EP1267046B1 - Hydraulisches Spielausgleichselement - Google Patents
Hydraulisches Spielausgleichselement Download PDFInfo
- Publication number
- EP1267046B1 EP1267046B1 EP02254170A EP02254170A EP1267046B1 EP 1267046 B1 EP1267046 B1 EP 1267046B1 EP 02254170 A EP02254170 A EP 02254170A EP 02254170 A EP02254170 A EP 02254170A EP 1267046 B1 EP1267046 B1 EP 1267046B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- adjuster
- assembly
- plunger assembly
- valve
- cam
- 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 - Fee Related
Links
Images
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
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
-
- 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
- F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
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- 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
- F01L2301/00—Using particular materials
-
- 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
- F01L2303/00—Manufacturing of components used in valve arrangements
Definitions
- This invention relates to hydraulic lash adjusters for taking up slack in a valve train, and to valve train assemblies which incorporate hydraulic lash adjusters.
- the valve train assembly 2 comprises a rocker arm 4 and a hydraulic lash adjuster 6.
- One end 8 of the rocker arm 4 engages the stem 10 of a valve 11.
- the other end 12 of the rocker arm is mounted for pivotal movement on the lash adjuster 6.
- the rocker arm 4 is provided with a roller 14 mounted on an axle 16 carried by the rocker arm 4.
- a cam 18 mounted on a cam shaft 15 has a lobe 17 which can engage the roller 14 and thus pivot the rocker arm 4 anti-clockwise as shown in the drawing. This depresses the valve stem 10 against the force of a valve spring (not shown) and thus opens the valve. As the cam continues to rotate, and the base circle 19 of the cam profile again engages the roller 14, the valve spring returns the valve and the rocker arm 4 to the position shown in Figure 1.
- a hydraulic lash adjuster has an oil-containing chamber and a spring arranged to enlarge the chamber and thus extend the lash adjuster. Oil flows into the chamber via a one-way valve, but can escape the chamber only slowly, for example via closely-spaced leakdown surfaces.
- the lash adjuster 6 of Figure 1 can extend to accommodate any slack in the valve train assembly, such as between the cam 18 and the roller 14. After it is extended, however, the oil-filled chamber provides sufficient support for the pivoting movement of the rocker arm 4.
- the base circle 19 of the cam 18 It is important for the base circle 19 of the cam 18 to be concentric with respect to the axis of rotation of the cam shaft 15. Any slight eccentricity (“run-out”) could cause the valve to close later than it should, or open during the movement of the base circle past the roller 14.
- the cam 18 is often formed by sintering and may not have, in its initial state, particularly accurate dimensions. Accordingly, it is conventional, before assembly, to grind either the outer surface, including the base circle 19, of the cam 18, or to grind the inner diameter which is fitted to the cam shaft 15, to ensure accurate concentricity of the base circle 19 relative to the axis of rotation of the cam shaft 15.
- lash adjusters which incorporate a seal to prevent leakage of oil from the high-pressure chamber, and in which the chamber valve is arranged such that it is normally open (known as “sealed-leakdown" adjusters). See US-A-5622147. This would permit a small amount of shortening of the lash adjuster before the valve closes as a result of the hydrodynamic force of the oil flowing out of the chamber. However, the amount of lift loss produced is somewhat uncertain, and will depend significantly on oil viscosity and hence temperature, as well as other factors. Also, this form of lash adjuster can sometimes encounter problems when a hot engine is stopped with a valve partially open. The pressure of the valve spring on the lash adjuster causes the high-pressure chamber to remain sealed, so that, if the engine cools and negative lash is created, oil cannot flow out of the chamber and the lash is therefore not accommodated.
- EP-A-0547653 discloses a lash adjuster incorporating a two-part plunger assembly, the parts having therebetween an additional chamber sealed by a diaphragm. A seal is provided between the plunger assembly and the cylinder in which it is housed to provide a sealed hydraulic system. Within the system, leakdown fluid flows from the high pressure chamber to the additional chamber and is controlled by the clearance between the plunger assembly and the cylinder.
- the high-pressure chamber is sealed by a sealing means engaging both the body of the lash adjuster and the plunger as the plunger moves inwardly, thus preventing further inward movement.
- the arrangement is such that as the cam turns, and returns to base circle, and the pressure on the plunger decreases, the plunger and sealing means separate, preferably assisted by a biasing means such as a leaf spring. Accordingly, the pressure in the chamber is relieved whenever the base circle of the cam is reached. Because the chamber is open, the plunger assembly can be pushed inwardly by a certain amount to guarantee valve closure before the chamber is again closed.
