spring brake

Abstract

The invention relates to a spring brake having a coil spring for exerting a force on a brake element in order to generate a braking action, and having a spring support for accommodating the coil spring. The spring support has a guide region which extends along the coil spring and a telescopic region which extends along the coil spring, wherein the telescopic region is located between the guide region and the brake element and has a larger cross section than the guide region.

Description

Technical Field

[0001] The present invention relates to a spring brake as described in the preamble of claim 1. Background Technology

[0002] The spring brake is characterized in that a force is applied to the braking element by a helical spring to generate a braking effect. The force applied to the braking element by the helical spring is converted into a braking effect by the braking element. Generally, the force applied to the braking element causes the braking element to move. The working surfaces formed by this movement come into contact with each other and press against each other. Friction pads are designed for this purpose on the working surfaces. The friction force generated between the working surfaces represents the final actual braking force.

[0003] The advantage of spring brakes is that braking force can still be applied to the braking element even if any auxiliary power supply is interrupted. This method allows the brake to close in the event of a power outage. This meets various application requirements and ensures the safe operation of technical equipment.

[0004] The helical spring that applies force to the braking element is typically located in the spring support of the spring brake. The spring support guides the movement of the helical spring along its extension direction. The extension direction of the helical spring is the direction in which the spring is expected to generate its elastic force during use. One of the main tasks of the spring support is to guide the spring along its extension direction when the brake is applied.

[0005] When the spring brake is in operation, the condition that typically affects the service life of the coil spring is material failure in the end region of the coil spring facing the braking element. In other words, material failure is the most frequent problem in spring brakes. Spring brakes are commonly used to provide fail-safe braking systems. For example, in the event of an auxiliary power outage as described above, material failure cannot guarantee the proper functioning of the spring brake. Summary of the Invention

[0006] The purpose of this invention is to demonstrate a spring brake that can ensure an extended service life of a helical spring.

[0007] This objective is achieved by a spring brake having the features of claim 1. The features of the dependent claims relate to advantageous embodiments.

[0008] According to the present invention, this objective is achieved by dividing the spring support into a guide area and a telescopic area extending along the helical spring, wherein the telescopic area is located between the guide area and the braking element, and its cross-section is larger than that of the guide area.

[0009] Wear of a coil spring is caused by the movement of the braking element perpendicular to the extension direction of the coil spring, resulting in increased deformation of the coil spring in the end region towards the braking element. The movement of the braking element is caused by the clearance typically present in the bearing or guiding braking element, coupled with the frictional force acting on the braking element perpendicular to the extension direction of the coil spring during braking. Therefore, the braking element can move not only along the extension direction of the coil spring according to its intended action, but also undergo additional movement, the direction of which depends on the direction of the frictional force generated when the brake is applied. According to the prior art, the movement of the braking element and the associated deformation of the coil spring only affect a very short region of the coil spring towards the end towards the braking element. This region is typically the area where the coil spring extends beyond the spring support. It generally includes only one single turn of the coil spring. The rest of the coil spring is supported by the spring support and is therefore unaffected by the deformation caused by the movement of the braking element perpendicular to the extension direction of the coil spring.

[0010] The solution of this invention is to add a telescopic zone to the spring support between the guide zone and the braking element. The cross-section of this telescopic zone is larger than that of the guide zone. In contrast, the guide zone of a conventional spring support can extend to its entire length, allowing the coil spring to move more strongly in a region perpendicular to the extension direction. Therefore, the movement of the braking element perpendicular to the extension direction not only causes deformation in the shortest section of the coil spring but also a significant change in its length. Consequently, material stress can be distributed over most of the coil spring after deformation. This method significantly reduces material stress, thereby substantially improving the service life of the coil spring.

[0011] In this invention, advantageously, the guide region of the spring support along the helical spring extends at least 20%, particularly at least 50%, and / or at most 95%, particularly at most 70%, along the extension length of the spring support. These dimensions of the guide region are suitable on the one hand to ensure reliable guidance of the helical spring, and on the other hand to allow for the extension of the telescopic region to achieve the effects of this invention.

