TW201400701A - Bent axis variable delivery inline drive axial piston pump and/or motor - Google Patents

Abstract

A bent axis, variable displacement inline drive device may comprise: a port plate having fluid passages; a cylinder block rotatably mounted adjacent the port plate and having axial cylinders having openings in alternating fluid communication with the fluid passages; a rotatable shaft coupled through the port plate to the cylinder block, pistons in the cylinders and having a connecting rod extending from the cylinder block; a rotatable spindle having receptacles for receiving the connecting rods; a pivotable yoke having the spindle rotatably mounted thereon, whereby the rotating group comprising the spindle, pistons and cylinder block are connected by the connecting rods for rotating together, the yoke being pivotable for angling the spindle relative to the cylinder block. The device may be employed as a pump, or as a motor, or as both a pump and a motor, and the yoke may be pivoted over center.

Description

Curved shaft variable delivery coaxial drive axial piston pump and / or motor

The present application claims the benefit of U.S. Provisional Patent Application Serial No. 61/594,091, filed on Feb. 2, 2012, entitled "BENT AXIS VARIABLE DELIVERY INLINE DRIVE AXIAL PISTON PUMP AND/OR MOTOR," This is hereby incorporated by reference.

The present invention relates to an axial piston assembly, and in particular to an axial piston pump and/or motor assembly including a coaxial drive and a curved shaft.

Fluid axial piston pumps (e.g., useful as hydraulic pumps) are known to be classified into two fundamentally distinct categories: a bending axis axial piston pump or a coaxial drive axial piston pump.

A rotary type axial piston pump has a rotatable cylinder block or cylinder bore having a plurality of juxtaposed cylinders disposed in an axially circular array of one of the central axes of rotation. Each cylinder has a reciprocating piston that is driven (as explained below) to move in an axial direction through a complete reciprocating cycle within the cylinder at each 360° rotation of the cylinder block. A flat end face of the cylinder block abuts a flat distribution surface of the valve disc having one of the curved inlet passages coupled to one of the inlet ports and one of the curved outlet passages coupled to one of the outlet ports. The cylinder block is rotated relative to the valve disc to operate the piston and cause pumping motion of the cylinder to pump fluid from the inlet port to the outlet port. The cylinder block is driven by a shaft member and a disc located at an end of the cylinder block away from the end adjacent to the valve disc, wherein the disc is mechanical The mode is coupled to the piston to cause the piston to reciprocate as the cylinder block rotates.

Each of the curved passages in the valve disc has an opening or slot in the shape of a partial circular arc of less than 180° at the flat flow surface of the valve disc for rotation of less than 180° for the cylinder block in the cylinder block The flat end face is in fluid communication with the open end of the cylinder. As it moves circularly along one of the distribution surfaces adjacent the valve disc, each cylinder is thus in fluid communication with the inlet passage during rotation of the cylinder block less than 180° and in fluid communication with the outlet passage during rotation of the cylinder block less than 180° .

Each piston is actuated in a reciprocating manner to move away from the valve disc as its cylinder opens toward the inlet passage, thereby drawing fluid into the cylinder and moving toward the valve disc as its cylinder opens toward the outlet passage, thereby discharging from the cylinder fluid. Thus, fluid in the inlet passage is drawn from the inlet passage into the cylinder and discharged from the cylinder into the outlet passage, thereby producing the desired flow by pumping fluid from the inlet port to the outlet port. The volume of the pumped fluid is substantially proportional to the working volume of the cylinder and the rate of rotation of the cylinder block.

1 includes FIGS. 1A and 1B, which are cross-sectional views of an exemplary embodiment of a conventional curved shaft axial piston pump 900 that is rotated 90° apart. Wherein, a rotatable drive shaft member 910 is rotated about an axis 912 at an angle with respect to the rotational axis 932 of the cylinder block 930 in a housing 920 and has an axis of rotation 912 perpendicular to the drive shaft member 912 attached thereto and One of its rotations drives the disk 940. The drive plate 940 has a circular array of sockets 942 of the piston 950 in the cylinder block 930 via the retention link 952 such that the drive shaft member 910, the drive plate 940 and the cylinder block 930 all rotate together. Since the drive shaft member 910 is at an angle α with respect to the cylinder block 930, the piston rod 952 and the piston 950 are reciprocally driven by the drive shaft member 910, the drive plate 940 and the cylinder block 930, and each piston 950 is moved. The distance is related to the angle α. Generally, a universal joint or coupling rod can be provided between the end of the drive shaft member 910 and the cylinder block 930 (e.g., at or near the intersection of its respective respective rotational axes 912, 932) to drive the cylinder in a rotational manner. Body 930.

Fluid passes through the fluid passage in the yoke 960 and is adjacent to the rotating cylinder block 930 A distribution plate 970 moves through the pump 900. The bearings that support the yoke 960 in a pivotal manner typically include a seal 924 that allows for relative pivotal rotation between the fluid passages of the yoke 960 and their fluid ports 922 of the housing 920. The pivotable parts of the pump 900, including the cylinder block 930, the yoke 960, and the valve plate 970, are relatively large and heavy parts of the pump 900 and are therefore often difficult to move (pivot) quickly or easily. Drive shaft 910 is typically supported by one or more bearings 914 and seal 916 for effecting its rotation.

In the case where the angle α between the drive plate 940 and the cylinder block 930 is fixed, the movement of the piston 950 and the working volume and pumping volume are also fixed. However, if the drive shaft member 910 and the drive plate 940 are mounted on a movable pivot yoke 960 such that the angle α between the drive shaft member 910 and the cylinder block 930 can be changed, the piston can be changed by changing the angle α. The magnitude of the reciprocating movement of 950 and a variable displacement pump 900 are available. When the drive shaft 910 is aligned with the cylinder block 930, for example, the angle a is zero, the piston 950 does not reciprocate and therefore does not pump fluid. Since the displacement varies with the sine of the angle a, a larger angle a produces a larger displacement of the piston 950 and a larger pumped volume at a given rate of rotation of the cylinder block 930.

While the bending axis axial piston pump 900 is extremely efficient and is, for example, the dominant type of hydraulic pump employed in aircraft for many years, one disadvantage of the bending axis axial piston pump 900 is that it must be pivoted by the yoke 960. The rotation group including the drive shaft 910 and the drive assembly 940 is moved to achieve variable displacement. Therefore, the bending axis axial piston pump 900 tends to be larger and heavier and difficult to manufacture as a variable delivery pump. The angle α represents the maximum angle α that can be practically utilized in a fixed displacement bending axis pump, for example, about 40°, and the maximum change in the angle α in a variable displacement bending axis pump is about 28° to 30°. °. Additionally, the rotating fluid seal 924 between the fluid passage of the yoke 960 and the housing 920 can be a source of leakage of fluid that can be pumped at relatively high pressures. For these reasons, despite its inherently high pumping efficiency, at least in aircraft and aerospace applications, the variable displacement bending axis has been replaced by a smaller and lighter conventional coaxial drive axial configuration pump. Axial pumps, although with lower pumping and mechanical efficiency.

2 is an excision perspective view of one exemplary embodiment of one of the conventional coaxially driven axial piston pumps 800 introduced in the mid-1960s. Therein, a rotatable drive shaft member 810 is rotated about a rotational axis 812 of the cylinder block 830 and rotates with one of the axes 812, and includes a non-swash plate 840 that is inclined relative to the axis of the drive shaft member 810. The swash plate 840 has a rotatable drive plate 844 having a circular array of sockets 842 in which the links (also referred to as shoes or shoes) 852 of the piston 850 are retained, such The piston 850 reciprocates in a bore in the cylinder block 830 to cause the drive shaft member 810, the drive plate 844, and the cylinder block 830 to all rotate together. Since the driving disk 844 and the swash plate 840 rotate together and are at an angle with respect to the cylinder block 830, the piston 850 is driven in a reciprocating manner by the driving shaft member 810 and the cylinder block 830, and the distance of each piston 850 is moved. The swash plate 840 is associated with an angle that is offset from the axis 812 of the drive shaft member 810. The drive shaft 810 is coaxial with the cylinder block 830 and can therefore be coupled directly mechanically. However, the sliding action of the piston shoe/slider 852 in the receptacle of the swash plate 840 tends to produce viscous friction that impedes low speed operation and reduces efficiency.

In the case where the angle between the drive plate 844 and the cylinder block 830 is fixed, the displacement of the piston 850 and the pumping volume are also fixed. However, if the drive plate 844 is mounted on a movable pivoting swash plate 840 such that the angle between the drive plate 844 and the cylinder block 830 can be changed, the amount of reciprocation of the piston 850 can be varied by varying the angle. A variable displacement pump 800 is also available for pumping fluid between the inlet and outlet ports 822. When the swash plate 840 and the drive plate 844 are perpendicular to the drive shaft member 810, for example, the angle is zero, the piston 850 does not reciprocate and therefore does not pump fluid. Since the displacement varies sinusoidally with the angle between the drive plate 844 and the cylinder block 830, a larger angle produces a larger displacement and a larger pumped volume at a predetermined rate of rotation of the cylinder block 830.

While the coaxial axial piston pump 800 can be small in size relative to a relatively curved shaft piston pump, the disadvantages of the coaxial axial piston pump 800 include lower pumping and mechanical efficiency than a curved shaft piston pump. This is because the coaxial drive piston pump can be transported in only one direction. Lines cannot be operated across the center, cannot operate as both a pump and a motor, and cannot operate at low speeds. The maximum angle at which the drive disc can be rotated from vertical has been limited to about 18° from vertical for many years, which limits the maximum displacement that this type of pump can provide; even in the latest advancements that allow the angle to be increased to approximately 21°. The displacement is still limited. Conventional coaxial axial structures cannot run across the center and therefore cannot be reversed.

Therefore, existing axial piston pumps are subject to one of the limitations of capacity due to the practical limitations of the maximum allowable angle between the cylinder block and the drive plate and/or the swash plate. It would be desirable to have an axial piston device that can operate at a greater angle, such as a pump and/or motor, which will reduce one of the resulting weight and size to produce a given flow. In addition, it would also be desirable to provide an axial piston device or machine that inherently provides lower losses resulting in higher pumping and mechanical efficiency. In addition, it would be desirable to have an axial piston device or machine that is not limited by the drive shaft member at the end opposite the inlet and outlet ports and/or has a reduced size and/or mass of one pivoting structure. A variable displacement is obtained and thus provides a faster response, for example, when changing displacement.

Applicants believe that it is desirable to not suffer from one of the foregoing limitations, one of the axial piston pumps and/or the motor.

Accordingly, a flexshaft variable displacement coaxial drive apparatus can include: a distribution plate having a fluid passage therein; a cylinder block rotatably mounted adjacent to the distribution plate and having an array of axial cylinders having a An opening adjacent the flow plate in fluid communication with the fluid passages alternately; a rotatable shaft member coupled to the cylinder block for rotation therewith through an opening in the distribution plate; a plurality of pistons, Disposed in the cylinder of the cylinder block for reciprocating therein, each piston having one of the links extending from one end of the cylinder block; and a rotatable mandrel having a receptacle for receiving the links a pivotable yoke having a mandrel rotatably mounted thereon, whereby the mandrel is coupled to the plurality of pistons disposed in the cylinder block for rotation therewith, The yoke is pivotable for rotating the mandrel at an angle relative to the cylinder block. The device can be used as a pump. It can be used as a motor or as both a pump and a motor, and the yoke can pivot across the center.

According to another aspect, a flexshaft variable displacement coaxial drive pump apparatus can include: a distribution plate having a fluid passage therein; a cylinder block rotatably mounted adjacent to the distribution plate and having an axial cylinder An array, each axial cylinder having an opening adjacent the flow distribution disk to alternately fluidly communicate with the fluid passages; a rotatable shaft member coupled to the cylinder block through an opening in the distribution plate for Rotating therewith; a plurality of pistons disposed in the cylinder of the cylinder block for reciprocating therein, each piston having a link extending therefrom; a rotatable mandrel having a receptacle for receiving the a pivotable yoke having a spindle rotatably mounted thereon, whereby the spindle is coupled to the plurality of pistons disposed in the cylinder block for use by the links Rotating together, the yoke is pivotable for rotating the mandrel at an angle relative to the cylinder block. The yoke can pivot across the center.

According to another aspect, a flexshaft variable displacement coaxial drive motor apparatus can include: a distribution plate having a fluid passage therein; a cylinder block rotatably mounted adjacent to the distribution plate and having an axial cylinder therein An array, each axial cylinder having an opening adjacent the flow distribution disk to alternately fluidly communicate with the fluid passages; a rotatable shaft member coupled to the cylinder block through an opening in the distribution plate Rotating therewith; a plurality of pistons disposed in the cylinder of the cylinder block for reciprocating therein, each piston having a link extending therefrom; a rotatable mandrel having a receptacle for receiving a receptacle of a connecting rod; a pivotable yoke having a spindle rotatably mounted thereon, whereby the spindle is coupled to the plurality of pistons disposed in the cylinder block for rotation together, The yoke is pivotable for rotating the mandrel at an angle relative to the cylinder block. The yoke can pivot across the center.

In another aspect, a bending axis variable displacement coaxial drive rotation group can include: a cylinder block rotatably mounted and having an array of axial cylinders, Each axial cylinder has an opening that is positioned to alternately fluidly communicate with a fluid passage opening of a distribution plate; the cylinder block has a central opening for receiving a rotatable shaft member, whereby a rotatable shaft member is Coupling to the cylinder block through an opening in a distribution plate; a plurality of pistons disposed in the cylinder of the cylinder block for reciprocating therein, each piston having a link extending from one end of the cylinder block a rotatable mandrel having a circular array of receptacles for receiving the ends of the links; a pivotable yoke having a mandrel rotatably mounted thereon for rotation, Thereby the mandrel is coupled to the plurality of pistons for rotation therewith, the yoke being pivotable for pivoting the mandrel relative to the cylinder block. The device rotation group can be used as a pump, or as a motor, or as both a pump and a motor, and the yoke can pivot across the center.

