JP4291847B2 - Elevator guide device - Google Patents

Description

  The present invention relates to a guide device for an elevator that guides the raising and lowering operation of a car along a hoistway.

  A schematic configuration of a conventional elevator is shown in FIG. The car frame 1 is suspended in a hoistway (not shown) of the building by a rope 3, and the car room 2 is attached to the inside of the car frame 1. The rope 3 is pulled by a hoist (not shown), and the car moves up and down. Guide rails 5a and 5b are vertically installed on both side walls of the hoistway (not shown) so as to face each other, and the left and right portions of the upper and lower ends of the car frame 1 rotate along the guide rails 5a and 5b, respectively. And the guide apparatus 6 which guides a car frame to the left-right direction and the front-back direction is provided. Hereinafter, for convenience of explanation, the surface with the door 88 is front, the x-axis positive direction in the figure is “front side” (the opposite side is “rear side”), and the y-axis positive direction is “right side” (the opposite side is “ The left side)) and the positive z-axis direction are referred to as “upper side” (the opposite side is “lower side”). One guide device 6 includes three sets of guide roller devices 17.

  FIG. 19 shows the configuration of one guide roller device 17 in the guide device 6. The base 8 is attached to the car frame 1, and a lever 11 is attached to the base 8 through a lever swing shaft 10 so as to be swingable. A guide roller 12 is rotatably supported by the lever via a guide roller rotating shaft 9. Further, shafts 13 and 14 are provided horizontally on the base 8 as shown in FIG. 19, and these shafts 13 and 14 protrude by loosely inserting the lever 11, and a spring 15 is provided on the one shaft 13 at the protruding portion. The other shaft 14 is provided with a stopper 16.

  The spring 15 elastically biases the lever 11 to the side where the guide rail 5 is disposed, and the peripheral surface of the guide roller 12 is elastically brought into contact with the surface of the guide rail 5. A stopper 16 is fixed to the shaft 14 to limit the inclination angle of the lever 11. Further, there is a damper 18 that is assembled between the lever 11 and the base 8.

  The car frame 1 is supported by the guide rails 5 a and 5 b by the guide device 6, and the car 7 is guided by the rolling contact between the individual guide rollers 12 and the guide rails 5 of the respective guide devices. Even when the guide rail 5 is bent or stepped, the guide roller 12 is elastically displaced against the spring 15, the lever 11 is inclined, and the vibration is absorbed by the spring 15. Prevent transmission of vibrations.

On the other hand, when the passenger rides intensively on the end of the car room 2 and an unbalanced load is generated, the car 7 is tilted, the tilted guide roller 12 is strongly pressed against the guide rail 5, and the lever 11 is moved to the base 8. It is greatly inclined to.
JP-A-8-151178

  However, with the recent increase in the number of buildings, elevators have been speeded up, and even small deformations of guide rails and small protrusions on the surface, which were not a problem at conventional speeds, can be performed at high speed. When passing, it causes an impact force to act on the guide roller.

  In general, as shown in FIG. 20, the impact force Fc received when the guide roller 12 passes through a minute protrusion on the surface of the guide rail 5 at a high speed is transmitted to the lever 11 via the guide roller 12. When an impact force is applied to a rigid body as a physical phenomenon, the rigid body instantaneously starts rotating and translating. And the point which becomes immovable in a rigid body by superposition of a rotational motion and a translational motion exists. This fixed point is called the instantaneous impact rotation center, and its position depends on the mass of the object, the moment of inertia, and the direction of the impact force. For this reason, when the impact force Fc acts on the lever 11, the lever 11 attempts to rotate instantaneously around a certain impact rotation center.

  Therefore, in the conventional guide apparatus as described above, the guide roller rotating shaft 9 is provided at a position (a distance a from the lever swinging shaft 10) that is separated from the lever swinging shaft 10 toward the one end side. Since the spring 15 supports a position further away from the guide roller rotating shaft 9 (distance b from the lever swing shaft 10), the instantaneous impact rotation center is displaced from the lever swing shaft 10, so that the lever swing naturally. A drag force Rb due to the impact force Fc is generated from the moving shaft 10 to the base 8, and the impact force Fc is directly transmitted to the base 8 without passing through the spring 15.

In general, when an external force Fc is transmitted from the guide rail 5 to the lever via the guide roller 12, the external force Fc is divided and transmitted to the lever swing shaft and the spring action point at a ratio based on the moment balance relation law. That is, the component force Rb to the lever swing shaft 10 and the component force Rs to the spring force application point 89a are Rs = a / b ^* Fc = 1 / R ^* Fc (a), depending on the force point, the action point, and their positional relationship.
Rb = (ba) / b ^* Fc = (1-1 / R) ^* Fc (b)
It becomes. Here, a is the height between the lever swing shaft / guide roller rotation center, b is the height between the lever swing shaft / spring force acting point, and R = b / a is called the lever ratio.

  In the conventional guide apparatus as described above, since the lever ratio R is large as shown in FIG. 20, the drag force Rb at the lever swing shaft 10 is larger than the drag force Rs at the spring force acting point 89a. Then, the ratio of the force transmitted directly to the base 8 rather than the absorption by the spring 15 increases, and the vibration from the guide rail 5 is easily transmitted to the car 7. Thus, in the conventional guide device, since the impact force from the guide rail is easily transmitted to the car, there is a problem that the car is swayed and the ride comfort is deteriorated.

  In order to suppress the vibration received by the car through the guide rollers, it may be necessary to increase the processing accuracy and installation accuracy of the guide rails. It will increase.

  In addition, the speed of the car is increased at the same time as the speed is increased, and the car is becoming larger, and the uneven load tends to increase due to an increase in the load capacity and the bottom area. In particular, in an elevator of a type called a double deck type in which the car room has an upper and lower two-layer structure, the load capacity is large and the offset load is larger. When the load on the car is increased, the spring must be stiffer so that the lever does not hit the stopper. However, with the hard spring, the guide roller is in contact with the guide rail and the vibration received from the guide rail is applied to the car. There is a risk that it may be difficult to maintain a good ride comfort.

  SUMMARY OF THE INVENTION Accordingly, the present invention is intended to provide a guide device for an elevator that can maintain a good riding comfort of the car even when the car ascending / descending speed is increased or the unbalanced load is increased.

  According to a first aspect of the present invention, guide roller devices each having a guide roller having a rotation axis perpendicular to the rectangular plane are provided at the upper and lower ends of the car cage frame at positions that form the vertices of the rectangular plane. In an elevator that lifts and lowers a car along a guide rail by rolling the guide roller to the guide rail, the guide roller device is supported swingably with respect to the car frame, and is separated from the lever support portion to one end side. A guide roller of one guide roller device for each of the guide roller devices that are diagonal to each other in a rectangular plane perpendicular to the rotation axis thereof. The external force received by the guide rail from the lever support portion of the lever member of the other guide roller device A guiding device of the elevator with the external force transmission mechanism for transmitting the.

