CN2425811Y - Fixed axle gert type automatic shifting speed variator - Google Patents
Fixed axle gert type automatic shifting speed variator Download PDFInfo
- Publication number
- CN2425811Y CN2425811Y CN 00202623 CN00202623U CN2425811Y CN 2425811 Y CN2425811 Y CN 2425811Y CN 00202623 CN00202623 CN 00202623 CN 00202623 U CN00202623 U CN 00202623U CN 2425811 Y CN2425811 Y CN 2425811Y
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- shaft
- gear
- overriding clutch
- power
- wheel
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Abstract
The utility model relates to an automatic shifting speed changing mechanism used for mechanical transmission. The utility model is characterized in that an overrunning clutch (mainly composed of a star wheel 2, a rolling post 3, an input gear 4) is arranged additionally between a power input shaft 1 and an input gear 4 on the basis of a fixed shaft type gear speed reduction device, and a torque limiter (mainly composed of a movable dialing pin 6, a force measuring spring 7, a star wheel 2 and a power output shaft 5) is arranged additionally between the power input shaft 1 and a power output shaft 5. When the external is a large load, motive power is sent to the power output shaft 5through the overrunning clutch and a two connection gear 8 and is exported at a low rotating speed; when the external is small load, motive power is sent to the power output shaft 5 through the torque limiter directly and is exported at a high rotating speed.
Description
The utility model relates to a kind of mechanical automatic speed changing mechanism, and this mechanism is applicable to mechanical transmission fields.
The speed-change and gearshift device is widely used in mechanical transmission fields, for example: the speed-changing gear box that automobile and tractor generally adopts, tighten during oil well repairing operation or unload underground pipelines and the gear gearshift that adopted in the Power Tong (also claiming thread screw on and-off machine) that uses.The characteristics of these transmission systems be utilize different engaging gears to transferring power reaching shifted purpose, and realize that the method for speed change is hand shifting transmission.Obviously,,, reduce energy consumption, reduce labour intensity of great advantage for improving operating efficiency if can select different engaging gears to reaching the autoshift speed change automatically according to the variation of external load.But with regard to present present situation, can realize that mechanism's finding of mechanical automatic speed changing is few, the automatic transmission that can try out is then more rare.By Jiang Jiaolin invention " have overriding clutch planetary gear type two-shift automatic variable speed mechanism (patent No.: 99202478.1) ", though solved this problem of mechanical automatic speed changing mechanism, but because sun and planet gear is made the processing trouble, and in existing speed-changing gear box, use seldom, therefore limited the field of application of this patent.
The purpose of this utility model provides a kind of new mechanical type autoshift speed-changing mechanism that is easy to hand in the common manual gear shift two gears of applying on the fast case, it can change the rotating speed of power take-off shaft automatically according to the variation of external load, to reach the purpose of power match.If plural this mechanism is carried out series combination, then can realize the automatic transmission of many gears.
This mechanism has significant advantage: 1. intelligent speed changing, improved work efficiency.2. gear shift promptly and accurately, energy savings.3. operation automatically, it is 4. practical to have alleviated labor intensity of operating personnel, is easy to apply on common change speed gear box.
