CN203384150U - Dual-purpose multipath hydraulic proportional valve - Google Patents
Dual-purpose multipath hydraulic proportional valve Download PDFInfo
- Publication number
- CN203384150U CN203384150U CN201320440370.8U CN201320440370U CN203384150U CN 203384150 U CN203384150 U CN 203384150U CN 201320440370 U CN201320440370 U CN 201320440370U CN 203384150 U CN203384150 U CN 203384150U
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- pump
- module
- pressure
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Fluid-Pressure Circuits (AREA)
- Mechanically-Actuated Valves (AREA)
Abstract
The utility model relates to a dual-purpose multipath hydraulic proportional valve which comprises a pump connecting module, wherein a second main oil way channel of the pump connecting module is sequentially communicated with the oil inlet of the pump connecting module, a hole in a valve rod of a tee joint overflow valve and an internal oil channel of the valve rod; one path of the second main oil way channel is connected with a first throttling hole and a spring cavity of the valve rod, and the other path of the second main oil way channel is connected with the left end of the valve rod of the tee joint overflow valve; pressure oil in a first loading pressure feedback oil way channel fed back by an executive module sequentially goes into an LS oil inlet, a small hole, a second throttling hole, an oil hole and the spring cavity of the valve rod of the pump connecting pump; the second throttling hole is communicated with an oil channel between the small hole and a third throttling valve and an oil channel between the first throttling hole and the spring cavity of the valve rod; a control pressure oil way is realized in the way that pump outlet pressure oil goes into a reducing valve from the oil inlet of the pump connecting module via a small hydraulic fluid port and a P hydraulic fluid port pressure collection point, and the other end of the reducing valve is connected with the executive module through an oil outlet hole. The dual-purpose multipath hydraulic proportional valve is suitable for both a variable pump and a constant delivery pump, and necessary flow is provided for maintaining the operation of the system only under the working pressure required by a load.
Description
Technical field
The utility model belongs to the cooling system of hydraulic press technical field, particularly a kind of dual-purpose multipath hydraulic Proportional valve.
Background technique
Hydraulic system is concluded roughly several forms:
1. constant pressure system
Provide constant flow by metering pump, system pressure is to be determined by the load acted on working medium, system limits maximum pressure by a high-pressure overflow valve, when system works pressure reaches setting value, almost all flow will be by the relief valve oil sump tank for oil hydraulic pump, power loss is large, generates heat high, and system effectiveness is low.
2. constant flow system
This system, by the metering pump fuel feeding, coordinates the Proportional valve with the threeway relief valve, and the valve rod opening pressure reduction that connection is carried out by Proportional valve in the position of threeway relief valve spool is definite, and unnecessary flow returns to fuel tank by the threeway relief valve.
3. variable pump systems
The hydraulic variable flow pumping system of meta sealing, this system is cancelled the system relief valve, in the meta sealing of execution valve or load, exceeds specified setting range, the compensator of variable displacement pump inside, by the piston of pressure limiting variable, the swashplate angle of pump is diminished, discharge capacity is almost equal to zero, now the variable displacement pump outlet pressure is higher, in the high-pressure service wait state, until be overcome or the state of a control of recovery operation valve to load, the shortcoming of this system is, Displacement Regulation under high pressure, cause the power loss heating large again.
4. the variable pump systems that the variable displacement pump of being controlled by induced pressure and bringing onto load pressure feedback Proportional valve group are positive.
The variable displacement pump that induced pressure is controlled receives the executive component working pressure oil (induced pressure oil is again the LS signal) fed back by Proportional valve, experience system pressure-traffic requirement, pump only provides the hydraulic oil of the needed flow of load and pressure, executive component working pressure (loaded work piece pressure) response that the pressure of variable displacement pump comes with the Proportional valve feedback, a little more than loaded work piece pressure; The flow of load sensitive pump cuts down opening degree by the cunning of Proportional valve and controls, and only provide executive component required flow, and not affected by induced pressure, unnecessary flow loss rarely, this system is comparatively advanced at present, and efficiency is higher.
Dual-purpose self check multi-channel proportional valve is exactly the variable pump systems that the variable displacement pump controlled by induced pressure for Equations of The Second Kind constant flow system and the 4th class and bringing onto load pressure feedback Proportional valve form.
What each large renowned company of the whole world often adopted at present is the system that metering pump adds quantitative Proportional valve, as follows with the system introduction of variable displacement pump addition of variable Proportional valve:
While connecing pump module for metering pump
Connect pump module at the Executive Module selector valve working condition during at neutral position, as shown in figure 22, Executive Module commutation valve rod, when neutral position, connects the module of pump module for metering pump, the sealing of P mouth, load feedback LS filler opening leads to oil circuit.When quantitative oil pump starts, pressure fuel pump oil enters the pressure hydraulic fluid port that connects pump module, valve rod pressure oil effect end through closing oil path to an end of threeway overflow valve rod, promote threeway overflow valve rod, the spring force overcome in threeway relief valve spring chamber moves, cut-in pressure oil P leads to the oil circuit of oil circuit, and pressure fuel pump oil is through the off-load of threeway relief valve.
Connect pump module at the Executive Module selector valve working condition during at working position, as shown in figure 22, Executive Module commutation valve rod (A mouth or B mouth are opened) when working position, connect the module P mouth logical executive component (A mouth or B mouth) of pump module for metering pump, for the executive component fuel feeding, the executive component pressure feedback arrives for metering pump module LS filler opening, enter the spring chamber of threeway relief valve through the 3rd throttle orifice and oil circuit, threeway overflow valve rod one end (valve rod pressure oil effect end) has pressure oil effect and the other end spring chamber to have the pressure oil of executive component feedback to add that spring force dynamically is being issued to balance.
When induced pressure surpasses the setting pressure of precursor overflow valve, precursor overflow valve is opened, the overflow of threeway relief valve, and system pressure is controlled under corresponding pressure and no longer raises.
While connecing pump module for variable displacement pump
Connect pump module at Executive Module commutation valve rod the working condition during at neutral position, as shown in figure 23, Executive Module commutation valve rod in immediately, connect the module of pump module for variable displacement pump, the sealing of P mouth, load feedback LS filler opening leads to oil circuit.When variable displacement pump starts, the pressure oil of variable displacement pump enters the pressure hydraulic fluid port that connects pump module, enter into Executive Module through the P mouth, enter into the valve rod spring chamber of threeway relief valve and the valve rod pressure oil effect end of threeway relief valve through closing oil path, the threeway relief valve, in closed condition, forms an enclosed cavity between pump and valve.The external hydraulic fluid port of LS is communicated with the LS hydraulic fluid port of variable displacement pump, when Executive Module commutation valve rod neutral position, the external hydraulic fluid port of LS does not have the induced pressure feedback in unloading condition, variable displacement pump outlet pressure oil now acts on the pressure-flow compensator of variable displacement pump, compensator controlled variable pump swashplate angle reaches less position, and variable displacement pump only provides less flow and pressure.
