JP2010038079A - Engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve the following problems: in a power transmission mechanism with a transmission direction significantly changed in a transmission passage leading from an engine to a drive device such as a mower, in order not to twist an endless band such as a belt, it is conceivable that a single power transmission case having a direction changing structure is provided to the engine itself, however, when power is distributed to a plurality of drive devices, enlargement of the power transmission case is unavoidable. <P>SOLUTION: At least one second power transmission case 34 internally supporting a second output shaft 38 arranged parallel to a crankshaft 25 and inputting power from the crankshaft 25 is juxtaposed to a first power transmission case 33 internally supporting a first input shaft 43 arranged parallel to the crankshaft 25 and inputting power from the crankshaft 25 and a first output shaft 44 perpendicular to the first input shaft 43. Power form the crankshaft 25 is supplied to the plurality of drive devices 5, 6 outside of the engine 1 through the first power transmission case 33 and second power transmission case 34. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a technology for an engine having a crankshaft in a substantially horizontal direction, and more particularly to a technology for supplying power from the crankshaft to a driving device outside the engine.

2. Description of the Related Art Conventionally, a technique for transmitting power from an engine to a shaft that is disposed perpendicular to a substantially horizontal crankshaft in the engine is known (for example, see Patent Document 1). In this technique, the work vehicle is an Ackermann-type lawn mower, and the lawn mower is provided with an engine having a crankshaft in a substantially horizontal direction in the front-rear direction. A counter shaft is provided, and a mower having an input shaft perpendicular to the crank shaft in the vertical direction is provided behind the counter shaft. A crank pulley at the front end of the crankshaft, a pair of counter pulleys at the left and right ends of the countershaft, and an input pulley at the upper end of the input shaft, respectively. A single belt is wound around the input pulley, and the power from the engine is transmitted from the crank pulley to the lower counter pulley via the single belt, where the transmission direction is changed by 90 degrees, And the rotary blade of the mower connected to the input pulley is driven to rotate.
Thus, in a power transmission mechanism in which the transmission direction changes greatly in the middle of a transmission path from an engine to a working machine such as a mower or an axle drive device (hereinafter simply referred to as “drive device”), a pulley・ Because endless belts such as belts and chains that wrap around rotation transmission bodies such as sprockets are twisted greatly at the direction change position in the middle, the service life of the endless belts is shortened and loud noise is generated. Furthermore, in order to change the direction of the endless belt, it is necessary to secure a large winding space at the direction changing position, and this winding space is a great limitation in reducing the size of the work vehicle. In addition, since three rotation transmission bodies consisting of a crank pulley, a pair of left and right counter pulleys, and an input pulley are wound by a long endless belt, transmission efficiency is poor, and during assembly, between these rotation transmission bodies Therefore, it cannot be said that the work efficiency during assembly is good.
Therefore, in order to solve such a problem, a single power transmission in which an input shaft arranged in parallel to the crankshaft for inputting power from the crankshaft and an output shaft perpendicular to the input shaft is internally supported. A technique is conceivable in which a case is provided in the engine itself and power is distributed to the drive device via the power transmission case. In this case, a direction changing structure such as a bevel gear is interposed between the input shaft and the output shaft in the power transmission case.
Japanese Utility Model Publication No. 60-10427

However, when power is distributed from such a single power transmission case to a plurality of driving devices, it is necessary to increase the output horsepower from the power transmission case, and the direction change structure becomes large accordingly, and the power transmission case There was a problem that the enlargement of the size was inevitable.
Furthermore, since there is only one type of output rotation speed from the power transmission case, it is not possible to input the optimal rotation speed according to the transmission shaft diameter, etc. to all the drive devices, generating a large noise, There was a problem that transmission efficiency deteriorated.

The problem to be solved by the present invention is as described above. Next, means for solving the problem will be described.
That is, according to claim 1, in an engine having a crankshaft in a substantially horizontal direction, a first input shaft that is arranged in parallel to the crankshaft and inputs power from the crankshaft and a first input shaft that is perpendicular to the first input shaft. At least one second power transmission case that internally supports a second input shaft that is arranged in parallel to the crankshaft and that inputs power from the crankshaft to the first power transmission case that supports the output shaft internally. By arranging them side by side, the power from the crankshaft can be supplied to a plurality of drive devices outside the engine via the first power transmission case and the second power transmission case.
According to a second aspect of the present invention, an oil pan is provided at a lower portion of the engine, and the first power transmission case is attached to the oil pan.
According to a third aspect of the present invention, a notch is formed below the oil pan, and the first power transmission case is disposed in the notch.
According to a fourth aspect of the present invention, the second power transmission case internally supports a second output shaft perpendicular to the second input shaft, and supplies rotational power from the second output shaft to the driving device.
According to a fifth aspect of the present invention, the second power transmission case includes a hydraulic pump and supplies hydraulic power from the hydraulic pump to the driving device.
The power from the crankshaft is input to the first input shaft and the second input shaft through a single endless belt.
In claim 7, the power from the crankshaft includes a first endless belt from the crankshaft to the first input shaft, and a second endless belt from the crankshaft to a single or a plurality of second input shafts. This is input to each input shaft via.
According to an eighth aspect of the present invention, an endless belt is provided for each input shaft between the crankshaft and a plurality of input shafts including the first input shaft and a single or a plurality of second input shafts.
According to a ninth aspect of the present invention, the first input shaft and the second input shaft are arranged on the same crankshaft end side in the axial direction of the crankshaft.
According to a tenth aspect of the present invention, the first input shaft and the second input shaft are arranged on opposite crankshaft end portions in the axial direction of the crankshaft.

