JP3672216B2 - Friction brake, disc brake device, disc brake device for elevator - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a friction brake, a disc brake device, and an elevator disc brake device capable of controlling a braking force.
[0002]
[Prior art]
FIG. 6 is an overall configuration diagram of an elevator including a conventional disc brake device disclosed in, for example, Japanese Patent Application Laid-Open No. 58-130875. In FIG. 6, 101 is a car driving motor, 101a is a rotating shaft, 102 is a sheave driven by the car driving motor 101 through the rotating shaft 101a, 103 is a car rope wound around the sheave 102, A car 104 and a counterweight 105 are coupled to the end. Reference numeral 106 denotes a brake disc fixed to the rotary shaft 101a, and 107 denotes an electromagnetic brake. A brake wheel 106 and a brake shoe 108 that is urged by a mechanism such as a spring (not shown) on the brake wheel 106 are separated from the brake wheel 106. And a coil 109.
[0003]
The conventional elevator disc brake device is configured as described above. When the car 104 is stopped, the applied current to the brake coil 109 is de-energized, and the brake shoe 108 is urged to the brake wheel 106 by the spring force. The car driving motor 101 is given a predetermined friction braking force.
[0004]
When the car 104 is moved to a predetermined floor from the stationary state, the braking force is released by energizing the brake coil 109 and releasing the brake shoe 108 from the brake wheel 106. Next, the car driving motor 101 is driven, and the sheave 102 connected to the car driving motor 101 rotates, whereby the car 104 travels toward a predetermined floor via the car rope 103. When the car 104 reaches the predetermined floor, the power supply to the car driving motor 101 is cut off, the current supply to the brake coil 109 is also turned off, and the braking force is applied to the car driving motor 101. .
[0005]
The above operation is a case of normal operation, but if any abnormality occurs during the traveling of the car 104 (for example, an abnormality in the car speed or opening of the passenger door), the power supply to the car driving motor 101 is cut off. The current to the brake coil 109 is also turned off. Accordingly, the braking force is applied while the car 104 is traveling. Then, the vehicle stops at a deceleration determined by the running conditions such as the weight in the car and the running direction and the braking force (hereinafter referred to as a sudden stop).
[0006]
In such a sudden stop, the passenger is subjected to excessive deceleration more than that which occurs during normal travel. For this reason, an extreme discomfort is given to a passenger.
[0007]
The above excessive deceleration occurs because the braking force generated by the brake device is set to be large. This is to provide a sufficient braking force to ensure safety during stationary holding, and is set so that the car 104 can be held stationary even when a load of about 170% of the loaded load is applied. . According to the above configuration, the braking force of the brake device is determined by the product of the coefficient of friction between the brake shoe and the brake wheel and the pressing force of the brake shoe on the brake wheel.
[0008]
The friction coefficient is a value determined by the material, and the pressing force is a constant value given by the spring force. Therefore, the braking force is almost equal to that during stationary while stationary. For this reason, while safety of stationary holding is ensured, there is a problem that the braking force during traveling is larger than necessary and excessive deceleration occurs. In order to solve this problem, it is necessary to reduce the braking force during traveling to an appropriate value. However, according to the brake mechanism, the braking force cannot be controlled.
[0009]
Conventionally, as a means for controlling braking force so as to obtain an appropriate deceleration, for example, in the devices disclosed in Japanese Patent Laid-Open Nos. 5-303607 and 7-76468, the brake coil constituting the electromagnetic brake is used as a brake coil. The current value to be supplied is controlled. FIG. 7 is an external view of a conventional brake device for controlling the braking force. The brake device of FIG. 7 includes a brake drum 229 and brake levers 230 disposed on both sides of the brake drum 229, a pin 231 that rotatably supports the brake lever 230 at its lower end, and a substantially rotating shaft of the brake lever 230. The brake shoe 233 is coupled to a position corresponding to the center of the 227 via a pin 232.
[0010]
A brake spring 236 is disposed above the brake lever 230, and the brake shoe 233 is biased by the brake drum 229 by the spring force of the brake spring 236 to generate a braking force. Further above the brake lever 230, electromagnetic magnets 219 for releasing the braking force by the brake spring 236 are provided between the brake levers 230 via the pressing rods 237, respectively.
