EP0250781A2 - Elément hydraulique de transmission de force - Google Patents

Elément hydraulique de transmission de force Download PDF

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Publication number
EP0250781A2
EP0250781A2 EP87106578A EP87106578A EP0250781A2 EP 0250781 A2 EP0250781 A2 EP 0250781A2 EP 87106578 A EP87106578 A EP 87106578A EP 87106578 A EP87106578 A EP 87106578A EP 0250781 A2 EP0250781 A2 EP 0250781A2
Authority
EP
European Patent Office
Prior art keywords
bellows
shafts
cylinder
power transmission
transmission element
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.)
Granted
Application number
EP87106578A
Other languages
German (de)
English (en)
Other versions
EP0250781A3 (en
EP0250781B1 (fr
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
Priority date (The priority date 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 date listed.)
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
Application granted granted Critical
Publication of EP0250781B1 publication Critical patent/EP0250781B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 open in an axial direction, a piston axially displaceably arranged therein, projecting beyond the cylinder opening, and a pressure medium volume which is essentially concentrically surrounding this cylinder piston unit and is received by a bellows element with at least one annularly corrugated bellows and which has at least one opening or recess of the cylinder and / or piston and a check valve arranged therein and closing under excess pressure in the cylinder chamber between the cylinder chamber and bellows chamber, wherein a bellows end is tightly connected to one of the parts forming the cylinder piston unit.
  • 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 space such as occurs when the machine is at a standstill by reducing the excess prevailing in the cylinder space pressure results, when the machine is running, it is immediately sucked in or balanced out of the stock in the bellows chamber via the check valve without causing the internal pressure in the bellows chamber to drop below 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 during operation. Then, if the bellows were shortened, a volume of pressure medium would not have to be added gradually from the bellows, but a volume of pressure medium would have to be gradually released if the bellows were increased in length.
  • 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 only the use of a bellows is required to form the bellows space while reducing the total pressure medium volume and reducing the vibrating masses, and accordingly in terms of material and manufacturing costs, a reduction in cost and a reduction in size of the power transmission element and thus a corresponding space saving at the installation site.
  • the problem is solved only by the fact that at least one, preferably of course several, of the bellows shafts have a significantly larger outer diameter or smaller inner diameter than the other bellows shafts.
  • the volume released within or next 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 taken up 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 happens, which should 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 volume deliver, 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 is also reduced by the invention and a vibration-related permanent displacement of a part of the pressure medium volume between two spaces formed by two bellows is avoided.
  • bellows shafts of larger outer diameter or smaller inner diameter there are several bellows shafts of larger outer diameter or smaller inner diameter, these can be arranged side by side.
  • one of the other bellows shafts is arranged between them, ie not all bellows shafts which are larger in the radial direction 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 and a second section with shafts of the larger and the reduced outside diameter or the smaller and the enlarged inside diameter, so that said first section essentially compensates or the recording of the change in length of the bellows, while the said second section serves essentially the simultaneous recording of 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.
  • a bellows with five bellows shafts of larger outer diameter and six other bellows shafts has a bellows length based on a bellows inner diameter of 1.0 of 2.2, an outer diameter of the other bellows shafts of 1.4 and an outer diameter of the larger bellows shafts of 1.8.
  • an outer diameter was obtained based on a bellows inner diameter of 1.0 with a bellows length of 2.2 the reduced bellows waves of 1.4, the other bellows waves of 1.6 and the bellows waves with a larger outer diameter of 1.8.
  • 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 chamber 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 is seated 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 through which the cylinder chamber 5 with the valve connected is.
  • 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 which are provided with an appreciably larger outer diameter, all bellows shafts starting from a uniform inner diameter 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 in the outside diameter above the other bellows shafts 19 enlarged bellows shafts 20, which, in the manner described in the introduction, permit additional volume absorption by the bellows 18 without any appreciable increase in internal pressure, while the other bellows shafts 19 essentially or at least largely predominantly the task of absorbing 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 for all bellows shafts and the outer diameter compared to the other bellows shafts 22 larger bellows shafts 23 and adjacent bellows shafts 24 with reduced outer diameter compared to the other bellows shafts 22.
  • 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 serve, even more than was the case with FIG. 1, to enable the flanks of the bellows shafts 23 with an enlarged outer diameter to move axially away from one another, since there is a specific one in the bellows 21 prevailing pressure, the axial force components exerted by the flanks of the small bellows shafts 24 are significant are less 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.
  • FIG. 3 shows the installation of a bellows of the type described with reference to FIG. 2 in a cylinder piston unit according to FIG. 1.
  • the latter is provided with the designations used in FIG. 1, so that in this respect also the function of the description of FIG. 1 is referred.
  • the bellows, generally designated 25, is tightly connected to the cylinder 1 with the free end of its section with bellows shafts 26 of larger outer diameter and bellows shafts 27 of reduced diameter, while the free end of its section is sealed with the other bellows shafts 28 with the piston 2 connected is.
  • 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 perform a change in length can.
  • This bellows section serves in the manner already explained with reference to FIG.
  • the arrangement is such that, with the inner diameter remaining the same, the outer diameter of the bellows shafts 39 increases continuously over the bellows length, so that the bellows shafts, from left to right, increasingly serve to accommodate an additional volume can.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Diaphragms And Bellows (AREA)
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 true EP0250781A2 (fr) 1988-01-07
EP0250781A3 EP0250781A3 (en) 1988-02-10
EP0250781B1 EP0250781B1 (fr) 1990-11-22

Family

ID=6303945

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87106578A Expired - Lifetime EP0250781B1 (fr) 1986-06-28 1987-05-06 Elément hydraulique de transmission de force

Country Status (2)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009050341A1 (fr) * 2007-10-17 2009-04-23 Valeo Systemes De Controle Moteur Butee hydraulique autonome

Families Citing this family (2)

* 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

Citations (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
EP0169437A2 (fr) * 1984-07-24 1986-01-29 RIV-SKF OFFICINE DI VILLAR PEROSA S.p.A Taquet hydraulique étanche à l'huile pour la commande d'une soupape d'un moteur à combustion interne
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

Patent Citations (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
EP0169437A2 (fr) * 1984-07-24 1986-01-29 RIV-SKF OFFICINE DI VILLAR PEROSA S.p.A Taquet hydraulique étanche à l'huile pour la commande d'une soupape d'un moteur à combustion interne
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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009050341A1 (fr) * 2007-10-17 2009-04-23 Valeo Systemes De Controle Moteur Butee hydraulique autonome

Also Published As

Publication number Publication date
EP0250781A3 (en) 1988-02-10
DE3621750A1 (de) 1988-01-14
EP0250781B1 (fr) 1990-11-22

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