JP6178853B2 - Transmission - Google Patents

Description

  The present invention relates to a transmission, and more particularly to a transmission capable of omitting a reverse-dedicated clutch, an idle shaft, and an idle gear.

  As a transmission used for an agricultural machine such as a construction machine or a tractor, for example, one disclosed in Patent Document 1 is known. Patent Document 1 discloses a first intermediate shaft having a gear that is always meshed with a gear provided on an input shaft, a second intermediate shaft having a gear that is always meshed with a gear provided on the first intermediate shaft, There is disclosed a multi-shaft transmission including an output shaft having a gear that is always meshed with a gear provided on a second intermediate shaft. In the transmission, a clutch exclusively for reverse travel is provided on the input shaft, and an idle shaft is provided between the input shaft and the first intermediate shaft. The idle shaft is provided with an idle gear that meshes with a gear provided on the input shaft. If the reverse clutch is connected, the rotation of the input shaft is reversed by the idle gear and transmitted to the first intermediate shaft, the second intermediate shaft and the output shaft.

JP-A-11-230278

  However, in the technique disclosed in Patent Document 1, it is necessary to provide a reverse-dedicated clutch, an idle shaft, and an idle gear that are not used during forward travel.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a transmission capable of omitting a reverse-dedicated clutch, an idle shaft, and an idle gear.

Means for Solving the Problems and Effects of the Invention

  According to the transmission of the first aspect, the first intermediate shaft having a gear that always meshes with the gear provided on the input shaft, and the second gear having the gear always meshed with the gear provided on the first intermediate shaft. An intermediate shaft and an output shaft having a gear that always meshes with a gear provided on the second intermediate shaft are provided. The first countershaft having a gear that always meshes with the gear provided on the input shaft has a gear that always meshes with the gear provided on the first intermediate shaft. The second countershaft having a gear that always meshes with the gear provided on the second intermediate shaft has a gear that always meshes with the gear provided on the output shaft. The gears provided on the input shaft, the first intermediate shaft, the first auxiliary shaft, the second intermediate shaft, the second auxiliary shaft and the output shaft rotate relative to the respective shafts by the switching means, It can be switched to a state of rotating integrally with each shaft. Since the gear that can transmit power can be selected by the switching means, for example, the forward movement is performed using five of the input shaft, the first intermediate shaft, the first auxiliary shaft, the second intermediate shaft, the second auxiliary shaft, and the output shaft. In this case, the reverse gear can be configured using four or six shafts. Since the reverse gear can be configured by using the gear used in the forward gear, there is an effect that the clutch, idle shaft and idle gear dedicated to the reverse can be omitted.

  According to the second aspect of the present invention, the power transmitted from the input shaft to the first intermediate shaft via the first auxiliary shaft is transmitted from the second intermediate shaft to the output shaft by the first power transmission means. . Further, the power transmitted from the input shaft to the first intermediate shaft is transmitted from the second intermediate shaft to the output shaft via the second auxiliary shaft by the second power transmission means. As a result, in addition to the effect of the first aspect, there is an effect that the rotation of the input shaft can be transmitted to the output shaft as forward rotation through five axes from the input shaft to the output shaft. Furthermore, since the number of shift stages of the transmission can be made the sum of the shift stage by the first power transmission unit and the shift stage by the second power transmission unit, there is an effect that the number of stages can be increased without increasing the number of shafts.

  According to the third aspect of the present invention, the power transmitted from the input shaft to the first intermediate shaft via the first auxiliary shaft by the third power transmission means passes from the second intermediate shaft to the second auxiliary shaft. And transmitted to the output shaft. The power transmitted from the input shaft to the first intermediate shaft is transmitted from the second intermediate shaft to the output shaft by the fourth power transmission means. As a result, in addition to the effect of the first or second aspect, the rotation of the input shaft can be reversed through four or six axes from the input shaft to the output shaft, and transmitted to the output shaft as a reverse rotation. Furthermore, since the number of shift stages of the transmission can be made the sum of the shift stage by the third power transmission unit and the shift stage by the third power transmission unit, there is an effect that the number of stages can be increased without increasing the number of shafts.

  According to the transmission of the fourth aspect, the friction type first clutch is disposed on any of the input shaft, the first intermediate shaft, and the first counter shaft, and the output shaft, the second intermediate shaft, or the second counter shaft. A friction type second clutch is disposed in any of the above. The first clutch and the second clutch are configured to be able to switch between connection and disconnection of power transmission between a shaft on which the first clutch and the second clutch are disposed and a gear disposed on the shaft. A coupling means for selectively coupling a gear and a shaft disposed on the shaft is disposed on a shaft other than the shaft on which the first clutch and the second clutch are disposed. Therefore, the number of friction clutches can be reduced by the amount of the coupling means.

  As a result, in addition to the effect of any one of the first to third aspects, the specific drag resistance can be reduced by the amount corresponding to the reduced number of friction clutches. As a result, friction loss can be suppressed and transmission efficiency can be improved. Also, the amount of oil supplied to the clutch for clutch lubrication and operation can be reduced. Thereby, there is an effect that energy loss for operating the transmission can be reduced. Furthermore, the oil pump that supplies pressure oil to the clutch can be reduced in size.

