CN113775590A - Constant pressure differential valve with buffering function - Google Patents
Constant pressure differential valve with buffering function Download PDFInfo
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- CN113775590A CN113775590A CN202111209370.2A CN202111209370A CN113775590A CN 113775590 A CN113775590 A CN 113775590A CN 202111209370 A CN202111209370 A CN 202111209370A CN 113775590 A CN113775590 A CN 113775590A
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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
- F15B13/024—Pressure relief 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
- 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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Abstract
The invention discloses a constant pressure difference valve with a buffering function, which comprises an oil inlet valve body and a constant pressure difference valve core, wherein an oil inlet cavity, an oil return cavity and an oil discharge way are formed in the oil inlet valve body; the constant pressure difference valve core is slidably arranged in the oil inlet valve body, the constant pressure difference valve core can block the communication position of the oil inlet cavity and the oil return cavity, and the constant pressure difference valve core is communicated with the oil drainage path; and one end of the constant pressure difference valve core, which is close to the oil inlet cavity, is provided with a throttling valve core. Along with the movement of the constant differential pressure valve core, the movement directions of the oil in the throttling valve core and the constant differential pressure valve core relative to the oil inlet valve body are opposite, so that a buffering effect is achieved, the movement speed of the constant differential pressure valve core is reduced, the oil in the oil inlet cavity is not completely introduced into the reversing linkage working cavity, after the buffering effect of the throttling valve core, the acting process of the constant differential pressure valve core is a process that the flow of the reversing linkage working cavity is gradually increased, and the instantaneous impact of the flow is greatly reduced.
Description
Technical Field
The invention relates to the technical field of hydraulic systems and peripheral supporting facilities thereof, in particular to a constant pressure differential valve with a buffering function.
Background
At present, more and more engineering machines using a load-sensitive hydraulic system are used in the market, and a load-sensitive multi-way valve is used as a core control element of the load-sensitive system, and the performance of the load-sensitive multi-way valve plays a decisive role in the action execution of the whole machine. When the hydraulic oil is output, the hydraulic oil is output by reversing the main valve core of the multi-way valve, and when the output flow is large, the initial speed of the reversing instant action exceeds the expected value, so that impact can be caused to the whole machine, and the service performance and the service life of the whole machine can be influenced.
With the prior art, there are roughly two solutions: and (I) adding a buffer groove on the valve core of the reversing valve to enable the flow part of the valve core to the working port to be divided into return oil when the valve core is opened. The solution can cause flow and energy loss, and the phenomenon of weak action can occur under certain special working conditions; and (II) for hydraulic pilot control reversing, one-way damping can be added at pilot control oil ports at two ends to throttle, so that the opening speed of the reversing valve core is reduced. Compared with the scheme (I), the solution is simple and easy to process, has no flow loss, but can affect the control feeling of a pilot handle by a manipulator, and is not feasible for a manually-reversed multi-way valve.
Therefore, how to change the current situation that the flow impact at the moment of reversing the load-sensitive reversing valve in the prior art is too large to influence the work of the whole machine becomes a problem to be solved urgently by technical personnel in the field.
Disclosure of Invention
The invention aims to provide a constant pressure differential valve with a buffering function, which is used for solving the problems in the prior art, buffering the instant flow impact of the reversing of a load-sensitive reversing valve and improving the working efficiency of the whole machine.
In order to achieve the purpose, the invention provides the following scheme: the invention provides a constant differential pressure valve with a buffer function, which comprises:
the oil inlet valve body is internally provided with an oil inlet cavity, an oil return cavity and an oil discharge way, the oil inlet cavity can be communicated with the oil return cavity, and the oil inlet cavity can be communicated with the reversing linkage working cavity;
the constant differential pressure valve core is slidably arranged in the oil inlet valve body, the constant differential pressure valve core can seal the communication position of the oil inlet cavity and the oil return cavity, and the constant differential pressure valve core is communicated with the oil drainage path; and one end of the constant pressure difference valve core, which is close to the oil inlet cavity, is provided with a throttling valve core, the throttling valve core is slidably arranged in the constant pressure difference valve core, the throttling valve core is communicated with the oil inlet cavity, and the flowing direction of hydraulic oil in the throttling valve core is opposite to the sliding direction of the constant pressure difference valve core relative to the oil inlet valve body.