  According to a second aspect of the present invention, there is provided an elevator for elevating and lowering a car along the guide rail by rolling the guide roller to the guide rail. Each guide roller device includes a lateral guide roller having a rotation axis in the longitudinal direction of the car. A front and rear guide roller having a rotation axis perpendicular to the rotation axis of the horizontal guide roller and positioned at the front and rear of the horizontal guide roller, and the respective guide roller devices are mounted on the upper and lower left and right ends of the car cage frame. The rotation axes of the rollers are on the same rectangular plane, the rotation axes of the front and rear guide rollers at the upper and lower left ends of the car frame are on the same rectangular plane, and the rotation axes of the front and rear guide rollers on the upper and lower sides of the car frame are on the same rectangular plane. Each having a guide roller whose rotational axes are diagonal to each other in at least one of the rectangular planes perpendicular to the rotational axis of each guide roller For an id roller apparatus, an elevator having an external force transmission mechanism that transmits an external force received by a guide roller of one guide roller apparatus from a guide rail to a position on the other end side from a lever support portion of a lever member of the other guide roller apparatus. It is a guidance device.

  According to a third aspect of the present invention, the external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting the position of the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. It is the guide apparatus of the elevator of 1st or 2nd description.

  According to a fourth aspect of the invention, the external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting a position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The elevator guide device according to the first or second aspect, wherein an elastic mechanism that elastically deforms when the tension of the push-pull cable becomes a predetermined value or more is provided in the middle of the push-pull cable.

  According to a fifth aspect of the invention, the external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting the position of the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The push-pull cable is the elevator guide device according to the first or second embodiment, wherein both ends of the push-pull cable are constituted by tension wires and the intermediate portion is constituted by a rod-shaped member.

  According to a sixth aspect of the invention, the external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting the position of the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The push-pull cable has tension wires at both ends, a rod-shaped member at the middle, and a suspension mechanism that suspends the rod-shaped member with a force that counteracts the weight of the rod-shaped member. It is the guide apparatus of the elevator of 1st or 2nd description.

  According to a seventh aspect of the invention, the external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting the position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. In this push-pull cable, both end portions are constituted by tension wires, and the intermediate portion is constituted by a rod-like member, and an elastic mechanism that elastically deforms when the tension wire tension exceeds a predetermined value is provided at the end of the rod-like member or It is the guide apparatus of the elevator of 1st or 2nd provided in the intermediate part.

  According to an eighth aspect of the invention, the external force transmission mechanism is provided at a position on the other end side from the lever support portion in the lever member of each guide roller device, and converts the swinging motion and the twisting motion of the lever member to each other. And a wire member capable of transmitting torsional torque that connects the motion conversion mechanism of each guide roller device, and the guide of the elevator according to the first or second aspect that transmits the external force received by the guide roller from the guide rail by the torsional torque. Device.

  According to a ninth aspect of the present invention, the external force transmission mechanism includes a gear member provided on a lever member of each guide roller device at a position on the other end side from the lever support portion, and a rod-shaped member having racks formed on both end portions. The elevator guide device according to claim 1 or 2, wherein each guide roller device is connected by meshing a rack of rod-like members with a gear of the roller device.

  A tenth aspect of the invention is the elevator guide apparatus according to the ninth aspect, in which an elastic mechanism that elastically deforms when the tension of the rod-shaped member of the external force transmission mechanism exceeds a predetermined value is provided in an intermediate portion of the rod-shaped member.

  An eleventh aspect of the present invention is an elevator that provides guide roller devices at the upper and lower ends of a car frame of a car, and moves the car up and down along the guide rail by rolling the guide roller of the guide roller device to the guide rail. The guide roller device includes a lever member that is swingably supported with respect to the car frame and that rotatably supports the guide roller at a position spaced from the lever support portion to one end side, and within the same rectangular plane of the car frame. In the guide roller devices that are diagonal to each other, the external force received by the roller support portion of the lever member of one guide roller device from the guide rail via the guide roller is mutually applied to the roller support portion of the lever member of the other guide roller device. It is the guide apparatus of the elevator provided with the external force transmission mechanism which transmits to.

  In a twelfth aspect of the invention, the external force transmission mechanism is enclosed in a piston cylinder device that interlocks with the movement of the roller support portion of the lever member of the guide roller device, a pipe that connects each piston cylinder device, and the piston cylinder device and the pipe. The elevator guide apparatus according to the eleventh aspect, comprising a liquid and a pressure adjusting mechanism that is provided in the middle of the pipe and adjusts the liquid pressure inside the pipe.

  As still another example, the first example is provided with guide roller devices at the upper and lower ends of the car frame of the car, and the car is moved along the guide rail by rolling the guide roller of the guide roller device to the guide rail. In the elevator that moves up and down, the guide roller device is supported swingably with respect to the car frame, and a lever member that rotatably supports the guide roller at a position spaced from the lever support portion to one end side, and the lever member The elevator guide device includes a weight member provided at a position apart from the lever support portion at the other end side.

  A second example is a guide device for an elevator according to the first example, in which the guide roller device has a lever member that protrudes from the lever support portion at the other end side and uses the protruding portion as a weight member.

  A third example is an elevator that provides guide roller devices at the upper and lower ends of the car frame of the car and moves the car up and down along the guide rail by rolling the guide roller of the guide roller device to the guide rail. The guide roller device is supported swingably with respect to the car frame, and a lever member that rotatably supports the guide roller at a position spaced from the lever support portion to one end side, and a guide rail near the support portion of the guide roller. It is the guide apparatus of the elevator provided with the urging mechanism urging | biasing in the direction pressed on.

The elevator guide device according to the present invention has the following effects.
As described above in detail, according to the first invention, for example, even if a laterally offset load occurs in the car, the external force acting on each lever member is transmitted between the guide roller devices. A moment that antagonizes the car is generated with respect to the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member has a biasing mechanism that absorbs vibration, the vibration absorbing effect can be maintained, so that a good riding comfort in the car can be maintained. Can do.

  According to the second aspect of the invention, even when a lateral load as well as a longitudinal load is generated on the car at the same time and the car is tilted, a moment is applied between the guide roller devices corresponding to each load. Occurring with respect to the car frame, the inclination of the car in all directions can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member is provided with an urging mechanism that absorbs vibration, the vibration absorbing effect can be maintained. Can maintain a good ride in the car.

  According to the third aspect of the invention, for example, even when a laterally offset load is generated in the car, the external force acting on each lever member between the guide roller devices is transmitted to each other as the tension of the push-pull cable. A moment that antagonizes the load is generated with respect to the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member has a biasing mechanism that absorbs vibration, the vibration absorbing effect can be maintained, so that a good riding comfort in the car can be maintained. Can do.

  According to the fourth aspect of the present invention, when an excessive tension is applied to the push-pull cable connecting the guide roller devices, the elastic mechanism is elastically deformed, and it is possible to avoid applying an excessive tension to the push-pull cable. As well as being able to maintain a good ride comfort in the car.

  According to the fifth aspect of the invention, for example, even when a laterally offset load is generated in the car, a moment that antagonizes the load is generated on the car frame. As a result, the inclination of the car can be suppressed, and even if an uneven load occurs, the inclination of the car can be suppressed, and if the lever member has a biasing mechanism that absorbs vibration, the vibration absorbing effect is provided. Therefore, it is possible to maintain a good ride comfort in the car. Furthermore, since the tension wire is bendable, it can be easily attached to a limited space around the car. In addition, the rigidity of the force transmission path can be made higher than when the wire is used alone, and the influence of the tension wire can be reduced.

  Moreover, according to 6th invention, it can prevent that the tension | tensile_strength of a push pull cable changes with the weight of a rod-shaped member, and can maintain the function of an apparatus.

