JP2008215587A - Bearing device, pulley using the bearing device, belt tension adjusting device having the pulley, and combine having the belt tension adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To effectively prevent foreign matter such as slurry from intruding in a bearing device for smoothly rotating rotary members such as pulleys and rollers. <P>SOLUTION: This bearing device 120 comprises a boss tube body 121 fixed to the rotating center part of a tension pulley 102, a pivot shaft body 122 inserted coaxially into the boss tube body 121, a bearing body 123 rolling between the boss tube body 121 and the pivot shaft body 122, and a pair of ring seal bodies 124 for sealing spaces S on both sides of the bearing body 123 in the direction of an axis A. A relief gap 140 so tilted that the orthogonal distance D thereof to the axis A is increased in the direction receding from the bearing body 123 along the axis A is formed between the mutually opposed edges 121a, 124a of the boss tube body 121 and each ring seal body 124. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a bearing device for smoothly rotating a rotating member such as a pulley or a roller, a pulley using the bearing device, a belt tension adjusting device having the pulley, and a combine having the belt tension adjusting device. It is about.

  Conventionally, for example, a bearing device for smoothly rotating a rotating member such as a pulley or a roller includes a boss cylinder attached to the rotation center of the rotating member, and a support shaft inserted concentrically through the boss cylinder. And a bearing body that rolls between the boss cylinder and the support shaft.

  An example of this type of bearing device is disclosed in Patent Document 1. The bearing device of Patent Document 1 is applied to a tension pulley for an endless belt for transmitting power from a transmission case to a pre-cutting processing device in a combine.

In Patent Document 1, a boss cylinder is integrally formed on a pulley body around which an endless belt is wound. An output shaft as a support shaft projecting outward from the transmission case is inserted into the boss cylinder concentrically through a bearing body. Of the pair of openings in the boss cylinder, a seal body is fitted into the opening opposite to the mission case. The opening near the transmission case communicates with the outside through a slight gap formed between the outer peripheral support portion of the output shaft and the boss cylinder in the transmission case.
Japanese Patent Laid-Open No. 7-236340 (see FIGS. 2 to 4)

  By the way, since the combine is a machine for performing operations such as cutting and threshing while running on mud, the bearing device and the tension pulley operate in a harsh environment where foreign matter such as muddy water and sawdust is scattered. There must be.

  However, in the bearing device of Patent Document 1, since the opening near the transmission case in the boss cylinder communicates with the outside through a slight gap, foreign matter such as muddy water enters the boss cylinder from the slight gap. easy. In addition, since there is a slight gap between the boss cylinder and the fitting seal body, foreign matter may enter through the gap. As a result, the bearing body in the boss cylinder is easily damaged.

  Therefore, the present invention has a technical problem to solve the above problems.

  In order to solve this technical problem, the invention of claim 1 is characterized in that a rotating member is mounted on the outer periphery of the support shaft body via a bearing body, and between the boss cylinder and the support shaft body of the rotating member. A bearing device comprising a pair of seal bodies that seal spaces on both sides in the axial direction across the bearing body, and between the opposing edges of the boss cylinder and the seal bodies, Inclined relief gaps are formed so that the distance in the radial direction from the axis increases as the distance from the bearing body increases along the axis.

  The invention of claim 2 relates to a pulley as a rotating member, and the pulley is configured to be rotatable by the bearing device described in claim 1.

  According to a third aspect of the present invention, there is provided a tension pulley that contacts an endless belt for power transmission, an arm body for moving the tension pulley in a direction in which the endless belt is tensioned / relaxed, and the tension pulley as the endless belt. A belt tension adjusting device including a spring body for pressing and urging the pulley, wherein the pulley according to claim 2 is used as the tension pulley.

  According to a fourth aspect of the present invention, there is provided a combine including a transmission case for shifting power from an engine mounted on a traveling machine body, and a counter case for relaying power transmission between the transmission case and a working unit. The transmission case and the counter case are configured to transmit power via an endless belt, and the belt tension adjusting device according to claim 3 is provided between the transmission case and the counter case to the endless belt. It is something related.

