CN108412831A - Shunt variable voltage control commutation pile-up valve - Google Patents
Shunt variable voltage control commutation pile-up valve Download PDFInfo
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- CN108412831A CN108412831A CN201810439614.8A CN201810439614A CN108412831A CN 108412831 A CN108412831 A CN 108412831A CN 201810439614 A CN201810439614 A CN 201810439614A CN 108412831 A CN108412831 A CN 108412831A
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- oil outlet
- overflow
- valve
- oil
- outlet chamber
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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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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention belongs to valves, particularly relate to a kind of shunting variable voltage control commutation pile-up valve.Including valve body, it is opened in oil inlet, overflow valve and guide's pressure regulation on valve body, throttling switching and speed adjustment unit；Oil return opening, throttling oil outlet, oil outlet are set on valve body, be equipped at intervals in valve body by main aperture axially through overflow back pressure cavity, oil outlet chamber, oil suction chamber, fuel-economizing oil outlet chamber, liquid controling cavity；The oil outlet chamber that throttles connection throttling oil outlet, oil outlet chamber are connected to oil outlet, and oil outlet chamber is with liquid controling cavity through hydraulic control hole link；Overflow main valve housing is plugged in main aperture formation dynamic sealing cooperation and its outer end is assembled with main aperture outer end seam allowance, and inner end is equipped with restriction；Off working state underflow stream main valve housing separates oil suction chamber and oil outlet chamber；The present invention efficiently solves high energy consumption existing in the prior art, working media temperature rises the technical barriers such as fast, has many advantages, such as to can be achieved to respectively drive multiple operating pressures and the different executive component of flow, achievable speed governing relatively low for system component class requirement.
Description
Technical field
The invention belongs to valves, particularly relate to a kind of shunting variable voltage control commutation pile-up valve.
Background technology
Existing Hydraulic Power Transmission System or movable hydraulic mechanical system need more than two work systems, each work system
It is required that flow and operating pressure to have different set, the effect of flow divider made in hydraulic system from the same oil sources to two
The above executive component supplies identical flow (equivalent shunting), or by a certain percentage to two executive component supply flow (ratios
Shunting), to realize that the speed of two executive components keeps synchronizing or surely comparing relationship.
Conventional hydraulic includes：
1, dynamical element
The effect of dynamical element is that the mechanical energy of prime mover is converted into the pressure energy of liquid, refers to the oil in hydraulic system
Pump, it provides power to entire hydraulic system.The structure type of hydraulic pump generally has gear pump, vane pump, plunger pump and screw rod
Pump.
2, executive component
The effect of executive component (such as hydraulic cylinder and hydraulic motor) is that the pressure energy of liquid is converted to mechanical energy, and driving is negative
Load makees straight reciprocating motion or rotary motion.
3, control element
Control element (i.e. various hydraulic valves) controls in hydraulic system and adjusts pressure, flow and the direction of liquid.Root
According to the difference of control function, hydraulic valve can be divided into pressure-control valve, flow control valve and directional control valve.Pressure-control valve includes
Overflow valve (safety valve), pressure reducing valve, sequence valve, pressure switch etc.；Flow control valve includes throttle valve, adjustment valve, shunting collection
Flow valve etc.；Directional control valve includes check valve, hydraulic control one-way valve, shuttle valve, reversal valve etc..According to control mode difference, hydraulic valve
Bang-bang control valve, setting control valve and proportional control valve can be divided into.
4, auxiliary element
Auxiliary element includes fuel tank, oil filter, cooler, heater, accumulator, oil pipe and pipe fitting, sealing ring, quick change
Connector, high-pressure ball valve, hose assembly, pressure measuring tie-in, pressure gauge, oil level indicator, oil thermometer etc..
5, hydraulic oil
Hydraulic oil is the working media that energy is transmitted in hydraulic system, there is various mineral oil, emulsion and synthesis type hydraulic pressure
Several major class such as oil.