100‧‧‧Flexible shaft variable transport coaxial drive axial piston pump and / or motor / pump and / or motor device / device / pump / motor / pump and / or motor / bending shaft variable transport coaxial drive Axial piston pump and motor / pump / motor device / coaxial drive bending shaft pump / motor device bending shaft variable transmission coaxial drive axial piston device pump device / pump and motor / pump / motor / variable Displacement device / bending axis variable displacement coaxial drive / bending axis variable displacement coaxial drive pump device

100W‧‧‧wheel drive/motor/wheel coupling/device/pump/wheel drive/fluid drive

102‧‧‧Rotary drive shaft/shaft/rotary shaft/drive shaft

110‧‧‧Example distribution plate/non-rotating distribution plate/distribution plate

112‧‧‧埠 Opening

112a‧‧‧ Opening/opening

112b‧‧‧ opening/opening

115‧‧‧Center opening/opening/drive opening

116‧‧‧Cylinder seat surface

117a‧‧‧Fluid channel/arc chamber

117b‧‧‧Fluid channel/arc chamber

120‧‧‧Distributor/fluid/埠/export埠

130‧‧‧Cylinder block/spin cylinder block/component

131‧‧‧General spherical socket / spherical socket / socket

132‧‧‧Cylinder/Axial Cylinder/Cylinder Block

133‧‧‧埠/cylinder 埠/opening

136‧‧‧bearing/cylinder bearing

137‧‧ ‧ spring

138‧‧‧ bearing spring plate

140‧‧‧Piston rod/link/assembly/rod/piston connecting rod

142‧‧‧Cylinder/Piston

143‧‧‧General spherical socket / socket

144‧‧‧General spherical end / spherical ball / ball end / spherical end

146‧‧‧General spherical end / connecting rod end / spherical ball / ball end / spherical end

150‧‧‧ mandrel / rotatable mandrel / yoke mandrel / component

151‧‧‧General spherical socket / spherical socket / movable spherical socket / movable socket / socket

152‧‧‧Pressure plate/piston rod compression plate

153‧‧‧General spherical socket/heart bearing socket/yoke core bearing socket/socket

154‧‧‧Axial bearing/cylindrical thrust roller bearing

156‧‧‧ Radial Bearings/Bearings

157‧‧‧ spherical race

160‧‧‧ Yoke/Pivotable Yoke/Component/Yoke Assembly/End Plate/Low Inertia Yoke

161‧‧‧Rotary shaft/yoke or spindle shaft/shaft

162‧‧‧Ying bearing/coaxial yoke bearing

163‧‧‧ Yoke pivot shaft/shaft

164‧‧‧Yoke/Yinger or Bearing Plate/Bearing Plate

169‧‧ ‧ spring

170‧‧‧Output drive shaft / shaft / drive shaft / rotatable drive shaft / output shaft / rotatable shaft

171‧‧‧ Spline/solid features

172‧‧‧Sealing/shaft seals

172c‧‧‧Sealing carrier

172g‧‧‧ cylindrical groove

174‧‧‧bearing/shaft bearing

175‧‧‧Electric motor or other motor/motor/drive motor

180‧‧‧Shell/shaft housing/yoke housing

182‧‧‧Shaft housing base

184‧‧‧ central part

185‧‧‧ hole

186‧‧‧Distributor receiver part/distributor part/receiver part

190‧‧‧Shell/yoke housing

192‧‧‧Sheet base

194‧‧‧Shell cover part / yoke shell cover

195‧‧‧ openings

200‧‧‧ million joint rod / coupling rod

202‧‧‧ linkage

204‧‧‧Focused generally spherical ball/spherical end/open spherical ball

206‧‧‧Focus type generally spherical ball / rod end / end / split spherical ball

300‧‧‧Vehicle kinetic energy recovery system/vehicle hydraulic hybrid drive system

300P‧‧‧Vehicle kinetic energy recovery system/vehicle hydraulic hybrid drive system/parallel hybrid system

300S‧‧‧Vehicle kinetic energy recovery system/series hybrid system

310‧‧‧Engine/Internal Combustion Engine

320‧‧‧Transmission

330‧‧‧Drive shaft parts

340‧‧‧Differential gear

350‧‧‧Drive shaft/differential gear/axle

360‧‧‧ Wheels

370H‧‧‧ fluid circuit

370L‧‧‧ fluid circuit

380H‧‧‧High Pressure Accumulator Device/High Pressure Accumulator/High Pressure Accumulator

380L‧‧‧Low Pressure Accumulator/Low Pressure Accumulator (Storage)

800‧‧‧Used coaxial drive axial piston pump / variable displacement pump / coaxial axial piston pump

810‧‧‧Rotary drive shaft/drive shaft

812‧‧‧Axis

822‧‧‧Import and export埠

830‧‧‧Cylinder block

840‧‧‧Non-swashplate/swashplate/movable pivoting swashplate

842‧‧‧ socket

844‧‧‧Rotary drive/driver

850‧‧‧Piston

852‧‧‧ Connecting rods (also known as shoes or shoes) / piston shoes / shoes

900‧‧‧Used bending axis axial piston pump / pump / variable displacement pump / bending axis axial piston pump

910‧‧‧Rotary drive shaft/drive shaft

912‧‧‧Axis/Rotary axis

914‧‧‧ bearing

916‧‧‧Seal

920‧‧‧shell

922‧‧‧ Fluid 埠

924‧‧‧Sealing/Rotating Fluid Seals

930‧‧‧Cylinder block/spin cylinder block

932‧‧‧Rotary axis

940‧‧‧ drive disk

942‧‧‧ socket

950‧‧‧Piston

952‧‧‧ Connecting rod/piston rod

960‧‧‧ Yoke/movable pivot yoke

970‧‧‧Distributor

A‧‧‧Angle/Pivot Angle/Maximum Yoke Angle/Yoke Angle/Angle Position

T _B ‧‧‧Torque/Brake Torque

T _D ‧‧‧Torque/Drive Torque

‧‧‧‧ angle

ω‧‧‧Rotate

The detailed description of the preferred embodiment will be more readily and better understood when read in conjunction with the drawings. FIG. 1 includes FIG. 1A and FIG. 1B, which is an example of a conventional curved shaft axial piston pump. A cross-sectional view of the embodiment rotated in a 90° cutaway view; FIG. 2 is a partially cutaway perspective view of an exemplary embodiment of a conventional coaxially driven axial piston pump; FIG. 3 is a curved shaft variable transport coaxial drive according to one of the configurations. A perspective view of one exemplary embodiment of an axial piston pump and motor, wherein the housing is illustrated as being transparent to reveal internal components; and FIG. 3A is an exemplary curved shaft variable delivery coaxially driven axial piston pump And a perspective view of one of the rotating components of the motor, and FIG. 3B is a perspective view of an exemplary distribution plate; FIG. 4 is a side view of an exemplary curved-shaft variable-conveying coaxially driven axial piston pump and motor, wherein The housing is illustrated as transparent to reveal internal parts; Figure 5 is an exemplary curved shaft variable delivery coaxial drive axial piston pump and one side of the motor Figure 5A is an enlarged side perspective view of an exemplary curved shaft variable delivery coaxial drive axial piston pump and motor showing certain details of its yoke assembly; Figure 6 includes Figures 6A through 6G, A series of partially transparent perspective views of a rotating and movable assembly used as an exemplary flexure-shaft variable-conveying coaxial drive axial piston device for a pump, wherein the yoke is moved to a different angular position; Figure 7 includes Figure 7A to Figure 7G is a series of partially transparent perspective views of a rotating and movable assembly of an exemplary curved-shaft variable-transport coaxial drive axial piston assembly for use as a motor with its yoke moved to a different angular position; Figure 8 includes 8A and 8B are schematic diagrams showing a kinetic energy recovery system and/or a hydraulic hybrid drive system in parallel and in a series configuration, and FIG. 9 includes FIGS. 9A to 9H, which are shown in a kinetic energy recovery system. A series of partially transparent perspective views of a rotating and movable assembly of an exemplary curved-shaft variable-conveying coaxial drive axial piston device for use as a pump and motor in a hydraulic hybrid drive system, in Figure 9 The difference between A and FIG. 9H is that the yoke moves to a different angular position.

In the figures, where an element or feature is shown in the above figures, the same reference numerals may be used to mark the element or feature in each figure, and a closely related or modified In the case of components, the same alphanumeric mark can be apostrophed to mark the modified component or feature. In accordance with the general practice, various features of the drawings are not to scale, and the dimensions of the various features may be arbitrarily expanded or reduced for clarity, and any value recited in any figure is merely an example.

The curved shaft variable delivery coaxial drive axial piston pump and/or motor 100 in accordance with one aspect of the present configuration is substantially different than both a conventional curved shaft axial piston pump and a conventional coaxially driven axial piston pump. In this configuration, the pump and/or motor assembly 100 has its drive connection at its end of the valve plate 120, and unlike the conventional curved shaft axial piston pump and conventional The coaxial drive axial piston pump has a drive connection at the drive plate or swash plate. Therefore, when the device 100 is used as a pump 100, a driving device (for example, an electric motor or other motor 175) is connected at the end of the valve plate 120 and mounted in a fixed manner, and when the device 100 is used as a motor 100, The output drive shaft member 170 is at the end of the distribution plate 120 and can be fixedly coupled to a driven load. If the device 100 is used as both a pump and a motor, the input drive and the output to a load are connected at the shaft member 170. Since the yoke 160 of the device 100 can be operated "over the center", that is, at both positive and negative angles with respect to the axis of rotation of the cylinder block 130, the device 100 can operate in both directions and can operate as a motor and A bunch of both. Furthermore, since the internal friction is rolling friction and is not viscous friction, the device 100 can operate at low speed and operate with high mechanical efficiency.

In addition, the rotating cylinder block 130 is coaxial with the drive shaft member, and the yoke 160 and the mandrel 150 are configured in a curved axis and are pivoted to provide the only part of variable delivery (variable displacement), thereby achieving a reduction. Small size (volume) while maintaining some of the efficiency advantages of a curved shaft configuration because the drive shaft and drive motor or load are coupled at the end of the distribution plate 120 and do not require pivoting. Moreover, the pivotable yoke 160 and mandrel 150 of the present device 100 have lower inertia and thus can be pivoted more easily and more quickly, thereby beneficially improving the response of the device 100 to allow for a faster change in delivery volume.

Since the device 100 can operate at a yoke angle of at least about ±30°, it can provide a greater displacement than a comparable size one of the conventional curved shaft pumps or a conventional coaxial drive pump, for example, greater fluid flow. A conventional coaxially driven axial pump is not capable of providing a yoke across the center as the device 100 does.

Thus, a device 100 can be used as a pump or as a motor, or as both a pump and a motor, and can be operated across the center of the yoke 160 in either or both applications to provide a The variable delivery (variable displacement) pump 100 and/or a reversibly variable delivery (variable displacement) motor 100 are reversed. In other words, when the device 100 is used as a pump, the direction of fluid flow generated by the pump 100 can be reversed by pivoting the yoke 160 without changing its drive shaft member. The direction of rotation of 170, and when the apparatus 100 is used as a motor, can reverse the direction of rotation of the drive shaft member 170 by pivoting the yoke 160 without changing the direction of flow of the drive fluid through the distribution plate 120.

Still further, the unique piston rod 140, mandrel 150 and yoke 160 configuration of the device 100 can provide a smaller size and weight (which is typically associated with a coaxially driven axial piston pump) and also has a higher One of the volume and torque efficiencies of the pump and/or motor 100, higher volume and torque efficiency are typically associated with a curved shaft axial piston pump.

3 is a perspective view of one exemplary embodiment of a curved shaft variable delivery coaxially driven axial piston pump and/or motor 100 in accordance with one aspect of the present configuration, wherein its housings 180, 190 are illustrated as being transparent to reveal FIG. 3A is a perspective view showing one of the exemplary curved shaft variable transport coaxial drive axial piston pumps and/or the rotating assembly of the motor 100, and FIG. 3B is a perspective view of an exemplary distribution plate 110. . Apparatus 100 includes a non-rotating distribution plate 110 having fluid passages 117a, 117b in fluid communication with two fluid ports 120 via openings 112a, 112b, respectively, which are generally radially spaced apart by approximately 180°. The positioning, through its fluid, enters and exits the device 100. The distribution plate 110 has two fluid passages 117a, 117b, each fluid passage having one of the two turns 120a, 112b and having an arcuate chamber 117a, 117b having a rotary cylinder block 130 The bore 133 of the cylinder 132 is an arcuate slot or opening in the cylinder seat surface 116 in fluid communication therewith for less than 180° of each 360° rotation of the cylinder block 130. Dispenser 110 is disposed in a cavity in housing 180, for example, in its central portion 184, with its fluid passage in fluid communication with bore 120. The distribution plate 110 has a shaft member 170 therethrough and freely rotates a central opening 115.

The cylinder block 130 rotates relative to the valve plate 110 about a shaft 102 that is perpendicular to the distribution plate 110 and coaxial with the rotational drive shaft 102 of the drive shaft member 170. The shaft member 170 extends through the housing 180 and the seal 172 and the bearing 174 therein, through the opening 115 of the distribution plate 110, into the cylinder block 130. Typically, the cylinder block 130 has a central opening into which the end of the shaft member 170 extends and engages the cylinder block 130 (e.g., by engagement of respective splines 171, one or more keys and slots or other physical features 171 thereof). . Therefore, the cylinder block 130 engages the shaft member 170 and rotates therewith. Preferably, the shaft member 170 is tightly coupled to the cylinder block 130 and is rotated as a unit radially supported at two locations, for example, by a pair of spaced apart bearings 136, 174.

The cylinder block 130 has a plurality of axial cylinders 132, each of which preferably has a cylinder bore 133 at one end thereof that alternately alternates with each of the two fluid passages of the valve disc 110 as the cylinder block 130 rotates. The fluid is connected. Preferably, the cylinder block 130 has an odd number of cylinders 142, typically seven, nine or eleven cylinders, and preferably nine cylinders. In each of the cylinders 132 of the cylinder block 130 is a piston 142 that is axially movable therein and has a link 140 coupled at one end thereof. As each piston 142 moves away from the distribution plate 110, fluid flows from one of the fluid passages of the distribution plate 110 into the cylinder 132 containing the piston 142, and as each piston 142 moves toward the distribution plate 110, fluid flows from the cylinder 132. In the other fluid passage to the distribution plate 110, such that for each rotation of the cylinder block 130, each piston 142 performs a reciprocating cycle during which fluid moves from one fluid passage of the distribution plate 110 to the other fluid passage. And thereby moving between one 埠120 and another 埠120. If the apparatus 100 is used as a pump 100, the piston 142 driven in synchronism with the rotation of the cylinder block 130 reciprocates to move (pump) the fluid. However, if the apparatus 100 is used as a motor 100, the fluid moves under pressure through the crucible 120 and the distribution plate 110 to drive the piston 142 in reciprocating motion, thereby imparting rotational motion to the cylinder block 130.

The device 100 has one or more of the housing portions 180 (eg, one or more of the shaft housings 180 and one of which can be mated and attached at their respective mounting plates or flanges, for example) by a plurality of fasteners The yoke housing 190) provides a housing. At least a portion of the distribution plate 110 and the cylinder block 130 generally reside in a shaft housing 180 through which a drive shaft member 170 passes, the drive shaft member 170 providing a cylinder block 130 and a drive source (eg, a motor 175) (when A device between the device 100 as a pump or a load (when the device 100 is used as a fluid-driven motor) connection. Therefore, the cylinder block 130 and the drive shaft member 170 are in a coaxial drive-like configuration. However, in this configuration, the drive shaft member 170 drives the opening 115 through one of the distribution plates 110 and is not connected to or supports a drive plate or A swashplate.

A pivotable yoke 160 and a rotatable mandrel 150 that can be rotated on the yoke 160 typically reside in the yoke housing 190. The yoke mandrel 150 rotates with the cylinder block 130 and pivots (or rotates) with the yoke 160. The yoke 160 generally includes a generally circular yoke plate 160P on which the mandrel 150 is rotatably mounted and a pair of yoke arms 164 extending from the yoke plate 160P, thereby defining a yoke 160. Each yoke arm 164 is coupled to, for example, one of the inner ring members of the yoke bearing 162, and the outer ring member of the yoke bearing 162 is supported by the yoke housing 190. Typically, each yoke or bearing plate 164 has a circular opening, for example one of the inner ring members in which the yoke bearing 162 is disposed, and the yoke housing 190 has a corresponding recess in one of the outer ring members in which the yoke bearing 162 is disposed. .

