JP3216376B2 - elevator - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device for an elevator car, and more particularly to an elevator equipped with a vibration damping device suitable for reducing the rolling and lateral vibration of a car.

[0002]

2. Description of the Related Art As elevators operate at higher speeds, a car undergoes bending when the guide rails are installed in a building or a roll or lateral vibration due to a step generated at a joint of the guide rails. Generally, the ride comfort of an elevator is better than other transportation means, but in a closed space of the elevator, this lateral vibration causes passengers to feel anxiety and discomfort, and this roll and lateral vibration are preferable. Not something.

[0003] Conventionally, as a vibration damping device for reducing the lateral vibration of an elevator car, a type in which the car is supported on a car frame by anti-vibration rubber to suppress the transverse vibration of the car is generally used. Widely used.

In addition to the above-mentioned vibration damping device, Japanese Patent Publication No. 52-26
As disclosed in Japanese Patent Publication No. 011, there is a type in which a ball is provided between a car frame and a car to enable the car to be displaced in the lateral direction on the car frame to suppress lateral vibration of the car. .

[0005]

In the above-mentioned prior art apparatus in which the car is supported on the car frame by the vibration isolating rubber to suppress the lateral vibration of the car, the spring constant of the vibration isolating rubber is as low as possible. Although it is set, the value is limited because the anti-vibration rubber also supports the car in the vertical direction, and eventually the spring constant of the anti-vibration rubber is not enough to significantly improve the lateral vibration of the car. Can't lower. For this reason,
If the accuracy of the guide rail is poor, there is a problem that the riding comfort is not good.

[0006] Further, in a device in which a ball is provided between a car frame and a car and the car is supported on the car frame so as to be able to be displaced in the lateral direction, the lateral vibration of the car is suppressed. The spring constant of the restoring means for returning the vehicle to the neutral position in the lateral direction can be set considerably low, so that the accuracy of the guide rails is poor, and even if the car frame vibrates laterally, the car is not affected so much that a good ride comfort can be maintained. Has advantages.

However, in recent years, the speed of the elevator has been further increased, and accordingly, the riding comfort performance has been further demanded. However, a ball is provided between the car frame and the car described above. Then, a new vibration is generated by the rolling of the ball due to the lateral vibration of the car, and there is a problem that the riding comfort performance cannot be further improved.

[0008]

Means for Solving the Problems To solve the above problems,
For example, the present invention provides a car
Up and down along the hoistway guide rails
A car and a car in an elevator that movably guides
Between the frame and the car vertically upward with respect to the car frame
An elastic member that supports the car
Supports relative movement with respect to the frame and has elastic members
Lifts the car vertically upwards relative to the car frame
That the pulling force acts by supporting
And a control member.

At this time, the regulating member is located below the car.
It is preferable to provide a plurality of these so as to be parallel.

At this time, the regulating member is located at the lower part of the car.
It is good to be provided in the corner.

[0011] Further , the regulating member is provided so that the car can move with respect to the car frame.
Is set to be vertical at the top position
Good.

[0012]

[Operation] When the car frame descends, the drop force acting on the car is generated by gravity, and furthermore, is the combined force of gravity and the reaction force of the regulating member. When the falling force goes out of the equilibrium point, the displacement in the vertical and horizontal directions increases in the vertical and horizontal directions, but the displacement due to the roll and lateral vibration of the car is very small at several mm. The drop force will be relatively small. The elastic member installed between the car frame and the car applies a restoring force to the car in the horizontal direction so that the car can always be located at the upper portion by overcoming the drop force. With this restoring force, the stability of the car can be maintained.

As described above, according to the present invention, the lateral spring constant of the car can be reduced, whereby the lateral natural frequency of the car can be lowered to suppress the roll, and the ride comfort can be reduced. Good elevator can be provided.

[0014]

Embodiments of the present invention will be described below with reference to the drawings.

1 and 2 show an embodiment of the present invention. FIG. 1 is a front view showing an embodiment of the elevator according to the present invention, and FIG. 2 is a side view thereof. In these figures, a main rope wire rope 3 is connected to a car frame 5 via a spring 4. The car frame 5 is guided vertically by a guide rail 6 and four sets of guide rollers 7. The guide roller 7 includes left and right rollers 8 for guiding the car frame 5 in the left and right directions, two front and rear rollers 9 for guiding the front and rear directions, an arm 10 and a spring 11 for supporting these rollers, and a guide for fixing the arm 10 and the spring 11. The guide 12 is attached to the car frame 5.

The regulating member 2 includes a car 14 shown by a white circle.
A first fulcrum 21 that is rotatable in the opposite direction, and a second fulcrum 22 that is rotatable below the first fulcrum 21 and located in the car frame 5 facing the first fulcrum 21 at both ends. And the distance between the first fulcrum 21 and the second fulcrum 22 is regulated to be always constant.

These restricting members 2 are arranged on the four sides below the car 14 and support the car 14 so as to be able to move relative to the car frame 5. Car 1
4. The regulating member 2, the car frame 5, and the other regulating members 2 constitute a link. That is, a line segment connecting the rotatable first fulcrum 21 provided on the car 114 and the other first fulcrum 21, the other first fulcrum 21 and the other second fulcrum 22
The other connecting member, a line segment connecting the other rotatable second fulcrum 22 provided on the car frame 5 and the second fulcrum 22,
And the regulating member 2 connecting the second fulcrum 22 and the first fulcrum 21 constitutes a link of at least four nodes.

In this embodiment, the elastic member 20 is provided with the regulating member 2.
Is installed between the car frame 5 and the car 14 by a number corresponding to each of them so as to directly apply a vertical force for lifting the car 14 to the upper part,
The operation of the link of the regulating member 2 generates a horizontal force that restores the car 14 to a mechanically stable position with respect to the car frame 5.

The door 15 of the car 14 is guided by a support 18 having rollers 17. The rollers 17 are guided by rails 19 attached to the car frame 5 and sills (not shown) provided on the floor of the car 14. The door 15 is generally driven by a motor (not shown) attached to the car frame 5.

The operation of the above-described configuration will be briefly described below.

The car 14 is pushed upward by the force of the elastic member 20. The push-up force of the elastic member 20 is a value that allows the car 14 to be pushed upward by a force greater than the rated value, not to mention when no one is in the elevator car, even when the load capacity is at the rated value. Is set to

Here, when the car 14 vibrates due to the bending of the guide rail and is displaced in the lateral direction relative to the car frame 5, the regulating member 2 rotates and the regulating member 2 is rotated.
Is narrowed in the vertical direction between the car 14 and the car frame 5 where the car is installed. Therefore, an upward force is generated in the elastic member 20 to return the car 14 to the initial position against the gravity, and the car 14 returns to the initial position.

The overall lateral spring constant of the car is:
Considering the non-linearity of the link mechanism, the spring constant of the elastic member is obtained by subtracting the spring constant of the elastic member which is laterally replaced by the link mechanism of the drop force generated by gravity.
This lateral spring constant can be set relatively freely, without any other constraints, and can be low or high. Therefore, the lateral natural frequency of the car is set to be lower than the frequency of about 2 Hz which is strongly vibrated from the guide rail by setting the lateral spring constant to be low, and the vibration level of the car at about 2 Hz is lowered. In this way, the ride comfort of the elevator can be significantly improved.

An embodiment of the present invention will be described with reference to FIGS. FIG. 3 is a front view showing a main part of a specific embodiment of the present invention in FIG. 1 and FIG.

