CN201145018Y - Hydraulic differential stepless speed changer - Google Patents
Hydraulic differential stepless speed changer Download PDFInfo
- Publication number
- CN201145018Y CN201145018Y CNU2007201149589U CN200720114958U CN201145018Y CN 201145018 Y CN201145018 Y CN 201145018Y CN U2007201149589 U CNU2007201149589 U CN U2007201149589U CN 200720114958 U CN200720114958 U CN 200720114958U CN 201145018 Y CN201145018 Y CN 201145018Y
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- speed change
- differential
- speed
- gear
- variable
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Abstract
The utility model provides a hydraulic differential stepless gear, belonging to the stepless speed change device technical field. The stepless gear is characterized in that a turbine, a pump impeller and an idler pulley are matched with a differential mechanism, a speed change planetary gear train, an intermediate clutch and a one-way clutch to form a differential torque converter; a speed change gear ring, a speed change planet wheel, a speed change planet carrier and a speed change sun wheel are matched to form the speed change planetary gear train; an output end of the differential torque converter is matched and connected with a reversing planetary gear train through the speed change planet carrier; the reversing planetary gear train is provided with a forward gear clutch and a reverse gear clutch; the differential mechanism is matched and connected with an input shaft, and the reversing planetary gear train is in matched connection with an output shaft; both ends of the speed change sun wheel are respectively matched with the input shaft and the output shaft by taking the same central shaft in a rotary mode. The gear has the advantages of novel design, simple structure, small volume and low cost; due to the adoption of the mechanical direct transmission, the gear can automatically adapt to the change of input and output torsional moments and the rotary speed, thereby improving the efficiency of the transmission system, having obvious fuel conservation effect and enlarging the application range of the stepless gear.
Description
Technical field
The utility model belongs to the stepless speed changes devices technical field, is specifically related to a kind of hydraulic differential variable-speed case that is applicable to that motors such as automobile, internal combustion locomotive, tractor, petroleum machinery, mining machinery, boats and ships, military transportation equipment are connected with drive unit.
Background technique
Buncher is the ideal style of system of vehicle transmission, auto continuously variable transmission of the prior art (CVT) but adopt the transmission device of steel band and reducing wheeled steel, its speed control system is quite complicated, by multichannel different modes sensor monitors motor, transmission system input output moment state, convert Monitoring Data to electrical signal and pass to micro computer, again by computer and setting program comparison, send instruction after the comparison, various instructions become control command to handle the multitude of different ways executive component through electrical signal conversion again, adjust velocity ratio.It is over half that its operation control system manufacture cost accounts for this speed changer cost.Because but steel band is to come transferring power by friction with the reducing wheeled steel, its physical dimension is big, and fault is many, and driving torque is little, is of limited application.
The model utility content
The utility model is according to the design principle of input power and output power balance, a kind of sensor, micro computer and executive component of need not is provided, have simple in structure, volume is little, cost is low and hydraulic differential variable-speed case technological scheme applied widely, that driving torque is big, to overcome problems of the prior art.
Described hydraulic differential variable-speed case, it is characterized in that by turbine, pump impeller, guide wheel and differential attachment, variable speed planetary row, interposed clutch, overrunning clutch cooperates the differential torque converter of formation, variable speed planetary row is by the speed change gear ring, the variable speed planetary wheel, the variable speed planetary frame, the speed change sun gear cooperates formation, differential torque converter output terminal closes with the deploying of commutation planet by the variable speed planetary frame and is connected, commutation planet row goes up to connect the forward gear clutch is set, clutch reverses gear, differential attachment and input shaft are connected, commutation planet row be connected with output shaft, speed change sun gear two ends respectively with input shaft, output shaft is rotatably assorted mutually by same central shaft.
Described hydraulic differential variable-speed case, it is characterized in that described differential attachment comprises the differential planetary frame, differential planetary gear train and a pair of driving cog, differential planetary gear train rotates to be arranged on the differential planetary frame and also cooperates with the driving cog engagement driving respectively, differential planetary frame and input shaft secure fit, and fixedly connected with guide wheel, driving cog, interposed clutch, turbine, the speed change gear ring links into an integrated entity, driving cog, pump impeller, the speed change sun gear links into an integrated entity, the speed change gear ring, the speed change sun gear cooperates with the variable speed planetary wheel engagement driving that rotation is arranged on the variable speed planetary frame respectively.
Described hydraulic differential variable-speed case, commutation planet carrier and commutation sun gear, commutation planet wheel are drawn together in the planet package that it is characterized in that commutating, gear ring commutates, commutation gear ring and output shaft secure fit, commutation sun gear and variable speed planetary frame secure fit, and cooperate with commutation planet wheel, commutation gear ring engagement driving respectively, the commutation planet wheel rotates and is arranged on the commutation planet carrier.
