EP1549829A1

EP1549829A1 - Adjusting device

Info

Publication number: EP1549829A1
Application number: EP03748114A
Authority: EP
Inventors: Jan Klindworth
Original assignee: INA Schaeffler KG
Current assignee: IHO Holding GmbH and Co KG
Priority date: 2002-10-10
Filing date: 2003-10-04
Publication date: 2005-07-06
Also published as: AU2003271698A1; WO2004035996A1; WO2004035995A1; US7316211B2; JP2006515917A; KR20050083734A; KR20050049532A; EP1552115A1; JP2006503237A; DE10247204A1; US20050280303A1; US20050268872A1; DE10247204B4; US7303499B2; AU2003267430A1

Abstract

The invention relates to an adjusting device for adjusting two parts (2, 3) with regard to one another that is used as a camshaft adjuster. The aim of the invention is, with an easy and smooth operability, to ensure a self-locking and an at least extensive play-free, continuous adjustment of the two parts with a high level of efficiency. To this end, the adjusting device comprises a first part (2) with webs (2.3, 22.3), which are interspaced in the peripheral direction and between which chambers (2.4) are formed, and comprises a second part (3) with an internal gearing (3.2, 13.2), and a number of teeth (7, 27) that are arranged inside the chambers (2.4) while being interspaced in the peripheral direction. The adjusting device also comprises an inner contact surface (7.4) for resting against an eccentric drive element (6), and comprises an outer contact surface (7.5) for engaging inside the internal gearing (3.2, 13.2). When an input shaft (4) is rotated by the teeth (7, 27) located inside the chambers (2.4), rotational motions about rotation axes, which are parallel to rotation axis (A) of the parts (2, 3), can be executed.

Description

Name of the invention

adjustment

description

Field of the Invention

The invention relates to an adjusting device for adjusting a camshaft in relation to a camshaft gear driven by a crankshaft, components provided for the adjustment process being arranged on the camshaft gear and on the camshaft, according to the preamble of claim 1.

Stepper motors, among others, can be used as adjusting devices, which have a self-locking and an exact, but only discrete, i.e. do not allow continuous adjustment. A worm gear can also be used to achieve self-locking and high reduction. However, worm gears have a low degree of efficiency with relatively high friction and require abrasion-resistant and heat-resistant materials.

DE 195 08 328 A1 shows a self-locking adjusting device for rotating two fitting parts relative to one another. One of the two fitting parts has an internal toothing into which bolts or teeth along a radial, radial direction can be inserted. The teeth are guided in chambers between webs of the other fitting part in such a way that the radial inward and outward movement is made possible. The teeth are supported inwards on a control surface which is designed as the outer surface of an egg-shaped control member. When the control member rotates, the teeth are thus periodically shifted outward in the radial direction, some of the teeth engaging in tooth gaps. The outer end sections of the teeth and the recesses or tooth gaps of the internal toothing taper towards the outside, so that the teeth transmit a torque between the webs of the second fitting part and the internal toothing of the first fitting part when inserted eccentrically into a recess.

On the one hand, this adjustment device has the disadvantage that only partial self-locking is achieved. If a torque acts on the fitting part having the internal toothing, only one or two teeth, which are pressed by the teeth of the internal toothing against the eccentric area of the control member, contribute to the self-locking effect, depending on the engagement situation of the teeth. The opposite teeth do not contribute to self-locking any more than those teeth that are in the radially outer position, ie. H. are positive in the recess, and those teeth that are in the radially inner position, d. H. do not engage in the tooth gaps of the internal toothing. The possibly only one tooth, which is supposed to contribute to the self-locking effect, can, however, transmit a force not directed towards the axis of rotation from the internal toothing to the control member between the point of engagement of the internal toothing on its outer contact surface and its inner contact surface resting on the control member thus leads to the transmission of a torque. In this case, in particular if only a few teeth are used, there is also no positive locking between the internal toothing and the webs and thus - at least in the case of an unfavorable engagement situation of the teeth - no complete self-locking is achieved.

