CN219570740U - Noise-reducing pad and elevator traction machine brake comprising same - Google Patents

Abstract

The utility model relates to a silencing pad and elevator traction machine brake comprising the same, the silencing pad comprises: the first silencing piece is inserted into the middle part of the second silencing piece and is connected with the second silencing piece, the first end face of the first silencing piece is flush with the first end face of the second silencing piece, the second end face of the first silencing piece protrudes out of the second end face of the second silencing piece, and the first silencing piece and the second silencing piece are made of elastic materials with different hardness.

Description

Noise-reducing pad and elevator traction machine brake comprising same

Technical Field

The present utility model relates to a damper device for a brake of an elevator traction machine, and more particularly, to a noise damping pad for reducing noise and vibration of a brake.

Background

A gasket needs to be provided between the movable core and the stationary core of the elevator traction machine brake to reduce impact during operation and noise caused thereby. Typically, the gasket used is a rubber integrally injection molded sound dampening gasket. Such a noise damping pad has problems such as susceptibility to wear and tear, concentration of stress, and large deformation amount, particularly in the outer peripheral portion. After these problems, the acoustic liner needs to be replaced. And frequent replacement causes an increase in the cost of manpower and material resources.

Accordingly, there is a need for improvements in the art of sound deadening liners.

The information disclosed in the background section of the utility model is only for enhancement of understanding of the general background of the utility model and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person of ordinary skill in the art.

Disclosure of Invention

In order to solve the problems of the prior art, an object of the present utility model is to provide a noise-reducing gasket which improves durability of the noise-reducing gasket by improving structural materials of the existing noise-reducing gasket.

Another object of the present utility model is to provide a noise damping pad to reduce noise and vibration generated by collision between a movable core and a stationary core.

To achieve the above object, the present utility model provides a sound deadening pad comprising: the first silencing piece is inserted into the middle part of the second silencing piece and is connected with the second silencing piece, the first end face of the first silencing piece is flush with the first end face of the second silencing piece, the second end face of the first silencing piece protrudes out of the second end face of the second silencing piece, and the first silencing piece and the second silencing piece are made of elastic materials with different hardness.

The aforementioned sound deadening liner, wherein the first sound deadening member may have a hardness greater than that of the second sound deadening member.

The foregoing muffler liner, wherein the first muffler member may be a cylindrical member, and the second muffler member may be an annular member.

The foregoing muffler liner, wherein a ratio of an area of the first end surface of the first muffler component to an area of the first end surface of the second muffler component may be 1:5 to 1:6.

the foregoing sound deadening liner, wherein a ratio of the thickness of the first sound deadening member to the thickness of the second sound deadening member may be 3:1 to 5:1.

the aforementioned sound deadening liner, wherein the middle portion of the first sound deadening member may be provided with a through hole that extends from the first end portion to the second end portion of the first sound deadening member.

The foregoing muffler liner, wherein the through-hole may have a diameter that gradually increases from the first end to the second end of the first muffler or gradually decreases from the first end to the second end of the first muffler.

The aforementioned sound damping pad, wherein the second sound damping member may have a wedge-shaped, drum-shaped or dumbbell-shaped cross section.

The silencing pad can be arranged between a movable iron core and a static iron core of the elevator traction machine brake.

The utility model also provides an elevator traction machine brake comprising the silencing pad.

The utility model has the beneficial effects that: because the second silencing piece is sleeved outside the first silencing piece, the pressure born by the silencing pad is dispersed, and therefore excessive stress born by local parts is not easy to generate. In addition, because the first silencing piece and the second silencing piece are different in hardness, compared with the traditional integrally-injection-molded silencing gasket, the compression deformation of the silencing gasket is reduced, the service life of the gasket is prolonged, the replacement requirement is reduced, and the cost is saved. In addition, since the buffering function of the noise damping pad of the present utility model is improved, noise generated due to collision between the movable core and the stationary core can be reduced when the brake is energized.

Drawings

FIG. 1 is a cross-sectional view of a sound deadening liner of an exemplary embodiment of the present utility model;

FIG. 2 is a cross-sectional view of a sound deadening liner having a through hole according to an exemplary embodiment of the present utility model;

FIG. 3 is a cross-sectional view of a second sound attenuating member having a different cross-sectional shape in accordance with an exemplary embodiment of the present utility model; and

fig. 4 is a schematic view of a block brake with the acoustic liner of the present utility model installed.