  Further, according to the seventh invention, the rigidity of the force transmission path can be made higher than that in the case where the wire is used alone, the tension wire can be less stretched, and excessive tension acts on the push-pull cable and the rod-shaped member. It can prevent and keep function.

  According to the eighth aspect of the invention, for example, even when a laterally offset load is generated in the car, the external force acting on each lever member between the guide roller devices is transmitted to the mutual as twisting torque by the wire member. Then, a moment that antagonizes the unbalanced load is generated on the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member has a biasing mechanism that absorbs vibration, the vibration absorbing effect can be maintained, so that a good riding comfort in the car can be maintained. Can do.

  According to the ninth aspect of the invention, for example, even when a laterally offset load is generated in the car, the external force acting on each lever member is transmitted between the guide roller devices. Then, a moment that antagonizes the unbalanced load is generated on the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member has a biasing mechanism that absorbs vibration, the vibration absorbing effect can be maintained, so that a good riding comfort in the car can be maintained. Can do.

  According to the tenth aspect, the rigidity of the path for transmitting the force between the guide roller devices can be made appropriate. In addition, it is possible to prevent an excessive tension from acting on the rod-shaped member and maintain a good riding comfort.

  According to the eleventh aspect of the invention, for example, even if a laterally offset load occurs in the car, the external force acting on each guide roller between the guide roller devices is supported by the roller of each guide roller device via the external force transmission mechanism. Communicate with each other. Then, a moment that antagonizes the unbalanced load is generated on the car frame, and the inclination of the car can be suppressed. As a result, the external force acting on the guide roller can be directly transmitted to the position of the rotation axis of the guide roller, so that the inclination of the lever member can be reduced and the biasing mechanism that absorbs vibration to the lever member. If it is provided, the vibration absorbing effect can be maintained, so that a good riding comfort in the car can be maintained.

  According to the twelfth aspect of the invention, for example, even when a laterally offset load is generated in the car, the external force acting on each guide roller between the guide roller devices is transmitted to each other in the form of liquid pressure, thereby A moment that antagonizes the load is generated in the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever member can be reduced, and if the lever member is provided with an urging mechanism for absorbing vibration, the vibration absorbing effect can be maintained, so that a good riding comfort in the car is maintained. be able to. Moreover, the rigidity with respect to the inclination of the car frame can be set to an appropriate value by the pressure adjusting mechanism.

  Further, according to the first example and the second example, the lever member is set to the center of impact force rotation by the impact force applied to the lever member by setting the physical quantity such as the moment of inertia and the center of gravity of the lever member to a predetermined value by the weight member. The lever support point can be made to coincide with the lever support point so that the impact force is not directly transmitted to the lever support portion. As a result, vibration from the guide rail is not directly transmitted to the car, and good riding comfort in the car can be maintained even when the lifting speed is increased and the vibration is increased.

  Further, according to the third example, most of the vibration from the guide roller is transmitted to the urging mechanism, and the vibration is efficiently absorbed by the urging mechanism. Therefore, even when the ascending / descending speed is increased and the vibration is increased, a good riding comfort in the car can be maintained.

  Hereinafter, a first embodiment will be described with reference to FIGS. FIG. 1 is a schematic side view of a guide roller device as a guide device according to the present embodiment. In the guide roller device 17 in the present embodiment, a lever 21 is attached to a base 19 via a lever swing shaft 20 so as to be swingable, and the base 19 is attached to the car frame 1. A guide roller 23 is rotatably supported by the lever 21 via a guide roller rotating shaft 22, and a balance weight 28 is provided at the lower end of the lever 21. Further, shafts 24 and 25 are horizontally provided on the base 19. These shafts 24, 25 are loosely inserted into the lever 21 and protrude to the side opposite to the side where the guide rail 5 is located, and one shaft 24 is provided with a stopper 26 at this protruding portion. The plate 106 is fixed to the shafts 24 and 25, and a spring length adjusting screw 105 is attached to the plate 106. The spring 27 is provided in the vicinity of the guide roller rotating shaft 22, is pressed by a spring length adjusting screw 105, and the other end presses the guide roller 23 against the guide rail 5 via the lever 21. Further, a damper 29 is provided between the arm 108 protruding from the lever 21 and the base 19.

  Here, the first principle in the present embodiment will be described with reference to FIGS. FIG. 2 is a schematic diagram for explaining the operation of the guide roller device according to the present embodiment. As already described with reference to FIG. 20, generally, the impact force received when the guide roller 12 passes through a small protrusion on the surface of the guide rail 5 at a high speed is transmitted as an impact force Fc to the lever 11 via the guide roller 12. The When an impact force is applied to a rigid body as a physical phenomenon, the rigid body instantaneously starts rotating and translating. And the point which becomes immovable in a rigid body by superposition of a rotational motion and a translational motion exists. This fixed point is called the instantaneous impact rotation center, and its position depends on the mass of the object, the moment of inertia, and the direction of the impact force. For this reason, when the impact force Fc acts on the lever 11, the lever 11 attempts to rotate instantaneously around a certain impact rotation center.

  Therefore, as in the present embodiment shown in FIG. 2, the balance weight 28 is provided below the lever 21 to adjust the mass / moment of inertia / center of gravity of the lever 21, and the instantaneous impact rotation center of the lever 21 is used as the lever swing shaft 20 If it is made to correspond to, drag | drug Rb 'by the impact force to the lever rocking shaft 20 will be set to zero. In other words, if the lever swing shaft 10 of the lever 11 coincides with the instantaneous impact rotation center, no drag Rb due to the impact force is generated from the lever swing shaft 10 to the base 8, and the impact force Fc is in principle the lever swing shaft 20. Is not transmitted to the base 19 via.

  The size and mounting position of the balance weight 28 are obtained, for example, as follows based on the first principle as described above. A simplified model of the lever 21 is shown in FIG. The meanings of symbols representing physical quantities in the figure are as follows.

M: Mass of the rigid body I: Moment of inertia around the center of gravity of the rigid body 90 a: Distance between the center of gravity G and the point of action of the impact force F h: Distance between the center of gravity G and point O on the AG extension line L: Center of gravity G and now Assume that the impact force of the impulse F is applied to the point A 91, and immediately after that, the rigid body 90 moves with the velocity v and the angular velocity ω with respect to the rigid body center of gravity 92. Then, M · v = F (1)
I ・ ω ＝ a ・ F (2)
Is established. The following equation is obtained by modifying the equations (1) and (2).

v = F / M (1) ′ ω = (a · F) / I (2) ′ Next, if the O point is taken on the extension line of AG and OG = h, then the velocity v0 at the O point is the translational motion V0 = vh · ω (3)
It becomes. Substituting the expressions (1) ′ and (2) ′ into the expression (3), v0 = F / M · (1− (h · a · M) / I) (4)
Is obtained. (4) The term in parentheses is 0 from the right side of the expression, that is, h · a · M = I (5)
Then, V0 = 0 and the point O becomes the center of instantaneous impact rotation. Therefore, if the mass and mounting position of the balance weight 97 are set so as to satisfy the expression (5), the drag of the swing fulcrum can be reduced to zero.

