EP1869296A1

EP1869296A1 - Device for variably adjusting control times of gas exchange valves of an internal combustion engine

Info

Publication number: EP1869296A1
Application number: EP06723539A
Authority: EP
Inventors: Jürgen Weber
Original assignee: Schaeffler KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2005-04-15
Filing date: 2006-03-20
Publication date: 2007-12-26
Also published as: CN101160454A; US20090038569A1; US7647905B2; WO2006108494A1; JP2008536047A; CN101160454B; DE102005017435A1; KR20070122213A

Abstract

The invention relates to device for variably adjusting control times of gas exchange valves of an internal combustion engine, comprising an internal rotor (3) and an external rotor (4), whereby one of the components is rigidly connected to the camshaft (2) and the other component is drivingly connected to the crank shaft.The external rotor (4) is rotationally mounted on the internal rotor (3). Also, at least one hydraulic chamber, which is defined by lateral walls (5, 6) and the internal rotor (3), is formed on the external rotor (4). The internal rotor (3) comprises a hub part (3b) and at least one wing (3a), whereby said wing (3a) of the internal rotor (3) extends into each hydraulic chamber (7) and separates said hydraulic chambers into two counter-working pressure chambers (10, 11). A groove (8), wherein a sealing strip is arranged, is formed on one of the surfaces of the internal rotor (3) or the external rotor (4), which is oriented towards the other component. A spring element (13) is arranged between a groove base (12) of the groove (8) and the sealing strip (9), the spring element pushes the sealing strip (9) in the direction of an opposite surface of the other component. According to the invention, the spring element (13) is introduced at the same time as the sealing element.

Description

Name of the invention

Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine

description

Field of the invention

The invention relates to a device for variably setting the timing of gas exchange valves of an internal combustion engine having an inner rotor and an outer rotor, wherein one of the components rotatably connected to the camshaft and the other component is in driving connection with a crankshaft, wherein the outer rotor rotatably mounted on the inner rotor is mounted on the outer rotor and at least one side walls and the inner rotor limited hydraulic chamber is formed, wherein the inner rotor has a hub portion and at least one wing, wherein in the hydraulic chamber, a wing of the inner rotor extends and divides these into two oppositely acting pressure chambers, wherein a groove facing the other component surface of the inner rotor or the outer rotor is formed, in which a sealing strip is arranged and wherein between a groove bottom of the groove and the sealing strip, a spring element is arranged, which the sealing strip in the direction e iner opposite surface of the other component urges.

Background of the invention

Devices of this type are well known in the art. For example, US Pat. No. 6,484,678 B2 describes a solution in which an inner rotor is screwed to the camshaft of the internal combustion engine via a central screw. The outer rotor is connected via a chain or via a toothed belt with the crankshaft in operative connection and is on the inner rotor rotatably mounted to this. Furthermore, the outer rotor is provided with circumferentially spaced jaws extending radially inwardly from a radially inner peripheral surface of the outer rotor. The radially inner boundary surfaces of the jaws rest on the inner rotor and thus serve as bearing surfaces. Furthermore, recesses are defined by the jaws on the outer rotor, which are sealed pressure-tight by the inner rotor and two side walls and thus serve as hydraulic chambers. Between the inner rotor and the outer rotor can - be initiated via an external hydraulic actuation - a relative rotational movement. For this purpose, the inner rotor is formed as an impeller, which consists of a hub part and integrally formed therewith wings. The wings close to the outer peripheral surface of the hub part and extend in the radial direction to the outside. Furthermore, each wing engage in a hydraulic chamber and divides it into two oppositely acting pressure chambers. By appropriate action on the respective pressure chamber, an adjustment of the inner rotor relative to the outer rotor between an "early stop" up to a "late stop" done.

