CN101583810B - Automatic transmission - Google Patents

Abstract

An automatic transmission (1) has a clutch (C-1), a clutch (C-3), and a clutch (C-4) that are arranged axially closer to the planetary gear (DP) than a planetary gear unit (PU). Friction plates (21) of the clutch (C-1) and friction plates (31) of the clutch (C-3) are arranged on the radially outer side of the planetary gear (DP). Friction plates (41) of the clutch (C-4) are arranged on the radially inner side of the friction plates (31) of the clutch (C-3) such that at least some of the friction plates (41) overlap on the friction plates (31). As a result, the axial length of the automatic transmission (1) is reduced by the amount of the axial overlap between the friction plates (31) of the clutch (C-3) and the friction plates (41) of the clutch (41).

Description

Automatic transmission

Technical field

The present invention relates to a kind of automatic transmission that is applicable on vehicle etc.; Particularly; Relate to a kind of have be used to be transfused to input rotation and output slow down rotation epicyclic reduction gear with have the planetary gear unit of 4 rotating members, and can realize advancing 8 grades with the automatic transmission of retreating shelves.

Background technique

In the past; For example in the automatic transmission of the vehicle that is applicable to FF type (front-mounted engine, front-wheel drive); Following automatic transmission has been proposed; That is, have the output link (counter shaft gear) that is used to produce automatic transmission gear ratio the variable speed planetary gear group be used to produce the epicyclic reduction gear of rotation that slows down, and can realize advancing 8 grades with retreat shelves.This automatic transmission has 3 clutch C1, C2, C3; 3 clutch C1, C2, C3 are used for optionally importing deceleration rotation and input rotation from this epicyclic reduction gear to each rotating member of variable speed planetary gear group; And said 3 clutch C1, C2, C3 with respect to variable speed planetary gear configuration set this epicyclic reduction gear one side in the axial direction (for example with reference to TOHKEMY 2007-32624 communique, Fig. 4).

But, in recent years, in the automatic transmission on being loaded in vehicle etc., from the requirement of environmental problem being considered hope to reduce oil consumption etc., in more small-sized vehicle etc., also require to realize many grades of speed changeizations.On the other hand, in automatic transmission, in the automatic transmission of the more than enough shelves of the ability of in the vehicle of FF (front-mounted engine, front-wheel drive) type such shown in the said patent documentation 1, using speed change, also hope to realize compactness.That is to say that in the vehicle of FF type, therefore configuration motor and automatic transmission between the front-wheel of the left and right sides, consider from the aspects such as steering angle of guaranteeing front-wheel that special hope can realize the compactness of automatic transmission on axial length.

Summary of the invention

But, in the automatic transmission of above-mentioned patent documentation 1, have 3 clutch C1, C2, the C3 configuration side by side in the axial direction of a plurality of friction plates respectively.Because the friction plate of said 3 clutch C1, C2, C3 has determined 3 torque capacity (torquecapacity) that clutch C1, C2, C3 bear separately, the number of the plate of therefore can't reducing friction.In addition,, consider to increase the area of every friction plate, but can cause the maximization of automatic transmission on diametric(al) like this in order to ensure the torque capacity of friction plate, thus not preferred.The result is difficult to make automatic transmission compactness in the axial direction in the past.

Therefore, the object of the present invention is to provide a kind of through can realize the automatic transmission of compactness in the axial direction to first clutch, three-clutch and four clutches reasonable disposition.

The present invention's (for example referring to figs. 1 through Fig. 4) automatic transmission (1), it has: epicyclic reduction gear (DP), the rotation of its input input shaft (7), and the rotation that can export this input shaft (7) the deceleration rotation of having been slowed down; Planetary gear unit (PU); Its with said epicyclic reduction gear be configured in coaxial on; Have first rotating member (S3), second rotating member (CR2), the 3rd rotating member (R3) and the 4th rotating member (S2), and the order of first rotating member (S3), second rotating member (CR2), the 3rd rotating member (R3) and the 4th rotating member (S2) is the relation according to rotating ratio; First clutch (C-1), it is used for said deceleration rotation is inputed to said the 4th rotating member (S2);

Second clutch (C-2), it is used for the rotation of said input shaft (7) is inputed to said second rotating member (CR2, CR3); Three-clutch (C-3), it is used for said deceleration rotation is inputed to said first rotating member (S3); Four clutches (C-4), it is used for the rotation of said input shaft (7) is inputed to said first rotating member (S3); First latch for printed circuit (B-1), it is used for fixing the rotation of said first rotating member (S3); Second latch for printed circuit (B-2), it is used for fixing the rotation of said second rotating member (CR2, CR3); Output link (8), it is connected with said the 3rd rotating member (R3); And; This automatic transmission (1) can realize advancing at least 7 grades with retreat shelves; It is characterized in that; Said first clutch (C-1), said three-clutch (C-3) and said four clutches (C-4) are configured in said epicyclic reduction gear (DP) side on leaning on axially than said planetary gear unit (PU); The friction plate (21) of said first clutch (C-1) is configured to friction plate (41) skew (offset) of the friction plate (31) and the four clutches (C-4) of said relatively three-clutch (C-3) in the axial direction, the friction plate (41) of said four clutches (C-4) is configured in interior all sides of the friction plate (31) of this three-clutch (C-3) with the overlapping in the axial direction mode of friction plate (31) of at least a portion and said three-clutch (C-3).

Thus, can make automatic transmission compactness in the axial direction, the length that automatic transmission shortens in the axial direction is equivalent to the overlapping in the axial direction length of friction plate of the friction plate and the four clutches of three-clutch.

In addition, first clutch and three-clutch are used for transmitting the rotation of slowing down, and four clutches is used for transmitting the input rotation, and therefore, first clutch and three-clutch torque transmitted are greater than the four clutches torque transmitted.And first clutch engages when realizing bottom gear, and three-clutch is compared when top gear with first clutch and engaged, and therefore, the first clutch torque transmitted is greater than the three-clutch torque transmitted.Therefore; It is not overlapping in the axial direction to need the first clutch of peak torque capacity to be configured to the friction plate of the friction plate of three-clutch and four clutches; The friction plate of the four clutches that needs the minimum torque capacity is configured in interior all sides of friction plate of the four clutches of the second largest torque capacity of needs; Therefore; The friction plate of first clutch can be configured under the situation of the friction plate of friction plate that does not receive three-clutch and four clutches restriction diametrically, and the external diameter of friction plate that can make three-clutch is greater than the external diameter of the friction plate of four clutches.Therefore; Can make the torque capacity of the torque capacity of three-clutch greater than four clutches; Make the torque capacity of the torque capacity of first clutch greater than three-clutch; Thereby can guarantee that clutch has required separately torque capacity, the axial length of automatic transmission is shortened.

In addition; Particularly (for example with reference to Fig. 4) is configured in the oil servomotor (40) of said four clutches (C-4) interior all sides of the oil servomotor (30) of this three-clutch (C-3) with the overlapping in the axial direction mode of oil servomotor (30) of at least a portion and said three-clutch (C-3).

Thus, can make automatic transmission go up compactness in the axial direction, the length that automatic transmission shortens in the axial direction is equivalent to the overlapping in the axial direction length of oil servomotor of the oil servomotor and the four clutches of three-clutch.

In addition, because three-clutch is used for to first rotating member transmission deceleration rotation, four clutches is used for to first rotating member transmission input rotation, and therefore the three-clutch torque transmitted is greater than the four clutches torque transmitted.Therefore; Be configured in interior all sides of the oil pressure servo of three-clutch through oil servomotor with four clutches; The diameter of oil servomotor that can make three-clutch is greater than the diameter of the oil servomotor of four clutches; And can make the torque capacity of the torque capacity of three-clutch, thereby the axial length of automatic transmission is shortened greater than four clutches.

