JP5355762B2 - Brake system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling stock cooling device capable of miniaturization and weight reduction, and preventing adverse effects of exhaust. <P>SOLUTION: In one embodiment, the braking system includes: a disk 11 that rotates interlocked with a rotor of equipment; a plurality of pads 10A, 10B each placed opposite the disk; and a pressing mechanism that presses each pad against the surface of the disk. The plurarity of pads are disposed opposite the disk in mutually different braking radius positions, or in mutually different angular positions, on different diameter lines, around the rotational center axis of the disk. <P>COPYRIGHT: (C)2013,JPO&amp;INPIT

Description

  Embodiments described herein relate generally to a brake system used in automobiles, railway vehicles, elevator hoisting machines, and the like.

  Automobiles, railway vehicles, elevator hoisting machines, and the like are provided with a brake system that brakes the rotation of rotating wheels or drive net vehicles. As a brake system, for example, an electromagnetic brake includes a brake disk that rotates in conjunction with a rotating body such as a wheel or a drive net, a pad that slides on one or both sides of the brake disk, and a pressure that presses the pad against the brake disk. And a mechanism. The pressing mechanism includes a fixed iron core and an operating iron core. Windings and springs wound inside the fixed iron core are disposed, and the operating iron core is pushed by the spring. The pad is fixed to the operating iron core on the side opposite to the fixed iron core and the spring, and is pressed against the sliding surface of the brake disk by the movement of the operating iron core.

  When a plurality of pads are used, these pads are arranged on the same braking radius (r) with respect to one side of the disk. Then, the braking force is generated by pressing the pad against the disk by the spring force of the pressing portion.

  Alternatively, two pads are arranged on the same braking radius (r) with respect to both sides of the brake disc, and a braking force is generated by sandwiching the brake disc from both sides (for example, Patent Document 1).

  In such a brake system, the pad and the disk generate friction by sliding, and the friction is converted into heat from the laws of thermodynamics. The temperature increase value of the disc caused by the braking capacity, that is, the brake torque will be described below.

The brake torque is expressed by Equation 1 below.
Brake torque: TB = 2 ・ μ ・ F ・ r ・ Np Equation 1
Here, μ: friction coefficient, F: pressing force, r: braking radius, Np: number of pads.

The energy generated by braking the brake is expressed by Equation 2 below.
Energy: E = 2 · π · n · TB · tb Formula 2
Here, n: rotational speed, tb: braking time.

The heat absorption mass of the disk at this time is expressed by the following formula 3.
Heat absorption mass: m = A · t · γ Equation 3
Here, A: sliding area, t: disc thickness, and γ: specific weight.
The temperature rise value of the disk at this time is expressed by the following equation 4.
Temperature rise value: Δt = E / (λ · m) Equation 4
Here, λ is specific heat.

JP 2006-335547 A

The conventional brake system described above has the following problems.
As shown in the above formulas 1 to 4, when the braking force of the brake is increased, the temperature rise value of the disk increases. This also increases the temperature of the opposing pad.

  1) The disk expands when the temperature rises and contracts when cooled. When the disk is constrained, compressive stress is generated during expansion and tensile stress is generated during contraction. As described above, when the brake system is braked / released together with the operation / stop of the equipment, a temperature cycle occurs in the disk, and repeated compression and tension stress acts on the disk. The same applies to the pad that is rubbed with the disk.

  This is called thermal fatigue. In general, the material structure becomes finer when strain and heat due to expansion / contraction described above are repeatedly applied. For this reason, not only deterioration of characteristics and destabilization, but also thermal cracking due to deterioration occurs, causing a short life of the brake and its application equipment.

  In addition, if braking is repeated in a short time, the temperature is accumulated, causing further temperature increase. If the cooling time is set after braking, the time until recovery is lost.

  The friction surface (sliding surface) of the pad changes due to thermal expansion corresponding to the temperature difference. Due to this change, the state of contact with the disk changes, and the temperature rise due to friction is high in places where the contact force is high, and the temperature rise due to friction is low in places where the contact force is low. As the frictional force and temperature increase, the wear of the pad increases and vice versa. Therefore, the friction surface of the pad becomes convex when the temperature rises, and becomes concave when the temperature decreases, resulting in unevenness of the friction surface. For this reason, the surface area of the pad does not reach the entire surface, and the predetermined braking ability cannot be exhibited, which causes deterioration of characteristics.

There are various measures to suppress the temperature rise value and thermal fatigue, but there are the following problems.
2) Change of disk shape
There are measures to improve the heat dissipation by configuring the disk with cooling fins.
In this case, an increase in the mass of the cooling fin causes an increase in the mass of the applied device and an increase in size. Further, the yield and productivity are deteriorated due to the complicated shape, and the manufacturing cost and lead time are increased.

  Furthermore, when a disk is made of cast iron or the like, internal defects such as a nest due to thickness deviation and variations in hardness become large, which causes deterioration of quality and deterioration of characteristics.

3) Change of brake specifications
Mainly, when the specifications related to Equation 1 are changed, the following problems are raised.
a. If the torque (braking capability) is reduced, it will naturally not be possible to satisfy the required specifications of the equipment. In addition, the range of application of the equipment has been reduced, which has been a negative effect of increasing the number of types of brake systems and standardization, and has been a factor in reducing productivity.

  b. If the friction coefficient is set to a low value, the braking ability decreases. Therefore, if the braking radius is increased as a countermeasure, it is necessary to increase the disk diameter. In this case, a high manufacturing technique is required to suppress the manufacturing error of the disk and to ensure the processing accuracy, resulting in a decrease in yield / productivity and an increase in manufacturing cost and lead time.

