Title of Invention

THRESHING APPARATUS

Abstract The invention provides a threshing apparatus of excellent processing capability, which can perform a sufficient threshing process on a threshing material without increasing a load of the threshing process even when the threshing material is fed in a large quantity. This threshing apparatus has a threshing cylinder 16 rotatable about a support shaft 15 for threshing reaped grain culms fed into a threshing chamber 14. The threshing cylinder 16 includes a plurality of rod members 47 extending along the support shaft 15 and arranged at predetermined intervals circumferentially of the threshing cylinder 16, support members 44, 46 mounted on front and rear portions of the support shaft 15 for supporting the rod members 47, and a plurality of threshing teeth 48 arranged at predetermined intervals in a fore and aft direction on each of the rod members 47, and projecting from each rod member 47 outwardly of the threshing cylinder 16 (see Fig. 3).
Full Text

THRESHING APPARATUS
[TECHNICAL FIELD]
This invention is related to a threshing apparatus having a threshing cylinder rotatable about a support shaft for threshing reaped grain culms fed to a threshing chamber.
[BACKGROUND ART]
A conventional threshing cylinder structure of a threshing apparatus as noted above has threshing teeth arranged helically around the outer periphery of a straight cylinder portion of the threshing cylinder (see Patent Document 1, for example).
Another example of threshing cylinder has a plurality of threshing teeth arranged in a bent, V-shaped form on the outer periphery of a cylindrical body (see Patent Document 2, for example).
[Patent Document 1] Japanese Unexamined Patent Publication Hll-266666 (JP-l 1-266666A)
[Patent Document 2] Japanese Unexamined Patent Publication No. 2006-67910 (JP2006-067910A)
[DISCLOSURE OF THE INVENTION] [PROBLEM TO BE SOLVED BY THE INVENTION]
In the above constructions, a large part of the threshing chamber is used as an accommodating space for the threshing cylinder, and only a narrow space remaining circumferentially of the threshing cylinder is used as a space for a threshing process. When a large quantity of reaped grain culms is fed to the threshing chamber to undergo the threshing process in a high-speed operation, for example, the processing space can be saturated. In the case of such saturation, an inconvenience tends to occur that the materials undergoing the threshing process stagnate in the processing space and spill down from a concave without being sufficiently threshed. An increased load of the threshing process resulting from the stagnation can cause damage to a transmission system or the like for driving the threshing cvlinder.

The object of this invention is to provide a threshing apparatus having a threshing cylinder structure of excellent processing capability, which can perform a sufficient threshing process on threshing materials without increasing a load of the threshing process even when the threshing materials are fed in a large quantity.
[MEANS FOR SOLVING THE PROBLEM]
In order to fulfill the above object, this invention provides a threshing apparatus having a threshing cylinder rotatable about a support shaft for threshing reaped grain culms fed into a threshing chamber, characterized in that the threshing cylinder includes a plurality of rod members extending along the support shaft and arranged at predetermined intervals circumferentially of the threshing cylinder, support members mounted on front and rear portions of the support shaft for supporting the rod members, and a plurality of threshing teeth arranged at predetermined intervals in a fore and aft direction on each of the rod members, said threshing teeth projecting from each of the rod members outwardly of the threshing cylinder.
With this characteristic construction, the threshing cylinder has an interior space in communication with the threshing chamber, to allow entry of processed materials to the interior space. As a result, in time of rotation of the threshing cylinder, while agitating the processed materials around the cylinder and those present in the interior space, the materials are threshed by impact and combing action of the plurality of rod members and threshing teeth.
Thus, even when a large quantity of reaped grain culms is fed into the threshing chamber to be processed, the interior space of the threshing cylinder can be used effectively as space for the threshing process. This can avoid stagnation of the processed materials in the processing space and saturation of the processing space. As a result, it is possible to preclude a possibility of such inconveniences as the processed materials falling from a concave without being sufficiently threshed, or an increased threshing load damaging a transmission system of the threshing cylinder, which are due to stagnation of the processed materials in the processing space or saturation of the processing space.

Moreover, by arranging a plurality of rod members at predetermined intervals circumferentially of the threshing cylinder, it is possible to prevent long culms from entwining the rod members, and avoid stagnation of the processed materials due to the entwining. In time of rotation of the threshing cylinder, not only the plurality of threshing teeth but the rod members forming a cylindrical portion of the threshing cylinder function as threshing members to strike and comb the processed materials. This realizes an improvement in threshing performance.
In addition to the above constr ction, the threshing cylinder may further include a partition member dividing the interior space thereof into a forward portion and a rearward portion. This provides the following further advantages.
With the partition member, discrete grains obtained from the threshing process in the forward portion of the threshing cylinder and grain-bearing culms having entered the interior space of the threshing cylinder in an early stage of the threshing process are inhibited from moving downstream in the direction of threshing process. With rotation of the threshing cylinder, the discrete grains and grain-bearing culms are guided to the periphery of the threshing cylinder. This prevents creation of a tertiary loss due to the discrete grains and unthreshed grain culms passing straight through the interior space of the threshing cylinder, to be discharged along with grain-stripped culms from an end downstream in the direction of threshing process.
Thus, even when a large quantity of materials is fed to be threshed, the materials can be threshed sufficiently without increasing the load of the threshing process, and generation of a tertiary loss is prevented. Thus, while avoiding damage to a threshing cylinder transmission system due to an increased load, it is possible to achieve improvement in threshing performance and grain collecting efficiency. As a result, the threshing cylinder structure of the threshing apparatus provided is excellent in durability and processing capability.
In addition, a winnowing fan may be provided for generating a sorting air current, the sortins air current beine directed from the wirmowins fan toward the partition member. This provides the following further

advantages.
With this construction, the materials to be threshed stopped by the partition member can be winnowed toward areas around the partition member (i.e. around threshing cylinder) by the sorting air current from the winnowing fan. With rotation of the threshing cylinder, the materials will move from around the partition member downstream in the direction of threshing process. This precludes the possibility of the materials to be threshed accumulating in a location immediately upstream of the partition member.
Thus, lowering of the processing capability due to accumulation of the processed materials can be prevented.
In one preferred embodiment, the threshing cylinder has an upper portion thereof covered by a top board, the top board having a plurality of feeding vanes for guiding the reaped grain culms downstream in the direction of threshing process with rotation of the threshing cylinder.
With this characteristic construction, the reaped grain culms are transported upward in the threshing chamber by rotation of the threshing cylinder, while undergoing threshing action in form of numerous impacts and combing by the plurality of threshing teeth. Having reached the upper part of the threshing chamber, the grain culms are guided downstream in the direction of threshing process by the plurality of feeding vanes.
That is, the materials under the threshing process may be transported downstream in the direction of threshing process while sufficiently securing desired threshing action in form of numerous impacts and combing applied to the materials by the plurality of threshing teeth attached to the threshing cylinder.
The threshing teeth may formed to have guide portions for guiding, with rotation of the threshing cylinder, the materials downstream in the direction of threshing process, for example. Then, the materials may be transported downstream in the direction of threshing process with increased effect. Altematively, the threshing teeth may formed to have a shape suited solely for threshing purposes, i.e. for striking and combing the processed materials. Then, the materials may be threshed with increased effect.
Thus, a whole culm discharging type combine-harvester is provided

to have the feeding vanes playing the main role in transporting the materials downstream in the direction of threshing process, whereby improvement is made in threshing performance and grain collecting efficiency without impairing performance for transporting the processed materials downstream in the direction of threshing process.
The feeding vanes may be formed to have a length extending between right and left side edges of the top board. Then, the feeding vanes have a sufficient length on the top board. As a result, the feeding vanes can guide and transport the processed materials downstream in the direction of threshing process with increased effect. Thus, while improving threshing performance and grain collecting efficiency by the plurality of threshing teeth, improvement is made in the performance for transporting the processed materials downstream in the direction of threshing process.
The top board may be curved to follow substantially revolving loci described by tip ends of the threshing teeth with rotation of the threshing cylinder. Then, the processed materials transported by rotation of the threshing cylinder to the upper part of the threshing chamber may be guided to move along the top board and feeding vanes, and downward and downstream in the direction of threshing process. Thus, while improving threshing performance and grain collecting efficiency by the plurality of threshing teeth, improvement is made in the performance for transporting the processed materials downstream in the direction of threshing process, and in addition, damage to grains by collision with the top board can be avoided.
In one preferred embodiment, the threshing cylinder further includes helical blades disposed at a front end thereof for raking in and transporting rearward, with rotation of the threshing cylinder, reaped grain culms fed toward the front end, the helical blades being detachably attached to the front end.
With this characteristic construction, when one of the helical blades is remarkably wom through a long period of intense contact with reaped grain culms and the like, only this helical blade can be changed. The trouble and cost of changing the helical blades are significantly reduced, compared with the case of the helical blades being undetachably attached, such as by welding, to the front end of the threshing cylinder. As a result,

