CN212928362U

CN212928362U - Shaft coupling

Info

Publication number: CN212928362U
Application number: CN201922373314.7U
Authority: CN
Inventors: 蔡明明
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-12-23
Filing date: 2019-12-23
Publication date: 2021-04-09
Anticipated expiration: 2029-12-23

Abstract

The utility model discloses a current drive shaft, axle body and enlarge tip and current driven shaft, connect the shaft coupling of accomplishing this in an axial body to the removal of same direction. The coupling includes a casing, which makes the front enlarged end and the back possible to apply force to control the inertia force generated by the driven shaft when the driven shaft advances to the end of the stroke. The existing driving shaft and the existing driven shaft can be connected, and the provided coupling can effectively control the behavior of the previous memory generated when the driven shaft advances to the stroke end at a high speed.

Description

Shaft coupling

Technical Field

The utility model relates to a coupler belongs to die casting machine die casting equipment field.

Background

In the casting apparatus, as shown in fig. 3, the molten metal in the plunger sleeve a6 is pushed forward (to the left in fig. 3) by the plastic core a4 at the front end of the plunger rod a5, and the molten metal is injected into the mold outside the drawing. Plunger rod a5 is connected to cylinder rod a1 by coupling a 3. A clearance a2 is provided between the coupling a5 and the cylinder rod a 1. During casting, although plunger rod a5 thermally expands and plunger rod a5 bends, the thickness of gap a2 controls the gap formed thereby and absorbs the stress (load) applied to plunger rod a5 and plunger sleeve a 6. In casting, when cylinder rod a1 as a driving shaft presses down plunger rod a5 as a driven shaft, and cylinder rod a1 moves to the stroke end at a relatively fast speed (e.g., 7 m/sec), plunger rod a5 tries to move further forward by inertia, and in addition, this movement is restricted by coupling a3 and also instantaneously moves backward by a reverse force. In this case, the movement of the plunger rod a5 is conspicuous by the presence of the aforementioned gap a 2. At the end of the stroke, plunger rod a5 operates as described above, and plunger core a4 fluctuates due to the extrusion of the molten metal, which adversely affects the quality of the cast product. Here, to inhibit the above-described condition of plunger rod a5, plunger rod a5 could be modified, but plunger rod a5 is a long-sized component, and modifying and exchanging plunger rods is not economical. Since the plunger sleeve a6 is repeatedly supplied with aluminum from the portion a7, the plunger sleeve a6 is deformed (bent upward) due to heat. In addition, the weight of the mold causes the plunger sleeve a6 to be displaced from the cylinder rod a1 due to the long-term use of the mold. As these changes begin to occur, the resistance of the plunger core a4 and plunger sleeve a6 becomes greater and the consumption of these components increases.

Disclosure of Invention

The to-be-solved technical problem of the utility model is: a coupling is provided which combines a drive shaft and a driven shaft to effectively control deformation and loss caused by relatively fast forward movement of the driven shaft from the start to the end of a stroke, and which can reduce the movable resistance caused by deformation and misalignment of a plunger sleeve a 6.

In order to solve the above-mentioned problems, an aspect of the present invention is to provide a coupling, which includes a conventional driving shaft that moves forward and backward in an axial direction, a shaft body that is coaxial with the driving shaft, and a conventional driven shaft that is provided at a rear end of the shaft body and has an enlarged end portion whose cross section is enlarged as compared with the shaft body, and which is operated to integrally move in the axial direction, a coupling that is operated to integrally move in an axial direction, a front end of the driving shaft and a rear end of the driven shaft, and a front portion that is accommodated in the front portion and has the front end enlarged end portion and a rear portion, and which is capable of applying force to the current portion, such as the front end enlarged end portion and the rear portion, and which is effective as a stopping means for the resistance of the driven shaft to the inertia generated by. And an annular spacer interposed between the urging portion and the enlarged end portion, having a front surface on which the urging surface is received from the urging means and a rear surface on which the contact surface between the enlarged end portion and the contact surface is formed.

According to the utility model discloses look, can be connected current drive shaft and current driven shaft, moreover, can effectively control the antecedent driven shaft to the stroke end be the inertia under relatively fast. Reducing its resistance to movement.

