Hydraulic rotary valve, hydraulic rotary system, control method and operating machinery

Abstract

The present 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 in series with the first reversing valve, and the second reversing valve is used to connect a rotary drive device; the left pilot oil port is respectively connected to the left pilot end of the first reversing valve and the left pilot end of the second reversing valve, and the right pilot oil port is respectively connected to the right pilot end of the first reversing valve and the right pilot end of the second reversing valve; the rotary drift valve comprises a first oil passage, and the first oil passage is connected between the left pilot oil port and the left pilot end of the first reversing valve; when the left pilot oil port establishes oil pressure, the first oil passage is delayed to be turned on, and when the left pilot oil port is depressurized, the first oil passage is delayed to be closed. The present invention can safely and stably control the start and stop of the boom through the hydraulic rotary valve, so that the boom of the operating machine achieves better rotary performance.

Description

Technical Field

[0001] The present invention relates to the technical field of hydraulic rotary control, and in particular to a hydraulic rotary valve, a hydraulic rotary system, a control method and an operating machine. Background Art

[0002] At present, cranes, concrete pump trucks, fire trucks and other working machines are usually equipped with booms, which perform the swing function under the drive of the hydraulic swing system on the working machine. For example, in the hydraulic swing of a crawler crane, the operator pushes the swing valve core to open by manipulating the hydraulic control handle, thereby driving the operation of the swing assembly corresponding to the boom.

[0003] However, in actual working conditions, especially when the operating machine operates the boom on a slope, the boom tends to rotate in the opposite direction when the rotation starts, and when the boom is stopped, a large impact will be generated, which will cause safety risks such as boom shaking and twisting. Therefore, in a slope environment, it is difficult for the operating machine to start and stop the boom safely and stably, and the rotation performance is greatly limited. Summary of the invention

[0004] The present invention provides a hydraulic rotary valve, a hydraulic rotary system, a control method and an operating machine, which are used to solve the problem that it is difficult for the existing operating machine to safely and stably start and stop the boom through the hydraulic rotary valve in a slope environment.

[0005] The present invention provides a hydraulic rotary valve, comprising: a first reversing valve, a second reversing valve, a left pilot oil port, a right pilot oil port and a rotary drift valve; the first reversing valve and the second reversing valve are connected in series, and the second reversing valve is used to connect a rotary drive device; the left pilot oil port is respectively connected to the left pilot end of the first reversing valve and the left pilot end of the second reversing valve, and the right pilot oil port is respectively connected to the right pilot end of the first reversing valve and the right pilot end of the second reversing valve; the rotary drift valve is installed 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 channel, and the first oil channel is connected between the left pilot oil port and the left pilot end of the first reversing valve; when the oil pressure is established at the left pilot oil port, the first oil channel is delayed to be opened, and when the pressure at the left pilot oil port is relieved, the first oil channel is delayed to be closed.

[0006] A hydraulic rotary valve provided according to the present invention also includes: a damping sliding valve and a shuttle valve, the first end of the shuttle valve and the second end of the shuttle valve are respectively connected to the two working oil ports of the second reversing valve, the third end of the shuttle valve is connected to the oil inlet of the hydraulic rotary valve through the damping sliding valve, and when the left pilot oil port is depressurized, the oil circuit on the damping sliding valve is delayed in closing.

[0007] A hydraulic rotary valve provided according to the present invention also includes: a rotary booster valve, which is installed between at least one of the two working oil ports of the second reversing valve and the return oil port of the hydraulic rotary valve, and when the left pilot oil port is depressurized, the oil circuit on the rotary booster valve is connected.

[0008] According to a hydraulic rotary valve provided by the present invention, the rotary drift valve also includes a second oil channel, and the second oil channel is used to connect the pilot pressure oil source and the left pilot end of the second reversing valve; the rotary drift valve can realize oil circuit switching between the first oil channel and the second oil channel.

[0009] A hydraulic rotary valve provided according to the present invention also includes a one-way valve, which is installed on the first valve stem of the first reversing valve to control the directional conduction of the oil port P of the first reversing valve to the oil port A or control the directional conduction of the oil port P of the first reversing valve to the oil port B; and / or, when the first valve stem of the first reversing valve is in a neutral position, the oil port T of the first reversing valve is respectively connected to the oil port P, oil port A and oil port B of the first reversing valve; when the second valve stem of the second reversing valve is in a neutral position, the oil port P of the second reversing valve is cut off from the oil port A, and the oil port T of the second reversing valve is cut off from the oil port B.

[0010] A hydraulic rotary valve provided according to the present invention further includes: an overflow valve, wherein the oil inlet of the hydraulic rotary valve is connected to the oil return port of the hydraulic rotary valve.

[0011] The present invention further provides a hydraulic rotary system, comprising: a rotary drive device and the hydraulic rotary valve as described above, wherein the two working oil ports of the second reversing valve are respectively connected to the rotary drive device.

[0012] According to a hydraulic rotary system provided by the present invention, the rotary drive equipment includes a hydraulic oil pump; the hydraulic oil pump is equipped with an angle detection device, the angle detection device is used to detect the rotation speed of the rotor of the hydraulic oil pump, and the angle detection device is respectively communicated with the rotary drift valve, the damping sliding valve and the rotary boost valve.

[0013] The present invention also provides an operating machine, comprising: the hydraulic rotary valve as described above, or the hydraulic rotary system as described above.

[0014] The present invention also provides a control method for the hydraulic rotary system as described above, comprising: starting a first control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve, and the first oil channel of the rotary drift valve is connected after a first preset time, so that the second reversing valve is opened later than the first reversing valve, and the second reversing valve is used to control the rotation of the rotary drive device; when controlling the rotary drive device to stop rotating, firstly depressurizing the left pilot oil port, and the first oil channel on the rotary drift valve is closed after a second preset time, so that the second reversing valve is closed later than the first reversing valve.

[0015] The control method of the hydraulic rotary system provided in the present invention also includes: starting a second control mode of the hydraulic rotary valve: inputting a pilot oil of a first preset pressure into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device; when the angle detection device monitors the rotation information of the rotary drive device, controlling the second oil channel of the rotary drift valve to be connected, inputting a pilot oil of a second preset pressure into the second reversing valve through the second oil channel, the second preset pressure being greater than the first preset pressure, and then controlling the rotation of the rotary drive device through the first reversing valve; when controlling the rotary drive device to stop rotating, firstly relieving the pressure on the left pilot oil port, and after the rotary drive device stops rotating, controlling the second oil channel of the rotary drift valve to be closed, so that the oil route of the rotary drift valve is switched from the second oil channel to the first oil channel, and pushing the second reversing valve to the middle position.

