CN100337040C - Automatic control valve block of biliquid flow - Google Patents
Automatic control valve block of biliquid flow Download PDFInfo
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- CN100337040C CN100337040C CNB2005100277918A CN200510027791A CN100337040C CN 100337040 C CN100337040 C CN 100337040C CN B2005100277918 A CNB2005100277918 A CN B2005100277918A CN 200510027791 A CN200510027791 A CN 200510027791A CN 100337040 C CN100337040 C CN 100337040C
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Abstract
The present invention relates to a double liquid flow type automatic control valve block, which belongs to the field of hydraulic control and comprises a valve body and control valve pieces, wherein the control valve pieces which have at least one group are all integral cartridge valves, and the group of valve pieces comprise an overflow valve, a one-way valve and a hydraulic control one-way valve; oil ports on the valve body mainly comprise an oil feed port, a working oil port and an oil return port. The oil feed port is respectively communicated with the one-way valve and the overflow valve, an outlet of the one-way valve is communicated with the working oil port and the hydraulic control one-way valve, and the return oil of all valves is communicated with the oil return port. The present invention has the advantages of reliable quality, selectable technical performance parameter, convenient mass production, direct disassembly of each cartridge valve for replacement, convenient installation and replacement, easy maintenance, simple control oilway, fewer sealing members, and reduced frequency of causing leakage malfunction.
Description
Technical field
The present invention relates to the hydraulic control field, relate to a kind of hydraulic grab that various hoists are used that is used for concretely, and be used for the hydraulic pressure installation that engineering machinery, mine and harbour facilities use, also be useful on the automatic control valve block of biliquid flow in the hydraulic pressure installation such as oil and geological drilling equipment.
Background technique
Present hydraulic grab adopts a power cable to make motor positive and inverse drive a bidirectional hydraulic pump, the hydraulic power supply of hydraulic grab and the problem of alternately controlling the grab bucket open and close have been finished with the hydraulic oil source (biliquid stream) of both direction, reduce the annex that brings during external control is used to equipment and reached difficult problems such as control section rate of fault height more, the principle that this bidirectional hydraulic pump is controlled automatically as shown in Figure 1, primary component comprises DV1 type pilot unloading overflow valve, the DV2 pilot-type relief valve, RV1, the RV2 one-way valve, SV1, the SV2 Pilot operated check valve, hydraulic fluid port P1, P2 is respectively the oil hydraulic pump pressure oil-source mouth that grab bucket is closed and open, hydraulic fluid port A receives the rodless cavity of operating cylinder, make grab bucket closed during oil-feed, come the gravity of material in the balance grab bucket or produce the power that grasps material with the power that hydraulic pressure produces.Hydraulic fluid port B receives the rod chamber of operating cylinder, during oil-feed, grab bucket is opened, and owing to the reasons such as weight of grab bucket itself, can make fluid pressure of generation in the rod chamber of operating cylinder all the time when opening.Hydraulic fluid port R is a return opening, and MP1, MP2, MA, MB are respectively and measure the hydraulic fluid port that each hydraulic fluid port pressure is used.The effect of DV1 is, the fluid pressure below the maximum pressure that is no more than setting is provided when grab bucket is closed, produces overflow when surpassing maximum pressure, prevents the damage that reasons such as operation mechanism's damage, oil hydraulic pump and motor superpressure overload cause.When hydraulic fluid port A reaches the highest setup pressure value, just off-load of DV1, the oil stream that makes the P1 mouth, has stopped to A hydraulic fluid port fuel feeding to the R mouth with extremely low pressure flow, greatly reduces the heating value of electrical consumption power and fluid.Because RV1, the pressure of hydraulic fluid port A is maintained.Pressure is owing to the internal leakage or the material of operating cylinder become flexible reasons such as variation in hydraulic fluid port A, when being reduced to the minimum pressure of a DV1 setting, DV1 stops off-load, replenishes fluid again to improve the pressure of A hydraulic fluid port, off-load once more after the maximum pressure value that reaches the DV1 setting in the A hydraulic fluid port.At the pressure of hydraulic fluid port P1 by oil duct ST2 control, the SV2 one-way valve opens, the oil in the operating cylinder rod chamber can oil sump tank, otherwise closes, and keeps the form of grab bucket constant.The working principle of hydraulic fluid port P2 oil-feed is similar during to hydraulic fluid port P1 oil-feed, just valve DV2 is a common relief valve, because the pressure that needs when grab bucket is opened is lower, so the setting pressure of this valve is low than DV1, DV2 overflow when the grab bucket claw is opened to limit position, the setting pressure of keeping pressure in the working oil path and be DV2 no longer rises, and prevents that the overload of element from damaging.