Adjustment of the impact rotation center of the lever by adding a balance weight will be described with reference to FIG. The mass / inertia / center of gravity of the lever 93 before the balance weight 97 is attached to the lever 93 are M1, I1, h1, the mass of the balance weight 97 is M2, and the distance from the lever swing shaft 95 is s. Then, the position h of the lever gravity center 96 with the balance weight after adding the weight is h = (M1 · h0−M2 · s) / (M1 + M2) (6)
It becomes. Then, the moment of inertia I about the center of gravity is I = {I0 + M1 · (h0−h) ^ 2} + M2 · (s + h) ^ 2 (7)
Therefore, if a balance weight 97 of mass M2 is established at the position of the distance s below the lever swing shaft 95 so that the formula obtained by substituting the formulas (6) and (7) into the formula (5) is established. good.

  As described above, the instantaneous impact rotation center of the lever 21 is made coincident with the lever swing shaft 20, and the drag force Rb 'corresponding to the impact force at the lever swing shaft 20 can be made zero. Actually, a drag Rb 'is slightly generated due to an installation error or the like. However, it is considered that the drag Rb can be made much smaller than the conventionally generated drag Rb. Therefore, the influence of the impact force transmitted directly to the car can be extremely reduced.

Next, the second principle in the present embodiment will be described with reference to FIG. As already described with reference to FIG. 20, when the external force Fc is transmitted from the guide rail 5 to the lever via the guide roller 12, the external force Fc is divided into the lever swing shaft and the spring action point at a ratio based on the moment balance relational law. To be transmitted. That is, the component force Rb to the lever swing shaft 10 and the component force Rs to the spring force application point 89a are Rs = a / b ^* Fc = 1 / R ^* Fc (8).
Rb = (ba) / b ^* Fc = (1-1 / R) ^* Fc (9)
It becomes. Here, a is the height between the lever swing shaft / guide roller rotation center, b is the height between the lever swing shaft / spring force acting point, and R = b / a is called the lever ratio (FIG. 2). reference). Therefore, if the lever ratio R is reduced, the drag force Rb at the lever swing shaft 10 becomes smaller than the drag force Rs at the spring force acting point 89a, and the rate of absorption by the spring 15 is increased more than the force transmitted directly to the base 8. It is considered that vibration from the guide rail 5 is easily transmitted to the car 7.

  In the present embodiment, on the basis of the second principle as described above, the spring 27 is arranged in the vicinity of the guide roller rotating shaft 22 as shown in FIG. 2 to reduce the lever ratio (in the figure, the arrows overlap and are difficult to see). Therefore, the position of the spring 27 is intentionally deviated from the guide roller rotating shaft 22). As a result, if a ′ → b ′ and R → 1, Rs → FcRb → 0 from Eqs. (8) and (9), the component force Rb ′ to the lever swing shaft 20 becomes 0, and the spring force The component force Rs to the action point 89b approaches Fc. That is, most of the vibration from the guide rail 5 is transmitted to the spring 27 side, and the ratio of transmission to the lever swinging shaft 20 side is reduced. Thereby, most of the external force received by the guide roller from the guide rail is transmitted to the spring side, and the vibration absorbing effect by the spring can be enhanced.

  In the embodiment of the present invention, the configuration including both the configuration based on the first principle and the configuration based on the second principle has been described. However, the configuration is not necessarily limited to this, and the first principle is not limited thereto. Only the configuration based on the second principle or the configuration based on the second principle may be applied.

  Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 4 is a schematic view of the car 7 as seen from the front. Guide roller devices 104a, 104b, 104c, and 104d are provided on the left and right portions of the upper and lower ends of the car 7, respectively. The upper left guide roller device 104a and the lower right guide roller device 104d are connected by a force transmission mechanism as indicated by a dotted line in the figure. Similarly to the above, the upper right guide roller device 104b and the lower left guide roller device 104c are connected by a force transmission mechanism different from the above. This force transmission mechanism transmits an external force acting in the direction in which the lever 19a of the upper left guide roller device 104a is tilted down to the lever 19d of the lower right guide roller device 104d as shown by a dotted line in FIG.

  Here, an example of the force transmission mechanism will be described with reference to FIG. The guide roller 23 in the present embodiment is rotatably attached to the lever 21, and the lever 21 is swingably attached to the base 19. The wire 33 is connected to the lower end portion of the lever 21 by a wire attachment portion 37. A tension wire 35 as a push-pull wire is composed of a wire 33 and an outer tube 34 covering the wire 33. The outer tube 34 is fixed to the base 19 with an outer tube end mounting portion 36a. In the drawing, the right side from the outer tube end mounting portion 36a is connected to a lever (not shown) of another guide roller device (not shown) having the same structure as that shown in FIG. Has been.

  In the embodiment of the present invention having such a configuration, as shown in FIG. 6, if a weight 32 is placed on, for example, the left end of the cab, the car is moved in the direction A shown in FIG. A moment is generated in the direction of tilting. Then, the upper left guide roller device 104a receives the external force B1 from the contacting guide rail and the lever tends to tilt with respect to the car 7. Similarly, the lower right guide roller device receives an external force B2 from the facing guide rail 5b, and the lever tends to tilt.

  As shown in FIG. 5, the external force B1 is transmitted to the lever 21 via the guide roller 23 and the guide roller rotating shaft 22, and tries to incline the lever 21 around the lever swing shaft 20 in the G direction. Then, the lower side of the lever 21 tries to incline in the H direction around the lever swing shaft 20 and the wire 33 is pulled in the I direction.

  The wire 33 moves relative to the outer tube 34 in the axial direction, thereby transmitting the force H acting on the lever 21 to the other end of the tension wire 35 as tension. The other end of the tension wire 35 transmits to the lever 19d of the lower right guide roller device 104d having the same configuration as that shown in FIG. 5 as indicated by the dotted line shown in FIG.

  Then, the lower end of the lever 19d is pulled, and a force D1 is returned to push the guide roller 23d back to the rolling guide rail 5b. This force becomes a reaction force and this time the guide roller 23a of the upper left guide roller device 104a is moved to the guide rail 5a. The force D2 is pushed back to (FIG. 6D). Accordingly, the forces D1 and D2 act as moments in a direction in which the car 7 is rotated in the E direction to cancel the inclination of the car 7.

  Further, when the direction of the unbalanced load is opposite to A, that is, when the weight 32 is placed on the right end of the cab, a force acts between the upper right guide roller device 104b and the lower left guide roller device 104c. Then, a rotational moment in the direction opposite to the E direction is generated in the car 7 to suppress the inclination of the car 7.

  As a result, a moment in a direction to cancel the moment generated by the unbalanced load can be generated in the car frame, and the inclination of the car can be suppressed. As a result, the inclination of the lever can be reduced, the spring is not pushed excessively, and the vibration absorbing effect by the spring can be maintained, so that it is possible to maintain a good riding comfort even in an uneven load state. Moreover, since a bendable tension wire is used for the force transmission mechanism, it can be easily mounted in a limited space around the car.