Furthermore, there is a play-free configuration of such an adjustment device problematic. The teeth which are linearly displaceable in the radial direction slide with their side surfaces on the side surfaces of the webs of the second fitting part. A play-free arrangement of the teeth between the webs is practically not possible; To achieve low-friction guidance of the teeth between the webs, a certain excess is rather necessary. Even in the case of a positive engagement of a tooth in its radially outer position in a recess in the internal toothing, a play between the control surface and the tooth will ultimately remain due to the tolerances caused by production technology.

Camshaft adjustments are used, in particular, for speed and load-dependent adjustment of the opening and closing times of the valves of an internal combustion engine in order to improve the filling. The camshaft is driven by the crankshaft - e.g. B. on toothed belts, a roller chain or spur gears - on a camshaft gear with which the camshaft is connected. The camshaft is adjusted by rotating the camshaft relative to the camshaft sprocket, the torque transmission still having to be ensured during the adjustment. Therefore, adjustment devices with high, infinitely variable setting accuracy and reliable self-locking in all positions are required. For this purpose, in conventional camshaft adjusting devices, a control piston is connected in a flange shaft connected to the camshaft by, for. B. adjusts a hydraulic drive against a spring force, the flange shaft being connected to the camshaft gear and possibly an actuating piston via helical gears. However, such training is complex, costly and requires maintenance. Furthermore, complex supply lines from a central hydraulic pump in the vehicle are required.

The invention has for its object to provide an adjustment device that ensures self-locking and at least largely free of play, stepless adjustment of the two components with simple and smooth operability. A high reduction ratio should advantageously be achievable.

This object is solved by the features of claim 1. The Unteran Sayings describe preferred further training.

According to the invention, the teeth therefore perform rotary movements during the adjustment movement. These movements of the teeth can generally be superimposed on a linear movement directed outwards and inwards in the radial direction and a rotational movement of the teeth about a respective rotation axis parallel to the rotation axis of the components. In a particularly preferred manner, the teeth each run back on a circular arc path from their inner contact with the drive member to the outer contact on the internal toothing and on a further circular arc path.

The rotational movements of the teeth according to the invention enable a good adaptation of the shape of the teeth and webs as well as the internal toothing to the sequence of movements, which enables a self-locking engagement of part of the teeth. In particular, a favorable transmission angle between the movable tooth and the internal toothing is achieved, in which the force transmission from the movable tooth to the internal toothing takes place with a small radial component, so that a high degree of efficiency can be achieved. Furthermore, a defined contact of a tooth on the two adjacent webs is made possible, which leads to a reduction in play.

Advantageously, in the radially outermost position of a tooth, no contact with the internal toothing is achieved in order to ensure a defined contact with the adjacent webs in this position as well. The coupling of the teeth to the internal toothing thus takes place on the preferably inclined tooth flanks of the internal toothing, with at least one tooth in each case resting on a front or rear tooth flank in the direction of rotation.

An eccentric is advantageously provided as the drive element for the adjustment of the teeth. For this purpose, an eccentrically attached circular disc can be rigidly attached to the input shaft, on the outer surface of which the teeth bear with their inner contact surfaces. Advantageously, however, an eccentric ring between the eccentric disc and the inner contact surfaces of the teeth provided. The eccentric ring essentially performs a wobble movement without rotation, so that the teeth can be driven essentially without frictional engagement of their inner contact surface on the eccentric ring. The teeth roll on the eccentric ring with only a slight rolling friction, so that a high degree of efficiency is achieved.

