阅读说明：本技术 频率和冲击力可调的液压系统 (Hydraulic system with adjustable frequency and impact force ) 是由 苗国华 迟峰 王永 刘淑强 于 2020-12-31 设计创作，主要内容包括：本发明公开了一种频率和冲击力可调的液压系统,其属于工程机械技术领域。它解决了现有技术中传统打桩机锤头的激振力存在的振动偏心距调整困难的缺陷。其主体结构包括压力可调系统、换向液压阀、执行元件和驱动装置,所述压力可调系统通过换向液压阀与执行元件连接,所述换向液压阀的旋转端与驱动装置连接。本发明主要用于打桩机等工程机械上。(The invention discloses a frequency and impact force adjustable hydraulic system, and belongs to the technical field of engineering machinery. The defect that the vibration eccentricity is difficult to adjust due to the exciting force of the hammer head of the traditional pile driver in the prior art is overcome. The main structure of the hydraulic control system comprises a pressure adjustable system, a reversing hydraulic valve, an actuating element and a driving device, wherein the pressure adjustable system is connected with the actuating element through the reversing hydraulic valve, and the rotating end of the reversing hydraulic valve is connected with the driving device. The invention is mainly used for engineering machinery such as a pile driver and the like.)

1. The utility model provides a frequency and impact force adjustable hydraulic system which characterized in that: the hydraulic control system comprises a pressure adjustable system, a reversing hydraulic valve (20), an actuating element (21) and a driving device (14), wherein the pressure adjustable system is connected with the actuating element (21) through the reversing hydraulic valve (20), and the rotating end of the reversing hydraulic valve (20) is connected with the driving device (14).

2. The hydraulic system with adjustable frequency and impact force of claim 1, wherein: the pressure adjustable system comprises a working pump B (17), a proportional overflow valve (18), a first speed regulating valve (19), a one-way valve (24) and an unloading valve (26), wherein the working pump B (17) is respectively connected with the proportional overflow valve (18), the one-way valve (24) and the unloading valve (26), the one-way valve (24) is connected with a reversing hydraulic valve (20) through the first speed regulating valve (19), an energy accumulator (23) is connected between the first speed regulating valve (19) and the reversing hydraulic valve (20) in parallel, and the driving device (14) is a motor (22).

3. The hydraulic system with adjustable frequency and impact force of claim 1, wherein: the pressure adjustable system comprises a variable pump B (28), a proportional overflow valve (18), a one-way valve (24) and an unloading valve (26), wherein the variable pump B (28) is respectively connected with the proportional overflow valve (18), the one-way valve (24) and the unloading valve (26), the one-way valve (24) is connected with a reversing hydraulic valve (20), an energy accumulator (23) is connected between the one-way valve (24) and the reversing hydraulic valve (20) in parallel, and the driving device (14) is a motor (22).

4. The hydraulic system with adjustable frequency and impact force of claim 1, wherein: the hydraulic system with adjustable frequency and impact force further comprises a frequency adjustable system, the frequency adjustable system comprises an overflow valve (15), a working pump A (16) and a second speed regulating valve (25), the driving device (14) is a motor, the working pump A (16) is respectively connected with the overflow valve (15) and the second speed regulating valve (25), and the second speed regulating valve (25) is connected with the motor; the pressure adjustable system comprises a working pump B (17), a proportional overflow valve (18), a first speed regulating valve (19), a one-way valve (24) and an unloading valve (26), wherein the working pump B (17) is respectively connected with the proportional overflow valve (18), the one-way valve (24) and the unloading valve (26), the one-way valve (24) is connected with a reversing hydraulic valve (20) through the first speed regulating valve (19), and an energy accumulator (23) is connected in parallel between the first speed regulating valve (19) and the reversing hydraulic valve (20).

5. The hydraulic system with adjustable frequency and impact force of claim 1, wherein: the frequency and impact force adjustable hydraulic system further comprises a frequency adjustable system, the frequency adjustable system comprises a variable pump A (27) and an overflow valve (15), the driving device (14) is a motor, the variable pump A (27) is respectively connected with the overflow valve (15) and the motor, the pressure adjustable system comprises a variable pump B (28), a proportional overflow valve (18), a one-way valve (24) and an unloading valve (26), the variable pump B (28) is respectively connected with the proportional overflow valve (18), the one-way valve (24) and the unloading valve (26), the one-way valve (24) is connected with a reversing hydraulic valve (20), and an energy accumulator (23) is connected between the one-way valve (24) and the reversing hydraulic valve (20) in parallel.