  In order to increase the pressing force of the pad, it is necessary to increase the spring force, and it is necessary to increase the size of the spring accompanying the increase in the size of the spring and the corresponding increase in the suction force. As a result, not only various productivity problems, but also the size of the brake and the entire device are increased. Further, when the spring force is increased, the force related to suction / release is increased, and the operation time is generally prolonged. This is a safety issue.

c. If the friction coefficient is set high and the pressing force or braking radius is reduced, generally the higher the friction coefficient, the greater the amount of wear, leading to a shortened life of the brake system and an increase in the number of maintenance and inspections.
In general, when the friction coefficient is high, the noise (squeal) during braking increases, which causes deterioration of the surrounding environment.

  d. When the number of pads, that is, the number of brakes is increased, the number of attachment mechanisms increases, resulting in duplication of equipment. Moreover, the difficulty of control for performing braking simultaneously becomes a problem.

4) Change of applicable specifications
Mainly, when each specification related to Equation 2 is changed, the following problems occur.
a. If the rotation speed is set low, the applicable range of equipment is reduced, which increases the types and standardization of brake systems, and causes deterioration of productivity.

  b. If the braking time is set short, the braking energy becomes small. In this case, a large number of times and time required for the alignment are required. For this reason, it has become a factor of deterioration of productivity due to an increase in shipping test time in manufacturing, and deterioration of maintainability due to an increase in alignment time during pad replacement in maintenance.

5) Change of heat capacity
Mainly, when the specifications related to Equation 3 are changed, the following problems occur.
a. In order to increase the sliding area, it is necessary to increase the size of the pad. Along with this, it has become a factor that leads to deterioration in accuracy or increase in manufacturing difficulty due to increase in size of the brake and expansion of the pad plane.

b. Increasing the disk thickness has been a factor in increasing the size of the disk and the accompanying equipment. In the configuration in which the pads are arranged opposite to each other, the holder of the fixed iron core differs depending on the disc thickness, and it is necessary to set parts according to the application specification and to manage it accordingly.
Moreover, in the manufacture of the holder, it is necessary to invest in molds and jigs and tools, which increases the design load, deteriorates productivity, and increases manufacturing costs.

6) Issues by application
The above-mentioned problems are general problems of brakes, and there are the following problems in specific applications.

a. Elevators represented by elevators
In general, an elevator requiring a large capacity requires a very large braking capacity, and a temperature rise value during one braking is very high. Therefore, the brake system tends to be large in order to set a large heat capacity. In addition, cooling after braking is often natural air cooling, and sometimes it was necessary to stop the system.

b. Brake for vehicles represented by Shinkansen
Since the rotational speed of the wheel is high and the number of times of braking is high, the temperature rise value is very high due to temperature rise during braking and intermittent repeated braking. In addition, since the running wind is used as a cooling method after braking, the cooling rate is very fast. From the above, the temperature cycle of temperature increase / decrease is high, and furthermore, the temperature difference is large, so the influence of thermal fatigue is very large.

c. Automobiles and motorcycles
One of the problems of this application is noise (squeal) during braking. Various studies have revealed that the unevenness of the pad friction surface affects the noise factor. If the temperature rise and temperature difference are large, irregularities on the friction surface of the pad are likely to occur, and it is necessary to hit the entire surface of the pad as a noise reduction measure.

  The present invention has been made in view of the above-mentioned circumstances, and the problem is that while maintaining the performance of the disc and the brake, the application range is expanded by suppressing the temperature rise of the disc and the pad, and the characteristics are improved. It is an object of the present invention to provide a brake system capable of improving productivity, reducing manufacturing lead time and manufacturing cost. It is another object of the present invention to provide a brake system that can realize a longer life, improved performance, smaller size and lighter weight by reducing the temperature, and can also improve the environment by reducing noise.

According to the embodiment, the brake system includes a disk that rotates in conjunction with a rotating body of the device, a plurality of pads that are respectively arranged to face the disk, and a pressing mechanism that presses each pad against the surface of the disk. The disk has sliding surfaces on both sides, and the plurality of pads are arranged so as to face one sliding surface and pads arranged to face the other sliding surface; The plurality of pads are disposed opposite to the different braking radius positions with respect to the disk, and are at different angular positions around the rotation center axis of the disk on different diameter lines of the disk. It is arranged.

FIG. 1 is a diagram schematically showing a disc and a pad of a brake system according to a first embodiment of the present invention. FIG. 2 is a side view showing a partially broken portion of the pressing mechanism of the brake system. FIG. 3 is a diagram schematically showing disks and pads of a brake system according to a second embodiment of the present invention. FIG. 4 is a diagram schematically showing a disc and a pad of a brake system according to a third embodiment of the present invention. FIG. 5 is a side view showing a partially broken portion of the pressing mechanism of the brake system. FIG. 6 is a side view partially showing a pressing jockey of a brake system according to a fourth embodiment of the present invention. FIG. 7 is a diagram schematically showing disks and pads of a brake system according to a fifth embodiment of the present invention. FIG. 8 is a diagram schematically showing disks and pads of a brake system according to a sixth embodiment of the present invention. FIG. 9 is a diagram schematically showing disks and pads of a brake system according to a seventh embodiment of the present invention. FIG. 10 is a diagram schematically showing disks and pads of a brake system according to an eighth embodiment of the present invention. FIG. 11 is a diagram schematically showing disks and pads of a brake system according to a ninth embodiment of the present invention. FIG. 12 is a diagram schematically showing disks and pads of a brake system according to a tenth embodiment of the present invention. FIG. 13 is a diagram schematically showing a disc and a pad of a brake system according to an eleventh embodiment of the present invention. FIG. 14 is a diagram schematically showing a disc and a pad of a brake system according to a twelfth embodiment of the present invention. FIG. 15 is a diagram schematically showing a disc and a pad of a brake system according to a thirteenth embodiment of the present invention.

