CN1173597A - Continuously variable transmission - Google Patents
Continuously variable transmission Download PDFInfo
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- CN1173597A CN1173597A CN 96109424 CN96109424A CN1173597A CN 1173597 A CN1173597 A CN 1173597A CN 96109424 CN96109424 CN 96109424 CN 96109424 A CN96109424 A CN 96109424A CN 1173597 A CN1173597 A CN 1173597A
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Abstract
A stepless speed variator is composed of speed varying system for transferring the power generated by engine to output axle after transmission, receiving and speed variation, and speed variation regulating system for automatically regulating the speed ratio according to the load state of output axle. In the speed variation regulating system, oil pump is arranged between improved torque converter and engine. There are direct clutch, unidirectional clutch and power mode clutch to regulate speed ratio according to drive resistance and transfer power via improved torque converter to output axle. Said speed varying system uses a planetary (differential) gear system.
Description
The present invention relates to stepless speed changes devices, especially relate in the following manner the stepless speed changes devices that constitutes: during speed change gear do not break away from or alternately and the transmission of power that variable speed to driving mode and dynamic mode ground usually will input to input shaft to output shaft, retreat driving and also undertaken by very simple method.Whole gears are in coupled condition and can obtain good sensation by bus during above-mentioned common driving mode; Above-mentioned dynamic mode then can travel in the mountain area or when going up a slope, perhaps can quick starting.
All general speed change gears all be by predetermined gear than selecting a kind of speed change of carrying out in the system of selection of decision, it is pretty troublesome that gear is broken away from, so require operation careful.The belt stepless automatic transmission machine that existing automatic speed variator and part are used has similarly textural very complicated, the inconvenience of expensive funds during manufacturing is simultaneously because wearing and tearing, the noise of belt and skid and can not use in wide scope and can only use in limiting range of capacity.
As the technology that addresses the above problem have May 16 nineteen ninety-five No. the 5th, 415,597, U. S. Patent, the present invention then structure with above-mentioned patent is different.Promptly, No. 597,, in statu quo transmitted in impeller thereby directly being connected the rotating force of input shaft with input shaft at U. S. Patent the 5th, 415.But, the present invention's difference with it is: make input be directly delivered to the method for impeller and made the method that is delivered to impeller than the big turning power of input turning power by the deceleration sun gear by using by clutch, not only can transmit revolution reposefully but also bigger propelling force can be provided, bring into play good performance.
Thereby the purpose of this invention is to provide a kind of stepless speed variator, it does not have prior art complicated like that, can carry out gear shifting operation really again, not only can make rapid reaction corresponding to load variations, but also can steadily undisturbedly travel, bigger thrust is provided, give full play to its performance.
In order to achieve the above object, the present invention includes speed variator system and speed change adjust system, above-mentioned speed variator system will be delivered on the output shaft after will being accepted to transmit speed change by the power that mechanisms such as motor produce; Above-mentioned speed change adjust system then can be adjusted speed ratio automatically corresponding to the load condition of output shaft, thus can from minimum compare decide than stepless change make turning power be passed to output shaft.
The formation of above-mentioned speed variator system and speed change adjust system in brief, the major character of speed variator system is: it comprises: use as the planetary gear system of well known device or differential gearing accept to transmit the input sun gear of the power that motor produces, the 2nd planetary pinion (or the 3rd differential gear) that is integrally formed into the 1st planetary pinion (or the 1st differential gear) of input sun gear engagement, with the 1st planetary pinion (or the 1st differential gear), with the deceleration sun gear of the 2nd planetary pinion (or the 3rd differential gear) engagement.Act on the deceleration sun gear and be delivered on the impeller of speed change adjust system than the bigger turning power of commentaries on classics power that is delivered to the input sun gear by the coupling shaft that is formed at one with the deceleration sun gear.The lock that advances uses when advancing, and retreats lock or retreat planetary gear set to use when retreating.Output shaft is connected with carriage or ring gear.
The speed change adjust system is the utilization again of improved type torque converter of the torque converter of using modified known automatic speed variator, for convenience of explanation, use the term that is associated with the component parts that in existing torque converter, uses, constitute as can be known from it, it comprises: the impeller of driving body, the turbine of driven member, increase the stator of torque, oil is absolutely supplied to torque converter inside completely and will move the oily oil pump that supplies on clutch and the lock, input shaft is cut off and the direct clutch that is connected with impeller, coupling shaft is cut off and the dynamic mode clutch (or overrunning clutch) that is connected with impeller, the adjustment axle that is connected with turbine, fixing housing.
Be applicable to the clutch of speed variator system and change control system and many plates wet clutch and the lock that lock can be not limited to use known automatic speed variator, perhaps use the band clutch.
The operating method of the stepless speed changes devices of above-mentioned formation mainly contains three kinds.
First kind of stepless change method is can obtain stably sensation by bus at common driving mode (I advances), and the most fuel-efficient.
Second kind of stepless change method is can travel during in the mountain area or when going up a slope or at the needs emergency starting at dynamic mode (II advances).
The third method is to obtain best power performance in conjunction with above-mentioned two kinds of patterns.
The features and advantages of the present invention are as mentioned above: the power performance that this stepless speed changes devices can be as requested and travelling.
Below, describe with regard to change control system of the present invention, the stepless speed changes devices that connects and composes corresponding to all embodiments' speed variator system.That is, speed variator system can be made of multiple mode, suitably connects and composes the speed change adjust system thus and carries out stepless change.
Followingly describe with reference to accompanying drawing, component identical among the figure use identical label, among the figure:
Fig. 1 is the assembling sectional view of the speed change adjust system of stepless speed changes devices of the present invention.
Fig. 2 to Fig. 6 is the 1st embodiment of stepless speed changes devices of the present invention.
Fig. 2 is the 1st embodiment's an assembling sectional view.
Fig. 3 represents the sectional view of stepless speed changes devices of the present invention idling conditions when neutral condition.
Fig. 4 is the advance sectional view of I state of expression, when this state was the direct clutch action that links with input shaft on stepless speed changes devices of the present invention, input power was separated on the impeller of the speed change adjust system that links to each other with direct clutch with the input sun gear and is delivered on the input shaft.
Fig. 5 is the advance sectional view of II state of expression, this state is that the action of the direct clutch that links with input shaft on stepless speed changes devices of the present invention is when removing, input power is increased by the 2nd planetary pinion and deceleration sun gear by means of the input sun gear, and this power is delivered on the output shaft through the impeller that overrunning clutch acts on change control system by coupling shaft again.
Fig. 6 represents the sectional view of the fallback state of stepless speed changes devices of the present invention.
Fig. 7 to Figure 11 is the 2nd embodiment of stepless speed changes devices of the present invention.
Fig. 7 is the 2nd embodiment's an assembling sectional view.
Fig. 8 is for representing the sectional view of the state that stepless speed changes devices of the present invention dallies when neutral condition.
Fig. 9 is for the advance sectional view of I state of expression, at this state, during the direct clutch action that is connected with input shaft input power with the impeller of importing the change control system that sun gear is connected with direct clutch on separate and be delivered on the output shaft.
Figure 10 is the advance sectional view of II state of expression, at this state, when the action of the direct clutch that is connected with input shaft is removed, input power is increased by the 2nd planetary pinion and deceleration sun gear by the input sun gear, and this power acts on change control system by coupling shaft through overrunning clutch again and is delivered on the output shaft.
Figure 11 is the sectional view of expression fallback state.
Figure 12 A to Figure 16 is the 3rd embodiment of stepless speed changes devices of the present invention.
Figure 12 A is the 3rd embodiment's an assembling sectional view.
Figure 12 B is the expansion sectional view along the I-I line among Figure 12 A.
Figure 13 represents the sectional view of neutral condition.
Figure 14 is for the advance sectional view of I state of expression, at this state, when the direct clutch action that is connected with input shaft input power with the impeller of importing the change control system that sun gear is connected with direct clutch on separate and be delivered on the output shaft.
Figure 15 is the advance sectional view of II state of expression, at this state, when the action of the direct clutch that is connected with input shaft is removed, input power is increased by the 3rd differential gear and deceleration sun gear by the input sun gear, and this power acts on the speed change adjust system by coupling shaft by overrunning clutch and is delivered to output shaft.
Figure 16 represents the sectional view of fallback state.
Figure 17 to Figure 21 is the 4th embodiment of stepless speed changes devices of the present invention.
Figure 17 is the 4th embodiment's an assembling sectional view.
Figure 18 is the sectional view of expression neutral condition.
Figure 19 is for the advance sectional view of I state of expression, at this state, when the direct clutch action that is connected with input shaft input power with the impeller of importing the change control system that sun gear is connected with direct clutch on separate and be relayed on the output shaft.
Figure 20 is the advance sectional view of II state of expression, at this state, when the action of the direct clutch that is connected with input shaft is removed, input power is increased by the 3rd differential gear and deceleration sun gear by the input sun gear, and this power acts on change control system by coupling shaft by overrunning clutch and is delivered to output shaft.
Figure 21 is the sectional view of fallback state.
Figure 22 to Figure 26 is the 5th embodiment of stepless speed changes devices of the present invention.
Figure 22 is the 5th embodiment's an assembling sectional view.
Figure 23 is the sectional view of neutral condition.
Figure 24 is for the advance sectional view of I state of expression, at this state, when the direct clutch action that is connected with input shaft input power with the impeller of importing the speed change adjust system that sun gear is connected with direct clutch on separate and be delivered on the output shaft.
Figure 25 is the advance sectional view of II state of expression, at this state, when the action of the direct clutch that is connected with input shaft is removed, input power is increased by the 2nd planetary pinion and deceleration sun gear by the input sun gear, and this power acts on the speed change adjust system by coupling shaft by overrunning clutch and is delivered to output shaft.
Figure 26 is the sectional view of fallback state.
Figure 27 is the skeleton diagram to Fig. 2 formation of the 1st embodiment of the present invention.
Figure 28 is the skeleton diagram to Fig. 7 formation of the 2nd embodiment of the present invention.
Figure 29 is the skeleton diagram to Figure 12 A formation of the 3rd embodiment of the present invention.
Figure 30 is the skeleton diagram to Figure 17 formation of the 4th embodiment of the present invention.
Figure 31 is the skeleton diagram to Figure 22 formation of the 5th embodiment of the present invention.
At first for change control system (10), speed variator system (110) and connect and compose according to drawing and describe the 1st embodiment of the present invention (100) in detail.
Change control system (10)
Change control system (10) has been used the torque converter as the automatic speed variator of well known device, common automatic speed variator is that oil pump is arranged between torque converter and the speed variator system, and constitutive characteristic of the present invention is oil pump is arranged on the position between torque converter and the motor.Common automatic speed variator is delivered on the input shaft of variable-speed motor through making driving force behind the torque converter by the power that motor produces.And in the present invention, the transmission method that two kinds of turning powers are then arranged, the first: the power that is produced by motor is directly delivered to input shaft, and the part in the turning power in the input shaft separately is delivered to turning power on the impeller by direct clutch plate and the direct clutch that links into an integrated entity with input shaft; It two is: by coupling shaft, by being arranged at the overrunning clutch between coupling shaft and the impeller housing or the action of dynamic mode clutch turning power is delivered on the impeller when direct clutch is removed.The torque converter of common automatic speed variator has the transmission of power function that directly transmission of power that produces in the motor is arrived the input shaft of variable-speed motor, in contrast, the present invention then has two characteristics, the first with drive the resistance ratio of consistently regulating the speed, it two is will be through the transmission of power of torque converter to output shaft.
Formation to change control system (10) is elaborated below.Shown in Fig. 1 and 2, on the section 1 (12A) of the input shaft of forming by 3 parts (12A, 12B, 12C) (12), oil pump (14) is set.The actuation gear of oil pump (16) is connected and fixed by spline (18S) and input shaft (12).Actuation gear of oil pump (16) and driven gear (20) are located in the oil pump case 22.Between oil pump case 22 and input shaft, insert bearing 24B, 24B ' are set, insert in the place adjacent and oil sealing 26C, 26C ' are set to prevent the oil leakage in the pump with bearing 24B, 24B '.Oil pump case 22 sealings are assemblied on the fixing housing 28.
On coupling shaft 34 and adjustment axle 38, be provided with the improved type torque converter coaxially.Between impeller housing 42 with the 1st end 42A and the 2nd end 42B and coupling shaft 34, have dynamic mode clutch 44 and overrunning clutch 48, the interior wheel of overrunning clutch 48 is fastened on the coupling shaft 34 by spline 50S.The direction that is provided with of overrunning clutch 48 is not provided with impeller housing 42 pivotally on the direction opposite with the gyratory directions of coupling shaft 34.Dynamic mode clutch 44 has makes impeller housing 42 cut off and the function that is connected with coupling shaft 34.And overrunning clutch 48 prevents that impeller housing 42 from the direction revolution opposite with the gyratory directions of input shaft, making from coupling shaft 34 and transmitting next transmission of power to impeller housing 42.And binding is provided with direct clutch between impeller housing 42 and direct clutch plate 30, and direct clutch has cuts off and the functions that are connected impeller housing 42 and direct clutch plate 30.
