Hydraulic device comprising a sealing element

Abstract

A hydraulic device for an internal combustion engine or a gearing system, the hydraulic device including a housing featuring a chamber wall structure which delineates a pressure chamber for a pressurised hydraulic fluid; an actuating member which can be adjusted in the housing relative to the chamber wall structure in an actuating direction and in an actuating counter direction opposite to the actuating direction in order to adjust the delivery volume or phase position; and a sealing element including a sealing structure and a spring structure which is supported or moulded on one of the chamber wall structure and the actuating member, preferably the actuating member, and presses the sealing structure into sealing contact with the other of the chamber wall structure and the actuating member with a spring force in order to seal off the pressure chamber. The sealing structure and the spring structure are moulded in one piece.

Claims

1. A sealing element comprising: (1) a sealing structure which exhibits a maximum extension in a longitudinal direction and comprises: a front side which extends in the longitudinal direction and comprises a sealing surface which forms a seal; and a rear side which extends in the longitudinal direction and faces oppositely away from the front side; and (2) a spring structure on the rear side of the sealing structure; (3) wherein the spring structure is spring-deflectable in a direction of the rear side of the sealing structure, and (4) wherein the sealing structure and the spring structure are moulded in one piece; (5) wherein the spring structure comprises a spring portion which extends at a distance from the rear side of the sealing structure and overlaps with the sealing structure in the longitudinal direction from a first end of the spring structure to a second end of the spring structure and protrudes from the sealing structure at the first and second end; (6) wherein the spring structure alone or together with the sealing structure encompasses a free space into which the spring structure is spring-deflectable; and (7) wherein the spring structure is shaped as a flat bracket and in a central region between root regions, the spring structure comprises a local supporting region which is curved outwards away from the sealing structure in a form of a bulge, the spring structure having a radius of curvature which in the central region changes with respect to the sealing structure from negative to positive and back to negative thereby forming the bulge.

2. The sealing element according to claim 1, wherein the sealing structure and the spring structure are moulded generatively or in a casting method from plastic.

3. The sealing element according to claim 1, wherein the sealing structure and the spring structure consist of plastic, wherein the plastic contains one or more additives configured to improve a sliding characteristic of the plastic.

4. The sealing element according to claim 1, wherein the sealing structure is a beam-shaped or rod- shaped sealing strip and/or a sealing strip which is resistant to bending in a spring plane of the spring structure.

5. The sealing element according to claim 1, wherein the sealing structure has a solid profile which extends in the longitudinal direction or a hollow profile which is circumferentially closed.

6. The sealing element according to claim 1, wherein the spring structure is bent elastically, in the direction of the rear side of the sealing structure in a spring surface which extends in the longitudinal direction and follows a profile of the sealing structure.

7. The sealing element according to claim 1, (i) wherein the spring structure has a spring constant of at least 2 N/mm; and (ii) wherein the spring structure has a spring constant of at most 6 N/mm.

8. The sealing element according to claim 1, wherein the spring structure is configured to elastically deform in a spring plane by shifting a straight line in the longitudinal direction of the sealing structure in parallel, and wherein the spring portion extends at a distance from the rear side of the sealing structure and overlaps with the sealing structure in a spring surface.

9. The sealing element according to claim 1, wherein in a region of the spring structure the sealing element comprises a cavity and/or passage and/or is narrower than the sealing structure in an actuating direction throughout the sealing element.

10. The sealing element according to claim 1, wherein the sealing structure and the spring structure consist of a thermoplastic and/or thermosetting material, wherein the material contains reinforcing particles and/or a sliding additive configured to improve a sliding characteristic of the material.

11. A hydraulic device for an internal combustion engine or a gearing system, namely a hydraulic pump exhibiting an adjustable delivery volume, or a hydraulic cam shaft phase setter for adjusting a phase position of a cam shaft relative to a crankshaft of an internal combustion engine, the hydraulic device comprising: (a) a housing including a chamber wall structure which delineates a pressure chamber for a pressurised hydraulic fluid; (b) an actuating member which is configured to adjust in the housing relative to the chamber wall structure in an actuating direction and in an actuating counter direction which is opposite to the actuating direction so as to adjust the delivery volume or phase position; (c) and a sealing element according to claim 1, wherein the spring structure is supported or moulded on one of the chamber wall structure and the actuating member and presses the sealing structure into a sealing contact with a remaining one of the chamber wall structure and the actuating member with a spring force so as to seal off the pressure chamber.

12. The hydraulic device according to claim 11, wherein the front side of the sealing structure is situated in the sealing contact, and the sealing structure and the spring structure extend from the front side of the sealing structure to the rear side of the sealing structure in a spring plane in which the spring structure is configured to elastically deform and which extends through the sealing contact and the rear side of the sealing structure.

13. The hydraulic device according to claim 11, wherein the spring structure is configured to elastically deform in a spring plane extending transverse to the actuating direction so as to generate the spring force.

14. The hydraulic device according to claim 11, wherein the spring structure is configured to elastically deform so as to be subjected to a spring biasing force which presses the sealing structure into the sealing contact in all positions which the actuating member assumes relative to the chamber wall structure when the hydraulic device is in operation.

15. The hydraulic device according to claim 11, wherein the rear side of the sealing structure is in fluid communication with the pressure chamber, such that the hydraulic fluid is applied to the rear side of the sealing structure in a direction of the sealing contact.

16. The hydraulic device according to claim 11, wherein the sealing element is arranged in a cavity of one of the chamber wall structure and the actuating member, and the cavity comprises side walls which face each other in the actuating direction and guide the sealing structure such that the sealing structure is moved in a direction of the sealing contact.

17. The hydraulic device according claim 11, wherein the sealing element is arranged in a cavity of one of the chamber wall structure and the actuating member, and the front side of the sealing structure comprises a sealing surface which is in the sealing contact with the chamber wall structure, and the rear side of the sealing structure locally comprises a supporting region via which the sealing element is supported in the cavity by a pressure contact.

18. The hydraulic device according to claim 11, wherein: the hydraulic device further comprises a rotor which rotates about a rotational axis; the actuating member surrounds the rotor or forms the rotor and comprises a circumference which extends around the rotational axis and lies opposite the chamber wall structure in a region of a sealing gap; and the sealing gap and the sealing element extend in a direction which comprises an axial directional component which is parallel to the rotational axis.