For reaching this purpose, the technical program is the improvement of carrying out on common fixed shaft type reduction gear apparatus, has adopted two mechanisms of torque limiter and overriding clutch, and the two has been carried out combination.The effect of torque limiter is: when external load is in the scope of torque limiter operation torque, be delivered on the power take-off shaft through torque limiter by the moment of torsion of power input shaft transmission, realize the high rotating speed output of little load.When external load exceeds torque limiter operation torque scope and is in big load, torque limiter skids, this moment, the power of power input shaft drove the overriding clutch outer ring through the overriding clutch star-wheel, to being delivered on the power take-off shaft, realized the output of big load slow speed of revolution through reducing gear.The effect of overriding clutch is: when the external world was in little load condition, overriding clutch was thrown off automatically, and promptly the star-wheel of overriding clutch separates with its outer ring and transferring power not.When the external world was in big load condition, overriding clutch engaged, and the power of power input shaft drives the outer ring realization high pulling torque slow speed of revolution output of overriding clutch through the star-wheel of overriding clutch.Therefore for overriding clutch and torque limiter, the two is that variation alternate run according to external load takes turns to operate and realizes the autoshift speed change.Because the folk prescription of common overriding clutch is to transferability, above-mentioned functions can only go up accomplished in a direction (cw or conter clockwise), in order all to realize above-mentioned functions on the rotating both direction, the spy has adopted the two-way roller-type overrunning clutch that has the pusher dog that commutates.In order to realize that automatic pusher dog reaches the directivity of automatic transposing overriding clutch, do not cause the interference of motion again, axle connects with power between the pusher dog that commutates and has adopted the friction connecting mode so output power, the friction force that produces when utilizing the power take-off shaft rotating drives the commutation pusher dog, thereby reaches auto reversive purpose.In order to guarantee that this friction force has stable numerical value, adopted holddown spring to compress, and adjusted the size of thrust by adjustment nut.
The utility model is described in further detail below in conjunction with accompanying drawing:
Fig. 1 is the utility model assembly section-drawing; Fig. 2 is the A-A section-drawing of Fig. 1; Fig. 3 is the clockwise direction sexual state figure of double rolling key clutch; The anticlockwise direction sexual state figure of Fig. 4 double rolling key clutch; Fig. 5 is U-shaped key cover left view; Fig. 6 is U-shaped key cover front view; Fig. 7 is that power take-off shaft A is to view; Fig. 8 is the power take-off shaft front view; Fig. 9 is that power take-off shaft B is to view; Figure 10 is commutation pusher dog right elevation; Figure 11 is commutation pusher dog front view; Figure 12 is movable finger front view; Figure 13 is movable finger left view; Figure 14 is the power input gear front view; Figure 15 is the power input gear left view; Figure 16 is an overriding clutch star-wheel front view; Figure 17 is an overriding clutch star-wheel left view; Figure 18 is the return pin front view; Figure 19 is the return pin left view.
Among the figure: 1. adjustment nut; 2. copper washer; 3.U type key cover; 4. holddown spring; 5. output gear; 6. power take-off shaft; 7. thrust ball bearing; 8. commutation pusher dog; 9. movable finger; 10. roller; 11. dynamometer spring; 12. plus-minus screw; 13. di-gear; 14. housing; 15. power input shaft; 16. power input gear; 17. lining; 18. overriding clutch star-wheel; 19. return pin; 20. pull back spring.
Fig. 1 is the utility model assembly section-drawing.The right gear of the di-gear among this figure is bigger than left gear.Correspondingly, power input gear 16 should be miniature gears, and the gear on the power take-off shaft 6 should be big gear wheel.So when the external load change needs changed speed operation (this moment, the route of transmission of power will pass through middle di-gear) greatly, the transfer route of power is the gear to the power take-off shaft 6 again from power input gear 16 to di-gear 13, is that a rotating speed reduces process.
We introduce structure of the present utility model first.
