DK167039B1 - PRESSURE REDUCING VALVE - Google Patents
PRESSURE REDUCING VALVE Download PDFInfo
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- DK167039B1 DK167039B1 DK586089A DK586089A DK167039B1 DK 167039 B1 DK167039 B1 DK 167039B1 DK 586089 A DK586089 A DK 586089A DK 586089 A DK586089 A DK 586089A DK 167039 B1 DK167039 B1 DK 167039B1
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- valve
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- bore
- pressure
- spring
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- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
- G05D16/101—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger the controller being arranged as a multiple-way valve
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
- G05D16/109—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger with two or more pistons acting as a single pressure controller that move together over range of motion during normal operations
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- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Safety Valves (AREA)
Description
i DK 167039 B1in DK 167039 B1
Opfindelsen angår en hydraulisk trykreduktionsventil med et hus, som har en husboring, i hvilken en tilløbs- og en udløbskanal udmunder, med et en aksialt forløbende gennemgangsboring indeholdende ventilgliderelement, som på sin 5 omkreds mindst har en styreåbning og i den ene aksiale retning belastes af det reducerede tryk og i den anden aksiale retning af en fjeder, hvorved den af fjederen belastede ende af ventilgliderelementet er udformet som ventilsæde, mod hvilket et aksialt bevægeligt sædeventil-luk-10 keelement presses af fjederen, og med en returkanal, som på den side af ventilgliderelementet, på hvilken fjederen er anbragt, udmunder i husboringen.BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a hydraulic pressure reducing valve having a housing having a housing bore into which an inlet and outlet duct opens, with an axially extending through bore containing valve sliding member which at least has a guide opening and in one axial direction is loaded by the reduced pressure and in the other axial direction of a spring, whereby the end loaded by the spring is formed by the valve slider as a valve seat against which an axially movable seat valve closing member is pressed by the spring, and with a return channel which on that side of the valve slider member on which the spring is mounted opens into the housing bore.
Trykreduktionsventiler indsættes for at nedsætte det af en 15 pumpe leverede pumpetryk til en for trykstyrede eller -aktiverede arbejdselementer egnet værdi. Derved skal det reducerede tryk uafhængigt af det højere pumpetryk holdes konstant på en forudbestemt værdi.Pressure reduction valves are inserted to reduce the pump pressure supplied by a pump to a value suitable for pressure controlled or activated working elements. Thereby the reduced pressure, regardless of the higher pump pressure, must be kept constant at a predetermined value.
20 Trykreduktionsventiler kan dog klemme i husboringen, når der ved hjælp af -hydraulikvæsken skylles smudspartikler, fx sandkorn,, ind mellem huset og ventilgliderelementet.20 Pressure reduction valves, however, can squeeze into the housing bore when dirt particles are flushed through the hydraulic fluid, for example sand grains, between the housing and the valve sliding element.
Hvis ventilgliderelementet klemmes i den åbne stilling, når det ikke-reducerede pumpetryk til de efterkoblede kom-25 ponenter, hvorved disse kan beskadiges.If the valve slider is clamped in the open position, the non-reduced pump pressure reaches the after-coupled components, thereby damaging them.