[0016] The control method of the hydraulic rotary system provided by the present invention also includes: starting a third control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device; when the angle detection device monitors the rotation information of the rotary drive device, controlling the oil circuit of the damping sliding valve to be open; when controlling the rotary drive device to stop rotating, first relieving the pressure on the left pilot oil port, and then controlling the oil circuit of the damping sliding valve to be closed after a third preset time.

[0017] The control method of the hydraulic rotary system provided in the present invention also includes: starting the fourth control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device, and during the rotation of the rotary drive device, controlling the rotary boost valve to close; when controlling the rotary drive device to stop rotating, firstly relieving the pressure on the left pilot oil port, and then controlling the opening of the rotary boost valve until the rotary drive device stops rotating.

[0018] The present invention provides a hydraulic rotary valve, a hydraulic rotary system, a control method and an operating machine. By arranging a first reversing valve, a second reversing valve and a rotary drift valve on the hydraulic rotary valve, when the pilot oil is introduced into the left pilot oil port, based on the damping effect of the first oil channel on the rotary drift valve, the second reversing valve can be delayed in opening after the first reversing valve, so as to control the boom of the operating machine to start smoothly and ensure the safety of the operating machine starting the boom rotation on a slope; at the same time, when controlling the boom to stop rotating, based on the damping effect of the first oil channel on the rotary drift valve, the second reversing valve can be delayed in closing after the first reversing valve, so as to realize buffering control of the boom rotation, thereby ensuring the stability of the boom stopping and preventing a large impact when stopping the rotation.

[0019] It can be seen that the operating machine shown in the present invention can safely and stably start and stop the rotation of the boom through the hydraulic rotary valve in a slope environment, so that the boom of the operating machine can achieve better rotation performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] In order to more clearly illustrate the technical solutions in the present invention or the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0021] Figure 1 It is a schematic diagram of the cross-sectional structure of the hydraulic rotary valve provided by the present invention;

[0022] Figure 2 It is a structural schematic diagram of the hydraulic rotary system provided by the present invention;

[0023] Figure 3 It is a structural schematic diagram of a first valve stem on a first reversing valve provided by the present invention;

[0024] Figure 4 It is a structural schematic diagram of the first reversing valve provided by the present invention when the first valve stem is in a neutral position in the first reversing valve;

[0025] Figure 5 It is a structural schematic diagram of the first valve stem provided by the present invention when it moves from the middle position to the right by a first preset distance so that the oil port P of the first reversing valve is isolated from the oil port A;

[0026] Figure 6 It is a structural schematic diagram of the first valve stem provided by the present invention moving rightward from the middle position by a second preset distance, so that the oil port B of the first reversing valve is isolated from the oil port T, and the one-way valve from the oil port P to the oil port B is opened;

[0027] Figure 7It is a structural schematic diagram of the first valve stem provided by the present invention when it moves from the middle position to the right by a third preset distance so that the oil port P of the first reversing valve is cut off from the oil port T on the left side of the middle position shoulder;

[0028] Figure 8 It is a structural schematic diagram of a valve body where a first reversing valve provided by the present invention is located;

[0029] Fig. 9 is a structural schematic diagram of a second valve stem on a second reversing valve provided by the present invention;

[0030] Fig.10 It is a structural schematic diagram of the second reversing valve provided by the present invention when the second valve stem is in a middle position in the second reversing valve;

[0031] Fig.11 It is a structural schematic diagram of a valve body provided by the present invention where a second reversing valve is located;

[0032] Reference numerals:

[0033] 100: first reversing valve; 200: second reversing valve; 300: valve body;

[0034] 1: first valve stem; 2: first valve stem cavity; 3: second valve stem;

[0035] 4: Second valve stem chamber; 5: Swing drift valve; 6: Damping sliding valve;

[0036] 7: Shuttle valve; 8: Rotary booster valve; 9: Relief valve;

[0037] 400: rotary drive device; 10: middle shaft shoulder; 11: first oil groove;

[0038] 12: first shaft shoulder; 13: second oil groove; 14: second shaft shoulder;

[0039] 101: balancing oil groove; 102: first oil guide groove; 103: second oil guide groove;

[0040] 121: oil guide structure; 131: oil outlet; 141: oil inlet;

[0041] 20: middle cavity section; 21: first sealing section; 22: first cavity section;

[0042] 23: second sealing section; 24: second cavity section; 25: third sealing section;

[0043] 26: third cavity section; 27: fourth sealing section; 1410: first oil inlet;

[0044] 1411: second oil inlet; 320: middle shaft shoulder section; 321: first oil groove section;

[0045] 322: first shaft shoulder section; 323: second oil groove section; 324: second shaft shoulder section;

[0046] 310: first oil port; 311: second oil port; 312: third oil port;

[0047] 313: first oil guide structure; 314: second oil guide structure; 410: middle sealing chamber;

[0048] 411: first cavity; 412: first sealed cavity; 413: second cavity;

[0049] 414: Second sealed chamber. DETAILED DESCRIPTION

[0050] In order to make the purpose, technical solution and advantages of the present invention clearer, the technical solution of the present invention will be clearly and completely described below in conjunction with the drawings of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0051] Combine the following Figure 1-Figure 11 The present invention describes a hydraulic rotary valve, a hydraulic rotary system, a control method and a working machine.

[0052] like Figure 1 to Figure 2 As shown, this embodiment provides a hydraulic rotary valve, including: an oil inlet P, an oil return port T, a first working oil port A1 and a second working oil port B1.

[0053] Furthermore, the hydraulic rotary valve further comprises: 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. Among them, the oil port P of the first reversing valve 100 is connected to the oil inlet P, the oil port T of the first reversing valve 100 is connected to the oil return port T, and the two working oil ports of the first reversing valve 100 are respectively represented as oil port A and oil port B, and the oil port A and the oil port B are connected to the oil port P and the oil port T of the second reversing valve 200 in a one-to-one correspondence. Correspondingly, the oil port P of the second reversing valve 200 is Figure 1 The oil port A of the first reversing valve 100 is connected to the oil port T of the second reversing valve 200. Figure 1 The middle mark is B, and is connected to the oil port B of the first reversing valve 100 to realize the series connection of the second reversing valve 200 and the first reversing valve 100 .