Described hydraulic differential variable-speed case is characterized in that speed change sun gear axle head and input shaft socket are rotatably assorted, speed change sun gear increment and output sleeve switch through movingly.
Described hydraulic differential variable-speed case is characterized in that described interposed clutch is equipped with between turbine, driving cog, any two parts of speed change gear ring.
Described hydraulic differential variable-speed case is characterized in that described overrunning clutch and speed change gear ring are rotatably assorted.
Above-mentioned hydraulic differential variable-speed case is novel, rational in infrastructure, do not need numerous and diverse change control system, automatically adapt to the input and output change in torque, the input and output rotating speed is changed thereupon, realized that transmission in 1: 1 and maximum transmission ratio are directly transmission of machinery, when transmission in 1: 1, not participation of torque converter work has improved transmission system efficiency, has tangible saving fuel oil effect, simultaneously simple in structure, volume is little, cost is low, enlarged stepless speed variator Applicable scope, adopt interposed clutch and brake system linkage structure, can realize the engine braking function, improve the driving safety guarantee, can make more automobile, internal combustion locomotive, tractor, petroleum machinery, mining machinery, boats and ships, motors such as military transportation equipment and drive unit bindiny mechanism can adopt this optimal system of vehicle transmission mode of buncher, generally improve the travelling comfort of vehicle ride.
Description of drawings
Fig. 1 is the utility model structure principle chart;
Fig. 2 is the utility model structural representation.
Among the figure: the 1-turbine, the 2-pump impeller, the 3-guide wheel, the 4-differential attachment, the 4a/4d-driving cog, the 4b-differential planetary gear train, 4c-differential planetary frame, the 5-input shaft, the 6-interposed clutch, the 7-overrunning clutch, 8-variable speed planetary row, 8a-speed change gear ring, 8b-variable speed planetary wheel, 8c-variable speed planetary frame, 8d-speed change sun gear, the 9-clutch that reverses gear, the 10-output shaft, 11-forward gear clutch, 12-commutation planet row, the 12a-sun gear that commutates, the 12b-planet wheel that commutates, the 12c-planet carrier that commutates, the 12d-gear ring that commutates.
Embodiment
The utility model is described in further detail below in conjunction with Figure of description:
Hydraulic differential variable-speed case, by turbine 1, pump impeller 2, guide wheel 3 and differential attachment 4, variable speed planetary row 8, interposed clutch 6, overrunning clutch 7 cooperates the differential torque converter of formation, variable speed planetary row 8 is by speed change gear ring 8a, variable speed planetary wheel 8b, variable speed planetary frame 8c, speed change sun gear 8d cooperates formation, differential torque converter output terminal is connected by variable speed planetary frame 8c and commutation planet row 12, connect on the commutation planet row 12 forward gear clutch 11 is set, clutch 9 reverses gear, differential attachment 4 is connected with input shaft 5, commutation planet row 12 be connected with output shaft 10, speed change sun gear 8d two ends respectively with input shaft 5, output shaft 10 is rotatably assorted mutually by same central shaft.
As shown in Figure 1 and Figure 2, cooperate with differential attachment 4, variable speed planetary row 8, interposed clutch 6, overrunning clutch 7 by turbine 1, pump impeller 2, guide wheel 3 and to constitute differential torque converter, variable speed planetary row 8 is made of speed change gear ring 8a, variable speed planetary wheel 8b, variable speed planetary frame 8c, speed change sun gear 8d cooperation, and overrunning clutch 7 is rotatably assorted with speed change gear ring 8a.Differential attachment 4 is connected with input shaft 5, differential attachment 4 comprises differential planetary frame 4c, differential planetary gear train 4b and a pair of driving cog 4a, 4d, differential planetary gear train 4b rotation is arranged on the differential planetary frame 4c and cooperates with driving cog 4a, 4d engagement driving respectively, differential planetary frame 4c and input shaft 5 are with mode secure fit such as key are connected, and fixedly connected with guide wheel 3, driving cog 4a, interposed clutch 6, turbine 1, speed change gear ring 8a link into an integrated entity, and interposed clutch 6 can be equipped with between turbine 1, any two parts of driving cog 4a, speed change gear ring 8a.Driving cog 4d, pump impeller 2, speed change sun gear 8d link into an integrated entity, and speed change gear ring 8a, speed change sun gear 8d cooperate with the variable speed planetary wheel 8b engagement driving that rotation is arranged on the variable speed planetary frame 8c respectively.Differential torque converter output terminal is connected by variable speed planetary frame 8c and commutation planet row 12, connect on the commutation planet row 12 forward gear clutch 11 is set, the clutch 9 that reverses gear, the commutation planet row 12 be connected with output shaft 10.Commutation planet row 12 comprises commutation planet carrier 12c and commutation sun gear 12a, commutation planet wheel 12b, commutation gear ring 12d, commutation gear ring 12d and output shaft 10 are by mode secure fit such as key are connected, commutation sun gear 12a and variable speed planetary frame 8c secure fit, and cooperate with commutation planet wheel 12b, commutation gear ring 12d engagement driving respectively, commutation planet wheel 12b rotates and is arranged on the commutation planet carrier 12c.Speed change sun gear 8d two ends are rotatably assorted by same central shaft mutually with input shaft 5, output shaft 10 respectively, speed change sun gear 8d axle head and input shaft 5 sockets are rotatably assorted, speed change sun gear 8d increment and output shaft 10 sockets are rotatably assorted, and speed change sun gear 8d, input shaft 5, output shaft 10 are pressed central shaft separately and rotated.
