External control commutation control double valve flow distribution radial plunger hydraulic device and working method thereof

Abstract

The application provides an externally-controlled commutation control double-valve flow distribution radial plunger hydraulic device and a working method thereof, and relates to the technical field of radial plunger hydraulic devices. The device comprises a shell, an eccentric main shaft rotatably arranged on the shell, a plurality of plunger assemblies, a flow distribution shaft in plug-in connection with the eccentric main shaft, a flow collecting disc, a flow distribution shaft end cover, and a liquid control one-way valve and a two-way plug-in valve corresponding to each plunger assembly. The flow distribution shaft end cover is provided with a first external control total port and a second external control total port suitable for connecting an external high-pressure oil source or a low-pressure oil source, so as to control the forward rotation or reverse rotation of the radial plunger hydraulic device. The application can realize bidirectional rotation when used as a hydraulic motor and a hydraulic pump, and the switching is convenient.

Description

Technical Field

[0001] This invention relates to the field of radial piston hydraulic devices, and more specifically, to an externally controlled reversing dual-valve flow distribution radial piston hydraulic device and its working method. Background Technology

[0002] Radial piston hydraulic devices are extremely important actuators in hydraulic systems, widely used in engineering machinery, military machinery, construction machinery, mining machinery and other fields. Common commercial radial piston hydraulic devices, including hydraulic motors and hydraulic pumps, are characterized by low speed and high torque. Radial piston pumps provide power to the hydraulic system by outputting oil with a certain pressure, while radial piston motors output a certain torque and speed to the outside world, enabling the actuator to perform work on the outside world. The performance of hydraulic motors and hydraulic pumps directly affects the performance of the hydraulic system.

[0003] The main flow distribution methods of radial piston hydraulic devices are divided into three types: shaft flow distribution, end face flow distribution, and valve flow distribution. Among them, shaft flow distribution and end face flow distribution can realize the pump state and motor state. When the device is input torque, it works in pump state and can output high-pressure fluid to the outside. When the device is input high-pressure fluid, it is in motor state and outputs torque and speed to the outside. However, radial piston hydraulic devices using these two flow distribution methods have large clearances and significant wear between some of the moving parts, which limits the performance of the motor and pump to some extent. In existing radial piston hydraulic devices, each piston requires two hydraulically controlled check valves or two-way cartridge valves with independent control oil circuits, which makes the oil circuit control inside the housing very complex and the flow distribution device structure complex and costly to manufacture. The invention with publication number CN115898748A discloses a radial piston hydraulic device and working method with a single set of oil circuits controlling dual valve flow distribution, but this invention can only achieve unidirectional rotation of the pump or motor and cannot meet the requirement of bidirectional rotation of the pump and motor. In addition, although there are devices that can achieve reverse rotation, they generally use a reversing spool valve inside the housing to achieve reversal, which also increases the internal volume of the housing and is not conducive to miniaturization design. For example, the four-quadrant radial piston hydraulic device and working method with dual valve flow distribution with publication number CN116378892A. Summary of the Invention

[0004] This invention discloses an externally controlled reversing dual-valve flow distribution radial piston hydraulic device, which aims to improve the problem of the complex structure of existing radial piston hydraulic devices for reversing, resulting in a large overall size of the radial piston hydraulic device.

[0005] The present invention adopts the following solution:

[0006] This application provides an externally controlled reversing dual-valve radial piston hydraulic device, comprising: a housing, an eccentric main shaft rotatably mounted on the housing and multiple piston assemblies, a distribution shaft inserted into the eccentric main shaft, a manifold, a distribution shaft end cap, and hydraulically controlled check valves and two-way cartridge valves corresponding to each piston assembly; the housing contains a plurality of high-pressure oil circuits, low-pressure oil circuits, and control oil circuits, multiple piston chambers corresponding to each piston assembly, multiple hydraulically controlled check valve chambers corresponding to each hydraulically controlled check valve, and multiple two-way cartridge valve chambers corresponding to each two-way cartridge valve. The corresponding two-way cartridge valve cavity has an oil discharge port, a high-pressure port, and a low-pressure port on the outer circumferential surface of the housing; the outer circumference of the distribution shaft is provided with a first control distribution ring groove, a second control distribution ring groove, a first control distribution semi-ring groove, a second control distribution semi-ring groove, a first control oil port of the distribution shaft, and a second control oil port of the distribution shaft. The first control oil port of the distribution shaft is connected to the first control distribution semi-ring groove and the first control distribution ring groove, and the second control oil port of the distribution shaft is connected to the second control distribution semi-ring groove and the second control distribution ring groove.

[0007] The manifold is connected to one side end face of the housing and sleeved on the distribution shaft. It has a high-pressure ring groove and a low-pressure ring groove on its outer periphery. The high-pressure ring groove is always connected to the high-pressure main port and the first high-pressure oil circuit of the housing. The low-pressure ring groove is always connected to the low-pressure main port and the low-pressure oil circuit of the housing. The distribution shaft end cover is provided with a first external control main port and a second external control main port suitable for connecting to an external high-pressure oil source or a low-pressure oil source.

[0008] The manifold is provided with multiple manifold first control oil circuits, manifold second control oil circuits, and manifold third control oil circuits. One end of the manifold first control oil circuit is connected to the housing first control oil circuit and the housing second control oil circuit, and the other end is adapted to be alternately connected to the distribution shaft first control oil port and the distribution shaft second control oil port.

[0009] The hydraulically controlled one-way valve includes a first oil control chamber, a first high-pressure chamber, and a first low-pressure chamber. The first high-pressure chamber is connected to a corresponding plunger chamber, and the first low-pressure chamber is connected to the low-pressure main port. The first oil control chamber is connected to the first control oil circuit of each corresponding manifold. When the first high-pressure chamber and the first oil control chamber are simultaneously subjected to high-pressure oil, the first high-pressure chamber and the first low-pressure chamber are connected. The two-way cartridge valve includes a second high-pressure oil chamber, a second low-pressure oil chamber, and a second control oil chamber. The second low-pressure oil chamber is connected to a corresponding plunger chamber, and the second high-pressure oil chamber is connected to the high-pressure main port. The second control oil chamber is connected to the first control oil circuit of each corresponding manifold. When the second control oil chamber and the second high-pressure oil chamber are simultaneously subjected to high-pressure oil, the second high-pressure oil chamber and the second low-pressure oil chamber are closed.

