DK157096B - TURNING VALVE - Google Patents
TURNING VALVE Download PDFInfo
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- DK157096B DK157096B DK149085A DK149085A DK157096B DK 157096 B DK157096 B DK 157096B DK 149085 A DK149085 A DK 149085A DK 149085 A DK149085 A DK 149085A DK 157096 B DK157096 B DK 157096B
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- DK
- Denmark
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- slider
- piston
- valve
- passage
- channel
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Classifications
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- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
- F15B11/15—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor with special provision for automatic return
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Multiple-Way Valves (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
- Fluid-Driven Valves (AREA)
- Actuator (AREA)
Description
DK 157096 BDK 157096 B
Den foreliggende opfindelse angâr en vendeventil ind-rettet til at pâvirke en hydraulisk arbejdscylinder, dreje-raotor eller anden hydraulisk motor til omkobling af denne, ekseinpelvis raed den hensigt at dreje en til arbejdscylinde-5 ren etc. koblet vendeplov, hvilken vendeventil er af den type, soin er anf0rt i indledningen til krav 1.The present invention relates to a reversing valve adapted to actuate a hydraulic working cylinder, rotary rotor or other hydraulic motor for switching thereto, for example it is intended to rotate a reversing plow connected to the working cylinder etc. type, soin is stated in the preamble of claim 1.
Sâdanne vendeventiler tjener blandt andet til at bringe en arbejdscylinder til at udf0re et arbejdsslag frem og tilbage, fx med den hensigt at vende et tilkoblet arbejds-10 redskab, fx en vendeplov. Dersom man tager udgangspunkt i en arbejdscylinder raed stempel i den inderste endestilling, skal vendeventilen s0rge for at styre stemplet, sâledes at det skydes ud til ydre stilling for derefter at koble om, sâledes at stemplet gâr tilbage til indre endestilling og 15 stopper. Uanset hvilken endestilling stemplet indtager i cylinderen ved start, skal vendeventilen styre stemplet sâledes, at det udf0rer et arbejdsslag frem og tilbage for derefter at stoppe i udgangsstillingen. Ventilen fâr da he-le tiden tilf0rt olie til et og samme 10b.Such reversing valves serve, inter alia, to cause a working cylinder to perform a working stroke back and forth, for example, with the intention of reversing a connected working tool, for example a reversing plow. If starting from a working cylinder with a piston in the inner end position, the reversing valve must make sure to control the piston so that it is pushed out to the outer position and then switched, so that the piston returns to the inner end position and stops. Regardless of which end position the piston occupies in the cylinder at start-up, the reversing valve must control the piston so that it performs a working stroke back and forth and then stops in its initial position. The valve will then be fed oil to the same 10b all the time.
20 De mest almindelige vendeventiler af denne art er trykstyrede, dvs. at de vil koble om, nâr olietrykket nâr op til en forudindstillet værdi. Trykstyringen medf0rer, at man mâ reservere en del af det tilgængelige arbejdstryk til styring af ventilen, hvilket mâ betragtes som et direk-25 te tab. Har man fx til râdighed et olietryk pâ 150 bar, er det ikke usædvanligt at reservere ca. 30 bar til styring af vendeventilen, og regner man med str0mningstabene i ventilen vil man ofte ikke hâve mere end 100 - 110 bar tilbage til at udf0re arbejdsslaget med. Skal vendeventilen be-30 nyttes til at pâvirke og omkoble en arbejdscylinder, som tjener til at dreje en vendeplov, vil man hâve et toppunkt, som kan være vanskeligt at komme over, især hvis traktoren stâr lidt skævt. Hvis der i et sâdant tilfælde bruges en trykstyret vendeventil, vil den ikke koble over f0r olie-35 trykket er steget til den forudindstillede værdi. Bevægel-sen mâ da n0dvendigvis stoppe op et 0jeblik.The most common reversing valves of this type are pressure controlled, ie. that they will switch when the oil pressure reaches a preset value. The pressure control means that a portion of the available working pressure must be reserved for controlling the valve, which must be regarded as a direct loss. For example, if an oil pressure of 150 bar is available, it is not unusual to reserve approx. 30 bar to control the reversing valve, and if the flow losses in the valve are calculated, you will often have no more than 100 - 110 bar left to carry out the work stroke. If the reversing valve is to be used to actuate and reverse a working cylinder which serves to rotate a reversing plow, a peak will be raised which can be difficult to get over, especially if the tractor is slightly skewed. If, in such a case, a pressure controlled reversing valve is used, it will not switch over until the oil pressure has risen to the preset value. The movement must then stop for a moment.
