JPS60132198A - Cam locking type flange coupling - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement of a cam l-cock type flange, which is improved so that no bending stress is generated on the shaft supporting the locking rotary cam during locking.

The cam 1 cock type flange joint is suitable for use at the end of pipes, etc.
This is a joint configured to use a cam to tightly fix the flanges that are bent together, and compared to normal flange joints,
It has the advantage of being able to connect pipes easily, quickly and reliably without the need to tighten bolts.

First, the structure and problems of a conventional cam lock type flange joint will be explained with reference to FIGS. 1 and 2.

The flange indicated by the symbol l in the figure is a flange fixed by welding or the like to the end of a suitable pipe material 2, and as shown in FIG. are formed at equal intervals. The cam support portion 3 is constructed by integrally extending an ear portion 4 that projects slightly radially outward from the reference outer circle of the flange l. 5 is a stepped screw that rotatably supports the cam body 6, and has a head 7, a large diameter shaft portion 8 that supports the cam body 6, and a tip & [threaded portion 9]. , the Mjm hole IO of the cam body 6 is rotatably fitted into the large diameter shaft part 8, and the female thread 1 bored in the above-mentioned 4 part 4 is inserted.
By screwing the tip male threaded portion 9 onto the cam body 6
is rotatably supported on the ear portion 4.

On the other hand, the cam body 6, as shown in FIG. It has a side view shape in which a flange-shaped cam part 13 extends radially from a boss part 12 provided with an opening hole 10. A cam surface that comes into contact with the outer surface !4a of the side flange 14 and functions to press the bend against the flange 14, and has an inclined surface inclined in the circumferential direction. This is a concave groove into which a rod-shaped tool (not shown) for rotating and lifting the body 6 is fitted.Furthermore, a criss-nino pull 16 is provided on the head 7 of the step screw 5, and from this 41- The applied grease lubricates the contact portion between the large diameter shaft portion 8 of the stage I'Nj lock 5 and the through hole 10 of the cam body 6.

As shown in FIG. 1, when the cam body 6 is positioned so that its notch faces inward, the opposing flantz 14 can be moved without interfering with the brim-shaped cam portion 13 of the cam body 6. It is now possible to position them in close contact with the connecting surface 1a of the flange 1.

As shown in FIG. 1, when the cam body 6 is rotated in a predetermined direction after the mating flange 14 is positioned, the brim-shaped cam portion 13 overlaps the outer surface of the mating flange 14. At the same time, the slanted cam surface 13a of this cam part 13 comes into contact with the outer edge 14a of the other flange 14, and when the cuff 1 is further rotated, the other flange 14 is directed toward the flange 1 due to the slope effect of the cuff 1 surface 13a. The flange 1 and the mating flange 14 are tightly fixed to each other and the pipes are connected.

If it is desired to remove the mating flange 14, it is sufficient to simply rotate the cam body 6 in the opposite direction to the above and position it so that its notch faces inward as shown in FIG.

By the way, in the conventional cam lock type flange joint having the above structure, when the cam lock is in effect, the cam contact part and the shaft 8 that supports the cam body 6 are biased, so that the cam surface 13a is Due to the reaction force pressing the flange 14, a large bending moment acts on the shaft 8, that is, the step screw 5. Therefore, in order to tightly fix the mating flange 14 to the flange 1 with sufficient force, it is necessary to use a sufficiently thick step 1 screw that can withstand the bending stress caused by the bending moment. Therefore, the overall size of the mechanism has to increase, and the weight has to increase as well, and there are also problems in that it is inconvenient to handle.

Furthermore, there is a problem that the life of the supporting portion of the cam body is generally short.

The present invention was devised under the above-mentioned circumstances, and its purpose is to generate only tensile stress and no bending stress on the shaft that supports the cam body when the cam is locked. By providing a cam lock type flange joint that allows the shaft that supports the cam body to be made much thinner than conventional ones, which in turn makes the entire cam opening and hook mechanism lighter and smaller. be.

In order to achieve such an objective, the present invention takes the following technical measures.

