CN102996556A - Direct-acting type hydraulic threaded cartridge balanced valve - Google Patents

Direct-acting type hydraulic threaded cartridge balanced valve Download PDF

Info

Publication number
CN102996556A
CN102996556A CN2012105127781A CN201210512778A CN102996556A CN 102996556 A CN102996556 A CN 102996556A CN 2012105127781 A CN2012105127781 A CN 2012105127781A CN 201210512778 A CN201210512778 A CN 201210512778A CN 102996556 A CN102996556 A CN 102996556A
Authority
CN
China
Prior art keywords
pressure port
valve
pressure
spring
diameter
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.)
Pending
Application number
CN2012105127781A
Other languages
Chinese (zh)
Inventor
于刚
孙燕
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
HUAITE (CHINA) DRIVING PRODUCT CO Ltd
WHITE (CHINA) DRIVE PRODUCTS CO Ltd
Original Assignee
HUAITE (CHINA) DRIVING PRODUCT CO Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by HUAITE (CHINA) DRIVING PRODUCT CO Ltd filed Critical HUAITE (CHINA) DRIVING PRODUCT CO Ltd
Priority to CN2012105127781A priority Critical patent/CN102996556A/en
Publication of CN102996556A publication Critical patent/CN102996556A/en
Pending legal-status Critical Current

Links

Images

Landscapes

  • Safety Valves (AREA)

Abstract

The invention discloses a direct-acting type hydraulic threaded cartridge balanced valve. The direct-acting type hydraulic threaded cartridge balanced valve comprises a valve sleeve, a main valve core, a one-way valve core and a balanced valve spring, wherein the valve sleeve is provided with a pressure port A, a pressure port B and a pressure port C, d 4 is the diameter of the pressure port C, and d 1 is the circulating diameter of the main valve core; the pressure port A and the pressure port C are arranged in the same side of the d 1, and the pressure port B is arranged in the other side of the d1 corresponding to the pressure port A and the pressure port C; and d 3 is the circulating diameter of the one-way valve core, and the diameter of a sealing strip of the pressure port A and the pressure port C is d 2. The direct-acting type hydraulic threaded cartridge balanced valve provided by the invention has the advantages that a required initial preliminary pressure is small when the balanced valve spring realizes an overflowing function, the spring stiffness is small, therefore, the spring design is simple, the requirement can be met by one spring, the opening ratio of the main valve core of the balanced valve is large, the pressure adjustment accuracy is good, and the operation is stable.

