CN110030052B

CN110030052B - Hydraulic camshaft adjuster

Info

Publication number: CN110030052B
Application number: CN201811407342.XA
Authority: CN
Inventors: 于尔根·韦伯
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Holding China Co Ltd
Priority date: 2017-11-23
Filing date: 2018-11-23
Publication date: 2023-01-03
Anticipated expiration: 2038-11-23
Also published as: DE102017127735B4; CN110030052A; DE102017127735A1

Abstract

The invention relates to a hydraulic camshaft adjuster, comprising a stator that can be driven by a crankshaft of an internal combustion engine and a rotor that can be coupled to a camshaft of the internal combustion engine, wherein the rotor can be rotated relative to the stator about a camshaft axis of rotation of the camshaft, wherein the stator comprises a seal, wherein the seal comprises a flange section extending in a rotational plane relative to the camshaft axis of rotation and a flange section connected to the flange section and extending in an axial direction, wherein the flange section is arranged axially on a side of the flange section facing away from the rotor and is connected to the flange section, wherein the stator comprises a sealing disk, wherein the sealing disk is arranged axially between the rotor and the flange section on the flange section, wherein the sealing disk engages in the flange section of the seal on a radially outer first section and is connected in a torque-locking manner to the seal, wherein a second section of the sealing disk, which is arranged radially inside relative to the first section, projects radially inside beyond the flange section.

Description

Hydraulic camshaft adjuster

Technical Field

The invention relates to a hydraulic camshaft adjuster.

Background

A camshaft adjuster is known from WO2014/048588 A1. The camshaft adjuster has a stator which can be driven by a crankshaft of the internal combustion engine and a rotor which can be connected in a rotationally fixed manner to a camshaft of the internal combustion engine. The stator has a stator disk and a stator ring, wherein the stator ring is connected to the stator disk by means of screws. The sealing of the screws is costly.

Disclosure of Invention

The object of the invention is to provide an improved hydraulic camshaft adjuster.

This object is achieved by means of a hydraulic camshaft adjuster according to the invention. Advantageous embodiments are given below.

It is clear that an improved hydraulic camshaft adjuster can be provided in that: the hydraulic camshaft adjuster has a stator which can be driven by a crankshaft of the internal combustion engine and a rotor which can be coupled to a camshaft of the internal combustion engine, wherein the rotor can be rotated relative to the stator about a camshaft axis of rotation of the camshaft, wherein the stator comprises a seal, wherein the seal comprises a flange section which extends in a rotational plane relative to the axis of rotation of the camshaft and a flange section which is connected to the flange section and extends in an axial direction, wherein the flange section is arranged axially on a side of the flange section facing away from the rotor and is connected to the flange section, the stator comprises a sealing disk, wherein the sealing disk is arranged axially between the rotor and the flange section on the flange section, wherein the sealing disk engages in the flange section of the seal on a radially outer first section and is connected to the seal in a torque-locking manner, wherein a second section of the sealing disk which is arranged radially inside relative to the first section projects radially inside beyond the flange section.

This design has following advantage: the seal is not formed in one piece but is formed from two separate components, which can each be produced separately by a forming process. In this way, the production of the sealing element by cutting can be dispensed with, since the geometry of the sealing element is determined as a whole by the fastening of the sealing disk to the sealing element. As a result, the hydraulic camshaft adjuster as a whole can be formed particularly simply and inexpensively.

In a further embodiment, the seal has a first recess on a first end side facing the rotor, said first recess having a recess base. The recess bottom is offset from the rotor toward the flange section. The first recess is open on the side facing the rotor. The sealing disk is arranged at least partially in the first recess and rests with the second end side facing the flange section against the recess base. The hydraulic camshaft adjuster is thus designed particularly compact in the axial direction.

In a further embodiment, the first recess has a first recess side and the sealing disk has an outer circumferential side, wherein the first recess side delimits the first recess in the radial direction. The sealing disk is pressed into the first recess and, on the outer circumferential side of the sealing disk, bears against the first recess flank and forms a press-fit connection for forming the connection. The sealing disk and the sealing element can thereby be connected to one another in a force-fitting manner.

In a further embodiment, the first recess and the flange section are arranged at least partially radially overlapping. Alternatively, the first recess flank is arranged radially outwardly with respect to the flange portion. This makes it possible to form the seal particularly easily.

In a further embodiment, the hydraulic camshaft adjuster has a locking device. The locking device is connected to the rotor and has a locking mechanism that is axially movable between an unlocked position and a locked position. A second recess is provided at least in sections in the sealing disk on a second end side facing the rotor. The second recess is axially open toward the rotor. In the locked position, the locking mechanism engages into the second recess to prevent rotation of the rotor relative to the stator. The rotor is relatively rotatable relative to the stator about a camshaft axis of rotation in an unlocked position. In the unlocked position, the locking mechanism is disposed outside of the second clearance. The recess can be introduced into the recess by a punching method, in particular simply and cost-effectively, by being arranged in the sealing disk, so that the sealing disk can be produced without further machining operations.

