CN201106670Y - Hydrodynamic torque converter - Google Patents
Hydrodynamic torque converter Download PDFInfo
- Publication number
- CN201106670Y CN201106670Y CNU2007201223074U CN200720122307U CN201106670Y CN 201106670 Y CN201106670 Y CN 201106670Y CN U2007201223074 U CNU2007201223074 U CN U2007201223074U CN 200720122307 U CN200720122307 U CN 200720122307U CN 201106670 Y CN201106670 Y CN 201106670Y
- Authority
- CN
- China
- Prior art keywords
- buffer
- turbine
- pump impeller
- torque converter
- fluid torque
- 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
- 239000000872 buffer Substances 0.000 claims abstract description 82
- 239000012530 fluid Substances 0.000 claims description 37
- 208000004141 microcephaly Diseases 0.000 claims description 4
- 230000003139 buffering effect Effects 0.000 abstract description 8
- 230000005540 biological transmission Effects 0.000 abstract description 5
- 238000013461 design Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 230000006872 improvement Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000007812 deficiency Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000004075 alteration Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000009347 mechanical transmission Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 238000004904 shortening Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000003756 stirring Methods 0.000 description 1
- 239000012224 working solution Substances 0.000 description 1
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
- F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
- F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Of Transmissions (AREA)
- Control Of Fluid Gearings (AREA)
Abstract
The utility model relates to a hydrotransmitter. A pump impeller cover and a pump impeller are welded, and are linked with a flexible disk of an engine through a bolt; a turbine is linked with an output shaft spline through a turbine hub; an idler pulley is fixed on a gear-box shell body through a spine; the pump impeller, the turbine and the idler pulley form a circulation round cavity. A lockup clutch is also arranged, is positioned at the front end of the turbine, and is formed by a locked piston, a friction plate, buffers and a turbine transmission plate, etc. The hydrotransmitter is characterized in that the buffers are composed of a main buffer and a secondary buffer connected in series. The shape of the working cavity circulation round is similar to an egg with the big end facing the axes. An outer space formed between the small end of the working cavity circulation round and the pump impeller cover is added with the secondary buffer. After changing into buffers, the main buffer is adjacent to the turbine hub. In a general working condition, the buffer capacity of the main buffer is ensured enough; in a working condition with larger load, the buffering capacity of the main buffer is not enough, and when a spring is compressed for a certain degree, the secondary buffer starts to play action, so two buffers work commonly to ensure enough buffering capacity.
Description
Technical field
The utility model relates to a kind of fluid torque converter, relates in particular to the CVT that is applied in the horizontal forerunner of motor and the fluid torque converter among the AT.
Background technique
At present, increasing car uses the horizontal forerunner of motor, development along with technology, the gear of number of engine cylinders and gearbox increases gradually, the axial distance of power assembly becomes increasing, and horizontal forerunner's car becomes more and more crowded in the general arrangement space of front axle, therefore just each layout on the front axle is proposed to reduce the requirement of axial distance, under this trend, the axial distance of fluid torque converter also constantly is being shortened.Fluid torque converter, guide wheel keep certain axial spacing with pump impeller and turbine respectively, and the axial longitudinal plane of three-wheel constitutes ring cavity, also claims circulate circle, and work fluid can be made circulation movement in circulate circle.Fluid torque converter all adopts circular or oval-shaped active chamber circulate circle design mostly, and the torsional damper setting is nearer from turbine output shaft.Such design takies bigger axial space, gives the whole axial arranged difficulty that increased.
The pump impeller cover cap of fluid torque converter and pump impeller weld, and connect with the flexible disc of motor by bolt, and turbine is by turbine hub and output shaft splined, and guide wheel is fixed on the gear box casing by spline, and pump impeller, turbine and guide wheel are formed the circulate circle active chamber.Motor drives the pump impeller rotation during work, and in active chamber, the blade of pump impeller stirs the rotation of fluid impulse turbine blade, makes power output, realizes flexible transmission.Realize increasing moment of torsion from the fluid that turbine comes out by guide wheel.Fluid torque converter is by the working solution transmitting torque, and is lower than the transmission efficiency of mechanical transmission.Therefore, locking (locking) clutch is set also in fluid torque converter, can under high-speed working condition, pump impeller and turbine be locked together, realize that power directly transmits, improve the transmission efficiency of torque-converters.The lock-up clutch of fluid torque converter is positioned at the turbine front end, is made up of lockup piston, friction plate, damping disk(-isc) (buffer) and worm gear drive plate etc.Lock-up clutch can be in due course and carry out the locking switching under the control of hydraulic pressure automatic handling system.Lockup clutch connects with the turbine hub, during locking, utilizes oil pressure that the friction plate of lockup clutch is pressed onto on the pump impeller cover cap, realizes power output by the friction plate effect.
At present, a lot of architecture advances were arranged in the research of shortening the fluid torque converter axial distance.What mostly propose is modification to active chamber circulate circle shape and motor flexible disc attachment bolt position, thereby shortens wheelbase, but this improvement has its narrow limitation.Arrange that from car load it is no doubt important to shorten axial dimension, but will do improvement under the prerequisite that does not influence performance as far as possible, the change of active chamber circulate circle shape has very big influence to the performance of torque-converters.Bolt is used for connecting motor flexible disc and fluid torque converter, and revising bolt position certainly will influence connecting of torque-converters and flexible disc, so such modification also will be seen the cooperation requirement of torque-converters and flexible disc.
Fluid torque converter in the past all is to use a buffer, behind converter lockout, become positive drive from flexible transmission, for steady output, use buffer by the spring transferring power, reduce because the torque ripple that the uneven stable yields of engine output torque is given birth to.Owing to all will consider to various operating modes, all be according to the strictest operating mode design when therefore designing buffer, the result who causes like this needs to select the buffer with very big buffer capacity, its structure of such buffer also is very big, but the operating mode of most severe impact seldom runs into, the operating mode of most of operating time is general buffering operating mode, therefore be sub load work in most time buffer, design size but is according to full load, therefore not only wasted the axial space size, utilization efficiency is also very low.
Summary of the invention
The purpose of this utility model provides a kind of axial distance weak point, power output steadily, and the good fluid torque converter of travelling comfort.Solve the technical problem of the axial arranged deficiency of existing fluid torque converter.
The utility model is to solve the problems of the technologies described above to adopt following technological scheme: a kind of fluid torque converter, the pump impeller cover cap of fluid torque converter and pump impeller welding, and connect with the flexible disc of motor by bolt, turbine is by turbine hub and output shaft splined, guide wheel is fixed on the gear box casing by spline, and pump impeller, turbine and guide wheel are formed the circulate circle active chamber.Lockup clutch also is set in fluid torque converter, and the lock-up clutch of fluid torque converter is positioned at the turbine front end, is made up of lockup piston, friction plate, buffer and worm gear drive plate etc.It is characterized in that: described buffer is to be composed in series by main buffer and time two buffers of buffer.
In order further to realize above-mentioned improvement project, for the design of change buffer structure under the prerequisite that does not influence the torque-converters performance, adopted a kind of in the technical solution of the utility model to active chamber circulate circle difference designing shape in the past.The similar egg type of active chamber circulate circle shape of the utility model design, major part is towards the axle center.The space outerpace of abdicating between active chamber circulate circle microcephaly and the pump impeller cover cap increases a secondary buffer, and the spring of buffer originally just can change into than original little spring to shorten axial dimension.From flow field analysis, in A place flow velocity maximum, B place flow velocity minimum can equate to reduce A place axial dimension according to the import and export flow and become similar egg type, and it is favourable therefore changing circulate circle shape stream field like this.Therefore, this design outline has not only shortened the axial dimension of fluid torque converter, for secondary buffer is abdicated arrangement space, and also is very suitable for work flow field.
Good effect of the present utility model is, make two buffers into after, near the turbine hub is main buffer.Under the general operating mode, the buffer capacity of main buffer enough guarantees, than high load working condition the time, and main buffer buffer capacity deficiency, after length of spring compressed was a certain amount of, secondary buffer began effect, and two buffer actings in conjunction guarantee enough buffer capacities.Like this, the utilization efficiency of main buffer is well utilized.
