Hydraulic system with adjustable frequency and impact force

Abstract

The invention discloses a hydraulic system with adjustable frequency and impact force, which belongs to the technical field of engineering machinery. It solves the defect of difficulty in adjusting the vibration eccentricity of the exciting force of the hammer head of a conventional pile driver in the prior art. Its main structure includes a pressure adjustable system, a reversing hydraulic valve, an actuator and a driving device. The pressure adjustable system is connected to the actuator through the reversing hydraulic valve, and the rotating end of the reversing hydraulic valve is connected to the driving device. The invention is mainly used in engineering machinery such as pile drivers.

Description

Technical field:

[0001] The invention belongs to the technical field of engineering machinery, and in particular, relates to a hydraulic system with adjustable frequency and impact force. Background technology:

[0002] The pile driver modified based on the crawler excavator uses the high-speed rotation of the hammer eccentric mechanism to generate periodic exciting force, thereby generating high-frequency vibration, and transmits the vibration to the pile body through the hammer clamping part. As the vibration is generated, the soil structure around the pile changes due to the vibration, the soil around the pile body liquefies, the structure between the soil particles becomes disordered, the instantaneous strength decreases, and the soil structure "fluidizes", thereby reducing the friction between the pile and the soil. The pile is then pressed into the soil by the combined force of the excavator's downforce, the pile driver and the pile's own weight.

[0003] The exciting force of this hammer is related to the eccentricity of the vibrating eccentric mechanism and the speed of the vibrating eccentric shaft, that is, when the eccentricity of the eccentric mechanism is constant, the exciting force is related to the speed of the vibrating eccentric shaft (that is, the vibration frequency). If the exciting force is changed, the vibration frequency must be reduced. Therefore, the exciting force and frequency cannot be controlled independently. When the vibration frequency remains unchanged, the eccentricity of the vibrating mechanism must be changed to change the exciting force. In actual operation, it is difficult to adjust the vibration eccentricity, and the labor intensity is relatively high. Summary of the invention:

[0004] The technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide a hydraulic system with adjustable frequency and impact force, which can change the on and off of the reversing hydraulic valve, the speed change, and the number of on and off times change accordingly, thereby achieving adjustable frequency.

[0005] In order to achieve the above object, the present invention is implemented by adopting the following technical solutions:

[0006] A frequency and impact force adjustable hydraulic system comprises a pressure adjustable system, a reversing hydraulic valve, an actuator and a driving device. The pressure adjustable system is connected to the actuator through the reversing hydraulic valve, and the rotating end of the reversing hydraulic valve is connected to the driving device.

[0007] Preferably, the adjustable pressure system includes a working pump B, a proportional relief valve, a first speed regulating valve, a one-way valve and a unloading valve, the working pump B is connected to the proportional relief valve, the one-way valve and the unloading valve respectively, the one-way valve is connected to the reversing hydraulic valve through the first speed regulating valve and an accumulator is connected in parallel between the first speed regulating valve and the reversing hydraulic valve, and the driving device is a motor.

[0008] Preferably, the adjustable pressure system includes a variable pump B, a proportional overflow valve, a one-way valve and a unloading valve, the variable pump B is connected to the proportional overflow valve, the one-way valve and the unloading valve respectively, the one-way valve is connected to the reversing hydraulic valve and an accumulator is connected in parallel between the one-way valve and the reversing hydraulic valve, and the driving device is a motor.

[0009] Preferably, the hydraulic system with adjustable frequency and impact force also includes a frequency adjustable system, which includes a relief valve, a working pump A and a second speed regulating valve, and the driving device is a motor. The working pump A is respectively connected to the relief valve and the second speed regulating valve, and the second speed regulating valve is connected to the motor; the pressure adjustable system includes a working pump B, a proportional relief valve, a first speed regulating valve, a check valve and a unloading valve, and the working pump B is respectively connected to the proportional relief valve, the check valve and the unloading valve, and the check valve is connected to the reversing hydraulic valve through the first speed regulating valve, and an accumulator is connected in parallel between the first speed regulating valve and the reversing hydraulic valve.