Det er derfor kendt (FR 2 341 891) at integrere en trykbegrænsningsventil i trykreduktionsventilen, således at trykreduktionsventil og trykbegrænsningsventil danner en 30 konstruktiv enhed. Hvis alle forbrugere ved en sådan trykreduktionsventil er frakoblet på den trykreducerede side, og pumpen alligevel leverer videre, kan det ske, at der flyder en lækageoliestrøm gennem den mellem husboringen og ventilgliderelementet dannede spalte fra pumpetryksiden 35 til den trykreducerede side. Denne lækageolie forøger trykket på den trykreducerede side og forskyder ved den DK 167039 B1 2 kendte trykreduktionsventil ventilglideren så langt mod fjederens kraft, at en i ventilgliderelementet dannet drosselkanal etablerer en forbindelse mellem udløbskanal og returkanal og danner en laekageolieudløbsvej. Denne læ-5 kageolieudløbsvej er kun åben i ventilgliderelementets lukkestilling. Lækageolien kan altså over denne vej strømme bort til tanken uden at bevirke en trykforhøjelse på den trykreducerede side. Ulempen er derved, at positioneringen af den lækageolievejen dannende drosselboring skal 10 være afstemt meget nøjagtigt til husets dimensioner. Drosselboringen må først udmunde i det med returkanalen i forbindelse stående rum, når ventilgliderelementet er lukket.Therefore, it is known (FR 2 341 891) to integrate a pressure limiting valve into the pressure reducing valve so that the pressure reducing valve and pressure limiting valve form a constructive unit. If all consumers at such a pressure reducing valve are disconnected on the pressure reduced side, and the pump still delivers, a leakage of oil flow may occur through the gap formed between the housing bore and the valve sliding element from the pump pressure side 35 to the pressure reduced side. This leakage oil increases the pressure on the pressure-reduced side and displaces the valve slider of the known pressure reduction valve so far against the force of the spring that a choke formed in the valve slider element establishes a connection between outlet channel and return channel and forms a leakage oil outlet path. This leakage oil discharge path is open only in the valve position of the valve slider. Thus, the leakage oil can flow over this path to the tank without causing a pressure increase on the pressure-reduced side. The disadvantage is that the positioning of the leakage oil-forming throttle bore must be precisely aligned to the dimensions of the housing. The throttle bore must first open in the space communicating with the return channel when the valve sliding element is closed.
En relativ præcis fremstilling er derfor nødvendig. Det er derfor heller ikke altid uden videre muligt at skifte ven-15 tilgliderelementer af forskellige trykreduktionsventiler ud med hinanden.A relatively precise preparation is therefore necessary. Consequently, it is not always possible to swap out friend sliding elements of different pressure reducing valves with each other.
Formålet med den opfindelse er at angive en konstruktiv enkel løsning for laekageolieudløbsvej en i en trykredukti-20 onsventil.The object of the present invention is to provide a constructively simple solution for leakage oil outlet path one in a pressure reduction valve.
Denne opgave løses ved en hydraulisk trykreduktionsventil af den i indledningen nævnte art ved, at sædeventil-lukke-elementet har en ventilgliderelementets gennemgangsboring 25 forlængende boring, og en drosselkanal er anbragt i væggen af denne boring.This task is solved by a hydraulic pressure reducing valve of the kind mentioned in the preamble by the seat valve closing member having an extension bore of the valve slider member 25 extending bore and a throttle channel being arranged in the wall of this bore.
Derved fås en meget enkel konstruktion. Sædeventil-lukke-elementet kan let bearbejdes, da der til fremstilling af 30 laekageolieudløbsvej en kun skal anbringes to yderligere boringer, nemlig for det første aksialboringen og for det andet drosselkanalboringen.This gives a very simple construction. The seat valve closure member can be easily machined, since in order to produce 30 leakage oil discharge paths only two additional bores have to be disposed, namely for the first axial bore and secondly the throttle channel bore.
Med fordel har sædeventil-lukkeelementets ende, som ligger 35 an mod ventilgliderelementets ventilsæde, form af en kuglekalot. Denne kuglekalot er selvcentrerende, således at 3 DK 167039 B1 sædeventil-lukkeelementet efter hver aktivering af trykbegrænsningsventilen igen kommer sikkert til tætnende anlæg mod ventilgliderelementet. Andre selvcentrerende udførelsesformer, som formen af en keglestub eller lignende, er 5 ligeledes tænkelige.Advantageously, the end of the seat valve closure member, which is adjacent to the valve seat of the valve slide member, is in the form of a ball bearing. This ball joint is self-centering, so that after each actuation of the pressure limiting valve, the seat valve closure element safely returns to sealing abutment against the valve slider element. Other self-centering embodiments, such as the shape of a cone stub or the like, are also conceivable.
Fortrinsvis har sædeventil-lukkeelementet et skaft, som fører fjederen. Derved beskyttes sædeventil-lukkeelementet endnu bedre mod kantning og dermed mod fastklemning i hus-10 boringen.Preferably, the seat valve closure member has a shaft which guides the spring. Thereby, the seat valve closure element is even better protected against edging and thus against clamping in the housing bore.
