JPS6221718B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION When the elevator is stopped at night or for a long period of time, and pressure is applied to the guide roller in a specific direction due to an unbalanced load, etc., a creep phenomenon occurs in the guide roller. When the elevator is started in such a state, running vibrations are generated due to deformation of the tires of the guide rollers, which are propagated to the car, causing unpleasant vibrations to the passengers, and often significantly impairing ride comfort. The present invention relates to a guide roller device that does not induce vibration during actual running even if such a creep phenomenon occurs.

Conventionally, as a general rule, one guide roller of an elevator is provided at each location on a guide rail.
When the elevator is stopped, it is electrically controlled so that it returns to the standard floor and stops.

In particular, if the elevator is stopped for a long time with an uneven load, the treads of the guide rollers are likely to deform. Usually, the outer periphery of the guide roller of an elevator is constructed by vulcanizing or adhering a tire made of elastic synthetic rubber or plastic material to dampen running vibrations. For this reason, even if it has a restoring force for a short period of time, if pressure is applied for a long period of time, a creep phenomenon will gradually occur as is well known. This phenomenon will return to its original state if it is repeatedly rolled, but it will take a considerable amount of time, and the vibrations during this period will significantly worsen the vertical comfort. In reality, some products may be difficult to put to practical use.

Particularly in recent years, with the appearance of high-rise buildings, high-speed elevators are used, and running vibrations simply affect the vibrations of the guide rollers, which may resonate, which is extremely dangerous.

In other words, if vibration occurs, not only will the riding comfort deteriorate, but it will also have a significant negative impact on speed control. Improving the running performance of both low-speed and high-speed elevators is currently physically difficult.

FIG. 1 shows a schematic side view of a conventional elevator. The hoisting rope 1, the upper beam 2, the rope hit spring 3, the spring receiver 4, the upper beam 2 for forming the elevator car frame, the vertical beams 7, 7', the lower beam 2, and the roller guide support frame 11, 11' are integrated. It is structured as follows.

A car 8 is provided on this car frame so as to be supported via vibration isolators 9, 9' and 10, 10'.

The elevator is guided in the hoistway by guide rails 5, so it has guide rails 5, 5' on the left and right.
are attached to the hoistway walls 6, 6' and mounted on the car frame, and the guide roller devices 100, 100' and 2
00, 200' guide the elevator car device up, down, left and right.

The guide roller device of each installation has guide rollers contacting the guide rails 5 and 5' from three directions, respectively.
It is a rolling mechanism and is configured so that it does not fall off the rails front to back, left or right.

The guide rails of these parts are formed by a single roller. For this reason, as mentioned above, if the elevator is stopped at a reference floor for a long time, the tread surface of the guide roller becomes depressed due to an uneven load, which is a so-called creep phenomenon. When the elevator is restarted, the elevator vibrates once per revolution as shown in FIG.

In particular, in high-speed elevators, the eccentricity of the guide roller's tread surface outside diameter is kept to around 10 to 20 microns.
This causes vibrations if the eccentric load or normal load causes the eccentricity to be out of order by more than the eccentricity accuracy, although it depends on the traveling speed. Eccentricity with normal machining accuracy results in relatively smooth rolling, but with creep, localized vibration characteristics become even worse.

Furthermore, this vibration also causes the walls of the hoistway to vibrate via the guide rail 5, thereby affecting adjacent rooms, offices, etc. with vibration noise.

In high-rise buildings, as a result of the maximum vibration of the rope, if there is a resonance point as mentioned above, the ride becomes even more dangerous, such as the rail swaying and falling off. (In order to control the vibrations of this long rope, various rope vibration damping devices are installed.) This invention provides a guide roller device that does not generate periodic vibrations when restarting even when the creep phenomenon described above occurs. The purpose is to provide Specific examples will be described below.

FIG. 2 shows guide roller devices 100 and 100' installed on the car frame, respectively, using the present invention.
and rollers 10 with different diameters at 200 and 200'
1 and 102 are arranged in parallel, the details of which are shown in FIG.

FIG. 3 is a plan view showing the guide roller device on the left side of the upper part of the elevator. Guide rollers 101 and 102 are arranged across the guide rail 5,
The diameter of the guide roller 102 is slightly larger. For this reason, although not shown in the drawings, the axes are slightly shifted. The amount is 1/2 the difference in diameter. These guide rollers 101 and 102 are engaged with a lever 104 via a shaft 103. That is, one end of the lever 104 is rotatably connected to a hinge 105 by a shaft 106, and the other end is connected to the guide rollers 101, 1.
02 are rotatably installed in parallel (or in series) and integrally.

The guide rollers 101 and 102 are of opposite sex, and are configured to be in constant contact with the rolling contact surface of the guide rail 5, respectively. Furthermore, an elastic member of a push spring 107 is interposed on the back of the lever 104 using a spring receiver 108 provided on the fixed car frame as a fulcrum, and presses the lever 104 toward the guide rail 5 to move the guide rollers 101 and 102 to the guide rail. I am trying to make contact with 5.

The guide rollers 101 and 102 are the guide rail 5
This direction corresponds to the front and rear of the elevator, and the unbalanced load in this direction is usually large, so it is important to prevent the creep phenomenon in this direction. The direction of the roller guide 109 (horizontal direction) is such that the loading device is relatively well balanced and the unbalanced load is small, so one guide roller is used in this embodiment.

