Sine-type excitation rotary valve

Abstract

This invention discloses a sinusoidal excitation rotary valve, comprising a left end cover A, a left end cover B, a rotary valve core, a sliding valve core, a valve sleeve, a valve body, a right end cover A, and a right end cover B. The left end cover B and the right end cover A are fixed to both ends of the valve body, respectively. Left end cover A and right end cover B are respectively disposed on the outer sides of the left end cover B and the right end cover A. An axially oriented inner hole is formed inside the valve body, and a valve sleeve that rotates circumferentially along the inner hole is disposed within the inner hole. A double-layer valve core is installed within the valve sleeve, comprising a sliding valve core that slides axially along the valve body and a rotary valve core disposed within the sliding valve core. The double-layer valve core design of this invention reduces the valve volume while allowing separate control of amplitude and frequency. The sinusoidal guide groove design forces the sliding valve core to reciprocate, and as the rotational speed of the rotary valve core increases, there is no valve attenuation of the sliding valve core.

Description

Technical Field

[0001] This invention belongs to the field of electro-hydraulic excitation technology, and specifically relates to a sinusoidal excitation rotary valve. Background Technology

[0002] Vibration is one of the most common phenomena in nature. Various forms of physical phenomena, including sound, light, and heat, all involve vibration. In the industrial sector, vibration can cause a series of serious problems. Long-term vibration not only accelerates the wear and tear of equipment and mechanical parts, affecting equipment lifespan and reliability, but also increases energy consumption and reduces operational accuracy and stability. Furthermore, vibration can lead to fatigue failure of building or mechanical structures, such as the 1940 collapse of the Tacoma Narrows Bridge suspension cables in the United States. Despite the problems that vibration can cause in industry, it also has its positive aspects. Vibration sensors can be used for equipment monitoring and fault diagnosis, improving reliability and efficiency; vibrating screening equipment can improve production efficiency and product quality; vibrating cutting technology can achieve high precision and efficiency in material processing; vibration transmission and mixing equipment can be used for material conveying and mixing; vibration energy utilization technology can convert vibration into electrical energy for power supply or storage. Therefore, in the industrial sector, the rational utilization and control of vibration can also bring a series of positive applications and effects, such as improving production efficiency, reducing energy consumption, and improving product quality.

[0003] Vibrators are key components in machinery and equipment, used to generate mechanical vibrations. They play a crucial role in vibration and strength testing of objects, as well as in the calibration of vibration testing instruments and sensors. Based on the type of excitation, vibrators are classified into electric, electromagnetic, mechanical, and electro-hydraulic types. Electric vibrators utilize the motion of a charged conductor in a magnetic field to generate vibration; they are simple and low-cost, but have a relatively short lifespan. Electromagnetic vibrators use a pulsating voltage generated by half-wave rectification to act on a coil, producing electromagnetic force to drive vibration; the waveform is relatively accurate, but the amplitude is small. Mechanical vibrators have relatively small output thrust and amplitude, suitable for low-frequency vibration experiments. Electro-hydraulic vibrators have a robust structure, high upper limit of thrust, large amplitude and high frequency, can be automatically programmed and loaded, and their waveforms are less prone to distortion, thus possessing significant research value.

[0004] Due to bandwidth limitations, traditional servo valves struggle to achieve high-frequency output. Furthermore, traditional hydraulic servo valves have complex structures, high manufacturing costs, and stringent tolerance requirements. The forces acting on the rotating valve core are numerous, large, and variable, demanding significant control force. When used as a pre-stage valve, their dynamic response is low, and during high-frequency operation, the output amplitude fluctuates considerably, resulting in substantial energy loss. Summary of the Invention

[0005] To overcome the aforementioned technical problems in the existing technology, the present invention provides a sinusoidal excitation rotary valve, which has a simple overall structure, stable working performance, and large output flow.

[0006] The technical solution adopted in this invention is:

[0007] A sinusoidal excitation rotary valve is characterized by comprising a left end cover A (1), a left end cover B (5), a rotary valve core (6), a sliding valve core (7), a valve sleeve (9), a valve body (10), a right end cover A (11), and a right end cover B (15); the two ends of the valve body (10) are respectively fixed with the left end cover B (5) and the right end cover A (11), and the outer sides of the left end cover B (5) and the right end cover A (11) are respectively arranged with the left end cover A (1) and the right end cover B (15); the valve body (10) has an axially formed opening inside. An inner hole is provided in which a valve sleeve (9) is rotated circumferentially along the inner hole of the valve body (10). A double-layer valve core is installed in the valve sleeve (9). The double-layer valve core includes a sliding valve core (7) that slides axially along the valve body (10) and a rotating valve core (6) disposed in the sliding valve core (7). The sliding valve core (7), the valve sleeve (9), and the valve body (10) cooperate to form an excitation chamber. The rotating valve core (6) rotates and drives the sliding valve core (7) to reciprocate left and right, realizing the switching of the oil circuit on the sliding valve core (7) between position A, middle position, and position B.

