CN108412831B - Shunt pressure-regulating speed-regulating reversing integrated valve - Google Patents
Shunt pressure-regulating speed-regulating reversing integrated valve Download PDFInfo
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- CN108412831B CN108412831B CN201810439614.8A CN201810439614A CN108412831B CN 108412831 B CN108412831 B CN 108412831B CN 201810439614 A CN201810439614 A CN 201810439614A CN 108412831 B CN108412831 B CN 108412831B
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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
- F15B13/022—Flow-dividers; Priority 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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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Safety Valves (AREA)
Abstract
The invention belongs to valves, and particularly relates to a split-flow pressure-regulating speed-regulating reversing integrated valve. The device comprises a valve body, an oil inlet valve, an overflow valve and a pilot pressure regulating, throttling switching and speed regulating unit, wherein the oil inlet valve and the overflow valve are arranged on the valve body; the valve body is provided with an oil return port, a throttle oil outlet and an oil outlet, and an overflow back pressure cavity, an oil outlet cavity, an oil inlet cavity, an oil saving and outlet cavity and a hydraulic control cavity which are axially communicated by the main hole are arranged in the valve body at intervals; the throttling oil outlet cavity is communicated with the throttling oil outlet, the oil outlet cavity is communicated with the oil outlet, and the oil outlet cavity is communicated with the hydraulic control cavity through a hydraulic control pore canal; the overflow main valve sleeve is inserted into the main hole to form dynamic seal fit, the outer end of the overflow main valve sleeve is assembled with a spigot at the outer end of the main hole, and a throttling port is arranged at the inner end of the overflow main valve sleeve; the overflow main valve sleeve separates the oil inlet cavity from the oil outlet cavity in a non-working state; the invention effectively solves the technical problems of high energy consumption, quick temperature rise of working medium and the like in the prior art, and has the advantages of respectively driving a plurality of executive components with different working pressures and flows, having lower requirements on the level of system components, realizing speed regulation and the like.
Description
Technical Field
The invention belongs to valves, and particularly relates to a split-flow pressure-regulating speed-regulating reversing integrated valve.
Background
The existing hydraulic transmission system or mobile hydraulic mechanical system needs more than two working systems, the flow and the working pressure required by each working system are set differently, and the diverter valve has the function of enabling the same oil source to supply the same flow (equal diversion) to more than two execution elements in the hydraulic system or supplying the flow (proportional diversion) to the two execution elements according to a certain proportion so as to realize that the speeds of the two execution elements keep synchronous or constant ratio relation.
The conventional hydraulic system includes:
1. power element
The power element is used for converting mechanical energy of the prime motor into pressure energy of liquid, namely an oil pump in the hydraulic system, and provides power for the whole hydraulic system. The hydraulic pump is generally structured in the form of a gear pump, a vane pump, a plunger pump and a screw pump.
2. Actuator element
The function of the actuating elements (such as hydraulic cylinders and hydraulic motors) is to convert the pressure energy of the fluid into mechanical energy and drive the load to perform linear reciprocating motion or rotary motion.
3. Control element
Control elements (i.e., various hydraulic valves) control and regulate the pressure, flow, and direction of fluid in the hydraulic system. The hydraulic valves may be classified into pressure control valves, flow control valves, and directional control valves according to the control functions. The pressure control valve comprises a relief valve (safety valve), a pressure reducing valve, a sequence valve, a pressure relay and the like; the flow control valve comprises a throttle valve, an adjusting valve, a flow dividing and collecting valve and the like; the direction control valve comprises a one-way valve, a hydraulic control one-way valve, a shuttle valve, a reversing valve and the like. According to different control modes, the hydraulic valve can be divided into a switch type control valve, a fixed value control valve and a proportional control valve.
4. Auxiliary element
The auxiliary elements comprise an oil tank, an oil filter, a cooler, a heater, an energy accumulator, an oil pipe, a pipe joint, a sealing ring, a quick-change joint, a high-pressure ball valve, a rubber pipe assembly, a pressure measuring joint, a pressure gauge, an oil level gauge, an oil temperature gauge and the like.
5. Hydraulic oil
Hydraulic oil is a working medium for transferring energy in hydraulic systems, and there are several kinds of mineral oil, emulsion, synthetic hydraulic oil, and the like.
