DK155895B - COMPENSATION VALVE - Google Patents
COMPENSATION VALVE Download PDFInfo
- Publication number
- DK155895B DK155895B DK561783A DK561783A DK155895B DK 155895 B DK155895 B DK 155895B DK 561783 A DK561783 A DK 561783A DK 561783 A DK561783 A DK 561783A DK 155895 B DK155895 B DK 155895B
- Authority
- DK
- Denmark
- Prior art keywords
- valve
- end faces
- spacer
- bore
- radial
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
- F16K11/105—Three-way check or safety valves with two or more closure members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/04—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves
- F16K11/056—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only lift valves with ball-shaped valve members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K15/00—Check valves
- F16K15/02—Check valves with guided rigid valve members
- F16K15/04—Check valves with guided rigid valve members shaped as balls
- F16K15/042—Check valves with guided rigid valve members shaped as balls with a plurality of balls
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Control Of The Air-Fuel Ratio Of Carburetors (AREA)
- Check Valves (AREA)
- Multiple-Way Valves (AREA)
- Magnetic Resonance Imaging Apparatus (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Safety Valves (AREA)
- Lift Valve (AREA)
- Valve Device For Special Equipments (AREA)
- Superconductors And Manufacturing Methods Therefor (AREA)
- Stereo-Broadcasting Methods (AREA)
- Details Of Valves (AREA)
- External Artificial Organs (AREA)
- Compressor (AREA)
Abstract
Description
iin
DK 155895 BDK 155895 B
Opfindelsen angår en udligningsventil med en ventilboring, til hvilken der er tilsluttet en første ledning samt på begge sider af denne med indbyrdes afstand en anden og en tredje ledning, og i hvilken der på begge sider af den første ledning 5 findes en ventil, som tillader henholdsvis at afspærre strømmen af et trykmiddel fra den anden og den tredje ledning til den første ledning, hvilke ventiler har lukkeelementer, som kan bringes til anlæg imod ventilsæder ved enden af den anden og den tredje ledning, og som skiftevis kan ligge an imod 10 en i ventilboringen forskydeligt anbragt afstandsholder, der har en cylinderdel, og som i området ved sine endeflader er forsynet med mindst tre fra cylinderdelen radialt udadgående radialdele til indstilling af afstandsholderen i ventilboringen.The invention relates to a compensating valve with a valve bore to which a first conduit is connected and on both sides thereof a second and a third conduit are mutually spaced, and in which on both sides of the first conduit 5 there is a valve which permits respectively blocking the flow of a pressure means from the second and third conduits to the first conduit, which valves have closure elements which can be brought into contact with valve seats at the end of the second and third conduits and which may alternately abut against a in the valve bore displaceable spacer having a cylinder portion and provided in the region at its end faces with at least three radially outward radial portions from the cylinder portion for adjusting the spacer in the valve bore.
1515
Ved denne udligningsventil (USA patent nr. 1.409.116) er normal-stillingen den vertikale, så at de som kugler udformede lukkeelementer lukker henholdsvis åbner under virkningen af tyngdekraften. I horisontalstillingen kan begge lukkeelementerne 20 være åbne og kun på grund af forskellige trykforhold blive lukket eller åbnet. Såkaldte stopplader er tilvejebragt med henblik på at forhindre et ukontrolleret frem- og tilbageløb af kuglerne i ledningerne. Hertil kommer, at radialdelene er udformet som i tværsnit trekantformede næser, hvis spidser 25 ligger an imod den indvendige cylinderflade i ventilboringen, hvorved gennemstrømningstværsnittet for trykmediet bliver stærkt begrænset og i området ved ventilsæderne danner sliberiller, som hæmmer en driftssikker lukning af kuglerne.In this balancing valve (US Patent No. 1,409,116), the normal position is the vertical so that the ball-shaped closure elements close or open, respectively, under the effect of gravity. In the horizontal position, both closing elements 20 can be open and closed or opened only due to different pressure conditions. So-called stop plates are provided to prevent uncontrolled back and forth of the balls in the wires. In addition, the radial members are formed as cross-sectional triangular noses, the tips of which 25 abut the inner cylinder surface of the valve bore, thereby greatly reducing the flow cross-section of the pressure medium and forming abrasive grooves in the area of the valve seats which inhibit reliable closing of the balls.
