WO2015178524A1

WO2015178524A1 - Multi terrain loader undercarriage

Info

Publication number: WO2015178524A1
Application number: PCT/KR2014/004665
Authority: WO
Inventors: 조철현; 남윤태
Original assignee: 동일고무벨트 주식회사
Priority date: 2014-05-22
Filing date: 2014-05-26
Publication date: 2015-11-26

Abstract

The purpose of the present invention is to provide a multi terrain loader undercarriage capable of efficiently transmitting power and preventing the rubber track from being damaged by stress concentration. The undercarriage according to the present invention comprises: a rubber track (40) having driving lugs (42) continuously formed on the inner surface thereof at a predetermined interval; and a driving sprocket (20), which is rotated by a driving force from the engine, which has a plurality of roll sleeves (22) that engage between the driving lugs, and which is installed on the rear end of the interior of the rubber track. In addition, an idler (52) is installed on the front end of the interior of the rubber track, and multiple track rollers (54) are installed between the driving sprocket and the idler. The rubber track contacts the ground between parts of contact with the idler and the driving sprocket, and the driving sprocket contacts the rubber track before the rubber track is spaced from the bottom surface. The driving sprocket is formed to have a diameter larger than those of the idler and the track rollers, and the driving sprocket is spaced from the rubber track at the upper end corresponding to a part at which the rubber track starts to make a contact. It is also possible to always maintain the tension of rubber track in an optimum state using first and second tension adjusting means.

Description

Undercarriage for multi-load loader

The present invention relates to an undercarriage of a multi-load loader, and more particularly, to an undercarriage of a multi-load loader configured to minimize damage to the rubber track, such as efficient power transmission by appropriately adjusting the tension of the rubber track. It is about.

Various types of driving devices that use tracks have been developed and utilized, for example, military equipment such as tanks, heavy equipment such as bulldozers and excavators, and devices such as snowmobiles and multi terrain loaders. Is designed to travel using various types of tracks.

The track driving device has various types of tracks. For example, in the case of heavy equipment, a metal track is used, and in the case of light equipment, a track made of an elastic material such as rubber is generally used. Here, the multi-load loader has the advantage of being able to work on soft ground such as wetlands and farmland by lowering the ground pressure of the equipment itself, and using a rubber track as a power transmission means for the ground.

1 and 2 show the undercarriage of a typical multi-load loader. The undercarriage in the loader can be said to be a part which drives the loader itself based on the driving force in the engine. As shown in the figure, the undercarriage of the multi-load loader includes a rubber track 10 that travels with respect to the ground, and a drive sprocket 4 that enables driving by transmitting power to the rubber track 10. It is included.

The rubber track 10 is made of rubber as a main component and has a constant elasticity. In addition, a plurality of drive lugs 12 are arranged in a row on the inner surface of the rubber track 10 to receive power from the drive sprocket 4. In addition, a tread is formed on the outer surface of the rubber track 10 so as to travel efficiently when it comes in contact with the ground.

In addition, the driving sprocket 4 is installed on the inner side of the rubber track 10 to apply a rotational force to the rubber track 10. The drive sprocket 4 is provided with a plurality of roll sleeves 4a engaged between the drive lugs 12 on the entire outer circumferential surface thereof. Since the configuration of the drive sprocket 4 itself is substantially known, a detailed description thereof will be omitted. The roll sleeve 4a is rotatably installed with respect to the support provided therein so as to generate rolling motion when the rubber track 10 comes into contact with the inside of the rubber track 10, that is, the driving lug 12.

The drive sprocket 4 has a force in the engine is transmitted through a hydraulic pump is rotated by a built-in hydraulic motor, the rotational force of the drive sprocket 4 through the above-mentioned roll sleeve (4a) rubber track ( 10) to be delivered. Therefore, the transmission of the force for rotating the rubber track 10, the roll sleeve 4a of the drive sprocket 4 is transmitted to the drive lug 12 of the rubber track 10, whereby the love track 10 This rotation allows the loader to travel.

The undercarriage of the loader includes an idler 6 provided at the front end of the rubber track 10 and a plurality of track rollers 8 provided on the inner side to maintain the shape of the rubber track 10. Doing. The idler 6 and the track roller 8 are generally arranged in a horizontal direction along the ground to support the rubber track 10 so as to maintain a predetermined shape. The idler 6 and the track roller 8 are rotatably supported by the main frame F.

In such a conventional configuration, the most important influence on the running performance of the multi-sized loader can be called power transmission. In other words, it is a matter of course that the driving performance of the loader is secured only when the transmission of the force is efficiently performed between the driving sprocket 4 and the rubber track 10 that rotate by the force in the engine. Looking at the conventional structure in this respect, as can be seen with reference to Figure 1, the roll sleeve 4a of the drive sprocket 4 is engaged with each other in the drive lug 12 of the rubber track 10 and only three or four parts. It can be seen that. The transfer of force from the drive sprocket 4 to the rubber track 10 takes place between the roll sleeve 4a which is engaged with each other and the drive lug 12 of the rubber track 10, such a small number of roll sleeves 4a. ) And the driving lug 12 is coupled to the power transmission is made in the stress concentration phenomenon that the stress is concentrated in a portion of the driving lug 12 is bound to occur.