Preferably, the constant pressure difference valve core is of a split structure, the constant pressure difference valve core comprises a movable part and a connecting part, the connecting part is connected with the oil inlet valve body, the movable part is slidably arranged in the oil inlet valve body and can be used for plugging the communication position of the oil inlet cavity and the oil return cavity, the movable part can be abutted against the connecting part, the abutting position of the movable part and the connecting part is communicated with the oil drainage path, and the throttling valve core is arranged at one end of the movable part far away from the connecting part.
Preferably, the movable portion and the end opposite to the connecting portion are provided with first mounting positions, two first mounting positions enclose a cavity capable of accommodating a first elastic member, and the first elastic member is located in the first mounting positions.
Preferably, the first elastic member is a spring, and a spring washer is arranged in the first mounting position.
Preferably, the connecting portion is in threaded connection with the oil inlet valve body.
Preferably, the oil inlet valve body is provided with a clearance groove, the clearance groove is communicated with the oil inlet cavity by utilizing the constant pressure difference valve core and the throttling valve core, and the constant pressure difference valve core can extend into the clearance groove.
Preferably, the constant-pressure-difference valve core is provided with a first communicating oil port and a second communicating oil port which are communicated with each other, the first communicating oil port is communicated with the oil inlet cavity, the second communicating oil port is communicated with the blank groove, the throttle valve core can block the communication position of the first communicating oil port and the second communicating oil port, the throttle valve core is provided with a damping hole, and the first communicating oil port can be communicated with the second communicating oil port by using the damping hole.
Preferably, a plug is arranged at the second communicating oil port, the plug is in threaded connection with the constant-pressure-difference valve core, the plug is provided with a through hole, the plug is communicated with the blank groove, and a second elastic element is arranged between the plug and the throttle valve core.
Preferably, a second installation position is arranged at one end of the throttle valve core opposite to the plug, the second elastic piece is arranged in the second installation position, and the second elastic piece is a spring.
Preferably, a communicating part of the first communicating oil port and the second communicating oil port is a cylindrical hole, the throttle valve core is provided with a circular table part, and the circular table part can extend into the cylindrical hole and block the cylindrical hole; when the circular table part plugs the cylindrical hole, the circular table part is in line contact with the cylindrical hole.
Compared with the prior art, the invention has the following technical effects: the constant pressure difference valve with the buffering function comprises an oil inlet valve body and a constant pressure difference valve core, wherein an oil inlet cavity, an oil return cavity and an oil discharge way are formed in the oil inlet valve body, the oil inlet cavity can be communicated with the oil return cavity, and the oil inlet cavity can be communicated with a reversing linkage working cavity; the constant pressure difference valve core is slidably arranged in the oil inlet valve body, the constant pressure difference valve core can block the communication position of the oil inlet cavity and the oil return cavity, and the constant pressure difference valve core is communicated with the oil drainage path; and one end of the constant pressure difference valve core, which is close to the oil inlet cavity, is provided with a throttling valve core, the throttling valve core is slidably arranged in the constant pressure difference valve core, the throttling valve core is communicated with the oil inlet cavity, and the flowing direction of hydraulic oil in the throttling valve core is opposite to the sliding direction of the constant pressure difference valve core relative to the oil inlet valve body.
