Hydraulic axial piston assembly

Abstract

The utility model relates to a hydraulic axial piston assembly. The hydraulic axial piston assembly may include a distributor plate, a bearing element directly orthogonally connected to one side of the distributor plate, and an adjustment screw orthogonally connected to the bearing element, where the adjustment screw is externally contactable and manually rotatable to adjust a timing angle of the distributor plate.

Description

Technical Field

[0001] The present disclosure relates generally to axial piston assemblies. More specifically, the present disclosure relates to an adjusting screw and bearing element for adjusting the position of a distributor plate of an axial piston assembly. Background Art

[0002] Hydraulic axial piston assemblies are often used as stand-alone pumps, hydraulic motors or compressors. Hydraulic axial piston assemblies may include an axial piston system and a distributor system. The axial piston system may include a plurality of cylinders arranged in a circular array around a central axis. Each cylinder may contain a reciprocating piston. Different mechanisms may be used to drive the reciprocating motion of the pistons in the cylinders, such as a swash plate drive. The swash plate is actually a cam surface that is connected to and rotates with the crankshaft, which drives or is driven by the reciprocating linear motion of the pistons. Each piston may have one or more bearings on it that slide or roll on the swash plate cam surface.

[0003] The reciprocating linear motion of the piston along its longitudinal axis can drive fluid into and out of the cylinder of the axial piston system through the distributor plate. The response of the axial piston system depends on the rotational position of the distributor plate relative to the body of the distribution system. In some examples, adjusting the rotational position of the distributor plate may require disassembly of at least a portion of the hydraulic axial piston assembly.

[0004] Other attempts to avoid disassembly of the hydraulic axial piston assembly when changing the position of the distributor plate include rotating the distributor plate via an external screw and eccentric pin located directly in the center of the distributor plate. However, the inventors have recognized potential problems with such a system. Such a system may require an increase in the thickness of the distributor plate to accommodate the rotation of the eccentric pin about the rotation axis of the external screw. The increased thickness of the distributor plate may increase manufacturing costs and require more packaging space. In addition, since only the eccentric pin couples the adjustment screw rotation to the distributor plate, the rotational force of the external screw may act directly on the eccentric pin, thereby increasing the aging rate of the eccentric pin. Utility Model Content

[0005] In one example, the above problem can be solved by a hydraulic axial piston assembly including a distributor plate, a bearing element directly orthogonally connected to one side of the distributor plate, and an adjustment screw orthogonally connected to the bearing element, wherein the adjustment screw is externally accessible and can be manually rotated to adjust the timing angle of the distributor plate. The externally accessible adjustment screw can allow the distributor plate to be rotated to change the behavior of the hydraulic axial piston assembly without disassembling and / or reassembling any part of the hydraulic axial piston assembly. In addition, the adjustment screw can release the force to the bearing element instead of directly to the eccentric pin, which can reduce the aging of the eccentric pin.

[0006] It should be understood that the above summary is intended to introduce in a simplified form the concepts that are further described in the detailed description. It is not intended to identify key or essential features of the claimed subject matter, the scope of which is uniquely determined by the claims that follow the detailed description. Furthermore, the claimed subject matter is not limited to implementations that solve any disadvantages noted above or in any part of this disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0007] Figure 1 A cross-sectional view showing one half of a hydraulic axial piston assembly;

[0008] Figure 2 Shows Figure 1 A front perspective view of a distributor system of a hydraulic axial piston assembly;

[0009] Figure 3 Shows Figure 2 a side perspective view of one half of the middle dispenser system;

[0010] Figure 4 Shows Figure 2 an enlarged view of the bearing elements and distributor plate of the distributor system;

[0011] Figure 5 Shows Figure 2 A magnified view of the distributor system's adjustment screws and distributor plate;

[0012] Figure 6 is a flow chart illustrating the changes Figure 2 Methods for allocator system behavior in;

[0013] Fig. 7A Yes Description Figure 2 Diagrams of various behaviors of the allocator system; and

[0014] Figure 7B Yes Description Fig. 7A Graph of the relationship between the tipping torque and the working pressure for various behaviors. DETAILED DESCRIPTION

[0015] Figure 1 A cross-sectional view of a hydraulic axial piston assembly 101 is shown, including a distributor system 100 and an axial piston system 105 . Figure 2-4 Various views of the dispenser system 100 are shown and will be described together. Figure 2 A front perspective view and a partial cross-sectional view of the dispenser system 100 are shown. Figure 3 A side perspective view of a cross section of the dispenser system 100 is shown. Figure 4 An enlarged view of the bearing element 111 and distributor plate 106 of the distributor system 100 is shown, with the distributor plate 106 being partially transparent to allow viewing of underlying features. Figure 5An enlarged view of the adjustment screw 118 and the distributor plate 106 of the distributor system 100 is shown. Figure 1-5 Shown to scale, other relative dimensions may be used.

[0016] Figure 1-5 A rectangular coordinate system 199 is included for determining the direction of the view. In one example, the Y axis can be a vertical axis (e.g., parallel to the gravity axis), the X axis can be a longitudinal axis (e.g., a horizontal axis), and / or the Z axis can be a transverse axis. However, in other examples, the axes can have other directions. Filled circles can represent arrows and axes pointing toward the view. Unfilled circles can represent arrows and axes pointing away from the view.

[0017] like Figure 1 As shown, the hydraulic axial piston assembly 101 may include a distributor system 100 and an axial piston system 105. The distributor system 100 may include a distributor body 102 and a distributor plate 106, wherein the distributor plate 106 may be in coplanar contact with the distributor body 102, as shown in FIG. Figure 2 and Figure 3 described.

[0018] The dispenser body 102 may include an adjustment screw hole 122 and a bearing element hole 116. The adjustment screw hole 122 may be cylindrical and may extend into the dispenser body 102 along an axis parallel to the Y-axis. The bearing element hole 116 may be cylindrical and may extend into the dispenser body 102 along an axis parallel to the x-axis (for example, the bearing element hole 116 may be orthogonal to the adjustment screw hole 122). In addition, the dispenser body 102 may also include an adjustment screw 118 and a bearing element 111, which are respectively located in the adjustment screw hole 122 and the bearing element hole 116. The bearing element 111 may include an eccentric pin 112 and a bearing body 114, wherein a portion of the eccentric pin 112 may be located in the bearing body 114. Similarly, as Figure 3 As described above, a portion of the eccentric pin 112 may be in coplanar contact with the distributor plate 106 .

[0019] The distributor body 102 may include an axial hole 104, wherein the axial hole 104 is circular and extends into the distributor body along a central axis 108. The axial hole 104 may be configured to accommodate an axis 109. In some examples, the axis 109 may be a crankshaft. The axis 109 may be positioned in the axial hole 104 so that the axis 109 may extend into the distributor body 102. The longitudinal axis of the axis 109 may be aligned with the central axis 108. In addition, the axis 109 may be configured to rotate around its longitudinal axis (e.g., around the central axis 108) in the axial hole 104 of the distributor body 102.

[0020] The axial piston system 105 may include an axial bore 136, a system body 107, a swash plate 130, a cylinder block 134, and a piston 124. The system body 107 of the axial piston system 105 may include an internal cavity 113. The swash plate 130, the cylinder block 134, and the piston 124 may be located in the internal volume 113 of the system body 107, respectively. In addition, the axial bore 136 may extend through the axial piston system 105 along the central axis 108.

