JPH01299109A - Horizontal rotary shelf - Google Patents

Abstract

PURPOSE:To aim at reduction of width of a machine and a high-speed by installing in the ratio of one tray to predetermined number of chain links, lying the inside of the tray on the outside of a sprocket at a turning portion and positioning the predetermined number of guide rollers outer than the inner end of the tray. CONSTITUTION:A tray 7 is arranged in the ratio of one to four links 51 and four guide rollers 53a-53d are arranged at one tray 7. The distance S of the trays 7 at a straight line portion is set much enough smaller than the diameter 2R of a sprocket 1 so that the sprocket 1 and the tray 7 are overlapped each other with a large overlap width E at a turning portion. And, the guide rollers 53a-53d are positioned outside the inner end of the tray 7 and its extension line. This construction can reduce the width of the machine and enable running at a high-speed.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a horizontal rotating shelf for horizontally circulating and transporting a plurality of trays for storing packets, etc., and particularly to a horizontal rotating shelf that can run at high speed.

[Prior Art 1] A rotating rack for horizontally circulating and transporting a plurality of trays for storing containers and the like is well known. This horizontal rotating shelf has two sprockets arranged horizontally with an interval between them, a drive device that rotates one of the sprockets, a chain that is endlessly hung around the two sprockets, and a container, etc., to be placed on it. It consists of a plurality of trays fixed to a chain, and inner and outer rails that support the inner and outer ends of the trays, respectively. The connection point between the chain and the tray is near the inner edge of the tray. Also 1
Some have two packets placed on one tray.

Such horizontal rotating shelves are disclosed in Japanese Utility Model Publication No. 59-28962, Japanese Patent Application Laid-open No. 102717-1982, and Japanese Patent Publication No. 62-29.
It is shown in Publication No. 321.

[Problems to be Solved by the Invention] Centrifugal acceleration acts in the radial direction of the tray at the turning section where the tray passes through the engagement portion of the sprocket, so when traveling at high speed, packets in the tray may fly out in the radial direction.
For this reason, a stopper that protrudes upward is provided at the bottom of the outer end of the tray to prevent the packets from flying out.

Generally, the traveling speed of the tray on the straight line between the two sprockets is 30 m/min or less. If the traveling speed is increased more than this, an accident such as a packet flying out over a stopper at a turning section may occur. To deal with this, the height of the stopper mentioned above can be increased, but
This becomes a major obstacle when pulling out packets from the tray. Furthermore, if the traveling speed is greater than this, parts within the bucket may become strained.

It can be seen that this problem can be solved by increasing the diameter of the sprocket and lowering its rotational speed. However, according to this, the machine width of the horizontal rotating shelf (meaning the width of the horizontal rotating shelf in the direction perpendicular to the moving direction of the tray in the straight line between the two sprockets) increases, and the installation area becomes large. It is impossible to save space.

For this reason, high-speed running of 30 m/min or more was practically impossible.

Furthermore, it is desirable to increase the distance between the two sprockets, that is, the length, in order to increase the number of trays to be stored, and to increase the traveling speed of the tray in order to carry out quick loading and unloading operations. However, in the past, it was not possible to increase the speed due to the reasons mentioned above.

An object of the present invention is to provide a horizontal rotating shelf that has a simple configuration, has a small machine width (and can run at high speed).

[Means for Solving the Problems] The present invention provides a rotating section in which, when trays are installed on the links constituting a chain, one tray is installed for at least three links, and the tray is made up of sprockets. , the inner side of the tray overlaps the outer side of the sprocket, and the four guide rollers installed at the connecting points of the at least three links in the rotating part are positioned on the outer side of the inner edge of the tray. It is characterized in that it is provided so that the

[Function 1] According to this, the sprocket can be made larger in diameter, so
It is capable of running at high speeds of /min or more.

[Example] Examples of the present invention are shown in FIGS. 1 to 8 below. In addition, in FIGS. 1 and 4 to 7, the guide rollers are originally shown by broken lines, but are shown by solid lines.

