CN105051425A - Hydraulic torque converter - Google Patents
Hydraulic torque converter Download PDFInfo
- Publication number
- CN105051425A CN105051425A CN201380059294.9A CN201380059294A CN105051425A CN 105051425 A CN105051425 A CN 105051425A CN 201380059294 A CN201380059294 A CN 201380059294A CN 105051425 A CN105051425 A CN 105051425A
- Authority
- CN
- China
- Prior art keywords
- torque
- converters
- turbine
- vibration damper
- transfer unit
- 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.)
- Pending
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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
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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
- 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
- F16H2045/0205—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type two chamber system, i.e. without a separated, closed chamber specially adapted for actuating a lock-up clutch
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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
- 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
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0226—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
- F16H2045/0231—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
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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
- 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
- F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
- F16H2045/0263—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a pendulum
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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
- 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
- F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
- F16H2045/0278—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch comprising only two co-acting friction surfaces
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Of Transmissions (AREA)
- Mechanical Operated Clutches (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
The invention relates to a hydrodynamic torque converter (1) having a driving impeller (2) and a driven turbine (3), which is rotatably arranged in a housing (7), wherein the housing (7) can be fixed on a driven shaft (26) of the drive unit, wherein a torque converter crossover coupling (4) is formed, by means of which the turbine (3) can be connected, preferably rotationally fixed, to the housing, the converter cross-over coupling (4) has at least one piston (5) and at least one friction disk (6) for the releasable, frictional connection of the turbine (3) to the housing, and at least one damper (13) connected to the turbine is formed, characterized in that at least one transmission unit (11) is provided, by means of which at least one friction disk (6) is connected to at least one of the vibration dampers (13) in order to transmit torque at least temporarily. A torque transmission that is substantially free of play in the circumferential direction can be achieved by the hydrodynamic torque converter shown here. At the same time, axial offset and axial clutch movement can be achieved almost without friction.
Description
Technical field
The present invention relates to a kind of fluid torque converter, especially can be loaded into the input shaft of driven shaft for junctor drive unit of vehicle and motor vehicle powertrain, the especially input shaft of speed changer.
Background technique
Fluid torque converter is often in a motor vehicle for transmitting and converting torque, especially in starting motor vehicle state.In order to separating vibration, that is in order to stop vibration be delivered on speed changer or be delivered on Motor Vehicle remaining part at large from the driver element of Motor Vehicle (this especially appear at explosive motor the driver element start up period), known various different schemes.As that band is with or without the list of centrifugal force pendulum or two torsional vibration dampers can be used.But such isolation performance is unsatisfactory, in this external transmission of torque, there is undesirable gap.
Summary of the invention
Set out thus, the present invention is based on following task, overcome shortcoming well known in the prior art at least in part.
The feature that task passes through independently claim solves.Favourable improvement project is the content of dependent claims.
Fluid torque converter of the present invention has pump impeller initiatively and driven turbine, this turbine is placed in housing revolvably, wherein, this housing can be fixed on the driven shaft of driver element, wherein, construct a torque-converters crossover coupler, by this torque-converters crossover coupler, turbine preferably can be connected with this housing without relative rotation, wherein, torque-converters crossover coupler has at least one piston and at least one friction disk, described friction disk is used for throwing off between turbine and housing, rub sealed connection, wherein, be configured with the vibration damper that at least one is connected with turbine, especially torsional vibration damper, the feature of this fluid torque converter is, be configured with at least one transfer unit, be connected with at least one in vibration damper by its at least one friction disk, with at least temporary transient transmitting torque.
An element is interpreted as transfer unit, by it, close at torque-converters crossover coupler, that is by pump impeller, turbine and the fluid torque converter that forms of guide vane is by cross-over connection if desired time, the mechanical coupling between friction disk and vibration damper can be realized.Vibration damper is especially interpreted as to the torsional vibration damper with at least one pressure spring.When open at torque-converters crossover coupler run in situation time, this damper action in isolation can by from pump impeller to turbine, the vibration of transmitting through the fluid power transmission of torque of guide wheel if desired.This vibration damper then stops or reduces vibration and continues to be delivered to output shaft, and this output shaft is connected with turbine by vibration damper.At least temporarily, namely torque is imported vibration damper when torque-converters crossover coupler is closed by transfer unit and thus import output shaft through vibration damper, this output shaft is generally the input shaft of speed changer or power train, even if also have isolating technique when torque-converters crossover coupler is closed.
