CN102575722B - Clutch apparatus - Google Patents
Clutch apparatus Download PDFInfo
- Publication number
- CN102575722B CN102575722B CN201080045671.XA CN201080045671A CN102575722B CN 102575722 B CN102575722 B CN 102575722B CN 201080045671 A CN201080045671 A CN 201080045671A CN 102575722 B CN102575722 B CN 102575722B
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- China
- Prior art keywords
- clutch
- friction
- bearing
- shell
- manipulation device
- Prior art date
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Classifications
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
- F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
- F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
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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
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
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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
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
It is a kind of for drive system multiple clutch apparatus, the speed changer that the driving system has driving unit and then arranges, it the multiple clutch apparatus and the driving axis connection of driving unit and is contained in the clutch cap (7) not rotated together with the drive shaft of the driving unit, there are two the friction disk clutch (K1 of wet operation for the multiple clutch apparatus tool, K2), they are respectively provided with input terminal and output end friction disc support and friction plate alternate in the axial direction, the multiple clutch apparatus also has manipulation device, wherein, the shell (28) of the manipulation device (27) is supported on the clutch cap (7), the friction disc support (10) of the input terminal of at least one of the friction disk clutch and the shell of the manipulation device pass through a support plate or bearing alms bowl (31) and an end bearing (30 ) connect in this way, so that the force flow of the steering force generated by the manipulation device is backed on the shell of the manipulation device by support plate or bearing alms bowl and end bearing, thus it is presented on closed force flow inside the multiple clutch apparatus.
Description
Technical field
Multiple clutch apparatus, the especially compound oily clutch that the present invention relates to a kind of for driving system, driving system tool
Have and driving unit and be placed on the speed changer of clutch apparatus, wherein the drive shaft of clutch apparatus and driving unit directly or
Grounding connection, and be contained in the clutch cap not rotated together with the drive shaft of driving unit, wherein clutch apparatus has
There are two friction disk clutch and a manipulation devices, and friction disk clutch respectively includes the friction of input terminal and output end
Plate rack, they have friction plate alternate in the axial direction.
Background technique
This compound oily clutch as known to DE 10 2,006 049 731.By grasping in multiple clutch known to this
The steering force that vertical device generates passes through the friction disc support of input terminal, end bearing and the clutch being fixedly connected on clutch cap
Lid bearing.For this purpose, corresponding friction disc support, end bearing and the clutch case for firmly designing input terminal, wherein respective manipulation
Power depends on the torque to be transmitted.Therefore need the steering force that correspondinglys increase when torque increases and correspondingly design especially from
The thickness of clutch lid.The output end of ZMS and the input terminal of clutch are also supported by this clutch case.Compound oil clutch
Device is lever-operated.Manipulation device have rotating lever, they can electricity ground or hydraulically manipulate.
Summary of the invention
Therefore, the purpose of the present invention is to provide the multiple clutch apparatus of an above-mentioned form, it has improved manipulation
Power bearing and/or improved radially and/or axially bearing type and/or improved cooling oil transporting pattern and/or multiple clutch
The more optimal design in processing technology of device device components.
The purpose is realized according to the present invention by the multiple clutch apparatus at least one independent claims feature.
The content of each dependent claims is the preferred embodiment of the present invention.
Detailed description of the invention
The present invention is explained in detail by preferred embodiment combination attached drawing below.Attached drawing is shown:
Fig. 1 according to the multiple clutch of first embodiment semi-section,
The inside force flow of Fig. 2 friction disk clutch K2 of inner radial setting in multiple clutch of the manipulation according to Fig. 1
Schematic diagram,
Fig. 3 according to the bearing of the multiple clutch of Fig. 1 and Fig. 2 schematic diagram,
Semi-section of the Fig. 4 according to the multiple clutch of another embodiment in gapless friction disc support,
The schematic diagram of the related friction disc support construction of Figures 5 and 6,
Fig. 7 has internal closed force flow and passes through compound ring according to the semi-section of the multiple clutch of another embodiment
Piston (" CSC ") manipulation,
Fig. 8 has according to the semi-section of the multiple clutch of another embodiment with the compound oily clutch that transmission shaft is fixed
There is the axial clearance compensation in oily input pipe,
Semi-section of the Fig. 9 according to the multiple clutch of another embodiment, the compound oily clutch with axial suspension bearing,
With radial oily input pipe,
Semi-section of the Figure 10 according to the multiple clutch of another embodiment, the compound clutch with the bearing of another axial suspension
Device has adagio bearing herein,
Semi-section of the Figure 11 according to the multiple clutch of another embodiment, the compound clutch with the bearing of another axial suspension
Device has adagio bearing and guide post herein,
Figure 12 has dry type ZMS according to the semi-section of the multiple clutch of another embodiment,
Figure 13 has dry type ZMS, wherein removing in external clutch according to the semi-section of the multiple clutch of another embodiment
Axial bearing between the outer friction plate rack and clutch case of device K1,
Figure 14 has internal closed force flow and wet operation according to the semi-section of the multiple clutch of another embodiment
ZMS and centrifugal force pendulum (" FKP "),
Figure 15 has internal closed force flow and wet operation according to the semi-section of the multiple clutch of another embodiment
ZMS and centrifugal force pendulum (" FKP "), wherein removing the plate pawl or clamping jaw according to Figure 14.
Specific embodiment
Multiple clutch 1 shown in fig. 1 is made of the friction disk clutch K1 and K2 of two radially nested, wet operations.
In this clutch K1 setting in radially outer, clutch K2 is arranged in inner radial.Multiple clutch 1 is by preposition in clutch 1
Double mass flywheel (not being shown specifically, hereinafter also referred to as ZMS) driven wheel hub driving.It is deposited between ZMS and multiple clutch 1
In clutch case 3, it separates grease chamber 4 with dry chamber 5.Clutch case 3 and the speed changer of the postposition in driving system (do not show individually
The static sealing 6 of gearbox case out) is realized preferably by O-ring or other static seal elements.Towards multiple clutch 1
Sealing is realized preferably by the radial shaft seal ring 8 as dynamic sealing component.
The driven wheel hub 2 of ZMS is connect by engaging tooth with 9 anti-torsion of clutch hub.Clutch hub 9 and radial direction are embedding
The input terminal friction disc support 10 of the external clutch K1 of set connects.Also can choose makes clutch hub 9 and input terminal
The construction of friction disc support 10 is integrated.(the input friction plate of=outside of input terminal friction disc support 10 of friction disk clutch K1
Bracket 10) He Yuqi anti-torsion connection clutch hub 9 by 16 radial support of transverse bearing in the first transmission input shaft
On 15 (it is configured to solid shafting).The friction disc support 10 of input terminal includes site of engagement, suspends external friction plate on it
The friction plate of the input terminal of the friction plate group of clutch K1, thus the input terminal of outside is displaceably arranged in anti-torsion and axial direction
Friction plate 11.The friction plate 11 of external input terminals and the friction plate 12 of external driven end are alternately arranged, wherein external input terminals
Friction plate 11 and the friction plate 12 of external driven end that is arranged alternately the friction plate group of clutch K1 is collectively formed.It is external driven
12 anti-torsion of friction plate at end and it is axial displaceably with the external driven end friction disc support 13 of outer friction slice clutch K1
Connection.The external driven end friction disc support 13 of friction disk clutch K1 includes wheel hub 14, it is compound with (not being shown specifically)
First transmission input shaft 15 of clutch speed changer connects.
