JP2023522176A - Auxiliary torque electrohydraulic piston pump system - Google Patents

Abstract

An electrohydraulic piston pump system directly connects the electric motor 16, the first hydraulic piston pump 30 and the second hydraulic piston pump 60, and the first port 48 of the first pump. a first hydraulic actuator 90 having a connected first port 93 and a second port 94 directly connected to the first pump second port 49 and a second pump third port 78; a second hydraulic actuator 100 having a third port 103 directly connected to and a fourth port 104 directly connected to a fourth port 79 of the second piston pump; An external force applied to the first hydraulic actuator 90 that provides a negative pressure differential with respect to the first pump applies an assist torque to the common motor shaft 18 to force the first pump 30 and the second pump to operate. 60 and provide a total negative pressure differential to the first and second pumps 30 and 60, the motor 16 Recharge the power supply for

Description

FIELD OF THE INVENTION The present invention relates in broad terms to the field of electro-hydraulic pump systems, and more particularly to an improved assistive torque electro-hydraulic piston pump system.

Hydraulic radial piston pumps are generally known in the prior art. The drive torque of the shaft is transmitted to a radial piston-cylinder block rotatably mounted on a control stud or journal, where the pistons are radially arranged within the cylinder block and thrust rings It is supported at its outer end by a thrust ring or stroke ring via an internal slide shoe. When the cylinder block rotates, the piston exerts a stroke motion as a result of the eccentric position of the thrust ring. Pump flow is routed into and out of the housing and control stud via channels and is controlled by suction and pressure windows in the control stud. be done. If the differential cylinder is actuated by a hydraulic radial piston motor, a proportional valve or a pressure distribution valve is inserted. A differential cylinder has two working spaces, each with its own working connection, a first working connection leading to the working space on the piston end and a second working connection. A device connects to the working space on the rod end of the differential cylinder. A volumetric flow of hydraulic fluid supplied by a hydraulic radial piston motor can be routed through the valves to reach specific working connections and thus specific working spaces.

For purposes of illustration only and not limitation, electrohydraulic pump systems (15, 115, 215, 315) is provided, this electro-hydraulic pump system (15, 115, 215, 315) having a drive shaft (18, 18A, 18B, 18C, 23, 123, 318, 323) to supply electrical current. an electric motor (16) adapted to receive; a first fluid control journal (31, 331) and a first motor about a first block axis (34, 334) by rotation of the drive shaft (18, 318); and a first displacement axis (38 , 338), and a first hydraulic piston pump (30, 330) having: A first neutral position between the first displacement axis (38, 338) and the first block axis (34, 334) and the first displacement axis (38, 338) and the first block axis ( a first displacement drive (34, 334) adapted to move within a first positive displacement range (40, 340) between 35, 335) between a first neutral position and a first negative maximum displacement position between the first displacement axis (38, 338) and the first block axis (34, 334). a first fluid control journal (31,331) adapted to move within a first negative displacement range (44,344) between the first pump port (48,348) and the second having a pump port (49, 349) and rotating the drive shaft (18, 318) when the first displacement drive (35, 335) is within the first positive displacement range (40, 340); to provide a higher pressure to the first pump port (48, 348) relative to the second pump port (49, 349) and the first displacement drive (35, 335) to the first The rotation of the drive shaft (18, 318) when within the negative displacement range (44, 344) of the first pump port (48, 348) causes a higher pressure in the second pump port (48, 348). A first hydraulic piston pump (30, 330) provided to port (49, 349); a plurality of pistons ( 62, 362) and a second displacement drive (65, 365) having a second displacement axis (68, 368), wherein A second neutral position in which the second displacement drive (65, 365) is between the second displacement axis (68, 368) and the second block axis (64, 364); move within a second positive displacement range (70, 370) between a second maximum positive displacement position between the axis (68, 368) and the second block axis (64, 364); and the second displacement drive (65, 365) is in a second neutral position between the second displacement axis (68, 368) and the second block axis (64, 364) and a second negative maximum displacement position between the second displacement axis (68,368) and the second block axis (64,364). , 374) and the second fluid control journal (61, 361) has a third pump port (78, 378) and a fourth pump port (79, 379). , the fourth pump port (79) by rotating the drive shaft (18,318) when the second displacement drive (65,365) is within the second positive displacement range (70,370) , 379) is provided to the third pump port (78, 378) and the second displacement drive (65, 365) is within the second negative displacement range (74, 374). a higher pressure is provided to the fourth pump port (79, 379) relative to the third pump port (78, 378) by rotation of the drive shaft (18, 318) when at a second hydraulic piston pump (60, 360); A first hydraulic actuator (90, 390) having one working port (93, 393), wherein the first hydraulic actuator (90, 390) is connected to a first piston pump (30, 330) a first hydraulic actuator (90, 390) having a second actuation port (94, 394) hydraulically connected (53, 353) to a second pump port (49, 349) of the; Second hydraulic with third working port (103, 403) hydraulically connected (82, 382) to third pump port (78, 378) of two piston pumps (60, 360) actuator (100, 400), wherein a second hydraulic actuator (100, 400) hydraulically connects a fourth pump port (79, 379) of a second piston pump (60, 360); a second hydraulic actuator (100, 400) having a fourth actuation port (104, 404) connected (83, 383) to the first displacement drive (35, 335); higher pressure (51) to the second pump port (49, 349) relative to the first pump port (48, 348) while within the first positive displacement range (40, 340); An external force (F1) applied to the first hydraulic actuator (90, 390), which provides an assist torque to the drive shaft (18, 318); providing a higher pressure (51) to the first pump port (48, 348) relative to the second pump port (49, 349) when within the negative displacement range (44, 344) of , an external force (F2) applied to the first hydraulic actuator (90, 390) applies an assist torque to the drive shaft (18, 318).

a higher pressure (81) relative to the third pump port (78, 378) when the second displacement drive (65, 165) is within the second positive displacement range (70, 370); An external force (F3) applied to the second hydraulic actuator (100, 400) providing the fourth pump port (79, 379) can apply an assist torque to the drive shaft (18, 318). higher pressure (81) relative to the fourth pump port (79, 379) when the second displacement drive (65, 365) is in the second negative displacement range (74, 374); to the third pump port (78, 378) can apply an assist torque to the drive shaft (18, 318). can.

An electrohydraulic pump system may have a battery (21) that supplies current to the electric motor (16). A motor (16) may be configured to selectively supply current to the battery (21) in a regeneration mode, in which an external force (F1) applied to the first hydraulic actuator (90, 390) is , a second higher pressure relative to the first pump port (48, 348) when the first displacement drive (35, 335) is within the first positive displacement range (40, 340). pump port (49, 349) or applied to the first hydraulic actuator (90, 390) causes the first displacement drive (35, 335) to cause the first providing a higher pressure (51) to the first pump port (48, 348) relative to the second pump port (49, 349) when in the negative displacement range (44, 344) of The external force (F3) applied to the second hydraulic actuator (100, 400) is a second force when the second displacement drive (65, 365) is within the second positive displacement range (70, 370). 3 pump port (78, 378) to provide a higher pressure (81) to the fourth pump port (79, 379) or to the second hydraulic actuator (100, 400) An applied external force (F4) is referenced to the fourth pump port (79, 379) while the second displacement drive (65, 365) is in the second negative displacement range (74, 374). A higher pressure (81) is provided to the third pump port (78, 378).

A first hydraulic actuator (90, 390) may be configured to actuate a first object (118) of an electric vehicle (116), and a second hydraulic actuator (100, 400) may actuate the electric vehicle (116). It may be configured to actuate the second object of (116). Electric motors may be selected from the group consisting of brushless DC servo motors, stepper motors, brush motors, and induction motors. The first hydraulic actuator can include a linear hydraulic actuator or a rotary hydraulic actuator. A first hydraulic actuator drives a first chamber (91, 241, 391), a second chamber (92, 242, 392), and a piston (95, 245, 395) separating the first and second chambers. ). A first hydraulic actuator may have a cylinder (98, 248, 398) having a first end wall (98A, 248A), a piston (95, 245, 395) sliding sealingly therein. Disposed within a cylinder (98, 248, 348) for movement, the piston (95, 245, 395) has a portion sealingly extending through the first end wall (98A, 248A). It may have an actuator bar (96, 246, 396). The cylinder (98) may have a second end wall (98B) and the piston (95) has a second actuator rod (97) having a portion sealingly extending through the second end wall (98B). can have An electrohydraulic pump system may have a position sensor configured to sense the position of the piston (95, 245, 395). An electrohydraulic pump system may have pressure sensors configured to sense the pressure in the first chamber (91, 141, 391) and the second chamber (92, 142, 392).

The electro-hydraulic pump system is driven by a third fluid control journal (131) and relative to the third fluid control journal (131) about a third block axis (134) by rotation of the drive shaft (18). a plurality of pistons (132) in a third cylinder block (133) adapted to rotate; and a third displacement drive (135) having a third displacement axis (138). A third hydraulic piston pump (130) in which a third displacement drive (135) is between a third displacement shaft (138) and a third block shaft (134). a third positive displacement range (140) between the neutral position of and a third maximum positive displacement position between the third displacement axis (138) and the third block axis (134) a third displacement drive (135) adapted to move within a third neutral position between the third displacement axis (138) and the third block axis (134); to move within a third negative displacement range (144) between a third maximum negative displacement position between the three displacement axes (138) and the third block axis (134); A third fluid control journal (131) has a fifth pump port (148) and a sixth pump port (149), and a third displacement drive (135) has a third positive a higher pressure is provided to the fifth pump port (148) relative to the sixth pump port (149) by rotation of the drive shaft (18) when within the displacement range (140) of Higher pressure relative to the fifth pump port (148) due to rotation of the drive shaft (18) when the third displacement drive (135) is within the third negative displacement range (144) is provided to the sixth pump port (149); hydraulically to the fifth pump port (148) of the third piston pump (130); A third hydraulic actuator (190) having a fifth actuation port (193) connected (152), wherein the third hydraulic actuator (190) is connected to the third piston pump (130). a third hydraulic actuator (190) having a sixth actuation port (194) hydraulically connected (153) to a sixth pump port (149); a third displacement drive; A third pump port (149) that provides a higher pressure to the sixth pump port (149) relative to the fifth pump port (148) when (135) is within the third positive displacement range (140). an external force applied to the hydraulic actuator (190) of the third displacement drive (135) applies an assist torque to the drive shaft (18); An external force applied to the third hydraulic actuator (190) providing a higher pressure to the fifth pump port (148) relative to the sixth pump port (149) assists the drive shaft (18). Add torque. The shaft comprises a first part (18A) mechanically connected to the first cylinder block (33), a second part (23, 18B), and a third part (123) mechanically connected to the third cylinder block (133).

An electrohydraulic pump system selectively moves a first displacement drive (35, 335) within a first positive displacement range (40, 340) and a first negative displacement mechanically connected to the first displacement drive (35, 335) configured to selectively move the first displacement drive (35, 335) within the range (44, 344); It may have a first displacement drive actuator (54, 354). An electrohydraulic pump system selectively moves a second displacement drive (65, 365) within a second positive displacement range (70, 370) and a second negative displacement mechanically connected to the second displacement drive (65, 365) configured to selectively move the second displacement drive (65, 365) within the range (74, 374); There may be a second displacement drive actuator (84, 384).

A first fluid control journal may comprise a first central control journal (31); a first displacement drive having a first stroke oriented about a first displacement axis (38); a ring (35); a first neutral position between the first displacement axis (38) and the first block axis (34); the first streak ring (35) may be adapted to move radially with respect to the first neutral position; the first A first positive maximum displacement position between the displacement axis (38) and the first block axis (34) is the first position in a first positive direction (41) relative to the first neutral position. a first positive eccentric position radially offsetting the first displacement axis (38) from the first block axis (34) by a maximum positive eccentric distance (42); the displacement range may include a first positive eccentric range (40) between a first neutral position and a first positive eccentric position; a first displacement axis (38) and a first block; A first negative maximum displacement position between the axis (34) at a first negative maximum eccentric distance (46) in a first negative direction (45) relative to the first neutral position. may include a first negative eccentric position radially offsetting the one displacement axis (38) from the first block axis (34); a first negative eccentric range (44) between a first negative eccentric position; a first stroke ring (35) within a first positive eccentric range (40); A higher pressure (51) may be provided to the first pump port (48) relative to the second pump port (49) by rotation of the drive shaft (18) at certain times; a higher pressure (51) relative to the first pump port (48) due to rotation of the drive shaft (18) when the ring (35) is within the first negative eccentricity range (44); A second fluid control journal may be provided at the second pump port (49); a second fluid control journal may have a second central control journal (61); a second displacement drive may be provided at the second displacement axis ( 68) oriented about a second stroke ring (65); a second neutral between the second displacement axis (68) and the second block axis (64); The position may include a position where the second displacement axis (68) and the second block axis (64) are coaxial; a second maximum positive displacement position between the second displacement axis (68) and the second block axis (64) relative to the second neutral position; a second positive eccentric position that offsets the second displacement axis (68) from the second block axis (64) by a second maximum positive eccentric distance (72) in the second positive direction (71). the second positive displacement range may comprise a second positive eccentric range (70) between the second neutral position and the second positive eccentric position; A second negative maximum displacement position between the displacement axis (68) of the second block axis (64) and the second block axis (64) in a second negative direction (75) relative to the second neutral position. a second negative eccentric position radially offsetting the second displacement axis (68) from the second block axis (64) by a maximum negative eccentric distance (76) of may include a second negative eccentric range (74) between a second neutral position and a second negative eccentric position; Rotation of the drive shaft (18) when within the positive eccentricity range (70) of two causes a higher pressure in the third pump port (78) relative to the fourth pump port (79). referenced to the third pump port (78) by rotating the drive shaft (18) when the second stroke ring (65) is within the second negative eccentric range (74); higher pressure can be provided to the fourth pump port (79) as; the first pump port when the first stroke ring (35) is within the first positive eccentric range (40) An external force (F1) applied to the first hydraulic actuator (90) providing a higher pressure (51) to the second pump port (49) relative to (48) causes the drive shaft (18) to Assist torque can be applied; higher pressure (51 ) to the first pump port (48) can apply an assist torque to the drive shaft (18).

