JPS5999166A - Drive for automobile with fluid torque converter which can be driven by overdrive gearing - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides a torque converter having an internal fluid operation circuit including a pump impeller and a turbine impeller, an input shaft that can be driven by an excitation drive, and a gear shift means that converts the input shaft into a torque converter. An automobile comprising a planetary gear speed increasing transmission device that can be inserted into a power path between the pump impeller and the pump impeller at an individual speed ratio of 1 or more, and a turbine impeller shaft that is coupled to the turbine impeller so as not to rotate relative to the turbine impeller. The present invention relates to a driving device for use in a vehicle.

In a known drive of this type (U.S. Pat. No. 3,054,307), the turbine blade axle acts as an input shaft of an automatic transmission, and when leaving the starting range, the main shaft of the drive prime mover and the turbine are connected by means of an interlocking clutch. Directly connected to the impeller shaft.

In contrast, the problem of the present invention is to make the torque converter participate in torque transmission in a different speed regardless of the speed increasing transmission in the first type of drive device, so that the torque converter can rotate without a comb clutch. The purpose is to make particular use of the vibration damping properties.

This object is advantageously achieved by the features of patent claim 1.

The embodiments of the claims are directed to advantageous embodiments of the drive device according to the invention.

BRIEF DESCRIPTION OF THE DRAWINGS Further details and advantages of the invention emerge from the claims, together with the following description of an exemplary embodiment shown diagrammatically in the drawing.

The embodiments of FIGS. 1 to 9 correspond in the following features.

First, the drive device IO connected before the automatic transmission 46 in the power path includes a pump impeller 2 and a turbine impeller 1.
3 and a guide impeller 41 . The turbine impeller 13 has a central turbine impeller i [1118
are connected to prevent relative rotation. Guide impeller 4
1 is a transmission 46 that is prevented from moving in the rotational direction opposite to the drive rotational direction by a one-way clutch 42 as usual.
The stator shaft 33, which is penetrated by the turbine impeller shaft 18, is fixed to the non-rotating housing 64. Drive bell-shaped body 2 covering the fluid torque converter 11
1 is connected to an input shaft 14 which can be driven by a drive shaft (not shown), and the range of this bell-shaped body 21 on the opposite side of the torque converter 11 is used for supplying pressure to the transmission 46 and to the next pump 25. The pump drive shaft 24 is coupled to the pump drive shaft 24 .

A planetary gear speed increasing transmission 17 is operatively inserted between the pump impeller 12 and the drive bell 21 , the planetary gear carrier 26 of which is connected to the drive bell 21 . The speed increasing transmission 417 can be inserted into the torque transmission path between the input shaft 14 and the pump impeller 12 by means of the speed change means 15 or 16, and the speed increasing transmission 17 is necessarily larger than 1. gear ratio. In the embodiments shown in FIGS. 1, 3 and 4, a multi-disc clutch is used as the gear switching means, while the embodiments shown in FIGS. 2 and 5 to 9 are used for this purpose. It has a multi-disc brake 16. A second driving connection between the input shaft 14 and the pump impeller 12, which takes place independently of the speed-up transmission 17, is achieved by the one-way clutch 19 when the gear changeover means 15 or 16 is released in traction operation. It is done. one way clutch 1
9 prevents the drive bell 21 from overtaking the pump impeller 12 in the drive rotation direction. In the actual ifW examples shown in FIGS. 1, 3 and 4, each gear switching clutch 15 is operatively inserted between the speed increasing transmission 17 and the pump impeller 12; In the embodiments of FIGS. 2 and 5 to 9, the respective gear shift brake 16 is operatively inserted between the step-up transmission 17 and the non-rotating brake housing part 20. The connection between the speed increasing transmission 17 and the pump impeller 12 takes place via a drive drum 27 which does not rotate with respect to the pump impeller 12, but the speed increase according to the embodiments of FIGS. When using the stage switching clutch 15, the drive drum 27
is indirectly connected to the outer concentric gear 29 of the speed increasing transmission 17 via this clutch 15, and in the examples shown in FIGS. is directly coupled to the outer concentric gear 29 to prevent relative rotation.