19. A sealing element comprising: (1) a sealing structure which exhibits a maximum extension in a longitudinal direction and comprises: a front side which extends in the longitudinal direction and comprises a sealing surface which forms a seal; and a rear side which extends in the longitudinal direction and faces oppositely away from the front side; and (2) a spring structure on the rear side of the sealing structure; (3) wherein the spring structure is spring-deflectable in a direction of the rear side of the sealing structure, and (4) wherein the sealing structure and the spring structure are moulded in one piece; (5) wherein the spring structure comprises a spring portion which extends at a distance from the rear side of the sealing structure and overlaps with the sealing structure in the longitudinal direction from a first end of the spring structure to a second end of the spring structure and protrudes from the sealing structure at the first and second end; (6) wherein the spring structure alone or together with the sealing structure encompasses a free space into which the spring structure is spring-deflectable; and (7) wherein the spring structure extends along a respective sealing structure from a first root region of the spring structure to a second root region of the spring structure as an arc which axially undulates a plurality of times providing supports, each in a form of a portion which is bulged away from the sealing structure.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention is described below on the basis of example embodiments. Features disclosed by the example embodiments, each individually and in any combination of features which are not mutually exclusive, advantageously develop the subject-matter of the claims and aspects and also the embodiments described prior to the aspects. There is shown:

(2) FIG. 1 a hydraulic pump comprising sealing elements, in a view onto an end-facing side;

(3) FIG. 2 an exploded representation of components of the hydraulic pump;

(4) FIG. 3 a view onto a sectional plane of the hydraulic pump;

(5) FIG. 4 an exploded representation of components of a cam shaft phase setter provided with sealing elements;

(6) FIG. 5 an isometric representation of a stator-rotor arrangement of the cam shaft phase setter;

(7) FIG. 6 a longitudinal section of the cam shaft phase setter;

(8) FIG. 7 a sealing element of a first example embodiment;

(9) FIG. 8 a sealing element of a second example embodiment;

(10) FIG. 9 a sealing element of a third example embodiment;

(11) FIG. 10 a sealing element of a fourth example embodiment;

(12) FIG. 11 a sealing element of a fifth example embodiment;

(13) FIG. 12 a sealing element of a sixth example embodiment;

(14) FIG. 13 a sealing element of a seventh example embodiment;

(15) FIG. 14 a sealing element of an eighth example embodiment;

(16) FIG. 15 a sealing element of a ninth example embodiment;

(17) FIG. 16 a sealing element of a tenth example embodiment; and

DETAILED DESCRIPTION OF THE INVENTION

(18) FIG. 1 shows a hydraulic rotary pump, which is embodied by way of example as a vane cell pump, in a perspective view onto an end-facing side of the pump. The pump comprises a housing 1. A housing cover has been removed, such that the functional components of the pump which are accommodated by the housing 1 can be seen. A delivery chamber 2 is formed in the housing 1, wherein a delivery rotor 3 is arranged in the delivery chamber 2 such that it can be rotated about a rotational axis R. The delivery chamber 2 comprises a low-pressure side and a high-pressure side. When the delivery rotor 3 is rotary-driven in the rotational direction indicated, i.e. anti-clockwise, a hydraulic fluid—for example, a lubricating oil or working oil—flows into the delivery chamber 2 via an inlet channel on the low-pressure side of the pump and through an inlet I and is expelled from the delivery chamber 2 at an increased pressure on the high-pressure side through an outlet O and discharged via an adjoining outlet channel, for example as a lubricating oil to lubricating points of an internal combustion engine and/or gearing system or as a working oil to a subsequent hydraulic device.

(19) The delivery rotor 3 is a vane wheel comprising vanes 4 which are arranged in a distribution around the rotational axis R. The outer circumference of the delivery rotor 3 is surrounded by an actuating member 5. When the delivery rotor 3 is rotary-driven, the vanes 4 slide over an inner circumferential surface of the actuating member 5. The vanes 4 are supported radially inwards on a supporting ring 9 which is arranged such that it can be moved. The actuating member 5 is annular, but can in principle also deviate more significantly than in the example embodiment from a uniformly annular shape. The rotational axis R is arranged eccentrically with respect to a parallel central axis of the actuating member 5, such that the delivery rotor 3 and the actuating member 5 form delivery cells which increase in size in the rotational direction on the low-pressure side of the delivery chamber 2 and decrease again in size on the high-pressure side. Due to this increase and decrease in the size of the delivery cells which is periodic with the rotational speed of the delivery rotor 3, the hydraulic fluid is suctioned through the inlet I on the low-pressure side and expelled at an increased pressure through the outlet O on the high-pressure side and discharged.

(20) The volume of fluid which is delivered per revolution of the delivery rotor 3, the so-called specific delivery volume, can be adjusted. The specific delivery volume depends on the eccentricity, i.e. the distance between the central axis of the actuating member 5 and the rotational axis R of the delivery rotor 3. In order to be able to change this axial distance, the actuating member 5 is arranged such that it can be adjusted back and forth in the housing 1 relative to the delivery rotor 3 in an actuating direction S and in an actuating counter direction which is opposite to the actuating direction S. In the example embodiment, the actuating member 5 can be adjusted linearly. In other embodiments, it can be able to be pivoted, as is for example known from DE 10 2011 086 175 B3. In yet other alternative embodiments, the respective actuating member can in principle be mounted such that its actuating movement is a superimposed movement consisting of a translation and a rotation. The ability of the actuating member 5 to be moved and/or adjusted is at any rate such that the actuating movement can adjust the eccentricity between the delivery rotor 3 and the actuating member 5 and therefore the delivery volume. This applies not only to vane cell pumps but also to other internal-axle pumps such as for example toothed ring pumps and pendulum-slider pumps.

(21) For adjusting in the actuating direction S, a pressure of the delivered hydraulic fluid which acts in the actuating direction S is applied to the actuating member 5. The restoring force of a spring 6 acts counter to this pressure. The restoring force acts in the actuating counter direction. In the example embodiment, the restoring force is generated by a single spring 6. In alternative embodiments, the restoring force can also be generated by the combined action of two or more springs and, in other alternatives, by a gas pressure device. The restoring force is expediently a spring force. Irrespective of whether it is generated mechanically and/or by gas pressure, the spring force expediently acts in the direction of increasing the delivery volume.

(22) In order to generate the hydraulic actuating force which acts in the actuating direction S, a pressure chamber K1 is formed on a rear side of the actuating member 5 which faces oppositely away from the spring 6. The pressure chamber K1 is delineated on the radially outer side in relation to the rotational axis R by the housing 1 and on the radially inner side by the actuating member 5. The pressure chamber K1 comprises an inlet 10 through which hydraulic fluid delivered by the pump can flow into the pressure chamber K1 and also flow off out of the pressure chamber K1 again in order to relieve the pressure on the actuating member 5. The inlet 10 can be connected directly to the high-pressure side of the delivery chamber 2. It is alternatively also possible to not connect the inlet/outlet 10 to the high-pressure side of the pump until a point downstream of the delivery chamber 2 and/or outlet O, expediently via a connecting channel which also extends within the housing 1.

(23) The outer circumference of the actuating member 5 and oppositely facing chamber wall structures 1a form narrow sliding gaps which extend in the actuating direction S, namely a left-hand sliding gap and a right-hand sliding gap, in order to seal off the pressure chamber K1. The actuating member 5 and an end-facing wall of the housing 1, and the actuating member 5 and an end-facing wall of the removed housing cover, also form axial sliding gaps for sealing off the pressure chamber K1. The chamber wall structures 1a are constituent parts of the housing 1. In modifications, the chamber wall structures can however also be formed by wall structures which are produced separately from the housing 1 and arranged in the housing 1, as long as it can be ensured that the pressure chamber K1 has a sufficient strength of seal.

(24) In order to improve the seal, sealing elements 20 are arranged in the region of the sliding gaps formed by the actuating member 5 and the chamber wall structures 1a, for example one sealing element 20 for each respective gap. The outer circumference of the actuating member 5 comprises cavities 7. One of the sealing elements 20 is respectively arranged in each one of the cavities 7. The respective sealing element 20 is supported on a base of the accommodating cavity 7 and is guided by the side walls of the cavity 7 such that it can slide in the direction of a sealing contact with the opposing chamber wall structure 1a and in the opposite direction. The breadth of the respective cavity 7, as measured in the actuating direction S, and the breadth of the sealing element 20 accommodated in said cavity, as measured in the actuating direction S, are mutually adjusted such that the sealing element 20 cannot perform any practically significant movements within its cavity 7 relative to the actuating member 5 in and counter to the actuating direction S. Because it is enclosed by the side walls, the sealing element 20 also in particular cannot tilt and/or twist. The side walls and/or the guide on both sides provided by the side walls ensures that the accommodated sealing element 20 always has a perfect sealing contact with the opposing chamber wall structure 1a and that the sealing contact remains intact even during rapid and direction-changing movements of the actuating member 5.

