CN101900188A - Automatic speed changer for vehicle - Google Patents
Automatic speed changer for vehicle Download PDFInfo
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- CN101900188A CN101900188A CN 200910201226 CN200910201226A CN101900188A CN 101900188 A CN101900188 A CN 101900188A CN 200910201226 CN200910201226 CN 200910201226 CN 200910201226 A CN200910201226 A CN 200910201226A CN 101900188 A CN101900188 A CN 101900188A
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- clutch
- mentioned
- gear train
- epicyclic gear
- input shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to an automatic speed changer (Z) for a vehicle. A third planetary gear row (P3), a first planet gear row (P1), a second planet gear row (P2) and a normally engaged driving gear (4) are sequentially and abreast arranged on an input shaft (1) from the (E) side of a driving source (F), wherein the third planet gear row (P3) is used for supplying constant deceleration for the automatic speed changer (Z), the first planet gear row (P1) is used for forming the element of the automatic speed changer (Z), the second planet gear row (P2) is used for forming the element of the automatic speed changer (Z), and the normally engaged driving gear (4) is used for outputting a rotary driving force to a middle output shaft (2). The sun gear (s2) of the second planet gear row (P2) is used as a system low-gear input element, the planet carrier (x1) of the first planet gear row (P1) is used as a high-gear input element, and the planet carrier (x2) of the second planet gear row (P2) is permanently connected with the sun gear (s1) of the first planet gear row (P1) and the normally engaged gear (4) of the middle output shaft, thereby avoiding overhigh rotating speed; and the invalid high-speed output of the first planet gear row is isolated through a third clutch between the first planet gear row and the third planet gear row, thereby avoiding the overhigh rotating speed of the third planet gear row. Therefore, a compact and low-noise advance 6-speed automatic speed changer is obtained through three planet gear row mechanisms, three clutches and two brakes.
Description
Technical field
The present invention relates to vehicle automatic transmission, particularly relate to by a plurality of epicyclic gear trains, clutch, break 6 grades the automatic transmission that obtains to advance.
Background technique
Day by day ripe along with automotive engineering, separates the automatic transmission that obtains a plurality of speed change gears and increases day by day joint by a plurality of epicyclic gear trains and clutch, break in the automatic transmission field.At present because day being becoming tight of petroleum resources, and, make many gears speed changer become trend for the fuel consume that reduces car load improves the efficient of speed changer.For automatic transmission, also require to develop more than the forward gears to 6 from 3,4,5 forward gearss in the past.
Automatic transmission at the many gears of preposition forerunner's automobile development requires more harsh, along with increasing of the various auxiliary component of vehicle in driving source cabin, make that the space of leaving automatic transmission for is very limited, therefore many gears automatic transmission should be used compact as far as possible gear train assembly, reduces the component of automatic transmission simultaneously as far as possible.
The speed changer scheme that in CN101315120 and US4070927, is proposed, following a kind of automatic transmission is disclosed, being about to 3 single planetary gear rows uses side by side, wherein 2 of the 1st, the 2nd epicyclic gear train sun gears are permanent connects and imports as system, wherein the planet carrier of the 1st epicyclic gear train is exported as system, output and input part with system is arranged on the same axis simultaneously, make each part bonding of above-mentioned epicyclic gear train with 2 clutches or separate by 3 breaks, thereby realize 6 forward gearss, 1 backward gear.
Adopt the structure in the above-mentioned patent, it is higher that bit is opened the so-called Ravigneaux epicyclic gear train efficient that proposes in the 2000-199549 communique, and system rigidity is better.Yet, the scheme that is proposed in CN101315120 and US4070927 is owing to the 1st forever be connected with 2 sun gears of the 2nd epicyclic gear train, at the sun gear of the 2nd epicyclic gear train the 1st planet row's during as input sun gear also high speed rotating thereupon, cause the sun gear of the 1st epicyclic gear train to do unnecessary high speed rotating at the gear ring of the planet carrier of the 1st epicyclic gear train and the 2nd epicyclic gear train during as input, promptly removing direct high each gear in addition, the sun gear of the 1st epicyclic gear train all is in unnecessary high speed rotating state, and then cause unnecessary wearing and tearing, make transmission efficiency reduce simultaneously.The automatic transmission scheme that in CN101315120 and US4070927, is proposed, because the 3rd epicyclic gear train planet carrier forever is connected with the 2nd epicyclic gear train gear ring that it closes on together, the 3rd epicyclic gear train planet carrier also rotated with rotating speed thereupon when said structure made the rotation of the 2nd epicyclic gear train gear ring, thereby make the 3rd epicyclic gear train gear ring produce unnecessary high speed rotating, wearing and tearing and noise control to gear all bring adverse effect, have reduced transmission efficiency simultaneously.In addition, arrange sun gear owing to forever be connected with the 3rd planet that input shaft forever links to each other away from input end and with input shaft, in input shaft transmission bad system variant that easily causes of rigidity during than high pulling torque, and then can influence the normal engaged of gear, the noise of controlling this automatic transmission is brought adverse effect.In the above-mentioned CN101315120 scheme, 2 clutches are arranged near driving source, 1 break is arranged on the rear end of close speed changer, thereby makes speed changer rear end diameter increase, and is unfavorable for the installation of this automatic transmission in the driving source cabin in preposition forerunner's vehicle.
Summary of the invention
In view of the above problems, the object of the present invention is to provide a kind of transmission efficiency height, small compact, single small gear planet row simple in structure to make up to realize the automatic transmission of 1 backward gear of 6 forward gearss.