A further embodiment of such devices is described, for example, in DE 198 08 618 A1, in DE 199 51 391 A1 and in DE 102 53 496 A1. In contrast to the first embodiment, the wing and the hub part of the inner rotor are manufactured separately here. The wings are arranged in vane grooves which are formed on the outer circumferential surface of the hub part. One wing each divides a hydraulic chamber into two counteracting pressure chambers. By appropriate action on the respective section of the hydraulic chamber, an adjustment of the inner rotor relative to the outer rotor can take place between an "early stop" and a "late stop". As an alternative to this embodiment, it is also possible to introduce the vane grooves into an inner circumferential surface of the outer rotor and to arrange the wings there.

To ensure that the wings are pressed radially outward against the radially outer end of the hydraulic chamber, so It is known from DE 199 63 094 A1, from DE 198 08 619 A1 and from DE 199 14 047 A1, to arrange a leaf spring element in the vane groove of the vane grooves carrying the vane, which radially adjusts the hydraulic chamber by means of the vane exerts outward force on the wing.

A problem with these devices is the fact that relatively high leakage flows flow between the pressure chamber of one hydraulic chamber or opposing pressure chambers of adjacent hydraulic chambers. In this case, the oil passes from the pressure chamber in which the higher pressure prevails over the gap between the wing and the outer rotor or over the gap between the inner rotor and outer rotor in the region of the bearing points to the respective pressure chamber in which the lower pressure prevails.

Although a reduction of the gaps leads to less leakage, but brings increased friction and increased manufacturing costs due to lower tolerances and thus higher manufacturing costs with it.

One solution to this problem is described in US 6,484,678. On the radially outer surface of the wings and in the area of the bearing surfaces of the outer rotor, radial grooves extending essentially in the axial direction are formed. In the grooves sealing strips are arranged, which are pressed by means of spring elements on the opposite surface of the respective other component. The spring elements are based on the one hand on the groove bottom of the grooves and on the other hand on the sealing strip. Thus, the gaps between the inner rotor and outer rotor are closed and reduces the leakage.

Although it is already possible with such a solution to achieve a good efficiency of the arrangement, leakage losses are still a problem of such devices. This leakage is inter alia due to the fact that hydraulic fluid from the one pressure chamber penetrates into the groove, the Carries sealing strip, and passes over the groove bottom to the other pressure chamber. Especially in applications where high reaction moments acting on the camshaft lead these leakage paths to unstable phase positions between the camshaft and the crankshaft.

The leakage behavior is an important quality criterion of such a device, as this determines the size, ie the installation space and the weight, of the adjuster and thus also influences the design of the valves, oil pumps, etc.

A disadvantage of the previously known solutions that in the middle position of the phase position in the groove increased leakage occurs; there is the sealing strip under a changing pressure load between the two areas of

Hydraulic chamber. This creates an alternating tilting of the sealing strip in the groove, which can lead to increased leakage. In particular, in the case of a plurality of hydraulic chambers and wings, the leakage losses add up to a considerable magnitude.

Although the reduction in internal leakage can be achieved by tighter tolerance of the grooves and Dichtieisten or by higher coefficients of friction in the leakage gap. However, the manufacturing accuracy required in this case entails considerably higher production costs, which is why this is not a viable option for substantially improving the leakage behavior, in particular the internal leakage behavior, of the phaser. Cost-driving are also additional sealing elements, which also increase the weight of the adjuster in a disadvantageous manner.

Object of the invention

The present invention is therefore based on the object, a device of the type mentioned in such a way that in particular the internal leakage losses are reduced. However, the manufacturing costs of the adjuster are not or not significantly increased. Furthermore, the adjuster should not be harder by the measures provided. With regard to the installation of the adjuster, the proposed measures did not negatively impact. It is also important that the proposed solution is maintenance-free, so that the maintenance costs of the adjuster should not be adversely affected. Overall, a higher efficiency of the adjuster should result without other factors, such as weight or production costs, being adversely affected.

Summary of the invention

The solu ng of this object by the invention is characterized in that the spring element is simultaneously designed as a sealing element and at least largely prevents a flow of hydraulic fluid from one side surface of the sealing strip on the groove bottom to the other side surface of the sealing strip.

