CN104358797A - Engagement type overrunning clutch - Google Patents
Engagement type overrunning clutch Download PDFInfo
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- CN104358797A CN104358797A CN201410565181.2A CN201410565181A CN104358797A CN 104358797 A CN104358797 A CN 104358797A CN 201410565181 A CN201410565181 A CN 201410565181A CN 104358797 A CN104358797 A CN 104358797A
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- inner ring
- tooth bar
- outer shroud
- planetary pinion
- planet carrier
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Abstract
The invention provides an engagement type overrunning clutch. The clutch consists of an inner ring (1), an outer ring (2), guide rails (3), racks (4), springs (5), planetary gears (6) and other parts, wherein when the inner ring (1) and the outer ring (2) are in a synchronous state, moment between the inner ring (1) and the outer ring (2) is transmitted by the gears which are in intermeshing engagement, and larger moment can be transmitted; when the inner ring (1) and the outer ring (2) are in an overrunning state, the planetary gears idle, and no sliding milling part exists. A roller type overrunning clutch and a wedge block type overrunning clutch which are widely used at present transmit the moment through friction, and have the defects of small transmission moment, large contact stress and short service life. Compared with the traditional roller type overrunning clutch and the wedge block type overrunning clutch, the engagement type overrunning clutch has the advantages of low manufacturing cost, large transmission moment, no sliding milling part, long service life, and the like, and the clutch disclosed by the invention is particularly suitable for internal-combustion engine starting engines, engineering machinery gearboxes, and other occasions requiring two-motor driving.
Description
Technical field
The present invention relates to mechanical transmission fields, be specifically related to a kind of high pulling torque, long-life free wheel device.
Background technique
Free wheel device as a kind of basic transmission parts, be widely used in mechanical engineering field.Free wheel device is mainly used in the transmission system of internal combustion engine start machine, pulse-type continuously variable transmission, loader two turbo-power manual transmissions used, hybrid vehicle, and the occasion needing double dynamical driving or double speed to drive.
The free wheel device of current extensive use mainly contains roller-type overrunning clutch and Wedge type over running clutch two type.Due to transmission mechanism, the free wheel device of this two type is difficult to meet the modern industry requirement more and more higher to engineering goods.
Roller-type overrunning clutch is made up of main parts size such as inner ring, outer shroud, rollers, different by structural type, is divided into again spring top pin and holder-type two kinds.Roller and inner ring and outer shroud are all that higher pair contacts, and rely on the friction carry-over moment between roller and inner and outer rings, there is contact stress large, the shortcoming that transmitting torque is little.In addition, roller-type overrunning clutch is all very high to the requirement manufactured and install.For making roller uniform force, the diameter error of the multiple rollers in same free wheel device controls within 0.005mm, needs to carry out measurement grouping to roller when assembling; The inner ring of roller-type overrunning clutch complex-shaped, processes more difficult.During roller-type overrunning clutch work, roller and easily produce wearing and tearing between inner ring, outer shroud, retainer or ejector pin, has a strong impact on working life.For the dynamic power shift gear box of wheel loader free wheel device used; its working life is generally 2000 hours; be significantly less than gear-driven working life, its main forms lost efficacy is: roller by conquassation be ground into dolioform, retainer heavy wear or break, spring and ejector pin lost efficacy, inner ring serious wear or collapse tooth.Free wheel device is the parts that Wheel type loader transmission case the most easily breaks down, and it has become the bottleneck improving the Wheel type loader transmission case life-span.
Wedge type over running clutch is made up of parts such as inner ring, outer shroud, voussoir and isolating rings.Compared with roller type Overloading clutch, Wedge type over running clutch voussoir replaces roller, and bearing capacity increases.But Wedge type over running clutch remains the moment by rubbing between transmission inside and outside ring, does not fundamentally solve the deficiency that contact stress is large, carry-over moment is little.After Wedge type over running clutch wearing and tearing, auto-compensation ability is poor.In the case of an overload, may have one or several voussoir rotate exceed maximum support line scope, make inner ring and outer shroud stuck, when moment reduce back wedge can not reset.
Due to the constraint of transmission mechanism, roller-type overrunning clutch and Wedge type over running clutch are difficult to the needs meeting modern mechanical industry.In the machinery such as engineering machinery, aeroengine, automatic transmission case, in the urgent need to can transmitting large torque, there is long-life freewheeling clutch.