To achieve these goals, automatic transmission feature of the present invention comprises: housing; Be arranged on the input shaft in this housing, with input shaft output block away from driving source on same axis, and by comprising sun gear, planetary pinion, the 1st of single pinion type epicyclic gear train formation of planet carrier and gear ring, the 2nd, the 3rd epicyclic gear train, wherein the 1st sun gear of the 1st epicyclic gear train forever is connected with the 2nd planet carrier of the 2nd epicyclic gear train, the planet carrier of the 1st epicyclic gear train forever is connected with the gear ring of the 2nd epicyclic gear train, the sun gear of the 3rd epicyclic gear train forever is connected with input shaft, the gear ring of the 3rd epicyclic gear train forever is connected by spline with case of transmission, the planet carrier of the 2nd epicyclic gear train forever is connected with above-mentioned carry-out part, in addition, also comprise, above-mentioned input shaft is separated with the 2nd epicyclic gear train sun gear, the 1st clutch that engages, above-mentioned input shaft is separated with the planet carrier of the 1st epicyclic gear train and the gear ring of the 2nd epicyclic gear train, the 2nd clutch that engages, the planet carrier of above-mentioned the 3rd epicyclic gear train is separated with the gear ring of the 1st epicyclic gear train, the 3rd clutch that engages, above-mentioned housing is engaged with the gear ring of the 2nd epicyclic gear train and the planet carrier of the 1st epicyclic gear train, the 2nd break that separates, the gear ring of above-mentioned the 1st epicyclic gear train is engaged, the 1st break that separates, realize the 1st forward gears by engaging above-mentioned the 1st clutch and the 2nd break, realize the 2nd forward gears by engaging above-mentioned the 1st clutch and the 1st break, by engaging above-mentioned the 1st clutch and the 3rd clutch device is realized the 3rd forward gears, realize the 4th forward gears by engaging above-mentioned the 1st clutch and the 2nd clutch, realize the 5th forward gears by engaging above-mentioned the 2nd clutch and the 3rd clutch, realize the 6th forward gears by engaging above-mentioned the 2nd clutch and the 1st break, realize backward gear by engaging above-mentioned the 3rd clutch and the 2nd break.
Adopt aforesaid structure, because the sun gear of above-mentioned the 1st epicyclic gear train forever is connected with the planet carrier of the 2nd epicyclic gear train, and the planet carrier of above-mentioned the 2nd epicyclic gear train forever is connected with above-mentioned carry-out part, make that the rotating speed of the planet carrier of sun gear rotating speed and the 2nd epicyclic gear train of above-mentioned the 1st epicyclic gear train and above-mentioned carry-out part is identical, and the sun gear rotating speed of above-mentioned the 1st epicyclic gear train will be far below the rotating speed of above-mentioned the 2nd epicyclic gear train sun gear, thereby prevented that the 1st epicyclic gear train sun gear output speed is too fast, and the gear wear that brings thus, loss in efficiency.And, because reduced the rotating speed of the sun gear of above-mentioned the 1st epicyclic gear train, the high frequency noise of control gear has been played favourable effect in high regime.
In above-mentioned automatic transmission structure, be provided with the constant epicyclic reduction gear row that described input shaft can be rotated constant deceleration output, this epicyclic gear train forever is connected described sun gear with described input shaft, described gear ring forever is connected with described case of transmission, is that the gear ring of the 1st epicyclic gear train is connected with described planet carrier by the 3rd clutch and next epicyclic gear train, for described next epicyclic gear train is that the 1st epicyclic gear train provides constant low speed rotation input, simultaneously owing to this constant epicyclic reduction gear row passes through the effect of clutch with the i.e. invalid high speed output isolation of the 1st epicyclic gear train of next epicyclic gear train, thereby avoided the generation of bad working environments such as the invalid high speed rotating of this epicyclic gear train, to the control gear noise, improve gear life and transmission efficiency and all played positive role.Especially, the friction plate of described the 3rd clutch and steel disc are configured in the position of described constant epicyclic reduction gear row's outer radial periphery side superimposed, and this layout has effectively shortened the axial length of described automatic transmission.
In addition, above-mentioned the 1st clutch and the 2nd clutch adopt nesting type structure, promptly the interior hub of the 1st clutch is as the outer hub of the 2nd clutch, this structure decrease amount of parts, the axial dimension that has effectively shortened described automatic transmission makes this automatic transmission structure more compact, has reduced the manufacture cost of described automatic transmission simultaneously.In addition, described the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives in the source of described output block, and from the central part of the speed changer rear end shell body wall of the anti-driving source that is arranged on these clutches to driving the hub portion that source extends, be provided with oil circuit to hydraulic chamber's supply working oil of described two clutches, perhaps from the central part of the transmission oil pump shell body wall of the driving source that is arranged on these clutches to the hub portion that anti-driving source extends, be provided with oil circuit to hydraulic chamber's supply working oil of described two clutches.
In the said structure, comparatively it is desirable to, one end of above-mentioned input shaft connects driving source, from this end, be arranged side by side the above-mentioned the 3rd single pinion type epicyclic gear train, the above-mentioned the 1st single pinion type epicyclic gear train, the above-mentioned the 2nd single pinion type epicyclic gear train on input shaft successively, above-mentioned carry-out part is arranged on the anti-side that drives source of above-mentioned the 2nd epicyclic gear train.And the 3rd planet that forever links to each other with input shaft in above-mentioned conception row's sun gear is owing to forever be connected near input end and with input shaft, the input shaft transmission during than high pulling torque rigidity better be difficult for causing system variant, thereby reduced because of its system variant to the influence that the normal engaged of gear causes, the noise of controlling this automatic transmission is played positive role.In the such scheme, 2 clutches are arranged on anti-driving source in addition, 2 breaks are arranged on the anti-driving source of above-mentioned carry-out part, thereby make that speed changer rear end diameter is less, make things convenient for the installation of this automatic transmission in front deck in the vehicle preposition forerunner.In horizontal driving source FF (preposition forerunner) the type vehicle that driving source and speed changer are arranged side by side, when using this automatic transmission, can driving torque exported in addition near the position of driving source that is in overall width direction central position.Thus, can with and final gear between the jack shaft of getting in touch constitute shorter, with automatic transmission constitute more compact.