Since this invention was comprised as mentioned above, there exists an effect shown below.
That is, according to claim 1, in an engine having a crankshaft in a substantially horizontal direction, a first input shaft that is arranged in parallel to the crankshaft and inputs power from the crankshaft and a first input shaft that is perpendicular to the first input shaft. At least one second power transmission case that internally supports a second input shaft that is arranged in parallel to the crankshaft and that inputs power from the crankshaft to the first power transmission case that supports the output shaft internally. By arranging in parallel, the power from the crankshaft can be supplied to a plurality of driving devices outside the engine via the first power transmission case and the second power transmission case. A second power transmission case (hereinafter simply referred to as “power transmission case”) is provided in the middle of the transmission path, and the endless belt is connected from the crankshaft to the input shaft and from the output shaft to the drive device. Divided can be wound, since the endless belt is not be diverted in the middle pathway, large twisting even a longer service life of the endless band without generation can also be reduced noise. At the same time, the length of each endless belt is shortened, making it difficult for slips and vibrations to occur, improving transmission efficiency and eliminating the need for position adjustment between rotating transmission bodies during assembly, thus improving work efficiency during assembly. . Further, a dedicated power transmission case can be provided for each drive device, and the output horsepower from the power transmission case can be small, and the direction change structure in the power transmission case is accordingly reduced. Miniaturization can be achieved. At the same time, it is possible to input the optimum number of rotations for each drive device from the corresponding power transmission case via an endless belt, and since each drive device is driven stably, no loud noise is generated and transmission efficiency is reduced. Will be further improved.
In claim 2, since an oil pan is provided at a lower portion of the engine and the first power transmission case is attached to the oil pan, the first power transmission case can be easily attached to the engine using the oil pan. This improves the work efficiency of the power transmission case mounting operation during assembly. Furthermore, the power transmission case can be set to the same vibration system as the engine, and the vibration-proofing measures can be simplified and the cost can be reduced.
In the third aspect of the present invention, a notch is formed on the lower side of the oil pan, and the first power transmission case is disposed in the notch, so that the first power transmission case is formed using the notch. It can be arranged compactly, and the engine can be made smaller to reduce the size of the work vehicle.
In the present invention, the second power transmission case supports the second output shaft perpendicular to the second input shaft and supplies rotational power to the drive device from the second output shaft. Power can be supplied from the second power transmission case to each drive unit via a mechanical transmission system consisting of endless belts and gears with an inexpensive and simple configuration, reducing component costs and improving transmission efficiency Can be achieved.
In the present invention, the second power transmission case includes a hydraulic pump and supplies hydraulic power from the hydraulic pump to the driving device. Therefore, power from the engine is supplied from the second power transmission case to the hydraulic pipe. It is possible to supply to each driving device via a hydraulic transmission system composed of, etc., and to drive the driving device with high accuracy to improve driving performance and turning performance.
In claim 6, since the power from the crankshaft is input to the first input shaft and the second input shaft through a single endless belt, the number of endless belts necessary for power transmission is reduced. Therefore, it is possible to reduce the cost of parts and improve the maintainability by reducing the number of parts.
In claim 7, the power from the crankshaft includes a first endless belt from the crankshaft to the first input shaft, and a second endless belt from the crankshaft to a single or a plurality of second input shafts. When the drive device is of two types, a drive device corresponding to the first power transmission case and a drive device corresponding to the second power transmission case, the crankshaft By simply changing the power transmission configuration up to the input shaft, it is possible to input the optimum number of rotations for each type of drive unit, and to stably drive each drive unit with the minimum number of endless belts. It is possible to reduce the cost of parts and improve the maintainability by reducing the number of parts.
In the eighth aspect of the present invention, an endless belt is provided for each input shaft between the crank shaft and the plurality of input shafts including the first input shaft and the single or plural second input shafts. Even if there are multiple types of drive units corresponding to the two power transmission cases and the optimum number of revolutions differs for each drive unit, each drive unit can be changed by simply changing the power transmission configuration from the crankshaft to the input shaft. Therefore, it is possible to input the optimum rotation speed to each drive device, to reliably drive each drive device reliably, and to greatly improve the drive performance of each drive device.
In claim 9, since the first input shaft and the second input shaft are arranged on the same crankshaft end side in the axial direction of the crankshaft, the crankshaft, the first input shaft, and the second input shaft Can be arranged close to each other, and the length of the transmission path from the crankshaft to these first and second input shafts can be shortened. By reducing the size of the engine, it is possible to reduce the size of the engine and improve the transmission efficiency.
In claim 10, since the first input shaft and the second input shaft are arranged on the opposite crankshaft end side in the axial direction of the crankshaft, the driving device corresponding to the first power transmission case, When the drive device corresponding to the second power transmission case is arranged separately on one end side and the other end side of the crankshaft, the length of the transmission path from the crankshaft to each drive device is reduced. Therefore, the work vehicle can be downsized by reducing the transmission space, and the transmission efficiency can be improved by suppressing slip, vibration, and the like. For example, when the first power transmission case for the work machine is disposed on the front end side of the crankshaft and the second power transmission case for the axle drive device is disposed on the rear end side of the crankshaft, It is an arrangement suitable for front-mounted work machines and rear-wheel drive work vehicles. Conversely, a second power transmission case for the axle drive device is arranged on the front end side of the crankshaft, and the rear end of the crankshaft. In the case where the first power transmission case for the work implement is arranged on the part side, the arrangement configuration is suitable for the rear work implement / front wheel drive type work vehicle. Can be shortened.

Next, embodiments of the invention will be described.
1 is a partial sectional side view of a work vehicle equipped with an engine according to a first embodiment of the present invention, FIG. 2 is a schematic plan view showing a power transmission configuration according to the first embodiment, and FIG. 3 is a first embodiment. 4 is a side view, FIG. 5 is a partial side sectional view of the transmission box of the first embodiment, and FIG. 5A is a partial sectional side view of the first transmission box. 5 (b) is a partial cross-sectional side view of the second transmission box, FIG. 6 is a partial front view showing another embodiment of the belt mechanism of the first embodiment, and FIG. 7 is an engine according to the second embodiment of the present invention. FIG. 8 is a schematic plan view showing a power transmission configuration according to the second embodiment, and FIG. 8A is a schematic plan view when the rear axle drive device is provided separately on the left and right, and FIG. b) is a schematic plan view when an axle drive device is provided in the front and rear, and FIG. 9 shows another embodiment of the belt mechanism of the second embodiment. FIG. 9A is a partial front view, and FIG. 9A is a partial front view showing a belt mechanism when a belt is wound separately on a first input shaft and left and right second input shafts, and FIG. FIG. 10 is a partial front view of an engine according to a third embodiment of the present invention, FIG. 11 is a side view thereof, and FIG. 12 is a third embodiment. FIG. 13 is a partial front view showing another form of the belt mechanism of the third embodiment, and FIG. 13A shows the first input shaft and the left and right pump shafts. FIG. 13B is a partial front view showing the belt mechanism when the belt is wound for each axis, and FIG. 14 is a fourth front view showing the belt mechanism when the belt is wound separately. FIG. 15 is a side view of the engine according to the embodiment, and FIG. 16 is related to the fifth embodiment of the present invention. Front view of an engine, FIG. 17 is a same side view.
In the present embodiment, the direction of the arrow 54 shown in FIG.

First, the overall configuration of a work vehicle 2 equipped with the engine 1 according to the first embodiment of the present invention will be described with reference to FIGS.
The work vehicle 2 is an Ackermann-steered lawn mower, and includes a vehicle frame 3, a rear axle drive device 5 supported on the rear portion of the vehicle frame 3, and a front portion supported on the front portion of the vehicle frame 3. An axle support device 4, an engine 1 supported by a vehicle frame 3 between the front axle support device 4 and the rear axle drive device 5, and a mower 6 suspended below the vehicle frame 3 so as to be movable up and down. I have.