[0010] The second control oil circuit of the manifold is always connected to the second external control port and the second control distribution ring groove, and is connected to the second control oil port of the distribution shaft through the second ring groove hole. It is then connected to multiple housing control oil circuits through multiple manifold first control oil circuits to achieve the opening and closing control of the two-way cartridge valve and the hydraulically controlled check valve. The third control oil circuit of the manifold is always connected to the first external control port and the first control distribution ring groove, and is connected to the first control oil port of the distribution shaft through the first ring groove hole. It is then connected to multiple housing control oil circuits through multiple manifold first control oil circuits to achieve the opening and closing control of the two-way cartridge valve and the hydraulically controlled check valve. Its control opening and closing is opposite to the control action of the second control oil circuit of the manifold. The first external control port and the second external control port are suitable for switching between high-pressure oil source and low-pressure oil source to realize the forward or reverse rotation of the radial piston hydraulic device.

[0011] Furthermore, counterweights are provided on both sides of the eccentric spindle, and the counterweights are fixedly connected to the eccentric spindle by screws.

[0012] Furthermore, the hydraulic control check valve includes a first valve body and a second valve body disposed within the first valve body. The first valve body is provided with a first oil control chamber, and the second valve body is provided with a first movable chamber, a first high-pressure chamber, a first low-pressure chamber, and a first valve core. The first valve core is movably installed in the first movable chamber and can control the on / off connection between the first high-pressure chamber and the first low-pressure chamber. The first high-pressure chamber is connected to the corresponding plunger chamber, the first low-pressure chamber is connected to the low-pressure main port, and the first oil control chamber is connected to the first control oil circuit of each corresponding manifold.

[0013] Furthermore, the two-way cartridge valve includes a third valve body, a fourth valve body, a fifth valve body, and a second valve core. The third valve body has a second high-pressure oil chamber and a second low-pressure oil chamber inside. The fourth valve body has a second control oil chamber inside. The second valve core is movably installed in the fourth valve body and can control the on / off connection between the second high-pressure oil chamber and the second low-pressure oil chamber. The second low-pressure oil chamber is connected to the corresponding plunger chamber. The second high-pressure oil chamber is connected to the high-pressure main port. The second control oil chamber is connected to the first control oil circuit of each corresponding manifold.

[0014] Furthermore, the distribution shaft is adapted to rotate with the eccentric main shaft, the first control distribution semi-annular groove and the second control distribution semi-annular groove on the distribution shaft are arranged opposite to each other, and the first control oil circuit of the plurality of manifolds is adapted to alternately communicate with the first control distribution semi-annular groove and the second control distribution semi-annular groove.

[0015] Furthermore, a first annular groove is formed on the first control distribution annular groove, and a plurality of second annular grooves are formed on the second control distribution annular groove.

[0016] This invention also provides a method for operating an externally controlled reversing dual-valve radial piston hydraulic device. When the radial piston hydraulic device is a hydraulic motor, the high-pressure main port is connected to the pressure oil source as the oil inlet, and the low-pressure main port is connected to the low-pressure oil tank as the oil outlet. At this time, the first external control main port is connected to the externally controlled high-pressure oil source, and the second external control main port is connected to the externally controlled low-pressure oil source. The externally controlled high-pressure oil enters the third control oil circuit of the manifold through the first external control main port. The third control oil circuit of the manifold is connected to the first distribution ring groove of the distribution shaft. The externally controlled high-pressure oil enters the first control oil port through the first ring groove hole on the first distribution ring groove of the distribution shaft. The first control oil port is connected to the first control oil circuit of the manifold. The externally controlled high-pressure oil enters the first control oil circuit and the second control oil circuit of the housing through the first control oil circuit of the manifold.

[0017] The externally controlled low-pressure oil enters the second control oil circuit of the manifold through the second external control port. The second control oil circuit of the manifold is connected to the second distribution ring groove of the distribution shaft. The externally controlled low-pressure oil enters the second control oil port through the second ring groove hole on the second distribution ring groove of the distribution shaft, so that the second control oil port is connected to the first control oil circuit of the manifold. The externally controlled low-pressure oil enters the first control oil circuit and the second control oil circuit of the housing through the first control oil circuit of the manifold.

[0018] The distribution shaft rotates together with the eccentric main shaft, causing the first control oil circuit and the second control oil circuit of the housing to switch between high pressure and low pressure; the first control oil circuit and the second control oil circuit of the housing are connected through the first control oil circuit of the manifold, so that the first control oil circuit and the second control oil circuit of the housing are simultaneously in a high pressure state or a low pressure state.

[0019] When one of the plunger assemblies is in the top position, high-pressure oil flows into the high-pressure annular groove of the manifold through the high-pressure main port and then into the first high-pressure oil circuit of the housing. The first high-pressure oil circuit of the housing is connected to the high-pressure chamber of the two-way cartridge valve. When the first control oil circuit and the second control oil circuit of the housing are both in a low-pressure state, the high-pressure oil chamber and the low-pressure oil chamber of the two-way cartridge valve are connected. The high-pressure oil flows through the low-pressure oil chamber of the two-way cartridge valve and enters the plunger chamber, pushing the plunger assembly to move downward.

[0020] When the plunger assembly is in the bottom position, the eccentric main shaft and the distribution shaft rotate 180 degrees counterclockwise. The corresponding first control oil circuit and second control oil circuit of the housing are in a high-pressure state. At this time, the high-pressure chamber and low-pressure chamber of the two-way cartridge valve are closed, and the first control oil circuit of the housing is connected to the oil control chamber of the hydraulic check valve. At this time, the high-pressure chamber and low-pressure chamber of the hydraulic check valve are connected. The oil in the plunger chamber flows out from the low-pressure main port. Under the action of the thrust of other plunger assemblies and the inertial force of the eccentric main shaft, the plunger assembly moves up and down. The reciprocating motion of several plunger assemblies makes the main shaft continuously output positive torque to convert hydraulic energy into mechanical energy.

[0021] When the hydraulic motor needs to rotate in the reverse direction, connect the first external control port to the external low-pressure oil source and the second external control port to the external high-pressure oil source.

[0022] The present invention also provides another method for operating a dual-valve flow distribution radial piston hydraulic device with external control reversing control. When the radial piston hydraulic device is a hydraulic pump, the high pressure main port is connected to the high pressure oil tank or hydraulic load and is the oil outlet. The low pressure main port is connected to the low pressure oil tank and is the oil inlet. The first external control main port is connected to the external high pressure oil source, and the second external control main port is connected to the external low pressure oil source.

[0023] During oil discharge, the eccentric spindle rotates in the opposite direction, driving the plunger assembly to move up and down. The corresponding plunger chamber volume decreases and the pressure increases. Its pressure is higher than that of the high-pressure oil chamber or hydraulic load. The oil in the plunger chamber enters the low-pressure oil chamber of the two-way cartridge valve. Since the valve core of the two-way cartridge valve is stepped, it can be opened in both directions. The oil then flows through the high-pressure oil chamber of the two-way cartridge valve, through the second oil passage of the end cover, into the first high-pressure oil passage of the housing, the high-pressure ring groove of the manifold, into the high-pressure main port, and finally into the high-pressure oil tank or hydraulic load, thus realizing the oil discharge movement of the plunger assembly.

