CN1843881A - Elevator without machine room - Google Patents

Abstract

There provides a machine-room-less elevator. In the machine-room-less elevator, comprising at least a car 1, a balance weight 2, a rope 6, a drive sheave 4, a motor 3 driving the drive sheave 4, and a deflection pulleys 5 are housed in the hoistway. A plurality of motors 3A, 3B are disposed on both sides of the drive sheave 4 to drive the drive sheave 4, and the rope 6 is wound so that one end of the rope 6 is disposed to the car 1 and the other end thereof is disposed to the balance weight 2 through the drive sheave 4 and the deflection pulleys 5 in a one-to-one roping manner. Thus, a machine-room-less elevator with reduced space in height of a hoistway in a top part of a car and with increased speed.

Description

Elevator without machine room

technical field

The invention relates to a machine-room-less elevator in which a driving device is arranged in an elevator passage.

Background technique

As a conventional elevator without a machine room, a traction sheave type elevator has been disclosed, such as the invention disclosed in Japanese Patent Laid-Open No. Hei 7-10434 of Patent Document 1, which is characterized in that the machine room is eliminated to reduce the occupied space. Space. In addition, for example, the invention disclosed in Japanese Patent Application Laid-Open No. 2002-80178 of Patent Document 2 uses a thin motor with a small axial dimension to reduce the planar area of the lift passage. Furthermore, for example, the invention disclosed in Japanese Patent Application Laid-Open No. 2004-142853 of Patent Document 3 suspends the elevator car in a 1-to-1 winding manner and suspends the balance counterweight in a 2-to-1 winding manner. , thus setting the lifting stroke of the balance counterweight to be shorter than that of the elevator car to ensure maintenance space.

Patent Document 1: Japanese Patent Application Laid-Open No. 7-10434

Patent Document 2: Japanese Invention Patent Laid-Open No. 2002-80178

Patent Document 3: Japanese Patent Application Laid-Open No. 2004-142853

However, in the structure of Patent Document 1, since the 2-to-1 winding method is adopted, there is no problem in the low-speed range, but in the high-speed range, noise and vibration are likely to occur in the elevator car, so it is difficult to achieve high speed. In the structure of Patent Document 2, since a thin motor with a small axial dimension is used, the planar area of the lifting passage can be effectively reduced, but since the radial width of the thin motor increases, it is difficult to save space in the height direction . In addition, in the structure of Patent Document 2, although a 1-to-1 winding structure is adopted, the structure in which the sling is wound around the driving sheave (about 360 degrees) is adopted. If multiple slings need to be erected, Adoption of the above-mentioned structure causes twisting of the sling, which shortens the life of the sling, and requires special measures different from the usual shape in order to ensure adhesion to the sheave and the like. Furthermore, in the structure of Patent Document 3, although the driving sheave and the diverting pulley are set on the upper part of the lifting passage at the same height, and a fully wound (full-enclosed) structure is adopted, but because the balance weight side adopts The 2-to-1 winding structure increases the length of the sling and tends to sway due to mechanical resonance, making it difficult to increase the speed. In addition, in the structure of Patent Document 3, since the sheave is arranged at the corner of the hoistway and driven by a single motor, it is difficult to realize efficient use of space and high speed at the same time.

Contents of the invention

An object of the present invention is to provide a machine room-less elevator capable of saving the space at the top of the elevator car in the height direction of the hoistway and at the same time achieving high speed.

In the present invention, in order to achieve the above object, a machine room-less elevator is provided. In the machine room-less elevator, at least an elevator car, a counterweight, a sling, a driving sheave, a For driving the motor and the diverting pulley of the driving sheave, wherein a plurality of motors for driving the driving sheave are arranged on both sides of the driving sheave, and a 1-to-1 ratio is adopted via the driving sheave and the diverting pulley. In the winding method, one end of the sling is wound on the elevator car, and the other end is wound on the balance counterweight.

According to the elevator without a machine room of the present invention, not only the space on the top of the elevator car of the elevator without a machine room can be saved, but also the speed of the elevator can be increased at the same time.

(effect of invention)

According to the elevator without a machine room of the present invention, not only the space on the top of the elevator car of the elevator without a machine room can be saved, but also the speed of the elevator can be increased at the same time.

Description of drawings

Fig. 1 is an overall configuration diagram of an elevator without a machine room as an embodiment of the present invention.