The input terminal friction disc support 10 of outer friction slice clutch K1 passes through the connecting plate that is suspended in friction disc support
17 connect with the friction disc support 18 of the inside input terminal of the friction disk clutch K2 built in radial direction.Friction plate built in radial direction from
The friction plate anti-torsion and axial direction of the inside input terminal of clutch K2 are displaceably suspended at nibbling for internal input friction disc support
Close position.The friction plate of these internal input terminals and the friction plate of internal output terminal of clutch K2 built in radial direction is alternately set
It sets, on the friction disc support 19 of their anti-torsions and the axial inside driven end that plate clutch K2 is displaceably set.It is interior
The friction disc support 19 of portion's driven end has wheel hub position, on it the friction disc support 19 and the second speed changer of internal driven end
Input shaft 20 (it is configured to hollow shaft) connection.
The friction disc support 19 of the inside driven end of plate clutch K2 built in radial direction by axis spring 21 (and if by
Need in structure also by connector 22) radial external plate clutch is pressed under conditions of interfix axial bearing 23
The friction disc support 13 of the external output end of K1.Other elastomeric elements, such as butterfly spring group also can be used instead of axis spring.Diameter is outside
The friction disc support 14 of the external driven end of the friction disk clutch K1 set is again in the condition of the second axial bearing of interfix 24
The friction disc support 10 of the external input terminals of the lower radial external friction disk clutch K1 of press, or press clutch hub 9.
The friction disc support 10 of the external input terminals of radial external friction disk clutch K1 is also in another axial bearing 25 of interfix
Under conditions of press clutch case 3, it is supported on the shell 7 of speed changer by fixation member 26.Especially as shown in Figure 1, axis
It holds 23,24,25 and is preferably constructed as axial direction (needle roller) bearing.Connector 22 is constructed in this way, can be realized the friction plate in output end
The flow path of cooling oil is used between bracket.
Transmission input shaft 15,20 is arranged coaxially and mutually nested herein, wherein external transmission input shaft 20 is logical
It crosses end bearing 38 to be supported in shell 7, and internal transmission input shaft 15 is supported on external hollow shaft 20 by bearing
In.
Multiple clutch 1 further includes manipulation device 27, it is configured to the center of two friction disk clutch K1 and K2
Clutch push rod, manipulation device have shell 28, it is supported on the shell 7 of speed changer by bearing frame 29.It is configured to herein
Compound ring piston connects the manipulation device of bar (also referred to as compound CSC, wherein CSC is Concentric Slave Cylinder)
27 pistons 31,32 that are including two circular ring shapes and being mutually arranged concentrically.
The variation of the manipulation device 27 shown in Fig. 1 to 4 indicates one embodiment, wherein two toroidal pistons 31,
32 is mutually coordinated.Therefore, the internal diameter of the outer piston 31 of clutch K1 is the sealing surface of clutch K2 internal piston simultaneously.It can also
With selection, it is contemplated that one embodiment, two of them piston are separated from each other by circular ring shape galianconism, and sealing can slide on.
It can exclude to influence each other as sealing to caused by piston 31,32 by this alternative embodiment.
But the above-mentioned possible expansion structure of manipulation device 27 is understood merely as example.Therefore, instead of annular piston
Can with being circumferentially distributed equipped with other cross-sectional shapes and/or multiple single pistons.Equally can be equipped with electricity or
Electromechanical push rod, instead of piston/cylinder unit.Furthermore mechanical manipulation device, especially lever-operated device can also be equipped with.
Be configured to elastomeric seal in the piston seal of this annular piston 31,32, they by the sealed connection of shape with
Each piston connection.The connection sealed as shape is for example contemplated that the cone tank in piston, can access elasticity wherein
The corresponding tenon or elastomeric seal itself of body sealing.Also it can choose and be lining into the sealing made of such as PTFE, or in piston
Upper direct injection moulded elastomer sealing.
Annular piston 31.32 is accommodated by connection bar shell 28, wherein connection bar shell 28 not separately shown in the accompanying drawings
In hole be used for, pass through pressure oil application piston.
Bar shell 28 is connected additionally to undertake through bearing frame 29 in 4 inner radial of clutch cap positioning piston.
Each manipulation unit of manipulation device 27 is connect by manipulating bearing 33,34 with force transfering device, is made respectively by it
Steering force is transmitted to each friction disk clutch K1, K2.Each force transfering device includes the press alms bowl 34A of substantially rigid herein,
35B, it is acted against on each bearing 33,34.Herein it should be noted that each press alms bowl has elasticity certainly, it leads to certain elasticity
Effect.But it is related with the existing steering force of multiple clutch, press alms bowl assume that " substantially rigid ".Furthermore each power transmitting
Device includes lever spring 36A, 36B, it is acted against on each press alms bowl 35A, 35B.Lever spring 36A, 36B are suspended at accordingly respectively
On the subordinate friction disc support of friction disk clutch K1, K2, wherein this suspension point forms each point of rotation for being used for lever spring.It is logical
The lever ratio for crossing this lever spring realizes the power no-load voltage ratio of the steering force generated by manipulation unit.Each force transfering device further includes top
Laminate 37A, 37B, it act against subordinate lever spring 36A, 36B it is upper and with each friction disk clutch K1, the friction plate group of K2
Friction plate function connects.It presses on body transmitting steering force to the friction plate group of friction disk clutch K1 and K2.Body 37A is pressed,
37B passes through and nibbles in the engaging tooth that radially outer position axially movably suspends the friction disc support of each input terminal
Tooth is closed to feel relieved radially.Can also be directly by press alms bowl manipulation instead of this lever no-load voltage ratio of steering force, they are arranged
It manipulates between bearing and friction plate group, i.e. lever ratio 1:1.
One (also referred to as " lid axis of end bearing 30 is set at external shell position on the shell 28 of manipulation device 27
Hold "), it is connect by drawing alms bowl 31 with the friction disc support 10 of the input terminal of radially outer friction disk clutch K1.Here, end
Bearing/lid bearing inner ring is supported on shell 28 by the annulus constituted on shell 28 in side, end bearing/lid bearing
Outer ring is supported on traction alms bowl 31 by this way and method in the other side, makes the friction of the input terminal by friction disk clutch K1
The power for the steering force that plate rack 10 is led back is transmitted on shell 28.End bearing 30 connects preferably by clamping with bar shell 28 is connected
It connects, end bearing is led back on steering force to connection bar shell 28 together with traction alms bowl 31.
In one piston of pressure-loaded or two pistons, a piston or two pistons are on crankshaft direction (in Fig. 1
The left side of the middle driven wheel hub that ZMS is set) movement, while press alms bowl 35A, 35B the guiding steering force by carrying subordinate arrives
In friction plate group.Pass through input friction disc support 18 and connector 17 (also referred to as connecting plate) in the clutch K2 built in radial direction
In the input of the input terminal friction disc support and radial external friction disk clutch K1 of the friction disk clutch K2 built in radial direction
Steering force is transmitted between the friction disc support 10 of end.Input terminal friction disc support 10 is transmitted again on steering force to traction alms bowl 31, it is logical
It crosses end bearing 30 and is connect with bar shell 28 is connected.