See Fig. 1, power input shaft 15 usefulness thrust ball bearings 7 are supported on the housing 14, the left end of power input shaft 15 is connected with overriding clutch star-wheel 18 with spline, overriding clutch star-wheel 18 combines with overriding clutch outer ring (being input shaft gear 16) by roller 10 and separates, and power input gear 16 drives the di-big gear wheel by tween drive shaft di-miniature gears and advances you and drive gear (this gear and power take-off shaft 6 are integral) on the power take-off shaft 6.Adopt torque limiter to connect between power input shaft 15 and power take-off shaft 6, its structure mainly is made up of the taper disk that has conical bore on dynamometer spring 11, movable finger 9 and the power take-off shaft 6.Concrete structure is to arrange three axial cylindrical bore on the overriding clutch star-wheel 18, dynamometer spring 11 and movable finger 9 are housed in the hole, the conical bore that movable finger 9 left ends are made on the disk of coniform and power take-off shaft 6 matches, right-hand member at dynamometer spring 11 is equipped with plus-minus screw 12, can adjust the predetermincd tension of dynamometer spring 11 by turning plus-minus screw 12, also just adjust the operation torque numerical value of torque limiter.For the directivity (stating the notion of directivity as follows) that reaches automatic transposing overriding clutch, so make spline-shaped to match with U-shaped key cover 3 at the left end of power take-off shaft 6, hollow shape is made in inside at power take-off shaft 6, its hollow position is equipped with commutation pusher dog 8 and holddown spring 4 respectively, the left end of commutation pusher dog 8 is screwed in adjustment nut 1 by the screw thread on it, between U-shaped key cover 3 and adjustment nut 1 abrasion resistant copper washer 2 is housed.The right-hand member of commutation pusher dog 8 is supported on (commutation pusher dog 8 and lining 17 running-fits) in the endoporus of power take-off shaft 6 by lining 17, pusher dog on it (see figure 2) that contacts with roller 10, to pusher dog 8 three rollers in the overriding clutch were lost efficacy by Rotation With Changing, but three rollers 10 then are in engagement state in addition.Also promptly can adjust the directivity (directivity is chatted face to face as follows and stated) of overriding clutch to pusher dog 8 by Rotation With Changing.Three slotted eye (see figure 10)s have circumferentially been offered at plate-like position at commutation pusher dog 8, the purpose of this slotted eye is that movable finger 9 can be stretched out from this hole, directly withstand in the conical bore of power take-off shaft 6 right-hand members, and when overriding clutch star-wheel 18 drive activity fingers 9 rotate, existence because of this elliptical aperture, make can have between commutation pusher dog 8 and the movable finger 9 one in relative rotation angular transposition (this angular transposition can make the pusher dog 8 that commutates stir roller 10, thereby finish the commutation work of overriding clutch directivity, see below), left end at commutation pusher dog 8 is equipped with holddown spring 4, the left end of holddown spring 4 withstands on the U-shaped key cover 3, its right-hand member withstands on the crossette of power take-off shaft 6 endoporus, adjust the size of holddown spring 4 elastic force by turning adjustment nut 1, advance the size that you adjust U-shaped key cover 3 and copper washer 2 positive pressures, just adjusted the size of the friction moment between power take-off shaft 6 and the commutation dial 8.At the spline place of the left end of power take-off shaft 6 output gear 5 is housed as can be seen from Figure 1, the output of power can realize thus.
Introduce the principle of work of this utility model below.
For the ease of discussing, we repeat two notions in the overriding clutch theory here: the clockwise direction of overriding clutch and anticlockwise direction.
Clockwise direction: power can only be delivered on the outer ring from star-wheel when the star-wheel of overriding clutch rotated in the clockwise direction, and can not be delivered on the star-wheel from the outer ring.
Anticlockwise direction: power can only be delivered on the outer ring from star-wheel when the star-wheel of overriding clutch rotated in the counterclockwise direction, and can not be delivered on the star-wheel from the outer ring.