(25) The cavities 7 which accommodate the sealing elements 20 for sealing off the pressure chamber K1 are each in fluid communication with the pressure chamber K1 via a connecting channel 8. The hydraulic fluid from the pressure chamber K1 is applied via the respective connecting channel 8 to a rear side of the respective sealing element 20 which faces away from the opposing chamber wall structure 1a, and the sealing element 20 is thus pressed hydraulically into the sliding contact.

(26) Another pressure chamber K2 is formed opposite the pressure chamber K1 across the rotational axis R, between an outer circumference of the actuating member 5 and an opposing inner circumference of the housing 1. The spring 6 is arranged in the pressure chamber K2. The hydraulic fluid delivered by the pump can also be introduced into the pressure chamber K2. For this purpose, the pressure chamber K2 comprises an inlet 10 of its own which simultaneously also forms the outlet of the pressure chamber K2. By introducing the pressure fluid into the pressure chamber K2, it is possible to hydraulically block the actuating member 5 in a desired actuating position and relieve the spring 6. Said other pressure chamber K2 can in principle be omitted, such that the spring 6 only acts counter to the pressure prevailing in the pressure chamber K1. In embodiments, such as the example embodiment, in which a first pressure chamber—for example, the pressure chamber K1—is provided on the circumference of the actuating member 5, and a second pressure chamber—for example, the pressure chamber K2—is provided so as to act counter to the first pressure chamber, then it is also possible to completely omit a spring, since the actuating member can be moved purely hydraulically into any actuating position and hydraulically blocked in said actuating position by appropriately applying pressure to the two pressure chambers K1, K2.

(27) The pressure chamber K2 is sealed off in the same way as the pressure chamber K1. In order to seal off the pressure chamber, the outer circumference of the actuating member 5 and opposing chamber wall structures 1 a form other sliding gaps—in the example embodiment, a left-hand and right-hand sliding gap. In order to improve the seal, other sealing elements 20 are arranged in the sliding gaps—in the example embodiment, one sealing element 20 for each respective sliding gap. The statements made with respect to the sliding gaps, the sealing elements 20, the sealing gaps thus formed and the cavities 7 within the context of the pressure chamber K1 similarly apply to the sliding gaps, the sealing elements 20, the sealing gaps thus formed and the cavities 7 for the pressure chamber K2, wherein the cavities 7 assigned to the pressure chamber K2 are in fluid communication with the pressure chamber K2 via connecting channels 8 for applying a hydraulic force to the sealing elements 20.

(28) FIG. 2 shows the functional components of the hydraulic pump which have already been described, in an exploded representation, i.e. in positions removed from each other. The components can be pushed into or onto each other from the positions shown by being shifted parallel to the rotational axis R, thus enabling the pump to be assembled. FIG. 2 also shows the housing cover 1b which closes off the housing 1 and therefore the delivery chamber 2 and the pressure chambers K1 and K2 on one of the two end-facing sides. The housing 1 and the housing cover 1b can also be jointly referred to as the “housing”.

(29) The sealing elements 20 can be axially inserted into the cavities 7 or can also in principle instead be introduced radially into the cavities 7. When fitted in series production, the actuating member 5 is inserted into the housing 1 which is open on its end-facing side which faces the housing cover 1b. Advantageously, the sealing elements 20 are only then axially inserted into the cavities 7. If the sealing elements 20 are axially inserted into the cavities 7 of the actuating member 5 or introduced radially from without into the radially open cavities 7 before the actuating member 5 is inserted, which is in principle possible, then the sealing elements have to be held in the cavities 7 as the actuating member 5 is fitted.

(30) FIG. 3 shows the hydraulic pump, with the housing cover 1b (FIG. 2) removed, in a perspective view onto a longitudinal sectional plane which extends through two sealing elements 20. The sealing elements 20 respectively comprise structural regions having different functions. The structural regions are a sealing structural region 21, which is referred to in the following as the sealing structure, and a spring structural region 24 which is referred to in the following as the spring structure. The sealing structure 21 of the respective sealing element 20 is in sealing contact with the opposing chamber wall structure 1a. The spring structure 24 is supported on the actuating member 5 opposite the chamber wall structure 1a—in the example embodiment, on the base of the accommodating cavity 7—and presses the sealing structure 21 into the sealing contact with a spring force.

(31) The sealing elements 20 are elongated in a longitudinal direction L. The respective sealing structure 21 is a sealing strip which extends in the longitudinal direction L. The cavities 7 are axially linear. In the example embodiment, they extend parallel to the rotational axis R. In modifications, they could also extend obliquely with respect to the rotational axis R, i.e. they could cross the rotational axis R at a distance. In other modifications, the cavities could describe a simple arc or have an undulating profile on the outer circumference of the actuating member 5 in a plan view onto the outer circumference. The sealing structures 21 are linear in the longitudinal direction L in accordance with the profile of the cavities 7. In the modifications mentioned, they could also describe a simple arc or exhibit an undulating profile in a plan view onto the outer circumference of the actuating member 5. However, linear cavities 7 and sealing elements 20 which are correspondingly linear in the longitudinal direction L make it easier to fit them, since the sealing elements 20 can be inserted into the cavities 7 in the longitudinal direction L, for example parallel to the rotational axis R, from the end-facing side.

(32) The spring force generated by spring-deflecting the spring structure 24 is introduced into the sealing structure 21 in the direction of the sealing contact on the rear side of the sealing structure 21 of the respective sealing element 20 which faces oppositely away from the sealing contact. The spring force is generated by elastically deforming the respective spring structure 24 in a spring plane which extends in the longitudinal direction L of the respective sealing element 20. If the sealing elements 20 were arc-shaped or undulating in a plan view onto the outer circumference of the actuating member 5, the respective spring structure 24 would be elastically deformed in a correspondingly arc-shaped or undulating spring surface.

(33) The sealing elements 20 are each arranged so as to exhibit a spring biasing force. The spring biasing force is set such that the respective sealing structure 21 is pressed into the sealing contact with a certain spring force, i.e. a spring force other than zero, in all actuating positions which the actuating member 5 can assume. This can compensate for a variation in the width of the respective sliding gap. In advantageous embodiments, the spring biasing force is large enough that the spring structure 24 presses the sealing structure 21 of the same sealing element 20 into the sealing contact with the opposing chamber wall structure 1 a in all operational states of the pump. This compensates for differences in the thermal expansions of the components forming the respective sliding gap, specifically the actuating member 5 and the chamber wall structures 1a. In yet another improvement, the spring biasing force is large enough that variations in the gap width, which can occur during the actuating movement and/or due to changes in temperature, are compensated for by the spring biasing force over the planned service life of the pump. It is also advantageous if a spring bias which is established even as the sealing element 20 is fitted, and a spring biasing force which is thus generated, also compensate for a relaxation of the material of the respective sealing element 20 which sets in over its operating time.