[0008] The sliding valve core (7) is provided with a first support shoulder (16), a second shoulder (18), a third shoulder (19), a fourth shoulder (20), and a fifth support shoulder (21) from left to right; the first support shoulder (16) is truncated circular, and the left end cap A (1) has a truncated circular hole on the right side. The truncated circle of the first support shoulder (16) and the truncated circular hole cooperate with each other to prevent the sliding valve core from rotating; the movement range of the first support shoulder (16) is limited to the depth range of the truncated circular hole.

[0009] The left end of the rotary valve core (6) passes through the left end cover B (5) and the left end cover A (1) in sequence. The surface of the rotary valve core (6) is provided with two parallel guide grooves (23). The sliding valve core (7) is provided with a first pin hole (17) that cooperates with the guide groove (23). A guide pin (8) is provided in the first pin hole (17). The guide groove (23) and the guide pin (8) constitute a reciprocating mechanism. When the rotary valve core (6) rotates, the sliding valve core (7) will only move laterally along the inner hole due to the limitation of the forced lateral displacement on the left side.

[0010] Furthermore, the valve sleeve (9) is provided with five sets of windows, which are arranged from left to right as the first return oil window group (24), the first working window group (25), the oil inlet window group (26), the second working window group (27), and the second return oil window group (28). Each window in each window group is evenly distributed around the circumference of the valve sleeve (9). The overlapping area of ​​the window and the oil inlet P port (32) on the valve body (10) forms a variable throttle orifice. By rotating the valve sleeve, the size of the variable throttle orifice is changed to achieve linear control of the oil flow rate entering the valve body (10).

[0011] Furthermore, the bottom of the valve body (10) is provided with an oil drain port T1 (30), an oil drain port T2 (34), an oil inlet port P (32), a working port A (31), and a working port B (33); the lower wall of the valve body (10) is provided with a first oil passage connecting the oil inlet port P (32), and the lower wall of the excitation chamber is provided with a second oil passage connecting the working port A (31) and the excitation chamber, a third oil passage connecting the working port B (33) and the excitation chamber, a fourth oil passage connecting the oil drain port T1 (30) and the excitation chamber, and a fifth oil passage connecting the oil drain port T2 (34) and the excitation chamber.

[0012] Furthermore, the first support shoulder (16) is located in the right limiting hole of the left end cover A (1), the second shoulder (18) has an active range on the left side of the working port A (31), and the third shoulder (19) works near the oil inlet P port (32).

[0013] Furthermore, each of the guide grooves (23) is a sinusoidal guide groove, and the sinusoidal curve corresponding to the sinusoidal guide groove has two cycles. The phase and amplitude of the two guide grooves (23) are the same. The amplitude change of the curve corresponding to the guide groove (23) is matched with the distribution of the shoulder and the relative position of the window on the valve sleeve (9). When the sinusoidal excitation rotary valve completes half a working cycle, the distance the shoulder moves is exactly twice the lateral distance of the window.

[0014] Furthermore, the guide groove (23) can change the number of periods and amplitude of the corresponding sine curve, thereby changing the frequency of switching of the working oil circuit when the rotational speed of the valve core is the same.

[0015] Furthermore, the guide groove (23) can change the shape of the corresponding curve, which can be non-sinusoidal, and the number of curves can be multiple. The distribution position of the guide groove (23) can be changed to improve the working stability of the vibration valve.

[0016] Furthermore, the left end of the rotary valve core (6) is located within the support step formed by the left end cover A (1) and the left end cover B (5). A deep groove ball bearing A (2) is provided on the support step. The deep groove ball bearing A (2) cooperates with the retaining ring A (3) to achieve axial positioning of the rotary valve core (6).

[0017] The right side of the valve sleeve (9) passes through the right end cover A (11) and the right end cover B (15) in sequence. The right end of the valve sleeve (9) is located in the support step formed by the right end cover A (11) and the right end cover B (15). A deep groove ball bearing B (12) is provided on the support step. The deep groove ball bearing B (12) cooperates with the retaining ring B (14) to realize the axial positioning of the valve sleeve (9).

[0018] Furthermore, the retaining ring A (3) and retaining ring B (14) are each provided with a second pin hole. The two second pin holes correspond to the third pin holes at the left end of the sliding valve core (7) and the right end of the valve sleeve (9), respectively, so as to achieve axial fixation and support of the rotating valve core (6) and valve sleeve (9).

[0019] Furthermore, the valve body (10) has threaded holes on both the left and right end faces for fixing the left end cover B (5) and the right end cover A (11), and the left end cover B (5) and the right end cover A (11) are respectively provided with through holes that cooperate with the upper threaded holes; the valve body (10) has a countersunk hole in the middle for connecting with the valve block.