I en videre udførelsesform har ventilgliderelementet og/ eller husboringen i området af henholdsvis styreåbningen og tilløbskanalen en ringnot. Denne forholdsregel forbed-15 rer strømningstværsnittet, således at strømningen igennem trykreduktionsventilen i åben stilling kun påvirkes ganske uvæsentligt. Pumpetrykket skal derfor også kun være ubetydeligt højere end det reducerede tryk.In a further embodiment, the valve slider element and / or housing bore in the region of the control opening and the inlet duct respectively have a ring groove. This precaution improves the flow cross-section so that the flow through the pressure reducing valve in the open position is only negatively affected. Therefore, the pump pressure must also be only slightly higher than the reduced pressure.
20 I en foretrukken udførelsesform udgør den af det reducerede tryk påvirkede tværsnitsflade af sædeventil-lukkeelementet ca. 50% til ca. 95% af ventilgliderelementets samlede diameter flade. Gennem valget af fladerne kan der opnås en indstilling af forholdene mellem det reducerede 25 tryk og det maksimale tryk.In a preferred embodiment, the cross-sectional area affected by the reduced pressure of the seat valve closure member is about 50% to approx. 95% of the total diameter of the valve sliding element. By selecting the surfaces, an adjustment of the ratio between the reduced pressure and the maximum pressure can be achieved.
Opfindelsen beskrives i det følgende ved hjælp af foretrukne udførelseseksempler i forbindelse med tegningen, der viser i 30 fig. 1 en skematisk fremstilling af en første udførelsesform og fig. 2 en trykreduktionsventil ifølge fig. 1.The invention will now be described by way of example with reference to the accompanying drawings, in which: FIG. 1 is a schematic representation of a first embodiment; and FIG. 2 shows a pressure reducing valve according to FIG. First
35 DK 167039 B1 435 DK 167039 B1 4
Fig. 1 viser et hus 1, som har en husboring 2. Huset 1 kan på ikke vist måde være delt på ethvert vilkårligt sted for at anbringe husboringen 2. I husboringen 2 er et ventil-gliderelement 3 lejret bevægeligt i aksial retning. Bevæ-5 gelsen er i en retning, i det viste tilfælde mod venstre, begrænset af et fremspring 17, mod hvilket ventilglider-elementet ligger an med en del af sin endeflade. Ventil-gliderelementet 3 trykkes af en fjeder 11, som over et sæ-deventil-lukkeelement 12 virker på ventilgliderelementet 10 og er understøttet på husboringens 2 bund 27, mod fremspringet 17.FIG. 1 shows a housing 1 having a housing bore 2. The housing 1 can in no way be divided at any location to place the housing bore 2. In the housing bore 2, a valve sliding element 3 is movable in an axial direction. The movement is restricted in one direction, in the case shown to the left, by a projection 17 against which the valve slider member abuts with a portion of its end surface. The valve slider 3 is pressed by a spring 11 which acts on a valve slider member 10 over a saw valve closing member 10 and is supported on the bottom 27 of the housing bore 2, against the projection 17.
I husboringen 2 udmunder tre kanaler, nemlig for det første en tilløbskanal 5, som fra en pumpe 7, som leverer hy-15 draulikolie, der står under pumpetrykket P , fører til tr husboringen 2, en udløbskanal 4, som leder hydraulikolie med reduceret tryk Pre(j videre til forbrugere, og en returkanal 6, som fører hydraulikolien tilbage til en tank 8. Hydraulikolien i returkanalen 6 står under trykket PT· 20 På det sted, hvor tilløbskanalen 5 udmunder i husboringen 2, er der i husboringen 2 anbragt en ringnot 18. Udløbskanalen 4 udmunder i husboringens 2 afsnit, som er dannet mellem fremspringet 17 og husboringens endeside.In the housing bore 2, three ducts, namely firstly, an inlet duct 5, which from a pump 7 which delivers hydraulic oil below the pump pressure P, leads to the three housing bore 2, an outlet duct 4 which conducts hydraulic oil at reduced pressure. Pre (j onwards to consumers, and a return channel 6 which returns the hydraulic oil to a tank 8. The hydraulic oil in the return channel 6 is pressurized PT · 20 At the point where the inlet channel 5 opens in the housing bore 2, a housing bore 2 is arranged. ringnote 18. The outlet channel 4 opens into the two sections of the housing bore formed between the projection 17 and the end side of the housing bore.
