JP5388054B2 - Elevator with elevator vibration control device - Google Patents

Description

  The present invention relates to an elevator including an elevator vibration control device for reducing vibration of the elevator.

  In recent years, with the space saving of buildings, elevators of a machine room-less type in which a hoisting machine is downsized and installed in a hoistway have become widespread. In a machine roomless type elevator, a car is moved up and down via a rope wound around a sheave of the hoisting machine when the hoisting machine is driven in the hoistway. At this time, the vibration of the hoisting machine is transmitted to the building side through a beam or the like. In particular, when the diameter of the sheave is reduced by improving the strength of the rope, the diameter of the sheave is reduced accordingly, and the sheave rotates at a high speed to generate vibration of about 10 Hz or more. This vibration causes noise on the wall of the house on the building side. From such a background, a vibration damping device is installed together with the vibration sensor on the support member that supports the hoisting machine, and the vibration detected by the vibration sensor by driving the vibration damping device is used as the vibration damping force. There has been proposed a technique for reducing vibrations transmitted to a building via a support member by giving the support member (see Patent Document 1).

JP 2007-297180 A

  A conventional vibration damping device includes a casing attached to a support member, an elastic body that supports a weight having a magnetic body at least partially in the casing so as to be displaceable in a vibration damping direction (for example, a vertical direction), and a weight in the casing. And an electromagnet disposed opposite to the electromagnet, and configured to apply a damping force to the support member via the casing by vibrating the weight in the damping direction by the action of the electromagnetic force generated by the electromagnet on the magnetic body. Yes. However, in the conventional vibration damping device, since the weight is simply supported by an elastic body, when a vibration having a component in a direction orthogonal to the vibration damping direction (for example, the left-right direction) is applied, the weight The displacement in the direction orthogonal to the vibration damping direction may make it impossible to effectively apply the vibration damping force to the support member. If the displacement is large, the weight may come into contact with the inner wall surface of the casing and break.

  In addition, in order to more reliably reduce the vibration transmitted to the building side via the rail bracket etc., it is necessary to install it in a place where the vibration for vibration suppression generated by the vibration suppression device can maximize its effect. . That is, Patent Document 1 described above discloses an example in which a vibration damping device is installed on a support member that supports the hoisting machine. However, the hoisting machine is considered to be the cause of the vibration of the elevator apparatus. There is no doubt that it will be more than a hoist. Therefore, there is room for examination as to where to install the vibration damping device in an elevator, such as a hoistway or an elevator car.

  Accordingly, an object of the present invention is to reduce the amount of displacement of the weight in the direction orthogonal to the vibration damping direction, and to efficiently and reliably reduce the vibration that can be generated from each part of the elevator with the vibration damping force. It is providing an elevator provided with the elevator damping device installed in the place.

  The feature of the embodiment of the present invention is that the elevator is guided by a car that is guided by a car-side guide rail and moves up and down in a hoistway, a hoisting machine that rotationally drives a traction sheave, and a counterweight guide rail. The counterweight that moves up and down in the hoistway, the car sheave that suspends the car, and the traction sheave are wrapped around the car, and one end of the car is suspended through the car sheave, and the other end receives the counterweight. A hoisting rope that is suspended, a casing that is attached to the object to be controlled, an elastic body that supports a weight having a magnetic body at least partially in the casing so as to be displaceable in a vibration-suppressing direction, and a weight that is opposed to the weight in the casing. And the weight is moved in the damping direction by the action of the electromagnetic force of the electromagnet on the magnetic body. The vibration damping force is applied to the object to be controlled through the casing, and the spring constant of the elastic body in the vibration control direction is set to be smaller than the spring constant in the direction orthogonal to the vibration control direction. Device.

  According to the elevator according to the present invention, the amount of displacement of the weight in the direction orthogonal to the vibration damping direction can be reduced, and vibration that can be generated from each part of the elevator can be efficiently and reliably reduced by the vibration damping force. An elevator including an elevator vibration control device installed at a place where it can be provided can be provided.

