CN106438748A - Clutch release device - Google Patents
Clutch release device Download PDFInfo
- Publication number
- CN106438748A CN106438748A CN201610633146.9A CN201610633146A CN106438748A CN 106438748 A CN106438748 A CN 106438748A CN 201610633146 A CN201610633146 A CN 201610633146A CN 106438748 A CN106438748 A CN 106438748A
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- CN
- China
- Prior art keywords
- release
- component
- shift fork
- hub
- clutch
- 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.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D2023/126—Actuation by rocker lever; Rocker levers therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
- F16D23/14—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings
- F16D2023/141—Clutch-actuating sleeves or bearings; Actuating members directly connected to clutch-actuating sleeves or bearings characterised by using a fork; Details of forks
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention discloses a clutch release device. The clutch release device comprises a release lever and a release bearing. The release lever has an elongated shape. The release bearing has a first member, a second member and a ball bearing. A cylindrical portion of the first member and a tubular portion of the second member have a gap between the cylindrical portion of the first member) and the tubular portion of the second member, so that the gap allows a movement of the second member in a direction perpendicular to an axis according to pivoting movement of the release lever. The gap is larger than a movement amount of a far end of the release lever in the direction perpendicular to the axis when the clutch is engaged and disengaged.
Description
Invention field
The present invention relates to engaging and departing from the clutch release dress using in the operation of the clutch being arranged in vehicle
Put.
Background technology
Known a kind of clutch release device, it includes：Release shift fork, when by operator clutch pedal, draws
Play described release shift fork to pivot around pivotal point；And release bearing, it moves in the axial direction according to the pivot of release shift fork
Dynamic.Describe clutch release device in No. 62-242132 (JP62-242132A) one is disclosed at Japanese patent application
Example.
In clutch release device, when discharging shift fork and pivoting, exist at the distal end portion discharging shift fork and release bearing
Contact surface at the problem of friction and wear occurs.In the device of JP62-242132A, rolling member is arranged on release and dials
Fork distal end portion, for by release shift fork resistance to sliding be converted into rolling resistance, with suppress release shift fork and release bearing it
Between abrasion.
Content of the invention
If rolling member is arranged on the distal end portion of release shift fork, such as the clutch release device at JP62-242132A
In, the frictional resistance between the distal end portion of release shift fork and release bearing reduces, and suppresses abrasion.But, due to needs by
Rolling member is arranged at the distal end portion of release shift fork, and therefore structure is complicated.Additionally, from whole loads of release shift fork
It is applied to rolling member, this problem that may cause the durability with regard to rolling member.
The invention provides can not make baroque in the case of the suppression release distal end portion of shift fork and release bearing
Between abrasion clutch release device.
The clutch release device of a scheme according to the present invention includes release shift fork and release bearing.Release shift fork tool
There is elongated shape.Release shift fork is arranged to pivot around the given lengthwise position as pivotal point so that when the axle along pivotal point
During the direction viewing of line, the distal end portion of release shift fork moves along the shape of arc-shaped.Release bearing supports with the distal end portion of release shift fork
Contact.Release bearing is configured to the movement of the distal end portion when clutch discharges according to release shift fork and axial along clutch
Direction is moved.Release bearing has the first component, second component and ball bearing.First component has cylindrical portion and from cylindrical portion
The first flange part of projecting radially outwardly of outer peripheral face.Second component have tube on the outer peripheral face being assemblied in cylindrical portion and
The second flange part projecting radially outwardly from tube.One end of the second flange part when watching along the axial direction of the first component
It is in close contact with the first flange part of the first component.The other end of the second flange part when watching along the axial direction of the first component
Distal end portion abutting contact with release shift fork.When watching along the axial direction of the first component, ball bearing is along the first component
The position being disposed radially outward in neighbouring first flange part of cylindrical portion.The cylindrical portion of the first component and the tubulose of second component
Portion has gap betwixt so that gap allows second component to move along the direction being perpendicular to axis according to the pivot of release shift fork
Dynamic.Gap is more than the amount of movement along the direction being perpendicular to axis of the distal end portion of release shift fork when clutch engages and departs from.
