A pump/motor control mechanism

Abstract: To adjust the volumetric displacement of a pump or motor a member 1 is reciprocated as shown by the arrows. For this purpose the control mechanism has a first actuator (4) for shifting the member 1 forward when fluid pressure is introduced into a first cylinder chamber 9 located in the member 1, a second actuator 5 for shifting the member 1 backward when fluid pressure is introduced into a second cylinder chamber 13 located in the member 1, a spool holding hole 14 provided in the member 1 with an axis parallel to the direction of reciprocation and a spool 15 which is slidably fitted in the hole 14. The spool 15 has on its outer periphery a high-pressure groove 16 connected at 19 to a high-pressure fluid source and a low-pressure groove 18 opened to a low-pressure zone at 22. A first pressure introducing path has one end 23 connected to the first cylinder chamber 9 and its other end open to an area 20 which is on the inner periphery of the spool holding hole 14 and connected to the high-pressure groove 16 when the spool is moved forward by actuator 28 and to the low-pressure groove 18 when the spool moves backward, and a second pressure introducing path 24 has one end connected to the second cylinder chamber 13 and its other end open to an area 21 which is on the inner periphery of the spool holding hole 14 and connected to the high-pressure groove 16 when the spool is moved backward by spring 27 and to the low-pressure groove 18 when the spool moves forward.

Description: BACKGROUND OF THE INVENTION The present invention relates to a displacement control mechanism utilized for a pump/motor which is arranged so as to change its displacement corresponding to the forward/backward displacement of a forward/backward member. Such type of a pump/motor is shown, for example, in Fig. 5. It is a static-pressure type pump/motor proposed in U.S. Pat. No. 4770081 which is arranged so as to perform pump function or motor function by increasing or decreasing the volume of a space 103 for fluid inflow or outflow following the relative rotation of a first member 101 to second member 102. The volume can be changed by reciprocatively moving a forward/backward member 104 supporting one of said members 101 and 102 in the direction perpendicular to a rotating axis center so as to adjust the eccentricity between both the members. As an eccentricity control mechanism, provided are input means 105 (a stepping motor for converting electrical digital signals to mechanical displacement, in Fig. 5) and a servo mechanism 106 for reciprocatively moving said forward/backward member 104 in proportion to a controlled variable of the input means 105. The servo mechanism 106 comprises an actuator 107₁ (107₂), for actuating forward (backward) the forward/backward means by introducing a fluid pressure into a cylinder chamber 107a₂ (107a₂), an operating stick 108 which is located along side forward/backward member 104 and reciprocatively moves in the same direction as the forward/backward means 104 by receiving an operating input, rack gears 109 and 110 which are located on the oppositely faced areas of the operating stick 108 and the forward/backward member 104 respectively, a spool 111 which is located between the rack gear 109 and the rack gear 110 and movable reciprocatively in the direction parallel to said operating stick 108, an idle gear 112 which is pivotally connected to the spool 111 and engaged with said rack gears 109 and 110, and a liquid pressure circuit 113 which is allowed to change over in such a manner as to lock said actuators 107₁ and 107₂ when said spool 111 is in a neutral position and to move said actuator 107₁ (107₂) in a direction in which said spool 111 returns back to its neutral position when said spool 111 is moved to a non-neutral position by the movement of said operating stick 108. Also, variable volume type inclined-plate pump and the like have a similar volume control mechanism to the one described above, which are externally equipped with a servo cylinder with which an actuator installed on a forward/backward member is driven and are designed to feed back the output displacement of the forward/backward member through a link mechanism and the like to said servo cylinder. However, where a volume control mechanism is arranged in such a manner that the output displacement of a forward/backward member is fed back through an intermediate mechanism such as rack pinion (or link) to a spool as described above, a large space becomes necessary to arrange the volume control mechanism around a pump body. This leads to a large size or increased weight pump along with an unavoidable problem such as higher cost and increased assembling man-days. Further, with respect to performance, because of a looseness or hysteresis of link mechanism and the like, stability, high-speed property and resolving power are liable to be deteriorated, causing a problem in reliability or durability. The present invention has been developed to solve such problems. Accordingly, the object of the present invention is to eliminate all such problems by excluding mechanical intermediate mechanism. In accordance with the invention in one form a control mechanism for shifting a reciprocating member to alter the volumetric displacement of a pump or motor comprises a first actuator for shifting the reciprocating member forwards when fluid pressure is introduced into a first cylinder chamber in the reciprocating