CN103615474A - Dry friction type double clutch of automatic transmission - Google Patents
Dry friction type double clutch of automatic transmission Download PDFInfo
- Publication number
- CN103615474A CN103615474A CN201310594301.7A CN201310594301A CN103615474A CN 103615474 A CN103615474 A CN 103615474A CN 201310594301 A CN201310594301 A CN 201310594301A CN 103615474 A CN103615474 A CN 103615474A
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- clutch
- clutch cover
- diaphragm spring
- fluted disc
- platen
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Abstract
The invention discloses a dry friction type double clutch of an automatic transmission. Pressure plates of a clutch cover assembly includes a first pressure plate, a second pressure plate and a third pressure plate, and driven plate assemblies include a first driven plate assembly and a second driven plate assembly. Diaphragm springs of the clutch cover assembly include a first diaphragm spring and a second diaphragm spring, the second diaphragm spring is mounted on the first pressure plate, the first diaphragm spring is mounted on a clutch cover of the clutch cover assembly through a limiting column, and the second diaphragm spring and the clutch cover as well as the first diaphragm spring and the clutch cover are connected through an inner toothed plate and an outer toothed plate respectively. The inner toothed plate and the outer toothed plate are in contact with the clutch cover respectively and connectively through a plurality of bosses thereon. Automatic gapless gear shifting can be realized, power stagnation cannot occur, driving comfortability of a complete vehicle and economical efficiency in fuel conservation and consumption reduction are effectively improved, and the dry friction type double clutch has the advantages of fuel conservation and consumption reduction, high acceleration and automatic gear shifting.
Description
Technical field
The present invention relates to a kind of automobile clutch field, specifically relate to a kind of clutch that is applied to automatic transmission.
Background technique
Traditional clutch cover and plate assembly, owing to being single clutch, in gear switch process, need hand shift, there will be power to stagnate, the speed of a motor vehicle slows down phenomenon, having the problems such as the sense of hysteresis, fuel consume are large, the speed of a motor vehicle is discontinuous while driving, and cause driving comfortability poor, lack dynamic.
Summary of the invention
The deficiency existing for prior art, the object of the present invention is to provide and a kind ofly can realize automatic gapless gear shift, there will not be power to stagnate, and have the dry friction formula double clutch of the automatic transmission of automatic compensation function.
For achieving the above object, the invention provides following technological scheme: the dry friction formula double clutch of automatic transmission, comprise clutch cover and plate assembly, clutch drived disk assy, the platen of described clutch cover and plate assembly is by the first platen, the second platen, the 3rd platen forms, described clutch drived disk assy is by the first clutch drived disk assy, the second clutch drived disk assy forms, the diaphragm spring of described clutch cover and plate assembly is by primary diaphragm spring, secondary diaphragm spring forms, described secondary diaphragm spring is contained on the first platen, primary diaphragm spring is contained on the clutch cover of clutch cover and plate assembly by limited post, and between secondary diaphragm spring and clutch cover, between primary diaphragm spring and clutch cover, pass through separately respectively interior fluted disc, outer tooth disk connects, described outer tooth disk is contained on clutch cover, interior fluted disc is contained under clutch cover, between described clutch cover and interior fluted disc, Regulation spring is all housed between clutch cover and outer tooth disk, contact between this interior fluted disc, outer tooth disk and clutch cover is connected by several boss on inside and outside fluted disc separately respectively, and the end face on these several boss is that interval arranges and has the first stepped tooth.End face on described boss becomes the gradient of 8.8-9.2 degree with horizontal plane, have the inclined-plane stepped tooth of the 8.8-9.2 degree corresponding with interior fluted disc, outer tooth disk on described clutch cover end face.
Further design of the present invention is: between described secondary diaphragm spring and clutch cover, the second supporting ring, the first supporting ring are housed respectively separately between primary diaphragm spring and clutch cover; Described the second supporting ring is contained under interior fluted disc, and this second supporting ring top edge has " 7 " font bearing claw and contacts with the flanged lip on interior fluted disc.Described the second supporting ring is fixed on clutch cover, on described clutch cover, there is crotch, the outside wall portions of described crotch becomes angle with the central shaft of this clutch be 10.8-11.2 degree, can make the crotch head on clutch cover effectively catch the fixed-wing on the second supporting ring.
