DK155548B - DISTRIBUTED PRESSURE LIMIT VALVE - Google Patents
DISTRIBUTED PRESSURE LIMIT VALVE Download PDFInfo
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- DK155548B DK155548B DK18175A DK18175A DK155548B DK 155548 B DK155548 B DK 155548B DK 18175 A DK18175 A DK 18175A DK 18175 A DK18175 A DK 18175A DK 155548 B DK155548 B DK 155548B
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- pressure limiting
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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
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/10—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve
- F16K17/105—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with auxiliary valve for fluid operation of the main valve using choking or throttling means to control the fluid operation of the main valve
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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
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
- F16K31/36—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor
- F16K31/38—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor in which the fluid works directly on both sides of the fluid motor, one side being connected by means of a restricted passage and the motor being actuated by operating a discharge from that side
- F16K31/383—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor in which the fluid works directly on both sides of the fluid motor, one side being connected by means of a restricted passage and the motor being actuated by operating a discharge from that side the fluid acting on a piston
- F16K31/3835—Actuating devices; Operating means; Releasing devices actuated by fluid in which fluid from the circuit is constantly supplied to the fluid motor in which the fluid works directly on both sides of the fluid motor, one side being connected by means of a restricted passage and the motor being actuated by operating a discharge from that side the fluid acting on a piston the discharge being effected through the piston and being blockable by a mechanically-actuated member making contact with the piston
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Safety Valves (AREA)
Description
iin
DK 155548 BDK 155548 B
5 Opfindelsen angår en forstyret og i en strømningsretning åbnelig trykbegrænsningsventil med et forbindelsen mellem en tilgangs- og en afgangsforbindelse styrende og som et bæger udformet hovedlukkestykke, hvis forside i åbningsretningen er påvirkbar af tilgangs-10 trykket og hvis bagside over en drøvleboring er påvirkbar af nævnte tilgangstryk, idet den af en styrefjeder belastede forstyreventil er anbragt på en sådan måde, at dens styrefjeder belaster hovedlukke-stykket i dets lukkestilling i lukkeretningen.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a disturbed and open flow restrictive valve having a connection between an inlet and outlet connection guiding and as a cup shaped head closure, the face of which in the opening direction is actuated by the inlet pressure and whose rear over a throttle bore is actuated by said supply pressure, the control valve loaded by a control spring being arranged in such a way that its control spring stresses the main closure piece in its closing position in the closing direction.
15 I modsætning til direkte styrede ventiler sikrer trykbegrænsningsventiler med forstyring en virksom dæmpning og en lille strømafhængighed.15 Unlike directly controlled valves, pressure limiting valves with interference ensure effective damping and a small current dependence.
20 Der kendes forstyrede trykbegrænsningsventiler med et af en fjeder belastet ventilstempel og en forstyringsventil, der er belastet af en anden fjeder. En sådan trykbegrænsningsventil er for eksempel anvendt som strømreguleringsventil i en pumpe, der er beskre-25 vet i DE offentliggørelsesskrift nr. 1.553.290. I denne ventil kræves der, som nævnt, to fjedre til ventilstempel og til forstyringsventilen. På grund af en styrekanal, der ligger i huset, og som leder trykmedium fra ventilens tilgangsforbindelse til fjeder-30 rummet på bagsiden af ventilstemplet, kræves der forholdsvis stor plads til indbygning af en sådan trykbegrænsningsventil. Dette er en ulempe, fordi der til indbygning i pumper og andre hydrauliske aggregater i almindelighed kun er et meget begrænset indbygnings-20 Distressed pressure relief valves are known with a spring-loaded valve piston and a control valve loaded by another spring. Such a pressure limiting valve is, for example, used as a flow control valve in a pump described in DE Publication No. 1,553,290. In this valve, as mentioned, two springs are required for the valve piston and for the control valve. Due to a control channel located in the housing directing pressure medium from the valve access connection to the spring compartment at the rear of the valve piston, relatively large space is required for incorporating such a pressure limiting valve. This is a disadvantage because for installation in pumps and other hydraulic units there is generally only a very limited installation capacity.