In addition; Particularly (for example with reference to Fig. 4); It is overlapping in the axial direction that at least a portion of the releasing grease chamber (38) of said three-clutch (C-3) is configured at the friction plate (41) of the outer circumferential side of the friction plate (41) of said four clutches (C-4) and this four clutches (C-4), and overlapping diametrically with the friction plate (31) of said three-clutch (C-3).

Thus, can make automatic transmission compactness in the axial direction, the length that automatic transmission shortens in the axial direction is equivalent to a part and the overlapping in the axial direction length of friction plate of four clutches of the releasing grease chamber of three-clutch.

In addition; Particularly (for example with reference to Fig. 4); Between oil servomotor (20) the configuration said epicyclic reduction gear (DP) and said planetary gear unit (PU) in the axial direction with said first clutch (C-1); And the oil servomotor (30) of said three-clutch (C-3) and the said relatively epicyclic reduction gear of oil servomotor (40) (DP) of said four clutches (C-4) are configured in a side opposite in the axial direction with said planetary gear unit (PU), and it is relative across said epicyclic reduction gear (DP) that the clutch drum (32) of the oil servomotor (30) of the clutch drum (22) of the oil servomotor (20) of said first clutch (C-1) and said three-clutch (C-3) is configured to opening direction.

Thus; Be configured between them, to exist the situation of clutch drum of the oil servomotor of first clutch to compare with the friction plate that for example makes first clutch and the friction plate of three-clutch; It is approaching each other that the friction plate of friction plate and the three-clutch of this first clutch is configured to, thereby make automatic transmission compact in the axial direction.

In addition, particularly (for example with reference to Fig. 1 and Fig. 4), said epicyclic reduction gear (DP) has: first sun gear (S1), and it is fixed on the casing (6); First planet carrier (CR1), it is used to import the rotation of said input shaft (7); First gear ring (R1), the rotation of the said input shaft (7) of said first sun gear (S1) that it is fixed through rotation and said first planet carrier (CR1) input becomes the deceleration rotation that rotating speed is lower than the rotation of said input shaft (7).

In addition; Particularly (for example with reference to Fig. 4); Outer circumferential side at first gear ring (R1) of said epicyclic reduction gear (DP) is formed with hub portion (51); This hub portion (51) part from this first gear ring (R1) at least to axial one side-prominent, at least a portion of the friction plate (31) of said three-clutch (C-3) be configured to said hub portion (51) from the outstanding part spline engagement of said first gear ring (R1).

Thus; One one of friction plate through making three-clutch is configured in simple structure such on the hub portion; The friction plate overlapping configuration in the axial direction of friction plate and the four clutches of this three-clutch can be made, thereby automatic transmission compactness in the axial direction can be made.

In addition, particularly (for example with reference to Fig. 4) is formed with the oilhole (51d) that is used for lubricant oil conducting to the outer circumferential side of supplying with from interior all side in said hub portion (51) from the outstanding part of said first gear ring (R1).

Thus, can make the lubricating efficiency of friction plate of the three-clutch on the outstanding part of first gear ring that is configured in hub portion good.That is, lubricant oil is supplied to efficiently and is used to transmit slow down rotation and the big three-clutch of torque capacity.

In addition, particularly (for example with reference to Fig. 2 and Fig. 3), said three-clutch (C-3) is by constituting at engaged clutch in a plurality of gears more than 2 grades.

Thus, even engage or the number of times that separates becomes under many such situation, also can make good as the lubricating efficiency of automatic transmission at engaged three-clutch in a plurality of gears more than 2 grades.

In addition; Particularly (for example with reference to Fig. 4); Make said hub portion (51) form also outstanding to axial opposite side at the outer circumferential side of said first gear ring (R1); The friction plate (21) of said first clutch (C-1) and the friction plate (31) of said three-clutch (C-3) are configured in the outer circumferential side of said hub portion (51) side by side, make the part spline engagement of giving prominence to opposite side of at least a portion and said hub portion (51) of friction plate (21) of said first clutch (C-1).

Thus, it is approaching each other that the friction plate of friction plate and the three-clutch of first clutch is configured at the outer circumferential side of epicyclic reduction gear, and can be configured to the friction plate and the epicyclic reduction gear of first clutch overlapping in the axial direction.Therefore, in the torque capacity of guaranteeing first clutch and three-clutch, can make automatic transmission compactness in the axial direction.

In addition; Particularly (for example with reference to Fig. 4); Has clutch hub (56) with friction plate (41) spline engagement of said four clutches (C-4); First planet carrier (CR1) of said epicyclic reduction gear (DP) has the side plate (CR1b) that is used to support the small gear that can rotate freely, and said clutch hub (56) and said side plate (CR1b) are constituted separately respectively, and with said clutch hub (56) fixed configurations on said side plate (CR1b).

Thus, under the situation that first planet carrier and clutch hub are formed as one, the supporting portion of pinion shaft and the root of clutch hub are staggered the position diametrically, thereby restricted the radial position that to dispose clutch hub.But, according to the present invention, side plate and the clutch hub of planet carrier are constituted respectively separately, therefore, can be in desired radial position with the clutch hub fixed configurations, and can four clutches be configured in interior all sides of three-clutch.

In addition; Particularly (for example with reference to Fig. 1); Said planetary gear unit (PU) has single small gear planetary pinion (PUS) and the double pinion planetary pinion (PUD) that is connected with each other by planet carrier; Said single small gear planetary pinion (PUS) is configured in than said double pinion planetary pinion (PUD) by said epicyclic reduction gear (DP) side; Said the 4th rotating member is second sun gear (S2) of said double pinion planetary pinion (PUD), and said first rotating member is the 3rd sun gear (S3) of said single small gear planetary pinion (PUS).

Thus; Second sun gear and the 3rd sun gear respectively with situation that the member that extends from the epicyclic reduction gear side is connected under; Can the member that be connected with second sun gear be configured to the interior all sides through the 3rd sun gear; Thereby can make and radially go up compactly, and when four clutches is configured in the side different with planetary gear unit of epicyclic reduction gear, axial length is shortened.

In addition; Particularly (for example with reference to Fig. 1); Said second rotating member is second planet carrier (CR2, CR3); This second planet carrier (CR2, CR3) is used to support long small gear (P3) and short and small gear (P4), and this long small gear (P3) and this short and small gear (P4) can rotate freely, wherein; Said long small gear (P3) public said short and small gear (P4) in single small gear planetary pinion (PUS) and said double pinion planetary pinion (PUD) is meshed with this long small gear and forms said double pinion planetary pinion (PUD), and said the 3rd rotating member is second gear ring (R3) that meshes with said long small gear (P3).

In addition, particularly (for example with reference to Fig. 1 and Fig. 2) engages through making said first clutch (C-1), and said second latch for printed circuit (B-2) card is ended; Thereby realize advancing 1 grade, engage, and said first latch for printed circuit (B-1) card is ended, thereby realize advancing 2 grades through making said first clutch (C-1); Through said first clutch (C-1) is engaged, and said three-clutch (C-3) is engaged, thereby realize advancing 3 grades; Through said first clutch (C-1) is engaged, and said four clutches (C-4) is engaged, thereby realize advancing 4 grades; Through said first clutch (C-1) is engaged, and said second clutch (C-2) is engaged, thereby realize advancing 5 grades; Through said second clutch (C-2) is engaged, and said four clutches (C-4) is engaged, thereby realize advancing 6 grades; Through said second clutch (C-2) is engaged, and said three-clutch (C-3) is engaged, thereby realize advancing 7 grades; Through said second clutch (C-2) is engaged, and said first latch for printed circuit (B-1) card is ended, thereby realize advancing 8 grades; Through said three-clutch (C-3) or said four clutches (C-4) are engaged, and said second latch for printed circuit (B-2) card is ended, thereby realize retreating shelves.

