DK159383B - SHUTTER VALVE FOR CLUTCH TO A POWER SHAFT ON A TRACTOR - Google Patents

SHUTTER VALVE FOR CLUTCH TO A POWER SHAFT ON A TRACTOR Download PDF

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Publication number
DK159383B
DK159383B DK225885A DK225885A DK159383B DK 159383 B DK159383 B DK 159383B DK 225885 A DK225885 A DK 225885A DK 225885 A DK225885 A DK 225885A DK 159383 B DK159383 B DK 159383B
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DK
Denmark
Prior art keywords
valve
bore
piston
opening
pressure
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DK225885A
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Danish (da)
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DK159383C (en
DK225885D0 (en
DK225885A (en
Inventor
Tapio Vainiomaeki
Pekka Kalevi Mailas
Original Assignee
Valmet Oy
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Publication of DK225885A publication Critical patent/DK225885A/en
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Publication of DK159383C publication Critical patent/DK159383C/en

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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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/14—Fluid pressure control
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0215—Control by fluid pressure for damping of pulsations within the fluid system
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Mechanical Operated Clutches (AREA)

Description

DK 159383 BDK 159383 B

Den foreliggende opfindelse vedrører en dæmperventil til koblingen til en kraftudtagsaksel på en traktor, hvilken dæmperventil er placeret mellem en koblingsventil og koblingen i et trykrør, som leder fra en af traktorens motor drevet hydraulisk pumpe til kraftudtagsak-5 selens kobling, som angivet i krav l's indledning.The present invention relates to a damper valve for the coupling to a PTO shaft of a tractor, which damper valve is located between a coupling valve and the coupling in a pressure pipe which leads from a hydraulic pump driven by the tractor engine to the PTO shaft coupling, as claimed in claim 1. introduction.

Normalt benyttes traktorens eget hydrauliske anlæg til indkobling af traktorens kraftudtagsaksel. Kraftudtagsakselen er normalt forbundet til en aksel, som udgår fra traktorens motor, ved hjælp af en vådkobling, fx en lamelkobling, idet kraftudtagsakselen indkobles, når 10 trykket i vådkoblingen er steget til det normale arbejdstryk. Ar-bejdstrykket i et sådant anlæg er normalt af størrelsesordenen 16 bar. Hvis kraftudtagsakselen indkobles uden nogen form for forsinkelse af trykforøgelsen, bliver tiden til trykforøgelsen af størrelsesordenen 0,2 s. En så hurtig indkobling frembringer et pludseligt ryk 15 i kraftudtaget, hvilket kan forårsage skader enten på en arbejdsmaskine, som er forbundet til kraftudtagsakselen, på selve kraftudtagsakselen eller på kardanakselen. Dette problem er specielt vanskeligt at løse, da oliens viskositet er lav.Normally, the tractor's own hydraulic system is used to connect the tractor's PTO shaft. The PTO shaft is normally connected to a shaft exiting the tractor engine by means of a wet clutch, for example a slat clutch, the PTO shaft being engaged when the pressure in the wet clutch has risen to normal working pressure. The working pressure in such a plant is usually of the order of 16 bar. If the PTO shaft is engaged without any delay in the increase of pressure, the time for the pressure increase to be of the order of 0.2 s. Such a rapid switch-on produces a sudden jerk 15 in the PTO, which can cause damage to either a working machine connected to the PTO shaft. the PTO shaft itself or the PTO shaft. This problem is particularly difficult to solve as the viscosity of the oil is low.

Til løsning af dette problem og forsinkelse af kraftudtagsakselens 20 indkobling er hidtil blevet benyttet manuelle regulerbare ventiler, ved hjælp af hvilke anlæggets koblingstryk kan forøges langsomt ved manuel styring. Ved hjælp af sådanne indretninger undgås skader på maskiner og indretninger ved indkoblingen. Følgen heraf er imidlertid en ekstra arbejdsoperation for brugeren af indretningen, og brugeren 25 skal altid huske at indstille trykforøgelsestiden på passende måde afhængigt af situationen. Hvis trykforøgelsestiden er alt for kort, kan følgen blive mekaniske skader på kraftoverføringsindretningerne.To solve this problem and delay the engagement of the PTO shaft 20, so far manual adjustable valves have been used, by which the coupling pressure of the system can be increased slowly by manual control. Such devices prevent damage to machines and devices when switching on. However, the consequence is an additional work operation for the user of the device, and the user 25 must always remember to adjust the pressure increase time appropriately depending on the situation. If the pressure increase time is too short, the result can be mechanical damage to the transmission devices.