Adopt technique scheme, in a set of product combining by a clutch cover, double-diaphragm spring, three platens and two clutch drived disk assy, have two cover clutch assemblies, can automatic gapless gear shift, there will not be power to stagnate, there is automatic compensation function, the Economy that has effectively improved driving comfortability energy and the joint combustion consumption reduction of car load, acceleration is fast, and structure space is little, compact to design, stability under loading.
Accompanying drawing explanation
Below in conjunction with drawings and the embodiments, the present invention is described in further detail.
Fig. 1 is the structural representation of the dry friction formula double clutch of automatic transmission of the present invention.
Fig. 2 is the B-B sectional view of Fig. 1.
Fig. 3 is that the K of Fig. 1 is to view.
Fig. 4 is the F-F sectional view of Fig. 1.
Fig. 5 is the interior fluted disc structural representation in Fig. 1.
Fig. 6 is that the H of Fig. 5 is to view.
Fig. 7 is the broken section enlarged view of the mark W in Fig. 6.
Fig. 8 is the structural representation of the combinations such as the clutch cover in Fig. 2, interior fluted disc, the second supporting ring.
Fig. 9 is the second supporting ring structural representation in Fig. 2.
Figure 10 is the fluted disc structure schematic diagram in Fig. 2.
Embodiment
Referring to Fig. 1, Fig. 2, Fig. 3, the dry friction formula double clutch of automatic transmission of the present invention, comprise clutch cover and plate assembly, clutch drived disk assy, the platen of described clutch cover and plate assembly is by the first platen 10, the second platen 12, the 3rd platen 14 forms, described clutch drived disk assy is by the first clutch drived disk assy 11, the second clutch drived disk assy 13 forms (this first clutch drived disk assy 11, the second clutch drived disk assy 13 is contained in respectively between the first platen 10 and the second platen 12, between the second platen 12 and the 3rd platen 14), the diaphragm spring of described clutch cover and plate assembly is by primary diaphragm spring 4, secondary diaphragm spring 9 forms, described secondary diaphragm spring 9 is contained on the first platen 10, primary diaphragm spring 4 is contained on the clutch cover 6 of clutch cover and plate assembly by limited post 2 (and spacing shim 1), and between secondary diaphragm spring 9 and clutch cover 6, between primary diaphragm spring 4 and clutch cover 6, pass through separately respectively interior fluted disc 8, outer tooth disk 3 connects, (as Fig. 4, Fig. 5, shown in Fig. 6 and Fig. 7) described outer tooth disk 3 is contained on clutch cover 6, interior fluted disc 8 is contained in clutch cover 6 times, between described clutch cover 6 and interior fluted disc 8, between clutch cover 6 and outer tooth disk 3, Regulation spring 18 is all housed, this interior fluted disc 8, contacting respectively by separately between outer tooth disk 3 and clutch cover 6, (projection) several boss 31 (being 12) on outer tooth disk connect, end face on these several boss 31 is that interval arranges and to have the first stepped tooth 32 and (on six boss, have the first stepped tooth, this is uniform-distribution with 18 the first stepped tooths above boss, the top of this first stepped tooth is wide: 0.2mm, root is wide: 0.3mm, the degree of depth: 0.2mm, on other six boss, there is no the first stepped tooth), the boss with the first stepped tooth is uniformly distributed (being 60 degree angles) in the circumference of 360 degree, effectively guarantees stability under loading.End face on described boss 31 becomes the gradient A of 8.8-9.2 degree with horizontal plane, have the inclined-plane stepped tooth 37 (as shown in Figure 4) of the 8.8-9.2 degree corresponding with interior fluted disc, outer tooth disk on described clutch cover 6 end faces.So just can effectively guarantee to have between outer tooth disk and interior fluted disc and clutch cover the effect of position stability, when platen surface and the generation wearing and tearing of clutch drived disk assy surface, between part, will produce certain gap, because boss is the inclined-plane of 8.8-9.2 degree, now under the active force of Regulation spring, in promoting, fluted disc or outer tooth disk are descending, and interior like this fluted disc and outer tooth disk can slide on the inclined-plane of clutch cover, thereby realize automatic compensation function.