According to the application range and the different adaptive execution elements, the design requirements of the traditional hydraulic system have a plurality of different technical requirements, wherein the main factors to be considered in the design of the hydraulic system when the oil cylinder is used as the execution element include: firstly, designing the pressure intensity and the acting area of a hydraulic system according to the load mass; secondly, designing the effective flow of a working medium in a hydraulic system and the pressure acting area of an executing element according to the requirement on the moving speed of a load; thirdly, rated pressure and displacement of the hydraulic power source are matched with the moving speed and the moving mass of the load; and fourthly, the sectional areas of the system pipeline and the control element at the drift diameter or the minimum position are matched with the flow, otherwise, the conditions of over-high temperature rise of a working medium or unstable operation of an executive component and the like can occur. In a hydraulic system, a plurality of executive components (hydraulic cylinders and hydraulic motors) with different load masses and displacement speeds are required to be independently operated, so that the purposes of saving power components, simplifying control components, reducing system failure rate and the like can be achieved by structural design or technical improvement of the hydraulic system.
To the extent that the applicant is aware of, the technical solutions to solve the above technical problems include:
1. adopting quantitative duplex pump as power element
The main problem in the prior art is that the quantitative duplex pump is preset in flow and cannot be adjusted, so that the adaptability cannot be adjusted when the working condition in the running environment changes, and the matching performance is poor; secondly, the quantitative duplex gear pump has high manufacturing cost and failure rate due to complex structure; and thirdly, when one pump in the quantitative duplex pump is in a working state, the other pump is in a non-working state, but still performs idle operation to generate reactive power loss, so that energy is wasted and the temperature of a working medium is increased.
2. Variable displacement pump (typically variable displacement pump) is selected as the power element
The main problem of the prior art is that the variable control of the variable pump is that the measured value of the sensor is transmitted to the control device and the control device sends out corresponding instructions to complete the control, so that the structure is complex and the cost is high; secondly, the variable pump can only realize displacement adjustment and cannot control pressure, so that pressure control elements (such as overflow valves) are required to be arranged for each executive element to meet the load requirements of different qualities, and meanwhile, control elements and pipelines are required to be additionally arranged to avoid pressure interference in loops of different executive elements; thirdly, the plunger pump has higher requirements on the cleanliness of the working medium, so that the system components assembled with the plunger pump have higher requirements on the level and the operation and maintenance costs.
3. The single constant displacement pump is provided with a throttle valve and an overflow valve as control elements
The main problem of the prior art is that the flow rate is regulated by changing the diameter area of the throttle valve, the execution pressure is changed along with the change of the load, but the pressure at the other side of the throttle valve is a set value due to the action of the constant displacement pump and the overflow valve, so that the pressure difference at the two sides of the throttle valve is inevitably overlarge, and the pressure difference can be converted into heat energy to generate the phenomena of oil temperature rise and energy consumption; secondly, the oil pump always operates under the high pressure condition to generate great energy consumption, so that the service life of the oil pump is greatly shortened; thirdly, because the overflow valve can only be arranged in the main loop with higher pressure, the overflow valve can only meet the working condition under the set pressure value.
The applicant has found no patent document report similar to or identical to the present application through searching.
Disclosure of Invention
The invention aims to provide a shunt pressure-regulating speed-regulating reversing integrated valve, which achieves the aim of respectively driving a plurality of executive components with different working pressures and flow by adopting a high-integration design of shunt, pressure regulation, speed regulation and reversing and matching a set of power components.