Drawings

FIG. 1 is a cross-sectional view of a coupling with a drive shaft connected to a driven shaft;

FIG. 2 is a sectional view showing a mechanism of fluid pressure as a force application member;

fig. 3 is an explanatory view of the prior art.

Description of the symbols:

10: coupling a 1: cylinder rod (drive shaft) a 11: first shaft body

a 12: first enlarged end a 5: plunger rod (driven shaft) a 51: second shaft body

a 52: second enlarged end portion 20: the housing 21: spring (embodiment)

22: the intermediate seat 30: spacer 52: pressure receiving surface

54: contact surface 72: annular space C1: first center line

C2: second center line r 1: diameter direction dimension r 2: dimension in diameter direction

Detailed Description

In order to make the present invention more comprehensible, preferred embodiments are described in detail below with reference to the accompanying drawings.

Example 1

Fig. 1 is a sectional view of a coupling connecting a drive shaft a1 and a driven shaft a 5. The coupling 10 shown in fig. 1 is used for connecting the cylinder rod a1 and the plunger rod a5 of the casting apparatus when they are moved integrally in the axial direction. The cylinder rod a1 and the plunger rod a5 are already existing, are applicable to the coupling 10 shown here, and are not new. That is, the coupling 10 shown here can replace the conventional coupling a 3. In the casting apparatus, although not shown, the melt is injected into the mold, and the melt (molten aluminum) supplied from the plunger sleeve a6 is injected by pressing the tip end of the plunger rod a 5.

The conventional cylinder rod a1 is a drive shaft a1 of a fluid cylinder (e.g., a hydraulic cylinder) not shown in the drawings, and moves forward and backward in the axial direction by fluid pressure. The direction along the center line C1 of the cylinder rod a1 is the "axial direction". In fig. 1, the mold side on the left side is "front", and the fluid cylinder side on the right side in fig. 1 is "rear". The direction of the center line is the middle "" radial direction "". The cylinder rod a1 is shared by the linear first shaft body a11 and a first enlarged end a12 having an enlarged cross section provided at the tip of the first shaft body a 11. The conventional plunger rod a5 is a driven shaft a5 that is pushed down and advanced by the cylinder rod a1, and is integrated with the cylinder rod a1 so as to advance and retreat in the axial direction. The plunger rod a5 has a second shaft body a51 coaxial with the cylinder rod a1, and is disposed at the rear end of the second shaft body a51 and has a cross section common to the enlarged second enlarged end a52 of the second shaft body a 51. The symbol of the second centerline of plunger rod a5 is C2. When molten water is injected into the direct plug sleeve a6, the cylinder rod a1 (and the plunger rod a5) advance toward the end of travel at a relatively fast speed (e.g., 7 m/sec). After the ejection, the rods a1, a5 are retreated at a speed slower than that in the forward movement. The coupling 10, the housing 20, the spring (mounting means) 21, and the spacer 22 are all mounted, and the coupling 10 of fig. 1 is connected to the washer 30 and the collet 31. The spring 21 is formed by spacing a plurality of spacers (equal spacers) in a circumferential direction around the center line C2. The number of the springs 21 may be changed according to the diameter of the plunger rod a5, for example, 8.

Housing 20 houses the front end of cylinder rod a1 and the rear end of plunger rod a 5. The housing 20 includes a first housing portion 32 on the rear side and a second housing portion 34 on the front side. The

housing portions

32, 34 are fixedly connected by bolts 36. A plurality of (for example, 8) bolts 36 are provided along the circumferential direction around the center line C1 (C2). The first housing part 32 is formed with bolts 36 that engage with the screw holes 37, and the second housing part 34 is formed with shaft through holes 44 for the bolts 36.

The first housing portion 32 houses a front portion including a first enlarged end a12 within the cylinder rod a 1. To this end, the bottom of the first housing portion 32 is cylindrical in shape. The first enlarged hole portion of the first housing portion 32 having a shape corresponding to the first enlarged end a12 is in contact with the hole portion 40 having a shape corresponding to the collet 31, which is larger than the first enlarged hole portion in a tapered shape. When the front end surface a13 of the cylinder rod a1 advances, it presses the disk-shaped bottom 42 of the first case portion 32. That is, the first enlarged portion is received by the first enlarged end portion a 12. The collet 31 is compatible with the tapered hole 40 corresponding to the collet 31. Are connected and fixed by nuts. The cylinder rod a1 is immovable relative to the first housing portion 32 in the axial direction.