The steering force imported in radial external clutch K1 directly passes through input friction disc support 10 and backs into traction
On alms bowl 31, backs into and connected on bar shell 28 from there through end bearing 30.
Existing compound CSC also generates the pressure on top surface acted on press alms bowl on driving unit direction, wherein in shell
Of corresponding size and phase opposite sense counter-force is generated in 28, and makes steering force with same size again by traction alms bowl and end bearing
It is backed on shell with the same direction.End bearing 30 transmits steering force to connecting on bar shell 28, thus also makes internal force flow
It is closed inside clutch 1.L1 shows out the steering force trend for manipulating friction disk clutch K2 by a dotted line in Fig. 2.
Herein in order to manipulate friction disk clutch K1 and K2 in radial delivery oil also without external force or axially conveying oil when almost
There is no external force, therefore clutch 1 is on clutch cap or motor side is without supporting steering force.
Hydraulic medium (manipulation module) is transported to manipulation device by the accessory connecting with clutch cap.
Connect bar shell 28 has torque support inside clutch cap 4, thus makes the bearing friction inside end bearing 30
It not will lead to the rotation for connecting bar shell 28.The accessory of discharge pressure is used in this as torque support.Also it can choose and pass through
Axle journal or similar parts individually support, it is embedded into clutch cap bottom when assembling clutch.
In Fig. 3 by arrow P1 to P5 show according to embodiment shown in Fig. 1 clutch 1 it is radial and axial
Bearing.
It observes radially, all 1 component parts of multiple clutch with motor speed rotation are collateral in speed changer one
It holds on connecting bar shell 28, and is supported on solid shafting 15 in motor side.Indicate radial external in this arrow P1
The friction disc support 10 of the input terminal of friction disk clutch 1 and the components connecting with this component are on connecting bar shell 28
Bearing.It connects bar shell 28 to be supported on cover bottom (gearbox case) further through bearing frame 29, as indicated by arrow P2
As.Bearing frame 29 is the angle compensation between solid shafting 15 and the bearing matrix of transmission side.Solid shafting 15 is in motor
Side supports the friction disc support 10 of the input terminal of radial external clutch K1 by bearing 16, as indicated by arrow P3
Like that.The clutch component part 14,19 rotated with solid shafting and each transmission input of hollow shaft 15,20 is by being located at
Wheel hub/wheel hub position radial support on axis.
Bearing frame 29 can be on external transmission input shaft, external preferably by being arranged in by radial support
Radial needle bearing replacement on transmission input shaft.
Axis looks up, and clutch 1 is supported on clutch case 3, wherein applying supporting force by axis spring 21.Axial supporting-point
It is indicated by arrow P4 and P5.This axis spring 21 be supported on be placed in hollow shaft 20 fixed ring and friction disk clutch K2 it is defeated
On the wheel hub of the friction disc support 19 of outlet.The friction disc support 19 of the driven end of friction disk clutch K3 is guided by gasket 22
In this axial force to the axial needle bearing 23 being located on driven end friction disc support 13 or its wheel hub position 14.Friction plate from
The friction disc support 13 of the driven end of clutch K1 is supported on the friction of the input terminal of clutch K1 further through axial needle bearing 24
On plate rack 10, it is supported on clutch case 3 by another needle bearing 25.Therefore clutch system 1 is always in alignment with clutch
Device lid 3.Axial vibration and error can be compensated by axis spring 21.Axial needle bearing 23,24,25 can also be replaced by starting board
It changes.The axial bearing of the above-mentioned form of existing clutch 1 can also with the closed force flow in above-mentioned inside independently, i.e. also other
In the manipulation force flow of form using and be the solution that can be applied independently for being usually used for compound (with oil) clutch.
Another embodiment of existing multiple clutch apparatus is shown in FIG. 4, it is complete in terms of manipulating force flow scheme
Corresponding to embodiment explained earlier.Therefore all features that are above-mentioned, being related to manipulation device according to Fig. 1 to 3 with according to
It is consistent between the embodiment of Fig. 4.Furthermore it also is provided with bearing frame herein, for making to manipulate 28 radial support of shell in speed changer
On shell 7 and compensate axile displacement.But be according to the embodiment of Fig. 4 and the difference of the above embodiments, in order to buffer
The element that rotation uniformity from internal combustion engine uses: ZMS and/or centrifugal force pendulum.Therefore, not according to the embodiment of Fig. 4
Only ZMS39 and centrifugal force pendulum 40 are all disposed in clutch cap 4, i.e. in grease chamber itself, and grease chamber is opposite by clutch case 41
It is separated in dry chamber.Clutch case 41 is not used in clutch shaft to bearing herein.But it exists only by sealing device 6 and 8
It is isolated between grease chamber and dry chamber.
ZMS39 includes the ZMS plate 42 of primary side, it constructs in this alms bowl shape and includes guide post axis at its inner radial position
Neck 43, it is embedded into the gap 44 of crankshaft 45, and the ZMS plate of primary side is made to feel relieved.In its radially outer position primary side
ZMS plate 42 have bag-shaped position, elastomeric element is accommodated wherein, wherein the end for the accumulator 46 not contacted with these bags
47 function connects of ZMS flange at position and secondary end.The engaging plate 48 of secondary end ZMS flange 47 and substantially cylindrical passes through rivet
49 connect, wherein friction disc support of the engaging plate 48 as the input terminal of radial external clutch K1.
The friction disc support 48 of input terminal passes through connecting plate 50 and the input terminal of the friction disk clutch K2 built in radial direction
Friction disc support 51 connects.This connecting plate 50 also connect (herein: construction is integrated) with centrifugal force pendulum 40, thus makes ZMS39
It is connect with centrifugal force pendulum 40 (preferably by rivet 49) and therefore is connected in parallel with engaging plate 48 jointly.
Engaging plate 48 is connect by drawing alms bowl 52 with end bearing 53, it, which is arranged, is connecting bar shell 28 (as described above)
On.
It is arranged in hollow shaft 15 to 54 anti-torsion of friction disc support of the driven end of friction disk clutch K1.Friction plate from
It is arranged in hollow shaft 20 to 55 anti-torsion of driven end friction disc support of clutch K2.The driven end friction of friction disk clutch K2
Plate rack 54 combines phase under conditions of interfix axial bearing with fixation member 21A and connecting component 22 by axis spring 21
The friction disc support 54 of driven end is carried in advance.The driven end friction disc support 54 of friction disk clutch K1 is another in interfix
It is carried under conditions of one axial bearing relative to the ZMS flange 42 of primary side (also referred to as " ZMS- plate ").In the ZMS plate of primary side
Drive disk 56 is fixedly disposed on 42, it is connect by bolt 57 with adagio 58, and wherein adagio passes through another bolt 59 and crankshaft
45 connections.
Manipulation device 27 also include manipulation unit, they are configured to piston/cylinder unit herein, they respectively by by
The force transfering device of press alms bowl, lever spring and press body composition acts in each friction plate group of friction disk clutch K1 and K2,
As described above.
It is connected on internal combustion engine according to the clutch 100 of Fig. 4 also by adagio 58.Driving plate 56 and primary side
ZMS plate directly (best oil seal) is connected with each other and accommodates the clutch case 41 of axial connection therebetween, has radial axle
Sealing ring 8.