It is a figure which shows the structure of the machine roomless type elevator used as one Embodiment of this invention. It is a figure which shows the internal structure of the damping device shown in FIG. It is a figure for demonstrating the structure of the control system of the damping device shown in FIG. It is a figure which shows the relationship between the spring constant of the damping direction of an elastic body, and the spring constant of the direction orthogonal to the damping direction. It is a figure which shows the frequency characteristic of the phase shift with respect to the damping force output from a damping device and its electromagnetic force. It is a figure which shows the change of the damping force output from the damping device with respect to the change of the gap length between a weight and an electromagnet. It is a figure which shows the change of the frequency characteristic of the damping force output from the damping device with the change of the damping constant of an elastic body. It is explanatory drawing which shows an example at the time of installing a damping device in a hitch part. It is explanatory drawing which shows an example at the time of installing a damping device in a hitch part. It is explanatory drawing about the installation position of the damping device at the time of preventing that the vibration which arises in a rope is transmitted to a passenger car via a car frame. It is explanatory drawing about the installation position of the damping device at the time of preventing that the vibration which arises in a rope is transmitted to a passenger car via a car frame. It is explanatory drawing about the installation position of the damping device at the time of preventing that the vibration which arises in a rope is transmitted to a passenger car via a car frame. It is explanatory drawing which shows an example at the time of installing a damping device in a rail bracket. It is explanatory drawing which shows an example at the time of installing a damping device in a rail bracket. It is explanatory drawing which shows an example at the time of installing a damping device in a rail bracket. It is explanatory drawing which shows an example at the time of installing a damping device in a rail bracket. It is the figure which looked at the rail bracket etc. in the arrow direction shown in FIG. It is explanatory drawing which shows an example at the time of installing a damping device in a winding machine. It is explanatory drawing which shows an example at the time of installing a damping device in a winding machine. It is the figure which simplified and showed the hoistway where the two passenger cars were installed adjacent to each other from the top. It is a perspective view which simplifies and shows the positional relationship with a building beam and a beam. It is a perspective view which shows the outline of the whole structure of the machine roomless type elevator used as another embodiment of this invention.

  The machine room-less type elevator configuration is such that, for example, a control panel or a hoisting machine is arranged on a wall or rail in a hoistway instead of a conventional machine room as disclosed in Japanese Patent Application Laid-Open No. 2004-115161. ing. These rails and the like are fixed to the inner wall of the hoistway by brackets and the like, and vibrations generated by driving the hoisting machine and raising and lowering the car are transmitted to the building, causing noise and the like. Hereinafter, a configuration of a machine roomless type elevator to which an elevator vibration control device according to the present invention is applied will be described with reference to the drawings.

[Overall configuration of elevator]
First, an overall configuration of a machine roomless elevator according to an embodiment of the present invention will be described with reference to FIG.

  In a machine roomless type elevator according to an embodiment of the present invention, as shown in FIG. 1, devices such as a hoisting machine 11 (including a control panel (not shown)) are downsized and arranged in a hoistway 10. Has been. The hoisting machine 11 is installed on a support member 12 installed in the horizontal direction above the hoistway 10 via a receiving base 13. The support member 12 is made of, for example, a strong iron member (a building beam can be used). The cradle 13 attached to the bottom of the hoisting machine 11 is made of a sound absorbing member such as a vibration-proof rubber. A main sheave (traction sheave; hereinafter referred to as “main sheave”) 14 is rotatably attached to a rotating shaft 11 a of the hoisting machine 11, and a (winding) rope 15 is wound around the main sheave 14.

  Both ends of the rope 15 are fixed to hitch portions provided at predetermined locations of the hoistway 10, and the car 16 is coupled with a counterweight W (not shown) via a car lower sheave 17a, 17b in a 2: 1 roping method. It is supported. Although only one rope 15 is shown in FIG. 1, in reality, a plurality of ropes 15 are wound around the main sheave 14, the car lower sheaves 17a, 17b, and the like. The car 16 is slidably supported by the pair of guide rails 18 a and 18 b and moves up and down via the rope 15 in accordance with the driving of the hoisting machine 11. The guide rails 18a and 18b are connected to the support member 12, and the end of the support member 12 is fixed to the side wall 19 of the building.

  In the machine roomless type elevator having such a configuration, vibration is generated as the hoisting machine 11 is driven, and the vibration is transmitted around the hoisting machine 11. In particular, when the diameter of the rope 15 is reduced by improving the strength of the rope 15, the diameter of the main sheave 14 is also reduced accordingly, so that vibration of about 10 Hz or more is likely to occur due to high-speed rotation. This vibration is transmitted to the side wall 19 of the building through the support member 12 and causes noise, for example, on the wall of a residence. Therefore, in this machine roomless type elevator, a vibration sensor 20 and a damping device 21 are provided on the support member 12 in order to reduce vibration transmitted from the hoisting machine 11 to the side wall 19 of the building.

  The vibration sensor 20 is composed of, for example, an acceleration sensor, and detects vibration generated at the installation location. The vibration damping device 21 applies a vibration damping force to the vibration damping target (the support member 12 in this example) by moving the weight 22 in a predetermined direction based on the vibration signal detected by the vibration sensor 20. More specifically, the vibration damping device 21 is provided together with the vibration sensor 20 on the back side of the support member 12 (that is, the surface opposite to the hoisting machine 11). The vibration transmitted to the support member 12 when the hoisting machine 11 is driven is detected by a vibration sensor 20 provided on the support member 12. The vibration damping device 21 generates a force having a phase opposite to that of the vibration transmitted to the support member 12 by moving the internal weight 22 based on the vibration signal detected by the vibration sensor 20. As a result, a damping force is applied to the support member 12 and the vibration from the hoisting machine 11 is offset. As a result, vibration transmitted from the hoisting machine 11 to the side wall 19 of the building via the support member 12 can be reduced.