According to the constant pressure differential valve with the buffering function, when the reversing valve works, high-pressure oil in the oil inlet cavity flows to the working oil cylinder or the motor, the pressure of the oil in the oil drainage path rises along with the reversing of the reversing valve, the oil in the oil drainage path pushes the constant pressure differential valve core to move, so that the communication part between the oil inlet cavity and the oil return cavity is blocked, and at the moment, all the oil in the oil inlet cavity is led to the reversing linkage working cavity. In the process, along with the movement of the constant differential pressure valve core, the movement directions of the oil in the throttling valve core and the constant differential pressure valve core relative to the oil inlet valve body are opposite, so that a buffering effect is achieved, the movement speed of the constant differential pressure valve core is reduced, the oil in the oil inlet cavity is not completely introduced into the reversing linkage working cavity, and part of the oil is shunted to the oil return cavity; when the constant pressure difference valve core is closed gradually (namely the communication part of the oil inlet cavity and the oil return cavity is plugged gradually), the cut-off area of the communication part of the oil inlet cavity and the oil return cavity is reduced gradually, the flow rate of the oil inlet cavity to the oil return cavity is reduced, when the constant pressure difference valve core is completely closed (namely the communication part of the oil inlet cavity and the oil return cavity is plugged), the oil inlet cavity does not shunt to the oil return cavity any more, but flows to the reversing linkage working cavity completely, therefore, after the buffer action of the throttling valve core, the action process of the constant pressure difference valve core is the process of gradually increasing the flow rate of the reversing linkage working cavity, the instantaneous impact of the flow rate is greatly reduced, the flow rate loss is avoided after the reversing valve is reversed in place, and the energy loss is reduced.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
FIG. 1 is a schematic structural view of a constant differential pressure valve with a buffering function according to the present invention in an open state;
FIG. 2 is an enlarged schematic view of a portion of the structure of FIG. 1;
FIG. 3 is a schematic structural view of a constant differential pressure valve with a cushion function according to the present invention in a closed state;
the oil leakage valve comprises an oil inlet valve body 1, a constant pressure difference valve core 2, an oil inlet cavity 3, an oil return cavity 4, an oil leakage path 5, a throttling valve core 6, a movable part 7, a connecting part 8, a first installation position 9, a first elastic part 10, a spring gasket 11, a blank groove 12, a first communication oil port 13, a second communication oil port 14, a damping hole 15, a plug 16, a second elastic part 17 and a second installation position 18.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. 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 invention aims to provide a constant pressure differential valve with a buffering function, which is used for solving the problems in the prior art, buffering the instant flow impact of the reversing of a load-sensitive reversing valve and improving the working efficiency of the whole machine.
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in further detail below.
Referring to fig. 1 to 3, fig. 1 is a schematic structural view of a constant differential pressure valve with a buffering function in an open state, fig. 2 is an enlarged schematic view of a part of the structure in fig. 1, and fig. 3 is a schematic structural view of the constant differential pressure valve with the buffering function in a closed state.
The invention provides a constant pressure difference valve with a buffering function, which comprises an oil inlet valve body 1 and a constant pressure difference valve core 2, wherein an oil inlet cavity 3, an oil return cavity 4 and an oil leakage way 5 are arranged in the oil inlet valve body 1, the oil inlet cavity 3 can be communicated with the oil return cavity 4, and the oil inlet cavity 3 can be communicated with a reversing linkage working cavity; the constant pressure difference valve core 2 is slidably arranged in the oil inlet valve body 1, the constant pressure difference valve core 2 can seal the communication position of the oil inlet cavity 3 and the oil return cavity 4, and the constant pressure difference valve core 2 is communicated with the oil drainage path 5; one end of the constant pressure difference valve core 2 close to the oil inlet cavity 3 is provided with a throttling valve core 6, the throttling valve core 6 is slidably arranged in the constant pressure difference valve core 2, the throttling valve core 6 is communicated with the oil inlet cavity 3, and the flowing direction of hydraulic oil in the throttling valve core 6 is opposite to the sliding direction of the constant pressure difference valve core 2 relative to the oil inlet valve body 1.