In a further embodiment, the hydraulic camshaft adjuster has an insertion ring. The insert ring is disposed in the second void. The insertion ring rests with an outer circumferential side against a second recess flank of the second recess and preferably forms a further press-fit connection with the second recess flank. The insertion ring is thereby reliably positioned and secured within the hydraulic camshaft adjuster against loss. The locking mechanism engages into the insertion ring in the locked position, wherein the insertion ring has a greater surface hardness than the second recess flank at least on the inner circumferential side. As a result, the wear of the stator in the region of the engagement of the locking mechanism can be kept low and at the same time the hydraulic camshaft adjuster can be produced particularly simply. A higher surface hardness on the circumferential side of the inner part of the insert ring can be achieved, for example, by means of a surface hardening method, in particular by means of an induction hardening method.

In a further embodiment, the hydraulic camshaft adjuster has a rotationally fixed housing with a housing interior delimited by the housing and a sealing element, in particular a radial shaft sealing ring, wherein the stator is arranged at least partially in the housing interior, wherein the sealing element is arranged radially between the housing and the flange section and is arranged on an outer circumferential side of the flange section or on an inner circumferential side of the flange section. This ensures a reliable sealing of the fluid chamber arranged radially inside the flange section.

In a further embodiment, the hydraulic camshaft adjuster has an intermediate disk, wherein the intermediate disk extends in a further plane of rotation relative to the camshaft axis of rotation, wherein the intermediate disk is arranged axially between the flange section of the seal and the sealing disk. A receptacle that is open axially toward the sealing disk and radially inward is provided in the flange section. The receptacle has a receptacle bottom, wherein the receptacle bottom is arranged parallel to the end face of the flange section, on which the sealing disk rests on the receptacle bottom. The intermediate disk is joined into the receptacle by means of a radially outer third section, wherein a fourth section of the intermediate disk, which is arranged radially inward with respect to the third section, is arranged outside the receptacle. The fourth section projects radially inwardly beyond the flange section.

In a further embodiment, the sealing disk is produced from a substantially flat raw material by means of a stamping method. The sealing disk comprises at least one of the following materials: aluminum, plastic, plate, steel plate, aluminum plate.

Advantageously, the seal is produced by means of a forming process, in particular a press bending process or a deep drawing process. The seal advantageously comprises at least one of the following further materials: steel, aluminium, in particular steel or aluminium sheets.

Drawings

The invention is explained in detail below with reference to the drawings. Shown here are:

fig. 1 shows a longitudinal section through a hydraulic camshaft adjuster according to a first embodiment;

fig. 2 shows a section through the longitudinal section of the hydraulic camshaft adjuster shown in fig. 1, which section is marked in fig. 1 by the reference X;

fig. 3 shows a perspective view of a sealing plate of the hydraulic camshaft adjuster shown in fig. 1 and 2 from a first perspective;

fig. 4 shows a perspective view of the sealing disk shown in fig. 1 to 3 from a second perspective;

fig. 5 shows a perspective view of the sealing element of the hydraulic camshaft adjuster and the sealing plate shown in fig. 1 to 4 in the assembled state;

fig. 6 shows a section through the longitudinal section of the hydraulic camshaft adjuster shown in fig. 1, which section is marked in fig. 1 by the reference Y;

fig. 7 shows a longitudinal section through a hydraulic camshaft adjuster according to a second embodiment;

fig. 8 shows a perspective view of a sealing disk of the hydraulic camshaft adjuster shown in fig. 7;

fig. 9 shows a perspective view of the seal of the hydraulic camshaft adjuster shown in fig. 7;

FIG. 10 shows a perspective view of the seal with the seal disk and insert ring assembled;

fig. 11 shows a longitudinal section through a stator of a hydraulic camshaft adjuster according to a third embodiment; and

fig. 12 shows the section marked with the reference Z in fig. 11 of the longitudinal section shown in fig. 11 through the expanded configuration of the hydraulic camshaft adjuster shown in fig. 11.

Detailed Description

Fig. 1 shows a longitudinal section through a hydraulic camshaft adjuster 10 according to a first embodiment.

The hydraulic camshaft adjuster 10 has a housing 15, a stator 20 and a rotor 25 which is rotatable relative to the stator 20. The rotor 25 and the stator 20 are mounted so as to be rotatable about a camshaft axis of rotation 30. The rotor 25 is connected to a camshaft 40 of the internal combustion engine 35 in the assembled state of the hydraulic camshaft adjuster 10 on the internal combustion engine 35. The camshaft 40 rotates about the camshaft rotational axis 30 when the internal combustion engine 35 is operated. The camshaft 40 can in this case be part of a valve train of the internal combustion engine 35 and is used to actuate, in particular open or close, the individual valves at specific points in time. The rotor 25 is connected to the camshaft 40 in a rotationally fixed manner.

