U.S. patent application number 12/161118 was filed with the patent office on 2010-06-24 for camshaft adjuster for an internal combustion engine.
This patent application is currently assigned to SCHAEFFLER KG. Invention is credited to Ali Bayrakdar.
Application Number | 20100154732 12/161118 |
Document ID | / |
Family ID | 37983405 |
Filed Date | 2010-06-24 |
United States Patent
Application |
20100154732 |
Kind Code |
A1 |
Bayrakdar; Ali |
June 24, 2010 |
CAMSHAFT ADJUSTER FOR AN INTERNAL COMBUSTION ENGINE
Abstract
The invention relates to a camshaft adjuster for an internal
combustion engine. In camshaft adjusters, spring elements which
influence the moment conditions for the positional definition and
influencing of the camshaft adjuster are usually arranged so as to
lie on the inside of the housing. According to the invention, a
spring element (29) is arranged outside the housing (4) in a
camshaft adjuster (1), a spring base point of the spring element
(29) being supported via a pin (21) which penetrates the housing
(4) and is connected fixedly in terms of rotation to a rotor
(6).
Inventors: |
Bayrakdar; Ali;
(Roethenbach/Pegnitz, DE) |
Correspondence
Address: |
LUCAS & MERCANTI, LLP
475 PARK AVENUE SOUTH, 15TH FLOOR
NEW YORK
NY
10016
US
|
Assignee: |
SCHAEFFLER KG
Herzogenaurach
DE
|
Family ID: |
37983405 |
Appl. No.: |
12/161118 |
Filed: |
December 6, 2006 |
PCT Filed: |
December 6, 2006 |
PCT NO: |
PCT/EP2006/009360 |
371 Date: |
July 16, 2008 |
Current U.S.
Class: |
123/90.17 |
Current CPC
Class: |
F01L 2001/34483
20130101; F01L 1/3442 20130101; F01L 1/34 20130101; F01L 1/344
20130101 |
Class at
Publication: |
123/90.17 |
International
Class: |
F01L 1/34 20060101
F01L001/34 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 21, 2006 |
DE |
10 2006 002 993.3 |
Claims
1. Camshaft adjuster (1) for an internal combustion engine,
comprising: a) a driven housing, b) an output element which can be
connected fixedly in terms of rotation to the camshaft and can be
rotated relative to the housing for an adjusting movement of the
camshaft adjuster, and c) a spring element which acts between the
driven housing and the output element, wherein the spring element
is arranged outside the housing.
2. Camshaft adjuster according to claim 1, wherein a spring base
point is supported on a supporting element which a) is connected
fixedly in terms of rotation to the output element which is
arranged in the housing, and b) penetrates a cut-out of a wall of
the housing, a relative movement between the housing and the
supporting element being made possible.
3. Camshaft adjuster according to claim 2, wherein the supporting
element is supported with respect to an output element which is
configured as a rotor of the camshaft adjuster in the vane cell
design.
4. Camshaft adjuster according to claim 3, wherein the supporting
element is configured as a pin.
5. Camshaft adjuster according to claim 4, wherein the pin is
connected to the rotor via a press joint fit.
6. Camshaft adjuster according to claim 2, wherein the wall of the
housing has a cut-out which extends in the circumferential
direction and through which the supporting element passes, making a
relative rotation possible.
7. Camshaft adjuster according to claim 3, wherein a seal is
provided between the rotor and the housing in the surrounding
region of the cut-out.
8. Camshaft adjuster according to claim 1, wherein the spring
element is configured with a helical torsion spring.
9. Camshaft adjuster according to claim 1, wherein the spring
element is arranged on that side of the camshaft adjuster which
faces a cylinder head.
10. Camshaft adjuster according to claim 1, wherein the spring
element is arranged radially on the inside of the drive element or
drive gear of the camshaft adjuster.
11. Camshaft adjuster according to claim 1, wherein a drive element
of the camshaft adjuster has a central bore or annular groove, in
which the spring element is received.
12. Camshaft adjuster according to claim 1, wherein the spring
element is arranged in the axial direction between the housing and
a covering.
13. Camshaft adjuster according to claim 1, wherein the spring
element has at least one hook-shaped spring base point which is
hooked into the output element, the supporting element and/or the
housing or a component which is connected fixedly in terms of
rotation to a component of this type.
14. Camshaft adjuster according to claim 13, wherein the spring
element is supported on a stop in the radial direction in the
surrounding region of a spring base point, in which radial
direction the hooking of the spring base point into the output
element, the supporting element or the housing is released.
