CN104696384A - Wet type running radial double clutch - Google Patents
Wet type running radial double clutch Download PDFInfo
- Publication number
- CN104696384A CN104696384A CN201410727244.XA CN201410727244A CN104696384A CN 104696384 A CN104696384 A CN 104696384A CN 201410727244 A CN201410727244 A CN 201410727244A CN 104696384 A CN104696384 A CN 104696384A
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- CN
- China
- Prior art keywords
- clutch
- friction plate
- plate rack
- radial
- internal friction
- 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
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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
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
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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
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
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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
-
- 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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- 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
- F16D2300/00—Special features for couplings or clutches
- F16D2300/02—Overheat protection, i.e. means for protection against overheating
- F16D2300/021—Cooling features not provided for in group F16D13/72 or F16D25/123, e.g. heat transfer details
- F16D2300/0214—Oil or fluid cooling
Landscapes
- 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
Provided is a wet type running radial double clutch, comprising a radial internal first clutch and a radial internal second clutch. The first clutch and the second clutch are arranged in a manner of rotating around a shared rotation axis. A first cooling channel is provided for radially converying liquid to the first clutch, and a second cooling channel is provided for radially conveying liquid to the second clutch. An isolation element is provided for isolating the first cooling channel from the second cooling channel.
Description
Technical field
The present invention relates to the radial double clutch that a kind of wet type is run.The invention particularly relates to cooling channel, for the clutch of radial delivery liquid to this radial double clutch.
Background technique
Dual-clutch transmission comprises the first input shaft and the second input shaft, and they are directed to the shelves gear mesh acted on public output shaft.Following double clutch is needed: it makes foundation that between drive motor with two input shafts, moment of torsion is sealed or separates and can realize independently of each other in order to be coupled in dual-clutch transmission by the moment of torsion of drive motor.The driven shaft of drive motor and the input shaft of dual-clutch transmission support usually mutually coaxially, are thus suitable for arranging with making two of this double clutch clutch coaxials and or radial or axially offset one from another.
In the double clutch of radial-type, two clutches stagger diametrically mutually.Can realize shorter double clutch axial arrangement length thus, such as, when the power assembly system comprising drive motor, double clutch and dual-clutch transmission will be installed transverse to direction of travel in a motor vehicle, this is useful.If radial double clutch wet type operably constructs, be then provided with at least one cooling channel, be directed to the friction means of clutch for making liquid, normally motor oil or transmission oil from inner radial and discharge at radial outside.The liquid of usually discharging with the clutch built-in from radial direction in the radial double clutch that wet type is run supplies radial external clutch.
In order to ensure the clutch sufficiently cooling radially outer, must make by the liquid volume flow of inner radial clutch sufficiently large, for making the clutch that may can also be used for sufficiently cooling radially outer by the liquid of radial built-in clutch heating.The volume flowrate that for this reason will provide may be large, and relatively large power may be needed thus for maintaining volume flowrate.
Usually in these two clutches, only clutch is closed and another is opened.However, the volume flow of liquid flows through clutch that do not cool accordingly, that open, produces simultaneously and pulls moment of torsion.Pull moment of torsion and depend on the size of volume flowrate and the gear synchronism that may affect in dual-clutch transmission.Make thus to need the longer time for the shift time of gear shift in dual-clutch transmission, produce travelling comfort and power character problem thus.
Summary of the invention
The object of the invention is, provide and the clutch of the radial double clutch that wet type is run better is cooled.The present invention utilizes the double clutch with independent claims feature to achieve this end.Dependent claims provides preferred embodiment.
The radial double clutch that wet type is run comprises the first clutch of radially outer and a second clutch for inner radial, and described first clutch and second clutch are rotatably arranged around public spin axis.In addition, the first cooling channel is set for radial delivery liquid to first clutch, the second cooling channel is set for radial delivery liquid to second clutch, wherein, provides an isolated component for isolating the first cooling channel and the second cooling channel.