[0011]
FIG. 8 is a configuration diagram of the electromagnetic magnet 219 of FIG. A yoke 238 constituting the box, a fixed iron core 239 fixed in the yoke 238, a movable rod 243 vertically passing through the fixed iron core 239 and the yoke 238, and a movable iron core fixed on the upper portion of the movable rod 243 240, a cylindrical coil 241 installed on the outer periphery of the fixed iron core 239 facing the movable iron core 240, a lever 242 whose one end abuts on the lower end of the movable rod 243, and one end abutting on the other end of the lever 242. 7 pressing rods 237. Note that the fixed iron core 239 and the movable iron core 240 are opposed to each other through the gap d.
[0012]
With this configuration, when a current is applied to the coil 241, the movable iron core 240 is attracted and moved toward the fixed iron core 239, and the movable rod 243 is moved downward. Then, the lever 242 rotates with the pin 247 as a fulcrum, and the movable rod 243 pushes the brake lever 230 against the spring force of the brake spring 236 in FIG. Further, since the attractive force of the movable iron core 240 can be controlled by changing the amount of current applied to the coil 241, the pressing force of the brake shoe 233 can be changed to change the braking force.
[0013]
However, in the above configuration, when the surface of the brake shoe 233 that contacts the brake drum 229 is worn, the gap d shown in FIG. 8 is increased. For this reason, even if the same current value as before the wear is supplied to the coil 241, the electromagnetic attractive force is reduced, the brake lever 230 cannot be spread with a predetermined pressing force, and a predetermined braking force cannot be obtained.
[0014]
[Problems to be solved by the invention]
As described above, the conventional disc brake device has various problems, and a predetermined braking force cannot be obtained.
[0015]
The present invention has been made to solve the above-described problems, and an object thereof is to provide a friction brake, a disc brake device, and an elevator disc brake device capable of setting a braking force to a predetermined magnitude. .
[0016]
[Means for Solving the Problems]
  In view of the above object, the present invention is a friction type having a first sliding member to be braked and a second sliding member to be braked that slide while contacting each other with a predetermined pressing force to generate a braking force. In the brake device, during braking, the time when the relative speed difference in the direction in which the braking force is generated between the sliding members becomes zero or the time when the sign is reversed is in a predetermined length while in contact with a predetermined pressing force. Braking force control means for driving the second sliding member to haveThe speed detecting means for detecting the speed of the first sliding member to be braked and the driving pattern in the predetermined speed region are stored in advance so that a predetermined braking force can be obtained according to the detected speed. And a calculation means for determining a drive pattern,
The braking force control means drives the second sliding member according to the drive pattern.The friction brake is characterized by that.
[0017]
Further, according to the present invention, the braking force control means has a predetermined length of time during which the relative speed difference in the direction in which the braking force is generated between the sliding members is 0 or when the sign is reversed, In the friction brake, the second sliding member is reciprocated in a direction substantially parallel to a direction in which a braking force is generated so as to be generated a plurality of times.
[0019]
  The present invention also provides a rotating disk, a brake shoe that is urged by the rotating disk to generate a braking force, and an urging force that allows the brake shoe to be urged against the rotating disk with a substantially constant pressing force and separated. And the brake shoe is urged against the rotating disk and vibrates in a direction in which a braking force is generated, and at least a difference in speed between contact portions of the brake shoe and the rotating disk is at least one cycle of vibration. Vibration means that vibrates so as to take positive and negative values one by one; drive control means that drives the vibration means under a predetermined drive condition;A speed detecting means for detecting the speed of the rotating disk; and a drive pattern of the vibrating means is determined so as to obtain a predetermined braking force based on a speed signal output from the speed detecting means, and the drive control means A computing means for outputting a drive pattern signal;A disc brake device comprising:
[0021]
The present invention also provides a rotating disk fixed to a rotating shaft of a car driving electric motor that raises and lowers an elevator car, a brake shoe that is urged by the rotating disk with a substantially constant pressing force to generate a braking force, An urging means that urges the brake shoe against the rotating disk with a substantially constant pressing force and separates the brake shoe, and vibrates the brake shoe in a direction in which a braking force is generated with the brake shoe being urged against the rotating disk. In addition, vibration means for vibrating so that the speed difference of the contact portion between the brake shoe and the rotating disk takes a positive value and a negative value at least once in one cycle of vibration, and the speed of the rotating disk is detected. Based on the speed detection means and the speed detected by the speed detection means, a driving pattern of the vibration means is determined so as to obtain a predetermined braking force. And means, located above the vibrating means according to the driving pattern of the operation unit in the elevator disc brake device characterized by comprising a driving control means for driving a predetermined driving condition.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described according to each embodiment.
