CN104358797B - Engagement overdrive clutch - Google Patents
Engagement overdrive clutch Download PDFInfo
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- CN104358797B CN104358797B CN201410565181.2A CN201410565181A CN104358797B CN 104358797 B CN104358797 B CN 104358797B CN 201410565181 A CN201410565181 A CN 201410565181A CN 104358797 B CN104358797 B CN 104358797B
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- outer shroud
- internal ring
- tooth bar
- planetary gear
- planet carrier
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Abstract
The present invention provides a kind of engagement overdrive clutch, and it is made up of parts such as internal ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5) and planetary gears (6).When internal ring (1) is in synchronous regime with outer shroud (2), moment therebetween is transmitted by pitch wheel, can transmit larger torque；When internal ring (1) and outer shroud (2) are in and surmount state, planetary gear dallies, without sliding wear parts.The roller-type overrunning clutch being widely used at present and Wedge type over running clutch are all dependent on friction transmission moment, have transmission moment little, and contact stress is big, the shortcoming that service life is short.Compared with traditional roller-type overrunning clutch and Wedge type over running clutch, engagement overdrive clutch have low cost of manufacture, transmission moment big, the advantage such as element without sliding wear, long service life, it is particularly well-suited to internal combustion engine start machine, construction machinery gear box, and some other needs the occasion of double dynamical driving.
Description
Technical field
The present invention relates to mechanical transmission fields, be specifically related to a kind of high pulling torque, long-life freewheel clutch.
Background technology
Freewheel clutch as a kind of basic transmission parts, be widely used in mechanical engineering field.Freewheel clutch is mainly used in the drive system of the double; two turbo-power manual transmissions used by internal combustion engine start machine, pulse-type continuously variable transmission, loader, hybrid vehicle, and needs double dynamical driving or the occasion of double speed driving.
The freewheel clutch being widely used at present mainly has roller-type overrunning clutch and Wedge type over running clutch two types.Due to transmission mechanism, the freewheel clutch of both types is difficult to meet the requirement that modern industry is increasingly higher to engineering goods.
Roller-type overrunning clutch is made up of main parts size such as internal ring, outer shroud, rollers, different by version, is divided into again spring top pin and holder-type two kinds.Roller is all that higher pair contacts with internal ring and outer shroud, relies on the friction transmission moment between roller and inner and outer rings, there is contact stress big, the shortcoming that transmission moment of torsion is little.Additionally, the requirement that roller-type overrunning clutch is to manufacturing and install is all significantly high.For making roller uniform force, the diameter error of the multiple rollers in same freewheel clutch controls within 0.005mm, needs when assembling roller measurement packet；The internal ring of roller-type overrunning clutch complex-shaped, processes relatively difficult.During roller-type overrunning clutch work, easily produce abrasion between roller and internal ring, outer shroud, retainer or ejector pin, have a strong impact on service life.For freewheel clutch used by the dynamic power shift gear box of wheel loader; its service life is generally 2000 hours; being significantly less than gear-driven service life, the main forms of its inefficacy is: roller by conquassation or be ground into dolioform, retainer heavy wear or break, spring and ejector pin lost efficacy, internal ring serious wear or collapse tooth.Freewheel clutch is the parts that Wheel type loader transmission case the most easily breaks down, and it has become as the bottleneck improving the Wheel type loader transmission case life-span.
Wedge type over running clutch is made up of parts such as internal ring, outer shroud, voussoir and shading rings.Compared with roller Overloading clutch, Wedge type over running clutch voussoir replaces roller, and bearing capacity increases.But, Wedge type over running clutch remains the moment frictionally transmitting between inner and outer ring, it does not have fundamentally solve the deficiency that contact stress is big, transmission moment is little.After Wedge type over running clutch abrasion, automatic compensation ability is poor.In the case of an overload, it is possible to have one or several voussoir to rotate more than maximum support line scope, make internal ring and outer shroud stuck, can not reset when moment reduces back wedge.
Owing to the constraint of transmission mechanism, roller-type overrunning clutch and Wedge type over running clutch are difficult to meet the needs of modern mechanical industry.In the plant equipment such as engineering machinery, aero-engine, automatic gear-box, in the urgent need to can transmitting large torque, there is long-life freewheeling clutch.