The primary side component part of ZMS is directly supported on crankshaft 45 by guide post axle journal 43.
In the end friction plate that the secondary end flanges 47 of this ZMS are friction disk clutch K1 simultaneously.
The input terminal friction disc support 48 (as described above) of friction disk clutch K1 is realized by the variation riveted.
The embodiment of the friction disc support of riveting is shown in figs. 5 and 6.
Fig. 5 is shown specifically mounted 134 (the input terminal friction disc support class with Fig. 4 of friction disc support with sectional view
Like).Friction disc support 134 by flange 113a, tray deck 136 and be axially disposed within therebetween, distribution interconnecting piece circumferentially
Part 190 is constituted.Connecting component 190 is made of the plate 191 of prebuckling in an illustrated embodiment, they have axially extending
Axis 192,193 is riveted, they are guided in flange 113a or tray deck 136 by corresponding hole 194,195 and phase from the outside
They are riveted.191 end of plate of circumferencial direction is directed toward in order to constitute the flank of tooth 196 towards inner radial and remove seamed edge or curved
Thus song constitutes flank profile in the cross section of plate 191, suspend friction plate 138 on it, they have complementary thus
Outer profile 197 is centered in friction plate 138 on friction disc support 134 and makes the torque being located on friction disc support 134
It is transmitted on friction plate 138.Friction plate 138 is alternately fixed with friction plate 140,140 anti-torsion of friction plate and axial has limit
It is suspended in the friction disc support 142 of output end with moving.
Implementation of the Fig. 6 in the form of the structure installed shows friction disc support 135a selectable for above-mentioned friction disc support
Example.Friction disc support 135a has the connecting component 198 being similarly constructed with the connecting component 190 of Fig. 5, they are riveted on end and rub
Between pad 172a and tray deck 136.In addition, Fig. 6 shows connecting component 190a, and the pin 186 with axially-extending, the connection
Component replaces the connecting component 190 of Fig. 5 for example on multiple circumferential positions and friction disc support 134 is thus made to act on friction dress
It sets on 185, drag ring 187 and thus control friction dress is carried relative to clutch outer member in a circumferential direction by pin 186
It sets.
According to the embodiment shown in Fig. 4, there are two different length for each engaging plate tool, and circumferentially replace
Ground distribution.50 riveting of connecting plate of the input terminal friction disc support 48 and 51 of shorter engaging plate and friction disk clutch K1 and K2
It connects.Longer engaging plate is connect with traction alms bowl 52, and steering force is backed into and connected on bar shell 28 by it.Pass through nibbling for this classification
Plywood is connected to centrifugal force pendulum with gap in the secondary end flanges of ZMS without spin.Thus make traction 52 shape of alms bowl sealed and power
It is connect in locking manner with the input terminal friction disc support 48 of friction disk clutch K1 and the steering force generated can be born.
The multiple clutch with internal closed force flow is shown in FIG. 7 and is combined in clutch by lid bearing
Compound ring piston connects the manipulation of bar, and the CSC fixed as shell, wherein the structure in principle corresponds to the implementation according to Fig. 1
Example.As explained in further detail below, the piston that compound ring piston connects bar guides herein connects power by adjusting disk
To friction disk clutch K1, in the friction plate group of K2.At this, steering force passes through outer friction piece branch in internal clutch K2
Frame (=input friction disc support) and intermediate galianconism (=connecting plate 214) flow to the outer friction plate rack of outer clutch.From
There power flow back into lid bearing 221 by fixed ring 229 and clutch case 220 (=traction alms bowl), it translates force through fixed ring 230
It backs into CSC, thus closes force flow.At this, power passes through outer friction piece branch behind friction plate group in outer clutch K1
Frame 211, fixed ring 229, clutch case 220, lid bearing 221 and fixed ring 230 are flow back between lid bearing and CSC shell.Cause
This does not have in manipulation around power imported into.
Fig. 7 is shown specifically the part of the driving system for automobile, such as car or bogie, in (not being shown specifically) drive
With drive shaft 200 (herein: the internal combustion engine with crankshaft) between moving cell, it connect with the input terminal 201 of ZMS,
Wherein this input terminal 201, which also has, starts tip edge 202, wherein being equipped with basic envelope in the radially outer position of input terminal 201
The receiving position 203 (in general: bending spring) for elastomeric element 204 closed.The output par, c 205 of ZMS is embedded into curved
In spring 204, wherein output par, c 205 Yu extraneous vibration quality 206 riveting of ZMS.ZMS output par, c 205 inner radial with
Flange position 207 connects, it has engaging tooth in inner radial, its engaging tooth external with the radial direction of clutch hub 208 is nibbled
It closes.Engaging tooth between the flange 207 in ZMS output par, c and clutch hub 208 as describing in further detail below
The input terminal of compound oil clutch is the compound oily clutch that the ZMS (motor configuration component) connecting with motor is connect with speed changer
Division surface between device (speed changer structure component) in assembly is equipped with the anti-torsion in axial displacement in the plane and connects
It connects.Clutch hub 208 is made up of in inner radial the bearing block (roller cup herein) for transverse bearing 209,
Wherein clutch hub 208 is axially supported on internal transmission input shaft 210 by bearing 209.In the bearing of this bearing 209
Outer ring is fixedly received in clutch hub 208, and rolling element is directly transported on the corresponding periphery of transmission input shaft 210
Turn.
The input friction disc support of the friction disk clutch K1 external with nested radial direction radially of clutch hub 208
211 axial restraints and anti-torsion connect (herein weld), wherein in input friction disc support 211 and clutch hub
The components 212 of shell-like are also additionally clamped between 208, it provides a surface of revolution and uses for radial shaft seal ring, it is sealed
Sealing station between clutch case 213 and ZMS output flange.
External input friction disc support 211 passes through the interior of connecting plate 214 and radially nested radial built-in clutch K2
Portion inputs friction disc support 215 and connects.Each connection between input friction disc support 211,215 and connecting plate 214 corresponds to
Above-mentioned connection.
The output friction plate bracket 216 of external friction disk clutch K1 passes through the axis that constitutes in the flange position of subordinate
It is axially displaceably connect to grafting engaging tooth with 210 anti-torsion of internal transmission input shaft, still.
The output friction plate bracket 217 of friction disk clutch K2 built in radial direction is equally by the flange position of subordinate
The axial grafting engaging tooth of composition and external 218 anti-torsion of transmission input shaft but axially connect.Herein
The engaging tooth of subordinate is constituted at wheel hub position, and the output friction plate bracket welding of it and clutch K2, wherein wheel hub position is additional
Ground has protrusion or concave, they form fluid channel 217A, for making cooling oil across the defeated of friction disk clutch K1 and K2
It is flowed between friction disc support out.
Furthermore between hub portion position 217 and hollow shaft 218 be arranged elastomeric element, such as axis spring 219, for make friction plate from
Wheel hub position/output friction plate bracket of clutch K2 pre-tightens the output friction plate branch in friction disk clutch K1 by axial bearing
It is pre-tightened on clutch hub 208 on frame and by another axial bearing.Clutch hub 208 is further through friction disk clutch
The input friction disc support 211 and traction alms bowl 220 of K1 is combined with lid bearing 221 on the axial shell 222 for being supported on CSC.CSC
The components 223 that are made up of the alms bowl shape of substantially rigid of shell 223 in machining tool for clamp workpiece clamping jaw or
Plate pawl is similar to be clamped on cover bottom 224 with functioning.Also it can be selected that the elasticity for being equipped with alms bowl shape components 223 pre-tightens.?