Hereinafter, a brake system according to an embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
Hereinafter, a brake system according to a first embodiment of the present invention will be described. FIG. 1 is a front view and a side view schematically showing a disk and a pad in the brake system, and FIG. 2 is a side view showing a pressing mechanism for driving the pad.

  As shown in FIGS. 1 and 2, the brake system is a disk that is attached to a rotating body of an applicable device, for example, a rotating shaft of a drive net provided in an elevator hoist, and rotates in conjunction with the rotating shaft. , A plurality of pads 10A and 10B arranged to face the sliding surface of the disk, and a pressing mechanism 12 that slides each pad against the sliding surface of the disk.

  The two pads 10 </ b> A and 10 </ b> B are arranged to face one side of the disk 11 and to face different braking radius positions with respect to the disk 11. With respect to the disk 11, the pad 10A is disposed so as to oppose the position of the braking radius r1 and the pad 10B is opposed to the position of the braking radius r2, and the pads 10A and 10B are 180 degrees apart from each other around the rotation center axis of the disk 11. They are spaced apart. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The relationship between the braking radii r1 and r2 is r1> r2.

  The pressing mechanism 12 is configured as an electromagnetic pressing mechanism, for example, and is provided with two pressing mechanisms 12 corresponding to the pads 10A and 10B, respectively. The pressing mechanism 12 includes a fixed iron core 14 and an operating iron core 16, and a wound winding 17 and a spring 18 are disposed inside the fixed iron core 14. The operating iron core 16 has a first protrusion 20 a inserted into the winding 17 and a second protrusion 20 b protruding in the opposite direction to the first protrusion, and is parallel to the central axis C of the disk 11. It is supported so as to be movable along the direction. The operating iron core 16 constitutes a pressing portion that presses one pad independently.

  The pads 10 </ b> A and 10 </ b> B are formed in, for example, a rectangular plate shape, and are fixed to the second protrusions 20 b of the operating iron core 16. The fixed iron core 14 is supported by a rigid body such as a support frame 22, and the pads 10 </ b> A and 10 </ b> B are opposed to one side of the disk 11.

  When the winding 17 is energized when the brake is not operating, the operating iron core 16 is urged away from the disk 11, and the pads 10A and 10B are held away from the disk surface. When the power supply to the winding 17 is cut off during the operation of the brake, the operating iron core 16 is urged toward the disk 11 by the spring 18, and the pads 10A and 10B are pressed against the sliding surface of the disk 11, respectively. Thereby, braking force is obtained. At this time, as shown in FIG. 1, the pads 10A and 10B are in sliding contact with the sliding surface of the disk 11 at different braking radii r1 and r2. That is, in the disk 11, the sliding contact surface with which the pad 10A is slidably contacted and the sliding contact surface with which the pad 10B is slidably contacted are displaced in the radial direction without overlapping each other. In addition, a part of these sliding contact surfaces may overlap.

  According to the brake system configured as described above, the pads 10A and 10B are in sliding contact with the sliding surface of the disk 11 at different braking radii r1 and r2. Therefore, the sliding area of the disk 11 on which the pads 10A and 10B slide can be increased. As a result, the heat absorption mass m shown in Equation 3 (m = A · t · γ) described above increases. As a result, the temperature increase value Δt shown in the above-described Expression 4 (Δt = E / (λ · m)) can be suppressed to a low level.

  In this way, by suppressing the temperature rise value low, thermal fatigue of the disk 11 and the pads 10A and 10B can be reduced. As a result, the life can be extended and the cooling time after braking can be shortened. Further, if the temperature of the friction surfaces of the pads 10A and 10B is low, the amount of wear can be reduced, and the temperature difference is also small, so that the friction surfaces can be easily maintained smooth, so that the braking ability and characteristics can be improved. Furthermore, noise reduction during braking can be realized. Since the temperature rise of the disk 11 is low, not only can the system configuration be simplified, the equipment can be reduced in size and weight and productivity can be improved, but also the quality can be stabilized.

  In the brake specification, the performance of the pad friction surface can be improved, so that the characteristics can be improved. When set to the same temperature as before, the friction coefficient can be set higher and the pressing force can be increased, so the brake system can be reduced in size and simplified, and can be standardized by improving characteristics and expanding the application range. It becomes. Since the sliding area can be expanded without changing the pad area, the brake can be downsized and the manufacturing can be simplified.

  In summary, by maintaining the disc and pad configuration and suppressing the temperature rise, the brakes can be expanded to improve the characteristics, improve productivity, reduce manufacturing lead time, and reduce manufacturing costs. A system is obtained. In addition, it is possible to extend the life of the brake system by lowering the temperature, to improve performance, to reduce the size and weight, and to improve the environment by reducing noise.

(Second Embodiment)
FIG. 3 is a front view and a side view schematically showing disks and pads in the brake system according to the second embodiment. In the second embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 3, according to the second embodiment, the two pads 10 </ b> A and 10 </ b> B are disposed so as to face one side of the disk 11 and to face different braking radius positions with respect to the disk 11. Has been. With respect to the disk 11, the pad 10 </ b> A is disposed opposite to the position of the braking radius r <b> 1 and the pad 11 </ b> B is disposed opposite to the position of the braking radius r <b> 2, and is disposed at equal angular positions around the rotation center axis C of the disk 11. Yes. That is, the pads 10 </ b> A and 10 </ b> B are disposed at the same location on the diameter line of the disk 11 and are disposed on the same side with respect to the rotation center axis of the disk 11. The relationship between the braking radii r1 and r2 is r1> r2.

