CN115370628A - Rotary hydraulic system, rotary device and working machine - Google Patents

Abstract

The invention relates to the field of engineering machinery, and provides a rotary hydraulic system, a rotary device and an operating machine, including a hydraulic motor, a main reversing valve, a rotary buffer valve and a pilot oil pipeline. The main reversing valve is used to switch the direction of rotation of the hydraulic motor. The rotary buffer valve includes two secondary pressure relief valves, and the oil inlets of the relief valves of the two secondary pressure relief valves are respectively connected to the hydraulic oil pipeline between the main reversing valve and the hydraulic motor. The pilot oil pipelines are respectively connected with the liquid control ports of the relief valves of the two secondary pressure relief valves. When starting, the pilot oil pipeline controls the opening pressure of the two-stage supercharging relief valve on the oil inlet side to reach the first opening pressure, and the opening pressure of the two-stage supercharging relief valve on the oil return side remains at the second opening pressure. Since the first cracking pressure is relatively large, a relatively large starting torque can be provided for the hydraulic motor. During slewing braking, because the second cracking pressure is relatively small, it can provide a low-pressure buffer for the hydraulic motor stall.

Description

Swing Hydraulics, Swing Units and Work Machinery

technical field

The invention relates to the technical field of engineering machinery, in particular to a rotary hydraulic system, a rotary device and an operating machine.

Background technique

At present, in the slewing device of construction machinery equipment, a large number of hydraulic circuits with buffer function are used, such as excavator slewing device, crane slewing device, aerial vehicle slewing device, manipulator slewing device and agricultural and forestry machinery slewing device, etc. The slewing buffer is in It plays an important role in the rotary hydraulic system.

In the prior art, the rotary buffer system is generally connected to the working oil port of the hydraulic motor through a relief valve and a one-way valve to realize the buffer function. When the slewing device is slewing at high speed, the system pressure value is very high, and when idling slewing, the system pressure value is very low. In order to meet the two working conditions, the setting pressure of the relief valve is based on the pressure required for high-speed slewing, but in When braking, the hydraulic motor rotates at idle speed, and the impact pressure of the system is not enough to overcome the opening pressure of the relief valve, causing the relief valve to be in a normally closed state, which cannot effectively realize the buffering function.

Contents of the invention

The invention provides a rotary hydraulic system, a rotary device and a working machine to solve the problem that in the prior art, the setting pressure of the overflow valve is based on the pressure required for high-speed rotation, resulting in a relatively large opening pressure. , the impact pressure of the system cannot top open the relief valve, and thus cannot effectively realize the defect of the buffer function, and realize the effect that the opening pressure of the relief valve is controllable.

The invention provides a rotary hydraulic system, comprising: a hydraulic motor; a main reversing valve, the two working oil ports of the main reversing valve communicate with the two motor working oil ports of the hydraulic motor in one-to-one correspondence; the rotary buffer The rotary buffer valve includes two secondary pressure relief valves, and the oil inlets of the relief valves of the two secondary pressure relief valves are respectively connected between the main reversing valve and the hydraulic motor. On the two hydraulic oil pipelines between; the pilot oil pipeline, the pilot oil pipeline is respectively connected with the relief valve liquid control ports of the two secondary pressure relief valves; when the relief valve liquid control port is connected with the When the pilot oil pipeline is connected, the opening pressure of the corresponding two-stage booster relief valve is the first opening pressure; when the liquid control port of the relief valve is disconnected from the pilot oil pipeline, the corresponding The cracking pressure of the two-stage pressure relief valve is the second cracking pressure, wherein the first cracking pressure is greater than the second cracking pressure.

According to the rotary hydraulic system provided by the present invention, the pilot oil pipeline includes: two reversing valves, each of which is provided with a pilot oil inlet, a pilot oil return port and a pilot oil outlet ; Pilot oil inlet pipeline, the pilot oil inlet pipeline is connected with the pilot oil inlet of the two reversing valves respectively; Pilot oil return pipeline, the pilot oil return pipeline is respectively connected with two The pilot oil return port of the reversing valve is connected; the pilot oil outlet pipeline, the pilot oil outlets of the two reversing valves are connected to the two two pilot oil outlets through the pilot oil outlet pipeline. The liquid control ports of the relief valves of the stage pressure relief valves are communicated in one-to-one correspondence.