The pinball 210 is fixed to the bottom of the car 14, and the first fulcrum 21 is
To form The anti-vibration rubber 131 is stacked on the mounting stand 24 and the bracket 23 in a laminated manner, and has a structure that insulates the vertical vibration of the car 14 from the car frame 5. The pinball 220 is directly attached to the mounting base 24, is fixed to the car frame 5 by the bolt 31 via the mounting base 24, the vibration-proof rubber 131, and the bracket 23, and is rotatable on the car frame 5. A second fulcrum 22 is formed. The regulating member 2 is configured to have a first fulcrum 21 and a second fulcrum 22 at both ends through a hole provided at the center of the mounting stand 24, the vibration isolating rubber 131, and the bracket 23. Sliding bearings 211 and 221 are arranged at locations corresponding to the pin 210 and the pinball 220, respectively.

The first fulcrum 21 and the second fulcrum 22 facing the first fulcrum 21 are positioned so that their positions match when viewed from above, and the plurality of regulating members 2 are parallel to each other, and It is set to be vertical when the car 14 is located at the top.

At both ends of the elastic member 20, there are cradles 209 which are fixed to the car 14 and the car frame 5, respectively, and push the car upward by the force of the elastic member 20. The push-up force of the elastic member 20 is not limited to the case where no one is riding on the elevator car, and even when the loading capacity reaches the rated value, the car 1
The value is set so that 4 can be pushed upward.
Therefore, a tensile force acts on the regulating member 2 and a compressive force acts on the vibration-proof rubber 131.

Next, the basic principle and operation of the above-described embodiment of the present invention will be described with reference to FIGS.

FIGS. 4 and 5 are front views of the drawings for schematically explaining the mechanical relationship between the car 14 and the car frame 5. FIG. In these figures, white circles having black circles therein indicate the first and second fulcrums 21 and 22 which are rotatable. In FIG. 4, it is assumed that the car 14 and the regulating member 5 indicated by solid lines are located at the uppermost position by the action of the elastic member 20 and are at a stable equilibrium point. From this state, it is assumed that a force acts in the lateral direction for some reason, and the car 14 and the regulating member 5 are displaced relative to the car frame 5 at a position indicated by a broken line. By the action of the regulating members 2 arranged in parallel, the car 14
, The component that moves in parallel and in the horizontal direction is the main component of the motion.

At this time, the car 14 is also displaced by a small amount in the vertical direction by the action of the regulating member 2. This vertical displacement amount is δ, the rotation angle of the regulating member 2 from the equilibrium point position is θ,
Let K be the spring constant of the elastic member 20. Here, a change in force from the equilibrium state will be considered. The vertical force Fs of the elastic member 20 is as shown in Expression 1.

[0031]

(Equation 1)

The normal force Fs becomes K · δ, and can be considered as a vector sum of two orthogonal forces Fm and Fd as shown in Expression 2.

[0033]

(Equation 2)

The force Fm is a force for extending the regulating member 2, and has no relation to the movement. The force Fd is a restoring force for rotating the regulating member 2 to return the regulating member 2 and the car 14 to the equilibrium point, and is related to the movement of the car 14. The restoring force Fd is shown by Expression 3.

[0035]

(Equation 3)

As shown in FIG. 5 and Equation 4, the restoring force Fd
Are two orthogonal forces, a lateral component Fx and a vertical component Fy
And the lateral component Fx
Can be expressed by Equation 5.

[0037]

(Equation 4)

[0038]

(Equation 5)

From equations (1) and (3), Fs and Fd are eliminated, and the lateral component Fx is rearranged using the relationship of trigonometric functions, as shown in equation (6).

[0040]

(Equation 6)

Assuming that the length of the regulating member is L, the vertical displacement δ can be expressed as shown in Expression 7, and from this relationship, Expression 6
The lateral component Fx shown in FIG.

[0042]

(Equation 7)

[0043]

(Equation 8)

The amplitude of the lateral vibration of the elevator car 14 relative to the car frame 5 is at most about several mm, and if the approximation that the rotation angle θ is small is obtained, the lateral displacement Equation 9 and Equation 10 for x and rotation angle θ
From this relationship, Equation 8 can be further expressed as Equation 11.

[0045]

(Equation 9)

[0046]

(Equation 10)

[0047]

[Equation 11]

That is, the force for restoring in the lateral direction and the lateral component force Fx are obtained by setting the spring constant of the elastic member 20 to K and the lateral displacement x to (1).
−cos θ) and Kx represented by Expression 12.

[0049]

(Equation 12)

The above (1-cos θ) is always a positive value, and is very small in the range where the rotation angle θ is small. That is, in the range where the rotation angle θ is small, the spring constant for restoring in the horizontal direction becomes very small. As a result, the natural frequency of the car in the vibration mode that moves in the lateral direction in parallel can be made very low.

For example, the spring constant K is 8 MN / m, the length L of the regulating member is 0.1 m, and the lateral displacement x at that time is 0.00.
If 5 m, θ = 2.87 (°), and cos θ =
0.9987, (1−cos θ) = 0.00125, and the lateral spring constant Kx is 10.0 kN / m.
Assuming that the mass M of the car is 1000 kg, the natural frequency at this time can be made extremely low as 0.50 Hz from Expression 13.

[0052]

(Equation 13)

As described above, since the natural frequency in the lateral direction of the car can be set lower than the frequency of about 2 Hz which is strongly vibrated from the guide rail, the vibration level of the car at about 2 Hz can be suppressed to be low. The ride comfort can be significantly improved.

Further, in the embodiment of the present invention, the vertical vibration of the car is insulated by the vibration-proof rubber, so that it can be compatible with the horizontal vibration isolation.

According to the embodiment of the present invention, the first fulcrum that is rotatable on the car is provided on the car frame below the first fulcrum and rotatably facing the first fulcrum. A second fulcrum is provided, and a regulating member connecting the first fulcrum and the second fulcrum is provided to support the car. Therefore, even if the length of the regulating member is short, its natural frequency can be made very low as compared with the conventional one, whereby the lateral natural frequency of the car can be lowered to suppress the roll, and the elevator having a good ride comfort. Can be provided. Further, since the short restricting member is installed at the lower part of the car, it is possible to reduce the size without taking up space.

FIG. 6 shows another embodiment of the present invention. This embodiment is a partial modification of the embodiment shown in FIG. 3, and shows a main part in a front view. In FIG. 6, the pinball 210 is fixed to the bottom of the car 14 and forms a first fulcrum 21 that is rotatable on the car 14.

The anti-vibration rubber 131 is superposed on the mounting stand 24 and the leaf spring 25 in a laminated manner, and has a structure for insulating the vertical vibration of the car 14 from the car frame 5. The two facing leaf springs 25 are bent into a U-shape, and both ends thereof are fixed to the vibration isolating rubber 131 and the bracket 23, respectively, to load passengers and luggage of the car 14. It can be displaced up and down according to the amount. The pinball 220 is directly attached to the mounting stand 24, and the bolt 3 is attached to the car frame 5 via the mounting stand 24, the vibration-proof rubber 131, the leaf spring 25, and the bracket 23.
1 and forms a second fulcrum 22 which is rotatable on the car frame 5.

The restricting member 2 includes a mounting table 24, an anti-vibration rubber 1
31, a first ball 21 and a second ball 22 are provided at both ends through a hole provided in the center of the bracket 23 and between the two leaf springs 25,
10, sliding bearings 211 and 212 are arranged at locations corresponding to the pinballs 220, respectively. First fulcrum 2
1 and the second fulcrum 22 facing it are positioned so that their positions match when viewed from above, and the plurality of regulating members 2 are parallel to each other, and the car 14 is positioned at the uppermost position. When you are set to be vertical.