In order to achieve a defined contact of the teeth on the drive member, they are advantageously radially preloaded. This can be done on the one hand by a bias towards the axis of rotation, the z. B. by a prestressed elastic O-ring, for. B. a rubber ring is exercised. The O-ring can surround axial projections or areas of the teeth, z. B. can also be placed through recesses in the teeth. In addition, an external bias can be applied. This bias can, for. B. done by a preloaded spring element which sits on the shaft and presses the eccentric in one direction radially outwards. The spring element can in this case be deformed in a purely elastic manner or can be introduced into the adjusting device with partial plastic deformation. Furthermore, a radial bias to the outside is also z. B. possible by an oversize. However, a pre-tension is generally not necessary.

The rotational movement of the teeth can advantageously be initiated by a control surface at their radially inner reversal point acting as bottom dead center. The control surface comes into contact with the inner contact surfaces of the teeth when they are in their radially inner positions. This particularly prevents the teeth from jamming at the bottom dead center of their movement. The control surface can, in particular, be a control toothing region of a control gearwheel which is connected to the second component in a rotationally fixed manner or is formed in one piece therewith. An external toothing can serve in particular as the control toothing. Here, the inner contact surface of a tooth comes into engagement with tooth gaps or recesses in the external toothing of the second component. Instead of an external toothing, an internal toothing can also be provided accordingly. According to one embodiment, the tooth can be rotated about a pivot point defined on the first component by a nose of the tooth engaging in a corresponding guide in the chamber between the webs of the other component. The guide tapers inwards in the radial direction in order to ensure the defined pivot point in the radially inner position of the tooth and to enable both the inward and the outward circular arc path in the radially outer positions, to which the side surfaces of the teeth adhere in a defined manner Glide the side surfaces of the webs.

As an alternative to this, the teeth and webs can also have shoulder regions which ensure the defined rotational movement when the teeth slide on the webs.

Furthermore, a control disk can also be provided with a control surface which causes a frictional connection with inner contact surfaces of the teeth. B. is rigidly connected to the input shaft or the drive member.

The adjustment device according to the invention is robust and can transmit high torques and ensure precise position adjustment with reliable self-locking. Thanks to the favorable transmission angle between the moving tooth and the internal toothing, high levels of efficiency can be achieved. A high reduction ratio is advantageously achieved, so that it is possible to use high-speed, small-sized and inexpensive motors with a low output torque.

The adjusting device according to the invention is designed as a camshaft adjusting device which adjusts the camshaft in relation to a camshaft wheel driven by the crankshaft. It is only necessary to actuate the input shaft for the adjustment process; Due to the self-locking, no actuation or energization is required in the respective positions.

The invention is described below with reference to the accompanying drawings some embodiments explained. Show it:

Figure 1 is an exploded view of an adjustment device according to an embodiment of the invention.

FIG. 2 shows a cross section of the adjusting device according to FIG. 1;

3 shows a longitudinal section of the adjusting device according to FIG. 1;

Fig. 4 is a perspective view of the assembled

adjustment;

5a, b show a front view and a side view of a tooth according to the invention used in the adjusting device;

Fig. 6 is a cross section showing in particular in the

Internal teeth engaging teeth;

7 shows a cross section or superimposed representation, in particular of the teeth engaging in the external toothing;

8a-d show the movement of a tooth between adjacent webs;

9a-d show the movement of a tooth between the internal and external teeth;

10a-c front, side and rear view of the second component;

11a-c front, side and rear view of the first component;

12 is an exploded view of the device for adjusting a camshaft; 13 shows a cross section of an adjusting device according to a further embodiment.

1 as a first component, an adjusting device 1 has a first flange part 2, which can be connected to a camshaft via fastening holes 2.1. The first flange part 2 has a central hole 2.2 and webs 2.3 which are spaced apart in the circumferential direction and project in the axial direction, between which chambers 2.4 are defined. A second flange part 3 serving as a second component has fastening holes 3.1 for attachment to a camshaft wheel and an internal toothing 3.2 with teeth 3.3 and depressions 3.4 formed between the teeth 3.3. An input shaft 4 has a square area 4.1, on which spacers 4.4 are placed on two opposite sides and an elastic (possibly also with additional plastic pre-bending) tension spring element 4.3 is placed on another side. A circular disc 4.2 with a square-shaped central hole 4.5 is placed on the spacers 4.4 and the tension spring element 4.3. The disc 4.2 is pressed radially outwards by the tension spring element 4.3 and serves in its eccentric position as an eccentric disc 4.2. The spacers 4.4 slide on the square area 4.1 and / or the eccentric 4.2.

