JP2012180154A - Elevator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an elevator including a hoist having an increased friction force between main ropes and a drive sheave, without changing outer dimensions.SOLUTION: The elevator 1 includes a plurality of main ropes 6 hanging a car 4 and a counter weight 5, and the drive sheave 31 with grooves 311 on which the main ropes 6 are wound, and drives the car 4 and the counter weight 5 by the friction force generated between the main ropes 6 and the grooves 311 in a well-bucket manner. The elevator 1 is provided with friction members 32. The friction members 32 are arranged on both outside of edges 311a of each of the grooves 311 at a distance (e) smaller than the diameter (d) of each of the main ropes 6 which are wound around the grooves 311 of the drive sheave 31, so that the main ropes 6 is held.

Description

  Embodiments of the present invention relate to an elevator including a drive sheave that drives a rope that suspends a riding rod and a counterweight in a slidable manner by friction engagement.

  In an elevator that suspends a carriage and a counterweight with a main rope in a slidable manner, a drive sheave assembled to the hoisting machine holds the main rope by frictional force. The frictional force between the main rope and the drive sheave is determined by the strength of the main rope and the drive sheave, the tension applied to the main rope, the layout of the hoist, the groove shape of the drive sheave, the contact length or winding angle, etc. . The weight of the counterweight is set so as to be balanced with the total weight obtained by adding the loading weight half of the maximum loading load to the weight of the riding rod.

  In order to reduce the load applied to the hoisting machine, it is required to reduce the weight of the riding board. However, it is not possible to reduce the weight to a certain extent from the viewpoint of increasing the maximum load capacity and obtaining the necessary driving frictional force.

  In order to increase the frictional force between the main rope and the drive sheave, a so-called “full wrap” method is used to wind the main rope further away from the drive sheave and the sheave. There is known an elevator equipped with a hoisting machine. That is, in this elevator, the hoisting machine obtains the necessary frictional force by increasing the winding angle of the main rope with respect to the drive sheave.

  In addition, there is an elevator that has a special mechanism that does not depend on the tension applied to the main rope or the groove shape of the drive sheave in order to increase the frictional force generated between the main rope and the sheave. This elevator includes a mechanism for pressing the main rope against the sheave with a belt from the outer periphery of the sheave in a range where the main rope is wound. This mechanism increases the frictional force between the main rope and the sheave.

Japanese Patent Laid-Open No. 2008-50071

Lubomir Janovsky, “Elevator Mechanical Design” (USA), 3rd edition, Elevator World, 1999, p74-83.

  In the case of an elevator that secures a frictional force between the main rope and the drive sheave by full hooking, the size of the hoisting machine including the drive sheave and the deflecting sheave increases in the direction along the rotation axis. Further, in the case of an elevator having a mechanism for pressing the main rope against the sheave by the belt, the apparatus becomes larger by the amount of the belt and the related parts arranged outside the sheave.

  Thus, the hoisting machine which fully hangs the main rope and the hoisting machine additionally provided with a mechanism for pressing the belt increase the size of the hoisting machine. For elevators that do not have a machine room for installing the hoisting machine by placing the hoisting machine at the upper part of the hoistway, the size of the hoisting machine becomes larger because the layout inside the hoistway can be reviewed and the hoistway It is necessary to change the design such as expanding When renewing an existing elevator, a mechanism that requires the hoistway to be expanded cannot be adopted.

  Therefore, the present invention provides an elevator provided with a hoisting machine in which the frictional force between the main rope and the drive sheave is increased without changing the external dimensions.

  The elevator of one embodiment is provided with a plurality of main ropes, a drive sheave, and a friction member. The main rope suspends the riding rod and the counterweight. The drive sheave has a groove around which the main rope is wound. The friction members are arranged on both outer sides of the edge of the groove at an interval narrower than the diameter of the main rope, and sandwich the main rope.

  Alternatively, an elevator according to an embodiment includes a plurality of main ropes for suspending the riding rod and the counterweight, and a drive sheave in which a groove around which these main ropes are wound is formed, between the main rope and the groove. The riding force and the counterweight are driven in a sliding manner by the generated frictional force. The elevator includes a friction member. The friction members are arranged on both outer sides of the edge of the groove at intervals smaller than the diameter of the main rope wound around the groove of the drive sheave, and sandwich the main rope.