When torque-converters crossover coupler is closed, turbine is connected without relative rotation with housing, and wherein, between turbine and torque-converters crossover coupler, especially centre connects a vibration damper.Concept " without relatively rotating " is interpreted as at this, turbine and housing associated movement, wherein, there is the direct attachment between turbine and housing or such attachment: in this attachment, between turbine and torque-converters crossover coupler, be configured with at least one element such as vibration damper.
Preferable configuration has two vibration dampers, and they are in series arranged especially mutually.This means, the carry-out part of first vibration damper is connected with the input part of the second vibration damper.In addition preferably accessory configurations has centrifugal force pendulum, for further damping and separating vibration.
According to an advantageous configuration of this torque-converters, this torque-converters has an axial direction, and wherein, on axial direction, turbine exists
-at least one piston, at least one friction disk and at least one vibration damper with
-described pump impeller
Between form.
This means, pump impeller and turbine form a unit together with guide wheel if desired, form piston, friction disk and vibration damper abreast in the axial direction with them.This makes it possible to construct fluid torque converter with saving position.
According to an advantageous configuration of torque-converters, be configured with the centrifugal force pendulum unit that at least one is connected without relative rotation with turbine.
The vibration damping to undesirable or harmful vibration and isolation can also be improved thus.Also higher vibration order effectively can be suppressed particularly by the centrifugal force pendulum unit with different pendulum mass.
According to an advantageous configuration of torque-converters, centrifugal force pendulum unit held by transfer unit bag.
This especially means, transfer unit is configured in outside centrifugal force pendulum at least in part diametrically.So just can form not by transfer unit form and construct the common centrifugal force pendulum unit affected.
According to an advantageous configuration of torque-converters, transfer unit is connected with at least one friction disk by least one pawl.
Hook-shaped mechanical component is especially interpreted as pawl.Especially, transfer unit has such pawl and friction disk has corresponding scarfing unit, for the connection between transfer unit and friction disk.Claw connects the in fact gapless transmission of torque making can be realized when torque-converters crossover coupler operates in circumference, has almost frictionless axile displacement possibility simultaneously.In addition transfer unit and friction disk can configurations neatly.
According to an advantageous configuration of torque-converters, transfer unit and at least one friction disk construct integratedly.
The Construction integration of friction disk and transfer unit allows simple assembling and element has good good endurance simultaneously.Torque simultaneously can seamlessly be transmitted in the circumferential.
According to an advantageous configuration of torque-converters, transfer unit and vibration damper are interconnected by Flange joint.
Flange joint is interpreted as at this, and transfer unit is fixed on two components of vibration damper especially in the axial direction, between the balancing mass of such as vibration damper, by such as corresponding rivet or analog.Flange joint allows almost gapless, the transmission of torque that can simply and at low cost make.
According to an advantageous configuration of torque-converters, transfer unit is connected with vibration damper as side panel.
In this case transfer unit axial direction is connected with vibration damper in side.A part for vibration damper, such as balancing mass or analog, be configured in the side of transfer unit in the axial direction and be such as connected with transfer unit by riveted joint or analog.
According to an advantageous configuration of torque-converters, transfer unit extends radially outward beyond friction disk outwards and radially-inwardly extend towards vibration damper therefrom.
According on the other hand, a kind of Motor Vehicle is proposed, it have band driven shaft driver element, there is power train and according to fluid torque converter of the present invention.Preferred driver element to be arranged in before operator cabin and in a motor vehicle transverse to the longitudinal axis of Motor Vehicle.
Most Motor Vehicle has pre-driver device at present, and therefore, driver element such as explosive motor or motor to be preferably arranged on before operator cabin and transverse to main direction of travel.Under this layout, installing space is little especially just, therefore, uses the clutch of minor structure size advantageous particularly.