At both ends of the elastic member 20, there are cradles 209 which are fixed to the car 14 and the car frame 5, respectively, and push the car upward by the force of the elastic member 20. The push-up force of the elastic member 20 is not limited to the case where no one is riding on the elevator car, and even when the loading capacity reaches the rated value, the car 1
The value is set so that 4 can be pushed upward.
Therefore, a tensile force acts on the regulating member 2 and a compressive force acts on the vibration-proof rubber 131.

The operation and effect of this embodiment are the same as those of the embodiment shown in FIG. 3, except that the lateral natural frequency of the car is set lower than the frequency of about 2 Hz which is strongly vibrated by the guide rail. The vibration level around 2Hz
In addition to significantly improving the ride comfort of the elevator, FIG.
As compared with the embodiment, the second fulcrum is provided on the car frame 5 via the leaf spring 25, so that the car 14
The car 14 is vertically displaced in accordance with the number of passengers and luggage loaded. For this reason, according to the present embodiment, the presence / absence of a passenger mounted on the car and the weight can be easily obtained by measuring the amount of deformation of the leaf spring, thereby enabling the operation of a plurality of elevators. It has the feature that information to control efficiently can be obtained.

FIG. 7 shows still another embodiment of the present invention. In this embodiment, an elastic member 20 is installed in a horizontal direction, and a restoring force is generated directly in the horizontal direction. It was done. In FIG. 7, the pinball 2
10 is fixed to the bottom of the car 14 and
A first fulcrum 21 which can rotate freely is formed.

The anti-vibration rubber 131 is superposed on the mounting stand 24 and the bracket 23 in a laminated manner, and has a structure for insulating the vertical vibration of the car 14 from the car frame 5.

The pinball 220 is directly mounted on the mounting table 2.
4, the mounting stand 24, the vibration isolating rubber 13
1. A second fulcrum 22 which is fixed to the car frame 5 by bolts 31 via the bracket 23 and is rotatable is formed on the car frame 5.

The regulating member 2 has a first fulcrum 21 and a second fulcrum 22 at both ends, and sliding bearings 211 and 212 are provided at positions corresponding to the pinball 210 and the pinball 220, respectively. Are located.

The first fulcrum 21 is disposed at four places at the bottom of the car 14, and the second fulcrum 22 facing the first fulcrum 22.
Are positioned so that their positions match when viewed from above, and the plurality of regulating members 2 are set so as to be parallel to each other and to be vertical when the car 14 is located at the uppermost position. ing.

The elastic member 20 is a coil spring made of steel, and is fixed to the bottom of the car 14 and has a support 501 having a projection 501 in the direction of the facing car frame 5 and a support 5.
0, the protruding portion 5 of the support tool 52 having the protruding portion 511 in the direction of the facing car 14 fixed to the facing car frame 5
It is provided horizontally between 10 and 511. The protrusions 510 and 511 are fixed by bolts 31 at a distance such that a compressive force always acts on the elastic member 20, and the horizontal position of the elastic member 20 acting on the car 14 when the car 14 is located at the uppermost position. The directional forces are set to balance.

In this embodiment, a compressive force acts on the regulating member 2 by gravity. The anti-vibration rubber 131 is disposed below the second fulcrum so that a compressive force acts thereon, and the car 1
4 to absorb the vertical vibration.

Next, the basic principle and operation of the embodiment of the present invention will be described with reference to FIGS. FIG. 8 is a schematic diagram for explaining the dynamics of FIG. 7 and is a front view. In the figure, only one elastic member 20 is shown. Although two regulating members 2 are shown in the figure, the following mechanical considerations will be made for one regulating member 2 and one elastic member 20.
Let's think of it as having all power concentrated in it.

In FIG. 8, the car 14 shown by a solid line
And the regulating member 5 are positioned at the uppermost position by the action of the elastic member 20 and show a state when the member is at a stable equilibrium point. From this state, it is assumed that the position of the car has moved as shown by a broken line due to disturbance outside the car such as bending of the rail. The movement of the car 14 mainly includes a component that moves in the lateral direction parallel to the car frame by the action of the regulating member 2 arranged in parallel, and this horizontal displacement is x.

The dynamics at this time will be described below.
The force acting on the first fulcrum 21 is the mass M of the car 14
Force M acting vertically downward with gravitational acceleration G applied to
The spring force Fs acting horizontally with G. Spring force F
s is obtained by multiplying the spring constant K by the displacement x as shown in Expression 14, and can be expressed as a function of θ.

[0071]

[Equation 14]

Considering the moment of the two falling forces MG and the spring force Fs about the second fulcrum 22, the condition under which the car 14 returns to the equilibrium point can be clarified. In order for the car to return to the equilibrium point, the moment due to the spring force Fs needs to overcome the moment due to the drop force MG.
The inequality of 5 needs to hold.

[0073]

(Equation 15)

By rearranging Equation 15 with respect to the spring constant K from the relation of Equation 14, the inequality equation of Equation 16 is obtained.

[0075]

(Equation 16)

That is, if the spring constant K of the elastic member 20 is set so as to satisfy the inequality expression (16), the car can overcome the gravity and be kept at a stable position.
The right side of Equation 16 is the lateral spring constant K of the elastic member 20, and the left side is the lateral spring constant generated in the regulating member 2 by gravity. These will be referred to as equivalent spring constants.

FIG. 9 shows an example in which the equivalent spring constants on the right and left sides of Equation 16 are calculated. The horizontal axis indicates the swing angle of the regulating member 2, and the vertical axis indicates the equivalent spring constant of the right side or the left side of Expression 16. The spring constant K in the lateral direction of the elastic member 20 is constant as shown by the broken line in the figure, but the regulating member 2 generated by the gravity on the right side of Formula 16
The spring constant in the horizontal direction changes when θ is 0 as a minimum value. In this example, the value of the lateral spring constant of the regulating member 2 generated by the gravity when θ is around 30 ° exceeds the lateral spring constant K of the elastic member 20. If θ becomes 30 ° or more, the car 14 falls to the lower part, and the stability cannot be maintained.

Therefore, in the present calculation example, it is necessary to set a movable range of θ from + 24 ° to −24 ° in which Expression 16 holds, and to provide a stopper at the boundary of the range. In this way, the stability of the car is maintained.

In the range where θ is small, it can be considered that cos θ = 1, and the spring constant Kx of the resultant force acting on the car is expressed by the following equation.
From Equation 6, Equation 17 is obtained.

[0080]

[Equation 17]

For example, the spring constant K is 38 kN / m, the length L of the regulating member is 0.3 m, and the mass M of the car is 1000
Assuming that kg and the gravitational acceleration are 9.8 m / s ² , the lateral spring constant Kx is 5.33 kN / m from Equation 17. At this time, the natural frequency can be made as very low as 0.37 Hz from Expression 13. For this reason, even when the rail is bent, the vibration at or above this frequency is hardly caused by the car frame 5.
Is not transmitted to the car 14 and the ride quality is very good.

Next, an embodiment of the present invention in which the elastic member 20 which is installed in the horizontal direction and generates a restoring force in the horizontal direction is made of rubber will be described with reference to FIG.

In this embodiment, two elastic members 20 are made of rubber as compared with the embodiment of FIG. Therefore, when the car 14 is displaced relative to the car frame 5, a compressive force or a tensile force acts on the elastic member 20, and the car 14 and the car frame 5 are stably moved by the restoring force of the rubber. It is to return to.