Hvis tiden er alt for lang, kan koblingen blive beskadiget som følge af varmen.If the time is too long, the coupling may be damaged by the heat.

30 Formålet med opfindelsen er at tilvejebringe en dæmperventil til koblingen til en kraftudtagsaksel på en traktor, hvilken ventil ikke er behæftet med de ovenfor nævnte ulemper. Den væsentligste fordel ved opfindelsen er, at koblingstrykket forøges automatisk, idet der kan benyttes en elektrisk styret ventil som koblingsventil. Opfindelsen 35 er ejendommelig ved, at dæmperventilen automatisk regulerer kraftud-The object of the invention is to provide a damping valve for the coupling to a PTO shaft of a tractor, which valve is not affected by the disadvantages mentioned above. The main advantage of the invention is that the coupling pressure is increased automatically, since an electrically controlled valve can be used as a coupling valve. The invention 35 is characterized in that the damper valve automatically regulates the power output.

DK 159383 BDK 159383 B

2 tagsakselens indkoblingstid ved regulering af trykket af den strøm, som tilføres koblingen, som angivet i krav l's kendetegnende del.2, the actuating time of the roof shaft by controlling the pressure of the current supplied to the coupling, as defined in the characterizing part of claim 1.

Opfindelsen vil i det følgende blive nærmere forklaret under henvisning til tegningen, på hvilken 5 fig. 1 viser et funktionsdiagram for en kraftudtagsaksel på en traktor, fig. 2 et snit gennem en dæmperventilkonstruktion ifølge opfindelsen, set fra siden og fig. 3 et koblings tidsdiagram for dæmperventilen ifølge opfindelsen.The invention will be explained in more detail below with reference to the drawing, in which: FIG. 1 is a functional diagram of a PTO shaft of a tractor; FIG. 2 is a side view of a damper valve assembly according to the invention; and FIG. 3 is a coupling timing diagram of the damper valve according to the invention.

10 I fig. 1 er vist et funktionsdiagram for en kraftudtagsaksel. I figuren er vist en aksel 1, som drives af en traktormotor, og som driver en hydraulisk pumpe 2. Den hydrauliske pumpe 2 tilfører tryk til et hydraulisk anlæg. På akselen 1 er desuden monteret en kobling til kraftudtagsakselen. Koblingen er i figuren vist som en lamelkob-15 ling 5. Koblingen kan imidlertid også være en vådkobling af en vilkårlig anden type. På akselen 1 er monteret en røraksel 6, der er forbundet til lamelkoblingen 5, og på hvilken der er monteret et tandhjul 7. Tandhjulet 7 er i indgreb med et andet tandhjul 8, der er koblet til kraftudtagsakselen 9. Det fremgår desuden af figuren, at 20 pumpen 2 tilfører tryk til en ventil 3, ved hjælp af hvilken traktorens kraftudtagsaksel 9 indkobles. Ventilen 3 føder imidlertid ikke tryk direkte til koblingen 5, men til en mellem ventilen 3 og koblingen 5 monteret og skematisk vist dæmperventil 4 ifølge opfindelsen, ved hjælp af hvilken ventil forøgelsen af koblingstrykket 25 forsinkes. 1 fig. 2 er vist en dæmperventil ifølge opfindelsen. Ventilen er et langstrakt emne. I den ene ende af et hus 10 er udformet et gennemgående hul i husets tværretning. Hullets ene ende A danner en indløbsåbning, gennem hvilken der ledes olie ind i ventilen, og hullets 30 anden ende B danner en udløbsåbning, fra hvilken der ledes olie ud fra ventilen til et olierum i koblingens koblingshus. Midt i ventil-huset 10 er udformet en boring 22, der strækker sig i husets længderetning, og som via en åbning 21 i boringens bund står i forbindelse med det tværgående hul i huset. I huset 10 er der ved siden af borin-35 gen 22 udformet en anden boring 11, der strækker sig i længderet- 310 In FIG. 1 is a functional diagram of a PTO shaft. In the figure is shown a shaft 1 driven by a tractor engine and driven by a hydraulic pump 2. The hydraulic pump 2 applies pressure to a hydraulic system. In addition, a coupling to the PTO shaft is mounted on the shaft 1. The coupling is shown in the figure as a slat coupling 5. However, the coupling can also be a wet coupling of any other type. On the shaft 1 is mounted a pipe shaft 6, which is connected to the slat coupling 5, and on which is mounted a gear 7. The gear 7 is in engagement with another gear 8, which is coupled to the PTO shaft 9. Furthermore, the figure shows: the pump 2 supplies pressure to a valve 3 by means of which the tractor shaft 9 is engaged. However, the valve 3 does not supply pressure directly to the coupling 5, but to a damper valve 4 according to the invention mounted between the valve 3 and the coupling 5, by means of which the valve increases the increase of the clutch pressure 25. 1 FIG. 2 is a damper valve according to the invention. The valve is an elongated item. At one end of a housing 10, a through hole is formed in the transverse direction of the housing. One end A of the hole forms an inlet opening through which oil is fed into the valve, and the other end B of the hole 30 forms an outlet opening from which oil is discharged from the valve into an oil chamber in the coupling housing. In the middle of the valve housing 10 is formed a bore 22 extending longitudinally of the housing, which communicates with the transverse hole in the housing via an opening 21 in the bottom of the bore. In the housing 10, next to the bore 22, a second bore 11 extending longitudinally is formed.