Reference numerals illustrate:

1. first silencing member

11. First end portion

12. Second end portion

13. Through hole

111. First end surface

112. Second end face

2. Second silencing member

21. First end portion

22. Second end portion

211. First end surface

212. Second end face

3. Silencing pad

4. First part

41. End face

42. Mounting hole

421. First section

422. Second section

5. A second component.

It should be understood that the drawings are not to scale but rather illustrate various features that are somewhat simplified in order to explain the basic principles of the utility model. In the drawings of the present utility model, like reference numerals designate like or equivalent parts of the present utility model.

Detailed Description

Reference will now be made in detail to various embodiments of the utility model, examples of which are illustrated in the accompanying drawings and described below. While the utility model will be described in conjunction with the exemplary embodiments thereof, it will be understood that the present description is not intended to limit the utility model to those exemplary embodiments. On the contrary, the utility model is intended to cover not only the exemplary embodiments of the utility model, but also various alternatives, modifications, equivalents, and other embodiments, which are included within the spirit and scope of the utility model as defined by the appended claims.

The specific structural and functional descriptions of the embodiments of the present utility model disclosed herein are merely illustrative of the embodiments of the present utility model. The present utility model may be embodied in many different forms without departing from its spirit or essential characteristics. Accordingly, embodiments of the present utility model have been disclosed for illustrative purposes only and should not be construed as limiting the utility model.

Although the terms "first," "second," etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element. For example, a first element discussed below could be termed a second element without departing from the teachings of the present utility model. Similarly, the second element may also be referred to as a first element.

Certain terminology is used throughout this document to refer to particular system components. As one skilled in the art will recognize, identical components may generally be referred to by different names, and thus the present document is not intended to distinguish between components that differ only in name, but not function. In the documents of the present utility model, the terms "comprising," "including," and "having" are used in an open-ended fashion, and thus should be interpreted to mean "including, but not limited to … …".

Hereinafter, various exemplary embodiments of the present utility model will be described more specifically with reference to the accompanying drawings.

Referring to fig. 1 to 4, the present utility model relates to a sound deadening liner 3 comprising a first sound deadening member 1 and a second sound deadening member 2, the first sound deadening member 1 being inserted into a middle portion of the second sound deadening member 2 and coupled with the second sound deadening member 2, wherein a first end face 111 of the first sound deadening member 1 is flush with a first end face 211 of the second sound deadening member 2, and a second end face 112 of the first sound deadening member 1 protrudes from a second end face 212 of the second sound deadening member 2, wherein the first sound deadening member 1 and the second sound deadening member 2 are made of elastic materials having different hardness.

The sound damping insert 3 of the present utility model may be located between the first part 4 and the second part 5 in use, wherein the first sound damping member 1 may be mounted to the end of the first part 4 facing the second part 5 and the first end 11 of the first sound damping member 1 partially protrudes from the end face 41 of the first part 4; meanwhile, the second sound attenuating member 2 may be mounted to the end of the first member 4 and face the second member 5, and the first end 21 of the second sound attenuating member 2 partially protrudes from the end surface 41 of the first member 4. For example, the noise damping pad 3 of the present utility model may be applied to an elevator hoist brake, wherein the first member 4 may be a moving core of the elevator hoist brake, and the second member 5 may be a stationary core of the elevator hoist brake, with reference to fig. 4.

In the exemplary embodiment of the present utility model, the noise-reducing packing 3 may be mounted to the first member 4 and face the second member 5, so that the noise-reducing packing 3 between the first member 4 and the second member 5 may have a vibration-reducing effect when the first member 4 moves toward the second member 5 and contacts each other.

In another embodiment of the utility model, the sound damping insert 3 may be mounted to the second part 5 and face the first part 4.

In yet another embodiment of the present utility model, the sound damping insert 3 may be mounted to both the first part 4 and the second part 5.

In the practical application of the silencing pad, the quantity of the silencing pads can be set to be multiple, so that the effects of shock absorption and noise reduction are better.