[0054] At the same time, the two working oil ports of the second reversing valve 200 are oil port A and oil port B respectively, and the oil port A of the second reversing valve 200 is connected with the first working oil port A1, and the oil port B of the second reversing valve 200 is connected with the second working oil port B1, and the first working oil port A1 and the second working oil port B1 are used to connect with the rotary drive device 400.

[0055] like Figure 2 As shown, the left pilot oil port pa shown in this embodiment is respectively connected to the left pilot end of the first reversing valve 100 and the left pilot end of the second reversing valve 200, and the right pilot oil port pb is respectively connected to the right pilot end of the first reversing valve 100 and the right pilot end of the second reversing valve 200.

[0056] The swing drift valve 5 shown in this embodiment includes a first oil passage, which is connected between the left pilot oil port pa and the left pilot end of the first reversing valve 100. When the left pilot oil port pa builds up oil pressure, the first oil passage is opened with delay, and when the left pilot oil port pa is depressurized, the first oil passage is closed with delay.

[0057] As can be seen from the above, in this embodiment, the first reversing valve 100, the second reversing valve 200 and the reversing drift valve 5 are arranged on the hydraulic reversing valve. When the pilot oil is introduced into the left pilot oil port pa so that the oil pressure is established at the left pilot oil port pa, the pilot oil will simultaneously push the first valve stem on the first reversing valve 100 and the second valve stem on the second reversing valve 200 to move under the action of the oil pressure of the pilot oil. However, due to the damping effect of the first oil channel on the reversing drift valve 5, the second reversing valve 200 can be delayed in opening after the first reversing valve 100, so as to control the boom of the operating machine to start smoothly and ensure the safety of the operating machine starting the boom rotation on the slope.

[0058] At the same time, when the boom is controlled to stop rotating, the left pilot oil port pa can be depressurized, and under the damping action of the first oil channel on the rotary drift valve 5, the first valve stem on the first reversing valve 100 can be returned to the middle position earlier than the second valve stem on the second reversing valve 200, that is, the second reversing valve 200 is closed later than the first reversing valve 100, so as to realize buffering control of the rotation of the boom, ensure the stability of the boom stopping, and prevent a large impact when stopping the rotation.

[0059] It can be seen that the working machine shown in this embodiment can safely and stably start and stop the rotation of the boom through the hydraulic rotary valve in a slope environment, so that the boom of the working machine can achieve better rotation performance.

[0060] Combine the following Figures 3 to 8 , the first reversing valve 100 is described in detail as follows.

[0061] Figure 3The first valve stem of the first reversing valve 100 provided in this embodiment is a schematic structural diagram. The rod body of the first valve stem 1 is provided with a middle shaft shoulder 10, a first oil groove 11, a first shaft shoulder 12, a second oil groove 13 and a second shaft shoulder 14 in sequence, and the first oil groove 11, the first shaft shoulder 12, the second oil groove 13 and the second shaft shoulder 14 are symmetrically arranged on both sides of the middle shaft shoulder 10.

[0062] At the same time, the first valve stem 1 shown in this embodiment is also provided with an oil inlet 141, an oil outlet 131, an oil guide structure 121 and a throttling structure; the oil inlet 141 is constructed on the side wall of the second shaft shoulder 14, and the oil outlet 131 is constructed on the second oil groove 13, and the oil outlet 131 is connected to the oil inlet 141; wherein, the diameter of the oil outlet 131 is larger than the diameter of the oil inlet 141, which can effectively prevent the oil pressure from rising after the hydraulic oil is transported from the oil inlet 141 to the oil outlet 131.

[0063] It should be noted 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 the diameter of the second oil inlet 1411; along the axial direction of the first valve stem 1, the distance between the first oil inlet 1410 and the center shaft shoulder 10 is greater than the distance between the second oil inlet 1411 and the center shaft shoulder 10. In this way, based on the improvement of the oil inlet 141, the oil guide gap between the oil inlet 141 and the oil outlet 131 can be gradually increased during the movement of the first valve stem 1 to the right station.

[0064] Preferably, in this embodiment, a one-way valve is provided in the rod body of the first valve stem 1, and the one-way valve is connected between the oil inlet 141 and the oil outlet 131 to control the flow of hydraulic oil from the oil inlet 141 to the oil outlet 131. Figure 3 Not specifically shown.

[0065] Here, by setting a one-way valve, when the first valve stem 1 moves to the right position, the hydraulic oil can only flow from the oil port P of the first reversing valve 100 to the oil port B. At the same time, when the first valve stem 1 moves to the left position, the hydraulic oil can only flow from the oil port P of the first reversing valve 100 to the oil port A, thereby realizing directional flow control of the hydraulic oil. Since the rotation of the boom is controlled by the hydraulic motor on the operating machine, when the operating machine is in a slope environment, the directional control of the hydraulic motor can be performed based on the first reversing valve 100 to prevent the boom from sliding down the slope.

[0066] Furthermore, the oil guide structure 121 shown in this embodiment is constructed on the side wall of the first shoulder 12 , the first end of the oil guide structure 121 is formed near the middle of the first shoulder 12 , and the second end is formed at one end of the first shoulder 12 away from the middle shoulder 10 .

[0067] like Figure 3As shown, in order to facilitate the oil guiding structure 121 to better guide the hydraulic oil to flow along the side wall of the first shaft 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 stem 1, and the oil guiding structure 121 includes an oil passing surface or an oil groove, and the radial distance of the second end of the oil guiding structure 121 relative to the central axis of the first valve stem 1 is smaller than the radial distance of the first end of the oil guiding structure 121 relative to the central axis of the first valve stem 1.

[0068] Furthermore, the throttling structure shown in this embodiment is constructed on the side wall of the median shoulder 10 , and the throttling structure extends from the middle of the median shoulder 10 or a position close to the middle of the median shoulder 10 to at least one end of the median shoulder 10 .

