CN201818739U - Parallel-shaft type dual-clutch automatic automobile speed changer - Google Patents
Parallel-shaft type dual-clutch automatic automobile speed changer Download PDFInfo
- Publication number
- CN201818739U CN201818739U CN 201020299735 CN201020299735U CN201818739U CN 201818739 U CN201818739 U CN 201818739U CN 201020299735 CN201020299735 CN 201020299735 CN 201020299735 U CN201020299735 U CN 201020299735U CN 201818739 U CN201818739 U CN 201818739U
- Authority
- CN
- China
- Prior art keywords
- clutch
- retaining
- gear
- oil
- driving gear
- 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.)
- Expired - Fee Related
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The utility model relates to a parallel-shaft type dual-clutch automatic automobile speed changer. An engine input shaft is provided with an input shaft gear; the parallel-shaft type dual-clutch automatic automobile speed changer comprises two independent single clutches, wherein a driving gear of an odd-gear clutch and a driving gear of an even-gear clutch are respectively meshed with the input shaft gear by different transmission ratio; the driving gear of the odd-gear clutch is fixed on a first auxiliary shaft; the driving gear of the even-gear clutch is fixed on a second auxiliary shaft; and the first auxiliary shaft and the second auxiliary shaft are respectively distributed at two edges of the input shaft and are parallel to the input shaft. A wet-type multi-disc clutch is adopted. In the parallel-shaft type dual-clutch automatic automobile speed changer, the integrated dual-clutch is disassembled into two independent single clutches, and the coaxial structure of the traditional dual-clutch speed changer is changed into a parallel structure, therefore, the manufacturing and processing difficulties of the dual-clutch speed change are simplified and the cost can be reduced.
Description
Technical field
The utility model relates to a kind of double-clutch speed changer, is specifically related to a kind of parallel-axis type double-clutch automatic speed changer for automobile.
Background technique
Double-clutch automatic gearbox has two groups of actuating units and two cover clutch systems, and system dynamic is few break period, owing to adopted conventional fixed axis gear transmission, transmission efficiency is than higher, mature production technology since the success entrucking of popular company, has progressively become the automobile industry hot of research and development.Stable friction performance, controllability and controlling performance are good, wearing and tearing are little and even, transmitting torque is big because multi-disc wet clutch has, can adopt the relevant heating component characteristics of lubricant oil cooling, therefore in the double clutch automatic speed changing transmission system, obtain using widely.In the double-clutch automatic gearbox transmission scheme of existing industrialization, owing to adopt the Driven by Coaxial mode of axle sleeve axle, two multi-disc wet clutch integrate, as the double clutch construction that has proposed in the U.S. Pat 2005067251 to adopt two groups of clutches radially to be arranged in juxtaposition, support and lubricating structure are all very complicated, the big and manufacture cost height of difficulty of processing.
Summary of the invention
In order to simplify the manufacturing difficulty of processing of double-clutch speed changer, reduce cost, the utility model proposes a kind of parallel-axis type double-clutch automatic speed changer for automobile, adopt gear transmission mode, driving gear and clutch is integrated, adopt parallel structure to replace coaxial configuration, integrated double clutch is resolved into independently two monomer clutches, there is the balance oil pocket in clutch in lubricating structure, and the centrifugal pressure that the centrifugal pressure that lubricant oil produces in the balance oil pocket can offset pressure oil produces in the annular piston chamber makes compact structure reliable.
The technical solution adopted in the utility model:
A kind of parallel-axis type double-clutch automatic speed changer for automobile, on the motor input shaft input shaft gear is installed, it comprises independently two monomer clutches, it is respectively odd number retaining clutch and even number retaining clutch, wherein the driving gear of the driving gear of odd number retaining clutch and even number retaining clutch is respectively with different drive ratios and input shaft gear engagement, odd number retaining clutch driving gear is fixed on first countershaft, even number retaining clutch driving gear is fixed on second countershaft, first countershaft and second countershaft are arranged in the both sides of input shaft, and all parallel with input shaft.
Above-mentioned first countershaft is equipped with described odd number retaining clutch driving gear, a retaining driving gear, three retaining driving gears and the five retaining driving gears coaxial with it from right to left successively, one retaining synchronizer is between a retaining driving gear and three retaining driving gears, and three or five retaining synchronizers are between three retaining driving gears and five retaining driving gears.
