RO133101A2 - Bearing for motor vehicle - Google Patents

Abstract

The invention relates to a bearing for a motor vehicle. According to the invention, the bearing comprises two races (1 and 4), an outer one and an inner one, and some rolling bodies (2) which are radially arranged between the two outer and inner races (1 and 4) and which are guided in relation to one another in a cage (3), where the inner race (4) is indirectly antirotatively arranged on a shaft (20) and has a plurality of recesses (24) having placed therebetween some piston bushes (6), where each such piston bush (6) is provided to accommodate and axially guide a piston (14) on an end face (25) of the inner race (4), where the said piston (14) can be actuated, at an axial end (30), by a slide disc (7) which is placed in an inclined position in relation with a bearing axis (A), between the axial end (30) of the piston (14) and the slide disc (7) there being a receiving element (11) meant to receive the piston (14), where, upon a rotary motion of the inner race (4), the receiving element (11) is guided in a sliding manner on the slide disc (7) for actuating the piston (14) and the rotary motion of the inner race (4) is alternately convertible into a linear movement of the piston (14) inside the piston bush (6), to generate a hydraulic pressure.

Description

Bearing for a vehicle

The invention relates to a bearing for a motor vehicle, comprising an inner ring and an outer ring, in which the rolling bodies are arranged radially between the inner ring and the outer ring and are guided spaced apart in a cage.

A ball bearing is known from EP 18 95 177 A2, consisting of an inner ring assembly and an outer ring assembly. The bearing comprises an end side mounted upstream and an end side mounted downstream. The outer ring assembly comprises an outer ring, which is rotatably connected to the inner ring and to a plurality of rolling bodies, in which case the rolling bodies are arranged between the inner ring and the outer ring. Furthermore, the outer ring assembly comprises at least one secondary flow channel, which extends through the outer ring assembly.

The object of the present invention is to extend the functionality of a bearing.

This object is achieved by the features of the independent claim. Advantageous configurations result from the dependent claims, description and drawings.

A bearing according to the invention, for a motor vehicle, comprises an inner ring and an outer ring, in which the rolling bodies are arranged radially between the inner ring and the outer ring and are guided spaced apart in a cage, in which the inner ring is arranged anti - rotating at least indirectly on a shaft and having a plurality of first recesses having received in them piston bushes, in which each piston bushing is provided to receive and drive axially a piston on a first end face of the inner ring, wherein said piston, at an axial end, is actuated by a sliding disc disposed inclined towards a bearing axis, wherein between said axial end of said piston and the sliding disc a respective receiving element is made for receiving the piston, in which the respective receiving element, at a rotational movement of the inner ring, can be guided in a sliding manner on the sliding disc for actuating the respective piston iv and in which the rotational movement of the inner ring is alternatively transformable into a linear movement of the respective piston inside the piston sleeve, to generate a hydraulic pressure.

The bearing thus fulfills a dual function. On the one hand, the shaft is rotatably supported by the bearing and, on the other hand, the bearing acts as a hydraulic pump. Alternatively, the bearing may also be provided as an air pump for filling a compressed air accumulator. The inner ring is from 2017 00545

04/08/2017 preferably driven by the respective shaft. Preferably, the bearing has an additional adjusting spring for the positive connection between the inner ring and the shaft. In other words, the inner ring is arranged on the shaft so that it can be removed. In particular, this prevents a relative rotational movement between the inner ring and the shaft.

The plurality of prime recesses are made in particular as holes on the inner ring, which are arranged uniformly distributed on the circumference of the end face of the inner ring. In the first places, the piston sleeves are received in a stationary manner, in which case the piston sleeve is provided as a cylinder for the respective piston. Each piston actuated by the sliding disc is arranged with the possibility of axial guidance in the respective piston sleeve. Thus, the respective piston sleeve and the piston received in it constitute a piston-cylinder arrangement. For a uniform guidance of the respective piston inside the piston sleeve during a pressurization, the piston has at least partially on a tubular profile. To reduce the oil leakage between the bushing and the piston, piston rings can be additionally provided in the bearing. Furthermore, the piston and the receiving element may have an axial hole, corresponding to each other, for reducing the friction, in order to lubricate the parts of the bearing which are moving relative to each other in the piston-cylinder arrangement.

