KR860000428B1 - Latch bolt having crank camming for positive bolt positioning - Google Patents

Abstract

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Description

Clasp Structure

1 is a fragmentary horizontal cross-sectional view of a preferred embodiment of the clasp structure of the present invention.

FIG. 2 is a vertical cross-sectional view of the clasp structure viewed from the direction of eyes 2-2 of FIG.

3 is a side view of the clasp structure with the clasp in the fully advanced position.

4 is a vertical section view as in FIG. 2 of the clasp structure with the clasp in the fully retracted position.

5 is a side view of FIG. 3 of the clasp structure with the clasp in the fully retracted position.

6 is an enlarged perspective view of a preferred embodiment of the cam-shaped crank hub and spring-type resilient means of the clasp structure removed from the clasp structures of FIGS.

7 is a fragmentary enlarged vertical sectional view of the clasp structure viewed in the direction of the eye 7-7 of FIG.

8 is a partially enlarged vertical sectional view of the clasp structure viewed in the direction of eye 8-8 of FIG.

* Explanation of symbols for main parts of the drawings

10: fixed frame 12: latch casing

14: side plate 16: hard plate

18: crank herb 20: crank arm

22: radial groove hole 24: drive lever

26: driving lever outer and rear end (後端) 28: driving pin

32: front end of driving lever 36: latch

38: forward side latch positioning groove 42: retracted side latch positioning groove

46: radial projection 48: center surface of the arc

52: U-shaped spring 54: full length

56: connection angle 58: olfactory

60: protrusion 66: door

68: external lock cylinder operator 70: internal manual operator

84: torque rod 85: hand knob

86: torque rod

The present invention relates to a rotatable crank hub, which is connected by a transverse drive pin so that the rear end can be pivoted to the crank arm of the crank hub, and by one or several drive levers connected to the latch so that the front end can be pivoted. The clasp structure of the type which drives a clasp between a forward position and a retracted position. Moreover, this clasp structure is applied to the clasp by retracting the clasp from the outside as the drive pin between the crank arm and one or several drive levers is located in the groove of the clasp frame when the clasp moves to the forward position. It is to prevent the movement from the forward position.

According to an improvement of the present invention, the resilient crank hub resiliently pushes the drive pin into the groove of the frame and resiliently prevents movement from the groove of the frame when the latch approaches the forward position and displaces. Since it acts on the upper cam, the engagement between the drive pin and the frame groove further ensures its intended function.

Several conventional clasp structures have been proposed so far to frustrate the secret effort to move the clasp from the forward position by applying force from the outside and to securely secure the clasp to the forward position.

For example, in a conventional deadbolt clasp structure mounted to a door, the clasp placed in the forward position is pushed into the support piece of the door frame for maximum safety.

In dead-bolt clasps, one of the main points of attack when attempting to destroy a safety device is acting on the clasp in the forward position, allowing the tool to penetrate through the gap between the door and the door frame or directly through the door frame. In any of these cases, a force is applied directly to the latch to move the latch from its forward position to its retracted position.

In order to thwart this type of attack that causes the clasp to move, once the clasp is in the forward position, in addition to the usual clasp drive mechanism, the catch is securely in the forward position and the means for countering an external force attack. Are being proposed.

Significantly used conventional deadbolt clasp structures have their own means of increasing this safety and have a rotatable crank hub which is moved across the door and connected by an internal or manual operation. The radially protruding crank arm is connected to the rear end of one or several longitudinal drive levers so that their ends can pivot.

The front end of the drive lever is pivotably connected to the rear end of the latch that can slide smoothly in the normal longitudinal direction. Therefore, when the crank hub is rotated in one direction, the clasp moves from the retracted position completely inside the clasp casing to the forward position a predetermined distance away from the clasp casing in the longitudinal direction, and in the same way the crank hub Limit turn in the opposite direction returns the latch to the retracted position from the forward position.

The above mentioned means of increasing safety when the latch is in the forward position are arranged in relation to the pivotable connection between the crank arm of the crank hub and one or several drive levers.

When the crank arm and one or several drive levers move longitudinally forward to move the latch to the forward position, the transverse drive pin is placed so that the drive pin is placed in the groove of the frame with the potential to the latch forward position. It is used for pivotable connections and has a groove in the vertical direction on the clasp frame.