  Of these, the rear axle driving device 5 includes a hydraulic pump 7, a hydraulic motor 8 fluidly connected to the hydraulic pump 7, and an output shaft of the hydraulic motor 8 differentially between the left and right rear axles 10L and 10R. The differential device 11 and the like to be connected are housed, and the power from the engine 1 input to the pump shaft 12 of the hydraulic pump 7 is a hydraulic continuously variable transmission 18 including the hydraulic pump 7 and the hydraulic motor 8. , The left and right rear axles 10L and 10R are driven to travel as differential power via the differential device 11.

  The engine 1 is housed in a hood 13, and a handle 14 extends from the dashboard immediately behind the hood 13 to the rear upper side, and a radiator 15 is mounted on the vehicle frame 3 immediately before the engine 1. ing. In addition, a reservoir tank 16 for replenishing hydraulic oil (not shown) or the like in the bonnet 13 is disposed behind the engine 1.

  Further, a rear cover 17 is disposed at the rear portion of the vehicle frame 3, and a driver seat 109 is mounted on the upper surface of the rear cover 17, and the rear axle drive device 5 is disposed in the rear cover 17. Has been.

  The mower 6 is disposed below the vehicle frame 3 between a rear wheel 20 driven by the rear axle drive device 5 and a front wheel 19 supported by the front axle support device 4. The left and right mower hangers 21 and 21 are coupled to the front end portions of the left and right side plates of the vehicle frame 3, respectively. The mower hangers 21 and 21 are coupled to the front end of the mower 6 through the link rods 21 a and 21 a. Thus, the mower 6 is suspended so as to be movable up and down.

Next, the engine 1 will be described with reference to FIGS.
As shown in FIGS. 3 and 4, in the engine 1, an oil pan 22 is provided in the lower part, a cylinder block 23 is provided in the upper part of the oil pan 22, and a cylinder head 24 is provided in the upper part of the cylinder block 23. Is provided.

  A crankshaft 25 is installed in the cylinder block 23 in a substantially horizontal direction in the front-rear direction, and front and rear end portions of the crankshaft 25 protrude from front and rear end surfaces of the cylinder block 23, respectively. A flywheel 26 is fixed to the rear end portion of the crankshaft 25, and a first crank pulley 25a and a second crank pulley 25b are fixed to the front end portion of the crankshaft 25 in order from the front. ing.

  A cooling fan 27 is disposed above the crankshaft 25. A pulley 28a is fixed to the fan shaft 28 of the cooling fan 27, and a cooling water pump 29 is attached thereto. An alternator 30 is disposed on the left side of the cooling fan 27, and a pulley 31 a is fixed to the alternator shaft 31 of the alternator 30.

  A belt 32 is wound around the second crank pulley 25b of the crankshaft 25, the pulley 28a of the fan shaft 28, and the pulley 31a of the alternator shaft 31 to form an auxiliary machine driving belt mechanism 53. The motive power from the crankshaft 25 is transmitted through the belt 32 by the accessory driving belt mechanism 53, and the cooling fan 27, the cooling water pump 29, and the alternator 30 are driven. Yes.

  Further, on the lower side of the front part of the oil pan 22, a notch 22a is formed by cutting the front lower corner of the oil pan 22 into a substantially rectangular shape in side view. On the lower surface 22b of the notch 22a, the mounting portion 35 of the first transmission box 33 is fastened and fixed to the left side of the lower surface 22b by a bolt 37, and the mounting portion of the second transmission box 34 is fixed to the right side of the lower surface 22b. 36 is fastened and fixed by bolts 37. The two transmission boxes 33 and 34 are located on the same horizontal plane, and are arranged at symmetrical positions with a vertical plane passing through the crankshaft 25 in front view.

  The first transmission box 33 includes a first input shaft 43 parallel to the crankshaft 25 and a first input box 43 perpendicular to the first input shaft 43 as shown in FIG. An output shaft 44 is rotatably supported by a bearing, and a bevel gear 46 fixed to the upper end of the first output shaft 44 is fixed to the rear end of the first input shaft 43. A bevel gear 45 is engaged.

  Further, a first input pulley 43a is fixed to the front end portion of the first input shaft 43, and an output shaft portion 44b is coaxially and detachably connected to the lower end of the first output shaft 44. A first output pulley 44 a is provided on the output shaft portion 44 b via an electromagnetic clutch 48. The power from the first output shaft 44 to the first output pulley 44a can be connected and disconnected by turning on and off the electromagnetic clutch 48.

  As shown in FIG. 3, the electromagnetic clutch 48 is extended to the left and right at the bottom of the first transmission box 33 by screwing a pair of left and right long bolts 49 and 49 into the bolt holes 48a of the electromagnetic clutch 48 from below. It can be securely attached to the boss portion 47 provided. This clutch is not limited to the electromagnetic clutch 48, and may be, for example, a hydraulic clutch. A cooling fan 42 is attached to the rear side of the first input pulley 43a. The cooling fan 42 blows cooling air backward so that the oil pan 22 and the like can be efficiently cooled. Yes.

  As shown in FIG. 5B, the second transmission box 34 also has a second input shaft 38 parallel to the crankshaft 25 and a second output shaft perpendicular to the second input shaft 38. 39 is rotatably supported by a bearing, and a bevel gear 41 fixed to the upper end of the second output shaft 39 is connected to a bevel gear 40 fixed to the rear end of the second input shaft 38. Are engaged.

  Further, a second input pulley 38a is fixed to the front end portion of the second input shaft 38, and a second output pulley 39a is fixed to the lower end portion of the second output shaft 39 by key fitting. Accordingly, the power input to the second input pulley 38a can be output from the second output pulley 39a after the transmission direction is changed by 90 degrees by the bevel gears 40 and 41. A cooling fan 42 is also attached to the rear side of the second input pulley 38a, and the cooling fan 42 blows cooling air backward so that the oil pan 22 and the like can be efficiently cooled. Yes.

  A belt 50 is wound around the first crank pulley 25a of the crankshaft 25, the first input pulley 43a of the first transmission box 33, and the second input pulley 38a of the second transmission box 34. A mechanism 51 is configured so that the power from the crankshaft 25 is transmitted through the belt 50 by the belt mechanism 51 so that the first output pulley 44a and the second output pulley 39a are rotationally driven. ing.

  As shown in FIGS. 1 to 3, a pulley 12a is fixed to the pump shaft 12 of the hydraulic pump 7 of the rear axle drive device 5 at a height substantially the same as the height 59 of the second output pulley 39a. A belt 57 is wound between the pulley 12a and the second output pulley 39a. Further, the height 60 of the first output pulley 44a is set at a position lower than the height 59 of the second output pulley 39a, and the input shaft 58 inputs a driving force to the rotary blade 6a of the mower 6. An input pulley 58a is fixed above the mower 6 so that the mower 6 is positioned lower than the height 59 even when the mower 6 moves up and down. A belt 56 is wound between the input pulley 58a and the first output pulley 44a.