Fig. 2 is a top view of the counterweight of Fig. 1 when it is arranged behind the elevator car.

Fig. 3 is a top view of the counterweight of Fig. 1 when it is arranged on the side of the elevator car.

Fig. 4 is a side view showing the relationship between the diameter of the driving sheave and the diameter of the wire rope in Fig. 1 .

Fig. 5 is an enlarged view of the drive sheave portion of Fig. 1 .

FIG. 6 is a configuration diagram showing an embodiment of a power conversion device.

FIG. 7 is a block diagram of part of the control circuit of FIG. 6. FIG.

FIG. 8 is a test chart showing a measured torque waveform when the phase difference of the magnetic pole positions is 0 degrees.

FIG. 9 is a test chart showing a measured torque waveform when the phase difference of the magnetic pole positions is 30 degrees.

In the figure: 1-elevator car, 2-balance counterweight, 3A, 3B-motor, 4-driving sheave, 5-turning pulley, 6-sling, 7-guide rail for elevator car, 8-for balance counterweight Guide rail, 9A, 9B, 9C, 9D-beam, 10-elevator passage, 11-elevator car pulley, 12-power supply, 13-power conversion device, 14-control circuit, 15-speed command part, 16-speed control system , 17a, 17b-gain part, 18a, 18b-speed control system, 19a, 19b-PWM modulation part.

Detailed ways

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

Fig. 1 is an overall structural diagram of an elevator without a machine room as an embodiment of the present invention, Fig. 2 is a top view of the counterweight of Fig. 1 when it is arranged behind the elevator car, and Fig. 3 is a view of the counterweight of Fig. The top view of the side of the car, Fig. 4 is a side view showing the relationship between the diameter of the driving sheave and the diameter of the sling, Fig. 5 is an enlarged view of the part of the driving sheave in Fig. 1, Fig. 6 is a diagram showing an embodiment of the power conversion device Structural diagram, Fig. 7 is a block diagram of the control circuit part in Fig. 6, Fig. 8 is a test diagram showing the torque measured waveform when the phase difference of the magnetic pole position is 0 degrees, Fig. 9 is a test diagram showing the phase difference of the magnetic pole position at 30 degrees Test chart of torque measured waveform.

In Fig. 1, 10 represents the hoistway, in the inside of this hoistway 10, at least include the elevator car 1 that lifts along the elevator car guide rail 7, the balance weight 2 that moves up and down along the balance counterweight with the guide rail 8, the motor 3A, Motor 3B, drive sheave 4 and deflection pulley 5 . The two motors 3A and 3B provided on both sides of the drive sheave 4 drive the drive sheave based on the output of a drive device not shown. In addition, the sling 6 adopts a one-to-one winding method, and in order to improve the torque transmission capacity, it is wound around the driving sheave and the diverting pulley in a fully enclosed manner, and one end is connected to the elevator car, and the other end is connected to the balance counterweight . And the beam 9 is set on the upper part of the guide rail 7 for the elevator car and the guide rail 8 for the counterweight, and the motors 3A, 3B, the driving sheave 4, and the deflection pulley 5 are fixed on the beam 9, and their heights are substantially equal. unanimous.

As shown in FIG. 1 , the drive sheave 4 is driven by two motors 3A and 3B. In this case, the capacity of each motor can be reduced by half, so the size of each motor in the height direction and width direction can be reduced. Even if the effective utilization of the space in the height direction is particularly emphasized, and a motor with a long axial length is used, since the hoisting center of the elevator car 1 is located at the center of the elevator car 1, the driving sheave 4 can be arranged at the center of the elevator car 1. In the center, the motors 3A, 3B are arranged symmetrically with the driving sheave 4 as the center, so that only one side of the driving sheave 4 needs to be provided with a motor with a long axial length, so that the motors on both sides of the driving sheave 4 can be effectively utilized. space.

At this time, the axial length of each electric motor is about 1/2 of that when an electric motor is adopted. Furthermore, by adopting a structure in which the motors 3A, 3B are provided on both sides of the drive sheave 4, it is possible to avoid load concentration on a part of the beam 9, thereby improving stability. In addition, as described above, by using two motors with substantially the same capacity, it is possible to avoid any one of the motors from being enlarged in height and width. In addition, as shown in Figure 1, by setting the driving sheave 4 and the diverting pulley 5 on the beam 9, and making the heights of the two substantially the same, the size of the top can be reduced, thereby reducing the head space (elevator car 1 and The space between the upper ends of the lifting passage 10).