Summary of the invention
It is an object of the invention to overcome the deficiency of roller-type overrunning clutch and Wedge type over running clutch, it is provided that a kind of high pulling torque, long-life freewheeling clutch.The technological means that the present invention adopts is as follows: changes the mode relying on friction transmission moment of roller-type overrunning clutch and Wedge type over running clutch, replaces frictional drive by meshed transmission gear, control the state of freewheel clutch with pinion and rack.
For realizing goal of the invention, the technical solution used in the present invention is: engagement overdrive clutch is made up of internal ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5) and planetary gear (6) etc., it is characterized in that: the dead in line of internal ring (1) and outer shroud (2), they can only make the circular motion rotated around the axis of self；The reference circle of planetary gear (6) is tangent with the reticule of tooth bar (4)；Internal ring (1) and outer shroud (2) can not only be used for planet carrier, again can as centre wheel, and when internal ring (1) is as planet carrier, outer shroud (2) is as centre wheel, when internal ring (1) is as centre wheel, outer shroud (2) as planet carrier；Planetary gear (6) and guide rail (3) are all arranged on planet carrier；Planetary gear (6) can rotate around the axis of its own, but can not opposing rows carrier move；Guide rail (3) is fixed on planet carrier, and it and planet carrier can not relative motioies；Tooth bar (4) is arranged on guide rail (3), tooth bar (4) can opposite rail (3) for linear motion, direction of relative movement is parallel with the reticule direction of tooth bar (4)；Spring (5) is compression type springs, and its one end contacts with guide rail (3), and the other end contacts with tooth bar (4), and the active force of tooth bar (4) is made tooth bar (4) close to the axis of planet carrier by spring (5)；Guide rail (3), tooth bar (4), spring (5), planetary gear (6) quantity all no less than two, they are circumferentially uniformly distributed.
Accompanying drawing explanation
Fig. 1 is the synchronous regime of embodiment 1.
Fig. 2 be embodiment 1 surmount state.
Fig. 3 is the synchronous regime of embodiment 2.
Fig. 4 be embodiment 2 surmount state.
Detailed description of the invention
Engagement overdrive clutch of the present invention has two kinds of versions: outer shroud is the first structure as planet carrier, and internal ring is the second structure as planet carrier.The first structure correspondence embodiment 1, the second structure correspondence embodiment 2.The detailed description of the invention of engagement overdrive clutch is now described for embodiment 1.
As it is shown in figure 1, engagement overdrive clutch is made up of main parts size such as internal ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5), planetary gears (6).Outer shroud (2) is as planet carrier, and guide rail (3), tooth bar (4), spring (5), planetary gear (6) are all located on outer shroud (2), and their quantity is all 3, is circumferentially uniformly distributed.Internal ring (1) be shaped as an external gear, it all keeps normal meshing relation with 3 planetary gears (6).
The dead in line of internal ring (1) and outer shroud (2), they can only make the circular motion rotated around own axes.Guide rail (3) is fixed on outer shroud (2), can not relative motion between it and outer shroud (2).Tooth bar (4) is arranged on guide rail (3), and it can go up for linear motion by opposite rail (3).The movement limit of tooth bar (4) in certain scope, and is ensured that the reticule of tooth bar (4) is tangent with the reference circle of planetary gear (6) by guide rail (3).In the range of movement of tooth bar (4), when tooth bar (4) from the distance of the axis of outer shroud (2) maximum time, tooth bar (4) location is remote stop；When tooth bar (4) from the distance of the axis of outer shroud (2) minimum time, tooth bar (4) location is nearly stop.Spring (5) is compression spring, and its one end contacts with guide rail (3), and the other end contacts with tooth bar (4), and in an initial condition, spring (5) pushes tooth bar (4) to nearly dead-centre position.Planetary gear (6) can not move relative to outer shroud (2), but can rotate around the axis of its own.Planetary gear (6) has two kinds of motions, and it is rotation around the rotary motion of the axis of self, and it is revolution with the rotation of outer shroud (2).