[0069] like Figure 3 As shown, in a specific embodiment, the throttling structure includes a balancing oil groove 101, which extends axially along the first valve stem 1, and the first end of the balancing oil groove 101 is formed at one end of the center shoulder 10, and the second end is formed at the other end of the center shoulder 10.

[0070] like Figure 3 As shown, in another specific embodiment, the throttling structure includes a first oil guide groove 102 and a second oil guide groove 103; the first oil guide groove 102 and the second oil guide groove 103 extend along the axial direction of the first valve stem 1; the first end of the first oil guide groove 102 is formed in the middle of the center shoulder 10, and the second end is formed at one end of the center shoulder 10; the first end of the second oil guide groove 103 is formed in the middle of the center shoulder 10, and the second end is formed at the other end of the center shoulder 10.

[0071] As can be seen from the above, this embodiment sets the oil inlet 141 on the second shoulder 14 of the first valve stem 1 and sets the oil outlet 131 on the second oil groove 13. Therefore, when the reversing valve control of the first reversing valve 100 is performed, it is convenient to supply oil to the oil inlets 141 at both ends of the first valve stem 1 and the position of the middle shoulder 10 in the middle through the oil supply port of the first reversing valve 100 at the same time. When returning the oil through the oil guide structure 121, based on the throttling effect of the oil guide structure 121, it is possible to balance the oil pressure in the first oil groove 11 on both sides of the middle shoulder 10, and control the amount of oil diverted from the oil supply port to the oil return port of the first reversing valve 100, thereby ensuring the stability of the oil return of the hydraulic system and realizing smooth control of the rotary action of the hydraulic motor.

[0072] Combine the following Figures 3 to 8 The throttling effect of the throttling structure during the movement of the first valve stem 1 to the right position in the first reversing valve 100 is described in detail.

[0073] like Figure 4 and Figure 8As shown, since the first reversing valve 100 and the second reversing valve 200 are integrated on the same valve body 300, the first reversing valve 100 is constructed in the first valve stem cavity 2 in the valve body 300, and the first valve stem 1 as described above is slidably installed in the first valve stem cavity 2.

[0074] The first valve stem cavity 2 shown in this 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 connected in sequence; 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 both sides of the middle cavity section 20.

[0075] like Figure 4 As shown, when the first valve stem 1 is in the middle position, the middle shoulder 10 is built into the middle cavity section 20. At this time, in the direction perpendicular to the axial direction of the first valve stem 1, the axial symmetry plane of the first valve stem 1 coincides with the axial symmetry plane of the first valve stem cavity 2 in the first reversing valve 100. At the same time, the end of the first shoulder 12 away from the middle shoulder 10 is sealed with the second sealing section 23, and the end of the first shoulder 12 close to the middle shoulder 10 is located in the first cavity section 22. The first end of the oil guide structure 121 on the first valve stem 1 is connected to the first cavity section 22, and the second end of the oil guide structure 121 is connected to the second cavity section 24. The second shoulder 14 is contact-sealed with the third sealing section 25 and the fourth sealing section 27 at the same time. The oil inlet P is respectively connected to the middle cavity section 20 and the third cavity section 26, and the oil outlet 131 is connected to the second cavity section 24.

[0076] like Figure 4 As shown, when the first valve stem 1 is in the middle position, based on the setting of the oil guide structure 121, the second cavity segment 24 on the left side of the middle cavity segment 20 can be connected with the first cavity segment 22 on the left side of the middle cavity segment 20, and the second cavity segment 24 on the right side of the middle cavity segment 20 is connected with the first cavity segment 22 on the right side of the middle cavity segment 20, so that the oil port A of the first reversing valve is connected with the oil port T of the first reversing valve, and the oil port B of the first reversing valve is connected with the oil port T of the first reversing valve.

[0077] like Figure 4 As shown, when the first valve stem 1 is in the middle position, based on the setting of the throttling structure, the middle cavity section 20 can be connected with the first sealing sections 21 on its left and right sides respectively, so that the oil port P of the first reversing valve is connected with the oil port T of the first reversing valve.

[0078] Although a one-way valve is further provided between the oil inlet 141 and the oil outlet 131 of the first valve stem 1 in this embodiment, when the first valve stem 1 is in the middle position, since the oil port A of the first reversing valve is connected to the oil port T, the oil port B is connected to the oil port T, and the oil port T is connected to the oil port P, the oil pressure at both ends of the one-way valve on the left rod body of the first valve stem 1 is the same, and the oil pressure at both ends of the one-way valve on the right rod body of the first valve stem 1 is also the same, so that when the first valve stem 1 is in the middle position, the oil port P of the first reversing valve is cut off from the oil port A, and the oil port P of the first reversing valve is cut off from the oil port B.

[0079] like Figure 4 As shown, when the first valve stem 1 is in the middle position, the distance from the end of the oil inlet 141 away from the middle shoulder 10 to the end of the second cavity segment 24 close to the middle cavity segment 20 is a first preset distance, which can be specifically set to 0.5 mm; the distance from the first end of the oil guide structure 121 to the end of the first cavity segment 22 away from the middle cavity segment 20 is a second preset distance, which can be specifically set to 1.0 mm; the distance between the end of the first shoulder 12 close to the middle shoulder 10 and the first cavity segment 22 away from the middle cavity segment 20 is a third preset distance, which can be specifically set to 2.1 mm.

[0080] like Figure 5 , Figure 8 As shown, when the first valve stem 1 moves a first preset distance to the right from the middle position, based on the sealing effect of the third sealing segment 25 on the oil inlet 141, the oil port P of the first reversing valve 100 can be isolated from the oil port A. At this time, the oil port P of the first reversing valve 100 is connected to the oil port T. However, since the oil port T of the first reversing valve 100 is connected to the oil port B, the oil port P and the oil port B of the first reversing valve 100 are still in a cut-off state.

[0081] like Figure 6 , Figure 8 As shown, when the first valve stem 1 continues to move rightward from the first preset distance to the second preset distance, based on the sealing effect of the second sealing section 23 on the oil guide structure 121, the oil port B of the first reversing valve 100 is isolated from the oil port T, and the one-way valve from the oil port P to the oil port B of the first reversing valve 100 is opened.

