JPH02291395A - Chain block provided with self-braking device - Google Patents

Abstract

PURPOSE:To decrease the generation of a metallic sound at the time of operation and to reduce noise by producing the rotating force in the opposite direction to the load direction, with the mesh point of a differential planetary gear with a sun gear as the cardinal points by the rotating force in the load direction of the differential planetary gear to self-brake the differential gear. CONSTITUTION:When a load is applied to the lower hook of a load chain, a load gear 24 is pressed and meshed with the large-diameter tooth portion 18 of a differential planetary gear 16 and a center floating tooth portion 20 while backlash is eliminated, to force the large-diameter tooth portion 18 to rotate in the load direction, so that the rotating force in the same direction is also produced in a small-diameter tooth portion 17. Accordingly, the differential planetary gear 16 is about to rotate in the reverse load direction, with the mesh point with the sun gear 12 as cardinal points and is self-braked at one point within the load side radius region of the sun gear 12. When a manual chain is operated in such a condition, the center floating gear 20 is rotated to push up load quietly. In this arrangement, a click and a ratchet are not used for braking load, so that the generation of a metallic sound is decreased.

Description

[Detailed description of the invention] a. INDUSTRIAL APPLICATION FIELD The present invention relates to a transmission device, and more specifically to a chain block to which a self-braking device in a rotating body is applied.

B. Conventional technology Conventional chain blocks have the same braking force as
Since a gourd wheel and brake plate are used, a metallic sound is generated from the gourd wheel, brake plate, etc. when operated, and this may cause problems when used in specific places, indoors, or at night in a quiet environment. there were.

Furthermore, during the frying process, the melons come off the melon wheel and the load is placed on the arms and elbows of the worker, which consumes a large amount of human energy and poses a health and hygiene problem.

C. Problems to be Solved by the Invention As mentioned above, conventional chain blocks are sometimes subject to environmental restrictions and have health and hygiene problems. In order to improve these points, the technical object of the present invention is to provide such a chain block.

D. Means for Solving the Problem The first invention is a differential planetary gear (hereinafter referred to as a differential planetary gear) whose small diameter teeth are meshed with the teeth of a sun gear via a holding shaft fixed to a rotating holding plate. The differential planetary gear mentioned above is a gear that consists of teeth of different diameters, the smaller diameter of which is meshed with the teeth of the sun gear, and revolves on the sun gear). between the large-diameter teeth of the differential planetary gear and the teeth of a center idler gear that is rotatably loosely fitted on the main shaft of the sun gear; its base on the main shaft of the sun gear; In a self-braking device for a rotating body in which a load gear is mounted in a meshing manner by an arbitrary means on a arm rod which is loosely fitted in a rotatable manner, the main shaft of the sun gear is Both ends are held unrotatably by a gear cover and an outer plate by arbitrary means, and the chain pulley has a plurality of chains connected and held at arbitrary intervals between the gear cover and the outer plate by stay bolts. A hand chain wheel is held rotatably at a fixed position between the side plate of the one side and the outer plate, and a hand chain wheel is fixed by any means on the cylindrical boss of the center idler gear. An upper hook is rotatably attached to the upper part between the plurality of side plates via a pin, and a lower hook is attached to one end of the chain chain installed astride the chain wagon. The hand chain wheel has an endless hand chain wound around it.

In the second invention, the inside of the sun gear is formed into a recessed body having an arbitrary shape.

In a third aspect of the present invention, the load transmission linking rod and the chain pulley are fitted and connected to an arbitrary number of protrusions carved on each side surface via a fitting groove.

In a fourth invention, the hand chain wheel is fitted and fixed to a spline shaft at the tip of a cylindrical boss of the center floating gear.

In a fifth aspect of the invention, the small-diameter tooth portion of the differential planetary gear is formed integrally with the holding shaft.

In a sixth invention, the load shaft is formed integrally with the flange.

