CN103244579A - One-way clutch - Google Patents
One-way clutch Download PDFInfo
- Publication number
- CN103244579A CN103244579A CN2012104829861A CN201210482986A CN103244579A CN 103244579 A CN103244579 A CN 103244579A CN 2012104829861 A CN2012104829861 A CN 2012104829861A CN 201210482986 A CN201210482986 A CN 201210482986A CN 103244579 A CN103244579 A CN 103244579A
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- cam
- ring
- inner ring
- cage
- rotation
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- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The present invention provides a one way clutch that is miniature, is large in torque and excellent in production rate. The one way clutch comprises an outer ring (12), an inner ring (20) and a cam retaining rack (30). The cam retaining rack (30) comprises a pair of isolating rings (32, 32), and blocking parts (32a) used for stopping the rotation of cams (38) are integrally formed on the isolating rings, so that the number of the parts can be reduced, the space of the cam retaining rack in the circumferential direction is guaranteed, and the cams (38) can be added.
Description
Technical field
The present invention relates to a kind of centrifugal force pull-up formula (lift-offtype) overrunning clutch.
Background technique
Centrifugal force pull-up formula overrunning clutch (below, sometimes abbreviate " overrunning clutch " as) possess inner ring, be installed on the cam retainer (cam cage) of inner ring, by cam (cam) and outer ring that cam retainer axle supports, wherein inner ring and cam retainer constitute in the mode of equidirectional rotation.When assembling during overrunning clutch, a plurality of cams of being turned round the helical spring application of force contact in the mode of the inner peripheral surface of the outer circumferential face that is squeezed in inner ring and outer ring.If be linked to one of them direction rotation of driving axial of inner ring, then cam skids at the inner peripheral surface of outer ring, so inner ring can dally with respect to the outer ring.And, if the driving axial equidirectional rotates at a high speed, then the centrifugal force mode of being turned round helical spring application of force direction with antagonism acts on the cam center of gravity, this cam center of gravity is positioned at the position at the axle center of off-axis supporting cam wheel, and to surpass the mode effect of its elastic force, thereby cam is rotated, between the inner peripheral surface of the outer circumferential face of cam and inner ring and outer ring, produce the gap, therefore do not produce friction between the inner peripheral surface of the outer circumferential face of cam and inner ring and outer ring, thereby inner ring dallies with respect to the outer ring.At this moment, can keep on the position of contactless state with the outer circumferential face of inner ring and the inner peripheral surface of outer ring at cam, the rotation portion of being blocked of cam stops.And cam is subjected to being turned round the helical spring application of force, therefore when live axle slowly runs or stop operating, returns the state when assembling.On the other hand, if live axle is desired to opposite spin, then cam is because of the friction between itself and the outer ring inner peripheral surface, be subjected to the torque (torque) with force application component application of force direction equidirectional, cam further is squeezed in the outer circumferential face of inner ring and the inner peripheral surface of outer ring, and therefore the torque from live axle is passed to the outer ring by the friction between cam and inner ring outer circumferential face and the outer ring inner peripheral surface via inner ring and cam.Below, for convenience of explanation, the situation of torque from the inner ring biography to the outer ring being called " conducting (on) state ", the situation that inner ring is dallied with respect to the outer ring is called " disconnecting (off) state ".
The effect of this centrifugal force pull-up formula overrunning clutch is divided into two kinds substantially.First kind of purposes is: inner ring is connected in live axle, the outer ring is connected in driven shaft, be on state when turning round usually, and carry out the transmission of torque to the outer ring from inner ring, on the other hand, when the live axle that is connected in inner ring reverses or the driven shaft that is connected in the outer ring when being in out-of-limit (overrun) state, form off state, so that can not transmitting torque between inner ring and the outer ring.In addition, second kind of purposes is: inner ring is connected in mechanical live axle, the outer ring is fixed in the mode that can not rotate, and live axle is rotated under off state, on the other hand, when live axle stops, forming on state, prevent the counter-rotating of the live axle that caused by external force thus.Can enumerate the use-case that makes of Ski Lift or slope conveyor (conveyor) as object lesson.