  Thus, since the height 60 of the first output pulley 44a of the first transmission box 33 and the height 59 of the second output pulley 39a of the second transmission box 34 are arranged so as to deviate from each other, the first output The belt 56 for power transmission from the pulley 44 a to the mower 6 can be prevented from coming into contact with the belt 57 for power transmission from the second output pulley 39 a to the rear axle drive device 5.・ 57 does not rub, prolonging the service life and reducing noise.

  In such a configuration, the power from the crankshaft 25 of the engine 1 is transmitted to the first input pulley 43a of the first transmission box 33 and the second via the first crank pulley 25a and the belt 50, that is, by the belt mechanism 51. It is simultaneously transmitted to the second input pulley 38a of the transmission box 34. The power transmitted to the first input pulley 43a is transmitted through the first input shaft 43, the bevel gear 45, the bevel gear 46, the first output shaft 44, the output shaft portion 44b, and the electromagnetic clutch 48, so that the transmission direction is 90 degrees. The power is transmitted from the first output pulley 44 a so that it can be connected and disconnected, and the power is transmitted to the mower 6 via the belt 56, the input pulley 58 a, and the input shaft 58. In the mower 6, the rotary blade 6a is rotationally driven.

  On the other hand, the power transmitted to the second input pulley 38a is output from the second output pulley 39a by changing the transmission direction by 90 degrees through the second input shaft 38, the bevel gear 40, the bevel gear 41, and the second output shaft 39. Further, power is transmitted to the hydraulic pump 7 of the rear axle drive device 5 through the belt 57, the pulley 12a, and the pump shaft 12. In the rear axle drive device 5, the left and right rear axles 10 </ b> L and 10 </ b> R are driven to travel by the speed change power continuously variable by the hydraulic continuously variable transmission 18.

  That is, in the engine 1 having the crankshaft 25 in a substantially horizontal direction, a first input shaft 43 that is arranged in parallel to the crankshaft 25 and inputs power from the crankshaft 25 and a first input shaft 43 that is perpendicular to the first input shaft 43. A first transmission box 33, which is a first power transmission case that supports one output shaft 44 internally, is internally supported by a second input shaft 38 that is arranged in parallel to the crankshaft 25 and that inputs power from the crankshaft 25. By arranging at least one second power transmission case, in this embodiment a single second transmission box 34 in parallel, the power from the crankshaft 25 is transmitted to the first transmission box 33 and the second transmission box. 34, the mower 6 and the rear axle drive device 5 which are a plurality of drive devices outside the engine 1 can be supplied respectively, so that the transmission boxes 33 and 34 are placed in the middle of the transmission path. The belt, which is an endless belt, is divided into a belt 50 from the crankshaft 25 to the input shafts 43 and 38 and a belt 56 and 57 from the output shafts 44 and 39 to the mower 6 and the rear axle drive device 5 to be wound. The belts 50, 56, and 57 can be rotated, and the direction of the belts 50, 56, and 57 is not changed in the middle of the transmission path, so that the service life of the belts 50, 56, and 57 is increased and noise is reduced. Can do. At the same time, as the belts 50, 56, and 57 are shortened and the belt is less likely to slip or vibrate, the transmission efficiency is improved, and the first crank pulley 25a and the pulley 58a, which are rotation transmission bodies during assembly, are improved. -Since the position adjustment between 12a is unnecessary, the work efficiency at the time of assembly is also improved. Further, a dedicated transmission box 33/34 can be provided for each of the mower 6 and the rear axle drive device 5, and the output horsepower from the transmission box 33/34 can be small, and accordingly the direction in the transmission box 33/34 In the conversion structure, in this embodiment, the bevel gears 40, 41, 45 and 46 are also reduced, and the transmission boxes 33 and 34 can be reduced in size. At the same time, it becomes possible to input the optimum rotational speed for the mower 6 / rear axle drive device 5 from the corresponding transmission boxes 33/34 via the belts 56/57, so that the mower 6 / rear axle drive device 5 is stabilized. Therefore, no loud noise is generated and transmission efficiency is further improved.

  Further, an oil pan 22 is provided in the lower part of the engine 1, and the first transmission box 33 as the first power transmission case is attached to the oil pan 22. It can be easily attached to the engine 1 and the work efficiency of the work of attaching the first transmission box 33 during assembly is improved. Furthermore, the first transmission box 33 can be set to the same vibration system as the engine 1, and the vibration-proofing measures can be simplified and the cost can be reduced.

  In addition, a notch 22a is formed below the oil pan 22, and the first transmission box 33, which is the first power transmission case, is disposed in the notch 22a. Therefore, the notch 22a is used. And the 1st transmission box 33 can be arrange | positioned compactly, the engine 1 can be made small and the work vehicle 2 can be reduced in size.

  Further, the second transmission box 34 as the second power transmission case supports and supports a second output shaft 39 perpendicular to the second input shaft 38 from the second output shaft 39 as a driving device. Since rotational power is supplied to the device 5, the power from the engine 1 is transmitted from the second transmission box 34 to a mechanical transmission system comprising an endless belt, gears, etc. of an inexpensive and simple configuration, in this embodiment the second output pulley. It can be supplied to the rear axle drive device 5 via a belt transmission system including 39a, a belt 57, a pulley 12a, etc., and parts cost can be reduced and transmission efficiency can be improved.

  In addition, since the power from the crankshaft 25 is input to the first input shaft 43 and the second input shaft 38 via the belt 50 that is a single endless belt, the number of belts necessary for power transmission It is possible to reduce the cost of parts and improve the maintainability by reducing the number of parts.

Further, as shown in FIG. 6, a belt mechanism 51 </ b> A can be applied instead of the belt mechanism 51.
The belt mechanism 51A uses a plurality of belts 61 and 62 instead of a single belt 50, and the first belt 61 includes a first crank pulley 25a of the crankshaft 25 and a first input. The second belt 62 is wound between the first input pulley 43a of the shaft 43 and the first crank pulley 25a of the crankshaft 25 and the second input pulley 38a of the second input shaft 38. It is wound around.

  Thereby, for example, when the rotational speed of the rotary blade 6a of the mower 6 is to be optimized by increasing / decreasing according to the mowing target, work content, etc., for example, the first crank pulley 25a is further increased in the front-rear direction. After the division, the first belt 61 is wound between one divided pulley and the first input pulley 43a, and the second belt 62 is wound between the other divided pulley and the second input pulley 38a. It is only necessary to change the diameter ratio of one of the divided pulleys and the first input pulley 43a and the length of the first belt 61 to appropriate values.