Description
FIELD OF THE INVENTION
[0001] The invention relates to a camshaft adjuster for an internal
combustion engine, according to the precharacterizing clause of
Claim 1. In particular, the invention relates to a camshaft
adjuster, by means of which, in order to influence [0002] the
charging of the combustion chamber, [0003] the combustion
conditions, [0004] the performance data and [0005] the exhaust-gas
values,
[0006] a relative angular position between a camshaft and a drive
element which is driven by a crankshaft of the internal combustion
engine, for example, via a drawing means can be changed in a
targeted manner according to a control device.
BACKGROUND OF THE INVENTION
[0007] U.S. Pat. No. 6,311,654 B1 has disclosed a camshaft adjuster
in the vane cell design, in which a chain sprocket drives a housing
of the camshaft adjuster, in which housing an output element which
is configured as a rotor is screwed fixedly in terms of rotation to
a camshaft via a central screw. Vanes which are assigned to the
rotor are arranged in pressure chambers of the housing in such a
way that, depending on the hydraulic loading of the pressure
chambers, the rotor and therefore the camshaft can be adjusted in
the direction "early" or "late" relative to the housing and the
drive gear. The document addresses the problem that a hydraulic
pump for loading the pressure chambers is usually driven by a
crankshaft, which has the consequence that the flow of the
hydraulic medium is reduced, in some circumstances, at a low speed
of the internal combustion engine. This can lead to undesirable
adjustments of the camshaft adjuster.
[0008] In order to eliminate problems of the type explained above,
JP A 9 264 110 proposes to connect a torsion spring between a drive
element and an output element. For this purpose, the torsion spring
is supported in the housing of the camshaft adjuster at one base
point on the chain sprocket, while the other base point of the
torsion spring is supported on the rotor.
[0009] This solution is considered problematic according to U.S.
Pat. No. 6,311,654 B1, as a bypass can be provided between the
pressure chambers of the camshaft adjuster via the receiving space
for the torsion springs, in some circumstances, which bypass can
lead to undesirable operating states and even failure of the
camshaft adjuster. In order to avoid problems of this type, U.S.
Pat. No. 6,311,654 B1 proposes to arrange the pressure chambers and
the vanes so as to lie radially outside the receiving space for the
torsion spring element, with the result that suitable sealing can
be effected in a radial intermediate space in the housing. As a
result, however, the overall radial structural size of the camshaft
adjuster is increased. Radial dimensions which are increased in
this way can be avoided according to U.S. Pat. No. 6,311,654 B1 in
that firstly the pressure chambers and secondly the receiving space
for the torsion spring are arranged so as to lie axially next to
one another with radially overlapping extents. Transfer of the
hydraulic medium between individual pressure chambers via the
receiving space for the spring element is avoided by a circularly
annular dividing disc which is connected axially between the
pressure chambers and the receiving space.
[0010] DE 40 32 586 A1 has disclosed a camshaft adjuster which is
actuated via a control piston, in which a torsion spring
arrangement which serves to transmit approximately a mean torque is
arranged parallel to the adjusting chambers between a drive gear
and a camshaft. This refinement is based on the finding that, for
adjustment in different directions, torques have to be generated in
the camshaft adjuster which have opposite directions, the
magnitudes of which, however, are different in some circumstances
for different directions, with the result that, for example as a
result of the drive movement and/or the friction conditions, a mean
moment for the torque requirements for different adjusting
directions results which is not equal to zero. In order to limit
the moments which are to be produced in the camshaft adjuster to
the difference of the extremes required from the main moment, and
not to the absolute extreme which is greater in some circumstances,
the document proposes to provide the mean moment by an energy
accumulator which is configured as a torsion spring arrangement
which is connected parallel to the adjusting chambers between the
drive sprocket and the camshaft. The torsion spring arrangement is
configured separately from the camshaft adjuster.
[0011] DE 690 28 063 T2 discloses a further refinement of the use
of torsion spring elements for influencing the moment conditions
for a camshaft adjuster.
[0012] DE 198 20 638 A1 discloses the use of a torsion spring in a
camshaft adjuster for compensation of the tooth play of what are
known as scissor gearwheels, cf. also U.S. Pat. No. 5,056,613, U.S.
Pat. No. 4,747,321, U.S. Pat. No. 4,739,670, U.S. Pat. No.