The internal structure of this control valve piece such as Fig. 2; shown in 3; adopted the cartridge valve of forming by the apportion element; design more flexible; but it is many to exist hydraulic element quantity; Sealing is many; the control oil chamber volume is big; movement speed is slow; control sensitivity is low; the processing request height; rate of fault is also high; and can not assemble adjusting in advance; change inconvenient during maintenance; heating value is big; shortcomings such as operating cylinder can not be protected when being subjected to the external strength impact; as by pilot pressure spool DV1; the element of main valve plug DV1a and three apportions of off-load control piston DV1b has been formed leading type unloading overflow valve DV1; for realizing cooperating each other the function of finishing an integral valve; add mutual alignment required precision strictness in man-hour; be difficult for processing; also need to bore several control oil ducts; ability transmitting control pressure; the binding site of the spool of each apportion and valve block body all needs sealing material and seals; what just be unlikely the loss that produces pilot pressure and prevent hydraulic oil is to leak, and therefore the Sealing quantity of using is many.SV1 for another example, SV1a two-part spool has been formed Pilot operated check valve SV1, and each part all also has several independently element compositions, because the push rod among the SV1a can only transmit pressure to the main valve plug of SV1, can not transmit pulling force, for solving processing and alignment error, also need to leave certain idle stroke, when the pilot pressure of this valve diminishes suddenly, can not help main valve plug to close immediately, can only lean on the return spring power of main valve plug that it is closed, therefore movement speed is slow, occurs hydraulic pressure flutter phenomenon sometimes, for preventing the generation of this phenomenon, with adjusting screw, the method of taking to regulate main valve plug open degree (throttling) is solved, but the liquid resistance when having increased proper functioning has also increased heating value.
Summary of the invention
The objective of the invention is according to above-mentioned the deficiencies in the prior art part, a kind of automatic control valve block of biliquid flow is provided, the cartridge valve that this valve piece adopts integrated type to have standalone feature has substituted march-past cartridge valve of the prior art, adopt the load maintaining valve to come the fluid pressure that produces because of external loading in the balance operating cylinder simultaneously, fundamentally solved defective in the prior art.
The object of the invention realizes being finished by following technological scheme:
A kind of automatic control valve block of biliquid flow, comprise valve body, the control valve member, in the fuel feeding or oil return loop of the corresponding connection of each valve member and pump and fuel tank, it is characterized in that: described control valve member is the integrated type cartridge valve, and described control valve member comprises one group of control valve member at least, this group valve member comprises: relief valve, one-way valve, Pilot operated check valve, main hydraulic fluid port on the valve body comprises: filler opening, actuator port and return opening, filler opening is communicated with one-way valve and relief valve respectively, and the one-way valve outlet is communicated with actuator port and Pilot operated check valve again, and the oil return of all valves all is communicated with return opening.