[Internal configuration of vibration control device]
Next, with reference to FIG. 2, the internal configuration of the vibration damping device 21 according to an embodiment of the present invention will be described.

  The vibration damping device 21 includes a casing 24 that forms a space 23 that accommodates a weight 22 having at least a part of a magnetic body therein, a recess 25 formed in a bottom surface 24 a inside the casing 24, and a weight 22. 24. Electromagnets 26a and 26b arranged opposite to the upper surface on the inner side 24 and the bottom surface 25a of the recess 25, and the bottom surface 24a on the inner side of the casing 24, and the weight 22 in the direction of arrows a and b in the figure (damping direction, vertical direction) ) Are provided with elastic bodies 27a and 27b that are movably supported. In the vibration damping device 21, when the electromagnets 26 a and 26 b are excited, the weight 22 having at least a part of the magnetic material is moved in the vibration damping direction by the electromagnetic force generated at that time, and the reaction force acts on the casing 24. . Therefore, if the electromagnets 26a and 26b are subjected to excitation control so that the reaction force acting on the casing 24 becomes a damping force, the vibration from the hoisting machine 11 can be offset.

  The casing 24 only needs to have upper and lower surfaces on which the electromagnets 26a and 26 are provided, and does not necessarily have four side surfaces. Further, the electromagnets 26a and 26b are positions corresponding to nodes (points that do not displace during vibration) of the rotation system of the vibration system constituted by the weight 22 and the elastic bodies 27a and 27b (the weight 22 when there are two elastic bodies). It is desirable to arrange at the center of gravity position. According to such a configuration, it is possible to prevent the damping force from being accurately controlled by exciting the secondary vibration mode of the weight 22 (for example, swinging rotation about the center of gravity of the weight 22).

  The cores constituting the electromagnets 26a and 26b are preferably formed of a material having a relatively large electrical resistance, such as laminated steel sheets, ferrite, and permalloy. This is because, when the core is formed of a material having a relatively small electrical resistance such as iron, when a high frequency current is applied to the coil, an eddy current is generated on the surface of the core, so that the generated electromagnetic force is generated in the electromagnets 26a and 26b. This is because there is a possibility that the vibration damping force cannot be accurately controlled.

[Control system configuration of vibration control device]
Next, the configuration of a control system according to an embodiment of the present invention that controls the operation of the vibration damping device 21 will be described with reference to FIG.

  The control device 40 is configured by a general-purpose computer such as a DSP (Digital Signal Processor), and includes an A / D converter 41, a high-pass filter 42, an integrator 43, a gain adjuster 44, a square root calculator 35, an electromagnetic force distribution calculator. 45, and D / A converters 46 and 47. The vibration signal detected by the vibration sensor 20 is A / D converted by the A / D converter 41 and then given to the high-pass filter 42, and the vibration component in the frequency range (for example, about 50 to 300 Hz) suppressed by the high-pass filter 42. Is extracted. The vibration component extracted by the high pass filter 42 is numerically integrated by the integrator 43 and then multiplied by a predetermined gain by the gain adjuster 44 to generate a vibration suppression signal.

  The electromagnets 26 a and 26 b provided in the vibration damping device 21 can only generate electromagnetic force in the direction in which the weight 22 is attracted (vibration damping direction). Therefore, in the electromagnetic force distribution computing unit 45, for example, at the moment when the weight 22 is moved upward (in the direction of arrow a), the attracting action by the electromagnetic force of one electromagnet 26a is increased, and the attracting action by the electromagnetic force of the other electromagnet 26b is increased. The electromagnetic force of the electromagnets 26a and 26b is distributed according to the timing at which the weight 22 is moved so as to reduce the weight. The damping signal output from the electromagnetic force distribution calculator 45 is D / A converted by the D / A converters 46 and 47 and amplified by the amplifiers (AMP) 48 and 49 as necessary, and then the electromagnets 26a and 46a. 26b. As a result, the electromagnets 26 a and 26 b are excited and the reaction force acts on the casing 24, so that the vibration from the hoisting machine 11 can be offset.

When the electromagnets 26a and 26b are U-shaped electromagnets, the electromagnetic force F generated by the electromagnets 26a and 26b is S for the magnetic path cross-sectional area, N for the number of coil turns, I for the coil current, and the magnetic path length of the electromagnet core. L1, the magnetic path length of the weight 22 is L2, the gap length between the electromagnets 26a, 26b and the weight 22 is L3, the permeability of the electromagnet core is μ1, the permeability of the weight 22 is μ2, and the air permeability is μ0. It is expressed as the following formula 1.

  That is, since the damping force generated by the damping device 21 is proportional to the square value of the coil current I, when the magnitude of the damping force is input to the control device 40 as a control signal, the control device 40 The coil current I must be derived by converting to a signed square root signal. From the above, when the magnitude of the damping force is input as a control signal to the control device 40, it is desirable that the square root calculator 35 converts the control signal into a signed square root signal.

