CN102032331A - Shell structure of torque converter - Google Patents
Shell structure of torque converter Download PDFInfo
- Publication number
- CN102032331A CN102032331A CN2010102883491A CN201010288349A CN102032331A CN 102032331 A CN102032331 A CN 102032331A CN 2010102883491 A CN2010102883491 A CN 2010102883491A CN 201010288349 A CN201010288349 A CN 201010288349A CN 102032331 A CN102032331 A CN 102032331A
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- Prior art keywords
- turbine
- pump
- case
- torque converter
- shell
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H41/00—Rotary fluid gearing of the hydrokinetic type
- F16H41/24—Details
-
- 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides a shell structure of a torque converter for preventing the contact between a turbine shell and a pump shell. In the torque converter (1), a pump wheel (20) and a turbine (30) are coaxially equipped with a mode that the relative rotation is allowed. In a main body shell (2) which is formed by a pump shell (21) and a front cover (10) of the pump wheel (20), a turbine shell (31) of the turbine (30) is set relatively to the pump shell (21) with a certain distance, wherein, the periphery of the turbine shell (31) is provided with a projection (36) which projects to the side of the pump shell (21). When the turbine shell (31) moves to the side of the pump shell (21), the projection (36) of the turbine shell (31) contacts with an abutting part (21c) of the pump shell (21) before the contact between the turbine blades (32) of the turbine shell (31) and the pump blades (22) of the pump shell (21).
Description
Technical field
The present invention relates to the shell construction of fluid torque converter.
Background technique
Fig. 5 is the figure of the formation of the common fluid torque converter of explanation.
In the fluid torque converter 100 of automatic transmission, pump impeller 110 and turbine 120 can be provided with on coaxial with the relative rotation so that stator 130 is clipped in therebetween.
In fluid torque converter 100, in the body shell 150 that pump case 111 and protecgulum 140 by pump impeller 110 form, the turbine case 121 of turbine 120 and pump case 111 are relative and be provided with.
On pump case 111, be provided with a plurality of pump blades 112 in opposite with turbine 120, linking in the end of internal side diameter has sleeve 113.
On turbine case 121, be provided with a plurality of turbine blades 122 at opposing side with pump impeller 110, linking at the internal side diameter of turbine case 121 has spline to be embedded in the turbine hub 123 of input shaft 170.
In this fluid torque converter 100, the rotary driving force of motor (not shown) is via protecgulum 140 input pump impellers 110, after the rotary driving force of input pump impeller 110 passes to turbine 120 via the fluid in the body shell 150, be delivered to the input shaft 170 of the gear portion (not shown) that links with turbine 120, thereby make input shaft 170 rotations.
In fluid torque converter, velocity ratio (secondary speed/pump impeller rotating speed) more little (convergence zero more), the difference of the rotating speed of turbine and pump impeller is big more.
When the difference of rotating speed becomes big, the flow through speed height of the fluid in their body shell 150 in the outside of the velocity ratio of the fluid that between turbine 120 and pump impeller 110, circulates, the pressure ratio outer space S2 in the space S 1 of being surrounded by turbine 120 and pump impeller 110 is low.
So because the power (thrust) of 110 sides of the pump impeller shown in the arrow Y acts on turbine 120 in figure, therefore, free end is that the outer circumferential side of turbine 120 can be to being moved by the direction shown in the arrow Y and contacting with pump impeller 110 sometimes.
Therefore, in existing fluid torque converter 100, thicken to improve rigidity by thickness the joint 121a of turbine case 121 and turbine hub 123, and increase the carrying capacity of the bearing 160 of bearing thrust, prevented contacting of turbine case 121 and pump case 111 thus, but because this measure, the fabricating cost of fluid torque converter 100 improves.
Fig. 6 is the sectional drawing of patent documentation 1 disclosed fluid torque converter 200.
