CN105221595A - A kind of automotive transmission sprag clutch - Google Patents
A kind of automotive transmission sprag clutch Download PDFInfo
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- CN105221595A CN105221595A CN201510764197.0A CN201510764197A CN105221595A CN 105221595 A CN105221595 A CN 105221595A CN 201510764197 A CN201510764197 A CN 201510764197A CN 105221595 A CN105221595 A CN 105221595A
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- inner ring
- retainer
- maintenance support
- support body
- fenestra
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Abstract
The present invention relates to a kind of automotive transmission sprag clutch, comprise outer shroud (1), inner ring (2), outer retainer (3), interior retainer (4), sway brace (5), spring (6), oil baffle (7), elastic collar (8) and one grade of gear needle bearing assembly (9), it is characterized in that: the overall structure that described outer shroud (1) is formed in one; The overall structure that described inner ring (2) is formed in one; The left end of the annular fitting recess (12) of described outer shroud (1) is provided with axially recessed and suitable with the outer contour shape size of the flange plate (40) of interior retainer (4) the left groove of annular (11) left, and the flange plate (40) of described interior retainer (4) is assemblied in annular left groove (11).The present invention has that wearing and tearing are less, working life is higher, manufacture difficulty and lower-cost beneficial effect.
Description
Technical field
The present invention relates to automotive transmission, be specifically related to a kind of automotive transmission sprag clutch.
Background technique
The collective friction element being called sway brace is depended in the work of sprag clutch, and its relies on sway brace wedging between inner and outer rings to be used for transmitting torque.Basic sprag clutch is primarily of compositions such as outer shroud, inner ring, sway brace in groups, interior retainer, outer retainer and springs.Sway brace is the load bearing element of transmitting torque, and inside and outside retainer keeps the radial location mode of certain interval to realize leading role by its flange plate respectively with inner and outer rings, keeps sway brace phase place when carrying consistent, thus makes carrying evenly.The Main Function of spring is that sway brace and inside and outside ring moment are kept in touch, and ensures that clutch is at any time from surmounting status transition to wedging state.
Sprag clutch involved by patent document CN201010599537.6, see Fig. 1, its outer shroud and inner ring all adopt split-type structural.Outer shroud is divided into the first outer ring body 14 and the second outer ring body 15, first outer ring body 14 and the second outer ring body 15 by interference fit and welds together, and its outer shroud does not have annular left groove; Inner ring is divided into the first inner ring body 20 and the second inner ring body 21, first inner ring body 20 and the second inner ring body 21 by together with spline fitted; The flange plate 40 of interior retainer 4 is shorter, and therefore, retainer 4 heat treatment hardness can not be too high, and the too high meeting of hardness causes heat treatment deformation large.The flange plate 40 of interior retainer 4 is directly radially positioned on the second inner ring body 21.In adopting, retainer 4 keeps the radial location mode of certain interval can bring following problem by its flange plate 40 and the second inner ring body 21.Because retainer under surmounting state in the limit and inner ring relative rotation speed can up to 13000rpm, so this radial location mode easily causes to occur between the flange plate 40 of interior retainer 4 and the second inner ring body 21 that mutual serious wear, life-span are lower.Because inner ring adopts split-type structural, the first inner ring body 20 and the second inner ring body 21 by together with spline fitted, can cause the very poor and respective circularity of the coaxality between the flange plate 40 of interior retainer 4 and the second inner ring body 21 or cylindricity overproof; Because outer shroud adopts split-type structural, first outer ring body 14 and the second outer ring body 15 are by interference fit and weld together, pilot hole 10 can be caused and annular fitting recess 12 coaxality is very poor, serious wear, life-span are lower, so under High Rotation Speed outer shroud and the dynamic unbalance of sprag clutch assembly serious; And flange plate 40 heat treatment hardness of interior retainer 4 is not high; The mutual rotation between the flange plate 40 of interior retainer 4 and the second inner ring body 21 finally can be caused dumb and wear and tear will be very serious, even occur that the second inner ring body 21 is cut into deep trouth by the flange plate 40 of interior retainer 4.The flange plate 40 of interior retainer 4 can be caused after heavy wear to lose leading role, each sway brace 5 carry time phase place by inconsistent, thus make carrying uneven.Sway brace 5 serious wear or sway brace 5 extruding finally can be caused to break the situation appearance of forfeiture sprag clutch effects such as rupture with the languid 60 of spring 6, more serious situation is that the metal fillings that sprag clutch damages flows to each position of speed changer inside with fluid, causes the inefficacy of other component.Showing at car load is that speed changer loses the function of transferring power and occurs serious abnormal sound.