The electro-hydraulic pump system is a third hydraulic piston pump (130) comprising a third central control journal (131) and a drive shaft ( 18) a plurality of pistons in a third cylinder block (133) adapted to rotate about a third block axis (134) with respect to a third central control journal (131) by rotation of (132) and a third stroke axis adapted to move radially with respect to a third central position coaxial with the third stroke axis (138) and the third block axis (134). a third stroke ring (135) oriented about (138), the third stroke ring (135) having a third center position and a third positive eccentric position; adapted to move linearly within a third positive eccentric range (140) between Offset from the third block axis (134) by a third maximum positive eccentric distance, a third stroke ring (135) is between the third center position and the third negative eccentric position adapted to move linearly within a third range of negative eccentricity (144), with a third stroke axis (138) having a third positively opposite third stroke relative to the third center position; offset from the third block axis (134) at a third negative maximum eccentric distance in the negative direction of the third control journal (131) to the fifth pump port (148) and the sixth pump port (149) and rotation of the drive shaft (18) when the third stroke ring (135) is within the third positive eccentric range (140) to the sixth pump port (149). A higher pressure is provided to the fifth pump port (148) relative to the drive shaft (18) when the third stroke ring (135) is within the third negative eccentric range (144). provides a higher pressure to the sixth pump port (149) relative to the fifth pump port (148) by rotating the third hydraulic piston pump (130); a third hydraulic actuator (190) having a fifth actuation port (193) directly hydraulically connected (152) to a fifth pump port (148) of the piston pump (130); , a sixth actuation port (194) in which a third hydraulic actuator (190) is directly hydraulically connected (153) to a sixth pump port (149) of a third piston pump (130). ); and a fifth pump actuator (190) when the third stroke ring (135) is within the third positive eccentric range (140). an external force applied to the third hydraulic actuator (190) providing a higher pressure to the sixth pump port (149) relative to the port (148) applies an assist torque to the drive shaft (18); A higher pressure is applied to the fifth pump port (148) relative to the sixth pump port (149) when the third stroke ring (135) is within the third negative eccentric range (144). An external force applied to the third hydraulic actuator (190), which provides , applies an assist torque to the drive shaft (18B). The shaft comprises a first part (18A) mechanically connected to the first cylinder block (33), a second part (23, 18B), and a third part (123) mechanically connected to the third cylinder block (133).

An electrohydraulic pump system selectively displaces the first stroke ring (35) within a first positive eccentric range (40) between a first center position and a first positive eccentric position. and within a first negative eccentric range (44) between a first central position and a first negative eccentric position. There may be a first hydraulic ring actuator (54) mechanically connected to the first stroke ring (35) configured for selective linear movement. An electrohydraulic pump system selectively displaces the second stroke ring (65) within a second positive eccentric range (70) between a second central position and a second positive eccentric position. and within a second negative eccentric range (74) between a second central position and a second negative eccentric position. There may be a second hydraulic ring actuator (84) mechanically connected to the second stroke ring (65) configured for selective linear movement.

A first fluid control journal may have a first port plate (331); a first displacement drive may have a first swash plate oriented about a first displacement axis (338); a plate (335); a first neutral position between the first displacement axis (338) and the first block axis (334); the first swash plate (335) may be adapted to move angularly with respect to the first neutral position; the first A first positive maximum displacement position between the displacement axis (338) and the first block axis (334) is a first positive angular direction relative to the first neutral position. may include a first positive angular position offsetting the first displacement axis (338) from the first block axis (334) at a maximum positive cam angle (340); , a first positive angular range (340) between a first neutral position and a first positive angular position; a first displacement axis (338) and a first block axis (334); ) on the first displacement axis at a first negative maximum cam angle (346) in a first negative angular direction relative to the first neutral position. (338) offset from the first block axis (334); the first negative displacement range includes a first neutral position and a first negative angular position when the first swash plate (335) is within the first positive angular range (340) the drive shaft (318 ) may rotate to provide a higher pressure to the first pump port (348) relative to the second pump port (349); A higher pressure may be provided to the second pump port (349) relative to the first pump port (348) by rotating the drive shaft (318) when within the angular range (344) of a second fluid control journal may have a second port plate (361); a second displacement drive may have a second swash oriented about a second displacement axis (368); a second neutral position between the second displacement axis (368) and the second block axis (364), the second displacement axis (368) and the second block A second swash plate (365) may be adapted to move angularly with respect to a second neutral position; a second displacement; A second positive maximum displacement position between the axis (368) and the second block axis (364) is a second positive angular direction in a second positive angular direction relative to the second neutral position. a second positive angular position offsetting the second displacement axis (368) from the second block axis (364) at the maximum cam angle (372); a second positive angular range (370) between two neutral positions and a second positive angular position; a second displacement axis (368) and a second block axis (364); and the second displacement axis ( 368) offset from the second block axis (364); a second negative displacement range between the second neutral position and the second negative angular position; A second negative angular range (374) may be included; the drive shaft (318) rotates when the second swash plate (365) is within the second positive angular range (370) higher pressure can be provided to the third pump port (378) relative to the fourth pump port (379); 374), a higher pressure may be provided to the fourth pump port (379) relative to the third pump port (378) by rotating the drive shaft (318) when in the first providing higher pressure to the second pump port (349) relative to the first pump port (348) when the swash plate (335) is within the first positive angular range (340); , an external force applied to the first hydraulic actuator (390) can apply an assist torque to the drive shaft (318); An external force applied to the first hydraulic actuator (390) that provides a higher pressure to the first pump port (348) relative to the second pump port (349) when in the drive A supplemental torque may be applied to the shaft (318).

A higher pressure is applied to the fourth pump port (379) relative to the third pump port (378) when the second swash plate (365) is within the second positive angular range (374). an external force (F3) applied to the second hydraulic actuator (400), which provides to the drive shaft (318), can apply an assist torque to the drive shaft (318); to a second hydraulic actuator (400) that provides a higher pressure to the third pump port (378) relative to the fourth pump port (379) when within the angular range (374) of An applied external force (F4) can apply an assist torque to the drive shaft (318).

An electrohydraulic pump system may have a battery (21) that supplies current to an electric motor (16) such that the motor (16) selectively supplies current to the battery (21) in regeneration mode. and in regeneration mode, the external force (F1) applied to the first hydraulic actuator (390) is such that the first swash plate (335) is within the first positive angular range (340) Sometimes providing a higher pressure to the second pump port (349) relative to the first pump port (348) or an external force (F2) applied to the first hydraulic actuator (390) but a higher pressure to the first pump port (348) relative to the second pump port (349) when the first swash plate (335) is in the first negative angular range (344). ); the external force (F3) applied to the second hydraulic actuator (400) provides a third Either a higher pressure is provided to the fourth pump port (379) relative to the second pump port (378), or an external force (F4) applied to the second hydraulic actuator (400) causes the second provides higher pressure to the third pump port (378) relative to the fourth pump port (379) when the swash plate (365) is in the second negative angular range (374). .

The electro-hydraulic pump system is a third hydraulic piston pump centered on the third port plate and the third block axis by rotation of the drive shaft. Coaxial third swash plate axis and third block axis with a plurality of pistons in a third cylinder block adapted to rotate with respect to the third port plate as a third a third swash plate oriented about a third swash plate axis adapted to move angularly with respect to the neutral position of the third swash plate is adapted to angularly move within a third positive angular range between a third neutral position and a third positive angular position, and the third swash plate axis is adapted to move the third Offset from the third block axis at a third maximum cam angle in a third positive angular direction relative to the neutral position of 3, the third swash plate is positioned between the third neutral position and the third wherein the third swash plate axis is adapted to angularly move within a third negative angular range between the negative angular position of and the third swash plate axis relative to the third neutral position offset from the third block axis at a third negative maximum cam angle in a third negative angular direction opposite to the positive angular direction of the third port plate; , and rotation of the drive shaft when the third swash plate is within the third positive angular range produces a higher pressure in the fifth pump relative to the sixth pump port. A higher pressure is applied to the sixth pump port relative to the fifth pump port by rotation of the drive shaft when the third swash plate is within the third negative angular range. a third hydraulic piston pump provided to the port; a third hydraulic actuator having a fifth actuation port hydraulically connected to a fifth pump port of the third piston pump; a third hydraulic actuator having a sixth actuation port hydraulically connected to a sixth pump port of the third piston pump; to a third hydraulic actuator that provides a higher pressure to the sixth pump port relative to the fifth pump port when the third swash plate is within the third positive angular range; An applied external force applies an assist torque to the drive shaft; a higher pressure to the fifth pump port relative to the sixth pump port when the third swash plate is within the third negative angular range. An external force applied to the third hydraulic actuator, provided to the port, applies an assist torque to the drive shaft. A shaft has a first portion connected to the first cylinder block, a second portion connected to the second cylinder block, and a third portion connected to the third cylinder block. be able to.

An electrohydraulic pump system selectively actuates the first swash plate (335) within a first positive angular range (340) between a first neutral position and a first positive angular position. and within a first negative angular range (344) between a first neutral position and a first negative angular position. There may be a first hydraulic swash plate actuator (354) connected to the first swash plate (335) configured to move to the . An electrohydraulic pump system selectively moves the second swash plate (365) within a second positive angular range (370) between a second neutral position and a second positive angular position. and within a second negative angular range (374) between a second neutral position and a second negative angular position. There may be a second hydraulic swash plate actuator (384) connected to the second swash plate (365) configured to move to the second swash plate (365).

A first fluid control journal may comprise a first central control journal (31); a ring (35); a first neutral position between the first displacement axis (38) and the first block axis (34); the first streak ring (35) may be adapted to move radially with respect to the first neutral position; the first displacement axis (38) and A first positive maximum displacement position between the first block axis (34) is a first positive maximum eccentric distance ( 42) can include a first positive eccentric position offsetting the first displacement axis (38) from the first block axis (34); the first positive displacement range includes a first neutral position; and a first positive eccentricity position; between the first displacement axis (38) and the first block axis (34); A first negative maximum displacement position moves the first displacement axis (38) at a first negative maximum eccentric distance (46) in a first negative direction (45) relative to the first neutral position. may include a first negative eccentric position offset from one block axis (34); a first negative displacement range is between a first neutral position and a first negative eccentric position; A first range of negative eccentricity (44) may be included; a second A higher pressure can be provided to the first pump port (48) relative to the pump port (49) of; when the first stroke ring is within the first negative eccentric range (44) Rotation of the drive shaft may provide a higher pressure to the second pump port (49) relative to the first pump port (48); (361); a second displacement drive may have a first swash plate (365) oriented about a second displacement axis (368); A second neutral position between the displacement axis (368) and the second block axis (364) includes a position where the second displacement axis (368) and the second block axis (364) are coaxial. a first swash plate (365) may be adapted to move angularly with respect to a second neutral position; a second displacement axis (368) and a second block axis ( 364) is a second displacement at a first positive maximum cam angle (372) in a first positive angular direction relative to a second neutral position. A second positive displacement range may include a first positive angular position offsetting the axis (368) from the second block axis (364); a first positive angular range (370) between the second displacement axis (368) and the second block axis (364); The displacement position aligns the second displacement axis (368) with the second block axis (364) at a first negative maximum cam angle (376) in a first negative angular direction relative to the second neutral position. a first negative angular position offset from; a second negative displacement range between the second neutral position and the first negative angular position; (374); rotation of the drive shaft when the first swash plate (365) is within the first positive angular range (370) to open the fourth pump port (379); higher pressure can be provided to the third pump port (378) relative to; the drive shaft rotates when the second swash plate (365) is within the first negative angular range (374) higher pressure can be provided to the fourth pump port (379) relative to the third pump port (378) by doing; External force applied to first hydraulic actuator (90) providing higher pressure to second pump port (49) relative to first pump port (48) when in (40) can apply an assist torque to the drive shaft; a higher pressure relative to the second pump port (49) when the first stroke ring is within the first range of negative eccentricity (44). to the first pump port (48), an external force applied to the first hydraulic actuator (90) can apply an assist torque to the drive shaft.

A higher pressure is applied to the fourth pump port (379) relative to the third pump port (378) when the first swash plate (365) is within the first positive angular range (370). An external force applied to the second hydraulic actuator (400) can apply an assist torque to the drive shaft, providing to the first negative angular range (374) the first swash plate (365) An external force applied to the second hydraulic actuator (400) that provides a higher pressure to the third pump port (378) relative to the fourth pump port (379) when in the drive An auxiliary torque can be applied to the shaft.