On travelling comfort, as buffer spring rigidity property plotted curve 1, minimal buffering torque T during design
MinWith hard-over θ
MaxIt is restricted requirement.Use the spring rate (k=T of a buffer
Min/ θ
Max) require to calculate selection according to actual design.After using two buffers, the main buffer rigidity k
1, the secondary buffer rigidity k
2(in order to satisfy the designing requirement of minimal buffering moment of torsion and hard-over: k
1* θ
Max+ k
2* (θ
Max-θ
1)=T
Min, θ
1Be the corner that secondary buffer begins to do the time spent main buffer).Under most operating modes, have only the main buffer effect, its spring rate is compared and is only used the spring rate of a buffer little, and therefore travelling comfort will be got well under most operating modes.Than under the high load working condition, though two coefficient spring rates of buffer use the spring rate of a buffer effect big than only, but the passenger is not high to the requirement of travelling comfort yet under such operating mode, moreover this operating mode also seldom runs into, therefore the fluid torque converter that uses two buffers is as a whole compared the travelling comfort of the torque-converters that uses a buffer and will be got well after locking.
Further specify the utility model below in conjunction with embodiment and accompanying drawing.
Description of drawings
Fig. 1 is a buffer spring rigidity property plotted curve in the fluid torque converter.Shown in the figure: the stiffness curve that 1, uses a buffer; 2, main buffer stiffness curve; 3, primary and secondary buffer co-operation stiffness curve.
Fig. 2 is the utility model organigram.
Among the figure: 1. guide wheel, 2. pump impeller, 3. turbine, 4. coupling block (be screwed into and connect the flexible disc bolt), 5. main buffer, 6. turbine hub, 7. lockup clutch, 8. time buffer, 9. friction plate, 10. pump impeller cover cap.A, B place are the flow field analysis positions.
Fig. 3 is a buffer organigram in the utility model fluid torque converter.
Embodiment
Embodiment is shown in Fig. 2,3, a kind of fluid torque converter, the pump impeller cover cap 10 of fluid torque converter and pump impeller 2 welding, and connect with the flexible disc of motor by bolt, turbine 3 is by turbine hub 6 and output shaft splined, guide wheel 1 is fixed on the gear box casing by spline, and pump impeller, turbine and guide wheel are formed the circulate circle active chamber.Coupling block 4 is screwed into and connects the flexible disc bolt.Lockup clutch 7 also is set in fluid torque converter, and the lock-up clutch of fluid torque converter is positioned at the turbine front end, is made up of lockup piston, friction plate 9, buffer and worm gear drive plate etc.; Described buffer is to be composed in series by main buffer 5 and time 8 two buffers of buffer.
As shown in Figure 2, described active chamber circulate circle shape is an egg type, and the egg type major part is towards the axle center.Described buffer is arranged on the space outerpace between egg type active chamber circulate circle microcephaly and the pump impeller cover cap.
The active chamber circulate circle is adopted different designing shapes in the past.The similar egg type of active chamber circulate circle shape of the utility model design, major part is towards the axle center.The space outerpace of abdicating between active chamber circulate circle microcephaly and the pump impeller cover cap increases a secondary buffer, and the spring of buffer originally just can change into than original little spring to shorten axial dimension.Active chamber circulate circle alteration of form will be confirmed the working condition in flow field through the analog simulation analysis of fluid software, selects best geomery to guarantee the performance of fluid torque converter.
Innovative point of the present utility model is exactly that different torque-converters in the past only use a buffer, and is to use two buffers, is selecting to need process calculating to confirm on the buffer spring rigidity so.Main buffer will guarantee that enough buffering torque capability are arranged under most of operating modes, calculates according to the Maximum Torque under most of operating modes and selects suitable main buffer spring.The spring of secondary buffer is selected in conjunction with main buffer, to determine the secondary buffer spring rate according to design minimal buffering torque demand, is selected suitable spring.The quantity of buffer spring also is to select according to the buffering moment of torsion.