The first sound damping member 1 and the second sound damping member 2 in the sound damping pad 3 of the present utility model may be made of different elastic materials, and the hardness of the first sound damping member 1 is different from the hardness of the second sound damping member 2. The first sound damping member 1 and the second sound damping member 2 may be made of different elastic materials having different hardness, or may be made of materials having the same elastic material but different hardness.

The elastic material is mainly rubber, and for example, it may be silicone rubber, nitrile rubber, natural rubber, etc., or polyurethane, etc.

With reference to fig. 1, the first muffler 1 may be a cylindrical member and the second muffler 2 may be an annular member.

In one embodiment of the present utility model, the first sound damping member 1 may have a hardness greater than that of the second sound damping member 2.

In another embodiment of the present utility model, the first sound damping member 1 may have a hardness smaller than that of the second sound damping member 2.

Preferably, the first sound damping member 1 has a hardness greater than that of the second sound damping member 2. That is, the hardness of the annular second sound deadening member 2 at the outer periphery is relatively low, while the hardness of the first sound deadening member 1 at the center portion is relatively high. The present utility model improves durability of a sound deadening pad by making the hardness of different portions of the pad different without changing its overall elastic properties. In actual use of the muffler liner, since the contact area of the annular second muffler 2 with the second member 5 is large, the annular second muffler 2 is generally subjected to relatively large impact, and accordingly, breakage of the annular second muffler 2 is more likely to occur. For this reason, by making the hardness of the annular second sound deadening member 2 low, the pressure (pressure) to which it is subjected per unit area can be reduced, so that the durability of the second sound deadening member 2 can be prolonged; by making the first sound damping member 1 of the central portion harder, the pressure (pressure) to which it is subjected per unit area can be increased, so that the durability of the second sound damping member 2 and the first sound damping member 1 tend to approach, thereby extending the overall service life of the sound damping pad.

Here, the method of extending the entire service life of the sound deadening liner is not limited thereto, and for example, the first end face 111 of the first sound deadening member 1 may protrude from the first end face 211 of the second sound deadening member 2 by 1mm to 2mm, whereby the pressure borne by the second sound deadening member 2 may be reduced while the pressure borne by the first sound deadening member 1 is increased, and such an arrangement also may extend the durability of the second sound deadening member 2, thereby extending the entire service life of the sound deadening liner.

Further, the ratio of the area of the first end face 111 of the first sound-deadening member 1 to the area of the first end face 211 of the second sound-deadening member 2 may be 1:5 to 1:6, preferably, the ratio of the area of the first end face 111 of the first sound damping member 1 to the area of the first end face 211 of the second sound damping member 2 may be 1:5.5. by setting the ratio of the areas in the above range, the pressure to which the first muffler and the second muffler are subjected can be set in a proper range. If the ratio is too small, the pressure to which the first sound damping member 1 is subjected is too small, and the second sound damping member 2 is subjected to a larger pressure, which is liable to cause premature failure of the second sound damping member 2. Conversely, if the ratio is too large, the pressure to which the first sound-deadening member 1 is subjected is too large, which is liable to cause premature failure of the first sound-deadening member 1.

Further, the ratio of the thickness of the first sound damping member 1 to the thickness of the second sound damping member 2 may be 3:1 to 5:1, preferably, the ratio of the thickness of the first sound damping member 1 to the thickness of the second sound damping member 2 may be 4:1. by increasing the thickness of the second sound deadening member 2, the durability thereof can be improved.

Because the first silencing piece 1 and the second silencing piece 2 have different hardness, compared with the traditional silencing gasket formed by integral injection molding, the service life of the silencing gasket 3 can be prolonged by more than 10%, so that the replacement requirement can be reduced, and the cost is saved.

Referring to fig. 4 in combination, the end of the first member 4 may be provided with a stepped mounting hole 42, and the first and second mufflers 1 and 2 may be mounted to the mounting hole 42.

More specifically, the mounting hole 42 of the first component 4 may comprise a first section 421 and a second section 422, the second section 422 having a diameter larger than the diameter of the first section 421, wherein the second end 12 of the first sound attenuating member 1 is received in the first section 421 and the second end 12 of the first sound attenuating member 1 abuts the first component 4; the second end 22 of the second sound attenuating member 2 is received in the second section 422 and the second end 22 of the second sound attenuating member 2 abuts the first member 4.