According to the difference of the executive component of the scope of application, adaptation, there are many differences for the design requirement of conventional hydraulic
Technology requirement, wherein design of Hydraulic System principal element needed to be considered includes when oil cylinder is as executive component：First, root
The pressure and active area of hydraulic system are designed according to load quality；Second is that designing hydraulic pressure according to the requirement of the movement speed to load
The pressure action area of the effective discharge of working media and executive component in system；Third, rated pressure and the row of hydraulic power supply
Amount should match with load movement speed and quality；Fourth, the latus rectum or the sectional area palpus at minimum of system pipeline and control element
With flows match, it otherwise will appear working media temperature and rise the situations such as excessively high or executive component fluctuation of service.In hydraulic system
In, it is frequently necessary to the different executive component of the multiple load qualities of independent manipulation, velocity of displacement (hydraulic cylinder, hydraulic motor), therefore
Saving dynamical element, simplify control element, the event of reduction system can be reached by carrying out structure design or technological improvement to hydraulic system
The purpose of barrier rate.
For the range that applicant is understood, the technical solution for solving above-mentioned technical problem includes：
1, using quantitative duplex pump as dynamical element
Above-mentioned main problem of the existing technology one is because quantitative duplex pump is that flow presets and cannot be adjusted
, it can not be adaptively adjusted when the operating mode in running environment changes, matching is poor；Second is that quantitative duplex gear pump
Due to it is complicated, lead to its manufacturing cost and high failure rate；Third, when a pump in quantitative duplex pump is in running order,
Although another pump is in off working state, still carries out air transport and transfer to generate reactive loss, while waste of energy
Cause the Wen Sheng of working media.
2, select variable pump is (representative for Variable plunger pump) to be used as dynamical element
Above-mentioned main problem of the existing technology one is that the Variable Control of variable pump is to transmit the measured value of sensor
It to control device and sends out command adapted thereto by it to complete, therefore complicated, of high cost；Second is that variable pump can only realize discharge capacity tune
It is whole, it can not control pressure, it is therefore desirable to be equipped with pressure control valve (such as overflow valve) for each executive component and meet not homogeneity
The load requirement of amount, while also needing to add control element and pipeline to avoid the pressure disturbances in different executive component circuits；
Third, since plunger pump is more demanding for working media cleannes, lead to the system component class requirement being equipped with therewith and operation
Maintenance cost is higher.
3, single constant displacement pump is equipped with throttle valve and overflow valve as control element
Above-mentioned main problem of the existing technology one is to change drift diameter area by throttle valve to realize flow-rate adjustment, is executed
Pressure changes with the variation of load, but due to the effect of constant displacement pump, overflow valve, the pressure of the throttle valve other side is a setting
Value, the pressure difference for inevitably resulting in throttle valve both sides in this way is excessive, can convert pressure difference to thermal energy and generate oil temperature increase,
The phenomenon that energy expenditure；Second is that oil pump runs under high pressure conditions and generates great energy expenditure always, the use of oil pump
Service life greatly shortens；Third, since overflow valve can only be set in the major loop of elevated pressures, it is only capable of meeting setting pressure
Operating mode under force value.
Applicant does not have found patent literature identical or similar to the present application by retrieval.
Invention content
The purpose of the present invention is to provide a kind of shunting variable voltage control commutate pile-up valve, by using will shunt, pressure regulation, tune
Speed, the highly integrated design of commutation, reaching a set of dynamical element of cooperation can realize that respectively drive multiple operating pressures, flow different
The purpose of executive component.