Zunawaji rotatably supports a cam body having a predetermined cam surface on a flange, and when a mating flange is stacked on this flange and the cam body is rotated, the cam surface presses the mating flange against the flange. In a cam lock type flange joint configured as shown in FIG. The large diameter part is inserted through the shaft and a large diameter part is provided at the end of the shaft to prevent the shaft from coming out of the shaft support hole toward the head, and the large diameter part contacts the cam support part. The surfaces are spherical so that they are in sliding contact with each other.

As mentioned above, there is a slight gap between the shaft supporting the cam body on the head and the shaft support hole of the cam support part into which it is inserted, and the size of the cam support part and the end of the shaft is large. Since the abutting surfaces with the diameter part are made into a spherical shape that is in sliding contact with each other, the -1 axis is basically oscillated from the center of the sphere with the upper position [h is -81; It becomes possible to swing within the above-mentioned pivot support as the center of movement. As a result, even if a force 1'1 is applied to the lock n5 via the cam body to bend the shaft, this force is avoided by the shaft elastically stretching and 1j;
The reaction force of the force of the cam body pressing the mating flange against the flange is finally supported by the bending support part as a tensile force of the shaft.

As a result, with the cam lock type flange joint of the present invention, LJ,
The shaft supporting the cam body can be made extremely thin considering only the tensile force. This leads to making the entire cam lock mechanism more compact, reducing the weight of the cam lock, and reducing material costs. Further, since no bending force is applied to the shaft supporting the cam body, the problem of bending of this shaft does not occur, and constant performance can be maintained over a long period of time.

Preferred embodiments of the present invention will be described in detail below with reference to the drawings.

3 to 6 show a first embodiment of the invention. In this example, in addition to the basic structure of the present invention, in which the shaft supporting the cam is slightly oscillated around a predetermined oscillation center inside its shaft support hole, This is an example in which the supported cam body is also allowed to play with respect to this shaft, thereby further enhancing the effect of the present invention that no bending force is applied from the cam body to the shaft.

As shown in the figure, the flange 21 provided with the cam lock mechanism 20 has three cam support portions 22 formed at equal intervals on its peripheral edge.

The cam support portion 22 can be formed by integrally extending the ear portion 23 projecting outward from the outside of the standard rotation of the flange 21, as in the conventional example shown in FIGS. 1 and 2. . A hub 25 having a shaft support hole 24 is formed in each ear portion 23 , and the cam body 32 is rotatably supported by a shaft 27 supported in the shaft support hole 24 .

In the present invention, the inner diameter of the shaft support hole 24 is set to be slightly larger than the outer diameter of the shaft 27 inserted therein, and basically the shaft 27 has a head 28 (left side in FIG. 4) that is oscillating. It becomes movable and is supported so that it cannot be removed.

In order to do this, in the illustrated example, as shown in FIG. 4, a contact surface 292 between the large-diameter nut 29 screwed onto the right end of the shaft 27 in FIG. 4 and the right end of the boss 25, 25
2 are in sliding contact with each other and are part of a spherical surface having the same center. In the case of the example shown in FIG. 4, the nut abutting surface 29a is a convex spherical surface, and the boss abutting surface 25a is a concave spherical surface. As a result, the shaft 27 has the ability to swing IjJ around the center P of the sphere constituting the spherical surface within the range permitted by the gap between the shaft 27 and the shaft support hole 24 of the boss. Taru Natsu 29 or Boss 2
5, the shaft 27 will not come off to the left in FIG. In the illustrated example, each time a spherical washer 31 is fitted into the end of the boss 25, the abutting surface 25a on the boss 25 side is configured as follows.
Of course, a spherical abutment surface may be integrally formed at the end of the boss 25. Further, the nut 29 is prevented from loosening and rotating by a pin 30 passing through the nut 29 and the shaft 27.

On the other hand, the shaft 27 protruding to the left in FIG. 4 of the boss 25
A cam body 32 is rotatably supported in a portion located between the head 28 and the boss 25 by fitting the through hole 33 therein. The inner diameter of the through hole 33 is set to be slightly wider than the outer diameter of the shaft 27. At the left end of the boss 25 in FIG.
is formed, and at the right end of the cam body 32, a male-shaped circular 1ff1 surface 35 that can fit into the conical surface 34 of the female body is formed, and the right end of the cam body 32 is aligned with the left end of the boss 25. This is to prevent it from shifting in the direction perpendicular to the axis. Also, the contact surface 283° 32a between the head 28 of the shaft 27 and the cam body 32
are formed by parts of spherical surfaces that are in surface contact with each other and have the same center. In this example, the contact surface 28a of the shaft head 28 is a convex spherical surface, and the contact surface 32a on the cam body side is a concave spherical surface. Further, in this example, in order to form the spherical contact surfaces 28a and 32a, the spherical surface Ir
The person who owns the 1j division/10-. The contact surfaces 28a and 32a are respectively fitted into the shaft portion adjacent to the HHr portion 28 and the through hole 3 of the cam body.
The shaft head 2B) may also be formed integrally with the cam body 32 itself, of course.