[0082] like Figure 7 , Figure 8As shown, when the first valve stem 1 continues to move rightward from the second preset distance to the third preset distance, the end of the first shoulder 12 on the left side close to the middle shoulder 10 begins to seal with the end of the first sealing section 21 away from the middle cavity section 20, so that the oil port P of the first reversing valve 100 is separated from the oil port T on the left side of the middle shoulder 10, and the hydraulic oil in the oil port P begins to enter the first oil groove 11 on the right side of the middle shoulder 10 through the second oil guide groove 103, and the oil port P of the first reversing valve 100 begins to build pressure. As the first valve stem 1 continues to move rightward, the corresponding oil guide gap of the second oil guide groove 103 gradually decreases, that is, the P / T speed regulation stage is entered, so that the hydraulic motor can be gradually accelerated, thereby realizing smooth control of the rotary action of the hydraulic motor.

[0083] Combine the following Figures 9 to 11 , the second reversing valve 200 is described in detail as follows.

[0084] Fig. 9 The schematic diagram of the structure of the second valve stem on the second reversing valve 200 provided in this embodiment. The rod body of the second valve stem 3 is provided with a middle shaft shoulder section 320, a first oil groove section 321, a first shaft shoulder section 322 and a second oil groove section 323 in sequence; the first oil groove section 321, the first shaft shoulder section 322 and the second oil groove section 323 are symmetrically arranged on both sides of the middle shaft shoulder section 320; the side wall of the first shaft shoulder section 322 is configured with a first oil port 310 and a first oil guide structure 313, the second oil groove section 323 is configured with a second oil port 311, and the second oil port 311 is connected to the first oil port 310; the first end of the first oil guide structure 313 is formed near the middle of the first shaft shoulder section 322, and the second end is formed at one end of the first shaft shoulder section 322 close to the middle shaft shoulder section 320.

[0085] Furthermore, a second oil guide structure 314 is also configured on the side wall of the first shoulder section 322 shown in this embodiment. The second oil guide structure 314 includes a plurality of second oil guide structures 314, which are arranged on both sides of the radial plane where the middle of the first shoulder section 322 is located. The first end of the second oil guide structure 314 is formed near the middle of the first shoulder section 322, and the second end is formed on one end of the first shoulder section 322 close to the middle shoulder section 320 or one end away 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.

[0086] Specifically, when the second valve stem 3 shown in the present embodiment performs reversing valve control of the oil circuit based on the first oil guide structure 313, it can also speed up the oil supply and return of the corresponding oil circuit with the assistance of the second oil guide structure 314. Since the plurality of second oil guide structures 314 are arranged on both sides of the radial plane where the middle part of the first shoulder section 322 is located, the pressure difference at both ends of the first shoulder section 322 can be avoided from being too large to cause fluctuations at the moment the oil circuit is connected, thereby making the movement of the buffer valve stem during reversing valve control smoother and smoother, so as to better drive the action of the hydraulic motor and other actuators.

[0087] Furthermore, at least one of the first oil guiding structure 313 and the second oil guiding structure 314 shown in this embodiment extends along the axial direction of the second valve stem 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.

[0088] Furthermore, if Fig. 9 As shown, the side wall of the first shaft shoulder section 322 shown in this embodiment is also configured with a third oil port 312, which is connected to the second oil port 311; along the axial direction of the second valve stem 3, the third oil port 312 is located between the first oil port 310 and the end of the first shaft shoulder section 322 away from the middle shaft shoulder section 320. In this way, as the second valve stem 3 moves to the left or right position, after the first oil port 310 is connected to the second oil port 311, the third oil port 312 will also be connected to the second oil port 311, so that the gap between the first cavity 411 and the second cavity 413 on the oil return side gradually increases.

[0089] Furthermore, the second reversing valve 200 shown in this embodiment includes a second valve stem cavity 4 constructed in the valve body 300, and the second valve stem 3 as described above is slidably installed in the second valve stem cavity 4.

[0090] like Figure 10 to Figure 11 As shown, the second valve stem chamber 4 shown in this embodiment includes a middle sealing chamber 410, a first cavity 411, a first sealing chamber 412 and a second cavity 413 which are connected in sequence, and the first cavity 411, the first sealing chamber 412 and the second cavity 413 are symmetrically arranged on both sides of the middle sealing chamber 410; the middle axial shoulder section 320 of the second valve stem 3 is sealed with the middle sealing chamber 410, and the first axial shoulder section 322 is sealed with the first sealing chamber 412.

[0091] Furthermore, when the second valve stem 3 is in the middle position in the second valve stem cavity 4, the distance between the first oil port 310 and the end of the first cavity 411 away from the middle sealing 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 sealing cavity 410.

[0092] The first oil-through groove section 321 and the second oil-through groove section 323 shown in this embodiment are both annular grooves constructed on the rod body of the second valve stem 3. The second valve stem cavity 4 shown in this embodiment also includes a second sealing cavity 414, and two second sealing cavities 414 are symmetrically arranged on both sides of the middle sealing cavity 410; one end of the second sealing cavity 414 is connected with one end of the second cavity body 413 away from the middle sealing cavity 410; the rod body of the second valve stem 3 is also provided with a second shaft shoulder section 324, and two second shaft shoulder sections 324 are symmetrically arranged on both sides of the middle shaft shoulder section 320, and one end of the second shaft shoulder section 324 is connected with one end of the second oil-through groove section 323 away from the middle shaft shoulder section 320; the second shaft shoulder section 324 is sealed and matched with the second sealing cavity 414.

[0093] When the second valve stem 3 is in the middle position, the middle shaft shoulder section 320 on the second valve stem 3 is sealed with the middle sealing cavity 410, and the first shaft shoulder section 322 on the second valve stem 3 is sealed with the first sealing cavity 412, so that the first cavity 411 is isolated from the second cavity 413. In this way, when the second reversing valve 200 is applied to an operating machine, when the operating machine is in an environment with a certain slope, the second valve stem 3 isolates the hydraulic oil between the first cavity 411 and the second cavity 413, so that the oil pressure on the oil circuit of the actuator of the operating machine can be ensured to be stable, and the arm connected to the actuator can be effectively prevented from sliding down the slope.

[0094] It should be pointed out here that the actuator shown in this embodiment is specifically a hydraulic motor, which is used to drive the revolving platform to rotate, and the boom is installed on the revolving platform.