  As described above, in the machine roomless type elevator according to the embodiment of the present invention, the vibration control device 21 is installed together with the vibration sensor 20 on the member (support member 12 or machine bed) that supports the elevator hoisting machine 11. By driving the vibration damping device 21 based on the vibration signal detected by the vibration sensor 20, the vibration transmitted from the hoisting machine 11 through the side wall 19 of the building through the support member is reduced, and to the next room in the building, etc. Can reduce the effects of

[Configuration of elastic body]
When the weight 22 is simply supported by the elastic bodies 27a and 27b, when a vibration having a component perpendicular to the vibration damping direction is applied, the weight 22 is displaced in a direction perpendicular to the vibration damping direction. By doing so, there is a possibility that high-frequency vibration in the damping direction cannot be effectively reduced. If the amount of displacement is large, the weight 22 may come into contact with the inner wall surface of the casing 24 and break. Therefore, in the present embodiment, as shown in FIG. 4, the spring constant k1 in the vibration damping direction of the elastic bodies 27a and 27b is set to be smaller than the spring constant k2 in the direction orthogonal to the vibration damping direction.

  According to such a configuration, the amount of displacement of the weight 22 in the direction orthogonal to the vibration damping direction can be reduced, so that vibration in the vibration damping direction can be effectively reduced and the weight 22 is provided in the casing 24. Can be prevented from contacting the inner wall surface. As a method of setting the spring constant k1 in the damping direction of the elastic bodies 27a and 27b to a magnitude smaller than the spring constant k2 in the direction orthogonal to the damping direction, for example, a method for controlling the material characteristics of the elastic bodies 27a and 27b Alternatively, a method of arranging a member that restricts displacement in a direction orthogonal to the vibration damping direction on the side surfaces of the elastic bodies 27a and 27b is conceivable.

  In the present embodiment, the dynamic characteristics of the vibration damping device 21 can be modeled as a two-degree-of-freedom vibration system in which one weight having translational and rotational degrees of freedom is supported by two springs. Therefore, the frequency characteristic of the output (vibration suppression force) of the vibration damping device 21 with respect to the electromagnetic force generated by the electromagnets 26a and 26b can be calculated as a forced vibration response of a general two-degree-of-freedom vibration system. FIGS. 5A and 5B show the results of calculating the frequency characteristics of the output of the vibration damping device 21 with respect to the electromagnetic force generated by the electromagnets 26a and 26b by this method. In this calculation, the primary resonance frequency determined by the mass of the weight 22 and the spring constant k1 of the elastic bodies 27a and 27b is set to 25 Hz, and the amplitude of the electromagnetic force applied is 120N.

As shown in FIGS. 5A and 5B, in the vibration damping device 21 of the present embodiment, the primary resonance frequency f1 (the following equation) determined by the mass m of the weight 22 and the spring constant k1 of the elastic bodies 27a and 27b. 2), the magnitude of the output substantially coincides with the applied electromagnetic force, and the output phase shift is within 30 °. As can be seen from FIG. From the above, the spring constant k1 of the elastic bodies 27a and 27b is the minimum frequency in the frequency range in which the primary resonance frequency f1 determined by the mass of the weight 22 and the spring constant k1 of the elastic bodies 27a and 27b is suppressed (FIG. 5 (a In the example shown in (2), it is desirable to set the frequency so that it is about 50 Hz) or less.

In the present embodiment, the active position control of the weight 22 is not performed, and the position of the weight 22 is passively controlled only by the restoring force of the elastic bodies 27a and 27b. Therefore, as shown in FIG. As the amount increases, the gap length L3 between the weight 22 and the electromagnets 26a and 26b decreases, and the electromagnetic force of the electromagnets 26a and 26b increases, which may cause the weight 22 to be attracted to the electromagnets 26a and 26b. is there. Here, the equation of motion of the weight 22 when the attractive force F is applied from the electromagnets 26a and 26b is approximately expressed by the following Equation 3. In Equation 2, the parameters m, c, k1, F, dx, α are the weight of the weight 22, the damping constant of the elastic bodies 27a, 27b, the spring constant of the elastic bodies 27a, 27b, the minute displacement of the weight 22, and The change rate of the attractive force F accompanying the change of the gap length is shown.

  That is, the change rate α of the suction force F acts as a negative spring force with respect to the displacement dx of the weight 22. Therefore, in order to prevent the weight 22 from being attracted to the electromagnets 26a and 26b, the actual spring constant (k1-α) with respect to the displacement of the weight 22 must always be positive. On the other hand, when the spring constants k1 of the elastic bodies 27a and 27b are large, the attractive force F generated by the electromagnets 26a and 26b is absorbed as internal forces by the elastic bodies 27a and 27b, and the performance deteriorates. For this reason, it is desirable that the spring constant k1 in the vibration damping direction of the elastic bodies 27a and 27b is substantially the same as the rate of change α of the attractive force F or greater than the rate of change α of the attractive force F.