When the sound damping liner 3 of the present utility model is mounted to the mounting hole 42, the first end 11 of the first sound damping member 1 and the first end 21 of the second sound damping member 2 each partially protrude from the end face 41 of the first member 4.

In one embodiment of the present utility model, the sound damping insert 3 may be mounted to the mounting hole 42 by a tolerance fit (e.g., a clearance fit, etc.), but it should be understood by those skilled in the art that the manner of mounting the sound damping insert 3 is not limited thereto.

Further, the second end 12 of the first sound attenuating member 1 of the sound attenuating liner 3 may be provided with a mounting chamfer (not shown) that may facilitate assembly of the sound attenuating liner 3.

Referring to fig. 2 in combination, the middle portion of the first sound damping member 1 may be provided with a through hole 13, and the through hole 13 may extend from the first end portion 11 to the second end portion 12 of the first sound damping member 1.

In one embodiment of the present utility model, the diameter size of the through hole 13 may be kept constant as shown in part (a) of fig. 2. Wherein the ratio of the diameter size of the through hole 13 to the diameter size of the first muffler 1 may be 1: 6-1: 8, preferably, the ratio of the diameter size of the through hole 13 to the diameter size of the first muffler 1 may be 1:7.

when the first silencing member 1 is pressed, the through hole 13 facilitates the transmission of force, thereby reducing compression deformation and increasing the service life.

In another embodiment of the present utility model, the diameter size of the through hole 13 may gradually increase from the first end 11 to the second end 12 of the first sound damping member 1, as shown in part (b) of fig. 2.

In still another embodiment of the present utility model, the diameter size of the through hole 13 may gradually decrease from the first end 11 to the second end 12 of the first sound damping member 1 (not shown).

When the first sound deadening member 1 is assembled with the second sound deadening member 2, the columnar first sound deadening member 1 may be inserted into the middle portion of the annular second sound deadening member 2, and the first end face 111 of the first sound deadening member 1 may be flush with the first end face 211 of the second sound deadening member 2. After the first muffler 1 and the second muffler 2 are assembled, the composed muffler pad 3 may be mounted to the mounting hole 42 of the first member 4.

In the exemplary embodiment of the present utility model, the first and second silencing members 1 and 2 may be combined to be integrally used, thereby achieving a shock absorbing and silencing effect. In another embodiment of the present utility model, the first muffler 1 and the second muffler 2 may be used separately, and the purposes of shock absorption and noise reduction may be achieved as well.

In the embodiment of the present utility model, the first muffler 1 and the second muffler 2 may be assembled to each other by adhesion, tolerance fit (e.g., interference fit), or the like.

Referring to fig. 1 and 3 in combination, the cross-sectional shape of the second sound attenuating member 2 may be a ring shape of constant size as shown in fig. 1, or a ring shape of varying size as shown in fig. 3, for example, the cross-sectional shape of the second sound attenuating member 2 may be wedge-shaped (as shown in part (a) of fig. 3), drum-shaped (as shown in part (b) of fig. 3), or dumbbell-shaped (as shown in part (c) of fig. 3). It will be appreciated by those skilled in the art that the cross-sectional shape of the second silencing member 2 should not be limited thereto, and that an appropriate shape may be selected according to the actual application, and that these modified embodiments should be included in the scope of the present utility model.

In the foregoing exemplary embodiment, the first component 4 is a moving core of an elevator traction machine brake, and the second component 5 is a stationary core of an elevator traction machine brake, but the application of the noise damping pad of the present utility model is not limited thereto.

Hereinafter, the noise damping pad of the present utility model will be described in detail by taking as an example its application to a movable core of an elevator traction machine brake.

When the brake is powered off, a small air gap is reserved between the static iron core 5 and the movable iron core 4, and the first end face 111 of the first silencing piece 1 and the first end face 211 of the second silencing piece 2 slightly protrude out of the end face 41 of the first component 4; when the brake is energized, the stationary core 5 generates electromagnetic force due to the energization of the coil, so that the movable core 4 overcomes the elastic force of the brake spring, and the movable core 4 is attracted to the stationary core 5, during which, since the first end face 111 of the first sound damping member 1 and the first end face 211 of the second sound damping member 2 slightly protrude from the end face 41 of the first member 4, the stationary core 5 first contacts the first end face 111 of the first sound damping member 1 and the first end face 211 of the second sound damping member 2, and then the sound damping pad is compressively deformed, and noise and vibration generated due to collision between the movable core 4 and the stationary core 5 at the time of attraction can be reduced by the compressive deformation of the sound damping pad.