[0021] The cylinder body 134 may be an annular body disposed circumferentially around the axial bore 136, with its longitudinal axis parallel to the central axis 108. The cylinder body 134 may include a cylinder bore 120. The cylinder bore 120 may be circular and extend into the cylinder body 134 from a first side 135 of the cylinder body 134, wherein the first side 135 is located at a distal end of the distributor system 100. A first end 121 of the cylinder bore 120 (e.g., an end of the cylinder bore 120 closest to the distributor system 100) may narrow into a fluid passage 128, which may be circular and extend from the first end 121 of the cylinder bore 120 to a second end 137 of the cylinder body 134. The second end 137 of the cylinder body 134 may be in coplanar contact with the distributor plate 106. The fluid passage 128 may fluidly couple the axial piston system 105 (e.g., the cylinder body 134) to the distributor system 100. Thus, fluid may flow between cylinder bore 120 and distributor system 100 as described herein.

[0022] At least a portion of the piston 124 may be positioned within the cylinder bore 120 such that the outer circumferential surface of the piston 124 is in coplanar contact with the inner surface of the cylinder bore 120. The piston 124 may include a coupling end 126 that is located outside the cylinder bore 120. The coupling end 126 may be coupled to a slider 132 that is in coplanar contact with the swash plate 130. In some examples, the slider 132 may not be rigidly coupled to the swash plate 130, but rather coupled to the swash plate 130 in a manner such that the slider 132 can translate on the surface of the swash plate 130. Thus, if the swash plate 130 rotates about the central axis 108, the slider 132 may not rotate, but rather remain in the same position relative to the Y-axis and the Z-axis. The swash plate 130 may be oriented such that the swash plate 130 is not orthogonal to the longitudinal axis of the shaft 109 (e.g., not orthogonal to the central axis 108). Thus, a portion of the swash plate 130 may be closer to the cylinder block 134 relative to the X-axis than another portion of the swash plate 130.

[0023] The shaft 109 may extend from the shaft hole 104 of the distributor body 102 to the shaft hole 136 of the axial piston system 105 along the central axis 108. In some examples, the shaft 109 may be connected to the swash plate 130. When the shaft 109 rotates about the central axis 108, the swash plate 130 may rotate about the central axis 108 simultaneously with the shaft 109 (e.g., rotate in the same direction at the same rotational speed). The slider 132 may not be rigidly connected to the swash plate 130, and therefore may not rotate about the central axis 108 together with the swash plate 130 and the shaft 109. Due to the orientation of the swash plate 130 relative to the cylinder block 134 (e.g., non-orthogonal orientation), the rotation of the swash plate 130 about the central axis may drive the slider 132 to reciprocate linearly along an axis parallel to the x-axis. Similarly, the slider 132 may drive the piston 124 to reciprocate linearly in the cylinder bore 120 through the connection end 126 of the piston 124. The reciprocating linear motion of the piston 124 in the cylinder bore 120 can drive the fluid to be displaced through the fluid passage 128. When the swash plate 130 pushes the piston 124 toward the bottom dead center (e.g., away from the distributor system 100) in the cylinder bore 120, the fluid can flow into the cylinder bore 120 through the fluid passage 128. Similarly, when the swash plate 130 pushes the piston 124 toward the top dead center (e.g., toward the distributor system 100) in the cylinder bore 120, the fluid will be squeezed out of the cylinder bore 120 and flow through the fluid passage 128. Figure 2-5 As mentioned above, any fluid flowing through the axial piston system 105 may also flow through the distributor plate 106 and the distributor body 102 .

[0024] In other examples, the shaft 109 may be coupled to the cylinder block 134 instead of the swash plate 130. When the shaft 109 rotates about the central axis 108, the cylinder block 134 may rotate about the central axis 108 simultaneously with the shaft 109. The position of the piston 124 in the cylinder bore 120 may drive the piston 124 to rotate about the central axis 108 simultaneously with the cylinder block 134 and the shaft 109. Similarly, the coupling end 126 of the piston 124 may drive the slider 132 to rotate about the central axis 108 simultaneously with the piston 124, the cylinder block 134, and the shaft 109. When the slider 132 rotates about the central axis 108, the slider 132 may maintain coplanar contact with the swash plate 130. When the slider 132 rotates about the central axis 108, the orientation of the swash plate 130 relative to the cylinder block 134 may drive the slider 132 to reciprocate linearly along an axis parallel to the x-axis. Likewise, when the piston 124 rotates about the central axis 108, the slider 132 can drive the piston 124 to perform reciprocating linear motion in the cylinder bore 120. When the piston 124 moves toward the bottom dead center in the cylinder bore 120 (e.g., away from the distributor system 100), the fluid can enter the cylinder bore 120 through the fluid passage 128. Likewise, when the piston 124 moves toward the top dead center in the cylinder bore 120 (e.g., toward the distributor system 100), the fluid is squeezed out of the cylinder bore 120 and passes through the fluid passage 128. Figure 2-5As mentioned above, any fluid flowing through the axial piston system 105 may also flow through the distributor plate 106 and the distributor body 102 .

[0025] In some examples, the axial piston system 105 may include a control piston (not shown). The control piston may be coupled to an outer surface of the system body 107 of the axial piston system 105 and may be located above the swash plate 130 relative to the Y axis. The control piston may apply a force to the swash plate 130 to change the angle of the swash plate 130 relative to the central axis 108. As the angle of the swash plate 130 changes, the stroke of the piston 124 in the cylinder bore 120 and the amount of fluid displaced by the piston 124 may also change. In some examples, the control piston may not control the angle of the swash plate 130, but rather sense the current displacement of the axial piston system 105 and send a signal to one or more additional components to change the angle of the swash plate 130.

[0026] Although Figure 1 The example of axial piston system 105 shows that it has a cylinder bore (e.g., cylinder bore 120), a piston (e.g., piston 124), a fluid channel (e.g., fluid channel 128), and a slider (e.g., slider 132), but in some examples, axial piston system 105 can have multiple cylinder bores, pistons, fluid channels, and sliders. Each of the multiple cylinder bores, pistons, fluid channels, and sliders can be configured in a manner similar to Figure 1 The cylinder bore 120, piston 124, fluid passage 128 and slider 132 are configured in the same manner. In addition, the distributor system 100, including the distributor body 102, the distributor plate 106, the bearing element 111 and the adjustment screw 118, will be referred to as Figure 2-5 Describe in more detail.

[0027] like Figure 2 As shown, the distributor system 100 may include a distributor body 102. The distributor body 102 may include a plurality of holes (such as holes), edges and mounting surfaces, which may allow the distributor body 102 to be coupled to other components in a hydraulic axial piston assembly (such as an axial piston assembly) through bolts or other suitable hardware, and to accommodate various hardware, such as shafts or pipes. The plurality of holes in the distributor body 102 may be formed by a suitable process such as machining or injection molding.

[0028] The distributor body 102 may include a front surface 224 and a top surface 226, and the top surface 226 is orthogonal to the front surface 224. The top surface 226 may be the outer surface of the distributor body 102. The top surface 226 may include a fluid inlet channel 228 and a fluid outlet channel 230, which may be the inlet and outlet of the hydraulic axial piston assembly, respectively, but the positions of the inlet and outlet may be interchangeable without departing from the scope of the present disclosure. In some examples, the fluid inlet channel 228 and the fluid outlet channel 230 may be arranged on a raised area of ​​the top surface 226. In addition, the top surface 226 may also include an adjustment screw hole 122 (e.g., a first hole). The adjustment screw hole 122 may extend from the top surface 226 along an axis parallel to the Y-axis into the distributor body 102.