Among the present invention,, comprise gear transmission, chain transmission etc. as the transmission form of " carry-out part ".
In the said structure, another desirable constituted mode is, one end of above-mentioned input shaft connects driving source, the other end from this input shaft, on input shaft, be arranged side by side the above-mentioned the 3rd single pinion type epicyclic gear train, the above-mentioned the 1st single pinion type epicyclic gear train, the above-mentioned the 2nd single pinion type epicyclic gear train successively, above-mentioned carry-out part is arranged on the side that above-mentioned the 2nd epicyclic gear train drives source, and described the 1st, 2 clutches are arranged on described carry-out part and drive source, and described the 1st, 2 breaks are arranged on the anti-driving source of described carry-out part.Therefore, in horizontal driving source FF (preposition forerunner) the type vehicle that driving source and speed changer are arranged side by side, when using this automatic transmission, can promptly driving torque be exported in position near driving source in overall width direction central position.Thus, can with and final gear between the jack shaft of getting in touch constitute shorter, with automatic transmission constitute more compact.
In another aspect of this invention, one end of described input shaft is connected on the driving source, begin on axle, to be arranged side by side successively the 2nd epicyclic gear train, the 1st epicyclic gear train and the 3rd epicyclic gear train from the other end, end at described the 2nd epicyclic gear train is provided with above-mentioned the 1st clutch and the 2nd clutch, described carry-out part, be arranged near the 2nd epicyclic gear train and above-mentioned the 1st clutch and the 2nd clutch one side as output shaft, with input shaft on the axle of same axle.
According to said structure, the present invention can carry out the layout as vertical formula speed changer, is applicable to FR (preposition rear-guard) vehicle.
Description of drawings
Fig. 1 relates to the automatic transmission skeleton diagram of embodiment of the present invention.
Fig. 2 is the chart of joint combination and the gear change relation of expression friction key element.
Fig. 3 A is the speed line chart of velocity ratio of each speed change key element of each gear of expression.
Fig. 3 B is the chart of the ratio of expression gear ratio (speed ratio) of each gear and the velocity ratio between each gear shelves.
Fig. 4 is the detailed section view of expression automatic transmission key position C1 clutch and C2 clutch.
Fig. 5 is the detailed section view of expression automatic transmission key position C3 clutch and epicyclic gear train P3.
Fig. 6 is the detailed structure sectional view of expression B1, B2 break, C3 clutch and planet row P1, P2, P3.
Fig. 7 is that the expression other embodiments of the invention are used the automatic transmission skeleton diagram when soon driving source F will be arranged on the G side
Fig. 8 is that the expression other embodiments of the invention are used the automatic transmission skeleton diagram when promptly indulging the formula gearbox arrangement
Embodiment
Below, based on accompanying drawing preferred implementation of the present invention is described in detail.
The 1st mode of execution
Fig. 1 is the plane skeleton diagram of Power Train that adopts the automatic transmission of first embodiment of the invention.
As shown in Figure 1, this automatic transmission Z is applied to the so-called FF type Power Train of horizontal lift-launch in vehicle.This automatic transmission Z constitutes as the shift drive mechanism of the three-axis structure that has respectively the input shaft 1, jack shaft 2 and the live axle 3 that extend in the overall width direction.
On the input shaft 1 of automatic transmission Z, from driving source E side (being designated hereinafter simply as " speed changer front side ") be disposed with the 3rd epicyclic gear train P3 of the fluid torque converter 8 that ends clutch with lock, performance low speed speed increasing mechanism function, to the countershaft drive gear 4 of jack shaft 2 output rotary driving forces, constitute the 1st epicyclic gear train P1 of speed change key element and constitute the 2nd epicyclic gear train P2 of speed change key element equally.
In addition, on the jack shaft 2, be disposed with the counter shaft driven gear 5 of countershaft drive gear 4 engagement, to the final actuation gear 6 of live axle 3 outputting rotary powers from anti-driving source E side (hereinafter to be referred as " speed changer rear side ").
In addition, live axle 3 is provided with the final driven gear 7 (differential mechanism gear ring) of above-mentioned final actuation gear 6 engagements, is positioned at the differential gearing 9 of all sides of this final driven gear 7, rotating force is passed to left and right sides semiaxis Y, the Y of the not shown left and right wheels in the overall width direction outside from this differential gearing.
Gear on the input shaft 1, remove the 1st～the 3rd above-mentioned epicyclic gear train P1, P2, outside the P3, the 1st clutch C1 and the 2nd clutch C2 that also comprise the speed changer rear side that is arranged on the 2nd epicyclic gear train P2, and be arranged on the 3rd clutch C3 between the 1st epicyclic gear train and the 3rd epicyclic gear train, wherein the 1st clutch C1 is used for engaging input shaft and the 2nd epicyclic gear train sun gear, the 2nd clutch is used for engaging input shaft and the 1st epicyclic gear train planet carrier and the 2nd epicyclic gear train gear ring, and the 3rd clutch is used for engaging the 3rd epicyclic gear train planet carrier and the 1st epicyclic gear train gear ring.
