JP5808941B2 - Rice transplanter transmission - Google Patents

Rice transplanter transmission Download PDF

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Publication number
JP5808941B2
JP5808941B2 JP2011103826A JP2011103826A JP5808941B2 JP 5808941 B2 JP5808941 B2 JP 5808941B2 JP 2011103826 A JP2011103826 A JP 2011103826A JP 2011103826 A JP2011103826 A JP 2011103826A JP 5808941 B2 JP5808941 B2 JP 5808941B2
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transmission
gear
shaft
pto
transmission shaft
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JP2012233544A (en
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黒田 智之
智之 黒田
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ヤンマー株式会社
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Description

  The present invention relates to a rice transplanter transmission.

  2. Description of the Related Art Conventionally, a rice transplanter transmission configured to transmit power shifted by a transmission from an output shaft of the transmission to a PTO transmission shaft and a traveling transmission shaft is known (see, for example, Patent Document 1). ).

  In the rice transplanter described in Patent Document 1, during planting work, the power shifted by the hydraulic transmission mechanism, which is a transmission, is transferred from the combined output shaft, which is the output shaft of the transmission, to the forward gear and the high-speed gear. Via the counter shaft. The power transmitted to the counter shaft is configured to be transmitted to a rear output shaft, which is a travel transmission shaft, via a low speed PTO transmission gear and a planting gear. The power transmitted to the counter shaft is configured to be transmitted to a PTO output shaft, which is a PTO transmission shaft, via a PTO transmission shaft and a PTO transmission mechanism.

Japanese Patent Laid-Open No. 2003-83421

  In such a rice transplanter transmission, there is a demand to reduce the number of transmission shafts. The present invention has been made in view of the above-described problems, and an object thereof is to provide a rice transplanter transmission having a small number of transmission shafts.

  The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.

  In claim 1, in the transmission of the rice transplanter configured to transmit the power shifted by the transmission from the output shaft of the transmission to the PTO transmission shaft and the traveling transmission shaft, in parallel with the output shaft, A travel transmission shaft, the PTO transmission shaft, and the travel transmission shaft are provided, a gear type PTO system power transmission path is formed on the output shaft, the travel transmission shaft, and the PTO transmission shaft, and the output shaft A gear-type travel system power transmission path is formed on the travel transmission shaft, the PTO transmission shaft, and the travel transmission shaft, and the travel transmission gear on the PTO transmission shaft in the gear-type travel system power transmission path is It is loosely fitted to the PTO transmission shaft.

According to a second aspect of the present invention , the output shaft of the transmission is arranged on the front side of the transmission, and the PTO transmission shaft and the traveling transmission shaft are arranged on the rear side of the transmission.

  According to a third aspect of the present invention, the rotation direction of the PTO transmission shaft and the traveling transmission gear is the same during operation.

  As effects of the present invention, the following effects can be obtained.

  In claim 1, the number of transmission shafts can be reduced.

  According to the second aspect, the front-rear width of the transmission can be shortened.

  According to the third aspect of the present invention, it is difficult for a difference between the rotational speeds of the PTO transmission shaft and the traveling transmission gear to be generated during a load operation. Therefore, the bearing provided between the PTO transmission shaft and the traveling transmission gear is not easily worn, and the life can be extended.

1 is an overall side view of a rice transplanter 1 according to an embodiment of the present invention. The partial sectional view showing the power transmission structure inside mission case 18 of rice transplanter 1 concerning one embodiment of the present invention. The conceptual diagram which shows the power transmission structure inside the mission case 18 of the rice transplanter 1 which concerns on one Embodiment of this invention.

  Below, the whole structure of the rice transplanter 1 which concerns on one Embodiment of this invention is demonstrated using FIG. In the present embodiment, the rice transplanter is an eight-row planter, but this is not particularly limited, and a six-plant or ten-row planter may be used.

  The rice transplanter 1 includes a traveling unit 10 and a planting unit 40, and is configured so that seedlings can be planted in a field by the planting unit 40 while traveling by the traveling unit 10. The planting part 40 is arrange | positioned behind the traveling part 10, and is connected with the rear part of this traveling part 10 via the raising / lowering mechanism 30 so that raising / lowering is possible.