The turbine blade axle 18 connects to a large rear inner concentric gear 48 of the Ravigneau device 47, which
7 is the second (rear) single contact planetary gear transmission 63
is combined with Main planetary gear 5 of Lavigneaux device 47
2 further meshes with an outer concentric gear 50 and a reverse star gear 53, which, like the main planetary gear 52, is supported on an M star gear carrier 51. Reversing star gear 53
meshes with a second inner concentric gear 49 which is smaller. The planetary gear carrier 51 is connected to the rear planetary gear transmission 63
The output shaft 57 of the transmission 46, which can be coupled to the wheels in the usual way, is connected to the planetary gear carrier 55 of the rear transmission 63. The outer concentric gear 50 of the Lavigneaux device 47 can be connected to the inner concentric gear 56 of the rear planetary gear transmission 63 by means of a gear changeover clutch 58 and a one-way clutch 59 . Both inner concentric gears 49 and 56'' front planetary gear carrier 51 are connected to gear shift brakes 62 and 65 and 6 respectively.
It can be constrained by 0. Finally, the Lavigneaux device 47 can also be locked by a gear shift clutch 61 located between the inner concentric gear 49 and the planetary gear carrier 5I.

The same transmission mechanism 46 is used in all embodiments of FIGS. 1-9. However, the drive device 10 according to the invention is independent of the configuration of the transmission chain, as will be explained in more detail below.

In the embodiments of FIGS. 1, 3 to 5, 8 and 9, the one-way clutch 19 for traction operation is located between the drive bell 21 and the drive drum 27 of the pump impeller 12. be. This arrangement is the subject of claim 4.

On the contrary, in the embodiments of FIGS. 2, 6, and 7,
The one-way clutch 19 is operatively connected to the gear shift brake 16.
The inner concentric gear 28 of the speed increasing transmission 17 can be restrained by
and the driving bell-shaped body 21. This configuration is the subject of claim 5. In this arrangement, the one-way clutch 19 prevents the inner concentric gear 28 from overtaking the input shaft 14 in the direction of drive rotation, so that the pump impeller 1
Speed-up transmission N17 coupled to 2 so as not to rotate relative to
The outer concentric gear 29 is also driven at the same rotation speed as the input shaft 14.

In the embodiments of FIGS. 1, 3 and 4, the inner concentric gear 28 of the speed increasing transmission 17 is fixed against rotation with respect to the brake housing 20, and the speed increasing transmission fil1
The outer concentric gear 29 of 7 is connected to the drive drum 27 of the pump impeller 12 by means of the gear changeover clutch 15. This arrangement is the subject of claim 6. Of course, in this arrangement, the inner concentric gear of the speed increasing transmission 17 can also be releasably connected to the brake housing 20 by means of a brake.

In the embodiment of FIGS. 2 and 5 to 7 operated by the gear changeover brake 16 in the speed increasing transmission 17,
The drive drum 27 of the pump impeller 12 is the speed increasing transmission device 17
is fixedly connected to an outer concentric gear 29 of. This configuration is the object of claim 7.

What is common to the embodiments of FIGS. 1 and 2 is that the speed-up transmission 17 is located in front of the torque converter 11. Here, the planetary gear carrier 26 is connected to radial drive connections 22 and 30, respectively, on both axial sides;
The rear drive connection piece 30 is connected to the input shaft 14,
The front drive connecting piece 22 is connected to the drive bell 21 . This configuration is the subject of claims 8 and 9.

What is also common to the embodiments of FIGS. 1 and 2 is that the drive drum 27 is not connected directly to the pump impeller 12 via an inner drive shell 31. This configuration is the object of claim 10.

The drive drum 27 of the embodiment shown in FIGS. 1 and 3 has a short structure in the axial direction and is provided between the one-way clutch 19 for traction operation and the gear change clutch 15. This configuration is the object of claim 11.

In the embodiments of FIGS. 2 and 9, 4. According to claim 12, a radiation piece 32 is provided between the drive bell-like body 21 and the drive drum 27 to reduce liquid friction on the inner wall of the drive bell-like body 21.

In the embodiment according to FIGS. 3 to 9, the speed-up transmission 17 is arranged structurally after the torque converter 11, and in the first special embodiment according to FIG. , the torque converter 11 and the speed increasing transmission 1
7, and in a second special embodiment according to FIGS. 7 to 9, the speed increasing transmission I7 is shifted radially inwardly,
The Annai vane is even moved forward in the direction of the one-way clutch 42 again.

The inner concentric gear 28 of the speed increasing transmission 17 acts directly as a reaction member in the embodiment of FIGS. 3 and 4, whereas in FIGS. The stator shaft 33 can be indirectly fixed so as not to rotate with respect to the stator shaft 33. In the embodiment shown in FIG. 6, the one-way clutch 19, the speed increasing transmission 17, and the speed change brake 16 are located concentrically with each other and approximately in the center of a plane perpendicular to the axis of rotation.