Sprag clutch involved by patent document CN200820041855.9, see Fig. 2, in it, the flange plate 40 of retainer 4 is shorter, and two, left and right annular end cap 16 is buckled on interior retainer 4 and outer retainer 3.The flange plate 40 of interior retainer 4 is radially positioned on annular end cap 16, though there is the situation of mutually wearing and tearing between the flange plate 40 of the interior retainer 4 that this orientation type sprag clutch avoided involved by patent document CN201010599537.6 occurs and the second inner ring body 21, and there is mutually wearing and tearing by between the flange plate 40 of interior retainer 4 and the second inner ring body 21 series of problems caused.But two of this structure annular end caps 16 belong to thin-wall part, easily cause distortion in the comparatively large and transportation process of Pressing Deformation, thus in impact, the location of the flange plate 40 of retainer 4, sprag clutch rotate and can not well play the guiding role with regard to dumb and annular end cap 16.For ensureing the gap between two annular end caps 16 and the second inner ring body 21, the flange plate 40 of interior retainer 4 just does shorter, and so, retainer heat treatment deformation can increase, and therefore flange surface circularity is just very poor.Therefore this design is wayward to two gaps between annular end cap and inner ring.If gap is too small, heat just can not well be discharged with fluid; If excesssive gap, lubricant oil just well can not form oil film; Annular end cap brings the problem that cost compare is high and manufacture difficulty is larger simultaneously.
Summary of the invention
The technical problem to be solved in the present invention is to provide that a kind of wearing and tearing are less, working life is higher, manufacture difficulty and lower-cost automotive transmission sprag clutch.
For solving the problems of the technologies described above, the present invention takes following technological scheme;
A kind of automotive transmission sprag clutch, comprises outer shroud, inner ring, outer retainer, interior retainer, sway brace, spring, oil baffle, elastic collar and one grade of gear needle bearing assembly;
Described outer shroud comprises left and right mutually through pilot hole and annular fitting recess, and the aperture of described pilot hole is less than the aperture of annular fitting recess, and the right-hand member of described annular fitting recess is provided with the annular snap ring recess that aperture is greater than the aperture of annular fitting recess;
Described inner ring comprises left and right the first inner ring body arranged side by side and the second inner ring body, the external diameter of described first inner ring body is less than the external diameter of the second inner ring body, and the external diameter of described second inner ring body is less than the aperture of the annular fitting recess of outer shroud, is greater than the aperture of the left groove of annular of outer shroud;
Described outer retainer entirety is ring bodies, comprise outer maintenance support body and respectively by 20 °, circumferential interval, by 90 °, circumferential interval and the fenestra be located at spaced reciprocally on this outer maintenance support body and elasticity seam, described fenestra is through hole, and described elasticity seam is raised up by outer maintenance support body;
Described interior retainer entirety is ring bodies, comprise interior maintenance support body, be located at the cooperation fenestra on this interior maintenance support body by 20 °, circumferential interval and be connected to the flange plate of this interior maintenance support body left end, the cooperation fenestra on described maintenance support body is corresponding with the fenestra on outer maintenance support body;
Described sway brace is the irregular quadrilateral voussoir shape that relative dual-side concaves; Described spring comprises spring body and with this spring body one and the languid corresponding with the fenestra on outer maintenance support body;
Described outer shroud is loaded in inner ring, and its pilot hole and annular fitting recess are corresponding with the first inner ring body of inner ring and the second inner ring body respectively, and fit in the left side of the second inner ring body of the right side of its annular fitting recess and inner ring;
Described interior retainer and outer retainer are arranged between the annular fitting recess of outer shroud and the second inner ring body of inner ring from the inside to the outside, all be provided with a sway brace in each cooperation fenestra of described interior retainer and each fenestra of outer retainer, described outer retainer passes through its elasticity seam elastic conjunction on the annular fitting recess of outer shroud;
The spring body circumference of described spring is wound on the periphery of interior maintenance support body of interior retainer, and radial direction is between interior retainer and outer retainer, and its languid is also against on sway brace to resiliently deformable by the fenestra on outer maintenance support body to individual stretching out;
Described oil baffle is axially between the outer maintenance support body and elastic collar of outer retainer, and described elastic collar is assemblied in the annular snap ring recess of outer shroud right-hand member;
Described one grade of gear needle bearing general assembly is in inner ring and between first inner ring body and the pilot hole of outer shroud of inner ring, it is characterized in that:
The left end of the annular fitting recess of described outer shroud is provided with axially recessed and suitable with the outer contour shape size of the flange plate of the interior retainer left groove of annular left, and the flange plate of described interior retainer is assemblied in annular left groove.