And the setting method of direct clutch, dynamic mode clutch, specifying of position etc. is set omits herein, such formation that is provided with does not limit scope of the present invention.
The part of the oil of discharging at oil pump 14 is by through oil hole 74 and suck path 76 and enter torque converter inside and make torque converter inside absolutely be full of oil, the oil of torque converter inside is cooled off by the Coolers that is positioned at the variable-speed motor outside by drain passageway 78 and oily exhaust port 80, enters oil pump afterwards again.And the part oil of discharging in the oil pump 14 is supplied to as the action oil of the clutch of direct clutch 52, dynamic mode clutch 44, other speed variator system and lock etc.At this, because oily drain passageway and exhaust port also can form on stationary axle, and also can there be different changes through oil hole and the position etc. that sucks path, therefore is not limited only to above-mentioned position and formation certainly.And, in order to carry out transmission of power, make clutch connecting plate 82 be connected the 2nd end 38B that adjusts axle 38 integratedly by spline 86S with speed variator system.
Speed variator system 110
The present invention the 1st embodiment's speed variator system 110 as shown in Figure 2, the power of motor is input on the input shaft 12, forms input sun gear 112 between the part 2 12B of input shaft 12 and the 3rd part 12C.On the part 2 12B of input shaft coaxially, on input shaft 12, can support the coupling shaft 34 of hollow freely pivotally by bearing 36B, 36B '.On the 2nd end 34B of coupling shaft 34, be and form deceleration sun gear 116 with coupling shaft 34.Carriage 118 is contained on this coupling shaft 34, and makes between coupling shaft 34 and the carriage 118 and mutually bearing 120B can be set freely to rotate.And the carriage 124 with inside diameter 124A is set on the 3rd part 12C of input shaft 12, between input shaft the 3rd part 12C and carriage 124, can inserts pivotally freely mutually bearing 126B is set.And insertion is provided with a plurality of fixing pins 128 and makes it fixing between two carriages 118,124 for two carriages 118,124 can be turned round jointly.
The 1st planetary pinion 130 and the 2nd planetary pinion 132 of mutual formation one are set on each fixing pin 128, between the 1st planetary pinion 130 and the 2nd planetary pinion 132, form recess 134, for these dual planetary gears 130,132 turn rounds freely, insertion is provided with bearing 130B, 132B between fixing pin 128 and dual planetary gear 130,132.In the inboard and 116 engagements of deceleration sun gear of the 2nd planetary pinion 132, then mesh with the gear ring 136 that advances in the outside.Certainly, the gear ring 136 that advances is inserted freely pivotally between coupling shaft 34 bearing 136B is set.And, in the inboard and 112 engagements of input sun gear of the 1st planetary pinion 130.Output shaft 138 and carriage 124 coaxial forming.
On the other hand, coaxial hollow is set on output shaft 138 retreats input shaft 140, for make output shaft 138 and retreat between the input shaft 140 revolution freely, insert bearing 140B, 140B ' be set.Make to retreat sun gear 144 and form retreating on the end 142 of input shaft 140, and on the other end 146, make by spline 148S to retreat connecting plate 150 and connect.And setting retreats carriage 152 on output shaft 138, for its revolution is inserted freely bearing 152B is set.Be provided with and retreat carriage 154 retreating sun gear 144 and retreat retreating on the input shaft between the connecting plate 150, bearing 154B is set for making to retreat carriage 154 and retreat to turn round between the input shaft 140 to insert freely.For two carriages 152,154 are turned round jointly, a plurality of fixing pins 156 are inserted be fixed between two carriages 152,154.
On each fixing pin 156, insert setting and retreat planetary pinion 158, bearing 158B is set for making to retreat to turn round freely between planetary pinion 158 and the fixing pin 156 to insert.Make and retreat gear ring 160 and make it to be connected integratedly with output shaft 138 with the outside engagement that retreats planetary pinion 158 and by spline 162S.Certainly retreating sun gear 144 is meshed with the inboard that retreats planetary pinion 158.And connect clutch plate 82 and retreat the hollow clutch coupling shaft 164 of connecting plate 150 in the arranged outside of gear ring 136, forward clutch 166 is set with advancing to be connected between the gear ring 136 at clutch coupling shaft 164.At the arranged outside overrunning clutch 170 of clutch coupling shaft 164, prevent that clutch coupling shaft 164 is in the direction revolution opposite with the input gyratory directions.Retreat lock 172 in the arranged outside that retreats carriage 154.
And, omit forward clutch 166, the setting method of clutch coupling shaft 164 and overrunning clutch 170, the specifying of constituent relation etc., this set constitutes the scope of the present invention that do not limit.
To describe the method for operating of stepless speed changes devices of the present invention below in detail.
The first, the occasion of common driving mode
Input separates at direct clutch plate 30 that is connected with the input shaft one and input sun gear 112, the part of input acts on the impeller 56 when direct clutch 52 actions that are arranged between direct clutch plate 30 and the impeller 56, consequently, the turning power that makes a ratio act on the turning power multiplication on the impeller 56 owing to the speed discrepancy as the turbine 58 of common torque transmission function and impeller 56 acts on the turbine 58 and is delivered on the adjustment axle 38 that is connected with turbine 58.When the resistance that the load on adjusting axle 38 is reduced the resistance that makes impeller 56 and turbine 58 reaches balance, the revolution ratio of turbine 58 and impeller 56 is necessary for 1: 1, owing to oily loss can not get hundred-percent efficient, so also should append during with common torque converter lock-up clutch is set in torque converter inside, and in the present invention, the dynamic mode clutch 44 of simple structure is arranged on impeller 56 and the coupling shaft 34, is moved simultaneously by direct clutch 52 and dynamic mode clutch 44 and obtains lock function.(lock function is to instigate impeller to be connected with turbine with being integral.)
The second, the occasion of dynamic mode
At this moment, the action of the direct clutch 52 that is connected with input shaft 12 is disengaged and overrunning clutch 48 actions.By input sun gear 112, power is divided into two-part, a part is delivered on the output shaft 138 by the 1st planetary pinion 130 of speed variator system, another part then is delivered to the 1st planetary pinion 130 and is on the deceleration sun gear 116 of the 2nd planetary pinion 132 engagements that form, and an input this moment part is doubled and is delivered on the impeller 56 by coupling shaft 34 and overrunning clutch 48.Producing the turning power bigger than the turning power that acts on impeller 56 at above-mentioned common driving mode is passed on the adjustment axle 38.Lock function is identical with above-mentioned common driving mode.
The 3rd, the situation that common driving mode is parallel mutually with dynamic mode
Explanation in two kinds of situation: (1) converts dynamic mode to common driving mode; (2) convert common driving mode to dynamic mode.
In (1) kind situation direct clutch 52 is connected.
Because built-in overrunning clutch 48 between coupling shaft 34 and impeller housing 42, the rotating speed of coupling shaft 34 rotating speed than input shaft 12 usually is little, institute is so that direct clutch 52 actions, when the direct clutch plate of being assembled by spline on input shaft 12 was connected with impeller housing, coupling shaft 34 was owing to overrunning clutch 48 dallies.
In (2) kind situation direct clutch 52 is removed.
Method of operating and the power transmission process corresponding when the following describes each speed change state (neutral, advance, retreat) of stepless speed changes devices of the present invention the 1st embodiment of this formation with it.
At first explanation, stepless speed changes devices of the present invention can be used for exporting after the driving force speed change of automobile and industrial machinery etc., but only are that example describes with the automobile herein.
About the definition of term, the rotation of each planetary pinion (or differential gear) is meant the revolution for himself axle (being fixing pin herein); Revolving round the sun then is meant under the rotating situation of carriage, Yi Bian carry out concurrently going forward side by side with common rotation, Yi Bian turn round jointly with carriage.
And for convenience of description, when the left side of figure was seen, along the direction of the rotating direction of counterclockwise direction as input shaft, the direction identical with the direction of this input shaft was defined as on each drawing ↑ direction (or A direction); Similarly the side with input shaft then is defined as ↓ direction (or B direction) in the opposite direction; (acceleration mode) usefulness O. when stopping back the revolution ↑ (or O. ↓) expression; Stop after the revolution (deceleration regime) usefulness ↑ .O (or ↓ .O) expression; Usefulness ↑ .1 when planetary pinion (or differential gear) revolution continues back fast state (that is, not from transferring all solid of rotation turn state integratedly) (or ↓ .1) expression.
1. neutral condition (Fig. 3): output shaft 138 stops
-retreat carriage 152,154 ↑: (idle running)
Neutral condition is the state of removing direct clutch 52, dynamic mode clutch 44, forward clutch 166 simultaneously and retreating lock 172, and the power of motor can not make output shaft 138 revolution, i.e. idling conditions as shown in Figure 3.
Promptly, when output shaft 138 loads, the carriage 124 that forms with output shaft 138, carriage 118 and be stopped by the gear ring 160 that retreats that spline 162S and output shaft 138 are fixed, when importing the power of motor, input shaft 12 revolution on one side, the input sun gear 112 that is integrally formed into input shaft 12 is also along same direction A revolution, and the direct clutch plate 30 that is connected with input shaft 12 by spline 32S is owing to the releasing of direct clutch 52 is dallied.
Because 112 revolutions of input sun gear make and the 1st planetary pinion 130 edges direction B revolution opposite with the gyratory directions of input sun gear 112 of importing sun gear 112 engagements.Thereby the 2nd planetary pinion 132 that is formed at one with the 1st planetary pinion 130 also turns round with direction B, with the gear ring 136 1 edge B directions revolutions of advancing of the 2nd planetary pinion 132 engagements, on one side owing to the releasing of forward clutch 166 is dallied.Turn round along the A direction opposite with the deceleration sun gear 116 of the 2nd planetary pinion 132 engagements with the gyratory directions of the 2nd planetary pinion 132.By means of and deceleration sun gear 116 overrunning clutch 48 that forms the coupling shaft 34 of one, between coupling shaft 34 and impeller housing 42, be provided with, make impeller housing 42 along A direction revolution, thereby also turn round along the A direction with impeller 56 that impeller housing 42 is formed at one.
Owing to fluid mobile makes turbine 58 that relative impeller 56 is provided with also with the revolution of A direction, the adjustment axle 38 that is connected with turbine 58, also turn round along the A direction with adjustment 38 clutch plate that are connected 82, the clutch shaft 164 that is connected with clutch connecting plate 82 and the sun gear 144 that retreats that is connected with clutch coupling shaft 164.Turn round along the B direction with the planetary pinion 158 that retreats that retreats sun gear 144 engagements.Stop, retreating carriage 152,154 1 edge A direction revolutions with the gear ring 160 that retreats of the outside engagement that retreats planetary pinion 158 owing to being connected with output shaft 138, on one side owing to the releasing that retreats lock 172 is dallied through spline 162S.
2. the advance speed change state (Fig. 4) of I (usually driving mode)
(2)
(1) impeller 56 ↑-turbine 58 O. ↑-adjust axle 38 O. ↑-clutch coupling shaft 164 O. ↑-(forward clutch)-gear ring 136 O. that advance ↑ the-the 2nd planetary pinion 132 ↑ .1-frame 118.124 O. ↑-clutch coupling shaft 164 O. ↑-forward clutch-gear ring 136 O. that advance ↑-
138?O.↑
Infinite variable speed process from rudimentary to senior as can be known, the power that is delivered to the motor on the input shaft 12 is separated on direct clutch plate 30 and the input sun gear 112, make direct clutch 52 and forward clutch 166 actions simultaneously in neutral condition (Fig. 3), so owing to making impeller housing 42 along the A direction revolution identical with input direction with the direct clutch plate 30 of input shaft 12 connections and the action of direct clutch 52.And the impeller 56 that forms with impeller housing 42 also turns round along the A direction.
On the other hand, the input sun gear 112 that is formed at one with input shaft 12 is along the A direction revolution identical with input shaft 12, turn round along the B direction with the 1st planetary pinion 130 of input sun gear 112 engagements.The 2nd planetary pinion 132 that is formed at one with the 1st planetary pinion 130 also turns round along the B direction.With the deceleration sun gear 116 of the inner mesh of the 2nd planetary pinion 132 along the revolution of A direction, the coupling shaft 34 that is formed at one with deceleration sun gear 116 also turns round along the A direction.Impeller housing 42 is with the winding number revolution identical with input shaft 12, coupling shaft 34 since the 2nd planetary pinion 132 and deceleration sun gear 116 always with the rotating speeds revolution little or more identical than input sun gear 112, so because overrunning clutch 48, coupling shaft 34 always dallies.