Formâlet med den foreliggende opfindelse er at af-hiælpe ulemoerne ved de kendte trvkstvrede vendeventiler.The object of the present invention is to alleviate the disadvantages of the known pressure-driven reversing valves.
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22
Der er herunder taget sigte pâ at komme frem til en vendeventil, som foruden at være enklere i konstruktionen end de hidtil kendte trykstyrede ventiler, skal kunne reagere smidigere og hurtigere end disse. Vendeventilen if0lge op-5 findelsen er i modsætning til kendte ventiler til tilsvaren-de formâl ikke afhængig af, at der oparbejdes et h0jt olie-tryk for at bringe glideren til at skifte stilling.The aim is, below, to arrive at a reversing valve, which, in addition to being simpler in construction than the previously known pressure controlled valves, must be able to react more smoothly and faster than these. The reversing valve according to the invention, in contrast to known valves for the corresponding purpose, does not depend on a high oil pressure being worked up to cause the slider to change position.
Disse og andre formâl er if0lge opfindelsen opnâet ved at vendeventilen er udformet og indrettet i overens-10 stemmelse med den kendetegnende del af krav 1. I modsætning til de kendte, trykstyrede ventiler, som er afhængige af et betydeligt olietryk for at fungere, er ventilen if0lge opfindelsen str0mningsstyret og kun afhængigt af et lille tryk-fald (2-3 bar) henover sædet i gliderens gennemgâende ka-15 nal for at holde glideren i den ene endestilling. Man kan derfor udnytte et tilgængeligt arbejdstryk maksimalt. Ventilen if0lge opfindelsen beh0ver heller ikke at blive indstil-let til et bestemt arbejdstryk, idet den vil fungere lige godt uanset trykket helt op til det maksimaltryk, den er kon-20 strueret til.These and other objects of the invention are achieved in that the reversing valve is designed and arranged in accordance with the characterizing part of claim 1. In contrast to the known pressure controlled valves which rely on a considerable oil pressure to operate, the valve is According to the invention, flow controlled and only depending on a small pressure drop (2-3 bar) across the seat in the slider's continuous channel to keep the slider in one end position. Therefore, an available working pressure can be maximized. The valve according to the invention also does not need to be adjusted to a particular working pressure, since it will function equally well regardless of the pressure up to the maximum pressure for which it is designed.
I underkravene er der angivet fordelagtige udf0relses-former, som repræsenterer videreudviklinger af den i krav 1 angivne opfindelse.In the subclaims there are advantageous embodiments which represent further developments of the invention as claimed in claim 1.
Opfindelsen beskrives nærmere i det efterf0lgende i 25 tilknytning til et udf0relseseksempel pâ opfindelsen og med henvisning til tegningerne, hvor fig. 1 viser et aksialsnit gennem en vendeventil if 01-ge opfindelsen i forbindelse med en hydraulisk arbejdscylin-der, 30 fig. 2 viser et udsnit af fig. 1 i st0rre mâlestok, fig. 3 og 4 viser aksialsnit svarende til fig. 1, men uden arbejdscylinder og med vendeventilens glider/stempel i fra fig. 1 afvigende stillinger.The invention will now be described in more detail below with reference to an embodiment of the invention and with reference to the drawings, in which: FIG. 1 shows an axial section through a reversing valve according to the invention in connection with a hydraulic working cylinder; FIG. 2 shows a section of FIG. 1 in a larger scale, FIG. 3 and 4 show axial sections corresponding to FIG. 1, but without a working cylinder and with the slider / piston of the reversing valve in FIG. 1 dissenting positions.