  When an external signal (for example, stepped electromagnetic force) is applied to the weight 22, the output of the damping device 21 is determined by the mass of the weight 22 and the spring constant of the elastic body as shown in FIG. Shows the characteristic of oscillating (waveforms P1 to P3), and there is a possibility that the electromagnets 26a and 26b and the weight 22 come into contact with each other. Therefore, it is desirable to set the damping constant c of the elastic bodies 27a and 27b to a value that does not contact the electromagnets 26a and 26b and the weight 22 when a stepped electromagnetic force is applied to the weight 22.

[Installation position of vibration control device]
As described above, in order to more surely reduce the vibration transmitted to the building side via the beam, etc., the vibration damping device is installed in a place where the vibration for vibration damping generated by the vibration damping device can maximize its effect. It is necessary to install. In FIG. 1, since the vibration suppression target is the support member 12, the vibration suppression device 21 is provided on the back side of the support member 12 together with the vibration sensor 20. That is, a portion where vibration is generated in the elevator is set as a vibration control target, and the vibration control device 21 is installed in that portion.

  For example, when the hoisting machine 11 is driven and the main sheave 14 is rotated to wind up the rope 15, vibration is transmitted to the hitch portion H via the rope 15, and the support member 12 is vibrated. In order to stop the vibration of the support member 12, a plurality of vibration control devices 21 are installed on the support member 12 and sandwich the hitch portion H in FIG. 8. By installing the vibration damping device 21 at this position, the above-described vibration is offset and reduced. Moreover, when there is no installation place on the support member 12, it is also possible to install the damping device 21 above the hitch portion H as shown in FIG. In this case, a base 50 for further transmitting the vibration transmitted to the support member 12 is installed on the support member 12 so as to sandwich the hitch portion H, and a plate 51 is passed over the base 50 and a vibration is suppressed on the plate 51. The device 21 is installed. By installing the vibration damping device 21 at this position, vibration can be reduced by the vibration damping force.

  The number of damping devices 21 to be installed can be arbitrarily set in accordance with the magnitude of vibrations to be generated. In the drawings used in the following description, only the vibration damping device 21 is displayed, and the display of the vibration sensor 20 is omitted.

  Next, the installation position of the vibration damping device 21 when preventing the vibration generated in the rope 15 from being transmitted to the car via the car frame when the rope 15 is wound up by the hoisting machine 11 will be described. The elevator car 16 shown in FIG. 1 described above is supported by a rope 15 via car lower sheaves 17a and 17b. FIG. 10 is an enlarged view showing the state.

  The lower sheaves 17a and 17b of the car are attached to a sheave mounting beam 60 that is a sheave support, and the lower beam 16a of the car 16 is attached via a pedestal 61 made of vibration-proof rubber or the like that absorbs vibration of the car 16. It has been. Since the rope 15 is stretched over the car lower sheaves 17a and 17b, for example, when the hoisting machine 11 winds the rope 15, the car lower sheaves 17a and 17b rotate to raise the car 16. Therefore, the vibration when the hoisting machine 11 winds the rope 15 is transmitted to the car 16 via the car lower sheaves 17a and 17b. Therefore, by installing the vibration damping device 21 on the sheave mounting beam 60, vibration to the car 16 that cannot be absorbed by the cradle 61 can be reduced by the vibration damping force.

  As for the installation position of the vibration damping device 21 for canceling and reducing the vibration of the rope 15 hung around the sheave, for example, the installation position is shown in FIG. 11 and FIG. 12, in addition to the position shown in FIG. It is also effective.

  FIG. 11 is a diagram showing an example in which the vibration damping device 21 is installed in the upper beam 62 constituting the car frame of the car 16. In FIG. 11, the sheave support 64 that supports the sheave 63 around which the rope 15 is hung is connected to the upper beam 62 via the connecting portion 65. When the hoisting machine 11 is driven, when the rope 15 is wound up and the sheave 63 moves, the vibration is transmitted to the upper beam 62 through the connecting portion 65. Therefore, vibration transmitted by installing the vibration control device 21 on the upper beam 62 to be controlled can be reduced by the vibration control force.

  FIG. 12 is a diagram illustrating an example in which a sheave 63 is provided under the upper beam 62. In this case, a sheave mounting beam 60 is provided on the car 16 side of the upper beam 62 via a cradle 61, and the rope 15 is stretched around sheaves 63 a and 63 b that are mounted on the sheave mounting beam 60. In the example shown in FIG. 12, the vibration damping device 21 is installed between the sheave mounting beam 60 and the car 16. By installing the damping device 21 at this position, the vibration that is generated when the rope 15 is wound up and cannot be absorbed by the cradle 61 is reduced by the damping force by the damping device 21. Can do.

