WO2015011414A1

WO2015011414A1 - Automatic transmission and corresponding control method

Info

Publication number: WO2015011414A1
Application number: PCT/FR2014/051908
Authority: WO
Inventors: Matthieu Rihn; Frédéric HEIT
Original assignee: Punch Powerglide Strasbourg (Societe Par Actions Simplifiee)
Priority date: 2013-07-25
Filing date: 2014-07-23
Publication date: 2015-01-29
Also published as: CN105705830A; FR3009053B1; CN105705830B; FR3009053A1

Abstract

The present invention relates to an automatic transmission comprising: - an input shaft (AE), - an output shaft (AS), - a stationary element (ES), such as a casing for example, - a first Ravigneaux gearset (T1) forming an input gearset, - a second Ravigneaux gearset (T2) forming an output gearset, - first, second, third, fourth, fifth, sixth and seventh torque-transmitting members (C1, C2, C3, C4, C5, C6, C7) that can be engaged or activated selectively in order to establish ten forward gear ratios and one reverse gear ratio, which automatic transmission is characterized in that the seven selective torque-transmitting members (C1, C2, C3, C4, C5, C6, C7) are positioned and arranged in order selectively, for each gear ratio, to connect two movement-input constituent functional elements (T2C3, T2C4, T2S3, T2S4) of the second output gearset (T2) each to one out of the input shaft (AE), the stationary element (ES) and the input gearset (T1).

Description

AUTOMATIC TRANSMISSION AND CORRESPONDING CONTROL METHOD

The present invention relates to a ten-speed automatic transmission in the forward direction for a motor vehicle or the like.

In the field of automatic transmission devices, there is a constant demand to provide an increasing number of forward gear ratios.

This demand results from a dual tendency for drivers and vehicle manufacturers to want, on the one hand, a large number of under-multiplied speeds for driving comfort and optimal adaptation of the driving system. motor at different low speeds and, on the other hand, a large number of overdrive speeds, at least three or four, to reduce consumption at high running speed (maintaining a low engine speed), while being able to to absorb variable relief patterns and to maintain the possibility of acceleration under these conditions.

By documents US 2009/0192009, US 201 1/0207575 and

US 201 1/0207573, there are already known automatic transmissions having ten speeds in forward and reverse. Such transmission seems to be a good compromise between increased performance and an acceptable structural complexity, industrially and economically.

In particular, the aforementioned documents US 201 1/0207573 and US 201 1/0207575 each relate to an automatic transmission comprising:

- an input tree,

- an output tree,

a stationary element, such as a housing, for example

- A first train train input train, the train having as functional components at least the first and second sun wheels, first and second ring gear, a set of satellite gears, a set of long gears and a satellite carriers,

a second train Ravigneaux forming an output train, this train comprising as functional elements constituting at least first and second sun wheels, at least one first ring gear, a set of satellite gears, a set of long gears and a planet carrier, a train in which the planet carrier is constantly connected to the output shaft,

first, second, third, fourth, fifth, sixth and seventh torque transmission members that can be selectively engaged or activated to establish ten forward speed ratios and a reverse speed ratio between the input shaft and the output shaft.

However, these known transmissions are not optimized in terms of configuration to allow operation limiting the number of members activated to achieve a speed ratio (reduction of power loss, increase in performance) or to achieve a reduced footprint and a simpler constitution.

For this purpose, the invention proposes, in connection with an automatic transmission of the aforementioned type, that the first sun gear is constantly connected to the input shaft and in which the planet carrier is constantly secured to the stationary element, that the seven torque transmission members are positioned and arranged to selectively connect, for each speed, two movement input functional components of the second output gear each to one of the input shaft; stationary element and the input train.

The invention will be better understood, thanks to the following description, which refers to the preferred embodiments, given by way of non-limiting examples, and explained with reference to the appended diagrammatic drawings, in which:

FIG. 1 is a partial schematic wiring diagram of a transmission according to one embodiment of the invention;

Figure 2 is a simplified functional schematic representation of an alternative embodiment of the transmission shown in Figure 1;

FIG. 3A represents, in connection with a first practical variant embodiment of the invention, a passage matrix or interlocking table of the various clutches and brakes forming part of the transmission, with indication of speeds, ratios, jumps between speeds (staging), as well as connected elements for each speed;

