yet another object of the present invention is to provide a power transfer unit in which leakage of fluid between the two hydraulic systems coupled by the power transfer unit is prevented. Still another object of the present invention is to provide a power transfer unit using entirely hydraulic control derived from one of the two hydraulic systems coupled by the power transfer unit. FR-A-2383339 discloses a power transfer unit for transferring power between two separate circuits. In this case, two fixed displacement fluid pumps are employed. According to the present invention, there is provided power transfer apparatus which comprises a first fluid pump-motor unit having associated high and low pressure fluid ports for connection to a first pressure fluid source, and a first rotary shaft, the first unit being operable to convert energy between pressurised fluid flow and mechanical rotation of the first shaft; a second fixed displacement fluid pump-motor unit also having associated high and low pressure fluid ports for connection to a second pressure fluid source and a second rotary shaft, the second unit being operable to convert energy between pressurised fluid flow and mechanical rotation of the second shaft, the first and second shafts being mechanically interconnected for common rotation to transmit power between the first and second units without mixture of their respective fluids; and control means responsive to the pressures of the high pressure ports of both the first and second units and operable to maintain the pressure differential therebetween below a preselected level whenever the first and second shafts are rotating; characterised in that the first unit is a variable displacement unit of the axial piston swashplate type with a variable swashplate member and in operation, the control means adjusts the position of the swashplate member. Preferably, the first motor-pump unit includes a member which is movable and engages the swashplate member to vary selectively the effective pump displacement, the control means including a first resilient means yieldably biasing the movable member to a selected first position of effective displacement, and first pressure responsive means operable to move the movable member to a second position of decreased effective displacement in opposition to the first resilient means in response to a fluid pressure differential of the second pressure fluid source over the first pressure fluid source. Preferably, the control means further includes a second resilient means yieldably biasing the movable member to the selected first position of effective displacement, and second pressure responsive means operable to move the movable member to a third position of increased effective displacement in opposition to the second resilient means in response to a fluid pressure differential of the first pressure fluid source over the second pressure fluid source. The control means may also include a stop respectively opposing each of the first and second resilient means at the selected first position of the movable member. Preferably, each of the responsive means includes a housing defining a bore, and a plunger sealingly and movably received in the respective bore to define a variable-volume chamber; the first plunger having a portion which engages the movable member to move the latter to the second position of decreased effective displacement and a portion which engages the respective stop at the first selected position for the movable member; the second plunger having a portion which engages the movable member to move the latter to the third position of increased effective displacement and a portion which engages the stop at the first selected position for the movable member. Preferably, the control means further includes valve means communicating one of the variable-volume chambers with the higher pressure fluid of the first pressure fluid source while simultaneously communicating the other variable-volume chamber with the lower pressure fluid of the first pressure fluid source, in response to movement of the valve means in a selected one of two directions; pressure responsive means operatively associated with the valve means for moving the latter in each of the two direction, the pressure responsive means having a first pressure responsive face and an oppositely disposed second pressure responsive face sealingly separated from one another; means communicating the first pressure responsive face with the comparatively high pressure fluid of the first pressure fluid source to effect movement of the pressure responsive member and the valve means in one of the two directions to communicate the other variable volume chamber with the comparatively high pressure fluid; means communicating the second pressure responsive face with the relatively higher pressure fluid of the second pressure fluid source to effect movement of the pressure responsive member and the valve means in the other direction to