3,365,973 and U.S. Pat. No. 2,607,238.
OBJECT OF THE INVENTION
[0013] The invention is based on the object of proposing a camshaft
adjuster which is improved with regard to [0014] assembly, [0015]
the required radial and/or axial installation space, [0016]
influencing of the moment conditions in the camshaft adjuster,
and/or [0017] the connection of a spring element to a drive element
and/or output element of the camshaft adjuster.
SUMMARY OF THE INVENTION
[0018] According to the invention, the object is achieved by the
features of independent Claim 1. Further refinements of the
solution according to the invention result in accordance with the
features of dependent Claims 2 to 14.
[0019] The invention is based first of all on the finding that it
is disadvantageous in some circumstances to connect a spring
element for influencing the moment conditions of the camshaft
adjuster between a drive element and the camshaft itself. A
connection of this type requires suitable measures for connecting
the spring element to the camshaft, which measures can increase the
manufacturing expenditure for the camshaft, the mass, the mass
moment of inertia and/or the installation space of the camshaft.
Secondly, a spring element of this type cannot already be mounted
during manufacture of the camshaft adjuster, but only when the
camshaft adjuster is assembled with the camshaft.
[0020] Furthermore, the invention is based on the finding that, for
refinements in accordance with U.S. Pat. No. 6,311,654 B1, the
spring element has to be mounted in the housing of the camshaft
adjuster. This has the consequence that the spring element has to
be secured, for example, for an open housing with exact positioning
of the housing parts and at the same time guaranteeing the
accessibility of the interior of the housing. Moreover, a torsion
spring which is arranged in the housing is the reason for the
problems which are addressed in U.S. Pat. No. 6,311,654 B1 with
regard to the risk of transfer of the hydraulic medium between
individual pressure chambers via a receiving space for the spring
element.
[0021] According to the invention, the spring element acts between
the housing and the output element. Here, the spring element can be
supported directly on the housing or the output element, or merely
indirectly with components which are connected fixedly in terms of
rotation to the housing or the output element being connected in
between.
[0022] Furthermore, it is proposed according to the invention to
arrange the spring element outside the housing. This makes mounting
of the housing possible, in particular with an output element which
lies in the latter, including closure of the said housing, with
subsequent mounting of the spring element, without it being
necessary for the camshaft to be present for this purpose. Rather,
mounting of the spring element can already take place during
manufacture of the camshaft adjuster in order to form one
structural unit which then merely has to be connected to the
camshaft.
[0023] For one refinement with an arrangement of the spring element
outside the housing, a wide variety of different embodiments are
possible: [0024] a) for example, the output element can have a
protrusion which is, in particular, hollow-cylindrical and [0025]
extends with a sealing function between the housing and the
circumferential face which lies on the outside through the housing
from the inside outwards, [0026] makes connection of the spring
element possible in the region of the outer circumferential surface
in a manner which lies on the outside of the housing, and [0027]
receives the camshaft in a manner which lies radially on the
inside, for mounting of the camshaft adjuster with the camshaft.
[0028] b) In one alternative or cumulative refinement of the
invention, a spring base point is supported on a section element.
The supporting element is connected fixedly in terms of rotation to
the output element which is arranged in the housing. Here, the
output element can be of single-piece or multiple-piece
configuration with the section element. One wall of the housing has
a cut-out. The supporting element extends through this cut-out,
with the result that forces which are applied to the supporting
element outside the housing can be transmitted through the cut-out
to the output element. Here, the cut-out of the wall of the housing
is configured in such a way that a relative rotation is made
possible between the housing and the supporting element and
therefore the output element. The supporting element can be
configured separately from the spring element or integrally with
the latter, it being possible for flexural elasticity to be
provided primarily by the spring element, or jointly by the spring
element and the supporting element by a connection of the
respective rigidities one behind another.
[0029] One particular semi-finished product, for which the
mechanical properties can be predefined in a simple structural
manner, can be used if the supporting element is configured as a
pin.
[0030] In a further refinement of the invention, simple connection
of a pin of this type to the output element, in particular a rotor
of a camshaft adjuster in the vane cell design, can be provided by
a press joint fit.
[0031] According to one further proposal of the invention, the
cut-out is provided in the wall of the housing with an extent in
the circumferential direction, for example in the shape of a curved
groove or a "banana-shaped" groove, with the result that the
relative rotation between the housing and the supporting element is
made possible in a cut-out or groove of this type.
[0032] In order to avoid an outflow of hydraulic medium from a
pressure chamber of the camshaft adjuster, in particular transfer
between individual pressure chambers, the invention proposes,
furthermore, that a seal is provided between the housing and the
rotor in the surrounding region of the above-mentioned cut-out. The
sealing action can be effected, for example, [0033] as has been
described in the introduction, by a radial offset of the pressure
chambers on one side and the cut-out on the other side, with a
sealing region being connected in between, [0034] via a sealing
washer or a sealing element, such as a labyrinth seal, a sealing
ring or the like.
[0035] Any desired springs may be suitable as spring elements, such
as tension or compression springs, helical springs made from
elastic material such as spring steel or, for example, an elastomer
element. According to one particular proposal of the invention, the
spring element is configured with a helical torsion spring, in
which the spring element extends in the circumferential direction
of the camshaft adjuster, preferably with an angle of extent which
is greater than 360.degree..
[0036] The spring element can be arranged on one end side of the
camshaft adjuster. However, the spring element is preferably
arranged on that end side of the camshaft adjuster which faces the
cylinder head, with the result that the spring element is arranged
between the housing of the camshaft adjuster and the cylinder head.
Accordingly, that end side of the camshaft adjuster which lies
opposite and faces away from the cylinder head can be used for
other functions, for example for assembly of the camshaft adjuster
with the camshaft via a central screw, the supply of hydraulic
medium or an end-side adjusting unit.
[0037] A particularly compact refinement of the invention results
if the spring element is arranged radially on the inside of a drive
gear of the camshaft adjuster. For this purpose, the drive element
of the camshaft adjuster can have a central bore or annular groove,
in which the spring element is received. The bore or annular groove
can serve as protection and/or for guidance of the spring element,
without these functions and the receiving space for the spring
element necessarily requiring an increase in the installation space
of the camshaft adjuster.
[0038] The spring element can be protected from contamination or
mechanical impairments and limited axially against drifting or
deflecting away by a cover, with the result that the spring element
is arranged in the axial direction between the housing and the
covering.
[0039] In one further refinement of the invention, the spring
element can be booked into the output element, the supporting
element and/or the housing or a component which is connected
fixedly in terms of rotation to a component of this type in the
region of the base point in a simple manner, for mounting (and
dismantling). For this purpose, the spring element has at least one
hook-shaped spring base point which can be hooked, for example,
into a lug, a journal or a bracket.
[0040] Furthermore, the invention has discovered that a movement of
the spring element with elastic loading of the spring element is
required in order to release hook-shaped spring base points of this
type. Here, the overall elasticity of the spring element can be
unsuitable, in order to predefine a force to a sufficient extent
for release of the spring element from the associated component, in
order that unintended release of the spring element can be avoided,
for example during operation of the internal combustion engine. The
invention therefore proposes that the spring element is supported
on a stop in the radial direction in the surrounding region of the
spring base point. Support of this type acts in the same direction,
in which the hooking of the spring base point into the associated
component is also released. This has the consequence that the
overall rigidity of the spring element is not critical for release
of the spring element, but rather changed boundary conditions which
can influence the force level for the release of the spring
element, in particular raise it, are active for the release of the
spring element as a consequence of the wear of the stop.
[0041] Advantageous developments of the invention result from the
patent claims, the description and the drawings. The advantages,
which are mentioned in the introduction to the description, of
features and of combinations of a plurality of features are merely
by way of example, without them necessarily having to be achieved
by the embodiments according to the invention. Further features are
to be gathered from the drawings, in particular the geometries
which are shown and the relative dimensions of a plurality of
components with respect to one another and their relative
arrangement and operative connection. The combination of features
of different embodiments of the invention or of features of
different patent claims is likewise possible in a manner which
deviates from the selected back-references of the patent claims and
is likewise suggested herewith. This also relates to features of
the kind which are shown in separate drawings or are mentioned in
their description. These features can also be combined with
features of different patent claims. Features which are specified
in the patent claims can likewise be omitted for further
embodiments of the invention.
BRIEF DESCRIPTION OF THE DRAWINGS
[0042] Further features of the invention result from the following
description and the associated drawings, in which exemplary
embodiments of the invention are shown diagrammatically and in
which:
[0043] FIG. 1 shows a camshaft adjuster according to the invention
which is assembled with a camshaft, in longitudinal section;
[0044] FIG. 2 shows an end-side view of the camshaft adjuster, with
a viewing angle from the side which faces the cylinder head,
without a cover which covers a spring element; and
[0045] FIG. 3 shows an end view according to FIG. 2, in this case
with a cover which covers the spring element, however.