  According to the configuration of the present invention, the axis line between the boss cylinder attached to the rotation center part of the rotary member and the opposing edges of the pair of seal bodies that seal the space on both sides in the axial direction across the bearing body. As the escape gap is inclined so that the radial distance from the axis increases with distance from the bearing body along the gap, even if foreign matter such as muddy water enters the escape gap, When the bearing device rotates together with the rotating member, a centrifugal force associated with the rotation of the bearing device acts on the foreign matter outward in the radial direction. Therefore, the foreign matter is pushed outward in the radial direction and rotates. It will be discharged to the outside through the escape gap. For this reason, it is difficult for the foreign matter to pass through the escape gap and reach the space on both sides in the axial direction across the bearing body.

  In addition, even if a foreign object enters the space, a centrifugal force due to the rotation of the bearing device acts on the foreign object, so that the foreign object in the space is radially outward when viewed from the space. It is pushed out into the escape gap located at the end, and in this case as well, it is discharged from the rotating escape gap to the outside. In other words, the foreign matter can easily escape from the space.

  Therefore, it is possible to suppress the entry of the foreign matter into the space by the action of the centrifugal force accompanying the rotation of the bearing device, and to significantly reduce the possibility that the foreign matter enters the space and breaks the bearing body. There is an effect.

  In addition, since both the seal bodies are set in a positional relationship to sandwich the bearing bodies from both sides in the axial direction, the both seal bodies not only perform a foreign substance sealing function, but also the bearing bodies with respect to the support shaft bodies. It also has the effect of serving as a spacer that determines the mounting position (position in the axial direction).

  DESCRIPTION OF EMBODIMENTS Embodiments embodying the present invention will be described below with reference to the drawings (FIGS. 1 to 8). 1 is a side view of a combine, FIG. 2 is a plan view of the combine, FIG. 3 is a schematic front view of a front part of a traveling machine body, FIG. 4 is a schematic side sectional view of a threshing device, and FIG. 5 is a skeleton diagram of a power transmission system. 6 is a schematic side view of the front part of the traveling machine body, FIG. 7 is a schematic side view of the transmission case, FIG. 8A is a front sectional view taken along the line VIIIa-VIIIa of FIG. 7, and FIG. It is an expanded front sectional view.

(1). First, a schematic structure of a combine will be described with reference to FIGS.

  The combine for 6-row cutting in the embodiment includes a traveling machine body 1 supported by a pair of left and right traveling crawlers 2 and 2. At the front part of the traveling machine body 1, a pre-cutting processing device 3 that takes in planted cereal pods (uncut cereal potatoes) in the field is mounted by a single-acting hydraulic cylinder 4 so as to be adjustable up and down.

  A threshing device 5 with a feed chain 6 and a glen tank 7 for storing grain after threshing are mounted on the traveling machine body 1 side by side. In the embodiment, the threshing device 5 is disposed on the left side in the traveling direction of the traveling machine body 1, and the Glen tank 7 is disposed on the right side in the traveling direction of the traveling machine body 1. A discharge auger 8 for discharging the grains in the Glen tank 7 to the outside of the machine is provided at the rear part of the traveling machine body 1 so as to be able to turn. The grain in the Glen tank 7 is carried out from the tip throat throw hole of the discharge auger 8 to, for example, a truck bed or a container.

  A steering cabin 9 is provided between the cutting pretreatment device 3 and the Glen tank 7. In the steering cabin 9, a steering handle 10 for changing the traveling (turning) direction and turning speed of the traveling body 1, a steering seat 11 on which an operator is seated, and the like are arranged.

  A side column 12 disposed on one side of the control seat 11 has a main transmission lever and a sub transmission lever for performing a speed change operation of the traveling machine body 1 and power transmission to the pre-cutting processing device 3 and the threshing device 5. A clutch lever for operation is provided.