Ho. Operation In the first invention, when a load is applied to the lower hook attached to the tip of the load chain, this load is transmitted to the load gear via the load transmission linkage rod, and this load gear is The large-diameter teeth of the planetary gear and the teeth of the center floating tooth are press-fitted to eliminate backlash, and the large-diameter teeth of the differential planetary gear are rotated in the direction of the load. Therefore, a rotational force in the same direction is generated in the small-diameter gear portion integrally formed with the large-diameter tooth portion, and as a result, the differential planetary gear rotates from the meshing point with the sun gear as a base point. The differential planetary gear attempts to roll in the opposite direction to the load and conflicts with the load, and is self-braking at a predetermined point within the radial area on the load side of the sun gear, so that the differential planetary gear is prevented from rolling. Under such conditions, when input is applied to the hand chain of the hand chain wheel, this input is transmitted to the center idler gear via the cylindrical boss, and the load is quietly lifted up.

In order to lower the load, input is applied to the hand chain in the opposite direction to that used for hoisting, the center idler gear rotates in the opposite direction and the load is lowered quietly.

F. Examples Before explaining the embodiments of the present invention, first of all, Figures 1 to 4 are extracted from the invention of Japanese Patent Application No. 62-160526, which is the basis of the present invention, and The diagram will be excerpted and explained as Figure 5. That is, FIG. 1 is a plan view showing the basic structure in a simplified manner. 2 to 4 show other embodiments; FIG. 2 is a plan view, FIG. 3 is a front view, and FIG. 4 is a sectional view taken along line A-A in FIG. FIG. 5 (FIG. 8 in the original application) is a schematic diagram showing an experimental example based on the embodiments shown in FIGS. 1 to 4.

Embodiments of the present invention will now be described with reference to FIGS. 6 to 26, with reference to the original application. In other words, the second part of the original application
In Fig. 4, the sun gear 12 (hereinafter referred to as sun gear 30)
As shown in Fig. 9, the side surface of the first example is formed directly from the periphery of the tooth root in the axial direction with a step of about 1/2 of the tooth width, and the side surface of the first example is They are formed parallel to each other and are smooth in the centripetal direction, and furthermore, a conical depression is formed in the central part parallel to the outer line of the conical boss 34, and the main shaft 11 (hereinafter referred to as the main shaft 31) is formed in the central part. ) A grooved shaft hole 33 for the key 32 for fitting is passed through. Further, the conical boss 34 has an arbitrary P as shown in FIG.
, a plurality of screw holes 35...35 are threaded on the D line.

Reference numeral 36 denotes a gear cover formed in a cross-sectional shape, and as shown in FIG. 12, a hole 38 is carved inside the central boss 37, and on lines P and D at arbitrary positions around the hole 38, as shown in FIG. A plurality of mounting holes 39...39 are drilled, and a plurality of mounting screw holes 40...40 are drilled in the periphery of the end face. The aforementioned sun gear 30 and gear cover 36 are connected to bolts 41...35 through screw holes 35...35 of the sun gear 30 examples and mounting holes 39...39 on the gear cover 36 side, as shown in FIG. It is screwed together with 41.

The main shaft 31 consisting of a plurality of steps is connected to the shaft hole 3 of the sun gear 30.
3 and the step at its base as shown in Fig. 12,
Fitted into the hole 38 inside the boss 37 of the gear cover 36,
As shown in FIG. 9, the sun gear 30 is fixed to the shaft hole 33 of the sun gear 30 with a key 32.

As shown in FIG. 9, in the step part at the top of the sun gear 30, there is a rotation holding plate 13 (hereinafter referred to as rotation holding plate 42) with a bearing fitted into a boss 43 at its base. 44, 44, and a bearing (a dry bearing in the illustrated example) 46 is fitted into the boss 45 at the tip.
are fitted.

The holding shaft 15 (hereinafter referred to as the holding shaft 48) integrally formed with the small-diameter tooth portion 17 (hereinafter referred to as the small-diameter gear 47) is inserted and penetrated into the aforementioned bearing 46. is extended outwardly, and a large-diameter tooth portion 1 is attached to this extended portion.
8 (hereinafter referred to as large-diameter gear 49) is fixed via a key 50. That is, this large-diameter gear 49 and the aforementioned small-diameter gear 47 together constitute a differential planetary gear 16 (hereinafter referred to as a differential planetary gear 51). The tooth portion 52 of the small diameter gear 47 is connected to the sun gear 3.
It is arranged to mesh with the tooth portion 53 of 0 so that it can roll freely.