Above-mentioned second countershaft is equipped with the even number retaining clutch driving gear coaxial with it, the driving gear that reverses gear, two retaining driving gears, four retaining driving gears from right to left successively, reverse gear and between driving gear and the even number retaining clutch driving gear synchronizer that reverses gear is installed, the two two or four shared retaining synchronizer is installed between two retaining driving gears and the four retaining driving gears, four retaining driving gears are carrier gear, four retaining driving gears can with the engagement of the differential gear of differential mechanism, above-mentioned differential mechanism is the speed of both sides wheel when being used to regulate motor turning.
The above-mentioned jack shaft that also comprises, being equipped with on jack shaft can be optionally and one group of driven gear of each driving gear engagement, this group driven gear right-to-left comprises a retaining driven gear respectively, two or three driven gears that reverse gear, four or five retaining driven gears, a wherein retaining driven gear and a retaining driving gear engagement, two or three reverse gear driven gear respectively with two the retaining driving gears, three retaining driving gears, the idler gear that reverses gear engagement, the idler gear that reverses gear is installed on the pony axle and also meshes with the driving gear that reverses gear, pony axle is installed on the casing, and four or five retaining driven gears keep off driving gears with four respectively, five retaining driving gear engagements.
Above-mentioned clutch is a multi-disc wet clutch.
Above-mentioned multi-disc wet clutch has fixed mounting base, oil duct on fixed supporting seat has hydraulic oil port A and lubricated hydraulic fluid port B, respectively with the mission case that connects clutch on corresponding oil duct link to each other, hydraulic oil passes through parallel axes on the fixed supporting seat to oil duct successively from hydraulic oil port A, connect radial direction oil C, be communicated to the outer annular oil groove of fixed supporting seat again, annular oil groove links to each other with the radial direction oil D of clutch plunger cylinder, pressure oil can pass through oil duct A, C, D arrives the clutch plunger cylinder, and control promotes clutch annular piston in conjunction with clutch.Lubricant oil enters parallel axes on the fixed supporting seat to oil duct from lubricated hydraulic fluid port B, be communicated with hydraulic fluid port G and hydraulic fluid port E respectively, part lubricant oil is by hydraulic fluid port G opposite end spherical bearing, the hub spline housing is lubricated in the clutch, part lubricant oil arrives the bearings mounted outer surface of right-hand member of fixed supporting seat by lubricated hydraulic fluid port E, a part of lubricant oil by lubricated hydraulic fluid port E is to bearing, be lubricated, and finally pass through clutch friction surface, clutch antithesis steel disc and clutch plate are carried out cooling and lubricating, another part lubricant oil by lubricated hydraulic fluid port E is by the radial direction oil F arrival clutch centrifugal oil pressure balance oil pocket of outer hub seat, the centrifugal pressure that produces owing to the high speed rotating of clutch with the pressure oil in the counterbalance annular piston cavity.
Pressure oil in the above-mentioned counterbalance annular piston cavity is meant that owing to the centrifugal pressure that the high speed rotating of clutch produces the lubricant oil that enters in the balance oil pocket produces centrifugal pressure equally, and with the centrifugal pressure described in the annular piston chamber, equal and opposite in direction, direction is opposite.
A left side is adopted at the two ends of above-mentioned outer hub seat respectively, right rolling or sliding bearing are sleeved on the external cylindrical surface of described fixed supporting seat, outer hub is contained on the outer hub seat left end outer peripheral surface by inner hole sleeve, outer hub seat left end contacts spacing by the end face bearing with the step end face of supporting base, the right-hand member of outer hub seat contacts spacing by described right side bearing with the step end face of interior hub spline housing, the outer hub of the active part of clutch links into an integrated entity by described outer hub seat and input gear, the antithesis steel disc and the friction plate of clutch are arranged at interval, clutch antithesis steel disc links to each other by the outer hub of keyway and clutch, clutch friction plate links to each other with hub in the clutch by spline, hub and interior hub spline housing fuse in the secondary part of clutch, and outputting power, clutch initiatively the input part by bearings on fixed supporting seat, and by a left side, it is spacing that the right side bearing carries out axially support, dispose pressure and oil leab on the fixed supporting seat, clutch carries out clutch for clutch control by pressurizing mechanism and resetting-mechanism.