  By the way, a tension adjusting mechanism 113 for adjusting the tension generated in the tension wire 35 may be inserted in an intermediate portion of the tension wire 35. Hereinafter, an example of the tension adjusting mechanism 113 will be described with reference to FIG. The outer tube 34 of the tension wire 35 is fixed to the side surface of the car frame 1 with a tension wire terminal fixture 79 before the tension adjusting mechanism 113. A stud terminal 84 is connected to the end of the wire 33a, and the stud terminal 84 is connected to a rod 81 that is internally threaded by a screw. The rod 81 is provided with a handle 83 at an intermediate portion, and the lower end thereof is accommodated in the case 80 and is supported by the spring press 114 so as to be slidable in the axial direction with respect to the case 80. Inside the case 80, a spring 82 is assembled between the spring presser 114 and the upper surface of the case 80. The lower end of the case 80 is connected to the wire 33b, and is covered with another outer tube (not shown) by a tension wire terminal fixture (not shown) having the same configuration as described above, and is diagonally opposed to the car. It is connected to a lever (not shown) of a guide roller device (not shown) at a position.

  When the rod 81 is manually rotated by the handle 83 in the W direction, the rod 81 moves in the X direction with respect to the stud terminal 84. By the above operation, the distance between the wire 33a and the rod 81 is changed to adjust the amount of bending of the spring 82, that is, the elastic force of the spring. After the adjustment, the tension of the wires 33a and 33b is maintained at a predetermined value by the elastic force of the spring 82. When the tension exceeds a certain value, the spring 82 is further bent to increase the distance between the wire 33a and the wire 33b.

  In this way, by inserting the tension adjusting mechanism 113 into the intermediate portion of the tension wire 35, the rigidity of the tension wire 35 that is a force transmission path can be set to a predetermined value. When an excessive tension is applied to the tension wire 35, the spring is bent to relieve the tension. That is, it is possible to avoid a situation in which excessive tension acts on the wire.

  Next, another example of the tension adjusting mechanism is shown in FIG. The tension adjusting mechanism 64 is inserted in an intermediate portion of the tension wire 35 that connects the two guide roller devices 104 and 104 according to the fourth embodiment. The tension wire 35 is fixed to the car frame 1 by the outer tube end mounting portion 36a before the tension adjusting mechanism 64, and the wire 33a is connected to the rod 65a. The other end of the rod 65a is housed in the case 66, and is supported by a spring retainer 68a so as to be slidable in the axial direction. A seat 107a is provided at the end of the rod 65a. A spring 67a is assembled between the seat 107a and the spring retainer 68a. The spring retainer 68a and the case 66 are connected by a screw, and the stroke in the case 66 can be changed. The spring 67a is adjusted to be bent in advance, and the seat 107a is pressed against the bottom of the case 66 in a state where normal tension is applied to the wires 33a and 33b.

  A mechanism similar to the above is also housed in the right side of the partition inside the case 66. That is, the other wire 33b is connected to the rod 65b, and the rod 65b is supported by the spring retainer 68b so as to be slidable in the axial direction. Further, the spring retainer 68 b is provided in the sub case 69 so that the axial position can be adjusted, and the sub case 69 is provided so that the axial position can be adjusted with respect to the case 66. The seat 107 b slides inside the case 66 and interferes with the end surface of the sub case 69. A spring 67b having a rigidity coefficient lower than that of the spring 67a is incorporated between the seat 107b and the spring retainer 68b. The position of the spring 67b is adjusted so that the seat 107b is located between the bottom of the right chamber of the case 66 and the end surface of the subcase 69 as shown in FIG. 8 in a state where a predetermined tension is applied to the wire 33b. . The guide 70 is installed in the car frame 1, and the entire case 66 is supported so as to be slidable in the axial direction with respect to the car frame 1.

  FIG. 9 shows the relationship between displacement and tension in the tension adjusting mechanism 64 as shown in FIG. In FIG. 9, the amount of displacement δ from the reference mounting state of rod 65a and rod 65b (the state when normal tension is applied to wires 33a and 33b) is taken on the horizontal axis, and the tension generated by tension adjusting mechanism 64 is shown. Taking Γ on the vertical axis, the relationship between δ and Γ is schematically shown.

  As shown in FIG. 9, when normal tension is applied to the wires 33a and 33b, the rigid spring 67a is bent by applying an initial pressure in advance so that it does not shrink any more, but it is supported by the soft spring 67b. The moved rod 65b moves (section α shown in FIG. 9). In this state, the position of the seat 107b changes according to the tension of the wires 33a and 33b. That is, in the section α, even if the displacement amount of δ is large, the fluctuation of the tension Γ is kept small.

  On the other hand, when an excessive tension is applied to the wire, the soft spring 67b contracts, and the seat 107b eventually interferes with the end portion of the sub case 69. Then, the tension of the wire 33 b is directly transmitted to the case 66 through the sub case 69. When the tension further increases and becomes greater than the initial pressing force of the hard spring 67a, the spring 67a is bent and the rod 65a moves (section β shown in FIG. 9). That is, displacement occurs when the tension exceeds a certain value.

  In this way, even if the inner wire itself is stretched due to aging etc. with a soft spring, the slack can be automatically absorbed, and if excessive tension is applied to the wire, This time the stiff spring flexes and relaxes the tension. That is, it is possible to avoid a situation in which excessive tension acts on the wire. In the case where the slack of the wire is small and can be ignored, the same effect can be obtained even if a close tension spring that requires an initial tensile force is used instead of the tension adjusting mechanism.

  Next, a third embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the guide roller device portion is configured in the same manner as in the above embodiment, and a part of the tension wire 35 is replaced with the rod 100. The connecting portion between the rod 100 and the tension wire 35 is configured as shown in FIG. That is, the outer tube 34 of the tension wire 35 is fixed to the housing 102, and the wire 33 passes through the housing 102 and is connected to the stud terminal 98. The stud terminal 98 is processed with a forward male screw so that it can be screwed into the connector 99. The other end of the connector 99 is subjected to reverse female thread processing. The end portion of the rod 100 is subjected to reverse threading and is screwed into the connector 99. Thus, the wire 33 and the rod 100 are connected so that the relative distance between the wire 33 and the rod 100 can be adjusted by turning the connector 99.

  The rod 100 is supported by a bush 101 so as to be slidable in the vertical direction, and has a length from the vicinity of the ceiling of the car 7 to the vicinity of the bottom surface of the car 7. The lower end (not shown) of the rod 100 is configured in the same manner as described above and is connected to another wire (not shown). The other wire (not shown) forms a tension wire (not shown) covered with an outer tube (not shown) again, and is connected to a guide device (not shown) at an obliquely opposite position. Yes.

  Even if it does in this way, the effect similar to embodiment of Claim 4 will be acquired. That is, it is possible to suppress and restore the inclination of the car by generating a force that resists the external force caused by the offset load between the guide roller devices at the diagonally opposed positions. As a result, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort can be maintained even when an unbalanced load is applied. Further, since the force is transmitted with a highly rigid rod, in addition to the above effects, the influence of the wire elongation can be reduced.

  As shown in FIG. 11, the wire / rod connecting device 103 may be provided with a balance weight 111 or the like. Specifically, a pulley 110 is rotatably provided in the housing 102, and a weight wire 109 is hung on the pulley 110. One end of the weight wire 109 is connected to the upper end of the rod 100, and the other end is connected to a balance weight 111 having the same mass as the rod 100. The balance weight 111 is supported by a guide (not shown) so as to be movable in the vertical direction, and can move up and down in conjunction with the vertical movement of the rod 100.