For centrifugal force pull-up formula overrunning clutch, when live axle carries out high speed when rotating under off state, between cam and outer ring inner face and inner ring outside, produce the gap by centrifugal force, therefore can prevent from being caused by the friction of cam, outer ring and inner ring wearing and tearing, sintering, in addition, compare with this other overrunning clutchs of roller free wheel (roller free wheel), it has allows the big advantage of torque (below, abbreviate " allowing torque " sometimes as) under the on state.
As the example of this centrifugal force pull-up formula overrunning clutch, can enumerate following example.
The prior art document
Patent documentation
Patent documentation 1: the spy opens clear 49-13551 communique
Patent documentation 2: the spy opens flat 9-151964 communique
Summary of the invention
Invent problem to be solved
For the overrunning clutch in the patent documentation 1,2, since be used for to prevent latching that the cam when live axle rotates at a high speed under off state rotates or block axis need with the corresponding quantity of each cam, therefore not only can increase the parts number of packages, increase manufacturing expense, and have problems in increase and the weightization in miniaturization, installation and maintenance man-hour.And not only camshaft is used the hole, and latching or block axis also must be located at the cam retainer with the hole, therefore need bore a hole processing and chamfering operation.Especially, the chamfering operation of disk shaped part once can only be finished one, therefore can spend processing charges and time.In addition, as described in patent documentation 2, rotation arranges independently separately with latching and cam retainer synchronously, therefore causes the increase of parts number of packages, causes the main cause of problem as mentioned above thereby become.
But the contacted total length in cam and inner ring and outer ring is more long, allows that torque is just more big.Therefore, by increasing cam quantity or increasing cam width, can increase and allow torque.But, if merely increase cam width, then can increase the axial dimension of overrunning clutch, in addition, even want to increase cam quantity, if the parts number of packages is many, then need to hold the space of each parts, therefore and can not guarantee the space for increasing cam, not increase size and increase and allow that torque is inconvenient.
Therefore, the present invention is in view of above-mentioned the problems of the prior art, and it is a kind of small-sized and allow the overrunning clutch that torque is big, productivity is good that its purpose is to provide.
The scheme of dealing with problems
The present invention solves above-mentioned problem by following overrunning clutch, it is characterized in that, possesses:
The outer ring;
Inner ring, it has two parallel annular slots at outer circumferential face;
Back-up ring, it is rabbeted at described annular slot;
The cam retainer, it constitutes by a pair of cage ring, and this cage ring is set up in parallel on the outer circumferential face of the described inner ring between the described annular slot, and keeps certain intervals by a plurality of latchings;
The cam that is supported by described cam retainer and turned round helical spring is describedly turned round direction that helical spring engages with described inner ring and from outer ring to this cam to this cam application of force;
Rotate synchronous portion, it is located at described cage ring, is used for keeping the rotation of described inner ring and described cam retainer synchronous, and engages with described back-up ring;
Stop part, itself and described cage ring are integrally formed, and are used for preventing the rotation of described cam.
In addition, preferably, the synchronous portion of described rotation and described cage ring are integrally formed, and with described latching double as stop part.
The invention effect
According to the present invention, because stop part and cage ring are integrally formed, this stop part is used for preventing the cam when live axle rotates at a high speed under off state to rotate, and does not therefore need as the prior art and cage ring independent and latching or the block axis of formation mutually.Thus, compared with prior art, because the parts number of packages tails off, therefore can reduce manufacturing expense, can assemble easily or safeguard, further help light.In addition, meanwhile, owing to need not to use the hole at cam retainer processing latching or block axis, therefore can realize the reduction of machining period, expense and time.In addition, no longer need the latching or the block axis that form separately, can dwindle the distance between the cam thus, thereby can increase cam quantity.Therefore, can be to realize allowing the increase of torque less than the axial dimension of prior art.