[0012] Preferably, the extension zone of the helical spring extends along the spring support for at least 5%, preferably at least 30%, and / or at most 80%, preferably at most 50%, of the extension length of the helical spring. Extending the extension zone within the above parameter range achieves the effects according to the invention on the one hand, and provides a sufficiently long guide zone to ensure reliable guidance of the helical spring on the other.

[0013] Preferably, the spring brake is designed so that the coil spring does not contact the telescopic zone when the spring brake is applied. This design is particularly relevant to the cross-section of the selected telescopic zone. If the coil spring does not contact the telescopic zone of the spring support when the spring brake is applied, localized deformation of various areas of the coil spring can be avoided, which can lead to premature material failure.

[0014] Preferably, the spring brake is designed so that the coil spring does not undergo any plastic deformation when the spring brake is applied. This design also specifically relates to the design of the cross-section of the extension zone. Plastic deformation caused by the movement of the braking element perpendicular to the extension direction of the coil spring is particularly prone to causing premature wear and potential material failure of the coil spring.

[0015] A hole is designed into the spring support. This hole can be located on the magnet housing, for example, in an electromagnetically actuated spring brake. This hole design allows for lower cost. Other designs for the spring support are also feasible.

[0016] Spring supports can have a stepped cross-section between the guide zone and the telescoping zone. The stepped cross-section design offers the advantage of ease of manufacturing. For example, spring supports can be designed with stepped holes.

[0017] Optionally, the telescopic region can be designed to gradually decrease in size towards the guide region. Preferably, in this invention, the telescopic region can be designed in a conical shape. The advantage of this design is that the error caused by the movement of the braking element is greatest in the end region towards the braking element, and the range of motion of the helical spring is also greatest.

[0018] The spring support, guide zone, and / or telescopic zone can be designed with a circular cross-section. This design is particularly advantageous in the guide zone because the cross-section of a conventional coil spring is also circular. To ensure optimal guidance of the coil spring, it is preferable that the cross-section of the guide zone is slightly larger than the cross-section of the coil spring. This is especially necessary because the cross-section expands when the coil spring is compressed. For example, when the cross-section is circular, the diameter of the guide zone can be approximately 0.5 mm larger than the diameter of the coil spring's cross-section in the unstressed state. If the spring support is designed with, for example, stepped holes, and the diameter of the telescopic zone is 1 mm larger than the diameter of the guide zone, the service life of the coil spring is significantly extended.

[0019] The telescopic zone can also have a non-circular cross-section. Preferably, the cross-section is designed to take into account the direction of movement of the braking element due to friction, which acts on the braking element during braking and typically points perpendicular to the extension direction of the coil spring. Therefore, for example, when designing a spring brake as a disc brake, it is particularly advantageous to have a larger cross-section of the telescopic zone compared to the guide zone cross-section in the circumferential direction of the spring brake and / or the rotating braking element, especially in the circumferential direction of the brake disc.

[0020] Preferably, it can be designed as an electromagnetically actuated spring brake. Electromagnetically actuated spring brakes typically use an auxiliary power source for release, and because they are spring brakes, they can be easily controlled electrically, have high operational reliability, and automatically shut off when the auxiliary power source is interrupted.

[0021] The braking element can be designed as an armature disc. The armature disc is a disc-shaped braking element, typically equipped with, for example, friction pads. The braking element is arranged around a shaft. Preferably, a rotary braking element, such as a brake rotor and / or brake disc, is arranged on this shaft. Particularly preferably, the rotary braking element is connected to the shaft, allowing it to move and / or rotate axially. To produce a braking effect, the braking element is pressed against the rotary braking element. Preferably, particularly in the case of an axially movable braking element, the braking element presses against a brake mating element, while simultaneously generating friction between the rotary braking element and the brake mating element. For this purpose, preferably, the braking element and / or the rotary braking element and / or the brake mating element are equipped with suitable friction pads.

[0022] According to the present invention, a spring brake can have multiple helical springs correspondingly mounted in multiple spring supports, and force applied to the braking element of the spring brake. In this case, preferably, the features and / or advantageous features according to the present invention are applicable to all spring support designs of the spring brake. Attached Figure Description

[0023] Reference Figures 1 to 6 The present invention will now be described in more detail.

[0024] Figure 1 This shows a cross-sectional schematic diagram of the spring support of a spring brake according to the prior art.

