CN203081879U - hydraulic control circuit - Google Patents
hydraulic control circuit Download PDFInfo
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- CN203081879U CN203081879U CN 201320080442 CN201320080442U CN203081879U CN 203081879 U CN203081879 U CN 203081879U CN 201320080442 CN201320080442 CN 201320080442 CN 201320080442 U CN201320080442 U CN 201320080442U CN 203081879 U CN203081879 U CN 203081879U
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- pressure
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- valve
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- oil
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- 239000003921 oil Substances 0.000 claims abstract description 52
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 5
- 239000012530 fluid Substances 0.000 claims description 53
- 239000000945 filler Substances 0.000 claims description 37
- 239000002828 fuel tank Substances 0.000 claims description 19
- 238000013016 damping Methods 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 8
- 239000000446 fuel Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 150000001875 compounds Chemical class 0.000 description 1
- 239000012467 final product Substances 0.000 description 1
- 238000001595 flow curve Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Abstract
The utility model discloses a hydraulic control loop, which comprises an actuating mechanism, a main reversing valve, a bypass oil circuit, a pump and an oil tank, wherein two working oil circuits of the actuating mechanism are respectively connected with a first working oil port and a second working oil port of the main reversing valve, an oil inlet and an oil return port of the main reversing valve are respectively connected with the pump and the oil tank, the bypass oil circuit is connected with the oil inlet, the bypass oil port and the oil return port of the main reversing valve, so that when the main reversing valve is positioned at the middle position, hydraulic oil flows back to the oil tank through the bypass oil port, wherein, the hydraulic control loop also comprises a pressure compensation valve, an oil inlet of the pressure compensation valve is connected with the bypass oil port, an oil outlet of the pressure compensation valve is connected with the oil tank, and the pressure of the first control oil port of the pressure compensation valve is the load pressure, and the second control oil port of the pressure compensation valve is connected with the bypass oil port, so that the load pressure of the actuating mechanism is approximately equal to the pressure of the bypass oil port. The flow rate of each oil passage of the hydraulic control circuit is less affected by the load pressure.
Description
Technical field
The utility model relates to Hydraulic Field, particularly, relates to a kind of hydraulic control circuit.
Background technique
Hydraulic control circuit shown in Figure 1 comprises actuator, main reversing valve 10, bleed off circuit, pump and fuel tank, two working oil path of described actuator are connected with the second actuator port B with the first actuator port A of main reversing valve 10 respectively, the oil inlet P of main reversing valve 10 is connected with described fuel tank with described pump respectively with oil return inlet T, described bleed off circuit connects oil inlet P, bypass hydraulic fluid port C and the oil return inlet T of main reversing valve 10, make when main reversing valve 10 is in meta that hydraulic oil flows back to described fuel tank by bypass hydraulic fluid port C.
As shown in Figure 1: when main reversing valve 10 was in position, a left side, the first actuator port A was the filler opening of actuator, and the second actuator port B is the return opening of actuator, and bypass hydraulic fluid port C ends; When main reversing valve 10 was in right position, the second actuator port B was the filler opening of actuator, and the first actuator port A is the return opening of actuator, and bypass hydraulic fluid port C ends; When main reversing valve 10 was in meta, the first actuator port A and the second actuator port B ended, bypass hydraulic fluid port C aperture maximum, and flow system flow all flows back to fuel tank from bleed off circuit.When meta switched, the aperture of bypass hydraulic fluid port C increased gradually from left (or right position) when main reversing valve 10, and the aperture of the first actuator port A and the second actuator port B reduces gradually, and the flow that flows into bleed off circuit increases gradually; When main reversing valve 10 when switch position (or right position) left from meta, bypass hydraulic fluid port C aperture reduces gradually, the aperture of the first actuator port A and the second actuator port B increases gradually, the flow that flows into the first actuator port A and the second actuator port B increases gradually, and the flow that flows into bleed off circuit reduces gradually.
The filler opening flow of this hydraulic control circuit is subjected to load effect bigger, constant when flow system flow, when main reversing valve 10 is in a certain working position, after fluctuation appears in filler opening (the first actuator port A or the second actuator port B) pressure, system pressure also can be along with fluctuation, cause the flow of filler opening also can be along with the fluctuation of load, thereby control accuracy, the working efficiency of influence operation, and increase operator's working strength.