In the clutch release device of the such scheme according to the present invention, formed and allow described second component according to release
The pivot of shift fork and along being perpendicular to the gap that the direction of axis is moved, thus when the distal end portion of release shift fork abuts described second structure
Part when pivoting, second component moves along the direction identical with the distal end portion of release shift fork.Therefore, it is possible to suppression there will be originally
Abrasion between the distal end portion and second component of release shift fork.It is not necessary at the distal end portion and second of release shift fork
Rolling member etc. is set between component, therefore prevents structure complicated.
In the clutch release device of the such scheme according to the present invention, release bearing can have elastic component, when
When clutch engages, elastic component makes second component be perpendicular to axis along the pivot according to release shift fork, the edge with second component
The direction in opposite direction of movement in direction move.
In clutch as above release device, described elastic component is provided for making when the clutch is engaged the
The side in opposite direction of the movement along the direction being perpendicular to axis with the pivot according to release shift fork of second component, edge for two components
To movement.Therefore, it is able to ensure that when clutch discharges and makes second component move.
In the clutch release device of the such scheme according to the present invention, release bearing can have guiding mechanism, draws
Lead the direction of the movement along the direction being perpendicular to axis according to the pivot of release shift fork along the distal end portion discharging shift fork for the mechanism
Guide second component.
In clutch as above release device, the direction guiding mechanism to be provided for along being perpendicular to axis guides
Second component.Therefore, can eliminate when second component is mobile according to the pivot of release shift fork or reduce and be applied to the second structure
The change of the load of part.
In the clutch release device of the such scheme according to the present invention, the first component can be formed by resin material,
And second component and release shift fork can be formed by metal material.
In above-mentioned clutch release device, the first member of resin material is formed, and second component and release are dialled
Fork is formed by metal material.Therefore, the coefficient of friction between the first component and second component is low, and when discharging shift fork and pivoting
The first component and second component can be made to slide.
Brief description
Feature, advantage and technology and the industry meaning of the one exemplary embodiment of the present invention will be described below with reference to the accompanying drawings
Justice, in the accompanying drawings, identical reference refers to identical element, and wherein：
Fig. 1 is the schematic diagram of the construction illustrating clutch, in described clutch, have employed a reality as the present invention
Execute the clutch release device of example；
Fig. 2 is the view of the relation between the structure and the power being applied to release bearing illustrating known release bearing；
Fig. 3 is regarding of the release bearing of the Fig. 1 when the side viewing in axial direction abutting release bearing from release shift fork
Figure；
Fig. 4 is the A-A sectional view of the release bearing of Fig. 3；
Fig. 5 is the view of the release bearing of Fig. 3 when watching from the direction of arrow B；With
Fig. 6 is to illustrate that the transition period from the engagement state of clutch to release conditions applies regarding of the load to spring
Figure.
Detailed description of the invention
Will be explained in more detail with reference to the drawing one embodiment of the present of invention.In the following embodiments, the parts in accompanying drawing or
Part simplifies or deformation as required, and all parts therefore described in accompanying drawing or the dimension scale of part, shape etc. are not must
So accurate.
Fig. 1 diagrammatically illustrates clutch 10, in clutch 10, have employed as one embodiment of the present of invention from
Clutch discharges device 12.Clutch 10 is the dry type single plate for arranging around the rotation C (axis C) identical with engine 11
Friction clutch.Clutch 10 includes that the 16th, the flywheel being arranged on the bent axle 14 of engine 11 is connected to the clutch of output shaft 18
The 20th, device dish is arranged on pressure plare the 24th, diaphragm spring the 26th, hydraulic clutch release cylinder 28 and release bearing on clutch cap 22
32.Diaphragm spring 26 is suitable to promote pressure plare 24 towards flywheel 16, in order to clutch disk 20 is pressed against flywheel 16 and is used for moving
Power is transmitted.Clutch release cylinder 28 is suitable to operate when clutch pedal (not shown) is depressed.Release bearing 32 is arranged to can edge
The direction of the axis C of clutch 10 is moved.In operation, release bearing 32 by clutch release cylinder 28 via being formed as elongated
The release shift fork 30 of shape and mobile towards flywheel 16 (right in Fig. 1), so that the inner end of diaphragm spring 26 is towards flying
Wheel 16 (to the right of Fig. 1) shifts thus discharges (disengaging) clutch 10.The clutch release device 12 of the present embodiment includes releasing
Put shift fork 30 and release bearing 32, and operate when clutch 10 engages and departs from.