Den pâ tegningen viste vendeventil, som er indrettet 35 til at pâvirke fx en hydraulisk arbejdscylinder 26 til om-kobling af denne, eksempelvis med henblik pâ at dreje en tilkoblet vendeplov (ikke vist), omfatter en gliderventil- 3The reversing valve shown in the drawing, which is arranged to act, for example, on a hydraulic working cylinder 26 for switching it, for example for turning a coupled reversing plow (not shown), comprises a sliding valve 3.
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blok 1, soin er udformet med et indvendigt kanalsystem, hvori der indgâr særskilte kanaler 18,20,2,17,21 til tilkobling af et trykfluidumreservoir T og en pumpe P, henholdsvis til-f0rsels-/returledninger A,B til arbejdscylinderen. Glideren 5 3 har en gennemgâende kanal 4,4', hvori der er anbragt et ventillegeme, fx i form af en fjederbelastet 10 kugle 6, soin samvirker med et sæde 7 udformet i den gennemgâende kanal 4,4'. Glideren er endvidere udformet med kanaler 5,9 og spor 22,23 langs den ydre omkreds, beregnet til at sam-10 virke vekselvis med ventilblokkens 1 kanaler i gliderens 3 to endestillinger.block 1, soin is configured with an internal duct system comprising separate ducts 18,20,2,17,21 for connecting a pressurized fluid reservoir T and pump P, respectively, supply / return lines A, B to the working cylinder. The slide 5 3 has a through passage 4,4 'in which is arranged a valve body, for example in the form of a spring loaded 10 ball 6, which cooperates with a seat 7 formed in the through passage 4,4'. The slide is further provided with channels 5.9 and grooves 22.23 along the outer circumference, designed to interact alternately with the channels of the valve block 1 in the two end positions of the slide 3.
Arbejdscylinderens 26 stempel er betegnet med hen-visningstallet 27 og stempelstangen med 28, stempelstangs-enden med 30 og cylinderen svingningspunkt med 29. Arbejds-15 cylinderens 26 længdeakse er med indskudt stempel i den vi~ ste udgangsstilling betegnet med a^, ved udskudt stempel med a2 og ved omkoblet stilling med indskudt stempel med a^. Længdeaksens stillinger er antydet med stiplede linier. Stempelstangsenden 30 er ledforbundet med en styrestang 20 31, med fast omdrejningspunkt 32, hvilken styrestang er indrettet til at ligge an mod et af to anslag 33,34 i cy-lxnderens 26 to endestillinger (med indskudt stempel 27). Stempelstangsenden 30 er pâ ikke vist mâde. forbundet med fx en vendeplov, der tjener til at dreje denne.The piston of the working cylinder 26 is designated by reference numeral 27 and the piston rod by 28, the piston rod end by 30 and the cylinder pivot point by 29. The longitudinal axis of the working cylinder 26 is with the inserted piston in the first starting position denoted by a with a2 and at switched position with inserted piston with a ^. The longitudinal axis positions are indicated by dotted lines. The piston rod end 30 is articulated with a guide rod 20 31, with fixed pivot point 32, which guide rod is arranged to abut one of two stops 33,34 in the two end positions of the cylinder 26 (with inserted piston 27). Piston rod end 30 is not shown in the manner. associated with, for example, a reversing plow that serves to rotate it.