(34) The cavities 7 extend axially and continuously parallel to the rotational axis R, i.e. they are open at their two end-facing sides. In advantageous embodiments, the sealing structures 21 extend over the entire axial length of the respective cavity 7, such that they also form sealing gaps with the end-facing surfaces of the housing 1 and housing cover 1b which face axially opposite.

(35) FIGS. 4 to 6 show a second example embodiment of a hydraulic device. The hydraulic device of the second example embodiment is a cam shaft phase setter for adjusting the phase position of a cam shaft of an internal combustion engine relative to a crankshaft of the internal combustion engine.

(36) FIG. 4 shows an exploded representation of the cam shaft phase setter. The cam shaft phase setter is formed as a hydraulic swing-vane motor. The cam shaft phase setter comprises an actuating member 15 and a housing 11 which surrounds the actuating member 15. The housing 11 is closed off at one end-facing side by a housing cover 13 and at the opposing end-facing side by a housing cover 14. The actuating member 15 can be rotated back and forth in the housing arrangement 11, 13 and 14 about a rotational axis R within a certain rotational angular range and thus adjusted relative to the housing 11 and the housing covers 13 and 14 which are connected immovably to the housing 11. The housing or housing part 11 together with the housing covers 13 and 14 can also be referred to as the “housing” within the meaning of the invention.

(37) When fitted on an internal combustion engine, the actuating member 15 is coupled to a cam shaft in a way which transmits torque. The cam shaft phase setter can in particular be arranged on an axial end of the cam shaft, and the actuating member 15 can be non-rotationally connected to the cam shaft. The housing arrangement 11, 13 and 14 is coupled to a crankshaft of the internal combustion engine in a way which transmits torque. The housing arrangement 11, 13 and 14 is coupled to the crankshaft in a way which is speed-resistant, i.e. invariant in terms of its rotational speed. The coupling can be formed as a toothed belt drive or chain drive or, as in the example embodiment, as a toothed wheel coupling. In the example embodiment, the housing cover 13 is provided with a drive wheel—in the example, a toothed wheel. In modifications, the drive wheel can instead also be provided on the outer circumference of the housing 11 or on the other housing cover 14. The housing 11 which is or can be coupled to the crankshaft in a way which is speed-resistant is usually referred to as the “stator”, and the actuating member 15 which is or can be coupled to the cam shaft in a way which is speed-resistant is usually referred to as the “rotor”.

(38) FIG. 5 shows a perspective view of the arrangement consisting of the housing 11 and the actuating member 15, without the housing covers 13 and 14. The housing 11 forms an outer ring from which multiple jaws 12 protrude radially inwards. The actuating member 15 comprises a ring from which vanes 16 protrude radially outwards in the direction of an inner circumference of the housing 11. Each of the vanes 16 respectively protrudes radially between two adjacent jaws 12, such that the angular distances between the adjacent jaws 12 determine the maximum actuating path for the relative rotational adjustment of the actuating member 15. In FIG. 5, the actuating member 15 has assumed a rotational end position relative to the housing 11, from which it can be hydraulically adjusted in the actuating direction S, for example clockwise. The actuating member 15 can be hydraulically adjusted, selectively in the actuating direction S or in the actuating counter direction which is opposite to the actuating direction S. The two rotational end positions are predetermined by an abutting contact between at least one of the vanes 16 and one of the jaws 12.

(39) In the circumferential direction, a pressure chamber K1 in the form of a leading chamber is formed between each of the vanes 16 and the next jaw 12 in the actuating counter direction, and another pressure chamber K2 in the form of a trailing chamber is formed with the respectively next jaw 12 in the actuating direction S. If the leading chambers K1 are pressurised using a hydraulic fluid, and the trailing chambers K2 are relieved of pressure, the actuating member 15 is adjusted in the actuating direction S, i.e. adjusted to lead, relative to the housing 11. If the trailing chambers K2 are pressurised using the hydraulic fluid, and the leading chambers K1 are relieved of pressure, the actuating member 15 is adjusted in the actuating counter direction.

(40) The pressure chambers K1 and K2 each comprise an inlet 18 for the hydraulic fluid. Only the inlets 18 of the pressure chambers K2 can be seen in FIG. 5. The pressure chambers K1 comprise inlets 18 of the same type, which are hidden in FIG. 5 by the jaws 12, i.e. they emerge at a point below the jaws 12. The inlet 18 also simultaneously forms the outlet of the respective pressure chamber K1 and K2. In the example embodiment, a connecting channel extends at least substantially radially through the ring of the actuating member 15, starting from the respective inlet/outlet 18. The connecting channels emerge at an inner circumferential surface of the actuating member 15. The cam shaft phase setter includes a control valve which is arranged centrally in the actuating member 15, in order to selectively supply either the leading chambers K1 or the trailing chambers K2 with the hydraulic fluid, and to relieve the respectively other type of chamber of pressure, in accordance with control signals from an engine controller of the internal combustion engine. It is also selectively possible to close both groups of chambers K1 and K2 in order to hydraulically block the actuating member 15 in an intermediate position. Controlling a phase setter by means of a control valve, which can also be implemented in the phase setter of the invention, may be gathered for example from EP 2 365 193 B1.

(41) In the end position assumed in FIG. 5, the actuating member 15 is locked relative to the housing 11. A torsionally stressed spring which can be seen in FIG. 6 rotates the actuating member 15 into the end position assumed in FIG. 5, when the pressure of the hydraulic fluid falls below a minimum pressure. In most practical applications, such as for example in motor vehicles, the actuating member 15 assumes this end position when the internal combustion engine is idling and in particular when it is not running. The lock is ensured by a locking pin 19 to which a spring force is applied in an axial direction and which latches into a depression in one of the two housing covers 13 and 14—in the example embodiment, the housing cover 13—which lies axially opposite in the end position, due to the effect of the spring force, when the end position is reached. Once the internal combustion engine has been started and a sufficient hydraulic pressure built up, and the hydraulic fluid is applied to the pressure chambers K1, the lock is released.

(42) FIG. 6 shows a longitudinal section of the assembled cam shaft phase setter, likewise without the central control valve.

(43) The pressure chambers K1 and K2 are sealed off at the end-facing sides of the actuating member 15, each in an axial sliding gap formed by the actuating member 15 and the respective housing cover 13 and 14. In order to radially seal off the pressure chambers K1 and K2, the housing 11 and the actuating member 15 form radial sliding gaps on the inner circumference of the jaws 12 and the outer circumference of the vanes 16. In order to improve the strength of seal, a sealing element 50 is arranged on the outer circumference of each vane 16. The sealing elements 50 and the radially opposing chamber wall structure 11a of the housing 11 respectively form a sealing gap. The chamber wall structures 11 a extend as annular segments between respectively adjacent jaws 12 of the housing 11. The sealing gaps formed by the sealing elements 50 seal the two pressure chambers K1 and K2, situated between adjacent jaws 12, from each other and thus ensure an improved fluidic separation between said adjacent chambers K1 and K2.

(44) In the example embodiment, sealing elements are not provided on the inner circumferences of the jaws 12. In further developments, a sealing element—in particular, a sealing element of the type in accordance with the invention—can likewise be arranged on the inner circumference of each of the jaws 12 and form a sealing gap with the oppositely facing outer circumference of the actuating member 15. In such developments, the circumferential portions of the actuating member 15 which are situated between adjacent vanes 16 would form chamber wall structures within the meaning of the invention.