  By doing in this way, the gravity by the balance weight 111 acts on the rod 100 via the weight wire 109, and the gravity for the mass of the rod 100 can be offset. Therefore, it is possible to prevent the tension of the cord-like body from changing due to the weight of the rod-like member, and to maintain the function. Note that the same effect can be obtained by providing a constant load spring having a constant elastic force regardless of the stroke, instead of providing a balance weight and compensating for gravity in the manner described above.

  In the embodiment of the present invention, the tension adjusting mechanisms 103 and 113 described in the second embodiment may be provided in the middle portion of the tension wire 35. As a result, the rigidity of the force transmission path can be made higher than when the wire is used alone, the elongation of the wire can be reduced, and when excessive tension is applied to the wire, the tension of the wire can be relaxed. it can.

  Next, a fourth embodiment of the present invention will be described with reference to FIG. The present embodiment is an example in which a mechanism different from that of the second embodiment is provided as an external force transmission mechanism. Hereinafter, a specific configuration of the present embodiment will be described.

  A sector gear 38 having the center of the lever swing shaft 20 as the center of the pitch circle is attached to the lower portion of the lever 21 in the present embodiment, and a gear 39 that meshes with the sector gear 38 is rotatable to the base 19 by the bearing 40. It is attached. The wire 41 is directly connected to the gear 39 and is rotatable inside the outer tube 42 to form a torque wire 43. The end of the outer tube 42 is connected to the base 19 by an outer tube end fitting 44. The other end of the torque wire 43 is connected to a guide roller device (not shown) of a mechanism similar to that shown in FIG.

  In the embodiment of the present invention having such a configuration, when an external force F is first generated to incline the car due to an unbalanced load, the external force F is transmitted to the lever 21, and the lever 21 is rotated around the lever swing shaft 20. Try to tilt in the G direction. Then, the sector gear 38 rotates in the J direction, and the gear 39 rotates in the K direction. The wire 41 connected to the gear 39 receives a twisting force in the L direction by the rotation of the gear 39. That is, the external force F is converted into a twisting force by the above-described action and transmitted to the other end of the torque wire 43. The other end (not shown) of the torque wire 43 is connected to a gear (not shown) of another device (not shown) having the same configuration as in FIG. 12, and the other guide roller (not shown) is connected to a guide rail (not shown). ) Is generated. Then, a moment that suppresses the inclination of the car is generated.

  Thereby, since the force which resists the external force resulting from an offset load generate | occur | produces between the guide roller apparatuses in the position which diagonally opposes a cage | basket, the inclination of a cage | basket | car can be suppressed. Further, since the torque wire is freely bendable, it can be easily assembled to the outside of the car frame. Therefore, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort can be maintained even when an unbalanced load is applied. When the torque wire 43 is little twisted and bent, the sector gear 38 and the gear 39 may be omitted, and the torque wire 43 may be directly connected to the lever 21 at the position of the lever swing shaft 20.

  The fifth embodiment of the present invention will be described below with reference to FIG. The present embodiment is an example in which a mechanism different from that of the second or fourth embodiment is provided as an external force transmission mechanism. Hereinafter, a specific configuration of the present embodiment will be described.

  A gear portion 74 having the center of the lever swing shaft 20 as the center of the pitch circle is attached to the lower end portion of the lever 73 in the present embodiment, and the gear portion 74 and the rack 75a mesh with each other. The rack 75 is slidably supported in the I direction by rack guides 76a and 76b. A force for sliding the rack 75 is transmitted to a guide roller device at an obliquely opposed position by a transmission mechanism (not shown) such as a wire.

  In the embodiment of the present invention having such a configuration, when a moment is applied to incline the car due to the offset load, the guide roller 23 receives the external force F, and the lever 73 moves around the lever swing shaft 20 in the F direction. Inclination causes the gear portion 74 to rotate in the H direction. Then, the rack 75 meshed with the gear portion 74 moves in the I direction. The rack 75 is transmitted by a transmission mechanism (not shown) to a roller guide (not shown) of the other guide roller device (not shown) at an obliquely opposite position, and a moment that suppresses the inclination of the car by the action already described. appear.

  Thereby, according to said structure, the effect similar to 2nd and 4th embodiment already demonstrated can be acquired. In other words, it is possible to suppress the inclination of the car by generating a force that resists the external force caused by the offset load in the guide roller device at an obliquely opposed position. Therefore, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort can be maintained even with an uneven load.

  In the embodiment of the present invention, the tension adjusting mechanisms 103 and 113 described in the second embodiment may be provided in an intermediate portion of the tension wire 35. Thereby, similarly to the second embodiment, the rigidity of the path for transmitting the force can be adjusted to an appropriate value, and a situation in which excessive tension acts on the force transmission mechanism can be avoided.

  Next, a sixth embodiment of the present invention will be described with reference to FIGS. In this embodiment, unlike the second to fifth embodiments in which the external force received by the guide roller of one guide roller device from the guide rail is transmitted via the lever of the other guide roller device, the guide rail The external force received from the lever is not transmitted as a moment by the lever but directly to the position of the rotation axis of the guide roller of the other guide roller device in the direction of pressing against the guide rail.

  FIG. 14 is an enlarged view of a guide roller device portion in the present embodiment. The guide roller 23 is rotatably attached to the lever 21, and the lever 21 is swingably attached to the base 19. The lever 21 is provided with a ball joint 45, and the ball joint 45 is connected to a rod 47a so as to be able to swing.

  The guide roller devices 50a, 50b, 50c, 50d are disposed in the car frame 1 as shown in FIG. The rod 47a is attached to the rear surface of the car frame 1, and is restrained in the axial direction and rotatably supported by rod supports 49, 49 provided with vibration-proof bushes. The lower end of the rod 47a is the same as in FIG. It is connected to another guide roller device 50b having the configuration. The upper right guide roller device 50c and the lower left guide roller device 50d are also configured in the same manner as described above, and are connected by a rod 47b.

  In the present embodiment having such a configuration, when an external force is applied to incline the car due to an unbalanced load, the guide roller 23 receives the external force F, and the lever 21 tends to incline around the lever swing shaft 20 in the G direction. And Then, the ball joint 45 is pushed in the M direction, and the rod 47 a is pushed through the ball joint 45. Since the rod 47 a is rotatably constrained by the rod support 49, it is twisted in the O direction within the rod support 49. In this way, the external force F from the guide rail 5 is converted into a twisting force of the rod 47a and a force pushing the rod support 49 in the lateral direction. The twisting force is transmitted below the rod 47a, and the rod 47a pushes the lever (not shown) of the other guide roller device 50b in the P direction. In this way, the guide roller device 50b generates a force that pushes a guide rail (not shown). Then, a moment that suppresses the inclination of the car is generated.

  Thereby, since the force which resists the external force resulting from an offset load generate | occur | produces in the guide roller apparatus in the position which opposes diagonally, the inclination of a cage | basket | car can be suppressed. Therefore, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort can be maintained even when an unbalanced load is applied.

  Further, the ball joints 45a and 45b and the joint rod 46 which are the connecting mechanism of the lever 21 and the rod 47a may be a pin-coupled link mechanism.

  Hereinafter, a seventh embodiment of the present invention will be described with reference to FIG. In the present embodiment, as in the sixth embodiment, the external force received from the guide rail is directly transmitted to the position of the rotation shaft of the guide roller of the other guide roller device.