In this embodiment, since the elastic member 20 is made of rubber, the amplitude of the vibration is not increased even at the natural frequency due to the damping action of the rubber, and the riding comfort is improved as compared with the metal spring alone. is there.

In the above embodiment, the first rotatable fulcrum and the second rotatable fulcrum provided on the car frame below the first fulcrum have been described as examples of the pinball joint. It is not always necessary to stick to this, and there are various methods, which will be described sequentially.

FIG. 11 shows another example of the first rotatable fulcrum constituting the present invention. In this example, both ends of the shaft 250 are fixed to the bottom of the car 14. ing. The ball joint 251 is connected to the shaft 2
50 penetrated by. The sliding bearing 211 is fixed to an end of the regulating member 2. Thus, the rotatable first fulcrum 21 is formed. This configuration can likewise be used for the second fulcrum.

According to the present embodiment, since both ends of the shaft are supported, the shaft has high strength and high reliability.

FIG. 12 shows still another example of the first rotatable fulcrum constituting the present invention. In this example, a universal joint is used at the bottom of the car 14. I have. Shaft 260, shaft 261
Are arranged orthogonally, and the supports 262 and 263 are
The shaft 260 and the shaft 261 are configured to be rotatable. Supporting tools 262, 26
Numerals 3 are fixed to the bottom of the car 14 and the end of the regulating member 2, respectively. The first fulcrum 2 which is rotatable as described above
1. This configuration can likewise be used for the second fulcrum.

According to the present embodiment, since both ends of the shaft are supported, the shaft has high strength and high reliability.

FIG. 13 shows another example of the first rotatable fulcrum constituting the present invention. In this example, both ends of the shaft 250 are fixed to the bottom of the car 14. ing. A hole penetrates an end of the regulating member 2, and its cross-sectional shape is a convex shape at the center, and the first fulcrum 21 is rotatable with a shaft 250 inserted into the hole.
Is composed. This configuration can likewise be used for the second fulcrum.

According to this embodiment, since both ends of the shaft are supported, the shaft is strong and the structure is simple.

FIG. 14 shows still another example of the first rotatable fulcrum that constitutes the present invention. In this example, the shaft 250 has both ends fixed to the bottom of the car 14. And its cross-sectional shape is convex at the center. A hole penetrates an end of the regulating member 2, and the first member is rotatable with a shaft 250 inserted into the hole.
Of the fulcrum 21 are formed. This configuration can likewise be used for the second fulcrum. According to the present embodiment, since both ends of the shaft are supported, the shaft is strong and has a simple structure.

FIG. 15 shows another embodiment of the present invention. In FIG. 15, a first eyebolt 60 is installed on the lower side surface of the car 14 and a second eyebolt 61 is It is installed on the car frame 5 at a position facing one eyebolt 60. The wire rope 63 is connected so as to connect the first eyebolt 60 and the second eyebolt 61. The first eyebolt 60 and the second eyebolt 56 are composed of the first eyebolt 60 and the wire rope 63.
Are arranged on all sides of the car 14.

At both ends of the elastic member 20, there are cradles 209 which are fixed to the car 14 and the car frame 5, respectively, and push the car upward by the force of the elastic member 20. The push-up force of the elastic member 20 is not limited to the case where no one is riding on the elevator car, and even when the loading capacity reaches the rated value, the car 1
The value is set so that 4 can be pushed upward.
For this reason, a pulling force acts on the wire rope 63.

When the position of the car moves due to disturbances outside the car such as bending of the rails, the movement of the car 14 is controlled by the action of the wire ropes 63 arranged in parallel so that the car is moved in the lateral direction parallel to the car frame. The component that moves to the main is the main component. That is, the wire rope 63 operates as the regulating member 2, and the present embodiment can also improve the riding comfort of the elevator.

According to this embodiment, the structure is simple because the regulating member is a wire rope, and the maintenance and inspection are facilitated.

FIGS. 16 and 17 show still another embodiment of the present invention.
0, the upper end is fixed to the bottom of the car 14 by the mounting brackets 271 and 272 and the mounting bolt 273,
Its lower end is fixed to the car frame 5 by mounting brackets 274 and 275 and mounting bolts 276.

At both ends of the elastic member 20, there are cradles 209 fixed to the car 14 and the car frame 5, respectively, and push the car 14 upward by the force of the elastic member 20. The lifting force of the elastic member 20 is, of course, when no one is on the elevator car 14,
The value is set so that the car 14 can be pushed upward by a force greater than the rated value even when the installed amount reaches the rated value. Therefore, a tensile force acts on the leaf spring 270.

The mounting brackets 271 are arranged at four places on the bottom of the car 14 and the mounting brackets 2 facing the mounting brackets 271.
74 are positioned so that their positions match when viewed from above, and the plurality of leaf springs 270 are set so as to be parallel to each other and to be vertical when the car 14 is located at the top. Have been.

FIG. 16 shows that the car 14 and the leaf spring 270
It is located at the uppermost position by the action of the elastic member 20 and shows a state when it is at a stable equilibrium point. FIG.
16 shows a state where the position of the car has moved as shown by a broken line due to disturbance outside the car such as bending of the rail from the state of FIG. The movement of the car 14 mainly includes a component that moves in the lateral direction parallel to the car frame by the action of the leaf spring 270 arranged in parallel.

In this embodiment, the first fulcrum 21 which is rotatable is provided.
At first glance, the rotatable second fulcrum 22 does not appear to exist. However, the leaf spring 270 allows the movement of the car 14 and the car frame 5 to move in the lateral direction in parallel with the car frame, functions as the regulating member 2, and includes the mounting brackets 271 and 272. A substantially pivotable first fulcrum 21 is provided at the boundary A between the fittings 271 and 272 that are free from restraint, and the boundary B between the fittings 274 and 275 that is free from restraint by the mounting fittings 274 and 275.
The portion has a substantially pivotable second fulcrum 22.
Therefore, the leaf spring 270 is configured to have the first fulcrum 21 and the second fulcrum 22 at both ends as the regulating member 2, and it is possible to provide an elevator with excellent ride comfort as in the embodiments described above. Has features.

Further, as a feature of this embodiment, since the first fulcrum 21 and the second fulcrum 22 utilize the flexibility of the elastic body, the elevator has a smooth ride comfort without play or play at the fulcrum portion. Can be provided.

FIGS. 18 and 19 show another embodiment of the present invention. FIG. 18 shows a main part of the present invention in a front view, and FIG. 19 shows a partial structure of FIG. FIG. In these figures, the bottom of the car 14
It has a concave recess and forms a first fulcrum 21. The cylindrical support 218 has a concave recess at the bottom thereof, and forms the second fulcrum 22. The regulating member 2 is composed of a shaft portion 28 whose both ends are processed into a hemispherical shape, and a disk portion 29 which is fixedly formed to the shaft portion 28 at the center, and both ends of the shaft portion 28 are The first and second fulcrums are engaged with each other to form a pivotable fulcrum.

At the upper and lower portions of the shaft portion 28 which is vertically divided by the disk portion 29, a column-shaped anti-vibration rubber block 131 having a hole at the center is inserted, and is inserted into the cylindrical support 218. , Press fit. Cylindrical support 2
18 is fixed to the car frame 5 by bolts 31.

A combined structure of the cylindrical support 218 having the first fulcrum 21 and the second fulcrum 22, the regulating member 2, and the block 131 of the vibration isolating rubber is arranged on all sides of the car 14. .

