EP2880332A1

EP2880332A1 - Wheel brake disc

Info

Publication number: EP2880332A1
Application number: EP13739467.2A
Authority: EP
Inventors: Christian Mosbach; Florian Walther
Original assignee: Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Current assignee: Knorr Bremse Systeme fuer Schienenfahrzeuge GmbH
Priority date: 2012-08-03
Filing date: 2013-07-23
Publication date: 2015-06-10
Also published as: JP2015527540A; WO2014019895A1; UA112710C2; KR20150040303A; US20150232108A1; AU2013298720B2; JP6226984B2; RU2644821C2; CN104641141A; AU2013298720A1; BR112015002038A2; CN104641141B; DE102012015378A1; RU2015107225A; US9669849B2

Abstract

A wheel brake disc for a wheel of a rail vehicle, wherein the wheel has a wheel web, on which friction rings (4, 5) are supported which are fastened to the wheel web by way of connecting means, wherein each friction ring (4, 5) has a plurality of spring elements (13, 34) which are arranged in each case on the circumference of the friction rings (4, 5), wherein, in the mounted state of the wheel brake disc, the spring elements (13) are arranged in each case between the friction rings (4, 5) and the wheel web.

Description

wheel brake

The present invention relates to a wheel brake disc according to the preamble of claim 1.

Such wheel brake disks, as used for example in rail vehicles are known in the prior art. In DE 44 17 813, the two friction rings are centered by sliding blocks acting in a form-fitting manner in the radial direction, so that the centering of the friction rings is also maintained by heating during the braking process. So that the deformation of the friction rings due to the thermal load does not affect a conical deformation of the friction rings, cooling ribs are mounted on the friction rings over which the friction rings are supported on the wheel disc of the rail vehicle wheel. The sliding blocks have integrated radial springs in the form of feather keys. The feather keys allow shifts due to the thermal expansion during braking. The screw connections with which the friction rings are fastened to the wheel disk are equipped with tapered clamping disks for increasing the elasticity and reducing the setting amount.

The DE 42 1 1 847 is also dedicated to the subject, to compensate for the thermal stresses caused by the braking process due to the heat input. For this purpose, it is proposed in DE 42 11 847 that centering rings inserted between the connecting means and the walls of the holes with radial pretension are made of an elastic material which loses its consistency when heated in accordance with the operating temperature of the brake disk. The centering ring are arranged in the component that expands when heated. This is the case with the friction rings.

In DE 100 47 980 is also on the required radial displaceability of the connecting pin relative to the present invention concentric to the connection tion bolt arranged sliding blocks to compensate for heat-related expansion and contraction.

Due to the design of a wheel brake disc, in which the wheel brake disc is formed by screwing two friction rings with the Radsteg, wherein the Radsteg is symmetrical between the two friction rings, the screwing of the two friction rings of a wheel brake in the course of braking with a thermal expansion of the Brake disc resulting thermal and mechanical additional force applied.

As a result, the brake disk is deformed, it "bulges" and thereby expands the screw by a corresponding amount.In addition, the brake disc on the Radsteg slips outward in the radial direction.This additional force and the associated relative movement of the disc with screw corresponding results Performance limits of a corresponding wheel brake disc with regard to brake intensity and braking power These parameters must be within an appropriate range of the life of the brake disc.

The brake disk can be buried in the wheel or in the wheel web, for example, by the acting contact pressure of the screw and the radial expansion resulting from the thermal load. As a result, there is a risk that this generates a wear on the wheel web in terms of amount, which leads to the complete Vorspannkraftverlust the screw, so that the screw can no longer fulfill their function.

Furthermore, due to the additional, cyclic longitudinal expansion of the screw due to the thermo-mechanical stress of the friction rings, the screw may permanently break.

The invention is therefore based on the object to provide a wheel brake which avoids the aforementioned disadvantages of the prior art. The invention solves this problem by providing a wheel brake disc for a wheel of a rail vehicle, in which each friction ring has a plurality of spring elements arranged respectively on the circumference of the friction rings, wherein the spring elements in the mounted state of the wheel brake between each of the friction rings and the Radsteg are arranged.

The invention is therefore based on the idea of designing the wheel brake disc in such a way that the primary screw connections - that is the screw connection with which the friction rings are connected to the wheel web - are free of relative movements resulting from the thermomechanical load and the spring elements thus compensate for the deformation.