  In the traveling unit 10, the front axle case 16 is supported by the front portion of the vehicle body frame 11, and the front wheels 12 are attached to the left and right sides of the front axle case 16. A rear axle case 17 is supported on the rear portion of the vehicle body frame 11, and the rear wheels 13 are attached to the left and right sides of the rear axle case 17. An engine 14 is provided at the front portion of the vehicle body frame 11 and is covered with a bonnet 15. A transmission case 18 is supported by the front portion of the vehicle body frame 11 and is disposed behind the engine 14.

  In the traveling unit 10, a driving operation unit 20 is provided in the middle part of the vehicle body frame 11 before and after. A dashboard 21 is disposed at the front of the driving operation unit 20, a steering handle 24 is disposed at the center of the left and right of the dashboard 21, and a driver seat 22 is disposed behind the steering handle 24. Below the driver's seat 22, a vehicle body cover 23, a part of which is a step for getting on and off, is arranged. In the driving operation unit 20, a plurality of operation tools including a main transmission lever 25, a transmission pedal 26, and a brake pedal are arranged, and appropriate operations are performed on the traveling unit 10 and the planting unit 40 with these operation tools. It is possible.

  In the planting part 40, the planting mission case 47 is supported near the center of the lower part of the planting frame 49, and the transmission shaft extends from the planting mission case 47 to the left and right sides. Four planting transmission cases 46 are respectively extended rearward from the transmission shaft and are arranged at appropriate intervals in the left-right direction.

  A rotary case 44 is rotatably supported on the left and right sides of the rear end portion of each planting transmission case 46. The number of the rotary cases 44 is the same as the number of planting strips, that is, eight in this embodiment. Then, the two planting claws 45 are attached to both sides of the rotary case 44 in the longitudinal direction so as to sandwich the rotation fulcrum of the rotary case 44.

  The seedling table 41 is arranged above the planting transmission case 46 in a tilted state with a front height and a low height. The seedling table 41 is attached to the rear portion of the planting frame 49 so as to be reciprocally movable in the left-right direction via a guide rail. The seedling table 41 can be reciprocated horizontally by a lateral feed mechanism.

  The seedling mounting bases 41 having a plurality of (eight) seedling mat mounting portions are arranged in the left-right direction so that each lower end side faces one rotary case 44. Then, the seedling mat is placed on each seedling stage 41, and one seedling can be cut from the seedling mat on the seedling stage 41 by the planting claws 45 when the rotary case 44 rotates.

  In the planting part 40, a plurality of floats 42 are supported by a planting frame 49 so that the float 42 can move up and down and the leveling rotor 43 can move up and down. Moreover, the drawing marker 48 is rotatably supported on the left and right sides of the planting frame 49.

  Hereinafter, the internal structure of the mission case 18 will be described with reference to FIGS. 2 and 3. In the following description, the arrow L in FIG. 2 is defined as the left direction, the arrow R as the right direction, the arrow F as the forward direction, and the arrow B as the backward direction.

  As shown in FIG. 2, the mission case 18 is formed so as to be divided into a left and right left case 18L and a right right case 18R, and a part of the transmission 100 is accommodated therein. Transmission 100 mainly includes a hydraulic-mechanical continuously variable transmission (HMT) 190, a main clutch 130, a main transmission mechanism 140, and a braking device 150.

  As shown in FIG. 3, the power of the engine 14 is transmitted from the input shaft 101 to the transmission 100 via a V-belt and a propeller shaft.

  The power transmitted to the input shaft 101 is shifted by the HST transmission 110 and the planetary gear mechanism 120 that constitute the HMT 190. The HST transmission 110 includes a variable displacement hydraulic pump 111 and a fixed displacement hydraulic motor 112. The power input from the input shaft 101 drives the hydraulic pump 111 and feeds the hydraulic oil from the hydraulic pump 111 to the hydraulic motor 112 to rotate the motor shaft 113 of the hydraulic motor 112.