Connect the situation that pump module at Executive Module commutation valve rod at working position is, as shown in figure 23, Executive Module commutation valve rod (A mouth or B mouth are opened) when working position, the P mouth that connects pump module is communicated with executive component (A mouth or B mouth are opened), for the executive component fuel feeding, the executive component pressure feedback, to connecing the pump module oilhole, feeds back to the LS filler opening of variable displacement pump through the LS hydraulic fluid port, variable displacement pump is provided according to the signal of load feedback by the angle of swash plate, the flow and the pressure that only provide load to need.Do not have unnecessary flow to flow out from the threeway relief valve.
When induced pressure surpasses the setting pressure of precursor overflow valve, precursor overflow valve is opened unnecessary flow and is flowed out from the threeway relief valve, and system pressure is controlled under corresponding pressure, no longer raises.
Although the enclosed hydraulic system of above-mentioned meta has the advantages such as discharge capacity is adjustable, the shortcoming of its existence also can not be ignored, near the discharge capacity Maximum operating pressure that oil hydraulic pump is attempted under all operating modes all to realize limiting is regulated, but also has such class operating mode in hydraulic system: i.e. expectation obtains larger flow and desired working pressure is very low.The hydraulic system of Center-Close has caused higher Pressure Drop and produced a large amount of heat in the energy loss process under this kind of operating mode.
In addition, process screw on front cover body and bonnet spring shield, directly withstand the selector valve both ends of the surface by protecgulum adjusting screw and bonnet adjusting screw, there are two defects in this kind of structure: the one, and the adjusting screw on spring shield is adjusted inconvenient in the back, and while adjusting, oil leakage phenomenon appears, the 2nd, and the adjusting screw frangibility causes leakage of oil.
Summary of the invention
The utility model provides a kind of variable displacement pump that can both be applicable to also to be applicable to metering pump for solving the technical problem existed in known technology, under the working pressure needed in load, only provides the necessary flow that maintains system works.
The technological scheme that the utility model is taked for the technical problem existed in the solution known technology is:
A kind of dual-purpose multipath hydraulic Proportional valve, comprise Executive Module, the both sides of described Executive Module connect respectively tail gang mould piece and connect pump module by oil circuit, be provided with commutation valve rod means for adjusting limit of movement on described Executive Module, the described pump module that connects mainly comprises and connects the pump module valve body by what connect that the pump module internal oil passages connects, threeway relief valve and precursor overflow valve, the described pump module internal oil passages that connects is mainly by the first working connection, the second working connection, the 3rd working connection, the first induced pressure feedback asphalt channel, the second induced pressure feedback asphalt channel, the 3rd induced pressure feedback asphalt channel, the pilot pressure oil circuit, the first oil return circuit and the second oil return circuit form,
Described the second main oil channel channel, be communicated with the inner oil duct of hole, valve rod connect on pump module filler opening, threeway relief valve valve rod successively, and a road is to first segment discharge orifice, valve rod spring chamber, and another road is to the left end of threeway relief valve valve rod; Described first segment discharge orifice is arranged in the valve rod of threeway relief valve;
Described the first induced pressure feedback asphalt channel, the pressure oil fed back by Executive Module enters successively and connects pump module LS filler opening, aperture, second section discharge orifice, oilhole, valve rod spring chamber, the oil duct between described second section discharge orifice connection aperture and the 3rd throttle valve and the oil duct between first segment discharge orifice and valve rod spring chamber.
The aperture of described first segment discharge orifice is tiny and all less than the aperture of second section discharge orifice and the 3rd throttle orifice.
Self check path U is set between the Executive Module LS filler opening of described Executive Module and Executive Module oil circuit, described Executive Module oil circuit is communicated with the first shuttle valve, described the first shuttle valve is communicated with recuperation valve, described the first shuttle valve is communicated with the second shuttle valve by the Executive Module oil circuit, described the second shuttle valve and A mouth, B mouth load feedback pressure pressure-limit valve is communicated with.
Described commutation valve rod means for adjusting limit of movement mainly is comprised of front cover body and the handle chassis with handle, the described handle chassis with handle is connected on front cover body by transaxle, be provided with on described handle chassis that A mouth symmetrical along horizontal center line and that have an identical angle with horizontal center line is regulated stop screw and the B mouth is regulated stop screw, be provided with axle sleeve on described transaxle, one end of described transaxle is provided with the bulb finger vertical with transaxle, and the termination of described bulb finger is arranged in the groove of Executive Module commutation valve rod coupling shaft.
Also include self check oil circuit and the hand pump module be connected with tail gang mould piece.
Described hand pump module is by hand pump valve body and hand pump, the hand pump inlet port of described hand pump is connected tail gang mould piece T hydraulic fluid port, the hand pump oil outlet of described hand pump is connected external hydraulic fluid port, the hand pump inlet port of described hand pump is connected tail gang mould piece LS filler opening, and between described tail gang mould piece LS filler opening and tail gang mould piece T hydraulic fluid port, the M place of oil circuit is provided with the stifled passage of oil can be installed.
Described self check oil circuit comprises connecing on pump module can place dead stifled Y place oil duct, and described Y place oil duct is arranged on the oil circuit connect between pump module filler opening and reduction valve, and the described reduction valve the other end connects Executive Module by oil outlet.
Described self check oil circuit comprises the dead stifled Y place oil duct of placing connect on pump module, described Y place oil duct is arranged on the oil circuit connect between pump module filler opening and reduction valve, the described reduction valve the other end connects Executive Module by oil outlet, be provided with on Executive Module LS filler opening on described Executive Module and the oil circuit between the first shuttle valve and can place dead stifled U place oil duct, described the first shuttle valve by oil circuit with connect pump module and be communicated with.
The described pump module filler opening place that connects that connects pump module arranges an external one-way valve.
The described valve oil mouth that connects that connects pump module connects two position two-way valve, and described two position two-way valve is communicated with fuel tank.
Advantage and the good effect that the utlity model has are: the utility model can both be applicable to variable displacement pump and also be applicable to metering pump, only provide the necessary flow that maintains system works under the working pressure needed in load, at the Executive Module valve rod during in neutral position, variable displacement pump is confessed larger flow fluid through connecing pump module T mouth draining, can dispel the heat through cooler, reach the purpose of working clearance cooling oil.