The center floating gear 20 (hereinafter referred to as the center floating gear 54) is rotatably fitted into the stepped portion of the upper plate of the rotation holding plate 42 via bearings 55, 55 fitted inside the center floating gear 20, The boss in one example (upper side in the figure) is formed in a cylindrical shape (hereinafter referred to as a cylindrical boss) 56 with a plurality of steps, extends close to the end surface of the main shaft 31, and has an inner diameter of It is formed slightly larger than the small diameter portion of the main shaft 31 described above, and a spline shaft 57 is carved in a portion of arbitrary length near the tip, as shown in FIG. A thrust washer 58 is fitted into the gap between the rotation holding plate 42 and the rotation holding plate 42 described above.

At the stepped portion of the cylindrical boss 56 of the center floating gear 54,
Adjacent to the aforementioned center floating gear 54, the arm rod 21 (hereinafter referred to as arm rod 59) rotates via a bearing (a dry bearing in the illustrated example) 61 fitted into a boss 60 at its base. As shown in Fig. 19, there are a plurality of mounting holes 62...6 for hexagonal socket bolts around the tip.
2 is bored, and a pin hole 63 is bored near the tip.

As shown in FIGS. 14 and 15, the arm pole 59 includes a load shaft 65 formed integrally with a flange 64, and a plurality of mounting screw holes 66 bored in the flange 64.
66, and are screwed into a plurality of hexagon socket bolt bolt mounting holes 62...62 on the above-mentioned arm pole 59 with hexagon socket bolts 67...67.

A load gear 24 (hereinafter referred to as a load gear 68) is loosely fitted onto the load shaft 65 via a bearing 69 fitted therein so as to be freely rotatable at a fixed position.

As shown in FIG. 9, one side of the tooth portion 70 of the load gear 68 is connected to the center of the tooth portion 70, as shown in FIG. floating gear 5
The second side is forcibly engaged with the tooth portion 71 of No. 4, eliminating backlash, and the second side is tightly engaged with the tooth portion 72 of the large diameter gear 49 of the differential planetary gear 51, as shown in FIG. They are placed in a natural state with backlash.

A thrust washer 73 is fitted into the gap between the arm rod 59 and the center floating gear 54.

Adjacent to the arm rod 59, sandwiching the thrust washer 74,
As shown in FIGS. 9, 13, and 18, the load transmission linking rod 75 has a shaft hole 77 bored in a boss 76 at its base.
The rod body is rotatably fitted onto the cylindrical boss 56 through the cylindrical boss 56, and the rod body is bent into a square shape, and the tip is formed into a U-shape, and pin holes 78, 78 are passed through the ends. ing. As shown in FIGS. 13, 14, and 18, a plurality of (four in the illustrated example) protrusions 79...79 are carved on the upper end surface of the boss 76 of the base.

As shown in FIG. 18, between the pin holes 78, 78 at the tip of the load transmission linking rod 75 and the pin hole 63 at the tip of the arm rod 59, as shown in FIG. Figures 13 and 14
As shown in the figure, a short chain, that is, a connecting chain 8
0 are connected by pins 81 and 82, respectively. The load is transferred to the load gear 6 via this connecting chain 80.
8.

In contact with the load transmission linking rod 75, a chain wheel (the illustrated example is a sprocket wheel) 83 is connected to the
As shown in the figure, the left and right bosses 84, 84 are rotatably fitted onto the cylindrical boss 56 through the shaft hole 122.
Locking grooves 85, 85 are carved at arbitrary positions, respectively, and an arbitrary number (four in the illustrated example) of fitting grooves are formed on one end of the boss 84, that is, the end face on the side that contacts the load transmission linking rod 75. Groove 86
...86 are carved, and the aforementioned load transmission linking rod 75 is inserted through the fitting grooves 86...86 as shown in FIGS. 9 and 18.
The projections 79...79 of the boss 76 are fitted and connected, respectively.