In the suction process, when the first and second silencing members 1 and 2 are in contact with the stationary core 5, the pressure received by the silencing pad 3 is dispersed by the cooperation of the second silencing member 2 and the first silencing member 1, so that stress concentration is not easily generated.

In addition, since the first and second silencing members 1 and 2 are different in hardness, the silencing pad of the present utility model is reduced in compression deformation and increased in pad life as compared with the conventional integrally injection-molded silencing pad, thereby reducing replacement requirements and saving costs.

In addition, since the damping effect of the noise damping gasket of the present utility model is improved, noise and vibration generated by collision between the movable core and the stationary core can be reduced when the brake is energized, and compared with the conventional integrated injection molding noise damping gasket, the noise damping gasket of the present utility model can reduce the noise by 8% to 12%, and the vibration by 4% to 7%.

Example 1:

taking a PMS145 type elevator traction machine brake as an example, adopting a structure shown in a part (a) in fig. 2, wherein the outer diameter of the first silencing piece 1 is 6mm, the thickness is 8mm, and the material is polyurethane of HA 93; the outer diameter of the second silencing piece 2 is 15mm, the thickness is 2mm, and the material is nitrile rubber of HA 90; the diameter of the through hole 13 of the first silencing member 1 is 1mm; the diameter of the hole of the middle portion of the second sound-deadening member 2 may be 0.1mm larger than the outer diameter of the first sound-deadening member 1, so that the first sound-deadening member 1 and the second sound-deadening member 2 may be coupled by interference fit.

Through the use, the service life of the silencing pad with the structure can reach 1100 ten thousand times.

Whereas the life of a sound deadening pad using a conventional structure is generally not more than 1000 tens of thousands times. Compared with the silencing pad, the service life of the silencing pad can be prolonged by at least 10%.

The foregoing description of specific exemplary embodiments of the utility model has been presented for the purposes of illustration and description. They are not intended to be exhaustive or to limit the utility model to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teaching. The exemplary embodiments were chosen and described in order to explain certain principles of the utility model and its practical application to thereby enable others skilled in the art to make and utilize various exemplary embodiments and various alternatives and modifications thereof. It is intended that the scope of the utility model be defined by the following claims and their equivalents.

Claims (10)

1. A sound deadening gasket, characterized by comprising:

a first muffler; and

the first silencing piece is inserted into the middle part of the second silencing piece and is connected with the second silencing piece, wherein the first end face of the first silencing piece is flush with the first end face of the second silencing piece, and the second end face of the first silencing piece protrudes out of the second end face of the second silencing piece;

wherein the first and second sound deadening members are made of elastic materials having different hardness.

2. The sound attenuating liner of claim 1, wherein the first sound attenuating member has a hardness greater than a hardness of the second sound attenuating member.

3. The sound attenuating liner of claim 2, wherein the first sound attenuating member is a cylindrical member and the second sound attenuating member is an annular member.

4. The sound attenuating liner of claim 1, wherein the ratio of the area of the first end face of the first sound attenuating member to the area of the first end face of the second sound attenuating member is 1:5 to 1:6.

5. the sound attenuating liner of claim 1, wherein a ratio of a thickness of the first sound attenuating member to a thickness of the second sound attenuating member is 3:1 to 5:1.

6. the sound attenuating liner of claim 1, wherein the first sound attenuating member is provided with a through hole in a middle thereof, the through hole extending from a first end to a second end of the first sound attenuating member.

7. The sound attenuating liner of claim 6, wherein the through-hole has a diameter that gradually increases from the first end to the second end of the first sound attenuating member or gradually decreases from the first end to the second end of the first sound attenuating member.

8. The sound attenuating liner of claim 1, wherein the second sound attenuating member has a wedge, drum or dumbbell shape in cross section.

9. The noise dampening shoe of claim 1, wherein the noise dampening shoe is mounted between a moving core and a stationary core of an elevator machine brake.

10. Elevator machine brake, characterized in that it comprises a sound-damping lining according to any one of the preceding claims.