  FIG. 16A is a diagram illustrating a configuration of the guide roller device according to the present embodiment. In the present embodiment, the piston 52 of the cylinder device 61 is swingably connected to the rear portion of the lever 87 in the vicinity of the guide roller rotating shaft 22 by a pin 51a. The other end of the cylinder 53 is swingably attached to the cylinder support 59 by a pin 51b. A pipe 60a is connected to the cylinder device 61, and an incompressible liquid 54 is sealed inside the cylinder device 61 and the pipe 60a.

  Specifically, as shown in FIG. 16B, the liquid pressure adjusting device 58 includes a piston 56 inside the cylinder base 63 and is slidably supported by a piston presser 57 so as to be movable in the vertical direction. Has been configured. A spring 55 is accommodated between the piston retainer 57 and the piston 56. The piston retainer 57 can be adjusted in the vertical direction with respect to the cylinder base 63, and also serves as an adjustment mechanism for the position of the spring 55. That is, when the height of the piston retainer 57 with respect to the cylinder base 63 is adjusted, the amount of bending of the spring 55 changes, the elastic force of the spring 55 changes, and the pressure of the incompressible liquid 54 is adjusted.

  A pipe 60a extending from the cylinder device 61 filled with the incompressible liquid 54 connects the cylinder base 63 to the inside of the liquid pressure adjusting device 58, and the pipe 60b has the same configuration as that shown in FIG. It is connected to a cylinder device (not shown) of another guide roller device (not shown).

  In the present embodiment having such a configuration, when a force to incline the car due to an offset load is applied, the guide roller 23 receives the force, and the lever 87 tries to incline around the lever swing shaft 20 in the G direction. . Then, the piston 52 of the cylinder device 61 is pushed in the Q direction. The pressure of the incompressible liquid 54 thus raised is transmitted to the cylinder device (not shown) of the other guide roller device (not shown) via the liquid pressure adjusting device 58 on the way through the pipes 61a and 61b. A force for pressing (not shown) against the guide rail (not shown) is generated. Then, a moment that suppresses the inclination of the car is generated in the same manner as described above.

  On the other hand, the initial pressure of the incompressible liquid 54 is adjusted by the liquid pressure adjusting device 58, and when the pressure of the incompressible liquid 54 becomes higher than a predetermined value, the spring 55 is further bent and the pressure is reduced. The rise is mitigated.

  Therefore, according to such a configuration, the guide roller device in the diagonally opposed position can generate a force that resists an external force caused by the offset load, thereby suppressing the inclination of the car. As a result, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort can be maintained even when an unbalanced load is applied.

  Hereinafter, an eighth embodiment of the present invention will be described with reference to FIG. In the center of FIG. 17, there is a schematic diagram of the car 7, and the guide devices attached to the upper, lower, left and right four places of the car 7 are enlarged and drawn around it. In the present embodiment, an external force acting on each guide roller provided in each of the guide roller devices 31a to 31l of the guide devices 63a, 63b, 63c, and 63d is transmitted between the guide roller devices as described below. It is configured to be.

  First, regarding the external force acting in the lateral direction of the car 7, the guide roller device 31a of the upper left guide device 63a, the guide roller device 31d (T1a and T1b) of the lower right guide device 63d, and the guide roller device 31b of the upper right guide device 63b The guide roller device 31c (T2a and T2b) of the lower left guide device 63c is connected so that the force can be transmitted to each other.

  Next, regarding the force acting in the longitudinal direction of the car 7, the front guide roller device 31e of the upper left guide device 63a and the rear guide roller device 31h (U1a and U1b) of the lower left guide device 63c provided on the left side of the car 7. The transmission is transmitted between the rear guide roller device 31f of the upper left guide device 63a and the front guide roller device 31g (U2a and U2b) of the lower left guide device 63c. On the other hand, on the right side of the car 7, the front guide roller device 31i of the upper right guide device 63b and the rear guide roller device 31l (V1a and V1b) of the lower right guide device 63d, the rear guide roller device 31j of the upper right guide device 63b and the right A front guide roller device 31k (V2a and V2b) of the lower guide device 63d is connected so as to transmit a force to each other.

  In the present embodiment having such a configuration, when a laterally offset load, that is, a moment in the direction of tilting around the x-axis, is generated, a reverse moment is generated around the x-axis to generate a lateral load on the car 7. Suppresses the inclination of the direction.

  On the other hand, even when a forward biased load, that is, a moment in the direction of tilting around the y-axis, is generated, the rear guide roller device 31f of the upper left guide device 63a and the front guide roller device 31g of the lower left guide device 63c are the same as described above. In combination (U2a and U2b), and the combination of the rear guide roller device 31j of the upper right guide device 63b and the front guide roller device 31k (V2a and V2b) of the lower right guide device 63d, respectively. The forward inclination of the car 7 is suppressed.

  Similarly, when a reverse bias load, that is, a moment in a negative direction around the y-axis, occurs, the front guide roller device 31e of the upper left guide device 63a and the rear guide roller device 31h of the lower left guide device 63c In combination with each other (U1a and U1b) and the combination of the front guide roller device 31i of the upper right guide device 63b and the rear guide roller device 31l (V1a and V1b) of the lower right guide device 63d, respectively, Suppresses the rearward inclination of the car 7.

  In addition, the device acts independently of the combined load in the lateral direction and the front-rear direction to generate moments that suppress the inclination of the car in the lateral direction and the front-rear direction.

  Therefore, according to the configuration of the present embodiment, a moment that antagonizes the unbalanced load in all directions of the car can be generated, and the inclination of the car is suppressed with respect to the unbalanced load in all directions of the car. be able to. As a result, the inclination of the lever can be reduced and the vibration absorbing effect by the spring can be maintained, so that a good riding comfort in the car can be maintained regardless of the biased load in any direction.

  In the second to seventh embodiments, the balance weight 28 in the first embodiment may be provided, or the spring 27 may be provided in the vicinity of the guide roller rotating shaft 22. In this way, when a force is applied to incline the car 7 due to an unbalanced load, a moment in the direction of canceling the car 7 is generated to suppress the inclination of the car 7, and this action suppresses the guide roller device. It can be prevented that the 30 springs 27 are excessively bent and vibrations are hardly absorbed. Further, external forces such as vibration and impact force are prevented from being transmitted from the guide rail 5 to the lever swing shaft 20, most of which is transmitted to the spring 27 side, and the vibration is absorbed by the spring 27. There is an effect.

  As a result, the inclination of the car can be suppressed even by an unbalanced load, and the pressing force of the spring can be kept at the same level as in the non-uneven load state, so that the effect of absorbing the vibration of the spring can be maintained, and the vibration from the guide rail The impact force can be absorbed by the spring to suppress the vibration from being transmitted directly to the car. Therefore, even if an unbalanced load is applied in any direction, and even when the ascending / descending speed increases and the vibration from the rail increases, a good riding comfort in the car can be maintained.