The stator 20 is connected in a torque-locking manner to a crankshaft (not shown in fig. 1) in the assembled state of the hydraulic camshaft adjuster 10 on the internal combustion engine 35. The stator 20 can be coupled to the crankshaft, for example, by means of a belt 45, in particular a toothed belt. As an alternative to the belt 45, a control chain is also conceivable. By means of the belt 45, torque is transmitted from the crankshaft to the stator 20. The rotor 25 is rotatable relative to the stator 20. The rotor 25 and the stator 20 delimit at least two pressure chambers 50, which are schematically represented in fig. 1 by dashed lines. The pressure chamber 50 can be filled with a pressure fluid 55. The pressure fluid 55 is preferably a liquid, preferably an oil, in particular an oil for lubricating components of the internal combustion engine 35. The pressure fluid 55 can be controlled by means of a central valve 56. The central valve 56 is surrounded on the circumferential side by the rotor 25 and the camshaft 40. The rotor 25 is caused to rotate relative to the stator 20 in relation to the pressure difference of the pressure fluid in the pressure chamber 50. This results in: the camshaft 40 is rotated relative to the crankshaft by the hydraulic camshaft adjuster 10 and, as a function of the rotation, actuates the valves of the valve train of the internal combustion engine 35 at a different time than before the adjustment of the camshaft 40.

The stator 20 has a seal 60 and a sealing disk 65 for delimiting the pressure chamber 50. The seal 60, together with the sealing disk 65, delimits the pressure chamber 50 in the axial direction. The stator 20 has a seal cover 70 axially opposite the seal 60. The sealing cover 70 delimits the pressure chamber 50 axially opposite the sealing element 60. Axially between seal 60 and seal cover 70, stator 20 includes a stator ring 75. The stator ring 75 delimits the pressure chamber 50 in the circumferential direction and radially to the outside. Radially inside and in the circumferential direction, the pressure chamber 50 is delimited by the rotor 25.

On the outside, an external toothing 80 is provided on the stator ring 75, for example, and the belt 45 is engaged in meshing fashion by means of an internal toothing 85 provided on the inside. Thereby, torque can be introduced from the toothed belt 45 into the stator ring 75. Furthermore, a first sealing element 90 is provided at the end face between the stator ring 75 and the sealing cover 70 and a second sealing element 95 is provided between the seal 60 and the stator ring 75. The sealing

elements

90, 95 seal the pressure chamber 50 axially and radially.

The first sealing element 90 and/or the second sealing element can be designed as an O-ring as shown in fig. 1 and be arranged in a corresponding sealing groove in the stator ring 75. It goes without saying that it is also conceivable for the sealing

elements

90, 95 to be formed or otherwise positioned, for example in the sealing cap 70 and/or in the sealing element 60.

Seal 60 has a flange section 100 and a flange section 105. The flange portion 100 extends in a plane of rotation perpendicular to the camshaft axis of rotation 30. Radially on the outside, a sub-section of the external toothing system 80 of the stator ring 75 is arranged at a distance from the flange section 100. Radially on the inside, the flange section 100 is connected to a flange section 105. The flange section 105 extends in the axial direction in a direction facing away from the stator ring 75 and the pressure chamber 50. The flange section 100 is annular. The flange section 105 is of hollow cylindrical design and delimits the fluid chamber on the inside. In the half-longitudinal section, the seal 60 therefore has an L-shaped design, wherein the wall thickness of the flange section 105 (in the radial direction) is, for example, smaller than the wall thickness of the flange section 100 (in the axial direction). This design is exemplary, however. It is therefore also conceivable for the wall thicknesses of the flange section 100 and of the flange section 105 to be substantially the same.

Radially on the outside, the flange section 105 has a sealing surface 110 which is configured as an active surface. Radially on the outside with respect to the sealing surface 110, a third sealing element 115 is provided, which in this embodiment is designed as a radial shaft sealing ring by way of example. The third sealing element 115 is arranged between a housing flange 116, which is designed in a hollow-cylindrical manner with respect to the camshaft rotational axis 30, and the flange section 105. The housing flange 116 of the housing 15 is arranged radially outside with respect to the flange section 105. The third sealing element 115 bears against the sealing surface 110 during operation of the hydraulic camshaft adjuster 10, wherein the sealing surface 10 rotates, while the third sealing element 115 is arranged in the housing 15 in a rotationally fixed manner. The third sealing element 115 fluid-tightly seals the fluid chamber from the environment. A pressurized fluid 55 can be disposed in the fluid chamber.

