Radial plunger hydraulic device and method for controlling flow distribution based on pilot reversing valve

Abstract

The invention discloses a radial plunger hydraulic device and method for controlling flow distribution based on pilot reversing valves. The radial plunger hydraulic device comprises a shell, plunger assemblies arranged around the shell, an eccentric main shaft rotationally arranged on the shell, a high-pressure total port, a low-pressure total port and the pilot two-position three-way reversing valves, wherein the high-pressure total port and the low-pressure total port are formed in one side of the shell, and the pilot two-position three-way reversing valves correspond to the plunger assemblies one to one. A plunger cavity, an eccentric main shaft cavity, a shell high-pressure oil way, a shell low-pressure oil way and a shell working oil way are arranged in the shell; plunger assemblies are arranged in the plunger cavities, and the plunger assemblies are arranged in the corresponding plunger cavities in an up-down sliding mode; the eccentric main shaft is rotationally mounted in the eccentric main shaft cavity and is in transmission connection with all the plunger assemblies; the high-pressure oil paths in the shell are communicated with one another and are communicated with the high-pressure main port; the low-pressure oil way of the shell is communicated with each other in the shell and is communicated with the low-pressure main port, and the two-position three-way reversing valve is matched with the conduction of the high-pressure oil way and the low-pressure oil way in the shell to realize the bidirectional rotation of the radial plunger hydraulic device.

Description

Technical Field

[0001] The present invention relates to the field of hydraulic devices, and particularly to a radial piston hydraulic device based on pilot-operated directional valve control for flow distribution. Background Art

[0002] The radial piston hydraulic device is a common hydraulic transmission equipment, which is widely used in fields such as mechanical manufacturing, mineral development, bridge building and road construction, aerospace, etc. The traditional radial piston hydraulic device usually adopts shaft flow distribution or end face flow distribution methods to realize the conversion between hydraulic energy and mechanical energy. However, the existing flow distribution methods have some limitations. For example, the structural clearance is relatively large, and the wear of moving parts is obvious, which may lead to a decline in sealing performance, thus affecting the overall efficiency and service life of the device. In addition, the independent control oil circuit design adopted to improve the above problems, although improving the performance to a certain extent, will lead to the complication of the oil circuit inside the housing and increase the processing cost of the flow distribution device. Summary of the Invention

[0003] In view of this, in view of the deficiencies of the prior art in the background art, the main purpose of the present invention is to adopt external control pilot pressure to control flow distribution, provide a brand-new flow distribution method, and realize the bidirectional rotation of the radial piston hydraulic device by setting an external control pilot oil circuit.

[0004] To achieve the above object, the present invention provides the following technical solution: A radial piston hydraulic device based on pilot-operated directional valve control for flow distribution, comprising a housing, a plunger assembly arranged around the housing, an eccentric main shaft rotatably arranged on the housing, a high-pressure manifold and a low-pressure manifold arranged on one side of the housing, and a pilot two-way three-way directional valve corresponding to each plunger assembly; a plunger chamber, an eccentric main shaft chamber, a housing high-pressure oil circuit, a housing low-pressure oil circuit and a housing working oil circuit are arranged inside the housing; a plunger assembly is arranged inside the plunger chamber, and the plunger assembly is slidably arranged up and down in the corresponding plunger chamber; the eccentric main shaft is rotatably connected in the eccentric main shaft chamber and is drivingly connected to all the plunger assemblies; the high-pressure oil circuits inside the housing are mutually communicated and are connected to the high-pressure manifold; the housing low-pressure oil circuit is mutually communicated inside the housing and is connected to the low-pressure manifold, and the bidirectional rotation of the radial piston hydraulic device is realized by the cooperation of the pilot two-way three-way directional valve with the conduction of the high-pressure oil circuit and the low-pressure oil circuit inside the housing.

[0005] Preferably, the pilot two-position three-way directional control valve includes a first valve body and a second valve body disposed outside the first valve body; a first moving chamber and a second moving chamber are provided in the first valve body, and a first spool and a second spool are movably installed in the first and second moving chambers respectively; a high-pressure valve hole, a low-pressure valve hole and a working valve hole are formed in the first valve body, the first spool is configured to control the on-off between the high-pressure valve hole and the working valve hole, and the second spool is configured to control the on-off between the low-pressure valve hole and the working valve hole; a first control oil chamber is provided in the second valve body, and when the first control oil chamber is under high pressure, the high-pressure valve hole is communicated with the working valve hole, and the low-pressure valve hole is disconnected from the working valve hole, and when the first control oil chamber is under low pressure, the low-pressure valve hole is communicated with the working valve hole, and the high-pressure valve hole is disconnected from the working valve hole;

[0006] Preferably, it further includes a distribution disk inserted and connected with the eccentric main shaft, and a distribution compensation disk with a compensation spring built therein and connected with the distribution disk. The distribution disk and the distribution compensation disk are arranged in a distribution disk end cover connected with the housing; the distribution compensation disk is adapted to move along the central axis direction of the distribution disk under the action of the compensation spring to achieve automatic compensation.

[0007] Preferably, the housing further includes a plurality of pilot control oil circuits, a housing high-pressure oil circuit communicated with the high-pressure valve hole of the pilot two-position three-way directional control valve, a housing low-pressure oil circuit communicated with the low-pressure valve hole, and a housing working oil circuit communicated with the working valve hole.

[0008] Preferably, the distribution disk end cover is provided with a first external oil control port and a second external oil control port adapted to switch and connect to a high-pressure oil source; the distribution compensation disk is provided with a first pilot oil circuit communicated with the first external oil control port and a second pilot oil circuit communicated with the second external oil control port; one side of the distribution disk is provided with a first pilot distribution ring groove communicated with the first pilot oil circuit and a second pilot distribution ring groove communicated with the second pilot oil circuit; the other side of the distribution disk is provided with a first distribution C-shaped groove and a second distribution C-shaped groove; the first pilot distribution ring groove is communicated with the first distribution C-shaped groove; the second pilot distribution ring groove is communicated with the second distribution C-shaped groove.