The rear position of the speed increasing transmission 17 relative to the torque converter 11 and the fixing of the inner concentric gear 28 as a reaction member are the subject of claim 13.

In the embodiment of FIG. 4, the gear shift clutch 15 and the drive drum 27 are located within the coring space 34 of the torque converter 11. The gear switching clutch 15 includes a drive connecting piece 6 that can move between the pump impeller 12 and the guide impeller 41.
6 is connected to an outer concentric gear 29 of the speed increasing transmission [7]. This arrangement is defined in claim 14.

In the embodiment of FIGS. 3 and 4, the inner concentric gear 28, which serves as a reaction member of the speed-up transmission 17, is connected directly to the stator shaft 33. This configuration is the object of claims 15 and 16.

In the embodiment of FIG. 5 with a primary pump 25 located axially between the speed increasing transmission 17 and the gear changeover brake 16, a hollow shaft located concentrically between the pump drive shaft 24 and the stator shaft 33 is used. 35 is connected at one end to the inner concentric gear 28 used as a reaction member, and at the other end to the gear shift brake 16. This configuration is the subject of claim 17.

In the embodiment of FIG. 6 with a primary pump 25 located axially between the torque converter 11 and the speed increasing transmission 17, the drive bell 21 is connected to the pump drive shaft 24 via a radial connection 23. This pump impeller 24 is further connected to the inner race 44 of the one-way clutch 19 for traction operation and, via a radial drive link 37, to the planetary gear carrier 26 of the speed increasing transmission 17. . A hollow shaft 36 is provided concentrically between the pump drive shaft 24 and the stator shaft 33 , the front end of which is connected to the pump impeller 12 , and the rear end of which is connected to a drive drum 27 that does not rotate relative to the outer concentric gear 29 . They are connected to prevent relative rotation.

This configuration is the object of claim 18.

In the embodiments of FIGS. 6, 8 and 9, the pump impellers 12 of 1 to 11 are connected to a separate clutch device 38 or 3 so that they can be braked by the prime mover in runaway operation.
It can be connected to the driving bell-shaped body 2] via 9. For this purpose, a gear shifting clutch 39 is used in the embodiment of FIG. 6 to couple the planet gear carrier 26 to the drive drum 27. For the same purpose, in the embodiment according to FIGS. 8 and 9, a reverse one-way clutch 38 is provided, which connects the inner concentric gear 28 as a reaction part with respect to the stator shaft 33 in the runaway operation. Fixed so that it can rotate in the opposite direction. This configuration is the subject of claims 19 and 21. Finally, in the embodiment of FIG. 6, it is further provided that the pump drive shaft 24
The speed-increasing transmission device 1 is activated by the one-way clutch 19 for towing operation.
Advantageously, it is connected to the inner concentric gear 28 of 7.

What is common to the embodiments shown in FIGS. 7 to 9 is that the gear changeover brake 16 of the speed increasing transmission excitation device M17 is located concentrically between the stator shaft 33 and the outer ring 40, and ring 40
The geometrical contours of the pump impeller 12 and the guide impeller 1
This is determined by the shape of the outer shell of No. 3. This arrangement is subject to the 22nd term of the range of the special FF H requirement.

A brake drum 20, further common to the embodiments of FIGS. 7 to 9, is fixedly connected to the stator shaft 33 and accommodates the gear shift brake 16. A hollow shaft 35 penetrated by the stator shaft 33 enters the brake drum 20 , and the gear shift brake 16 is connected to the inner concentric gear 28 by this hollow shaft 35 . This arrangement is the subject of claim 23.

Furthermore, what is common to FIGS. 7 to 9 is that the brake housing 20 is used as a support for the guide impeller 41 according to claim 24.

Finally, what is further common to the embodiments of FIGS. 7 to 9 is that the brake housing 20 axially supports a one-way clutch 42 and a speed increasing transmission 17 which support a guide impeller 41 relative to the stator shaft 33. (Claim 25).

In both the embodiments shown in FIGS. 8 and 9, a reverse one-way clutch 38 is further provided radially inwardly with respect to the outer ring 40, and therefore between the gear changeover brake 16 and the stator shaft 33. (Claim 27).

In the embodiments of FIGS. 8 and 9, the speed increasing transmission 17 also has a drive drum 27 that does not rotate relative to the pump impeller 12.
The structure is excellent in that it has a particularly short structure because it is provided concentrically between the outer ring 40 and the stator shaft 33 (Claim 28).