Description

Direct moving type hydraulic thread cartridge equilibrium valve
Technical field
The present invention relates to a kind of equilibrium valve of Hydraulic Power Transmission System, particularly a kind of direct moving type hydraulic thread cartridge equilibrium valve.
Background technique
Hydraulically balanced valve can be described as and integrates one-way function, hydraulic-control throttling function, relief function, and it plays a part very important to betterment works machinery usability, simultaneously the overall engineering machine performance is also had important impact.For example the lifting mechanism of hydraulic hoist, jib lubbing mechanism and extending means are when band carries decline, if without equilibrium valve, mechanism will produce hypervelocity decline, uncontrollable under the effect of load, dangerous phenomenon etc. occurs.Equally, in All Hydraulic Travelling System, in descending, also can produce the danger that hypervelocity glides, therefore also need the balance valve.
The working principle of hydraulically balanced valve is as shown in Figure 1:
(1) one-way function, hydraulic oil are from pressure port B → pressure port A, and it allows hydraulic oil to pass through with very little pressure drop, enters hydraulic actuator, for example cylinder or motor;
(2) hydraulic-control throttling function, hydraulic oil be from pressure port A → pressure port B, controls the open amount of throttle valve by the pressure of pilot pressure mouth C, thereby so that the speed of load is steady;
(3) relief function, without pilot pressure, but the pressure of induced pressure mouth A is when surpassing setting pressure at pressure port C, and the relief valve function is opened, and hydraulic oil is from pressure port A → pressure port B, to avoid hydraulic actuator owing to superpressure is damaged.
Accompanying drawing 2 is depicted as the structure principle chart of existing hydraulically balanced valve.Offer pressure port A, pressure port B, pressure port C on the valve pocket 1, d4 is that diameter, the d1 of pressure port C is main valve plug 2 circulation diameters, wherein, pressure port B and pressure port C offer the position at the homonymy of d1, pressure port A offers the position with respect to pressure port B and the pressure port C opposite side at d1, d3 is nonreturn valve core 3 circulation diameters, and the sealing strip diameter of pressure port B and pressure port C is d2.
When realizing one-way function, hydraulic oil is from pressure port B → pressure port A, because d3 is nonreturn valve core 3 circulation diameters, this moment, d1 and d3 were the same place diameter, so d1 equates with d3.
When realizing relief function, without pilot pressure, main valve plug 2 is opened and is adopted the forward oil-feeds at pressure port C, and hydraulic oil is from pressure port A → pressure port B, pressure port A place pressure P A* π (d1) 2/ 4=F SA, F SAExpression overcomes the required spring force of equilibrium valve spring 4, this moment equilibrium valve spring 4 rigidity F '=△ F SA/ △ H SA=△ P A* π (d1) 2/ (4 * △ H SA), wherein: △ F SAWhen the expression equilibrium valve is realized relief function, under initial pressure state and the rated pressure state, the variable quantity of equilibrium valve spring pressure; △ H SAWhen the expression equilibrium valve is realized relief function, under initial pressure state and the rated pressure state, the changing value of equilibrium valve spring high compression.So equilibrium valve spring rate F ' with (d1) 2Be directly proportional.But d1 is main valve plug circulation diameter, for guaranteeing the rated flow of equilibrium valve, so require equilibrium valve spring rate F ' and the initial precompression F of equilibrium valve spring SAVery large, therefore, it is higher to exist control spring pressure, and pressure regulation precision, stable working, Security are relatively poor, the problems such as spring design complexity, and the equilibrium valve spring that has has adopted many, and spring rate is excessive, is difficult to design.
Summary of the invention
Goal of the invention: for the problems referred to above, the purpose of this invention is to provide the direct moving type hydraulic thread cartridge equilibrium valve that a kind of spring force is easy to control, the pressure regulation precision high, stable working is good.
Technological scheme: a kind of direct moving type hydraulic thread cartridge equilibrium valve, comprise valve pocket, main valve plug, nonreturn valve core, equilibrium valve spring, offer pressure port A, pressure port B, pressure port C on the described valve pocket, d4 is that diameter, the d1 of pressure port C is described main valve plug circulation diameter, described pressure port A and described pressure port C offer the position at the homonymy of d1, described pressure port B offers the position with respect to described pressure port A and the described pressure port C opposite side at d1, d3 is described nonreturn valve core circulation diameter, and the sealing strip diameter of described pressure port A and described pressure port C is d2.