The first embodiment shown in FIGS. 1 to 4 will be described.

In FIG. 3, the horizontal rotating shelf 110 includes two sprockets 1.2 arranged at a constant interval in the horizontal direction;
A drive device 3 that drives one sprocket 2, and a chain 5 that is hung endlessly around the two sprockets 1.2.
and a plurality of trays 7 on which packets 6 and the like are placed, fixed to the chain 5 and connected at equal intervals ΔA,
It is composed of an inner rail 8, an outer rail 9, etc. for horizontally supporting the tray 7. One horizontal rotating shelf 10 is configured with the above configuration. These horizontal rotating shelves are stacked in multiple stages. In this case, W is the machine width.

15 is a transfer device for taking out and putting in the packets 6 from the tray 7. This configuration is well known,
be. Since two packets 6 can be placed on one tray 7 in parallel, two sets of transfer mechanisms are installed in the transfer device 15 in parallel. The two transfer mechanisms can be operated independently or simultaneously.

In FIGS. 1 and 2, one tray 7 can carry two packets 6 horizontally in parallel. Reference numeral 21 denotes a partition wall that separates the two packets 6.6, and a stopper 22 raised from the bottom is provided at the outer end 26 of the tray 7, which is not provided near the inside of the tray 7. At the inner end 25 of the tray 7 are two inner rollers 23.
is provided and rests on the inner rail 8. inner roller 2
No. 3 has a self-aligning function, and its inner roller 23 is inclined with respect to the axis to reduce sliding movement. At the outer end 26 of the tray 7 are two outer rollers 24.
is provided and rests on the outer rail 9. Inner rail 8
And the outer rail 9 has not only a straight part but also a sprocket 1.
．． 2 is also installed on the rotating part.

The chain 5 includes a plurality of links 51, a plurality of bins 52 connecting these links, and guide rollers 53a, 53b, 53c, and 53d rotatably attached to the lower ends of the bins 52.
It consists of. Sprocket 1.2 is guide roller 53a
~53d to drive the chain 5.

In the straight line between the two sprockets 1.2, there is a U-shaped guide rail 11 that guides the guide rollers 53a to 53d.
is provided to prevent meandering movement of each tray 7-.

One tray 7 is installed for every four links 51. Therefore, approximately five links 51 are located below one tray 7, and four guide rollers 53a, 53b,
53c and 53d are located. Guide rollers 53a and 53
In reality, the link 51 between the tray 7 and the tray 7 is often absent (the tray 7 also serves as the link 51, the guide roller 53a,
The bin 52, which is the rotating shaft of the bin 53b, is fixed to the tray 7 with bolts and nuts. This guide roller 53a.

The bin 52, which is the rotating shaft of the guide rollers 53c and 53d located on both sides of the bin 53b, is not fixed to the tray 7.
The bin 52 only connects the links 5a. Therefore, the bin 52 having the guide roller 53C153d
The link 51 connected to the bin 52 can freely move horizontally with respect to the tray 7.

The gap S between the two trays in the straight section (upper and lower in FIG. 1) is sufficiently larger than the pitch circle diameter 2R of the sprocket 1.2. That is, in the turning section, the sprocket 1.2 and the tray 7 overlap each other. In the six embodiments, this overlap margin E is sufficiently larger than the conventional one,
Guide rollers 53a and 53b are installed near the radial center of the tray 7 (that is, the center of the loaded packet in the depth direction).
Two bins 52 are installed. The center of the packet 6 in the depth direction can generally be said to be the center of gravity of the packet 6 in the depth direction.

The number of teeth Z of the sprocket 1.2 is 12.

An object of the present invention is to prevent the packets 6 from jumping out of the tray 7 at the turning section even if the traveling speed of the tray 7 is increased (40 m/min or more).

The centrifugal angular acceleration α at the desired position R of the tray 7 rotated by the sprocket 1.2 (distance from the center of the sprocket 1.2) is determined by the following equation.