As such, when the stress concentration phenomenon occurs, it is natural that the rubber track 10 portion where the driving lug 12 in which the stress is concentrated is located may be damaged. For example, the driving lug 12 may be damaged. Damage to the track, such as falling from the rubber track 10, will occur. Since the driving sprocket 4 is located on the upper side of the rubber track, the rubber track 10 is jumped due to the force force of the roll sleeve 4a pushing the driving lug 12. In addition, due to such a jumping phenomenon, power is not efficiently transmitted and stress concentration may occur as a part of the driving lug, thereby causing damage to the rubber track.

In addition, although the plurality of track rollers 8 are used to maintain the shape of the rubber track 10 as described above, in general, the track rollers 8 are located at the rearmost positions because the track rollers are relatively small in size. The rubber track will form an acute angle. As described above, the formation of the acute angle of the track roller 3 means a radical change of the path, and it can be said that the concentration of the stress and the damage of the track roller due to this are also concerned.

In addition, according to the related art, as shown, the driving sprocket may point out a problem for more efficient power transmission because the portion in contact with the rubber track in order to transmit power to the rubber track is a part floating on the ground rather than the ground. . That is, considering that the rubber track has a certain elasticity, it can be obvious that the efficiency of the rubber track is lowered as compared with the transmission of power to the rubber track while the driving sprocket is on the ground.

Moreover, according to the prior art, the rubber track made of rubber material by long-term use has no choice but to be elongated, and there is no countermeasure against elongation of the rubber track. Therefore, it can be seen that the above-described prior art has a disadvantage in that the efficiency of power transmission due to the rubber track in the extended state is substantially reduced due to long-term use.

The present invention has been made in view of such a conventional problem, and a main object of the present invention is to provide an undercarriage for a multi-load loader in which power transmission from a drive sprocket to a rubber track is most efficiently performed.

Another object of the present invention is to provide an undercarriage for a multi-load loader which is configured to suppress the damage of the rubber track as much as possible by repeated fatigue load even in long term use.

Still another object of the present invention is to provide an undercarriage for a multi-load loader configured to sufficiently increase power efficiency even when the rubber track is extended by long-term use.

The undercarriage of the multi-load loader of the present invention for achieving the above object is a frame for supporting the engine that is the drive source of the multi-load loader; A rubber track in which a driving lug having a predetermined interval is formed on an inner side thereof; A driving sprocket rotated by a driving force of an engine, coupled to the driving lug to transmit rotational power to a rubber track, and installed at an inner rear end of the rubber track and rotatably supported by the frame; An idler installed at the front end of the rubber track and supported by the frame; A plurality of track rollers installed between the driving sprocket and the idler and rotatably supported by the frame; And it comprises a tension adjusting means for adjusting the tension of the rubber tracks; The rubber track is in contact with the ground between the portion in contact with the idler and the driving sprocket, and the driving sprocket is in contact with the rubber track before the rubber track is spaced apart from the bottom.

According to the embodiment of the present invention, the driving sprocket is spaced apart from the rubber track at a point above the center point.

According to another embodiment of the invention, the rubber track is designed to have the highest position at the upper end of the drive sprocket.

According to another embodiment of the present invention, the drive sprocket is configured to be spaced apart from the rubber track at an upper end corresponding to the contact start of the rubber track.

According to an embodiment of the driving sprocket, the driving sprocket includes a plurality of protrusions formed on an outer circumferential surface thereof to be engaged with the driving lug to transmit rotational power.

According to another embodiment of the drive sprocket, it comprises a pair of ring members spaced apart at regular intervals, and a roll sleeve is installed between the ring member, the roll sleeve is coupled between the drive lug to transfer power It is configured to be possible. In this case, the roll sleeve is preferably rotatably supported between the ring members.

According to an embodiment of the tension adjusting means of the present invention, the first tension adjusting means for adjusting the rubber tracks by pushing the rubber tracks to the outside, and extending the front and rear length of the frame to adjust the tension of the rubber tracks It consists of two tension control means.

In addition, the frame of the present invention is composed of a main frame rotatably supported by the drive sprocket and a plurality of track rollers, and an idler frame installed in front of the main frame to rotatably support the idler. The first tension adjusting means includes an upper roller contacting an inner surface of a rubber track positioned at an upper side between an idler and a driving sprocket, and a first arm and a second arm supporting the upper roller on a main frame. One of the first arm and the second arm is configured to be adjustable in length to adjust the tension of the rubber track.