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2 rum til disposition.2 rooms available.
Ved en anden trykbegrænsningsventil, der kendes fra DE offentliggørelsesskrift nr. 2.049.818, var formå-5 let at angive en overtryksventil af begrænset omfang.In another pressure relief valve known from DE Publication No. 2,049,818, it was possible to specify a limited pressure relief valve.
Derfor er forstyreventilen anbragt i en ventilbøsning i hovedstemplet i trykbegrænsningsventilen. En enkelt trykfjeder virker på forstyreventilens stempel og i ventilens lukkede stilling via ventilbøsningen også 10 mod hovedstemplet. Fjederen ligger derved i et lavtryksrum og må derfor udformes tilsvarende kraftig. Ventilbøsningen kan gennem det på højtrykssiden virksomme tryk bevæges bort fra hovedstemplet, så fjederen ikke mere er virksom i styringen af hovedstemp-15 let. Svingninger, der optræder i denne tilstand, for hindres gennem anvendelse af et yderligere dæmpningsstempel. Som følge af den i lavtryksrummet anbragte og derfor relativt store trykfjeder, der virker på forstyrestemplet, og den derfor nødvendige 20 ventilbøsning og dæmpningsstemplet kan heller ikke denne kendte ventil udføres i en for indbygning i hydraulikpumper nødvendig lille størrelse.Therefore, the control valve is located in a valve bush in the main piston of the pressure limiting valve. A single pressure spring acts on the piston of the control valve and in the closed position of the valve via the valve sleeve also 10 against the main piston. The spring is thereby located in a low pressure space and must therefore be designed similarly vigorously. The valve sleeve can be moved away from the main piston through the pressure acting on the high pressure side, so that the spring is no longer effective in the control of the main piston. Fluctuations occurring in this state are prevented by the use of a further damping piston. As a result of the low pressure chamber located in the low pressure chamber and therefore relatively large spring acting on the piston piston, and the therefore necessary valve bushing and the damping piston, this known valve cannot be made in a small size necessary for installation in hydraulic pumps.
Den foreliggende opfindelse tager sigte på at angive 25 en forstyret trykbegrænsningsventil af den nævnte art, som ikke kræver ret megen plads, og som er egnet til en let indbygning i hydrauliske pumper og hydrauliske anlæg, der kun har en lille indbygningsplads. 1SUMMARY OF THE INVENTION The present invention aims to provide a disturbed pressure relief valve of the kind which does not require much space and which is suitable for easy installation in hydraulic pumps and hydraulic systems having only a small installation space. 1
Denne opgave løses ved en forstyret trykbegrænsnings-ventil af den angivne art, hvilken trykbegrænsnings-ventil ifølge opfindelsen er særegen ved, at forsty-reventilens lukkestykke er udformet som en trinventil, hvis store endeflade er forbundet umiddelbartThis task is solved by a disturbed pressure limiting valve of the specified type, which pressure limiting valve according to the invention is peculiar in that the closing valve of the control valve is designed as a step valve whose large end surface is connected immediately
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3 med tilgangsforbindelsen og hvis lille endeflade via drøvleboringen ligeledes er forbundet med tilgangsforbindelsen, at forstyreventilens mellem den store og lille endeflade liggende differensflade er forbun-5 det med afgangsforbindelsen, og at forstyreventilens styrefjeder er anbragt i et af hovedlukkestykkets bagside begrænset trykrum.3 with the inlet connection and whose small end surface via the throttle bore is also connected to the inlet connection, that the differential valve lying between the large and small end surface is connected to the outlet connection and that the control spring of the control valve is placed in one of the back cover of the main closing piece.