And then, if it is integrally formed for the synchronous portion of rotation rotation synchronous, that engage with back-up ring that keeps inner ring and cam retainer in cage ring, then need not to be formed for the latching of the rotation of synchronous inner ring and cam retainer in addition as the prior art, so can obtain effect same as described above.In addition, if adopt structure with latching double as stop part, then need not stop part to be set being provided with the latching place, therefore can reduce machining period.
Description of drawings
Fig. 1 is the plan view of the overrunning clutch of expression first embodiment of the invention.
Fig. 2 is the sectional arrangement drawing along the 2-2 line of Fig. 1.
Fig. 3 is for the helical spring plan view of being turned round of overrunning clutch.
Fig. 4 is the plan view when the inner ring of the overrunning clutch of first embodiment of the invention is equipped with the cam retainer.
Fig. 5 is the plan view (fragmentary cross-sectional view) of cam retainer of the overrunning clutch of first embodiment of the invention.
Fig. 6 is the enlarged view of the A of Fig. 5.
Fig. 7 is the enlarged view of the B of Fig. 5.
Fig. 8 is the major component enlarged view (fragmentary cross-sectional view) of cam retainer of the overrunning clutch of second embodiment of the invention.
Fig. 9 is the major component enlarged view (fragmentary cross-sectional view) of cam retainer of the overrunning clutch of third embodiment of the invention.
Figure 10 is the view (fragmentary cross-sectional view) of the cam retainer of existing overrunning clutch.
Figure 11 is the figure of the axial dimension of comparison overrunning clutch of the present invention and existing overrunning clutch.
Description of reference numerals
10 overrunning clutchs
12 outer rings
20 inner rings
The outer circumferential face of 24 inner rings
26 annular slots
28 back-up rings
The engagement portion of 28a back-up ring
30 cam retainers
32 cage rings
The 32a stop part
32b rotates synchronous portion
All side recesses in the 32c
32d outer circumferential side recess
34 latchings
38 cams
39 are turned round helical spring
Embodiment
Below, describe referring to figs. 1 through 11 pairs of embodiment of the present invention.But the present invention is not limited to this embodiment.
As shown in Figure 1, the overrunning clutch 10 of first embodiment of the invention possesses outer ring 12, inner ring 20 and cam retainer 30.In addition, in Fig. 1, omitted the detailed icon of cam retainer 30.Inner ring 20 has axis hole 22, and live axle (omitting diagram) is inserted in this axis hole 22, and it forms the key connection thus.In addition, certainly, the method beyond also can connecting by key links live axle and inner ring 20.On the other hand, outer ring 12 or be connected in driven shaft (omit diagram) or be fixed in the mode that can not rotate.
Fig. 2 is the sectional arrangement drawing along the 2-2 line of Fig. 1.Cam retainer 30 is between outer ring 12 and inner ring 20.Cam retainer 30 constitutes as follows: make cage ring 32,32 keep certain interval with latching 34, described cage ring 32,32 is set up in parallel on the outer circumferential face 24 between 20 liang of parallel annular slots 26 of inner ring, 26.In cage ring 32,32 many places (being three places among Fig. 4) latching 34 is installed with bolt 35,35, in addition, embed installation back-up ring 28,28 at the annular slot 26 that is formed at inner ring 20,26, stop cam retainer 30 in axial movement thus, thereby cam retainer 30 is installed breaking away from ground from inner ring 20.In addition, cage ring 32 is not limited to make by cutting from iron, steel, by punch process make also can, in addition, as long as satisfy intensity, can also use non-steel materials such as engineering plastics resins such as (engineering plastic) or aluminium.