  The pressing mechanism for pressing the pads 10A and 10B against the disk 11 is the same as in the first embodiment, and the pad 10A and the pad 10B are driven by a common pressing mechanism. In addition, you may make it press-drive with a separate press mechanism for every pad 10A, 10B.

  Also in the brake system according to the second embodiment configured as described above, the same operations and effects as those of the first embodiment described above can be obtained. Further, by adopting a configuration in which the two pads are driven by a common pressing mechanism, the brake system can be reduced in size and weight.

(Third embodiment)
FIG. 4 is a front view and a side view schematically showing a disk and a pad in the brake system according to the third embodiment, and FIG. 5 is a side view showing a pressing mechanism for driving the pad. In the third embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 4, according to the third embodiment, the brake system has four pads 10A, 10B, 10C, and 10D. Both sides of the disk 11 are used as sliding surfaces, and the disk is sandwiched from both sides by the pads. It is configured as a double-sided sliding contact type brake system that brakes with

  The pads 10A and 10C are opposed to each other with the disk 11 interposed therebetween, and are opposed to both sides of the disk. The pads 10 </ b> A and 10 </ b> C are disposed to face the disk 11 at the position of the braking radius r <b> 1.

The pads 10B and 10D are opposed to each other with the disk 11 interposed therebetween, and are opposed to both surfaces of the disk. The pads 10 </ b> B and 10 </ b> D are arranged to face the disk 11 at the position of the braking radius r <b> 2, respectively.
The pads 10A and 10B are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The pads 10C and 10D are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10C and 10D are arranged on the same diameter line of the disk 11.
The relationship between the braking radii r1 and r2 is r1> r2.

  As shown in FIG. 5, the pressing mechanism 12 that presses the pads 10 </ b> A, 10 </ b> B, 10 </ b> C, and 10 </ b> D to the sliding surface of the disk 11 is the same as in the first embodiment, and separate pressing mechanisms 12 for each of the four pads 10. Are provided, and the four pads are independently pressed and driven. Each pressing mechanism 12 has a pressing portion that presses one pad independently.

  According to the third embodiment configured as described above, the pads 10A and 10B and the pads 10C and 10D are in sliding contact with the sliding surface of the disk 11 at different braking radii r1 and r2. Therefore, the sliding area of the disk 11 on which the pads 10A and 10B slide can be increased. Therefore, in the third embodiment, the same operation and effect as in the first embodiment can be obtained. Further, the braking force can be increased by providing pads on both sides of the disc and braking the disc with both sides sandwiched. Furthermore, according to the above configuration, the disk thickness can be changed infinitely, the degree of design freedom can be expanded with respect to the specifications of the equipment, and standardization of the brake can be achieved.

(Fourth embodiment)
FIG. 6 is a side view schematically showing a disk, a pad, and a pressing mechanism in the brake system according to the fourth embodiment. In the fourth embodiment, the same parts as those in the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 6, according to the fourth embodiment, the pressing mechanism 12 has a pad facing that simultaneously presses the pad 10 </ b> A provided on one side of the disk 11 and the pad 10 </ b> C provided on the opposite side of the disk. It is configured as a pressing mechanism of the type, and the disk 11 is sandwiched from both sides by the pads 10A and 10C to be braked.

  The pressing mechanism 12 includes a brake body having a fixed iron core 14, an operating iron core 16, and a holder 24. Inside the fixed iron core 14, a wound winding 17 and a spring 18 are arranged. The operating iron core 16 has a first protrusion 20 a inserted into the winding 17 and a second protrusion 20 b protruding in the opposite direction to the first protrusion, and is parallel to the central axis C of the disk 11. It is supported so as to be movable along the direction.

  The pad 10 </ b> A is fixed to the second protrusion 20 b of the operating iron core 16 and faces one side of the disk 11. The fixed iron core 14 is supported by a support frame (not shown) so as to be movable along a direction parallel to the rotation axis of the disk 11.

  The holder 24 extends from the fixed iron core 14 beyond the disk 11 to the opposite surface side of the disk. A rod 26 is integrally formed at the extending end of the holder 24, and this rod 26 is located on the opposite surface side of the disk 11 and extends parallel to the central axis of the disk. A pad 10 </ b> C is fixed to the tip of the rod 26 and faces the opposite surface of the disk 11. The rod 26 and the operating iron core 16 each constitute a pressing portion that presses one pad independently.

  During operation of the brake, the operating iron core 16 is urged toward the disk 11 by the spring 18, and the pad 10 </ b> A is pressed against one sliding surface of the disk 11. Thereby, braking force is obtained. At this time, since the position of the disk 11 is not changed, the urging force of the spring 18 reacts to move the fixed iron core 14, the holder 24, the rod 26, and the pad 10 </ b> C in the opposite direction to the operating iron core 16. As a result, the pad 10 </ b> C is pressed against the sliding surface on the opposite side of the disk 11. As a result, the pads 10A and 10C generate a pressing force to sandwich the disk 11 from both sides.

  When the winding 17 is energized when the brake is not in operation, the operating iron core 16 is energized in a direction away from the disk 11, and the pad 10A is separated from the disk 11, and in conjunction with this, the fixed iron core 14, The holder 24, the rod 26 and the pad 10 </ b> C move in the direction opposite to the operating iron core 16, and the pad 10 </ b> C is separated from the disk 11.

  Also in the brake system according to the fourth embodiment configured as described above, the same operations and effects as those of the first embodiment described above can be obtained. Further, by driving the two pads with the single pressing mechanism 12, the brake system can be reduced in size and weight.

