Pilot valve controlled intelligent radial piston hydraulic device and working method thereof

Abstract

The application provides a pilot valve controlled intelligent radial plunger hydraulic device and a working method thereof, and relates to the technical field of hydraulic devices.The device adopts an external control pilot pressure to control flow distribution, optimizes the valve group structure of a pilot two-position three-way valve, improves the neutral and anti-oscillation performance, reduces the liquid dynamic force impact, and improves the stability and reliability of flow distribution.In addition, a rotating speed sensor and a pressure sensor are integrated, and a signal processing module is arranged to collect and process the rotating speed signal and the pressure signal, so that the real-time acquisition of the rotating speed parameter and the pressure parameter is realized, and the power is further calculated, the integration of the rotating speed detection, the pressure monitoring and the power calculation is realized, and thus the state monitoring of the hydraulic device is supported.Compared with the prior art, the application has the advantages of compact structure, good sealing performance, stable operation under high pressure working conditions, and effective improvement of the service life, operation efficiency and intelligent level of the device.

Description

Technical Field

[0001] This invention relates to the field of hydraulic device technology, and more specifically, to a pilot valve-controlled intelligent radial piston hydraulic device and its working method. Background Technology

[0002] Radial piston hydraulic devices are important actuators in hydraulic systems, widely used in engineering machinery, machining, and metallurgical industries, characterized by low speed, high torque, and strong load-bearing capacity. In existing high-pressure, large-displacement devices, to address the high-pressure leakage and wear problems of traditional shaft and end-face distribution methods, invention publication CN120140307A proposes a novel externally controlled pilot pressure distribution technology, which can effectively improve sealing performance under high-pressure conditions.

[0003] However, as modern industry increasingly demands higher frequencies, greater reliability, and greater intelligence from hydraulic systems, existing pilot valve control devices are showing some limitations. First, during high-pressure, high-frequency reversing flow distribution, existing pilot control valve assemblies, due to insufficient valve core alignment, are highly susceptible to hydraulic shock, resulting in oscillations and deformation, thus reducing flow distribution stability. Second, the piston assembly proposed in invention CN120007550A uses a rubber cavity assembly for sealing and return assist, but actual measurements show that rubber materials not only have limited high-temperature resistance and fatigue resistance, but their elastic characteristics also weaken the overall mechanical rigidity of the hydraulic system, affecting the immediacy of power transmission. Furthermore, existing radial piston hydraulic systems generally lack internally integrated operational status monitoring methods, especially for acquiring key parameters such as speed and pressure. They typically rely on external sensors and additional transmission structures, which not only increases system size and structural complexity but also introduces additional energy losses and reduces mechanical efficiency. Moreover, most existing technologies only achieve single-parameter detection, lacking the ability to collaboratively acquire and process speed and pressure signals, making it difficult to achieve real-time monitoring of operating power and failing to meet the needs of hydraulic systems for high-precision intelligent monitoring. Summary of the Invention

[0004] The purpose of this application is to provide a pilot valve-controlled intelligent radial piston hydraulic device, which aims to improve the problems mentioned above.

[0005] The present invention adopts the following solution:

[0006] A pilot-controlled intelligent radial piston hydraulic device includes a housing, a high-pressure main port and a low-pressure main port disposed on the outside of the housing, a plurality of piston assemblies disposed around the housing, an eccentric main shaft rotatably disposed on the housing, piston end caps disposed corresponding to each piston assembly, and a transmission structure disposed between the eccentric main shaft and the plurality of piston assemblies; the housing contains piston cavities corresponding to each piston assembly, a plurality of interconnected high-pressure oil passages connected to the high-pressure main port, a plurality of interconnected low-pressure oil passages connected to the low-pressure main port, and a plurality of housing working oil passages; it also includes a pilot control oil passage disposed within the housing, a pilot two-position three-way valve disposed corresponding to each piston cavity, a distribution plate inserted into and connected to the eccentric main shaft, a distribution compensation plate cooperating with the distribution plate, a distribution plate end cap disposed at one end of the eccentric main shaft and connected to the housing, and a power calculation component; The pilot-operated two-position three-way valve is connected to the corresponding high-pressure oil circuit of the housing, the low-pressure oil circuit of the housing, the working oil circuit of the housing, and the pilot control oil circuit, respectively. It is configured to alternately switch the connection state between the high-pressure oil circuit and the working oil circuit of the housing, and between the low-pressure oil circuit and the working oil circuit of the housing, based on the pilot control pressure provided by the pilot control oil circuit. It also works in conjunction with the pilot distribution section of the distribution plate to achieve forward and reverse drive of the radial piston hydraulic device. Specifically, the pilot-operated two-position three-way valve includes a working valve body. A control valve body is disposed outside the working valve body. The working valve body has a first movable chamber and a second movable chamber. The first movable chamber contains a high-pressure valve core and a high-pressure valve core guide band for guiding the axial movement of the high-pressure valve core. The second movable chamber contains a low-pressure valve core and a low-pressure valve core guide band for guiding the axial movement of the low-pressure valve core. The high-pressure valve core and the low-pressure valve core are connected by a ball joint connecting rod. The two ends of the ball joint connecting rod respectively form a spherical fit with the high-pressure valve core and the low-pressure valve core to transmit axial force while allowing relative deflection between the two. The working valve body has a high-pressure valve port, a low-pressure valve port, and a working valve port. The high-pressure valve port is connected to the corresponding high-pressure oil circuit of the housing through a high-pressure transition chamber. The low-pressure valve port is connected to the corresponding low-pressure oil circuit of the housing through a low-pressure transition chamber. The working valve port is connected to the corresponding working oil circuit of the housing through a working transition chamber. The control valve body has a pilot control oil chamber, which is connected to the corresponding pilot control oil circuit through a pilot transition chamber. When the pilot control oil chamber is under high pressure, the high-pressure valve port is connected to the working valve port, and the low-pressure valve port is disconnected from the working valve port; when the pilot control oil chamber is under low pressure, the high-pressure valve port is disconnected from the working valve port, and the low-pressure valve port is connected to the working valve port. The distribution plate and the distribution compensation plate are coaxially disposed inside the end cover of the distribution plate. The distribution compensation plate is equipped with a compensation spring and can apply an axial compensation force to the distribution plate along the central axis direction of the distribution plate under the elastic force of the compensation spring, so as to realize automatic compensation for wear of the distribution plate. The distribution plate end cover is provided with a first external oil control port and a second external oil control port suitable for switching the connection of a high-pressure oil source. The distribution compensation plate is provided with a first pilot oil passage connected to the first external oil control port and a second pilot oil passage connected to the second external oil control port. The distribution plate is provided with a pilot distribution section, which is used to alternately connect the first pilot oil circuit or the second pilot oil circuit with the corresponding pilot control oil circuit when the distribution plate rotates with the eccentric main shaft, so as to alternately provide pilot control pressure to each of the pilot two-position three-way valves; The power calculation component includes a speed sensor component, a pressure sensor component, and a signal processing module. The speed sensor component is used to detect the speed signal of the eccentric spindle or distributor plate, the pressure sensor component is used to detect the pressure signal at the high-pressure main port, and the signal processing module is used to calculate the power parameters of the radial piston hydraulic device based on the speed signal and the pressure signal.