The accompanying drawing explanation
Fig. 1 is the utility model structural representation;
Fig. 2 connects the pump module hydraulic schematic diagram;
Fig. 3 connects the pump module plan view;
Fig. 4 is Fig. 3 left side view;
Fig. 5 is Fig. 3 N-N sectional view;
Fig. 6 is that attempt on Fig. 3 right side;
Fig. 7 is Fig. 3 U-U sectional view;
Fig. 8 connects the pump module partial sectional view;
Fig. 9 is the Executive Module hydraulic schematic diagram;
Figure 10 is the Executive Module plan view;
Figure 11 is Figure 10 side view;
Figure 12 is that Figure 11 P-P is to sectional view;
Figure 13 is Figure 12 U amplification view;
Figure 14 is front cover body partial cutaway schematic diagram;
Figure 15 is that Figure 14 X-X is to sectional view;
Figure 16 is Figure 14 side view;
Figure 17 is that Figure 14 W-W is to sectional view;
Figure 18 is that tail gang mould piece adds the hand pump hydraulic schematic diagram;
Figure 19 is that tail gang mould piece adds hand pump module plan view;
Figure 20 is Figure 19 side view;
Figure 21 is Figure 19 partial sectional view;
Figure 22 improves to connect pump module for hydraulic system with constant displacement pump figure before;
Figure 23 improves to connect pump module for the variable displacement pump hydraulic scheme before;
Figure 24 is that the utility model is for metering pump and variable displacement pump hydraulic scheme.
In Fig. 1～24, 1. hand pump module, 101. the external LSZ hydraulic fluid port of load feedback, 102. hand pump oil outlet, 103. hand pump, 104. hand pump inlet port, 105. hand pump valve body, 2. tail gang mould piece, 201. tail gang mould piece LS hydraulic fluid port, 202. tail gang mould piece P hydraulic fluid port, 203. tail gang mould piece T hydraulic fluid port, 204. tail connection valve body, 205. external hydraulic fluid port, 206.T1 hole, 207.TP mouthful, 3. Executive Module, 301. Executive Module pressure oil P mouth, 302. Executive Module return opening, 303. Executive Module LS oil outlet, 304. the first shuttle valve, 305. Executive Module oil circuit, 306. recuperation valve, 307. Executive Module LS filler opening, 308. the second shuttle valve, 309. Executive Module B mouth load feedback oil circuit, 310. Executive Module pressure oil circuit, 311. Executive Module oil return circuit, 312. Executive Module A mouth load feedback oil circuit, 313. Executive Module B mouth load feedback collection point, 314. Executive Module A mouth load feedback collection point, 315. induced pressure feedback oil circuit, 316. Executive Module pressure oil P mouth, 317. Executive Module oil return T mouth, 318. selector valve, carry oil sucting valve 319.A make a slip of the tongue, 320. sealing plug cock, carry oil sucting valve 321.B make a slip of the tongue, 322.A mouthful load feedback pressure pressure-limit valve, 323.B mouthful load feedback pressure pressure-limit valve, 324.B mouthful solenoid-operated proportional reduction valve, 325.A mouthful solenoid-operated proportional reduction valve, 326. protecgulum, 327. bonnet spring shield, 328. handle chassis, 329. front cover body, 330.A mouthful adjusting stop screw, 331. bulb finger, 332. Executive Module commutation valve rod coupling shaft, 333. guide's oilhole, 334.O oblique crank Z cover seal ring, 335. axle sleeve, 336. transaxle, 337. transaxle O-ring seals, 338.B mouthful adjusting stop screw, 4. connect pump module, 401. pressure measurement oilhole, 402. little hydraulic fluid port, 403. reduction valve, 404. one-way valve, 405. connect pump module filler opening (P mouth), 406. oil back chamber (T mouth), 407.P hydraulic fluid port pressure acquisition point, 408. first segment discharge orifice, 409. oilhole, 410. second section discharge orifice, 411. aperture, 412. connect pump module LS filler opening, 413. valve rod pressure oil effect end, 414. the 3rd throttle orifice, 415.LS external hydraulic fluid port, 416. connect the pump module working connection, 417. threeway relief valve, 418. precursor overflow valve, 419. precursor overflow valve oil circuit, 420. connect the pump module return opening, 421. Executive Module is communicated with hydraulic fluid port, 422. valve rod spring chamber, 423. oil outlet, 424. connect the valve oil mouth.
Embodiment
For further understanding model utility content of the present utility model, Characteristic, hereby exemplify following examples, and coordinate accompanying drawing to be described in detail as follows:
Refer to Fig. 1, a kind of dual-purpose multipath hydraulic Proportional valve, comprise that the both sides that connect pump module 4, Executive Module 3, tail gang mould piece 2 connect respectively hand pump module 1 and Executive Module 3, Executive Module 3 with connect pump module 4 and be connected, connecing pump module 4 is connected with pump, can connect metering pump, but link variable pump again connects between pump module 4 and Executive Module 3 and is provided with the self check oil circuit.
Referring to Fig. 2～Fig. 8, connect pump module 4 and mainly comprise that the oil circuit that connects pump module 4 mainly is comprised of the first working connection, the second working connection, the 3rd working connection, the first induced pressure feedback asphalt channel (abbreviation of executive component working pressure feedback oil circuit), the second induced pressure feedback asphalt channel, the 3rd induced pressure feedback asphalt channel, pilot pressure oil circuit, the first oil return circuit and the second oil return circuit by connecing one-way valve 404 that the pump module internal oil passages connects, connecing pump module valve body, threeway relief valve 417 and precursor overflow valve 418.