In this embodiment, the seal 60 is produced from a flat material, preferably sheet metal, by means of a forming process, in particular by means of a deep-drawing process or a press-bending process. In order to ensure the functionality of the third sealing element 115 during the service life of the hydraulic camshaft adjuster 10, the sealing surface 110 is reworked, for example, after the forming process by means of a cutting process, in order to ensure a particularly good surface quality and a high concentricity on the sealing surface 110. Needless to say, the reworking of the sealing surface 110 can be dispensed with after the forming process for producing the sealing element 60 has been carried out.

The sealing disk 65 is arranged radially on the inside relative to the flange section 100. The sealing disk 65 is thinner in the axial direction than the flange section 100. The sealing disk 65 extends parallel to the flange section 100 and is arranged axially between the pressure chamber 50 and the flange section 105. On the end side on the side facing the stator ring 75, the sealing disk 65 is arranged adjacent to the stator ring 75 on the radial outside and on the radial inside relative to the rotor 25.

Fig. 2 shows a section marked by the reference X in fig. 1 through the longitudinal section of the hydraulic camshaft adjuster 10 shown in fig. 1.

The seal 60 has a first recess 120 on a first end side 117 facing the pressure chamber 50 and the stator ring 75. The first recess 120 is open in the axial direction to the stator ring 75 or the pressure chamber 50. Radially, the first recess 120 is bounded radially on the outside by a first recess flank 125. On the side facing away from the stator ring 75 in the axial direction, the first recess 120 has a first recess base 130. The first recess foot 130 extends in a rotation plane perpendicular to the camshaft rotation axis 30. The first recess base 130 is arranged offset from the pressure chamber 50 toward the flange section 105.

The sealing disk 65 engages with the radially outer first section 135 into the first recess 120 and rests flat with the second end side 145 against the first recess base 130. A second section 140, which is arranged radially inward with respect to the first section 135, projects radially inward beyond the flange section 105. The sealing disk 65 delimits the pressure chamber 50 on the side facing the stator ring 75.

In this embodiment, the first recess flank 125 is formed, for example, cylindrically. The first recess flank 125 delimits the first recess 120 radially inwardly on the circumferential side, wherein the conical design is selected in the axial direction such that the first recess flank 125 tapers from the stator ring 75 and the pressure chamber 50 toward the flange section 105.

In this embodiment, the sealing disk 65 is pressed into the first recess 120 and forms a press-fit connection 151 with the first recess flank 125 on the outer circumferential side 150. The outer circumferential side 150 of the sealing disk 65 is here of cylindrical design, corresponding to the first recess side 125. By pressing the engagement 151, the sealing disk 65 is connected with a force fit to the seal 60 in this embodiment, so that: during assembly of the hydraulic camshaft adjuster 10, the seal 60 can be assembled together with the sealing disk 65 without the sealing disk 65 undesirably coming loose from the seal 60. It is also possible to dispense with the press-fit connection 151 and to arrange the outer circumferential side 150 at a distance from the first recess flank 125 in order to form a leakage fluid channel.

The sealing disk 65 is in this embodiment stamped, for example, by means of a stamping method, from a flat, preferably plate-shaped starting material, in particular from a sheet metal. As a result, the sealing disk 65 can be produced particularly cost-effectively on the one hand and on the other hand a reliable positioning of the sealing disk 65 relative to the seal 60 is ensured.

In this embodiment, the first recess 120 and the flange section 105 are arranged partially overlapping radially. Radial overlap is understood here to mean: in the projection of the two components in the axial direction, in this embodiment the first recess 120 and the flange section 105 are in a projection plane perpendicular to the camshaft axis of rotation 30, the two components, in this embodiment the first recess 120 and the flange section 105, coincide in projection. Since the first clearance portion 120 and the flange section 105 overlap, it is possible to ensure that: a particularly compact and material-saving design of the sealing element 60 together with the sealing disk 65 can be provided, so that the sealing element 60 together with the sealing disk 65 has a low weight. As a result, the hydraulic camshaft adjuster 10 as a whole remains particularly lightweight.

Fig. 3 shows a perspective view of the sealing disk 65 of the hydraulic camshaft adjuster 10 shown in fig. 1 and 2 from a first viewing angle.

The sealing disk 65 is formed flat on the second end side 145 and has no interruptions. The second end side 145 is formed in a ring shape in plan view. The inner circumferential side 155 of the sealing disk 65 is designed in a stepped manner. It is also conceivable, of course, for the inner circumferential side 155 to be of cylindrical design extending around the camshaft axis of rotation 30. The step of the inner circumferential side 155 is selected in this embodiment in such a way that the inner circumferential side 155 decreases in the direction of the inner diameter of the inner circumferential side 155 of the stator ring 75 from the flange section 105.

Fig. 4 shows a perspective view of the sealing disk 65 shown in fig. 1 to 3 from a second viewing angle.

The sealing disk 65 has a first section 161 of a second recess 165 on a third end side 160 opposite the second end side 145. The first section 161 of the second recess 165 adjoins the outer circumferential side 150 of the sealing disk 65 on the radially outer side. The first section 161 of the second recess 165 has a substantially partially circular design. The first section 161 of the second recess 165 is formed open radially to the outside and axially on the side facing the third end side 160.