The invention has the following overall technical concept:
the diversion, pressure regulation and speed regulation reversing integrated valve comprises a valve body, an oil inlet arranged on the valve body, wherein the oil inlet is communicated with an oil inlet cavity, and an overflow valve is inserted on the valve body; an oil return port, a throttle oil outlet and an oil outlet are formed in the valve body, and an overflow back pressure cavity, an oil outlet cavity, an oil inlet cavity, an oil saving and outlet cavity and a hydraulic control cavity which are axially communicated by the main hole are sequentially arranged in the valve body from left to right at intervals; the throttling oil outlet cavity is communicated with the throttling oil outlet, the oil outlet cavity is communicated with the oil outlet, and the oil outlet cavity is communicated with the hydraulic control cavity through a hydraulic control pore canal; the overflow main valve sleeve is inserted into the main hole to form dynamic seal fit, the outer end of the overflow main valve sleeve is assembled with a spigot at the outer end of the main hole, and a throttling port is arranged at the inner end of the overflow main valve sleeve; the overflow main valve sleeve separates the oil inlet cavity from the oil outlet cavity in a non-working state;
the structure unit comprises the following structure units:
A. and a pilot pressure regulating unit: the overflow valve is a direct-acting overflow valve, an oil inlet of the direct-acting overflow valve is communicated with the overflow back pressure cavity, and an oil outlet of the direct-acting overflow valve is communicated with the oil return port through an oil return channel; a reset spring is arranged in the overflow back pressure cavity, and two ends of the reset spring respectively act on the outer end face of the overflow main valve sleeve and the inner wall of the overflow back pressure cavity;
B. a throttle switching unit: the throttle valve core is of a variable diameter structure, the small diameter at the left side of the throttle valve core is inserted into the overflow main valve sleeve and is in dynamic seal fit with the overflow main valve sleeve, a speed regulation throttling opening is formed at the joint of the left end face of the large diameter at the right side of the throttle valve core and the outer circle surface, the oil outlet cavity and the oil inlet cavity realize throttling conduction through the speed regulation throttling opening, the large diameter at the right side of the throttle valve core is inserted into the main hole between the throttle oil outlet cavity and the hydraulic control cavity and is in dynamic seal fit with the main hole, and a spigot matched with the main hole is formed at the end face of the large diameter at the right side of the throttle valve core; a back pressure pore canal arranged in the throttle valve core is used for communicating the throttle outflow oil cavity with the overflow back pressure cavity, and a damping screw is arranged in the back pressure pore canal;
C. and the speed regulating unit is used for: the outside of the hydraulic control cavity is sequentially provided with a speed regulation screw plug, a lock nut and a speed regulation screw, wherein the speed regulation screw is in threaded fit with the speed regulation screw plug and drives the speed regulation piston to axially act on the large-diameter end face on the right side of the throttle valve core.
The specific technical concept of the invention is as follows:
the oil outlet cavity and the oil saving outlet cavity are arranged at two sides of the oil inlet cavity, the outer side of the oil saving outlet cavity is provided with a hydraulic control cavity at intervals, and the outer side of the oil outlet cavity is provided with an overflow back pressure cavity at intervals.
In order to facilitate the installation of the overflow valve, the preferred technical implementation means is that the outer side of the overflow back pressure cavity is provided with a cover plate, the direct-acting overflow valve is arranged on the cover plate, and the inner side of the cover plate is embedded into the overflow back pressure cavity and forms an annular limiting boss matched with the outer end face of the overflow main valve sleeve.
The blocking caused by the relative movement of the overflow main valve sleeve and the throttling valve core in the pressure-bearing dynamic sealing state is effectively avoided; in the preferred implementation mode, the outer surface of the small diameter at the left side of the throttle valve core is provided with pressure equalizing grooves along the axial direction at intervals and along the radial direction, and the small diameter at the left side of the throttle valve core at the inner side of the overflow main valve sleeve is provided with a spring retainer ring for a shaft along the radial direction.
The applicant needs to say that:
in the description of the present invention, the directions or positional relationships indicated by the terms "two sides", "outer side", "inner end", "outer end face", "inner side", "outer surface", "left side", "right side", "axial", "radial", etc. are directions or positional relationships based on the drawings, are merely for convenience of simplifying the description of the present invention, and do not indicate or imply that the apparatus or elements referred to must have a specific direction, be configured and operated in the specific direction, and thus should not be construed as limiting the present invention.
The invention has the substantial characteristics and the remarkable technical progress that:
1. the invention can realize the technical effects of respectively driving a plurality of executive components with different working pressures and flows by integrating the flow dividing, pressure regulating, speed regulating and reversing and matching with a set of power components, thereby effectively saving the power components; secondly, the device can be suitable for matching with power elements with more types, has lower requirements on the level of system components, and greatly reduces the installation, operation and maintenance costs; thirdly, the speed regulating function is added on the function realization.