[0020] Furthermore, the first support shoulder (16) and the fifth support shoulder (21) are provided with pressure equalization grooves, and the second shoulder (18), the third shoulder (19) and the fourth shoulder (20) are provided with grooves to reduce friction.

[0021] In this invention, both the left and right end caps are separate end caps, specifically:

[0022] The left end cover is divided into left end cover A and left end cover B. There is a stepped hole on the right side of the left end cover A, and there is a stepped hole on the left side of the left end cover B that is symmetrical to the right side of the left end cover A. The left end cover A and left end cover B are used together. Deep groove ball bearings A are placed near the center of their respective end covers through the stepped holes on both sides, and a retaining ring A is placed in the middle combined part.

[0023] The right end cover is divided into right end cover A and right end cover B. Right end cover A has a stepped hole on the right side, and right end cover B has a stepped hole on the left side that is symmetrical to the right side of right end cover A. Right end cover A and right end cover B are used together. Deep groove ball bearings B are placed near the center of their respective end covers through the stepped holes on both sides, and a retaining ring B is placed in the middle combined part.

[0024] The working principle of the sinusoidal vibration rotary valve of this invention is as follows: A guide groove is provided on the surface of the rotary valve core. Utilizing the rotational motion of the rotary valve core, the sliding valve core can achieve horizontal reciprocating motion, thereby switching the oil circuit. When the valve sleeve rotates axially, the throttling area formed by the oil inlet window group on the valve sleeve and its corresponding oil inlet channel changes, thus adjusting the flow rate entering the vibration rotary valve from the peak flow rate to the minimum steady-state flow rate, achieving flow control. When the rotary valve core rotates, the horizontal reciprocating motion of the sliding valve core along the vibration chamber causes the hydraulic oil channel on the valve sleeve to overlap successively with its corresponding oil inlet channel and oil outlet window. This causes the flow rate at the oil inlet P and the oil outlets A and B on the valve body to undergo periodic alternating changes, resulting in periodic changes in the flow rate in the left and right chambers of the hydraulic cylinder, thereby achieving the periodic reciprocating motion of the hydraulic cylinder and realizing the vibration function. The excitation frequency of the hydraulic cylinder is determined by the reciprocating speed of the sliding valve core, while the amplitude of the excitation is determined by the flow rate entering and exiting the hydraulic cylinder. The flow rate depends on the overlap area between the oil inlet window of the valve sleeve and the P port of the valve body, as well as the overlap time. Therefore, the amplitude and frequency of the vibration can be adjusted by changing the rotation angle of the valve sleeve and the rotation speed of the valve core.

[0025] The valve sleeve of this invention moves as follows: a mechanical device causes the valve sleeve to rotate axially, thereby regulating the high-pressure hydraulic oil entering the inlet P port. The regulated high-pressure hydraulic oil then enters the excitation chamber. The input shaft on the right side of the valve sleeve is connected to a servo motor via a gearbox, sleeve, and other connecting devices. By controlling the frequency and number of pulses received by the servo driver, the rotation of the valve sleeve is controlled, thus achieving flow control.

[0026] The movement of the rotary valve core in this invention is as follows: A motor drives the rotary valve core to rotate, which in turn drives the outer sliding valve core to reciprocate axially. The rotary valve core is connected to a servo motor via a gearbox, sleeve, and other connecting devices. By changing the motor speed, the rotational speed of the rotary valve core is controlled. The rotation of the rotary valve core drives the horizontal reciprocating motion of the sliding valve core. When hydraulic oil enters one side of the hydraulic cylinder piston through the main input channel on the sliding valve core via working port A, the hydraulic cylinder piston moves horizontally. Excess hydraulic oil returns to the oil tank through working port B and the return channel via drain port T2. After the motor drives the rotary valve core to rotate half a cycle, the oil circuit changes. Hydraulic oil enters the other side of the hydraulic cylinder through working port B, causing the hydraulic cylinder to move horizontally in the opposite direction. Excess hydraulic oil returns to the oil tank through the return channel on the valve sleeve and the drain port T1. Because of the sinusoidal reciprocating mechanism between the rotary valve core and the sliding valve core, when the rotary valve core rotates continuously, the valve sleeve reciprocates horizontally along the guide groove on the rotary valve core. The oil inlet switches back and forth between working ports A and B, generating a vibration effect in the hydraulic cylinder. The vibration amplitude depends on the rotation angle of the valve sleeve, and the vibration frequency depends on the rotational speed of the rotary valve core. The vibration characteristics of the vibrating valve can be adjusted by changing the motion of the rotary valve core.