25 Ventilblokken 1 er begrænset med stiplede linier. En trykkanal 2 stâr i forbindelse med glideren 3 via et kanal-afsnit 25 med stprre tværsnitsareal end trykkanalen 2, men mindre end den kanal 25', hvori glideren 3 er anbragt forskydeligt. Gliderens 3 gennemgâende boring eller kanal 30 bestâr i udf^relseseksemplet af to partier 4,4' med indbyr-des noget afvigende diameter til dannelse af et ventilsæde 7 for et ventillegeme i form af en fjederbelastet 10 kugle 6. Sædet 7 er if0lge fig. 2 udformet med to symmetrisk pla-cerede spor 8, sâledes at kuglen 6 ikke kan tætne helt mod 35 sædet 7. Fra gliderens 3 gennemgâende kanal 4,4' f0rer ud-adrettede, radiale kanaler 5,9, som udmunder ved gliderens ydre omkreds. Kuglens 6 trykfjeder 10 hviler ved den modsat-The valve block 1 is restricted by dotted lines. A pressure channel 2 communicates with the slide 3 via a channel section 25 with a larger cross-sectional area than the pressure channel 2, but smaller than the channel 25 'in which the slide 3 is slidably disposed. The through bore or channel 30 of the slider 3 consists in the embodiment of two portions 4,4 'of slightly different diameter to form a valve seat 7 for a valve body in the form of a spring-loaded 10 ball 6. The seat 7 is according to FIG. 2, formed with two symmetrically positioned grooves 8, so that the ball 6 cannot fully close to the seat 7. From the passage 4,4 'of the slider 3, radial channels 5,9 extend which open at the outer circumference of the slider . The pressure spring 10 of the ball 6 rests at the opposite
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4 te ende mod en lâsering 11, som er indsat i et tværgâende omkredsspor i glideren 3. Pâ modsat side af lâseringen 11 ligger en anden fjeder 12 an, som i modsat ende hviler mod et stempel 13 med en snæver, gennemgâende kanal 14, som 5 udmunder i et ringformet, skarpkantet endeparti 15. En fjeder 16; som er kraftigere end fjederen 12, holder stemp-let 13 i anlæg mod glideren 3.4 terminates against a locking ring 11 which is inserted in a transverse circumferential groove in the slide 3. On the opposite side of the locking ring 11 lies another spring 12 which rests at an opposite end against a piston 13 with a narrow, continuous channel 14 which 5 opens into an annular, sharp-edged end portion 15. A spring 16; which is more powerful than the spring 12 keeps the piston 13 in contact with the slide 3.
I ventilblokken 1 er der som nævnt boret kanaler fra gliderboringen 25'. En sâdan kanal 21 star if0lge fig. 1 i 10 forbindelse med ventilens A-l0b, medens en tilsvarende kanal 17 star i forbindelse med B-l0bet. André radiale kanaler 18 -20 i ventilblokken 1 star i forbindelse med ventilblokkens 1 tankudl0b T.In the valve block 1, as mentioned, channels are drilled from the slider bore 25 '. Such a channel 21 stars according to FIG. 1 in connection with the valve A-lobe, while a corresponding channel 17 is connected with the B-lobe. André radial ducts 18 -20 in the valve block 1 star in connection with the valve block 1 tank outlet T.
If0lge fig. 1 er A- og B-l0bet koblet til tilf0rsels-/ 15 returledningen pâ den hydrauliske arbejdscylinder 26, som imidlertid kan erstattes af en drejemotor eller en anden hy-draulisk motor. Vendeventilens funktion vil her blive forkla-ret i forbindelse med en hydraulisk arbejdscylinder ligesom det er illustreret.According to FIG. 1, the A and B circuits are connected to the supply / return line of the hydraulic working cylinder 26, which can, however, be replaced by a rotary or other hydraulic motor. The operation of the reversing valve will here be explained in connection with a hydraulic working cylinder just as illustrated.
20 _ I udgangsstillingen star if0lge fig. 1 cylinder og gli- der i sin ene hovedstilling, nemlig i 'h0jre” endestilling.20 _ In the starting position according to fig. 1 cylinder and slides in its one main position, namely in the 'right' end position.