  A transmission gear 115 is fixed to the pump output shaft 114 of the hydraulic pump 111. One end of a charge output shaft 116 disposed coaxially with the pump output shaft 114 is inserted and fixed to the transmission gear 115, and from the other end, the charge pump 71 of the HST transmission 110 and the lifting mechanism 30 are fixed. Power is transmitted to the charge pump 72 such as.

  A sun gear 121 is pivotally supported on the motor shaft 113 of the hydraulic motor 112, and a planetary carrier 122 having a tooth portion on the outer periphery is pivotally supported on a boss portion of the sun gear 121. The tooth portion meshes with the transmission gear 115 and three planetary gears 123, 123, and 123 are rotatably provided around the sun gear 121. A ring gear 124 is engaged with the outside of the three planetary gears 123, 123, and 123. Thus, the planetary gear mechanism 120 is formed by the sun gear 121, the planetary carrier 122, the three planetary gears 123, 123, and 123 and the ring gear 124.

  In such an HMT 190, by changing the angle of the movable swash plate of the hydraulic pump 111 by operating the shift pedal 26, the hydraulic oil corresponding to the angle is fed from the hydraulic pump 111. The power (rotational speed) of the motor shaft 113 of the hydraulic motor 112 is changed according to the amount of oil fed from the hydraulic pump 111, and the sun gear 121 rotates at a speed corresponding to this power. On the other hand, when the pump output shaft 114 of the hydraulic pump 111 rotates, the transmission gear 115 and the planetary carrier 122 rotate, and the planetary gears 123, 123, 123 rotate.

  Thereafter, the planetary gear mechanism 120 combines the power of the sun gear 121 and the power of the planetary gears 123, 123, and 123, and outputs the combined power from the combined output shaft 102 inserted into the ring gear 124. That is, the combined output shaft 102 rotates or stops at a speed corresponding to the angle of the movable swash plate of the hydraulic pump 111.

  A main clutch 130 is interposed between the ring gear 124 and the composite output shaft 102. The main clutch 130 switches whether power can be transmitted from the HMT 190 to the combined output shaft 102. In the main clutch 130, the ring gear 124 and the composite output shaft 102 are connected or disconnected as the clutch shifter 131 slides. In this way, the power of the ring gear 124 is transmitted to the composite output shaft 102. Or it is not transmitted.

  The power transmitted to the composite output shaft 102 is transmitted to the left and right front wheels 12 and the rear wheels 13 via a gear-type traveling system power transmission path. The gear-type traveling system power transmission path is formed on the composite output shaft 102, the counter shaft 103, the traveling transmission shaft 104, the main transmission mechanism 140, the front output shaft 105, the rear transmission shaft 107, and the rear output shaft 108. In addition, the power transmitted to the composite output shaft 102 is transmitted to the planting unit 40 via a gear-type PTO system power transmission path. The gear-type PTO system power transmission path is formed on the composite output shaft 102, the travel transmission shaft 104, the PTO transmission shaft 106, and the PTO output shaft 109.

  As shown in FIG. 2, a counter shaft 103, a travel transmission shaft 104, a PTO transmission shaft 106, and a rear transmission shaft 107 are arranged in parallel with the combined output shaft 102. The composite output shaft 102 is supported at its midway part by a middle wall 80 provided in the left case 18L via a bearing, and at its right end by a right case 18R via a bearing. The counter shaft 103, the travel transmission shaft 104, and the PTO transmission shaft 106 are supported at the left end by the middle wall 80 via bearings and at the right end by the right case 18R via bearings. The rear transmission shaft 107 has a left end supported by the left case 18L via a bearing, and a right end supported by the middle wall 80 via a bearing.

  As shown in FIGS. 2 and 3, a main transmission mechanism 140 is provided between the combined output shaft 102, the counter shaft 103, and the traveling transmission shaft 104 in the gear system traveling transmission path. The main transmission mechanism 140 shifts the power from the combined output shaft 102 to a plurality of stages and outputs it to the traveling transmission shaft 104. The main transmission mechanism 140 includes a reverse input gear 141, a forward gear 142, a moving gear 143, a reverse output gear 144, a reverse gear 145, and a slider 146.