Above-mentioned pressurizing mechanism comprises outer hub, outer hub seat and annular piston, annular piston is by first seal ring and described external sealed, and by second seal ring and described outer hub seat sealing, form the annular piston pressure chamber of sealing, pressure oil enters the piston cavity of sealing, thereby the promotion annular piston can pressurize to the multi-disc antithesis steel disc and the clutch plate of clutch arranged spaced; Resetting-mechanism is made of annular balance oil pocket chamber lid and spring, spring is single big spring, spring one end is against by the balance oil pocket chamber of axle with the collar axial limiting and covers, the other end of spring links to each other with the annular piston end face, under the conventional assembling condition of clutch separation, spring has certain pre compressed magnitude, in conjunction with clutch the time, the further pressure spring of pressure oil, multi-disc antithesis steel disc and clutch plate to the clutch arranged spaced are pressurizeed, behind annular piston pressure chamber draining, under the spring force effect of pressure spring, the promotion annular piston resets, clutch separation.
The technique effect that the utility model is obtained:
1, integrated double clutch is resolved into independently two monomer clutches, the coaxial configuration of traditional dual-clutch transmission is converted to parallel structure, thereby can simplifies the manufacturing difficulty of processing of double-clutch speed changer, reduce cost;
2, compare with the integrated bearing technological scheme that the support location employing of existing multi-disc wet clutch is made one with end face bearing and rolling bearing, the above-mentioned design proposal support stiffness height of multi-disc wet clutch of the present utility model, axial dimension is little, transmission and installation precision height, cost of production is lower.
Description of drawings
Fig. 1 is the structural layout plan of the utility model double-clutch automatic gearbox;
Fig. 2 is the structural representation of the utility model multi-disc wet clutch.
Embodiment
Referring to Fig. 1-2, double-clutch automatic gearbox as shown in Figure 1, wherein on the motor input shaft 31 input shaft gear 332 is installed, it comprises independently two monomer clutches 35,36, wherein the driving gear 34 of the driving gear 33 of odd number retaining clutch 35 and even number retaining clutch 36 is respectively with different drive ratios and input shaft gear 332 engagements, odd number retaining clutch driving gear 33 is fixed on first countershaft 37, even number retaining clutch driving gear 34 is fixed on second countershaft 313, first countershaft 37 and second countershaft 313 are arranged in the both sides of input shaft 31, and all parallel with input shaft 31.
The right-hand member that odd number retaining clutch 35 and even number retaining clutch 36 odd number friction plate 326 or the even number friction plate 327 by inside is fixedly mounted on first countershaft 37 and second countershaft 313 respectively, odd number retaining clutch 35 and even number retaining clutch 36 have odd number retaining clutch driving gear 33 and even number retaining clutch driving gear 34 respectively.When odd number friction plate 326 or even number friction plate 327 clamps mutually with corresponding odd number retaining clutch 35 or even number retaining clutch 36 friction disks, can make from the transmission of power of odd number retaining clutch driving gear 33 or even number retaining clutch driving gear 34 and give corresponding first countershaft 37 or second countershaft 313, when odd number friction plate 326 or even number friction plate 327 breaks away from mutually with corresponding odd number retaining clutch 35 or even number retaining clutch 36 friction disks, can't pass to corresponding first countershaft 37 or second countershaft 313 from the power of odd number retaining clutch driving gear 33 or even number retaining clutch driving gear 34.When odd number friction plate 326 or even number friction plate 327 and corresponding odd number retaining clutch 35 or even number retaining clutch 36 friction disks mutually during mutual friction, will be transformed into first countershaft 37 corresponding or second countershaft 313 mutually with it from the power of odd number retaining clutch driving gear 33 or even number retaining clutch driving gear 34.
First countershaft 37 is equipped with the odd number retaining clutch driving gear coaxial with it 33, a retaining driving gear 38, three retaining driving gears 310 and five retaining driving gears, 312, one retaining synchronizers 39 from right to left successively on first countershaft 37 between a retaining driving gear 38 and the three retaining driving gears 310; Three or five retaining synchronizers 311 are on first countershaft 37 between three retaining driving gears 310 and the five retaining driving gears 312.