Above-mentioned control valve member can comprise two groups of control valve members, pass through corresponding pipeline connection between two groups, promptly comprise: two relief valves, two one-way valves, two Pilot operated check valves, main hydraulic fluid port on the valve body comprises: two filler openings, two actuator ports and a return opening, the filler opening of one of them direction is communicated with an one-way valve and relief valve, and the one-way valve outlet is communicated with the actuator port and the Pilot operated check valve of this direction again, the filler opening of another direction and one-way valve and relief valve are communicated with, this one-way valve outlet is communicated with the actuator port and the Pilot operated check valve of this direction again, and the oil return of all valves all is communicated with return opening.Wherein have at least a Pilot operated check valve on the direction can adopt equilibrated valve to substitute, this equilibrated valve can be the load maintaining valve.Wherein have at least a relief valve on the direction can select unloading overflow valve for use.
Be threaded between described integrated type cartridge valve and the valve body.
Advantage of the present invention is, because the cartridge valve with standalone feature of the integral body that adopts is the standardization valve member, its reliable in quality, technical performance parameter can be selected, and are convenient to tissue and produce in enormous quantities, on the structure, any other element need not be dismantled in all outer surface that is exposed at valve body of all valve members that need change, and each cartridge valve all can directly split out and change, installation and maintenance, replacing are easily, control oil channel is simple, and Sealing quantity is few, has reduced the occurrence frequency of leakage failure.
Owing to used the load maintaining valve, the fluid pressure that produces because of external loading in can the balance operating cylinder is when the impact that is subjected to external loading, when the internal pressure of operating cylinder surpasses the pressure of setting up, can automatic deloading, guarantee that the load of operating cylinder is no more than specified value.When two oil pockets of operating cylinder all will be subjected to the impact of external load, use two load maintaining valves, two oil pockets of operating cylinder all are protected.The load maintaining valve is a kind of pressure autocontrol valve, handles the flow of operating cylinder oil return side by the pressure of operating cylinder oil-feed side, and during no input pressure, opposite side does not have oil return yet.When the K of the pressure of operating cylinder oil-feed side doubly stresses the difference of pressure of generations such as power load less than load maintaining valve set pressure value with oil return, the load maintaining valve is in the state that will open, but (K is the pilot pressure ratio of load maintaining valve also not have oil return, greater than 1), play the effect of the unlikely downslide of balancing gravity load, when selecting oily side pressure when continuing to raise, the open degree of load maintaining valve progressively increases.When the K of oil return side unloading pressure and suction side pressure doubly was equal to or greater than the setting pressure of load maintaining valve, the load maintaining valve was all opened the oil return resistance minimum of valve.The adjusting of the flow (or oil return resistance) of load maintaining valve is by input pressure, two parameters of oil return lateral load pressure, automatically carry out under the synergy, can not produce scavenger valve opens excessive, load is fallen automatically, the hydraulic pressure flutter phenomenon of closing scavenger valve again and producing, also do not exist the open degree of turning scavenger valve (Throttle Principle) down to cause next time with the operating mode that prevents load and fall voluntarily that resistance is big, the shortcoming of fluid heating, not influenced by oily temperature, regulating effect is reliable and stable.
Description of drawings
Accompanying drawing 2 is hydraulic control schematic diagram of the present invention;
Accompanying drawing 3 is control valve block structural diagram of the present invention;
The type pilot unloading overflow valve structural representation that accompanying drawing 4 adopts for the present invention;
The pilot-type relief valve structural representation that accompanying drawing 5 adopts for the present invention;
The one-way valve structures schematic representation that accompanying drawing 6 adopts for the present invention;
The Pilot operated check valve structural representation that accompanying drawing 7 adopts for the present invention;
The load maintaining valve structural representation that accompanying drawing 8 adopts for the present invention;
Accompanying drawing 9 is the embodiment of the invention one a hydraulic control schematic diagram;
Accompanying drawing 10 is the embodiment of the invention two hydraulic control schematic diagrams;
Accompanying drawing 11 is the embodiment of the invention three hydraulic control schematic diagrams;
Embodiment
Feature of the present invention and other correlated characteristic are described in further detail by embodiment below in conjunction with accompanying drawing, so that technician's of the same trade understanding:
Shown in Fig. 1-11, label 1-25 represents respectively: motor 1, bidirectional hydraulic pump 2, oil sucting one-way valve 3, oil return oil purifier 4, control valve piece 5 of the present invention, operating cylinder 6, oil hydraulic motor 7, rib valve 8, reel, wire rope and weight 9, break 10, valve body 11, the filler opening 12 of type pilot unloading overflow valve, return opening 13, control port 14, the pressure hydraulic fluid port 15 of pilot-type relief valve, main return opening 16, control oily return opening 17, the filler opening 18 of one-way valve, oil outlet 19, the actuator port 20 of Pilot operated check valve, return opening 21, control port 22, the actuator port 23 of load maintaining valve, leak hydraulic fluid port 24, control port 25.