Described d1 more than or equal to or less than described d3, d1 and d3 are the diameter that do not exist together at valve pocket, can determine size according to actual conditions.
When pressure port B place pressure P B* π (d3) 2/ 4=F SB, F SBExpression overcomes the required spring force of spring of nonreturn valve core, and equilibrium valve is realized one-way function, and hydraulic oil is from pressure port B → pressure port A.At this moment, pressure port B place pressure P BD4＞d1 arrives spring chamber by the main valve plug throttle orifice, owing to can not be opened main valve plug.
When pressure port C place pressure P C* π ［ (d4) 2-(d3) 2］/4=F SC, F SCExpression overcomes the required spring force of equilibrium valve spring, and main valve plug is opened, and hydraulic oil is from pressure port A → pressure port B, pressure port C place pressure P CBe used for controlling the open amount of throttle valve, so that loading speed is steady.
When realizing relief function, without pilot pressure, main valve plug is opened and is reverse oil-feed, pressure port A place pressure P at pressure port C A* π ［ (d2) 2-(d1) 2］/4=F SA, this moment equilibrium valve spring rate F '=△ F SA/ △ H SA=△ P A* π ［ (d2) 2-(d1) 2］/(4 * △ H SA), so equilibrium valve spring rate F ' with (d2) 2-(d1) 2Be directly proportional, and only need control ［ (d2) 2-(d1) 2］＜(d1) 2, therefore, both can guarantee main valve plug flow area π (d1) 2/ 4 satisfy the rated flow requirement, can obtain again preferably equilibrium valve spring rate F ' and the initial precompression F of equilibrium valve spring SA, spring design is simple, and the pressure regulation precision is good, stable working.
Beneficial effect: compared with prior art, advantage of the present invention is that the equilibrium valve spring is when realizing relief function, required initial precompression is little, spring rate is little, therefore spring design is simple, only need adopt a spring to satisfy the demands, and the unlatching of equilibrium valve main valve plug is than large, the pressure regulation precision is good, and motion steadily.
Description of drawings
Fig. 1 is the fundamental diagram of hydraulically balanced valve;
Fig. 2 is the structure principle chart of existing hydraulically balanced valve;
Fig. 3 is hydraulically balanced valve structure principle chart initial position schematic representation of the present invention;
Fig. 4 is that hydraulically balanced valve structure principle chart nonreturn valve core of the present invention is opened the position view of realizing one-way function;
Fig. 5 is that hydraulically balanced valve structure principle chart main valve plug of the present invention is opened the position view of realizing the hydraulic-control throttling function;
Fig. 6 is that hydraulically balanced valve structure principle chart main valve plug of the present invention is opened the position view of realizing relief function;
Fig. 7 is the structure principle chart during with the normal operation of the rotary motor of hydraulically balanced valve of the present invention;
Fig. 8 is the structure principle chart during with the braking of the rotary motor of hydraulically balanced valve of the present invention or hypervelocity;
Continuous arrow points represents that hydraulic oil flows among above-mentioned each figure.
Embodiment
Below in conjunction with the drawings and specific embodiments, further illustrate the present invention, should understand these embodiments only is used for explanation the present invention and is not used in and limits the scope of the invention, after having read the present invention, those skilled in the art all fall within the application's claims limited range to the modification of the various equivalent form of values of the present invention.
As shown in Figure 3, a kind of direct moving type hydraulic thread cartridge equilibrium valve mainly comprises valve pocket 1, main valve plug 2, nonreturn valve core 3, equilibrium valve spring 4, adjusting screw 5, locking nut 6, plug screw 7, Packing spring seat 8, spring seat 9, steel ball 10, check valve spring 11.