Wherein, being peripherally equipped with to draw of primary diaphragm spring 4 and clutch cover 6 covers 7, and this draws and covers 7 and be connected with the 3rd platen 14.Between described the first platen 10 and clutch cover 6, by the first driver blade 21, be connected, the second platen 12 is connected together with connecting sheet 23 by the second driver blade 19 between the 3rd platen 14.
As shown in Fig. 2, Fig. 8, Fig. 9, between described secondary diaphragm spring 9 and clutch cover 6, the second supporting ring 17, the first supporting ring 5 (to strengthen the supporting between two diaphragm springs and clutch cover) are housed respectively separately between primary diaphragm spring 4 and clutch cover 6; Described the second supporting ring 17 is contained in interior fluted disc 8 times; these the second supporting ring 17 top edges have " 7 " font bearing claw 33 (eight; two is one group) and (difference) contact with the flanged lip (four) on interior fluted disc 8 (for fluted disc in protection slide and using process performance stable; play good supporting role; make interior fluted disc 8 slide and using process in there will not be inclination, performance is more stable).Simultaneously, described the second supporting ring 17 is fixed on clutch cover 6, on described clutch cover 6, there is crotch 34 (eight), the outside wall portions of described crotch 34 becomes included angle B with the central shaft of this clutch be 10.8-11.2 degree, can make the crotch head on clutch cover effectively catch the fixed-wing 35 (eight) on the second supporting ring 17, so not only stable but also reliable.
As shown in Figure 3, between described the first platen 10 and clutch cover 6, by the first driver blade 21, be connected (between one end of the first driver blade 21 and the first platen 10, by the first rivet 20, be connected, between the other end of the first driver blade 21 and clutch cover 6, by the second rivet 24, be connected); The second platen 12 with between the 3rd platen 14, (first between connecting sheet 23 and the second platen 12, by the 3rd rivet 25, be connected by connecting together with the second driver blade 19 and connecting sheet 23, then between one end of the second driver blade 19 and connecting sheet 23, by the 4th rivet 26, link together, between the other end of the second driver blade 19 and the 3rd platen 14, by the 5th rivet 27, be connected); Draw cover 7 with the 3rd platen 14 between (by the 6th rivet 28) be connected.On described the second platen 12, by the 3rd rivet 25, banking stop 22 is housed, is conducive to that it is spacing.
As shown in Figure 2, by component such as primary diaphragm spring 4, the second clutch drived disk assy 13, the second platen 12 and the 3rd platens 14, form first clutch assembly, its second clutch drived disk assy is connected with the first axle of double clutch gearbox, controls odd gear; By component such as secondary diaphragm spring 9, the first clutch drived disk assy 11, the first platen 10 and the second platens 12, form second clutch assembly, its first clutch drived disk assy is connected with the second axle of double clutch gearbox, controls even number gear (wherein the second platen 12 is common component).In design process, dexterously 4 bore design of the primary diaphragm spring in first clutch assembly are become:
its separation finger fulcrum is designed to:
the second clutch drived disk assy 13 large footpaths of hub spline are designed to:
secondary diaphragm bullet 9 spring bore design in second clutch assembly become:
its separation finger fulcrum is designed to:
the first clutch drived disk assy 11 large footpaths of hub spline are designed to:
by the size design difference of two diaphragm springs and two clutch drived disk assys, the first axle of realizing double clutch gearbox is to be contained in the endoporus of the second axle, the second axle is a hollow shaft, the mutual noninterference of diaxon phase, and there are enough bit spaces that allows, so just contribute to the first axle and the second driven disc hub spline joint with double clutch gearbox, the second axle and the first driven disc hub spline joint, design proposal like this, just realize a set of dry friction formula double clutch and can there are two clutches in work simultaneously, in shift process, realize power and transmit continuously.
As shown in Fig. 2, Figure 10, the assembly parts that is peripherally equipped with land 15 and fluted disc 16 of described the 3rd platen 14, has the second stepped tooth 36 (being that 30 circumference that are evenly distributed on 360 degree are interior) on described fluted disc 16.Dry friction formula double clutch of the present invention carries out power by its fluted disc 16 and double mass flywheel and is connected, and has stability under loading, stressed uniform feature.