  An engine 17 as a power source is arranged below the control cabin 9. A transmission case 18 is disposed in front of the engine 17 for appropriately shifting the power from the engine 17 and transmitting it to the left and right traveling crawlers 2. A diesel engine is employed as the engine 17 of the embodiment.

  The pre-harvest processing device 3 includes a clipper-type cutting blade device 19, a cereal pulling device 20 for six strips, a pestle conveying device 21 and a weed body 22. The cutting blade device 19 is disposed below the cutting frame 3a constituting the framework of the pre-cutting processing device 3. The grain raising apparatus 20 is disposed above the cutting frame 3a. The corn straw transporting device 21 is disposed between the corn straw pulling device 20 and the feed start end of the feed chain 6. The weed body 22 is provided in front of the lower part of the grain raising device 20. The traveling machine 1 continuously cuts the uncut grain culm in the field by driving the pre-cutting processing device 3 while driving the left and right traveling crawlers 2 by the engine 17 and moving in the field.

  The threshing device 5 includes a handling cylinder 23 for threshing the harvested cereal, a swing sorting mechanism 24 and a wind sorting mechanism 25 arranged below the handling cylinder 23, and a threshing taken out from the rear part of the handling cylinder 23. And a dust-feed port processing cylinder 26 for reprocessing. The handling cylinder 23 is arranged in the handling chamber of the threshing device 5. The swing sorting mechanism 24 is for swinging and sorting the cereals threshed by the handling cylinder 23, and the wind sorting mechanism 25 is for wind sorting the threshing.

  The stocker side of the harvested cereal meal sent from the pre-harvest processing device 3 is inherited by the feed chain 6. Then, the tip side of the harvested cereal culm is carried into the threshing device 5 and threshed by the handling cylinder 23. In addition, the rotating shaft 46 (refer FIG.4 and FIG.5) of the handling cylinder 23 is extended along the feed direction (advancing direction of the traveling body 1) of the harvested cereal by the feed chain 6. FIG.

  In the lower part of the threshing device 5, there are a first receiving bowl 27 where most of the grains selected from the two sorting mechanisms 24, 25 are collected, a grain with a branch stem, a grain of ears, etc. There is provided a second receiving bowl 28 where second things gather. The two receiving rods 27 and 28 of the embodiment are horizontally provided above the rear portion of the traveling crawler 2 in a side view in order of the first receiving rod 27 and the second receiving rod 28 from the front side in the traveling direction of the traveling machine body 1.

  The swing sorting mechanism 24 includes a crimp net 29 stretched below the handling cylinder 23, a feed pan 30 and a chaff sheave 31 disposed below the crimp net 29, and a net-like grain sheave 32 disposed below the chaff sheave 31. And a Strollac 33 disposed on the downstream side (rear side) of the chaff sheave 31.

  The wind sorting mechanism 25 includes a tang fan 34 disposed below the feed pan 30, and a sorting fan 35 disposed between the first receiving bowl 27 and the second receiving bowl 28. The tang fan 34 is configured to blow through the chaff sheave 31 upward from the bottom and blow out the sorting air toward the dust exhaust fan 36 disposed at the rear of the threshing device 5.

  The sorting fan 35 is for blowing a sorting wind as an auxiliary to the cereal crops (second product) that cannot pass through the grain sieve 32. The sorting wind from the sorting fan 35 blows away the sawdust in the second thing backward, thereby improving the wind sorting efficiency of the second thing.

  The threshing that has been threshed by the handling cylinder 23 and leaked from the crimp net 29 falls on the feed pan 30 that swings back and forth and is sent to the rear chaff sheave 31 while undergoing swing selection. At this time, the threshing on the feed pan 30 and the chaff sheave 31 receives a sorting wind flowing backward from the Kara fan 34. Due to the interaction between the rocking sorting and the wind sorting, the threshing is separated into grains and swarf.