6. The hydraulic system with adjustable frequency and impact force according to any one of claims 1-5, wherein: the reversing hydraulic valve (20) comprises a valve body (1), an oil port A, an oil port B, an oil port P and an oil port T are arranged on the valve body (1), a rotary valve core (2) is arranged in the valve body (1), the rotary valve core (2) is connected with the valve body (1) through an end cover (5), a first bearing (3) and a second bearing (10) are arranged between the rotary valve core (2) and the valve body (1), a driving device (14) is arranged on the end cover (5), and a driving shaft of the driving device (14) is connected with the rotary valve core (2).

7. The hydraulic system with adjustable frequency and impact force of claim 6, wherein: one end of the valve body (1) is provided with two process holes (101), and the process holes (101) are provided with a static seal II (11) and a plug screw (12); the outer side of the end cover (5) is provided with a baffle (9), the baffle (9) is connected with the end cover (5), a static seal I (4) is arranged between the valve body (1) and the end cover (5), and a rotary seal (7) is arranged between the rotary valve core (2) and the end cover (5).

8. The hydraulic system with adjustable frequency and impact force of claim 7, wherein: the oil-gas separator is characterized in that a first annular oil duct (201), a second annular oil duct (204) and a third annular oil duct (205) are arranged on the rotary valve core (2), two or more first axial oil grooves (202) and two or more second axial oil grooves (217) are uniformly distributed on the periphery of the rotary valve core (2), the first axial oil grooves (202) and the second axial oil grooves (217) are alternately distributed, the first oil grooves (203) are symmetrically arranged on two sides of the first axial oil grooves (202), the second oil grooves (218) are symmetrically arranged on two sides of the second axial oil grooves (217), the first annular oil duct (201) is communicated with the first axial oil grooves (202), and the second annular oil duct (204) is communicated with the second axial oil grooves (217).

9. The hydraulic system with adjustable frequency and impact force of claim 8, wherein: the rotary valve core (2) is provided with a first balance groove (219) and a second balance groove (220), and the first balance groove (219) is communicated with the first annular oil duct (201) through a first axial oil groove (202).

10. The frequency and impact force adjustable hydraulic system according to claim 9, wherein: the oil cylinder is characterized in that a first radial hole (210) and a second radial hole (211) are symmetrically formed in the first annular oil duct (201), a third radial hole (206) and a sixth radial hole (215) are symmetrically formed in the third annular oil duct (205), a second axial hole (207) and a first axial hole (208) are formed in the rotary valve core (2), one end of the first annular oil duct (201) is communicated with the third annular oil duct (205) through the first radial hole (210), the first axial hole (208) and the sixth radial hole (215), and the other end of the first annular oil duct (201) is communicated with the third annular oil duct (205) through the second radial hole (211), the second axial hole (207) and the third radial hole (206).

The technical field is as follows:

the invention belongs to the technical field of engineering machinery, and particularly relates to a hydraulic system with adjustable frequency and impact force.

Background art:

pile driver based on crawler excavator transformation utilizes the high-speed rotation of tup eccentric mechanism, produce periodic exciting force, thereby produce high-frequency vibration, and will vibrate and pass through the tup centre gripping part and transmit for the pile body, along with the vibration that produces, the soil body structure around the pile changes because of vibrating, soil texture liquefaction around the pile body, the structure between the soil granule takes place disorderly, instantaneous strength reduces, cause the "fluidization" phenomenon of soil structure, thereby reduce the frictional force of stake and soil body, then with excavator downforce, pile driver and stake dead weight etc. common effort are beaten the stake and are pushed into soil.

The exciting force of the hammer head is related to the eccentricity of the vibrating eccentric mechanism and the rotating speed of the vibrating eccentric shaft, namely under the condition that the eccentricity of the eccentric mechanism is fixed, the exciting force is related to the rotating speed (namely the vibrating frequency) of the vibrating eccentric shaft. If the magnitude of the exciting force is changed, the vibration frequency must be reduced, so that the magnitude of the exciting force and the magnitude of the vibration frequency cannot be independently controlled, and under the condition that the vibration frequency is not changed, the eccentric distance of the vibration mechanism must be changed to change the exciting force, so that the adjustment of the vibration eccentric distance is difficult in actual operation, and the labor intensity is high.