Yderligere midler til fremme af løsningen af den 10 nævnte opgave fremgår af underkravene.Further means for promoting the solution of the said 10 task are set out in the subclaims.
Opfindelsen forklares nærmere under henvisning til tegningen, på hvilken 15 fig. 1 viser et længdesnit gennem en udførelses form for trykbegrænsningsventilen ifølge opfindelsen i snit, og fig. 2-8 viser hver sin udførelsesform for tryk-20 begrænsningsventilen, idet kun forstyre ventilen og de omgivende dele er vist i større målestok og i snit.The invention is further explained with reference to the drawing, in which FIG. 1 shows a longitudinal section through an embodiment of the pressure limiting valve according to the invention in section; and FIG. 2-8 show each embodiment of the pressure limiting valve, only the valve and the surrounding parts are shown on a larger scale and section.
På tegningen og i den efterfølgende beskrivelse er 25 dele i de enkelte udførelsesformer, der svarer til hinanden, forsynet med numre, der foran et fælles nummer har figurnummeret. Når der i en udførelsesform er dele, som ikke har noget særskilt nummer, betyder det, at de kan beskrives på ganske samme måde som 30 tilsvarende dele i tidligere udførelsesformer.In the drawing and in the following description, 25 parts in each corresponding embodiment are provided with numbers having a number in front of a common number. When in one embodiment there are parts which have no separate number, it means that they can be described in much the same way as 30 corresponding parts in previous embodiments.
Et ventilstempel 1, der virker som trykvægt, er aksi-alt forskydeligt i et hus 2. Huset 2 har en tilgangsforbindelse 4, der fører til den ene flade 3 på ven-A valve piston 1 acting as pressure weight is axially slidable in a housing 2. The housing 2 has an inlet connection 4 which leads to one surface 3 of the valve member.
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4 tilstemplet 1, og en afgangs forbindelse 5. En trykfjeder 6 er anbragt i et fjederrum, der vender bort fra stempelfladen 3. I ventilstemplet 1 er der anbragt en forstyringsventil 8 i form af en trinventil, 5 der er belastet af en trykfjeder 6 og har et trinstempel 9.4 is piston 1, and an outlet connection 5. A compression spring 6 is arranged in a spring compartment facing away from the piston surface 3. In the valve piston 1 there is arranged a control valve 8 in the form of a step valve 5, which is loaded by a pressure spring 6 and has a step stamp 9.
En drøvleboring 10, der ligger i trinstemplet 9, forbinder tilgangsforbindelsen 4 med fjederrummet 7, så 10 at der hersker samme tryk på ventilstemplet l's to lige store stempelflader og på de to forskelligt store stempelflader på trinstemplet 9. Den differensflade 11, der ligger mellem de to stempelflader på trinstemplet 9, er gennem en tværboring 12 i venti1-15 stemplet 1 forbundet med afgangsforbindelsen 5.A throttle bore 10 located in the step piston 9 connects the inlet connection 4 with the spring space 7 so that 10 the same pressure is applied to the two piston faces of the valve piston 1 and to the two different piston faces of the piston 9. The differential surface 11 which lies between the two piston surfaces on the step piston 9, are connected to the outlet connection 5 through a cross bore 12 in the valve piston 1.