Der tilf0res nu en oliestr0m under tryk gennem kanalen 2.An oil stream is now pressurized through the duct 2.
Olien str0mmer videre via kanalafsnittet 25 gennem glide-rens 3 kanal 4. Olien vil selvsagt str0mme den letteste vej, 25 dvs. gennem kanalen 4 over sædet 7, forbi kuglen 6 og videre gennem den gennemgâende kanal 14 i stemplet 13 og derfra via en radial kanal 18 i ventilbokken 1 til tanken T. Nâr oliestr0mmen passerer sædet 7 via sporene 8, vil kuglen 6 s0rge for, at der opstâr et forudbestemt trykfald, som til-30 nærmelsesvis vil være konstant inden for den kapacitetsram-me, ventilen er konstrueret til. Dette trykfald bevirker, at glideren 3 vil skifte stilling, sâledes at kanalen 9 i glideren 3 kommer i forbindelse med kanalen 21 i ventilblokken og dermed ogsâ med A-l0bet til arbejdscylinderen. Sam-35 tidig vil der opbygges et olietryk mellem stemplet 13 og glideren 3 pâ grund af kanalens 14 betydeligt mindre tvær-snitsareal i forhold til kanalen 4,4’ i glideren, sâledes 5The oil flows further through the channel section 25 through the channel 4 of the slider 3. The oil will of course flow the easiest way, ie. through the channel 4 over the seat 7, past the ball 6 and further through the through channel 14 in the piston 13 and thence via a radial channel 18 in the valve box 1 to the tank T. As the oil flow passes the seat 7 through the grooves 8, the ball 6 will ensure that a predetermined pressure drop occurs which will be approximately constant within the capacity frame for which the valve is designed. This pressure drop causes the slider 3 to change position so that the channel 9 of the slider 3 communicates with the channel 21 in the valve block and thus also with the A-loop of the working cylinder. At the same time, an oil pressure will build up between the piston 13 and the slider 3 due to the significantly smaller cross-sectional area of the channel 14 relative to the channel 4,4 'in the slider, thus 5
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at stemplets 13 kanal 14 virker soin en forsnævring. Dette olietryk er tilstrækkeligt h0jt til at stemplets 13 ende-parti 15 med kanalmundingen gâr til anlæg mod et dertil ud-forraet parti 24 pâ ventilblokken 1, sâledes at forbindelsen 5 for oliestr0mmen gennem kanalen 14 til tankl0bet 18 tætnes (fig. 3). Olietrykket vil da stige sâ meget, at stemplet 27 begynder at bevæge sig fremefter i arbejdscylinderen 26. Olien vil 10be fra stangsiden i cylinderen til B-l0bet gennem kanalen 17 og et cirkulært omkredsspor 22 i glideren 10 3, gennem kanalen 20 tilbage til tanken T. Sâlænge denne bevægelse foregâr, vil oliestr0mmen passere henover sædet 7 og opretholde det n0dvendige trykfald til at holde slæ-den i den stilling, som fig. 3 viser.that the channel 14 of the piston 13 acts so narrowly. This oil pressure is sufficiently high that the end portion 15 of the piston 13, with the channel orifice, abuts against an annular portion 24 of the valve block 1 so as to seal the connection 5 of the oil flow through the channel 14 to the tank 18 (Fig. 3). The oil pressure will then increase so much that the piston 27 begins to move forwardly in the working cylinder 26. The oil will 10be from the rod side in the cylinder to the B-loop through the channel 17 and a circular circumferential groove 22 in the slide 10 3, through the channel 20 back to the tank T During this movement, the oil flow will pass over the seat 7 and maintain the necessary pressure drop to hold the sled in the position shown in FIG. 3 shows.