[0029] The front surface 224 can be a coupling surface and can be configured to couple with the axial piston system to facilitate the distribution of fluid into and out of the axial piston system. In some examples, the axial hole 104 can be included on the front surface 224 of the dispenser body 102. The axial hole 104 can be circular and along an axis parallel to the x-axis (e.g. Figure 3 The central axis 108 in the dispenser body 102 extends from the front surface 224 to the rear surface (not visible) of the dispenser body 102. The shaft hole 104 can be configured to accommodate a shaft (e.g., a crankshaft) that is oriented perpendicular to the front surface 224 and passes through the front surface 224 and the rear surface (not visible) of the dispenser body 102. The longitudinal axis of the shaft can be aligned with Figure 3 In addition, the shaft can be configured to be arranged in the axial hole 104 of the dispenser body 102 about its longitudinal axis (e.g., about Figure 3 The shaft may be coupled to a swash plate or other suitable surface and may cause one or more pistons in one or more cylinder bores of an axial piston system to rotate about a central axis 108. Figure 3 The central axis 108 (eg, the longitudinal axis of the shaft) rotates.

[0030] As each piston rotates about the longitudinal axis of the shaft, the swash plate causes the piston to move back and forth in a linear motion within the cylinder bore. The reciprocating linear motion of the piston within the cylinder bore drives fluid displacement through the distributor system 100. When the swash plate pushes the piston toward bottom dead center (BDC), fluid may be forced into the cylinder bore. Similarly, when the swash plate pushes the piston toward top dead center (TDC), fluid may be forced out of the cylinder bore.

[0031] The front surface 224 may also include a plurality of body ports 210. The plurality of body ports 210 may include a first body port 210a, a second body port 210b, a third body port 210c, a fourth body port 210d, a fifth body port 210e, and a sixth body port 210f. In some examples, the first body port 210a, the second body port 210b, and the third body port 210c may be inlet ports. Similarly, in some examples, the fourth body port 210d, the fifth body port 210e, and the sixth body port 210f may be outlet ports. Each of the plurality of body ports 210 may be arranged so that the plurality of body ports 210 are concentrically arranged around the shaft hole 104. In other examples, the plurality of body ports 210 may include a different number of total ports, including one or more inlet ports and one or more outlet ports.

[0032] Each of the first body port 210a, the second body port 210b, and the third body port 210c (e.g., each inlet port in the plurality of body ports 210) can be connected to a fluid inlet passage 228 on the upper surface 226 of the distributor body 102. Thus, the fluid can flow from the fluid inlet passage 228 to each of the first body port 210a, the second body port 210b, and the third body port 210c. Similarly, each of the fourth body port 210d, the fifth body port 210e, and the sixth body port 210f (e.g., each outlet port in the plurality of body ports 210) can be connected to a fluid outlet passage 230 on the upper surface 226 of the distributor body 102. Thus, the fluid can flow from each of the fourth body port 210d, the fifth body port 210e, and the sixth body port 210f to the fluid outlet passage 230.

[0033] The front surface 224 of the dispenser body 102 may not be completely flat (e.g., planar), and may include one or more recessed areas, such as the recessed area 260. The recessed area 260 may be recessed into the front surface 224 by an amount within a range of 0.08 + / - 0.01 cm. A first portion 262 of the recessed area 260 may be an annular area adjacent to the shaft hole 104 on the front surface 224. Thus, the first portion 262 of the recessed area 260 may be located between the shaft hole 104 and the plurality of body ports 210 on the front surface 224. A second portion 264 of the recessed area 260 may be an annular area located around the plurality of body ports 210 on the front surface 224. Thus, the plurality of body ports 210 may be disposed on an area of ​​the front surface 224 that is surrounded by the recessed area 260 but is not recessed itself. In addition, the bearing element hole 116 may be located at the topmost point of the second portion 264 of the recessed area 260 relative to the Y-axis.

[0034] The first portion 262 and the second portion 264 of the recessed area 260 can be connected by a third portion 266 and a fourth portion 268 of the recessed area 260. The third portion 266 of the recessed area 260 can include two oblong grooves extending downward (e.g., relative to the Y axis) from the first portion 262 and through the second portion 264. The first oblong groove of the third portion 266 can be laterally offset (e.g., relative to the Z axis) from the second oblong groove of the third portion 266. The bottommost edge (e.g., relative to the Y axis) of each oblong groove of the third portion 266 can be rounded.

[0035] The fourth portion 268 of the recessed area 260 may include two oblong grooves extending upward (e.g., relative to the y-axis) from the first portion 262 and through the second portion 264. The first oblong groove of the fourth portion 268 may be laterally offset (e.g., relative to the z-axis) from the second oblong groove of the fourth portion 268. The topmost edge (e.g., relative to the y-axis) of each oblong groove of the fourth portion 268 may be rounded. In addition, the bearing element hole 116 may be located on the front surface 224 between the first oblong groove and the second oblong groove of the fourth portion 268 of the recessed area 260.

[0036] like Figure 2 As shown, the distributor system 100 may also include a distributor plate 106. The distributor plate 106 may have a first plane 232. The distributor plate 106 may also have a second plane 306, such as Figure 3 As shown, the second plane 306 is opposite to the first plane 232 on the distributor plate 106. The first plane 232 can be away from the distributor body 102 of the distributor system 100 (e.g., the positive X direction), and the second plane 306 can be toward the distributor body 102 (e.g., the negative X direction). Therefore, the first plane 232 can be configured to contact the axial piston system of the distributor system 100, and the second plane 306 can be configured to contact the distributor body 102. The first plane 232 can be configured to be fluidly coupled to one or more cylinder bores of the axial piston system. In addition, the distributor plate 106 can also include a circumferential outer surface 236, wherein the circumferential outer surface 236 is located between the first plane 232 and the second plane 306 and is orthogonal thereto. The diameter D1 of the distributor plate 106 is approximately 10.3 cm (e.g., the diameter of the first plane 232 and the second plane 306), and the thickness W1 is approximately 0.05 cm (e.g., the width of the circumferential outer surface 236). Additionally, the distributor plate 106 may further include a notch 256. The notch 256 may be disposed at the topmost portion of the distributor plate 106 (eg, relative to the Y-axis) and may extend downward from the circumferential outer surface 236 to the second plane 306.

[0037] In some examples, the distributor plate 106 may include a center hole 258, which may be circular. Relative to the yz plane of the distributor plate 106, the center hole 258 may pass through the center of the first plane 232 and the center of the second plane 306. The center hole 258 can accommodate the axis passing through the axial hole 104 of the distributor body 102. In addition, the distributor plate 106 may also include a plurality of plate ports 208. The plurality of plate ports 208 may include a first plate port 208a, a second plate port 208b, a third plate port 208c, a fourth plate port 208d, a fifth plate port 208e, and a sixth plate port 208f. Each port of the plurality of plate ports 208 may pass through the first plane 232 and the second plane 306 of the distributor plate 106, and may be arranged so that the plurality of plate ports 208 are concentrically distributed around the center hole 258. As shown in FIG. Figure 5 As shown, one or more of the plurality of plate ports 208 (e.g., the first plate port 208a and the sixth plate port 208f) may include a tapered edge and / or a pointed notch on the first plane 232 that does not extend through the distributor plate 106 to the second plane 306.