I den i fig. 1 viste neutrale stilling af ventilen holdes trinstemplet 9 ved hjælp af trykfjederen 6 og dermed også ventilstemplet 1 i den viste endestil-20 ling. Hvis trykket i tilgangsforbindelsen 4 overstiger en bestemt størrelse, der er et resultat af størrelsen af kraften fra trykfjederen 6 og størrelsen af differensfladen 11, vil styrestemplet 9 blive forskudt til højre fra sin viste stilling, indtil fje-25 derrummet 7 gennem en på trinstemplet 9 anbragt styrekant 13 og tværboringen 12 bliver forbundet med afgangsforbindelsen 5. Trykket i fjederrummet 7 synker så, så at trykket på stempelfladen 3 af ventilstemplet 1 får overvægt, hvorved ventilstemplet 1 ligele-30 des bliver forskudt til højre mod kraften fra trykfjederen 6. Derved frembringes der en direkte forbindelse fra tilgangsforbindelsen 4 til afgangsforbindelsen 5.In the embodiment shown in FIG. 1 in the neutral position of the valve, the step piston 9 is held by the pressure spring 6 and thus also the valve piston 1 in the end position 20 shown. If the pressure in the inlet connection 4 exceeds a certain size resulting from the magnitude of the force of the compression spring 6 and the size of the differential surface 11, the guide plunger 9 will be displaced to the right from its shown position until the spring space 7 through an on the plunger 9. The guide edge 13 and the cross bore 12 are connected to the outlet connection 5. The pressure in the spring compartment 7 then decreases so that the pressure on the piston surface 3 of the valve piston 1 becomes overweight, and the valve piston 1 is also displaced to the right against the force of the compression spring 6. there is a direct connection from the access connection 4 to the exit connection 5.
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Ved den i fig. 2 viste udførelsesform for den principielle indretning i fig. 1 er trinstemplet 9 erstattet af et mere enkelt stempel 4 med en stiftlignende fortsættelse 15 og af en kugle 16 med et ventilsæde 5 17 i ventilstemplet 201. Disse dele i fig. 2 er let tere at fremstille og giver en bedre tætningsvirkning.In the embodiment shown in FIG. 2 of the principle device of FIG. 1, the step piston 9 is replaced by a simpler piston 4 with a pin-like extension 15 and by a ball 16 with a valve seat 5 17 in the valve piston 201. These parts of FIG. 2 is easy to manufacture and provides a better sealing effect.
Forstyreventilen 208 kommer til at virke som trinven-10 til ved, at tværsnitsfladen af stemplet 14 er større end tværsnitsfladen for vehtilsædet 17. Tværsnitsfladen af stemplet 14 svarer sltså til en større tværsnitsflade af trinventilen, medens tværsnitsfladen af ventilsædet 17 svarer til en mindre tværsnitsflade af 15 trinventilen. Kuglen 16 trykkes ved hjælp af en fjedertallerken 18 og en trykfjeder 206 mod ventilsædet 17 for ventilstemplet 201. En drøvleboring 210 forbinder tilgangsforbindelsen 4 med et fjederrum 207.The guide valve 208 acts as a step valve in that the cross-sectional surface of the piston 14 is larger than the cross-sectional surface of the vehicle seat 17. The cross-sectional surface of the piston 14 thus corresponds to a larger cross-sectional surface of the step valve, while the cross-sectional surface of the valve seat 17 corresponds to a smaller cross-sectional surface. 15 step valve. The ball 16 is pressed by means of a spring plate 18 and a pressure spring 206 against the valve seat 17 of the valve piston 201. A throttle bore 210 connects the access connection 4 to a spring space 207.
20 På grund af de store differenstryk og den lille tryk-mediumgennemstrømning ved ventilsædet 17 kræves der kun en meget lille vej for kuglen 16 og dermed også for stemplet 14 til påvirkning af forstyreventilen 208. Det er derfor muligt at opnå en aftætning af 25 stemplet 14 i boringen 19 for ventilstemplet 201 blot ved hjælp af en skive 20 af højviskost formstof. Denne skive 20 hindres ved en radial forspænding i at forskydes aksialt i boringen 19, så at trykket i tilgangsforbindelsen 4 uden friktionstab alene ved hjælp 30 af elasticiteten af skiven 20 overføres til stemplet 14 i forstyreventilen 208.Due to the large differential pressures and the small pressure medium flow at the valve seat 17, only a very small path is required for the ball 16 and thus also for the piston 14 for actuating the control valve 208. It is therefore possible to obtain a seal of the piston 14. in the bore 19 of the valve piston 201 simply by means of a disc 20 of high-viscosity plastic. This disc 20 is prevented by a radial bias from being displaced axially in the bore 19, so that the pressure in the inlet connection 4 without frictional loss is transmitted solely by means of the elasticity of the disc 20 to the piston 14 in the control valve 208.