As shown in FIG. 9, the left and right bosses 84 of the chain wagon 83,
At 84, the cargo chain side plates 87 and 88, which are formed with bent ears in the left cross section of the outer periphery, are connected to the aforementioned cargo chains via bearings 91 and 92 fitted in respective bosses 89 and 90. car 83
It is held in place so that it can rotate freely. each side plate 87;
88, as shown in FIG.
An arbitrary number (4 in the illustrated example) of connecting holes 93...93 and 93'...93' are bored in the axial direction on line D. Also, on the bent edge portion around the side plate 87 on the side of the sun gear 30, there is a first
As shown in FIG. 0, a plurality of screw holes 94...94 are threaded in the centripetal direction, and the mounting holes 40...94 of the gear cover 36 described above are threaded in the centripetal direction.
40 and are integrally screwed together via a plurality of bolts 95...95.

As shown in FIGS. 6 and 9, the side plates 87 and 88 are connected to a plurality of stepped stay bolts 96...96 and nuts 97...97 through respective connecting holes 93...93, 93'...93.
are connected by screws. As shown in FIGS. 9 and 16, the inner side of each of the side plates 87 and 88 is provided with a retaining ring 98.
, 98, the locking groove 85 of the boss 84 of the chain pulley 83
, 85 to hold the chain wagon 83 in a fixed position.

As shown in FIGS. 6, 7, and 9, a locking bar 100 of a cargo chain 99 is located at an arbitrary position on the opposite side of the load between the side plates 87 and 88, with both ends of the locking bar 100. The aforementioned side plate 8
7 and 88 by arbitrary means (not shown). One end of the cargo chain 99 is locked to this locking bar 100 by arbitrary means (not shown).

As shown in FIGS. 9 and 21, the center floating gear 5
The spline shaft 5 is carved at the tip of the cylindrical boss 56 of 4.
7, as shown in FIGS. 23 and 24, there is a hand chain car 1.
01 is fitted and fixed to the inner peripheral surface of the shaft hole 103 of the boss 102 via a groove 104 carved in an indented manner. A thrust washer 105 is fitted into the gap with the chain pulley 83.

As shown in FIG. 11, the outer plate 106 extends from a plane toward a housing 108 for a bearing 111 toward a boss 107.
A small-diameter shaft hole 109 is further carved from the housing 108 toward the back. The peripheral portion of the outer plate 106 is bent to have a square cross section as shown in the figure, and a plurality of connecting holes 110 . As shown in FIG.
Bearing 111 fitted into housing 108 of 07
Fitted onto the spline shaft 57 of the cylindrical boss 56 via the
A small-diameter shaft hole 109 at the center is fitted into the tip of the main shaft 31 .

And between the chain wheel 101 and the thrust washer 1
21 are fitted into the stay bolts 96, .

As mentioned above, the main shaft 31 is connected to the gear cover 36 and the outer plate 10.
6 and is securely held in a non-rotatable manner. The retaining ring 113 is in contact with the outer surface of the bearing 111, as shown in FIG.
14 is fitted and locked. By doing so, the aforementioned center floating gear 54 has one side connected to the main shaft 3.
Vibration from side to side is suppressed at the first stepped portion and the second side by the aforementioned retaining ring 113.

As shown in FIGS. 6, 7, and 8, the upper parts of the side plates 87 and 88 of the chain wagon are extended into an arbitrary shape (the side shown is F-shaped), and a pin hole (not shown) is provided near the top. ) are each penetrated. The upper hook 116, which is rotatably attached to the hanging fitting 115 by an arbitrary means (not shown), is attached to the pin hole (not shown) of the above-mentioned hanging fitting 115.
Then, the headed pin 11 is inserted through the pin holes in the side plates 87 and 88 of the aforementioned cargo vehicle side plates (the pin holes are not shown).
7, and a split pin 118 is inserted into the tip of the headed pin 117 to prevent it from falling off.

As shown in FIG. 20, a lower hook 119 is rotatably connected in one direction to the tip of a chain chain 99 installed astride the chain pulley 83 via a connecting pin 123.

As shown in FIGS. 7 and 8, a hand chain 120 is wound around the hand chain wheel 101 in an endless manner.