As a result, a dense barrier for hydraulic fluid is created, which extends over the entire radial extent of the gap between the groove base and radially inner end face of the sealing strip, wherein the number of items and thus the assembly cost is not increased.

In a concretization of the invention it is proposed that the groove is formed on a bearing surface of the outer rotor, via which the outer rotor is mounted on the inner rotor, and the sealing strip and the spring element are arranged in this groove. As a result, the leakage flow between adjacent pressure chambers of adjacent hydraulic chambers is effectively prevented.

In this case, the use of the sealing strips and the spring element designed as a sealing element is conceivable both in embodiments of the device in which the inner rotor consists of a hub part and wings made separately from the hub part, as well as in devices in which the one or more wings integral with the Hub part are formed.

Furthermore, it can be provided that the wing is formed integrally with the hub part, that the groove is formed on a radially outer region of the wing. is formed and that the sealing strip and the spring element are arranged in this groove. As a result, mutually acting pressure chamber of a hydraulic chamber are sealed against each other.

Conceivable, of course, embodiments in which both sealing strips between the wings and the outer rotor and between the hub portion of the inner rotor and the outer rotor are provided, wherein the sealing strips are urged by spring elements, which are designed as sealing elements to the respective opposite component.

In a concretization of the invention it is provided that the spring element has at least two sealing edges or surfaces sealingly abut against the radially inner end face of the sealing strip and the groove bottom.

Preferably, the spring element in a section perpendicular to the axis of rotation of the inner rotor along the axial direction has a constant cross-section. The spring element can continue to extend in the axial direction substantially over the entire width of the sealing strip or the groove bottom.

The spring element rests with at least one sealing edge or surface, preferably with two sealing edges or surfaces, flat on the radially inner end face of the sealing strip and / or on the groove base.

According to one embodiment of the invention, the spring element may be arranged fixed to the radially inner end face of the sealing strip, d. H. Spring element and sealing strip then form a structural unit. The spring element can be glued to the radially inner end face of the sealing strip. It is also possible that the spring element is vulcanized on the radially inner end face of the sealing strip.

A further embodiment provides that the groove has a greater width in its groove base than corresponds to the width of the groove in the region in which the sealing strip is guided. The spring element preferably has with its A section arranged in the groove base has a width adapted to the width of the groove base.

The spring element can, for example, have a T-shaped, a double-T-shaped or a Z-shaped configuration in a section perpendicular to the axis of rotation of the inner rotor. Likewise conceivable is a circular, elliptical or rectangular shape in the section perpendicular to the axis of rotation of the rotor.

The spring element may be made of metal, in particular of spring steel. Alternatively, plastic, such as a silicone elastomer, is possible as a material. The metal may be at least partially coated or encased by a coating material. The coating material used is preferably a thermoplastic or duroplastic plastic or an elastomer.

The spring element may be integrally formed or composed of several parts.

The proposed solution has several advantages:

Internal leakage losses in the phaser are considerably reduced. The leaking oil flow from one side of the flight over the bottom of the groove to the other side of the wing and between adjacent pressure chambers of adjacent hydraulic chambers is largely eliminated. This increases the efficiency of the transmitter. In particular, a leakage loss in the center position of the sealing strips in its groove is significantly reduced; this loss can be reduced by up to 90%.

As a result of the proposed invention, this is very simple in terms of manufacturing technology, so that no appreciable additional costs arise from the implementation of the invention. On the contrary, cost reductions can occur if other measures to reduce leakage are avoided. In particular, it is possible to have a very narrow tolerances of the inner rotor and to dispense with the outer rotor or the sealing strip and the grooves receiving them, since tightness is ensured by the proposed measures even with greater tolerance.