The second clearance 165 has a second clearance bottom 170. In a second recess base 170 of the first section 161 of the second recess 165, a first subsection 171 of a pressure channel 175 is provided. The first subsection 171 is formed in the form of a partial trough. The pressure channel 175 is in fluid connection with other pressure channels of the hydraulic camshaft adjuster 10, which are not shown. The first subsection 171 of the pressure channel 175 is formed in a groove-like manner in the second recess bottom 170. It goes without saying that other designs of the pressure channel 175 are also conceivable.

The second recess base 170 is formed flat and the pressure channel 175 is formed as a depression in the second recess base 170. The pressure channel 175 extends in the circumferential direction over almost the entire width of the second recess 165.

Fig. 5 shows a perspective view of the sealing disk 65 and the sealing element 60 shown in fig. 1 to 4 in the assembled state.

The first end side 117 and the third end side 160 are arranged in a common plane of rotation.

Furthermore, a second section 185 of the second recess 165 is provided in the flange section 100. In plan view, the second section 185 of the second recess 165 is formed partially circularly. Together, second section 185 and first section 161 form second recess 165, so that second recess 165 is circular in plan view of second recess 165. The second section 185 of the second recess 165 is open inward in the circumferential direction. Furthermore, the second portion 185 is open on the end face on the first end face 117.

A second subsection 190 of the pressure channel 175 is likewise provided in the second recess bottom 170. The second subsection 190 is formed in a partially trough-shaped manner. The second sub-section 190 forms a channel-shaped configuration of the pressure channel 175 with the first sub-section 170. Pressure channel 175 has a slotted design.

Second recess 165 has a second recess flank 195, second recess flank 195 being formed by first section 161 and second section 185 together. In this embodiment, the second recess side 195 is formed in a circular shape in plan view. Other designs of second clearance side 195 are also contemplated.

Fig. 6 shows the part marked by the reference Y in fig. 1 through the longitudinal section of the hydraulic camshaft adjuster 10 shown in fig. 1.

The hydraulic camshaft adjuster 10 has a locking device 200. The locking device 200 is arranged in a third recess 205 of the rotor 25. The third recess 205 extends in the axial direction and can be formed, for example, as a bore in the rotor 25. The locking device 200 is connected to the rotor 25 and has a locking mechanism 210, for example a locking cage, which is axially movable between an unlocked position and a locked position.

It is particularly advantageous for the stator 20 to have an insert ring 215. The insert ring 215 is disposed in the second space 165. The insert ring 215 is formed annularly. The insertion ring 215 rests with an outer circumferential side 220 against the second recess side 195. Preferably, on the outer circumferential side 220, the insertion ring 215 forms a further press-fit connection 216 with the second recess flank 195, so that the position of the insertion ring 215 during the assembly of the hydraulic camshaft adjuster 10 is reliably ensured in the axial direction. On the inner ring peripheral side 225, the insert ring 215 is hardened and has a higher surface hardness than the second recess side 195. The insertion ring 215 rests at the end face on the second recess foot 170. The insert ring 215 is designed in the axial direction such that the insert ring 215 does not project beyond the first and third end sides 117, 160. Thereby ensuring reliable movement of the rotor 25. The insertion ring 215 delimits on the inside a latching receptacle 226.

In the locked position, the locking mechanism 210 engages into the lock receptacle 226 of the insert ring 215. A small wear of the insertion ring 215 on the locking receptacle 226 is ensured by the hardened inner circumferential side 225 of the insertion ring 215. Furthermore, the case hardening of the second recess side 195 can be dispensed with, so that the hydraulic camshaft adjuster 10 is particularly cost-effective to construct.

In the locked position, the locking mechanism 210 couples the rotor 25 to the stator 20, in particular when the camshaft adjuster 10 is operating below a predetermined rotational speed. The predetermined rotational speed can be, for example, slightly below the idle rotational speed or the idle rotational speed relative to the internal combustion engine 35. Above a predetermined rotational speed, the supply device of the internal combustion engine 35 for the pressurized fluid 55 provides a pressure which is higher than a predetermined pressure, wherein the pressurized fluid 55 acts on the front side of the closure element 210 via the pressure channel 175. When the pressure of the pressure fluid 55 exceeds a predetermined pressure, the locking mechanism 210 is pressed out of the locking receptacle 226 of the insert ring 215 against the action of the tensioning device 230 of the locking device 200 and pushed into the rotor 25, so that the locking device 200 releases the rotor 25 relative to the stator 20 above a predetermined rotational speed or above the predetermined pressure of the pressure fluid 55, and the rotor 25 can rotate relative to the stator 20 as a function of the pressure ratio in the pressure chamber 50.