-1 The cam body 32 has a shape in plan view that looks like a part of a circle cut out in an arc shape, as shown in FIG.
e+' (see Figure 5)'! <As shown, cut 2
The shoulder surface of the recessed, spring-shaped cam g++3G, that is, facing the flange 21 side, has a cuff surface inclined in the circumferential direction, as explained for the conventional example in FIGS. 1 and 2. Further, a protrusion 38 is formed on the surface of the notch tW-shaped portion 36 to rotate the cam body 32 by hitting it with a hammer (1 dark in the figure) or the like. .Furthermore, in FIG. This is a grease dispenser that feeds grease into the gap that is formed to lubricate it.

Next, the operation of the cam lock type flange joint of this example will be explained.

First, as shown in FIG. 3, each cam body 32 is positioned so that its notch faces inward in the radial direction of the flange 21, and the mating flange 39 is positioned so that it overlaps the flange 2I. let Next, by tapping the protrusion 38, etc. (when the cam body 32 is rotated in a predetermined direction, the flange-shaped portion 3fi comes to over-harap the peripheral edge of the mating flange 39, and The slanted cam surface 37 presses the upper surface of the mating flange, bringing it into tight contact with the flange 21.

Figure 6 shows the internal state of the cam lock mechanism when the cam is cocked.

When the cam is locked, the cam surface 37 of the cam body 32 tries to rotate the cam body 32 in the direction of arrow B around a point as a reaction force to the force that strongly pushes the mating flange 39 against the flange 21. The power to do so works. At this time,
The 1Jf1 portion 28 of the shaft 27 engages with the cuff 3 body 32 through the contact surface 28a of the shaft 27, and b) Z+, so the shaft 27 has the following:
On the other hand, the shaft 27 and the cam body 32 are rubbed together with the spherical contact surfaces 28a and 32a of the shaft head 28 and the cam body 32 in surface contact with each other. Since it can move relatively, if the axis 27 is extended by a very small length, the axis 27 becomes as shown in Fig. 6. , pos25
The cuff 32 is tilted slightly in the direction of arrow C centering on the center P of the sphere, which includes the narrow abutment surfaces 25a and 29a of I. niwa - (1s 1ku. At this time, iji' of axis 27
The contact surfaces 28a and 32a of the J section 28 and the contact surface 28a and 32a are
Since they are a convex spherical surface and a concave spherical surface that are at the same center, they maintain only 4) surface contact. Zunawara,
When the l:1 is turned on, the cam body 32 and the shaft 27
In other words, rather than the blood pressure on the contact surfaces 28a and 32a being equalized by 5H, in other words, the blood pressure on the contact surfaces 28a and 32a is relatively moved and balanced so as to be in the most stable state. In addition, the contact surface 25 between the host 25 and the nut 29
．． ．． l, 29a also slides relatively under the garment, but there is no bloody contact F.
l! l! “C” is maintained.

As is clear from Fig. 6, when the cam locks, the cam body 3
The moment that attempts to rotate the shaft 2 in the direction of arrow B is supported by the shaft 27 as a tension force, and the force that attempts to bend the shaft 27 is 1,1 total < IIJ. Therefore, in the A1:I type flange joint of the present invention, since no bending force is applied to the shaft that rotatably supports the cam, this shaft can be made to have a small diameter. 11 Contributes to making the mechanism more compact and lightweight. Furthermore, since the shaft supporting the cam body cannot be bent, its lifespan is extended and constant performance can be maintained over a period of time.

FIG. 7 shows a second embodiment of the cam lock type flange joint of the present invention.