According to the constant pressure differential valve with the buffering function, when the reversing valve works, high-pressure oil in the oil inlet cavity 3 flows to the working oil cylinder or the motor, the pressure of the oil in the oil discharge way 5 rises along with the reversing of the reversing valve, the oil in the oil discharge way 5 pushes the constant pressure differential valve core 2 to move, so that the communication part between the oil inlet cavity 3 and the oil return cavity 4 is blocked, and at the moment, all the oil in the oil inlet cavity 3 is led to the reversing linkage working cavity. In the process, along with the movement of the constant differential pressure valve core 2, the movement directions of the oil in the throttle valve core 6 and the constant differential pressure valve core 2 relative to the oil inlet valve body 1 are opposite, so that a buffer effect is achieved, the movement speed of the constant differential pressure valve core 2 is reduced, the oil in the oil inlet cavity 3 is not completely introduced into the reversing linkage working cavity, and part of the oil is shunted to the oil return cavity 4; when the constant pressure difference valve core 2 is gradually closed (namely the communication part of the oil inlet cavity 3 and the oil return cavity 4 is gradually blocked), the cut-off area of the communication part of the oil inlet cavity 3 and the oil return cavity 4 is gradually reduced, the flow rate of the oil inlet cavity 3 to the oil return cavity 4 is also reduced, when the constant pressure difference valve core 2 is completely closed (namely the communication part of the oil inlet cavity 3 and the oil return cavity 4 is blocked), the oil inlet cavity 3 does not shunt to the oil return cavity 4 any more, but completely flows to the reversing linkage working cavity, therefore, after the buffering action of the throttle valve core 6, the action process of the constant pressure difference valve core 2 is the process that the flow rate of the reversing linkage working cavity is gradually increased, the instantaneous impact of the flow rate is greatly reduced, the flow rate loss is avoided after the reversing valve is in place, and the energy loss is reduced.
Wherein, level pressure difference valve core 2 is split type structure, and level pressure difference valve core 2 includes movable part 7 and connecting portion 8, and connecting portion 8 links to each other with oil feed valve body 1, and movable part 7 slidable sets up in oil feed valve body 1, and movable part 7 can shutoff oil feed chamber 3 and the intercommunication department that returns oil chamber 4, and movable part 7 can offset with connecting portion 8, and movable part 7 is linked together with draining way 5 with the butt department of connecting portion 8, and throttle valve core 6 sets up in the one end that connecting portion 8 was kept away from to movable part 7. When the reversing valve is reversed, high-pressure oil in the oil inlet cavity 3 flows to the working oil cylinder or the motor, the pressure of the oil in the oil discharge channel 5 rises along with the reversing of the reversing valve, and the oil in the oil discharge channel 5 pushes the movable part 7 to move, so that the movable part 7 can plug the communication position of the oil inlet cavity 3 and the oil return cavity 4.
In addition, the opposite ends of the movable part 7 and the connecting part 8 are provided with first installation positions 9, the two first installation positions 9 enclose a cavity capable of accommodating a first elastic part 10, and the first elastic part 10 is located in the first installation positions 9. Under the action of oil in the oil drainage path 5 and the acting force of the first elastic part 10, the movable part 7 moves relative to the oil inlet valve body 1, and the communication part of the oil inlet cavity 3 and the oil return cavity 4 is smoothly plugged, so that the oil inlet of the oil inlet cavity 3 is completely communicated with the reversing linkage working cavity.
In the present embodiment, the first elastic member 10 is a spring, and it should be noted that a spring washer 11 is disposed in the first mounting location 9, so that the purpose of adjusting the magnitude of the acting force of the first elastic member 10 can be achieved by adjusting the number of the spring washers 11, and the flexible adaptability of the constant pressure difference valve core 2 is improved.
In this embodiment, connecting portion 8 and 1 threaded connection of oil feed valve body make things convenient for the dismouting, and set up the sealing washer between connecting portion 8 and the oil feed valve body 1, avoid leaking, can set up spring shim 11 in the first installation position 9 of connecting portion 8, make things convenient for the adjustment, set up spring shim 11 in the first installation position 9 of one side and can reach the purpose of adjusting first elastic component 10 effort.