I almindelighed er skiven 20 tilstrækkelig til at sikre stemplet 14 mod at falde ud af boringen 19 iIn general, washer 20 is sufficient to secure piston 14 against falling out of bore 19 in
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6 ventilstemplet 201. Hvis ventilen indbygges på en sådan måde, at en stigning af trykhøjden i afgangsforbindelsen ud over trykket i tilgangsforbindelsen 4 er mulig, kan skiven 20 sikres yderligere ved hjælp af 5 en støtteskive, der ikke er vist på tegningen, men for eksempel kan være indrullet i ventilstemplet.6 the valve piston 201. If the valve is built in such a way that an increase in the pressure height of the outlet connection in addition to the pressure in the access connection 4 is possible, the disc 20 can be further secured by means of a support disc not shown in the drawing, but for example may be rolled into the valve piston.
Aftætningen af boringen 19 ved hjælp af skiven 20 muliggør en god pastolerance mellem boringen 19 og 10 stemplet 14, så at man derved får en forenkling af fremstillingen.The sealing of the bore 19 by means of the disc 20 permits a good paste tolerance between the bore 19 and 10 the piston 14, thereby simplifying the production.
Da der på grund af anbringelsen af formstofskiven 20 i boringen 19 mangler en lækstrømning ved stemplet 15 14, bliver en hydraulisk sammenklemning forhindret.Since due to the placement of the plastic disc 20 in the bore 19 a leakage flow at the piston 15 14 is lacking, a hydraulic clamping is prevented.
Derved bliver reaktionsnøjagtigheden for forstyreventilen 208 forøget. Samtidig kan man undvære ekstra aflastningriller i stemplet 14.Thereby, the reaction accuracy of the control valve 208 is increased. At the same time, no additional relief grooves can be dispensed in the piston 14.
20 Hele trykbegrænsningsventilen anbringes hensigtsmæs sigt i en indskruningspatron 21. Denne indskrunings-patron kan indskrues i forskellige aggregater, uden at der kræves en nøjagtig bearbejdning af pasboringer i huset. Derved opnår man en let udskiftelighed af 25 ventilen.20 The entire pressure limiting valve is conveniently placed in a screw-in cartridge 21. This screw-in cartridge can be screwed into various assemblies without requiring precise machining of pass bores in the housing. This results in a slight interchangeability of the valve.
Ved den i fig. 3 viste udførelsesform for trykbegrænsning svent i len bliver forstyreventilen 208, som allerede beskrevet ovenfor, kun gennemstrømmet af en 30 meget lille trykmediumstrøm, der kun kræver en meget lille slaglængde for kuglen 16 og dermed en meget lille åbningsspalte mellem denne kugle og ventilsædet 17. På grund af sin lille størrelse virker spalten som et meget fint spaltfilter, der udfiltrerer småIn the embodiment shown in FIG. 3, the pressure valve 208, as already described above, is only flowed through a very small pressure medium flow which requires only a very small stroke of the ball 16 and thus a very small opening gap between this ball and the valve seat 17. On Due to its small size, the gap acts as a very fine gap filter that filters out small ones
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7 smudspartikler, som indeholdes i trykmediet. Disse smudspartikler kan afsætte sig på tætningskanten af ventilsædet 17 og føre til en utæthed i forstyreventilen og til et deraf følgende utilstrækkeligt luk-5 ketryk for ventilstemplet 201.7 dirt particles contained in the print medium. These dirt particles can settle on the sealing edge of valve seat 17 and lead to a leak in the control valve and to a consequent insufficient closure pressure for valve piston 201.
