JP2007333040A - Brake device for rotating machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a brake device for a rotating machine capable of effectively reducing the operation noise of a brake. <P>SOLUTION: In this brake device for the rotating machine comprising an iron core 4 incorporating a coil, an armature 5 magnetically attracted to the magnetic attraction face of the iron core by magnetically exciting the coil, a brake shoe connected to the armature 5, a compression spring disposed between the armature 5 and the magnetic attraction face of the iron core 4, and pressing the armature 5 to press the brake shoe to a rotor, a fixing hole 11 formed at the magnetic attraction face of the armature 5, and a buffer material 12 inserted into the fixing hole 11 in a state of projecting from the magnetic attraction face, and the buffer material 12 is composed of an inner buffer material 12a and an outer buffer material 12b having projecting heights from the magnetic attraction face different from each other. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a brake device for a rotating machine, and more particularly to a structure for reducing operating noise of a brake used in the rotating machine.

  In the conventional brake device of a rotating machine, by energizing the electromagnetic coil built in the iron core, the armature connected to the brake pad pressed against the disc is attracted to the iron core to release the brake, and the electromagnetic coil is in the non-excited state Thus, the armature is released by a spring and the brake pad is pressed against the disc for braking.

  An operating noise is generated when the iron core collides with the armature when the brake is released and when the brake pad collides with the disk during braking. In order to reduce this operating noise, rubber or the like is provided as a cushioning material between the iron core and the armature. The cushioning material is always attached in a compressed state between the iron core and the armature, and absorbs vibration energy transmitted to the armature at the time of suction and release to reduce sound (for example, see Patent Document 1). ).

JP-A-2005-180626 (page 3-4, FIG. 1)

  In the brake configuration disclosed in Patent Document 1, the reaction force of the cushioning material such as rubber is almost linear, whereas the suction force of the iron core against the armature is inversely proportional to the square of the gap with the iron core. As the coil is excited and the armature is attracted to the iron core, the attractive force increases rapidly and does not change linearly.

  When reducing the operating noise of the brake with a cushioning material, it is necessary to effectively suppress the energy acting on the armature, and it is important to absorb the energy according to the increase rate of the kinetic energy of the armature. Therefore, there is a problem that it is difficult to effectively reduce the operating noise when the change in the reaction force of the cushioning material is linear.

  In addition, when the braking force of the brake increases, the energy for attracting the armature also increases, the area of the cushioning material necessary to reduce the operating noise increases, the brake becomes larger than necessary, the coil excitation Problems such as increased current and increased power consumption occur.

  Furthermore, when the braking force of the brake increases, it is necessary to increase the strain in the compression direction of the cushioning material, and it is difficult to reduce the operating noise due to plastic deformation (sagging) of the cushioning material due to long-term use. There's a problem.

  This invention solves the above problems, and it aims at providing the brake device of the rotary machine which can reduce the operating sound of a brake effectively.

  It is another object of the present invention to provide a brake device for a rotating machine that can effectively reduce the operation sound of the brake without increasing the brake.

The brake device for a rotating machine according to the present invention includes an iron core having a built-in coil, an armature in which the coil is excited and magnetically attracted to a magnetic adsorption surface of the iron core, a brake shoe connected to the armature, the armature, and the above A compression spring provided between the magnetic adsorption surfaces of the iron core and pressing the armature to push the brake shoe against the rotor; a fixing hole formed in the magnetic adsorption surface of the iron core or the armature; and the magnetic adsorption surface in the fixing hole In a brake device for a rotating machine having a cushioning material inserted so as to protrude from the
The cushioning material is composed of a plurality of members, and each of the members has a different protruding height from the magnetic adsorption surface.