Second countershaft 313 is equipped with the even number coaxial with it retaining clutch driving gear 34, one reverse gear driving gear 317, one two retaining driving gear 316, four retaining driving gears 314 from right to left successively, on second countershaft 313 between driving gear 317 and the even number retaining clutch driving gear 34 of reversing gear the synchronizer 318 that reverses gear is installed; The two two or four shared retaining synchronizer 315 is installed between two retaining driving gears 316 and the four retaining driving gears 314.Four retaining driving gears 314 be carrier gear, and four retaining driving gears 314 can mesh with the differential gear 334 of differential mechanism 335, and above-mentioned differential mechanism 335 is the speed of both sides wheel when being used to regulate motor turning.
Being equipped with on the jack shaft 319 can be optionally and one group of driven gear of each driving gear engagement, this group driven gear right-to-left comprises a retaining driven gear 322 respectively, two or three driven gears 321 that reverse gear, four or five retaining driven gears 320, a wherein retaining driven gear 322 and a retaining driving gear 38 engagements, two or three reverse gear driven gear 321 respectively with two the retaining driving gears 316, three retaining driving gears 310, the idler gear 323 that reverses gear meshes, in conjunction with shown in Figure 1, the idler gear 323 that reverses gear is installed on the pony axle 324 and also meshes with the driving gear 317 that reverses gear, pony axle 324 is installed on the mission case (not shown), four or five retaining driven gears 320 keep off driving gears 314 with four respectively, five retaining driving gears 312 engagements, and the velocity ratio that the every pair of driving gear and driven gear produce has nothing in common with each other.
Multi-disc wet clutch of the present utility model (odd number clutch 35, even number clutch 36), as shown in Figure 2, design has hydraulic oil port A and lubricated hydraulic fluid port B respectively on the supporting base 1 of clutch, respectively with the double-clutch automatic gearbox casing on corresponding oil duct link to each other, hydraulic oil from hydraulic oil port A by the parallel axes on the fixed supporting seat to oil duct, radial direction oil C arrives the outer annular oil groove of fixed supporting seat, annular oil groove links to each other with the radial direction oil D of clutch plunger cylinder, therefore pressure oil can pass through oil duct A, C, D arrives the clutch plunger cylinder, and control promotes clutch annular piston 7 in conjunction with clutch.Lubricant oil enters parallel axes on the fixed supporting seat to oil duct from lubricated hydraulic fluid port B, a part lubricant oil as shown hydraulic fluid port G to right side bearing 15, hub spline housing 13 parts such as grade are lubricated in the clutch, part lubricant oil arrives the right-hand member rolling of fixed supporting seat 1 or the outer surface of sliding bearing 16 by lubricated hydraulic fluid port E, a part of lubricant oil by lubricated hydraulic fluid port E is to right side bearing 15, right-hand member rolls or sliding bearing 16 is lubricated, and finally pass through clutch friction surface, clutch antithesis steel disc 19 and clutch plate 18 are carried out cooling and lubricating, another part lubricant oil by lubricated hydraulic fluid port E is by the radial direction oil F arrival clutch centrifugal oil pressure balance oil pocket of outer hub seat 3, the lubricant oil that enters in the balance oil pocket produces centrifugal pressure equally, with pressure oil in the annular piston chamber because the centrifugal pressure that clutch runs up and produces, equal and opposite in direction, direction is opposite, so balance owing to rotate the annular piston chamber centrifugal pressure that brings, offset in the annular pressure piston cavity centrifugal pressure oil to the influence of Clutch Control.System carries out control and management by the oil duct on the fixed supporting seat 1 to the pilot pressure of clutch oil and lubricant oil, and compact structure is reliable.
Simultaneously, this clutch comprises positioning supports unit, power input unit, performance element and power output unit, clutch power input unit comprises outer hub 5, gear 4, outer hub seat 3 and a plurality of active part: clutch antithesis steel disc 19, clutch backboard 11, outer hub 5, gear 4 and outer hub seat 3 can manufacture the structure that one links to each other.The clutch performance element comprises outer hub 5, outer hub seat 3 and annular piston 7, annular piston 7 is by first seal ring 6 and outer hub 5 sealings, by second seal ring 20 and outer hub seat 3 sealings, form the annular piston chamber of sealing, performance element also is included in the resetting-mechanism that allows annular piston 7 move to left and to reset under the pressure release state in annular oil cavity, resetting-mechanism comprises spring 9 and covers 17 by clutch counter balance pocket chamber, outside framework oil seal 8, outer hub seat 3 and annular piston 7 are formed the centrifugal oil pressure counter balance pocket of compensation clutch centrifugal pressure, paste mutually with the left end of spring 9 in the outside, annular piston 7 right sides, the right-hand member of spring 9 withstands on the clutch counter balance pocket chamber lid 17, and covers 17 by axle with collar 14 axial restraint counter balance pocket chambeies.Clutch antithesis steel disc 19 and clutch friction plate 18 be layout at interval, and links to each other by keyway and the outer hub 5 of clutch, and the clutch antithesis steel disc 19 of clutch low order end links to each other with clutch backboard 11, and clutch backboard 11 is by hole collar 10 axial limitings.The clutch power output unit comprises multiplate clutch friction plate 18, interior hub 12, interior hub spline housing 13, and interior hub 12 and interior hub spline housing 13 can be processed into one-piece parts.Multiplate clutch antithesis steel disc 19 and clutch friction plate 18 interlaced layouts, when the annular piston chamber oil-filled, after pressure oil promotion annular piston 7 compresses antithesis steel disc 19 and clutch friction plate 18, power is promptly by the outer hub 5 of clutch, clutch antithesis steel disc 19, clutch friction plate 18, hub 12 is delivered to hub spline housing 13 in the clutch in the clutch, clutch is in bonding state, the centrifugal oil pressure that produces owing to running up in the annular piston chamber is offset by the oil of the centrifugal pressure in the clutch balance oil pocket, when the pressure release of annular piston chamber, annular piston 7 is resetted by the spring 9 pretensioned spring power effect bottom lefts of resetting-mechanism, lay down the axial positive pressure of antithesis steel disc 19 and clutch friction plate 18, clutch is in separated state.The positioning supports unit comprises columniform supporting base 1 and the left side bearing 2 and the left side that are installed on the supporting base 1, the right rolling or sliding bearing 22,16, and right side bearing 15, the left end of tubular supporting base 1 has land, a left side is adopted at the two ends of outer hub seat 3 respectively, the right rolling or sliding bearing 22,16 are sleeved on the external cylindrical surface of supporting base 1, outer hub 5 is contained on the outer hub seat 3 left end outer peripheral surfaces by inner hole sleeve, outer hub seat 3 left ends contact spacing by left side bearing 2 with the step end face of supporting base, the right-hand member of outer hub seat 3 contacts spacing by right side bearing 15 with the step end face of interior hub spline housing, compare with the integrated bearing technological scheme that the support location employing of existing multi-disc wet clutch is made one with end face bearing and rolling bearing, the above-mentioned design proposal support stiffness height of multi-disc wet clutch of the present utility model, axial dimension is little, transmission and installation precision height, cost of production is lower.
Embodiment recited above is described preferred implementation of the present utility model; be not that scope of the present utility model is limited; under the prerequisite that does not break away from the utility model design spirit; various distortion and improvement that the common engineers and technicians in related domain make the technical solution of the utility model all should fall in the definite protection domain of the utility model claims.
Claims (8)
1. parallel-axis type double-clutch automatic speed changer for automobile, wherein on the motor input shaft (31) input shaft gear (332) is installed, it is characterized in that: it comprises independently two monomer clutches, it is respectively odd number retaining clutch (35) and even number retaining clutch (36), wherein the driving gear (34) of the driving gear (33) of odd number retaining clutch (35) and even number retaining clutch (36) is respectively with different drive ratios and input shaft gear (332) engagement, odd number retaining clutch driving gear (33) is fixed on first countershaft (37), even number retaining clutch driving gear (34) is fixed on second countershaft (313), first countershaft (37) and second countershaft (313) are arranged in the both sides of input shaft (31), and all parallel with input shaft (31).
2. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 1, it is characterized in that: described first countershaft (37) is equipped with described odd number retaining clutch driving gear (33), a retaining driving gear (38), three retaining driving gears (310) and the five retaining driving gears (312) coaxial with it from right to left successively, one retaining synchronizer (39) is positioned between a retaining driving gear (38) and the three retaining driving gears (310), and three or five retaining synchronizers (311) are positioned between three retaining driving gears (310) and the five retaining driving gears (312).
3. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 2, it is characterized in that: described second countershaft (313) is equipped with the even number retaining clutch driving gear (34) coaxial with it from right to left successively, the driving gear that reverses gear (317), one two retaining driving gear (316), one four retaining driving gear (314), reverse gear and between driving gear (317) and the even number retaining clutch driving gear (34) synchronizer that reverses gear (318) is installed, the two two or four shared retaining synchronizer (315) is installed between two retaining driving gears (316) and the four retaining driving gears (314), four retaining driving gears (314) be carrier gear, and four retaining driving gears (314) can mesh by the differential gear (334) of the differential mechanism (335) of both sides wheel velocity when being used to regulate motor turning.
4. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 3, it is characterized in that: it also comprises jack shaft (319), being equipped with on jack shaft (319) can be optionally and one group of driven gear of each driving gear engagement, this group driven gear right-to-left comprises a retaining driven gear (322) respectively, two or three driven gears (321) that reverse gear, four or five retaining driven gears (320), wherein a retaining driven gear (322) meshes with a retaining driving gear (38), two or three reverse gear driven gear (321) respectively with two the retaining driving gears (316), three retaining driving gears (310), the idler gear (323) that reverses gear engagement, the idler gear (323) that reverses gear is installed in pony axle (324) and goes up and also mesh with the driving gear that reverses gear (317), pony axle (324) is installed on the gearbox casing, and four or five retaining driven gears (320) keep off driving gears (314) with four respectively, five retaining driving gear (312) engagements.
5. as claim 1,2,3 or 4 described parallel-axis type double-clutch automatic speed changer for automobile, it is characterized in that: described clutch is a multi-disc wet clutch.
6. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 5, it is characterized in that: described multi-disc wet clutch has fixed mounting base (1), oil duct on fixed supporting seat (1) has hydraulic oil port (A) and lubricated hydraulic fluid port (B), respectively with mission case on corresponding oil duct link to each other, hydraulic oil passes through parallel axes on the fixed supporting seat to oil duct successively from hydraulic oil port (A), radial direction oil (C) arrives the outer annular oil groove of fixed supporting seat (1), annular oil groove links to each other with the radial direction oil (D) of clutch plunger cylinder, pressure oil can pass through oil duct (A, C, D) arrive the clutch plunger cylinder, control promotes clutch annular piston (7) in conjunction with clutch; Lubricant oil enters parallel axes on the fixed supporting seat to oil duct from lubricated hydraulic fluid port (B), be communicated with hydraulic fluid port (G) and hydraulic fluid port (E) respectively, part lubricant oil passes through hydraulic fluid port (G) to right side bearing (15), hub spline housing (13) is lubricated in the clutch, part lubricant oil arrives the outer surface of the right-hand member installation bearing (16) of fixed supporting seat (1) by lubricated hydraulic fluid port (E), a part of lubricant oil by lubricated hydraulic fluid port (E) is to right side bearing (15), right rolling or sliding bearing (16) are lubricated, and finally pass through clutch friction surface, clutch antithesis steel disc (19) and clutch plate (18) are carried out cooling and lubricating, be communicated with the radial direction oil (F) of outer hub seat (3) by another part lubricant oil of lubricated hydraulic fluid port (E), be switched to clutch centrifugal oil pressure balance oil pocket again.
7. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 6, it is characterized in that: a left side is adopted at the two ends of described outer hub seat (3) respectively, the right rolling or sliding bearing (22), (16) be sleeved on the external cylindrical surface of described fixed supporting seat (1), the outer hub (5) of the active part of clutch is contained on outer hub seat (3) the left end outer peripheral surface by inner hole sleeve, outer hub seat (3) left end contacts spacing by left side bearing (2) with the step end face of supporting base, the right-hand member of outer hub seat (3) contacts spacing by described right side bearing (15) with the step end face of interior hub spline housing, the outer hub (5) of the active part of clutch links into an integrated entity by described outer hub seat (3) and input gear (4), the antithesis steel disc (19) of clutch is arranged at interval with friction plate (18), clutch antithesis steel disc (19) links to each other by the outer hub (5) of keyway and clutch, clutch friction plate (18) links to each other with hub (12) in the clutch by spline, hub (12) fuses with interior hub spline housing (13) in the secondary part of clutch, and outputting power, clutch initiatively input part passes through a left side, the right rolling or sliding bearing (22), (16) be supported on the fixed supporting seat (1), and by a left side, it is spacing that right side bearing (2) (15) carries out axially support, dispose pressure and oil leab on the fixed supporting seat, clutch carries out clutch for clutch control by pressurizing mechanism and resetting-mechanism.
8. parallel-axis type double-clutch automatic speed changer for automobile as claimed in claim 7, it is characterized in that: described pressurizing mechanism comprises the outer hub (5) of the active part of clutch, outer hub seat (3) and annular piston (7), annular piston (7) is by first seal ring (6) and described outer hub (5) sealing, and by second seal ring (20) and described outer hub seat (3) sealing, form the annular piston pressure chamber of sealing, pressure oil enters the piston cavity of sealing, thereby promote annular piston (7), can pressurize the multi-disc antithesis steel disc (19) and the clutch plate (18) of clutch arranged spaced; Described resetting-mechanism is made of annular balance oil pocket chamber lid (17) and spring (9), spring (9) is single big spring, spring one end is against by the balance oil pocket chamber of axle with collar (14) axial limiting and covers, the other end of spring links to each other with annular piston (7) end face, under the conventional assembling condition of clutch separation, spring (9) has certain pre compressed magnitude.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201020299735 CN201818739U (en) | 2010-08-20 | 2010-08-20 | Parallel-shaft type dual-clutch automatic automobile speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201020299735 CN201818739U (en) | 2010-08-20 | 2010-08-20 | Parallel-shaft type dual-clutch automatic automobile speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201818739U true CN201818739U (en) | 2011-05-04 |
Family
ID=43916693
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201020299735 Expired - Fee Related CN201818739U (en) | 2010-08-20 | 2010-08-20 | Parallel-shaft type dual-clutch automatic automobile speed changer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201818739U (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101979898A (en) * | 2010-08-20 | 2011-02-23 | 重庆青山工业有限责任公司 | Dual-clutch automated transmission |
| CN102221055A (en) * | 2011-06-16 | 2011-10-19 | 东风汽车有限公司 | Wet-type double clutch |
| CN102425634A (en) * | 2011-12-27 | 2012-04-25 | 山东潍坊鲁中拖拉机有限公司 | Clutch with braking function |
| CN104819219A (en) * | 2015-04-23 | 2015-08-05 | 青岛丰宝汽车离合器有限公司 | Wet clutch assembly |
| CN105485266A (en) * | 2014-10-09 | 2016-04-13 | 晏明 | Separation type double-clutch transmission |
| CN108317225A (en) * | 2018-03-23 | 2018-07-24 | 重庆青山工业有限责任公司 | Double disengaging type automatic transmission transmission mechanisms |
| CN108548715A (en) * | 2018-03-26 | 2018-09-18 | 吉林大学 | A kind of Wet-type friction material testing machine |