An eccentric ring 6 is placed around the eccentric disc 4.2 and performs a wobble movement when the input shaft 4 rotates. Teeth 7 are distributed in the circumferential direction in such a way that they bear on the eccentric ring 6 with inner contact surfaces 7.4 and extend away from the axis of rotation A. Outer contact surfaces 7.5 of the teeth 7 engage in the internal toothing 3.2 of the second component 3 when the input shaft 4 rotates. By prestressing the tension spring element 4.3, the teeth 7 are pressed into the internal toothing 3.2. An O-ring 8 is pre-tensioned around axially projecting projections 7.1 of the teeth 7 and causes each tooth 7 to rest with its inner contact surface 7.4 on the outside of the eccentric ring 6. In principle, the pre-tension can also be caused by the O-ring 8 or by the Tension spring element 4.3 (and the projections 7.1) are omitted since one of the two preloads is sufficient. A clamping ring 10 serves to compress the Components in the axial direction.

The guidance of the teeth 7 in the chambers 2.4 between the webs 2.3 can be seen in particular from FIG. 2 and FIGS. 8 and 9, since the teeth 7 are each in different, successive engagement positions when the eccentric disk 4.2 rotates. The lowest tooth 7 in FIG. 2 is in the innermost position in the radial direction, in which it rests with its outer contact surface 7.5 against the apex of a tooth 3.3 of the internal toothing 3.2. Here, the tooth 7 extends exactly in the radial direction. The top tooth 7 in FIG. 2 is in its outermost position in the radial direction, in which it is in engagement with a recess 3.4 (tooth gap) of the internal toothing 3.2. This tooth 7 as well as the other teeth of the lower half, which are shown in FIG. 7, experience a torque through the external toothing 5.2, which in the innermost position acting as the bottom dead center of the inward and outward movement of the teeth has a defined tilting of the Zahns causes. The teeth 7 move on circular arc paths between the innermost and outermost positions. 5, the teeth 7 taper from the inner contact surface 7.4 to the outer contact surface 7.5, which, as shown, can be flat or curved. Side surfaces 7.6 of the teeth advantageously have concave side surface regions 7.7. The teeth 7 slide according to FIG. 8 with their side surfaces 7.6, essentially with the concave side surface region 7.7 on the webs 2.3. The webs 2.3 taper towards the axis of rotation A, are essentially triangular or wedge-shaped and advantageously also have concave side surface areas 2.6.

In the chambers 2.4, guides 2.7 are furthermore formed as depressions into which axially projecting lugs 7.9 of the teeth 17 engage. The lugs 7.9 are arranged approximately in the middle of the teeth 7 and extend in the axial direction opposite to the projections 7.1 arranged at the lower end of the teeth 7. The guides 2.7 taper towards the axis of rotation A, so that the lugs 7.9 are accommodated in the innermost position of the teeth 7 essentially without play and form a defined pivot point for the teeth 7. The circular arc-shaped outward and inward movements of the teeth 7 are caused by the widening of the guides 7.7 towards the outside. made possible.

The external gear 5 is designed to be torsionally rigid or in one piece with the second flange part 3. In the representations of Figures 2 and 7, the external gear 5 and the eccentric ring 6 are shown superimposed. The external toothing area 5.2 of the external gear 5 with teeth 5.3 and recesses 5.4 formed between them (tooth gaps) serves as a control surface. The number of tooth gaps 5.4 of the external toothing 5 can, for. B. be one higher than the number of teeth 7 and the number of teeth 7 again equal to the number of webs 12.3 and one less than the number of teeth 3.3 of the internal toothing 3.2 of the second flange part 3. The inner contact surfaces 7.4 of the teeth 7 come close to their radially inner position, i.e. in the lower teeth of FIG. 2 or the teeth 7 shown in FIG. 7, in contact with side flanks of the teeth 5.3 of the external gear 5.