Article three, the composition that connects the pump module working connection is respectively:
The first main oil channel channel, be communicated with successively and connect pump module filler opening 405, little hydraulic fluid port 402, two pressure taps 401;
The second main oil channel channel, be communicated with successively the inner oil duct of hole, valve rod, the road that connect on pump module filler opening 405, threeway relief valve 417 valve rods and arrive first segment discharge orifice (valve rod throttle orifice) 408, valve rod spring chamber 422; Another road is to the left end of threeway relief valve valve rod;
The 3rd main oil channel channel, be communicated with connect pump module filler opening 405, Executive Module is communicated with hydraulic fluid port 421, for the Executive Module of back provides pressure oil;
Article four, the composition of induced pressure feedback oil circuit (LS) is respectively:
The first induced pressure feedback asphalt channel, the pressure oil fed back by Executive Module enters successively and connects pump module LS filler opening 412, aperture 411, second section discharge orifice 410, oilhole 409, valve rod spring chamber 422; Oil duct between second section discharge orifice 410 connection apertures 411 and the 3rd throttle orifice 414 and the oil duct between first segment discharge orifice 408 and valve rod spring chamber 422;
Second connects pump module induced pressure feedback asphalt channel, and the pressure oil fed back by Executive Module enters successively and connects pump module LS filler opening 412, oil duct, the external hydraulic fluid port 415 of LS;
The 3rd connects pump module induced pressure feedback asphalt channel, the induced pressure oil fed back by Executive Module enters the LS pressure tap that connects pump module LS filler opening 412, oilhole, oil duct, precursor overflow valve 418 successively, and precursor overflow valve 418 is opened by precursor overflow valve oil circuit 419 oil sump tanks;
The 4th connects pump module induced pressure feedback asphalt channel, the induced pressure oil fed back by Executive Module enters successively and connects pump module LS filler opening 412, oilhole, oil duct, the 3rd throttle orifice 414, the 3rd throttle orifice 414 is divided into two-way, one route hydraulic fluid port enters threeway relief valve valve rod spring chamber 422, and another road arrives the off-load hydraulic fluid port;
The pilot pressure oil circuit is: pump discharge pressure oil is by connecing pump module filler opening 405, enter reduction valve 403 through little hydraulic fluid port 402, P hydraulic fluid port pressure acquisition point 407, reduction valve 403 is offered back using the pressure oil of about 30bar left and right of reducing pressure Executive Module by oil outlet 423 is used as pilot pressure oil, meet between pump module filler opening 405 and reduction valve 420 the Y place on oil circuit and feign death when using hand pump stifledly, block oil circuit control and use;
Article two, oil return circuit is respectively:
The first oil return circuit passage, by connecing pump module return opening 420 through the direct oil sump tank of oil back chamber (T mouth) 406;
The second oil return circuit passage, by connecing pump module filler opening 405 through 417 off-loads of threeway relief valve, then by oil back chamber (T mouth) 406 oil sump tanks.
Referring to Fig. 9～Figure 17, Executive Module 3 comprise valve body, recuperation valve 306, selector valve 318, A make a slip of the tongue carry an oil sucting valve 319, B makes a slip of the tongue and carries an oil sucting valve 321, A mouth load feedback pressure pressure-limit valve 322, B mouth load feedback pressure pressure-limit valve 323, protecgulum 326, bonnet spring shield 327, B mouth solenoid-operated proportional reduction valve 324, A mouth solenoid-operated proportional reduction valve 325, the second shuttle valve 308, the first shuttle valves 304, self check cut off point U;
Executive Module working connection: by the pressure oil that connects pump module and come, enter successively the Executive Module pressure oil circuit 310 in Executive Module pressure oil P mouth 316, pressure-compensated valve 306, confining pressure oil district, commutation valve rod middle part, when the valve rod of selector valve 318 moves to right, Executive Module pressure oil circuit 310 is connected with the B mouth, now A mouth and Executive Module oil return circuit 311 are connected, when the valve rod of selector valve 318 moves to left, the pressure oil district of Executive Module pressure oil circuit 310 and A mouth are connected, and now the B mouth communicates with the oil return of Executive Module oil return circuit 311;
Executive Module induced pressure feedback oil circuit: when the valve rod of selector valve 318 moves to right, pressure oil enters executive component by the B mouth, the working pressure oil of executive component, enter into Executive Module B mouth load feedback oil circuit 309 by Executive Module B mouth load feedback collection point 313, the steel ball that the working pressure oil of executive component is pushed open in the second shuttle valve 308 is blocked towards the oil circuit of Executive Module A mouth load feedback oil circuit 312, enter Executive Module oil circuit 305, now the A mouth is connected, 311 oil returns of Executive Module oil return circuit, Executive Module A mouth load feedback oil circuit 312 is connected oil return with the oilhole of selector valve 318.
When the valve rod of selector valve 318 moves to left, the pressure oil at Executive Module pressure oil circuit 310 places enters executive component by the A mouth, the working pressure oil of executive component is incorporated into Executive Module A mouth load feedback oil circuit 312 by the oilhole of selector valve 318, the working pressure oil of executive component is pushed the steel ball of the second shuttle valve 308 open and is blocked towards the oil circuit of Executive Module B mouth load feedback oil circuit 309, enter Executive Module oil circuit 305, now the B mouth is connected Executive Module oil return circuit 311, and Executive Module B mouth load feedback collection point 313 and Executive Module B mouth load feedback oil circuit 309 are connected oil return;
The induced pressure feedback oil of the right side Executive Module oil circuit 305 of the first shuttle valve 304 is from this valve block, A mouth or B mouth executive component working pressure oil, the first shuttle valve 304 left hole induced pressures feedback oil are from the working pressure oil of the executive component of adjacent Executive Module, and in the middle of the first shuttle valve 304, the Executive Module LS filler opening 303 of oil circuits leads to the induced pressure feedback hole that connects pump module or adjacent Executive Module;
Between Executive Module oil circuit 315 and Executive Module LS filler opening, self check path U is set, the sealing plug cock 320 of packing at the U place during self check of this module, block the executive component working pressure oil circuit Executive Module LS filler opening 307 that leads to adjoining Executive Module.
Also be provided with Executive Module commutation valve rod means for adjusting limit of movement on Executive Module 3, mainly by front cover body 329, handle chassis 328 with handle, the A mouth is regulated stop screw 330, the B mouth is regulated stop screw 338, bulb finger 331, Executive Module commutation valve rod coupling shaft 332, transaxle 336, axle sleeve 335 forms, handle chassis 328 with handle is connected on front cover body 329 by transaxle 336, be provided with on handle chassis 328 that A mouth symmetrical along horizontal center line and that have an identical angle with horizontal center line is regulated stop screw 330 and the B mouth is regulated stop screw 338, be provided with axle sleeve 335 on transaxle 336, be provided with the transaxle O-ring seals between axle sleeve 335 and transaxle 336, be provided with O oblique crank Z cover seal ring 334 between axle sleeve 335 and front cover body 329, one end of transaxle 336 is provided with the bulb finger 331 vertical with transaxle 336, the termination of bulb finger 331 is arranged in the groove of Executive Module commutation valve rod coupling shaft 332.
The commutation valve rod of Executive Module moves, drive that spacing handle turns, adjusting screw top on spacing handle props up the boss on protecgulum, change by the length of regulating stop screw the angle that spacing handle rotates, thereby limit the openings of sizes of commutation valve rod, the distance that the commutation valve rod of change Executive Module moves.
Limiting hand protecgulum oil circuit control, pilot pressure oil is entered by guide's oilhole 333, then by oil circuit, enters the protecgulum chamber, promotes the commutation valve rod and moves right.
