EP0250781B1 - Elément hydraulique de transmission de force - Google Patents

Elément hydraulique de transmission de force Download PDF

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Publication number
EP0250781B1
EP0250781B1 EP87106578A EP87106578A EP0250781B1 EP 0250781 B1 EP0250781 B1 EP 0250781B1 EP 87106578 A EP87106578 A EP 87106578A EP 87106578 A EP87106578 A EP 87106578A EP 0250781 B1 EP0250781 B1 EP 0250781B1
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EP
European Patent Office
Prior art keywords
bellows
corrugation
cylinder
transmission element
peaks
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP87106578A
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German (de)
English (en)
Other versions
EP0250781A2 (fr
EP0250781A3 (en
Inventor
Manfred Dipl.-Ing. Wünschmann
Bernd Dr.-Ing. Faber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Witzenmann GmbH
Original Assignee
Witzenmann GmbH
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Filing date
Publication date
Application filed by Witzenmann GmbH filed Critical Witzenmann GmbH
Publication of EP0250781A2 publication Critical patent/EP0250781A2/fr
Publication of EP0250781A3 publication Critical patent/EP0250781A3/de
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Publication of EP0250781B1 publication Critical patent/EP0250781B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets
    • F01L1/25—Hydraulic tappets between cam and valve stem
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2309/00—Self-contained lash adjusters