In addition, at the outer circumferential side of the 1st epicyclic gear train P1, the 2nd epicyclic gear train P2, be provided with the 1st break, the 2nd break that utilize this automatic transmission housing H to prevent the rotation of speed change key element.Wherein, the 1st break is used for preventing the rotation of the 1st epicyclic gear train gear ring, and the 2nd break is used for preventing the rotation of the 2nd epicyclic gear train gear ring and the 1st epicyclic gear train planet carrier.Above-mentioned the 1st～the 3rd epicyclic gear train P1, P2, P3, all single pinion type epicyclic gear train for constituting by sun gear, gear ring, single planetary gear and support single planetary gear planet carrier.Be convenient narration, do following regulation in the present invention: comprise the 1st sun gear s1, the 1st gear ring r1 and the 1st planet carrier x1 among the 1st epicyclic gear train P1, comprise the 2nd sun gear s2, the 2nd gear ring r2 and the 2nd planet carrier x2 among the 2nd epicyclic gear train P2, comprise the 3rd sun gear s3, the 3rd gear ring r3 and the 3rd planet carrier x3 among the 3rd epicyclic gear train P3.
According to shown in Figure 6, below annexation of this automatic transmission etc. is elaborated.
Among the 3rd epicyclic gear train P3, the 3rd sun gear s3 and input shaft 1 forever are connected by spline, the 3rd gear ring r3 forever is connected by spline with case of transmission H2, thereby the 3rd planet carrier x3 of the 2nd epicyclic gear train P3 is as the constant speed deceleration output of this epicyclic gear train, the 3rd planet carrier x3 is connected by the 3rd clutch C3 with the 1st gear ring r1 and imports as the low speed of the 1st epicyclic gear train P1, thereby when the 3rd, the 5th forward gears, provide the low speed input of 2DOF, for it provides low speed speedup function for the 1st epicyclic gear train P1.
Among the 1st epicyclic gear train P1, the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 of the 2nd epicyclic gear train P2, and the 1st planet carrier x1 forever is connected with the 2nd gear ring r2 of the 2nd epicyclic gear train, and the 1st planet carrier is connected with input shaft 1 by the 2nd clutch C2.
Among the 2nd epicyclic gear train P2, the 2nd sun gear s2 is connected with input shaft 1 by the 1st clutch C1, and the 2nd planet carrier x2 forever is connected with countershaft drive gear (above-mentioned carry-out part) 4, and the 2nd gear ring is connected with case of transmission H2 by the 2nd break.
Especially, because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, thereby avoided the high speed rotating of the 1st sun gear.
Above-mentioned the 1st, the 2nd epicyclic gear train P1, P2 have 4 degrees of freedom such as the 2nd sun gear s2, the 1st sun gear s1 and the 2nd planet carrier x2, the 1st planet carrier x1 and the 2nd gear ring r2, the 1st gear ring r1, can realize 4 forward gearss.
Among the 3rd epicyclic gear train P3, the 3rd sun gear s3 forever is connected with input shaft by spline, the 3rd gear ring forever is connected with case of transmission H2 by spline and is fixed on the housing H2, the 3rd planet carrier x3 is as the constant deceleration output of the 3rd epicyclic gear train P3, and the 3rd planet carrier x3 is connected with the 1st planet carrier x1 of the 1st epicyclic gear train by clutch C3, as the low speed speed increasing mechanism of above-mentioned the 1st, the 2nd epicyclic gear train P1, P2,6 forward gearss and 1 reverse gear have been realized by combination with the 1st, the 2nd epicyclic gear train P1, P2.
The automatic transmission Z that possesses the said structure key element, by not shown hydraulic control system 5 friction key elements are engaged and the control that separates, drive situations such as situation, driving source rotating speed, the speed of a motor vehicle, vehicle load simultaneously according to reality, select suitable gear to carry out speed Control thereby the not shown electronic control system for automatic speed transmission of process calculates.
Fig. 2 represents the joint of each clutch C1, C2, C3 and break B1, B2 in each gear, the joint action figure of separated state (wherein о represents to engage, and does not have this and is labeled as separation).Wherein, the 1st clutch C1 engages at the 1st～the 4th forward gears, therefore be called as the bottom gear clutch, the 2nd clutch C2 engages at the 4th～the 6th forward gears, therefore be called as the top gear clutch, the 3rd clutch engages at the 3rd, the 5th forward gears and backward gear, therefore is called as 3/5/ reverse clutch.The 1st break engages at the 2nd, the 6th forward gears, therefore is called as 2/6 grade of break, and the 2nd break engages at the 1st forward gears and reverse gear, therefore is called as 1/ reverse gear brake.
Fig. 3 A is the speed line chart of the velocity ratio of expression each gear each speed change key element, and Fig. 3 B is the chart of the ratio of the gear ratio of each gear of expression and the velocity ratio between each gear shelves.
Following elder generation describes with regard to the speed line chart of Fig. 3 A.