In the case of not having hydraulic oil to be supplied in the hydraulic pressure chamber of clutch release cylinder 28, pressure plare 24 is at diaphragm spring
Press clutch disk 20 under the bias force of 26, thus clutch 10 is coupled.When clutch pedal is depressed by driver, and liquid
Pressure oil feeder is to when in the hydraulic pressure chamber of clutch release cylinder 28, and the piston 34 of clutch release cylinder 28 moves, and release bearing
32 is mobile along the direction of axis C towards flywheel 16 (to the right of Fig. 1) via release shift fork 30 so that release bearing 32 presses
The inner peripheral of diaphragm spring 26.As a result, the bias force of diaphragm spring 26 reduces；Therefore, pressure plare 24 presses clutch disk 20
Power weakens, and the torque capacity of clutch 10 reduces.Then, if the amount of movement of release bearing 32 reaches scheduled volume, pressure
Plate 24 stops pressing clutch disk 20, thus discharges clutch 10.
Release shift fork 30 is formed as elongated shape, and is arranged to around the pivot being arranged on given lengthwise position
Point 36 pivot.When discharging clutch 10, release shift fork 30 is caused to pivot, and when the direction viewing of the axis along pivotal point
When release shift fork 30 the distal end portion 30a with release bearing 32 abutting contact move along camber line.Therefore, when release shift fork 30 pivots
When, its distal end portion 30a moves along the direction of the axis C of release bearing 32 towards engine 11, and also along be perpendicular to axis C and
Move close to the direction of pivotal point 36.Release shift fork 30 is formed by metal material.
Hereinafter, the problem that the structure of known release bearing 40 will be described and produce from described structure.Fig. 2 illustrates
Relation between the structure of known release bearing 40 and the power being applied to release bearing 40.Release bearing 40 is arranged to
Move along the direction of axis C, and include that the 42nd, columnar retainer is slidably fitted within releasing on the outer peripheral face of retainer 42
Put bearing hub 44 and be arranged in the ball bearing 48 of radial outside of release bearing hub 44.The one of the inner ring of ball bearing 48
End and diaphragm spring 46 abutting contact.
The release shift fork 50 (it will be referred to as " shift fork 50 ") being represented by single dotted broken line in Fig. 2 and release bearing hub 44
(it will be referred to as " bearing hub 44 ") abutting contact.Load F represents that applying is to the distal end portion of shift fork 50 when shift fork 50 pivots
Power, between the distal end portion and bearing hub 44 of shift fork 50, frictional force Ff produces along the direction being perpendicular to load F.Frictional force Ff quilt
The product (Ff=μ f × F) of the coefficientoffrictionμ f being calculated as between load F and shift fork 50 and bearing hub 44.Frictional force Ff eliminates axle
Hold the radial gap between hub 44 and retainer 42 or play, and frictional force Ff be also applied to bearing hub 44 and retainer 42 it
Between；Therefore, frictional force Fr being parallel to axis C produces between bearing hub 44 and retainer 42.Frictional force Fr is calculated as rubbing
The product (Fr=μ r × Ff=μ r × μ f × F) of the coefficientoffrictionμ r between wiping power Ff and bearing hub 44 and retainer 42.
It is equal to the release load Fc/c of the bias force corresponding to the diaphragm spring 46 and summation (F of frictional force Fr due to load F
=F=Fc/c+Fr), so load F increases with frictional force Fr and increases.Therefore, if frictional force Fr becomes big, clutch pedal
Pedal force may increase, or extraordinary noise may be produced between friction surface.Due to the load F therefore increasing, abrasion
Possibly be present between shift fork 50 and bearing hub 44.The release bearing 32 of the present embodiment has been developed to solve the problems referred to above.
The release bearing of the present embodiment when Fig. 3 illustrates the side viewing abutting when the direction from release shift fork 30 along axis C
32.Fig. 4 is the A-A sectional view of the release bearing 32 of Fig. 3.Fig. 5 illustrates the release when the direction of the arrow B from Fig. 3 is watched
Bearing 32.Fig. 3 is corresponding to the view when the direction of the arrow D from Fig. 4 is watched.