communicate the one variable volume chamber with the comparatively higher pressure fluid; and resilient means yieldably biasing the pressure responsive member and the valve means to a centred position in which neither of the two variable volume chambers communicates with the comparatively higher pressure fluid. Preferably, the pressure responsive means further includes an elongate plunger member which defines at its opposite ends respectively the first and second pressure responsive faces and in which the control means includes a first annular drain chamber circumscribing and communicating with the plunger member between its ends but nearer to the first pressure responsive face, a second annular drain chamber circumscribing and communicating with the plunger member between its ends and spaced from the first drain chamber but nearer to the second pressure responsive face, a first flow path communicating the first drain chamber with the lower pressure fluid of the first pressure fluid source, and a second flow path communicating the second drain chamber with the lower pressure fluid of the second pressure fluid source, and sealing means sealingly separating the first pressure responsive face, the first drain chamber, the second drain chamber, and the second pressure responsive face, each from all of the others. Preferably, the sealing means is constituted by the plunger being slidably received in close sealing relationship within a bore defined by the control means, and by the plunger having a series of radially extending and circumferentially continuous grooves spaced along its length to define a plurality of labyrinth seals within the bore. Preferably, the second motor-pump unit is of bent-axis axial piston type, and movable member comprises a control lever affixed to the swash plate of the first motor-pump unit for angular movement thereof. The invention may be carried into practice in various ways and one embodiment will now be described by way of example with reference to the accompanying drawings in which: Figure 1 is a schematic diagram showing a power transfer unit according to the present invention coupling two otherwise separate hydraulic systems each having a charging pump and primary high-pressure pump drawing fluid from a respective reservoir for supply to a respective load; Figure 2 is a schematic view partially in cross section, of a power transfer unit according to the present invention; and Figure 3 is an enlarged portion of Figure 2. In Figure 1, reference numeral 10 refers to a pair of coupled hydraulic systems in which many of the components may be duplicated in each of the two hydraulic systems. Because of this duplication, a reference numeral which is used to refer to a component of the system illustrated on the left-hand portion of Figure 1 which is duplicated on the right-hand portion of Figure 1 will also be employed on the right-hand portion of the figure but with a prime added. Turning now to the left-hand portion of Figure 1, it will be seen that a reservoir 12 is provided, holding a store of hydraulic fluid 14. The fluid 14 flows from the reservoir 12 to a charging pump 16 via a conduit 18. The charging pump 16 provides the fluid pressurises to an intermediate level via a conduit 20 to a primary or main high-pressure pump 22. The pump 22 provides high-pressure fluid to a load 24 via a conduit 26. The load 24 may comprises any of a variety of motors or actuators which are driven by high-pressure hydraulic fluid selectively under the control of manual or automatic devices. During operation of the system 10, the load 24 has a pressure fluid absorption or consumption characteristic which varies markedly in dependence upon the number and size of the actuators, motors, or other devices which are drawing fluid from the conduit 26 at any one particular time. Relatively lower pressure fluid is exhausted from the load 24 via a conduit 28 which joins the conduit 20 between the charging pump 16 and the high-pressure pump 22. A relief valve 30 couples the conduit 28 to the reservoir 12 so that the pressure in the conduits 20 and 28 is limited to about 150% of the design discharge pressure of charging pump 16. Interconnecting the two hydraulic systems described immediately above is a power transfer unit 32. The power transfer unit 32 includes a first high-pressure inlet/outlet port 34 and a first low-pressure inlet/outlet port 36 which are respectively connected to the conduits 26 and 20 via conduits 38 and 40. Similarly, the power transfer unit 32 includes second high-pressure inlet/outlet port 42 and second low-pressure inlet/outlet port 44 which are respectively connected with the conduits 26′ and 20′ via conduits 46 and 48. During operation of the system 10, all of the pumps 16, 16′, 22 and 22′ are driven such that high-pressure fluid is supplied at equal design pressure levels via the conduits 26,26′ to the respective load 24, 24′. However, in the event that one of the loads 24, 24′ exceeds the