30 Fra australsk patentskrift nr. 141.469 er det ved en anden udligningsventil kendt at belaste lukkeelementerne med fjedre, hvor fjederkræfterne er forskellige.30 From Australian Patent Specification No. 141,469 it is known in another compensating valve to load the closing elements with springs where the spring forces are different.
Formålet med opfindelsen er at udforme udligningsventilen 35 så driftssikkert, at der bliver opnået det størst mulige gen nemstrømningstværsnit for trykmediet.The object of the invention is to design the compensating valve 35 so reliably that the largest possible flow cross-section of the pressure medium is obtained.
DK 155895 BDK 155895 B
22
Dette bliver opnået ved hjælp af udligningsventilen ifølge opfindelsen, som er ejendommelig ved, at lukkeelementerne hver kan belastes hen imod ventilsæderne ved hjælp af en fjeder, og hvor radialdelene har form som vinger med parallelle sideflader og/eller som radialstifter, hvorhos der i området ved afstandsholderens endeflader i overkanten af radialdelenes vinger er udformet udsparinger, og/eller cylinderdelens endeflader er udformet kugleformede, og hvor radialstifterne ved ^ ikke-kugleformet udformning af endefladerne er anbragt i af stand fra cylinderdelens endeflader. På denne måde opstår der ved den særlige indretning af radialdelene et gennemstrømningstværsnit, der ikke forhindrer gennemstrømningen af trykmediet, og som ved hjælp af fjedrene kan lukkes pålideligt, ^ hvorved der i området ved ventilsæderne ikke opstår nogen sliberiller, og en gratdannelse ligeledes bliver forhindret, så at der alt i alt også gennem en lang brugstid fremkommer en mere driftssikker udformning.This is achieved by means of the balancing valve according to the invention, which is characterized in that the closing elements can each be loaded towards the valve seats by means of a spring, and in which the radial parts are in the form of wings with parallel lateral surfaces and / or as radial pins, where in the region of the end faces of the spacer in the upper edge of the wings of the radial member are recesses, and / or the end faces of the cylinder member are spherical, and the radial pins, by non-spherical configuration of the end faces, are spaced apart from the end faces of the cylinder member. In this way, a special cross-section is formed by the special arrangement of the radial parts which does not prevent the flow of the pressure medium and which can be reliably closed by means of the springs, whereby no abrasive grooves are formed in the area of the valve seats and a grating is also prevented. so that all in all, even over a long useful life, a more reliable design emerges.
20 For at den trykledning, i hvilken mindre væsketryk hersker, skal være forbundet med udtømningen bliver ifølge opfindelsen foreslået, at fjedrene har forskellige fjederkræfter.In order that the pressure line in which less fluid pressure prevails must be connected to the discharge, it is proposed according to the invention that the springs have different spring forces.
Opfindelsen forklares i det følgende nærmere under henvisning 2 5 til tegningen, hvor fig. 1 viser en udførelsesform for en udligningsventil ifølge opfindelsen set i længdesnit, 3 0 fig. 2 en afstandsholder i ventilen set i perspektiv, fig. 3 afstandsholderen i en anden udførelsesform og fig. 4 afstandsholderen i en yderligere udførelsesform.The invention will now be explained in more detail with reference to the drawings, in which fig. 1 is a longitudinal sectional view of an equalizing valve according to the invention; FIG. 2 is a perspective view of a spacer in the valve; FIG. 3 shows the spacer in another embodiment; and FIG. 4 in a further embodiment.