The operating state of the chain block of the present invention constructed as described above will be explained with reference to the schematic diagram of FIG. 25. That is, when a load W is applied via the lower hook (omitted) 119 to the chain block chain 99 suspended via the upper hook 116 by any means, this load W is The transmission is transmitted to the load gear 68 via the connecting rod (omitted) 75, and the load gear 68 further transfers its tooth portion 70 to the tooth portion 7 of the center idler gear 54.
1 and the teeth 72 of the large-diameter gear 49 of the differential planetary gear 51, respectively, to eliminate backlash, and the differential planetary gear 51 is self-braking by embracing the rotational force thereof. .

The types, sizes, etc. of the sun gear 30, differential planetary gear 51, center floating gear 54, load gear 68, etc. used in the embodiments of the present invention are as per the original patent application 1986-160.
Since this is exactly the same as No. 526, the more detailed explanation of the operating state of the present invention described above will be substituted by quoting and excerpting the experimental examples of the original application. (The original text remains unchanged below. In the cited examples, notes have been inserted where the meaning is thought to be unclear.) Section 8
According to the schematic diagram in the figure (note: Fig. 5 in the present invention),
An experimental example will be explained based on the examples shown in FIGS. 1 and 7 (note: FIGS. 1 to 7). In this experimental example, a load transmission chain wheel 46, an input chain wheel 56, an arm pole 21, and a small arm pole 71 (
Note: The embodiment shown in FIG. 7 in the original application is omitted, and a load cable 27 is fastened to the small shaft 23 of the load gear 24, and an input cable 72 is connected to the side surface of the center floating gear 20. Its one end is locked and wound. And the load gear 24 is
As shown in FIG. 7, it is assumed that the small arm pole 71 is attached.

The dimensions of each part corresponding to each symbol shown in FIG. 1 are as follows.

Code Name Model Number of teeth: 12 Sun gear Module 2 10016-17 Small-diameter teeth of differential planetary gear Module 2 20 16-18 Large-diameter teeth of differential planetary gear Module 2
50 20 Center floating gear module 2 2524 Load gear module 2 25 In the schematic diagram showing the experimental example of the present invention installed as above, load gear 2
The teeth 25 of No. 4 are placed in even and light engagement with the large-diameter teeth 18 of the differential planetary gear 16 and the teeth 26 of the center floating gear 20.

In this state, the load gear 24 is connected via the load cable 27.
When a load K is applied to the load gear 24, this load K causes the tooth portion 25 of the load gear 24 to be damaged, the large diameter tooth portion 18 of the differential planetary gear 16 on both sides, and the tooth portion 26 of the center idler gear 20. The differential planetary gears 16 are pressed evenly and deep into each other's teeth until they stop contacting each other, eliminating backlash and strongly engaging in the load direction, and developing a complex load distribution. We will try to analyze the effect of these forces, which are made to oppose each other in opposite directions.

First, when a load K is applied to the axial center P of the load gear 24, this load K is divided into the axial center O direction of the center idler gear 20 and the axial center N direction of the differential planetary gear 16. .

Therefore, a line connecting the axis P of the load gear 24, the meshing point L between the load gear 24 and the center idler gear 20, and the axis O of the center idler gear 20, that is, the line P-
The angle d' formed by L-O and the load line D-K is the area of action in the direction of the load, and the line of force action in this area is P-Y, which is the angle d' formed by dividing d' into two. , is a line. Then, a line O-H, which intersects the above-mentioned line P-Y at right angles with the axis O of the center floating gear 20 as a starting point, becomes the torque in the load direction region.

This torque attempts to rotate the aforementioned load gear 24 and center planetary gear 20 in the load direction while maintaining the meshed state. Here, if R' of the sun gear 12 is 100, then O
-H is actually 29.

Also, the axis P of the load gear 24 described above, the load gear 24 described above, and the large diameter tooth portion 1 of the differential planetary gear 16 described above.
The angle d2 formed by the line P-M-N, which connects the meshing point M with 8 and the axis N of the differential planetary gear 16 mentioned above, and the load line PK is the input direction. In the region of action, the line of action of the force in this region is the P-X ray that bisects the aforementioned d2. And the small diameter tooth portion 17 of the aforementioned differential planetary gear 16
and a line G that intersects the load action line P-X at right angles with the meshing point G of the sun gear 12 with the teeth 19 as a base point.
−J is the torque in the input direction region.