Second housing portion 34 houses a rear portion that includes second enlarged end a52 in plunger rod a 5. The second housing portion 34 and the second enlarged hole portion 46 are connected to the second small-diameter hole portion 48. The second enlarged hole 46 has an inner diameter larger than the outer diameter of the second enlarged end a52 (the spacer 30 and the spacer 22). The second small-diameter hole portion 48 is a hole smaller in diameter than the second enlarged hole portion 46, but has an inner diameter slightly larger than the outer diameter of the second shaft main body a 51. The first housing part 32 and the second housing part 34 are integrated, and the spacer 30 is interposed between the bottom 42 of the first housing part 32 and the plunger rod a 5. Bottom 42 pushes plunger rod a5 forward via gasket 30. The second housing portion 34 also houses a plurality of springs 21 and spacers 22. The second enlarged hole 46 accommodates the spacer 30, the second enlarged end a52, and the like, so that the plunger rod a5 and the second case 34 can move integrally in the axial direction. The second housing part 34 is assembled with the plunger rod a5 in two separate parts.

The housing 20 is made of the same material as the cylinder rod a1 and the plunger rod a5, and its mechanical structure is made of carbon steel (S45C, etc.). The first housing part 32 in which the cylinder rod a1 is housed and the second housing part 34 in which the plunger rod a5 is housed are connected by a bolt 36 in the bolt centerline axis direction. In the assembled state, the spring 21 is disposed in a compressed state inside the housing 20. Therefore, when the bolt 36 is tightened gradually during assembly of the coupling 10, the spring 21 is compressed to connect the first housing part 32 and the second housing part 34. That is, since the housing 20 is constructed to be separated front and rear, it is easy to assemble. The housing 20 may be constructed in a single body as well as in a separate structure.

The spring 21 is provided on the front portion (annular side wall 50) of the housing 20 and on the annular side wall 50 of the second housing part 34. The bottomed holes 50a of the same number as the springs 21 are provided at intervals in the circumferential direction. This hole 50a accommodates the spring 21. The spring 21 is disposed between the bottom of the hole 50a and the intermediate seat 22 where the second enlarged end a52 contacts. The spring 21 is a loaded or extremely loaded coil spring. In the present embodiment, all the springs 21 are compressed in the assembled state, and the total of the elasticity (reaction force: thrust) generated by the springs 21 is 900N or more and 1800N or less. That is, this value is a target value only, and if the capacity is changed according to the capacity of the casting machine and the capacity becomes large, the elastic force is set to be larger. That is, the spring force is at least 900N.

The intermediate seat 22 is an annular member interposed between the plurality of springs 21 and the second enlarged end portion a 52. The outer peripheral contour of the intermediate seat 22 is greater than the outer peripheral contour of the second enlarged end a 52. In the present embodiment, since the outer peripheral contour of the intermediate seat 22 and the second enlarged end a52 is circular, the outer diameter of the intermediate seat 22 is larger than the outer diameter of the second enlarged end a 52. The housing of the intermediate holder 22 is attached to the second shaft main body a51 and is in surface contact with the annular front surface of the second enlarged end a 52. The intermediate seat 22 has a pressure receiving surface 52 for receiving the pressing force from the spring 21 at the front and a contact surface 54 for contacting the second enlarged end portion a52 at the rear.

The diameter of the circumscribed circle of the plurality of springs 21 is larger than the outer diameter (diameter of the circumscribed circle) of the second enlarged end a 52. Therefore, if the spacer 22 is omitted, the spring 21 cannot entirely contact the front face of the second enlarged end portion a 52. However, in the present embodiment, the spacer 22 is provided between the spring 22 and the second enlarged end a 52. The diameter of the outer peripheral side of the pressure receiving surface 52 is the same as the diameter of the circumscribed circle of the plurality of springs 21 or is set larger than the diameter of the circumscribed circle. Therefore, the entire end of the spring 21 is in contact with the pressure receiving surface 52. Thus, the front face of the second enlarged end a52 is substantially contactable with the contact surface 54 of the intermediate seat 22. Therefore, the urging force of the spring 21 can be appropriately transmitted to the second enlarged end portion a52 through the intermediate seat 22. The intermediate base 22 is made of steel, and is made of, for example, carbon steel for machine structural use, bearing steel, or the like.