Fig. 7 shows a longitudinal section through a hydraulic camshaft adjuster 10 according to a second embodiment.

The hydraulic camshaft adjuster 10 is substantially identical to the hydraulic camshaft adjuster 10 shown in fig. 1 to 6. Only the differences with respect to the hydraulic camshaft adjuster 10 shown in fig. 1 to 6 will be discussed below.

In contrast to the hydraulic camshaft adjuster 10 shown in fig. 1 to 6, the sealing disk 65 is formed radially wider than in fig. 1 to 6. As a result, second recess 165 is completely arranged in sealing disk 65, so that the two-part design of second recess 165 can be dispensed with.

Since the sealing disk 65 is formed radially wider, the first recess 120 is also formed wider than shown in fig. 1 to 6, corresponding to the design of the sealing disk 65. The first recess 120 terminates with its first recess flank 125 radially outside the locking device 200. The first recess flank 125 is arranged radially on the outside of the flange section 105 approximately at the level of the housing flange 116 of the housing 15, on which the third sealing element 115 is arranged radially on the inside. The radially wider design of the sealing disk 65 has the following advantages: the circumferential orientation of the sealing disk 65 relative to the seal 60 can be dispensed with, and the sealing disk 65 can be pressed into the seal 60 independently of the circumferential orientation. The hydraulic camshaft adjuster 10 is thus particularly simple and inexpensive to assemble.

Fig. 8 shows a perspective view of the sealing disk 65 of the hydraulic camshaft adjuster 10 shown in fig. 7.

Second recess 165 can be introduced into sealing disk 65 together with pressure channel 175, for example by means of an extrusion method, in particular a pressing method. Since the cutting method for producing second recess 165 and pressure channel 175 can be dispensed with, sealing disk 65 is produced solely by a forming method, so that sealing disk 65 can be produced particularly quickly and simply and at low cost.

Fig. 9 shows a perspective view of the seal 60 of the hydraulic camshaft adjuster 10 shown in fig. 7.

The seal 60 is particularly simple in design compared to the seal 60 shown in fig. 5, in that: the second recess 165 is arranged completely in the sealing disk 65. Thus, only the first recess 120 is provided in the flange portion 100 on the first end side 117 of the seal 60, the first recess flank 125 extending completely on a circular path around the camshaft axis of rotation 30 and having no further interruptions. The seal 60 can thus be produced in a particularly simple and cost-effective manner in a molding process. In addition, slit-shaped fourth recesses 235 are provided radially outside the first recesses 120, which are arranged at regular intervals from one another, for example, in the circumferential direction. In this case, the fourth recess 235 is open radially to the outside. When assembling the hydraulic camshaft adjuster 10, a tool can engage in the fourth recess 235.

Fig. 10 shows a perspective view of the seal 60 with the assembled sealing disk 65 and the insert ring 215 inserted into the second recess 165.

Insert ring 215 partially covers pressure channel 175 at the bottom in second recess 165. By means of the sealing disk 65, on the side facing the rotor 25, the molding region, i.e. the region on which the flange section 105 is connected to the flange section 100 and in which the first material of the seal 60 has its greatest deformation during the production of the seal 60, is reliably covered by the sealing disk 65. This reliably prevents any leaks at the seal 60 by means of the sealing disk 65.

A moldable material is particularly suitable as the first material for the sealing element 60. The seal 60 thus has, for example, steel, aluminum, in particular steel or aluminum plate as the first material. The sealing disk 65 has at least one of the following second materials: aluminum, plastic, steel plate, aluminum plate. The overall weight of the hydraulic camshaft adjuster 10 can also be kept particularly low by a suitable material combination of the first and second material.

Fig. 11 shows a longitudinal section through the stator 20 of the hydraulic camshaft adjuster 10 according to the third embodiment.

The hydraulic camshaft adjuster 10 is constructed essentially identically to the hydraulic camshaft adjuster 10 shown in fig. 1 to 10. In the following, only the differences of the hydraulic camshaft adjuster 10 shown in fig. 10 in relation to the hydraulic camshaft adjuster 10 shown in fig. 1 to 10 are to be discussed.

The seal 60 has an axial section 240 in addition to the seal 60 shown in fig. 1 to 10, so that the seal 60 has an overall pot-shaped design. The axial section 240 is of hollow-cylindrical design and is connected at an axial end to the radially outer end of the flange section 100. Radially on the inside, the flange section 100 is connected to a flange section 105. The axial section 240 is arranged axially on the side of the flange section 100 facing away from the flange section 105. Radially on the outside, a drive wheel 245, on which the external toothing 80 is provided, can be provided on the flange section 100. Alternatively, the external toothing system 80 can also be arranged radially on the outside on the axial section 240.