The installation of the motors 3A, 3B, the drive sheave 4 and the diverting pulley 5 will be described below with reference to FIGS. 2 and 3 . Fig. 2 is a plan view when looking down on the elevator from above, especially with respect to the car door side of the elevator car 1, the plan view when the counterweight 2 is raised and lowered on the opposite side (rear side) (the counterweight is arranged on the rear side). The beam 9A is fixed to the guide rail 7 for the elevator car, and the beam 9B is fixed to the guide rail 8 for the counterweight. Also, the beam 9C is fixed to the beam 9A and the beam 9B, or to the guide rail 7 for the elevator car and the beam 9B, or to the beam 9A, 9B and the guide rail for the counterweight. On the beam 9A, the motors 3A, 3B are fixed symmetrically about the driving sheave 4 so that the hoisting center of the elevator car 1 is located approximately at the center of the elevator car 1 . In addition, the diverting pulley 5 is fixed to the beam 9B so that the lifting center of the balance weight 2 is located substantially at the center of the balance weight 2 . In the structure shown in Fig. 2, its characteristic is that when the elevator is viewed from above, the beam 9A and the beam 9B are in a substantially parallel positional relationship, and the sling 6 and the beam 9A, or the sling 6 and the beam 9B are in a vertical position relation.

Fig. 3 is a plan view when looking down on the elevator from above, especially with respect to the elevator car door side of the elevator car 1, the plan view when the counterweight 2 is raised and lowered on the lateral side (the counterweight is arranged on the lateral side). The beam 9A is fixed to the guide rail 7 for the elevator car, and the beam 9B is fixed to the guide rail 8 for the counterweight. Beam 9C is fixed to beam 9A and beam 9B, or is fixed to guide rail 7 for elevator car and beam 9B, or is fixed to beam 9A, beam 9B and guide rail for counterweight. And, the beam 9D is fixed on the beam 9A or the beam 9C, and on the beam 9D, the motors 3A, 3B are fixed symmetrically with the drive sheave 4 as the center, so that the hoisting center of the elevator car 1 is approximately located at the center of the elevator car 1. central. In addition, the beam 9E is fixed to the beam 9A or 9B, or to the beam 9C, and the diverting pulley 5 is fixed to the beam 9E so that the lifting center of the balance weight 2 is located approximately at the center of the balance weight 2 .

In the structure of Fig. 3, it is characteristic that when the elevator is viewed from above, the beam 9D and the beam 9E are in a substantially parallel positional relationship, and the sling 6 and the beam 9D, or the sling 6 and the beam 9E are in a vertical positional relationship. In addition, in Fig. 2 and Fig. 3, adopt the structure that drive sheave 4 is set on the side of elevator car 1, and deflection pulley 5 is set on side of counterweight 2, but of course also can adopt the structure that deflection is set on side of elevator car 1. Pulley 5, and the structure of driving sheave 4 is set on the counterweight 2 side. Especially, in the case of using the balance counterweight shown in Figure 3 on the side, if the drive sheave 4 is set on the balance counterweight 2 side, when a large-capacity motor is used, it may be caused by the large volume. Installation work is difficult, but as shown in Figure 1, since two motors are used instead of large-capacity motors, there is an effect of facilitating installation work. In addition, it is also possible to provide the driving sheave 4 on both the side of the elevator car 1 and the side of the counterweight 2, and use four motors to drive the structure. In this case, there is an effect that the volume and capacity of each motor can be reduced.

The relationship between the diameter of the drive sheave 4 and the diameter of the suspension rope 6 in the elevator system will be described below with reference to FIG. 4 . In FIG. 4, suppose the diameter of the driving sheave 4 is D, and the diameter of the sling 6 is d. In FIG. 9 , the smaller the diameter D of the driving sheave 4 is, the smaller the bending radius of the sling 6 is, and the bending becomes steeper. On the contrary, the larger the diameter d of the sling 6 is, the more difficult it is to bend the sling. If the sling is bent forcibly, the sling will be stretched and partially broken, thereby reducing the service life of the sling. Therefore, the ratio of the diameter D of the drive sheave 4 to the diameter d of the wire rope 6 is now defined as D/d≧40 (Formula 1). And, generally use diameter d in the past and be the sling of 12mm, 14mm and 20mm, so the diameter D of the driving sheave that used in the past is generally all greater than 400mm. However, if a sling whose diameter d is smaller than that of the conventional sling and has high tension characteristics is used, according to the relationship of (Formula 1), a sheave 4c with a diameter smaller than 400mm in the past can be used, thereby reducing the size of the motor and the lift. Spacing between the upper ends of the channels.

