SU1586988A1 - Escalator drive - Google Patents

Abstract

The invention relates to a lifting and transport machinery, in particular, to a continuous passenger transport, and can be used as a drive for a tunnel escalator intended for large lifting heights. The purpose of the invention is to reduce the size of the drive. The escalator drive includes a gearbox housing 1 with a main shaft 2 placed on it, on which a low-speed gear 3 is fixed, which is engaged with at least two driving gears 4 and 5. On the main shaft 2 there are also sprockets 6 that provide moving the stairway. The drive is made up of kinematic chains placed in the housing 1 and installed at an angle to each other on different sides of the vertical plane passing through the axis of the main shaft 2 and according to the number of meshes with the low-speed gear 3 driving gears 4 and 5. The angle between the axes connecting the centers of the driving gears 4 and 5 of the kinematic chains with the center of the low-speed gear 3, is not less than a certain ratio depending on the gearing parameters of the gearbox. The electric motors 17 and 19, rotating independently, drive the kinematic chains of the reducer into rotation. Power summation is carried out directly on the low-speed wheel. 2 hp f-ly, 6 ill.

Description

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 The invention relates to a lifting machinery industry, in particular to a continuous passenger transport, and can be used as a drive for tunnel escalators intended for high lifting heights.

The aim of the invention is to reduce the dimensions of the drive, and the investigator, o, and the size of the main room, and to simplify the maintenance of the drive and its repair.

: Fig, 1 is a schematic representation: the route of an escalator with a drive, general; view; figure 2 is a view of And figure 1; on fig.Z - drive; figure 4 - section bb in fig.Z, fig.Z - drive escalator; figure 6 - the same option.

The escalator drive includes a gearbox housing 1 with an escalator main shaft 2, on which a low-speed gear wheel is attached: with 3, which is engaged with at least two driving gears 4 and 5, the main shaft 2 is also placed t new stars 6, providing movement of the stairway 7. The drive is made in the form placed in the housing 1 of the gearbox and installed at an angle to each other on different sides of the vertical plane ee, passing through the axis of the main shaft 2, kinematic chains 8 and 9; by number in gear with the output gear wheel 3 leading;: gears 4 and 5. Each of the kinematic chains 8 and 9 of the gearboxes contains an input stage that includes the input shaft 10 or 11 with gear wheel 12 or 13, which meshes with the gear wheel - 14 or 15, respectively. The input shaft 10 of the kinematic chain 8 of the gearbox is connected by means of the coupling 16 with the electric motor 17, and the shaft 11 of the chain 9 through the coupling 18 is connected with the electric motor 19. The electric motors 17 and 19 are arranged in such a way that their longitudinal axes are parallel to the axis of the main shaft 2 and their dimensions do not exceed the dimensions of the stairway 7.

The second stage of each kinematic chain 8, 9 of the gearbox consists of shaft-shchestren 20 or 21 and the way i x s with gear teeth 22 and 23 respectively, Last stage of kinematic chains 8 and 9

Toit. Of shafts-shafts 24 and 25 and, respectively, associated gears 4 and 5. Leading gears 4 and 5 are placed on fixed axles 26 on spherical bearings 27.

The angle between the axes f-f and k-k, 1 linking the centers of the vedus 1x gear 4 and 5 of the kinematic chains 8 and 9 with the center of the low-speed gear

wheels

h q

z b

is defined by the expression:

 arcsin- - (-Y - -. About ayu a 2 m 2cos | i

where m is the leading meshing module

gears with low-speed gear;

 the center-to-center distance between the center of the low-speed gear and the center of the pinion gear;

gear head height ratio; coefficient of displacement of the initial contour of the low-speed gear;

the number of teeth of the low-speed gear;

B is the angle of the gearing engagement profile (for transmittable transmissions A 0 and cos 1). In general terms, this relationship is an inequality in which the minimum value of the angle Y determines the smallest possible volume and dimensions of the drive, expressed in terms of the center-to-center distance and the geometric parameters of the low-speed gear.

The minimum distance 2b between the drive gears 4 and 5 in this case (Fig. 3) may be equal to two radii of the circumferences of the protrusions of these wheels, i.e.

mi p

 da

(one)

de b

P1 P

011

a minimum distance from the center of the drive gear, which is engaged with the low-speed gear, to a vertical point of symmetry passing through the axis of the main shaft;

the diameter of the projections of the pinion gear, which meshes with the low-speed gear.