The overall technology of the present invention is conceived：
Variable voltage control commutation pile-up valve is shunted, including valve body, the oil inlet being opened on valve body, oil inlet are connected to oil inlet
Chamber inserts overflow valve on valve body；Oil return opening, throttling oil outlet, oil outlet are opened up on valve body, are spaced successively from left to right in valve body
Offer by main aperture axially through overflow back pressure cavity, oil outlet chamber, oil suction chamber, fuel-economizing oil outlet chamber, liquid controling cavity；The oil outlet chamber that throttles connects
Logical throttling oil outlet, oil outlet chamber are connected to oil outlet, and oil outlet chamber is with liquid controling cavity through hydraulic control hole link；Overflow main valve housing is plugged in master
Hole forms dynamic sealing cooperation and its outer end is assembled with main aperture outer end seam allowance, and overflow main valve housing inner end is equipped with restriction；Inoperative shape
State underflow stream main valve housing separates oil suction chamber and oil outlet chamber；
Including following structural unit：
A, guide's pressure regulation unit：Overflow valve selects direct acting overflow valve, oil inlet and the overflow back pressure cavity of direct acting overflow valve to connect
Logical, oil outlet is connected to through drainback passage with oil return opening；Resetting spring is equipped in overflow back pressure cavity, the both ends of resetting spring are distinguished
Act on overflow main valve housing outer end face and overflow back pressure cavity cavity inner wall；
B, throttle switch unit：Throttling valve core is variable-diameter structure, left side path be plugged in overflow main valve housing and and its
Dynamic sealing coordinates, and right side major diameter left side offers timing throttle mouth with outer round surface junction, and oil outlet chamber is passed through with oil suction chamber
Timing throttle cause for gossip now throttles conducting, on the right side of throttling valve core major diameter be plugged in the main aperture between throttling oil outlet chamber and liquid controling cavity and with
Its dynamic sealing coordinates, and major diameter end face forms the seam allowance being adapted to main aperture on the right side of throttling valve core；The back pressure hole opened up in throttling valve core
Throttling oil outlet chamber is connected with overflow back pressure cavity in road, and damping screw is equipped in back pressure duct；
C, speed adjustment unit：Speed governing screw plug, locking nut, droop adjustment screw, droop adjustment screw screw thread are equipped on the outside of liquid controling cavity successively
It is assemblied in speed governing screw plug and speed-regulating piston is driven to act on major diameter end face on the right side of throttling valve core in an axial direction.
The particular technique design of the present invention also has：
The oil outlet chamber, fuel-economizing oil outlet chamber are set to oil suction chamber both sides, and the outside spacers of fuel-economizing oil outlet chamber are equipped with liquid controling cavity,
Oil outlet chamber outside spacers are equipped with overflow back pressure cavity.
For ease of the installation of overflow valve, preferred technology realization rate is to be equipped with cover board on the outside of the overflow back pressure cavity,
Direct acting overflow valve is set on cover board, the ring that embedded overflow back pressure cavity and formation are adapted to the outer end face of overflow main valve housing on the inside of cover board
Shape positive stop lug boss.
For effectively avoid pressure-bearing dynamic sealing state underflow stream main valve housing because with caused by throttling valve core relative motion
Card resistance；Balanced pressure-bearing dynamic sealing state underflow stream main valve housing and throttling valve core fit clearance reduce interior discharge, preferred to implement
Mode is that path outer surface is axially spaced on the left of the throttling valve core and radially offers balancing slit, overflow main valve housing
Path upper edge is radially provided with axis check ring on the left of the throttling valve core of inside.
Applicant it should be noted that：
In the description of the present invention, term " both sides ", " outside ", " inner end ", " outer end face ", " inside ", " outer surface ",
The orientation or positional relationship of the instructions such as " left side ", " right side ", " axial direction ", " radial direction " is that orientation based on ... shown in the drawings or position are closed
System is merely for convenience of simplifying the description present invention, does not indicate or imply the indicated device or element must be with specific
Orientation, with specific azimuth configuration and operation, therefore be not considered as limiting the invention.