Further, an iron core with a built-in coil, an armature in which the coil is excited and magnetically attracted to the magnetic adsorption surface of the iron core, a brake shoe connected to the armature, the armature, and the magnetic adsorption surface of the iron core are provided. And a compression spring that presses the armature and presses the brake shoe against the rotor, a fixed hole formed in the iron core or the magnetic adsorption surface of the armature, and a brake device for a rotating machine provided with a cushioning material inserted into the fixed hole In
The cushioning material has a ridge protruding from the upper end in parallel with the magnetic adsorption surface, and the height of the upper surface of the ridge and the thickness of the ridge is at least one member protruding from the magnetic adsorption surface. It is provided with at least one member that protrudes from the magnetic adsorption surface and is disposed at the lower part of the cage.

  According to the brake device for a rotating machine according to the present invention, since the reaction force of the shock absorbing material can be increased immediately before the iron core and the armature come into contact with each other, the operating noise of the brake device can be suppressed without impairing the brake performance. it can.

Embodiment 1 FIG.
FIG. 1 is a front view showing a first embodiment of a brake device for a rotating machine according to the present invention, and FIG. 2 is a cross-sectional view taken along the line AA of FIG. The brake device is shown.

  As shown in the figure, the brake 1 is disposed on the inner peripheral side of the rotor 2. The brake 1 includes an iron core 4 incorporating a coil 3, an armature 5, a compression spring 10 provided on a magnetic adsorption surface between the iron core 4 and the armature 5, a shoe 7 attached to the armature 5 via a connecting member 6, The armature 5 is provided with a fixing hole 11 provided on the magnetic adsorption surface of the armature 5 and a buffer material 12 inserted into the fixing hole 11, and a lining 8 is fixed to the shoe 7. The brake 1 is fixed to the housing 9.

  The brake 1 is braked by cutting off the current of the coil 3 and pushing out the armature 5 with a compression spring 10 built in the iron core 4, and the lining 8 is pressed against the rotor 2 to stop the hoisting machine. The brake 1 is released by exciting the coil 3 to magnetically attract the armature 5 to the iron core 4 and pulling the lining 8 away from the rotor 7.

  A cylindrical fixing hole 11 such as a cylinder or a rectangular tube is formed in the armature 5, and a cushioning material 12 made of a cylindrical member is inserted into the fixing hole 11, so that an operating sound when the armature 5 collides with the iron core 4 is generated. Reduce.

FIG. 3 is a cross-sectional view showing Embodiment 1 of the cushioning material in the brake device for a rotating machine according to the present invention. As shown in FIG. 3A, the cushioning material 12 is formed by coaxially arranging an inner cushioning material 12a and an outer cushioning material 12b made of cylindrical members having different heights, as shown in FIG. 3B. As described above, the heights H ₁ and H ₂ are projected from the surface of the armature 5 adsorbed to the iron core 4.

4 (a) and 4 (b) are graphs showing the relationship between the gap between the armature 5 and the iron core 4 and the reaction force of the cushioning material 12, or the suction force between the iron core / armature, and FIG. In b), the curves indicated by A ₁ and A ₂ indicate changes in the magnetic attractive force by which the iron core 4 attracts the armature 5, and the straight lines indicated by K ₂ and the curve indicated by K ₁ indicate changes in the reaction force of the buffer material 12. ing.

When the coil 3 is excited, the magnetic attractive force increases in inverse proportion to the square of the gap between the armature 5 and the iron core 4. That is, as shown by the curve of A ₁ in FIG. 4 (a) and (b), the magnetic attraction force, the suction force when the gap is large is small, the suction force wants the gap becomes smaller increases.

The magnetic attraction force thus rapidly changes, for example, as indicated by K ₂ in FIG. 4 (a), when the reaction force characteristic is used buffer material 12 which changes linearly, the gap becomes smaller Therefore, a region in which the reaction force of the cushioning material 12 exceeds the magnetic attraction force occurs and the brake cannot be released. For this reason, when trying to obtain the same reaction force, as shown in FIG. 4B, the excitation current of the coil 3 is increased, and the attraction force of A ₂ exceeds the reaction force of the buffer material 12. There is a need for a curved line, resulting in a problem of increased power consumption. Further, it becomes difficult to effectively reduce the collision noise of the armature 5 because the magnetic attractive force becomes too large.