Embodiment 1 FIG.
FIG. 1 is a schematic configuration diagram of a friction brake and a disc brake device according to an embodiment of the present invention. In the figure, reference numeral 2 denotes a brake shoe, which is supported so as to be capable of reciprocating (vibrating) in a direction substantially parallel to the direction in which the braking force indicated by the arrow B is applied, and an urging means (not shown in the figure) 5, the arm 43a, 43b, etc.) is biased and separated from the rotating disk 10 with a constant pressing force P. Reference numeral 10 denotes a rotating disk that moves (rotates) in the direction of arrow A, and is fixed to a rotating shaft 5. The rotating shaft 5 is engaged with an electric motor or sheave not shown.
[0023]
Reference numeral 1 denotes vibration means for causing the brake shoe 2 to vibrate in a direction substantially parallel to the direction in which the braking force indicated by the arrow B acts, and is engaged with the brake shoe 2. Further, the vibration means 1 can generate a force greater than the braking force acting between the brake shoe 2 and the rotating disk 10. For the vibration means 1, for example, a piezoelectric element, a magnetostrictive element, a voice coil motor, or the like is used. Reference numeral 4 denotes a drive control unit that causes the vibration unit 1 to vibrate at a predetermined timing. Further, the vibration means 1 is supported by a structure not shown so that the braking force acting between the brake shoe 2 and the rotary disk 10 can be sufficient.
[0024]
The braking force control means includes the vibration means 1 and the drive control unit 4, and the drive control unit means includes the drive control unit 4.
[0025]
Based on the configuration shown in FIG. 1, the operation during braking of this embodiment will be described. First, when the rotating disk 10 is rotating in the direction A, the brake shoe 2 is at a position away from the rotating disk 10. Then, the brake shoe 2 is urged to the rotating disk 10 with a predetermined pressing force P at a predetermined timing by an urging means (not shown) to generate a braking force. At the same time as the brake shoe 2 is urged to the rotating disk 10, a predetermined drive signal is output from the drive control unit 4. Based on this drive signal, the vibration means 1 vibrates the brake shoe 2 in the direction of arrow B, Control the braking force. The vibration of the brake shoe 2 by the vibration means 1 is performed from the start of braking until the rotating disk 10 stops or for a predetermined time set in advance.
[0026]
Next, the control principle of the braking force will be described with reference to FIG. 1 and FIG. 2 showing the speed, speed difference and braking force of the brake shoe 2 and the rotating disk 10. FIG. 2A shows the speed Vm of the contact portion of the rotating disk 10 with the brake shoe 2 and the speed Vs of the brake shoe 2 in a certain time region during braking. FIG. 2B shows the speed difference between Vs and Vm. FIG. 2C shows the braking force F received by the rotary disk 10. Note that the speed direction of the rotating disk 10 is positive for both Vm and Vs. On the other hand, the value of the braking force F is positive when it works in the direction in which the rotary disk 10 is stationary. In addition, the time regions in each of FIGS. 2A to 2C generally indicate changes during one period T0 of vibration.
[0027]
After the start of braking, the brake shoe 2 is expanded and contracted by the vibration means 1.
[0028]
Vs = f (t) (1)
∫₀ ^T0f (t) dt = 0
t: Time from the start of vibration means drive
[0029]
Vibrate at a speed Vs such that Here, the function f (t) in the expression (1) is a periodic function having a period T0. Further, as shown in FIG. 2A, the interval a-b where Vs> Vm exists in the period T0. For this reason, as shown in FIG. 2B, the sign of the relative speed (speed difference) between the brake shoe 2 and the rotating disk 10 is reversed between the section ab and the other sections. Further, the magnitude F0 of the braking force applied to the rotating disk 10 is as follows: P is the pressing force of the brake shoe 2, and μ is the friction coefficient between the rotating disk 10 and the brake shoe 2.