Can realize thus for that cool first clutch and second clutch, different liquid volume flow.Described volume flowrate can regulate independently of each other according to the manipulation of each clutch, wherein especially when the clutch of subordinate has the cooling requirement of minimizing, such as, when this clutch is opened completely time, can reduce volume flowrate.In the corresponding way, such as, when this clutch is only partly opened and is in friction slip, the volume flowrate of the clutch with large cooling requirement can be improved.The flow resistance of the total volumetric flow rate for cooling two clutches can be reduced.The synchronism of the dual-clutch transmission being placed on this double clutch can be improved.
In a preferred embodiment, described isolated component comprises an independently component.Also preferably, described isolated component is the structural element that a friction disc support being both different from first clutch is also different from the friction disc support of second clutch.Thus can better with to associated clutch or from the power transmission of associated clutch independently structurally treatment fluid to the guiding of each clutch.Especially can with isolated component described in the size design significantly less than friction disc support section, because its not transmitting torque in this clutch engagement force stream.
Preferably, described isolated component extends between the second area of the second axial end portion of the first area of the first axial end portion of the internal friction plate rack of first clutch and the outer friction plate rack of second clutch, and wherein said axial end portion is reciprocally arranged.
The liquid flowed out from second clutch at radially outer can be made thus to keep separating with the liquid flowing into first clutch in inner radial.Described isolated component can cause the deflection in the axial direction of one or two volume flow.
In a modification, described isolated component is fixed on the internal friction plate rack of first clutch in the first region, and forms gap with the outer friction plate rack of second clutch in the second area.This gap is preferably annular gap.When enough hour of this gap, liquid overflow by this gap between the first cooling channel and the second cooling channel can be tolerated.By this isolated component is fixed on the internal friction plate rack of first clutch, although this gap may become large when high rotating speed, the collision between the outer friction plate rack eliminating isolated component and second clutch under centrifugal action.
In another modification, described isolated component is fixed on the outer friction plate rack of second clutch in the second area, and forms gap with the internal friction plate rack of first clutch in the first region.Isolated component can be settled like this, this gap is extended in the axial direction.Described isolated component can reserve sufficient space in the first region on radial outside, for allowing isolated component to be out of shape when high rotating speed, and the parts of isolated component and first clutch can not be made to collide.Liquid is lower by the overflow harm in this gap in this variant, because liquid is in the interface of first clutch, and it natively should be guided by there.
Preferably, described isolated component is made up of sheet material.This sheet material such as utilize deep-draw can simply and cost advantages make.One preferred embodiment described in sheet material radial symmetric and basic tank shape form.In another embodiment, described isolated component also can be made of plastics.Buckle connection can be used in order to be fixed on friction disc support in this case, locking connects or clamping connects.
Described first clutch can comprise the flange for axially handling, and wherein said flange has the radial opening for the liquid flowed out from second clutch.Can avoid thus, the liquid from the heating in second clutch region flow in first clutch region.
Described first clutch can comprise outer friction plate rack, and it has the radial opening for the liquid flowed out from second clutch.The liquid radially outward discharge in a better way from second clutch can be made thus.
First cooling channel can axially be bound between the radial segment of the radial segment of the internal friction plate rack of first clutch and the internal friction plate rack of second clutch within the radial direction of the inner diameter of the internal friction plate rack of first clutch.
Second cooling channel can axially be bound between the radial segment of the internal friction plate rack of second clutch and radial that extend, handle second clutch for axis flange within the radial direction of the inner diameter of the internal friction plate rack of second clutch.
If described cooling channel continues between an axle and a hollow shaft or between two hollow shafts in the axial direction in inner radial, so especially latter two mode of execution above-mentioned advantageously can be used.
Accompanying drawing explanation
The present invention is described in detail below, in the accompanying drawings by accompanying drawing
Fig. 1 illustrates the half-sectional view of the radial double clutch that wet type is run,
Fig. 2 illustrates the view of Fig. 1, indicates the flowing of liquid to two clutches,
Fig. 3 illustrates the detailed drawing of Fig. 2 in this clutch region.