member, a second actuator for shifting the reciprocating member backwards when fluid pressure is introduced into a second cylinder chamber in the reciprocating member, a spool slidable in a bore in the reciprocating member in a direction parallel to the direction of reciprocation, and an actuator for moving the spool to initiate shifting of the reciprocating member, the spool having on its outer periphery a high-pressure groove connected to a high pressure source and a low-pressure groove connected to a drain, and the reciprocating member having a first flow path connecting the first cylinder chamber to a zone of the bore which is connected to the high-pressure groove when the spool is moved forward and to the low-pressure groove when the spool is moved backward and a second flowpath connecting the second cylinder chamber to a zone of the bore which is connected to the high-pressure groove when the spool is moved backward and to the low-pressure groove when the spool is moved forward. When the spool moves forward, a fluid pressure is introduced into the first cylinder chamber while the second cylinder chamber is opened to the low-pressure zone, so that the forward/backward member follows the spool in such a manner as to move forward by the distance equal to the travel of the spool. On the contrary, when the spool moves backward, a fluid pressure is introduced into the second cylinder chamber while the first cylinder chamber is opened to the low-pressure zone, so that the forward/backward member follows in such a manner as to move backward by the distance equal to the travel of the spool. Thus, according to the present invention, almost all elements of the volume control mechanism including the spool can be housed in the inside of the forward/backward member, thereby allowing a much more simple structure than that of prior art. Additionally, with such structure, a self-feedback system can be arranged only by the relative-position relationship between the spool and the forward/backward member, thereby making it unnecessary to provide a mechanical intermediate mechanism. Accordingly, various problems which have been derived from such intermediate mechanism used for prior art can now be completely eliminated. In an alternative form of the invention, as claimed in claim 2, the first flow path connects the first cylinder chamber to a zone of the bore which is connected to the high pressure groove at all times, and the second cylinder chamber has a larger operating area than the first cylinder chamber. Thus, when the spool moves backward, a fluid pressure is introduced into the first and the second cylinder chambers and since the pressure-receiving surface of the second cylinder chamber is larger than that of the first cylinder chamber, the forward/ backward member follows the spool in such a manner as to move backward by the distance equal to the travel of the spool. On the contrary, when the spool moves forward, a fluid pressure is introduced into the first cylinder chamber while the second cylinder chamber is opened to the low-pressure zone, so that the forward/backward member follows the spool in such a manner as to move forward by the distance equal to the travel of the spool. The present invention can thus arrange a self-feedback system without using any intermediate mechanism, so that the present invention can eliminate problems which have been derived from such intermediate mechanism used for prior art and provide a compact and high-performance pump/motor volume control mechanism. BRIEF DESCRIPTION OF THE DRAWING Figs. 1 through 4 show an embodiment according to the present invention: Fig. 1 is a sectional front view, Fig. 2 is a sectional side view taken along line II - II of Fig. 1, and Figs. 3 and 4 are typical action illustrative drawings. Also, Fig. 5 is a general sectional view showing a situation where a prior art example has been applied to a pump/motor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT With reference to drawings, an embodiment according to the present invention will be explained hereinafter. A volume control mechanism of the embodiment which can be applied to, for example, as shown in Fig. 5 a static-pressure type pump/motor is provided with a large-diametral through hole 2 along the forward/backward direction of and in the center of a forward/backward mechanism 1, and a center block 3 made as a separate part is press fitted in said through hole 2 (Figs. 1 and 2). First actuators 4 and second actuators 5 which have a competitively opposite relationship to each other are arranged on their respective areas displaced from the through hole 2 to its both sides. As shown in Fig. 1, the first actuator 4 is formed by concavely providing a cylinder bore 6 on the right end face of the forward/backward member 1 and by defining a first cylinder chamber 9 in such a manner that a piston 8 fixed to a housing inner-wall 7₁ at its outer end is slidably fitted in the cylinder bore 6. The first acutuator 4 plays a role to actuate forward said forward/backward member 1 leftward in Fig. 1 as viewed when a fluid pressure is introduced into the first cylinder chamber 9. As also shown in Fig. 1, the second actuator 5 is formed by concavely providing a cylinder bore 10 on the left end face of the forward/backward member 1 and by defining a second cylinder chamber 13 in such a manner that a piston 12 fixed to a housing inner-wall 7₂ at its outer end is slidably fitted in the cylinder bore 10. The