  That is, in the belt mechanism 51, when one belt 50 is wound between many pulleys 25a, 43a, and 38a, when the tension is loosened due to work for a long time or under a high load. However, in order to optimize the tension balance of the belt 50, it is necessary to finely adjust the positional relationship between many pulleys 25a, 43a, and 38a. However, in this belt mechanism 51A, only fine adjustment between two pulleys is required. As a matter of course, it is possible to reliably and easily input the optimum rotational speed to the rotary blade 6a of the mower 6.

  That is, the power from the crankshaft 25 is a first belt 61 that is a first endless belt from the crankshaft 25 to the first input shaft 43, and a single or a plurality of second input shafts from the crankshaft 25, In this embodiment, since the input is made to the input shafts 43 and 38 via the second belt 62 which is the second endless belt up to the single second input shaft 38, the drive device is a first power transmission case. When the mower 6 is a drive device corresponding to a certain first transmission box 33 and the rear axle drive device 5 is a drive device corresponding to a second transmission box 34 that is a second power transmission case, The power transmission configuration from the crankshaft 25 to the input shafts 43 and 38, for example, the optimum rotational speed for the mower 6 and the rear axle drive device 5 by simply changing the diameter ratio of the pulleys 25a, 43a and 38a and the belts 61 and 62. Can be entered Next, it is possible to stabilize driving the mower 6 and rear transaxle apparatus 5 with minimum number of belt 61, 62, it is possible to reduce increase of decrease and maintenance of parts cost due to the number of components. In the following, another embodiment of the engine 1 will be described, but the same reference numerals are used for the same members and structures, and detailed description thereof will be omitted.

Next, an engine 1A according to a second embodiment of the present invention will be described with reference to FIGS.
As shown in FIGS. 7 and 8 (a), the engine 1A is provided with a pair of left and right second transmission boxes 34L and 34R by adding one new second transmission box 34 to the engine 1, The power from the pair of left and right second transmission boxes 34L and 34R is transmitted to the rear axle drive devices 64L and 64R provided separately on the left and right sides of the work vehicle 2A.

  In the engine 1A, the mounting portion 67 of the first transmission box 33 is fastened and fixed to the lower surface 22b of the notched portion 22a of the oil pan 22 by bolts 37, and the left and right extending portions of the mounting portion 67 are respectively left and right. The second transmission boxes 34L and 34R are fastened and fixed to the lower ends of the support plates 67L and 67R by bolts (not shown), respectively. Further, the pair of left and right second transmission boxes 34L and 34R are arranged at symmetrical positions with the first transmission box 33 in between when viewed from the front.

  The first crank pulley 25a of the crankshaft 25, the second input pulley 38a of the left second transmission box 34L, the first input pulley 43a of the first transmission box 33, and the second of the second transmission box 34R on the right side. A belt mechanism 71 is configured by winding a single belt 72 around the input pulley 38a. The belt mechanism 71 transmits power from the crankshaft 25 via the belt 72, and The output pulley 44a and the left and right second output pulleys 39a and 39a are driven to rotate.

  In the belt mechanism 71, one side of the belt 72 is pushed down by the lower half of the left and right second input pulleys 38a and 38a, and the approximate center of the belt 72 between the left and right second input pulleys 38a and 38a is the first. By being pushed up by the upper half of the one-input pulley 43a, a tensioning structure stronger than the belt mechanism 51 is configured. As a result, a belt mechanism 71 with high power transmission efficiency that reduces slip generated in the belt 72 is formed.

  Here, in the rear axle drive devices 64L and 64R separately provided on the left and right sides of the work vehicle 2A, pulleys 65a and 66a are fixed to the pump shafts 65 and 66 of the hydraulic pumps 73 and 73, respectively. Belts 69 and 70 are wound around 65a and 66a and the second output pulleys 39a and 39a, respectively. A belt 68 is wound around an input pulley 58a fixed to an input shaft 58 for inputting a driving force to the rotary blade 6a of the mower 6 and the first output pulley 44a.

  In such a configuration, power from the crankshaft 25 of the engine 1A is transmitted to the first input pulley 43a of the first transmission box 33 and the left and right via the first crank pulley 25a and the belt 72, that is, by the belt mechanism 71. It is simultaneously transmitted to the second input pulleys 38a and 38a of the second transmission boxes 34L and 34R. Then, the power transmitted to the first input pulley 43a is output through the first transmission box 33 and the electromagnetic clutch 48 so that the transmission direction can be changed by 90 degrees from the first output pulley 44a. Power is transmitted to the mower 6 through the belt 68, the input pulley 58a, and the input shaft 58. In the mower 6, the rotary blade 6a is rotationally driven.

  On the other hand, the power transmitted to the pair of left and right second input pulleys 38a and 38a is changed from the left and right second output pulleys 39a and 39a by changing the transmission direction by 90 degrees through the left and right second transmission boxes 34L and 34R. Further, the power is further transmitted to the hydraulic pumps 73 and 73 of the left and right rear axle drive devices 64L and 64R through belts 69 and 70, pulleys 65a and 66a, and pump shafts 65 and 66, respectively. In the rear axle drive devices 64L and 64R, the left and right rear axles 75L and 75R are driven to travel by the shift power from the hydraulic motors 74 and 74 fluidly connected to the hydraulic pumps 73 and 73.

  That is, as in this embodiment, the power from the crankshaft 25 is increased by increasing or decreasing the number of second transmission boxes arranged according to the number of rear axle drive devices 64L and 64R that are drive devices. It can be supplied for each axle drive unit 64L and 64R. As a result, the rotational speed of the power input to the left and right rear axle drive devices 64L and 64R can be changed by simply changing the diameter ratio of the pulleys 39a, 65a and 66a in the middle of transmission and the lengths of the belts 69 and 70 to appropriate values. The engine 1A can drive the left and right rear axle drive devices 64L and 64R with a better balance than the engine 1 to improve the running performance.

Moreover, as shown in FIG.8 (b), the engine 1A of a present Example is applicable also to the working vehicle 2B which has the axle drive devices 76 * 77 in the front and back.
In the axle drive devices 76 and 77 before and after the work vehicle 2B, pulleys 78a and 79a are fixed to the pump shafts 78 and 79 of the hydraulic pumps 80 and 83, respectively, and the pulleys 78a and 79a and the second output Belts 86 and 87 are wound around the pulleys 39a and 39a, respectively. A belt 68 is wound around the input pulley 58a of the mower 6 and the first output pulley 44a in the same manner.