[0009] Preferably, the plunger end cover is provided with a plunger end cover main oil circuit and a plunger end cover working oil circuit communicated with the plunger end cover main oil circuit; wherein, the plunger end cover working oil circuit is communicated with the housing working oil circuit; the plunger end cover main oil circuit is communicated with the corresponding plunger chamber;

[0010] Preferably, the high-pressure valve hole of the pilot two-position three-way reversing valve is connected to the corresponding high-pressure oil circuit of the housing, the low-pressure valve hole is connected to the corresponding low-pressure oil circuit of the housing, the working valve hole is connected to the corresponding working oil circuit of the housing, and the first control oil chamber is alternately connected to the first distribution C-shaped groove and the second distribution C-shaped groove through the pilot control oil circuit; when the radial piston hydraulic device is a hydraulic motor, the high-pressure main port is connected to the pressure oil source, and the low-pressure main port is connected to the low-pressure oil tank, and the pressure oil source is connected to the first external control oil port or the second external control oil port to control the forward or reverse rotation of the hydraulic motor, and at this time, the high-pressure main port and the first external control oil port or the second external control oil port are oil inlet channels, and the low-pressure main port is an oil outlet channel; when the radial piston hydraulic device is a hydraulic pump, the high-pressure main port is connected to the high-pressure oil tank or the hydraulic load, and is an oil outlet, and the low-pressure main port is connected to the low-pressure oil tank and is an oil inlet.

[0011] A working method of the radial piston hydraulic device as described above, characterized in that it comprises the following steps: when the piston hydraulic device is a hydraulic motor, the high-pressure main port and the first external control oil port are respectively connected to the pressure oil source, the low-pressure main port is connected to the low-pressure oil tank, and the high-pressure main port and the first external control oil port are oil inlet channels, and the low-pressure main port is an oil outlet channel;

[0012] When one of the plunger assemblies is in the upper top position, high-pressure oil is introduced into both the high-pressure main port and the first external control oil port. The high-pressure oil introduced into the high-pressure main port enters the high-pressure valve hole of the corresponding pilot two-position three-way reversing valve through the high-pressure oil circuit of the housing. The high-pressure oil introduced into the first external control oil port enters the corresponding first control oil chamber through the first pilot oil circuit, the first pilot distribution ring groove, and the first distribution C-shaped groove. At this time, the high-pressure valve hole of the corresponding pilot two-position three-way reversing valve is connected with the working valve hole. The high-pressure oil entering through the high-pressure main port flows through the corresponding high-pressure oil circuit of the housing, the working oil circuit of the housing, the working oil circuit of the plunger end cover, and the main oil circuit of the plunger end cover and enters the corresponding plunger cavity, pushing the plunger to move downward, increasing the volume of the plunger cavity, and driving the eccentric spindle to do positive circular motion until the plunger assembly reaches When the plunger assembly is in the lower bottom position, the eccentric main shaft and the distribution plate are rotated 180 degrees. At this time, the first control oil chamber of the corresponding pilot two-position three-way reversing valve is connected with the second distribution C-shaped groove of the distribution plate, so that the high-pressure valve hole of the corresponding two-position three-way reversing valve is disconnected from the working valve hole, and the corresponding low-pressure valve hole is connected with the working valve hole; under the thrust of other plunger assemblies and the inertia force of the eccentric main shaft, the plunger assembly moves upward, so that the volume of the plunger cavity is reduced, and the oil in the plunger cavity flows out from the low-pressure main port after passing through the corresponding plunger end cover main oil circuit, plunger end cover working oil circuit, housing working oil circuit, and housing low-pressure oil circuit, thereby realizing the periodic motion of a single plunger assembly; the reciprocating motion of several plunger assemblies causes the main shaft to continuously output positive torque to convert hydraulic energy into mechanical energy.

[0013] A working method of a radial piston hydraulic device as described above, characterized by comprising the following steps: When the piston hydraulic device is a hydraulic pump, the high-pressure main port is connected to a high-pressure oil tank or a hydraulic load and serves as an oil outlet, and the low-pressure main port is connected to a low-pressure oil tank and serves as an oil inlet; When one of the piston assemblies is in the upper top position, low-pressure oil is introduced from the low-pressure main port. At this time, the eccentric main shaft rotates in the reverse direction to drive a piston assembly to move downward from the upper top position, causing the volume of the corresponding piston chamber to increase and generating a vacuum. At this time, the pressure in the piston chamber is lower than that of the low-pressure oil tank, and the low-pressure oil flows through the low-pressure main port, the low-pressure valve hole of the pilot two-position three-way directional control valve and the working valve hole it communicates with, the housing working oil circuit, the piston end cover working oil circuit, and the piston end cover main oil circuit and then enters its corresponding piston chamber until the piston assembly moves to the lower bottom position. At this time, the eccentric main shaft drives the distribution plate to rotate in the reverse direction by 180 degrees; The eccentric main shaft continues to rotate in the reverse direction, and the piston assembly begins to move upward. The volume of the corresponding piston chamber decreases, and the pressure increases. Its pressure is higher than the pressure at the high-pressure oil tank or the hydraulic load. The oil in the piston chamber flows through the piston end cover main oil circuit, the piston end cover working oil circuit, the working valve hole of the pilot two-position three-way directional control valve and the high-pressure valve hole it communicates with, and the housing high-pressure oil circuit and then enters the high-pressure oil tank or the hydraulic load to realize the oil discharge movement of the piston assembly; Driven by the reverse rotation of the eccentric main shaft, several piston assemblies suck in low-pressure oil and discharge pressure oil to realize the conversion of mechanical energy into hydraulic energy.

[0014] The present invention has the following beneficial effects: The present invention provides a radial piston hydraulic device based on pilot-operated directional control valve for flow distribution. This device uses external control pilot pressure to control flow distribution, providing a brand-new flow distribution method. By setting up an external control pilot oil circuit, the bidirectional rotation of the radial piston hydraulic device is realized; A brand-new flow distribution valve is provided, simplifying the principle of realizing secondary flow distribution by pilot pressure control, effectively reducing the complexity of the housing oil circuit and the overall machining cost of the motor; In addition, through the built-in flow distribution compensation disc, automatic wear compensation of the pilot flow distribution pair is realized, improving the sealing performance of the oil circuit. In summary, this device can be used in a high-pressure environment and can achieve a relatively high volumetric efficiency. This radial piston hydraulic device can realize bidirectional rotation in the states of hydraulic motor and hydraulic pump, solving the problem of the limitations of valve flow distribution in the application of motors and pumps. Description of the Drawings

[0015] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as limiting the scope. For those of ordinary skill in the art, other related drawings can also be obtained based on these drawings without creative efforts.

[0016] Figure 1This is an exploded view schematic diagram of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0017] Figure 2 This is an axial sectional view schematic diagram of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0018] Figure 3 For Figure 2 it is a sectional view schematic diagram in the A-A direction.

