CN115370628A - Rotary hydraulic system, rotary device and working machine - Google Patents
Rotary hydraulic system, rotary device and working machine Download PDFInfo
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- CN115370628A CN115370628A CN202211060734.XA CN202211060734A CN115370628A CN 115370628 A CN115370628 A CN 115370628A CN 202211060734 A CN202211060734 A CN 202211060734A CN 115370628 A CN115370628 A CN 115370628A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/027—Check valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
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- Fluid Mechanics (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to the field of engineering machinery, and provides a rotary hydraulic system, a rotary device and operating machinery. The main directional control valve is used for switching the rotation direction of the hydraulic motor. The rotary buffer valve comprises two secondary supercharging overflow valves, and overflow valve oil inlets of the two secondary supercharging overflow valves are respectively connected to a hydraulic oil pipeline between the main reversing valve and the hydraulic motor. And the pilot oil pipeline is respectively connected with overflow valve hydraulic control ports of the two secondary supercharging overflow valves. When the starting device is started, the pilot oil pipeline controls the opening pressure of the two-stage supercharging overflow valve on the oil inlet side to reach the first opening pressure, and the opening pressure of the two-stage supercharging overflow valve on the oil return side is kept at the second opening pressure. Due to the large first opening pressure, a large starting torque can be provided for the hydraulic motor. During the slewing brake, the second opening pressure is smaller, so that low-pressure buffering can be provided for the stop of the hydraulic motor.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a rotary hydraulic system, a rotary device and an operation machine.
Background
At present, in a slewing device of engineering machinery equipment, a large number of hydraulic circuits with a buffering function are applied, such as an excavator slewing device, a crane slewing device, an overhead working truck slewing device, a manipulator slewing device, an agricultural and forestry machinery slewing device and the like, and slewing buffering plays an important role in a slewing hydraulic system.
In the prior art, a rotary buffering system is generally communicated with a working oil port of a hydraulic motor through an overflow valve and a check valve so as to realize a buffering function. The slewer is when high-speed gyration, and the system pressure value is very high, and when the idle speed gyration, the system pressure value is very low, and for satisfying two kinds of operating modes, the set pressure of overflow valve is accurate when using high-speed gyration required pressure, but when the braking, hydraulic motor idle speed gyration, the opening pressure of overflow valve is not enough overcome to system impulse pressure, leads to the overflow valve to be the normally closed state, can not effectual realization buffer function.
Disclosure of Invention
The invention provides a rotary hydraulic system, a rotary device and an operation machine, which are used for solving the defects that in the prior art, the set pressure of an overflow valve is based on the pressure required by high-speed rotation, so that the opening pressure is larger, and the system impact pressure cannot jack the overflow valve during idling rotation of a hydraulic motor, so that the buffer function cannot be effectively realized, and the effect of controllable opening pressure of the overflow valve is realized.
The invention provides a rotary hydraulic system, comprising: a hydraulic motor; the two working oil ports of the main reversing valve are communicated with the two motor working oil ports of the hydraulic motor in a one-to-one correspondence manner; the rotary buffer valve comprises two secondary pressurization overflow valves, and overflow valve oil inlets of the two secondary pressurization overflow valves are respectively connected to two hydraulic oil pipelines between the main reversing valve and the hydraulic motor; the pilot oil pipeline is respectively connected with overflow valve hydraulic control ports of the two secondary booster overflow valves; when the overflow valve hydraulic control port is communicated with the pilot oil pipeline, the corresponding opening pressure of the two-stage supercharging overflow valve is a first opening pressure, and when the overflow valve hydraulic control port is disconnected with the pilot oil pipeline, the corresponding opening pressure of the two-stage supercharging overflow valve is a second opening pressure, wherein the first opening pressure is greater than the second opening pressure.
According to the swing hydraulic system provided by the present invention, the pilot oil line includes: the two reversing valves are respectively provided with a pilot oil inlet, a pilot oil return port and a pilot oil outlet; the pilot oil inlet pipeline is respectively communicated with the pilot oil inlets of the two reversing valves; the pilot oil return pipeline is respectively communicated with the pilot oil return ports of the two reversing valves; and the pilot oil outlets of the two reversing valves are correspondingly communicated with the overflow valve hydraulic control ports of the two secondary booster overflow valves one by one through the pilot oil outlet pipelines.