[0030]
F0 = P ・ μ (2)
[0031]
The value represented by Accordingly, in FIG. 2C, a positive braking force F0 is applied to the rotating disk 10 except for the section ab, whereas a negative braking force -F0 is applied to the section ab. Here, considering an average braking force Fa during time T0 corresponding to one cycle of Vs,
[0032]
Fa = F0 · (T0-2 · Td) / T0 (3)
Td: time interval for negative braking force
[0033]
It becomes. Also, when comparing the case where the braking force is vibrated and the case where it is not vibrated,
[0034]
F0> Fa = α · F0 (4)
However, 0 <α <1
[0035]
It becomes. In the equation (4), α is a coefficient representing the rate of change of the braking force. Accordingly, the average braking force can be reduced by vibrating the brake shoe 2 with the speed pattern of the condition of the expression (1), and the braking force is controlled by changing the time interval Td that becomes a negative braking force. Can do.
[0036]
In the above description, the period T0 has been described. However, the vibration unit 1 is continuously driven over a predetermined time until actually stopping. During this time, the rotating disk 10 decelerates. This corresponds to a decrease in V0 in FIG. For this reason, if the drive pattern of the vibration means 1 is constant, the time interval Td where Vs> Vm increases, and the braking force Fa decreases from the equation (3). Therefore, in order to obtain a desired Fa, a change in speed of the rotating disk when a predetermined braking force is applied is calculated in advance, and based on this, a predetermined Td value can be obtained for each vibration period. You only need to set a vibration pattern.
[0037]
Further, according to the above embodiment, the braking force is controlled by vibrating the brake shoe in parallel with the direction in which the braking force works while the brake shoe is urged against the rotating disk with a predetermined pressing force. Therefore, even if the brake shoe wears and its thickness changes, the operation of the vibration means is not affected, and the braking force can be stably controlled over a long period.
[0038]
Further, if the period T0 is reduced, the amount of work spent for braking during one period is reduced, so that the change in deceleration for each period is reduced, and smooth deceleration is possible.
[0039]
Embodiment 2. FIG.
FIG. 3 shows an example of a brake shoe and vibration means in the brake device of the present invention, in which (a) is a plan view and (b) is a right side view. As the vibration means 1, stacked piezoelectric elements 11a and 11b are used. The stacked piezoelectric elements 11a and 11b can expand in the direction of arrow C according to the applied voltage. One end of each of the stacked piezoelectric elements 11a and 11b is in contact with the levers 12a and 12b. Each other end is in contact with preload screws 14a and 14b.
[0040]
The preload screws 14a and 14b apply preload to the laminated piezoelectric elements 11a and 11b by tightening the screws. When a voltage is applied by the preload screws 14a and 14b, it is possible to prevent a tensile stress from being applied in the extending direction of the stacked piezoelectric elements 11a and 11b. The levers 12a and 12b are fixed to the fixing bases 21a and 21b with the notches 13a and 13b as fulcrums, respectively. One end portions of the levers 12a and 12b are in contact with the movable base 15, respectively.
[0041]
The movable table 15 is supported by leaf springs 16a, 16b, 16c, and 16d, and can move in the direction of arrow D in the figure. The brake shoe 2 is fixed to the movable table 15. Each of the leaf springs 16a, 16b, 16c, and 16d is joined to the movable base 15 at one end and the fixed bases 21a and 21b at the other end. The fixing bases 21a and 21b are fixed to urging means (not shown) with fixing screws 20a, 20b, 20c and 20d, respectively.
[0042]
Based on FIG. 3, the operation | movement which vibrates the brake shoe 2 is demonstrated. In order to displace the brake shoe 2 in the direction of the arrow D1, a predetermined voltage is applied only to the laminated piezoelectric element 11a. Thereby, the lever 12a rotates about the notch 13a as a fulcrum, and the movable base 15 is displaced in the direction of the arrow D1. At this time, the stacked piezoelectric element 11b is compressed via the lever 12b by the displacement of the movable base 15 in the direction of the arrow D1. Similarly, in order to displace the brake shoe 2 in the direction of the arrow D2, a predetermined voltage is applied only to the laminated piezoelectric element 11b. Thus, by extending the stacked piezoelectric elements 11a and 11b, the brake shoe 2 can be vibrated in the direction of arrow D. In this embodiment, the brake shoe 2 is driven in a predetermined speed pattern by controlling the applied voltage.
[0043]
According to this embodiment, the vibration means can be made smaller than when a solenoid or a hydraulic actuator is used as the vibration means.