2. The invention integrates the functions of flow dividing, pressure regulating, speed regulating and reversing in one valve body, and has good wildness for loads with different working pressures and flows; secondly, because of the structural design with the reversing function, the pressure interference in loops of different execution elements is avoided, and the system failure rate is effectively reduced on the premise of greatly simplifying the control elements; thirdly, the adoption of the structural design with the reversing function effectively meets the design specification requirements that the rated pressure and the discharge capacity of the hydraulic power source are matched with the moving speed and the quality of the load according to the application background of the hydraulic system under the specific working condition.
3. The design of the damping screw, the pore canal, the reset spring and other structures is combined with the pressure feedback of the oil inlet cavity and the throttling oil outlet cavity in the working process, so that the pressure difference value between the oil inlet cavity and the throttling oil outlet cavity, which is generated by the throttling valve core throttling orifice, tends to be balanced in the action state, and the problems of overhigh working medium temperature rise, high energy loss and high long-term overrun operation failure rate of the working element, which are caused by overlarge pressure difference, are solved.
4. The adoption of the direct-acting overflow valve is combined with the pressure change in the overflow back pressure cavity in the working process, so that the working pressure of the system is effectively ensured to be in a set safety range, and the high-pressure hazard to the power element caused by the increase of the working pressure of the oil inlet cavity due to misoperation is avoided by combining with the structural design of the axial spring retainer ring.
5. The speed regulating piston and the speed regulating screw are used as a speed regulating mechanism to act on the throttle valve core, so that the set speed of the executing element connected with the throttle oil outlet cavity is regulated, and the working condition requirements of the executing element with different running speeds are met.
6. The structural design of the pressure equalizing groove effectively avoids the blocking caused by the relative movement of the overflow main valve sleeve and the throttling valve core in the pressure-bearing dynamic sealing state; and secondly, the fit clearance between the overflow main valve sleeve and the throttling valve core in the pressure-bearing dynamic sealing state is balanced, and the internal leakage is reduced.
7. The invention realizes the output of two paths of working media with different pressures and flows in the oil outlet cavity and the throttling oil outlet cavity, firstly, the invention can be assembled with execution elements with different types to realize the functions, and can simplify the structure of control elements for realizing more than two paths of different pressures and flows; and secondly, the control of more than two executive components with different set pressures and flow rates is realized at the output end of the oil outlet cavity in a serial connection mode.
Drawings
Fig. 1 is a front view of the present invention.
Fig. 2 is a top view of the present invention.
Fig. 3 is a left side view of the present invention.
Fig. 4 is a view in the A-A direction of fig. 1.
Fig. 5 is a right side view of the present invention.
Fig. 6 is a B-B view of fig. 5.
Fig. 7 is a perspective view of the present invention.
Fig. 8 is a structural view of a throttle body according to the present invention.
Fig. 9 is a C-C view of fig. 8.
Fig. 10 is a schematic view of the relief valve sleeve of the present invention.
Fig. 11 is a D-D view of fig. 10.
Fig. 12 is a hydraulic schematic of the present invention.
Reference numerals in the drawings are as follows:
1. a cover plate; 2. a direct-acting overflow valve; 3. an oil return passage; 4. a main hole; 5. a throttle valve core; 6. a speed regulating piston; 7. a lock nut; 8. a return spring; 9. overflowing the main valve sleeve; 10. a valve body; 11. speed regulation screw plug; 12. a speed regulating screw; 13. a hydraulically controlled orifice; 14. damping screw; 15. a spring retainer ring; 16. a speed regulating orifice; 17. a pressure equalizing groove; 18. a back pressure port; 19. a choke; p, an oil inlet; t, an oil return port; FL, throttled oil outlet; ZL, oil outlet; FQ, throttled oil outlet cavity; BQ, overflow back pressure chamber; PQ, oil inlet cavity; ZQ, oil outlet cavity; YQ, hydraulically controlled cavity.
Detailed Description
The present invention will be further described with reference to the following examples, but should not be construed as limiting the invention, and the scope of the invention is defined by the appended claims, and any equivalents thereof may be substituted according to the description without departing from the scope of the invention.