(45) The sealing elements 50 are arranged in cavities 17. Each of the vanes 16 comprises a cavity 17 on its outer circumference. The cavities 17 each extend axially and continuously from one end-facing side of the actuating member 15 to the other end-facing side. The sealing elements 50 each press into the sealing contact with a spring force. The respective sealing element 50 is supported in its accommodating cavity 17, such that the spring force can be applied, and guided on the side walls of the cavity 17, which are mutually opposing in the circumferential direction, in the direction of the sealing contact and in the opposite direction.

(46) In a comparable way to the sealing elements 20 of the hydraulic pump, the sealing elements 50 each comprise a sealing structure 51 and a spring structure 54 which are moulded in one piece. On a front side of the sealing element 50, the sealing structure 51 comprises a sealing surface via which the sealing element 50 is in sealing contact with the opposing chamber wall structure 11a of the housing 11. How the sealing elements 50 are arranged and operate can readily be seen from an overview of FIGS. 5 and 6. The spring structure 54 of the respective sealing element 50 is supported on the base of the accommodating cavity 17, and the sealing element 50 presses its sealing structure 51 into the sealing contact with a spring force. The sealing elements 50 are each installed with a spring biasing force.

(47) The statements made with respect to the sealing elements 20 and cavities 7 of the hydraulic pump apply to the sealing elements 50, the cavities 17, and how the sealing elements 50 are supported, guided and installed with a spring biasing force.

(48) Sealing elements are described below in different embodiments. Each of the sealing elements can substitute for the sealing elements 20 of the hydraulic pump and the sealing elements 50 of the cam shaft phase setter. Common to all the embodiments is that a sealing structure, which comprises a sealing surface for the sealing contact on a free front side of the respective sealing element, and a spring structure are moulded in one piece, and that the sealing element acts as a unit consisting of the sealing structure and the spring structure and can be handled and in particular fitted as a unit. The sealing elements are each designed to be installed in a cavity which can in particular correspond to the cavities 7 of the hydraulic pump or the cavities 17 of the cam shaft phase setter. The sealing elements are numbered consecutively in increments of ten. Structures and sub-structures having the same function are denoted by the same final digit, respectively. Thus, for example, the final digit “1” denotes the respective sealing structure, the final digit “2” denotes the sealing surface of the respective sealing structure, the final digit “3” denotes the guide, and the final digit “4” denotes the respective spring structure.

(49) FIG. 7 shows the sealing element 20, described using the example of the hydraulic pump, in three isometric representations.

(50) The sealing structure 21 is a slim sealing strip which extends in the longitudinal direction L. On a free front side, it comprises a sealing surface 22 for the sealing contact. The sealing surface 22 is planar. In modifications, it can however also be curved, in particular so as to conform to a sealing counter surface which may be curved. The sealing counter surface formed by the chamber wall structures 11a of the cam shaft phase setter is then for example curved concavely and, expediently, circularly in relation to the actuating member 15. For using the sealing element 20 in this way, the sealing surface 22 can be curved so as to conform to the sealing counter surface. A planar sealing surface 22 is advantageous with regard to production and in particular manufacturing costs. In modifications, the sealing surface 22 can be curved concavely inwards in relation to the sealing structure 21, i.e. in relation to the opposing sealing counter surface. A sealing surface 22 which is curved concavely in relation to the sealing counter surface, or a sealing surface 22 which is planar even though the sealing counter surface is concave, has only a linear contact, or a contact in one or two or even more narrow parallel strips, with the sealing counter surface. A linear contact or a contact in only one or more narrow strips can be set more precisely, as viewed over the entire length, than a sealing contact over a relatively larger area. In the running-in phase, the sliding partners—specifically, the sealing element 50 and the chamber wall structure 11a which co-operates with it; in the first example embodiment, the sealing element 20 and the chamber wall structure 1a—rub against each other until they conform, such that the surface of the sealing contact is increased but a defined sealing contact is still maintained or, if the sealing contact is over an area from the outset, is further improved.

(51) The sealing structure 21 is beam-shaped. Its longitudinal sides comprise parallel lateral surfaces which form guides 23 for guiding in the accommodating cavity, for example one of the cavities 7 or 17. The guides 23 serve to guide the sealing structure 21 in the direction of the sealing contact and in the opposite direction. As already described, the accommodating cavity 7 or 17 comprises corresponding guiding counter surfaces in the form of its side walls.

(52) The sealing structure 21 is resistant to deformation, in particular bending deformation, along its length as measured in the longitudinal direction L, in relation to the forces which act on it during operation, such that a uniform sealing contact is ensured over its entire length during operation.

(53) On a rear side of the sealing structure 21, the spring structure 24 projects from the sealing structure 21 in a root region near each of the two axial ends and extends in the longitudinal direction L starting from the left-hand and left-hand root region. The spring structure 24 is shaped as a flat bracket or arc which extends from one axial end of the sealing structure 21 to the other axial end and is only connected to the sealing structure 21 near the axial ends of the sealing structure 21. The spring structure 24 is clear of the sealing structure 21 between the root regions which are short in comparison with the length of the sealing structure 21. The length of the clear region between the root regions is advantageously at least 50% or at least 70% or at least 80% of the axial length of the sealing structure 21.

(54) For a sealing element itself, for example the sealing element 20, the word “axial” describes a position in relation to the longitudinal direction L or an extension in the longitudinal direction L. In advantageous embodiments, such as for example the example embodiments illustrated, the longitudinal direction L of the respective sealing element, when installed, is parallel to the rotational axis of a component of the hydraulic device—the delivery rotor 3 in the first example embodiment, and the actuating member 15 in the second example embodiment. In the example embodiments, the sealing elements are linear in the longitudinal direction L. In modifications, they can however also deviate from a linear profile in the longitudinal direction L, in a plan view onto the respective sealing surface, and exhibit a curvature or sweep. The use of the term “longitudinal direction” does not itself restrict the respective sealing element to a linear profile, although a profile which is continuously linear in the longitudinal direction is advantageous.

(55) In a central region between the root regions, the spring structure 24 comprises a supporting region 25 which is curved concavely outwards away from the sealing structure 21 and via which the installed spring structure 24 is supported in the accommodating cavity 7 or 17. Instead of a supporting region 25 which is concave in relation to the sealing structure 21, the spring structure 24 can also comprise a cam or fin between the root regions which protrudes away from the sealing structure 21, in order to obtain a supporting region which is only local, i.e. shorter than the longitudinal extension of the spring structure 24. By providing the local supporting region 25 in the form of a bulge instead of a cam, fin or the like, it is advantageously possible to increase the spring path of the spring structure 24.

(56) In order to generate the spring force, the spring structure 24 can be elastically deformed in a spring surface which follows the profile of the sealing structure 21 in the longitudinal direction L and extends at least substantially orthogonally with respect to the sealing surface 22. The sealing structure 21 overlaps the spring surface completely in a plan view onto the sealing surface 22. In the example embodiment, it also overlaps the spring structure 24 completely in the plan view. Because the profile of the sealing structure 21 is linear in the longitudinal direction, the spring surface in which the spring structure 24 can be spring-deflected is a spring plane, i.e. the spring surface is planar.

(57) When installed, the spring structure 24 is primarily subjected to elastic bending stress, i.e. it acts as a flexible spring. The spring plane of the spring structure 24 extends in the longitudinal direction L of the sealing structure 21. In preferred embodiments, such as for example the example embodiments, the spring plane of the installed spring structure 24 extends orthogonally with respect to the actuating direction S of the respective actuating member, such as for example the actuating members 5 and 15 of the example embodiments. In principle, however, it would also be conceivable to position it obliquely with respect to the actuating direction S. In such modifications, the spring plane would however still extend parallel to the longitudinal extension of the accommodating cavity.