This corresponds to clamping jaw/plate pawl components 223 for clamping oily input pipe 224, so that oil is continued to direct into CSC and is located at by it
Piston-cylinder unit therebetween.
This piston-cylinder unit is connected in CSC by the press alms bowl 226,227 of manipulation bearing and substantially rigid, it
Acted in each friction plate group of friction disk clutch K1 and K2 with lever ratio 1:1, in correspondingly pressure-loaded piston-cylinder
When unit.
It is equipped with adjustment plate 228,229 between the press alms bowl 226,227 and manipulation bearing of substantially rigid, for adjusting friction
The air gap of the friction plate group of slice clutch K1 and K2 is used for radial positioning adjustment plate wherein can shape connection strap by press alms bowl,
As shown in 227 example of press alms bowl of friction disk clutch K2 as built in radial direction.
The radially-directed of the press alms bowl 227 of friction disk clutch K2 realized by the neck that shapes on connecting plate 214, it
It is correspondingly constructed with the cylindrical portion of press alms bowl 227.
Connecting plate 214 further includes connection strap, supports reset spring on it, it is in the opening direction of friction disk clutch
Load press alms bowl 227.
The radially-directed of the press alms bowl 226 of friction disk clutch K1 passes through the cylindrical portion that is formed on traction alms bowl 220
It realizes, wherein the reset spring for preloading press alms bowl 226 in the direction of the opening is supported on the neck constituted on connecting plate 220
Between 220 end faces.
In short, relatively determining with the embodiment according to Fig. 7, the unit that can be assembled is collectively formed in CSC and clutch.
On the cover bottom that this system unit clutch/CSC is axially fixed in clutch cap by plate pawl.Plate pawl is axially pre- in assembly
Tightly and in operation endurance and torque, they are directed into CSC by clutch by lid bearing.Additional floor pawl supporting top
Pressure, they are upper axially guiding into CSC in oil transfer.
This system unit clutch/CSC by the bourrelet on CSC in radial support in cover bottom.By fixed
The power of central band bearing is directed into CSC shell by lid bearing.Clutch floating bearing by being made of on opposed side
Transverse bearing be supported on internal transmission input shaft.
In order to adjust air gap measure herein fixed ring between the contact surface on clutch case with adjustment plate connect bearing
On the distance between contact surface.Additionally measure fixed ring connecing on the slot in the outer friction plate rack of outer clutch
Contacting surface is at a distance from adjustment plate is between the contact surface on press alms bowl.This measured value subtracts the required air gap in friction plate group
Difference provides required adjustment disc thickness.
The fixed compound oily clutch embodiment of transmission shaft is shown in FIG. 8, there is the axial gap in oily input pipe
Compensation.
Correspond to bending spring in terms of the ZMS expansion structure with input terminal 201 according to the compound oily clutch embodiment of Fig. 8
204 and output end 205 and and additional mass 206 and flange position 207 combination, and in compound oily clutch and its manipulation
And transmission input shaft corresponds to the description of above-mentioned combination Fig. 7 with the main feature aspect of cover bottom.
The flange position 207 ' of ZMS has internal messing tooth, outer on it and the clutch hub 208 ' of compound oily clutch
Engaging tooth is in connection, but flange position is constituted in the axial direction shorterly, because radial shaft seal ring directly pushes up on lid 213
It leans against on the outer enclosure face of clutch hub 208 ', grease chamber is sealed relative to dry chamber.
The difference of structure and the structure according to Fig. 7 according to Fig. 8 also resides in supporting scheme, because clutch hub 208 ' is logical
It crosses on the radial and axial transmission input shaft 210 ' for being supported on inside of fixing bearing 209 '.In order to assemble fixing bearing 209 ' from
Clutch wheel hub 208 ' have clutch wheel hub cap 208 ", wherein the outer race of fixing bearing 209 ' be clamped in this lid 208 " with
Between clutch hub 208 '.The inner ring of bearing 209 ' is fixed between the shaft shoulder and fixed ring on axis 210 '.Outer friction piece
The input friction disc support 211 of clutch K1, which corresponds to, to be connect according to the embodiment of Fig. 7 with clutch hub 208 ', wherein equally
Expansion structure traction alms bowl 22 corresponding to Fig. 7 is connect by lid bearing 221 with the shell 222 of CSC.
The expansion structure and formation manipulation bearing, adjustment plate and manipulation blocking of piston-cylinder unit in CSC correspond to
In the content in conjunction with described in Fig. 7.
Furthermore oily clutch is axially supported on clutch hub 208 ' by axis spring and two axial bearings corresponds to knot
Close structure described in Fig. 7.
But it is (hereinafter referred to as " soft equipped with plate 300 flexible herein instead of playing the role of clamping jaw/plate pawl components 223
Plate "), it plays the role of axially and radially upper " soft " torque support.CSC shell 222 is further through outside tubule 301 and speed changer
Oily input pipe in shell connects (passing through at least one tubule of piston-cylinder unit), wherein design tubule length dimension in this way,
It can be realized the axial movement of CSC shell 222.Therefore adagio does not transmit any power in the axial direction.
It is defeated in CSC shell 222 and external speed changer for the system unit that radial support is made of clutch and CSC
Enter and is equipped with transverse bearing 302 between axis 218.
In short, relatively determining with the embodiment according to Fig. 8, system unit clutch/CSC is axially solid by fixing bearing
It is scheduled on internal transmission input shaft.In order to assemble fixed ring in fixing bearing, clutch also has wheel hub cover, it
It is fixed on fixing bearing in clutch and separates grease chamber with dry chamber.Furthermore pressure oil is transported to by horizontal-extending pipe
CSC.These pipes (each separation clutch one pipe) are by sealing towards CSC and clutch cap both sides sealing.Pipe has in the axial direction
There is gap, for axial axis and clutch movement can be compensated.Adagio in existing embodiment it is axial constitute softly and with
With the movement of clutch.The friction that adagio is rigidly constituted in a circumferential direction and bearing is connected in bearing on cover bottom turns
Square.Adagio is not made of the components of rotational symmetry necessarily herein, but can also be made of lath, it and CSC and cover
Bottom screws.
It is supported on internal transmission input shaft and right as shown, clutch passes through fixing bearing radially
It is supported between external transmission input shaft and CSC shell on the side set by lid bearing and needle bearing.
The embodiment of the compound oily clutch of axial suspension bearing is shown in FIG. 9, there is radial oily input pipe.
It is consistent with according to the embodiment of Fig. 8 in many features according to the embodiment of Fig. 9, therefore only describe below according to figure
Difference between these clutches of 8 and Fig. 9.Position from crankshaft 200 to clutch hub 208 ' is in the reality according to Fig. 8 and 9
It applies in example and is consistent.First main difference is that, between clutch hub 208 ' and built-in transmission input shaft 210 "
Bearing is made of axial floating bearing, because while the outer race of bearing 400 is clamped in clutch wheel hub cap 208 " and clutch
Between device wheel hub 208 ', but the bearing inner ring of bearing 400 is not fixed on transmission input shaft 210 ".