[0010] Preferably, the hydraulic system with adjustable frequency and impact force also includes an adjustable frequency system, the adjustable frequency system includes a variable pump A and a relief valve, the driving device is a motor, the variable pump A is connected to the relief valve and the motor respectively, the adjustable pressure system includes a variable pump B, a proportional relief valve, a one-way valve and an unloading valve, the variable pump B is connected to the proportional relief valve, the one-way valve and the unloading valve respectively, the one-way valve is connected to the reversing hydraulic valve and an accumulator is connected in parallel between the one-way valve and the reversing hydraulic valve.

[0011] Preferably, the reversing hydraulic valve includes a valve body, which is provided with oil port A, oil port B, oil port P and oil port T. A rotating valve core is provided in the valve body, and the rotating valve core is connected to the valve body through an end cover. Bearing 1 and bearing 2 are provided between the rotating valve core and the valve body. A driving device is provided on the end cover, and the driving shaft of the driving device is connected to the rotating valve core.

[0012] Preferably, two process holes are provided at one end of the valve body, and static seal 2 and screw plugs are installed on the process holes; a baffle is provided on the outer side of the end cover, and the baffle is connected to the end cover by screw A, a static seal 1 is provided between the valve body and the end cover, and a rotary seal is provided between the rotary valve core and the end cover.

[0013] Preferably, the rotating valve core is provided with a first annular oil channel, a second annular oil channel and a third annular oil channel, and two or more first axial oil grooves and two or more second axial oil grooves are evenly distributed around the periphery of the rotating valve core, the first axial oil grooves and the second axial oil grooves are alternately distributed, the first oil grooves are symmetrically arranged on both sides of the first axial oil groove, the second oil grooves are symmetrically arranged on both sides of the second axial oil groove, the first annular oil channel is connected to the first axial oil groove, and the second annular oil channel is connected to the second axial oil groove.

[0014] Preferably, a first balancing groove and a second balancing groove are provided on the rotary valve core, and the first balancing groove is connected to the first annular oil channel through a first axial oil groove.

[0015] Preferably, the first annular oil channel is symmetrically provided with a first radial hole and a second radial hole, the third annular oil channel is symmetrically provided with a third radial hole and a sixth radial hole, a second axial hole and a first axial hole are provided inside the rotary valve core, one end of the first annular oil channel is connected to the third annular oil channel through the first radial hole, the first axial hole and the sixth radial hole, and the other end of the first annular oil channel is connected to the third annular oil channel through the second radial hole, the second axial hole and the third radial hole.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] 1. The present invention drives the reversing hydraulic valve to rotate by a motor or an electric machine, thereby changing the on and off of the reversing hydraulic valve, the speed changes, and the number of on and off times changes accordingly, thereby realizing frequency adjustment. Since the rotation speed is much higher than the axial speed of the ordinary slide valve, high-frequency on and off can be realized, and the opening frequency of the reversing hydraulic valve is used to control the periodic frequency movement of the actuator, and the set pressure of the system is controlled to control the pressure value at the impact end, so as to realize the impact end force adjustment, and realize the frequency and impact force adjustment;

[0018] 2. The proportional relief valve can adjust the system pressure, thereby combining with the high-frequency on-off of the reversing hydraulic valve to form the output of high-frequency pulses of adjustable pressure oil. Combined with the actuator, a high-frequency pulse hydraulic system with adjustable frequency and pulse force is realized. It has a simple structure and low cost. It can be widely used in pulse tests of hydraulic pipelines and hydraulic cylinders or combined with other actuators for high-frequency pulse vibration.