- a hydraulic lash adjuster which provides lift loss means that the base circle radius variation of the cam no longer has to be minimised by grinding, allowing the use of net-shaped cam shaft technology instead of more expensive ground cams.
- FIG. 3 shows a lash adjuster 30 according to a first embodiment of the invention.
- the lash adjuster has a cylindrical body 23 formed with a longitudinal blind bore 24.
- the plunger assembly 26 and blind bore 24 define between them a high-pressure oil chamber 28 at the lower end of the lash adjuster 30.
- the plunger assembly 26 is formed with a relatively narrow waist 31 so that a low-pressure oil chamber 32 is formed between this waist and the bore 24. Oil from the associated engine can enter the chamber 32 via an aperture 33.
- the lash adjuster 30 is provided with an annular polytetrafluoroethylene (PTFE) seal 34 (also shown in cross-section in Figure 4).
- PTFE polytetrafluoroethylene
- the cylindrical outer surface of the seal 34 is an interference fit in, and sealingly engages, the bore 24.
- the upper surface of the seal 34 can sealingly engage a circumferential outer sealing surface 36 on the bottom of the plunger assembly 26.
- a spring 40 engages the upper, central part of a cap-shaped retainer 42 (shown in plan view in Figure 5 and side view in Figure 6), and forces the retainer 42 into engagement with the plunger assembly 26, the retainer 42 engaging the centre of the base of the assembly 26.
- the upper part of the retainer is located within the annular seal 34 and the circumferential outer part is located under the annular seal.
- the spring 40 pushes the seal 34 and the plunger assembly 26 outwardly of the bore 24.
- oil can flow from the low pressure chamber 32 around the side of the plunger assembly, through a gap 44 between the sealing surface 36 and the seal 34 and into the high pressure chamber 28.
- the outer diameter of the lower part of the plunger assembly 26 is sufficiently smaller than the diameter of the bore 24 to allow oil readily to flow therebetween. Accordingly, the plunger assembly can move outwardly to take up slack in the valve train. Any significant outward movement of the plunger assembly will also result in the seal 34 being shifted in the same direction by the outer part of the retainer 42.
- the lash adjuster 30 is also provided with a leaf spring 46, shown in plan view in Figure 7, disposed between the lower end of the plunger assembly 26 and the upper surface of the retainer 42. See also the enlarged views of Figures 8 and 9.
- the lower surface of the plunger assembly 26 is provided with a circular recess 48, which is deeper at the radially outer part thereof.
- the leaf spring 46 has four arms 50 which are located under the recess 48, and the outer ends of which are located over the PTFE seal 34.
- Figure 8 shows the state of the lash adjuster when the lobe of the cam is applying force to open the valve.
- the plunger assembly 26 is depressed, engaging the PTFE seal 34 so that the high pressure chamber 28 is closed and further inward movement of the plunger assembly 26 is thus prevented.
- the arms 50 of the leaf spring 46 are deflected upwardly by their engagement with the PTFE seal 34.
- the plunger assembly 26 When the base circle of the cam is approached, the plunger assembly 26 is allowed to move outwardly under the force of the spring 40. This of course can occur only if oil is allowed to flow into the chamber via the gap 44 ( Figure 9) which is at that stage created between the sealing surface 36 of the plunger assembly 26 and the seal 34.
- Various forces combine to ensure this movement occurs, including the resilience of the arms 50 of the leaf spring 46, the force of the spring 40 and the force holding the seal 34 against the wall of the bore 24 (which may be a combination of friction and stickiness caused by migration of PTFE into the wall). Such forces have to be sufficient to overcome the pressure holding the seal 34 against the sealing surface 36, and then any hydrodynamic forces of the oil escaping the chamber 28, which would tend to move the seal 34 upwardly.
- the spring 46 is particularly desirable in this connection, as it tends to peel apart the seal 34 and the sealing surface 36. However, the exact force exerted by the leaf spring 46 is not critical.
- the lash adjuster of Figure 3 is intended to be used with a rocker arm such as that shown at 4 in Figure 1.
- the lash adjuster could form the pivot of the arm, and the cam could operate on the rocker arm at a location between the lash adjuster and the valve stem (as in Figure 1), or various other configurations (known in themselves) could be used, for example having the lash adjuster disposed between the rocker arm and either the valve stem or the cam.
- Figure 10 shows a second embodiment, in the form of a direct-acting bucket tappet 120 incorporating a hydraulic lash adjuster 30 and arranged to move a valve stem 10 in response to the rotation of a cam 18.
