CN2320843Y - Planetary steel ball stepless speed change device - Google Patents
Planetary steel ball stepless speed change device Download PDFInfo
- Publication number
- CN2320843Y CN2320843Y CN 97244353 CN97244353U CN2320843Y CN 2320843 Y CN2320843 Y CN 2320843Y CN 97244353 CN97244353 CN 97244353 CN 97244353 U CN97244353 U CN 97244353U CN 2320843 Y CN2320843 Y CN 2320843Y
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- CN
- China
- Prior art keywords
- steel ball
- radius
- circular arc
- planet wheel
- ball
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- Expired - Fee Related
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Abstract
The utility model relates to a stepless speed changer with a planetary steel ball. The friction transmission of the utility model adopts that the pressurizing and pressing force of a disk spring can be increased and reduced in direct proportion with speed regulation and torque. The utility model comprises two driving wheels with circular arc and conical surfaces and two inwardlydished outer pressing rings with circular arc camber; the outer pressing rings which are in point contact with a planetary wheel with a steel ball move horizontally in axial direction to be separated and combined to cause the steel ball and a driving wheel to shift; a contact point, transmission radius and the variation of the compression amount of the disk spring realize constant power transmission; an axle hole of the steel ball is in movable fit with a T-shaped pin axle via needle roller, and thus speed regulation is convenient; the range of the speed regulation is extended.
Description
The utility model relates to the stepless speed variator that a kind of friction driving adopts the pressurization of dish spring, especially can change the planetary steel ball stepless transmission device that impacting force that the dish spring produces is directly proportional with the speed governing torque and increases and decreases voluntarily.
Adopt the stepless speed variator of friction driving pair to be provided with pressurization device, divide constant voltage pressurization and pressurization automatically, the constant voltage that belongs to the pressurization of dish spring is pressurizeed, its impacting force in speed governing is kept constant basically, for doing permanent power transmission, then should reduce in proportion in high rotating speed district so that the minimizing heating that reduces the wastage improves transmission efficiency along with the corresponding increase impacting force of speed governing speed drop low torque must increase.Though pressurization device has impacting force and torque to increase and decrease synchronously automatically; but its complex structure damages easily and can not prevent overload; particularly existing market is than planetary bevel-type stepless speed variator commonly used; it adopts the pressurization of dish spring; but the reduction torque of disc spring pressing power and rotating speed increases required being inversely proportional in speed governing; because outside the crop rotation radially of slow-speed of revolution timing planet, move; the edge body withdraws from from two driving wheels and makes the dish spring loosen the not enough transmission meeting of impacting force to skid; the high loss of generating heat is big because cone pulley is radially got into disc spring pressing power increase transmission to high rotating speed timing; have to design cone pulley flat for alleviating this conflicting increase and decrease, but cause speed governing displacement difficulty and when forbidding to shut down speed governing have influence on using scope.
The purpose of this utility model provides the pressurization of the easy dish spring of a kind of same employing and its impacting force and torque increase and decrease corresponding to planetary steel ball stepless transmission device, and the deficiency that the two-fold advantage that it has constant voltage pressurization and automatic pressurization device concurrently has but overcome them has realized permanent power transmission fully.