Claims (3)
1. fluid torque converter, the pump impeller cover cap of fluid torque converter and pump impeller weld, and connect with the flexible disc of motor by bolt, and turbine is by turbine hub and output shaft splined, guide wheel is fixed on the gear box casing by spline, and pump impeller, turbine and guide wheel are formed the circulate circle active chamber; Lockup clutch also is set in fluid torque converter, and the lock-up clutch of fluid torque converter is positioned at the turbine front end, is made up of lockup piston, friction plate, buffer and worm gear drive plate etc.; It is characterized in that: described buffer is to be composed in series by main buffer and time two buffers of buffer.
2. fluid torque converter according to claim 1 is characterized in that: described active chamber circulate circle shape is an egg type, and the egg type major part is towards the axle center.
3. fluid torque converter according to claim 1 is characterized in that: described buffer is arranged on the space outerpace between egg type active chamber circulate circle microcephaly and the pump impeller cover cap.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201223074U CN201106670Y (en) | 2007-08-17 | 2007-08-17 | Hydrodynamic torque converter |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201223074U CN201106670Y (en) | 2007-08-17 | 2007-08-17 | Hydrodynamic torque converter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201106670Y true CN201106670Y (en) | 2008-08-27 |
Family
ID=39958472
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007201223074U Expired - Fee Related CN201106670Y (en) | 2007-08-17 | 2007-08-17 | Hydrodynamic torque converter |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201106670Y (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101532564B (en) * | 2009-04-05 | 2012-09-05 | 徐州工程机械科技股份有限公司 | Full flow electrohydraulic control system for construction machinery gear box |
| WO2017079933A1 (en) * | 2015-11-12 | 2017-05-18 | 孙英 | Hydraulic torque converter |
| CN107208768A (en) * | 2015-02-23 | 2017-09-26 | 株式会社艾科赛迪 | The locking device of fluid torque-converter |
| CN113324007A (en) * | 2021-06-29 | 2021-08-31 | 吉林大学 | Hydraulic torque converter device with multistage damping function |
| WO2022001877A1 (en) * | 2020-06-29 | 2022-01-06 | 法雷奥凯佩科液力变矩器(南京)有限公司 | Hydraulic torque converter, power transmission system and vehicle |
| CN114434201A (en) * | 2022-01-14 | 2022-05-06 | 南通固邦数控机床有限公司 | Double-gantry high-rigidity ram machining device |
-
2007
- 2007-08-17 CN CNU2007201223074U patent/CN201106670Y/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101532564B (en) * | 2009-04-05 | 2012-09-05 | 徐州工程机械科技股份有限公司 | Full flow electrohydraulic control system for construction machinery gear box |
| CN107208768A (en) * | 2015-02-23 | 2017-09-26 | 株式会社艾科赛迪 | The locking device of fluid torque-converter |
| US10337596B2 (en) | 2015-02-23 | 2019-07-02 | Exedy Corporation | Lock-up device for torque converter |
| WO2017079933A1 (en) * | 2015-11-12 | 2017-05-18 | 孙英 | Hydraulic torque converter |
| WO2022001877A1 (en) * | 2020-06-29 | 2022-01-06 | 法雷奥凯佩科液力变矩器(南京)有限公司 | Hydraulic torque converter, power transmission system and vehicle |
| CN113324007A (en) * | 2021-06-29 | 2021-08-31 | 吉林大学 | Hydraulic torque converter device with multistage damping function |
| CN114434201A (en) * | 2022-01-14 | 2022-05-06 | 南通固邦数控机床有限公司 | Double-gantry high-rigidity ram machining device |
| CN114434201B (en) * | 2022-01-14 | 2023-03-14 | 南通固邦数控机床有限公司 | Double-gantry high-rigidity ram machining device |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Wuhu Xinlian Shipbuilding Co., Ltd. Assignor: Saic Chery Automobile Co., Ltd. Contract record no.: 2011340000300 Denomination of utility model: Forming mold for pump impeller blade in hydraulic torque converter Granted publication date: 20080827 License type: Exclusive License Record date: 20110810 |
|
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080827 Termination date: 20120817 |