Here, R: Radius of subrocket 1.2 (m) a: Difference between desired position R1 and R (m) υ: Traveling speed of tray 7 on straight section (m/sl Therefore,
If R is increased, the centrifugal angular acceleration α will be decreased, but if R is increased, the machine width W will be uniquely increased. Therefore,
It is sufficient to fix the machine width W, increase the diameter 2R of the sprocket 1.2, and increase the overlapping margin E between the diameter 2R of the sprocket 1.2 and the tray 7, as shown in FIG.

However, if the gap △A between the trays 7 is not set above a predetermined value, the inner corner 2 of the adjacent trays 7° 7 at the rotating part
5a Comrades collide. Therefore, the relationship between the overlap margin E and the gap ΔA will be explained with reference to FIG.

E=R cos(i/Z) F −−−−−−−−−−
(2) From equations (2) and (3), equation (4) is obtained.

Sprocket 1.2 pitch circle diameter = 2R 4P = A + △A −−−−−−−−−−−−−−−−−
-(7) From equations (6) and (7), the following is obtained.

Substituting equation (8) into equation (4) yields equation (9).

Here, P ------- Pitch dimension A of the links 51 of the chain 5 ------- 1 - Width ΔA of the lay 7 ---- Gap 2 between the trays 7 in the straight part ---- --The sprocket tooth number type deviation E is calculated using formula (9), and the specifications A of the tray 7,
Determined from ΔA, P, Z, R, etc. If the value exceeds that value, as described above, adjacent trays 7 will collide with each other at the rotating portion.

Here, an example of the dimensions of each part will be explained.

Width of target packet 6: 38C1n+++
Depth of target packet 6: 650mm Width A of tray 7: 800mm Tray 7
Depth B: 670+nm Tray 7
Gap between comrades ΔA: 320mm Machine width W Machine width 2R+2B+250-2E): 2050 Overlapping allowance of tray 7 E: 291.3mm Number of links per one tray 7 N=4 Length of link 51 P: 280+nm Pitch circle diameter 2R of sprocket 1.2: 1081.9mm Number of teeth Z of sprocket 1.2: 12 Sprocket 1
．． 2 rotation speed N: 14.5 rpm (moving speed υ of the tray 7 in the straight section: 50 m/m1ni In this configuration, the centrifugal angular acceleration α acting on each part of the packet 6 is as shown in Table 1, and at 50 m/min. Even when the speed is increased, it is possible to sufficiently prevent the packet 6 from flying out and the load within the packet 6 from collapsing.The unit in Table 1 is gravitational acceleration (calculated value).

In the comparative conventional example shown in Table 1, the diameter of sprocket 1.2 is 2R.
This is a case where the speed is set to 61.8 mr* and the traveling speed υ is set to 50 m/IWin. In addition, the centrifugal angular acceleration of the conventional R = 545 mm, where 2R is 561.8 mm and the moving speed is 40 m/min, is 0.31 g, which is larger (
For example, when the speed reaches 41 m/m1n), packet 6 pops out.

Also, sprocket 1 for tray 7 (packet 6)
．． The point of action of the centrifugal force from 2 is near the center of gravity G of the tray 7 (packet 6). Therefore, the moment of acceleration force F1 and deceleration force F2 acting in the pitch angle (2π/Z) region of sprocket 1.2 where tray 7 transitions from the straight section to the rotating section and from the rotating section to the straight section is °'F+xL, or F2×L". In this embodiment, the pitch circle diameter 2R is increased so that the pitch circle of the sprocket 1.2 is located near the center of gravity G, so L can be made small (and the moment can be made small). Yes, so tray 7 (packet 6)
It is possible to reduce the fluctuation of the

In the embodiment, the partition wall 21 that partitions the two packets 6.6 in one tray 7 is not provided inside the tray 7, and this is because the partition wall 21 is not provided inside the tray 7. Since the angular acceleration decreases toward the center of the sprocket 1.2, the angular acceleration acting in the longitudinal direction also decreases.