worn helical blades can be changed easily. With worn helical blades changeable with ease, it becomes easy to avoid such an inconvenience that the rake-in and transport action of the helical blades on the reaped grain culms weakens as is the case where nothing is done to wom helical blades, and the weakened action will lower the threshing capability.
Thus, by making the simple improvement of detachably attaching the helical blades to the front end of the threshing cylinder, an appropriate step can be taken against wear of the helical blades simply and at low cost. It is possible as a result to avoid lowering the threshing capability due to wear of the helical blades.
In addition to the above construction, a transport aiding guide may be disposed below the threshing cylinder for covering the front end from below, and for receiving the reaped grain culms fed toward the front end and aiding the helical blades in raking in and transporting the reaped grain culms, the transport aiding guide having, as a detachable part, at least a portion located downstream in a direction of rotation of the threshing cylinder. When the transport aiding guide is remarkably wom through a long period of intense contact with reaped grain culms and the like, only a wom portion of the transport aiding guide can be changed. The trouble and cost of changing the wom transport aiding guide are significantly reduced, compared with the case of the transport aiding guide being undetachably attached, such as by welding, to a support frame or the like. As a result, the wom transport aiding guide can be changed easily. With the wom transport aiding guide changeable with ease, it becomes easy to avoid such an inconvenience that the rake-in and transport action of the helical blades on the reaped grain culms weakens due to a large gap formed between the helical blades and transport aiding guide as is the case where nothing is done to the wom transport aiding guide, and the weakened action will lower the threshing capability.
The reaped grain culms raked in and transported rearward by the helical blades, under the influence of rotation of the threshing cylinder, collect in a portion of the transport aiding guide downstream in the direction of rotation of the threshing cylinder. Consequently, the portion of the transport aiding guide the more downstream in the direction of rotation of the

threshing cylinder is the more intensely contacted by the reaped grain culms to become wom the more easily through the contact.
By taking this point into account, the portion of the transport aiding guide downstream in the direction of rotation of the threshing cylinder may be made detachable. Then, when the portion of the transport aiding guide downstream in the direction of rotation of the threshing cylinder is remarkably wom through a long period of intense contact with the reaped grain culms and the like, only the wom portion of the transport aiding guide can be changed. The cost of changing can be further reduced than the case of changing the whole transport aiding guide.
Thus, by making the simple improvement of detachably attaching at least a portion of the transport aiding guide downstream in the direction of rotation of the threshing cylinder, an appropriate step can be taken against wear of the transport aiding guide simply and at low cost. It is possible as a result to avoid with ease lowering the threshing capability due to wear of the transport aiding guide.
In one preferred embodiment, the threshing cylinder is covered by a concave from below, and by a top board from above, joint members being detachably mounted between the concave and the top board, and formed to define guide surfaces serving as smooth and continuous cormection between inner surfaces of the concave and the top board.
With this characteristic constmction, when the guide surface of one of the joint members is remarkably wom through a long period of intense contact with reaped grain culms and the like, only this wom joint member can be changed. The trouble and cost of changing wom joint members are significantly reduced, compared with the case of the joint members being undetachably attached, such as by welding, to the concave or top board. As a result, wom joint members can be changed easily. With wom joint members changeable with ease, it becomes easy to avoid such an inconvenience that the inner surface of the concave and the inner surface of the top board cannot be connected continuously by the guide surfaces of the joint members, as is the case where nothing is done to wom joint members, so that the reaped grain culms and the like cannot move smoothly between the concave and top board of the threshing cylinder. This will lower the

threshing capability
Thus, by making the simple improvement of detachably mounting the joint members between the concave and the top board, an appropriate step can be taken against wear of the joint members simply and at low cost. It is possible as a result to avoid with ease lowering the threshing capability due to wear of the joint memers.
Other features and advantages resulting therefrom may be apparent from the following description to be taken with reference to the accompanying drawings.
[BRIEF DESCRIPTION OF THE DRAWINGS]
[Fig. 1] Side elevation of a whole culm discharging type combine-harvester
[Fig. 2] Plan view of the whole culm discharging type combine-harvester
[Fig. 3] Side view in vertical section of a threshing apparatus
[Fig. 4] Front view, partly in section, showing the construction of a front end portion of the threshing apparatus
[Fig. 5] Front view, partly in section, showing the construction of a middle portion in the fore and aft direction of the threshing apparatus
[Fig. 6] Plan view of a principal portion showing the constructions of a threshing cylinder and a transport aiding guide
[Fig. 7] Plan view in cross section of a principal portion showing the construction of the threshing cylinder
[Fig. 8] Sectional view of a principal portion showing a mounting structure of a helical blade
[Fig. 9] Rear view in vertical section of the threshing cylinder
[Fig. 10] Plan view in cross section of a principal part showing a modified construction of the threshing cylinder
[Fig. 11] Front view in vertical section of a principal part showing the construction of a joint member
[Fig. 12] Plan view in cross section of a principal part showing the length and position of feeding vanes
[Fig. 13] Plan view, of a principal portion showing the construction

of a transport aiding guide
[Fig. 14] Side view in vertical section of the principal portion
showing the construction of the transport aiding guide
[Fig. 15] Perspective view of a principal portion showing the
construction of a concave
[Fig. 16] Perspective view of a principal portion showing the
construction of a chaff sieve
[Fig. 17] Front view in vertical section of a transmission case [Fig. 18] Side view, partly in section, of the transmission case [Fig. 19] Explanatory view of operation of a breather apparatus [Fig. 20] Exploded perspective view showing an outline of the
breather apparatus
[BEST MODE FOR CARRYING OUT THE INVENTION]
Fig. 1 shows a side elevation of a whole culm discharging type combine-harvester for harvesting rice, wheat and the like. Fig. 2 shows a plan view of the combine-harvester. As shown in these figures, the whole culm discharging type combine-harvester includes a body frame 1 formed of square steel pipe and having an engine 2, a change speed device (not shown) and so on mounted on a right forward portion thereof. A pair of, right and left, crawler type propelling devices 3 are arranged under the body frame 1 to be driven by power transmitted from the engine 2 through the change speed device. A reaping and transporting implement 4 is vertically swingably connected to the front of the body frame 1 for reaping standing grain culms to be harvested, and transporting the grain culms rearward. A threshing apparatus 5 is mounted on the left half of the body frame 1 for threshing the reaped grain culms received from the reaping and transporting implement 4, and sorting the object obtained by the threshing process. A bagging apparatus 6 is mounted on the right half of the body frame 1 for storing grains received from the threshing apparatus 5, and allowing the stored grain to be bagged. A driving platform 7 is formed on a right forward portion of the body frame 1.
The right and left crawler type propelling devices 3 are switchable between a straight traveling state in which the propelling devices 3 are driven