The model utility content
The purpose of this utility model provides a kind of hydraulic control circuit, and it is less that each oil circuit flow of this hydraulic control circuit is influenced by induced pressure.
To achieve these goals, the utility model provides a kind of hydraulic control circuit, this hydraulic control circuit comprises actuator, main reversing valve, bleed off circuit, pump and fuel tank, two working oil path of described actuator are connected with second actuator port with first actuator port of described main reversing valve respectively, the filler opening of described main reversing valve is connected with described fuel tank with described pump respectively with return opening, described bleed off circuit connects the described filler opening of described main reversing valve, bypass hydraulic fluid port and described return opening, make when described main reversing valve is in meta, hydraulic oil flows back to described fuel tank by described bypass hydraulic fluid port, wherein, described hydraulic control circuit also comprises pressure-compensated valve, the filler opening of this pressure-compensated valve links to each other with described bypass hydraulic fluid port, the oil outlet of described pressure-compensated valve links to each other with described fuel tank, and the pressure of first control port of described pressure-compensated valve is induced pressure, second control port of described pressure-compensated valve links to each other with described bypass hydraulic fluid port, so that the pressure of the induced pressure of described actuator and described bypass hydraulic fluid port equates.
Preferably, described hydraulic control circuit also comprises the pressure comparator that can gather described induced pressure, and first control port of described pressure-compensated valve links to each other with the oil outlet of described pressure comparator.
Preferably, described pressure comparator is the shuttle valve that is connected between described first actuator port and described second actuator port, and first filler opening of this shuttle valve links to each other with described first actuator port, and second filler opening of described shuttle valve links to each other with described second actuator port.
Preferably, described pressure comparator is the comparison selector valve that is connected between described first actuator port and described second actuator port, this first filler opening that compares selector valve links to each other with described first actuator port, described relatively second filler opening of selector valve links to each other with described second actuator port, described relatively first control port of selector valve links to each other with described first actuator port, and described relatively second control port of selector valve links to each other with described second actuator port.
Preferably, described main reversing valve is provided with the pressure acquisition mouth of gathering induced pressure, when described main reversing valve is in position, a left side, described pressure acquisition mouth is communicated with described first actuator port, when described main reversing valve is in right position, described pressure acquisition mouth is communicated with described second actuator port, and first control port of described pressure-compensated valve links to each other with described pressure acquisition mouth, and second control port of described pressure-compensated valve links to each other with described bypass hydraulic fluid port.
Preferably, described pressure-compensated valve is a Fixed differential reducing valve.
Preferably, be serially connected with the throttle valve that to control separately at least one in described first actuator port, described second actuator port and the described bypass hydraulic fluid port.
Preferably, described throttle valve is the hydraulic control throttle valve.
Preferably, described throttle valve is automatically controlled throttle valve.
Preferably, the in-line of described main reversing valve, oil circuit have Y type meta function, all are serially connected with damping hole on described first actuator port and described second actuator port.
By being set on bleed off circuit, pressure-compensated valve can make induced pressure approximate identical all the time with the bypass oil mouth pressure, thereby make in the actuator port to the pressure reduction of the hydraulic fluid port of actuator's fuel feeding and the pressure reduction approximately equal of bypass hydraulic fluid port, thereby make in the actuator port the only approximate and area between the two of assignment of traffic to the hydraulic fluid port flow of actuator's fuel feeding and bypass hydraulic fluid port than relevant.
Other feature and advantage of the present utility model will partly be described in detail in embodiment subsequently.