  In such a configuration, power from the crankshaft 25 of the engine 1A is transmitted via the belt mechanism 71 to the first input pulley 43a of the first transmission box 33 and the second inputs of the left and right second transmission boxes 34L and 34R. Simultaneously transmitted to the pulleys 38a and 38a. Of these, the power transmitted to the first input pulley 43a is output to the mower 6 after being transmitted from the first output pulley 44a by changing the transmission direction by 90 degrees as described above. The rotary blade 6a is rotationally driven.

  On the other hand, the power transmitted to the left and right second input pulleys 38a and 38a is output from the left and right second output pulleys 39a and 39a by changing the transmission direction by 90 degrees through the left and right second transmission boxes 34L and 34R. Further, power is transmitted to the hydraulic pumps 80 and 83 of the front and rear axle drive devices 76 and 77 via belts 86 and 87, pulleys 78a and 79a, and pump shafts 78 and 79, respectively. In the front axle drive device 76, the left and right front axles 82 </ b> L and 82 </ b> R are driven to travel by the shift power from the left and right hydraulic motors 81 </ b> L and 81 </ b> R fluidly connected to the hydraulic pump 80. Similarly, in the rear axle drive device 77, the left and right rear axles 85L and 85R are driven to drive by the shifting power from the left and right hydraulic motors 84L and 84R fluidly connected to the hydraulic pump 83. Thus, the engine 1A of the present embodiment can be applied to a work vehicle having various drive arrangement configurations.

Further, as shown in FIG. 9A, a belt mechanism 71 </ b> A can be applied instead of the belt mechanism 71.
The belt mechanism 71A uses a plurality of belts 88 and 89 instead of the single belt 72, and the first belt 88 includes a first crank pulley 25a of the crankshaft 25 and a first input shaft. The second belt 89 is wound between the first input pulley 43a and the first crank pulley 25a of the crankshaft 25 and the second input pulley 38a of the left and right second input shafts 38 and 38. -It is wound between 38a.

  Thereby, for example, the diameter ratio of the pulleys 25a and 43a and the first belt 88 are changed, or the diameter ratio of the pulleys 25a, 38a and 38a and the second belt 89 are changed, so that the mower 6 and the rear axle drive device 64L The optimum rotational speed can be separately input to 64R, and the mower 6 and the rear axle drive devices 64L and 64R can be stably driven by the minimum number of belts 88 and 89.

Further, as shown in FIG. 9B, a belt mechanism 71 </ b> B can be applied instead of the belt mechanism 71.
The belt mechanism 71B uses a plurality of belts 88, 90, 91 instead of a single belt 72, as in the belt mechanism 71A. However, unlike the belt mechanism 71A, the input shafts 43, 38, Belts 88, 90 and 91 are wound around every 38.

  Accordingly, for example, the diameter ratio of the pulleys 25a and 43a and the first belt 88 are changed, the diameter ratio of the pulleys 25a and 38a and the second belt 90 are changed, the diameter ratio of the pulleys 25a and 38a, and the second belt 91. Can be input to the mower 6 and the rear axle drive devices 64L and 64R separately, and the mower 6 and the rear axle drive devices 64L and 64R can be connected to the belt mechanism. It can be driven more stably than 71A.

  That is, from the crankshaft 25, a plurality of input shafts 43, 38 comprising the first input shaft 43 and a single or a plurality of second input shafts, in this embodiment a plurality of second input shafts 38, 38. Since the belts 88, 90, 91, which are endless belts, are provided for each of the input shafts 43, 38, 38 up to 38, this is a driving device corresponding to the second transmission box 34, which is the second power transmission case. Even when the optimum rotational speed differs between the left and right rear axle drive devices 64L and 64R, a simple change in the power transmission configuration from the crankshaft 25 to the input shafts 43, 38, and 38, in this embodiment, the pulley diameter ratio It is possible to input the optimum rotational speed for each of the rear axle drive devices 64L and 64R only by changing the belt and the belt, and the mower 6 and the rear axle drive devices 64L and 64R can be reliably driven stably. 6 and rear axle drive Driving performance of the device 64L · 64R can be greatly improved.

Next, an engine 1B according to a third embodiment of the present invention will be described with reference to FIGS.
As shown in FIGS. 10 to 12, the engine 1B includes a hydraulic pump 92 in place of the pair of left and right second transmission boxes 34L and 34R in which the gear transmission mechanism such as the bevel gears 40 and 41 is installed in the engine 1A. By providing a pair of left and right hydraulic transmission boxes 93L and 93R, the pressure oil from the pair of left and right hydraulic transmission boxes 93L and 93R is respectively provided to the left and right rear axles separately provided in the work vehicle 2C. The driving devices 96L and 96R are supplied and discharged.

  In the engine 1B, as in the engine 1A, the mounting portion 98 of the first transmission box 33 is fastened and fixed to the lower surface 22b of the notch portion 22a of the oil pan 22 by bolts 37. In addition, the pair of left and right hydraulic transmission boxes 93L and 93R are disposed at left and right symmetrical positions with the first transmission box 33 in front view by a support member (not shown).

  Further, the first input shaft 43 of the first transmission box 33 and the pump shafts 99 and 99 of the pair of left and right hydraulic transmission boxes 93L and 93R are both disposed on the front end side of the crankshaft 25, The shaft 25, the first input shaft 43, and the pump shafts 99 and 99 are arranged close to each other. Thereby, the pulleys 43a, 99a, and 99a for input to the transmission boxes 33, 93L, and 93R can also be disposed close to the first crank pulley 25a for output from the crankshaft 25.

  The first crank pulley 25a of the crankshaft 25, the pulley 99a fixed to the pump shaft 99 of the left hydraulic transmission box 93L, the first input pulley 43a of the first transmission box 33, and the right hydraulic transmission box 93R. A belt mechanism 100 is configured by winding a single belt 101 around a pulley 99 a fixed to the pump shaft 99. The belt mechanism 100 simultaneously transmits power from the crankshaft 25 to the first input pulley 43a and the pair of left and right pulleys 99a and 99a via the belt 101.

  The power transmitted to the first input pulley 43a is cut off from the first output pulley 44a by changing the transmission direction by 90 degrees through the first transmission box 33 and the electromagnetic clutch 48, similarly to the engine 1A. The power is transmitted to the mower 6 through the belt 68, the input pulley 58a, and the input shaft 58, and the rotary blade 6a is rotationally driven in the mower 6.

  On the other hand, the rotational power transmitted to the pair of left and right pulleys 99a and 99a is converted into hydraulic power by the hydraulic pumps 92 and 92. Among these, the hydraulic pump 92 in the left hydraulic transmission box 93L is fluidly connected to the hydraulic motor 97 in the left rear axle drive device 96L via a pair of hydraulic pipes 94a and 94b. Pressure oil from the box 93L is supplied to the left rear axle drive device 96L.