The invention content is as follows:

the invention aims to overcome the defects of the prior art and provides a hydraulic system with adjustable frequency and impact force, which can change the on-off, the rotation speed change and the on-off times of a reversing hydraulic valve, thereby realizing the frequency adjustment.

In order to realize the purpose, the invention is realized by adopting the following technical scheme:

the hydraulic system with adjustable frequency and impact force comprises a pressure adjustable system, a reversing hydraulic valve, an actuating element and a driving device, wherein the pressure adjustable system is connected with the actuating element through the reversing hydraulic valve, and the rotating end of the reversing hydraulic valve is connected with the driving device.

Preferably, the pressure adjustable system comprises a working pump B, a proportional overflow valve, a first speed regulating valve, a one-way valve and an unloading valve, the working pump B is respectively connected with the proportional overflow valve, the one-way valve and the unloading valve, the one-way valve is connected with a reversing hydraulic valve through the first speed regulating valve, an energy accumulator is connected between the first speed regulating valve and the reversing hydraulic valve in parallel, and the driving device is a motor.

Preferably, the pressure adjustable system comprises a variable pump B, a proportional overflow valve, a one-way valve and an unloading valve, the variable pump B is respectively connected with the proportional overflow valve, the one-way valve and the unloading valve, the one-way valve is connected with a reversing hydraulic valve, an energy accumulator is connected between the one-way valve and the reversing hydraulic valve in parallel, and the driving device is a motor.

Preferably, the frequency and impact force adjustable hydraulic system further comprises a frequency adjustable system, the frequency adjustable system comprises an overflow valve, a working pump a and a second speed regulating valve, the driving device is a motor, the working pump a is respectively connected with the overflow valve and the second speed regulating valve, and the second speed regulating valve is connected with the motor; the pressure adjustable system comprises a working pump B, a proportional overflow valve, a first speed regulating valve, a one-way valve and an unloading valve, wherein the working pump B is respectively connected with the proportional overflow valve, the one-way valve and the unloading valve, the one-way valve is connected with a reversing hydraulic valve through the first speed regulating valve, and an energy accumulator is connected in parallel between the first speed regulating valve and the reversing hydraulic valve.

Preferably, the frequency and impact force adjustable hydraulic system further comprises a frequency adjustable system, the frequency adjustable system comprises a variable pump A and an overflow valve, the driving device is a motor, the variable pump A is respectively connected with the overflow valve and the motor, the pressure adjustable system comprises a variable pump B, a proportional overflow valve, a one-way valve and an unloading valve, the variable pump B is respectively connected with the proportional overflow valve, the one-way valve and the unloading valve, the one-way valve is connected with the reversing hydraulic valve, and an energy accumulator is connected in parallel between the one-way valve and the reversing hydraulic valve.

Preferably, the reversing hydraulic valve comprises a valve body, wherein an oil port A, an oil port B, an oil port P and an oil port T are arranged on the valve body, a rotary valve core is arranged in the valve body and connected with the valve body through an end cover, a bearing I and a bearing II are arranged between the rotary valve core and the valve body, a driving device is arranged on the end cover, and a driving shaft of the driving device is connected with the rotary valve core.

Preferably, one end of the valve body is provided with two process holes, and the process holes are provided with a static seal II and a screw plug; the outer side of the end cover is provided with a baffle plate, the baffle plate is connected with the end cover through a screw A, a first static seal is arranged between the valve body and the end cover, and a rotary seal is arranged between the rotary valve core and the end cover.

Preferably, the rotary valve core is provided with a first annular oil passage, a second annular oil passage and a third annular oil passage, two or more first axial oil grooves and two or more second axial oil grooves are uniformly distributed on the periphery of the rotary valve core, the first axial oil grooves and the second axial oil grooves are alternately distributed, the first oil grooves are symmetrically arranged on two sides of the first axial oil grooves, the second oil grooves are symmetrically arranged on two sides of the second axial oil grooves, the first annular oil passage is communicated with the first axial oil grooves, and the second annular oil passage is communicated with the second axial oil grooves.

Preferably, a first balance groove and a second balance groove are formed in the rotary valve element, and the first balance groove is communicated with the first annular oil channel through a first axial oil groove.