FIG. 5 is a cross-sectional view showing the operation of the cushioning material 12 in the first embodiment. In the first embodiment, since the projection height H ₁ of the inner cushioning materials 12a larger than the outer cushioning member 12b protruding height H ₂ of, during the gap larger FIG 5 (a) ~ FIG 5 (c ) and the inner cushioning material 12a is elastically deformed so as, in the curve shown in K ₁ in FIG. 4 (a) (i) - (as in b), varies along the a ₁ showing the magnetic attraction force FIG 5 (d) ~ FIG 5 (e) of the way after the protruding height _{H 1} of the inner cushioning material 12a is the same as the protruding height _{H 2} of the outer cushioning material 12b, the inner cushioning material 12a and the outer cushioning material 12b is elastically deformed, the reaction force of the cushioning material 12, the curve indicated by K ₁ in FIG. 4 (a) (ii) - a showing a magnetic attraction force rapidly increases as shown in (c) It changes almost along ₁ .

  According to the first embodiment, the reaction force of the cushioning material 12 can be increased immediately before the iron core 4 and the armature 5 come into contact with each other, so that the operating noise of the brake device can be suppressed without impairing the brake performance. .

Further, by adjusting the area of the inner cushioning material 12a and the outer buffer material 12b receives a magnetic attraction force, the magnetic attraction protrusion height of forces inside the buffer material 12a H ₁ and the outer buffer protrusion height of material 12b H _2, a buffer the reaction force of the wood 12 can be a desired value along the a ₁ showing the magnetic attraction force.

  Further, by making the elastic modulus (stress / strain) of the outer buffer material 12b larger than the elastic modulus of the inner buffer material 12a, the area where the outer buffer material 12b receives the magnetic attractive force can be reduced, and the buffer material 12 can be reduced. Can be miniaturized.

  Further, as the buffer material 12, an elastomer such as rubber or a thermoplastic elastomer can be used.

  In addition, in the example shown in FIG. 3, two of the inner cushioning material 12a and the outer cushioning material 12b are used as the cushioning material 12, but the number is not limited to two, for example, using three or more, By changing the height of each of the three protrusions, the reaction force of the buffer material 12 having a plurality of different inclinations substantially along the gap distance dependence of the magnetic attractive force shown in FIGS. 4 (a) and 4 (b). Characteristics can be obtained.

Also, may be a high protrusion of the outer buffer material 12b is H ₂ greater protruding height H ₁ of the inner cushioning materials 12a, also in the case of using three or more, are arranged in descending order of protrusion height There is no need to combine them, and the arrangement order can be arbitrarily combined.

  Further, the shape of the cushioning material is not limited to the shape shown in FIG. 3, and various shapes can be used. An example is shown in FIGS. 6 (a) and 6 (b). FIG. 6 is a plan view. In FIG. 6A, a plurality of cushioning materials 12a and 12b having different projecting heights are formed in the fixing hole 11 having a semicircular shape, and in FIG. The example which provided is shown.

Embodiment 2. FIG.
FIG. 7 is a sectional view showing a second embodiment of the cushioning material in the brake device for a rotating machine according to the present invention.

  When the suction force of the iron core 4 and the armature 5 is large, the reaction force of the cushioning material 12 is insufficient, and it becomes difficult to suppress the brake operating noise. When the load area of the buffer material 12 is increased in order to increase the reaction force of the buffer material 12, the diameter of the fixing hole 11 into which the buffer material 12 is inserted into the armature 5 inevitably increases, and the magnetic flux when the coil is energized is increased. As a result, the attraction force of the armature 5 decreases, and the braking performance deteriorates. FIG. 7 shows a method for avoiding such a problem.