As described above, the rods a1, a5 advance at a relatively fast speed to the end of the stroke. Plunger rod a5 exerts a force to further advance by inertial force when cylinder rod a1 pushes plunger rod a5 to the end of the stroke. Here, the front end (annular side wall 50) of the housing 20 is passed through the plurality of springs 21. In the pushed-back state of the second enlarged end a52 of the intermediate seat 22, the plunger rod a5 of the plurality of springs 21 advances to the end of the stroke at a high speed, which generates inertial resistance to the plunger rod a 5. For this reason, when cylinder rod a1 advances to the end of travel, plunger rod a5 may also stop at the end of travel. That is, as plunger rod a5 advances to the end of travel, plurality of springs 21 generate a reaction force that inhibits further advancement of plunger rod a5 due to the inertia (spring rate) of plunger rod a 5.

The gasket 30 shown in fig. 1 has a flat surface 56 in axial contact with the rear end surface a52b of the second enlarged end a52 and a convex curved surface 58 opposite the flat surface 56. The front portion of the gasket 30 has a structure that engages with the second enlarged end portion a52, and neither is movable downward in the radial direction, forming a shape with the concave surface 60 that is contacted by the convex curved surface 58 of the front face of the first housing part 32. Convex curve 58 in combination with concave surface 60 results in a spherical configuration for which plunger rod a5 may be displaced to first centerline C1 of plunger rod a5 upon the force of plunger rod a5 bending it, etc., such that second centerline C2 of plunger rod a5 has a refractive angle. The concave surface 60 may have a shape corresponding to the convex curved surface 58 (i.e., a shape having the same radius of curvature), but the radius of curvature of the concave surface 60 may be larger than that of the convex curved surface 58 as shown by a two-dot chain line in fig. 1. In this case, the spacer 30, together with the plunger rod a5, may also be displaceable in the radial direction within the housing 20. That is, second centerline C2 of plunger rod a5 may be eccentric with respect to first centerline C1 of cylinder rod a 1. Although not shown, the gasket 30 may have a concave curved surface as described above, and the first shell portion 32 may have a convex curved surface as described above. Plunger rod a5 is tiltable or eccentric with respect to cylinder rod a1, and plunger rod a5, spacer 22, second enlarged end a52, and spacer 30 are provided with diametrical clearances respectively between inner peripheral surfaces (hole portions 46, 48) of (second housing part 34).

As described above, in the coupling 10 of each of the above aspects, when the plunger rod a5 advances toward the stroke end at a relatively fast speed, the plunger rod a5 moves further forward according to inertia. The movement is restricted by the coupling 10, and instantaneous backward movement is generated by the reaction force. By this operation, in the conventional structure (see fig. 3), the plunger rod a5, particularly the tip thereof vibrates slightly in the axial direction, and thus the soup-melting pressing force (pressure) of the plastic core a4 in the plunger sleeve a6 fluctuates. The quality of the molded cast product may be affected. However, the front of each coupling 10 shown in this figure is comprised of a housing 20 with a spring 21 and an intermediate seat 22. The spring 21 is provided at the front portion (annular side wall 50) of the housing 20, and the second enlarged end portion a52 is biased rearward with respect to the front portion (annular side wall 50) and has a resistance force against an inertial force generated when the plunger rod a5 advances to the end of the stroke. The intermediate seat 22 is interposed between the spring 21 and the second enlarged end a52, and has a pressure receiving surface 52 on the front side that receives pressure from the spring 21 and a contact surface 54 on the rear side that contacts the second enlarged end a 52.