The assembly of the adjuster and especially the introduction of the invention provided with sealing edges or surfaces spring element is possible in a very simple and therefore cost-effective manner. This can lead to simplifications in the assembly of the adjuster; the supply of the proposed spring element in the groove can be made easier than is the case with previously known solutions.

Maintenance of the elements according to the invention is not required, so that in this respect no higher costs. are. The proposed solution works absolutely reliably even without any maintenance.

The weight of the adjuster is practically not increased compared to previously known solutions. It can even be reduced if the invention dispenses with more complex and heavier solutions, such as providing sealing elements in addition to the spring elements.

The entire dimensions of the adjuster are not changed by the proposed invention, so that the space of the adjuster remains unchanged. An implementation of the proposed solution in series products is easily possible.

Brief description of the figures

In the drawings, embodiments of the invention are shown. Show it:

1 very schematically an internal combustion engine, 1a shows a cross section of a device according to the invention along the line CD of FIG. 1b, shown without ancillaries,

FIG. 1b shows a longitudinal section of the device from FIG. 1a along the line A-B, FIG.

2a shows a cross section of another device according to the invention along the line E-F of FIG. 2b, shown without ancillary units,

2b shows a longitudinal section of the device of Figure 2a along the line G-H,

3 is an enlarged view of a detail of Fig. 1a and 2a namely a sealing strip in the receiving groove,

4 shows an alternative to FIG. 3 embodiment,

5 shows another embodiment alternative to FIG. 3,

FIG. 6 shows another alternative embodiment to FIG. 3, FIG.

Fig. 7 shows a further alternative to Fig. 3 embodiment and

Fig. 8 is a further alternative to Fig. 3 embodiment.

Detailed description of the figures

In Fig. 1, an internal combustion engine 100 is outlined, wherein a seated on a crankshaft 101 piston 102 is indicated in a cylinder 103. The crankshaft 101 is in the illustrated embodiment via a Zugmit- teltrieb 104 and 105 with an intake camshaft 106 and exhaust camshaft 107 in conjunction, wherein a first and a second device 1 for a relative rotation between the crankshaft 101 and camshafts 106, 107 can provide. Cams 108, 109 of the camshafts 106, 107 actuate an intake gas diverter valve 110 and the exhaust gas exchange valve 111, respectively.

In the figures 1a and 1b partially only a device 1 for the variable adjustment of the timing of gas exchange valves of an internal combustion engine is shown. The device 1 has an inner rotor 3 and an outer rotor 4, which can be adjusted relative to one another by means of a hydraulic adjustment mechanism, not shown, between two end positions. As an example, reference is made to DE 101 35 146 A1, where the usual mode of operation of such a device is explained.

Via a chain, not shown, an operative connection between a crankshaft of the internal combustion engine and designed as a sprocket drive wheel 20 is produced, which is rotatably connected to the outer rotor 4 and whose body simultaneously forms a first side wall 5. The adjustment mechanism, not shown, establishes a relative rotational position between outer rotor 4 and inner rotor 3. The inner rotor 3 is rotatably screwed by a central screw 21 with a camshaft 2 of the internal combustion engine. The adjuster 1 rotates about the axis of rotation 19.

In the exemplary embodiment, the outer rotor 4 has four incorporated recesses 7a, which are separated from one another by jaws 7b and form hydraulic chambers 7. These will be - s. Fig. 1 b - limited on the one hand by the already mentioned side wall 5 and on the other hand by a second side wall 6.

In a hub part 3b of the inner rotor 3, four vane grooves 8a are incorporated in the exemplary embodiment, which in the present case extend radially and along the axial direction a. In each wing groove 8a, a wing 3a is inserted. The wing 3a extends in its assembled state radially to the outer radial Limiting the hydraulic chamber 7. As a result, the hydraulic chamber 7 is divided into two pressure chambers 10 and 11, each of which - not shown in detail - are connected to hydraulic lines, can be introduced via the hydraulic fluid into the pressure chambers 10, 11. Viewed in the axial direction a, the wing 3a extends over a width b which corresponds to the width of the outer rotor 4 (see Fig. 1b).