Therefore, the acceleration force and deceleration force acting in the front-rear direction are smaller than the frictional resistance force acting between the tray 7 and the packet 6, so the packet 6 does not slip, so the partition wall 21 is removed in this portion. Therefore, it can be made at low cost.

When the tray 7 is located at the turning part of the inner rail 8, the inner roller 23 is inclined with respect to its axis due to the self-aligning function, so that the inner roller 23 is less likely to slip against the inner rail 8 due to steering operation. , it is possible to achieve low noise due to sliding. Another embodiment shown in FIG. 5 (hereinafter,
In the second embodiment (hereinafter referred to as the second embodiment), the pitch circle diameter 2R of the sprocket 1.2 is made smaller than in the above-described embodiment (hereinafter referred to as the first embodiment). Even in this case,
When the tray 7 is located in the rotating part, the guide roller 53c
, 53d and the center of the bin 52 is located at the inner edge 25 of the tray 7.
It is located on the outside. Guide rollers 53c, 53
When d is located near the inner end 25 of the tray 7,
The pitch circle diameter 2R of sprocket 1.2 is 830.7+
nl11, moving speed v: 50 m/min,
The centrifugal angular acceleration α at the position R=545 mm is 0.28 g, and a movement of about 50 m 2 /1 IIin can be obtained. Specifications different from the first embodiment will be described below.

Gap ΔA between trays 7: 60mm Overlap margin E of trays 7: 170mm Length P of link 5a: 215+nm Pitch circle diameter 2R of sprocket 1.2: 830. In+m Rotation speed N of sprocket 1.2: 19.2 rpm The minimum dimension E min of the overlap margin E for the centers of the guide rollers 53c, 53d, bin 52, etc. to be located outside the inner end 25 of the tray 7 is the As is clear from Figure 4, it is expressed by the following equation.

? Bimin = Jesin'2i/Z) --------
--(10) Therefore, the following equation is obtained.

Therefore, the overlap E is the minimum value E shown in equation (11).
The value is determined to be between min and the maximum value E max shown in equation (9). However, °°8°゛ in equation (9) is '2N
” is.

FIG. 6 shows the overlap E with respect to the gap ΔA between the trays 7. As shown, equation (9) is a solid line, and equation (11)
The formula is shown as a dashed line.

As can be seen from this figure, if the gap ΔA between the trays 7 is 60 mm, the overlapping margin E of the trays 7 is the maximum value Emax = 170 mn+ from equation (9), and (11
), the minimum value Emin = 107.5 mm.

As mentioned above, in the former case, the moving speed υ = 50 m/
min, and the centrifugal angular acceleration α=0.28 g. Similarly, in the latter case, the centrifugal angular acceleration α=0.32g. Therefore, when the overlap distance E is set to less than the equation (11), the packet 6 tends to fly out from the tray 7.

In the embodiment shown in FIG. 7 (hereinafter referred to as the third embodiment), the pitch circle diameter 2R of the sprocket 1.2 is changed to the pitch diameter 2R of the first embodiment.
This is a case in which the number of links N per one tray 7 is 3, and the number of teeth Z of the sprocket 1.2 is 10. Guide rollers 53a, 53b, and 53c are located near the outer end 26 of the tray 7. The guide roller 53C is located in the gap ΔA. 2R of sprocket 1°2 is 1.780mm. Length P of link 51
is 550 mm, which is larger than that of the first embodiment.

In this case, when the moving speed υ=50 m/min, R=5
The centrifugal angular acceleration a = 0.05 g at the 45 mm position, and similarly, the centrifugal angular acceleration α = 0.28 g at the moving speed υ = 120 m/min, so the packet 6 does not fly out.
A movement of about 120 m/min can be obtained. However, only specifications different from the first embodiment are shown.

Gap between comrades of tray 7 △A: 850mm Overlap margin of tray 7 E: 680mm Length of link 5a P: 550mm Pitch circle diameter of sprocket 1.2 2R: 1.780+no+sprocket 1
．． 2 rotation speed N: 8.9 rpm (v = 50 m/m1
nt 21.4 rpm (υ=120m/m1n) In this case as well, as is clear from FIG. End 2
5 and the extension line of the inner end 25.