In addition, cam retainer 30 possesses the direction that engages with inner ring 20 and outer ring 12 by the cam 38 of cage ring 32,32 supports with to this cam 38 these cam 38 application of forces is turned round helical spring 39, during assembling, by being turned round the active force that helical spring 39 cams 38 are subjected to being squeezed in the inner peripheral surface 14 of the outer circumferential face 24 of inner ring 20 and outer ring 12.In addition, the back shaft 36 of cam 38 is members of perforation cam 38 as shown in Figure 2, first outside, can also be integrally formed as pivot (trunnion) and cam 38.In addition, turned round helical spring 39 and be the shape shown in Fig. 3 (a), and have the structure that a coil portion 39a is positioned at cam one side sidepiece, and turned round helical spring 39c but also can have shown in use Fig. 3 (b), make two coil portion 39d, 39d be positioned at the structure of cam both sides sidepiece.In addition, the method for being turned round helical spring 39 that at a place have coil portion 39a of use shown in (a) can be guaranteed the space between the cage ring 32,32, and be therefore preferred.For example, being turned round helical spring 39 is stuck in the card that is arranged at all sides in the cage ring 32 with one side end 39b and ends with recess 32e(with reference to Fig. 5), and end side 39b is stuck in cam 38, the direction that engages with inner ring 20 and outer ring 12 to cam 38 is to cam 38 application of forces thus.On the other hand, for example, being turned round the card that helical spring 39c is stuck in its end 39e, 39e the cage ring 32 of adjacency ends with recess 32e(with reference to Fig. 5), and joint 39f is stuck in cam, the direction that engages with inner ring 2 and outer ring 12 to cam 38 is to cam 38 application of forces thus.
Secondly, as shown in Figure 2, back-up ring 28,28 is installed in the mode that is closely attached on annular slot 26 by its elasticity.At this moment, as shown in Figure 4, the engagement portion of back-up ring 28 28a be provided with form one with cage ring 32 and to annular slot 26(with reference to Fig. 2) the synchronous 32b of portion of rotation of direction bending, if therefore inner ring 20 rotations, then the engagement portion 28a of back-up ring 28 contacts with the synchronous 32b of portion of rotation, and the torque with inner ring 20 equidirectionals passes to cam retainer 30 thus.In addition, rotate the synchronous 32b of portion integrally formed with cage ring 32 as described above after, form by it is become to the processing mode of the outstanding projection of annular slot 26, in addition, in integrally formed with cage ring 32 just so that it becomes to form to the mode of the outstanding projection of annular slot 26 also can.In addition, the engagement portion 28a that rotates between the synchronous 32b of portion and the back-up ring 28 is not limited to as the grooving portion under back-up ring 28 situations, as long as the synchronous 32b of portion of rotation can be sticked in back-up ring, can change according to the shape of back-up ring.In addition, with regard to cam retainer 30, as shown in Figure 5, rotate the synchronous 32b of portion can be in being arranged at cage ring 32 interior all side recess 32c place of all sides arrange, and with in a pair of cage ring 32,32 at least one to annular slot 26 bendings.Like this, by all side recess 32c in arranging, can realize the light of cage ring 32.In addition, according to the shape of back-up ring, cage ring 32 can adopt the structure that a plurality of interior all side recess 32c, the synchronous 32b of portion of rotation are set.
In addition, be provided with outer circumferential side recess 32d with cam 38 equal numbers at the outer circumferential side of cage ring 32, be provided with the stop part 32a of overshooting shape at outer circumferential side recess 32d.The stop part 32a of at least one cage ring 32 in a pair of cage ring 32,32 is to cam 38 bendings.Like this, by outer circumferential side recess 32d is set, can realize the light of cage ring 32.In addition, after stop part 32a is integrally formed with cage ring 32 as mentioned above, form by it is become to the processing mode of the outstanding projection of cam 38 directions, in addition, in integrally formed with cage ring 32 just so that it becomes to form to the mode of the outstanding projection of cam 38 also can.