[0007] Furthermore, the pilot distribution section includes a first pilot distribution annular groove and a second pilot distribution annular groove disposed on one side of the distribution plate, and a first distribution C-shaped groove and a second distribution C-shaped groove disposed on the other side of the distribution plate; the first pilot distribution annular groove is connected to the first pilot oil circuit, the second pilot distribution annular groove is connected to the second pilot oil circuit, the first pilot distribution annular groove is connected to the first distribution C-shaped groove, and the second pilot distribution annular groove is connected to the second distribution C-shaped groove; the first distribution C-shaped groove and the second distribution C-shaped groove are located on the same circumference and arranged opposite to each other, and the first distribution C-shaped groove and the second distribution C-shaped groove are alternately connected to the pilot control oil circuits at different positions during the rotation of the distribution plate, so that the distribution plate alternately provides pilot control pressure to each of the pilot two-position three-way valves when rotating with the eccentric main shaft.

[0008] Furthermore, the transmission structure is a polygonal assembly, which is mounted on the eccentric part of the eccentric spindle and can rotate relative to the eccentric part. Each side of the polygonal assembly cooperates with the corresponding plunger assembly to drive the plunger assembly to reciprocate when the eccentric spindle rotates, or to drive the eccentric spindle to rotate when the plunger assembly reciprocates. The polygonal assembly includes a polygonal wheel, a polygonal wheel sleeve, and a self-lubricating plate. The polygonal wheel is mounted on the eccentric part of the eccentric spindle through the polygonal wheel sleeve, and the self-lubricating plate is disposed between the polygonal wheel and the plunger assembly.

[0009] Furthermore, the plunger assembly includes a return spring, a guide belt, a guide sleeve, and a plunger. The plunger slides within the corresponding plunger cavity via the guide belt and the guide sleeve. The return spring is used to maintain the plunger assembly in contact with the transmission structure.

[0010] Furthermore, the speed sensor assembly is a Hall speed sensor assembly, which includes a speed sensor cover, a speed sensor sensing probe, a speed sensor body, and a speed sensor signal output terminal. The Hall speed sensor assembly is radially semi-embedded on the distribution compensation disk and fixed by the speed sensor cover. Two sensors are provided on the outer circumferential surface of the distribution plate. The two sensors rotate with the distribution plate and pass through the sensing area of ​​the speed sensor probe in sequence, so that the main body of the speed sensor outputs a pulse signal related to the speed. The two sensing elements are sensing screws respectively installed in two sensing screw holes. The two sensing screw holes are not coplanar and are 90° out of phase. The sensing distances between the two sensing screws and the speed sensor sensing probe are different, so that the signal processing module can determine the forward or reverse direction of the radial piston hydraulic device based on the phase sequence and / or amplitude difference of the output signals corresponding to the two sensing screws.

[0011] Furthermore, the pressure sensor assembly is connected to the high-pressure main port, and the signal processing module includes a central processing unit, an analog-to-digital converter module, and a timing and counting module. The analog-to-digital converter module is used to acquire the pressure signal output by the pressure sensor assembly and convert it into pressure parameters. The timing and counting module is used to acquire the pulse signal output by the speed sensor assembly and convert it into speed parameters. The central processing unit is used to calculate power parameters based on the pressure parameters, the speed parameters, and preset displacement parameters.

[0012] Furthermore, the calculation process of power parameters by the central processing unit includes pressure acquisition, speed acquisition, theoretical flow conversion, theoretical power calculation, and power correction calculation; specifically: The pressure acquisition process involves the pressure sensor assembly acquiring the pressure signal at the high-pressure main inlet in real time, and the analog-to-digital converter module converting it into pressure parameters. When the low-pressure main port is connected to the low-pressure oil tank, and the low-pressure side pressure is approximated as the return oil pressure, the central processing unit will convert the high-pressure main port pressure... With low pressure total port pressure The difference is used as the working pressure difference. ,Right now: ; In the formula, This represents the working pressure differential of the radial piston hydraulic device, expressed in MPa. This refers to the total pressure at the high-pressure port, expressed in MPa. This refers to the low-pressure main inlet pressure or the preset return oil pressure, in MPa. The rotational speed is acquired by the timing and counting module counting the number of pulses at the output of the rotational speed sensor within a set sampling time, thereby calculating the real-time rotational speed of the eccentric spindle. The calculation relationship is expressed as follows: ; In the formula, The rotational speed of the eccentric spindle is expressed in r / min. The frequency of the pulse signal output by the speed sensor, in Hz; The number of effective pulses generated per revolution of the distribution plate. When two sensing screws are set, the central processing unit determines the forward or reverse direction of the device by combining the phase relationship of the two pulse signals, and uses the absolute value of the rotation speed for power calculation. After obtaining the working pressure differential and rotational speed, the central processing unit calculates the theoretical effective flow rate based on the theoretical displacement of the radial piston hydraulic device. For a constant displacement radial piston hydraulic device, its theoretical effective flow rate can be expressed as: ; In the formula, The theoretical effective flow rate is expressed in L / min. This is the theoretical displacement of the radial piston hydraulic device, expressed in cm³ / r. The rotational speed of the eccentric spindle is expressed in r / min. This theoretical effective flow rate represents the effective flow rate involved in energy conversion, determined by the rotational speed and displacement. The central processing unit calculates the theoretical hydraulic power based on the working pressure difference and the theoretical effective flow rate. The calculation relationship is as follows: ; In the formula, The theoretical power is expressed in kW. The pressure difference is the working pressure, and the unit is MPa. The theoretical effective flow rate is expressed in L / min. Substituting the theoretical effective flow rate formula into the equation yields the theoretical power calculation formula based on pressure and rotational speed: ; Therefore, the central processing unit does not need to collect actual flow rate and output torque; it can complete the online calculation of theoretical power solely based on the pressure parameters collected by the pressure sensor, the speed parameters collected by the speed sensor, and the preset displacement parameters. Considering the factors that exist in the actual operation of the radial piston hydraulic unit, such as piston pair leakage, distribution pair leakage, sealing gap leakage, bearing friction, friction between the piston and guide, distribution pressure loss, and oil viscosity loss, there will be a deviation between the theoretical power and the actual output power. Therefore, the central processing unit introduces a power correction coefficient based on the theoretical power calculation results. To obtain the corrected actual power estimate: ; In the formula, The power estimate is the corrected value, in kW; This is a power correction factor, the power correction factor It is used to comprehensively correct the impact of internal leakage, mechanical friction, local pressure loss and other factors not modeled separately on the power calculation results; The power correction coefficient was obtained through experimental calibration. During the calibration process, the radial piston hydraulic device was installed on a test bench, and the high-pressure main port pressure, low-pressure side pressure, output speed, and output torque were collected under different working pressure differentials and different speed conditions. The actual output power was then calculated using the torque-speed method. ; In the formula, The actual output power measured in the experiment is expressed in kW. Output torque, in N·m; The output speed is given in r / min; the actual output power measured in the experiment is then compared with the theoretical power to obtain the power correction coefficient under the corresponding operating conditions. ; Under stable operating conditions, the above formula can be used to back-calculate the power correction coefficient corresponding to that operating condition. Although the speed term can be canceled algebraically, since leakage loss, friction loss, and pressure loss all change with speed and operating pressure difference, the power correction coefficient can still be treated as a parameter related to operating pressure difference and speed. The relationship between the power correction coefficient and the working pressure difference and speed can be established through multiple sets of test conditions, and the power correction function can be obtained by fitting. ; In actual operation, the central processing unit first calculates the current working pressure difference based on the data collected by the pressure sensor and speed sensor. and rotational speed Then, the power correction coefficient under the current operating condition is determined by the preset power correction function, and finally the power parameters are calculated and output according to the following formula: ; Therefore, the power calculation component can calculate and digitally display power without additional flow meters and torque sensors, relying only on the pressure sensor and speed sensor integrated on the device. Compared with the detection method of directly using external flow meters and torque sensors, this calculation method has a simple structure, high integration, and little impact on the original structure of the hydraulic device, and can meet the needs of real-time monitoring of the operating power of radial piston hydraulic devices under high pressure conditions.