FIG. 3B is an example of a table for dimensioning the teeth of the different stages of the transmission in order to obtain the total opening of the table of FIG. 3A; FIG. 4A represents, in connection with a second practical variant embodiment of the invention, a table for engaging the various clutches and brakes forming part of the transmission, with indication of speeds, ratios, jumps between speeds, as well as connected elements for each speed;

FIG. 4B is an example of a table for dimensioning the teeth of the different stages of the transmission in order to obtain the total opening of the table of FIG. 4A;

FIG. 5A represents, in connection with a third practical variant embodiment of the invention, a table for engaging the various clutches and brakes forming part of the transmission, with indication of speeds, ratios, jumps between speeds, as well as connected elements for each speed;

FIG. 5B is an example of a table for dimensioning the teeth of the different stages of the transmission to obtain the total opening of the table of FIG. 5A, and

Figure 6 is a partial sectional view of a practical construction variant of a transmission as shown in Figure 1.

Figures 1, 2 and 6 illustrate, partially and in section along a plane passing through the longitudinal axis, in different forms of representation, an automatic transmission according to the invention. These partial representations allow the skilled person to easily deduce by symmetry the complete construction of the transmission.

As shown in the appended figures, the transmission according to the invention comprises:

an input shaft AE,

an output shaft AS,

a stationary element ES, such as a casing for example, a first train Ravigneaux T1 forming an input train, this train T1 comprising as functional elements at least first and second solar wheels T1S 1, T1S2, first and second ring gears T1C1, T1C2, a set of planet gears T1PS, a set of long gears T1PL and a planet carrier T1SC, - a second train Ravigneaux T2 forming an output train, this train T2 comprising as elements functional components constituting at least first and second solar wheels T2S3, T2S4, at least one first ring gear T2C3, a set of T2PS satellite gears, a set of T2PL long gears and a T2SC gear carrier, train T2 in which the T2SC carrier is constantly connected to the output shaft AS,

first, second, third, fourth, fifth, sixth and seventh torque transmission members C1, C2, C3, C4, C5, C6, C7 that can be selectively engaged or activated to establish ten forward gears and one gears; speed ratio in reverse between the input shaft AE and the output shaft AS.

According to the invention, the first sun gear T1 S1 is constantly connected to the input shaft AE and in which the carrier T1SC is constantly secured to the stationary element ES and the output gear T2 comprises a second ring toothed T2C4. In addition, the seven torque selector members C1, C2, C3, C4, C5, C6, C7 (or selective connection members) are positioned and arranged to selectively connect, for each speed, two functional components T2C3, T2C4. , T2S3, T2S4 of movement input of the second output train T2 each to one of the input shaft AE, the stationary element ES and the input train T 1.

As also shown in Figure 1, the various meshing means (planet gears, long gears, rings, solar wheels) are arranged on four floors distributed in parallel planes perpendicular to the longitudinal axis and spaced along the latter.

Thus, to achieve the ten speeds in forward and reverse, the automatic transmission according to the invention comprises only two trains Tl and T2 knuckle and seven connection members or torque selector C1 to C7, and only two elements T2 output stream movement input or reception are connected to realize each gear ratio.

It is further noted that for each of the forward speeds the output gear T2 is connected directly to the input shaft AE by at least one of the torque selector members C1 and C7.

According to a preferred embodiment of the invention, apparent from FIGS. 3A, 4A and 5A, only two of the torque selective transmission members C1 to C7, more precisely exactly two such members, are each time active or engaged for the establishment of each possible gear ratio, forward and reverse. As a result, the loss of power is generally limited compared to automatic transmissions with a large number of known speeds that require the engagement or activation of at least three torque transmission members to perform some or all of the ratios. possible speeds (see US documents cited above).

Furthermore and additionally, each forward speed is advantageously established by engagement or activation of a clean and unique pair of members among the seven torque transmission members C1 to C7, the transition from a given speed to an immediately higher or immediately lower speed being advantageously performed, on the one hand, by disengagement or deactivation of a single member of the pair of members realizing the current speed and, on the other hand, by engagement or activation of a single member forming part of the pair of members intended to achieve the new speed, that is to say establish the new speed ratio.

Thanks to this arrangement, the successive gearshifts in the forward direction each time involve only a transition or simple switching (and not double) at the members C1 to C7, thus simplifying the control and increasing comfort and convenience. fluidity of said shifts.