  According to the fifth aspect of the present invention, the input shaft, the first intermediate shaft, and the first auxiliary shaft are each provided with a plurality of gears, and the first clutch is the input shaft, the first intermediate shaft, or the first intermediate shaft. Two of them are arranged in parallel on any one of the one auxiliary shaft. One of the gears arranged on the shaft and the shaft are selected by the coupling means arranged on the input shaft other than the shaft on which the first clutch is arranged, the first intermediate shaft or the first auxiliary shaft. Combined. Therefore, when one of the first clutches is engaged and power is transmitted, the gear after the shift linked to the other of the first clutch can be selected by the coupling means with the other of the first clutch opened. . By engaging one of the first clutches while disengaging one of the first clutches at the time of shifting, in addition to the effect of claim 4, there is an effect of eliminating torque interruption and shift shock at the time of shifting. .

  According to the transmission of the sixth aspect, a plurality of the second clutches are arranged in parallel on any one of the output shaft, the second intermediate shaft, and the second auxiliary shaft. The power of the second intermediate shaft or the second countershaft transmitted when the plurality of second clutches are engaged is transmitted to the output shaft by the transmission means. Therefore, in addition to the effect of Claim 4 or 5, there exists an effect which can make the transmission torque capacity | capacitance of each 2nd clutch small.

  According to the transmission of the seventh aspect, the plurality of second clutches can be coupled to each other by the connecting means. Since the plurality of second clutches are coupled to each other by the connecting means, in addition to the effect of the sixth aspect, there is an effect that the power of the second intermediate shaft or the second auxiliary shaft can be reliably transmitted to the output shaft.

FIG. 1A is a schematic diagram showing one power transmission path when moving forward in the transmission according to the first embodiment, and FIG. 1B is a schematic diagram of the transmission showing another power transmission path when moving forward. FIG. 2A is a schematic diagram of a transmission that shows one power transmission path during reverse travel, and FIG. 2B is a schematic diagram of the transmission that shows another power transmission path during reverse travel. It is a skeleton figure of a transmission. It is a skeleton figure of the transmission in 2nd Embodiment.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. First, the transmission 1 according to the first embodiment of the present invention will be described with reference to FIGS. 1A to 3. FIG. 1A is a schematic diagram showing one power transmission path at the time of forward movement in the transmission 1 according to the first embodiment, and FIG. 1B is a schematic diagram of the transmission 1 showing another power transmission path at the time of forward movement. 2A is a schematic diagram of the transmission 1 showing one power transmission path during reverse travel, and FIG. 2B is a schematic diagram of the transmission 1 showing another power transmission path during reverse travel. The direction of rotation of each axis is shown by arrows.

  As shown in FIGS. 1A, 1B, 2A, and 2B, the transmission 1 includes an input shaft 10, a first countershaft 20, a first intermediate shaft 30, a second intermediate shaft 40, a second countershaft 60, and an output shaft. 50 are provided in parallel. The gears 11, 12, 13, and 14 of the input shaft 10 mesh with the gears 21, 22, 23, and 24 of the first countershaft 20, and the gears 31, 32, 33, and 34 of the first intermediate shaft 30, respectively. Mesh. The gear 27 of the first countershaft 20 meshes with the gear 37 of the first intermediate shaft 30. The gear 38 of the first intermediate shaft 30 meshes with the gear 48 of the second intermediate shaft 40. The gears 51 and 52 of the output shaft 50 mesh with the gears 61 and 62 of the second counter shaft 60 and mesh with the gears 41 and 42 of the second intermediate shaft 40, respectively. The gear 63 of the second countershaft 60 meshes with the gear 43 of the second intermediate shaft 40.

  Although details will be described later, as shown in FIG. 1A, the transmission 1 includes a first intermediate shaft from the input shaft 10 via the first auxiliary shaft 20 by the first power transmission means F1 configured by meshing of gears. The power transmitted to 30 is transmitted from the second intermediate shaft 40 to the output shaft 50. The transmission 1 is configured so that four forward speeds are obtained by the power transmission path of the input shaft 10 -the first countershaft 20 -the first intermediate shaft 30, and the power transmission path of the second intermediate shaft 40 -the output shaft 50 is obtained. It is configured to obtain two forward stages. Accordingly, the transmission 1 can obtain eight forward speeds obtained by multiplying the fourth speed and the second speed by the first power transmission means F1.

  Further, when the gear meshing is changed from the state shown in FIG. 1A, the transmission 1 is moved from the input shaft 10 by the second power transmission means F2 configured by the gear meshing as shown in FIG. 1B. The power transmitted to the intermediate shaft 30 is transmitted from the second intermediate shaft 40 to the output shaft 50 via the second counter shaft 60. The transmission 1 is configured so that four forward speeds are obtained by the power transmission path of the input shaft 10 -the first intermediate shaft 30, and by the power transmission path of the second intermediate shaft 40 -the second countershaft 60 -the output shaft 50. It is configured to obtain two forward stages. Therefore, the transmission 1 can obtain eight forward speeds obtained by multiplying the fourth speed and the second speed by the second power transmission means F2.

  From the above, the transmission 1 can obtain 16 forward speeds, which is the sum of 8 speeds by the first power transmission means F1 and 8 speeds by the second power transmission means F2. In the forward stage, the rotation of the input shaft 10 can be transmitted to the output shaft 50 as a forward rotation through five axes from the input shaft 10 to the output shaft 50.

  As shown in FIG. 2A, the transmission 1 has power transmitted from the input shaft 10 to the first intermediate shaft 30 via the first countershaft 20 by the third power transmission means R1 configured by meshing of the gears. Is transmitted from the second intermediate shaft 40 to the output shaft 50 via the second auxiliary shaft 60. The transmission 1 is configured such that four reverse speeds are obtained by a power transmission path of the input shaft 10 -the first countershaft 20 -the first intermediate shaft 30, and the second intermediate shaft 40 -the second countershaft 60 -the output shaft. Two reverse stages are obtained by 50 power transmission paths. Therefore, the transmission 1 can obtain eight reverse gears by multiplying the fourth gear and the second gear.