Of course, the method using a plurality of different diameters can also be used.

FIG. 4 shows guide rollers 101 and 102 that roll on the guide rail 5 and have different diameters.

When the diameter of the tread surface of the guide roller 101 is D ₁ and the diameter of the tread surface of the guide roller 102 is D ₁ +d, the center-to-center distance between the rotating shafts is d/2. The tread surface 117 of the guide rail 5 is the point at which the guide roller creeps. The guide rollers 101 and 102 do not necessarily have to be coaxially engaged, and may be arranged on the same line or separately by separate shafts.

FIG. 5 shows a partial sectional view of the guide roller device, and the axes of the two guide rollers 101 and 102 are offset by d/2.

With this relationship, the distance l ₁ that the smaller guide roller 101 travels in one revolution is l ₁ =πD ₁ , and the distance l 2 that the larger guide roller 102 travels in one revolution is l _{2 =} π(D ₁ +d). The difference in distance traveled by guide rollers 101 and 102 at the same rotation speed is πd, 2πd......(n-1)πd, n
It changes with πd. Eventually, due to this difference, the first creep points of the two guide rollers 101 and 102 are synchronized. (This point is important for the large guide roller 10.
2 is delayed by one rotation or the guide roller 101 is small.
This is when it has advanced one revolution. ) The distance is that the guide roller 101 is smaller and the guide roller 1 is larger by one rotation.
Since it is equal to the distance traveled from 02, the relationship is l ₁ = nπd, and the creep synchronous rotation speed that first appears is n
= l ₁ /πd.

For example, guide roller D ₁ =200mm, D ₁ +d=
In the case of 201mm, d=1mm, so l ₁ =π200=
It becomes 628mm. A creep synchronization point appears at n=628/π×1=200th rotation. The moving distance L during that time is L = 0.628 x 100 = 125.6 m. That is, it is possible to set the lifting stroke within the range in which the next creep synchronization point appears. This relationship is illustrated in figures as shown in Figures 6a and 6b, where figure a shows the locus drawn by the guide roller 101 as it rolls when it creeps. Figure b shows the locus drawn by the guide roller 102 as it creeps and rolls. As a result, the next creep point is the n-th rotation, during which no vibrations due to creep appear.

This diagram is shown in FIG. 6(d) and is remarkable when compared with the guide roller vibration characteristic in the conventional method shown in FIG. 6(c).

As a result, if the vertical movement is within the range where the next creep point appears as shown in Fig. 6e, even if the guide roller creeps, there will be no vibration effect.
It is possible to provide an elevator that is always quiet and whose running characteristics do not change at any time.

Furthermore, even if the lifting stroke increases and passes through the next creep synchronization point, the number of vibrations is extremely small compared to the conventional one, so quiet operation can be performed without any problem.

This reduces vibration noise, simplifies other vibration isolating devices, improves the stability of elevator electrical control, prevents the hoisting rope from becoming a source of vibration, and the anti-vibration measures for the guide roller device basically eliminate the source of vibration. As a result of cutting off, the effects on others are great.

In the above, guide rollers 101 and 102 are
Although it is provided coaxially with 03, the same effect can be obtained even if it is divided and provided in separate positions.

Although two embodiments have been shown as the guide rollers, it is of course possible to provide three or more guide rollers to eliminate synchronization points due to small diameters.

[Brief explanation of the drawing]

FIG. 1 is a schematic front view of a conventional elevator car device, FIG. 2 is a schematic front view of an elevator car device using the present invention, and FIG. 3 is a top view of a guide roller device according to the present invention. Figure 4 is a diagram explaining the basic principle of the present invention, Figure 5 is a sectional view of the main part of Figure 3, and Figure 6 is a diagram illustrating the basic principle of the present invention.
Figures a and b are creep locus diagrams of the guide roller according to the present invention, Figure 6c is a vibration characteristic diagram of a conventional guide roller, Figure 6d is a vibration characteristic diagram of a guide roller according to the present invention, and Figure 6e is a diagram of the vibration characteristics of a conventional guide roller. FIG. 3 is a diagram showing an example of elevator head setting using the invention. 1...Hoisting rope, 5...Guide rail, 8
...car, 100, 100', 200, 20
0'... Guide roller device, 101, 102...
Guide roller, 104... Lever, 117... Guide roller creep point.

Claims (1)

[Claims] 1. An elevator car that ascends and descends along a guide rail laid in a hoistway, and the car is composed of a plurality of guide rollers having different diameters, and the outer periphery of the elevator car is arranged so as to be in contact with the guide rail. In an elevator comprising a plurality of guide roller devices arranged as a set, one end of the guide roller device is rotatably attached to the car, and the other end is pressed from the main body side of the car. An elevator characterized in that a set of the guide rollers having different diameters is attached to an integrated lever via an elastic member. 2. The elevator according to claim 1, comprising a guide roller device in which a pair of guide rollers having different diameters are fixedly attached to a shaft provided on the lever. 3 In claim 1, the traveling distance of a set of guide roller devices made up of guide rollers with different diameters until they return to the state in which they were initially in contact with the guide rail due to elevation is a required distance. An elevator characterized by comprising a guide roller device configured with a diameter difference between the guide rollers so as to be equal to or longer than an elevator service distance.