Definitions

  • the invention relates to a hydraulic power transmission element with a cylinder which is open in an axial direction, a piston arranged therein, which projects beyond the cylinder opening and which, together with the cylinder, delimits a cylinder space, and with a single cylinder cylinder piston which extends essentially in the axial direction.
  • Unit concentrically surrounding annular corrugated bellows, which has several bellows waves with troughs and wave peaks and the two bellows ends are each tightly connected to one of the parts forming the cylinder-piston unit, a variable pressure medium volume being formed between the cylinder-piston unit and the bellows is connected to the cylinder chamber via at least one opening or recess in the cylinder and / or piston with the interposition of a check valve closing under excess pressure in the cylinder chamber.
  • Such power transmission elements with bellows made of metal known from DE-OS 35 06 730 are used, for example, to which the invention is not limited, in internal combustion engines in the valve drive as an intermediate element between the cams of the camshaft and the valves, in order to automatically occur wear and temperature-related changes in length to ensure a play-free power transmission.
  • As a closed system they are independent of a pressurized oil supply and consequently also of the running and maintenance of the machine.
  • the effect of wear on the valve seat is that the total length of the cylinder-piston unit must be axially shortened, that is, the displacement of pressure oil from the cylinder chamber is required, which essentially takes place via the sliding seat between the cylinder and the piston.
  • a corresponding pressure oil displacement results when the engine is stopped and the cam is positioned under the action of the force of the valve spring.
  • the amount of pressurized oil displaced in the course of time and while the engine is at a standstill must be absorbed by the bellows space formed by the bellows element without the internal pressure increasing above a limit value there.
  • a loss of pressure oil in the cylinder chamber which results when the machine is at a standstill due to the reduction of the excess pressure in the cylinder chamber, can be sucked in or compensated for immediately from the reservoir in the bellows chamber via the check valve while the machine is running, without the internal pressure in the bellows chamber below to lower a certain limit.
  • the bellows space compensates for temperature-related changes in volume of the pressure medium, so that the transmission element as a whole always ensures a play and maintenance-free connection between the cam and the valve stem.
  • two bellows arranged concentrically to one another are provided to form the bellows space, which are located in an annular space surrounding the cylinder piston unit, the outer wall of which is concentric with the cylinder piston unit and is formed by a jacket connected, for example, to the cylinder base.
  • the ends of the bellows which are located at substantially the same height, are connected to the piston on the one hand and to the casing on the other hand, while their opposite ends are fastened to a common ring plate which is arranged axially displaceably in the said annular space and is also below corresponding change in length of the bellows axially adjusted according to the pressure medium volume to be absorbed by the bellows chamber.
  • this force transmission element would result in a correspondingly reverse manner if the distance between two components involved in the force transmission would increase in the course of operation. Then, if the bellows were shortened, a volume of pressure medium would not have to be taken in gradually from the bellows, but a volume of pressure medium would have to be gradually released with a corresponding increase in the length of the bellows.
  • the object of the invention is to modify and simplify a power transmission element of the type mentioned above and described in more detail above in such a way that to form the bellows space while reducing the total pressure medium volume and reducing the vibrating masses, only the use of a bellows with at least one specially designed Bellows shaft is required and there is a reduction in the cost of material and manufacturing, and in terms of space, a reduction in the size of the force transmission element and thus a corresponding saving in space at the installation site.
  • This task is based on a power transmission element of the type mentioned solved in that at least one of the troughs of the bellows adjacent to two flanks has an inner diameter smaller than that of the other troughs and / or that at least one of the wave peaks of the bellows adjacent to two flanks has a larger outer diameter than the other wave peaks.
  • the problem is solved only by the fact that at least one, preferably of course several, of the troughs or wave peaks of the bellows have an inner diameter or larger outer diameter that is significantly smaller than that of the other wave troughs or wave peaks.
  • the volume released within or in addition to the larger bellows waves in the radial direction is also greater than the volume that may be displaced by the axial compression of the other bellows waves and then to be absorbed by the larger bellows waves, so that overall in or next to the larger ones in the radial direction Bellows waves an additional volume is available. This is done, which is to be emphasized in particular, without a significant pressure increase within the bellows compared to a bellows of the same size waves, which would have to absorb an additional pressure medium volume only by inflating the wave flanks.
  • the bellows shafts which are larger or smaller in inner diameter, in addition to the flaring of their flanks which occurs equally for all bellows shafts due to the pressure medium increase caused by the additional volume, also with their base points or vertices at the expense of the other bellows shafts move axially in such a way that an additional volume is released in or next to the bellows waves larger in the radial direction, which is also larger than the volume possibly displaced in the other bellows waves, which essentially allows the bellows waves larger in the radial direction to accommodate an additional one Deliver volume, while the other bellows waves serve to absorb the movement resulting from the simultaneous shortening of the total length of the bellows.