[0019] Figure 4 This is a sectional view schematic diagram of the pilot-operated two-position three-way directional valve of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0020] Figure 5 This is an external view schematic diagram of the flow distribution disc of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0021] Figure 6 This is an external view schematic diagram of the piston end cover of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0022] Figure 7 This is a schematic diagram of one side (F2) of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0023] Figure 8 For Figure 7 it is a sectional view schematic diagram in the B-B direction.

[0024] Figure 9 For Figure 8 it is a sectional view schematic diagram in the C-C direction.

[0025] Figure 10 For Figure 8 it is a sectional view schematic diagram in the D-D direction.

[0026] Figure 11 This is a partial sectional view schematic diagram of one side (F1) of the radial piston hydraulic device based on pilot-operated directional valve control for flow distribution according to an embodiment of the present invention.

[0027] Figure 12 For Figure 11 it is a sectional view schematic diagram in the E-E direction.

[0028] In the figure: 1 - plunger end cover; 2 - housing; 3 - distribution disk; 4 - distribution compensation disk; 5 - compensation spring; 6 - distribution disk end cover; 7 - first external oil control port; 8 - second external oil control port; 9 - pilot two - position three - way directional valve; 10 - directional valve cavity; 11 - plunger cavity; 12 - plunger assembly; 13 - eccentric main shaft; 14 - first bearing; 15 - housing end cover; 16 - shaft end cover; 20 - plunger; 21 - connecting rod and slipper; 22 - eccentric main shaft cavity; 23 - second bearing; 24 - first pilot distribution ring groove; 25 - first pilot oil path; 26 - second pilot oil path; 27 - second pilot distribution ring groove; 28 - limit pin; 29 - third bearing; 30 - low - pressure main port; 31 - return ring; 32 - high - pressure main port; 40 - first return spring; 41 - first valve body; 42 - high - pressure valve hole; 43 - first spool; 44 - first movable cavity; 45 - second spool; 46 - second return spring; 47 - second movable cavity; 48 - second valve body; 49 - pilot transition cavity; 50 - first control oil cavity; 51 - detachable pilot hole; 52 - low - pressure transition cavity; 53 - low - pressure valve hole; 54 - working valve hole of the pilot two - position three - way directional valve; 55 - working transition cavity; 56 - high - pressure transition cavity; 58 - first distribution C - shaped groove; 59 - second distribution C - shaped groove; 60 - main oil path of the plunger end cover; 61 - working oil path of the plunger end cover; 62 - working oil path of the housing; 63 - high - pressure oil path of the housing; 64 - low - pressure oil path of the housing; 70 - pilot oil path of the housing. Detailed implementation manners

[0029] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are some, but not all, of the embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the protection scope of the present invention. Therefore, the following detailed description of the embodiments of the present invention provided in the drawings is not intended to limit the scope of the claimed invention, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

[0030] Embodiment

[0031] The following are only the preferred embodiments of the present invention, and the protection scope of the present invention is not limited to the following embodiments. All technical solutions falling within the idea of the present invention belong to the protection scope of the present invention.

[0032] In combination with Figures 1 to 12As shown in the figure, this embodiment provides a radial piston hydraulic device based on a pilot-operated directional valve for flow distribution, which includes a housing 2, a plurality of plunger assemblies 12, an eccentric main shaft 13 rotatably arranged on the housing 2, and a pilot-operated two-position three-way directional valve 9 corresponding to each plunger assembly 12; a plurality of plunger cavities 11, an eccentric main shaft cavity 22, a plurality of directional valve cavities 10 corresponding to the plunger assemblies 12, a plurality of high-pressure oil passages 63 in the housing, a plurality of low-pressure oil passages 64 in the housing, a plurality of pilot control oil passages 70, and a plurality of working oil passages 62 in the housing are provided in the housing 2; the plunger assemblies 12 are slidably arranged up and down in the corresponding plunger cavities 11; the eccentric main shaft 13 is rotatably connected in the eccentric main shaft cavity 22 and is drivingly connected to all the plunger assemblies 12; it further includes a flow distribution disc 3 inserted and connected to the eccentric main shaft 13, and a flow distribution compensation disc 4 with a compensation spring 5 built therein.

[0033] The flow distribution compensation disc 4 is provided with a first pilot oil passage 25 communicating with the first external oil control port 7 and a second pilot oil passage 26 communicating with the second external oil control port 8; wherein, the first pilot oil passage 25 is communicated with the first pilot flow distribution ring groove 24, and the second pilot oil passage 26 is communicated with the second pilot flow distribution ring groove 27.

[0034] Further, a limit pin 28 for realizing the circumferential positioning of the flow distribution compensation disc 4 but allowing its axial sliding is provided at one end of the flow distribution compensation disc 4 close to the flow distribution disc end cover 6, and a compensation spring 5 is clamped between the flow distribution compensation disc 4 and the flow distribution disc end cover 6.

[0035] One side of the flow distribution disc 3 is provided with a first pilot flow distribution ring groove 24 communicating with the first pilot oil passage 25 and a second pilot flow distribution ring groove 27 communicating with the second pilot oil passage 26; the other side of the flow distribution disc 3 is provided with a first flow distribution C-shaped groove 58 and a second flow distribution C-shaped groove 59; wherein, the first flow distribution C-shaped groove 58 and the second flow distribution C-shaped groove 59 are located on the same circumference and are symmetrically arranged; the first pilot flow distribution ring groove 24 is communicated with the first flow distribution C-shaped groove 58; the second pilot flow distribution ring groove 27 is communicated with the second flow distribution C-shaped groove 59.

[0036] The pilot-operated two-position three-way directional valve 9 is installed in the corresponding directional valve cavity 10 and is configured to control the on-off between the high-pressure oil passage 63 in the housing 2 and the working oil passage 62 in the housing, or the on-off between the low-pressure oil passage 64 in the housing and the working oil passage 62 in the housing;

[0037] Further, the pilot two-position three-way valve 9 includes a first valve body 41, on which a high-pressure valve hole 42, a working valve hole 54, and a low-pressure valve hole 53 are provided; wherein, the high-pressure valve hole 42 is communicated with the high-pressure oil path 63 of the housing through a high-pressure transition cavity 56, the working valve hole 54 is communicated with the working oil path 62 of the housing through a working transition cavity 55, and the low-pressure valve hole 53 is communicated with the low-pressure oil path 64 of the housing through a low-pressure transition cavity 52; a first moving cavity 44 and a second moving cavity 47 are provided in the first valve body 41, and a slidable first valve core 43 and a second valve core 45 are respectively installed therein; in the static state, the first valve core 43 and the second valve core 45 are kept in close contact under the combined action of a first return spring 40 and a second return spring 46;