In the embodiment according to FIG. 9, the drive drum 27 and the speed-up transmission 17 are located in the transition region between the pump impeller 12 and the guide impeller 41 in the axial direction and are therefore completely within the radial compartment side of the torque converter 11. (Claim 29).

Furthermore, in the embodiment of FIG. 9, as shown in claims 30 to 33, the driving bell-shaped body 21 is connected to the outer concentric wheel 29 of the speed increasing transmission 17 by the one-way clutch 19 for traction operation. combined. In order to similarly accommodate the reverse one-way clutch 19 concentrically between the outer ring 40 and the stator shaft 33, the speed increasing transmission 17 is configured as a thick friction wheel transmission, and The fan-shaped race portion of the planet wheel carrier 26 enters into the space between the two planet wheels 67 in the axial direction. Speed-up transmission device 1
One of the two concentric wheels 28 and 29 of 7, in this case the outer concentric wheel 29, is configured as a race 44 for the coupling of the one-way clutch 19.

However, as a modification of the embodiment shown in FIG.
It is also possible to configure 7 as a gear transmission in the usual way, the corresponding concentric gear 29 and the race 44 or 45 of the one-way clutch 19 being aligned with the axis, as in the embodiments of FIGS. 5 and 8. They can also be arranged adjacent to each other in the direction and configured integrally.

It is, of course, within the scope of the invention to use features of one embodiment in other embodiments.

The type and configuration of the transmission 46 may also be arbitrary, regardless of the configuration of the drive device 10 according to the present invention.

The drive device according to the present invention is based on the premise that in a five-speed transmission having increasing speeds, braking by the prime mover is not necessarily required in the first speed. For this reason, the special latch for the higher gears was omitted and only a one-way clutch for traction operation was used.

With the drive device according to the present invention, it is possible to start the vehicle at the full gear ratio of the first gear without using an increasing gear only for the purpose of starting. In that case, in order to always operate the remaining gears in increasing gears,
A speed increase stage can be added as a 1/2 switch.

It is also possible to exclude the gear increase in the first and second gears of the transmission 46 and add it only in the third gear.

In the drive device according to the invention, the strength of the torque converter is significantly increased by the high speed drive of the pump impeller, so that a comb clutch of the torque converter can be omitted.

In the drive device according to the present invention, the second pump for pressure supply of the automatic transmission idler 46 is rotated at the rotational speed of the prime mover, and the rotational speed of the prime mover is lowered by the increasing speed in a plurality of gears with respect to the output rotational speed of the transmission. It has the advantage of being able to

It should be mentioned with respect to the embodiment of FIG. Gear carrier 26, drive bell 21. It is connected to the turbine impeller shaft 18 via the one-way clutch 19 and the torque converter 11.

In the first gear, the gear switching clutch 58 and the gear switching brake 65 are engaged, and the one-way clutch 59 is activated.

In the second gear, the gear changeover brakes 62 and 65 are applied.

In the third gear, the gear switching clutch 61 and the gear switching brake 65 are engaged.

In the fourth gear, gear change clutches 6I and 58 are engaged to form a gear ratio of 1:1.

In reverse gear, the gear switching clutch 58 and the gear switching brake 6
0 is engaged, and the one-way clutch 59 is activated.

Now, by using the speed increasing transmission 17, engaging all gear changeover clutches 61, 58 and 15, and using only the inner concentric gear 28 in the speed increasing transmission 17 as the reaction member 2, from 1. An additional fifth forward gear with an overall transmission ratio of 11 can be formed. Since all three clutches act, braking can also be performed by the prime mover in this increased gear.

In the other gears, the gear changeover clutch 15 of the speed increasing transmission 17 is additionally engaged, so that this clutch 15
However, since the one-way clutch 38 shown in FIGS. 8 and 9 or the gear switching clutch 39 shown in FIG. be able to.

[Brief explanation of the drawing]

FIG. 1 is a configuration diagram of a first embodiment of a drive device according to the present invention connected before an automatic transmission in a power path, and FIG. 2 shows a structure of a torque converter similar to FIG. The configuration diagrams of the second embodiment of the drive device according to the present invention provided above, and FIGS. 3 to 6 show another 4 of the drive device according to the present invention in which the speed increasing transmission device is provided after the torque converter in the figure A. FIGS. 7 to 9 show configuration diagrams of two embodiments of a drive device according to the present invention in which all or a part of the speed increasing transmission device is provided concentrically between the outer ring of the torque converter and the stator shaft. FIG. 6 is a configuration diagram of three other embodiments.