Valve member in the prior art control valve piece comprises: type pilot unloading overflow valve DV1, pilot-type relief valve DV2, one-way valve RV1, RV2, Pilot operated check valve SV1, SV2.
Valve member in the control valve piece of the present invention comprises: type pilot unloading overflow valve CT1, pilot-type relief valve CT2, one-way valve CT3, CT4, Pilot operated check valve CT5, load maintaining valve CT6.
Embodiment one: control valve piece 5 of the present invention is applied on the hydraulic grab.
As shown in Figure 9, hydraulic grab generally by a motor 1, bidirectional hydraulic pump 2, two directly be contained in oil sucting one-way valve 3 on the bidirectional hydraulic pump inlet port, oil return oil purifier 4, control valve piece 5 of the present invention, at least one oil cylinder 6 (quantity of oil cylinder is identical with the quantity of claw), and the hydraulic element such as oil pipe, joint, fuel tank that connect usefulness are formed.The hydraulic control principle as shown in figure 10.
Present embodiment is when work, when grab bucket need be closed, motor 1 is just changeing, and the hydraulic oil in the fuel tank sucks from the oil sucting one-way valve 3 in left side, after the oil hydraulic pump pressurization, enter in the valve piece 5 by the P1 mouth, enter the rodless cavity of operating cylinder 6 by one-way valve CT3, hydraulic fluid port A, because the control of P1 mouth pressure is opened load maintaining valve CT6, hydraulic oil in the operating cylinder rod chamber is got back to fuel tank by hydraulic fluid port B, load maintaining valve CT6, hydraulic fluid port T, filter 4, makes the claw closure of grab bucket.The minimum cracking pressure P1 of load maintaining valve CT6 is that the setting pressure of the induced pressure that bears with operating cylinder, load maintaining valve CT6 is relevant.Because before CT6 does not open, operating cylinder is in closed state, this moment, the pressure of P1 can rise automatically, the rising of operating cylinder rodless cavity pressure P 1, can cause the rising of rod chamber pressure, just improved the load pressure value of CT6, the unlatching pilot pressure that CT6 is needed reduces, when both reach balance CT6 and open till.
Grab bucket is closed in the closed procedure, when running into resistances such as material when claw, the pressure of P1 can continue to raise, when material is grabbed full or claw when arriving the stroke end, can be elevated to the setting pressure of type pilot unloading overflow valve CT1, the oily stream of the oil pump P1 mouth of working this moment stops to the operating cylinder fuel feeding, and CT3 also closes immediately, the oil stream of work oil pump is got back to fuel tank by CT1, hydraulic fluid port T, return filter 4, promptly begins off-load.This moment, the resistance of unloading valve CT1 was very little.The power of hydraulic grab material clamping is to keep by the sealing of each hydraulic fluid port in the operating cylinder rodless cavity.The continuing of the off-load of unloading overflow valve CT1 action is to realize by the active force of the off-load control piston among control oil duct and the valve CT1 by the pressure of hydraulic fluid port A.Reason such as unrestrained owing to the internal leakage of operating cylinder, material, the pressure of hydraulic fluid port P1 can constantly descend, when being reduced to the minimum pressure (being generally the 85-90% of set pressure) of unloading overflow valve CT1 regulation, CT1 stops off-load, and the oil of oil pump flows to the rodless cavity of hydraulic fluid port A and operating cylinder.When the pressure of hydraulic fluid port A reaches the setting pressure of valve CT1, carry out off-load once more.Generally in the process that material grasps, do not stop motor, can remain enough chucking powers to guarantee grab bucket.