Thus, this automatic transmission is applicable to be used to and realizes advancing 8 grades and the automatic transmission of retreating 1 grade at least.

In addition, reference character in the above-mentioned bracket is used for comparing with accompanying drawing, and this is for the ease of invention is more readily understood, and can the structure that will protect in claims not had any impact.

Description of drawings

Fig. 1 is the schematic representation of the automatic transmission of this mode of execution of expression.

Fig. 2 is the table of joint of automatic transmission.

Fig. 3 is the speed curve diagram of automatic transmission.

Fig. 4 is the side sectional view of the part of expression automatic transmission.

Embodiment

Based on Fig. 1 to Fig. 4 mode of execution of the present invention is described below.Fig. 1 is the schematic representation of the automatic transmission of this mode of execution of expression, and Fig. 2 is the table of joint of automatic transmission, and Fig. 3 is the speed curve diagram of automatic transmission, and Fig. 4 is the side sectional view of the part of expression automatic transmission.In addition; The automatic transmission of this mode of execution is on being loaded on vehicle the time; Direction of advance with respect to vehicle axially becomes left and right directions, in this manual, and being the observed automatic transmission 1 of torque converter 2 sides as positive from be connected a side with motor.Therefore, Fig. 4 is the side sectional view that unilateral observation is from the side arrived.In addition, in the axial direction, with these torque converter 2 one sides as front side, with clutch C-2 one side as rear side.

At first, based on Fig. 1 the schematic configuration that can be suitable for automatic transmission 1 of the present invention is described.As shown in Figure 1; Be applicable to that for example the automatic transmission 1 of the vehicle of FF type (front-mounted engine, front-wheel drive) has the casing 6 that is made up of housing and gearbox casing, have input link (protecgulum and center piece) 10 as the automatic transmission 1 that can be connected with not shown motor at the front side of this casing 6.In addition, automatic transmission 1 disposes the torque converter 2 with lock-up clutch 2a, in casing 6, disposes gear 3, middle axial region 4 and differential mechanism portion 5.

Said torque converter 2 has pump impeller (pump impeller) 2b that is connected with the input link 10 of automatic transmission 1 and transmits turbine (turbineruuner) 2c of the rotation of this pump impeller 2b through working fluid, and this turbine 2c is connected with being equipped on said input link 10 coaxial input shafts 7 of said gear 3.In addition, this torque converter 2 has lock-up clutch 2a, and when the oil pressure control of this lock-up clutch 2a through not shown hydraulic pressure control device engaged, the rotation of the input link 10 of said automatic transmission 1 directly was passed to the input shaft 7 of gear 3.

In said gear 3, on input shaft 7, have planetary pinion (epicyclic reduction gear) DP and planetary gear unit PU.This planetary pinion DP is so-called double pinion planetary pinion; This planetary pinion DP has sun gear (first sun gear) S1, planet carrier (first planet carrier) CR1 and gear ring (first gear ring) R1; On this planet carrier CR1, have and the small gear P2 of sun gear S1 engagement and with the small gear P1 of gear ring R1 engagement, and small gear P1 and small gear P2 are meshing with each other.

In addition; Said planetary gear unit PU is so that the mode that these two planetary pinions of single small gear planetary pinion PUS and double pinion planetary pinion PUD couple together constitutes; This list small gear planetary pinion PUS has sun gear (the 3rd sun gear) S3, planet carrier (second planet carrier) CR3 and gear ring (second gear ring) R3, and this double pinion planetary pinion PUD has sun gear (second sun gear) S2 and planet carrier (second planet carrier) CR2.And said single small gear planetary pinion PUS and double pinion planetary pinion PUD have public small gear as long small gear P3, and this double pinion planetary pinion PUD has the intermeshing short and small gear P4 with this long small gear P3.And; This list small gear planetary pinion PUS and this double pinion planetary pinion PUD have planet carrier CR2, CR3, and said planet carrier CR2, CR3 are used to support the pinion shaft PS4 that supports this short and small gear P4 with the pinion shaft PS3 of this long small gear P3 of free rotation mode support with free rotation mode.In addition; Planet carrier CR2, CR3 are illustrated as the planet carrier CR3 of the planet carrier CR2 of double pinion planetary pinion PUD and single small gear planetary pinion PUS, but this planet carrier CR2, CR3 are planet carriers that has public long small gear P3 and carry out identical rotation.Promptly; Planetary gear unit PU is so-called Ravigneaux (Ravigneaux) formula planetary pinion; Planetary gear unit PU have the sun gear that becomes double pinion planetary pinion PUD sun gear (the 4th rotating member, second sun gear) S2, become sun gear (first rotating member of the sun gear of single small gear planetary pinion PUS; The 3rd sun gear) S3, said planet carrier (second rotating member, second planet carrier) CR2, CR3 and gear ring (the 3rd rotating member, second gear ring) R3 are as 4 rotating members.The order of the rotating ratio the when order of the numeral of each rotating member of in said bracket, representing in addition, (first to fourth rotating member) is these rotating member rotations.That is, as shown in Figure 3, specifically refer to after the planetary gear unit PU part order that the left side begins from figure in the speed curve diagram stated.

And then interior all sides of the long small gear P3 of planetary gear unit PU in double pinion planetary pinion PUD have short and small gear P3.Therefore, the external diameter of the sun gear S3 of single small gear planetary pinion PUS is bigger than the sun gear S2 of double pinion planetary pinion PUD.In addition; Single small gear planetary pinion PUS is configured in than double pinion planetary pinion PUD and leans on planetary pinion DP one side (right-hand side among the figure); When single small gear planetary pinion PUS is connected with the member that extends from this planetary pinion DP side, the member that is connected with sun gear S2 is disposed, therefore through interior all sides of sun gear S3; The situation that is configured in planetary pinion DP side with double pinion planetary pinion PUD is compared, and can make automatic transmission 1 compactness diametrically.

The sun gear S1 of said planetary pinion DP is fixed on the casing 6 and forms as one.In addition, said planet carrier CR1 carries out the rotation identical with the rotation of said input shaft 7 (below be called " input rotation "), and is connected with clutch (four clutches) C-4.And; Said gear ring R1 becomes the rotation of slowing down through said sun gear S1 that is fixing and the said planet carrier CR1 that imports rotation slows down input rotation rotating speed, and this gear ring R1 is connected with clutch (first clutch) C-1 and clutch (three-clutch) C-3.

The sun gear S3 of said planetary gear unit PU is connected with break (first latch for printed circuit) B-1; Can freely fix with respect to casing 6; And be connected with said clutch C-4 and clutch C-3; Can freely import the input of said planet carrier CR1 through this clutch C-4 and rotate, and can freely import the deceleration rotation of said gear ring R1 through this clutch C-3.In addition, said sun gear S2 is connected with clutch C-1, and can freely import the deceleration rotation of said gear ring R1.