[0025] Figure 2 This diagram shows a cross-sectional view of a spring support for an exemplary spring brake according to the present invention, wherein the spring support has a stepped hole.

[0026] Figure 3 This diagram shows a cross-sectional view of a spring support for an exemplary spring brake according to the present invention, wherein the extension and retraction area of ​​the spring support is conical.

[0027] Figure 4 This diagram shows a cross-sectional view of an exemplary spring brake according to the present invention, wherein the spring support has a stepped hole.

[0028] Figure 5 This diagram shows a cross-sectional view of an exemplary spring brake according to the present invention, wherein the telescopic region is conical.

[0029] Figure 6 This diagram shows a top view of the spring support of an exemplary spring brake according to the present invention, wherein the cross-section of the telescopic region is non-circular. Detailed Implementation

[0030] According to the prior art, in the spring brake 1, the spring support 2 for the helical spring 3 typically has Figure 1 The design shown is illustrated. The helical spring 3 extends along its extension direction X. The extension direction X of the helical spring 3 is also the direction in which the helical spring 3 applies force to the braking element 4. In the example, the spring support 2 is a hole in the housing 5 of the spring brake 1. Due to tolerances and the resulting clearances, the braking element 4 moves along a direction of movement Y perpendicular to the extension direction X. As a result, the end region of the helical spring 3 facing the braking element 4 presses against the wall of the spring support 2. This generates strong mechanical stress in the end region of the helical spring 3 facing the braking element 4, ultimately leading to a shortened service life of the helical spring 3.

[0031] Figure 2 This illustrates an embodiment of the spring support 2 according to the invention. In the example, the spring support 2 is designed as a stepped hole. The spring support 2 according to the invention is divided into a guide region 6 and a telescopic region 7. The cross-section of the telescopic region 7 is larger than that of the guide region 6. In this way, the helical spring 3 can be properly guided along its extension direction X through the guide region 6. At the same time, the braking element 4 towards the end of the helical spring 3 can move freely, avoiding an increase in direct stress on the end region of the helical spring 3 towards the braking element 4.

[0032] Figure 3 This illustrates another embodiment of the invention. In this embodiment, the telescopic region 7 is conical. According to the invention, it is related to... Figure 2 The effects of the illustrated embodiments are essentially the same. The helical spring 3 has a greater range of motion along the direction of movement Y of the braking element 4 in the end region toward the braking element 4.

[0033] Figure 4 and Figure 5 This shows a cross-sectional schematic diagram of an exemplary spring brake 1. Figure 4 The spring brake 1 shown has a spring support 2 designed with stepped holes that basically correspond to... Figure 2 The exemplary embodiment shown. Accordingly, Figure 5The exemplary spring brake 1 shown has a conical telescopic region 7, the design of which is basically corresponding to Figure 3 The exemplary embodiment shown includes a telescopic region 7. In the example, the braking element 4 is an armature disc. When the brake is actuated, the braking element 4 moves parallel to the extension direction X of the coil spring 3. In the example, the braking element 4 acts on the rotary braking element 8 or the brake rotor, and then presses against the brake mating element 9. Advantageously, the braking element 4 and / or the rotary braking element 8 and / or the brake mating element 9 are equipped with friction pads 10. The rotary braking element 8 is mounted relative to the spring brake 1 and is movable along the extension direction X of the coil spring 3.

[0034] Figure 6 This illustrates another embodiment of the spring brake 1 according to the present invention. In this spring brake 1, the cross-section of the telescopic region 7 is larger than that of the guide region 6, but the cross-section is not circular. The telescopic region 7 is designed as an elongated hole. Simultaneously, the larger cross-section of the telescopic region 7 compared to the guide region 6 expands the range of motion of the helical spring 3 in the direction Y of motion of the braking element 4, said direction Y being perpendicular to the extension direction X of the helical spring 3. Figure 4 and Figure 5 In the example shown, the direction of motion Y is curved because it corresponds to the circumferential direction of the spring brake 1, in which friction produces a braking effect.