In patent documentation 1, disclose, in possessing the lock-up clutch usefulness fluid torque converter 200 of piston 270 that is welded with turbine case 221, the opposite with pump case 211 at piston 270 is provided with friction means 271, at turbine 220 during to pump impeller 210 side shiftings, contact with the extension part 214 of pump case 211 by friction means 271, pump case 211 is not contacted with turbine case 221.
Patent documentation 1:(Japan) spy opens the 2004-332801 communique
But under the situation of using fluid torque converter 200, though can prevent contacting of pump case 211 and turbine case 221, when friction means 271 and extension part 214 butts, turbine 220 and pump impeller 210 become lockup state.
Therefore, under the situation of using fluid torque converter 200, be difficult to control the moment of locking.
So, require turbine case not to be contacted with pump case with more cheap structure.
Summary of the invention
The invention provides a kind of shell construction of fluid torque converter, in this fluid torque converter, pump impeller and turbine can be provided with on coaxial with the relative rotation, in the body shell that pump case and protecgulum by described pump impeller form, the turbine case of described turbine is provided with predetermined distance with respect to described pump case, is provided with to the side-prominent protuberance of described pump case in the periphery of described turbine case.
According to the present invention, at turbine case during to the pump case side shifting, with before pump case contacts, the protuberance side-prominent to pump case contacts with pump case, thereby prevents contacting of turbine case and pump case at turbine case.
In addition, the protuberance that contacts with pump case is because of bearing the part of the thrust that acts on turbine case, therefore, the requirement of load capacity of bearing that the rigidity of turbine case required and be subjected to acting on the thrust of turbine obtains relaxing according to the thrust of being born, therefore, can provide fluid torque converter more at an easy rate.
Description of drawings
Fig. 1 is the sectional drawing of the fluid torque converter of present embodiment;
Fig. 2 (a) and (b) are enlarged views of the major component of fluid torque converter;
Fig. 3 (a) and (b) are figure of effect of the fluid torque converter of explanation present embodiment;
Fig. 4 is the associated diagram of thrust and velocity ratio;
Fig. 5 is the sectional drawing of the fluid torque converter of conventional example;
Fig. 6 is the sectional drawing of the fluid torque converter of conventional example.
Description of reference numerals
1 fluid torque converter
2 body shell
3 input shafts
4 stator axis
10 protecgulums
20 pump impellers
21 pump cases
22 pump blades
23 impeller sleeves
30 turbines
31 turbine cases
The 31a linking department
The 31b joint
The 31c peripheral part
32 turbine blades
33 turbine hub
34 plectane portions
35 cylindrical portion
36 protuberances
The 36a front end
The 36b curved part
36c top (mountain portion)
36d ditch portion (paddy portion)
40 stators
41 base portions
The 41a cylindrical part
41b plectane portion
41c bearing supporting mass
42 stator vanes
50 overrunning clutchs
51 inner rings
52 clutch main bodys
53 outer rings
60 baffle plates
61 plectane portions
70,71 thrust-bearings
100,200 fluid torque converters
110,210 pump impellers
111,211 pump cases
112,212 pump blades
113,213 sleeves
120,220 turbines
121,221 turbine cases
The 121a joint
122 turbine blades
123 turbine hub
130 stators
140 protecgulums
150 body shell
160 bearings
170 input shafts
214 extension parts
231 friction means
270 pistons
The R rivet
S1, S2 space
The X running shaft
Embodiment
Below, embodiments of the present invention are described.
As shown in Figure 1, in the fluid torque converter 1 of vehicle automatic transmission, pump impeller 20 and turbine 30 can be provided with on same axle with the relative rotation, and in the body shell 2 that pump case 21 and protecgulum 10 by pump impeller 20 form, the turbine case 31 of turbine 30 and pump case 21 are clipped in stator 40 therebetween and opposed.
The attachment portion of embedding part 12a and front end 21a spreads all over full week and soldered, and when the rotary driving force of motor was imported protecgulum 10, protecgulum 10 and pump impeller 20 rotated integratedly around running shaft X.
