JP2006055129A - Machinery for plant husbandry - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the finished state of tilled field by decreasing the amount of untilled soil just under a transmission case or thereabout. <P>SOLUTION: The plant husbandry machine is provided with right and left normal rotation shafts 62, 62 placed adjacent to the right and left sides of a transmission case 12 and right and left reverse rotation shafts 63, 63 placed coaxially to the normal rotation shafts and adjacent to the outside of the right and left of the normal rotation shafts. The right and left normal rotation shafts are provided with a plurality of normal rotation tines 121-124 and the right and left reverse rotation shafts are provided with a plurality of reverse rotation tines 131, 132. The power of a power source is transmitted through a power transmission mechanism housed in the transmission case to the right and left normal rotation shafts and the right and left reverse rotation shafts to rotate the normal rotation tines and the reverse rotation tines. The right and left normal rotation shafts are provided with unplowed soil treating tines 125, 126 adjacent to the right and left sides of the transmission case to break up the soil remaining immediately below the transmission case or thereabout. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an improvement technique for a management machine in which a plurality of forward rotation claws and a plurality of reverse rotation claws are arranged and cultivated in the body width direction.

The management machine has a right and left forward rotation shaft and a left and right reverse rotation shaft arranged concentrically, and includes a plurality of forward rotation pawls on the left and right forward rotation shafts, and a tillage equipped with a plurality of reverse rotation claws on the left and right reverse rotation shafts. There is a machine. An example of such a cultivator is a rotary working machine. 2. Description of the Related Art A rotary work machine is provided with a transmission case at the lower part of a power source, and a rotary working part and traveling wheels are provided on the transmission case, and various types are known (for example, see Patent Document 1).
Japanese Examined Patent Publication No. 7-114561 (FIGS. 1, 4, and 9)

A conventional rotary working machine shown in Patent Document 1 will be described with reference to FIG.
FIGS. 9A and 9B are schematic views of a conventional rotary working machine. FIG. 9A shows the configuration of the rotary working machine viewed from the side, and FIG. 9B shows the rotary work of FIG. The structure which looked at the part from the b arrow direction is shown.

  As shown in FIG. 9 (a), a rotary work machine 200 according to the prior art has a transmission case 202 disposed below an engine 201, and the transmission case 202 has a front traveling drive shaft 203 and a rear work drive shaft. 204 is a walking type management machine in which a handle 205 is housed and a handle 205 is extended from the rear part of the transmission case 202 to the rear upper part. The power of the engine 201 can be transmitted to the traveling wheel 206 via the traveling drive shaft 203 and can be transmitted to the rotary working unit 207 via the work driving shaft 204.

  As shown in FIG. 9B, the work drive shaft 204 extends left and right from the rear portion of the transmission case 202 disposed at the center of the machine body, and is connected to the left and right forward rotation shafts adjacent to the left and right sides of the transmission case 202. 301, 301 and left and right reversing shafts 311 and 311 adjacent to the left and right outer sides of these left and right forward rotation shafts 301 and 301. The left and right normal rotation shafts 301 and 301 that rotate in the normal rotation direction R11 include four normal rotation claws 302 to 305, respectively. On the other hand, the left and right reverse rotation shafts 311 and 311 rotating in the reverse rotation direction R12 include four reverse rotation claws 312 to 315, respectively.

  By the way, the rear storage portion 202a of the transmission case 202, that is, the rear storage portion 202a, stores a working power distribution unit for distributing power to the left and right forward claws 302 to 305 and the left and right reverse claws 312 to 315. ing. Naturally, the dimension Wi11 (width dimension Wi11) in the machine width direction of the rear storage part 202a is significantly larger than the width dimension Wi12 in front of the dimension.

For this reason, simply providing the forward rotation claws 302 and 303 with the tip directed toward the transmission case 202 may cause soil to remain without being plowed near the transmission case 202, that is, so-called residual tilling. Therefore, there is room for improvement in order to ensure good finishing characteristics of tillage.
On the other hand, it is conceivable to make the work power distribution unit as small as possible. However, in order to ensure the performance of distributing power, there is a limit to downsizing, and as a result, there is a limit to reducing the width dimension Wi11 of the rear storage portion 202a.

  It is an object of the present invention to provide a technique capable of improving the finishing performance of tillage by reducing the state where soil remains without being plowed in the vicinity of the transmission case, that is, so-called residual plowing.

According to the first aspect of the present invention, the left and right forward rotation shafts adjacent to the left and right sides of the transmission case and the left and right reverse rotation shafts adjacent to the left and right outer sides of the left and right forward rotation shafts are arranged on the same center. The forward rotation shaft is provided with a plurality of forward rotation claws, and the left and right reverse rotation shafts are provided with a plurality of reverse rotation claws, so that the power of the power source is transmitted to the left and right forward rotation shafts via a power transmission mechanism housed in the transmission case. And in the management machine that transmits to the left and right reversing shafts and rotates the normal claw and the reverse claw,
The left and right forward rotation shafts are provided with a residual tillage processing claw for cultivating the soil remaining immediately below the transmission case adjacent to both the left and right sides of the transmission case.

  In the invention according to claim 2, the after-plow processing claw is arranged with a phase shifted immediately after the normal rotation direction with respect to the normal rotation claw with the tip portion directed to the transmission case side among the plurality of normal rotation claws, It is arranged adjacent to the transmission case.

  The invention according to claim 3 is characterized in that all of the reverse rotation claws adjacent to the forward rotation axis among the plurality of reverse rotation claws have their tips directed in the opposite direction to the transmission case side.

In the invention according to claim 1, since the left and right forward rotation shafts are provided with the remaining tillage processing claws in addition to the normal forward rotation claws, and the remaining tilling treatment claws are adjacent to the left and right sides of the transmission case, the transmission case Among them, it is possible to cultivate the soil immediately below the power distribution unit storage portion having a large width dimension that stores the work power distribution unit that distributes the power to the normal rotation claw and the reverse rotation claw.
Therefore, the residual tillage under the transmission case can be further reduced, and as a result, the finishing performance of tillage can be improved. Moreover, since it is possible to deeply cultivate under the transmission case, it is possible to improve the tillability of the management machine.

In the invention according to claim 2, among the plurality of normal rotation claws, with respect to the normal rotation claws whose front end faces the transmission case side, the residual tillage processing claws are arranged with a phase shifted immediately after the normal rotation direction. The plow processing claw is disposed adjacent to the transmission case.
When the forward rotation shaft is rotated forward, the forward rotation claw with the tip portion directed toward the transmission case first hits the soil in the vicinity of the power distribution unit storage portion and applies an impact. As a result, the hit part and the soil in the vicinity thereof crack. An impact is applied to the cracked portion by continuously hitting the plowed nail continuously. As a result, the soil directly under the power distribution unit storage portion can be easily cultivated and crushed by the soil crack entering the machine width center side. Therefore, the remaining tillage under the transmission case can be further reduced, and as a result, the finishing performance of tillage can be further enhanced.

In the invention which concerns on Claim 3, the front-end | tip part of all the reverse rotation claws adjacent to the normal rotation axis | shaft among several reverse rotation claws is made into the reverse direction with respect to the transmission case side.
Since the left and right forward rotation shafts are provided with the remaining tillage processing claws in addition to the normal forward rotation claws, the cultivated soil is easily gathered toward the center of the machine width.
On the other hand, in claim 3, by making the tip portions of all the reverse claws adjacent to the forward rotation shaft in the opposite direction to the transmission case side, the soil cultivated by these reverse claws is removed in the machine width direction. Can be dispersed outward. As a result, the soil gathering toward the machine width center side can be offset by the soil dispersed outward. Therefore, since the cultivated soil does not rise to the center side of the machine width and becomes generally flat, the finishing performance of the tillage can be further enhanced.

  The best mode for carrying out the present invention will be described below with reference to the accompanying drawings. “Front”, “Rear”, “Left”, “Right”, “Up”, “Down” follow the direction seen from the operator, Fr is front, Rr is rear, L is left, R is right , CL indicates the machine width center (machine body center).

FIG. 1 is a left side view of a front rotary working machine according to the present invention. FIG. 2 is a plan view of the front rotary working machine according to the present invention.
As shown in FIG. 1, the front rotary working machine 10 has a transmission case 12 attached to the lower part of the engine 11, and a front work drive shaft 13 and a rear travel drive shaft 14 are rotatably attached to the transmission case 12. A small walking type self-propelled agricultural working machine that drives the rotary working unit 15 and the traveling wheel 16 by the engine 11 by attaching the rotary working unit 15 to the work driving shaft 13 and the traveling wheel 16 to the traveling drive shaft 14. That is, a cultivator (management machine).

As described above, the front rotary working machine 10 (hereinafter, simply referred to as “working machine 10”) has the transmission case 12 also serving as the machine body disposed below the engine 11 and further forwards from the front of the transmission case 12. A travel assisting wheel 22 is attached so as to be vertically adjustable via an extended support mechanism 21, and a handle 23 is extended from the rear part of the transmission case 12 to the rear upper part.
The engine 11 as a power source is a so-called vertical engine in which a crankshaft 11a extends substantially vertically. There are two traveling wheels 16 as shown in FIG.

  In FIG. 1, 24 is an air cleaner, 25 is a fuel tank, 26 is a fuel tank filler cap, 27 is an engine cover that covers the upper side of the engine 11, and 28 is a front part of the transmission case 12 and an upper side of the rotary working unit 15. A fender 29, which is a fuselage guard. In FIG. 2, 31 is a power switch, 32 is a clutch lever, 33 is a shift lever, 34 is a recoil starter knob for manually starting the engine 11, 35 is a throttle lever for the engine 11, and 36 is a differential lock lever. is there.

FIG. 3 is a cross-sectional view of the periphery of the transmission case according to the present invention as viewed from the left side, and shows the right half of the transmission case 12 having a left and right divided structure.
FIG. 4 is a cross-sectional view of the transmission case and the power transmission mechanism according to the present invention as viewed from above, and shows the transmission case 12 and the transmission 40 deployed front and rear.

As shown in FIGS. 3 and 4, the transmission case 12 is a case having a left and right bifurcated structure elongated in the front-rear direction and housing the transmission 40.
The transmission 40 is a power transmission mechanism that transmits the driving force of the engine 11 to the rotary working unit 15 and the traveling wheels 16 (see FIG. 4), and includes a working transmission mechanism 50 and a traveling transmission mechanism 80. Such a transmission 40 includes a vertical input shaft 41 concentric with the crankshaft 11a of the engine 11, a power transmission shaft 42, a counter shaft 43, an intermediate shaft 44, a work drive shaft 13, and a travel drive shaft that are respectively horizontal in the body width direction. 14.

  With respect to the transmission case 12, the work drive shaft 13 at the front part of the case, the counter shaft 43, the power transmission shaft 42 at the middle part of the case, the intermediate shaft 44, and the travel drive shaft 14 at the rear part of the case are arranged in this order from front to back. By arranging them in parallel, these shafts 13, 14, 42 to 44 can be rotatably supported in the transmission case 12 and can be stored together.

  As shown in FIG. 3, the input shaft 41 is connected to the lower end portion of the crankshaft 11 a via a main clutch 45. Power can be transmitted from the input shaft 41 to the power transmission shaft 42 by meshing the drive bevel gear 46 provided at the lower end portion of the input shaft 41 with the driven bevel gear 47 provided on the power transmission shaft 42. The main clutch 45 is turned on and off by operating the clutch lever 32 (see FIG. 2), and has a combination structure of a drum brake and a planetary gear.

  As shown in FIG. 4, the work transmission mechanism 50 is a mechanism that transmits power from the power transmission shaft 42 to the work drive shaft 13, and transmits power from the power transmission shaft 42 to the counter shaft 43 via the work clutch 51. A chain transmission mechanism 52 for transmitting and a rotation direction changing mechanism 70 for transmitting power while changing the rotation direction from the counter shaft 43 to the work drive shaft 13 in the normal direction and the reverse direction.

The chain transmission mechanism 52 includes a drive sprocket 53 attached to the power transmission shaft 42 so as to be relatively rotatable, a driven sprocket 54 attached to the counter shaft 43, and a chain 55 hung between the drive and driven sprockets 53, 54. .
The work clutch 51 is a mechanism for switching on and off between the power transmission shaft 42 and the drive sprocket 53 by operating the shift lever 33 (see FIG. 1).

  The work drive shaft 13 includes a long reverse drive shaft 61 extending horizontally in the machine body width direction, and left and right forward rotation shafts 62 and 62 (indicated by phantom lines) attached to the middle of the reverse drive shaft 61 so as to be relatively rotatable. ) And left and right reverse shafts 63 and 63 (indicated by imaginary lines) attached to the left and right ends of the reverse drive shaft 61. The reverse drive shaft 61 is a solid shaft, and the forward rotation shafts 62 and 62 and the reverse rotation shafts 63 and 63 are cylindrical shafts. The reverse drive shaft 61, the normal rotation shafts 62 and 62, and the reverse rotation shafts 63 and 63 are arranged on the same center (on the work center line Pc). Reference numerals 121 to 125 denote tilling claws of the rotary working unit 15.

  The rotation direction changing mechanism 70 includes a reverse drive sprocket 71 attached to the counter shaft 43, a reverse driven sprocket 72 attached to the reverse drive shaft 61, and a chain 73 hung between the reverse drive and driven sprockets 71, 72. Left and right forward drive gears 74, 74 attached to both ends of the counter shaft 43, and left and right forward drive shafts 74, 62 individually attached to the left and right forward drive shafts 74, 74 so as to mesh with these forward drive gears 74, 74. It consists of diverted driven gears 75, 75.

  On the other hand, the travel drive shaft 14 includes a left axle 17L to which the left traveling wheel 16 is attached and a right axle 17R to which the right traveling wheel 16 is attached. The left axle 17L and the right axle 17R are arranged concentrically with each other (on the travel center line Pd).

  The traveling transmission mechanism 80 is a mechanism that transmits power from the power transmission shaft 42 to the traveling drive shaft 14, and a transmission mechanism 81 that transmits power while switching the transmission from the power transmission shaft 42 to the intermediate shaft 44, and the intermediate shaft 44 includes a differential device 83 (differential gear device 83) that transmits power to the left axle 17L and the right axle 17R via the chain transmission mechanism 82, and a differential lock mechanism 84 that regulates the differential action of the differential device 83. .

  The speed change mechanism 81 is a mechanism capable of switching the forward travel speed to three stages and switching to the reverse travel by operating the shift lever 33 (see FIG. 1). The differential device 83 is a mechanism that absorbs a rotational difference between the left traveling wheel 16 and the right traveling wheel 16 when the work machine 10 turns, and ensures smooth turning performance. The differential lock mechanism 84 is a mechanism that stops the function of the differential device 83 in accordance with the operation of the differential lock lever 36 (see FIG. 1), and as a result, rotates the left axle 17L and the right axle 17R integrally.

  As is clear from the above description, by operating the speed change mechanism 81 and the working clutch 51 with the shift lever 33, (1) both the rotary working portion 15 and the traveling wheels 16, 16 are stopped, and (2) the traveling. The rotary working unit 15 can be switched to the rotating state while the wheels 16 and 16 are moved forward or backward at three stages of traveling speed, and (3) the traveling wheels 16 and 16 are moved forward at two stages of traveling speed.

  Incidentally, as shown in FIG. 4, in the transmission case 12, (1) the front part having the work power distribution unit 77 formed by combining the work drive shaft 13, the counter shaft 43 and the rotation direction changing mechanism 70 is wide. The storage portion is referred to as a front storage portion 91, and (2) a wide rear portion that stores the travel drive shaft 14, the power transmission shaft 42, the intermediate shaft 44, the drive / driven bevel gears 46 and 47, the travel transmission mechanism 80, and the like. The storage portion is referred to as a rear storage portion 92, and (3) a narrow portion through which the chain 55 passes between the front storage portion 91 and the rear storage portion 92 is referred to as an intermediate storage portion 93. The width Wi1 of the front storage portion 91 is about 3 to 4 times larger than the width Wi2 of the intermediate storage portion 93 (Wi1> Wi2). Similarly, the width of the rear storage portion 92 is larger than the width Wi2 of the intermediate storage portion 93.

Here, the arrangement relationship among the work drive shaft 13, the power transmission shaft 42, the counter shaft 43, the intermediate shaft 44, and the travel drive shaft 14 will be described in detail with reference to FIG.
With respect to the power transmission shaft 42, the work drive shaft 13 is in a position lowered to the front lower side. The counter shaft 43 is lower than the power transmission shaft 42 and higher than the work drive shaft 13. As a result, the counter shaft 43 is above the straight line Si1 passing through the power transmission shaft 42 and the work drive shaft 13.
On the other hand, the intermediate shaft 44 is slightly lower than the power transmission shaft 42, and the traveling drive shaft 14 is slightly lower than the intermediate shaft 44. As a result, the power transmission shaft 42, the intermediate shaft 44, and the travel drive shaft 14 are arranged slightly rearwardly, that is, at substantially the same height.

Here, the center line of the power transmission shaft 42 is a drive center line Pa, and the center line of the counter shaft 43 is a counter center line Pb. The center line of the work drive shaft 13 is defined as a work center line Pc, and the center line of the travel drive shaft 14 is defined as a travel center line Pd. Each center line Pa, Pb, Pc, Pd is a horizontal line parallel to each other. The drive center line Pa is orthogonal to a vertical line Pe (engine center Pe) passing through the center of the crankshaft 11a and the center of the input shaft 41.
A horizontal distance from the drive center line Pa to the work center line Pc is defined as a work side distance L11, and a horizontal distance from the drive center line Pa to the travel center line Pd is defined as a travel side distance L12. The work side distance L1 is larger than the travel side distance L2 (L11> L12).

  Since the work drive shaft 13, the counter shaft 43, the power transmission shaft 42, the intermediate shaft 44 and the travel drive shaft 14 are arranged in this manner, the transmission case 12 has a substantially “h” shape in side view as shown in FIG. 3. It can be in the shape presented. That is, the transmission case 12 extends forward and backward on the fuselage width center CL (see FIG. 4), is a case that is long in the front and rear direction and narrow in the vehicle width direction. Is substantially horizontal.

  Further, the transmission case 12 is characterized in that a recess 12b is provided between the counter shaft 43 and the work drive shaft 13 in the case lower surface 12a. More specifically, the recess 12b was formed at the boundary between the first half and the second half. The recess 12b has an arc shape in the front and rear direction.

  FIG. 5 is a sectional view of the work drive shaft and the rotary working part according to the present invention as seen from the front. The left and right forward rotation shafts 62, 62 are arranged adjacent to both the left and right sides of the transmission case 12, while the left and right reverse rotation shafts 63, 63 are adjacent to the left and right forward rotation shafts 62, 62 outside in the left-right direction. Arranged. The forward rotation shafts 62, 62 surround a part of the reverse rotation shafts 63, 63 (machine width center CL side) fitted to the reverse rotation drive shaft 61 so as to be relatively rotatable.

  The rotary working unit 15 includes a plurality of normal rotation claws 121 to 126 provided on the left and right normal rotation shafts 62 and 62 and a plurality of reverse rotation claws 131 and 132 provided on the left and right reverse rotation shafts 63 and 63. The normal claws 121 to 126 and the reverse claws 131 and 132 are tilling claws. The normal rotation claws 121 to 126 and the reverse rotation claws 131 and 132 can be rotated reversely to perform the tilling work. Hereinafter, the rotary working unit 15 will be described in detail.

The rotary working units 15 are arranged in six rows from the first claw group 101 to the sixth claw group 106 in the machine body width direction.
The first claw group 101 is composed of normal rotation claws 121 to 126 attached to the attachment plate 111 of the left inner normal rotation shaft 62. The 2nd nail | claw group 102 consists of the normal rotation nail | claws 121-126 attached to the attachment plate 112 of the normal rotation axis | shaft 62 of the right inner side. The third claw group 103 is composed of reverse rotation claws 131 and 132 attached to the inner attachment plate 113 of the left outer reverse rotation shaft 63. The fourth claw group 104 includes reverse claw 131 and 132 attached to the inner attachment plate 114 of the right outer reverse rotation shaft 63. The fifth claw group 105 includes reverse rotation claws 131 and 132 attached to the outer attachment plate 115 of the left outside reverse rotation shaft 63. The sixth claw group 106 is composed of reverse rotation claws 131 and 132 attached to the outer attachment plate 116 of the right outside reverse rotation shaft 63.
Each of the mounting plates 111 to 116 is a steel plate having a substantially square shape in a side view with the plate surface directed in the body width direction.

  FIGS. 6A and 6B are configuration diagrams of a rotary working unit according to the present invention. (A) is the figure which disassembled and represented the rotary working part 15 seen from the front. (B) is the figure which represented the 1st nail | claw group 101 in (a) seeing from b arrow direction. For easy understanding, the forward rotation shafts 62 and 62 and the reverse rotation shafts 63 and 63 shown in FIG. 5 are omitted.