When grab bucket needs discharging (unlatching), motor 1 counter-rotating.Hydraulic oil in the fuel tank sucks from the oil sucting one-way valve 3 on right side, after the oil hydraulic pump pressurization, enter in the control valve 5 by the P2 mouth, enter the rod chamber of operating cylinder 6 by one-way valve CT4, hydraulic fluid port B, because the control of P2 mouth pressure is opened Pilot operated check valve CT5, the hydraulic oil in the operating cylinder rodless cavity is got back to fuel tank by hydraulic fluid port A, Pilot operated check valve CT5, hydraulic fluid port T, filter 4, the claw of grab bucket is opened, unloaded the junk material.The minimum cracking pressure P2 of Pilot operated check valve CT5 is relevant with the pilot pressure ratio of operating cylinder A hydraulic fluid port pressure and Pilot operated check valve.The maximum pressure of bidirectional hydraulic pump P2 hydraulic fluid port is determined by pilot-type relief valve CT2.When the pressure of hydraulic fluid port P2 was higher than the setting pressure of CT2 valve, CT2 produced overflow, and the oil of oil hydraulic pump is got back to fuel tank through hydraulic fluid port P2, valve CT2, hydraulic fluid port T, return filter 4.
Because the control valve piece has the heating value that off-load guarantees, reduces hydraulic system greatly, automatically keep effect with the automatic adjustment movement of pressure, by just needs of various pressure under the different operating modes of may command of motor positive and inverse, be specially adapted to use on the mobile device such as hydraulic grab.
Embodiment two: control valve piece 5 of the present invention can also be applied on the opening and closing device of harbour suspender, on the starting drive of harbour and inland river sluice, the method of its control is similar to hydraulic grab, just object has been become other devices such as gate by claw, the hydraulic control principle as shown in Figure 9, with the hydraulic grab unanimity, do not giving unnecessary details.
Embodiment three: control valve piece 5 of the present invention is applied on the boring mechanic, in order to drive drill bit, is applied on the rotary mechanism such as engineering machinery chassis, and the hydraulic control principle as shown in figure 10.
Be used to drive the hydraulic power supply and the controlling method of drill bit on the boring mechanic, all adopt the method for unidirectional oil hydraulic pump and selector valve basically.After adopting hydraulic control principle as shown in figure 10, just can reach drill bit and creep into and the purpose of oppositely changing working procedure controls such as drilling rod with the change motor drive direction.The control principle of control valve piece 5 inside as shown in Figure 9.With last different be; hydraulic fluid port B is as the power hydraulic fluid port of normal boring; lower work protection pressure is provided; the power oil sources mouth that hydraulic fluid port A uses as dismounting drilling rod; the oil sources that is higher than normal operating pressure can be provided, and the higher pressure oil-source that needs when solving the dismounting drilling tool can also provide the function of off-load pressurize; for drilling rods of some difficult dismountings under the prerequisite of maximum removal force, the time of distortion gradually is provided and is unlikely to take place the overheated phenomenon of hydraulic oil.Can certainly be without elements such as motor 1, oil hydraulic pump 2, one-way valve 3, oil purifiers 4, P1, P2 hydraulic fluid port directly received use on the existing selector valve of main frame, possess above-mentioned performance equally.
Embodiment four: control valve piece 5 of the present invention is applied on the hoist, and in order to drive cable drum, the hydraulic control schematic diagram as shown in figure 11.