The whole structure of the embodiment is shown in the figure, wherein the valve comprises a valve body 10, an oil inlet P arranged on the valve body 10, the oil inlet P is communicated with an oil inlet cavity PQ, and an overflow valve is inserted on the valve body 10; the valve body 10 is provided with an oil return port T, a throttling oil outlet FL and an oil outlet ZL, and an overflow back pressure cavity BQ, an oil outlet cavity ZQ, an oil inlet cavity PQ, an oil saving oil outlet cavity FQ and a hydraulic control cavity YQ which are axially communicated by the main hole 4 are sequentially arranged in the valve body 10 from left to right at intervals; the throttling oil outlet cavity FQ is communicated with a throttling oil outlet FL, the oil outlet cavity ZQ is communicated with an oil outlet ZL, and the oil outlet cavity ZQ and the hydraulic control cavity YQ are communicated through a hydraulic control pore canal 13; the overflow main valve sleeve 9 is inserted into the main hole 4 to form dynamic seal fit, the outer end of the overflow main valve sleeve is assembled with a spigot at the outer end of the main hole 4, and a throttle orifice 19 is arranged at the inner end of the overflow main valve sleeve 9; the overflow main valve sleeve 9 cuts off the oil inlet cavity PQ from the oil outlet cavity ZQ in a non-working state;
the structure unit comprises the following structure units:
A. and a pilot pressure regulating unit: the overflow valve is a direct-acting overflow valve 2, an oil inlet of the direct-acting overflow valve 2 is communicated with an overflow back pressure cavity BQ, and an oil outlet of the direct-acting overflow valve is communicated with an oil return port T through an oil return channel 3; a reset spring 8 is arranged in the overflow back pressure cavity BQ, and two ends of the reset spring 8 respectively act on the outer end face of the overflow main valve sleeve 9 and the inner wall of the overflow back pressure cavity BQ;
B. a throttle switching unit: the throttle valve core 5 is of a variable diameter structure, the small diameter at the left side of the throttle valve core 5 is inserted into the overflow main valve sleeve 9 and is in dynamic seal fit with the overflow main valve sleeve, a speed regulation throttle opening 16 is formed at the joint of the left end face of the large diameter at the right side of the throttle valve core 5 and the outer circle surface, the throttle conduction of the oil outlet cavity FQ and the oil inlet cavity PQ is realized through the speed regulation throttle opening 16, the large diameter at the right side of the throttle valve core 5 is inserted into the main hole 4 between the throttle oil outlet cavity FQ and the hydraulic control cavity YQ and is in dynamic seal fit with the main hole 4, and a spigot matched with the main hole 4 is formed on the large diameter end face at the right side of the throttle valve core 5; a back pressure pore canal 18 arranged in the throttle valve core 5 conducts the throttle outflow oil cavity FQ with the overflow back pressure cavity BQ, and a damping screw 14 is arranged in the back pressure pore canal 18;
C. and the speed regulating unit is used for: the outside of the hydraulic control cavity YQ is sequentially provided with a speed regulating screw plug 11, a locking nut 7 and a speed regulating screw 12, wherein the speed regulating screw 12 is in threaded fit in the speed regulating screw plug 11 and drives a speed regulating piston 6 to axially act on the large-diameter end face on the right side of the throttle valve core 5.
The working principle of this embodiment is as follows:
when in use, the oil outlet cavity and the throttling oil outlet cavity are communicated with corresponding control elements and drive different execution elements through the corresponding control elements.