According to the rotary hydraulic system provided by the invention, the main reversing valve is a hydraulic control reversing valve, and the two pilot oil outlet pipelines are communicated with the two hydraulic control ports of the main reversing valve in a one-to-one correspondence manner.
According to the rotary hydraulic system provided by the invention, the main reversing valve is an electric control reversing valve.
According to the rotary hydraulic system provided by the invention, the main reversing valve is a three-position four-way reversing valve, when the three-position four-way reversing valve is positioned at a first working position and a 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 positioned at a third working position, the oil supply and the oil return of the three-position four-way reversing valve are cut off.
The rotary hydraulic system further comprises an oil supplementing pipeline, two oil outlet ends of the oil supplementing pipeline are respectively communicated with two motor working oil ports of the hydraulic motor, and the oil supplementing pipeline can be used for selectively supplementing oil to one of the motor working oil ports of the hydraulic motor.
According to the rotary hydraulic system provided by the invention, the oil supplementing pipeline comprises: the oil inlet end of the main oil supplementing pipe is communicated with a hydraulic oil source; two sub oil supply pipes, two the oil inlet end of the sub oil supply pipe all communicates with the oil outlet end of the main oil supply pipe, two the oil outlet end of the sub oil supply pipe respectively communicate with the two motor working oil ports of the hydraulic motor, and each sub oil supply pipe is connected with a check valve, and the flow direction of the check valve is formed by the oil inlet end of the sub oil supply pipe facing the oil outlet end.
According to the rotary hydraulic system provided by the invention, the number of the hydraulic motors is two or more, and the two or more hydraulic motors are connected in parallel.
The invention also provides a slewing device comprising a slewing hydraulic system as described in any one of the preceding claims.
The invention also provides a working machine comprising a slewing hydraulic system as defined in any one of the preceding claims or comprising a slewing device as defined in the preceding claims.
The invention provides a rotary hydraulic system which comprises a hydraulic motor, a main reversing valve, a rotary buffer valve and a pilot oil pipeline. Two working oil ports of the main reversing valve are communicated with two motor working oil ports of the hydraulic motor in a one-to-one correspondence mode, and the main reversing valve is used for controlling the start and stop of the hydraulic motor and switching the rotating direction of the hydraulic motor. The rotary buffer valve comprises two secondary pressurizing overflow valves, and overflow valve oil inlets of the two secondary pressurizing overflow valves are respectively connected to a hydraulic oil pipeline between the main reversing valve and the hydraulic motor. And the pilot oil pipeline is respectively connected with overflow valve hydraulic control ports of the two secondary booster overflow valves. When the hydraulic motor works, the main reversing valve controls oil inlet at one side of the hydraulic motor and oil return at one side of the hydraulic motor, the pilot oil pipeline controls the opening pressure of the two-stage booster overflow valve connected to the hydraulic oil pipeline at the oil inlet side to reach a first opening pressure, and the opening pressure of the two-stage booster overflow valve at the oil return side is still maintained at a second opening pressure. Because first cracking pressure is great, consequently, the oil pressure of oil feed one side is great, can provide a great starting torque for hydraulic motor. During the rotary braking, the second opening pressure is smaller, so that the oil return at the oil return side can overcome the second opening pressure, the oil is discharged through the two-stage pressure-boosting overflow valve at the oil return side, the buffer can be provided for the stop of the hydraulic motor, and the hydraulic motor can brake slowly under low pressure. The rotary hydraulic system provided by the invention uses the hydraulic-controlled two-stage supercharging overflow valve, and controls the opening pressure of the two-stage supercharging overflow valve at the oil inlet side and the oil return side through the pilot oil pipeline, so that the hydraulic motor can be started under large torque and can realize mild braking under low pressure.
Further, the slewing device and the working machine provided by the invention have the same advantages as described above because the slewing hydraulic system is provided.