Preferably, the overall structure that is formed in one of described outer shroud.
Preferably, the overall structure that is formed in one of described inner ring.
Preferably, be located at fenestra on outer maintenance support body described in and outer maintenance support body integrated punching shaping.
Preferably, be located at elasticity seam on outer maintenance support body described in and outer maintenance support body integrated punching shaping.
Preferably, be located at cooperation fenestra on interior maintenance support body described in and interior maintenance support body integrated punching shaping.
Compared with prior art, the present invention comprises following beneficial effect;
Left end due to the annular fitting recess 12 of outer shroud of the present invention is provided with axially recessed and suitable with the outer contour shape size of the flange plate of the interior retainer left groove of annular left, the flange plate of described interior retainer is assemblied in annular left groove, namely adopts annular left groove to realize radial location to flange plate.The flange plate which solves interior retainer in prior art is radially positioned in the low cooperation fenestra of serious wear and interior retainer between the flange plate of interior retainer and the second inner ring body of inner ring that causes of interior retainer heat treatment hardness existing on the second inner ring body of inner ring and is subject to sway brace 5 extrusion-deformation large, the flange plate wearing and tearing of interior retainer and the extrusion-deformation of cooperation fenestra cause greatly sway brace phase place when carrying inconsistent, the problem that coaxality between the flange plate of interior retainer and the second inner ring body of inner ring not easily ensures, and in solving in prior art the flange plate of retainer to be radially positioned in manufacture cost existing on annular end cap high, the problem that manufacture difficulty is large.As can be seen here, the present invention wear and tear less, working life is higher, manufacture difficulty and cost lower.
Accompanying drawing explanation
Fig. 1 is the structural representation of the sprag clutch involved by patent document CN201010599537.6;
Fig. 2 is the structural representation of the sprag clutch involved by patent document CN200820041855.9;
Fig. 3 is structural representation of the present invention;
Fig. 4 is the structural representation that outer retainer 3 of the present invention and interior retainer 4 are assembled together.
In figure, outer shroud 1, inner ring 2, outer retainer 3, interior retainer 4, sway brace 5, spring 6, oil baffle 7, elastic collar 8, one grade of gear needle bearing assembly 9, pilot hole 10, annular left groove 11, annular fitting recess 12, annular snap ring recess 13, first inner ring body 20, second inner ring body 21, elasticity seam 30, outer maintenance support body 31, fenestra 32, flange plate 40, interior maintenance support body 41, cooperation fenestra 42, languid 60, spring body 61.