The notable technological progress for the substantive distinguishing features and acquirement that the present invention has is：
1, for the present invention by the Integrated design of shunting, pressure regulation, speed governing, commutation, it is achievable to coordinate a set of dynamical element one
The technique effect for respectively driving the different executive component of multiple operating pressures, flow, effectively saves dynamical element；Second is that can be with
Relatively low for system component class requirement suitable for the dynamical element for coordinating type more, installation and operation expense are substantially
Degree reduces；Third, also adding speed-regulating function on functional implementation.
2, the present invention is integrated with shunting, pressure regulation, speed governing, commutation function in a valve body inner height, first, for different works
The load for making pressure and flow has preferable compatibility；Second is that because of the structure design with commutation function, avoid generating not
With the pressure disturbances in executive component circuit, system failure rate is effectively reduced under the premise of greatly simplifying control element；Three
It is that the use of the structure design with commutation function effectively meets liquid for the application background under hydraulic system specific operation
The design specification requirement that the rated pressure and discharge capacity in pressure power source should match with load movement speed and quality.
3, damping screw, duct, the isostructural design of resetting spring, in conjunction with oil suction chamber in the course of work and throttling oil outlet chamber
Pressure feedback, make oil suction chamber throttling oil outlet chamber between because the pressure difference that throttling valve core restriction generates becomes under action state
In balance, to solve, working media temperature liter is excessively high, energy loss is big, operation element transfinites for a long time caused by pressure difference is excessive
The high problem of operational failure rate.
4, the use of direct acting overflow valve has been effectively ensured in conjunction with the pressure change in overflow back pressure cavity in the course of work and is
Operating pressure of uniting is in the safe range of setting, in conjunction with the structure design of axial check ring, is avoided because maloperation generates
Come the high pressure of dynamical element is endangered of oil suction chamber operating pressure elevated band.
5, throttling valve core is acted on as speed adjusting gear using speed-regulating piston and droop adjustment screw, realize pair and throttled out
The setting speed adjustment of the executive component of oil pocket connection, meets the working condition requirement of the executive component for the different speeds of service.
6, the structure design of balancing slit, when effectively prevent pressure-bearing dynamic sealing state underflow stream main valve housing because with section
Card resistance caused by flow valve core relative motion；Second is that balanced pressure-bearing dynamic sealing state underflow stream main valve housing is matched with throttling valve core
Gap is closed, interior discharge is reduced.
It is 7, of the invention due to realizing the different working media output of two-way pressure, flow in oil outlet chamber, throttling oil outlet chamber,
Above-mentioned function is realized first, can not only be assembled with the executive component of different model, but also can be simplified and be realized two-way or more no
With pressure and the control element structure of flow；Second is that being set to more than two differences by series system realization in oil outlet chamber output end
The control of the executive component of constant-pressure and flow.
Description of the drawings
Fig. 1 is the front view of the present invention.
Fig. 2 is the vertical view of the present invention.
Fig. 3 is the left view of the present invention.
Fig. 4 is the A-A direction views of Fig. 1.
Fig. 5 is the right view of the present invention.
Fig. 6 is the B-B direction view of Fig. 5.
Fig. 7 is the stereoscopic appearance figure of the present invention.
Fig. 8 is the structure chart of throttling valve core in the present invention.
Fig. 9 is the C-C direction views of Fig. 8.
Figure 10 is the structure chart of overflow main valve housing in the present invention.
Figure 11 is the D-D direction views of Figure 10.
Figure 12 is the hydraulic schematic diagram of the present invention.
Reference numeral in attached drawing is as follows：
1, cover board；2, direct acting overflow valve；3, drainback passage；4, main aperture；5, throttling valve core；6, speed-regulating piston；7, locking screw
It is female；8, resetting spring；9, overflow main valve housing；10, valve body；11, speed governing screw plug；12, droop adjustment screw；13, hydraulic control duct；14, it hinders
Buddhist nun's screw；15, check ring；16, timing throttle mouth；17, balancing slit；18, back pressure duct；19, restriction；P, oil inlet；T、
Oil return opening；FL, throttling oil outlet；ZL, oil outlet；FQ, throttling oil outlet chamber；BQ, overflow back pressure cavity；PQ, oil suction chamber；It is ZQ, fuel-displaced
Chamber；YQ, liquid controling cavity.