Drawings
In order to more clearly illustrate the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the description of the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a schematic diagram of a rotary hydraulic system provided by the present invention;
reference numerals:
100: a rotary cushion valve; 110: a first secondary booster overflow valve; 120: a second two-stage booster overflow valve; 200: a hydraulic motor; 300: a main directional control valve; 400: a pilot oil line; 410: a first direction change valve; 420: a second directional control valve; 430: leading oil enters the oil pipeline; 440: a pilot oil return line; 450: a first pilot oil outlet pipeline; 460: a second pilot oil outlet pipeline; 510: a main oil supply pipe; 520: a sub oil replenishing pipe; 521: a one-way valve; p: an oil inlet; t: an oil return port; a: a first working oil port; b: a second working oil port; a: a first hydraulic control port; b: a second hydraulic control port; c 1 : a first motor working oil port; c 2 : a second motor working oil port; e.g. of the type 1 : a first spill valve hydraulic control port; e.g. of the type 2 : a second spill valve hydraulic control port; p is 1 : an oil inlet of a first overflow valve; p 2 : an oil inlet of the second overflow valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The swing hydraulic system, the swing device, and the work machine of the present invention will be described with reference to fig. 1.
The present invention provides a rotary hydraulic system including a hydraulic motor 200, a main directional control valve 300, a pilot oil line 400, and a rotary cushion valve 100.
The hydraulic motor 200 is used to rotationally drive a rotating part of the slewing device, and may rotationally drive a turntable of a machine such as an excavator, a crane, an aerial work vehicle, a manipulator, or an agricultural or forestry machine. The number of the hydraulic motors 200 can be one, two or more, the increase of the number of the hydraulic motors 200 can improve the torque, and the rotation requirements under various working conditions can be met by increasing and decreasing the number of the hydraulic motors 200.
The hydraulic motor 200 includes two motor working ports, which may be the first motor working port C, respectively 1 And a second motor working oil port C 2 . When the number of the hydraulic motors 200 is greater than or equal to two, the first motor working ports C of the plurality of hydraulic motors 200 1 Second motor working ports C of the plurality of hydraulic motors 200 communicating at one point, likewise 2 Also, in other words, the plurality of hydraulic motors 200 are connected in parallel.
The rotary cushion valve 100 includes two-stage pressure relief valves, which may be a first two-stage pressure relief valve 110 and a second two-stage pressure relief valve 120. Referring to fig. 1, the two-stage supercharging overflow valve located on the left side in the drawing is a first two-stage supercharging overflow valve 110, and the two-stage supercharging overflow valve located on the right side is a second two-stage supercharging overflow valve 120.
The overflow valve oil inlet positioned in the first two-stage supercharging overflow valve 110 is a first overflow valve oil inlet P 1 An oil inlet P of a first overflow valve 1 Working oil port C of the first motor connected to the hydraulic motor 200 1 And (4) communicating. The overflow valve oil inlet positioned at the second two-stage supercharging overflow valve 120 is a second overflow valve oil inlet P 2 And an oil inlet P of a second overflow valve 2 A second motor working oil port C connected with the hydraulic motor 200 2 And (4) communicating.
The two-stage supercharging overflow valve is also provided with an overflow valve hydraulic control port, and the overflow valve hydraulic control port on the first two-stage supercharging overflow valve 110 can be a first overflow valve hydraulic control port e 1 The second relief valve hydraulic control port e may be a relief valve hydraulic control port located on the second two-stage supercharging relief valve 120 2 。
The pilot oil line 400 may be connected to the first spill valve pilot port e 1 And a second relief valve hydraulic control port e 2 Connected to the first overflow valve hydraulic control port e 1 Or second overflow valve hydraulic control port e 2 And supplying pilot oil. When the pilot oil pipeline 400 is towards the first overflow valve hydraulic control port e 1 When pilot oil is supplied, the opening pressure of the first secondary booster relief valve 110 reaches a first opening pressure, which is relatively high, and the starting requirement of the hydraulic motor 200 can be met. When the first overflow valve is in hydraulic control 1 When no pilot oil is supplied, the opening pressure of the first secondary booster relief valve 110 is the second opening pressure, which is relatively low, so that the hydraulic motor 200 can be smoothly braked under the second opening pressure. The second-stage pressure-increasing overflow valve 120 is controlled in the same manner as the first-stage pressure-increasing overflow valve 110, and is not described again here.