Embodiment
Below in conjunction with the drawings and specific embodiments, the present invention is described in further detail;
See Fig. 3 and Fig. 4, automotive transmission sprag clutch of the present invention, comprises outer shroud 1, inner ring 2, outer retainer 3, interior retainer 4, sway brace 5, spring 6, oil baffle 7, elastic collar 8 and one grade of gear needle bearing assembly 9; Described outer shroud 1 comprises left and right mutually through pilot hole 10 and annular fitting recess 12, the aperture of described pilot hole 10 is less than the aperture of annular fitting recess 12, and the right-hand member of described annular fitting recess 12 is provided with the annular snap ring recess 13 that aperture is greater than the aperture of annular fitting recess 12; Described inner ring 2 comprises left and right one the first inner ring body 20 and the second inner ring body 21 arranged side by side, the external diameter of described first inner ring body 20 is less than the external diameter of the second inner ring body 21, and the external diameter of described second inner ring body 21 is less than the aperture of the annular fitting recess 12 of outer shroud 1, is greater than the aperture of the left groove 11 of annular of outer shroud 1; Described outer retainer 3 entirety is ring bodies, comprise outer maintenance support body 31 and respectively by 20 °, circumferential interval, by 90 °, circumferential interval and the fenestra 32 be located at spaced reciprocally on this outer maintenance support body 31 and elasticity seam 30, described fenestra 32 is through hole, and described elasticity seam 30 is raised up by outer maintenance support body 31; Described interior retainer 4 entirety is ring bodies, comprise interior maintenance support body 41, be located at the cooperation fenestra 42 on this interior maintenance support body 41 by 20 °, circumferential interval and be connected to the flange plate 40 of this interior maintenance support body 41 left end, the cooperation fenestra 42 on described maintenance support body 41 is corresponding with the fenestra 32 on outer maintenance support body 31; Described sway brace 5 is the irregular quadrilateral voussoir shape that relative dual-side concaves; Described spring 6 comprises spring body 61 and with this spring body 61 one and the languid 60 corresponding with the fenestra 32 on outer maintenance support body 31; Described outer shroud 1 is loaded in inner ring 2, and its pilot hole 10 and annular fitting recess 12 are corresponding with the first inner ring body 20 of inner ring 2 and the second inner ring body 21 respectively, and fit in the left side of the second inner ring body 21 of the right side of its annular fitting recess 12 and inner ring 2; Described interior retainer 4 and outer retainer 3 are arranged between the annular fitting recess 12 of outer shroud 1 and the second inner ring body 21 of inner ring 2 from the inside to the outside, all be provided with a sway brace 5 in each cooperation fenestra 42 of described interior retainer 4 and each fenestra 32 of outer retainer 3, described outer retainer 3 passes through its elasticity seam 30 elastic conjunction on the annular fitting recess 12 of outer shroud 1; Spring body 61 circumference of described spring 6 is wound on the periphery of interior maintenance support body 41 of interior retainer 4, and radial direction is between interior retainer 4 and outer retainer 3, its languid 60 is also against on sway brace 5 to resiliently deformable by the fenestra 32 on outer maintenance support body 31 to individual stretching out; Described oil baffle 7 is axially between the outer maintenance support body 31 and elastic collar 8 of outer retainer 3, and described elastic collar 8 is assemblied in the annular snap ring recess 13 of outer shroud 1 right-hand member; Described one grade of gear needle bearing assembly 9 to be assemblied in inner ring 2 and between first inner ring body 20 and the pilot hole 10 of outer shroud 1 of inner ring 2: as seen from Figure 3, the overall structure that outer shroud 1 of the present invention is formed in one; The overall structure that described inner ring 2 is formed in one; The left end of the annular fitting recess 12 of described outer shroud 1 is provided with axially recessed and suitable with the outer contour shape size of the flange plate 40 of the interior retainer 4 left groove 11 of annular left, and the flange plate 40 of described interior retainer 4 is assemblied in annular left groove 11.Therefore, the present invention adopts annular left groove 11 pairs of flange plate 40 to achieve radial location.The flange plate 40 which solves interior retainer 4 in prior art is radially positioned in the low cooperation fenestra 42 of serious wear and interior retainer 4 between the flange plate 40 of interior retainer 4 and the second inner ring body 21 of inner ring 2 that causes of interior retainer 4 heat treatment hardness existing on the second inner ring body 21 of inner ring 2 and is subject to sway brace 5 extrusion-deformation large, the flange plate 40 of interior retainer 4 weares and teares and coordinates fenestra 42 extrusion-deformation to cause greatly sway brace 5 phase place when carrying inconsistent, the problem that coaxality between the flange plate 40 of interior retainer 4 and the second inner ring body 21 of inner ring 2 not easily ensures, and in solving in prior art the flange plate 40 of retainer 4 to be radially positioned in manufacture cost existing on the annular end cap 16 shown in accompanying drawing 3 high, the problem that manufacture difficulty is large.As can be seen here, the present invention wear and tear less, working life is higher, manufacture difficulty and cost lower.
