CN101900188B - Automatic speed changer for vehicle - Google Patents
Automatic speed changer for vehicle Download PDFInfo
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- CN101900188B CN101900188B CN 200910201226 CN200910201226A CN101900188B CN 101900188 B CN101900188 B CN 101900188B CN 200910201226 CN200910201226 CN 200910201226 CN 200910201226 A CN200910201226 A CN 200910201226A CN 101900188 B CN101900188 B CN 101900188B
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- gear train
- epicyclic gear
- epicyclic
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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)
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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 through 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 gear and increases day by day joint through 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 to 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; Be about to 3 single planetary gears rows and use side by side, wherein 2 of the 1st, the 2nd epicyclic gear train sun gears are permanent connects and as system's input, 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; Through 3 breaks and 2 clutches each part bonding of above-mentioned epicyclic gear train is perhaps separated, 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 in CN101315120 and US4070927, is proposed 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 at each gear of removing beyond the direct high, 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,, reduced transmission efficiency simultaneously the wearing and tearing of gear and noise control deleterious impact all.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; Rigidity is bad during than high pulling torque is prone to cause system variant in the input shaft transmission; And then can influence the normal engaged of gear, to controlling the noise deleterious impact of this automatic transmission.In the above-mentioned CN101315120 scheme; 2 clutches are arranged near driving source; 1 break is arranged on the rear end near speed changer, thereby makes speed changer rear end diameter increase, and in preposition forerunner's vehicle, is unfavorable for the installation of this automatic transmission in the driving source cabin.
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, 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 characteristic 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 the 1st, the 2nd, the 3rd epicyclic gear train that constitutes by the single pinion type epicyclic gear train that comprises sun gear, planetary pinion, planet carrier and gear ring; 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, and the planet carrier of the 1st epicyclic gear train forever is connected with the gear ring of the 2nd epicyclic gear train, and 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 through 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 comprises; The 1st clutch that makes above-mentioned input shaft and the 2nd epicyclic gear train sun gear separate, engage; The 2nd clutch that makes the gear ring of planet carrier and the 2nd epicyclic gear train of above-mentioned input shaft and the 1st epicyclic gear train separate, engage makes the planet carrier and the 3rd clutch that the gear ring of the 1st epicyclic gear train separates, engages of above-mentioned the 3rd epicyclic gear train, the 2nd break that makes the planet carrier of gear ring and the 1st epicyclic gear train of above-mentioned housing and the 2nd epicyclic gear train engage, separate; Make the gear ring joint of above-mentioned the 1st epicyclic gear train, the 1st break that separates; Realize the 1st forward gears through engaging above-mentioned the 1st clutch and the 2nd break, realize the 2nd forward gears, through engaging above-mentioned the 1st clutch and the 3rd clutch device is realized the 3rd forward gears through engaging above-mentioned the 1st clutch and the 1st break; Realize the 4th forward gears through engaging above-mentioned the 1st clutch and the 2nd clutch; Realize the 5th forward gears through engaging above-mentioned the 2nd clutch and the 3rd clutch, realize the 6th forward gears, realize backward gear through engaging above-mentioned the 3rd clutch and the 2nd break through engaging above-mentioned the 2nd clutch and the 1st 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 planet carrier and above-mentioned carry-out part of sun gear rotating speed and the 2nd epicyclic gear train of above-mentioned the 1st epicyclic gear train 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 has 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 can said input shaft be rotated constant deceleration output; This epicyclic gear train forever is connected said sun gear with said input shaft; Said gear ring forever is connected with said case of transmission; With said planet carrier through the 3rd clutch and next epicyclic gear train promptly the gear ring of the 1st epicyclic gear train is connected, for said next epicyclic gear train promptly the 1st epicyclic gear train constant low speed rotation input is provided, simultaneously since should constant epicyclic reduction gear row effect through clutch be that the invalid high speed of the 1st epicyclic gear train is exported isolation with next epicyclic gear train; Thereby avoided the generation of bad working environments such as the invalid high speed rotating of this epicyclic gear train, control gear noise, raising gear life and transmission efficiency have all been played positive role.Especially, the friction plate of said the 3rd clutch and steel disc are configured in the position of said constant epicyclic reduction gear row's outer radial periphery side superimposed, and this layout has effectively shortened the axial length of said 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 said automatic transmission makes this automatic transmission structure more compact, has reduced the manufacture cost of said automatic transmission simultaneously.In addition; Said the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives in the source of said 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 said 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 said two clutches.