FIG. 18 shows a state where the car 14 and the regulating member 5 are located at the uppermost position and are at a stable equilibrium point. From this state, the position of the car moves due to disturbance outside the car such as bending of the rail. The movement of the car 14 mainly includes a component that moves in the lateral direction parallel to the car frame 5 by the action of the regulating member 2 arranged in parallel. At this time, the regulating member 2 is inclined with respect to the car 14 and the car frame 5, so that the disc portion 29 of the regulating member 2 moves the cylindrical anti-vibration rubber block 131 inside the cylindrical support 218. Press. Since the block 131 of the vibration isolating rubber is in a state of being confined inside the cylindrical support 218, a reaction force is generated to return the regulating member to the initial position. As described above, in this embodiment, the block 131 of the vibration-proof rubber operates as the elastic member 20.

According to the present embodiment, the characteristic of rubber is used as the elastic member 20, so that the vibration at the natural frequency is greatly attenuated, and the riding comfort is smooth.

FIG. 20 shows still another embodiment of the present invention. In this FIG.
It has a concave recess and forms a first fulcrum 21. The regulating member 2 is composed of a shaft portion 28 having an upper end portion processed into a hemispherical shape, and a disk portion 29 fixedly formed to the shaft portion 28 at the center. The upper end portion of the shaft portion 28 is The first fulcrum engages with the first fulcrum to form a rotatable fulcrum.

At the lower portion of the shaft portion 28, which is vertically divided by the disk portion 29, a columnar vibration-proof rubber block 131 having a hole at the center similar to that described with reference to FIG. Inner surface of the support 218 and the disk portion 29
Pressed in between. At this time, the lower end of the shaft 28 has not reached the bottom of the inner surface of the support 218. The cylindrical support 218 is fixed to the car frame 5 by bolts 31.

The first fulcrum 21, the cylindrical support 218,
The structure in which the regulating member 2 and the vibration-proof rubber block 131 are combined is disposed on all sides of the car 14.

FIG. 20 shows a state in which the car 14 and the regulating member 5 are at the uppermost position and are at a stable equilibrium point. At this time, the car 14
Presses the anti-vibration rubber block 131 in the direction indicated by the arrow C via the disc portion 29 of the regulating member 2, and the anti-vibration rubber block 131 is relatively uniformly compressed in the vertical direction. It is in. In this state, inertia acts on the car frame and the car so that the relative position between the car frame and the car moves due to disturbance outside the car such as bending of the rail. Arrow D in the figure
The inertial force indicated by the symbol acts on the vibration-proof rubber block 131 as a moment multiplied by the appropriate length of the shaft 28 of the regulating member 2 with the first fulcrum 21 as the point of action.
The vibration-proof rubber block 131 was compressed relatively uniformly in the vertical direction. However, the compression amount changes according to the moment due to the inertial force, and the disk portion 29 is inclined as shown by a broken line in the figure. Accordingly, the regulating member 2 is also inclined, and the car 14 can move in the lateral direction with respect to the car frame 5 by the action of the regulating member 2 arranged in parallel.

In the present embodiment, the rotatable second fulcrum 22
Seem to be absent at first glance. However, by utilizing the flexibility of the vibration isolating rubber as an elastic body, a second fulcrum substantially rotatable near the boundary of the disc portion 29 of the regulating member 2 at the center of the block 131 of the vibration isolating rubber. 22.
Therefore, the regulating member 2 is configured to have the first fulcrum 21 and the second fulcrum 22 at both ends.

When the regulating member 2 is inclined and the car 14 moves in the lateral direction, the moment generated by the inertia force is balanced, but a reaction force is generated in the vibration-proof rubber block 131. After the moment due to the inertial force disappears, the above-described reaction force moves the car 14 to a stable equilibrium point located at the top. That is, the block 131 made of the vibration-proof rubber is used as the elastic member 2 for returning the regulating member to the initial position.
It also has the function of zero. Therefore, similarly to the embodiments described so far, the present invention has a feature that an elevator having a particularly excellent ride quality can be provided.

Further, as a feature of this embodiment, since the second fulcrum 22 utilizes the flexibility of the elastic body, it is possible to provide an elevator having a smooth ride comfort without play or play at the fulcrum. Further, the vibration-proof rubber block 131 is a car 1
4 can absorb the vertical vibration of the car 14 without restraining the vertical movement of the car 4, and furthermore, because the elastic member 20 uses the characteristics of rubber, the vibration at the natural frequency greatly attenuates, It has the characteristics of a smooth ride.

FIG. 21 shows another embodiment of the present invention. In this figure, an anti-vibration rubber unit 135 is one in which an anti-vibration rubber 132 is fixed between two plates 133 in a laminated manner. is there. The regulating member 2 is provided with mounting portions 28 at both ends.
1 and a structure in which the shaft portion 28 is connected therebetween. The first anti-vibration rubber unit 135 is fixed to the bottom of the car 14 by bolts via a plate 133, and the second anti-vibration rubber unit 135 faces the first anti-vibration rubber unit 135. Anti-vibration rubber unit 13
The lower part 5 is similarly fixed to the car frame 5 by bolts via the plate 133. The regulating member 2 is a plate 1
It is connected to the first and second anti-vibration rubber units 135 via bolts 33 and mounting portions 281 by bolts. Each of the first and second anti-vibration rubber units 135 insulates the vertical vibration of the car 14 and the car frame 5, and uses the flexibility of the elastic body to rotate freely at the first fulcrum. And constitute the second fulcrum.

Therefore, the regulating member 2 is connected to the first fulcrum 2
It is configured to have a first and a second fulcrum 22 at both ends. Further, the vibration isolating rubber unit 135 has a structure that also functions as the elastic member 20 that returns the regulating member 2 to the initial position by using the elastic action. The structure combining the regulating member 2 and the first and second vibration-isolating rubber units 135 is as follows.
They are arranged on all sides of the car 14.

The car 14 shown in FIG. 21 is located at the top and shows a state where the car is at a stable equilibrium point. At this time, the car 14 is pressing the vibration isolating rubber unit 135 by gravity, and the vibration isolating rubber 132 is relatively uniformly compressed in the vertical direction. In this state, inertia force acts on the car frame and the car so that the relative position between the car frame and the car moves due to disturbance outside the car such as bending of the rail, and the car 14 is provided with a regulating member arranged in parallel. 2 allows the car to move laterally relative to the car frame 5. After the moment due to the inertial force disappears, the car 14 moves to a stable equilibrium point located at the uppermost position by the elastic action of the vibration isolating rubber 132.

Therefore, the present embodiment also has a feature that an elevator having an exceptionally comfortable ride can be provided, similarly to the above-described embodiments. Further, as a feature of this embodiment, since the first and second fulcrums 21 and 22 utilize the flexibility of the elastic body, it is possible to provide an elevator with a smooth ride without play or play at the fulcrum. Further, the anti-vibration rubber 132 does not restrain the vertical movement of the car 14 and can absorb the vibration of the car 14 in the vertical direction. Further, since the rubber member is used as the elastic member 20, the natural vibration is reduced. It has the characteristic that the vibration is greatly attenuated by the number, and the ride quality is smooth.