pumping capability of its respective main high pressure pump 20 or 22′, the fluid pressure level in the associated conduit 26,26′ will drop below the design pressure range for the hydraulic system. In such an event, the power transfer unit 32 is operative to "borrow" hydraulic power from the other hydraulic system. Alternatively, in the event that one of the hydraulic systems is disabled, for example, because of failure of its charge pump 16 or main high-pressure pump 22, the loads associated with that hydraulic system may still be operated, albeit at a lower level of speed or power consumption by transferring, via the power transfer unit 32, hydraulic power from the system which is still fully functioning. Considering now Figure 2, it will be seen that the power transfer unit 32 includes a first variable-displacement motor-pump unit 50 which is of the axial piston swashplate type. The motor-pump unit 50 includes a rotational barrel 52 defining a plurality of axially extending bores 54 each of which receives an axially reciprocal plunger unit 56. The plungers 56 engage shoe members 58 which are in sliding engagement with a variable angle swashplate member 60. The barrel member 52 is journaled by bearings 62 and 64 which engage shaft portions 66 of the motor pump unit 50. The power transfer unit 32 also includes a second fixed-displacement motor-pump unit 68 of bent axis type. The second motor-pump unit 68 includes a rotatable barrel portion 70 which defines a plurality of axially extending bores 72 reciprocally receiving a corresponding number of axially reciprocal plunger members 74. The barrel member 70 is journaled by a pair of axially spaced bearing members 76 and 78 and is rotationally driven by a drive shaft member 80 having constant velocity universal joints on each end. The universal joints drivingly connect the barrel member 70 and a socket member 82, respectively, to couple these members for rotation in unison. The socket member 82 is drivingly connected with the shaft portion 66 of the motor-pump unit 50, and includes a plurality of radially outwardly extending drive arms 84, matching the bores 72 in number. Each one of the plunger members 74 is drivingly connected to a respective one of the drive arms 84 by a connecting rod 86, each having a spherical termination end which is received in ball and socket relationship at a respective one of the drive arms 84, and with a respective one of the plunger members 74. In order to complete this preliminary description of the power transfer unit 32 it must be noted that a radially outer and axially extending surface 88 of the socket member 82 defines a sealing surface against which a pair of back-to-back fluid seals 90 and 92 are engaged. Furthermore, the power transfer unit 68 includes a casing which is only schematically depicted partially in Figure 2, but which will be understood to receive and support the component parts of the unit. As a consequence, fluid transfer between the first fluid motor-pump 50 and the second fluid motor-pump 68 is positively prevented. It will be understood from Figure 2 that when high-pressure fluid is supplied to the conduits 38 and 46 as described above, each of the fluid motor-pump units 50 and 68 tends to operate as a motor and to drive the other. However, because the fluid motor-pump units 50 and 68 are coupled to oppose one another and have substantial static friction, there will exist within a certain range of fluid pressures within the conduits 38 and 46, a static torque balance between the fluid motor-pump units. However, when the fluid pressure differential between the conduits 38 and 46 exceeds the above-mentioned range, one of the fluid motor-pump units 50 or 68 will begin to operate as a motor and to drive the other motor-pump unit in its pumping mode of operation. Under such conditions, the driving motor-pump unit will receive pressurised fluid at the respective conduit 38 or 46 and discharge spent fluid via the respective conduit 40 or 48. The motor pump unit which is being driven in a pumping mode will receive relatively lower-pressure fluid via the conduit 40 or 48 and will discharge this fluid pressurised via the respective conduit 46 or 38. It will be further recognised that the static torque balance between the fluid motor-pump units 50 and 68 is greatly influenced by the angular position of the swashplate member 60. Also, this angular position greatly influences the operating speed and torque versus pressure characteristic of the power transfer unit 32 in operation. In order to control the angular position of the swashplate member 60, an elongate control arm 94 is attached to it. At its outer end, the control arm 94 defines oppositely disposed concave arcuate surfaces 96 and 98. The arcuate surfaces 96 and 98 are located between the precisely spaced apart opposite ends of two control plungers 100 and 102. Each of the plungers 100 and 102 defines an operative part of respective control assemblies 104 and 106. The