Summary of the invention
The object of the invention is the deficiency overcoming roller-type overrunning clutch and Wedge type over running clutch, a kind of high pulling torque, long-life freewheeling clutch are provided.The technological means that the present invention adopts is as follows: the mode changing the dependence friction carry-over moment of roller-type overrunning clutch and Wedge type over running clutch, replaces friction driving by meshed transmission gear, control the state of free wheel device 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 inner ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5) and planetary pinion (6) etc., it is characterized in that: the dead in line of inner ring (1) and outer shroud (2), they can only make the circular movement rotated around the axis of self; The standard pitch circle of planetary pinion (6) and the reticule of tooth bar (4) tangent; Inner ring (1) and outer shroud (2) both can be used as planet carrier, can be used as central gear again, when inner ring (1) is as planet carrier, outer shroud (2) as central gear, when inner ring (1) is as central gear, outer shroud (2) as planet carrier; Planetary pinion (6) and guide rail (3) are all arranged on planet carrier; Planetary pinion (6) can rotate around it self axis, but can not opposing rows carrier move; Guide rail (3) is fixed on planet carrier, and it and planet carrier can not relative movement; Tooth bar (4) is arranged on guide rail (3), and tooth bar (4) can opposite rail (3) moving linearly, and 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 spring (5) to tooth bar (4) makes tooth bar (4) close to the axis of planet carrier; The quantity of guide rail (3), tooth bar (4), spring (5), planetary pinion (6) is all no less than two, and they are circumferentially being uniformly distributed.
Accompanying drawing explanation
Fig. 1 is the sync state of embodiment 1.
Fig. 2 be embodiment 1 surmount state.
Fig. 3 is the sync state of embodiment 2.
Fig. 4 be embodiment 2 surmount state.
Embodiment
Engagement overdrive clutch of the present invention has two kinds of structural types: outer shroud is the first structure as planet carrier, and inner ring is the second structure as planet carrier.The corresponding embodiment 1 of the first structure, the corresponding embodiment 2 of the second structure.The embodiment of engagement overdrive clutch is now described for embodiment 1.
As shown in Figure 1, engagement overdrive clutch is made up of main parts size such as inner ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5), planetary pinions (6).Outer shroud (2) is as planet carrier, and guide rail (3), tooth bar (4), spring (5), planetary pinion (6) are all positioned on outer shroud (2), and their quantity is all 3, is circumferentially being uniformly distributed.The shape of inner ring (1) is an external gear, and it and 3 planetary pinions (6) all keep normal meshing relation.
The dead in line of inner ring (1) and outer shroud (2), they can only make the circular movement rotated around own axes.Guide rail (3) is fixed on outer shroud (2), can not relative movement between it and outer shroud (2).Tooth bar (4) is arranged on guide rail (3), and it can the upper moving linearly of opposite rail (3).The movement limit of tooth bar (4) in certain scope, and is ensured that the standard pitch circle of the reticule of tooth bar (4) and planetary pinion (6) is tangent by guide rail (3).In the range of movement of tooth bar (4), when tooth bar (4) is maximum from the distance of the axis of outer shroud (2), the position residing for tooth bar (4) is stop far away; When tooth bar (4) is minimum from the distance of the axis of outer shroud (2), the position residing for tooth bar (4) is nearly stop.Spring (5) is Compress 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 pinion (6) can not move relative to outer shroud (2), but can rotate around it self axis.Planetary pinion (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, suppose that inner ring (1) rotates clockwise relative to outer shroud (2), under the drive of inner ring (1), planetary pinion (6) rotates counterclockwise around it self axis, planetary pinion (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, thus make planetary pinion (6) can not rotation, cause inner ring (1) can not rotate relative to outer shroud (2), inner ring (1) is turned clockwise with identical angular velocity with outer shroud (2), planetary pinion (6) only has revolution, there is no rotation.State when inner ring (1) is identical with the angular velocity of outer shroud (2) is the sync state of engagement overdrive clutch.When synchronous, inner ring (1) is delivered to the moment of outer shroud (2) by gear transmission, and load suffered by gear is static load, can transmit larger moment.
As shown in Figure 2, suppose that inner ring (1) rotates counterclockwise relative to outer shroud (2), under the drive of inner ring (1), planetary pinion (6) rotates around it self axis both clockwise, planetary pinion (6) band carry-over bar (4) moves to stop far away, and spring (5) is compressed.When tooth bar (4) and planetary pinion (6) depart from engage time, planetary pinion (6) dallies under the effect of inner ring (1) and outer shroud (2), and inner ring (1) and outer shroud (2) do not interfere with each other, and are now in and surmount state.When surmounting, the existing rotation of motion of planetary pinion (6) has revolution again.
When surmounting state, because tooth bar (4) promotes to nearly stop by spring (5), planetary pinion (6) and tooth bar (4) can collide, and this situation is disadvantageous.When surmounting state, outer shroud (2) makes rotation status usually, tooth bar (4) rotates with outer shroud (2), the centrifugal force of tooth bar (4) can be utilized to overcome the elastic force of spring (5), tooth bar (4) is made to remain on stop far away, avoid planetary pinion (6) and tooth bar (4) to come in contact, the collision of both eliminations and wearing and tearing, thus make engagement overdrive clutch have very long working life.