1. When the control element is in a neutral state, the oil inlet P is communicated with the oil return port T, the power element is started, a working medium enters the oil inlet cavity PQ from the oil inlet P, a part of the working medium enters the throttling outflow oil cavity FQ through a speed regulation throttling port 19 on the throttling valve core 5, and the working medium is unloaded through the control element connected with the throttling outflow oil cavity FQ; the other part of working medium overcomes the acting force of the return spring 8 to push the overflow main valve sleeve 9 to move leftwards, the oil inlet cavity PQ is communicated with the oil outlet cavity ZQ, and when the acting force of the oil inlet cavity PQ on the overflow main valve sleeve 9 is equal to the acting force of the return spring 8, the overflow main valve sleeve 9 is in a dynamic balance state, and the working medium is unloaded through a control element connected with the working medium;
2. when a control element connected with the throttling oil outlet cavity PQ is started, the control element connected with the oil outlet cavity ZQ is in a neutral state, when the pressure in the oil inlet cavity PQ is larger than the sum of the pressure in the overflow back pressure cavity BQ and the acting force of the return spring 8, the overflow main valve sleeve 9 moves leftwards, the working medium flux between the oil inlet cavity PQ and the oil outlet cavity ZQ is increased, the working medium pressure in the oil inlet cavity PQ is reduced to be equal to the sum of the pressure in the overflow back pressure cavity BQ and the acting force of the return spring 8, and when the working medium pressure in the oil inlet cavity PQ is kept to be a fixed value by the overflow main valve sleeve 9 in a balanced state;
when the load changes, the working pressure in the throttling oil outlet cavity FQ changes along with the change, when the working pressure in the throttling oil outlet cavity FQ decreases, the working pressure in the overflow back pressure cavity BQ decreases along with the change of the working pressure because the throttling oil outlet cavity FQ is communicated with the damping screw 14 through the back pressure pore canal 18, when the sum of the working pressure and the acting force of the reset spring is smaller than the working pressure in the oil inlet cavity, the overflow main valve sleeve 9 moves leftwards, the working medium flux between the oil inlet cavity PQ and the oil outlet cavity ZQ increases, and when the working medium pressure in the oil inlet cavity PQ decreases to be equal to the sum of the pressure in the overflow back pressure cavity BQ and the acting force of the reset spring 8, the overflow main valve sleeve 9 is in a balanced state. When the working pressure in the throttle outflow oil cavity FQ increases, the working pressure in the overflow back pressure cavity BQ increases, when the working pressure rises to the point that the sum of the working pressure and the acting force of the return spring 8 is larger than the working pressure in the oil inlet cavity PQ, the overflow main valve sleeve 9 moves rightwards, the working medium flux between the oil inlet cavity PQ and the oil outlet cavity ZQ decreases, and when the working medium pressure in the oil inlet cavity PQ increases to the point that the sum of the working pressure in the overflow back pressure cavity BQ and the acting force of the return spring 8 is equal, the overflow main valve sleeve 9 is in a balanced state, and the working medium pressure in the oil inlet cavity PQ is dynamically adjusted and finally maintained in the working process along with the change of the load.
Due to the load effect, the pressure of the working medium in the throttling oil outlet cavity FQ continuously increases, the pressure of the working medium in the oil inlet cavity PQ and the working medium in the overflow back pressure cavity BQ continuously increases, when the working pressure in the overflow back pressure cavity BQ exceeds the set pressure value of the direct-acting overflow valve 2, the direct-acting overflow valve 2 is opened to rapidly complete the pressure relief of the working medium in the overflow back pressure cavity BQ, due to the damping effect of the damping screw 14, the pressure relief speed of the working medium in the overflow back pressure cavity BQ is higher than the pressure relief speed of the working medium in the throttling oil outlet cavity FQ, the working medium is slowly supplemented into the overflow back pressure cavity BQ, the pressure of the working medium in the overflow back pressure cavity BQ is reduced, the overflow main valve sleeve 9 moves leftwards under the pushing of the working medium in the oil inlet cavity PQ, the working medium pressure in the oil inlet cavity PQ is reduced, and then the working medium pressure in the throttling oil outlet cavity FQ is reduced in turn, when the pressure of the working medium in the overflow back pressure cavity BQ is reduced to be lower than the set pressure value of the direct-acting overflow valve 2, and the working medium reciprocating circulation is enabled to continuously not to exceed the set pressure value of the direct-acting overflow valve 2.