The perspective view which shows the elevator of 1st Embodiment. The perspective view which shows the drive sheave of the elevator shown in FIG. Sectional drawing of the groove | channel of the drive sheave shown in FIG. The figure of the frictional force of the main rope which acts on the groove | channel of the drive sheave shown in FIG. The figure of the tension | tensile_strength of the main rope which acts on the drive sheave shown in FIG. Sectional drawing which shows the groove | channel of the drive sheave of 2nd Embodiment. Sectional drawing which shows the groove | channel of the drive sheave of 3rd Embodiment. Sectional drawing which shows the groove | channel of the drive sheave of 4th Embodiment. Sectional drawing which shows the groove | channel of the drive sheave of 5th Embodiment.

  The elevator 1 of 1st Embodiment is demonstrated with reference to FIGS. 1-5. In the elevator 1 shown in FIG. 1, a hoisting machine 3 is disposed on an upper part of a hoistway 2. The hoisting machine 3 includes a drive sheave 31 on the output shaft. The elevator 1 suspends a riding rod 4 and a counterweight 5 moving along the respective guide rails 41 and 51 into a hoistway 2 in a lifting manner by a plurality of main ropes 6 wound around the drive sheave 31. ing. The drive sheave 31 has a groove 311 around which the plurality of main ropes 6 are wound. In the elevator 1, the plurality of main ropes 6 are hung on the carriage 4, the counterweight 5, and the drive sheave 31 by 2: 1 (Two to One) roping. The hoist 4 and the counterweight 5 are driven by the hoisting machine 3 by the frictional force generated between the main rope 6 and the groove 311 of the drive sheave 31.

  The drive sheave 31 includes a friction member 32 as shown in FIG. As shown in the left part of FIG. 3, the friction member 32 is arranged on both outer sides of the edge 311 a of the groove 311 at a distance e narrower than the diameter d of the main rope 6 wound around the groove 311 of the drive sheave 31. ing. When the main rope 6 is hung over the groove 311 of the drive sheave 31 as in the central part or the right part in FIG. 3, the friction member 32 is flattened and sandwiches the main rope 6. As shown in FIG. 2, the friction member 32 is formed in a continuous annular shape that is attached to the outer periphery of the drive sheave 31. In the first embodiment, the friction members 32 arranged adjacent to each other at the edge 311a of each groove 311 are formed in a continuous manner.

  The friction member 32 is a synthetic resin having elasticity and excellent wear resistance, and is adhered to the outer peripheral surface of the drive sheave 31. As shown in FIG. 3, a holding fitting 33 is wound around the outer periphery of the friction member 32 so that the friction member 32 does not fall off, and is fixed with a screw 34 that penetrates the drive sheave 31 in the radial direction. As the synthetic resin forming the friction member 32, for example, polyurethane having a durometer D (Shore D) hardness of about 50 to 67 is employed.

  The groove 311 of the drive sheave 31 does not contact the main rope 6 at the center portion of the support portion 312 and the support portion 312 formed along a curved surface that fits the outer shape of the main rope 6 to be wound, that is, the so-called “toroidal surface”. And an undercut portion 313 that is recessed. The support portion 312 is formed so that the center of the main rope 6 is disposed outside the groove 311. Therefore, the friction member 32 sandwiches the diameter portion of the main rope 6 in parallel with the rotational axis of the drive sheave 31. The friction member 32 generates a pressing force corresponding to the flattened amount. As a result, a holding force along the circumferential direction of the drive sheave 31 is generated in proportion to the dynamic friction coefficient between the main rope 6 and the friction member 32. This holding force acts on the main rope 6 separately from the frictional force generated between the main rope 6 and the support portion 312 of the groove 311 of the drive sheave 31.