If R' of the sun gear 12 is 100, then G-J is actually 31.

In this way, the large-diameter tooth portion 1 of the aforementioned differential planetary gear 16
8 is rotated in the direction of the load by torque G-J and is about to be rotated clockwise in the figure, so the small diameter tooth portion 17 formed integrally with the large diameter tooth portion 18 described above also rotates in the same direction. As the sun gear 12 attempts to rotate, the torque toward the input direction, that is, the upward direction in the figure, is balanced by the torque O-H toward the load direction, and the aforementioned differential planetary gear 16 is rotated on the toothed portion 19 of the sun gear 12. As a result, the load K is self-braking and remains in the lock due to static friction. The above-mentioned self-braking point was about 47 points in the centrifugal direction from the axis O. (The numbers indicating the load reciprocity state mentioned above are
In addition, in this experimental device, in order to cause the differential planetary gear 16 to roll in the opposite load direction, that is, in the input direction, by an external force, the static friction force that remains in the engagement must be (a force that overcomes static friction) is applied to the center floating gear 2 according to the desired output.
0 through the input cable 72 wound around
Just put it in the direction. With this input, R2 (center floating gear 20) is oriented in the direction of arrow C (the same applies hereafter) indicated by the chain double-dashed line, R3 (load gear 24) is oriented in the direction of arrow D, and R4 (differential planetary gear 16) is oriented in the direction of arrow D. rotates in the direction of arrow E and rolls on the sun gear 12 in the direction of arrow F. The peripheral speeds of the center floating gear 20 (R2) and the large-diameter tooth portion 18 of the differential planetary gear 16 (R4) are constant (note: the same).

Further, the input operation in the embodiment of the present invention shown in FIGS. 2 to 5 is performed by an input chain wheel 56 and an input chain 60 fixed on the boss 37 of the center idler gear 20.

In the above experimental example, the differential planetary gear 16 is the sun gear 1.
Based on the assumption that the vehicle was traveling on the toothed portion 19 of No. 2 at a height of 100 m/m (hereinafter m/m units are omitted) in the input direction, that is, in the direction of arrow F in the figure, the input and output, That is, the speed relationship between the center floating gear 20, the differential planetary gear 16, and the load K will be explained.

a. Size ratio of the small diameter tooth portion 17 and the large diameter tooth portion 18 of the differential planetary gear 16: 20:50 = 1:2.5 b. Traveling distance at load point (47 from the shaft center) 100 x 47/
100=47 c. The peripheral speed of the large-diameter tooth portion 18 of the differential planetary gear 16 is transferred to the input cable 7 of the center idler gear 20 via the load gear 24.
Length of rolling out 2 100 x 25 = 250 d. If it is assumed that the key 34 of the sun gear 12 is removed and the entire gear group (gear group) is rotated in the input direction while the differential planetary gear 16 and the sun gear 12 remain meshed, The center floating gear 20 is rotated equiangularly and in the same direction as the differential planetary gear 16, that is, in the input direction.
2 is added as an extra length. Such a dynamic is also referred to as dislocation of the center floating gear 20. (The same applies hereinafter) The dislocation of the center floating tooth 20 described above is determined by the following equation. (However, the movement of the small diameter tooth portion 17 of the differential planetary gear 16 is on the P.C.D. of the sun gear 12 and is assumed to be 100.) 50×3.14/(100×2)×3.14 /100=
25 In the above formula, 50 is the P. of the center floating gear 20. C
．． D (100×2) is P. of the sun gear 12. C. D100 is the moving distance of the small diameter tooth portion 17 of the differential planetary gear 16.

e. Final length 250+25 of which the input cable 72 is paid out
=275 f. Load reduction ratio: 47:275=1:5.85 As described above, in this experimental example, the load is self-braked at approximately 1/6 deceleration. This is an area that cannot be reached using conventional mechanisms. Also, the torque in the input direction range, G-J, as mentioned above,
The torque in the load direction region, the ratio of O-H is 31:29, which is slightly positive on the input direction side, but this positive amount becomes potential energy on the input region side and is It stays in the planetary gear 16.