[0024] When oil is drawn in, high pressure is established at the oil outlet. At this time, the valve core of the two-way cartridge valve is closed, and the eccentric main shaft continues to rotate in the opposite direction, driving at least one plunger assembly to move downward from the top position. The corresponding plunger cavity volume increases, creating a vacuum. The pressure in the plunger cavity is lower than that in the low-pressure oil tank. The oil in the low-pressure oil tank enters the second high-pressure oil circuit of the housing and finally enters the plunger cavity, pushing the plunger assembly downward until the plunger assembly moves to the bottom position. This process is repeated to convert mechanical energy into hydraulic energy.

[0025] When the hydraulic pump needs to rotate in reverse, connect the first external control port to the external low-pressure oil source and the second external control port to the external high-pressure oil source.

[0026] Beneficial effects:

[0027] This solution uses a first external control port and a second external control port to control the radial piston hydraulic device to achieve forward or reverse rotation. By setting up the internal oil circuit, the control oil circuit of the entire device is simplified, and a new type of dual-valve flow distribution method is provided. This can reduce the volume of the entire radial piston hydraulic device housing, which is beneficial for miniaturization design. Attached Figure Description

[0028] Figure 1 This is an exploded structural diagram of an externally controlled reversing dual-valve flow distribution radial plunger hydraulic device provided in an embodiment of the present invention.

[0029] Figure 2 This is an axial cross-sectional schematic diagram of an externally controlled reversing dual-valve flow distribution radial plunger hydraulic device provided in an embodiment of the present invention.

[0030] Figure 3 for Figure 2 A cross-sectional view along the AA direction.

[0031] Figure 4 This is a cross-sectional schematic diagram of a hydraulically controlled check valve for a dual-valve radial piston hydraulic device with externally controlled reversing control, provided in an embodiment of the present invention.

[0032] Figure 5 This is a cross-sectional schematic diagram of a two-way cartridge valve of a dual-valve radial piston hydraulic device for external control reversing control provided in an embodiment of the present invention.

[0033] Figure 6 A front view of the manifold of a dual-valve radial piston hydraulic device for external control reversing control provided in an embodiment of the present invention.

[0034] Figure 7 for Figure 6 BB cross-sectional diagram.

[0035] Figure 8 for Figure 6 CC cross-sectional view.

[0036] Figure 9 This is a cross-sectional schematic diagram of the high and low pressure oil holes of a dual-valve flow distribution radial piston hydraulic device with external control reversing control provided in an embodiment of the present invention.

[0037] Figure 10 for Figure 9 DD cross-sectional view.

[0038] Figure 11 for Figure 9 EE sectional view.

[0039] Figure 12 This is a schematic diagram of side F2 of an externally controlled reversing dual-valve flow distribution radial piston hydraulic device provided in an embodiment of the present invention.

[0040] Figure 13 for Figure 12 A cross-sectional view of FF.

[0041] Figure 14 for Figure 13 A cross-sectional view of GG.

[0042] Figure 15 for Figure 12 A cross-sectional view of HH. Detailed Implementation

[0043] Please see Figures 1 to 15The first embodiment of the present invention provides an externally controlled reversing control dual-valve distribution radial piston hydraulic device, including a housing 4, an eccentric main shaft 18 rotatably disposed on the housing 4 and a plurality of piston assemblies 15, a distribution shaft 6 inserted into the eccentric main shaft 18, a manifold 5, and a hydraulically controlled check valve 11 and a two-way cartridge valve 14 corresponding to each piston assembly 15.

[0044] The housing 4 is provided with a plurality of plunger chambers 20 corresponding to each plunger assembly 15, an eccentric spindle chamber 22, a plurality of hydraulic control check valve chambers 12 corresponding to each of the hydraulic control check valves 11, a plurality of two-way cartridge valve chambers 13 corresponding to each of the two-way cartridge valves 14, a high-pressure oil circuit, a low-pressure oil circuit, and a control oil circuit. The outer circumferential surface of the housing 4 is provided with a drain port 16, a high-pressure port 32, and a low-pressure port 30. Each plunger assembly 15 can slide up and down in the corresponding plunger chamber 20. Each hydraulic control check valve 11 is respectively disposed in the corresponding hydraulic control check valve chamber 12, and each two-way cartridge valve 14 is respectively disposed in the corresponding two-way cartridge valve chamber 13.

[0045] The eccentric spindle 18 is rotatably disposed within the eccentric spindle cavity 22 and is connected in transmission to each of the plunger assemblies 15. The eccentric spindle 18 is screwed to the counterweight plate 17 and is inserted into the distribution shaft 6. The distribution shaft 6 has a first control distribution ring groove 81, a second control distribution ring groove 80, a first control distribution semi-ring groove 85, a second control distribution semi-ring groove 82, a first control oil port 84, and a second control oil port 83 on its outer periphery. The first control oil port 84 is connected to the first control distribution semi-ring groove 85 and the first control distribution ring groove 81, and the second control oil port 83 is connected to the second control distribution semi-ring groove 82 and the second control distribution ring groove 80.

[0046] The manifold 5 is fixed to the side end face of the housing F2 with screws. Its outer circumference is provided with a high-pressure annular groove 65 and a low-pressure annular groove 68. The high-pressure annular groove 65 is always connected to the high-pressure main port 32, and the low-pressure annular groove 68 is always connected to the low-pressure main port 30. The manifold 5 is provided with multiple manifold first control oil passages 66, manifold second control oil passages 69, and manifold third control oil passages 67. The manifold second control oil passage 69 is always connected to the second external control main port 10 and the second control distribution annular groove 80, and is connected to the second control oil port 83 of the distribution shaft through the second annular groove hole 86. The opening and closing control of the two-way cartridge valve 14 and the hydraulic check valve 11 is achieved through multiple first control oil circuits 66 of the manifold and multiple control oil circuits of the housing. The third control oil circuit 67 of the manifold is always connected to the first external control port 9 and the first control distribution ring groove 81. It is connected to the first control oil port 84 of the distribution shaft through the first ring groove hole 89. It is then connected to multiple control oil circuits 66 of the manifold and multiple control oil circuits of the housing to achieve the opening and closing control of the two-way cartridge valve 14 and the hydraulic check valve 11. Its opening and closing control is opposite to the control action of the second control oil circuit 69 of the manifold.