The side view which shows schematic structure of the guide roller apparatus in the guide apparatus concerning the 1st Embodiment of invention. Action | operation explanatory drawing of the guide roller apparatus in this Embodiment. Explanatory drawing of the principle of the guide roller device in the present embodiment The side view which shows schematic structure of the cage | basket part provided with the guide apparatus concerning the 2nd Embodiment of invention. The perspective view which shows schematic structure of the guide roller apparatus in the guide apparatus concerning this Embodiment. Explanatory drawing in the guide apparatus concerning this Embodiment. The perspective view explaining schematic structure of one example of the tension adjustment apparatus in this Embodiment. Sectional drawing explaining schematic structure of the other example of the tension adjustment apparatus in this Embodiment. The figure explaining the correlation of the displacement and tension | tensile_strength of the tension adjusting device shown in FIG. The perspective view explaining schematic structure of the wire / rod coupling device in this Embodiment. The perspective view explaining the schematic structure of the other example of the wire / rod coupling apparatus shown in FIG. The perspective view which shows schematic structure of the guide roller apparatus of the guide apparatus concerning the 4th Embodiment of invention. The perspective view which shows schematic structure of the guide roller apparatus of the guide apparatus concerning the 5th Embodiment of invention. The perspective view which shows schematic structure of the guide roller apparatus of the guide apparatus concerning the 6th Embodiment of invention. The perspective view which shows schematic structure of the whole cage | basket provided with the guide apparatus concerning this Embodiment. It is a figure explaining the structure of the guide apparatus concerning 7th Embodiment of this invention, The figure (A) is a perspective view which shows schematic structure of a guide roller apparatus, The figure (B) is the outline of a liquid pressure regulator. It is sectional drawing which shows a structure. The figure explaining the force transmission path | route between each guide roller apparatus of the guide apparatus concerning this Embodiment. The perspective view which shows schematic structure of the whole cage | basket | car provided with the conventional guide apparatus. The side view which shows schematic structure of the guide roller apparatus in the conventional guide apparatus. Action | operation explanatory drawing of the guide roller apparatus in the conventional guide apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Car frame 2 ... Car room 5a, 5b ... Guide rail 7 ... Car (ride car)
12 ... guide rollers 15, 27 ... spring (biasing mechanism)
20 ... Lever swing shaft (lever support)
21, 73, 87 ... lever (lever member)
22 ... Guide roller rotation shaft (roller support)
28 ... balance weights 30, 31b to 31l, 50, 72, 104 ... guide roller device 35 ... tension wire 37 ... wire terminal mounting portion 38 ... sector gear 39 ... gear 40 ... bearing 43 ... torque wire 45 ... ball joints 47a, 47b ... Rod 49 ... Rod support 54 ... Incompressible liquid 58 ... Liquid pressure adjusting device 61 ... Cylinder devices 63a, 63b, 63c, 63d ... Guide devices 64, 113 ... Tension adjusting mechanism 74 ... Gear portion 75 ... Rack 79a, 79b ... Tension Wire end fixing portion 103, 112 ... Wire / rod connecting device 109 ... Weight wire

Claims (12)

  Each guide roller device having a guide roller having a rotation axis perpendicular to the rectangular plane is provided at the upper and lower ends of the car cage frame at the position of the vertex of the rectangular plane, and the guide roller of each guide roller device is used as a guide rail. In the elevator that lifts and lowers the car along the guide rail by rolling contact, the guide roller device is supported swingably with respect to the car frame, and is spaced apart from the lever support portion to one end side. And a guide member of one guide roller device for each of the guide roller devices that are diagonal to each other in a rectangular plane perpendicular to the rotation axis of the guide roller device. The external force received by the guide rail from the lever support portion of the lever member of the other guide roller device Guiding device of elevator characterized by comprising an external force transmission mechanism for transmitting each other to the position of the side.   In the elevator that lifts and lowers the car along the guide rail by rolling the guide roller to the guide rail, each guide roller device includes a horizontal guide roller having a rotation axis in the front-rear direction of the car, Front and rear guide rollers having a rotation axis perpendicular to the rotation axis of the guide roller and positioned at the front and rear of the horizontal guide roller are provided, and the guide roller devices are respectively mounted on the upper and lower left and right ends of the car cage frame. The rotation axes are the same rectangular plane, the rotation axes of the front and rear guide rollers at the upper and lower left ends of the car frame are the same rectangular plane, and the rotation axes of the front and rear guide rollers at the upper and lower right ends of the car frame are the same rectangular plane. The guides are arranged such that the rotation axes are diagonal to each other in at least one of the rectangular planes perpendicular to the rotation axis of each guide roller. For each guide roller device having a roller, the external force that the guide roller of one guide roller device receives from the guide rail to the position on the other end side from the lever support portion of the lever member of the other guide roller device. An elevator guide device comprising a transmission mechanism.   The external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting a position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The elevator guide device according to claim 1 or 2.   The external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting the position of the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The elevator guide apparatus according to claim 1 or 2, wherein an elastic mechanism is provided in the middle of the push-pull cable to be elastically deformed when the tension of the cable becomes a predetermined value or more.   The external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting a position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The elevator guide apparatus according to claim 1 or 2, wherein both ends of the cable are constituted by tension wires, and intermediate portions thereof are constituted by rod-like members.   The external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting a position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The cable is characterized in that both ends thereof are constituted by tension wires, the middle portion thereof is constituted by a rod-shaped member, and further a suspension mechanism is provided for suspending with a force that cancels the weight of the rod-shaped member. The elevator guide device according to claim 1 or 2.   The external force transmission mechanism is configured to be push-pullable in a direction in which the lever member swings by connecting a position on the other end side from the lever support portion of the lever member of each guide roller device with a push-pull cable. The cable has a tension wire at both ends and a rod-like member at the middle, and an elastic mechanism that elastically deforms when the tension wire tension exceeds a predetermined value. The elevator guide device according to claim 1, wherein the elevator guide device is provided in the elevator.   The external force transmission mechanism is provided at a position on the other end side from the lever support portion in the lever member of each guide roller device, and converts each of the swinging motion and the twisting motion of the lever member, and each guide 3. A wire member capable of transmitting a twisting torque for connecting a motion conversion mechanism of the roller device is provided, and an external force received by the guide roller from the guide rail is transmitted by the twisting torque. Elevator guide device.   The external force transmission mechanism includes a gear member provided on the lever member of each guide roller device at a position on the other end side from the lever support portion, and a rod-shaped member having a rack formed on both ends thereof. The elevator guide device according to claim 1 or 2, wherein the guide roller devices are connected by meshing the racks of the rod-shaped members.   The elevator guide apparatus according to claim 9, wherein an elastic mechanism that elastically deforms when a tension of the rod-shaped member of the external force transmission mechanism exceeds a predetermined value is provided in an intermediate portion of the rod-shaped member.   A guide roller device provided with guide roller devices at upper and lower ends of a car frame of a car, and the guide roller device ascending and descending the car along the guide rail by rolling the guide roller of the guide roller device to the guide rail. And a lever member rotatably supported with respect to the car frame, and rotatably supporting the guide roller at a position spaced from the lever support part to one end side, and within the same rectangular plane of the car frame In the guide roller devices that are diagonal to each other, the external force that the roller support portion of the lever member of one guide roller device receives from the guide rail via the guide roller to the roller support portion of the lever member of the other guide roller device A guide device for an elevator comprising an external force transmission mechanism for mutual transmission.   The external force transmission mechanism includes a piston cylinder device that interlocks with the movement of the roller support portion of the lever member of the guide roller device, a pipe that connects each piston cylinder device, the piston cylinder device and a liquid sealed in the pipe, The elevator guide apparatus according to claim 11, further comprising a pressure adjusting mechanism that is provided in the middle of the pipe and adjusts a liquid pressure inside the pipe.

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