Nâr arbejdsstemplet 27 i cylinderen 26 kommer til den 15 ydre endestilling, repræsenteret ved den stiplede cylinder-akse a^r vil oliestr0mmen forbi sædet 7 oph0re, og trykket vil udjævne sig ved hjælp af sporene 8, sâledes at glideren 3 kommer i ligevægt. Fjederen 12 vil da skyde glideren over mod den oprindelige stilling (fig. 1 og 4), men stemplet 20 13 vil fortsat indtage sin venstre endestilling (fig. 3 og 4) og tætne pâ grund af olietrykket mellem stemplet 13 og glideren 3. Denne gensidige stilling af glideren 3 og stemplet 13 er vist pâ fig. 4. Nâr glideren 3 skifter stilling, for0ges rumfanget mellem glideren 3 og stemplet 13. Den lil-25 le oliemængde, som kræves hertil, efterfyldes via sporene 8.When the working piston 27 in the cylinder 26 reaches the outer end position, represented by the dashed cylinder axis, the oil flow past the seat 7 will cease and the pressure will equalize by the grooves 8 so that the slider 3 is in equilibrium. The spring 12 will then slide the slider over to the original position (Figures 1 and 4), but the piston 20 13 will continue to take its left end position (Figures 3 and 4) and close due to the oil pressure between the piston 13 and the slider 3. This reciprocal position of the slider 3 and piston 13 is shown in FIG. 4. When the slider 3 changes position, the volume between the slider 3 and the piston 13 is increased. The small amount of oil required for this is replenished via the grooves 8.
Oliestr0mmen gâr nu gennem gliderens 3 kanal 5 og ventilblokkens 1 kanal 17 til B-l0bet til arbejdscylinderen 26, som derved kan fuldf0re arbejdsslaget (indskubning af 30 stemplet 27 - længdeaksestilling a^). Samtidig kan olien fra cylinderens 26 A-l0b str0mme gennem kanalen 21 i ventilblokken 1 videre gennem et andet cirkulært omkredsspor 23 i glideren og via kanalen 19 til tanken T.The oil flow now passes through the channel 5 of the slider 3 and the channel 17 of the valve block 1 to the B-loop of the working cylinder 26, which can thereby complete the working stroke (pushing in the piston 27 - longitudinal axis a). At the same time, the oil from the cylinder A-lobe of the cylinder 26 can flow through the channel 21 in the valve block 1 further through another circular circumferential groove 23 in the slider and via the channel 19 to the tank T.
Nâr stemplet 27 kommer til sin indre endestilling i 35 cylinderen 26, er det frem- og tilbagegâende arbejdsslag fuldf0rt. Et nyt arbejdsslag frem og tilbage vil ikke auto-matisk igangsættes, eftersom stemplets 13 endeparti 15 med kanalmundingen tætner mod ventilblokpartiet 24. Der vil 6As the piston 27 reaches its inner end position in the cylinder 26, the reciprocating work stroke is completed. A new working stroke back and forth will not start automatically, since the end portion 15 of the piston 13 with the channel mouth seals against the valve block portion 24. There will be 6
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under disse forhold ikke kunne opstâ nogen oliestr0mning henover sædet 7, hvilket er n0dvendigt for at opretholde et trykfald til forskydning af glideren 3. Stemplet 13 vil befinde sig i denne stilling, indtil olietrykket synker i 5 trykl0bet 2. Da vil fjederen 16 f0re stemplet 13 tilbage til udgangsstillingen (fig. 1), hvorved ventilen er klar til at styre et nyt arbejdsslag frem og tilbage i cylinderen 26, soin da fra a^-stillingen kommer tilbage til a^-stillingen if01ge fig. 1.under these conditions, no oil flow could occur across the seat 7, which is necessary to maintain a pressure drop for displacement of the slide 3. The piston 13 will be in this position until the oil pressure drops in the pressure run 2. Then the spring 16 will feed the piston 13. back to the initial position (Fig. 1), whereby the valve is ready to control a new working stroke back and forth in the cylinder 26, so that from the a ^ position returns to the a ^ position according to fig. First
10 Opfindelsen er ikke begrænset til den viste og i det forëgâende beskrevne udf0relsesform, men kan varieres, modi-ficeres og/eller kompletteres inden for rammerne af krav 1.The invention is not limited to the embodiment shown and described previously, but can be varied, modified and / or supplemented within the scope of claim 1.