[0047] Each of the hydraulically controlled check valves 11 includes a first valve body 44 and a second valve body 51 disposed within the first valve body 44. The first valve body 44 is provided with a first oil control chamber 43, and the second valve body 51 is provided with a first movable chamber 49, a first high-pressure chamber 35, a first low-pressure chamber 38, and a first valve core 48. The first valve core 48 is movably installed within the first movable chamber 49 and is capable of controlling the connection and disconnection between the first high-pressure chamber 35 and the first low-pressure chamber 38. The first high-pressure chamber 35 is connected to the corresponding plunger chamber 20, the first low-pressure chamber 38 is connected to the low-pressure main port 30, and the first oil control chamber 43 is connected to the first control oil circuit of each corresponding manifold.

[0048] Each of the two-way cartridge valves 14 includes a third valve body 57, a fourth valve body 58, a fifth valve body 63, and a second valve core 56. The third valve body 57 has a second high-pressure oil chamber 52 and a second low-pressure oil chamber 55 inside. The fourth valve body 58 has a second control oil chamber 59 inside. The second valve core 56 is movably installed in the fourth valve body 58 and can control the on / off connection between the second high-pressure oil chamber 52 and the second low-pressure oil chamber 55. The second low-pressure oil chamber 55 is connected to the corresponding plunger chamber 20. The second high-pressure oil chamber 52 is connected to the high-pressure main port 32. The second control oil chamber 59 is connected to the first control oil circuit of each corresponding manifold.

[0049] Please see Figures 1 to 2In one possible embodiment of the present invention, it further includes a shaft end cover 1, a housing end cover 2, and a distribution shaft end cover 8, wherein the shaft end cover 1, the housing end cover 2, the manifold 5, and the distribution shaft end cover 8 are sequentially connected and coaxially disposed on the housing 4.

[0050] Specifically, in this embodiment, for example, a first high-pressure oil passage 90 for the housing, a second high-pressure oil passage 95 for the housing, a first control oil passage 97 for the housing, a second control oil passage 96 for the housing, and a low-pressure oil passage 98 for the housing are provided. The plunger end cap 3 and the plunger 21 form a plunger cavity 20. Figure 3 As shown, there are 5 plunger end caps 3 and 5 plunger chambers 20. Each plunger chamber 20 is equipped with a hydraulically controlled check valve 11 and a two-way cartridge valve 14. The hydraulically controlled check valve 11 and the two-way cartridge valve 14 are respectively installed on the hydraulically controlled check valve chamber 12 and the two-way cartridge valve chamber 13. The number of plunger chambers 20 is not limited to this and can also be 8 or 10. The eccentric spindle 18 is installed in the eccentric spindle chamber 22. The first bearing 23 and the second bearing 25 are respectively installed on the housing end cap 2 and the housing 4 to support the eccentric spindle 18.

[0051] In one possible embodiment of the present invention, the plunger assembly 15 includes a plunger 21 and a connecting rod slipper 26 that can slide up and down within the corresponding plunger cavity 20. The top end of the connecting rod slipper 26 is sleeved inside the plunger 21, and the bottom end of the connecting rod slipper 26 abuts against the bearing at the outer end of the eccentric spindle 18 via a return ring 31.

[0052] Specifically, in this embodiment, the bottom end of the connecting rod slipper 26 is fixed to the third bearing 24 outside the eccentric main shaft 14 by the return ring 31. The plunger 21 slides up and down in the plunger cavity 20, which can drive the eccentric main shaft 18 to rotate through the connecting rod slipper 26 and the return ring 31. This is the working state of the hydraulic motor; or, the rotation of the eccentric main shaft 18 drives the plunger 21 to slide up and down in the plunger cavity 20 through the connecting rod slipper 26 and the return ring 31. This is the working state of the hydraulic pump.

[0053] In this embodiment, the eccentric spindle 18 is installed in the eccentric spindle cavity 22, and there are first bearings 23 and second bearings 25 on its left and right sides, respectively, which are installed on the housing end cover 2 and the housing 4 to provide stable support for the eccentric spindle 18.

[0054] Please see Figures 1 to 4In one possible embodiment of the present invention, the first valve body 44 of the hydraulic control check valve 11 is provided with a first annular groove 46, and the first annular groove 46 is provided with a first through hole 45 communicating with the first oil control chamber. The second valve body 51 is provided with a second annular groove 50, and the second annular groove 50 is provided with a second through hole 39 communicating with the low pressure chamber 38.

[0055] The first valve core 48 includes a valve core column 40, a first valve core block 37 and a second valve core block 41 respectively fixed at both ends of the valve core column 40, and a first elastic member 47 sandwiched between the second valve core block 41 and the second valve body 51. The valve core column 40 is movably sleeved in the first movable cavity 49 and can drive the first valve core block 37 and the second valve core block 41 to move synchronously. The second valve core block 41 is disposed in the first oil control cavity 43 and can divide the first oil control cavity 43 into two independent valve body oil control sub-cavities. The first valve core block 37 is disposed in the first high pressure cavity 35 and can control the opening and closing of the first high pressure cavity 35.

[0056] Specifically, in this embodiment, there are five hydraulically controlled check valves 11, which are evenly distributed in the hydraulically controlled check valve chambers 12 on the housing 4, facing the F2 side. The first valve core block 37 is provided with a first pressure-bearing surface 36, and the second valve core block 41 is provided with a second pressure-bearing surface 42. The area of ​​the first pressure-bearing surface 36 is smaller than the area of ​​the second pressure-bearing surface 42. Therefore, under a suitable pilot ratio, when the first high-pressure chamber 35 and the first oil control chamber 43 are simultaneously subjected to high-pressure oil, the first high-pressure chamber 35 and the first low-pressure chamber 38 will open, that is, the hydraulically controlled check valve 11 is conductive under high pressure.

[0057] Please see Figures 1 to 5 In one possible embodiment of the present invention, the two-way cartridge valve 14 further includes a second elastic element 61 disposed between the second valve core 56 and the fourth valve body 58. The second valve core 56 is provided with an inclined surface 54. The second valve core 56 is provided with a first pressure-bearing surface 53 near the inclined surface 54. The second valve core 56 is provided with a second pressure-bearing surface 62 and a third pressure-bearing surface 60 away from the inclined surface 54.

[0058] The inclined surface 54 is configured to control the opening and closing of the second high-pressure oil chamber 52 and the second low-pressure oil chamber 55. The area of ​​the first pressure-receiving surface 53 is smaller than the sum of the areas of the second pressure-receiving surface 62 and the third pressure-receiving surface 60, so as to ensure that the second high-pressure oil chamber 52 and the second low-pressure oil chamber 55 are closed when the second control oil chamber 59 is under high pressure under a suitable pilot ratio.