  The reverse side input gear 141 and the forward gear 142 are integrally configured with the reverse side input gear 141 arranged on the left side and the forward gear 142 on the right side. The reverse side input gear 141 and the forward gear 142 are fixed in the middle of the composite output shaft 102. The moving gear 143 is disposed on the right side of the forward gear 142 and is fixed to the composite output shaft 102. The reverse output gear 144 is fixed to the left end of the counter shaft 103, and the reverse input gear 141 and the reverse output gear 144 are meshed so that the power of the combined output shaft 102 is always applied to the counter shaft 103. Communicated. The reverse gear 145 is fixed to the right end of the counter shaft 103.

  The slider 146 is spline-fitted to the middle portion of the travel transmission shaft 104 and is provided so as not to be relatively rotatable and slidable. The slider 146 is formed with a small diameter gear 146a and a large diameter gear 146b. The slider 146 slides with respect to the travel transmission shaft 104 by operating the main transmission lever 25, and the small-diameter gear 146a meshes with the forward gear 142 so that the main transmission mechanism 140 is moved forward, and the large-diameter gear 146b is moved forward. By meshing with the moving gear 143, the main transmission mechanism 140 is "moved", and when the large diameter gear 146b is meshed with the reverse gear 145, the main transmission mechanism 140 is "reversed", and the small diameter gear 146a and the large diameter gear 146b are When not engaging with any gear, the main transmission mechanism 140 is switched to “neutral”. Thus, the power from the combined output shaft 102 is shifted and output to the travel transmission shaft 104.

  A braking device 150 is provided at the right end of the travel transmission shaft 104. The braking device 150 brakes the rotation of the travel transmission shaft 104. In the brake device 150, the travel transmission shaft is pressed by pressing the cylindrical piston 151 and bringing the plurality of friction plates 152 provided on the travel transmission shaft 104 and the right case 18R into contact with each other by operating the brake pedal. 104 is braked.

  As shown in FIG. 3, a front transmission gear 161 is fixed to the left end of the travel transmission shaft 104, and the front transmission gear 161 meshes with an input gear of the differential device 162. The power of the travel transmission shaft 104 is transmitted to the left and right front output shafts 105 via the differential device 162. The power transmitted to the left and right front output shafts 105 is transmitted to the left and right front wheels 12 via a transmission mechanism in the front axle case 16, and the front wheels 12 rotate. The differential device 162 can be locked by the front differential lock device 163.

  As shown in FIGS. 2 and 3, a rear first transmission gear 171 is fixed in the middle of the travel transmission shaft 104, and the rear first transmission gear 171 is a rear second transmission gear serving as a counter gear. 172 is engaged. The rear second transmission gear 172 is loosely fitted to the left end of the PTO transmission shaft 106. Specifically, a rolling bearing 76 such as a ball bearing is interposed between the rear second transmission gear 172 and the PTO transmission shaft 106 so as to be relatively rotatable. Instead of the rolling bearing 76, a sliding bearing such as a bush may be used.

  The rear second transmission gear 172 is meshed with a rear third transmission gear 173 fixed to the right end of the rear transmission shaft 107. A bevel gear 174 is fixed to the left end of the rear transmission shaft 107, and a bevel gear 175 that meshes with the bevel gear 174 is fixed to one end of the rear output shaft 108. Then, the power of the travel transmission shaft 104 is transmitted to the rear output shaft 108 via the rear transmission shaft 107. The power transmitted to the rear output shaft 108 is transmitted to the left and right rear wheels 13 via a transmission mechanism in the rear axle case 17, and the left and right rear wheels 13 rotate.

  In the gear-type PTO system power transmission path, a PTO first transmission gear 181 is fixed to the right end of the composite output shaft 102, and the PTO first transmission gear 181 is connected to a PTO second transmission gear 182 serving as a counter gear. Meshed. The PTO second transmission gear 182 is loosely fitted to the right end of the travel transmission shaft 104. Specifically, a sliding bearing 74 such as a bush is interposed between the PTO second transmission gear 182 and the travel transmission shaft 104 so as to be relatively rotatable. Instead of the sliding bearing 74, a rolling bearing such as a ball bearing may be used.

  The PTO second transmission gear 182 is meshed with a PTO third transmission gear 183 fixed in the middle of the PTO transmission shaft 106. A bevel gear 184 is fixed to the right end of the PTO transmission shaft 106, and a bevel gear 185 that meshes with the bevel gear 184 is fixed to one end of the PTO output shaft 109. Then, the power of the combined output shaft 102 is transmitted to the PTO output shaft 109 via the PTO transmission shaft 106.

  The power transmitted to the PTO output shaft 109 is shifted by an increase / decrease gear or a transmission mechanism built in the inter-shaft transmission case 50, and the lateral feed mechanism and each rotary case via a planting clutch, a planting mission case 47, and the like. 44. As a result, the lateral feed mechanism is actuated, and the seedling stage 41 slides in the left-right direction, and the rotary case 44 is rotationally actuated so that the two planting claws 45 alternately seedling the seedling stage. It can be taken out from the seedling mat on 41 and planted in the field.

  As described above, the rear second transmission gear 172 of the gear type traveling system power transmission path is supported by the PTO transmission shaft 106 of the gear type PTO system power transmission path, so that the transmission gear in the gear type traveling system power transmission path can be changed. The number of transmission shafts to be supported can be reduced. Therefore, the structure of the transmission 100 is simplified, the cost is reduced, and the assemblability is improved. Similarly, the PTO second transmission gear 182 of the gear type PTO system power transmission path is supported by the traveling speed change shaft 104 of the gear type traveling system power transmission path, thereby supporting the transmission gear in the gear type PTO system power transmission path. The number of transmission shafts to be reduced can be reduced. Therefore, the structure of the transmission 100 is simplified, the cost is reduced, and the assemblability is improved.

  Further, since the composite output shaft 102 is disposed on the front side of the transmission 100 and the PTO transmission shaft 106 and the rear transmission shaft 107 are disposed on the rear side of the transmission 100, the PTO transmission shaft 106 and the rear transmission shaft 107 are arranged from the composite output shaft 102. The structure up to this can be simplified, and the longitudinal width of the transmission 100 can be shortened.

  As shown in FIG. 2, the rotation direction of the combined output shaft 102 is the clockwise rotation direction when viewed from the left side, regardless of the working state. During the planting operation, the rotational direction of the traveling transmission shaft 104 is counterclockwise when viewed from the left side, and the rotational direction of the rear second transmission gear 172 is clockwise when viewed from the left side as indicated by an arrow X in a two-dot chain line. Direction. Further, during the planting operation, the rotation direction of the PTO transmission shaft 106 is clockwise as viewed from the left side as indicated by the solid arrow Y.

  That is, during the planting operation, the rear second transmission gear 172 and the PTO transmission shaft 106 are configured to have the same rotational direction, so that there is a difference in the rotational speed between the rear second transmission gear 172 and the PTO transmission shaft 106. It becomes difficult. Therefore, the rolling bearing 76 is hardly worn, and the life can be extended. Similarly, at the time of planting work, the rotational directions of the PTO second transmission gear 182 and the travel transmission shaft 104 are configured to be the same, so there is a difference in the rotational speed between the PTO second transmission gear 182 and the travel transmission shaft 104. It becomes difficult to occur. Therefore, the sliding bearing 74 is less likely to be worn and the life can be extended.

  As described above, in the rice transplanter 1 according to an embodiment of the present invention, the power shifted by the HMT 190 serving as a transmission is used to convert the power output from the combined output shaft 102 of the HMT 190 to the PTO transmission shaft 106 and the traveling transmission shaft. In the transmission 100 of the rice transplanter 1 configured to transmit to the transmission shaft 107, a travel transmission shaft 104, the PTO transmission shaft 106, and the rear transmission shaft 107 are provided in parallel with the composite output shaft 102. A gear-type PTO system power transmission path is formed on the combined output shaft 102, the traveling transmission shaft 104, and the PTO transmission shaft 106, and the combined output shaft 102, the traveling transmission shaft 104, the PTO transmission shaft 106, And a gear-type traveling system power transmission path on the rear transmission shaft 107, and the PTO transmission shaft in the gear-type traveling system power transmission path. Rear second transmission gear 172 to be traveling transmission gears on the 06 is intended to be loosely fitted to the PTO transmission shaft 106. Thereby, the number of transmission shafts can be reduced.

  Further, the output shaft 102 of the HMT 190 is disposed on the front side of the transmission 100, and the PTO transmission shaft 106 and the rear transmission shaft 107 serving as the traveling transmission shaft are disposed on the rear side of the transmission 100. Thereby, the front-rear width of the transmission 100 can be shortened.

  Further, during the operation, the PTO transmission shaft 106 and the rear second transmission gear 172 are configured to have the same rotational direction. Thereby, it becomes difficult to produce a difference in the rotational speed between the PTO transmission shaft 106 and the rear second transmission gear 172. Accordingly, the rolling bearing 76 serving as a bearing provided between the PTO transmission shaft 106 and the rear second transmission gear 172 is less likely to be worn and the life can be extended.

1 Rice transplanter 74 Sliding bearing 76 Rolling bearing (bearing)
100 Transmission 102 Composite output shaft (output shaft)
104 Traveling transmission shaft 106 PTO transmission shaft 107 Rear transmission shaft (traveling transmission shaft)
172 Rear second transmission gear (travel transmission gear)
190 HMT (transmission)

Claims (3)

  1. In the rice transplanter transmission configured to transmit the power shifted by the transmission from the output shaft of the transmission to the PTO transmission shaft and the traveling transmission shaft,
    In parallel with the output shaft, a travel transmission shaft, the PTO transmission shaft, and the travel transmission shaft are provided,
    A gear type PTO system power transmission path is formed on the output shaft, the traveling speed change shaft, and the PTO transmission shaft,
    A gear-type traveling system power transmission path is formed on the output shaft, the traveling speed change shaft, the PTO transmission shaft, and the traveling transmission shaft,
    The transmission of the rice transplanter, wherein the traveling transmission gear on the PTO transmission shaft in the gear-type traveling system power transmission path is loosely fitted to the PTO transmission shaft.
  2. 2. The rice transplanter according to claim 1, wherein an output shaft of the transmission is disposed on a front side of the transmission, and the PTO transmission shaft and the traveling transmission shaft are disposed on a rear side of the transmission. transmission.
  3.   The rice transplanter transmission according to claim 1 or 2, wherein the PTO transmission shaft and the traveling transmission gear are configured to have the same rotational direction during operation.
JP2011103826A 2011-05-06 2011-05-06 Rice transplanter transmission Active JP5808941B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2011103826A JP5808941B2 (en) 2011-05-06 2011-05-06 Rice transplanter transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2011103826A JP5808941B2 (en) 2011-05-06 2011-05-06 Rice transplanter transmission

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JP2012233544A JP2012233544A (en) 2012-11-29
JP5808941B2 true JP5808941B2 (en) 2015-11-10

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* Cited by examiner, † Cited by third party
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JP5931698B2 (en) * 2012-11-01 2016-06-08 ヤンマー株式会社 Rice transplanter

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* Cited by examiner, † Cited by third party
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JPH0725271B2 (en) * 1988-04-22 1995-03-22 株式会社クボタ Power transmission structure of walking type work machine
JP2000320644A (en) * 1999-05-17 2000-11-24 Kanzaki Kokyukoki Mfg Co Ltd Transmission for running vehicle
JP4220663B2 (en) * 2000-09-26 2009-02-04 株式会社Ihiシバウラ Hydraulic and mechanical continuously variable transmission
ITBO20060355A1 (en) * 2006-05-11 2007-11-12 Cnh Italia Spa Transmission hydromechanical cvt, in particular for an agricultural tractor
JP5355538B2 (en) * 2010-12-10 2013-11-27 ヤンマー株式会社 Farm work vehicle

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