DK 159383 BDK 159383 B

ningen, og som desuden står i direkte forbindelse med det tværgående hul. Boringen 11 er en såkaldt lukkekanal, i hvilken der er monteret et fritbevægeligt lukkestempel 12. Huset 10 har gevind i den ende, der ligger modsat det tværgående hul. På gevindet er skruet en lukke-5 møtrik 15. Møtrikken 15 lukker enden af ventilhuset 10 tæt, så at boringerne 11 og 22, der strækker sig i længderetningen, ikke står i direkte forbindelse med ventilens ydre omgivelser via denne ende. I væggen af boringen 22, som strækker sig i længderetningen, er der midt i ventilen udformet en radial boring 13, via hvilken boringerne 10 11 og 22 står i forbindelse med hinanden. Møtrikken 15 lukker den radiale boring 13, så at denne ikke står i direkte forbindelse med omgivelserne. I ventilhuset 10 er der desuden udformet en radial boring C, der står i forbindelse med boringen 22 via åbningen 21 i boringens bund. I bunden af boringen 22 findes en kugle 20, som 15 lukker åbningen 21. I den anden ende af boringen 22 er monteret et stempel 16, der kan bevæge sig frem og tilbage i boringen, og som har en stempelstang 17, der er rettet mod kuglen 20, og en tap 18, der er rettet modsat. Mellem kuglen 20 og stemplet 16 er monteret en fjeder 19, der presser kuglen og stemplet bort fra hinanden. Mellem tappen 20 18 og boringen 22’s væg dannes der et ringformet .rum 14, som lukkeka nalen 11 står i forbindelse med via den radiale boring 13.and which is also in direct contact with the transverse hole. The bore 11 is a so-called closure channel in which is mounted a freely movable closure piston 12. The housing 10 has threads at the end opposite the transverse hole. On the thread is screwed a lock-5 nut 15. The nut 15 closes the end of the valve housing 10 tightly so that the bores 11 and 22 extending longitudinally do not communicate directly with the external environment of the valve via this end. In the wall of the bore 22 which extends longitudinally, a radial bore 13 is formed in the middle of the valve, through which the bores 10 11 and 22 are connected. The nut 15 closes the radial bore 13 so that it is not in direct contact with the surroundings. In the valve housing 10, a radial bore C is also formed, which communicates with the bore 22 via the opening 21 in the bottom of the bore. At the bottom of the bore 22 is a ball 20 which closes the opening 21. At the other end of the bore 22 is mounted a piston 16 which can move back and forth in the bore and has a piston rod 17 directed towards it. the ball 20, and a pin 18, directed opposite. Between the ball 20 and the piston 16 is mounted a spring 19 which pushes the ball and piston away from each other. Between the pin 20 18 and the wall of the bore 22, an annular space 14 is formed, which the closure channel 11 communicates with via the radial bore 13.