(58) For applications in which the hydraulic fluid is applied to the rear side of the sealing structure 21 which faces oppositely away from the sealing surface 22, whereby the sealing structure 21 is to be pressed into the sealing contact with hydraulic assistance or primarily hydraulically, such as is for example the case in the hydraulic pump of the example embodiment, the spring structure 24 is narrower than the accommodating cavity, at least in regions. In the case of the sealing element 20, the spring structure 24 is slightly narrower than the sealing structure 21—and therefore also slightly narrower than the accommodating cavity, for example the cavity 7—over its entire length. The reduced breadth can clearly be seen in FIG. 7 in the root regions of the spring structure 24 in the form of a recess on each of the two sides of the sealing element 20. Due to the reduced breadth, an increase in pressure is propagated quickly and uniformly on the rear side over the entire length of the sealing structure 21.

(59) The spring structure 24 is narrower than the sealing structure 21 over its entire length and over its height. In modifications, the spring structure 24 can also be recessed only in regions, in order to establish a fluid connection for the hydraulic fluid, for example in one or both root regions and/or in the supporting region 25 and/or in one or both spring portions which extend(s) in the longitudinal direction L between the supporting region 25 and one of the root regions, respectively. Instead of or in addition to one or more cavities, the fluid connection can also be provided by means of one or more passages which extend(s) through the spring structure 24.

(60) FIG. 8 shows a lateral view and three isometric representations of a sealing element 30 of a second example embodiment. The sealing element 30 comprises a sealing structure 31 and a spring structure 34 which are moulded in one piece. As in the first example embodiment, the spring structure 34 is shaped as a bracket or arc which extends from one root region at one end of the sealing structure 31 to a second root region at the other end of the sealing structure 31, as viewed in the longitudinal direction. Unlike the spring structure 24, the spring structure 34 is curved outwards away from the sealing structure 31, i.e. in a uniformly concave shape with respect to the sealing structure 31, between its root regions. The spring portion of the spring structure 34 which extends in the longitudinal direction is shaped as a simple arc. In the lateral view, the sealing element 30 is shaped like a flat “D”. The middle portion of the arc, which exhibits the maximum distance from the sealing structure 31, forms the supporting region 35 of the sealing element 30. Since the supporting region 35 is derived from the arc shape, a shaped supporting element—comparable to the supporting region 25 of the first example embodiment—can be omitted.

(61) In order to improve the spring characteristic of the spring structure 34, a clearance 37 in the form of a widening is provided for the arc portion at both axial ends, each in the root region.

(62) Another difference with respect to the first example embodiment is how the hydraulic fluid feed to the rear side of the sealing structure 31 is embodied. To provide the feed, a cavity 36 is formed in the root regions of the spring structure 34 on each of the two sides, such that a fluid connection for the hydraulic fluid is obtained at the axial ends of the sealing element 30, on each of the two sides. Instead of just one or more local cavities 36, the spring structure 34 can be narrower than the sealing structure 31 over its entire length and height, as in the first example embodiment. As already mentioned with respect to the sealing element 20, a fluid connection can also be established by means of a passage through the spring structure 34, for example one or more bores. One or more cavities can also be implemented together with one or more passages.

(63) Aside from the differences described, the statements with respect to the sealing element 20 of the first example embodiment apply similarly to the sealing element 30. Thus, as in the first example embodiment, the sides of the sealing structure 31 comprise parallel guides 33 which extend in the longitudinal direction, for linearly guiding in the direction of the sealing contact and in the opposite direction.

(64) FIG. 9 shows a lateral view and two isometric representations of a sealing element 40 of a third example embodiment. The sealing element 40 differs from the sealing element 20 of the first example embodiment only in that it comprises a moulded abutment 48 which is moulded on the rear side of the sealing structure 41 such that it protrudes in the direction of the spring structure 44. The abutment 48 is axially arranged in the region of the bulged support 45—in the example embodiment, below the point of maximum bulge. The abutment 48 is moulded on the sealing structure 41 as a protruding fin. The abutment 48 limits the spring path of the spring structure 44 in order to predetermine a maximum possible deformation of the spring structure 44. By limiting the deformation, it is advantageously possible to prevent the sealing element 40 from becoming damaged while being handled, in particular when fitted in series production. In one modification, an abutment which is comparable to the abutment 48 can be moulded on the spring structure 44, rather than the sealing structure 41, such that it protrudes in the direction of the sealing structure 41. Following the taxonomy of the other example embodiments, the sealing surface is denoted as 42, the lateral guide for the sealing structure 41 is denoted as 43, and the fluid connection—in this case, in the form of a recess—is denoted as 46.

(65) FIG. 10 shows three isometric representations of the sealing element 50, which has been described using the example of the cam shaft phase setter, as a fourth example embodiment. The sealing element 50 is derived from the sealing element 20 of the first example embodiment. Unlike the sealing element 20, it comprises: two supports 55, each in the form of a portion which is bulged concavely with respect to the sealing structure 51; a clearance 57, provided by a widening, in the spring structure 54 on each of the inner sides of the root regions; and an alternatively implemented hydraulic fluid feed 56. The feed 56 is formed by two troughed spring portions, each between one of the root regions and the nearest support 55. Another difference with respect to the first example embodiment is that an abutment 58 which is troughed convexly in relation to the sealing structure 51 is moulded between the supports 55. In a comparable way to the abutment 48 of the third example embodiment, the abutment 58 limits the maximum possible deformation of the spring structure 54 and therefore protects the sealing element 50 from becoming damaged due to deformation, in particular while the sealing element 50 is being fitted. The sealing surface is denoted as 52, and the lateral guides for the sealing structure 41 are denoted as 53. Aside from the differences described, the sealing element 50 corresponds to the sealing element 20 of the first example embodiment.

(66) FIG. 11 shows a lateral view and two isometric representations of a sealing element 60 of a fifth example embodiment. Whereas the spring structures of the previous example embodiments extend along the respective sealing structure from a first root region to a second root region as a closed arc, for example as a simple arc as in the case of the sealing element 30 or as an arc which axially undulates one or more times as in the case of the sealing elements 20, 40 and 50, the sealing element 60 comprises a spring structure 64 featuring two spring portions which are arced concavely with respect to the sealing structure 61, each denoted as 64. The spring portions 64 protrude towards each other in the longitudinal direction L, each starting from a root region which is a root region which is an outer root region in the longitudinal extension, and at a clear distance from the sealing structure 61. Accordingly, their free ends point towards each other in the longitudinal direction L. The two spring portions 64 can be elastically bent, independently of each other, in the spring plane which extends in the longitudinal direction L. When installed, however, they are simultaneously subjected to bending stress, i.e. they jointly generate the spring force which acts on the sealing structure 61, due to the geometric conditions at the point of installation and due to the spring bias which is advantageously provided. It should also be noted that a spring portion clearance in the root region of the respective spring portion 64 is denoted as 67. The sealing surface is denoted as 62, the lateral guides for the sealing structure 61 are denoted as 63, and the supporting region at the free end of each spring portion 64 is denoted as 65.