(Fifth embodiment)
FIG. 7 is a front view and a side view schematically showing disks and pads in the brake system according to the fifth embodiment. In the fifth embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 7, according to the fifth embodiment, the two pads 10 </ b> A and 10 </ b> B are disposed so as to face both surfaces of the disk 11 and to face different braking radius positions with respect to the disk 11. Has been. The pad 10A faces the disk 11 with respect to one side at the position of the braking radius r1, and the pad 10B faces the face opposite to the disk 11 at the position of the braking radius r2. The pads 10 </ b> A and 10 </ b> B are disposed at equal angular positions around the rotation center axis C of the disk 11. That is, the pads 10 </ b> A and 10 </ b> B are disposed at the same location on the diameter line of the disk 11 and are disposed on the same side with respect to the rotation center axis of the disk 11. The relationship between the braking radii r1 and r2 is r1> r2.

  The pressing mechanism that presses the pads 10A and 10B against the disk 11 is the same as in the third embodiment, and the pads 10A and 10B are pressed and driven by separate pressing mechanisms. Or as shown in 4th Embodiment, it is good also as a structure which drives two pads simultaneously using the pad opposing press mechanism 12. FIG.

  Also in the brake system according to the fifth embodiment configured as described above, the same operations and effects as those of the first embodiment described above can be obtained. In addition, by adopting a configuration in which the two pads are driven by a common pressing mechanism, the brake system can be reduced in size and weight, and the mounting configuration can be simplified and shared.

(Sixth embodiment)
FIG. 8 is a front view and a side view schematically showing disks and pads in the brake system according to the sixth embodiment. In the sixth embodiment, the same parts as those in the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 8, according to the sixth embodiment, the brake system has four pads 10A, 10B, 10C, and 10D. Both sides of the disk 11 are used as sliding surfaces, and the disk is sandwiched from both sides by the pads. It is configured as a double-sided sliding contact type brake system that brakes with

  The pads 10A and 10C are opposed to each other with the disk 11 interposed therebetween, and are opposed to both sides of the disk. With respect to the disk 11, the pad 10A is disposed at the position of the braking radius r1, and the pad 10C is disposed at the position of the control radius r2. Two or more sets of such pads are arranged.

  That is, the pad 10B and the pad 10D are opposed to each other with the disk 11 interposed therebetween, and are opposed to both surfaces of the disk. With respect to the disk 11, the pad 10B is disposed at the position of the braking radius r2, and the pad 10D is disposed to face the position of the control radius r1.

  The pads 10A and 10B are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The pads 10C and 10D are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10C and 10D are arranged on the same diameter line of the disk 11. The relationship between the braking radii r1 and r2 is r1> r2. On the same sliding surface of the disk 11, the plurality of pads are arranged to face each other at different braking radius positions.

  According to the sixth embodiment configured as described above, the pads 10A and 10B and the pads 10C and 10D are in sliding contact with the sliding surface of the disk 11 at different braking radii r1 and r2. Therefore, the sliding area of the disk 11 on which the pads 10A and 10B slide can be increased. Therefore, in the sixth embodiment, the same operation and effect as in the first embodiment can be obtained. Further, the braking force can be increased by providing pads on both sides of the disc and braking the disc with both sides sandwiched.

(Seventh embodiment)
FIG. 9 is a front view and a side view schematically showing disks and pads in the brake system according to the seventh embodiment. In the seventh embodiment, the same parts as those in the third embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 9, according to the seventh embodiment, the brake system has four pads 10A, 10B, 10C, and 10D. Both sides of the disk 11 are used as sliding surfaces, and the disk is sandwiched from both sides by the pads. It is configured as a double-sided sliding contact type brake system that brakes with

  The pads 10A and 10C are opposed to each other with the disk 11 interposed therebetween, and are opposed to both sides of the disk. With respect to the disk 11, the pad 10A is disposed at the position of the braking radius r1, and the pad 10C is disposed at the position of the control radius r2. Two or more sets of such pads are arranged.

  That is, the pad 10B and the pad 10D are opposed to each other with the disk 11 interposed therebetween, and are opposed to both surfaces of the disk. With respect to the disk 11, the pad 10B is disposed at the position of the braking radius r1, and the pad 10D is disposed at the position of the control radius r2. The relationship between the braking radii r1 and r2 is r1> r2.

  The pads 10A and 10B are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The pads 10C and 10D are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10C and 10D are arranged on the same diameter line of the disk 11. On the same sliding surface of the disk 11, the plurality of pads are arranged opposite to each other at the same braking radius position.

  According to the seventh embodiment configured as described above, the same actions and effects as those of the third embodiment described above can be obtained. Further, the braking force can be increased by providing pads on both sides of the disc and braking the disc with both sides sandwiched. A plurality of pads can be pressed and driven by a single brake body, and the mounting structure of the brake body can be simplified or shared. Further, since the plurality of pads are arranged opposite to each other at the same braking radius position on the same sliding surface, the sliding surface in the disk can be reduced. As a result, not only the size and weight of the brake can be reduced, but also the circumferential structure can be configured uniformly.

(Eighth embodiment)
FIG. 10 is a front view schematically showing a disk and a pad in the brake system according to the eighth embodiment. In the eighth embodiment, the same parts as those in the sixth embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 10, according to the eighth embodiment, the brake system has four pads 10A, 10B, 10C, and 10D. Both sides of the disk 11 are used as sliding surfaces, and the disk is sandwiched from both sides by the pads. It is configured as a double-sided sliding contact type brake system that brakes with

The pads 10 </ b> A and 10 </ b> B are arranged to face one side of the disk 11, and the pads 10 </ b> C and 10 </ b> D are arranged to face the opposite surface of the disk 11. With respect to the disk 11, the pad 10A is disposed at the position of the braking radius r1, and the pad 10B is disposed at the position of the control radius r2. With respect to the disk 11, the pad 10C is disposed at the position of the braking radius r2, and the pad 10D is disposed to face the position of the control radius r1. On the same sliding surface of the disk 11, the plurality of pads are arranged to face each other at different braking radius positions.
The relationship between the braking radii r1 and r2 is r1> r2.