  Similarly, the hydraulic pump 92 in the right hydraulic transmission box 93R is also fluidly connected to the hydraulic motor 97 in the right rear axle drive device 96R via a pair of hydraulic pipes 95a and 95b. Pressure oil from the box 93R is supplied to the right rear axle drive 96R. In the pair of left and right rear axle driving devices 96L and 96R, the left and right rear axles 102L and 102R are driven to travel by the hydraulic motors 97 and 97 that are operated by the supplied pressure oil.

  That is, the hydraulic transmission boxes 93L and 93R as the second power transmission case include hydraulic pumps 92 and 92, and supply hydraulic power from the hydraulic pumps 92 and 92 to the rear axle driving devices 96L and 96R as driving devices. Therefore, the power from the engine 1B can be supplied from the hydraulic transmission boxes 93L and 93R to the rear axle driving devices 96L and 96R via the hydraulic transmission system including the hydraulic pipes 94a, 94b, 95a, and 95b. In addition, high-accuracy drive control can be performed on the rear axle drive devices 96L and 96R to improve running performance and turning performance.

  Further, since the first input shaft 43 and the pump shafts 99 and 99 as the second input shaft are arranged on the front end side which is the same crankshaft end side in the axial direction of the crankshaft 25, the crankshaft 25, the first input shaft 43 and the pump shafts 99 and 99 are arranged close to each other, and the length of the transmission path from the crankshaft 25 to the first input shaft 43 and the pump shafts 99 and 99 can be shortened. In addition, the transmission system such as the belt 101 and the gear, which are endless belts, can be reduced, and the engine 1B can be reduced in size and the transmission efficiency can be improved by reducing the arrangement space.

As shown in FIG. 13A, a belt configuration like the belt mechanism 100A can be applied to the engine 1B instead of the belt mechanism 100, similarly to the engine 1A.
The belt mechanism 100A uses a plurality of belts 88 and 103 instead of the single belt 101, and the first belt 88 includes a first crank pulley 25a of the crankshaft 25 and a first input shaft. The second belt 103 is wound between the first crank pulley 25a of the crankshaft 25 and the pulleys 99a and 99a of the left and right pump shafts 99. It has been turned.

  Thus, for example, by changing the diameter ratio of the pulleys 25a and 43a and the first belt 88, or by changing the diameter ratio of the pulleys 25a, 99a and 99a and the second belt 103, the mower 6 and the rear axle drive device 96L The optimum rotational power and hydraulic power can be separately supplied to 96R, and the mower 6 and the rear axle driving devices 96L and 96R can be stably driven by the minimum number of belts 88 and 103.

Furthermore, as shown in FIG. 13B, a belt mechanism 100B can be applied instead of the belt mechanism 100.
The belt mechanism 100B uses a plurality of belts 88, 104, and 105 instead of the single belt 101 as in the belt mechanism 100A. However, unlike the belt mechanism 100A, the first input shaft 43 and the pump Different belts 88, 104, and 105 are wound around the shafts 99 and 99, respectively.

  Thereby, for example, the diameter ratio of the pulleys 25a and 43a and the first belt 88 are changed, the diameter ratio of the pulleys 25a and 99a and the second belt 104 are changed, the diameter ratio of the pulleys 25a and 99a, and the second belt 105. Can be supplied to the mower 6 and the rear axle drive devices 96L and 96R separately, respectively, so that the optimum rotational power and hydraulic power can be separately supplied to the mower 6 and the rear axle drive devices 96L and 96R. It can be driven more stably than the belt mechanism 100A.

Next, an engine 1C according to the fourth embodiment of the present invention and an engine 1D according to the fifth embodiment will be described with reference to FIGS.
In each of the engines 1C and 1D, the first transmission box 33 and the pair of left and right hydraulic transmission boxes 93L and 93R in the engine 1B are arranged on opposite sides in the axial direction of the crankshaft 25, and the mower 6 and The length of the transmission path to the rear axle drive devices 96L and 96R can be shortened.

  As shown in FIGS. 14 and 15, in the engine 1 </ b> C, the mounting portion 98 of the first transmission box 33 is fastened by the bolt 37 to the lower surface 22 b of the notch portion 22 a of the oil pan 22, similarly to the engine 1 </ b> B. It is fixed. That is, the first input shaft 43 to the first transmission box 33 is disposed on the front end side of the crankshaft 25.

  A first belt 88 is wound between the first crank pulley 25 a of the crankshaft 25 and the first input pulley 43 a of the first transmission box 33. The power is input from the crankshaft 25 to the first input pulley 43a. Similarly to the engine 1B, the input rotational power is output through the first transmission box 33 and the electromagnetic clutch 48 so that the transmission direction is changed by 90 degrees from the first output pulley 44a.

  On the other hand, the pump shafts 99 and 99 of the pair of left and right hydraulic transmission boxes 93L and 93R are disposed below the oil pan 22 on the rear end side of the crankshaft 25 by a support member (not shown). A belt 106 is wound between a pair of left and right pulleys 99a and 99a of the pump shaft 99 and 99 and a third crank pulley 25c fixed to the rear end of the crankshaft 25. The rotational power is transmitted simultaneously from the crankshaft 25 to the pulleys 99a and 99a via the belt 106. The transmitted power is converted into hydraulic power and output by the hydraulic pumps 92 and 92 in the pair of left and right hydraulic transmission boxes 93L and 93R, as in the engine 1B.

  In such a configuration, rotational power is output from the front end side of the crankshaft 25 via the first transmission box 33, and from the rear end side of the crankshaft 25 via the hydraulic transmission boxes 93L and 93R. Hydraulic power can be output. For example, when a work machine such as a mower 6 is disposed at the front portion of the work vehicle and an axle drive device that houses the hydraulic motor is disposed at the rear portion of the work vehicle, The length of the transmission path to the work machine and the axle drive device can be shortened.

  Also, as shown in FIGS. 16 and 17, in the engine 1 </ b> D, unlike the engine 1 </ b> C, the mounting portion 98 of the first transmission box 33 is fastened and fixed to the lower surface of the rear portion of the oil pan 22 by bolts 37. . That is, the first input shaft 43 to the first transmission box 33 is disposed on the rear end side of the crankshaft 25.

  A belt 107 is wound between the third crank pulley 25 c at the rear end of the crankshaft 25 and the first input pulley 43 a of the first transmission box 33, and the belt 107 passes through the belt 107. Power is input from the crankshaft 25 to the first input pulley 43a. Similarly to the engine 1C, the input rotational power is output from the first output pulley 44a through the first transmission box 33 and the electromagnetic clutch 48 so that the transmission direction is changed by 90 degrees.

