CN112923100A - Hydraulic rotary valve, hydraulic rotary system, control method and working machine - Google Patents

Abstract

The invention provides a hydraulic rotary valve, a hydraulic rotary system, a control method and an operating machine, wherein the hydraulic rotary valve comprises a first reversing valve, a second reversing valve, a left pilot oil port, a right pilot oil port and a rotary drift valve; the second reversing valve is connected with the first reversing valve in series and is used for being connected with the rotary driving equipment; the left pilot oil port is communicated with the left pilot end of the first reversing valve and the left pilot end of the second reversing valve respectively, and the right pilot oil port is communicated with the right pilot end of the first reversing valve and the right pilot end of the second reversing valve respectively; the rotary drift valve comprises a first oil duct, and the first oil duct is communicated between the left pilot oil port and the left pilot end of the first reversing valve; the first oil passage is in delayed conduction under the condition that oil pressure is established at the left pilot oil port, and is in delayed closing under the condition that the pressure is released at the left pilot oil port. The invention can safely and stably control the starting and stopping of the arm support through the hydraulic rotary valve, so that the arm support of the working machine achieves better rotation performance.

Description

Hydraulic rotary valve, hydraulic rotary system, control method and working machine

Technical Field

The invention relates to the technical field of hydraulic rotation control, in particular to a hydraulic rotating valve, a hydraulic rotating system, a control method and an operating machine.

Background

Currently, an arm support is generally disposed on a crane, a concrete pump truck, a fire fighting truck, and other operation machines, and the arm support is driven by a hydraulic rotation system on the operation machine to perform a rotation function. For example, in the hydraulic rotation of a crawler crane, an operator operates a hydraulic control handle to push a rotary valve core to open, so as to push the operation of a rotary assembly corresponding to an arm support.

However, under actual conditions, especially when the working machine operates the boom on a slope to rotate, when the rotation is started, the boom is easy to rotate in the opposite direction, and when the boom is controlled to stop rotating, a large impact is generated, which may cause safety risks such as the boom shaking and twisting. Therefore, in a slope environment, the work machine is difficult to safely and stably control the starting and stopping of the boom, and the slewing performance is greatly limited.

Disclosure of Invention

The invention provides a hydraulic rotary valve, a hydraulic rotary system, a control method and an operating machine, which are used for solving the problem that the conventional operating machine is difficult to safely and stably control the starting and stopping of an arm support through the hydraulic rotary valve in a ramp environment.

The present invention provides a hydraulic rotary valve comprising: the first reversing valve, the second reversing valve, the left pilot oil port, the right pilot oil port and the rotary drift valve; the first reversing valve is connected with the second reversing valve in series, and the second reversing valve is used for being connected with a rotary driving device; the left pilot oil port is communicated with a left pilot end of the first reversing valve and a left pilot end of the second reversing valve respectively, and the right pilot oil port is communicated with a right pilot end of the first reversing valve and a right pilot end of the second reversing valve respectively; the rotary drift valve is arranged between the left pilot oil port and the left pilot end of the first reversing valve and/or between the right pilot oil port and the right pilot end of the first reversing valve; the rotary drift valve comprises a first oil duct, and the first oil duct is communicated between the left pilot oil port and the left pilot end of the first reversing valve; the first oil passage is in delayed conduction under the condition that oil pressure is established at the left pilot oil port, and the first oil passage is in delayed closing under the condition that the pressure is released at the left pilot oil port.

According to the present invention, there is provided a hydraulic rotary valve further comprising: the first end of the shuttle valve and the second end of the shuttle valve are respectively communicated with the two working oil ports of the second reversing valve, the third end of the shuttle valve is communicated with the oil inlet of the hydraulic rotary valve through the damping slip valve, and the oil path on the damping slip valve is closed in a delayed mode under the condition that the pressure of the left pilot oil port is relieved.

According to the present invention, there is provided a hydraulic rotary valve further comprising: and the rotary booster valve is arranged between at least one of the two working oil ports of the second reversing valve and the oil return port of the hydraulic rotary valve, and an oil path on the rotary booster valve is communicated under the condition of releasing pressure to the left pilot oil port.

According to the hydraulic rotary valve provided by the invention, the rotary drift valve further comprises a second oil channel, and the second oil channel is used for communicating a pilot pressure oil source with the left pilot end of the second reversing valve; the rotary drift valve can realize oil path switching between the first oil path and the second oil path.

The hydraulic rotary valve further comprises a one-way valve and a check valve, wherein the one-way valve is arranged on a first valve rod of the first reversing valve so as to control the directional conduction from an oil port P to an oil port A of the first reversing valve or the directional conduction from the oil port P to an oil port B of the first reversing valve; and/or under the condition that the first valve rod of the first reversing valve is positioned at the middle position, the oil port T of the first reversing valve is respectively communicated with the oil port P, the oil port A and the oil port B of the first reversing valve; and under the condition that the second valve rod of the second reversing valve is positioned at the middle position, the oil port P and the oil port A of the second reversing valve are cut off, and the oil port T and the oil port B of the second reversing valve are cut off.

According to the present invention, there is provided a hydraulic rotary valve further comprising: and the oil inlet of the hydraulic rotary valve is communicated with the oil return port of the hydraulic rotary valve through the overflow valve.

The present invention also provides a hydraulic swing system comprising: the two working oil ports of the second reversing valve are respectively communicated with the rotary driving device.

According to a hydraulic swing system provided by the present invention, the swing driving apparatus includes a hydraulic oil pump; the hydraulic oil pump is provided with an angle detection device, the angle detection device is used for detecting the rotating speed of a rotor of the hydraulic oil pump, and the angle detection device is respectively in communication connection with the rotary drift valve, the damping slip valve and the rotary pressurization valve.

The present invention also provides a work machine comprising: a hydraulic swing valve as described above, or a hydraulic swing system as described above.

The invention also provides a control method of the hydraulic slewing system, which comprises the following steps: initiating a first control mode for the hydraulic rotary valve: pilot oil is input into a left pilot oil port on the hydraulic rotary valve, a first oil duct of the rotary drift valve is conducted after first preset time, so that a second reversing valve is delayed to be opened compared with the first reversing valve, and the rotary driving equipment is controlled to rotate by the second reversing valve; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and the first oil duct on the rotation drift valve is closed after a second preset time, so that the second reversing valve is delayed from the first reversing valve to be closed.