  • the other bellows shafts must also be dimensioned accordingly in their radial extension, i.e. they must be designed so that their sum in terms of flexibility and service life alone is sufficient to accommodate the axial change in length of the cylinder-piston unit during operation, while the bellows shafts, which are larger in the radial direction, are sufficient their number and radial extension are essentially to be interpreted to the size of the additional volume to be accommodated, which results from the shortening of the total length of the bellows, the volume displaced from the cylinder space and the increase in the pressure medium volume with increasing temperature.
  • the total volume of pressure medium required between two spaces formed by two bellows is also avoided by the invention.
  • bellows shafts with peaks of larger outside diameter or troughs of smaller inside diameter these can be arranged next to one another.
  • one of the other bellows shafts is arranged between them, i.e. not all bellows shafts which are larger in the radial direction are grouped on the one hand and all other bellows shafts on the other hand are grouped side by side.
  • the bellows length can be divided into a first section with shafts of the other diameter of its shaft summit and a second section with shafts of the larger and the reduced outer diameter of its summit or the smaller and the enlarged inner diameter of its wave trough, so that the said one the first section essentially serves to compensate or accommodate the change in length of the bellows, while the said second section essentially serves to simultaneously accommodate an enlarged volume.
  • said second section is blocked against length changes, so that it remains unaffected by the change in the overall length of the bellows.
  • Such blocking can take place, for example, in that between the two bellows sections mentioned, a rigid support part engages in the trough there, which is fastened together with the free end of the second bellows section to the cylinder or to the piston.
  • Fig. 1 shows in axial half section the cylinder 1 and the axially displaceable in its bore and thus guided relative to the cylinder 1 piston 2 of a power transmission element, for example between the cam of a camshaft and the valve stem of the valve of an internal combustion engine, for example the cam in contact the end face 3 of the cylinder and the valve stem may be in contact with the end face 4 of the piston 2.
  • Cylinder 1 and piston 2 form a cylinder space 5, which is connected to the outside thereof by an axial bore 6 and a radial bore 7 of the cylinder-piston unit thus formed.
  • the bore 6 is closed by the ball 8 of a check valve that closes under excess pressure in the cylinder chamber 5 and is pressed against the valve seat 10 by a spring 9, which is supported against the bottom of a cage 11.
  • the cage 11 sits in a recess 12 of the piston 2 and is held against the bottom 13 of this recess by a spring 14, which in turn is supported against the cylinder 1.
  • the cage 11 has openings 15, via which the cylinder space 5 is connected to the valve.
  • cylinder 1 and piston 2 form a respective collar 16 and 17 with the same outside diameter, with which the ends of a bellows, designated as a whole with 18, are welded, which concentrically surrounds the unit formed by cylinder 1 and piston 2.
  • the bellows 18 consists of bellows shafts 19 arranged alternately next to one another and bellows shafts 20 provided with a noticeably larger outer diameter of their shaft peaks, all bellows waves starting from a uniform inner diameter of their shaft peaks which essentially corresponds to the outer contour of the cylinder-piston unit.
  • the system closed by the bellows 18 is filled with a hydraulic pressure fluid.
  • this bellows has some bellows shafts 20 which are enlarged in the outer diameter of their summit compared to the other bellows shafts 19 and which, in the manner described in detail above, have an additional volume absorption by the bellows 18 allow without significant internal pressure increase, while the other bellows shafts 19 essentially or at least largely predominantly perform the task of accommodating the length reduction of the bellows and the axial displacement of the base points of the bellows shafts 20.
  • Fig. 2 shows a radial half section and in isolation, a bellows 21 with the same inner diameter of the troughs for all bellows and the outer diameter of their wave peaks compared to the other bellows waves 22 larger bellows 23 and adjacent bellows 24 with last compared to the other bellows 22 reduced outer diameter of their wave peak .
  • the larger bellows shafts 23 are always spaced apart from one another by a smaller bellows shaft 24, as is also the case in the example according to FIG. 1.
  • the bellows shafts 24 with a reduced outer diameter of their shaft summit serve, even more than was the case with FIG. 1, to enable the flanks of the bellows shafts 23 with an enlarged outer diameter of their shaft summit to move axially away from one another, since at one determined pressure prevailing in the bellows 21, the axial force components exerted by the flanks of the small bellows shafts 24 are substantially lower than those exerted by the flanks of the large bellows shafts 23.
  • the volume displaced by compressing the bellows shafts 24 is considerably smaller than the volume which arises in the bellows shafts 23 as their flanks diverge, so that the bellows shafts 23 can correspondingly take up an additional volume.
  • the bellows designated as a whole by 25, is tightly connected to the cylinder 1 with the free end of its section with bellows shafts 26 having a larger outer diameter of its shaft top and bellows shafts 27 with a reduced diameter of its shaft top, while the free end of its section is connected to the other bellows shafts 28 the piston 2 is tightly connected.
  • the bellows section connected to the cylinder 1 is bridged by a support body 29 which is fastened on the one hand to the cylinder 1 with the bellows end and on the other hand engages with its free end 30 in the trough 31 separating the two bellows sections from one another and thus prevents that in relation to FIG Fig. 3 right bellows section can perform a change in length.
  • This bellows section in the manner already explained with reference to FIG. 2 with respect to the shafts 23 and 24 serves exclusively to accommodate an additional pressure medium volume, while the bellows section having the other bellows shafts 28 serves practically exclusively to accommodate the change in length which occurs when the cylinders move axially 1 and piston 2 in the sense of shortening the total length of the cylinder-piston unit.
  • the arrangement is such that, with the inner diameter of the troughs remaining the same, the outer diameter of the wave peaks of the bellows shafts 39 increases continuously over the bellows length, so that the bellows waves are seen to an increasing extent from left to right an additional volume can serve.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Diaphragms And Bellows (AREA)