25 Husboringen 2 har en som ringnot 18 dimensioneret styreåbning ved enden af kanalen 5. Ventilgliderelementet 3 har en styreåbning 10, som indvendigt er udformet som drossel med en diameter D og udvendigt som ringnot 19. Ventilgliderelementet 3 har en gennemgående aksialboring 9, i hvil-30 ken styreåbningen 10 udmunder.The housing bore 2 has a guide opening dimensioned as a ring groove 18 at the end of the channel 5. The valve slider element 3 has a guide opening 10 which is internally formed as a choke with a diameter D and externally as a ring groove 19. The valve slider element 3 has a through axial bore 9, in the rest. 30, the guide opening 10 opens.
Ved den ende, som ikke ligger an mod fremspringet 17, har ventilgliderelementet 3 et ventilsæde 15, mod hvilket sædeventil- lukkeelementet 12 med en tætningsflade 16 lægger 35 an. Da sædeventil-lukkeelementet 12 af fjederen 11 trykkes mod ventilgliderelementet 3, er der mellem ventilglider- 5 DK 167039 B1 elementet 3 og sædeventil-lukkeelementet 12 en kraftoverførende forbindelse. Fjederen 11 angriber derved på en skulder 20 af sædeventil-lukkeelementet og føres gennem en fortykning 21 af sædeventil-lukkeelementet 12. I øvrigt 5 har sædeventil-lukkeelementet 12 et skaft 22, som med sin samlede længde befinder sig inden i fjederen 11. Sædeventil-lukkeelementet har en ringere diameter end husboringen 2 og er ført berøringsfrit i denne.At the end which does not abut the projection 17, the valve slider member 3 has a valve seat 15 against which the seat valve member 12 with a sealing surface 16 abuts 35. Since the seat valve closing member 12 of the spring 11 is pressed against the valve sliding member 3, there is a power transmitting connection between the valve sliding member 3 and the seat valve closing member 12. The spring 11 thereby attacks on a shoulder 20 of the seat valve closing member and is passed through a thickening 21 of the seat valve closing member 12. Moreover, 5 the seat valve closing member 12 has a shaft 22 which, with its total length, is located within the spring 11. the closure member has a diameter smaller than the housing bore 2 and is guided in it without contact.
10 Sædeventil-lukkeelementet 12 har en aksial boring 14, som forlænger ventilgliderelementets 3 aksiale gennemgangsboring 9. I denne borings 14 væg er en radialboring 13 anbragt, som danner en drosselkanal.The seat valve closure member 12 has an axial bore 14 which extends the axial passage bore of the valve slider member 3. In the wall of this bore 14, a radial bore 13 is provided which forms a choke.
15 Hydraulikolie flyder fra pumpen 7 igennem tilløbskanalen 5, ringnoterne 18, 19, styreåbningens 10 drossel, ventilgliderelementets 3 aksialboring 9 og husboringen 2 til udløbskanalen 4. Når trykket forøges i udløbskanalen 4, forskydes ventilgliderelementet 3 mod højre mod fjederens 11 20 kraft, hvorved det for hydraulikolien til rådighed stående strømningstværsnit reduceres gennem styreåbningen 10, eller- denne styreåbning lukkes. Når ventilgliderelementet 3 forskydes så langt mod højre, at de to ringnoter 18, 19 ingen overlapning har mere, kan der ikke mere flyde hy-25 draulikolie fra tilløbskanalen 5 til udløbskanalen 4.Hydraulic oil flows from the pump 7 through the inlet duct 5, the ring grooves 18, 19, the throttle of the control opening 10, the axial bore 9 of the valve slider 3 and the housing bore 2 to the outlet duct 4. As the pressure increases in the outlet duct 4, the valve slider 3 is displaced to the right by the spring 11 20. the flow cross-section available to the hydraulic oil is reduced through the control opening 10, or this control opening is closed. When the valve slider 3 is displaced so far to the right that the two ring grooves 18, 19 have no overlap, no more hydraulic oil can flow from the inlet duct 5 to the outlet duct 4.
Trykket i udløbskanalen 4 reduceres. Derpå forskydes ventilgliderelementet 3 igen mod venstre mod fjederens 11 kraft for at lade hydraulikolie flyde fra tilløbsledningen 5 til udløbsledningen 4.The pressure in the outlet duct 4 is reduced. Then the valve slider 3 is shifted again to the left against the force of the spring 11 to allow hydraulic oil to flow from the inlet line 5 to the outlet line 4.
30 Når smudspartikler, som fx sand, skylles ind gennem hydraulikolien, kan det forekomme, at ventilgliderelementet 3 klemmes i en eller anden stilling. Hvis ventilgliderelementet 3 klemmes i den åbne stilling, dvs. ved anslag mod 35 fremspringet 17, kan ikke-reduceret tryk Pp nå fra pumpen 7 igennem tilløbskanalen 5 og styreåbningen 10 til udløbs- DK 167039 B1 6 kanalen 4. For at forhindre dette er sædeventil-lukkeele-mentet 12 anbragt. Stiger trykket i ventilgliderelementets 3 aksialboring 9 over en forudbestemt værdi, forskydes sæ-deventil-lukkeelementet 12 mod højre mod fjederens 11 5 kraft og lader hydraulikolien sive ud gennem den mellem ventilsædet 15 og tætningsfladen 16 opstående spalte og videre igennem returkanalen 6 til tanken 8. Ved valg af forholdene mellem ventilgliderelementets 3 diameterflade og den af trykket påvirkede flade af sædeventil-lukkeele-10 mentet 12 kan forholdet mellem det maksimalt mulige tryk i udløbskanalen 4 og det ønskede reducerede tryk Pre(j bestemmes. Derved fås forholdet mellem det maksimale tryk og det reducerede tryk Precj af forholdet mellem ventilgliderelementets 3 samlede diameter flade og den af trykket på-15 virkede flade af sæde vent i 1- lukkee 1 ement e t 12. Når disse to flader kun er uvæsentlig forskellig fra hinanden, fx når sædeventil-lukkeelementets virksomme flade udgør ca.When dirt particles, such as sand, are flushed through the hydraulic oil, it may occur that the valve slider 3 is clamped in some position. If the valve slider 3 is clamped in the open position, ie. upon impact against the projection 17, non-reduced pressure Pp can reach from the pump 7 through the inlet duct 5 and the control opening 10 to the outlet duct 4. In order to prevent this, the seat valve closing element 12 is arranged. If the pressure in the axial bore 9 of the valve slider element 3 rises above a predetermined value, the sealing valve element 12 is shifted to the right against the force of the spring 11 and allows the hydraulic oil to seep out through the gap which arises between the valve seat 15 and the sealing surface 16 and further through the return channel 6 to the tank 8. By choosing the ratio of the diameter face of the valve slider member 3 to the pressure-influenced face of the seat valve closure member 12, the ratio of the maximum possible pressure in the outlet duct 4 to the desired reduced pressure Pre (j) can be determined. the reduced pressure Precj of the ratio of the total diameter surface of the valve slider element 3 to that of the pressure-influenced surface of the seat vent in the 1-closure 1 element 12. When these two surfaces are only substantially different from each other, for example, when the seat valve closure element operates flat constitutes approx.
95% af ventilgliderelementets 3 diameter flade, adskiller det maksimale tryk sig også kun ca. 5% fra det reducerede 20 tryk. Når derimod sædeventil-lukkeelementets 12 virksomme flade er væsentlig mindre end ventilgliderelementets 3 diameter flade, er det maksimale tryk væsentlig højere end det reducerede tryk Pred· 25 Styreåbningen 10 er udført som drossel. Derved kan der selv ved åben spalte mellem ventilgliderelement 3 og sæde-ventil-lukkeelement 12 kun nå en begrænset mængde hydraulikolie fra tilløbskanalen 5 til returkanalen 6. Derved forhindres, at den af ventilgliderelementet 3 og sædeven-30 til- lukkee 1 ement et 12 dannede trykbegrænsningsventil over belastes .95% of the diameter of the valve slide element 3, the maximum pressure also differs only about 5% from the reduced 20 pressure. In contrast, when the effective surface of the seat valve closure member 12 is substantially smaller than the diameter of the valve slide member 3, the maximum pressure is substantially higher than the reduced pressure. Pred · 25 The control opening 10 is designed as a throttle. Thus, even at an open gap between valve slider element 3 and seat valve closure element 12, only a limited amount of hydraulic oil can be reached from the inlet duct 5 to the return duct 6. This prevents the formation of valve 12 formed by the valve slider element 3 and the seat valve closure element 12. pressure relief valve over loaded.
Også i ventilgliderelementets 3 lukkede stilling, dvs. når ventilgliderelementet 3 er forskudt så langt mod højre, at 35 der ikke mere kan nå hydraulikolie gennem styreåbningen 10 til aksialboringen 9, flyder en ringe mængde hydraulikolie DK 167039 B1 7 gennem den mellem husboringen 2 og ventilgliderelementet 3 dannede spalte til udløbskanalen 4. Denne ringe mængde olie, som her betegnes som lækageolie, ville ved spærrede forbrugere føre til en uønsket trykforhøjelse i udløbska-5 nalen 4. For at forhindre denne trykforhøjelse er der i sædeventil-lukkeelementet anbragt en lækageolieudløbsvej, som dannes af aksialboringen 14 og radialboringen 13. Gennem denne vej kan den til ventilgliderelementets 3 aksial-boring 9 kommende lækageolie strømme bort til tanken. For 10 at forhindre at en for stor mængde hydraulikolie strømmer bort til tanken også under normal drift, er radialboringen 13 udformet som drosselkanal med en forudbestemt diameter d. Den samlede mængde af den herved bortstrømmende hydraulikolie, dvs. det permanente tab gennem denne drosselkanal 15 13, bestemmes efter formlen ft. - * · -¾5 · ÆTi hvorved Qy er tabet, K er blændefaktoren, d er drosselkanalens diameter, Pred er det reducerede tryk og PT er 20 trykket i returkanalen 6.Also in the closed position of the valve slide element 3, ie. when the valve sliding element 3 is displaced so far to the right that 35 no longer can reach hydraulic oil through the control opening 10 to the axial bore 9, a small amount of hydraulic oil DK 167039 B1 7 flows through the gap formed between the housing bore 2 and the valve sliding element 3. amount of oil, herein referred to as leakage oil, would result in an undesirable pressure rise in the outlet channel by blocked consumers 4. To prevent this pressure rise, a leakage oil outlet path formed by the axial bore 14 and radial bore 13. is provided in the seat valve closure element. this way, the leakage oil coming to the axial bore 9 of the valve slider element 3 can flow to the tank. In order to prevent an excessive amount of hydraulic oil from flowing into the tank during normal operation, the radial bore 13 is formed as a predetermined diameter dunnage channel d. The total amount of the flowing hydraulic oil, ie. the permanent loss through this choke 15 13 is determined by the formula ft. - * · -¾5 · ÆTi whereby Qy is the loss, K is the aperture factor, d is the diameter of the choke, Pred is the reduced pressure and PT is the pressure in the return channel 6.
Sædeventil-lukkeelementet 12 har ved den ende, ved hvilken det presses mod ventilgliderelementet 3, form af en kuglekalot. Denne form har den fordel, at sædeventil-lukkeele-25 mentet efter hver aktivering af trykbegrænsningsventilen igen centreres automatisk i ventilgliderelementets 3 ventilsæde 15. Derved er en sikker lukning af denne trykbegrænsningsventil sikret.At the end at which it is pressed against the valve slide member 3, the seat valve closing member 12 is in the form of a ball bearing. This shape has the advantage that, after each activation of the pressure limiting valve, the seat valve closure element is automatically centered again in the valve seat 15 of the valve slider member 3, thereby ensuring a secure closure of this pressure limiting valve.