If it is that right-hand revolution (from power input shaft 15 axle heads), event overriding clutch star-wheel 18 are also for clockwise rotating that overriding clutch is in position, the power of clockwise direction.When the external world is in little load condition and promptly is in the operation torque scope of torque limiter, movable finger 9 do not withdraw, so the time power input shaft 15 power be delivered to power take-off shaft 6 outputs through the high rotating speed of torque limiter.Though clockwise rotating of power take-off shaft 6 can be by the gear driven di-gear 13 on it at this moment, advance you and drive power input shaft gear 16 and clockwise rotate as raising speed, also promptly this moment overriding clutch the speed that clockwise rotates of outer ring (being power input shaft gear 16) fast than the star-wheel 18 of overriding clutch.But because overriding clutch is on the clockwise direction, so the time overriding clutch must throw off, thereby can not produce the restriction of superfluous constraint.The block diagram of the transfer route of power is at this moment:
When the external world is in big load also is that the external load moment of torsion is when exceeding the operation torque scope of torque limiter, movable finger 9 withdrawals in the torque limiter, the conical bore that overriding clutch star-wheel 18 drive activity fingers 9 are crossed on the right-hand member disk of power take-off shaft 6 enters planar section, therefore, power can't be exported through torque limiter, along with overriding clutch star-wheel 18 continue clockwise rotate, to drive power input gears 16 by roller 10 and clockwise rotate (so time overriding clutch be clockwise direction), so power is just through tween drive shaft di-gear, the gear that drives on the power take-off shaft 6 is exported power, and this moment, the block diagram of power transmission line was:
Because of the cooresponding two pairs of gear mesh reductions of speed of transfer route process di-gear of power, therefore power is low speed output under big load condition.So just finished purpose according to the rotating speed of the variation automatically regulating power take-off shaft 6 of external load.
In order to make this mechanism all can realize the autoshift speed change when the rotating, the spy has adopted the double rolling key clutch structure of band pusher dog, therefore, pusher dog 8 pushes the clockwise direction of double rolling key clutch if will commutate, be that overriding clutch star-wheel 18 can drive power input gear 16 rotations when rotating in the clockwise direction, and overriding clutch star-wheel 18 when rotating in the counterclockwise direction overriding clutch throw off (overriding clutch star-wheel 18 is thrown off with power input shaft gear 16), then this mechanism can realize clockwise rotating the automatic speed changing function on the direction.Otherwise, pusher dog 8 pushes the anticlockwise direction of double rolling key clutch if will commutate, in the time of driving power input gear 16 rotation overriding clutch star-wheels 18 when promptly overriding clutch star-wheel 18 rotates in the counterclockwise direction and rotate in the clockwise direction overriding clutch throw off (overriding clutch star-wheel 18 and power input gear 16 disengagements) then this mechanism can realize rotating counterclockwise the autoshift speed changing function on the direction.
In order to realize the function of automatic pusher dog commutation, the circular shaft of commutation pusher dog 8 left ends is stretched out from the endoporus of power take-off shaft 6, and by being screwed in U type key cover 3 frictions (U type key cover 3 is used splined with power take-off shaft 6) on adjustment nut 1, copper washer 2 and the power take-off shaft 6 on the commutation pusher dog 8, when power take-off shaft 6 rotates, just switch operation is delivered on the commutation pusher dog 8 by this friction force.Its concrete enforcement principle is as follows:
If power input shaft 15 clockwise directions rotate (from power input shaft 15 ends), and commutation pusher dog 8 is in the center position with respect to overriding clutch star-wheel 18, the claw of pusher dog 8 of commutating this moment makes the roller 10 at its two ends all be in the disengaged position (see figure 2), when the external world is in little load, because of power through the torque limiter transmission, power take-off shaft 6 is clockwise rotated.Therefore, power take-off shaft 6 connects by friction rotates commutation pusher dog 8 synchronously, at this moment, overriding clutch star-wheel 18 also rotates in the same way with commutation pusher dog 8, just still keeping each roller 10 to be in disengaged condition, so power input shaft gear 16 is thrown off with overriding clutch star-wheel 18, power is stirred power take-off shaft 6 outputs by movable finger 9.When the external world is in big load, can't stir power take-off shaft 6 rotations because of movable finger 9 withdraws, at this moment, power take-off shaft 6 is motionless, so commutation pusher dog 8 is also motionless, because of overriding clutch star-wheel 18 continues to clockwise rotate, therefore, commutation pusher dog 8 just rotates counterclockwise an angle (as " clockwise direction " constitution diagram among Fig. 3) with respect to overriding clutch star-wheel 18, so, make the roller 10 of three tape labels among this figure be in disengaged position, but three rollers 10 that do not have mark then are in engagement state, thus the position at roller 10 places as can be known, this direction just is the overriding clutch clockwise direction.So power is transferred on the power take-off shaft 6 through tween drive shaft di-gear 13 through overriding clutch, so finish the automatic speed changing process on the clockwise direction.