second actuator 5 plays a role to actuate backward said forward/backward member 1 rightward in Fig. 1 as viewed when a fluid pressure is introduced into the second cylinder chamber 13. On the other hand, said center block 3 is provided with a spool holding hole 14 having an axis center parallel to the forward/backward direction and a spool 15 is slidably fitted in the spool holding hole 14. The spool 15 is provided on its outer periphery with a high-pressure groove 16 located widely on its center, intermediate grooves 17₁ and 17₂ located across a land on the both sides of the high-pressure groove, and low-pressure grooves 18₁ and 18₂ located across a land on the both ends of the intermediate grooves. On the other hand, the spool holding hole 14 in the neutral position shown in Fig. 1 is provided on its inner periphery with a high-pressure port 19 opened to said high-pressure groove 16, a first port 20 opened to said intermediate groove 17₁, a second port 21 opened to said intermediate groove 17₂, and drain ports 22₁ and 22₂ opened to said low-pressure grooves 18₁ and 18₂ respectively. Also, said first port 20 is connected through a first pressure introducing path 23 to said first cylinder chamber 9 in the inside of the forward/backward member 1, while said second port 21 is connected through a second pressure introducing path 24 to said second cylinder chamber 13 in the inside of the forward/backward member 1. Fluid flowing paths (not illustrated) connecting the pump/motor body to an external pert are provided in pair in the inside of the forward/backward member 1, and have an unfixed pressure in terms of high or low so that the pressure may be reversed depending on service condition. Accordingly, the volume control mechanism is arranged in such a manner that said high-pressure port 19 is connected through a shuttle valve to the both fluid flowing paths so as to introduce a high-pressure from either of the fluid flowing paths at all times. The drain ports 22₁ and 22₂ are separately connected to a tank. An end plate 25 is mounted on the right end of said spool 15, and a spring 27 is elastically provided between the end plate 25 and a concavely provided edge 26 of said forward/backward member 1. The spool 15 can be correctly maintained at a command position at all times in such a manner that with spring force said spool end plate 25 is allowed to be pushed on the edge of a command rod 28 being input means externally inserted through a housing 7 into the inside of said housing 7 so as to offset any gap between the spool and the rod edge. The operation of the embodiment will be explained hereinafter. When an input signal is applied through the command rod 28 to the spool 15 to be moved forward from the neutral position shown in Fig. 1, the first port 20 is connected to the high-pressure groove 16 as shown in Fig. 3, so that a fluid pressure is introduced through the first pressure introducing path 23 to the first cylinder chamber 9. On the other hand, the second port 21 is connected to the low-pressure groove 18₂, so that the second cylinder chamber 13 is opened through the pressure introducing path 24 to a low-pressure zone. Accordingly, the forward/backward member 1 is actuated in the forward direction to follow the spool 15. When the travel becomes equal to that of the spool 15 having previously been moved, said spool 15 is reset to a relatively neutral position with respect to the forward/backward member 1, so that the operating pressure is dissipated to cause the forward/backward member 1 to be stopped. On the contrary, when the spool 15 is moved backward from the neutral position shown in Fig. 1, the second port 21 is connected to the high-pressure groove 16 as shown in Fig. 4, so that a fluid pressure is introduced through the second pressure introducing path 24 into the second cylinder chamber 13. On the other hand, the first port 20 is connected to the low-pressure groove 18₁, so that the first cylinder chamber 9 is opened through the first pressure introducing path 23 to the low-pressure zone. Accordingly, the forward/backward member 1 is actuated in the backward direction to follow the spool 15. When the travel becomes equal to that of the spool having previously been moved, said spool 15 is reset to a relatively neutral position with respect to the forward/backward member 1, so that the operating pressure is dissipated to cause the forward/backward member 1 to be stopped. Thus, the forward/backward member 1 is displaced forward or backward correctly responding to the input signal applied to the command rod 28 to allow the pump (motor) volume to be changed. As apparent also by comparing Fig. 1 with Fig. 5, with such arrangement, almost all elements of the volume control mechanism can be housed in the inside of the forward/backward member 1. This requires a slightly increased weight and size affecting the pump/motor body and at the same time allows a decreased number of parts and cost, as well as a reduced assembling man-days. Additionally, a self-feedback system can be arranged only by the relative position relationship between the spool 15 and the forward/ backward member 1, so that with respect to performance a looseness or hysteresis is eliminated, and a higher wear-resistance and a larger feedback gain are obtained. Consequently, this makes it possible to increase control speed, response characteristic and resolving power and to provide an excellent safety and durability. Also, the forward/backward