  As shown in FIG. 7B, the cushioning material 12 having an outer peripheral dimension larger than the inner peripheral dimension of the fixing hole 11 of the armature 5 is inserted. For example, the outer peripheral size of the outer cushioning material 12b is made larger than that of the fixing hole 11, and the inner cushioning material 12a is combined, and the buffering material 12 is compressed and inserted into the fixing hole 11. By compressing the buffer material 12, the elastic modulus of the buffer material 12 is apparently increased, and the reaction force can be increased even with the same deformation amount.

  FIG. 8 is a cross-sectional view showing a deformed state of the cushioning material 12 when the armature 5 approaches the iron core 4. The deformation state when the cushioning material 12 shown in FIG. 7 is inserted into the armature 5 is forcibly deformed as shown in FIG. 8A, and the initial strain of the cushioning material 12 is large. When the inner cushioning material 12a is deformed as shown in FIGS. 8A to 8C, the reaction force gradually increases as the gap is reduced by the magnetic attractive force, and FIG. Thus, after the height of the inner cushioning material 12a becomes the same as the height of the outer cushioning material 12b, in FIGS. 8D and 8E, the reaction force of the cushioning material 12 rapidly increases.

  According to the second embodiment, even if the brake has a large magnetic attraction force, the reaction force of the buffer material 12 is increased without increasing the fixing hole 11 in which the buffer material 12 is provided, so that the iron core 4 and the armature 5 are The operation sound at the time of contact can be suppressed.

  Further, by making the elastic modulus of the outer buffer material 12b larger than the elastic modulus of the inner buffer material 12a, the area where the outer buffer material 12b receives the magnetic attractive force can be reduced, and the buffer material 12 can be downsized. Can do.

Embodiment 3 FIG.
9, 10 and 11 are sectional views showing Embodiment 3 of the cushioning material in the brake device for a rotating machine according to the present invention.

  In the first and second embodiments, the case where the inner cushioning material 12a and the outer cushioning material 12b are made of cylindrical members has been shown. However, in this third embodiment, as shown in FIG. Of the cushioning material, the inner cushioning material 12a is a columnar member. However, in this case, when the cushioning material 12 is deformed, it is pressed in the magnetic attracting direction of the armature 5, protrudes from the fixing hole 11, bites between the iron core 4 and the armature 5, and damages the cushioning material 12. Therefore, it is necessary to make it possible to absorb the deformation of rubber in a plane perpendicular to the magnetic adsorption direction.

  Therefore, as shown in FIG. 9B, the tapered portion 15 is provided on the outer peripheral upper ends of the inner cushioning material 12a and the outer cushioning material 12b. As described above, by providing the tapered portion 15, even if the cushioning material 12 is compressed and the outer peripheral dimension is expanded and deformed, the deformation is absorbed by the tapered portion 15 to prevent damage due to biting or the like. be able to. In the example shown in FIG. 9B, the tapered portion 15 is provided on both the inner cushioning material 12a and the outer cushioning material 12b. However, when the amount of deformation is small, either one of the tapered portions 15 is provided. Should be provided.

  According to the third embodiment, since the inner cushioning material 12a is a columnar member, it can be manufactured at a low cost, and when the inner cushioning material 12a is deformed, the outer cushioning material 12b is distorted. The apparent elastic modulus increases and the outer shape of the outer cushioning material 12b can be reduced.

  In FIG. 9B, the tapered portion 15 is provided at the outer peripheral end of the upper surface that receives the magnetic attraction force of the buffer material 12, but the same effect can be obtained by providing the tapered portion 15 at the outer peripheral end of the lower surface.

  In addition, as shown in FIG. 10, the buffer material 12 is not provided with a tapered portion, and a stepped fixing hole 16 in which the diameter of the upper portion of the fixing hole is larger than the outer diameter of the buffer material 12 is provided. 11, when the armature 5 is sucked into the iron core 4 and the cushioning material 12 is deformed in the compression direction as shown in FIG. By swelling in the upper space, it is possible to prevent damage such as the buffer material 12 biting between the armature 5 and the iron core 4.