  Next, the installation position of the vibration damping device 21 when the car 16 is lifted and lowered along the guide rail 18 in the hoistway 10 will be described. For example, as shown in FIG. 13, the guide rail 18 is fixed to the side wall 19 of the hoistway 10 using a rail bracket 70. The rail bracket 70 is formed of, for example, an L-shaped metal piece, and may be lower in strength than the support member 12 described above, for example. Therefore, when the car 16 moves up and down in the hoistway 10 along the guide rail 18, the vibration is transmitted to the side wall 19 through the rail bracket 70. When vibration is transmitted to the side wall 19, for example, it resonates on a wall of a residence and causes noise. Therefore, as shown in FIG. 13, the vibration transmitted to the side wall 19 of the building can be reduced by the damping force by installing the vibration damping device 21 on the rail bracket 70 that transmits the vibration from the guide rail 18 to the side wall 19. Can do.

  14 to 17 are modifications of the installation position of the vibration damping device 21 for canceling and reducing the vibration transmitted from the guide rail 18 to the side wall 19. FIG. 14 shows an example where the distance between the guide rail 18 and the side wall 19 is narrow. In this case, the rail bracket 70 is fixed to the guide rail 18 side by, for example, bolts and nuts, and the rail bracket 70 and the bracket 71 fixed to the side wall 19 are fixed, whereby the guide rail 18 is fixed. Is fixed to the side wall 19. In this case, unlike the case of FIG. 13, two rail brackets 70 are not combined and fixed, so that the vibration control device 21 installed on the rail bracket 70 also has a width that matches the distance between the guide rail 18 and the side wall 19. Narrow vibration damping device 21 is selected. The vibration damping device 21 may have any dimension in the thickness direction of the electromagnet as long as the required cross-sectional area of the electromagnet is ensured. That is, by increasing the vibration damping device 21 described in FIG. 2 in the left-right direction, the thickness in the depth direction (thickness direction) can be reduced accordingly.

  FIG. 15 shows an example in which the vibration control device 21 is directly fixed to the guide rail 18 instead of the rail bracket 70, and the guide rail 18 is fixed to the side wall 19 by connecting with the bracket 71 fixed to the side wall 19. Show. By using the vibration damping device 21 in this way, it is possible to better cancel and reduce the vibration from the guide rail 18 that is a vibration generation source and is a vibration control target. In addition, although the example which fixed the damping device 21 directly to the guide rail 18 was demonstrated in FIG. 15, it may be made to reduce the vibration which generate | occur | produced by fixing the damping device 21 directly to the side wall 19 with a damping force. good.

  FIG. 16 is a view as seen from the side wall 19 toward the guide rail 18, and FIG. 17 is a view of the rail bracket 70 and the vibration damping device 21 as seen from the direction of the arrow in FIG. 16. As described with reference to FIG. 14, when the space between the guide rail 18 and the side wall 19 is narrow, it is dealt with by installing the damping device 21 having a small width on the rail bracket 70. However, it is not necessary to install the vibration damping device 21 having a particularly narrow width by taking measures as shown in FIGS. 16 and 17 shown below.

  That is, as shown in FIG. 16, a plate-like arm 72 is fixed on the rail bracket 70, and the vibration damping device 21 is installed on the arm 72. Position where guide rail 18, rail bracket 70, bracket 71, and side wall 19 are connected in series when arm 72 is provided and damping device 21 is installed thereon to narrow the space between guide rail 18 and side wall 19. It is possible to avoid the installation of the vibration damping device 21 at the center, and it becomes unnecessary to prepare the vibration damping device 21 having a particularly narrow width. That is, as shown in FIG. 17, the thickness of the vibration damping device 21 can be absorbed by the thickness of the guide rail 18 by installing the vibration damping device 21 while shifting the position. Therefore, by fixing the arm 72 to the rail bracket 70 and installing the vibration damping device 21 thereon, the degree of freedom in designing the vibration damping device 21 itself is increased. Of course, the vibration transmitted to the rail bracket 70 is transmitted to the vibration sensor 20 (not shown) even when installed on the arm 72, so that the vibration transmitted to the side wall 19 of the building can be reduced by the damping force. .

  16 and 17 show an example in which the arm 72 is extended to one side of the rail bracket 70 and the vibration damping device 21 is installed thereon, but the rail bracket 70 is centered on the arms 72 on both sides thereof. Alternatively, the vibration control device 21 may be installed. Further, the frequency of vibration generated by adding a weight to the side opposite to the side where the vibration damping device 21 of the arm 72 is installed is controlled, and the vibration of the controlled frequency is controlled using the vibration damping device 21. It may be used for reduction.

  So far, an example has been described in which the vibration damping device 21 is installed in components such as a hitch portion, a sheave, and a rail bracket that constitute an elevator and generate vibration. In FIG. 1 described above, the vibration from the hoisting machine 11 is offset and reduced by installing the damping device 21 on the support member 12. However, the damping device 21 may be installed directly on the hoisting machine 11. Conceivable. 18 and 19 show an example in which the vibration damping device 21 is installed in different hoisting machines 80 and 90.