The yoke 160 is thus pivotable on a coaxial yoke bearing 162 whose axis defines a yoke pivot axis 163 that is perpendicular to and intersects the rotational axis 102 of the cylinder block 130 and the drive shaft member 170. When the yoke 160 and the rotatable mandrel 150 thereon pivot, the axis of rotation 161 of the mandrel 150 defines a plane that also includes the cylinder block 130 and the axis of rotation 102 of the drive shaft member 170 and the yoke pivot axis 163 is perpendicular thereto. Thus, the rotatable mandrel 150 is in a variable angular relationship with the axis 102 of the cylinder block 130 at an angle A, for example, in a curved axis configuration. The pivoting of the yoke 160 causes a corresponding pivoting of the mandrel 150 that can be rotated thereon, with the result that the angle A between the axis of rotation 161 of the mandrel 150 and the axis of rotation 102 of the cylinder block 130 is varied, thereby changing the link 140 And the distance traveled by the piston 142 during reciprocation and correspondingly changes the displacement of the pump and/or motor 100.

An assembly of apparatus 100 including at least cylinder block 130, connecting rod 140, piston 142, and mandrel 150 may be referred to as a "rotating group" because all of the components in device 100 rotate together as a unit during operation. However, in some cases, the yoke 160 can also be considered part of the rotating group, for example, because the mandrel 150 can be provided to be rotatably mounted to the yoke 160 in the form of a typical replacement component. . The assembled components 130, 140, 150 and One or more of the rotating groups are used as a replacement component so that they can be easily replaced as a unit or group, whether this portion will be used for transactions, or for an authorized repair and maintenance agent or factory or both.

4 is a side elevational view of an exemplary curved shaft variable delivery coaxial drive axial piston pump and/or motor 100 with its housings 180, 190 illustrated as being transparent. Additional details of the foregoing description of the pump and/or motor 100 can be seen. It can be seen that the shaft housing 180 has a shaft housing base 182 that can be used to mount the pump and/or motor 100, has a central portion 184 for the shaft member 170 and one of the apertures 185 of the associated component, and is adapted to receive the flow therein. The disk 110 and the crucible 120 and the yoke housing 190 are attached to one of the distribution plate receiver portions 186. The jaws 120 can be press fit to threadably or otherwise be disposed in the valve housing portion 186 for coupling to and sealing to the weir opening 112 of the valve plate 110.

The bore 185 in the central portion 184 of the shaft housing 180 has a larger outer diameter portion in which a shaft seal 172 and a shaft member bearing 174 (for supporting and sealing the drive shaft member 170 therein) are disposed. And the shaft member 170 passes therethrough to then pass through the drive opening 115 of the distribution plate 110 to engage the cylinder block 130 such that the cylinder block 130 rotates with the drive shaft member 170 by a smaller inner diameter portion.

The yoke housing 190 has a base portion corresponding to the distal end of the receiver portion 186 of the shaft housing 180 for mating thereto, for example, by screws, bolts or other fasteners in its corresponding aperture. The yoke housing 180 has a housing cover portion 194 extending from its housing base 192 to define a cavity in which a pivotable yoke 160 is disposed, wherein the cavity is sufficiently sized to permit full pivoting of the yoke 160, for example, The pivot axis 102 is pivoted relative to the rotational axis 102 of the cylinder block 130 to a pivot angle A of at least about ±30° for varying the displacement of the pump and/or motor 100 in proportion to the pivot angle.

The yoke housing cover 194 can have an opening 195 through which a mechanical connection can be made from the exterior of the pump and/or motor 100 to one of the arms of the yoke 160 for causing the yoke 160 to rotate relative to the cylinder block 130. 102 moves to the desired pivot angle A. Mechanical connections to it can include (for example) mechanical linkages, rotatable shafts, flexible shafts, lever handles, hydraulic linkages and equipment, electric motors, stepper motors, solenoids, electronic controls and the like, such as in pumps and / or any particular use of the motor 100 is suitable and convenient.

While the yoke 160 and the mandrel 150 thereon are illustrated as being pivoted to an exemplary angular position, they are pivotable relative to the rotational axis 102 of the cylinder block 130 to a pivot angle A of at least about ±30° Any angular position is used to obtain a particular displacement of one of the pump and/or motor 100. When the angle A is zero, for example, the shafts 102 and 163 are substantially aligned, and the piston rod 140 and the piston 142 do not move with the rotation of the cylinder block 130 and the mandrel 150, and thus the displacement of the device 100 is zero, and No fluid is pumped when the device 100 is used as a pump 100 and there is no motion when the device 100 is used as a motor 100.

When the yoke 160 is pivoted in a first direction to increase the angle A relative to the drive shaft 102, for example, the angle A becomes a positive value, the flow direction of the fluid between the cymbals 120 and the cylinder block 130 and the mandrel 150 There is a defined relationship between the directions of rotation. However, when the yoke is pivoted in one direction opposite to the first direction to increase the angle A, for example, the angle A becomes a negative value, the flow direction of the fluid between the cymbals 120 and the cylinder block 130 and the mandrel 150 There is an inverse relationship between the directions of rotation. Therefore, the device 100 is reversible regardless of whether it is used as a motor 100 or a pump 100.

5 is a side cross-sectional view of an exemplary curved shaft variable delivery coaxial drive axial piston pump and motor 100, and FIG. 5A is an enlarged side cross-sectional view showing certain details of the yoke assembly 160. It can be seen that the drive shaft member 170 is disposed through the shaft housing 180 and the valve plate 110 to engage the cylinder block 130 (e.g., via axial spline engagement) with the cylinder block 130 rotating thereabout about the shaft 102. The cylinder block 130 is supported by and rotated on a cylinder block bearing 136 which is held in position by a bearing spring plate 138.

Between the bearing spring plate 138 and the bearing 136 is a spring 137, such as a wave spring or a Belleville spring, which urges the cylinder block 130 toward and against the valve disc 120, thereby minimizing fluid leakage and at the device. 100 allows fluid to be established when not under fluid pressure pressure. The fluid pressure in the cylinders 132 and cylinder bores 133 (which have a smaller diameter than the cylinders 132) provides a force that tends to urge the cylinder block 130 toward and against the valve disc 120 when the apparatus 100 is in operation.

The shaft seal 172 in the larger diameter portion of the bore 185 can include a seal carrier 172C having respective sealing gaskets or other sealing materials that carry sliding and sealing contact with the rotatable drive shaft member 170. One or more cylindrical recesses 172G. It can be seen that the shaft member bearing 174 is, for example, a ball or roller type bearing in which an inner ring member abuts the shaft member 170 and an outer ring member abuts the shaft member housing 180 whereby the shaft member 170 rotates about the drive shaft 102.

It can be seen that the cylinder block 130 has a plurality of axial cylinders 132 therethrough, one of which is visible. The cylinder 132 has a cylinder bore 133 at its end adjacent to the distribution plate 110, which cylinder bore 133 typically has a smaller diameter than the cylinder 132. It can be seen that one of the pistons 142 of one of the cylinders 132 has a generally spherical socket at its end remote from the distribution plate 110. Visible link 140 has generally spherical ends 144, 146, one of which is retained in one of generally spherical sockets 143 of piston 142, for example, by being squeezed or otherwise retained therein, and the other end 146 therein. The plate 153 is held in a generally spherical socket 153 of one of the rotatable mandrels 150, for example, by attachment to the yoke mandrel 150 and one of the plates 152.

Since each end of each link 140 has a generally spherical ball and socket arrangement, each link 140 can position itself in a low strain position relative to a respective piston 142 and yoke mandrel 150, thereby The rotation of the cylinder block 130 and the spindle 150 is synchronously moved and partially transmitted to maintain the synchronous rotational movement while causing the reciprocating movement of the piston 142 in the cylinder 132 synchronized with the rotation of the cylinder block 130 and the spindle 150. The link 140 can have a central axial passage, for example, for allowing fluid to pass therethrough, for example, to provide lubricant to the mandrel 150 and the rod end 146 therein.

Since the pump/motor assembly 100 includes a curved shaft-like geometry, the total effective displacement of the piston 142 and the cylinder block 130 is the diameter of the piston 142 in the mandrel 150 socket 153. A function, rather than a function of the diameter of the circle 142 of the piston 142 in the cylinder 132 of the cylinder block 130. Since the piston 142 is miterally connected in a curved axis geometry, the yoke bearing pocket 153 of the yoke 160 spindle 150 has a circular diameter (by geometric necessity) that is greater than the diameter of the piston circle in the cylinder block 130. Due to the slanting of the piston circle to the yoke core, the coaxially driven bending shaft pump/motor unit 100 has the advantage of a larger diameter than the diameter of the piston circle. Thus, the flow advantage with an increased maximum yoke angle A is advantageously further increased by the diameter of the mitered core bearing pocket 153 of the present curved shaft geometry.

The unidirectional coupling rod 200 connects the end of the drive shaft member 170 with the spindle 150 on the yoke 160. It is believed that the universal joint rod 200 does not transmit a substantial amount of torque between the cylinder block 130 and the mandrel 150, but acts to ensure its synchronous rotational motion.

In particular, when the apparatus 100 is used as a pump 100, the cylinder block 130 is rotationally driven by the drive shaft member 170 and the link 140 transmits a force that tends to cause the spindle 150 to follow the cylinder block 130, thereby causing it to rotate synchronously. motion. When the apparatus 100 is used as a motor 100, the pressure of the fluid transferred between the bores 120 via the cylinders 132 of the rotating cylinder block 130 imparts a force to the piston 142, causing it to reciprocate, and the link 140 transmits the force from the piston 142. To the mandrel 150 such that it rotates and the synchronous rotational motion of the cylinder block 130.

The mandrel 150 has a plurality of generally spherical sockets 153 that receive a generally spherical end 146 of the link 140 that is retained therein by one of the piston rod compression plates 152 attached to the mandrel 150 and rotated with the mandrel 150. The mandrel 150 rotates on the end plate 160 of the yoke 160 and is axially supported by an axial bearing 154 and is radially supported by a radial bearing 156 that is seated in a spherical race 157. The bearing 156 is preferably housed in a radial needle bearing of a spherical race 157 having a cylindrical thrust roller bearing 154 on its side, the combination of which is often provided to tolerate, for example, the mandrel 150 and/or the yoke 160. One of the misaligned bearing configurations. The low inertia yoke 160 and the low operating force required to pivot the yoke 160 complement its alignment tolerance feature.

The universal joint rod 200 includes a single rod 202 having a pair of open generally spherical balls 204, 206 at each end thereof, and a generally spherical ball residing in the cylinder body 130. One of the sockets 131 resides in one of the generally spherical sockets 151 in the mandrel 150. Each end of the coupling rod 200 is keyed to its spherical socket 131, 151 such that the coupling rod 200 constrains the cylinder block 130 and the spindle 160 to rotate together. Preferably, a spring 169 is provided to bias and abut the rod end 206 of the coupling rod 200 and bias the movable spherical socket 151 of the mandrel 150 toward the cylinder block 130. When the effective geometric length of the universal joint rod 200 changes as the pivot angle A of the yoke 160 changes, the spring 169 allows the movable socket 151 to move, for example, to allow the coupling rod 200 to pivot when the yoke 160 pivots. move". Since the mandrel 150 and the coupling rod 200 do not rotate about the same axis, the geometric length of the coupling rod 200 is the longest when the yoke 160 is at the center (for example, at a yoke angle A of 0°), and the magnitude of the angle A is The yoke 160 pivots away from the center and decreases as it increases, and is the shortest at the maximum of the angle A (e.g., at about ± 30°). In a typical example, the difference in geometric length can be about 1/8 inch (about 3 mm).

One spherical end 204 of the universal joint rod 200 is centered on the drive shaft member 170 of the yoke pivot shaft 163, the drive shaft 102 on the cylinder block 130 side, and the other end 206 of the universal joint rod 200 is pivoted to the center of the yoke pivot shaft 163. The shaft 150 and the yoke 160 side are centered. The half of the split spherical balls 204, 206 can be brought closer together, for example by a threaded connection, to reduce their diameter for placement in the respective sockets 131, 151, and then It is expanded, for example, by the threaded connection to correspond to a generally spherical outer shape to more completely fill the sockets 131, 151 and remain therein.

6 includes FIGS. 6A-6G showing a series of partially transparent perspective views of a rotating assembly of an exemplary curved shaft variable delivery coaxially driven axial piston assembly 100 for use as a pump 100 with its yoke 160 moved to Different angular positions A. In FIGS. 6A to 6G, arrows indicated by thin lines indicate, for example, an arrow driving motion applied to a device 100 serving as a pump 100 from a power source or other power source, and an arrow drawn in outline Indicates the direction and volume of the flow of the fluid produced by the pump 100. In general, the relationship between the fluid flow and rotational motion of the drive shaft member 170 and the displacement of the cylinder block 130, its rate of rotation, and the sine of the angle A between the drive shaft 102 and the yoke of the device 100 or the spindle shaft 161. Proportionate. In mathematics Upper system: FF = D x R x (sin A) x K, wherein: FF-based fluid flow, displacement of all pistons 142 in the D-system cylinder block 130, rotation rate of the R-system shaft member 170, and K-system representation One of constants for efficiency, unit conversion, and other factors.

In FIG. 6A, the yoke 160 of the pump 100 is shown moving relative to the drive shaft 102 of the pump 100 in a first direction to an angular position of angle A=+30°. In this position of the yoke 160, the pump 100 moves the fluid in a first direction at a rate proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A, which is relatively high. The fluid flow rate, as indicated by the relatively long length of the contour arrow representing the flow of fluid produced by the pump 100. The fluid flow system can be illustrated as one of the first directions of "upward" as shown in Figure 6A.

For a conventional coaxial axial pump, the fluid flow rate (and pump/motor displacement) is also a function of the swashplate angle, but the geometry is determined by the tangent of the yoke angle rather than its sine compared to the curved axis. In a newer type of conventional coaxial axial pump, the maximum practical drive offset angle (swashplate angle) is about 21° and therefore the maximum pumped volume is limited by the displacement 21°=0.383. In the present configuration of the pump/motor 100, a drive angle of up to about A = 30° is achieved and the displacement is limited by a displacement of 30° = 0.50. Thus, the pump/motor assembly 100 provides an increase in displacement of about 0.500/0.383 = 1.305 or about 30.5 percent (%) relative to the conventional cylinder and piston displacement conventional pump. In a more conventional conventional pump in which the driving offset angle is limited to about 18°, the increase in displacement is about 0.500/0.325=1.538 or about 53.88% (%) relative to the conventional pump and piston displacement. The system is quite remarkable.

Another artificial factor that favors the fluid flow rate and displacement advantages of the curved shaft geometry compared to the coaxial axial geometry relates to item D, the combined total displacement of all of the pistons in the cylinder block. For a coaxial axial geometry, one of the diameters of the piston circle in the cylinder of the item D Function, and for the bending axis geometry, the term D is a function of the diameter of the piston in the yoke socket rather than the diameter of the piston in the cylinder block. For a coaxial axial pump (which is defined by the term "coaxial"), the diameter of the piston circle is equal to the diameter of the effective yoke socket circle. However, since the piston is miterally connected in a curved axis geometry, the yoke socket diameter (due to geometric inevitability) is greater than the diameter of the piston circle in the cylinder block. Due to the slanting of the piston circle to the yoke core, the bending shaft pump has the advantage of a larger diameter than the diameter of the piston (cylinder), which is usually one of the minimum of about 8 percentage percent. value. The flow advantage with an increased maximum yoke angle is beneficially further increased by the slanted core bearing circle diameter of the curved shaft geometry.