Claims (1)

[Scope of Claims] l A torque converter having an internal fluid operation circuit including a pump impeller and a turbine impeller, an input shaft that can be driven by a driving motor, and a gear switching means that connects the input shaft and the pump impeller. In a drive device having a planetary gear speed increasing transmission device that can be inserted into the power path at an individual speed ratio of 1 to 4\ and a turbine impeller shaft coupled to the turbine impeller so as not to rotate relative to the turbine impeller, a clutch for traction operation is used. Device(
19), the input shaft (14) is additionally connected to the pump impeller (
12) and can be connected to this clutch device! (19) prevents a delay of the pump impeller (12) in the direction of drive rotation and enables overtaking, and the speed change means (15 or 16) connects the speed increasing transmission (17) and the pump impeller (12).
2) Alternatively, a drive device for a self-excited vehicle, characterized in that it is inserted between the housing part (20) which does not rotate. 2 Drive bell-shaped body (21) that rotates the torque converter (11)
) is the drive shaft (25) of the primary pump (25) on the opposite side to the input shaft (14) (7) and the input shaft (14).
2. Drive device according to claim 1, characterized in that it is further connected in a rotationally fixed manner to the planetary gear carrier (26) of the speed increasing transmission (17). 3. Drive according to claim 1, characterized in that the drive drum (27), which is connected to the pump impeller (12) so as not to rotate relative to each other, can be connected to an accelerating transmission (I7). Device. 4 The drive bell-shaped body (21) is a clutch device for towing operation! (
19) to the drive drum (27) (Figs. 1, 3 to 5, and 8). and Figure 9). 5 The driving bell-shaped body (21) is connected to the towing clutch device (
19), the brake (16) as a gear switching means
The reaction member (
28) The drive device according to claim 2 or 3 (FIGS. 2, 6, and 7). 6 The reaction member (28) of the speed increasing transmission (17) is fixed non-rotatably, and the third transmission part U' (29) of the speed increasing transmission (7) is connected to the clutch ( 15
) is connectable to the drive drum [27].
Figures 3 and 4). 7 The reaction member (28) of the speed increasing transmission (17) can be restrained by the gear changeover brake (16), and the third transmission part (29) of the speed increasing transmission (17) is connected to the drive drum (
27) in a manner that prevents relative rotation.
Figures 5 to 9). 8. The speed-up transmission (17) has two radial drive connections (22 and 30) each connected in the axial direction in a rotationally fixed manner to the planetary gear carrier (26).
), one drive connection piece (22 or 30) is connected to the drive bell-shaped body (21) so as not to rotate relative to it, and the other drive connection piece (30 or 2
2) is coupled to the input shaft (14) so as not to rotate relative to each other. The drive device M (FIGS. 1 and 2) according to claim 7. 9 The inner concentric gear (28) is used as a reaction member of the speed-increasing transmission bag ff1if (17), and the speed-increasing transmission (17)
) and the torque converter (11) is coupled to the input M ( ] 4 ). Apparatus (Figures 1 and 2). 10 Drive shell (31) within drive bell (21)
covers the turbine impeller (13) and the pump impeller (1
10. The drive device (FIGS. 1 and 2) according to claim 8, wherein the drive device (FIGS. 1 and 2) is coupled to the drive drum (27) and the drive drum (27) so as not to rotate relative to each other. 11. Claim 6, characterized in that the drive drum (27) is provided between the radially outer clutch device (19) for traction operation and the radially inner gear switching clutch (15). The drive device described in section. 12. The drive device according to claim 10, characterized in that a sealing piece (32) is provided between the drive bell-shaped body (21) and the drive drum (27). Figure 9). 13 Turbine impeller shaft (18) and pump drive shaft (2
A hollow stator shaft (3) is provided concentrically between the hollow stator shaft (3) and
3) is non-rotatably fixed to the non-rotating housing part, and the speed increasing transmission bag fil (17) is provided on the side of the torque converter (11) that is far from the input shaft (14),
The drive device according to claim 11 or 12, characterized in that the reaction member (28) of the speed-up transmission device (17) is non-rotatably fixable to the stator shaft (33). 3 to 5 and 7 to 9). 14 Drive drum (27) and gear switching clutch (15
) is the coring space (34) of the torque converter (11).