The working principle of dry dual clutch of the present invention is: in a set of double clutch product, be equivalent to have two clutch assemblies.1 gear on replacing vehicle, second clutch assembly is also changed 2 grades in advance simultaneously, 2 grades only in standby condition, pass through pedal, promote primary diaphragm spring finger tip, produce anti-cone, the diaphragm cylindrical position of primary diaphragm spring contacts and will draw caping to rise with drawing lid, now drawing lid is to be connected with the 3rd platen, draw and cover when rising, the 3rd platen also rises, until be adjacent to the second clutch drived disk assy, by sliding friction, produce synchronous rotation, the second clutch drived disk assy just drives clutch spindle synchronously to rotate, now first clutch cap assembly is in running order, drive vehicle start, second clutch cap assembly is in open mode, while preparing to change 2 grades in the speed of a motor vehicle, by unclamping pedal, under the effect of return spring, drive release bearing return, secondary diaphragm spring returns to installment state, the first platen declines under the effect of the large end of secondary diaphragm spring, the first platen and the first clutch drived disk assy are adjacent to, second clutch cap assembly and the first clutch drived disk assy synchronously rotate, now second clutch cap assembly is in running order, first clutch cap assembly is in open mode, also change in advance 3 grades simultaneously, 3 grades only in standby condition, so just omitted gear in an instant vacant, power is realized continuously and being transmitted, there is point image relay race, this pair of clutch system (two cover Clutches Transmission Systems) controlled co-ordination by computer.
Claims (5)
1. the dry friction formula double clutch of automatic transmission, comprise clutch cover and plate assembly, clutch drived disk assy, the platen of described clutch cover and plate assembly is by the first platen (10), the second platen (12), the 3rd platen (14) forms, described clutch drived disk assy is by the first clutch drived disk assy (11), the second clutch drived disk assy (13) forms, the diaphragm spring of described clutch cover and plate assembly is by primary diaphragm spring (4), secondary diaphragm spring (9) forms, it is characterized in that: described secondary diaphragm spring (9) is contained on the first platen (10), primary diaphragm spring (4) is contained on the clutch cover (6) of clutch cover and plate assembly by limited post (2), and between secondary diaphragm spring (9) and clutch cover (6), between primary diaphragm spring (4) and clutch cover (6), pass through separately respectively interior fluted disc (8), outer tooth disk (3) connects, described outer tooth disk (3) is contained on clutch cover (6), interior fluted disc (8) is contained under clutch cover (6), between described clutch cover (6) and interior fluted disc (8), Regulation spring (18) is all housed between clutch cover (6) and outer tooth disk (3), contact between this interior fluted disc (8), outer tooth disk (3) and clutch cover (6) is connected by several boss (31) on inside and outside fluted disc separately respectively, and the end face on these several boss (31) is that interval arranges and has the first stepped tooth (32).
2. the dry friction formula double clutch of automatic transmission as claimed in claim 1, it is characterized in that: the end face on described boss (31) becomes the gradient of 8.8-9.2 degree with horizontal plane on described clutch cover (6) end face, thering is the inclined-plane stepped tooth (37) of the 8.8-9.2 degree corresponding with interior fluted disc, outer tooth disk.
3. the dry friction formula double clutch of automatic transmission as claimed in claim 1 or 2, is characterized in that: between described secondary diaphragm spring (9) and clutch cover (6), the second supporting ring (17), the first supporting ring (5) are housed respectively separately between primary diaphragm spring (4) and clutch cover (6); Described the second supporting ring (17) is contained under interior fluted disc (8), and this second supporting ring (17) top edge has " 7 " font bearing claw (33) and contacts with the flanged lip on interior fluted disc (8).
4. the dry friction formula double clutch of automatic transmission as claimed in claim 3, it is characterized in that: described the second supporting ring (17) is fixed on clutch cover (6), on described clutch cover (6), there is crotch (34), the outside wall portions of described crotch (34) becomes angle with the central shaft of this clutch be 10.8-11.2 degree, can make the crotch head on clutch cover effectively catch the fixed-wing (35) on the second supporting ring (17).