Description of drawings
Accompanying drawing is to be used to provide further understanding of the present utility model, and constitutes the part of specification, is used from explanation the utility model with following embodiment one, but does not constitute restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the schematic diagram of existing hydraulic control circuit;
Fig. 2 is the schematic diagram of first kind of mode of execution of hydraulic control circuit described in the utility model;
Fig. 3 is the schematic diagram of second kind of mode of execution of hydraulic control circuit described in the utility model;
Fig. 4 is the schematic diagram of the third mode of execution of hydraulic control circuit described in the utility model;
Fig. 5 is the schematic diagram of the 4th kind of mode of execution of hydraulic control circuit described in the utility model;
Fig. 6 is the schematic diagram of the 5th kind of mode of execution of hydraulic control circuit described in the utility model;
Fig. 7 is the schematic diagram of the 6th kind of mode of execution of hydraulic control circuit described in the utility model;
Fig. 8 is the schematic diagram of the 7th kind of mode of execution of hydraulic control circuit described in the utility model.
Description of reference numerals
10 main reversing valves, 20 pressure-compensated valves
30 shuttle valves, 40 throttle valve
Embodiment
Below in conjunction with accompanying drawing embodiment of the present utility model is elaborated.Should be understood that embodiment described herein only is used for description and interpretation the utility model, is not limited to the utility model.
As shown in Fig. 2 to Fig. 8, the utility model discloses a kind of hydraulic control circuit, this hydraulic control circuit comprises actuator, main reversing valve 10, bleed off circuit, pump and fuel tank, two working oil path of actuator are connected with the second actuator port B with the first actuator port A of main reversing valve 10 respectively, the oil inlet P of main reversing valve 10 is connected with fuel tank with pump respectively with oil return inlet T, bleed off circuit connects the oil inlet P of main reversing valve, bypass hydraulic fluid port C and oil return inlet T, make when main reversing valve 10 is in meta, hydraulic oil flows back to fuel tank by bypass hydraulic fluid port C, wherein, described hydraulic control circuit also comprises pressure-compensated valve 20, the filler opening of this pressure-compensated valve 20 links to each other with bypass hydraulic fluid port C, the oil outlet of pressure-compensated valve 20 links to each other (in the utility model with fuel tank, the oil outlet of pressure-compensated valve 20 can directly link to each other with fuel tank, also can link to each other with fuel tank) by the oil return inlet T of main reversing valve 10, and the pressure of first control port of pressure-compensated valve 20 is induced pressure, second control port of pressure-compensated valve 20 links to each other with bypass hydraulic fluid port C, so that the induced pressure approximately equal of the pressure of bypass hydraulic fluid port C and actuator.
As shown in Figure 2, pressure-compensated valve 20 comprises the soft spring that is used for the valve core reset of pressure-compensated valve 20.Because soft spring is very soft, can be similar to and thinks that described soft spring is zero to the active force of spool.Therefore, can be similar to think the pressure P at described bypass hydraulic fluid port C place ' with the induced pressure P of actuator
LEquate.
The filler opening of actuator is one among the first actuator port A and the second actuator port B, the pressure differential deltap P of the filler opening of actuator
1=system pressure P-induced pressure P
L, and bypass hydraulic fluid port pressure differential deltap P
2The pressure P at=system pressure P-bypass hydraulic fluid port C place '.As mentioned above, because induced pressure P
LPressure P with bypass hydraulic fluid port C place ' equate, so, the pressure differential deltap P of the filler opening of actuator
1With bypass hydraulic fluid port pressure differential deltap P
2Also equate.According to the valve port flow formula
(wherein, C
qBe flow coefficient, ρ is a fluid density, and A is the opening area of valve port) as can be known, the filler opening flow of described actuator
The flow of bypass hydraulic fluid port C
And the filler opening flow Q of actuator
1Flow Q with bypass hydraulic fluid port C
2Ratio be
Therefore, the assignment of traffic of the filler opening flow of described actuator and bypass hydraulic fluid port C only with the opening area A of filler opening
1The opening area A of (that is the aperture of the filler opening of actuator) and bypass hydraulic fluid port C
2(that is, the aperture of bypass hydraulic fluid port C) is relevant, and irrelevant with the induced pressure of actuator.
Hence one can see that, and hydraulic control circuit provided by the utility model has good discharge stability, can improve control accuracy, working efficiency and the comfort level of operation, reduces operator's working strength.In addition, because it is very fast that pressure-compensated valve is built pressure ratio, different actuator load voltage built-up rates is almost synchronous, therefore when starting different actuator loads, the guide's pilot pressure that starts much at one, the operating position of corresponding operating grip also much at one, this also can improve control accuracy, working efficiency and the comfort level of operation, and can reduce operator's labor intensity.