A defined rotation of the teeth 7 in their innermost position corresponding to a bottom dead center is achieved by the positive reception of the inner contact surfaces 7.4 of the teeth 7 on the external gear 5; alternatively, a frictional engagement of the teeth 7 on a with z. B. the input shaft 4 torsionally rigid control disc possible. There is a continuing support of the teeth 7 on which acts as a driving member ^'eccentric ring 6, by a functional separation of the driving action and the rotation or tilting of the teeth is reached effecting control surface.

According to the embodiment in FIG. 12, the two component 20 is made in one piece with the camshaft and the first component 30 is made in one piece with the camshaft gear 30.

In the embodiment shown in FIG. 18, essential parts correspond to the first embodiment and are therefore not described in more detail. The adjusting device has teeth 27 with lateral shoulder regions 27.1 and webs 22.3 with lateral shoulder regions 22.4, which come into contact with one another when the teeth 27 slide. By the shape the movement of the teeth can be adequately defined with the shoulder regions, so that, compared to the embodiment in FIGS. 1 to 11, the slot-pin guide is omitted. Thus, the entire management and power transmission takes place in one level, which z. B. tilting moments acting on the teeth from the plane can be avoided. In this embodiment, too, an external gear 15 is provided as the control gear. With its external toothing 15.2, this captures the lower areas of the teeth 27.

According to the invention, the external gear 5 or 15 can also be decoupled from the output shaft and, for. B. be freely rotating. In such an arrangement, the teeth 7 and 27 drive the freely rotating external gear 5 in their inward movement and are rotated by the external gear.

Claims

claims

1. adjusting device for adjusting a camshaft (20) relative to a camshaft gear (30) driven by a crankshaft, components (2, 3) provided for the adjustment process being arranged on the camshaft gear (30) and on the camshaft (20), and the adjusting device further comprises an input shaft (4), an eccentric drive element which can be driven by the input shaft

(4.2, 6), a first component (2) with webs (2.3, 22.3) spaced apart in the circumferential direction, between which chambers (2.4) are formed, a second component (3) with internal teeth (3.2, 13.2), and several teeth (7, 27), which are arranged in the chambers (2.4) at a distance from each other in the circumferential direction, each have an inner contact surface

(7.4) for contact with the drive member (6) and an outer contact surface

(7.5) for engagement in the internal toothing (3.2, 13.2) and can be adjusted in the radial direction when the input shaft (4) rotates, the components (2, 3) engaging the teeth (7, 27) in the webs (22.3) and in the internal toothing (3.2) can be rotated relative to one another in a self-locking manner, characterized in that when the input shaft (4) rotates, the teeth (7, 27) in the chambers (2.4) rotate in rotation axes of rotation parallel to the axis of rotation (A) of the components (2, 3) can be carried out.

2. Adjusting device according to claim 1, characterized in that at

Rotation of the input shaft (4) of each tooth (7, 27) can be guided radially inwards on a first circular arc-shaped path and subsequently radially outwards on a second circular-arc-shaped path.

3. Adjusting device according to claim 1 or 2, characterized in that a control surface (5.2) for engagement in the teeth (7, 27) is provided , with the control surface (5.2) being able to exert torques on the teeth (7) in order to carry out the rotary movements.

4. Adjusting device according to claim 3, characterized in that the teeth (7, 27) are supported radially inwards by the drive member (6) and the control surface (5.2) only in radially inner positions of a tooth (7, 27) in engagement with an inner contact surface (7.4) of the tooth (7, 27).