DETAILED DESCRIPTION OF THE INVENTION
[0046] FIG. 1 shows a camshaft adjuster 1 in longitudinal section,
which camshaft adjuster 1 is assembled with a camshaft 2. The
camshaft adjuster 1 in the exemplary embodiment which is shown in
the figures is of the vane cell design which is known per se. The
camshaft adjuster 1 has a drive element which is configured as a
chain sprocket 3 in the exemplary embodiment which is shown. The
chain sprocket 3 is drive-connected fixedly in terms of rotation to
a further chain sprocket which is connected to the crankshaft, via
a drawing means (not shown), a chain here. The chain sprocket 3 is
connected fixedly in terms of rotation to a housing 4 or a part of
the housing 4. A rotor 6 which is connected fixedly in terms of
rotation to the camshaft 2 is arranged in the housing 4 such that
it can be rotated relatively about the longitudinal axis 5-5 of the
camshaft adjuster 1. There are pressure chambers 7 in the housing
6, in which pressure chambers 7 vanes which are connected fixedly
to the rotor 6 can be pivoted according to the loading with the
hydraulic medium, which is associated with the rotation of the
rotor 6 relative to the housing 4. For the exemplary embodiment
which is shown, the pressure chambers 7 are loaded with pressure
via end-side feed channels of the camshaft adjuster 1. The fixed
connection between the rotor 6 and the camshaft 2 is effected for
the exemplary embodiment which is shown by means of a central screw
8 which is screwed on the end side into a central bore, having a
thread, of the camshaft 2. The rotor 6 is captured and clamped
between an end face 9 of the camshaft and a head 10 of the central
screw 8, optionally with further components 18 being connected in
between. The central screw 8 has an end-side blind bore 11 on that
side which faces away from the camshaft 2, in which end-side blind
bore 11 hydraulic elements are received for suitable loading of the
camshaft adjuster 1 with the hydraulic medium. The hydraulic medium
is fed from the blind bore 11 to the pressure chambers 7 via
suitable, in particular radial channels.
[0047] The housing 4 is formed with an approximately U-shaped half
section which has an approximately axially oriented base limb 12
and parallel, radially oriented side limbs 13, 14. The side limbs
13, 14 reach around the rotor 6 in a radially inward manner.
Radially inner end faces 15, 16 of the side limbs 13, 14 form a
gap, a contact face or a sealing face with a circumferential face
17 of the camshaft 2 and the component 18 which is connected
fixedly in terms of rotation to the rotor 6. For the exemplary
embodiment which is shown, the side limbs 13, 14 are formed with
two substantially circularly annular discs 23, 24. The disc 24 for
the side limb 14 has a hollow-cylindrical protrusion 22 with a bore
38 which extends in the direction of the cylinder head and bears
the chain sprocket 13 radially on the outside The disc 24, the
protrusion 22 and the chain sprocket 3 are of single-piece
configuration for the exemplary embodiment which is shown.
[0048] The base limb 12 is formed by a hollow-cylindrical outer
casing of the housing 4, which has radially inwardly oriented
projections for delimiting the pressure chambers 7 in the
circumferential direction. The housing 4 therefore has discs 23,
24, which are configured separately from one another but are sealed
with respect to one another, and the outer casing. A seal 19 is
arranged between the side limbs 13, 14 and the rotor 6 which can be
pivoted relative to the latter, which seal 19 prevents lubricant
from passing from one pressure chamber into an adjacent pressure
chamber and/or from migrating radially inwards or outside the
camshaft adjuster 1. The seal 19 can be configured as a narrow gap
or contact face between the side limbs 13, 14 and the facing end
faces of the rotor 6. The arrangement of a labyrinth seal, an
additional sealing element such as a sealing ring or the like is
likewise possible.
[0049] The rotor 6 has a bore 20 which is oriented parallel with
respect to the longitudinal axis 5-5 and can be configured as a
through bore or blind bore. The spacing of the longitudinal axis of
the bore 20 from the longitudinal axis 5-5 is greater than the
diameter of the camshaft 2 in the region of the camshaft adjuster,
but smaller than the diameter for an inner delimitation of the
pressure chamber 7. A supporting element which is configured as a
cylindrical pin 21 is inserted into the bore 20 with an accurate
fit, in particular with a press fit. The pin 21 extends in a
contactless manner, in particular with formation of a play 26,
through a cut-out 25 of the disc 24 on that side which faces away
from the cylinder head, and protrudes from the disc 24 with an end
region 27 on that side which faces the cylinder head. The end
region 27 is arranged in the bore 38 in a manner which lies
radially on the inside of the protrusion 22.