And; Said planet carrier CR2 (CR3) is connected with clutch (second clutch) C-2 of the rotation that is used to import input shaft 7; And can freely import rotation through this clutch C-2; And said planet carrier CR2 (CR3) is connected with overrunning clutch F-1 and break (second latch for printed circuit) B-2; Be limited with respect to the rotation of casing 6 through the said planet carrier CR2 of this overrunning clutch F-1 (CR3), and can freely fix through the rotation of the said planet carrier CR2 of this break B-2 (CR3) to a direction.And said gear ring R3 is connected with counter shaft gear (output link) 8, and this counter shaft gear (output link) 8 is supported on the not shown intermediate support member fixing on the casing 6, and can rotate freely with respect to this intermediate support member.

In addition, this counter shaft gear 8 be fixed on said in the middle of gear wheel in large diameter 11 engagements on the jack shaft 12 of axial region 4, the small diameter gear 12a of this jack shaft 12 on the outer circumferential face that is formed on this jack shaft 12 meshes with the gear 14 of differential mechanism portion 5.And this gear 14 is fixed on differential gear 13, is connected with left and right sides axletree 15,15 through this differential gear 13.

Next, according to said structure, the effect of gear 3 is described based on Fig. 1 to Fig. 3.

Under the control of not shown electric control device and hydraulic pressure control device, said automatic transmission 1 with said structure is carried out speed change according to vehicle load in the corresponding gear scope of the gear of selecting with the driver.Fig. 2 figures out the gear of realizing through the joint of each clutch and break and separation (represent to engage with " zero " mark, unmarked expression separates).In addition, Fig. 3 illustrates joint through each clutch and break (joint of representing clutch and break with " ● " mark) with velocity curve and relation between the rotating ratio of the gear realized and each speed change member at this moment.In addition, in this speed curve diagram, the longitudinal axis is represented the rotating speed of each rotating member (each gear), the gear speed ratio of the said rotating member of the corresponding expression of transverse axis.In addition; In the part of the planetary gear unit PU of this speed curve diagram; If (left side Fig. 3) is when being made as first to fourth rotating member with each speed change member successively along X direction from the one of which end; First rotating member is corresponding to large diameter sun gear S3, is connected with the path of the path of the rotation of having been slowed down by planetary pinion DP through clutch C-3 input and the input rotation through clutch C-4 input input shaft 7, and connected can block mode only through break B-1.And second rotating member is connected with the path that rotates through the input of clutch C-2 input input shaft 7, and is connected can block the mode of ending through break B-2 corresponding to planet carrier CR2 (CR3).In addition, the 3rd rotating member is connected with counter shaft gear 8 corresponding to gear ring R3.And the 4th rotating member corresponds to the sun gear S2 of minor diameter, is connected with the path of the rotation of having been slowed down by planetary pinion DP through clutch C-1 input.

For example under the situation of D (driving) gear, as shown in Figure 2 in advance 1 grade (lst), clutch C-1 and overrunning clutch F1 engage.So like Fig. 1 and shown in Figure 3, the slow down rotation of the first gear ring R1 of rotation inputs to sun gear S2 through first clutch C1-1 through the first sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, the rotation of planet carrier CR2 (CR3) is restricted to facing one direction (positive veer), also says so, and prevents that planet carrier CR2 from reversing and be in fixing state.So the deceleration rotation that inputs to sun gear S2 exports gear ring R3 to through the planet carrier CR2 that is fixing, as 1 grade the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In addition, engine brake (when sliding), break B-2 card ends and planet carrier CR2 is fixed, and under the situation of just changeing that prevents this planet carrier CR2, keeps said 1 grade the state of advancing.In addition, advance in 1 grade, can prevent second planet carrier CR2 counter-rotating and can just change through overrunning clutch F1 at this, therefore, can be through the automatic joint of overrunning clutch F1, for example successfully realize switching to and advance 1 grade when going grade from the non-shelves that go.

In advance 2 grades (2nd), as shown in Figure 2, clutch C-1 engages, and break B-1 card ends.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S2 through first clutch C-1 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, only fix the rotation of sun gear S3 through the card of break B-1.So planet carrier CR2 carries out the deceleration rotation that rotating speed is lower than sun gear S2, the deceleration rotation that inputs to this sun gear S2 exports gear ring R3 to through this planet carrier CR2, as 2 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 3 grades (3rd), as shown in Figure 2, clutch C-1 and clutch C-3 engage.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S2 through clutch C-1 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, through the joint of clutch C-3, the deceleration of gear ring R1 rotation inputs to sun gear S3.That is, the deceleration of gear ring R1 rotation inputs to sun gear S3 and sun gear S2, thereby planetary gear unit PU is in slow down the direct coupled condition of rotation, keeps the deceleration invariable rotary to export gear ring R3 to, as 3 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 4 grades (4th), as shown in Figure 2, clutch C-1 and clutch C-4 engage.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S2 through clutch C-1 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, through the joint of clutch C-4, the input of planet carrier CR1 rotation inputs to sun gear S3.So planet carrier CR2 carries out the deceleration rotation that rotating speed is higher than sun gear S2, the deceleration rotation that inputs to this sun gear S2 exports gear ring R3 to through this planet carrier CR2, as 4 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 5 grades (5th), as shown in Figure 2, clutch C-1 and clutch C-2 engage.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S2 through clutch C-1 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, through the joint of clutch C-2, the input rotation inputs to planet carrier CR2.So, deceleration rotation through inputing to this sun gear S2 and the input rotation that inputs to planet carrier CR2 form rotating speed be higher than said advance 4 grades the deceleration rotation and export gear ring R3 to, as 5 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 6 grades (6th), as shown in Figure 2, clutch C-2 and clutch C-4 engage.So like Fig. 1 and shown in Figure 3, through the joint of clutch C-4, the input of planet carrier CR1 rotation inputs to sun gear S3.In addition, through the joint of clutch C-2, the input rotation inputs to planet carrier CR2.That is, because input rotation inputs to sun gear S3 and planet carrier CR2, so planetary gear unit PU is in the direct coupled condition of input rotation, keeps input rotation invariable rotary to export gear ring R3 to, as 6 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 7 grades (7th), as shown in Figure 2, clutch C-2 and clutch C-3 engage.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 through clutch C-3 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, the joint through clutch C-2 makes the input rotation input to planet carrier CR2.So the speedup rotation that deceleration rotation through inputing to this sun gear S3 and the input rotation that inputs to planet carrier CR2 form a little higher than input rotation of rotating speed exports gear ring R3 to, as 7 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In advance 8 grades (8th), as shown in Figure 2, clutch C-2 engages, and break B-1 card ends.So like Fig. 1 and shown in Figure 3, through the joint of clutch C-2, the input rotation inputs to planet carrier CR2.In addition, the card through break B-1 ends, and sun gear S3 does not rotate.So, through the sun gear S3 that is fixing, the input of planet carrier CR2 rotation form rotating speed be higher than said advance 7 grades the speedup rotation and export gear ring R3 to, as 8 grades the just commentaries on classics of advancing from counter shaft gear 8 outputs.

In retreating 1 grade (Rev1), as shown in Figure 2, clutch C-3 engages, and break B-2 card ends.So like Fig. 1 and shown in Figure 3, the slow down rotation of gear ring R1 of rotation inputs to sun gear S3 through clutch C-3 through the sun gear S1 that fixing with as the planet carrier CR1 of input rotation.In addition, the card through break B-2 ends, and planet carrier CR2 does not rotate.So the deceleration rotation that inputs to sun gear S3 exports gear ring R3 to through the planet carrier CR2 that is fixing, export from counter shaft gear 8 as the counter-rotating of retreating 1 grade.