Specific implementation mode
The present invention is described further with reference to embodiments, but should not be construed as limitation of the invention, the present invention
Protection domain be subject to the content of claim record, any equivalent technical elements made according to specification are replaced,
Protection scope of the present invention is not departed from.
The overall structure of the present embodiment is as shown, including valve body 10, the oil inlet P being opened on valve body 10, and oil inlet
Mouth P is connected to oil suction chamber PQ, and overflow valve is inserted on valve body 10；Oil return inlet T, throttling oil outlet FL, oil outlet ZL are opened up on valve body 10,
In valve body 10 from left to right successively be spaced apart be equipped with by main aperture 4 axially through overflow back pressure cavity BQ, oil outlet chamber ZQ, oil suction chamber
PQ, fuel-economizing oil outlet chamber FQ, liquid controling cavity YQ；The oil outlet chamber that throttles FQ is connected to throttling oil outlet FL, and oil outlet chamber ZQ connection oil outlet ZL go out
Oil pocket ZQ is connected to liquid controling cavity YQ through hydraulic control duct 13；Overflow main valve housing 9 is plugged in main aperture 4 and forms dynamic sealing cooperation and its outer end
It is assembled with 4 outer end seam allowance of main aperture, 9 inner end of overflow main valve housing is equipped with restriction 19；Off working state underflow stream main valve housing 9 is by oil inlet
Chamber PQ separates with oil outlet chamber ZQ；
Including following structural unit：
A, guide's pressure regulation unit：Overflow valve selects direct acting overflow valve 2, oil inlet and the overflow back pressure cavity of direct acting overflow valve 2
BQ is connected to, and oil outlet is connected to through drainback passage 3 with oil return inlet T；Resetting spring 8, resetting spring 8 are equipped in overflow back pressure cavity BQ
Both ends be respectively acting on 9 outer end face of overflow main valve housing and overflow back pressure cavity BQ cavity inner walls；
B, throttle switch unit：Throttling valve core 5 is variable-diameter structure, left side path be plugged in overflow main valve housing 9 and with
Its dynamic sealing coordinates, and right side major diameter left side and outer round surface junction offer timing throttle mouth 16, oil outlet chamber FQ with into
Oil pocket PQ realizes that throttling conducting, 5 right side major diameter of throttling valve core are plugged in throttling oil outlet chamber FQ and liquid controling cavity through timing throttle mouth 16
Coordinate in main aperture 4 between YQ and with its dynamic sealing, 5 right side major diameter end face of throttling valve core forms the seam allowance being adapted to main aperture 4；Throttling
Throttling oil outlet chamber FQ is connected with overflow back pressure cavity BQ in the back pressure duct 18 opened up in spool 5, and damping is equipped in back pressure duct 18
Screw 14；
C, speed adjustment unit：Speed governing screw plug 11, locking nut 7, droop adjustment screw 12, speed governing spiral shell are equipped on the outside of liquid controling cavity YQ successively
12 Screw assemblies are followed closely in speed governing screw plug 11 and speed-regulating piston 6 is driven to act on 5 right side major diameter end face of throttling valve core in an axial direction.
The operation principle of the present embodiment is as follows：
Oil outlet chamber, throttling oil outlet chamber are connected to corresponding control element and are driven by it when use and different executes member
Part.