According to the control method of the hydraulic swing system provided by the invention, the method further comprises the following steps: initiating a second control mode for the hydraulic rotary valve: inputting pilot oil with a first preset pressure to a left pilot oil port on the hydraulic rotary valve to control the rotary driving device to rotate; when the angle detection device monitors rotation information of the rotation driving equipment, controlling the conduction of a second oil duct of the rotation drift valve, inputting pilot oil with second preset pressure to a second reversing valve through the second oil duct, wherein the second preset pressure is greater than the first preset pressure, and controlling the rotation of the rotation driving equipment through the first reversing valve; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and after the rotation of the rotation driving equipment is stopped, the second oil duct of the rotation drift valve is controlled to be closed, so that the oil duct of the rotation drift valve is switched from the second oil duct to the first oil duct, and the second reversing valve is pushed to a middle position.

According to the control method of the hydraulic swing system provided by the invention, the method further comprises the following steps: activating a third control mode for the hydraulic rotary valve: pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate; when the angle detection device monitors rotation information of the rotary driving equipment, controlling the oil way of the damping slip valve to be communicated; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the oil way of the damping slip valve is controlled to be closed after the third preset time.

According to the control method of the hydraulic swing system provided by the invention, the method further comprises the following steps: initiating a fourth control mode for the hydraulic rotary valve: pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate, and a rotary pressurization valve is controlled to be closed in the rotation process of the rotary driving equipment; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the rotation pressurization valve is controlled to be opened until the rotation driving equipment stops rotating.

According to the hydraulic rotary valve, the hydraulic rotary system, the control method and the operation machine, the first reversing valve, the second reversing valve and the rotary drift valve are arranged on the hydraulic rotary valve, when pilot oil is introduced into a left pilot oil port, the second reversing valve can be delayed from the first reversing valve to be opened based on the damping action of the first oil duct on the rotary drift valve, so that the boom of the operation machine is controlled to be started stably, and the safety of starting the boom to rotate on a slope by the operation machine is ensured; meanwhile, when the boom is controlled to stop rotating, the second reversing valve can be delayed from the closing of the first reversing valve based on the damping effect of the first oil duct on the rotating drift valve, so that the rotation of the boom is buffered, the stopping stability of the boom is ensured, and the large impact is prevented from occurring when the boom stops rotating.

Therefore, the operation machine disclosed by the invention can safely and stably control the rotation of the arm support through the hydraulic rotary valve under the ramp environment, so that the arm support of the operation machine achieves better rotation performance.

Drawings

In order to more clearly illustrate the technical solutions of the present invention or the prior art, the drawings needed for the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and those skilled in the art can also obtain other drawings according to the drawings without creative efforts.

FIG. 1 is a schematic cross-sectional view of a hydraulic rotary valve according to the present invention;

FIG. 2 is a schematic diagram of a hydraulic swing system provided by the present invention;

FIG. 3 is a schematic view of a first valve stem on a first reversing valve provided by the present invention;

FIG. 4 is a schematic structural view of the first direction valve when the first valve stem is in a neutral position within the first direction valve;

fig. 5 is a schematic structural view illustrating the first valve rod moving rightwards from the middle position by a first preset distance so that the oil port P of the first direction valve is separated from the oil port a;

fig. 6 is a schematic structural view of the first valve rod moving from the middle position to the right by a second preset distance so that the oil port B of the first directional valve is separated from the oil port T, and the check valve from the oil port P to the oil port B is opened;

fig. 7 is a schematic structural view when the first valve rod provided by the present invention moves rightward from the middle position by a third preset distance so that the oil port P of the first direction valve is blocked from the oil port T on the left side of the middle shaft shoulder;

FIG. 8 is a schematic structural view of a valve body of a first reversing valve provided by the present invention;

FIG. 9 is a schematic illustration of a second valve stem on a second reversing valve provided by the present invention;

FIG. 10 is a schematic illustration of the second reversing valve with the second valve stem in the neutral position within the second reversing valve according to the present invention;

FIG. 11 is a schematic structural view of a valve body of a second reversing valve provided in accordance with the present invention;

reference numerals:

100: a first direction changing valve; 200: a second directional control valve; 300: a valve body;

1: a first valve stem; 2: a first valve stem cavity; 3: a second valve stem;

4: a second valve stem chamber; 5: a rotary drift valve; 6: a damping slip valve;

7: a shuttle valve; 8: a rotary booster valve; 9: an overflow valve;

400: a swing drive device; 10: a middle position shaft shoulder; 11: a first oil through groove;

12: a first shoulder; 13: a second oil through groove; 14: a second shoulder;

101: balancing the oil groove; 102: a first oil guide groove; 103: a second oil guide groove;

121: an oil guiding structure; 131: an oil outlet; 141: an oil inlet;

20: a median cavity section; 21: a first seal section; 22: a first cavity section;

23: a second seal section; 24: a second cavity section; 25: a third seal section;

26: a third cavity section; 27: a fourth seal section; 1410: a first oil inlet;

1411: a second oil inlet; 320: a middle shoulder section; 321: a first oil through groove section;

322: a first shoulder section; 323: a second oil tank section; 324: a second shoulder section;

310: a first oil port; 311: a second oil port; 312: a third oil port;

313: a first oil guiding structure; 314: a second oil guide structure; 410: a middle sealing cavity;

411: a first cavity; 412: a first sealed chamber; 413: a second cavity;

414: a second sealed chamber.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention clearer, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

The hydraulic swing valve, the hydraulic swing system, the control method, and the work machine of the present invention will be described below with reference to fig. 1 to 11.

As shown in fig. 1 to 2, the present embodiment provides a hydraulic rotary valve including: the oil inlet P, the oil return port T, a first working oil port A1 and a second working oil port B1.

Further, the hydraulic rotary valve further includes: a first reversing valve 100, a second reversing valve 200, a left pilot oil port pa, a right pilot oil port pb, and a rotary drift valve 5. The oil port P of the first reversing valve 100 is communicated with the oil inlet P, the oil port T of the first reversing valve 100 is communicated with the oil return port T, two working oil ports of the first reversing valve 100 are respectively represented as an oil port a and an oil port B, and the oil ports P and the oil ports T of the second reversing valve 200 are communicated with each other in a one-to-one correspondence manner. Correspondingly, the oil port P of the second direction valve 200 is labeled a in fig. 1 and is communicated with the oil port a of the first direction valve 100, and the oil port T of the second direction valve 200 is labeled B in fig. 1 and is communicated with the oil port B of the first direction valve 100, so as to realize the series connection of the second direction valve 200 and the first direction valve 100.