[0059] Specifically, in this embodiment, there are five two-way cartridge valves 14, evenly distributed within the two-way cartridge valve chambers 13 on the housing 4. The second valve core 56 can slide within the cavity of the third valve body 57. One end of the second elastic member 61 contacts the fourth valve body 58, and the other end contacts the second valve core 56. The second valve core 56 is provided with the inclined surface 54 to control the opening and closing of the second high-pressure oil chamber 52 and the second low-pressure oil chamber 55. Near the inclined surface 54, the second valve core 56 has the first pressure-receiving surface 53, and the other end is provided with the second pressure-receiving surface 62 and the third pressure-receiving surface 60. The first pressure-receiving surface 53 is smaller than the sum of the second pressure-receiving surface 62 and the third pressure-receiving surface 60. Therefore, under a suitable pilot ratio, when the second control oil chamber 59 and the second high-pressure oil chamber 52 are both high-pressure oil, the second valve core 56 closes, and the second high-pressure oil chamber 52 and the second low-pressure oil chamber 55 are cut off, that is, the two-way cartridge valve 14 closes under high pressure.

[0060] Please see Figures 1 to 8 In one possible embodiment of the present invention, the manifold 5 has a high-pressure ring groove 65 and a low-pressure ring groove 68 on its circumference, and has a first control oil circuit 66, a second control oil circuit 69 and multiple third control oil circuits 67 inside it.

[0061] Specifically, in this embodiment, the manifold 5 serves as a bridge between the housing 4 and the distribution shaft 6. The manifold 5 is fixed to one side of the housing F2 by screws. The manifold 5 is provided with a high-pressure annular groove 65, a low-pressure annular groove 68, a first control oil passage 66, a second control oil passage 69, and multiple third control oil passages 67. The high-pressure annular groove 65 is always connected to the high-pressure main port 32 and the first high-pressure oil passage 90 of the housing. The low-pressure annular groove 68 is always connected to the low-pressure main port 30 and the low-pressure oil passage 98 of the housing. One end of the first control oil passage 66 of the manifold is connected to the first control oil passage 97 and the second control oil passage 96 of the housing, and the other end is alternately connected to the first control oil port 80 and the second control oil port 81 of the distribution shaft.

[0062] Please see Figures 1 to 11In one possible embodiment of the present invention, it further includes a distribution shaft bearing 7, a distribution shaft end cover 8, a first external control port 9, and a second external control port 10. The first external control port 9 and the second external control port 10 are threadedly fixed to the distribution shaft end cover 8. One end of the distribution shaft 6 is supported on the distribution shaft end cover 8 by the distribution shaft bearing 7. The distribution shaft 6 is provided with a first control distribution ring groove 81 and a second control distribution ring groove 80. The first control distribution ring groove 81 and the first ring groove hole 89 are located on the same plane. The first external control port 9, the third control oil passage 67 of the manifold, and the first control distribution ring groove 81 are connected. The second control distribution ring groove 80 and the second ring groove hole 86 are located on the same plane. The second external control port 10, the second control oil passage 69 of the manifold, and the second control distribution ring groove 80 are connected.

[0063] The distribution shaft 6 is also provided with a first control distribution semi-annular groove 85 and a second control distribution semi-annular groove 82. When the distribution shaft 6 rotates with the eccentric main shaft 18, the first control oil passages 66 of the multiple manifolds are alternately connected to the first control distribution semi-annular groove 85 and the second control distribution semi-annular groove 82 respectively.

[0064] The first control distribution ring groove 81 has a plurality of first ring groove holes 89, the second control distribution ring groove 80 has a plurality of second ring groove holes 86, the first control distribution semi-ring groove 85 has a plurality of first semi-ring groove holes 87, and the second control distribution semi-ring groove 82 has a plurality of distribution shaft second semi-ring groove holes 88.

[0065] Specifically, in this embodiment, the first control distribution ring groove 81 has a first ring groove hole 89, and the second control distribution ring groove 80 has multiple second ring groove holes 86. The left end of the distribution shaft 6 is inserted and connected to the eccentric main shaft 18, and the right end of the distribution shaft 6 is supported on the distribution shaft end cover 8 by the distribution shaft bearing 7. The distribution shaft 6 has a first control distribution ring groove 81, a second control distribution ring groove 80, a first control distribution semi-ring groove 85, a second control distribution semi-ring groove 82, a first ring groove hole 89, a second ring groove hole 86, a first semi-ring groove hole 87, and a second semi-ring groove hole 88. The first control distribution ring groove 81 has a first ring groove hole 89, one end of which is connected to the first external control port 9, and the other end is connected to the... The first control port 81 is connected; a second annular groove 86 is provided on the second control distribution annular groove 80, one end of the second annular groove 86 is connected to the second external control main port 10, and the other end is connected to the second control port 80; a first semi-annular groove 87 and a second semi-annular groove 88 are respectively provided on the first control distribution semi-annular groove 85 and the second control distribution semi-annular groove 82, and the first control port 81 is connected to the first semi-annular groove 87 and the first annular groove 89; the second control port 80 is connected to the second semi-annular groove 88 and the second annular groove 86.

[0066] In summary, the externally controlled reversing dual-valve flow distribution radial piston hydraulic device adopts dual-valve flow distribution, which firstly provides a brand-new flow distribution method, allowing the two valves corresponding to each piston to be controlled by the same control oil circuit, simplifying the control oil circuit of the entire device; secondly, the hydraulically controlled check valve has excellent sealing performance, and the two-way cartridge valve has the advantages of excellent sealing performance and large valve port diameter. This device can be used in high-pressure environments and can achieve high volumetric efficiency. This radial piston hydraulic device can be used as a hydraulic motor or a hydraulic pump, solving the problem of the limitation of valve flow distribution in motor applications.