Furthermore the consistent place of the embodiment of Fig. 8 and 9 is as follows, is equipped with adagio 300, it connects CSC shell 222 and cover bottom
224, but be provided with another form of radial oily input pipe herein, by be arranged radially the oil input in transmission side with
Pipeline 401 and 402 between CSC.CSC shell 222 is supported on external speed change further through radial needle bearing 302 radially
On device input shaft 218.
In short, system unit clutch/CSC is by floating bearing radial support in inside in the embodiment according to Fig. 9
Transmission input shaft on.Input clutch in external speed changer by lid bearing and needle bearing radial support
Between axis and CSC shell.Furthermore adagio 300 and spring are suspended at according to the compound oily clutch axial suspension of this embodiment
Between 403,404, they are being required for generating in the double mass flywheel to rub substantially.Furthermore the pilot oil of clutch exists
Radially by two pipelines, wherein constituting pipeline in this way, them is allow to bear the axial movement of clutch.Each pipe
Road, which is for example in charge of by two, to be formed, wherein the pipeline section being located in CSC shell assembles jointly with system unit, is then in charge of second
It is introduced into clutch cap across aperture and is in charge of with first and connect.The link position of pipeline section seals against each other and so respectively
It constitutes, the pressure (being not shown herein) for allowing to bear to act on pipeline longitudinal direction.For separated grease chamber and dry chamber, at this
In there are additional sealings between the aperture of clutch cap and second are in charge of.
The embodiment of the multiple clutch of another axial suspension bearing is shown in FIG. 10, there is adagio bearing herein.
Embodiment according to Figure 10 includes compound oily clutch, has clutch hub 208 and clutch hub 208 exists
It is supported on internal transmission input shaft 210 by floating bearing 209, as front has been combined as Fig. 7 described.Furthermore
Embodiment according to Figure 10 includes the connecting flange 207 between the output end 205 of ZMS, it corresponds to the method for combining Fig. 7 description
It is blue.This is externally provided with the components 212 of shell-like, it was described also in conjunction with Fig. 7.Furthermore clutch case 213 and compound oily clutch
Feature, combine with two axial needle bearings particularly by axis spring 219 and axial to be supported on clutch hub 208 and pass through
The manipulation for pressing alms bowl 226 and 227 corresponds to the content in conjunction with described in Fig. 7.This is especially also applied in CSC shell 222 and outside
Transmission shaft 218 between not only in the embodiment according to Fig. 7 but also in the embodiment according to Figure 10 all without radial support.
But it is as follows according to the difference of two embodiments of Fig. 7 and Figure 10, in CSC in the embodiment according to Fig. 7
Shell is equipped with axial attachment, and 222 radial support of CSC shell is in clutch cap 224 on it, and in the implementation according to Figure 10
Adagio 500 is equipped in example, it connect CSC shell 222 with cover bottom 224, wherein the connection position between adagio 500 and cover bottom
It sets and is radially arranged in other than compound oily clutch diameter, for being easy to assemble accordingly.
It is similar with according to the embodiment of Fig. 9, it is hydraulic for supplying CSC equipped with the oily input pipe for passing through tubule 501 and 502
Medium.The tubule 501 and transmission shell for being driven shell side herein screw.Furthermore the tubule of the side CSC, which is bolted, is fixed on
On CSC shell 222.Tubule 501 and 502 can be axially opposite mobile and seal against each other, and two of them tubule 501 and 502 is basic
Extend radially.
In short, in motor side to pass through floating bearing radial by system unit clutch/CSC in the embodiment according to Figure 10
It is supported on internal transmission input shaft.(=transmission side) clutch is supported on radial through lid bearing and adagio over there
In clutch cap.The oil-piping part of the side CSC is connect and is sealed with CSC by bolt.Second pipeline section (gearbox case side)
It is screwed with clutch cap by flange and is sealed by O-ring from the outside.Oily input pipe also structure in the axial direction softly herein
At for that can bear the axial movement of clutch and system unit is made to be suspended in double mass flywheel between adagio and spring
On, as in conjunction with as having been noted above Fig. 9.
The multiple clutch of another axial suspension bearing is shown in FIG. 11, there is adagio bearing herein, wherein adding
Ground for axial suspension supports and adagio bearing is equipped with and is supported between crankshaft and clutch by guide post.Herein according to Figure 11
This structure it is consistent with according to the structure of Figure 10, be provided with guide post 600, it is configured to the extension body of clutch hub 208.
Floating bearing (such as radial needle bearing) is set between guide post 600 and crankshaft 200.
The embodiment of another compound oily clutch is shown in FIG. 12, there is dry type ZMS.
ZMS is exemplified according to the implementation of Figure 12, there is the bending spring built in radial external bending spring and radial direction, it especially can be with
Used in the internal combustion engine with obvious rotation uniformity, but the structure of ZMS for multiple clutch and ZMS with it is compound
The expansion structure of connection between clutch and the meaning that do not limit to also for the manipulation device of multiple clutch.And only
Importantly, being equipped with ZMS and another whirling vibration buffer system between crankshaft 200 and compound oily clutch, there is input terminal
201 and output end 205 ', wherein output flange 207 " is connect with input hub 700 (it corresponds essentially to the structure according to Fig. 1).
The expansion structure of input friction disc support 701 also corresponds to the input friction disc support 13 in conjunction with described in Fig. 1.Furthermore input hub
The input friction disc support of 700 and clutch K1 connected to it corresponds to the transverse bearing according to Fig. 1 by transverse bearing 702
16 radial supports are on internal transmission input shaft 703.Compound grease chamber clutch is accommodated in grease chamber, grease chamber 704 is by cover bottom
Portion 705 and clutch case 706 support, wherein radial shaft seal ring is equipped between clutch case 706 and input hub 700, it
In 707 upper rotary of the surface of revolution, the surface of revolution is placed on the outer enclosure line of clutch hub, and wherein this surface of revolution 707 is in axis
Upwards in order to which axial grafting is engaged between ZMS output flange 707 " and clutch hub 700.
The output friction plate bracket 708 of external friction disk clutch K1 and the output flange of subordinate are equally largely
The upper output friction plate bracket 13 and output flange 14 for corresponding to the embodiment according to Fig. 1.Radially thereto built-in friction plate from
The input friction disc support of clutch K2 corresponds largely to the input friction disc support 18 of friction disk clutch K2, wherein
It is used and the company according to Fig. 1 in the embodiment according to Figure 12 between the input friction disc support of friction disk clutch K1 and K2
The different connecting plate 709 alternatively formed of fishplate bar 17.This connecting plate 709 is constituted substantially planarly and including connection strap
709A, it is outstanding from connecting plate 709, their press alms bowls 711 as friction disk clutch K2 built in radial direction
The support strip of reset spring 710 uses.Connecting plate 214 further includes cylindrical neck in the embodiment according to Fig. 7 and Fig. 8,
It has been used as the guide way of the press alms bowl of clutch K2 to use.This cylindrical neck is in the embodiment according to Figure 12
Fall, wherein realizing guiding by the cylindrical end face area of the connecting plate of neck plane.In the embodiment according to Fig. 7 and Fig. 8
Bearing position of the cylindrical neck equally as the reset spring of the press alms bowl of outer clutch K1 uses.Instead of this
Cylindrical neck portion is equipped with annular element 712, it is supported on connecting plate 709 and it passes through including 713 radial centering of fixed ring
On the input friction disc support of portion clutch K2, and it also has the position radially extended other than cylindrical portion,
The reset spring 713 of the press alms bowl 714 of outer clutch K1 is supported thereon.Reset spring 713 and top in clutch K1 and K2
It presses between alms bowl 714 or round steel wire elastomeric element is set between reset spring 710 and press alms bowl 711, support spring on it
Each end face area.