1 is a schematic diagram of a first radial embodiment of an assist torque electrohydraulic piston pump system; FIG. Figure 28 is a transverse cross-sectional view of the radial piston pump shown in Figures 1 and 27; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a first drive-drive configuration; FIG. Figure 4 is a transverse cross-sectional view of the first radial piston pump shown in Figure 3; Figure 4 is a transverse cross-sectional view of the second radial piston pump shown in Figure 3; 4B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in FIG. 4A; FIG. Figure 4D is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 4B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a second drive-drive configuration; FIG. Figure 7 is a transverse cross-sectional view of the first radial piston pump shown in Figure 6; Figure 7 is a transverse cross-sectional view of the second radial piston pump shown in Figure 6; 7B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in FIG. 7A; FIG. Figure 7C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 7B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a first regenerative-drive configuration; FIG. Figure 10 is a transverse cross-sectional view of the first radial piston pump shown in Figure 9; Figure 10 is a transverse cross-sectional view of the second radial piston pump shown in Figure 9; 10B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in FIG. 10A; FIG. Figure 1OB is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 1OB; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a second regenerative-drive configuration; FIG. Figure 13 is a transverse cross-sectional view of the first radial piston pump shown in Figure 12; Figure 13 is a transverse cross-sectional view of the second radial piston pump shown in Figure 12; 13B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in FIG. 13A; FIG. Figure 13C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 13B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a first drive-regenerate configuration; FIG. Figure 16 is a transverse cross-sectional view of the first radial piston pump shown in Figure 15; Figure 16 is a transverse cross-sectional view of the second radial piston pump shown in Figure 15; Figure 16B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 16A; Figure 16C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 16B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a second drive-regenerate configuration; FIG. Figure 19 is a transverse cross-sectional view of the first radial piston pump shown in Figure 18; Figure 19 is a transverse cross-sectional view of the second radial piston pump shown in Figure 18; Figure 19B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 19A; Figure 19C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 19B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a first regenerate-regenerate configuration; FIG. Figure 22 is a transverse cross-sectional view of the first radial piston pump shown in Figure 21; Figure 22 is a transverse cross-sectional view of the second radial piston pump shown in Figure 21; Figure 22B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 22A; Figure 22C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 22B; 2 is a partial longitudinal section and partial schematic view of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 in a second regenerate-regenerate configuration; FIG. Figure 25 is a transverse cross-sectional view of the first radial piston pump shown in Figure 24; Figure 25 is a transverse cross-sectional view of the second radial piston pump shown in Figure 24; Figure 25B is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 25A; Figure 25C is a schematic diagram showing the resulting port pressure profile for eccentric conditions of the radial piston pump shown in Figure 25B; 2 is a schematic diagram of a second embodiment of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 showing three radial piston pumps and hydraulic actuators in the system; FIG. Figure 28 is a schematic diagram showing the assist torque electrohydraulic radial piston pump system shown in Figure 27 employed on an electric vehicle; Figure 28 is a schematic diagram showing the assist torque electrohydraulic radial piston pump system shown in Figure 27 employed on an electric vehicle; 2 is a schematic diagram of a third embodiment of the assist torque electrohydraulic radial piston pump system shown in FIG. 1 showing non-uniform piston areas and a single actuation rod configuration; FIG. FIG. 4 is a schematic diagram of a fourth axial embodiment of an assist torque electrohydraulic piston pump system; Figure 32 is a cross-sectional view of the first axial piston pump shown in Figure 31; Figure 32 is a cross-sectional view of the second axial piston pump shown in Figure 31;

First, like reference numerals are intended to identify the same structural element, portion, or surface consistently throughout the multiple figures, and thus the element, portion, or surface may be further described or illustrated throughout the specification. It should be clearly understood that this Detailed Description of the Specification is an essential part. Unless otherwise stated, the drawings are intended to be read in conjunction with the specification (e.g., cross-hatching, arrangement of parts, proportions, extents, etc.) and are considered part of the entire written description of the invention. be The terms "horizontal," "vertical," "left," "right," "above," and "below," as used in the following description, as well as adjective and adverbial derivatives thereof (e.g., "Horizontal," "rightward," "upward," etc.) simply indicate the orientation of the structures shown as if that particular figure were facing the reader. Similarly, the terms "inwardly" and "outwardly" generally refer to the orientation of a surface relative to its longitudinal or rotational axis, as appropriate.

Referring now to the drawings, and more particularly to FIG. 1 of the drawings, the present invention generally provides an assist torque electrohydraulic piston pump system, a first embodiment of which is indicated at 15. . As shown in FIG. 1, system 15 is adapted to actuate at least two objects, generally power supply 21, motor controller 22, variable speed electric motor 16, rotating about axis 20 by motor 16. A driven shaft 18, a first radial piston pump 30 mechanically connected to the shaft 18, a first hydraulic actuator 90 hydraulically connected to the first radial piston pump 30, a shaft 18 and a second hydraulic actuator 100 hydraulically connected to the second radial piston pump 60 .

In this embodiment, the motor 16 is a current fed brushless DC variable speed servomotor. A motor 16 has an inner rotor with permanent magnets, a fixed non-rotating stator with coil windings. A magnetic field is induced when a current is properly applied through the coils of the stator. The magnetic field interaction between the stator and rotor produces torque that can rotate the output shaft 18 . There are no mechanical brushes to commutate the stator field in this embodiment of the motor. In this embodiment, motor 16 rotates shaft 18 about axis 20 in one direction only. Thus, motor 16 selectively applies torque to shaft 18 in only one direction about axis 20 at variable speeds. Other motors may be used as an alternative. For example, variable speed stepper motors, brush motors, or induction motors may be used.

A motor controller 22 has drive electronics that generate and commutate a stator field to vary the speed of the motor 16 based on resolver angular position feedback. Controller 22 receives drive commands and feedback from sensors in system 15 and controls motor 16 accordingly. For example, pressure and position transducers within system 15 may be fed back to motor controller 22 .

In this embodiment, the power source 21 comprises a battery and has a regenerative power circuit for utilizing the regenerative mode described below, in which the motor 16 operates as a generator in the power generating mode. , and in power generation mode, external regenerative forces F1, F2, F3, and/or F4, such as gravitational loads on hydraulic actuators 90 and 100, provide threshold actuation of pumps 30 and 60. The pressure difference and the driving torque of the motor 16 are exceeded.

As shown in FIGS. 1-8B, radial piston pump 30 is generally adapted to rotate relative to central control journal 31 and drive shaft 18 about block axis 34 . a plurality of pistons 32 in a cylinder block 33, a stroke ring 35 oriented about a stroke axis 38 adapted to move radially with respect to a neutral or central position N1; , and in the neutral or central position N1, the stroke axis 38 and block axis 34 are coaxial, and the stroke ring 35 and cylinder block 33 are concentric. Stroke ring 35 does not rotate with cylinder block 33 rotation. As shown, hydraulic ring actuator 54 strokes the ring from center position N1 to a position within positive eccentricity range 40 between center position N1 and the positive eccentricity position shown in FIG. 35 linearly or radially, the positive eccentric position offsets the stroke axis 38 from the block axis 34 by a positive maximum eccentric distance 42 in the positive direction 41 with respect to the central position N1. . Hydraulic ring actuator 54 also linearly actuates stroke ring 35 from central position N1 to a position within negative eccentricity range 44 between central position N1 and the negative eccentricity position shown in FIG. 8A. or controlled to move radially so that, in the negative eccentric position, the stroke axis 38 coincides with the block axis 34 with the maximum negative eccentric distance 46 in the negative direction 45 being opposite in the positive direction 41 with respect to the center position N1. offset from

As shown, drive torque from motor 16 is transmitted from shaft 18 to cylinder block 33 by cross-key coupling 18A. Cylinder block 33 rotates on central journal 31 and central journal 31 is shrink-fitted to housing 17 . Pistons 32 are arranged radially within cylinder block 33 and are held in contact with stroke ring 35 by slipper pads 36, where each piston 32 and slipper pad 36 are connected by a ball and socket joint. connected to each other. A slipper pad 36 is retained within the stroke ring 35 by overlapping retainer rings and is pressed against the stroke ring 35 during operation by centrifugal force and oil pressure. Rotation of cylinder block 33 by shaft 18 causes piston 32 to perform a radial stroke motion due to the eccentricity of stroke ring 35 .

Pressure flow from and suction flow into the cylinder chamber are controlled by control journal 31 . Control journal 31 has pump port 48 and pump port 49 . A higher pressure 51 is provided to pump port 48 relative to pump port 49 by rotation of drive shaft 18 (19) when stroke ring 35 is within positive eccentricity range 40 . Alternatively, higher pressure 51 is provided to pump port 49 relative to pump port 48 by rotation of drive shaft 18 when stroke ring 35 is within negative eccentricity range 44 . Thus, in the positive eccentricity range 40, the normal drive pressure difference is P48/P49, which is positive under normal drive conditions (P48/P49>0), and in the negative eccentricity range 44, the normal drive pressure difference is is P49/P48, which is positive under normal driving conditions (P49/P48>0). In this embodiment, the piston stroke "h" is equal to twice the stroke ring 35 eccentric distance "e".

A hydraulic ring actuator 54 is connected to the stroke ring 35 and within a positive eccentric range 40 between the central position N1 and the positive eccentric position shown in FIG. It selectively moves the stroke ring 35 both within a negative eccentric range 44 between the negative eccentric positions. Hydraulic servo valve 54 thus varies the radial eccentric distance of stroke ring 35 . In this embodiment, the normal flow direction, either from port 48 or from port 49, is determined by the direction of the eccentric distance from the neutral center position, with positive eccentric distance 40 providing flow out of port 48. , negative eccentric distance 44 provides flow out of port 49 . Thus, in this embodiment, motor 16 rotates shaft 18 about axis 20 in only one direction and the direction of flow is not determined by the direction of rotation of shaft 18 .

As shown in FIG. 2, hydraulic ring control actuator 54 has hydraulic control pistons 55 and 56 in opposite alignment on axis 54A that vary the eccentric distance of stroke ring 35. As shown in FIG. The effective areas of pistons 55 and 56 are different, with the effective area of piston 56 being greater than the effective area of piston 55 . Hydraulic pressure is constantly applied to the small area control piston 55 to press the stroke ring 35 against the large area control piston 56 . Equal pressure to maintain the stroke ring 35 in the neutral center position, Higher pressure to move the stroke ring 35 toward the maximum positive eccentricity distance 42 into the positive eccentricity range 40, or Large area control piston 56 is selectively pressurized to move stroke ring 35 into negative eccentricity range 44 toward maximum negative eccentricity 46 with less pressure. Hydraulic ring actuator 54 thus controls the position of stroke ring 35 and, in turn, the flow rate, flow direction, and system pressure.

As shown in FIGS. 1, 3 and 6, hydraulic actuator assembly 90 has a piston 95 slidably disposed within a cylindrical housing 98 oriented about axis 99 . In this embodiment, a rod 96 is mounted on one side of piston 95 for movement therewith, extends to the right, and sealingly passes through right end wall 98A of housing 98. As shown in FIG. A rod 97 is mounted on the other side of piston 95 for movement therewith and extends leftward and sealingly through left end wall 98B of housing 98 . A piston 95 is slidably disposed within cylinder 98 and sealingly separates left chamber 91 from right chamber 92 . In this embodiment, the left-facing annular vertical end face of piston 95 faces toward the interior of left-hand chamber 91 and the right-facing annular vertical end face of piston 95 faces toward the interior of right-hand chamber 92, providing uniform Creates a piston area configuration. Left chamber 91 has fluid port 93 and right chamber 92 has fluid port 94 . Hydraulic actuator 90 thus has chamber 91 , chamber 92 and piston 95 separating first chamber 91 and second chamber 92 . A hydraulic actuator may have a position sensor configured to sense the position of the piston 95 . Although actuator 90 is shown as a linear hydraulic actuator in this embodiment, a rotary hydraulic actuator that provides a rotary output may alternatively be used.

As shown in FIG. 1, port 48 of pump 30 is hydraulically connected directly to left chamber 93 via fluid line 52 and the opposite side or port 49 of pump 30 is connected via fluid line 53 to the right side. It is hydraulically connected directly to chamber 93 . By using such a direct hydraulic connection 52 , no one-way check or proportional valve is provided in line 52 between pump port 48 and actuator chamber port 93 . By using such a direct hydraulic connection 53 , no one-way check or proportional valve is provided in line 53 between pump port 49 and actuator chamber port 94 .

Piston 95 will move to the right when motor 16 is rotated and pump 30 is within positive eccentricity range 40, thereby pressurizing port 48 with respect to port 49 and from port 48 to conduit 52. Advances fluid through chamber 91 and draws fluid from chamber 92 through port 94, conduit 53, and port 49, thereby creating a pressure differential over piston 55 which causes rod 96 to move to the right. stretched to When the motor 16 is rotated and the pump 30 is within the negative eccentricity range 44, the piston 95 will move to the left, thereby pressurizing port 49 relative to port 48 and from port 49 to conduit 53. Advances fluid through chamber 92 and draws fluid from chamber 91 through port 93, conduit 52, and port 48, thereby creating a pressure differential over piston 55 which causes rod 97 to move leftward. stretched to Thus, in normal drive mode, rotation of the drive shaft 18 when the stroke ring 35 is within the positive eccentricity range 40 provides a higher pressure 51 to the pump port 48 relative to the pump port 49 . , a higher pressure 51 is provided to pump port 49 relative to pump port 48 by rotation of shaft 18 when stroke ring 35 is within negative eccentricity range 44 .

As shown in FIG. 3, central control journal 31 has a cylindrical central bore oriented on central axis 20 configured to receive through shaft 23 of drive shaft 18 . Through shaft 23 of drive shaft 18 extends through and rotates through this central bore in central journal 31 . Accordingly, the through shaft 23 rotates with the rotation of the shaft 18 .

Radial piston pump 60 is constructed and functions in substantially the same manner as radial piston pump 30, as shown in FIGS. 1-8B. A radial piston pump 60 generally includes a central control journal 61, a plurality of pistons in a cylinder block 63 adapted to rotate relative to a control journal 611 about a block axis 64 by rotation of the drive shaft 18. 62 and a stroke ring 65 oriented about a stroke axis 68 adapted to move radially with respect to the neutral or central position N2, in which the , the stroke axis 68 and the block axis 64 are coaxial, and the stroke ring 65 and the cylinder block 63 are concentric. Stroke ring 65 does not rotate with cylinder block 63 rotation. As shown, hydraulic ring actuator 84 strokes the ring from center position N2 to a position within positive eccentricity range 70 between center position N2 and the positive eccentricity position shown in FIG. 65 linearly or radially, the positive eccentric position offsets the stroke axis 68 from the block axis 64 by a positive maximum eccentric distance 72 in the positive direction 71 with respect to the central position N2. . Hydraulic ring actuator 84 also linearly actuates stroke ring 65 from center position N2 to a position within negative eccentricity range 74 between center position N2 and the negative eccentricity position shown in FIG. 8B. or controlled to move radially so that, in the negative eccentric position, the stroke axis 68 is aligned with the block axis 64 with the maximum negative eccentric distance 76 in the negative direction 75 opposite the positive direction 71 with respect to the central position N2. offset from

As shown, drive torque from motor 16 is transmitted to cylinder block 63 via through shaft 23 of drive shaft 18 and by cross key coupling 18B. Cylinder block 63 rotates on central journal 61 and central journal 61 is shrink-fitted to housing 17 . Pistons 62 are arranged radially within cylinder block 63 and are held in contact with stroke ring 65 by slipper pads 66, where each piston 62 and slipper pad 66 are connected by a ball and socket joint. connected to each other. A slipper pad 66 is retained within the stroke ring 65 by overlapping retainer rings and is pressed against the stroke ring 65 during operation by centrifugal force and oil pressure. Rotation of cylinder block 63 by shaft 23 of drive shaft 18 causes piston 62 to perform radial stroke motion due to the eccentric distance of stroke ring 65 .