  Here, a force acting on one main rope 6 wound around the drive sheave 31 will be described with reference to FIGS. 4 and 5. As shown in FIG. 4, the angle between the outer edge of the support portion 312, that is, the edge 311 a of the groove 311 with respect to the center of the main rope 6 in the state where the main rope 6 is fitted to each groove 311. The angle between the inner edges of the support portion 312 formed by δ and the undercut portion 313 is referred to as an undercut angle β. In the first embodiment, optimum values are selected in the range of the groove angle δ of 125 to 150 ° and the undercut angle β of 70 to 105 °.

Therefore, as shown in FIG. 5, the larger one of the diameter D of the drive sheave 31 and the tension acting in the direction in which the carriage 4 is suspended and the tension acting in the direction in which the counterweight 5 is suspended. T ₁ , the smaller tension T ₂ , the angle of the range in which the main rope 6 is wound around the drive sheave 31, the winding angle θ, and the minute portion of the wound main rope 6 with respect to the center of the drive sheave 31 The winding angle dθ is a force dN generated toward the center S of the drive sheave 31 at a minute portion of the main rope 6 around the winding angle dθ due to the action of tension.

Assuming that the tension T _(θ) acting on an arbitrary position within the range of the winding angle θ and the tension T _(θ) + dT applied to the arbitrary position in the opposite direction of the minute portion, the arbitrary position of the main rope 6 The force dN generated in the minute portion is expressed by the following equation (1).

Here, an apparent dynamic friction coefficient μ between the main rope 6 and the drive sheave 31 is set. When the friction member 32 is not provided, the change amount dT of the tension T _{(θ) with} respect to the winding angle dθ is an apparent friction force dF = μ · dN between the main rope 6 and the groove 311 of the drive sheave 31. Since they are balanced, the following equation (2) is obtained.

When the equation (2) is solved, the equation showing the balance of tension due to the friction shown in the equation (3) is obtained.

The apparent dynamic friction coefficient μ is determined by the cross-sectional shape of the groove 311. In the case of the groove 311 having the support portion 312 and the undercut portion 313 shown in FIG. 4, as shown in FIGS. 4 and 5, the diameter D of the drive sheave 31, the diameter d of the main rope 6, and the winding of the main rope 6 When the angle θ is an opening angle φ up to an arbitrary contact position between the main rope 6 and the drive sheave 31 with respect to the center of the main rope 6, the surface of the main rope 6 and the groove 311 The contact pressure p _(φ) generated between the surface and the surface has a relationship shown in the equation (4).

It has been found that the contact pressure p (φ) can be replaced as shown in the following equation (5).

Substituting this equation (5) into equation (4), from equation (1), P becomes equation (6).

Further, when Expression (6) is substituted into Expression (5), Expression (7) is obtained.

By using p (φ) according to this equation (7), the frictional force dF generated at the winding angle dθ is obtained by using the actual dynamic friction coefficient μ ′ due to the material between the surface of the main rope 6 and the surface of the groove 311. It can be expressed as equation (8).

Substituting equation (7) into equation (8) and rearranging results in equation (9).

From the equations (9) and (2), the apparent dynamic friction coefficient μ of the groove 311 having the undercut portion 313 is obtained. At this time, if the groove coefficient κ is defined as a constant determined by the shape of the groove, Expression (10) is obtained.

In the case of the groove 311 having the undercut portion 313, the maximum value P _UCmax of the contact pressure P _(φ) with respect to the support portion 312 is φ = β / 2 in the equation (7), and the support portion 312 and the undercut portion 313 Is generated at the edge portion of the boundary of the above, and is shown in Expression (11).

If the Nokago 4 no live load is, the state since towards the counterweight 5 is heavy, which is a tension T ₂ that acts by the tension T _1, Nokago 4 exerted by the counterweight 5, Nokago 4 is increased From the above, the respective tensions when the speed decreases at the deceleration α are obtained. Mass _{M CW} counterweight 5 is equal to the mass _{M CAR} of Nokago 4 half of the rated load weight _{M L} was loaded, the tension _{T 1} and the tension _{T 2} are of the formula (12), formula (13) become that way.