[0044]
Embodiment 3 FIG.
In the first embodiment, in order to obtain a predetermined braking force, it is necessary to estimate the speed change of the rotating disk in advance and to determine the drive pattern of the vibration means 1 of the equation (1) based on this. Therefore, if the rotating disk is different from the expected rotation speed, a desired braking force cannot be obtained and stable braking cannot be performed. This embodiment solves this problem. This embodiment is for obtaining a predetermined braking value regardless of the speed of the rotating disk.
[0045]
FIG. 4 is a schematic configuration diagram of a friction brake and a disc brake device according to another embodiment of the present invention. In the figure, the same reference numerals as those in FIG. 1 denote the same or corresponding parts, and the description thereof is omitted. Reference numeral 31 in FIG. 4 denotes a speed detector that detects the speed of the rotating disk 10. The detected speed value is output to the 32 arithmetic units as a speed signal. The calculation unit 32 calculates a drive pattern of the vibration means 1 for controlling to a desired braking force from the speed signal from the speed detection unit 31 and a desired braking force value stored in advance. The calculated drive pattern is output to the drive control unit 4 as a drive pattern signal, and the vibration unit 1 is driven based on this drive pattern.
[0046]
The speed detector 31 constitutes a speed detector and the calculator 32 constitutes a calculator.
[0047]
Based on the configuration of FIG. 4, the operation principle of this embodiment will be described. In the following explanation, the braking force during braking is approximately constant regardless of the relative speed.
[0048]
Fc = α ′ · F0
[0049]
The case will be described. The value of the braking force change rate α at a certain speed of the rotating disk is such that the speed of the brake shoe 2 is larger than the speed of the rotating disk 10 during one vibration period T0, as shown in FIG. Determined by the ratio of time Td. Therefore, in order to make the rate of change α ′ constant in a predetermined speed region, the drive pattern of the vibration unit 1 is selected so that the ratio of Td to the period T0 is constant.
[0050]
In this embodiment, a driving pattern within a predetermined speed range is obtained in advance so as to obtain a desired change rate α ′, and this is stored in the computing means 32. At the time of actual braking, the speed of the rotating disk 10 is detected at the same time as braking is started, and the drive pattern is determined by the calculation unit 32 so that a predetermined braking force is obtained according to the detected speed value. As described above, by detecting the speed of the rotating disk 10 and changing the drive pattern of the vibration means 1 according to the detected speed value, the braking force is kept at a constant rate regardless of the speed change of the rotating disk 10. It is possible to change with.
[0051]
Note that the same effect as described above can be obtained even if the brake shoe 2 of FIG. 4 of this embodiment and the vibration means 1 for vibrating the same are used in the configuration shown in FIG. 3 of the second embodiment. .
[0052]
Embodiment 4 FIG.
FIG. 5 is an overall configuration diagram of an elevator disc brake device according to an embodiment of the present invention. In the figure, the same reference numerals as those in FIG. 6 denote the same or corresponding parts, and a description thereof will be omitted. The arms 43a and 43b are supported so as to be freely rotatable about the rotation shafts 44a and 44b. An electromagnetic magnet 45 and a spring 46 are connected to one end of each of the arms 43a and 43b, and vibration means 1a and 1b are fixed to the other end. The electromagnetic magnet 45 generates an electromagnetic attractive force by applying a voltage, and the brake shoes 2 a and 2 b can be separated from the rotating disk 10 against the spring force of the spring 46. The spring 46 biases the brake shoes 2a and 2b to the rotating disk 10 with a constant pressing force. A speed detector 31a detects the rotational speed of the motor, that is, the rotational speed of the rotary disk 10. The speed signal of the speed detector 31a is output to the calculation unit 32. Reference numeral 50 denotes an elevator control unit.
[0053]
Next, the operation of the brake device when braking for sudden stop will be described. First, in response to the emergency stop signal, voltage application to the electromagnetic magnet 45 is stopped, and an open state is set. The arms 43 a and 43 b are rotated about the rotation shafts 44 a and 44 b by the spring force of the spring 46, and the brake shoes 2 a and 2 b are urged to the rotating disk 10. Then, the brake shoes 2a and 2b are vibrated in a direction parallel to the direction in which the braking force is applied by the vibrating means 1a and 1b (for example, those shown in FIG. 3). The driving pattern of the vibration means 1a, 1b is set so as to have a predetermined braking force in the arithmetic unit 32 based on the speed signal detected by the speed detector 31a. The predetermined braking force is set in advance so as to satisfy the following two conditions. The condition is that the deceleration of the car 104 does not cause discomfort to the passengers and that the car 104 can be stopped within a predetermined braking distance.