[0067] Combination Figures 12 to 15 As shown, in another embodiment, this invention provides a method for operating an externally controlled reversing dual-valve flow distribution radial piston hydraulic device. Specifically, when the radial piston hydraulic device is a hydraulic motor, the high-pressure main port 32 is connected to the pressure oil source and serves as the oil inlet, while the low-pressure main port 30 is connected to the low-pressure oil tank and serves as the oil outlet. Taking one of the piston components 15 as an example:

[0068] Continue to combine Figures 12 to 15As shown, when the first external control port 9 is connected to the external high-pressure oil source, the second external control port 10 is connected to the external low-pressure oil source (pressure much lower than the pressure of the high-pressure oil source). The external high-pressure oil enters the third control oil circuit 67 of the manifold through the first external control port 9. The third control oil circuit 67 of the manifold is connected to the first distribution ring groove 84 of the distribution shaft. The external high-pressure oil enters the first control oil port 81 through the first ring groove hole 89 on the first distribution ring groove 84 of the distribution shaft. The first control oil port 81 is connected to the first control oil circuit 66 of the manifold. The external high-pressure oil enters the first control oil circuit 97 and the second control oil circuit 96 of the housing through the first control oil circuit 66 of the manifold. The externally controlled low-pressure oil enters the second control oil circuit 69 of the manifold through the second external control port 10. The second control oil circuit 69 of the manifold is connected to the second distribution ring groove 83 of the distribution shaft. The externally controlled low-pressure oil enters the second control oil port 80 through the second ring groove hole 86 on the second distribution ring groove 83 of the distribution shaft. The second control oil port 80 is connected to the first control oil circuit 66 of the manifold. The externally controlled low-pressure oil enters the first control oil circuit 97 and the second control oil circuit 96 of the housing through the first control oil circuit 66 of the manifold. The distribution shaft 6 rotates together with the eccentric main shaft 18, so the first control oil circuit 97 and the second control oil circuit 96 of the housing continuously switch between high pressure and low pressure. The first control oil circuit 97 and the second control oil circuit 96 of the housing are connected through the first control oil circuit 66 of the manifold, so the first control oil circuit 97 and the second control oil circuit 96 of the housing are simultaneously in a high-pressure state or a low-pressure state.

[0069] When one of the plunger assemblies 15 is in the top position, high-pressure oil flows into the high-pressure annular groove 65 of the manifold through the high-pressure main port 32 and then into the first high-pressure oil passage 90 of the housing. The first high-pressure oil passage 90 of the housing is connected to the high-pressure chamber 52 of the two-way cartridge valve. When the first control oil passage 97 and the second control oil passage 96 of the housing are both in a low-pressure state, the high-pressure oil chamber 52 of the two-way cartridge valve is connected to the low-pressure oil chamber 55. The high-pressure oil flows through the low-pressure oil chamber 55 of the two-way cartridge valve and into the third high-pressure oil passage 94 of the housing, then into the second high-pressure oil passage 95 of the housing, and flows through the third oil passage 93 of the plunger end cap and the first oil passage 91 of the plunger end cap to enter the plunger chamber 20, pushing the plunger assembly 15 to move downward.

[0070] When the plunger assembly 15 is in the bottom position, the eccentric main shaft 18 and the distribution shaft 6 rotate 180 degrees counterclockwise (viewed from the F1 direction). The corresponding first control oil circuit 97 and second control oil circuit 96 of the housing are in a high-pressure state. At this time, the high-pressure chamber 52 and the low-pressure chamber 55 of the two-way cartridge valve are closed, and the first control oil circuit 97 of the housing is connected to the control oil chamber 43 of the hydraulic check valve. At this time, the high-pressure chamber 32 and the low-pressure chamber 38 of the hydraulic check valve are connected. The oil in the plunger chamber 20 flows through the first oil circuit 91 and the third oil circuit 93 of the plunger end cap, the second high-pressure oil circuit 95 of the housing, the high-pressure chamber 35 of the hydraulic check valve, the low-pressure chamber 38, and then flows into the low-pressure ring groove 68 of the manifold through the low-pressure oil circuit 98 of the housing, and finally flows out from the low-pressure main port 30.

[0071] When the hydraulic motor needs to rotate in the reverse direction, connect the first external control port 9 to the external control low-pressure oil source (lower than the pressure of the pressure oil source), and connect the second external control port 10 to the external control high-pressure oil source.

[0072] In the hydraulic motor state, the flow direction of the oil is as follows: the pressure oil source flows to the high-pressure main port 32, to the manifold high-pressure annular groove 65, to the housing first high-pressure oil passage 90, to the plunger end cap second oil passage 92, to the two-way cartridge valve high-pressure oil chamber 52, to the two-way cartridge valve low-pressure oil chamber 55, to the housing third high-pressure oil passage 94, to the housing second high-pressure oil passage 95, to the plunger end cap third oil passage 93, to the plunger end cap first oil passage 91, to the plunger chamber 20, to the plunger end cap first oil passage 91, to the plunger end cap third oil passage 93, to the housing second high-pressure oil passage 95, to the hydraulic control check valve high-pressure chamber 35, to the hydraulic control check valve low-pressure chamber 38, to the housing low-pressure oil passage 98, to the manifold low-pressure annular groove 68, and to the low-pressure main port 30.

[0073] In this embodiment, when the radial plunger hydraulic device is a hydraulic pump, the high-pressure main port 32 is connected to the high-pressure oil tank or hydraulic load and serves as the oil outlet, while the low-pressure main port 30 is connected to the low-pressure oil tank and serves as the oil inlet. Taking one of the plunger assemblies 15 as an example:

[0074] During oil discharge, the eccentric spindle 18 rotates in the opposite direction, driving the plunger assembly 15 to move upward. The volume of the corresponding plunger chamber 20 decreases, and the pressure increases. Its pressure is higher than that of the high-pressure oil chamber or the hydraulic load. The oil in the plunger chamber 20 flows through the first oil passage 91 and the third oil passage 93 of the plunger end cover, the second high-pressure oil passage 95 and the third high-pressure oil passage 95 of the housing, and enters the low-pressure oil chamber 55 of the two-way cartridge valve. Since the valve core of the two-way cartridge valve is stepped, it can be opened in both directions. The oil then flows through the high-pressure oil chamber 52 of the two-way cartridge valve, through the second oil passage 92 of the end cover, into the first high-pressure oil passage 90 of the housing, the high-pressure ring groove 65 of the manifold, and into the high-pressure main port 32. Finally, it enters the high-pressure oil tank or the hydraulic load, realizing the oil discharge movement of the plunger assembly 15.

[0075] When oil is drawn in, high pressure has been established at the oil outlet, the two-way cartridge valve core is closed, and the eccentric spindle 18 continues to rotate in the opposite direction, driving at least one plunger assembly 15 to move downward from the top position. The volume of the corresponding plunger cavity 20 increases, creating a vacuum. The pressure in the plunger cavity 20 is lower than that in the low-pressure oil tank. The oil in the low-pressure oil tank flows through the low-pressure main port 30, the low-pressure ring groove 68 of the manifold, the low-pressure oil passage 98 of the housing, the low-pressure chamber 38 of the hydraulic control check valve, and the high-pressure chamber 35 into the second high-pressure oil passage 95 of the housing. It then flows through the third oil passage 93 of the plunger end cap and the first oil passage 91 into the plunger cavity 20, pushing the plunger assembly 15 downward until the plunger assembly 15 moves to the bottom position.