In immediately, since the turbine 58 that the mobile phase of fluid is provided with for impeller 56 along the A direction revolution identical with impeller 56, with the gear ring 136 that advances of the outside engagement of the 2nd planetary pinion 132 be in along with the reverse B direction idle running of input shaft 12, but when making forward clutch 166 actions, suppress revolution to the B direction by the overrunning clutch on the external diameter that is arranged at clutch coupling shaft 164 170,136 moments of gear ring of advancing stop.In a single day the gear ring 136 that advances stops, the clutch shaft 164 that is connected by forward clutch, the clutch plate 82 that is connected with clutch coupling shaft 164, the adjustment axle 38 that is connected with clutch plate 82 and just be endowed resistance with an adjustment turbine 58 that is connected.In immediately with the rotating equidirectionally turbine 58 of impeller 56 owing to this resistance reduce the revolution or stop, thereby produced speed discrepancy between impeller 56 and the turbine 58.
Because the characteristic of torque converter, speed discrepancy between impeller 56 and the turbine 58 is big more, the turning power that produces is also big more and be delivered on the turbine 58, thereby be delivered on this turbine 58 turning power since the effect of the load of output shaft 138 and with act on resistance on the turbine 58 when balancing each other, just drive output shaft 138, be the low speed starting state this moment.
After making the revolution increase of motor, because impeller 56 becomes big with the speed discrepancy of turbine 58, the turning power that is delivered to turbine is increased, the turning power that is delivered to turbine 58 is because the load effect of output shaft 138 and during greater than the resistance that acts on the turbine, the rotating speed of output shaft increases, when the turning power of the turbine that is transmitted by impeller 56 balances each other with the resistance that acts on turbine.
If output shaft 138 is accelerated, the load of output shaft 138 just reduces so, so the resistance that acts on the turbine 58 also reduces.If the resistance that acts on the turbine 58 reduces, so until with this resistance balance, impeller 56 also reduces with the speed discrepancy of turbine 58.Thereby the revolution of turbine 58 is an A direction and increasing in the direction identical with impeller 56, and linking the advance revolution of gear ring 136 of all-in-one-piece with turbine also increases along the A direction.That the load of output shaft 138 becomes is littler, when balancing each other with the driving force of input shaft 12, impeller 56 turns round with 1: 1 ground with turbine 58, the 1st planetary pinion 130 and the 132 not rotations of the 2nd planetary pinion but whole solid of rotation turns round (revolution) with being integral.Be fast state this moment.
Above-mentioned present embodiment (other embodiment described later is also identical) is characterised in that the load according to output shaft carries out stepless change to the gear ratio of necessity.
Usually the loss owing to the oil in the torque converter between impeller and turbine can not get impeller and 1: 1 hundred-percent efficient of turbine.And the present invention has such characteristics: make dynamic mode clutch 44 move and can prevent because the efficient reduction that the loss of oil causes.
3. the advance speed change state (Fig. 5) of II (dynamic mode)
(1) the 2nd planetary pinion 132 ↓ .1-deceleration sun gear 116 ↑-coupling shaft 34 ↑-(overrunning clutch 48)-impeller housing 42 ↑-impeller 56 ↑-turbine 58 O. ↑-adjustment axle 38 O. ↑-clutch coupling shaft 164 O. ↑-(forward clutch)-gear ring 136 O. that advance ↑ the-the 2nd planetary pinion 132
With the speed change state of the common driving mode of the above-mentioned I that advances relatively, the gyratory directions of each product is identical with the stepless change process, still is delivered to the power transfer path difference of impeller 56.In forward clutch 166 action immediately, or forward clutch 166 and dynamic mode clutch 44 moved simultaneously and become the speed change state of dynamic mode.The action that only relates to forward clutch 166 herein describes.
Be formed at the input sun gear 112 of one along input shaft 12 same direction A revolutions with input shaft, turn round along the B direction with the 1st planetary pinion 130 of input sun gear 112 engagements, the 2nd planetary pinion 132 that is formed at one with the 1st planetary pinion 130 also turns round along the B direction.With the deceleration sun gear 116 of the inner mesh of the 2nd planetary pinion 132 in the revolution of slowing down of A direction, the coupling shaft 34 that is formed at one with deceleration sun gear 116 also turns round in the A direction.Impeller housing 42 turns round in the A direction owing to overrunning clutch 48.Between impeller housing 42 and coupling shaft 34, and also turn round along the A direction with impeller 56 that impeller housing 42 is formed at one.
In immediately, because flowing of fluid, the turbine 58 that makes with respect to impeller 56 and be provided with is along the direction A revolution identical with impeller 56, be in along the time with the gear ring 136 that advances of the outside of the 2nd planetary pinion 132 engagement with the state of the opposite direction B idle running of input shaft 12, make forward clutch 166 actions, so owing to the effect of the overrunning clutch 170 of the external diameter that is arranged at clutch coupling shaft 164 suppresses revolution to the B direction, 136 moments of forward clutch just stop.In a single day the gear ring 136 that advances stops, and the coupling shaft 164 that forward clutch connects, the clutch connecting plate 82 that is connected with coupling shaft 164, the adjustment axle 38 that is connected with clutch connecting plate 82 and a turbine 58 that is connected with the adjustment axle just are endowed resistance.In reduce owing to this resistance with 58 of impeller 56 equidirectional rotating turbines immediately or stop, so and produce speed discrepancy between impeller 56 and the turbine 58.
Because the characteristic of torque converter, the big more turning power of the big more just generation of the speed discrepancy of impeller 56 and turbine 58, and be delivered on the turbine 58, so, the turning power that is delivered to this turbine 58 is with regard to because the effect of the load of output shaft 138 and when acting on resistance on the turbine 58 and balance each other, output shaft 138 is driven.Be the low speed starting state this moment.
When making the revolution increase of motor, because it is big that the speed discrepancy of impeller 56 and turbine 58 becomes, the turning power that is delivered on the turbine also increases, be delivered to turning power on the turbine 58 because the load of output shaft 138 and output shaft 138 is quickened during greater than the resistance that acts on turbine, until till the turning power of the turbine of impeller transmission is when acting on resistance on the turbine and balance.
When output shaft 138 was quickened, because the load of output shaft 138 reduces, the resistance that acts on the turbine 58 also reduced.Act on the resistance on the turbine in case reduce, till the speed discrepancy of impeller and turbine 58 also reduces when balancing each other with this resistance.Thereby the revolution of turbine 58 increases at the direction A identical with impeller 56, and the revolution of the gear ring 136 that advances that links into an integrated entity with turbine also increases in the A direction.That the load of output shaft 138 becomes is littler, with the driving force balance of input shaft 12 time, impeller 56 is 1: 1 rotating speed revolution with turbine 58, the 1st planetary pinion 130 and the 2nd planetary pinion 132 from then whole solid of rotation do not turn round with being integral.Be fast state this moment.At this fast state, because the loss of the oil between impeller 56 and the turbine 58, and the impeller 56 and the rotating ratio of turbine 58 were not reached 1: 1, input also can not get 1: 1 hundred-percent efficient with the ratio of output, dynamic mode clutch 44 and direct clutch 52 are moved simultaneously, then since input shaft 12 and output shaft 138 become one, thereby can obtain hundred-percent efficient.
At present embodiment, from be delivered on the impeller 56 turning power as can be known, the turning power that turning power than input shaft 12 is increased owing to the effect of the 2nd planetary pinion 132 and deceleration sun gear 116 is delivered on the impeller by coupling shaft 34, so be delivered on the turbine than the big turning power of turning power that when the speed change of aforementioned normal mode, is delivered on the turbine, thereby drive output shaft with big turning power during low speed, to improve acceleration and efficient.
4. fallback state (Fig. 6)
In fallback state, remove direct clutch 52 and forward clutch 166, make dynamic mode clutch 44 and retreat lock 172 actions.The input sun gear 112 that the power of motor links into an integrated entity from input shaft 12 input back and input shaft 12 is along the direction A revolution identical with input shaft 12, turns round along the direction A opposite with input sun gear 112 with the 1st planetary pinion 130 of input sun gear 112 engagements.The 2nd planetary pinion 132 that is one with the 1st planetary pinion 130 also turns round along the B direction, and the gear ring 136 that advances that meshes with the outside of the 2nd planetary pinion 132 also dallies along the B direction.With the deceleration sun gear 116 of the inner mesh of the 2nd planetary pinion 132 along with the opposite direction A revolution of the 2nd planetary pinion 132.The coupling shaft 34 that is connected with deceleration sun gear 116, the impeller housing 42 that is connected with coupling shaft by dynamic mode clutch 44 or overrunning clutch 48, be formed at one with impeller housing impeller 56 with the revolution of A direction, because the effect turbine 58 of impeller 56 also turns round along the A direction.
The adjustment axle 38 that is connected with turbine 58, with adjust the clutch connecting plate 82 that axle is connected, the clutch coupling shaft 164 that is connected with the clutch connecting plate, be connected with the clutch coupling shaft retreat connecting plate 150, with retreat that connecting plate is connected retreat input shaft 140, and retreat the sun gear 144 that retreats that input shaft is formed at one and also turn round along the A direction.With retreat sun gear 144 engagement retreat planetary pinion 158 along the revolution of B direction, also turn round along the B direction with the gear ring 160 that retreats of the outside engagement that retreats planetary pinion 158.Retreat gear ring 160 owing to is connected with output shaft 138, so output shaft 138 edges and input shaft 12 opposite directions are that the B direction is turned round by spline 162S.
The following describes the 2nd embodiment of the present invention.
In the 2nd embodiment 200 of stepless speed changes devices of the present invention, since change control system structure is set and method of operating identical with the 1st embodiment's change control system 10, so omit the formation of change control system 10 and the explanation of method of operating, and at first just for the 2nd embodiment's speed variator system 210 relatively the difference part of the 1st embodiment on formation describe.
The speed variator system 210 of the 2nd embodiment's of the present invention stepless speed changes devices constitutes as illustrated in fig. 7.With the 1st embodiment's comparison with regard to it is provided with structure, form with the output gear 214 and the output shaft 138 of the outside of the 1st planetary pinion 212 engagement.(being formed at one with output shaft 138) at the 1st embodiment's carriage 124, owing to retreating the forward clutch 218 that is provided with the usefulness of advancing between carriage 216 and the clutch connecting plate 82, so there is not the gear ring that advances among the 1st embodiment.And, owing to retreat lock 222 in the arranged outside that retreats carriage 216, so just do not needed for the independent planetary gear system that retreats as the 1st embodiment in order to retreat.
And constitute from other, on the 3rd part 12C of input shaft 12, be provided with and retreat carriage 226, and can insert with freely rotating to be provided with and hold 226B together, and on coupling shaft 34, setting retreats carriage 216 with freely rotating by means of bearing 216B, inserts fixing many fixing pins 228 for two carriages 216,226 are turned round simultaneously.Then, mutual all-in-one-piece the 1st planetary pinion 212 and the 2nd planetary pinion 230 are set on each fixing pin 228, between them, form recess 232 and this dual planetary gear 212,230 is inserted with freely rotating bearing 212B, 230B are set.Between the 3rd part 12C of output gear 214 with inside diameter 234 and input shaft 12, insert bearing 236B with freely rotating.
Be the method for operating and the power transmission process thereof of each speed change state (neutral, advance, retreat) of the 2nd embodiment's of the present invention stepless speed changes devices below.
1. neutral condition (Fig. 8): output shaft 138 stops
(1) the 2nd planetary pinion 230 ↓-deceleration sun gear 116 ↑-impeller 56 ↑-turbine 58 ↑-clutch connecting plate 82 ↑: (idle running)
Neutral condition is to make direct clutch 52, forward clutch 218, retreat the state that lock 222 is removed simultaneously, and the power of motor does not make output shaft 138 revolutions, is in the state of idle running as shown in Figure 8.
Promptly, if on output shaft 138, load is arranged, the output gear 214 that is formed at one with output shaft 138 just is stopped so, if the power of input motor, input shaft 12 revolution on one side so, 30 of direct clutch plates that links into an integrated entity with input shaft 12 are dallied by the releasing of direct clutch 52, the input sun gear 112 that is formed at one with input shaft 12 is the revolution of A direction along the direction identical with input shaft 12, turn round along the B direction with the 1st planetary pinion 212 of input sun gear 112 engagements, the 2nd planetary pinion 230 that is formed at one with the 1st planetary pinion 212 also turns round along the B direction.Owing to remove forward clutch 218 and retreat lock 222, retreat carriage 216 and dally along the A direction.