Når den i fig. 1 viste koblingsventil 3 åbnes, føres olien via denne ventil til indløbsåbningen A i den i fig. 2 viste dæmperventil. Olien føres direkte gennem denne tværgående boring og ud gennem udløbs-25 åbningen B til kraftudtagsakselens kobling. Den modstand, som koblingen frembringer, medfører en trykforøgelse i dæmperventilen, og som følge af denne trykforøgelse bevæger den kugle 20, som ligger mod åbningen 21, sig mod højre i fig. 2, hvorved der fra indløbsåbningen A åbnes en direkte forbindelse via lækåbningen C. Fjederen 19, der 30 ligger bag kuglen 20, bestemmer, ved hvilket begyndelsestryk p0 lækåbningen C åbnes. Når trykket stiger, strømmer olien også ind i lukkekanalen 11. Mellem lukkestemplet 12 i kanalen 11 og kanalvæggen findes der et vist mellemrum, et såkaldt lukkemellemrum, hvis størrelse kan være fx 0,2 mm. Olien, som kommer ind i kanalen 11, skyder 35 stemplet 12 mod højre i fig. 2, men samtidigt lækker olien gennem lukkespillerummet forbi stemplet 12 og via den radiale boring 13 til det ringformede rum 14 bag arbejdsstemplet 16. Bag stemplet opstår 4When in FIG. 1, opening the oil via this valve to the inlet opening A in the embodiment shown in FIG. 2. The oil is passed directly through this transverse bore and out through the outlet opening B to the coupling of the PTO shaft. The resistance produced by the coupling results in a pressure increase in the damper valve, and as a result of this pressure increase, the ball 20 which lies against the opening 21 moves to the right in FIG. 2, whereby a direct connection is opened from the inlet opening A via the leakage opening C. The spring 19, which lies behind the ball 20, determines at which initial pressure on the leakage opening C is opened. As the pressure rises, the oil also flows into the closing duct 11. Between the closing piston 12 in the duct 11 and the duct wall there is a certain gap, a so-called closing gap, the size of which can be, for example, 0.2 mm. The oil entering the channel 11 pushes piston 12 to the right in FIG. 2, but at the same time the oil leaks through the closing chamber past the piston 12 and via the radial bore 13 to the annular space 14 behind the working piston 16. Behind the piston 4

DK 159383 BDK 159383 B

der herved en trykforøgelse, hvorved stemplet 16 søger at bevæge sig mod venstre i figuren mod den af fjederen 19 frembragte kraft og at trykke kuglen 20 tilbage mod åbningen 21. Når stemplet 16 ved hjælp af fjederen 19 skyder kuglen 20 i retningen mod den lukkede stilling, 5 bliver afstanden mellem kuglen 20 og åbningen 21 mindre, hvorved trykket i anlægget stiger. Trykforøgelsen i anlægget forøger også trykket i rummet 14, hvorved stemplet 16 bevæger sig længere mod venstre, og slutteligt har stemplet 16 bevæget sig så langt, at stempelstangen 17 tvangsstyret trykker kuglen til siden, hvorved 10 åbningen 21 lukkes helt, og lækstrømmen ophører. På denne måde er der opnået fuldt koblingstryk, og indkoblingen er fuldført. Når indkoblingen har fundet sted, hersker der samme tryk i hele anlægget.thereby increasing the pressure, whereby the piston 16 seeks to move left in the figure against the force produced by the spring 19 and to push the ball 20 back towards the opening 21. When the piston 16, by means of the spring 19, pushes the ball 20 in the direction towards the closed position. 5, the distance between the ball 20 and the opening 21 becomes smaller, whereby the pressure in the system increases. The pressure increase in the plant also increases the pressure in the space 14, whereby the piston 16 moves farther to the left, and finally the piston 16 has moved so far that the piston rod 17 forcibly pushes the ball to the side, thereby closing the opening 21 completely and the leakage flow ceases. In this way, full clutch pressure is obtained and the connection is completed. When the connection is made, the same pressure prevails throughout the system.