Thus, for example, in a present pump/motor device 100 that provides the advantage of increasing one of the displacements by a factor of 30.5 percent (%), the displacement and thus its fluid flow is further increased by 1.08 times, thereby A conventional coaxial axial pump of the same piston cylinder circle and piston diameter provides a total increase of approximately 41.0% (%) more displacement (and therefore more fluid flow output). Regardless of whether the device 100 is used as a motor, or as a pump or as a device that acts as both a pump and a motor (eg, at different times and/or under different operating conditions), a similar result is obtained and advantage. In the case where the yoke 160 is pivoted to an angle of A = +30° (as in Figure 6A), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is substantially at a maximum volume, for example, its capacity. 100%, which is substantially larger than the capacity of the conventional coaxial axial pump and the conventional bending shaft pump.

In FIG. 6B, the yoke 160 of the pump 100 is shown moving relative to the drive shaft 102 of the pump 100 in a first direction to an angular position of angle A=+20°. In this position of the yoke 160, the pump 100 moves the fluid in a first direction at a rate proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A, which is relatively moderate. The fluid flow rate, as indicated by the relatively medium length of the contour arrow representing the flow of fluid produced by the pump 100. The fluid flow is also along a first direction that can be described as "upward", as shown in Figure 6B. In the case where the yoke 160 is pivoted to an angle of A = +20° (as in Figure 6B), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is The maximum volume is about 68.4%, for example, as in Figure 6A.

In FIG. 6C, the yoke 160 of the pump 100 is shown moving relative to the drive shaft 102 of the pump 100 in a first direction to an angular position of angle A=+10°. In this position of the yoke 160, the pump 100 moves the fluid in a first direction at a rate proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A, which is relatively low. The fluid flow rate, as indicated by the relatively short length of the contour arrow representing the flow of fluid produced by the pump 100. The fluid flow is also in the first direction that can be described as "upward", as shown in Figure 6C. In the case where the yoke 160 is pivoted to an angle of A = +10° (as in Figure 6C), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is about 34.7% of the maximum volume, for example, As in the volume in Figure 6A.

In Figure 6D, the yoke 160 of the pump 100 is shown moving relative to the drive shaft 102 of the pump 100 to a neutral angle position of angle A = 0°. In this position of the yoke 160, the pump 100 does not move the fluid due to the sinusoidal zero of angle A = 0, i.e., Sin 0° = 0, which is fluid free, such as the contour of the fluid flow. Indicated by the absence of an arrow. One of the yokes 160 that can be moved to both the positive and negative angular positions can be referred to as a device that can be moved or pivoted "over the center" (the center is about 0°) and has one of the yokes 160 that can be moved "crossing the center" It can be said to be able or have "cross-center operation". It is further noted that the direction of rotation of the pump 100 remains the same, that is, there is no need to reverse the direction of rotation of the shaft member 170, and the change in position of the yoke 160 at the positive and negative yoke angles is sufficient to reverse the flow of fluid at the 埠120. direction.

In FIG. 6E, the yoke 160 of the pump 100 is shown as being moved relative to the drive shaft 102 of the pump 100 in a second direction opposite the first direction to an angular position of the angle A=-10°, for example, relative to The yoke position shown in Figures 6A-6C moves across the center. In the A=-A° position of the yoke 160, the pump 100 causes the fluid to be in a direction opposite to the first direction in a volume proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A. Moving in a second direction, which is a relatively low fluid flow rate, as indicated by the relatively short length of the contour arrow representing the flow of fluid produced by the pump 100, however, the fluid The flow system is along a second direction that may be described as "downward" opposite the first direction, as shown in Figure 6E. In the case where the yoke 160 is pivoted to an angle of A = -10° (as in Figure 6E), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is about 34.7% of the maximum volume, for example, As in the volume in Figure 6A, but in the opposite direction.

In FIG. 6F, the yoke 160 of the pump 100 is shown moving relative to the drive shaft 102 of the pump 100 in a second direction opposite the first direction to an angular position of angle A=-20°. In this position of the yoke 160, the pump 100 moves the fluid in a second direction in a volume that is proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A, which is a relatively medium fluid. The flow rate, as indicated by the relatively medium length of the contour arrow representing the flow of fluid produced by the pump 100, however, the fluid flow is also along a second direction that can be illustrated as "downward", as shown in Figure 6F. . In the case where the yoke 160 is pivoted to an angle of A = -20° (as in Figure 6F), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is about 68.4% of the maximum volume, for example, As in the volume in Figure 6A, but in the opposite direction.

In FIG. 6G, the yoke 160 of the pump 100 is shown as being moved relative to the drive shaft 102 of the pump 100 in a second direction opposite the first direction to an angular position of angle A=-30°. In this position of the yoke 160, the pump 100 moves the fluid in a second direction at a rate proportional to the rate of rotation of the drive shaft member 170 and the cylinder block 130 and the sine of the angle A, which is relatively high. The fluid flow rate, as indicated by the relatively long length of the contour arrow representing the flow of fluid produced by the pump 100, however, the fluid flow is also along a second direction that can be illustrated as "downward", as in Figure 6G. Shown. In the case where the yoke 160 is pivoted to an angle of A = -30° (as in Figure 6G), the volume of fluid flow provided by the pump device 100 from the inlet to the outlet is about 100% of the maximum volume, for example, The same volume as in Figure 6A, but flowing in the opposite direction.

Thus, when used as a pump 100, the device 100 can be pivoted to the angular position only by changing the yoke 160 (eg, the yoke 160 can be pivoted across the center relative to the input drive shaft 102 to positive And both of the negative angles A) to move the fluid in either direction without changing the direction or speed of the input drive, which advantageously simplifies the drive mechanism and apparatus for use with the pump 100, thereby resulting in simplified control, Low weight, low cost and / or high reliability. Furthermore, it is only necessary to pivot the yoke 160 and the spindle 150 mounted thereon in a rotational manner, thereby reducing the size and quality of the rotating parts that must be pivotable to vary the displacement of the pump 100, and thus Reduce the total weight and cost of the pump 100.

Figure 7 includes Figures 7A through 7G which are a series of partially transparent perspective views showing a rotating assembly of an exemplary curved shaft variable delivery coaxially driven axial piston assembly 100 for use as a motor 100, wherein the yoke 160 is moved to a different Angle position A. In FIGS. 7A-7G, the arrows at the inlet (P) and outlet (R), which are outlined, are shown, for example, applied under pressure from one of the fluids of the fluid or other pressurized source to serve as a motor 100. The input fluid of device 100 is driven, and the arrows in the vicinity of shaft member 170 indicate the direction of rotation and the rate of rotation of the rotational motion generated at output shaft 170 of motor 100. In general, the relationship between the fluid flow and the rotational motion of the drive shaft member 170 that produces the torque output is related to the displacement of the cylinder block 130, its rate of rotation, and the angle A between the drive shaft 102 and the yoke or spindle shaft 161 device. The sine is proportional, as above.

In FIG. 7A, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 in a first direction to an angular position of angle A=+30°. In this position of the yoke 160, the motor 100 responds to the movement of the fluid under pressure in a first direction to produce at its drive shaft 170 and cylinder block 130 and in proportion to the sine of angle A. A proportional rotation rate, which is a relatively high rate of rotation, as indicated by the relatively long length of the arrow representing the rotation produced by motor 100, for example, and substantially 100% of the maximum available torque. The fluid flow system can be illustrated as producing a first direction of clockwise rotation as illustrated, as shown in Figure 7A.

In FIG. 7B, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 in a first direction to an angular position of angle A=+20°. At this position of the yoke 160 The motor 100 responds to the movement of the fluid under pressure in a first direction by a proportional rotation rate at its drive shaft member 170 and cylinder block 130 and proportional to the sine of the angle A. It is a relatively moderate rate of rotation, as indicated by the relatively medium length of the arrow of rotation produced by motor 100, for example, and is about 68.4% of the maximum available torque. The rotation of the same line can be illustrated as a clockwise first direction, as shown in Figure 7B.

In FIG. 7C, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 in a first direction to an angular position of angle A=+10°. In this position of the yoke 160, the motor 100 produces a proportional rotation rate at a pressure in the drive shaft member 170 and the cylinder block 130 in proportion to the sine of the angle A. The response in one direction is a relatively low rate of rotation, as indicated by the relatively short length of the arrow representing the rotation produced by motor 100, for example, and at about 37.4% of the maximum available torque. The fluid flow drive is also in the same direction that can be described as "upward" (as shown in Figure 7C) and the motor rotation is also clockwise.

In FIG. 7D, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 to a neutral angular position of angle A = 0°. In this position of the yoke 160, the motor 100 does not respond to the movement of the fluid under pressure due to the sinusoidal zero of angle A = 0, i.e., sin 0° = 0, which does not produce a rotation, such as a rotation. Indicated by the absence of one of the arrows. One of the yokes 160 that can be moved to both positive and negative angular positions can be referred to as a device that can be "crossed through the center" (the center is about 0°) and has one of the yokes 160 that can be moved or pivoted "over the center" It can be said to be able or have "cross-center operation". It is further noted that the direction of fluid flow at the crucible 120 remains the same, that is, there is no need to reverse the direction of fluid flow at the crucible 120, and the yoke 160 is at the positive and negative yoke angles (eg, across the center). The change is sufficient to reverse the direction of rotation of the motor 100.

In FIG. 7E, the yoke 160 of the motor 100 is shown as being moved relative to the drive shaft 102 of the motor 100 in a second direction opposite the first direction to an angular position of the angle A=-10°, For example, the yoke position shown in Figures 7A-7C moves across the center. In this position of the yoke 160, the motor 100 responds to the movement of the fluid under pressure in a first direction relative to the volume, thereby producing at its drive shaft member 170 and cylinder block 130 and proportional to the sine of angle A. A proportional rotation rate, which is a relatively low rate of rotation, as indicated by the relatively short length of the arrow of rotation produced by motor 100, for example, and about 37.4% of the maximum available torque, however, the rotation edge It can be illustrated as a counterclockwise one of the second directions opposite the first direction, as shown in Figure 7E.

In FIG. 7F, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 in a second direction opposite the first direction to an angular position of angle A=-20°. In this position of the yoke 160, the motor 100 responds to the movement of the fluid under pressure in a first direction to produce a displacement at its drive shaft 170 and cylinder block 130 in proportion to the sine of angle A. Proportional rotation rate, which is a relatively moderate rate of rotation, as indicated by the relatively medium length of the arrow of rotation produced by motor 100, for example, and about 68.4% of the maximum available torque, although the same line of rotation can be illustrated It is one of the counterclockwise second directions, as shown in Figure 7F.

In FIG. 7G, the yoke 160 of the motor 100 is shown moving relative to the drive shaft 102 of the motor 100 in a second direction opposite the first direction to an angular position of angle A = -30°. In this position of the yoke 160, the motor 100 responds to the movement of the fluid under pressure in a first direction to produce a displacement at its drive shaft 170 and cylinder block 130 in proportion to the sine of angle A. Proportional rotation rate, which is a relatively high rate of rotation, as indicated by the relatively long length of the arrow of rotation produced by motor 100, for example, and substantially 100% of the maximum available torque, while rotating the same line It can be illustrated as one of the counterclockwise second directions, as shown in Figure 7G.

Thus, when used as a motor 100, the device 100 can be pivoted to the angular position only by changing the yoke 160 (eg, the yoke 160 can be pivoted across the center relative to the input driven shaft 102 to both positive and negative angles A) ) to respond to the movement of the fluid in one direction under pressure without changing Varying the direction or flow of the input fluid under pressure advantageously simplifies the fluid drive mechanism and apparatus used with the motor 100, thereby resulting in simplified control, lower weight, lower cost, and/or higher reliability. Furthermore, it is only necessary to pivot the yoke 160 and the spindle 150 mounted thereon in a rotational manner, thereby reducing the size and quality of the rotating parts that must be pivotable to vary the displacement of the motor 100, and thus may be reduced The total weight and cost of the small motor 100.

Figure 8 includes Figures 8A and 8B, which respectively show a schematic and parallel configuration of a vehicle kinetic energy recovery system (KERS) 300, 300P, 300S and/or a vehicle hydraulic hybrid drive system (HHDS) 300, 300P. . The 300S employs a pump/motor device 100 as described, wherein the device 100 acts as a pump at different times and as a motor in different modes of operation. The placement of the device capable of operating as a pump or a motor at different times is controlled by the movement of the yoke 160, as explained below.

In both embodiments, engine 310 (e.g., an internal combustion engine (ICE) 310) having one of the primary sources of power has a drive shaft 312 (e.g., a crankshaft 312) coupled to one of the shaft members 170 of the apparatus 100 through which The energy is converted by the device 100 from the rotational motion/torque applied at the shaft member 170 to the energy stored in the high pressure accumulator device 380H under pressure, for example, by passing the fluid from the low pressure accumulator 380L (eg, reservoir) Pumped to a high pressure accumulator 380H (eg, a pressure storage tank). When energy stored in the high pressure accumulator 380H is required to assist the engine 310, fluid flows from the high pressure accumulator 380H to the low pressure accumulator 380L via the device 100, thereby applying additional torque to the engine 310 via the shaft 170. Drive shaft.

In the parallel hybrid system 300P of FIG. 8A, the engine 310 drives the wheels 360 via the transmission 320, the drive shaft 330, the differential gear 340, and the axle 350, as is conventional in a motor vehicle. Simultaneously and in parallel, the engine 310 can also drive the device 100 operating as a pump 100 to move fluid from the low pressure accumulator (reservoir) 380L through the fluid lines 370L, 370H to a high level at which the fluid is stored under high pressure. Pressure accumulator 380H. In addition, the vehicle The deceleration is generated via the drive shaft member 350, the differential gear 340, the drive shaft member 330, and the transmission 320 coupled through the engine 310 to drive the device 100 as a pump 100 to pass fluid through the fluid lines 370H, 370L from the low pressure accumulator The (reservoir) 380L moves to the torque of the high pressure accumulator 380H where the fluid is stored under high pressure, thereby generating braking torque at the wheel 360 while pressurizing the fluid to high pressure in the high pressure accumulator vessel 380H. The kinetic energy removed from the vehicle is stored as potential energy.

When additional torque, for example, higher than the torque available from the engine 310 is required, fluid flowing from the high pressure accumulator 380H through the fluid lines 370H, 370L to the low pressure accumulator 380L and passing through the device 100 causes the device 100 to operate as A motor 100 produces drive torque coupled to the wheels 360 via the engine 310, the transmission 320, the drive shaft 330, the differential gear 340, and the axle 350, thereby supplementing the torque available to the engine 310.

In the tandem hybrid system 300S of FIG. 8B, the engine 310 is not coupled to the wheel 360 and does not directly drive the wheel 360, and thus does not require a transmission 320, drive shaft 330, and differential gear 340 as in a conventional motor vehicle. . The engine 310 drives the device 100 operating as a pump 100 via its drive shaft 312 to move fluid from the low pressure accumulator (reservoir) 380L to the high pressure accumulator 380H where the fluid is stored under high pressure, and is available The energy that powers the vehicle. In effect, the wheel drive 100W operates in a manner similar to a hydraulic or hydrostatic type of transmission.

To accelerate the vehicle, the required acceleration torque flows from the high pressure accumulator 380H through the fluid lines 370H, 370L to the low pressure accumulator 380L and through the wheel coupling device 100W operating as the motor 100W to generate the drive from the device 100W. The shaft member 170 is fluidly coupled to the drive torque of the wheel 360 via the axle 350.