As shown in Figure 1, assume that internal ring (1) rotates clockwise relative to outer shroud (2), under the drive of internal ring (1), planetary gear (6) rotates counterclockwise around the axis of its own, planetary gear (6) band carry-over bar (4) moves to nearly stop, when tooth bar (4) arrives nearly stop, tooth bar (4) can not be moved by guide rail (3) restriction, so that planetary gear (6) can not rotation, cause that internal ring (1) can not rotate relative to outer shroud (2), internal ring (1) is made to turn clockwise with identical angular velocity with outer shroud (2), planetary gear (6) is revolution only, there is no rotation.The synchronous regime that state is engagement overdrive clutch when internal ring (1) is identical with the angular velocity of outer shroud (2).When synchronizing, internal ring (1) is delivered to the moment of outer shroud (2) and is transmitted by gear, and gear institute is loaded for dead load, it is possible to transmit bigger moment.
As shown in Figure 2, assuming that internal ring (1) rotates counterclockwise relative to outer shroud (2), under the drive of internal ring (1), planetary gear (6) rotates around the axis both clockwise of its own, planetary gear (6) band carry-over bar (4) moves to remote stop, and spring (5) is compressed.When tooth bar (4) is disengaged from planetary gear (6), planetary gear (6) dallies under the effect of internal ring (1) and outer shroud (2), and internal ring (1) and outer shroud (2) do not interfere with each other, and are now in surmounting state.When surmounting, the existing rotation of motion of planetary gear (6) has again revolution.
When surmounting state, owing to tooth bar (4) is promoted by spring (5) to nearly stop, planetary gear (6) and tooth bar (4) can collide, and this situation is disadvantageous.When surmounting state, outer shroud (2) generally makes rotation status, tooth bar (4) rotates with outer shroud (2), the centrifugal force of available tooth bar (4) overcomes the elastic force of spring (5), tooth bar (4) is made to be maintained at remote stop, avoid planetary gear (6) and tooth bar (4) to come in contact, eliminate collision and the abrasion of the two, so that engagement overdrive clutch has very long service life.
Engagement overdrive clutch of the present invention is particularly well-suited to the occasions such as the starter motor of internal combustion engine, construction machinery gear box.Illustrate that it is applied for Fig. 1, by internal ring (1) with start motor be connected, outer shroud (2) is connected with the bent axle of internal combustion engine, startup stage, driven by motor internal combustion engine rotation, engagement type Overloading clutch is in synchronous regime；After startup completes, internal combustion engine self starts to rotate, and the rotating speed of outer shroud (2) is more than the rotating speed of internal ring (1), and engagement type Overloading clutch is in and surmounts state.When knowing the working speed of internal combustion engine, correctly design the elastic force of spring (5) and the quality of tooth bar (4), tooth bar (4) can be made to overcome the elastic force of spring (5) to be in remote dead-centre position under the influence of centrifugal force, it is to avoid planetary gear (6) and tooth bar (4) collide.
Fig. 3 and Fig. 4 is the another embodiment of engagement overdrive clutch of the present invention, and in this embodiment, internal ring (1) serves as planet carrier, outer shroud (2) be shaped as internal gear, Fig. 3 is synchronous regime, and Fig. 4 is for surmounting state.Its work process is similar with embodiment 1, no longer describes at this.
Claims (4)
1. engagement overdrive clutch, it is made up of internal ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5) and planetary gear (6), it is characterized in that: the dead in line of internal ring (1) and outer shroud (2), they can only make the circular motion rotated around the axis of self；The reference circle of planetary gear (6) is tangent with the reticule of tooth bar (4)；Internal ring (1) and outer shroud (2) can not only be used for planet carrier, again can as centre wheel, and when internal ring (1) is as planet carrier, outer shroud (2) is as centre wheel, and when internal ring (1) is as centre wheel, outer shroud (2) is as planet carrier；Planetary gear (6) and guide rail (3) are all arranged on planet carrier；Planetary gear (6) can rotate around the axis of its own, but can not opposing rows carrier move；Guide rail (3) is fixed on planet carrier, and it and planet carrier can not relative motioies；Tooth bar (4) is arranged on guide rail (3), tooth bar (4) can opposite rail (3) for linear motion, direction of relative movement is parallel with the reticule direction of tooth bar (4)；Spring (5) is compression type springs, and its one end contacts with guide rail (3), and the other end contacts with tooth bar (4), and the active force of tooth bar (4) is made tooth bar (4) close to the axis of planet carrier by spring (5)；Guide rail (3), tooth bar (4), spring (5), planetary gear (6) quantity all no less than two, they are circumferentially uniformly distributed.