Each piston has, at one end away from the inner ring, a hinge head in the form of a ball, which is received on the receiving element. The receiving element preferably has a hinge cup made complementary to the hinge head. In other words, the piston forms a spherical joint with the receiving element. The piston with the spherical articulation head is limited to move freely depending on the configuration of the articulation cup. Moreover, the mobility of the piston depends on the angle at which the sliding disc is inclined with respect to the longitudinal axis. The receiving element further includes a bearing surface, which comes into axial contact on the sliding disc, in which case the receiving element has a complementary angle with respect to the sliding disc. Preferably, the receiving element is made of a friction reducing material, through which the piston can be actuated by the sliding disc.

Preferably, the sloping sliding disc is arranged stationary in the bearing through a first and a second tubular element, in which case both tubular elements are made as obliquely cut tubular cylinders and corresponding to the sliding disc. The sliding disc is preferably arranged axially between the two tubular elements. Both tubular elements have, at a contact face from the sliding disc, the same angle, which means that the angle of the sliding disc with respect to the longitudinal axis is predefined 2017 00545 04/08/2017. Thus, the angle of the sliding disc with respect to the longitudinal axis is dependent on the angle of the oblique contact face made with the two tubular elements.

Preferably, the receiving elements can be guided in a retaining plate spaced apart from each other in a sliding manner on the sliding disc. In other words, the receiving elements of the pistons slide with a defined distance between them on the surface of the sliding disc. The distance between the receiving elements is defined by the retaining plate, which receives the receiving elements. The receiving elements preferably have a circumferential eclipse, which is provided to engage the retaining plate through the back, in order to constantly press the receiving element, on an axial actuation of the respective piston, on the surface of the sliding disc. At a rotational movement of the inner ring, the piston sleeves rotate with the pistons guided in them. Due to the inclined sliding disc, for the generation of a hydraulic pressure, there is a permanent and continuous alternating pushing and removal of the pistons in the respective piston bushes, respectively. In other words, when removing the piston from the piston sleeve, the inner space of the piston sleeve and the tubular portion of the piston are filled with hydraulic oil. Moreover, by removing the respective, the volume that can be filled with hydraulic oil is increased. When pushing the piston into the piston sleeve, the volume that can be filled with hydraulic oil decreases again and the hydraulic oil is pressurized out of the piston sleeve.

The retaining plate is preferably prestressed by means of an elastic pretensioning element, as well as by means of at least one spring element relative to the sliding disc. That at least one spring element is made on an outer radius of the retaining plate. Advantageously, the at least one spring element is axially supported by an angular element, which is firmly connected to the sliding disc. The spring element can be made for example as a corrugated spring. Alternatively, two or more spring elements may also be provided in the bearing, which press the retaining plate towards the sliding disc. Those at least two spring elements can be made for example as lamellar springs. The prestressing element is arranged on an inner radius of the retaining plate and rests on the inner ring. Preferably, the pretensioning element is made of an elastic plastic material. Thus, the receiving element is pressed at least indirectly by that at least one spring element and the elastic pretensioning element, with a constant pressure, on the sliding disc.

According to a preferred embodiment, the elastic pretensioning member is made as an obliquely cut tubular cylinder, in which case the pretensioning member has

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04/08/2017 at the end a protective cover designed to reduce friction between the pretensioning element and the sliding disc. The protective cover is arranged circumferentially on one of the end faces of the prestressing element from the retaining plate and thus allows a reduced frictional rotation of the retaining plate during a rotational movement of the inner ring around the longitudinal axis. The prestressing element has at one end face from the retaining plate the same angle with respect to the longitudinal axis as the sliding disc and the two contact faces of the tubular elements.

The bearing preferably has an additional cover element with an oil inlet and an oil outlet, in which case the cover element will come into contact at least indirectly with the second end face of the inner ring. The cover element is provided to axially fix the inner ring. In this case, the inner ring will come into particular contact with a protrusion of the shaft and is fixed axially in the bearing by means of the cover element.

Preferably, the inner ring has on a second end face a circumferential recess having received in it a sliding ring, in which case the sliding ring has a plurality of second slots, which are made to correspond to the first slots. In addition, the cover element further has a circumferential recess having at least partially received in it a valve plate, which has a third slot for the oil inlet and the oil outlet. The valve plate of the cover element and the sliding ring on the inner ring have a similar inner diameter and outer diameter and are rotatable relative to each other. The slide ring rotates with the inner ring, in which case the valve plate is arranged substantially anti-rotating on the cover element. The second recesses of the sliding ring are made parallel to the longitudinal axis of the shaft. Advantageously, both the slip ring and the valve plate are made of a material that reduces friction. In a preferred embodiment, both the slip ring and the valve plate have variable thicknesses made complementary to each other. This particularly simplifies the assembly of the bearing, as the possibility of damage due to the shape of the slip ring and the valve plate is reduced.