[0095] like Fig.10 As shown, when the second valve stem 3 is in the middle position, the first oil port 310 and the end of the first cavity 411 away from the middle sealing cavity 410 form a distance of L1, and the first end of the first oil guide structure 313 and the end of the second cavity 413 close to the middle sealing cavity 410 form a distance of L2, and L1 is smaller than L2. Among them, L1 can be 1mm-1.5mm, for example: L1 is specifically 1.0mm, 1.2mm, 1.5mm, etc., which is not specifically limited here; L2 can be 2mm-2.5mm, L2 is specifically 2.0mm, 2.2mm, 2.5mm, etc., which is not specifically limited here.

[0096] In this way, when the rotation of the hydraulic motor is controlled by the second reversing valve 200 in this embodiment, based on the valve control action of the second valve stem 3, the first cavity 411 and the second cavity 413 on the oil inlet side can be opened to a small degree before being connected, thereby effectively preventing the second reversing valve 200 from having a back pressure problem at the moment the hydraulic motor is turned on, thereby achieving stable control of the hydraulic motor and ensuring the service life of the second reversing valve 200.

[0097] Combination Figure 6 and Fig.10 It can be seen that when the pilot oil is introduced into the left pilot oil port pa of the hydraulic rotary valve to establish oil pressure at the left pilot oil port pa, the pilot oil will simultaneously push the first valve stem on the first reversing valve 100 and the second valve stem on the second reversing valve 200 to move under the action of the oil pressure of the pilot oil. However, due to the damping effect of the first oil passage on the rotary drift valve 5, the second valve stem on the second reversing valve 200 will start to move to the right only when the first valve stem on the first reversing valve 100 moves to the right by the second preset distance, so that the second reversing valve 200 can be opened later than the first reversing valve 100. In this process, the return oil gap on the return oil side of the first reversing valve 100 gradually increases, and the conduction gap on the oil inlet side of the second reversing valve 200 also gradually increases, so as to control the boom of the operating machine to start smoothly and ensure the safety of the operating machine starting the boom rotation on the ramp.

[0098] Correspondingly, the left pilot oil port pa is pressure-relieved. Due to the damping effect of the first oil channel on the rotary drift valve 5, the first valve stem on the first reversing valve 100 can return to the middle position earlier than the second valve stem on the second reversing valve 200, that is, the second reversing valve 200 is closed later than the first reversing valve 100, so as to achieve buffering control of the rotation of the boom, ensure the stability of the boom stopping, and prevent a large impact when stopping the rotation.

[0099] Preferably, if Figure 2 As shown, the rotary drift valve 5 shown in this embodiment also includes a second oil passage, which is used to connect the pilot pressure oil source and the left pilot end of the second reversing valve 200. The rotary drift valve 5 can realize the switching between the first oil passage and the second oil passage. Figure 2 In the figure, the pilot pressure oil source is represented by pa'.

[0100] Specifically, the swing drift valve 5 shown in this embodiment can be connected to a control system, and the control system can be an electric control button, a touch screen controller, etc. In this embodiment, the coil of the swing drift valve 5 can be energized by the control system to make the second oil passage of the swing drift valve 5 open 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.

[0101] Therefore, in this embodiment, when the second oil passage of the rotary drift valve 5 is connected, when the pilot oil is introduced into the left pilot end of the second reversing valve 200 through the pilot pressure oil source, the open state of the second reversing valve 200 can be locked, and the operator can directly control the rotation of the rotary drive device through the first reversing valve 100, so that the hydraulic rotary valve works in the rotary drift mode, and the rotary movement of the arm of the operating machinery can be efficiently controlled.

[0102] Furthermore, if Figure 2 As shown, the present embodiment is further provided with a damping sliding valve 6 and a shuttle valve 7. The first end of the shuttle valve 7 shown in the present embodiment is connected to the first working oil port A1, the second end of the shuttle valve 7 is connected to the second working oil port B1, and the third end of the shuttle valve 7 is connected to the oil inlet P through the damping sliding valve 6. When the left pilot oil port is depressurized so that the first valve stem of the first reversing valve 100 is in the middle position, the oil circuit on the damping sliding valve 6 is closed with delay. Therefore, when the present embodiment controls the boom to stop rotating, based on the delayed closing of the oil circuit on the damping sliding valve 6, the oil pressure on the first working oil port A1 and the second working oil port B1 can be balanced, so as to control the boom of the working machine to rotate slowly until it stops, thereby achieving buffer control on the rotation of the boom and preventing a large impact when the rotation stops.

[0103] Furthermore, if Figure 2 As shown, this embodiment is also provided with a rotary booster valve 8. A rotary booster valve 8 is installed between at least one of the first working oil port A1 and the second working oil port B1 and the oil return port T. Figure 2 As shown, a rotary boosting valve 8 is installed between the first working oil port A1, the second working oil port B1 and the return oil port T shown in this embodiment. When the left pilot oil port is depressurized so that the first valve stem of the first reversing valve 100 is in the middle position, the oil circuit on the rotary boosting valve 8 is connected. In this way, when the swing of the boom of the working machine is stopped, when 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 boosting valve 8 to control the boom of the working machine to slowly swing until it stops, thereby achieving buffer control of the swing of the boom and preventing a large impact when the swing stops.

[0104] Furthermore, if Figure 2 As shown, this embodiment is also provided with a relief valve 9, and the oil inlet P is connected to the oil return port T. In this way, when the oil pressure of the oil inlet P is too high, the relief valve 9 opens to protect the first reversing valve 100 and the second reversing valve 200.

[0105] As can be seen from the above, by setting a one-way valve on the first reversing valve 100, this embodiment can prevent the rotary pressure from being insufficient to overcome the slope resistance when the hydraulic rotary system is turned uphill with a small opening, so as to start and prevent the hydraulic rotary system from slipping. By designing the second reversing valve 200 with an O-type neutral function, this embodiment can use the second reversing valve 200 to prevent the rotary system from slipping when the working machine stays on the slope. At the same time, based on the design of the rotary drift valve 5, the damping sliding valve 6 and the rotary boosting valve 8, this embodiment further realizes the buffering function of multiple modes of the boom in different application scenarios on the basis of anti-slip.