  9 and 10, the protruding height of the inner cushioning material 12a is larger than the protruding height of the outer cushioning material 12b, but the protruding height of the outer cushioning material 12b is larger than the protruding height of the inner cushioning material 12a. May be.

  Further, by making the elastic modulus of the outer buffer material 12b larger than the elastic modulus of the inner buffer material 12a, the area where the outer buffer material 12b receives the magnetic attractive force can be reduced, and the buffer material 12 can be downsized. Can do.

Embodiment 4 FIG.
12 and 14 are cross-sectional views showing a fourth embodiment of the brake device for a rotating machine according to the present invention, and FIG. 13 is a shock absorber 12 when the armature 5 approaches the iron core 4 in the fourth embodiment. It is sectional drawing which shows the deformation | transformation state. In the second embodiment, as a method for increasing the reaction force of the cushioning material 12, a method for inserting the cushioning material 12 having an outer diameter larger than the diameter of the fixing hole 11 has been described. In addition, as shown in FIG. 12A, the inner cushioning material 12 having a tapered portion at the upper portion is inserted into a ring-shaped fixing hole 17 having a columnar wall 18 formed at the center. When the buffer material 12 is inserted into the ring-shaped fixing hole 17, a gap is formed between the inner periphery of the inner buffer material 12 a and the wall 18.

  As shown in FIG. 13 (a), before the armature 5 is magnetically attracted to the iron core 4, there is a gap between the inner periphery of the inner cushioning material 13 and the wall 18, as shown in FIG. 13 (b). Thus, as the gap between the iron core 4 and the armature 5 becomes smaller, the gap between the inner cushioning material 12a and the wall 18 decreases, and as shown in FIG. When the height and the height of the outer cushioning material 12b become the same, and the inner cushioning material 12a starts to contact the wall 18, the reaction force of the cushioning material 12 starts to rise rapidly. After that, as shown in FIG. 13 (d), the deformation of the inner cushioning material 12a is restricted by the contact between the wall 18 and the inner cushioning material 12a, and the apparent elastic modulus is increased, as shown in FIG. 13 (e). As shown, when the gap between the iron core 4 and the armature 5 becomes almost zero, the space between the inner cushioning material 12a and the wall 18 and the outer cushioning material 12b and the ring-shaped fixing hole 17 disappears and a large reaction force is generated. Obtainable.

  When the diameter of the hard cushioning material 12 is reduced and inserted into the fixing hole 11, it may take time to assemble, but according to the fourth embodiment, it is not necessary to shrink and fix the cushioning material 12, Assembling is easy and the cost can be reduced.

  For the inner cushioning material 12a, a tapered portion 15 is provided at the upper end portion on the inner peripheral side, and for the outer cushioning material 12b, a tapered portion 15 is provided at the upper end portion on the outer peripheral side, so that the wall 18 side and the ring-shaped fixing The inner cushioning material 12 a and the outer cushioning material 12 b are prevented from protruding outside the hole 17. However, when the cushioning material 12 is used in an area where deformation is small, it is not necessary to provide the tapered portion 15. Further, the tapered portion 15 may be provided on either the outer periphery or the inner periphery of the inner cushioning material 12a and the outer cushioning material 12b.

  In order to further increase the reaction force of the cushioning material 12 when the armature 5 is sucked into the iron core 4, the outer dimension of the outer cushioning material 12b is made larger than the ring-shaped fixing hole 17 and the cushioning material 12 is compressed. May be inserted.