14. The drive device (FIG. 4) according to claim 13, characterized in that the drive device is provided within a . 15. The drive device according to claim 13 (FIGS. 3 and 4), characterized in that the reaction member (28) is connected to the stator shaft (33) so as not to rotate relative to it. 16. Drive device according to claim 13 or 15, characterized in that an inner concentric gear (28) is used as the reaction member. 17 - A secondary pump (25) is provided between the speed increasing transmission (17) and the gear switching brake (16) in the axial direction, and the hollow shaft (35) is connected to the stator shaft (33) and the pump drive shaft (24). ) and a hollow shaft (35
) is connected at one end to the reaction member (28) and at the other end to the gear changeover brake (16) (see FIG. 5). )
. An 18-order pump (25) is provided axially between the torque converter (11) and the speed increasing transmission (17), and concentrically between the pump drive shaft (24) and the stator shaft (33). A located hollow shaft (36) is fixedly coupled at one end to the pump impeller (12) and fixedly coupled at the other end to the drive drum (27), and also fixedly coupled to the pump drive shaft (24). is the planetary gear carrier (26
) The drive device according to claim 7 (FIG. 6), characterized in that the drive device is coupled so as not to rotate relative to the drive device (FIG. 6).
. 19 In order to connect the pump impeller (12) to the input shaft (14) via the speed-up transmission device (17) during runaway operation, the speed-up transmission bag! The drive device (FIGS. 6, 8, and 9) 20 according to claim 17 or 18, characterized in that (17) has a speed switching means (38 or 39). Gear switching brake (16)
Claims 18 or 19, characterized in that the inner concentric gear (28) and the pump drive shaft (24), which can be stopped by the pump drive shaft, are connected to each other by a one-way clutch for traction operation (19). The drive device described in (Fig. 6)
. 21. The drive device according to claim 18 (see Fig. 6 ). 22 The gear switching brake (16) is connected to the outer ring (40) geometrically formed by the outer shell of the impeller (12, 13, 14) of the torque converter (11) and the stator shaft (
33) The drive device according to claim 13 or 19 (FIGS. 7 to 9), characterized in that the drive device is provided concentrically between the drive device (FIG. 7 to FIG. 9). 23 A cylindrical brake housing (20) that is coupled to the stator shaft (33) so as not to rotate relative to the stator shaft (33), and an inner concentric gear (28) that is penetrated by the stator shaft (33).
A hollow shaft (35) that is connected so as not to rotate relative to the
23. The drive device (FIGS. 7 to 9) according to claim 22, characterized in that the gears are connected to each other by a gear changeover brake (16). 24. Drive device according to claim 23, characterized in that the guide impeller (41) of the 24 torque converter (11) is supported on the brake housing (20).
Figures 7 to 9). 25 The brake housing (22) includes a one-way clutch (42) that connects the guide vane (41) to the stator shaft (33) in the axial direction, and a speed-increasing transmission bag! (17) The drive device according to claim 23 or 24 (see FIGS. 7 to 9). 26. The drive device (No. 8 (Fig. and Fig. 9). 27. Claim 26, characterized in that the reverse one-way clutch for overrunning operation (38) is provided concentrically between the gear changeover brake (16) and the stator shaft (33). (FIG. 8 and FIG. 9). 28. Claim 2, characterized in that the drive drum (27) and the speed-increasing transmission (17) are provided concentrically between the outer ring (40) and the stator shaft (33).
2. The drive device according to item 2 (FIGS. 8 and 9). 29 Drive drum (27) and speed increasing transmission bag fa (17
) is provided between the pump impeller (12) and the guide impeller (41) in the axial direction. Figure 9). 30. Claims 22 to 2, characterized in that the drive bell (21) is connected to the outer concentric gear (29) by a one-way clutch (19) for traction operation.
9. The drive device according to any one of Item 8 (FIG. 9). 3) A patent characterized in that a one-way clutch (19) for traction operation is provided concentrically between a concentric gear (28 or 29) and a sector race (43) of a planetary gear carrier (26). The drive device according to claim 30 (
Figure 9). 32. The patent claim is characterized in that a toothless planetary friction transmission is used as the speed-increasing transmission, and the concentric gear (29) is configured as a race (44) of a one-way clutch (19) for traction operation. The drive device according to range 29 (FIG. 9). 33 One concentric gear (28
or 29) and one race (44 or 45) of the one-way clutch for traction operation (19) are adjacent in the axial direction and are integrally constructed. Drive device as described.