Meanwhile, the two working oil ports of the second directional valve 200 are respectively an oil port a and an oil port B, the oil port a of the second directional valve 200 is communicated with the first working oil port a1, the oil port B of the second directional valve 200 is communicated with the second working oil port B1, and the first working oil port a1 and the second working oil port B1 are used for being communicated with the rotary driving device 400.

As shown in fig. 2, the left pilot oil port pa shown in this embodiment is respectively communicated with the left pilot end of the first direction valve 100 and the left pilot end of the second direction valve 200, and the right pilot oil port pb is respectively communicated with the right pilot end of the first direction valve 100 and the right pilot end of the second direction valve 200.

The rotary drift valve 5 shown in this embodiment includes a first oil passage that communicates between the left pilot oil port pa and the left pilot end of the first direction valve 100. The first oil passage is turned on in a delayed manner when the oil pressure is established at the left pilot oil port pa, and is turned off in a delayed manner when the pressure is released at the left pilot oil port pa.

As can be seen from the above, in the embodiment, the first direction valve 100, the second direction valve 200 and the rotary drift valve 5 are arranged on the hydraulic rotary valve, and the pilot oil is introduced into the left pilot oil port pa, so that when the oil pressure is established at the left pilot oil port pa, the pilot oil can simultaneously push the first valve rod on the first direction valve 100 and the second valve rod on the second direction valve 200 to move under the action of the oil pressure of the pilot oil, but due to the damping effect of the first oil passage on the rotary drift valve 5, the second direction valve 200 can be delayed from the opening of the first direction valve 100, so as to control the boom of the working machine to start stably, and ensure the safety of the working machine for starting the boom on the slope.

Meanwhile, when the boom is controlled to stop rotating, the pressure relief treatment can be performed on the left pilot oil port pa, and under the damping action of the first oil duct on the rotating drift valve 5, the first valve rod on the first reversing valve 100 can return to the middle position in advance compared with the second valve rod on the second reversing valve 200, that is, the second reversing valve 200 is delayed from being closed by the first reversing valve 100, so that the rotation of the boom is buffered, the stability of the boom stop is ensured, and the occurrence of large impact when the boom stops rotating is prevented.

Therefore, in the working machine shown in the embodiment, the rotation of the boom can be safely and stably controlled to start and stop through the hydraulic rotary valve under the slope environment, so that the boom of the working machine achieves better rotation performance.

The first direction valve 100 will be described in detail below with reference to fig. 3 to 8.

Fig. 3 is a schematic structural diagram of a first valve stem on the first direction valve 100 provided in this embodiment. Be equipped with meso position shaft shoulder 10, first oil groove 11, first shaft shoulder 12, second oil groove 13 and second shaft shoulder 14 on the body of rod of first valve rod 1 in proper order, first oil groove 11, first shaft shoulder 12, second oil groove 13 and the second shaft shoulder 14 symmetry of leading to set up in the both sides of meso position shaft shoulder 10.

Meanwhile, the first valve rod 1 shown in the embodiment is further provided with an oil inlet 141, an oil outlet 131, an oil guide structure 121 and a throttling structure; the oil inlet 141 is formed on the side wall of the second shaft shoulder 14, the oil outlet 131 is formed on the second oil through groove 13, and the oil outlet 131 is communicated with the oil inlet 141; the diameter of the oil outlet 131 is larger than that of the oil inlet 141, so that the oil pressure rise of the hydraulic oil after the hydraulic oil is conveyed from the oil inlet 141 to the oil outlet 131 can be effectively avoided.

It should be noted here that the oil inlet 141 on the first valve stem 1 includes a first oil inlet 1410 and a second oil inlet 1411, and the diameter of the first oil inlet 1410 is smaller than that of the second oil inlet 1411; in the axial direction of the first valve rod 1, the distance from the first oil inlet 1410 to the middle shoulder 10 is greater than the distance from the second oil inlet 1411 to the middle shoulder 10. In this way, based on the improvement on the oil inlet 141, in the process that the first valve rod 1 moves to the right station, the oil guide gap between the oil inlet 141 and the oil outlet 131 is gradually increased.

Preferably, the present embodiment is provided with a check valve in the rod body of the first valve rod 1, and the check valve is connected between the oil inlet 141 and the oil outlet 131 to control the hydraulic oil to flow from the oil inlet 141 to the oil outlet 131. Wherein the one-way valve is not specifically illustrated in fig. 3.

Here, through setting up the check valve, when first valve rod 1 moves to the right station, hydraulic oil can only flow to hydraulic fluid port B from hydraulic fluid port P of first switching-over valve 100, simultaneously, when first valve rod 1 moves to the left station, hydraulic oil can only flow to hydraulic fluid port a from hydraulic fluid port P of first switching-over valve 100 to the directional flow control to hydraulic oil has been realized. Because the rotation of the arm support is controlled by the hydraulic motor on the operation machine, when the operation machine is in a gradient environment, the directional control of the hydraulic motor can be carried out based on the first reversing valve 100, and the arm support is prevented from slipping down the gradient.

Further, the oil guiding structure 121 shown in the present embodiment is configured on the side wall of the first shoulder 12, a first end of the oil guiding structure 121 is formed near the middle of the first shoulder 12, and a second end is formed at an end of the first shoulder 12 far from the middle shoulder 10.

As shown in fig. 3, in order to facilitate the oil guiding structure 121 to better guide the hydraulic oil to flow along the side wall of the first shoulder 12 for oil return of the reversing valve, the oil guiding structure 121 shown in this embodiment extends along the axial direction of the first valve rod 1, the oil guiding structure 121 includes an oil passing surface or an oil groove, and a radial distance of the second end of the oil guiding structure 121 relative to the central axis of the first valve rod 1 is smaller than a radial distance of the first end of the oil guiding structure 121 relative to the central axis of the first valve rod 1.