According to the invention, the spring element is designed in such a way that all occurring relative movements amount in terms of elastic deformation of the spring elements. As a result, the primary screw connection of the wheel brake disk and thus also the spring elements do not perform any relative movement in the direction of the wheel web over the region of the connection to the wheel web.

Furthermore, according to the invention, the spring elements are designed so that the maximum area moment of inertia can act in the circumferential direction and thus only slightly deform the connecting elements due to the influence of the braking torque, but nevertheless permit radial expansion -also a parallel displacement of the friction surface to the wheel by thermal load , Further advantageous embodiments of the wheel brake disc according to the invention can be found in the dependent claims.

Embodiments of a wheel brake disc according to the invention are illustrated in the drawings and will be described in more detail below.

Show it: a front view of a wheel brake disc of the prior art of Figure 1, in which the friction rings are bolted and are inserted for centering sliding blocks. a sectional view of a wheel brake disc of the prior art of Figure 1, in which the friction rings are bolted and are inserted for centering sliding blocks. a further sectional view of a wheel brake disc from the prior art of Figure 1, in which the friction rings are bolted and are inserted for centering sliding blocks. a spatial front view of a friction ring with inserted band-shaped spring elements of a wheel brake disc according to the invention; an enlarged detail of the front view of Figure 4 a friction ring with a variant of the inserted band-shaped spring elements of a wheel brake disc according to the invention. a spatial front view of a variant of a band-shaped spring element of a wheel brake disc according to the invention; a spatial front view of a friction ring with inserted band-shaped spring elements in a further embodiment of a wheel brake according to the invention; an enlarged detail of the front view of Figure 7 of a friction ring with a further embodiment of the inserted band-shaped spring elements of a wheel brake disc according to the invention.

FIG. 9 shows a perspective front view of a further embodiment variant of a band-shaped spring element of a wheel brake disk according to the invention; In Figures 1, 2 and 3, the basic structure of a wheel brake disc 1 according to the prior art is shown, as used in particular for rail vehicles. At the wheel web 2 of the wheel 3 of a rail vehicle, a friction ring 4, 5 is arranged symmetrically to the symmetry axis of the wheel web 2. The friction ring 4, 5 is supported by ribs 6 on the Radsteg 2 from. The friction rings 4, 5 are screwed to the Radsteg 2 with screws that are designed as expansion bolts. In order to minimize the thermal expansion of the screw, the screw head 7 is supported on a sleeve 8, which is embedded in the friction ring 5 via a countersink. The nut 9 is also designed as a sleeve, which is embedded in a reduction in the friction ring 4. The positive connection of the connection is generated by separate sliding blocks 10.

4 and 5 show by way of example a spatial front view of a friction ring 4, 5 with inserted spring elements 13 of a wheel brake disk 1 according to the invention. The friction ring 4, 5 has Radstegseitig ribs or cams 14, 15, 16, 17, 18, 19 with different geometry, which rise in relation to the Radsteg in the radial direction and extend substantially in the axial direction. The ribs or cams 14, 15, 16, 17, 18, 19 are arranged in two defined, recurring patterns on the friction ring 4, 5 which are arranged several times in an integer pitch-preferably six times-on the circumference of the friction ring 4, 5 are. The first pattern is formed by the ribs 14, 15 and 16, while the second pattern is formed by the cams 17, 18 and 19. The patterns are each separated by the arrangement of a spring element 13, so that when a 6-fold division of the pattern 12 spring elements are arranged uniformly on the circumference of the friction ring 4, 5. In principle, it is also possible according to the invention to arrange fewer or more than twelve spring elements 13 on the circumference of the friction ring 4, 5 and thus also the patterns less than or more than six times. The geometry of the ribs or cams 14, 15, 16, 17, 18, 19 is selected so that a deformation of the friction ring 4, 5 due to the introduced by the braking heat in relation to the wheel 3 axial direction in terms of magnitude as evenly as possible. In addition, the geometry of the ribs or cams 14, 15, 16, 17, 18, 19 is selected so that upon rotation of the wheel 3 as high as possible. he heat dissipation is done by convection. Furthermore, the ribs or cams 14, 15, 16, 17, 18, 19 are fundamentally designed so that they bear on the wheel web 2 only at their respective two ends 20, so that the heat input from the friction rings 4, 5 into the wheel web 2 is reduced to a minimum by the geometric design of the ribs or cams 14, 15, 16, 17, 18, 19.