[0027] Compared with the prior art, the beneficial effects of the present invention are reflected in:

[0028] 1. This invention has a high pressure gain, its characteristics are easy to calculate and control, it has good anti-pollution performance, it can realize high-frequency commutation, and it separates the control of flow rate and frequency, which are driven by two motors respectively, thereby improving the stability of frequency and flow control.

[0029] 2. This invention can convert the axial rotation of the shaft into a sinusoidal signal pressure output; the double-layer valve core design can control the amplitude and frequency separately while reducing the valve volume.

[0030] 3. The present invention uses a sinusoidal guide groove design to force the sliding valve core to reciprocate. As the rotation speed of the valve core increases, there will be no valve port attenuation of the sliding valve core.

[0031] 4. The present invention has a simple overall structure, stable working performance, and large output flow. Attached Figure Description

[0032] Figure 1 This is an assembly diagram of the present invention;

[0033] Figure 2 This is a structural schematic diagram of the present invention.

[0034] Figure 3 This is a schematic diagram of the sliding valve core of the present invention;

[0035] Figure 4 This is a schematic diagram of the rotary valve core of the present invention;

[0036] Figure 5 This is a schematic diagram of the valve sleeve of the present invention;

[0037] Figure 6 This is a schematic diagram of the valve body of the present invention;

[0038] Figure 7 This means that the sliding valve core of the present invention is in the working state of port A;

[0039] Figure 8 This is the state in which the sliding valve core of the present invention is in the cut-off position.

[0040] Figure 9 This means that the sliding valve core of the present invention is in the working state of port B;

[0041] Figure 10a This is a structural schematic diagram of the left end cap B of the present invention from the right side view;

[0042] Figure 10b This is a structural schematic diagram of the left end cap B of the present invention from the left side view.

[0043] Figure 11This is a schematic diagram of the retaining ring of the present invention;

[0044] Figure 12 This invention ensures that the valve sleeve is in the state of maximum flow.

[0045] Figure 13 This invention ensures that the valve sleeve is in a state of minimum flow.

[0046] Explanation of reference numerals in the attached drawings: 1. Left end cover A; 2. Deep groove ball bearing A; 3. Retaining ring A; 4. Pin A; 5. Left end cover B; 6. Rotary valve core; 7. Sliding valve core; 8. Guide pin; 9. Valve sleeve; 10. Valve body; 11. Right end cover A; 12. Deep groove ball bearing B; 13. Retaining ring B; 14. Pin B; 15. Right end cover B; 16. First support shoulder; 17. Guide pin hole; 18. Second shoulder; 19. ... 20. Third shoulder; 21. Fourth shoulder; 22. Fifth support shoulder; 23. Pin hole A1; 24. Guide groove; 25. First oil return window group; 26. First working window group; 27. Oil inlet window group; 28. Second working window group; 29. ​​Second oil return window group; 30. Pin hole B; 31. Oil drain hole T1 port; 32. Working A port; 33. Oil inlet P port; 34. Working B port; 35. Oil drain hole T2 port. Detailed Implementation

[0047] The specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for illustration and explanation only and are not intended to limit the scope of the present invention.

[0048] It should be noted that, unless otherwise specified, the embodiments and features described in the present invention can be combined with each other.

[0049] The present invention will now be described in detail with reference to the accompanying drawings and exemplary embodiments.

[0050] refer to Figures 1 to 6The sinusoidal excitation rotary valve of the present invention includes a left end cover A1, a left end cover B5, a rotary valve core 6, a sliding valve core 7, a valve sleeve 9, a valve body 10, a right end cover A11, and a right end cover B15; the left end cover B5 and the right end cover A11 are respectively fixed at both ends of the valve body 10, and the left end cover A1 and the right end cover B15 are respectively disposed on the outer side of the left end cover B5 and the outer side of the right end cover A11; an inner hole is formed axially inside the valve body 10. A valve sleeve 9, which rotates circumferentially along the inner bore of the valve body 10, is disposed within the valve sleeve 9. A double-layer valve core is installed within the valve sleeve 9. The double-layer valve core includes a sliding valve core 7 that slides axially along the valve body 10 and a rotating valve core 6 disposed within the sliding valve core 7. The sliding valve core 7, the valve sleeve 9, and the valve body 10 cooperate to form a vibration chamber. The rotation of the rotating valve core 6 drives the sliding valve core 7 to reciprocate left and right, thereby switching the oil circuit on the sliding valve core 7 between position A, neutral position, and position B. Wherein:

[0051] The sliding valve core 7 is provided with a first support shoulder 16, a second shoulder 18, a third shoulder 19, a fourth shoulder 20 and a fifth support shoulder 21 from left to right; the first support shoulder 16 is truncated circular, and the right side of the left end cover A1 has a truncated circular hole. The truncated circle of the first support shoulder 16 and the truncated circular hole cooperate with each other to prevent the sliding valve core from rotating; the movement range of the first support shoulder 16 is limited to the depth range of the truncated circular hole.