5. the dry friction formula double clutch of automatic transmission as claimed in claim 1 or 2, it is characterized in that: the assembly parts that is peripherally equipped with land (15) and fluted disc (16) of described the 3rd platen (14), has the second stepped tooth (36) on described fluted disc (16).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310594301.7A CN103615474A (en) | 2013-11-15 | 2013-11-15 | Dry friction type double clutch of automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310594301.7A CN103615474A (en) | 2013-11-15 | 2013-11-15 | Dry friction type double clutch of automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103615474A true CN103615474A (en) | 2014-03-05 |
Family
ID=50166187
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310594301.7A Pending CN103615474A (en) | 2013-11-15 | 2013-11-15 | Dry friction type double clutch of automatic transmission |
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| Country | Link |
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| CN (1) | CN103615474A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109114126A (en) * | 2017-06-23 | 2019-01-01 | 舍弗勒技术股份两合公司 | Self-adjustable clutch and automobile |
| CN111089122A (en) * | 2018-10-24 | 2020-05-01 | 舍弗勒技术股份两合公司 | Pressure tank locking mechanism for clutch |
| CN114992253A (en) * | 2022-07-11 | 2022-09-02 | 洛阳东方众成离合器有限公司 | Long-life independent control double-acting clutch |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1047370A (en) * | 1996-08-07 | 1998-02-17 | Exedy Corp | Clutch cover for friction clutch |
| EP1384911A2 (en) * | 2002-07-25 | 2004-01-28 | ZF Sachs AG | Double clutch assembly |
| US20090288926A1 (en) * | 2007-01-31 | 2009-11-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device |
| CN102032316A (en) * | 2009-10-05 | 2011-04-27 | 通用汽车环球科技运作公司 | System and method for attaching a dual clutch to a flywheel |
| CN102084148A (en) * | 2007-09-19 | 2011-06-01 | Valeo离合器公司 | Clutch device including a diaphragm constantly applying an axial preload effort on the bearing of a reaction plate |
| CN102155535A (en) * | 2009-08-26 | 2011-08-17 | 通用汽车环球科技运作有限责任公司 | Actuation device for a dual clutch transmission |
| CN203641319U (en) * | 2013-11-15 | 2014-06-11 | 浙江华信汽车零部件有限公司 | Dry-friction double clutches for automatic gearbox |
-
2013
- 2013-11-15 CN CN201310594301.7A patent/CN103615474A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH1047370A (en) * | 1996-08-07 | 1998-02-17 | Exedy Corp | Clutch cover for friction clutch |
| EP1384911A2 (en) * | 2002-07-25 | 2004-01-28 | ZF Sachs AG | Double clutch assembly |
| US20090288926A1 (en) * | 2007-01-31 | 2009-11-26 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Torque transmission device |
| CN102084148A (en) * | 2007-09-19 | 2011-06-01 | Valeo离合器公司 | Clutch device including a diaphragm constantly applying an axial preload effort on the bearing of a reaction plate |
| CN102155535A (en) * | 2009-08-26 | 2011-08-17 | 通用汽车环球科技运作有限责任公司 | Actuation device for a dual clutch transmission |
| CN102032316A (en) * | 2009-10-05 | 2011-04-27 | 通用汽车环球科技运作公司 | System and method for attaching a dual clutch to a flywheel |
| CN203641319U (en) * | 2013-11-15 | 2014-06-11 | 浙江华信汽车零部件有限公司 | Dry-friction double clutches for automatic gearbox |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109114126A (en) * | 2017-06-23 | 2019-01-01 | 舍弗勒技术股份两合公司 | Self-adjustable clutch and automobile |
| CN111089122A (en) * | 2018-10-24 | 2020-05-01 | 舍弗勒技术股份两合公司 | Pressure tank locking mechanism for clutch |
| CN111089122B (en) * | 2018-10-24 | 2023-08-22 | 舍弗勒技术股份两合公司 | Pressure tank locking mechanism for clutch |
| CN114992253A (en) * | 2022-07-11 | 2022-09-02 | 洛阳东方众成离合器有限公司 | Long-life independent control double-acting clutch |
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Application publication date: 20140305 |