As the mass M _{CAR of the} car 4 decreases, the traction ratio T ₁ / T ₂ increases. Since the limit of the driving frictional force is determined by the right side of the equation (3), the weight limit when the riding rod 4 is lightened is the groove coefficient κ derived from the shape of the groove 311 of the driving sheave 31 and the winding of the main rope 6. It can be seen that it depends on the angle θ.

In the case of the elevator 1 according to the first embodiment, a friction member 32 is provided outside the drive sheave 31, and the friction member 32 sandwiches the main rope 6. Contact pressure p _h to the friction member 32 sandwich the main rope 6, as shown in FIG. 4, acts along a direction parallel to the rotational axis of the drive sheave 31, drive sheave 31 with respect to the center of the main rope 6 It acts symmetrically in the radial direction. Therefore, the frictional force dF ′ generated by the frictional member 32 is added without affecting the frictional force dF obtained by the equation (9).

Therefore, in the case of the first embodiment, the change amount dT of the tension T _{(θ) with} respect to the wrapping angle dθ is the apparent friction force dF between the main rope 6 and the drive sheave 31 and the main rope 6 and the friction member 32. Is balanced with the frictional force dF ′. The coefficient of dynamic friction μ _h between the main rope 6 and the friction member 32, the distance from the rotation center of the drive sheave 31 to the center of the contact range of the main rope 6 and the friction member 32, that is, the drive sheave from the rotation center of the drive sheave 31. Assuming that the radius of rotation R is about the center of the main rope 6 wound around 31, the formula (14) is obtained.

When this equation (14) is solved, the relationship between the tensions T ₁ and T ₂ applied to the main rope 6 suspended from the drive sheave 31 and the winding angle θ is expressed by equation (15).

  In Expression (15), exp {μθ}> 1. Compared with the equation (3) in which the element of the friction member 32 is not included, it can be seen that the driving frictional force increased by the friction member 32 is the second term of the equation (15).

  The undercut angle β of the groove 311 of the drive sheave 31 is in the range of 70 to 105 ° and the groove angle δ is in the range of 125 to 150 °, and the winding angle θ of the main rope 6 is a so-called “half wrap”. . When the actual dynamic friction coefficient μ ′ is set to 0.1, the traction ratio obtained from the equation (3) is 1.67 to 1.97. From the equations (12) and (13), when the friction member 32 is not provided, if the rated load weight of the riding rod 4 is 1000 kg, the mass of the riding rod 4 needs to be about 1000 kg. On the other hand, in the case of the present embodiment, a sufficient driving friction force can be obtained even if the mass of the riding rod 4 is reduced by the amount corresponding to the second term of Expression (15).

  As described above, by providing the friction member 32, an additional frictional force can be obtained without changing the outer dimensions of the hoisting machine. Therefore, it can be easily introduced not only into a new elevator but also into an existing elevator. If applied to the drive sheave 31 of an existing elevator, the weight of the carriage 4 can be reduced to reduce the load applied to the hoisting machine 3, and the weight of the counterweight 5 can be added to increase the rated load weight. It can also be enlarged.

  In the first embodiment, the main rope 6 is wound around each sheave of the hoisting machine 3, the riding rod 4, and the counterweight 5 by 2: 1 roping. The roping of the main rope 6 of the elevator is not limited to the 2: 1 roping shown in FIG. Therefore, the first embodiment is also applied to an elevator in which the hoisting machine 3 is disposed in a pit at the bottom of the hoistway 2. Furthermore, the first embodiment is also applied to an elevator by 1: 1 roping.

  Hereinafter, elevators 1 according to second to fifth embodiments will be described with reference to the drawings. In each embodiment, the shape of the groove 311 of the drive sheave 31 of the hoisting machine 3 and the friction members 32 mounted on both sides of each groove 311 are different from each other. Otherwise, the elevator 1 of the first embodiment. Is the same. Configurations having the same functions as those of the elevator 1 of the first embodiment are denoted by the same reference numerals in the drawings of the respective embodiments. Moreover, even if it is a structure which is not illustrated in each embodiment, the same code | symbol is attached | subjected to the structure which has the same function. In the detailed description, the description of the first embodiment and the corresponding drawings are referred to, and the description is omitted here.