The two working oil ports of the main directional control valve 300 are communicated with the two motor working oil ports of the hydraulic motor 200 in a one-to-one correspondence manner, so as to switch the flow direction of hydraulic oil in the hydraulic motor 200, further control the forward rotation or the reverse rotation of the hydraulic motor 200, and meanwhile, the main directional control valve 300 can also block the oil supply to the hydraulic motor 200 and the oil return of the hydraulic motor 200.
The main directional control valve 300 may be a hydraulic control directional control valve, which may be a three-position four-way directional control valve having an oil inlet P, an oil return port T, two working oil ports, and two hydraulic control ports. The two working oil ports are respectively a first working oil port A and a second working oil port B, and the two hydraulic control ports are respectively a first hydraulic control port a and a second hydraulic control port B.
Referring to fig. 1, an oil inlet P is located at the left side of the bottom of the main directional control valve 300, an oil return port T is located at the right side of the bottom of the main directional control valve 300, a first working oil port a is located at the left side of the top of the main directional control valve 300, a second working oil port B is located at the right side of the top of the main directional control valve 300, a first hydraulic control port a is located at the left side of the main directional control valve 300, and a second hydraulic control port B is located at the right side of the main directional control valve 300.
When connected, the first pilot oil outlet pipeline 450 is communicated with the second hydraulic control port b, the second pilot oil outlet pipeline 460 is communicated with the first hydraulic control port a, the oil inlet P is communicated with a hydraulic oil source, the oil return port T is communicated with a hydraulic oil tank, and the first working oil port A is communicated with the first motor working oil port C of the hydraulic motor 200 1 A second working oil port B is communicated with a second motor working oil port C of the hydraulic motor 200 2 And (4) communicating.
When the main directional control valve 300 is located at the third working position, i.e., 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 directional control valve 300 is located at the first working position, i.e., the left position, the oil inlet P is communicated with the first working oil port a, the second working oil port B is communicated with the oil return port T, and the hydraulic oil in the hydraulic motor 200 is communicated with the first motor working oil port C 1 To the second motor working oil port C 2 And (4) flowing. When the main directional control valve 300 is located at the second working position, i.e. the right position, the oil inlet P is communicated with the second working oil port B, the first working oil port a is communicated with the oil return port T, and the hydraulic oil in the hydraulic motor 200 is communicated with the second motor working oil port C 2 To the working oil port C of the first motor 1 And (4) flowing.
Of course, the main directional control valve 300 may also be an electric directional control valve or a manual directional control valve, and the directional control effect of the main directional control valve 300 can still be achieved.
In the rotary hydraulic system provided by the invention, the rotary cushion valve 100 uses the two-stage booster overflow valves capable of being hydraulically controlled, and the pilot oil pipeline 400 is used for controlling the opening pressure of the two-stage booster overflow valves, so that the opening pressure of the two-stage booster overflow valve at the oil supply side is kept at the first opening pressure, and the opening pressure of the two-stage booster overflow valve at the oil return side is kept at the second opening pressure, thereby realizing the large-torque starting of the hydraulic motor 200 and the stable braking of the hydraulic motor 200.
In one embodiment of the present invention, the pilot oil line 400 includes two directional valves, a pilot oil inlet line 430, a pilot oil return line 440, and a pilot oil outlet line.
Wherein the two direction valves can be a first direction valve 410 and a second direction valve 420, respectively, and referring to fig. 1, the first direction valve 410 is positioned at the left side, and the second direction valve 420 is positioned at the right side. The two reversing valves can be electric control reversing valves, and the electric control reversing valves can be two-position three-way reversing valves.
And a pilot oil inlet, a pilot oil return port and a pilot oil outlet are arranged on the two reversing valves. Wherein the oil inlet end of the pilot oil inlet pipeline 430 is communicated with a pilot oil source, and the oil outlet end of the pilot oil inlet pipeline 430 is respectively communicated with the pilot oil inlets of the two reversing valves. The oil inlet end of the pilot oil return line 440 is respectively communicated with the pilot oil return ports of the two directional control valves.