The narrow and small situation of installing space seems outstanding especially in the car of the sedan car grade according to European classification.The equipment applied in the car of dolly series does not obviously reduce compared with the equipment compared with cart system.But operational installing space is significantly less in dolly.It is especially favourable that compensation adjustment device described above or friction clutch are used for dolly, because total installation dimension is little and realize and Compensation Regulation reliably.Car is by according to such as size, and price, weight, power is included into different automobile ranks, and wherein its definition is always different along with the transformation of market demand.According to the dolly of European classification and the vehicle of most dolly rank on American market corresponding to the compact car of low side (subcompactcar) rank, corresponding to super mini car (superminicar) rank on English market, such as city car (CityCar) rank.The example of most dolly rank is the Fox of popular company or the Twingo of RJ Reynolds Tobacco Holdings ,Inc..The example of dolly rank is the Clio of Mito, the Polo of popular company of Alpha Luo Miou company, the Fiesta of Ford or RJ Reynolds Tobacco Holdings ,Inc..
In the claims the single feature enumerated can with arbitrarily, technically significant mode mutually combine, and can be supplemented by the explanatory content in specification and the details in accompanying drawing, of the present invention other shown in the drawings implement modification.
Accompanying drawing explanation
The present invention and technical field is explained in detail below by accompanying drawing.Accompanying drawing illustrates particularly preferred embodiment, but the present invention is not limited to these embodiments.Will point out especially, accompanying drawing, especially shown magnitude relationship are just schematically.Accompanying drawing illustrates:
Fig. 1: the cross section of the first case of fluid torque converter,
Fig. 2: the cross section of the details of the second case of fluid torque converter,
Fig. 3: the cross section of the details of the 3rd example of fluid torque converter,
Fig. 4: the cross section of another details of fluid torque converter,
Fig. 5: the cross section of the details of the 4th example of fluid torque converter, and
Fig. 6: Motor Vehicle.
Embodiment
Fig. 1 diagrammatically illustrates the first case of fluid torque converter 1, has pump impeller 2 initiatively and driven turbine 3.Fluid torque converter 1 also comprises torque-converters crossover coupler 4, and this torque-converters crossover coupler has a piston 5 and at least one friction disk 6, such as friction plate, with the lining that rubs accordingly.By piston 5, friction disk 6 is pressed to the housing 7 of fluid torque converter 1, make to there is at housing 7 and between piston 5 and friction disk 6 the sealed connection that rubs.
Housing 7 is connected without relative rotation with input propeller boss 8, and input propeller boss 8 is connected without relative rotation with the input shaft do not illustrated here again.Output shaft is such as the driven shaft of the driven shaft of driver element, the explosive motor of such as Motor Vehicle.Therefore, housing 7 rotates with input propeller boss 8, and input propeller boss 8 rotates around spin axis 9 with input shaft again.
As long as torque-converters crossover coupler 4 is opened, namely between friction disk 6 and piston 5 and housing 7, there is not the sealed connection that rubs, then pump impeller 2 is just by the rotary actuation of housing 7.At this, by the guide wheel do not illustrated here, due to the turning to of flowing of the liquid between pump impeller and turbine, such as oil, torque is delivered to turbine 3 from pump impeller 2 in fluid power mode.The structure of pump impeller 2, turbine 3 and guide wheel can be such as so-called Te Liluoke (Trilok) torque-converters.
Turbine 3 is connected without relative rotation with output propeller boss 10, and this output propeller boss 10 such as, is connected without relative rotation with output shaft, the input shaft of motor vehicle powertrain do not illustrated here, such as vehicle transmission input shaft again.Thus, the rotation of turbine 3 causes the rotation of output propeller boss 10 and thus causes output shaft to rotate.At this, the transmission of torque of carrying out through pump impeller 2 and turbine 3 is normally used for starter motor motor-car.
In order to avoid the skidding determined physically of this device, when rotating speed is higher, torque-converters crossover coupler 4 is closed.Piston 5 moves to housing 7 on spin axis 9 direction for this reason, is compressed by friction disk 6 at this between piston 5 and housing 7.Then torque is mechanically transmitted on friction disk 6.
At this, friction disk 6 and transfer unit 11 are mechanically connected, and are being connected by least one pawl 12 according in the present example of Fig. 1.Pawl 12 is configured on transfer unit 11, and friction disk 6 is scarfed at least one pawl 12 described in transfer unit 11 from inner radial.By one, the connection carried out of preferred multiple such pawl 12 makes torque substantially seamlessly be delivered in the circumferential in transfer unit 11.