FIG. 22 shows still another embodiment of the present invention. In this drawing, a plate 140 has a hole in the center and is fixed to the bottom of the car 14 by bolts 31. The upper and lower ends of the regulating member 2 are formed in a columnar shape having a cross-section formed into an arc and having a hollow portion in the longitudinal direction, and the upper end thereof is connected to the car 14 and the first fulcrum 21 via a plate 140. And the lower end thereof forms a car frame 5 and a second fulcrum 22. The rod 201 is mounted through the hole provided in the car frame 5, the hollow part of the regulating member 2, and the center hole of the plate 140, and is mounted between the car frame 5 and the lower end formed in a disc shape. The rubber 139 has an elastic member 20 between an upper end formed in a disk shape and the plate 140. The elastic member 20 is in a compressed state, and the rod 201 is in a pulled state. The combined structures described above are arranged on all sides of the car 14.

The car 14 shown in FIG. 22 is located at the uppermost position and shows a state at a stable equilibrium point. When the inertial force acts on the car frame and the car so that the relative position between the car frame and the car moves due to disturbance outside the car such as bending of the rail from this state, the car 14
It moves laterally with respect to the car frame 5 by the action of the regulating member 2 arranged in parallel. At this time, the distance between the contact point between the upper end of the regulating member 2 and the plate 140 and the contact point between the lower end of the regulating member 2 and the car frame 5 becomes longer, and the elastic member 20 is further compressed. For this reason, a new reaction force is generated in the elastic member 20. After the inertial force has disappeared, the car 14 returns to the stable equilibrium point located at the top due to the newly generated reaction force on the elastic member 20. Therefore, similarly to the embodiments described so far, the present invention has a feature that an elevator having a particularly excellent ride quality can be provided.

As a feature of this embodiment, the state of the elastic member 20 can be inspected from outside the car frame, and there is an advantage that maintenance and management become easy.

In the above description, the regulating members 2 constituting the present invention are installed in parallel with each other. The vibration characteristics thereof will be described in detail with reference to FIGS. 23 to 26. FIG. 23 is a graph showing the frequency characteristics of the vibration of the present invention, and FIGS. 24 to 26 show the vibration modes at that time.

FIG. 23 is a graph showing the frequency characteristics of the vibration. The characteristics indicated by the solid line are those according to the present invention, and the characteristics indicated by the broken lines are the characteristics of the conventional elevator shown in FIGS. 35 and 36. The horizontal axis in FIG. 23 is the frequency. The vertical axis in the figure shows the acceleration on the floor of the car with respect to the displacement of the bending of the rail in decibels. The characteristics of the conventional elevator indicated by the broken line are 2 Hz, 4 Hz, 12 H
There is a peak near z. The solid line characteristic according to the present invention is:
There are peaks around 0.8 Hz and 4 Hz. At the above large frequency of vibration, either the car 14 or the car frame 5
Or a vibration mode peculiar to both exists.

The vibration modes shown in FIGS. 24 to 26 will be described. The vibration modes shown in FIGS. 24 to 26 are diagrams schematically illustrating the car 14 and the car frame 5. The car 14 and the car frame 5 shown by solid lines in the figure show a state without vibration, and the car 14 and the car 14 shown by broken lines.
The car frame 5 indicates the vibration mode.

The vibration mode shown in FIG.
This shows a mode in which the car frame 5 integrally vibrates horizontally in the horizontal direction.

The vibration mode shown in FIG.
The rotation vibration mode in which the car frame 5 swings integrally is shown.

The vibration mode shown in FIG.
This shows a mode in which the car frame 5 separately vibrates horizontally in the horizontal direction.

The peak near 2 Hz of the conventional elevator shown by the broken line in FIG. 23 is due to the mode in which the car 14 and the car frame 5 shown in FIG. 24 vibrate in the horizontal direction integrally. The peak around 4 Hz in the conventional elevator is due to the rotational vibration mode in which the car 14 and the car frame 5 swing together as shown in FIG. The peak around 12 Hz of the conventional elevator is due to the mode in which the car 14 and the car frame 5 separately vibrate horizontally in the horizontal direction. In a conventional elevator, car 14 and car frame 5
Are connected by a vibration-proof rubber and are relatively rigidly connected in the lateral direction, so that a mode in which vibrations integrally vibrate at a low frequency of 10 Hz or less becomes dominant.

On the other hand, the characteristics according to the present invention shown by the solid line in FIG. 23 have peaks at around 0.8 Hz and 4 Hz. The peak around 0.8 Hz is shown in FIG. 26 in which the car 14 and the car frame 5 separately vibrate horizontally in the horizontal direction, which are caused by sufficiently lowering the lateral support rigidity as described in some embodiments. It depends on the mode shown in
Its vibration level is low enough. In the present invention, the vibration peak around 2 Hz due to the mode in which the car 14 and the car frame 5 shown in FIG. 24 vibrate integrally and horizontally in the conventional elevator is eliminated.

However, the peak around 4 Hz of the characteristic according to the present invention shown by the solid line in FIG. 23 is the rotational vibration mode in which the car 14 and the car frame 5 swing together as shown in FIG. It shows the same characteristics as the peak around 4 Hz generated in the elevator. That is, in the embodiments described so far, since the car 14 does not have the degree of freedom to swing separately with respect to the car frame 5, the car 14 and the car frame 5 shown in FIG. Regarding the rotational vibration mode, the same result as the conventional example is obtained.

As described above, according to the present invention, it is understood that large vibrations are eliminated as compared with the prior art, and the riding comfort is dramatically improved. However, depending on the shape of the bending of the guide rail actually constructed in the building, the vibration caused by the rotation vibration mode in which the car 14 and the car frame 5 swing together around 4 Hz is closer to 2 Hz. In some cases, the ride comfort may be worse than in the mode in which the car 14 and the car frame 5 vibrate integrally and horizontally in the horizontal direction.

The present invention can also be applied to a case where the vibration in the rotational vibration mode deteriorates the riding comfort more than the mode in which the car 14 and the car frame 5 vibrate horizontally in the horizontal direction integrally. An embodiment of the present invention in this case will be described with reference to FIGS.

FIG. 27 is a schematic front view showing another embodiment of the present invention. In this embodiment, an elastic member, which is an essential element of the present invention, is omitted in the drawings. A first fulcrum indicated by a circle is provided at a lower portion of the car 14. A second fulcrum indicated by a circle is provided on the car frame 5 at a position facing the first fulcrum and below the first fulcrum, and is connected by the regulating member 2.

In this embodiment, the regulating member 2 is set obliquely so that a straight line passing through the first fulcrum and the second fulcrum facing the first fulcrum passes through the position of the center of gravity of the car 14. The car frame 5 and the car 14 reciprocate with each other. Here, if the car frame 5 is fixed with reference to the car frame 5, the first fulcrum rotates about the second fulcrum. The rotation center of the car 14 is a point where a plurality of straight lines passing through the first fulcrum and the second fulcrum facing the first fulcrum cross each other. In this embodiment, the center of gravity of the car 14 is set.
The car 14 and the regulating member 2 indicated by a solid line in the drawing indicate when the car 14 is located at the equilibrium point, and the car 14 and the regulating member 2 indicated by the broken line indicate the center of gravity of the car 14. This shows a state of swinging as a rotation center. In this embodiment, the degree of freedom in which the car 14 moves in the horizontal direction with respect to the car frame 5 is not set.

FIG. 28 is a graph showing the frequency characteristic of the vibration at this time. The characteristic shown by the solid line is according to the present invention, and the characteristic shown by the broken line is the characteristic of the conventional elevator as described with reference to FIG. Is shown. The horizontal axis in FIG. 28 is the frequency. The vertical axis in the figure shows the acceleration on the floor of the car with respect to the displacement of the bending of the rail in decibels. The characteristic of the solid line according to the present invention has peaks at around 1.1 Hz and 2 Hz.
A vibration mode unique to one or both of the cage frames 5 exists.