[0076] When the hydraulic pump needs to rotate in reverse, connect the first external control port 9 to the external control low-pressure oil source (lower than the pressure of the pressure oil source), and connect the second external control port 10 to the external control high-pressure oil source.

[0077] In hydraulic pump mode, the oil flow direction is as follows: from the low-pressure tank to the low-pressure main port 30, to the low-pressure annular groove 68 of the manifold, to the low-pressure oil passage 98 of the housing, to the low-pressure chamber 38 of the hydraulic control check valve, to the high-pressure chamber 35 of the hydraulic control check valve, to the second high-pressure oil passage 95 of the housing, to the third oil passage 93 of the plunger end cap, to the first oil passage 91 of the plunger end cap, to the plunger chamber 20, and to the third oil passage 93 of the plunger end cap. One oil passage 91 flows to the third oil passage 93 of the plunger end cap, flows to the second high-pressure oil passage 95 of the housing, flows to the third high-pressure oil passage 94 of the housing, flows to the low-pressure oil chamber 55 of the two-way cartridge valve, flows to the high-pressure oil chamber 52 of the two-way cartridge valve, flows to the second oil passage 92 of the plunger end cap, flows to the first high-pressure oil passage 90 of the housing, flows to the high-pressure annular groove 65 of the manifold, flows to the high-pressure main port 32, and flows to the high-pressure oil tank or hydraulic load.

[0078] The present invention employs a novel dual-valve flow distribution scheme, which places the control oil circuit outside the housing. This reduces the required switching space and simplifies the control oil circuit of the flow distribution device. At the same time, it enables the radial piston hydraulic device to achieve bidirectional rotation of the hydraulic pump and hydraulic motor, and solves the problem that existing hydraulic control check valves or two-way cartridge valves cannot achieve bidirectional rotation of the hydraulic pump and hydraulic motor.

[0079] It should be understood that the above are merely preferred embodiments of the present invention, and the scope of protection of the present invention is not limited to the above embodiments. All technical solutions that fall within the scope of the present invention are within the scope of protection of the present invention.

[0080] The accompanying drawings used in the above description of the embodiments only illustrate certain embodiments of the present invention and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained from these drawings without creative effort.

Claims

1. A dual-valve radial piston hydraulic device with externally controlled reversing function, comprising: The system comprises a housing, an eccentric main shaft rotatably mounted on the housing, multiple plunger assemblies, a distribution shaft inserted into the eccentric main shaft, a manifold, a distribution shaft end cap, and hydraulically controlled check valves and two-way cartridge valves corresponding to each plunger assembly. The housing contains a first high-pressure oil circuit, a second high-pressure oil circuit, a low-pressure oil circuit, a first control oil circuit, and a second control oil circuit; multiple plunger chambers corresponding to each plunger assembly; multiple hydraulically controlled check valve chambers corresponding to each hydraulically controlled check valve; and multiple two-way cartridge valve chambers corresponding to each two-way cartridge valve. The valve chamber is a through-hole valve. The outer circumferential surface of the housing is provided with an oil discharge port, a high-pressure port, and a low-pressure port. The outer circumference of the distribution shaft is provided with a first control distribution ring groove, a second control distribution ring groove, a first control distribution semi-ring groove, a second control distribution semi-ring groove, a first control oil port of the distribution shaft, and a second control oil port of the distribution shaft. The first control oil port of the distribution shaft is connected to the first control distribution semi-ring groove and the first control distribution ring groove. The second control oil port of the distribution shaft is connected to the second control distribution semi-ring groove and the second control distribution ring groove. The manifold is connected to one side end face of the housing and sleeved on the distribution shaft. It has a high-pressure ring groove and a low-pressure ring groove on its outer periphery. The high-pressure ring groove is always connected to the high-pressure main port and the first high-pressure oil circuit of the housing. The low-pressure ring groove is always connected to the low-pressure main port and the low-pressure oil circuit of the housing. The distribution shaft end cover is provided with a first external control main port and a second external control main port suitable for connecting to an external high-pressure oil source or a low-pressure oil source. The manifold is provided with multiple manifold first control oil circuits, manifold second control oil circuits, and manifold third control oil circuits. One end of the manifold first control oil circuit is connected to the housing first control oil circuit and the housing second control oil circuit, and the other end is adapted to alternately connect to the distribution shaft first control oil port and the distribution shaft second control oil port. The distribution shaft is adapted to rotate with the eccentric main shaft. The first control distribution semi-annular groove and the second control distribution semi-annular groove on the distribution shaft are arranged opposite to each other, and the multiple manifold first control oil circuits are adapted to alternately connect to the first control distribution semi-annular groove and the second control distribution semi-annular groove. A first annular groove hole is opened on the first control distribution annular groove, and multiple second annular groove holes are opened on the second control distribution annular groove. The hydraulically controlled one-way valve includes a first oil control chamber, a first high-pressure chamber, and a first low-pressure chamber. The first high-pressure chamber is connected to a corresponding plunger chamber, and the first low-pressure chamber is connected to the low-pressure main port. The first oil control chamber is connected to the first control oil circuit of each corresponding manifold. When the first high-pressure chamber and the first oil control chamber are simultaneously subjected to high-pressure oil, the first high-pressure chamber and the first low-pressure chamber are connected. The two-way cartridge valve includes a second high-pressure oil chamber, a second low-pressure oil chamber, and a second control oil chamber. The second low-pressure oil chamber is connected to a corresponding plunger chamber, and the second high-pressure oil chamber is connected to the high-pressure main port. The second control oil chamber is connected to the first control oil circuit of each corresponding manifold. When the second control oil chamber and the second high-pressure oil chamber are simultaneously subjected to high-pressure oil, the second high-pressure oil chamber and the second low-pressure oil chamber are closed. The second control oil circuit of the manifold is always connected to the second external control port and the second control distribution ring groove, and is connected to the second control oil port of the distribution shaft through the second ring groove hole. It is then connected to multiple housing control oil circuits through multiple manifold first control oil circuits to achieve the opening and closing control of the two-way cartridge valve and the hydraulically controlled check valve. The third control oil circuit of the manifold is always connected to the first external control port and the first control distribution ring groove, and is connected to the first control oil port of the distribution shaft through the first ring groove hole. It is then connected to multiple housing control oil circuits through multiple manifold first control oil circuits to achieve the opening and closing control of the two-way cartridge valve and the hydraulically controlled check valve. Its control opening and closing is opposite to the control action of the second control oil circuit of the manifold. The first external control port and the second external control port are suitable for switching between high-pressure oil source and low-pressure oil source to realize the forward or reverse rotation of the radial piston hydraulic device.

2. The externally controlled reversing dual-valve flow distribution radial piston hydraulic device according to claim 1, characterized in that, The eccentric spindle is provided with counterweights on both sides, and the counterweights are fixedly connected to the eccentric spindle by screws.