In retreating 2 grades (Rev2), as shown in Figure 2, clutch C-4 engages, and break B-2 card ends.So like Fig. 1 and shown in Figure 3, through the joint of clutch C-4, the input of planet carrier CR1 rotation inputs to sun gear S3.In addition, the card through break B-2 ends, and planet carrier CR2 does not rotate.So the input rotation that inputs to sun gear S3 exports gear ring R3 to through the planet carrier CR2 that is fixing, export from counter shaft gear 8 as the reverse of retreating 2 grades.

In addition, for example in P (Parking) gear and N (neutral gear) gear, clutch C-1, clutch C-2, clutch C-3 and clutch C-4 separate.So, between planet carrier CR1 and the sun gear S3, between gear ring R1 and the sun gear S3, gear ring R1 sun gear S2 and between, promptly be in dissengaged positions between planet gear D P and the planetary gear unit PU.In addition, be in dissengaged positions between input shaft 7 and the planet carrier CR2.Thus, the power transmission between input shaft 7 and the planetary gear unit PU is in dissengaged positions, and promptly the power transmission between input shaft 7 and the counter shaft gear 8 is in dissengaged positions.

In addition; In the automatic transmission 1 of this mode of execution; To realizing advancing 8 grades and retreat 2 grades automatic transmission and be illustrated; But also can be 7 grades and the automatic transmission of retreating 2 grades of advancing that for example realizes not using said advance 8 grades (8th), promptly so long as the automatic transmission that the latch for printed circuit through regulation and 4 clutches can form gear get final product, even the automatic transmission of any gear number can both be suitable for the present invention.

Next, based on Fig. 4 clutch C-1, clutch C-3, clutch C-4 and the planetary pinion DP of automatic transmission 1 of the present invention are described.In the inboard of casing 6 (with reference to Fig. 1), on input shaft 7, dispose: have the planetary planetary pinion DP of double pinion, sun gear S1, planet carrier CR1, gear ring R1.Wherein, sun gear S1 embeds the outer circumferential face of input shaft 7, and the spline 71s that forms on the outer circumferential face of this sun gear S1 through the rear side end of the shroud member 71 that forwards extends is connected with this shroud member 71.This shroud member 71 supports input shaft 7 through bearing b1 and this input shaft 7 can rotate freely; And this shroud member 71 is fixed on the inner peripheral surface of boss part 70 and forms as one with boss part 70, said boss part 70 from the internal side diameter of the pump cover (not shown) of the oil hydraulic pump in the place ahead of being arranged at casing 6 rearward side extend and be provided with.Therefore, sun gear S1 is connected on the casing 6 and with respect to casing 6 and can not rotates.

Said planet carrier CR1 has the back planet frame plate CR1a of rear side and the preceding planet frame plate CR1b of front side, is supporting pinion shaft PS1, PS2 by these two planet frame plate CR1a, CR1b.In addition, pinion shaft PS1 is used for can free rotation mode supporting said small gear P1, and pinion shaft PS2 is used for can free rotation mode supporting said small gear P2.And, small gear P1 outer circumferential side and gear ring R1 engagement and with small gear P2 engagement, this small gear P2 meshes with sun gear S1 in interior all sides.And back planet frame plate CR1a is fixed in interior all ends on the input shaft 7 and is integrally formed with input shaft 7.Thus, planet carrier CR1 is supported on the input shaft 7, and constitutes and carry out the rotation identical with input shaft 7.

Said gear ring R1 is formed with the hub portion 51 that specifies of back at outer circumferential side, and side sections is bonded on the external diameter end that forms the tabular supporting member 53 of open circles roughly in the wings.The rear side of this supporting member 53 in interior all sides on the hollow axial region 22c of bearing 66 with the clutch drum 22 of the clutch C-1 that states after can free rotation mode being supported on, the front side of this supporting member 53 interior all sides through bearing 67 with can free rotation mode be supported on said planet carrier CR1 after on the planet frame plate CR1a.Thus, gear ring R1 planet frame plate CR1a and supporting member 53 behind the clutch drum 22 of clutch C-1, planet carrier CR1 are supported on the input shaft 7, and this gear ring R1 can rotate freely with respect to input shaft 7.

Next, clutch C-1 of the present invention, C-3 and C-4 are elaborated.In interior all sides of said break B-1, disposing clutch C-1 to rear side from the outer circumferential side of planetary pinion DP.The oil servomotor 20 that this clutch C-1 has the friction plate 21 that is made up of external friction plate 21a and interior friction plate 21b and makes this friction plate 21 engage or separate, in this friction plate 21b and after state hub portion 51 spline engagement.

Said oil servomotor 20 has clutch drum 22, piston component 24, removes plate 25, Returnning spring 26, is constituted work grease chamber 27, is removed grease chamber 28 by above-mentioned these members.Clutch drum 22 is that outer circumferential side member 22A and interior all side member 22B is bonding and constitute one, and towards planetary pinion DP side (front side) opening, and this clutch drum 22 has: lip part 22b, and it extends from interior all side direction outer circumferential sides; Tympanic part 22a, its from the outer circumferential side of this lip part 22b forwards side extend to planetary pinion DP outer circumferential side; Hollow axial region 22c, its interior all side direction front side at this lip part 22b extend and form the hollow shaft shape.

At the front side of said lip part 22b, be formed with the 22d of cylinder body portion that is used to constitute said work grease chamber 27 with piston component 24 relative parts.At the outer circumferential side of planet gear D P, said external friction plate 21a spline engagement is on the inner peripheral surface of the tympanic part 22a of clutch drum 22.Said hollow axial region 22c is configured to embed in the shroud member 72, this shroud member 72 through bearing b2 can free rotation mode being configured on this input shaft 7.That is, hollow axial region 22c through shroud member 72 can free rotation mode being configured on the input shaft 7.

Said piston component 24 is positioned at the front side of the lip part 22b of said clutch drum 22, with relative with the said cylinder body 22d of portion with the chimeric form of the front side of said hollow axial region 22c, and be configured to and can move freely vertically.In addition, piston component 24 is sealed through seal ring 61 and sealing component 62, between this piston component 24 and clutch drum 22, constitutes thus to be the work grease chamber 27 that seals oil-proof state.And, extending at the outer circumferential side of piston component 24 and to be provided with press part 24a, the front end of this press part 24a and friction plate 21 dispose relatively.In addition, the peripheral end of 24a is formed with spline in this press part, with the spline spline engagement of interior all sides of the tympanic part 22a that is formed at said clutch drum 22.

Opening elasticity baffle ring 73 through being entrenched in said hollow axial region 22c front side limits said releasing plate 25 side shifting forwards.Be provided with Returnning spring 26 removing to compress between plate 25 and the piston component 24 that is configured in these releasing plate 25 rear sides, and constitute by the sealing component 74 of the peripheral part that is configured in this releasing plate 25 and to be the releasing grease chamber 28 that seals oil-proof state.

In interior all sides of said break B-1, disposing clutch C-3 from outer circumferential side to the front side of planetary pinion DP.The oil servomotor 30 that this clutch C-3 has the friction version 31 that is made up of external friction version 31a and interior friction version 31b and is used to make this friction version 31 to engage or separates, in this friction plate 31b and after hub portion 51 spline engagement stated.

Said oil servomotor 30 has: form clutch drum 32, piston component 34, releasing plate 35 and the Returnning spring 36 of the cylinder body 32e of portion, constituted work grease chamber 37, removed grease chamber 38 by above-mentioned these members.Clutch drum 32 is that outer circumferential side member 32A and interior all side member 32B is bonding and constitute one; And be configured to state towards direction (rear side) opening relative with the clutch drum of said clutch C-1 22; Wherein, Said outer circumferential side member 32A has the lip part 32b that extends from interior all side direction outer circumferential side and extends to the tympanic part 32a of the outer circumferential side of said friction plate 31 from the outer circumferential side of this lip part 32b, said in the hollow axial region 32c of all side member 32B with boss part 70 of the said pump cover of embedding people (not shown).In addition, all side member 32B have from the front side of hollow axial region 32c part and extend to outer circumferential side in this, and form the flange shape 32f of piston supports portion.