Embodiment
Fig. 1 illustrates the half sectional view of the radial double clutch 100 that wet type is run.First clutch 110 and a radial built-in second clutch 130 of a radially outer is furnished with around spin axis 102.First clutch 110 comprises the first outer friction plate rack 112 and the first internal friction plate rack 114, alternately settles the first friction element 116 and the first friction plate 118 between the first outer friction plate rack and the first internal friction plate rack in the axial direction.Friction plate 118 is preferably made of steel and serve as a contrast with other friction unlike friction element 116.At this first friction element 116 moment of torsion in locking manner and be axially movably connected with the first internal friction plate rack 114, and the first friction plate 118 moment of torsion in locking manner and be axially movably connected with the first outer friction plate rack 112.The stacking first clutch 110 that can make be made up of the first friction element 116 and the first friction plate 118 axial compression closes, for transmitting torque between the first outer friction plate rack 112 and the first internal friction plate rack 114.In another embodiment, also can attach troops to a unit in the first outer friction plate rack 112 by the first friction element 116, and the first friction plate 118 is attached troops to a unit in the first internal friction plate rack 114.Also two-sided friction plate 118 or two-sided friction element 116 can be used.
Be provided with flange 120 to handle first clutch 110, it is illustratively embodied as hydraulic piston in the present embodiment.Clutch spring 122 be arranged to make flange 120 axial compression be made up of the first friction element 116 and the first friction plate 118 stacking on.If set up hydraulic pressure inside the first hydraulic pressure room 124, flange 120 is extruded by the power against clutch spring 122, make to act on by the first friction element 116 and the first friction plate 118 form stacking on axial pressure relax and the sealed reduction of moment of torsion between the first outer friction plate rack 112 and the first internal friction plate rack 114.In the present embodiment, supported by axially support 126 by being stacked in contrary axial side of forming of the first friction element 116 and the first friction plate 118.Axially support 126 can radial direction be placed on the first outer friction plate rack 112.
In another mode of execution of double clutch 100, also can be realized the axially extruding mutually of the first friction element 116 and the first friction plate 118 by alternate manner.Replace spring force especially also can utilize the hydraulic pressure in the first hydraulic pressure room 124, for performing the extruding mutually of this axis.In another embodiment, replace hydraulically, mechanically handle first clutch 110.Equally alternately utilize first clutch spring 122 at this first clutch 110 or utilize this manipulation to close.
Second clutch 130 preferably basic and first clutch 110 forms similarly and comprises the second outer friction plate rack 132 and the second internal friction plate rack 134, extends the second friction element 136 and the second friction plate 138 between the second outer friction plate rack and the second internal friction plate rack diametrically.In order to handle second clutch 130, be provided with the second flange 140, it is illustratively configured to hydraulic piston equally.At this, if the hydraulic pressure in the second hydraulic pressure room 144 is enough large, then the force direction work done on the contrary of the second flange 140 and second clutch spring 142.The modification relating to first clutch 110 described above or imply also can be applied to second clutch 130 independent of first clutch.
Clutch 110 in shown preferred implementation, 130 are connected in locking manner with mutually concentric axle moment of torsion.Exemplarily, solid shaft 150 is connected with the first internal friction plate rack 114, and the first hollow shaft 152 is connected with the second internal friction plate rack 134.Engaging tooth is preferably utilized to transmit a torque to axle 150,152 at this.Be arranged radially at the first hollow shaft 152 to be connected with the first outer friction plate rack 112 and the second outer friction plate rack 132 in locking manner with the preferred moment of torsion of the second hollow shaft 154 outside solid shaft 150.Axially support 126 can be connected with the first outer friction plate rack 112 by moment of torsion equally in locking manner.Alternatively, engaging tooth can be settled in axially support 126, for importing or deriving moment of torsion and ensure assembling.