Det er sâledes et essentielt træk if0lge opfindelsen, at der er oprettet en permanent passage ved sædet 7 forbi kuglen 6, 15 men en sâdan passage kan etableres ved samvirkende spor i sæde og kugle eller blot i kuglen 6, i stedet for at udforme sædet 7 med symmetrisk placerede spor 8. Pâ tegningens figurer er stemplet 13 placeret lige bagved glideren 3, hvilket er en fordelagtig udformning (patentkrav 2), men ikke 20 ubetinget en forudsætning for at opfindelsen skal virke ef-ter hensigten. Stemplet 13 kan sâledes være placeret i en kanal, hvor som helst i ventilblokken. Det er imidlertid en forudsætning herunder, at stemplet 13 stâr i forbindelse med de samme kanaler som vist i tegningens figurer. Desuden 25 kan vendeventilen if0lge opfindelsen kompletteres gennem indbygning af forskellige kendte ventiler, dersom der skul-le være behov for dette. Der kan eksempelvis indbygges en lâse- og/eller overtryksventil. Eftersom et sâdant tillægs-udstyr ikke har nogen indvirkning pâ selve vendeventilens 30 funktion, er dette ikke medtaget hverken pâ tegningsfigurer eller i beskrivelsen.According to the invention, it is an essential feature of the invention that a permanent passage at the seat 7 is past the ball 6, 15, but such a passage can be established by cooperating grooves in the seat and ball or simply in the ball 6, instead of forming the seat 7 with symmetrically positioned grooves 8. In the drawings, the plunger 13 is located directly behind the slide 3, which is an advantageous design (claim 2), but not necessarily a condition for the invention to work according to the intention. The piston 13 can thus be located in a duct anywhere in the valve block. However, it is a prerequisite that the plunger 13 is connected to the same channels as shown in the drawings. In addition, the reversing valve according to the invention can be supplemented by incorporation of various known valves if this is necessary. For example, a locking and / or overpressure valve can be fitted. Since such ancillary equipment has no effect on the operation of the reversing valve 30 itself, this is not included either in the drawing figures or in the description.
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Claims (4)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NO841452 | 1984-04-12 | ||
| NO841452A NO154239C (en) | 1984-04-12 | 1984-04-12 | TURNING VALVE. |
Publications (4)
| Publication Number | Publication Date |
|---|---|
| DK149085D0 DK149085D0 (en) | 1985-04-02 |
| DK149085A DK149085A (en) | 1985-10-13 |
| DK157096B true DK157096B (en) | 1989-11-06 |
| DK157096C DK157096C (en) | 1990-04-02 |
Family
ID=19887595
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK149085A DK157096C (en) | 1984-04-12 | 1985-04-02 | TURNING VALVE |
Country Status (8)
| Country | Link |
|---|---|
| DE (1) | DE3511252A1 (en) |
| DK (1) | DK157096C (en) |
| FI (1) | FI72785C (en) |
| FR (1) | FR2562965B1 (en) |
| GB (1) | GB2157400B (en) |
| NL (1) | NL8500933A (en) |
| NO (1) | NO154239C (en) |
| SE (1) | SE462176B (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2656386B1 (en) * | 1989-12-22 | 1992-04-30 | Matairco Hydro Air Sa | |