Pressure flow from and suction flow into the cylinder chamber are controlled by control journal 61 . Control journal 61 has pump port 78 and pump port 79 . A higher pressure 71 is provided to pump port 78 relative to pump port 79 by rotation of drive shaft 18 (19) when stroke ring 75 is within positive eccentricity range 70 . Alternatively, higher pressure 71 is provided to pump port 79 relative to pump port 78 by rotation of drive shaft 18 when stroke ring 65 is within negative eccentricity range 74 . Thus, in the positive eccentricity range 70, the normal drive pressure difference is P78/P79, which is positive under normal drive conditions (P78/P79>0), and in the negative eccentricity range 74, the normal drive pressure difference is is P79/78, which is positive under normal driving conditions (P79/P78>0). In this embodiment, the piston stroke "h" is equal to twice the stroke ring 65 eccentric distance "e".

A hydraulic ring actuator 84 is connected to the stroke ring 65 and within a positive eccentric range 70 between the central position N2 and the positive eccentric positions shown in FIG. 5B and between the first central position N2 and FIG. Selectively moves the stroke ring 65 both within a negative eccentric range 74 between the first negative eccentric position shown in . Hydraulic servo valve 84 thus varies the radial eccentric distance of stroke ring 65 . In this embodiment, the normal flow direction, either from port 78 or from port 79, is determined by the direction of the eccentric distance from the neutral center position, with positive eccentric distance 70 providing flow out of port 78. , negative eccentric distance 74 provides flow out of port 79 .

As shown in FIG. 2, hydraulic ring control actuator 84 has hydraulic control pistons 85 and 86 in opposite alignment on axis 84A that vary the eccentric distance of stroke ring 65. As shown in FIG. The effective areas of pistons 85 and 86 are different, with the effective area of piston 86 being greater than the effective area of piston 85 . Hydraulic pressure is constantly applied to the small area control piston 85 to press the stroke ring 65 against the large area control piston 86 . To maintain the stroke ring 65 in the neutral center position at equal pressure, to move the stroke ring 65 into the positive eccentric range 70 towards the maximum positive eccentric distance 72 at higher pressure, or more Large area control piston 86 is selectively pressurized to move stroke ring 65 into negative eccentricity range 74 toward maximum negative eccentricity 76 with less pressure. Hydraulic ring actuator 84 thus controls the position of stroke ring 75 and, in turn, the flow rate, flow direction, and system pressure.

As shown in FIGS. 1, 3 and 6, hydraulic actuator assembly 100 has piston 105 slidably disposed within cylindrical housing 108 oriented about axis 109 . In this embodiment, a rod 106 is mounted on one side of piston 105 for movement therewith, extends to the right, and sealingly passes through right end wall 108A of housing 108. As shown in FIG. A rod 107 is mounted on the other side of the piston 105 for movement therewith and extends leftward and sealingly through the left end wall 108B of the housing 108 . A piston 105 is slidably disposed within cylinder 108 and sealingly separates left chamber 101 from right chamber 102 . In this embodiment, the left-facing annular vertical end face of piston 105 faces toward the interior of left-hand chamber 101 and the right-facing annular vertical end face of piston 105 faces toward the interior of right-hand chamber 102, resulting in a uniform Creates a piston area configuration. Left chamber 101 has fluid port 103 and right chamber 102 has fluid port 104 . Thus, hydraulic actuator 100 has chamber 101 , chamber 102 and piston 105 separating first chamber 101 and second chamber 102 . A hydraulic actuator may have a position sensor configured to sense the position of the piston 105 . Although actuator 100 is shown as a linear hydraulic actuator in this embodiment, a rotary hydraulic actuator that provides a rotary output may alternatively be used.

As shown in FIG. 1, port 78 of pump 60 is directly hydraulically connected to left chamber 101 via fluid line 82 and the opposite side or port 79 of pump 60 is connected via fluid line 83 to the right side. It is hydraulically connected directly to chamber 102 . By using such a direct hydraulic connection 82, no one-way check or proportional valve is provided in line 82 between pump port 78 and actuator chamber port 103. FIG. By using such a direct hydraulic connection 83, no one-way check or proportional valve is provided in line 83 between pump port 79 and actuator chamber port 104. FIG.

Piston 105 will move to the right when motor 16 is rotated and pump 60 is within positive eccentricity range 70, thereby pressurizing port 78 relative to port 79 and diverting from port 78 to conduit 82. Advances fluid through chamber 101 and draws fluid from chamber 102 through port 104, conduit 83, and port 79, thereby creating a differential pressure on piston 85 which forces rod 106 to the right. stretched to When the motor 16 is rotated and the pump 60 is within the negative eccentricity range 74, the piston 105 will move to the left, thereby pressurizing port 79 relative to port 78 and diverting from port 79 to conduit 83. Advances fluid through chamber 102 and draws fluid from chamber 101 through port 103, conduit 82, and port 78, thereby creating a pressure differential over piston 85 which forces rod 107 to the left. stretched to Thus, in normal drive mode, rotation of drive shaft 18 when stroke ring 65 is within positive eccentricity range 70 provides higher pressure 81 to pump port 78 relative to pump port 79 . , higher pressure 81 is provided to pump port 79 relative to pump port 78 by rotation of drive shaft 18 when stroke ring 65 is within negative eccentricity range 74 .

3-8B show assist torque electrohydraulic rotary pump system 15 in different exemplary normal drive modes. 3-5B show a normal drive mode in which the desired drive direction D1 of actuator 90 is downward and the desired drive direction D3 of actuator 100 is downward. In this configuration, ring actuator 54 is commanded to stroke ring 35 into positive eccentricity range 40 . As shown, rotation of shaft 18 provides a higher pressure 51 to pump port 48 and thus chamber 91 of actuator 90 relative to pump port 49 and chamber 92, causing actuator rod 96 to move in direction D1. drive. In this configuration, ring actuator 84 is commanded to stroke ring 65 into positive eccentricity range 70 . As shown, rotation of shaft 18 provides a higher pressure 81 to pump port 78 and thus chamber 101 of actuator 100 relative to pump port 79 and chamber 102, causing actuator rod 106 to move in direction D3. drive.

Figures 6-8B show a normal drive mode in which the desired drive direction D2 of actuator 90 is upward and the desired drive direction D4 of actuator 100 is upward. In this configuration, ring actuator 54 is commanded to stroke ring 35 into negative eccentricity range 44 . As shown, rotation of shaft 18 provides a higher pressure 51 to pump port 49 and thus chamber 92 of actuator 90 relative to pump port 49 and chamber 91, causing actuator rod 97 to move in direction D2. drive. In this configuration, ring actuator 84 is commanded to stroke ring 65 into negative eccentricity range 74 . As shown, rotation of shaft 18 provides a higher pressure 81 relative to pump port 78 and chamber 101 to pump port 79 and thus chamber 102 of actuator 100, causing actuator rod 107 to move in direction D4. drive. Other combinations of actuator directions can also be commanded, such as D1/D4 or D2/D3, with stroke ring eccentric ranges of 40/74 or 44/70 respectively.

9-26B show assist torque electrohydraulic rotary pump system 15 in different exemplary regeneration modes. 9-20B show that either one of the pump/actuator combinations 30/90 or 60/100 provides assist torque applied through the shaft 18 to the other of the pump/actuator combinations 30/90 or 60/100. , indicating a mechanical torque-assisted regeneration mode. 21-26B illustrate that pump/actuator combinations 30/90 and 60/100 provide net regenerative torque to shaft 18 that is used by motor 16 and drive electronics 22 to charge battery 21; Indicates power regeneration mode.

Figures 9-11B show a first exemplary mechanical play mode. As shown, the commanded drive direction of actuator 90 is D1, where the commanded stroke ring eccentricity range 40 is obtained, and the commanded drive direction of actuator 100 is D3, where , the commanded stroke ring eccentricity range 70 is obtained. However, as shown, an external force is applied to actuator 90 having a force component F1 in direction D1. This results in a higher pressure in chamber 92 relative to chamber 91 and a higher pressure at port 49 relative to port 48 due to direct hydraulic connection 53 . This negative pressure differential P48/P49 provides additional torque to the cylinder block 33, given the commanded positive pressure differential, which additional torque is applied to the shaft connection 18a, the through shaft 23, and through shaft connection 18B to cylinder block 63 of pump 60 to assist in driving actuator 100. Therefore, when an external force F1 is applied to the hydraulic actuator 90 that provides a higher pressure 51 to the pump port 49 relative to the pump port 48 when the stroke ring 35 is within the positive eccentricity range 40 (P48/ P49<0), an assist torque is applied to the drive shaft 18; As a result, the power required by motor 16 is reduced.

12-14B illustrate a second exemplary mechanical play mode. As shown, the commanded drive direction for actuator 90 is D2, where the commanded stroke ring eccentricity range 44 is obtained, and the commanded drive direction for actuator 100 is D4, where , the commanded stroke ring eccentricity range 74 is obtained. However, as shown, an external force is applied to actuator 90 having a force component F2 in direction D2. This results in higher pressure in chamber 91 relative to chamber 92 and direct hydraulic connection 52 provides higher pressure at port 48 relative to port 49 . This negative pressure differential (P49/P48) also provides additional torque to the cylinder block 33, given the commanded positive pressure differential, which additional torque is applied to the shaft connection device. 18A, through shaft 23, and shaft connection 18B to cylinder block 63 of pump 60 to assist in driving actuator 100. Therefore, when an external force F2 is applied to the hydraulic actuator 90 that provides a higher pressure 51 to the pump port 48 relative to the pump port 49 when the stroke ring 35 is within the negative eccentricity range 44 (P49/ P48<0), an assist torque is applied to the drive shaft 18; As a result, the power required by motor 16 is reduced.

Figures 15-17B show a third exemplary mechanical play mode. As shown, the commanded drive direction of actuator 90 is D1, where the commanded stroke ring eccentricity range 40 is obtained, and the commanded drive direction of actuator 100 is D3, where , the commanded stroke ring eccentricity range 70 is obtained. However, as shown, an external force is applied to actuator 100 having a force component F3 in direction D3. This results in higher pressure in chamber 102 relative to chamber 101 and direct hydraulic connection 83 provides higher pressure at port 79 relative to port 78 . This negative pressure differential provides additional torque to the cylinder block 63, given the commanded positive pressure differential, which is applied to the shaft connection 18B, the through shaft 23, and the It is transmitted back through shaft connection 18 A to cylinder block 33 of pump 30 to help drive actuator 90 . Therefore, when an external force F3 is applied to the hydraulic actuator 100 that provides a higher pressure 81 to the pump port 79 relative to the pump port 78 when the stroke ring 65 is within the positive eccentricity range 70 (P78/ P79<0), an assist torque is applied to the drive shaft 18; As a result, the power required by motor 16 is reduced.

Figures 18-20B illustrate a fourth exemplary mechanical play mode. As shown, the commanded drive direction for actuator 90 is D2, where the commanded stroke ring eccentricity range 44 is obtained, and the commanded drive direction for actuator 100 is D4, where , the commanded stroke ring eccentricity range 74 is obtained. However, as shown, an external force is applied to actuator 100 having a force component F4 in direction D4. This provides higher pressure in chamber 101 relative to chamber 102 and direct hydraulic connection 82 provides higher pressure at port 78 relative to port 79 . This negative pressure differential also provides additional torque to cylinder block 63, given the commanded positive pressure differential, which additional torque is applied to shaft connection 18B, through shaft 23 , and shaft connection 18 A to cylinder block 33 of pump 30 to assist in driving actuator 90 . Therefore, when an external force F4 is applied to the hydraulic actuator 100 that provides a higher pressure 81 to the pump port 78 relative to the pump port 79 when the stroke ring 65 is within the negative eccentricity range 74 (P79/ P78<0), an assist torque is applied to the drive shaft 18; As a result, the power required by motor 16 is reduced.

This allows actuator directions such as when D1/D4 or D2/D3 commands are issued and the subject pressure differential is negative, with stroke ring eccentric ranges of 40/74 or 44/70 respectively. Other combinations of are also applicable. Thus, if the commanded pump port pressure differential is positive and the resulting operational pump port pressure differential is negative for the eccentric distance of interest, regeneration mode is employed.

21-23B illustrate a first exemplary generator regeneration mode. As shown, the commanded drive direction of actuator 90 is D1, where the commanded stroke ring eccentricity range 40 is obtained, and the commanded drive direction of actuator 100 is D3, where , the commanded stroke ring eccentricity range 70 is obtained. However, as shown, an external force having force component F1 in direction D1 is applied to actuator 90, and an external force having force component F3 in direction D3 is applied to actuator 100. FIG. This results in a higher pressure in chamber 92 relative to chamber 91 and a higher pressure at port 49 relative to port 48 due to direct hydraulic connection 53 . This further provides higher pressure in chamber 102 relative to chamber 101 and direct hydraulic connection 83 provides higher pressure at port 79 relative to port 78 . This total negative pressure differential causes additional torque to cylinder block 33 that is transmitted through shaft connection 18a to shaft 18 and motor 16, given the commanded positive pressure differential. and provides additional torque to cylinder block 63 that is transmitted to shaft 18 and motor 16 via shaft connection 18B and through shaft 23 . The motor 16 acts as a generator and converts this regenerated torque into current which is stored in the battery 21 . External forces F1 and F3 thus provide a higher combined pressure to pump ports 49 and 79 relative to pump ports 48 and 78 when stroke rings 35 and 65 are within positive eccentric ranges 40 and 70, respectively. is applied to hydraulic actuators 90 and 100 (Σ(P48/P49+P78/P79)<0), this torque is used to charge battery 21.