2. engagement overdrive clutch according to claim 1, it is characterised in that: if outer shroud (2) is as planet carrier, be shaped as external gear, internal ring (1) and the planetary gear (6) of internal ring (1) keep normal meshing relation.
3. engagement overdrive clutch according to claim 1, it is characterised in that: if internal ring (1) is as planet carrier, be shaped as internal gear, outer shroud (2) and the planetary gear (6) of outer shroud (2) keep normal meshing relation.
4. engagement overdrive clutch according to claim 1, it is characterised in that: when planetary gear (6) by tooth bar (4) constraint can not time rotational, internal ring (1) and outer shroud (2) can not relative motion, engagement overdrive clutch is in synchronous regime；When planetary gear (6) can time rotational, internal ring (1) and outer shroud (2) can produce relative motion, and engagement overdrive clutch is in and surmounts state.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410565181.2A CN104358797B (en) | 2014-10-22 | 2014-10-22 | Engagement overdrive clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410565181.2A CN104358797B (en) | 2014-10-22 | 2014-10-22 | Engagement overdrive clutch |
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| Publication Number | Publication Date |
|---|---|
| CN104358797A CN104358797A (en) | 2015-02-18 |
| CN104358797B true CN104358797B (en) | 2016-07-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410565181.2A Active CN104358797B (en) | 2014-10-22 | 2014-10-22 | Engagement overdrive clutch |
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Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL233394B1 (en) * | 2015-11-18 | 2019-10-31 | Efneo Spolka Z Ograniczona Odpowiedzialnoscia | Freewheel mechanism |
| CN109519487A (en) * | 2017-09-19 | 2019-03-26 | 周承岗 | Fluted disc freewheel clutch |
| CN107965532B (en) * | 2017-10-24 | 2023-07-07 | 四川大学 | Non-friction overrunning clutch |
| CN113531001B (en) * | 2021-06-29 | 2022-08-02 | 温岭市广达电磁科技有限公司 | Overrunning clutch capable of being used for high-torque transmission |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101608677A (en) * | 2009-08-03 | 2009-12-23 | 任寿年 | Adopt the free wheel device of gear-type clutch |
| CN101608676A (en) * | 2009-08-03 | 2009-12-23 | 任寿年 | Gear-type overrunning clutch |
| JP2010032014A (en) * | 2008-07-30 | 2010-02-12 | Masaru Tanabe | Ratchet mechanism, and generator drive device for driving generator |
| CN102401034A (en) * | 2010-09-14 | 2012-04-04 | 何良智 | Electromagnetic tension friction synchronous directly-driven kidney-shaped roller clutch |
| CN103511157A (en) * | 2012-06-27 | 2014-01-15 | 罗伯特·博世有限公司 | Starting device and method therefor |
| CN204200904U (en) * | 2014-10-22 | 2015-03-11 | 四川大学 | Engagement overdrive clutch |
-
2014
- 2014-10-22 CN CN201410565181.2A patent/CN104358797B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010032014A (en) * | 2008-07-30 | 2010-02-12 | Masaru Tanabe | Ratchet mechanism, and generator drive device for driving generator |
| CN101608677A (en) * | 2009-08-03 | 2009-12-23 | 任寿年 | Adopt the free wheel device of gear-type clutch |
| CN101608676A (en) * | 2009-08-03 | 2009-12-23 | 任寿年 | Gear-type overrunning clutch |
| CN102401034A (en) * | 2010-09-14 | 2012-04-04 | 何良智 | Electromagnetic tension friction synchronous directly-driven kidney-shaped roller clutch |
| CN103511157A (en) * | 2012-06-27 | 2014-01-15 | 罗伯特·博世有限公司 | Starting device and method therefor |
| CN204200904U (en) * | 2014-10-22 | 2015-03-11 | 四川大学 | Engagement overdrive clutch |
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| CN104358797A (en) | 2015-02-18 |
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