In the said structure; Comparatively it is desirable to; One end of above-mentioned input shaft connects driving source; Begin from this end, 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 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; A kind of in addition desirable constituted mode does; One end of above-mentioned input shaft connects driving source; Begin from the other end of 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 said the 1st, 2 clutches are arranged on said carry-out part and drive source, and said the 1st, 2 breaks are arranged on the anti-driving source of said 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 said 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, be provided with above-mentioned the 1st clutch and the 2nd clutch, said carry-out part at an end of said the 2nd epicyclic gear train; 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 ratio of gear ratio (speed ratio) and the velocity ratio between each gear shelves of each gear of expression.
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 other embodiments of expression the present invention use the automatic transmission skeleton diagram when soon driving source F will be arranged on the G side
Fig. 8 is that other embodiments of expression the present invention use 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 detailed.
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; Except that the 1st～the 3rd above-mentioned epicyclic gear train P1, P2, 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, and 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, the following annexation of facing 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 through spline; The 3rd gear ring r3 forever is connected through 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 through the 3rd clutch C3 with the 1st gear ring r1 and imports as the low speed of the 1st epicyclic gear train P1, thereby is the low speed input that the 1st epicyclic gear train P1 provides 2DOF when the 3rd, the 5th forward gears, for it provides low speed speedup function.
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 through the 2nd clutch C2.
Among the 2nd epicyclic gear train P2, the 2nd sun gear s2 is connected with input shaft 1 through 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 through 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 through spline; The 3rd gear ring forever is connected with case of transmission H2 through 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 through clutch C3, as the low speed speed increasing mechanism of above-mentioned the 1st, the 2nd epicyclic gear train P1, P2, has realized 6 forward gearss and 1 reverse gear through the combination with the 1st, the 2nd epicyclic gear train P1, P2.
The automatic transmission Z that possesses the said structure key element; Through 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 representes the joint of each clutch C1, C2, C3 and break B1, B2 in each gear, the joint action figure of separated state (wherein о representes 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 is 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 ratio of gear ratio and the velocity ratio between each gear shelves of each gear of expression.
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 planet carrier x1 and the 2nd gear ring r2 of the 2nd epicyclic gear train P2, the 1st sun gear s1 of the 1st epicyclic gear train P1 and the 2nd planet carrier x2 of the 2nd epicyclic gear train P2 of the 1st gear ring r1 of the 1st epicyclic gear train P1, the 1st epicyclic gear train P1, the 2nd sun gear s2 of the 2nd epicyclic gear train P2 from left to right successively.In addition, r2 representes 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 " representes 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 is output as below this zero line and 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 in the face of the related automatic transmission of this enforcement describes down.
The 1st forward gears is realized through 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.To 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 through said 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 through said 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 forever is connected the input as system with input shaft 1, and 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 through 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 through 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 through 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 through said 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; Because the 1st planet carrier x1 forever is connected with the 2nd gear ring r2, to 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 simultaneously; 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 through said 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 forever is connected the input as system with input shaft 1, and 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 through 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 through C3 simultaneously.For the 1st epicyclic gear train P1; The 1st planet carrier x1 is connected as a single entity through C1 and input shaft and imports as system; The 1st gear ring r1 is connected as a single entity as system's speedup input through C3 and x3; Simultaneously the 1st sun gear s1 exports as system, because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, just obtains 5th forward gears of reduction speed ratio less than 1 hypervelocity driving thus.