As seen from Figure 3, the overall structure that is formed in one of described outer shroud 1.Which solves that the soldering reliability of prior art outer-loop 1 existing for split-type structural is low, spline joint precision is low, the pilot hole of outer shroud 1 10 be poor with annular fitting recess 12 coaxality, the problem of sway brace 5 serious wear.
As seen from Figure 3, the overall structure that is formed in one of described inner ring 2.Which solves that the soldering reliability of prior art inner ring 2 existing for split-type structural is low, spline joint precision is low, the pilot hole of outer shroud 1 10 be poor with annular fitting recess 12 coaxality, the problem of sway brace 5 serious wear.
The described fenestra 32 be located on outer maintenance support body 31 is shaping with outer maintenance support body 31 integrated punching.Avoiding problems and rush frame that fenestra 32 brings and the large problem of heat treatment deformation again processing outer maintenance support body 31, effectively can control the accuracy of manufacturing of fenestra 32.
The described elasticity seam 30 be located on outer maintenance support body 31 is shaping with outer maintenance support body 31 integrated punching.Avoiding problems and rush frame that elasticity seam 30 brings and the large problem of heat treatment deformation again processing outer maintenance support body 31, effectively can control the accuracy of manufacturing of elasticity seam 30.
The described cooperation fenestra 42 be located on interior maintenance support body 41 is shaping with interior maintenance support body 41 integrated punching.Avoiding problems and rush frame that fenestra 42 brings and the large problem of heat treatment deformation again processing outer maintenance support body 41, effectively can control the accuracy of manufacturing of fenestra 42.
Working principle of the present invention is as follows:
When the turn clockwise rotating speed of rotating speed higher than inner ring 2 that turn clockwise of outer shroud 1; Under the influence of centrifugal force, a few sway braces 5 overcome the elastic force of spring 6 and throw off the second inner ring body 21 of inner ring 2 before this.A few the sway braces 5 of first throwing off inner ring 2 second inner ring body 21 promote interior retainer 4 around annular left groove 11 center line of outer shroud 1 and rotate, now the left groove 11 of annular of the flange plate 40 of interior retainer 4 just outer ring 1 realizes leading role, and interior retainer 4 promotes again to remain sway brace 5 to start to rotate around its rotating center.Under the effect of thrust and centrifugal force, residue sway brace 5 also overcomes the elastic force of spring 6 and throws off the second inner ring body 21 of inner ring 2.After throwing off the second inner ring body 21 of inner ring 2, the wedging height of sway brace 5 is less than the height of radial gap between the second inner ring body 21 of inner ring 2 and the annular fitting recess 12 of outer shroud 1, so sprag clutch is just in surmount state.
When the turn clockwise rotating speed of rotating speed higher than outer shroud 1 that turn clockwise of described inner ring 2; Because the rotating speed of outer shroud 1 reduces, centrifugal action weakens, and under the spring-force driven dual of spring 6, sway brace 5 starts to be fitted on the second inner ring body 21 of inner ring 2.Before this under the second inner ring body 21 of inner ring 2 and the frictional force effect of a few sway braces 5, sway brace 5 rotated around its rotating center.A few the sway braces 5 first rotated promote interior retainer 4 around annular left groove 11 center line of outer shroud 1 and rotate, now the left groove 11 of annular of the flange plate 40 of interior retainer 4 just outer ring 1 realizes leading role, and interior retainer 4 promotes again to remain sway brace 5 to start to rotate around its rotating center.At the second inner ring body 21 of thrust and inner ring 2 with under the effect of the frictional force of sway brace 5, the wedging height of sway brace 5 is greater than the second inner ring body 21 of inner ring 2 and the height of radial gap of the annular fitting recess 12 of outer shroud 1 between installation sprag clutch place, so sprag clutch is just in wedging state.