two control assemblies 104 and 106 are similar in construction, although they may differ in their effective fluid pressure-responsive area. Each control assembly 104 and 106 includes a respective coil compression spring 108, 110 extending between a rear wall of the control assembly and a respective annular movable spring seat member 112, 114. The spring seat members 112, 114 are each respectively arranged to engage an annular radially inwardly extending flange 116, 118 on the respective control assembly as well as an annular radially outwardly extending collar 120, 122 on the respective plunger 100, 102. Consequently, a rest position is defined for the control arm 94 in which each of the spring seats 112, 114 is in engagement with the respective flange 116 and 118 as well as with its respective collar part 120, 122. In the rest position of the lever 94, the swashplate member 60 defines a selected angle with respect to a perpendicular from the shaft 66. Consequently, the first motor pump unit 50 defines at the rest position of the lever 94 a selected effective fluid displacement per rotation of the shaft 66, and also has a selected characteristic of static and dynamic torques verses fluid pressure and operating speed, respectively. Also included in the power transfer unit 32 is a fluid pressure responsive control valve apparatus 124, shown in more detail in Figure 3. The control valve apparatus 124 includes a housing 126 defining a stepped bore 128 therein. Received within the stepped bore 128 are a pair of sleeve members 130, 132 respectively receiving a plunger member 134, and a spool valve member 136. At the left-hand end of the control valve assembly 124 as illustrated, the sleeve 130 and plunger 134 cooperate with the housing 126 to define a chamber 138 which receives a coil compression spring 140 and a spring seat member 142. At its right-hand end, the member 142 bears against the plunger member 134. A port 144 opens from the chamber 138 and communicates with the high pressure conduit 46 of the second motor-pump unit 68 via a conduit 146. At the right end of the control valve apparatus 124 the housing 126 cooperates with a cap member 148 to define a chamber 150 which receives a respective coil compression spring 152 extending between the cap member 148 and a spring seat member 154. The spring seat 154 bears upon the right-hand end of the spool valve 136 to bias the latter into engagement with the plunger member 134. The housing 126 also includes ports 156 and 158 which respectively communicate separately with the interior or case cavities of the respective first and second motor-pump units 50 and 68 via conduits 160 and 162. A port 164 in the housing 126 communicates with the high pressure conduit 38 of the first fluid motor-pump unit 50 via a respective conduit 166. Within the housing 126 the sleeves 130 and 132 cooperate to define an annular chamber 168 communicating with the port 164 and its conduit 166. The sleeve 130 defines a radially extending notch 170 at its end which abuts the sleeve member 132. The notch 170 communicates pressurised fluid from the conduit 166 to a chamber 172 defined between the ends of the plunger member 134 and the valve member 136. The housing 126 also defines a passage 174 connecting the chambers 168 and 150. Consequently, the spool valve member 136 is exposed at both of its ends to pressure fluid communicated via the conduit 166 from the high-pressure port 38 and of the motor-pump unit 50. Similarly, the sleeve member 132 cooperates with the housing 126 to define an annular chamber 176 which communicated with the port 158 and the conduit 162. The housing 126 also defines a passage 178 connecting the chamber 176 with an annular chamber 180 circumscribing the sleeve member 130. The chamber 180 is matched by a similar annular chamber 182 communicating with the port 156 and the conduit 160. Viewing now the sleeve member 132 and spool valve member 136 in greater detail, it will be seen that the spool valve member 136 is slidably and sealingly received within the sleeve member 132. The spool valve member 136 defines a pair of axially spaced lands 184 and 186 in which when in a centred position, align with axially and radially extending slot-like passages 188 and 190 in the sleeve member 132. An axially extending groove portion 192 extends between the lands 184 and 186 and defines a radial clearance with the sleeve member 132. A radially extending passage 194 communicates through the sleeve member 132 radially outwardly of the groove portion 192 to the annular chamber 176. The slots 188 and 190 are of narrow circumferential extent, and their axial ends precisely align in a sealing relationship with the axial ends of the lands 184 and 186. Radially outwardly of the slots 188 and 190, the housing 126 cooperates with the sleeve member 132 to define respective annular chambers 200 and 202. The chamber 200 communicates via a port 204 and a conduit 206 with the control assembly 