at an equal speed, and a turning state in which the propelling devices 3 are driven differentially. This switching is made by a steering system (not shown) operable in response to right and left rocking of a control lever 8 of the cross rocking and neutral return type provided on the driving platform 7.
The reaping and transporting implement 4 has dividers 9 arranged at right and left sides of the front end thereof for combing and dividing standing grain culms into those to be harvested and those not to be harvested. The reaping and transporting implement 4 has a rotation reel 10 mounted on an upper front part thereof for raking rearward tip parts of the standing grain culms divided, by the right and left dividers 9, into those to be harvested. A cutting mechanism 11 is disposed at the bottom of the reaping and transporting implement 4 for cutting foot parts of the standing grain culms to be harvested. An auger 12 is disposed rearward of the cutting mechanism 11 for gathering the grain culms cut by the cutting mechanism 11 (i.e. reaped grain culms) to a predetermined location in the transverse direction, and feeding the grain culms rearward from the predetermined location. In the predetermined location of the auger 12, a feeder 13 in the form of a transporting conveyer is provided for feeding the reaped grain culms from the predetermined location toward the threshing apparatus 5.
The reaping and transporting implement 4 is vertically swingable about a connection point between the body frame 1 and feeder 13 by a hydraulic lift cylinder (not shown) extending between the body frame 1 and feeder 13. The lift cylinder is controlled by switching states of a control valve (not shown) which controls the flow of a hydraulic fluid to the lift cylinder, based on fore and aft rocking of the control lever 8. That is, by rocking the control lever 8 in the fore and aft direction, the reaping and transporting implement 4 may be raised and lowered to change a height of the cutting mechanism 11 relative to the standing grain culms, thereby to effect a reaping height adjustment.
As shown in Figs. 3 to 5, the threshing apparatus 5 has a threshing chamber 14 formed in an upper portion thereof. The threshing chamber 14 houses a threshing cylinder 16 rotatable about a support shaft 15 extending fore and aft along the transport direction of reaped grain culms. The threshing cylinder 16 has a lower portion thereof covered from below by a

concave 17 U-shaped in front view. The concave 17 receives the reaped grain culms threshed by rotation of the threshing cylinder 16, and allows the materials obtained by the threshing process to fall therethrough. The threshing apparatus 5 has a culm discharge opening 18 formed rearwardly of the concave 17, at a downstream end in the direction of threshing process, for discharging the grain culms after the threshing process. An oscillatory sorting mechanism 19 is disposed below the concave 17 for sifting and sorting the processed materials falling through the concave 17. A winnowing fan 20 is disposed forwardly of and below the oscillatory sorting mechanism 19 for supplying currents of sorting air toward the processed materials falling through the concave 17 or the processed materials undergoing the sifting process to winnow the processed materials. A primary collector 21 is formed rearwardly of the winnowing fan 20 for collecting materials passing through and falling from a forward region of the oscillatory sorting mechanism 19. A secondary collector 22 is formed rearwardly of the primary collector 21 for collecting materials passing through and falling from a rearward region of the oscillatory sorting mechanism 19. A discharge opening 23 is formed rearwardly of the oscillatory sorting mechanism 19 for discharging materials transported to the rear end of the oscillatory sorting mechanism 19 instead of passing through and falling from the oscillatory sorting mechanism 19. An openable top board 24 is disposed above the threshing cylinder 16 for covering an upper portion of the cylinder 16, and guiding, toward the concave 17, reaped grain culms and threshed materials transported upward by rotation of the threshing cylinder 16.
The threshing chamber 14 is partitioned by the concave 17, top board 24 and so on covering the threshing cylinder 16. A feed opening 25 is formed in a position below the forward end of the threshing chamber 14 for receiving an entire quantity of reaped grain culms transported by the feeder 13.
The threshing cylinder 16 has the support shaft 15 rotatably extending between a front wall 26 and a rear wall 27 of the threshing apparatus 5. The threshing cylinder 16 is rotatable about the support shaft 15 clockwise in front view by the power transmitted from the engine 2

through the winnowing fan 20. By this rotation, the reaped grain culms fed into the threshing chamber 14 are threshed to promote separation of individual grains from the culms. At the same time, the reaped grain culms are transported rearward, i.e. downstream in the direction of threshing process.
The concave 17 is in the form of a lattice to receive the reaped grain culms fed into the threshing chamber 14 and assist, in the threshing process of the reaped grain culms by the threshing cylinder 16. Specifically, the concave 17 catches the reaped grain culms undergoing the threshing process by rotation of the threshing cylinder 16, and allows discrete grains and eared grains obtained from the threshing process and materials such as waste culms resulting from the threshing process to fall toward the oscillatory sorting mechanism 19, but prevents grain-stripped culms from falling to the oscillatory sorting mechanism 19.
The oscillatory sorting mechanism 19 has a sieve case 29 frame-like in plan view and oscillatable fore and aft by a cam-type drive mechanism 28. The sieve case 29 has a grain pan 30, a chaff sieve 31 and a straw rack 32 for rough sorting arranged in the stated order from front to rear in an upper portion of the sieve case 29. In a lower portion of the sieve case 29, a grain pan 33 and a grain sieve 34 for fine sorting are arranged in order from front to rear. In the upper portion of the oscillatory sorting mechanism 19, the upper grain pan 30, chaff sieve 31 and straw rack 32 receive materials falling through the concave 17 as a mixture of discrete grains, waste culms and so on, and carry out a rough sorting process by sifting selection. In the lower part of the oscillatory sorting mechanism 19, the lower grain pan 33 and grain sieve 34 receive materials falling from the chaff sieve 31 as a mixture of discrete grains, eared grains and so on, and carry out a fine sorting process by sifting selection. As a result, the materials are sorted out into discrete grains as primary product, a mixture of eared grains, waste culms and so on as secondary product, and dust such as waste culms as tertiary product.
The winnowing fan 20 is rotatable about a support shaft 20A thereof by the power transmitted from the engine 2 through a drive mechanism 35 of the belt type, to generate currents of sorting air. The sorting air currents pass through three air passages R1-R3, to be directed toward the materials

falling through the concave 17 to be sorted, and the materials to be sorted by the oscillatory sorting mechanism 19. Thus, waste culms and the like having low specific gravity are winnowed from the materials, and transported toward the discharge opening 23 located downstream in the direction of threshing process.
The primary collector 21 collects, as first product, discrete grains falling from the grain sieve 34 of the oscillatory sorting mechanism 19, with dust such as waste straw separated out by the sorting air currents from the winnowing fan 20. The primary collector 21 has a primary screw 36 disposed at the bottom thereof and extending in the transverse direction, to be driven by the power transmitted from the engine 2 through the winnowing fan 20. The primary screw 36 transports the primary product collected by the primary collector 21 toward an elevating screw 37 linked to the right end thereof (Fig. 2).
The secondary collector 22 collects, as secondary product, a mixture of eared grains, waste culms and so on falling over the rear end of the grain sieve 34 instead of passing down through the grain sieve 34, and a mixture of eared grains, waste culms and so on passing down through the straw rack 32 of the oscillatory sorting mechanism 19. The secondary collector 22 has a secondary screw 38 disposed at the bottom thereof and extending in the transverse direction, to be driven by the power transmitted from the engine 2 through the winnowing fan 20, The secondary screw 38 transports the secondary product collected by the secondary collector 22 toward a secondary retum mechanism 39 linked to the right end thereof (Fig. 2).
The elevating screw 37 elevates the primary product transported by the primary screw 36, and feeds it into a grain tank 40 disposed in an upper portion of the bagging apparatus 6 (see Figs. 1 and 2), The secondary retum mechanism 39 includes a reprocessor (not shown) for carrying out a threshing process again on the secondary product transported by the secondary screw 38, and elevates and retums the secondary product after the threshing process by the reprocessor to the oscillatory sorting mechanism 19 (see Figs. 2 and 3).
The discharge opening 23 discharges grain-stripped culms flowing down the culm discharge opening 18 instead of passing down through the

concave 17, and waste culms and so on selectively transported rearwardly of the oscillatory sorting mechanism 19 through the sifting process and wind selection process.
As shown in Figs. 3 to 9, the threshing cylinder 16 includes an intake portion 41 in the shape of a truncated cone and forming the forward end, and a threshing portion 42 continuous with the rear end of the intake portion 41. The intake portion 41 has two helical blades 43 attached to the outer peripheral surface thereof. With rotation of the threshing cylinder 16, the helical blades 43 take in the reaped grain culms fed into the feed opening 25 by the feeder 13, and transports the grain culms toward the threshing portion 42.
The threshing portion 42 includes a first plate (an example of support members) 44 integral with a front part of the support shaft 15, a second plate (an example of partition members) 45 integral with a fore and aft intermediate part of the support shaft 15, a third plate (an example of support members) 46 integral with a rear end of the pivot shaft 15, six threshing cylinder frames (an example of rod members) 47 in the form of round steel pipes supported by the plates 44-46 to extend fore and aft along the support shaft 15 and at predetermined intervals circumferentially of the threshing cylinder 16, and a plurality of threshing teeth 48 arranged on each threshing cylinder frame 47 at predetermined intervals in the fore and aft direction, and projecting from the threshing cylinder frame 47 outwardly of the threshing cylinder 16.
That is, the threshing cylinder 16 has a plurality of threshing teeth 48 arranged in order at predetermined intervals circumferentially and longitudinally of the threshing portion 42. The threshing cylinder 16 has an interior space S of the threshing portion 42 in communication with the threshing chamber 14, to allow entry of the processed materials to the interior space S. As a result, in time of rotation of the threshing cylinder 16, while agitating the processed materials around the cylinder 16 and those present in the interior space S. the materials are threshed by impact and combing action of the threshing cylinder frames 47 and threshing teeth 48.
Moreover, with the interior space S of the threshing portion 42 communicating with the threshing chamber 14, even when a large quantity of