The seal 60 forms a first recess 120 by means of the inner circumferential side 250 and by means of the first end side 117. The sealing disk 65 can thereby be formed particularly widely in the radial direction. A relief 251 can be provided at the junction between the axial section 240 and the flange section 100 in order to ensure a flat contact of the sealing disk 65 against the flange section 100. The outer circumferential side 150 is formed cylindrically. The outer circumferential side 150 can be arranged radially spaced apart from the axial section 240 or form a press fit 151 with the axial section 240.

Furthermore, a first receptacle 255 can be provided in the flange section 100, wherein the first receptacle 255 is closed on the side facing the flange section 105. The first housing 255 is provided in alignment with the through hole 260 of the seal disk 65. A fixing mechanism 261 for fixing the stator ring 75 may be engaged into the first housing portion 255 and the through hole 260.

Additionally, as shown in fig. 11, an intermediate disk 265 can be provided between the sealing disk 65 and the flange section 100. The intermediate disk 265 extends in a plane of rotation perpendicular to the camshaft axis of rotation 30.

For fastening the intermediate disk 265, a second receptacle 270 can be provided in the flange section 100, wherein the second receptacle 270 has a receptacle circumferential surface 275 and a receptacle base 280. The receptacle base 280 is arranged perpendicular to the first end side 117 of the flange portion 100. The intermediate disk 265 engages in the second receptacle 270 by means of a radially outer third portion 285. The fourth section 290 projects radially inward beyond the flange section 105 on the inside. The fourth section 290 and the second section 140 terminate, for example, at the same level radially inside.

The intermediate disk 265 rests in a surface-like manner on the receptacle bottom 280 by means of a fourth end face 295 of the intermediate disk 265. The receiving portion annular surface 275 is provided radially inward of the first receiving portion 255. A particularly compact stator 20 can thereby be provided.

Fig. 12 shows the section marked with the reference Z in fig. 11 of the longitudinal section shown in fig. 11 through the expanded configuration of the hydraulic camshaft adjuster 10 shown in fig. 11.

Instead of the undercut 251 shown in fig. 11, the sealing disk 65 has a chamfer 300 on the radially outer portion at the transition between the second end side 145 and the outer circumferential side 150. This chamfer ensures that the sealing plate 65 is reliably pressed into the first recess 120 without the sealing plate 65 being deflected on the seal 60.

The invention has been particularly shown and described with reference to the preferred embodiments. The invention is not limited to the disclosed examples. Rather, a person skilled in the art will be able to derive other variants therefrom without departing from the scope of protection of the invention. In particular, the following can be considered: the embodiments shown in the figures can be combined with each other.

List of reference numerals

10. Hydraulic camshaft adjuster

15. Shell body

20. Stator

25. Rotor

30. Camshaft axis of rotation

35. Internal combustion engine

40. Cam shaft

45. Leather belt

50. Pressure chamber

55. Pressure fluid

56. Central valve

60. Sealing element

65. Sealing disc

70. Sealing cover

75. Stator ring

80 External tooth (of stator ring)

85 Internal tooth part (of belt)

90. First sealing element

95. Second sealing element

100. Flange section

105. Flange section

110. Sealing surface

115. Third sealing element

116. Shell flange

117. First end side

120. First hollow part

125. Side surface of the first hollow part

130. The bottom of the first hollow part

135 First section (of sealing disc)

140 Second section (of sealing disc)

145. Second end side

150 Outer circumferential side (of sealing disc)

151. Compression joint

155 Circumferential side of the interior (of the gland plate)

160. Third end side

161. First section of the second hollow

165. Second hollow part

170. Second hollow part bottom

171. First subsection of a pressure channel

175. Pressure channel

185. Second section of the second recess

190. Second sub-section of the pressure channel

195. Second side surface of the hollow part

200. Locking device

205. The third hollow part

210. Locking mechanism

215. Insert ring

216. Compression joint

220. The outer circumferential side of the insert ring

225. The circumferential side of the inner part of the insert ring

226. Lock receiving part

230. Tensioning device

235. The fourth hollow part

240. Axial segment

245. Driving wheel

250. Circumferential side of the inner part

251. Tool withdrawal groove

255. The first accommodating part

260. Through hole

261. Fixing mechanism

265. Intermediate disc

270. Second accommodating part

275. Circumferential surface of the receiving portion

280. Bottom of the container

285 Third section (of the intermediate disc)

290 Fourth section (of the intermediate disc)

295 Fourth end side (of intermediate disc)

300. Chamfering edge

Claims

1. A hydraulic camshaft adjuster (10),

having a stator (20) which can be driven by a crankshaft of an internal combustion engine (35) and a rotor (25) which can be coupled to a camshaft (40) of the internal combustion engine (35),

wherein the rotor (25) is rotatable relative to the stator (20) about a camshaft axis of rotation (30) of the camshaft (40),

wherein the stator (20) comprises a seal (60),

wherein the seal (60) comprises a flange section (100) and a flange section (105) connected to the flange section (100), the flange section extending in a plane of rotation relative to the camshaft rotational axis (30), the flange section extending in an axial direction,