And the second tension adjusting means of the present invention, the idler frame is composed of a linear movement means capable of adjusting the relative position forward and backward with respect to the main frame. According to an embodiment of the linear movement means, having a nut block connected to the idler frame, a front portion screwed to the nut block and a rear portion extending rearward from the front portion and not rotatable to the main frame It comprises a screw member. Here, by the rotation of the screw member, the idler frame, which is supported by the idler, can be linearly moved forward and backward, thereby adjusting the tension of the rubber track.

The second tension adjusting means is fixed to the middle portion of the screw member and extends radially so that the screw member contacts the front surface of the stop plate which is installed in the main frame and has a through hole through which the screw member passes. A stopper for regulating movement; The main frame may be installed on the rear side of the stop plate, the neck portion of the screw member is inserted may further comprise a support plate for restricting the movement of the screw member forward.

According to another embodiment of the present invention, the front end portion of the main frame is formed to accommodate the idler frame from the front, the both sides of the front end of the slot to accommodate the idler support portions protruding from both sides of the idler frame to support the idler It is molded backward.

According to the present invention having the above-described configuration, the number of roll sleeves of the driving sprockets and the driving lugs of the rubber tracks engaged with each other is sufficiently large as compared with the conventional structure. That is, since the driving sprocket and the rubber track are in contact with each other in a sufficiently large area, it is possible to prevent stress concentration in the process of transferring power from the driving sprocket to the rubber track, thereby enabling stable power transmission. Therefore, it is possible not only to allow stable running of the multi-load loader, but also to prevent partial damage of the driving lug caused by stress concentration.

In addition, since the rubber track is supported by the ground at the time when the driving sprocket starts contacting the rubber track, stress concentration of the corresponding part can be prevented as much as possible when power is transferred to the rubber track.

And according to the present invention, it can be seen that it becomes possible to adjust the tension of the rubber track more smoothly. That is, the first tension adjusting means adjusts the rubber track tension by pushing upward the rubber track located above the idler and the driving sprocket. The second tension adjusting means adjusts the tension of the rubber track by moving the idler frame forward and backward with respect to the main frame.

By using the first tension adjusting means and the second tension adjusting means, the rubber track can always maintain the optimum tension state, and can be expected to use the same to facilitate the replacement of the rubber track. have.

1 is a front view of a conventional undercarriage.

Figure 2 is an exploded perspective view illustrating a conventional undercarriage.

3 is a perspective view of the undercarriage according to the present invention.

4 is an exploded perspective view illustrating an undercarriage according to the present invention.

5 is a front view of the undercarriage according to the present invention.

6 is a longitudinal sectional view of the undercarriage according to the present invention.

Figure 7 is an illustration of the second tension adjusting means of the present invention.

Figure 8 shows the state of the second tension control means of the present invention, (a) is an exemplary view showing a state before the tension adjustment, and (b) a state after the tension adjustment.

Next, the present invention will be described in more detail with reference to the embodiments shown in the drawings.

As can be seen with reference to Figures 3 to 6 showing the undercarriage of the multi-load loader of the present invention, the undercarriage according to the present invention is a drive sprocket 20 that rotates by the driving force in the engine, and It is comprised including the rubber track 40 which rotates by the drive sprocket 20. As shown in FIG.

The rubber track 40 is made of rubber as a main component and has a constant elasticity. If necessary, a plastic cord may be inserted into the rubber track 40. As such, when the plastic cord is embedded in the rubber track 40, the weight of the plastic cord is reduced compared to that of inserting the steel cord. Therefore, when the ground pressure is considered, the driving performance is sufficiently secured even in the softer ground. It is easy to apply to.

In addition, the rubber track 40 incorporating the plastic cord has an advantage of preventing the rubber track 40 from being broken due to overload, compared to the rubber track having the steel cord due to the elasticity of the plastic itself. It can be said to have. However, the rubber track 40 having a plastic cord has a disadvantage of being stretched due to repeated fatigue loads, etc. In the present invention, the rubber track 40 is configured to ensure sufficient power transmission efficiency even when the rubber track 40 is extended. This will be described later.

On the inner side of the rubber track 40, a plurality of drive lugs 42 for receiving power from the drive sprocket 20 are continuously arranged in a row. And the outer surface of the rubber track 10 is formed with a tread (tread) for running when in contact with the ground to enable efficient grounding with the ground.

And the drive sprocket 20 is rotated by the power transmitted from the engine, and transmits this rotational force to the rubber track (40). That is, the driving sprocket 20 transmits rotational power to the rubber track 40 by using the driving lug 42 formed on the inner surface of the rubber track 40.

The driving sprocket 20 may transmit the rotational power to the rubber track 40 using the driving lug 42 may have various structures of the driving sprocket 20. For example, as the basic shape of the drive sprocket 20, it is also possible to comprise so that a plurality of continuous protrusions may be provided on the outer circumferential surface that engages the drive lug 42 of the rubber track 40 described above. That is, when the protrusion is formed on the outer circumferential surface of the driving sprocket 20, the protrusion enters and engages between the driving lugs 42, and transfers power from the driving sprocket 20 to the rubber track 40 in such a coupled state. This will be possible. Such a projection may be said to perform a function substantially similar to the teeth in the sprocket driving the chain.