[0019] 3. High-frequency opening and closing control can be achieved through the reversing hydraulic valve, which solves the disadvantage of the complexity of the high-frequency opening and closing axial motion control of the slide valve. The rotary valve core and the valve body are connected by a bearing to solve the disadvantage of the high-frequency axial motion of the slide valve or the friction between the valve core and the housing of the rotary valve. It has a simple structure and low cost.

[0020] 4. The bearing is lubricated by the leakage of pressure oil. At the same time, the pressure oil forms a lubricating oil film between the rotating valve core and the valve body. The pressure oil in the axial groove and the pressure oil in the annular channel can play the role of static pressure bearing balance support for the rotating valve core. Description of the drawings:

[0021] Figure 1 This is a hydraulic principle diagram of Example 1 of the present invention;

[0022] Figure 2 This is a hydraulic principle diagram of Example 2 of the present invention;

[0023] Figure 3This is a hydraulic principle diagram of Example 3 of the present invention;

[0024] Figure 4 This is a hydraulic principle diagram of Example 4 of the present invention;

[0025] Figure 5 It is a structural schematic diagram of the reversing hydraulic valve in the present invention;

[0026] Figure 6 A top view of the reversing hydraulic valve of the present invention;

[0027] Figure 7 It is a front view of the reversing hydraulic valve in the present invention;

[0028] Figure 8 It is a structural schematic diagram of the rotary valve core in the present invention;

[0029] Fig. 9 for Figure 6 Sectional view of AA in the middle;

[0030] Fig.10 for Figure 7 Cross-sectional view of the middle BB;

[0031] Fig.11 for Figure 6 Cross-sectional view of CC (left view);

[0032] Fig.12 for Figure 6 Cross-sectional view of the middle CC (median view);

[0033] Fig.13 for Figure 6 Cross-sectional view of the middle CC (right view);

[0034] Fig.14 for Figure 6 Cross-sectional view of the CC (center-right position switching).

[0035] In the figure: 1. valve body; 2. rotary valve core; 3. bearing 1; 4. static seal 1; 5. end cover; 6. screw A; 7. rotary seal; 8. process plug; 9. baffle; 10. bearing 2; 11. static seal 2; 12. screw plug; 13. screw B; 14. drive device; 15. relief valve; 16. working pump A; 17. working pump B; 18. proportional relief valve; 19. first speed regulating valve; 20. reversing hydraulic valve; 21. actuator; 22. motor; 23. accumulator; 24. check valve; 25. second speed regulating valve; 26. unloading valve; 27. variable pump A; 28. variable pump B ; 101, process hole; 201, first annular oil channel; 202, first axial oil groove; 203, first oil groove; 204, second annular oil channel; 205, third annular oil channel; 206, third radial hole; 207, second axial hole; 208, first axial hole; 209, third axial hole; 210, first radial hole; 211, second radial hole; 212, fifth radial hole; 213, fourth radial hole; 214, leakage oil channel; 215, sixth radial hole; 217, second axial oil groove; 218, second oil groove; 219, first balancing groove; 220, second balancing groove. Specific implementation method:

[0036] The present invention will be further described below through specific embodiments in conjunction with the accompanying drawings.

[0037] Embodiment 1:

[0038] like Figure 1 As shown, a frequency and impact force adjustable hydraulic system includes a pressure adjustable system, a reversing hydraulic valve 20, an actuator 21 and a drive device 14, wherein the pressure adjustable system is connected to the actuator 21 through the reversing hydraulic valve 20, and the rotating end of the reversing hydraulic valve 20 is connected to the drive device 14. The pressure adjustable system includes a working pump B17, a proportional relief valve 18, a first speed regulating valve 19, a check valve 24 and an unloading valve 26, wherein the working pump B17 is connected to the proportional relief valve 18, the check valve 24 and the unloading valve 26 respectively, the check valve 24 is connected to the reversing hydraulic valve 20 through the first speed regulating valve 19, and an accumulator 23 is connected in parallel between the first speed regulating valve 19 and the reversing hydraulic valve 20, and the drive device 14 is a motor 22.

[0039] Embodiment 2:

[0040] like Figure 2As shown, a hydraulic system with adjustable frequency and impact force, the adjustable pressure system includes a variable pump B28, a proportional relief valve 18, a one-way valve 24 and a unloading valve 26, the variable pump B28 is connected to the proportional relief valve 18, the one-way valve 24 and the unloading valve 26 respectively, the one-way valve 24 is connected to the reversing hydraulic valve 20 and an accumulator 23 is connected in parallel between the one-way valve 24 and the reversing hydraulic valve 20, and the driving device 14 is a motor 22.

[0041] Embodiment 3:

[0042] like Figure 3 As shown, a hydraulic system with adjustable frequency and impact force, the hydraulic system with adjustable frequency and impact force also includes a frequency adjustable system, the frequency adjustable system includes a relief 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 respectively connected to the relief valve 15 and the second speed regulating valve 25, and the second speed regulating valve 25 is connected to the motor; the pressure adjustable system includes a working pump B17, a proportional relief valve 18, a first speed regulating valve 19, a check valve 24 and a unloading valve 26, the working pump B17 is respectively connected to the proportional relief valve 18, the check valve 24 and the unloading valve 26, the check valve 24 is connected to the reversing hydraulic valve 20 through the first speed regulating valve 19, and an accumulator 23 is connected in parallel between the first speed regulating valve 19 and the reversing hydraulic valve 20. The overflow valve 15 is a pressure setting protection for the frequency adjustable system, and the second speed regulating valve 25 adjusts the flow input to the motor, thereby controlling the speed of the motor, thereby achieving adjustable opening and closing times of the reversing hydraulic valve 20 and achieving high frequency opening and closing.

[0043] When not working, the pressure oil output by the working pump B17 is unloaded through the unloading valve 26, which can reduce energy loss; when working, the solenoid valve of the unloading valve 26 is energized, the unloading valve 26 is closed, and the pressure oil output by the working pump B17 is output to the actuator 21 through the one-way valve 24, the first speed regulating valve 19, the accumulator 23, and the reversing hydraulic valve 20. The proportional relief valve 18 can adjust the system pressure, so that the pressure of the actuator 21 can be adjusted. The one-way valve 24 prevents the pressure change shock during the operation of the reversing hydraulic valve 20 and the actuator 21 from being transmitted to the working pump B17, thereby protecting the working pump B17. The accumulator 23 absorbs the pressure fluctuations in the pressure adjustable system circuit and eliminates the peak value. The first speed regulating valve 19 adjusts the system flow to ensure the flow demand during the high-frequency movement of the actuator 21.

[0044] During operation, the motor drives the reversing hydraulic valve 20 to open and close at a high frequency. The working pump B17 opens and closes the output pulse pressure oil through the reversing hydraulic valve 20. The proportional relief valve 18 can adjust the pressure of the pulse pressure oil. By changing the rotation speed of the reversing hydraulic valve 20 (ie the motor speed) and the working pressure of the proportional relief valve 18, the output pressure and frequency can be variable, thereby achieving the output of variable high-frequency pulse force.

[0045] Embodiment 4:

[0046] like Figure 4 As shown, a frequency and impact force adjustable hydraulic system, the frequency and impact force adjustable hydraulic system also includes a frequency adjustable system, the frequency adjustable system includes a variable pump A27 and a relief valve 15, the drive device 14 is a motor, the variable pump A27 is connected to the relief valve 15 and the motor respectively, the pressure adjustable system includes a variable pump B28, a proportional relief valve 18, a check valve 24 and an unloading valve 26, the variable pump B28 is connected to the proportional relief valve 18, the check valve 24 and the unloading valve 26 respectively, 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. By adjusting the swash plate angle of the variable pump A27 and the variable pump B28 to control the output flow, and then control the speed of the driving motor, the opening and closing frequency of the reversing hydraulic valve 20 is adjusted and the action flow requirement of the actuator 21 is met, and compared with embodiment 3, the first speed regulating valve 19 and the second speed regulating valve 25 are saved.