[0013] The present invention also provides a method for operating the aforementioned pilot valve controlled intelligent radial piston hydraulic device. When the pilot valve controlled intelligent radial piston hydraulic device operates as a hydraulic motor, the high pressure main port is connected to a pressure oil source, the low pressure main port is connected to a low pressure oil tank, and the first external control oil port or the second external control oil port is connected to a control pressure oil source to control the forward or reverse rotation of the radial piston hydraulic device. When any plunger assembly is in the top position, high-pressure oil enters the high-pressure valve port of the corresponding pilot two-position three-way valve through the high-pressure main port and the high-pressure oil circuit of the housing. At the same time, control pressure oil enters the pilot control oil chamber of the corresponding pilot two-position three-way valve through the first external control oil port or the second external control oil port, the distribution compensation plate, the distribution plate and the pilot control oil circuit, so that the high-pressure valve port and the working valve port are connected, and the low-pressure valve port and the working valve port are disconnected. High-pressure oil enters the corresponding plunger chamber through the working valve port, the working oil circuit of the housing and the plunger end cover, pushing the plunger assembly to move and driving the eccentric spindle to rotate. When the plunger assembly moves to the bottom position, the distribution plate rotates with the eccentric spindle to a position that switches the corresponding pilot control oil chamber to a low-pressure state, so that the low-pressure valve port of the corresponding pilot two-position three-way valve is connected to the working valve port. The oil in the plunger chamber is discharged through the plunger end cover, the housing working oil passage, the working valve port, the low-pressure valve port, and the housing low-pressure oil passage to the low-pressure main port, thereby causing multiple plunger assemblies to reciprocate periodically and drive the eccentric spindle to continuously output torque.

[0014] The present invention also provides another method of operating the pilot valve controlled intelligent radial piston hydraulic device described above. When the pilot valve controlled intelligent radial piston hydraulic device is used as a hydraulic pump, the low pressure main port is connected to the low pressure oil tank and serves as the oil inlet, and the high pressure main port is connected to the high pressure oil tank or hydraulic load and serves as the oil outlet. An external torque drives the eccentric spindle to rotate, and the eccentric spindle drives each plunger assembly to reciprocate within the corresponding plunger cavity through the transmission structure. When any plunger assembly moves downward and increases the volume of the corresponding plunger cavity, the low-pressure oil enters the corresponding plunger cavity through the low-pressure main port, the housing low-pressure oil passage, the low-pressure valve port and working valve port of the corresponding pilot two-position three-way valve, the housing working oil passage, and the plunger end cap. When the plunger assembly moves upward and reduces the volume of the corresponding plunger cavity, the oil in the plunger cavity is discharged through the plunger end cap, the working oil passage of the housing, the working valve port and high pressure valve port of the corresponding pilot two-position three-way valve, and the high pressure oil passage of the housing, so as to realize the conversion of mechanical energy into hydraulic energy.

[0015] Beneficial effects: This pilot-controlled intelligent radial piston hydraulic device employs externally controlled pilot pressure to control flow distribution. By setting up an externally controlled pilot oil circuit, it achieves bidirectional rotation of the hydraulic pump motor and self-compensation after wear of the distribution plate, thus improving service life and oil circuit sealing. Furthermore, an optimized pilot-controlled two-position three-way valve structure is provided, effectively solving the problem of deformation due to hydraulic shock caused by insufficient valve core centering, which reduces flow distribution stability. Further, separating the guide component and the piston effectively improves the centering during piston movement and simplifies the complexity of the motor return mechanism. The self-lubricating plate and hydrostatic support structure reduce friction during piston movement, improving wear life. In addition, an integrated power unit component is incorporated into the device structure, effectively solving the problem of significant stirring loss in existing inductive gear speed sensors and enabling real-time, high-precision power monitoring.

[0016] In summary, this device can be used in high-pressure environments and achieves high volumetric efficiency. This radial piston hydraulic device can achieve bidirectional rotation in both hydraulic motor and hydraulic pump states, solving the current limitations of valve distribution in high-pressure applications to motors and pumps, such as large efficiency losses and lack of integrated intelligence. Attached Figure Description

[0017] Figure 1 This is an exploded structural diagram of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0018] Figure 2 This is an axial cross-sectional schematic diagram of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0019] Figure 3 for Figure 2 A cross-sectional view along the AA direction.

[0020] Figure 4 for Figure 2A cross-sectional view along the BB direction.

[0021] Figure 5 for Figure 2 A cross-sectional view along the CC direction.

[0022] Figure 6 This is a schematic diagram of the speed sensor assembly of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0023] Figure 7 This is a cross-sectional schematic diagram of a pilot two-position three-way valve of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0024] Figure 8 This is a schematic diagram of the distribution plate of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0025] Figure 9 This is a schematic diagram of the piston end cap of a pilot valve-controlled intelligent radial piston hydraulic device according to an embodiment of the present invention.

[0026] Figure label: 1. Plunger end cap; 2. Housing; 301. Sensing screw one; 302. Sensing screw two; 303. Sensing screw hole one; 304. Sensing screw hole two; 4. Distribution plate; 5. Distribution compensation plate; 6. Compensation spring; 7. First external oil control port; 8. Second external oil control port; 9. Distribution plate end cap; 101. Speed ​​sensor cover; 102. Speed ​​sensor sensing probe; 103. Speed ​​sensor body; 104. Speed ​​sensor signal output terminal; 105. Pressure sensor body; 106. Pressure sensor signal output terminal; 107. Signal processing module; 108. Display screen; 11. Pilot-operated two-position three-way valve; 12. Two-position three-way valve chamber; 13. Plunger chamber; 14. Guide sleeve; 15. Plunger assembly; 151. Return spring; 152. Guide belt; 153. Guide sleeve; 154. Plunger; 16. Five-star wheel sleeve; 17. Self-lubricating plate; 18. Five-star wheel; 19. Eccentric spindle; 20. First bearing; 21. Housing end cover; 22. Shaft end cover; 23. 24. Eccentric spindle cavity; 25. Main bearing; 26. Bushing; 27. First pilot distribution ring groove; 28. First pilot oil passage; 29. ​​Second pilot oil passage; 30. Second pilot distribution ring groove; 31. Limiting pin; 32. Second bearing; 33. Low-pressure main port; 34. High-pressure main port; 35. High-pressure valve hole; 36. Working valve body; 37. High-pressure valve core guide band; 38. High-pressure valve core; 39. First movable cavity; 40. Ball joint connecting rod; 41. Second movable cavity; 42. Low-pressure valve core guide. 42. Low-pressure valve core; 43. Pilot transition chamber; 44. Pilot control oil chamber; 45. Control valve body; 46. Low-pressure transition chamber; 47. Low-pressure valve port; 48. Working valve port; 49. Working transition chamber; 50. High-pressure transition chamber; 51. First distribution C-shaped groove; 52. Second distribution C-shaped groove; 53. Pilot control oil circuit; 54. Housing high-pressure oil circuit; 55. Housing low-pressure oil circuit; 56. Housing working oil circuit; 57. Plunger end cover working oil circuit; 58. Plunger end cover main oil circuit. Detailed Implementation