In addition, the third recesses of the valve plate are made as partially elongated holes on the circumference. In other words, a third slot interconnects at least one second slot, preferably two and particularly preferably three second slots. In addition, the third seats are made in such a way as to correspond to the oil inlet and the oil outlet. In other words, the oil inlet and the oil outlet go substantially together in 2017 00545

04/08/2017 taper in the axial direction of the valve plate until the oil outlet has a sufficient size for the connection of a supply line, respectively for the connection of an outlet line. Thus, the oil inlet and the oil outlet have a circumference on the valve plate which corresponds to the circumference of the partially circumferential elongated hole of the respective third seat of the valve plate.

The invention includes the technical teaching, that the bearing has at least two sealing rings, in order to seal the cover element relative to the inner ring. Both radially inside and radially outside the prime recesses, a circumferential sealing ring is provided on the second end face of the inner ring on the inner ring. In order to seal, the cover element is pressed onto the inner ring, for example by screwing at least one housing element with the bearing.

Other measures for improving the invention are represented in more detail below, together with a description of a preferred embodiment of the invention based on the six figures, in which case identical or similar elements are provided with the same reference numerals. Here it is shown in:

Figure 1 is a schematic sectional representation of the bearing according to the invention according to a first embodiment,

Figure 2 is a schematic perspective view of a sliding washer arranged axially between two tubular elements, of the bearing according to the invention according to Figure 1,

Figure 3 is a detailed sectional representation of a receiving element coming into contact with the sliding disc of the bearing according to the invention according to Figure 1,

Figure 4 is a schematic perspective view of the bearing according to the invention according to Figure 1, illustrated only in part,

Figure 5 is a schematic perspective view of a bearing valve cover according to the invention according to Figure 1, and

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Figure 6 is a schematic perspective view of a bearing cover element according to the invention according to Figure 1.

According to Figure 1, a bearing 23 according to the invention for a motor vehicle not shown here - comprises in one embodiment an inner ring 4 and an outer ring 1, in which case the rolling bodies are arranged radially between the inner ring 4 and the outer ring 1 and are guided spaced apart in a cage 3. The bearing is arranged in this case inside a housing 32. The inner ring 4 has six first recesses 24 with a piston sleeve 6 received in them. For perspective reasons, only two first seats 6 with a piston sleeve 6 are shown here.

The piston bushes 6 are provided to each receive a piston 14 on a first end face 25 of the inner ring 4 and to guide it axially. The pistons 14 can be actuated, at an axial end 30, by a sliding disc 7 arranged at an angle W with respect to a bearing axis A, in which case between the axial end 30 of the respective piston 14 and the sliding disc 7 a receiving element 11 is made for receiving the piston 14. The receiving elements 11, at a rotational movement of the inner ring 4, can be guided in a sliding manner on the sliding disk 7 for actuating the respective piston 14, in which case which the rotational movement of the inner ring 4 is alternately transformable into a linear movement of the respective piston 14 inside the respective piston sleeve 6, for generating a hydraulic pressure. In addition to the rotary bearing function of the shaft 30, the bearing 23 thus also fulfills the function of a hydraulic pump. The receiving element 11 receiving the piston 14 is explained in more detail in the description of Figure 3. The piston 14 together with the associated piston sleeve 6 forms a cylinder-piston arrangement.

The inner ring 4 has on a second end face 26 a circumferential recess 27 having received in it a sliding ring 5. With the sliding ring 5 a valve plate 19 will come into axial contact, having approximately the same inner diameter and outer diameter with he. In the present case, both the sliding ring 5 and the valve plate 19 have variable thicknesses made complementary to each other. This particularly simplifies bearing assembly, as the possibility of damage during assembly is reduced. Alternatively, the slip ring 5 and the valve plate 19 have the same constant thickness. It is also possible to make the sliding ring 5 and the valve plate 19 with different constant thicknesses.

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Furthermore, the bearing 23 has a cover element 17 with an oil inlet 17a and an oil outlet 17b. For perspective reasons, only the oil inlet 17a is illustrated here. The exact shape of the oil inlet 17a and the oil outlet 17b can be seen in Figure 6. The cover member 17 comes into contact with a second end face 26 of the inner ring 4 and fixes the axial position of the inner ring 4 It is secured here by a first and a second housing element 16, 21, which are screwed for example by screws - not shown here - axially with the cover element 17 and / or with the inner ring 4. The cover element 17 has additionally a circumferential recess 31, which partially receives at the end the valve plate 19. A hydraulic oil leak is prevented by the bearing 23 having at least two sealing rings 18a, 18b, to seal the cover element 17 relative to the inner ring 4. The first sealing ring 18a is arranged here radially inside the housing 24 arranged circumferentially on the inner ring 4. The second sealing ring 18b is arranged here radially outside the housing 24 arranged circumferentially on the inner ring 4.