reaped grain culms is fed into the threshing chamber 14 to be processed, the interior space S of the threshing portion 42 can be used effectively as space for the threshing process. This can avoid stagnation of the processed materials in the processing space and saturation of the processing space. As a resulty it is possible to preclude a possibility of such inconveniences as the processed materials falling through the concave 17 without being sufficiently threshed, or an increased threshing load damaging the transmission system for the threshing cylinder 16, which are due to stagnation of the processed materials in the processing space or saturation of the processing space.
In time of rotation of the threshing cylinder 16, not only the plurality of threshing teeth 48 but the six threshing cylinder frames 47 forming the threshing portion 42 of the threshing cylinder 16 function as threshing members to act on the processed materials. This realizes an improvement in threshing performance and threshing efficiency.
As a result of threshing process in a forward region of the threshing cylinder 16, a large quantity of grains becomes discrete grains to fall from the concave 17, thereby reducing the quantity of materials to be processed in a fore and aft intermediate region of the threshing cylinder 16. In the fore and aft intermediate region, the second plate 45 dividing the interior space S of the threshing cylinder 16 into forward and rearward parts prevents the processed materials in the interior space S of the threshing cylinder 16 from moving downstream in the direction of threshing process and, with rotation of the threshing cylinder 16, guides the processed materials to the periphery of the threshing cylinder 16, This promotes threshing of the processed materials by impact and combing action of the threshing teeth 48, and falling of discrete grains through the concave 17. As a result, discrete grains and unthreshed grain culms included in the processed materials have little chance of passing straight through the interior space S of the threshing cylinder 16, to be discharged along with grain-stripped culms through the culm discharge opening 18 formed downstream in the direction of threshing process. This prevents creation of a tertiary loss.
Further, in time of rotation of the threshing cylinder 16, ambient air drawn in through the feed opening 25 by rotation of the helical blades 43, along with reaped grain culms taken in and transported by' action of the

intake portion 41, flows smoothly to areas around the threshing cylinder 16 and into the interior space S of the threshing portion 42. This prevents outflow from the feed opening 25 to the feeder 13 of waste culms and the like produced by the threshing process, and transport the processed materials downstream in the direction of threshing process.
Moreover, the ambient air drawn in through the feed opening 25 passes beforehand along the interior of the feeder 13 connected to the feed opening 25. The feeder 13 communicates the feed opening 25 with a grain culm outlet port (not shown) formed in a reaping and collecting portion of the reaping and transporting implement 4 having the cutting mechanism 11 and auger 12. Therefore, in time of rotation of the threshing cylinder 16, the sucking action of the helical blades 43 in rotation causes dust such as waste culms generated by the reaping process and collecting process in the reaping and collecting portion to flow, along with the ambient air, from the outlet port of the reaping and collecting portion through the interior space of the feeder 13 and feed opening 25 into the areas around the threshing cylinder 16 and the interior space S of the threshing portion 42. As a result, waste culms and the like are restrained from adhering to, depositing on, or scattering up from the reaping and collecting portion. This inhibits trouble in transporting reaped grain culms due to such adhesion and deposition, and inhibits worsening of working environment and field of view by the scattering up of waste matter.
Each of the plates 44-46 is shaped circular about the support shaft 15, with the threshing cylinder frames 47 connected by bolts to peripheral positions thereof at an equal distance from the support shaft 15. That is, the six threshing cylinder frames 47 are arranged at fixed intervals circumferentially of the plates 44"46 to increase the diameter of the threshing cylinder 16. This arrangement can prevent the reaped grain culms from twining around the threshing cylinder 16.
Each threshing cylinder frame 47 is bolted to the plates 44-46 in a normal position having its fore and aft direction coinciding with the fore and aft direction of the threshing cylinder 16, or in a reversed position having its fore and aft direction opposite to the fore and aft direction of the threshing cylinder 16, and to have its fore and aft direction opposite to the fore and aft

direction of adjoining threshing cylinder frames 47.
Each threshing cylinder frame 47 has a plurality of mounting bores 47A and 47B arranged at constant intervals P in the fore and aft direction for attaching the threshing teeth 48. A difference of a half interval (= 1/2P) is provided between a distance LI from the forward end of the threshing cylinder frame 47 to the center of a foremost mounting bore 47A and a distance L2 from the rear end of the threshing cylinder frame 47 to the center of a rearmost mounting bore 47A.
Each threshing cylinder frame 47 is connected to and supported by the plates 44-46 to have its fore and aft direction opposite to the fore and aft direction of adjoining threshing cylinder frames 47. Thus, while the six threshing cylinder frames 47 have the same construction, the threshing teeth 48 attached to each threshing cylinder frame 47 can be staggered by a half interval in the fore and aft direction with respect to the threshing teeth 48 of the adjoining threshing cylinder frames 47. As a result, intervals between impacts on the processed materials by the threshing teeth 48 can be reduced without reducing the intervals between adjacent threshing teeth 48,
That is, the threshing performance is improved by increasing the number of times the threshing teeth 48 strike the processed materials. This can be realized while achieving a cost reduction by using the threshing cylinder frames 47 of the same construction, and while effectively avoiding jamming of the processed materials due to the grain culms in the processed materials entwining the threshing teeth 48, which is the more likely to occur the smaller the intervals are between adjacent threshing teeth 48.
Each threshing cylinder frame 47 is reversible between the normal position and reversed position as noted above. The threshing teeth 48 located upstream in the direction of threshing process tend to wear relatively quickly because of a heavy processing load. When wear of such threshing teeth has become conspicuous through long period of use, the direction of each threshing cylinder frame 47 may be changed. The plurality of threshing teeth 48 on each threshing cylinder frame 47 can be positionally changed all at once, swapping the threshing teeth 48 located upstream in the direction threshing process, which are relatively easily worn., with those located downstream in the direction threshing process, which do not easily

wear. In this way, the less worn threshing teeth 48 located downstream in the direction of threshing process can be used effectively as threshing teeth 48 upstream in the direction of threshing process for processing large quantities of materials.
Among the plurality of mounting bores 47A and 47B, four mounting bores 47A located in opposite, forward and rearward end regions (two in each region) of each threshing cylinder frame 47 are formed to have a smaller diameter than the intermediate mounting bores 47B.
Among the threshing teeth 48, each of the threshing teeth 48A attached to the mounting bores 47A of small diameter is formed of a round steel bar stepped to defme a small diameter portion 48a inserted through the mounting bore 47A and detachably fixed by a nut to the threshing cylinder frame 47. Each threshing tooth 48A has its axis passing through the axis of the support shaft 15 and the axis of the threshing cylinder frame 47.
Each of the threshing teeth 48B attached to the intermediate mounting bores 47B is formed of a round steel bar without a step, and is undetachably welded to the threshing cylinder frame 47. Each threshing tooth 48B has its axis passing through the axis of the support shaft 15 and the axis of the threshing cylinder frame 47.
That is, each of the threshing teeth 48A located in the opposite, forward and rearward end regions of the threshing portion 42 is attachable and detachable. These threshing teeth 48A, when remarkably worn through a long period of use including direction changes of the threshing cylinder frames 47, may easily be replaced with new threshing teeth 48A.
In a region downstream in the direction of threshing process having a large quantity of grain-stripped culms, as modified and shown in Fig. 10, the threshing teeth 48A located in the rear end region of the threshing cylinder 16 may be thinned out to enlarge the intervals between the threshing teeth 48A in that region. This effectively inhibits stagnation of the grain-stripped culms being caught by the threshing teeth 48A in the rear end region of the threshing cylinder 16. As a result, discharge of the grain-stripped culms from the culm discharge opening 18 can be promoted.
As shown in Figs. 3-5, 11 (a) and (b) and 12, the top board 24

includes, as integral parts thereof, a curved portion 24A curved to follow substantially revolving loci K of tip ends of the threshing teeth 48, semicircular vertical walls 24B located at opposite, forward and rearward ends of the curved portion 24A, and linear side edges 24C disposed at right and left sides of the curved portion 24A. The top board 24 is pivotable about a plurality of hinges 24D arranged along the left side edge 24C, between a closed position covering the upper part of the threshing cylinder 16 from above, and an open position revealing the upper part of the threshing cylinder 16. A plurality of bolts 24E are arranged along the right side edge 24C for fixing the top board 24 to the closed position.
The curved portion 24A is formed with an inner surface thereof serving to guide, smoothly downward toward the concave 17, processed materials transported by rotation of the threshing cylinder 16 to the areas above the threshing cylinder 16. A plurality of feeding vanes 49 are detachably fixed, as arranged at predetermined intervals in the fore and aft direction, to the inner surface of the curved portion 24A for guiding downstream in the direction of threshing process the processed materials transported by rotation of the threshing cylinder 16 to the areas above the threshing cylinder 16. Among the plurality of feeding vanes 49, the foremost feeding vane 49A is formed arcuate to extend from the front vertical wall 24B to the left side edge 24C. The other feeding vanes 49B are formed arcuate to extend between the right and left side edges 24C.
That is, with the top board 24 having the curved portion 24A, the processed materials transported to upper areas in the threshing chamber 14 as raked up by the plurality of threshing teeth 48 with rotation of the threshing cylinder 16 may be guided smoothly along the inner surface and feeding vanes 49 of the curved portion 24A toward the concave 17 below and downstream in the direction of threshing process. Each feeding vane 49 formed elongate and arcuate to extend to the left side edge 24C or between the right and left side edges 24C has an improved and effective action for guiding the processed materials transported to the upper areas in the threshing chamber 14 with rotation of the threshing cylinder 16. Thus, the processed materials may be guided and transported effectively downstream in the direction of threshing process, while allowing each threshing tooth 48

to be shaped exclusively for threshing purposes to be suitable for striking and raking up the processed materials, instead of being shaped to perform a transporting function. As a result, improvement is achieved in the threshing performance and transporting perfonnance for the processed materials.
The right and left side edges 24C have, detachably connected by bolts thereto, joint members 50 formed of steel plate and curved to define guide surfaces 50a serving as smooth and continuous connection between the inner surface of the curved portion 24A and the inner surface of the concave 17. In this way, the joint members 50 are detachably attached to joints between the concave 17 and top board 24 to undergo intense contact with the processed materials. When one of these joint members 50 is remarkably wom through contact with the processed materials, only this joint member 50 can be changed easily. That is, wear of the joint members 50 can be dealt with appropriately without involving the trouble and economic disadvantage of changing the entire top board 24 with wom joint members 50 as where, for example, the joint members 50 are undetachably welded to the top board 24.
A small clearance is set between the tip end of each threshing tooth
48 and the lower edge of each feeding vane 49 in order that the feeding vane
49 effectively guides the processed materials. A larger clearance than the clearance between the tip end of each threshing tooth 48 and the lower edge of each feeding vane 49 is set between the tip end of each threshing tooth 48 and the inner surface of the concave 17 in order to promote falling of discrete grains through the concave 17.
As shown in Figs. 3, 4, 6-8 and 10, two support plates 41A are welded in helical form to the peripheral surface of the intake portion 41 of the threshing cylinder 16, The helical blades 43 are detachably connected by bolts to rear surfaces of these support plates 41 A, each to have an outer edge protruding from the outer edge of the corresponding support plate 41 A,
That is, the threshing cylinder 16 has, detachably mounted on the intake portion 41 thereof, two helical blades 43 for raking in and transporting rearward, with rotation of the threshing cylinder 16, reaped grain culms fed to the feed opening 25 by the feeder 13. Thus, the helical blades 43 can

easily wear through intense contact with the reaped grain culms. When each helical blade 43 is remarkably worn through a long period of use, only this helical blade 43 can be changed easily. As a result, wear of the helical blades 43 can be dealt with appropriately without involving the trouble and economic disadvantage of changing the intake portion 41 together with wom helical blades 43 as where, for example, the helical blades 43 are undetachably w^elded to the intake portion 41.
Each support plate 41A is reinforced with a plurality of reinforcing ribs 4IB welded to extend between the front surface thereof and peripheral surface of the intake portion 41.
As shown in Figs. 3, 4, 6, 13 and 14, the threshing apparatus 5 includes a transport aiding guide 51 disposed between the front wall 26 and concave 17 for receiving reaped grain culms fed to the feed opening 25 by the feeder 13, and aiding the raking and transporting action of the two helical blades 43. The transport aiding guide 51 is formed of a pair of left and right guide members 51A and 5 IB connected by bolts to be U-shaped to cover the intake portion 41 from below. The left and right guide members 51A and 5 IB have first stainless steel plates 51a detachably bolted to the front wall 26 of the threshing apparatus 5 and to a pair of left and right support fi"ames 52 arranged in upper parts of the threshing apparatus 5 to extend fore and aft, and second stainless steel plates 51b welded to the first plates 51a and defining guide surfaces extending from the front wall 26 to the concave 17 of the threshing apparatus 5.
That is, this threshing apparatus 5 has the transport aiding guide 51 detachably attached for aiding the raking in and transport of the reaped grain culms by the two helical blades 43. Thus, the transport aiding guide 51 can easily wear through intense contact with the reaped grain culms. The transport aiding guide 51 has a split construction dividable left and right into the left guide member 51A located upstream in the direction of rotation of the threshing cylinder 16, and the right guide member 5 IB located downstream in the direction of rotation of the threshing cylinder 16. When the transport aiding guide 51 is remarkably wom through a long period of use, only the transport aiding guide 51 can be changed easily. When one of

the left and right guide members 51A or 5 IB of the transport aiding guide 51 is remarkably wom through a long period of use, only the guide member 51A or 5 IB remarkably wom can be changed easily. As a result, wear of the transport aiding guide 51 can be dealt with appropriately without involving the trouble and economic disadvantage of changing the concave 17 or left and right support frames 52 with the transport aiding guide 51 as where, for example, the transport aiding guide 51 is undetachably welded to the concave 17 or left and right support frames 52, or changing the entire transport aiding guide 51 even if only one of the left and right guide members 51A or 5 IB is remarkably wom as where the transport aiding guide 51 is constmcted not to be dividable.
Moreover, since the transport aiding guide 51 is formed of stainless steel resistant to corrosion and highly strong, the frequency of change due to wear can be reduced.
As shown in Figs. 3, 5, 6 and 15, the concave 17 is formed of four concave members 53 of the same shape, and is detachably connected by bolts to the left and right support frames 52. Each concave member 53 has a base frame 53A formed rectangular. The base frame 53A has a plurality of longitudinal pieces 53B in the form of beltlike steel plates extending fore and aft and arranged at fixed intervals circumferentially of the threshing cylinder 16. A plurality of first crosspieces 53C in the form of beltlike steel plates curved to be arcuate extend right and left and are arranged at predetermined intervals in the fore and aft direction axially of the threshing cylinder 16. Further, a plurality of second crosspieces 53D in the form of piano wire rods curved to be arcuate extend right and left and are arranged at predetermined intervals in the fore and aft direction between adjoining first crosspieces 53C. The intervals between the pieces 53B-53D are set to define rectangular meshes within the base frame 53A such that the meshes are transversely elongated, i.e. longer circumferentially of the threshing cylinder 16 than in the fore and aft direction.
That is, by taking into account that, in time of threshing process with the threshing cylinder 16 rotated, discrete grains obtained from the threshing process of reaped grain culms flow in the direction of rotation of the

threshing cylinder 16, the concave 17 is constructed to have rectangular meshes elongated in the direction of rotation of the threshing cylinder 16. This construction allows the discrete grains and the like to fall easily through a forward portion of the concave 17, compared with the case where the concave 17 has rectangular meshes elongated in the direction of threshine process by the threshing cylinder 16 (i.e. in the fore and aft direction). It is possible as a result to effectively restrain generation of hulled grains due to inhibition of discrete grains falling through the forward portion of the concave 17. The concave members 53 of the same shape enable an improvement in productivity and assembling efficiency of the concave 17.
As shown in Figs. 3 and 16, the chaff sieve 31 for rough sorting comprises a single sorting plate 54 detachably connected by bolts to the sieve case 29 in an inclined posture lying progressively upward as it extends downstream in the sorting direction.
The sorting plate 54 has, in a forward region thereof (i.e. a forward region corresponding to about one third of the total area of the sorting plate 54), a plurality of spill bores 54A shaped rectangular in plan view and arranged zigzag such that the bores 54A in one row are located between the bores 54 A in the next row. In a rearward region of the sorting plate 54 (i.e. a rearward region corresponding to about two thirds of the total area of the sorting plate 54), a plurality of spill bores 54B and 54C shaped rectangular in plan view and having sorting pieces 54a and 54b are arranged zigzag such that the bores 54B and 54C in one row are located between the bores 54B and 54C in the next row.
Among the sorting pieces 54a and 54b, the sorting pieces 54a located in a transversely intermediate region of the sorting plate 54 are punched out in shape of scales tapered upward and downstream in the sorting direction. The sorting pieces 54b located at transversely opposite ends of the sorting plate 54 are punched out in a rectangular shape shorter than the sorting pieces 54a in the transversely intermediate region and extending upward and downstream in the sorting direction.
The chaff sieve 31 for rough sorting in the form of the single sorting plate 54 simplifies its construction at reduced cost, compared wdth the case

where, for example, the chaff sieve 31 has numerous chaff lips foraied of belt-like steel plates and arranged at fixed intervals in the fore and aft direction.
Since the spill bores 54A having no sorting pieces 54a or 54b are formed in the forward region of the chaff sieve 31 which receives processed materials with a high rate of content of discrete grains, a large quantity of discrete grains falls through the forward region of the chaff sieve 31 to the grain pan 33 and grain sieve 34 below. This raises the collecting rate of discrete grains in the primary collector 21 located below the grain pan 33 and grain sieve 34.
Since the spill bores 54B and 54C having the sorting pieces 54a and 54b are arranged zigzag all over the rearward region of the chaff sieve 31, the processed materials on the chaff sieve 31 are distributed uniform, without moving to either side, in the transverse direction in the sifting and sorting process. This promotes falling f the discrete grains through the spill bores 54B and 54C.
With the chaff sieve 31 inclined to extend upward and rearward, the chaff sieve 31 imparts a strong force to drive the processed material upward and upstream in the direction of sorting process during the sifting and sorting process, compared with the case where the chaff sieve 31 is installed in horizontal posture. This restricts transport of the processed material dovmstream in the direction of sorting process during the sifting and sorting process, and intensifies the up-and-down motion of the processed materials, thereby carrying out a specific gravity difference sorting of the processed materials with increased effect. This promotes falling through the spill bores 54B and 54C of grains with high specific gravity, and effectively restricts a tertiary loss due to the discrete grains being discharged through the discharge opening 23. This improves grain collecting efficiency.
Moreover, the sorting pieces 54b at the right and left ends of the chaff sieve 31 formed shorter than the sorting pieces 54a in the transversely intermediate region can promote falling of the grains through the spill bores 54C at the right and left end regions of the chaff sieve 31 where the processed materials tend to deposit. This checks lowering of sorting efficiency due to deposition of the processed materials in the right and left

end regions of the chaff sieve 31.
The ratio between the spill bores 54A having no sorting pieces 54a or 54b and the spill bores 54B and 54C having the sorting pieces 54a and 54b, formed in the chaff sieve 31, may be varied according to the type of grains to be sorted, for example.
The sorting plate 54 may have, in the forward region thereof, a plurality of spill bores 54C shaped rectangular in plan view and having short rectangular sorting pieces 54b. These spill bores 54C may be arranged zigzag such that the bores 54C in one row are located between the bores 54C in the next row.
With reference back to Fig. 3 showing various sorting air currents from the winnowing fan 20, the air current passing through the passage Rl in the upper stage flows through a passage R4 formed in the sieve case 29, toward the second plate 45 of the threshing cylinder 16. This constitutes an air transport whereby the processed materials prevented by the second plate 45 from moving downstream in the direction of threshing process may be blown to peripheral areas of the threshing cylinder 16. It is possible as a result to preclude the possibility of the processed materials accumulating in a location immediately upstream of the second plate 45 to obstruct the threshing process.
As shown in Figs. 3 and 6, the threshing cylinder 16 has threshing teeth 48A located at the rear end thereof, which are located further rearward than the rear end of the concave 17, to face the culm discharge opening 18. In the absence of the concave 17, a relatively large space is formed around the rear end of the threshing cylinder 16. Thus, grain-stripped culms entwining the threshing teeth 48 at the rear end of the threshing cylinder 16, if any, are releasable from the tip ends of the threshing teeth 48 by the centrifugal force produced by rotation of the threshing cylinder 16. As a result, stagnation of the grain-stripped culms as caught by the threshing teeth 48 at the rear end of the threshing cylinder 16 is effectively inhibited, to promote discharge of the grain-stripped culms through the culm discharge opening 18.

Next, a split case of a transmission case and a breather apparatus provided therefor will be described with reference to Figs. 17 to 20.
[Overall Construction of Split Case]
Fig. 17 shows a transmission case 101 for use in the whole culm discharging type combine-han-ester, as an example of split cases where the breather apparatus of this invention is applied.
The transmission case 101 comprises a combination of a pair of right and left split case units 102. The split case units 102 are connected together by bolts with a packing 103 interposed between mating surfaces 120 in a location of division shown in a parting line y in Fig. 17.
This transmission case 101 has, connected to and supported by an upper portion thereof, a hydrostatic stepless transmission (HST) 105 having a different case. A lower portion of the transmission case 101 is supported by axles 106.
The hydrostatic stepless transmission 105 is supported by an upper end of the transmission case 101, with an input shaft 150 integral with a pump drive shaft inserted through a support portion 121 projecting upward from' one of the right and left split case units 102. The input shaft 150 has a belt pulley 151 mounted thereon for receiving propelling power transmitted by a belt from an engine (not shown) as divided from power for working.
An output shaft 152 integral with a motor shaft of the hydrostatic stepless transmission 105 is inserted into the upper portion of the transmission case 101. Thus, power having undergone a change speed by the hydrostatic stepless transmission 105 is inputted to a change speed mechanism in the transmission case 101. The power transmitted from the hydrostatic stepless transmission 105 is put to gear change speed into two, high and low speeds by an auxiliary change speed mechanism 113 acting as the change speed mechanism mounted in the transmission case 101. Then, the power is transmitted as divided through right and left side clutches 114 to the right and left axles 106, to be outputted to right and left crawler type propelling devices 3.
An outline of the change speed mechanism mounted in the transmission case 101 is as shown in Figs. 17 and 18.

That is, the transmission case 101 supports a first shaft 161, a counter shaft 162, a second shaft 163 and the pair of right and left axles 106. The auxillary change speed mechanism 113 is arranged on the first shaft 161 and counter shaft 162 to be shiftable to provide two, high and low speeds.
The first shaft 161 has a shift gear SG splined thereto and integrating a small diameter gear G3 and a large diameter gear G4.
The counter shaft 162 has a center gear CG loosely mounted on a middle portion thereof, and integrating a large diameter change speed gear G5 for meshing with the small diameter gear G3 and a small diameter change speed gear G6 for meshing with the large diameter gear G4.
The shift gear SG is slidable rightward in Fig. 17 to mesh the small diameter gear G3 with the large diameter change speed gear G5 to provide a "low speed". The shift gear SG is slidable leftward in Fig. 17 to mesh the large diameter gear G4 with the small diameter change speed gear G6 to provide a "high speed". The shift gear SG may be placed in a middle position out of mesh with the center gear CG to provide "neutral".
A parking brake PB is provided in one of the support positions for the first shaft 161 having the shift gear SG. This parking brake PB prevents rotation of the shift gear SG to lock a downstream part of power transmission.
The counter shaft 162 has, axially slidably mounted in right and left positions thereof, clutch gears G7 forming the side clutches 114. The clutch gears G7 are meshed with a pair of output gears G8 loosely mounted on the second shaft 163.
The clutch gears G7 are slidable inward to mesh with an inner gear G9 formed in the center of the center gear CG to produce a "clutching" state. The clutch gears G7 are slidable outward to be out of mesh with the inner gear G9 to produce a "declutching" state. Normally, the clutch gears G7 are biased in the direction of "clutching" state by springs 168 mounted on the counter shaft 162. The clutch gears G7 have a large width for constantly meshing with the output gears G8 whether in the "clutching" state or "declutchina" state.
Each output gear G8 is integrally connected to an intermediate small diameter gear GIG loosely mounted on the second shaft 163. Each

intermediate small diameter 2ear G10 is meshed with a reduction gear Gil of large diameter fixed to an inward end of each axle 106. Thus, power taken from the output gears G8 is transmitted at reduced speed to the right and left axles 106.
Side brakes SB are mounted adjacent right and left ends of the counter shaft 162 to act on the clutch gears G7. Each side brake SB is a multi-plate friction brake including friction plates 175 engaged with the outer periphery of a boss portion 169, and friction plates 177 engaged with the inner periphery of a fixed bearing case 176, the friction plates 175 and friction plates 177 being altemately arranged in the axial direction. When each clutch gear G7 is slid outward beyond a "declutching" position, an operating plate 171 presses on the friction plates 175 and 177 to apply a friction brake to the clutch gear 07.
[Construction of Breather Apparatus]
In an upper location of the transmission case 101 housing the change speed mechanism described above, the breather apparatus 104 is provided as explained in Fig. 19 and outlined in Fig. 20.
By using an empty space occurring between upper outer walls 122 of the right and left split case units 102 and the transmission members present adjacent thereto (i.e. the output shaft 152, first shaft 161 and the gears arranged around the shafts), partitions 123 are provided for forming extension chambers 140 with the outer walls 122.
The extension chambers 140 in the respective split case units 102 are surrounded by the partitions 123 to define a small chamber open adjacent the mating surfaces 120 of the transmission case 101, and closed in other locations with respect to an oil storage space 110 in the transmission case 101 where the above change speed mechanism and so on are immersed in lubricating oil.
The extension chambers 140 in the respective split case units 102 are divided right and left by the packing 103 disposed in the mating surfaces 120 of the transmission case 101. One of these chambers, i.e. a first extension chamber 140a, has a small communication port 141 for aeration cut in a bottom thereof adjacent the matins surfaces 120. The other, second

extension chamber 140b formed in the other split case unit 102 opposite across the packing 103 has a sideways discharge tube acting as a breather port 142 for communication with ambient air.
The packing 103 disposed between the two extension chambers 140a and 140b has a communicating bore 130 formed adjacent the outer walls 120 of transmission case 101 for permitting aeration from the first extension chamber 140a communicating with the oil storage space 110 to the second extension chamber 140b having the breather port 142.
That is, the breather apparatus 104 is constructed by using the extension chambers 140a and 140b provided in the right and left split case units 102, and the packing 103 disposed between the two extension chambers 140a and 140b.
The breather apparatus 104 constructed in this way can supply and discharge air as indicated by arrows in Fig. 19.
In more particular, when the pressure of gas in the oil storage space 110 below is increased by a rise in oil temperature or an inclination of the vehicle body, gas is forced into the upper, first extension chamber 140a through the small communication port 141.
At this time, in the upper, first extension chamber 140a, decompression occurs in the space of larger capacity than the small communication port 141. It is thus possible to remove a certain amount of oil from the incoming gas, and retum it through the small communication port 141 to the oil storage space 110.
When the intemal pressure of the first extension chamber 140a increases, the gas will flow into the opposite, second extension chamber 140b through the communicating bore 130 of packing 103. The gas is decompressed again in the large space to reduce its oil content, and then flows out through the breather port 142.
Although the second extension chamber 140b has no passage formed therein for retuming the oil produced by gas/liquid separation to the oil storage space 110, there is very little possibility of a large quantity of oil remaining in the second extension chamber 140b since a large part of oil is already removed in the first extension chamber 140a.
If a large quantity of oil should remain in the second extension

chamber 140b, the breather port 142 may be opened to apply suction from outside to draw the oil. Altematively, the cases may be disassembled as part of maintenance of the transmission case 101, to get rid of the oil.
The discharge tube providing the breather port 142 has, connected thereto, a breather pipe 143 curved to extend upward and then downward in a semicircular form. The breather pipe 143 curved in this way is connected in order to prevent entry of water from outside to the transmission case 101 in time of washing the vehicle body.
As described above, the breather apparatus 104 is provided for the transmission case 101 of the split type formed by joining the plurality of split case units 102 at the mating surfaces 120. Each of the split case units 102 at opposite sides of the mating surfaces 120 has a small extension chamber 140 (140a or 140b) formed integrally therewith and opening adjacent the mating surface 120. One of the extension chambers 140a defines a small communication port 141 in communication with the oil storage space 110 within the split case. The other extension chamber 140b has a breather port 142. The packing 103 is interposed between the mating surfaces 120, to divide the extension chambers 140a and 140b at the mating surfaces 120, and has a communicating bore 130 formed for permitting aeration from the first extension chamber 140a communicating with the oil storage space 110 to the second extension chamber 140b having the breather port 142.
According to the above construction, when constmcting the transmission case 101 of the split type, the extension chambers 140 (140a and 140b) may only be formed inside as integral parts thereof Then, the breather apparatus 104 may be provided by using the packing 103 which is certainly mounted between the mating surfaces 120.
Thus, the breather apparatus can be constructed to have a labyrinth structure or extension chambers without requiring special, additional components. This breather apparatus can achieve a simple construction and a cost reduction.
The extension chambers 140 (140a and 140b) are formed in a space between the upper outer walls 122 of the right and left split case units 102 and the transmission members present adjacent thereto (i.e. the output shaft

152, first shaft 161 and the gears arranged around the shafts)
According to the above construction, the extension chambers 140 (140a and 140b) are formed by using an empty space between the upper outer walls 122 of the right and left split case units 102 and the transmission members present adjacent thereto. Thus, the highly efficient breather apparatus 104 can be formed compact without requiring changes in the shape and size of the whole transmission case 101.
[Other Embodiments]
While a threshing apparatus in one preferred embodiment of this invention has been described referring to the drawings, this invention is not limited to the construction in this embodiment. Various modifications can be made as set out below, for example:
[1] The threshing apparatus may be mounted on a culm head discharging type combine-harvester which feeds only heads of culms are fed into the threshing chamber 14, instead of the whole culm discharging type combine-harvester illustrated,
[2] The threshing cylinder 16 may not be provided with the intake portion 41. The intake portion 41 may have straightening teeth or threshing teeth 48 instead of the helical teeth 43.
[3] The threshing cylinder 16 may have, as the threshing cylinder frames (rod members) 47, round steel rods, square steel rods, square steel pipes, angle bars, or channel bars.
[4] The threshing cylinder 16 may have a varied number of threshing cylinder frames (rod members) 47, e.g. eight threshing cylinder frames 47.
[5] The threshing cylinder 16 may have a plurality of threshing cylinder frames (rod members) 47 fixed to the plates 44-46 not to be reversible.
[6] All the threshing teeth 48 on the rod members 47 may be welded to the rod members 47, or may be detachably connected to the rod members 47 by bolts.
[7] All or part of the threshing teeth 48 on the rod members 47 may be in the form of blades having guide surfaces for guiding, with rotation of

the threshing cylinder 16, processed materials downstream in the direction of threshing process. Or such blades may be bent into an L-shape so that tip ends thereof act as guides for guiding, with rotation of the threshing cylinder 16, processed materials downstream in the direction of threshing process.
[8] The threshing teeth 48 may be formed of square steel rods or round pipes, or may be bent into a U-shape or V-shape.
[9] Various modifications are possible for the arranging intervals of the threshing teeth 48. Where, for example, the number of threshing cylinder frames (rod members) 47 is a multiple of 3 (three), the threshing teeth 48 may be shifted by 1/3 intervals in the fore and aft direction with respect to the threshing teeth 48 mounted on a next threshing cylinder frame (rod member) 47. Where the number of threshing cylinder frames (rod members) 47 is a multiple of 4 (four), the threshing teeth 48 may be shifted by 1/4 intervals in the fore and aft direction with respect to the threshing teeth 48 mounted on a next threshing cylinder frame (rod member) 47. The arranging intervals of the threshing teeth 48 may be varied for the forward region and rearward region such that, for example, the threshing teeth 48 are arranged at larger fore and aft intervals in the rearward region than in the forward region.
[10] Various modifications are possible for the construction, shape and number of partition member(s) 45. For example, the partition member 45 may be formed of a circular porous plate. The partition member may have a plurality of rod-like extension members extending from the support shaft 15 to the respective rod members 47, and an annular connecting member connecting distal ends of the extension members. Further, the partition member 45 may be shaped conical to have outer peripheries thereof located downstream in the direction of threshing process, to have a function to guide the processed materials to areas peripherally of the threshing cylinder 16. A plurality of partition members may be provided for the threshing cylinder 16 instead of the illustrated, single partition member 45.
[11] An air current generator (e.g. a further winnowing fan) may be provided exclusively for generating an air current flowing toward the partition member 45 from upstream in the direction of threshing process.
[12] All or part of the feeding vanes 49 attached to the top board 24

may be formed short not to extend to one of the right and left side edges or to extend to neither of the side edges 24C of the top board 24.
[13] The feeding vanes 49 may be constructed movable to adjust the degree of opening according to the quantity of materials undergoing the threshing process in the threshing chamber 14, to improve the threshing perfonnance or threshing efficiency further.
[14] The top board 24 may have the curved portion 24A curved to follow the revolving loci K described by the tip ends of the threshing teeth 48. The curved portion 24A may be replaced with a bent portion bent to cover the upper portion of the threshing cylinder 16 from above.
[15] The threshing cylinder 16 may have a threshing portion 42 of the drum type including a cylindrical barrel, two screws mounted peripherally of the barrel to be continuous with the two helical blades 43 of the intake portion 41, and numerous threshing teeth detachably attached at predetermined intervals to outer peripheries of the screws to project outward therefrom.
[16] The threshing cylinder 16 may have a single helical blade 43, or three or more helical blades 43, attached to the peripheral surface of the forward end 41 thereof.
[17] The threshing cylinder 16 may have a plurality of support metal fittings arranged helically on the peripheral surface of the forward end 41 for detachably attaching the helical blades 43.
[18] Each helical blade 43 may be formed of a plurality of blade-like members arranged helically on the peripheral surface of the forward end 41 of the threshing cylinder 16.
[19] The transport aiding guide 51 may constructed dividable right and left, or may be dividable into three or more parts.
[20] The transport aiding guide 51 may have, as a detachable part, only the member 5 IB located downstream in the direction of rotation of the threshing cylinder 16.
[21] As a material for forming the transport aiding guide 51, a steel material such as carbon steel may be employed instead of stainless steel.
[22] The joint members 50 may be detachably attached to the concave 17.

[23] In the foregoing embodiment the extension chambers 140 are formed in a space between the upper outer walls of split case units 102 and the transmission members present adjacent thereto. This is not limitative. The extension chambers may be formed in any appropriate location above an intended level of the oil surface in the oil storage space 110.
[24] The small communication port 141 formed in the first extension chamber 140a is a cutout opening to one side as shown in the foregoing embodiment. This port may have any other shape such as a round bore. Its location may be freely selected as long as oil remaining in the chamber can be drained to the oil storage space 110 below.
[25] Where the split case is formed of three or more units, an extension chamber 140 may be formed in each location opposed to the mating surfaces 120 with a packing 103 interposed therebetween. In this way, the breather apparatus 104 may have a labyrinth structure of three or more stages.
*
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What we claim is:-
[Claim 1]
A threshing apparatus having a threshing cylinder rotatable about a support shaft for threshing reaped grain culms fed into a threshing chamber,
characterized in that
said threshing cylinder includes a plurality of rod members extending along said support shaft and arranged at predetermined intervals circumferentially of said threshing cylinder, support members mounted on front and rear portions of said support shaft for supporting said rod members, and a plurality of threshing teeth arranged at predetermined intervals in a fore and aft direction on each of said rod members, said threshing teeth projecting from each of said rod members outwardly of said threshing cylinder.
[Claim 2]
A threshing apparatus as defined in claim 1, characterized in that said threshing cylinder further includes a partition member dividing an interior space thereof into a forward portion and a rearward portion.
[Claim 3]
A threshing apparatus as aefined in claim 2, characterized in that a winnowing fan is provided for generating a sorting air current, said sorting air current being directed from said winnowing fan toward said partition member.
[Claim 4]
A threshing apparatus as defined in claim 1, characterized in that said threshing cylinder has an upper portion thereof covered by a top board, said top board having a plurality of feeding vanes for guiding said reaped grain culms downstream in a direction of threshing process with rotation of said threshing cylinder.
[Claim 5]

A threshing apparatus as defined in claim 4. characterized in that said feeding vanes are formed to have a length extending between right and left side edges of said top board.
[Claim 6]
A threshing apparatus as defined in claim 4, characterized in that said top board are curved to follow substantially revolving loci described by tip ends of said threshing teeth with rotation of said threshing cylinder.
[Claim 7]
A threshing apparatus as defined in claim 1, characterized in that said threshing cylinder further includes helical blades disposed at a front end thereof for raking in and transporting rearward, with rotation of said threshing cylinder, reaped grain culms fed toward said fi:'ont end,
said helical blades being detachably attached to said front end.
[Claim 8]
A threshing apparatus as defined in claim 7, characterized in that a transport aiding guide is disposed below said threshing cylinder for covering said front end from below, and for receiving the reaped grain culms fed toward said front end and aiding said helical blades in raking in and transporting the reaped grain culms,
said transport aiding guide having, as a detachable part, at least a portion located downstream in a direction of rotation of said threshing cylinder.
[Claim 9]
A threshing apparatus as defined in claim 1, characterized in that said threshing cylinder is covered by a concave from below, and by a top board from above,
joint members being detachably mounted between said concave and said top board, and formed to define guide surfaces serving as smooth and continuous connection between inner surfaces of said concave and said top

Documents:

2043-che-2007 amended claims 26-04-2011.pdf

2043-che-2007 power of attorney 17-03-2011.pdf

2043-che-2007 amended claims 17-03-2011.pdf

2043-che-2007 correspondence others 26-04-2011.pdf

2043-che-2007 form-3 17-03-2011.pdf

2043-che-2007 other patent document 17-03-2011.pdf

2043-che-2007 other patent document 26-04-2011.pdf

2043-che-2007 examination report reply recieved 17-03-2011.pdf

2043-che-2007-abstract.pdf

2043-che-2007-claims.pdf

2043-che-2007-correspondnece-others.pdf

2043-che-2007-description(complete).pdf

2043-che-2007-drawings.pdf

2043-che-2007-form 1.pdf

2043-che-2007-form 18.pdf

2043-che-2007-form 3.pdf

2043-che-2007-form 5.pdf

abs-2043-che-2007.jpg


Patent Number 249257
Indian Patent Application Number 2043/CHE/2007
PG Journal Number 42/2011
Publication Date 21-Oct-2011
Grant Date 13-Oct-2011
Date of Filing 12-Sep-2007
Name of Patentee KUBOTA CORPORATION
Applicant Address 2-47, SHIKITSUHIGASHI 1-CHOME NANIWA-KU OSAKA-SHI OSAKA
Inventors:
# Inventor's Name Inventor's Address
1 FUKUOKA, YOSHITAKE C/O KUBOTA CORPORATION SAKAI SEIZOSHO 64, ISHIZUKITAMACHI SAKAI-KU SAKAI-SHI OSAKA
2 BUNNO, YUICHI C/O KUBOTA CORPORATION SAKAI SEIZOSHO 64, ISHIZUKITAMACHI SAKAI-KU SAKAI-SHI OSAKA
3 TANAKA, YUJI C/O KUBOTA CORPORATION SAKAI SEIZOSHO 64, ISHIZUKITAMACHI SAKAI-KU SAKAI-SHI OSAKA
PCT International Classification Number A01F 12
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 2007-114283 2007-04-24 Japan
2 2007-003644 2007-01-11 Japan
3 2007-003645 2007-01-11 Japan
4 2007-070967 2007-03-19 Japan