According to the coupling 10 of the present disclosure, the behavior generated when the plunger rod a5 advances to the end of the stroke at a relatively fast speed may be suppressed by the spring 21. The spring 26 having the above-described resistance is provided between the second enlarged end a52 of the existing plunger rod a5 and the front portion (annular side wall 50) of the coupling 10, but if the second enlarged end a52 is small in the radial direction, that is, if the radial expansion from the second enlarged end a52 of the second shaft body a51 is small, it is difficult to transmit the urging force of the spring 21 to the second enlarged end a52 without the spacer 22. However, according to each coupling 10 of the present disclosure, even if the second enlarged end a52 is small in the radial direction (even if the protruding force is small), the urging force of the spring 21 can be appropriately transmitted to the second enlarged end a52 through the intermediate seat 22 due to the interposition of the intermediate seat 22. Therefore, it is possible to connect the existing plunger rod a5 and cylinder rod a1, not only to suppress the above memory behavior. That is, there is no need to newly provide plunger rod a5 and cylinder rod a 1. The plunger rod a5 is a long structural member, and is provided with a hole or the like through which cooling water flows, which is very expensive. According to the couplings 10 of the present illustration, the existing plunger rod a5 like this can be used directly.

In the coupling 10, the spring 21 is provided at the front portion (annular side wall 50) of the coupling 10, and if another spring is provided between the second enlarged end a52 and the first housing portion 32 (cylinder rod a1), the plunger rod portion a5 is allowed to move backward, and if the plunger rod portion a5 moves forward to the stroke end at a relatively high speed, the plunger rod a5 is likely to vibrate in the axial direction due to the above-described behavior, although not shown. However, in the coupling 10 of the present disclosure, rearward movement of plunger rod a5 (via spacer 30 and base 42) is limited by cylinder rod a 1. Therefore, the vibration phenomenon can be prevented.

As described above, the plurality of springs 21 generate, for example, a total of over 900N of elastic force in the axial direction. The casting apparatus can function as the biasing means described above by providing a plurality of springs 21 having the above characteristics, which are various in output from the cylinder rod a1 from a large size to a small size.

In each coupling 10 of the present disclosure, an axial force acts on the plunger rod a5, and even when the plunger rod a5 is bent, the configuration can allow this. One of which is a shim 30. That is, as described above, according to gasket 30, first centerline C1 of cylinder rod a1 makes second centerline C2 of plunger rod a5 have a refraction angle, and plunger rod 10 is likely to be displaced. In addition, spring 21 acts to allow plunger rod a5 to flex. That is, when the plunger rod a5 is bent, its force presses the plunger rod a5 along a portion of the circumferentially disposed plural spring 21 in the direction of the insertion of the seat 22 between the second enlarged ends a52, and its elasticity is compressed more. Similarly, since the plurality of springs 21 are elastically compressed by being partially pressed in the circumferential direction, the displacement of the plunger rod a5 is not restricted, and high stress such as the plunger rod a5 can be prevented from acting. The spring 21 is a coil spring which is heavily or extremely heavily loaded (in addition, the subsequent fluid pressure means is also the same) capable of resisting the rapid movement inertia force speed of its plunger rod a5 (that is, its elasticity is not easily deformed), the elastic deformation due to the bending of the plunger rod a5 which is slower than this speed, and the like is possible (easy).

In each coupling 10 of the present disclosure, the outer peripheral profile shape of the intermediate seat 22 is larger than the outer peripheral profile shape of the second enlarged end a52 of the plunger rod a 5. In the spacer 22, the radial dimension r1 of the region on the front surface side (pressure receiving surface 52) to which the biasing force is applied by the spring 21 is larger than the radial dimension r2 of the region on the rear surface side with which the second enlarged end a52 actually contacts in the contact surface 54 (r1 > r 2). According to this structure, even if the second enlarged end a52 is small in the radial direction (that is, even if the expansion of the second enlarged end a52 is small), the urging force of the spring a52 can be appropriately transmitted to the second enlarged end a52 through the intermediate seat 22.

According to each aspect of the present disclosure, plunger rod a5 is unconstrained and may prevent the action of high stresses on plunger rod a 5. Like each of the couplings 10 of the present disclosure, by providing the configuration for allowing the plunger rod a5 to bend, it is possible to suppress the occurrence of the misfit due to the so-called deformation phenomenon of the plunger rod a5 in the casting apparatus.