5. Adjusting device according to claim 3 or 4, characterized in that the control surface is a control tooth area (5.2, 15.2) of a control gear (5, 15), preferably an external gear.

6. Adjusting device according to claim 5, characterized in that the control toothing area is an external toothing area (5.2, 15.2) of an external gear (5.15) connected to the second component (13) in a rotationally fixed manner.

7. Adjusting device according to claim 5, characterized in that the control gear (5, 15) about the axis of rotation (A) of the components is freely rotatable.

8. Adjusting device according to one of claims 3 to 5, characterized in that an axially projecting nose (7.9) is formed on the tooth (7, 27), which is received in a guide (2.7) of the first component (2).

9. Adjusting device according to claim 8, characterized in that the guide is a recess (2.7) formed in the first component (2) between the webs (22.3).

10. Adjusting device according to claim 8 or 9, characterized in that the guide (2.7) tapers towards the axis of rotation.

11. Adjusting device according to claim 10, characterized in that the tooth (7, 27) is rotatable in a radially inner position about an axis of rotation defined by the nose (7.9).

12. Adjusting device according to one of claims 1 to 5, characterized in that the teeth (27) and webs (22) on their side surfaces serving as sliding surfaces have shoulder regions (22.4, 27.1) which come into contact with one another.

13. Adjusting device according to one of the preceding claims, characterized in that the webs 2.3, (22.3) taper towards the axis of rotation.

14. Adjusting device according to one of claims 1 to 3, characterized in that the control surface (15.2, 5.2) is formed on a control disk (5, 15) rotatable by the input shaft (4), preferably with frictional engagement between the control surface (5.2, 15.2) and the radially inner contact surfaces (7.4) of the teeth in their radially inner positions.

15. Adjusting device according to claim 14, characterized in that the control disc (5) engages only in the control surface (5.2) with the inner contact surfaces (7.4) of the teeth (7, 27).

16. Adjusting device according to claim 14 or 15, characterized in that the control disc (6) on the drive shaft (4) is rigidly fixed, preferably by a locking lug of the drive shaft (4), which is guided by a locking recess of the control disc (5) is.

17. Adjusting device according to one of the preceding claims, characterized in that the webs (2.3, 22.3) have a taper with concave side surfaces (2.5) in a radially central region (2.6).

18. Adjusting device according to one of the preceding claims, characterized in that the teeth (7, 27) each between one of the nere contact surface (7.4) having a radially inner region (7.2) and a radially outer region (7.3) having the outer contact surface (7.5), a central region (7.6) connecting the regions (7.2, 7.3) with at least partially concave side surfaces (7.7) for sliding and / or have rolling contact on the webs (2.4).

19. Adjusting device according to one of the preceding claims, characterized in that the drive member is an eccentric ring (6) which is slidably guided on an eccentric disc (4.2) of the drive shaft (4).

20. Adjusting device according to claim 19, characterized in that the eccentric ring (6) performs a wobble movement, preferably substantially without rotation, the inner contact surfaces of the teeth (7, 27) rolling on the eccentric ring (6).

21. Adjusting device according to one of the preceding claims, characterized in that the teeth (7, 17, 27) are biased in the radial direction.

22. Adjusting device according to claim 21, characterized in that the teeth (7, 17, 27) are biased towards the axis of rotation and have axially projecting projections (7.1, 17.1) or areas around which an elastic ring (8, biased towards the axis of rotation) 18) is laid.

23. Adjusting device according to claim 21, characterized in that the teeth (7, 17, 27) are biased radially outwards and a tension spring element (4.3) is arranged between an eccentric disc (4.2, 14.2) and the input shaft (4, 14) , which presses the eccentric disc (4.2, 14.2) radially outwards from the input shaft (4, 14).

24. Adjusting device according to claim 23, characterized in that the tension spring element (4.3) by at least partially plastic deformation between the input shaft (4), preferably a flattened th area (4.1) of the input shaft (4), and the eccentric disc (4.2, 14.2) is introduced.