As another embodiment of the drive sprocket 20, the drive sprocket 20 may be provided with a plurality of roll sleeves 22 engaged between the drive lugs 42. For example, as illustrated in FIGS. 3 and 4, a plurality of roll sleeves 22 arranged in a circle between a pair of

ring members

24 and 26 forming both sides of the driving sprocket 20 may be provided. have. The roll sleeve 22 is coupled between the plurality of continuous drive lugs 42 to perform the function of transmitting power to the drive lugs 42, in the above-described embodiment is coupled between the drive lugs 42 It is to perform a function corresponding to the engaging projection.

The roll sleeve 22 is supported between the pair of

ring members

24 and 26. The roll sleeve 22 may be engaged with the driving lug 42 to transmit the rotation of the driving sprocket 20 to the rubber track 40. The roll sleeve 22 is also preferably configured to be rotatable between a pair of ring members (24, 26). That is, by configuring the roll sleeve 22 to be rotatable, the rubber track 40 can be brought into contact with the rubber track 40 in contact with the roll sleeve 22 as opposed to the sliding track as described below. It will be more advantageous to the wear protection of the.

The drive sprocket 20 described above is rotated by a hydraulic motor 28 which is rotationally driven by a hydraulic pump (not shown) operated by an engine. In the illustrated embodiment, it can be seen that the drive sprocket 20 is installed inside the rear end of the rubber track 40. In this case, the rear stage is based on the traveling direction of the multi-load loader and means rearward from the traveling direction.

The idler 52 is rotatably provided on the opposite side of the drive sprocket 20, that is, inside the front end of the rubber track 40. According to the present invention, it can be seen that the idler 52 and the driving sprocket 20 are respectively installed in the front and rear ends of the rubber track 40. The drive sprocket 20 and the idler 52 have a relatively larger diameter than the plurality of track rollers 54, in particular the drive sprocket 20 has a larger diameter than the idler 52 and the track roller 54. It can be seen that. By arranging the driving sprocket 20 having a large diameter in the rear end as described above, the number of the driving sprockets 20 engaged with the driving sprocket 20 can be sufficiently increased.

In the illustrated embodiment, it can be seen that the drive sprocket 20 is disposed at the rear end and the idler 52 is disposed at the front end. As such, disposing the driving sprocket 20 at the rear end may be more advantageous in terms of power transmission in the multi-load loader that must travel in various terrains. That is, the multi-load loader performs a work along a substantially inclined ground. In this case, when driving or performing a work along an inclined ground, it is preferable to arrange the driving sprocket 20 at the rear end of the rubber track 40. Naturally, it is effective in terms of power transmission.

A plurality of track rollers 54 are provided between the drive sprocket 20 and the idler 52. The track roller 54 may be installed to maintain a predetermined shape of the rubber track 54. The drive sprocket 20 and the plurality of track rollers 54 are rotatably supported by the main frame 30. The mechanism for supporting the idler 52 will be described later.

In this specification, the mainframe 30 is substantially other components of the multi-load loader except for the undercarriage, for example, an engine for generating power, a power converter for converting power in the engine, and It can be said that it is a general support member for supporting various parts for driving the terrain loader.

The undercarriage of the present invention further includes an upper roller 32. The upper roller 32 is in contact with the inner side of the rubber track 40 to adjust the tension, and prevents the vibration generated by the rubber track 40 in the upper portion between the drive sprocket 20 and the idler 52 and , Like the idler is installed to maintain a fixed track of the rubber track 40. That is, the upper roller 32 is installed to adjust the tension of the rubber track 40 itself by pushing the rubber track 40 upward, where the upper portion is the portion where the rubber track substantially contacts the ground. It can be seen that the floating part is not in the air.

The upper roller 32 is supported by the main frame 30 by the first arm 34 and the second arm 36. The lower end of the first arm 34 is connected to the main frame 30 in front of the upper roller 32, and the lower end of the second arm 36 is connected to the main frame 30 from the rear of the upper roller 32. Connected. And for example, at least one side of the first arm 34 and the second arm 36 is configured to adjust the length, by contacting the inside of the rubber track 40 by adjusting the length of the rubber track 40 It is possible to adjust the tension. As in the illustrated embodiment, the tension of the rubber track 40 may be adjusted by using the first arm 34 as an arm having a length adjustable in a turn buckle manner.

Since the rubber track 40 of the present invention is made of a rubber material and has a plastic cord embedded therein, the rubber track 40 is extended by long-term use as described above. And it can be seen that the upper roller 32 and the length-adjustable first arm 34 has a function of maintaining the same tension with respect to the rubber track 40, which is substantially extended. That is, by adjusting the length of the first arm 34 of the turnbuckle system, the tension of the rubber track 40 can be adjusted to cope with the change in the length thereof.