  The first thing such as a granule passes from the chaff sheave 31 through the grain sheave 32 and is collected in the first receiving bowl 27 while being guided by the cereal plate etc. From here, the first conveyor 37 in the first receiving bowl 27 and It is sent to the grain tank 7 through the cereal conveyor 40 in the cereal cylinder 39.

  The second item such as the grain with the branch stem cannot pass through the Glen sieve 32 and is collected in the second receiving rod 28 behind the first receiving rod 27, and from here the second conveyor 38 in the second receiving rod 28. And it is sent to the second processing cylinder 43 through the reduction conveyor 42 in the reduction cylinder 41. The second product is threshed again by the second processing cylinder 43 and then returned to the threshing device 5 for re-sorting. The sawdust is sucked into the dust exhaust fan 36 and then discharged out of the machine from a discharge port (not shown) provided in the rear portion of the threshing device 5.

  An exhaust chain 44 is disposed on the rear side (feed end side) of the feed chain 6. The waste (the grain that has been shattered) inherited from the rear end of the feed chain 6 to the waste chain 44 is discharged to the rear of the traveling machine body 1 in a long state, or the waste cutter 45 at the rear of the threshing device 5. After being cut to a short length as appropriate at, it is discharged to the rear of the traveling machine body 1.

(2). Next, the power transmission system of the combine will be described with reference to FIG.

  The engine 17 includes an output shaft 50 that protrudes forward and backward, and one of the power from the engine 17 passes from the front side of the output shaft 50 to the mission case 18 via the universal joint shaft 51 and the mission input shaft 52. Communicated.

  The transmission case 18 is provided with a hydraulic pump hydraulic motor type (HST type) straight-running hydraulic continuously variable transmission 53 and a HST type hydraulic continuously variable transmission 54 for turning. The branching power from the output shaft 50 of the engine 17 toward the transmission case 18 is transmitted to the linear input shaft 53a of the linear hydraulic continuously variable transmission 53 and the rotational input shaft 54a of the hydraulic hydraulic continuously variable transmission 54, respectively. Is done.

  Then, by adjusting the inclination angle of the rotary swash plate in each hydraulic pump according to the operation amount of the steering handle 10 and the main speed change lever arranged in the steering cabin 9, the discharge of the pressure oil between the hydraulic pump hydraulic motors The direction and the discharge amount are changed, and the rotation direction and the number of rotations of the straight output shaft 53b and the turning output shaft (not shown), and thus the driving speed and driving direction of the left and right traveling crawlers 2 are arbitrarily adjusted.

  The rotational power of the rectilinear output shaft 53b is also applied to a tuning input shaft 65 protruding from the counter case 61 disposed on one side of the engine 17 toward the center of the machine body via a pulley / belt type transmission means 90 described later. Branched and transmitted.

  A cooling fan 57 for the radiator is provided on the fan shaft 56 that relays power between the straight and turning input shafts 53a and 54a and the mission input shaft 52. In the embodiment, the power is transmitted from the fan shaft 56 to both the straight and turning input shafts 53a and 54a via the transmission gear mechanism.

  Further, a charge pump 58 for supplying hydraulic oil to each hydraulic pump and hydraulic motor is provided on the turning input shaft 54a. The charge pump 58 can be interlocked with the turning input shaft 54 a and is driven by the rotational power of the engine 17.

  On the other hand, the other power from the engine 17 is transmitted from the rear side of the output shaft 50 by branching in two directions of the counter case 61 and the discharge auger 8 arranged on one side of the engine 17.

  The branching power from the output shaft 50 of the engine 17 toward the counter case 61 is transmitted to the threshing input shaft 63 of the counter case 61 via the threshing clutch 62 for power transmission, and further from the threshing input shaft 63 in two directions. Branched and transmitted.

  Part of the power transmitted to the threshing input shaft 63 is transmitted to the rotating shaft 23a of the handling cylinder 23, the rotating shaft of the dust feeding port processing cylinder 26 (not shown in FIG. 6), etc., via a pulley / belt transmission system. Then, the handling cylinder 23 and the dust feeding port processing cylinder 26 are driven to rotate. The other power from the threshing input shaft 63 is transmitted to the constant speed rotating shaft 64 of the counter case 61 via a bevel gear mechanism provided in the middle of the threshing input shaft 63.