Further, the throttling structure shown in the present embodiment is configured on the side wall of the neutral shoulder 10, and the throttling structure extends from the middle of the neutral shoulder 10 or a position near the middle of the neutral shoulder 10 to at least one end of the neutral shoulder 10.

As shown in fig. 3, in one embodiment, the throttling structure includes a balance oil groove 101, the balance oil groove 101 extends along the axial direction of the first valve rod 1, a first end of the balance oil groove 101 is formed at one end of the middle shoulder 10, and a second end is formed at the other end of the middle shoulder 10.

As shown in fig. 3, in another embodiment, the throttling structure includes a first oil guiding groove 102 and a second oil guiding groove 103; the first oil guide groove 102 and the second oil guide groove 103 extend along the axial direction of the first valve rod 1; a first end of the first oil guide groove 102 is formed in the middle of the middle shaft shoulder 10, and a second end is formed at one end of the middle shaft shoulder 10; a first end of the second oil guide groove 103 is formed at the middle of the center shoulder 10, and a second end is formed at the other end of the center shoulder 10.

As can be seen from the above, in the present embodiment, the oil inlet 141 is disposed on the second shoulder 14 of the first valve rod 1, and the oil outlet 131 is disposed on the second oil groove 13, so that when the reversing valve of the first reversing valve 100 is controlled, oil can be simultaneously supplied to the oil inlet 141 at both ends of the first valve rod 1 and the middle shoulder 10 at the middle portion through the oil supply port of the first reversing valve 100, and when oil is returned through the oil guide structure 121, based on the throttling effect of the oil guide structure 121, the oil pressure in the first oil groove 11 at both sides of the middle shoulder 10 can be balanced, the amount of oil guided from the oil supply port to the oil return port of the first reversing valve 100 can be controlled, the stability of oil return of the hydraulic system is ensured, and the smooth control of the rotation action of the hydraulic motor can be realized.

The throttling effect of the throttling structure in the process that the first valve rod 1 moves to the right position in the first direction valve 100 will be described in detail with reference to fig. 3 to 8.

As shown in fig. 4 and 8, since the first direction valve 100 and the second direction valve 200 are integrated on the same valve body 300, the first direction valve 100 is configured in the first valve rod chamber 2 in the valve body 300, and the first valve rod 1 as described above is slidably installed in the first valve rod chamber 2.

The first valve stem cavity 2 shown in the present embodiment includes a middle cavity section 20, a first sealing section 21, a first cavity section 22, a second sealing section 23, a second cavity section 24, a third sealing section 25, a third cavity section 26, and a fourth sealing section 27, which are sequentially connected; the first sealing section 21, the first cavity section 22, the second sealing section 23, the second cavity section 24, the third sealing section 25, the third cavity section 26 and the fourth sealing section 27 are symmetrically arranged on two sides of the middle cavity section 20.

As shown in fig. 4, the neutral shoulder 10 is built into the neutral chamber section 20 with the first stem 1 in the neutral position, and at this time, the axial symmetry plane of the first stem 1 coincides with the axial symmetry plane of the first stem chamber 2 in the first direction valve 100 in an orientation perpendicular to the axial direction of the first stem 1. Meanwhile, one end of the first shaft shoulder 12, which is far away from the middle shaft shoulder 10, is in sealing fit with the second sealing section 23, one end of the first shaft shoulder 12, which is close to the middle shaft shoulder 10, is located in the first cavity section 22, the first end of the oil guiding structure 121 on the first valve rod 1 is communicated with the first cavity section 22, the second end of the oil guiding structure 121 is communicated with the second cavity section 24, the second shaft shoulder 14 is simultaneously in contact sealing with the third sealing section 25 and the fourth sealing section 27, the oil inlet P is respectively communicated with the middle cavity section 20 and the third cavity section 26, and the oil outlet 131 is communicated with the second cavity section 24.

As shown in fig. 4, when the first valve rod 1 is in the neutral position, based on the setting of the oil guiding structure 121, the second cavity section 24 on the left side of the neutral cavity section 20 is communicated with the first cavity section 22 on the left side of the neutral cavity section 20, and the second cavity section 24 on the right side of the neutral cavity section 20 is communicated with the first cavity section 22 on the right side of the neutral cavity section 20, so that the oil port a of the first reversing valve is communicated with the oil port T of the first reversing valve, and the oil port B of the first reversing valve is communicated with the oil port T of the first reversing valve.

As shown in fig. 4, when the first valve rod 1 is located at the middle position, based on the arrangement of the throttling structure, the middle position cavity section 20 can be respectively communicated with the first sealing sections 21 at the left and right sides thereof, so that the oil port P of the first direction valve is communicated with the oil port T of the first direction valve.

Although this embodiment still is equipped with the check valve between oil inlet 141 and oil-out 131 of first valve rod 1, when first valve rod 1 is in the meso position, because hydraulic fluid port A and the hydraulic fluid port T of first switching-over valve switch on, hydraulic fluid port B switches on with hydraulic fluid port T, and hydraulic fluid port T switches on with hydraulic fluid port P, it is the same to lead to the oil pressure at check valve both ends on the body of rod of first valve rod 1 left side, and the oil pressure at check valve both ends is also the same on the body of rod of first valve rod 1 right side, thereby when first valve rod 1 is in the meso position, hydraulic fluid port P and hydraulic fluid port A of first switching-over valve cut, and hydraulic fluid port P and hydraulic fluid port B of first.

As shown in fig. 4, when the first valve rod 1 is in the neutral position, a distance from one end of the oil inlet 141, which is far away from the neutral shoulder 10, to one end of the second cavity section 24, which is close to the neutral cavity section 20, is a first preset distance, and the first preset distance may be specifically set to 0.5 mm; the distance that the first end of the oil guiding structure 121 extends out of the first cavity section 22 and is far away from one end of the middle cavity section 20 is a second preset distance, and the second preset distance can be specifically set to be 1.0 mm; the distance between the end of the first shoulder 12 close to the median shoulder 10 and the first cavity section 22 remote from the median cavity section 20 is a third predetermined distance, which may be specifically set to 2.1 mm.

As shown in fig. 5 and 8, when the first valve rod 1 moves rightwards from the middle position by a first preset distance, the oil port P of the first direction valve 100 is separated from the oil port a based on the sealing effect of the third sealing section 25 on the oil inlet 141, at this time, the oil port P of the first direction valve 100 is conducted with the oil port T, but the oil port P of the first direction valve 100 is still in a cut-off state because the oil port T of the first direction valve 100 is conducted with the oil port B.