In pump case 21, the opposition side (left side among the figure) that bends to turbine 30 with the opposed part of the turbine blade 32 on right side among the figure expands.The opposing side with turbine 30 of the part of this bending is provided with a plurality of pump blades 22, pump blade 22 around running shaft X circumferentially be configured to radial.
The front end 21a of pump case 21 at the radial outside of turbine case 31, is embedded in the cylindrical part 12 (embedding part 12a) of protecgulum 10 more extending along running shaft X by the position of radial outside than turbine 30.
The part that pump blade 22 is installed of pump case 21 and the part 21c between the front end 21a are along with near turbine 30, and tilt to the direction away from input shaft 3 (running shaft X), become the abutting part (below, note do abutting part 21c) of protuberance 36 butts of turbine case 31 described later.
The impeller sleeve 23 of pump impeller 20 possesses along the axially extended cylindrical portion 23a of input shaft 3 and the 23b of plectane portion that extends to radial outside from the end of turbine 30 sides (right side the figure) of cylindrical portion 23a, and section is for having roughly L word shape.
The peripheral part 23b1 of the 23b of plectane portion is from interior all side end 21b butts of radially inner side and pump case 21, and it is soldered that the attachment portion of peripheral part 23b1 and end 21b spreads all over full week.
In addition, between the 41b of plectane portion of the base portion 41 of 23b of plectane portion and stator described later 40, be provided with thrust-bearing 71.
Turbine 30 possesses turbine case 31, is installed on a plurality of turbine blades 32 of turbine case 31, supporting turbine case 31 and simultaneously spline be embedded in the turbine hub 33 of input shaft 3.
On turbine case 31, pump case 21 is that the opposition side (right side among the figure) that outer circumferential side bends to pump impeller 20 expands with relative part pump blade 22.
The opposing side with pump impeller 20 in the part of this bending is provided with a plurality of turbine blades 32, turbine blade 32 around running shaft X circumferentially be configured to radial.
Be provided with linking department 31a with turbine hub 33 in interior all sides of turbine case 31.Linking department 31a has circular plate shape, is provided with in the mode with running shaft X quadrature in the position (position of keeping right among the figure) by motor of turbine case 31.
On linking department 31a, around running shaft X circumferentially be provided with a plurality of rivet inserting hole 31a1 with predetermined distance, in mode of execution, the linking department 31a of turbine case 31 is fixed on the turbine hub 33 with rivet R.
In addition, the part that turbine blade 32 is installed of turbine case 31 and the part between the linking department 31a are that joint 31b tilts to the direction near input shaft 3 along with approaching linking department 31a.
(a) is the figure that amplifies the major component of presentation graphs 1 among Fig. 2, (b) is the figure that schematically shows along around the state of the A-A section of running shaft X (a) that circumferentially see from radial outside.
Fig. 3 (a) is that outer circumferential side arrow Y direction in (a) at Fig. 2 of expression turbine case 31 moves, the figure of protuberance 36 and the state of the abutting part 21c butt of pump case 21 (b) is the figure that schematically shows along around the state of the A-A section of running shaft X (a) that circumferentially see from radial outside.
At the peripheral part 31c of turbine case 31, spread all over being provided with in full week of outer periphery of turbine case 31 and see to the outstanding protuberance 36 of radial outside from input shaft 3.
The abutting part 21c of pump case 21 separates predetermined distance and protuberance 36 is opposed, and the inner peripheral surface 21c1 of abutting part 21c is the bearing surface of protuberance 36 butts (below, be designated as bearing surface 21c1).
Bearing surface 21c1 is the tilted tabular surface of predetermined angular of relative rotation axi X, and the full week of spreading all over the interior week of pump case 21 is provided with in the mode of surrounding running shaft X.