1, oil inlet P is connected with oil return inlet T when control element is in middle position state, starts dynamical element, working media is certainly
Oil inlet P enters oil suction chamber PQ, and a part of working media enters throttling oil outlet chamber by the timing throttle mouth 19 in throttling valve core 5
FQ is unloaded by the control element being attached thereto；Another part working media overcomes 8 active force of resetting spring to push overflow main valve
Set 9 is moved to the left, and oil suction chamber PQ is connected with oil outlet chamber ZQ, when oil suction chamber PQ is to the active force and resetting spring 8 of overflow main valve housing 9
When active force is equal, overflow main valve housing 9 is in dynamic equilibrium state, and working media is unloaded by the control element being attached thereto；
2, when the control element being connected with throttling oil outlet chamber PQ starts, in being in the oil outlet chamber ZQ control elements being connected
Under the state of position, when the pressure in oil suction chamber PQ is more than pressure and the sum of the active force of resetting spring 8 in overflow back pressure cavity BQ,
Overflow main valve housing 9 is moved to the left, and the working media flux between oil suction chamber PQ and oil outlet chamber ZQ increases, work Jie in oil suction chamber PQ
Matter pressure drop to the pressure in overflow back pressure cavity BQ it is equal with the sum of the active force of resetting spring 8 when, overflow main valve housing 9 is in
Equilibrium state makes the working medium pressure in oil suction chamber PQ remain definite value；
When load changes, the operating pressure in the oil outlet chamber that throttles FQ can change therewith, when in throttling oil outlet chamber FQ
Operating pressure reduce when, due to throttling oil outlet chamber FQ overflow back pressure cavity BQ is connected to damping screw 14 by back pressure duct 18,
Operating pressure in overflow back pressure cavity BQ decreases, when it is reduced to the sum of itself and the active force of resetting spring to be less than oil suction chamber
When interior operating pressure, overflow main valve housing 9 is moved to the left, and the working media flux between oil suction chamber PQ and oil outlet chamber ZQ increases,
The pressure that working medium pressure in oil suction chamber PQ drops in overflow back pressure cavity BQ is equal with the sum of the active force of resetting spring 8
When, overflow main valve housing 9 is in equilibrium state.When operating pressure in the oil outlet chamber that throttles FQ increases, the work in overflow back pressure cavity BQ
It increases as pressure, when it is increased to the sum of itself and the active force of resetting spring 8 more than operating pressure in oil suction chamber PQ, overflows
Stream main valve housing 9 moves right, and the working media flux between oil suction chamber PQ and oil outlet chamber ZQ reduces, and the work in oil suction chamber PQ is situated between
When pressure in matter pressure rise to overflow back pressure cavity BQ is equal with the sum of the active force of resetting spring 8, overflow main valve housing 9 is in
Equilibrium state, working medium pressure in oil suction chamber PQ is with the variation of load dynamically adjustment and final in the above-mentioned course of work
It is maintained.
Due to load effect, working medium pressure continues to increase in throttling oil outlet chamber FQ, oil suction chamber PQ and overflow back pressure
Working medium pressure in chamber BQ persistently increases therewith, when the operating pressure in overflow back pressure cavity BQ is more than direct acting overflow valve 2
When setup pressure value, direct acting overflow valve 2 opens the pressure release for quickly completing overflow back pressure cavity BQ working medias, due to damping screw 14
Damping action, working media pressure release speed of the working media pressure release speed higher than throttling oil outlet chamber FQ in overflow back pressure cavity BQ
Degree, working media are slowly supplemented in overflow back pressure cavity BQ, and working medium pressure declines in overflow back pressure cavity BQ, overflow main valve housing
9 are moved to the left under the promotion of working media in oil suction chamber PQ working medium pressure are caused in oil suction chamber PQ to decline, and then successively
Envoy is flowed out the working medium pressure in oil pocket FQ, overflow back pressure cavity BQ and is declined, the working media pressure in overflow back pressure cavity BQ
When power is decreased below the setup pressure value of direct acting overflow valve 2, direct acting overflow valve 2 is closed, and above-mentioned course of work reciprocation cycle makes
Working media pair provides a setup pressure value no more than direct acting overflow valve 2 with the throttling oil outlet chamber FQ executive components being connected
Continuous action power.