[0038] It further includes a second valve body 48, a pilot transition cavity 49 is provided in the second valve body 48 and is communicated with the pilot oil path 70 of the housing, and is communicated with a first control oil cavity 50 through a detachable pilot hole 51; the structure of the detachable pilot hole 51 can be regarded as an internal hexagonal screw with a small hole opened inside, is threadedly connected with the second valve body 48, and different sizes of apertures can be selected according to the requirements of pilot flow distribution performance; the first control oil cavity 50 is alternately communicated with the first flow distribution C-shaped groove 58 and the second flow distribution C-shaped groove 59 through the housing pilot oil path 70, and when the first control oil cavity 50 is under high pressure, the second valve core 45 overcomes the resistance under the action of hydraulic pressure and pushes the first valve core 43 to move to the first limit position, at this time the high-pressure valve hole 42 is communicated with the working valve hole 54, and the low-pressure valve hole 53 is disconnected from the working valve hole 54; when the first control oil cavity 50 is under low pressure, the first valve core 43 overcomes the resistance under the action of hydraulic pressure and pushes the second valve core 45 to move to the second limit position, at this time the low-pressure valve hole 53 is communicated with the working valve hole 54, and the high-pressure valve hole 42 is disconnected from the working valve hole 54.

[0039] As Figure 1 and Figure 2 shown, in this embodiment, the housing 2 is coaxially connected to the shaft end cover 16, the housing end cover 15, the eccentric main shaft 13, the flow distribution disk 3, the flow distribution compensation disk 4, and the flow distribution disk end cover 6 in sequence. A plurality of plunger cavities 11, an eccentric main shaft cavity 22, a reversing valve cavity 10 corresponding to the plunger assembly 12 one by one, a plurality of high-pressure oil paths, low-pressure oil paths, working oil paths, and control oil paths are provided in the housing 2, for example, a housing high-pressure oil path 63, a housing low-pressure oil path 64, a housing working oil path 62, and a pilot control oil path 70 are provided; the plunger 20 and the plunger end cover 1 enclose the plunger cavity 11. As Figure 2As shown, in this embodiment, there are 5 plunger end caps 1 and 5 plunger chambers 11. Each plunger chamber 11 is correspondingly provided with a pilot two-position three-way directional control valve 9, and the pilot two-position three-way directional control valve 9 is installed on the directional control valve chamber 10. The number of plunger chambers 11 is not limited to this and can also be 8, 10, etc. The eccentric main shaft chamber 22 is used for installing the eccentric main shaft 13. The first bearing 14 and the third bearing 29 are respectively installed on the housing end cap 15 and the housing 2 to support the eccentric main shaft 13.

[0040] The plunger assembly 12 can slide up and down in the plunger chamber 11. In this embodiment, the plunger assembly 12 includes a plunger 20 and a connecting rod and slipper 21. The plunger 20 is slidably connected up and down in the plunger chamber 11. The top end of the connecting rod and slipper 21 is sleeved in the plunger 20, and the bottom end is fixed to the second bearing 23 outside the eccentric main shaft 13 through a return spring ring 31. The up and down sliding of the plunger 20 in the plunger chamber 11 can drive the eccentric main shaft 13 to rotate through the connecting rod and slipper 21 and the return spring ring 31, which is the working state of the hydraulic motor; or the rotation of the eccentric main shaft 13 can drive the plunger 20 to slide up and down in the plunger chamber 11 through the connecting rod and slipper 21 and the return spring ring 31, which is the working state of the hydraulic pump.

[0041] The eccentric main shaft 13 is installed in the eccentric main shaft chamber 22. There is a counterweight and the first bearing 14 on the left side, and a second bearing 23 on the right side. The first bearing 14 and the third bearing 29 are respectively installed on the housing end cap 15 and the housing 2 to stably support the eccentric main shaft 13.

[0042] As Figure 1 and Figure 4As shown, in this embodiment, there are five pilot two-position three-way directional control valves 9, which are evenly distributed on the housing 2 on the side of direction F2. The structure of the pilot two-position three-way directional control valve 9 includes a first valve body 41, a second valve body 48, a first spool 43, a second spool 45, a first return spring 40 and a second return spring 46. The first valve body 41 is provided with a first moving cavity 44 suitable for the axial sliding of the first spool 43 and a second moving cavity 47 suitable for the axial sliding of the second spool 45; in the stationary state, one end of the first spool 43 corresponding to the second spool 45 remains in close contact under the combined action of the first return spring 40 and the second return spring 46, and the other non-contact ends are respectively affected by hydraulic pressure, and the force-receiving area of the first spool 43 is smaller than that of the second spool 45; a high-pressure valve hole 42, a low-pressure valve hole 53 and a working valve hole 54 are opened on the first valve body 41, and a first control oil cavity 50 is provided in the second valve body, and the on-off between the high-pressure valve hole 42 and the working valve hole 54 or between the low-pressure valve hole 53 and the working valve hole 54 can be controlled by controlling the first spool 43 and the second spool 45 to move to the limit position. The high-pressure valve hole 42 is communicated with the housing high-pressure oil circuit 63 through a high-pressure transition cavity 56, the low-pressure valve hole 53 is communicated with the housing low-pressure oil circuit 64 through a low-pressure transition cavity 52, the working valve hole 54 is communicated with the housing working oil circuit 62 through a working transition cavity 55, and the first control oil cavity 50 is alternately communicated with the first distribution C-shaped groove 58 and the second distribution C-shaped groove 59 through a detachable pilot hole 51, a pilot transition cavity 49 and a housing pilot oil circuit 70 in sequence. Specifically, when high pressure is introduced into the first control oil cavity 50, the pilot hydraulic pressure received by the second spool 45 is greater than the hydraulic pressure and other resistances received by the first spool 43, thereby pushing the first spool 43 to move to the first limit position. At this time, the passage between the high-pressure valve hole 42 and the working valve hole 54 is opened, and the passage between the low-pressure valve hole 53 and the working valve hole 54 is closed, that is, the housing high-pressure oil circuit 63 is communicated with the housing working oil circuit 62, and the housing low-pressure oil circuit 64 is disconnected from the housing working oil circuit 62; when low pressure is introduced into the first control oil cavity 50, the hydraulic pressure received by the first spool 43 overcomes the pilot hydraulic pressure and other resistances received by the second spool 45, and then pushes the second spool 45 to move to the second limit position. At this time, the passage between the high-pressure valve hole 42 and the working valve hole 54 is closed, and the passage between the low-pressure valve hole 53 and the working valve hole 54 is opened, that is, the housing high-pressure oil circuit 63 is disconnected from the housing working oil circuit 62, and the housing low-pressure oil circuit 64 is communicated with the housing working oil circuit 62.