The number of the pilot oil outlet lines is two, and the two pilot oil outlet lines may be a first pilot oil outlet line 450 and a second pilot oil outlet line 460, respectively. The oil inlet end of the first pilot oil outlet pipeline 450 is communicated with the pilot oil outlet of the first reversing valve 410, and the oil outlet end of the first pilot oil outlet pipeline 450 is communicated with the second relief valve hydraulic control port e of the second secondary booster relief valve 120 2 And (4) communicating. The oil inlet end of the second pilot oil outlet pipeline 460 is communicated with the pilot oil outlet of the second reversing valve 420, and the oil outlet end of the second pilot oil outlet pipeline 460 is communicated with the first overflow valve hydraulic control port e of the first secondary booster overflow valve 110 1 And (4) communicating.
When the first direction valve 410 is energized, the first direction valve 410 connects the pilot oil inlet line 430 and the first pilot oil outlet line 450, and at this time, the pilot oil is supplied to the second relief valve hydraulic control port e of the second two-stage booster relief valve 120 2 The opening pressure of the second-stage booster spill valve 120 is brought to the first opening pressure. When the first direction valve 410 is de-energized, the first direction valve 410 cuts off the communication between the pilot oil inlet pipe 430 and the first pilot oil outlet pipe 450, and the second direction valve 410 is openedSecond relief valve hydraulic control port e of stage supercharging relief valve 120 2 And releasing the pressure, and returning the opening pressure to the second opening pressure.
Since the two direction valves are direction valves with the same structure, only the operation process of the first direction valve 410 will be described here, and the operation process of the second direction valve 420 is the same as that of the first direction valve 410, and will not be described here again. However, during operation, the first direction valve 410 and the second direction valve 420 are alternatively energized.
In an embodiment of the present invention, the rotary hydraulic system further includes an oil supply line, the oil supply line includes two oil outlet ends, the oil outlet end located on the left side is connected to the first motor working oil port C of the hydraulic motor 200 1 The oil outlet end on the right side is communicated with the second motor working oil port C of the hydraulic motor 200 2 And the oil supplementing pipeline can be used for selectively supplementing oil to one of the motor working oil ports of the hydraulic motor 200.
Specifically, the oil supply pipeline includes a main oil supply pipe 510 and two sub oil supply pipes 520, an oil inlet end of the main oil supply pipe 510 is communicated with a hydraulic oil source, oil inlet ends of the two sub oil supply pipes 520 are both communicated with an oil outlet end of the main oil supply pipe 510, and the sub oil supply pipe 520 located on the left side is communicated with a first motor working oil port C of the hydraulic motor 200 1 The sub oil compensating pipe 520 on the right side is communicated with the second motor working oil port C of the hydraulic motor 200 2 And (4) communicating. Each sub oil supply pipe 520 is further provided with a check valve 521, and the flow direction of the check valve 521 is from the oil outlet end of the main oil supply pipe 510 to the oil outlet end of the sub oil supply pipe 520. In other words, the check valve 521 on the left sub-oil supply pipe 520 has a flow direction toward the left, and the check valve 521 on the right sub-oil supply pipe 520 has a flow direction toward the right.
After stopping supplying oil to the hydraulic motor 200, the hydraulic motor 200 can continue to rotate under the action of rotational inertia, and in the rotating process, the hydraulic oil can still be driven to continue to flow, and the oil supplementing pipeline can be arranged to continuously supplement oil for the oil inlet end of the hydraulic motor 200, so that the hydraulic motor 200 is prevented from being sucked empty.
The operation of the swing hydraulic system will be described below, taking the case where the main directional control valve 300 is in the right position as an example.