3, when the control element being connected with oil outlet chamber starts, middle position shape is in the throttling oil outlet chamber FQ control elements being connected
Under state, the working medium pressure in oil outlet chamber ZQ and oil suction chamber PQ increases, and working media pushes overflow main valve housing 9 to moving to left
Dynamic, the working media flux between oil suction chamber PQ and oil outlet chamber ZQ increases, until the limit stage and limited mouth of overflow main valve housing 9
19 fittings；It works at the same time medium and liquid controling cavity YQ is entered to by back pressure duct 18, throttling valve core 5 is pushed to be moved to the left its right side
The seam allowance of major diameter end face is bonded with the left end face of liquid controling cavity YQ, the timing throttle mouth 16 of 5 right side major diameter left side of throttling valve core
It closes, oil suction chamber PQ separates with throttling oil outlet chamber FQ, and working media is all delivered to oil outlet chamber ZQ and acts on and oil outlet chamber ZQ
Connected executive component；When the control element being connected with oil outlet chamber ZQ is in middle position state, working media is logical in oil outlet chamber ZQ
Control element unloading is crossed, working medium pressure declines, and overflow main valve housing 9 moves right, when oil suction chamber PQ is to overflow main valve housing 9
When active force is equal with 8 active force of resetting spring, overflow main valve housing 9 is in dynamic equilibrium state, and working media is by being attached thereto
Control element unloading, working media simultaneously act on throttling valve core 5 right side major diameter end face push throttling valve core 5 move right
It is bonded to its right side seam allowance with speed-regulating piston 6, working media is entered by the timing throttle mouth 16 in throttling valve core 5 to be throttled out
Oil pocket ZQ is unloaded by the control element being attached thereto.
4, when needing to adjust with the action movement speed of the throttling oil outlet chamber FQ executive components being connected, droop adjustment screw is adjusted
12 axial position drives the axis for making 5 surface timing throttle mouth 16 and 4 counterface of main aperture of throttling valve core by speed-regulating piston 6
It changes to spacing, and then adjusts the flux of working media.
5, when the executive component startup being connected with throttling oil outlet chamber FQ reaches working condition, generation will be with oil outlet chamber ZQ phases
When the maloperation that executive component even starts, the timing throttle mouth 16 in 5 major diameter of throttling valve core is closed, overflow back pressure cavity BQ with
Under the action of resetting spring 8, overflow main valve housing 9 moves to left slow movement, because of the working media between oil suction chamber PQ and oil outlet chamber ZQ
Flux is small, and operating pressure in oil suction chamber PQ is caused to increase rapidly, and generates high pressure harm to dynamical element.
Promotion is generated to overflow main valve housing 9 with check ring 15 by 5 axial movement axis of throttling valve core, it is mandatory
Increase the working media flux between oil suction chamber PQ and oil outlet chamber ZQ, operating pressure is avoided in oil suction chamber PQ to increase rapidly and right
The high pressure harm that dynamical element generates.
Claims (4)
1. shunting variable voltage control commutation pile-up valve, including valve body (10), the oil inlet (P) being opened on valve body (10), oil inlet
(P) connection oil suction chamber (PQ), valve body insert overflow valve on (10)；It is characterized in that opening up oil return opening (T), throttling on valve body (10)
Oil outlet (FL), oil outlet (ZL), be spaced apart successively from left to right in valve body (10) be equipped with by main aperture (4) axially through overflow
Back pressure cavity (BQ), oil outlet chamber (ZQ), oil suction chamber (PQ), fuel-economizing oil outlet chamber (FQ), liquid controling cavity (YQ)；The oil outlet chamber that throttles (FQ) is connected to
Throttle oil outlet (FL), and oil outlet chamber (ZQ) is connected to oil outlet (ZL), and oil outlet chamber (ZQ) is with liquid controling cavity (YQ) through hydraulic control duct (13)
Connection；Overflow main valve housing (9) is plugged in main aperture (4) formation dynamic sealing cooperation and its outer end is assembled with main aperture (4) outer end seam allowance, overflows
It flows main valve housing (9) inner end and is equipped with restriction (19)；Off working state underflow stream main valve housing (9) is by oil suction chamber (PQ) and oil outlet chamber
(ZQ) separate；
Including following structural unit：
A, guide's pressure regulation unit：Overflow valve selects direct acting overflow valve (2), oil inlet and the overflow back pressure cavity of direct acting overflow valve (2)
(BQ) it is connected to, oil outlet is connected to through drainback passage (3) with oil return opening (T)；Resetting spring is equipped in overflow back pressure cavity (BQ)
(8), the both ends of resetting spring (8) are respectively acting on overflow main valve housing (9) outer end face and overflow back pressure cavity (BQ) cavity inner wall；
B, throttle switch unit：Throttling valve core (5) is variable-diameter structure, left side path be plugged in overflow main valve housing (9) and with
Its dynamic sealing coordinates, and right side major diameter left side offers timing throttle mouth (16), oil outlet chamber (FQ) with outer round surface junction
Realize that throttling conducting, throttling valve core (5) right side major diameter are plugged in throttling oil outlet chamber through timing throttle mouth (16) with oil suction chamber (PQ)
(FQ) main aperture (4) between liquid controling cavity (YQ) is interior and coordinates with its dynamic sealing, and major diameter end face is formed and master on the right side of throttling valve core (5)
The seam allowance of hole (4) adaptation；It the back pressure duct (18) opened up in throttling valve core (5) will throttling oil outlet chamber (FQ) and overflow back pressure cavity
(BQ) it is connected, damping screw (14) is equipped in back pressure duct (18)；
C, speed adjustment unit：Speed governing screw plug (11), locking nut (7), droop adjustment screw (12) are equipped on the outside of liquid controling cavity (YQ) successively, is adjusted
Fast screw (12) Screw assembly is in speed governing screw plug (11) and speed-regulating piston (6) is driven to act on throttling valve core (5) right side in an axial direction
Side major diameter end face.
The pile-up valve 2. shunting variable voltage control according to claim 1 commutates, it is characterised in that the oil outlet chamber (ZQ), section
Oily oil outlet chamber (FQ) is set to the both sides oil suction chamber (PQ), and the outside spacers of fuel-economizing oil outlet chamber (FQ) are equipped with liquid controling cavity (YQ), oil outlet chamber
(ZQ) outside spacers are equipped with overflow back pressure cavity (BQ).
The pile-up valve 3. shunting variable voltage control according to claim 1 commutates, it is characterised in that the overflow back pressure cavity
(BQ) outside is equipped with cover board (1), and direct acting overflow valve (2) is set on cover board (1), embedded overflow back pressure cavity (BQ) on the inside of cover board (1)
And form the annular stop boss being adapted to the outer end face of overflow main valve housing (9).
The pile-up valve 4. shunting variable voltage control according to any one of claim 1-3 commutates, it is characterised in that the section
Path outer surface is axially spaced on the left of flow valve core (5) and radially offers balancing slit (17), on the inside of overflow main valve housing (9)
Path upper edge is radially provided with axis check ring (15) on the left of throttling valve core (5).
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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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| CN108412831A true CN108412831A (en) | 2018-08-17 |
| CN108412831B CN108412831B (en) | 2023-07-25 |
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| CN112049828A (en) * | 2020-08-18 | 2020-12-08 | 温州大学 | Secondary flow distribution device and load sensitive flow distribution mechanism |
| CN112196853A (en) * | 2020-11-05 | 2021-01-08 | 上海航天控制技术研究所 | Hydraulic energy control valve block |
| CN114483696A (en) * | 2022-02-17 | 2022-05-13 | 河北墨峻科技有限公司 | Multipurpose valve with throttling and unloading functions |
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| 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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|---|---|
| CN108412831B (en) | 2023-07-25 |
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