[0106] Furthermore, if Figure 2 As shown, this embodiment also provides a hydraulic rotary system, including: a rotary drive device and the hydraulic rotary valve as described above, wherein the first working oil port A1 and the second working oil port B1 on the hydraulic rotary valve are respectively connected to the rotary drive device.

[0107] Specifically, the slewing drive device shown in this embodiment includes a hydraulic oil pump; the hydraulic oil pump is used to drive the rotation of the turntable on the slewing assembly of the working machinery. Since the arm of the working machinery is installed on the turntable, the hydraulic oil pump can realize the rotation control of the arm under the control of the hydraulic slewing valve.

[0108] Furthermore, the hydraulic oil pump shown in this embodiment is equipped with an angle detection device, wherein the angle detection device can be an encoder known in the art, the encoder is coaxially mounted on the rotor of the hydraulic oil pump to detect the rotation speed of the rotor of the hydraulic oil pump.

[0109] The hydraulic rotary system shown in this embodiment may also be provided with a control module, which may be a single chip microcomputer or a PLC controller known in the art. When controlling the working state of the hydraulic rotary valve, this embodiment may connect the angle detection device to the control module for communication, and the control module controls the energization state of the coils on the rotary drift valve, the damping sliding valve, and the rotary boost valve in real time based on the rotation information of the hydraulic oil pump monitored by the angle detection device, so as to control the opening and closing states of the rotary drift valve, the damping sliding valve, and the rotary boost valve in real time.

[0110] Furthermore, this embodiment also provides a working machine, including: the hydraulic rotary valve as described above, or the hydraulic rotary system as described above.

[0111] The operating machinery shown in this embodiment includes mechanical equipment such as cranes with a rotation function, concrete pump trucks, fire trucks, etc., which are not specifically limited here.

[0112] Furthermore, the present embodiment also provides a control method for the hydraulic rotary system as described above, and the control method includes: starting a first control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve, and the first oil channel of the rotary drift valve is opened after a first preset time, so that the second reversing valve is opened later than the first reversing valve, and the second reversing valve is used to control the rotation of the rotary drive device; when controlling the rotary drive device to stop rotating, the left pilot oil port is first depressurized, and the first oil channel on the rotary drift valve is closed after a second preset time, so that the second reversing valve is closed later than the first reversing valve.

[0113] Here, based on the first control mode, this embodiment can utilize the damping effect of the first oil passage of the swing drift valve to buffer the swing start of the boom on the working machine and the stop swing of the boom, thereby ensuring the stability of the boom stop and preventing a large impact when the boom stops. The first preset time and the second preset time can be set to 8-15s, for example: 8s, 12s, 15s, etc., which are not specifically limited here.

[0114] Furthermore, the control method shown in this embodiment also includes: starting a second control mode for the hydraulic rotary valve: inputting a pilot oil of a first preset pressure into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device; when the angle detection device monitors the rotation information of the rotary drive device, controlling the second oil channel of the rotary drift valve to be opened, inputting a pilot oil of a second preset pressure into the second reversing valve through the second oil channel, the second preset pressure being greater than the first preset pressure, and then controlling the rotation of the rotary drive device through the first reversing valve; when controlling the rotary drive device to stop rotating, firstly relieving the pressure on the left pilot oil port, and after the rotation of the rotary drive device stops, controlling the second oil channel of the rotary drift valve to be closed, so that the oil route of the rotary drift valve is switched from the second oil channel to the first oil channel, pushing the second reversing valve to the middle position, and the O-type middle position function design of the second reversing valve can be used to prevent the boom from sliding down the slope and rotating when the operating machinery stays on the slope.

[0115] Here, the angle detection device shown in this embodiment monitors the rotation information of the rotary drive equipment, which can be understood as, when the pilot oil of the first preset pressure is input into the left pilot oil port on the hydraulic rotary valve, the angle detection device monitors the information that the hydraulic oil pump rotates again in the same rotation direction by a preset angle based on the original rotation angle.

[0116] Based on the second control mode, this embodiment can lock the open state of the second reversing valve during the boom rotation process. The operator can directly control the rotation of the rotary drive device through the first reversing valve, so that the hydraulic rotary valve works in the rotary drift mode, thereby efficiently controlling the rotary movement of the boom of the operating machinery.

[0117] Furthermore, the control method shown in this embodiment also includes: starting the third control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device; when the angle detection device monitors the rotation information of the rotary drive device, controlling the oil circuit of the damping sliding valve to be open; when controlling the rotary drive device to stop rotating, firstly relieving the pressure of the left pilot oil port, and then controlling the oil circuit of the damping sliding valve to be closed after a third preset time. The third preset time can be 8-15s, for example: 8s, 12s, 15s, etc., which is not specifically limited here.

[0118] Here, this embodiment can stop the rotation of the boom on the operating machine through the third control mode. When the first reversing valve returns to the center position, based on the delayed closing of the oil circuit on the damping sliding valve, the oil pressure on the first working oil port A1 and the second working oil port B1 can be balanced to control the boom of the operating machine to rotate slowly until it stops, thereby achieving buffering control of the rotation of the boom and preventing a large impact when stopping the rotation.

[0119] Furthermore, the control method shown in this embodiment also includes: starting the fourth control mode of the hydraulic rotary valve: inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotation of the rotary drive device, and during the rotation of the rotary drive device, controlling the rotary boost valve to close; when controlling the rotary drive device to stop rotating, first release the pressure on the left pilot oil port, and then control the opening of the rotary boost valve until the rotary drive device stops rotating.

[0120] Here, this embodiment can stop the rotation of the boom on the working machine through the fourth control mode. When 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 swing booster valve to control the boom of the working machine to rotate slowly until it stops, thereby achieving buffering control of the rotation of the boom and preventing a large impact when stopping the rotation.

[0121] Finally, it should be pointed out that the present embodiment can also be designed to prevent misoperation. When the inclination angle of the whole operating machine relative to the horizontal plane is greater than 3 degrees, the present embodiment can control the hydraulic rotary system of the operating machine to forcibly switch to the first control mode.