With what

- SU1-,

"TW i

I

where a is the interpentral distance between the center of the gear 3 and the center of the pinion gear engaged with this wheel;

- the angle between the axes connecting the center of the toothed wheel 3 with the centers of the leading gears of the adjacent kinematic chains.

Putting the value from the expression (1) in the expression (2), we obtain the ratio between the minimum value of the angle y and the parameters of the gear transmission

chi:

. From 1P-It is known that

2L -

about 1H ---,

2aw 2

(3)

da, d, + 2m (, - fiy), (4) de d, is the pitch diameter of the leading

gears; m - gear module from

pinion to the low-speed gear; h - head height ratio

tooth transfer;

X, is the displacement factor of the initial contour of the driving gear; and Y - the coefficient of equalization

 displacement, 35

d, x-iiJ cos

(five)

/five

Z, is the number of teeth of the pinion gear;

- the angle of the gear profile for the transfer gear (for the spur gear 0), LU xy, (6) de x - the sum of the displacements

low-speed drive gear 45 wheels;

Y is the coefficient of perceived displacement,

X2- X, h-hz, (7) de x is the coefficient of displacement of the initial 50 contour of the low-speed gear,

t

(eight)

where a is the separation center-to-center distance.

() m 2 cosp

(9)

15869Я8

d

where z is the number of teeth low-speed

gear wheel.

Substituting successively the values of the parameters from relations (4) - (9) into the relation (3) and having carried out the transformation w, finally we get the ratio between the minimum angle y and the gear geometry in the form

J5

20

-

35

40

45

50

55

m

aw

z y

before /, and Wl, V

jf,;, 2 arcsin - (-----).

m 2coS | 3

The housing 1 of the gearbox can be made of a common crankcase 28 and a number of covers, for example, 29-31, providing a volume that isolates gears from the environment (Fig. 1 and Fig. 5). The most appropriate design solution, providing a rational weight and The dimensions of the drive, depending on the required lifting height (Fig. 6), are the removal of the gearbox housing 1 from individual blocks of body parts, according to the number of kinematic chains. For interfacing the gearbox housing, they are fitted with flanges. At the same time, in one of the blocks, which is basic and consisting of body 32 and crush 33, there is a low-speed gear 3 with one of the kinematic chains, and the other block 34 with its kinematic chain is fixed on the base unit with removable.

The drive works as follows. The electric motors 17 and 19, rotating independently, drive the kinematic chains 8 and 9 into rotation. Since all independent kinematic chains have a rigid kinematic connection through the low-speed gear wheel 3 located on the main shaft 2, they are rotated with the same frequency and the power developed by the engines is equal (a slight difference in the power flows caused by the individual losses in each kinematic chain may not be taken into account).

Thus, for each kinematic chain, a power corresponding to the engine power of each kinematic chain is supplied to the low-speed gear wheel 3. Power summation is performed directly on the low-speed wheel 3. Power summation is carried out at a constant specific power on the crown of the low-speed wheel 3.

Each of the leading gears 4 and 5, which are the last element of the corresponding kinematic chain 8 and 9, engages with different teeth of a low-speed gear. Thus, for one revolution of the wheel, each tooth of the wheel experiences the number of 1.xg of loadings, corresponding to the number of associated gears.

Claims (3)

1. An escalator drive containing traction sprockets fixed on the main shaft and a low-speed toothed gear meshed at the edge, at least with two driving gears of gears made with parallel shafts, characterized in that in order to reduce its dimensions The axes of the gearboxes are located in planes intersecting along the axis of rotation of the low-speed gear wheel, and the angle between the planes is determined by the expression 0 five 0 five Y Where 2 arcsin (h - aw " V 4. 2 m 2COS / 3 - angle between axes of reducers} m - module of engagement of leading gears with low-speed gear; a is the center-to-center distance between pinion and low-speed gear; h - coefficient of head height tooth; x is the displacement factor of the initial contour of the low-speed gear; z is the number of teeth of a low-speed gear; In - the angle of the gearing of the drive gears with a low-speed gear. 2. Drive POP.1, characterized in that it is provided with flanges made on the body of both gearboxes for their interfacing. 3. The actuator according to claim 2, characterized in that the housing of one of the gearboxes is made basic, and the low-speed gear wheel is located in the housing of this gearbox. and FIG. 2 thirty yj 29 33 3