As a result, when the latch is in the forward position and the drive pin is in the groove of the frame, whatever force is applied to the latch to retract it, the force is transmitted to the longitudinal rear of one or several drive levers. Since the groove is directly transmitted to the grooved clasp frame through the driving pin between the crank arm and the crank arm, the force to retreat is prevented by the clasp frame to fix the clasp in the advanced position.

The spring is arranged at the pivotable connection between the front and rear ends of one or several drive levers so that the drive pin is always completely in the groove of the frame when the latch is in the forward position.

The spring is arranged to pivot the drive pin in the proper direction with respect to the clasp so that the drive pins at the rear end of one or several drive levers are always pushed into the grooves of the frame when the clasps approach the full forward position.

Thus, the turning force by the spring applied to the front of one or several driving levers is transmitted to the rear driving pin via the driving lever, so that the driving pin is completely positioned in the groove of the frame when the latch reaches the full forward position. It is.

One of the main problems with this conventional clasp structure is that the spring to increase stability is located at the front of one or several driving levers, so that the distance from the driving pin is required to ensure the operation.

It is clear that there is considerable doubt about the effectiveness of the substrates placed so far away.

Unless the spring, which is the core of the clasp structure, is correctly manufactured and correctly positioned, the intended result is neither partly nor entirely obtainable.

Another conventional clasp structure of similar shape has been attempted to achieve the desired safety using other types of springs arranged in other ways.

This spring is arranged in the clasp frame as a leaf spring extending longitudinally throughout the drive lever and its path of travel. This spring is uniquely positioned so that the drive pins enter the frame grooves, always engaged by the drive lever and the crank arm end when the latch is moved to the full forward position. Such a clasp structure is also suspicious in effect, and the above-described safety guarantee will not be obtained unless all the members are manufactured and assembled correctly.

It is an object of the present invention, having the general features described above, to reliably control the action of the crank arm and the drive lever so that the pivotable connection of the drive pin is securely located in the groove of the clasp frame when the clasp is at its full forward position. The cam and the resilient means is to provide a fastened metal structure.

In a preferred embodiment of the invention, the surface of the cam is formed on the rotatable crank hub, and the resilient means pushes it, so that the specially arranged substrates resiliently frame the drive pin when the clasp approaches and displaces in the forward position. It is pushed into the groove of the frame and cooperates to resiliently stop it from coming out of the groove of the frame.

Thus, by means of forces acting closer to the drive pin position than anything possible with conventional safety measures, and by a more secure and secure method, the drive pin position is reliably in the groove of the frame when the latch is in the fully forward position. It is guaranteed.

It is a second object of the present invention to provide a clasp structure having a structure that enhances the safety when the clasp is in the fully forward position, which prevents the clasp from being inadvertently advanced even when it is not desired even when the clasp is in the fully retracted position. To prevent it.

In a preferred embodiment of the present invention, as long as the cam surface on the rotatable crank hub and the resilient means actable in cooperation therewith can be relatively simple with a few additional measures to ensure that the clasp has the same function even in the fully retracted position. If necessary, by forming a suitable cam on the crank hub and by this relationship with the resilient means, obtaining a secure resilient means for pushing the drive pin into the clasp frame groove at either the full forward or full retracted position of the clasp. It is possible.

It is a third object of the present invention to provide a clasp structure having the above-mentioned advantages, the most preferred form of which is that the cam and the resilient means cooperate and drive with constant elasticity while the clasp is in its full dislocation position. The drive pin is elastically pushed into one or several clasp frame grooves so that the pin is in the safe position of one or several frame grooves. Due to the cooperation of the specially formed cam and the resilient means, the proper resilience is always applied to the drive pin through the crank hub and the crank arm so that the clasp pushes the drive pin into the frame groove evenly after full transfer. .

The drive pin is thus firmly and resiliently pushed into the frame's unique latch positioning groove, which not only prevents the drive pin from moving out of the groove while the latch is in the fully moved position, but also once it is completely in the groove. Since the drive pins are held completely and securely in their grooves by the pushing resiliency, this preferred embodiment of the present invention achieves the best possible safety and obvious improvement over conventional structures.