Preferably, the first annular oil duct is symmetrically provided with a first radial hole and a second radial hole, the third annular oil duct is symmetrically provided with a third radial hole and a sixth radial hole, the rotary valve core is internally provided with a second axial hole and a first axial hole, one end of the first annular oil duct is communicated with the third annular oil duct through the first radial hole, the first axial hole and the sixth radial hole, and the other end of the first annular oil duct is communicated with the third annular oil duct through the second radial hole, the second axial hole and the third radial hole.

Compared with the prior art, the invention has the beneficial effects that:

1. the reversing hydraulic valve is driven to rotate by the motor or the motor, so that the on-off, the rotating speed change and the on-off frequency change of the reversing hydraulic valve are changed, the frequency is adjustable, the high-frequency on-off can be realized due to the fact that the rotating speed is much higher than the axial speed of a common slide valve, the periodic frequency motion of an execution element is controlled by the opening frequency of the reversing hydraulic valve, the pressure value of an impact tail end is controlled by the set pressure of a control system, the force of the impact tail end is adjustable, and the frequency and the impact force are adjustable;

2. the proportional overflow valve can adjust the system pressure, so that the proportional overflow valve is combined with the high-frequency on-off of the reversing hydraulic valve to form the output of high-frequency pulse of adjustable pressure oil, and is combined with an actuating element to realize a high-frequency pulse hydraulic system with adjustable frequency and adjustable pulse force;

3. the reversing hydraulic valve can realize high-frequency opening and closing control, solves the defect of complexity in controlling the high-frequency opening and closing axial movement of the slide valve, is connected with the valve body through the bearing, solves the defect of friction between the high-frequency axial movement of the slide valve or the rotary movement of the rotary valve and the shell, and has simple structure and low cost;

4. the bearing is lubricated through leakage of pressure oil, and the pressure oil forms a lubricating oil film between the rotary valve core and the valve body, and the axial groove pressure oil and the annular channel pressure oil can play a role in balance support of the static pressure bearing on the rotary valve core.

Description of the drawings:

FIG. 1 is a hydraulic schematic diagram of embodiment 1 of the present invention;

FIG. 2 is a hydraulic schematic diagram of embodiment 2 of the present invention;

FIG. 3 is a hydraulic schematic diagram of embodiment 3 of the present invention;

FIG. 4 is a hydraulic schematic diagram of embodiment 4 of the present invention;

FIG. 5 is a schematic diagram of the reversing hydraulic valve of the present invention;

FIG. 6 is a top plan view of the reversing hydraulic valve of the present invention;

FIG. 7 is a front view of the reversing hydraulic valve of the present invention;

FIG. 8 is a schematic view of a rotary valve cartridge according to the present invention;

FIG. 9 is a cross-sectional view A-A of FIG. 6;

FIG. 10 is a cross-sectional view taken along line B-B of FIG. 7;

FIG. 11 is a cross-sectional view (to the left) of C-C of FIG. 6;

FIG. 12 is a cross-sectional view of C-C of FIG. 6 (neutral);

FIG. 13 is a cross-sectional view (right) of C-C in FIG. 6;

fig. 14 is a cross-sectional view (middle-right switching) of C-C in fig. 6.

In the figure: 1. a valve body; 2. rotating the valve core; 3. a first bearing; 4. static sealing is carried out; 5. an end cap; 6. a screw A; 7. rotating and sealing; 8. a process plug; 9. a baffle plate; 10. a second bearing; 11. static sealing II; 12. a plug screw; 13. a screw B; 14. a drive device; 15. an overflow valve; 16. a working pump A; 17. a working pump B; 18. a proportional relief valve; 19. a first speed regulating valve; 20. a reversing hydraulic valve; 21. an actuator; 22. a motor; 23. an accumulator; 24. a one-way valve; 25. a second speed regulating valve; 26. an unloading valve; 27. a variable pump A; 28. a variable pump B; 101. a fabrication hole; 201. a first annular oil passage; 202. a first axial oil groove; 203. a first oil groove; 204. a second annular oil passage; 205. a third annular oil passage; 206. a third radial hole; 207. a second axial bore; 208. a first axial bore; 209. a third axial bore; 210. a first radial bore; 211. a second radial bore; 212. a fifth radial hole; 213. a fourth radial hole; 214. an oil leakage passage; 215. a sixth radial hole; 217. a second axial oil groove; 218. a second oil groove; 219. a first balance groove; 220. a second balancing groove.