[0047] Embodiment 5:

[0048] like Figure 5-10 As shown, a hydraulic system with adjustable frequency and impact force, the reversing hydraulic valve 20 includes a valve body 1, the valve body 1 is provided with oil ports A, B, P and T, a rotary valve core 2 is provided in the valve body 1, the rotary valve core 2 is connected to the valve body 1 through an end cover 5, a bearing 1 3 and a bearing 2 10 are provided between the rotary valve core 2 and the valve body 1, the end cover 5 is provided with a driving device 14, and the driving shaft of the driving device 14 is connected to the rotary valve core 2.

[0049] One end of the valve body 1 is provided with two process holes 101 , on which a static seal 11 and a screw plug 12 are installed. The process holes 101 are used for disassembly of the bearing 10 .

[0050] A baffle plate 9 is provided on the outer side of the end cover 5, and the baffle plate 9 is connected to the end cover 5 by screws A6. A static seal 4 is provided between the valve body 1 and the end cover 5, a rotary seal 7 is provided between the rotary valve core 2 and the end cover 5, and the valve body 1 and the end cover 5 are connected by screws B13.

[0051] The rotary valve core 2 is provided with a first annular oil passage 201, a second annular oil passage 204 and a third annular oil passage 205. Two or more first axial oil grooves 202 and two or more second axial oil grooves 217 are uniformly distributed around 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 passage 201 is connected to the first axial oil groove 202, and the second annular oil passage 204 is connected to the second axial oil groove 217. At this time, the reversing hydraulic valve 20 is an O-type function.

[0052] The first oil grooves 203 are symmetrically arranged on both sides of the first axial oil groove 202, and the second oil grooves 218 are symmetrically arranged on both sides of the second axial oil groove 217. By adding the first oil grooves 203 and the second oil grooves 218, the reversing hydraulic valve 20 has an H-type function.

[0053] The rotary valve core 2 is provided with a first balancing groove 219 and a second balancing groove 220 . The first balancing groove 219 is connected to the first annular oil passage 201 through the first axial oil groove 202 .

[0054] 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 core 2 is provided with a second axial hole 207 and a first axial hole 208, one end of the first annular oil passage 201 is connected to 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 connected to the third annular oil passage 205 through the second radial hole 211, the second axial hole 207 and the third radial hole 206. Process plugs 8 are provided at the ends of the second axial hole 207 and the first axial hole 208 to prevent leakage.

[0055] The second annular oil passage 204 is provided with a fourth radial hole 213, the interior of the rotary valve core 2 is also provided with a third axial hole 209 and a fifth radial hole 212, a leakage oil passage 214 is provided between the bearing 1 3 and the rotary seal 7, and the second annular oil passage 204 is connected with the leakage oil passage 214 through the fourth radial hole 213, the third axial hole 209, and the fifth radial hole 212. The leaked oil between the bearing 1 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 passage 204, and the oil port T of the valve body 1, so as to avoid the high pressure phenomenon caused by the trapped oil of the lubricating oil of the bearings on both sides.

[0056] The first annular oil passage 201 in the rotary valve core 2 is connected to the oil port P, the second annular oil passage 204 is connected to the oil port T, the oil port A and the oil port B are distributed on the valve body 1, and the distribution angle between the oil port A and the oil port B is The other parts are the same as those of Example 1-4.