- This embodiment has components corresponding to those of the Figure 3 arrangement, with like components bearing like reference numerals, and operates in the same way. The arrangement differs from the Figure 3 arrangement only insofar as the components are configured in a per se known way for use with a bucket tappet which has the low-pressure reservoir 32.
- the cams 18 used to operate the valves of the above arrangements have been formed by a sintering operation (but could alternatively have been formed by other means, such as hydroforming or hot- or cold-forming).
- no additional grinding operations have been performed on either the outer surface of the base circles or the inner surfaces of the cams.
- the base circle of each cam is not necessarily accurately concentric with respect to the axis of rotation.
- the cam 18 is thus net-shaped.
- the base circle radius variations of the cam no longer have to be minimised by grinding, because any non-concentricity of the base circle will be accommodated by inward movement of the outer end of the plunger assembly 26, thus avoiding incorrect valve opening.
- net-shaped is generally understood, and used herein, in the sense of having a shape and dimensions which are at least substantially the same as those resulting from the initial forming of the object. This does not exclude the possibility of small changes in dimensions which are a consequence of, for example, surface-treatment for the purpose of smoothing, as distinct from dimensional changes (e.g. by grinding) for the purpose of altering the function performed as a result of those dimensions.)
- the outer surface of the cam may be treated for the purpose of smoothing the exterior of the cam. This may be of particular value in the embodiment of Figure 10 when the cam operates on a direct-acting bucket tappet, rather than on a roller.
- the valve opens later and closes sooner, in relation to the rotation of the cam, than in prior art arrangements.
- the profile of the cam is altered as compared with prior art arrangements. A further alteration to the profile may be made in order to extend the ramp of the cam lobe to ensure that the movement of the outer end of the plunger assembly 26 takes place at a controlled velocity to reduce impact forces.
- the gap 44 defines the maximum amount of lift loss. This in turn is specified by the dimensions of the seal 34 and the retainer 42.
- the leaf spring 46 preferably has a thickness substantially equal to the thus-defined gap size (although if the spring is slightly thicker, this simply means it will remain in a partially-flexed condition). The gap, and hence the amount of lift loss, should:
- the size of the gap 44 is in the range of 0.1 mm to 0.3 mm, and more preferably in the range 0.15 mm to 0.25 mm.
- the spring 40 of the embodiments described above biases both the plunger assembly 26 and the seal 34 outwardly, although it does not bias these components towards each other and so does not inhibit opening of the chamber. It would alternatively be possible to have separate biasing means for the plunger assembly 26 and the seal 34; in this case, preferably, the biasing means for the seal is limited in the extent to which it can move the seal towards the plunger (e.g. by inter-engagement of the separate biasing means and the plunger, or suitable selection of the strength of this biasing means with respect to that of the leaf spring 46) so that it does not inhibit the restoration of the gap 44.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Claims (12)
- Ein hydraulischer Spieleinsteller für einen Verbrennungsmotor, wobei der Spieleinsteller Folgendes aufweist: einen Körper (23), eine Kolben- oder Plungeranordnung (26), die gleitbar innerhalb einer Bohrung (24) in dem Körper aufgenommen ist und mit dem Körper zusammenarbeitet, um eine Fluiddruckkammer (28) zu definieren, und Vorspannmittel (40) zum Drücken der Plungeranordnung (26) in einer nach außen gerichteten Richtung bezüglich der Bohrung (24), um dadurch die Druckkammer (28) zu vergrößern, um Spiel in einer Ventilantriebskette aufzunehmen, wobei der Einsteller ferner Dichtmittel (34) aufweist, die in abdichtender Weise mit dem Körper (23) in Eingriff stehen; wobei der Einsteller dadurch gekennzeichnet ist, dass die Dichtmittel (34) angeordnet sind, um in Dichteingriff mit der Plungeranordnung (26) gebracht zu werden ansprechend auf eine Bewegung der Plungeranordnung in eine nach innen gerichtete Richtung bezüglich der Bohrung, zum Einschränken einer Fluidströmung von der Druckkammer (28), um eine weitere Bewegung der Plungeranordnung in die nach innen gerichtete Richtung zu blockieren bzw. zu unterdrücken, wobei der Einsteller derart angeordnet ist, dass die Plungeranordnung aus dem Dichteingriff mit den Dichtmitteln (34) herausgebracht wird, und der Druck in der Druckkammer (28) entlastet wird, bei einer Bewegung der Plungeranordnung in der nach außen gerichteten Richtung, so dass eine begrenzte Größe der nach innen gerichteten Bewegung jedes Mal auftreten kann, wenn ein Druck auf die Plungeranordnung (26) angelegt wird, und zwar bevor die Druckkammer (28) wieder geschlossen wird.