When power take-off shaft 6 is in the big load low-speed running stage, because commutation pusher dog 8 is under the drive of overriding clutch star-wheel 18, do higher speed and clockwise rotate (for power take-off shaft 6), and this moment power take-off shaft 6 for slowly run, that the two rotating speed occurs is asynchronous, but owing to adopt friction to connect between the two, the two motion is separated and do not restricted.This shows, the effect that this axle head adopts friction to connect is that (this friction force should be enough big in the automatic reverse that should guarantee overriding clutch, to overcome the resistance that pull back spring 20 produces on return pin 19), guarantee behind power take-off shaft 6 reductions of speed the cut-out of motion between power take-off shaft 6 and the commutation pusher dog 8 again.
More than be the situation that power input shaft 15 clockwise rotates, power input shaft 15 be discussed below by clockwise rotating the auto reversive process of overriding clutch when rotating counterclockwise that becomes.
At first, if the external world is in big load condition, therefore movable finger 9 can't be stirred power take-off shaft 6 rotations when power input shaft 15 anticlockwise motions, then as shown in Figure 1, overriding clutch star-wheel 18 will be thrown off with power input gear 16, and this moment, transmission of power was interrupted, thereby power take-off shaft 6 does not rotate, axle head friction through power take-off shaft 6 connects, and makes commutation pusher dog 8 be in motionless state.Along with overriding clutch star-wheel 18 anti-clockwises are rotated further, on the overriding clutch star-wheel 18 three not the roller 10 of tape label be in engageable state, three then are in disengaged condition in addition.By the principle of overriding clutch as can be known, this moment, the direction of transfer of overriding clutch was just commutated, and changed into present anticlockwise direction (seeing anticlockwise direction sexual state figure among Fig. 4) by original clockwise direction sexual intercourse.
Next is established the external world and is in little load condition, if movable finger 9 was in and can not stirs power take-off shaft 6 position of anticlockwise motion (this moment, movable finger 9 was in the planimetric position of power take-off shaft 6 disk end faces) together this moment, the commutation process when then Ci Shi commutation process is in big load with the external world is identical; If movable finger 9 is in and can stirs power take-off shaft 6 position of anticlockwise motion (being the position that its conical surface withstands on the disk taper hole of power take-off shaft 6) together, because of the outer ring (being power input gear 16) that speedup drives overriding clutch being rotated counterclockwise by gear on the power take-off shaft 6 and di-gear 13, and the residing state of overriding clutch this moment is the cw state, so overriding clutch star-wheel 18 will hinder power input gear 16 by roller 10 and rotate counterclockwise, the moment of torsion of the power that transmitted this moment can sharply increase, movable finger 9 withdrawals, therefore overriding clutch star-wheel 18 just cross power take-off shaft 6 the disk taper hole the position and be on the position on plane, so the commutation process when being in big load with the above-mentioned external world is the same, still can finish the commutation effect of overriding clutch.Therefore next can carry out the anti-clockwise changed speed operation (promptly when little load power take-off shaft 6 high-speed operations, when big load, power take-off shaft 6 low-speed runnings), whole process is identical with the clws situation.
More than be that power input shaft 18 clockwise rotates the process that becomes its directivity of double rolling key clutch automatic compensation when rotating counterclockwise, remaining each process is similar, is not giving unnecessary details.