Torque is delivered in the first vibration damper 13 at this by transfer unit 11, and this first vibration damper is configured to the torsional vibration damper with at least one first torsional vibration damper spring 14 and the first balancing mass 15.Transfer unit 11 extends radially outward beyond friction disk 6 and radial direction extends towards vibration damper 13 inwards therefrom.These first balancing masses 15 are connected by rivet 16 force closure ground.First balancing mass 15 and transfer unit 11 form Flange joint.As being shown specifically in the diagram, transfer unit 11 abuts on two the first torsional vibration damper springs 14 with transmitting torque.This torque is delivered on the first torsional vibration damper spring 14 by transfer unit 11, is delivered to therefrom again in the first balancing mass 15.Torque is delivered to the second vibration damper 17 from the first balancing mass 15, and this second vibration damper is also configured to common torsional vibration damper, has the second torsional vibration damper spring 18.Through the first balancing mass 15, transmission of torque, on the second torsional vibration damper spring 18, is delivered in the second balancing mass 19 of the second vibration damper 17 therefrom.Second balancing mass 19 is connected with output propeller boss 10 again, thus torque can be delivered on output shaft that do not demonstrate, that be connected with output propeller boss 10 here, such as, on the input shaft of vehicle transmission.
First vibration damper 13 and the second vibration damper 17 play function in this as torsional vibration damper, they can damping determine, the vibration frequency that produces usually used as the resonance in whole system, thus vibration can be stoped to be delivered to power train from driver element or to be broadly delivered to Motor Vehicle remaining part.Namely isolating technique is achieved by the first vibration damper 13 and the second vibration damper 17.
In order to improve vibration characteristics further, fluid torque converter 1 has centrifugal force pendulum unit 20, and this centrifugal force pendulum unit has multiple pendulum mass 21 in a known way, and these pendulum masses can offset relative to the basic component 22 of centrifugal force pendulum unit 20.Be in operation, centrifugal force is used for pendulum mass 21 is accelerated, to produce the anti-vibration relative to inputted vibration thus.Especially, when common explosive motor is as driver element, especially when explosive motor starts, produce vibration, this vibration should not be delivered to the remaining part of system as far as possible.To this, the centrifugal force pendulum unit 20 with pendulum mass 21 confirms it is effective especially, and these pendulum masses resist the vibration of driver element in resonance region.
Centrifugal force pendulum unit 20 also have turbine 3 to be connected with output propeller boss 10 by the second vibration damper 17 and abreast, can be rotated to support on and export on propeller boss.In order to construct the fluid torque converter 1 saving position as far as possible, piston 5, friction disk 6, first vibration damper 13, second vibration damper 17 and centrifugal force pendulum unit 20 are arranged on the side of turbine 3, and pump impeller 2 is arranged on the opposite side of turbine 3.The pendulum mass 21 of the first vibration damper 13 and centrifugal force pendulum unit 20 obtains radial as far as possible outer in housing 7 internal placement.Second vibration damper 17 with saving position, radial built-inly relative to the first vibration damper 13 is formed.
At Fig. 2, only set forth about the difference of the example relative to Fig. 1 in other example shown in 3 and 5.Other side can refer to the explanation done for Fig. 1.The same symbology of same element.
Fig. 2 schematically shows the details of the second case of fluid torque converter 1.At this, transfer unit 11 is configured to one with at least one friction disk 6 (not shown in FIG.) being embodied as a friction plate or multiple friction plate.Transfer unit 11 is fastened between the first balancing mass 15 by flange-type.In the region of the first vibration damper 13, transfer unit 11 is S-type.Second balancing mass 19 is carried out like the support exported on propeller boss 10 and first case subclass, is similar to turbine 3, centrifugal force pendulum unit 20 and exports propeller boss 10 by the connection of the second vibration damper 17 and the supporting on output propeller boss 10.At this, torque realizes from the intermediate mass 23 that passes through of the first vibration damper 13 to the second vibration damper 17.
Fig. 3 illustrates the details of another example of fluid torque converter 1.At this, transfer unit 11 and friction disk 6 (not shown in FIG.) are integrated.Different from the example in Fig. 2, not be connected with the first balancing mass 15 by Flange joint, but as the side panel in one of first balancing mass 15.Torque imports in the second torsional vibration damper spring 18 by the first balancing mass 15, is imported export propeller boss 10 by the second torsional vibration damper spring and the second balancing mass 19.Radial support is substantially the same with example previously discussed.