The pattern formed by the ribs 14, 15 and 16 is a symmetrical pattern whose line of symmetry is formed by the symmetry line of the rib 15. Rib 15 is a straight rib that extends in radial direction with respect to the wheel 3. The rib 15 has a lower height in its central portion than at its two ends 20, so that the rib 15 only touches the wheel web 2 via its ends 20. Both ribs 14, 16 have an arcuate central portion, the central portion having a lower height than the respective ends 20 of the ribs 14 and 16. The recessed central portion of the ribs 14, 16 continues in each case in the direction of the ends 20 of the rib 14, 16 still beyond the arc away. The vertex of the arc of the central portion of the ribs 14 and 16 respectively points to the rib 15, so that a symmetrical pattern is formed whose line of symmetry is formed by the symmetry line of the rib 15.

The pattern formed by the cams 17, 18 and 19 is a symmetrical pattern whose line of symmetry is formed by the line of symmetry of the rib 18. The rib 18 has a cam-shaped central portion, wherein the rib 18 extends in total in relation to the wheel 3 radial-radial direction. The rib 18 has a lower height in its middle section than at its two ends 20, so that the rib 18 only touches the wheel disc 2 via its ends 20. The recessed central portion of the rib 18 is stepped, so that the central portion in the cam-shaped central part of the rib 18 has a smaller depth than in the two rib parts, which are outside the cam-shaped central portion of the rib 18. The cam-shaped middle part is thereby traversed by the recess groove-shaped, wherein the groove width corresponds to the width of the rib members, which are located outside of the cam-shaped central part of the rib 18 spaced on both sides of the rib 18, the pairs of cams 17 and 19 extend 19. Both cam pairs 17, 19 have a basic geometry of the rib 15 corresponds, wherein the height of the central portion of the cam pairs 17 and 19 coincides with the height of the wheel disc facing plane of the friction rings 4, 5, from which the ribs or cams 14, 15, 16, 17, 18, and 19 rise, so that no continuous ribs, but each two pairs of cams 17 and 19 result. The respectively inner section of the cams of a cam pair 17, 19 has a lower height than the end section 20 of the respective cam, so that only the respective end section 20 of the cam is supported on the wheel web 2 in the mounted state of the friction linings 4, 5. The recessed central portion of the ribs 14, 15, 16, the recessed portion of the two rib portions which lie outside the cam-shaped central portion of the rib 18 and the recessed portions of the cam pairs 17 and 19 each have an identical depth with respect to the contact plane of the friction ring 4, 5 with the Radsteg 2 and an identical width with respect to the width of the friction ring 4, 5 in relation to the wheel 2 radial direction. The recess is in each case symmetrical to the ring width of the friction ring 4, 5 executed, so that the contact surface of the respective ribs or cams 14, 15, 16, 17, 18, 19 is as small as possible, but is large enough to the surface pressure between the friction ring 4, 5 and Radsteg 2 to keep to a tolerable degree.

In each case between the ribs or cams 16 and 17 and between the cams or ribs 19 and 14 are in the embodiment shown in Figures 4, 5 and 6 of a wheel brake disc according to the invention 1 pairs of cams 21 and 22 arranged on the friction rings 4, 5. The cam 21 is machined on its radially outer side with respect to the wheel 3, while the cam 22 is machined on its radially inner side with respect to the wheel 3, the axial boundary of the machining being formed by the solid part of the respective friction ring 4, 5 is, so that a corresponding shoulder of the machined surface is formed in the axial direction. The spring element 13 of this embodiment, which is shown in isolation in FIG. 6, is a bent part made of a flat or strip material and has a geometry which is essentially formed by three plateaus 23, 24, 25 which are defined by two "valleys". 26, 27, wherein the two ends of the spring element 13 are formed by two legs 28, 29. The plateaus 23, 24, 25 All on the same horizontal plane and thus in the assembled state of the wheel brake disc 1 on the wheel web 2 at. The legs 28, 29 close by a 90 ° bend to the respective outer plateaus 23, 25 and have a length in relation to the wheel 3 axial length which is greater than the depth t of the valleys 26, 27 of the Spring element 13. As a result, the valley bottom is not on the friction rings 4, 5 respectively. The geometry of the spring element 13 results in an axis of symmetry which extends perpendicularly through the plateau 24 of the spring element 13, whereby embodiments with non-symmetrical design of the spring element 13 are possible. The bore 30, whose axis of symmetry coincides with the symmetry axis of the spring element 13 in the example shown in FIG. 4 or FIG. 5 respectively, engages in the mounted state of the friction rings 4, 5 in each case a screw (not shown) with which the friction rings 4 5 are fixed to the wheel web 2 and forms the primary screw connection of the friction rings 4, 5 with the wheel web 2. Accordingly, the friction rings 4, 5 also have a bore 30 coaxial bore 31.