- Einsteller nach Anspruch 1, wobei die Vorspannmittel (40) angeordnet sind zum Drücken sowohl der Plungeranordnung (26) als auch der Dichtmittel (34) in einer nach außen gerichteten Richtung bezüglich der Bohrung (24).
- Einsteller nach Anspruch 1 oder 2, der zweite Vorspannmittel (46) aufweist, die angeordnet sind, zum Vorspannen der Dichtmittel (34) und der Plungeranordnung (26) voneinander weg.
- Einsteller nach Anspruch 3, wobei die zweiten Vorspannmittel eine Blattfeder (46) sind.
- Einsteller nach Anspruch 3 oder 4, wobei die zweiten Vorspannmittel (46) zur Bewegung mit der Plungeranordnung (26) angebracht sind.
- Einsteller nach Anspruch 2, der Haltemittel (42) umfasst, die mit der Plungeranordnung (26) bewegbar sind zum Tragen der Dichtmittel (34) für eine begrenzte Bewegung bezüglich des Plungers, um dadurch ein Öffnen und Schließen der Kammer zu erlauben.
- Einsteller nach Anspruch 6, der zweite Vorspannmittel (46) umfasst, die auch durch die Haltemittel (42) getragen werden und die angeordnet sind, zum Vorspannen der Dichtmittel (34) und der Dichtoberfläche (36) der Plungeranordnung (26) voneinander weg.
- Ventilketten- bzw. -reihenanordnung zum Betrieb eines Ventils, wobei die Anordnung Folgendes aufweist: einen Nocken (18), der angeordnet ist um das Öffnen und Schließen des Ventils (11) zu bewirken und ein hydraulischer Spieleinsteller nach einem der vorhergehenden Ansprüchen zur Aufnahme des Spiels in der Kette zwischen dem Nocken (18) und dem Ventil (11).
- Anordnung nach Anspruch 8, wobei der Nocken (18) ein ungeschliffener Nocken ist.
- Anordnung nach Anspruch 9, wobei der Nocken (18) netzförmig ist.
- Anordnung nach einem der Ansprüche 8 bis 10, wobei die Anordnung einen Kipphebel umfasst, der angeordnet ist, um durch den Nocken geschwenkt zu werden, um das Ventil zu betätigen.
- Anordnung nach einem der Ansprüche 8 bis 10, wobei der Spieleinsteller ein direkt wirkender Tassenstössel ist.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP02254170A EP1267046B1 (de) | 2001-06-15 | 2002-06-14 | Hydraulisches Spielausgleichselement |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP01830399 | 2001-06-15 | ||
EP01830399A EP1267045A1 (de) | 2001-06-15 | 2001-06-15 | Hydraulisches Ventilspiel-Einstellsystem einer Ventilbetätigungsanordnung einer Brennkraftmaschine |
EP02254170A EP1267046B1 (de) | 2001-06-15 | 2002-06-14 | Hydraulisches Spielausgleichselement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1267046A1 EP1267046A1 (de) | 2002-12-18 |
EP1267046B1 true EP1267046B1 (de) | 2004-09-15 |
Family
ID=26077484
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02254170A Expired - Fee Related EP1267046B1 (de) | 2001-06-15 | 2002-06-14 | Hydraulisches Spielausgleichselement |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP1267046B1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008075519A (ja) | 2006-09-20 | 2008-04-03 | Otics Corp | ラッシュアジャスタ |
JP2009013830A (ja) | 2007-07-03 | 2009-01-22 | Otics Corp | ラッシュアジャスタ |
JP4865740B2 (ja) | 2008-01-30 | 2012-02-01 | 株式会社オティックス | ラッシュアジャスタ |
DE102014212112A1 (de) * | 2014-06-24 | 2015-12-24 | Schaeffler Technologies AG & Co. KG | Selbsttätige Ventilspielausgleichseinrichtung für einen Ventiltrieb einer Hubkolbenbrennkraftmaschine |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5129373A (en) * | 1991-12-16 | 1992-07-14 | General Motors Corporation | Self-contained hydraulic lash adjuster with pressurizing diaphragm |
US5622147A (en) * | 1996-03-08 | 1997-04-22 | Eaton Corporation | Hydraulic lash adjuster |
US5758613A (en) * | 1997-01-30 | 1998-06-02 | Eaton Corporation | Hydraulic lash adjuster and biased normally open check valve system therefor |
-
2002
- 2002-06-14 EP EP02254170A patent/EP1267046B1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP1267046A1 (de) | 2002-12-18 |
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