[0054]
According to this embodiment, an excessive braking force is not applied to the car during a sudden stop, and it is possible to prevent the passenger from feeling uncomfortable.
[0055]
The brake mechanism described in each of the above embodiments is not limited to a disc brake device or an elevator disc brake device, but is a friction brake that slides while being pressed against each other and generates a braking force. Applicable to all.
[0056]
【The invention's effect】
As described above, in the present invention, the friction brake device having the first sliding member to be braked and the second sliding member to be braked that slide while contacting each other with a predetermined pressing force to generate a braking force. In this case, during braking, the time when the relative speed difference in the direction in which the braking force is generated between the sliding members becomes zero or the time when the sign is reversed is set to a predetermined length in the state of contact with a predetermined pressing force. Since the friction brake is provided with a braking force control means for driving the second sliding member, the braking force generated by the sliding member that generates the braking force is temporarily applied to 0 or in the reverse direction. Therefore, the average braking force during braking can be controlled, and the braking force can be increased to a predetermined level without being affected by the shape change due to wear of the sliding member that generates the braking force. Can be set.
[0057]
Further, in the present invention, the braking force control means has a predetermined length of time during which the relative speed difference in the direction in which the braking force is generated between the sliding members is 0 or the time when the sign is reversed. When the second sliding member is reciprocated in a direction substantially parallel to the direction in which the braking force is generated so that it is generated a plurality of times, the time interval for changing the braking force can be reduced and the braking force is controlled. But smooth braking is possible.
[0058]
Further, according to the present invention, the speed detecting means for detecting the speed of the first sliding member to be braked and the drive pattern in the predetermined speed region are stored in advance, and a predetermined braking force is applied according to the detected speed. Calculating means for determining a drive pattern so as to be obtained, and the braking force control means drives the second sliding member in accordance with the drive pattern. Stable braking force control is possible regardless of the speed of the moving member, that is, the magnitude or change of the relative speed difference between the sliding members.
[0059]
According to the present invention, the rotating disk, the brake shoe that is urged by the rotating disk and generates a braking force, and the urging force that urges the brake shoe against the rotating disk with a substantially constant pressing force and can be separated. And the brake shoe is urged against the rotating disk and vibrates in a direction in which a braking force is generated, and at least a difference in speed between contact portions of the brake shoe and the rotating disk is at least one cycle of vibration. Since the disc brake device is provided with the vibration means that vibrates so as to take positive and negative values once and the drive control means that drives the vibration means under a predetermined drive condition, the brake shoe to the rotary disk By reversing the direction of the braking force at predetermined time intervals, the braking force can be controlled and the shape of the brake shoe due to wear Without being affected by the reduction, it is possible to set the braking force to a predetermined size.
[0060]
According to the present invention, in the disc brake device, the vibration means is driven so that a predetermined braking force is obtained based on a speed detection means for detecting the speed of the rotating disk and a speed signal output from the speed detection means. And a calculation means for determining a pattern and outputting a drive pattern signal to the drive control means, so that the drive pattern of the vibration means is controlled in accordance with the speed of the rotary disk. A stable desired braking force can be obtained regardless of the speed change.
[0061]
According to the present invention, a rotating disk fixed to a rotating shaft of a car driving motor that raises and lowers an elevator car, a brake shoe that is urged by the rotating disk with a substantially constant pressing force to generate a braking force, An urging means that urges the brake shoe against the rotating disk with a substantially constant pressing force and separates the brake shoe, and vibrates the brake shoe in a direction in which a braking force is generated with the brake shoe being urged against the rotating disk. In addition, vibration means for vibrating so that the speed difference of the contact portion between the brake shoe and the rotating disk takes a positive value and a negative value at least once in one cycle of vibration, and the speed of the rotating disk is detected. Based on the speed detection means and the speed detected by the speed detection means, the drive pattern of the vibration means is determined so as to obtain a predetermined braking force. Since the elevator disc brake device is provided with calculation means and drive control means for driving the vibration means under a predetermined drive condition in accordance with the drive pattern of the calculation means, the brake shoe according to the speed of the car during a sudden stop Since the braking force generated by the brake device is controlled by vibrating the vehicle, an excessive braking force is not applied to the car and it is possible to prevent the passenger from feeling uncomfortable.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram of a friction brake and a disc brake device according to an embodiment of the present invention.