Fig. 4 illustrates that torque imports to the example in the first vibration damper 13.At this, transfer unit 11 is configured between two the first torsional vibration damper springs 14, and torque can be delivered in the first torsional vibration damper spring 14.
Fig. 5 illustrates the details of another example of fluid torque converter 1.In this instance, transfer unit 11 and friction disk 6 are configured to one, and the connection between transfer unit 11 and the first balancing mass 15 is flanged.Other is with reference to the elaboration to Fig. 1.
Fig. 6 illustrates the example of Motor Vehicle 24, and it has driver element 25 with driven shaft 26 as explosive motor.Driven shaft 26 is connected with the input shaft of the speed changer of the power train 27 of Motor Vehicle 24 by fluid torque converter 1.Driver element 25 is laterally contained in before operator cabin 28, and that is, the spin axis 9 of driven shaft 26 is directed perpendicular to the longitudinal axis 29 of Motor Vehicle 24.
By shown here fluid torque converter 1, substantially gapless transmission of torque in the circumferential can be realized.Simultaneously can almost without frictionally realizing axile displacement and axial clutch motion.
Reference numerals list
1 fluid torque converter
2 pump impellers
3 turbines
4 torque-converters crossover couplers
5 pistons
6 friction disks
7 housings
8 input propeller boss
9 spin axiss
10 export propeller boss
11 transfer units
12 pawls
13 first vibration dampers
14 first torsional vibration damper springs
15 first balancing masses
16 rivets
17 second vibration dampers
18 second torsional vibration damper springs
19 second balancing masses
20 centrifugal force pendulum unit
21 pendulum masses
22 basic components
23 intermediate masses
24 Motor Vehicle
25 driver elements
26 driven shafts
27 power trains
28 operator cabins
29 longitudinal axis
Claims (10)
1. fluid torque converter (1), there is pump impeller (2) initiatively and driven turbine (3), described turbine can be arranged in housing (7) rotationally, wherein, housing (7) can be fixed on the driven shaft (26) of driver element (25), wherein, be configured with torque-converters crossover coupler (4), by this torque-converters crossover coupler, turbine (3) can be connected with housing (7), wherein, torque-converters crossover coupler (4) has at least one piston (5) and at least one friction disk (6), for throwing off of turbine (3) and housing (7), rub sealed connection, wherein, be configured with at least one vibration damper (13) be connected with turbine (3), it is characterized by, be configured with at least one transfer unit (11), by this transfer unit, at least one friction disk (6) is connected with at least one in vibration damper (13), with at least temporarily transmitting torque.
2. torque-converters according to claim 1 (1), has axial direction (9), wherein, exists at the upper described turbine (3) of axial direction (9)
-described at least one piston (5), at least one friction disk described (6) and at least one vibration damper described (13,17) with
-described pump impeller (2)
Between form.
3. according to the torque-converters (1) of one of above claim, wherein, be configured with at least one with described turbine (3) without the centrifugal force pendulum unit (20) be mutually connected rotationally.
4. torque-converters according to claim 3 (1), wherein, described centrifugal force pendulum unit (20) held by described transfer unit (11) bag.
5. according to the torque-converters (1) of one of above claim, wherein, described transfer unit (11) is connected with at least one friction disk (6) by least one pawl (12).
6. according to the torque-converters (1) of one of Claims 1-4, wherein, described transfer unit (11) and at least one friction disk (6) are formed integratedly.
7. according to the torque-converters (1) of one of above claim, wherein, described transfer unit (11) and described vibration damper (13) are interconnected by Flange joint.
8. according to the torque-converters (1) of one of claim 1 to 6, wherein, described transfer unit (11) is connected with described vibration damper (13) as side panel.
9. according to the torque-converters (1) of one of above claim, wherein, described transfer unit (11) extends radially outward beyond described friction disk (6) and radially-inwardly extends towards described vibration damper (13) therefrom.
10. Motor Vehicle (24), have with driven shaft (26) driver element (25), there is the power train (27) with input shaft and the fluid torque converter (1) according to one of above claim, for the driven shaft that is releasably coupled (26) and input shaft.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012221371 | 2012-11-22 | ||
| DE102012221371.6 | 2012-11-22 | ||
| PCT/DE2013/200311 WO2014079442A1 (en) | 2012-11-22 | 2013-11-21 | Hydrodynamic torque converter |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105051425A true CN105051425A (en) | 2015-11-11 |
Family
ID=49918347
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380059294.9A Pending CN105051425A (en) | 2012-11-22 | 2013-11-21 | Hydraulic torque converter |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN105051425A (en) |
| DE (2) | DE102013223753A1 (en) |
| WO (1) | WO2014079442A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704519A (en) * | 2015-11-17 | 2017-05-24 | 熵零股份有限公司 | Power unit |
| CN110039987A (en) * | 2018-01-16 | 2019-07-23 | 舍弗勒技术股份两合公司 | Connecting assembly and hybrid power system |
| CN111734807A (en) * | 2020-08-01 | 2020-10-02 | 盛瑞传动股份有限公司 | Control method for relieving whole-vehicle resonance of hydraulic automatic transmission |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR3034483B1 (en) * | 2015-03-30 | 2019-11-22 | Valeo Embrayages | TORQUE TRANSMISSION DEVICE FOR A MOTOR VEHICLE |
| DE102015216837A1 (en) | 2015-09-03 | 2017-03-09 | Schaeffler Technologies AG & Co. KG | centrifugal pendulum |
| DE102017102730A1 (en) * | 2017-02-13 | 2018-08-16 | Schaeffler Technologies AG & Co. KG | Hydrodynamic torque converter with speed-adaptive torsional vibration damper |
| CN118462802B (en) * | 2024-07-10 | 2024-11-19 | 陕西法士特齿轮有限责任公司 | Hydraulic coupler, working method thereof and transmission system for vehicle |
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|---|---|---|---|---|
| US20040226794A1 (en) * | 2003-04-05 | 2004-11-18 | Zf Sachs Ag | Torsional vibration damper |
| CN102245936A (en) * | 2008-12-10 | 2011-11-16 | Zf腓特烈斯哈芬股份公司 | Hydrodynamic coupling arrangement, in particular torque converter |
| US20110287844A1 (en) * | 2010-05-18 | 2011-11-24 | Schaeffler Technologies Gmbh & Co. Kg | Single row series damper with input flange |
| DE102012205764A1 (en) * | 2011-04-26 | 2012-10-31 | Schaeffler Technologies AG & Co. KG | torsional vibration damper |
| CN102792057A (en) * | 2010-03-11 | 2012-11-21 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10362274C5 (en) * | 2003-04-05 | 2018-03-01 | Zf Friedrichshafen Ag | torsional vibration damper |
-
2013
- 2013-11-21 DE DE102013223753.7A patent/DE102013223753A1/en not_active Withdrawn
- 2013-11-21 WO PCT/DE2013/200311 patent/WO2014079442A1/en active Application Filing
- 2013-11-21 CN CN201380059294.9A patent/CN105051425A/en active Pending
- 2013-11-21 DE DE112013005615.1T patent/DE112013005615A5/en not_active Ceased
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040226794A1 (en) * | 2003-04-05 | 2004-11-18 | Zf Sachs Ag | Torsional vibration damper |
| CN102245936A (en) * | 2008-12-10 | 2011-11-16 | Zf腓特烈斯哈芬股份公司 | Hydrodynamic coupling arrangement, in particular torque converter |
| CN102792057A (en) * | 2010-03-11 | 2012-11-21 | 舍弗勒技术股份两合公司 | Torsional vibration damper |
| US20110287844A1 (en) * | 2010-05-18 | 2011-11-24 | Schaeffler Technologies Gmbh & Co. Kg | Single row series damper with input flange |
| DE102012205764A1 (en) * | 2011-04-26 | 2012-10-31 | Schaeffler Technologies AG & Co. KG | torsional vibration damper |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704519A (en) * | 2015-11-17 | 2017-05-24 | 熵零股份有限公司 | Power unit |
| CN110039987A (en) * | 2018-01-16 | 2019-07-23 | 舍弗勒技术股份两合公司 | Connecting assembly and hybrid power system |
| CN111734807A (en) * | 2020-08-01 | 2020-10-02 | 盛瑞传动股份有限公司 | Control method for relieving whole-vehicle resonance of hydraulic automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| DE112013005615A5 (en) | 2015-08-20 |
| WO2014079442A1 (en) | 2014-05-30 |
| DE102013223753A1 (en) | 2014-05-22 |
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