In the utility model, can adopt multiple mode to gather described induced pressure, for example described hydraulic control circuit can also comprise the pressure comparator 30 that can gather induced pressure, and first control port of pressure-compensated valve 20 links to each other with the oil outlet of pressure comparator 30.Pressure comparator 30 passes to pressure-compensated valve 20 with the induced pressure that collects by oil outlet.
Shown in (the third mode of execution of the present utility model) among Fig. 4, pressure comparator 30 can also be for being connected the comparison selector valve between the first actuator port A and the second actuator port B, as shown in Figure 4, this first filler opening that compares selector valve links to each other with the first actuator port A, relatively second filler opening of selector valve links to each other with the second actuator port B, relatively first control port of selector valve links to each other with the first actuator port A, and relatively second control port of selector valve links to each other with the second actuator port B.When the first actuator port A was the filler opening of described actuator, pressure comparator 30 was in right position.When the second actuator port B was the filler opening of described actuator, pressure comparator 30 was in position, a left side.
In the utility model, can also utilize main reversing valve 10 to gather induced pressure, (the 4th kind of mode of execution of the present utility model) as shown in Figure 5, can be provided with the pressure acquisition mouth D that gathers induced pressure on the main reversing valve 10, when main reversing valve 10 is in a when position left side (at this moment, the first actuator port A is the filler opening of actuator), pressure acquisition mouth D is communicated with the first actuator port A, the pressure of pressure acquisition mouth D is induced pressure, when main reversing valve 10 is in right position (at this moment, the second actuator port B is the filler opening of actuator), pressure acquisition mouth D is communicated with the second actuator port B, the pressure of pressure acquisition mouth D is induced pressure, and first control port of pressure-compensated valve 20 links to each other with pressure acquisition mouth D, and second control port of pressure-compensated valve 20 links to each other with bypass hydraulic fluid port C.The quantity that pressure acquisition mouth D can reduce employed valve in the described hydraulic control circuit is set on main reversing valve 10, simplifies the structure of described hydraulic control circuit.
In the utility model, the concrete structure of pressure-compensated valve 20 there is not specific (special) requirements, as long as can make induced pressure P
LPressure P with bypass hydraulic fluid port C place ' approximately equal gets final product, and as shown in Fig. 2 to Fig. 8, pressure-compensated valve 20 can be Fixed differential reducing valve.
In the utility model, the soft spring of pressure-compensated valve 20 can be installed in induced pressure side (that is, the first control port side of pressure-compensated valve 20) (extremely shown in Figure 8 as Fig. 2, Fig. 4), and pressure-compensated valve 20 is the normal close type loop during meta.Certainly, the soft spring of pressure-compensated valve 20 also can be installed in the side (that is, the second control port side of pressure-compensated valve 20) (as shown in Figure 3) of bypass hydraulic fluid port C, and pressure-compensated valve 20 is the open type loop during meta.
In above-mentioned several mode of executions, the first actuator port A, the second actuator port B and bypass hydraulic fluid port C link.In the utility model, be serially connected with the throttle valve 40 that to control separately on any one among the first actuator port A, the second actuator port B and the bypass hydraulic fluid port C.Aperture by control throttle valve 40 then can be controlled flow by the hydraulic fluid port that is serially connected with throttle valve 40.Preferably, be connected in series a throttle valve 40 respectively on the first actuator port A, the second actuator port B and the bypass hydraulic fluid port C, thereby can control flow by the first actuator port A, the flow by the second actuator port B and the flow by bypass hydraulic fluid port C respectively, thereby can obtain required flow curve.
The 5th kind of mode of execution of the present utility model as shown in Figure 6, throttle valve 40 can be the hydraulic control throttle valve.
The 6th kind of mode of execution of the present utility model as shown in Figure 7, throttle valve 40 can be automatically controlled throttle valve.