Further, as shown in FIG. 14, the reaction force characteristic is more appropriate by providing a multi-step tapered portion 19 formed in multiple steps toward the bottom of the ring-shaped fixing hole 17 on the inner peripheral surface of the inner cushioning material 12 a. Can be controlled. To the height of the inner cushioning material 12a is the same as the height of the outer side cushioning material 14, FIGS. 4 (a) to show the curve K ₁ of (i) - inclination adjusted to an appropriate value for (b) can do. In the case where the tapered portions 15 shown in FIG. 12 are not formed in multiple stages, the reaction force is small until the inner cushioning material 12a and the wall 18 are almost in contact with each other. As shown in FIG. 14B, when the multistage tapered portion 19 is provided, the wall 18 and the inner cushioning material 12a are brought into contact with each other at the lower part of the inner cushioning material 12a from the beginning, and the inner cushioning material 12a is deformed. The contact area between the inner cushioning member 12a and the wall 18 is increased, and the reaction force of the cushioning member 12 can be increased from the initial stage, and can be increased as the gap between the armature 5 and the iron core 4 is decreased. Further, by adjusting the elastic modulus of the inner cushioning material 12a and the taper angle of the multi-step taper portion 19, the inclination of the reaction force characteristic can be freely adjusted, and the outer shape of the cushioning material 12 can be adjusted even if the braking force of the brake increases. There is an effect that the operating noise can be reduced without enlarging it.

  Further, by making the elastic modulus of the outer buffer material 12b larger than the elastic modulus of the inner buffer material 12a, the area where the outer buffer material 12b receives the magnetic attractive force can be reduced, and the buffer material 12 can be downsized. Can do.

Embodiment 5 FIG.
FIG. 15 is a sectional view showing Embodiment 5 of the brake device for a rotating machine according to the present invention. In the fourth embodiment, the wall 18 is provided in the ring-shaped fixing hole 17 as a fixing hole. However, in this fifth embodiment, a compression spring 10 for separating the armature 5 from the iron core 4 is provided instead of the wall 18. It is what you use. As shown in FIG. 1 and FIG. 2, the compression spring 10 is normally built in the brake, and when the coil 3 is not energized, it is separated from the iron core 4 by the restoring force of the compression spring 10. The armature 5 is pressed, and the lining 8 of the brake shoe 7 connected to the armature 5 is pressed against the rotor 2 to brake the rotation of the rotor 2.

  As shown in FIG. 15A, the spring holding hole 21 is provided in the fixing hole 11 to hold the compression spring 10, and the armature 5 is attracted to the iron core 4 as shown in FIG. In addition, the inner peripheral surface of the inner cushioning member 12a comes into contact with the compression spring 10 so that deformation is restricted.

  According to the fifth embodiment, the deformation of the buffer material 12 is regulated by the compression spring 10 so that a large reaction force can be obtained, and the outer shape of the buffer material 12 is increased even in a brake that requires a large suction force. Therefore, the reaction force of the cushioning material 12 can be increased, and the installation space of the compression spring 10 is utilized, so that the brake device for the rotating machine having a large braking force can be reduced in size.

  Further, by making the elastic modulus of the outer buffer material 12b larger than the elastic modulus of the inner buffer material 12a, the area where the outer buffer material 12b receives the magnetic attractive force can be reduced, and the buffer material 12 can be downsized. Can do.

Embodiment 6 FIG.
16 and 18 are sectional views showing Embodiment 6 of the brake device for a rotating machine according to the present invention, and FIG. 17 is a shock absorber 12 when the armature 5 approaches the iron core 4 in Embodiment 6. It is sectional drawing which shows the deformation | transformation state.

In the sixth embodiment, as shown in FIG. 16, the outer cushioning material 12b from the suction surface of the armature 5 and H ₂ protrudes further upward having an inner cushioning member 12a and the gap, eave portion 12c is The total height of the thickness t of the flange portion 12c and the height H3 of the inner cushioning member 12a protrudes from the magnetic attraction surface of the armature 5.

  As shown in FIG. 17A, from the start of contact between the iron core 4 and the outer cushioning material 12b, the armature 4 is sucked, and the flange 12c indicated by the arrow in FIG. The reaction force characteristic is determined by the bending rigidity of the flange portion 12c. As shown in FIG. 17C, the reaction force of the cushioning material 12 suddenly increases when the flange portion 12c of the outer cushioning material 12b and the inner cushioning material 12a start to contact each other. As shown in FIG. 17D, as the gap between the two cushioning materials decreases, the reaction force of the cushioning material 12 further increases. In FIG. 17E, the armature 5 is attracted to the iron core 4. The gap between the flange 12c and the inner cushioning member 12a is almost eliminated, and the reaction force of the cushioning member 12 is maximized.