| CN108871743A (en) * | 2018-05-09 | 2018-11-23 | 江苏大学 | A kind of wet clutch visual testing device |
| CN109236888A (en) * | 2018-11-05 | 2019-01-18 | 绿传（北京）科技有限公司 | A kind of clutch and relevant device for speed changer |
| CN109882507A (en) * | 2017-12-06 | 2019-06-14 | 舍弗勒技术股份两合公司 | Bearing arrangement for a dual clutch transmission |
| CN110725867A (en) * | 2019-10-15 | 2020-01-24 | 宁波上中下自动变速器有限公司 | Synchronizer, synchronizer speed regulation system and vehicle |
| CN111853080A (en) * | 2019-04-24 | 2020-10-30 | 本田技研工业株式会社 | Hydraulic pressure supply structure of clutch |
-
2010
- 2010-08-20 CN CN 201020299735 patent/CN201818739U/en not_active Expired - Fee Related
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101979898B (en) * | 2010-08-20 | 2013-06-26 | 重庆青山工业有限责任公司 | Dual-clutch automated transmission |
| CN101979898A (en) * | 2010-08-20 | 2011-02-23 | 重庆青山工业有限责任公司 | Dual-clutch automated transmission |
| CN102221055A (en) * | 2011-06-16 | 2011-10-19 | 东风汽车有限公司 | Wet-type double clutch |
| CN102425634A (en) * | 2011-12-27 | 2012-04-25 | 山东潍坊鲁中拖拉机有限公司 | Clutch with braking function |
| CN105485266A (en) * | 2014-10-09 | 2016-04-13 | 晏明 | Separation type double-clutch transmission |
| CN104819219A (en) * | 2015-04-23 | 2015-08-05 | 青岛丰宝汽车离合器有限公司 | Wet clutch assembly |
| CN109882507A (en) * | 2017-12-06 | 2019-06-14 | 舍弗勒技术股份两合公司 | Bearing arrangement for a dual clutch transmission |
| CN108317225A (en) * | 2018-03-23 | 2018-07-24 | 重庆青山工业有限责任公司 | Double disengaging type automatic transmission transmission mechanisms |
| CN108548715A (en) * | 2018-03-26 | 2018-09-18 | 吉林大学 | A kind of Wet-type friction material testing machine |
| CN108871743A (en) * | 2018-05-09 | 2018-11-23 | 江苏大学 | A kind of wet clutch visual testing device |
| CN109236888A (en) * | 2018-11-05 | 2019-01-18 | 绿传（北京）科技有限公司 | A kind of clutch and relevant device for speed changer |
| CN111853080A (en) * | 2019-04-24 | 2020-10-30 | 本田技研工业株式会社 | Hydraulic pressure supply structure of clutch |
| CN110725867A (en) * | 2019-10-15 | 2020-01-24 | 宁波上中下自动变速器有限公司 | Synchronizer, synchronizer speed regulation system and vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201818739U (en) | Parallel-shaft type dual-clutch automatic automobile speed changer | |
| CN101979898B (en) | Dual-clutch automated transmission | |
| CN102384248B (en) | Gear assembly for automatic transmission case | |
| US11293525B2 (en) | Seven-speed double clutch transmission and vehicle | |
| EP3059476B1 (en) | Dual-clutch automatic transmission | |
| CN101349327B (en) | Countershaft clutch and gear assembly | |
| CN101709750B (en) | Wet-type multi-disc clutch | |
| JP2006077987A (en) | Transmission of countershaft structure | |
| EP3921558B1 (en) | Multi-shaft gearbox | |
| CN104061319A (en) | Double-clutch lubricating structure for double-clutch gear box | |
| KR20150026941A (en) | Clutch axial bearing on main hub | |
| CN103562582B (en) | Clutch for transmission | |
| US5367914A (en) | Power transmission having creeping speed by concurrent suppling engagement of the dual input plate clutches of the countershafts | |
| CN201747872U (en) | Transmission case main shaft gear positioning mechanism of heavy-duty truck | |
| CN104132076B (en) | Coaxial separate opposed type double clutch and dual-clutch transmission | |
| CN101949430A (en) | Novel double clutch type automatic transmission (DCT) layout structure | |
| US8960032B2 (en) | Multi-clutch transmission for a motor vehicle | |
| US20100180704A1 (en) | Double clutch of a double clutch transmission | |
| CN101248293B (en) | Hydraulic servo for a brake in an automatic transmission | |
| CN102943828B (en) | Automated mechanical transmission (AMT) braking device | |
| CN112901752A (en) | Transmission integrated power take-off for commercial vehicle transmission | |
| CN201561072U (en) | Wet type multi-sheet clutch | |
| CN106555827A (en) | Automobile and its wet type double clutch gearbox, wet-type dual-clutch | |
| CN204004062U (en) | Coaxial separate opposed type double clutch and dual-clutch transmission | |
| CN104879397A (en) | Wet type double-clutch unit |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110504 Termination date: 20140820 |
|
| EXPY | Termination of patent right or utility model |