  In addition, when the gear meshing is changed from the state shown in FIG. 2A, the transmission 1 is moved from the input shaft 10 by the fourth power transmission means R2 configured by the gear meshing as shown in FIG. 2B. The power transmitted to the intermediate shaft 30 is transmitted from the second intermediate shaft 40 to the output shaft 50. The transmission 1 is configured such that four reverse speeds are obtained by the power transmission path of the input shaft 10 -first intermediate shaft 30, and two reverse speeds are obtained by the power transmission path of the second intermediate shaft 40 -output shaft 50. Configured as follows. Therefore, the transmission 1 can obtain eight reverse gears by multiplying the fourth gear and the second gear.

  From the above, the transmission 1 can obtain 16 reverse speeds, which is the sum of 8 speeds by the third power transmission means R1 and 8 speeds by the fourth power transmission means R2. In the case of the reverse speed, the rotation of the input shaft 10 can be reversed through four or six axes from the input shaft 10 to the output shaft 50 and transmitted to the output shaft 50 as a reverse rotation. Therefore, it is possible to increase the number of stages within a limited number of axes without increasing or increasing the number of axes of the transmission 1. Further, the reverse speed can be increased to the same number as the forward speed.

  Next, the configuration of the transmission 1 will be described with reference to FIG. FIG. 3 is a skeleton diagram of the transmission 1. FIG. 3 shows gears 11, 12, 13, 14, 31, 32, 33 that mesh with gears 21, 22, 23, 24 provided on the first countershaft 20 in order to facilitate understanding of gear meshing. , 34 and the second intermediate shaft 40 having gears 51, 52, 43 that mesh with gears 61, 62, 63 provided on the second auxiliary shaft 60. And the output shaft 50 is disassembled and illustrated. In the transmission 1, power from the engine 2 is input to the input shaft 10, and the shifted power is output from the front output member 3 and the rear output member 4 provided at both ends of the output shaft 50.

  The input shaft 10 is provided with gears 11, 12, 13, 14 and first hydraulically driven first clutches 15, 16 (wet multi-plate clutch, clutch pack). The gears 11, 12, 13, and 14 are rotatably provided on the input shaft 10. The gears 11 and 13 transmit the power of the input shaft 10 when the first clutch 15 is engaged, and the gears 12 and 14 transmit the power of the input shaft 10 when the first clutch 16 is engaged.

  The first countershaft 20 is rotatably provided with gears 21, 22, 23, and 24 that mesh with the gears 11, 12, 13, and 14, respectively. A dog clutch 25 is provided between the gears 21 and 23 to selectively couple one of the gears 21 and 23 to the first countershaft 20, and between the gears 22 and 24, one of the gears 22 and 24 is selectively placed. A dog clutch 26 coupled to the first countershaft 20 is provided. A gear 27 is fixed to the first countershaft 20.

  A gear 37 that meshes with the gear 27 is fixed to the first intermediate shaft 30, and a cylindrical shaft member 30a is rotatably provided. The shaft member 30a is rotatably provided with gears 31, 32, 33, and 34 that mesh with the gears 11, 12, 13, and 14, respectively. A dog clutch 35 is provided between the gears 31 and 33 to selectively couple one of the gears 31 and 33 to the shaft member 30a. Between the gears 32 and 34, one of the gears 32 and 34 is selectively coupled to the shaft member 30a. A dog clutch 36 coupled to 30a is provided. A gear 38 is fixed to the shaft member 30a.

  A gear 47 that meshes with the gear 37 is fixed to the second intermediate shaft 40, and a gear 48 that meshes with the gear 38 is rotatably provided. The gears 41 and 42 are rotatably provided on the second intermediate shaft 40, and the gear 43 is fixed to the gear 48 and is rotatably provided on the second intermediate shaft 40. A dog clutch 44 is provided between the gears 41 and 42 to selectively couple any one of the gears 41 and 42 to the second intermediate shaft 40. In addition, a dog clutch that selectively couples one or both of the gears 42 and 43 to the second intermediate shaft 40 by moving a sleeve having dog teeth formed on the inner periphery in the axial direction between the gears 42 and 43. 45 is provided. Note that the dog clutch 45 can also rotate both the gears 42 and 43 relative to the second central shaft 40 depending on the axial position of the sleeve.

  A gear 63 that meshes with the gear 43 is fixed to the second countershaft 60, and gears 61 and 62 are rotatably provided. A dog clutch 64 is provided between the gears 61 and 62 for selectively coupling one of the gears 61 and 62 to the second countershaft 60.

  The output shaft 50 includes gears 51 and 52, hydraulically driven second clutches 53 and 54 (wet multi-plate clutch, clutch pack), and a dog clutch 55 that selectively engages either of the gears 51 and 52. Provided. The gears 51 and 52 mesh with the gears 61 and 62, respectively, and are rotatably provided on the output shaft 50. The gear 51 transmits power to the output shaft 50 when the second clutch 53 is engaged. Further, the gear 51 transmits power to the output shaft 50 through the second clutches 53 and 54 arranged in parallel by the engagement of the second clutches 53 and 54 and the engagement of the dog clutch 55 with the gear 51. The gear 52 transmits power to the output shaft 50 by engaging the second clutch 54 and engaging the gear 52 of the dog clutch 55.