Application controls valve piece 5 has solved the hydraulic control problem in the steady lifting of hoist effectively.This device mainly is made up of motor 1, bidirectional hydraulic pump 2, oil sucting one-way valve 3, oil return oil purifier 4, control valve piece 5, oil hydraulic motor 7, rib valve 8, hydraulic brake 10, operation mechanism 9 (reel, wire rope and weight) etc.In the use, the oil hydraulic motor that is produced by the weight of lifting has a side oil pipe of pressure, receives the B hydraulic fluid port of control valve piece 5, and promptly in the control valve piece 5 during the outside fuel feeding of A hydraulic fluid port, weight descends, and during the outside fuel feeding of B hydraulic fluid port, weight promotes.
Principle is: when pump 2 is just changeing, when hydraulic fluid port P1 has pressure, by rib valve 8 break 10 is opened, the oil of oil hydraulic pump 2 is just changeing through CT3, hydraulic fluid port A drive motor 7, weight descends, this moment, the oil return of motor 7 was got back to fuel tank through hydraulic fluid port B, valve CT6, oil return inlet T, oil purifier 4 because the pressure control of P1 is opened load maintaining valve CT6.When pump 2 stopped, because hydraulic fluid port P1, P2 all do not have pressure, so the delivery outlet of rib valve 8 do not have pressure yet, break 10 auto-closings, and reel shuts down.When pump 2 counter-rotatings, when hydraulic fluid port P2 had pressure, pressure oil was opened through rib valve 8 control brake devices 10 by P2, and hydraulic oil flows into oil hydraulic motor 7 through valve CT4, hydraulic fluid port B, drives reel, and weight is risen.
Certainly the power source of this device also can share with main frame, saves element 1-4, hydraulic fluid port P1, P2 is directly connected on the selector valve of main frame, can carry out work equally.
Claims (5)
1, a kind of automatic control valve block of biliquid flow, comprise valve body, the control valve member, it is characterized in that: described control valve member is the integrated type cartridge valve, and described control valve member comprises two groups of control valve members at least, every group of valve member comprises: relief valve, one-way valve, Pilot operated check valve, main hydraulic fluid port on the valve body comprises: filler opening, actuator port and return opening, filler opening is communicated with one-way valve and relief valve respectively, and the one-way valve outlet is communicated with actuator port and Pilot operated check valve again, the oil return of all valves all is communicated with return opening, pass through corresponding pipeline connection between group and the group, the filler opening of one of them direction is communicated with an one-way valve and relief valve, and the one-way valve outlet is communicated with the actuator port and the Pilot operated check valve of this direction again, the filler opening of another direction and one-way valve and relief valve are communicated with, this one-way valve outlet is communicated with the actuator port and the Pilot operated check valve of this direction again, and the oil return of all valves all is communicated with return opening.
2, a kind of automatic control valve block of biliquid flow according to claim 1 is characterized in that having at least a Pilot operated check valve on the direction can adopt equilibrated valve to substitute.
3, a kind of automatic control valve block of biliquid flow according to claim 2 is characterized in that described equilibrated valve is the load maintaining valve.
4, a kind of automatic control valve block of biliquid flow according to claim 1, it is characterized in that having at least a relief valve on the direction is unloading overflow valve.