In the case of bearing operation 23, during the rotational movement of the inner ring 4, the hydraulic oil - not shown here - is pumped by a pump - not shown here - into the oil inlet 17a of the cover element 17 and then reaches the bushing piston 6. By tilting the disc 7, the piston 14 is removed, by rotating the inner ring 4 in a first direction of the stroke of the piston 34, from the piston sleeve 6, which increases the volume of oil reception inside the sleeve of the piston 6. The hydraulic oil is pumped further into the internal space of the piston sleeve 6. After reaching the peak point on the sliding disc 7, the piston 14 is pushed back, by another rotation of the inner ring 4, into the piston sleeve 6, whereby the volume of receiving oil is reduced inside the piston sleeve 6. The hydraulic oil contained therein is compressed externally from the piston sleeve 6, in a second direction of the piston stroke 35 opposite to the first piston stroke direction 34. Thus, by turning the piston 14 in the piston sleeve 6 in the second piston stroke direction 35, a hydraulic pressure is generated.

According to Figure 2, the sloping sliding disc 7 is arranged anti-rotating in the bearing 23 by a first and a second tubular element 15a, 15b according to Figure 1. Both tubular elements 15a, 15b are made as obliquely and appropriately cut tubular cylinders. of the sliding disc 7. Due to the obliquely cut shape of the tubular elements 15a, 15b, an angle W is established represented in Figure 1, of the sliding disc 7 in relation to the longitudinal axis A. Moreover, by a modified shape of the elements of 2017 00545

04/08/2017 tabular 15a, 15b, a desired angle W of the sliding disc 7 can be set 7. The sliding disc 7, in this case together with the tubular elements 15a, 15b, during the assembly of the inner ring 4 and the outer ring 1, is supported axially by the outer ring on the housing 32.

In Figure 3, the receiving elements 11, at the rotational movement of the inner ring 4, can be guided spaced apart in a retaining plate 9, sliding on the sliding disk 7. For this, the receiving elements 11 have an eclipse circumferential 33, which is arranged axially between the sliding disc 7 and the retaining plate 9. The retaining plate 9 is prestressed axially by means of an elastic pretensioning element 13 and three spring elements 10 relative to the sliding disc 7. The retaining plate it is supported by the eclipse 33 of the respective receiving element 11 and presses the receiving element 11 axially in the direction of the sliding disc 7. The elastic pretensioning element 13 is made in this case of an elastic plastic material and is arranged radially inside the pistons 14 arranged circumferentially. The resilient prestressing element 13 is additionally supported, according to Figure 1, by the inner ring 4. Moreover, the resilient prestressing element 13 is made as an obliquely cut tubular cylinder, with an angle analogous to the angle W of the tubular elements 15a, 15b and the disc. slide 7 illustrated in Figure 2. At the end, the pretensioning element 13 has a protective cover 12 for reducing friction between the pretensioning element 13 and the sliding disc 7. In this case, the protective cover 12 is made of a plastic material which reduces friction. However, the protective cover 12 can also be made of metal.

For perspective reasons, only one spring element 10 is illustrated here, in which case the bearing 23 according to the invention has three spring elements 10, which are made as lamellar springs. The spring elements 10 are here made of flexible metal and are arranged radially outside the pistons 14 arranged circumferentially. The spring elements 10 further press axially on the sliding disc 7 the retaining plate 9 and the respective receiving element 11, in which case the spring elements 10 rest axially on a circumferential angular element 8, which is firmly connected to the sliding disc 7. In order to reduce friction, the angular element 8 may for example have a surface treatment or an integrated ring, on which the spring elements 10 slide when the inner ring 4 rotates. Alternatively, a circumferential spring element 10 is provided in the bearing 23, which is made like a wavy arc. Thus, by means of the elastic pretensioning element 13 and the spring elements 10, a constant axial pressure is generated with which the receiving elements 11 press on the sliding disc 7.

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According to Figure 4, the inner ring 4 is arranged anti-rotating on a shaft 20. For this purpose, the bearing 23 illustrated here only partially has an adjusting spring 22 for the positive connection between the inner ring 4 and the shaft 20. The sliding ring 5 has six second seats 28, which are made corresponding to the first seats 24 shown in Figure 1 and which are arranged evenly distributed on the circumference.