30 Fig. 2 viser en udførelsesform af trykreduktionsventilen, som i det væsentlige svarer til den skematiske fremstilling i fig. 1. Elementer, som svarer til de i fig. 1, er forsynet med 200 forhøjede henvisningsbetegnelser.FIG. 2 shows an embodiment of the pressure reducing valve which corresponds substantially to the schematic representation of FIG. 1. Elements corresponding to those of FIG. 1 is provided with 200 elevated reference numerals.
DK 167039 B1 8 I huset 201 er der anbragt en husboring 202. I denne husboring 202 er efter hinanden indsat fjederen 211, sædeven-til-lukkeelementet 212 og ventilgliderelementet 203. Et i det væsentlige cylindrisk filterelement 228 er anbragt i 5 en aksialboring af et lukkestykke 229, som ved hjælp af et gevind 230 under mellemkobling af en tætning 231 er fastskruet i huset 201 og med sin endeflade 232 danner et anslag for ventilgliderelementet 203.In the housing 201 a housing bore 202 is arranged. In this housing bore 202, the spring 211, the seat valve-closing element 212 and the valve slider element 203 are successively inserted. A substantially cylindrical filter element 228 is arranged in an axial bore of a housing. closure piece 229 which is screwed into housing 201 by means of a thread 230 during interconnection of a seal 231 and with its end surface 232 forms a stop for the valve slider element 203.
10 Ventilgliderelementet 203 har igen i området en styreåbning 210 med en ringnot 219. Denne virker sammen med tilløbskanalens 205 munding. Herved er vinkelstillingen, med hvilken ventilgliderelementet 203 er indsat i husboringen 202, ubetydelig. I hvert tilfælde er et tilstrækkeligt 15 strømningstværsnit givet for at lade hydraulikvæsken flyde igennem tilløbskanalen 205 til styreåbningen 210.The valve slider element 203 again has in the region a guide opening 210 with a ring groove 219. This cooperates with the mouth of the inlet duct 205. Hereby, the angular position with which the valve slide element 203 is inserted into the housing bore 202 is negligible. In each case, a sufficient flow cross section is provided to allow the hydraulic fluid to flow through the inlet duct 205 to the control opening 210.
Claims (5)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3840865A DE3840865A1 (en) | 1988-12-03 | 1988-12-03 | Pressure reducing valve |
| DE3840865 | 1988-12-03 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| DK586089D0 DK586089D0 (en) | 1989-11-22 |
| DK586089A DK586089A (en) | 1990-06-04 |
| DK167039B1 true DK167039B1 (en) | 1993-08-16 |
Family
ID=6368452
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| DK586089A DK167039B1 (en) | 1988-12-03 | 1989-11-22 | PRESSURE REDUCING VALVE |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE3840865A1 (en) |
| DK (1) | DK167039B1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3820488C2 (en) * | 1988-06-16 | 1999-06-02 | Medizintechnik Promedt Gmbh | Device for draining river accumulations from body cavities |
| DE9016844U1 (en) * | 1990-12-13 | 1991-02-28 | Schiefer, Rolf, 4050 Mönchengladbach | Hydraulic pressure regulator with self-relief at O-bar control pressure |
| DE4239109C1 (en) * | 1992-11-20 | 1994-06-30 | Danfoss As | Hydraulic system |
| DE4304117C2 (en) * | 1993-02-12 | 1997-01-09 | Parker Hannifin Nmf Gmbh | Pressure reducing valve in piston spool design |
| US9638154B2 (en) | 2011-06-28 | 2017-05-02 | Caterpillar Inc. | Common rail fuel pump control system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2341891A1 (en) * | 1976-02-23 | 1977-09-16 | Leduc Gerard | Filling and safety valve for hydraulic vessel - has sliding sleeve and pressure relief end cap held by single spring |
-
1988
- 1988-12-03 DE DE3840865A patent/DE3840865A1/en active Granted
-
1989
- 1989-11-22 DK DK586089A patent/DK167039B1/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| DE3840865A1 (en) | 1990-06-07 |
| DK586089D0 (en) | 1989-11-22 |
| DE3840865C2 (en) | 1990-09-13 |
| DK586089A (en) | 1990-06-04 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| B1 | Patent granted (law 1993) | ||
| PBP | Patent lapsed |