[0043] Combined Figures 1 to 5As shown in the figure, a limit pin 28 for realizing circumferential positioning of the flow distribution compensation disc 4 but allowing its axial sliding is provided at one end of the flow distribution compensation disc 4 close to the flow distribution disc end cover 6 to prevent the rotation of the flow distribution compensation disc 4. At the same time, a compensation spring 5 sandwiched between the flow distribution compensation disc 4 and the flow distribution disc end cover 6 is provided, so that the flow distribution compensation disc 4 can play a role in axial compensation and press the flow distribution disc 3 against the housing 2. The flow distribution compensation disc 4 is provided with a first pilot oil passage 25 and a second pilot oil passage 26. Among them, the first external oil control port 7 and the first pilot flow distribution ring groove 24 are respectively communicated with the first pilot oil passage 25, and the second external oil control port 8 and the second pilot flow distribution ring groove 27 are respectively communicated with the second pilot oil passage 26.

[0044] Combined with Figures 7 to 12 As shown in the figure, the left end of the flow distribution disc 3 is inserted and connected with the eccentric main shaft 13, and the right end of the flow distribution disc 3 is pressed by the flow distribution compensation disc 4, so that the left end of the flow distribution disc 3 is closely attached to the end face of the housing 2. The flow distribution disc 3 is provided with a first pilot flow distribution ring groove 24, a second pilot flow distribution ring groove 27, a first flow distribution C-shaped groove 58, and a second flow distribution C-shaped groove 59. Among them, the first pilot flow distribution ring groove 24 is communicated with the first pilot oil passage 25, and the second pilot flow distribution ring groove 27 is communicated with the second pilot oil passage 26. The first flow distribution C-shaped groove 58 and the second flow distribution C-shaped groove 59 are located on the same circumference and are symmetrically arranged. The first pilot flow distribution ring groove 24 is communicated with the first flow distribution C-shaped groove 58. The second pilot flow distribution ring groove 27 is communicated with the second flow distribution C-shaped groove 59.

[0045] Embodiment 2

[0046] Combined with Figures 6 to 12 As shown in the figure, in this embodiment, a working method of a radial piston hydraulic device based on pilot-operated directional valve control for flow distribution is provided. Specifically, when the radial piston hydraulic device is a hydraulic motor, the high-pressure main port 32 and the first external oil control port 7 are respectively connected to a pressure oil source, the low-pressure main port 30 is connected to a low-pressure oil tank, and the high-pressure main port 32 and the first external oil control port 7 are oil inlet channels, and the low-pressure main port 30 is an oil outlet channel. Taking one plunger assembly 12 as an example:

[0047] When the plunger assembly 12 is in the upper top position, high-pressure oil is introduced into both the high-pressure main port 32 and the first external oil control port 7. The high-pressure oil introduced into the high-pressure main port 32 enters the high-pressure valve hole 42 of its corresponding pilot two-way three-position directional control valve 9 after passing through the high-pressure oil path 63 in the housing, the high-pressure transition cavity 56. The high-pressure oil introduced into the first external oil control port 7 enters the first control oil cavity 50 of its corresponding pilot two-way three-position directional control valve 9 after passing through the first pilot oil path 25, the first pilot flow distribution ring groove 24, the first flow distribution C-shaped groove 58, the housing pilot oil path 70, the pilot transition cavity 49, and the detachable pilot hole 51. At this time, the pilot hydraulic pressure received by the second spool 45 is greater than the hydraulic pressure and other resistances received by the first spool 43, and it pushes the first spool 43 to move to the first limit position. At this time, the high-pressure valve hole 42 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the working valve hole 54, and the low-pressure valve hole 53 is disconnected from the working valve hole 54. The high-pressure oil flowing through the high-pressure main port enters the corresponding plunger cavity 11 after passing through the high-pressure oil path 63 in the housing, the high-pressure transition cavity 56, the high-pressure valve hole 42, the working valve hole 54, the working transition cavity 55, the housing working oil path 62, the plunger end cover working oil path 61, and the plunger end cover main oil path 60, pushing the plunger 20 to move downward, increasing the volume of the plunger cavity 11, and driving the eccentric main shaft 13 to make a positive circular motion until the plunger assembly 12 reaches the lower bottom position. When the plunger assembly 12 is in the lower bottom position, the eccentric main shaft 13 and the flow distribution disc 3 both rotate 180 degrees. At this time, the first control oil cavity 50 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the second flow distribution C-shaped groove 59 of the flow distribution disc 3. The low-pressure oil introduced into the second external oil control port 8 enters the first control oil cavity 50 of its corresponding pilot two-way three-position directional control valve 9 after passing through the second pilot oil path 26, the second pilot flow distribution ring groove 27, the second flow distribution C-shaped groove 59, the housing pilot oil path 70, the pilot transition cavity 49, and the detachable pilot hole 51. At this time, the hydraulic pressure received by the first spool 43 is greater than the pilot hydraulic pressure and other resistances received by the second spool 45, and it pushes the second spool 45 to move to the second limit position. At this time, the low-pressure valve hole 53 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the working valve hole 54, and the high-pressure valve hole 42 is disconnected from the working valve hole 54. Under the action of the thrust of other plunger assemblies 12 and the inertial force of the eccentric main shaft 13, this plunger assembly 12 moves upward, reducing the volume of the plunger cavity 11. The oil in the plunger cavity 11 flows out from the low-pressure main port 30 after passing through the corresponding plunger end cover main oil path 60, the plunger end cover working oil path 61, the housing working oil path 62, the working valve hole 54, the low-pressure valve hole 53, the low-pressure transition cavity 52, and the housing low-pressure oil path 64, thus realizing the periodic motion of a single plunger assembly 12; the reciprocating motion of several plunger assemblies 12 enables the main shaft to continuously output positive torque to convert hydraulic energy into mechanical energy;