In this example, the head t? of the axis 27? II 28 and the end R of the cam body
1; and a contact surface 25 formed on the contact surface between the nut 29, which is the large diameter portion of the shaft 27, and the end of the post 25;
, 29a is changed from that of the first embodiment, the swing center P of the J-marked shaft 27 that swings within the shaft support hole 24 of the boss 25 is changed. .

That is, as shown in FIG.
+>::Abutment surface 29 between nut 29 and boss 25 of i part
Contrary to the case of FIG. 4, the spherical surfaces formed on a and 25a are such that the abutting surface 29a on the nut side is a concave spherical surface, and the abutting surface 29a on the boss side is a convex spherical surface (while the contact surface 25a is a convex spherical surface, the head of the shaft is 28 and cam body 32
Contrary to the case of FIG. 4, form the contact surface 28a, :32a with the
is a concave spherical surface, and the contact surface 32a on the cam body side is a convex spherical surface.
Good too. In this example as well, no bending force is applied to the shaft supporting the cam body during the cam lock operation, and the same effects as in the first example can be expected.

The first figure shows a second embodiment of the hook-and-lock type flange joint of the present invention.

In this example, the cam body and the shaft supporting the cam body are integrally formed. Of course, the shaft 27 that should support the cam body 32 is a bolt having a square shaft portion 44 in the first part of the neck of the hexagonal head 28. A through hole 33 of the cam body 32 having a square hole portion that can be fitted with the shaft portion 47I is inserted and fitted. Therefore, the cam body 32 in this example has integrity with respect to the shaft 27.

The rest of the configuration of this example is almost the same as the second example illustrated in FIG. 7. However, the pivoting center of the shaft 27, that is, the contact surfaces 25a and 2 of the boss 25 and the navels 1 to 29,
It is preferable that the center 1> of the spherical surface formed as 9a be located at a position that substantially coincides in the axial direction with the contact portion between the circle &(0 surface 35 of the cam body 32 and the conical surface 34 of the boss 25.

Thus, when the cam body 32 is rotated by rotating the hexagonal head 28 of the shaft 27 with a tool such as a spanner, and the cam body is caused to perform a locking action, the cam body 32 presses the mating flange 39 against the flange 21. This cam body 32 due to the reaction force
tries to rotate in the direction of arrow B in Figure 8 using point A as a fulcrum, but since there is naturally a slight play between the cam body 32 and the shaft 27, the shaft 27 stretches slightly elastically. It balances in a slightly oscillating state around point △ in the direction of arrow C. However, a tensile force acts on the shaft.
Therefore, no bending force acts at all. In the example shown in FIG.
11. The body 32 and the shaft 27 are fitted together. However, it goes without saying that almost the same effect can be achieved even if the cam body 32 and the shaft 27 are formed into a complete integral body.

[Brief explanation of drawings]

Fig. 1 is a side view showing the conventional example, Fig. 2 is a side view of the conventional example. Fig. 3 is a side view of the conventional example. The figure shows an example fi
If14 Norm curve diagram, Figure 5 is a perspective view showing details of nine cuffs, Figure 0 is a vertical sectional view to explain the cuff for υ11.1''i, Figure 7 is 4.I, , 4-Invention FIG. 8 is a vertical cross-sectional view showing still another embodiment of the present invention (h Z+ 6 2I... flange, 22... cam support part, 24...
- Pivot support hole 25-... contact surface, 29. I... Contact surface, 27... Shaft, 28... 1st part, 29... Dog f,
= part (naso l-), 32... cam body, 37... cam surface, 3... mating flange Applicant Asahi Kakureki Seisakusho Co., Ltd. Britiston Tie-1 Co., Ltd.

Claims (1)

[Claims] (1) When a cam body having a predetermined cam surface is rotatably supported on a flange, and a mating flange is stacked on this flange and the above cam body is rotated, the two faces will press the mating flange against the flange. Cam L configured to press against
In the J, type flange joint, 1 and 181;
Take one of the above cuffs (=J), line up the shaft with the shaft support hole, insert it freely, and provide a large diameter part at the end of this shaft so that this Head 1Ji from the above shaft support hole
A cam lock type flange joint Y, characterized in that the contact surface between the large diameter portion and the cam support portion is made into a spherical shape that makes surface-wise sliding contact with the cam while preventing the joint from coming off. .