CN111664223A

CN111664223A - Sealing chain

Info

Publication number: CN111664223A
Application number: CN202010146830.0A
Authority: CN
Inventors: 林航平
Original assignee: Daido Kogyo Co Ltd
Current assignee: Daido Kogyo Co Ltd
Priority date: 2019-03-08
Filing date: 2020-03-05
Publication date: 2020-09-15
Anticipated expiration: 2040-03-05
Also published as: JP2020143765A; JP7308626B2; CN111664223B

Abstract

The seal chain of the present invention comprises: outer links for fixing pins to both end portions of the pair of outer plates; an inner link that is coupled to the outer link by press-fitting a bushing into a bushing hole formed in a pair of inner plates and fitting the pin into the bushing; and a seal ring for sealing the lubricating oil interposed between the pin and the sleeve. The inner surface of the outer plate is formed as a flat surface, the outer surface of the inner plate has a recess concentric with the sleeve hole, and the seal ring is accommodated in the recess and sandwiched so as to form a predetermined gap between the inner surface of the outer plate and the outer surface of the inner plate.

Description

Sealing chain

Technical Field

The present invention relates to a chain such as a roller chain, and more particularly to a seal chain in which a seal ring for retaining lubricating oil on a sliding surface between a pin and a sleeve is sandwiched between an inner plate and an outer plate.

Background

Conventionally, as shown in fig. 8, a seal chain 1 is configured with a roller chain as a basic structure, in which both ends of a bush 7 are partially protruded from an outer surface 6a of an inner plate 6, and a seal ring 11 is sandwiched between the inner plate 6 and the outer plate 2 so as to surround the bush protrusion 7a, the roller chain is configured by inserting a pin 3 into the bush 7 and alternately and jointlessly coupling outer links 5 and inner links 10, wherein the outer links 5 are configured by press-fitting the pin 3 to both ends of a pair of outer plates 2 and fixedly securing both ends of the pin by caulking or the like, and the inner links 10 are configured by press-fitting the bush 7 to both ends of a pair of inner plates 6 and loosely fitting rollers 9 into the bush 7 between the inner plates 6.

The seal chain 1 seals the lubricating oil sealed between the pin 3 and the sleeve 7 by the seal ring 11, and keeps the relative movement between the pin 3 and the sleeve 7 smooth, thereby maintaining the smooth bending of the seal chain 1 for a long period of time. At this time, the sleeve protrusion 7a restricts the gap between the inner plate 6 and the outer plate 2, and restricts the compression margin of the seal ring 11 sandwiched between the two plates 6 and 2, thereby preventing the seal ring 11 from being excessively deformed by pressure and worn out early, and further preventing the breakage.

However, in the seal chain 1, since the seal ring 11 is sandwiched between the outer side surface 6a of the inner plate 6 formed with a flat surface and the inner side surface 2a of the outer plate 2 similarly formed with a flat surface, the gap between the two plates 2 and 6 is enlarged, the gap between the pair of

outer plates

2 and 2 facing each other is enlarged, and the bending moment of the pin 3 fixed to the outer plates is increased. As a result, although it is illustrated in fig. 8 with a strong emphasis, the pin 3 is elastically bent and deformed, and the outer plate is elastically deformed by bending so as to expand outward, and the fatigue strength of the chain is reduced, and the pin 3 tends to fall off the outer plate 2, which reduces the tensile strength of the chain.

Further, since the outer panel 2 is expanded outward, the seal ring 11 is caught between the sleeve protrusion 7a and the inner surface 2a of the outer panel 2 on the outer side in the longitudinal direction of the outer panel 2, and the seal ring 11 is excessively pressed and deformed on the inner side in the longitudinal direction of the outer panel 2, which causes an unstable compression margin of the seal ring and an unnatural force to act on the seal ring, thereby hindering a proper sealing function. This may prevent smooth operation of the seal chain and shorten the life of the seal chain.

The sleeve 7 is formed by winding a plate-like member, cutting a round bar member, or cutting a pipe member. Therefore, the accuracy of the sleeve, particularly the end surface thereof, is not high, and the seal ring may be damaged by the end surface of the sleeve protrusion 7 a.