Interposed clutch 6 travels vehicle start with the accelerator pedal interlock, and interposed clutch 6 and braking system interlock can be utilized engine braking in vehicle driving.
When forward gear clutch 11, the clutch 9 that reverses gear, when interposed clutch 6 all is in separated state, variable speed planetary row 8, commutation planet row 12, differential attachment 4 all can't be exported because of not restricting power, and the hydraulic differential speed changer is in neutral at this moment.
Work as vehicle starting, at first make the forward gear clutch 11 and clutch 9 one of them combination of reversing gear, interposed clutch 6 and accelerator pedal interlock when stepping accelerator pedal, interposed clutch 6 begins combination gradually, because output shaft 4 remains static and starting torque is very big, under the effect of overrunning clutch 7, variable speed planetary row 8 speed change gear ring 8a, worm gear 1 and driving cog 4a are static, input shaft 5 drives guide wheels 3 at this moment, pump impeller 2, driving cog 4d, speed change sun gear 8d rotates simultaneously, 10 maximum transmission ratios of setting with variable speed planetary row 8 of output shaft begin to rotate, vehicle start, pump impeller 2 at this moment, guide wheel 3 and worm gear 1 speed discrepancy maximum.
When input torque and driving torque ratio during less than the ratio of the variable speed planetary row's 8 who sets speed change gear ring 8a and speed change sun gear 8d, speed change gear ring 8a begins to rotate together with input shaft 5, make input of differential torque converter and output speed ratio level off to input torque and driving torque ratio, automobile begins to be tending towards speedup, and pump impeller 2, guide wheel 3 also reduce with ratio with the speed discrepancy of worm gear 1 at this moment.
When input torque and driving torque changed, differential torque converter input and output speed were also along with changing simultaneously, and the speed discrepancy of pump impeller 2, guide wheel 3 and worm gear 1 also reduces with ratio when input torque and driving torque ratio reduce gradually, and automobile is speedup gradually.When input torque and driving torque ratio increased gradually, pump impeller 2, guide wheel 3 also increased with ratio with the speed discrepancy of worm gear 1, and automobile slows down gradually.Realized electrodeless variable-speed this moment, pump impeller 2, guide wheel 3 and worm gear 1 have played the effect of trimming moment.
When input torque during greater than driving torque, differential attachment is not motion relatively, makes guide wheel 3, pump impeller 2, worm gear 1, variable speed planetary row 8 relatively all not have motion, and this hydraulic differential speed changer has been realized transmission in 1: 1, torque converter does not participate in work, and pump impeller 2, guide wheel 3 are zero with worm gear 1 speed discrepancy at this moment.
Claims (6)
1. hydraulic differential variable-speed case, it is characterized in that by turbine (1), pump impeller (2), guide wheel (3) and differential attachment (4), variable speed planetary row (8), interposed clutch (6), overrunning clutch (7) cooperates the differential torque converter of formation, variable speed planetary row (8) is by speed change gear ring (8a), variable speed planetary wheel (8b), variable speed planetary frame (8c), speed change sun gear (8d) cooperates formation, differential torque converter output terminal is connected with commutation planet row (12) by variable speed planetary frame (8c), commutation planet row (12) goes up to connect forward gear clutch (11) is set, clutch (9) reverses gear, differential attachment (4) is connected with input shaft (5), commutation planet row (12) is connected with output shaft (10), speed change sun gear (8d) two ends respectively with input shaft (5), output shaft (10) is rotatably assorted mutually by same central shaft.