Herved skyder fjederen 19 stemplet 16 tilbage mod højre, og ved påvirkning fra den olie, som trækkes bort af stemplet 16, bevæger 15 lukkestemplet 12 sig tilbage til udgangsstillingen. Den i fig. 2 viste og af en fjeder 19 påvirkede ventil behøver ikke nødvendigvis at være en kugleventil 20, men den kan generelt være en lækventil, såsom en konusventil. 1 fig. 3 er vist et koblingstidsskema for dæmperventilen. Figurens 20 lodrette akse angiver koblingstrykket, og den vandrette akse koblingstiden. Af figuren fremgår det, at trykket først stiger hurtigt til værdien pQ, der er det såkaldte starttryk. Størrelsen af dette starttryk pQ bestemmes af den på lækventilen 20 virkende fjeder 19's stivhed. Fjederen 19's stivhed kan fordelagtigt vælges fx således, at 25 dette starttryk pQ er af størrelsesordenen 5 bar. Når starttrykket p0 er nået, begynder lækventilen 20 at åbne sig, hvorved trykforøgelsen forsinkes betydeligt, således som det fremgår af figuren.In this, the spring 19 pushes the piston 16 back to the right, and under the influence of the oil which is withdrawn by the piston 16, the closing piston 12 moves back to its initial position. The FIG. 2 and a valve 19 actuated by a spring 19 need not necessarily be a ball valve 20, but it can generally be a leak valve such as a taper valve. 1 FIG. 3 is shown a switching timing diagram for the damper valve. The vertical axis of the figure 20 indicates the coupling pressure and the horizontal axis the coupling time. The figure shows that the pressure first increases rapidly to the value pQ, which is the so-called initial pressure. The magnitude of this initial pressure pQ is determined by the stiffness of the spring 19 acting on the leak valve 20. The stiffness of the spring 19 can advantageously be selected, for example, such that this initial pressure pQ is of the order of 5 bar. When the initial pressure p0 is reached, the leakage valve 20 begins to open, thereby significantly delaying the pressure increase, as shown in the figure.

Denne trykforøgelse foregår langsommere til værdien p^, der er det totale koblingstryk. Koblingstrykkets størrelse er ca. 16 bar. Tiden 30 T til trykforøgelsen fra vædien p0 til værdien p^ kaldes dæmpnings-tiden. Denne dæmpertid kan vælges mellem 0,5 og 30 s, men er passende 1-2 s. Dæmpertiden Τ's størrelse kan påvirkes på forskellig måde. Lukkespillerummet mellem lukkestemplet 12 og kanalen 11 kan vælges på en sådan måde, at den ønskede dæmpertid T opnås. Jo mindre dette 35 spillerum er, desto længere bliver dæmpningstiden. Selv arbejdsstemplet 16's diameter påvirker dæmpningstiden T på en sådan måde, at jo større denne diameter er, desto længere bliver dæmpningstiden. EnThis pressure increase occurs more slowly to the value p ^, which is the total coupling pressure. The coupling pressure is approx. 16 bar. The time 30 T of the pressure increase from the value p0 to the value p ^ is called the damping time. This damping time can be selected between 0.5 and 30 seconds, but is suitably 1-2 seconds. The size of the damping time Τ can be affected in different ways. The shutter clearance between the shutter piston 12 and the channel 11 can be selected such that the desired damper time T is obtained. The smaller this 35 leeway, the longer the damping time. Even the diameter of the working piston 16 affects the damping time T in such a way that the larger this diameter is, the longer the damping time becomes. One

Claims (4)