5, a kind of automatic control valve block of biliquid flow according to claim 1 is characterized in that being threaded between described integrated type cartridge valve and the valve body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100277918A CN100337040C (en) | 2005-07-15 | 2005-07-15 | Automatic control valve block of biliquid flow |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100277918A CN100337040C (en) | 2005-07-15 | 2005-07-15 | Automatic control valve block of biliquid flow |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1719046A CN1719046A (en) | 2006-01-11 |
| CN100337040C true CN100337040C (en) | 2007-09-12 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100277918A Expired - Fee Related CN100337040C (en) | 2005-07-15 | 2005-07-15 | Automatic control valve block of biliquid flow |
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| CN (1) | CN100337040C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100516554C (en) * | 2006-06-28 | 2009-07-22 | 卢永松 | Built-in constant-pressure output control pressure source module |
| CN103836016A (en) * | 2012-11-23 | 2014-06-04 | 上海立新液压有限公司 | Electric hydraulic control check valve |
| DE202014104599U1 (en) * | 2014-09-25 | 2014-10-09 | Bürkert Werke GmbH | Modular valve system |
| CN105156730B (en) * | 2015-09-17 | 2017-09-05 | 浙江松乔气动液压有限公司 | Snap joint modular valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2052458U (en) * | 1989-01-31 | 1990-02-07 | 吴明坚 | Energy saving hydraulic pressure installation |
| CN2185341Y (en) * | 1993-02-22 | 1994-12-14 | 周龙生 | Electromagnetic combined control valve for tilting oil tank of car |
| CN2539868Y (en) * | 2002-02-07 | 2003-03-12 | 仇九桃 | Hydraulic integrated block |
| US6669169B2 (en) * | 2000-01-31 | 2003-12-30 | Freni Brembo S.P.A. | Bleed device and kit for hydraulic circuits |
| US6866485B2 (en) * | 2001-11-28 | 2005-03-15 | Minibooster Hydraulics A/S | Double-acting hydraulic pressure intensifier |
| CN2690642Y (en) * | 2004-02-23 | 2005-04-06 | 仇九桃 | Hydraulic integrated block |
| CN2864184Y (en) * | 2005-07-15 | 2007-01-31 | 上海昂丰矿机科技有限公司 | Double liquid flow automatic control valve |
-
2005
- 2005-07-15 CN CNB2005100277918A patent/CN100337040C/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2052458U (en) * | 1989-01-31 | 1990-02-07 | 吴明坚 | Energy saving hydraulic pressure installation |
| CN2185341Y (en) * | 1993-02-22 | 1994-12-14 | 周龙生 | Electromagnetic combined control valve for tilting oil tank of car |
| US6669169B2 (en) * | 2000-01-31 | 2003-12-30 | Freni Brembo S.P.A. | Bleed device and kit for hydraulic circuits |
| US6866485B2 (en) * | 2001-11-28 | 2005-03-15 | Minibooster Hydraulics A/S | Double-acting hydraulic pressure intensifier |
| CN2539868Y (en) * | 2002-02-07 | 2003-03-12 | 仇九桃 | Hydraulic integrated block |
| CN2690642Y (en) * | 2004-02-23 | 2005-04-06 | 仇九桃 | Hydraulic integrated block |
| CN2864184Y (en) * | 2005-07-15 | 2007-01-31 | 上海昂丰矿机科技有限公司 | Double liquid flow automatic control valve |
Also Published As
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| CN1719046A (en) | 2006-01-11 |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Shanghai Nanbu Plastic Products Co., Ltd. Assignor: Shanghai Angfeng Mineral Machine Technology Co., Ltd. Contract fulfillment period: 2009.7.30 to 2014.7.30 contract change Contract record no.: 2009310000229 Denomination of invention: Automatic control valve block of biliquid flow Granted publication date: 20070912 License type: Exclusive license Record date: 2009.9.29 |
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| LIC | Patent licence contract for exploitation submitted for record |
Free format text: EXCLUSIVE LICENSE; TIME LIMIT OF IMPLEMENTING CONTACT: 2009.7.30 TO 2014.7.30; CHANGE OF CONTRACT Name of requester: SHANGHAI SOUTHERN PLASTIC PRODUCTS CO.,LTD. Effective date: 20090929 |
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| EC01 | Cancellation of recordation of patent licensing contract |
Assignee: Shanghai Nanbu Plastic Products Co., Ltd. Assignor: Shanghai Angfeng Mineral Machine Technology Co., Ltd. Contract record no.: 2009310000229 Date of cancellation: 20100518 |
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| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070912 Termination date: 20130715 |