So that the wing 3a bears tightly against the outer radial boundary surface of the hydraulic chamber 7, a leaf spring element 13a is arranged in the area of the vane groove bottom 12a, as is known in the prior art.

The outer rotor 4 is rotatably supported to the inner rotor 3 by means of bearing surfaces 24 formed on the jaws 7b. In order to prevent leakage losses between adjacent pressure chambers 10, 11 of adjacent hydraulic chambers 7 by oil flow along a gap in the region of the bearing surfaces 24, a groove 8 is formed on the outer rotor 4 in the region of the bearing surfaces 24 in which a sealing strip 9 is arranged. The sealing strip 9 is urged by means of a spring element 13 in the direction of the inner rotor 3. In this case, the spring element 13 is disposed within the groove 8 and is supported on the one hand on a groove bottom 12 of the groove 8 and the other on the sealing strip 9 from. In order to prevent leakage flows via the groove base 12 from one pressure chamber 10, 11 to the other pressure chamber 10, 11, the spring element 13 is designed as a sealing spring element. In the exemplary embodiment, the spring element 13 is provided with two sealing edges or sealing surfaces 14 and 15. The sealing edges or surfaces 14, 15 are on the one hand to the radially inner end face 16 of the sealing strip 9 and the other on the groove base 12 sealingly and thus prevent a flow of hydraulic fluid from the one side surface 17, 18 of the sealing strip 9 on the groove bottom 12 to the other side surface 17, 18 of the sealing strip. 9

In a section perpendicular to the axis of rotation 19, the spring element 13 has a constant cross section along the axial direction a. The axial extent of the Spring element 13 and the sealing strip corresponds to the width b of the outer rotor. 4

FIGS. 2 a and 2 b show a second embodiment of a device 1 according to the invention. As in the first embodiment of FIGS. 1 a and 1 b, recesses 7 a are formed on the radially inner boundary surface of the outer rotor 7 b, which jaws 7 b project radially inwardly are separated from each other. The recesses 7a are pressure-tightly sealed by side walls 5, 6 and the inner rotor 3 and thus form hydraulic chambers 7. In each of the Hydraulikkammem 7 projects in each case a wing 3a of the inner rotor 3, whereby the hydraulic chamber 7 is divided into two oppositely acting pressure chambers 10, 11. By selectively applying a group of the pressure chambers 10, 11 or, both groups, the phase angle of the inner rotor 3 to the outer rotor 4 can be changed or maintained. In contrast to the first embodiment, which is shown in FIGS. 1a and 1b, here the hub part 3b and the wings 3a are made in one piece.

In order to keep leakage flows between the pressure chambers 10, 11 of a hydraulic chamber 7 low, a radially and substantially axially extending groove 8 is formed in each wing 3a at the radially outer, abutting the outer rotor surface 4, in which a sealing strip 9 is arranged. The sealing strips 9 are urged in the direction of the outer rotor 4 by means of a respective spring element 13, which is arranged in the groove base 12 of the groove 8. The spring element 13 is in this case also designed as a sealing spring element, whereby leakage currents from one side surface 17, 18 of the sealing strip 9 to the other side surface 17, 18 are effectively prevented via the groove bottom 12.

It can also be provided, as shown in Figures 2a and 2b, in the region of the bearing surface 24 of the jaws 7b of the outer rotor 4 each provide one or optionally a plurality of grooves 8, in which sealing strips 9 are arranged by a spring element 13 in the direction of the inner rotor 3 are urged. These spring elements 13 are advantageously also as Density spring elements running, whereby the leakage flow between adjacent pressure chambers 10, 11 adjacent Hydraulikkammem 7 via the groove bottom 12 of the grooves 8 is prevented. It would also be conceivable to arrange the sealing strip 9 in grooves, which are introduced into the inner rotor 3. It is important to ensure that the sealing strip 9 is in the circumferential direction in the area of the bearing surface 24 in any position of the inner rotor 3 relative to the outer rotor 4. Also in this embodiment, the use of a sealing spring element is advantageous, which urges the sealing strip 9 in the direction of the outer rotor 4.