104. Similarly, the chamber 202 communicates via a port 208 and a conduit 210 with the control assembly 106. Recalling the structure of the control assemblies 104 and 106, it will be seen that the conduit 206 opens into a chamber 212 defined by the plunger 100 and the remainder of the control assembly 104, while the conduit 210 opens into a chamber 214 defined by the plunger 102 and the remainder of the control assembly 106. In order to complete this description of the control valve apparatus 124, it must be noted that the sleeve member 130 cooperates with the plunger member 134 to define an annular chamber 216 which communicates with the chamber 180 via a radially extending passage 218. Similarly, the plunger member 134 cooperates with the sleeve member 130 to define an annular chamber 220 communicating with the chamber 182 via a radially extending passage 222. Between the ends of the plunger member 134 and spaced along its length, the plunger member 134 defines a plurality of circumferentially continuous grooves 224 which cooperate with the sleeve member 130 to define labyrinth seals. The operation of the hydraulic system 10 and of the power transfer unit 32 will now be described. With all of the pumps 16, 16′, 22 and 22′ operating, the conduits 26, 26′ are charged with high-pressure fluid at substantially equal pressures according to the design of the hydraulic system 10. As the pressure fluid absorptions of the loads 24 and 24′ vary as their various load items are valved in and out of operation, the fluid flow rates and pressures within the conduits 26 and 26′ vary. Spent fluid from each of the loads 24 and 24′ is returned via the respective conduits 28 and 28′ to the conduits 20 and 20′ between the charging pumps 16 and 16′ and the main high-pressure pumps 22, 22′. The relief valves 30 and 30′ operate to limit the pressure within conduits 20 and 20′ to about 150% of the design output pressure of the charging pumps 16 and 16′. Accordingly, the conduits 40 and 48 communicating with the power transfer unit 32 are also maintained at a pressure between the design discharge pressure of the charging pumps 16 and 16 and the relief pressure value of the respective relief valves 30 and 30′. While the conduits 26 and 26′ are charged to pressure levels which are substantially at the design pressure level for the hydraulic system 10, the motor-pump units 50 and 68 of power transfer unit 32 will not operate despite fluid pressure fluctuations within conduits 26 and 26′ which are within a limited and predetermined range. This is the case because the motor-pump units 50 and 68 are connected via the shaft portions 66 and 80 in an opposing torque relationship. Even though the torque produced by one of the motor-pump units 50 and 68 may exceed the opposing torque produced by the other motor-pump unit, the torque differential between the two units will not be sufficient to overcome the static friction, or breakaway torque, required to start the two units into rotation. However, even while the two motor-pump units 50 and 68 are static, the control valve apparatus 124 is operational in actuating the control assemblies 104 and 106 in preparation for the beginning of operation of the motor-pump units 50 and 68. By way of example only, let us say that the load 24 exceeds the pumping capacity of the high-pressure pump 22 so that the pressure in the conduit 26 is lower than that in the conduit 26′ but, that the pressure differential between them is not sufficient to begin operation of the motor-pump units 50 and 68. The relatively lower fluid pressure in the conduit 26 is communicated via the conduit 38 to the port 34 from there, via the conduit 166 into the chamber 170, and thence via the passage 174 to the chamber 150. On the other hand, the comparatively higher fluid pressure from the conduit 26′ is communicated via the conduit 46 to the port 42 and thence via the conduit 146 to the chamber 138 at the left-and of the control valve apparatus 124. Accordingly, the pressure differential between the chambers 138 and 172 is effective to shift the plunger member 134 and the spool valve member 136 slightly to the right in opposition to the spring 152 (as seen in Figure 2). Movement of the spool valve member 136 to the right shifts the land 186 to the right with respect to the radially extending slot 190 to connect the chamber 172 with the slot 190, and thus to communicate (low) high-pressure fluid to the conduit 210 via the port 208 and the chamber 202. The high-pressure fluid communicated via the conduit 210 to the control assembly 106 is effective in the chamber 214 to urge the plunger member 102 to the right. Simultaneously, the land 184 of the spool valve member 136 is shifted slightly to the right with respect to the slot 188 to connect the chamber 212 of the control assembly 104 with the case of the motor-pump unit 50 via the flow path defined by the features 206, 204, 188, 194, 176, 158 and 162. Therefore, fluid within the chamber 212 of