As mentioned above, in the original application, the reduction ratio between the load and the input is approximately 1:6, but in the present invention, the self-braking position is approximately equal to R of the trailer 83. Since it is a point of 34 m/m, the reduction ratio is approximately 1:8 according to the following equation.

(100×34/100):275=1:8.07 (rounded off to the nearest whole number) In the above formula, 100 in the former is the standard movement distance.

The latter 100 is the radius of the sun gear 30. The final speed reduction ratio when using the hand chain car 101 is approximately 1:33 according to the following equation. (Round to the nearest whole number) 283.07 (P, D of hand chain car 101) ÷ 67.62
(P, D of carts and carts 83) x 8 = 33.4 In the original application, the gear group (sun gear 12, differential planetary gear 16, center In the self-braking device using a combination of the floating gear 20 and the load gear 24), the self-braking point is approximately 47 m/m in the centrifugal direction, as shown on the experimental side of FIG. This 47m
Strictly speaking, the point /m is the limit braking point. In other words, the area between the points 47 m/m in the centrifugal direction apart from the axis is a self-braking zone, and when this 47 m/m point is exceeded in the centrifugal direction, the self-braking of the load W is broken and the above-mentioned condition occurs. The load W drops.

In the case of the present invention, the self-braking point is in the centrifugal direction,
The position is approximately 34 m/m from 1/2P and D of the chain car 83, but if necessary, the R of the chain car 83 mentioned above.
can be set to a size of up to 47 m/m. If the distance exceeds 47 m/m, the load W will not be self-braking as described above.

That is, as shown in FIG. 26, by increasing the diameter of the chain pulley 83 and setting its R to 52,
If the load W is set at a point exceeding 7 m/m, this load W causes the differential planetary gear 51 to roll in the load direction.
Load W is not self-braking. Therefore, in the case of the embodiment of the present invention shown in the drawings, the self-braking point of 47 m/m must not be exceeded.

to. Effects of the Invention Since the present invention is configured as described above, it exhibits the effects described below.

Since parts such as gourds, gourd wheels, and brake plates are not used to brake the load, it is quiet and produces little metallic noise during operation, and can be used in specific locations or at night, adapting to the static environment. .

With conventional chain blocks, the melons come off the melon wheel when they are turned up, so the load is directly transmitted to the arms and elbows of the human body, and a large amount of energy is consumed to resist this. Even during frying, the load is self-braking within the device, so it is easy to operate, consumes little energy, and is safe.

[Brief explanation of the drawing]