3. The externally controlled reversing dual-valve flow distribution radial piston hydraulic device according to claim 1, characterized in that, The hydraulic control check valve includes a first valve body and a second valve body disposed within the first valve body. The first valve body is provided with a first oil control chamber, and the second valve body is provided with a first movable chamber, a first high-pressure chamber, a first low-pressure chamber, and a first valve core. The first valve core is movably installed in the first movable chamber and can control the on / off connection between the first high-pressure chamber and the first low-pressure chamber. The first high-pressure chamber is connected to the corresponding plunger chamber, the first low-pressure chamber is connected to the low-pressure main port, and the first oil control chamber is connected to the first control oil circuit of each corresponding manifold.

4. The externally controlled reversing dual-valve flow distribution radial piston hydraulic device according to claim 1, characterized in that, The two-way cartridge valve includes a third valve body, a fourth valve body, a fifth valve body, and a second valve core. The third valve body has a second high-pressure oil chamber and a second low-pressure oil chamber inside. The fourth valve body has a second control oil chamber inside. The second valve core is movably installed in the fourth valve body and can control the on / off connection between the second high-pressure oil chamber and the second low-pressure oil chamber. The second low-pressure oil chamber is connected to the corresponding plunger chamber. The second high-pressure oil chamber is connected to the high-pressure main port. The second control oil chamber is connected to the first control oil circuit of each corresponding manifold.

5. A method for operating the externally controlled reversing dual-valve flow distribution radial piston hydraulic device according to any one of claims 1-4, characterized in that, When the radial piston hydraulic device is a hydraulic motor, the high-pressure main port is connected to the pressure oil source and serves as the oil inlet, and the low-pressure main port is connected to the low-pressure oil tank and serves as the oil outlet. At this time, the first external control main port is connected to the external high-pressure oil source, and the second external control main port is connected to the external low-pressure oil source. The external high-pressure oil enters the third control oil circuit of the manifold through the first external control main port. The third control oil circuit of the manifold is connected to the first distribution ring groove of the distribution shaft. The external high-pressure oil enters the first control oil port through the first ring groove hole on the first distribution ring groove of the distribution shaft. The first control oil port is connected to the first control oil circuit of the manifold. The external high-pressure oil enters the first control oil circuit and the second control oil circuit of the housing through the first control oil circuit of the manifold. The externally controlled low-pressure oil enters the second control oil circuit of the manifold through the second external control port. The second control oil circuit of the manifold is connected to the second distribution ring groove of the distribution shaft. The externally controlled low-pressure oil enters the second control oil port through the second ring groove hole on the second distribution ring groove of the distribution shaft, so that the second control oil port is connected to the first control oil circuit of the manifold. The externally controlled low-pressure oil enters the first control oil circuit and the second control oil circuit of the housing through the first control oil circuit of the manifold. The distribution shaft rotates together with the eccentric main shaft, causing the first control oil circuit and the second control oil circuit of the housing to switch between high pressure and low pressure; the first control oil circuit and the second control oil circuit of the housing are connected through the first control oil circuit of the manifold, so that the first control oil circuit and the second control oil circuit of the housing are simultaneously in a high pressure state or a low pressure state. When one of the plunger assemblies is in the top position, high-pressure oil flows into the high-pressure annular groove of the manifold through the high-pressure main port and then into the first high-pressure oil circuit of the housing. The first high-pressure oil circuit of the housing is connected to the high-pressure chamber of the two-way cartridge valve. When the first control oil circuit and the second control oil circuit of the housing are both in a low-pressure state, the high-pressure oil chamber and the low-pressure oil chamber of the two-way cartridge valve are connected. The high-pressure oil flows through the low-pressure oil chamber of the two-way cartridge valve and enters the plunger chamber, pushing the plunger assembly to move downward. When the plunger assembly is in the bottom position, the eccentric main shaft and the distribution shaft rotate 180 degrees counterclockwise. The corresponding first control oil circuit and second control oil circuit of the housing are in a high-pressure state. At this time, the high-pressure chamber and low-pressure chamber of the two-way cartridge valve are closed, and the first control oil circuit of the housing is connected to the oil control chamber of the hydraulic check valve. At this time, the high-pressure chamber and low-pressure chamber of the hydraulic check valve are connected. The oil in the plunger chamber flows out from the low-pressure main port. Under the action of the thrust of other plunger assemblies and the inertial force of the eccentric main shaft, the plunger assembly moves up and down. The reciprocating motion of several plunger assemblies makes the main shaft continuously output positive torque to convert hydraulic energy into mechanical energy. When the hydraulic motor needs to rotate in the reverse direction, connect the first external control port to the external low-pressure oil source and the second external control port to the external high-pressure oil source.

6. A method for operating the externally controlled reversing dual-valve flow distribution radial piston hydraulic device according to any one of claims 1-4, characterized in that, When the radial piston hydraulic device is a hydraulic pump, the high pressure port is connected to the high pressure tank or hydraulic load and is the oil outlet; the low pressure port is connected to the low pressure tank and is the oil inlet; the first external control port is connected to the external high pressure oil source; and the second external control port is connected to the external low pressure oil source. During oil discharge, the eccentric spindle rotates in the opposite direction, driving the plunger assembly to move up and down. The corresponding plunger chamber volume decreases and the pressure increases. Its pressure is higher than that of the high-pressure oil chamber or hydraulic load. The oil in the plunger chamber enters the low-pressure oil chamber of the two-way cartridge valve. Since the valve core of the two-way cartridge valve is stepped, it can be opened in both directions. The oil then flows through the high-pressure oil chamber of the two-way cartridge valve, through the second oil passage of the end cover, into the first high-pressure oil passage of the housing, the high-pressure ring groove of the manifold, into the high-pressure main port, and finally into the high-pressure oil tank or hydraulic load, thus realizing the oil discharge movement of the plunger assembly. When oil is drawn in, high pressure is established at the oil outlet. At this time, the valve core of the two-way cartridge valve is closed, and the eccentric main shaft continues to rotate in the opposite direction, driving at least one plunger assembly to move downward from the top position. The corresponding plunger cavity volume increases, creating a vacuum. The pressure in the plunger cavity is lower than that in the low-pressure oil tank. The oil in the low-pressure oil tank enters the second high-pressure oil circuit of the housing and finally enters the plunger cavity, pushing the plunger assembly downward until the plunger assembly moves to the bottom position. This process is repeated to convert mechanical energy into hydraulic energy. When the hydraulic pump needs to rotate in reverse, connect the first external control port to the external low-pressure oil source and the second external control port to the external high-pressure oil source.

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