As shown in fig. 6 and 8, when the first valve rod 1 moves from the first preset distance to the second preset distance, the oil port B of the first direction valve 100 is separated from the oil port T based on the sealing effect of the second sealing section 23 on the oil guiding structure 121, and the check valve from the oil port P to the oil port B of the first direction valve 100 is opened.

As shown in fig. 7 and 8, when the first valve rod 1 moves from the second preset distance to the third preset distance continuously in the rightward direction, one end of the first shoulder 12 located on the left side, which is close to the middle shoulder 10, starts to be in sealing fit with one end of the first sealing section 21, which is far from the middle cavity section 20, so that the oil port P of the first directional valve 100 is separated from the oil port T on the left side of the middle shoulder 10, hydraulic oil of the oil port P starts to enter the first oil passing groove 11 on the right side of the middle shoulder 10 through the second oil guiding groove 103, the oil port P of the first directional valve 100 starts to build pressure, and as the first valve rod 1 continues to move in the rightward direction, the oil guiding gap of the second oil guiding groove 103 gradually decreases, that is, the hydraulic motor enters a P/T speed regulation stage, so that the hydraulic motor can be gradually accelerated, and smooth control over the.

The second direction valve 200 will be described in detail below with reference to fig. 9 to 11.

Fig. 9 is a schematic structural diagram of a second valve stem on the second direction valve 200 provided in the present embodiment. A middle shaft shoulder section 320, a first oil through groove section 321, a first shaft shoulder section 322 and a second oil through groove section 323 are sequentially arranged on the rod body of the second valve rod 3; the first oil through groove section 321, the first shoulder section 322 and the second oil through groove section 323 are symmetrically arranged at two sides of the middle shaft shoulder section 320; a first oil port 310 and a first oil guiding structure 313 are formed on the side wall of the first shaft shoulder section 322, a second oil port 311 is formed on the second oil trough section 323, and the second oil port 311 is communicated with the first oil port 310; the first end of the first oil guiding structure 313 is formed near the middle of the first shoulder section 322, and the second end is formed at an end of the first shoulder section 322 near the middle shoulder section 320.

Further, in the embodiment, a second oil guiding structure 314 is further configured on the sidewall of the first shoulder section 322, the second oil guiding structure 314 includes a plurality of oil guiding structures and is respectively disposed on two sides of the radial plane where the middle portion of the first shoulder section 322 is located, a first end of the second oil guiding structure 314 is formed near the middle portion of the first shoulder section 322, and a second end is formed at an end of the first shoulder section 322 close to the middle shoulder section 320 or an end of the first shoulder section 322 far from the middle shoulder section 320. The radial plane shown in this embodiment is a plane located in the middle of the first shoulder section 322 and perpendicular to the axial direction of the first shoulder section 322.

Specifically, when the second valve rod 3 shown in this embodiment is used for performing the reversing valve control of the oil path based on the first oil guide structure 313, the oil supply and the oil return of the corresponding oil path can be accelerated with the aid of the second oil guide structure 314, and since the plurality of second oil guide structures 314 are respectively arranged on the two sides of the radial plane where the middle portion of the first shoulder section 322 is located, the fluctuation caused by the overlarge pressure difference at the two ends of the first shoulder section 322 can be avoided at the moment of oil path communication, so that the movement of the buffer valve rod during the reversing valve control is smoother and smoother, and the actions of the hydraulic motor and other executing components can be better driven.

Further, in the embodiment, at least one of the first oil guiding structure 313 and the second oil guiding structure 314 extends along the axial direction of the second valve rod 3, and at least one of the first oil guiding structure 313 and the second oil guiding structure 314 includes an oil passing surface or an oil groove.

Further, as shown in fig. 9, a third oil port 312 is further configured on the side wall of the first shoulder section 322 shown in this embodiment, and the third oil port 312 is communicated with the second oil port 311; in the axial direction of the second valve stem 3, the third oil port 312 is located between the first oil port 310 and an end of the first shoulder section 322 remote from the neutral shoulder section 320. Thus, as the second valve rod 3 moves to the left station or the right station, after the first oil port 310 is communicated with the second oil port 311, the third oil port 312 is also communicated with the second oil port 311, so that the gap between the first cavity 411 and the second cavity 413 on the oil return side is gradually increased.

Further, the second direction valve 200 of the present embodiment includes a second stem chamber 4 formed in the valve body 300, and the second stem 3 as described above is slidably installed in the second stem chamber 4.

As shown in fig. 10 to 11, the second valve stem chamber 4 of the present embodiment includes a middle sealing chamber 410, a first chamber 411, a first sealing chamber 412 and a second chamber 413 which are sequentially communicated, and the first chamber 411, the first sealing chamber 412 and the second chamber 413 are symmetrically disposed at two sides of the middle sealing chamber 410; the middle shoulder section 320 of the second valve stem 3 is in sealing engagement with the middle seal cavity 410, and the first shoulder section 322 is in sealing engagement with the first seal cavity 412.

Further, under the condition that the second valve rod 3 is located in the middle position in the second valve rod cavity 4, the distance between the first oil port 310 and the end of the first cavity 411 far away from the middle position sealed cavity 410 is smaller than the distance between the first end of the first oil guide structure 313 and the end of the second cavity 413 close to the middle position sealed cavity 410.

In the embodiment, the first oil through groove section 321 and the second oil through groove section 323 are annular grooves formed on the rod body of the second valve rod 3. The second valve stem chamber 4 shown in this embodiment further includes a second seal chamber 414, and two second seal chambers 414 are symmetrically disposed on two sides of the middle seal chamber 410; one end of the second sealed cavity 414 is communicated with one end of the second cavity 413 far away from the middle sealed cavity 410; a second shoulder section 324 is further arranged on the rod body of the second valve rod 3, the two second shoulder sections 324 are symmetrically arranged on two sides of the middle shoulder section 320, and one end of the second shoulder section 324 is connected with one end, far away from the middle shoulder section 320, of the second oil through groove section 323; the second shoulder section 324 is in sealing engagement with the second seal cavity 414.