Release bearing 32 includes：Release bearing hub 54 (it will be referred to as " bearing hub 54 "), it is being represented by single dotted broken line
Columnar retainer 52 outer peripheral face on slide；And ball bearing 56, it is arranged in the radial outside of bearing hub 54.
Bearing hub 54 includes：First hub 58, it has cylindrical portion 62, discharge shift fork 30 pivot when, cylindrical portion 62 is along axle
Slide on the outer peripheral face of retainer 52 in the direction of line C；And second hub 60, it has the cylindrical portion 62 being assemblied in the first hub 58
Outer peripheral face on tube 66.First component of the first corresponding present invention of hub 58, and the of the corresponding present invention of the second hub 60
Two components.
First hub 58 is arranged around the axis C as central axis.First hub 58 includes：Cylindrical portion 62, it is at retainer
Slide on the outer peripheral face of 52；And first flange part 64, it is from the outer peripheral face of the immediate vicinity along axis C direction of cylindrical portion 62
Project radially outwardly.First hub 58 is formed by resin component element.
Second hub 60 is arranged around the axis C as central axis, and is formed as L-shaped in the cross-section.Second hub 60
Including：Tube 66, the cylindrical portion 62 of the first hub 58 passes through tube；And second flange part 68, it is from the edge of tube 66
The direction of axis C projects radially outwardly closer to one end of the first flange part 64.Second hub 60 is formed by metal material.
In the inner peripheral surface of the tube 66 that the outer peripheral face of the cylindrical portion 62 of the first hub 58 is assemblied in the second hub 60.Additionally, the
The surface being perpendicular to axis C of the first flange part 64 of one hub 58 is perpendicular to axis C with the second flange part 68 of the second hub 60
Intimate surface contact.First hub 58 is pressed along the direction of axis C to the second hub 60 by diaphragm spring 26 via ball bearing 56.
Therefore, the first hub 58 and the second hub 60 are configured to unit.In addition, on the direction of axis C be in close contact the first flange part 64
The distal end portion 30a abutting contact of surface and release shift fork 30 of contrary the second flange part 68 in side.First hub 58 and the second hub
The contact surface of 60 is pre-coated with grease, so that the coefficient of friction between these surfaces reduces.
Ball bearing 56 is being positioned at the cylinder of the first hub 58 along the square position upwardly adjacent to the first flange part 64 of axis C
The radially outer in portion 62.Ball bearing 56 includes：Annular inner race 70, itself and diaphragm spring 26 abutting contact；Annular outer ring 72, its
The first flange part 64 abutting contact with the first hub 58；And multiple ball 74, it is inserted between inner ring 70 and outer ring 72.Separately
Outward, being provided with a pair clip 76, the pair of clip 76 is by sandwiched therebetween to outer ring 72 and the release bearing hub 54 of ball bearing 56.
In this arrangement, the radial clearance 78 representing such as the hacures in Fig. 3 is formed at the cylindrical portion 62 of the first hub 58
And second hub 60 tube 66 matching surface between.
Gap 78 is formed so that when the release shift fork 30 of the second flange part 68 abutting the second hub 60 is around pivotal point 36
During pivot, the second hub 60 can be perpendicular to the direction (axle as center of axis C along the edge of the distal end portion 30a with release shift fork 30
The radial direction of line C) the identical direction of moving direction move.(see figure owing to release shift fork 30 pivots around pivotal point 36
1), the distal end portion 30a of release shift fork 30 moves along the direction of axis C, and also edge is perpendicular to axis C and close to pivotal point 36
Direction is somewhat moved.In figure 3, when discharging shift fork 30 and pivoting, its distal end portion 30a moves to the dorsal part of paper, and also mobile
Left to paper.Therefore, power edge is perpendicular to axis C and the direction close to pivotal point 36 is applied to and the distal end portion discharging shift fork 30
Second hub 60 (the second flange part 68) of 30a abutting contact.Gap 78 be formed so that with and release shift fork 30 pivot close
On the identical direction in the direction moving radially of distal end portion 30a of the release shift fork 30 of connection, it is allowed to the movement of the second hub 60.
In figure 3, if release shift fork 30 pivots, the distal end portion 30a of release shift fork 30 somewhat moves to the left on paper.