Den i fig. 1 viste udligningsventil 10 har et ventillegeme 35The FIG. 1, the balancing valve 10 shown has a valve body 35
DK 155895 BDK 155895 B
3 12, i hvilket der er indarbejdet en langsgående første ventilboring 14, som omtrent i sin midte bliver gennemskåret af en anden ventilboring 16. Ved enderne af den første ventilboring 14 er der tilsluttet to i kravene som anden og tredje ledning 5 betegnede trykledninger 18 og 20, og den anden ventilboring 16 er ved den ende, der ligger bortvendt fra den første ventilboring 14, via en første ledning eller en udgangsledning 22 forbundet med et forbrugssted 24. Den første ventilboring 14 er endvidere udformet således, at den på begge sider af 10 indføringsstedet for den anden ventilboring 16 har to ventilsæder 26 og 28, mellem hvilke der befinder sig en afstandsholder 30. Denne har en totallængde, der svarer til afstanden mellem de to ventilsæder 26 og 28. Dens længde kan imidlertid også være noget større eller eventuelt mindre end denne afstand.3 12, in which is incorporated a longitudinal first valve bore 14 which is approximately cut in its center by a second valve bore 16. At the ends of the first valve bore 14, two pressure lines 18 referred to as second and third conduit 5 are connected. 20, and the second valve bore 16 is connected at the end, away from the first valve bore 14, via a first conduit or an outlet conduit 22 to a consuming site 24. The first valve bore 14 is further configured such that 10, the insertion point of the second valve bore 16 has two valve seats 26 and 28 between which is a spacer 30. This has a total length corresponding to the distance between the two valve seats 26 and 28. However, its length may also be somewhat larger or possibly less than this distance.
15 Det skal dog være sikret, at de lukkeelementer, der lukker ventilsæderne, ikke samtidigt lukker begge ventilsæder. Afstandsholderen 30 er selv udformet af en langsgående cylinderdel 32, der på sin periferiflade har radialdele 34. I detaljer findes der ved hver ende af cylinderdelen 32 tre radialdele 34, der 20 har samme indbyrdes periferiafstand, og som strækker sig parallelt med cylinderdelens langsgående midterakse og er udformet som vinger med parallelle sideflader. Radialdelene 34 ved den ene ende af cylinderdelen 32 er rettet ind med dem ved cylinderdelens anden ende, og deres længde er sådan, at de slutter 25 før cylinderdelens 32 midte i længderetningen. Højden af radi aldelene 34 er valgt således, at afstandsholderen netop kan forskydes i den første ventilboring 14. Derved er afstandsholderen 30 tilpasset til den første ventilboring 14, og en kantning i den første ventilboring 14 bliver undgået, hvorved 30 der mellem ved siden af hinanden liggende radialdele 34 for bliver et tilstrækkeligt frirum til gennemstrømning af væske. Desuden er der ved de udvendigt liggende ender af radialdelene 34 indarbejdet yderligere udsparinger 35, så at radialdelene 34 i deres endeområde har en ringere højde end i det øvrige 35 område, hvorved det forhindres, at der i området ved ventil-15 However, it must be ensured that the closing elements closing the valve seats do not simultaneously close both valve seats. The spacer 30 is itself formed by a longitudinal barrel portion 32 having on its peripheral surface radial portions 34. In detail, at each end of the barrel portion 32, there are three radial portions 34, which have the same circumferential spacing, which extend parallel to the longitudinal center axis of the barrel portion and is designed as wings with parallel side surfaces. The radial members 34 at one end of the cylinder part 32 are aligned with those at the other end of the cylinder part, and their length is such that they end 25 before the middle portion of the cylinder part 32 in the longitudinal direction. The height of the radius members 34 is selected such that the spacer can be precisely displaced in the first valve bore 14. Thus, the spacer 30 is adapted to the first valve bore 14, and an edge in the first valve bore 14 is avoided, whereby 30 between each other lying radial portions 34 to become a sufficient clearance for flow of liquid. In addition, at the outer ends of the radial members 34, additional recesses 35 are incorporated so that the radial members 34 have a lower height in their end region than in the other 35 region, thereby preventing the
DK 155895 BDK 155895 B
4 sæderne 26 og 28 opstår sliberiller eller en gratdannelse, som ville skade en driftssikker lukning af lukkeelementerne. Lukkeelementerne er ved udførelseseksemplet udformet som ventilkugler 36 og 38. Hertil kommer, at som følge af udsparingerne 5 har radialdelene 34 i området ved ventilsæderne i styreindsatsen en afstand til den første ventilboring 14, dvs. at de dér ikke berører dens indervæg. Da de i fig. 2 gengivne radial-dele 34 kun findes på ydersiden af cylinderdelen 32, påvirker de ikke gennemstrømningen af under tryk stående væske mellem 10 den første og den anden ventilboring 14 og 16.4, the seats 26 and 28 produce abrasive grooves or a grating which would damage the reliable closing of the closing elements. In the exemplary embodiment, the closing elements are formed as valve balls 36 and 38. In addition, as a result of the recesses 5, the radial parts 34 in the region of the valve seats in the guide insert have a distance from the first valve bore 14, ie. that they do not touch its inner wall there. Since in FIG. 2 shown radial portions 34 are present only on the outside of cylinder portion 32, they do not affect the flow of pressurized fluid between the first and second valve bores 14 and 16.