Specifically, the oil inlet valve body 1 is provided with a blank groove 12, the blank groove 12 is communicated with the oil inlet cavity 3 by using the constant pressure difference valve core 2 and the throttling valve core 6, and the constant pressure difference valve core 2 can extend into the blank groove 12. When the constant pressure difference valve core 2 blocks the communication position of the oil inlet cavity 3 and the oil return cavity 4, the constant pressure difference valve core 2 extends into the clearance groove 12, and oil in the clearance groove 12 flows into the oil inlet cavity 3 through the throttle valve core 6 and the inside of the constant pressure difference valve core 2.
More specifically, the constant pressure difference valve core 2 is provided with a first communicating oil port 13 and a second communicating oil port 14 which are communicated, the first communicating oil port 13 is communicated with the oil inlet cavity 3, the second communicating oil port 14 is communicated with the blank groove 12, the throttle valve core 6 can block the communication position of the first communicating oil port 13 and the second communicating oil port 14, the throttle valve core 6 is provided with a damping hole 15, and the first communicating oil port 13 can be communicated with the second communicating oil port 14 by using the damping hole 15. In the closing process of the constant differential pressure valve core 2, along with the movement of the constant differential pressure valve core 2, under the action of oil in the blank groove 12, the throttle valve core 6 blocks the communication position of the first communication oil port 13 and the second communication oil port 14, hydraulic oil in the blank groove 12 enters the throttle valve core 6 through the second communication oil port 14 and reaches the first communication oil port 13 through the damping hole 15 of the throttle valve core 6, due to the throttling action of the damping hole 15, the movement directions of the oil in the throttle valve core 6 and the constant differential pressure valve core 2 relative to the oil inlet valve body 1 are opposite, the movement speed of the constant differential pressure valve core 2 is slowed down, the oil in the oil inlet cavity 3 is not completely introduced into the reversing connection working cavity, part of the oil is shunted to the oil return cavity 4, and the phenomenon that the instantaneous flow is impacted too much is avoided. It should be emphasized here that the throttle valve core 6 is a one-way motion valve core, when the valve core of the reversing valve returns to the middle position, the oil drainage path 5 releases pressure, the oil inlet cavity 3 of the constant pressure difference valve core 2 moves under the high pressure action, the constant pressure difference valve core 2 is opened, the hydraulic oil in the oil inlet cavity 3 enters the inside of the constant pressure difference valve core 2 through the first communication oil port 13 to push the throttle valve core 6 to open, the damping hole 15 does not play a throttling role at this time, the hydraulic oil enters the blank slot 12 through the first communication oil port 13 and the second communication oil port 14, and the oil in the blank slot 12 pushes the constant pressure difference valve core 2 to reset. In other embodiments of the present invention, a damping form such as a chute may be provided on the throttle valve core 6 to achieve the throttling function.
Further, a plug 16 is arranged at the second communicating oil port 14, the plug 16 is in threaded connection with the constant pressure difference valve core 2, disassembly and assembly are facilitated, the plug 16 is provided with a through hole, the plug 16 is communicated with the blank groove 12, it is further ensured that the second communicating oil port 14 is communicated with the blank groove 12, a second elastic part 17 is arranged between the plug 16 and the throttle valve core 6, and when the constant pressure difference valve core 2 is completely opened (namely the oil inlet cavity 3 is communicated with the oil return cavity 4), the throttle valve core 6 blocks the communicating position of the first communicating oil port 13 and the second communicating oil port 14 under the acting force of the second elastic part 17.
It should be further noted that the opposite ends of the throttle valve core 6 and the plug 16 are both provided with a second mounting position 18, the second elastic member 17 is disposed in the second mounting position 18, the second elastic member 17 is a spring, and the second mounting position 18 can avoid the second elastic member 17 from being dislocated, thereby improving the operational reliability of the throttle valve core 6.