Therefore, power applies similarly to the second hub 60 of the distal end portion 30a abutting contact with release shift fork 30, in order to move the second hub 60
Move the left to paper.Therefore, gap 78 is formed so that permission shifting in transverse direction on the paper of Fig. 3 for second hub 60
Dynamic.More specifically, the parts of outer peripheral face of the cylindrical portion 62 as the first hub 58, gap 78 is by pruning on the left side of paper and the right side
Shadow part on side and formed.Therefore, the second hub 60 can move (slip) corresponding to gap 78 by the horizontal direction along paper
The distance of size.In the following description, the second hub 60 according to release shift fork 30 pivot be perpendicular to axis C and close to pivot
The direction of the movement of turning point 36 will be defined as (the second hub 60) glide direction.The size in gap 78 is set to be greater than distally
The size of the amount of movement along the direction being perpendicular to axis C of the pivot according to release shift fork 30 of end 30a.That is, gap 78 is big
Little being set so that allows the second hub 60 to move along the direction being perpendicular to axis C during the pivot of release shift fork 30.
As it is shown on figure 3, the pair of notches 80 each with rectangular shape is formed in the second flange part 68 of the second hub 60
The position along glide direction.Otch 80 is formed with guide surface 80a, and guide surface 80a edge is parallel to the second hub 60 according to release
The pivot of shift fork 30 and the glide direction slided extends.In addition, the rounded angle in the corner closer to axis C of otch 80 becomes circular arc
Shape portion.
Additionally, a pair guide protrusion 82 engaging with the guide surface 80a of otch 80 is formed at the first flange of the first hub 58
In portion 64.Guide protrusion 82 is formed as highlighting from the first flange part 64 respectively, and engages with the guide surface 80a of pair of notches 80.
Otch 80 (guide surface 80a) and guide protrusion 82 constitute guiding mechanism 83.By such guiding mechanism 83 being formed, when release is dialled
During fork 30 pivot, the direction of the movement along the direction being perpendicular to axis C by the distal end portion 30a along release shift fork 30 for second hub 60
Guide, so that the second hub 60 smoothly moves along glide direction.Can also eliminate or reduce and apply when the second hub 60 moves
Change to the load of the second hub 60.
As it is shown in figure 5, spring 84 is provided for when clutch 10 engages specifying the phase of the first hub 58 and the second hub 60
To position.One end of spring 84 and the first hub 58 abutting contact, and the other end and the second flange part 68 being formed at the second hub 60
On projection 86 abutting contact.Projection 86 by stay when forming the otch 80 of the second hub 60 second hub 60 a part and not
Cut away it and described part bent to its position being parallel to axis C extension and is formed.Spring 84 is corresponding to the present invention's
Elastic component.
Spring 84 and projection 86 abutting contact.When clutch 10 engages, the second hub 60 is moved to such as bottom by spring 84
Put：It is being not provided with the one of spring 84 when watching along the glide direction (horizontal direction on paper) of the second hub 60 shown in Fig. 3
Gap 78 on side (left-hand side on paper in Fig. 3) eliminates.That is, when clutch 10 engages, spring 84 makes the second hub 60 move
The opposition side in the direction of the movement moved to the pivot according to release shift fork 30 with the second hub 60.Therefore, although gap 78 is formed
The opposition side along glide direction in figure 3, but when clutch 10 engages, the second hub 60 is moved along glide direction by spring 84
Move to spring 84 side (right-hand side on paper) so that the gap 78 on the side (left-hand side on paper) being not provided with spring 84 disappears
Remove.In other words, footpath is formed along between the outer peripheral face and the inner peripheral surface of tube 66 of the cylindrical portion 62 in spring 84 side for the glide direction
To gap 78, and the size in gap 78 is equal to the gap 78 being formed along on the opposition side of the glide direction shown in Fig. 3
Summation.
The bias force of spring 84 is set as such amplitude：Make when clutch 10 engages upper (when release shift fork 30 not pivot
When turning), the second shown in figure 3 hub 60 at least moves to spring 84 side along glide direction, and when along glide direction viewing
When gap 78 be formed at spring 84 side.It is equal to or big more specifically, the bias force of spring 84 is adjusted to produce from spring 84
Friction between the bias force F1 and the first hub 58 and the second hub 60 of the diaphragm spring 26 in the case that clutch 10 engages
The product of the coefficientoffrictionμ 2 between the distal end portion 30a of the sum of products biasing force F1 of coefficient μ 1 and release shift fork 30 and the second hub 60
The bias force of the summation (F1 × (μ 1+ μ 2)) of (F1 × μ 2).