Mellem tilgangsforbindelsen 4 og drøvleboringen 310 er der derfor anbragt et filter 22, som er omsluttet af et rørstykke 23. Til opnåelse af en god filter-10 virkning anvendes et snævermasket filtermateriale.Therefore, between the inlet connection 4 and the throttle bore 310 is a filter 22, which is enclosed by a pipe piece 23. To obtain a good filter effect, a narrow mesh filter material is used.
Herved bevirkes der et forholdsvis stort trykfald, men dette er uden betydning, da der kun strømmer en lille trykmediumstrøm gennem drøvleboringen 310. Et sådant filter kan også anvendes ved andre udførelses-15 former end den i fig. 3 viste.This results in a relatively large pressure drop, but this is of no importance since only a small pressure medium flow flows through the throttle bore 310. Such a filter can also be used in other embodiments than the one in FIG. 3.
Til forskel fra udførelsesformen i fig. 2 er kuglen 16 i forstyreventilen 308 erstattet af en kegleventil 24. Ventilkeglen er mindre tilbøjelig til svingninger 20 end kuglen. En stiftformet fortsættelse 315 er forbundet med keglen 24. Derved bliver det muligt til stemplet 314 at anvende en seriefremstillet lagernål.Unlike the embodiment of FIG. 2, the ball 16 in the control valve 308 is replaced by a cone valve 24. The valve cone is less prone to oscillations 20 than the ball. A pin-shaped extension 315 is connected to the cone 24. This makes it possible for the piston 314 to use a series-made bearing needle.
Ved den i fig. 4 viste udførelsesform er et ventilsæ-25 de 417 i en kegleventil 424 dannet af en ring 25, som er indsættelig i et ventilstempel 401. Denne ring 25 begrænser en mindre tværsnitsflade af trinventilen i radial retning. Ved en todelt byggemåde for ventilsædet 417 i ventilstemplet 401 er det muligt at frem-30 stille ventilsædet meget nøjagtigt.In the embodiment shown in FIG. 4, a valve seat 25 in a cone valve 424 is formed by a ring 25 insertable into a valve piston 401. This ring 25 limits a smaller cross-sectional surface of the step valve in the radial direction. By a two-part construction method for valve seat 417 in valve piston 401, it is possible to produce the valve seat very accurately.
Ved den i fig. 5 viste udførelsesform er den større tværsnitsflade af trinventilen dannet af en sædeventil 524, medens den mindre tværsnitsflade er dannetIn the embodiment shown in FIG. 5, the larger cross-sectional surface of the step valve is formed by a seat valve 524, while the smaller cross-sectional surface is formed.
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8 af et stempel 514. Stemplet 514 er ført i en ring 525, der er anbragt i ventilstemplet 501. Drøvlebo-ringen 510 er anbragt i påstrømningsretningen foran forstyreventilen 508. En boring 26 forbinder de to 5 endeflader på forstyreventilen 508 med hinanden, så at der foran og efter forstyreventilen 508 hersker det samme drøvlede tryk. Sædeventilen 524 gennemstrømmes ved denne udførelsesform indefra og udefter.8 of a piston 514. The piston 514 is inserted into a ring 525 disposed in the valve piston 501. The throttle bore 510 is disposed in the flow direction in front of the control valve 508. A bore 26 connects the two 5 end faces of the control valve 508 with each other so that the same swirling pressure prevails before and after the control valve 508. In this embodiment, the seat valve 524 is flowed from the inside out.
Derved sikres en større driftssikkerhed ved et slid 10 på ventilsædet 517 og en deraf følgende forøgelse af den virksomme tværsnitsflade med faldende åbningstryk af forstyreventilen 508.Thereby, greater operational safety is ensured by a wear 10 on the valve seat 517 and a consequent increase in the effective cross-sectional surface with decreasing opening pressure of the control valve 508.