As mentioned above, cam 38 is subjected to therefore becoming the A condition of Fig. 5 to the active force of inner ring 20 and outer ring 12 engaging directions when assembling by turning round helical spring 39, namely is squeezed in the state of outer ring 12 inner peripheral surfaces 14 and inner ring 20 outer circumferential faces 24.Fig. 6 is the part enlarged view of the A condition of presentation graphs 5.The center of gravity G of cam 38 is positioned at the position of departing from back shaft 36 centers, and cam 38 is by being turned round the active force that helical spring 39 is subjected to the anticlockwise direction.When not shown live axle carries out anticlockwise, the also torque of transmitting the anticlockwise directions to inner ring 20 and cam retainer 30.At this moment, the size of cam 38 is set as from assembling and the time begins the form of only rotating to a direction (right rotation direction), in addition, because contact with the inner peripheral surface 14 of outer ring 12, therefore pass through the friction of 14 of cam 38 and outer ring 12 inner peripheral surfaces, desire sense of rotation rotation to the right centered by back shaft 36.Thereby 12 inner peripheral surface 14 skids cam 38 in the outer ring, so be off state when the live axle anticlockwise.
On the other hand, shown in the arrow of Fig. 6, when live axle carried out right rotation, cam 38 contacted with outer ring 12 inner peripheral surfaces 14, thus desire by its with the inner peripheral surface 14 of outer ring 12 between friction sense of rotation rotation left centered by back shaft 36.Therefore, cam 38 can further be squeezed in outer ring 12 inner peripheral surfaces 14 and inner ring 20 outer circumferential faces 24 and be rotated, so be on state when the live axle right rotation.
Secondly, live axle carries out high speed when rotating under off state, and cam 38 is the B state of Fig. 5.Fig. 7 is the part enlarged view of this B state.If live axle carries out high speed rotation, then the centrifugal force of F direction to be surpassing the center of gravity G that the elastic force of being turned round helical spring 39 acts on cam 38, thus cam 38 until with rotate till stop part 32a contacts.At this moment, between cam 38 and inner ring 20 outer circumferential faces 24 and and outer ring 12 inner peripheral surfaces 14 between produce the gap.Therefore, cam 38 does not contact with inner ring 20 outer circumferential faces 24 and outer ring 12 inner peripheral surfaces 14, thereby can prevent the heating that caused by these frictions, and can prevent wearing and tearing, the sintering of parts.In addition, cam 38 is by being turned round the active force that helical spring 39 is subjected to the 12 engaging directions to inner ring 20 and outer ring, so during the rotation low speed of live axle or when stopping, returning state shown in Figure 6.
As shown in Figure 8, will be turned round helical spring 39(with reference to Fig. 3 (a) if adopt) a side end 39b be stuck in the structure of stop part 32a, then need not to arrange card and end with recess 32e(with reference to Fig. 4), so can reduce machining period and expense.In addition, also can will fix by being wound in methods such as stop part 32a at a side end 39b who is turned round helical spring 39.In addition, when use is turned round helical spring 39c(with reference to Fig. 3 (b)) time, its end 39e, 39e can be stuck in stop part 32a.
In addition, as shown in Figure 9, if employing then need not the structure of latching 34 double as stop part 32a in the part with latching 34 stop part 32a to be set, therefore can reduce machining period and expense.In addition, also can be stuck in the structure of stop part 32a and with the textural association of latching 34 double as stop part 32a, at this moment, can will be turned round helical spring end and be stuck in latching 34 being turned round helical spring end.
Secondly, Figure 10 is the plan view (fragmentary cross-sectional view) of the cam retainer 130 of the existing overrunning clutch shown in patent documentation 2.The diameter of cam retainer 130 is identical with cam retainer 30 shown in Figure 4.Cam retainer 130 possesses: latching 134, and it is fixed in cage ring 132 by back shaft 136, flush bolt 135; Rotation is synchronously with latching 131, and it is sticked in the engagement portion of back-up ring (omitting diagram) as the synchronous portion of rotation.Cam 138 is had coil portion 139a, 139a(with reference to Figure 11 at Liang Chu) turned round helical spring 139 application of forces, the joint of being turned round helical spring 139 is stuck in cam 138, end 139b is stuck in latching 134.