  The dog clutches 25, 26, 35, 36, 44, 45, 55, 64 convert the rotational force of an electric motor (not shown) into a linear motion by a cam, and move a selector fork (not shown) in the axial direction. This is a meshing mechanism having a non-hydraulic operating mechanism to be moved. The selector fork moves in the axial direction a sleeve having dog teeth formed on the inner periphery. Power is transmitted by meshing the dog teeth of the sleeve with the outer peripheral teeth formed on each gear.

  Next, the operation of the transmission 1 will be described. First, the forward gear will be described. In the first forward stage, the first clutch 15, dog clutches 35 and 64, and the second clutch 53 are operated, the gear 11 is the input shaft 10, the gear 31 is the shaft member 30 a, the gear 61 is the second countershaft 60, and the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 63, 61, 51.

  In the second forward stage, the first clutch 16, the dog clutches 36, 64, and the second clutch 53 are operated, the gear 12 is used as the input shaft 10, the gear 32 is used as the shaft member 30a, the gear 61 is used as the second countershaft 60, and the gear. 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 32, 38, 48, 63, 61, 51.

  The third forward stage operates the first clutch 15, the dog clutches 35 and 64, and the second clutch 53, the gear 13 as the input shaft 10, the gear 33 as the shaft member 30a, the gear 61 as the second countershaft 60, and the gear. 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 33, 38, 48, 63, 61, 51.

  In the fourth forward stage, the first clutch 16, the dog clutches 36, 64, and the second clutch 53 are operated, the gear 14 is used as the input shaft 10, the gear 34 is used as the shaft member 30a, and the gear 61 is used as the second counter shaft 60. 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 34, 38, 48, 63, 61, 51.

  The fifth forward stage operates the first clutch 15, the dog clutches 25, 44 and the second clutch 53, the gear 11 as the input shaft 10, the gear 21 as the first auxiliary shaft 20, and the gear 41 as the second intermediate shaft 40. The gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 21, 27, 37, 47, 41, 51.

  The sixth forward stage operates the first clutch 16, the dog clutches 26, 44 and the second clutch 53, the gear 12 as the input shaft 10, the gear 22 as the first countershaft 20, and the gear 41 as the second intermediate shaft 40. The gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 22, 27, 37, 47, 41, 51.

  The seventh forward stage operates the first clutch 15, the dog clutches 25, 44 and the second clutch 53, the gear 13 as the input shaft 10, the gear 23 as the first countershaft 20, and the gear 41 as the second intermediate shaft 40. The gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 23, 27, 37, 47, 41, 51.

  The eighth forward stage operates the first clutch 16, the dog clutches 26, 44 and the second clutch 53, the gear 14 as the input shaft 10, the gear 24 as the first countershaft 20, and the gear 41 as the second intermediate shaft 40. The gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 24, 27, 37, 47, 41, 51.

  The ninth forward stage operates the first clutch 15, the dog clutches 35, 64, 55, and the second clutch 54, the gear 11 as the input shaft 10, the gear 31 as the shaft member 30 a, and the gear 62 as the second countershaft 60. The gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 43, 63, 62, 52.

  In the forward 10th stage, the first clutch 16, the dog clutches 36, 64, 55 and the second clutch 54 are operated, the gear 12 is used as the input shaft 10, the gear 32 is used as the shaft member 30 a, and the gear 62 is used as the second countershaft 60. The gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 32, 38, 48, 43, 63, 62, 52.

  In the forward 11th stage, the first clutch 15, the dog clutches 35, 64, 55 and the second clutch 54 are operated, the gear 13 as the input shaft 10, the gear 33 as the shaft member 30 a, and the gear 62 as the second countershaft 60. The gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 33, 38, 48, 43, 63, 62, 52.

  In the forward 12th stage, the first clutch 16, the dog clutches 36, 64, 55 and the second clutch 54 are operated, the gear 14 is used as the input shaft 10, the gear 34 is used as the shaft member 30 a, and the gear 62 is used as the second countershaft 60. The gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 34, 38, 48, 43, 63, 62, 52.

  In the 13th forward, the first clutch 15, the dog clutches 25, 44, 55 and the second clutch 54 are operated, the gear 11 is used as the input shaft 10, the gear 21 is used as the first auxiliary shaft 20, and the gear 42 is used as the second intermediate shaft. 40, the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 21, 27, 37, 47, 42, 52.

  In the 14th forward stage, the first clutch 16, the dog clutches 26, 44, 55 and the second clutch 54 are operated, the gear 12 is used as the input shaft 10, the gear 22 is used as the first auxiliary shaft 20, and the gear 42 is used as the second intermediate shaft. 40, the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 22, 27, 37, 47, 42, 52.

  The forward 15 stage operates the first clutch 15, the dog clutches 25, 44, 55 and the second clutch 54, the gear 13 as the input shaft 10, the gear 23 as the first auxiliary shaft 20, and the gear 42 as the second intermediate shaft. 40, the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 23, 27, 37, 47, 42, 52.

  In the forward 16th stage, the first clutch 16, the dog clutches 26, 44, 55 and the second clutch 54 are operated, the gear 14 is used as the input shaft 10, the gear 24 is used as the first auxiliary shaft 20, and the gear 42 is used as the second intermediate shaft. 40, the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 24, 27, 37, 47, 42, 52.

  Next, the reverse gear will be described. In the first reverse stage, the first clutch 15, the dog clutches 35, 44, 45 and the second clutch 53 are operated, the gear 11 is used as the input shaft 10, the gear 31 is used as the shaft member 30a, and the gears 41 and 48 are used as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 41, 51.

  In the second reverse stage, the first clutch 16, the dog clutches 36, 44, 45 and the second clutch 53 are operated, the gear 12 is used as the input shaft 10, the gear 32 is used as the shaft member 30a, and the gears 41 and 48 are used as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 32, 38, 48, 41, 51.