Offer pressure port A, pressure port B, pressure port C on the valve pocket 1, d4 is that diameter, the d1 of pressure port C is main valve plug 2 circulation diameters, pressure port A and pressure port C offer the position at the homonymy of d1, pressure port B offers the position with respect to pressure port A and the pressure port C opposite side at d1, and d3 is nonreturn valve core 3 circulation diameters.Pressure port A and pressure port C outside seal by seal ring 12, inside cooperates by sealing strip, sealing band diameter is d2, pressure port A and pressure port B seal by plane d on the valve pocket and main valve plug firewire, the spring chamber of equilibrium valve spring 4 seals by seal ring 14 and seal ring 15, and is communicated with pressure port B by main valve plug damping hole 13.
Adjust adjusting screw 5 screw-in lengths and control equilibrium valve spring 4 initial compression amounts, to regulate cracking pressure and the rated pressure of main valve plug 2; Locking nut 6 is with adjusting screw 5 lockings; The spring force that is applied on the main valve plug 2 transmits by steel ball 10, has guaranteed accuracy of alignment.
As shown in Figure 4, when pressure port B place pressure P B* π (d3) 2/ 4=F SB, F SBExpression overcomes the required spring force of check valve spring 11 of nonreturn valve core 3, and equilibrium valve is realized one-way function, and hydraulic oil is from pressure port B → pressure port A.At this moment, pressure port B place pressure P BBy the spring chamber of main valve plug 2 throttle orifices arrival equilibrium valve spring 4, because d4＞d1 can not be opened main valve plug 2.
As shown in Figure 5, when pressure port C place pressure P C* π ［ (d4) 2-(d3) 2］/4=F SC, F SCExpression overcomes the required spring force of equilibrium valve spring 4, and main valve plug 2 is opened, and hydraulic oil is from pressure port A → pressure port B, pressure port C place pressure P CBe used for controlling the open amount of throttle valve, so that loading speed is steady.
As shown in Figure 6, when realizing relief function, without pilot pressure, main valve plug 2 is opened and is reverse oil-feed, pressure port A place pressure P at pressure port C A* π ［ (d2) 2-(d1) 2］/4=F SA, this moment equilibrium valve spring 4 rigidity F '=△ F SA/ △ H SA=△ P A* π ［ (d2) 2-(d1) 2］/(4 * △ H SA), so equilibrium valve spring 4 rigidity F ' with (d2) 2-(d1) 2Be directly proportional, and only need control ［ (d2) 2-(d1) 2］＜(d1) 2, therefore, both can guarantee main valve plug 2 flow area π (d1) 2/ 4 satisfy the rated flow requirement, can obtain again preferably equilibrium valve spring 4 rigidity F ' and equilibrium valve spring 4 initial precompression F SA, spring design is simple, and the pressure regulation precision is good, stable working.
The below take with the rotary motor of hydraulically balanced valve of the present invention as example, introduce the application of hydraulically balanced valve of the present invention on rotary motor.
As shown in Figure 7, when the pressure port Ba of equilibrium valve 16 advances high pressure oil, equilibrium valve 16 is realized one-way functions, and hydraulic oil is from pressure port Ba → pressure port Aa, through the pressure port Ab of rotary motor 18 → equilibrium valve 17; Because the high pressure oil of the pressure port Ba of equilibrium valve 16 is communicated with the pressure port Cb of equilibrium valve 17, the main valve plug 20 of equilibrium valve 17 is opened, realize the hydraulic-control throttling function, hydraulic oil is realized pressure port Ba oil-feed, the fuel-displaced loop of pressure port Bb through the pressure port Ab of equilibrium valve 17 → pressure port Bb.
As shown in Figure 8, advance high pressure oil as prerequisite take the pressure port Ba of equilibrium valve 16, rotary motor 18 is realized braking or hypervelocity when (actual speed of rotary motor is called hypervelocity when surpassing the corresponding rotating speed of oil hydraulic pump fuel delivery), and pressure port Ba becomes zero-pressure.Because the pressure port Ba of equilibrium valve 16 and the pressure port Cb of equilibrium valve 17 are communicated with, and also become zero-pressure, so the nonreturn valve core 19 of equilibrium valve 16 is all closed under spring-force driven dual with the main valve plug 20 of equilibrium valve 17.But because rotary motor 18 continues rotation under effect of inertia, the hydraulic fluid port E pressure of rotary motor 18 continues to increase, E is communicated with Ab, be that pressure port Ab pressure continues to increase, when this pressure overcomes the spring force of equilibrium valve spring 21 of equilibrium valve 17, the main valve plug 20 of equilibrium valve 17 is opened again, the pressure port Ab of equilibrium valve 17 and pressure port Bb are communicated with, hydraulic oil by pressure port Ab to pressure port Bb pressure release, it is hydraulic fluid port E pressure release, equilibrium valve 17 is realized relief function, avoids hydraulic actuator owing to superpressure is damaged.