[0057] The working principle of this embodiment is:

[0058] The pressure oil enters the first annular oil passage 201 and the first axial oil groove 202 through the oil port P of the valve body 1, and part of the pressure oil enters the third annular oil passage 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 passage 205 forms a static pressure support, and at the same time leaks through the matching clearance between the valve body 1 and the rotating valve core 2 to the second annular oil passage 204, the leakage oil channel 214 between the bearing 1 3 and the rotating seal 7, on the one hand, forming a lubricating oil film between the rotating valve core 2 and the valve body 1, and on the other hand, providing lubrication for the bearing 1 3; at the same time, the pressure oil in the first annular oil passage 201 leaks through the matching clearance between the rotating valve core 2 and the valve body 1 to flow to the left bearing 2 10 to provide lubrication. The lubricating oil leakage of the bearing 2 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.

[0059] When the rotary valve core 2 rotates a certain angle (such as Fig.11 As shown in the left diagram, the three black filled parts are high-pressure oil, and the three blank parts are low-pressure oil), the pressure oil passes through the oil port P of the valve body 1, the first annular oil passage 201 of the rotating valve core 2, and the first axial oil groove 202 to the oil port A of the valve body 1, forming a connection between P and A; at this time, the oil port B of the valve body 1 passes through the second axial oil groove 217 of the rotating valve core 2 and the second annular oil passage 204 to the oil port T of the valve body 1, forming a connection between B and T.

[0060] When the rotary valve core 2 rotates a certain angle (such as Fig.12 As shown in the middle diagram, the pressure oil passes through the oil port P of the valve body 1, the first annular oil passage 201 of the rotating valve core 2, the first axial oil groove 202, and the throttling effect of the first oil groove 203 to the oil port A of the valve body 1, forming a communication between P and A; at the same time, the pressure oil passes through the oil port P of the valve body 1, the first annular oil passage 201 of the rotating valve core 2, the first axial oil groove 202, and the throttling effect of the first oil groove 203 to the oil port A of the valve body 1, forming a communication between P and B.

[0061] At this time, the oil port B of the valve body 1 is connected to 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 passage 204 of the rotating valve core 2, forming a connection between B and T; at the same time, the oil port A of the valve body 1 is connected to 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 passage 204 of the rotating valve core 2, forming a connection between B and T, so that PABT is connected in the middle position, forming an H-type function.

[0062] When the rotary valve core 2 rotates a certain angle (such as Fig.13As shown in the right diagram, the pressure oil passes through the oil port P of the valve body 1, the first annular oil passage 201 of the rotating valve core 2, and the first axial oil groove 202 to the oil port B of the valve body 1, forming a connection between P and B; at this time, the oil port A of the valve body 1 passes through the second axial oil groove 217 of the rotating valve core 2 and the second annular oil passage 204 to the oil port T of the valve body 1, forming a connection between A and T.

[0063] like Fig.14 As shown, when the rotary valve core 2 rotates one circle, P / A will be connected n times (B / T will be connected n times) (n is the number of the first axial oil grooves 202), P / A will be cut off n times (B / T will be cut off n times), P / B will be connected n times (A / T will be connected n times) (n is the number of the second axial oil grooves 217), that is, the A / B port will output n times of pressure oil; when the rotation speed of the rotary valve core 2 is changed, the number of P / A / B / T on and off can be changed to achieve high-frequency opening and closing, and the frequency is adjustable. P / A / B / T is an H-type function, which gradually changes during the opening and closing process of the oil port to reduce the impact of instantaneous opening and closing.