Other objects and advantages of the present invention will become apparent from the accompanying drawings and the foregoing detailed description for purposes of illustration.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The accompanying drawings that describe preferred embodiments of clasp structures incorporating the principles of the crank cam of the present invention are described. 1 shows a clasp structure attached to a typical door, while the remaining figures show the clasp structure removed from the door for clarity and brevity. Overall, the clasp structure can be manufactured by conventional materials and conventional manufacturing methods well known to those skilled in the art.

In general, the clasp structure has a fixed frame 10 consisting of a cylindrical clasp casing 12 at the front and a side plate 14 terminated at a transversely arranged and vertically independent end plate 16 in the rear. have.

The crank hub 18 having a transverse side extends laterally, penetrates the side plate 14 and is attached to the side plate so as to be rotatable between both side plates, corresponding to various angles according to the rotatable position of the crank hub. It has the crank arm 20 which protruded upwards from the radial direction.

The crank arm 20 is formed with a radial groove hole 22 that penetrates in the lateral direction, and the groove hole 22 is slightly away from the free end of the crank arm, and is recessed toward the crank hub 18 radially inward. have.

The drive levers 24 are spaced in the transverse direction in a pair, and extend in the longitudinal direction as a whole. The rear ends 26 are provided on both sides of the crank arm 20 between the side plates 14 of the fixed frame. Is pivotally connected to the crank arm 20 by a transversely extending drive pin 28.

The drive pin 28 penetrates through the groove hole 22 of the crank arm and the rear end 26 of both drive levers and reaches the upper end line 30 of the fixed frame side plate 14 for the purpose described later. Penetrates in the transverse direction;

The drive lever 24 protrudes forward from the side plate of the fixed frame into the clasp casing 12 of the fixed frame, and its front end 32 is actuated longitudinally in the clasp casing by the fever pin 34. It is connected to the rear end of the clasp 36 as much as possible.

As shown in the figures and described above, it is apparent to those skilled in the art that the preferred embodiment of the clasp structure is a typical deadbolt clasp structure.

Moreover, although it is common in the conventional dead bolt type clasp structure, the forward side latch positioning groove 38 having the upper side open side by side in the transverse direction is formed on the top line 30 of the fixed frame side plate 14, and the clasp casing of the fixed frame ( 12) are formed at a distance slightly rearward from the longitudinal direction.

This groove 38 is a groove generally entered in a vertical direction and has a hook-shaped rear surface 40 for later examination. In addition, the retracting side latch positioning groove 42 is formed on the upper end line 30 of the fixed frame side plate 14 at a distance slightly ahead of the longitudinal plate 16 in the longitudinal direction, and this groove has no special surface shape. It is a simple vertical groove.

Note that the groove 38 for determining the forward side latch position and the groove 42 for determining the retracting side latch position are arranged to form a longitudinal movement limit of the drive pin 28 when the latch is moved forward and backward. This will be discussed in detail later.

In particular, in the refinement of the invention, the outer surface 44 of the crank hub 18 is cam-shaped, which is two sides 50 having a relatively smooth angle with the arcuate center surface 48 on the radially outer side. Consists of a radial projection 46 having a.

Both sides 50 are smoothly connected to the central surface 48 of the radial projection 46 and are fused to the usual circumference of the crank hub 18. The radial projection 46 is formed to extend laterally along the axis of the crank hub, as shown in the figure.

The resilient means of the U-shaped spring 52 as a whole is disposed between the shaft plate 14 of the fixed frame 10 at the rear of the crank hub 18, the front end of the spring 54, the front end 54 of the crank hub Push the radial projection 46, the connection angle 56 extends rearward to the high plate of the frame 16, the rear 58 is in contact with the plate 16 of the fixed frame, the plate 16 Raises vertically upwards to the height of.

The springs 52 are fixed in an assembled state by both protruding ears 60 protruding from both sides of the spring 58 laterally in the transverse direction and exiting through the grooves 62 at the rear of the fixing frame side plate 14. As in the fixed plate 16 of the fixed frame is separated vertically. Furthermore, as will be described later in detail, the embossed portion 64 of the spring 52 is formed with a concave portion 64 opened upwardly in the center of the distal end thereof to provide a gap with respect to the crank arm 20 of the crank hub 18. .