On the machined surfaces of the cams 21, 22 is supported in relation to the wheel 3 axial direction in each case a leg 28, 29 of the spring element 13, each of which forms the outer boundary of the spring element 13 in relation to the wheel 3 radial direction. The spring element 13 is connected via the legs 28, 29 and corresponding holes 32, 33 with suitable connecting elements (not shown) with the cams 21, 22.

According to the invention, the spring element 13 is designed such that all relative movements that occur are in the range of the elastic deformation of the spring elements 13. As a result, the primary screw connection of the wheel brake disk 1 does not execute a relative movement in the direction parallel to the wheel web 2, which completely prevents wear on the wheel web 2.

In addition, the spring elements 13 according to the invention are designed so that their maximum area moment of inertia can act in the circumferential direction and so the spring elements 13 are only slightly deformed by the influence of the braking torque but still allow a radial expansion -also a parallel displacement of the friction surface to the wheel by thermal load , FIG. 7 shows a further embodiment variant of a friction ring 4, 5 with inserted spring elements 34 of a wheel brake disk 1 according to the invention.

Notwithstanding the embodiment of the spring element 13 shown in Figures 4, 5 and 6, the spring element 34, that is also made of a flat or strip material bent part, although also plateaus 24, 25, 26, but the plateau 25 is higher than that Plateaus 24 and 26, so that the spring element 34 rests in the mounted state of the wheel brake disk 1 only with the plateau 25 on the wheel web 2. Moreover, the plateaus are not separated by valleys 26,27, but by junctions 35,36 connecting the two different height levels of the plateau 25 and the two plateaus 24,26.

The plateaus 24 and 26 of the spring element 34 each have at their ends at least two free accordion-shaped turns 37 of the steel strip, which extend in relation to the wheel in the axial direction and act as a spring. The windings 37 open at both ends in each case as a free end 38, 39, wherein the free ends 38, 39 are each cast in the friction ring 4, 5 and are so firmly bonded to the friction ring 4, 5. A separate attachment of the spring element 34 via cams 21, 22 -as in the spring element 13- thereby eliminates.

In a further variant of the invention, not shown, the spring elements 34 can be integrally cast by corresponding cores together with the friction rings 4, 5. This is especially true in the manufacture of the friction rings 4, 5 from a ductile cast material, such as e.g. Cast iron with spheroidal graphite possible.

In order to improve the sound damping properties of the friction rings 4, 5, the spring elements 13, 34 according to the invention can also be designed as a double-layered. From the resulting during a braking oscillations of the friction rings 4, 5 and the resulting structure-borne noise is effectively attenuated in the case by the friction of the two spring element layers together. LIST OF REFERENCE NUMBERS

1 wheel brake disc

2 wheel bridge

3 wheel

4 friction ring

5 friction ring

6 rib

7 screw head

8 sleeve

9 mother

10 sliding block

1 1 groove

12 ring

13 spring element

14 rib

15 rib

16 rib

17 cam pair

18 rib

19 cam pair

20 end

21 cam

22 cam

23 plateau

24 plateau

25 plateau

26 valley

27 valley

28 thighs

29 thighs

30 hole

31 hole

32 bore

33 hole

34 spring element

35 transition

36 transition

37 turn

38 Free end

39 Free end

Claims

claims

1 . Wheel brake disc (1) for a wheel (3) of a rail vehicle, wherein the wheel (3) has a wheel web (2) on which friction rings (4, 5) are supported, which are fastened to the wheel web (2) by connecting means, characterized in that each friction ring (4, 5) has a plurality of spring elements (13, 34) arranged on the circumference of the friction rings (4, 5), the spring elements (13, 34) in each case between the friction rings in the mounted state of the wheel brake disk (1) (4, 5) and the Radsteg (2) are arranged.

2. wheel brake disc (1) according to claim 1, characterized in that the spring elements (13, 34) are arranged at the points at which the at least one friction ring (4, 5) is connected by connecting elements with the Radsteg (2).

3. wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) have a band-shaped basic geometry.

4. Wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) are arranged uniformly on the circumference of the at least one friction ring (4, 5).