  In the third reverse speed, the first clutch 15, the dog clutches 35, 44, 45 and the second clutch 53 are operated, the gear 13 as the input shaft 10, the gear 33 as the shaft member 30a, and the gears 41 and 48 as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 33, 38, 48, 41, 51.

  In the fourth reverse stage, the first clutch 16, the dog clutches 36, 44, 45 and the second clutch 53 are operated, the gear 14 is used as the input shaft 10, the gear 34 is used as the shaft member 30a, and the gears 41 and 48 are used as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 34, 38, 48, 41, 51.

  In the fifth reverse, the first clutch 15, the dog clutches 25, 45, 64 and the second clutch 53 are operated, the gear 11 is used as the input shaft 10, the gear 21 is used as the first auxiliary shaft 20, and the gear 43 is used as the second intermediate shaft. 40, the gear 61 is coupled to the second countershaft 60, and the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 21, 27, 37, 47, 43, 63, 61, 51.

  In the sixth reverse, the first clutch 16, the dog clutches 26, 45, 64, and the second clutch 53 are operated, the gear 12 is used as the input shaft 10, the gear 22 is used as the first auxiliary shaft 20, and the gear 43 is used as the second intermediate shaft. 40, the gear 61 is coupled to the second countershaft 60, and the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 22, 27, 37, 47, 43, 63, 61, 51.

  In the seventh reverse, the first clutch 15, the dog clutches 25, 45, 64 and the second clutch 53 are operated, the gear 13 is used as the input shaft 10, the gear 23 is used as the first auxiliary shaft 20, and the gear 43 is used as the second intermediate shaft. 40, the gear 61 is coupled to the second countershaft 60, and the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 23, 27, 37, 47, 43, 63, 61, 51.

  In the reverse eight stage, the first clutch 16, the dog clutches 26, 45, 64, and the second clutch 53 are operated, the gear 14 is used as the input shaft 10, the gear 24 is used as the first auxiliary shaft 20, and the gear 43 is used as the second intermediate shaft. 40, the gear 61 is coupled to the second countershaft 60, and the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 24, 27, 37, 47, 43, 63, 61, 51.

  In the reverse 9-th stage, the first clutch 15, the dog clutches 35, 44, 45, 55 and the second clutch 54 are operated, the gear 11 is used as the input shaft 10, the gear 31 is used as the shaft member 30 a, and the gears 42 and 48 are used as the second clutch. The gear 52 is coupled to the intermediate shaft 40 and the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 42, 52.

  In the reverse 10-stage, the first clutch 16, the dog clutches 36, 44, 45, 55 and the second clutch 54 are operated, the gear 12 is used as the input shaft 10, the gear 32 is used as the shaft member 30a, and the gears 42 and 48 are used as the second clutch. The gear 52 is coupled to the intermediate shaft 40 and the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 32, 38, 48, 42, 52.

  In the reverse 11th stage, the first clutch 15, the dog clutches 35, 44, 45, 55 and the second clutch 54 are operated, the gear 13 is used as the input shaft 10, the gear 33 is used as the shaft member 30 a, and the gears 42, 48 are used as the second clutch. The gear 52 is coupled to the intermediate shaft 40 and the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 33, 38, 48, 42, 52.

  In the reverse 12-speed, the first clutch 16, the dog clutches 36, 44, 45, 55 and the second clutch 54 are operated, the gear 14 is used as the input shaft 10, the gear 34 is used as the shaft member 30a, and the gears 42 and 48 are used as the second clutch. The gear 52 is coupled to the intermediate shaft 40 and the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 34, 38, 48, 42, 52.

  The reverse 13-stage operates the first clutch 15, the dog clutches 25, 45, 64, 55 and the second clutch 54, and the gear 11 is used as the input shaft 10, the gear 21 is used as the first countershaft 20, and the gear 43 is used as the second clutch. The intermediate shaft 40, the gear 62 is coupled to the second countershaft 60, and the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 21, 27, 37, 47, 43, 63, 62, 52.

  The reverse 14-stage operates the first clutch 16, dog clutches 26, 45, 64, 55 and the second clutch 54, the gear 12 as the input shaft 10, the gear 22 as the first countershaft 20, and the gear 43 as the second The intermediate shaft 40, the gear 62 is coupled to the second countershaft 60, and the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 12, 22, 27, 37, 47, 43, 63, 62, 52.

  The reverse 15 stage operates the first clutch 15, dog clutches 25, 45, 64, 55 and the second clutch 54, the gear 13 as the input shaft 10, the gear 23 as the first countershaft 20, and the gear 43 as the second The intermediate shaft 40, the gear 62 is coupled to the second countershaft 60, and the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 13, 23, 27, 37, 47, 43, 63, 62, 52.

  The reverse 16-stage operates the first clutch 16, the dog clutches 26, 45, 64, 55 and the second clutch 54, the gear 14 as the input shaft 10, the gear 24 as the first countershaft 20, and the gear 43 as the second The intermediate shaft 40, the gear 62 is coupled to the second countershaft 60, and the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 14, 24, 27, 37, 47, 43, 63, 62, 52.

  In agricultural machinery and construction machinery, there is a request to repeatedly change the traveling direction following deceleration of the vehicle, and therefore the transmission 1 has a request for a shuttle shift that alternately switches between a forward gear and a reverse gear. Therefore, a shuttle shift between the first forward speed and the reverse first speed will be described. As described above, the first forward stage operates the first clutch 15, the dog clutches 35 and 64, and the second clutch 53, the gear 11 as the input shaft 10, the gear 31 as the shaft member 30 a, and the gear 61 as the second countershaft 60. In addition, the gear 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 63, 61, 51.