[0050] It can be seen in FIG. 2 that the cut-out 25 is configured
as a groove 28 which extends in the circumferential direction. The
spring element 29 has hook-shaped spring base points 30, 31 which
are connected elastically to one another via a helical torsion
spring 32 which extends with a plurality of turns in the
circumferential direction. The hook-shaped spring base point 30
which is bent in a hook-shaped manner approximately over a
circumferential angle of 180.degree. and has a diameter which is
slightly greater than the external diameter of the end region 27
engages around the end region 27, while the hook-shaped spring base
point 31 is bent in a hook-shaped manner approximately over a
circumferential angle of 90.degree. and is hooked into the
projection 33 of the protrusion 22, which projection 33 is oriented
radially inwards. The spring element 29 is formed from an elastic
material, in particular a resilient metal. For the exemplary
embodiment which is shown in the figures, a spring wire of the
torsion spring 32 has a substantially rectangular cross section. A
stop 34 is arranged in a manner which is offset approximately by
60.degree. in the circumferential direction about the longitudinal
axis 5-5 with respect to the projection 33, at a radius which
corresponds approximately to the internal radius of the projection
33, on the outer side of which the torsion spring 32 is supported.
In order to mount the spring element 29, the hook-shaped spring
base point 30 of the spring element 29 is hooked into the end
region 27 of the pin 21 for substantially finished mounting of the
camshaft adjuster 1 itself and finished assembly of the housing 4.
Furthermore, the associated region of the torsion spring 32 is
positioned on the stop 34. The hook-shaped spring base point 31 is
deformed elastically radially inwards, with loading of that region
of the torsion spring 32 which extends in the circumferential
direction between the projection 33 and the stop 34. The
hook-shaped spring base point 31 is then hooked or clipped into the
projection 33. Further support of further part regions of the
torsion spring is possible, for example in the region of a further
pin 35 which is configured in accordance with the pin 21, extends
through a corresponding cut-out 36 and on which the torsion spring
32 is supported on the radially outer side. The torsion spring 32
is preferably configured with a radial play between individual
turns, in order to avoid friction which impedes the pivoting
between the rotor 6 and the housing 4.
[0051] A cover 37 is introduced radially on the inside into the
protrusion 22. For the exemplary embodiment which is shown, the
cover is configured as a circularly annular disc-shaped metal
plate, the inner bore of the metal plate having a radius which is
slightly greater than the radius of the outer side of the pins 35,
21. The cover 37 is bent over in the direction of the cylinder head
radially on the outside. The cover 37 is deformed radially inwards
by its insertion into the protrusion 22 and, for the operating
position which is shown in FIG. 1, bears with radial pressure
against the inner bore 38 of the protrusion 22 in a manner which is
positioned fixedly in the latter with a frictional fit. The
protrusion 22 can have a suitable groove for an additional
form-fitting connection.
LIST OF REFERENCE NUMERALS
[0052] 1 Camshaft adjuster
[0053] 2 Camshaft
[0054] 3 Chain sprocket
[0055] 4 Housing
[0056] 5 Longitudinal axis
[0057] 6 Rotor
[0058] 7 Pressure chamber
[0059] 8 Central screw
[0060] 9 End face
[0061] 10 Head
[0062] 11 Blind bore
[0063] 12 Base limb
[0064] 13 Side limb
[0065] 14 Side limb
[0066] 15 End face
[0067] 16 End face
[0068] 17 Circumferential face
[0069] 18 Component
[0070] 19 Seal
[0071] 20 Bore
[0072] 21 Pin
[0073] 22 Protrusion
[0074] 23 Disc
[0075] 24 Disc
[0076] 25 Cut-out
[0077] 26 Play
[0078] 27 End region
[0079] 28 Groove
[0080] 29 Spring element
[0081] 30 Spring base point
[0082] 31 Spring base point
[0083] 32 Torsion spring
[0084] 33 Projection
[0085] 34 Stop
[0086] 35 Pin
[0087] 36 Cut-out
[0088] 37 Cover
[0089] 38 Bore
* * * * *