[0048] When the hydraulic motor needs to rotate in the reverse direction, high-pressure oil is introduced into both the high-pressure main port 32 and the second external oil control port 8. The high-pressure oil introduced into the high-pressure main port 32 enters the high-pressure valve hole 42 of its corresponding pilot two-way three-position directional control valve 9 through the high-pressure oil circuit 63 in the housing. The high-pressure oil introduced into the second external oil control port 8 enters the first control oil chamber 50 of its corresponding pilot two-way three-position directional control valve 9 after passing through the second pilot oil circuit 26, the second pilot distribution ring groove 27, and the second distribution C-shaped groove 59. At this time, the high-pressure valve hole 42 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the working valve hole 54, and the low-pressure valve hole 53 is disconnected from the working valve hole 54. The high-pressure oil flowing through the high-pressure main port passes through its corresponding high-pressure oil circuit 63 in the housing, the high-pressure transition chamber 56, the high-pressure valve hole 42, the working valve hole 54, the working transition chamber 55, the housing working oil circuit 62, the plunger end cover working oil circuit 61, and the plunger end cover main oil circuit 60 and then enters the corresponding plunger chamber 11, pushing the plunger 20 to move downward, increasing the volume of the plunger chamber 11, and driving the eccentric main shaft 13 to perform a reverse circular motion until the plunger assembly 12 reaches the lower bottom position. When the plunger assembly 12 is at the lower bottom position, the eccentric main shaft 13 and the distribution disk 3 both rotate 180 degrees in the reverse direction. At this time, the first control oil chamber 50 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the second distribution C-shaped groove 59 of the distribution disk 3. The low-pressure oil introduced into the second external oil control port 8 enters the first control oil chamber 50 of its corresponding pilot two-way three-position directional control valve 9 after passing through the second pilot oil circuit 26, the second pilot distribution ring groove 27, the second distribution C-shaped groove 59, the housing pilot oil circuit 70, the pilot transition chamber 49, and the detachable pilot hole 51. At this time, the low-pressure valve hole 53 of its corresponding pilot two-way three-position directional control valve 9 is communicated with the working valve hole 54, and the high-pressure valve hole 42 is disconnected from the working valve hole 54. Under the action of the thrust of other plunger assemblies 12 and the inertial force of the eccentric main shaft 13, this plunger assembly 12 moves upward, reducing the volume of the plunger chamber 11. The oil in the plunger chamber 11 flows out from the low-pressure main port 30 after passing through its corresponding plunger end cover main oil circuit 60, plunger end cover working oil circuit 61, housing working oil circuit 62, working valve hole 54, low-pressure valve hole 53, low-pressure transition chamber 52, and housing low-pressure oil circuit 64, thus realizing the periodic motion of a single plunger assembly 12. The reciprocating motion of several plunger assemblies 12 enables the main shaft to continuously output reverse torque to convert hydraulic energy into mechanical energy;

[0049] That is, in the state of the hydraulic motor, the oil flow direction is as follows: pressure oil source → high-pressure main port 32 → housing high-pressure oil circuit 63 → high-pressure transition chamber 56 → high-pressure valve hole 42 of the pilot two-way three-position directional control valve 9 → working valve hole 54 of the pilot two-way three-position directional control valve 9 → working transition chamber 55 → housing working oil circuit 62 → plunger end cover working oil circuit 61 → plunger end cover main oil circuit 60 → plunger chamber 11 → plunger end cover main oil circuit 60 → plunger end cover working oil circuit 61 → housing working oil circuit 62 → working transition chamber 55 → low-pressure valve hole 53 of the pilot two-way three-position directional control valve 9 → low-pressure transition chamber 52 → housing low-pressure oil circuit 64 → low-pressure main port 30.

[0050] Embodiment 3

[0051] Continue to combine Figures 6 to 12 As shown, another embodiment of the present invention further provides a working method of another radial piston hydraulic device based on pilot directional control valve for flow distribution. Specifically, when the radial piston hydraulic device is a hydraulic pump, the high-pressure main port 32 is connected to a high-pressure oil tank or a hydraulic load and is an oil outlet, and the low-pressure main port 30 is connected to a low-pressure oil tank and is an oil inlet. Taking one of the plunger assemblies 12 as an example:

[0052] Viewed from the F2 side, when the eccentric main shaft 13 rotates clockwise under the action of torque, the first external oil control port 7 is supplied with high-pressure oil, and the second external oil control port 8 is supplied with low-pressure oil. When the plunger assembly 12 is in the upper top position, at this time, the rotation of the eccentric main shaft 13 drives the plunger assembly 12 to move downward from the upper top position, increasing the volume of the corresponding plunger chamber 11 and generating a vacuum. At this time, the pressure in the plunger chamber 11 is lower than that of the low-pressure oil tank, and the first control oil chamber 50 of the pilot two-way three-way valve 9 is supplied with low-pressure oil, causing the low-pressure valve hole 53 to communicate with the working valve hole 54 and disconnecting the high-pressure valve hole 42 from the working valve hole 54. Under the action of the pressure difference, the low-pressure oil passes through the low-pressure main port 30, the housing low-pressure oil path 64, the low-pressure transition chamber 52, the low-pressure valve hole 53, the working valve hole 54, the working transition chamber 55, the housing working oil path 62, the plunger end cover working oil path 61, and the plunger end cover main oil path 60 and then enters its corresponding plunger chamber 11, realizing the oil suction movement of the plunger assembly until the plunger assembly 12 moves to the lower bottom position. At this time, the eccentric main shaft 13 drives the distribution disc 3 to rotate 180 degrees clockwise; the eccentric main shaft 13 continues to rotate, and the plunger assembly 12 starts to move upward, the volume of the corresponding plunger chamber 11 decreases, the pressure increases, and its pressure is higher than the pressure of the high-pressure oil tank or the hydraulic load. The first control oil chamber 50 of the pilot two-way three-way valve 9 is supplied with high-pressure oil, causing the high-pressure valve hole 42 to communicate with the working valve hole 54 and disconnecting the low-pressure valve hole 53 from the working valve hole 54. Under the action of the pressure difference, the high-pressure oil in the plunger chamber 11 passes through the plunger end cover main oil path 60, the plunger end cover working oil path 61, the housing working oil path 62, the working transition chamber 55, the working valve hole 54, the high-pressure valve hole 42, the high-pressure transition chamber 56, the housing high-pressure oil path 63, and the high-pressure main port 32 and then enters the high-pressure oil tank or the hydraulic load, realizing the oil discharge movement of the plunger assembly 12; driven by the clockwise rotation of the eccentric main shaft 13, several plunger assemblies 12 suck in low-pressure oil and discharge the pressure oil to realize the conversion of mechanical energy into hydraulic energy.