De i fig. 3 og 4 viste afstandsholdere har den samme fordelagtige virkning som den ifølge fig. 2. Den i fig. 3 viste afstandsholder 30' er ligeledes forsynet med en cylinderdel 15 32', der i forhold til den i fig. 2 viste har den forskel, at den har kugleformede endeflader. Radialdelene 34' er ikke udformet som vinger, men som flere på periferifladen fordelte radialt udstående stifter, som er anbragt således, at afstandsholderen 30' i indsatsen er rettet ind i forhold til den langs- 20 gående midterakse i den første ventilboring 14.The 3 and 4 have the same advantageous effect as that of FIG. 2. The embodiment of FIG. 3, spacer 30 'is also provided with a cylinder portion 32' which, in relation to that of FIG. 2 has the difference that it has spherical end faces. The radial members 34 'are not shaped as blades, but as a plurality of radially projecting pins distributed on the peripheral surface, arranged so that the spacer 30' in the insert is aligned with the longitudinal center axis of the first valve bore 14.
Afstandsholderen 30'' ifølge fig. 4 svarer i hovedsagen til afstandsholderen ifølge fig. 2 med den forskel, at der er anbragt otte raialdele 34'' med udsparinger 35'' på cylinder-25 delen 32''.The spacer 30 '' according to FIG. 4 corresponds substantially to the spacer of FIG. 2, with the difference that eight spacer parts 34 '' with recesses 35 '' are arranged on the cylinder 25 part 32 ''.
Ved de i figurerne 2 og 4 viste afstandsholdere 30 henholdsvis 30'' har cylinderdelene 32 henholdsvis 32'1 plane , altså ikke kugleformede endeflader, medens cylinderdelen 32' ved 3 0 den i fig. 3 viste afstandsholder 30' har kugleformede endeflader.At the spacers 30 and 30 'shown in FIGS. 2 and 4, the cylinder portions 32 and 32'1, respectively, have planar, ie non-spherical end faces, while the cylinder portion 32' at 30, as shown in FIG. 3, spacer 30 'has spherical end faces.
De i det ovenstående beskrevne udførelsesformer for de enkelte afstandsholdere kan kombineres med hinanden.The embodiments of the individual spacers described above can be combined with each other.
Ventilkuglerne 36 og 38 ligger an mod de over for hinanden liggende sider af afstandsholderne 30,30' eller 30'r og bliver 35The valve balls 36 and 38 abut the opposite sides of the spacers 30,30 'or 30s and become 35
DK 155895 BDK 155895 B
5 ved hjælp af en første og en anden fjeder 40 og 42 trykket i retning hen imod deres ventilsæder 26 og 28. I den forbindelse ligger de yderste ender af fjedrene 40 og 42 an imod inderflader 44 og 46 af propper 48 og 50. Sidstnævnte kan 5 være indskruet i ventilhuset 12 i den første ventilboring 14, så at indsætningen og i givet fald udskiftningen af afstandsholderne, ventilkuglerne og fjedrene let kan gennemføres.5 by means of a first and a second spring 40 and 42 pressed in the direction towards their valve seats 26 and 28. In this connection, the outer ends of the springs 40 and 42 abut against inner surfaces 44 and 46 of plugs 48 and 50. The latter can 5 can be screwed into the valve housing 12 in the first valve bore 14 so that the insertion and, where appropriate, the replacement of the spacers, valve balls and springs can be easily carried out.