When the hydraulic motor 200 needs to be started, the first directional control valve 410 is powered on, the second directional control valve 420 is kept in a power-off state, the pilot oil inlet pipeline 430 is communicated with the first pilot oil outlet pipeline 450 through the pilot oil inlet of the first directional control valve 410, and pilot oil is supplied to the second hydraulic control port b of the main directional control valve 300 and the second overflow valve hydraulic control port e of the second two-stage booster overflow valve 120 2 。
At this time, the right side pressure of the valve core of the main directional control valve 300 is greater than the left side pressure, the valve core is pushed to the right position, the oil inlet P of the main directional control valve 300 is communicated with the second working oil port B, and the first working oil port a is communicated with the oil return port T. The second overflow valve hydraulic control port e of the second two-stage supercharging overflow valve 120 2 There is oil pressure, and therefore, the opening pressure of the second-stage booster spill valve 120 is increased to the first opening pressure. First overflow valve hydraulic control port e of first two-stage supercharging overflow valve 110 1 There is no oil pressure, and therefore, the opening pressure of the first secondary booster spill valve 110 is maintained at the second opening pressure.
When the oil is supplied from the oil inlet P of the main directional control valve 300, the hydraulic oil is supplied to the second motor working port C of the hydraulic motor 200 through the second working port B of the main directional control valve 300 2 During oil supply, the hydraulic oil passes through the second relief valve oil inlet P of the second two-stage booster relief valve 120 2 And thus, the second motor working port C supplied to the hydraulic motor 200 2 The hydraulic oil pressure of (1) is equal to the first opening pressure, and the hydraulic motor 200 can be started with a large torque because the first opening pressure is large.
The hydraulic oil passes through the second motor working oil port C of the hydraulic motor 200 2 Working oil port C flowing to first motor 1 And finally returns oil through the first working oil port a of the main directional control valve 300 through the oil return port T.
When the hydraulic motor 200 brakes, the first directional valve 410 is powered off, the second directional valve 420 is kept in a powered-off state, the second hydraulic control port B of the main directional valve 300 loses oil pressure, the spring of the main directional valve 300 rebounds the valve core to the middle position, and at the moment, 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 timeThe hydraulic motor 200 continues to rotate under the action of the rotational inertia, and simultaneously, the hydraulic motor 200 drives the hydraulic oil to be continuously supplied to the second motor working oil port C 2 To the working oil port C of the first motor 1 And (4) flowing. However, at this time, the hydraulic system stops supplying oil to the hydraulic motor 200 through the oil inlet P of the main directional control valve 300, and in order to prevent the hydraulic motor 200 from being emptied, the oil supply line may be opened, and hydraulic oil is supplied to the second motor working fluid port C of the hydraulic motor 200 through the sub oil supply pipe 520 located at the right side 2 And (5) oil supply.
At this time, the return oil from the hydraulic motor 200 cannot return from the return port T of the main directional control valve 300, and the return-side pressure increases. Because the opening pressure of the first secondary booster overflow valve 110 is the second opening pressure, which is lower, the hydraulic oil pushes the first secondary booster overflow valve 110 open to discharge oil and release pressure, so that the hydraulic motor 200 can brake gently under low oil pressure.
In the prior art, the opening pressure of the overflow valve on the oil return side is high, so that the oil return side pressure is high, the hydraulic motor 200 is forcibly stopped, and the hydraulic impact on the hydraulic motor 200 is large. The rotary hydraulic system provided by the invention can reduce the oil pressure at the oil return side and realize mild braking.
The above is the working condition of driving the hydraulic motor 200 to start and brake when the main directional control valve 300 is in the right position, and similarly, the hydraulic motor 200 can be driven to rotate reversely when the directional control valve is in the left position, and the working principle is the same, so the detailed description is not repeated here.
The invention also provides a slewing device which can be an excavator slewing device, a crane slewing device, an overhead working truck slewing device, a manipulator slewing device, an agricultural and forestry machinery slewing device and the like, and has the same advantages as the slewing hydraulic system.
The present invention also provides a working machine, which may be an excavator, a crane, an aerial work vehicle, a manipulator, an agricultural and forestry machine, etc. having a swing device, and has the same advantages as described above since it has the above-described swing hydraulic system or swing device.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. A swing hydraulic system, comprising:
a hydraulic motor (200);
the hydraulic control system comprises a main reversing valve (300), wherein two working oil ports of the main reversing valve (300) are communicated with two motor working oil ports of the hydraulic motor (200) in a one-to-one correspondence manner;
the rotary buffer valve (100), the rotary buffer valve (100) comprises two secondary pressurization overflow valves, and overflow valve oil inlets of the two secondary pressurization overflow valves are respectively connected to two hydraulic oil pipelines between the main reversing valve (300) and the hydraulic motor (200);
the pilot oil pipeline (400), the pilot oil pipeline (400) is respectively connected with the overflow valve hydraulic control ports of the two secondary booster overflow valves;
when the overflow valve hydraulic control port is communicated with the pilot oil pipeline (400), the corresponding opening pressure of the two-stage supercharging overflow valve is a first opening pressure, and when the overflow valve hydraulic control port is disconnected with the pilot oil pipeline (400), the corresponding opening pressure of the two-stage supercharging overflow valve is a second opening pressure, wherein the first opening pressure is greater than the second opening pressure.