With the second valve stem 3 in the neutral position, the neutral shoulder section 320 on the second valve stem 3 sealingly engages the neutral seal cavity 410 and the first shoulder section 322 on the second valve stem 3 sealingly engages the first seal cavity 412 such that the first cavity 411 is isolated from the second cavity 413. In this way, when the second directional valve 200 is applied to a working machine, in an environment where the working machine is at a certain gradient, the second valve rod 3 isolates hydraulic oil between the first cavity 411 and the second cavity 413, so that stable oil pressure on an oil path of an execution component of the working machine can be ensured, and the phenomenon that an arm support connected with the execution component slips down on the slope can be effectively prevented.

It should be noted that the actuating component shown in this embodiment is specifically a hydraulic motor, the hydraulic motor is used for driving the rotary platform to rotate, and the arm support is mounted on the rotary platform.

As shown in fig. 10, when the second valve rod 3 is in the neutral position, a distance between the first oil port 310 and one end of the first cavity 411, which is far from the neutral sealing cavity 410, is L1, a distance between the first end of the first oil guide structure 313 and one end of the second cavity 413, which is near to the neutral sealing cavity 410, is L2, and L1 is smaller than L2. Wherein L1 may be 1mm to 1.5mm, for example: l1 is specifically 1.0mm, 1.2mm, 1.5mm, etc., and is not specifically limited herein; l2 may be 2mm to 2.5mm, L2 is specifically 2.0mm, 2.2mm, 2.5mm, etc., and is not specifically limited herein.

Therefore, when the hydraulic motor is controlled to rotate by the second reversing valve 200 in the embodiment, based on the valve control effect of the second valve rod 3, before the first cavity 411 and the second cavity 413 located on the oil inlet side are communicated, the first cavity 411 and the second cavity 413 located on the oil return side are already opened by a small opening degree, so that the problem of back pressure of the second reversing valve 200 at the moment of opening the hydraulic motor can be effectively prevented, stable control over the hydraulic motor can be realized, and the service life of the second reversing valve 200 is ensured.

As can be seen from fig. 6 and 10, when the pilot oil is introduced into the left pilot oil port pa of the hydraulic rotary valve, so that the oil pressure is established at the left pilot oil port pa, the pilot oil pushes the first valve rod on the first direction valve 100 and the second valve rod on the second direction valve 200 to move simultaneously under the action of the oil pressure of the pilot oil, but due to the damping effect of the first oil passage on the rotary drift valve 5, only when the first valve rod on the first direction valve 100 moves rightwards by the second preset distance, the second valve rod on the second direction valve 200 starts to move rightwards, so that the second direction valve 200 is delayed from the opening of the first direction valve 100. In the process, the oil return clearance on the oil return side of the first reversing valve 100 is gradually increased, and the conduction clearance on the oil inlet side of the second reversing valve 200 is also gradually increased, so that the boom of the working machine is controlled to be started stably, and the safety of starting the boom to rotate on a slope by the working machine is ensured.

Correspondingly, the pressure of the left pilot oil port pa is relieved, and under the damping action of the first oil channel on the rotary drift valve 5, the first valve rod on the first reversing valve 100 can return to the middle position in advance compared with the second valve rod on the second reversing valve 200, that is, the second reversing valve 200 is delayed from the closing of the first reversing valve 100, so that the buffer control of the rotation of the boom is realized, the stability of the boom stop is ensured, and the large impact is prevented from occurring when the rotation is stopped.

Preferably, as shown in fig. 2, the rotary drift valve 5 shown in the present embodiment further includes a second oil passage for communicating between the pilot pressure oil source and the left pilot end of the second directional valve 200, and the rotary drift valve 5 is capable of switching between the first oil passage and the second oil passage, where in fig. 2, the pilot pressure oil source is denoted by pa'.

Specifically, the rotary drift valve 5 shown in the present embodiment may be connected to a control system, and the control system may be an electric control button, a touch screen controller, or the like. The present embodiment may control the coil of the rotary drift valve 5 to be energized through the control system, so as to conduct the second oil passage of the rotary drift valve 5, and control the switching between the first oil passage and the second oil passage. In this embodiment, the oil pressure of the pilot oil introduced into the second oil passage through the pilot pressure oil source should be greater than the oil pressure of the pilot oil introduced into the first oil passage through the left pilot oil port pa.

Therefore, in the present embodiment, when the second oil passage of the swing drift valve 5 is connected, when the pilot oil is introduced to the left pilot end of the second directional valve 200 through the pilot pressure oil source, the open state of the second directional valve 200 can be locked, and the operator can directly control the swing of the swing driving device through the first directional valve 100, so that the hydraulic swing valve operates in the swing drift mode, and the swing motion of the boom of the working machine can be efficiently controlled.

Further, as shown in fig. 2, the present embodiment is further provided with a damping shuttle valve 6 and a shuttle valve 7. In the embodiment, the first end of the shuttle valve 7 is communicated with the first working oil port a1, the second end of the shuttle valve 7 is communicated with the second working oil port B1, the third end of the shuttle valve 7 is communicated with the oil inlet P through the damping shuttle valve 6, and the oil path on the damping shuttle valve 6 is closed in a delayed manner when the left pilot oil port is depressurized so that the first valve rod of the first reversing valve 100 is located at the middle position. Therefore, in this embodiment, when the boom is controlled to stop rotating, based on the delayed closing of the oil path on the damping slip valve 6, the oil pressures on the first working port a1 and the second working port B1 may be equalized to control the boom of the working machine to slowly rotate until the boom stops rotating, so that the rotation of the boom is buffered, and a large impact is prevented from occurring when the boom stops rotating.

Further, as shown in fig. 2, the present embodiment is also provided with a swing pressurization valve 8. A rotary pressure-increasing valve 8 is installed between at least one of the first working port a1 and the second working port B1 and the oil return port T shown in the present embodiment. As shown in fig. 2, a rotary booster valve 8 is installed between each of the first working port a1, the second working port B1, and the oil return port T in the present embodiment. When the pressure of the left pilot oil port is released so that the first valve rod of the first direction changing valve 100 is in the middle position, the oil path on the rotary pressure increasing valve 8 is communicated. In this way, when stopping control of the rotation of the boom of the working machine is performed, under the condition that the left pilot oil port pa is depressurized, the oil pressure on the first working oil port a1 or the second working oil port B1 can be reduced by unloading the rotary pressurization valve 8, so that the boom of the working machine is controlled to slowly rotate until stopping, and therefore, the buffer control of the rotation of the boom is realized, and large impact is prevented from occurring when the rotation is stopped.