Claims

1. A frequency and impact force adjustable hydraulic system, comprising a pressure adjustable system, a reversing hydraulic valve (20), an actuator (21) and a drive device (14), wherein the pressure adjustable system is connected to the actuator (21) via the reversing hydraulic valve (20), and the rotating end of the reversing hydraulic valve (20) is connected to the drive device (14); the reversing hydraulic valve (20) comprises a valve body (1), the valve body (1) is provided with oil ports A, B, P and T, a rotary valve core (2) is provided in the valve body (1), the rotary valve core (2) is connected to the valve body (1) via an end cover (5), a bearing 1 (3) and a bearing 2 (10) are provided between the rotary valve core (2) and the valve body (1), the end cover (5) is provided with a drive device (14), and the drive shaft of the drive device (14) is connected to the rotary valve core (2); characterized in that: The rotary valve core (2) is provided with a first annular oil passage (201), a second annular oil passage (204) and a third annular oil passage (205); two or more first axial oil grooves (202) and two or more second axial oil grooves (217) are evenly distributed around the rotary valve core (2); the first axial oil grooves (202) and the second axial oil grooves (217) are alternately distributed; first oil grooves (203) are symmetrically provided on both sides of the first axial oil groove (202); second oil grooves (218) are symmetrically provided on both sides of the second axial oil groove (217); the first annular oil passage (201) is in communication with the first axial oil groove (202); and the second annular oil passage (204) is in communication with the second axial oil groove (217); the reversing hydraulic valve (20) is of H-type function; The rotary valve core (2) is provided with a first balancing groove (219) and a second balancing groove (220), and the first balancing groove (219) is connected to the first annular oil passage (201) through a first axial oil groove (202).

2. The frequency and impact force adjustable hydraulic system according to claim 1, characterized in that: The adjustable pressure system comprises a working pump B (17), a proportional relief valve (18), a first speed regulating valve (19), a check valve (24) and a relief valve (26); the working pump B (17) is connected to the proportional relief valve (18), the check valve (24) and the relief valve (26) respectively; the check valve (24) is connected to a reversing hydraulic valve (20) via the first speed regulating valve (19); an accumulator (23) is connected in parallel between the first speed regulating valve (19) and the reversing hydraulic valve (20); and the driving device (14) is a motor (22).

3. The frequency and impact force adjustable hydraulic system according to claim 1, characterized in that: The pressure adjustable system comprises a variable pump B (28), a proportional relief valve (18), a check valve (24) and a relief valve (26); the variable pump B (28) is connected to the proportional relief valve (18), the check valve (24) and the relief valve (26) respectively; the check valve (24) is connected to 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).

4. The frequency and impact force adjustable hydraulic system according to claim 1, characterized in that: The frequency and impact force adjustable hydraulic system also includes a frequency adjustable system, the frequency adjustable system includes a relief 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 connected to the relief 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 includes a working pump B (17), a proportional relief valve (18), a first speed regulating valve (19), a check valve (24) and a unloading valve (26), the working pump B (17) is connected to the proportional relief valve (18), the check valve (24) and the unloading valve (26) respectively, the check valve (24) is connected to the reversing hydraulic valve (20) through the first speed regulating valve (19), and an accumulator (23) is connected in parallel between the first speed regulating valve (19) and the reversing hydraulic valve (20).

5. The frequency and impact force adjustable hydraulic system according to claim 1, characterized in that: 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 a relief valve (15), the driving device (14) is a motor, the variable pump A (27) is respectively connected to the relief valve (15) and the motor, the pressure adjustable system comprises a variable pump B (28), a proportional relief valve (18), a check valve (24) and a unloading valve (26), the variable pump B (28) is respectively connected to the proportional relief 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).

6. The frequency and impact force adjustable hydraulic system according to any one of claims 1 to 5, characterized in that: One end of the valve body (1) is provided with two process holes (101), and static seals (11) and screw plugs (12) are installed on the process holes (101); a baffle (9) is provided on the outer side of the end cover (5), and the baffle (9) is connected to the end cover (5); a static seal (4) is provided between the valve body (1) and the end cover (5); and a rotary seal (7) is provided between the rotary valve core (2) and the end cover (5).

7. The frequency and impact force adjustable hydraulic system according to claim 6, characterized in that: 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); a second axial hole (207) and a first axial hole (208) are provided inside the rotary valve core (2); one end of the first annular oil passage (201) is connected to the third annular oil passage (205) through the first radial hole (210), the first axial hole (208) and the sixth radial hole (215); the other end of the first annular oil passage (201) is connected to the third annular oil passage (205) through the second radial hole (211), the second axial hole (207) and the third radial hole (206).

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