  The counter case 61 includes a threshing input shaft 63 and a constant speed rotating shaft 64, a tuning input shaft 65, a vehicle speed tuning shaft 66, a cutting transmission shaft 67, and an FC input shaft 68 extending in parallel with the constant speed rotating shaft 64, respectively. , A cutting speed change mechanism 69 associated with the tuning input shaft 65 and the vehicle speed tuning shaft 66, a cutting constant speed mechanism 70 associated with the constant speed rotating shaft 64 and the vehicle speed tuning shaft 66, the vehicle speed tuning shaft 66 and the FC input shaft 68. And an FC transmission mechanism 71 associated therewith.

  A part of the power transmitted to the constant speed rotating shaft 64 is transmitted to the swing sorting mechanism 24, the wind sorting mechanism 25, the exhaust chain 44 (not shown in FIG. 6), etc., via the pulley / belt transmission system. The The other power from the constant speed rotating shaft 64 is transmitted to the vehicle speed tuning shaft 66 through the cutting constant speed mechanism 70 when the pre-cutting processing device 3 is not driven in synchronization with the vehicle speed (traveling speed), and is synchronized with the vehicle speed. Power is transmitted from the shaft 66 to each of the devices 19 to 21 of the pre-cutting processing device 3 through the cutting transmission shaft 67.

  As described above, a part of the rotational power of the straight output shaft 53 b is transmitted to the tuning input shaft 65 via the cutting clutch 55. The rotational power transmitted to the tuning input shaft 65 is transmitted to the vehicle speed tuning shaft 66 via the one-way clutch 72 and the cutting speed change mechanism 69 when the pre-cutting processing device 3 is driven in synchronization with the vehicle speed. Power is transmitted to the devices 19 to 21 of the pre-cutting processing device 3 through the cutting transmission shaft 67. The one-way clutch 72 is configured such that power is transmitted only when the straight-travel output shaft 53b is rotating forward.

  The power transmitted to the vehicle speed tuning shaft 66 is transmitted to the FC input shaft 68 through the FC transmission mechanism 71 and the FC clutch 73, and the feed chain 6 is driven to rotate by the power transmission from the FC input shaft 68. Has been.

  The branching power from the output shaft 50 of the engine 17 toward the discharge auger 8 is transmitted through an auger clutch 75 for power disconnection to a bottom conveyor 76 disposed on the inner bottom of the Glen tank 7 and a vertical auger cylinder 81 in the discharge auger 8. The power is transmitted to the internal vertical conveyor 77, and then the power is transmitted to the discharge conveyor 79 in the horizontal auger cylinder 82 in the discharge auger 8 through the connection screw 78 and the like.

(3). Next, the structure around the mission case 18 and the counter case 61 will be described with reference to FIGS. 3, 6, and 7. FIG.

  As shown in FIGS. 3, 6, and 7, the mission case 18 is provided between the left and right traveling crawlers 2 at the front portion of the body frame 81 constituting the traveling body 1. A frame-like cabin frame 82 that supports the steering cabin 9 from below is provided at a position in front of the engine 17 on the upper surface of the body frame 81. Further, a frontal cutting-type mowing rack 83 that supports the pre-harvest processing device 3 via the mowing frame 3a is provided on the upper surface of the machine body frame 81 in front of the threshing device 5. A counter case 61 is provided on the upper surface of the machine body frame 81 at a position behind the cutting stand 83. The cabin frame 82 and the cutting frame 83 are connected via a horizontal connection frame 84. The engine 17 located behind the cabin frame 82 is covered with an engine room cover 85.

  The transmission case 18 is provided with a cylindrical axle case 86 that protrudes toward the left and right outer sides. The axle case 86 has a built-in axle (not shown) that extends concentrically therewith. Starting wheels 87 for driving the traveling crawler 2 to circulate are attached to both ends of the axle.

(4). Next, the structure of the pulley / belt type transmission means 90 positioned between the transmission case 18 and the counter case 61 will be described with reference to FIGS. 3 and 5 to 8.

  The transmission means 90 of the embodiment is for transmitting power from the straight traveling output shaft 53a on the mission case 18 side to the tuning input shaft 65 on the counter case 61 side, and is a cutting drive pulley fixed to the straight traveling output shaft 53a. 91, left and right idler pulleys 92 and 93 (only the left idler pulley 93 is shown in FIG. 7) disposed in front of the cutting frame 83, a tuning input pulley 94 fixed to the tuning input shaft 65, a cutting drive pulley 91, A first endless belt 96 wound around the right idler pulley 92 and a second endless belt 97 wound around the left idler pulley 93 and the tuning input pulley 94 are provided.

  The horizontal rotation support shafts 98 in the idler pulleys 92 and 93 are rotatably supported on an upper portion of a mounting seat 99 having a substantially triangular shape in a side view, which is bolted to the front surface of the cutting rack 83. Both idler pulleys 92 and 93 of the embodiment are arranged separately on both the left and right sides with the mounting seat 99 interposed therebetween.

  Around the idler pulleys 92 and 93, first and second belt tension adjusting devices 100 and 101 associated with the first and second endless belts 96 and 97, respectively, are arranged. Each of these belt tension adjusting devices 100 (101) includes a tension pulley 102 (103) that contacts the endless belt 96 (97) from below, and a tension pulley 102 (103) in the vertical direction in which the endless belt 96 (97) is tensioned / relaxed. ) And a spring body 106 (107) for pressing and urging the tension pulley 102 (103) toward the endless belt 96 (97).

  In the embodiment, both arm bodies 104 and 105 are also arranged separately on the left and right sides with the mounting seat 99 interposed therebetween, and the respective base end portions extend in parallel with the rotation support shafts 98 of both idler pulleys 92 and 93. The arm shaft 108 is pivotally attached to the lower portion of the mounting seat 99 so as to be able to rotate independently of each other. Due to the positional relationship between the endless belts 96 and 97, the arm body 104 of the first belt tension adjusting device 100 extends forward, and the arm body 105 of the second belt tension adjusting device 101 extends backward.

  Each tension pulley 102 (103) is rotatably supported at the tip of the arm body 104 (105), and the endless belt 96 (corresponding to the rotation of the arm body 104 (105) around the arm shaft 108). 97) is configured to be tense / relaxed.

  One end portion (lower end portion) of the spring body 106 in the first belt tension adjusting device 100 is hooked on the protruding end portion of the support shaft body 122 that protrudes outward in the lateral direction from the tension pulley 102. The other end (upper end) of the spring body 106 is connected to a bracket plate 110 formed integrally with the upper end of the mounting seat 99 via a tension adjustment bolt 109.

  On the other hand, one end portion (lower end portion) of the spring body 107 in the second belt tension adjusting device 101 is hooked on a locking pin 111 projecting sideways in the middle of the arm body 105. The other end portion (upper end portion) of the spring body 107 is connected to a spring receiving plate 113 fixed to the left side surface of the cutting rack 83 via a tension adjusting bolt 112.

(5). Next, the structure of the bearing device 120 according to the present invention will be described with reference to FIGS. 8 (a) and 8 (b).

  The bearing device 120 of the embodiment is applied to a tension pulley 102 as a rotating member in the first belt tension adjusting device 100, and a boss cylinder 121 fixed to the rotation center portion of the tension pulley 102 by press-fitting, and a boss A support shaft body 122 inserted concentrically into the cylinder body 121, a bearing body 123 rolling between the boss cylinder body 121 and the support shaft body 122, and a space S on both sides in the axis A direction across the bearing body 123. And a pair of annular seal bodies 124.