10 Opfindelsen er ikke begrænset til den ovenfor beskrevne og i figurerne viste udførelsesform, men den kan modificeres inden for de efterfølgende patentkravs rammer.The invention is not limited to the embodiment described above and shown in the figures, but it can be modified within the scope of the following claims. 1. Dæmperventil til koblingen (5)’ til en kraftudtagsaksel (9) på en 15 traktor, hvilken dæmperventil (4) er monteret mellem en koblings- ventil (3) og koblingen (5) i et trykrør, der fører fra en hydraulisk pumpe (2), som drives af traktorens motor, til kraftudtagsakselens (9) kobling (5), og hvilken dæmperventil (4) har organer (10-22), der er indrettet til at reagere på trykket i den strøm, der fører gennem 20 dæmperventilen (4), hvilke organer er indrettet til automatisk at regulere trykket i den strøm, der fører til koblingen (5), og indkoblingstiden for kraftudtagsakslen (9) afhængigt af en eventuelt trykforøgelse, idet ventilen (4) har en indløbsåbning (A) og en udløbsåbning (B), der står i direkte forbindelse med hinanden, samt en lækåb-25 ning (C), som via en lækventil (20), der er placeret i dæmperventilens (4) hus (10), står i forbindelse med dæmperventilens indløbs- og udløbsåbninger (A og B), idet lækventilen (20) ved hjælp af sine påvirkningsorganer automatisk regulerer forholdet mellem strømningerne gennem udløbsåbningen (B) og lækåbningen (C) i dæmperventilen (4) 30 og trykket af strømningen til koblingen (5) gennem udløbsåbningen (B), kendetegnet ved, at DK 159383 B lækventilen består af en glider (20), der er placeret i en boring (22), og en åbning (21) i bunden af boringen (22), hvilken åbning (21) står i direkte forbindelse med dæmperventilens (4) indløbs- og udløbsåbninger (A og B), og hvilken åbnings (21) 5 diameter er mindre end boringens (22) og gliderens (20) diame ter, idet den mod boringen (22) placerede kant af åbningen (21) fungerer som sædeflade for glideren (20), og at lækventilens (20) påvirkningsorganer omfatter en boringslignende lukkekanal (11) med et bevægeligt lukkestempel (12) og 10 et arbejdsstempel (16), der er placeret i den nævnte boring (22) i lækventilen (20), hvilket arbejdsstempel (16) virker på lækventilen ved hjælp af en fjeder (19), idet lukkekanalen (11) og boringen (22) står i forbindelse med hinanden.A damping valve for the clutch (5) of a power take-off shaft (9) on a tractor, which damping valve (4) is mounted between a clutch valve (3) and the clutch (5) in a pressure pipe leading from a hydraulic pump (2), driven by the tractor engine, to the clutch (5) of the PTO shaft (9), and which damper valve (4) has means (10-22) adapted to respond to the pressure in the flow passing through 20 the damper valve (4), which means is adapted to automatically regulate the pressure in the flow leading to the clutch (5) and the switch-on time of the PTO shaft (9), depending on any pressure increase, the valve (4) having an inlet opening (A) and an outlet opening (B) communicating directly with each other, and a leakage opening (C) which communicates with a leak valve (20) located in the housing (10) of the damper valve (4). the inlet and outlet openings (A and B) of the damper valve, the leakage valve (20) having its influence means regulate automatically the relationship between the flows through the outlet opening (B) and the leakage opening (C) in the damper valve (4) 30 and the pressure of the flow to the coupling (5) through the outlet opening (B), characterized in that the DK 159383 B leakage valve consists of a slider ( 20) located in a bore (22) and an opening (21) at the bottom of the bore (22), which opening (21) is in direct communication with the inlet and outlet openings (A and B) of the damper valve (4). and the diameter of the aperture (21) is smaller than the diameters of the bore (22) and the slider (20), the edge of the aperture (21) positioned against the bore (22) acts as a seat surface for the slider (20) and (20) actuating means comprise a bore-like closure channel (11) with a movable closure piston (12) and a working piston (16) located in said bore (22) in the leak valve (20), which working piston (16) acts on the leak valve. by means of a spring (19), closing cap the link (11) and the bore (22) are interconnected. 2. Dæmperventil ifølge krav 1, 15 kendetegnet ved, at lukkekanalen (11) står i forbindelse med dæmperventilens indløbsåbning (A), og at lukkekanalen (11) står i forbindelse med den nævnte boring (22) i den ende af boringen (22), der ligger modsat åbningen (21), via en boring (13), der strækker sig radialt gennem boringens (22) væg. 20Damper valve according to claim 1, 15, characterized in that the closing channel (11) communicates with the inlet opening (A) of the damper valve and that the closing channel (11) communicates with said bore (22) at the end of the bore (22). located opposite the opening (21) via a bore (13) extending radially through the wall of the bore (22). 20 3. Dæmperventil ifølge krav 1 eller 2, kendetegnet ved, at lukkestemplets (12) diameter er mindre end lukkekanalens (11) diameter, så at der mellem kanalen (11) og stemplet (12) findes et lukkespillerum, gennem hvilket der kan strømme olie forbi stemplet (12). 25Damper valve according to claim 1 or 2, characterized in that the diameter of the closing piston (12) is smaller than the diameter of the closing channel (11), so that there is a clearance between the channel (11) and the piston (12) through which oil can flow. past the plunger (12). 25 4. Dæmperventil ifølge krav 2 eller 3, kendetegnet ved, at arbejdsstemplet (16) har en stempelstang (17), der er rettet mod lækventilen (20), og på hvilken stempelstang (17) der er monteret en skruefjeder (19), der er placeret mellem stemplet (16) og lækventilen (20), og som skyder disse bort 30 fra hinanden, idet stempelstangen (17), når fjederen (19) er trykket sammen, trykker direkte mod lækventilens glider (20), og at stempelstangen (16) har en tap (18), der er rettet modsat i forhold til stempelstangen (17), idet der mellem boringens (22) væg og tappen (18) findes et ringformet rum (14), via hvilket lukkekanalen (11) 35 står i forbindelse med den nævnte boring (13).Suspension valve according to claim 2 or 3, characterized in that the working piston (16) has a piston rod (17) directed against the leak valve (20) and on which piston rod (17) is mounted a screw spring (19) which is positioned between the piston (16) and the leak valve (20), and which pushes them away from each other, the piston rod (17), when the spring (19) is compressed, presses directly against the slider (20) of the leak valve and the piston rod (20) 16) has a tab (18) which is directed opposite to the piston rod (17), there being between the wall of the bore (22) and the pin (18) an annular space (14) through which the closing channel (11) 35 stands in connection with said bore (13).
DK225885A 1984-05-22 1985-05-21 SHUTTER VALVE FOR CLUTCH TO A POWER SHAFT ON A TRACTOR DK159383C (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI842051A FI72931C (en) 1984-05-22 1984-05-22 Damping valve for the clutch in a tractor's PTO shaft.
FI842051 1984-05-22