In addition, the bias force of spring 84 is set in, in the range of exceeding value (F1 × (μ 1+ μ 2)) indicated above, from
In the range of the increase of the pedal force on clutch pedal does not causes any problem.As shown in Figure 6, apply when clutch 10 engages
It is minimum to the load (=F1 × (μ 1+ μ 2)) of spring 84, and be applied to the load of spring 84 and discharge with clutch 10
And increase.The bias force of spring 84 is set in the load producing when the clutch is engaged and the load producing when clutch discharges
Between.
The operation of release bearing 32 configured as above will be described.When clutch 10 engages, the second hub 60 is at spring
Spring 84 side (right on the paper of Fig. 3) is moved to along glide direction under the bias force of 84.Now, in figure 3, along glide direction
Between being formed between the inner peripheral surface of the tube 66 of the outer peripheral face of the cylindrical portion 62 of the first hub 58 in spring 84 side and the second hub 60
Gap 78, and the outer peripheral face of cylindrical portion 62 and very close to each other between the inner peripheral surface of the tube 66 of the side being not provided with spring 84.
When release shift fork 30 is when clutch 10 discharges from engagement state and pivots, release bearing 32 is released shift fork 30
Pressing, and move along the direction of axis C towards diaphragm spring 26.Further, since the distal end portion 30a of release shift fork 30 is along camber line
Mobile, power edge is perpendicular to axis C with distal end portion 30a's and is applied to close to the identical glide direction of the moving direction of pivotal point 36
The second hub 60 with the distal end portion 30a abutting contact of release shift fork 30.
In this, distal end portion 30a and the contact of the second hub 60 metal each other of shift fork 30 are discharged；Thus, these components
Between coefficientoffrictionμ 2 to the first hub 58 and the second hub 60 between coefficientoffrictionμ 1 high.Therefore, the distally of shift fork 30 is discharged
End 30a and the second hub 60 are mobile along glide direction (radial direction) as unit, and send out between the first hub 58 and the second hub 60
Raw slip.As a result, abrasion may be less likely to or between the far less likely to occur distal end portion 30a at release shift fork 30 and the second hub 60.
If slided between the first hub 58 and the second hub 60, then vertical from producing between the first hub 58 and the second hub 60
Frictional force Ff in the direction of axis C；But, because the coefficientoffrictionμ 1 between the first hub 58 and the second hub 60 is little, so rubbing
Wiping power Ff is little.In this, move, by the cylindrical portion 62 of the first hub 58 sliding on retainer 52, the frictional force producing
Fr also reduces.Therefore, the pedal force on clutch pedal may be less likely to or unlikely increase, and also suppresses or decrease circle
The extraordinary noise producing between cylinder portion 62 and retainer 52.Coefficientoffrictionμ 1 between first hub 58 and the second hub 60 is low, and this is
Because their contact is the contact between resin and metal, and between the first hub 58 and the second hub 60, grease coating is set,
So that coefficientoffrictionμ 1 reduces further.
Release owing to the size in gap 78 is set to be greater than during the engagement state from clutch 10 is transitioned into release conditions
Put the amount of movement of the distal end portion 30a of shift fork 30 along glide direction, so allowing the first hub 58 and the second hub 60 to release at clutch 10
Slide in the range of putting.Therefore, from the engagement state of clutch 10 be transitioned into release conditions period the second hub 60 may be less likely to or
Unlikely stop sliding, and discharge the distal end portion 30a of shift fork 30 and the second hub 60 may be less likely to or unlikely slides each other
Dynamic slip contiguously or mobile.Additionally, when clutch 10 engages, the second hub 60 is moved to original at the bias force of spring 84
Position, and the first hub 58 and the second hub 60 necessarily can be made to slide when clutch 10 discharges.