The spring elements 13 in the embodiment illustrated in FIGS. 2a and 2b can be identical to those of the first embodiment (FIGS. 1a and 1b).

Figures 2a and 2b show, in addition to the drive wheel 20 designed as a sprocket, a spur gear toothing, via which a second camshaft can be driven. This embodiment is used, for example, in dohc engines in which separate, adjacent camshafts are provided for the intake and exhaust valves.

Furthermore, the device 1 is provided with a locking mechanism 25. This consists of a locking piston 26 and a spring 27, which are arranged in an axially extending receptacle 28 of the inner rotor. The spring 27 urges the locking piston 26 in the direction of the first side wall 5. In insufficient supply of the device 1 with hydraulic means engages the locking piston 26 at a certain relative position of the inner rotor 3 to the outer rotor 4 in a formed on the first side cover 5 recess 29, whereby the phase angle of the inner rotor 3 is set to the outer rotor 4. During operation of the internal combustion engine of the first side cover 5 facing end side of the locking piston 26 hydraulic fluid is supplied, whereby this completely against the force of the spring 27 in which the receptacle 28 is urged and thus the locking of the inner rotor 3 is lifted to the outer rotor 4. Details of the spring element 13 result from FIGS. 3 to 8. Here, various embodiments of the spring element 13 and, in particular, its sealing edges or sealing surfaces 14 and 15 are outlined. The illustrations show a sealing strip 9 and the associated spring element 13, which are arranged in a wing 3a of the second embodiment of the device 1. Analogously, however, the components can also be provided on the bearing surface 24 between the inner rotor 3 and the outer rotor 4 of both embodiments of the device 1. The size of the gap between the upper wing side and the outer rotor 4 is greatly exaggerated.

The spring element 13 may have different shapes in section, of which various possibilities are shown in the figures. The element 13 may have an L-shape or a double-T-shape in cross-section (FIGS. 3 and 4). Likewise, a Z-shape is possible (Figure 5). In all cases, the sealing edges or sealing surfaces 14 and 15 lie flat once on the radially inner end face 16 of the sealing strip 9 and once on the groove base 12, so that reliable oil flow is prevented at these locations.

In order to anchor the spring element 13 securely in the groove, the embodiment variants according to FIGS. 6 to 8 provide that the groove 8 is widened in the region of the groove bottom 12. As best seen in Fig. 9, the groove 8 in the region of the groove bottom 12 has a groove base width bβ which is larger than the groove width b _F in the region in which the sealing strip 9 is held.

In FIGS. 6 to 8 again different cross-sectional shapes of the spring element 13 are sketched, namely an I-shaped or double-T-shaped (FIGS. 6 and 7) and a Z-shaped (FIG. 8). As can be seen, the shape of the spring element 13 and, in particular, its sealing edge or sealing surface 15 is adapted to the shape of the enlarged groove base 12. The groove 8 extends in the embodiment in the axial direction a; but it can also be provided that the groove 8 extends obliquely to the axial direction.

The spring element 13 can - as in the embodiment - be used as a separate element, which is paired with the sealing strip 9 during assembly. But it can also be provided that the spring element 13 is connected to the sealing strip 9, for example by gluing or by scorching.

The spring element 13 may consist of several individual parts which are connected to each other in a suitable manner, for. As by vulcanization, by bonding, by welding or soldering, etc. It may consist of metallic or non-metallic material or a combination of such materials. As a metallic material, for example, spring steel or sintered material in question. The spring element 13 may have a coating or casing with sealing material. Also conceivable is a spring element 13 made of an elastic plastic, such as a silicone elastomer.

The spring element 13 can be manufactured as a continuous profile, are cut off from the pieces with the width b of the sealing strip 9 and the groove bottom.