Secondly, Figure 11 is the figure that relatively has cam retainer 130 and the axial dimension of cam retainer 30 of the present invention, 30a now.In addition, in existing cam retainer 130, the flush bolt head that is arranged at cage ring 128 is embedded in cage ring 128, on the other hand, in cam retainer 30 of the present invention, 30a, bolt 35 heads are positioned at the outside of cage ring 28,28a, therefore to the axial dimension that comprises cage ring 128,128 cam retainer 130 and comprise the cam retainer 30 of bolt 35 heads, the axial dimension of 30a compares.Herein, (a) expression has cam retainer 130 now; (b) expression use cage ring thickness, cam width and quantity and the coil portion identical with (a) is a situation of being turned round helical spring 39; (c) be illustrated on the basis of (b) structure, set up a cam, and make cam and the total length of inner ring outer circumferential face or the contact of outer ring inner peripheral surface and (a) identical situation; Thin-walled property and coil portion were a situation of being turned round helical spring 39 more when (d) expression was used cam width and the quantity identical with (a) and made cage ring than (a); (e) be illustrated on the basis of (d) structure, set up a cam, and make cam and the total length of inner ring outer circumferential face or the contact of outer ring inner peripheral surface and (a) identical situation.
Under (b) situation, can guarantee the space of the 139a of twist coil portion of (a); (c) situation is based on (b) situation, when setting up a cam 39, can correspondingly reduce the axial dimension of each cam 39.In addition, (d) situation is based on (b) situation, when making cage ring 28a thin-walled property, can correspondingly guarantee the space; (e) situation is based on (d) situation, when setting up a cam 39, can correspondingly reduce the axial dimension of each cam 39.Therefore, if the axial dimension of the cam retainer integral body of Figure 11 (a) to (e) is made as A, B, C, D, E, A＞B＞C＞D＞E then.Therefore, by adopting structure of the present invention, compared with prior art can realize miniaturization or allow the increase of torque, and if then use the cage ring 28a of thin-walled, then can further realize miniaturization or allow the increase of torque.
As described above, according to the present invention, by cutting down the parts number of packages, can guarantee the space of cam retainer on Zhou Fangxiang of overrunning clutch, and can set up cam, therefore a kind of miniaturization can be provided and allow the overrunning clutch that torque is big, productivity is good.
Claims (3)
1. overrunning clutch is characterized in that possessing:
The outer ring;
Inner ring, it has two parallel annular slots at outer circumferential face;
Back-up ring, it is rabbeted at described annular slot;
The cam retainer, it constitutes by a pair of cage ring, and this cage ring is set up in parallel on the outer circumferential face of the described inner ring between the described annular slot, and keeps certain intervals by a plurality of latchings;
The cam that is supported by described cam retainer and turned round helical spring is describedly turned round direction that helical spring engages with described inner ring and from outer ring to this cam to this cam application of force;
Rotate synchronous portion, it is located at described cage ring, is used for keeping the rotation of described inner ring and described cam retainer synchronous, and engages with described back-up ring;
Stop part, itself and described cage ring are integrally formed, and are used for preventing the rotation of described cam.
2. the described overrunning clutch of claim 1, wherein, the synchronous portion of described rotation and described cage ring are integrally formed.