Similar with according to the embodiment of Fig. 7, the shell 715 of CSC is by axially extending attachment 715A radial centering in cover
It is clamped axially on cover bottom on bottom 705 and by corresponding to the components 716 that clamping jaw/plate pawl functions.
Lid bearing 717 is mutually tied by round steel wire clamping ring with the inclined surface constituted on bearing inner ring on CSC shell 715
Conjunction is fixed in the axial direction, and in order to can establish the inside force flow of steering force, rectangular cross section is used in the embodiment according to Fig. 7
The ring that rises.
There is no additional transverse bearing position between CSC shell 715 and hollow shaft 718.
In short, including following feature according to the structure of Figure 12:
1. the first interstitial site in torque flow is located at behind the friction plate group of external clutch K1.Because this
Gap position is located at behind friction system, does not generate click noise in operation herein.
2. back pressure spring passes through the round steel wire ring bearing being either open or closed.Thus the better bullet in controlled clutch is obtained
Spring rolling characteristic, this leads to the basic lag for reducing steerable system.
3. for the back pressure spring of clutch K1 outside by the circular ring bearing constituted on traction alms bowl, it passes through inside
The fixed ring of the outer friction plate rack of clutch is felt relieved.
4. it is connected with each other the input friction disc support of two clutches on connecting plate or linking arm, internal straight
There are multiple stylus pins on diameter, support the back pressure spring of internal clutch on it.
5. in order to which axial needle bearing of feeling relieved (also can choose slider disc) squeezes out draw pin (at least three) from plate.
6. the lid bearing of clutch, it is centered on CSC by bearing inner ring, passes through the ring bearing axial direction that rises on CSC
The steering force of generation.This ring that rises can have rectangle or circular cross section.Using round steel wire rise ring when generate in CSC
Than using rectangle rise ring when smaller peak stress.
The annular piston of 7.CSC has the gap (other than piston seal) with CSC shell and piston guide length
Ratio with piston inner diameter is less than 0.5.Thus piston can not only move axially in the shell, but also tumble, and therefore hold
Carry on a shoulder pole universal joint function.When making clutch tumble based on CSC due to error and in operation due to dynamic effect, the piston of CSC
This is compensated to tumble or this is followed to tumble.
8. cooling oil is transported to the clutch between the output friction plate bracket of clutch.Oil passes through press body flowing, top
Laminate has the slot radially extended.Then it the oily through-flow hole being placed in internal clutch internal friction plate rack and subsequently enters
The pressure chamber of internal clutch.
9. the input friction disc support of outer clutch and the output friction plate bracket of two separation clutchs pass through axial rolling
Needle bearing (or rolling disk or slider disc) is spaced apart from each other.In order to which interference-free operation must exist axially when using needle bearing
Minimum preload.This load is generated by axis spring or pressure spring, it is located at and is supported on needle roller and the outside change of internal clutch
Between the fixed ring or step of fast device input shaft.Preload spring can be with the internal diameter that is not located on wheel hub shown in Figure 12
On, as shown in connection with fig. 7.
10. passing through the step branch that is combined in outer clutch wheel hub for being spaced the axial bearing of output friction plate bracket
It holds.
11. functionally without the axial axis between the outer friction plate rack and clutch case of external clutch K1
(grease chamber isolation) is held, because the preload of axis spring can also be born by the lid bearing of clutch, as below with reference to Figure 13 institute
Show with it is described as.
The embodiment of another compound oily clutch in figure 13 illustrates, has dry type ZMS, wherein removing in external clutch
Axial bearing between the outer friction plate rack and clutch case of device K1, because being functionally not necessarily to this bearing, such as ibid
As face is explained.It is consistent with each other according to the other parts and Figure 13 of Figure 12 embodiment.
The embodiment of another compound oily clutch is shown in FIG. 14, there is the force flow of internal distribution and with oil operating
ZMS and centrifugal force pendulum (" FKP ").This embodiment and the essentially identical therefore following description of the embodiment according to Fig. 4 to 6 are only
The difference being confined between these embodiments.
Embodiment according to Figure 14 includes CSC shell 800, it includes axial step 801, makes CSC shell diameter by it
To being centered in cover bottom 802, wherein there is no other transverse bearing positions between CSC shell 800 and transmission input shaft 803
It sets.800 axis of CSC shell is upwardly through corresponding to clamping jaw/plate pawl component 804 (it includes radial external bolt hole 805) phase
For 802 axial grip of cover bottom.The ring 806 that rises of circular cross section is equipped on the outer enclosure face of CSC shell 800, it makees
For the positioning surface of the bearing inner ring of lid bearing 807.The input friction plate branch that lid bearing 807 passes through traction alms bowl 808 and clutch K1
Frame connection, it is connect by connecting plate with the input friction disc support of clutch K2.Clutch K1 and K2 pass through substantially rigid
It presses alms bowl to manipulate with the lever ratio of 1:1, wherein setting manipulation bearing and tune between press alms bowl and the piston-cylinder unit of CSC
Whole disk, wherein the input friction disc support of clutch K1 and K2 and output friction plate bracket and manipulation blocking, adjustment plate and behaviour
The feature that the longitudinal axis is held corresponds to the feature in conjunction with described in Fig. 4.
But the output friction plate bracket 809 of the friction disk clutch built in radial direction in its structure with according to Fig. 4 from
The structure of the output friction plate bracket 45 of clutch K2 is different, as described below:
Output friction plate bracket 809 is in addition to having the cylindrical portion for hanging the axial grafting engaging tooth of each friction plate
Also there is the part radially extended, as the connection of connecting flange 810, it makes output flange 809 and hollow speed change other than point
Device input shaft 803 passes through axial grafting engaging tooth connection.The position setting that this is radially extended in the embodiment according to Figure 14
In the motor side of friction plate group, and the speed change of friction plate group is arranged in the position radially extended in the embodiment according to Fig. 4
Device side.Furthermore output friction plate bracket 809 includes fracture 811, and the friction plate of clutch K2 can be flowed to across its cooling oil
Group.In order to purposefully guide cooling oil stream, it is equipped with plate 812, it is arranged in connecting flange 810 and output friction plate bracket
Between 809 cylindrical part.
Remaining feature of this embodiment please refers to the description of Fig. 4 and there.
The embodiment of another compound oily clutch is shown in FIG. 15, there is internal closed force flow and with oil operating
ZMS and centrifugal force pendulum (" FKP "), wherein having been left out the plate pawl or clamping jaw 804 according to Figure 14.Such as it can also be by correspondingly
Selection is in ZMS and/or in the friction disc support of installation and/or between crankshaft and ZMS input terminal/clutch input
Prestressing force in the friction spring of axial action in connecting plate is realized for CSC shell and covers what the connection between bottom sealed
It pre-tightens.