3. When a control element connected with the oil outlet cavity is started, the control element connected with the throttling oil outlet cavity FQ is in a neutral state, the pressure of working medium in the oil outlet cavity ZQ and the oil inlet cavity PQ is increased, the working medium pushes the overflow main valve sleeve 9 to move leftwards, and the working medium flux between the oil inlet cavity PQ and the oil outlet cavity ZQ is increased until a limit step of the overflow main valve sleeve 9 is attached to the limit port 19; simultaneously, a working medium enters the hydraulic control cavity YQ through the back pressure pore canal 18, the throttle valve core 5 is pushed to move leftwards until the spigot of the right large-diameter end face of the throttle valve core is attached to the left end face of the hydraulic control cavity YQ, the speed regulation throttling mouth 16 of the right large-diameter left end face of the throttle valve core 5 is closed, the oil inlet cavity PQ is separated from the throttle oil outlet cavity FQ, and the working medium is completely conveyed to the oil outlet cavity ZQ and acts on an executing element connected with the oil outlet cavity ZQ; when the control element connected with the oil outlet cavity ZQ is in a neutral state, working medium in the oil outlet cavity ZQ is unloaded through the control element, the pressure of the working medium is reduced, the overflow main valve sleeve 9 moves rightwards, when the acting force of the oil inlet cavity PQ on the overflow main valve sleeve 9 is equal to the acting force of the return spring 8, the overflow main valve sleeve 9 is in a dynamic balance state, the working medium is unloaded through the control element connected with the overflow main valve sleeve 9, and simultaneously acts on the right large-diameter end face of the throttle valve core 5 to push the throttle valve core 5 to rightwards to be attached to the speed regulating piston 6, and the working medium enters the throttle outflow oil cavity ZQ through the speed regulating orifice 16 on the throttle valve core 5 and is unloaded through the control element connected with the throttle valve core.
4. When the action movement speed of an executing element connected with the throttling oil outlet cavity FQ needs to be regulated, the axial position of the speed regulating screw 12 is regulated, the speed regulating piston 6 drives the speed regulating orifice 16 on the surface of the throttling valve core 5 to change the axial distance between the surface of the throttling valve core 5 and the matched end surface of the main hole 4, and then the flux of a working medium is regulated.
5. When the actuating element connected with the throttle outflow oil cavity FQ is started to reach a working state, and misoperation of starting the actuating element connected with the oil outflow cavity ZQ occurs, the speed regulation throttling port 16 on the large diameter of the throttle valve core 5 is closed, the left movement of the overflow main valve sleeve 9 is delayed under the action of the overflow back pressure cavity BQ and the return spring 8, and the working pressure in the oil inflow cavity PQ is rapidly increased due to small working medium flux between the oil inflow cavity PQ and the oil outflow cavity ZQ, and high-pressure harm is generated on the power element.
The axial spring retainer ring 15 is used for pushing the overflow main valve sleeve 9 in the axial movement process of the throttle valve core 5, so that the working medium flux between the oil inlet cavity PQ and the oil outlet cavity ZQ is forcedly increased, and the rapid increase of the working pressure in the oil inlet cavity PQ and the high-pressure hazard to the power element are avoided.
Claims (4)
1. The shunt pressure-regulating speed-regulating reversing integrated valve comprises a valve body (10), an oil inlet (P) formed in the valve body (10), the oil inlet (P) is communicated with an oil inlet cavity (PQ), and an overflow valve is inserted in the valve body (10); the oil return valve is characterized in that an oil return port (T), a throttling oil outlet (FL) and an oil outlet (ZL) are formed in a valve body (10), and an overflow back pressure cavity (BQ), an oil outlet cavity (ZQ), an oil inlet cavity (PQ), an oil saving oil outlet cavity (FQ) and a hydraulic control cavity (YQ) which are axially communicated by a main hole (4) are sequentially arranged in the valve body (10) from left to right at intervals; the throttling oil cavity (FQ) is communicated with the throttling oil outlet (FL), the oil outlet cavity (ZQ) is communicated with the oil outlet (ZL), and the oil outlet cavity (ZQ) is communicated with the hydraulic control cavity (YQ) through a hydraulic control pore canal (13); the overflow main valve sleeve (9) is inserted into the main hole (4) to form dynamic seal fit, the outer end of the overflow main valve sleeve is assembled with the spigot of the outer end of the main hole (4), and a throttle orifice (19) is arranged at the inner end of the overflow main valve sleeve (9); the overflow main valve sleeve (9) cuts off the oil inlet cavity (PQ) from the oil outlet cavity (ZQ) in a non-working state;