Preferably, each set of planet gears T1PS, T2PS and each set of long gears T1PL, T2PL comprises at least two, preferably three, pinions distributed uniformly about the longitudinal axis of the transmission (characteristic not illustrated in the accompanying drawings). By longitudinal axis of the transmission means in the present the virtual axis in which are aligned the AE input shaft and AS output.

According to another characteristic of the invention appearing in FIGS. 1 and 6 and allowing a simplification and a reduction of the bulk and losses of the transmission, the long gears T1PL and T2PL consist of stepped gears each with two stages with diameters and different teeth T1PL1, T1PL2 and T2PL1, T2PL2.

As also shown in FIGS. 1 and 6, the automatic transmission advantageously comprises three selective torque transmission members C3, C5 and C6 suitable for connecting the input gear T1 to the output gear T2 and two transmission members. selective torque Cl and C7 suitable for connecting the input shaft AE to the output train T2.

Furthermore, it is advantageously provided that the transmission of motion from T1 to T2 systematically involves the same movement input element at T2, namely T2S3 (for the second, fourth, fifth, seventh, eighth and tenth speeds ), thus facilitating the control, the configuration, the reduction in size and the dimensioning of the automatic transmission according to the invention.

In order to simplify the gearshifts in the forward direction and to best adapt the constructive characteristics of the members C1 to C7 to their function and to their operating stress, it can be provided that among the two selective torque transmission members C1 and C7 able to connect the input shaft AE to the output gear T2, one Cl is systematically active or engaged for the first six speed gears in the forward direction and the other C7 is systematically active or engaged for the five last gear ratios forward, the two aforementioned bodies C1 and C7 being active or engaged simultaneously to achieve the sixth gear ratio, preferably equal to 1 (see Figures 3A, 4A and 5A).

According to another characteristic of the invention also apparent from the appended figures, two of the torque transmission members C2, C4 are adapted and intended to each connect a constituent functional element T2C3, T2S3 of the output train T2 to the stationary element ES , thus forming brakes.

According to a practical embodiment shown in FIGS. 1 and 6, all the torque-selective transmission members C1, C2, C3, C4, C5, C6 and C7 consist of releasable or releasable coupling elements of the clutch type, preferably friction clutch type.

According to an alternative embodiment that emerges from FIG. 2, the torque selective transmission member C1 connecting the input shaft AE to the output gear T2 for the six low speed ratios, or six first gear ratios, consists of a detachable coupling member with claws or dog clutch.

In accordance with an alternative or additional variant, one C2 of the torque selective transmission members C2, C4 adapted and intended to connect a functional element constituting the output gear T2 to the stationary element ES is active or engaged for the realization the first report of forward speed and the realization of the speed ratio in reverse, this member C2 advantageously consisting of a removable coupling member with claws or clutch.

The realization of the body Cl and / or the member C2 in the form of clutch (s) allows to save space and limit power losses in the transmission.

Figures 1 to 6 of the accompanying drawings illustrate a preferred example of advantageous configuration for the automatic transmission, associated with the following specific arrangement of the organs C1 to C7:

the first and seventh torque selective transmission members C1 and C7 are arranged in parallel in the torque transmission flux between the input shaft AE and the output gear T2, preferably to be connected respectively to the second sun gear T2S4 and the second ring gear T2C4 of the output gear T2,

the fifth, third and sixth torque transmission members C5, C3 and C6 are arranged in parallel in the torque transmission flux between the input gear T1 and the output gear T2, preferably between the first ring gear T1C1 , the second ring gear T1C2 and the second sun gear T1S2 of the input gear Tl respectively, on the one hand, and the first sun gear T2S3 of the output gear T2, on the other hand,

the fourth and the second torque transmission members C4, C2 are arranged in parallel in the torque transmission flux between the stationary element ES and the output gear T2, preferably to be connected to the first sun gear T2S3 and to the first ring gear T2C3 respectively of said output gear T2.

As illustrated in FIGS. 3A, 4A and 5A, in connection with a preferred implementation and operation of the automatic transmission of the invention, the following couples of torque transmission members C1 to C7 are engaged or activated. to set respectively the ten forward gears and the reverse gears speed:

the second and sixth members C2 and C6 for reversing,

the first and second members C1 and C2 for the first speed in the forward direction, the first and third members C1 and C3 for the second speed in the forward direction,

the first and fourth members C1 and C4 for the third gear in the forward direction,

the first and fifth members C1 and C5 for the fourth speed in the forward direction,

the first and sixth members C1 and C6 for the fifth speed in the forward direction,

the first and seventh members C1 and C7 for the sixth gear in the forward direction,

the sixth and seventh members C6 and C7 for the seventh speed in the forward direction,

the fifth and seventh members C5 and C7 for the eighth speed in the forward direction,

the fourth and seventh members C4 and C7 for the ninth speed in the forward direction,

the third and seventh members C3 and C7 for the tenth speed in the forward direction.