Example 2

Fig. 2 is a sectional view of the assembly means described above, in which a fluid structure is used instead of the spring 21 (fluid damper). In the coupling 10, the housing 20 (the second housing portion 34) forms a flow hole 70 through which a fluid can flow. The flow hole 70 is formed to penetrate inside and outside the housing 20, and forms an opening of an annular space 72 between the housing 20 and the plunger rod a5 (second shaft body a 51). The space is sealed by the annular space 72. Specifically, seals (O-rings) 74 and 76 are provided on the inner side of the front side (annular side wall 50) of the housing 20, the inner peripheral seal 74 is in contact with the outer peripheral surface of the plunger rod a5 (second shaft body a51), and the outer peripheral seal 76 is in contact with the inner peripheral surface (second enlarged hole portion 46) of the housing 20. When air is supplied as a fluid to the flow holes 70, the annular space 72 includes a portion inside the housing 20, instead of the mounting function of the spring 21 described above. That is, the inertial force of plunger rod a5 as plunger rod a5 advances to the end of its stroke is controlled as viewed from the front of housing 20 (annular sidewall 50) mounted behind second enlarged end portion a52 in accordance with the air pressure supplied by annular space 72. In addition, in its fluid-mounted manner, plunger rod a5 is intended to flex, whereupon plunger rod a5 acts to partially push second enlarged portion 22 into compression. Like this mounting means, the annular space 72 formed in the middle of the housing 20 and the plunger rod a5 (second shaft body a51) may be configured as a cavity in which a fluid exists. The urging means is composed of a plurality of springs 21 (see fig. 1), and has the same structure as the circumscribed circle of the plurality of springs 21 but has a larger diameter than the outer diameter of the second enlarged end a52 (the diameter of the circumscribed circle), and as shown in fig. 2, when the annular space 72 is in the form of a cavity, the diameter (outer diameter) of the outermost periphery of the annular space 72 (the cavity, i.e., the outer peripheral seal 76) is larger than the diameter (outer diameter) of the circumscribed circle of the second enlarged end a 52. That is, the air pressure means may be used, and the hydraulic pressure means for controlling the operation may be used. In the case of a large-sized (high output) die casting machine, the fluid (air pressure, oil pressure) system is preferably used. In the coupling 10 (see fig. 2) in which the annular space 72 is used as the urging member, the respective configurations (configurations other than the spring 21) described with reference to fig. 1 can be applied to the coupling 10 shown in fig. 2.

As described above, each coupling 10 of the present disclosure can connect the existing cylinder rod a1 and the existing plunger rod a5, and can suppress the above-described behavior that occurs when the plunger rod a5 advances to the stroke end at a relatively fast speed. As a result, adverse effects on casting quality can be suppressed.

The presently disclosed embodiments are intended in all respects to be illustrative rather than restrictive. The scope of the present invention is not limited to the above embodiments, and all equivalent configurations described in the claims and the claims are intended to be included within the scope of the present invention.

Claims

1. The utility model provides a coupler, includes drive shaft and driven shaft, its characterized in that: a shaft body having a driving shaft coaxial with the driving shaft in a direction of advancing and retreating along the shaft, a rear end of the shaft body being larger than a cross section of the shaft body, a coupling for connecting the rear end of the shaft body and the driven shaft to move integrally in an axial direction thereof, the coupling connecting the driven shaft and the driving shaft; the coupling comprises a shell, the shell for containing is arranged at the front end of the driving shaft and the rear end of the driven shaft, and the annular space seat of the rear end contact surface of the shaft body is connected with the coupling.

2. A coupling according to claim 1, wherein the driven shaft is coupled to the drive shaft by the coupling, the driven shaft having a second enlarged end portion for driving movement of the driven shaft.

3. A coupling as defined in claim 1, wherein said annular spacer is formed to have a larger outer peripheral shape than the outer peripheral contour of the rear end of the shaft body.

4. The coupling of claim 1, wherein said drive shaft and said driven shaft are eccentric about a first centerline of said drive shaft and a second centerline of said second driven shaft, and wherein said first centerline and said second centerline are angled and wherein said driven shaft is angled with a shim.

5. A coupling as claimed in claim 1, wherein a plurality of springs are provided at intervals in the axial direction of the coupling, the springs having a larger diameter of the circumscribed circle than the shaft body.

6. A coupling as claimed in claim 1, wherein an annular space is formed intermediate the housing and the driven shaft.