Usually in power assembly system, axially support 126 is utilized to make moment of torsion import to clutch 110 from drive motor, the outer friction plate rack 112,132 of 130.Imported to second clutch 130 by the first outer friction plate rack 112, second hollow shaft 154 and the second outer friction plate rack 132 from first clutch 110 at this moment of torsion.This moment of torsion is sent to solid shaft 150 by first clutch 110 and is sent to the first hollow shaft 152 by second clutch 130 independently therewith.Solid shaft 150 and the first hollow shaft 152 arrange and are connected with the input shaft of dual-clutch transmission in locking manner for moment of torsion.
An isolated component 160 is furnished with in the radial zone between the outer diameter and the inner diameter of the first internal friction plate rack 114 of the second outer friction plate rack 132.This isolated component preferably includes a section extended radially outwardly, and it is transitioned into an axially extended section, and this axially extended section itself adjoins a section extended radially outwardly, and obtains S or Z-shaped shape thus in shown longitudinal sectional drawing.This isolated component 160 extends to second area 164 from first area 162 in the axial direction, wherein, first area 162 is positioned on the first axial end portion of the first internal friction plate rack 114, and second area 164 is positioned on the second axial end portion of the second outer friction plate rack 132.That is, two regions 162 and 164 are not preferably opposed each other, but setting opposite each other is axially misplaced in other words mutually.
In the mode of execution shown in Fig. 1, this isolated component 160 is fixed on the first internal friction plate rack 114 in first area 162, in second area 164, form gap 166 between isolated component 160 and the second outer friction plate rack 132.In the mode of execution substituted, this isolated component 160 also can be fixed on the second outer friction plate rack 132 in second area 164, and forms gap 166 relative to the first internal friction plate rack 114 in first area 162.The liquid that can be reduced by gap 166 in this case thus is further through-flow: the friction disc support region being positioned at gap 166 axial rearward of the first internal friction plate rack 114 extends radially inwardly in that side of isolated component 160, as illustratively seen on the second internal friction plate rack 134 in FIG.
Gap 166 is preferably little as much as possible in both cases, is difficult to be overflowed by gap 166 to make liquid.Usually gap 166 can be made no problemly so littlely to form, make its cross section sufficiently little, to such an extent as to the amount of liquid flowed out by gap 166 can be ignored.
Fig. 2 illustrates the view of Fig. 1, indicates the flowing of liquid to these two clutches 110 and 130.First liquid stream 205 profit is indicated by the solid line and be directed to first clutch 110.Second liquid stream 210 profit is represented by dashed line and be directed to second clutch 130.
Be described in more detail below the first liquid stream 205 on the radial double clutch 100 run in this exemplary wet type, wherein liquid stream 205 until isolated component 160 guiding and enter into the later guiding of first clutch 110 also can be different from shown in implement.
First liquid stream 205 is in first diametrically in the region between solid shaft 150 and the first hollow shaft 152 and flows through.Liquid flows to the first internal friction plate rack 114 left along two axles 150,152 in the view of Fig. 2 always, then flows radially outward.In this region, first liquid stream 205 is bound between the radial segment of the first internal friction plate rack 114 and the radial segment of the second internal friction plate rack 134.In the region of second clutch 130, the insignificant sub-fraction of first liquid stream 205 enters into inside second clutch 130, and cools this clutch.Remaining first liquid stream 205 continues to flow radially outward second area 164.Another insignificant fraction of first liquid stream 205 may lose through the gap 166 isolated component 160 and the second outer friction plate rack 132.Then first liquid stream 205 continues flowing in the axial direction, and wherein, it is bound between the first internal friction plate rack 114 and isolated component 160 diametrically.Then first liquid stream 205 flow in the region of the first friction element 116 and the first friction plate 118, for cooling them through the one or more radial openings in the first internal friction plate rack 114.Then first liquid stream is passing radially outward the one or more opening radially outwards outflows in the first outer friction plate rack 112.
Be described in more detail below the second liquid stream 210 on radial double clutch 100 that exemplary herein wet type runs, wherein liquid stream 210 be transported to isolated component 160 region guiding and implement shown in also can being different from the further trend after isolated component 160.