  On the other hand, the pump shafts 99 and 99 of the pair of left and right hydraulic transmission boxes 93L and 93R are disposed below the front portion of the oil pan 22 on the front end side of the crankshaft 25 by a support member (not shown). A belt 108 is wound between the pair of left and right pulleys 99a and 99a of the pump shaft 99 and 99 and the first crank pulley 25a at the front end of the crankshaft 25. Rotational power is transmitted from the crankshaft 25 to the pulleys 99a and 99a. The transmitted power is converted into hydraulic power by the hydraulic pumps 92 and 92 in the pair of left and right hydraulic transmission boxes 93L and 93R and output in the same manner as the engine 1C.

  In such a configuration, hydraulic power is output from the front end side of the crankshaft 25 via the hydraulic transmission boxes 93L and 93R, and from the rear end side of the crankshaft 25 via the first transmission box 33. Rotational power can be output. For example, when an axle driving device that houses a hydraulic motor is disposed at the front of the work vehicle and a work machine such as a mower 6 is disposed at the rear of the work vehicle, The length of the transmission path to the work machine and the axle drive device can be shortened.

  That is, in the present embodiment, the first input shaft 43 and the pump shafts 99 and 99 as the second input shaft are disposed on the opposite crankshaft end side in the axial direction of the crankshaft 25. A mower 6 that is a driving device corresponding to the first transmission box 33 that is one power transmission case and an axle driving device that is a driving device corresponding to the hydraulic transmission boxes 93L and 93R that are second power transmission cases are a crankshaft. 25, the length of the transmission path from the crankshaft 25 to the mower 6 and the axle drive device can be shortened, and the work by reducing the transmission space is possible. The transmission efficiency can be improved by downsizing the vehicle 2 and suppressing slip, vibration, and the like. For example, when the first transmission box 33 for the mower 6 is disposed on the front end side of the crankshaft 25 and the hydraulic transmission boxes 93L and 93R for the axle drive device are disposed on the rear end side of the crankshaft 25. Is an arrangement configuration suitable for a front work machine / rear wheel drive type work vehicle, and conversely, on the front end side of the crankshaft 25, hydraulic transmission boxes 93L and 93R for axle drive devices are disposed, When the first transmission box 33 for the mower 6 is arranged on the rear end side of the shaft 25, the arrangement configuration is suitable for a rear work machine / front wheel drive type work vehicle. The length of the transmission path can be shortened.

  Although not provided in the above-described embodiments, a tension pulley supported by a swingable pulley arm is used to wind an endless belt such as a belt or chain around a plurality of rotation transmission bodies such as pulleys and sprockets. By providing a tension adjusting mechanism such as the above, it is possible to further suppress noise and improve transmission efficiency.

  The present invention can be applied to all engines having a crankshaft in a substantially horizontal direction.

1 is a partial cross-sectional side view of a work vehicle equipped with an engine according to a first embodiment of the present invention. It is a plane schematic diagram which shows the power transmission structure concerning a 1st Example. It is a front view of the engine concerning a 1st example. It is a side view similarly. FIG. 5A is a partial side sectional view of the transmission box of the first embodiment, FIG. 5A is a partial sectional side view of the first transmission box, and FIG. 5B is a partial sectional side view of the second transmission box. It is. It is a partial front view which shows another form of the belt mechanism of 1st Example. It is a front view of the engine concerning the 2nd example of the present invention. FIG. 8A is a schematic plan view showing a power transmission configuration according to the second embodiment, in which FIG. 8A is a schematic plan view when a rear axle drive device is provided separately on the left and right sides, and FIG. It is a plane schematic diagram at the time of providing an apparatus. FIG. 9A is a partial front view showing another embodiment of the belt mechanism of the second embodiment, and FIG. 9A shows the belt mechanism when the belt is wound separately on the first input shaft and the left and right second input shafts. FIG. 9B is a partial front view showing the belt mechanism when the belt is wound around each input shaft. It is a front view of the engine concerning the 3rd example of the present invention. It is a side view similarly. It is a plane schematic diagram which shows the power transmission structure concerning a 3rd Example. FIG. 13A is a partial front view showing another form of the belt mechanism of the third embodiment, and FIG. 13A shows the belt mechanism when the belt is wound separately on the first input shaft and the left and right pump shafts. FIG. 13B is a partial front view showing the belt mechanism when the belt is wound around each axis. It is a front view of the engine concerning the 4th example of the present invention. It is a side view similarly. It is a front view of the engine concerning the 5th example of the present invention. It is a side view similarly.

Explanation of symbols

1 Engine 5, 6, 96L, 96R Drive 22 Oil pan 22a Notch 25 Crankshaft 33 First power transmission case 34, 93L, 93R Second power transmission case 38, 99, 99 Second input shaft 39 Second output Shaft 43 First input shaft 44 First output shaft 50 Single endless belt 61 First endless belt 62 Second endless belt 88/90/91 Multiple endless belts 92 Hydraulic pump

Claims (10)

  In an engine having a crankshaft in a substantially horizontal direction, a first input shaft that is arranged in parallel to the crankshaft and inputs power from the crankshaft and a first output shaft that is perpendicular to the first input shaft are internally supported. By arranging at least one second power transmission case arranged in parallel to the crankshaft and supporting a second input shaft for inputting power from the crankshaft in the first power transmission case, An engine characterized in that power from a shaft can be supplied to a plurality of driving devices outside the engine via the first power transmission case and the second power transmission case.   The engine according to claim 1, wherein an oil pan is provided at a lower portion of the engine, and the first power transmission case is attached to the oil pan.   The engine according to claim 2, wherein a notch portion is formed on a lower side of the oil pan, and the first power transmission case is disposed in the notch portion.   The said 2nd power transmission case supports the 2nd output shaft perpendicular | vertical to the said 2nd input shaft internally, and supplies rotational power to the said drive device from this 2nd output shaft. Item 4. The engine according to any one of Items 3 to 3.   The engine according to any one of claims 1 to 3, wherein the second power transmission case includes a hydraulic pump and supplies hydraulic power from the hydraulic pump to the driving device.   6. The power from the crankshaft is input to the first input shaft and the second input shaft via a single endless belt. 6. Engine.   The power from the crankshaft is input through the first endless belt from the crankshaft to the first input shaft and the second endless belt from the crankshaft to the single or plural second input shafts. The engine according to any one of claims 1 to 5, wherein the engine is input to a shaft.   An endless belt is provided for each input shaft between the crankshaft and a plurality of input shafts composed of the first input shaft and a single or a plurality of second input shafts. The engine according to any one of claims 5 to 6.   The first input shaft and the second input shaft are arranged on the same crankshaft end portion side in the axial direction of the crankshaft, according to any one of claims 1 to 8. engine.   The first input shaft and the second input shaft are disposed on opposite crankshaft end portions in the axial direction of the crankshaft, according to any one of claims 1 to 8. Engine.

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