The pads 10A and 10B are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The pads 10 </ b> C and 10 </ b> D are arranged with a deviation of several tens of degrees around the rotation center axis of the disk 11 with respect to the pads 10 </ b> A and 10 </ b> B.
According to the sixth embodiment configured as described above, the pads 10A and 10B and the pads 10C and 10D are in sliding contact with the sliding surface of the disk 11 at different braking radii r1 and r2. Therefore, the sliding area of the disk 11 on which the pads 10A and 10B slide can be increased. Therefore, in the sixth embodiment, the same operation and effect as in the first embodiment can be obtained. Further, the braking force can be increased by providing pads on both sides of the disc and braking the disc with both sides sandwiched. In addition, the disk thickness can be changed infinitely, the degree of design freedom can be expanded with respect to the specifications of the equipment, and the standardization and improvement of the brake can be achieved.

(Ninth embodiment)
FIG. 11 is a front view and a side view schematically showing disks and pads in the brake system according to the ninth embodiment. In the ninth embodiment, the same parts as those in the seventh embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 11, according to the ninth embodiment, the brake system has four pads 10A, 10B, 10C, and 10D. It is configured as a double-sided sliding contact type brake system that brakes with

  The pads 10 </ b> A and 10 </ b> B are arranged to face one side of the disk 11, and the pads 10 </ b> C and 10 </ b> D are arranged to face the opposite surface of the disk 11. With respect to the disk 11, the pads 10A and 10B are disposed at the position of the braking radius r1, and the pads 10C and 10D are disposed at the position of the control radius r2. On the same sliding surface of the disk 11, the plurality of pads are arranged opposite to each other at the same braking radius position. The relationship between the braking radii r1 and r2 is r1> r2.

The pads 10A and 10B are disposed 180 degrees apart from each other around the rotation center axis of the disk 11. Further, the pads 10A and 10B are arranged on the same diameter line of the disk 11. The pads 10 </ b> C and 10 </ b> D are arranged with a deviation of several tens of degrees around the rotation center axis of the disk 11 with respect to the pads 10 </ b> A and 10 </ b> B.
According to 9th Embodiment comprised as mentioned above, the effect | action and effect similar to 7th Embodiment mentioned above can be acquired. Further, the braking force can be increased by providing pads on both sides of the disc and braking the disc with both sides sandwiched. A plurality of pads can be pressed and driven by a single brake body, and the mounting structure of the brake body can be simplified or shared. Further, since the plurality of pads are arranged opposite to each other at the same braking radius position on the same sliding surface, the sliding surface in the disk can be reduced. As a result, not only the size and weight of the brake can be reduced, but also the circumferential structure can be configured uniformly.

  Since the braking radius position of the pad on each sliding surface of the disk is constant, the sliding surface in the disk can be reduced. As a result, not only the size and weight can be reduced, but also the circumferential structure can be configured uniformly.

(10th Embodiment)
FIG. 12 is a front view and a side view schematically showing disks and pads in the brake system according to the tenth embodiment. In the tenth embodiment, the same parts as those in the second embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 12, in the disk 11, for example, conical convex portions 30a and 30b are formed on the surface opposite to the sliding surface of the pads 10A and 10B. These convex portions 30a and 30b are provided such that the top portions thereof are at the positions of the braking radii r1 and r2 with respect to the disk 11, and the convex portions 30a and 30b are respectively placed on the pad 10A with the disk 11 in between. 10B.

  By providing such convex portions 30a and 30b, it is possible to increase the heat absorption mass of the disk 11 where the temperature rise is high during braking, and to make the relative temperature rise of the pads 10A and 10B uniform. it can. This not only keeps the temperature rise value constant, but also makes the amount of wear constant. As a result, the effects obtained in the first to ninth embodiments can be further enhanced.

(Eleventh embodiment)
FIG. 13 is a front view and a side view schematically showing disks and pads in the brake system according to the eleventh embodiment. In the eleventh embodiment, the same parts as those in the fifth embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 13, the pad 10A faces the disk 11 with respect to one side at the position of the braking radius r1, and the pad 10B faces the face opposite to the disk 11 at the position of the braking radius r2. It is. The pads 10 </ b> A and 10 </ b> B are disposed at equal angular positions around the rotation center axis C of the disk 11. That is, the pads 10 </ b> A and 10 </ b> B are arranged on the same diameter line of the disk 11 and are arranged on the same side with respect to the rotation center axis of the disk 11. The relationship between the braking radii r1 and r2 is r1> r2.

  In the disk 11, for example, conical convex portions 30a and 30b are formed on the surface opposite to the sliding surface of the pads 10A and 10B. These convex portions 30a and 30b are provided such that the top portions thereof are at the positions of the braking radii r1 and r2 with respect to the disk 11, and the convex portions 30a and 30b are respectively placed on the pad 10A with the disk 11 in between. 10B.

  By providing such convex portions 30a and 30b, it is possible to increase the heat absorption mass of the disk 11 where the temperature rise is high during braking, and to make the relative temperature rise of the pads 10A and 10B uniform. it can. This not only keeps the temperature rise value constant, but also makes the amount of wear constant. As a result, the effects obtained in the first to ninth embodiments can be further enhanced.