To decelerate the vehicle, the required deceleration torque is pumped by the wheel coupling device 100W operating as a pump 100W to flow from the low pressure accumulator 380L through the fluid lines 370H, 370L to the fluid being stored under high pressure. High pressure accumulator 380H whereby brake torque is generated at wheel 360 while fluid is added in high pressure accumulator vessel 380H Pressurize to high pressure to store kinetic energy removed from the vehicle as potential energy.

9 includes FIGS. 9A-9H showing an exemplary curved shaft variable delivery coaxial drive axial piston assembly for use as a pump and motor 100 in a kinetic energy recovery system and/or in a hydraulic hybrid drive system. A series of partially transparent perspective views of a rotating and movable assembly of 100 in which the yoke 160 is moved to a different angular position. In Figures 9A through 9H, the arrows, which are outlined, indicate the flow of input fluid to and from the device 100 used as a pump and motor 100, for example, in a reservoir (R). Between a hydraulic or other pressurized source (P), and the outlined arrows indicate the direction, torque, and/or rate of rotation of the rotational motion produced at the shaft 170 of the device 100, for example, the shaft 170 can Connected to, for example, a mechanical shaft or transmission or wheel for use in a kinetic energy recovery and/or hydraulic hybrid drive. In general, the relationship between fluid flow and rotational motion of the drive shaft member 170 is proportional to the displacement of the cylinder block 130, its rate of rotation, and the sine of the angle A between the drive shaft 102 and the yoke or spindle shaft 161 device. .

The kinetic energy of a moving object (eg, a truck, bus, car, train, streetcar, or other vehicle) must be reduced to slow and/or stop the item and typically use friction braking (eg, common drum or A disc brake) or a dynamic brake (for example, a drive connected to one of the resistors) dissipates as heat. In a kinetic energy recovery system, in order not to waste the removed kinetic energy, the kinetic energy is usually converted into another form and stored in a storage device, for example, as electrical energy for charging a battery or a capacitor or as a storage The rotational kinetic energy in the flywheel can later retract the stored energy from the spinning flywheel and put it into use. In a vehicle, the stored energy is typically used to drive a vehicle, such as in a blended gasoline-electric car, truck, and bus.

Since the present configuration of the device 100 allows it to be used as a pump 100 or as a motor 100 or as both a pump and a motor 100 without reconfiguring its fluid (eg, hydraulic) and mechanical connections, The apparatus 100 is suitable for use in a kinetic energy recovery system and in a Kinetic Energy Recovery System (KERS), or for a hydraulic drive (HD) or another fluid drive system Medium, and/or used in a hydraulic hybrid drive (HHD) or another fluid hybrid drive system. In a typical KERS, the HD and/or HHD system 120 of the device 100 is fluidly coupled to a pressurizable fluid container (P) and a fluid reservoir (R) for removing fluid therebetween to enable By moving the fluid to the pressurized container (P), the device 100 and the container (P) act as a storage accumulator in which kinetic energy is converted and stored in the pressurizable container (P) as pressurized Fluid, in which the fluid can be stored under pressure, and the fluid can be withdrawn from the pressurizable container (P) to use the stored energy therein as a pressurized fluid.

Figure 9A illustrates one of the KERS systems in a brake off and throttle off condition, wherein the pump/motor assembly 100 is in a zero displacement condition, for example, substantially "neutral", wherein the yoke 160 In a center or 0° or zero displacement position, wherein the shaft 161 of the yoke 160 is aligned with the shaft 102 of the drive shaft member and thus the rotation of the drive shaft member 170, if any, does not create any fluid flow at the bore 120 (no flow) And the pump/motor 100 does not provide resistance and assist torque T to the rotation ω of the shaft member 170. Thus, if the vehicle is stationary, it tends to remain stationary, and if it is moving, it tends to continue moving, for example, taxiing. The symbolic storage accumulator at the left side of Figure 9A reflects this condition, which has only a simple line at its bottom to indicate that there is no pressure or one of the fluid flow connections.

Figure 9B illustrates one of the KERS systems in a relatively mild brake on and throttle off condition, wherein the pump/motor assembly 100 is operating as a pump 100 with the yoke 160 in one of the off-center positions - In 10°, wherein the shaft 161 of the yoke 160 is rotated about -10° relative to the shaft 102 of the drive shaft member and thus the rotation of the drive shaft member creates a fluid flow at the bore 120 to pump fluid from the reservoir (R) to the outlet. The pressurizable container (P) at the crucible 120, thereby generating a torque T _B at the drive shaft member 170 in a direction opposite to the rotation ω, thereby generating a braking action. The relative magnitude of the generated torque is indicated by the relative length of the torque arrow, for example, a relatively low level of brake application generating device 100 having a relatively small displacement and a relatively low level of braking torque T _B . Therefore, if the vehicle is moving, it tends to be relatively mildly slowed by the relatively low torque T _B produced by the small displacement pumping of the device 100. The symbolic storage accumulator has a relatively short inwardly directed arrow at its bottom to indicate a pumping of a relatively low level of pressure in the pressurized container (P) due to fluid flow generated by the device 100. Thereby storing energy. The stored pressure is indicated by an arrow pointing inwardly within one of the accumulator symbols.

Figure 9C illustrates one of the KERS systems in a relatively medium brake on and throttle off condition, wherein the pump/motor assembly 100 is operating as a pump 100 with the yoke 160 in one of the off-center positions - In 20°, wherein the shaft 161 of the yoke 160 is rotated about -20° relative to the shaft 102 of the drive shaft member and thus the rotation ω of the drive shaft member creates a fluid flow at the bore 120 to pump fluid from the reservoir (R) to The pressurizable container (P) at the outlet 埠 120, thereby generating a torque T _B at the drive shaft member 170 in a direction opposite to the rotation ω, thereby generating a braking action. The relative magnitude of the generated torque T _B is indicated by the relative length of the torque arrow, for example, a relatively intermediate level of braking application produces a relatively intermediate displacement of the apparatus 100 and a relatively intermediate level of braking torque. Thus, if the vehicle is moving, it tends to be relatively moderately slow due to the relatively intermediate torque produced by the intermediate displacement pumping of the device 100 and due to the braking torque T _B produced by the pumping motion of the device 100. The symbolic storage accumulator has an inwardly directed arrow at its bottom relative to the intermediate length to indicate that one of the pressures in the pressurized container (P) is increased relative to the intermediate level due to fluid flow generated by the device 100. Pumped to store energy. The stored pressure is indicated by an arrow pointing inwardly within one of the accumulator symbols.

Figure 9D illustrates one of the KERS systems in a relatively heavy brake on and throttle off condition, wherein the pump/motor assembly 100 is operating as a pump 100 with the yoke 160 in one of the off center positions -30°, wherein the shaft 161 of the yoke 160 is rotated about -30° relative to the axis 102 of the drive shaft member 170 and thus the rotation of the drive shaft member creates a fluid flow at the bore 120 to pump fluid from the reservoir (R). The pressurizable container (P) to the outlet port 120, thereby generating a torque T _B at the drive shaft member 170 in a direction opposite to the rotation ω, thereby generating a braking action. The relative magnitude of the generated torque T _B is indicated by the relative length of the torque arrow, for example, a relatively high level of brake application generating device 100 having a relatively high displacement and a relatively high level of braking torque T _B . Thus, if the vehicle is moving, it tends to slow down relatively more quickly due to the relatively high torque T _B produced by the higher displacement pumping of the device 100. The symbolic storage accumulator has a relatively long inwardly directed arrow at its bottom to indicate an increase in the relatively high level of pressure in the pressurized container (P) due to fluid flow generated by the device 100. Transport, thereby storing energy. The stored pressure is indicated by an arrow pointing inwardly within one of the accumulator symbols.

Figure 9E illustrates one of the KERS systems in a brake off, throttle off, and KERS non-command condition, where the system can, for example, be regenerated from a pattern (eg, pumped to draw fluid under pressure) Pumping into a storage container (accumulator) to recover kinetic energy) is converted to a boost or drive mode, for example, where energy recovered from the braking operation is stored in a pressurized container (P) for providing drive torque. Under this condition, the pump/motor assembly 100 is under a zero displacement condition, for example, substantially "neutral", wherein the yoke 160 is illustrated as being in the center or 0° or zero displacement position, wherein the yoke The shaft 161 of 160 is aligned with the shaft 102 of the drive shaft member and thus the rotation ω (if any) of the drive shaft member 170 does not create any fluid flow (no flow) at the bore 120, and the pump/motor 100 is not aligned with the shaft member 170. Rotation provides resistance and assistance. Thus, if the vehicle is stationary, it tends to remain stationary, and if it is moving, it tends to continue moving, for example, taxiing. The symbolic storage accumulator at the left side of Figure 9A reflects this condition, which has only a simple line at its bottom to indicate that there is no pressure or one of the fluid flow connections.

Figure 9F illustrates one of the KERS systems in a brake-off, relatively gentle throttle-on and KERS commanded condition, wherein the pump/motor assembly 100 is operating as a motor 100 to move energy from the accumulator to A load. Under this condition, the yoke 160 is illustrated as being in one of the off-center positions +10°, wherein the shaft 161 of the yoke 160 is rotated about 10° relative to the shaft 102 of the drive shaft member and thus from the pressurized container (P The fluid flow at the crucible 120 generated by the pressurized fluid flowing to the reservoir (R) to generate the torque T _D produces a rotation ω of the drive shaft member 170, whereby the torque T _D generated at the drive shaft member 170 A direction of rotation ω of the drive shaft member 170 is increased, thereby generating a drive or acceleration action. The relative magnitude of the generated torque is indicated by the relative length of the flow and torque arrows. For example, a relatively low level throttle application produces a relatively small displacement of the apparatus 100 and a relatively low level of drive torque. Accordingly, when the vehicle is moving, which is often due to a small displacement from the apparatus 100 of generating operation of the motor driving torque T _D is relatively low and relatively mild accelerated. The symbolic storage accumulator has a relatively short outwardly directed arrow at its bottom to indicate a decrease in pressure in the pressurized container (P) to produce a relatively low level of fluid flow through the device 100. Thereby recovering the previously stored energy. The reduced stored pressure (emission) of the accumulator is indicated by an outwardly directed arrow within the accumulator symbol.

Figure 9G illustrates one of the KERS systems in a brake-off, intermediate throttle-on, and KERS condition, where the pump/motor assembly 100 is operating as a motor 100 to move energy from the accumulator to a load. Under this condition, the yoke 160 is illustrated in a position at 20° from the center position, wherein the shaft 161 of the yoke 160 is rotated about 20° with respect to the shaft 102 of the drive shaft member and thus from the pressurized container (P) The fluid flow at the crucible 120 generated by the pressurized fluid flowing to the reservoir (R) to generate torque produces a rotation ω of the drive shaft member 170, whereby the torque T _D generated at the drive shaft member 170 is increased in drive. One direction of rotation ω of the shaft member 170, thereby generating an acceleration action. The relative magnitude of the generated torque T _D is indicated by the relative lengths of the flow and torque arrows. For example, a relatively intermediate level throttle application produces an intermediate displacement and an intermediate level of drive torque for the apparatus 100. Accordingly, when the vehicle is moving, which is often due to the displacement of the motor 100 from the middle of the operation of the apparatus relative to the intermediate level generating driving torque T _D of relatively moderately accelerated. The symbolic storage accumulator has an outwardly directed arrow at its bottom opposite the intermediate length to indicate a reduction in the pressure in the pressurized container (P) to create an intermediate level of fluid flow through the device 100. Flow out to recover previously stored energy. The reduced stored pressure (emission) of the accumulator is indicated by an outwardly directed arrow within the accumulator symbol.

Figure 9H illustrates one of the KERS systems in a KERS condition with a brake off, relatively high throttle on, and the pump/motor device 100 is operating as a motor 100 to move energy from the accumulator to a load . Under this condition, the yoke 160 is illustrated in a position at 30° from the center position, wherein the shaft 161 of the yoke 160 is rotated about 30° relative to the shaft 102 of the drive shaft member and thus from the pressurized container (P) The fluid flow at the crucible 120 generated by the pressurized fluid flowing to the reservoir (R) to produce the torque T _D produces a rotation ω of the drive shaft member 170, whereby the torque T _D generated at the drive shaft member 170 is along One direction of the rotation ω of the drive shaft member 170 is increased, thereby tending to generate an acceleration action. The relative magnitude of the generated drive torque T _D is indicated by the relative length of the flow and torque arrows. For example, a relatively high level throttle application produces a relatively high displacement of the device 100 and a relatively high level of drive torque. . Accordingly, when the vehicle is moving, which is often due to a relatively high from the apparatus 100 of generating operation of the motor displacement relatively high level of driving torque T _D is relatively strongly accelerated. The symbolic storage accumulator has a relatively long outwardly directed arrow at its bottom to indicate that the pressure in the pressurized container (P) is reduced to produce a relatively high level of fluid flow through the device 100. Thereby recovering the previously stored energy. The reduced stored pressure (emission) of the accumulator is indicated by an outwardly directed arrow within the accumulator symbol.

In an exemplary embodiment, one of the maximum displacements having a maximum displacement of about 0.5 cubic feet per revolution (about 8.2 cc/rev.) may be about 4 inches (about 10.2 cm) in diameter and length. It can be about 6 inches (about 15.2 cm) and can weigh about 4.5 pounds (about 2.05 Kg). When used as a pump 100, rotating the shaft member 170 at about 6500 rpm produces a head pressure of about 5000 psi (about 351.5 Kg/cm ² ) at a pressure of about 4800 psi (about 337.4 Kg/cm ² ). (no flow) or one pumping volume of approximately 14 gallons per minute (approximately 53 liters per minute). When used as a motor 100, one of the input fluid pressures of about 5000 psi (about 351.5 Kg/cm ² ) at the weir 120 produces a torque of about 33 feet-pounds (about 4.57 Kg-m) at the shaft member 170. And one of about 14 gallons per minute (about 53 liters per minute) of fluid flow through the crucible 120 causes the shaft member 170 to rotate at about 6500 rpm.

Typically, the housings 180, 190 can be aluminum, aircraft grade aluminum, titanium, steel, stainless steel, carbon fiber reinforced compositions, or other suitable materials. The distribution plates 110 and 埠120 can be steel, hardened steel, stainless steel, coated titanium. , carbon-graphite (CAGR), tantalum carbide (SiC) or other suitable material, the cylinder block 130 may be bronze, ductile iron, aluminum or other suitable metal, for example, preferably a soft metal, the piston 142 and the connecting rod 140 may be High-strength steel or stainless steel with a wear-resistant coating, titanium with a wear-resistant coating or other suitable metal and wear-resistant coating, the mandrel 150 can be high-strength bearing steel or stainless steel, titanium or other suitable metal, yoke 160 can be high-strength steel or stainless steel, titanium, aluminum or other suitable metal, the drive shaft 170 and the universal joint rod 200 can be high-strength steel or stainless steel with a wear-resistant coating, titanium with a wear-resistant coating Or other suitable metal and wear resistant coatings. Examples of wear resistant coatings include high velocity oxidative flame spraying, chrome plating, and the like.

Thus, apparatus 100 in accordance with the present configuration can generally have a lower weight and comparable volume compared to conventional axial coaxial pumps and motors of similar capacity, while having a similar high efficiency of a bending axis axial pump (eg, , volume, torque and volumetric efficiency) and higher displacement, and can be used as either or both of a pump and a motor, both of which can be operated across a central variable displacement. When used as a pump, a device 100 will generally be more economical, have less power extraction and generate less heat, and operate smoothly, typically due to the relatively high incidence of rolling interfaces and the low sliding interface. Rate, relatively little pre-compression and decompression. When used as a motor, a device 100 will typically produce more torque at lower pressures and lower fluid flow, and will tend to operate smoothly with minimal viscous friction.