In this speed line chart, the longitudinal axis is represented each speed change key element of the 1st～the 3rd epicyclic gear train P1, P2, P3, and the horizontal spacing between each longitudinal axis is by the ratio decision of the gear ratio of each speed change key element.The speed change key element that 3 longitudinal axis on the left side are represented the 3rd epicyclic gear train P3 from left to right successively respectively i.e. the 3rd gear ring r3, the 3rd planet carrier x3, the 3rd sun gear s3, and 4 longitudinal axis on the right are represented the 1st sun gear s1 and the 2nd planet carrier x2 of the 2nd epicyclic gear train P2, the 2nd sun gear s2 of the 2nd epicyclic gear train P2 of the 2nd gear ring r2, the 1st epicyclic gear train P1 of the 1st planet carrier x1 of the 1st gear ring r1 of the 1st epicyclic gear train P1, the 1st epicyclic gear train P1 and the 2nd epicyclic gear train P2 from left to right successively.In addition, r2 represents permanent the connection with x1, x2 with the short longitudinal axis between the s1 among the figure.
In this speed line chart, the transverse axis that dotted line is represented is represented the input (being input shaft 1) of system, and the long solid line transverse axis below the above-mentioned short solid line transverse axis is represented housing.
In this speed line chart, 5 frictions of " " expression key element, " о " represents the system output of each gear, if will long solid line transverse axis regard zero line as and be " just " with the sense of rotation of input shaft, then following being output as of this zero line is output as " just " more than " bear " zero line.
Method for changing speed
According to the schematic diagram of this automatic transmission of Fig. 1 and clutch, brake engages relation shown in Figure 2, the method for changing speed to the related automatic transmission of this enforcement describes below.
The 1st forward gears is realized by above-mentioned the 1st clutch C1 and the 2nd break B2 are engaged.In other words, pass to the 2nd sun gear s2 of the 2nd epicyclic gear train P2 from the power of input shaft 1 input via the 1st clutch C1, the joint of B2 makes the 2nd gear ring r2 and the 1st planet carrier x1 and housing be connected as a single entity simultaneously becomes state of rest.At the 2nd epicyclic gear train P2, the 2nd sun gear s2 imports as system, and the 2nd gear ring is fixed, and then the 2nd planet carrier x2 is as output, thereby realizes the 1st forward gears.
The 2nd forward gears is realized by described the 1st clutch C1 and the 1st break B1 are engaged.In other words, pass to the 2nd sun gear s2 of the 2nd epicyclic gear train P2 from the power of input shaft 1 input via the 1st clutch C1, the joint of B1 makes the 1st gear ring r1 and case of transmission be connected as a single entity simultaneously becomes state of rest.Because the 2nd gear ring r2 forever is connected with the 1st planet carrier x1, and the 1st sun gear s1 forever is connected with the 2nd planet carrier x2, according to the linear speed figure of Fig. 3 A and for the 2nd epicyclic gear train P2, the 2nd gear ring r2 and the 2nd sun gear s2 be simultaneously as system's input, just obtains reduction speed ratio thus less than 1 grade the 2nd forward gears.
The 3rd forward gears is realized by described the 1st clutch C1 and the 3rd clutch C3 are engaged.In other words, pass to the 2nd sun gear s2 of the 2nd epicyclic gear train P2 via the 1st clutch C1 from the power of input shaft 1 input, for the 3rd epicyclic gear train P3, the 3rd sun gear s3 imported with 1 permanent the connection as system of input shaft, the 3rd gear ring r3 forever is connected with case of transmission H2, and the 3rd planet carrier x3 is as the constant deceleration output of the 3rd epicyclic gear train.Simultaneously since the 3rd planet carrier x3 and the 1st gear ring r1 connect as one by the 3rd clutch C3, therefore the low speed rotation of the 3rd planet carrier x3 of the 3rd epicyclic gear train P3 passes to the 1st gear ring r1 of the 1st epicyclic gear train P1 by C3, for the 1st, the 2nd epicyclic gear train P1, P2, the input of this system has and the 2nd sun gear s2 of input shaft with rotating speed, and be lower than the low speed rotation input of input shaft rotating speed by the rotational speed that x3 passes to r1, just obtain reduction speed ratio thus less than 2 grades the 3rd forward gears.The 4th forward gears is realized by described the 1st clutch C1 and the 2nd clutch C2 are engaged.In other words, pass to the 2nd sun gear s2 of the 2nd epicyclic gear train P2 via the 1st clutch C1 from the power of input shaft 1 input, and the 1st planet carrier x1 that passes to the 1st epicyclic gear train P1 via the 2nd clutch C2, forever be connected with the 2nd gear ring r2 owing to the 1st planet carrier x1 simultaneously, at the 2nd epicyclic gear train P2, the 2nd sun gear s2 is identical as system's input and rotating speed simultaneously with the 2nd gear ring r2, the output speed of the 2nd planet carrier x2 is also identical with input speed thus, thereby obtains output speed and corresponding to the 4th forward gears of input speed (being also referred to as direct high).
The 5th forward gears is realized by described the 2nd clutch C2 and the 3rd clutch C3 are engaged.In other words, pass to the 1st planet carrier x1 of the 1st epicyclic gear train P1 via the 2nd clutch C2 from the power of input shaft 1 input, for the 3rd epicyclic gear train P3, the 3rd sun gear s3 imported with 1 permanent the connection as system of input shaft, the 3rd gear ring r3 forever is connected with case of transmission H2, and the 3rd planet carrier x3 is as the constant deceleration output of the 3rd epicyclic gear train.Because the 3rd planet carrier x3 and the 1st gear ring r1 connect as one by the 3rd clutch C3, therefore the low speed rotation of the 3rd planet carrier x3 of the 3rd epicyclic gear train P3 passes to the 1st gear ring r1 of the 1st epicyclic gear train P1 by C3 simultaneously.For the 1st epicyclic gear train P1, the 1st planet carrier x1 is connected as a single entity by C1 and input shaft and imports as system, the 1st gear ring r1 is connected as a single entity as system's speedup input by C3 and x3, the 1st sun gear s1 exports as system simultaneously, because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, just obtain 5th forward gears of reduction speed ratio thus less than 1 hypervelocity driving.