Kinetic current under wedging state is as follows: kinetic current is inputted by inner ring 2, by sway brace 5 wedge action between the annular fitting recess 12 and the second inner ring body 21 of inner ring 2 of outer shroud 1, frictional force between second inner ring body 21 of inner ring 2 and sway brace 5 is delivered on sway brace 5, be delivered on outer shroud 1 by the frictional force between the annular fitting recess 12 of outer shroud 1 and sway brace 5 again, eventually through outer shroud 1, transmission of power gone out.
Claims (6)
1. an automotive transmission sprag clutch, comprises outer shroud (1), inner ring (2), outer retainer (3), interior retainer (4), sway brace (5), spring (6), oil baffle (7), elastic collar (8) and one grade of gear needle bearing assembly (9);
Described outer shroud (1) comprises left and right mutually through pilot hole (10) and annular fitting recess (12), the aperture of described pilot hole (10) is less than the aperture of annular fitting recess (12), and the right-hand member of described annular fitting recess (12) is provided with the annular snap ring recess (13) that aperture is greater than the aperture of annular fitting recess (12);
Described inner ring (2) comprises left and right the first inner ring body (20) arranged side by side and the second inner ring body (21), the external diameter of described first inner ring body (20) is less than the external diameter of the second inner ring body (21), and the external diameter of described second inner ring body (21) is less than the aperture of the annular fitting recess (12) of outer shroud (1), is greater than the aperture of the left groove of annular (11) of outer shroud (1);
Described outer retainer (3) entirety is ring bodies, comprise outer maintenance support body (31) and respectively by 20 °, circumferential interval, by 90 °, circumferential interval and the fenestra (32) be located at spaced reciprocally on this outer maintenance support body (31) and elasticity seam (30), described fenestra (32) is through hole, and described elasticity seam (30) is raised up by outer maintenance support body (31);
Described interior retainer (4) entirety is ring bodies, comprise interior maintenance support body (41), be located at the cooperation fenestra (42) on this interior maintenance support body (41) by 20 °, circumferential interval and be connected to the flange plate (40) of this interior maintenance support body (41) left end, the cooperation fenestra (42) on described maintenance support body (41) is corresponding with the fenestra (32) on outer maintenance support body (31);
The irregular quadrilateral voussoir shape that described sway brace (5) concaves for relative dual-side; Described spring (6) comprises spring body (61) and with this spring body (61) one and the languid (60) corresponding with the fenestra (32) on outer maintenance support body (31);
Described outer shroud (1) is loaded in inner ring (2), its pilot hole (10) and annular fitting recess (12) are corresponding with first inner ring body (20) of inner ring (2) and the second inner ring body (21) respectively, and fit in the left side of second inner ring body (21) of the right side of its annular fitting recess (12) and inner ring (2);
Described interior retainer (4) and outer retainer (3) are arranged between the annular fitting recess (12) of outer shroud (1) and second inner ring body (21) of inner ring (2) from the inside to the outside, in each cooperation fenestra (42) of described interior retainer (4) and each fenestra (32) of outer retainer (3), a sway brace (5) is all installed, described outer retainer (3) by its elasticity seam (30) elastic conjunction on the annular fitting recess (12) of outer shroud (1);
Spring body (61) circumference of described spring (6) is wound on the periphery of interior maintenance support body (41) of interior retainer (4), and radial direction is positioned between retainer (4) and outer retainer (3), its languid (60) is also against on sway brace (5) to resiliently deformable by the fenestra (32) on outer maintenance support body (31) to individual stretching out;
Described oil baffle (7) is axially positioned between the outer maintenance support body (31) of outer retainer (3) and elastic collar (8), and described elastic collar (8) is assemblied in the annular snap ring recess (13) of outer shroud (1) right-hand member;
Described one grade of gear needle bearing assembly (9) is assemblied in inner ring (2) and goes up and be positioned between first inner ring body (20) of inner ring (2) and the pilot hole (10) of outer shroud (1), it is characterized in that:
The left end of the annular fitting recess (12) of described outer shroud (1) is provided with axially recessed and suitable with the outer contour shape size of the flange plate (40) of interior retainer (4) the left groove of annular (11) left, and the flange plate (40) of described interior retainer (4) is assemblied in annular left groove (11).