Here, another embodiment for supporting the upper roller 32 on the main frame 30 may include a hydraulic cylinder. That is, the hydraulic cylinder is installed between the upper roller 2 and the main frame 30, and the upper roller 32 is moved upward by the driving of the inflow cylinder, so that the tension of the rubber track 40 can be adjusted. It also means that it is possible.

Undercarriage according to the present invention, in addition to the first tension adjusting means including the second arm 34 and the upper roller 32 is adjustable in length, the second tension that can adjust the tension of the rubber track 40 It further comprises an adjustment means. And the first tension adjusting means is to push up the rubber track 40 in the upper portion between the driving sprocket 20 and the idler 52, the second tension adjusting means is the driving sprocket 20 and the idler It can be implemented by adjusting the interval between 52.

Next, referring to Figures 4, 6 and 7, will be described with respect to the second tension adjusting means of the present invention. First, as shown in FIG. 7, the frame of the present invention includes the idler frame 60 with respect to the main frame 30 described above. And since the idler frame 60 is configured to be stretchable forward with respect to the main frame 30, it is possible to adjust the front and rear length of the overall frame. Being able to adjust the overall length of the frame, means that the tension of the rubber track 40 lengthened by the long-term use can be adjusted.

The idler frame 60 and the main frame 30 are connected to each other by a screw member 80 having a threaded portion formed on an outer surface thereof. The idler frame 60 is a nut block 64 screwed to the front portion 82 of the screw member 80, and protrudes from both sides of the nut block 64 is rotatably supported by the idler 52 The idler support part 62 is included.

In addition, the screw member 80, the front portion 82 is a screw threaded on the outer surface and the rear portion 84 extending rearward to the front portion 82, and between them fixed by welding or the like radially An extended stopper 86 is included. And the rear end of the rear portion 85 is provided with a hexagonal head, for example, as a user-operable operation unit 88, the diameter between the hexagonal head operation unit 88 and the rear portion 84 is reduced Neck portion 85 is provided. The outer periphery of the front portion 82 is screwed, so that the nut block 64 is moved back and forth by the rotation.

Referring to FIGS. 3 and 4 again, the main frame 30 may have a constant width in the left and right direction and may have a substantially rectangular cross section, and the front end portion 30A may be described above. Opening is formed toward the front to enter the idler frame 60. On both sides of the front end portion 30A, a slot 38 is formed which is open toward the front and has a constant length to the rear. The upper and lower widths of the slot 38 may be enough to accommodate the idler support 62.

7 and 8, when the idler frame 60 is inserted into the front end portion 30A of the main frame 30, the idler support portion 62 opens the slot 38. It is in a state protruding to the outside through. The idler support part 62 supports the idler 52 in a state where the nut block 64 protrudes outward through the slot 38 in a state where the nut block 64 is inserted into the main frame 30. External force applied to) may be received and supported by the main frame 30.

In the state where the idler frame 60 enters from the front end of the main frame 30, the rear portion 84 of the screw member 80, in which the front portion 82 is screwed to the nut block 64, is the main portion. Passed through the through hole (30b) of the stop plate (30B) is installed in the longitudinal direction in the inner middle portion of the frame 30 is coupled to the rear. And the support plate 30C is shape | molded in the main frame 30 of the position corresponding to the back of the said stop plate 30B. The support plate 30C has a support groove 30c formed coaxially with the through hole 30b.

The support groove 30c is formed into a groove shape having an opening downward, for example, an inverted U-shaped groove, and the left and right width thereof are smaller than the diameter of the screw member 80, and can accommodate the neck portion 85. It has a size that is. Therefore, when the screw member 80 is coupled to the main frame 30, the rear portion 84 passes through the through hole 30b, and the stopper 86 contacts the front surface of the stop plate 30B. In this state, the neck portion 85 is in the support groove 30c. That is, the stopper 86 comes into contact with the stop plate 30B, and the idler frame 30 and the screw member 80 may further restrict the rearward movement.

And this state is shown in Figure 8 (a), this state can be said that the idler frame 60 is not extended forward with respect to the main frame 30, the idler frame 60 This is no longer able to move backwards. In this state, the idler frame 60 may be extended forward by manipulation of the screw member 80 so that the overall length of the frame may be adjusted. In the state shown in FIG. 8A, the idler support part 62 of the idler frame 60 is supported in the slot 38.

In this state, when the rubber track 40 is extended by using for a long time, it is possible to adjust the tension of the rubber track 40 by using the second tension adjusting means in addition to the first tension adjusting means. In other words, the user rotates the screw member 80 in one direction by rotating the operation unit 88 constituted of the hexagonal head in one direction (the direction in which the idler frame is extended) by using a tool such as a hexagon wrench.