According to the sixth embodiment, by changing the gap H ₃ and the eave portion 12c URN thickness between eaves section 12c and the inner cushioning material 12a provided on the outer cushioning member 12b, in FIGS. 4 (a) It is possible to adjust the rate of increase of the reaction force (b) → (b) and (b) → (c) of the curve K ₁ to a desired value, and the effect of reducing the operating noise can be improved.

  Moreover, as shown in FIG. 18, the inner side shock absorbing material 12a may be made to protrude from the adsorption | suction surface of the armature 5, and the collar part 12c may be provided in the inner side shock absorbing material 12a.

  16 and 18, the inner circumference dimension of the flange 12c and the inner circumference and outer circumference dimensions of the inner cushioning material 12a are the same. The rate of increase in force can be adjusted to a desired value.

  16 and 18, the surface that receives the magnetic attraction force of the inner cushioning material 12 a may protrude from the magnetic attraction surface of the armature 5.

  Further, in order to further increase the reaction force of the buffer material 12 when the armature 5 is attracted to the iron core 4, the diameter of the outer buffer material 12 b is made larger than that of the fixing hole 11, and the buffer material 12 is compressed. It may be inserted.

  In addition, as shown in the fifth or sixth embodiment, the wall 18 or the spring 10 can be used in combination by using the cushioning material 12 having the configuration shown in FIGS. Reaction force can be obtained.

  Further, in FIG. 16, by making the elastic modulus of the inner cushioning member 12a larger than that of the outer cushioning member 12b, the area of the inner cushioning member 12a that receives the magnetic attractive force can be reduced. By making the elastic modulus of the outer buffer material 12b larger than the elastic modulus of the inner buffer member 12a, the area that receives the magnetic attractive force can be reduced and the size can be reduced.

  In the example shown in FIG. 16 and FIG. 18, two pieces of the inner cushioning material 12 a and the outer cushioning material 12 b are used as the cushioning material 12, but the number is not limited to two. By dividing one or both of the outer cushioning material 12b and the outer cushioning material 12b into a plurality of different heights, the reaction force characteristics of the cushioning material 12 having a plurality of different inclinations along the inclination of the magnetic attractive force can be obtained. .

  In the first to sixth embodiments, the buffer material 12 is provided on the magnetic adsorption surface of the armature 5. However, the buffer material 12 may be provided on the magnetic adsorption surface of the iron core 4.

  Moreover, although the said Embodiment 1-6 demonstrated the elevator hoisting machine to the example, it is not restricted to this, It can apply as a brake device of a rotary machine.

  The brake device for a rotating machine according to the present invention can be effectively used to reduce the operating sound of a brake used in a rotating machine such as an elevator hoisting machine.

It is a front view which shows Embodiment 1 of the brake device of the rotary machine which concerns on this invention. It is AA sectional drawing of FIG. It is sectional drawing which shows Embodiment 1 of the shock absorbing material in the brake device of the rotary machine which concerns on this invention. It is a graph which shows the relationship between the gap of the armature 5 and the iron core 4, and the reaction force of the shock absorbing material 12, or the attraction | suction force between an iron core / armature. 6 is a cross-sectional view showing the operation of the cushioning material 12 in the first embodiment. FIG. 10 is a plan view showing another example in the first embodiment. It is sectional drawing which shows Embodiment 2 of the shock absorbing material in the brake device of the rotary machine which concerns on this invention. In Embodiment 2, it is sectional drawing which shows the deformation | transformation state of the shock absorbing material 12 when the armature 5 approaches the iron core 4. FIG. It is sectional drawing which shows Embodiment 3 of the shock absorbing material in the brake device of the rotary machine which concerns on this invention. It is sectional drawing which shows Embodiment 3 of the shock absorbing material in the brake device of the rotary machine which concerns on this invention. It is sectional drawing which shows Embodiment 3 of the shock absorbing material in the brake device of the rotary machine which concerns on this invention. It is sectional drawing which shows Embodiment 4 of the brake device of the rotary machine which concerns on this invention. In Embodiment 4, it is sectional drawing which shows the deformation | transformation state of the shock absorbing material 12 when the armature 5 approaches the iron core 4. FIG. It is sectional drawing which shows Embodiment 4 of the brake device of the rotary machine which concerns on this invention. It is sectional drawing which shows Embodiment 5 of the brake device of the rotary machine which concerns on this invention. It is sectional drawing which shows Embodiment 6 of the brake device of the rotary machine which concerns on this invention. In Embodiment 6, it is sectional drawing which shows the deformation | transformation state of the shock absorbing material 12 when the armature 5 approaches the iron core 4. FIG. It is sectional drawing which shows Embodiment 6 of the brake device of the rotary machine which concerns on this invention.