The 6th forward gears is realized by described the 2nd clutch C2 and the 1st break B1 are engaged.In other words, pass to the 1st planet carrier x1 of the 1st epicyclic gear train P1 from the power of input shaft 1 input via the 2nd clutch C2, the joint of B1 makes the 1st gear ring r1 and case of transmission be connected as a single entity simultaneously becomes state of rest.At the 1st epicyclic gear train P1, the 1st gear ring r1 fixes, the 1st planet carrier x1 imports as system, the 1st sun gear s1 is as output at a high speed, because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, just obtain 6th forward gears of reduction speed ratio thus less than the 5th grade hypervelocity driving.
Backward gear (Rev) is realized by described the 2nd break B2 and the 3rd clutch C3 are engaged.In other words, the 3rd sun gear s3 imported with 1 permanent the connection as system of input shaft, the 3rd gear ring r3 forever is connected with case of transmission H2, the 3rd planet carrier x3 is as the constant deceleration output of the 3rd epicyclic gear train, engaging clutch C3 makes the 3rd planet carrier x3 and the 1st gear ring r1 connect as one by the 1st clutch C3, therefore the 1st gear ring r1 is as the input of the 1st epicyclic gear train P1, and the joint of B1 makes the 1st gear ring r1 and case of transmission be connected as a single entity becomes state of rest, thereby the 1st sun gear s1 counterrotating is exported as system, because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, just obtain exporting the sense of rotation backward gear opposite thus with input.
In above-described speed change, if the number of teeth of each gear is set in following tabulation 1 like that, then the ratio of the velocity ratio of each gear stage and velocity ratio is shown in Fig. 3 B.
| Sun gear | Gear ring | Planet |
Planet |
|
| The 1st epicyclic gear train P1 | 64 | 88 | 13 | 0 |
| The 2nd epicyclic gear train P2 | 28 | 58 | 15 | 0 |
| The 3rd epicyclic gear train P3 | 55 | 62 | 10 | 0 |
The number of teeth of table 1-gear is set
Fig. 4 is the detailed section view of expression automatic transmission key position C1 clutch and C2 clutch,
Wherein, H1 is the rear case of described automatic transmission, this rear case is connected with main casing by not shown bolt, the outer hub 12 of C1 clutch links to each other with disc-shaped part 10 by spline, and parts 10 are rigidly connected with described the 2nd epicyclic gear train sun gear s2, it is continuous with the friction plate of C1 that outer hub 13 outer circumferential sides of C2 are provided with spline, be the interior hubs of 13 whiles of parts as C1, this parts 13 are rigidly connected with input shaft 1 and are one simultaneously, and C1, C2 clutch are arranged near near the driven shaft actuation gear 4.And from the central part of the speed changer rear end housing H1 of the anti-driving source that is arranged on these clutches to driving the hub portion that source extends, be provided with oil circuit to hydraulic chamber's supply working oil of described two clutch C1, C2.
Fig. 5 is the detailed section view of expression automatic transmission key position C3 clutch and epicyclic gear train P3,
Wherein, clutch C3 is arranged on the space between the planet carrier x1 of the 3rd epicyclic gear train P3 and the 1st epicyclic gear train P1, and the friction plate of C3 clutch and steel disc have at least a part to be arranged in the outer circumferential side of the 3rd epicyclic gear train P3 and the space between the described automatic transmission main casing H2, thereby have effectively shortened the axial dimension of this automatic transmission.
The effect of implementing
Therefore, the automatic transmission 1 related according to embodiment, adopt aforesaid structure, because the 1st sun gear s1 of above-mentioned the 1st epicyclic gear train P1 forever is connected with the 2nd planet carrier x2 of the 2nd epicyclic gear train P2, and the 2nd planet carrier x2 of above-mentioned the 2nd epicyclic gear train P2 forever is connected with above-mentioned carry-out part (being countershaft drive gear 4), therefore prevented that the 1st sun gear s1 output speed of the 1st epicyclic gear train P1 is too fast, and gear wear that brings thus and loss in efficiency.And, because reduced the rotating speed of the 1st sun gear s1 of above-mentioned the 1st epicyclic gear train P1, the control gear noise has been played favourable effect in high regime.
In above-mentioned automatic transmission structure, the 3rd sun gear s3 of the 3rd epicyclic gear train P3 forever is connected with input shaft 1 and it is arranged on a side of close driving source, thereby increased the torsional stiffness of the 3rd sun wheel shaft of above-mentioned the 3rd epicyclic gear train P3, make when this planetary pinion comes the low-grade location transmission than high pulling torque, transmission error when avoiding increasing gear engagement plays advantageous effects to the control of system noise.In the automatic transmission structure that the present invention simultaneously takes, be provided with the constant epicyclic reduction gear row P3 that described input shaft can be rotated constant deceleration output, this epicyclic gear train forever is connected described sun gear s3 with described input shaft 1, described gear ring r3 forever is connected with described case of transmission H2, described planet carrier x3 is connected with the gear ring r1 of next epicyclic gear train P1 by clutch C3, for described next epicyclic gear train P1 provides constant low speed rotation input, simultaneously owing to this constant epicyclic reduction gear row P3 isolates the invalid high speed output of next epicyclic gear train P1 by the effect of clutch C3, thereby avoided the generation of the bad working environments such as invalid high speed rotating of this epicyclic gear train P3, to the control gear noise, improve gear life and transmission efficiency and all played positive role.Especially, the friction plate of described clutch C3 and steel disc are configured in the position of the outer radial periphery side superimposed of described constant epicyclic reduction gear row P3, and this layout has effectively shortened the axial length of described automatic transmission Z.