Engagement overdrive clutch of the present invention is specially adapted to the occasion such as Starter, construction machinery gear box of internal-combustion engine.Illustrate that it is applied for Fig. 1, inner ring (1) be connected with starting electrical machinery, outer shroud (2) is connected with the bent axle of internal-combustion engine, start up period, driven by motor internal-combustion engine rotate, engagement type Overloading clutch is in sync state; After startup completes, internal-combustion engine self starts to rotate, and the rotating speed of outer shroud (2) is greater than the rotating speed of inner ring (1), and engagement type Overloading clutch is in and surmounts state.When knowing the working speed of internal-combustion engine, the elastic force of correct design spring (5) and the quality of tooth bar (4), tooth bar (4) can be made to overcome the elastic force of spring (5) under the influence of centrifugal force and be in dead-centre position far away, avoid planetary pinion (6) and tooth bar (4) to collide.
Fig. 3 and Fig. 4 is the another one embodiment of engagement overdrive clutch of the present invention, and in this embodiment, inner ring (1) serves as planet carrier, and the shape of outer shroud (2) is internal gear, and Fig. 3 is sync state, and Fig. 4 is for surmounting state.Its working procedure and embodiment's 1 is similar, no longer describes at this.
Claims (4)
1. engagement overdrive clutch is made up of inner ring (1), outer shroud (2), guide rail (3), tooth bar (4), spring (5) and planetary pinion (6) etc., it is characterized in that: the dead in line of inner ring (1) and outer shroud (2), they can only make the circular movement rotated around the axis of self; The standard pitch circle of planetary pinion (6) and the reticule of tooth bar (4) tangent; Inner ring (1) and outer shroud (2) both can be used as planet carrier, can be used as central gear again, when inner ring (1) is as planet carrier, outer shroud (2) as central gear, when inner ring (1) is as central gear, outer shroud (2) as planet carrier; Planetary pinion (6) and guide rail (3) are all arranged on planet carrier; Planetary pinion (6) can rotate around it self axis, but can not opposing rows carrier move; Guide rail (3) is fixed on planet carrier, and it and planet carrier can not relative movement; Tooth bar (4) is arranged on guide rail (3), and tooth bar (4) can opposite rail (3) moving linearly, and 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 spring (5) to tooth bar (4) makes tooth bar (4) close to the axis of planet carrier; The quantity of guide rail (3), tooth bar (4), spring (5), planetary pinion (6) is all no less than two, and they are circumferentially being uniformly distributed.
2. engagement overdrive clutch according to claim 1, is characterized in that: if outer shroud (2) is as planet carrier, and the shape of inner ring (1) is external gear, and inner ring (1) and planetary pinion (6) keep normal meshing relation.
3. engagement overdrive clutch according to claim 1, is characterized in that: if inner ring (1) is as planet carrier, and the shape of outer shroud (2) is internal gear, and outer shroud (2) and planetary pinion (6) keep normal meshing relation.
4. engagement overdrive clutch according to claim 1, is characterized in that: when planetary pinion (6) can not time rotational by tooth bar (4) constraint, and inner ring (1) and outer shroud (2) can not relative movement, and engagement overdrive clutch is in sync state; When planetary pinion (6) can time rotational, inner ring (1) and outer shroud (2) can produce relative movement, 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 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104358797A true CN104358797A (en) | 2015-02-18 |
| CN104358797B CN104358797B (en) | 2016-07-06 |
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Family Applications (1)
| 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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| Country | Link |
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| CN (1) | CN104358797B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110246A (en) * | 2015-11-18 | 2017-08-29 | 艾弗奈欧股份有限公司 | Rotating flywheel mechanism |
| CN107965532A (en) * | 2017-10-24 | 2018-04-27 | 四川大学 | A kind of non-friction type freewheel clutch |
| CN109519487A (en) * | 2017-09-19 | 2019-03-26 | 周承岗 | Fluted disc freewheel clutch |
| CN113531001A (en) * | 2021-06-29 | 2021-10-22 | 鞠长军 | 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 |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107110246A (en) * | 2015-11-18 | 2017-08-29 | 艾弗奈欧股份有限公司 | Rotating flywheel mechanism |
| CN107110246B (en) * | 2015-11-18 | 2020-01-14 | 艾弗奈欧股份有限公司 | Rotary flywheel mechanism |
| CN109519487A (en) * | 2017-09-19 | 2019-03-26 | 周承岗 | Fluted disc freewheel clutch |
| CN107965532A (en) * | 2017-10-24 | 2018-04-27 | 四川大学 | A kind of non-friction type freewheel clutch |
| CN113531001A (en) * | 2021-06-29 | 2021-10-22 | 鞠长军 | Overrunning clutch capable of being used for high-torque transmission |
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| Publication number | Publication date |
|---|---|
| CN104358797B (en) | 2016-07-06 |
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