Turn round along the A direction with the deceleration sun gear 116 of the 2nd planetary pinion 230 engagements, the coupling shaft 34 that is formed at one with deceleration sun gear 116 also turns round along the A direction, turn round along the A direction by means of the overrunning clutch 48, the impeller housing 42 that are arranged between coupling shaft 34 and the impeller housing 42, the impeller 56 that is formed at one with impeller housing also turns round along the A direction.
Owing to the mobile phase of fluid is also turned round along the A direction for the turbine 58 that impeller 56 is provided with, the adjustment axle 38 that is connected with turbine 58, the clutch connecting plate 82 1 edge A directions revolutions that are connected with the adjustment axle are simultaneously owing to the releasing of forward clutch 218 is dallied.
2. the advance speed change state (Fig. 9) of I (usually driving mode)
(1) impeller 56 ↑-turbine (58) O. ↑-adjust axle (38) O. ↑-(forward clutch)-retreat carriage 216,226 ↑ the-the 1st planetary pinion 212 ↓ .1
If make direct clutch 52 and forward clutch 218 moves simultaneously, to make impeller housing 42 be the revolution of A direction along the direction identical with input direction to the action by the direct clutch plate 30 that connects with input shaft 12 and direct clutch 52 so in neutral condition (Fig. 8).
On the other hand, the input sun gear 112 that is formed at one with input shaft 12 along and the A direction revolution of input shaft equidirectional, turn round along the B direction with 212 of the 1st planetary pinions of input sun gear 112 engagements.The 2nd planetary pinion 230 that is formed at one with the 1st planetary pinion 212 also turns round along the B direction, and the deceleration sun gear 116 that meshes with the 2nd planetary pinion then turns round along the A direction.The coupling shaft 34 that is connected with the deceleration sun gear also turns round along the A direction.Because the revolution of deceleration sun gear is always little than the revolution of input sun gear, be connected with input shaft 12 and the revolution revolution than coupling shaft 34 always of rotating impeller housing 42 is big, so coupling shaft 34 is owing to overrunning clutch 48 dallies.
In neutral condition be the idle running of A direction because fluid mobile makes the turbine 58 that is provided with respect to impeller 56 along the direction identical with impeller 56, retreat carriage 216,226 since stopping of output gear 214 and with planetary fixedly than dallying along the A direction.At this state, if make forward clutch 218 action, the load of output shaft 138 is given turbine by retreating carriage 216,226 with resistance so, suppresses the revolution of turbine, so, be delivered on the turbine after the turning power of impeller is increased owing to produce big speed discrepancy at impeller 56 and turbine 58.The turning power of this turbine 58 acts on the resistance of turbine when big than the load by output shaft 138, drives output shaft 138.Be the low speed starting state this moment.
Below, the explanation of stepless change process from low speed to high speed is because identical with the speed change state of the 1st embodiment's the I that advances (driving mode usually), so omit.
3. the speed change state (Figure 10) of protrusive II (dynamic mode)
(1) the 2nd planetary pinion (230) ↓ .1-deceleration sun gear 116 ↑-coupling shaft 34 ↑-
-(overrunning clutch)-impeller housing 42 ↑-impeller 56 ↑-
-turbine (58) O. ↑-adjustment axle (38) O. ↑-(forward clutch)-
Retreat carriage 216,226 ↑ the-the 1st planetary pinion 212 ↓ .1-
If in 218 actions of neutral condition forward clutch, forward clutch 218 and dynamic mode clutch 44 are moved simultaneously, so just become the speed change state of dynamic mode.Relatively the time, the gyratory directions of each parts is all identical with the stepless change process with the speed change state of the common driving mode of the above-mentioned I that advances, but the power transfer path that is delivered on the impeller is then different.By removing direct clutch 52, just idle running of the direct clutch plate that is connected with input shaft 12 30,34 of coupling shafts that are formed at one with deceleration sun gear 116 are delivered to impeller housing 42 with turning power along the A direction by overrunning clutch 48 (or action of dynamic mode clutch 44).
Below, stepless change process and action are identical with the common driving mode of the above-mentioned I that advances.
4。Fallback state (Figure 11)
Input shaft 121-output sun gear 112 ↑ the-the 1st planetary pinion 212 ↓-
Clutch connecting plate 82 ↑: (idle running)
Constitute not independent the retreating planetary gear system as the 1st embodiment retreating of present embodiment, and setting retreats lock 222 on the carriage 216 retreating.Retreat lock 222 action then become fallback state if make in neutral condition.
If the power of motor is by input shaft 12 inputs, the input sun gear 112 that links into an integrated entity with input shaft 12 so is the revolution of A direction along the direction identical with input shaft 12 just, and the direction opposite with sun gear with 212 edges of the 1st planetary pinion of sun gear 112 engagements is the revolution of B direction.If retreating carriage 216,226 stops by the action that retreats lock 222, so because the characteristic of planetary gear system, with the output gear 214 of the 1st planetary pinion 212 engagements just along the direction identical with the 1st planetary pinion be the revolution of B direction, the output shaft 138 that is formed at one with output gear 214 also turns round along the B direction.The 2nd planetary pinion 230 that is formed at one with the 1st planetary pinion 212 is along the revolution of B direction, turns round along the A direction with 116 of the deceleration sun gears of the 2nd planetary pinion engagement.The revolution that subtracts sun gear 116 is delivered on the clutch connecting plate 82, and clutch connecting plate 82 is disengaged and turns round along the A direction owing to forward clutch 218.
Even with in the 1st embodiment when the fallback state stepless change more different than also changing, fallback state at present embodiment, because releasing by forward clutch 218, being delivered to the power that retreats on the carriage 216 from clutch connecting plate 82 is cut off, if to retreat carriage 216 fixing so make by the action that retreats lock 222, import so with the rotating ratio of exporting the ratio by planetary gear set 112,212,214 just become setting fixedly than.
Describe with regard to the 2nd embodiment 300 of the present invention below.
The 2nd embodiment 300 of stepless speed changes devices of the present invention, since change control system structure is set and method of operating identical with the 1st embodiment's change control system 10, so omit the formation of change control system 10 and the explanation of method of operating, only speed variator system 310 be elaborated.
Be shown in as Figure 12 A between the part 2 12B of input shaft 12 of power of input motor and the 3rd part 12C and form input sun gear 112.Hollow coupling shaft 34 is set on the part 2 12B of input shaft coaxially, and on the 2nd end 34B of coupling shaft 34, forms the permanent wheel 116 that slows down.Between input shaft 12 and coupling shaft 34, can insert with freely rotating mutually bearing 36N, 36B ' are set.
On the coupling shaft 34 in the left side of deceleration sun gear 116, the adjustment sun gear axle 312 of hollow is set coaxially, on an end 314 of adjusting sun gear axle 312, form and adjust sun gear 316.Between adjustment sun gear axle 312 and coupling shaft 34, can insert pivotally freely mutually bearing 312B, 312B ' are set.Clutch connecting plate 320 is connected on the other end 318 of adjusting the sun gear axle integratedly by spline 320S.Overrunning clutch 322 is fixedly installed on the outside of clutch connecting plate 320.The outside at clutch then is provided with the lock 324 that advances.Between clutch connecting plate 320 and clutch connecting plate 82, connect forward clutch 328 is set.
Below, make carriage 332 be positioned to adjust on the sun gear axle 312, between adjustment sun gear axle and carriage 332, can insert pivotally freely mutually bearing 332B is set.On the other hand, carriage 334 is positioned on the 3rd part 12C of input shaft 12, and can be mutually between input shaft and carriage 334 inserts pivotally freely bearing 334B is set.For two carriages 332,334 are turned round jointly, between two carriages, insert fixing many fixing pins (336,338), (each carriage is provided with two in the present embodiment, referring to Figure 12 B).
On each fixing pin 336, insert the 3rd differential gear 342 the 1st differential gear 340 is set and is formed at one with it, and this compound differential gear 340,342 is inserted with freely rotating bearing 340B, 340B ' are set.When being provided with, importing the inner mesh (Figure 12 B) of sun gear 112 and the 1st differential gear 340, and make a part of inner mesh of deceleration sun gear 116 and the 3rd differential gear 342.On the other hand, on other fixing pin 338, insert the 4th differential gear 346 the 2nd differential gear 334 is set and is formed at one with it, and this compound differential gear 344,346 is inserted with freely rotating bearing 344B, 344B ' are set.The part of the 2nd differential gear 344 and the 2nd differential gear 342 engagement (referring to Figure 12 B) when being provided with, and make the inner mesh of adjusting sun gear 316 and the 4th differential gear 346.
If the left side of the 1st, 3 differential gears 340,342 on fixing pin 336 is provided with spacer element 348, and the right side of the 2nd, four differential gears 344,346 on fixing pin 338 is also inserted spacer element 350 is set, and so just can prevent each differential gear moving vertically.And make and forming recess 352 and recess 354 respectively between the 1st differential gear 340 and the 3rd differential gear 342 and between the 2nd differential gear 344 and the 4th differential gear 346.The output gear with inside diameter 356A 356 that is formed at one with output shaft 138 is positioned on the 3rd part 12C of input shaft 12, make the outside engagement of gear ring 356 and the 1st differential gear 340, and between the 3rd part 12C of input shaft 12 and output gear 356, can insert pivotally freely mutually a 358B is set.And,, be provided with braking force is added to and retreat lock 358 on the carriage 332 in order to retreat driving.
The following describes the method for operating of each speed change state (neutral, advance, retreat) of the 3rd embodiment's of the present invention stepless speed changes devices and the process of transmission of power thereof.
1. neutral condition (Figure 13): output shaft (138) stops
-direct clutch plate 30 ↑: (idle running)
(1) the 3rd differential gear 342 ↓ the-the 2nd differential gear 344 ↑-
-Di 4 differential gears 346 ↑-
-adjustment sun gear 316 ↓: (idle running)
-deceleration sun gear 116 ↑
Clutch connecting plate 82 ↑: (idle running)
Neutral condition be make direct clutch 52, forward clutch 328 simultaneously, state that the lock 324 that advances, laggard lock 358 removed, the power of motor does not make output shaft 138 revolutions, is idling conditions as shown in figure 13.
If that is: input shaft 138 has load, the output gear 356 that is formed at one with output shaft stops so, in a single day the power of motor be transfused to, input shaft 12 revolution on one side so, the direct clutch plate 30 that is connected with input shaft is owing to the releasing of direct clutch 52 is dallied, the input sun gear 112 that is formed at one with input shaft is the revolution of A direction along the direction identical with input shaft, turn round along the B direction with the 1st differential gear 340 of input sun gear 112 engagements, the 3rd differential gear 342 that is formed at one with the 1st differential gear also turns round along the B direction.Turn round along the A direction with the 2nd differential gear 344 of the 3rd differential gear in abutting connection with engagement, the 4th differential gear 346 that is formed at one with the 2nd differential gear also turns round along the A direction.
Because the forward clutch 328 and the lock 32 4 that advances are in relieving state, so dally along the B direction with the adjustment sun gear 316 of the 4th differential gear 346 engagements.Turn round along the A direction with the deceleration sun gear 116 of the 3rd differential gear 342 engagements, the coupling shaft 34 that is formed at one with the deceleration sun gear also turns round along the A direction.Because the overrunning clutch 48 that is arranged between coupling shaft 34 and the impeller housing 42 makes impeller housing along the revolution of A direction, the impeller 56 that is formed at one with impeller housing 42 also turns round along the A direction.Along the revolution of A direction, adjustment axle 38 that is connected with turbine and clutch connecting plate 82 dally along the A direction owing to the releasing of forward clutch 328 by impeller turbine 58.
2. the advance speed change state (Figure 14) of (usually driving mode)
(2)
(1) impeller housing 42 ↑-impeller 56 ↑-turbine (58) O. ↑-
Adjustment axle (38) O. ↑-(forward clutch)-adjustment sun gear axle (312) O. ↑-
Adjust sun gear (316) O. ↑ the-the 4th differential gear 346 ↑ .1-
The 3rd differential gear 342 ↓ .1-the 1st differential gear 340 ↓ .1-
If when neutral condition, make direct clutch 52, forward clutch 328, the lock 324 that advances moves simultaneously, direct clutch plate 30, impeller housing 42 and 56 edges of impeller that connect with input shaft 12 direction identical with input shaft is that the A direction is with identical rotating speed revolution so.
On the other hand, the input sun gear 112 that is formed at one with input shaft 12 also turns round along the A direction.Turn round along the B direction with the 1st differential gear 340 of input sun gear 112 engagements, carriage 332,334 turns round along the A direction.The 3rd differential gear 342 that is formed at one with the 1st differential gear 340 turns round along the B direction, turn round along the A direction with the 2nd differential gear 344 of the 3rd differential gear 342 in abutting connection with engagement, the 4th differential gear 346 that is formed at one with the 2nd differential gear 344 also turns round along the A direction.Turn round along the A direction with the deceleration sun gear 116 of the 3rd differential gear 342 engagements.Because the rotating speed of the deceleration sun gear always rotating speed than impeller housing 42 (connecting with input shaft 42) is little or identical, so the coupling shaft that is formed at one with deceleration sun gear 116 dallies along the A direction by overrunning clutch.