In addition, above-mentioned the 1st clutch C1 and the 2nd clutch C2 adopt nesting type structure, promptly the interior hub of the 1st clutch C1 is as the outer hub of the 2nd clutch C2, this structure decrease amount of parts, the axial dimension that has effectively shortened speed changer makes this automatic transmission more compact, has reduced the manufacture cost of speed changer simultaneously.
In addition, according to said structure, the present invention can carry out the layout as vertical formula speed changer, is applicable to FR (preposition rear-guard) vehicle.
Other embodiments
Can adopt following structure simultaneously among the described embodiment of the present invention,
Promptly as shown in Figure 7, Fig. 7 is that the expression other embodiments of the invention are used the automatic transmission skeleton diagram when soon driving source F will be arranged on the G side.Be to be research object in described embodiment with FF (preposition forerunner's type) car.Driving source F is arranged in an end E of input shaft 1, in addition, also driving source F can be arranged in the other end G side, and from this side be arranged side by side the 1st, 2 clutches successively, described automatic transmission carry-out part is driven shaft actuation gear the 4, the 2nd epicyclic gear train P2, the 1st epicyclic gear train P1, the 3rd epicyclic gear train P3.
Perhaps as shown in Figure 8, under the situation that the present invention is applied to FR (preposition rear-guard type) car, as long as input shaft 1 one ends are connected the E side of driving source F, begin to be arranged side by side successively the 1st, 2 clutches, the 2nd epicyclic gear train P2, the 1st epicyclic gear train P1, the 3rd epicyclic gear train P3 from opposite side and get final product.In this case, be that the axle of same axle is provided with the output shaft 2 that this automatic transmission Z output is connected with not shown live axle with input shaft 1, this output shaft 2 is connected on the not shown live axle.By such layout, can arrange as the vertical formula speed changer of the most suitable FR (preposition rear-guard type) car.
Remark additionally a bit, the foregoing description is as desirable example, and the present invention does not limit its scope of using thing and purposes etc.
Claims (10)
1. vehicle automatic transmission,
The input shaft that rotates according to the output of driving source is being set, have with described input shaft at same axis and be arranged on and drive source or the anti-carry-out part that drives a side in the source, has sun gear, single small planetary gear, planet carrier, single pinion type epicyclic gear train of gear ring rotation key element, have and to output to the low speed speedup epicyclic gear train of next epicyclic gear train after the constant deceleration of the rotation of described input shaft, has the output mechanism that described the 1st epicyclic gear train sun gear and the 2nd epicyclic gear train planet carrier and described carry-out part are connected as a single entity
Have the 1st clutch between described input shaft and described the 2nd epicyclic gear train sun gear,
Have the 2nd clutch that is between described input shaft and described the 1st epicyclic gear train planet carrier,
Have the 3rd clutch that is between described the 1st epicyclic gear train gear ring and described the 3rd epicyclic gear train planet carrier, it is characterized in that:
Described automatic transmission, carry-out part and the coaxial setting of input shaft comprise the 1st to the 3rd single pinion type epicyclic gear train, 2 multi-plate brakes and 3 multidisc clutches,
The above-mentioned the 1st single pinion type epicyclic gear train has the 1st sun gear, the 1st planet carrier and the 1st gear ring, the above-mentioned the 2nd single pinion type epicyclic gear train has the 2nd sun gear, the 2nd planet carrier and the 2nd gear ring, the above-mentioned the 3rd single pinion type epicyclic gear train has the 3rd sun gear, the 3rd planet carrier and the 3rd gear ring
Above-mentioned the 3rd sun gear and input shaft, above-mentioned the 3rd gear ring and described automatic transmission housing, above-mentioned the 1st planet carrier and the 2nd gear ring, above-mentioned the 1st sun gear and the 2nd planet carrier and carry-out part all forever connect,
Possess the 1st clutch that separate to engage above-mentioned input shaft and the 2nd sun gear, separate the 2nd clutch that engages above-mentioned input shaft and the 1st planet carrier and the 2nd gear ring, separate the 3rd clutch that engages above-mentioned the 3rd planet carrier and the 1st gear ring, separate the 1st break that engages above-mentioned the 1st gear ring and case of transmission, separate the 2nd break that engages above-mentioned the 2nd gear ring and case of transmission
Realize the 1st forward gears by engaging above-mentioned the 1st clutch and the 2nd break, realize the 2nd forward gears by engaging above-mentioned the 1st clutch and the 1st break, realize the 3rd forward gears by engaging above-mentioned the 1st clutch and the 3rd clutch, realize the 4th forward gears by engaging above-mentioned the 1st clutch and the 2nd clutch, realize the 5th forward gears by engaging above-mentioned the 2nd clutch and the 3rd clutch, realize the 6th forward gears by engaging above-mentioned the 2nd clutch and the 1st break, realize backward gear by engaging above-mentioned the 3rd clutch and the 2nd break.
2. automatic transmission according to claim 1 is characterized in that:
Above-mentioned the 4th grade is set at the direct high of exporting from carry-out part with original rotating speed from the rotation of input shaft.