[0035] Figure label:

[0036] 1. Spring brake

[0037] 2. Spring support

[0038] 3. Coil springs

[0039] 4. Braking components

[0040] 5. Outer shell

[0041] 6. Guiding Area

[0042] 7. Expansion / Retraction Area

[0043] 8 Rotary braking element

[0044] 9 Braking components

[0045] 10 Friction Liners

[0046] X is the direction of extension of the helical spring.

[0047] Y direction of motion

Claims

1. A spring brake (1) having a plurality of helical springs (3) for applying force to a braking element (4) to generate a braking effect, and having a plurality of spring supports (2) for accommodating the plurality of helical springs (3), the braking element (4) being about an axis, a rotary braking element (8) being disposed on the axis and connected to the axis in a manner that allows for axial movement and rotational fixation, the braking element (4) pressing against the rotary braking element to generate a braking effect. Its features are, Each spring support (2) has a guide area (6) and a telescopic area (7) extending along each helical spring (3), the telescopic area (7) being located between the guide area (6) and the braking element (4), and its cross-section being larger than that of the guide area (6).

2. The spring brake (1) according to claim 1. Its features are, The guide area (6) along the helical spring (3) extends at least 20% and / or at most 95% of the extension length of the spring support (2) along the helical spring (3).

3. The spring brake (1) according to claim 1. Its features are, The guide area (6) along the helical spring (3) extends at least 50% and / or at most 70% of the extension length of the spring support (2) along the helical spring (3).

4. The spring brake (1) according to claim 1 or 2. Its features are, The extension region (7) along the helical spring (3) extends at least 5% and / or at most 80% of the extension length of the spring support along the helical spring (3).

5. The spring brake (1) according to claim 1 or 2. Its features are, The extension region (7) along the helical spring (3) extends at least 30% and / or at most 50% of the extension length of the spring support along the helical spring (3).

6. The spring brake (1) according to claim 1. Its features are, The spring brake (1) is designed so that the helical spring (3) does not come into contact with the extension zone (7) when the spring brake (1) is engaged.

7. The spring brake (1) according to claim 1. Its features are, The cross section of the telescopic region (7) is selected so that the helical spring (3) does not contact the telescopic region (7) when the spring brake (1) is applied.

8. The spring brake (1) according to claim 1. Its features are, The spring brake (1) is designed so that the helical spring (3) will not undergo any plastic deformation when the spring brake (1) is applied.

9. The spring brake (1) according to claim 1. Its features are, The cross section of the telescopic region (7) is selected so that the helical spring (3) will not undergo any plastic deformation when the spring brake (1) is applied.

10. The spring brake (1) according to claim 1. Its features are, The spring support (2) is designed with holes.

11. The spring brake (1) according to claim 1. Its features are, The spring support (2) has a stepped cross section between the guide area (6) and the telescopic area (7).

12. The spring brake (1) according to claim 1. Its features are, The spring support (2) has a stepped hole between the guide area (6) and the telescopic area (7).

13. The spring brake (1) according to claim 1. Its features are, The telescopic area (7) gradually shrinks toward the guide area (6).

14. The spring brake (1) according to claim 1. Its features are, The telescopic area (7) is designed to be conical in shape facing the guide area (6).

15. The spring brake (1) according to claim 1. Its features are, The spring support (2) has a circular cross-section.

16. The spring brake (1) according to claim 1. Its features are, The guide area (6) has a circular cross-section.

17. The spring brake (1) according to claim 1. Its features are, The expansion joint (7) has a circular cross-section.

18. The spring brake (1) according to claim 1. Its features are, The expansion zone (7) has a non-circular cross-section.

19. The spring brake (1) according to claim 1. Its features are, In the circumferential direction of the spring brake (1), the cross-section of the telescopic region (7) is larger than that of the guide region (6).

20. The spring brake (1) according to claim 1. Its features are, The spring brake (1) is electromagnetically actuated.

21. The spring brake (1) according to claim 1. Its features are, The spring brake (1) is released electromagnetically.

22. The spring brake (1) according to claim 1. Its features are, The braking element (4) is an armature disk.

23. The spring brake (1) according to claim 1. Its features are, The spring brake (1) has a rotary braking element (8).

24. The spring brake (1) according to claim 1. Its features are, The spring brake (1) has a brake rotor and / or a brake disc.

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