In mode of execution, the forward end of the peripheral part 31c of crooked sleekly turbine case 31, thereby the curved part 36b that the protuberance 36 that forms turbine case 31 is arranged in than terminal side the bearing surface 21c1 almost parallel of the relative pump case 21 of its bearing of trend, the front end 36a of protuberance 36 more leans on figure right side (protecgulum 10 sides).
This protuberance 36 forms when forming turbine case 31 by drawing simultaneously.
Shown in Fig. 2 (b), protuberance 36 along around running shaft X circumferentially, the mode that replaces mutually with top 36c and the 36d of ditch portion forms wavy, top 36c is positioned at the abutting part 21c side of pump case 21.
In mode of execution, shown in Fig. 2 (a), the bearing surface 21c1 of top 36c and abutting part 21c leave distance D 1 be set to than pump blade 22 and turbine blade 32 immediate parts to leave distance D 2 little.
In Fig. 2 (a), turbine case 31 is when bearing along the power of arrow Y directive effect among the figure and to pump case 21 side shiftings, before the pump blade 22 of the turbine blade 32 of turbine case 31 and pump case 21 contacted, the protuberance 36 of turbine case 31 contacted with the abutting part 21c of pump case 21.
In addition, when protuberance 36 contacted with the bearing surface 21c1 of abutting part 21c, protuberance 36 can not spread all over and contacts with bearing surface 21c1 in circumferentially full week, and only the top 36c of protuberance 36 contacts with bearing surface 21c1.
As shown in Figure 1, turbine hub 33 constitutes to possess and links with the linking department 31a of turbine case 31 and the plectane portion 34 of supporting turbine case 31, the axially extended cylindrical portion 35 from the internal side diameter of plectane portion 34 along input shaft 3, and the inner peripheral surface of cylindrical portion 35 and input shaft 3 splines are chimeric.
Be fixed with the plectane portion 61 of the linking department 31a and the baffle plate 60 of turbine case 31 by rivet R at the outer circumferential side of plectane portion 34.
In addition, between the bearing supporting mass 41c of the internal side diameter of plectane portion 34 and stator 40, be provided with the thrust-bearing 70 that bears the thrust that acts on turbine 30.
Overrunning clutch 50 possesses inner ring 51, the clutch main body 52 that is equipped on the outer circumferential face of inner ring 51 that spline is embedded in stator axis 4, the outer ring 53 that is equipped on the outer circumferential face of clutch main body 52, and 53 outer circumferential face is fixed with cylindrical part 41a in the outer ring.
And the inner ring 51 of the 41b of plectane portion of base portion 41 and bearing supporting mass 41c and overrunning clutch 50, clutch main body 52, and the front and back sides of outer ring 53 contact and slipping are carried out axial location.
Below, effect of the present invention is described.
Fig. 4 is an illustration in the chart of the relation of the thrust of turbine 30 and velocity ratio, is the figure of explanation thrust-bearing 70 thrust of bearing.
After for example vehicle began to start, in the speed stage littler than e, as shown in Figure 2, owing to the rate of circulating flow height of the oil in the space S 1 of being surrounded by turbine case 31 and pump case 21, therefore, the pressure in the pressure ratio outer space S2 in the space S 1 was low.
Therefore, the thrust (being set at the power of turbine 30 to pump impeller 20 side shiftings that makes) of the directive effect of representing along arrow Y among the figure acts on the turbine 30, and as shown in Figure 3, free end is peripheral part 31c side direction pump impeller 20 side shiftings of turbine case 31.
At this, at the peripheral part 31c of turbine case 31, be provided with to the outstanding protuberance 36 of radial outside, the abutting part 21c of pump case 21 so that the radial outside of turbine case 31 along with trend front end 21a away from the oblique extension of the mode of turbine 31.And, protuberance 36 and abutting part 21c leave distance D 1 be set to than pump blade 22 and turbine blade 32 immediate parts to leave distance D 2 little.