| DE4243343C2 (en) * | 1992-12-21 | 1994-09-29 | Weber Hydraulik Gmbh | Control device for pivoting a reversible plow |
| WO1998008012A1 (en) * | 1996-08-19 | 1998-02-26 | Australian Water Products Pty. Ltd. | Outlet pressure limiting valve |
| CN101900144B (en) * | 2010-07-22 | 2012-11-07 | 泸州众大科技液压件有限公司 | Small-sized drill pile-up valve |
| CN103791022B (en) * | 2014-01-22 | 2016-03-09 | 南通爱慕希机械有限公司 | A kind of piston Zeng Zu mechanism |
| CN105586847B (en) * | 2016-03-04 | 2018-04-20 | 武汉理工大学 | A kind of vacuum sweeper sucker road clearance automatic regulating apparatus |
| CN109306980A (en) * | 2018-11-06 | 2019-02-05 | 河南航天液压气动技术有限公司 | A kind of reversal valve |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH413605A (en) * | 1964-03-04 | 1966-05-15 | Ramax Ag Maschinen Und Apparat | Backflow pulse control arrangement on a hydraulic or pneumatic axial piston motor |
| DE2413531C3 (en) * | 1974-03-21 | 1980-03-06 | Wabco Fahrzeugbremsen Gmbh, 3000 Hannover | Pneumatically driven double-acting piston engine |
| GB2073564B (en) * | 1980-04-15 | 1983-06-08 | Thomas K H | Plough turn-over mechanism |
| US4341148A (en) * | 1980-09-30 | 1982-07-27 | Modular Controls Corporation | Hydraulic sequencing valve |
| DE3122594C2 (en) * | 1981-06-06 | 1984-02-23 | Integral Hydraulik & Co, 4000 Düsseldorf | Reversing device for a hydraulic turning device for agricultural implements |
| DE3212285A1 (en) * | 1982-04-02 | 1983-10-13 | Integral Hydraulik & Co, 4000 Düsseldorf | Reversing device for the automatic reversing of a piston-cylinder unit, in particular of a plough-turning cylinder |
| US4722262A (en) * | 1983-05-21 | 1988-02-02 | Massey-Ferguson Services N.V. | Fluid pressure system and value therefor |
-
1984
- 1984-04-12 NO NO841452A patent/NO154239C/en unknown
-
1985
- 1985-03-26 GB GB08507780A patent/GB2157400B/en not_active Expired
- 1985-03-28 FI FI851256A patent/FI72785C/en not_active IP Right Cessation
- 1985-03-28 DE DE19853511252 patent/DE3511252A1/en active Granted
- 1985-03-29 NL NL8500933A patent/NL8500933A/en not_active Application Discontinuation
- 1985-04-02 DK DK149085A patent/DK157096C/en not_active IP Right Cessation
- 1985-04-09 SE SE8501719A patent/SE462176B/en not_active IP Right Cessation
- 1985-04-11 FR FR8505488A patent/FR2562965B1/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| DK157096C (en) | 1990-04-02 |
| FI851256L (en) | 1985-10-13 |
| SE8501719D0 (en) | 1985-04-09 |
| DK149085A (en) | 1985-10-13 |
| NL8500933A (en) | 1985-11-01 |
| SE8501719L (en) | 1985-10-13 |
| DE3511252C2 (en) | 1990-09-27 |
| FR2562965B1 (en) | 1989-12-08 |
| DK149085D0 (en) | 1985-04-02 |
| NO841452L (en) | 1985-10-14 |
| GB8507780D0 (en) | 1985-05-01 |
| NO154239C (en) | 1986-08-13 |
| FI851256A0 (en) | 1985-03-28 |
| FR2562965A1 (en) | 1985-10-18 |
| SE462176B (en) | 1990-05-14 |
| FI72785B (en) | 1987-03-31 |
| GB2157400A (en) | 1985-10-23 |
| FI72785C (en) | 1987-07-10 |
| GB2157400B (en) | 1987-07-01 |
| DE3511252A1 (en) | 1985-10-24 |
| NO154239B (en) | 1986-05-05 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed | ||
| PBP | Patent lapsed |