[0052] The left end of the rotary valve core 6 passes through the left end cover B5 and the left end cover A1 in sequence. The surface of the rotary valve core 6 is provided with two parallel guide grooves 23. The sliding valve core 7 is provided with a first pin hole 17 that cooperates with the guide grooves 23. A guide pin 8 is provided in the first pin hole 17. The guide grooves and the guide pins constitute a reciprocating mechanism. When the rotary valve core 6 rotates, the sliding valve core 7 will only move laterally along the inner hole due to the limitation of the forced lateral displacement on the left side.

[0053] Specifically, the oil circuit switching frequency is controlled by rotating the valve core 6, the oil flow rate into the excitation chamber is controlled by rotating the valve sleeve 9, and the cycle of the reciprocating horizontal motion of the sliding valve core 7 is changed by changing the number of periods of the sine curve corresponding to the sine guide groove on the rotating valve core 6 at the same rotating valve core 6 speed; the output curve of the hydraulic excitation valve is changed by changing the curve shape corresponding to the guide groove 23 on the rotating valve core 6.

[0054] In one embodiment, the valve sleeve 9 is provided with five sets of windows, which are arranged from left to right as the first return oil window group 24, the first working window group 25, the inlet oil window group 26, the second working window group 27, and the second return oil window group 28. Each window in each window group is evenly distributed around the circumference of the valve sleeve 9. The overlapping area of ​​the window and the inlet P port 32 on the valve body 10 forms a variable throttle orifice. By rotating the valve sleeve, the size of the variable throttle orifice is changed to achieve linear control of the oil flow rate entering the valve body 10.

[0055] In one embodiment, the bottom of the valve body 10 is provided with an oil drain port T1 30, an oil drain port T2 34, an oil inlet port P 32, a working port A 31, and a working port B 33; the lower wall of the valve body 10 is provided with a first oil passage connecting the oil inlet port P 32, and the lower wall of the excitation chamber is provided with a second oil passage connecting the working port A 31 and the excitation chamber, a third oil passage connecting the working port B 33 and the excitation chamber, a fourth oil passage connecting the oil drain port T1 30 and the excitation chamber, and a fifth oil passage connecting the oil drain port T2 34 and the excitation chamber.

[0056] In one embodiment, the first support shoulder 16 is located in the right limiting hole of the left end cover A1, the second shoulder 18 is movable to the left of the working port A 31, and the third shoulder is located near the oil inlet P port 32.

[0057] In one embodiment, each of the guide grooves 23 is a sinusoidal guide groove, and the sinusoidal curve corresponding to the sinusoidal guide groove has two periods. The phase and amplitude of the two guide grooves 23 are the same. The amplitude change of the curve corresponding to the guide groove 23 is coordinated with the shoulder distribution and the relative position of the window on the valve sleeve 9. When the sinusoidal excitation rotary valve completes half a working cycle, the distance the shoulder moves is exactly twice the lateral distance of the window.

[0058] In one embodiment, the guide groove 23 can change the number of periods and amplitude of the corresponding sine curve, thereby changing the frequency of switching of the working oil circuit when the rotational speed of the valve core is the same.

[0059] In one embodiment, the curve corresponding to the guide groove (23) can change shape and can be non-sinusoidal; the number and position of the curve distribution can be changed to improve the working stability of the rotary valve.

[0060] In one embodiment, the left end of the rotary valve core 6 is located within the support step formed by the left end cover A1 and the left end cover B5. A deep groove ball bearing A2 is provided on the support step. The deep groove ball bearing A2 cooperates with the retaining ring A3 to achieve axial positioning of the rotary valve core 6.

[0061] The right side of the valve sleeve 9 passes through the right end cover A11 and the right end cover B15 in sequence. The right end of the valve sleeve 9 is located in the support step formed by the right end cover A11 and the right end cover B15. A deep groove ball bearing B12 is provided on the support step. The deep groove ball bearing B12 cooperates with the retaining ring B14 to realize the axial positioning of the valve sleeve 9.

[0062] In one embodiment, both the retaining ring A3 and the retaining ring B14 are provided with second pin holes. The two second pin holes correspond to the third pin holes at the left end of the sliding valve core 7 and the right end of the valve sleeve 9, respectively, so as to achieve axial fixation and support of the rotating valve core 6 and the valve sleeve 9.

[0063] In one embodiment, the valve body 10 has threaded holes on both the left and right end faces for fixing the left end cover B5 and the right end cover A11, and the left end cover B5 and the right end cover A11 are respectively provided with through holes that cooperate with the threaded holes; the valve body 10 has a countersunk hole in the middle for connecting with the valve block.