As shown in FIG. 2 and FIG. 3, when the crank hub 18 is rotated counterclockwise so that the crank arm moves forward, the clasp 36 is moved by the drive lever 24 to the full forward position. The driving pin 28 enters the forward side latch positioning groove 38 along the side plate 14, at which time the central surface 48 of the radial projection 46 of the crank hub is spring 50. Moving forward along the full width 54 of the crank hub, whereby the full width 54 of the spring comes into contact with the rear face 50 of the radial projection of the crank hub. Relative position with 20).

In Figure 2, this state is well specified when the latch is in the fully advanced position.

When the driving pin 28 approaches the forward side latch positioning groove 38 while the clasp is in the forward motion, the spring emc 54 is with respect to the side 50 of the radial projection 46 of the crank hub. The elasticity is applied to move the crank hub 18 in this rotational direction (in this case counterclockwise).

This resilience continuously and reliably pushes the drive pin 28 into the forward side positioning groove 38 so that the clasp 36 is eventually placed in the complete forward positioning groove 38.

Furthermore, even after the drive pin 28 enters the full forward positioning groove 38 in its forward positioning operation, the drive pin 28 continues to be elastic by the elasticity of the spring 52 acting on the radial projection 46 of the crank hub. The spring angle 54 does not completely contact the side surface 50 of the radial protrusion 46 of the crank hub as shown in FIG. 2 so as to be pushed downward in the forward positioning groove. It is preferable to come into tangential contact with i).

As in FIGS. 2-5, the crank hub 18 is rotated counterclockwise, or clockwise, so that the latch 36 is fully retracted in FIGS. 4 and 5 from the fully advanced positions of FIGS. Go to location. At this time, the crank arm 20 retracts the latch 36 by the drive lever 24 and simultaneously pulls the drive pin 28 upward from the forward side latch positioning groove 38 and finally moves it backward. It enters the retracting side latch positioning groove 42.

The central surface 48 of the radial projection 46 of the crank hub is slid backwards along the spring angle 54 and the crank hub 18 has the center surface (as shown in FIG. 4) of the spring angle 54. The end is finished in the state in contact with the end of the side 50 past the 48. As described above, it is preferable that the spring 52 is not completely in contact with the side surface 50 of the radial protrusion.

Thus, the drive pin 28 is not only elastically pushed into the groove 42 when approaching the retracting side latch positioning groove, but also as shown in FIGS. 4 and 5, once the retracting side latch positioning groove. When it is in, it is pushed in the direction of the groove with continuous elasticity.

As shown in FIG. 1, in a preferred embodiment, a clasp structure embodying the principle of the crank cam of the present invention is mounted on a typical door, and the clasp structure includes an external lock cylinder 68 and an internal manual operator. 70) is installed in the door 66.

The clasp casing 12 of the fixing frame 10 is contained in the longitudinal clasp opening 72 of the door 66 and its end face is finished with the same face as the cross section of the door.

In the assembled state, the outer lock cylinder operator 68 fixed to the door outer surface 78, the inner manual operator 70 fixed to the door inner surface 80, the side plate 14 and the crank hub 18 are in the transverse direction. The clasp casing 12 protrudes in the clasp opening 72 which penetrated in the horizontal direction of the door 66 to the rear in the longitudinal direction.

As is commonly used, the lock plug 82 of the outer lock shire operator 68 is driven by the torque rod 84 and the manual knob 86 of the inner manual operator 70 is the torque rod 88. Is connected to the crank hub 18, and the torque rod and the crank hub do not rotate each other.

Next, the action of the clasp structure attached to the door will be described. As shown in Figs. 4 and 5, the latch is fully retracted, i.e., the latch of Fig. 1 is retracted. When either of the external lock cylinder operator 68 or the internal manual operator 70 is rotated in a conventional manner, the crank hub 19 rotates counterclockwise as shown in FIGS. 4 and 5 to crank the arm. 20, the drive lever 24, and the latch 36 move forward so that the latch advances from the end face 74 of the door into the support surface (not shown) of a conventional door frame (not shown). do. A spring which retracts the radial projection 46 of the crank hub 18 when the catch 36 approaches the full forward position and finally reaches its position, as shown in FIGS. 1 to 3. By means of 52, the drive pin 28 is elastically pushed into the forward side latch positioning groove 38 of the fixed frame shaft plate 14.