Referring to Figure 18～Figure 21, Executive Module 3 is connected with tail gang mould piece 2, and tail gang mould piece 2 joins valve body 204 by tail and is connected with hand pump valve body 105, and hand pump valve body 105 connects hand pump 103.
Tail connection oil circuit comprises working connection, induced pressure feedback oil circuit figure, hand pump oil circuit, oil circuit, oil circuit control five parts;
Tail gang mould piece working connection, the Executive Module pressure oil P mouth 301 of the tail gang mould piece P hydraulic fluid port 202 adjacent Executive Modules 3 of UNICOM, the hydraulic fluid port linked at the tail connection is as external hydraulic fluid port 205.
Tail gang mould piece induced pressure feedback oil circuit is entered by the tail gang mould piece LS hydraulic fluid port 201 of the induced pressure feedback oil circuit of the adjacent Executive Module 3 of UNICOM successively, to the external hydraulic fluid port 101 of LSZ, through Figure 18 M place, import the oil return circuit of tail gang mould piece T hydraulic fluid port 203, M packs at place and blocks towards the oil return circuit of tail gang mould piece T hydraulic fluid port 203 when oil blocks up, and now induced pressure feedback oil is connected on the induced pressure feedback oil circuit (LS oil circuit) of another Proportional valve through the external hydraulic fluid port 101 of LSZ.
Tail gang mould piece hand pump oil circuit: hand pump inlet port 104 is connected tail gang mould piece T hydraulic fluid port 203, the hand pump oil outlet 102 external hydraulic fluid ports 205 of UNICOM;
Tail gang mould piece oil circuit: two tail gang mould piece T hydraulic fluid ports 203 pass through oil circuit UNICOM, then by T1 hole 206 oil sump tanks.
Tail gang mould piece oil circuit control: oil circuit control is by the independent oil sump tank of TP hydraulic fluid port 207 of tail gang mould piece.
Job description: when the utility model connects pump module for metering pump, referring to Fig. 2, when Executive Module commutation valve rod, during at neutral position, connect 421 mouthfuls of sealings of pump module P mouth, the load feedback hydraulic fluid port connects the logical oil circuit of pump module LS filler opening 412.
The oil outlet of metering pump connects pump module filler opening 405(P mouth), during the metering pump running, Executive Module commutation valve rod seals at neutral position, pump discharge pressure oil is waited in commutation valve rod meta confined area, executive component working pressure feedback channel place unloading condition, the spring chamber of threeway relief valve 417 is equally in unloading condition.
When the pressure of metering pump progressively rises, pressure oil enters by P hydraulic fluid port pressure acquisition point 407 on valve rod the central oil passage that connects pump module threeway overflow valve rod, be divided into two-way, wherein lead up to and connect the valve rod pressure oil effect end 413 that the arrival of pump module threeway relief valve valve rod central oil passage connects pump module threeway relief valve, another road is by connecing the valve rod central oil passage of pump module threeway relief valve, enter through first segment discharge orifice 408 the valve rod spring chamber 422 that connects pump module threeway relief valve, now valve rod spring chamber 422 is through second section discharge orifice 410, connect respectively pump module LS filler opening 412 with the 3rd throttle orifice 414.Because the aperture of first segment discharge orifice 408 is tiny and all less than the aperture of second section discharge orifice 410 and the 3rd throttle orifice 414, therefore the flow, the pressure loss that cause are minimum, at pump module LS filler opening 412 during in unloading condition, because the valve rod spring chamber 422 that connects pump module threeway relief valve right-hand member still is in unloading condition, valve rod spring chamber 422 can not set up pressure, be close to and only have spring-force driven dual on threeway overflow valve rod at valve rod spring chamber 422, so act on the power that connects pump module threeway relief valve valve rod right-hand member, remain the active force that spring force produces.Threeway overflow valve rod pressure oil effect end 413 is under the effect of pressure oil, overcome the spring force of the threeway overflow valve rod the other end, when connecing pump module threeway overflow valve rod left end power and be greater than the spring force that connects pump module threeway overflow valve rod right-hand member, connecing pump module threeway overflow valve rod moves right, promote threeway overflow valve rod and open the path of pressure oil P to oil return T, the pressure oil off-load, threeway relief valve valve rod two ends, under hydraulic coupling and spring-force driven dual, reach transient equiliblium.
Executive Module 3 is when working position, connect the logical Executive Module A mouth of pump module P mouth 420 or B mouth, for being connected to the executive component fuel feeding of Executive Module A mouth or B mouth, the executive component working pressure feed back to connect pump module connect pump module LS mouth 412, through second section discharge orifice 410 and the 3rd throttle orifice 414, connect the valve rod spring chamber 422 that pump module working connection 416 enters into the threeway relief valve.
When the commutation valve rod of Executive Module 3 commutates, pressure oil is through Executive Module A mouth or the B mouth is fuel-displaced while entering executive component, be connected on the working pressure of the executive component of Executive Module A mouth or B mouth, by executive component working pressure feedback oil circuit in Executive Module, feed back to and connect pump module LS hydraulic fluid port 412, enter into the valve rod spring chamber 422 of threeway relief valve through second section discharge orifice 410 by connecing pump module LS hydraulic fluid port 412 again, react on spring force one right-hand member that connects pump module threeway overflow valve rod, connect pump module threeway overflow valve rod left end and pass into metering pump outlet pressure oil by P hydraulic fluid port pressure acquisition point 407 on threeway relief valve valve rod, the power at two ends dynamically is being issued to balance, the unnecessary pressure oil that metering pump is confessed arrives oil back chamber 406 through the armshaft off-load in the middle of threeway relief valve 417 valve rod bars, first segment discharge orifice 408 is because the valve rod spring chamber 422 load feedback pressure of tiny the caused threeway relief valve of diameter change minimum, the threeway relief valve is flowing out unnecessary flow a little more than executive component working pressure underflow.
When the actuator movement of Executive Module actuator port A mouth or B mouth during to terminal or overload, when the setting pressure of induced pressure over precursor overflow valve 418, limit the pressure of valve rod spring chamber 422, precursor overflow valve 418 is opened, 417 overflows of threeway relief valve, the threeway relief valve is opened off-load and is gone out many flows under restriction pressure, and system pressure is controlled under relevant pressure and is not raising
Connect valve oil mouth 424 and can connect a two position two-way valve, when two position two-way valve is connected fuel tank, connect the valve rod spring chamber 422 and the off-load of executive component load feedback oil circuit of pump module 4, now the threeway relief valve also is in unloading condition.