[0064] In one embodiment, the first support shoulder 16 and the fifth support shoulder 21 are each provided with pressure equalization grooves, and the second shoulder 18, the third shoulder 19 and the fourth shoulder 20 are each provided with grooves for reducing friction.

[0065] Both the left and right end caps are separate end caps, specifically:

[0066] The left end cover is divided into left end cover A and left end cover B. There is a stepped hole on the right side of the left end cover A, and there is a stepped hole on the left side of the left end cover B that is symmetrical to the right side of the left end cover A. The left end cover A and left end cover B are used together. Deep groove ball bearings A are placed near the center of their respective end covers through the stepped holes on both sides, and a retaining ring A is placed in the middle combined part.

[0067] The right end cover is divided into right end cover A and right end cover B. Right end cover A has a stepped hole on the right side, and right end cover B has a stepped hole on the left side that is symmetrical to the right side of right end cover A. Right end cover A and right end cover B are used together. Deep groove ball bearings B are placed near the center of their respective end covers through the stepped holes on both sides, and a retaining ring B is placed in the middle combined part.

[0068] The working principle of the sinusoidal vibration rotary valve of this invention is as follows: A guide groove is provided on the surface of the rotary valve core. Utilizing the rotational motion of the rotary valve core, the sliding valve core can achieve horizontal reciprocating motion, thereby switching the oil circuit. When the valve sleeve rotates axially, the throttling area formed by the oil inlet window group on the valve sleeve and its corresponding oil inlet channel changes, thus adjusting the flow rate entering the vibration rotary valve from the peak flow rate to the minimum steady-state flow rate, achieving flow control. When the rotary valve core rotates, the horizontal reciprocating motion of the sliding valve core along the vibration chamber causes the hydraulic oil channel on the valve sleeve to overlap successively with its corresponding oil inlet channel and oil outlet window. This causes the flow rate at the oil inlet P and the oil outlets A and B on the valve body to undergo periodic alternating changes, resulting in periodic changes in the flow rate in the left and right chambers of the hydraulic cylinder, thereby achieving the periodic reciprocating motion of the hydraulic cylinder and realizing the vibration function. The excitation frequency of the hydraulic cylinder is determined by the reciprocating speed of the sliding valve core, while the amplitude of the excitation is determined by the flow rate entering and exiting the hydraulic cylinder. The flow rate depends on the overlap area between the oil inlet window of the valve sleeve and the P port of the valve body, as well as the overlap time. Therefore, the amplitude and frequency of the vibration can be adjusted by changing the rotation angle of the valve sleeve and the rotation speed of the valve core.

[0069] The valve sleeve of this invention moves as follows: a mechanical device causes the valve sleeve to rotate axially, thereby regulating the high-pressure hydraulic oil entering the inlet P port. The regulated high-pressure hydraulic oil then enters the excitation chamber. The input shaft on the right side of the valve sleeve is connected to a servo motor via a gearbox, sleeve, and other connecting devices. By controlling the frequency and number of pulses received by the servo driver, the rotation of the valve sleeve is controlled, thus achieving flow control.

[0070] The movement of the rotary valve core in this invention is as follows: A motor drives the rotary valve core to rotate, which in turn drives the outer sliding valve core to reciprocate axially. The rotary valve core is connected to a servo motor via a gearbox, sleeve, and other connecting devices. By changing the motor speed, the rotational speed of the rotary valve core is controlled. The rotation of the rotary valve core drives the horizontal reciprocating motion of the sliding valve core. When hydraulic oil enters one side of the hydraulic cylinder piston through the main input channel on the sliding valve core via working port A, the hydraulic cylinder piston moves horizontally. Excess hydraulic oil returns to the oil tank through working port B and the return channel via drain port T2. After the motor drives the rotary valve core to rotate half a cycle, the oil circuit changes. Hydraulic oil enters the other side of the hydraulic cylinder through working port B, causing the hydraulic cylinder to move horizontally in the opposite direction. Excess hydraulic oil returns to the oil tank through the return channel on the valve sleeve and the drain port T1. Because of the sinusoidal reciprocating mechanism between the rotary valve core and the sliding valve core, when the rotary valve core rotates continuously, the valve sleeve reciprocates horizontally along the guide groove on the rotary valve core. The oil inlet switches back and forth between working ports A and B, generating a vibration effect in the hydraulic cylinder. The vibration amplitude depends on the rotation angle of the valve sleeve, and the vibration frequency depends on the rotational speed of the rotary valve core. The vibration characteristics of the vibrating valve can be adjusted by changing the motion of the rotary valve core.