Den i fig. 6 viste udførelsesform er en forenkling af 15 udførelsesformen i fig. 5. Det i ét stykke udførte trinstempel med ventilsædet 524 og stemplet 514 i fig. 5 er i fig. 6 erstattet af en sædeventil 624 i form af en kugle og af et stempel 614 i form af en valse eller en lagernål. Stemplet 614 er ført i en 20 ring 625. Dr ø viebor ingen 610 er anbragt i en drøvle-kappe 27 foran forstyreventilen 608.The FIG. 6 is a simplification of the embodiment of FIG. 5. The one-piece step piston with valve seat 524 and piston 514 in FIG. 5 is in FIG. 6 is replaced by a seat valve 624 in the form of a ball and by a piston 614 in the form of a roller or a bearing needle. The piston 614 is inserted into a ring 625. Drill no 610 is disposed in a throttle cap 27 in front of the control valve 608.
Boringen 626 tjener samtidig som udligningsboring for lækolie ved stemplet 614 og ventilstemplet 601 og som 25 dæmpningsboring for ventilstemplet 601.The bore 626 simultaneously serves as a counterbalancing bore for leakage oil at piston 614 and valve piston 601 and as damping bore for valve piston 601.
I fjederrummet 607 er der anbragt en tilslutningsboring 28 til en ikke vist fjernstyringsmekanisme. En fjernstyring af trykbegrænsningsventilen, der er an-30 vendelig ved alle de viste udførelsesformer for ventilen, kan opnås ved, at fjederrummet 607 over fjernstyremekanismen, for eksempel en enkel omkoblingsventil, bliver forbundet med en ikke vist tryk-mediumbeholder.In the spring compartment 607 a connection bore 28 is provided for a remote control mechanism not shown. A remote control of the pressure limiting valve which is applicable to all of the illustrated embodiments of the valve can be achieved by the spring space 607 over the remote control mechanism, for example a simple switching valve, being connected to a pressure medium container not shown.
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En forstyreventil 708 i fig. 7 har et stempel hen-holsvis 714a og 714b på sin større og på sin mindre tværsnitsflade. En drøvleboring 710 er i drøvlekappen 727 anbragt foran forstyreventilen 708.A control valve 708 in FIG. 7 has a piston respectively 714a and 714b on its larger and smaller cross-sectional surface. A throttle bore 710 is located in the throttle cap 727 in front of the control valve 708.
5 I fig. 8 er en forstyreventil 808 anbragt i en ind-skruningspatron 821. En sådan indretning er principielt også mulig ved alle andre viste udførelsesformer.5 In FIG. 8, a control valve 808 is arranged in a screw-in cartridge 821. Such a device is in principle also possible in all other embodiments shown.
10 Ved de ovenfor beskrevne udførelsesformer vokser forspændingen af forstyreventilen med en tiltagende forskydning af ventilstemplet, i modstæning til, hvad der er tilfældet ved kendte forstyrede trykbegrænsningsventiler. Derved får man alt efter størrelsen af 15 fjederkonstanten for trykfjederen en karakteristik, der stiger med reguleringsstrømmen. Denne stigning kan vælges frit ved dimensionering af trykfjederen og åbningstværsnittet for den af ventilstemplet dannede trykvægt inden for vide grænser.In the embodiments described above, the biasing of the control valve increases with increasing displacement of the valve piston, in contrast to that of prior art controlled pressure relief valves. Thus, depending on the size of the spring constant of the compression spring, a characteristic which increases with the control current is obtained. This increase can be freely selected by dimensioning the compression spring and the opening cross section of the pressure weight formed by the valve piston within wide limits.
2020
Denne egenskab er meget fordelagtig for ventilens dynamiske forhold, da den giver tilbagevirkningsforhold til en tilsluttet reguleringskreds. Dermed kan man uden særlige dæmpningsforholdsregler meget virknings-25 fuldt undertrykke svingninger.This property is very advantageous for the dynamic conditions of the valve, as it provides a retroactive relationship to a connected control circuit. Thus, without special damping precautions, highly effective vibrations can be fully suppressed.