Furthermore, the communication part of the first communication oil port 13 and the second communication oil port 14 is a cylindrical hole, the throttle valve core 6 is provided with a circular table part, and the circular table part can extend into the cylindrical hole and block the cylindrical hole; when the circular table part plugs the cylindrical hole, the circular table part is in line contact with the cylindrical hole, and the sealing form between the throttling valve core 6 and the constant-pressure-difference valve core 2 is line sealing, so that the sealing effect is enhanced.
As shown in fig. 1, the directional control valve is in an inoperative state, and the spool of each directional control valve is in a neutral position. When a certain reversing valve plate of the reversing valve works in a reversing mode or a plurality of reversing valve plates work in a reversing mode simultaneously, high-pressure oil in an oil inlet cavity 3(P) flows to a working oil cylinder or a motor through an oil groove of a reversing valve core, oil discharge channels LS1 and LS2 are communicated with an LS oil channel and a first installation position 9 of a constant pressure difference valve core 2, the LS oil channel is boosted along with reversing of the reversing valve core, high pressure of the LS oil channel acts on the part, located in the leakage channel, of the constant pressure difference valve core 2, acting force of a first elastic piece 10 is added, the constant pressure difference valve core 2 is pushed to move towards the direction of an arrow below the valve core 1, and finally the state that the constant pressure difference valve core 2 in the figure 3 is closed is achieved, and at the moment, all oil inlet of the oil inlet cavity 3 is led to a reversing linkage working cavity. In the process, as shown in fig. 2, with the closing of the constant pressure difference valve core 2, the hydraulic oil in the blank slot 12 flows to the oil inlet chamber 3 through the direction shown by the arrow, under the action of the hydraulic force, the throttle valve core 6 moves leftwards relative to the constant pressure difference valve core 2, the throttle valve core 6 is closed, the hydraulic oil in the blank slot 12 can only flow to the oil inlet chamber 3 through the damping hole 15 on the throttle valve core 6, due to the throttling action of the damping hole 15, the closing speed of the constant pressure difference valve core 2 becomes slow, at this time, the oil inlet of the oil inlet chamber 3 does not completely enter the reversing linkage working chamber, part of the flow is shunted to the oil return chamber 4(T) through the constant pressure difference valve core 2, when the constant pressure difference valve core 2 is gradually closed, the oil passage cut-off area between the oil inlet chamber 3 and the oil return chamber 4 is gradually reduced, and when the flow rate of the oil inlet chamber 3 to the oil return chamber 4 is gradually reduced, when the constant pressure difference valve core 2 is completely closed, the oil inlet of the oil inlet cavity 3 is not shunted towards the oil return cavity 4 any more, but completely flows to the reversing linkage working cavity, and the process is a process that the flow of the reversing linkage working cavity is gradually increased, so that the instantaneous impact of the flow is greatly reduced. On the contrary, as shown in fig. 3, when each reversing valve core returns to the neutral position, the LS oil paths communicated with LS1 and LS2 are decompressed, the constant pressure difference valve core 2 moves along the arrow direction below fig. 3 under the high pressure action of the oil inlet cavity 3, the constant pressure difference valve core 2 is opened, at this time, the hydraulic oil in the oil inlet cavity 3 flows along the direction opposite to the arrow direction in fig. 2, the hydraulic force overcomes the acting force of the second elastic member 17, the throttle valve core 6 can be opened instantly, the damping hole 15 does not play a throttling role at this time, the constant pressure difference valve core 2 can be reversed in place instantly, the state in fig. 1 is reached, and the resetting of the constant pressure difference valve core 2 is realized.
Compared with the technical scheme of adding the buffer groove on the reversing valve core, the constant pressure differential valve with the buffer function has the advantages that the flow loss is avoided after the reversing valve core is reversed in place, and the energy loss is reduced while the buffer function is achieved. In addition, compared with the method for increasing the damping at the pilot-controlled pilot position, the method does not influence the curve of pilot pressure, the stroke of the reversing valve core and the output flow of the working cavity, and does not influence the operation feeling of the pilot handle. The constant pressure differential valve with the buffering function is suitable for load sensitive multi-way valves with various control modes, such as hydraulic control, manual control and electric control, and the application range is not limited by the control modes.