  In the case of switching to the first reverse speed, the second clutch 53 is released and the dog clutch 45 is operated with the first clutch 15 and the dog clutch 35 maintained, and then the second clutch 54 is operated. As a result, the gear 11 is coupled to the input shaft 10, the gear 31 is coupled to the shaft member 30 a, the gears 42 and 48 are coupled to the second intermediate shaft 40, and the gear 52 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 11, 31, 38, 48, 42, 52.

  In the case of the first forward speed, power is transmitted from the second intermediate shaft 40 to the output shaft 50 via the second auxiliary shaft 60, whereas in the case of the first reverse speed, the output shaft 50 is reversed. Therefore, power is transmitted from the second intermediate shaft 40 to the output shaft 50 without passing through the second countershaft 60. Therefore, the power transmission path from the input shaft 10 to the second intermediate shaft 40 is shared, the forward path for transmitting power from the second intermediate shaft 40 to the output shaft 50 via the second auxiliary shaft 60, and the second A reverse path for transmitting power from the intermediate shaft 40 to the output shaft 50 without passing through the second auxiliary shaft 60 is created in advance. By alternately switching the connection and disconnection of the second clutches 53 and 54, the forward path and the reverse path are smoothly switched. Therefore, a smooth shuttle shift can be performed while simplifying the control of the transmission 1.

  In addition, each of the shuttle shifts of the second forward speed—the second reverse speed, the third forward speed—the third reverse speed, and the fourth forward speed—the fourth reverse speed, each changes the gear ratio of the power transmission path from the input shaft 10 to the second intermediate shaft 40. By setting to a step, it can be performed in the same manner as switching from one forward step to one reverse step.

  As described above, the first countershaft 20 having the gears 21, 22, 23, 24 that always mesh with the gears 11, 12, 13, 14 provided on the input shaft 10 is provided on the first intermediate shaft 30. A gear 27 that always meshes with the gear 37 is provided. The second countershaft 60 having the gear 63 that is always meshed with the gear 43 provided on the second intermediate shaft 40 has a gear that is always meshed with gears 51 and 52 provided on the output shaft 50. Gears 11, 12, 13, 14, which are rotatably provided on the input shaft 10, the first intermediate shaft 30, the first auxiliary shaft 20, the second intermediate shaft 40, the second auxiliary shaft 60 and the output shaft 50. 21, 22, 23, 24, 31, 32, 33, 34, 41, 42, 43, 48, 51, 52, 61, 62 include first clutch 15, 16, second clutch 53, 54 and dog clutch 25, By 26, 35, 36, 44, 45, 55, 64, it is possible to switch between a state of rotating relative to each axis and a state of rotating integrally with each axis.

  As a result, since a gear capable of transmitting power can be selected, five of the input shaft 10, the first intermediate shaft 30, the first auxiliary shaft 20, the second intermediate shaft 40, the second auxiliary shaft 60, and the output shaft 50 are selected. When the forward shift speed is configured using, the reverse shift speed can be configured using four or six axes. Since the reverse gear can be configured using the gear used in the forward gear, the reverse clutch, idle shaft and idle gear can be omitted. Further, since the reverse gear can be configured using the gears used in the forward gear, the reverse gear and the reverse gear can be set to the same number.

  The input shaft 10 is provided with hydraulically driven first clutches 15 and 16 (wet multi-plate clutch), and the output shaft 50 is provided with hydraulically driven second clutches 53 and 54 (wet multi-plate clutch). Is done. The first clutch 15, 16 and the second clutch 53, 54 switch the power transmission / disconnection between the gears disposed on the input shaft 10 and the output shaft 50 and each shaft. The first intermediate shaft 30, the first countershaft 20, the second intermediate shaft 40, and the second countershaft 60 are non-hydraulic dog clutches 25 that selectively couple the shaft and the gear disposed on the shaft. 26, 35, 36, 44, 45, 64 are arranged. Therefore, the number of wet multi-plate clutches can be reduced by adopting a non-hydraulic dog clutch. As a result, the transmission 1 can reduce drag resistance unique to the hydraulically driven wet multi-plate clutch, and can reduce the amount of oil supplied to the clutch for lubrication and operation of the clutch. Furthermore, the oil pump that supplies pressure oil to the clutch can be reduced in size. As a result, the transmission 1 can be reduced in weight and cost can be reduced.

  Further, the first clutches 15 and 16 are juxtaposed with the input shaft 10, and the gears 21, 22, 23, 24, 31, 32, 33 mesh with the gears 11, 12, 13, 14 provided on the input shaft 10. , 34 are provided on the first countershaft 20 and the first intermediate shaft 30. The gears 21, 22, 23, 24, 31, 32, 33, and 34 are selectively coupled to the respective shafts by the dog clutches 25, 26, 35, and 36. Therefore, in both the forward speed and the reverse speed, when one of the first clutches 15 and 16 is engaged and power is transmitted, the dog clutches 25 and 26 are opened with the other of the first clutches 15 and 16 open. , 35, and 36 can select (pre-shift) a gear after shifting that is linked to the other of the first clutches 15 and 16. At the time of shifting, it is possible to smoothly switch to the preshifted gear position by engaging one of the first clutches 15 and 16 while disengaging one of the first clutches 15 and 16. Therefore, it is possible to eliminate torque loss and shift shock at the time of shifting.