The spring element 13 can be produced using known manufacturing methods and brought into its desired shape, for example by primary molding (casting), by chipless forming, by machining and by other methods such as bonding, coating, fusing, etc. LIST OF REFERENCE NUMBERS

1 device

2 camshaft

3 inner rotor

3a wing

3b hub part

4 outer rotor

5 first side wall

6 second side wall

7 hydraulic chamber

7a recess

7b cheek

8 groove

8a wing groove

9 sealing strip

10 first pressure chamber

11 second pressure chamber

12 groove base

12a wing groove ground

13 spring element

13a leaf spring element

14 sealing edge or surface

15 sealing edge or surface

16 radially inner end face

17 first side surface

18 second side surface

19 axis of rotation

20 drive wheel

21 central screw

24 storage area

25 locking mechanism

26 locking piston 7 spring 8 recording

29 recess

100 internal combustion engine

101 crankshaft

102 pistons

103 cylinders

104 traction drive

105 traction drive

106 intake camshaft

107 exhaust camshaft

108 cams

109 cams

110 inlet gas exchange valve

111 outlet gas exchange valve

a axial direction b width of the sash or groove base b _G groove base width b _F groove width

Claims

claims

1. Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with,

- An inner rotor (3) and an outer rotor (4), wherein one of the components rotatably connected to the camshaft (2) and the other component is in driving connection with a crankshaft,

- wherein the outer rotor (4) is rotatably mounted on the inner rotor (3) and - on the outer rotor (4) at least one by side walls (5, 6) and the inner rotor (3) limited hydraulic chamber (7) is formed,

- wherein the inner rotor (3) has a hub part (3b) and at least one wing. (3a),

wherein a wing (3a) of the inner rotor (3) extends into each hydraulic chamber (7) and divides these into two pressure chambers (10, 11) acting against each other,

- Wherein on one of the other component facing surface of the inner rotor (3) or the outer rotor (4) is formed a groove (8),

- In which a sealing strip (9) is arranged and between a groove bottom (12) of the groove (8) and the sealing strip (9) a spring element (13) is arranged, which the sealing strip (9) in the direction of an opposite surface of the other component, characterized in that

- The spring element (13) is simultaneously designed as a sealing element and a flow of hydraulic fluid from one side surface (17) of the sealing strip (9) on the groove base (12) to the other side surface (18) of the sealing strip (9) at least largely prevented.

2. Device according to claim 1, characterized in that the wing (3a) is formed integrally with the hub part (3b), that the groove (8) on a radially outer region of the wing (9a) is formed and that the sealing strip (9) and the spring element (13) in this groove (8) are arranged.

3. Device according to claim 1, characterized in that the groove (8) on a bearing surface (24) of the outer rotor (4), via which the outer rotor (4) is mounted on the inner rotor (3) is formed, and the sealing strip ( 9) and the spring element (13) in this groove (8) are arranged.

4. The device according to claim 1, characterized in that the spring element (13) has at least two sealing edges or surfaces (14, 15) sealingly on the radially inner end face (16) of the sealing strip (9) and on the groove base (12) issue.

5. The device according to claim 1, characterized in that the spring element (13) with at least one sealing edge or surface (14, 15), preferably with two sealing edges or surfaces (14, 15), flat on a radially inner end face (16 ) of the sealing strip (9) and / or on the groove base (12).

6. The device according to claim 1, characterized in that the spring element (13) fixed to the radially inner end face (16) of the sealing strip (9) is arranged.

7. The device according to claim 1, characterized in that the spring element (13) consists of metal.

8. The device according to claim 1, characterized in that the spring element (13) consists of plastic.

9. Apparatus according to claim 8, characterized in that the plastic is a silicone elastomer.

10.Vorrichtung according to claim 7, characterized in that the metal is at least partially coated with a coating material or coated by this.

11.Vorrichtung according to claim 10, characterized in that the coating material is an elastomer.