Further, as shown in fig. 2, the present embodiment is further provided with a relief valve 9, and the relief valve 9 is communicated between the oil inlet P and the oil return port T. Thus, when the oil pressure in the oil inlet P is too high, the relief valve 9 is opened, and the first direction valve 100 and the second direction valve 200 can be protected.

As can be seen from the above, in the present embodiment, the check valve is provided in the first direction valve 100, so that when the hydraulic swing system is swung in an uphill direction with a small opening, the swing pressure is prevented from being insufficient to overcome the resistance of the slope, and the hydraulic swing system is prevented from starting and slipping. In the present embodiment, the second direction valve 200 is designed to have an O-type neutral function, so that the swing system can be prevented from slipping down by the second direction valve 200 when the work machine is stopped on a slope. Meanwhile, in the embodiment, based on the design of the rotary drift valve 5, the damping sliding valve 6 and the rotary pressure increasing valve 8, the multi-mode buffer function of the arm support under different application scenes is further realized on the basis of anti-sliding.

Further, as shown in fig. 2, the present embodiment further provides a hydraulic swing system, including: in the swing drive device and the hydraulic swing valve described above, the first hydraulic port a1 and the second hydraulic port B1 of the hydraulic swing valve are respectively communicated with the swing drive device.

Specifically, the swing drive apparatus shown in the present embodiment includes a hydraulic oil pump; the hydraulic oil pump is used for driving the rotation of the rotary table on the rotary assembly of the operation machine, and the arm support of the operation machine is arranged on the rotary table, so that the hydraulic oil pump can realize the rotary control of the arm support under the control of the hydraulic rotary valve.

Further, the hydraulic oil pump shown in this embodiment is provided with an angle detection device. The angle detecting device may be an encoder known in the art, and the encoder is coaxially mounted on the rotor of the hydraulic oil pump for detecting the rotation speed of the rotor of the hydraulic oil pump.

The hydraulic rotary system shown in this embodiment may further be provided with a control module, and the control module may be a single chip microcomputer or a PLC controller known in the art. When the working state of the hydraulic rotary valve is controlled, the angle detection device can be in communication connection with the control module, and the control module controls the power-on states of coils on the rotary drift valve, the damping slide valve and the rotary pressure increasing valve in real time based on the rotation information of the hydraulic oil pump monitored by the angle detection device, so that the opening and closing states of the rotary drift valve, the damping slide valve and the rotary pressure increasing valve are controlled in real time.

Further, the present embodiment also provides a working machine including: a hydraulic swing valve as described above, or a hydraulic swing system as described above.

The working machine shown in this embodiment includes a crane, a concrete pump truck, a fire engine, and other mechanical devices with a rotation function, and is not limited specifically herein.

Further, the present embodiment also provides a control method of the hydraulic swing system as described above, including: initiating a first control mode for the hydraulic rotary valve: pilot oil is input into a left pilot oil port on the hydraulic rotary valve, a first oil duct of the rotary drift valve is conducted after first preset time, so that a second reversing valve is delayed to be opened compared with the first reversing valve, and the rotary driving equipment is controlled to rotate by the second reversing valve; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and the first oil duct on the rotation drift valve is closed after a second preset time, so that the second reversing valve is delayed from the first reversing valve to be closed.

Here, in this embodiment, based on the first control mode, the damping function of the first oil passage of the swing drift valve may be utilized to buffer the swing start of the boom on the working machine and the stop swing of the boom, so as to ensure the stop stability of the boom and prevent a large impact from occurring when the swing is stopped. Wherein, the first preset time and the second preset time can be set to be 8-15s, for example: 8s, 12s, 15s, etc., and are not particularly limited herein.

Further, the control method shown in this embodiment further includes: initiating a second control mode for the hydraulic rotary valve: inputting pilot oil with a first preset pressure to a left pilot oil port on the hydraulic rotary valve to control the rotation of the rotation driving equipment; when the angle detection device monitors rotation information of the rotation driving device, the second oil duct of the rotation drift valve is controlled to be conducted, pilot oil with second preset pressure is input to a second reversing valve through the second oil duct, the second preset pressure is larger than the first preset pressure, and then the first reversing valve controls rotation of the rotation driving device; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, after the rotation driving equipment stops rotating, the second oil duct of the rotation drift valve is controlled to be closed, so that the oil way of the rotation drift valve is switched to the first oil duct from the second oil duct, the second reversing valve is pushed to a middle position, and the O-shaped middle position function design of the second reversing valve can be utilized to prevent the arm support from sliding and rotating when the operation machinery stays on a ramp.

Here, the angle detection device shown in the present embodiment monitors the rotation information of the swing drive apparatus, and it can be understood that when the pilot oil of the first preset pressure is input to the left pilot oil port of the hydraulic swing valve, the angle detection device monitors the information that the hydraulic oil pump rotates again by the preset angle in the same rotation direction based on the original rotation angle.

The embodiment is based on the second control mode, the opening state of the second reversing valve can be locked in the rotation process of the boom, and an operator can directly control the rotation of the rotation driving device through the first reversing valve, so that the hydraulic rotary valve works in the rotation drifting mode, and the rotation motion of the boom of the working machine is efficiently controlled.

Further, the control method shown in this embodiment further includes: activating a third control mode for the hydraulic rotary valve: pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate; when the angle detection device monitors rotation information of the rotary driving equipment, controlling the oil way of the damping slip valve to be communicated; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the oil way of the damping slip valve is controlled to be closed after the third preset time. Wherein, the third preset time may be 8 to 15s, for example: 8s, 12s, 15s, etc., and are not particularly limited herein.

Here, in this embodiment, the rotation of the upper boom of the working machine may be stopped through the third control mode, and when the first directional valve returns to the neutral position, based on the delayed closing of the oil passage on the damping slip valve, the oil pressures of the first working oil port a1 and the second working oil port B1 may be equalized to control the boom of the working machine to slowly rotate until the boom is stopped, so that the rotation of the boom is buffered, and a large impact is prevented from occurring when the rotation is stopped.