Here, a new vibration mode will be described with reference to FIG. The vibration mode shown in FIG. 29 is a drawing schematically showing the car 14 and the car frame 5. In the drawing, the car 14 and the car frame 5 indicated by solid lines indicate a state without vibration, and the car 14 and the car frame 5 indicated by broken lines indicate a vibration mode.

The vibration mode shown in FIG.
The rotation vibration mode in which the car frame 5 swings separately is shown.

The peak near 1.1 Hz of the characteristic according to the present invention shown by the solid line in FIG. 28 is due to the sufficiently low rotational support rigidity in the lateral direction as described in the embodiment of FIG. This is due to the mode in which the car frame 5 vibrates separately in the lateral direction, but the vibration level is sufficiently low. The vibration peak near 2 Hz caused by the mode in which the car 14 and the car frame 5 integrally vibrate horizontally in the horizontal direction shown in FIG. 24, which is generated in the conventional elevator, similarly exists in the present invention.

In this embodiment, since the car 14 and the car frame 5 are not supported so as to have a degree of freedom of translational movement in the horizontal direction, the vibration at around 2 Hz in the mode in which the car 14 and the car frame 5 vibrate horizontally in the horizontal direction is a conventional example. The result is similar to.

As described above, the present embodiment also eliminates large vibrations as compared with the prior art, and dramatically improves riding comfort.

However, depending on the bent shape of the guide rail actually constructed in the building, the characteristics when the regulating members 2 are set parallel to each other may be better.

The present invention can be applied to a case where both the vibration in the rotational vibration mode and the vibration in the horizontal vibration mode are effectively reduced. In this case, the embodiment of the present invention is shown in FIG. This will be described with reference to FIGS.

FIG. 30 is a schematic front view showing still another embodiment of the present invention. In this embodiment, an elastic member, which is an essential element of the present invention, is omitted in the drawings. A first fulcrum indicated by a circle is provided at a lower portion of the car 14. The car frame 5 has a second circle indicated by a circle at a position facing the first fulcrum and below the first fulcrum.
Fulcrum is provided and connected by the regulating member 2. In this embodiment, the first fulcrum and the second
The restricting member 2 is set obliquely so that a straight line passing through the fulcrum passes above the position of the center of gravity of the car 14. The car frame 5 and the car 14 reciprocate with each other. Here, if the car frame 5 is fixed with reference to the car frame 5, the first fulcrum rotates about the second fulcrum. The rotation center of the car 14 is a point at which a straight line passing through the first fulcrum and the second fulcrum facing the first fulcrum intersect each other. In this embodiment, it is set above the position of the center of gravity of the car 14. The car 14 and the regulating member 2 shown by solid lines in the figure
Indicates when the car 14 is located at the equilibrium point,
The car 14 and the regulating member 2 indicated by the broken lines are connected to the car 1
4 shows a state of swinging with the position of the center of gravity as the center of rotation.

FIG. 31 is a graph showing the frequency characteristics of the vibration. The characteristics indicated by the solid lines are those according to the present invention, and the characteristics indicated by the broken lines are the same as those described with reference to FIGS.
37 shows characteristics of the conventional elevator shown in FIG. 36 and FIG. The horizontal axis in FIG. 31 is the frequency. The vertical axis in the figure shows the acceleration on the floor of the car with respect to the displacement of the bending of the rail in decibels. The solid line characteristic according to the present invention is:
The vibration characteristics described in FIGS. 23 and 28 are moderate, and no large peaks are found. As a result, favorable vibration characteristics are obtained regardless of the bent shape of the guide rail installed in the building.

A specific embodiment in which the regulating member 2 described with reference to FIGS. 27 to 31 is set obliquely will be described below with reference to the drawings.

An embodiment of the present invention will be described with reference to FIG. FIG. 1 is a front view showing a main part of a specific embodiment of the present invention. In this embodiment, the regulating member 2 is used.
Has the same configuration as that of the embodiment shown in FIG. 3, except that it is obliquely set so as to pass through the center of gravity of the car 14 or a point above the center of gravity. That is, the regulating member 2
Is configured to have a first fulcrum 21 and a second fulcrum 22 at both ends through a hole provided at the center of the mounting stand 24, the vibration isolating rubber 131, and the bracket 23. And a second fulcrum 22 facing the first fulcrum 21 is located closer to the center of the car 14 than the second fulcrum 22 when viewed from above. The axes are respectively set so as to be directed to the center of gravity of the car or to a point located above the center of gravity.

With the above configuration, the vibration of the car in the rotation mode can be significantly reduced.

Another embodiment of the present invention will be described with reference to FIG. FIG. 1 is a front view showing a main part of a specific embodiment of the present invention. This embodiment has the same configuration as the embodiment shown in FIG. 21 except that the axis of the regulating member 2 is directed to the center of gravity of the car 14 or a point above the center of gravity. That is, the regulating member 2 has a structure in which the shaft portions 28 are diagonally connected between the mounting portions 281 at both ends, and the first vibration-proof rubber unit is located inside the second vibration-proof rubber unit. are doing. For this reason, the positional relationship between the rotatable first fulcrum and the second fulcrum existing in the vibration isolating rubber unit 135 using the flexibility of the elastic body is as follows.
When viewed from above, the position of the first fulcrum 21 is located closer to the center of the car 14 than the position of the second fulcrum 22,
Each of the plurality of regulating members 2 is set to be directed to the center of gravity of the car or a point located above the center of gravity of the car. With the above-described configuration, the vibration of the car in the rotation mode can be significantly reduced, and an elevator having significantly less lateral vibration as compared with the related art can be provided.

FIG. 34 shows still another embodiment of the present invention.
This will be described with reference to FIG. FIG. 1 is a front view showing a main part of a specific embodiment of the present invention. In the embodiment of FIG. 33, the angle at which the regulating member 2 faces and the angle at which the vibration isolating rubber unit is set are not right angles, so that the vibration isolating rubber 132 always has a moment in addition to the compressive force due to gravity. Is acting, which may not be preferable in terms of reliability depending on the set angle of the regulating member 2.

The present embodiment is an improvement on this point.
The regulating member 2 has plates at both ends thereof, and anti-vibration rubbers 134 are fixed to the plates at both ends. The anti-vibration rubbers 134 fixed to both ends of the regulating member 2 are each fixed to the mounting base 41 having a slope.
The upper mounting table 41 is fixed to the car 14 by a bolt, and the upper mounting table 41 is fixed to a car frame by bolts. A rotatable first fulcrum 21 is provided on the lower vibration isolating rubber 134 and a second fulcrum 22 is provided so as to be rotatable.
The first rubber cushion unit is located inside the second rubber cushion unit.

For this reason, the positional relationship between the rotatable first fulcrum and the second fulcrum present in the vibration isolating rubber 134 is such that the position of the first fulcrum 21 is the second fulcrum 22 The plurality of restricting members 2 are arranged to be located closer to the center of the car 14 than to the center of the car 14 and to a point located above the center of gravity of the car or the center of gravity of the car.

According to this embodiment, when the inertia force acts on the car frame 5 and the car 14 so that the relative position between the car frame and the car moves due to disturbance outside the car such as bending of the rail, vibration is prevented. As the first force, a shear force due to the relative displacement of the car frame 5 and the car 14 acts on the rubber 134, and the second force is obtained by multiplying the inertial force by the length of the regulating member 2 as the second force. Acts as a moment. The shearing force does not depend on the length of the regulating member 2. The moment acting on the vibration isolation rubber 134 depends on the length of the regulating member 2, and the longer the length, the larger the moment.