[0071] The specific working principle of this invention is as follows:

[0072] One end of the rotary valve core 6 can be connected to a servo motor or hydraulic motor via a gearbox or similar connecting device to achieve high-speed rotation of the rotary valve core. A sinusoidal reciprocating mechanism, consisting of the sinusoidal guide groove 23 on the rotary valve core 6 and the guide pin 8 on the sliding valve core 7, enables the cyclic reciprocating horizontal movement of the sliding valve core 7. The amplitude of the guide groove corresponds to the curve and is coordinated with the relative positions of the shoulders and the relative positions of the window groups on the valve sleeve 9. The hydraulic vibration valve is approximately a three-position four-way valve; refer to the attached diagram. Figure 8 When the sinusoidal excitation rotary valve is in the neutral position, the second shoulder 18 on the sliding valve core 7 is located in the first return oil window group 24, the third shoulder 19 is located in the inlet oil window group 26, and the fourth shoulder 20 is located in the second return oil window group 28, and the working oil port is closed; see attached... Figure 7 When the sinusoidal excitation rotary valve is in position A, the second shoulder 18 on the sliding valve core 7 is located to the right of the first return oil window group 24, the third shoulder 19 is located to the right of the inlet oil window group 26, and the fourth shoulder 20 is located to the second return oil window group 28. Oil enters from working port A 31, returns from working port B 33, and is guided to the drain port T2 34. (See attached reference.) Figure 9 When the sinusoidal excitation rotary valve is in position B, the second shoulder 18 on the sliding valve core 7 is located to the left of the first return oil window group 24, the third shoulder 19 is located to the left of the inlet oil window group 26, and the fourth shoulder 20 is located to the left of the second return oil window group 28. The oil enters from the working port B 33, returns from the working port A 31, and is guided to the drain port T1 31.

[0073] During the rotation of the rotary valve core 6, before the high-pressure hydraulic oil enters the excitation chamber through the inlet P port 32, it is output with a defined pressure and flow rate by the combined action of the valve sleeve 9 and the inlet window group 26, and then enters the excitation chamber. As the rotary valve core 6 continues to rotate, it drives the sliding valve core 7 to perform horizontal reciprocating motion, achieving high-frequency oil circuit switching. Simultaneously, because the rotary valve core 6 adopts a sinusoidal guide groove, it can convert the stable axial rotation into a horizontal reciprocating motion with sinusoidal characteristics. When the rotational speed of the rotary valve core 6 is increased, the cycle period shortens, and the excitation frequency increases. One end of the valve sleeve 9 can be connected to a stepper motor via a speed-changing gearbox or other connecting device. By inputting the stepper motor's rotation angle, the overlap area between the window in the inlet window group on the valve sleeve 9 and the P port can be controlled, thus achieving flow control. Before the sinusoidal excitation rotary valve operates, the valve sleeve 9 needs to be calibrated to determine the positions of maximum and minimum flow rates. Figure 12 This is the location with the highest traffic, such as... Figure 13 This is the position where the flow rate is at its minimum.

[0074] Changes in excitation amplitude: See attached document Figure 12 and attached Figure 13The vibration valve controls the vibration amplitude of the hydraulic vibration valve by changing the rotation angle of the valve sleeve 9 and controlling the overlap area between a certain window in the oil inlet window group and the first oil passage (P port) on the valve body 10.

[0075] Enhanced vibration stability: The vibration valve can improve the stability of the cyclic reciprocating horizontal motion of the sliding valve core 7 by changing the number and position of the sinusoidal guide grooves on the rotary valve core 6 and changing the number of guide pins 8 on the sliding valve core 7.