Figures 24-26B illustrate a second exemplary generator regeneration mode. As shown, the commanded drive direction of actuator 90 is D2, where the commanded stroke ring eccentricity range 44 is obtained, and the commanded drive direction of actuator 100 is D4, where , the commanded stroke ring eccentricity range 74 is obtained. However, as shown, an external force having force component F2 in direction D2 is applied to actuator 90, and an external force having force component F4 in direction D4 is applied to actuator 100. FIG. This results in higher pressure in chamber 91 relative to chamber 92 and direct hydraulic connection 52 provides higher pressure at port 48 relative to port 49 . This also provides higher pressure in chamber 101 relative to chamber 102 and direct hydraulic connection 82 provides higher pressure at port 78 relative to port 79 . This total negative pressure differential is the additional torque to cylinder block 33 that is transmitted through shaft connection 18A to shaft 18 and motor 16, given the commanded positive pressure differential. also provides additional torque to cylinder block 63 which is transmitted to shaft 18 and motor 16 via shaft connection 18B and through shaft 23. The motor 16 acts as a generator and converts this regenerated torque into current which is stored in the battery 21 . External forces F2 and F4 thus provide a higher combined pressure to pump ports 48 and 78 relative to pump ports 49 and 79 when stroke rings 35 and 65 are within negative eccentricity ranges 44 and 74, respectively. is applied to the hydraulic actuators 90 and 100 (Σ(P49/P48+P79/P78)<0), this torque is used to charge the battery 21 .

This allows for other actuator directions, such as when a D1/D4 or D2/D3 command is issued and the target pressure differential is negative, with stroke ring eccentric ranges of 40/74 or 44/70 respectively. Also applies in combination. Thus, if the commanded pump port pressure differential is positive and the total resulting operating pump port pressure differential is negative for the eccentric distance of interest, regeneration mode is employed.

A controller 22 controls the appropriate magnitude of the current 16 to the motor. The positions of pistons 95 and 105 are monitored via position transducers and position signals are then fed back to motor controller 22 . Additionally or alternatively, pressure in lines 52, 53, 82, and 83 to and from chambers 91, 92, 101, and 102, respectively, may be measured using pressure transducers. is monitored and a pressure signal is fed back to controller 22 . Variable speed motor 16 and ring actuators 54 and 84 of pumps 30 and 60 vary the flow and pressure acting on pistons 95 and 105, respectively, thereby causing pistons 95 and 105 and thus rods 96, 97, 106 and 107 direction, speed and force. This is accomplished by observing the feedback of the position and/or pressure transducers and then closing the control loop by adjusting the speed of the motor 16 and the eccentric distance of the stroke rings 35 and 65 accordingly. be done.

Referring now to FIG. 27, a second embodiment 115 of an assist torque electrohydraulic pump system is shown. As shown, system 115 is adapted to actuate at least three objects, generally power supply 21, motor controller 22, variable speed electric motor 16, driven by motor 16 to rotate about axis 20. a first radial piston pump 30 mechanically connected to the shaft 18; a first hydraulic actuator 90 hydraulically connected to the first radial piston pump 30; a second radial piston pump 60 mechanically connected; a second hydraulic actuator 100 hydraulically connected to the second radial piston pump 60; 3 radial piston pumps 130 and a third hydraulic actuator 190 hydraulically connected to the third radial piston pump 130 .

a power supply 21, a motor controller 22, a variable speed electric motor 16, a first radial piston pump 30 mechanically connected to the shaft 18, a first hydraulically connected to the first radial piston pump 30; , a second radial piston pump 60 mechanically connected to the shaft 18 , and a second hydraulic actuator 100 hydraulically connected to the second radial piston pump 60 . is configured substantially the same as the fifteenth embodiment. However, in this embodiment, a third pump and hydraulic actuator combination 130/190 is added in series with the pump and hydraulic actuator combinations 30/90 and 60/100.

Radial piston pump 130 is substantially the same as radial piston pump 60 . Thus, referring to FIG. 2, radial piston pump 130 generally includes a central control journal 131 and a cylinder adapted to rotate relative to control journal 131 about block axis 134 by rotation of drive shaft 18. - having a plurality of pistons 132 within a block 133 and a stroke ring 135 oriented about a stroke axis 138 adapted to move radially with respect to a neutral or centered position; , in the neutral or center position, the stroke axis 138 and block axis 134 are coaxial, and the stroke ring 135 and cylinder block 133 are concentric. Stroke ring 135 does not rotate with cylinder block 133 rotation. As shown, the hydraulic ring actuator 154 linearly or radially moves the stroke ring 135 from the center position to a position within a positive eccentric range 140 between the center position and the positive eccentric position. and in the positive eccentric position the stroke axis 138 is offset from the block axis 134 by the maximum positive eccentric distance in the positive direction with respect to the center position. Hydraulic ring actuator 154 further moves stroke ring 135 linearly or radially from the center position to a position within negative eccentricity range 144 between the center position and the negative eccentricity position. and in the negative eccentric position, the stroke axis 138 is offset from the block axis 134 by a maximum negative eccentric distance in the negative direction which is positively opposite to the center position.

In this embodiment, the central control journal 61 of the radial piston pump 60 has a cylindrical central bore oriented on the central axis 20 configured to receive the through shaft 123 of the drive shaft 18 . Through shaft 123 of drive shaft 18 extends through and rotates through this central bore in central journal 61 . Accordingly, the through shaft 123 rotates with the rotation of the shaft 18 .

Drive torque from motor 16 is transmitted from shaft 18 through through shafts 23 and 123 of drive shaft 18 to cylinder block 133 . Cylinder block 133 rotates on central journal 131 and central journal 131 is shrink-fitted to housing 117 . Pistons 132 are arranged radially within cylinder block 133 and are held in contact with stroke ring 135 by slipper pads 136, where each piston 132 and slipper pad 136 are connected by a ball and socket joint. connected to each other. A slipper pad 136 is retained within the stroke ring 135 by overlapping retainer rings and is pressed against the stroke ring 135 during operation by centrifugal force and oil pressure. Rotation of cylinder block 133 by shaft 18 causes piston 132 to perform radial stroke motion due to the eccentric distance of stroke ring 135 .

Pressure flow from and suction flow into the cylinder chamber are controlled by control journal 131 . Control journal 131 has pump port 148 and pump port 149 . Rotation of drive shaft 18 (19) when stroke ring 135 is within positive eccentricity range 140 provides higher pressure to pump port 148 relative to pump port 149 . Alternatively, rotation of drive shaft 18 when stroke ring 135 is within negative eccentricity range 144 provides higher pressure to pump port 149 relative to pump port 148 . Thus, in the positive eccentric range 140, the normal drive pressure difference is P148/P149, which is positive under normal drive conditions (P148/P149>0), and in the negative eccentric range 144, the normal drive pressure difference is is P149/148, which is positive under normal driving conditions (P149/P148>0). In this embodiment, the piston stroke is equal to twice the stroke ring 135 eccentric distance.

A hydraulic ring actuator 154 is connected to the stroke ring 135 to selectively move the stroke ring 135 within both the positive eccentricity range 140 and the negative eccentricity range 144 . Hydraulic servo valve 154 thus varies the radial eccentric distance of stroke ring 135 . In this embodiment, the normal flow direction, either from port 148 or from port 149, is determined by the direction of the eccentric distance from the neutral center position, with positive eccentric distance 140 providing flow out of port 148. , negative eccentric distance 144 provides flow out of port 149 .

As shown in FIG. 2, hydraulic ring control actuator 154 has hydraulic control pistons 155 and 156 in opposite alignment on the same axis that vary the eccentric distance of stroke ring 135 . The effective areas of pistons 155 and 156 are different, with the effective area of piston 156 being greater than the effective area of piston 155 . Hydraulic pressure is constantly applied to the small area control piston 155 to press the stroke ring 135 against the large area control piston 156 . to maintain the stroke ring 135 in the neutral center position at equal pressure, to move the stroke ring 135 toward the maximum positive eccentricity distance at higher pressures to the positive eccentricity range 140, or less Large area control piston 156 is selectively pressurized to move stroke ring 135 into negative eccentricity range 144 toward maximum negative eccentricity with pressure. Hydraulic ring actuator 154 thus controls the position of stroke ring 135 and, in turn, the flow rate, flow direction, and system pressure.

As shown in FIG. 27, hydraulic actuator assembly 190 has a piston 195 slidably disposed within a cylindrical housing 198 oriented about axis 199 . In this embodiment, a rod 196 is mounted on one side of piston 195 for movement therewith, extends to the right, and sealingly passes through the right end wall of housing 198 . A rod 197 is mounted on the other side of piston 195 for movement therewith and extends leftward and sealingly through the left end wall of housing 198 . A piston 195 is slidably disposed within cylinder 198 and sealingly separates left chamber 191 from right chamber 192 . In this embodiment, the left facing annular vertical end face of piston 195 faces the interior of left chamber 191 and the right facing annular vertical end face of piston 195 faces the interior of right chamber 192, resulting in a uniform piston area. creating a configuration. Left chamber 191 has fluid port 193 and right chamber 192 has fluid port 194 . Hydraulic actuator 190 thus has chamber 191 , chamber 192 and piston 195 separating first and second chambers 191 and 192 . A hydraulic actuator can have a position sensor configured to sense the position of the piston 195 . Although actuator 190 is shown as a linear hydraulic actuator in this embodiment, a rotary hydraulic actuator that provides a rotary output may alternatively be used.

As shown in FIG. 27, port 148 of pump 130 is hydraulically connected directly to left chamber 191 via fluid line 152 and the opposite side or port 149 of pump 130 is connected via fluid line 153 to the right side. It is hydraulically connected directly to chamber 192 . By using such a direct hydraulic connection 152 , no one-way check or proportional valve is provided in line 152 between pump port 148 and actuator chamber port 193 . By using such a direct hydraulic connection 153 , no one-way check or proportional valve is provided in line 153 between pump port 149 and actuator chamber port 194 .

Piston 195 will move to the right when motor 16 is rotated such that pump 130 is within positive eccentricity range 140, thereby pressurizing port 148 relative to port 149 and diverting from port 148 to conduit 152. Advances fluid through chamber 191 and draws fluid from chamber 192 through port 194, conduit 153, and port 149, thereby creating a pressure differential over piston 155 which causes rod 196 to move to the right. stretched to When the motor 16 is rotated such that the pump 130 is within the negative eccentricity range 144, the piston 195 will move to the left, thereby pressurizing port 149 relative to port 148 and diverting from port 149 to conduit 153. Advances fluid through chamber 192 and draws fluid from chamber 191 through port 193, conduit 152, and port 148, thereby creating a pressure differential over piston 155 which causes rod 197 to move to the left. stretched to Thus, in normal drive mode, rotation of drive shaft 18 when stroke ring 135 is within positive eccentricity range 140 provides higher pressure to pump port 148 relative to pump port 149 and Rotation of shaft 18 when stroke ring 135 is within negative eccentricity range 144 provides higher pressure to pump port 149 relative to pump port 148 .

As in Example 15, all three actuators 90, 100, and 190 are actuated depending on the eccentric distance of stroke ring centers 38, 68, and 138 relative to block axes 34, 64, and 134, respectively. , can be driven in either direction by rotation of the shaft 18 . Accordingly, various combinations of actuator directions may be commanded, such as, but not limited to, directions D1/D3/D5 having stroke ring eccentric ranges of 40/70/140; Directions D2/D4/D6 with 74/144 respectively; Directions D1/D4/D5 with Stroke Ring Eccentric Ranges of 40/74/140 respectively; Directions D2/D4 with Stroke Ring Eccentric Ranges of 44/74/140 respectively. /D5; and directions D2/D3/D5 with stroke ring eccentric ranges of 44/70/140 respectively. Under normal drive conditions, eccentric ranges 40, 70, and 140 produce positive pressure differentials P48/P49, P78/P79, and P148/P149, and eccentric ranges 44, 74, and 144 are positive. Pressure differentials P49/P48, P79/P78, and P149/P148 are generated.

Similar to the pump/actuator combinations 30/60 and 60/100, an external force applied to actuator 190 having a force component in direction D5 can create a higher pressure in chamber 192 relative to chamber 191. , a direct hydraulic connection 153 allows a higher pressure to be developed at port 149 relative to port 148 . This negative pressure differential P148/P149 provides additional torque to the cylinder block 133, given the positive pressure differential commanded, which additional torque is applied to the through shaft 123 and the shaft connection. 18B to cylinder block 63 of pump 60 to assist in driving actuator 100 . In addition, an external force having a force component in direction D6 applied to actuator 190 can create a higher pressure in chamber 191 with respect to chamber 192 and, by direct hydraulic connection 152, with respect to port 149. A higher pressure can be developed at port 148 as . This negative pressure differential (P149/P148) also provides additional torque to the cylinder block 133, given the positive pressure differential commanded, which additional torque is applied to the through shaft 123 and through shaft connection 18B to cylinder block 63 of pump 60 to assist in driving actuator 100. Thus, when an external force is applied to hydraulic actuator 190 that provides a higher pressure to pump port 149 relative to pump port 148 when stroke ring 135 is within positive eccentricity range 140 (P148/P149< 0), an assist torque is applied to the drive shaft 18; Further, when an external force is applied to hydraulic actuator 190 that provides a higher pressure to pump port 148 relative to pump port 149 when stroke ring 135 is within negative eccentricity range 144 (P149/P148< 0), an assist torque is applied to the drive shaft 18;

As in Example 15, pressure differences P48/P49, P78/P79, and P148/P149 in eccentric ranges 40, 70, and 140, or pressure differences P49/P48, P79/ If any of P78 and P149/P148 are negative, then one or more of the pump/actuator combinations 30/90, 60/100, and 130/190 will reduce the assist torque applied through the shaft 18 to The remainder of the pump/actuator combinations 30/90, 60/100, 130/190 can be provided. Thus, if the commanded pump port pressure differential is positive and the resulting operational pump port pressure differential is negative for the eccentric distance of interest, regeneration mode is employed.