[0027] Combination Figure 1 and Figure 9As shown, this embodiment provides a pilot-controlled intelligent radial piston hydraulic device, including a housing 2, a high-pressure main port 33 and a low-pressure main port 32 disposed on the outside of the housing, a plurality of piston assemblies 15 arranged around the housing 2, an eccentric main shaft 19 rotatably disposed on the housing 2, a polygonal assembly mounted on the eccentric wheel of the eccentric main shaft 19, a pilot two-position three-way valve 11 corresponding to each piston assembly 15, a piston end cap 1 corresponding to each piston assembly 15, and a power calculation component; the housing 2 is provided with an eccentric main shaft cavity 23 and a plurality of pistons. The device comprises a plug cavity 13, several high-pressure oil passages 54, several low-pressure oil passages 55, and several working oil passages 56; wherein, the high-pressure oil passages 54 are interconnected within the housing 2 and connected to the high-pressure main port 33; the low-pressure oil passages 55 are interconnected within the housing 2 and connected to the low-pressure main port 32; the pilot two-position three-way valve 11 achieves bidirectional rotation of the radial plunger hydraulic device by alternately switching the connection states of the high-pressure oil passages 54 / 55 and the working oil passages 56. The plunger end cap 1 is provided with a plunger end cap main oil passage 58 and a plunger end cap working oil passage 57 connected to the plunger end cap main oil passage 58; wherein, the plunger end cap working oil passage 57 is connected to the housing working oil passage 56; the plunger end cap main oil passage 58 is connected to the corresponding plunger cavity 13; the plunger assembly 15 is slidably disposed in the corresponding plunger cavity 13; the eccentric spindle 19 is rotatably mounted in the eccentric spindle cavity 23 and is connected to all the plunger assemblies 15 through the polygonal assembly; it also includes a distribution plate 4 inserted and connected to the eccentric spindle 19, and a distribution compensation plate 5 with a built-in compensation spring 6 and connected to the distribution plate 4.

[0028] The distribution plate end cover 9 is provided with a first external oil control port 7 and a second external oil control port 8 suitable for switching the connection of a high-pressure oil source; the distribution compensation plate 5 is provided with a first pilot oil passage 27 communicating with the first external oil control port 7 and a second pilot oil passage 28 communicating with the second external oil control port 8; the end of the distribution compensation plate 5 near the distribution plate end cover 9 is provided with a limiting pin 30 for realizing the circumferential positioning of the distribution compensation plate 5 but allowing its axial sliding, and a compensation spring 6 is provided between the distribution compensation plate 5 and the distribution plate end cover 9.

[0029] The right end of the distribution plate 4 is pressed tightly against the housing 2 by the compensation effect of the distribution compensation plate 5; the right side of the distribution plate 4 is provided with a first pilot distribution ring groove 26 communicating with the first pilot oil passage 27 and a second pilot distribution ring groove 29 communicating with the second pilot oil passage 28; the left side of the distribution plate 4 is provided with a first distribution C-shaped groove 51 and a second distribution C-shaped groove 52; the first distribution C-shaped groove 51 and the second distribution C-shaped groove 52 are located on the same circumference and are symmetrically arranged; the first pilot distribution ring groove 26 is connected to the first distribution C-shaped groove 51; the second pilot distribution ring groove 29 is connected to the second distribution C-shaped groove 52. The power calculation component includes a Hall effect speed sensor component, a pressure sensor component, and a digital display component. The Hall effect speed sensor component includes a speed sensor cover 101, a speed sensor sensing probe 102, a speed sensor body 103, and a speed sensor signal output terminal 104. The pressure sensor component includes a pressure sensor body 105 and a pressure sensor signal output terminal 106. The digital display component includes a signal processing module 107 and a display screen 108. The signal processing module 107 integrates a central processing unit, an analog-to-digital conversion module, and a timing and counting module. The Hall effect speed sensor component can be radially semi-embedded in the distribution compensation disk 5 and fixed by the speed sensor cover 101. The outer circumferential surface of the distribution disk 4 has two non-coplanar sensing screw holes 303 and 304 with a phase difference of 90°, which are used for mounting. Sensing screw 301 and sensing screw 302; specifically, when the radial piston hydraulic device starts operating, the eccentric main shaft 19 rotates, and the distribution plate 4 rotates together with the eccentric main shaft 19. When sensing screw 301 / sensing screw 302 approaches the speed sensor probe 102 and generates magnetic induction, a frequency change occurs. This frequency change is converted into a signal by the speed sensor body 103 and then output to the signal processing module 107 of the digital display component through the speed sensor signal output terminal 104. Furthermore, the two sensing screws are at different distances from the speed sensor probe 102, resulting in different magnetic field magnitudes. Therefore, the forward and reverse rotation of the radial piston hydraulic device can be determined by the phase difference and amplitude of the output signal. The number and phase of the sensing screws are not limited by this and can be adjusted as needed. In addition, the communication between the speed sensor signal output terminal and the pressure sensor signal output terminal and the signal processing module can be achieved through shielded wire connection or Bluetooth communication, etc.

[0030] The pressure sensor assembly is connected to the high-pressure main port 33 via a T-junction. The pressure sensor body 105 measures the real-time pressure change of the high-pressure main port 33 and outputs the signal to the signal processing module 107 of the digital display assembly through the pressure sensor signal output terminal 106. The timing and counting module is used to collect the pulse signal from the speed sensor signal output terminal 104 and calculate the speed parameters. The analog-to-digital conversion module is used to collect the analog signal from the pressure sensor signal output terminal 106 and convert it into pressure parameters. The central processing unit calculates the power parameters according to the speed parameters and pressure parameters according to a preset relationship and controls the display screen 108 to display them in real time. Specifically, the signal processing module 107 can be a microcontroller, microprocessor, or embedded controller, and can be an MCU with ADC and timer functions, such as STM32 or 51 microcontroller.

[0031] The pilot two-position three-way valve 11 is installed in the two-position three-way valve chamber 12 and is configured to control the connection and disconnection between the housing high-pressure oil circuit 54 and the housing working oil circuit 56 of the housing 2, or between the housing low-pressure oil circuit 55 and the housing working oil circuit 56. Furthermore, the pilot two-position three-way valve 11 includes a working valve body 35 and a control valve body 45 disposed outside the working valve body 35; the working valve body 35 is provided with a first movable cavity 38 and a second movable cavity 40, and a high-pressure valve core guide band 36 and a low-pressure valve core guide band 41 are movably installed in the first movable cavity 38 and the second movable cavity 40, respectively; the high-pressure valve core 37 and the low-pressure valve core 42 are slidably disposed in the first movable cavity 38 and the second movable cavity 40 through the high-pressure valve core guide band 36 and the low-pressure valve core guide band 41, respectively; a ball joint connecting rod 39 is provided between the high-pressure valve core 37 and the low-pressure valve core 42, and the two ends of the ball joint connecting rod 39 form a spherical fit with the high-pressure valve core 37 and the low-pressure valve core 42, respectively. The valve body 35 is connected to transmit axial thrust and tension while allowing relative deflection. The high-pressure valve core guide band 36 and the low-pressure valve core guide band 41 are used to limit the axial movement trajectory of the high-pressure valve core 37 and the low-pressure valve core 42. The ball joint connecting rod 39 is used to compensate for the angular deviation between the valve cores. The working valve body 35 is also provided with a high-pressure valve hole 34, a low-pressure valve hole 47 and a working valve hole 48. The high-pressure valve core 37 controls the opening and closing of the high-pressure valve hole 34 and the working valve hole 48 by axial movement. The low-pressure valve core 42 controls the opening and closing of the low-pressure valve hole 47 and the working valve hole 48 by axial movement. The control valve body 45 is provided with a pilot control oil chamber 44 and is connected to the pilot control oil circuit 53 through a pilot transition chamber 43. like Figure 1 and Figure 2As shown, in this embodiment, the housing 2 is coaxially connected to the shaft end cover 22, housing end cover 21, eccentric main shaft 19, distribution plate 4, distribution compensation plate 5, and distribution plate end cover 9 in sequence. The housing 2 contains several plunger chambers 13, one eccentric main shaft chamber 23, two-position three-way valve chambers 12 corresponding one-to-one with the plunger assembly 15, and several high-pressure oil circuits, low-pressure oil circuits, working oil circuits, and control oil circuits. For example, it includes a housing high-pressure oil circuit 54, a housing low-pressure oil circuit 55, a housing working oil circuit 56, and a pilot control oil circuit 53. Figure 2 As shown, in this embodiment, there are 5 plunger end caps 1 and 5 plunger cavities 13, with each plunger cavity 13 corresponding to a pilot two-position three-way valve 11. The number of plunger cavities 13 is not limited to this and can also be 7 or 9. The eccentric spindle cavity 23 is used to install the eccentric spindle 19, and the first bearing 20 and the second bearing 31 are respectively installed on the housing end cap 21 and the housing 2 to support the eccentric spindle 19.