Further, the control method shown in this embodiment further includes: initiating a fourth control mode for the hydraulic rotary valve: pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate, and the rotary booster valve is controlled to be closed in the process of rotating the rotary driving equipment; when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the rotation pressurizing valve is controlled to be opened until the rotation driving equipment stops rotating.

Here, in this embodiment, the swing of the upper boom of the working machine may be stopped and controlled through the fourth control mode, and under the condition that the pressure of the left pilot oil port pa is relieved, the oil pressure on the first working oil port a1 or the second working oil port B1 may be reduced by unloading the swing pressurization valve, so as to control the boom of the working machine to swing slowly until stopping, thereby implementing the buffer control on the swing of the boom and preventing a large impact from occurring when the swing is stopped.

Finally, it should be noted that the embodiment may also be designed to prevent misoperation, and in the case that the inclination angle of the whole machine of the working machine relative to the horizontal plane is greater than 3 degrees, the embodiment may control the hydraulic swing system of the working machine to forcibly switch to the first control mode.

Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.

Claims (12)

1. A hydraulic rotary valve, comprising:

the first reversing valve and the second reversing valve are connected in series, and the second reversing valve is used for being connected with a rotary driving device;

the left pilot oil port is communicated with the left pilot end of the first reversing valve and the left pilot end of the second reversing valve respectively, and the right pilot oil port is communicated with the right pilot end of the first reversing valve and the right pilot end of the second reversing valve respectively;

the rotary drift valve comprises a first oil duct, and the first oil duct is communicated between the left pilot oil port and the left pilot end of the first reversing valve; the first oil passage is in delayed conduction under the condition that oil pressure is established at the left pilot oil port, and the first oil passage is in delayed closing under the condition that the pressure is released at the left pilot oil port.

2. A hydraulic rotary valve as claimed in claim 1,

further comprising: the first end of the shuttle valve and the second end of the shuttle valve are respectively communicated with the two working oil ports of the second reversing valve, the third end of the shuttle valve is communicated with the oil inlet of the hydraulic rotary valve through the damping slip valve, and the oil path on the damping slip valve is closed in a delayed mode under the condition that the pressure of the left pilot oil port is relieved.

3. A hydraulic rotary valve as claimed in claim 1,

further comprising: and the rotary booster valve is arranged between at least one of the two working oil ports of the second reversing valve and the oil return port of the hydraulic rotary valve, and an oil path on the rotary booster valve is communicated under the condition of releasing pressure to the left pilot oil port.

4. A hydraulic rotary valve as claimed in claim 1,

the rotary drift valve further comprises a second oil duct, and the second oil duct is used for communicating a pilot pressure oil source and the left pilot end of the second reversing valve; the rotary drift valve can realize oil path switching between the first oil path and the second oil path.

5. A hydraulic rotary valve as claimed in any one of claims 1 to 4,

further comprising: the check valve is arranged on a first valve rod of the first reversing valve so as to control the directional conduction from an oil port P to an oil port A of the first reversing valve or control the directional conduction from the oil port P to an oil port B of the first reversing valve;

and/or under the condition that the first valve rod of the first reversing valve is positioned at the middle position, the oil port T of the first reversing valve is respectively communicated with the oil port P, the oil port A and the oil port B of the first reversing valve; and under the condition that the second valve rod of the second reversing valve is positioned at the middle position, the oil port P and the oil port A of the second reversing valve are cut off, and the oil port T and the oil port B of the second reversing valve are cut off.

6. A hydraulic swing system, comprising:

a swing drive device;

a hydraulic rotary valve as claimed in any one of claims 1 to 5, wherein the two working ports of said second direction valve are respectively in communication with said rotary drive means.

7. The hydraulic swing system of claim 6,

the swing drive apparatus includes a hydraulic oil pump; the hydraulic oil pump is provided with an angle detection device, the angle detection device is used for detecting the rotating speed of a rotor of the hydraulic oil pump, and the angle detection device is respectively in communication connection with the rotary drift valve, the damping slip valve and the rotary pressurization valve.

8. A work machine, comprising:

a hydraulic rotary valve as claimed in any one of claims 1 to 5, or a hydraulic rotary system as claimed in claim 6 or 7.

9. A control method of a hydraulic swing system according to claim 6 or 7, comprising: initiating a first control mode for the hydraulic rotary valve;

pilot oil is input into a left pilot oil port on the hydraulic rotary valve, a first oil duct of the rotary drift valve is conducted after first preset time, so that a second reversing valve is delayed to be opened compared with the first reversing valve, and the rotary driving equipment is controlled to rotate by the second reversing valve;

when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and the first oil duct on the rotation drift valve is closed after a second preset time, so that the second reversing valve is delayed from the first reversing valve to be closed.

10. The control method of the hydraulic swing system according to claim 9, further comprising: initiating a second control mode for the hydraulic rotary valve;

inputting pilot oil with a first preset pressure to a left pilot oil port on the hydraulic rotary valve to control the rotary driving device to rotate;

when the angle detection device monitors rotation information of the rotation driving equipment, controlling the conduction of a second oil duct of the rotation drift valve, inputting pilot oil with second preset pressure to a second reversing valve through the second oil duct, wherein the second preset pressure is greater than the first preset pressure, and controlling the rotation of the rotation driving equipment through the first reversing valve;

when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and after the rotation of the rotation driving equipment is stopped, the second oil duct of the rotation drift valve is controlled to be closed, so that the oil way of the rotation drift valve is switched from the second oil duct to the first oil duct, and the second valve rod of the second reversing valve is pushed to the middle position.

11. The control method of the hydraulic swing system according to claim 9, further comprising: initiating a third control mode for the hydraulic rotary valve;

pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate;

when the angle detection device monitors rotation information of the rotary driving equipment, controlling the oil way of the damping slip valve to be communicated;

when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the oil way of the damping slip valve is controlled to be closed after the third preset time.

12. The control method of the hydraulic swing system according to claim 9, further comprising: initiating a fourth control mode for the hydraulic rotary valve;

pilot oil is input to a left pilot oil port on the hydraulic rotary valve to control the rotary driving equipment to rotate, and a rotary pressurization valve is controlled to be closed in the rotation process of the rotary driving equipment;

when the rotation driving equipment is controlled to stop rotating, the pressure of the left pilot oil port is relieved, and then the rotation pressurization valve is controlled to be opened until the rotation driving equipment stops rotating.

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