member receives a sawtooth load with an amplitude proportional to the pressure on the high-pressure side of the liquid-pressure circuit. However, in this embodiment, the control pressure of the forward/backward member 1 is obtained from the high-pressure port 19 connected through the shuttle valve to the fluid flowing pathes, so that the forward/backward member 11 can be controlled with a control pressure corresponding to the amplitude of the sawtooth load, providing a smooth control regardless of the pressure on the high-pressure side. In an alternative embodiment the second cylinder chamber 13 has a larger pressure-receiving surface than the first cylinder chamber 9. The first path 23 is connected at all times to the high-pressure groove 19. The second path 24 is connected as before so that when the spool 15 moves backward it connects the second chamber 13 to the high-pressure groove 19 and because of the difference in area of the two chambers the member 1 is moved backwards. When the spool 15 moves forward the chamber 13 is connected to the low pressure groove 18 and the member 1 is moved forwards by the high pressure in the chamber 9. Further, the spool may be allowed to penetrate directly to the outside of the housing so as to be connected to external input means. However, if the spool is arranged as shown in Fig. 1, any slight looseness in the command rod will not be transferred to the spool providing a favourable condition for machining. It will be appreciated that the relationship in position between the high-pressure groove, the low-pressure groove and the pressure introducing path is not limited to the illustrated examples, and can be embodied with various modes. Additionally, although the high-pressure side of the pair of the fluid flowing paths provided in the forward/backward member is connected to the high-pressure port in the above embodiment, there is also a case where with the low-pressure side utilized an effective control can be performed. Also, as another embodiment of the present invention, a three-way valve type servo mechanism as it is called can be practiced. In this case, such mechanism not only exhibits an effect similar to that of the first embodiment, but also has an advantage of simpler structure. Further, it will be appreciated that the volume control mechanism can be utilized for inclined-type, bent-axis type and other types of pumps/motors.

Claims: A control mechanism for shifting a reciprocating member (1) to alter the volumetric displacement of a pump or motor comprising a first actuator (4) for shifting the reciprocating member (1) forwards when fluid pressure is introduced into a first cylinder chamber (9) in the reciprocating member (1), a second actuator (5) for shifting the reciprocating member (1) backwards when fluid pressure is introduced into a second cylinder chamber (13) in the reciprocating member (1), a spool (15) slidable in a bore (14) in the reciprocating member in a direction parallel to the direction of reciprocation, and an actuator (28) for moving the spool to initiate shifting of the reciprocating member, the spool (15) having on its outer periphery a high-pressure groove (16) connected to a high pressure source and a low-pressure groove (18) connected to a drain, and the reciprocating member having a first flow path (23) connecting the first cylinder chamber to a zone of the bore which is connected to the high-pressure groove when the spool is moved forward and to the low-pressure groove when the spool is moved backward and a second flowpath (24) connecting the second cylinder chamber to a zone of the bore which is connected to the high-pressure groove when the spool is moved backward and to the low-pressure groove when the spool is moved forward. A control mechanism for shifting a reciprocating member (1) to alter the volumetric displacement of a pump or motor comprising a first actuator (4) for shifting the reciprocating member (1) forwards when fluid pressure is introduced into a first cylinder chamber (9) in the reciprocating member (1), a second actuator (5) for shifting the reciprocating member (1) backwards when fluid pressure is introduced into a second cylinder chamber (13) in the reciprocating member (1), a spool (15) slidable in a bore (14) in the reciprocating member in a direction parallel to the direction of reciprocation, and an actuator (28) for moving the spool to initiate shifting of the reciprocating member, the spool (15) having on its outer periphery a high-pressure groove (16) connected to a high pressure source and a low-pressure groove (18) connected to a drain, and the reciprocating member having a first flow path (23) connecting the first cylinder chamber (9) to a zone of the bore which is connected to the high pressure groove at all times and a second flow path (24) connecting the second cylinder chamber to a zone of the bore which is connected to the high-pressure groove when the spool is moved backward and to the low-pressure groove when the spool is moved forward, the second cylinder chamber (13) having a larger operating area than the first cylinder chamber (9).

Inventors: KITA YASUO KYOTO ENGINEERING C, MURAKAMI HIROAKI SHIMADZU CORP, SUGAHARA RYOSUKE SHIMADZU CORP, KITA, YASUO KYOTO ENGINEERING CO. LTD.,, MURAKAMI, HIROAKI SHIMADZU CORPORATION, SUGAHARA, RYOSUKE SHIMADZU CORPORATION
Applicants: SHIMADZU CORP, SHIMADZU CORPORATION
Application year: 1990
Main classification: F04B49
IPC codes: F03C1, F04B49, F04B1