the structure unit comprises the following structure units:
A. and a pilot pressure regulating unit: the overflow valve is a direct-acting overflow valve (2), an oil inlet of the direct-acting overflow valve (2) is communicated with the overflow back pressure cavity (BQ), and an oil outlet of the direct-acting overflow valve is communicated with the oil return port (T) through the oil return channel (3); a reset spring (8) is arranged in the overflow back pressure cavity (BQ), and two ends of the reset spring (8) respectively act on the outer end surface of the overflow main valve sleeve (9) and the inner wall of the overflow back pressure cavity (BQ);
B. a throttle switching unit: the throttle valve core (5) is of a variable diameter structure, the small diameter at the left side of the throttle valve core is inserted into the overflow main valve sleeve (9) and is in dynamic seal fit with the overflow main valve sleeve, a speed regulation throttle opening (16) is formed at the joint of the left end face of the large diameter at the right side of the throttle valve core and the outer circle surface, the throttle conduction is realized by the oil outlet cavity (FQ) and the oil inlet cavity (PQ) through the speed regulation throttle opening (16), the large diameter at the right side of the throttle valve core (5) is inserted into the main hole (4) between the throttle oil outlet cavity (FQ) and the hydraulic control cavity (YQ) and is in dynamic seal fit with the main hole, and a spigot matched with the main hole (4) is formed on the large diameter end face at the right side of the throttle valve core (5); a back pressure pore canal (18) arranged in the throttle valve core (5) is used for conducting the throttle oil outlet cavity (FQ) and the overflow back pressure cavity (BQ), and a damping screw (14) is arranged in the back pressure pore canal (18);
C. and the speed regulating unit is used for: the outside of the hydraulic control cavity (YQ) is sequentially provided with a speed regulation screw plug (11), a lock nut (7) and a speed regulation screw (12), and the speed regulation screw (12) is assembled in the speed regulation screw plug (11) in a threaded manner and drives a speed regulation piston (6) to axially act on the large-diameter end face on the right side of the throttle valve core (5).
2. The split-flow pressure-regulating speed-regulating reversing integrated valve according to claim 1, wherein the oil outlet cavity (ZQ) and the oil-saving oil outlet cavity (FQ) are arranged on two sides of the oil inlet cavity (PQ), the outer side of the oil-saving oil outlet cavity (FQ) is provided with a hydraulic control cavity (YQ) at intervals, and the outer side of the oil outlet cavity (ZQ) is provided with an overflow back pressure cavity (BQ) at intervals.
3. The split-flow pressure-regulating speed-regulating reversing integrated valve according to claim 1, characterized in that a cover plate (1) is arranged on the outer side of the overflow back pressure cavity (BQ), the direct-acting overflow valve (2) is arranged on the cover plate (1), and the inner side of the cover plate (1) is embedded into the overflow back pressure cavity (BQ) and forms an annular limiting boss matched with the outer end face of the overflow main valve sleeve (9).
4. The diversion, pressure regulation and speed regulation reversing integrated valve according to any one of claims 1-3 is characterized in that pressure equalizing grooves (17) are formed in the outer surface of the small diameter on the left side of the throttle valve core (5) at intervals along the axial direction along the radial direction, and a spring retainer ring (15) for a shaft is arranged on the small diameter on the left side of the throttle valve core (5) on the inner side of the overflow main valve sleeve (9) along the radial direction.
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| CN201810439614.8A CN108412831B (en) | 2018-05-09 | 2018-05-09 | Shunt pressure-regulating speed-regulating reversing integrated valve |
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| CN201810439614.8A CN108412831B (en) | 2018-05-09 | 2018-05-09 | Shunt pressure-regulating speed-regulating reversing integrated valve |
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| CN112049828B (en) * | 2020-08-18 | 2022-04-22 | 温州大学 | Secondary flow distribution device and load sensitive flow distribution mechanism |
| CN112196853B (en) * | 2020-11-05 | 2022-08-16 | 上海航天控制技术研究所 | Hydraulic energy control valve block |
| CN114483696B (en) * | 2022-02-17 | 2022-10-14 | 河北墨峻科技有限公司 | Multipurpose valve with throttling and unloading functions |
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