Conventionally, as disclosed in japanese patent application laid-open No. 2018-179121, a seal chain (roller chain) has been proposed in which a recess concentric with a pin hole is formed on the inner surface side of an outer plate, a projection is formed on the outer surface side, and a sleeve projection is housed in the recess together with a seal ring (see patent document 1).

In the seal chain disclosed in japanese patent application laid-open No. 2018-179121, the distance (gap) between the outer plate and the inner plate can be reduced by housing the sleeve protrusion and the seal ring in the recess, but in order to ensure the rigidity of the outer plate, a protrusion is formed on the outer surface side of the outer plate in a shape corresponding to the recess, and the pin is relatively lengthened. In this outer panel, the concave portion is formed on the inner surface side, the convex portion is formed on the outer surface side, and the rigidity is secured without increasing the weight, and the elastic bending of the pin and the flexibility of the outer panel associated therewith are suppressed to be small, and even if the pin is lengthened as such, the bending moment of the pin becomes larger, and the possibility of bending deformation of the pin and deflection in the expanding direction of the outer panel occurring is large as in the conventional seal chain shown in fig. 8.

Further, since the recessed portion is formed in the outer plate and the seal ring and the sleeve projecting portion are accommodated in the recessed portion, a predetermined gap is provided between the sleeve and the pin in order to ensure relative movement between the sleeve and the pin in accordance with bending of the chain, and thus relative movement is generated between the seal ring and the sleeve projecting portion accommodated in the recessed portion of the outer plate integrated with the pin in accordance with the gap. As a result, the seal ring may be caught between the front end of the sleeve protrusion and the outer plate, and the seal ring may be worn or broken early.

Disclosure of Invention

In one aspect of the present invention, a seal chain includes: an outer link having pins fixed to both end portions of the pair of outer plates; an inner link that is coupled to the outer link by press-fitting a bushing into a bushing hole formed in a pair of inner plates and inserting the pin into the bushing; and a seal ring that seals the lubricating oil interposed between the pin and the sleeve, wherein an inner surface of the outer plate is formed as a flat surface, the inner plate has a recess on an outer surface thereof, the recess is concentric with the sleeve hole, and the seal ring is accommodated in the recess and is sandwiched so as to form a predetermined gap between the inner surface of the outer plate and an outer surface of the inner plate.

Other features and advantages of the present invention will become apparent from the following description, which refers to the accompanying drawings.

Drawings

Fig. 1 is a plan view partially cut away a seal chain according to an embodiment of the present invention.

Fig. 2 is a perspective view showing an outer panel thereof.

Fig. 3 is a partially enlarged cross-sectional view of a seal ring having an X-shaped cross section attached to a recess portion having an edge portion.

Fig. 4 is a partially enlarged sectional view of a seal ring having an O-shaped cross section attached to a recessed portion communicating with a sleeve hole.

Fig. 5 is an enlarged cross-sectional view showing an embodiment in which the recess of the inner plate communicates with the sleeve hole.

Fig. 6 is an enlarged cross-sectional view showing an embodiment in which the gap between the recessed portion of the inner plate and the sleeve hole is defined by the edge portion.

Fig. 7 is a partially sectional plan view of the seal chain according to the embodiment of the present invention in which a tensile force acts.

Fig. 8 is a plan view showing a partial cross section of a conventional seal chain.

Detailed Description

Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in fig. 1, the seal chain 21 has a basic structure of a roller chain in which outer links 25 and inner links 30 are alternately and jointlessly connected, the outer links 25 are configured to be connected by press-fitting pins 23 to both end portions of a pair of outer plates 22 and to be prevented from coming off by caulking the both end portions of the pins, and the inner links 30 are configured to be fixed by press-fitting bushes 27 to both end portions of a pair of inner plates 26 and to loosely fit rollers 29 into the bushes 27.