(Twelfth embodiment)
FIG. 14 is a front view schematically showing disks and pads in the brake system according to the twelfth embodiment. In the twelfth embodiment, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  The plurality of pads opposed to one side of the disk 11 are not necessarily arranged on the same diameter line, and may be arranged on different diameter lines. That is, as shown in FIG. 14, with respect to the disk 11, the pad 10A is disposed at the position of the braking radius r1, and the pad 10B is disposed at the position of the braking radius r2. The pads 10A and 10B are arranged on different diameter lines of the disk 11, respectively. The angle at which the pads 10A and 10B are separated from each other can be arbitrarily set.

  According to the twelfth embodiment, the same operations and effects as those of the first embodiment described above can be obtained. Further, the distance H between the pads 10A and 10B can be shortened, and the size and weight of the brake system can be reduced. The configuration of the present embodiment can be applied to the first to eleventh embodiments described above, and as its effect, it can be reduced in size and weight.

(13th Embodiment)
FIG. 15 is a front view schematically showing a disk and a pad in the brake system according to the thirteenth embodiment. In the thirteenth embodiment, the same parts as those in the second embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 15, according to the thirteenth embodiment, three pads 10 </ b> A, 10 </ b> B, and 10 </ b> C are arranged to face one side of the disk 11. The pads 10A, 10B, and 10C are arranged to face the disc 11 at the positions of the braking radii r1, r2, and r3, respectively, and the relationship between the braking radii is r1> r2> r3.

  Thus, two or more pads may be provided on one sliding surface of the disk 11. Even in this case, the same operations and effects as those of the first to twelfth embodiments can be obtained. Further, the braking force can be increased by increasing the number of pads. The decrease in the braking force by the pad 10B provided at the position of the braking radius r2 can be assisted by the braking force of the pad 10C provided at the position of the braking radius r3.

(14th Embodiment)
In the fourteenth embodiment, although not shown, the brake pressing force (F) is changed for the pads 10A and 10B having different braking radius positions. In this case, as shown in Equation 1 described above, even if the brake torque in each brake is constant, the heat absorption mass shown in Equation 3 can be changed, that is, expanded. As a result, an increase in the temperature of the brake can be suppressed. In the fourteenth embodiment, the same effect as in the first to thirteenth embodiments can be obtained.

(Fifteenth embodiment)
In the fifteenth embodiment, although not shown, when a plurality of pads and brake bodies are used, the one-surface braking type and the pad opposing type are used in combination. Even in this configuration, the same effects as those of the first to fourteenth embodiments can be obtained.

(Sixteenth embodiment)
In the sixteenth embodiment, although not shown, any one of the brake systems according to the first to fifteenth embodiments is applied to an elevator represented by an elevator.
In general, an elevator that requires a large capacity requires a very large braking capacity, and it is very effective in reducing the size and weight by suppressing the temperature rise value during one braking. In addition, since the cooling after braking can be performed quickly, the system stop time can be shortened.

(17th Embodiment)
In the seventeenth embodiment, although not shown, any one of the brake systems according to the first to fifteenth embodiments described above is applied to a vehicle brake represented by the Shinkansen.

  Vehicle wheels have a high rotational speed and a large number of brakings. Therefore, if the temperature rise during braking is kept low, the temperature rise can be kept low even during intermittent repeated braking, thereby suppressing the effects of thermal fatigue. it can. Further, even when traveling wind or the like is used as a cooling method after braking, the temperature difference between the temperature rise and the temperature fall can be reduced, so that the influence of thermal fatigue can be suppressed as described above. Furthermore, the configuration of the anti-sliding surface can be simplified, and not only the quality of the disk can be stabilized, but also the productivity can be improved.

(Eighteenth embodiment)
In the eighteenth embodiment, although not shown, any one of the brake systems according to the first to fifteenth embodiments is applied to an automobile or a two-wheeled vehicle. According to this brake system, since the pad friction surface can be made smooth, the noise of the brake represented by the squeal can be reduced.
As described above, the brake system according to the present invention can overcome various problems in various applications.

In the embodiment described above, the brake body of the sub-pressing mechanism is an electromagnetic brake, but is not limited thereto, and may be a hydraulic brake or a pneumatic brake.
Generally, in a hydraulic brake that requires a large capacity, a very large braking capacity is required. As described above, the brake system according to each embodiment is extremely effective in reducing the size and weight by suppressing the temperature rise value at the time of one braking, and cooling after braking is also quick. By doing so, it is possible to shorten the system stop time.

  In addition, in a pneumatic brake that requires small size and light weight, by using the brake system according to each embodiment, the temperature rise value is suppressed, and the small size and light weight are achieved. It is done.

  The braking operation may be performed simultaneously with a plurality of pads, or the pad operation start timing may be different for each braking radius position. When the operation timing of the pad is changed for each braking radius position, detailed settings other than the braking time are possible, so the temperature can be set even for intermittent temperature rises, and the system can be improved in quality. .

Note that the present invention is not limited to the above-described embodiment as it is, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the embodiments. For example, some components may be deleted from all the components shown in the embodiment. Furthermore, constituent elements over different embodiments may be appropriately combined.
For example, the number of pads and the shape of the pads are not limited to the above-described embodiments, and can be changed as necessary. The sliding surface of the disk by each pad is not limited to being completely separated from each other, and a part thereof may overlap.

The present invention has been described in detail above with reference to the embodiments. Hereinafter, in order to facilitate understanding of the present invention, specific modes of the invention will be added.
(Appendix 1)
A disc that rotates in conjunction with the rotating body of the device,
A plurality of pads each facing the disc;
A pressing mechanism for pressing each pad against the surface of the disc,
The brake system, wherein the plurality of pads are arranged opposite to different braking radius positions with respect to the disk.