FIGS. 1 to 5 are drawings quoting Examples and Experimental Examples of Patent Application No. 160526 of 1988. FIG. 1 is a plan view showing the basic structure in a simplified manner. FIG. 2 is a plan view showing a specific example. FIG. 3 is a front view of FIG. 2. FIG. 4 is a sectional view taken along line A-A in FIG. 2. FIG. 5 is a schematic diagram showing an experimental example based on the embodiments shown in FIGS. 1 to 4. (Original application, Japanese Patent Application No. 62-160526
Figure 8 in the issue. 6 to 26 show embodiments of the present invention. FIG. 6 is a plan view with the cargo chain and hand chain omitted. FIG. 7 is a cutaway front view of one end of the load chain including the lower hook and a part of the hand chain. FIG. 8 is a right side view showing both ends of the load chain including the lower hook and a part of the hand chain with the locking bar omitted. FIG. 9 is a cross-sectional view taken along the line A-A in FIG. 7, with the cargo chain and hand chain omitted. FIG. 10 is a side view of the chain wheel side plate on the gear cover side, with a plurality of sections cut away. FIG. 11 is a sectional view of the outer panel. FIG. 12 is a plan view of the gear cover shown with the upper and lower sides cut away and the left and right parts cut away. FIG. 13 is a sectional view taken along line B-B in FIG.
Assume the above-mentioned FIG. 9 as the entire circumferential plane before cutting, B-
The cross section taken along line B is shown. FIG. 14 is a sectional view taken along the line CC in FIG. 13, but the sun gear is omitted. FIG. 15 is a bottom view of the load shaft in FIG. 14. FIG. 16 is a plan view of the chain wagon. FIG. 17 is a front view of FIG. 16. FIG. 18 is a plan view showing the coupled state of the load transmission coupling rod and the chain car, with a part of the chain car cut away and the load transmission coupling rod cut away. FIG. 19 is a plan view of the arm pole. FIG. 20 is a front view of the lower hook connected to the tip of the cargo chain. FIG. 21 is a plan view of a spline shaft provided at the tip of a cylindrical boss. FIG. 22 is a sectional view taken along the line DD in FIG. 21. FIG. 23 is a plan view of the hand chain wheel, with both ends cut away. FIG. 24 is a sectional view taken along the line E-E in FIG. 23. FIG. 25 is a schematic diagram showing the operating state of the embodiment of the present invention. FIG. 26 is a schematic diagram showing a prohibited example of the present invention. Figure 27 shows the original application, ie, Japanese Patent Application No. 62-160526.
This is a reference drawing of Figure 7 in the issue. Main symbols (Figures 6 to 26) 30...Sun gear, 31...Main shaft, 36...Gear cover, 42
...Rotating holding plate, 47...Small diameter gear, 48...Holding shaft, 49
... Large diameter gear, 51 ... Differential planetary gear, 56 ... Cylindrical boss, 57 ... Spline shaft, 59 ... Arm rod, 65 ... Load shaft, 6
8... Load gear, 75... Load transmission linking rod, 79... Convex body,
80...Connection chain, 83...Chain truck, 86...Fitting groove, 8
7... Chain chain car side plate, 88... Chain chain car side plate, 96... Stay bolt, 99... Chain chain, 101... Hand chain car, 104
...concave groove, 116...upper hook, 119...lower hook, 12
0...Hand chain chain. Cited Document: Patent Application No. 160526 in 1988 Title of Invention Self-braking method and device for a rotating body

Claims (1)

[Claims] [1] Holding shaft (15) fixed to rotating holding plate (13)
The differential planetary gear (1) has its small-diameter teeth (17) meshed with the teeth (19) of the sun gear (12) through the
6) Large diameter tooth portion (18) of the differential planetary gear (16)
and a tooth portion (26) of a center idler gear (20) rotatably loosely fitted onto the main shaft (11) of the sun gear (12).
The base of the sun gear (12) is connected to the main shaft (
11) A load gear (24) mounted rotatably on the arm rod (21), which is rotatably loosely fitted on the upper side or coaxially with the differential planetary gear (16), is meshed and mounted. In the self-braking device for a rotating body, the main shaft (11) of the sun gear (12) is held unrotatably at both ends by a gear cover (36) and an outer plate (106). Chain car (83)
A plurality of side plates (87) and (88) are connected and held at arbitrary intervals by stay bolts (96)...(96) between the gear cover (36) and the outer plate (106). Between,
It is rotatably held at a fixed position, and the one side plate (88
) and the side plate (106), the hand chain wheel (
101) is the cylindrical boss (
56), and a pin (117) is fixed to the upper part between the plurality of side plates (87) and (88) by any means.
The upper hook (116) is rotatably attached to the chain chain (99) which is installed astride the chain truck (83).
A lower hook (119) is attached to one end by arbitrary means, and a hand chain (12) is attached to the hand chain wheel (101).
A chain block equipped with a self-braking device characterized in that 0) is wound endlessly. [2] The chain block equipped with a self-braking device according to claim 1, wherein the sun gear (12) has an interior recessed in an arbitrary shape. [3] The load transmission linkage rod (75) and the chain truck (83) are
The self-braking device according to claim 1, characterized in that the self-braking device is fitted and connected via an arbitrary number of protrusions (79) carved on each side surface and a fitting groove (86). chain block. [4] Cylindrical boss (56) of center floating gear (20)
2. The chain block equipped with a self-braking device according to claim 1, wherein the tip of the is formed as a spline shaft (57). [5] The small diameter tooth portion (17) of the differential planetary gear (16) is
A chain block equipped with a self-braking device according to claim 1, characterized in that it is formed integrally with the holding shaft (15). [6] The chain block equipped with a self-braking device according to claim 1, wherein the load shaft (65) of the load gear (24) is formed integrally with the flange (64).