The principle and the implementation mode of the invention are explained by applying a specific example, and the description of the embodiment is only used for helping to understand the method and the core idea of the invention; meanwhile, for a person skilled in the art, according to the idea of the present invention, the specific embodiments and the application range may be changed. In view of the above, the present disclosure should not be construed as limiting the invention.
Claims (10)
1. A constant differential pressure valve having a damping function, comprising:
the oil inlet valve body is internally provided with an oil inlet cavity, an oil return cavity and an oil discharge way, the oil inlet cavity can be communicated with the oil return cavity, and the oil inlet cavity can be communicated with the reversing linkage working cavity;
the constant differential pressure valve core is slidably arranged in the oil inlet valve body, the constant differential pressure valve core can seal the communication position of the oil inlet cavity and the oil return cavity, and the constant differential pressure valve core is communicated with the oil drainage path; and one end of the constant pressure difference valve core, which is close to the oil inlet cavity, is provided with a throttling valve core, the throttling valve core is slidably arranged in the constant pressure difference valve core, the throttling valve core is communicated with the oil inlet cavity, and the flowing direction of hydraulic oil in the throttling valve core is opposite to the sliding direction of the constant pressure difference valve core relative to the oil inlet valve body.
2. The fixed differential pressure valve with a damping function according to claim 1, wherein: the constant pressure difference valve core is of a split structure and comprises a movable part and a connecting part, the connecting part is connected with the oil inlet valve body, the movable part can be slidably arranged in the oil inlet valve body and can be plugged into the oil inlet cavity and the communication part of the oil return cavity, the movable part can be abutted against the connecting part, the movable part is communicated with the oil drainage path by abutting against the connecting part, and the throttling valve core is arranged at one end of the connecting part, which is far away from the movable part.
3. The fixed differential pressure valve with a damping function according to claim 2, wherein: the movable part with the one end that connecting portion are relative all is provided with first installation position, two first installation position encloses into the cavity that can hold first elastic component, first elastic component is located in the first installation position.
4. The fixed differential pressure valve with a damping function according to claim 3, wherein: the first elastic piece is a spring, and a spring gasket is arranged in the first installation position.
5. The fixed differential pressure valve with a damping function according to claim 2, wherein: the connecting part is in threaded connection with the oil inlet valve body.
6. The fixed differential pressure valve with a damping function according to claim 1, wherein: the oil inlet valve body is provided with a clearance groove, the clearance groove is communicated with the oil inlet cavity by utilizing the constant pressure difference valve core and the throttling valve core, and the constant pressure difference valve core can extend into the clearance groove.
7. The fixed differential pressure valve with a damping function according to claim 6, wherein: the constant-pressure-difference valve core is provided with a first communicating oil port and a second communicating oil port which are communicated, the first communicating oil port is communicated with the oil inlet cavity, the second communicating oil port is communicated with the clearance groove, the throttle valve core can block the communication position of the first communicating oil port and the second communicating oil port, the throttle valve core is provided with a damping hole, and the first communicating oil port can be communicated with the second communicating oil port by utilizing the damping hole.
8. The fixed differential pressure valve with a damping function according to claim 7, wherein: the second communicating oil port is provided with a plug, the plug is in threaded connection with the constant-pressure-difference valve core, the plug is provided with a through hole, the plug is communicated with the clearance groove, and a second elastic piece is arranged between the plug and the throttle valve core.
9. The fixed differential pressure valve with a damping function according to claim 8, wherein: and one end of the throttling valve core opposite to the plug is provided with a second installation position, the second elastic piece is arranged in the second installation position, and the second elastic piece is a spring.