  The groove 311 and the friction member 32 of the drive sheave 31 in the elevator 1 of the second embodiment will be described with reference to FIG. As in the first embodiment, the groove 311 includes a support portion 312 and an undercut portion 313 as shown in FIG. The friction member 32 is disposed outside the edge 311 a of the groove 311. And the friction member 32 is comprised integrally by what is arrange | positioned between the adjacent main ropes 6.

Friction member 32 includes a pad portion 321 made of synthetic resin in a range in contact with the main rope 6, and an elastic body 322 for generating the pressing force p _h pressing the pad portion 321 to the main ropes 6. The pad portion 321 is made of polyurethane similar to the friction member 32 of the first embodiment, and is bonded to the elastic body 322. The elastic body 322 is formed of spring steel.

  Further, the elastic body 322 is attached to the drive sheave 31 with a spacer 35 and a shim 36 interposed therebetween as shown in FIG. By replacing the spacers 35 and shims 36 with different thicknesses, the position of the pad portion 321 contacting the main rope 6 is adjusted around the diameter portion of the main rope 6 parallel to the rotation axis of the drive sheave 31.

  In the second embodiment configured as described above, the function is divided into the pad portion 321 having a high friction coefficient for the friction member 32 and the elastic body 322 for pressing the pad portion 321 against the main rope 6, thereby stabilizing the friction member 32. Performance. Since the shape of the groove 311 of the drive sheave 31 is the same as that of the drive sheave 31 of the first embodiment, the frictional force generated between the groove 311 and the main rope 6 is as described in the first embodiment. is there. Further, the frictional force generated by the frictional member 32 is additionally generated irrespective of the frictional force generated between the groove 311 and the main rope 6 as in the first embodiment. The weight of the riding rod 4 can be reduced or the rated load weight can be increased by the holding force obtained by the frictional force generated by the friction member 32.

  The groove 311 and the friction member 32 of the drive sheave 31 in the elevator 1 of the third embodiment will be described with reference to FIG. The groove 311 of the drive sheave 31 shown in FIG. 7 is a so-called V groove provided with support portions 312 formed along two conical surfaces that contact the main rope 6 from two directions. Similar to the second embodiment, the friction member 32 includes a pad portion 321 and an elastic body 322.

  That is, in the third embodiment, as shown in FIG. 7, the drive sheave 31 is configured by adopting the friction member 32 of the second embodiment in the drive sheave 31 having the V groove. Therefore, in the third embodiment, as in the first embodiment, the frictional force is additionally applied between the friction member 32 and the main rope 6 regardless of the frictional force between the groove 311 and the main rope 6. Occurs. By providing this drive sheave 31, the same effect as in the first and second embodiments is obtained.

The groove coefficient κ _V of the V groove corresponding to the groove coefficient κ shown in Expression (10) of the first embodiment is expressed by Expression (16), where the angle formed by the support portion 312 is the groove angle γ. .

The groove 311 of the third embodiment is the same as the groove 311 of the first embodiment in which the undercut angle β is 70 to 105 ° and the groove angle δ is 125 to 150 ° if the groove angle γ is 60 ° or less. Equivalent driving friction force can be obtained. Considering the practical life of each member, the groove angle γ of the V groove is preferably 35 ° or more. Further, the maximum value p _Vmax of the contact pressure p _(φ) with respect to the support portion 312 is a position where the main rope 6 is in contact with the support portion 312 as shown in FIG. 7, that is, a position where φ = (π−γ) / 2. Occurs.

  The groove 311 and the friction member 32 of the drive sheave 31 in the elevator 1 according to the fourth embodiment will be described with reference to FIG. The groove 311 of the drive sheave 31 shown in FIG. 8 has a support portion 312 formed along a curved surface that conforms to the outer shape of the main rope, but has the undercut portion 313 of the first embodiment. There is no so-called U-groove. That is, in the fourth embodiment, the drive sheave 31 is configured by adopting the friction member 32 of the second embodiment with respect to the U groove.