Pump/actuator combinations 30/90, 60/100, and 130/160 also provide net regenerative torque to shaft 18 that is used by motor 16 and drive electronics 22 to charge battery 21; can be done. For example, without limitation, a higher combined pressure relative to pump ports 48, 78, and 148 when stroke rings 35, 75, and 135 are within positive eccentricity ranges 40, 70, and 140, respectively. When an external force providing pump ports 49, 79 and 149 is applied to hydraulic actuators 90, 100 and/or 190 (Σ(P48/P49+P78/P79+P148/P149)<0), this torque causes battery 21 to used for charging. The motor 16 acts as a generator and converts this regenerated torque into current which is stored in the battery 21 . Further, for example, but not by way of limitation, the higher combined When an external force is applied to hydraulic actuators 90, 100 and/or 190 that provides pressure to pump ports 48, 78 and 148 (Σ(P49/P48+P79/P78+P149/P148)<0), this torque is applied to battery 21 is used to charge. Thus, if the commanded pump port pressure differential is positive and the total resulting operating pump port pressure differential is negative for the eccentric distance of interest, regeneration mode is employed.

Similarly, the controller 22 changes the flow and pressure acting on the pistons 95, 105 and 195 respectively, and adjusts the speed of the motor 16 and the eccentric distance of the stroke rings 35, 65 and 135 accordingly. and motor 16 and pump 30 to control the direction, speed and force of pistons 95, 105 and 195 and thus rods 96, 97, 106, 107, 196 and 197. , 60 and 130 control the current to the ring actuators 54 , 84 and 154 .

28 and 29 show the system 115 for operating the tilt cylinders, the lift cylinders, and the accessory implementations cylinders of the skid steer 116. FIG. Direct hydraulic lines extend from the motor and pump assembly housing 117 to the respective hydraulic cylinders, where lines 52 and 53 supply from pump 30 to accessory cylinders 98 and lines 82 and 83 feeds the tilt cylinder 108 of the bucket 119 from the pump 130 and lines 152 and 153 feed the lift cylinder 198 of the bucket 119 from the pump 60 . System 15 may also be employed in a variety of other applications including, but not limited to, applications where diesel engines are replaced by electric systems. For example, without limitation, the system may be employed on excavators, wheel loaders, and other mobile equipment that require multiple actuations.

Referring now to FIG. 30, a third embodiment 215 of an assist torque electrohydraulic pump system is shown. Power supply 21, motor controller 22, variable speed electric motor 16, first radial piston pump 30 mechanically connected to shaft 18, second radial piston pump 60 mechanically connected to shaft 18. , and a third radial piston pump 130 mechanically connected to the shaft 18 are constructed substantially the same as in the 115th embodiment. However, in this embodiment, the dual piston rod, uniform piston area actuators 90, 100, and 190 are replaced by single rod, non-uniform piston area actuators 220, 230, and 240. . Referring to actuator 240 , actuators 220 , 230 and 240 each have a piston 245 slidably disposed within a cylindrical housing 248 oriented about axis 249 . In this embodiment, a single rod 246 is mounted on one side of piston 245 for movement therewith, extends to the right, and sealingly passes through right end wall 248 A of housing 248 . A piston 245 is slidably disposed within cylinder 248 and sealingly separates left chamber 241 from right chamber 242 . In this embodiment, the left-facing circular vertical end surface 245B of piston 245 faces the interior of left-hand chamber 241, and the right-facing annular vertical end surface 245A of piston 245 faces the interior of right-hand chamber 242. It creates a uniform piston area configuration. Thus, substantially the entire left-facing circular vertical end face 245 B of the piston 245 faces the interior of the left-hand chamber 241 . However, due to the addition of rod 246 which passes through chamber 242 and extends to the outside of housing 248, only the right-facing annular vertical end face 245A of piston 245 faces the interior of right-hand chamber 242 on the right. . This creates a non-uniform piston area configuration, where the surface area of face 245B is greater than the surface area of face 245A.

Referring now to FIG. 31, a fourth embodiment 315 of an assist torque electrohydraulic pump system is shown. A power supply 21, a motor controller 22, and a variable speed electric motor 16 are configured substantially the same as in the fifteenth embodiment. Additionally, hydraulic actuator 390 in system 315 is configured substantially the same as actuator 90 in Example 15, and hydraulic actuator 400 in system 315 is configured substantially the same as actuator 100 in Example 15. Configured. However, in this embodiment radial piston pumps 30 and 60 have been replaced by axial piston pumps 330 and 360 .

As shown in FIG. 32, axial piston pump 330 was generally adapted to rotate relative to plate 331 about block axis 334 by rotation of fluid control journal plate 331 and drive shaft 318. A plurality of pistons 332 within a cylinder block 333 and axially positioned adjacent to one end face of the cylinder block 333 and oriented about a swash plate axis 338 in a neutral or central position. a swash plate 335 adapted to move angularly with respect to the swash plate 335, wherein in the neutral or centered position the swash plate axis 338 and the block axis 334 are coaxial; A cam surface is perpendicular to the cylinder block axis 334 . Swash plate 335 does not rotate with cylinder block 333 rotation. The tilt angle or Controlled to adjust the cam angle, the positive angular position angularly offsets the swash plate axis 338 from the block axis 334 at a positive maximum angle 342 in the positive angular direction relative to the center position. Hydraulic plate actuator 354 further tilts swash plate 335 relative to cylinder block 333 from the central position to a position within negative angular range 344 between the central position and the negative angular position. or controlled to adjust the cam angle such that the swash plate axis 338 is aligned with the block axis at the maximum negative angle 346 in the negative angular direction which is opposite to the positive angular direction with respect to the center position. Angularly offset from 334.

Drive torque from motor 16 is transmitted from shaft 318 to cylinder block 333 causing cylinder block 333 to rotate with shaft 318 . Pistons 332 are arranged axially in cylinder block 333 and are held in contact with swash plate 335 by slipper pads 336, where each piston 332 and slipper pad 336 are connected by a ball and socket joint. connected to each other. Rotation of cylinder block 333 by shaft 318 causes piston 332 to perform an axial stroke motion due to the tilt angle of swash plate 335 .

A port plate 331 has pump ports 348 and 349 on both sides of cylinder block 333 to swash plate 335 . Rotation of drive shaft 318 (19) when swash plate 335 is in positive angular range 340 provides higher pressure to pump port 348 relative to pump port 349 . Alternatively, rotation of drive shaft 318 when swash plate 335 is within negative angular range 344 provides a higher pressure to pump port 349 relative to pump port 348 . Thus, in the positive angle range 340 the normal drive pressure difference is P348/P349, which is positive under normal drive conditions (P348/P349>0), and in the negative angle range 344 the normal drive pressure difference is P349/P348, which is positive under normal driving conditions (P349/P348>0).

A hydraulic swash plate actuator 354 is connected to swash plate 335 to selectively move swash plate 335 both within positive angle range 340 and within negative angle range 344 . Hydraulic servo valve 354 thus varies the tilt or cam angle of swash plate 335 . In this embodiment, the normal flow direction, either out of port 448 or out of port 449, is determined by the direction of tilt from the neutral center position, with positive tilt 440 providing flow out of port 448. , negative slope 444 provides flow out of port 449 .

As shown in FIG. 31, hydraulic actuator assembly 390 has a piston 395 slidably disposed within a cylindrical housing 398 oriented about axis 339 . In this embodiment, a rod 396 is mounted on one side of piston 395 for movement therewith, extends to the right, and sealingly passes through the right end wall of housing 398 . A rod 397 is mounted on the other side of piston 395 for movement therewith and extends leftward and sealingly through the left end wall of housing 398 . A piston 395 is slidably disposed within cylinder 398 and sealingly separates left chamber 391 from right chamber 392 . Left chamber 391 has fluid port 393 and right chamber 392 has fluid port 394 . Hydraulic actuator 390 thus has chamber 391 , chamber 392 and piston 395 separating first and second chambers 391 and 392 . A hydraulic actuator can have a position sensor configured to sense the position of the piston 395 .

As shown in FIG. 31, port 348 of pump 330 is hydraulically connected directly to left chamber 391 via fluid line 352 and the opposite side or port 349 of pump 330 is connected via fluid line 353 to the right side. It is hydraulically connected directly to chamber 392 . By using such a direct hydraulic connection 352 , no one-way check or proportional valve is provided in line 352 between pump port 348 and actuator chamber port 393 . By using such a direct hydraulic connection 353 , no one-way check or proportional valve is provided in line 353 between pump port 349 and actuator chamber port 394 .

Piston 395 will move to the right when motor 16 is rotated such that pump 330 is in positive angular range 340, thereby pressurizing port 348 relative to port 349 and diverting from port 348 to conduit 352. Advances fluid through chamber 391 into chamber 391 and draws fluid from chamber 392 through port 394, conduit 353, and port 349, thereby creating a pressure differential over piston 355 which causes rod 396 to move to the right. stretched to When the motor 16 is rotated and the pump 330 is in the negative angle range 344, the piston 395 will move to the left, thereby pressurizing port 349 relative to port 348 and diverting from port 349 to conduit 353. Advances fluid through chamber 392 and draws fluid from chamber 391 through port 393, conduit 352, and port 348, thereby creating a pressure differential over piston 355 which causes rod 397 to move to the left. stretched to Thus, in normal drive mode, rotation of drive shaft 318 when swash plate 335 is in positive angular range 340 provides higher pressure to pump port 348 relative to pump port 349, Rotation of shaft 318 when swash plate 335 is in negative angular range 344 provides higher pressure to pump port 349 relative to pump port 348 .

In this embodiment, through shaft 323 of drive shaft 318 extends through swash plate 335 and rotates with rotation of shaft 318 . Through shaft 323 is connected to swash plate 365 of axial piston pump 360 .

As shown in FIG. 33, axial piston pump 360 was generally adapted to rotate relative to plate 361 about block axis 364 by rotation of fluid control journal plate 361 and drive shaft 318. A plurality of pistons 362 within a cylinder block 363 and axially positioned adjacent one end face of the cylinder block 363 and oriented about a swash plate axis 368 and in a neutral or central position. a swash plate 365 adapted to move angularly with respect to the swash plate 365; A cam surface is perpendicular to the cylinder block axis 364 . Swash plate 365 does not rotate with cylinder block 363 rotation. The tilt angle or Controlled to adjust the cam angle, the positive angular position angularly offsets the swash plate axis 368 from the block axis 364 at a positive maximum angle 372 in the positive angular direction relative to the center position. Hydraulic plate actuator 384 further tilts swash plate 365 relative to cylinder block 363 from the central position to a position within negative angular range 374 between the central position and the negative angular position. or controlled to adjust the cam angle such that the swash plate axis 368 is aligned with the block axis at the maximum negative angle 376 in the negative angular direction which is opposite to the positive angular direction with respect to the center position. Angularly offset from 364.

Drive torque from motor 16 is transmitted from shaft 318 to cylinder block 363 via through shaft 323 causing cylinder block 363 to rotate with shaft 318 . Pistons 362 are arranged axially in cylinder block 363 and are held in contact with swash plate 365 by slipper pads 366, where each piston 362 and slipper pad 366 are connected by a ball and socket joint. connected to each other. Rotation of cylinder block 363 by shaft 318 causes piston 362 to perform an axial stroke motion due to the tilt angle of swash plate 365 .

Port plate 361 has pump ports 378 and 379 on both sides of cylinder block 363 to swash plate 365 . Rotation of drive shaft 318 (19) when swash plate 365 is in positive angular range 370 provides higher pressure to pump port 378 relative to pump port 379 . Alternatively, rotation of drive shaft 318 when swash plate 365 is within negative angular range 374 provides a higher pressure to pump port 379 relative to pump port 378 . Thus, in the positive angle range 370, the normal drive pressure difference is P378/P379, which is positive under normal drive conditions (P378/P379>0), and in the negative angle range 374, the normal drive pressure difference is is P379/P378, which is positive under normal driving conditions (P379/P378>0).

A hydraulic swash plate actuator 384 is connected to swash plate 365 to selectively move swash plate 365 both within positive angle range 370 and within negative angle range 374 . Hydraulic servo valve 384 thus varies the tilt or cam angle of swash plate 365 . In this embodiment, the normal flow direction, either out of port 448 or out of port 449, is determined by the direction of tilt from the neutral center position, with positive tilt 440 providing flow out of port 448. , negative slope 444 provides flow out of port 449 .

As shown in FIG. 31, hydraulic actuator assembly 400 has piston 405 slidably disposed within cylindrical housing 408 oriented about axis 409 . In this embodiment, a rod 406 is mounted on one side of piston 405 for movement therewith, extends to the right, and sealingly passes through the right end wall of housing 408 . A rod 407 is mounted on the other side of piston 405 for movement therewith and extends to the left and sealingly passes through the left end wall of housing 408 . A piston 405 is slidably disposed within cylinder 408 and sealingly separates left chamber 401 from right chamber 402 . Left chamber 401 has fluid port 403 and right chamber 402 has fluid port 404 . Thus, hydraulic actuator 400 has chamber 401 , chamber 402 and piston 405 separating first chamber 401 and second chamber 402 . A hydraulic actuator can have a position sensor configured to sense the position of the piston 405 .

As shown in FIG. 31, port 378 of pump 360 is hydraulically connected directly to left chamber 401 via fluid line 382 and the opposite side or port 379 of pump 360 is connected via fluid line 383 to the right side. It is hydraulically connected directly to chamber 402 . By using such a direct hydraulic connection 382 , no one-way check or proportional valve is provided in line 382 between pump port 378 and actuator chamber port 403 . By using such a direct hydraulic connection 383 , no one-way check or proportional valve is provided in line 383 between pump port 379 and actuator chamber port 404 .

Piston 405 will move to the right when motor 16 is rotated and pump 360 is in positive angular range 370, thereby pressurizing port 378 with respect to port 379 and from port 378 to conduit 382. Advances fluid through chamber 401 and draws fluid from chamber 402 through port 404, conduit 383, and port 379, thereby creating a pressure differential over piston 385 which causes rod 406 to move to the right. stretched to Piston 405 will move to the left when motor 16 is rotated and pump 360 is in negative angle range 374, thereby pressurizing port 379 with respect to port 378 and from port 379 to conduit 383. Advances fluid through chamber 402 and draws fluid from chamber 401 through port 403, conduit 382, and port 378, thereby creating a pressure differential over piston 385 which causes rod 407 to move to the left. stretched to Thus, in normal drive mode, rotation of drive shaft 318 when swash plate 365 is within positive angular range 370 provides higher pressure to pump port 378 relative to pump port 379, Rotation of shaft 318 when swash plate 365 is in negative angular range 374 provides higher pressure to pump port 379 relative to pump port 378 .