Describe the present invention only in conjunction with multiple clutch apparatus above, wherein in this respect, it is noted that the present invention, especially make
It can also be used in combination with single-acting clutch with the structural unit being made of clutch and manipulation device and clamping jaw/plate pawl.
Claims (4)
1. a kind of clutch apparatus, for driving system, the speed changer with driving unit and postposition, the clutch apparatus has extremely
A few friction disk clutch, the friction disc support and alternately friction in the axial direction that they are respectively provided with input terminal and output end
Piece also has manipulation device, and wherein several friction disk clutch are several with it in other words with its manipulation device for friction disk clutch
Manipulation device is combined into a structural unit by lid bearing, wherein manipulation device/several manipulation devices shell relative to from
Clutch cover is pre-tightened by clamping component in the axial direction, which bears the power and torque that occur in operation, the clamping section
Part is that alms bowl type, clamping jaw, the link position between plate pawl or flexible board, with clutch cap are radially arranged in the friction plate clutch
Other than device diameter.
2. clutch apparatus as described in claim 1, which is characterized in that the friction disk clutch is radially arranged up and down,
The input terminal friction disc support of the friction disk clutch of radially outer passes through support plate or bearing alms bowl radial direction rotatably but axis
To on the shell for being fixedly supported at manipulation device, the force flow of the steering force generated by manipulation device is thus made to pass through radially outer
The bearing of axial restraint of friction disc support of input terminal be supported on the shell of manipulation device, and be presented on clutch device
Set internal closed force flow.
3. clutch apparatus as described in claim 1, which is characterized in that the wherein manipulation device/several manipulation devices
Shell have axial projection or gap, by it transmission side in clutch cap radial support by clutch and manipulation device
The structural unit of composition inputs wherein another radial support is located at clutch input hub by floating bearing with a speed changer
Between axis.
4. clutch apparatus as claimed in claim 1 or 2, which is characterized in that the clutch apparatus tool there are two friction plate from
Clutch.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009053887.9 | 2009-11-20 | ||
| DE102009053887 | 2009-11-20 | ||
| DE102010014718 | 2010-04-12 | ||
| DE102010014718.4 | 2010-04-12 | ||
| PCT/DE2010/001342 WO2011060763A2 (en) | 2009-11-20 | 2010-11-15 | Clutch system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102575722A CN102575722A (en) | 2012-07-11 |
| CN102575722B true CN102575722B (en) | 2019-05-28 |
Family
ID=43598536
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080045671.XA Expired - Fee Related CN102575722B (en) | 2009-11-20 | 2010-11-15 | Clutch apparatus |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5738305B2 (en) |
| CN (1) | CN102575722B (en) |
| DE (2) | DE102010051447A1 (en) |
| WO (1) | WO2011060763A2 (en) |
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| DE102016223277A1 (en) | 2016-11-24 | 2018-05-24 | Schaeffler Technologies AG & Co. KG | coupling device |
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| DE102017114439A1 (en) | 2017-06-29 | 2019-01-03 | Schaeffler Technologies AG & Co. KG | clutch assembly |
| DE102017118288B3 (en) * | 2017-08-11 | 2018-11-15 | Schaeffler Technologies AG & Co. KG | Slave cylinder with transport lock and coupling with pressure pot and slave cylinder |
| DE102021207065B4 (en) | 2021-03-29 | 2023-05-17 | Magna Pt B.V. & Co. Kg | Multi-plate clutch arrangement, in particular a triple-plate clutch with connected compensation chambers |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN1637310A (en) * | 2003-12-23 | 2005-07-13 | 卢克摩擦片和离合器两合公司 | Torque transmitting unit and drive train for it |
| DE102006010707A1 (en) * | 2006-03-08 | 2007-09-13 | Zf Friedrichshafen Ag | Dual clutch device for e.g. commercial motor vehicle-drive train, has gear with two gear input shafts that are assigned to respective clutch arrangements that are implemented as dry running multi-disk-clutch arrangements |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2517000B1 (en) * | 1981-11-24 | 1987-03-20 | Peugeot | HYDRAULIC CONTROL FOR FRICTION CLUTCH |
| FR2745616B1 (en) * | 1996-02-29 | 1998-04-10 | Valeo | HOLDING DEVICE, ESPECIALLY FOR A MOTOR VEHICLE |
| DE10138722C5 (en) * | 2000-08-17 | 2017-05-24 | Schaeffler Technologies AG & Co. KG | powertrain |
| JP4006187B2 (en) * | 2001-03-08 | 2007-11-14 | ジヤトコ株式会社 | Transmission unit |
| DE10223780C1 (en) * | 2002-05-29 | 2003-10-16 | Porsche Ag | Gear shift mechanism, for an IC motor with a multiple hydraulic clutch, has a bearing flange around the gear housing opening as a support for the roller bearing between it and the clutch cage with the drive hub |
| FR2851627B1 (en) * | 2003-02-20 | 2005-12-30 | Valeo Embrayages | TORQUE TRANSMISSION DEVICE FOR MOTOR VEHICLE |
| JP4520762B2 (en) * | 2003-05-20 | 2010-08-11 | ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト | Drive train |
| DE102006049731A1 (en) | 2005-11-11 | 2007-05-31 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Clutch actuating device for dual clutch transmission, has first clutch actuator and second clutch actuator whereby each rotary lever has spherical external teeth which stand in intervention with internal geared receiving-sleeve |
| DE102007022422A1 (en) * | 2007-05-10 | 2008-11-13 | Borgwarner Inc., Auburn Hills | Double clutch arrangement with piston guide element |
| DE102009006649B4 (en) * | 2008-02-11 | 2021-06-17 | Schaeffler Technologies AG & Co. KG | Double clutch arrangement |
| CN102227573B (en) * | 2009-01-19 | 2014-04-23 | 舍弗勒技术股份两合公司 | Multiple clutch device |
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2010
- 2010-11-15 DE DE102010051447A patent/DE102010051447A1/en not_active Withdrawn
- 2010-11-15 DE DE112010004490T patent/DE112010004490A5/en not_active Withdrawn
- 2010-11-15 JP JP2012539179A patent/JP5738305B2/en not_active Expired - Fee Related
- 2010-11-15 WO PCT/DE2010/001342 patent/WO2011060763A2/en active Application Filing
- 2010-11-15 CN CN201080045671.XA patent/CN102575722B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1637310A (en) * | 2003-12-23 | 2005-07-13 | 卢克摩擦片和离合器两合公司 | Torque transmitting unit and drive train for it |
| DE102006010707A1 (en) * | 2006-03-08 | 2007-09-13 | Zf Friedrichshafen Ag | Dual clutch device for e.g. commercial motor vehicle-drive train, has gear with two gear input shafts that are assigned to respective clutch arrangements that are implemented as dry running multi-disk-clutch arrangements |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013511668A (en) | 2013-04-04 |
| JP5738305B2 (en) | 2015-06-24 |
| CN102575722A (en) | 2012-07-11 |
| WO2011060763A3 (en) | 2011-07-21 |
| WO2011060763A2 (en) | 2011-05-26 |
| DE102010051447A1 (en) | 2011-05-26 |
| DE112010004490A5 (en) | 2012-10-11 |
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