The exemplary transmission embodiment described and illustrated herein has four overdrive speeds and provides a total aperture that may vary from about 6 to about 10.

According to an additional characteristic of the invention illustrated in FIG. 2, the fifth selective torque transmission member C5 consists of a clutch of a pseudo-static nature, this member C5 comprising an independent PS actuating means and separated from the two elements. that said member C5 is adapted and intended to couple (ease of realization by lack of power supply at the rotating elements).

The present invention also relates to a method of controlling an automatic transmission as described above, characterized in that it consists, to perform the starting in reverse or starting in first gear in the forward direction, to close or gradually engage the second torque selective transmission member C2, after having previously closed or engaged the first torque selective transmission member C1 to achieve the first gear ratio or after having previously closed or engaged the sixth torque selector member C6 to achieve the report of the march back. The member C2 then makes it possible to dissipate the energy of the starting in first or in reverse and to get rid of the torque converter or the electrical element with a similar function, normally mounted upstream of the transmission.

Of course, the invention is not limited to the embodiments described and shown in the accompanying drawings. Modifications are possible, particularly from the point of view of the constitution of the various elements or by substitution of technical equivalents, without departing from the scope of protection of the invention.

Claims

EVENDICATIONS

1. Automatic transmission comprising:

an input shaft (AE),

an output shaft (AS),

a stationary element (ES), such as a casing for example, a first train Ravigneaux (Tl) forming an input train, this train (Tl) comprising as functional components at least first and second wheels solar (T1S1, T1S2), first and second ring gears (T1C1, T1C2), a set of planet gears (T1PS), a set of long gears (T1PL) and a planet carrier (T1SC),

a second train Ravigneaux (T2) forming an output train, this train (T2) comprising as functional elements constituting at least first and second solar wheels (T2S3, T2S4), at least one first ring gear (T2C3), a set of planet gears (T2PS), a set of long gears (T2PL) and a planet carrier (T2SC), train (T2) in which the planet carrier (T2SC) is constantly connected to the output shaft (AS )

first, second, third, fourth, fifth, sixth and seventh torque transmission members (C1, C2, C3, C4, C5, C6, C1) which can be engaged or selectively activated to establish ten forward speed gears; and a speed ratio in reverse between the input shaft (AE) and the output shaft (AS),

automatic transmission characterized in that the first sun gear (T1S1) is constantly connected to the input shaft (AE) and in which the planet carrier (T1SC) is constantly secured to the stationary element (ES), in that that the output gear (T2) comprises at least one second ring gear (T2, C4), and in that the seven selectively geared transmission members (C1, C2, C3, C4, C5, C6, C1) are positioned and arranged to selectively connect, for each speed, two functional components (T2C3, T2C4, T2S3, T2S4) of motion input of the second output gear (T2) each to one of the input shaft (AE ), the stationary element (ES) and the input train (Tl).

Automatic transmission according to claim 1, characterized in that for each gear ratio two of the gear selector members (C1, C2, C3, C4, C5, C6, C1) are active. or engaged, each forward speed being established by engagement or activation of a clean and unique pair of members among the seven selectively transmitting torque members (C1 to C1), passing from a given speed to a speed immediately higher or immediately lower being advantageously performed, on the one hand, by disengagement or deactivation of a single member of the pair of members realizing the current speed and, on the other hand, by engagement or activation of a single member forming part of the pair of organs intended to achieve the new speed.

3. Automatic transmission according to claim 1 or 2, characterized in that each set of planet gears (T1PS, T2PS) and each set of long gears (T1PL, T2PL) comprises at least two, preferably three, pinions distributed uniformly around the wheel. longitudinal axis of the transmission and in that the long gears (T1PL and T2PL) consist of stepped gears each with two stages with different diameters and teeth (T 1 PL 1, T 1 PL2 and T2PL 1, T2PL2).