As in Example 15, both actuators 390 and 400 are driven in either direction by rotation of shaft 318 depending on the degree of tilt of swashplate axes 338 and 378 relative to block axes 334 and 364, respectively. can be Accordingly, various combinations of actuator directions may be commanded, such as, but not limited to, directions D1/D3 having swash plate angle ranges of 340/370 respectively; directions D1/D4 with swash plate angle ranges 340/374 respectively; and directions D2/D3 with swash plate angle ranges 344/370 respectively. Under normal driving conditions, angular ranges 340 and 370 produce positive pressure differentials P348/P349 and P378/P379, and angular ranges 344 and 374 produce positive pressure differentials P349/P348 and P379/P378. Let

Similar to the pump/actuator combinations 30/60 and 60/100, an external force applied to actuator 390 having a force component in direction D1 can cause a higher pressure in chamber 392 relative to chamber 391. , a direct hydraulic connection 353 allows a higher pressure to be developed at port 349 relative to port 348 . This negative pressure differential P348/P349 provides additional torque to the cylinder block 333 given the commanded positive pressure differential, which additional torque is transmitted through the through shaft 323 to It is transmitted to cylinder block 363 of pump 360 and assists in driving actuator 400 . In addition, an external force having a force component in direction D2 applied to actuator 390 can create a higher pressure in chamber 391 with respect to chamber 392 and, by direct hydraulic connection 352, with respect to port 349. A higher pressure can be developed at port 348 as . This negative pressure differential (P349/P348) also provides additional torque to the cylinder block 333, given the positive pressure differential commanded, which additional torque is applied to the through shaft 323 to cylinder block 363 of pump 360 to assist in driving actuator 400 . Thus, when an external force is applied to hydraulic actuator 390 that provides a higher pressure to pump port 349 relative to pump port 348 when swash plate 335 is within positive angular range 340 (P348/P349< 0), an assist torque is applied to the drive shaft 318; Further, when an external force is applied to hydraulic actuator 390 that provides a higher pressure to pump port 348 relative to pump port 349 when swash plate 335 is within negative angular range 344 (P349/P348< 0), an assist torque is applied to the drive shaft 318;

As in Example 15, if either the pressure differentials P348/P349 and P378/P379 in angular ranges 340 and 370 or the pressure differentials P349/P348 and P379/P378 in angular ranges 344 and 374 are negative, the pump One or more of the /actuator combinations 330/390 and 360/400 may provide assist torque applied through the shaft 318 to the remainder of the pump/actuator combinations 330/390 and 360/400. can. Thus, if the commanded pump port pressure differential is positive and the resulting operating pump port pressure differential is negative for the slope of interest, the regeneration mode is employed.

Pump/actuator combinations 330/390 and 360/400 can also provide net regenerative torque to shaft 318 that is used by motor 16 and drive electronics 22 to charge battery 21 . For example, without limitation, providing pump ports 349 and 379 with a higher combined pressure relative to pump ports 348 and 378 when swash plates 335 and 375 are within positive angular ranges 340 and 370, respectively. This torque is used to charge the battery 21 when an external force is applied to the hydraulic actuators 390 and/or 400 and/or 19 (Σ(P348/P349+P378/P379)<0). The motor 16 acts as a generator and converts this regenerated torque into current which is stored in the battery 21 . Further, for example, and without limitation, a higher combined pressure to pump ports 348 and 378 relative to pump ports 349 and 379 when swash plates 335 and 375 are within negative angular ranges 344 and 374, respectively. This torque is used to charge the battery 21 when an external force is applied to the hydraulic actuators 390 and/or 400 (Σ(P349/P348+P379/P378)<0). Thus, if the commanded pump port pressure differential is positive and the total resulting operating pump port pressure differential is negative for the slope of interest, the regeneration mode is employed.

Similarly, controller 22 closes the control loop by varying the flow and pressure acting on pistons 395 and 405, respectively, and adjusting the speed of motor 16 and the tilt of swash plates 335 and 365 accordingly. and to swash plate actuators 354 and 384 of motor 16 and pumps 330 and 360 to control the direction, velocity and force of pistons 395 and 405 and thus rods 396, 397, 406 and 407. control the current.

Assist torque electrohydraulic piston pump systems 15, 115, 215, and 315 provide a number of benefits. Unexpectedly, the system provides actuation forces that are large enough to meet the demanding demands of mobile equipment. The system allows variable speed actuation and full control of the location of the actuator within its range of motion. The system has a built-in hydraulic supply, has return porting, and can operate in a closed system, limiting fluid contamination and fluid leakage problems. The system does not use proportional valves to regulate flow between the pumps and hydraulic actuators, instead the pumps control the flow directly to their respective actuators. The system is battery operated, very efficient, highly robust to large shocks, compact and low cost. Regenerated power from the gravity load is transferred directly to the pump and motor shafts, rather than first to the battery and then back. The system can handle very large shocks, does not require delicate electromechanical solutions, and the actuator cylinders within the system are easy to replace. Additionally, the increased energy efficiency of the system minimizes the size of the battery pack, thereby reducing cost.

Many variations and modifications can be made. Thus, having shown and described embodiments of an improved assist torque electrohydraulic piston pump system and considered numerous alternatives, the present invention is defined and distinguished by the following claims. Those skilled in the art will readily recognize that various additional changes and modifications can be made without departing from the scope of the invention.

Claims (32)