If small diameter slings are used, the number of slings can be increased as a means of increasing tension. In FIG. 5 , it is assumed that the diameter of the driving sheave 4 is D, and the axial length of the driving sheave 4 is Ls. As shown in Figure 1, when the full-enclosed method is adopted, and the number of slings increases due to the use of small-diameter slings, as shown in Figure 5, by using the driving sheave 4 whose axial length Ls is greater than the diameter D, it is possible to A reduction in the headroom of the elevator car 1 is achieved. In addition, the deflection pulley (not shown) also has an axial length larger than a diameter at this time. Moreover, as shown in FIG. 5, by setting the shaft of the driving sheave 4 in parallel with the beam 9 for fixing the driving sheave 4, even if the driving sheave 4 having a long axial length Ls is used, it is possible to stably place the shaft of the driving sheave 4 on the shaft. Motors 3A, 3B (not shown) on both sides of the drive sheave 4 are provided on the beam 9 .

An embodiment of the power conversion device used in the elevator without a machine room in Fig. 1 will be described below with reference to Fig. 6 . As shown in FIG. 6 , two power converters 13A and 13B convert the voltage value and frequency of the power supplied by the power source 12 to drive the motors 3A and 3B. The control circuit 14 takes the output current information ia, 1b of the power conversion devices 13A, 13B and the speed information v1 obtained from a sensor such as a rotary encoder provided on at least one of the motors 3A, 3B as inputs, performs calculations, and outputs the power Instructions sa, sb for converting devices 13A, 13B for driving.

In a power conversion device and motor system (such as a system of power conversion device 13A and motor 3A) shown in FIG. 6, after calculating the speed control system (ASR: Auto Speed Regulator) using speed information v1, the current control The system (ACR: Auto Current Regulator) performs calculations for driving. Also, another power conversion device and motor system (for example, the system of the power conversion device 13B and the motor 3B) performs the calculation of the current control system based on the calculation result of the speed control system for driving. That is, one system is driven by the speed control method, and the other system is driven by the torque control method based on the calculation result of the speed control system. Under ideal conditions, the two systems can be driven by speed control. However, in reality, due to the parameter error of the device and the error of the detection device, there is a slight speed difference between the two systems, which will lead to The motors interfere with each other. As shown in Fig. 6, by driving one system in speed control mode and the other system in torque control mode, it is possible to prevent the motors from adversely affecting each other. The details of the control block will be described in detail with reference to FIG. 7 .

FIG. 7 is a block diagram of the control circuit 14 shown in FIG. 6 . First, in the speed command section 15, the speed command value v ^* based on the elevator speed pattern is calculated. The difference between this and the motor speed information v1 is then input to the speed control system 16 . The speed control system 16 calculates the current command value i ^* from the difference between the speed command value v ^* and the speed information v1. Then, in order to simultaneously drive the two motors, it is necessary to divide the current command value i ^* to drive the respective motors. This distribution is performed in the gain sections 17a, 17b. Gains of the gain sections 17a, 17b are set to be 1 at all times. That is, if the capacities of the two motors are the same, the calculated gains of the gain sections 17a and 17b are both 0.5.

In the gain sections 17a, 17b, the set gains are integrated to calculate the current command values ia ^* , ib ^* of the respective systems. Then, the difference between the current command values ia ^* , ib ^* and the output current information ia, ib of the power conversion device is calculated and input to the current control systems 18a, 18b. In the current control system 18a, 18b, command voltages va ^* , vb ^* are calculated according to the difference between ia ^* , ib ^* and ia, ib, and modulated in the PWM modulation part of blocks 19a, 19b to generate Instructions sa and sb for driving the power conversion device. In addition, if one of the two motors fails, the values of the gain parts 17a and 17b can be changed so that the motor can be driven only by the motor of the one system that is not failed. At this time, although the torque that can be output is reduced, this can be solved by performing low-speed operation in the failure mode.