2. hydraulic differential variable-speed case as claimed in claim 1, it is characterized in that described differential attachment (4) comprises differential planetary frame (4c), differential planetary gear train (4b) and a pair of driving cog (4a, 4d), differential planetary gear train (4b) rotate be arranged on that differential planetary frame (4c) is gone up and respectively with driving cog (4a, 4d) engagement driving cooperates, differential planetary frame (4c) and input shaft (5) secure fit, and fixedly connected with guide wheel (3), driving cog (4a), interposed clutch (6), turbine (1), speed change gear ring (8a) links into an integrated entity, driving cog (4d), pump impeller (2), speed change sun gear (8d) links into an integrated entity, speed change gear ring (8a), speed change sun gear (8d) cooperates with variable speed planetary wheel (8b) engagement driving that rotation is arranged on the variable speed planetary frame (8c) respectively.
3. hydraulic differential variable-speed case as claimed in claim 1, the planet that it is characterized in that commutating row (12) comprises commutation planet carrier (12c) and commutation sun gear (12a), commutation planet wheel (12b), gear ring (12d) commutates, commutation gear ring (12d) and output shaft (10) secure fit, commutation sun gear (12a) and variable speed planetary frame (8c) secure fit, and cooperate with commutation planet wheel (12b), commutation gear ring (12d) engagement driving respectively, commutation planet wheel (12b) rotates and is arranged on the commutation planet carrier (12c).
4. hydraulic differential variable-speed case as claimed in claim 1 is characterized in that speed change sun gear (8d) axle head and input shaft (5) socket are rotatably assorted, speed change sun gear (8d) increment and output shaft (10) socket be rotatably assorted.
5. hydraulic differential variable-speed case as claimed in claim 1 is characterized in that described interposed clutch (6) is equipped with between turbine (1), driving cog (4a), any two parts of speed change gear ring (8a).
6. hydraulic differential variable-speed case as claimed in claim 1 is characterized in that described overrunning clutch (7) and speed change gear ring (8a) are rotatably assorted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201149589U CN201145018Y (en) | 2007-09-21 | 2007-09-21 | Hydraulic differential stepless speed changer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2007201149589U CN201145018Y (en) | 2007-09-21 | 2007-09-21 | Hydraulic differential stepless speed changer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201145018Y true CN201145018Y (en) | 2008-11-05 |
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ID=40081895
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2007201149589U Expired - Fee Related CN201145018Y (en) | 2007-09-21 | 2007-09-21 | Hydraulic differential stepless speed changer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201145018Y (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100520115C (en) * | 2007-09-21 | 2009-07-29 | 黄兴隆 | Hydraulic differential continuously variable transmission |
| CN102312982A (en) * | 2010-07-07 | 2012-01-11 | 吴志强 | Composite torque limiting water medium hydraulic coupler |
| CN104482162A (en) * | 2014-12-12 | 2015-04-01 | 吴志强 | Compound box type hydraulic coupler and starter |
| CN105934611A (en) * | 2014-02-07 | 2016-09-07 | 加特可株式会社 | Control device for continuously variable transmission |
| CN106838197A (en) * | 2011-10-26 | 2017-06-13 | 卡特彼勒公司 | Buncher and the method for operating buncher |
| CN108597348A (en) * | 2018-06-28 | 2018-09-28 | 北京理工大学 | Zero differential speed type split path transmission demo system of one kind and method |
-
2007
- 2007-09-21 CN CNU2007201149589U patent/CN201145018Y/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100520115C (en) * | 2007-09-21 | 2009-07-29 | 黄兴隆 | Hydraulic differential continuously variable transmission |
| CN102312982A (en) * | 2010-07-07 | 2012-01-11 | 吴志强 | Composite torque limiting water medium hydraulic coupler |
| CN102312982B (en) * | 2010-07-07 | 2015-07-08 | 吴志强 | Composite torque limiting water medium hydraulic coupler |
| CN106838197A (en) * | 2011-10-26 | 2017-06-13 | 卡特彼勒公司 | Buncher and the method for operating buncher |
| CN106838197B (en) * | 2011-10-26 | 2019-07-05 | 卡特彼勒公司 | Stepless transmission and method for operating stepless transmission |
| CN105934611A (en) * | 2014-02-07 | 2016-09-07 | 加特可株式会社 | Control device for continuously variable transmission |
| CN104482162A (en) * | 2014-12-12 | 2015-04-01 | 吴志强 | Compound box type hydraulic coupler and starter |
| CN104482162B (en) * | 2014-12-12 | 2016-11-30 | 吴志强 | Compound box type hydraulic coupler and starter |
| CN108597348A (en) * | 2018-06-28 | 2018-09-28 | 北京理工大学 | Zero differential speed type split path transmission demo system of one kind and method |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20081105 Termination date: 20110921 |