the control assembly 104 is drained to the relatively low pressure established by charging pump 16 and the relief valve 30. When the force effective on the plunger 102 is sufficient to overcome the preload of the spring 108, the lever 94 is moved to the right by an amount dependent upon the spring rate of the spring 108. Considering the motor-pump unit 50 in greater detail, it will be seen that movement of lever 94 to the right in response to the above-described sequence of events results in a movement of the swashplate member 60 from its rest position towards a position of decreased displacement for the motor-pump unit 50. Consequently, the resisting torque generated by motor-pump unit 50 is decreased while the driving torque generated by the motor-pump unit 68 retains its previous level. Consequently, the power transfer unit 32 is prepared for the beginning of operation with the motor-pump unit 68 operating as a motor driving the motor-pump unit 50 in a pumping mode. Should the pressure differential between the conduits 26 and 26′ reach the predetermined level at which the breakaway torque of the motor-pump units 50 and 68 is exceeded by the torque differential between the units, they will begin to operate with the motor-pump unit 68 driving the motor-pump unit 50 thereby pumping fluid from the conduit 40 to the conduit 38 to assist in maintaining the pressure level in the conduit 26 approximately at the design pressure level. Once the motor-pump units 50 and 68 begin operation, the difference between the static friction of the components of the power transfer unit and the inherent dynamic friction during operation results in the pressure differential maintained between the conduits 26 and 26′ being less that that pressure differential which is necessary to begin operation of the power transfer unit. Accordingly, during operation of the power transfer unit, the control valve apparatus 24 modulates the position of control lever 94 and the displacement of the variable displacement motor-pump unit 50 in a range extending between its decreased displacement position, and that displacement which is defined at the rest position of the swashplate member 60 and the control lever 94. On the other hand, in the event that the load 24′ exceeds the pumping capacity of the primary high-pressure pump 22′, so that the pressure in the conduit 26′ is lower than that in the conduit 26, a higher effective pressure will prevail in the chamber 172 of the control valve apparatus 124 than that prevailing in the chamber 138. Consequently, the plunger member 134 will be shifted slightly to the left in opposition to the compression spring 140 while the compression spring 152 acting through the spring seat member 154 urges the spool valve member 136 to follow the plunger member 134. This movement of the spool valve member 136 to the left results in communication between the chambers 150 and 200 and from there to the port 204 and the conduit 206 extending to the control assembly 104. Also, this movement of the spool valve member 136 to the left results in communication between the conduit 210 (from control apparatus control assembly 106) via the port 208 and the passage 190 and the axially extending clearance between the groove portion 192 of spool valve 136 and sleeve 132 to drain fluid via the passage 194 to the conduit 162 communicating with the case of the motor-pump unit 50. As a result, the control lever 94 is shifted to the left in position to the compression spring 110 of the control assembly 106 according to its preload and spring rate. This shifting of the control lever 94 moves the swashplate member 60 angularly to a position which increases the effective displacement and static torque of the motor-pump unit 50 in preparation for its operation as a motor. The increase in effective displacement of the motor-pump unit 50 as described above results in this motor-pump unit generating a greater effective driving torque. On the other hand, the resisting torque generated by the motor-pump unit 68 is decreased by the relatively lower fluid pressure effective in the conduit 26′ and connected to it via the conduit 46. When the pressure differential between the conduits 26 and 26′ reaches the determined level necessary to overcome the break away torque set by the static frictions within the power transfer unit 32, operation begins with the motor-pump unit 50 operating as a motor driving the motor-pump unit 68 in a pumping mode. Consequently, the motor-pump unit 68 receives fluid via the conduit 48 and delivers this fluid pressurised via the conduit 46 to the conduit 26′ to assist in meeting the demands of the load 24′. During this operation of the power transfer unit, the control valve assembly 124 acts to modulate the position of the control lever 94 and so the swashplate member 60 in the range extending from its maximum displacement position to the rest position previously described. In view of the above, it will be seen that when the power transfer unit is in operation with either one of the motor-pump units 50 and 68 driving the other, the control lever 94 and swashplate member 60 is modulated between its rest position and either its minimum or maximum displacement position according to the direction of operation of the power transfer unit. That is, if the power transfer unit is operating to transfer power from the left-hand side of the system illustrated in Figure 1 to the right-hand side, the swashplate member 60 is positioned in a range extending from its maximum displacement position to its rest position. On the other hand, if the power transfer unit 32 is operating to transfer power from the right-hand side of the hydraulic system illustrated in Figure 1 to the left-hand side, then the position of the swashplate member 60 is modulated in a range extending from its minimum effective displacement position to its rest position. In view of this, it will be seen that when the load demand of either of the loads 24 or 24′ decreases such that the associated primary high-pressure pump 22 or 22′ is able to meet the design pressure requirement for the hydraulic system 10, the control lever 94 and the swashplate member 60 will be modulated to the rest position. Consequently, operation of the power transfer unit 32 will continue until such time as the torque differential between the two motor pump units falls below the total of dynamic frictional torque effective within the power transfer unit 32 and the resisting torque of that unit which is being operated in the pumping mode. When this stall condition is reached, operation of the motor-pump units 50 and 68 of the power transfer unit 32 will cease. However, the control valve apparatus 124 and the control assemblies 104 and 106 will be continuously operative to move the control lever 94 and the swashplate member 60 away from its rest position in anticipation of once again beginning operation of the motor-pump units of the power transfer unit 32 as the pressure levels in the conduits 26 and 26′ vary dynamically in response to variations of the pressure fluid utilisation effective within the loads 24 and 24′. The prefered embodiment described is predicated upon coupling hydraulic systems of equal design operating pressures. However, the invention is equally applicable to systems of unequal design simply by altering the relative size and pressure responsive areas of the component parts as necessary.

Claims: Power transfer apparatus which comprises a first fluid pump-motor unit (50) having associated high and low pressure fluid ports (34,36) for connection to a first pressure fluid source (14), and a first rotary shaft (66), the first unit (50) being operable to convert energy between pressurised fluid flow and mechanical rotation of the first shaft (66); a second fixed displacement fluid pump-motor unit (68) also having associated high and low pressure fluid ports (42,44) for connection to a second pressure fluid source (14') and a second rotary shaft (80), the second unit (68) being operable to convert energy between pressurised fluid flow and mechanical rotation of the second shaft (80), the first and second shafts (66,80) being mechanically interconnected for common rotation to transmit power between the first and second units (50,68) without mixture of their respective fluids; and control means (32) responsive to the pressure of the high pressure ports (34,42) of both the first and second units (50,68) and operable to maintain the pressure differential therebetween below a preslected level whenever the first and second shafts (50,68) are rotating; charcterised in that the first unit (50) is a variable displacement unit of the axial piston swashplate type with a variable swashplate member (60) and in operation, the control means (32) adjusts the position of the swashplate member. Apparatus as claimed in Claim 1 characterised in that the first motor-pump unit (50) includes a member (94) which is movable and engages the swashplate member (60) to vary selectively the effective pump displacement, the control means (32) including a first resilient means (108) yieldably biasing the movable member (94) to a selected first position of effective displacement, and first pressure responsive means (102,106) operable to move the movable member (94) to a second position of decreased effective displacement in opposition to the first resilient means (108) in response to a fluid pressure differential of the second pressure fluid source (26') over the first pressure fluid source (26). Apparatus as claimed in Claim 2, characterised in that the control means (32) further includes a second resilient means (110) yieldably biasing the movable member (94) to the selected first position of effective displacement, and second pressure responsive means (100,104) operable to move the movable member (94) to a third position of increased effective displacement in opposition to the second resilient means (110) in response to a fluid pressure differential of the first pressure fluid source (26) over the second pressure fluid source (26'). Apparatus as claimed in Claim 3, characterised in that the control means further includes a stop (116,118) respectively opposing each of the first and second resilient means (108,110) at the selected first position of the movable member (94). Apparatus as claimed in Claim 3 or Claim 4, characterised in that each of the pressure responsive means includes a housing (106,104) defining a bore, and a plunger (102,100) sealingly and movably received in the respective bore to define a variable-volume chamber (214,212); the first plunger (102) having a portion which engages the movable member (94) to move the latter to the second position of decreased effective displacement and a portion (114) which engages the respective stop (118) at the first selected position for the movable member (94); the second plunger (100) having a portion which engages the movable member (94) to move the latter to the third position of increased effective displacement and a portion (112) which engages the stop (116) at the first selected position for the movable member (94). Apparatus as claimed in Claim 5, characterised in that the control means (32) further includes valve means (136) communicating one of the variable-volume chambers (214) with the higher pressure fluid of the first pressure fluid source while simultaneously communicating the other variable-volume chamber (212) with the lower pressure fluid of the first pressure fluid source, in response to movement of the valve means (136) in a selected one of two directions; pressure responsive means (134) operatively associated with the valve means (136) for moving the latter in each of the two direction, the pressure responsive means (134) having a first pressure responsive face and an oppositely disposed second pressure responsive face sealingly separated from one another; means (166) communicating the first pressure responsive face with the comparatively high pressure fluid of the first pressure fluid source (14) to effect movement of the pressure responsive means (134) and the valve means (136) in one of the two directions to communicate the other variable volume chamber (212) with the comparatively high pressure fluid; means (146) communicating the second pressure responsive face with the relatively higher pressure fluid of the second pressure fluid source (14') to effect movement of the pressure responsive means (134) and the valve means (136) in the other direction to communicate the one variable volume chamber (214) with the comparatively higher pressure fluid; and resilient means (140,152) yieldably biasing the pressure responsive means (134) and the valve means (136) to a centred position in which neither of the two variable volume chambers (214,212) communicates with the comparatively higher pressure fluid. Apparatus as claimed in Claim 6, characterised in that the pressure responsive means further includes an elongate plunger (134) member which defines at its opposite ends respectively the first and second pressure responsive faces and in which the control means (32) includes a first annular drain chamber (180) circumscribing and communicating with the plunger member (134) between its ends but nearer to the first pressure responsive face, a second annular drain chamber (182) circumscribing and communicating with the plunger member (134) between its ends and spaced from the first drain chamber (180) but nearer to the second pressure responsive face, a first flow path 162,178) communicating the first drain chamber (180) with the lower pressure fluid of the first pressure fluid source (14), and a second flow path (156,160) communicating the second drain chamber (182) with the lower pressure fluid of the second pressure fluid source (14'), and sealing means sealingly separating the first pressure responsive face, the first drain chamber (180), the second drain chamber (182), and the second pressure responsive face, each from all of the others. Apparatus as claimed in Claim 7, characterised in that the sealing means is constituted by the plunger (134) being slidably received in close sealing relationship within a bore defined by said control means, and by the plunger (134) having a series of radially extending and circumferentially continuous grooves (224) spaced along its length to define a plurality of labyrinth seals within the bore. Apparatus as claimed in any preceding Claim, of Claims 2 to 8 characterised in that the second motor-pump (68) unit is of the bent-axis axial piston type. Apparatus as claimed in any preceding Claim, characterised in that the movable member comprises a control lever (94) affixed to the swash plate (60) of the first motor-pump unit for angular movement thereof.

Inventors: MCGOWAN, PETER T.
Applicants: ALLIED-SIGNAL INC. (A DELAWARE CORPORATION)
Application year: 1988
Main classification: F01B3
IPC codes: F03C1, F04B49, F01B3, F04B1, F15B11, B64C13