As shown in Figs. 1 to 3, as the latch 36 reaches the full forward position, the drive pin 28 enters completely into the forward side latch positioning groove 38 and moves downward to move the hook type. It comes in contact with the back of the groove.

Furthermore, as clearly shown in FIG. 2, the unique relationship between the U-shaped spring 52 and the radial projection 46 of the crank hub allows the drive pin 28 to be held in constant elasticity, even after it has finally been in full position. The drive pin 28 is reliably retained even while the latch 36 is in the fully advanced position since it is pushed into the engaged position of the final groove.

The clasp structure is thus left locked in the door 66 in which it is installed.

While locked in this way, the drive pin 28 is pushed by the forward side latch positioning groove 38 to the side plate of the fixed frame even when the tool penetrates into the gap between the door and the door frame or the door frame to retract the latch 36. Because of the engagement, it is not possible to move the latch backwards. The hook-shaped rear surface 40 of the forward side latch positioning groove 38 prevents any movement of the drive pin 28 from engaging with the side plate 14 of the fixed frame, and the drive pin ( 28) The unique relationship between the U-shaped spring and the crank hub radial projection 46, which pushes it completely into the forward side latch positioning groove 38, always drives when the latch is in the fully advanced position. It is assured that an accurate and safe position is maintained between the pin and the forward side latch positioning groove.

In this way there is a maximal defense against the clasp's covert movement, so any attempt to destroy the safety of the clasp structure will fail.

The movement of the latch 36 from the fully advanced position, in which the doors of FIGS. 1-3 are locked, to the fully retracted position, in which the doors of FIGS. 4 and 5 are not locked, is performed by the external lock cylinder 68 or the internal manual. Either of the operators 70 can be achieved by rotating the crank hub 18 in the usual manner. Rotating the crank hub 18 clockwise as in FIGS. 2-5, the latch 36 retracts completely into the latch casing 12 and the drive pin 28 is in FIGS. 4 and 5 As shown in the drawing, the retraction-side clasp positioning groove 42 is pushed completely and resiliently.

As in the case of the clasp in the eddy forward position, the engagement between the driving pin and the retracting clasp positioning groove 42 in the state where the clasp is fully retracted is the radial projection of the U-shaped spring 52 and the crank hub ( 46, which can be reliably maintained by the constant resilience acting on the engagement of the drive pin and the retracting latch positioning groove.

In this way, due to the engagement of the drive pin and the groove in the retracted state, it is absolutely impossible for the latch to pop out from the fully retracted position due to vibration force or other causes.

According to the principles of the present invention as described above, a unique clasp structure has been obtained, which is significantly improved compared to the conventional structure by safely holding the clasp at least in the fully advanced position.

The resilient means in the crank hub acts to push the substrate to a position that ensures absolute safety by providing resilience very close to the clasp base and to keep it in an absolute safety position.

Furthermore, in the case of the preferred embodiment, once the substrate of the clasp structure is resiliently pushed into the final absolute safety position, the unique positional relationship of the resilient means and the radial projection of the crank hub allows the substrate to remain in this position. Since the elasticity is continuously received, this absolute safety position can always be fixed as necessary.

Although the principles of the present invention have been described as specific embodiments of clasp structures, it is not intended that the above principles be limited only to the structures of the preferred embodiments as the same principles can be readily applied to various types of clasp structures.

Therefore, the principles of the invention should be construed broadly and should not be limited to more than the specific limits set forth in the claims, including those corresponding to the claims.