The 6th forward gears is realized through said 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.To 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 because the 1st sun gear s1 forever is connected with the 2nd planet carrier x2 and countershaft drive gear 4, just obtains 6th forward gears of reduction speed ratio less than the 5th grade hypervelocity driving as output at a high speed thus.
Backward gear (Rev) is realized through said 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, and engaging clutch C3 makes the 3rd planet carrier x3 and the 1st gear ring r1 connect as one through the 1st clutch C3, and 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 obtains exporting the sense of rotation backward gear opposite with input thus.
In above-described speed change, if following tabulation 1 such number of teeth of setting each gear, 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 said automatic transmission; This rear case is connected with main casing through not shown bolt, and the outer hub 12 of C1 clutch links to each other with disc-shaped part 10 through spline, and parts 10 are rigidly connected with said 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 parts 13 simultaneously as the interior hubs of C1, these 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 said 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 said 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 the side near 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 that the 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 and can said input shaft be rotated the constant epicyclic reduction gear row P3 of constant deceleration output; This epicyclic gear train forever is connected said sun gear s3 with said input shaft 1; Said gear ring r3 forever is connected with said case of transmission H2; Said planet carrier x3 is connected with the gear ring r1 of next epicyclic gear train P1 through clutch C3, for said 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 through 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, control gear noise, raising gear life and transmission efficiency have all been played positive role.Especially, the friction plate of said clutch C3 and steel disc are configured in the position of the outer radial periphery side superimposed of said constant epicyclic reduction gear row P3, and this layout has effectively shortened the axial length of said 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 said embodiment of the present invention,
Promptly as shown in Figure 7, Fig. 7 is that other embodiments of expression the present invention use the automatic transmission skeleton diagram when soon driving source F will be arranged on the G side.Be to be research object in said embodiment with FF (preposition forerunner's type) car.Driving source F is arranged in an end E of input shaft 1; In addition; Also can driving source F be arranged in the other end G side, and from this side be arranged side by side the 1st, 2 clutches successively, said 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 said 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; Have the 3rd epicyclic gear train that outputs to the 1st epicyclic gear train after the constant deceleration of the rotation of said input shaft; Has the 2nd epicyclic gear train that is arranged side by side with the 1st epicyclic gear train, the 3rd epicyclic gear train; Have case of transmission, have the 1st sun gear and the 2nd planet carrier of the 2nd epicyclic gear train and the output mechanism that said carry-out part is connected as a single entity of said the 1st epicyclic gear train
Have the 1st clutch between the 2nd sun gear that is in said input shaft and said the 2nd epicyclic gear train,
Have the 2nd clutch between the 1st planet carrier that is in said input shaft and said the 1st epicyclic gear train,
Have the 3rd clutch between the 3rd planet carrier of the 1st gear ring that is in said the 1st epicyclic gear train and said the 3rd epicyclic gear train,
It is characterized in that:
Said automatic transmission, carry-out part and the coaxial setting of input shaft comprise the 1st to the 3rd epicyclic gear train, 2 multi-plate brakes and 3 multidisc clutches,
Above-mentioned the 1st epicyclic gear train has the 1st sun gear, the 1st planet carrier and the 1st gear ring, and above-mentioned the 2nd epicyclic gear train has the 2nd sun gear, the 2nd planet carrier and the 2nd gear ring, and above-mentioned the 3rd epicyclic gear train has the 3rd sun gear, the 3rd planet carrier and the 3rd gear ring,
Above-mentioned the 3rd sun gear forever is connected with input shaft, above-mentioned the 3rd gear ring forever is connected with said case of transmission, above-mentioned the 1st planet carrier forever is connected with the 2nd gear ring, above-mentioned the 1st sun gear forever is connected with carry-out part with the 2nd planet carrier,
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, 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 through engaging above-mentioned the 1st clutch and the 2nd break; Realize the 2nd forward gears through engaging above-mentioned the 1st clutch and the 1st break; Realize the 3rd forward gears through engaging above-mentioned the 1st clutch and the 3rd clutch; Realize the 4th forward gears through engaging above-mentioned the 1st clutch and the 2nd clutch; Realize the 5th forward gears through engaging above-mentioned the 2nd clutch and the 3rd clutch, realize the 6th forward gears, realize backward gear through engaging above-mentioned the 3rd clutch and the 2nd break through engaging above-mentioned the 2nd clutch and the 1st break.