By initial stage low speed starting state as can be known, (output gear 356 is stopped in neutral condition by the load of output shaft 138, adjust sun gear 316 along the idle running of B direction), if make direct clutch 52, forward clutch 328, the lock 324 that advances move simultaneously, so by means of be arranged on clutch connecting plate 320 and advance between the lock 324 overrunning clutch 322 and make and adjust sun gear and be suppressed to the revolution of B direction, and moment is in halted state.At this moment, because the load of output shaft 138 makes adjustment sun gear 316 be subjected to resistance.Input is set at fixing ratio with the gear ratio of output by input sun gear the 112, the 1st differential gear 340, carriage 332,334 and output gear 356.And, because the turbine 58 that the action of forward clutch 328 is connected with adjustment sun gear 316 also is subjected to resistance and moment is stopped.At this moment, impeller 56 produces speed discrepancies with turbine 58, because this speed discrepancy, the turning power of impeller is increased and is delivered on the turbine.If the turning power of this turbine 58 with from the resistance balance of output shaft, output shaft 138 is driven.Be the low speed starting state this moment.
Below, since identical with the 1st embodiment from low state stepless change to the process of fast state, so omit herein.
3. the advance speed change state (Figure 15) of II (dynamic mode)
(1) the 3rd differential gear 342 ↓ .1-deceleration sun gear 116 ↑-coupling shaft 34 ↑
-(overrunning clutch)-impeller housing 42 ↑-impeller 56 ↑-turbine 58 O. ↑
-adjustment axle 38 O. ↑-(forward clutch)-adjustment sun gear axle
(312) O. ↑-adjust sun gear 316 O. ↑ the-the 4th differential gear 346 ↑ .1
The 2nd differential gear 344 ↑ .1-the 3rd differential gear 342 ↓ .1-
In neutral condition,, so just become the dynamic mode operating state if advance lock 324 and forward clutch 328 are moved simultaneously.Compare with the speed change state of the common driving mode of the aforesaid I of advancing, the gyratory directions of each parts is identical with the stepless change process, but is delivered to the power transfer path difference of impeller 56.By removing direct clutch 52, with direct clutch plate 30 idle running that input shaft 12 links, the revolution (that is: the turning power that is increased) that is decelerated by the 3rd differential gear 342 and deceleration sun gear 116 just is delivered on the impeller by coupling shaft 34 overrunning clutchs 48.
Below, stepless change process and action are identical with the common driving mode of the aforementioned I that advances.
4. fallback state (Figure 16)
Connecting plate 320 ↓: (idle running)
The formation that retreats of present embodiment does not need retreating separately as the 1st embodiment to use planetary gear system, retreats lock 358 but be provided with on carriage 332.Make in neutral condition and to retreat lock 358 action.
If the power of motor is from input shaft 12 inputs, the input sun gear 112 that links into an integrated entity with input shaft so is the revolution of A direction along the direction identical with the input shaft mouth just, turn round along the B direction with 340 of the 1st differential gears of input sun gear engagement, carriage 332,334 is because owing to the action that retreats lock 358 is fixed, the direction opposite with the gyratory directions of input shaft with 356 edges of output gear of the outside of the 1st differential gear 340 engagement is the revolution of B direction, and the output shaft 138 that is formed at one with output bracket also turns round along the B direction.
The direct clutch plate 30 that is connected with input shaft 12 dallies along the A direction, turn round along the A direction with the 2nd differential gear 344 of the 2nd differential gear 342 engagements, the 4th differential gear 346 that is formed at one with the 2nd differential gear also turns round along the A direction, and the adjustment sun gear 316 that meshes with the 4th differential gear is dallying when the B direction is turned round.With the deceleration sun gear 116 of the 3rd differential gear 342 engagement along the revolution of A direction, the impeller housing 42 that be formed at the coupling shaft 34 of one with the deceleration sun gear, is connected by overrunning clutch 48 with coupling shaft, be formed at the impeller 56 of one with impeller, the turbine 58 that is provided with respect to impeller, the adjustment axle 38 that is connected with turbine and all when the A direction is turned round, dallying with an adjustment clutch connecting plate 82 that is connected.
The following describes the 4th embodiment of the present invention.
In the 4th embodiment 400 of stepless speed changes devices of the present invention, since change control system structure is set and method of operating identical with the 1st embodiment's change control system 10, so omit explanation, and only speed variator system 410 described to the structure and the method for operating of change control system 10.
At first, when comparing with the 3rd embodiment 300, maximum difference is to make the lock 450 that retreats that is formed at one with output shaft 138 to be arranged on and to retreat on the gear ring 448.More specifically observing it constitutes as can be known, as shown in figure 17, be provided with input shaft 12, between the part 2 12B of input shaft 12 and the 3rd part 12C, form input sun gear 112, coupling shaft 34 is set on the part 2 12B of input shaft, make deceleration sun gear 116 be integrally formed in the 2nd end 34B of coupling shaft, insert with freely rotating mutually between input shaft 12 and coupling shaft 34 bearing 36B, 36B ' are set, such formation is identical with the 3rd embodiment.
Hollow is adjusted on the coupling shaft 34 in left side that sun gear axle 412 is arranged on deceleration sun gear 116 coaxially, make and adjust the end 414 that sun gear 416 is integrally formed in the adjustment sun gear, between adjustment sun gear axle 412 and coupling shaft 34, insert with freely rotating mutually bearing 412B, 412B ' are set.The clutch connecting plate is connected the other end 418 that is arranged on adjustment sun gear axle 412 by spline 420S.On the adjustment sun gear axle 412 in the left side of adjusting sun gear 416, carriage 422 is set, and inserts between the two at this pivotally freely bearing 422B is set.And the carriage 424 that is formed at one with output shaft 138 is arranged on the 3rd part 12C of input shaft 12, between the 3rd part 12C of carriage 424 and input shaft, can insert with freely rotating mutually bearing 426B is set.
For two carriages 422,424 are turned round jointly, many fixing pins 428,430 are provided with are fixed between two carriages, the 1st differential gear 432 is set on every fixing pin 428 reaches the 3rd differential gear 434 that is formed at one with it; The 2nd differential gear 436 is set on every fixing pin 430 reaches the 3rd differential gear 438 that is formed at one with it.
For each fixing pin and each differential gear can be turned round each other freely, between the 1st, 3 differential gears 432,434 and fixing pin 428, insert bearing 432B, 432B ' are set, between the 2nd, four differential gears 436,438 and fixing pin 430, then insert bearing 436B, 436B ' are set.The inner mesh of input sun gear 112 and the 1st differential gear 432, the part engagement of the 2nd differential gear 436 and the 3rd differential gear 434, the inner mesh of another part of deceleration sun gear 116 and the 3rd differential gear 434 is adjusted the inner mesh of 416 of sun gears and the 4th differential gear 438.
In addition, form recess 440 and recess 442 respectively between the 1st differential gear 432 and the 3rd differential gear 434 and between the 2nd differential gear 436 and the 4th differential gear 438, on each fixing pin 428,430, can insert the spacer element 444,446 that setting is moved in order to prevent each differential gear.Above-mentioned formation and setting method and the 3rd embodiment are similar, so omit its detailed explanation.
And, on the adjustment sun gear axle 412 in the left side of carriage 422, be provided with and retreat gear ring 448 and make it outside engagement with the 4th differential gear, retreating gear ring and adjusting that insertion with freely rotating is provided with bearing 448B between the sun gear axle.Make and retreat lock 450 and be arranged on the outside that retreats gear ring 448.On the other hand, at the arranged outside of clutch connecting plate 420 lock 454 that advances, at the clutch connecting plate with advance between the lock to insert overrunning clutch 458 is set, when advancing lock 454 actions, prevent to adjust sun gear 416 along the direction revolution opposite with input shaft 12.And between clutch connecting plate 420 and clutch connecting plate 82, forward clutch 460 is set.
Be the method for operating and the power transmission process thereof of each speed change state (neutral, advance, retreat) of the stepless speed changes devices in the present embodiment below.
1. neutral condition (Figure 18): output shaft (138) stops
(3) turbine 58 ↑-clutch connecting plate 82 ↑: (idle running)
Neutral condition is to make direct clutch 52, dynamic mode clutch 44, forward clutch 460 and retreat the state that lock 450 is removed simultaneously, is that the power of motor can not make output shaft 138 revolutions, idling conditions as shown in figure 18.
That is, if load is added on the output shaft 138, carriage 424 and the carriage 422 that is formed at one with output shaft is stopped so.If direct clutch plate 30 idle running that the power of input motor is connected with input shaft 12 so, the input sun gear 112 that is formed at one with input shaft is the revolution of A direction along the direction identical with the gyratory directions of input shaft, and the direction opposite with the gyratory directions of input shaft with the 1st differential gear 432 edges of input sun gear 112 engagements is the revolution of B direction.The 3rd differential gear 434 that forms one with the 1st differential gear also turns round along the B direction, turns round along the A direction with the 2nd differential gear 436 of the 3rd differential gear in abutting connection with engagement, and the 4th differential gear 438 that is formed at one with the 2nd differential gear also turns round along the A direction.The action that retreat lock 450, makes forward clutch 460 is removed and is dallied along the B direction with the adjustment sun gear 416 of the inner mesh of the 4th differential gear.With the deceleration sun gear 116 of the inner mesh of the 3rd differential gear 434 along the revolution of A direction, the coupling shaft 34 that is connected with the deceleration sun gear, impeller 56, turbine 58, adjust spools 38, clutch connecting plate 82 dallies along the A direction.
2. the advance speed change state (Figure 19) of I (usually driving mode)
-input sun gear 112 ↑ the-the 1st differential gear 432 ↓ .1-(2)
(1) impeller housing 42 ↑-impeller 56 ↑-turbine (58) O. ↑-adjust axle
(38) O. ↑-(forward clutch)-adjust sun gear axle (412) O. ↑--adjust sun gear (416) O. ↑ the-the 4th differential gear 438 ↑ .1--the 2nd differential gear 436 ↑ .1-the 3rd differential gear 434 ↓ .1-
At neutral condition (Figure 18), if make direct clutch 52, forward clutch 460, lock 454 action of advancing, the direct clutch plate 30 that connects with input shaft 12, impeller housing 42, impeller 56 sides are the revolution of A direction along the direction identical with input shaft 12 so.
On the other hand, the input sun gear 112 that is formed at one with input shaft 12 also turns round along the A direction.Turn round along the B direction with the 1st differential gear 432 of input sun gear 112 engagements, the 3rd differential gear 432 that is formed at one with the 1st differential gear also turns round along the B direction.Turn round along the A direction with the 2nd differential gear 436 of the 3rd differential gear in abutting connection with engagement, the 4th differential gear 438 that is formed at one with the 2nd differential gear also turns round along the A direction.Turn round along the A direction with the deceleration sun gear 116 of the inner mesh of the 3rd differential gear 434; Because the rotating speed of the deceleration sun gear 116 always rotating speed than impeller housing 42 (connecting with input shaft 12) is little or identical, so the coupling shaft 34 that is formed at one with deceleration sun gear 116 dallies along the A direction through overrunning clutch.
From the initial stage starting state as can be known, at the load of neutral condition by output shaft 138 carriage 422,424 is stopped, adjusting sun gear 416 dallies along the B direction, if make direct clutch 52, forward clutch 460, lock 454 action of advancing, so by being arranged at clutch connecting plate 420 and the overrunning clutch 458 between the lock 454 of advancing, adjusting sun gear 416 and be suppressed and moment becomes halted state to the revolution of B direction.(adjust sun gear 416 and bear load from output shaft 138 this moment), in this halted state moment, input is set at fixedly gear ratio with the gear ratio of output by the ratio of importing sun gear the 112, the 1st differential gear the 432, the 2nd differential gear the 436, the 4th differential gear 438 and adjustment sun gear 416, and output shaft 138 keeps certain rotating speed.And through the action of forward clutch 460, turbine 58 is connected with adjustment sun gear 416, and also moment stops in the revolution of turbine.At this moment, impeller 56 produces speed discrepancy with turbine 58, because the turning power of this speed discrepancy impeller is increased and is delivered on the turbine.The turning power of this turbine with when the moment of adjusting sun gear 416 stops by differential gearing set fixedly than and the turning power that produces is synthetic and be delivered on the output shaft 138, when the balancing the load of the turning power of turbine and output shaft, output shaft is driven.Be the low speed starting state this moment.