In this third embodiment, links 52 constituting the chain 5
The number of connections is N=3. This is because compared to the first and second embodiments (when N=4, the limit is υ=lOOm/min), this embodiment allows the rotation speed of the sprocket 1.2 to be smaller, so the moving speed υ to 120 m/+++i
You can get up to n. In other words, since equation (9) is generally replaced by equation (12), when N decreases from 4 to 3, the overlap E increases and the sprocket l
, 2 can be increased.

Incidentally, if there is a large gap 2 between the inner edge 27 of the packet 6 placed on the tray 7 and the inner edge 25 of the tray 7, as a modification of the second embodiment, as shown in FIG. , the fourth embodiment), the inner corner end 25 of the tray 7
If a is configured by cutting out the overlap margin E from the equation (9), the overlap distance E becomes the equation (13).

Here, if the overlapping distance E in this embodiment is equal to the overlapping distance E in FIG. 5 and 2R of the sprocket 1.2, then the gap β
ΔA becomes smaller in proportion to the value of , and space can be saved more than in the second embodiment.

〔Effect of the invention〕

As described above, according to the present invention, the tray runs at high speed (30m
/ffl1n or higher).

[Brief explanation of the drawing]

FIG. 1 is a plan view of a rotating section of a horizontal rotating shelf according to an embodiment of the present invention, FIG. 2 is a vertical sectional view of the rotating section of FIG. 1, and FIG. 3 is a plan view of the entire horizontal rotating shelf. Figure 4 is a plan view for explaining the positional relationship of the rotating parts in Figure 1, Figure 5 is a plan view of the rotating part of a horizontal rotating shelf according to another embodiment of the present invention, and Figure 6 is a tray of the present invention. FIG. 7 is a plan view of a rotating part of a horizontal rotary shelf according to another embodiment of the present invention;
FIG. 8 is a plan view of a rotating section of a horizontal rotating shelf according to another embodiment of the present invention. 1, 2---1 sprocket, 3------1 drive device, 5------chain, 7---1 tray, 6------packet, 21- --1--Partition wall, 51-----Link, 52-----Bin, 5
3a, 53b, 53c, 53d---Guide Rollei 2 Flash 3 Figure

Claims (1)

[Claims] 1. Two sprockets arranged at intervals in the horizontal direction and with the center of rotation in the vertical direction, a drive device that rotates at least one of the sprockets, and a drive device that is hung endlessly on the two sprockets. a chain, a guide roller installed at each connecting point between the links constituting the chain and engaging with the teeth of the sprocket, and a guide roller for carrying a load and fixed to two adjacent connecting points. a plurality of trays installed at a ratio of one to at least three links, and when the tray is located in a rotating part constituted by the sprocket, the inside of the tray and the outside of the sprocket are connected to each other. The four guide rollers, which overlap each other and are installed at connection points of the at least three links in the pivoting portion, are located between the inner end and the outer end of the tray. Features a horizontal rotating shelf. 2. The horizontal rotating shelf according to claim 1, wherein the connection point between the tray and the chain is provided near the center of gravity of the load placed on the tray. 3. Two sprockets spaced apart horizontally and with the center of rotation in the vertical direction, a drive device that rotates at least one of the sprockets, a chain that hangs endlessly around the two sprockets, and a load. It is made up of a plurality of trays fixed to the links constituting the chain, and the inner end of the tray is located inside the connection point with the chain, and the tray and the sprocket are connected to each other. A horizontal rotary shelf characterized in that an overlapping margin E is provided between Emin and Emax. Emin=(A+ΔA)/N・sin(2π/Z)Em
ax=(A+ΔA)/2Ntan(π/Z)−A/2t
an(Nπ/Z) A: Tray width ΔA: Gap between trays Z: Number of sprocket teeth N: Number of links per tray