  The normal rotation claws 121 to 126 are claws that rotate in the direction R1 from the upper front in the forward direction Ru of the work machine 10 (see FIG. 1) toward the ground, that is, in the normal rotation direction R1. The reverse claws 131 and 132 are claws that rotate in the direction R2 from the rear top to the ground in the forward direction Ru, that is, in the reverse direction R2.

  The first claw group 101 is formed as a set by superimposing the bases of the six normal rotation claws 121 to 126 substantially in the form of a cross with respect to the work center line Pc. More specifically, the first claw group 101 includes a first forward claw 121 extending forward from the lower portion of the mounting plate 111 (that is, the forward direction Ru of the work machine 10), and a second positive claw 121 extending rearward from the upper portion of the mounting plate 111. Rolling claw 122, third forward claw 123 extending upward from the front part of the mounting plate 111, fourth forward claw 124 extending downward from the rear part of the mounting plate 111, and fifth extending rearward from the front part of the mounting plate 111. It consists of a combination of a forward rotation claw 125 and a sixth forward rotation claw 126 extending forward and downward from the rear portion of the mounting plate 111.

  The first and second normal rotation claws 121 and 122 are heel claws that are curved in the reverse rotation direction R2 while the distal ends 121a and 122a are curved toward the third claw group 103 side. The third and fourth normal rotation claws 123 and 124 are heel claws that are curved in the reverse rotation direction R2 while the distal end portions 123a and 124a are curved toward the second claw group 102 side. The fifth normal rotation claw 125 is a residual tilling claw arranged with a phase shifted from the third normal rotation claw 123 immediately after the rotation direction (normal rotation direction R1). For example, the fifth forward claw 125 is arranged with the phase shifted by approximately 45 ° in the reverse rotation direction R2 (the direction opposite to the normal rotation direction R1) with respect to the third normal rotation claw 123. The sixth normal rotation claw 126 is a remaining tillage processing claw arranged with a phase shifted immediately after the rotation direction with respect to the fourth normal rotation claw 124. For example, the sixth normal claw 126 is arranged with a phase shifted by approximately 45 ° in the reverse rotation direction R2 with respect to the fourth normal rotation claw 124.

The fifth and sixth forward rotation claws 125 and 126 are heel claws that are curved in the reverse rotation direction R2 while the distal end portions 125a and 126a are curved toward the second claw group 102 side.
Here, the remaining tillage processing claw is a tilling claw that cultivates the soil remaining just below the transmission case 12 (see FIG. 5). Accordingly, the fifth and sixth normal rotation claws 125 and 126 will be appropriately referred to as “residual tillage processing claws 125 and 126”.

Hereinafter, the second nail group 102 to the sixth nail group 106 will be described with reference to the first nail group 101.
The second claw group 102 is a group that is symmetrical with the first claw group 101 and is arranged with a phase shift of about 90 ° in the normal rotation direction R1 with respect to the first claw group 101. That is, the second claw group 102 also has a base set of six normal rotation claws 121 to 126 that are superposed in a substantially cross-shaped manner with the work center line Pc as a reference in the same manner as the first claw group 101.

  The third claw group 103 is a set of two reversing claws 131 and 132 arranged opposite to each other on the basis of the work center line Pc. That is, the third claw group 103 includes a combination of a first reverse claw 131 that extends downward from the front portion of the mounting plate 113 and a second reverse claw 132 that extends upward from the rear portion of the mounting plate 113. The first and second reverse claws 131 and 132 are heel claws that are curved in the forward rotation direction R1 while the distal end portions 131a and 132a are curved toward the fifth claw group 105 side.

  The fourth claw group 104 is a group that is symmetrical to the third claw group 103 and is arranged with a phase shift of about 45 ° in the reverse rotation direction R2 with respect to the third claw group 103. The first and second reverse claws 131 and 132 are heel claws that are curved in the forward rotation direction R1 while the distal end portions 131a and 132a are curved toward the sixth claw group 106 side.

  The fifth claw group 105 is a group that is symmetrical to the third claw group 103 and is arranged with a phase shift of about 90 ° in the reverse rotation direction R2 with respect to the third claw group 103. The first and second reverse claws 131 and 132 are heel claws that are curved in the forward rotation direction R1 while the distal end portions 131a and 132a are curved toward the third claw group 103 side.

  The sixth claw group 106 is a group that is symmetrical with the fourth claw group 104 and is arranged with a phase shift of about 90 ° in the forward rotation direction R1 with respect to the fourth claw group 104. The first and second reverse claws 131 and 132 are heel claws that are curved in the forward rotation direction R1 while the distal end portions 131a and 132a are curved toward the fourth claw group 104 side.

  As described above, the phases of the nail groups 101 to 106 do not match each other. However, matching is optional. As a matter of course, the directions of the forward rotation claws 121 to 126 and the reverse rotation claws 131 and 132 change according to the rotation of the work drive shaft 13 (see FIG. 5).

The nail groups 101 to 106 are summarized as follows.
As shown in FIGS. 5 and 6, the left and right forward rotation shafts 62 and 62 include two remaining tillage processing claws 125 and 126 in addition to the four normal forward rotation claws 121 to 124, respectively.
These residual tilling claws 125 and 126 are adjacent to the left and right sides of the transmission case 12. Further, the remaining tilling claws 125 and 126 are immediately after the forward rotation direction R1 with respect to the forward rotation claws 123 and 124 with the tip ends 123a and 124a facing the transmission case 12 among the plurality of forward rotation claws 121 to 124. They are arranged with a phase shift and are arranged adjacent to the transmission case 12.

  As shown in FIG. 5, when the rotary working unit is viewed from the front, the left and right forward claws 123, 123, 124, 124 facing the transmission case 12 side have the tips 123 a, 123 a, 124 a, 124 a The interval between the tips, that is, the first interval is referred to as Cr1. In addition, in the left and right residual tillage processing claws 125, 125, 126, 126, the interval between the tips of the tip portions 125a, 125a, 126a, 126a, that is, the second interval is referred to as Cr2.

  The first interval Cr <b> 1 is smaller than the width Wi <b> 1 of the front storage portion 91. On the other hand, the remaining tilling claws 125, 125, 126, 126 are biased toward the transmission case 12 (offset configuration) with respect to the normal rotation claws 123, 123, 124, 124. Accordingly, the second interval Cr2 is smaller than the first interval Cr1 and slightly larger than the width Wi2 of the intermediate storage portion 93.

  Among the plurality of reverse claws 131..., 132..., All the reverse claws 131, 131, 132, adjacent to the forward claws 62, 62, that is, the claws of the third and fourth claw groups 103, 104. Reference numeral 132 denotes a tip portion 131a, 131a, 132a, 132a facing in the opposite direction to the transmission case 12 side (left-right direction in FIG. 5).

  The operation of the front rotary working machine 10 (management machine 10) having the above configuration will be described with reference to FIGS. 7A to 7D are first operational views of the front rotary working machine according to the present invention.

As shown in FIG. 7 (a), the left and right forward rotation shafts 62, 62 are provided with normal tillage processing claws 125, 126 in addition to normal forward rotation claws 121-124 (see also FIG. 5). Since the plowing claws 125 and 126 are adjacent to the left and right sides of the transmission case 12, the soil Er in the vicinity of the front storage portion 91 (the power distribution portion storage portion 91) having a large width in the transmission case 12 is plowed. can do.
Therefore, the remaining tillage under the transmission case 12 can be further reduced, and as a result, the finishing performance of tillage can be improved. Moreover, since the bottom of the transmission case 12 can be deeply cultivated, the tillability of the front rotary working machine 10 can be improved.

  Furthermore, in the present invention, as shown in FIG. 7 (a), among the plurality of forward rotation claws 121 to 124, the remaining forward ends of the forward rotation claws 123 and 124 with the distal end portions 123a and 124a facing the transmission case 12 are left. The tilling claws 125 and 126 are arranged with a phase shifted immediately after the normal rotation direction R1, and the tilling claws 125 and 126 are arranged adjacent to the transmission case 12.

  As shown in FIGS. 7A and 7B, when the forward rotation shafts 62 and 62 are rotated forward, the forward rotation claws 123 and 124 having the front end portions 123a and 124a facing the transmission case 12 side are The impact is applied to the soil Er near the front storage portion 91 (power distribution portion storage portion 91). As a result, crack Cra ... enters the hit portion and the soil Er in the vicinity thereof.

As shown in FIG. 7C, an impact is applied to the portion where the cracks Cra. As a result, as shown in FIGS. 7 (a) and 7 (c), when the soil crack Cra ... enters to the machine width center CL side, the soil Er just below the front storage portion 91 is easily cultivated. Can be crushed.
As the forward rotation of the forward rotation shafts 62 and 62 progresses, the state below FIG. 7C proceeds to the state of FIG. 7D, so that the bottom of the transmission case 12 can be deeply plowed.

  In this way, the remaining tillage under the transmission case 12 can be further reduced, and as a result, the finishing performance of tillage can be further enhanced.

FIG. 8 is a second operation diagram of the front rotary working machine according to the present invention and is shown corresponding to FIG.
As shown in FIG. 8, since the left and right forward rotation shafts 62 and 62 are provided with the remaining tillage processing claws 125 and 126 in addition to the normal forward rotation claws 121 to 124, respectively, the cultivated soil Er is machine width. It becomes easy to gather to the center CL side.
On the other hand, in the present invention, among the plurality of reverse rotation claws 131, 132, the tip portions 131a, 132a of all the reverse rotation claws 131, 132 adjacent to the forward rotation shafts 62, 62 are opposite to the transmission case 12 side. By doing so, the soil Er plowed by the reverse claws 131 and 132 can be dispersed to the outside in the machine width direction (left and right direction in FIG. 8). As a result, the soil Er gathering toward the machine width center CL can be offset by the soil Er dispersed outward. Therefore, since the cultivated soil Er is flattened without being raised to the machine width center CL side, the finishing performance of the tillage can be further enhanced.

  In the embodiment of the present invention, the power source is not limited to the engine 11 and may be, for example, an electric motor.

  In the management machine of the present invention, the transmission case 12 is disposed below the power source 11, and the rotary working unit 15 including the forward rotation claws 121 to 124 and the reverse rotation claws 131 and 132 is provided at the front portion of the transmission case 12. This is suitable for a front rotary working machine in which left and right traveling wheels 16 are provided at the rear of the twelve.

It is a left view of the front rotary type work machine (management machine) concerning an invention. It is a top view of the front rotary type work machine concerning the present invention. It is sectional drawing which looked at the transmission case periphery which concerns on this invention from the left side. It is sectional drawing which looked at the transmission case and power transmission mechanism which concern on this invention from the top. It is sectional drawing which looked at the work drive shaft and rotary working part which concern on this invention from the front. It is a block diagram of the rotary working part which concerns on this invention. It is the 1st operation view of the front rotary type working machine concerning the present invention. It is the 2nd operation figure of the front rotary type work machine concerning the present invention. It is a schematic diagram of a conventional rotary working machine.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Management machine (front rotary type working machine), 11 ... Power source (engine), 12 ... Transmission case, 13 ... Work drive shaft, 14 ... Travel drive shaft, 15 ... Rotary working part, 16 ... Traveling wheel, 40 ... Power transmission mechanism (transmission), 42 ... power transmission shaft, 43 ... counter shaft, 62 ... forward rotation shaft, 63 ... reverse rotation shaft, 91 ... power distribution portion storage portion (front storage portion), 121-124 ... forward rotation claw 121a to 124a ... forward rotation claw tip, 125, 126 ... residual tillage processing claw, 125a, 126a ... residual tillage processing claw tip, 131, 132 ... reverse claw, 131a, 132a ... reverse claw tip, Cra ... crack, Er ... soil, R1 ... forward direction, R2 ... reverse direction.

Claims (3)

The left and right forward rotation shafts adjacent to the left and right sides of the transmission case and the left and right forward rotation shafts adjacent to the left and right outer sides of the left and right forward rotation shafts are arranged concentrically, and a plurality of By providing a forward rotation claw and a plurality of reverse rotation claws on the left and right reverse shafts, the power of the power source is transferred to the left and right forward rotation shafts and the left and right reverse rotation shafts via a power transmission mechanism housed in the transmission case. In the management machine that transmits and rotates the forward and reverse claws,
The left and right forward rotation shafts are provided with a residual tilling claw for cultivating soil remaining immediately below the transmission case adjacent to both the left and right sides of the transmission case.   The after-plow processing claw is arranged with a phase shifted immediately after the normal rotation direction with respect to the normal rotation claw with the tip portion facing the transmission case side among the plurality of normal rotation claws and adjacent to the transmission case The management machine according to claim 1, wherein the management machine is arranged as described above. The all reverse rotation claws adjacent to the forward rotation axis among the plurality of reverse rotation claws have their tip portions directed in a direction opposite to the transmission case side. Management machine.

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