When the utility model connects pump module for variable pump systems:
See Fig. 2, Executive Module commutation valve rod is when neutral position, the utility model connects pump module P mouth 420 sealing, the oil outlet of variable displacement pump with connect pump module filler opening 405(P mouth) be connected, the induced pressure feedback port connects pump module LS oil outlet 415 and is connected with the LS mouth of variable displacement pump.
When variable displacement pump starts, variable displacement pump outlet hydraulic oil enters the meta enclosed cavity of the selector valve of Executive Module and waits for, variable displacement pump outlet hydraulic oil is divided into two-way, wherein a road enters the pressure oil cavity that connects pump module threeway relief valve 417 and meets pump module filler opening 405 places, another road pump discharge pressure oil, entered the inner oil duct of valve rod of threeway relief valve by P hydraulic fluid port pressure acquisition point 407 on threeway relief valve valve rod, be further divided into two tunnels, one tunnel enters the left end of threeway relief valve valve rod, another road enters threeway relief valve valve rod right-hand member, enter the valve rod spring chamber 422 of threeway relief valve by first segment discharge orifice 408, now spring chamber is in unloading condition, because the aperture of first segment discharge orifice 408 is very little, the pressure oil passed through from first segment discharge orifice 408 had not both caused very large flow and the pressure loss, at valve rod spring chamber 422, do not set up pressure again, threeway overflow valve rod right-hand member only has spring-force driven dual, promote threeway overflow valve rod and move right when the pressure oil pressure (pump discharge pressure) of threeway overflow valve rod left end overcomes spring force, the shaft shoulder in the middle of threeway relief valve valve rod is opened sealed up pressure oil cavity and is connect pump module filler opening 405 to the path that connects pump module oil back chamber 406, because connecing pump module LS filler opening 412, the induced pressure feedback path still is in unloading condition, the LS oil circuit of the variable displacement pump be attached thereto is also at unloading condition, larger position, the swashplate angle place of variable displacement pump amount, variable displacement pump with the fluid of larger discharge capacity the P by connecing pump module to the T mouth, again by the T mouth, oil sump tank after supercooler is cooling, oil oil is through the radiator oil sump tank, the heat dissipation problem worked long hours to improve variable pump systems.
Threeway relief valve valve rod, under the pressure oil effect of valve rod pressure oil effect end 413, overcomes the spring force in threeway overflow valve rod the other end valve rod valve spring chamber 422, promotes threeway overflow valve rod and opens the path of pressure oil P to oil return T, system unloaded.
Now due to the induced pressure off-load, variable displacement pump outlet pressure oil acts on the pressure-flow compensator of variable displacement pump, pressure-flow compensator controlled variable pump swash plate is pressed onto a corresponding swashplate angle, the hydraulic oil that variable displacement pump is confessed returns to fuel tank through the threeway relief valve, now the fluid that returns to fuel tank can be dispelled the heat to reduce oil liquid temperature through cooler, solve variable displacement pump fluid cooling problem can't be unloaded the time.
In Executive Module commutation valve rod working condition of (A mouth or B mouth are opened) during at working position:
Executive Module is when working position, connecing pump module P mouth 420, to connect the executive component of Executive Modules (A mouth or B mouth) be the executive component fuel feeding, the executive component pressure feedback to the oilhole that connects pump module connect pump module LS filler opening 412 through second section discharge orifice 410 and the 3rd throttle orifice 414, connect the valve rod spring chamber 422 that pump module working connection 416 enters into the threeway relief valve.
Threeway overflow valve rod under the pressure oil effect of valve rod pressure oil effect end 413 with the valve rod spring chamber 422 of the threeway overflow valve rod the other end in the pressure oil effect of executive component feedback add that the spring force acted on valve rod dynamically is being issued to balance.
When induced pressure surpasses the setting pressure of precursor overflow valve 418, precursor overflow valve 418 is opened, and the oil pressure relief of threeway relief valve 417 is controlled under relevant pressure and no longer raises.
Load feedback pressure is through connecing pump module LS filler opening 412, connecing the external hydraulic fluid port of pump module LS, the flow that the pressure-flow compensator of variable displacement pump controlled variable pump swashplate angle under load feedback pressure and the effect of variable displacement pump outlet pressure provides corresponding load to need, when now executive component normal operation does not have overload, the sealing of threeway relief valve, do not have unnecessary flow to flow out, the flow that pump is discharged is approximately equal to the required flow of executive component, reaches energy-conservation purpose.
When the commutation of Executive Module commutation valve rod, A mouth or the B mouth of Executive Module are fuel-displaced, the executive component working pressure of being come by A mouth or the collection of B mouth is fed back oil circuit by induced pressure, one road enters into valve rod spring chamber 422, the pressure of the valve rod spring chamber 422 of threeway relief valve 417 right-hand members adds that spring force is greater than the power of threeway relief valve valve rod left end, the shaft shoulder that now connects pump module threeway relief valve valve rod centre is sealing all the time pressure oil cavity and is connecing the path of pump module filler opening 405 to oil back chamber 406, while only having load to move to terminal or overload, precursor overflow valve 418 is opened, connect the pump module threeway overflow valve rod path of cut-in pressure oil pocket to oil back chamber that move to right, system unloaded.
When executive component is worked, variable displacement pump is being experienced the openings of sizes of Executive Module commutation valve rod, with the caused pressure conversion of the working pressure of executive component, conversion swash plate angle, the opening of commutation valve rod is larger, variable displacement pump provides flow larger, and the variable displacement pump outlet pressure, a little more than the executive component working pressure.
Manual function and self-checking function when the utility model stops in emergency in order to have, take following corrective measure:
1. the stifled oil duct of can feigning death of connecting at the Y place (Fig. 2) that connects pump module 2.
2. the induced pressure at Executive Module 3 feeds back the series connection stifled oil duct of can feigning death in U place on oil circuit (LS) 315.
3. add a hand pump 103 at tail gang mould piece, hand pump inlet port (104) UNICOM's tail gang mould piece T hydraulic fluid port (203), the hand pump oil outlet 102 tail gang mould piece P1 of UNICOM mouth pressure oil ducts.
4. add an external one-way valve 404 connecing pump module filler opening (P mouth) 405.
During manually-operable, connecing pump module Y place dress dead blocking up, then move Executive Module manual reverse of direction valve rod, more manually press hand pump, can make the executive component action, the situation that is applicable to stop in emergency and resets.
Use while shutting down self-checking function; connecing pump module Y place series connection dead blocking up; block control loop; start order one by one from the Executive Module near tail gang mould piece and start check; put at Executive Module U place respectively and extremely intercept disconnected executive component working pressure feedback loop when the check Executive Module; manually move the commutation valve rod of detected Executive Module, by tail connection hand pump manual pressure, see the pressurize situation, the analysis of failure point.