At the outer circumferential side of said planetary pinion DP, said external friction plate 31a in interior all side spline engagement of said tympanic part 32a, be formed with lip part 32b in the front ends of said tympanic part 32a towards interior all sides.In addition, tympanic part 32a extends to the roughly rear side of this clutch drum 22 through the outer circumferential side of said clutch drum 22, and is connected with connector element 76.And this connector element 76 is connected with the sun gear S3 of said planetary gear unit PU.That is, when clutch C-3 engaged, clutch drum 32 formed identical rotation with connector element 76, that is to say, the rotation of the gear ring R1 of planetary pinion DP (rotation of slowing down) is passed to the sun gear S3 of planetary gear unit PU.

In addition, at the front end of tympanic part 32a, promptly the peripheral end of lip part 32b has the wall thickness 32d that forms heavy wall.Can utilize to bore to wait to run through vertically at the arbitrary portion of the circumferencial direction of this wall thickness 32d the hole is set, thus, can obtain the balance of clutch drum 32 from front side.

The inner peripheral surface of the rear side of said hollow axial region 32c part is supported on the fore-end of boss part 70 of pump cover through bearing b3 as aforementioned, and said hollow axial region 32c can rotate freely.In addition; The front side of hollow axial region 32c partly be said on the 32f of piston supports portion of all side member 32B; Have the lip portions 32g that extends shortly to the axial rearward direction side at outer circumferential side, this lip portions 32g is in the end difference 42d of the clutch drum 42 of interior all sides and clutch C-4 spline engagement.

Said piston component 34, and can move freely with relative with the said cylinder body 32e of portion with the state of the said piston supports 32f of portion tabling at the rear of the lip part 32b of said clutch drum 32 vertically; Utilize sealing component 63 and seal ring 64 sealings, formation is the work grease chamber 37 that seals oil-proof state between said piston component 34 and clutch drum 32 thus.In addition, outer circumferential side is formed with press part 34a at the rear of piston component 34, and the rear end of this press part 34a and friction plate 31 dispose relatively.And the outer circumferential face of 34a is formed with spline in this press part, with the spline spline engagement of interior all sides of the tympanic part 32a that is formed at said clutch drum 32.

Said releasing plate 35 is configured in the rear side of said piston component 34; And and compression is provided with Returnning spring 36 between this piston component 34, and utilization is configured in the peripheral part of this releasing plate 35 and the sealing component formation of interior perimembranous is the releasing grease chamber 38 that seals oil-proof state.

On the other hand, between planet gear D P and clutch C-3, the part that promptly is built in the clutch drum 32 is disposing said clutch C-4.In this clutch C-4, have by external friction plate 41a and in the friction plate 41 that constitutes of friction plate 41b and the oil servomotor 40 that is used to make this friction plate 41 engage or separate, this friction plate 41 interior all sides of the friction plate 31 of said clutch C-3 be configured to a part of and friction plate 31 overlapping in the axial direction.In addition, interior friction plate 41b and clutch hub 56 spline engagement, this clutch hub 56 is connected with the preceding planet frame plate CR1b of said planet carrier CR1.Thus; Constitute by independent member with the clutch hub 56 of the interior friction plate 41b spline engagement of clutch C-4 and the preceding planet frame plate CR1b of planet carrier CR1; Compare with the situation that the preceding planet frame plate CR1b of this clutch hub 56 and this is integrally formed, the radial position of the radial position of the pinion shaft PS1 of planet frame plate CR1b, PS2 and clutch hub 56 forms and staggers before can not restricting.

Said oil servomotor 40 has: form clutch drum 42, piston component 44, releasing plate 45 and the Returnning spring 46 of the cylinder body 42e of portion, constituted work grease chamber 47, removed grease chamber 48 by above-mentioned these members.Clutch drum 42 is made up of lip part 42b, tympanic part 42a and boss part 42c; And be configured to towards direction (rear side) opening identical with the opening direction of said clutch C-3; Wherein, Said lip part 42b extends from interior all side direction outer circumferential side, and said tympanic part 42a extends to the outer circumferential side of said friction plate 41 from the outer circumferential side of this lip part 42b, and said boss part 42c embeds the hollow axial region 32c of said clutch drum 32.

Said tympanic part 42a is configured in interior all sides of friction plate 31 of front side and the clutch C-3 of said planetary pinion DP; In interior all sides and said external friction plate 41a spline engagement; Front ends at said tympanic part 42a is formed with end difference 42d and lip part 42b; The lip portions 32g spline engagement of end difference 42d and said clutch drum 32 wherein, said lip part 42b from this end difference 42d towards interior all sides.Said boss part 42c embeds the place ahead part of the hollow axial region 32c of said clutch drum 32, and utilizes the said boss part 42c of opening elasticity baffle ring 55 restrictions side shifting rearward.

Said piston component 44 is configured at the rear of the lip part 42b of said clutch drum 42 with relative with the said cylinder body 42e of portion with the state of the hollow axial region 32c tabling of said clutch drum 32, and can be along axially moving freely; Utilize sealing component 68 and seal ring 69 sealings, formation is the work grease chamber 47 that seals oil-proof state between this piston component 44 and clutch drum 42 thus.In addition, outer circumferential side is formed with press part 44a at the rear of piston component 44, and the rear end of this press part 44a and friction plate 41 dispose relatively.

Said releasing plate 45 is configured in the rear side of said piston component 44; Compression is provided with Returnning spring 46 between this releasing plate 45 and this piston component 44, utilizes sealing component 59 formations of the peripheral part that is configured in this releasing plate 45 to be the releasing grease chamber 48 that roughly seals oil-proof state.

Next, hub portion 51 is described.Hub portion 51 has: base end part 51c, and it is integrally formed at the outer circumferential face side of said gear ring R1 and said gear ring R1 and becomes the outer circumferential face part of gear ring R1; Preceding protuberance 51a, it is configured to axial front side outstanding; Back protuberance 51b, it is configured to axial rearward direction side-prominent.In addition, at the outer circumferential face of hub portion 51, all be formed with spline 51s in this base end part 51c, preceding protuberance 51a and back protuberance 51b part.And; The preceding protuberance 51a part of these splines 51s and the interior friction plate 31b spline engagement of said clutch C-3; In addition, base end part 51c and back protuberance 51b part with this in the adjacent form of friction plate 31b and the interior friction plate 21b spline engagement of said clutch C-1.

In addition, on the preceding protuberance 51a of hub portion 51, be formed with a plurality of oilhole 51d that the root of said spline 51s is communicated with interior all sides along circumferencial direction.And, on the back protuberance 51b of hub portion 51, be formed with a plurality of oilhole 51e that the root of said spline 51s is communicated with interior all sides along circumferencial direction.

Next, the effect to clutch C-1, clutch C-3 and clutch C-4 describes.About clutch C-1, utilize the oil pressure that produces in the work grease chamber 27 that piston component 24 is moved vertically, clutch C-1 is engaged or separation through pushing friction plate 21.The never illustrated hydraulic pressure control device of the operating oil pressure that clutch C-1 uses is supplied to this work grease chamber 27 through the oil circuit c21 that is formed at clutch drum 22.In addition; Because work grease chamber 27 is acting on centrifugal oil pressure; Therefore lubricant oil is supplied to across the relative releasing grease chamber 28 in piston component 24 and work grease chamber 27 via the oil circuit c23 that is formed at clutch drum 22, thus with work grease chamber 27 in the centrifugal oil pressure balances that produce.