Claims (2)

1. direct moving type hydraulic thread cartridge equilibrium valve, comprise valve pocket (1), main valve plug (2), nonreturn valve core (3), equilibrium valve spring (4), described valve pocket is offered pressure port A on (1), pressure port B, pressure port C, d4 is the diameter of pressure port C, d1 is described main valve plug (2) circulation diameter, it is characterized in that: described pressure port A and described pressure port C offer the position at the homonymy of d1, described pressure port B offers the position with respect to described pressure port A and the described pressure port C opposite side at d1, d3 is described nonreturn valve core (3) circulation diameter, and the sealing strip diameter of described pressure port A and described pressure port C is d2.
2. direct moving type hydraulic thread cartridge equilibrium valve according to claim 1 is characterized in that: described d1 more than or equal to or less than described d3.
CN2012105127781A 2012-12-04 2012-12-04 Direct-acting type hydraulic threaded cartridge balanced valve Pending CN102996556A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN2012105127781A CN102996556A (en) 2012-12-04 2012-12-04 Direct-acting type hydraulic threaded cartridge balanced valve

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN2012105127781A CN102996556A (en) 2012-12-04 2012-12-04 Direct-acting type hydraulic threaded cartridge balanced valve

Publications (1)

Publication Number Publication Date
CN102996556A true CN102996556A (en) 2013-03-27

Family

ID=47925535

Family Applications (1)

Application Number Title Priority Date Filing Date
CN2012105127781A Pending CN102996556A (en) 2012-12-04 2012-12-04 Direct-acting type hydraulic threaded cartridge balanced valve

Country Status (1)

Country Link
CN (1) CN102996556A (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104806594A (en) * 2015-04-23 2015-07-29 圣邦集团有限公司 Multi-way valve with oil cylinder load holding function
CN108930682A (en) * 2018-08-22 2018-12-04 佛山信卓派思机械科技有限公司 A kind of improved balanced valve of structure
CN108953633A (en) * 2018-09-27 2018-12-07 邵延荣 A kind of screw-in cartridge valve
CN108953266A (en) * 2018-08-21 2018-12-07 东莞海特帕沃液压科技有限公司 A kind of balanced valve opened stage by stage
CN108953267A (en) * 2018-08-22 2018-12-07 东莞海特帕沃液压科技有限公司 A kind of flow type balanced valve
CN108980133A (en) * 2018-09-27 2018-12-11 邵延荣 A kind of unloading overflow valve
CN109026891A (en) * 2018-08-22 2018-12-18 佛山信卓派思机械科技有限公司 A kind of modified form balanced valve
CN111594504A (en) * 2020-05-26 2020-08-28 柳州柳工挖掘机有限公司 Balance valve for traveling motor and crawler excavator

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0007712A1 (en) * 1978-07-27 1980-02-06 Modular Controls Corporation Load control and holding valve
US4346733A (en) * 1980-07-29 1982-08-31 Fluid Controls, Inc. Control valve
US4836240A (en) * 1988-03-31 1989-06-06 Webster Electric Company, Inc. Pilot-assisted pressure relief valve
US6497251B1 (en) * 2001-08-06 2002-12-24 Gilmore Valve Co., Ltd. Hydraulic latching spool valve
CN101576100A (en) * 2008-12-18 2009-11-11 上海电气液压气动有限公司 Equilibrium valve capable of supplementing oil
CN101634317A (en) * 2009-08-21 2010-01-27 宁波汉商液压有限公司 Plug-in type balance valve
CN101865171A (en) * 2010-07-02 2010-10-20 镇江大力液压马达有限责任公司 Thread cartridge balanced valve
CN202176567U (en) * 2011-08-17 2012-03-28 浙江圣邦机械有限公司 Balance valve
CN102562699A (en) * 2011-12-16 2012-07-11 中联重科股份有限公司 Balance valve, hydraulic cylinder telescopic control loop and crane
CN202971371U (en) * 2012-12-04 2013-06-05 怀特(中国)驱动产品有限公司 Directly-operated type hydraulic screw-in balance valve

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0007712A1 (en) * 1978-07-27 1980-02-06 Modular Controls Corporation Load control and holding valve
US4346733A (en) * 1980-07-29 1982-08-31 Fluid Controls, Inc. Control valve
US4836240A (en) * 1988-03-31 1989-06-06 Webster Electric Company, Inc. Pilot-assisted pressure relief valve
US6497251B1 (en) * 2001-08-06 2002-12-24 Gilmore Valve Co., Ltd. Hydraulic latching spool valve
CN101576100A (en) * 2008-12-18 2009-11-11 上海电气液压气动有限公司 Equilibrium valve capable of supplementing oil
CN101634317A (en) * 2009-08-21 2010-01-27 宁波汉商液压有限公司 Plug-in type balance valve
CN101865171A (en) * 2010-07-02 2010-10-20 镇江大力液压马达有限责任公司 Thread cartridge balanced valve
CN202176567U (en) * 2011-08-17 2012-03-28 浙江圣邦机械有限公司 Balance valve
CN102562699A (en) * 2011-12-16 2012-07-11 中联重科股份有限公司 Balance valve, hydraulic cylinder telescopic control loop and crane
CN202971371U (en) * 2012-12-04 2013-06-05 怀特(中国)驱动产品有限公司 Directly-operated type hydraulic screw-in balance valve