An electrohydraulic pump system comprising:
an electric motor having a drive shaft and adapted to be supplied with electric current;
a first fluid control journal, a plurality of pistons in a first cylinder block adapted to rotate relative to said first fluid control journal about a first block axis by rotation of said drive shaft; and a first displacement drive having a first displacement axis, comprising:
The first displacement drive has a first neutral position between the first displacement axis and the first block axis and a position between the first displacement axis and the first block axis. adapted to move within a first positive displacement range between a first positive maximum displacement position at
The first displacement drive has a first displacement between the first neutral position and a first negative maximum displacement position between the first displacement axis and the first block axis. adapted to move within a negative displacement range,
The first fluid control journal has a first pump port and a second pump port, and the drive shaft is displaced when the first displacement drive is within the first positive displacement range. When rotation provides a higher pressure to the first pump port relative to the second pump port and the first displacement drive is within the first negative displacement range. rotation of the drive shaft provides a higher pressure to the second pump port relative to the first pump port;
a first hydraulic piston pump;
a second fluid control journal, a plurality of pistons in a second cylinder block adapted to rotate relative to said second fluid control journal about a second block axis by rotation of said drive shaft; and a second displacement drive having a second displacement axis, comprising:
The second displacement drive has a second neutral position between the second displacement axis and the second block axis and a position between the second displacement axis and the second block axis. adapted to move within a second positive displacement range between a second maximum positive displacement position at
The second displacement driving device has a second neutral position between the second displacement axis and the second block axis and a position between the second displacement axis and the second block axis. adapted to move within a second range of negative displacement between and a second maximum negative displacement position therebetween;
The second fluid control journal has a third pump port and a fourth pump port, wherein the drive shaft is displaced when the second displacement drive is within the second positive displacement range. when rotation provides a higher pressure to the third pump port relative to the fourth pump port and the second displacement drive is within the second negative displacement range; rotation of the drive shaft provides a higher pressure to the fourth pump port relative to the third pump port;
a second hydraulic piston pump;
a first hydraulic actuator having a first actuation port hydraulically connected to the first pump port of the first piston pump, comprising:
said first hydraulic actuator having a second actuation port hydraulically connected to said second pump port of said first piston pump;
a first hydraulic actuator;
a second hydraulic actuator having a third actuation port hydraulically connected to the third pump port of the second piston pump, comprising:
the second hydraulic actuator has a fourth actuation port hydraulically connected to the fourth pump port of the second piston pump;
a second hydraulic actuator;
providing a higher pressure to the second pump port relative to the first pump port when the first displacement drive is within the first positive displacement range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the first pump port relative to the second pump port when the first displacement drive is within the first negative displacement range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
Electro-hydraulic pump system. providing a higher pressure to the fourth pump port relative to the third pump port when the second displacement drive is within the second positive displacement range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the third pump port relative to the fourth pump port when the second displacement drive is within the second negative displacement range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
An electrohydraulic pump system according to claim 1. 2. An electrohydraulic pump system as claimed in claim 1, comprising a battery for supplying said current to said electric motor. The motor is configured to selectively supply current to the battery in a regeneration mode, wherein in the regeneration mode:
An external force applied to said first hydraulic actuator causes said first pressure to be higher relative to said first pump port when said first displacement drive is within said first positive displacement range. 2 pump ports, or applied to the first hydraulic actuator, to the second pump port when the first displacement drive is in the first negative displacement range. providing a higher pressure to the first pump port relative to the port, and an external force applied to the second hydraulic actuator causing the second displacement drive to move within the second positive displacement range. providing a higher pressure to the fourth pump port relative to the third pump port when at or an external force applied to the second hydraulic actuator causes the second displacement actuation providing a higher pressure to the third pump port relative to the fourth pump port when the device is in the second negative displacement range;
An electrohydraulic pump system according to claim 3. wherein the first hydraulic actuator is configured to actuate a first object of the electric vehicle and the second hydraulic actuator is configured to actuate a second object of the electric vehicle; An electrohydraulic pump system according to claim 1. 2. The subsea actuation system of claim 1, wherein said electric motor is selected from the group consisting of brushless DC variable speed servo motors, stepper motors, brush motors, and induction motors. 2. The electrohydraulic pump system of claim 1, wherein said first hydraulic actuator comprises a linear hydraulic actuator or a rotary hydraulic actuator. 8. The electric of claim 7, wherein said first hydraulic actuator comprises a linear hydraulic actuator having a first chamber, a second chamber, and a piston separating said first and second chambers. Hydraulic pump system. The first hydraulic actuator has a cylinder having a first end wall, the piston is disposed within the cylinder for sealing sliding movement therein, the piston is adapted to move the first 9. The electrohydraulic pump system of claim 8, having a first actuator rod having a portion sealingly extending through one end wall. 10. The electrohydraulic pump of claim 9, wherein said cylinder has a second end wall and said piston has a second actuator rod having a portion sealingly extending through said second end wall. system. 9. The electrohydraulic pump system of claim 8, comprising a position sensor configured to sense the position of said piston. 9. The electrohydraulic pump system of claim 8, comprising a pressure sensor configured to sense pressure in said first chamber and said second chamber. a third fluid control journal, a plurality of pistons in a third cylinder block adapted to rotate relative to said third fluid control journal about a third block axis by rotation of said drive shaft; , and a third hydraulic piston pump having a third displacement drive having a third displacement axis,
The third displacement drive has a third neutral position between the third displacement axis and the third block axis and a position between the third displacement axis and the third block axis. adapted to move within a third positive displacement range between a third maximum positive displacement position at
The third displacement driving device has a third neutral position between the third displacement axis and the third block axis, and a position between the third displacement axis and the third block axis. adapted to move within a third range of negative displacement between and a third maximum negative displacement position therebetween;
The third fluid control journal has a fifth pump port and a sixth pump port, wherein the drive shaft is displaced when the third displacement drive is within the third positive displacement range. when rotation provides a higher pressure to the fifth pump port relative to the sixth pump port and the third displacement drive is within the third negative displacement range; rotation of the drive shaft provides a higher pressure to the sixth pump port relative to the fifth pump port;
a third hydraulic piston pump;
a third hydraulic actuator having a fifth actuation port hydraulically connected to the fifth pump port of the third piston pump, comprising:
the third hydraulic actuator has a sixth actuation port hydraulically connected to the sixth pump port of the third piston pump;
a third hydraulic actuator;
providing a higher pressure to the sixth pump port relative to the fifth pump port when the third displacement drive is within the third positive displacement range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the fifth pump port relative to the sixth pump port when the third displacement drive is within the third negative displacement range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
An electrohydraulic pump system according to claim 1. The shaft has a first portion connected to the first cylinder block, a second portion connected to the second cylinder block, and a third portion connected to the third cylinder block. 14. The electrohydraulic pump system of claim 13, having a portion of . a first displacement drive actuator connected to the first displacement drive to selectively move the first displacement drive within the first positive displacement range; 2. The electrohydraulic pump system of claim 1, comprising a first displacement drive actuator configured to selectively move said first displacement drive within one negative displacement range. a second displacement drive actuator connected to the second displacement drive to selectively move the second displacement drive within the second positive displacement range; 16. The electrohydraulic pump system of claim 15, comprising a second displacement drive actuator configured to selectively move the second displacement drive within two negative displacement ranges. said first fluid control journal having a first central control journal;
said first displacement drive having a first stroke ring oriented about said first displacement axis;
wherein said first neutral position between said first displacement axis and said first block axis comprises a position where said first displacement axis and said first block axis are coaxial;
said first streak ring adapted to move radially with respect to said first neutral position;
wherein the first positive maximum displacement position between the first displacement axis and the first block axis is a first positive position in a first positive direction relative to the first neutral position; a first positive eccentric position that offsets the first displacement axis from the first block axis by a maximum eccentric distance;
said first positive displacement range includes a first positive eccentric range between said first neutral position and a first positive eccentric position;
wherein the first negative maximum displacement position between the first displacement axis and the first block axis is a first negative position in a first negative direction relative to the first neutral position; a first negative eccentric position that offsets the first displacement axis from the first block axis by a maximum eccentric distance;
said first negative displacement range includes a first negative eccentric range between said first neutral position and a first negative eccentric position;
Rotation of the drive shaft when the first stroke ring is within the first positive eccentric range causes a higher pressure at the first pump port relative to the second pump port. and rotation of the drive shaft when the first stroke ring is within the first range of negative eccentricity provides a higher pressure relative to the first pump port to the second pump port. provided to the pump ports of
said second fluid control journal having a second central control journal;
said second displacement drive having a second stroke ring oriented about said second displacement axis;
wherein said second neutral position between said second displacement axis and said second block axis comprises a position where said second displacement axis and said second block axis are coaxial;
said second stroke ring adapted to move radially with respect to said second neutral position;
wherein the second positive maximum displacement position between the second displacement axis and the second block axis is a second positive displacement position in a second positive direction relative to the second neutral position; a second positive eccentric position offsetting said second displacement axis from said second block axis by a maximum eccentric distance;
said second positive displacement range includes a second positive eccentric range between said second neutral position and a second positive eccentric position;
wherein the second negative maximum displacement position between the second displacement axis and the second block axis is a second negative maximum displacement position in a second negative direction relative to the second neutral position; a second negative eccentric position that offsets the second displacement axis from the second block axis by a maximum eccentric distance;
said second negative displacement range includes a second negative eccentric range between said second neutral position and a second negative eccentric position;
Rotation of the drive shaft when the second stroke ring is within the second positive eccentric range causes a higher pressure at the third pump port relative to the fourth pump port. and the rotation of the drive shaft when the second stroke ring is within the second range of negative eccentricity provides a higher pressure relative to the third pump port to the fourth pump port. provided to the pump ports of
providing a higher pressure to the second pump port relative to the first pump port when the first stroke ring is within the first positive eccentric range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the first pump port relative to the second pump port when the first stroke ring is within the first negative eccentric range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
An electrohydraulic pump system according to claim 1. providing a higher pressure to the fourth pump port relative to the third pump port when the second stroke ring is within the second positive eccentric range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the third pump port relative to the fourth pump port when the second stroke ring is within the second negative eccentric range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
18. Electrohydraulic pump system according to claim 17. a battery that supplies the current to the electric motor, the motor being configured to selectively supply current to the battery in a regeneration mode, wherein the regeneration mode comprises:
An external force applied to the first hydraulic actuator creates a higher pressure relative to the first pump port when the first stroke ring is within the first range of positive eccentricity. 2 pump ports or applied to the first hydraulic actuator causes the second pump to operate when the first stroke ring is within the first range of negative eccentricity. providing a higher pressure to the first pump port relative to the port, and an external force applied to the second hydraulic actuator causes the second stroke ring to move through the second positive eccentric range; providing a higher pressure to the fourth pump port relative to the third pump port when in or an external force applied to the second hydraulic actuator causes the second stroke - providing a higher pressure to the third pump port as a reference to the fourth pump port when the ring is within the second range of negative eccentricity;
18. Electrohydraulic pump system according to claim 17. a third central control journal and a plurality of cylinder blocks in a third cylinder block adapted to rotate relative to the third central control journal about a third block axis by rotation of the drive shaft; oriented about a piston and said third stroke axis adapted to move radially to a third neutral position coaxial with said third stroke axis and said third block axis; a third hydraulic piston pump having a third stroke ring,
said third stroke ring adapted to move linearly within a third positive eccentric range between said third neutral position and a third positive eccentric position; a stroke axis offset from said third block axis by a third positive maximum eccentric distance in a third positive direction relative to said third neutral position;
said third stroke ring adapted to move linearly within a third negative eccentric range between said third neutral position and a third negative eccentric position; a stroke axis offset from said third block axis by a third negative maximum eccentric distance in a third negative direction opposite said third positive direction relative to said third neutral position;
said third control journal includes a fifth pump port and a sixth pump port, and said drive shaft rotates when said third stroke ring is within said third range of positive eccentricity; thereby providing a higher pressure to the fifth pump port relative to the sixth pump port, and to the drive when the third stroke ring is within the third negative eccentric range. rotation of the shaft provides a higher pressure to the sixth pump port relative to the fifth pump port;
a third hydraulic piston pump;
a third hydraulic actuator having a fifth actuation port hydraulically connected to the fifth pump port of the third piston pump, comprising:
the third hydraulic actuator has a sixth actuation port hydraulically connected to the sixth pump port of the third piston pump;
a third hydraulic actuator;
providing a higher pressure to the sixth pump port relative to the fifth pump port when the third stroke ring is within the third positive eccentric range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the fifth pump port relative to the sixth pump port when the third stroke ring is within the third range of negative eccentricity; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
18. Electrohydraulic pump system according to claim 17. The shaft has a first portion connected to the first cylinder block, a second portion connected to the second cylinder block, and a third portion connected to the third cylinder block. 21. The electrohydraulic pump system of claim 20, having a portion of . a first hydraulic ring actuator connected to said first stroke ring, said first positive eccentricity being between said first neutral position and said first positive eccentricity; said first negative eccentric range between said first neutral position and said first negative eccentric position for selectively linearly moving said first stroke ring within a range; 18. The electrohydraulic pump system of claim 17, comprising a first hydraulic ring actuator configured to selectively linearly move the first stroke ring therein. a second hydraulic ring actuator connected to said second stroke ring, said second positive eccentricity being between said second neutral position and said second positive eccentricity; said second negative eccentric range between said second neutral position and said second negative eccentric position for selectively linearly moving said second stroke ring within a range; 23. The electrohydraulic pump system of claim 22, comprising a second hydraulic ring actuator configured to selectively linearly move the second stroke ring therein. said first fluid control journal having a first port plate;
said first displacement drive having a first swash plate oriented about said first displacement axis;
wherein said first neutral position between said first displacement axis and said first block axis comprises a position where said first displacement axis and said first block axis are coaxial;
said first swash plate adapted to move angularly with respect to said first neutral position;
the first positive maximum displacement position between the first displacement axis and the first block axis in a first positive angular direction relative to the first neutral position; a first positive angular position offsetting said first displacement axis from said first block axis at a maximum positive cam angle;
said first positive displacement range comprising a first positive angular range between said first neutral position and a first positive angular position;
the first negative maximum displacement position between the first displacement axis and the first block axis in a first negative angular direction relative to the first neutral position; a first negative angular position offsetting said first displacement axis from said first block axis at a maximum negative cam angle;
said first negative displacement range comprising a first negative angular range between said first neutral position and a first negative angular position;
Rotation of the drive shaft when the first swash plate is within the first positive angular range results in a higher pressure at the first pump port relative to the second pump port. and rotation of the drive shaft when the first swash plate is within the first negative angular range provides a higher pressure relative to the first pump port to the second provided to the pump ports of
said second fluid control journal having a second port plate;
said second displacement drive having a second swash plate oriented about said second displacement axis;
wherein said second neutral position between said second displacement axis and said second block axis comprises a position where said second displacement axis and said second block axis are coaxial;
said second swash plate adapted to move angularly with respect to said second neutral position;
said second maximum positive displacement position between said second displacement axis and said second block axis in a second positive angular direction relative to said second neutral position; a second positive angular position offsetting said second displacement axis from said second block axis at a maximum positive cam angle;
said second positive displacement range includes a second positive angular range between said second neutral position and a second positive angular position;
the second maximum negative displacement position between the second displacement axis and the second block axis in a second negative angular direction relative to the second neutral position; a second negative angular position offsetting said second displacement axis from said second block axis at a maximum negative cam angle;
said second negative displacement range includes a second negative angular range between said second neutral position and a second negative angular position;
Rotation of the drive shaft when the second swash plate is within the second positive angular range causes a higher pressure at the third pump port relative to the fourth pump port. and rotation of the drive shaft when the second swash plate is within the second negative angular range provides a higher pressure relative to the third pump port to the fourth provided to the pump ports of
providing a higher pressure to the second pump port relative to the first pump port when the first swash plate is within the first positive angular range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the first pump port relative to the second pump port when the first swash plate is within the first negative angular range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
An electrohydraulic pump system according to claim 1. providing a higher pressure to the fourth pump port relative to the third pump port when the second swash plate is within the second positive angular range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the third pump port relative to the fourth pump port when the second swash plate is within the second negative angular range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
25. Electrohydraulic pump system according to claim 24. a battery that supplies the current to the electric motor, the motor being configured to selectively supply current to the battery in a regeneration mode, wherein the regeneration mode comprises:
An external force applied to the first hydraulic actuator creates a higher pressure relative to the first pump port when the first swash plate is within the first positive angular range. 2 pump ports or applied to the first hydraulic actuator causes the second pump to operate when the first swash plate is within the first negative angular range. providing a higher pressure port to port to said first pump port, and an external force applied to said second hydraulic actuator causing said second swash plate to move through said second positive angular range; providing a higher pressure to the fourth pump port relative to the third pump port when in the second swash, or an external force applied to the second hydraulic actuator - providing a higher pressure to the third pump port relative to the fourth pump port when the plate is within the second negative angular range;
25. Electrohydraulic pump system according to claim 24. a third port plate and a plurality of cylinder blocks in a third cylinder block adapted to rotate relative to said third port plate about a third block axis upon rotation of said drive shaft; a piston and said third swashplate axis adapted to move angularly relative to a third neutral position coaxial with said third swashplate axis and said third block axis; a third hydraulic piston pump having a third centrally oriented swash plate;
said third swash plate adapted to angularly move within a third positive angular range between said third neutral position and a third positive angular position; three swash plate axes offset from said third block axis at a third positive maximum cam angle in a third positive angular direction relative to said third neutral position;
said third swash plate adapted to angularly move within a third negative angular range between said third neutral position and a third negative angular position; 3 swash plate axes at a third negative maximum cam angle in a third negative angular direction opposite to the third positive angular direction relative to the third neutral position; offset from the block axis,
said third port plate including a fifth pump port and a sixth pump port, said drive shaft rotating when said third swash plate is within said third positive angular range; to provide a higher pressure to the fifth pump port relative to the sixth pump port, and when the third swash plate is within the third negative angular range, the rotation of the drive shaft provides a higher pressure to the sixth pump port relative to the fifth pump port;
a third hydraulic piston pump;
a third hydraulic actuator having a fifth actuation port hydraulically connected to the fifth pump port of the third piston pump, comprising:
the third hydraulic actuator has a sixth actuation port hydraulically connected to the sixth pump port of the third piston pump;
a third hydraulic actuator;
providing a higher pressure to the sixth pump port relative to the fifth pump port when the third swash plate is within the third positive angular range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the fifth pump port relative to the sixth pump port when the third swash plate is within the third negative angular range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
25. Electrohydraulic pump system according to claim 24. The shaft has a first portion connected to the first cylinder block, a second portion connected to the second cylinder block, and a third portion connected to the third cylinder block. 28. The electrohydraulic pump system of claim 27, having a portion of . a first hydraulic swash plate actuator connected to said first swash plate, said first positive angular position being between said first neutral position and said first positive angular position; and the first negative angular range between the first neutral position and the first negative angular position to selectively move the first swash plate within an angular range of 25. The electrohydraulic pump system of claim 24, comprising a first hydraulic swash plate actuator configured to selectively move the first swash plate within. a second hydraulic swash plate actuator connected to the second swash plate, wherein the second positive angular position is between the second neutral position and the second positive angular position; and said second negative angular range between said second neutral position and said second negative angular position to selectively move said second swash plate within an angular range of 30. The electrohydraulic pump system of claim 29, comprising a second hydraulic swash plate actuator configured to selectively move the second swash plate within. said first fluid control journal having a first central control journal;
said first displacement drive having a first stroke ring oriented about said first displacement axis;
wherein said first neutral position between said first displacement axis and said first block axis comprises a position where said first displacement axis and said first block axis are coaxial;
said first streak ring adapted to move radially with respect to said first neutral position;
wherein the first positive maximum displacement position between the first displacement axis and the first block axis is a first positive position in a first positive direction relative to the first neutral position; a first positive eccentric position that offsets the first displacement axis from the first block axis by a maximum eccentric distance;
said first positive displacement range includes a first positive eccentric range between said first neutral position and a first positive eccentric position;
wherein the first negative maximum displacement position between the first displacement axis and the first block axis is a first negative position in a first negative direction relative to the first neutral position; a first negative eccentric position that offsets the first displacement axis from the first block axis by a maximum eccentric distance;
said first negative displacement range includes a first negative eccentric range between said first neutral position and a first negative eccentric position;
Rotation of the drive shaft when the first stroke ring is within the first positive eccentric range causes a higher pressure at the first pump port relative to the second pump port. and rotation of the drive shaft when the first stroke ring is within the first range of negative eccentricity provides a higher pressure relative to the first pump port to the second pump port. provided to the pump ports of
said second fluid control journal having a first port plate;
said second displacement drive having a first swash plate oriented about said second displacement axis;
wherein said second neutral position between said second displacement axis and said second block axis comprises a position where said second displacement axis and said second block axis are coaxial;
said first swash plate adapted to move angularly with respect to said second neutral position;
The second maximum positive displacement position between the second displacement axis and the second block axis is a first positive angular direction relative to the second neutral position. a first positive angular position offsetting said second displacement axis from said second block axis at a maximum positive cam angle;
said second positive displacement range includes a first positive angular range between said second neutral position and a first positive angular position;
The second maximum negative displacement position between the second displacement axis and the second block axis is at a first negative angular direction relative to the second neutral position. a first negative angular position offsetting said second displacement axis from said second block axis at a maximum negative cam angle;
said second negative displacement range includes a first negative angular range between said second neutral position and a first negative angular position;
Rotation of the drive shaft when the first swash plate is within the first positive angular range results in a higher pressure at the third pump port relative to the fourth pump port. and rotation of the drive shaft when the second swash plate is within the first negative angular range provides a higher pressure relative to the third pump port to the fourth provided to the pump ports of
providing a higher pressure to the second pump port relative to the first pump port when the first stroke ring is within the first positive eccentric range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the first pump port relative to the second pump port when the first stroke ring is within the first negative eccentric range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
An electrohydraulic pump system according to claim 1. providing a higher pressure to the fourth pump port relative to the third pump port when the first swash plate is within the first positive angular range; an external force applied to the hydraulic actuator applies an assist torque to the drive shaft;
providing a higher pressure to the third pump port relative to the fourth pump port when the first swash plate is within the first negative angular range; an external force applied to a hydraulic actuator applies an assist torque to the drive shaft;
32. The electrohydraulic pump system of claim 31.

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