5. wheel brake disc (1) according to one of the preceding claims, character- ized in that the spring elements (13, 34) twelve times on the circumference of the at least one friction ring (4, 5) are arranged.

6. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the number of spring elements (13, 34) which are arranged on the circumference of the at least one friction ring (4, 5) corresponds to a prime number.

7. wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) each with a friction ring (4, 5) in the mounted state of the wheel brake disc (1) are non-positively connected.

8. wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) on cams (21, 22) are supported.

9. wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) on cams (21, 22) are supported, which are each arranged on the friction ring (4, 5).

10. Wheel brake disc (1) according to any one of the preceding claims, character- ized in that the cams (21, 22) which are each arranged on the friction ring (4, 5) are integrally connected to the friction ring (4, 5) ,

1 1. Wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34) are each connected to a friction ring (4, 5) cohesively.

12. wheel brake disc (1) according to one of the preceding claims, characterized in that the spring elements (13, 34), in each case with a friction ring (4, 5) are integrally connected by a casting process.

13. Wheel brake disc (1) according to one of the preceding claims, characterized in that the friction rings (4, 5) each have at least one pattern of ribs or cams (14, 15, 16, 17, 18, 19).

14. wheel brake disc (1) according to one of the preceding claims, characterized in that the at least one pattern of ribs or cams (14, 15, 16, 17, 18, 19) respectively uniformly on the circumference of a friction ring (4, 5) is distributed.

15. Wheel brake disc (1) according to one of the preceding claims, characterized in that the at least one pattern of ribs or cams (14, 15, 16, 17, 18, 19) each twelve times on the circumference of a friction ring (4, 5 ) is distributed.

16. Wheel brake disc (1) according to one of the preceding claims, characterized in that the number of at least one pattern of ribs or Cam (14, 15, 16, 17, 18, 19), which is arranged in each case on the circumference of a Reibnnges (4, 5) corresponds to a prime number.

17. Wheel brake disc (1) according to one of the preceding claims, character- ized in that the at least one pattern of ribs or cams (14, 15, 16, 17, 18, 19) has a symmetry.

18. Wheel brake disc (1) according to one of the preceding claims, characterized in that the friction rings (4, 5) each have two different patterns of ribs or cams (14, 15, 16, 17, 18, 19).

19. Wheel brake disc (1) according to one of the preceding claims, characterized in that the at least one pattern of ribs or cams (14, 15, 16, 17, 18, 19) in each case six times on the circumference of a friction ring (4, 5 ).

20. Wheel brake disc (1) according to one of the preceding claims, characterized in that the arrangement of the two different patterns of ribs and cams (14, 15, 16, 17, 18, 19) on the circumference of the friction rings (4, 5) each - Because before or after the position of a spring element (13, 34) alternates.

21. Wheel brake disc (1) according to one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) on the circumference of the friction rings (4, 5) in each case with respect to the wheel (3 ) are arranged radial direction.

22. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) on the circumference of the friction rings (4, 5) respectively in relation to the wheel (3) Radial radial direction are arranged.

23. Radbremsscheibe (1) according to any one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) on the circumference of the friction rings (4, 5) each symmetrical to the width of the friction rings ( 4, 5) are arranged.

24. Radbremsscheibe (1) according to any one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) on the circumference of the friction rings (4, 5) by a primary molding process in one piece with one Friction ring (4, 5) are made.

25. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) have a uniform height at their ends (20).

26. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the ribs and cams (14, 15, 16, 17, 18, 19) between their respective ends (20) have a height which is less than the height at their respective ends (20).

27. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the friction rings (4, 5) respectively over the ends (20) of the ribs and cams (14, 15, 16, 17, 18, 19) on Radsteg ( 2) of the wheel (1) abut.

28 wheel brake disc (1) according to any one of the preceding claims, character- ized in that the spring elements (13, 34) are executed double-layered.

29. Wheel brake disc (1) according to one of the preceding claims, characterized in that the spring element (34) has at least one free turn (37).

30. Wheel brake disc (1) according to any one of the preceding claims, characterized in that the spring element (13, 34) in the assembled state of the wheel brake disc (1) via at least one plateau (23, 24, 25) on the wheel web (2).

31. Wheel brake disc (1) according to one of the preceding claims, characterized in that the spring element (13, 34) is designed so that its maximum area moment of inertia acts in the circumferential direction of the wheel brake disc (1).

32. Wheel (3) with a wheel brake disc (1) according to one of the preceding claims.