Publications (4)

Publication Number Publication Date
DK225885D0 DK225885D0 (en) 1985-05-21
DK225885A DK225885A (en) 1985-11-23
DK159383B true DK159383B (en) 1990-10-08
DK159383C DK159383C (en) 1991-03-18

Family

ID=8519118

Family Applications (1)

Application Number Title Priority Date Filing Date
DK225885A DK159383C (en) 1984-05-22 1985-05-21 SHUTTER VALVE FOR CLUTCH TO A POWER SHAFT ON A TRACTOR

Country Status (7)

Country Link
BR (1) BR8502401A (en)
DK (1) DK159383C (en)
FI (1) FI72931C (en)
FR (1) FR2564922B1 (en)
GB (1) GB2159228B (en)
NO (1) NO159842C (en)
SE (1) SE458298B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2336641B (en) * 1998-04-25 2002-10-16 Agco Gmbh & Co Hydraulic system for a power-take-off clutch
CN105378298B (en) * 2013-07-24 2017-11-17 舍弗勒技术股份两合公司 Hydraulic system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE543023A (en) * 1954-12-03 1900-01-01
DE1284184B (en) * 1964-09-11 1968-11-28 Hengstler Hydraulik Control unit for the alternating loading of two hydraulically operated friction clutches
US3363649A (en) * 1965-12-27 1968-01-16 Allis Chalmers Mfg Co Fluid pressure control valve
US4083382A (en) * 1976-06-03 1978-04-11 J. I. Case Company Regulating valve with hydraulic detent
US4465168A (en) * 1981-11-25 1984-08-14 Kabushiki Kaisha Komatsu Seisakusho Pressure control system for a transmission
ATE25871T1 (en) * 1982-06-23 1987-03-15 Deere & Co HYDRAULIC REGULATOR.

Also Published As

Publication number Publication date
GB2159228B (en) 1988-09-01
FR2564922A1 (en) 1985-11-29
NO159842C (en) 1989-02-15
FI72931C (en) 1987-08-10
SE458298B (en) 1989-03-13
FR2564922B1 (en) 1990-09-14
GB8512789D0 (en) 1985-06-26
NO159842B (en) 1988-11-07
BR8502401A (en) 1986-01-21
GB2159228A (en) 1985-11-27
NO852019L (en) 1985-11-25
DK159383C (en) 1991-03-18
FI72931B (en) 1987-04-30
SE8502395L (en) 1985-11-23
SE8502395D0 (en) 1985-05-14
FI842051A (en) 1985-11-23
DK225885D0 (en) 1985-05-21
FI842051A0 (en) 1984-05-22
DK225885A (en) 1985-11-23

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