Further, the regulating member 2 enlarges the lateral displacement generated on the vibration isolating rubber 134 by the effect of its length.
In combination with this effect and the effect of the regulating member 2 increasing the moment force, the lateral displacement becomes extremely large in the present embodiment, and the lateral supporting rigidity is reduced as compared with the conventional invention. it can. Further, the car 14 is rotatably moved in the lateral direction with respect to the car frame 5 by the action of the restricting member 2 disposed obliquely, so that a comfortable ride can be achieved.

With the above configuration, the vibration in the rotation mode of the car can be significantly reduced, and an elevator having significantly less lateral vibration than the conventional one can be provided. Further, since the vibration isolating rubber is symmetrically disposed with respect to the axis of the regulating member 2, there is an advantage that the moment does not act on the vibration isolating rubber in a stable state and the reliability is high.

Although the embodiments of the present invention have been described in detail, many modifications are possible. A metal spring and a vibration-proof rubber have been described as the elastic members 20. The gist of the present invention is that the elastic member 20 applies a force between the car 14 and the car frame 5 in the lateral direction in accordance with the relative displacement between the car 14 and the car frame 5 to place the car in a stable position. It means something to be restored. Therefore, by using a motor, an electromagnet, an actuator such as a hydraulic device or a pneumatic device as the elastic member 20, the relative displacement between the car 14 and the car frame 5 is detected, and the actuator is actuated by the output signal of the car 14 to operate the car. A force may be applied between the car 14 and the car frame 5 in the lateral direction so that the relative displacement between the car 14 and the car frame 5 becomes a target value, and the car may be restored to a stable position.

As the elastic member 20, the vertical direction, the horizontal direction,
Alternatively, the embodiments in which the restoring force is generated by the moment have been described individually, but they can be used in combination with each other.

Although various types of regulating members have been described, many of them can be considered in combination with an elastic member, but these are within the scope of the present invention. Further, the regulating member may be configured such that its car side end is located outside the car frame side end.

[0158]

As described above, according to the present invention, it is possible to reduce the lateral spring constant of the car, thereby reducing the lateral natural frequency of the car and suppressing the roll. It is possible to provide a comfortable elevator.

[Brief description of the drawings]

FIG. 1 is a front view showing a configuration of an elevator provided with an example of a vibration damping device according to the present invention.

FIG. 2 is a side view showing the configuration of an elevator provided with an example of the vibration damping device of the present invention.

FIG. 3 is a front view showing a vibration control device provided in the elevator of the present invention in a partial cross section.

FIG. 4 is an explanatory diagram illustrating the operation of the vibration damping device constituting the present invention shown in FIG.

FIG. 5 is an explanatory diagram for explaining the operation of the vibration damping device constituting the present invention shown in FIG. 3;

FIG. 6 is a front view showing a partial cross section of an embodiment of the vibration damping device constituting the present invention.

FIG. 7 is a front view showing a partial cross section of another embodiment of the vibration damping device constituting the present invention.

FIG. 8 is an explanatory diagram for explaining the operation of another embodiment of the vibration damping device constituting the present invention shown in FIG. 7;

FIG. 9 is a characteristic diagram showing setting conditions of another embodiment of the vibration damping device constituting the present invention shown in FIG. 7;

FIG. 10 is a front view showing, in partial cross section, still another embodiment of the vibration damping device constituting the present invention.

FIG. 11 is a cross-sectional view showing an example of a fulcrum used in the vibration damping device constituting the present invention.

FIG. 12 is a front view showing another example of a fulcrum used in the vibration damping device constituting the present invention.

FIG. 13 is a cross-sectional view showing still another example of a fulcrum used in the vibration damping device constituting the present invention.

FIG. 14 is a cross-sectional view showing another example of a fulcrum used in the vibration damping device constituting the present invention.

FIG. 15 is a front view showing a partial cross section of another embodiment of the vibration damping device constituting the present invention.

FIG. 16 is a front view showing, in partial cross section, still another embodiment of the vibration damping device constituting the present invention.

FIG. 17 is an explanatory diagram for explaining the operation of a further embodiment of the vibration damping device constituting the present invention shown in FIG.

FIG. 18 is a front view showing a partial cross section of another embodiment of the vibration damping device constituting the present invention.

FIG. 19 is a perspective view showing a main part of the vibration damping device constituting the present invention shown in FIG. 18 in an exploded state.

FIG. 20 is a front view showing, in partial cross section, still another embodiment of the vibration damping device constituting the present invention.

FIG. 21 is a front view showing a partial cross section of another embodiment of the vibration damping device constituting the present invention.

FIG. 22 is a front view showing a partial cross section of still another embodiment of the vibration damping device constituting the present invention.

FIG. 23 is a characteristic diagram showing vibration characteristics of the elevator of the present invention.

FIG. 24 is a front view showing one vibration mode of the elevator of the present invention.

FIG. 25 is a front view showing another vibration mode of the elevator of the present invention.

FIG. 26 is a front view showing still another vibration mode of the elevator according to the present invention.

FIG. 27 is a front view showing a main part of an elevator provided with another embodiment of the vibration damping device constituting the present invention.

FIG. 28 is a characteristic diagram showing vibration characteristics of an elevator provided with another embodiment of the vibration damping device constituting the present invention.

FIG. 29 is a front view showing another vibration mode of the elevator according to the present invention.

FIG. 30 is a front view showing a main part of an elevator provided with still another embodiment of the vibration damping device constituting the present invention.

31 is a characteristic diagram showing vibration characteristics in the example of the present invention shown in FIG.

FIG. 32 is a front view, partially in section, of another embodiment of the vibration damping device constituting the present invention.

FIG. 33 is a front view showing, in partial cross section, still another embodiment of the vibration damping device constituting the present invention.

FIG. 34 is a front view showing a partial cross section of another embodiment of the vibration damping device constituting the present invention.

[Explanation of symbols]

2: regulating member, 5: car frame, 13: anti-vibration rubber, 14: car, 20: elastic member, 21: first fulcrum, 22: second fulcrum.

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Masayuki Shigeta 1070 Mo, Katsuta-shi, Ibaraki Hitachi, Ltd. Mito Plant (56) References JP-A-52-101547 (JP, A) 26011 (JP, B2) JP-B-51-38133 (JP, B2) JP-B-51-22274 (JP, B1) (58) Fields investigated (Int. Cl. ⁷ , DB name) B66B 11/02

Claims (4)

(57) [Claims] An elevator for elastically supporting a car on which a passenger gets on a car frame and guiding the car frame to be vertically movable along a guide rail of a hoistway, wherein the car and the car frame are disposed between the car and the car frame. An elastic member for supporting the car to be lifted vertically upward with respect to the car frame; and an elastic member for supporting the car so as to be relatively movable with respect to the car frame, and the elastic member supporting the car. An elevator, comprising: a restricting member for restricting an uppermost position of the car by applying a pulling force when lifting the car frame vertically upward. 2. An elevator according to claim 1, wherein a plurality of said regulating members are provided at a lower portion of said car so that each of them is parallel. 3. The elevator according to claim 2, wherein said regulating members are provided at four lower corners of said car. 4. The elevator according to claim 2, wherein said regulating member is set so as to be vertical with said car positioned at the highest position with respect to said car frame. .