In hydraulic control circuit described in the utility model, can select the meta function of main reversing valve 10 according to concrete actuator, for example, in the mode of execution shown in Fig. 2 to Fig. 7, the in-line of main reversing valve 10, oil circuit have O type meta function.
In example the 7th kind of mode of execution of the present utility model as shown in FIG. 8, the in-line of main reversing valve 10, oil circuit have Y type meta function.
When in-line, the oil circuit of main reversing valve 10 have Y type meta function, all be serially connected with damping hole on the first actuator port A and the second actuator port B.When main reversing valve 10 was in position, a left side or right position, main reversing valve 10 did not have the effect of throttling, and when main reversing valve 10 was in meta, filler opening, return opening were communicated with fuel tank after all passing through throttling, and this function can play certain buffer function in the transition of commutation.
By being set on bleed off circuit, pressure-compensated valve can make induced pressure identical all the time with the bypass oil mouth pressure, thereby make in the actuator port pressure reduction to the hydraulic fluid port of actuator's fuel feeding equate with the pressure reduction of bypass hydraulic fluid port, thus make in the actuator port to the assignment of traffic of the hydraulic fluid port flow of actuator's fuel feeding and bypass hydraulic fluid port only and the area between the two than relevant.
Make hydraulic control circuit provided by the utility model have good discharge stability by said structure, can improve control accuracy, working efficiency and the comfort level of operation, reduce operator's working strength.In addition, because it is very fast that pressure-compensated valve is built pressure ratio, different actuator load voltage built-up rates is almost synchronous, therefore when starting different actuators, the guide's pilot pressure that starts much at one, the operating position of corresponding operating grip also much at one, this also can improve control accuracy, working efficiency and the comfort level of operation, and can reduce operator's labor intensity.
Below describe preferred implementation of the present utility model in conjunction with the accompanying drawings in detail; but; the utility model is not limited to the detail in the above-mentioned mode of execution; in technical conceive scope of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
Need to prove that in addition each the concrete technical characteristics described in above-mentioned embodiment under reconcilable situation, can make up by any suitable manner.For fear of unnecessary repetition, the utility model is to the explanation no longer separately of various possible compound modes.
In addition, also can carry out combination in any between the various mode of execution of the present utility model, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (10)
1. hydraulic control circuit, this hydraulic control circuit comprises actuator, main reversing valve (10), bleed off circuit, pump and fuel tank, two working oil path of described actuator are connected with second actuator port (B) with first actuator port (A) of described main reversing valve (10) respectively, the filler opening (P) of described main reversing valve (10) is connected with described fuel tank with described pump respectively with return opening (T), described bleed off circuit connects the described filler opening (P) of described main reversing valve, bypass hydraulic fluid port (C) and described return opening (T), make described main reversing valve (10) when being in meta, hydraulic oil flows back to described fuel tank by described bypass hydraulic fluid port (C), it is characterized in that, described hydraulic control circuit also comprises pressure-compensated valve (20), the filler opening of this pressure-compensated valve (20) links to each other with described bypass hydraulic fluid port (C), the oil outlet of described pressure-compensated valve (20) links to each other with described fuel tank, and the pressure of first control port of described pressure-compensated valve (20) is induced pressure, second control port of described pressure-compensated valve (20) links to each other with described bypass hydraulic fluid port (C), so that the pressure of the induced pressure of described actuator and described bypass hydraulic fluid port (C) equates.
2. hydraulic control circuit according to claim 1, it is characterized in that, this hydraulic control circuit also comprises the pressure comparator (30) that can gather described induced pressure, and first control port of described pressure-compensated valve (20) links to each other with the oil outlet of described pressure comparator (30).
3. hydraulic control circuit according to claim 2, it is characterized in that, described pressure comparator (30) is for being connected the shuttle valve between described first actuator port (A) and described second actuator port (B), first filler opening of this shuttle valve links to each other with described first actuator port (A), and second filler opening of described shuttle valve links to each other with described second actuator port (B).
4. hydraulic control circuit according to claim 2, it is characterized in that, described pressure comparator (30) is for being connected the comparison selector valve between described first actuator port (A) and described second actuator port (B), this first filler opening that compares selector valve links to each other with described first actuator port (A), described relatively second filler opening of selector valve links to each other with described second actuator port (B), described relatively first control port of selector valve links to each other with described first actuator port (A), and described relatively second control port of selector valve links to each other with described second actuator port (B).