Below, because the process from the lower-speed state stepless change to fast state is identical with the 1st embodiment's method of operating and basic principle, so omit its explanation herein.
3. the advance speed change state (Figure 20) of II (dynamic mode)
(1) the 3rd differential gear 434 ↓ .1-deceleration sun gear 116 ↑-coupling shaft 34 ↑-(overrunning clutch 48)-impeller housing 42 ↑-impeller 56 ↑-turbine 58 O. ↑-adjustment axle 38 O. ↑-
(forward clutch)-adjustment sun gear axle (412) O. ↑-adjustment sun gear O. ↑-
-Di 4 differential gears 438 ↑ .1-the 2nd differential gear 436 ↑ .1-
-Di 3 differential gears 434 ↓ .1-the 1st differential gear 432 ↓ .1-
As shown in figure 20, in neutral condition,, so just become the dynamic mode state if the forward clutch 460 and the lock 454 that advances are moved simultaneously.With the speed change state of the common driving mode of the aforementioned I that advances relatively, the gyratory directions of each parts is identical with the stepless change process, but the bang path difference of the power that transmits to impeller.By removing direct clutch 52, direct clutch plate 30 idle running that are connected with input shaft 12, the revolution (that is, increasing turning power) of being slowed down by the 3rd differential gear 434 and deceleration sun gear 116 is delivered on the impeller by overrunning clutch 48 by coupling shaft 34.
The common driving mode of following stepless change process and action thereof and the aforesaid I that advances is identical.
4. fallback state (Figure 21)
(2) coupling shaft 34 ↑-impeller 56 ↑-turbine 58 ↑-adjust axle 38 ↑-one clutch connecting plates 82 ↑: (idle running).
Make in neutral condition as shown in figure 21 and retreat lock 450 actions.If the power of motor is transfused to from input shaft 12, the input sun gear 112 that is formed at one with input shaft 12 is the revolution of A direction along the direction identical with input shaft just so, with 432 of the 1st differential gears of input sun gear 112 engagement along the revolution of B direction, the 3rd differential gear 434 that is formed at one with the 1st differential gear also turns round along the B direction.Turn round along the A direction with the 2nd differential gear 436 of the 3rd differential gear in abutting connection with engagement, the 4th differential gear 438 that is formed at one with the 2nd differential gear also turns round along the A direction.Owing to fix by retreating lock 450 with the gear ring 448 that retreats that mesh in the outside of the 4th differential gear, so carriage 422,424, also turns round along the B direction with the bracket-shaped output shaft 138 that is formed in one along the revolution of B direction.With the adjustment sun gear 416 of the inner mesh of the 4th differential gear 438 along the idle running of B direction, the deceleration sun gear 116 that closes with the inner mesh of the 3rd differential gear 434 also with coupling shaft 34, impeller 56, turbine 58, adjust axle 38 idle running.
Below the 5th embodiment of the present invention is described.
The speed change adjust system 10 that structure and method of operating and the 1st embodiment are set of the speed change adjust system among the 5th embodiment 500 of stepless speed changes devices of the present invention is identical, so the explanation of speed change adjust system 10 is omitted, speed variator system 510 only is described.
As shown in figure 22, observe it and structure is set as seen, have input shaft (12) and reach with the coupling shaft 34 of the input sun gear 112 of its formation one, hollow and deceleration sun gear 116, input shaft and the coupling shaft of its formation one between bearing 36B, 36B ', these are identical with previous embodiment.
On the coupling shaft 34 in the left side of deceleration sun gear 116, be provided with the adjustment bracket axle 512 of hollow coaxially, adjusting between bracket axle 512 and the coupling shaft 34, can insert freely to rotate bearing 512B, 512B ' are set.Be integral to be provided with at an end 514 places that adjust bracket axle 512 and adjust carriage 516.Be formed with through hole 518 on the adjustment carriage, bearing 554B described later inserts this hole.Forward clutch plate 522 forms with the other end 520 of adjusting bracket axle by spline 522S and is connected integratedly.Adjusting on the bracket axle 512, what be provided with hollow coaxially retreats sun gear axle 524, retreats sun gear 528 and forms one with an end 526 that retreats sun gear axle 524.Certainly, for can freely turn round, be inserted with bearing 524B, 524B ' retreating between sun gear axle 524 and the adjustment bracket axle 512.Retreating connecting plate 532 fuses with the other end 530 that retreats sun gear axle 524 by spline 532S.
The sun gear axle 524 that retreats that retreats connecting plate 532 and retreat between the sun gear 528 is provided with carriage 534, for can freely turn round, at carriage 534 with retreat and be inserted with bearing 534B between the sun gear axle 524.Be provided with and output shaft 138 all-in-one-piece carriages 536 at the 3rd part 12C place of input shaft 12,, between carriage 536 and the 3rd part 12C, be inserted with bearing 538B in order freely to turn round.In order to allow two carriages 534,536 turn round jointly, between two carriages 534,536, be provided with and be fixed with a plurality of fixing pins 540.
On each fixing pin 540, be inserted with the 1st planetary pinion the 542, the 2nd planetary pinion 544 that forms one, retreat planetary pinion 546,, be inserted with bearing 548B, 548B ' between each fixing pin and the planetary pinion in order freely to turn round.Between the 1st planetary pinion 542 and the 2nd planetary pinion 544, be formed with short tube portion 550, the 2 planetary pinions and retreat and be formed with short tube portion 552 between the planetary pinion 546.Short tube portion 552 inserts in the through hole 518 of adjusting carriages 516, short tube portion 552 and adjust between the carriage 516 and be inserted with bearing 554B.In addition, when being provided with, the 1st planetary pinion 542 is meshed with input sun gear 112, the 2nd planetary pinion 544 is meshed with deceleration sun gear 516, make to retreat planetary pinion 546 and retreat sun gear 528 and be meshed.And between forward clutch plate 522 and clutch web 82 forward clutch 556 being set is connected.Retreat lock 560 in the arranged outside that retreats connecting plate 532.
The speed change state of the present invention the 5th embodiment's stepless speed changes devices (neutral, advance, retreat) method of operating and consequent power transmission process are as follows.
1. neutral condition (Figure 23): output shaft 138 stops
(1) the 2nd planetary pinion 544 ↓-deceleration sun gear 116 ↑-coupling shaft 34 ↑-impeller 56 ↑-turbine 58 ↑-adjustment axle 38 ↑-clutch connecting plate 82 ↑: (idle running)
(2) retreat planetary pinion 546 ↓-retreat sun gear 528 ↑: (idle running)
Neutral condition is the state of removing direct clutch 52, dynamic mode clutch 44, forward clutch 556 simultaneously, retreating lock 560, is that the power of motor does not make output shaft 138 rotating, idling conditions as shown in figure 23.
That is, if load is added in output shaft 138, then carriage 536 and the carriage 534 with output shaft 138 formation one just stops.When the power of motor was transfused to, direct clutch plate 30 idle running with input shaft 12 is connected formed the input sun gear 112 of one along turning round with input shaft 12 equidirectional A directions with input shaft 12.The 1st planetary pinion 542 edges and the reciprocal B direction of input shaft that are meshed with input sun gear 112 are turned round, and form the 2nd planetary pinion 544 of one and retreat planetary pinion 546 with the 1st planetary pinion 542 and also turn round along the B direction.The deceleration sun gear 116 that is meshed with the 2nd planetary pinion (544) turns round along the A direction, coupling shaft 34 that is connected with deceleration sun gear 116 and impeller 56, turbine 58, adjust axle 38,82 idle running of clutch connecting plate, and retreat the sun gear 528 that retreats that planetary pinion 546 is meshed and dally along the A direction.
2. the advance speed change state (Figure 24) of I (usually driving mode)
(1) impeller housing 42 ↑-impeller 56 ↑-turbine 58 O. ↑-adjust axle 38 O. ↑-(forward clutch)-adjust bracket axle 512 O. ↑-
In neutral condition, as direct clutch 52 and forward clutch 556 are moved simultaneously, then the direct clutch plate 30 that is connected with input shaft 12, impeller housing 42 and impeller 56 are along turning round with the equidirectional A direction of input shaft.Also turn round with input shaft 12 all-in-one-pieces input sun gear 112 along the A direction.The 1st planetary pinion 542 that is meshed with input sun gear 112 turns round along the reciprocal B direction of input shaft, forms the 2nd planetary pinion 544 of one and retreats planetary pinion 546 with the 1st planetary pinion and also turn round along the B direction.The deceleration sun gear 116 that is meshed with the 2nd planetary pinion 544 and dally along the A direction with coupling shaft 34 that the deceleration sun gear forms one.With retreat that planetary pinion 546 is meshed retreat sun gear 528 and dally to the A direction owing to retreat the releasing of lock 560.
The power transmission process of the initial stage of observing during the low speed starting state as can be known, at abort state (because the load of output shaft 138, carriage 534,536 stops, adjusting carriage 516 also stops), as direct clutch 52 and forward clutch 556 are moved simultaneously, then because the action of forward clutch is adjusted carriage 516 and turbine 58 and is connected, resistance moment that turbine 58 is equivalent to the load of output shaft 138 stops.At this moment, impeller 56 produces speed discrepancies with turbine 58, is passed to turbine by this rotating speed official post than the turning power of the turning power multiplication of impeller.When the resistance of turning power that passes to turbine 58 and output shaft load generation balances each other, begin to drive output shaft.Be called the low speed starting state this moment.
Infinite variable speed process from the lower-speed state to the fast state is identical with method of operating and principle among the embodiment 1, in this description will be omitted.
3. the advance speed change state (Figure 25) of II (dynamic mode)
(1) the 2nd planetary pinion 544 ↓ .1-deceleration sun gear 116 ↑-coupling shaft 34
↑-(overrunning clutch 48)-impeller housing 42 ↑-impeller 56 ↑-turbine 58O. ↑-adjustment axle (38) O. ↑-(forward clutch)-
As shown in figure 25,, as make forward clutch 556 actions, then become dynamic mode at neutral condition (Figure 23).Compare with the common walking mode of the aforesaid I of advancing, the gyratory directions of each parts is identical with the stepless change process, but to the transfer route difference of impeller 56 transferring power.Because the releasing of direct clutch 52, direct clutch plate 30 idle running that are connected with input shaft 12, the revolution of being slowed down by the 2nd planetary pinion 544 and deceleration sun gear 116 (promptly double turning power) through coupling shaft 34, passes to impeller 56 by overrunning clutch 48.
Following stepless change process is identical with the common walking mode of the aforesaid I that advances.
4. fallback state (Figure 26)
534,536 ↓-output shaft 138 ↑
As shown in figure 26, at neutral condition (Figure 23), as make laggard lock 560 actions, then laggard sun gear 528 stops.When the power of motor during from input shaft 12 inputs, direct clutch plate 30 idle running that are connected with input shaft 12, input sun gear 112 edges that fuse with input shaft 12 and the revolution of the A direction of input shaft 12 equidirectionals, the 1st planetary pinion 542 that is meshed with input sun gear 112 is along turning round with input shaft 12 rightabout B directions, and the 2nd planetary pinion 544 and the laggard planetary pinion 546 that form one with the 1st planetary pinion 542 also turn round along the B direction.The deceleration sun gear 116 that is meshed with the 2nd planetary pinion 544, the coupling shaft 34 that is connected with deceleration sun gear 116, impeller 56, turbine 58 and adjust axle 38 and dally along the A direction.With retreat the sun gear 528 that retreats that planetary pinion 546 is meshed and stop owing to retreating lock 560 effects, thereby carriage 534,536 is along the revolution of B direction, the output shaft 138 that is connected with carriage 536 also along and input shaft 12 rightabout B directions turn round.Because forward clutch 556 is disengaged, so adjust carriage 516 along dallying with output shaft 138 equidirectionals.
As previously discussed, for stepless speed changes devices of the present invention, even the state that all connects at all gears, become the common walking mode of ride comfort and can be fit to mountain region, ramp walking or the anxious dynamic mode that starts by speed change, can will be input to transmission of power on the input shaft to output shaft, and retreat driving also can be with simple method realization.
And, stepless speed changes devices of the present invention is not limited only to present embodiment, for all vehicles and the industrial machine that do not break away from aim of the present invention, all can use this device the driving force speed change is exported to output shaft, and, can do various changes within the scope of the invention.
For example the number of teeth of the gear that the present invention can be used etc. is suitably regulated according to the purpose difference, can obtain the revolution of necessary output shaft in view of the above, does not also limit the size of gear certainly.
In addition, each embodiment's formation has been carried out concrete representing with Fig. 2, Fig. 7, Figure 12 A, Figure 17 and Figure 22, but also can represent with the such skeleton diagram of Figure 27 to Figure 31.