Connect the external hydraulic fluid port 415 of pump module LS shut down detecting while connecing pump module to block, extremely get lodged in adjacent Executive Module U place and put extremely and block up connecing one of pump module Y place series connection, join the hand pump manual pressure with tail and see the pressurize situation, the analysis of failure point.
Certainly; above-mentioned explanation is not limitation of the utility model; the utility model also is not limited only to above-mentioned giving an example, and the variation that those skilled in the art make in essential scope of the present utility model, remodeling, interpolation or replacement, also belong to protection domain of the present utility model.
Claims (10)
1. a dual-purpose multipath hydraulic Proportional valve, comprise Executive Module (3), the both sides of described Executive Module (3) connect respectively tail gang mould piece (2) and connect pump module (4) by oil circuit, be provided with commutation valve rod means for adjusting limit of movement on described Executive Module (3), the described pump module (4) that connects mainly comprises and connects the pump module valve body by what connect that the pump module internal oil passages connects, threeway relief valve (417) and precursor overflow valve (418), it is characterized in that, the described pump module internal oil passages that connects is mainly by the first working connection, the second working connection, the 3rd working connection, the first induced pressure feedback asphalt channel, the second induced pressure feedback asphalt channel, the 3rd induced pressure feedback asphalt channel, the pilot pressure oil circuit, the first oil return circuit and the second oil return circuit form,
Described the second main oil channel channel, be communicated with successively the inner oil duct of hole, valve rod connect on pump module filler opening (405), threeway relief valve (417) valve rod, one road is to first segment discharge orifice (408), valve rod spring chamber (422), and another road is to the left end of threeway relief valve valve rod; Described first segment discharge orifice (408) is arranged in the valve rod of threeway relief valve (417);
Described the first induced pressure feedback asphalt channel, the pressure oil fed back by Executive Module enters successively and connects pump module LS filler opening (412), aperture (411), second section discharge orifice (410), oilhole (409), valve rod spring chamber (422), the oil duct between described second section discharge orifice (410) connection aperture (411) and the 3rd throttle valve (414) and the oil duct between first segment discharge orifice (408) and valve rod spring chamber (422).
2. dual-purpose multipath hydraulic Proportional valve according to claim 1, is characterized in that, the aperture of described first segment discharge orifice (408) is tiny and all less than the aperture of second section discharge orifice (410) and the 3rd throttle orifice (414).
3. dual-purpose multipath hydraulic Proportional valve according to claim 1, it is characterized in that, between the Executive Module LS filler opening (307) of described Executive Module (3) and Executive Module oil circuit (315), self check path U is set, described Executive Module oil circuit (315) is communicated with the first shuttle valve (304), described the first shuttle valve (304) is communicated with recuperation valve (306), described the first shuttle valve (304) is communicated with the second shuttle valve (308) by Executive Module oil circuit (305), described the second shuttle valve (308) and A mouth, B mouth load feedback pressure pressure-limit valve (323) is communicated with.
4. dual-purpose multipath hydraulic Proportional valve according to claim 1, it is characterized in that, described commutation valve rod means for adjusting limit of movement mainly forms by front cover body (329) with the handle chassis (328) of handle, the described handle chassis with handle (328) is connected on front cover body (329) by transaxle (336), be provided with A mouth symmetrical along horizontal center line and that there is identical angle with horizontal center line on described handle chassis (328) and regulate stop screw (330) and B mouth adjusting stop screw (338), be provided with axle sleeve (335) on described transaxle (336), one end of described transaxle (336) is provided with the bulb finger (331) vertical with transaxle (336), the termination of described bulb finger (331) is arranged in the groove of Executive Module commutation valve rod coupling shaft (332).
5. dual-purpose multipath hydraulic Proportional valve according to claim 1, is characterized in that, also includes self check oil circuit and the hand pump module (1) be connected with tail gang mould piece (2).
6. dual-purpose multipath hydraulic Proportional valve according to claim 5, it is characterized in that, described hand pump module (1) is by hand pump valve body (105) and hand pump (103), the hand pump inlet port (104) of described hand pump (103) is connected tail gang mould piece T hydraulic fluid port (203), the hand pump oil outlet (102) of described hand pump (103) is connected external hydraulic fluid port (205), the hand pump inlet port (104) of described hand pump (103) is connected tail gang mould piece LS filler opening (201), between described tail gang mould piece LS filler opening (201) and tail gang mould piece T hydraulic fluid port (203), the M place of oil circuit is provided with the stifled passage of oil can be installed.
7. according to the described dual-purpose multipath hydraulic Proportional valve of claim 5 or 6, it is characterized in that, described self check oil circuit comprises connecing on pump module (4) can place dead stifled Y place oil duct, described Y place oil duct is arranged on the oil circuit connect between pump module filler opening (405) and reduction valve (403), and described reduction valve (403) the other end connects Executive Module (2) by oil outlet (423).
8. according to the described dual-purpose multipath hydraulic Proportional valve of claim 5 or 6, it is characterized in that, described self check oil circuit comprises the dead stifled Y place oil duct of placing connect on pump module (4), described Y place oil duct is arranged on the oil circuit connect between pump module filler opening (405) and reduction valve (403), described reduction valve (403) the other end connects Executive Module (3) by oil outlet (423), be provided with on Executive Module LS filler opening (307) on described Executive Module (3) and the oil circuit between the first shuttle valve (304) and can place dead stifled U place oil duct, described the first shuttle valve (304) by oil circuit with connect pump module (4) and be communicated with.
9. according to the described dual-purpose multipath hydraulic Proportional valve of claim 5 or 6, it is characterized in that, the described pump module filler opening (405) that connects that connects pump module (4) locates to arrange an external one-way valve (404).