  First, FIG. 18 is a sectional view showing an example of the hoisting machine 80. The hoisting machine 80 is a thin hoisting machine that employs a permanent magnet type synchronous motor, for example, and the left side is the back side. In the hoisting machine 80, a stator 81 is provided in the center, a bearing 82 is provided so as to surround the stator 81, and a traction sheave 83 around which the rope 15 is wound is rotated outside the bearing 82. It is attached freely. The traction sheave 83 is provided with a rotor coil 84. The traction sheave 83 is rotated by the electromagnetic force generated between the rotor coil 84 and the stator coil 85, and the rope 15 is wound up. Will be. When the traction sheave 83 rotates, that is, when the hoisting machine 80 is driven, vibration is generated in the direction of the arrow shown in FIG. Therefore, the vibration generated from the hoisting machine 80 can be reduced by the damping force by installing the damping device 21 at the upper part, the lower part of the hoisting machine 80, or both as shown in FIG. Can do. 18 shows that the vibration damping device 21 is separated from the stator 81, but FIG. 18 is a sectional view, and the vibration damping device 21 is installed on the hoisting machine 80. ing.

  FIG. 19 is a perspective view showing an example of a hoisting machine different from the hoisting machine 80 described above. The hoisting machine 90 includes a motor 91 having a large rectangular parallelepiped shape and a traction sheave 92 connected to the motor 91. The hoisting machine 90 is installed on the support beam, and the traction sheave 92 winds the rope 15. The vibration generated when the rope 15 is wound up can be generated by, for example, a damping force by installing the damping device 21 on the motor 91 or on the side thereof (on the support beam on the same plane as the hoisting machine 90). Can be reduced.

  FIG. 20 is a simplified view of a hoistway in which two passenger cars (not shown) are installed next to each other when viewed from above. The rail bracket 70 for fixing the guide rail 18 for the car is provided on the surface where the two adjacent cars are opposed to each other. The building beam 101 provided on the elevator door side and the building beam 101 in the hoistway 10 are provided. Are joined together into a single beam 103 that connects the building beam 102 provided at a position opposite to.

  FIG. 21 is a perspective view showing the positional relationship between the building beam 101 and the beam 103 in a simplified manner. In FIG. 21, the building beam 102 is not shown. As described above, the rail bracket 70 is joined to the beam 103 by the two cars together. Furthermore, a vibration damping device 21 is provided on the beam 103 via an installation plate 104.

  Vibration generated when the car 16 moves up and down in the hoistway 10 is transmitted to the beam 103 via the guide rail 18 and the rail bracket 70. This vibration is further transmitted to the building via the building beams 101 and 102. In order to reduce this vibration more reliably, the vibration damping device 21 is installed on the beam 103 via the installation plate 104 as shown in FIG.

  Note that the vibration damping device 21 may be installed directly on the beam 103 (via the installation plate 104) in this way, but the vibration damping device 21 is attached to either the building beam 101, the building beam 102, or both. May be installed.

  FIG. 22 is a perspective view showing an outline of the overall configuration of a machine roomless type elevator according to another embodiment of the present invention. In FIG. 22, the hoisting machine 90 described above is used as the hoisting machine (see FIG. 19), and the car 16 is not shown.

  This elevator 110 is further provided with a deflecting sheave 111 for guiding the rope 15 extending from the main sheave (traction sheave) 14 of the rope 15 to the counterweight W side in addition to the above-described elevator configuration. The elevator 110 is a machine roomless elevator, and a hoisting machine is mounted on a pedestal 112 provided obliquely on a support member 12 assembled squarely in accordance with the shape of a hoistway 10 (not shown) for space saving. This is due to the installation of 90. In this case, one end of the rope 15 is stopped by the hitch Ha shown in FIG. Then, the lower sheave 17 (not shown in FIG. 22) of the car 16, the traction sheave 92, the deflecting sheave 111, the upper deflecting sheave 113, and the counterweight-side sheave 114 are wound in order, and the other end is stopped on the hitch Hb. It is done.

  The deflecting sheave 111 is fixed to the horizontal member 116 via a bracket 115. Further, the horizontal member 116 is combined with the first vertical member 117a and the second vertical member 117b through, for example, vibration-proof rubber 118 or the like. In FIG. 22, the second vertical member 117b is partially omitted in order to indicate the degree of engagement of the rope 15.

  The hoisting machine 90 lifts and lowers the car 16 to wind and release the rope 15, but the movement of the rope 15 causes vibration in the deflecting sheave 111. The horizontal member 116 on which the deflecting sheave 111 is provided, and the first and second vertical members 117 are used to prevent the vibration from being transmitted to the building using the anti-vibration rubber 118 or the like as described above. It is impossible to prevent the vibration from being transmitted.