[0076] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0077] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0078] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between them; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0079] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "beneath" of the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0080] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0081] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A sinusoidal excitation rotary valve, characterized in that, The valve body (10) includes a left end cap A (1), a left end cap B (5), a rotary valve core (6), a sliding valve core (7), a valve sleeve (9), a valve body (10), a right end cap A (11), and a right end cap B (15). The valve body (10) has a left end cap B (5) and a right end cap A (11) fixed at both ends. A left end cap A (1) and a right end cap B (15) are respectively disposed on the outer side of the left end cap B (5) and the outer side of the right end cap A (11). An axially oriented inner hole is formed inside the valve body (10). A valve sleeve (9) is provided that rotates circumferentially along the inner hole of the valve body (10). A double-layer valve core is installed inside the valve sleeve (9). The double-layer valve core includes a sliding valve core (7) that slides axially along the valve body (10) and a rotating valve core (6) disposed inside the sliding valve core (7). The sliding valve core (7), the valve sleeve (9), and the valve body (10) cooperate to form an excitation chamber. The rotating valve core (6) rotates and drives the sliding valve core (7) to reciprocate left and right, realizing the switching of the oil circuit on the sliding valve core (7) between position A, intermediate position, and position B. The sliding valve core (7) is provided with a first support shoulder (16), a second shoulder (18), a third shoulder (19), a fourth shoulder (20), and a fifth support shoulder (21) from left to right; the first support shoulder (16) is truncated circular, and the left end cap A (1) has a truncated circular hole on the right side. The truncated circle of the first support shoulder (16) and the truncated circular hole cooperate with each other to prevent the sliding valve core from rotating; the movement range of the first support shoulder (16) is limited to the depth range of the truncated circular hole. The left end of the rotary valve core (6) passes through the left end cover B (5) and the left end cover A (1) in sequence. The surface of the rotary valve core (6) is provided with two parallel guide grooves (23). The sliding valve core (7) is provided with a first pin hole (17) that cooperates with the guide grooves (23). A guide pin (8) is provided in the first pin hole (17). The guide grooves and the guide pin constitute a reciprocating mechanism. When the rotary valve core (6) rotates, the sliding valve core (7) will only move laterally along the inner hole due to the limitation of the forced lateral displacement on the left side. The valve sleeve (9) is provided with five sets of windows, which are arranged from left to right as the first return oil window group (24), the first working window group (25), the oil inlet window group (26), the second working window group (27), and the second return oil window group (28). Each window in each window group is evenly distributed around the valve sleeve (9). The overlapping area of ​​the window and the oil inlet P port (32) on the valve body (10) forms a variable throttle orifice. By rotating the valve sleeve, the size of the variable throttle orifice is changed to achieve linear control of the oil flow rate entering the valve body (10). Each of the guide grooves (23) is a sinusoidal guide groove, and the sinusoidal curve corresponding to the sinusoidal guide groove has two cycles. The phase and amplitude of the two guide grooves (23) are the same. The amplitude change of the curve corresponding to the guide groove (23) is matched with the distribution of the shoulder and the relative position of the window on the valve sleeve (9). When the sinusoidal excitation rotary valve completes half a working cycle, the distance the shoulder moves is exactly twice the lateral distance of the window. The guide groove (23) can change the number of periods and amplitude of the corresponding sine curve, thereby changing the frequency of switching of the working oil circuit under the same rotation speed of the rotary valve core; The guide groove (23) changes the shape of the corresponding curve. It is non-sinusoidal and there are multiple curves. By changing the distribution position of the guide groove (23), the working stability of the vibration valve can be improved.

2. The sinusoidal excitation rotary valve as described in claim 1, characterized in that, The bottom of the valve body (10) is provided with an oil drain port T1 (30), an oil drain port T2 (34), an oil inlet port P (32), a working port A (31), and a working port B (33); the lower wall of the valve body (10) is provided with a first oil passage connecting the oil inlet port P (32), and the lower wall of the excitation chamber is provided with a second oil passage connecting the working port A (31) and the excitation chamber, a third oil passage connecting the working port B (33) and the excitation chamber, a fourth oil passage connecting the oil drain port T1 (30) and the excitation chamber, and a fifth oil passage connecting the oil drain port T2 (34) and the excitation chamber.

3. The sinusoidal excitation rotary valve as described in claim 1, characterized in that, The first support shoulder (16) is located in the right limit hole of the left end cover A (1), the second shoulder (18) is in the left side of the working port A (31), and the third shoulder is in the vicinity of the oil inlet P (32).

4. The sinusoidal excitation rotary valve as described in claim 1, characterized in that, The left end of the rotary valve core (6) is located in the support step formed by the left end cover A (1) and the left end cover B (5). The support step is provided with a deep groove ball bearing A (2). The deep groove ball bearing A (2) cooperates with the retaining ring A (3) to realize the axial positioning of the rotary valve core (6). The right side of the valve sleeve (9) passes through the right end cover A (11) and the right end cover B (15) in sequence. The right end of the valve sleeve (9) is located in the support step formed by the right end cover A (11) and the right end cover B (15). A deep groove ball bearing B (12) is provided on the support step. The deep groove ball bearing B (12) cooperates with the retaining ring B (14) to realize the axial positioning of the valve sleeve (9).

5. The sinusoidal excitation rotary valve as described in claim 4, characterized in that, The retaining ring A (3) and retaining ring B (14) are each provided with a second pin hole. The two second pin holes correspond to the third pin holes at the left end of the sliding valve core (7) and the right end of the valve sleeve (9), respectively, so as to achieve axial fixation and support of the rotating valve core (6) and valve sleeve (9).

6. The sinusoidal excitation rotary valve as described in claim 1, characterized in that, The valve body (10) has threaded holes on both the left and right ends for fixing the left end cover B (5) and the right end cover A (11). The left end cover B (5) and the right end cover A (11) are respectively provided with through holes that cooperate with the threaded holes. The valve body (10) has a countersunk hole in the middle for connecting with the valve block.

7. The sinusoidal excitation rotary valve as described in claim 1, characterized in that, The first support shoulder (16) and the fifth support shoulder (21) are provided with pressure equalization grooves, and the second shoulder (18), the third shoulder (19) and the fourth shoulder (20) are provided with grooves to reduce friction.

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