  Also in the fourth embodiment, similarly to the second embodiment, a frictional force is additionally generated between the friction member 32 and the main rope 6 regardless of the frictional force between the groove 311 and the main rope 6. To do. By providing this drive sheave 31, the same effect as the first to third embodiments can be obtained.

The groove coefficient κ _U of the U groove corresponding to the groove coefficient κ shown in Expression (10) of the first embodiment is an angle formed by the outer edge 311 a of the support portion 312 with respect to the center of the main rope 6. Assuming that the groove angle δ is given by equation (17).

The maximum value p _Umax of the contact pressure p _(φ) with respect to the support portion 312 is generated at the bottom of the groove 311 as shown in FIG.

  Note that the groove 311 of the drive sheave 31 of the fourth embodiment is a U-groove, and the contact range with the main rope 6 is wider than the groove 311 of the drive sheave 31 of the first embodiment. Therefore, the contact pressure per unit area generated between the main rope 6 and the groove 311 of the drive sheave 31 of the first embodiment is reduced. This is clear when the equation (11) of the first embodiment is compared with the equation (18) of the fourth embodiment.

  Even in such a case, the driving friction force between the groove 311 of the driving sheave 31 and the main rope 6 is added by the amount of the friction member 32 provided, so that the mass of the riding rod 4 can be reduced.

The groove 311 and the friction member 32 of the drive sheave 31 in the elevator 1 according to the fifth embodiment will be described with reference to FIG. As in the first embodiment, the groove 311 includes a support portion 312 and an undercut portion 313 as shown in FIG. The friction member 32 is disposed outside the edge 311 a of the groove 311. In the fifth embodiment, the friction members 32 arranged between the adjacent main ropes 6 are provided separately. Each friction member 32 is pressed by an annular holding metal fitting 33 attached from the outer peripheral side of the drive sheave 31. Insert the shim 36 between the outer peripheral surface and the holding metal fitting 33 of the drive sheave 31, by adjusting the tightening allowance of the friction member 32, the pressing force p _h of the friction member 32 relative to the main rope 6 is adjusted.

  As described above, according to the elevator 1 of the first to fifth embodiments, the drive sheave 31 includes the friction member 32 that sandwiches the main rope 6 to be wound in a direction parallel to the rotation axis of the drive sheave. . Since the driving frictional force is added by the friction member 32 without changing the outer dimensions of the hoisting machine 3, the mass of the riding rod 4 can be reduced. While the load applied to the hoisting machine 3 is reduced, the energy required for accelerating or decelerating the riding rod 4 is reduced. Therefore, an environment-friendly elevator with little energy loss can be provided.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

  DESCRIPTION OF SYMBOLS 1 ... Elevator, 4 ... Saddle, 5 ... Counterweight, 6 ... Main rope, 31 ... Drive sheave, 311 ... Groove, 311a ... Edge, 312 ... Support part, 313 ... Undercut part, 32 ... Friction member, 321 ... pad part, 322 ... elastic body.

Claims (8)

A plurality of main ropes for suspending the carriage and counterweight;
A drive sheave formed with a groove around which the main rope is wound;
An elevator comprising: a friction member disposed on both outer sides of the edge of the groove at an interval narrower than a diameter of the main rope and sandwiching the main rope. The elevator according to claim 1, wherein the friction member disposed between the adjacent main ropes is integrally formed. The said groove | channel is provided with the support part formed along the curved surface which adapts the external shape of the said main rope, and the undercut part which does not contact | connect the said main rope in the center part of the said support part. The elevator described in 1. The elevator according to claim 1, wherein the groove includes a support portion formed so as to come into contact with the main rope from two directions at two conical surfaces. The elevator according to claim 1, wherein the groove includes a support portion formed along a curved surface that conforms to an outer shape of the main rope. The elevator according to claim 1, wherein the friction member is made of a synthetic resin having excellent wear resistance. 2. The elevator according to claim 1, wherein the friction member generates a holding force that sandwiches the main rope in parallel with a rotation shaft of the drive sheave. 2. The friction member includes a pad portion made of a synthetic resin in a range in contact with the main rope, and an elastic body that generates a pressing force that presses the pad portion against the main rope. The elevator described in 1.

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