3. automatic transmission according to claim 1 is characterized in that:
Above-mentioned the 1st epicyclic gear train is arranged between the Hydrauservo System and described the 2nd epicyclic gear train of described the 3rd clutch, above-mentioned the 2nd epicyclic gear train is arranged between described carry-out part and described the 1st epicyclic gear train, above-mentioned the 3rd epicyclic gear train is arranged on the driving source or an anti-side that drives in the source of described the 3rd clutch equalizing piston, and described the 3rd clutch friction plate is configured in the position of the outer radial periphery side superimposed of at least a portion and described the 3rd epicyclic gear train.
4. automatic transmission according to claim 1 is characterized in that:
One end of above-mentioned input shaft connects driving source, from this end or an anti-end that drives source, be arranged side by side the above-mentioned the 3rd single pinion type epicyclic gear train, the above-mentioned the 1st single pinion type epicyclic gear train, the above-mentioned the 2nd single pinion type epicyclic gear train on input shaft successively, above-mentioned carry-out part with the coaxial setting of input shaft is arranged between the above-mentioned the 2nd single pinion type epicyclic gear train and above-mentioned the 1st, the 2nd clutch.
5. automatic transmission according to claim 4 is characterized in that:
Described the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives source of described output block, and described the 1st, the 2nd break is arranged on the driving source or the anti-opposite side that drives the described side in the source of described output block.
6. automatic transmission according to claim 4 is characterized in that:
Above-mentioned the 1st clutch and above-mentioned the 2nd clutch be arranged on the above-mentioned the 2nd single pinion type epicyclic gear train near.
7. according to claim 3 or 4 described automatic transmission, it is characterized in that:
Described the 1st, the 2nd clutch nesting type setting diametrically.The interior hub portion of described the 1st clutch is as the outer hub of the 2nd clutch, the friction plate of the outer hub splined joint of all sides and described the 2nd clutch in described the 1st clutch has, comprise Hydrauservo System and with the outer circumferential side splined joint of this friction plate, and the outer hub of the 1st clutch that is connected with described the 2nd epicyclic gear train sun gear, compress the 1st clutch plunger of this friction plate, and the hydraulic pressure cavity that forms between the interior all sides by above-mentioned this piston of oil sealing sealing and outer circumferential side and the outer hub of the 1st clutch
In described the 2nd clutch has all sides be connected described the 1st epicyclic gear train planet carrier on the parts splined joint friction plate, comprise the hydraulic servo-machine construction system and with the outer circumferential side splined joint of this friction plate and the 2nd clutch that is connected with described input shaft outward hub, compress the hydraulic pressure cavity that the 2nd clutch plunger of this friction plate and the interior all sides by above-mentioned this piston of oil sealing sealing and outer circumferential side and above-mentioned the 2nd clutch form between the hub outward
The friction plate of the parts splined joint in described the 3rd clutch has on all sides and described input rotation key element that is connected described constant epicyclic reduction gear row or the described output key element, comprise Hydrauservo System and and the outer hub of the 3rd clutch of the outer circumferential side splined joint of this friction plate, compress the hydraulic pressure cavity that forms between the hub outside the 3rd clutch plunger of this friction plate, the interior all sides by above-mentioned this piston of oil sealing sealing and outer circumferential side and the 3rd clutch.
8. automatic transmission according to claim 7 is characterized in that:
Described the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives in the source of described output block, and from the central part of the speed changer rear end shell body wall of the anti-driving source that is arranged on these clutches to driving the hub portion that source extends, be provided with oil circuit to hydraulic chamber's supply working oil of described two clutches, perhaps from the central part of the transmission oil pump shell body wall of the driving source that is arranged on these clutches to the hub portion that anti-driving source extends, be provided with oil circuit to hydraulic chamber's supply working oil of described two clutches.
9. according to claim 3 and 4 described automatic transmission, it is characterized in that:
Above-mentioned the 1st break, above-mentioned the 2nd break are arranged on the outer circumferential side of the above-mentioned the 1st single pinion type epicyclic gear train, the above-mentioned the 2nd single pinion type epicyclic gear train, and are arranged side by side in the axial direction.
10. automatic transmission according to claim 5 is characterized in that:
Above-mentioned the 1st break is arranged between above-mentioned the 3rd clutch and above-mentioned the 2nd break, and above-mentioned the 2nd break is arranged near near the 1st clutch and the 2nd clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910201226 CN101900188B (en) | 2009-12-16 | 2009-12-16 | Automatic speed changer for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200910201226 CN101900188B (en) | 2009-12-16 | 2009-12-16 | Automatic speed changer for vehicle |
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| CN101900188A true CN101900188A (en) | 2010-12-01 |
| CN101900188B CN101900188B (en) | 2012-03-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200910201226 Expired - Fee Related CN101900188B (en) | 2009-12-16 | 2009-12-16 | Automatic speed changer for vehicle |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244624A (en) * | 2012-02-08 | 2013-08-14 | 黄振强 | Novel automatic gearbox of stepless gear |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4070927A (en) * | 1976-06-04 | 1978-01-31 | General Motors Corporation | Planetary gearing arrangement for a transmission |
| US7140997B2 (en) * | 2003-07-31 | 2006-11-28 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| KR100610791B1 (en) * | 2004-09-01 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
| JP2008075721A (en) * | 2006-09-20 | 2008-04-03 | Mazda Motor Corp | Automatic transmission |
| JP2008298126A (en) * | 2007-05-30 | 2008-12-11 | Mazda Motor Corp | Automatic transmission |
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2009
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103244624A (en) * | 2012-02-08 | 2013-08-14 | 黄振强 | Novel automatic gearbox of stepless gear |
| WO2013116957A1 (en) * | 2012-02-08 | 2013-08-15 | Huang Zhenqiang | Continuously variable automatic gearbox |
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| CN101900188B (en) | 2012-03-28 |
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