2. The swing hydraulic system according to claim 1, wherein the pilot oil line (400) comprises:
the two reversing valves are respectively provided with a pilot oil inlet, a pilot oil return port and a pilot oil outlet;
a pilot oil inlet pipeline (430), wherein the pilot oil inlet pipeline (430) is respectively communicated with the pilot oil inlets of the two reversing valves;
a pilot oil return line (440), the pilot oil return line (440) being respectively communicated with the pilot oil return ports of the two directional control valves;
and the pilot oil outlets of the two reversing valves are correspondingly communicated with the overflow valve hydraulic control ports of the two secondary booster overflow valves one by one through the pilot oil outlet pipelines.
3. The rotary hydraulic system of claim 2, wherein the main directional control valve (300) is a pilot operated directional control valve, and the two pilot oil outlet lines are in one-to-one communication with two pilot operated ports of the main directional control valve (300).
4. The swing hydraulic system of claim 1, wherein the main directional control valve is an electronically controlled directional control valve.
5. The rotary hydraulic system according to claim 3 or 4, characterized in that the main directional control valve (300) is a three-position four-way directional control valve, the three-position four-way directional control valve being supplied with oil in opposite directions when in the first and second operating positions, and the three-position four-way directional control valve being shut off when in the third operating position.
6. The rotary hydraulic system according to claim 1, further comprising an oil supply line, wherein two oil outlets of the oil supply line are respectively communicated with two motor working ports of the hydraulic motor (200), and the oil supply line can selectively supply oil to one of the motor working ports of the hydraulic motor (200).
7. The swing hydraulic system of claim 6, wherein the oil replenishment circuit comprises:
the oil inlet end of the main oil supplementing pipe (510) is communicated with a hydraulic oil source;
two sub oil supply pipes (520), two the oil feed end of sub oil supply pipe (520) all with the end intercommunication that produces oil of main oil supply pipe (510), two the end that produces oil of sub oil supply pipe (520) respectively with two of hydraulic motor (200) motor working fluid port intercommunication, and every all connect one check valve (521) on sub oil supply pipe (520), the circulation direction of check valve (521) by the place the oil feed end of sub oil supply pipe (520) is towards producing oil the end.
8. The swing hydraulic system according to claim 1, wherein the number of the hydraulic motors (200) is two or more, and two or more hydraulic motors (200) are connected in parallel.
9. A swivel arrangement comprising a swivel hydraulic system according to any one of claims 1-8.
10. A working machine comprising a slewing hydraulic system according to any one of claims 1-8 or comprising a slewing device according to claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211060734.XA CN115370628A (en) | 2022-08-31 | 2022-08-31 | Rotary hydraulic system, rotary device and working machine |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211060734.XA CN115370628A (en) | 2022-08-31 | 2022-08-31 | Rotary hydraulic system, rotary device and working machine |
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| CN115370628A true CN115370628A (en) | 2022-11-22 |
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| CN202211060734.XA Pending CN115370628A (en) | 2022-08-31 | 2022-08-31 | Rotary hydraulic system, rotary device and working machine |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116624449A (en) * | 2023-07-25 | 2023-08-22 | 索特传动设备有限公司 | Overflow valve, hydraulic system and working machine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116624449A (en) * | 2023-07-25 | 2023-08-22 | 索特传动设备有限公司 | Overflow valve, hydraulic system and working machine |
| CN116624449B (en) * | 2023-07-25 | 2023-10-03 | 索特传动设备有限公司 | Overflow valve, hydraulic system and working machine |
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