When the device 100 is used in place of a conventional electro-hydraulic actuator (EHA) pump, it is typically used with a conventional fixed displacement bending axis EHA pump (for which it is necessary to reverse the direction of rotation of the drive to reverse the gang In contrast to the operation of the device, the device 100 is expected to provide a frequency response of at least about 8 to 10 times higher, for example, an order of magnitude improvement, which is provided by the mandrel 150 that can be rotated on the yoke 160 across the center. Turn feature. Note that a conventional coaxial axial pump cannot be used as an EHA pump because it cannot operate in the opposite direction and cannot be effective. Ground across the center.

In addition, the power required to reverse drive a conventional EHA pump is not only much higher (e.g., about twice as much) as the power required to move the yoke 160 of the device 100 across the center, and when a faster response is required The increase, and thus the device 100, can be not only smaller and lighter, but also reduces the requirements for drive motors, power, wiring, and the like. In addition, there may be substantially less wear in the fixed direction of operation of the device 100, as it may operate at a smaller yoke angle than a fixed displacement device, and may be simpler than using an EHA pump with one of the reverse drive The control algorithm operates because the drive motor 175 operates at a constant speed in one direction.

In an aircraft or other power transfer unit (PTU) application, the device 100 can also replace a conventional fixed displacement bending shaft pump in which the pumping volume is achieved by varying the speed of the drive (eg, an electric motor). The direction of the change, the conventional pump produces the same shortcomings as the above disadvantages of an EHA pump. When replacing a conventional EHA pump in a PTU, the device 100 can provide similar advantages such as lower drive power, faster response, smaller size and lighter weight, and simpler control.

A curved shaft variable displacement coaxial drive device 100 can include: a distribution plate 110 having a seat for receiving a rotatable cylinder block 130 therein, and having at least two fluid passages, each fluid passage coupled to one Each fluid channel 120 and each fluid channel has an arcuate opening corresponding to a portion of less than 180° different from one of the circles; a cylinder block 130 adjacent to the seat of the valve plate 110 is rotatably mounted for rotation about an axis The cylinder block 130 has a circular array of axial cylinders 132 each having a seat at one of its seats adjacent the distribution plate 110 and positioned for different rotational positions in the rotation of the cylinder block 130. An opening is alternately in fluid communication with each of the two fluid passages; a rotatable shaft member 170 coupled through the opening in the distribution plate 110 to the cylinder block 130 for rotation therewith; a plurality of pistons 142 And disposed in the cylinder 132 of the cylinder block 130 for reciprocating therein, each piston having one end of the cylinder block 130 opposite to the distribution plate 110 Extending a link 140; a rotatable mandrel 150 having a circular array of receptacles for receiving respective ends of the link 140; a pivotable yoke 160 having a rotatably mounted thereto The upper mandrel 150 is for rotating about an axis, wherein the mandrel 150 and the plurality of pistons 142 disposed in the cylinder block 130 are connected by the link 140 for rotation together, and the yoke 160 is pivotable for the mandrel 150 The rotating shaft is rotated by an angle with respect to the rotational axis of the cylinder block 130. The opening 133 at the seat end of each axial cylinder 132 may have a smaller diameter than the axial cylinder 132, whereby the operating pressure urges the cylinder block 130 toward the valve disc 120; or a spring 169 may urge the cylinder block toward the valve disc 120 130; or the opening 133 at the seat end of each axial cylinder 132 may have a diameter that is smaller than the axial cylinder 132 and a spring 169 may urge the cylinder block 132 toward the distribution plate. The device 100 can further include a compression plate 152 attached to the rotatable mandrel 150 and rotatable therewith, wherein the compression plate 152 retains the ends of the links 140 in respective receptacles of the rotatable mandrel 150. Each link 140 can include: at least one of the spherical balls 144, 146 disposed in one of the pistons at one end of the link 140; or at least at the other end of the link 140 is rotatable One of the spherical balls 144, 146 in the receptacle of the mandrel 150; or one of the spherical balls 144, 146 disposed in one of the sockets of the piston at one end of the link 140 and at the other end of the link 140 One of the spherical balls 144, 146 disposed in the receptacle of the rotatable mandrel 150. The apparatus 100 can further include a universal joint rod 200 coupled to at least one of the shaft member 170 and the cylinder block 130 at one end and to one of the rotatable mandrels 150 at the other end. The universal joint rod 200 may include: at least one of the split spherical balls 204, 206 disposed in one of the shaft members 170 and one of the cylinder blocks 130 at one end of the universal joint rod 200; or At least one of the split spherical balls 204, 206 disposed in one of the sockets at the rotatable mandrel at the other end of the universal joint rod 200; or at each end of the universal joint rod 200 One of the pivotal balls 204, 206 in one of the shaft member 170 and the cylinder block 130 and the respective socket at the rotatable mandrel 150. The rotatable mandrel 150 can include: a movable socket 151 for receiving one end 206 of the universal joint rod 200, wherein the movable socket 151 is axially movable relative to the rotatable mandrel 150; and a spring 169, which can face 10,000 The coupling rod 200 is biased to the movable socket 151, whereby the movable socket 151 is moved to change the effective geometric length of one of the universal joint rods 200 when the pivotable yoke 160 is pivoted. The yoke 160 can include a pair of bearing plates 164 for rotatably supporting and extending from one of the bases of the rotatable mandrel 150, wherein the yoke 160 is pivotally supported by one of the bearing plates 164 coupled to the yoke 160 Transfer mode support. The yoke 160 can be pivoted by the torque applied at its bearing plate 164. The mandrel 150 can be rotatably supported on the yoke 160 by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The apparatus 100 may further include a shaft housing 180 that supports the valve plate 110 in a fixed manner and rotatably supports the shaft member 170 and the cylinder block 130. The shaft housing 180 may further include: a shaft member for rotatably supporting the shaft member 170; or a shaft member seal surrounding the shaft member 170; or a bearing for rotatably supporting the cylinder a shaft member; or a shaft member for rotatably supporting the shaft member 170; and a shaft member seal surrounding the shaft member 170; or a shaft member bearing for rotatably supporting the shaft member 170; a bearing for rotatably supporting the cylinder block 130; or a bearing for rotatably supporting the cylinder block 130; a shaft member bearing for supporting the shaft member 170; and a shaft member seal member The shaft member 170 is surrounded. The apparatus 100 can further include a yoke 160 housing mounted to the shaft housing 180 for enclosing the yoke 160, the mandrel 150, and the link 140. In the apparatus 100: a power source rotates the shaft member 170 to rotate the cylinder block 130 and the mandrel 150, thereby operating the device 100 to pump a pump through the distribution plate 110; or the fluid flows under pressure to the flow distribution The disk 110 rotates the mandrel 150 and the cylinder block 130 to operate the device 100 to generate torque and/or rotate one of the motors at the shaft member 170; or a power source rotates the shaft member 170 to cause the cylinder block 130 and the mandrel 150 is rotated whereby the apparatus 100 is operated to pump a pump of fluid through the distribution plate 110, and wherein the fluid flows under pressure to the distribution plate 110 to rotate the mandrel 150 and the cylinder block 130 to operate the device 100 as One of the torques and/or rotation of the shaft 170 produces a motor. The yoke 160 is pivotable across the center relative to the axis of rotation of the cylinder block 130 for reversing the direction of fluid flow between the respective fluid ports 120 when the device 100 is used as a pump and for use in the device 100 When used as a motor, the direction of rotation of the shaft member 170 is reversed.

A curved shaft variable displacement coaxial drive pump device 100 can include: a distribution plate 110 having a seat for receiving a rotatable cylinder block 130 therein, and having at least two fluid passages, each fluid passage coupling Up to a respective fluid crucible 120 and each fluid passage having an arcuate opening corresponding to a portion of less than 180° different from one of the circles; a cylinder block 130 adjacent to the seat of the distribution plate 110 for rotatably mounting for winding One axis of rotation, the cylinder block 130 has a circular array of axial cylinders 132, each axial cylinder 132 having a seat end adjacent the seat of the distribution plate 110 and positioned to vary in rotation of the cylinder block 130 One of the openings in the rotational position is alternately in fluid communication with the respective openings of the two fluid passages; a rotatable shaft member 170 coupled through the opening in the distribution plate 110 to the cylinder block 130 for rotation therewith; a piston 142 disposed in the cylinder 132 of the cylinder block 130 for reciprocating therein, each piston having a link 140 extending from one end of the cylinder block 130 opposite the valve disc 110; a rotatable spindle 150, A circular array having a receptacle for receiving respective ends of the link 140; a pivotable yoke 160 having a spindle 150 rotatably mounted thereon for rotation about an axis, wherein The mandrel 150 and the plurality of pistons 142 in the cylinder block 130 are coupled for rotation by a link 140, and the yoke 160 is pivotable for rotating the axis of rotation of the mandrel 150 with respect to the axis of rotation of the cylinder block 130. The opening 133 at the seat end of each axial cylinder 132 may have a smaller diameter than the axial cylinder 132, whereby the operating pressure urges the cylinder block 130 toward the valve disc 120; or a spring 169 may urge the cylinder block toward the valve disc 120 130; or the opening 133 at the seat end of each axial cylinder 132 may have a diameter that is smaller than the axial cylinder 132 and a spring 169 may urge the cylinder block 132 toward the distribution plate. The device 100 can further include a compression plate 152 attached to the rotatable mandrel 150 and rotatable therewith, wherein the compression plate 152 retains the ends of the links 140 in respective receptacles of the rotatable mandrel 150. Each link 140 can include: at least one of the spherical balls 144, 146 disposed in one of the pistons at one end of the link 140; or at least at the other end of the link 140 is rotatable a spherical ball 144, 146 in the receptacle of the mandrel 150; or in the connection One of the spherical rods 144, 146 disposed at one end of the rod 140 in one of the sockets of the piston and one of the spherical balls 144, 146 disposed at the other end of the connecting rod 140 in the receptacle of the rotatable mandrel 150 . The apparatus 100 can further include a universal joint rod 200 coupled to at least one of the shaft member 170 and the cylinder block 130 at one end and to one of the rotatable mandrels 150 at the other end. The universal joint rod 200 may include: at least one of the split spherical balls 204, 206 disposed in one of the shaft members 170 and one of the cylinder blocks 130 at one end of the universal joint rod 200; or At least one of the split spherical balls 204, 206 disposed in one of the sockets at the rotatable mandrel at the other end of the universal joint rod 200; or at each end of the universal joint rod 200 One of the pivotal balls 204, 206 in one of the shaft member 170 and the cylinder block 130 and the respective socket at the rotatable mandrel 150. The rotatable mandrel 150 can include: a movable socket 151 for receiving one end 206 of the universal joint rod 200, wherein the movable socket 151 is axially movable relative to the rotatable mandrel 150; and a spring 169, which can bias the universal joint rod 200 to the movable socket 151, whereby the movable socket 151 can change the effective geometric length of one of the universal joint rods 200 when the pivotable yoke 160 pivots. mobile. The yoke 160 can include a pair of bearing plates 164 for rotatably supporting and extending from one of the bases of the rotatable mandrel 150, wherein the yoke 160 is pivotally supported by one of the bearing plates 164 coupled to the yoke 160 Transfer mode support. The yoke 160 can be pivoted by the torque applied at its bearing plate 164. The mandrel 150 can be rotatably supported on the yoke 160 by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The apparatus 100 of claim 1 may further include: a shaft housing 180 that supports the valve plate 110 in a fixed manner and rotatably supports the shaft member 170 and the cylinder block 130. The shaft housing 180 may further include: a shaft member for rotatably supporting the shaft member 170; or a shaft member seal surrounding the shaft member 170; or a bearing for rotatably supporting the cylinder a shaft member; or a shaft member for rotatably supporting the shaft member 170; and a shaft member seal surrounding the shaft member 170; or a shaft member bearing for rotatably supporting the shaft member 170; a bearing for rotatably supporting the cylinder block 130; or a A bearing for rotatably supporting the cylinder block 130; a shaft member for supporting the shaft member 170; and a shaft member seal surrounding the shaft member 170. The apparatus 100 can further include a yoke 160 housing mounted to the shaft housing 180 for enclosing the yoke 160, the mandrel 150, and the link 140. In the apparatus 100, a power source rotates the shaft member 170 to rotate the cylinder block 130 and the spindle 150, thereby operating the pump device 100 for pumping fluid through the valve plate 110. The yoke 160 is pivotable across the center relative to the axis of rotation of the cylinder block 130 for reversing the direction of fluid flow between the respective fluid ports 120 of the pump assembly 100.

A curved shaft variable displacement coaxial drive device 100 can include: a distribution plate 110 having a seat for receiving a rotatable cylinder block 130 therein, and having at least two fluid passages, each fluid passage coupled to one Each fluid channel 120 and each fluid channel has an arcuate opening corresponding to a portion of less than 180° different from one of the circles; a cylinder block 130 adjacent to the seat of the valve plate 110 is rotatably mounted for rotation about an axis The cylinder block 130 has a circular array of axial cylinders 132 each having a seat at one of its seats adjacent the distribution plate 110 and positioned for different rotational positions in the rotation of the cylinder block 130. An opening is alternately in fluid communication with each of the two fluid passages; a rotatable shaft member 170 coupled through the opening in the distribution plate 110 to the cylinder block 130 for rotation therewith; a plurality of pistons 142 And disposed in the cylinder 132 of the cylinder block 130 for reciprocating therein, each piston having a connecting rod 140 extending from one end of the cylinder block 130 opposite to the valve disc 110; a rotatable spindle 150, wherein A circular array of receptacles for receiving respective ends of the link 140; a pivotable yoke 160 having a spindle 150 rotatably mounted thereon for rotation about an axis, wherein the cylinder is disposed The mandrel 150 and the plurality of pistons 142 in the body 130 are coupled for rotation by a link 140, and the yoke 160 is pivotable for rotating the axis of rotation of the mandrel 150 with respect to the axis of rotation of the cylinder block 130. The opening 133 at the seat end of each axial cylinder 132 may have a smaller diameter than the axial cylinder 132, whereby the operating pressure urges the cylinder block 130 toward the valve disc 120; or a spring 169 may urge the cylinder block toward the valve disc 120 130; or the opening 133 at the seat end of each axial cylinder 132 may have a ratio The axial cylinder 132 is one of the smaller diameters and a spring 169 can urge the cylinder block 132 toward the distribution plate. The device 100 can further include a compression plate 152 attached to the rotatable mandrel 150 and rotatable therewith, wherein the compression plate 152 retains the ends of the links 140 in respective receptacles of the rotatable mandrel 150. Each link 140 can include: at least one of the spherical balls 144, 146 disposed in one of the pistons at one end of the link 140; or at least at the other end of the link 140 is rotatable One of the spherical balls 144, 146 in the receptacle of the mandrel 150; or one of the spherical balls 144, 146 disposed in one of the sockets of the piston at one end of the link 140 and at the other end of the link 140 One of the spherical balls 144, 146 disposed in the receptacle of the rotatable mandrel 150. The apparatus 100 can further include a universal joint rod 200 coupled to at least one of the shaft member 170 and the cylinder block 130 at one end and to one of the rotatable mandrels 150 at the other end. The universal joint rod 200 may include: at least one of the split spherical balls 204, 206 disposed in one of the shaft members 170 and one of the cylinder blocks 130 at one end of the universal joint rod 200; or At least one of the split spherical balls 204, 206 disposed in one of the sockets at the rotatable mandrel at the other end of the universal joint rod 200; or at each end of the universal joint rod 200 One of the pivotal balls 204, 206 in one of the shaft member 170 and the cylinder block 130 and the respective socket at the rotatable mandrel 150. The rotatable mandrel 150 can include: a movable socket 151 for receiving one end 206 of the universal joint rod 200, wherein the movable socket 151 is axially movable relative to the rotatable mandrel 150; and a spring 169, which can bias the universal joint rod 200 to the movable socket 151, whereby the movable socket 151 can change the effective geometric length of one of the universal joint rods 200 when the pivotable yoke 160 pivots. mobile. The yoke 160 can include a pair of bearing plates 164 for rotatably supporting and extending from one of the bases of the rotatable mandrel 150, wherein the yoke 160 is pivotally supported by one of the bearing plates 164 coupled to the yoke 160 Transfer mode support. The yoke 160 can be pivoted by the torque applied at its bearing plate 164. The mandrel 150 can be rotatably supported on the yoke 160 by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The device 100 of claim 1 may further include: a shaft housing 180 that supports the valve plate 110 in a fixed manner and is rotatable The shaft member 170 and the cylinder block 130 are supported in a rotating manner. The shaft housing 180 may further include: a shaft member for rotatably supporting the shaft member 170; or a shaft member seal surrounding the shaft member 170; or a bearing for rotatably supporting the cylinder a shaft member; or a shaft member for rotatably supporting the shaft member 170; and a shaft member seal surrounding the shaft member 170; or a shaft member bearing for rotatably supporting the shaft member 170; a bearing for rotatably supporting the cylinder block 130; or a bearing for rotatably supporting the cylinder block 130; a shaft member bearing for supporting the shaft member 170; and a shaft member seal member The shaft member 170 is surrounded. The apparatus 100 of claim 9 may further include: a yoke 160 housing mounted to the shaft housing 180 for enclosing the yoke 160, the mandrel 150, and the link 140. In apparatus 100: fluid flows under pressure to valve plate 110 to rotate mandrel 150 and cylinder block 130 to operate device 100 to generate torque and/or rotate one of the motors at shaft 170. The yoke 160 is pivotable across the center with respect to the axis of rotation of the cylinder block 130 for reversing the direction of rotation of the shaft member 170 of the motor assembly 100.