2., according to all automotive transmission sprag clutches stated of claim 1, it is characterized in that: the overall structure that described outer shroud (1) is formed in one.
3., according to all automotive transmission sprag clutches stated of claim 1, it is characterized in that: the overall structure that described inner ring (2) is formed in one.
4., according to all automotive transmission sprag clutches stated of claim 1, it is characterized in that: described in be located at fenestra (32) on outer maintenance support body (31) shaping with outer maintenance support body (31) integrated punching.
5., according to all automotive transmission sprag clutches stated of claim 1, it is characterized in that: described in be located at elasticity seam (30) on outer maintenance support body (31) shaping with outer maintenance support body (31) integrated punching.
6. all automotive transmission sprag clutches stated any one of claim 1 to 5, is characterized in that: described in be located at cooperation fenestra (42) on interior maintenance support body (41) shaping with interior maintenance support body (41) integrated punching.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510764197.0A CN105221595B (en) | 2015-11-11 | 2015-11-11 | A kind of automotive transmission sprag clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510764197.0A CN105221595B (en) | 2015-11-11 | 2015-11-11 | A kind of automotive transmission sprag clutch |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105221595A true CN105221595A (en) | 2016-01-06 |
| CN105221595B CN105221595B (en) | 2018-05-08 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510764197.0A Active CN105221595B (en) | 2015-11-11 | 2015-11-11 | A kind of automotive transmission sprag clutch |
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| Country | Link |
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| CN (1) | CN105221595B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0341082A2 (en) * | 1988-05-06 | 1989-11-08 | Dana Corporation | Hydraulically actuated release mechanism for a clutch |
| CN1264652A (en) * | 1998-12-18 | 2000-08-30 | 易通公司 | Automatic regulating friction clutch with torsional spring casing |
| CN2600644Y (en) * | 2003-02-18 | 2004-01-21 | 兰永福 | Freewheel clutch with double-retainer deformed wedge |
| CN201953978U (en) * | 2011-04-18 | 2011-08-31 | 重庆阿尔迪机电技术开发有限公司 | Electromagnetically controlled overrunning clutch gear-shifting device |
| CN102278394A (en) * | 2011-07-21 | 2011-12-14 | 西南大学 | Bearing type overrunning clutch |
| CN203713411U (en) * | 2013-12-09 | 2014-07-16 | 杭州萧山鼎立机械有限公司 | Hub unit preloaded by double-arc riveting structure |
| CN104806630A (en) * | 2015-04-13 | 2015-07-29 | 卢雨 | Rolling bearing and assembling tool thereof |
| CN205190564U (en) * | 2015-11-11 | 2016-04-27 | 重庆青山工业有限责任公司 | Automotive transmission bracing clutch |
-
2015
- 2015-11-11 CN CN201510764197.0A patent/CN105221595B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0341082A2 (en) * | 1988-05-06 | 1989-11-08 | Dana Corporation | Hydraulically actuated release mechanism for a clutch |
| CN1264652A (en) * | 1998-12-18 | 2000-08-30 | 易通公司 | Automatic regulating friction clutch with torsional spring casing |
| CN2600644Y (en) * | 2003-02-18 | 2004-01-21 | 兰永福 | Freewheel clutch with double-retainer deformed wedge |
| CN201953978U (en) * | 2011-04-18 | 2011-08-31 | 重庆阿尔迪机电技术开发有限公司 | Electromagnetically controlled overrunning clutch gear-shifting device |
| CN102278394A (en) * | 2011-07-21 | 2011-12-14 | 西南大学 | Bearing type overrunning clutch |
| CN203713411U (en) * | 2013-12-09 | 2014-07-16 | 杭州萧山鼎立机械有限公司 | Hub unit preloaded by double-arc riveting structure |
| CN104806630A (en) * | 2015-04-13 | 2015-07-29 | 卢雨 | Rolling bearing and assembling tool thereof |
| CN205190564U (en) * | 2015-11-11 | 2016-04-27 | 重庆青山工业有限责任公司 | Automotive transmission bracing clutch |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105221595B (en) | 2018-05-08 |
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