wherein the flange section (105) is arranged axially on a side of the flange section (100) facing away from the rotor (25) and is connected to the flange section (100),

it is characterized in that the preparation method is characterized in that,

the stator (20) comprising a sealing disc (65),

wherein the sealing disk (65) is arranged on the flange section (100) axially between the rotor (25) and the flange section (105),

wherein the sealing disk (65) engages on a first radially outer section (135) into a flange section (100) of the seal (60) and is connected to the seal (60) in a torque-locking manner,

wherein a second section (140) of the sealing disk (65), which is arranged radially inside with respect to the first section (135), projects radially inwardly beyond the flange section (105); wherein the seal (60) has a first recess (120) on a first end face (117) facing the rotor (25), said first recess having a recess base (130),

the recess base (130) is arranged offset from the rotor (25) toward the flange section (105) and the first recess (120) is open on the side facing the rotor (25),

wherein the sealing disk (65) is arranged at least in sections in the first recess (120) and rests on the recess base (130) with the second end face (145) facing the flange section (105).

2. The hydraulic camshaft adjuster (10) according to claim 1,

wherein the first recess (120) has a first recess side (125) and the sealing disk (65) has an outer circumferential side (150),

wherein the first recess flank (125) delimits the first recess (120) in the radial direction,

wherein the sealing disk (65) is pressed into the first recess (120) and bears against the first recess flank (125) on an outer circumferential side (150) and has a press-fit connection (151) for producing the connection.

3. The hydraulic camshaft adjuster (10) as claimed in claim 2,

wherein the first recess (120) and the flange section (105) are arranged at least partially radially overlapping,

or

Wherein the first recess flank (125) is arranged radially outwardly with respect to the flange section (105).

4. The hydraulic camshaft adjuster (10) according to one of the preceding claims,

having a locking device (200),

wherein the locking device (200) is connected to the rotor (25) and comprises a locking mechanism (210) which is axially movable between an unlocked position and a locked position,

wherein a second recess (165) is provided in the sealing disk (65) at least in sections on a third end face (160) facing the rotor (25),

wherein the second recess (165) is open axially to the rotor (25),

wherein in the locked position the blocking mechanism (210) engages into the second recess (165) to prevent the rotor (25) from rotating relative to the stator (20),

wherein in the unlocked position the rotor (25) is relatively rotatable with respect to the stator (20) about the camshaft axis of rotation (30),

wherein in the unlocked position the latching mechanism (210) is disposed outside the second recess (165).

5. The hydraulic camshaft adjuster (10) according to claim 4,

having an insert ring (215),

wherein the insert ring (215) is arranged in the second recess (165),

wherein the insertion ring (215) rests with an outer circumferential side (220) against a second recess flank (195) of the second recess (165) and forms a further press fit (216) with the second recess flank (195),

wherein in the locked position the locking mechanism (210) is engaged into the insertion ring (215),

wherein the insertion ring (215) has a greater surface hardness than the second recess flank (195) at least on the inner circumferential side (225).

6. The hydraulic camshaft adjuster (10) according to claim 1,

having a rotationally fixed housing (15) having a housing interior delimited by the housing (15) and a sealing element (115), wherein the stator (20) is arranged at least in sections in the housing interior,

wherein the sealing element (115) is arranged radially between the housing (15) and the flange section (105) and is placed on the circumferential side of the outside of the flange section (105) or on the circumferential side of the inside of the flange section (105).

7. The hydraulic camshaft adjuster (10) as claimed in claim 1,

having an intermediate disk (265),

wherein the intermediate disk (265) extends in a further plane of rotation relative to the camshaft axis of rotation (30),

wherein the intermediate disk (265) is arranged axially between the flange section (100) of the seal (60) and the sealing disk (65),

wherein a receptacle (270) which is open axially towards the sealing disk (65) and radially inwards is provided in the flange section (100),

wherein the receptacle (270) has a receptacle bottom (280),

wherein the receptacle base (280) is arranged parallel to the end face (117) of the flange section (100) at which the sealing disk (65) rests on the flange section (100),

wherein the intermediate disk (265) is joined into the receptacle (270) by means of a radially outer third section (285),

wherein a fourth section (290) of the intermediate disk (265) which is arranged radially inside with respect to the third section (285) is arranged outside the receptacle (270),

wherein the fourth section (290) projects radially inwardly beyond the flange section (105).

8. The hydraulic camshaft adjuster (10) as claimed in claim 1,

wherein the sealing disc (65) is produced from a substantially flat raw material by means of a stamping method,

wherein the sealing disk (65) comprises at least one of the following materials: aluminum, plastic, steel.

9. The hydraulic camshaft adjuster (10) as claimed in claim 1,

wherein the sealing element (60) is produced by means of a moulding process,

wherein the seal (60) advantageously comprises at least one of the following further materials: steel, aluminum.