An outer surface 26a of the inner plate 26 is formed as a flat surface, and an annular recess 36 concentric with the sleeve hole 35 is formed in the outer surface 26 a. The sleeve 27 is press-fitted and fixed to the sleeve hole 35 so that both ends thereof are substantially flush with the outer surface 26a of the inner plate 26. The gap between the recess 36 and the sleeve hole 35 is defined by an annular rim 37, and the front end surface of the rim 37 is flush with the outer surface 26a of the inner plate 26. Therefore, as shown in fig. 2, the recess 36 is formed of three surfaces, namely, an outer diameter side surface 36a, an inner diameter side surface 36b, and a bottom surface 36c, and is a groove independent of the sleeve 27 and the sleeve hole 35. As shown in fig. 3, the seal ring 31 is accommodated in the recess 36, the seal ring 31 is sandwiched between the inner plate 26 and the outer plate 22 with a predetermined compression margin, and the outer surface 26a of the inner plate 26 and the inner surface 22a of the outer plate 22 face each other with a relatively narrow gap C left.

As shown in fig. 3, the seal ring 31 may be an X-shaped seal ring having an X-shaped cross section, but is not limited thereto, and may have any shape such as an O-shaped seal ring having an O-shaped cross section (see fig. 4). The gap C between the inner plate 26 and the outer plate 22 may be a minute gap for maintaining a predetermined compression margin of the seal ring 31, but the gap G between the pin 23 and the sleeve 27 is set to be smaller than the gap C in order to avoid contact between the inner plate and the outer plate. The clearance C is 2% to 5% of the diameter of the pin 23, but is also preferably used to reduce the bending moment of the pin and to maintain the strength of the chain.

In the seal chain 21, a lubricating oil such as grease is injected between the pin 33 and the sleeve 27, and the lubricating oil is sealed by the seal ring 31. The seal chain 21 is configured such that the outer links 25 and the inner links 30 are bent as the chain travels, and the pins 23 and the bushings 27 are moved relative to each other during the bending, and the relative movement is smoothly performed by the lubricating oil sealed in the seal rings 31.

The seal chain 21 may have a simple structure in which the concave portion 36 is formed on the outer side surface 26a of the inner plate 26, and cost reduction can be achieved. In the seal chain 21, the seal ring 31 is accommodated in the recess 36 formed in the inner plate 26, so that the gap C between the inner plate 26 and the outer plate 22 is a minute space, and the inner surface 22a of the outer plate 22 is formed as a flat surface, so that the outer plate 22 has a predetermined rigidity without changing the plate shape. Therefore, the axial length of the pin 23 is longer than that of a normal roller chain without a seal ring by the above-mentioned minute clearance C, but the amount thereof is extremely small, and it is considered that the pin has substantially the same length as that of a normal roller chain.

Fig. 7 shows a seal chain 21 according to the present embodiment in a state where the same tensile load as that of the conventional seal chain 1 shown in fig. 8 is applied. In the present seal chain 21, since the pin 23 is not long, as shown in fig. 7, the bending moment acting on the pin 23 via the outer plate 22 is also small, the bending deformation of the pin 23 is small, and the flexural deformation in the expanding direction of the outer plate 22 is also extremely small, and as a result, the seal chain has high resistance to fatigue strength and tensile strength. In addition, the flexural deformation of the outer panel 22 is also small, the seal ring 31 is accommodated in the recess 36, the compression margin is also restricted by the gap C, and the deformation is not promoted by being appropriately compressed.

Next, a partially modified embodiment will be described with reference to fig. 4. In the present embodiment, since the shape of the recess portion for housing the seal ring 31 is different from that of the previous embodiment and other portions are the same, the same reference numerals are given thereto and the description thereof is omitted. The recess 36 'of the present sealing chain 21' communicates up to the sleeve hole 35, and the edge portion 37 dividing the sleeve hole 35 and the recess 36 in the previous embodiment does not exist. Fig. 4 shows a seal ring 31 having an O-shaped cross section (O-ring 31)₂) However, it may be a ring (X-shaped ring 31) having an X-shaped cross section as shown in FIG. 3₁)。

In the present embodiment, the concave portion 36' may be formed in the inner plate 26 so as to be concentric with the sleeve hole 35 and communicate with the sleeve hole, thereby facilitating the manufacture and further reducing the cost. In particular, for the recess 36', an O-ring 31₂Does not interfere with the sleeve 27, has good compatibility, and is formed by using the O-ring 31₂Cost reduction can be further achieved.

According to fig. 5 and 6, the X-seal ring 31 is applied₁The difference between the recess 36 formed by the separate annular grooves and the recess 36' communicating with the sleeve hole 35 will be described. For the X sealing ring 31₁In a natural state, the X seal ring 31 is positioned such that a flange a having a relatively wide width and a substantially circular tip portion is positioned on the center inner diameter side₁Is formed in a cross-sectional shape (see Japanese patent laid-open publication No. Sho 64-030946Japanese patent laid-open publication No. 2006-349086). When the cross-shaped ring is mounted between the inner plate 26 and the outer plate 22 and sandwiched therebetween, the cross-shaped ring is rotated about the center flange a, and is mounted with an X-shaped seal ring 31 having an X-shaped cross section₁。

As shown in FIG. 5, the X-seal ring 31 mounted on the recess 36₁A predetermined space e is present between the center flange a and the sleeve 27, the center flange a is in contact with only the inner surface 22a of the outer panel 22, the other flange b is in contact with the inner surface 22a, and the flanges c and d are in contact with the bottom surface 36c of the recess 36'. Therefore, the X seal ring 31₁The joint 4 is sealed by being sandwiched between the inner panel 26 and the outer panel 22 with a predetermined gap C therebetween and by being in contact with a predetermined compression margin.

As shown in FIG. 6, the X-seal ring 31 is installed₁When attached to the recessed portion 36, the center flange a comes into contact with the front end of the rim portion 37 to cause the X-seal ring 31 to be attached₁The center flange a is rotated so that the front end of the edge portion 37 and the inner surface 22a of the outer plate 22 are brought into close contact with the center flange a having a relatively wide width and the gap C for holding the lubricating oil is sealed. The X-shaped seal ring 31₁The other flange b is in contact with the inner side surface 22a, the flange c is in contact with the bottom surface 36c of the recess 36, and the flange d is in contact with the bottom surface 36c of the recess 36 and the corner of the inner diameter side surface 36b on the brim portion 37 side. Therefore, the X seal ring 31 is sealed with a predetermined gap C₁In the mounted state of being sandwiched between the inner panel 26 and the outer panel 22, the center flange a is brought into close contact with the sealing lubricant oil, and is reliably sealed with higher accuracy by the contact at 5 points in total.

A seal chain (21, 21') according to the present embodiment is configured such that a pin (23) is fitted into a bushing (27) and an outer link (25) and an inner link (30) are alternately and jointlessly connected, wherein the outer link (25) is configured such that the pin (23) is fixed to both end portions of a pair of outer plates (22), the inner link (30) is configured such that the bushing (27) is press-fitted into bushing holes (35) formed in both end portions of a pair of inner plates (26), and lubricating oil sandwiched between the pin and the bushing is sealed by a seal ring (31),

the inner side surface (22a) of the outer plate (22) is formed into a flat surface,

a recessed part (36) (36') concentric with the sleeve hole (35) is formed on the outer side surface (26a) of the inner plate (26),

the seal ring (31) is housed in the recess, and the seal ring (31) is sandwiched between the inner surface (22a) of the outer plate and the outer surface (26a) of the inner plate so that a predetermined gap (C) is present therebetween.

The seal chain may be formed with a simple structure in which a recess is formed in the outer side surface of the inner plate, and the seal ring is accommodated in the recess, so that the cost can be reduced, the inner side surface of the outer plate is a flat surface, the seal ring is accommodated in the recess, and the gap between the inner plate and the outer plate is a relatively narrow gap which is almost unchanged from a normal seal-free chain. Thus, the pin does not become long, the increase in bending moment of the stopper pin is prevented, the bending deformation of the pin and the extension flexural deformation of the outer plate are reduced, and the fatigue strength and the tensile strength of the seal chain can be improved. Further, the change in the compression margin of the seal ring is reduced, and the excessive compression deformation of the seal ring can be prevented by the gap, so that the sealing function of the seal ring can be maintained for a long period of time.

For example, referring to fig. 1, 3, and 6, the gap between the inner diameter side of the recess (36) and the sleeve hole (35) is defined by an edge portion (37) having a tip end coplanar with the outer surface (26a) of the inner plate (26).

The recessed portion and the sleeve hole are divided by the edge portion, so that the accuracy of the recessed portion, particularly the accuracy of the inner diameter side surface of the edge portion, is improved, the accuracy of contact with the seal ring is improved, and the wear and damage of the seal ring can be reduced.

For example, referring to fig. 4 and 5, the recess (36') communicates with the sleeve hole (35).

Since the recess communicates with the sleeve hole, molding of the recess is facilitated, so that productivity can be improved.

For example, the sealing ring (31)₁) Is formed in a cross section X in a shape of a letter.

The seal ring is an X-shaped ring with an X-shaped cross section, so that the sealing performance is improved, and the friction resistance caused by sealing can be reduced.

For exampleThe above-mentioned sealing ring (31)₂) Is formed in a shape of a letter in cross section O.

Since the seal ring is an O-ring having an O-shaped cross section, cost reduction can be achieved.

For example, referring to fig. 6, the seal ring (311) is formed in an X-shaped cross section having four flanges (a, b, c, d), one flange (a) of the four flanges is formed in a shape closer to a circle and wider in width than the other flanges (b, c, d) at the tip end of the flange (a), and the flange (a) is in contact with both the tip end of the rim portion (37) and the inner surface (22a) of the outer panel (22).

One flange of the X-shaped seal ring is formed to have a wide width and a circular front end portion, and the flange is brought into contact with the front end portion of the edge portion and the inner surface 2 of the outer panel, whereby the sealing performance of the seal ring can be improved

The clearance (C) is 2-5% of the diameter of the pin (23) and is set to be wider than the gap (G) between the pin (23) and the sleeve (27).

The gap is a narrow gap of 2-5% of the diameter of the pin, and is wider than the gap between the pin and the sleeve, so that the contact between the inner plate and the outer plate can be prevented.

Further, although the above embodiments are applied to a roller chain, the present invention is not limited to this, and may be applied to a chain other than a roller-less bush chain, for example. Further, by reducing the deformation of the pin and the outer plate, the pin can be reduced in diameter and the seal chain can be reduced in size and weight.

The present invention is not limited to the above embodiments, and various changes and modifications can be made without departing from the spirit and scope of the present invention. Therefore, for the purpose of disclosing the scope of the invention, the appended claims are presented.

Claims

1. A sealing chain is characterized in that a sealing chain body is provided,

the seal chain is provided with:

an outer link having pins fixed to both end portions of the pair of outer plates;

an inner link that is coupled to the outer link by a bushing pressed into a bushing hole formed in a pair of inner plates and by the pin being inserted into the bushing; and

a seal ring that seals lubricating oil interposed between the pin and the sleeve,

the inner side surface of the outer panel is formed as a flat surface,

a concave part is arranged on the outer side surface of the inner plate, the concave part and the sleeve hole are concentric,

the seal ring is accommodated in the recess and is sandwiched between the inner surface of the outer panel and the outer surface of the inner panel with a predetermined gap therebetween.

2. The sealing chain according to claim 1,

the gap between the inner diameter side of the recess and the sleeve hole is defined by an edge portion of which the front end is coplanar with the outer side surface of the inner plate.

3. The sealing chain according to claim 1,

the recess communicates with the sleeve bore.

4. The sealing chain according to claim 1,

the seal ring is formed in an X-shaped cross section.

5. The sealing chain according to claim 1,

the seal ring is formed in an O-shaped cross section.

6. The sealing chain according to claim 2,

the seal ring is formed in an X-shape in cross section having four flanges, one of which is more circular and wider in width than the other flanges at a front end portion thereof, and which is in contact with both the front end portion of the edge portion and the inner side surface of the outer panel.

7. The seal chain according to any one of claims 1 to 6,

the clearance is 2% to 5% of the diameter of the pin and is set to be wider than a gap between the pin and the sleeve.