(Appendix 2)
The disk has a sliding surface on one side,
The brake system according to claim 1, wherein the plurality of pads are arranged to face the sliding surface and are arranged at different braking radius positions on the same diameter line of the disc.

(Appendix 3)
The brake system according to claim 2, wherein the plurality of pads are disposed 180 degrees apart from the disk on the same diameter line of the disk and around the rotation center axis of the disk.

(Appendix 4)
The brake system according to claim 2, wherein the plurality of pads are disposed at the same angular position around the rotation center axis of the disk on the same diameter line of the disk with respect to the disk.

(Appendix 5)
The brake system according to claim 2, wherein the plurality of pads are arranged at different angular positions around the rotation center axis of the disc on different diameter lines of the disc with respect to the disc.

(Appendix 6)
The disk has sliding surfaces on both sides,
The plurality of pads include a pad arranged to face one sliding surface and a pad arranged to face the other sliding surface,
The brake system according to appendix 1, wherein the plurality of pads are arranged to face different braking radius positions from each other with respect to the disk.

(Appendix 7)
The brake system according to claim 6, wherein the plurality of pads are disposed at the same angular position around the rotation center axis of the disk with respect to the disk.

(Appendix 8)
The brake system according to appendix 6, wherein the plurality of pads are disposed at different angular positions around the rotation center axis of the disk with respect to the disk.

(Appendix 9)
The disk has sliding surfaces on both sides,
The plurality of pads include a plurality of pads arranged to face one sliding surface and a plurality of pads arranged to face the other sliding surface,
The brake system according to appendix 1, wherein the plurality of pads are arranged to face different braking radius positions from each other with respect to the disk.

(Appendix 10)
The brake system according to appendix 9, wherein the plurality of pads are arranged to face each sliding surface of the disk at different braking radius positions.

(Appendix 11)
The plurality of pads are arranged to face each sliding surface of the disk at the same braking radius position, and the pads facing the one sliding surface and the pads facing the other sliding surface are different from each other. The brake system according to appendix 9, wherein the brake systems are arranged to face each other at a braking radius position.

(Appendix 12)
The brake system according to appendix 10 or 12, wherein the plurality of pads are arranged to face the disc on the same diameter line of the disc.

(Appendix 13)
The plurality of pads arranged to face the one sliding surface are arranged to face the disk on the same diameter line of the disk, and the plurality of pads arranged to face the other sliding surface are 13. The brake system according to appendix 10 or 12, wherein the brake system is disposed at different angular positions around the rotation center axis of the disk with respect to the pad disposed opposite to the one sliding surface.

(Appendix 14)
The brake system according to any one of appendices 1 to 13, wherein the pressing mechanism includes a pressing portion that presses one pad independently.

(Appendix 15)
The brake system according to any one of appendices 1 to 14, wherein the pressing mechanism applies different brake pressing forces (F) to the plurality of pads.

(Appendix 16)
The brake system according to any one of appendices 1 to 15, wherein the pressing mechanism is an electromagnetic pressing mechanism.

(Appendix 17)
The brake system according to any one of appendices 1 to 15, wherein the pressing mechanism is a hydraulic pressing mechanism.

(Appendix 18)
The brake system according to any one of appendices 1 to 15, wherein the pressing mechanism is a pneumatic pressing mechanism.

(Appendix 19)
The brake system according to any one of appendices 1 to 18, wherein the pressing mechanism has different pad pressing timings for each pad at each sliding radius position.

10A, 10B, 10C, 10D ... Pad, 11 ... Disk, 12 ... Pressing mechanism,
14 ... Fixed iron core, 16 ... Working iron core, 17 ... Winding, 18 ... Spring

Claims (10)

A disc that rotates in conjunction with the rotating body of the device,
A plurality of pads each facing the disc;
A pressing mechanism for pressing each pad against the surface of the disc,
The disk has sliding surfaces on both sides,
The plurality of pads include a pad arranged to face one sliding surface and a pad arranged to face the other sliding surface,
The plurality of pads are arranged opposite to different braking radius positions with respect to the disk, and are arranged at different angular positions around the rotation center axis of the disk on different diameter lines of the disk. Brake system. Brake system according to claim 1 for each sliding surface of the disc, the plurality of pads which are oppositely arranged at a different braking radial positions. The plurality of pads are arranged to face each sliding surface of the disk at the same braking radius position, and the pads facing the one sliding surface and the pads facing the other sliding surface are different from each other. The brake system according to claim 1 , wherein the brake systems are arranged to face each other at a braking radius position. The plurality of pads arranged to face the one sliding surface are arranged to face the disk on the same diameter line of the disk, and the plurality of pads arranged to face the other sliding surface are 4. The brake system according to claim 2 , wherein the brake system is disposed at different angular positions around a rotation center axis of the disk with respect to a pad disposed opposite to one sliding surface. 5. The brake system according to any one of claims 1 to 4 , wherein the pressing mechanism includes a pressing portion that presses one pad independently. The brake system according to any one of claims 1 to 4 , wherein the pressing mechanism applies different brake pressing forces (F) to the plurality of pads. The brake system according to any one of claims 1 to 4 , wherein the pressing mechanism is an electromagnetic pressing mechanism. The brake system according to any one of claims 1 to 4 , wherein the pressing mechanism is a hydraulic pressing mechanism. The brake system according to any one of claims 1 to 4 , wherein the pressing mechanism is a pneumatic pressing mechanism. The brake system according to any one of claims 1 to 9 , wherein the pressing mechanism has different pad pressing timing for each pad at each sliding radius position.

Images