[0122] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A hydraulic rotary valve, characterized in that: include: A first reversing valve and a second reversing valve, wherein the first reversing valve and the second reversing valve are connected in series, and the second reversing valve is used to connect a rotary drive device; A left pilot oil port and a right pilot oil port, the left pilot oil port is respectively connected to the left pilot end of the first reversing valve and the left pilot end of the second reversing valve, and the right pilot oil port is respectively connected to the right pilot end of the first reversing valve and the right pilot end of the second reversing valve; The rotary drift valve comprises a first oil passage, wherein the first oil passage is connected between the left pilot oil port and the left pilot end of the second reversing valve; when the oil pressure is established in the left pilot oil port, the first oil passage is delayed to be opened, and when the pressure in the left pilot oil port is released, the first oil passage is delayed to be closed; The first reversing valve and the second reversing valve are both three-position four-way valves, the middle position function of the first reversing valve is H type, and the middle position function of the second reversing valve is O type; the hydraulic rotary valve includes an oil inlet P, an oil return port T, a first working oil port A1 and a second working oil port B1, the oil port P of the first reversing valve is connected to the oil inlet P, the oil port T of the first reversing valve is connected to the oil return port T, the two working oil ports of the first reversing valve are connected to the oil port P and the oil port T of the second reversing valve in a one-to-one correspondence, the two working oil ports of the second reversing valve are connected to the first working oil port A1 and the second working oil port B1 in a one-to-one correspondence, and the first working oil port A1 and the second working oil port B1 are used to communicate with the rotary drive device; It also includes: a damping sliding valve and a shuttle valve, wherein the first end of the shuttle valve and the second end of the shuttle valve are respectively connected to the two working oil ports of the second reversing valve, and the third end of the shuttle valve is connected to the oil inlet of the hydraulic rotary valve through the damping sliding valve, and when the left pilot oil port is depressurized, the oil circuit on the damping sliding valve is closed with a delay; It also includes: a rotary boosting valve, wherein the rotary boosting valve is installed between at least one of the two working oil ports of the second reversing valve and the return oil port of the hydraulic rotary valve, and the oil circuit on the rotary boosting valve is connected when the left pilot oil port is depressurized; when the rotary drive device is stopped and the left pilot oil port is depressurized, the rotary boosting valve is unloaded to reduce the oil pressure at the first working oil port A1 or the second working oil port B1; The rotary drift valve also includes a second oil channel, which is used to connect the pilot pressure oil source and the left pilot end of the second reversing valve; the rotary drift valve can realize oil circuit switching between the first oil channel and the second oil channel. When the second oil channel of the rotary drift valve is connected, the hydraulic rotary valve operates in a rotary drift mode.

2. The hydraulic rotary valve according to claim 1, characterized in that: It also includes: a one-way valve, which is installed on the first valve stem of the first reversing valve to control the directional conduction from the oil port P of the first reversing valve to the oil port A or to control the directional conduction from the oil port P of the first reversing valve to the oil port B; And / or, when the first valve stem of the first reversing valve is in the middle position, the oil port T of the first reversing valve is respectively connected to the oil port P, oil port A and oil port B of the first reversing valve; when the second valve stem of the second reversing valve is in the middle position, the oil port P of the second reversing valve is cut off from the oil port A, and the oil port T of the second reversing valve is cut off from the oil port B.

3. A hydraulic rotary system, characterized in that: include: Rotary drive equipment; According to the hydraulic rotary valve as described in any one of claims 1 to 2, the two working oil ports of the second reversing valve are respectively connected to the rotary drive device.

4. The hydraulic rotary system according to claim 3, characterized in that: The rotary drive device includes a hydraulic oil pump; the hydraulic oil pump is equipped with an angle detection device, the angle detection device is used to detect the rotation speed of the rotor of the hydraulic oil pump, and the angle detection device is respectively communicated with the rotary drift valve, the damping sliding valve and the rotary boost valve.

5. A working machine, characterized in that: include: A hydraulic rotary valve as claimed in any one of claims 1 to 2, or a hydraulic rotary system as claimed in claim 3 or 4.

6. A control method for a hydraulic rotary system according to claim 3 or 4, characterized in that: include: Starting a first control mode of the hydraulic rotary valve; The pilot oil is input into the left pilot oil port on the hydraulic rotary valve, and the first oil passage of the rotary drift valve is opened after a first preset time, so that the second reversing valve is opened later than the first reversing valve, and the rotary drive device is controlled by the second reversing valve to rotate; When the rotary drive device is controlled to stop rotating, the left pilot oil port is first depressurized, and the first oil passage on the rotary drift valve is closed after a second preset time, so that the second reversing valve is closed later than the first reversing valve.

7. The control method of the hydraulic rotary system according to claim 6, characterized in that: Also includes: Starting a second control mode for the hydraulic rotary valve; Inputting pilot oil of a first preset pressure into the left pilot oil port on the hydraulic rotary valve to control the rotary drive device to rotate; When the angle detection device monitors the rotation information of the rotary drive device, the second oil passage of the rotary drift valve is controlled to be open, and the pilot oil of the second preset pressure is input to the second reversing valve through the second oil passage, wherein the second preset pressure is greater than the first preset pressure, and the rotary drive device is controlled to rotate through the first reversing valve; When controlling the rotary drive device to stop rotating, the left pilot oil port is first depressurized. After the rotary drive device stops rotating, the second oil channel of the rotary drift valve is controlled to be closed, so that the oil channel of the rotary drift valve is switched from the second oil channel to the first oil channel, and the second valve stem of the second reversing valve is pushed to the middle position.

8. The control method of the hydraulic rotary system according to claim 6, characterized in that: Also includes: Starting the third control mode of the hydraulic rotary valve; Inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotary drive device to rotate; When the angle detection device detects the rotation information of the rotary drive device, the oil circuit of the damping sliding valve is controlled to be open; When the rotary drive device is controlled to stop rotating, the left pilot oil port is firstly depressurized, and then the oil circuit of the damping sliding valve is controlled to be closed after a third preset time has passed.

9. The control method of the hydraulic rotary system according to claim 6, characterized in that: Also includes: Starting a fourth control mode for the hydraulic rotary valve; Inputting pilot oil into the left pilot oil port on the hydraulic rotary valve to control the rotary drive device to rotate, and during the rotation of the rotary drive device, controlling the rotary booster valve to close; When the rotary drive device is controlled to stop rotating, the left pilot oil port is firstly depressurized, and then the rotary booster valve is controlled to open until the rotary drive device stops rotating.

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