Therefore, with before pump case 21 (pump blade 22) contacts, protuberance 36 contacts with the abutting part 21c of pump case 21, and turbine blade 32 is directly contacted with pump blade 22 at turbine case 31 (turbine blade 32).
At this, the mode that protuberance 36 replaces with top 36c and the 36d of ditch portion mutually along the Zhou Fangxiang around running shaft X forms wavy, therefore, and as shown in Figure 3, when protuberance 36 and abutting part 21c butt, be only the top 36c of protuberance 36 and the state of bearing surface 21c1 butt.
That is, the area of contact of protuberance 36 and abutting part 21c is restricted, because of the surface friction drag that bears from these contact interfaces is little, so pump impeller 20 and turbine 30 are not lockup state, but can rotate relatively.
At this moment, the outside diameter of turbine case 31 bears the part of the thrust that acts on turbine 30 by the abutting part 21c supporting of pump case 21, and therefore, the thrust that acts on thrust-bearing 70 correspondingly reduces.
For example shown in Figure 4, under the situation that is not provided with protuberance 36, the thrust that acts on thrust-bearing 70 changes along curve L1 than e according to speed.
In contrast, under the situation that is provided with protuberance 36, protuberance 36 is supported and is born the part of the thrust that acts on thrust-bearing 70 by abutting part 21c, therefore, the thrust that acts on thrust-bearing 70 than the speed of the contacting of protuberance 36 and abutting part 21c/boundary that non-contact is switched than the low low speed of ex than side, change along curve L2.
That is, the thrust that acts on thrust-bearing 70 reduces the height part in the zone represented with symbol among the figure, therefore, compares with the situation of the fluid torque converter that is not provided with protuberance 36, and thrust-bearing 70 desired carrying capacity reduce.
Therefore, thrust-bearing 70 can be changed to little, the more cheap thrust-bearing of carrying capacity, therefore can make the reduction of the fabricating cost of fluid torque converter.
In addition,, thrust-bearing can be replaced into the more cheap parts as metallic shim and resin pad, therefore, fabricating cost further be reduced according to the size of the thrust that acts on turbine 30.
In addition, because of the outer circumferential side of turbine case 31 can not reduce to the rigidity that pump impeller 20 side shiftings need turbine case 31 (joint 31b), so correspondingly the thickness of attenuate turbine case 31 (joint 31b) can make fluid torque converter 1 lightweight.
As mentioned above, in the fluid torque converter 1 of present embodiment, constitute, pump impeller 20 and turbine 30 can be provided with on same axle with the relative rotation, in the body shell 2 that pump case 21 and protecgulum 10 by pump impeller 20 form, the turbine case 31 of turbine 30 and pump case 21 are oppositely arranged with predetermined distance, are provided with to the side-prominent protuberance 36 of pump case 21 in the periphery of turbine case 31.
Thus, though turbine case 31 to pump case 21 side shiftings, because of the abutting part 21c of the protuberance 36 of turbine case 31 and pump case 21 contacts earlier, therefore, turbine blade 32 (turbine case 31) can directly not contact with pump blade 22 (pump case 21).
In addition, protuberance 36 contacts with the abutting part 21c of pump case 21 and bearing thrust, therefore, the outer circumferential side of turbine case 31 does not make turbine case 31 (joint 31b) need to pump impeller 20 side shiftings rigidity reduces, therefore, correspondingly the thickness of attenuate turbine case 31 (joint 31b) can make fluid torque converter 1 lightweight.
Simultaneously, can make thrust-bearing 70 change to the little more cheap thrust-bearing of carrying capacity, therefore, the fabricating cost of fluid torque converter is reduced.In addition,, can make thrust-bearing be replaced into more cheap thrust-bearing as metallic shim and resin pad, therefore fabricating cost is further reduced according to the size of the thrust that acts on turbine 30.