Pjederkraften i den første fjeder 40 er noget større end hos 10 den anden fjeder 42. Derved bliver ventilkuglen 36 trykket mod sit ventilsæde 26, så længe der i trykledningerne 18 og 20 hersker samme trykforhold. Som det fremgår af fig. 1, har fjederen 40 en større udvendig diameter end fjederen 42 ved samme afspændte fjederlængde, hvorved der skal henvises til 15 de forskellige fjederkræfter. Når nu ventilkuglen 36 ligger an imod sit ventilsæde 26, har afstandsholderen 30,30* eller 30'' løftet ventilkuglen 38 fra dens ventilsæde 28. Derved kan væske komme ud af trykledningen 20 omkring ventilkuglen 38 og afstandsholderen gennem den anden ventilboring 16 og 20 udgangsledningen 22 ud til forbrugsstedet 24. Udligningsventilen 10 bliver holdt fast i denne stilling, indtil væsketrykket i trykledningen 20 bliver større end det i trykledningen 18 og sammen med fjederen 42 er i stand til at løfte ventilkuglen 36 fra dens ventilsæde 26. Så bliver ventilkuglen 38 i forhold 25 til fig. 1 bevæget mod venstre i retning mod dens ventilsæde 28, som den i givet fald helt lukker, og samtidigt bliver ventilkuglen 36 ved hjælp af afstandsholderen 30,30' eller 30'' løftet fra sit ventilsæde 26. Det tidsrum, der er nødvendigt til at sætte ventilkuglen 38 på dens ventilsæde 28 og 30 til at løfte ventilkuglen 36 fra dens ventilsæde 26, udgør kun en brøkdel af et sekund. I dette tidsrum består der en væskeforbindelse mellem trykledningen 18 og 20, dog er en eventuel væskestrøm da så ringe, at funktionen på forbrugsstedet 24 ikke bliver påvirket deraf, eller hvis den overhovedet 35 bliver det, da kun i yderst ringe grad.The spring force in the first spring 40 is somewhat greater than in the second spring 42. Thereby the valve ball 36 is pressed against its valve seat 26, as long as the same pressure ratio prevails in the pressure lines 18 and 20. As shown in FIG. 1, the spring 40 has a larger external diameter than the spring 42 at the same tensioned spring length, whereby reference is made to the different spring forces. Now that the valve ball 36 is in contact with its valve seat 26, the spacer 30,30 * or 30 '' has lifted the valve ball 38 from its valve seat 28. This allows fluid to come out of the pressure line 20 around the valve ball 38 and the spacer through the second valve bore 16 and 20 the outlet line. 22 to the point of consumption 24. The compensating valve 10 is held in this position until the fluid pressure in the pressure line 20 becomes greater than that in the pressure line 18 and together with the spring 42 is able to lift the valve ball 36 from its valve seat 26. Then the valve ball 38 is 25 to FIG. 1 is moved to the left in the direction towards its valve seat 28, which it completely closes, and at the same time the valve ball 36 is lifted from its valve seat 26. by means of the spacer 30,30 'or 30'. placing the valve ball 38 on its valve seat 28 and 30 to lift the valve ball 36 from its valve seat 26 constitutes only a fraction of a second. During this time there is a fluid connection between the pressure line 18 and 20, however, any liquid flow is so low that the function at the consumption point 24 is not affected by it, or if at all it becomes 35, then only to a very small extent.