  Further, in the case of the first forward speed to the eighth forward speed and the reverse first speed to the reverse eighth speed (especially at the time of starting), in addition to the second clutch 53, the dog clutch 55 and the second clutch 54 are operated, so that the output shaft 50 The second clutches 53 and 54 can be coupled. As a result, the power of the input shaft 10 can be transmitted to the output shaft 50 through the two second clutches 53 and 54. Since the vehicle (agricultural machinery, construction machinery, etc.) can be driven (started) by the combined torque of the second clutches 53, 54, the transmission torque capacity of each of the second clutches 53, 54 can be reduced. As a result, each of the second clutches 53 and 54 can be reduced in weight and size.

  Further, since the second clutches 53 and 54 can be coupled to each other by the dog clutch 55, the power of the second intermediate shaft 40 is surely transmitted to the output shaft 50 when the second clutches 53 and 54 are coupled to each other by the dog clutch 55. Can communicate to. Since the second clutches 53 and 54 are mechanically coupled by the dog clutch 55, the control can be simplified and the durability can be improved.

  The coupling of the second clutches 53 and 54 is basically performed simultaneously with the maximum value of the transmission torque capacity of each clutch. However, the drive wheels (not shown) may slip depending on the condition of the road surface on which the vehicle travels. In that case, the torque can be reduced as appropriate. By adjusting the torque of the second clutches 53 and 54 within the range of the transmission torque capacity, it is possible to avoid slipping of the drive wheels and improve the durability of the second clutches 53 and 54.

  Next, a second embodiment will be described with reference to FIG. In the first embodiment, a case where four forward stages (16 forward stages and 16 reverse stages in total) are obtained by the power transmission path of the input shaft 10 -the first countershaft 20 -the first intermediate shaft 30 is used. Explained. On the other hand, in the second embodiment, the transmission 101 that can obtain two forward speeds (8 forward speeds-8 reverse speeds as a whole) through the power transmission path of the input shaft 110, the first countershaft 120, and the first intermediate shaft 130. Will be described. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 4 is a skeleton diagram of the transmission 101 according to the second embodiment.

  As shown in FIG. 4, the transmission 101 includes an input shaft 110, a first countershaft 120, a first intermediate shaft 130, a second intermediate shaft 40, a second countershaft 60, and an output shaft 50 provided in parallel. In the transmission 101, power from the engine 2 is input to the input shaft 110, and the shifted power is output from the front output member 3 and the rear output member 4 provided at both ends of the output shaft 50. The gears 111 and 112 of the input shaft 110 mesh with the gears 121 and 122 of the first countershaft 120 and mesh with the gears 131 and 132 of the first intermediate shaft 130, respectively.

  The input shaft 110 is provided with gears 111 and 112 and hydraulically driven first clutches 115 and 116 in parallel. The gears 111 and 112 are rotatably provided on the input shaft 110. The gear 111 transmits the power of the input shaft 110 when the first clutch 115 is engaged, and the gear 112 transmits the power of the input shaft 110 when the first clutch 116 is engaged.

  The first countershaft 120 is rotatably provided with gears 121 and 122 that mesh with the gears 111 and 112, respectively. A dog clutch 125 that selectively couples the gears 121 and 122 to the first countershaft 120 is provided between the gears 121 and 123. The gear 27 is fixed to the first countershaft 120.

  A gear 37 that meshes with the gear 27 is fixed to the first intermediate shaft 130, and a cylindrical shaft member 30a is rotatably provided. Gears 131 and 132 meshing with the gears 111 and 112 are rotatably provided on the shaft member 30a. A dog clutch 135 for selectively coupling the gears 131 and 132 to the shaft member 30a is provided between the gears 131 and 132.

  Next, the operation of the transmission 101 will be described. In the first forward stage, the first clutch 115, the dog clutches 135 and 64, and the second clutch 53 are operated, the gear 111 is used as the input shaft 110, the gear 131 is used as the shaft member 30a, and the gear 61 is used as the second counter shaft 60. 51 is coupled to the output shaft 50. The power of the input shaft 110 is transmitted to the output shaft 50 through the gears 111, 131, 38, 48, 63, 61, 51.

  In the second forward stage, the first clutch 116, the dog clutches 135 and 64, and the second clutch 53 are operated, the gear 112 is used as the input shaft 110, the gear 132 is used as the shaft member 30a, and the gear 61 is used as the second counter shaft 60. 51 is coupled to the output shaft 50. The power of the input shaft 10 is transmitted to the output shaft 50 through the gears 112, 132, 38, 48, 63, 61, 51. Since the third forward speed to the eighth forward speed can be realized by switching the power transmission path between the six axes in the same manner as the transmission 1 described in the first embodiment, the description thereof is omitted.

  In the first reverse stage, the first clutch 115, the dog clutches 135, 44, and 45 and the second clutch 53 are operated. The gear 111 is used as the input shaft 110, the gear 131 is used as the shaft member 30a, and the gears 41 and 48 are used as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 110 is transmitted to the output shaft 50 through the gears 111, 131, 38, 48, 41, 51.

  In the second reverse stage, the first clutch 116, the dog clutches 135, 44, 45 and the second clutch 53 are operated, the gear 112 is used as the input shaft 110, the gear 132 is used as the shaft member 30a, and the gears 41 and 48 are used as the second intermediate shaft. 40, the gear 51 is coupled to the output shaft 50. The power of the input shaft 110 is transmitted to the output shaft 50 through the gears 112, 132, 38, 48, 41, 51. Note that the reverse 3 to reverse 8 can be realized by switching the power transmission path between the six axes in the same manner as the transmission 1 described in the first embodiment, and thus the description thereof is omitted. As in the transmission 101 in the second embodiment, a desired shift speed can be obtained by appropriately setting the number of gears provided on each shaft.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the number of gears arranged on each shaft and the number of gears that can be changed can be set as appropriate.

  In each of the above-described embodiments, the case where the first clutches 15, 16, 115, 116 are arranged on the input shafts 10, 110 has been described. However, the present invention is not necessarily limited thereto. Of course, the first clutches 15, 16, 115, 116 can be arranged on the first countershafts 20, 120 or the first intermediate shafts 30, 130. Even when the first clutches 15, 16, 115, 116 are arranged on the first countershafts 20, 120 or the first intermediate shafts 30, 130, one of the first clutches 15, 16 and one of the first clutches 115, 116 are also provided. This is because the other of the first clutches 15 and 16 and the other of the first clutches 115 and 116 can be released to perform pre-shifting while the power is transmitted to the second intermediate shaft 40. That is, the first clutches 15, 16, 115, and 116 may be arranged on the shaft that performs gear shifting.

  In each of the above embodiments, the case where the second clutches 53 and 54 are arranged on the output shaft 50 has been described, but the present invention is not necessarily limited thereto. It is naturally possible to arrange the second clutches 53 and 54 on the second intermediate shaft 40 or the second counter shaft 60. Even when the second clutches 53 and 54 are arranged on the second intermediate shaft 40 or the second countershaft 60, it is possible to change the speed in the power transmission path of the second intermediate shaft 40-the second countershaft 60-the output shaft 50. is there. That is, the second clutches 53 and 54 need only be arranged on the shaft that performs gear shifting similarly to the first clutches 15, 16, 115, and 116.

DESCRIPTION OF SYMBOLS 1,101 Transmission 10,110 Input shaft 20,120 1st countershaft 30,130 1st intermediate shaft 40 2nd intermediate shaft 50 Output shaft 60 2nd subshaft 11,12,13,14,21,22,23 , 24, 27, 31, 32, 33, 34, 37, 41, 42, 43, 47, 48, 51, 52, 61, 62, 63, 111, 112, 121, 122, 131, 132 Gears 15, 16 , 115, 116 First clutch (part of switching means)
25, 26, 35, 36, 44, 45, 64, 125, 135 Dog clutch (part of switching means, coupling means)
53, 54 Second clutch (part of switching means)
55 Dog clutch (part of switching means, transmission means, coupling means)
F1 first power transmission means F2 second power transmission means R1 third power transmission means R2 fourth power transmission means

Claims (7)

A first intermediate shaft having a gear that is always meshed with a gear provided on the input shaft; a second intermediate shaft having a gear that is always meshed with a gear provided on the first intermediate shaft; 2 In a transmission including an output shaft having a gear that is always meshed with a gear provided on an intermediate shaft,
A first countershaft having a gear that always meshes with a gear provided on the input shaft, and a gear that always meshes with a gear provided on the first intermediate shaft;
A second countershaft having a gear that always meshes with a gear provided on the second intermediate shaft, and a gear that always meshes with a gear provided on the output shaft;
A state in which gears provided on the input shaft, the first intermediate shaft, the first counter shaft, the second intermediate shaft, the second sub shaft, and the output shaft rotate relative to each shaft. And a switching means for switching between a state of rotating integrally with each shaft.   The gear and the switching means are first power transmission means for transmitting power transmitted from the input shaft to the first intermediate shaft via the first auxiliary shaft from the second intermediate shaft to the output shaft, And a second power transmission means for transmitting the power transmitted from the input shaft to the first intermediate shaft to the output shaft from the second intermediate shaft via the second auxiliary shaft. The transmission according to claim 1.   The gear and the switching means transmit power transmitted from the input shaft to the first intermediate shaft via the first auxiliary shaft from the second intermediate shaft to the output shaft via the second auxiliary shaft. And a fourth power transmission means for transmitting the power transmitted from the input shaft to the first intermediate shaft from the second intermediate shaft to the output shaft. The transmission according to claim 1 or 2. The switching means includes a friction type first clutch disposed on either the input shaft, the first intermediate shaft or the first counter shaft;
A friction-type second clutch disposed on any one of the output shaft, the second intermediate shaft, and the second countershaft;
A coupling means for selectively coupling the shaft and the gear disposed on the shaft, the shaft being disposed on a shaft other than the shaft on which the first clutch and the second clutch are disposed;
The first clutch and the second clutch are configured so as to be able to switch between connection and disconnection of power transmission between a shaft on which the first clutch and the second clutch are disposed and a gear disposed on the shaft. The transmission according to any one of claims 1 to 3. The input shaft, the first intermediate shaft, and the first countershaft are each provided with a plurality of gears,
Two of the first clutches are arranged side by side on any of the input shaft, the first intermediate shaft, and the first auxiliary shaft,
The coupling means is disposed on the input shaft other than the shaft on which the first clutch is disposed, on the first intermediate shaft, on the first sub shaft, and on a gear disposed on the shaft. 5. The transmission according to claim 4, wherein one and the shaft are selectively coupled. A plurality of the second clutches are arranged in parallel on any one of the output shaft, the second intermediate shaft, and the second auxiliary shaft,
Any one of the output shaft, the second intermediate shaft, and the second counter shaft is configured to transmit the power of the second intermediate shaft or the second counter shaft transmitted by the plurality of second clutches being engaged. 6. The transmission according to claim 4, further comprising transmission means for transmitting to the output shaft.   The transmission according to claim 6, further comprising a coupling means configured to couple the plurality of second clutches to each other.

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