Further, since the guide surface 80a of the otch 80 that the guide protrusion 82 of the first hub 58 is with the second hub 60 engages, so working as
When first hub 58 and the second hub 60 slide, guide protrusion 82 moves along guide surface 80a.Therefore, the second hub 60 is put down along glide direction
Slidingly mobile, and suppress the increase of load.Further, since the rounded angle in the corner of otch 80 becomes the shape of arc-shaped, so
These parts may be less likely to or unlikely engage with the first hub 58.
As described above, according to the present embodiment, the edge forming the pivot allowing the second hub 60 according to release shift fork 30 is perpendicular to
The gap 78 of the movement in the direction of axis C；Therefore, when the distal end portion 30a discharging shift fork 30 abuts the second hub 60 and pivots, the
Two hubs 60 move along the direction identical with the distal end portion 30a of release shift fork 30.Dial therefore, it is possible to suppression appears in release originally
Abrasion between the distal end portion 30a of fork 30 and the second hub 60.Further, since there is no need the distal end portion 30a at release shift fork 30
With second provide rolling member between hub 60 so that suppression abrasion, so preventing structure from becoming complicated.
Additionally, according to the present embodiment, spring 84 be provided for when clutch 10 engages moving to the second hub 60 with
The opposition side of the moving direction along the direction being perpendicular to axis C of the pivot according to release shift fork 30 of the second hub 60.Therefore, when
When clutch 10 discharges, the second hub 60 can be ensured that movement.
Additionally, according to the present embodiment, the direction guiding mechanism 83 to be provided for along being perpendicular to axis C guides the second hub
60.Therefore, can eliminate when the second hub 60 is mobile according to the pivot of release shift fork 30 and to be applied to the load of the second hub 60
Change.
In addition, in the present embodiment, the first hub 58 is formed by resin material, and the second hub 60 and release shift fork 30 are by gold
Belong to material to be formed.Therefore, the coefficient of friction between the first hub 58 and the second hub 60 is low, and can when discharging shift fork 30 and pivoting
The first hub 58 and the second hub 60 is made to slide.
Although one embodiment of the present of invention being described in detail with reference to the accompanying drawings, but the present invention can be in other forms
Application.
For example, the outer peripheral face of the cylindrical portion 62 by the first hub 58 of pruning for the gap 78 and formed；But, they also can pass through
Prune the inner peripheral surface of tube 66 of the second hub 60 and formed.
In the above-described embodiments, when clutch 10 engages, the second hub 60 moves to along glide direction by spring 84
Spring 84 side, thus gap 78 is formed at a position.But, as it is shown on figure 3, when clutch 10 engages, also may be used in gap 78
To be formed at two positions.
Although guiding mechanism 83 to be arranged on two positions in the above-described embodiments, but guide the quantity of the position of mechanism 83
It is not limited to two, but can be a position.In addition, guide mechanism 83 not necessarily necessary, but can omit.
It should be understood that an only embodiment described above, and knowing based on those skilled in the art
Knowing, the present invention can be implemented by various changes and/or improvement.
Claims (4)
1. a clutch release device, it is characterised in that include：
Discharging shift fork, it has elongated shape, and described release shift fork is arranged to around the given lengthwise position pivot as pivotal point
Turn so that the described shape shifting discharging the distal end portion of shift fork along arc-shaped when the direction of the axis along described pivotal point is watched
Dynamic；And
Release bearing, its described distal end portion abutting contact with described release shift fork, described release bearing is configured to work as clutch
The movement of the described distal end portion according to described release shift fork during release and move along the axial direction of described clutch, described release
Bearing has the first component, second component and ball bearing, and described first component has cylindrical portion and from described cylindrical portion
The first flange part that side face projects radially outwardly, described second component has on the described outer peripheral face being assemblied in described cylindrical portion
Tube and the second flange part projecting radially outwardly from described tube, described second flange part has along described first component
Axial direction towards first surface, described first flange part of described first surface and described first component is in close contact,
Described second flange part have along described first component described axial direction towards second surface, described second surface and institute
State the described distal end portion abutting contact of release shift fork, when watching along the described axial direction of described first component, described ball
Bearing is along the position being disposed radially outward in neighbouring described first flange part of the described cylindrical portion of described first component, described
The described tube of the described cylindrical portion of the first component and described second component has the described cylindrical portion at described first component
And the gap between the described tube of described second component so that described gap allows described second component according to described release
The pivot of shift fork and move along the direction being perpendicular to described axis, described gap is more than when described clutch engages and departs from when institute
State the amount of movement along the described direction being perpendicular to described axis of the described distal end portion of release shift fork.