Claims (2)
1, fixed axis gear formula autoshift speed-changing mechanism, it is the improvement of on the basis of fixed shaft type reduction gear apparatus, carrying out, make original gear decide ratio speed reducer and constitute the speed-changing mechanism that can change transmitting ratio automatically according to the variation of external load, it is characterized in that: between the power input shaft ⒂ of fixed shaft type reduction gear apparatus and power input gear ⒃, add and load onto overriding clutch, this overriding clutch star-wheel ⒅ drives by splined with power input shaft ⒂, the outer ring of this overriding clutch and power input gear ⒃ are made of one, between power input shaft ⒂ and power take-off shaft ⑹, adopt torque limiter to link, the A end of torque limiter and overriding clutch star-wheel ⒅ are made of one, the secondary part of torque limiter and power take-off shaft ⑹ are made of one, overriding clutch star-wheel ⒅ axially on offer cylinder pin hole, dynamometer spring ⑾ and movable finger ⑼ are installed on cylinder pin hole, on the right side of power take-off shaft ⑹, are provided with the conical bore that can allow movable finger ⑼ stir.
2, fixed axis gear formula autoshift speed-changing mechanism according to claim 1 is characterized in that: overriding clutch has adopted the two-way roller-type overrunning clutch structure of band commutation pusher dog ⑻.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00202623 CN2425811Y (en) | 2000-02-21 | 2000-02-21 | Fixed axle gert type automatic shifting speed variator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 00202623 CN2425811Y (en) | 2000-02-21 | 2000-02-21 | Fixed axle gert type automatic shifting speed variator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2425811Y true CN2425811Y (en) | 2001-04-04 |
Family
ID=33571529
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 00202623 Expired - Fee Related CN2425811Y (en) | 2000-02-21 | 2000-02-21 | Fixed axle gert type automatic shifting speed variator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2425811Y (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100383435C (en) * | 2004-12-28 | 2008-04-23 | 广东工业大学 | Double-power inputting automatic shifting speed reducer |
| CN100396971C (en) * | 2005-03-22 | 2008-06-25 | 广东工业大学 | Double-power bidirectional automatic switching worm reducer |
| CN101407175B (en) * | 2008-09-02 | 2010-12-29 | 安徽奥马特汽车变速系统有限公司 | Buffering mechanism of electromechanical shifter |
| CN104043881A (en) * | 2013-03-15 | 2014-09-17 | 陈忠维 | Automatic tapping device |
| CN105539463A (en) * | 2016-01-14 | 2016-05-04 | 北京新联铁科技股份有限公司 | Transmission connection structure, axle carrier vehicle, bogie and wheel set overhaul system |
| CN107061533A (en) * | 2015-10-07 | 2017-08-18 | 泰雷兹公司 | Radar arrangement |
| CN109664178A (en) * | 2018-12-14 | 2019-04-23 | 天津大学 | Change the polishing mechanism of eccentricity value and transmission ratio-variable by eccentric adjusting block |
-
2000
- 2000-02-21 CN CN 00202623 patent/CN2425811Y/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100383435C (en) * | 2004-12-28 | 2008-04-23 | 广东工业大学 | Double-power inputting automatic shifting speed reducer |
| CN100396971C (en) * | 2005-03-22 | 2008-06-25 | 广东工业大学 | Double-power bidirectional automatic switching worm reducer |
| CN101407175B (en) * | 2008-09-02 | 2010-12-29 | 安徽奥马特汽车变速系统有限公司 | Buffering mechanism of electromechanical shifter |
| CN104043881A (en) * | 2013-03-15 | 2014-09-17 | 陈忠维 | Automatic tapping device |
| CN107061533A (en) * | 2015-10-07 | 2017-08-18 | 泰雷兹公司 | Radar arrangement |
| CN105539463A (en) * | 2016-01-14 | 2016-05-04 | 北京新联铁科技股份有限公司 | Transmission connection structure, axle carrier vehicle, bogie and wheel set overhaul system |
| CN109664178A (en) * | 2018-12-14 | 2019-04-23 | 天津大学 | Change the polishing mechanism of eccentricity value and transmission ratio-variable by eccentric adjusting block |
| CN109664178B (en) * | 2018-12-14 | 2020-10-16 | 天津大学 | Polishing mechanism with variable transmission ratio and eccentric value changed through eccentric adjusting block |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |