JP2012126398A - Crawler traveling device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a crawler traveling device capable of facilitating engagement between the engaging recessed part of a crawler belt and the driving nail body of a driving sprocket.SOLUTION: A core metal projection 63 is covered with a rubber material. An engaging recessed part 62, to be engaged with the driving nail body 31 of a driving sprocket, is formed on the inner peripheral surface of a crawler belt 6. The engaging recessed part 62 is located between the right and left core metal projections 63 of core metals 61 arranged side by side in a belt peripheral direction, and an end surface in a belt width direction is formed into a tapered surface to be narrower toward the deep side. The driving sprocket is provided with, on the outer peripheral side of a disk-like member 30 fitted between the right and left core metal projections 63, a driving nail body 31 bulging in the horizontal direction of the disk-like member 30 inserted in the engaging recessed part 62 formed in the crawler belt 6 for each predetermined interval in the peripheral direction. The end surface of the driving nail body 31 in the horizontal direction is formed into a tapered surface to be narrower toward the outer side of a radial direction.

Description

  The present invention embeds a cored bar in a belt body made of a rubber material at a constant pitch in the circumferential direction of the belt, and a pair of left and right cores for rolling guide from the intermediate part in the belt width direction of each cored bar to the belt inner peripheral surface side The present invention relates to a crawler traveling device including a crawler belt provided with a gold protrusion and a drive sprocket that applies rotational power to the crawler belt in the belt circumferential direction.

  In this type of crawler travel device, a concave portion for engagement formed in a rubber belt main body portion between core bars embedded at a constant pitch in the circumferential direction of the crawler belt is longer in the belt width direction than in the belt circumferential direction. The drive sprocket that drives the crawler belt is provided with a drive claw body that is formed long in the same direction as the longitudinal direction of the engagement recess, and the contact at the engagement point between the drive claw and the engagement recess is provided. A structure having a structure in which a large driving force of a driving claw body can be transmitted to a rubber belt body of a crawler belt by increasing the area is known (see Patent Document 1).

JP 2009-78796 A (paragraphs [0031], [0041], FIG. 1, FIG. 2, FIG. 3, FIG. 5, FIG. 6)

In the crawler traveling device described above, driving is performed using a driving sprocket having a concave portion for engagement formed in the belt main body portion of the crawler belt and a driving claw body formed long in the same direction as the longitudinal direction of the concave portion for engagement. Although the contact area between the nail body and the engaging recess is increased, there are the following problems.
That is, in such a structure that transmits power by engaging a driving claw body formed long in the same direction as the longitudinal direction of the engaging recess with the engaging recess formed in the belt main body portion, The crawler belt and the drive sprocket are not provided with a function of suppressing the positional deviation in the belt width direction.
For this reason, when the left and right direction in the traveling direction of the airframe is an inclined road surface, the crawler belt and the drive sprocket are displaced in the belt width direction, and the engagement recesses and the drive claws formed in the belt main body portion. There may be situations where the body does not engage well.
In order to avoid this, for example, it is conceivable that the dimension of the engaging recess in the belt width direction is set to a sufficiently large size rather than the lateral width of the driving claw body to facilitate engagement. However, when the dimension in the belt width direction of the engaging recess is increased in this way, it is not stable at which position in the belt width direction the drive claw body is engaged in the engagement recess, and the drive claw body is eventually engaged. There is a problem that the strength of the crawler belt is reduced due to the presence of an engagement recess that becomes unnecessarily long near the one end side of the recess.

  An object of the present invention is to provide a crawler traveling device that can easily engage a crawler belt engaging recess and a driving claw of a driving sprocket, and can suppress positional deviation in the belt width direction between the crawler belt and the driving sprocket. It is to provide.

The technical means of the present invention taken in order to achieve the above object has the following structural features and operational effects.
[Solution 1]
The cored bar is embedded in the belt body made of rubber material at a constant pitch in the belt circumferential direction, and a pair of left and right cored bar projections for rolling guides project from the intermediate part in the belt width direction of each cored bar to the belt inner peripheral surface side. A crawler traveling device comprising a crawler belt provided and a drive sprocket that applies rotational power to the crawler belt in the belt circumferential direction,
The crawler belt has an engagement concave portion that engages with the drive claw of the drive sprocket on the inner peripheral surface side of the crawler belt, and the engagement concave portion is located between the core bars in the belt circumferential direction and is closer to the belt circumferential direction. It is formed in a tapered surface that is long in the belt width direction, and the end surface in the belt width direction becomes narrower toward the inner back side,
The drive sprocket is inserted into the engagement recess formed in the crawler belt at predetermined intervals in the circumferential direction on the outer peripheral side of the disk-shaped member fitted between the left and right core metal protrusions. Drive claw body formed longer in the left-right direction than the circumferential direction of the member, and the end face in the left-right direction of the drive claw body is formed in a tapered surface that becomes narrower toward the radially outer side. Features.

[Operation and effect of invention according to Solution 1]
According to the configuration shown in the above solution 1, the engagement recess that engages with the drive claw of the drive sprocket on the inner peripheral surface side of the crawler belt is located between the core bars in the belt circumferential direction. The driving claw of the driving sprocket that is engaged with the engaging recess is also formed longer in the left-right direction than in the circumferential direction of the disk-shaped member. As a result, the contact surface in the engaged state between the engaging recess and the driving claw body is elongated in the belt width direction, the contact area is increased, and the surface pressure at the contact surface is kept relatively low with a large driving force. The crawler belt can be driven.

The engaging recess is formed into a tapered surface whose end surface in the belt width direction becomes narrower toward the inner back side, and the driving claw body is formed into a tapered surface whose end surface in the left-right direction becomes narrower toward the radially outer side. Is formed. For this reason, even if the length in the belt width direction of the concave portion for engagement, which is the same direction, and the length in the left-right direction of the drive claw body are the same, the width of the tip of the drive claw body at the time when they start to mesh with each other Since the narrow portion corresponds to the wide portion on the entrance side of the engaging recess, there is a relatively large difference in the same direction dimension at the engagement start location, and the engagement becomes easy.
However, in the engagement completion state in which the driving claw body is completely fitted in the engaging recess, the difference in the same direction dimension is smaller than that at the start of engagement, and the engagement recess and the driving claw body are displaced in the same direction. Stable power transmission in a state where is suppressed is possible. In addition, since it is not necessary to make the length of the engaging recess in the belt width direction extremely larger than the length of the driving claw in the same direction, it is possible to avoid impairing the strength of the crawler belt.

  In addition, since the end surface of the engaging recess in the belt width direction and the end surface of the drive claw body in the left-right direction are each formed into a tapered surface, the center position of the engagement recess in the belt width direction and the drive claw body When the meshing is started from the state where the center positions in the left and right directions are shifted from each other in the same direction, the meshing is deepened while the center positions of the two are guided toward each other while being guided by the respective tapered surfaces. There is an advantage that it can be easily engaged as expected.

[Solution 2]
Another technical means of the present invention taken to solve the above-mentioned problem is that, as described in claim 2, the inclination angle of the tapered surface, which is the end surface in the belt width direction of the engaging concave portion, with respect to the horizontal plane is It is set to the same inclination angle as the inclination angle with respect to the horizontal surface of the taper surface which is the end surface of the left-right direction of a body.

[Operation and effect of invention according to Solution 2]
According to the configuration shown in the solving means 2 above, the inclination angle of the tapered surface on the engaging recess side and the inclination angle of the tapered surface on the drive claw body side are set to the same inclination angle with respect to the horizontal plane. In a state where the end surface in the belt width direction on the engagement recess side and the end surface in the left-right direction on the drive claw body are in contact with each other, the taper surfaces having the same slope are in contact with each other, and the entire surface of the contact portion The contact is made with the pressure almost uniform.
Therefore, by ensuring the area of the contact portion at this end surface location as large as possible and making the surface pressure almost uniform, the surface pressure at this location can also be relatively low, and the left and right direction acting from the drive claw body side on an inclined ground etc. When the load is applied to the end face of the engaging concave portion facing this, there is an advantage that the crawler belt wear at the contact point can be reduced by keeping the surface pressure as low as possible.

[Solution 3]
Another technical means of the present invention taken to solve the above-mentioned problem is that, as described in claim 3, the disc-shaped member of the drive sprocket is formed in the left-right direction of the outer peripheral side portion that enters between the left and right cored bar projections. The width of the disc is formed to be narrower than the distance between the inner end sides of the left and right cored bar projections, and after the end surface in the left-right direction of the driving claw contacts the end surface of the engaging recess, the disc shape The relative left and right position between the end face in the left and right direction of the disk-shaped member and the drive claw body is set so that the end face in the left and right direction of the member contacts the inner end side surface of the core metal protrusion. That is.

[Operation and effect of invention according to Solution 3]
According to the configuration shown in the solution means 3 described above, not only the contact between the end surface in the belt width direction of the recess for engagement of the crawler belt and the end surface in the left-right direction of the drive claw body of the drive sprocket, but also the core metal of the crawler belt The contact between the inner surface of the protrusion and the end surface of the disk-shaped member in the left-right direction can also suppress the displacement of the crawler belt in the belt width direction with respect to the drive sprocket.
Therefore, compared to the case where the displacement of the crawler belt in the belt width direction is suppressed only by the contact between the end surface in the belt width direction of the recess for engagement of the crawler belt and the end surface in the left-right direction of the drive claw body of the drive sprocket, There is an effect that the displacement of the crawler belt in the belt width direction can be more reliably suppressed.

And the relative left-right direction position of the end surface in the left-right direction of the disc-shaped member and the drive claw body is determined after the end surface in the left-right direction of the drive claw body abuts the end surface of the engaging recess. Since the end face in the left-right direction is set to contact the inner end face of the cored bar projection, it is also effective in suppressing noise and crawler belt wear.
In other words, when a displacement of the crawler belt in the belt width direction with respect to the drive sprocket occurs, the end surface of the drive claw body in the left-right direction first contacts the end surface of the engagement recess of the crawler belt, and the end surface of the engagement recess After being compressed and elastically deformed, the end face in the left-right direction of the disk-shaped member comes into contact with the inner end side face of the cored bar protrusion. By adopting such a structure that contacts in a stepwise manner, the end face of the metal disk-shaped member and the inner end face of the cored bar protrusion are directly connected without elastic deformation of the engaging recess. There is an advantage that the magnitude of noise can be reduced compared to the structure of contact.
Further, the engaging recess that is compressed and deformed in contact with the end face of the drive claw body is in contact with the crawler belt end face in the left-right direction of the disk-shaped member, and driven further than the crawler belt. By stopping the relative movement with the sprocket, the relative movement between the engagement recess and the drive claw body is also restricted, and the pressing force from the drive claw body in the direction of elastically deforming the engagement recess disappears. There is an advantage that the degree of wear of the engaging recess can be reduced in this respect as well.

[Solution 4]
According to another technical means of the present invention, as set forth in claim 4, a plurality of wheels arranged in parallel in the belt circumferential direction so as to contact the inner peripheral surface side of the crawler belt, And an idler wheel disposed at each of the front and rear positions of the wheel, and a drive sprocket is provided at an intermediate position between the front and rear idler wheels and at an upper position of the wheel. It is.

[Operations and effects of invention according to Solution 4]
According to the configuration shown in the solution means 4 described above, a suitable drive configuration is obtained in a so-called semi-crawler type crawler traveling device in which the drive sprocket is provided at an intermediate position between the front and rear idler wheels and at an upper position of the wheel. There are advantages to being

Overall side view of tractor Overall side view of crawler traveling device Top view of crawler belt IV-IV sectional view in FIG. Partial cross-sectional view of the crawler belt in the belt circumferential direction Schematic perspective view showing cored bar protrusion Perspective view showing a part of the drive sprocket Side view showing the outer periphery of the drive sprocket IX-IX sectional view in FIG. Arrow view in FIG. Explanatory drawing which shows the relationship between a drive nail | claw body, the recessed part for engagement, and a metal core protrusion. The stopper guide is shown, (a) is a plan view, (b) is a side view, and (c) is a front view. It is explanatory drawing which shows the action state of the related member with respect to a crawler belt, (a) shows a relationship with a drive sprocket, (b) shows a relationship with an idler wheel, (c) shows a relationship with a slip-off prevention guide. Show It is explanatory drawing which shows the proximity | contact regulation state of a slip-off prevention guide and a core metal protrusion, (a) shows a reference | standard attitude | position, (b) shows a maximum proximity | contact attitude | position. Explanatory drawing which shows the contact state of an idler wheel and a crawler belt Explanatory drawing which shows the relationship between a drive nail | claw body, the recessed part for engagement, and a metal core protrusion.

Hereinafter, an example of an embodiment of the present invention will be described based on the drawings.
[Overall structure of tractor]
FIG. 1 shows a semi-crawler type tractor provided with a crawler traveling device 2 according to the present invention on the rear side of the machine body. This semi-crawler type tractor is a four-wheel drive type tractor with a specification change to a semi-crawler type, and includes a pair of left and right front wheels 10 that can be steered at the front of the tractor with a cabin 1 and at the rear of the fuselage. The main propulsion device includes a pair of left and right crawler traveling devices 2. Further, the rear portion of the machine body is configured to connect a tilling device, a harvesting device, or various intermediate management working devices via a three-point link mechanism (not shown).

[Crawler traveling device]
As shown in FIGS. 1 and 2, the crawler travel device 2 includes a large-diameter drive spcket 3 connected to a rear axle 12 provided for driving rear wheels in a rear transmission case 11 of the tractor main unit 1. .
The crawler belt 6 is wound around the drive sprocket 3, the idler wheels 4, 4 provided before and after the track frame 20, and a plurality of rollers 5 arranged in parallel in the longitudinal direction of the track frame 20. Thus, the drive sprocket 3 is provided at an intermediate position between the front and rear idler wheels 4 and 4 and at an upper position of the wheel 5.
The tread in the left-right direction of the crawler traveling device 2 is set to be substantially the same as the tread of the front wheel 10 in order to travel between the fences in the field.

As shown in FIG. 2, three rolling wheels 5 are arranged in parallel in the front-rear direction, and the foremost rolling wheel 5 is attached to a track frame 20 via a fixing bracket 21 in a fixed position.
The two wheels 5 and 5 on the rear side of the balance 5 are pivotally attached to the support bracket 22 attached to the track frame 20 so that the middle part thereof is swingable up and down around the horizontal axis x. The members 23 are arranged at both ends of the member 23 so as to be able to swing the seesaw.

Each of the rollers 5 and the crawler belt 6 maintains a predetermined positional relationship in the width direction of the belt and is provided with anti-separation guides 7 for preventing the crawler belt 6 from being detached from the rollers 5 at two front and rear positions. .
The front-side locking guide 7 is connected to the lower end side of the fixing bracket 21 that fixes and supports the frontmost roller 5, and the rear-side locking guide 7 is the last side of the balance-like member 23. It is continuously provided in a state extending before and after the wheel 5 at the end position.

[Crawler belt]
The crawler belt 6 is configured as shown in FIGS.
The crawler belt 6 has a core body 61 embedded in a belt body 60 formed in an endless belt shape with a rubber material at a constant pitch in the belt circumferential direction, and on the inner peripheral surface side of the belt between the core bars 61. An engaging recess 62 for engaging the driving claw body 31 of the driving sprocket 3 and transmitting power to the crawler belt 6 side is formed.

As shown in FIGS. 5 and 11, the engaging recess 62 is located between the core bars 61 in the belt circumferential direction and is formed longer in the belt width direction than in the belt circumferential direction. The end surfaces 62a on both ends of the engaging recess 62 in the belt width direction are not perpendicular to the horizontal plane when the crawler belt 6 is positioned on the horizontal plane as shown in FIG. And an inclined surface having a predetermined belt inclination angle β (corresponding to an inclination angle with respect to a horizontal plane).
The engaging recesses 62 in which the end surfaces 62a, which are inclined surfaces having the belt inclination angle β, are formed on both end sides in the belt width direction as described above are formed on the inner back side (the lower side in the figure) by the end surfaces 62a on both the left and right sides. ) Is formed on a tapered surface that becomes narrower.

Each cored bar 61 is provided with a pair of left and right cored bar projections 63 for guiding the wheel from the intermediate part in the belt width direction toward the inner peripheral surface of the belt. The idler wheels 4 and 4 are configured to pass through.
In addition, a flat roller raceway surface 64 on which the rolling wheels 5 roll is formed on the inner peripheral surface of the belt main body 60 located at the laterally outer side of each cored bar protrusion 63, and the outer peripheral surface of the belt main body 60. On the side, a propulsion lug 65 thicker than the thickness of the belt main body 60 excluding the cored bar projection 63 is integrally formed at a position overlapping the engaging recess 62 in the belt circumferential direction.

  On the inner peripheral surface side of the belt main body 60 between the core bar 61 and the engagement recess 62, the driving force of the drive claw body 31 of the drive sprocket 3 engaged with the engagement recess 62 is transmitted to the core bar 61. For this purpose, a pressure receiving block 66 is provided. In other words, the rubber pressure receiving block portion 66 is configured to transmit a driving force to the metal core bar 61 while receiving a compression action by the metal driving claw body 31 entering the engaging recess 62. Yes, it is possible to avoid the occurrence of noise by avoiding direct contact between the metal of the driving claw body 31 and the cored bar 61.

  Further, as shown in FIG. 15, the pressure receiving block 66 has an inner peripheral surface of the idler wheel 4 and the inner core 61 in the state where the idler wheel 4 is in contact with the inner peripheral surface of the pressure receiving block 66. Projecting from the inner peripheral surface of the core metal 61 toward the inner peripheral surface of the belt so as to form a predetermined gap S3 for avoiding direct contact between the idler wheel 4 and the core metal 61 between the peripheral surface and the peripheral surface. Formed.

As shown in FIGS. 4 to 6, the metal core protrusion 63 constitutes a belt main body 60 by a metal protrusion 61 a that is integrally formed with a part of the metal core 61 and protrudes toward the inner peripheral surface of the belt. The outer shape is formed substantially in a mountain shape by covering with a mountain-shaped protrusion 67 made of a rubber material.
That is, the core metal protrusion 63 is formed in a mountain shape in a sectional view both in the belt width direction shown in FIG. 4 and in the belt circumferential direction shown in FIG. As shown in FIG. 6, the surface facing the inner side of the core metal protrusion 63 in the belt width direction is formed by an inclined surface that serves as a guide surface C for the idler wheel 4 and the detachment prevention guide 7.
Further, the mountain-shaped cored bar projection 63 is formed in a T shape in a plan view with a top portion 63a of a line along the belt circumferential direction and a line directed inward so as to be orthogonal to the line. The protrusion 67 is formed in a shape in which a recess 63 b is provided at a position located on the inner side in the belt width direction near the top 63 a on the guide surface C.

(Drive sprocket)
The drive sprocket 3 is configured as shown in FIGS. 2 and 7 to 11.
That is, a large-diameter disk-shaped member 30 connected to the rear axle 12 and a drive claw body 31 provided so as to protrude outward in the radial direction from the outer peripheral edge of the disk-shaped member 30 are configured. ing.

  The disk-shaped member 30 includes a hub plate 13 fixed to the rear axle 12 as a drive shaft, and an annular outer peripheral member 14 (corresponding to an outer peripheral side portion) bolted to the outer peripheral side of the hub plate 13. The outer peripheral member 14 is configured by a combination of partial arc-shaped divided arc-shaped members 14a, 14b, and 14c that are equally divided into three in the circumferential direction.

As shown in FIGS. 7 to 10, the outer peripheral member 14 is thicker in the radial direction near the outer peripheral edge 16 than in the vicinity of the mounting portion 15 on the radially inner hub plate 13. In the vicinity of the outer peripheral edge 16, an annular rib portion 32 is formed.
The drive claw body 31 is integrally formed by projecting outward in the radial direction of the outer peripheral edge 16 of the outer peripheral member 14 and projecting outward in the left-right direction from the rib portion 32. It is.

The thickness d1 of the rib portion 32 in the left-right direction is formed to be narrower than the facing distance between the left and right core metal protrusions 63 of the crawler belt 6, and the core metal protrusion 63 and the drive claw body are formed. The correlation is set as follows.
That is, as shown in FIG. 11A, after the end surface 31a in the left-right direction of the drive claw body 31 contacts the end surface 62a of the engagement recess 62, the end surface 62a of the engagement recess 62 is driven by the drive claw body. When the pressing force of 31 is applied and the rib 32 is deformed by a certain amount of compression δ as shown in FIG. 11B, the edge 32 a of the rib portion 32 is formed on the inner end surface 63 c of the core metal protrusion 63. Get in touch.
Thus, after the end surface 31a in the left-right direction of the driving claw body 31 abuts on the end surface 62a of the engaging recess 62 and is elastically deformed to some extent, the rib portion corresponding to the end surface in the left-right direction of the disk-shaped member 30 is obtained. The left and right end edges 32 a of the ribs 32 are in contact with the inner end surface 63 c of the core metal protrusion 63. The position is set.

That is, as shown in FIG. 11A, when a part of the surface where the end surface 31a in the left-right direction of the driving claw body 31 abuts the end surface 62a of the engaging recess 62 is a contact location P1 for convenience, As shown in FIG. 11B, the time lag is generated until the contact point P2 between the end edge 32a of the rib portion 32 and the inner end surface 63c of the cored bar 63 contacts. The relative left-right direction position of the end surface 31a in the left-right direction of the driving claw body 31 and the end edge 32a in the left-right direction of the rib portion 32 is set.
That is, this positional relationship will be described with reference to FIG.
When the center position of the drive claw body 31 in the left-right direction is positioned on the center line CL of the engagement recess 62 in the belt width direction, the end face 31a in the left-right direction of the drive claw body 31 and the engagement recess The contact point P1 with the end surface 62a of 62 and the contact point P2 with the end edge 32a of the rib portion 32 and the surface 63c on the inner end side of the cored bar 63 are in a non-contact state.
At this time, of the contact location P1, the distance LP1-1 from the center line CL to the contact location P1 of the end surface 62a of the engagement recess 62, and the end surface in the left-right direction of the drive claw body 31 from the center line CL. The first gap LP1 exists between the distance LP1-2 to the contact point P1 of 31a.
Further, in the contact location P2, the distance LP2-1 from the center line CL to the contact location P2 of the inner end surface 63c of the cored bar 63, and the edge of the rib portion 32 from the center line CL. A second gap LP2 exists between the distance LP2-2 to the contact point P2 at 32a.
Then, the second gap LP2 is set larger than the first gap LP1 by an amount corresponding to the compression amount δ when the end face 62a of the engaging recess 62 is compressed and deformed by the pressing force of the driving claw body 31. Therefore, as described above, the end surface 62 a of the engaging recess 62 is compressed and deformed by the pressing force of the driving claw body 31, and the end edge 32 a of the rib portion 32 is the surface on the inner end side of the core metal protrusion 63. There is a time lag until the amount of movement necessary to contact 63c is reached.

As shown in FIGS. 7 to 13A, the drive claw body 31 projects in the lateral direction (left-right direction) perpendicular to the plate surface of the disk-shaped member 30, thereby causing the belt width of the engaging recess 62. The length is slightly shorter than the length in the direction, and the length in the left-right direction is approximately the same as the length of both the left and right cored bar protrusions 63.
As shown in FIGS. 9 and 11, the end surface 31a in the left-right direction of the driving claw body 31 is in a state in which the outer end edge of the driving claw body 31 is positioned on the horizontal plane. On the other hand, it is formed of an inclined surface having a predetermined claw inclination angle α (corresponding to an inclination angle with respect to a horizontal plane), not perpendicular to the surface.
End surfaces 31a, which are inclined surfaces having the claw inclination angle α, are formed on both left and right sides of the drive claw body 31, and the drive claw body 31 is located on the outer side in the radial direction by the end surfaces 31a on both the left and right sides. It is formed on a tapered surface that becomes narrow.
The claw inclination angle α is set to the same angle as the belt inclination angle β formed on the end surface 62a in the belt width direction of the engaging recess 62.

A front-facing surface 31b (a surface on the side where the driving force is applied to the crawler belt 6 in the forward direction of the machine body) and a rearward surface 31c (a crawler belt 6 in the backward direction of the machine body) that are positioned forward and backward in the circumferential direction of the drive claw body 31. The surface to which the driving force is applied) is generally in the direction along the normal line from the center of rotation of the disk-shaped member 30, but the circumferential width d2 at the portion (base side) slightly closer to the center of rotation is the center of rotation. The taper surface has a tapered shape that is wider than the circumferential width d3 of the outer portion (nail tip side) away from the taper and is slightly narrower toward the radially outer side of the drive claw body 31.
A partial stealing portion 33 is provided on the end surface 31a of the driving claw body 31 to reduce the weight of the entire disk-shaped member 30.

[Release prevention guide]
The detachment prevention guide 7 is configured as shown in FIGS. 2, 12, 13 (c), and 14.
That is, it is continuously provided on the track frame 20 so as to be positioned between the left and right cored bar projections 63, 63 at the position where the front end wheel 5 and the rear end wheel 5 are provided. The detachment prevention guides 7 connected and fixed to the fixed bracket 21 and the balance-like member 23 connected to the support bracket 22 are the same in the front and rear.

As shown in FIG. 12, the detachment prevention guide 7 is formed in a boat shape as a whole in a side view, and the balance-like member 23 connected to the fixed bracket 21 or the support bracket 22 at two positions on the front and rear sides thereof. There are provided mounting portions 72, 72 having screw holes 71, 71 for connecting and fixing to.
In the mounting posture with respect to the fixed bracket 21 or the balance-like member 23, the position which becomes the lowermost end of the locking guide 7 is a perpendicular line y1 from the rotation center p of the wheel 5 shown in FIG. 2 and FIG. It is a crossing position. The lowermost position of the stopper guide 7 is in a state closest to the inner peripheral surface of the crawler belt 6 between the left and right core metal projections 63, 63. The width L1 in the width direction of the belt at the location intersecting the perpendicular line y1 is the contact at the upper portion of the core metal projection 63 at the location where the center line y2 in the belt circumferential direction of the core metal projection 63 on the crawler belt 6 side exists. It is set to be larger than the lateral width L2 at the location P3.

As shown in FIGS. 12A and 12B, the width L1 of the contact position in the belt lateral width direction of the slip-off preventing guide 7 is a linear portion in the belt circumferential direction (front-rear direction) of the slip-off preventing guide 7. The front and rear ends of the stopper guide 7 are tapered in a plan view as shown in FIG. 12A before and after the linear portion L3. In the side view, as shown in FIG. 12B, the front and rear ends are warped upward.
Further, in the linear portion L3 of the locking guide 7, near the portion intersecting the perpendicular y1, there is an orthogonal lower edge portion 73 orthogonal to the perpendicular y1 as shown in FIG. 12 (b). An orthogonal lower edge range L4 is formed, and among the linear portions L3 before and after that, the front lower edge portion 74 in front of the orthogonal lower edge range L4 is formed in a slightly upward shape, and the orthogonal lower edge The rear lower edge portion 75 behind the range L4 is formed in a slightly rearwardly rising shape.

The reason why the lower edge guide 7 is formed in this way is as follows. That is, as shown in FIG. 2, when it is assumed that all the wheels 5 are located on a flat ground, the front end side and the rear end of the crawler traveling device 2 with respect to the lower tangent line to all the wheels 5. The lower edge of the side idler wheels 4, 4 is located higher. For this reason, the crawler belt 6 is stretched slightly forward on the front side of the frontmost roller 5 and slightly lifted on the rear side of the rearmost roller 5, so that This is to maintain a necessary gap between the lower edge of the stop guide 7 and the inner peripheral surface of the crawler belt 6.
Further, the front end side and the rear end side of the slip prevention guide 7 are formed in a tapered shape in a plan view, as described above, the guiding action by the slip prevention guide 7 having a wide width L1 in the belt lateral width direction is smooth. This is to make it happen. Furthermore, as described above, the front and rear ends of the slip prevention guide 7 are formed in a shape that warps upward in addition to the tapered shape in plan view. This is in order to avoid direct contact.

  The anti-separation guide 7 configured as described above has a reference posture shown in FIG. 14A (all the rollers 5 are in contact with the roller raceway surface 64 and the crawler belt 6 receives an average pressure as a whole. (Traveling posture in the state) is sufficiently between the position that is the lowermost end of the stopper guide 7 and the inner peripheral surface of the crawler belt 6 (the inner peripheral surface of the pressure receiving block portion 66 in this embodiment). The relative height position between the contact surface of the wheel 5 and the lower surface of the slip-off preventing guide 7 is set so as to have a large distance S1.

However, as shown in FIG. 14B, in the maximum proximity posture (running posture in a state where a concentrated thrust force is applied from below some of the wheels 5 by riding on a convex portion or the like), the crawler belt 6 is partially compressed or bent, and the anti-separation guide 7 is in a state of relatively approaching the inner peripheral surface of the crawler belt 6.
However, in the present invention, as described above, the lateral width L1 of the stopper guide 7 is set to be larger than the lateral width L2 in the belt lateral width direction at the contact point P3 at the upper portion of the core metal projection 63 on the crawler belt 6 side. Therefore, as shown in the figure, when the slip prevention guide 7 and the inner peripheral surface of the crawler belt 6 (in this embodiment, the inner peripheral surface of the pressure receiving block portion 66) approach each other, Due to the contact between the contact point P3 and the contact point P3 at the upper part of the core metal protrusion 63, further approach is prevented, and the interval S2 can be secured so as to avoid contact between the two.
That is, the lower edge of the stopper guide 7 contacts the inner peripheral surface of the crawler belt 6 by the contact point P3 in the range of the linear portion L3 having the lateral width L1 set to the stopper guide 7. Proximity restricting section A that prevents this is configured.

Note that the contact point P3 with the contact point P3 of the stopper guide 7 in the upper part of the core metal protrusion 63 is the drive in the core metal protrusion 63 shown in FIG. 11B and FIG. The sprocket 3 is set at a position away from the contact point P2 with the contact point P2 at the edge 32a in the left-right direction of the rib portion 32 of the sprocket 3.
This prevents the rubber material covering the outer surface of the cored bar protrusion 63 from coming into contact with both the rib portion 32 of the drive sprocket 3 and the anti-separation guide 7 at the same location, so that the rubber material It is for suppressing that it wears out.

The proximity restricting portion A of the locking guide 7 is a contact portion at the upper portion of the guide surface C of the cored bar projection 63 of both side surfaces B and B having a slanted slope of the locking guide 7. The both side surfaces B, B are slightly inclined from the taper angle formed by the inclination of the guide surfaces C, C of the left and right cored bar projections 63. The inclination angle is set so as to obtain a large taper.
Therefore, even if the locking guide 7 is relatively strong and fits between the left and right cored bar projections 63, 63, the contact area at the proximity restricting portion A is relatively small, and the situation where the locking guide 7 is strongly bitten and is difficult to come off. Easy to avoid.

[Idler wheel]
As shown in FIGS. 2 and 13 (b), the idler wheels 4 and 4 are free to play between the left and right cored bar projections 63 and 63 and in contact with the inner peripheral surface of the crawler belt 6. Rotate.
At this time, the outer peripheral surfaces of the idler wheels 4 and 4 are rotated in contact with the inner peripheral surface side of the pressure receiving block portion 66 of the crawler belt 6 as described above. It can be avoided.
The both side surfaces of the idler wheels 4 and 4 may come into contact with the metal portions of the left and right cored bar protrusions 63 and 63, but at this point, the idler wheels 4 and 4 and the crawler belt 6 are almost relative to each other. Since it rotates without moving, even if the metal parts touch each other, the noise does not become so loud at this point, and the generation of noise can be suppressed.

[Other Embodiment 1]
The proximity restricting portion A is not limited to the one based on the setting of the lateral width L2 of the contact point P3 of the stopper guide 7 with respect to the core metal protrusions 63, 63 as described in the embodiment. In part, a portion that does not contact in the reference posture but contacts with the maximum protruding portion of the cored bar protrusions 63 and 63 in the maximum proximity posture is formed, and the detachment prevention guide 7 further covers the inner circumference of the crawler belt 6. You may comprise so that space | interval S2 may be ensured with the structure which prevented approaching to the surface side.

[Second embodiment]
The stopper guide 7 is not limited to one having two front and rear structures as described in the embodiment. For example, only one of the front and rear is provided, or a long disconnection from the front end side to the rear end side is provided. A stop guide 7 may be provided.

[3 of another embodiment]
In the embodiment, as the proximity restricting portion A of the locking guide 7, the both side surfaces B and B having a tapered shape of the locking guide 7 are connected to the guide surfaces C and C of the left and right metal core protrusions 63. Although the inclination angle is set so that the taper is slightly larger than the angle of the taper formed by the inclination, the present invention is not limited to this, and both sides of the anti-skid guide 7 have a constricted inclination. The taper angle formed by the inclination of the surfaces B and B and the guide surfaces C and C of the left and right cored bar protrusions 63 may be set to the same angle. When the same angle is set in this way, the area near the contact point P3 can be widened to reduce the surface pressure per unit area, which is advantageous in that the degree of wear at the contact point P3 can be reduced. There is.

[4 of another embodiment]
In the above-described embodiment, the claw inclination angle α of the driving claw body 31 is set to the same angle as the belt inclination angle β at the end surface 62a in the belt width direction of the engaging recess 62, but the present invention is not limited to this. The angle α may be set larger than the belt inclination angle β, or vice versa.
Incidentally, when the claw inclination angle α with respect to the horizontal plane is set to be larger than the belt inclination angle β, there are the following advantages.
If comprised in this way, the inclination angle of the taper surface by the side of the drive nail | claw body 31 side is set to the inclination angle with respect to a horizontal surface larger than the inclination angle of the taper surface by the side of the recessed part 62 for engagement. For this reason, when the engagement recess 62 and the drive claw body 31 start to engage with each other, the narrow portion at the tip of the drive claw body 31 corresponds to the wide portion on the entrance side of the engagement recess 62.
Therefore, when the inclination angles of the tapered surfaces of the engaging recess 62 and the drive claw body 31 with respect to the horizontal plane are the same, or the inclination angle on the engagement recess 62 side is the inclination angle on the drive claw body 31 side. The difference between the distance from the center position of the engagement recess 62 in the belt width direction to the taper surface and the distance from the center position of the drive claw body 31 in the same direction to the taper surface are compared with each other. When the engagement starts, the narrow portion at the tip of the drive claw body 31 corresponds to the wide portion on the entrance side of the engagement recess 62, so that a larger difference can be made. The possibility of disengagement from the entrance side of the engaging recess 62 can be reduced and the engagement can be further facilitated.
Further, in this structure, when the end face in the belt width direction on the engagement recess 62 side and the end face in the left-right direction on the drive claw body 31 side contact each other, the surface pressure on the inner back side of the engagement recess 62 is increased. The contact is made in a state where the contact pressure is high and the surface pressure on the entrance side of the engaging recess 62 is low.
As a result, the wear caused by the contact with the driving claw body 31 in the engaging recess of the crawler belt progresses more slowly on the entrance side than on the inner side of the engaging recess 62. As a result, it is easy to avoid the problem that the wear on the entrance side of the engaging recess 62 progresses faster than the inner depth side, and the drive claw body 31 is easily detached from the engaging recess 62 in the early stage.

  The crawler traveling device of the present invention can be used as a propulsion device for various vehicles such as a combine and a construction machine in addition to the tractor shown in the embodiment.

2 crawler traveling device 3 drive sprocket 5 wheel 6 crawler belt 30 disk-shaped member 31 drive claw body 31a end face 32 rib part 32a edge 60 belt main body 61 cored bar 62 engaging recess 62a end face 63 cored bar projection 63c on the inner end side Surface 64 Roller raceway surface α Claw inclination angle (inclination angle with respect to horizontal plane)
β Belt inclination angle (Inclination angle with respect to horizontal plane)
d1 interval

  The present invention embeds a cored bar in a belt body made of a rubber material at a constant pitch in the circumferential direction of the belt, and a pair of left and right cores for rolling guide from the intermediate part in the belt width direction of each cored bar to the belt inner peripheral surface side The present invention relates to a crawler traveling device including a crawler belt provided with a gold protrusion and a drive sprocket that applies rotational power to the crawler belt in the belt circumferential direction.

  In this type of crawler travel device, a concave portion for engagement formed in a rubber belt main body portion between core bars embedded at a constant pitch in the circumferential direction of the crawler belt is longer in the belt width direction than in the belt circumferential direction. The drive sprocket that drives the crawler belt is provided with a drive claw body that is formed long in the same direction as the longitudinal direction of the engagement recess, and the contact at the engagement point between the drive claw and the engagement recess is provided. A structure having a structure in which a large driving force of a driving claw body can be transmitted to a rubber belt body of a crawler belt by increasing the area is known (see Patent Document 1).

JP 2009-78796 A (paragraphs [0031], [0041], FIG. 1, FIG. 2, FIG. 3, FIG. 5, FIG. 6)

In the crawler traveling device described above, driving is performed using a driving sprocket having a concave portion for engagement formed in the belt main body portion of the crawler belt and a driving claw body formed long in the same direction as the longitudinal direction of the concave portion for engagement. Although the contact area between the nail body and the engaging recess is increased, there are the following problems.
That is, in such a structure that transmits power by engaging a driving claw body formed long in the same direction as the longitudinal direction of the engaging recess with the engaging recess formed in the belt main body portion, The crawler belt and the drive sprocket are not provided with a function of suppressing the positional deviation in the belt width direction.
For this reason, when the left and right direction in the traveling direction of the airframe is an inclined road surface, the crawler belt and the drive sprocket are displaced in the belt width direction, and the engagement recesses and the drive claws formed in the belt main body portion. There may be situations where the body does not engage well.
In order to avoid this, for example, it is conceivable that the dimension of the engaging recess in the belt width direction is set to a sufficiently large size rather than the lateral width of the driving claw body to facilitate engagement. However, when the dimension in the belt width direction of the engaging recess is increased in this way, it is not stable at which position in the belt width direction the drive claw body is engaged in the engagement recess, and the drive claw body is eventually engaged. There is a problem that the strength of the crawler belt is reduced due to the presence of an engagement recess that becomes unnecessarily long near the one end side of the recess.

  An object of the present invention is to provide a crawler traveling device that can easily engage a crawler belt engaging recess and a driving claw of a driving sprocket, and can suppress positional deviation in the belt width direction between the crawler belt and the driving sprocket. It is to provide.

The technical means of the present invention taken in order to achieve the above object has the following structural features and operational effects .
The core metal belt body made of rubber material as well as embedded in the belt circumferential direction at a predetermined pitch, a pair of left and right core metal projections for track roller guide the belt in the circumferential surface of the belt width direction intermediate portion of each core metal A crawler traveling device provided with a crawler belt that protrudes and a drive sprocket that applies rotational power to the crawler belt in the belt circumferential direction,
The core metal protrusion is covered with a rubber material, and an engagement recess is provided on the inner peripheral surface side of the crawler belt to engage with the drive claw of the drive sprocket . The engagement recess is aligned in the belt circumferential direction. located between the left and right of each set have been the core metal of the metal core protrusions each other, the end faces at the belts width direction is formed into a tapered surface which becomes narrower as the inner back side,
The drive sprocket on the outer periphery side of the disc-shaped member that fits between the left and right core metal projections, the disc-shaped member that engages the engaging recess formed in the crawler belt at predetermined intervals in the circumferential direction The drive claw body projects in the left-right direction, and the end surface of the drive claw body in the left-right direction is formed into a tapered surface that becomes narrower toward the radially outer side.

According to the above configuration, the engaging recess is formed into a tapered surface whose end surface in the belt width direction becomes narrower toward the inner back side, and the driving claw body has a narrower end surface in the left-right direction toward the radially outer side. It is formed on a tapered surface. For this reason, even if the length in the belt width direction of the concave portion for engagement, which is the same direction, and the length in the left-right direction of the drive claw body are the same, the width of the tip of the drive claw body at the time when they start to mesh with each other Since the narrow portion corresponds to the wide portion on the entrance side of the engaging recess, there is a relatively large difference in the same direction dimension at the engagement start location, and the engagement becomes easy.
However, in the engagement completion state in which the driving claw body is completely fitted in the engaging recess, the difference in the same direction dimension is smaller than that at the start of engagement, and the engagement recess and the driving claw body are displaced in the same direction. Stable power transmission in a state where is suppressed is possible. In addition, since it is not necessary to make the length of the engaging recess in the belt width direction extremely larger than the length of the driving claw in the same direction, it is possible to avoid impairing the strength of the crawler belt.

According to another technical means of the present invention, the engagement recess has an interval between a right end surface adjacent to the right core metal projection and a left end surface adjacent to the left core metal protrusion in the belt circumferential direction. It is formed longer than the interval between the end faces at
  In the left and right directions of the disk-shaped member, the drive claw body has a distance between a right end surface projecting rightward from the disk-shaped member and a left end surface projecting leftward from the disk-shaped member. It is formed longer than the interval between the end faces in the circumferential direction.

According to another technical means of the present invention, an inclination angle of a tapered surface, which is an end surface in the left-right direction of the drive claw body, with respect to a horizontal plane is an inclination angle of a tapered surface, which is an end surface in the belt width direction, of the engaging recess. Is set to a larger angle.

According to another technical means of the present invention, the disk-shaped member of the drive sprocket includes a rib portion at an outer peripheral portion on the outer side in the radial direction, and the thickness of the rib portion in the thickness direction of the disk-shaped member is The disk-shaped member is formed to be thicker than the inner portion on the inner side in the radial direction, and narrower than the facing distance between the pair of left and right cored bar protrusions of the crawler belt. .

Another technical means of the present invention includes a plurality of rolling wheels that are juxtaposed in the front and rear inner peripheral surface belt circumferential direction so as to brought into contact with the side of the crawler belt, the front side position of the plurality of rolling wheels And an idler wheel arranged at each of the rear side positions, and a drive sprocket is provided at an intermediate position between the front and rear idler wheels and at an upper side position of the wheel.

According to the above configuration, the drive sprocket at the intermediate position of the front and rear idler wheel, and wherein provided on the upper side position of the rolling wheels, there is an advantage obtained by suitable drive form in the crawler traveling device of a so-called Semikurora type.

Overall side view of tractor Overall side view of crawler traveling device Top view of crawler belt IV-IV sectional view in FIG. Partial cross-sectional view of the crawler belt in the belt circumferential direction Schematic perspective view showing cored bar protrusion Perspective view showing a part of the drive sprocket Side view showing the outer periphery of the drive sprocket IX-IX sectional view in FIG. Arrow view in FIG. Explanatory drawing which shows the relationship between a drive nail | claw body, the recessed part for engagement, and a metal core protrusion. The stopper guide is shown, (a) is a plan view, (b) is a side view, and (c) is a front view. It is explanatory drawing which shows the action state of the related member with respect to a crawler belt, (a) shows a relationship with a drive sprocket, (b) shows a relationship with an idler wheel, (c) shows a relationship with a slip-off prevention guide. Show It is explanatory drawing which shows the proximity | contact regulation state of a slip-off prevention guide and a core metal protrusion, (a) shows a reference | standard attitude | position, (b) shows a maximum proximity | contact attitude | position. Explanatory drawing which shows the contact state of an idler wheel and a crawler belt Explanatory drawing which shows the relationship between a drive nail | claw body, the recessed part for engagement, and a metal core protrusion.

Hereinafter, an example of an embodiment of the present invention will be described based on the drawings.
[Overall structure of tractor]
FIG. 1 shows a semi-crawler type tractor provided with a crawler traveling device 2 according to the present invention on the rear side of the machine body. This semi-crawler type tractor is a four-wheel drive type tractor with a specification change to a semi-crawler type, and includes a pair of left and right front wheels 10 that can be steered at the front of the tractor with a cabin 1 and at the rear of the fuselage. The main propulsion device includes a pair of left and right crawler traveling devices 2. Further, the rear portion of the machine body is configured to connect a tilling device, a harvesting device, or various intermediate management working devices via a three-point link mechanism (not shown).

[Crawler traveling device]
As shown in FIGS. 1 and 2, the crawler traveling apparatus 2 includes a drive spool rocket 3 of larger diameter which is connected to the axle 12 after being provided as a rear-wheel drive to rear transmission case 11 in the tractor the machine 1 ing.
The crawler belt 6 is wound around the drive sprocket 3, the idler wheels 4, 4 provided before and after the track frame 20, and a plurality of rollers 5 arranged in parallel in the longitudinal direction of the track frame 20. Thus, the drive sprocket 3 is provided at an intermediate position between the front and rear idler wheels 4 and 4 and at an upper position of the wheel 5.
The tread in the left-right direction of the crawler traveling device 2 is set to be substantially the same as the tread of the front wheel 10 in order to travel between the fences in the field.

As shown in FIG. 2, three rolling wheels 5 are arranged in parallel in the front-rear direction, and the foremost rolling wheel 5 is attached to a track frame 20 via a fixing bracket 21 in a fixed position.
The two wheels 5 and 5 on the rear side of the balance 5 are pivotally attached to the support bracket 22 attached to the track frame 20 so that the middle part thereof is swingable up and down around the horizontal axis x. The members 23 are arranged at both ends of the member 23 so as to be able to swing the seesaw.

Each of the rollers 5 and the crawler belt 6 maintains a predetermined positional relationship in the width direction of the belt and is provided with anti-separation guides 7 for preventing the crawler belt 6 from being detached from the rollers 5 at two front and rear positions. .
The front-side locking guide 7 is connected to the lower end side of the fixing bracket 21 that fixes and supports the frontmost roller 5, and the rear-side locking guide 7 is the last side of the balance-like member 23. It is continuously provided in a state extending before and after the wheel 5 at the end position.

[Crawler belt]
The crawler belt 6 is configured as shown in FIGS.
The crawler belt 6 has a core body 61 embedded in a belt body 60 formed in an endless belt shape with a rubber material at a constant pitch in the belt circumferential direction, and on the inner peripheral surface side of the belt between the core bars 61. An engaging recess 62 for engaging the driving claw body 31 of the driving sprocket 3 and transmitting power to the crawler belt 6 side is formed.

As shown in FIGS. 5 and 11, the engaging recess 62 is located between the core bars 61 in the belt circumferential direction and is formed longer in the belt width direction than in the belt circumferential direction. The end surfaces 62a on both ends of the engaging recess 62 in the belt width direction are not perpendicular to the horizontal plane when the crawler belt 6 is positioned on the horizontal plane as shown in FIG. And an inclined surface having a predetermined belt inclination angle β (corresponding to an inclination angle with respect to a horizontal plane).
The engaging recesses 62 in which the end surfaces 62a, which are inclined surfaces having the belt inclination angle β, are formed on both end sides in the belt width direction, the end surfaces 62a on the left and right sides (the right end surface and the left end of the engaging recesses). corresponding to the surface) by the inner back side (formed in the tape path over surface to be narrow enough in the drawing downward).

Each cored bar 61 is provided with a pair of left and right cored bar projections 63 for guiding the wheel from the intermediate part in the belt width direction toward the inner peripheral surface of the belt. The idler wheels 4 and 4 are configured to pass through.
In addition, a flat roller raceway surface 64 on which the rolling wheels 5 roll is formed on the inner peripheral surface of the belt main body 60 located at the laterally outer side of each cored bar protrusion 63, and the outer peripheral surface of the belt main body 60. On the side, a propulsion lug 65 thicker than the thickness of the belt main body 60 excluding the cored bar projection 63 is integrally formed at a position overlapping the engaging recess 62 in the belt circumferential direction.

  On the inner peripheral surface side of the belt main body 60 between the core bar 61 and the engagement recess 62, the driving force of the drive claw body 31 of the drive sprocket 3 engaged with the engagement recess 62 is transmitted to the core bar 61. For this purpose, a pressure receiving block 66 is provided. In other words, the rubber pressure receiving block portion 66 is configured to transmit a driving force to the metal core bar 61 while receiving a compression action by the metal driving claw body 31 entering the engaging recess 62. Yes, it is possible to avoid the occurrence of noise by avoiding direct contact between the metal of the driving claw body 31 and the cored bar 61.

  Further, as shown in FIG. 15, the pressure receiving block 66 has an inner peripheral surface of the idler wheel 4 and the inner core 61 in the state where the idler wheel 4 is in contact with the inner peripheral surface of the pressure receiving block 66. Projecting from the inner peripheral surface of the core metal 61 toward the inner peripheral surface of the belt so as to form a predetermined gap S3 for avoiding direct contact between the idler wheel 4 and the core metal 61 between the peripheral surface and the peripheral surface. Formed.

As shown in FIGS. 4 to 6, the metal core protrusion 63 constitutes a belt main body 60 by a metal protrusion 61 a that is integrally formed with a part of the metal core 61 and protrudes toward the inner peripheral surface of the belt. The outer shape is formed substantially in a mountain shape by covering with a mountain-shaped protrusion 67 made of a rubber material.
That is, the core metal protrusion 63 is formed in a mountain shape in a sectional view both in the belt width direction shown in FIG. 4 and in the belt circumferential direction shown in FIG. As shown in FIG. 6, the surface facing the inner side of the core metal protrusion 63 in the belt width direction is formed by an inclined surface that serves as a guide surface C for the idler wheel 4 and the detachment prevention guide 7.
Further, the mountain-shaped cored bar projection 63 is formed in a T shape in a plan view with a top portion 63a of a line along the belt circumferential direction and a line directed inward so as to be orthogonal to the line. The protrusion 67 is formed in a shape in which a recess 63 b is provided at a position located on the inner side in the belt width direction near the top 63 a on the guide surface C.

(Drive sprocket)
The drive sprocket 3 is configured as shown in FIGS. 2 and 7 to 11.
That is, a large-diameter disk-shaped member 30 connected to the rear axle 12 and a drive claw body 31 provided so as to protrude outward in the radial direction from the outer peripheral edge of the disk-shaped member 30 are configured. ing.

  The disk-shaped member 30 includes a hub plate 13 fixed to the rear axle 12 as a drive shaft, and an annular outer peripheral member 14 (corresponding to an outer peripheral side portion) bolted to the outer peripheral side of the hub plate 13. The outer peripheral member 14 is configured by a combination of partial arc-shaped divided arc-shaped members 14a, 14b, and 14c that are equally divided into three in the circumferential direction.

As shown in FIGS. 7 to 10, the outer peripheral member 14 is thicker in the radial direction near the outer peripheral edge 16 than in the vicinity of the mounting portion 15 on the radially inner hub plate 13. In the vicinity of the outer peripheral edge 16, an annular rib portion 32 is formed.
The drive claw body 31 is integrally formed by projecting outward in the radial direction of the outer peripheral edge 16 of the outer peripheral member 14 and projecting outward in the left-right direction from the rib portion 32. It is.

The thickness d1 of the rib portion 32 in the left-right direction is formed to be narrower than the facing distance between the left and right core metal protrusions 63 of the crawler belt 6, and the core metal protrusion 63 and the drive claw body are formed. The correlation is set as follows.
That is, as shown in FIG. 11A, after the end surface 31a in the left-right direction of the drive claw body 31 contacts the end surface 62a of the engagement recess 62, the end surface 62a of the engagement recess 62 is driven by the drive claw body. When the pressing force of 31 is applied and the rib 32 is deformed by a certain amount of compression δ as shown in FIG. 11B, the edge 32 a of the rib portion 32 is formed on the inner end surface 63 c of the core metal protrusion 63. Get in touch.
Thus, after the end surface 31a in the left-right direction of the driving claw body 31 abuts on the end surface 62a of the engaging recess 62 and is elastically deformed to some extent, the rib portion corresponding to the end surface in the left-right direction of the disk-shaped member 30 is obtained. The left and right end edges 32 a of the ribs 32 are in contact with the inner end surface 63 c of the core metal protrusion 63. The position is set.

That is, as shown in FIG. 11A, when a part of the surface where the end surface 31a in the left-right direction of the driving claw body 31 abuts the end surface 62a of the engaging recess 62 is a contact location P1 for convenience, As shown in FIG. 11B, the time lag is generated until the contact point P2 between the end edge 32a of the rib portion 32 and the inner end surface 63c of the cored bar 63 contacts. The relative left-right direction position of the end surface 31a in the left-right direction of the driving claw body 31 and the end edge 32a in the left-right direction of the rib portion 32 is set.
That is, this positional relationship will be described with reference to FIG.
When the center position of the drive claw body 31 in the left-right direction is positioned on the center line CL of the engagement recess 62 in the belt width direction, the end face 31a in the left-right direction of the drive claw body 31 and the engagement recess The contact point P1 with the end surface 62a of 62 and the contact point P2 with the end edge 32a of the rib portion 32 and the surface 63c on the inner end side of the cored bar 63 are in a non-contact state.
At this time, of the contact location P1, the distance LP1-1 from the center line CL to the contact location P1 of the end surface 62a of the engagement recess 62, and the end surface in the left-right direction of the drive claw body 31 from the center line CL. The first gap LP1 exists between the distance LP1-2 to the contact point P1 of 31a.
Further, in the contact location P2, the distance LP2-1 from the center line CL to the contact location P2 of the inner end surface 63c of the cored bar 63, and the edge of the rib portion 32 from the center line CL. A second gap LP2 exists between the distance LP2-2 to the contact point P2 at 32a.
Then, the second gap LP2 is set larger than the first gap LP1 by an amount corresponding to the compression amount δ when the end face 62a of the engaging recess 62 is compressed and deformed by the pressing force of the driving claw body 31. Therefore, as described above, the end surface 62 a of the engaging recess 62 is compressed and deformed by the pressing force of the driving claw body 31, and the end edge 32 a of the rib portion 32 is the surface on the inner end side of the core metal protrusion 63. There is a time lag until the amount of movement necessary to contact 63c is reached.

As shown in FIGS. 7 to 13A, the drive claw body 31 projects in the lateral direction (left-right direction) perpendicular to the plate surface of the disk-shaped member 30, thereby causing the belt width of the engaging recess 62. The length is slightly shorter than the length in the direction, and the length in the left-right direction is approximately the same as the length of both the left and right cored bar protrusions 63.
As shown in FIGS. 9 and 11, the left and right end surfaces 31a of the drive claw body 31 (corresponding to the right end surface and the left end surface of the drive claw body) have the outer edge of the drive claw body 31 on a horizontal plane. In the positioned state, the end surface 31a in the left-right direction is not perpendicular to the horizontal plane, but is formed by an inclined surface having a predetermined claw inclination angle α (corresponding to an inclination angle with respect to the horizontal plane).
End surfaces 31a, which are inclined surfaces having the claw inclination angle α, are formed on both left and right sides of the drive claw body 31, and the drive claw body 31 is located on the outer side in the radial direction by the end surfaces 31a on both the left and right sides. It is formed on a tapered surface that becomes narrow.
The claw inclination angle α is set to the same angle as the belt inclination angle β formed on the end surface 62a in the belt width direction of the engaging recess 62.

A front-facing surface 31b (a surface on the side where the driving force is applied to the crawler belt 6 in the forward direction of the machine body) and a rearward surface 31c (a crawler belt 6 in the backward direction of the machine body) that are positioned forward and backward in the circumferential direction of the drive claw body 31. The surface to which the driving force is applied) is generally in the direction along the normal line from the center of rotation of the disk-shaped member 30, but the circumferential width d2 at the portion (base side) slightly closer to the center of rotation is the center of rotation. The taper surface has a tapered shape that is wider than the circumferential width d3 of the outer portion (nail tip side) away from the taper and is slightly narrower toward the radially outer side of the drive claw body 31.
A partial stealing portion 33 is provided on the end surface 31a of the driving claw body 31 to reduce the weight of the entire disk-shaped member 30.

[Release prevention guide]
The detachment prevention guide 7 is configured as shown in FIGS. 2, 12, 13 (c), and 14.
That is, it is continuously provided on the track frame 20 so as to be positioned between the left and right cored bar projections 63, 63 at the position where the front end wheel 5 and the rear end wheel 5 are provided. The detachment prevention guides 7 connected and fixed to the fixed bracket 21 and the balance-like member 23 connected to the support bracket 22 are the same in the front and rear.

As shown in FIG. 12, the detachment prevention guide 7 is formed in a boat shape as a whole in a side view, and the balance-like member 23 connected to the fixed bracket 21 or the support bracket 22 at two positions on the front and rear sides thereof. There are provided mounting portions 72, 72 having screw holes 71, 71 for connecting and fixing to.
In the mounting posture with respect to the fixed bracket 21 or the balance-like member 23, the position which becomes the lowermost end of the locking guide 7 is a perpendicular line y1 from the rotation center p of the wheel 5 shown in FIG. 2 and FIG. It is a crossing position. The lowermost position of the stopper guide 7 is in a state closest to the inner peripheral surface of the crawler belt 6 between the left and right core metal projections 63, 63. The width L1 in the width direction of the belt at the location intersecting the perpendicular line y1 is the contact at the upper portion of the core metal projection 63 at the location where the center line y2 in the belt circumferential direction of the core metal projection 63 on the crawler belt 6 side exists. It is set to be larger than the lateral width L2 at the location P3.

As shown in FIGS. 12A and 12B, the width L1 of the contact position in the belt lateral width direction of the slip-off preventing guide 7 is a linear portion in the belt circumferential direction (front-rear direction) of the slip-off preventing guide 7. The front and rear ends of the stopper guide 7 are tapered in a plan view as shown in FIG. 12A before and after the linear portion L3. In the side view, as shown in FIG. 12B, the front and rear ends are warped upward.
Further, in the linear portion L3 of the locking guide 7, near the portion intersecting the perpendicular y1, there is an orthogonal lower edge portion 73 orthogonal to the perpendicular y1 as shown in FIG. 12 (b). An orthogonal lower edge range L4 is formed, and among the linear portions L3 before and after that, the front lower edge portion 74 in front of the orthogonal lower edge range L4 is formed in a slightly upward shape, and the orthogonal lower edge The rear lower edge portion 75 behind the range L4 is formed in a slightly rearwardly rising shape.

The reason why the lower edge guide 7 is formed in this way is as follows. That is, as shown in FIG. 2, when it is assumed that all the wheels 5 are located on a flat ground, the front end side and the rear end of the crawler traveling device 2 with respect to the lower tangent line to all the wheels 5. The lower edge of the side idler wheels 4, 4 is located higher. For this reason, the crawler belt 6 is stretched slightly forward on the front side of the frontmost roller 5 and slightly lifted on the rear side of the rearmost roller 5, so that This is to maintain a necessary gap between the lower edge of the stop guide 7 and the inner peripheral surface of the crawler belt 6.
Further, the front end side and the rear end side of the slip prevention guide 7 are formed in a tapered shape in a plan view, as described above, the guiding action by the slip prevention guide 7 having a wide width L1 in the belt lateral width direction is smooth. This is to make it happen. Furthermore, as described above, the front and rear ends of the slip prevention guide 7 are formed in a shape that warps upward in addition to the tapered shape in plan view. This is in order to avoid direct contact.

  The anti-separation guide 7 configured as described above has a reference posture shown in FIG. 14A (all the rollers 5 are in contact with the roller raceway surface 64 and the crawler belt 6 receives an average pressure as a whole. (Traveling posture in the state) is sufficiently between the position that is the lowermost end of the stopper guide 7 and the inner peripheral surface of the crawler belt 6 (the inner peripheral surface of the pressure receiving block portion 66 in this embodiment). The relative height position between the contact surface of the wheel 5 and the lower surface of the slip-off preventing guide 7 is set so as to have a large distance S1.

However, as shown in FIG. 14B, in the maximum proximity posture (running posture in a state where a concentrated thrust force is applied from below some of the wheels 5 by riding on a convex portion or the like), the crawler belt 6 is partially compressed or bent, and the anti-separation guide 7 is in a state of relatively approaching the inner peripheral surface of the crawler belt 6.
However, in the present invention, as described above, the lateral width L1 of the stopper guide 7 is set to be larger than the lateral width L2 in the belt lateral width direction at the contact point P3 at the upper portion of the core metal projection 63 on the crawler belt 6 side. Therefore, as shown in the figure, when the slip prevention guide 7 and the inner peripheral surface of the crawler belt 6 (in this embodiment, the inner peripheral surface of the pressure receiving block portion 66) approach each other, Due to the contact between the contact point P3 and the contact point P3 at the upper part of the core metal protrusion 63, further approach is prevented, and the interval S2 can be secured so as to avoid contact between the two.
That is, the lower edge of the stopper guide 7 is brought into contact with the inner peripheral surface side of the crawler belt 6 by the contact point P3 in the range of the linear portion L3 having the lateral width L1 set to the stopper guide 7. Proximity restricting part A that prevents this is configured.

Note that the contact point P3 with the contact point P3 of the stopper guide 7 in the upper part of the core metal protrusion 63 is the drive in the core metal protrusion 63 shown in FIG. 11B and FIG. The sprocket 3 is set at a position away from the contact point P2 with the contact point P2 at the edge 32a in the left-right direction of the rib portion 32 of the sprocket 3.
This prevents the rubber material covering the outer surface of the cored bar protrusion 63 from coming into contact with both the rib portion 32 of the drive sprocket 3 and the anti-separation guide 7 at the same location, so that the rubber material It is for suppressing that it wears out.

The proximity restricting portion A of the locking guide 7 is a contact portion at the upper portion of the guide surface C of the cored bar projection 63 of both side surfaces B and B having a slanted slope of the locking guide 7. The both side surfaces B, B are slightly inclined from the taper angle formed by the inclination of the guide surfaces C, C of the left and right cored bar projections 63. The inclination angle is set so as to obtain a large taper.
Therefore, even if the locking guide 7 is relatively strong and fits between the left and right cored bar projections 63, 63, the contact area at the proximity restricting portion A is relatively small, and the situation where the locking guide 7 is strongly bitten and is difficult to come off. Easy to avoid.

[Idler wheel]
As shown in FIGS. 2 and 13 (b), the idler wheels 4 and 4 are free to play between the left and right cored bar projections 63 and 63 and in contact with the inner peripheral surface of the crawler belt 6. Rotate.
At this time, the outer peripheral surfaces of the idler wheels 4 and 4 are rotated in contact with the inner peripheral surface side of the pressure receiving block portion 66 of the crawler belt 6 as described above. It can be avoided.
The both side surfaces of the idler wheels 4 and 4 may come into contact with the metal portions of the left and right cored bar protrusions 63 and 63, but at this point, the idler wheels 4 and 4 and the crawler belt 6 are almost relative to each other. Since it rotates without moving, even if the metal parts touch each other, the noise does not become so loud at this point, and the generation of noise can be suppressed.

[Other Embodiment 1]
The proximity restricting portion A is not limited to the one based on the setting of the lateral width L2 of the contact point P3 of the stopper guide 7 with respect to the core metal protrusions 63, 63 as described in the embodiment. In part, a portion that does not contact in the reference posture but contacts with the maximum protruding portion of the cored bar protrusions 63 and 63 in the maximum proximity posture is formed, and the detachment prevention guide 7 further covers the inner circumference of the crawler belt 6. You may comprise so that space | interval S2 may be ensured with the structure which prevented approaching to the surface side.

[Second embodiment]
The stopper guide 7 is not limited to one having two front and rear structures as described in the embodiment. For example, only one of the front and rear is provided, or a long disconnection from the front end side to the rear end side is provided. A stop guide 7 may be provided.

[3 of another embodiment]
In the embodiment, as the proximity restricting portion A of the locking guide 7, the both side surfaces B and B having a tapered shape of the locking guide 7 are connected to the guide surfaces C and C of the left and right metal core protrusions 63. Although the inclination angle is set so that the taper is slightly larger than the angle of the taper formed by the inclination, the present invention is not limited to this, and both sides of the anti-skid guide 7 have a constricted inclination. The taper angle formed by the inclination of the surfaces B and B and the guide surfaces C and C of the left and right cored bar protrusions 63 may be set to the same angle. When the same angle is set in this way, the area near the contact point P3 can be widened to reduce the surface pressure per unit area, which is advantageous in that the degree of wear at the contact point P3 can be reduced. There is.

[4 of another embodiment]
In the above-described embodiment, the claw inclination angle α of the driving claw body 31 is set to the same angle as the belt inclination angle β at the end surface 62a in the belt width direction of the engaging recess 62, but the present invention is not limited to this. The angle α may be set larger than the belt inclination angle β, or vice versa.
Incidentally, when the claw inclination angle α with respect to the horizontal plane is set to be larger than the belt inclination angle β, there are the following advantages.
If comprised in this way, the inclination angle of the taper surface by the side of the drive nail | claw body 31 side is set to the inclination angle with respect to a horizontal surface larger than the inclination angle of the taper surface by the side of the recessed part 62 for engagement. For this reason, when the engagement recess 62 and the drive claw body 31 start to engage with each other, the narrow portion at the tip of the drive claw body 31 corresponds to the wide portion on the entrance side of the engagement recess 62.
Therefore, when the inclination angles of the tapered surfaces of the engaging recess 62 and the drive claw body 31 with respect to the horizontal plane are the same, or the inclination angle on the engagement recess 62 side is the inclination angle on the drive claw body 31 side. The difference between the distance from the center position of the engagement recess 62 in the belt width direction to the taper surface and the distance from the center position of the drive claw body 31 in the same direction to the taper surface are compared with each other. When the engagement starts, the narrow portion at the tip of the drive claw body 31 corresponds to the wide portion on the entrance side of the engagement recess 62, so that a larger difference can be made. The possibility of disengagement from the entrance side of the engaging recess 62 can be reduced and the engagement can be further facilitated.
Further, in this structure, when the end face in the belt width direction on the engagement recess 62 side and the end face in the left-right direction on the drive claw body 31 side contact each other, the surface pressure on the inner back side of the engagement recess 62 is increased. The contact is made in a state where the contact pressure is high and the surface pressure on the entrance side of the engaging recess 62 is low.
Thus, abrasion due to contact with the driving pawl 31 in the engaging recess 62 of the crawler belt, than the inner back side of the engaging recesses 62, and it proceeds slowly at the inlet side. As a result, it is easy to avoid the problem that the wear on the entrance side of the engaging recess 62 progresses faster than the inner depth side, and the drive claw body 31 is easily detached from the engaging recess 62 in the early stage.

The crawler traveling device of the present invention can be used as a propulsion device for various vehicles such as a combine and a construction machine in addition to the tractor shown in the embodiment .

2 Crawler traveling device 3 Drive sprocket
4 idler wheel 5 wheel 6 crawler belt 30 disk-shaped member 31 drive claw body 31a right end surface and left end surface end surface 32 of the drive claw body rib portion
6 0 belt body 61 right end surface of the recess concave portion 62a engaging the metal core 62 engaging and the left end surface 63 Shinkin突electromotive

Claims (5)

The cored bar is embedded in the belt body made of rubber material at a constant pitch in the belt circumferential direction, and a pair of left and right cored bar projections for rolling guides project from the intermediate part in the belt width direction of each cored bar to the belt inner peripheral surface side. A crawler traveling device comprising a crawler belt provided and a drive sprocket that applies rotational power to the crawler belt in the belt circumferential direction,
The core metal protrusion is covered with a rubber material, and an engagement recess is provided on the inner peripheral surface side of the crawler belt to engage with the drive claw of the drive sprocket. The engagement recess is aligned in the belt circumferential direction. Located between the left and right cored bar projections of the cored bar provided, the end surface in the belt width direction is formed into a tapered surface that becomes narrower toward the inner back side,
The drive sprocket is a disk-shaped member that engages in a recess for engagement formed in the crawler belt at predetermined intervals in the circumferential direction on the outer peripheral side of a disk-shaped member fitted between the left and right cored bar protrusions. A crawler traveling device comprising: a drive claw body projecting in the left-right direction, and an end face in the left-right direction of the drive claw body formed on a tapered surface that becomes narrower toward the radially outer side. In the engagement recess, the gap between the right end surface adjacent to the right core metal protrusion and the left end surface adjacent to the left core metal protrusion in the belt width direction is longer than the interval between the end surfaces in the belt circumferential direction. Formed,
In the left and right directions of the disk-shaped member, the drive claw body has a distance between a right end surface projecting rightward from the disk-shaped member and a left end surface projecting leftward from the disk-shaped member. The crawler traveling device according to claim 1, wherein the crawler traveling device is formed longer than a distance between end surfaces in a circumferential direction.   The inclination angle of the taper surface, which is the end surface in the left-right direction of the drive claw body, with respect to the horizontal plane is set to be larger than the inclination angle of the taper surface, which is the end surface in the belt width direction of the engagement recess, with respect to the horizontal plane. The crawler traveling device according to claim 1.   The disk-shaped member of the drive sprocket includes a rib portion at an outer peripheral portion on the outer side in the radial direction, and the thickness of the rib portion in the thickness direction of the disk-shaped member is the radial direction of the disk-shaped member. Any one of Claims 1-3 which are thicker than the inner site | part of an inner side, and are narrower than the opposing space | interval between the said left-right paired core metal protrusions of the said crawler belt. The crawler traveling device according to item.   A plurality of rollers arranged side by side in the belt circumferential direction so as to contact the inner peripheral surface side of the crawler belt, and a front side position and a rear side position of the plurality of wheels are arranged respectively. The crawler traveling device according to any one of claims 1 to 4, further comprising an idler wheel and a drive sprocket provided at an intermediate position between the front and rear idler wheels and at an upper position of the wheel.

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