[0053] Viewed from the side of F2, when the eccentric main shaft 13 rotates counterclockwise under the action of torque, the first external oil control port 7 admits low-pressure oil, and the second external oil control port 8 admits high-pressure oil. When the plunger assembly 12 is in the upper top position, at this time, the rotation of the eccentric main shaft 13 drives the plunger assembly 12 to move downward from the upper top position, causing the volume of the corresponding plunger chamber 11 to increase and generating a vacuum. At this time, the pressure in the plunger chamber 11 is lower than that of the low-pressure oil tank, and the first control oil chamber 50 of the pilot two-way three-way valve 9 admits low-pressure oil, making the low-pressure valve hole 53 communicate with the working valve hole 54 and disconnecting the high-pressure valve hole 42 from the working valve hole 54. Under the action of the pressure difference, the low-pressure oil passes through the low-pressure main port 30, the housing low-pressure oil passage 64, the low-pressure transition chamber 52, the low-pressure valve hole 53, the working valve hole 54, the working transition chamber 55, the housing working oil passage 62, the plunger end cover working oil passage 61, and the plunger end cover main oil passage 60 and then enters its corresponding plunger chamber 11 to realize the oil suction movement of the plunger assembly until the plunger assembly 12 moves to the lower bottom position. At this time, the eccentric main shaft 13 drives the distribution disk 3 to rotate counterclockwise by 180 degrees; the eccentric main shaft 13 continues to rotate, and the plunger assembly 12 starts to move upward, the volume of the corresponding plunger chamber 11 decreases, the pressure increases, and its pressure is higher than the pressure of the high-pressure oil tank or the hydraulic load. The first control oil chamber 50 of the pilot two-way three-way valve 9 admits high-pressure oil, making the high-pressure valve hole 42 communicate with the working valve hole 54 and disconnecting the low-pressure valve hole 53 from the working valve hole 54. Under the action of the pressure difference, the high-pressure oil in the plunger chamber 11 passes through the plunger end cover main oil passage 60, the plunger end cover working oil passage 61, the housing working oil passage 62, the working transition chamber 55, the working valve hole 54, the high-pressure valve hole 42, the high-pressure transition chamber 56, the housing high-pressure oil passage 63, and the high-pressure main port 32 and then enters the high-pressure oil tank or the hydraulic load to realize the oil discharge movement of the plunger assembly 12; driven by the counterclockwise rotation of the eccentric main shaft 13, several plunger assemblies 12 suck in low-pressure oil and discharge pressure oil to realize the conversion of mechanical energy into hydraulic energy.

[0054] That is to say, in the state of the hydraulic pump, the flow direction of the oil is: low-pressure oil tank → low-pressure main port 30 → housing low-pressure oil passage 64 → low-pressure transition chamber 52 → low-pressure valve hole 53 → working valve hole 54 → working transition chamber 55 → housing working oil passage 62 → plunger end cover working oil passage 61 → plunger end cover main oil passage 60 → plunger chamber 11 → plunger end cover main oil passage 60 → plunger end cover working oil passage 61 → housing working oil passage 62 → working transition chamber 55 → working valve hole 54 → high-pressure valve hole 42 → high-pressure transition chamber 56 → housing high-pressure oil passage 63 → high-pressure main port 32 → high-pressure oil tank or hydraulic load.

[0055] Through the solution of the embodiment of the present invention, a new pilot two-position three-way valve control flow distribution solution is used, which simplifies the control oil circuit of the flow distribution device, reduces the complexity of the housing oil circuit and the overall machining cost of the motor. At the same time, the radial piston hydraulic device can realize the function of bidirectional rotation of the hydraulic pump and the hydraulic motor, and solves the problem of the limitation of valve flow distribution in the application of the motor and the pump. In addition, through the built-in flow distribution compensation disc, automatic wear compensation of the pilot flow distribution pair is realized, and the sealing performance of the oil circuit is improved. The above embodiments are only for illustrating the technical concept and characteristics of the present invention, and the purpose is to enable those who are familiar with this technology to understand the content of the present invention and implement it accordingly, and cannot be used to limit the protection scope of the present invention. Any equivalent changes or modifications made according to the spirit and essence of the present invention should be covered within the protection scope of the present invention.

Claims

1. A radial piston hydraulic device based on a pilot reversing valve to control the flow distribution, characterized in that: It includes a housing, a plunger assembly arranged around the housing, an eccentric main shaft rotatably arranged on the housing, a high-pressure main port and a low-pressure main port arranged on one side of the housing, and a pilot two-position three-way reversing valve corresponding to the plunger assembly one by one; The housing is provided with a plunger cavity, an eccentric main shaft cavity, a housing high-pressure oil circuit, a housing low-pressure oil circuit and a housing working oil circuit; the plunger cavity is provided with a plunger assembly, and the plunger assembly can be slidably arranged in the corresponding plunger cavity; the eccentric main shaft is rotatably mounted in the eccentric main shaft cavity and transmission-connected to all the plunger assemblies; the high-pressure oil circuits in the housing are interconnected and connected to the high-pressure main port; the low-pressure oil circuits in the housing are interconnected in the housing and connected to the low-pressure main port, and the two-way rotation of the radial plunger hydraulic device is realized by guiding a two-position three-way reversing valve to cooperate with the conduction of the high-pressure oil circuit and the low-pressure oil circuit in the housing.

2. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 1, characterized in that: The pilot two-position three-way reversing valve includes a first valve body and a second valve body arranged outside the first valve body; a first active chamber and a second active chamber are arranged inside the first valve body, and a first valve core and a second valve core are movably installed in the first and second active chambers respectively; a high-pressure valve hole, a low-pressure valve hole and a working valve hole are opened on the first valve body, the first valve core is configured to control the connection and disconnection between the high-pressure valve hole and the working valve hole, and the second valve core is configured to control the connection and disconnection between the low-pressure valve hole and the working valve hole; a first control oil chamber is arranged inside the second valve body, and when the first control oil chamber is subjected to high pressure, the high-pressure valve hole is connected to the working valve hole, and the low-pressure valve hole is disconnected from the working valve hole, and when the first control oil chamber is subjected to low pressure, the low-pressure valve hole is connected to the working valve hole, and the high-pressure valve hole is disconnected from the working valve hole.

3. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 2, characterized in that: It also includes a distribution plate that is plugged into the eccentric main shaft, and a distribution compensation plate that has a built-in compensation spring and is connected to the distribution plate. The distribution plate and the distribution compensation plate are arranged in an end cover of the distribution plate connected to the shell; the distribution compensation plate is suitable for moving along the central axis direction of the distribution plate under the action of the compensation spring to achieve automatic compensation.

4. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 3, characterized in that: The housing also includes a plurality of pilot control oil circuits and a housing high-pressure oil circuit communicating with the high-pressure valve hole of the pilot two-position three-way reversing valve, a housing low-pressure oil circuit communicating with the low-pressure valve hole, and a housing working oil circuit communicating with the working valve hole.

5. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 4, characterized in that: The distribution disc end cover is provided with a first external control oil port and a second external control oil port suitable for switching and connecting to a high-pressure oil source; the distribution compensation disc is provided with a first pilot oil circuit communicating with the first external control oil port, and a second pilot oil circuit communicating with the second external control oil port; one side of the distribution disc is provided with a first pilot distribution ring groove communicating with the first pilot oil circuit, and a second pilot distribution ring groove communicating with the second pilot oil circuit; the other side of the distribution disc is provided with a first distribution C-shaped groove and a second distribution C-shaped groove; the first pilot distribution ring groove is connected to the first distribution C-shaped groove; the second pilot distribution ring groove is connected to the second distribution C-shaped groove.

6. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 5, characterized in that: The plunger end cover is provided with a plunger end cover main oil circuit and a plunger end cover working oil circuit connected to the plunger end cover main oil circuit; wherein, the plunger end cover working oil circuit is connected to the housing working oil circuit; the plunger end cover main oil circuit is connected to the corresponding plunger cavity.

7. The radial piston hydraulic device based on pilot reversing valve control flow distribution according to claim 6, characterized in that: The high-pressure valve hole of the pilot two-position three-way reversing valve is connected to the high-pressure oil circuit of the housing corresponding to it, the low-pressure valve hole is connected to the low-pressure oil circuit of the housing corresponding to it, the working valve hole is connected to the working oil circuit of the housing corresponding to it, and the first control oil chamber is alternately connected to the first distribution C-shaped groove and the second distribution C-shaped groove through the pilot control oil circuit; when the radial piston hydraulic device is a hydraulic motor, the high-pressure main port is connected to the pressure oil source, and the low-pressure main port is connected to the low-pressure oil tank, and the pressure oil source is connected to the first external control oil port or the second external control oil port to control the forward or reverse rotation of the hydraulic motor, and at this time, the high-pressure main port and the first external control oil port or the second external control oil port are oil inlet channels, and the low-pressure main port is an oil outlet channel; when the radial piston hydraulic device is a hydraulic pump, the high-pressure main port is connected to the high-pressure oil tank or the hydraulic load, and is an oil outlet, and the low-pressure main port is connected to the low-pressure oil tank and is an oil inlet.

8. A method for operating a radial piston hydraulic device according to any one of claims 1 to 7, characterized in that: The method comprises the following steps: when the plunger hydraulic device is a hydraulic motor, the high-pressure main port and the first external control oil port are respectively connected to the pressure oil source, the low-pressure main port is connected to the low-pressure oil tank, and the high-pressure main port and the first external control oil port are oil inlet channels, and the low-pressure main port is an oil outlet channel; When one of the plunger assemblies is in the upper top position, high-pressure oil is introduced into both the high-pressure main port and the first external control oil port. The high-pressure oil introduced into the high-pressure main port enters the high-pressure valve hole of the corresponding pilot two-position three-way reversing valve through the high-pressure oil circuit of the housing. The high-pressure oil introduced into the first external control oil port enters the corresponding first control oil chamber through the first pilot oil circuit, the first pilot distribution ring groove, and the first distribution C-shaped groove. At this time, the high-pressure valve hole of the corresponding pilot two-position three-way reversing valve is connected with the working valve hole. The high-pressure oil entering through the high-pressure main port flows through the corresponding high-pressure oil circuit of the housing, the working oil circuit of the housing, the working oil circuit of the plunger end cover, and the main oil circuit of the plunger end cover and enters the corresponding plunger cavity, pushing the plunger to move downward, increasing the volume of the plunger cavity, and driving the eccentric spindle to do positive circular motion until the plunger assembly reaches When the plunger assembly is in the lower bottom position, the eccentric main shaft and the distribution plate are rotated 180 degrees. At this time, the first control oil chamber of the corresponding pilot two-position three-way reversing valve is connected with the second distribution C-shaped groove of the distribution plate, so that the high-pressure valve hole of the corresponding two-position three-way reversing valve is disconnected from the working valve hole, and the corresponding low-pressure valve hole is connected with the working valve hole; under the thrust of other plunger assemblies and the inertia force of the eccentric main shaft, the plunger assembly moves upward, so that the volume of the plunger cavity is reduced, and the oil in the plunger cavity flows out from the low-pressure main port after passing through the corresponding plunger end cover main oil circuit, plunger end cover working oil circuit, housing working oil circuit, and housing low-pressure oil circuit, thereby realizing the periodic motion of a single plunger assembly; the reciprocating motion of several plunger assemblies causes the main shaft to continuously output positive torque to convert hydraulic energy into mechanical energy.

9. A method for operating a radial piston hydraulic device according to any one of claims 1 to 7, characterized in that: The method comprises the following steps: when the plunger hydraulic device is a hydraulic pump, the high-pressure main port is connected to the high-pressure oil tank or the hydraulic load and is the oil outlet, and the low-pressure main port is connected to the low-pressure oil tank and is the oil inlet; when one of the plunger assemblies is in the upper top position, low-pressure oil is introduced from the low-pressure main port, at which time the eccentric main shaft rotates in the opposite direction to drive a plunger assembly to move downward from the upper top position, so that the volume of the corresponding plunger cavity increases and a vacuum is generated. At this time, the pressure in the plunger cavity is lower than that in the low-pressure oil tank, and the low-pressure oil enters the corresponding plunger cavity through the low-pressure main port, the low-pressure valve hole of the pilot two-position three-way reversing valve and the working valve hole connected thereto, the working oil circuit of the housing, the working oil circuit of the plunger end cover, and the main oil circuit of the plunger end cover until the plunger assembly The component moves to the lower bottom position, at which time the eccentric main shaft drives the distribution plate to rotate 180 degrees in the opposite direction; the eccentric main shaft continues to rotate in the opposite direction, and the plunger assembly starts to move upward, the corresponding plunger cavity volume decreases, and the pressure increases, and its pressure is higher than the pressure at the high-pressure oil tank or the hydraulic load. The oil in the plunger cavity flows through the main oil circuit of the plunger end cover, the working oil circuit of the plunger end cover, the working valve hole of the pilot two-position three-way reversing valve and the high-pressure valve hole connected to it, and the high-pressure oil circuit of the housing, and then enters the high-pressure oil tank or the hydraulic load to realize the oil discharge movement of the plunger assembly; driven by the reverse rotation of the eccentric main shaft, each plunger cavity of the plurality of plunger assemblies sucks in low-pressure oil, and forms pressure oil to be discharged, so as to realize the conversion of mechanical energy into hydraulic energy.

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