[0032] like Figure 1 and Figure 2 As shown, in this embodiment, the plunger assembly 15 is provided with five sets, and the transmission structure is a polygonal assembly. For example, a pentagonal assembly is used in this embodiment. The plunger assembly 15 includes a return spring 151, a guide belt 152, a guide sleeve 153, and a plunger 154; a gap space is formed between the guide sleeve 153 and the plunger 154 to accommodate the insertion of the guide sleeve 14 of the plunger end cap 1. The pentagonal assembly includes a five-star wheel 18, a five-star wheel sleeve 16, and a self-lubricating plate 17; the pentagonal assembly is mounted on the eccentric wheel of the eccentric main shaft 19 and can rotate relative to the eccentric wheel. When the eccentric main shaft 19 rotates, it drives the pentagonal assembly to perform circular motion. Since each side of the pentagonal assembly is always perpendicular to the axis of the corresponding plunger assembly 15, the polygonal assembly only translates and does not rotate. The plunger assembly 15 is slidably connected to the plunger cavity 13. The plunger assembly 15 is pressed against the self-lubricating plate 17 by the elastic force of the return spring 151. The plunger assembly 15 can slide up and down in the plunger cavity 13 by the translation of the five-star wheel 18 and the rotation of the main bearing 24, which drives the eccentric main shaft 19 to rotate. This is the working state of the hydraulic motor. Alternatively, the rotation of the eccentric main shaft 19 can drive the plunger assembly 15 to slide up and down in the plunger cavity 13 by the main bearing 24 and the five-star wheel 18. This is the working state of the hydraulic pump.

[0033] The eccentric spindle 19 is installed in the eccentric spindle cavity 23. A bushing 25 and a first bearing 20 are provided on the left side, and a main bearing 24 is provided on the right side. The first bearing 20 and the second bearing 31 are respectively installed on the housing end cover 21 and the housing 2 to provide stable support for the eccentric spindle 19.

[0034] like Figure 1 , Figure 2 and Figure 7As shown, in this embodiment, there are five pilot two-position three-way valves 11, evenly distributed on the housing 2. Its structure includes a working valve body 35, a control valve body 45, a high-pressure valve core 37, a low-pressure valve core 42, a high-pressure valve core guide band 36, a low-pressure valve core guide band 41, and a ball joint connecting rod 39. The working valve body 35 is provided with a first movable chamber 38 suitable for the axial sliding of the high-pressure valve core 37 and a second movable chamber 40 suitable for the axial sliding of the low-pressure valve core 42. In the static state, the ends of the high-pressure valve core 37 and the low-pressure valve core 42 near the working valve hole 48 are connected by a ball joint connecting rod 39, and the other ends that are not in contact with each other are subjected to hydraulic pressure, and the force-bearing area of ​​the high-pressure valve core 37 is smaller than that of the low-pressure valve core 42. The working valve body 35 is provided with a high-pressure valve hole 34, a low-pressure valve hole 47 and a working valve hole 48. The control valve body 45 is provided with a pilot control oil chamber 44, and the on / off state between the high-pressure valve hole 34 and the working valve hole 48 or between the low-pressure valve hole 47 and the working valve hole 48 can be controlled by controlling the movement of the high-pressure valve core 37 and the low-pressure valve core 42 to the limit position. The high-pressure valve port 34 is connected to the high-pressure oil circuit 54 of the housing through the high-pressure transition chamber 50. The low-pressure valve port 47 is connected to the low-pressure oil circuit 55 of the housing through the low-pressure transition chamber 46. The working valve port 48 is connected to the working oil circuit 56 of the housing through the working transition chamber 49. The pilot control oil chamber 44 is alternately connected to the first distribution C-shaped groove 51 and the second distribution C-shaped groove 52 through the pilot transition chamber 43 and the pilot control oil circuit 53 in sequence. Specifically, when high pressure is supplied to the pilot control oil chamber 44, the pilot hydraulic pressure on the low-pressure valve core 42 is greater than the hydraulic pressure on the high-pressure valve core 37 and other resistances, thus pushing the high-pressure valve core 37 to the high-pressure limit position. At this time, the passage between the high-pressure valve port 34 and the working valve port 48 is opened, and the passage between the low-pressure valve port 47 and the working valve port 48 is closed. That is, the high-pressure oil circuit 54 of the housing is connected to the working oil circuit 56 of the housing, and the low-pressure oil circuit 55 of the housing is disconnected from the working oil circuit 56 of the housing. When low pressure is supplied to the pilot control oil chamber 44, the hydraulic pressure on the high-pressure valve core 37 overcomes the pilot hydraulic pressure on the low-pressure valve core 42 and other resistances, thus pushing the low-pressure valve core 42 to the low-pressure limit position. At this time, the passage between the high-pressure valve port 34 and the working valve port 48 is closed, and the passage between the low-pressure valve port 47 and the working valve port 48 is opened. That is, the high-pressure oil circuit 54 of the housing is disconnected from the working oil circuit 56 of the housing, and the low-pressure oil circuit 55 of the housing is connected to the working oil circuit 56 of the housing.

[0035] Combination Figures 1 to 8As shown, the distribution compensation disk 5 is provided with a limiting pin 30 at one end near the distribution disk end cover 9 to achieve circumferential positioning of the distribution compensation disk 5 but allow its axial sliding, which is used to prevent the rotation of the distribution compensation disk 5. At the same time, a compensation spring 6 is provided between the distribution compensation disk 5 and the distribution disk end cover 9, so that the distribution compensation disk 5 can play an axial compensation role and press the distribution disk 4 onto the housing 2. The distribution compensation disk 5 is provided with a first pilot oil passage 27 and a second pilot oil passage 28. The first external control oil port 7 and the first pilot distribution ring groove 26 are respectively connected to the first pilot oil passage 27, and the second external control oil port 8 and the second pilot distribution ring groove 29 are respectively connected to the second pilot oil passage 28.