Claims (16)

A crank hub rotatable about a transverse axis in the frame and having a radially elongated crank arm and pivotally connected to a rear end and a longitudinally reciprocating clasp pivotally connected to an end of the crank arm with a transverse drive pin; It has a longitudinal drive lever with a front end, and the latch moves to the forward position by the drive lever due to the forward movement of the crank arm according to the rotation of the crank hub. It enters inside and acts an external force on the clasp to prevent the clasp moving backwards from its forward position by engaging the drive pin and the clasp positioning groove, which is driven first by the rear movement of the crank arm by the rotation of the crank hub. The pin is pulled out of the latch positioning groove and the latch is retracted at the same time. In the clasp structure of the type to move to the position: a cam surface means provided in the rotatable crank hub and the cam surface means in cooperation with the cam surface means when the clasp approaches the forward position and displaces the crank hub and the crank An improvement of the present invention includes an elastic means for elastically pushing the drive pin into the latch positioning groove of the frame by an arm and elastically pushing the face of the cam to prevent movement from the groove. The clasp structure described above. 2. The elastic means according to claim 1, wherein the resilient means is formed to push the driving pin into the latch positioning groove of the frame with constant elasticity even after the drive pin enters the latch positioning groove of the frame. Clasp structure, characterized in that arranged. 2. The clasp positioning groove according to claim 1, wherein the latch positioning groove of the frame is a forward side latch positioning groove, and the latch is rearwardly retracted by the drive lever in a rearward movement of the crank arm according to the rotation of the crank hub. At the same time as the drive pin is moved into the retracting side latch positioning groove in the overall vertical direction of the frame, the cam surface means and the resilient means work in cooperation so that the clasp approaches the retracted position Wherein said crank hub and crank arm elastically push a drive pin into said retracting side latch positioning groove while resiliently preventing movement from said groove. 2. The latch positioning groove according to claim 1, wherein the latch positioning groove is a forward side latch positioning groove, and the latch is moved to the rearward retracted position by the driving lever due to the rearward movement of the crank arm according to the rotation of the crank hub. At the same time the drive pin is moved into the retracting side latch positioning groove in the vertical direction of the frame as a whole, and the cam surface means and the resilient means cooperate to act so that the clasp approaches and displaces the retracted position. Elastically pushing the driving pin into the retracting side latch positioning groove by the hub and the crank arm while resiliently preventing movement from the groove, and the driving pin being the forward side latch positioning groove or the retracting side latch. The driving pin is placed in the above position even after being placed in either one of the positioning grooves. To give pushing a certain elasticity in the positioning groove of the cam surface means and the latch structure, it characterized in that the elastic means are formed and arranged. 2. The clasp positioning groove in the generally vertical direction of the frame is formed with a hook-like surface that is drilled downward and is generally hooked, and the cam surface means and the resilient means flexibly move the driving pin to the latch position. The clasp structure being pushed into the crystal groove and aligned in a longitudinal direction with the hook-shaped surface of the clasp positioning groove. 2. The clasp positioning groove in the generally vertical direction of the frame is formed with a hook-like surface that is drilled downward and is generally hooked, and the cam surface means and the resilient means elastically move the driving pin to the clasp position. Pushing the driving pin into the latch positioning groove evenly after the driving pin is placed in the latch positioning groove and pushing the drive pin into the latch face in the longitudinal direction with the hook face of the latch positioning groove. And the cam surface means and the resilient means are formed and arranged such that a driving pin is reliably held in line with the hooked surface of the clasp positioning groove. 2. The cam face means according to claim 1, wherein the cam face means on the crank hub has a radial cam protrusion, and the resilient means causes the radial cam protrusion to be circumferentially pushed into the latch positioning groove of the frame. Clasp structure, characterized in that for pushing. 2. The cam face means on the crank hub has a radial cam protrusion and the resilient means moves the radial cam protrusion in the circumferential direction when the driving pin is pushed into the latch positioning groove of the frame. And the resilient means is formed to push the drive pin into the clasp positioning groove of the frame with constant resilience even after the drive pin is placed in the clasp positioning groove of the frame. A clasp structure, characterized in that it is arranged against a projection. The clasp positioning groove according to claim 1, wherein the latch positioning groove is a forward side latch positioning groove, and the latch is moved to the rearward retreat position by the driving lever due to the rearward movement of the crank arm according to the rotation of the crank hub. At the same time the drive pin is moved into the retracting side latch positioning groove, which extends in a generally vertical direction of the frame, and the cam surface means and the resilient means cooperate to act so that the clasp approaches and displaces the retracted position. The drive pin is pushed into the retracting side latch positioning groove elastically by the hub and the crank arm, while elastically preventing movement from the groove, and the cam face means on the crank hub have radial cam projections. And the driving pin are either of the forward side or the backward side latch positioning grooves. The resilient means is formed so that the resilient means pushes the radial cam projection in the circumferential direction when being pushed and while the drive pin is in the clasp positioning groove and the radial cam of the cam surface means A clasp structure characterized by being disposed against a projection. 2. The elastic means according to claim 1, wherein the resilient means has one corner portion in contact with the cam surface means and the other corner portion in contact with the frame, and elastically pushes between the cam surface means and the frame. Hasp structure characterized in that it has a U-shaped spring. The U-shaped spring according to claim 1, wherein the resilient means has one corner portion in contact with the cam surface means and the other corner portion in contact with the frame and is elastically pushed between the cam surface means and the frame. And the spring and the cam surface means are arranged to push the driving pin into the latch positioning groove of the frame with a constant elasticity even after the driving pin is located in the latch positioning groove of the frame. Clasp structure. 2. The latch positioning groove of the frame is a forward side latch positioning groove, and the latch is rearwardly retracted by the drive lever in the latter half movement of the crank arm according to the rotation of the crank hub. At the same time the drive pin is moved into the retracting side latch positioning groove which is generally vertical in the frame, and the cam surface means and the resilient means cooperate to move the latch to the retracted position. And a resilient means for the crank hub and the crank arm to push the drive pin into the retracting side latch positioning groove while resiliently preventing movement from the groove and the resilient means being in contact with the cam face means. The cam face means and the frame A clasp structure characterized by having a U-shaped spring pushing elastically between the forest. 2. The latch positioning groove of the frame is a forward side latch positioning groove, and the latch is rearwardly retracted by the drive lever in a rearward movement of the crank arm according to the rotation of the crank hub. At the same time the drive pin is moved into the retracting side latch positioning groove in the generally vertical direction of the frame, and the cam face means and the resilient means cooperate to move the latch to the retracted position. When the crank hub and the crank arm elastically pushes the drive pin into the retracting side latch positioning groove while resiliently preventing movement from the groove and the resilient means is in contact with the cam surface means The cam face means and the frame It has a U-shaped spring that is elastically pushed between the grooves and the latching position of the drive pin with a constant elasticity even after the drive pin is located in either one of the forward side or the retracted side latch positioning groove. And the spring and the cam face means are arranged to be pushed into the crystal groove. 2. The cam surface means according to claim 1, wherein the cam surface means on the crank hub has a radial cam protrusion, and the resilient means has a U-shaped spring that is elastically pushed between the cam surface and the frame, and the spring is the cam. And an angled portion that is in contact with the frame and another angled portion that is in contact with the frame, forcing the drive pin into the latch positioning groove of the frame when the latch is approached and displaced. Clasp structure. 2. The cam surface means according to claim 1, wherein the cam face means on the crank hub has a radial cam protrusion, and the resilient means has a U-shaped spring that pushes elastically between the cam face and the frame. Has a corner that is in contact with the frame and another that is in contact with the frame, and acts to push the drive pin into the latch positioning groove of the frame when the latch approaches the forward position and displaces. The spring and the radial cam projection are arranged to push the driving pin into the latch positioning groove of the frame with a constant elasticity even after the drive pin is located in the latch positioning groove of the frame. Clasp structure. 2. The latch positioning groove of the frame is a forward side latch positioning groove, and the latch is moved to the retracted position by the drive lever due to the rearward movement of the crank arm according to the rotation of the crank hub. At the same time as the drive pin is moved into the retracting side latch positioning groove, which is generally vertical in the frame, and the cam surface and the resilient means cooperate to act as the clasp approaching the retracted position. A crank hub and a crank arm elastically push a driving pin into the retracting latch positioning groove while resiliently preventing movement from the retracting latch positioning groove, and the cam face means has a radial cam protrusion. And the elastic means pushes elastically between the cam surface and the frame. Which has a spring of which the radial cam projection moves with respect to the spring while the clasp is moved to the forward or retracted position and the drive pin is either of the forward or retracted latch positioning groove. A clasp structure, characterized in that the spring is formed and arranged to engage both sides of the radial cam protrusion so that the drive pin is pushed into the clasp positioning groove on which it is placed while still in one groove.

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