4. Automatic transmission according to any one of claims 1 to 3, characterized in that it comprises three selective torque transmission members (C3, C5, C6) adapted and intended to connect the input gear (Tl) to output gear (T2) and two torque transmission members (Cl and Cl) adapted and adapted to connect the input shaft (AE) to the output gear (T2).

5. Automatic transmission according to claim 4, characterized in that among the two torque transmission members (Cl and Cl) adapted to connect the input shaft (AE) to the output gear (T2), one (Cl) is systematically active or engaged for the first six forward gears and the other (C7) is systematically active or engaged for the last five forward gears, the two aforementioned gears (Cl and Cl) being active or engaged simultaneously to achieve the sixth gear ratio, preferably equal to 1.

6. Automatic transmission according to any one of claims 1 to 5, characterized in that two of the torque transmission members (C2, C4) are adapted and intended to each connect a constituent functional element (T2C3, T2S3) of the train output (T2) to the stationary element (ES), thereby forming brakes.

7. Automatic transmission according to any one of claims 1 to 6, characterized in that all the torque transmission members (C1, C2, C3, C4, C5, C6 and C7) consist of releasable or releasable coupling elements of the clutch type, preferably of the friction clutch type.

Automatic transmission according to claim 5, characterized in that the torque selective transmission member (C1) connecting the input shaft (AE) to the output gear (T2) for the six low speed gears, or first six gear ratios, consists of a removable coupling claw or dog clutch.

9. Automatic transmission according to claim 6, characterized in that one (C2) of torque transmission members (C2, C4) adapted and intended to connect a functional element constituting the output gear (T2) to the stationary element (ES) is active or engaged for the realization of the first gear ratio in forward gear and the achievement of the gear ratio in reverse, this member (C2) advantageously consisting of a removable coupling member with claws or dog clutch .

10. Automatic transmission according to any one of claims 1 to 9, characterized in that:

the first and seventh selective torque transmission members (Cl and Cl) are arranged in parallel in the torque transmission flux between the input shaft (AE) and the output gear (T2), preferably to be connected respectively to the second sun gear (T2S4) and the second ring gear (T2C4) of the output gear (T2),

the fifth, third and sixth torque transmission members (C5, C3 and C6) are arranged in parallel in the torque transmission flux between the input gear (Tl) and the output gear (T2), preferably between the first ring gear (T1C1), the second ring gear (T1C2) and the second sun gear (T1S2) of the input gear (Tl) respectively, on the one hand, and the first sun gear (T2S3) of the gear train output (T2), on the other hand,

the fourth and the second torque transmission members (C4, C2) are arranged in parallel in the torque transmission flux between the stationary element (ES) and the output gear (T2), preferably to be connected to the first sun gear (T2S3) and the first ring gear (T2C3) respectively of said output gear (T2).

Automatic transmission according to any one of claims 1 to 10, characterized in that the following couples of torque transmission members (C1 to C1) are engaged or activated for set the ten forward speed ratios and the reverse gear ratio, respectively:

the second and sixth members (C2 and C6) for reversing,

the first and second members (C1 and C2) for the first speed in the forward direction,

the first and third members (C1 and C3) for the second speed in the forward direction,

the first and fourth members (C1 and C4) for the third gear in the forward direction,

the first and fifth members (C1 and C5) for the fourth gear in the forward direction,

the first and sixth members (C1 and C6) for the fifth speed in the forward direction,

the first and seventh bodies (Cl and Cl) for the sixth gear in the forward direction,

the sixth and seventh members (C6 and Cl) for the seventh gear in the forward direction,

the fifth and seventh members (C5 and C1) for the eighth speed in the forward direction,

the fourth and seventh members (C4 and C1) for the ninth speed in the forward direction,

the third and seventh members (C3 and C1) for the tenth speed in the forward direction.

12. Automatic transmission according to any one of claims 1 to 1 1, characterized in that the fifth torque selective transmission member (C5) consists of a clutch pseudo-static nature, this member (C5) comprising a means of actuation (PS) independent and separate from the two elements that said member (C5) is adapted and intended to couple.

13. The method of controlling an automatic transmission according to claims 5 and 6, characterized in that it consists, to perform the start in reverse or starting in first gear in the forward direction, to close or gradually engage the second member for selectively transmitting torque (C2), after having previously closed or engaged the first selective torque transmission member (C1) to achieve the first gear ratio or after having closed or engaged previously the sixth selector torque transmission member (C6) to achieve the ratio of reverse.