Second liquid stream 210 flows through in the region first in the axial direction between the first hollow shaft 152 and the second hollow shaft 154.In the region of the second internal friction plate rack 134, second liquid stream 210 radially outward deflection and directed with between a radial members be preferably connected with the second hollow shaft 154 in a radial segment of the second internal friction plate rack 134 in the axial direction.Outside in radial direction, second liquid stream 210 is in the axial direction by radial segment and the axial gauge of the second flange 140 of the first internal friction plate rack 134.Then second liquid stream 210 enters into the region of the second friction element 136 and the second friction plate 138 by one or more opening, for absorbing the heat of there.Then second liquid stream 210 is continued to guide this second outer friction plate rack and isolated component 160 through the one or more radial opening in the second outer friction plate rack 132 in the axial direction.In shown preferred implementation, the first flange 120 has opening 215, and second liquid stream 210 then continues flowing diametrically through this opening 215.When be different from shown hydraulic operation this first clutch 110, if be not provided with the first flange piston 120 in other words, so also can remove opening 215.Finally, second liquid stream 210 is alternatively also by radial another opening 220 be arranged in the first outer friction plate rack 112.
Fig. 3 to go out in the view of Fig. 2 clutch 110 and 130 together with the region of isolated component 160 with enlarged icon.
Reference numerals list
100 double clutches
110 first clutches (radially outer)
112 first outer friction plate racks
114 first internal friction plate racks
116 first friction elements
118 first friction plates
120 first flanges (piston)
122 first clutch springs
124 first hydraulic pressure rooms
126 axially support
130 second clutches (inner radial)
132 second outer friction plate racks
134 second internal friction plate racks
136 second friction elements
138 second friction plates
140 second flanges (piston)
142 second clutch springs
144 second hydraulic pressure rooms
150 solid shafts
152 first hollow shafts
154 second hollow shafts
160 isolated components
162 first areas
164 second areas
166 gaps
205 first liquid streams
210 second liquid streams
215 openings
220 another openings
Claims (10)
1. the radial double clutch (100) of wet type operation, comprising:
The first clutch (110) of-radially outer and
The second clutch (130) of-inner radial,
-described first clutch and described second clutch are arranged in the mode that can rotate around a public spin axis (102);
-the first cooling channel (205), for radial delivery liquid to first clutch (110),
-the second cooling channel (210), for radial delivery liquid to second clutch (130),
It is characterized in that
-one isolated component (160), for isolating the first cooling channel (205) and the second cooling channel (210).
2. double clutch (100) as claimed in claim 1, wherein, described isolated component (160) comprises independently component.
3. double clutch (100) as claimed in claim 1 or 2, wherein, described isolated component (160) extends between the second area (164) of the second axial end portion of the first area (162) of the first axial end portion of the internal friction plate rack (114) of first clutch (110) and the outer friction plate rack (132) of second clutch (130), wherein, described axial end portion is reciprocally arranged.
4. double clutch (100) as claimed in claim 3, wherein, in first area (162), be fixed on the internal friction plate rack (114) of first clutch (110) upper and form gap (166) with the outer friction plate rack (132) of second clutch (130) in second area (164) for described isolated component (160).
5. double clutch (100) as claimed in claim 3, wherein, in second area (164), be fixed on the outer friction plate rack (132) of second clutch (130) upper and form gap (166) with the internal friction plate rack (114) of first clutch (110) in first area (162) for described isolated component (160).
6. the double clutch (100) according to any one of the claims, wherein, described isolated component (160) is made up of sheet material.
7. the double clutch (100) according to any one of the claims, wherein, described first clutch (110) comprises the flange (120) for axially handling, further, described flange (120) has the radial opening (215) of the liquid for flowing out from second clutch (130).
8. the double clutch (100) according to any one of the claims, wherein, the outer friction plate rack (112) of described first clutch (110) has the radial opening (220) of the liquid for flowing out from second clutch (130).
9. the double clutch (100) according to any one of the claims, wherein, described first cooling channel (205) is axially bound between the radial segment of internal friction plate rack (114) of first clutch (110) and the radial segment of the internal friction plate rack (134) of second clutch (130) within the radial direction of the inner diameter of the internal friction plate rack (114) of first clutch (110).