In addition, situation at existing fluid torque converter, for fear of contacting of pump impeller 20 and turbine 30, need to enlarge and to leave distance D 2 (with reference to Fig. 2) between them, by flowing of the hydraulic oil of pump impeller 20 ejection by the flow damage of the hydraulic oil in the gap inflow space S1 of pump case 21 and turbine case 31, the mis-behave of fluid torque converter.
But, in the fluid torque converter 1 of mode of execution, owing to can avoid contacting of pump impeller 20 and turbine 30 reliably, can make therefore that to leave distance D 2 narrower.Therefore, be suppressed by the degree from the flow damage of the hydraulic oil of the gap inflow space S1 of pump case 21 and turbine case 31 by flowing of the hydraulic oil of pump impeller 20 ejection, therefore, the performance of fluid torque converter improves.
In addition, shown in Fig. 2 (b), protuberance 36 spreads all over the outer thorough week of turbine case 31 and is provided with, the constituting of protuberance 36 and opposing side pump case 21, with along around running shaft X circumferentially, the mode that top 36c and the 36d of ditch portion replace mutually forms wavy.
Thus, when protuberance 36 and abutting part 21c butt, form only the top 36c of protuberance 36 and the state of bearing surface 21c1 butt, in the part of the 36d of ditch portion, and abutting part 21c between guarantee clearance C.
Promptly, the area of contact of protuberance 36 and abutting part 21c is restricted, the surface friction drag that bears from these contact interfaces is little, therefore, pump impeller 20 and turbine 30 do not form lockup state, and can rotate relatively reliably, therefore, can be as patent documentation 1 disclosed fluid torque converter, it is difficult that the control that locking is gone on foot constantly becomes.
In addition, under the state of protuberance 36 and abutting part 21c butt, even pump case 21 and turbine case 31 relative rotations, the oil in the body shell 2 also can be reciprocal between space S 1 and space S 2 by clearance C, and therefore, bearing surface 21c1 is lubricated reliably.
At this, when whole of protuberance 36 contacted with bearing surface 21c1, pump case 21 was not supplied with enough oil (oil) to the contact interface of protuberance 36 and bearing surface 21c1 during with turbine case 31 relative rotations.Therefore, can cause metal of the same race is that pump case 21 and turbine case 31 burn out.
On the other hand, as the enforcement mode, protuberance 36 forms when wavy, when rotation relatively, because of the contact interface of protuberance 36 and abutting part 21c is suitably lubricated, therefore can suitably prevent to burn out.
In mode of execution example make the peripheral part 31c of turbine case 31 crooked and form protuberance 36, and the situation of integrally formed protuberance 36 and turbine case 31, but also protuberance and turbine case 31 splits ground can be formed, for example wait protuberance with ring-type to be installed on the outer circumferential face of peripheral part 31c of turbine case 31 by welding.
Claims (2)
1. the shell construction of a fluid torque converter, in this fluid torque converter, pump impeller and turbine can be provided with on coaxial with the relative rotation, in the body shell that pump case and protecgulum by described pump impeller form, the turbine case of described turbine is provided with predetermined distance with respect to described pump case, it is characterized in that
Periphery at described turbine case is provided with to the side-prominent protuberance of described pump case.