(67) The spring portions 64 can be elongated at each of their mutually opposing free ends by a portion which extends some way in the direction of the sealing structure 61. This can provide a defined abutment, for limiting the deformation, for each of the spring portions 64 in a comparable effect to the abutment 48 of the third example embodiment. Kinked ends, which are preferably bent roundly inwards towards the sealing structure 61, can in particular prevent the sealing element 60 from becoming hooked as it is being fitted. Limiting the deformation serves only to protect the sealing element from becoming unintentionally damaged as it is being fitted. An abutting function is implemented, as also elsewhere in all the other embodiments of the sealing element, such that an abutting contact is not made under the conditions which are to be expected during operation, but rather such that at least a minimum residual spring path always remains.

(68) FIG. 12 shows a lateral view and two isometric representations of a sealing element 70 of a sixth example embodiment. Like the sealing element 60 of the preceding example embodiment, the sealing element 70 comprises two spring portions 74 which can be elastically deformed independently of each other. The spring portions 74 protrude on the rear side of the sealing structure 71 in the longitudinal direction L of the sealing element 70, but away from each other and from a root region which is a middle root region in the longitudinal extension. In the lateral view, the sealing element 70 is shaped like a flat “K”. In order to improve the elastic bending characteristic of the spring portions 74, a clearance 77 is formed in the root region of the respective spring portion 74. The spring portions 74 spread outwards away from each other in the longitudinal direction L, forming a slightly concave curvature in the longitudinal direction L. The spring portions 74 could in principle also project in a uniformly oblique way or linearly in the lateral view. The sealing surface is denoted as 72, the lateral guide for the sealing structure 71 is denoted as 73, and the supporting region at the free end of each spring portion 74 is denoted as 75. The outer ends of the spring portions 74 can be elongated such that they kink inwards, preferably in a round bend, in order to limit the deformation at each of the two ends in a defined way.

(69) FIG. 13 shows a lateral view and two isometric representations of a sealing element 80 of a seventh example embodiment. The sealing element 80 substantially corresponds to the sealing element 30 of the second example embodiment. The spring structure 84 axially projects from an axial end region of the sealing structure 81 and describes an arc which is curved in a uniformly concave shape with respect to the sealing structure 81, starting from its root region, as in the second example embodiment. Unlike the second example embodiment, however, the arc comprises a free end which lies opposite the sealing structure 81 at a clear distance. A clearance 87 is again formed in the root region of the spring structure 84 in order to improve its spring characteristic. The sealing surface is denoted as 82, the lateral guides for the sealing structure 81 are denoted as 83, and the supporting region derived from the arc shape is denoted as 85. Due to its elongated concave shape, the spring structure 84 inherently forms an abutment at its free end, for protecting the sealing element from excessive deformation as it is being fitted.

(70) If hydraulic fluid for applying pressure is introduced in specially provided fluid connections, such as for example the fluid connections 8 of the first example embodiment (FIG. 1), advantageous embodiments of such fluid connections would be configured such that the hydraulic fluid can directly flow into and flow off out of the region between the sealing structures 21.

(71) One advantage of sealing elements comprising a freely protruding spring portion, such as the sealing elements 60, 70 and 80, is that tensile stresses are not introduced into the sealing structure when the sealing element is installed with a spring biasing force. The sealing structure of sealing elements comprising a freely protruding spring portion can be dimensioned to be slimmer than the sealing structure of sealing elements exhibiting a flow of force which is closed across the sealing structure. Conversely, self-contained sealing elements in which the flow of force is closed across the sealing structure, spring structure and root regions can be more easily handled in series production and in particular more easily separated. There is also no danger of them becoming hooked as they are inserted or introduced into the cavities.

(72) FIG. 14 shows a lateral view and two isometric representations of a sealing element 90 of an eighth example embodiment. The sealing element 90 is derived from the sealing elements 20 and 50 of the first and fourth example embodiments. Its spring structure 94 is connected to the sealing structure 91 near the two axial ends of the sealing structure 91, in each of the root regions, and forms an arc and/or bracket between the root regions which undulates multiple times in the longitudinal direction L. This provides supports 95 in spring portions of the spring structure 94 which are curved concavely with respect to the sealing structure 91, and abutments 98 in spring portions of the spring structure 94 which are curved convexly with respect to the sealing structure 91. The supports 95 serve to support the sealing element 90 in the accommodating cavity, and the abutments 98 limit the deformation and therefore in particular the danger of the sealing element becoming damaged as it is being fitted by an automatic assembly machine. The sealing surface is denoted as 92, and the lateral guides and/or side walls of the sealing structure 91, which is formed as a beam-shaped sealing strip as in the other example embodiments, are denoted as 93.

(73) FIG. 15 shows a lateral view and two isometric representations of a sealing element 100 of a ninth example embodiment. Like the other sealing elements, the sealing element 100 comprises a sealing structure 101 in the form of a sealing strip comprising a sealing surface 102 and lateral guides 103, and a spring structure 104 which is moulded in one piece with the sealing structure 101. The spring structure 104 projects on the rear side of the sealing structure 101 in a root region, which in this case is an axially middle root region, and forms a spring ring which is flat in the lateral view and which comprises two inner spring portions, which project axially outwards from the root region, and an arc-shaped outer spring portion which also simultaneously forms the supporting region 105 and serves as a support in the accommodating cavity.

(74) FIG. 16 shows a lateral view and three isometric representations of a sealing element 110 of a tenth example embodiment. The sealing element 110 comprises two identical sealing structures 111 and a spring structure 114 between the sealing structures 111. As in the other example embodiments, the sealing structures 111 and the spring structure 114 are moulded in one piece. Each of the sealing structures 111 can selectively form the sealing structure for the sealing contact, while the other sealing structure 111 in each case serves as a support in the accommodating cavity. This installation invariance of the sealing element 110 makes it easier to fit. With regard to being installed and/or fitted, the sealing element 110 is not only invariant against rotating by 180° about a central vertical axis of the sealing element 110 which points orthogonally with respect to the sealing surface 112, like the other sealing elements, but is also invariant in terms of rotating by 180° about a central longitudinal axis of the sealing element 110. The sealing element 110 is invariant against these two rotations not only for the practical purposes of being handled during fitting, but is also mirror-symmetrical in relation to a central plane of symmetry which is orthogonal with respect to the longitudinal axis and also mirror-symmetrical with respect to another central plane of symmetry which extends in the longitudinal direction L. In principle, however, exact mirror-symmetry is not required in relation to either one or other of the planes of symmetry in order to obtain the advantageous invariance in orientation for installation.

(75) The two sealing structures 111 themselves are each formed as beam-shaped sealing strips which extend axially, as in the other example embodiments, although only one or other sealing strip selectively passes into the sealing contact, while the other one comes to rest in the accommodating cavity. When the sealing element 110 is installed, the spring structure 114 which is situated between the sealing structures 111 is subjected to bending stress, i.e. it acts as a flexible spring, in a spring plane which points orthogonally with respect to the actuating direction S, like the other spring structures. It is formed as a closed spring ring which is connected to and/or transitions into the sealing structures 111 in an axially middle region of the sealing element 110.

(76) When the sealing element 110 is installed, one of the sealing structures 111 is situated in the sealing contact with the counter surface—the chamber wall structure 1a or 11a in the example embodiments—while the other of the two sealing structures 111 is accommodated in a cavity—the cavity 7 or 17 in the example embodiments—and serves to support the sealing element 110. The relevant sealing structure 111 thus forms a supporting structure in addition to the sealing structure 111, situated in the sealing contact, and the spring structure 114. Due to their symmetry, either of the two sealing structures 111 can selectively form the sealing contact, while the other in each case serves as the supporting structure.