Claims (9)

1. Elément hydraulique de transmission de force comprenant un cylindre (1) ouvert dans une direction axiale, un piston (2) monté dans ce cylindre, qui émerge de l'ouverture du cylindre et qui, en combinaison avec le cylindre (1), délimite une chambre de cylindre (5), ainsi qu'un unique soufflet annulaire ondulé (18, 21, 25, 31, 32, 33, 38, 40), s'étendant sensiblement dans la direction axiale, qui entoure concentriquement l'unité cylindre-piston, et qui présente plusieurs ondes (19, 20, 22, 23, 24, 26, 27, 28, 34, 35, 36, 37, 39, 41) comprenant elles-même des creux d'onde et des sommets d'onde,et dont les deux extrémités sont fixées à joint étanche, chacune à l'une des parties (1, 2) qui forment l'unité cylindre-piston, élément dans lequel il se forme entre l'unité cylindre-piston et le soufflet (18, 21, 25, 33, 38, 40) un volume variable de fluide de pression qui est relié à la chambre (5) du cylindre par l'intermédiaire d'au moins une ouverture ou d'un évidement (6, 7) ménagé dans le cylindre (1) et/ou dans le piston (2), avec interposition d'un clapet anti-retour (8) qui se ferme en réponse à une surpression régnant dans la chambre (5) du cylindre, caractérisé en ce qu'au moins un des creux d'onde du soufflet (18, 21, 25, 32, 33, 38, 40) attenant à deux flancs présente un diamètre intérieur plus petit que celui des autres creux d'onde et/ou au moins qu'au moins un l'un des sommets d'onde du soufflet (18, 21, 25, 32, 33, 38, 40) qui est attenant à deux flancs présente un diamètre extérieur plus grande que à celui des autres sommets d'onde.
2. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que le diamètre intérieur est identique pour tous les creux d'onde du soufflet (18, 21, 25, 38).
3. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que le diamètre extérieur est identique pour tous les sommets d'onde du soufflet (32, 33).
4. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que, dans le cas où plusieurs ondes du soufflet présentent des sommets de plus grand diamètre extérieur ou des creux d'onde de plus petit diamètre intérieur (34), ces ondes sont disposées les unes à côté des autres.
5. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que, dans le cas où plusieurs ondes du soufflet possèdent des sommets de plus grand diamètre extérieur (20) ou des creux d'onde de plus petit diamètre intérieur (35), au moins une des autres ondes (19, 37) du soufflet est disposée entre ces ondes.
6. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que, dans le cas où plusieurs ondes (23, 26) du soufflet possèdent des sommets de plus grand diamètre extérieur ou des creux d'onde de plus petit diamètre intérieur, il est prévu entre ces ondes une onde ( 24, 27 ) possédant un diamètre extérieur de sommet réduit comparativement aux autres ondes ( 22, 28 ) ou un diamètre intérieur de creux d'onde agrandi comparativement à ces autres ondes.
7. Elément de transmission de force hydraulique selon la revendication 6, caractérisé en ce que la longueur du soufflet est divisée en un premier segment possédant des ondes ( 22, 28 ) présentant un autre diamètre de sommet d'onde et un deuxième segment possédant des ondes qui présentent un diamètre extérieur de sommet d'onde agrandi (23, 26) ou réduit (24, 27) ou des ondes présentant un diamètre intérieur de creux d'onde plus petit ou agrandi.
8. Elément de transmission de force hydraulique selon la revendication 7, caractérisé en ce que le deuxième segment est bloqué à l'encontre de la variation de sa longueur.
9. Elément de transmission de force hydraulique selon la revendication 1, caractérisé en ce que le diamètre extérieur des sommets d'onde et/ou le diamètre intérieur des creux d'onde des ondes (39, 41) du soufflet varient continuellement, éventuellement sans palier, sur la longueur du soufflet, pour passer d'une valeur minimale à une valeur maximale.
EP87106578A 1986-06-28 1987-05-06 Elément hydraulique de transmission de force Expired - Lifetime EP0250781B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3621750 1986-06-28
DE19863621750 DE3621750A1 (de) 1986-06-28 1986-06-28 Hydraulisches kraftuebertragungselement

Publications (3)

Publication Number Publication Date
EP0250781A2 EP0250781A2 (fr) 1988-01-07
EP0250781A3 EP0250781A3 (en) 1988-02-10
EP0250781B1 true EP0250781B1 (fr) 1990-11-22

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EP87106578A Expired - Lifetime EP0250781B1 (fr) 1986-06-28 1987-05-06 Elément hydraulique de transmission de force

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EP (1) EP0250781B1 (fr)
DE (1) DE3621750A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9100074U1 (fr) * 1990-01-30 1991-03-28 Buchner, Martin, 8000 Muenchen, De
DE19930852C1 (de) * 1999-07-03 2000-07-27 Witzenmann Metallschlauchfab Schweißverbindung
WO2009050341A1 (fr) * 2007-10-17 2009-04-23 Valeo Systemes De Controle Moteur Butee hydraulique autonome

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2109815A (en) * 1935-06-13 1938-03-01 Packard Motor Car Co Valve operating mechanism
DE1005787B (de) * 1953-09-21 1957-04-04 Daimler Benz Ag Selbsttaetiges hydraulisches Nachstellglied
IT1180083B (it) * 1984-07-24 1987-09-23 Riv Officine Di Villar Perosa Punteria idraulica a tenuta stagna per il comando del moto di una valvola di un motore endotermico
DE3506730A1 (de) * 1985-02-26 1986-04-17 Daimler-Benz Ag, 7000 Stuttgart Hydraulisches ventilspielausgleichselement fuer brennkraftmaschinen
US4590899A (en) * 1985-05-17 1986-05-27 Stanadyne, Inc. Self-contained lash adjuster with shell mounted cartridge assembly

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Publication number Publication date
EP0250781A2 (fr) 1988-01-07
EP0250781A3 (en) 1988-02-10
DE3621750A1 (de) 1988-01-14

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