2. the shell construction of fluid torque converter as claimed in claim 1 is characterized in that,
Described protuberance spreads all over the full week of described turbine case periphery and is provided with,
Described protuberance form wavy with opposing side described pump case.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009222612A JP2011069464A (en) | 2009-09-28 | 2009-09-28 | Shell structure of torque converter |
| JP222612/09 | 2009-09-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN102032331A true CN102032331A (en) | 2011-04-27 |
Family
ID=43885620
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010102883491A Pending CN102032331A (en) | 2009-09-28 | 2010-09-19 | Shell structure of torque converter |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP2011069464A (en) |
| KR (1) | KR20110034551A (en) |
| CN (1) | CN102032331A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104755813A (en) * | 2012-10-04 | 2015-07-01 | 舍弗勒技术股份两合公司 | Turbine piston propulsion path |
| CN105156630A (en) * | 2015-07-06 | 2015-12-16 | 金钟吉 | Torque converter |
| CN105593569A (en) * | 2013-11-28 | 2016-05-18 | 株式会社F.C.C. | Lock-up device and torque converter |
| CN106461046A (en) * | 2014-05-07 | 2017-02-22 | 舍弗勒技术股份两合公司 | Centering column for positioning hub |
| CN106641167A (en) * | 2015-08-28 | 2017-05-10 | 卡特彼勒公司 | Torque converter and a method for cooling a clutch assembly of the torque converter |
| CN109906326A (en) * | 2016-11-28 | 2019-06-18 | 舍弗勒技术股份两合公司 | Torque converter with finger-tab brazed inertia ring |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010033552A1 (en) * | 2010-08-05 | 2012-02-09 | Daimler Ag | converter device |
| JP2016160989A (en) * | 2015-02-27 | 2016-09-05 | 株式会社エクセディ | Torque converter |
| WO2017105481A1 (en) | 2015-12-18 | 2017-06-22 | Schaeffler Technologies AG & Co. KG | Reduced volume torque converter having inverted cover closure |
| KR102270690B1 (en) * | 2019-11-13 | 2021-06-28 | 주식회사 카펙발레오 | One-way clutch, method for manufacturing and installing the same and torque converter comprising the same |
| KR102423616B1 (en) * | 2020-11-20 | 2022-07-22 | 큐빅스테크 주식회사 | Toque converter with wobble prevention structure of turbine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2841262A (en) * | 1952-05-16 | 1958-07-01 | Borg Warner | Clutch |
| JP3651751B2 (en) * | 1998-08-06 | 2005-05-25 | 株式会社エクセディ | Torque converter |
| JP2009185912A (en) * | 2008-02-06 | 2009-08-20 | Toyota Motor Corp | Torque converter |
-
2009
- 2009-09-28 JP JP2009222612A patent/JP2011069464A/en active Pending
-
2010
- 2010-09-16 KR KR1020100090848A patent/KR20110034551A/en not_active Application Discontinuation
- 2010-09-19 CN CN2010102883491A patent/CN102032331A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104755813A (en) * | 2012-10-04 | 2015-07-01 | 舍弗勒技术股份两合公司 | Turbine piston propulsion path |
| CN105593569A (en) * | 2013-11-28 | 2016-05-18 | 株式会社F.C.C. | Lock-up device and torque converter |
| CN105593569B (en) * | 2013-11-28 | 2018-04-17 | 株式会社F.C.C. | Locking device and torque-converters |
| CN106461046A (en) * | 2014-05-07 | 2017-02-22 | 舍弗勒技术股份两合公司 | Centering column for positioning hub |
| CN106461046B (en) * | 2014-05-07 | 2019-09-24 | 舍弗勒技术股份两合公司 | Centering column for positioning hub |
| CN105156630A (en) * | 2015-07-06 | 2015-12-16 | 金钟吉 | Torque converter |
| CN106641167A (en) * | 2015-08-28 | 2017-05-10 | 卡特彼勒公司 | Torque converter and a method for cooling a clutch assembly of the torque converter |
| CN106641167B (en) * | 2015-08-28 | 2021-12-03 | 卡特彼勒公司 | Torque converter and method for cooling a clutch assembly of a torque converter |
| CN109906326A (en) * | 2016-11-28 | 2019-06-18 | 舍弗勒技术股份两合公司 | Torque converter with finger-tab brazed inertia ring |
| CN109906326B (en) * | 2016-11-28 | 2022-10-11 | 舍弗勒技术股份两合公司 | Torque converter with finger-tab brazed inertia ring |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011069464A (en) | 2011-04-07 |
| KR20110034551A (en) | 2011-04-05 |
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Application publication date: 20110427 |