Det tryk, der er nødvendigt til at forskyde ventilkuglen 38The pressure needed to displace the valve ball 38
Claims (2)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US44688282A | 1982-12-06 | 1982-12-06 | |
| US44688282 | 1982-12-06 |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK561783D0 DK561783D0 (en) | 1983-12-06 |
| DK561783A DK561783A (en) | 1984-06-07 |
| DK155895B true DK155895B (en) | 1989-05-29 |
| DK155895C DK155895C (en) | 1989-10-30 |
Family
ID=23774175
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK561783A DK155895C (en) | 1982-12-06 | 1983-12-06 | COMPENSATION VALVE |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP0110289B1 (en) |
| JP (1) | JPS59113377A (en) |
| AT (1) | ATE20131T1 (en) |
| AU (1) | AU2154083A (en) |
| BR (1) | BR8306683A (en) |
| DE (1) | DE3363816D1 (en) |
| DK (1) | DK155895C (en) |
| ES (1) | ES527783A0 (en) |
| ZA (1) | ZA839000B (en) |
Families Citing this family (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5190356A (en) * | 1988-07-01 | 1993-03-02 | Wabco Automotive U.K. Limited | AND-type control valve for a tractor-trailer braking system |
| GB8815703D0 (en) * | 1988-07-01 | 1988-08-10 | Dewandre Co Ltd C | Type control valve |
| FR2705403B1 (en) * | 1993-05-14 | 1995-06-23 | Renault | Pressure limiting device in an engine lubrication circuit. |
| KR100337635B1 (en) * | 2000-04-20 | 2002-05-24 | 밍 루 | Anti-lock brake system for vehicle |
| US8869824B2 (en) | 2007-08-30 | 2014-10-28 | Perlick Corporation | Check valve and shut-off reset device for liquid delivery systems |
| US7913714B2 (en) | 2007-08-30 | 2011-03-29 | Perlick Corporation | Check valve and shut-off reset device for liquid delivery systems |
| EP2714183A2 (en) * | 2011-05-24 | 2014-04-09 | Sanofi-Aventis Deutschland GmbH | Check valve arrangement |
| WO2014090268A1 (en) | 2012-12-10 | 2014-06-19 | Abb Technology Ltd | Valve arrangement |
| CN104295769B (en) * | 2014-10-17 | 2016-06-15 | 宁波凯波集团有限公司 | Draw water switching valve, multiple flow passages of multiple flow passages draws water Combination conversion valve and multidirectional water supply installation |
| JP6456155B2 (en) * | 2015-01-19 | 2019-01-23 | 日本電産トーソク株式会社 | Spool switching valve device |
| CN107631057B (en) * | 2017-10-30 | 2024-08-13 | 海南甘霖农业科技发展有限公司 | Pressure induction automatic reversing device |
| PL71873Y1 (en) * | 2018-01-24 | 2021-04-06 | Politechnika Rzeszowska Im Ignacego Lukasiewicza | Element that synchronizes operation of two actuators |
| CN109373012B (en) * | 2018-12-03 | 2023-09-15 | 四川理工学院 | Micro-flow equal-flow diverter valve |
| CN111946868B (en) * | 2020-08-04 | 2022-08-02 | 安徽斯瑞尔阀门有限公司 | Oil delivery valve with oil distribution structure and machining process thereof |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1409116A (en) * | 1916-08-08 | 1922-03-07 | Fire Gun Mfg Company Inc | Valve |
| US2774369A (en) * | 1955-03-18 | 1956-12-18 | Ross Operating Valve Co | Valve |
| DE1224577B (en) * | 1963-12-17 | 1966-09-08 | Teves Kg Alfred | Automatic, pressure-dependent accumulator shut-off valve for hydraulic systems |
| FR2081122A1 (en) * | 1970-03-06 | 1971-12-03 | Wallach Oscar | |
| JPS52133128A (en) * | 1976-04-30 | 1977-11-08 | Borisobuichi Sosuruniko Gurubu | Valve |
-
1983
- 1983-11-21 AU AU21540/83A patent/AU2154083A/en not_active Abandoned
- 1983-11-22 AT AT83111637T patent/ATE20131T1/en not_active IP Right Cessation
- 1983-11-22 EP EP83111637A patent/EP0110289B1/en not_active Expired
- 1983-11-22 DE DE8383111637T patent/DE3363816D1/en not_active Expired
- 1983-12-02 ZA ZA839000A patent/ZA839000B/en unknown
- 1983-12-05 ES ES527783A patent/ES527783A0/en active Granted
- 1983-12-05 BR BR8306683A patent/BR8306683A/en unknown
- 1983-12-06 DK DK561783A patent/DK155895C/en not_active IP Right Cessation
- 1983-12-06 JP JP58230490A patent/JPS59113377A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| EP0110289A1 (en) | 1984-06-13 |
| ES8501095A1 (en) | 1984-11-01 |
| BR8306683A (en) | 1984-07-17 |
| DK561783D0 (en) | 1983-12-06 |
| DK155895C (en) | 1989-10-30 |
| DE3363816D1 (en) | 1986-07-03 |
| ZA839000B (en) | 1985-07-31 |
| AU2154083A (en) | 1984-06-14 |
| JPS59113377A (en) | 1984-06-30 |
| ATE20131T1 (en) | 1986-06-15 |
| ES527783A0 (en) | 1984-11-01 |
| EP0110289B1 (en) | 1986-05-28 |
| DK561783A (en) | 1984-06-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |