WO2008113264A1

WO2008113264A1 - Sealing device and crawler with said sealing device

Info

Publication number: WO2008113264A1
Application number: PCT/CN2008/000564
Authority: WO
Inventors: Mingguo Dong
Original assignee: Mingguo Dong
Priority date: 2007-03-21
Filing date: 2008-03-21
Publication date: 2008-09-25

Abstract

A sealing device and a crawler with said sealing device are disclosed. The sealing device is used to create a seal between a first part (7) and a second part (6) of the crawler, in which the second part (6) can rotate with respect to the first part (7). The sealing device includes an annual spacing sealer (2), the annual spacing sealer (2) is used to space the first part (7) and the second part (6) and seal the corresponding end face of the second part (6) by its end face, and an annual elastomer (1) used to bias the spacing sealer (2) toward the second part (6). The crawler includes said sealing device.

Description

Sealing device and track with sealing device

Technical field

The present invention relates to a sealing device and a crawler provided with a sealing device which can be applied to a crawler type engineering machine. Background technique

In the sealing device of the Chinese Patent Publication Nos. CN 1721718 A and CN 1980828 A, the number of the seals in the countersunk hole (i.e., the annular space) of the track link is three to four, and is arranged in the radial direction. For example, for a 190mm pitch track, the sealing surface of the pin sleeve face has a radial dimension of about 8.4mm left and right. Three seals are arranged in the plane of 8.4mm in the radial direction to ensure the elastic rubber ring and the sealing ring. Under the premise of strength, the one-side radial dimension left to the thrust washer is less than 1 mm. For example, the number of seals arranged in the radial direction in the slot counterbore is four, and the thrust washer has no room for selection. Therefore, there is a lack of strength of the thrust washer, which in turn has a certain degree of applicability in application.

In addition, the contact area of the track link and the contact area of the roller (there is a longitudinal and horizontal gap between the connecting sections of the two links) is less than the middle section. The wear is also greater than the middle section, which in turn causes the track working surface of the track link to be uneven (that is, the middle of each link rail is low in the middle), and the roller travels on the uneven working surface of the rail to cause the cycle of the vehicle. The upper and lower jaws of the track link and the supporting roller of the track link impact each other. The impact of the impact on the roller is particularly serious, which increases the axial and radial clearance of the roller and leaks oil.

Moreover, the track shoes and the fastening bolts have not lost their use value, because the width of the track link fastening nut fixing work groove is larger than the diagonal of the outer square fastening nut, and the bolt is rotated together or exposed by the thread. Extra long rust can't be disassembled, but it is forced to be broken by flame cutting. 'The fastening bolt becomes a disposable product.

In addition, in the existing crawler integral chain link, the first type: the pin shaft and the link pin hole are gap-fitted. The fit of the pin and the pin hole of this structure is quickly increased due to the impact load. The other is: The pin and the link pin hole are interference fit. This type of construction requires special equipment for maintenance.

Furthermore, in the existing crawler split connecting link, the splitting of the split connecting link splitting interface to the large angle and the longitudinal depth of the connecting teeth reduces the joint strength of the links and increases the risk of breaking. Summary of the invention

Accordingly, it is an object of the present invention to provide a sealing device and a sealing device crawler having the sealing device, The sealing device and track at least partially overcome the problems of the prior art.

It is still another object of the present invention to provide a method of encapsulating an oil hole for a track lubrication system. Λ This method simplifies the sealing process of the packaging process.

Sealing Device Another object of the present invention is to provide a track link that can at least alleviate the problems of the prior art.

Another object of the present invention is to provide a split track link and an integral track link which can enhance the strength of the split track link, and the integral track link can facilitate the installation of the pin. . Sealing Device According to one aspect of the invention, the present invention provides a sealing device for sealing between a first portion and a second portion of a track. The second portion is rotatable relative to the first portion. The sealing device includes: an annular spacer seal for spacing the first portion and the second portion and for sealing by a corresponding end surface of the second portion through the end surface thereof; and an annular elastic member for The spacer seal is biased toward the second portion.

Preferably, the first portion is fixed to the shaft member and forms a substantially annular space with the shaft member, the annular space has an opening toward the second portion, and the second portion is rotatable about the shaft member The spacer seal is disposed in the annular space and mounted on the shaft member, and wherein the elastic member is disposed in the annular space.

According to an embodiment of the present invention, the spacer seal has an annular cut-away portion at an end of the outer periphery close to the first portion, and at least a portion of the elastic member is located at the cut-away portion.

The annular spacer seal can be made of metal. The end face of the second portion and the end face of the annular spacer seal may be substantially flat surfaces.

Preferably, the end surface of the annular spacer seal has an annular seal band on the outer peripheral side for preventing leakage of lubricating oil.

Preferably, the end surface of the annular spacer seal has a plurality of lubrication grooves on the inner circumferential side.

The plurality of lubrication grooves may adopt an axisymmetric structure and are evenly distributed in the circumferential direction.

The inlet of the lubrication groove may be in communication with the inner bore of the spacer seal. The lubrication groove may be linear, circular, or spiral.

Preferably, the lubrication groove has a width of 1 to 5 mm and a depth of 0.2 to 2 mm.

Preferably, the end face of the annular spacer seal has oil-storing pores in addition to the sealing tape and the lubrication groove.

Alternatively, the end face of the entire annular spacer seal forms a sealing tape for preventing leakage of lubricating oil.

The sealing device may further include a dust seal disposed between the inner peripheral wall of the first portion and the outer peripheral surface of the annular spacer seal.

Preferably, the elastic member seals between the inner wall of the first portion and the spacer seal. The object of the present invention is achieved by the following technical solutions:

A crawler belt using a sealing device of the present invention includes a crawler member provided with a counterbore, a rotating member of the crawler, a liquid sealing device disposed in a counterbore of the crawler member, and a rotation of the crawler belt disposed thereon a liquid lubricating device in the component, the sealing device comprising a metal ring and an elastic rubber ring attached to the metal ring, the liquid lubricating device comprising oil filling provided in the crawling member of the crawler belt a hole, an oil reservoir communicating with the oil hole, and a rubber stopper provided at the port of the oil hole.

According to another aspect of the invention, the present invention provides a sealing device for sealing between a first portion and a second portion of a track. The second portion is rotatable relative to the first portion. The sealing device includes: an annular spacer for spacing the first portion and the second portion; an annular elastic member disposed on an outer circumference of the annular spacer; and the annular elastic member shaft To the stacked combination seals, the seal forms a seal with the end faces of the second portion.

Preferably, the first portion is fixed on the shaft member and forms a substantially annular space with the shaft member, the annular space has a mouth opening toward the second portion, and the second portion is rotatable around the shaft member Rotating, the spacer is disposed in the annular space, mounted on the shaft, and wherein the elastic member and the sealing ring are disposed in the annular space.

Preferably, the annular elastic member is an elastic rubber ring.

Preferably, the inner peripheral surface of the annular elastic member is provided with at least one axial lubrication groove.

The annular elastic member may include a first portion having a smaller radial width and a second portion having a larger radial width, whereby the annular elastic member has a cross section of a figure-eight shape.

The seal ring may include: a body; and a cavity disposed in the body near an end of the annular elastic member, at least a first portion of the elastic member being fitted in the cavity.

The combination seal ring may further include: at least one annular seal lip extending from the body toward the second portion for forming a seal with an end surface of the second portion; a diameter of the at least one seal lip An outer side of the direction, an annular dust lip extending from the outer peripheral portion of the main body toward the second portion, an inner peripheral surface of the dust lip and a chamfered portion of the end surface of the second portion or a periphery of the rounded portion The outer peripheral surface is in contact with the inner peripheral wall of the first portion.

The combined sealing ring may further include: an annular groove disposed between the dust lip and the sealing lip. The annular groove may have a U-shaped or circular arc-shaped cross section.

Preferably, the annular groove has a depth of 1 to 5 mm and a width of 0.5 to 3 mn! .

The combination seal may further include: a slit extending from a bottom of the groove to the cavity.

In accordance with another aspect of the invention, the present invention provides a track comprising the above described sealing means for sealing between a first portion and a second portion of the track.

The crawler belt may further include: a shaft member having a cavity extending axially therein, the cavity having an opening portion at at least one end of the shaft member, the mouth portion being sealed by the plug. The plug may be provided with a blind hole in a substantially central portion.

The crawler belt may further include: a stepped portion provided at the opening portion, the stepped portion having a diameter larger than a diameter of the cavity portion for mounting the plug.

According to still another aspect of the present invention, there is provided a crawler belt comprising: a crawler chain link having a hole for placing a track shoe fastening nut; and a track shoe, the track shoe passing The bolt and track shoe fastening nut are secured to the track link, wherein the track shoe fastening nut has a generally cylindrical body.

The axis of the threaded bore of the track shoe fastening nut may be substantially perpendicular to the axis of the cylindrical body. The threaded hole may be closed on the side opposite to one side of the bolt.

The through hole may have a cylindrical shape corresponding to the track shoe fastening nut.

At least one of the two sides of the track shoe fastening nut in the axial direction of the threaded hole may have a plane substantially perpendicular to the axis of the threaded hole.

According to an aspect of the invention, there is provided a crawler belt comprising: a plurality of track links, each of the track links having a connecting section at two ends thereof for adjacent two link connections And an intermediate section between the connecting sections, the plurality of track links having a surface as a working surface, wherein the intermediate section has a cut-away portion on a side of the surface, through the cut-out portion, the plurality of crawlers The effective width of the working faces of the links remains substantially uniform in the longitudinal direction.

The intermediate section includes two sides extending in the longitudinal direction of the intermediate section and two ribs formed by the working face, and the cut-out portion may be a chamfer of at least one of the two ribs.

The cut-away portion may be a recess on one side of the surface between the two side faces extending in the longitudinal direction of the intermediate section.

The recess may be generally linear.

According to another aspect of the present invention, there is provided a split connecting link for a crawler belt, the split connecting link comprising: a first portion having a first main connecting surface and a first auxiliary connecting surface Providing at least one first connecting tooth and a second portion respectively on the first main connecting surface and the first auxiliary connecting surface, the second portion having a second main connecting surface and a second auxiliary connecting corresponding to the first portion The surface is respectively provided with at least one second connecting tooth on the second main connecting surface and the second auxiliary connecting surface, and the second connecting tooth is engaged with the corresponding first connecting tooth.

Preferably, the first primary attachment surface and the first secondary attachment surface and the second primary attachment surface and the second secondary attachment surface generally form part of an interface of the first portion and the second portion.

The first primary connection surface and the second primary connection surface are generally planar.

The angle of the first main connecting surface and the second main connecting surface with respect to the connecting plane connecting the center lines of the two connecting holes of the split connecting links for connecting the links may be a, where 0° a 29°.

The first auxiliary connecting surface and the second auxiliary connecting surface are used for two purposes of connecting the split connecting links The angle of the connection plane of the center line of the hole connecting the links may be 0°.

Preferably, the first auxiliary connecting surface and the first main connecting surface overlap at a projection portion on a connecting plane connecting the center lines of the two pin holes of the split connecting link, and the second auxiliary The connecting surface and the second main connecting surface overlap at a projection portion on the connecting plane connecting the centerlines of the two connecting links of the split connecting links, thereby increasing the total length of the connecting surface.

Preferably, one of the first portion and the second portion connected to the track shoe includes a pre-joining hole, and the other of the first portion and the second portion includes a corresponding threaded hole, thereby mounting the track shoe The first part and the second part are previously joined together by screws.

According to an aspect of the present invention, there is provided an integral connecting link for a crawler belt, the integral connecting link comprising: a first hole and a second hole for connecting a link; an expansion groove, the expansion a slot extending from the inner wall of at least one of the first aperture and the second aperture for a predetermined length for dividing a portion of the unitary link link into a first portion and a second portion that are relatively displaceable, thereby facilitating A shaft member is mounted in the at least one of the first hole and the second hole.

Preferably, the first portion includes a through hole, and the second portion includes a threaded hole coaxial with the through hole, by inserting a bolt into the through hole of the first portion and screwing into the threaded hole of the second portion The first portion is adjacent to the second portion, and the diameter of the at least one of the first hole and the second hole is reduced, and the shaft member is fixed in the first hole and the second hole Said at least one.

Alternatively, the first portion includes a threaded hole, the two portions being separated by screwing a bolt into the threaded hole of the first portion and pushing the second portion, the at least one of the first hole and the second hole Expanding in diameter to facilitate insertion of the shaft into the at least one of the first and second apertures, thereby securing the shaft to the shaft after the screw is removed In at least one of the first hole and the second hole.

Preferably, the first portion and the second portion are secured together by bolts after the screws are removed. Preferably, the integral connecting link for the track may further include: a bolt through hole for fixing the track shoe, wherein the expansion groove stops at the through hole. Alternatively, the integral connecting link for the crawler belt may further include: a terminating hole, the expansion groove terminating in the terminating hole for preventing stress concentration.

Preferably, the expansion tank communicates with the first hole and the second hole.

The integral connecting link for the track may also include two slots that branch from the end of the expansion slot. The expansion groove may have a linear shape, a curved shape, or a combination of a linear shape and a curved shape.

The expansion groove may have a width of between 0.12 and 5 mm.

The integral connecting link for the track may further include a sealing assembly for preventing lubricating oil in one of the first and second holes containing the lubricating oil from passing through the expansion groove Leaked to the outside.

According to an aspect of the present invention, the present invention provides a packaging method for an oil hole of a crawler lubrication system, The system includes a cavity formed in a pin of a track for connecting links and extending axially therewith, the cavity having an oil fill hole at at least one end of the pin, the method comprising: passing oil After the hole is filled in the system, a plug for closing the oil hole is provided; the plug is pierced through the plug along the direction in which the plug is inserted into the oil hole; the plug is pressed into the oil hole, and the gas in the system and the excess lubrication are passed through the tube. The oil is drained; and the tube is withdrawn from the plug, wherein the plug is resilient so that the plug can close the through hole pierced by the tube after the tube is withdrawn from the plug. The invention has the advantages that the single component of the sealing device highlights the versatility, the structure is simple, the manufacturing cost is low, and the process is advanced, and the application of the new scheme realizes liquid sealing and lubrication of various pitch tracks, especially the lubrication below 190 mm pitch. The track breaks through the bottleneck of the existing technology. The change of the track link and the connection method makes the product more scientific, competitive, and practical. The liquid sealed and lubricated track is concentrated in: saving money, material saving, energy saving, environmental protection, The field has important practical value and broad application prospects. DRAWINGS

These and/or other aspects and advantages of the present invention will become apparent and readily understood from the following description of the preferred embodiments,

Figure 1 is a schematic view showing the structure of the present invention;

Figure 2 is a partially enlarged schematic view showing a sealing device of the present invention;

Figure 3 is a schematic view of the metal ring structure;

Figure 4 is a partially enlarged schematic view showing another sealing device of the present invention;

Figure 5 is an enlarged schematic view showing the structure of the pin sleeve of Figure 1;

Figure 6 is a schematic view of the structure of the double pin seal lubricating track;

Figure 7 is a schematic view showing the structure of a double-sealed roller type lubricating track and a cross-sectional view of the roller;

Figure 8 is a schematic view showing the structure of the crawler chain link of the present invention;

Figure 9 is a schematic view showing the structure of the fastening nut of the present invention;

Figure 10 is an enlarged schematic view showing the structure of the crawler chain fastening nut fixing working groove of the present invention;

Figure 11 is a schematic view showing the structure of the present invention and the existing split type connecting link;

Figure 12 is a schematic view showing the structure of the split ambush double-layer connecting tooth link;

Figure 13 is a schematic view showing the structure of the integral track connecting link section;

Figure 14 is a schematic view showing the structure of the integral track connecting link curve of the expansion groove;

Figure 15 Schematic diagram of small pitch, short pin and package rubber plug structure;

Figure 16 is a schematic structural view of a monolithic crawler connecting link expansion groove sealing device; Figure 17 is a schematic illustration of a sealing device for an integral track link link in accordance with the present invention. detailed description

The specific embodiments of the present invention are further described below in conjunction with the embodiments.

Referring to Figures 1, 2, 4, there is depicted a sealing device for sealing between an outer link 7 (an example of a first portion) and a pin sleeve 6 (an example of a second portion) of a track according to the present invention. The pin sleeve 6 is rotatable relative to the outer link 7. The sealing device comprises a metal ring 2 (an example of an annular spacer seal). The spacer seal 2 is used to space the outer link 7 and the pin sleeve 6 and to seal against the corresponding end faces of the pin sleeve 6 through its end faces. The sealing device further includes an elastic rubber seal 1 (an example of an annular elastic member) for biasing the metal ring 2 toward the pin sleeve 6.

As shown in FIGS. 2 and 3, the stepped large end of the outer surface of the metal ring has the same sealing surface area as the rotating surface of the rotating part of the crawler belt, and the stepped small end non-sealing surface is a plane parallel to the large end sealing surface. The inner surface of the sealing surface is provided with a lubrication groove, and the outer surface is provided with a sealing tape.

The metal ring sealing surface lubrication groove adopts an axisymmetric structure or an open axisymmetric structure in which the ends communicate, and the lubrication grooves are evenly distributed in the circumferential direction.

The inlet of the metal ring sealing surface lubrication groove communicates with the inner hole of the metal ring, and the outer edge of the lubrication groove is connected with the inner edge 27 of the metal ring sealing tape.

The groove shape of the metal ring sealing surface lubrication groove may be a rectangular shape, a circular arc shape or a spiral wedge shape.

The metal ring sealing surface lubrication groove has a width of 1 to 5 mm and a depth of 0.2 to 2 mm. The remaining part of the surface of the metal ring sealing surface is processed with oil and pores, and the pore diameter is 0.50 mm, and the stepped small end surface and the outer surface are There is a shoulder on the surface.

The sealing surface of the metal ring is a smooth surface that does not lick the lubrication groove, and forms a full sealing band structure.

The counterbore of the track member is provided with only one elastic rubber ring and one metal ring, and the counterbore is located outside the rotating member of the track.

A separate polyurethane, rubber or modified rubber dust seal is inserted between the side wall of the counterbore of the track member and the outer side surface of the large end of the metal ring.

The assembled sealing device under the action of the elastic rubber ring realizes three functions of thrust, sealing and stability - 1) and the role of the thrust washer. In the countersink of the track link, the radial dimension of the unilateral side of any type of track pin bushing is defined by the design size, and the sum of the thickness of the seal member in contact with the pin bushing sealing face is limited by the unilateral radial dimension of the pin bushing. Lubricating the track to ensure the minimum effective mechanical strength of the seal, the thickness of the thrust washer in the seal can only be passively selected in the remaining space, and its strength determines the sealing quality of the track. ' A reasonable solution is to reduce the number of existing seals to two in the slot counterbore without losing functionality, ie the seal consists of "one elastic rubber ring 1 and one metal ring 2". This allows a limited space to be distributed to the remaining elastic rubber ring and metal ring seals, thereby increasing the radial dimension of the seal on one side and increasing the mechanical strength of the seal. The existing sealing ring and the thrust washer are replaced by a metal ring, and the outer surface of the metal ring is stepped. The stepped large end is the parallel plane of the sealing surface and the non-sealing surface, and the area of the mating surface is the same.

When the machine turns left, the non-sealing surface side of the metal ring in the counterbore of the track link contacts the bottom surface of the chain sinking hole, the other side sealing surface is in contact with the sealing surface of the pin sleeve, and the frictional resistance of the track plate contacting the ground and the driving wheel The forces are eventually concentrated on the metal ring, which is subjected to large axial loads. At this time, the strong thrust function of the metal ring ensures that there is no chance of contact between the inner side of the shaft end of the two links and the outer side of the sleeve end, and there is no friction and no trace of wear and falling metal powder. The metal ring between the end face of the pin sleeve and the bottom surface of the counterbore bears the strong impact caused by the torsional moment from the sudden right turn of the machine while receiving the axial load of the left turn. The magnitude of the impact strength is related to the axial clearance. In this way, the left and right movements are repeated to check the impact of the metal ring on the impact and wear. Due to the increase in the wall thickness of the metal ring, it is more than double the existing 203mm pitch lubrication track thrust washer, and the sealing surface is increased to With the same surface area, the impact bearing capacity is increased. Under the same axial force, the pressure of the metal ring sealing surface is reduced, and the strength of the thrust washer is completely solved.

2), the role of the seal. When the machine is in the process of turning and turning, the metal ring is subjected to the pressure and the impact force, and is also subjected to the rotating moment; when the track is turned from the straight section to the curved section of the outer surface of the driving wheel or the guiding wheel, the two links are The pin shaft starts to rotate with each other. This rotation is finally reflected in the relative movement between the metal ring sealing surface and the pin sleeve sealing surface. In the rotating state, the diameter and the area of the metal ring sealing surface are larger than the non-sealing surface, and the relative grinding The force is also larger than the non-sealing surface, and the metal ring may be driven to rotate. This requires that the elastic rubber ring and the metal ring, the bottom surface of the counterbore sinking hole, and the side surface of the counterbore have a static friction resistance greater than that of the metal ring and the pin sleeve sealing surface. Relative movement of friction. Otherwise, this action will cause relative rotation between the metal ring and the elastomeric rubber ring to disable the seal. Increasing the static friction resistance is equivalent to increasing the interference of the elastic rubber ring and the counterbore side. Excessive force will cause the elastic rubber ring to creep and seal.

The metal ring is in the same surface contact with the mating surface. The magnitude of the friction force interaction is reflected in the magnitude of the torsion amplitude of the elastic rubber ring. Under the condition that the friction force is not changed, the friction coefficient can be reduced to reduce the elastic rubber ring to be twisted. The extent of the lubrication of the lubricating oil in the metal ring lubrication groove at this time reduces the frictional force to solve the problem of following rotation, thereby ensuring the sealing between the two sealing faces in a rotating state.

The sealing surface of the metal ring is flat, and the sealing band 27 at the outer edge is a closed annular band to prevent the intrusion of contaminants to prevent leakage of lubricating oil. The width of the sealing band is only 1 mm and only a small part of the sealing surface of the metal ring. Belt The rest of the thrust bearing surface shares the pressure of the overload. The thrust bearing surface is machined with different shapes of lubrication grooves and fine holes. The lubricating groove and the pores are filled with lubricating oil to reduce the pressure of the sealing band. The metal ring sealing surface and pin The face seal of the end face makes the seal safer and more reliable.

Metal ring working conditions should be complex enough to resist impact, high hardness and wear resistance without changing the state of the art. The design uses alloy materials, and the sealing surface is super-finished. The surface hardness of the heat treatment is between HRC60~70, which is higher than the sealing surface of the pin sleeve, so that the metal ring becomes a seal with the same sealing surface size. The versatility of the metal ring changes the sealing structure, and the elastic rubber ring forms a sealing device in a new form, which enables liquid lubrication of the 190mm pitch and below.

The outer ring surface of the metal ring sealing surface and the pin sleeve sealing surface is in contact with the outside, and we control it to a minimum extent, mutually protecting the sealing surface from sand erosion to prevent sealing failure, and also to metal The outer diameter of the large end of the ring is reduced in part and inserted into a separate polyurethane dust ring.

When the metal ring is subjected to the axial force from the pin sleeve, the non-sealing surface is in contact with the bottom surface of the chain sinking hole, and the non-sealing surface is easy to follow the inclination tolerance of the bottom surface of the link counterbore and the center line of the pin hole; When the bottom of the metal ring of the factor is radially inclined, the sealing compensation function of the elastic rubber ring and the bottom surface of the counterbore can avoid the seal failure caused by the seal. There is also a factor that the radial clearance between the pin and the pin sleeve causes the metal ring sealing surface to follow the bearing surface of the pin sleeve to oscillate radially. Even if the clearance is controlled within a desired range, the radial oscillation between the two is inevitable. When a certain factor is radially inclined relative to the pin shaft, the axial clearance of the pin bushing should have a larger space than when the pin bushing is radially inclined to avoid interference.

The perpendicularity of the sealing surface of the pin sleeve face and the center line of the hole, the verticality of the bottom surface of the counterbore and the center line of the pin hole should be controlled between 0 and 0.02 mm; the machining accuracy and roughness of the inner surface of the pin shaft and the chain pin hole And the press-fit strength affects the sealing quality of the track; the parallelism of the two bottom surfaces of the metal ring also affects the sealing quality of the track. Excluding the above disadvantages, the sealing device achieves dynamic sealing.

3), the role of stable axial clearance. Figure 3 shows the six types of lubrication rings with different shapes on the surface of the metal ring. The sealing device with the elastic rubber ring is applied to the structure with different motion modes.

The metal ring has a tendency to increase in clearance by the action of the elastic rubber ring and the friction surface of the pin sleeve sealing surface for a long time. Whether the axial gap is stable and long-lasting is an important factor for the seal, and it is also the only unstable factor that changes. When the axial gap increases beyond the elastic range of the elastic rubber ring, the seal will fail.

The metal ring sealing surface is the same as the mating surface, which overcomes the shortcoming of the existing thrust washer wall thinness and the small contact area of the pin sleeve end face, which is easy to wear and cause the axial gap to increase. However, increasing the contact area is limited. To further strengthen and stabilize the axial gap, changing the shape, width, angle and spacing of the lubrication groove of the metal ring seal surface helps to reduce the sealing surface. The coefficient of friction will play a positive role in stabilizing the axial clearance of the track under different working conditions.

When the track link is in the upper and lower straight sections, there is almost no relative movement between the metal ring sealing surface and the pin sleeve sealing surface. When the driving wheel or the outer surface of the guiding wheel is curved, the angle between the two links is about 35°. When the track links are rotated relative to each other, the metal ring sealing surface is separated by 36°. The lubricating oil in the lubrication groove ensures that the sealing surface of the pin bushing is fully lubricated except for the sealing tape (Fig. 3c).

Theory and practice point out that the spiral wedge lubrication groove can produce large bearing capacity and liquid film stiffness. For example, the fluid dynamic effect mechanism is applied optimally in the sealing lubrication of the metal ring and the end face of the pin bushing, which is of great significance for extending the service life of the track.

Fluid dynamic mechanical seals are now used under high-parameter (high-pressure, high-speed) conditions. There are no precedents for poor static conditions in low-speed shock rings and changing the direction of rotation at any time. The metal ring of the pin sleeve and the different quality partner materials is equivalent to the dynamic and static two rings. When the existing single-directional spiral wedge type lubrication groove is rotated in the forward direction, the positive pressure effect is supported to support the external load. When the impurity is invaded, the seal will fail; when it is rotated in the opposite direction, a negative pressure effect will occur. This negative pressure effect is consistent with the closing force direction of the elastic rubber ring and points to the sealing surface of the pin sleeve end face. The two forces are superimposed to increase the rotational resistance. The strength of the elastic rubber ring is also increased by the torsion, which will invalidate the seal.

Therefore, the metal ring lubrication groove establishes a spiral wedge structure, and the generation of a negative pressure effect is the most desirable result. The curve adopted by the metal ring sealing surface lubrication groove 17 (Fig. 3d) is an axisymmetric figure in which the parabola is converging and the wedge end is connected. When the pin sleeve (moving ring) rotates in a certain direction, the metal ring (static ring) is symmetric. Both sides of the shaft: one side produces a positive pressure effect; the other side produces a negative pressure effect. The lubrication groove on the side of the positive pressure effect is at the end of the convergent structure. The pumping effect is increased by the pumping effect. The moment of rotation promotes the formation of the liquid film. This effect is beneficial even if it is small, which can reduce the friction. Force, this pair of friction points in the boundary lubrication state undoubtedly improve the lubrication quality, the inlet and outlet of the lubrication groove are equal in size and the ends are connected, and the lubricating oil in the wedge groove under the pressure difference Accelerated flow, taking away frictional heat and impurities, this structure of the lubrication groove strengthens the lubrication effect of the end face to prevent dry friction, which is beneficial to lubrication and heat dissipation.

The end of the parabolic wedge lubrication groove 30 is connected to the inner diameter of the sealing band, where it is the outermost edge of the lubrication. The forced delivery of the lubricating oil to it is the meaning of the present invention. The end-reduced reduced diameter channel acts as a throttling, parabolic wedge lubrication groove. The number is 5-7 pairs. The remaining portion of the surface of the sealing tape 27 except the lubricating groove 17 is machined with oil storage pores 29 for storing lubricating oil, and the pores 29 have a diameter of 0.50 mm. Under special circumstances, the end of the symmetry axis of the lubrication groove can be broken by the factors such as the speed and temperature (see Figure 3f). The angle and shape of the lubrication groove can be changed according to different angles (see Figure 3e, g). ). Since the friction surface is lubricated, the oil film with a certain thickness is maintained, the lubrication condition of the surface is improved, the axial gap is stabilized and durable, the sealing surface is lubricated to reduce the rotational resistance, and the torsion of the elastic rubber ring is reduced. The torsional fatigue strength avoids relative rotation between the metal ring and the elastic rubber ring. Regardless of the speed of the above-mentioned lubrication grooves, the two rings are always closed to meet the requirements of zero leakage of the lubricating crawler liquid.

As shown in Fig. 4, there is described a sealing device for sealing between the outer link 7 (an example of the first portion) and the pin sleeve 6 (an example of the second portion) of the track according to the present invention. The pin sleeve 6 is rotatable relative to the outer link 7. The sealing device includes: a thrust washer 124 (an example of an annular spacer) for spacing the outer link 7 and the pin sleeve 6; an elastic rubber ring 125 (an example of an annular elastic member) And an outer circumference of the thrust washer 124; and a combined sealing ring 118 axially overlapping the elastic rubber ring 125, the sealing ring forming a seal with the end surface of the pin sleeve 6.

The sealing device is axially superposed by a thrust washer 124 in the counterbore 4 of the member of the track, a profiled elastic rubber ring 125 radially adjacent to the thrust washer, and the profiled elastic rubber ring. A combination seal 118 is formed.

The end faces of the thrust washers 124 are each provided with a linear lubrication groove having a width and a depth of 1 to 3 mm and a spacing of 120°, and the outer surface roughness Ra is 0.4.

The inner surface of the shaped elastic rubber ring 125 has at least an axial lubrication groove, and the outer surface thereof has a figure-eight shape.

The combined sealing ring 118 is formed of rubber or polyurethane to form a sealing ring and is integrated with the dustproof ring. The combined sealing ring 118 is provided with at least one sealing lip 126, at least one inner dust lip 128 and one outer dust lip. 121, the inner surface of the inner cavity of the combined sealing ring is a figure-eight shape, and a U-shaped or arc-shaped regulating groove 129 is formed between the dustproof lip and the sealing lip to prevent mutual interference, and the depth of the adjusting groove is 1 5mm, the width is 0.5-3mm, the angle between the adjustment groove and the horizontal plane is between 0° and 90°, and the radius of the circular arc adjustment groove is 1 to 5mm.

A combined through seal is formed on the combined seal between the adjustment groove 129 and the upper surface of the profiled elastic rubber ring 125.

The counterbore 4 of the track member is provided with only one thrust washer 124 and an outer 8-shaped elastic rubber ring axially overlapping with an inner 8-shaped combination seal.

The outer 8-shaped elastic rubber ring and the inner 8-shaped combined sealing ring are combined into one integral piece by the same material.

The number of seals in such a sealing device is the primary design condition, and the combination sealing ring 118 and the elastic rubber ring 125 are axially superposed to reduce the radial space occupied by the sealing member, and the two sealing members have the same radial dimension, The minimum of the figure-eight shape in the cavity of the sealing ring is to lock the connection of the outer part of the outer shape of the outer ring of the elastic rubber ring into the joint sinking hole 4 (see Fig. 4), and the sealing is only one position in the radial direction. The piece implements the functionality of two pieces. This structural change provides a relatively loose radial space for the repositioned seal, i.e., the required thickness of the thrust washer 124 is ensured, and the resilient rubber ring 125 is left in sufficient position to increase the body thickness to ensure a reliable, long lasting The elastic energy avoids the shortage of the three seals in order to reduce the wall thickness and reduce the strength. The counterbore is only equipped with a thrust washer and an axially superimposed seal assembly, so that the seal of the medium and small pitch lubrication track is Another way to implement it.

The track link counterbore 4 is the mounting position of the seal at the end of the link shaft end 7, and the countersunk port 127 is the only passage for the intrusion of contaminants. The outer ports of the existing dry crawler and sealed lubricated crawler are all open, and the small foreign pollutants in this mouth are not easy to be discharged after being invaded, and the elastic force of the elastic rubber ring is weakened by the precipitation of the pollutants at the port. Invalid. If the open gap is blocked here, the intrusion of contaminants is blocked, which will prolong the service life of the seal. Here, the narrow seals are only supported by the combination.

The combination of the dust seal 117 has a support to enter the counterbore port 127, and an anti-dust ring 117 of the combination seal 118 and the seal ring 116 are provided with an adjustment groove 129 to prevent interference with each other. The adjustment slot is provided with a certain depth, width and angle to ensure reliable operation of the dust lip 128 and the sealing lip 126.

In the initial state of assembly, the diameter of the inner lip 128 of the dust seal is larger than the outer diameter of the sealing surface S of the sleeve end face. Under the action of the elastic rubber ring, the inner chamfer of the inner ring of the dust ring and the end face of the pin sleeve 81 is straight. — t The working surface starts to contact. At this time, the elastic rubber ring 125 is strengthened by the compressive elasticity. The lip 128 that continues to press the dust ring is swollen by the outer chamfered surface 81 of the end face of the pin sleeve. At this time, the sealing of the combined sealing ring The lip 126 comes into contact with the sealing surface of the pin sleeve 6 end face. Due to machining tolerances and cumulative tolerances, the u-shaped or circular arc-shaped adjustment groove 129 starts to function, which ensures the sealing ring lip 126 and the inner dust-proof lip. 128 does not interfere.

When press-fitted in place, the sealing lip 126 of the combined sealing ring and the sealing surface of the pin sleeve 6 are tightly combined to achieve sealing, and the diameter of the outer surface of the pin-faced outer chamfering working surface 81 and the inner dust-proof lip 128 is greater than dustproof. The inner diameter of the ring lip is free, and the inner dust ring lip 128 is inflated so that the two are combined tightly to achieve sealing, and the first portion is protected from dust while achieving sealing.

The outer port of the side wall 119 of the link counterbore is the last stop position of the outer lip 121 of the combined seal ring. Here, it is static dustproof, and the outer side wall of the outer port of the link counterbore has no relative rotation with the outer lip of the dust seal. Movement, but the axial direction is fretting. In order to make the seal here effective and durable, the roughness Ra of the surface of the side wall 119 of the link counterbore is 0.8, when the lip of the first inner dust ring is outside the end face of the pin sleeve When the chamfered cone is inflated, the outer lip 121 of the dustproof ring is also swollen and pressed against the side wall 119 of the outer port of the counterbore to achieve dustproofing of the second portion.

The above two lip-type dust seals, when the axial clearance of the pin bushing changes, the dust seal and seal of the combined seal ring The change of the circle is not equal. The function of the adjustment groove is to evenly distribute the elastic force of the elastic rubber ring to the dust ring and the sealing ring, so as to ensure no interference between the dustproof and the sealing, and not because of one of the sealing rings or the prevention The resistance of the dust ring increases and affects the force of the other sealing ring or the dust ring. The mediation groove of the combined sealing ring acts as a mediator to achieve the compensation function. In order to increase the mediation function, the u-shaped or circular arc-shaped regulating groove 129 can be opened through the groove 115 (see FIG. 4b), and the dust-proof ring 117 and the sealing ring 116 can also be made of the same or different sealing materials.

No matter how the axial and radial gaps of the pin bushing change, the two kinds of mediating grooves (blind grooves, troughs) can force the dust ring and the sealing ring at the same time, and the dust ring prevents the mud from entering the inside through the outer port. The sealing ring permanently seals the liquid lubricating oil in the oil reservoir under protected conditions.

The inner diameter of the thrust washer 124 and the outer diameter of the pin 5 are not interfered with each other, and the outer diameter of the thrust washer and the inner diameter of the combined sealing ring and the elastic rubber ring are also left, and the combined sealing ring of the polyurethane material after pressing has a certain The radial change of the strength is not large, but the axial and radial directions of the elastic rubber ring will change, especially the radial deformation is easy to occur. The inner surface of the elastic rubber ring is in contact with the outer diameter of the thrust washer to prevent friction and friction. The friction is avoided by the outer 8-shaped curve in the middle and lower part of the elastic rubber ring. At the same time, the inner surface of the elastic rubber ring has at least one longitudinal lubrication groove in the longitudinal direction, and the lubricating groove is filled with lubricating oil to reduce friction and anti-wear. The outer surface of the thrust washer is ground. The roughness Ra value is 0.4, and a linear lubrication groove with a width of 1 to 3 mm and a depth of 120° is provided on both ends of the thrust washer to facilitate the flow of lubricating oil.

The above two liquid seals are mechanical seals. It is suitable for the end face seal with large space impact load.

In particular, the first sealing device is more suitable for forward and reverse operation, and the fluid dynamic pressure effect mechanism can be applied to the floating oil seal of the roller, the guide wheel and the driving wheel in an optimal manner, thereby increasing the bearing surface in the wheel and reducing The over-extrusion of the elastic rubber ring prolongs the sealing life. The metal ring in the first sealing device can be separately used for the sealing of the end faces of various rotating shafts and pumps, such as composite materials, ceramics, etc.; The same rubber or polyurethane can be used to form the elastic rubber ring, the dust ring and the sealing ring to form a combined sealing ring.

When the track is a single-axis crawler including a pin and a pin bushing, a track shoe fastening nut, a track link, a track connecting link, and a track shoe, on the inner side of each track link or connecting link shaft end The counterbore is provided with a sealing device consisting of a metal ring and an elastic rubber ring which is attached to the metal ring or a sealing device composed of a thrust washer, an elastic rubber ring and a combined sealing ring. The pin shaft is provided with an oil filling hole, and the pin shaft oil hole port is encapsulated by a cone blind hole rubber plug.

The track pin shaft diameter may be a through hole in the oil hole of Φ 38mm or less; the pin hole oil hole port may also be processed into a stepped hole, and the short pin shaft oil hole port is formed with a groove.

The track pin sleeve has at least one oil reservoir 13 on the surface of the inner hole below Φ 38ιηιη, and the end face of the pin sleeve 6 The outer chamfer is Y 45°, and the outer surface (s—t) of the chamfer is a straight line segment, and a small rounded transition is adopted at both ends of the straight line segment; the perpendicularity of the pin end face and the center line of the inner hole is 0~0.02 Mm, the pin cover sealing surface roughness Ra value is 0.4.

Since the adaptability of the sealing device will be extended in various track applications of small and medium pitches, the volume of the lubricant volume is particularly valuable and important. When the oil hole is too thin, the meaning of the oil reservoir is reduced. Can be used as a channel. Therefore, excavating and increasing the volume of the oil reservoir is a key to whether small pitch and short pin lubrication can be implemented.

No matter what kind of equipment is used to process the elongated hole, it is difficult to turn the pin oil hole into the short hole, and the processing technology is improved. The through hole 95 of the pin can improve the productivity and reduce the cost, for example, the oil hole is too thin. If the pin strength is not affected, the diameter of the pin hole port can be appropriately enlarged. The stepped hole is used for packaging. The rubber plug at both ends can be removed from the special purpose track to change the oil. ' ,

Shortening the length of the center hole at the other end of the pin can extend the pin oil passage to increase the oil storage volume; the shortened cone blind hole rubber plug 92 is equal to the extension oil passage 91 and can also increase the oil storage volume; however, the short cone blind hole rubber plug 92 is used. Bonding to the side of the filler port will result in frictional failure and seal failure. Therefore, the short pin bore port is machined with a recess 93 that accommodates and meets the need for a shortened tapered blind bore rubber plug package (Figure 15).

The outer surface of the pin sleeve and the outer chamfer surface are in contact with the sealing ring and the dust ring. Here, there is a rotary motion and an axial movement. The surface roughness, dimensional accuracy, pin end face and inner hole center line The verticality is critical to the sealing of the lubricated track.

The press sleeve 6 press-fit working surface and the link 8 are pressed without any damage to the front section of the outer chamfered surface 81 (see Fig. 5), and the only available inner dustproof is on the outer chamfered surface 81 of the pin sleeve 6 Therefore, the outer face chamfering angle Y 45° of the pin sleeve adopts the straight section working face (s-t) to facilitate the dust seal sealing, and the small rounded transition is adopted at both ends of the straight section to facilitate assembly; the pin sleeve end face and the inner hole The verticality of the center line is 0-0.02 mm, and the surface roughness Ra of the pin sleeve sealing surface is 0.4 to ensure the sealing quality.

The oil reservoir volume of the pin hole in the center oil hole of the pin above Φ 38mm can meet the demand. As the track pitch becomes smaller, the pin shaft strength is naturally thinned due to the shear stress, and the oil hole becomes thinner. The storage of oil is difficult to guarantee. Therefore, a small portion of at least one portion of the inner surface of the pin sleeve 6 is removed by machining to form an oil reservoir in the sleeve to compensate for the reduced oil volume of the pinhole oil hole diameter; The hole 12 is in communication with the pin oil hole, and the two oil reservoirs are integrated to provide sufficient lubricating oil for the small shaft diameter lubricating track. At the same time, the outer diameter of the outer diameter of the pin sleeve is constant, so that the strength of the pin sleeve can be extended and the service life can be prolonged.

The elastic rubber ring 1 is placed on the outer surface of the metal ring 2, and one side is in contact with the a surface of the back surface of the metal ring sealing surface, and the other surface is higher than a part of the non-sealing surface of the metal ring, and is inserted into the counterbore 7, 10 of the counterbore 4, Elastic rubber ring and sink The outer side of the hole is an interference fit, and the metal ring is suspended in the center of the counterbore. After assembly, the elastic rubber ring is compressed higher than the part of the non-sealing surface of the metal ring, and the height is equal to the height between the non-sealing surface and the a-side, the compressed rubber The ring is sealed to the bottom of the counterbore sinkhole, blocking the passage of lubricant from it. At this time, the compressed rubber ring generates compression energy between the bottom surface of the chain sinking hole and the metal ring a surface, and the compression energy is converted into an elastic force acting on the metal ring a surface, and the metal ring is under the action of the elastic rubber ring. The sealing surface is in close contact with the sealing surface of the pin bushing to achieve a reliable seal. This sealing finally seals the lubricating oil in the shaft and the sleeve to achieve liquid lubrication.

When the machine turns to the left, the pin sleeve is displaced along the axial direction relative to the pin shaft by the torsional moment. The clearance between the metal ring sealing surface on the left side of the chain link and the pin sleeve sealing surface is zero, and the left rubber ring is slightly compressed by the elastic force. Reinforcement; a slight gap between the metal ring sealing surface on the right side and the sealing surface of the pin sleeve is in a floating state. At this time, the compression energy of the elastic rubber ring is instantaneously released, and the metal ring is elastically bombed to the sealing surface of the right pin sleeve. The clearance is eliminated, and the elastic force of the elastic rubber ring is slightly reduced, but it is still in the effective elastic range, and the gap cannot exceed the elastic range of the elastic rubber ring beyond the oil leakage.

With the support of the strong axial thrust bearing capacity of the metal ring 2, the inner side of the chain link 7 and the outer side of the chain link 8, the outer side of the chain link 9 and the inner side of the chain link 10 are no longer in contact. . Thereafter, the metal ring 2 floats freely in the axial direction within the set gap range with the external force and the elastic rubber ring. Any axial movement of the pin sleeve 6 relative to the pin 5, and the occurrence of the pin end face clearance, will instantaneously compensate for the axial floating of the metal ring to achieve a dynamic seal.

The detection and oiling are simultaneously performed on the special equipment, and the seal is detected by the pinned oil injection hole in the medium vacuum state, and the oil storage chamber 13 communicating with the radial communication hole 12 is filled after passing.

The center hole of the pin shaft is the oil filling hole filled with liquid lubricating oil. There are two seals for the existing oil filling hole. First, insert a rubber rubber plug with a cone through hole into the pin oil hole. When the pin seal is tested, the injection is qualified. After the liquid lubricant is full, a plastic plug with a self-locking boss is inserted into the through-hole of the cone rubber plug. Among them, the plastic plug has a minimum diameter of 6.5 mm, and when the pin oil hole diameter is 5 mm, it is obvious that the prior art cannot be packaged.

The cone blind hole rubber plug is a seal for the oil-filled hole (see Figure 1). The cone-shaped blind rubber plug is used to reduce the number of package seals to one. It forms a complete sealing system together with the sealing device. The rubber plug of the cone blind hole is not limited by the size of the oil hole. The blind hole of the rubber plug can be set at any end. The length of the rubber plug can be increased or decreased to meet different needs. The blind hole shortens the length of the unopened section of the rubber plug and reduces ventilation. The penetration strength of the catheter for packaging.

A method of encapsulating an oil hole for a track lubrication system according to the present invention will now be described with reference to Figs. 1, 15, and 17. The system includes an oil passage 11 (an example of a cavity) formed in a pin of a crawler belt for connecting a link and extending axially thereof, the oil passage 11 having an oil hole at at least one end of the pin shaft , the method includes - After filling the system through the oil hole, a plug 3 for closing the oil hole is provided;

Insert the tube 150 into the plug 3 along the direction in which the plug 3 is inserted into the oil hole;

Pressing the plug 3 into the oil hole while discharging the gas in the system and the excess oil through the pipe;

The tube 150 is withdrawn from the plug 3, wherein the plug 3 has elasticity so that after the tube 150 is withdrawn from the plug 3, the plug 3 can close the through hole pierced by the tube.

When the oil storage chamber 13 is filled with oil, the oil injection hole port is upward, and a fine ventilation duct 150 is embedded in the center of the round body with a flat surface at the front end, so that the end point of the extension portion of the ventilation duct has a horizontal hole 152 and the outside atmosphere. The cooperating encapsulation device 151 encapsulates the oil injection hole by a method of balancing the air pressure inside and outside the oil reservoir.

The specific operation is as follows:: A package device 151 (a) having a sharp end with a fine ventilation duct 150 is penetrated along the center of the blind end of the rubber plug 3 of the cone blind hole (b), and the plane of the front end of the round body abuts the cone The large end plane of the blind hole rubber plug 3 is inserted into the port of the oil hole 11 together. When the small end of the rubber plug cone enters the oil hole port, force the rubber plug of the blind hole to enter the hole along the oil hole port. At this time, the pressure in the oil injection hole rises, the gas or liquid is discharged with the ventilation duct, and the rubber plug enters the depth of the oil injection hole until the attachment drawing requirements; the compressed cone blind hole rubber plug is tightly coupled with the oil injection hole side wall (c ), while the ventilation duct is set, the small hole of the blind hole rubber plug is quickly restored to the original state (d), and the liquid lubricating oil in the oil injection hole is isolated from the outside, that is, the package is completed.

When the track is a double pin lubrication track comprising a track shoe, a pin shaft and a double cone hole connection plate, the track member provided with a counterbore is a double cone hole connection plate, and is connected in each double cone hole. The counterbore on the inner side of the plate is provided with a sealing device consisting of a metal ring 2b and an elastic rubber ring lb which is attached to the metal ring. Each track plate 16 has at least two oil hole holes on the side of the pin hole. 11 is an oil storage chamber, and communicates with the pin hole 22 through the through hole 21, at least one oil storage groove is omitted on the inner surface of the pin shaft hole (not shown), and the double taper hole connecting plate with the sealing device is installed in the pin shaft At both ends, the pin and the connecting plate are connected by a cone or a taper hole, and the track plate is an integral track or a split track, and the split type has an intermediate connecting plate, and the opposite ends of the intermediate connecting plate are countersunk. The sealing device is installed inside, and the oil filling hole port of the oil storage chamber is encapsulated by a cone blind rubber plug.

The problems to be solved with small shaft diameter lubricated tracks are: chain sinking holes and oil storage chambers. Double pin lubrication track (see Figure 6) The oil reservoir is located in the track plate to solve the problem of oil storage on the small shaft diameter lubrication track; and the counterbore is where the seal is installed, and the counterbore is placed in the double cone connection In the board, this solves the sealing problem of the small shaft diameter lubrication track.

The connecting working surfaces of the two ends of the double pin-lubricated track pin and the connecting plate are respectively processed into a cone and a tapered hole, and the countersunk hole is processed at the outer end of the large end of the connecting plate to prepare the sealing member lb, 2b; The tapered hole head also processes the countersunk hole to provide a working space for the anti-loose fastening nut. The fine thread at both ends of the track pin shaft is connected with the connecting plate and then tightened with a loosening fastening nut, and the connecting plate taper hole is small. The bottom plane of the hole is assembled and the height of the pin cone is at least 2 mm, so that the anti-loose fastening nut is tightened and the cone and the taper hole are tightly connected. The anti-loose fastening nut is used for quick disassembly and assembly. After tightening, the nut cannot be exposed to prevent hard objects from being scratched. The sealing surface of the track pin hole end face is lower than the thickness of a metal ring on the end face of the track shoe, so that the seal in the counterbore of the connecting plate is assembled and protected from the impact of the drive gear. The design dimensions are automatically adjusted after the anti-loose fastening nut is tightened, and the axial clearance of the pin shaft is automatically adjusted. At least two oil storage chambers are opened in one track shoe.

Referring to Figure 6, this embodiment is a double pin liquid seal lubricated crawler, which is another type of lubricated crawler. The double-spindle track shoes are available in single or split type. The single track shoes 16 are connected by a double tapered hole connecting plate 14 at the left and right ends; the split track plate has an intermediate connecting plate 200 to increase the joint strength, and the double tapered connecting plate 14 is equivalent to a driven gear. The drive gear is in the vacant part between the two double cone connection plates.

The pin 5b penetrates into the pin hole of the track shoe 16, and the double taper connecting plate 14 with the sealing device is fitted into the two ends of the pin 5b, and then the screw of the loosening fastening nut 15 is screwed into the both ends of the pin 5b. When the anti-loose fastening nut is tightened according to the specified torque, the axial clearance is adjusted. The axial clearance is ensured by the design size, and the track pin shaft 5b and the double-cone hole connecting plate 14 adopt a cone and a taper hole. The method makes the connection firm and reliable, and the tapered hole ensures the sealing between the sealing device and the counterbore of the double-cone hole connecting plate, and further seals with the sealing surface of the pin hole of the track shoe.

When the track is a roller type lubricating track including an inner link, an outer link, a pin and a pin sleeve, a roller, and a needle bearing, a metal is installed in the inner counterbore at both ends of each link. The sealing device consisting of the ring 2a and an elastic rubber ring la which is in contact with the metal ring processes three through holes in the middle of the outer circumferential surface of the roller to the center of the roller by 120°, and is an oil filling hole and an oil storage chamber. And communicating with the oil storage chamber through the through hole of the pin sleeve, the surface of the inner hole of the roller is a straight line segment and is equipped with a needle roller shaft of the same length without a cage, the bosses at the two ends of the roller are 3-10 mm as a sealing surface, and the metal ring sealing surface is completely The sealing strip structure, the slotted counterbore is molded or side welded, and the oil filling port of the oil reservoir is encapsulated by a cone blind rubber plug.

The extension lines of the three through holes do not intersect at the center of the circle only in a straight line (see Fig. 7A-A), and the stress concentration at the time when the roller is subjected to a certain force is discharged, and the surface convex contact with the metal ring 2a at both end faces of the roller is convex. A step of 3-10 mm is provided, so that the sealing surface is hidden in the counterbore 4, and the thrust function of the metal ring makes the end faces of the roller not contact with the inner surface of the link 8; the inner side of the outer link 7 and the outer side of the inner link 8 Do not touch.

A cage-free needle roller bearing 33 is arranged between the surface of the inner hole of the roller and the outer surface of the pin sleeve, and the ends of the needle bearing are rounded to a length slightly lower than the end faces of the roller, and the long needle bearing has a reasonable radial clearance to prevent rolling. The needle is twisted on the surface of the inner hole of the roller, and the surface of the metal ring 2a which is in contact with both end faces of the needle bearing does not process the lubrication groove to avoid interference with the end surface of the needle bearing, so as to adapt to the roller rolling and the axial movement of the needle roller bearing, so The surface of the metal ring 2a adopts a fully sealed band structure (see Fig. 3b).

The groove of the existing inner surface of the roller is machined with a groove to install the needle roller, so that the surface of the inner hole of the roller is stepped. The outer circumference and the inner hole of the roller 20 of the invention are straight segments without strong step load carrying capacity, saving raw materials and processing, and high production efficiency, and replacing the grease with liquid lubrication is obviously superior to the former.

The slotted counterbore adopts a molded or side welded reinforcing plate, and a rubber ring and a metal ring seal are arranged in the counterbore of the inner link 8 to respectively form a first seal with the sealing faces of the two end faces of the roller; The middle portion has a through hole 34 for communicating the oil hole 26 with the inner surface of the pin sleeve, and the lubricating oil reaches the inner surface of the pin sleeve and the pin shaft to achieve liquid lubrication; the intermediate recess portion 35 of the pin sleeve is also a part of the oil storage chamber. A rubber ring and a metal ring seal are also installed in the counterbore of the outer link 7, and a second seal is formed on both end faces of the pin sleeve. It adopts liquid lubrication, low temperature starting resistance, small running stability, low shock absorption capacity and low noise. It overcomes the large resistance of the existing grease aging operation and the lack of stuck phenomenon of the needle roller bearing.

Referring to Figure 7, this embodiment is a roller type liquid seal lubricated crawler, which is another type of lubricated crawler. The roller-type lubricated tracks are respectively composed of two identically acting sealing devices, one internally and one externally sealed. A bolt hole is drilled in the plane of the ear plate perpendicular to the inner link 8 for mounting a track shoe or a material box, etc., and the outer diameter of the roller 20 of the roller track is larger than the link height to roll on the relatively stationary rail.

The chain link of the roller track is stamped and formed by a thin plate die, and a reinforcing plate is welded on the outer end surface of the outer link 7, and the counterbore is machined around the center line of the hole or the countersunk hole of the outer link 7 is forged; the inner link 8 Use thick plate or die forging, and also machine the counterbore on the inner side of the hole center.

The sealing device is respectively inserted into the counterbore of the outer link 7 and the inner link 8, and the pin sleeve 6a is inserted into the inner hole of the roller 20 which is filled with the needle bearing 33, and both ends are press-fitted with the inner link 8, axial direction The gap is ensured by the tooling, and the sealing surfaces of the two end faces of the roller are in contact with the outer edge sealing surface of the metal ring 2a of the full sealing band structure, and the inner side surface of the metal ring acts as a smooth retaining ring to limit the axial displacement of the needle bearing, the needle roller The bearing is restrained between the two metal rings, and is radially restrained between the outer surface of the pin sleeve 6a and the inner surface of the roller 20; the pin 5a is reloaded into the pin sleeve 6a, and the pin 5a and the outer link 7 are pressed. The double seal formed by the pin sleeve 6a and the external sealing device is realized, and the inner and outer links of the same piece number are assembled in pairs each time.

The double-sealed roller-type lubricated track is designed to ensure that there is a gap between the links after the assembly of the track, which eliminates the risk of the existing friction between the axially-loaded links of the track being broken.

As shown in Figures 9 and 10, the present invention provides a track. The crawler includes: a track link 149 having a hole for placing the track shoe fastening nut 146; and a track shoe 56 that secures the nut 146 and the track with the bolt 141 and the track shoe The links 148 are fastened together. The track shoe fastening nut 146 has a generally cylindrical body.

The track shoe fastening nut is a cylindrical shape 146 or a non-cylindrical shape formed by a plane 142 or two equal parallel planes 112 at a centerline of a vertical threaded hole on the outer surface of the cylindrical fastening nut; The end faces of the non-cylindrical fastening nut are parallel to the center line of the threaded hole, equidistant or not equidistant, cylindrical and open with a flat surface The threaded holes of the non-cylindrical fastening nut can be blind holes.

The track link fastening nut fixing work groove adopts an asymmetric structure of the side edges 113, 110 and the center line of the bolt hole, and the side edges and the bottom surface can be vertical or inclined, and the fastening nut is restricted by any side. The degree of freedom of rotation, the bottom working surface 111 is parallel to the bottom surface of the link, and the radius of the transition fillet between the two sides and the bottom working surface of the working slot is smaller than the radius of the non-cylindrical fastening nut 112, non-cylindrical fastening The width of the plane working face of the nut is smaller than the width of the working face at the bottom of the working groove, and the top 109 of the working groove is arched.

The track link fastening nut fixing work groove adopts a symmetrical structure of the side edges 144 and the bolt hole center line, and the two sides and the bottom surface can be vertical or inclined, and the working groove width is larger than the non-cylindrical fastening nut diameter 2 10mm, the bottom working surface 143 is parallel to the bottom surface of the chain link, and the radius of the transition fillet between the two sides and the bottom working surface of the working slot is smaller than the radius of the non-cylindrical fastening nut 142, and the non-cylindrical nut 142 is flat. The width of the working surface is smaller than the width of the working surface of the bottom 143 of the working groove, and the top 147 of the working groove is arched.

The track link fastening nut fixing working groove adopts a circular 145 and a bolt hole center line symmetrical structure, the working groove diameter is larger than the cylindrical fastening nut 146 diameter 2-10 mm, the circular working groove bottom working surface and the chain The bottom surface of the joint is a parallel curved surface, which is parallel with the pin hole at both ends of the chain link, and the radial tolerance of the center line of the link fastening bolt hole 140 and the center line of the circular working groove is 0.20 mm, and the circular fastening nut fixed working groove The position can be arbitrarily selected between the two bottom faces.

The track links 108, 148, 149 are thickened by 0-10 mm on the side. When the link guide rail is placed horizontally on the upper side, the angle from the outer side of the longitudinal middle section working face is 0-10 mm below the angle of less than 45°. Remove a part from the surface of the working surface of the guide rail, or in the longitudinal middle of the working surface of the middle section of the link, perpendicular to the working surface of the link rail 0-5 mm, at least a u-shaped groove with a width of 0-10 mm, the link rail working surface The side surface may be a single inner side surface, a single outer side surface, or an inner side surface and an outer side surface.

The non-cylindrical fastening nut 112 has two identical parallel working faces; the non-cylindrical fastening nut 142 has two different working faces, one flat surface and one curved surface to adapt to two different working grooves; The fastening nut 146 has two identical curved working faces that are not constrained by direction; cylindrical holes and threaded holes with a flat non-cylindrical fastening nut can be blind holes to prevent thread contamination. As shown in Figure 9,

In order to prevent stress concentration at the bottom turn of the working slot, the existing outer square nut increases the radius of the avoidance, so that the width of the working groove is larger than the diagonal of the outer square nut, thereby causing the fixing work slot to be fixed. The vertical distance from the outer surface of the non-cylindrical nut to the center line of the threaded hole is greater than the vertical distance from the surface of the outer square nut to the center line of the threaded hole, which is designed according to the curve of the outer surface of the nut. Work slot.

The non-cylindrical nuts a, b are converging and narrowing from the X point down to the working surface y point. When the X point of the nut contacts the side of the working groove, the bottom corner of the working groove intersects with the bottom plane. The bottom point of the bottom face of the cap is y There is also a certain distance, no contact with each other and no interference. The curved structure of the outer surface of the non-cylindrical nut gives the condition that the bottom corner of the working groove increases the rounded corner. The increase of the rounded corner can reduce the stress at the corner of the link working groove. Concentrate on the craftability and mechanical strength of the track chain forging. More importantly, the ideal spacing required on the side of the non-cylindrical nut and the side of the link groove makes the width of the working groove smaller than the diagonal of the nut, thereby limiting the freedom of rotation of the nut to a fixed degree. purpose. The cylindrical fastening nut c differs from the non-cylindrical nut a in that the shape of the working surface is different, which is the difference between the plane and the curved surface (as shown in Fig. 10). The cross-sectional curve of the outer surface of the cylindrical or non-cylindrical nut may also be elliptical.

The outer surfaces of the three nuts have a common curve characteristic. The difference from the existing working groove is the change of the distance between the nut and the sides of the working groove; the combination with the working surface of the working groove is the same as the existing one. The position change can generate a variety of suitable track link fastening nut fixing work slots, just to name a few (see Figures 9, 10).

The existing track link connecting section has a slit 136, 150 in the longitudinal direction and the transverse direction (see FIG. 8b), so that the force receiving area of the link rail working face connecting section 135 and the intermediate section 133 are not equal. The reason for the mechanical operation is that the wear is not equal due to the unequal area of the force, and the working surface 134 of the guide rail is uneven. This is a common phenomenon, only the light and heavy, in the middle section and the connecting section of the link rail working surface 134, The middle section and the connecting section of the side working face of the guide rail are adjusted by increasing or decreasing the geometrical dimension; or in the middle of the middle section of the working surface of the link rail (see Fig. 8e), the longitudinal and transverse gap areas of the connecting section are excavated. The sum or the sum of the areas, the force areas of different sections of the working face of the guide rail are equal or tend to be equal.

The side of the working surface of the thickened track link rail is 0-10 mm. From the sides of the longitudinal working face of the middle section, the angle is less than 45° from the 0-10 mm to the surface of the working surface of the guide rail. The remaining thickness is still retained. At the same time, full consideration is given to the contact area between the inner side of the outer end flange of the roller shell and the remaining portion of the outer side working surface 130 of the track link rail. Keeping the remaining portion of the outer side working surface 130 in a straight line, and ensuring that the inner side of the flange of the outer end of the roller shell does not interfere, and the contact area necessary for the correcting ability is ensured; Figure 8a, b As shown in Fig. 8c, as shown in Fig. 8c, from the outer side of the intermediate section working surface 130 downwards from 0 to 10 mm, the angle is less than 45°, and the surface width of the working surface of the rail is 0-10 mm, and the inner side is not moved. ;

It can also be as shown in Fig. 8d as shown in Fig. 8d. It is less than 45° from 0~10mm outside the working face of the middle section. The width of the working surface of the guide rail is 0~10mm, and the outer side is not moved.

It can still be as shown in Fig. 8e as shown in Fig. 8e. In the longitudinal direction of the working section of the middle section of the link, perpendicular to the working surface of the link guide, 0-5 mm, at least one u-shaped groove with a width of 0-10 mm; the two sides are not moving.

As shown in FIG. 8, the crawler according to the present invention includes: a plurality of crawler links 149, which are in the crawler links 149 Each has a connecting section 135 at its two ends for connection with two adjacent links and an intermediate section 132 between the connecting sections 135, the plurality of track links 149 having a surface as a working surface 134. The intermediate section 132 has a cut-away portion on one side of the surface, by which the effective width of the working face of the plurality of track links 149 is maintained in the longitudinal direction (the direction in which the plurality of crawler links extend) Generally consistent.

After the track link is assembled, the effective width of the rail working surface connecting section 135 is equal to the effective width of the intermediate section 132 or the effective width of the connecting section is larger than the middle section, so that the stress area of the connecting section and the middle section of the working surface of the link rail is also increased. Equal to each other, so that the link rail working surface 134 is worn and the hook is always in a straight state, which increases the stability of the mechanical running, and the service life of the crawler is naturally prolonged.

Referring to FIG. 10a, the track links 108 fastening nut circumferential working groove sides 110, 113 and the bolt hole center line adopt a non-equal width upper narrow lower width structure, and the outer surface of the non-cylindrical fastening nut is The curved surface is completely different from the planar structure on both sides of the existing fastening nut, and the curved surface has a strong obstacle resistance. When the outer surface of the nut 112 is in contact with the side of the working groove 113 of the link 108, the nut 112 does not occur. The stagnation phenomenon; after the fastening bolt 141 is connected to the fastening nut 112 through the track shoe 56 and the link fastening bolt hole 140, the working groove side 113 guides the nut to the fixed working groove bottom 111, as the nut When entering the bottom of the working tank, the width of the bottom working surface is greater than the width of the plane working surface of the non-cylindrical fastening nut, the bottom plane of the nut is not interfered in the space at the bottom of the working groove, and the side of the working groove is restricted by the side 113 The freedom of rotation of the nut facilitates the overall layout of the bolt fastening bolt holes.

Referring to FIG. 10b, the track link 148 fastening nut fixing work groove sides 144 and the bolt hole center line adopts an upper narrow and a lower width structure, the width of which is smaller than the diagonal of the non-cylindrical fastening nut 142, the working groove The narrower lower width on both sides of the 144 and the outer side surface of the curved surface of the fastening nut 142 are not the X point of the diameter of the nut 142, and the working groove is narrow so that the closest point is at the diameter of the X point, and the working groove is wider. Keep the extension lines on both sides away from the link fastening bolt holes 140, and the rounded corners at the intersection of the bottoms are away from the link fastening bolt holes 140, so that the outer edge of the bottom surface of the nut is enlarged and the pitch of the fillet is large, subject to interference. The possibility is reduced. The two sides can choose an optimal angle around the center of the outer circumference of the nut, and maintain a desired distance from the outer surface of the nut surface to limit the degree of freedom of rotation of the nut, so that the radius of the fillet at the intersection can be kept constant. . The bottom working surface of the working tank 143 does not need to be machined to fix the groove, only the processing plane is required, and the small processing amount can ensure the technical requirement of contacting the working surface with the nut 142.

The non-cylindrical fastening nut is combined with the chamfering of the two sides 144, 113 and the bottom surface 143, 111 of the working groove to avoid interference and realize the combination of the bottom surface of the working groove and the working surface of the nut, as shown in FIG. b is shown in the enlarged view; the diagonal of the non-cylindrical fastening nut is larger than the width of the working groove and cannot exceed the side of the working groove. It is limited in the working groove. It is the freedom to tighten the nut by the sides of the working groove. The degree is fixed, instead of the existing fastening nut being fixed by the chamfers on both sides of the working groove. The non-cylindrical fastening nut has only the up and down direction of freedom and a small deflection angle, and it is no longer possible. Follow the bolts to rotate together, no need to use other auxiliary fixing tools for disassembly and assembly. Non-cylindrical fastening nuts are assembled with anti-loose threads and the bolt threads will not be exposed and will not be polluted.

Referring to FIG. 10c, the track link 149 fastening nut fixing working groove 145 adopts a circular structure, no stress concentration point around the circular structure, good mechanical property, and a small amount of processing can ensure the technology of fixing the working groove joint surface. Claim;

The two holes of the circular fastening nut fixing work groove are different from any one of the working grooves, and it can be drilled on the production line. For example, the hot die forging and blanking process can be used to reduce the workpiece on-line with the pin hole. Time, round work slots are very beneficial for specialized production.

The cylindrical fastening nut 146 is different from the existing U-shaped fastening nut, and is also different from the existing outer square fastening nut. It can be used as a working surface on either side without directionality, in order to disassemble the nut. The radius of the convenient circular working groove is larger than the radius of the cylindrical nut.

The cylindrical fastening nut 146 is combined with the circular fixed working groove 145 in a recumbent manner, and the cylindrical fastening nut enters the working groove with only a small degree of freedom in any direction. When the nut 146 is combined with the bolt 141, Limited by the upper and lower degrees of freedom of the working slot, the hexagonal bolt ends are convex to facilitate assembly, and the left and right degrees of freedom of the working slot are limited. The nut does not need a fixing process to facilitate production and assembly. As the torque increases, the curved surface of the outer surface of the nut 146 automatically follows the circular working groove 145, and the contact area is uniformly fixed and reliable; the fastening nut is freely reusable and becomes a durable fastener instead of once. Sex products.

Referring to Figure 1, a split connecting link 49 for a crawler according to the present invention includes a shaft end link 51 (an example of a first portion) having a first main connecting surface (e.g., NW) And a first auxiliary connecting surface, at least one connecting tooth is disposed on the first main connecting surface, and at least one connecting tooth 54 is disposed on the first auxiliary connecting surface. The split connecting link 49 further includes: a socket end link 50 (an example of a second portion) having a second main connecting surface (e.g., EF) corresponding to the shaft end link 51 and a second auxiliary a connecting surface, at least one connecting tooth is disposed on the second main connecting surface, and the connecting teeth on the second main connecting surface are engaged with the connecting teeth on the corresponding first main connecting surface. At least one connecting tooth 55 is provided on the second auxiliary connecting surface, the connecting tooth 55 being engaged with the corresponding connecting tooth 54.

The split track connecting link adopts a linear extended working face (E-F, NW) multi-tooth a small angle structure, and the shaft end link and the end link are combined on the multi-tooth split surface, and the split link is arranged Between the point M of the bottom surface and the line N of the lower bottom surface (between M and N), one or more tension teeth 54 and 55 are added, and the angle β of the tension tooth is in the range of < β 90°, and the multi-tooth working surface The angle a is between 0° a 29 ^D. The number of teeth is 5 to 10. The non-toothed section of the multi-tooth working surface is an extension of the bottom surface of the tooth or an extension of the flank. The split track connecting link 49 adds an ambush servo bolt 53 which is connected in the middle of the two fastening bolt holes 57 of the link; the ambush servo bolt end is lower than the track shoe and the connecting chain The joint faces of the joints are such that the link fastening bolt holes 57 are identical to the integral link fastening bolt holes of the same type.

The split track connecting link 49 adds an exposed service bolt 58 for connecting between the two fastening bolt holes 57 of the link, and the exposed servo bolt end is higher than the track shoe and the connecting chain. The connecting surface of the joint, and the fastening bolt hole 57 of the chain link is the same as the integral chain fastening bolt hole of the same type, and the track shoe 40 of the exposed service bolt connecting link is added with two through holes, and The through hole is welded around the reinforcing sleeve. The connecting tooth working face of the split track connecting link 49 is double-layered, and there is a hollow through groove 47 between the M-N, so that the shaft end link 51 and the end link 50 are connected along the center line of the two holes. The vertical direction can be moved up and down, and the degree of freedom of movement up and down allows the connecting teeth to be combined and separated, and the cut-out portion 48 of the hollow through groove is returned to the original position to function as a safety lock.

The split track connecting link technology requires that each pair of shaft end links and sleeve end links are assembled in one plane so that the rear link guide working faces are also in one plane, and the existing assembly datum is mostly in the link. On the two bottom surfaces, that is, the working surface of the rail and the link and the track shoe are connected to the working surface. It is difficult to detect whether the left and right connecting link sections are in one plane, and the assembly surface without the assembly surface poses a hidden danger to the quality of the product. In this case, the assembly reference surface will be lost after the next maintenance welding by using the guide working surface of the connecting link, and the re-assembly will have no reference surface, so that the left and right connecting links are not in one plane, and the internal stress is serious after the connection. It will be pulled off in a short time, and it is difficult to repair on site. This requires a precedent; this requires a two-bottom surface that does not depend on the link, and it is convenient and quick to ensure that the split face of the link is secured in one plane. Assembly datum.

The added 54 sets of end pull teeth and 55 shaft end pull teeth are like two hook hooks, which are pulled together to form a first force point. The center of the pin hole 59 is used as the origin to set a plane rectangular coordinate system, so that the first force point is The y-axis direction rises to the upper L line of the pin hole 59, and moves in the horizontal direction of the X-axis to the center of the pin hole 59 to the K line, and the intersection point of the L and K lines increases the height of the first force point, and its purpose It is to lower the height of the second force point. Then, the first force point is directly down to the N point to form a second force point, and the second force point is composed of a plurality of teeth to form a main force point. At this point, the first force point V, the second force point N, together with the third force point D of the conjoined portion below the pin hole, constitute a stable triangle of the VND force.

With a stable triangle, the multi-tooth straightening length E-F working surface a can be lowered even lower, and a series of problems with low angle connection can be solved. Otherwise, the chain extended working surface E-F can not achieve low angle. (It changes the existing single, double, arc tooth, large _a angle, split track link, the first force point is low, the right side is insufficient), because the geometric angle of the split surface changes, various The force direction of the force also changes, reducing the component force of the connecting tooth surface and the shear stress of the connecting bolt.

With a stable triangle, the angle between the connecting teeth of the split track link (E~"F, N-W) and the bottom surface is between 0° and 29°. Work surface (E~~F, N-W) to increase joint strength and assembly accuracy.

The connecting lines of the connecting tooth working faces E-F and NW of the split connecting link are respectively in a straight line and the two straight lines are parallel. When the connecting links are separated, the E-F straight line is on the shaft end link 51, N — The W line is on the end link 50 and its length is greater than the length of the straight line of the existing connecting link split face. First put a pair (left and right) The end links 50 are assembled with the ends of the pin sleeve 6, respectively, and the left and right end link segments are separated in one plane.

When assembling, the left and right link sections are in a plane, and can be measured immediately by a flat gauge. The basis is that a flat gauge is placed on the N-W linear working surface of the left and right links. Whether it is corrected on the press machine in a plane at any time until it is ensured that the left and right link sections are pressed in place in one plane. At this time, the two bottom faces of the connecting links are also in one plane. The extended multi-tooth straight working surface increases the joint strength, assembly accuracy and speed of the connecting links. The assembled end of the inline track end link and the shaft end link become a closed endless track.

The connected split link is subjected to the same external load as the integral link, not at the two stress points of V and N in the same tooth plane, and one main and one auxiliary are simultaneously forced to connect the separated two links 50, 51. The combination of the tension teeth 54, 55 and the main force-bearing teeth form the same whole, together with the third force point D, forming a stable triangle of the VND force, which makes the connection reliable and durable. It is conceivable that the tensile strength of the action link without the tension tooth in the M-N segment will be greatly reduced, and the force arm with a height h=h0-hi will be different, so that the first force point V will be lowered to the second force point. N, which can be derived from the comparison of the drawings la la, b; that is, the first point of the prior art, point N in Fig. 11c, when the angle of a falls to 0°, the embodiment can still The implementation is shown in Figure l lb, especially on small to medium pitches.

The added servo bolt has two functions:

1. The split track connecting link is provided with a servo bolt 53 which is connected during assembly in the middle of the two fastening bolt holes 57. The track shoes 40 and 56 are removed from the split fastening bolt 52. Trouble and inconvenience. When the split shaft end link and the end link are connected, screw the servo bolt into the servo screw hole and tighten it according to the standard torque, and then install the track shoe. The added connection servo bolts 53 and 58 can be compared. Make the track connection easy and convenient.

Second, to strengthen the strength and reliability of the connection, the connection of the servo bolts 53, 58 is also a fastening bolt, so that a fastening bolt is added to the working surface of each track connecting link, and the strength of the connection naturally increases. Extended multi-tooth straight line The working surface increases the freedom to select the position of the bolt holes. The ideal size can be selected in the same size as the integral chain fastening bolt holes of this model, and the track shoes can be interchanged and unified.

Referring to Figure 12, this embodiment is another form of the split connecting link - the split connecting link can be combined and separated by the upper and lower movable degrees of freedom connecting teeth, and the first layer of teeth of the connecting tooth is The tooth shape of the second layer of teeth may be the same or different, but the first layer of teeth cannot affect the bonding and separation of the second layer of teeth, and the movable distance between the M-N hollow channels is at least combined with the connecting teeth. The required heights are equal, or greater than the height required to combine and separate.

Since the number of connecting working teeth is increased by the large angle folding, the cutting point M of the first layer of teeth can be extended from the connecting section of the chain link to the beginning of the middle section of the chain link, and the thickness of the middle section is double the connecting section, so that the first layer of teeth The connection strength is more stable and reliable; the connecting working surface of the second layer of teeth is reduced to the same height as the bottom surface of the common link working groove, the tooth angle of the connecting tooth working surface can be set more reasonable, and the reliability of the connection is further enhanced.

The tooth angle can also be other shapes that are easy to assemble, whereby the component forces generated on the second tooth surface are M- The first layer of the back of the N-shaped hollow channel is replaced by the first tooth back, and the fastening bolt hole 57 of the connecting link is the same as the integral chain fastening bolt hole of the same type. The bolts are divided into an ambush type 53 and an exposed type 58.

When the cut-out portion of the hollow through groove is replaced, the fastening bolt can be lengthened through the cut-out portion of the hole and extended through the cut-out portion of the first layer of the toothed hole, and the hollow through groove is cut out. Part of the freedom to move up and down in the original position eliminates the separation of the shaft end link and the end link, and the cut-out portion of the hollow groove is returned to the original position to add a safety lock to the connection of the link.

The integral connecting link 60 for a crawler according to the present invention includes: a first hole 66 and a second hole 65 for connecting links; an expansion groove 63 from the first hole 66 and the second hole An inner wall of at least one of the 65 extends a predetermined length for dividing a portion of the unitary link link into a first portion and a second portion that are relatively displaceable (eg, in Figures 13a, 13c, 14b, 14c, the first portion and the The two portions are generally the expansion groove 63 and the portion above the hole 65 and the expansion groove 63 and the portion below the hole 65), thereby facilitating the mounting of the shaft in the at least one of the first hole 66 and the second hole 65. A piece, such as a pin.

The integral track connecting link 60 is from the inner wall of the link shaft end 65 to the inner wall of the sleeve end 66 to 10 mm, or from the inner wall of the end of the link sleeve 66 to the end of the shaft 65. The expansion wall 63 is located at the end of the expansion groove. The end of the expansion groove is provided with a termination groove 64. The two ends of the expansion groove are processed to terminate the hole 76. The expansion groove can also extend from the inner wall of the link end to the end of the sleeve. The hole wall is opened;

The expansion tank and the termination groove may be straight lines, curved lines, or a parabola;

The expansion tank is connected to the center line of the two holes, and may also be on both sides of the center line;

The width of the expansion groove is equal to or wider than 0.12-5 mm;

A servo threaded hole 68 for expansion is assembled in the middle of each of the two fastening bolt holes 69 of each connecting link to mount the expansion servo bolt 62.

The integral track connecting link 60 is provided with two circular fastening nut fixing working grooves on the upper side of the expansion groove, and the end hole thereof is extended into the circular fastening nut fixing working groove.

The outer surface of the integral track connecting link pin shaft is processed by the optical axis center, and the oil nozzle is installed in the stepped hole of the oil filling port.

The existing method of installing the integral track connecting link pin shaft using the flame heating pin hole and the artificial sledge hammer striking pin is still adopted, and the result is easy to be cooled and cannot be disassembled, or the assembly is not in place. Therefore, the pin diameter is reduced and the two middle ends are thinned so as to smoothly enter the link pin hole, thereby weakening the interference fit which is easy to cause the connection loose pin to be thrown out, and then the pin is inserted through the end. There is a connection method in which the cross-holes are connected and then inserted into the split pin. This kind of dynamic fit structure is quickly increased due to the impact load, and the center distance between the links is changed, and the shaft, the sleeve and related components are accelerated to wear.

Set the servo threaded hole to install the expansion servo bolt to expand the expansion groove, and pull the pin hole to be larger than the pin diameter. The connection of the belt is simple, fast, safe and reliable, and opens up new ways of connection.

When machining the threaded hole of the servo, the width of the expansion groove of 0.12mm is not enough to overcome the taper angle of the front end of the drill bit, so that the threaded hole of the servo can not be processed into position. The groove can be removed 5mm before the end of the vertical threaded hole. The corresponding surface of the threaded hole is opened to eliminate a groove, and the non-equal width groove can be used to produce a permanent preload force on the pin shaft.

The integral track connecting link has a stop groove and a stop hole to prevent stress concentration: the expansion groove, the end groove, and the final hole can be processed according to different needs, different positions, or the like. In order to adapt to different working conditions and different models, the expansion tank and the termination tank can be straight or curved, or can be a parabola. Two circular fastening nut fixing working grooves are provided on the upper side of the expansion tank, and the end is extended to extend into the circular fastening nut fixing working groove.

For the convenience of the track connection, the thread 68 of the expansion servo bolt hole is the same as the thread of the solid bolt 61.

Referring to Figures 13 and 14, the integral link is connected differently from the split type. It uses the lateral assembly of the pin to connect the track links end to end.

The expansion servo bolt 62 is screwed into the integral connecting link 60 by the ordinary wrench, and the expansion servo bolt passes over the expansion groove 63 to contact the opposite surface under the action of the rotating torque, and continues to rotate the expansion groove. 63 starts to expand, and pulls the end groove 64 to the end hole to start elastic deformation, so that the slotted pin hole 65 is larger than the diameter of the pin shaft, and then the pin shaft is aligned with the link pin shaft hole 65 by hand. It can be loaded, and then the expansion bolt 62 is unscrewed. After the external force is released, the pin hole is tightly coupled with the pin shaft, and the moving track turns the integral connecting link 60 to the upper plane to position the track plate 67, and then tightens the solid bolt 61. Under the action of the bolt preloading force, the pin shaft and the pin hole are firmly matched and connected; when disassembling, it can be easily implemented in the reverse order of installation.

The on-site maintainability of the integral track connecting link is better than that of the split type. Different shapes of the expansion groove and the terminating groove can be used to connect the links, especially in the case of rare personnel and no maintenance conditions, the integral connecting link of the present invention can be used. In response to unexpected situations, the operator is free to choose and process on-site to achieve the purpose of the connection.

The integral connection link pin shaft hole 65 breaks the sealing condition of the link counterbore from the inner hole wall, resulting in the seal failure. The shaft and the sleeve cannot be lubricated with liquid; in order to improve the service life of the coupling pin, the center of the pin can be machined with a grease hole to install the grease nozzle to fill the grease, and the grease fitting is placed in the collision-free stepped hole. When the grease overflows through the nozzle and the oil passage from the opening intersecting the pin hole 65 and the inflation groove 63, the overflow grease seals the opening to prevent the intrusion of the contaminant, and good maintainability can be applied. Liquid lubricated track.

The liquid seal can be restored when the following technical solutions are employed.

Referring to Figures 16a and b, a groove 43 is provided along the circumferential surface of the pin inner hole 65 for mounting the O-ring 44, and a circular shape is formed on the expansion groove in the same direction as the expansion groove 63 at the bottom of the groove. The through hole 45 is provided with an excessive groove 46 which is smaller than the diameter of the circular through hole between the circular through hole and the circumferential surface of the pin inner hole 65.

Forcefully pull a round elastic rubber strip 151, and pass the excessive groove 46 into the circular through hole to release the external force. The rear round elastic rubber strip is restored to its original shape, and is tightly combined with the circular through hole 45. The 151-end of the round elastic rubber strip is in contact with the elastic rubber ring of the bottom sealing device of the chain sinking hole, and the other end side and the groove are 0. The outer side of the seal 44 is in contact to achieve a liquid seal.

The change and implementation of the connection mode of the integral connecting link, as long as the same type of track pin is made into a specification, any pin of the same type can be used as the connecting pin and the press pin, Mass production reduces the cost and convenience, and also enhances the convenience and reliability of the connection. It changes the long-term structure and connection of the integral link chain pin shaft, eliminates the hidden danger of the link center distance and eliminates the pin. The embodiment of the present invention has been shown and described with respect to the embodiment of the present invention, in which the outer diameter of the shaft shaft is thick and thin in the middle, and the outer surface is uniformly realized by the optical axis using the optical axis to achieve the outer diameter of the same type of track connecting pin. It is to be understood that the scope of the invention is defined by the appended claims and their equivalents.

Claims

Rights request

What is claimed is: 1. A sealing device for sealing between a first portion and a second portion of a track, wherein the second portion is rotatable relative to the first portion,

The sealing device comprises:

An annular spacer seal for spacing the first portion and the second portion and for sealing through respective end faces of the second portion;

An annular resilient member for biasing the spacer seal toward the second portion.

2. The sealing device of claim 1 wherein said first portion is secured to the shaft member and forms a generally annular space with the shaft member, said annular space having an opening toward the second portion, said The second portion is rotatable about a shaft member, the spacer seal being disposed in the annular space, mounted on the shaft member, and wherein the elastic member is disposed in the annular space.

The sealing device according to claim 1, wherein the spacer seal has an annular cut-away portion at an end of the outer periphery close to the first portion, and at least a portion of the elastic member is located at the cut-away portion.

4. The sealing device according to claim 1, wherein the annular spacer seal is made of metal.

.

The sealing device according to claim 1, wherein the end face of the second portion and the end face of the annular spacer seal are substantially flat surfaces.

The sealing device according to claim 3, wherein said end surface of said annular spacer seal has an annular seal band on the outer peripheral side for preventing leakage of lubricating oil.

The sealing device according to claim 6, wherein the end surface of the annular spacer seal has a plurality of lubrication grooves on the inner circumferential side.

The sealing device according to claim 7, wherein the plurality of lubrication grooves are of an axisymmetric structure and are evenly distributed in the circumferential direction.

9. A sealing device according to claim 8 wherein the inlet of the lubrication groove is in communication with the inner bore of the spacer seal.

28

Correction page (Article 91)

10. The sealing device according to claim 9, wherein the lubrication groove is linear, circular arc or spiral.

11. The sealing device according to claim 10, wherein the lubrication groove has a width of 1 to 5 mm and a depth of 0.2 to 2 mm.

The sealing device according to claim 11, wherein the end face of the annular spacer seal has oil-storing pores in addition to the sealing tape and the lubrication groove.

13. The sealing device of claim 1 wherein said end faces of said annular spacer seal form a sealing strip for preventing leakage of lubricating oil.

A sealing device according to claim 1, further comprising a dust seal disposed between the inner peripheral wall of the first portion and the outer peripheral surface of the annular spacer.

15. The sealing device of claim 3, the resilient member sealing between the inner wall of the first portion and the spacer seal.

16. A track comprising the sealing device of claim 1 for sealing between a first portion and a second portion of the track.

17. A sealing device for sealing between a first portion and a second portion of a track, wherein the second portion is rotatable relative to the first portion,

The sealing device comprises:

An annular spacer, the spacer for spacing the first portion and the second portion;

An annular elastic member disposed on an outer circumference of the annular spacer;

A combined seal ring axially overlapping the annular elastic member, the seal ring forming a seal with the end surface of the second portion.

18. The sealing device of claim 17, wherein the first portion is secured to the shaft member and forms a generally annular space with the shaft member, the annular space having an opening toward the second portion, The second portion is rotatable about a shaft member, the spacer member is disposed in the annular space, mounted on the shaft member, and wherein the elastic member and the seal ring are disposed in the annular space.

19. The sealing device according to claim 17, wherein the annular elastic member is an elastic rubber ring.

The sealing device according to claim 18, wherein said annular elastic member has at least an inner peripheral surface

29 Correction page (Article 91) An axial lubrication groove.

21. A sealing device according to claim 18, said annular resilient member comprising a first portion having a smaller radial extent and a second portion having a greater radial extent, whereby the annular resilient member has a cross section of 8 Glyph.

22. The sealing device of claim 21, wherein the sealing ring comprises:

Subject;

Provided in the body is a cavity adjacent one end of the annular elastic member, at least a first portion of the elastic member is fitted in the cavity.

23. The sealing device of claim 22, said combination seal further comprising - at least one annular sealing lip extending from said body toward said second portion for forming an end face with said second portion Sealed

An annular dust lip extending from an outer peripheral portion of the main body toward the second portion on an outer side of the radial direction of the at least one sealing lip, an inner circumferential surface of the dust lip and an end surface of the second portion The chamfered portion or the outer circumference of the rounded portion is in contact with each other, and the outer peripheral surface is in contact with the inner peripheral wall of the first portion.

24. The sealing device of claim 23, the combined sealing ring further comprising:

An annular groove disposed between the dust lip and the sealing lip.

25. The sealing device according to claim 24, wherein: the annular groove has a U-shaped or circular arc-shaped cross section.

26. The sealing device according to claim 25, wherein: the annular groove has a depth of 1 to 5 mm and a width of 0.5 to 3 mm.

27. The sealing device of claim 26, wherein: the combination seal further comprises: a slit extending from a bottom of the groove to the cavity.

28. A track comprising the sealing device of claim 17 for sealing between the first portion and the second portion of the track.

29. The crawler belt according to claims 1 and 28, further comprising - a shaft member having a cavity extending axially therein, the cavity having an opening portion at at least one end of the shaft member, The mouth part is sealed by a plug.

30

Correction page (Article 91) 30. The crawler of claim 29, wherein:

The plug is provided with a blind hole in a substantially central portion.

31. The crawler of claim 30, further comprising:

a stepped portion provided in the opening portion, the stepped portion having a diameter larger than a diameter of the cavity portion for mounting the plug.

32. A track comprising:

a track link having a hole for placing a track shoe fastening nut;

A track shoe that is fastened to the track link by bolts and track shoe fastening nuts, wherein the track shoe fastening nut has a generally cylindrical body.

33. The crawler of claim 32, wherein:

The axis of the threaded bore of the track shoe fastening nut is substantially perpendicular to the axis of the cylindrical body.

34. The crawler of claim 32, wherein:

The threaded hole is closed on the side opposite to one side of the bolt.

35. The crawler of claim 32, wherein:

The through hole has a cylindrical shape that substantially corresponds to the track shoe fastening nut.

The crawler belt according to claim 35, wherein said track shoe fastening nut has a plane substantially perpendicular to an axis of said threaded hole at at least one of both sides in the axial direction of the threaded hole.

37. A crawler belt comprising: a plurality of track links, each of the track links having a connecting section at its two ends for connecting with two adjacent links and an intermediate section between the connecting sections, The plurality of track links have a surface as a work surface, wherein the intermediate section has a cut-away portion on a side of the surface, through which the effective width of the working faces of the plurality of track links is longitudinal The direction remains roughly the same.

38. A crawler as claimed in claim 37, wherein said intermediate section comprises two sides extending in the longitudinal direction of said intermediate section and two ribs formed by the working face, said cut-away portions being in pairs of two ribs At least one of the chamfers.

31 Correction page (Article 91)

39. A crawler according to claim 37, wherein the cut-away portion is a recess on one side of the surface between the two sides extending in the longitudinal direction of the intermediate section.

40. The crawler of claim 39, wherein the recess is generally linear.

41. A split connecting link for a crawler belt, comprising:

a first portion, the first portion has a first main connecting surface and a first auxiliary connecting surface, and at least one first connecting tooth is respectively disposed on the first main connecting surface and the first auxiliary connecting surface, and

a second portion having a second main connecting surface and a second auxiliary connecting surface corresponding to the first portion, and at least one second connecting tooth is respectively disposed on the second main connecting surface and the second auxiliary connecting surface The second connecting tooth engages with a corresponding first connecting tooth.

42. The split link link for a track according to claim 41, wherein the first main connecting surface and the first auxiliary connecting surface and the second main connecting surface and the second auxiliary connecting surface generally constitute the first portion and the second portion Part of the interface.

43. The split link link for a track of claim 42, wherein the first primary connection surface and the second primary connection surface are generally planar.

44. The split link link for a crawler belt according to claim 43, wherein said first main connecting surface and said second main connecting surface are opposite to two connecting connecting links for connecting the split links. The angle of the connection plane of the center line of the hole is a, where 0° a 29°.

45. The split connecting link for a track according to claim 44, wherein said first auxiliary connecting surface and said second auxiliary connecting surface are opposite to two connecting connecting links for connecting the links. The angle of the connection plane of the center line of the hole is 0°.

46. The split link link for a track according to claim 43, wherein said first auxiliary connecting surface and said first main connecting surface are in the center of two pin holes connecting the split connecting links The projections on the connection plane of the lines partially overlap, and the second auxiliary connection surface and the second main connection surface are on a connection plane connecting the centerlines of the two holes of the split connection links for connecting the links The projections partially overlap, thereby increasing the total length of the joining surface.

32

Correction page (Article 91)

47. The split link link for a track according to claim 43, wherein one of said first and second portions connected to the track shoe includes a pre-joining hole, and said first portion and said second portion The other of the two includes a corresponding threaded hole, thereby joining the first portion and the second portion together by screws prior to mounting the track shoe.

48. An integral connecting link for a crawler belt, comprising:

a first hole and a second hole for connecting the links;

An expansion groove extending from the inner wall of at least one of the first hole and the second hole by a predetermined length for dividing a portion of the integral connecting link into the first portion and the second portion that are relatively displaceable, This facilitates mounting the shaft member in the at least one of the first and second holes.

49. The integral connecting link for a track according to claim 48, wherein said first portion includes a through hole and said second portion includes a threaded hole coaxial with said through hole, by inserting a bolt a through hole of the first portion and screwed into the threaded hole of the second portion to bring the first portion and the second portion close, and to reduce the diameter of the at least one of the first hole and the second hole, the shaft A member is fixed in the at least one of the first hole and the second hole.

50. The integrally coupled link for a track according to claim 48, wherein said first portion includes a threaded bore, the two portions being separated by screwing a bolt into the threaded bore of the first portion and pushing the second portion, Enlarging the diameter of the at least one of the first and second holes to facilitate insertion of the shaft into the at least one of the first and second holes, thereby After the screw is removed, the shaft is fixed in the at least one of the first hole and the second hole.

51. An integral connecting link for a track according to claim 50, wherein the first portion and the second portion are secured together by bolts after the screw is removed.

52. The integral connecting link for a track according to claim 48, further comprising: a bolt through hole for fixing the track shoe, wherein the expansion groove terminates in the through hole.

The integral connecting link for a crawler belt according to claim 48, further comprising: a terminating hole, the expansion groove terminating in the terminating hole for preventing stress concentration.

54. An integral connecting link for a track according to claim 48, wherein said expansion slot communicates said first aperture and said second aperture.

Correction page (Article 91)

55. The integral link link for a track of claim 48, further comprising two slots branching from an end of the expansion slot.

An integral connecting link for a crawler belt according to claim 48, wherein said expansion groove has a linear shape, a curved shape, or a combination of a linear shape and a curved shape.

57. The integral connecting link for a track according to claim 48, wherein said expansion groove has a width of between 0.12 and 5 mm.

58. The integral connecting link for a track according to claim 48, further comprising a seal assembly for preventing a hole in the first and second holes from which the lubricating oil is contained Lubricating oil leaks to the outside through the expansion tank.

59. A method of encapsulating an oil hole for a track lubrication system, the system comprising a cavity formed in a pin of a track for connecting a link and extending axially thereof, the cavity being at the pin At least one end of the shaft has an oil hole, and the method includes:

After filling the system through the oil hole, a plug for closing the oil hole is provided;

Insert the tube into the plug along the direction in which the plug is inserted into the oil hole;

Pressing the plug into the oil hole while discharging the gas in the system and the excess oil through the pipe;

The tube is withdrawn from the plug, wherein the plug is resilient so that the plug can close the through hole pierced by the tube after the tube is withdrawn from the plug.

A method of encapsulating an oil hole for a track lubrication system according to claim 59, wherein said plug is a rubber stopper.

A method of encapsulating an oil hole for a crawler lubrication system according to claim 59, wherein said plug has a blind hole in a direction in which the plug is inserted into the oil hole, and the blind hole is in the direction of the plug At least one side of the side to facilitate the pipe piercing the plug.

62. A method of encapsulating an oil fill hole for a track lubrication system according to claim 59, wherein said tube has a sharp end to facilitate passage of the tube through the plug.

34

Correction page (Article 91)