According to the rotary hydraulic system provided by the present invention, the main reversing valve is a hydraulic control reversing valve, and the two pilot oil outlet pipelines communicate with the two hydraulic control ports of the main reversing valve in one-to-one correspondence.

According to the rotary hydraulic system provided by the present invention, the main reversing valve is an electronically controlled reversing valve.

According to the rotary hydraulic system provided by the present invention, the main reversing valve is a three-position four-way reversing valve, and when the three-position four-way reversing valve is located at the first working position and the second working position, the three-position four-way The oil supply direction of the three-position four-way reversing valve is opposite, and when the three-position four-way reversing valve is in the third working position, both the oil supply and the oil return of the three-position four-way reversing valve are cut off.

According to the rotary hydraulic system provided by the present invention, it also includes an oil supply pipeline, the two oil outlet ends of the oil supply pipeline are respectively connected with the two motor working oil ports of the hydraulic motor, and the oil supply pipeline can be selected Supplement oil to one of the motor working oil ports of the hydraulic motor.

According to the rotary hydraulic system provided by the present invention, the oil supply pipeline includes: a main oil supply pipe, the oil inlet end of the main oil supply pipe communicates with the hydraulic oil source; two sub oil supply pipes, the oil inlet of the two sub oil supply pipes Both ends communicate with the oil outlet of the main oil supply pipe, the oil outlet ends of the two sub oil supply pipes communicate with the two motor working ports of the hydraulic motor respectively, and each of the sub oil supply pipes Both are connected with a one-way valve, and the flow direction of the one-way valve is from the oil inlet end of the sub oil supply pipe where it is located to the oil outlet end.

According to the rotary hydraulic system provided by the present invention, the number of the hydraulic motors is two or more, and the two or more hydraulic motors are connected in parallel.

The present invention also provides a slewing device, including the slewing hydraulic system described in any one of the above items.

The present invention also provides a work machine, comprising the swing hydraulic system described in any one of the above or including the swing device described above.

The rotary hydraulic system provided by the invention includes a hydraulic motor, a main reversing valve, a rotary buffer valve and a pilot oil pipeline. The two working oil ports of the main reversing valve communicate with the two motor working oil ports of the hydraulic motor one by one, and the main reversing valve is used to control the start and stop of the hydraulic motor, and is used to switch the rotation direction of the hydraulic motor. The rotary buffer valve includes two secondary pressure relief valves, and the oil inlets of the relief valves of the two secondary pressure relief valves are respectively connected to the hydraulic oil pipeline between the main reversing valve and the hydraulic motor. The pilot oil pipelines are respectively connected with the liquid control ports of the relief valves of the two secondary pressure relief valves. When working, the main reversing valve controls the oil on one side of the hydraulic motor and the oil on the other side, and the pilot oil pipeline controls the opening pressure of the two-stage booster relief valve connected to the hydraulic oil pipeline on the oil inlet side to reach the first level. Opening pressure, the opening pressure of the secondary pressure relief valve on the oil return side is still maintained at the second opening pressure. Since the first cracking pressure is relatively large, the oil pressure on the oil inlet side is relatively large, which can provide a large starting torque for the hydraulic motor. During slewing braking, since the second opening pressure is relatively small, the return oil on the oil return side can overcome the second opening pressure, and the oil can be unloaded through the two-stage pressure relief valve on the oil return side, which can be used for the hydraulic motor. Stall provides cushioning, allowing the hydraulic motor to brake smoothly at low pressure. The rotary hydraulic system provided by the present invention uses a hydraulically controlled two-stage supercharging relief valve to control the opening pressure of the two-stage supercharging relief valve on the oil inlet side and the oil return side through the pilot oil pipeline, so that the hydraulic motor It can not only start under high torque, but also achieve smooth braking under low pressure.

Further, the slewing device and the working machine provided by the present invention have the same advantages as the slewing hydraulic system as described above.

Description of drawings

In order to more clearly illustrate the present invention or the technical solutions in the prior art, the accompanying drawings that need to be used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the accompanying drawings in the following description are the For some embodiments of the present invention, those of ordinary skill in the art can also obtain other drawings based on these drawings on the premise of not paying creative efforts.

Fig. 1 is a schematic diagram of the principle of the rotary hydraulic system provided by the present invention;

Reference signs:

100: rotary buffer valve; 110: first and second stage pressure relief valve; 120: second stage and two stage pressure relief valve; 200: hydraulic motor; 300: main reversing valve; 400: pilot oil pipeline; 410: The first reversing valve; 420: the second reversing valve; 430: the pilot oil inlet pipeline; 440: the pilot oil return pipeline; 450: the first pilot oil outlet pipeline; 460: the second pilot oil outlet pipeline; 510: main oil supply pipe; 520: sub-oil oil supply pipe; 521: one-way valve; P: oil inlet; T: oil return port; A: first working oil port; B: second working oil port; a: first b: the second hydraulic control port; C ₁ : the working oil port of the first motor; C ₂ : the working oil port of the second motor; e ₁ : the liquid control port of the first relief valve; e ₂ : the second relief valve Flow valve liquid control port; P ₁ : oil inlet of the first relief valve; P ₂ : oil inlet of the second relief valve.

Detailed ways

In order to make the purpose, technical solutions and advantages of the present invention clearer, the technical solutions in the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the present invention. Obviously, the described embodiments are part of the embodiments of the present invention , but not all examples. Based on the embodiments of the present invention, all other embodiments obtained by persons of ordinary skill in the art without creative efforts fall within the protection scope of the present invention.

The slewing hydraulic system, slewing device and working machine of the present invention will be described below with reference to FIG. 1 .

The present invention provides a rotary hydraulic system, which includes a hydraulic motor 200 , a main reversing valve 300 , a pilot oil pipeline 400 and a rotary buffer valve 100 .

The hydraulic motor 200 is used to drive the rotating part of the slewing device to rotate, for example, it can drive the turntable of machines such as excavators, cranes, aerial work vehicles, manipulators or agricultural and forestry machinery to rotate. The number of hydraulic motors 200 can be set to one, two or more. The increase in the number of hydraulic motors 200 can increase the torque, and the rotation requirements under various working conditions can be met by increasing or decreasing the number of hydraulic motors 200 .

The hydraulic motor 200 includes two motor working oil ports, and the two motor working oil ports may be respectively a first motor working oil port C ₁ and a second motor working oil port C ₂ . When the number of hydraulic motors 200 is greater than or equal to two, the first motor working ports _C1 of multiple hydraulic motors 200 are connected at one point, and similarly, the second motor working ports _C2 of multiple hydraulic motors 200 are also connected. At one point, in other words, multiple hydraulic motors 200 are connected in parallel.

The above-mentioned rotary buffer valve 100 includes two two-stage supercharged relief valves, and the two two-stage supercharged relief valves can be respectively the first two-stage supercharged relief valve 110 and the second two-stage supercharged relief valve 120. Referring to Fig. 1, the two-stage supercharging relief valve on the left side in the figure is the first two-stage supercharging relief valve 110, and the two-stage supercharging relief valve on the right is the second two-stage supercharging relief valve 120.

The oil inlet of the relief valve located in the first two-stage pressure relief valve 110 is the oil inlet P ₁ of the first relief valve, and the oil inlet P ₁ of the first relief valve is connected with the first motor working oil of the hydraulic motor 200 Port _C1 is connected. The oil inlet of the relief valve located at the second stage pressure relief valve 120 is the oil inlet P ₂ of the second relief valve, and the oil inlet P ₂ of the second relief valve is connected with the second motor working oil of the hydraulic motor 200 Port C ₂ is connected.

The above-mentioned two-stage supercharging relief valve is also provided with a relief valve liquid control port, and the relief valve liquid control port located on the first two-stage supercharging relief valve 110 can be the first relief valve liquid control port e _1. The pilot port of the relief valve located on the second stage pressure relief valve 120 may be the pilot port e ₂ of the second relief valve.

The pilot oil pipeline 400 can be respectively connected with the first relief valve liquid control port _e1 and the second relief valve liquid control port _e2 , and can be connected to the first relief valve liquid control port _e1 or the second relief valve liquid respectively. Control port e ₂ supplies pilot oil. When the pilot oil pipeline 400 supplies pilot oil to the first relief valve liquid control port _e1 , the cracking pressure of the first two-stage supercharged relief valve 110 reaches the first cracking pressure, which is relatively large and can satisfy hydraulic pressure. The starting demand of the motor 200 . When there is no pilot oil supply in the hydraulic control port _e1 of the first relief valve, the cracking pressure of the first two-stage pressure relief valve 110 is the second cracking pressure, and the second cracking pressure is relatively small, so that the hydraulic motor 200 can Smooth braking under this pressure. For the second two-stage pressure relief valve 120 , its control method is the same as that of the first two stage pressure relief valve 110 , which will not be repeated here.

The two working oil ports of the main reversing valve 300 communicate with the two motor working oil ports of the hydraulic motor 200 in one-to-one correspondence, and are used to switch the flow direction of the hydraulic oil in the hydraulic motor 200, and then control the forward rotation or reverse rotation of the hydraulic motor 200 , and at the same time, the main reversing valve 300 can also block the oil supply to the hydraulic motor 200 and the oil return of the hydraulic motor 200 .

The above-mentioned main reversing valve 300 can be a hydraulic control reversing valve, and the hydraulic control reversing valve can be a three-position four-way reversing valve, which is provided with an oil inlet P, an oil return port T, and two working oil ports. , Two liquid control ports. Wherein, the two working oil ports are respectively the first working oil port A and the second working oil port B, and the two hydraulic control ports are respectively the first hydraulic control port a and the second hydraulic control port b.

Referring to Fig. 1, the oil inlet P located on the left side of the bottom of the main selector valve 300 is the oil return port T located on the right side of the bottom of the main selector valve 300, and the first working port is located on the left side of the top of the main selector valve 300. Oil port A, the second working oil port B on the right side of the top of the main reversing valve 300, the first hydraulic control port a on the left side of the main reversing valve 300, and the second working oil port a on the right side of the main reversing valve 300 Second fluid control port b.

When connected, the first pilot oil outlet pipeline 450 communicates with the second hydraulic control port b, the second pilot oil outlet pipeline 460 communicates with the first hydraulic control port a, the oil inlet P communicates with the hydraulic oil source, and the oil return port T communicates with the hydraulic oil tank, the first working oil port A communicates with the first motor working oil port _C1 of the hydraulic motor 200 , and the second working oil port B communicates with the second motor working oil port _C2 of the hydraulic motor 200 .

When the main reversing valve 300 is in the third working position, that is, in the middle position, the oil inlet P, the oil return port T, the first working oil port A, and the second working oil port B are all blocked. When the main reversing valve 300 is in the first working position, that is, in the left position, the oil inlet P communicates with the first working oil port A, the second working oil port B communicates with the oil return port T, and the hydraulic oil in the hydraulic motor 200 It flows from the first motor working oil port _C1 to the second motor working oil port _C2 . When the main reversing valve 300 is in the second working position, that is, in the right position, the oil inlet P communicates with the second working oil port B, the first working oil port A communicates with the oil return port T, and the hydraulic oil in the hydraulic motor 200 It flows from the second motor working oil port _C2 to the first motor working oil port _C1 .

Of course, the above-mentioned main reversing valve 300 can also be an electronically controlled reversing valve, or a manual reversing valve, which can still realize the reversing effect of the main reversing valve 300 .

In the rotary hydraulic system provided by the present invention, the rotary buffer valve 100 uses a hydraulically controlled two-stage supercharging relief valve, and the opening pressure of the two two-stage supercharging relief valves is controlled through the pilot oil pipeline 400, so that the oil supply side The opening pressure of the two-stage supercharging relief valve is kept at the first opening pressure, so that the opening pressure of the two-stage supercharging relief valve on the oil return side is kept at the second opening pressure, which can realize the high-torque start of the hydraulic motor 200 , and smooth braking of the hydraulic motor 200 can also be achieved.

In one embodiment of the present invention, the pilot oil pipeline 400 includes two reversing valves, a pilot oil inlet pipeline 430 , a pilot oil return pipeline 440 and a pilot oil outlet pipeline.

Wherein, the two reversing valves can be respectively the first reversing valve 410 and the second reversing valve 420, referring to Fig. 1, the one on the left is the first reversing valve 410, and the one on the right is the second reversing valve 420. Both reversing valves can be electronically controlled reversing valves, and the electrically controlled reversing valve can be a two-position three-way reversing valve.

Both reversing valves are provided with a pilot oil inlet, a pilot oil return port and a pilot oil outlet. Wherein the oil inlet end of the pilot oil inlet pipeline 430 communicates with the pilot oil source, and the oil outlet end of the pilot oil inlet pipeline 430 communicates with the pilot oil inlet ports of the two reversing valves respectively. The oil inlet ends of the pilot oil return pipeline 440 communicate with the pilot oil return ports of the two reversing valves respectively.

There are two pilot oil outlet pipelines, and the two pilot oil outlet pipelines may be the first pilot oil outlet pipeline 450 and the second pilot oil outlet pipeline 460 respectively. The oil inlet end of the first pilot oil outlet pipeline 450 communicates with the pilot oil outlet port of the first reversing valve 410 , and the oil outlet end of the first pilot oil outlet pipeline 450 communicates with the second stage pressure relief valve 120 The liquid control port _e2 of the second relief valve is connected. The oil inlet end of the second pilot oil outlet pipeline 460 communicates with the pilot oil outlet port of the second reversing valve 420, and the oil outlet end of the second pilot oil outlet pipeline 460 communicates with the first two-stage pressure relief valve 110. The hydraulic control port _e1 of the first relief valve is connected.

When the first reversing valve 410 is energized, the first reversing valve 410 communicates with the pilot oil inlet pipeline 430 and the first pilot oil outlet pipeline 450. At this time, the pilot oil is supplied to the second two-stage pressure relief valve 120 The hydraulic control port e ₂ of the second relief valve makes the cracking pressure of the second two-stage pressure relief valve 120 reach the first cracking pressure. When the first reversing valve 410 is de-energized, the first reversing valve 410 cuts off the communication between the pilot oil inlet pipeline 430 and the first pilot oil outlet pipeline 450, and the second relief valve 120 of the second stage pressure relief valve 120 The hydraulic control port _e2 of the flow valve is depressurized, and the cracking pressure returns to the second cracking pressure.

Since the two reversing valves are reversing valves with the same structure, only the working process of the first reversing valve 410 will be described here, and the working process of the second reversing valve 420 is the same as that of the first reversing valve 410. Same, no more details here. However, during the working process, one of the first reversing valve 410 and the second reversing valve 420 is electrified.

In one embodiment of the present invention, the slewing hydraulic system further includes an oil supply pipeline, the oil supply pipeline includes two oil outlets, and the oil outlet on the left side communicates with the first motor working oil port _C1 of the hydraulic motor 200 , the oil outlet on the right side communicates with the second motor working oil port C ₂ of the hydraulic motor 200 , and the oil supply line can selectively replenish oil to one of the motor working oil ports of the hydraulic motor 200 .

Specifically, the above oil supply pipeline includes a main oil supply pipe 510 and two sub oil supply pipes 520, the oil inlet end of the main oil supply pipe 510 is connected with the hydraulic oil source, and the oil inlet ends of the two sub oil supply pipes 520 are connected with the main oil supply pipe 510. The oil outlet is connected, the sub-oil supply pipe 520 on the left communicates with the first motor working oil port _C1 of the hydraulic motor 200, and the sub-oil supply pipe 520 on the right communicates with the second motor working oil port _C2 of the hydraulic motor 200 . A one-way valve 521 is also provided on each sub-replenishment pipe 520 , and the flow direction of the one-way valve 521 is from the oil outlet end of the main oil-replenishment pipe 510 to the oil outlet end of the sub-replenishment pipe 520 where it is located. In other words, the flow direction of the one-way valve 521 on the left sub-oil supply pipe 520 faces left, and the flow direction of the one-way valve 521 on the right sub-oil supply pipe 520 faces right.

When the oil supply to the hydraulic motor 200 is stopped, the hydraulic motor 200 will continue to rotate under the effect of the rotational inertia. During the rotation, the hydraulic oil will still be driven to continue to flow. Fill oil at the oil end to prevent the hydraulic motor 200 from sucking air.

The working principle of the rotary hydraulic system will be described below, taking the case where the main reversing valve 300 is in the right position as an example.

When the hydraulic motor 200 needs to be started, the first reversing valve 410 is energized, the second reversing valve 420 remains in a power-off state, and the pilot oil inlet line 430 passes through the pilot oil inlet of the first reversing valve 410 and the first pilot oil inlet. The oil outlet pipeline 450 is connected, and the pilot oil is supplied to the second pilot port b of the main reversing valve 300 and the second pilot port e ₂ of the second two-stage pressure relief valve 120 .

At this time, the pressure on the right side of the spool of the main reversing valve 300 is greater than the pressure on the left side, the spool is pushed to the right position, the oil inlet P of the main reversing valve 300 communicates with the second working oil port B, and the first working Oil port A communicates with oil return port T. Since the hydraulic control port _e2 of the second two-stage pressure relief valve 120 has oil pressure, the opening pressure of the second two-stage pressure relief valve 120 increases to the first opening pressure. The hydraulic control port _e1 of the first two-stage boost relief valve 110 has no oil pressure, so the cracking pressure of the first two-stage boost relief valve 110 remains at the second cracking pressure.

When the oil inlet P of the main reversing valve 300 supplies oil, the hydraulic oil is supplied to the second motor working oil port C2 of the hydraulic motor 200 through the second working oil port _B of the main reversing valve 300. During the oil supply process, The hydraulic oil passes through the second relief valve oil inlet _P2 of the second two-stage pressure relief valve 120, so the pressure of the hydraulic oil supplied to the second motor working oil port _C2 of the hydraulic motor 200 is different from the first cracking pressure Equally, since the first cracking pressure is relatively large, the hydraulic motor 200 can be started with high torque.

The hydraulic oil flows through the second motor working oil port C ₂ of the hydraulic motor 200 to the first motor working oil port C ₁ , and finally returns through the first working oil port A of the main reversing valve 300 through the oil return port T.

When the hydraulic motor 200 brakes, the first reversing valve 410 is de-energized, the second reversing valve 420 remains in a power-off state, the second hydraulic control port b of the main reversing valve 300 loses oil pressure, and the main reversing valve 300 The spring springs the spool back to the neutral position, and at this time, the oil inlet P, the oil return port T, the first working oil port A, and the second working oil port B are all cut off.

At this time, the hydraulic motor 200 continues to rotate under the action of the rotational inertia, and at the same time, the hydraulic motor 200 will drive the hydraulic oil to continuously flow from the second motor working oil port _C2 to the first motor working oil port _C1 . However, at this time, the hydraulic system has stopped supplying oil to the hydraulic motor 200 through the oil inlet P of the main reversing valve 300. In order to prevent the hydraulic motor 200 from sucking air, the oil supply line can be opened, and the hydraulic oil passes through the sub-oil supply line on the right side. 520 supplies oil to the second motor working oil port C ₂ of the hydraulic motor 200 .

At this time, since the return oil of the hydraulic motor 200 cannot return oil from the oil return port T of the main reversing valve 300 , the pressure on the oil return side increases. Since the cracking pressure of the first two-stage boosting relief valve 110 is the second cracking pressure, and the second cracking pressure is relatively low, the hydraulic oil pushes open the first two-stage boosting relief valve 110 to discharge oil and release pressure, thus, The hydraulic motor 200 can be smoothly braked under low oil pressure.

In the prior art, due to the high opening pressure of the relief valve on the oil return side, the pressure on the oil return side is relatively high, and the hydraulic motor 200 is forced to stop, resulting in a large hydraulic impact on the hydraulic motor 200 . The rotary hydraulic system provided by the invention can reduce the oil pressure on the oil return side to realize gentle braking.

The above is the working condition of driving the hydraulic motor 200 to start and brake when the reversing valve 300 is in the right position. Similarly, when the reversing valve is in the left position, the hydraulic motor 200 can be driven to reverse, and its working principle is the same. Therefore, this will not be described in detail.

The present invention also provides a slewing device, which can be an excavator slewing device, a crane slewing device, an aerial work vehicle slewing device, a manipulator slewing device, an agricultural and forestry machine slewing device, etc., since they are all equipped with the above-mentioned slewing hydraulic system, so , with the same advantages as above.

The present invention also provides a working machine, which can be an excavator, a crane, an aerial work vehicle, a manipulator, an agricultural and forestry machine, etc. with a slewing device. Since they all have the above-mentioned slewing hydraulic system or slewing device, they have the same Same advantages as above.

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 them; although the present invention has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that: it can still be Modifications are made to the technical solutions described in the foregoing embodiments, or equivalent replacements are made to some of the technical features; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the various embodiments of the present invention.

Claims (10)

1. A rotary hydraulic system, characterized in that, comprising: hydraulic motor (200); The main reversing valve (300), the two working oil ports of the main reversing valve (300) communicate with the two motor working oil ports of the hydraulic motor (200) in one-to-one correspondence; Rotary buffer valve (100), the rotary buffer valve (100) includes two secondary pressure relief valves, the relief valve oil inlets of the two secondary pressure relief valves are respectively connected to the main on the two hydraulic oil pipelines between the reversing valve (300) and the hydraulic motor (200); Pilot oil pipelines (400), the pilot oil pipelines (400) are respectively connected to the liquid control ports of the relief valves of the two secondary pressure relief valves; When the liquid control port of the relief valve is in communication with the pilot oil pipeline (400), the opening pressure of the corresponding two-stage supercharging relief valve is the first opening pressure, and when the liquid control port of the relief valve When the pilot oil pipeline (400) is disconnected, the opening pressure of the corresponding two-stage supercharging relief valve is the second opening pressure, wherein the first opening pressure is greater than the second opening pressure. 2. The rotary hydraulic system according to claim 1, characterized in that, the pilot oil pipeline (400) comprises: Two reversing valves, each of which is provided with a pilot oil inlet, a pilot oil return port and a pilot oil outlet; A pilot oil inlet pipeline (430), the pilot oil inlet pipeline (430) is respectively communicated with the pilot oil inlets of the two reversing valves; Pilot oil return pipeline (440), the pilot oil return pipeline (440) communicates with the pilot oil return ports of the two reversing valves respectively; Pilot oil outlet pipelines, the pilot oil outlets of the two reversing valves pass through the pilot oil outlet pipelines and the relief valve liquid control ports of the two two-stage booster relief valves One-to-one correspondence connection. 3. The rotary hydraulic system according to claim 2, characterized in that, the main reversing valve (300) is a hydraulic control reversing valve, and the two pilot oil outlet pipelines are connected with the main reversing valve ( 300) of the two liquid control ports are communicated in one-to-one correspondence. 4. The rotary hydraulic system according to claim 1, wherein the main directional valve is an electronically controlled directional valve. 5. The rotary hydraulic system according to claim 3 or 4, characterized in that, the main reversing valve (300) is a three-position, four-way reversing valve, and the three-position, four-way reversing valve is located in the first working position and the second working position, the oil supply direction of the three-position four-way reversing valve is opposite, and when the three-position four-way reversing valve is in the third working position, Both oil and oil return are cut off. 6. The rotary hydraulic system according to claim 1, further comprising an oil supply line, the two oil outlet ends of the oil supply line work with the two motors of the hydraulic motor (200) respectively The oil port is connected, and the oil supply line can selectively supply oil to one of the motor working oil ports of the hydraulic motor (200). 7. The rotary hydraulic system according to claim 6, characterized in that, the oil replenishment pipeline comprises: The main oil supply pipe (510), the oil inlet end of the main oil supply pipe (510) communicates with the hydraulic oil source; Two sub-oil supply pipes (520), the oil inlet ends of the two sub-oil supply pipes (520) are connected with the oil outlet ends of the main oil supply pipe (510), and the outlets of the two sub-oil supply pipes (520) The oil end is respectively communicated with the two motor working ports of the hydraulic motor (200), and each of the sub oil supply pipes (520) is connected with a check valve (521), and the check valve ( 521) flow direction from the oil inlet end of the sub-oil supply pipe (520) where it is located toward the oil outlet end. 8. The rotary hydraulic system according to claim 1, characterized in that, the number of the hydraulic motors (200) is two or more, and the two or more hydraulic motors (200) are connected in parallel. 9. A slewing device, characterized in that it comprises the slewing hydraulic system according to any one of claims 1-8. 10. An operating machine, characterized by comprising the rotary hydraulic system according to any one of claims 1-8 or comprising the rotary device according to claim 9.

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