Claims (18)
1. stepless speed changes devices, it comprises: the transmission of power that motor produces is given input shaft, is delivered to the speed variator system of output shaft after speed change; Rotating ratio is adjusted to the speed change adjust system of the load condition of corresponding output shaft; It is characterized in that it also comprises: can independently be arranged on coupling shaft (34) on the part 2 (12B) pivotally with respect to the input shaft (12) that constitutes by 3 parts (12A, 12B, 12C); Adjustment axle (38) with respect to the independent rotating setting of coupling shaft (34) energy; With the stationary axle (62) of adjusting axle (38) coaxial setting; Be arranged near the impeller housing (42) in an end (34A) of coupling shaft (34) pivotally; Prop up pivotally and be held on the stationary axle (62), form the impeller (56) of one simultaneously with impeller housing (42); Land relatively with impeller housing, form the turbine (58) of one with an end (38A) of adjusting axle (38); Be arranged on the stator (60) between impeller (56) and the turbine (58); For preventing that stator (60) from reversing the overrunning clutch (66) that is arranged between stator (60) and the stationary axle (62); Between the section 1 (12A) and part 2 (12B) of input shaft, with input shaft all-in-one-piece direct clutch plate (30); Be used for cutting off, connecting the direct clutch (52) of the power between impeller housing (42) and the direct clutch plate (30); For preventing that impeller housing (42) from turning round the overrunning clutch (48) that is provided with along the opposite direction of the gyratory directions of coupling shaft (34); Have the actuation gear (16) that is connected with section 1 (12A) one of input shaft and driven gear (20) and be arranged at oil pump (14) on the section 1 (12A) of input shaft; Accommodate the oil pump case (22) of oil pump (14); Be oil sealing (26C, 26C ', 68C, 72C) and the axle bush (40B, 40B ', 70B) that prevents that leakage of oil from inserting; With oil pump case (22) sealing assembling, be fixed on the external stability housing (28) on the end (64) of stationary axle (62) simultaneously; Form the clutch connecting plate (82) of one with an end (38B) of adjusting axle (38) for the transmission of power of speed variator system; The through oil hole (74), suction path (76), drain passageway (78) and the oily exhaust port (80) that are used for the suction and the discharge of oil.
2. by the described stepless speed changes devices of claim 1, it is characterized in that it also appends and is provided with the dynamic mode clutch (44) that is used for cutting off, connecting the power of impeller housing (42) and coupling shaft (34).
3. by the described stepless speed changes devices of claim 1, it is characterized in that above-mentioned speed variator system comprises: between the part 2 (12B) of input shaft and the 3rd part (12C) with the input sun gear (112) of input shaft formation one; Form the deceleration sun gear (116) of one with a end (34B) that can independent rotating coupling shaft (34) with respect to input shaft; Coupling shaft (34) can independently be arranged on the carriage (118) on the coupling shaft (34) pivotally relatively; Relatively the 3rd part (12C) of input shaft can be independently pivotally, form the carriage (124) of one with output shaft (138); For being turned round simultaneously, carriage (118,124) between carriage (118,124), inserts fixing a plurality of fixing pins (128); Be arranged on each fixing pin (128) its a plurality of the 1st planetary pinions (130) inboard and input sun gear (112) engagement pivotally; A plurality of the 2nd planetary pinions (132) of form one with the 1st planetary pinion (130), be arranged on each fixing pin (128) pivotally, it is inboard and deceleration sun gear (116) meshes; Be supported on pivotally coupling shaft (34) go up, simultaneously with the gear ring that advances (136) of the 2nd planetary pinion (132) engagement; The hollow that relative output shaft (138) can independently be arranged on the output shaft pivotally retreats input shaft (140); Retreat sun gear (144) with an end (142) that retreats input shaft (140) forms one; Retreat connecting plate (150) with the other end that retreats input shaft (140) (146) forms one; Retreating input shaft relatively can independently be arranged on pivotally to retreat sun gear (144) and retreat retreating between the connecting plate (150) and retreat carriage (154) on the input shaft (140); Be arranged on pivotally and retreat carriage (152) on the input shaft (138); For being turned round simultaneously, two carriages (152,154) insert a plurality of fixing pins (156) that are fixed between the carriage (152,154); Be arranged at pivotally on the fixing pin (156), simultaneously its inboard and a plurality of planetary pinions (158) that retreat that retreat sun gear (144) engagement; With retreat planetary pinion (158) engagement, and retreat gear ring (160) with output shaft (138) forms one; Be connected clutch connecting plate (82) and retreat clutch coupling shaft (164) between the connecting plate (150); Be arranged on the forward clutch (166) between gear ring that advances (136) and the clutch coupling shaft (164); Be arranged on the overrunning clutch (170) in the outside of clutch coupling shaft (164); For retreating lock (172) to what retreat that carriage (154) applies that braking force is provided with.
4. by the described stepless speed changes devices of claim 1, it is characterized in that above-mentioned speed variator system comprises: between the part 2 (12B) and the 3rd part (12C) of input shaft, with the input sun gear (112) of input shaft formation one; End (34B) that can independent rotating coupling shaft (34) with relative input shaft forms the deceleration sun gear (116) of one; Relatively coupling shaft (34) can independently be arranged at pivotally and retreat carriage (216) on the coupling shaft (34); Can independently be arranged on pivotally with respect to the 3rd part (12C) of input shaft and to retreat carriage (226) on the 3rd part (12C); For being turned round simultaneously, two carriages (216,226) between carriage (216,226), insert fixing a plurality of fixing pins (228); Be arranged at pivotally on each fixing pin (228), and its a plurality of the 1st planetary pinions (212) inboard and input sun gear (112) engagement; Form one, be arranged on each fixing pin (228) pivotally with the 1st planetary pinion (212), and its a plurality of the 2nd planetary pinions (230) inboard and deceleration sun gear (116) engagement; With the 1st planetary pinion (212) engagement, form the output gear (214) of one simultaneously with output shaft (138); For retreating lock (222) to what retreat that carriage (216) applies that braking force is provided with; In order to cut off, to connect clutch connecting pin (82) and retreating the power between the carriage (216) and the forward clutch (218) that is provided with.
5. by the described stepless speed changes devices of claim 1, it is characterized in that above-mentioned speed variator system comprises: be arranged between the part 2 (12B) and the 3rd part (12C) of input shaft, with the input sun gear (112) of input shaft formation one; End (34B) that can independent rotating coupling shaft (34) with relative input shaft forms the deceleration sun gear (116) of one; With the be separated by adjustment sun gear axle (312) of the hollow that required separation distance, relative coupling shaft (34) can independently be provided with pivotally of deceleration sun gear (116); Adjustment sun gear (316) with an end (314) the formation one of adjusting sun gear axle (312); Form the clutch connecting plate (320) that is provided with integratedly with the other end (318) of adjusting sun gear axle (312); Adjust sun gear axle (312) relatively and can independently be arranged on the carriage of adjusting on the sun gear axle (312) (332) pivotally; The 3rd part (12C) of input shaft can independently be arranged on the carriage (334) on the 3rd part (12C) pivotally relatively; For being turned round simultaneously, two carriages (332,334) insert a plurality of fixing pins (336,338) that are fixed between the carriage (332,334); Be arranged on a plurality of the 1st differential gears (340) that each fixing pin (336) is gone up, it is inboard is meshed with input sun gear (112) pivotally; A plurality of the 3rd differential gears (342) that form one with the 1st differential gear (340), be arranged on each fixing pin (336) pivotally, it is inboard to be meshed with deceleration sun gear (116); Be arranged on a plurality of the 2nd differential gears (344) that each fixing pin (338) is gone up, is meshed with the 3rd differential gear pivotally; A plurality of the 4th differential gears (346) that form one with the 2nd differential gear (344), be arranged on each fixing pin (338) pivotally, it is inboard to be meshed with adjustment sun gear (316); The output gear (356) that is meshed with the 1st differential gear (340), links into an integrated entity with output shaft (138) simultaneously; Have for clutch connecting plate (320) being applied the lock that advances (324) of the overrunning clutch (322) that braking force is provided with; Retreat lock (358) for what carriage (332) is applied braking force is provided with; For cutting off, connect the forward clutch (328) that the power between clutch connecting plate (82) and clutch connecting plate (320) is provided with.
6. by the described stepless speed changes devices of claim 1, it is characterized in that above-mentioned speed variator system comprises: be arranged between the part 2 (12B) and the 3rd part (12C) of input shaft, with the input sun gear (112) of input shaft formation one; End (34B) that can independent rotating coupling shaft (34) with relative input shaft forms the deceleration sun gear (116) of one; With the be separated by adjustment sun gear axle (412) of the hollow that required separation distance, relative coupling shaft (34) can independently be provided with pivotally of deceleration sun gear (116); Adjustment sun gear (416) with an end (414) the formation one of adjusting sun gear axle (412); Form the clutch connecting plate (420) that is provided with integratedly with the other end (418) of adjusting sun gear axle (412); Adjust sun gear axle (412) relatively and can independently be arranged on the carriage of adjusting on the sun gear axle (412) (422) pivotally; The 3rd part (12C) of input shaft can independently be provided with pivotally and go into the carriage (424) that axle (138) links into an integrated entity with axle relatively; For being turned round simultaneously, carriage (422,424) inserts a plurality of fixing pins (428,430) that are fixed between the carriage (422,424); Be arranged on a plurality of the 1st differential gears (432) that each fixing pin (428) is gone up, it is inboard is meshed with input sun gear (112) pivotally; A plurality of the 3rd differential gears (434) that form one with the 1st differential gear (432), be arranged on each fixing pin (428) pivotally, it is inboard to be meshed with deceleration sun gear (116); Be arranged on a plurality of the 2nd differential gears (436) that each fixing pin (430) is gone up, is meshed with the 3rd differential gear (434) pivotally; A plurality of the 4th differential gears (438) that form one with the 2nd differential gear (436), be arranged on each fixing pin (430) pivotally, it is inboard to be meshed with adjustment sun gear (416); What be supported on pivotally that adjustment sun gear axle (412) between clutch connecting plate (420) and the carriage (422) goes up, is meshed with the 4th differential gear (438) simultaneously retreats gear ring (448); Have for clutch connecting plate (420) being applied the lock that advances (454) of the overrunning clutch (458) that braking force is provided with; Retreat lock (450) for what gear ring (448) is applied braking force is provided with; For cutting off, connect the forward clutch (460) that the power between clutch connecting plate (82) and the clutch connecting plate (420) is provided with.
7. by the described stepless speed changes devices of claim 1, it is characterized in that above-mentioned speed variator system comprises: between the part 2 (12B) and the 3rd part (12C) of input shaft, with the input sun gear (112) of input shaft formation one; Form the deceleration sun gear (116) of one with a end (34B) that can independent rotating coupling shaft (34) with respect to input shaft; Can independently be arranged at adjustment bracket axle (512) on the coupling shaft (34) pivotally with respect to coupling shaft (34); Form the forward clutch plate (522) that is provided with integratedly with an end (520) of adjusting bracket axle (512); That relatively adjusts that bracket axle (512) can independently be arranged on the hollow adjusted on the bracket axle (512) pivotally retreats sun gear axle (524); Retreat sun gear (528) with an end (526) that retreats sun gear axle (524) forms one; With the other end that retreats sun gear axle (524) (530) form be provided with integratedly retreat connecting plate (532); Retreat connecting plate (532) and retreating the carriage (534) that retreating between the sun gear (528) can independently be provided with on the sun gear axle (524) pivotally; Relatively the 3rd part (12C) of input shaft can independently be provided with pivotally, form the carriage (536) of one with output shaft (138); For being turned round simultaneously, two carriages (534,536) insert a plurality of fixing pins (540) that are fixed between the carriage (534,536); Be arranged on a plurality of the 1st planetary pinions (542) that each fixing pin (540) is gone up, it is inboard is meshed with input sun gear (112) pivotally; Fuse, be arranged on pivotally a plurality of the 2nd planetary pinions (544) that each fixing pin (540) is gone up, it is inboard to be meshed with deceleration sun gear (116) with the 1st planetary pinion (542); Form one, be arranged at that each fixing pin (540) is gone up, it is inboard with retreat a plurality of planetary pinions (546) that retreat that sun gear (528) is meshed pivotally with the 2nd planetary pinion (544); Be bearing in the adjustment carriage (516) of the other end (514) the formation one that retreats short tube portion (522), the while that forms between planetary pinion (546) and the 2nd planetary pinion (544) and adjust bracket axle (512) pivotally; For retreating lock (560) to what retreat that connecting plate (532) applies that braking force is provided with; The forward clutch (556) that is provided with in order to cut off, connect the power between clutch connecting plate (82) and the forward clutch plate (522).