  Therefore, it is possible to reduce the vibration generated by installing the vibration damping device 21 on the baffle sheave 111 that can be a vibration source with the damping force.

  As described above, according to the elevator according to the present invention, the amount of displacement of the weight in the direction orthogonal to the vibration damping direction is reduced, and the vibration that can be generated from each part of the elevator is efficiently and reliably suppressed. It is possible to provide an elevator including an elevator vibration control device installed in a place where it can be reduced by the above.

  As mentioned above, although embodiment which applied this invention was described, this invention is not limited with the description and drawing which make | form a part of indication of this invention by this embodiment. For example, in the present embodiment, the positions of the electromagnets 26a and 26b are fixed, but a movable mechanism may be provided in the electromagnets 26a and 26b so that the gap length between the weight 22 and the electromagnets 26a and 26b can be adjusted. . Further, in the present embodiment, the vibration damping device is provided in the elevator, but the present invention is not limited to this and can be applied to vehicles such as trains and automobiles. Of course, the vibration damping device 21 can be installed at a position where vibrations other than the above-described components in the elevator are generated. As described above, other embodiments, examples, operation techniques, and the like made by those skilled in the art based on the present embodiment are all included in the scope of the present invention. Furthermore, in the above description, an elevator in the case of the 2: 1 roping method as shown in FIG. 1 is described as an example. For example, in the case of the 1: 1 roping method, a damping device is installed at the same position. Needless to say, it has the effect of reducing the generated vibration by the damping force.

10: hoistway 11: hoisting machine 11a: rotating shaft 12: support member 13: cradle 14: main sheave (traction sheave)
15: Rope 16: Cars 17a, 17b: Car sheaves 18a, 18b: Guide rail 19: Side wall 20 of building: Vibration sensor 21: Damping device 22: Weight 23: Space 24: Casing 25: Recesses 26a, 26b: Electromagnets 27a and 27b: Elastic body 35: Square root calculator 40: Controller 41: A / D converter 42: High-pass filter 43: Integrator 44: Gain adjuster 45: Electromagnetic force distribution calculators 46, 47: D / A Converters 48 and 49: AMP
60: sheave mounting support 61: pedestal 62: upper beam 63: sheave 64: sheave support 65: connecting portion 70: rail bracket 71: bracket 72: arm 80: hoisting machine 81: stator 82: bearing 83: Traction sheave 84: Rotor coil 85: Stator coil 90: Hoisting machine 91: Motor 92: Traction sheave 101: Building beam 102: Building beam 103: Beam 104: Installation plate 110: Elevator 111: Baffle sheave 112: Receptacle 113: Upper deflecting sheave 114: Counterweight side sheave 115: Bracket 116: Horizontal member 117a: First vertical member 117b: Second vertical member 118: Anti-vibration rubber W: Counterweight

Claims (10)

A car that is guided by the car-side guide rail and goes up and down in the hoistway,
A hoisting machine that rotationally drives the traction sheave;
A counterweight which is guided by a counterweight guide rail and moves up and down in the hoistway;
A car sheave for suspending the car;
A winding rope wound around the traction sheave, one end of which suspends the car via the car sheave, and the other end of which suspends the counterweight;
A casing attached to the object to be damped; an elastic body that supports a weight having a magnetic body at least partially in the casing so as to be displaceable in a vibration damping direction; and an electromagnet disposed opposite to the weight in the casing. A damping force is applied to the damping object via the casing by moving the weight in the damping direction by the action of the electromagnetic force of the electromagnet on the magnetic body, and the damping direction of the elastic body An elevator damping device in which the spring constant is set to a magnitude less than the spring constant in the direction orthogonal to the damping direction;
An elevator characterized by comprising:   The elevator according to claim 1, wherein the elevator vibration control device is installed in the vicinity of a hitch portion that fixes the rope.   The elevator according to claim 1, wherein the elevator vibration control device is installed on the car sheave mounting support.   The elevator according to claim 1, wherein the elevator vibration control device is installed on a rail bracket that fixes a guide rail on which the car moves up and down.   The elevator according to claim 1, wherein the elevator vibration control device is installed on a wall surface of the hoistway.   The elevator according to claim 1, wherein the elevator vibration control device is directly installed on the hoisting machine.   The elevator according to claim 1, wherein the elevator vibration control device is installed on a beam that connects building beams to each other and fixes the rail bracket.   The rope has a deflecting sheave that guides the rope extending from the traction sheave to the counterweight side, and the elevator vibration control device is installed in the deflecting sheave. The elevator according to 1.   The elevator according to claim 1, wherein a member that regulates displacement in a direction orthogonal to the vibration damping direction is disposed on a side surface of the elastic body. Said damping direction of the spring constant k1 An elevator according to claim 1, wherein the suction force change rate α and a substantially same value F of the electromagnet, or is the attraction force F of the change rate α or more.

Images