The purpose of this utility model is achieved in that the driving wheel that is with two circular arc conical surfaces on the input splined shaft, the outside has the dish spring compressing all the time to make its trend in axially drawing close, one group of ball planet wheel enters between the driving wheel and the impacting force of bearing the dish spring is always tried hard to do the footpath and outwards moved, two outer trim ring working surfaces are that interior concave circular arc (less than semicircle) always comprises obvolvent and the ball planet wheel and make it move and accept to derive from the impacting force that the dish spring produces outward no longer arbitrarily, the radius of four circular arcs be R on year-on-year basis the big e of radius r of steel ball be R-r=e, wider range of e is often got e=5～8mm.Four circular arc cambers are symmetry with the central cross-section perpendicular to steel ball axis hole line, the direction correspondence, circular arc contacts with umbilical point, its initial station: the centre point of two driving wheel circular arc camber radius Rs to the distance of central shaft (input shaft) greater than the centre point distribution circle radius (centre point is to the input shaft distance) of trim ring circular arc camber radius R outside two four circular curves contain the obvolvent steel ball, become three one straight lines by the centre of sphere to circular curve and spherical intersection from the central point of circular arc camber radius R, this structure station forms steel ball exactly and does the contact of pure rolling point with circular arc camber.Axial translation is made in the screw pair transmission that trim ring is subjected to worm and worm gear and moves seat outside two, two outer trim rings are made directly inwardly to move (the distribution circle radius of steel ball reduces) its point of contact with point of contact transmission pressure promotion steel ball and are progressively changed the minimizing of (moving to steel ball axis hole center) transmission radius, and revolution speed is slack-off.The footpath of steel ball is inwardly moved and is forced two initiatively axially separately translations of crop rotation simultaneously, and point of contact is progressively change also: the transmission radius of steel ball is increased, the transmission radius of driving wheel is reduced, so the steel ball speed of autorotation reduces.At this moment driving wheel is because transmission radius gradually reduces, and peripheral force scales up, and the nominal torque that has been enough to can the transmission slow-speed of revolution increase is so permission disc spring pressing power progressively increases.Because drive sprocket axle makes the dish spring be compressed the impacting force increase to separating translation, its impacting force designs control by the axial compression amount of dish spring, guarantees permanent power transmission.The impacting force that dish spring decrement just can be controlled transmission of controlling in the speed governing displacement has prevented to transship to be unlikely again to skid.Next is that the transition of steel ball and circular arc camber speed governing displacement point of contact make the multiple increase and decrease of normal direction positive pressure by 1/sin β, especially low rotation speed area, the normal direction positive pressure increases greatlyyer and the impacting force addition that is increased of compressing once again of dish spring makes the useful horsepower of motor be not fully exerted together.R-r=e recited above and O
1＞O＞O
2(being respectively that driving wheel, steel ball, outer trim ring radius of arc central point are to the input shaft distance between center line) and four radius of arc R equal and opposite in direction direction symmetries (with perpendicular to the steel ball central cross-section) and point of contact, steel ball centre point and 3 straight dynamic and static station structures of radius of arc centre point are essential characteristics of the present utility model, have realized that thus speed adjustable range torque and impacting force increase and decrease and reach the planetary steel ball stepless transmission device of permanent power transmission synchronously.
Ball planet wheel is moved with T shape bearing pin by needle roller with axis hole joins, and the T shape termination of T shape bearing pin is connected in output shaft or the corresponding T shape of the bearing inner race lasso slippage slot, is convenient to do radial displacement.T shape bearing pin connects in the output shaft slippage does the output of arm planetary formula; T shape bearing pin connects with the lasso slippage of bearing inner race does the output of differential planetary formula, and the ball planet wheel is evenly distributed, and is adapted to the high speed rotation, and the speed adjustable range of differential type has enlarged, and output speed reverses again after " zero output ".
Two outer trim rings of the present utility model have bigger axial deciliter to move apart from scope, because it is bigger to make outer trim ring make the axial translation velocity ratio by worm and worm gear and screw pair, so speed governing is light, and can speed governing during shutdown.
Below in conjunction with drawings and Examples the utility model is further specified.
Fig. 1 is the structural drawing of the utility model pivoted arm output type.
Fig. 2 is the structure of the another kind of form of the utility model pivoted arm output type.
Fig. 3 is the structural drawing of differential type of the present utility model.
Fig. 4 is a station cross section coordinate of the utility model pivoted arm output type.
Fig. 5 is a station cross section coordinate of the utility model differential type.
Among the figure: 1. input splined shaft (abbreviation input shaft) 2. dish spring 3. active friction wheels (abbreviation driving wheel) 4. ball planet wheel (abbreviation steel ball) 5. rub outer trim ring (being called for short outer trim ring) 6.T shape bearing pin (abbreviation bearing pin) 7. output shaft 8. bearing inner race lassos (abbreviation lasso) 9. move seat
In Fig. 1, input shaft (1) is supported on that intermediate active is with two driving wheels (3) and dish spring (2) on two bearings, dish spring (2) is compressing two driving wheels (3) trend all the time in doing axially to press translation, steel ball (4) enters always will be done the footpath behind the neutral position pressurized that two driving wheels (3) and dish spring (2) transmit impacting force and outwards move, steel ball (4) has axis hole to join by needle roller and T shape bearing pin (6) are moving, the termination of bearing pin (6) is connected in the T shape slippage slot of output shaft (7) can make radial displacement and transmitting torque neatly, two outer trim rings (5) contain obvolvent with the contact of indent circular arc camber point steel ball (4), the radius of the point of contact that rotate at the axis hole center of two outer trim rings (5) when initial station is a maximum, so the revolution rotating speed is for the highest on outer trim ring (5) circular arc camber, and the impacting force on the point of contact at this moment is minimum, is suitable for high rotating speed transmission.It is to make axial advance by worm screw, worm gear and the screw pair outer trim ring of interlock (5) that two outer trim rings (5) axially close up translation, the circular arc camber translation, changing with the intersection point of steel ball (4), promoting steel ball (4) does directly inwardly to move, force two driving wheels (3) to do axially separately translation, progressively change with the point of contact of steel ball (4), gradually reducing of transmission radius reduces steel ball (4) rotation rotating speed, at this moment dish spring (2) is axially moved apart from compression once again by driving wheel (3), impacting force increases by the ratio of decrement, presses permanent power transmission calculation definite value during design.Secondly because steel ball (4) displacement contacts the intersection point transition, the multiple that the normal direction positive pressure of impacting force is pressed 1/sin β increases also always consistent with the torque increase and decrease.
Fig. 3 is the structural drawing of differential type planetary steel ball stepless transmission device of the present utility model, it is connected in T shape bearing pin (6) in a bearing inner race (8) the T shape slippage slot, allow ball planet wheel (4) with bearing pin (6) rotation and be evenly distributed, also allow two outer trim rings (5) axial translation amount increase, output speed also is inverted to (0.15～0.20) n (n is the input shaft rotating speed) of input speed after zero.
Fig. 4 and Fig. 5 are the initial station figure of the utility model pivoted arm output type and differential output type: the circular arc conical surface radius of two driving wheels (3) is R, and centre point is O
1, O
1Point is called station coordinate height with the output shaft distance between center line, is abbreviated as O
1, same two outer trim rings (5) circular arc camber radius is R, centre point is O
2, the coordinate height is 0
2, steel ball (4) radius is r, and the center of circle (or claiming the centre of sphere) is the O point, and the coordinate height is O, O
1, O, O
2Three centre points have definite scope all the time in whole station translation and displacement, be exactly O
1＞O＞O
2, that is to say that meeting the pure rolling point of steel ball (4) on circular arc camber (R) in each center of arc's point translation of whole speed adjustable range and displacement contacts, from O
1Point or 0
2Point by the O point to the intersection point of circular arc (R) and steel ball (4) be all the time 3 in line, this coordinate relation is convenient to designing and calculating and is controlled the decrement of dish spring (2), just makes dish spring (2) by the needed impacting force work of torque.
The utility model is owing to had radius size, direction and coordinate station and each circular arc camber of the circular arc camber of determining to contact with the point of steel ball, point of contact rolls relatively and separates and combine in the speed governing translation, slippage obviously reduces, the friction impacting force can be controlled proper again, make whole speed governing and in servicely reduced slip, prevented to skid and transship, improved working life and transmission efficiency, realized that to running long time stability and reliability provide effective assurance from structure.
Claims (4)
1, a kind of planetary steel ball stepless transmission device of friction driving, input shaft, driving wheel, planet wheel, outer trim ring, output shaft, dish spring are housed and move seat, it is characterized in that: the transmission working surface is that two driving wheels and the dish spring kink of circular arc conical surface compresses one group of ball planet wheel on input shaft, the outer trim ring of two indent circular arc cambers encloses outside and comprises obvolvent ball planet wheel, and the ball planet wheel is connected by moving joining of needle roller and T shape bearing pin with axis hole.
2, planetary steel ball stepless transmission device according to claim 1 is characterized in that: its relation of radius r of the circular arc conical surface radius R of two driving wheels, two outer trim ring indent radius of arc R, ball planet wheel is: R-r=e, e often get 5～8mm.
3, planetary steel ball stepless transmission device according to claim 1 is characterized in that: the centre point O of driving wheel radius of arc R
1, the centre of sphere point O of ball planet wheel, outer trim ring the centre point O of radius of arc R
2Should meet O with input shaft center line station distance
1＞O＞O
2
4, planetary steel ball stepless transmission device according to claim 1, it is characterized in that: ball planet wheel is connected with T shape bearing pin by needle roller movingly with axis hole, the T shape termination of T shape bearing pin be connected in the corresponding T-slot of output shaft or the T shape slippage slot of a bearing inner race lasso in loose joint.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97244353 CN2320843Y (en) | 1997-11-16 | 1997-11-16 | Planetary steel ball stepless speed change device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 97244353 CN2320843Y (en) | 1997-11-16 | 1997-11-16 | Planetary steel ball stepless speed change device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2320843Y true CN2320843Y (en) | 1999-05-26 |
Family
ID=33953102
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 97244353 Expired - Fee Related CN2320843Y (en) | 1997-11-16 | 1997-11-16 | Planetary steel ball stepless speed change device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2320843Y (en) |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100455848C (en) * | 2007-02-09 | 2009-01-28 | 覃勇 | Spherical stageless transmission speed changing device |
| CN105485279A (en) * | 2016-01-13 | 2016-04-13 | 昆明理工大学 | Universal continuously-variable transmission |
| CN105757200A (en) * | 2016-03-17 | 2016-07-13 | 中研技术有限公司 | Continuously variable transmission |
| CN107246463A (en) * | 2008-06-23 | 2017-10-13 | 福博科知识产权有限责任公司 | Buncher |
| US10428939B2 (en) | 2003-02-28 | 2019-10-01 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US10428915B2 (en) | 2012-01-23 | 2019-10-01 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
| US10458526B2 (en) | 2016-03-18 | 2019-10-29 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, systems and methods |
| CN111022866A (en) * | 2019-12-30 | 2020-04-17 | 郑州工程技术学院 | All-round scanning tool |
| US10634224B2 (en) | 2008-06-06 | 2020-04-28 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
| US10703372B2 (en) | 2007-02-01 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Systems and methods for control of transmission and/or prime mover |
| US10704687B2 (en) | 2007-12-21 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Automatic transmissions and methods therefor |
| US10704657B2 (en) | 2008-08-26 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US10711869B2 (en) | 2005-11-22 | 2020-07-14 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| CN111457066A (en) * | 2020-04-09 | 2020-07-28 | 重庆大学 | Bearing type traction speed reducer |
| US10746270B2 (en) | 2009-04-16 | 2020-08-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| CN111720508A (en) * | 2020-06-04 | 2020-09-29 | 陈驰川 | Planetary transmission speed variator with thin-wall structure |
| US10920882B2 (en) | 2016-01-15 | 2021-02-16 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
| US11125329B2 (en) | 2007-11-16 | 2021-09-21 | Fallbrook Intellectual Property Company Llc | Controller for variable transmission |