FIG. 2 is a diagram for explaining a braking force control method in the friction brake and disc brake device of FIG. 1;
FIG. 3 is a view showing an example of a brake shoe and vibration means in the brake device of the present invention.
FIG. 4 is a schematic configuration diagram of a friction brake and a disc brake device according to another embodiment of the present invention.
FIG. 5 is an overall configuration diagram of an elevator disc brake device according to an embodiment of the present invention.
FIG. 6 is an overall configuration diagram of an elevator including a conventional disc brake device.
FIG. 7 is an external view of a conventional brake device that controls braking force.
8 is a configuration diagram of the electromagnetic magnet of FIG. 7. FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Vibrating means, 2 brake shoes, 4 Drive control part, 5 Rotating shaft, 10 Rotating disk, 11a, 11b Laminated piezoelectric element, 12a, 12b Lever, 13a, 13b Notch part, 14a, 14b Preload screw, 15 Movable Base, 16a-16d leaf spring, 20a-20d fixing screw, 21a, 21b fixing base, 31, 31a speed detection unit, 32 calculation unit, 43a, 43b arm, 44a, 44b rotating shaft, 45 electromagnetic magnet, 46 spring, 50 Elevator control unit, 101 car driving motor, 102 sheave, 103 car rope, 104 car, 105 counterweight.

Claims (4)

In a friction brake device having a first sliding member to be braked and a second sliding member to be braked, which slide while contacting each other with a predetermined pressing force and generate a braking force,
During braking, in a state of contact with a predetermined pressing force, it has a predetermined length of time when the relative speed difference in the direction in which the braking force is generated between the sliding members becomes 0 or when the sign is reversed. Braking force control means for driving the second sliding member ;
Speed detecting means for detecting the speed of the first sliding member to be braked;
Calculation means for preliminarily storing a drive pattern in a predetermined speed region and determining the drive pattern so as to obtain a predetermined braking force according to the detected speed;
With
The friction brake , wherein the braking force control means drives the second sliding member according to the drive pattern .   The braking force control means is configured to generate a plurality of times with a predetermined length of time during which the relative speed difference in the direction in which the braking force is generated between the sliding members is 0 or the time when the sign is reversed during braking. The friction brake according to claim 1, wherein the second sliding member is reciprocated in a direction substantially parallel to a direction in which a braking force is generated. A rotating disk;
A brake shoe that is urged by the rotating disk to generate a braking force;
An urging means capable of urging the brake shoe against the rotating disc with a substantially constant pressing force and separating the urging shoe;
The brake shoe is oscillated in the direction in which a braking force is generated in a state where the brake shoe is urged to the rotating disk, and the speed difference between the contact portions of the brake shoe and the rotating disk is at least once in one cycle of vibration. Vibration means for vibrating to take positive and negative values;
Drive control means for driving the vibration means under a predetermined drive condition ;
Speed detecting means for detecting the speed of the rotating disk;
A calculation means for determining a drive pattern of the vibration means so as to obtain a predetermined braking force based on the speed signal output from the speed detection means, and outputting a drive pattern signal to the drive control means;
A disc brake device comprising: A rotating disk fixed to the rotating shaft of a car driving motor for raising and lowering the elevator car;
A brake shoe that is urged against the rotating disk by a substantially constant pressing force to generate a braking force;
Urging means for urging the brake shoe against the rotating disk with a substantially constant pressing force and separating the urging shoe;
The brake shoe is oscillated in the direction in which a braking force is generated in a state where the brake shoe is urged to the rotating disk, and the speed difference between the contact portions of the brake shoe and the rotating disk is at least once in one cycle of vibration. Vibration means for vibrating to take positive and negative values;
Speed detecting means for detecting the speed of the rotating disk;
Arithmetic means for determining a drive pattern of the vibration means so as to obtain a predetermined braking force based on the speed detected by the speed detection means;
Drive control means for driving the vibration means under a predetermined drive condition according to the drive pattern of the calculation means;
A disc brake device for an elevator, comprising:

Images