About clutch C-3, utilize the oil pressure that produces in the work grease chamber 37 that piston component 34 is moved vertically, clutch C-3 is engaged or separation through pushing friction plate 31.The operating oil pressure that clutch C-3 uses all is set to planar gap A from the oil circuit c24 that is formed at clutch drum 32 through whole circumference by not shown hydraulic pressure control device and is supplied to this work grease chamber 37.In addition; Because this work grease chamber 37 is acting on centrifugal oil pressure; Therefore lubricant oil is supplied to across the relative releasing grease chamber 38 in piston component 34 and this work grease chamber 37 via all be set to planar gap B in whole circumference from the oil circuit c25 that is formed at clutch drum 32; In this removes grease chamber 38, produce centrifugal oil pressure, thus with work grease chamber 37 in the centrifugal oil pressure balances of generations.

About clutch C-4, utilize the oil pressure that produces in the work grease chamber 47 to make piston component 44 along moving axially, clutch C-4 is engaged or separation through pushing friction plate 41.The never illustrated hydraulic pressure control device of the operating oil pressure that clutch C-4 uses is supplied to this work grease chamber 47 through the oil circuit c28 that the hollow axial region 32c at clutch drum 32 forms.In addition, work grease chamber 47 is acting on centrifugal oil pressure, and lubricant oil is supplied to across the relative releasing grease chamber 48 in piston component 44 and this work grease chamber 47 via the oil circuit c29 that is formed at hollow axial region 32c, thus with work grease chamber 47 in the centrifugal oil pressure balances that produce.

Next, the supply to lubricant oil describes.When the lubricant oil based on the oil pressure that is produced by for example oil hydraulic pump (not shown) is supplied to the oil circuit c23 that is formed at said clutch drum 22; Be supplied to and remove grease chamber 28 as separating oil removing, and via be arranged at remove plate 25 the 25a of corner cut portion through being supplied to outer circumferential side between this releasing plate 25 and the said supporting member 53.Be supplied to interior all sides that the lubricant oil of removing between plate 25 and the supporting member 53 is supplied to the back protuberance 51b of hub portion 51, said friction plate 21 be lubricated via the oilhole 51e of this hub portion 51.

On the other hand, when the lubricant oil based on the oil pressure that is produced by for example oil hydraulic pump (not shown) is supplied to the said oil circuit c26 that is formed at boss part 70, be supplied to via oil circuit c27 between the hollow axial region 32c of boss part 70 and clutch drum 32.The lubricant oil that is supplied between boss part 70 and the hollow axial region 32c is lubricated bearing b3, and through being supplied to the front side of planetary pinion DP between this hollow axial region 32c and the sun gear S1.The lubricant oil that is supplied to the front side of planetary pinion DP is lubricated small gear P1 and small gear P2 via the oil circuit that is formed at said preceding planet frame plate CR1b; And the lubricant oil that is supplied to the front side of planetary pinion DP is supplied to interior all sides of the preceding protuberance 51a of hub portion 51 through the gap of this preceding planet frame plate CR1b, via the oilhole 51d of this hub portion 51 said friction plate 31 is lubricated.

At this moment; The ratio of the axial length under the internal diameter of oilhole 51d and the state that is disposing friction plate 31 is greater than the ratio of the axial length under the internal diameter of oilhole 51e and the state that is disposing friction plate 21, and promptly the efficient to friction plate 31 supplying lubricating oils is higher than the efficient to friction plate 21 supplying lubricating oils.In addition, as shown in Figure 2, for clutch C-1 and clutch C-3 consider the joint of clutch C-3 in motion or the number of times that separates than the joint of clutch C-1 or separation often.Therefore, be higher than efficient to the friction plate that closes device C-1 21 supplying lubricating oils to the efficient of friction plate 31 supplying lubricating oils of the clutch C-3 often that engages or separate, thus good as the lubricating efficiency of automatic transmission 1.

As stated, automatic transmission 1 of the present invention, because clutch C-1 and clutch C-3 transmit the rotation of slowing down, clutch C-4 transmits the input rotation, so clutch C-1 and clutch C-3 torque transmitted are greater than clutch C-4 torque transmitted.In addition, because clutch C-1 engages when realizing bottom gear, clutch C-3 compares when top gear with clutch C-1 and engages, so clutch C-1 torque transmitted is greater than by clutch C-3 torque transmitted.Therefore; It is not overlapping in the axial direction to need the maximum clutch C-1 of torque capacity to be configured to the friction plate 41 of the friction plate 31 of clutch C-3 and clutch C-4; The friction plate 41 of the clutch C-4 that needs the minimum torque capacity is configured in interior all sides of friction plate 31 of the clutch C-3 of the second largest torque capacity of needs; Therefore; The friction plate 21 of clutch C-1 can be configured under the situation of friction plate 41 restrictions of friction plate that does not receive clutch C-3 31 and clutch C-4 diametrically, and the external diameter of friction plate 31 that can make clutch C-3 is greater than the external diameter of the friction plate 41 of clutch C-4.Therefore; Can make the torque capacity of the torque capacity of clutch C-3 greater than clutch C-4; Make the torque capacity of the torque capacity of clutch C-1, thereby can guarantee that clutch has required separately torque capacity, the axial length of automatic transmission 1 is shortened greater than clutch C-3.

In addition; It is relative across planetary pinion DP that the clutch drum 32 of the clutch drum 22 of the oil servomotor 20 of clutch C-1 and the oil servomotor 30 of clutch C-3 is configured to opening direction; Outer circumferential side at gear ring R1; On the hub portion 51 that axial two side-prominent modes form, to dispose the friction plate 21 of clutch C-1 and the friction plate 31 of clutch C-3 side by side with the mode of spline engagement from this gear ring R1; Therefore, can the friction plate 31 of the friction plate 21 of clutch C-1 and clutch C-3 be configured between them, not exist the clutch drum 22 of the oil servomotor 20 of clutch C-1.Thus, can make the friction plate 21 of this clutch C-1 approaching each other with the friction plate 31 of clutch C-3, and the friction plate 21 that can make clutch C-1 and planetary pinion DP be configured to overlapping in the axial direction, thereby can make automatic transmission 1 compact in the axial direction.

In addition; Be configured at the friction plate 31 of the interior all side at least a portion of the friction plate 31 of clutch C-3 and clutch C-3 the friction plate 41 of clutch C-4 overlapping in the axial direction; Therefore; Compare along the situation of axially-aligned configuration with the friction plate 41 of this clutch C-4 and the friction plate 31 of clutch C-3, can shorten axial dimension, thereby can make automatic transmission 1 compact in the axial direction.

In addition, the friction plate 31 of the clutch C-3 gear ring R1 from hub portion 51 in the axial direction is outstanding, and with the part spline engagement that is formed with oilhole 51d of hub portion 51, therefore, lubricant oil is supplied with from interior all sides.Therefore; The friction plate 21 of clutch C-1 disposes from the mode with spline engagement with the overlapping in the axial direction part of gear ring R1 of crossing over hub portion 51 to axial one side-prominent part from gear ring R1 of hub portion 51; Therefore; Can be to the friction plate 31 of clutch C-3 supplying lubricating oil efficiently, even engage or the number of times that separates becomes under many such situation, also can make good as the lubricating efficiency of automatic transmission 1 at engaged clutch C-3 in a plurality of gears more than 2 grades.