2. automatic transmission according to claim 1 is characterized in that:
Above-mentioned the 4th forward gears 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 said the 3rd clutch and said the 2nd epicyclic gear train; Above-mentioned the 2nd epicyclic gear train is arranged between said carry-out part and said the 1st epicyclic gear train; Above-mentioned the 3rd epicyclic gear train is arranged on said the 3rd clutch near a driving source or an anti-side that drives in the source, and the friction plate of said the 3rd clutch is configured in the position of the outer radial periphery side superimposed of at least a portion and said 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; Begin from this end or an anti-end that drives source; On input shaft, be arranged side by side above-mentioned the 3rd epicyclic gear train, above-mentioned the 1st epicyclic gear train, above-mentioned the 2nd epicyclic gear train successively, above-mentioned carry-out part with the coaxial setting of input shaft is arranged between above-mentioned the 2nd epicyclic gear train and above-mentioned the 1st, the 2nd clutch.
5. automatic transmission according to claim 4 is characterized in that:
Said the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives source of said carry-out part, and said the 1st, the 2nd break is arranged on the driving source or the anti-opposite side that drives the said side in the source of said carry-out part.
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 above-mentioned the 2nd epicyclic gear train near.
7. according to claim 3 or 4 described automatic transmission, it is characterized in that:
Said the 1st, the 2nd clutch nesting type setting diametrically, the interior hub portion of said the 1st clutch is as the outer hub of the 2nd clutch.
8. automatic transmission according to claim 7 is characterized in that:
Said the 1st, the 2nd clutch is arranged on the driving source or an anti-side that drives in the source of said carry-out part; And from the central part of the speed changer rear end shell body wall of the anti-driving source that is arranged on said the 1st, the 2nd clutch to driving the hub portion that source extends; Be provided with oil circuit to hydraulic chamber's supply working oil of said the 1st, the 2nd clutch; Perhaps from the central part of the transmission oil pump shell body wall of the driving source that is arranged on said the 1st, the 2nd clutch to the hub portion that anti-driving source extends, be provided with oil circuit to hydraulic chamber's supply working oil of said the 1st, the 2nd clutch.
9. according to claim 3 or 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 above-mentioned the 1st epicyclic gear train, above-mentioned the 2nd epicyclic gear train, and on axial direction, are arranged side by side.
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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| Publication Number | Publication Date |
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| CN101900188A CN101900188A (en) | 2010-12-01 |
| CN101900188B true 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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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103244624A (en) * | 2012-02-08 | 2013-08-14 | 黄振强 | Novel automatic gearbox of stepless gear |
Citations (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 |
| CN1743699A (en) * | 2004-09-01 | 2006-03-08 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| US7140997B2 (en) * | 2003-07-31 | 2006-11-28 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
| CN101315120A (en) * | 2007-05-30 | 2008-12-03 | 马自达汽车株式会社 | Automatic transmission |
-
2009
- 2009-12-16 CN CN 200910201226 patent/CN101900188B/en not_active Expired - Fee Related
Patent Citations (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 |
| CN1743699A (en) * | 2004-09-01 | 2006-03-08 | 现代自动车株式会社 | Six-speed powertrain of an automatic transmission |
| CN101149092A (en) * | 2006-09-20 | 2008-03-26 | 马自达汽车股份有限公司 | Automatic transmission |
| CN101315120A (en) * | 2007-05-30 | 2008-12-03 | 马自达汽车株式会社 | Automatic transmission |
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|---|---|
| CN101900188A (en) | 2010-12-01 |
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