10. The fixed differential pressure valve with a damping function according to claim 7, wherein: the communication part of the first communicating oil port and the second communicating oil port is a cylindrical hole, the throttling valve core is provided with a circular table part, and the circular table part can extend into the cylindrical hole and block the cylindrical hole; when the circular table part plugs the cylindrical hole, the circular table part is in line contact with the cylindrical hole.
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| CN202111209370.2A CN113775590B (en) | 2021-10-18 | 2021-10-18 | Constant pressure difference valve with buffering function |
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| CN202111209370.2A CN113775590B (en) | 2021-10-18 | 2021-10-18 | Constant pressure difference valve with buffering function |
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| CN212272696U (en) * | 2020-08-04 | 2021-01-01 | 涌镇液压机械（上海）有限公司 | Electro-hydraulic valve reversing anti-impact structure |
| CN112555214A (en) * | 2020-12-10 | 2021-03-26 | 山东泰丰智能控制股份有限公司 | Three-port two-way constant pressure difference valve |
| CN216447213U (en) * | 2021-10-18 | 2022-05-06 | 山东泰丰智能控制股份有限公司 | Constant pressure differential valve with buffering function |
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| EP0829794A1 (en) * | 1996-09-05 | 1998-03-18 | HEILMEIER & WEINLEIN Fabrik für Oel-Hydraulik GmbH & Co. KG | Pressure reducing lift valve |
| JP2007107677A (en) * | 2005-10-17 | 2007-04-26 | Komatsu Ltd | Flow control valve |
| CN101025235A (en) * | 2006-02-24 | 2007-08-29 | 罗伯特·博世有限公司 | Directional or flow control valve |
| CN201288869Y (en) * | 2008-10-28 | 2009-08-12 | 上海立新液压有限公司 | Balance control valve |
| CN101871543A (en) * | 2009-04-23 | 2010-10-27 | 昆明物理研究所 | Parallel time-delay pressure-reducing valve |
| CN101929571A (en) * | 2009-06-21 | 2010-12-29 | 陆平 | Slow closure back pressure valve |
| CN102859204A (en) * | 2010-05-17 | 2013-01-02 | 沃尔沃建造设备有限公司 | Pressure control valve |
| CN102042432A (en) * | 2010-12-10 | 2011-05-04 | 北京工业大学 | Direct-acting water pressure overflow valve with damping piston |
| CN102313049A (en) * | 2011-08-12 | 2012-01-11 | 深圳市家乐士净水科技有限公司 | Pressure reducing valve |
| CN103122880A (en) * | 2011-11-18 | 2013-05-29 | 广西柳工机械股份有限公司 | Adjustable pilot reducing valve |
| CN102705288A (en) * | 2012-06-19 | 2012-10-03 | 常德中联重科液压有限公司 | Anti-shaking balance valve, telescopic control loop of hydraulic cylinder and hydraulic device |
| CN103671321A (en) * | 2013-11-25 | 2014-03-26 | 武汉船用机械有限责任公司 | Hydraulic control valve |
| CN104132016A (en) * | 2014-07-25 | 2014-11-05 | 常德中联重科液压有限公司 | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machinery |
| CN105909583A (en) * | 2016-03-02 | 2016-08-31 | 杭州力龙液压有限公司 | Buffer overflow valve and hydraulic system |
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| CN110285104A (en) * | 2019-06-04 | 2019-09-27 | 常德中联重科液压有限公司 | Constant difference overflow valve and engineering machinery |
| CN212272696U (en) * | 2020-08-04 | 2021-01-01 | 涌镇液压机械（上海）有限公司 | Electro-hydraulic valve reversing anti-impact structure |
| CN112555214A (en) * | 2020-12-10 | 2021-03-26 | 山东泰丰智能控制股份有限公司 | Three-port two-way constant pressure difference valve |
| CN216447213U (en) * | 2021-10-18 | 2022-05-06 | 山东泰丰智能控制股份有限公司 | Constant pressure differential valve with buffering function |
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