  An annular rib 126 protruding radially inward is formed on the inner peripheral surface of the boss cylinder 121 near the arm body 104. By means of the annular rib 126 and the snap ring type retaining ring 127, the bearing body 123 is locked so as not to be displaced in the direction of the axis A of the support shaft body 122 and to be detachable.

  The support shaft body 122 includes a nut shaft 128 that protrudes laterally from the distal end portion of the arm body 104, and a fixing bolt 129 with a large-diameter head portion 129 a that is screwed into the nut shaft 128. The nut shaft 128 is formed in a tapered stepped shape, and a base end large diameter portion 128a near the arm body 104 is fixed to the distal end portion of the arm body 104 by welding.

  In this case, the small-diameter shaft portion 128b of the nut shaft 128 is inserted into the through hole 135 of the annular seal body 124 and the shaft hole 134 of the bearing body 123, and the collar 130 is fitted into the nut hole 128c on the distal end side of the nut shaft 128. By screwing the fixing bolt 127, the bearing body 123 and the two annular seal bodies 124 are sandwiched and fixed between the base end large diameter portion 128a of the nut shaft 128 and the collar 130.

  Therefore, even if there is a slight gap between the contact surfaces of the annular seal bodies 124 and the support shaft body 122, the base end large diameter portion 128a of the nut shaft 128 and the collar 130 are not connected to the small gap and the outside. Since the communication is cut off, it is unlikely that a foreign substance such as muddy water will enter the space S on both sides in the axis A direction across the bearing body 123 through the annular seal bodies 124 and the support shaft body 122.

  The bearing body 123 is a well-known rolling bearing, and includes a substantially cylindrical inner case 131, an outer case 132 that covers the outer peripheral side of the inner case 131, and an outer peripheral surface of the inner case 131 and the outer case 132. It comprises a plurality of balls 133 inserted between the inner peripheral surface. The aforementioned shaft hole 134 is formed on the inner peripheral side of the inner case 131.

  A distance D (radial distance) between the boss cylinder 121 and each of the annular seal bodies 124 facing the axis A as the distance from the bearing body 123 increases along the axis A. An escape gap 140 that is inclined so as to be longer is formed.

  In this case, the opening edge portions 121a on both sides in the axis A direction of the boss cylinder 121 are formed in a tapered shape in which the inner diameter increases as going outward in the axis A direction (a direction away from the bearing body 123 along the axis A). . On the contrary, the outer peripheral edge portion 124a of each annular seal body 124 is formed in a tapered shape whose outer diameter increases toward the outer side in the axis A direction. And the above-mentioned relief clearance 140 is formed by making the taper-shaped opening edge part 121a in the boss | hub cylinder 121 and the taper-shaped outer peripheral edge part 124a in each annular seal body 124 oppose each other. Therefore, the spaces S on both sides in the direction of the axis A across the bearing body 123 communicate with the outside via the escape gap 140.

  With the above configuration, the tension pulley 102 normally rotates around the support shaft body 122 as the first endless belt 96 is driven. For example, it is assumed that foreign matter such as muddy water has entered the escape gap 140. However, since the centrifugal force generated by the rotation of the tension pulley 102 and the bearing device 120 acts radially outward on the foreign matter, the foreign matter is pushed outward in the radial direction and is discharged to the outside through the rotating escape gap 140. Will be. For this reason, it is difficult for foreign matter to escape and pass through the clearance 140 to reach the space S on both sides in the axis A direction with the bearing body 123 interposed therebetween.

  Even if foreign matter enters the space S on both sides of the axis A direction across the bearing body 123, the centrifugal force accompanying the rotation of the tension pulley 102 and the bearing device 120 acts on the foreign matter. The foreign matter in the space S is pushed out to the escape gap 140 located on the outer side in the radial direction when viewed from the space S. After all, the foreign matter is discharged from the rotating escape gap 140 to the outside. In other words, it is easy for foreign matter to escape from the space S.

  Therefore, it is possible to suppress the entry of foreign matter into the space S by the action of the centrifugal force accompanying the rotation of the tension pulley 102 and the bearing device 120, and the possibility that the foreign matter enters the space S and breaks the bearing body 123 is markedly increased. Can be reduced. Further, as the tension pulley 102 rotates at a higher speed, the centrifugal force acting on the foreign matter in the escape gap 140 and the space S increases, so that the foreign matter is easily driven out of the bearing device 120 and the sealing effect is enhanced.

  In particular, since the first belt tension adjusting device 100 according to the embodiment is located between the mission case 18 and the counter case 61 and close to the field scene, the tension pulley 102 and the bearing device 120 include muddy water, sawdust, and the like. It will operate in a harsh environment where foreign objects are scattered. In this regard, by adopting the above-described configuration, due to the centrifugal force caused by the rotation of the tension pulley 102 and the bearing device 120, foreign matters such as muddy water are located on both sides in the axis A direction across the bearing body 123 in the bearing device 120. Intrusion into the space S can be effectively suppressed.

  Further, the bearing body 123 is clamped by the both annular seal bodies 124 and the nut shaft 128 and the fixing bolt 129 are fastened, so that the bearing body 123 cannot be displaced with respect to the support shaft body 122 in the axis A direction. it can. In other words, both annular seal bodies 124 not only perform a foreign matter sealing function, but also serve as spacers that determine the mounting position (position in the axis A direction) of the bearing body 123 with respect to the support shaft body 122.

(6). Others The present invention is not limited to the above-described embodiment, and can be embodied in various forms. For example, the rotating member is not limited to a pulley, and may be a roller, a gear, or the like. In addition, the configuration of each unit is not limited to the illustrated embodiment, and various modifications can be made without departing from the spirit of the present invention.

It is a side view of a combine. It is a top view of a combine. It is a schematic front view of a traveling machine body front part. It is a schematic side sectional view of a threshing apparatus. It is a skeleton figure of a power transmission system. It is a schematic side view of a traveling machine body front part. It is a schematic side view of a mission case. (A) is a VIIIa-VIIIa view front sectional view of Drawing 7, (b) is an important section expanded front sectional view of (a).

Explanation of symbols

A Axis axis of support shaft D Distance perpendicular to axis S Space on both sides in the axial direction across the bearing body 1 Traveling machine body 18 Transmission case 61 Counter case 90 Pulley / belt type transmission means 100 First belt tension adjusting device 101 Second Belt tension adjusting device 102, 103 Tension pulley 104, 105 Arm body 106, 107 Spring body 120 Bearing device 121 Boss cylinder 121a Open edge 122 Support shaft body 123 Bearing body 124 Annular seal body 124a Outer peripheral edge 140 Relief gap

Claims (4)

A rotating member is mounted on the outer periphery of the support shaft body via a bearing body, and a pair of seals are provided on both sides in the axial direction by sandwiching the bearing body between the boss cylinder and the support shaft body of the rotating member. A bearing device comprising a seal body,
The clearance gap which inclines so that the distance of the radial direction with the said axis line may become long as it leaves | separates from the said bearing body along the said axis line between the edge parts which the said boss | hub cylinder and each said sealing body oppose. Is formed,
Bearing device. The bearing device according to claim 1 is configured to be rotatable.
Pulley as a rotating member. A tension pulley that contacts an endless belt for power transmission, an arm body for moving the tension pulley in a direction in which the endless belt is tensioned / relaxed, and a pressure pulley that urges the tension pulley toward the endless belt A belt tension adjusting device comprising:
The pulley according to claim 2 is used as the tension pulley.
Belt tension adjuster. A combine that includes a transmission case that shifts power from an engine mounted on a traveling machine body, and a counter case that relays power transmission between the transmission case and the working unit;
The transmission case and the counter case are configured to transmit power via an endless belt, and the belt tension adjusting device according to claim 3 is associated with the endless belt between the transmission case and the counter case. Provided,
Combine.

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