The specific implementation mode is as follows:

the invention is further illustrated by the following specific examples in combination with the accompanying drawings.

Example 1:

as shown in FIG. 1, the hydraulic system with adjustable frequency and impact force comprises a pressure adjustable system, a reversing hydraulic valve 20, an actuating element 21 and a driving device 14, wherein the pressure adjustable system is connected with the actuating element 21 through the reversing hydraulic valve 20, and the rotating end of the reversing hydraulic valve 20 is connected with the driving device 14. The pressure adjustable system comprises a working pump B17, a proportional overflow valve 18, a first speed regulating valve 19, a one-way valve 24 and an unloading valve 26, wherein the working pump B17 is respectively connected with the proportional overflow valve 18, the one-way valve 24 and the unloading valve 26, the one-way valve 24 is connected with a reversing hydraulic valve 20 through the first speed regulating valve 19, an energy accumulator 23 is connected between the first speed regulating valve 19 and the reversing hydraulic valve 20 in parallel, and the driving device 14 is a motor 22.

Example 2:

as shown in fig. 2, the frequency and impact force adjustable hydraulic system comprises a variable pump B28, a proportional overflow valve 18, a check valve 24 and an unloading valve 26, wherein the variable pump B28 is respectively connected with the proportional overflow valve 18, the check valve 24 and the unloading valve 26, the check valve 24 is connected with a reversing hydraulic valve 20, an accumulator 23 is connected in parallel between the check valve 24 and the reversing hydraulic valve 20, and the driving device 14 is a motor 22.

Example 3:

as shown in fig. 3, the frequency and impact force adjustable hydraulic system further includes a frequency adjustable system, the frequency adjustable system includes an overflow valve 15, a working pump a16 and a second speed regulating valve 25, the driving device 14 is a motor, the working pump a16 is connected to the overflow valve 15 and the second speed regulating valve 25, respectively, and the second speed regulating valve 25 is connected to the motor; the pressure adjustable system comprises a working pump B17, a proportional overflow valve 18, a first speed regulating valve 19, a one-way valve 24 and an unloading valve 26, wherein the working pump B17 is respectively connected with the proportional overflow valve 18, the one-way valve 24 and the unloading valve 26, the one-way valve 24 is connected with a reversing hydraulic valve 20 through the first speed regulating valve 19, and an energy accumulator 23 is connected in parallel between the first speed regulating valve 19 and the reversing hydraulic valve 20. The overflow valve 15 is used for pressure setting protection of a frequency adjustable system, and the second speed regulating valve 25 regulates the flow input to the motor, so that the rotating speed of the motor is controlled, the opening and closing times of the reversing hydraulic valve 20 are adjustable, and high-frequency opening and closing can be realized.

When the working pump B17 does not work, pressure oil output by the working pump B17 is unloaded through the unloading valve 26, so that energy consumption loss can be reduced; when the hydraulic control valve works, the electromagnetic valve of the unloading valve 26 is electrified, the unloading valve 26 is closed, and the pressure oil output by the working pump B17 is output to the execution element 21 through the one-way valve 24, the first speed regulating valve 19, the energy accumulator 23 and the reversing hydraulic valve 20. The proportional relief valve 18 can regulate the system pressure, so that the pressure of the actuator 21 can be regulated. The check valve 24 prevents the pressure change impact during the work of the reversing hydraulic valve 20 and the actuator 21 from being transmitted to the working pump B17, and the working pump B17 is protected. The accumulator 23 absorbs pressure fluctuations in the pressure-adjustable system circuit, eliminating peaks. The first speed valve 19 regulates the system flow to ensure flow demand during high frequency movement of the actuator 21.

When the pulse pressure oil pump works, the motor drives the reversing hydraulic valve 20 to open and close at high frequency, the working pump B17 outputs pulse pressure oil through the opening and closing of the reversing hydraulic valve 20, the pressure of the pulse pressure oil can be adjusted by the proportional overflow valve 18, and when the rotating speed (namely the motor speed) of the reversing hydraulic valve 20 is changed and the working pressure of the proportional overflow valve 18 is changed, the output pressure and the frequency can be changed, so that the output of variable high-frequency pulse force is realized.

Example 4:

as shown in fig. 4, the frequency and impact force adjustable hydraulic system further includes a frequency adjustable system, the frequency adjustable system includes a variable pump a27 and an overflow valve 15, the driving device 14 is a motor, the variable pump a27 is respectively connected to the overflow valve 15 and the motor, the pressure adjustable system includes a variable pump B28, a proportional overflow valve 18, a check valve 24 and an unloading valve 26, the variable pump B28 is respectively connected to the proportional overflow valve 18, the check valve 24 and the unloading valve 26, the check valve 24 is connected to the reversing hydraulic valve 20, and an accumulator 23 is connected in parallel between the check valve 24 and the reversing hydraulic valve 20. The output flow is controlled by adjusting the swash plate angles of the variable pump A27 and the variable pump B28, the rotating speed of the driving motor is further controlled, the opening and closing frequency of the reversing hydraulic valve 20 is adjusted, the action flow requirement of the actuating element 21 is met, and compared with embodiment 3, the first speed regulating valve 19 and the second speed regulating valve 25 are saved.

Example 5:

as shown in fig. 5-10, in the hydraulic system with adjustable frequency and impact force, the reversing hydraulic valve 20 includes a valve body 1, an oil port a, an oil port B, an oil port P, and an oil port T are arranged on the valve body 1, a rotary valve element 2 is arranged in the valve body 1, the rotary valve element 2 is connected to the valve body 1 through an end cover 5, a first bearing 3 and a second bearing 10 are arranged between the rotary valve element 2 and the valve body 1, a driving device 14 is arranged on the end cover 5, and a driving shaft of the driving device 14 is connected to the rotary valve element 2.

Two process holes 101 are formed in one end of the valve body 1, a second static seal 11 and a plug screw 12 are mounted on the process holes 101, and the process holes 101 are used for disassembling the second bearing 10.

The outer side of the end cover 5 is provided with a baffle plate 9, the baffle plate 9 is connected with the end cover 5 through a screw A6, a static seal 4 is arranged between the valve body 1 and the end cover 5, a rotary seal 7 is arranged between the rotary valve core 2 and the end cover 5, and the valve body 1 is connected with the end cover 5 through a screw B13.

The rotary valve core 2 is provided with a first annular oil duct 201, a second annular oil duct 204 and a third annular oil duct 205, two or more first axial oil grooves 202 and two or more second axial oil grooves 217 are uniformly distributed on the periphery of the rotary valve core 2, the first axial oil grooves 202 and the second axial oil grooves 217 are alternately distributed, the first annular oil duct 201 is communicated with the first axial oil grooves 202, and the second annular oil duct 204 is communicated with the second axial oil grooves 217. The reversing hydraulic valve 20 is now in an O-mode function.

The first oil groove 203 is symmetrically arranged on two sides of the first axial oil groove 202, the second oil groove 218 is symmetrically arranged on two sides of the second axial oil groove 217, and the reversing hydraulic valve 20 has an H-shaped function by adding the first oil groove 203 and the second oil groove 218.

The rotary valve core 2 is provided with a first balance groove 219 and a second balance groove 220, and the first balance groove 219 is communicated with the first annular oil passage 201 through a first axial oil groove 202.

The first annular oil passage 201 is symmetrically provided with a first radial hole 210 and a second radial hole 211, the third annular oil passage 205 is symmetrically provided with a third radial hole 206 and a sixth radial hole 215, the rotary valve element 2 is internally provided with a second axial hole 207 and a first axial hole 208, one end of the first annular oil passage 201 is communicated with the third annular oil passage 205 through the first radial hole 210, the first axial hole 208 and the sixth radial hole 215, and the other end of the first annular oil passage 201 is communicated with the third annular oil passage 205 through the second radial hole 211, the second axial hole 207 and the third radial hole 206. The ends of the second axial hole 207 and the first axial hole 208 are provided with process plugs 8 to prevent leakage.

The second annular oil passage 204 is provided with a fourth radial hole 213, a third axial hole 209 and a fifth radial hole 212 are further formed in the rotary valve core 2, a leakage oil passage 214 is formed between the bearing I3 and the rotary seal 7, and the second annular oil passage 204 is communicated with the leakage oil passage 214 through the fourth radial hole 213, the third axial hole 209 and the fifth radial hole 212. Leaked oil between the first bearing 3 and the rotary seal 7 returns to the oil tank through the fifth radial hole 212, the third axial hole 209, the fourth radial hole 213, the second annular oil duct 204 and the oil port T of the valve body 1, so that the phenomenon that the leaked oil for lubricating the bearings on the two sides forms high pressure due to oil trapping is avoided.

The first annular oil duct 201 in the rotary valve core 2 is communicated with the oil port P, the second annular oil duct 204 is communicated with the oil port T, the oil ports a and B are distributed on the valve body 1, and the distribution angle between the oil ports a and B is The other portions are the same as in examples 1 to 4.

The working principle of the embodiment is as follows:

pressure oil enters the first annular oil duct 201 and the first axial oil groove 202 through an oil port P of the valve body 1, part of the pressure oil enters the third annular oil duct 205 through the first radial hole 210, the second radial hole 211, the first axial hole 208, the second axial hole 207, the sixth radial hole 215 and the third radial hole 206, the pressure oil in the third annular oil duct 205 forms static pressure support, and meanwhile leaks into the second annular oil duct 204 and a leakage oil passage 214 between the bearing I3 and the rotary seal 7 through a fit clearance between the valve body 1 and the rotary valve core 2, so that a lubricating oil film between the rotary valve core 2 and the valve body 1 is formed on one hand, and lubrication is provided for the bearing I3 on the other hand; meanwhile, the pressure oil in the first annular oil passage 201 leaks to flow to the second bearing 10 on the left side through the fit clearance between the rotary valve element 2 and the valve body 1, so that lubrication is provided. And lubricating leakage oil of the second bearing 10 returns to the oil tank through the third axial hole 209, the fourth radial hole 213, the second annular oil passage 204 and the oil port T of the valve body 1.

When the rotary valve core 2 rotates a certain angle (as shown in the left diagram of fig. 11, wherein three black filled parts are high pressure oil, and three blank parts are low pressure oil), the pressure oil is communicated to the oil port a of the valve body 1 through the oil port P of the valve body 1, the first annular oil passage 201 of the rotary valve core 2, and the first axial oil groove 202 to form P, A; at this time, the oil port B of the valve body 1 is communicated with the oil port T of the valve body 1 through the second axial oil groove 217 of the rotary valve core 2 and the second annular oil passage 204 to form B, T.

When the rotary valve core 2 rotates a certain angle (as shown in the middle bit map of fig. 12), the pressure oil is led to the oil port a of the valve body 1 through the throttling action of the oil port P of the valve body 1, the first annular oil channel 201, the first axial oil groove 202 and the first oil groove 203 of the rotary valve core 2, so that P, A intercommunication is formed; meanwhile, the pressure oil is led to the oil port A of the valve body 1 through the throttling action of the oil port P of the valve body 1, the first annular oil channel 201 of the rotary valve core 2, the first axial oil groove 202 and the first oil groove 203, so that P, B intercommunication is formed.

At this time, the oil port B of the valve body 1 is communicated with the oil port T of the valve body 1 through the second oil groove 218, the second axial oil groove 217 and the second annular oil channel 204 of the rotary valve core 2 to form B, T; meanwhile, an oil port A of the valve body 1 is communicated with an oil port T of the valve body 1 through ｃA second oil groove 218, ｃA second axial oil groove 217 and ｃA second annular oil channel 204 of the rotary valve core 2 to form B, T, so that P-A-B-T communication is formed in the middle position, and an H-type function is formed.

When the rotary valve core 2 rotates a certain angle (as shown in the right side view of fig. 13), the pressure oil is led to the oil port B of the valve body 1 through the oil port P of the valve body 1, the first annular oil passage 201 of the rotary valve core 2 and the first axial oil groove 202 to form P, B intercommunication; at this time, the oil port a of the valve body 1 is communicated with the oil port T of the valve body 1 through the second axial oil groove 217 of the rotary valve core 2 and the second annular oil passage 204 to form A, T.

As shown in fig. 14, when the rotary valve core 2 rotates one cycle, P/a communication is generated n times (B/T communication n times) (n is the number of the first axial oil grooves 202), P/a cut is generated n times (B/T cut n times), P/B communication is generated n times (a/T communication n times) (n is the number of the second axial oil grooves 217), that is, a/B port is generated and pressure oil is output n times; when the rotating speed of the rotary valve core 2 is changed, the on-off times of P/A/B/T can be changed, high-frequency opening and closing are realized, and the frequency is adjustable. The P/A/B/T is H-shaped, and gradually changes in the opening and closing process of the oil port, so that the impact of instantaneous opening and closing is reduced.