10. the double clutch (100) according to any one of the claims, wherein, described second cooling channel (210) is axially bound between the radial segment of the internal friction plate rack (134) of second clutch (130) and radial that extend, handle second clutch (130) for axis flange (140) within the radial direction of the inner diameter of the internal friction plate rack (134) of second clutch (130).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013224796 | 2013-12-04 | ||
| DE102013224796.6 | 2013-12-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104696384A true CN104696384A (en) | 2015-06-10 |
| CN104696384B CN104696384B (en) | 2019-03-15 |
Family
ID=53185536
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410727244.XA Active CN104696384B (en) | 2013-12-04 | 2014-12-03 | The radial double clutch of wet type operation |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104696384B (en) |
| DE (1) | DE102014223033A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109790875A (en) * | 2016-10-06 | 2019-05-21 | 舍弗勒技术股份两合公司 | Double clutch device |
| CN111094780A (en) * | 2017-07-06 | 2020-05-01 | 法雷奥离合器公司 | Output disc carrier for a dual clutch and mechanism comprising such a disc carrier |
| CN113251083A (en) * | 2020-02-11 | 2021-08-13 | 广州汽车集团股份有限公司 | Hybrid power transmission system |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3059378B1 (en) * | 2016-11-30 | 2020-10-30 | Valeo Embrayages | COOLING SYSTEM FOR CLUTCH MECHANISM |
| CN110612400B (en) * | 2017-05-11 | 2021-04-06 | 舍弗勒技术股份两合公司 | Switching unit for cooling oil and hybrid module having a switching unit |
| FR3070458B1 (en) * | 2017-08-29 | 2020-01-10 | Valeo Embrayages | WET CLUTCH MODULE OF A MOTOR VEHICLE |
| FR3097919A1 (en) * | 2019-06-30 | 2021-01-01 | Valeo Embrayages | Piston for clutch mechanism |
| CN112443590B (en) * | 2019-09-05 | 2022-07-22 | 广州汽车集团股份有限公司 | Vehicle and wet-type double clutch |
| DE102021112150A1 (en) | 2021-05-10 | 2022-11-10 | Miba Frictec Gmbh | Method of manufacturing a friction disk assembly |
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| DE102011006027A1 (en) * | 2011-03-24 | 2012-09-27 | Zf Friedrichshafen Ag | Clutch i.e. wet running dual clutch, for transferring torque from drive unit to transmission in drive train of motor car, has ribs arranged such that oil is guided in direction of clutch arrangement after attachment of bearings to hub |
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2014
- 2014-11-12 DE DE102014223033.0A patent/DE102014223033A1/en active Pending
- 2014-12-03 CN CN201410727244.XA patent/CN104696384B/en active Active
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| US6499578B1 (en) * | 1999-09-30 | 2002-12-31 | Mannesmann Sachs Ag | Multiple-clutch device |
| DE102006040506A1 (en) * | 2006-08-30 | 2008-03-20 | Audi Ag | Coupling device, in particular wet-running multi-plate clutch for a motor vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109790875A (en) * | 2016-10-06 | 2019-05-21 | 舍弗勒技术股份两合公司 | Double clutch device |
| CN109790875B (en) * | 2016-10-06 | 2021-03-23 | 舍弗勒技术股份两合公司 | Double clutch device |
| CN111094780A (en) * | 2017-07-06 | 2020-05-01 | 法雷奥离合器公司 | Output disc carrier for a dual clutch and mechanism comprising such a disc carrier |
| CN113251083A (en) * | 2020-02-11 | 2021-08-13 | 广州汽车集团股份有限公司 | Hybrid power transmission system |
| CN113251083B (en) * | 2020-02-11 | 2022-08-19 | 广州汽车集团股份有限公司 | Hybrid power transmission system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN104696384B (en) | 2019-03-15 |
| DE102014223033A1 (en) | 2015-06-11 |
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