10. according to claim 1,5 or 6 described dual-purpose multipath hydraulic Proportional valves, it is characterized in that, the described valve oil mouth (424) that connects that connects pump module (4) connects two position two-way valve, and described two position two-way valve is communicated with fuel tank.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320440370.8U CN203384150U (en) | 2012-09-18 | 2013-07-23 | Dual-purpose multipath hydraulic proportional valve |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201220474282 | 2012-09-18 | ||
| CN201220474282.5 | 2012-09-18 | ||
| CN201320440370.8U CN203384150U (en) | 2012-09-18 | 2013-07-23 | Dual-purpose multipath hydraulic proportional valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203384150U true CN203384150U (en) | 2014-01-08 |
Family
ID=49190943
Family Applications (5)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320438418.1U Expired - Fee Related CN203384149U (en) | 2012-09-18 | 2013-07-23 | Manual hydraulic proportional valve |
| CN201320440370.8U Expired - Fee Related CN203384150U (en) | 2012-09-18 | 2013-07-23 | Dual-purpose multipath hydraulic proportional valve |
| CN2013103127029A Pending CN103343759A (en) | 2012-09-18 | 2013-07-23 | Dual-purpose multi-channel hydraulic proportional valve |
| CN201320442515.8U Expired - Fee Related CN203384151U (en) | 2012-09-18 | 2013-07-23 | Manual and self-inspection hydraulic proportional valve |
| CN201320442568.XU Expired - Fee Related CN203384152U (en) | 2012-09-18 | 2013-07-23 | Limit adjusting device for hydraulic proportional valve |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320438418.1U Expired - Fee Related CN203384149U (en) | 2012-09-18 | 2013-07-23 | Manual hydraulic proportional valve |
Family Applications After (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013103127029A Pending CN103343759A (en) | 2012-09-18 | 2013-07-23 | Dual-purpose multi-channel hydraulic proportional valve |
| CN201320442515.8U Expired - Fee Related CN203384151U (en) | 2012-09-18 | 2013-07-23 | Manual and self-inspection hydraulic proportional valve |
| CN201320442568.XU Expired - Fee Related CN203384152U (en) | 2012-09-18 | 2013-07-23 | Limit adjusting device for hydraulic proportional valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (5) | CN203384149U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103343759A (en) * | 2012-09-18 | 2013-10-09 | 赵江 | Dual-purpose multi-channel hydraulic proportional valve |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105840573B (en) * | 2015-01-16 | 2018-04-06 | 徐工集团工程机械股份有限公司 | Load sensing multi-way valve first valve body and load sensing multi-way valve first |
| CN106286481B (en) * | 2016-08-19 | 2018-08-21 | 中航飞机起落架有限责任公司 | A kind of hydraulic commutating circuit and its commutation method of no channelling |
| CN107285012A (en) * | 2017-07-03 | 2017-10-24 | 张连杰 | A kind of visual type double track just presss from both sides handling facilities |
| CN108240366B (en) * | 2018-01-25 | 2019-07-26 | 凯文斯流体控制(江苏)有限公司 | A kind of flow divider valve for the hydraulic accessory of excavator |
| CN108087367B (en) * | 2018-01-25 | 2019-07-26 | 凯文斯流体控制(江苏)有限公司 | A kind of flow divider valve for load-sensitive pumping system |
| CN110714957A (en) * | 2019-08-26 | 2020-01-21 | 宁波江北宇洲液压设备厂 | High-integration pilot multi-way valve bank and crane |
| CN112228620A (en) * | 2020-11-11 | 2021-01-15 | 力源液压（苏州）有限公司 | Variable pump bidirectional control valve assembly and variable pump |
| CN112762037A (en) * | 2020-11-27 | 2021-05-07 | 徐工集团工程机械股份有限公司 | Quick-insertion valve group, remote hydraulic control system and engineering vehicle |
| CN112555206B (en) * | 2020-12-15 | 2023-01-06 | 潍柴动力股份有限公司 | Hydraulic control system and silage harvester |
| CN113202839B (en) * | 2021-04-13 | 2023-03-24 | 中国煤炭科工集团太原研究院有限公司 | Pilot valve for measuring valve element displacement of multi-way valve |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201963627U (en) * | 2011-02-02 | 2011-09-07 | 卢宇 | Ratio control multi-way valve |
| CN102287413B (en) * | 2011-09-29 | 2014-01-01 | 卢宇 | Proportional multi-way valve with turning load feedback function |
| CN203384149U (en) * | 2012-09-18 | 2014-01-08 | 赵江 | Manual hydraulic proportional valve |
-
2013
- 2013-07-23 CN CN201320438418.1U patent/CN203384149U/en not_active Expired - Fee Related
- 2013-07-23 CN CN201320440370.8U patent/CN203384150U/en not_active Expired - Fee Related
- 2013-07-23 CN CN2013103127029A patent/CN103343759A/en active Pending
- 2013-07-23 CN CN201320442515.8U patent/CN203384151U/en not_active Expired - Fee Related
- 2013-07-23 CN CN201320442568.XU patent/CN203384152U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103343759A (en) * | 2012-09-18 | 2013-10-09 | 赵江 | Dual-purpose multi-channel hydraulic proportional valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103343759A (en) | 2013-10-09 |
| CN103321982A (en) | 2013-09-25 |
| CN203384149U (en) | 2014-01-08 |
| CN203384152U (en) | 2014-01-08 |
| CN203384151U (en) | 2014-01-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN203384150U (en) | Dual-purpose multipath hydraulic proportional valve | |
| CN202673874U (en) | Constant-pressure variable control system of load sensitive hydraulic pump | |
| CN104089078B (en) | For the proportion adjustment device of linear rows stroke valve | |
| CN104032792A (en) | Quantitative and variable hydraulic system of loading machine | |
| CN101191507A (en) | Hydraulic system for tunneling machine | |
| CN202851491U (en) | Load-sensitive multi-way valve used in loader variable system | |
| CN109306976B (en) | Load sensitive control system | |
| CN203297181U (en) | load sensing system | |
| CN201144902Y (en) | Hydraulic system for development machine | |
| CN206754027U (en) | A kind of plug-in integrated package of differential cylinder control | |
| CN201799552U (en) | Hydraulic system for proportional overflow pressure relief for hydraulic forging press | |
| CN208442095U (en) | LEP electricity proportional load sensitive pump and hydraulic system | |
| CN208565105U (en) | A kind of device for eliminating load sensitive system hydraulic shock | |
| CN203835836U (en) | Synchronous lifting hydraulic control system | |
| CN107830001B (en) | Scissor fork type aerial work platform and hydraulic system thereof | |
| CN104030199A (en) | Forklift hydraulic system with bypass oil way throttling speed regulation loop | |
| CN212106422U (en) | Hydraulic valve and load sensing system | |
| CN103321982B (en) | Manually, self-inspection hydraulic proportion valve | |
| CN104776077B (en) | Load-sensitive multiway valve with micromotion valve element | |
| CN204041600U (en) | Multipath hydraulic motor speed governing feedback control valve | |
| CN202913450U (en) | Pressure compensator used for loader | |
| CN203835850U (en) | Lifting balance pile-up valve for hydraulic molten metal trolley | |
| CN106678112B (en) | A kind of underwater cylinder control system | |
| CN212225648U (en) | Valve group with pressure measuring connector | |
| CN106640817B (en) | The pressure compensation type energy-saving control valve of shunting hydraulic system is closed suitable for double pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140108 Termination date: 20150723 |
|
| EXPY | Termination of patent right or utility model |