Here, the screw member 80 itself cannot move in the front-back direction because the neck portion 85 is confined to the support groove 30c, but the screw member 80 rotates at the position by the rotation of the operation unit 88. Will be done. In addition, the nut block 64 screwed to the front portion 82 of the screw member 80 and the bracket 65 connected to the nut block 64 are connected to the idler 52 and the like. It cannot be rotated.

Therefore, by the rotation of the screw member 80, the idler frame 60 including the nut block 64 is bound to move forward. Therefore, the idler frame 60 is shown to move forward with respect to the main frame 30, this state is shown in Figure 8 (b). By the forward movement of the idler frame 60, it is natural that the tension of the stretched rubber track 40 can be adjusted. As shown in FIG. 8B, the idler support 62 of the idler frame 60 is supported in the slot 38 even in this state.

In the above-described embodiment, it can be seen that the second tension adjusting means is configured to be able to extend the idler frame 60 and the main frame 30 in the front-rear direction. As described above, the second tension adjusting means may be modified in various ways within the range configured to extend or contract the idler frame 60 and the main frame 30 in the extended state.

For example, by mounting a hydraulic cylinder between the idler frame 60 and the main frame 30, the idler frame 60 and the main frame 30 in accordance with the forward and backward movement of the piston of the hydraulic cylinder by the operation of such a hydraulic cylinder. It may be possible to adjust the spacing between Here, adjusting the distance between the idler frame 60 and the main frame 30 substantially adjusts the tension of the rubber track 20 by adjusting the distance between the idler 52 and the driving sprocket 20. Naturally, it has the same meaning as the above.

Next, the driving of the undercarriage according to the present invention having the above configuration will be described. In the present invention, it can be seen that the drive sprocket 20 is installed at the rearmost end of the rubber track 40. According to the present invention, it can be seen that the portion of the rubber track 40 in contact with the ground is a section between the idler 52 and the driving sprocket 20. That is, it can be seen that the rubber track 40 travels while contacting the ground in the section between the idler 52, the plurality of track rollers 54, and the driving sprocket 20.

That is, the rubber track 40 is brought into contact with the ground between the parts in contact with the idler 52 and the driving sprocket 20, which is substantially a time when the driving sprocket 20 is in contact with the rubber track 40. At this point, it means that the rubber track 40 is in contact with the ground. And when the rubber track 40 rotates by the rotation of the drive sprocket 20, the portion where the drive sprocket 20 and the rubber track 40 start to contact for the first time is substantially perpendicular to the center point of the drive sprocket 20. It will be the bottom part. And this point is the portion corresponding to the rubber track 40 is substantially spaced apart from the ground.

This means, according to the present invention, that at least the rubber track 40 is in contact with the drive sprocket 20 before being spaced apart from the ground. Here, the driving sprocket 20 in contact with the rubber track 40 means that the roll sleeve 22 of the driving sprocket 20 enters and contacts between the driving lugs 42 of the rubber track 40. have. In addition, the illustrated embodiment of the driving sprocket 20 and the rubber track 40 are separated from each other by the driving sprocket 20 and the rubber track 40.

Therefore, in the illustrated embodiment, as can be clearly seen in FIGS. 5 and 6, it can be seen that the drive sprocket 20 is in contact with the rubber track 40 at a portion corresponding to half the diameter. That is, according to the present invention, it can be said that about half of the roll sleeves 22 of the drive sprocket 20 are in contact with each other by being sandwiched between the drive lugs 42 of the rubber tracks 40. The contact between the drive sprocket 20 and the rubber track 40 in such a large area, or the engagement of the roll sleeves 22 in half of the number between the drive lugs 42 as a whole, is a stable power. It can be said that delivery is taking place.

As described above, the driving sprocket 20 is installed at the inner rear end of the rubber track 40, and as described above, the contact start and the power transmission with the rubber track 40 have substantial significance. can do. That is, when driving the forward direction of the multi-load loader, the driving sprocket 20 is capable of transmitting sufficient power to the rubber track 40 before being spaced apart from the ground.

For example, as shown in FIG. 1, when power is transmitted from a drive sprocket in a state in which the rubber track is spaced from the ground, the love track is in the air, and thus, there is no limit in efficient power transmission because there is not enough reaction force. none. However, according to the present invention, since the driving sprocket 20 transmits power before the rubber track 40 is spaced apart from the ground, it is possible to transmit power to the rubber track most efficiently without slippage or slippage of the rubber track.

Furthermore, when the drive sprocket 40 transmits power to the rubber track 20, the largest power transfer point may actually be the part where the first drive sprocket 40 contacts the rubber track 20, in the present invention. By setting the initial contact portion before the rubber track 40 is separated from the ground, it can be said that the efficiency of power transmission is secured to the maximum.

In particular, the multi-sized loader travels along the inclined ground, but the transmission of power is not very important in the downward slope, but the transmission of power is very important in the upward slope. In addition, when the multi-load loader performs a task, it is natural that much of the forward operation and the task are performed at the same time. Considering the operation of the multi-load loader and the driving of the inclined ground, the design of the drive sprocket of the present invention as described above and the contact and separation with the love track can realize a significant improvement in power transmission. You will know.

In addition, the present invention has a significant meaning in terms of the number of contacts between the roll sleeve 22 of the drive sprocket 20 and the lugs 42 of the love track 40 for power transmission. That is, in the past, three or four roll sleeves of the drive sprocket were engaged with the drive lugs, but according to the present invention, the roll sleeve 22 corresponding to half of the drive sprockets was engaged with the drive lugs 42, thereby transmitting power. .

Therefore, according to the present invention, it can be seen that the force of the sprocket 20 is transmitted to the lug track 20 by the roll sleeve corresponding to half of the drive sprocket 20 and the corresponding number of drive lugs 42. have. And this fact is that the contact of the drive sprocket 20 and the rubber track 40 is started in the part corresponding to the lower part of the center of the drive sprocket 20, and corresponds to the upper part of the center of the drive sprocket 20. This means that the drive sprocket 20 and the rubber track 40 are separated from each other.

In this configuration, the drive sprocket 20 is formed to have the largest diameter among the rotating bodies rotating inside the rubber track, and the rubber track 40 is maintained at the highest position at the upper end of the drive sprocket 20. It is done by making it possible. In the illustrated embodiment, it can be seen that the upper roller 32 is disposed at a height substantially similar to or lower than the upper end of the rubber track 40.

Therefore, it is possible to prevent the stress concentration to occur as much as possible during the power transmission from the sprocket 20 to the rubber track 40, as well as a more secure power transmission will be possible. In addition, such a relatively large number of roll sleeves 22 and the driving lugs 42 may be sufficiently prevented from damaging the driving lugs 42 due to stress concentration.

As such, the rubber track 40 comes into contact with the driving sprocket 20 in a wide area (approximately half of the driving sprocket), whereby the rubber track 20 is bent rapidly, for example, as in the prior art. It will be possible to prevent the rubber track from forming an acute angle before and after the track roller. As shown in the illustrated embodiment, the contact with the rubber track 40 over about half of the drive sprocket 20 indicates that stable power transmission is possible and damage to the rubber track due to stress concentration can be suppressed as much as possible. Can be.

In the illustrated embodiment, it will be appreciated that the jumping phenomenon of the rubber track 40 may not occur at the portion where the rubber track 40 and the driving sprocket 20 contact each other. That is, the jumping phenomenon may occur generally at the upper end of the rubber track 40, for example, at the upper part between both end portions of the rubber track 40. However, according to the present invention, since the drive sprocket 20 is installed at the rear end of the rubber track 40 and has a larger diameter than the idler 52 inside, the rubber track is located at the portion where the drive sprocket 20 is located. It is expected that the jumping phenomenon of 40 can be sufficiently prevented.

In the illustrated embodiment, it can be seen that the lower end of the driving sprocket 20 starts to contact the rubber track 40 and is spaced apart from the rubber track 40 at the upper end. In the present invention, it can be seen that the drive sprocket 20 and the rubber track 40 are configured to transmit power in a wide area. 5 and 6, it may be said that it is most preferable to contact the rubber track 40 at a circumferential surface corresponding to half of the driving sprocket 20.

That is, the portion where the driving sprocket 20 is in contact with the rubber track 40 is a portion corresponding to the lower portion of the center point of the driving sprocket, and the portion in which the driving sprocket is spaced apart from the rubber track is corresponding to the portion at which contact is started. That's the top part. Here the upper and lower parts are not strictly meant to be physically accurate point parts, one or two drive lugs 42 and roll sleeves 22 on the upper part, and one or two drive lugs on the lower part and It can be said that it means the area | region containing a roll sleeve.

However, it is apparent that the present invention is not limited by this point. For example, the drive sprocket 20 may start to contact the rubber track 40 at the lower end thereof or start contacting the love track 40 before the rubber track 40 is spaced from the ground, so that at least the drive sprocket 20 It may be configured to be spaced apart from the upper portion of the center or more.

As such, when the driving sprocket 20 and the rubber track 40 come into contact with each other at the lower end of the center of the driving sprocket 20 or before the rubber track 40 is spaced from the ground, the driving sprocket 20 contacts the ground. It means that the rubber track 40 in contact with the state. As described above, when the driving sprocket 20 is in contact with the rubber track 40, the ground is supported under the rubber track 40 so that the roll sleeve 22 and the rubber track 40 of the driving sprocket 20 are supported. The slip between the driving lugs 42 of)) can be prevented from occurring or the slip can be suppressed as much as possible. This point can be said that the transmission of power from the drive sprocket 20 to the rubber track 40 proceeds efficiently.

In addition, the present invention can respond quickly even when the rubber track 40 is increased by long-term use. For example, using the first tension adjusting means and the second tension adjusting means as described above, it may be possible to have the tension required as quickly and accurately as possible to the extended rubber track 40.

For example, the rubber track at the top between the idler and the drive sprocket will be able to easily adjust the tension through the adjustable arm 34 and the upper roller 32. In addition, by adjusting the front and rear positions of the idler frame 60 by rotating the screw member 80, the tension of the overall rubber track can also be adjusted as described above.

In addition, it is natural that considerable convenience can be expected even when the rubber track itself is mounted on the undercarriage using the first tension adjusting means and the second tension adjusting means of the present invention.

As described above, it can be seen that the present invention has a basic technical idea to make the contact between the driving sprocket and the rubber track in a sufficiently wide area. In addition, within the scope of the basic technical idea of the present invention, various modifications are possible to those skilled in the art, and the protection scope of the present invention should be interpreted based on the appended claims. It is obvious too.

The undercarriage according to the present invention as described above may be applied to various types of agricultural traveling devices using a rubber track, including a multi-sized loader capable of various tasks. And of course, it can be applied to equipment such as small excavators and bulldozers.

Claims

A frame for supporting an engine which is a driving source of the multi-load loader;

A rubber track in which a driving lug having a predetermined interval is formed on an inner side thereof;

A driving sprocket rotated by a driving force of an engine, coupled to the driving lug to transmit rotational power to a rubber track, and installed at an inner rear end of the rubber track and rotatably supported by the frame;

An idler installed at the front end of the rubber track and supported by the frame;

A plurality of track rollers installed between the driving sprocket and the idler and rotatably supported by the frame; And

A tension adjusting means for adjusting the tension of the rubber track;

The rubber track is in contact with the ground between the portion in contact with the idler and the drive sprocket, the drive sprocket is undercarriage of the multi-load loader in contact with the rubber track before the rubber track is spaced apart from the bottom.
The undercarriage of the multi-load loader of claim 1, wherein the driving sprocket is spaced apart from the rubber track at a point above the center point.
The undercarriage of the multi-load loader according to claim 1, wherein the rubber track has the highest position at the upper end of the driving sprocket.
The undercarriage of the multi-load loader according to any one of claims 1 to 3, wherein the driving sprocket is spaced apart from the rubber track at an upper end portion corresponding to the contact start portion of the rubber track.
The undercarriage of the multi-load loader of claim 4, wherein the driving sprocket includes a plurality of protrusions formed on an outer circumferential surface of the driving sprocket to engage with the driving lug to transmit rotational power.
The method of claim 4, wherein the drive sprocket comprises a pair of ring members spaced apart at regular intervals, and the roll sleeve is provided between the ring member, the roll sleeve is coupled between the drive lug capable of transmitting power Undercarriage of the multi-load loader.
7. The undercarriage of claim 6, wherein the roll sleeve is rotatably supported between the ring members.
The method of claim 4, wherein

The tension control means, the first tension control means for adjusting the rubber track tension by pushing the rubber track not in contact with the ground upwards, and the second tension control for adjusting the tension of the rubber track by extending the front and rear length of the frame Undercarriage of a multi-load loader consisting of means.
The method of claim 8,

The frame comprises a main frame rotatably supported by a drive sprocket and a plurality of track rollers, and an idler frame installed in front of the main frame to rotatably support an idler;

The first tension adjusting means includes an upper roller in contact with an inner surface of a rubber track positioned at an upper side between an idler and a driving sprocket, and a first arm and a second arm supporting the upper roller on a main frame. Become;

Either of the first arm or the second arm is an undercarriage of the adjustable multi-load loader.
The method of claim 9,

The second tension adjusting means, the undercarriage of the multi-load loader consisting of a linear movement means capable of adjusting the idler frame relative to the main frame forward and backward.
The method of claim 10, wherein the linear movement means,

Nut block connected to idler frame,

And a screw member having a front portion screwed to the nut block and a rear portion extending rearward from the front portion and not rotatably supported on the main frame.

Undercarriage of the multi-load loader, the idler frame, the idler is supported by the rotation of the screw member to move linearly forward and backward.
12. The screw member of claim 11, wherein the screw member is fixed to a middle portion of the screw member and extends radially so as to contact the front surface of the stop plate provided in the main frame and having a through hole through which the screw member passes. A stopper for regulating the thing;

The main carriage is installed on the rear side of the stop plate, the undercarriage of the multi-load loader is configured to further include a support plate for restricting the movement of the screw member is inserted into the neck portion of the screw member forward.
12. The method of claim 11, wherein the front end portion of the main frame is formed to receive the idler frame from the front, the slot is formed rearward to receive the idler support portions protruding from both sides of the idler frame to support the idler on both sides of the front end portion. Undercarriage of the multi-load loader.