Explanation of symbols

1 Brake, 2 Rotor, 3 Coil, 4 Iron core, 5 Armature,
6 connecting member, 7 brake shoe, 8 lining, 9 housing,
10 compression spring, 11 fixing hole, 12 cushioning material, 12a inner cushioning material,
12b outer cushioning material, 12c collar part, 15 taper part, 16 stepped fixing hole,
17 ring-shaped fixing hole, 18 walls, 19 multi-step taper part, 21 spring holding hole.

Claims (9)

An iron core including a coil; an armature in which the coil is excited and magnetically attracted to the magnetic adsorption surface of the iron core; a brake shoe connected to the armature; the armature; and the magnetic adsorption surface of the iron core, A compression spring that presses the armature to press the brake shoe against the rotor, a fixed hole formed in the iron core or the magnetic adsorption surface of the armature, and a cushioning material inserted into the fixed hole so as to protrude from the magnetic adsorption surface In the rotating machine brake device provided,
The brake device for a rotating machine, wherein the cushioning material includes a plurality of members, and each of the members has a different protruding height from the magnetic adsorption surface. An iron core with a built-in coil, an armature in which the coil is excited and magnetically attracted to the magnetic adsorption surface of the iron core, a brake shoe connected to the armature, the armature, and the magnetic adsorption surface of the iron core, In a brake device for a rotating machine comprising a compression spring that presses the armature and presses the brake shoe against the rotor, a fixing hole formed in the iron core or the magnetic adsorption surface of the armature, and a cushioning material inserted into the fixing hole,
The cushioning material has a ridge protruding from the upper end in parallel with the magnetic adsorption surface, and the height of the upper surface of the ridge and the thickness of the ridge is at least one member protruding from the magnetic adsorption surface. A brake device for a rotating machine, comprising: at least one member protruding from the magnetic attraction surface and disposed at a lower portion of the cage. The brake device for a rotating machine according to claim 1 or 2, wherein at least two of the members have different elastic moduli. The buffer material is formed of a cylindrical member, and a wall is provided in the fixing hole located at the innermost periphery of the cylindrical member to restrict the buffer material from being deformed in a direction parallel to the magnetic adsorption surface. The brake device for a rotating machine according to claim 1 or 2. The brake device for a rotating machine according to claim 4, wherein a gap is provided between the innermost periphery of the cylindrical member and the wall. 5. The brake device for a rotating machine according to claim 4, wherein a tapered portion formed in multiple stages toward the bottom portion of the fixing hole is provided on the innermost periphery of the cylindrical member. The brake device for a rotary machine according to claim 4, wherein the wall is the compression spring fixed in the fixing hole. The brake device for a rotating machine according to claim 1 or 2, wherein the cushioning material includes a columnar member and a cylindrical member disposed on an outer periphery of the columnar member. The brake device for a rotating machine according to claim 1 or 2, wherein the cushioning material has an outer peripheral dimension larger than an inner peripheral dimension of the fixed hole, and is compressed and inserted into the fixed hole.

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