5. hydraulic control circuit according to claim 1, it is characterized in that, described main reversing valve (10) is provided with the pressure acquisition mouth (D) of gathering induced pressure, when described main reversing valve (10) is in position, a left side, described pressure acquisition mouth (D) is communicated with described first actuator port (A), when described main reversing valve (10) is in right position, described pressure acquisition mouth (D) is communicated with described second actuator port (B), first control port of described pressure-compensated valve (20) links to each other with described pressure acquisition mouth (D), and second control port of described pressure-compensated valve (20) links to each other with described bypass hydraulic fluid port (C).
6. according to any described hydraulic control circuit in the claim 1 to 5, it is characterized in that described pressure-compensated valve (20) is a Fixed differential reducing valve.
7. hydraulic control circuit according to claim 6 is characterized in that, is serially connected with the throttle valve (40) that can control separately at least one in described first actuator port (A), described second actuator port (B) and the described bypass hydraulic fluid port (C).
8. hydraulic control circuit according to claim 7 is characterized in that, described throttle valve (40) is the hydraulic control throttle valve.
9. hydraulic control circuit according to claim 7 is characterized in that, described throttle valve (40) is automatically controlled throttle valve.
10. hydraulic control circuit according to claim 6 is characterized in that, in-line, the oil circuit of described main reversing valve (10) has Y type meta function, all is serially connected with damping hole on described first actuator port (A) and described second actuator port (B).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320080442 CN203081879U (en) | 2013-02-21 | 2013-02-21 | hydraulic control circuit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320080442 CN203081879U (en) | 2013-02-21 | 2013-02-21 | hydraulic control circuit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203081879U true CN203081879U (en) | 2013-07-24 |
Family
ID=48827720
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320080442 Expired - Fee Related CN203081879U (en) | 2013-02-21 | 2013-02-21 | hydraulic control circuit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203081879U (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106402059A (en) * | 2016-12-26 | 2017-02-15 | 徐工集团工程机械有限公司 | Load port individual valve, hydraulic bus control system and engineering machinery |
| CN108317119A (en) * | 2018-04-09 | 2018-07-24 | 徐州燕大传动与控制技术有限公司 | A kind of proportional multi-way valve that hydraulic control inlet and outlet throttling side can be separately adjustable |
| CN108661966A (en) * | 2018-06-08 | 2018-10-16 | 东莞海特帕沃液压科技有限公司 | A kind of plug-in pressure-compensated valve |
| CN108661965A (en) * | 2018-05-28 | 2018-10-16 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with Y type Median Functions |
| CN108716491A (en) * | 2018-05-28 | 2018-10-30 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with O-shaped Median Function |
-
2013
- 2013-02-21 CN CN 201320080442 patent/CN203081879U/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106402059A (en) * | 2016-12-26 | 2017-02-15 | 徐工集团工程机械有限公司 | Load port individual valve, hydraulic bus control system and engineering machinery |
| CN108317119A (en) * | 2018-04-09 | 2018-07-24 | 徐州燕大传动与控制技术有限公司 | A kind of proportional multi-way valve that hydraulic control inlet and outlet throttling side can be separately adjustable |
| CN108661965A (en) * | 2018-05-28 | 2018-10-16 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with Y type Median Functions |
| CN108716491A (en) * | 2018-05-28 | 2018-10-30 | 徐州燕大传动与控制技术有限公司 | A kind of 3 position-5 way load port independent control multi-way valve with O-shaped Median Function |
| CN108661965B (en) * | 2018-05-28 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Three-position five-way load port independent control multi-way valve with Y-shaped neutral position function |
| CN108716491B (en) * | 2018-05-28 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Three-position five-way load port independent control multi-way valve with O-shaped neutral position function |
| CN108661966A (en) * | 2018-06-08 | 2018-10-16 | 东莞海特帕沃液压科技有限公司 | A kind of plug-in pressure-compensated valve |
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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 | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130724 |