[0036] Example 2 Combination Figures 1 to 9 The present invention also provides a working method of a pilot valve controlled intelligent radial piston hydraulic device. Specifically, when the pilot valve controlled intelligent radial piston hydraulic device is a hydraulic motor, the high pressure port 33 is connected to a pressure oil source, and the low pressure port 32 is connected to a low pressure oil tank. The forward rotation of the hydraulic motor is controlled by connecting a control pressure oil source to the first external control oil port 7. At this time, the high pressure port 33 and the first external control oil port 7 are oil inlet channels, and the low pressure port 32 is oil outlet channel. Taking one of the piston assemblies 15 as an example; When the plunger assembly 15 is in the top position, high-pressure oil is introduced into both the high-pressure main port 33 and the first external control oil port 7. The high-pressure oil introduced through the high-pressure main port 33 passes through the high-pressure oil passage 54 of the housing and the high-pressure transition chamber 50 before entering the high-pressure valve hole 34 of its corresponding pilot two-position three-way valve 11. The high-pressure oil introduced through the first external control oil port 7 passes through the first pilot oil passage 27, the first pilot distribution ring groove 26, the first distribution C-shaped groove 51, the pilot control oil passage 53, and the pilot transition chamber 43 before entering its corresponding pilot control oil chamber 44. At this time, the pilot hydraulic pressure on the low-pressure valve core 42 is greater than the hydraulic pressure and other resistances on the high-pressure valve core 37, and pushes it forward. When the high-pressure valve core 37 moves to the high-pressure limit position, the high-pressure valve port 34 of the corresponding pilot two-position three-way valve 11 is connected to the working valve port 48. The high-pressure oil entering through the high-pressure main port 33 flows through the corresponding housing high-pressure oil passage 54, housing working oil passage 56, plunger end cap working oil passage 57, and plunger end cap main oil passage 58 before entering the corresponding plunger cavity 13. This pushes the plunger 154 downward, increasing the volume of the plunger cavity 13 and driving the eccentric main shaft 19 to perform positive circular motion, thereby driving the polygonal assembly to perform positive circular translation until the plunger assembly 15 reaches the bottom position. When the plunger assembly 15 is in the bottom position, the eccentric main shaft 19... Both the distribution plate 4 and the flow distribution disk 4 rotate 180 degrees in the positive direction. At this time, the pilot control oil chamber 44 of the corresponding pilot two-position three-way valve 11 is connected to the second flow distribution C-shaped groove 52 of the distribution plate 4. At this time, the pilot hydraulic pressure on the low-pressure valve core 42 is less than the hydraulic pressure and other resistances on the high-pressure valve core 37, pushing the low-pressure valve core 42 to the low-pressure limit position, so that the low-pressure valve hole 47 of the corresponding pilot two-position three-way valve 11 is connected to the working valve hole 48. Under the action of the thrust of other plunger assemblies 15 and the inertial force of the eccentric main shaft 19, the plunger assembly 15 moves upward, reducing the volume of the plunger cavity 13. The oil in the plunger cavity 13 flows through its corresponding plunger. The end cap main oil passage 58, the plunger end cap working oil passage 57, the housing working oil passage 56, and the housing low-pressure oil passage 55 flow out from the low-pressure main port 32, thereby realizing the periodic movement of a single plunger assembly 15; the reciprocating motion of several plunger assemblies 15 causes the eccentric spindle 19 to continuously output positive torque, so as to convert hydraulic energy into mechanical energy; at this time, the first sensing screw 301 approaches the speed sensor sensing probe 102 before the second sensing screw 302, and the output signal phase of the first sensing screw 301 leads the output signal phase of the second sensing screw 302. This state is defined as the forward rotation of the hydraulic motor, and the real-time output speed of the motor can be calculated according to the output frequency.

[0037] When the hydraulic motor needs to reverse, the high pressure port 33 is connected to the pressure oil source, the low pressure port 32 is connected to the low pressure oil tank, and the control pressure oil source is connected to the second external control oil port 8 to control the reverse rotation of the hydraulic motor. At this time, the high pressure port 33 and the second external control oil port 8 are the oil inlet channels, and the low pressure port 32 is the oil outlet channel. When the plunger assembly 15 is in the top position, high-pressure oil is introduced into both the high-pressure main port 33 and the second external control oil port 8. The high-pressure oil introduced through the high-pressure main port 33 passes through the high-pressure oil passage 54 of the housing and the high-pressure transition chamber 50 before entering the high-pressure valve hole 34 of its corresponding pilot two-position three-way valve 11. The high-pressure oil introduced through the second external control oil port 8 passes through the second pilot oil passage 28, the second pilot distribution ring groove 29, the second distribution C-shaped groove 52, the pilot control oil passage 53, and the pilot transition chamber 43 before entering its corresponding pilot control oil chamber 44. At this time, the pilot hydraulic pressure on the low-pressure valve core 42 is greater than the hydraulic pressure on the high-pressure valve core 37 and others. The resistance pushes the high-pressure valve core 37 to the high-pressure limit position. At this time, the high-pressure valve port 34 of the corresponding pilot two-position three-way valve 11 is connected to the working valve port 48. The high-pressure oil entering through the high-pressure main port 33 flows through the corresponding housing high-pressure oil passage 54, housing working oil passage 56, plunger end cover working oil passage 57, and plunger end cover main oil passage 58 before entering the corresponding plunger cavity 13. This pushes the plunger 154 downward, increasing the volume of the plunger cavity 13 and driving the eccentric main shaft 19 to perform a reverse circular motion, thereby driving the polygonal assembly to perform a reverse circular translation until the plunger assembly 15 reaches the bottom position. When the plunger assembly 15 is in the bottom position, the eccentric main shaft 19... Both shaft 19 and distribution plate 4 rotate 180 degrees in the opposite direction. At this time, the pilot control oil chamber 44 of the corresponding pilot two-position three-way valve 11 is connected to the first distribution C-shaped groove 51 of the distribution plate 4. At this time, the pilot hydraulic pressure on the low-pressure valve core 42 is less than the hydraulic pressure and other resistances on the high-pressure valve core 37, pushing the low-pressure valve core 42 to the low-pressure limit position, so that the low-pressure valve hole 47 of the corresponding pilot two-position three-way valve 11 is connected to the working valve hole 48. Under the thrust of other plunger assemblies 15 and the inertial force of the eccentric main shaft 19, the plunger assembly 15 moves upward, reducing the volume of the plunger cavity 13. The oil in the plunger cavity 13 flows through its corresponding plunger... The main oil passage 58 of the piston end cap, the working oil passage 57 of the piston end cap, the working oil passage 56 of the housing, and the low-pressure oil passage 55 of the housing flow out from the low-pressure main port 32, thereby realizing the periodic movement of a single piston assembly 15; the reciprocating movement of several piston assemblies 15 causes the eccentric spindle 19 to continuously output reverse torque to convert hydraulic energy into mechanical energy; at this time, the first sensing screw 301 approaches the speed sensor sensing probe 102 later than the second sensing screw 302, and the output signal phase of the first sensing screw 301 lags behind the output signal phase of the second sensing screw 302. This state is defined as the hydraulic motor reversing, and the real-time output speed of the motor can be calculated based on the output frequency.

[0038] That is, in the hydraulic motor state, the flow direction of the oil is as follows: pressure oil source → high pressure main port 33 → high pressure oil circuit 54 of the housing → high pressure valve port 34 of the pilot two-position three-way valve 11 → working valve port 48 of the pilot two-position three-way valve 11 → working transition chamber 49 → working oil circuit 56 of the housing → working oil circuit 57 of the plunger end cap → main oil circuit 58 of the plunger end cap → plunger chamber 13 → main oil circuit 58 of the plunger end cap → working oil circuit 57 of the plunger end cap → working oil circuit 56 of the housing → working transition chamber 49 → low pressure valve port 47 of the pilot two-position three-way valve 11 → low pressure transition chamber 46 → low pressure oil circuit 55 of the housing → low pressure main port 32.

[0039] Example 3 Continue to combine Figures 1 to 9 The present invention also provides another method for operating a pilot valve controlled intelligent radial piston hydraulic device. Specifically, when the pilot valve controlled intelligent piston hydraulic device is a hydraulic pump, the high pressure port 33 is connected to the high pressure tank or hydraulic load and is the oil outlet, and the low pressure port 32 is connected to the low pressure tank and is the oil inlet. At this time, the first external control port 7 and the second external control port 8 are both disconnected. Taking one of the piston assemblies 15 as an example; When the plunger assembly 15 is in the top position, low-pressure oil is introduced from the low-pressure main port 32. At this time, the eccentric spindle 19 rotates in the forward direction under the action of external torque, driving the plunger assembly 15 to move downward from the top position, increasing the volume of the corresponding plunger cavity 13 and creating a vacuum. At this time, the pressure in the plunger cavity 13 is lower than that in the low-pressure oil tank. The low-pressure oil flows through the low-pressure main port 32, the housing low-pressure oil passage 55, the low-pressure valve port 47 and working valve port 48 of the corresponding pilot two-position three-way valve 11, the housing working oil passage 56, the plunger end cover working oil passage 57, and the plunger end cover main oil passage 58 before entering the corresponding plunger cavity 13, until the plunger assembly 15 moves to the bottom position. At this time, the eccentric spindle 19 drives the distribution plate 4 to rotate 180 degrees in the forward direction. The main shaft 19 continues to rotate, driving the polygonal component to perform positive circular translation, which in turn drives the plunger assembly 15 to begin upward movement. The volume of the corresponding plunger cavity 13 decreases, and the pressure increases. The pressure is higher than that of the high-pressure oil tank or hydraulic load. The oil in the plunger cavity 13 flows through the main oil passage 58 of the plunger end cover, the working oil passage 57 of the plunger end cover, the working oil passage 56 of the housing, the working valve hole 48 and the high-pressure valve hole 34 of the corresponding pilot two-position three-way valve 11, and the high-pressure oil passage 54 of the housing before entering the high-pressure oil tank or hydraulic load, thus realizing the oil discharge movement of the plunger assembly 15. Under the rotation of the eccentric main shaft 19, each of the plunger assemblies 15 draws in low-pressure oil in each plunger cavity 13 and discharges high-pressure oil, thereby realizing the conversion of mechanical energy into hydraulic energy. At this time, the first sensing screw 301 approaches the speed sensor probe 102 before the second sensing screw 302. The output signal phase of the first sensing screw 301 leads the output signal phase of the second sensing screw 302. This state is defined as the hydraulic pump rotating in the forward direction, and the real-time output speed of the hydraulic pump can be calculated based on the output frequency.

[0040] The working principle and speed measurement process of the hydraulic pump when the eccentric spindle 19 rotates in the opposite direction under the action of external torque are the same as above, and will not be repeated here.

[0041] That is, in the hydraulic pump state, the oil flow direction is: pressure oil source → low pressure main port 32 → housing low pressure oil circuit 55 → low pressure transition chamber 46 → low pressure valve port 47 → working valve port 48 → working transition chamber 49 → housing working oil circuit 56 → plunger end cover working oil circuit 57 → plunger end cover main oil circuit 58 → plunger chamber 13 → plunger end cover main oil circuit 58 → plunger end cover working oil circuit 57 → housing working oil circuit 56 → working transition chamber 49 → working valve port 48 → high pressure valve port 34 → high pressure transition chamber 50 → high pressure main port 33 → high pressure oil tank or hydraulic load.

[0042] Through the above embodiments, the externally controlled pilot pressure is used to control the flow distribution, optimizing the valve group structure of the pilot-operated two-position three-way valve, improving neutrality and anti-vibration performance, reducing hydraulic shock, and enhancing the stability and reliability of the flow distribution. Simultaneously, the plunger assembly is simplified, the rubber cavity assembly is eliminated, improving the fatigue resistance and temperature resistance of the plunger structure and increasing system rigidity. Furthermore, a speed sensor is integrated at the flow distribution plate, and a pressure sensor is installed at the high-pressure main port. Combined with a signal processing module, the speed and pressure signals are collected and processed to achieve real-time acquisition of speed and pressure parameters, and further calculate power, realizing integrated speed detection, pressure monitoring, and power calculation, thereby supporting the condition monitoring of the hydraulic device. Compared with existing technologies, this invention has a compact structure, good sealing performance, can operate stably under high-pressure conditions, and effectively improves the service life, operating efficiency, and intelligence level of the device.

[0043] 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.

[0044] 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 pilot-controlled intelligent radial piston hydraulic device, comprising a housing, a high-pressure main port and a low-pressure main port disposed on the outside of the housing, a plurality of piston assemblies disposed around the housing, an eccentric main shaft rotatably disposed on the housing, piston end caps corresponding one-to-one with the piston assemblies, and a transmission structure disposed between the eccentric main shaft and the plurality of piston assemblies; wherein the housing contains piston cavities corresponding one-to-one with the piston assemblies, a plurality of interconnected high-pressure oil passages connected to the high-pressure main port, a plurality of interconnected low-pressure oil passages connected to the low-pressure main port, and a plurality of housing working oil passages; characterized in that, It also includes a pilot control oil circuit disposed in the housing, a pilot two-position three-way valve disposed one-to-one with the plunger chamber, a distribution plate inserted and connected to the eccentric spindle, a distribution compensation plate cooperating with the distribution plate, a distribution plate end cover disposed at one end of the eccentric spindle and connected to the housing, and a power calculation component; The pilot-operated two-position three-way valve is connected to the corresponding high-pressure oil circuit of the housing, the low-pressure oil circuit of the housing, the working oil circuit of the housing, and the pilot control oil circuit, respectively. It is configured to alternately switch the connection state between the high-pressure oil circuit and the working oil circuit of the housing, and between the low-pressure oil circuit and the working oil circuit of the housing, based on the pilot control pressure provided by the pilot control oil circuit. It also works in conjunction with the pilot distribution section of the distribution plate to achieve forward and reverse drive of the radial piston hydraulic device. Specifically, the pilot-operated two-position three-way valve includes a working valve body. A control valve body is disposed outside the working valve body. The working valve body has a first movable chamber and a second movable chamber. The first movable chamber contains a high-pressure valve core and a high-pressure valve core guide band for guiding the axial movement of the high-pressure valve core. The second movable chamber contains a low-pressure valve core and a low-pressure valve core guide band for guiding the axial movement of the low-pressure valve core. The high-pressure valve core and the low-pressure valve core are connected by a ball joint connecting rod. The two ends of the ball joint connecting rod respectively form a spherical fit with the high-pressure valve core and the low-pressure valve core to transmit axial force while allowing relative deflection between the two. The working valve body has a high-pressure valve port, a low-pressure valve port, and a working valve port. The high-pressure valve port is connected to the corresponding high-pressure oil circuit of the housing through a high-pressure transition chamber. The low-pressure valve port is connected to the corresponding low-pressure oil circuit of the housing through a low-pressure transition chamber. The working valve port is connected to the corresponding working oil circuit of the housing through a working transition chamber. The control valve body has a pilot control oil chamber, which is connected to the corresponding pilot control oil circuit through a pilot transition chamber. When the pilot control oil chamber is under high pressure, the high-pressure valve port is connected to the working valve port, and the low-pressure valve port is disconnected from the working valve port; when the pilot control oil chamber is under low pressure, the high-pressure valve port is disconnected from the working valve port, and the low-pressure valve port is connected to the working valve port. The distribution plate and the distribution compensation plate are coaxially disposed inside the end cover of the distribution plate. The distribution compensation plate is equipped with a compensation spring and can apply an axial compensation force to the distribution plate along the central axis direction of the distribution plate under the elastic force of the compensation spring, so as to realize automatic compensation for wear of the distribution plate. The distribution plate end cover is provided with a first external oil control port and a second external oil control port suitable for switching the connection of a high-pressure oil source. The distribution compensation plate is provided with a first pilot oil passage connected to the first external oil control port and a second pilot oil passage connected to the second external oil control port. The distribution plate is provided with a pilot distribution section, which is used to alternately connect the first pilot oil circuit or the second pilot oil circuit with the corresponding pilot control oil circuit when the distribution plate rotates with the eccentric main shaft, so as to alternately provide pilot control pressure to each of the pilot two-position three-way valves; The power calculation component includes a speed sensor component, a pressure sensor component, and a signal processing module. The speed sensor component is used to detect the speed signal of the eccentric spindle or distributor plate, the pressure sensor component is used to detect the pressure signal at the high-pressure main port, and the signal processing module is used to calculate the power parameters of the radial piston hydraulic device based on the speed signal and the pressure signal.

2. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 1, characterized in that, The pilot distribution section includes a first pilot distribution annular groove and a second pilot distribution annular groove disposed on one side of the distribution plate, and a first distribution C-shaped groove and a second distribution C-shaped groove disposed on the other side of the distribution plate; the first pilot distribution annular groove is connected to the first pilot oil circuit, the second pilot distribution annular groove is connected to the second pilot oil circuit, the first pilot distribution annular groove is connected to the first distribution C-shaped groove, and the second pilot distribution annular groove is connected to the second distribution C-shaped groove; the first distribution C-shaped groove and the second distribution C-shaped groove are located on the same circumference and arranged opposite to each other, and the first distribution C-shaped groove and the second distribution C-shaped groove are alternately connected to the pilot control oil circuits at different positions during the rotation of the distribution plate, so that the distribution plate alternately provides pilot control pressure to each of the pilot two-position three-way valves when rotating with the eccentric main shaft.

3. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 1, characterized in that, The transmission structure is a polygonal assembly, which is mounted on the eccentric part of the eccentric spindle and can rotate relative to the eccentric part. Each side of the polygonal assembly cooperates with the corresponding plunger assembly to drive the plunger assembly to reciprocate when the eccentric spindle rotates, or to drive the eccentric spindle to rotate when the plunger assembly reciprocates. The polygonal assembly includes a polygonal wheel, a polygonal wheel sleeve, and a self-lubricating plate. The polygonal wheel is mounted on the eccentric part of the eccentric spindle through the polygonal wheel sleeve, and the self-lubricating plate is disposed between the polygonal wheel and the plunger assembly.

4. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 1, characterized in that, The plunger assembly includes a return spring, a guide belt, a guide sleeve, and a plunger. The plunger slides within the corresponding plunger cavity via the guide belt and the guide sleeve. The return spring is used to keep the plunger assembly in contact with the transmission structure.

5. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 1, characterized in that, The speed sensor assembly is a Hall speed sensor assembly, which includes a speed sensor cover, a speed sensor sensing probe, a speed sensor body, and a speed sensor signal output terminal. The Hall speed sensor assembly is radially semi-embedded on the current distribution compensation disk and is fixed by the speed sensor cover. Two sensors are provided on the outer circumferential surface of the distribution plate. The two sensors rotate with the distribution plate and pass through the sensing area of ​​the speed sensor probe in sequence, so that the main body of the speed sensor outputs a pulse signal related to the speed. The two sensing elements are sensing screws respectively installed in two sensing screw holes. The two sensing screw holes are not coplanar and are 90° out of phase. The sensing distances between the two sensing screws and the speed sensor sensing probe are different, so that the signal processing module can determine the forward or reverse direction of the radial piston hydraulic device based on the phase sequence and / or amplitude difference of the output signals corresponding to the two sensing screws.

6. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 5, characterized in that, The pressure sensor assembly is connected to the high-pressure main port. The signal processing module includes a central processing unit, an analog-to-digital converter, and a timing and counting module. The analog-to-digital converter is used to collect the pressure signal output by the pressure sensor assembly and convert it into pressure parameters. The timing and counting module is used to collect the pulse signal output by the speed sensor assembly and convert it into speed parameters. The central processing unit is used to calculate power parameters based on the pressure parameters, the speed parameters, and preset displacement parameters.

7. The pilot valve-controlled intelligent radial piston hydraulic device according to claim 6, characterized in that, The central processing unit calculates the power parameters using the following formula: ； In the formula, This refers to the working pressure differential of the radial piston hydraulic device. This represents the theoretical displacement of the radial piston hydraulic device. The rotational speed of the eccentric spindle; This is the power correction function obtained by fitting multiple sets of test conditions.

8. A method of operating the pilot valve-controlled intelligent radial piston hydraulic device as described in claim 1, characterized in that, When the pilot valve controlled intelligent radial piston hydraulic device works as a hydraulic motor, the high pressure main port is connected to the pressure oil source, the low pressure main port is connected to the low pressure oil tank, and the first external control oil port or the second external control oil port is connected to the control pressure oil source to control the forward or reverse rotation of the radial piston hydraulic device. When any plunger assembly is in the top position, high-pressure oil enters the high-pressure valve port of the corresponding pilot two-position three-way valve through the high-pressure main port and the high-pressure oil circuit of the housing. At the same time, control pressure oil enters the pilot control oil chamber of the corresponding pilot two-position three-way valve through the first external control oil port or the second external control oil port, the distribution compensation plate, the distribution plate and the pilot control oil circuit, so that the high-pressure valve port and the working valve port are connected, and the low-pressure valve port and the working valve port are disconnected. High-pressure oil enters the corresponding plunger chamber through the working valve port, the working oil circuit of the housing and the plunger end cover, pushing the plunger assembly to move and driving the eccentric spindle to rotate. When the plunger assembly moves to the bottom position, the distribution plate rotates with the eccentric spindle to a position that switches the corresponding pilot control oil chamber to a low-pressure state, so that the low-pressure valve port of the corresponding pilot two-position three-way valve is connected to the working valve port. The oil in the plunger chamber is discharged through the plunger end cover, the housing working oil passage, the working valve port, the low-pressure valve port, and the housing low-pressure oil passage to the low-pressure main port, thereby causing multiple plunger assemblies to reciprocate periodically and drive the eccentric spindle to continuously output torque.

9. A method of operating the pilot valve-controlled intelligent radial piston hydraulic device as described in claim 1, characterized in that, When the pilot valve controlled intelligent radial piston hydraulic device works as a hydraulic pump, the low-pressure main port is connected to the low-pressure oil tank and serves as the oil inlet, and the high-pressure main port is connected to the high-pressure oil tank or hydraulic load and serves as the oil outlet. An external torque drives the eccentric spindle to rotate, and the eccentric spindle drives each plunger assembly to reciprocate within the corresponding plunger cavity through the transmission structure. When any plunger assembly moves downward and increases the volume of the corresponding plunger cavity, the low-pressure oil enters the corresponding plunger cavity through the low-pressure main port, the housing low-pressure oil passage, the low-pressure valve port and working valve port of the corresponding pilot two-position three-way valve, the housing working oil passage, and the plunger end cap. When the plunger assembly moves upward and reduces the volume of the corresponding plunger cavity, the oil in the plunger cavity is discharged through the plunger end cap, the working oil passage of the housing, the working valve port and high pressure valve port of the corresponding pilot two-position three-way valve, and the high pressure oil passage of the housing, so as to realize the conversion of mechanical energy into hydraulic energy.

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