A bending axis variable displacement coaxial drive rotation group 130 to 160 may include a cylinder block 130 rotatably mounted for rotation about an axis, and a circular array of axial cylinders 132 in the cylinder block 130 Each axial cylinder 132 has two fluids at one of the seat ends of the cylinder block 130 positioned to be at a different rotational position in the rotation of the cylinder block 130 when the valve plate 110 is adjacent to the cylinder block 130, and two fluids of a valve plate 110 The respective openings in the passage openings are alternately fluidly connected to one of the openings; the cylinder block 130 has a central opening at a seat end for receiving a rotatable shaft member 170, whereby a rotatable shaft member 170 can pass through One of the orifices 110 is coupled to the cylinder block 130 for rotation therewith; a plurality of pistons 142 are disposed in the cylinders 132 of the cylinder block 130 for reciprocating therein, each piston having a cylinder opposite the seat end thereof One end of the body 130 extends a link 140; a rotatable mandrel 150 having a circular array of receptacles for receiving respective ends of the link 140; a pivotable yoke 160 having a rotatable Way to install on it For rotation about an axis 150, which is disposed in the cylinder body 130 of the mandrel 150 and the piston 142 by a plurality of link 140 The connection is used for rotation together, and the yoke 160 is pivotable for rotating the axis of rotation of the mandrel 150 with respect to the axis of rotation of the cylinder block 130. The opening 133 at the seat end of each axial cylinder 132 may have a smaller diameter than the axial cylinder 132, whereby the operating pressure urges the cylinder block 130 toward the valve disc 120; or a spring 169 may urge the cylinder block toward the valve disc 120 130; or the opening 133 at the seat end of each axial cylinder 132 may have a diameter that is smaller than the axial cylinder 132 and a spring 169 may urge the cylinder block 132 toward the distribution plate. The rotating groups 130-160 can further include a compression plate 152 attached to the rotatable mandrel 150 and rotatable therewith, wherein the compression plate 152 retains the end of the link 140 at each of the rotatable mandrels 150 In the seat. Each link 140 can include: at least one of the spherical balls 144, 146 disposed in one of the pistons at one end of the link 140; or at least at the other end of the link 140 is rotatable One of the spherical balls 144, 146 in the receptacle of the mandrel 150; or one of the spherical balls 144, 146 disposed in one of the sockets of the piston at one end of the link 140 and at the other end of the link 140 One of the spherical balls 144, 146 disposed in the receptacle of the rotatable mandrel 150. The rotating groups 130-160 can further include a universal joint rod 200 coupled to at least one of the shaft member 170 and the cylinder block 130 at one end and to one of the rotatable spindles 150 at the other end. The universal joint rod 200 may include: at least one of the split spherical balls 204, 206 disposed in one of the shaft members 170 and one of the cylinder blocks 130 at one end of the universal joint rod 200; or At least one of the split spherical balls 204, 206 disposed in one of the sockets at the rotatable mandrel at the other end of the universal joint rod 200; or at each end of the universal joint rod 200 One of the pivotal balls 204, 206 in one of the shaft member 170 and the cylinder block 130 and the respective socket at the rotatable mandrel 150. The rotatable mandrel 150 can include: a movable socket 151 for receiving one end 206 of the universal joint rod 200, wherein the movable socket 151 is axially movable relative to the rotatable mandrel 150; and a spring The 169 can be biased toward the universal coupling rod 200 to the movable socket 151, whereby the movable socket 151 moves with an effective geometric length of one of the universal joint rods 200 that changes when the pivotable yoke 160 pivots. The yoke 160 can include a base for rotatably supporting and extending one of the bases of the rotatable mandrel 150 A carrier plate 164, wherein the yoke 160 is pivotally supported by a pair of bearing plates 164 coupled to the yoke 160. The yoke 160 can be pivoted by the torque applied at its bearing plate 164. The mandrel 150 can be rotatably supported on the yoke 160 by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The rotating groups 130 to 160 may further include: a housing that rotatably supports the cylinder block 130; and a bearing in the housing for rotatably supporting the cylinder block 130. The yoke 160 is pivotable across the center relative to the axis of rotation of the cylinder block 130 for reversing the fluid flow between the respective fluid passages of a valve plate 120 when the device rotation groups 130-160 are used in a pump. The direction is used to reverse the direction of rotation of the cylinder block 130 when the device rotation groups 130-160 are used in a motor.

As used herein, the term "about" means that the size, size, formula, parameters, shape, and other quantities and characteristics are not required to be precise, but may be approximated and/or larger or smaller as needed to reflect Tolerances, scaling factors, rounding, measurement errors, and the like, as well as other factors known to those skilled in the art. In general, a size, size, formula, parameter, shape or other quantity or characteristic is "about" or "approximately", whether or not explicitly stated as such. It is noted that embodiments of extremely different sizes, shapes and sizes may employ the configurations set forth.

Although such as "upper", "lower", "left", "right", "front", "back", "side", "top", "bottom", "forward", "backward", "below" And/or "above" terms and the like may be used herein as a convenient means of illustrating one or more embodiments and/or uses of the present configuration, but the recited items may be positioned and/or in any desired orientation. Use the desired location and/or orientation. The location and/or orientation terms are to be understood as being for convenience only and not limiting the claimed invention.

In addition, those who are stated as "best" or "best" may or may not be a truly optimal condition, but rather because they are based on the decision rules and/or criteria defined by the designer and/or applicable. The selection of control functions is considered to be the desired or acceptable "best" condition, for example, one of the best operating conditions for pressure, fluid flow and shaft rotation can be specified, even if The setting 100 can generally be operated under a different operating condition or within a range of operating conditions, and the optimum conditions can be different when the device 100 is used as a pump as when it is used as a motor.

Although the present invention has been described in terms of the foregoing exemplary embodiments, those skilled in the art will recognize the scope of the invention and the spirit of the invention as defined in the following claims. For example, the link 140 is illustrated as having one instance ball and socket connection to the piston 142 and at the mandrel 150, however, this connection need not be provided at the piston 142 and other configurations may be provided at the mandrel 150 , for example, a slipper or a slipper.

In addition, cylinder block 130 and shaft member 170, as illustrated, may be two separate pieces joined by one or more splines or keys, or may be machined or permanently secured together in a single piece.

Still further, the piston 142 can be one piece and assembled to the link 140, for example, by squeezing the lip of the socket 143 of the piston 142 to capture and retain the ball end 144 of the rod 140 therein, or can be two The pieces, the piston and an annular plug, are assembled to press the annular plug into the socket 143 to capture and retain the ball end 144 of the rod 140 to the piston 142. Additionally and/or alternatively, the link 140 can be a single piece as illustrated, or can be two pieces, each piece including a ball end 144, 146 and a smaller connecting ball end 144, 146. One part of the shaft connecting the shaft. Portions of the connecting shaft members are joined together by welding, for example, before or after the ball ends 144 are captured and held in the socket 143 of the piston 142 by welding of the connecting shaft members.

Typically, the compression plate 152 that captures and retains the ball end 146 of the link 140 in the socket 153 of the mandrel 150 can have a circular opening through which the piston link 140 passes, and each circular opening can have a connection The circular opening is radially grooved with one of the perimeters of the compression plate 152 such that the connecting shaft portion of the connecting rod 140 can pass through the radial slot. Alternatively, in the case where the link 140 is provided in two pieces, one of the pieces may pass through the circular opening of the pressing plate 152 before the two portions of the connecting shaft of the connecting rod 140 are welded together.

In KERS and / or HD systems, two or four wheel drives can be side by side mixed A conventional transmission and drive shaft member in the system and a plurality of wheel drive units 100W in a series of hybrid systems are provided. In a side-by-side two-wheel drive hybrid system, two wheels that are not mechanically driven can be driven by the wheel drive 100W, thereby providing a pseudo tandem/parallel configuration in which all four wheels can be driven, with two wheels coming from The mechanical coupling of the engine 310 is driven and the other wheel is driven by the fluid drive 100W.

Each of the U.S. Provisional Application, U.S. Patent Application, and/or U.S. Patent, as discussed herein, is hereby incorporated by reference in its entirety for all purposes and for all purposes. Incorporated herein.

In the end, the stated values are typical or exemplary values, not limiting values, and do not exclude substantially larger and/or substantially smaller values. The values in any given embodiment may be substantially greater than and/or may be substantially less than the stated exemplary or typical values.

102‧‧‧Rotary drive shaft/shaft/rotary shaft/drive shaft

110‧‧‧Example distribution plate/non-rotating distribution plate/distribution plate

115‧‧‧Center opening/opening/drive opening

130‧‧‧Cylinder block/spin cylinder block/component

132‧‧‧Cylinder/Axial Cylinder/Cylinder Block

133‧‧‧埠/cylinder 埠/opening

136‧‧‧bearing/cylinder bearing

137‧‧ ‧ spring

138‧‧‧ bearing spring plate

140‧‧‧Piston rod/link/assembly/rod/piston connecting rod

142‧‧‧Cylinder/Piston

143‧‧‧General spherical socket / socket

144‧‧‧General spherical end / spherical ball / ball end / spherical end

146‧‧‧General spherical end / connecting rod end / spherical ball / ball end / spherical end

150‧‧‧ mandrel / rotatable mandrel / yoke mandrel / component

152‧‧‧Pressure plate/piston rod compression plate

153‧‧‧General spherical socket/heart bearing socket/yoke core bearing socket/socket

154‧‧‧Axial bearing/cylindrical thrust roller bearing

156‧‧‧ Radial Bearings/Bearings

160‧‧‧ Yoke/Pivotable Yoke/Component/Yoke Assembly/End Plate/Low Inertia Yoke

161‧‧‧Rotary shaft/yoke or spindle shaft/shaft

170‧‧‧Output drive shaft / shaft / drive shaft / rotatable drive shaft / output shaft / rotatable shaft

171‧‧‧ Spline/solid features

172‧‧‧Sealing/shaft seals

172c‧‧‧Sealing carrier

172g‧‧‧ cylindrical groove

174‧‧‧bearing/shaft bearing

180‧‧‧Shell/shaft housing/yoke housing

182‧‧‧Shaft housing base

184‧‧‧ central part

185‧‧‧ hole

190‧‧‧Shell/yoke housing

192‧‧‧Sheet base

194‧‧‧Shell cover part / yoke shell cover

200‧‧‧ million joint rod / coupling rod

A‧‧‧Angle/Pivot Angle/Maximum Yoke Angle/Yoke Angle/Angle Position

Claims (57)

A curved shaft variable displacement coaxial drive device comprising: a distribution plate having a seat for receiving a rotatable cylinder block therein, and having at least two fluid passages, each fluid passage coupled to a respective one Fluid and each fluid passage has an arcuate opening corresponding to a portion of less than 180° different from a circle; a cylinder block adjacent to the seat of the distribution plate rotatably mounted for rotation about an axis, the cylinder block Having a circular array of axial cylinders, each axial cylinder having a seat end adjacent to the seat of the distribution plate and positioned to rotate at different rotational positions in the rotation of the cylinder block The respective openings of the fluid passage are alternately fluidly connected to one of the openings; a rotatable shaft member coupled to the cylinder block for rotation therewith through an opening in the distribution plate; a plurality of pistons disposed thereon The cylinders of the cylinder block are for reciprocating therein, each piston having a link extending from one end of the cylinder block opposite the valve plate; a rotatable mandrel having a receptacle therein a circular array for receiving respective ends of the links; a pivotable yoke having a spindle rotatably mounted thereon for rotation about an axis, wherein the mandrel and the mandrel are disposed a plurality of pistons in the cylinder block are coupled by the links for rotation together, the yoke being pivotable for rotating an axis of rotation of the spindle relative to an axis of rotation of the cylinder block, whereby the pivot The yoke can pivot across the center. The device of claim 1, wherein: the opening at the seat end of each axial cylinder has one smaller than the axial cylinder a diameter by which the operating pressure advances the cylinder block toward the valve disc; or a spring urges the cylinder block toward the valve disc; or the opening at the seat end of each axial cylinder has one smaller than the axial cylinder A diameter and a spring urge the cylinder block toward the valve plate. The device of claim 1, further comprising a compression plate attached to the rotatable mandrel and rotatable therewith, wherein the compression plate retains the ends of the links on the rotatable mandrel These are the various seats. The device of claim 1, wherein each of the links comprises: a spherical ball disposed in one of the sockets of the piston at least at one end of the link; or at least at the other end of the link a spherical ball in the receptacle of the rotatable mandrel; or a spherical ball disposed in one of the sockets of the piston at one end of the connecting rod and disposed at the other end of the connecting rod One of the spherical balls in the receptacle of the rotatable mandrel. The device of claim 1, further comprising a universal joint rod coupled to at least one of the shaft member and the cylinder block at one end and to the rotatable mandrel at the other end. The apparatus of claim 5, wherein the universal joint rod includes: at least one of the sockets disposed at one of the shaft member and the one of the cylinder blocks at one end of the universal joint rod a spherical ball; or at least at one end of the universal joint rod, a split spherical ball disposed in one of the sockets at the rotatable mandrel; or at each end of the universal joint rod One of the shaft member and the one of the cylinder blocks and one of the respective sockets at the rotatable mandrel. The device of claim 1, wherein the rotatable spindle comprises: a movable socket for receiving one end of a universal joint rod, wherein the movable socket is axially movable relative to the rotatable spindle; and a spring biased toward the universal joint rod The movable socket is thereby moved by the movable geometrical length of one of the universal joint rods when the pivotable yoke is pivoted. The device of claim 1, wherein the yoke includes a pair of bearing plates for rotatably supporting a base of the rotatable mandrel and extending from the base, wherein the yoke is coupled to the bearing plates of the yoke One of the pair of bearings is pivotally supported. The device of claim 8 wherein the yoke is pivotable by a torque applied at its bearing plate. The device of claim 1, wherein the mandrel is rotatably supported on the yoke by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The device of claim 1, further comprising: a shaft housing that supports the valve plate in a fixed manner and rotatably supports the shaft member and the cylinder block. The device of claim 11, wherein the shaft housing further comprises: a shaft member for rotatably supporting the shaft member; or a shaft seal surrounding the shaft member; or a bearing for use To rotatably support the cylinder block; or a shaft member for rotatably supporting the shaft member; and a shaft member seal surrounding the shaft member; or a shaft member bearing for being rotatable Supporting the shaft member; and a bearing for rotatably supporting the cylinder block; or a bearing for rotatably supporting the cylinder block; a shaft member bearing for supporting the shaft member; And a shaft seal that surrounds the shaft member. The device of claim 11, further comprising: a yoke housing mounted to the shaft housing for enclosing the yoke, the mandrel, and the links. The device of claim 1, wherein: a power source rotates the shaft member to rotate the cylinder block and the spindle, thereby operating the device to pump a pump through the distribution plate; or the fluid is Flowing to the flow plate to rotate the mandrel and the cylinder block to operate the device to generate torque and/or rotate a motor at the shaft; or a power source to rotate the shaft to Rotating the cylinder block and the mandrel, thereby operating the device to pump a pump through the distribution plate, and wherein the fluid flows under pressure to the valve plate to rotate the mandrel and the cylinder block to The device operates to generate torque and/or rotate one of the motors at the shaft. The device of claim 1 wherein the yoke is pivotable across the center relative to the axis of rotation of the cylinder block for reversing fluid flow between the respective fluid ports when the device is used as a pump The direction is used to reverse the direction of rotation of the shaft when the device is used as a motor. A curved shaft variable displacement coaxial drive pump device comprising: a distribution plate having a seat for receiving a rotatable cylinder block therein, and having at least two fluid passages, each fluid passage coupled to one Each fluid channel has an arcuate opening corresponding to a portion of less than 180° different from one of the circles; a cylinder block adjacent to the seat of the valve plate for rotatably mounting for rotation about an axis, a circular array of axial cylinders in the cylinder block, each axial cylinder having a seat end adjacent to the seat of the distribution plate and positioned to rotate at a different rotational position in the rotation of the cylinder block The respective openings of the two fluid passages are alternately fluidly connected to one of the openings; a rotatable shaft member coupled to the cylinder block for rotation therewith through an opening in the distribution plate; a plurality of pistons Placed in the cylinders of the cylinder block for use therein a plurality of movements, each of the pistons having a link extending from one end of the cylinder block opposite the valve plate; a rotatable mandrel having a circular array of receptacles for receiving each of the links a pivotable yoke having a spindle rotatably mounted thereon for rotation about an axis, wherein the spindle and a plurality of pistons disposed in the cylinder block are connected by the links For rotation together, the yoke is pivotable for rotating the axis of rotation of the mandrel relative to the axis of rotation of the cylinder block whereby the pivotable yoke can pivot across the center. The apparatus of claim 16, wherein: the opening at the seat end of each axial cylinder has a diameter smaller than the axial cylinder, whereby the operating pressure advances the cylinder block toward the valve plate; or a spring orientation The valve plate advances the cylinder block; or the opening at the seat end of each axial cylinder has a diameter smaller than the axial cylinder and a spring urges the cylinder block toward the distribution plate. The device of claim 16, further comprising a compression plate attached to the rotatable mandrel and rotatable therewith, wherein the compression plate retains the ends of the links on the rotatable mandrel These are the various seats. The device of claim 16, wherein each of the links comprises: a spherical ball disposed in one of the sockets of the piston at least at one end of the link; or at least at the other end of the link a spherical ball in the receptacle of the rotatable mandrel; or a spherical ball disposed in one of the sockets of the piston at one end of the connecting rod and disposed at the other end of the connecting rod One of the spherical balls in the receptacle of the rotatable mandrel. The device of claim 16, further comprising a universal joint rod coupled to at least one of the shaft member and the cylinder block at one end and to the rotatable mandrel at the other end. The apparatus of claim 20, wherein the universal joint rod comprises: at least one of the sockets disposed at one of the shaft member and the one of the cylinder blocks at one end of the universal joint rod a spherical ball; or at least at one end of the universal joint rod, a split spherical ball disposed in one of the sockets at the rotatable mandrel; or at each end of the universal joint rod One of the shaft member and the one of the cylinder blocks and one of the respective sockets at the rotatable mandrel. The device of claim 16, wherein the rotatable mandrel comprises: a movable socket for receiving one end of a universal coupling rod, wherein the movable socket is axially movable relative to the rotatable spindle And a spring biasing the universal coupling rod to the movable socket, whereby the movable socket is adapted to change an effective geometry of the universal joint rod when the pivotable yoke is pivoted Move by length. The device of claim 16, wherein the yoke includes a pair of bearing plates for rotatably supporting a base of the rotatable mandrel and extending from the base, wherein the yoke is coupled to the bearing plates of the yoke One of the pair of bearings is pivotally supported. The device of claim 23, wherein the yoke is pivotable by a torque applied at its bearing plate. The device of claim 16, wherein the mandrel is rotatably supported on the yoke by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The device of claim 16, further comprising: a shaft housing that supports the valve plate in a fixed manner and rotatably supports the shaft member and the cylinder block. The device of claim 26, wherein the shaft housing further comprises: a shaft member for rotatably supporting the shaft member; or a shaft member seal surrounding the shaft member; or a bearing for rotatably supporting the cylinder block; or a shaft member bearing For rotatably supporting the shaft member; and a shaft member seal surrounding the shaft member; or a shaft member bearing for rotatably supporting the shaft member; and a bearing for rotating Supporting the cylinder block; or a bearing for rotatably supporting the cylinder block; a shaft bearing for supporting the shaft member; and a shaft seal surrounding the shaft member. The device of claim 26, further comprising: a yoke housing mounted to the shaft housing for enclosing the yoke, the mandrel, and the links. The apparatus of claim 16, wherein: a power source rotates the shaft member to rotate the cylinder block and the spindle, thereby operating the pumping device for pumping fluid through the valve plate. The apparatus of claim 16, wherein the yoke is pivotable across the center relative to the axis of rotation of the cylinder block for reversing the direction of fluid flow between the respective fluid ports of the pumping device. A curved shaft variable displacement coaxial drive motor device comprising: a distribution plate having a seat for receiving a rotatable cylinder block therein, and having at least two fluid passages, each fluid passage coupled to each And the fluid passage has an arcuate opening corresponding to a portion of less than 180° different from one of the circles; a cylinder block adjacent to the seat of the distribution plate rotatably mounted for rotation about an axis, the cylinder The body has a circular array of axial cylinders, each axial cylinder having a seat end adjacent to the seat of the distribution plate and positioned to rotate at different rotational positions in the rotation of the cylinder block Each of the fluid passages The opening is alternately fluidly connected to one of the openings; a rotatable shaft member coupled to the cylinder block for rotation therewith through an opening in the distribution plate; a plurality of pistons disposed on the cylinder block a cylinder for reciprocating therein, each of the pistons having a link extending from one end of the cylinder block opposite the valve plate; a rotatable mandrel having a circular array of receptacles for receiving a respective end of the links; a pivotable yoke having a spindle rotatably mounted thereon for rotation about an axis, wherein the spindle and a plurality of pistons disposed in the cylinder block Connected by the links for rotation together, the yoke is pivotable for rotating the axis of rotation of the mandrel relative to the axis of rotation of the cylinder block, whereby the pivotable yoke can span the central pivot turn. The device of claim 31, wherein: the opening at the seat end of each axial cylinder has a diameter smaller than the axial cylinder, whereby the operating pressure advances the cylinder block toward the valve plate; or a spring orientation The valve plate advances the cylinder block; or the opening at the seat end of each axial cylinder has a diameter smaller than the axial cylinder and a spring urges the cylinder block toward the distribution plate. The device of claim 31, further comprising a compression plate attached to the rotatable mandrel and rotatable therewith, wherein the compression plate retains the ends of the links on the rotatable mandrel These are the various seats. The device of claim 31, wherein each of the links comprises: a spherical ball disposed in one of the sockets of the piston at least at one end of the link; or at least at the other end of the link In the receptacle of the rotatable mandrel a spherical ball; or a spherical ball disposed at one end of the connecting rod in one of the sockets of the piston and disposed at the other end of the connecting rod in the receptacle of the rotatable mandrel A spherical ball. The device of claim 31, further comprising a universal joint rod coupled to one of the shaft member and the cylinder block at one end and to the rotatable mandrel at the other end. The device of claim 35, wherein the universal joint rod comprises: at least one of the sockets disposed at one of the shaft member and the one of the cylinder blocks at one end of the universal joint rod a spherical ball; or at least at one end of the universal joint rod, a split spherical ball disposed in one of the sockets at the rotatable mandrel; or at each end of the universal joint rod One of the shaft member and the one of the cylinder blocks and one of the respective sockets at the rotatable mandrel. The device of claim 31, wherein the rotatable mandrel comprises: a movable socket for receiving one end of a universal joint rod, wherein the movable socket is axially movable relative to the rotatable spindle And a spring biasing the universal coupling rod to the movable socket, whereby the movable socket is adapted to change an effective geometry of the universal joint rod when the pivotable yoke is pivoted Move by length. The device of claim 31, wherein the yoke includes a pair of bearing plates for rotatably supporting one of the rotatable mandrels and extending from the base, wherein the yoke is coupled to the bearing plates of the yoke One of the pair of bearings is pivotally supported. The device of claim 38, wherein the yoke is pivotable by a torque applied at its bearing plate. The device of claim 31, wherein the mandrel is comprised of an axial bearing or a radial axis The bearing is rotatably supported on the yoke by an axial bearing and a radial bearing. The device of claim 31, further comprising: a shaft housing that supports the valve plate in a fixed manner and rotatably supports the shaft member and the cylinder block. The device of claim 41, wherein the shaft housing further comprises: a shaft member for rotatably supporting the shaft member; or a shaft member seal surrounding the shaft member; or a bearing for use To rotatably support the cylinder block; or a shaft member for rotatably supporting the shaft member; and a shaft member seal surrounding the shaft member; or a shaft member bearing for being rotatable Supporting the shaft member; and a bearing for rotatably supporting the cylinder block; or a bearing for rotatably supporting the cylinder block; a shaft member bearing for supporting the shaft member; And a shaft seal that surrounds the shaft member. The device of claim 41, further comprising: a yoke housing mounted to the shaft housing for enclosing the yoke, the mandrel, and the links. The device of claim 31, wherein: the fluid flows under pressure to the valve plate to rotate the mandrel and the cylinder block to operate the device to generate torque and/or rotate a motor at the shaft. The device of claim 31, wherein the yoke is pivotable across the center relative to the axis of rotation of the cylinder block for reversing the direction of rotation of the shaft member of the motor assembly. A rotary shaft variable displacement coaxial drive rotating group includes: a cylinder block rotatably mounted for rotation about an axis, the cylinder block having a circular array of axial cylinders, each axis The cylinder has a position at a seat end of the cylinder block to alternate between respective openings of a plurality of fluid passages of a distribution plate at different rotational positions in the rotation of the cylinder block when a distribution plate is adjacent to the cylinder block One of the openings of the ground fluid; The cylinder block has a central opening at a seat end for receiving a rotatable shaft member, whereby a rotatable shaft member is coupled to the cylinder block for rotation therewith through an opening in a distribution plate; Pistons disposed in the cylinders of the cylinder block for reciprocating therein, each piston having a link extending from one end of the cylinder block opposite the seat end; a rotatable mandrel, wherein a circular array having a receptacle for receiving respective ends of the links; a pivotable yoke having a spindle rotatably mounted thereon for rotation about an axis, wherein the spindle And the plurality of pistons disposed in the cylinder block are connected by the connecting rods for pivoting together, the yoke being pivotable for rotating an axis of rotation of the spindle with respect to an axis of rotation of the cylinder block, Thereby the pivotable yoke can pivot across the center. [0058] The device rotation group of claim 46, wherein: the opening at the seat end of each axial cylinder has a diameter that is smaller than the axial cylinder, whereby the operating pressure advances the cylinder block toward the valve plate; or A spring urges the cylinder block toward the distribution plate; or the opening at the seat end of each axial cylinder has a diameter smaller than the axial cylinder and a spring urges the cylinder block toward the distribution plate. A device rotation group of claim 46, further comprising a compression plate attached to the rotatable mandrel and rotatable therewith, wherein the compression plate holds the ends of the links at the Rotate the respective spindles of the mandrel. [0058] The device rotation group of claim 46, wherein each of the links includes: at least one ball disposed in one of the sockets of the piston at one end of the link; or at least at the other end of the link Placed in the receptacle of the rotatable mandrel a spherical ball; or a spherical ball disposed at one end of the connecting rod in one of the sockets of the piston and disposed at the other end of the connecting rod in the receptacle of the rotatable mandrel A spherical ball. The device rotation group of claim 46, further comprising a universal coupling rod coupled to the shaft member and the cylinder block at one end and to the rotatable spindle at the other end. [0058] The device rotation group of claim 50, wherein the universal joint rod includes: at least one end of the universal joint rod disposed in one of the shaft member and the one of the cylinder blocks a pair of open spherical balls; or at least one of the split spherical balls disposed in one of the sockets of the rotatable mandrel at the other end of the universal joint rod; or at each end of the universal joint rod And a pair of split spherical balls disposed in the one of the shaft member and the cylinder block and the respective sockets at the rotatable mandrel. The apparatus rotation group of claim 46, wherein the rotatable mandrel comprises: a movable socket for receiving one end of a universal joint rod, wherein the movable socket is relative to the rotatable spindle Moving axially; and a spring biasing the universal coupling rod to the movable socket, whereby the movable socket changes the universal coupling rod when the pivotable yoke pivots Move with an effective geometric length. A device rotation group of claim 46, wherein the yoke includes a pair of bearing plates for rotatably supporting one of the rotatable mandrels and extending from the base, wherein the yoke is coupled to the yoke One of the bearing plates is pivotally supported by the pair of bearings. The device rotation group of claim 53, wherein the yoke is pivotable by a torque applied at its bearing plate. The apparatus rotates the group of claim 46, wherein the mandrel is rotatably supported on the yoke by an axial bearing or by a radial bearing or by an axial bearing and a radial bearing. The apparatus rotation group of claim 46, further comprising: a housing rotatably supporting the cylinder block; and a bearing in the housing for rotatably supporting the cylinder block. The apparatus rotates the group of claim 46, wherein the yoke is pivotable across the center relative to the axis of rotation of the cylinder block for reversing a distribution plate when the device rotation group is used in a pump The direction of fluid flow between the respective fluid passages and for reversing the direction of rotation of the cylinder block when the rotating group of the device is used in a motor.