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104806594A (en) * 2015-04-23 2015-07-29 圣邦集团有限公司 Multi-way valve with oil cylinder load holding function
CN108953266A (en) * 2018-08-21 2018-12-07 东莞海特帕沃液压科技有限公司 A kind of balanced valve opened stage by stage
CN108930682A (en) * 2018-08-22 2018-12-04 佛山信卓派思机械科技有限公司 A kind of improved balanced valve of structure
CN108953267A (en) * 2018-08-22 2018-12-07 东莞海特帕沃液压科技有限公司 A kind of flow type balanced valve
CN109026891A (en) * 2018-08-22 2018-12-18 佛山信卓派思机械科技有限公司 A kind of modified form balanced valve
CN108930682B (en) * 2018-08-22 2020-06-26 江苏金晟元特种阀门股份有限公司 Balance valve with improved structure
CN108953633A (en) * 2018-09-27 2018-12-07 邵延荣 A kind of screw-in cartridge valve
CN108980133A (en) * 2018-09-27 2018-12-11 邵延荣 A kind of unloading overflow valve
CN108953633B (en) * 2018-09-27 2019-08-23 上海江浪科技股份有限公司 A kind of screw-in cartridge valve
CN111594504A (en) * 2020-05-26 2020-08-28 柳州柳工挖掘机有限公司 Balance valve for traveling motor and crawler excavator
CN111594504B (en) * 2020-05-26 2022-05-17 柳州柳工挖掘机有限公司 Balance valve for traveling motor and crawler excavator

Similar Documents

Publication Publication Date Title
CN102996556A (en) Direct-acting type hydraulic threaded cartridge balanced valve
CN202971371U (en) Directly-operated type hydraulic screw-in balance valve
CN102562699B (en) Balance valve, hydraulic cylinder telescopic control loop and crane
CN201896802U (en) Unidirectional differential speed-regulation hydraulic control device
CN201786795U (en) Hydraulic pressure stop valve
CN103925254A (en) Pressure compensation valve and load sensory system
CN202732526U (en) Combined hydraulic balance valve
CN204493329U (en) A kind of proportional hydraulic equilibrium valve
WO2012088892A1 (en) Rotating valve and rotating control loop using same
CN103557195B (en) A kind of bringing onto load sensitivity and emergent manual chip proportional reversing valve
CN107461516A (en) A kind of differential type electric-hydraulic proportion uniform-pressure-drop valve
CN106050775B (en) Structure improved pilot-actuated valve
CN108061070B (en) A kind of pressure-control valve
CN105402182A (en) Load sensing multi-way directional valve and hydraulic control system of loader
CN104653539A (en) Proportional hydraulically balanced valve
CN108412831B (en) Shunt pressure-regulating speed-regulating reversing integrated valve
CN110671379A (en) Flow control type hoist balance valve
CN112431806B (en) Pilot high-flow load control valve with back pressure compensation function
CN204164067U (en) A kind of equilibrium valve
CN106382269A (en) Combination valve with speed governing, reversing and overflow functions
CN205207311U (en) Meso position burden flow valve, swing arm energy -saving control system and excavator
CN103541942B (en) Be applicable to the bidirectional control valve of short-wall coal-winning machine height-adjusting system
CN105422538A (en) Pressure self-adapted multi-passage equalizing valve
CN201486952U (en) Balance valve for controlling hydraulic motor
CN203835841U (en) Pressure compensation valve and load sensitive system

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C05 Deemed withdrawal (patent law before 1993)
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20130327