[0038] In some examples, the first plate port 208a, the second plate port 208b, and the third plate port 208c can be inlet ports. Similarly, in some examples, the fourth plate port 208d, the fifth plate port 208e, and the sixth plate port 208f can be outlet ports. In other examples, the plurality of body ports 210 can include a different number of total ports, including one or more inlet ports and one or more outlet ports.

[0039] Each port in the plurality of plate ports 208 may be fluidically coupled to a fluid inlet channel 228 or a fluid outlet channel 230 on the top surface 226 through a port in the plurality of body ports 210. The first plate port 208a, the second plate port 208b, the third plate port 208c, the fourth plate port 208d, the fifth plate port 208e, and the sixth plate port 208f may be fluidically coupled to the first body port 210a, the second body port 210b, the third body port 210c, the fourth body port 210d, the fifth body port 210e, and the sixth body port 210f, respectively. Therefore, the fluid may flow from the fluid inlet channel 228 through each inlet port in the plurality of body ports 210 to each port in the first plate port 208a, the second plate port 208b, and the third plate port 208c (e.g., to each inlet port in the plurality of plate ports 208). Likewise, fluid may flow from the fourth plate port 208 d , the fifth plate port 208 e , and the sixth plate port 208 f (eg, from each outlet port in the plurality of plate ports 208 ), through each outlet port in the plurality of body ports 210 , and toward the fluid outlet passage 230 .

[0040] As described above, the reciprocating linear motion of the axial piston system piston can drive fluid through the distributor system 100. In addition, when the cylinder is aligned with a port in the plurality of plate ports 208, fluid can be pumped into or out of the cylinder. As the piston moves downward toward BDC, the fluid can be forced into the cylinder when the cylinder passes one of the three inlets of the plurality of plate ports 208. Similarly, as the piston moves from BDC to TDC, the fluid can be forced out of the cylinder when the cylinder passes one of the three outlets of the plurality of plate ports 208.

[0041] The second planar surface 306 of the distributor plate 106 can be oriented parallel to the front surface 224 of the distributor body 102. Figure 3-5 As shown, at least a portion of the second plane 306 of the distributor plate 106 may be in coplanar contact with the front surface 224 of the distributor body 102. The second plane 306 of the distributor plate 106 may not be in coplanar contact with the front surface 224 in the recessed area 260. Therefore, the second plane 306 may only be in contact with the portion of the front surface 224 of the distributor body 102 that is not in the recessed area 260. In addition, when the distributor plate 106 is located Figure 3 When in the position shown (eg, with notch 256 in the vertically highest position), each of the plurality of plate ports 208 may be aligned with one of the plurality of body ports 210 such that fluid may flow in series through one body port and one plate port.

[0042] like Figure 4 As shown, the first body port 210a can be aligned with the first plate port 208a so that at least a portion of the first plate port 208a overlaps with the first body port 210a relative to an axis parallel to the X-axis. The circular arrangement of the plurality of body ports 210 and the plurality of plate ports 208 can allow at least a portion of each body port to overlap around the distributor plate 106. Figure 3 The central axis 108 in the plate is rotated to overlap at least a portion of the plate port. Figure 4In the illustrated distributor plate position, the first plate port 208a includes an end region 406 that overlaps the distributor body front surface 224 but not the first body port 210a. The end region 406 may have a length L1 and may extend from one end of the first body port 210a to a corresponding end of the first plate port 208a. Thus, as the distributor plate 106 rotates and the position of the first plate port 208a changes relative to the position of the first body port 210a, the length L1 may change. As the length L1 of the end region 406 changes through the rotation of the distributor plate 106, the amount of overlap between the first plate port 208a and the first body port 210a may also change. In addition, as the amount of overlap between the first plate port 208a and the first body port 210a changes (e.g., as the length L1 of the end region 406 changes), the timing angle of pumping fluid through the first plate port 208a and the first body port 210a may also change.

[0043] Figure 4 Also shown are a first portion 262, a second portion 264, and a fourth portion 268 of the recessed area 260, which are partially located behind the distributor plate 106 (e.g., relative to the X-axis). The recessed area 260 can reduce friction between the distributor plate 106 and the front surface 224 of the distributor body 102 when the distributor plate 106 rotates. In addition, the shape of the portions of the recessed area 260 may not prevent the distributor plate 106 from forming a seal with the front surface 224 of the distributor body 102. Therefore, when fluid is pumped through the front surface 224 of the distributor system 100, it may be restricted from passing through the plurality of plate ports 208 and the plurality of body ports 210.

[0044] The distributor plate 106 may include one or more tapered edges on the plurality of plate ports 208, such as a first tapered edge 408 on the first plate port 208a. Figure 5 As shown, one or more tapered edges may have different sizes and shapes. The first tapered edge 408 may have a shorter length (e.g., relative to the Z-axis direction), a shorter height (e.g., relative to the Y-axis direction), and a shorter depth (e.g., relative to the X-axis direction) than the second tapered edge 502. In some examples, one or more tapered edges, such as the first tapered edge 408 and the second tapered edge 502, may be pyramid-shaped.

[0045] like Figure 2 As shown, the dispenser system 100 may include a bearing element 111 (e.g., an eccentric bearing) consisting of a bearing body 114 and an eccentric pin 112. The bearing body 114 may be cylindrical and may have a front surface 238 and a rear surface (at Figure 2-5The eccentric pin 112 may include a front hole 252, which may be eccentrically disposed on the front surface 238. The front hole 252 may be circular and extend from the front surface 238 into the bearing body 114 along an axis parallel to the x-axis. In addition, the bearing body 114 may also include an outer circumferential surface 240, which is located in the middle and orthogonal to the front surface 238 and the rear surface. The outer circumferential surface 240 may include a top hole 254. The top hole 254 may be elliptical or oval and may extend downward from the top of the outer circumferential surface 240 (e.g., relative to the Y-axis) into the bearing body 114 along an axis parallel to the Y-axis. The eccentric pin 112 may include a base 242 and a head 244, wherein the base 242 is connected to the head 244.

[0046] The dispenser system 100 may include an adjustment screw 118 and a locking nut 220. The adjustment screw 118 may include a body 246, a longitudinal end 248, and a coupling end 250, wherein the body 246 may be located between the longitudinal end 248 and the coupling end 250. Thus, the longitudinal end 248 may be connected to the body 246, and the body 246 may be connected to the coupling end 250. In some examples, the locking nut 220 may be a sealed locking nut.

[0047] Reference Figure 3 , the bearing element 111 can be positioned (e.g., accommodated) in a bearing element hole 116 (e.g., a second hole) of the distributor body 102. The bearing element hole 116 can be circular and can extend from the front surface 224 into the distributor body 102 along an axis parallel to the x-axis. In some examples, the bearing element hole 116 can end in a taper. Relative to the Y-axis, the bearing element hole 116 can be located above the shaft hole 104 on the front surface 224. In addition, the center of the bearing element hole 116 can be aligned with the center of the shaft hole 104 along the Z-axis. In addition, the position of the bearing element hole 116 can be such that the bottom point of the bearing element hole 116 is roughly aligned with the top point of the plurality of body ports 210 relative to the Y-axis. Viewed from the front, the distributor plate 106 can at least partially overlap with the bearing element hole 116, Figure 4 and Figure 5 In some examples, the distributor plate 106 may overlap 80% of the bearing element hole 116. The bearing body 114 may be positioned within the bearing element hole 116 so that the outer circumferential surface 240 of the bearing body 114 is in coplanar contact with the inner surface of the bearing element hole 116.

[0048] The front surface 238 of the bearing body 114 can be oriented in the same direction (e.g., along the x-axis) as the front surface 224 of the dispenser body 102. In addition, the front surface 238 of the bearing body 114 can be coplanar with the front surface 224, such that the front surface 238 and the front surface 224 can both extend in the xz plane. In some examples, the front hole 252 can extend along an axis parallel to the x-axis to a position approximately 50% within the bearing body 114. The front hole 252 can accommodate the base 242 of the eccentric pin 112, and the head 244 of the eccentric pin 112 can extend outwardly relative to the x-axis, beyond the front surface 238 of the bearing body 114.

[0049] The base 242 (e.g., front hole 252) of the eccentric pin 112 can be positioned between the upper lip 310 of the bearing body 114 and the lower portion 312 of the bearing body 114. The upper lip 310 can be positioned above the base 242 of the eccentric pin 112 (e.g., relative to the Y-axis) so that the upper lip 310 is located between the base 242 and the top of the inner surface of the bearing element hole 116 (e.g., relative to the Y-axis). The upper lip 310 can be thinner than the lower portion 312 of the bearing body 114 (e.g., relative to the y-axis), so that the position of the base 242 of the eccentric pin 112 is eccentrically positioned relative to the y-axis.

[0050] In some examples, the head 244 of the eccentric pin 112 may be rectangular when viewed from the side, such as Figure 3 From the front, as shown. Figure 4 and Figure 5 As shown, the head 244 of the eccentric pin 112 may include two straight sides parallel to the Y axis and two semicircles above and below the straight sides. In addition, the thickness of the head 244 of the eccentric pin 112 relative to the x-axis (e.g., along an axis parallel to the x-axis) may be substantially equal to the thickness of the distributor plate 106.

[0051] like Figure 3 As shown, the groove 256 of the distributor plate 106 can accommodate at least a portion of the head 244 of the eccentric pin 112. The head 244 can be in coplanar contact with the groove 256, so that the head 244 cannot move freely in the groove 256. Therefore, when the head 244 of the eccentric pin 112 rotates around the rotation axis of the bearing body 114, the head 244 may generate a rotational force on the distributor plate 106. In this way, the eccentric pin 112 can drive the distributor plate 106 to rotate around the central axis 108 (for example, an axis perpendicular to the center of the first plane 232 and the second plane 306 of the distributor plate 106). Similarly, the crankshaft of the axial piston system can rotate around the central axis 108. In addition, the central axis 108 can also define the central axis of the circumferential cylinder array in the axial piston system.

[0052] The base 242 of the eccentric pin 112 can be located in the front hole 252 of the bearing body 114. Therefore, the eccentric pin can be eccentrically positioned in the bearing body 114 (e.g., closer to the top of the bearing body 114 than the bottom of the bearing body 114). The base 242 of the eccentric pin 112 can be in coplanar contact with the inner surface of the front hole 252, so that the eccentric pin 112 cannot translate within the bearing body 114. However, the eccentric pin 112 can rotate about its longitudinal axis (e.g., an axis parallel to the x-axis) within the front hole 252. In this way, when the bearing body 114 and / or the distributor plate 106 rotate about their respective rotational axes, the groove 256 of the distributor plate 106 can accommodate the head 244 of the eccentric pin 112.

[0053] like Figure 3 As shown, the top hole 254 of the outer circumferential surface 240 can extend about 30% into the bearing body 114 along an axis parallel to the Y-axis. The top hole 254 can accommodate the connecting end 250 of the adjustment screw 118 between the rear wall 314 and the upper lip 310. The rear wall 314 can extend upward (e.g., relative to the Y-axis) from the lower portion 312 of the bearing body 114. Therefore, the upper edge of the rear wall 314 of the bearing body 114 can be in coplanar contact with the inner surface of the bearing element hole 116.

[0054] The coupling end 250 of the adjustment screw 118 can be spherical and can extend from the body 246 of the adjustment screw 118 through the connector 304. The radius of the connector 304 can be smaller than the adjustment screw 118 or the connection end 250. In some examples, the size and shape of the coupling end 250 and the connector 304 can lock the coupling end 250 in the groove (e.g., the coupling end 250 can be prevented from translating in one or more directions). For example, the coupling end 250 can be inserted vertically (e.g., along an axis parallel to the Y axis) into the hole (e.g., the top hole 254) and translated in a direction perpendicular to the longitudinal axis of the adjustment screw 118 (e.g., perpendicular to the Y axis). In this way, the connector 304 can be positioned in a recess or groove (e.g., an opening) having a radius smaller than the radius of the coupling end 250. Therefore, the coupling end 250 may not be able to translate vertically (e.g., translate along an axis parallel to the Y axis), and the adjustment screw 118 may be locked in place by the recess or groove.

[0055] The body 246 of the adjustment screw 118 can be cylindrical and can be positioned (e.g., mounted) within the adjustment screw hole 122. The adjustment screw hole 122 can be open to the atmosphere (e.g., accessible from the outside) through an upper surface 226 (e.g., an outer surface) of the dispenser body 102. The adjustment screw 118 can be shorter than the adjustment screw hole 122 so that the adjustment screw 118 can be completely loaded into the adjustment screw hole 122. The body 246 can include threads to connect the adjustment screw 118 to the adjustment screw hole 122. Similarly, at least a portion of the adjustment screw hole 122 can include threads that couple with threads on the body 246 of the adjustment screw 118. In this way, the body 246 of the adjustment screw 118 can be in coplanar contact with the adjustment screw hole 122. In some examples, such as Figure 3 As shown, the lower portion of the adjustment screw hole 122 may have a smaller radius than the upper portion of the adjustment screw hole.

[0056] like Figure 3 and Figure 5 As shown, the longitudinal end 248 of the adjusting screw 118 may include a tool slot 302. The tool slot 302 may be sized and shaped to accommodate a screwdriver, an Allen wrench, or other suitable tool that may be used to rotate the adjusting screw 118. The tool slot 302 may be externally accessible (e.g., open to the atmosphere) such that a tool may be positioned within the tool slot 302 and the adjusting screw 118 may be manually rotated by the tool without disassembling the dispenser system 100. The longitudinal end 248 of the adjusting screw 118 and the tool slot 302 may be positioned within the retaining nut 220 in the dispenser system 100.

[0057] Thus, the adjusting screw 118 can be rotated by a suitable tool disposed in the tool slot 302 of the longitudinal end 248. In turn, the coupling end 250 of the adjusting screw 118 can be rotated and at least a portion of the rotation can be converted into the bearing element 111 through the bearing body 114 (e.g., the adjusting screw 118 can drive the bearing element 111 to rotate). The bearing body 114 can rotate along an axis orthogonal to the rotation axis of the adjusting screw 118. Thus, the eccentric pin 112 can rotate about the rotation axis of the bearing body 114 at the same time as the bearing body 114 (e.g., rotate in the same direction at the same rotation speed). The bearing body 114 can reduce the force applied to the eccentric pin 112 by the adjusting screw 118, and thus can reduce the degradation of the eccentric pin 112.

[0058] The head 244 of the eccentric pin 112 can directly engage with the surface of the distributor plate 106 forming the groove 256. Therefore, the eccentric pin 112 can be rotationally coupled with the groove 256 of the distributor plate 106. The front surface, the bottom surface, the first side surface, and the second side surface of the head 244 can be in coplanar contact with the groove 256, so that the rotational force can be transmitted from the eccentric pin 112 to the distributor plate 106 without increasing the thickness of the distributor plate 106. In this way, the distributor plate 106 can rotate around a rotation axis (e.g., around the central axis 108), which is parallel to the rotation axis of the bearing body 114, but offset therefrom. Due to the offset of the rotational axes of the bearing body 114 and the distributor plate 106, and the position of the head 244 of the eccentric pin 112 in the groove 256, the eccentric pin 112 can also rotate around the longitudinal axis of the eccentric pin in the front hole 252. Therefore, by rotating the adjustment screw 118, the operator can rotate the distributor plate 106. As the distributor plate 106 rotates, the behavior of the distributor system 100 may be varied by changing the operating pressure and timing angle of the fluid passing through the distributor system 100 .

[0059] Figure 6 is a flow chart illustrating a method 600 of changing the behavior of a dispenser system. The dispenser system may be Figure 1-5 6 is a non-limiting example of a dispenser system 100. The method 600 may be performed by an operator using a screwdriver, a hex wrench, or other suitable tool.

[0060] At 602, method 600 may include rotating an adjustment screw using an external tool. The external tool may be a screwdriver, an Allen wrench, or other suitable tool. The adjustment screw may be Figure 1-5 A non-limiting example of an adjusting screw 118 in the dispenser system. Therefore, one longitudinal end of the adjusting screw may include a tool slot for mounting an external tool. The external tool may apply a rotational force to the adjusting screw to rotate the adjusting screw in the adjusting screw hole of the dispenser body of the dispenser system. The tool slot and the adjusting screw hole may be respectively Figure 3 Tool slot 302 and Figure 1 Non-limiting example of an adjustment screw hole 122 .

[0061] At 604, method 600 may include rotating a coupling end of an adjusting screw within a bearing element. The coupling end of the adjusting screw may be positioned at a longitudinal end of the adjusting screw that is distal from the tool slot, so that when the adjusting screw is rotated within the adjusting screw hole, the coupling end of the adjusting screw may also rotate simultaneously with the rotation of the tool end (e.g., at the same speed and in the same direction). The coupling end may be positioned within a top hole of a bearing body, such as top hole 254 of bearing body 114.

[0062] At 606, method 600 may include rotating the bearing body and the eccentric pin via an adjusting screw. The adjusting screw may be rotationally coupled to the bearing body via a coupling end and a top hole. Thus, rotating the adjusting screw via an external tool may drive the bearing body to rotate within the bearing element hole. In some examples, the rotation axis of the bearing body may be orthogonal to the rotation axis of the adjusting screw. A portion of the eccentric pin may be located within the bearing body, and thus, the eccentric pin may be rotationally coupled to the bearing body. Thus, when the bearing body is rotated via the adjusting screw, the eccentric pin may rotate about the rotation axis of the bearing body.

[0063] At 608, method 600 may include rotating a distributor plate connected to the distributor body via an eccentric pin. As previously described, the distributor plate may include a notch (e.g., Figure 2 The distributor plate is provided with a recess 256 in the bearing body, which can accommodate a portion of the eccentric pin so that at least a portion of the eccentric pin is in coplanar contact with at least a portion of the inner surface of the recess. In this way, the distributor plate can be rotatably connected to the eccentric pin. Therefore, when the eccentric pin rotates about the rotation axis of the bearing body, a rotational force is applied to the distributor plate. The rotational force applied by the eccentric pin to the distributor plate can cause the distributor plate to rotate about an axis that passes perpendicularly through the center hole of the distributor plate.

[0064] As the distributor plate of the distributor system rotates, the position of the plurality of plate ports on the distributor plate may change relative to the plurality of body ports (e.g., the plurality of body ports 210) on the distributor body of the distributor system. Fluid may be pumped through one of the plurality of body ports first and then immediately pumped through one of the plurality of plate ports (e.g., fluid flowing out of the distributor system), or vice versa (e.g., fluid flowing into the distributor system). When the alignment between the ports in the plurality of plate ports and the corresponding ports in the plurality of body ports changes, the area through which the fluid may flow to enter or flow out of the axial piston system may also change. The volume of each cylinder in the axial pump system may remain fixed, so the volume of fluid displaced by the reciprocating piston in the cylinder may also remain fixed. Therefore, if the alignment between the plurality of plate ports and the plurality of body ports changes, the speed at which the fluid enters and exits each cylinder of the axial piston system may also change. Therefore, the pressure at which the distributor system pumps the fluid may change depending on the orientation of the plurality of plate ports relative to the plurality of body ports.

[0065] More specifically, as the distributor plate rotates, the alignment between the plurality of plate ports and the plurality of body ports may change. When the alignment between the ports in the plurality of plate ports and the corresponding ports in the plurality of body ports changes, the area through which fluid may flow to enter or exit the axial piston system may also change. The volume of each cylinder in the axial pump system may remain fixed, and therefore the volume of fluid displaced by the reciprocating piston in the cylinder may also remain fixed. Therefore, if the alignment of the plurality of plate ports with the plurality of valve body ports decreases (e.g., the fluid path becomes narrower), the pressure drop across the distributor plate may increase. Similarly, if the alignment of the plurality of plate ports with the plurality of body ports becomes higher (e.g., the fluid path becomes less constricted), the pressure drop across the distributor plate may decrease. In addition, the rotation of the distributor plate may adjust the timing angle of the fluid pumped by the axial piston system. Changes in the timing angle of the fluid pumped into / out of the cylinder through three independent inlets and three independent outlets may cause fluid pulsation and may affect the amount of noise generated by the axial piston system and the distributor system.

[0066] Fig. 7A A diagram 700 is shown illustrating various behaviors of a dispenser system. A dispenser system may be Figure 1-5 The distributor system 100 is a non-limiting example of a hydraulic axial piston assembly, such as Figure 1 The hydraulic axial piston assembly 101 in the embodiment of the present invention. The hydraulic axial piston assembly may also include an axial piston system, such as Figure 1 In some examples, the axial piston system 105 may be provided with a swash plate at an angle of 3.75 degrees to the distributor plate. In addition, in some examples, the operating pressure of the axial piston system is 420 bar. In addition, in some examples, the piston of the axial piston system may rotate around the central axis at a speed of 3300 revolutions per minute (rpm). In other examples, the angle of the swash plate relative to the distributor plate, the operating pressure, and the rotational speed of the piston around the central axis may also be different suitable values.

[0067] During operation of the hydraulic axial piston assembly, each behavior exhibited by the distributor system may illustrate the movement of a single piston relative to a given position on the distributor plate. When the position of the piston relative to a given position on the distributor plate changes, the timing of the hydraulic axial piston assembly also changes. Therefore, the x-axis of graph 700 may represent the position along a first axis, and the y-axis of graph 700 may represent the position along a second axis, wherein the second axis is orthogonal to the first axis. In some examples, the x-axis of graph 700 may represent the lateral position of the piston (e.g., an axis parallel to the plane of the distributor plate), and the y-axis of graph 700 may represent the longitudinal position of the piston (e.g., an axis perpendicular to the plane of the distributor plate).

[0068] The graph 700 may include a first behavior 702 and a second behavior 708, which may represent a first extreme behavior and a second extreme behavior of the dispenser system, respectively. The dispenser system may exhibit the first behavior 702 when the dispenser plate of the dispenser system is oriented in the first extreme position. The dispenser plate may be configured to rotate within a range of angles (e.g., -10 to 10 degrees, where 0 degrees is Figure 2-5 ), when positioned at one extreme position of the angular range (e.g., rotated to -10 degrees), may be oriented at a first extreme position. Thus, movement of the piston during first behavior 702 may occur at the highest position relative to the Y-axis on graph 700. When the distributor plate is oriented to a second extreme position, the distributor system may exhibit a second behavior 708. When the distributor plate is positioned at the second extreme position of the angular range (e.g., rotated 10 degrees), the distributor plate may be oriented at the second extreme position. Thus, during second behavior 708, movement of the piston may occur at the lowest position relative to the Y-axis on graph 700 because the distributor plate may not be rotated any further away from the first extreme position.

[0069] In addition, graph 700 may also include a first intermediate behavior 704 and a second intermediate behavior 706. When the distributor plate is oriented at a position intermediate to the first extreme position and the second extreme position, the distributor system may exhibit the first intermediate behavior 704. Therefore, relative to the Y-axis, the movement of the piston during the first intermediate behavior 704 may occur at a position on graph 700 that is lower than the first behavior 702 but higher than the second behavior 708. Similarly, when the distributor plate is located between the first intermediate position and the second extreme position, the distributor system may exhibit the second intermediate behavior 706. Therefore, relative to the Y-axis, the movement of the piston during the second intermediate behavior 706 may occur at a position on graph 700 that is lower than the first intermediate behavior 704 but higher than the second behavior 708.

[0070] Each of the first behavior 702, the second behavior 708, the first intermediate behavior 704, and the second intermediate behavior 706 may occur when the distributor plate is in different rotational positions. The position of the distributor plate and the timing of the distributor may also affect the position and / or reaction of the control piston. In turn, the control piston may at least partially affect the relationship between the operating pressure of the axial piston system and the overturning torque on the swash plate of the axial piston system. The overturning torque on the swash plate may at least partially determine the amount of fluid displacement of the axial piston system.

[0071] Figure 7B A graph 710 is shown which illustrates the amount of overturning torque on the hydraulic axial piston assembly swash plate versus Fig. 7AThe relationship between the working pressure of the hydraulic axial piston assembly and the behavior of each distributor system in the graph 710 is shown. Therefore, the x-axis of the graph 710 can represent the working pressure of the hydraulic axial piston assembly as a percentage of the maximum working pressure of the hydraulic axial piston assembly. The y-axis of the graph 710 can represent the overturning torque on the swash plate of the hydraulic axial piston assembly as a percentage of the maximum overturning torque on the swash plate of the hydraulic axial piston assembly.

[0072] Graph 710 may include a first relationship 712, which may correspond to Fig. 7A The first row of graph 700 is 702. Thus, when the distributor plate of the hydraulic axial piston assembly is oriented in a first extreme position (e.g., oriented at one extreme of the distributor plate angular range), a first relationship 712 may occur. When the distributor plate is in the first extreme position, the operating pressure of the hydraulic axial piston assembly may be between 10% and 70% of the maximum operating pressure. When the operating pressure is 10% of the maximum operating pressure, the first relationship 712 may result in 75% of the maximum overturning torque on the swash plate. When the operating pressure increases to 70% of the maximum operating pressure, the overturning moment on the swash plate may decrease to 0% of the maximum overturning moment.

[0073] Graph 710 may include a fourth relationship 718, which may correspond to Fig. 7A Second behavior 708 of graph 700. Thus, when the distributor plate of the hydraulic axial piston assembly is oriented in a second extreme position (e.g., oriented at the opposite end of the distributor plate angular range from the first extreme position), a fourth relationship 718 may occur. When the distributor plate is in the second extreme position, the operating pressure of the hydraulic axial piston assembly may be between 10% and 100% of the maximum operating pressure. When the operating pressure is 10% of the maximum operating pressure, the fourth relationship 718 may result in 90% of the maximum overturning torque on the swash plate. When the operating pressure increases to 100% of the maximum operating pressure, the overturning moment on the swash plate may be reduced to 35% of the maximum overturning moment.

[0074] Graph 710 may include a second relationship 714, which may correspond to Fig. 7A The first intermediate row of graph 700 is 704. Thus, when the distributor plate of the hydraulic axial piston assembly is oriented in a first intermediate position (e.g., oriented between the first extreme position and the second extreme position), a second relationship 714 may occur. When the operating pressure is 10% of the maximum operating pressure, the second relationship 714 may result in 80% of the maximum overturning torque on the swash plate. When the operating pressure increases to 100% of the maximum operating pressure, the overturning moment on the swash plate may decrease to 0% of the maximum overturning moment.

[0075] Graph 710 may include a third relationship 716, which may correspond to Fig. 7AThe second intermediate row of graph 700 is 706. Thus, when the distributor plate of the hydraulic axial piston assembly is oriented in a second intermediate position (e.g., oriented between the first intermediate position and the second extreme position), a third relationship 716 may occur. When the operating pressure is 10% of the maximum operating pressure, the third relationship 716 may result in 85% of the maximum overturning torque on the swash plate. When the operating pressure increases to 100% of the maximum operating pressure, the overturning moment on the swash plate may decrease to 20% of the maximum overturning moment.

[0076] like Figure 7B As shown, for any given percentage of the maximum operating pressure, the overturning torque on the swash plate is lowest at the first relationship 712, second lowest at the second relationship 714, lowest at the third relationship 716, and highest at the fourth relationship 718. When the distributor plate is rotated from the first extreme position to the second extreme position (e.g., from one extreme of the distributor plate angular range to another extreme), if the operating pressure of the hydraulic axial piston pump remains unchanged, the overturning torque on the swash plate may increase. Similarly, if the position of the distributor plate remains unchanged, the overturning torque on the swash plate may increase as the operating pressure of the hydraulic axial piston assembly decreases. Thus, the overturning torque on the swash plate can be adjusted by adjusting the operating pressure of the hydraulic axial piston assembly or by adjusting the position of the distributor plate through an externally accessible and manually rotatable adjustment screw.

[0077] The present disclosure also provides support for a hydraulic axial piston assembly, which includes: a distributor plate, a bearing element directly orthogonally connected to one side of the distributor plate, and an adjustment screw orthogonally connected to the bearing element, wherein the adjustment screw is accessible from the outside and can be manually rotated to adjust the timing angle of the distributor plate. In a first example of the hydraulic axial piston assembly, the bearing element includes a front surface, a rear surface and a circumferential outer surface, and the adjustment screw includes a connecting end, a longitudinal end and a body located between the connecting end and the longitudinal end. In a second example of the hydraulic axial piston assembly, the first example can be optionally included, the circumferential outer surface of the bearing element includes a top hole, and the connecting end of the adjustment screw is located in the top hole. In a third example of the hydraulic axial piston assembly, one or both of the first and second examples can be optionally included, and the hydraulic axial piston assembly further includes: a distributor body, wherein the distributor body includes a front surface and a top surface orthogonal to the front surface. In a fourth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to third examples, the distributor body includes a bearing element hole extending through the front surface of the distributor body, and the distributor body includes an adjustment screw hole extending through the top surface of the distributor body and orthogonal to the bearing element hole. In a fifth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to fourth examples, the bearing element is located in the bearing element hole of the distributor body so that the circumferential outer surface of the bearing element is in coplanar contact with the inner surface of the bearing element hole. In a sixth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to fifth examples, the adjustment screw is located in the adjustment screw hole of the distributor body so that the body of the adjustment screw is in coplanar contact with the inner surface of the adjustment screw hole. In a seventh example of a hydraulic axial piston assembly, optionally including one or more or each of the first to sixth examples, the adjustment screw hole is open to the atmosphere, and the longitudinal end of the adjustment screw includes a tool slot, which is configured to accommodate a tool to rotate the adjustment screw. In an eighth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to seventh examples, the distributor plate includes a first plane, a second plane, and an outer circumferential surface. In a ninth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to eighth examples, the distributor plate includes a center hole and a plurality of plate ports extending through the first plane and the second plane. In a tenth example of a hydraulic axial piston assembly, optionally including one or more or each of the first to ninth examples, the front surface of the bearing element includes a front hole offset from the center of the front surface, wherein the base of the eccentric pin is located in the front hole. In an eleventh example of a hydraulic axial piston assembly, optionally including one or more or each of the first to tenth examples, the head of the eccentric pin is coupled to the base of the eccentric pin, and the head of the eccentric pin extends outward beyond the front surface of the bearing element.In a twelfth example of the hydraulic axial piston assembly, optionally including one or more or each of the first to eleventh examples, the distributor plate includes a recess, an inner surface of the recess being in coplanar contact with a front surface, a bottom surface, a first side surface, and a second side surface of the eccentric pin head of the bearing element.

[0078] The present disclosure also provides support for a hydraulic axial piston assembly, the assembly including: a distributor plate configured to fluidly couple one or more cylinder bores of an axial piston system to a distributor body, the distributor body including a fluid inlet channel and a fluid outlet channel; and an eccentric bearing including a pin mounted in a recess of the distributor plate and configured to rotate by rotation of an adjustment screw, wherein the eccentric bearing and the adjustment screw are located in the distributor body, and the adjustment screw extends orthogonally to the eccentric bearing. In a first example of the hydraulic axial piston assembly, the distributor plate fluidly couples one or more cylinder bores of the axial piston system to the distributor body through a plurality of plate ports of the distributor plate, wherein the positions of the plurality of plate ports are changed by rotation of the distributor plate. In a second example of the hydraulic axial piston assembly, optionally including the first example, the distributor body includes a plurality of body ports, wherein rotating the distributor plate can change the positions of the plurality of plate ports of the distributor plate relative to the plurality of body ports of the distributor body. In a third example of the hydraulic axial piston assembly, optionally including one or both of the first and second examples, the rotation of the adjustment screw drives the eccentric bearing to rotate about a rotation axis orthogonal to the rotation axis of the adjustment screw.

[0079] The present disclosure also provides support for a hydraulic axial piston assembly, the assembly including an axial piston system, a distributor body coupled to the axial piston system via a coupling surface, the distributor body including a fluid inlet channel and a fluid outlet channel, the distributor body also including a first hole extending from an outer surface of the distributor body to a second hole in the distributor body coupling surface, the first hole extending along a first axis, the axis being orthogonal to a second axis along which the second hole extends, and a distributor plate configured to fluidly couple one or more cylinder bores of the axial piston system to the fluid inlet channel and the fluid outlet channel of the distributor body, wherein the distributor plate is rotatable via an eccentric bearing, the eccentric bearing including a pin mounted in a recess of the distributor plate and configured to be rotated by rotation of an adjustment screw, wherein the eccentric bearing is mounted in the second hole and the adjustment screw is mounted in the first hole. In a first example of the hydraulic axial piston assembly, the pin is located in the eccentric bearing such that the pin is offset from the rotation axis of the eccentric bearing. In a second example of the hydraulic axial piston assembly, optionally including the first example, the adjustment screw includes a tool slot accessible from an outer surface of the distributor body, wherein the tool slot is configured to receive a tool to rotate the adjustment screw.

[0080] As used herein, the term "approximately" should be understood to mean a range of plus or minus 5%, unless otherwise specified.

[0081] The following claims particularly point out certain combinations and subcombinations regarded as novel and non-obvious. The claims may refer to "an" element or a "first" element or the equivalent. The claims should be understood to include one or more such elements, neither requiring nor excluding two or more such elements. Other combinations and subcombinations of the disclosed features, functions, elements, and / or properties may be claimed by amendment of the present claims or by presentation of new claims in this or a related application. Such claims, whether broader, narrower, equal, or different in scope to the original claims, are also deemed to be included in the subject matter of the present disclosure.

Claims

1. A hydraulic axial piston assembly, characterized in that: include Distributor plate; a bearing element directly orthogonally connected to one side of the distributor plate; and An adjustment screw is orthogonally connected to the bearing element, the adjustment screw being externally accessible and manually rotatable to adjust the timing angle of the distributor plate.

2. The hydraulic axial piston assembly according to claim 1, characterized in that The bearing element includes a front surface, a rear surface and a circumferential outer surface, and the adjusting screw includes a connecting end, a longitudinal end and a main body located between the connecting end and the longitudinal end.

3. The hydraulic axial piston assembly according to claim 2, characterized in that The circumferential outer surface of the bearing element comprises a top hole, and the connecting end of the adjusting screw is located in the top hole.

4. The hydraulic axial piston assembly according to claim 1, characterized in that Also included is a dispenser body, wherein the dispenser body includes a front surface and a top surface orthogonal to the front surface.

5. The hydraulic axial piston assembly according to claim 4, characterized in that The distributor body includes a bearing element hole passing through the front surface of the distributor body, and the distributor body also includes an adjustment screw hole passing through the top surface of the distributor body and orthogonal to the bearing element hole.

6. The hydraulic axial piston assembly according to claim 5, characterized in that The bearing element is located in the bearing element bore of the dispenser body such that a circumferential outer surface of the bearing element is in coplanar contact with an inner surface of the bearing element bore.

7. The hydraulic axial piston assembly according to claim 5, characterized in that The adjusting screw is located in the adjusting screw hole of the dispenser body so that the body of the adjusting screw is in coplanar contact with the inner surface of the adjusting screw hole.

8. The hydraulic axial piston assembly according to claim 5, characterized in that The adjusting screw hole is open to the atmosphere, and a longitudinal end of the adjusting screw includes a tool slot configured to receive a tool to rotate the adjusting screw.

9. The hydraulic axial piston assembly according to claim 1, characterized in that: The distributor plate includes a first planar surface, a second planar surface, and an outer circumferential surface.

10. The hydraulic axial piston assembly according to claim 9, characterized in that The distributor plate includes a central hole and a plurality of plate ports extending through a first plane and a second plane.

11. The hydraulic axial piston assembly according to claim 2, characterized in that The front surface of the bearing element comprises a front hole offset from the center of the front surface, and the base of the eccentric pin is located in the front hole.

12. The hydraulic axial piston assembly according to claim 11, characterized in that The head of the eccentric pin is connected to the bottom of the eccentric pin, and the head of the eccentric pin extends outwardly beyond the front surface of the bearing element.

13. The hydraulic axial piston assembly of claim 12, wherein: The distributor plate includes a recess, the inner surface of which is in coplanar contact with the front surface, the bottom surface, the first side surface and the second side surface of the eccentric pin head of the bearing element.

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