8. speed change adjust system, it comprises: can independently be arranged on coupling shaft (34) on the part 2 (12B) pivotally with respect to the input shaft of being made up of 3 parts (12A, 12B, 12C) (12); The adjustment axle (38) that relative coupling shaft (34) can independently be provided with pivotally; Be arranged on the stationary axle of adjusting on the axle (38) (62) coaxially; Be arranged on an end (34A) impeller housing (42) nearby of coupling shaft (34) pivotally; Be supported on the impeller (56) that stationary axle (62) is gone up, formed one simultaneously with impeller housing (42) pivotally; With impeller vis-a-vis, form the turbine (58) of one at an end (38A) of adjusting axle (38); Be arranged on the stator (60) between impeller (56) and the turbine (58); For preventing the contrary overrunning clutch (66) that is arranged between stator (60) and the stationary axle (62) that turns round of stator (60); Between the section 1 (12A) and part 2 (12B) of input shaft, form the direct clutch plate (30) of one with input shaft; The direct clutch (52) that is provided with for the power that cuts off, connects impeller housing (42) and direct clutch plate (30); For preventing that impeller housing (42) from turning round the overrunning clutch (48) that is provided with along the opposite direction of the gyratory directions of coupling shaft (34); Have with the section 1 (12A) of input shaft and form the actuation gear (16) that is connected integratedly and driven gear (20), be arranged on oil pump (14) on the section 1 (12A) of input shaft simultaneously; Accommodate the oil pump case (22) of oil pump (14); For prevent the oil sealing that oil leakage inserts (26C, 26C ', 68C, 72C) and axle bush (40B, 40B ', 70B); Assemble, be fixed in simultaneously the housing (28) of external stability of an end (64) of stationary axle (62) hermetically with oil pump case (22); For transmitting and the power of speed variator system and the clutch connecting plate (82) of an end (38B) the formation one of adjusting axle (38); The through oil hole (74) that forms for the suction of oil and discharge, suck path (76), drain passageway (78) and oily exhaust port (80).
9. by the described speed change adjust system of claim 8, it is characterized in that it also is included as cut-out, connects the dynamic mode clutch (44) that impeller housing (42) is provided with the power of coupling shaft (34).
10. stepless speed changes devices, it comprises: the transmission of power that motor produces is given input shaft, is delivered to the speed variator system of output shaft after speed change; Rotating ratio is adjusted to the speed change adjust system of the load condition of corresponding output shaft; It is characterized in that above-mentioned speed change adjust system comprises: relative input shaft (12) is the coupling shaft of coaxial setting pivotally (34) independently; The adjustment axle (38) that relative coupling shaft (34) can independently be provided with pivotally; The coaxial stationary axle of adjusting on the axle (38) (62) that is arranged at; Be arranged on the impeller housing (42) on the coupling shaft (34) pivotally; Be supported in the impeller (56) that stationary axle (62) is gone up, formed one simultaneously with impeller housing (42) pivotally; With impeller (56) vis-a-vis, with adjust the turbine (58) that axle (38) forms one; Be arranged on the stator (60) between impeller (56) and the turbine (58); For preventing the contrary overrunning clutch (66) that is arranged between stator (60) and the stationary axle (62) that turns round of stator (60); For cutting off, connect the direct clutch (52) that the power between impeller housing (42) and input shaft (12) is provided with; For preventing that impeller housing (42) from turning round the overrunning clutch (48) that is provided with along the opposite direction of the gyratory directions of coupling shaft (34).
11. by the described stepless speed changes devices of claim 10, it is characterized in that it also is included as the power between cut-outs, connection impeller housing (42) and coupling shaft (34) and the dynamic mode clutch (44) that is provided with.
12., it is characterized in that above-mentioned speed variator system comprises by the described stepless speed changes devices of claim 10: and input shaft forms the input sun gear (112) of one; Deceleration sun gear (116) with coupling shaft (34) formation one; A plurality of the 1st planetary pinions (130) that are meshed with input sun gear (112); Form one with the 1st planetary pinion, and a plurality of the 2nd planetary pinions (132) that are meshed with deceleration sun gear (116); Support the 1st and the 2nd planetary pinion (130,132) pivotally, simultaneously form the carriage (118,124) of one with output shaft (138); The gear ring that advances (136) that is meshed with the 2nd planetary pinion (132); Can be independently pivotally with respect to output shaft (138), coaxial setting retreat input shaft (140); With retreat that input shaft (140) forms one retreat sun gear (144); With retreat a plurality of planetary pinions (158) that retreat that sun gear (144) is meshed; Support to retreat the carriage (152,154) of planetary pinion (158) pivotally; With retreat planetary pinion (158) and be meshed, simultaneously retreat gear ring (160) with output shaft (138) forms one; Functionally be connected and adjust axle (38) and retreat clutch coupling shaft (164) between the input shaft (140); For cutting off, connect the forward clutch (166) that the power that advances between gear ring (136) and the clutch coupling shaft (164) is provided with; Be arranged on the overrunning clutch (170) in the outside of clutch coupling shaft (164); For retreating lock (172) to what retreat that carriage (152,154) applies that braking force is provided with.
13., it is characterized in that above-mentioned speed variator system comprises by the described stepless speed changes devices of claim 10: and input shaft forms the input sun gear (112) of one; And coupling shaft (34) forms the deceleration sun gear (116) of one; A plurality of the 1st planetary pinions (212) that are meshed with input sun gear (112); A plurality of the 2nd planetary pinions (230) that form one and be meshed with the 1st planetary pinion (212) with deceleration sun gear (116); Support the carriage (216,226) of the 1st and the 2nd planetary pinion (212,230) pivotally; Be meshed, form with output shaft (138) simultaneously the output gear (214) of one with the 1st planetary pinion (212); For retreating lock (222) to what retreat that carriage (216) applies that braking force is provided with; Adjust axle (38) and retreat the forward clutch (218) that the power between the carriage (216) is provided with for cutting off, connecting.
14., it is characterized in that above-mentioned speed variator system comprises: with the input sun gear (112) of input shaft formation one by the described stepless speed changes devices of claim 10; And coupling shaft (34) forms the deceleration sun gear (116) of one; With deceleration sun gear (116) the adjustment sun gear axle (312) that required separation distance, relative coupling shaft (34) can independently be provided with pivotally of being separated by; With the adjustment sun gear (316) of adjusting sun gear axle (312) formation one; A plurality of the 1st differential gears (340) that are meshed with input sun gear (112); A plurality of the 3rd differential gears (342) that form one and be meshed with the 1st differential gear (340) with deceleration sun gear (116); A plurality of the 2nd differential gears (344) that are meshed with the 3rd differential gear (342); With the 2nd differential gear (344) form one and with adjust a plurality of the 4th differential gears (346) that sun gear (316) is meshed; Support the carriage (332,334) of the 1st differential gear (340), the 3rd differential gear (342), the 2nd differential gear (344) and the 4th differential gear (346) pivotally; Be meshed, form with output shaft (138) simultaneously the output gear (356) of one with the 1st differential gear (340); Have for give adjusting the lock that advances (324) that sun gear axle (312) applies the overrunning clutch (322) that braking force is provided with; Retreat lock (358) for what carriage (332,334) is applied braking force is provided with; Adjust axle and adjust the forward clutch (328) that the power between the sun gear axle (312) is provided with for cutting off, connecting.
15., it is characterized in that above-mentioned speed variator system comprises: with the input sun gear (112) of input shaft formation one by the described stepless speed changes devices of claim 10; Deceleration sun gear (116) with coupling shaft (34) formation one; With deceleration sun gear (116) the adjustment sun gear axle (412) that desired spacing, relative coupling shaft (34) can independently be provided with pivotally of being separated by; With the adjustment sun gear (416) of adjusting sun gear axle (412) formation one; A plurality of the 1st differential gears (432) that are meshed with input sun gear (112); A plurality of the 3rd differential gears (434) that form one, are meshed with the 1st differential gear (432) with deceleration sun gear (116); A plurality of the 2nd differential gears (436) that are meshed with the 3rd differential gear (434); With the 2nd differential gear (436) form one and with adjust a plurality of the 4th differential gears (438) that sun gear (416) is meshed; Support the 1st differential gear (432) pivotally; The 3rd differential gear (434), the 2nd differential gear (436) and the 4th differential gear (438) and form the carriage (422,424) of one with output shaft (138); What be meshed with the 4th differential gear (438) retreats gear ring (448); Have for to adjusting the lock that advances (454) that sun gear axle (412) applies the overrunning clutch (458) that braking force is provided with; For retreating lock (450) to what retreat that gear ring (448) applies that braking force is provided with; Adjust axle (38) and adjust the forward clutch (460) that sun gear axle (412) is provided with for cutting off, connecting.
16., it is characterized in that above-mentioned speed variator system comprises: with the input sun gear (112) of input shaft formation one by the described stepless speed changes devices of claim 10; Deceleration sun gear (116) with coupling shaft (34) formation one; The adjustment bracket axle (512) that relative coupling shaft (34) can independently be provided with pivotally; That relatively adjusts that bracket axle (512) can independently be provided with pivotally retreats sun gear axle (524); With retreat that sun gear axle (524) forms one retreat sun gear (528); With a plurality of the 1st planetary pinions (542) of being meshed of input sun gear (112); A plurality of the 2nd planetary pinions (544) that form one, are meshed with the 1st planetary pinion (542) with deceleration sun gear (116); With the 2nd planetary pinion (544) form one and with retreat that sun gear (528) is meshed a plurality of planetary pinions (546) that retreat; Support the 1st planetary pinion (542), the 2nd planetary pinion (544) and the 3rd planetary pinion (546) pivotally, simultaneously form the carriage (534,536) of one with output shaft (138); And adjustment bracket axle (512) formation one, while prop up pivotally and are held in the adjustment carriage (516) that retreats between planetary pinion (546) and the 2nd planetary pinion (544); For give retreat that sun gear axle (524) applies that braking force is provided with retreat lock (560); Adjust axle (38) and adjust the forward clutch (556) that the power between the bracket axle (512) is provided with for cutting off, connecting.
17. a speed change adjust system is characterized in that it comprises: with respect to the independent coupling shaft of coaxial setting pivotally (34) of input shaft (12); The adjustment axle (38) that can independently be provided with pivotally with respect to coupling shaft (34); Be arranged at the stationary axle of adjusting on the axle (38) (62) with coaxial form; Be arranged at the impeller housing (42) on the coupling shaft (34) pivotally; Be supported on the impeller (56) that stationary axle (62) is gone up, formed one simultaneously with impeller housing (42) pivotally; With impeller (56) vis-a-vis, with adjust the turbine (58) that axle (38) forms one; Be arranged on the stator (60) between impeller (56) and the turbine (58); For preventing that the contrary revolution of stator (60) is arranged on the overrunning clutch (66) between stationary axle (62) and the stator (60); For cutting off, connect the direct clutch (52) that the power between impeller housing (42) and the input shaft (12) is provided with; For preventing that impeller housing (42) from turning round the overrunning clutch (48) that is provided with along the opposite direction of coupling shaft (34) gyratory directions.
18., it is characterized in that it also is included as the power between cut-outs, connection impeller housing (42) and coupling shaft (34) and the dynamic mode clutch (44) that is provided with by the described speed change adjust system of claim 17.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96109424 CN1173597A (en) | 1996-08-09 | 1996-08-09 | Continuously variable transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96109424 CN1173597A (en) | 1996-08-09 | 1996-08-09 | Continuously variable transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1173597A true CN1173597A (en) | 1998-02-18 |
Family
ID=5120351
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 96109424 Pending CN1173597A (en) | 1996-08-09 | 1996-08-09 | Continuously variable transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1173597A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106062424A (en) * | 2013-07-23 | 2016-10-26 | 舍弗勒技术股份两合公司 | Torque converter including an elastic element preloading an axially movable turbine |
| CN108679188A (en) * | 2018-06-06 | 2018-10-19 | 陕西航天动力高科技股份有限公司 | It is a kind of that there is the anti-fluid torque-converter for dragging function |
| US11505063B2 (en) | 2018-05-30 | 2022-11-22 | Carrier Corporation | Energy management systems (EMS) for transportation refrigeration units (TRU) |
-
1996
- 1996-08-09 CN CN 96109424 patent/CN1173597A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106062424A (en) * | 2013-07-23 | 2016-10-26 | 舍弗勒技术股份两合公司 | Torque converter including an elastic element preloading an axially movable turbine |
| US11505063B2 (en) | 2018-05-30 | 2022-11-22 | Carrier Corporation | Energy management systems (EMS) for transportation refrigeration units (TRU) |
| CN108679188A (en) * | 2018-06-06 | 2018-10-19 | 陕西航天动力高科技股份有限公司 | It is a kind of that there is the anti-fluid torque-converter for dragging function |
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