En yderligere fordel ved trykbegrænsningsventilen i-følge opfindelsen ligger i, at den er enkel, og at den kan udføres lille, fordi en anden fjeder og en 30 særlig forbindelseskanal falder bort.A further advantage of the pressure limiting valve according to the invention lies in the fact that it is simple and that it can be made small because another spring and a special connecting channel fail.
Claims (10)
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19742403007 DE2403007C2 (en) | 1974-01-23 | 1974-01-23 | Pilot operated pressure relief valve |
| DE2403007 | 1974-01-23 | ||
| DE2500537A DE2500537C2 (en) | 1975-01-08 | 1975-01-08 | Pilot operated pressure relief valve |
| DE2500480A DE2500480C2 (en) | 1975-01-08 | 1975-01-08 | Pilot operated pressure relief valve |
| DE2500480 | 1975-01-08 | ||
| DE2500537 | 1975-01-08 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| DK18175A DK18175A (en) | 1975-10-27 |
| DK155548B true DK155548B (en) | 1989-04-17 |
| DK155548C DK155548C (en) | 1989-09-11 |
Family
ID=27185737
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK18175A DK155548C (en) | 1974-01-23 | 1975-01-22 | DISTRIBUTED PRESSURE LIMIT VALVE |
Country Status (10)
| Country | Link |
|---|---|
| JP (1) | JPS5920911B2 (en) |
| BG (1) | BG29576A3 (en) |
| DK (1) | DK155548C (en) |
| ES (1) | ES434051A1 (en) |
| FR (1) | FR2258579B1 (en) |
| GB (1) | GB1466022A (en) |
| IT (1) | IT1026433B (en) |
| PL (1) | PL108692B1 (en) |
| RO (1) | RO64385A (en) |
| SE (1) | SE406800B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0750612Y2 (en) * | 1989-03-16 | 1995-11-15 | 株式会社小松製作所 | Pressure control valve |
| US7137406B2 (en) | 2002-11-19 | 2006-11-21 | Hydraforce, Inc. | Self-cleaning filter |
| CN108488395B (en) * | 2018-05-30 | 2024-04-02 | 中国重型机械研究院股份公司 | Stepped flow type injection valve controlled by multistage pressure |
-
1975
- 1975-01-20 SE SE7500585A patent/SE406800B/en not_active IP Right Cessation
- 1975-01-22 FR FR7501898A patent/FR2258579B1/fr not_active Expired
- 1975-01-22 IT IT4780375A patent/IT1026433B/en active
- 1975-01-22 DK DK18175A patent/DK155548C/en not_active IP Right Cessation
- 1975-01-22 ES ES434051A patent/ES434051A1/en not_active Expired
- 1975-01-23 JP JP50010139A patent/JPS5920911B2/en not_active Expired
- 1975-01-23 BG BG7528795A patent/BG29576A3/en unknown
- 1975-01-23 GB GB296975A patent/GB1466022A/en not_active Expired
- 1975-01-23 RO RO8120475A patent/RO64385A/en unknown
- 1975-01-23 PL PL17750675A patent/PL108692B1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| PL108692B1 (en) | 1980-04-30 |
| GB1466022A (en) | 1977-03-02 |
| FR2258579B1 (en) | 1982-02-19 |
| SE7500585L (en) | 1975-08-20 |
| DK155548C (en) | 1989-09-11 |
| IT1026433B (en) | 1978-09-20 |
| BG29576A3 (en) | 1980-12-12 |
| SE406800B (en) | 1979-02-26 |
| RO64385A (en) | 1979-07-15 |
| JPS5920911B2 (en) | 1984-05-16 |
| FR2258579A1 (en) | 1975-08-18 |
| ES434051A1 (en) | 1977-02-16 |
| DK18175A (en) | 1975-10-27 |
| JPS50124221A (en) | 1975-09-30 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PBP | Patent lapsed |