| US11174922B2 (en) | 2019-02-26 | 2021-11-16 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
| US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
| US11454303B2 (en) | 2005-12-09 | 2022-09-27 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US11598397B2 (en) | 2005-12-30 | 2023-03-07 | Fallbrook Intellectual Property Company Llc | Continuously variable gear transmission |
| US11667351B2 (en) | 2016-05-11 | 2023-06-06 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission |
-
1997
- 1997-11-16 CN CN 97244353 patent/CN2320843Y/en not_active Expired - Fee Related
Cited By (30)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10428939B2 (en) | 2003-02-28 | 2019-10-01 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US10711869B2 (en) | 2005-11-22 | 2020-07-14 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US11454303B2 (en) | 2005-12-09 | 2022-09-27 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US11598397B2 (en) | 2005-12-30 | 2023-03-07 | Fallbrook Intellectual Property Company Llc | Continuously variable gear transmission |
| US10703372B2 (en) | 2007-02-01 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Systems and methods for control of transmission and/or prime mover |
| CN100455848C (en) * | 2007-02-09 | 2009-01-28 | 覃勇 | Spherical stageless transmission speed changing device |
| US11125329B2 (en) | 2007-11-16 | 2021-09-21 | Fallbrook Intellectual Property Company Llc | Controller for variable transmission |
| US10704687B2 (en) | 2007-12-21 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Automatic transmissions and methods therefor |
| US10634224B2 (en) | 2008-06-06 | 2020-04-28 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
| CN107246463A (en) * | 2008-06-23 | 2017-10-13 | 福博科知识产权有限责任公司 | Buncher |
| US10704657B2 (en) | 2008-08-26 | 2020-07-07 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US10746270B2 (en) | 2009-04-16 | 2020-08-18 | Fallbrook Intellectual Property Company Llc | Continuously variable transmission |
| US10428915B2 (en) | 2012-01-23 | 2019-10-01 | Fallbrook Intellectual Property Company Llc | Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor |
| CN105485279B (en) * | 2016-01-13 | 2018-08-14 | 昆明理工大学 | A kind of universal stepless speed changer |
| CN105485279A (en) * | 2016-01-13 | 2016-04-13 | 昆明理工大学 | Universal continuously-variable transmission |
| US10920882B2 (en) | 2016-01-15 | 2021-02-16 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
| US11306818B2 (en) | 2016-01-15 | 2022-04-19 | Fallbrook Intellectual Property Company Llc | Systems and methods for controlling rollback in continuously variable transmissions |
| CN105757200A (en) * | 2016-03-17 | 2016-07-13 | 中研技术有限公司 | Continuously variable transmission |
| US10458526B2 (en) | 2016-03-18 | 2019-10-29 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, systems and methods |
| US11667351B2 (en) | 2016-05-11 | 2023-06-06 | Fallbrook Intellectual Property Company Llc | Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission |
| US11215268B2 (en) | 2018-11-06 | 2022-01-04 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
| US11624432B2 (en) | 2018-11-06 | 2023-04-11 | Fallbrook Intellectual Property Company Llc | Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same |
| US11174922B2 (en) | 2019-02-26 | 2021-11-16 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
| US11530739B2 (en) | 2019-02-26 | 2022-12-20 | Fallbrook Intellectual Property Company Llc | Reversible variable drives and systems and methods for control in forward and reverse directions |
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| CN111022866B (en) * | 2019-12-30 | 2021-07-30 | 深圳瑞尔康生物科技股份有限公司 | All-round scanning tool |
| CN111022866A (en) * | 2019-12-30 | 2020-04-17 | 郑州工程技术学院 | All-round scanning tool |
| CN111457066B (en) * | 2020-04-09 | 2021-07-23 | 重庆大学 | Bearing type traction speed reducer |
| CN111457066A (en) * | 2020-04-09 | 2020-07-28 | 重庆大学 | Bearing type traction speed reducer |
| CN111720508A (en) * | 2020-06-04 | 2020-09-29 | 陈驰川 | Planetary transmission speed variator with thin-wall structure |
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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 |