In addition; Preceding planet frame plate CR1b with the planet carrier CR1 of planetary pinion DP constitutes respectively individually owing to the clutch hub that makes clutch C-4 56; And with these clutch hub 56 fixed configurations on this preceding planet frame plate CR1b; Therefore for example under the situation that planet carrier CR1 and clutch hub 56 are formed as one; The supporting portion of pinion shaft PS1, PS2 and the root of clutch hub 56 are staggered the position diametrically, thereby restricted the radial position that to dispose clutch hub 56.But, according to the present invention, planet frame plate CR1b and clutch hub 56 formation separately respectively before making, therefore, can be in desired radial position with clutch hub 56 fixed configurations, and can clutch C-4 be configured in interior all sides of clutch C-3.

In addition; Sun gear S2 and sun gear S3 respectively with situation that the member that extends from planetary pinion DP side is connected under; Can the member that be connected with sun gear S2 be configured to the interior all sides through sun gear S3; Thereby can make radially-compact, and axial length is shortened when clutch C-4 is configured in the side different with planetary gear unit PU with planetary pinion DP.

Utilizability on the industry

Automatic transmission of the present invention can be used on the vehicles such as minibus, truck, motor bus and agricultural vehicle; Be applicable to the situation that the axial length that requires automatic transmission shortens, the situation that is specially adapted to require the axial length of the automatic transmission of the more than enough shelves of the ability speed change used in the FF type vehicle to shorten.

Claims (12)

1. automatic transmission has:

Epicyclic reduction gear, it is transfused to the rotation of input shaft, and can export with after the rotational delay of this input shaft deceleration rotation;

Planetary gear unit, its with said epicyclic reduction gear be configured in coaxial on, and have first rotating member, second rotating member, the 3rd rotating member and the 4th rotating member according to the order of the relation of rotating ratio;

First clutch, it is used for said deceleration rotation is inputed to said the 4th rotating member;

Second clutch, it is used for the rotation of said input shaft is inputed to said second rotating member;

Three-clutch, it is used for said deceleration rotation is inputed to said first rotating member;

Four clutches, it is used for the rotation of said input shaft is inputed to said first rotating member;

First latch for printed circuit, it is used for fixing the rotation of said first rotating member;

Second latch for printed circuit, it is used for fixing the rotation of said second rotating member;

Output link, it is connected with said the 3rd rotating member;

And, this automatic transmission can realize at least advancing 7 grades with retreat shelves, it is characterized in that,

Said first clutch, said three-clutch and said four clutches are configured in said epicyclic reduction gear one side on more leaning on axially than said planetary gear unit,

The friction plate of said first clutch is configured to the friction plate skew of the friction plate and the four clutches of said relatively three-clutch in the axial direction,

The friction plate of said four clutches is configured in interior all sides of the friction plate of this three-clutch with the overlapping in the axial direction mode of friction plate of at least a portion and said three-clutch,

The oil servomotor of said four clutches is configured in interior all sides of the oil servomotor of said three-clutch with the overlapping in the axial direction mode of oil servomotor of at least a portion and said three-clutch.

2. automatic transmission according to claim 1; It is characterized in that; It is overlapping in the axial direction that at least a portion of the releasing grease chamber of said three-clutch is configured at the friction plate of the outer circumferential side of the friction plate of said four clutches and this four clutches, and overlapping diametrically with the friction plate of said three-clutch.

3. automatic transmission according to claim 1 and 2; It is characterized in that; Between the oil servomotor configuration said epicyclic reduction gear and said planetary gear unit in the axial direction of said first clutch; And the oil servomotor of said three-clutch and the oil servomotor of said four clutches are configured in a side opposite in the axial direction with said planetary gear unit with respect to said epicyclic reduction gear

It is relative across said epicyclic reduction gear that the clutch drum of the clutch drum of the oil servomotor of said first clutch and the oil servomotor of said three-clutch is configured to opening direction.

4. according to each described automatic transmission in the claim 1 to 3, it is characterized in that said epicyclic reduction gear has:

First sun gear, it is fixed on the casing;

First planet carrier, it is used to be transfused to the rotation of said input shaft;

First gear ring, the rotation of the said input shaft of said first sun gear that it is fixed through rotation and the input of said first planet carrier becomes the deceleration rotation that rotating speed is lower than the rotation of said input shaft.

5. automatic transmission according to claim 4 is characterized in that, is formed with hub portion at the outer circumferential side of first gear ring of said epicyclic reduction gear, the part of this hub portion from this first gear ring at least to axial one side-prominent,

At least a portion of the friction plate of said three-clutch be configured to said hub portion from the outstanding part spline engagement of said first gear ring.

6. automatic transmission according to claim 5 is characterized in that, is formed with the oilhole that is used for lubricant oil conducting to the outer circumferential side of supplying with from interior all sides in said hub portion from the outstanding part of said first gear ring.

7. automatic transmission according to claim 6 is characterized in that, said three-clutch is by constituting at engaged clutch in a plurality of gears more than 2 grades.

8. according to each described automatic transmission in the claim 5 to 7, it is characterized in that it is also outstanding to axial opposite side that said hub portion is formed at the outer circumferential side of said first gear ring,

The friction plate of said first clutch and the friction plate of said three-clutch are configured in the outer circumferential side of said hub portion side by side, make said first clutch friction plate at least a portion and said hub portion to the outstanding part spline engagement of opposite side.

9. according to each described automatic transmission in the claim 4 to 8, it is characterized in that having the clutch hub with the friction plate spline engagement of said four clutches,

First planet carrier of said epicyclic reduction gear has the side plate that is used to support the small gear that can rotate freely, and said clutch hub and said side plate are constituted respectively separately, and with said clutch hub fixed configurations on said side plate.

10. according to each described automatic transmission in the claim 1 to 9, it is characterized in that said planetary gear unit has single small gear planetary pinion and the double pinion planetary pinion that is connected with each other by planet carrier,

Said single small gear planetary pinion is configured in than said double pinion planetary pinion and more leans on said epicyclic reduction gear one side,

Said the 4th rotating member is planetary second sun gear of said double pinion,

Said first rotating member is planetary the 3rd sun gear of said single small gear.

11. automatic transmission according to claim 10 is characterized in that, said second rotating member is second planet carrier; This second planet carrier is used to support long small gear and short and small gear; And this long small gear and this short and small gear can rotate freely, wherein, shown in long small gear public on said single small gear planetary pinion and said double pinion planetary pinion; Said short and small gear is meshed with this long small gear and forms said double pinion planetary pinion

Said the 3rd rotating member is second gear ring with said long pinion.

12., it is characterized in that according to each described automatic transmission in the claim 1 to 11, engage through making said first clutch, and the said second latch for printed circuit card is ended, thereby realize advancing 1 grade,

Through said first clutch is engaged, and the said first latch for printed circuit card is ended, thereby realizes advancing 2 grades,

Through said first clutch is engaged, and said three-clutch is engaged, thereby realizes advancing 3 grades,

Through said first clutch is engaged, and said four clutches is engaged, thereby realizes advancing 4 grades,

Through said first clutch is engaged, and said second clutch is engaged, thereby realizes advancing 5 grades,

Through said second clutch is engaged, and said four clutches is engaged, thereby realizes advancing 6 grades,

Through said second clutch is engaged, and said three-clutch is engaged, thereby realizes advancing 7 grades,

Through said second clutch is engaged, and the said first latch for printed circuit card is ended, thereby realizes advancing 8 grades,

Through said three-clutch or said four clutches are engaged, and the said second latch for printed circuit card is ended, thereby realize retreating shelves.

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