Figure 5 shows a perspective view of the valve plate 19, which is arranged between the cover element 17 and the slide ring 5. The valve plate 19 has two third recesses 29a, 29b, which are made as partially elongated holes on the circumference. The third seats 29a, 29b are made in such a way that through a third seat 29a the hydraulic oil is pumped from the oil inlet 17a shown in Figure 6, and through the other third seat 29b the hydraulic oil is pumped to the oil outlet 17b shown in Figure 6.

According to Figure 6, the oil inlet 17a as well as the oil outlet 17b are made to correspond to the third seats 29a, 29b shown in Figure 5. In this context, the oil inlet 17a the oil outlet 17b works in a manner substantially conical apart from each other in the direction of the valve plate 19.

List of reference numbers

15a, 15b outer ring rolling body cage inner ring sliding ring piston sleeve sliding disc angular element support plate spring element receiving element protective cap pretensioning element piston tubular element 2017 2017 00545

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16 housing element 17 lid element 17 oil inlet 17b oil outlet 18a, 18b sealing ring 19 valve plate 20 shaft 21 housing element 22 adjusting spring 2. 3 bearing 24 dwelling 25 towards the end 26 towards the end 27 depression 28 dwelling 29a, 29b dwelling 30 axial end 31 depression 32 housing 33 strap 34 piston stroke direction 35 piston stroke direction A bearing shaft W angle

Claims (10)

claims 1. A bearing (23) for a motor vehicle, comprising an inner ring (4) and an outer ring (1), in which the rolling bodies (2) are arranged radially between the inner ring (4) and the outer ring (1) and are guided spaced apart in a cage (3), characterized in that the inner ring (4) is arranged anti-rotating at least indirectly on an axis (20) and has a plurality of first recesses (24) having received bushes therein piston sleeve (6), in which each piston sleeve (6) is provided to receive and guide axially a piston (14) on a first end face (25) of the inner ring (4), in which said piston ( 14), at an axial end (30), is operable by a sliding disc (7) arranged inclined towards a bearing axis (A), in which between the axial end (30) of the respective piston (14) and the disc sliding member (7) is provided with a respective receiving element (11) for receiving the piston (14), wherein said receiving element (11), at a rotational movement of the of the inner ring (4), can be guided in a sliding manner over the sliding disc (7) for actuating the respective piston (14) and in which the rotational movement of the inner ring (4) is alternately transformable into a linear movement of the of the respective piston (14) inside the piston sleeve (6), for generating a hydraulic pressure. Bearing (23) according to claim 1, characterized in that said receiving elements (11) can be guided in a support plate (9) in a manner spaced apart on the sliding disc (7). . Bearing (23) according to claim 2, characterized in that the support plate (9), by means of a resilient prestressing element (13) and at least one spring element (10), is prestressed on the sliding disc ( 7). Bearing (23) according to claim 3, characterized in that the elastic pretensioning element (13) is made as an obliquely cut tubular cylinder, wherein the pretensioning element (13) has a protective cover (12) on the front for reducing friction between the pretensioning element (13) and the sliding disc (7). and 2017 00545 08/04/2017 Bearing (23) according to one of the preceding claims, characterized in that the inner ring (4) at a second end face (26) has a circumferential recess (27) having received in it a sliding ring (5), in which the slip ring (5) has a plurality of second seats (28), formed to correspond to the plurality of first seats (24). Bearing (23) according to one of the preceding claims, characterized in that the inclined sliding disc (7) is arranged fixed in the bearing (23) by a first and a second tubular element (15a, 15b), in which the two tubular elements (15a, 15b) are each formed as a tubular cylinder cut obliquely and corresponding to the sliding disc (7). Bearing (23) according to one of the preceding claims, characterized in that the bearing (23) further has a cover element (17) having an oil inlet port (17a) and an oil outlet port (17b), wherein the cover element (17) will come into contact at least indirectly on the second end face (26) of the inner ring (4). Bearing (23) according to claim 7, characterized in that the cover element (17) further has a circumferential recess (31), with a valve plate (19) partially received frontally therein, which has a third seat (29a, 29b) for the oil inlet (17a) and the oil outlet (17b). Bearing (23) according to one of the preceding claims, characterized in that the bearing (23) has at least two sealing rings (18a, 18b) for sealing the cover element (17) relative to the inner ring (4). Bearing (23) according to one of the preceding claims, characterized in that the bearing (23) further has an adjusting spring (22) for the positive connection between the inner ring (4) and the shaft (20).