2. clutch according to claim 1 release device, it is characterised in that described release bearing has elastic component,
When described clutch engages, described elastic component make described second component along with described second component according to described release dial
The direction in opposite direction of the movement that the pivot of fork, edge are perpendicular to the described direction of described axis is moved.
3. clutch according to claim 1 and 2 release device, it is characterised in that described release bearing has vectoring aircraft
Structure, according to the described pivot discharging shift fork, the edge along the described distal end portion of described release shift fork is perpendicular to institute in described guiding mechanism
The direction of the movement stating the described direction of axis guides described second component.
4. clutch according to any one of claim 1 to 3 release device, it is characterised in that described first component by
Resin material is formed, and described second component and described release shift fork are formed by metal material.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015157739A JP2017036779A (en) | 2015-08-07 | 2015-08-07 | Clutch release device |
| JP2015-157739 | 2015-08-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN106438748A true CN106438748A (en) | 2017-02-22 |
Family
ID=57853987
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610633146.9A Pending CN106438748A (en) | 2015-08-07 | 2016-08-04 | Clutch release device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2017036779A (en) |
| CN (1) | CN106438748A (en) |
| DE (1) | DE102016114367A1 (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5315239U (en) * | 1976-07-19 | 1978-02-08 | ||
| JPS608180Y2 (en) * | 1979-12-25 | 1985-03-22 | トヨタ自動車株式会社 | Connection structure between clutch release bearing hub and release fork |
| JPS62237119A (en) * | 1986-04-04 | 1987-10-17 | Nippon Seiko Kk | Clutch release bearing device |
| JPS62242132A (en) * | 1986-04-14 | 1987-10-22 | Koyo Seiko Co Ltd | Clutch release device |
| JPS63289331A (en) * | 1987-05-21 | 1988-11-25 | Nachi Fujikoshi Corp | Clutch release bearing device |
| JPS6426029A (en) * | 1988-06-07 | 1989-01-27 | Koyo Seiko Co | Clutch release device |
| JPH01171929U (en) * | 1988-05-26 | 1989-12-06 | ||
| JPH1026149A (en) * | 1996-07-09 | 1998-01-27 | Nippon Seiko Kk | Clutch releas bearing device |
| JP2004340203A (en) * | 2003-05-14 | 2004-12-02 | Nsk Ltd | Clutch release bearing device |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0665904B2 (en) | 1986-04-11 | 1994-08-24 | ヤンマーディーゼル株式会社 | Marine deceleration reversing machine |
-
2015
- 2015-08-07 JP JP2015157739A patent/JP2017036779A/en active Pending
-
2016
- 2016-08-03 DE DE102016114367.7A patent/DE102016114367A1/en not_active Withdrawn
- 2016-08-04 CN CN201610633146.9A patent/CN106438748A/en active Pending
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5315239U (en) * | 1976-07-19 | 1978-02-08 | ||
| JPS608180Y2 (en) * | 1979-12-25 | 1985-03-22 | トヨタ自動車株式会社 | Connection structure between clutch release bearing hub and release fork |
| JPS62237119A (en) * | 1986-04-04 | 1987-10-17 | Nippon Seiko Kk | Clutch release bearing device |
| JPS62242132A (en) * | 1986-04-14 | 1987-10-22 | Koyo Seiko Co Ltd | Clutch release device |
| JPS63289331A (en) * | 1987-05-21 | 1988-11-25 | Nachi Fujikoshi Corp | Clutch release bearing device |
| JPH01171929U (en) * | 1988-05-26 | 1989-12-06 | ||
| JPS6426029A (en) * | 1988-06-07 | 1989-01-27 | Koyo Seiko Co | Clutch release device |
| JPH1026149A (en) * | 1996-07-09 | 1998-01-27 | Nippon Seiko Kk | Clutch releas bearing device |
| JP2004340203A (en) * | 2003-05-14 | 2004-12-02 | Nsk Ltd | Clutch release bearing device |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102016114367A1 (en) | 2017-02-09 |
| JP2017036779A (en) | 2017-02-16 |
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| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20170222 |
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