Hereinafter, a method for controlling torque ripple occurring during elevator driving when synchronous motors are used for the two motors of the elevator without a machine room in Fig. 1 will be described. Torque ripple occurs when the resonance point of the mechanical system determined by the weight of the elevator car and the sling and the spring coefficient of the sling coincides with the high frequency (mainly the sixth-order high frequency component) of the synchronous motor rotation frequency . That is, when the rotation frequency or its high frequency becomes a frequency near the resonance point during acceleration or deceleration, torque ripple occurs, causing the elevator car to vibrate. In order to suppress the occurrence of torque ripple, the phase difference of the magnetic pole positions of the two motors is set to satisfy 30°+60°×N (N=0, 1, 2, 3 . . . ) (electrical angle) (1).

FIG. 8 is a test chart showing a measured torque waveform when the phase difference of the magnetic pole positions is 0 degrees. It can be seen from Fig. 8 that the motors of the two systems respectively generate torques of about 2.5 N·m including high frequencies, and the sum of the torques also vibrates due to high frequency components. Usually, complex control methods are employed to suppress this vibration.

9 is a test chart showing a torque actual measurement waveform when the phase difference of the magnetic pole positions is set to 30 degrees according to the expression (1). It can be known from Fig. 9 that the motors of the two systems generate torques of about 2.5 N·m including high frequencies with a phase difference of half a period, and the high frequency components are canceled out in the sum of the torques. That is, when two synchronous motors are used, torque ripple can be suppressed by setting the phase difference between the magnetic pole positions of the respective motors so as to satisfy the expression (1).

As mentioned above, although embodiment of this invention was described, it cannot be overemphasized that this invention is not limited to said embodiment, Various modification examples can be implemented within the range which does not deviate from the summary. In addition, in the description of the embodiment, an example of using two electric motors has been described, but two or more electric motors can also be used.

Claims (10)

1. A machine room-free elevator, at least provided with an elevator car, a counterweight, a sling, a drive sheave, an electric motor and a diverting pulley for driving the drive sheave inside the hoistway, characterized in that, A plurality of motors for driving the driving sheave are arranged on both sides of the driving sheave, and one end of the sling is wound around the on the elevator car, and wrap the other end around the balance counterweight. 2. The elevator without a machine room according to claim 1, wherein the drive sheave, the plurality of motors, and the diverting pulley are fixed so as to be located at substantially the same height. 3. The elevator without a machine room as claimed in claim 1, wherein said driving sheave, said plurality of electric motors and said diverting pulleys are fixed on a beam which is mounted on a guide rail for the elevator car. Alternatively, the upper parts of the guide rails for the balance weight are connected at positions having substantially the same height. 4. The elevator without a machine room according to claim 1, wherein the plurality of motors are two motors with substantially the same capacity. 5. The elevator without a machine room according to claim 1 or 4, wherein the plurality of motors are motors whose axial length is longer than the radial length. 6. The elevator without a machine room according to claim 1, characterized in that, it is arranged in the following manner, that is, the first beam and the second beam are arranged on the upper part of the elevator passage, so that they are in a position when looking down on the elevator from above. The positional relationship is basically parallel, and the driving sheave and the two motors are fixed on the first beam, wherein the driving sheave is set so that the lifting center is basically located in the center of the elevator car or the balance counterweight, and the two motors The motor is arranged at a substantially symmetrical position with the driving sheave as the center, and the diverting pulley is fixed on the second beam, and the sling wound on the driving sheave or the diverting pulley is connected between the first beam and the first beam. A substantially vertical positional relationship is formed, or a substantially vertical positional relationship is formed between the sling wound on the driving sheave or the diverting pulley and the second beam. 7. The elevator without machine room as claimed in claim 1, wherein the plurality of motors are two motors, and the two motors are respectively driven by power conversion devices of different systems, and in the At least one of the two motors is provided with a sensor capable of detecting the rotation speed of the motor, and one motor is driven in a speed control mode, while the other motor is driven in a torque control mode. 8. The elevator without a machine room according to claim 1, wherein the diameter of the driving sheave is less than or equal to 400 mm. 9. The elevator without machine room as claimed in claim 1, characterized in that, the axial length of the driving sheave is greater than the diameter of the driving sheave, and the shaft of the driving sheave is arranged to be in contact with the fixed The beams of the drive sheave are basically parallel to each other. 10. The elevator without machine room as claimed in claim 1, characterized in that, the plurality of motors are two synchronous motors, and the phase difference of the magnetic pole positions of each motor is set to basically satisfy 30°+60° in terms of electrical angle ×N (N=0, 1, 2, 3...) relationship.

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