(77) Cavities which serve to feed the hydraulic fluid to the rear side of the sealing structure 111, which is situated in the sealing contact when the sealing element 110 is installed, are denoted as 116. In advantageous developments, the spring structure 114 can comprise one or more cavities and/or one or more passages in order to effect a rapid equalisation of pressure between the interior space surrounded by the annular spring structure 114 and the exterior space surrounding the spring structure 114. The lateral guides for the sealing structure 111 are denoted as 113.

(78) FIG. 17 shows a lateral view and two isometric representations of a sealing element 120 of an eleventh example embodiment. Like the sealing element 110 of the tenth example embodiment (FIG. 16), the sealing element 120 comprises two identical sealing structures 121 and a spring structure 124 which is arranged between the sealing structures 121. The sealing structures 121 and the spring structure 124 are moulded in one piece. Unlike the tenth example embodiment, the spring structure 124 undulates transversely. Following the taxonomy of the other example embodiments, the sealing surface is denoted as 122, and the lateral guide for the sealing structure 121 is denoted as 123.

(79) The sealing elements of the example embodiments are produced from plastic. The sealing elements can consist of an elastomer material or can contain an elastomer material in particular regions, for example in order to achieve particular spring characteristics. Advantageously, however, the spring structures are elastic due to their shape and are in this sense dimensionally elastic, such that they can be moulded completely or at least predominantly from a thermoplastic material. Moulding them completely or at least predominantly from a thermoplastic material is preferred. The plastic sealing elements can in particular be manufactured in an injection-moulding method and thus provided as injection-moulded elements.

(80) The respective sealing structure and the respective spring structure can consist of different plastic materials, in order to optimise the two structures for their respective functions. The material for the sealing structure can thus for example be chosen from the viewpoint of maximum possible wear resistance and/or low friction while still maintaining a good sealing characteristic, while the material for the spring structure is for example chosen with regard to minimum possible fatigue due to the constant spring movements. The sealing element can then be produced from two different plastic materials in a two-component injection-moulding method. It would also be conceivable, when using non-identical plastic materials and even when using the same material, to mould the sealing structure only or the spring structure only in a first method step and to mould the other structure in each case onto the already moulded structure in a subsequent method step, which can likewise be performed in an injection-moulding method by placing the already produced structure in the injection-moulding die and moulding the other structure onto it.

(81) Sealing elements in accordance with the invention are designed to be used in hydraulic devices of the type described. Due to their geometry, they are suitable for continuous operation at working temperatures above 100° C. The choice of material is also relevant to their fitness for use. Through the configuration of its geometry and the choice of material, the sealing element is designed such that even towards the end of the service life for which it is designed, it still has sufficiently good spring characteristics, in order that it can perform its sealing function despite the working temperatures and varying loads which are to be expected during operation and the resultant relaxation of the material.

(82) Suitable plastics are disclosed in the “aspects” section. In order to improve their mechanical characteristics, the plastics can contain a reinforcing material, for example glass fibres, or multiple different reinforcing materials. In order to improve its sliding characteristics, the respective plastic can contain one or more different sliding additives. One preferred additive is carbon fibre, since carbon fibres both increase the mechanical strength and positively influence the sliding characteristics. Alternatively or additionally, PTFE can also be added to the plastic as a sliding additive.

(83) Particularly suitable original-moulding methods include generative moulding and casting methods. A 3D printing method can in particular be used for generatively moulding from plastic. In preferred embodiments, the two structures—the sealing structure and the spring structure—are moulded from the same plastic material in a combined method step, preferably in an injection-moulding method or generatively. If the sealing element comprises additional structures, such as for example the other sealing structure which can simultaneously serve as a supporting structure, then in the preferred embodiments, the sealing element comprising all its functional structures is moulded from the same plastic material in a combined method step, preferably in an injection-moulding method or generatively.

REFERENCE SIGNS

(84) 1 housing

(85) 1a chamber wall structure

(86) 1b housing cover

(87) 2 delivery chamber

(88) 3 delivery rotor

(89) 4 vane

(90) 5 actuating member

(91) 6 spring

(92) 7 cavity

(93) 8 connecting channel

(94) 9 supporting ring

(95) 10 inlet and outlet

(96) 11 housing, stator

(97) 11a chamber wall structure

(98) 12 jaw

(99) 13 housing cover

(100) 14 housing cover

(101) 15 actuating member, rotor

(102) 16 vane

(103) 17 cavity

(104) 18 inlet and outlet

(105) 19 latching pin

(106) 20 sealing element

(107) 21 sealing structure

(108) 22 sealing surface

(109) 23 guide

(110) 24 spring structure

(111) 25 supporting region

(112) 26 fluid connection (recess)

(113) 27-29 -

(114) 30 sealing element

(115) 31 sealing structure

(116) 32 sealing surface

(117) 33 guide

(118) 34 spring structure

(119) 35 supporting region

(120) 36 fluid connection (cavity)

(121) 37 clearance

(122) 38, 39 -

(123) 40 sealing element

(124) 41 sealing structure

(125) 42 sealing surface

(126) 43 guide

(127) 44 spring structure

(128) 45 support

(129) 46 fluid connection (recess)

(130) 47 -

(131) 48 abutment

(132) 49 -

(133) 50 sealing element

(134) 51 sealing structure

(135) 52 sealing surface

(136) 53 guide

(137) 54 spring structure

(138) 55 supporting region, support

(139) 56 fluid connection, feed (cavity)

(140) 57 clearance

(141) 58 abutment

(142) 59 -

(143) 60 sealing element

(144) 61 sealing structure

(145) 62 sealing surface

(146) 63 guide

(147) 64 spring structure, spring portion

(148) 65 supporting region

(149) 66 -

(150) 67 clearance

(151) 68, 69 -

(152) 70 sealing element

(153) 71 sealing structure

(154) 72 sealing surface

(155) 73 guide

(156) 74 spring structure, spring portion

(157) 75 supporting region

(158) 76 -

(159) 77 clearance

(160) 78, 79 -

(161) 80 sealing element

(162) 81 sealing structure

(163) 82 sealing surface

(164) 83 guide

(165) 84 spring structure

(166) 85 supporting region

(167) 86 -

(168) 87 clearance

(169) 88, 89 -

(170) 90 sealing element

(171) 91 sealing structure

(172) 92 sealing surface

(173) 93 guide

(174) 94 spring structure

(175) 95 support

(176) 96, 97 -

(177) 98 abutment

(178) 99 -

(179) 100 sealing element

(180) 101 sealing structure

(181) 102 sealing surface

(182) 103 guide

(183) 104 spring structure

(184) 105 supporting region

(185) 106-109 -

(186) 110 sealing element

(187) 111 sealing structure

(188) 112 sealing surface

(189) 113 guide

(190) 114 spring structure

(191) 115 -

(192) 116 fluid connection (cavity)

(193) 117-119 -

(194) 120 sealing element

(195) 121 sealing structure

(196) 122 sealing surface

(197) 123 guide

(198) 124 spring structure

(199) I inlet

(200) O outlet

(201) R rotational axis

(202) S actuating direction

(203) K1 pressure chamber

(204) K2 pressure chamber

(205) L longitudinal axis