3. claim 1 or 2 described overrunning clutchs, wherein, with the described stop part of described latching double as.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012020866A JP5858530B2 (en) | 2012-02-02 | 2012-02-02 | One-way clutch |
| JP2012-020866 | 2012-02-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103244579A true CN103244579A (en) | 2013-08-14 |
| CN103244579B CN103244579B (en) | 2017-03-01 |
Family
ID=48924330
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210482986.1A Active CN103244579B (en) | 2012-02-02 | 2012-11-23 | One-way clutch |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP5858530B2 (en) |
| CN (1) | CN103244579B (en) |
| BR (1) | BR102012029703B1 (en) |
| TW (1) | TWI570336B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112406777A (en) * | 2020-11-19 | 2021-02-26 | 东风汽车有限公司 | Actively controlled belt clutch and actively controlled belt system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6084189B2 (en) * | 2014-09-11 | 2017-02-22 | パンパシフィック・カッパー株式会社 | Positioning mechanism of electrode plate transfer device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09151964A (en) * | 1995-11-30 | 1997-06-10 | Tsubakimoto Emason:Kk | Lift-off type one-way clutch, and motor with lift-off type one-way clutch |
| US20110278124A1 (en) * | 2008-11-10 | 2011-11-17 | Schaeffler Technologies Gmbh & Co. Kg | Clamping element freewheel |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1915567B2 (en) * | 1969-03-27 | 1972-03-16 | Ringspann Albrecht Maurer Kg, 6380 Bad Homburg | FREE WHEEL COUPLING WITH CLAMPING PIECES |
| DE2214840C3 (en) * | 1972-03-27 | 1981-03-26 | Stieber Antriebselemente GmbH, 68775 Ketsch | One-way clutch with sprags |
| DE2361916C2 (en) * | 1973-12-13 | 1975-03-06 | Stieber Division Der Borg-Warner Gmbh, 6900 Heidelberg | Sprag overrunning clutch |
| DE3229685C1 (en) * | 1982-08-10 | 1983-11-03 | Ringspann Albrecht Maurer Kg, 6380 Bad Homburg | Clamping body cage ring for one-way clutches |
| DE3313639A1 (en) * | 1983-04-15 | 1984-10-18 | INA Wälzlager Schaeffler KG, 8522 Herzogenaurach | KAEFIG FOR A CLAMP ROLLER FREEWHEEL |
| JPH08291832A (en) * | 1995-04-21 | 1996-11-05 | Koyo Seiko Co Ltd | One way clutch |
| WO2011038707A2 (en) * | 2009-09-29 | 2011-04-07 | Schaeffler Technologies Gmbh & Co. Kg | Freewheel, in particular for permanently meshed starters |
-
2012
- 2012-02-02 JP JP2012020866A patent/JP5858530B2/en active Active
- 2012-11-14 TW TW101142363A patent/TWI570336B/en active
- 2012-11-22 BR BR102012029703-5A patent/BR102012029703B1/en active IP Right Grant
- 2012-11-23 CN CN201210482986.1A patent/CN103244579B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09151964A (en) * | 1995-11-30 | 1997-06-10 | Tsubakimoto Emason:Kk | Lift-off type one-way clutch, and motor with lift-off type one-way clutch |
| US20110278124A1 (en) * | 2008-11-10 | 2011-11-17 | Schaeffler Technologies Gmbh & Co. Kg | Clamping element freewheel |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112406777A (en) * | 2020-11-19 | 2021-02-26 | 东风汽车有限公司 | Actively controlled belt clutch and actively controlled belt system |
| CN112406777B (en) * | 2020-11-19 | 2022-05-27 | 东风汽车有限公司 | Actively controlled belt clutch and actively controlled belt system |
Also Published As
| Publication number | Publication date |
|---|---|
| TW201335503A (en) | 2013-09-01 |
| BR102012029703A2 (en) | 2015-01-06 |
| BR102012029703B1 (en) | 2021-06-15 |
| BR102012029703A8 (en) | 2018-02-14 |
| CN103244579B (en) | 2017-03-01 |
| TWI570336B (en) | 2017-02-11 |
| JP5858530B2 (en) | 2016-02-10 |
| JP2013160266A (en) | 2013-08-19 |
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