JP2005090375A - Engine lubricating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve sealing property of lubricating oil supplied into a slide part of an engine and improve assembly property of the engine having a lubricating device. <P>SOLUTION: A crank shaft 11 is rotatably supported on a crank case 10, a piston 14 is assembled into a cylinder 12, and the piston 14 is connected with the crank shaft 11 by a connecting rod 16. An oil jet shaft 82 is attached to a crank case 10 by striding a chain chamber 81, a distributing pipe 72 supplying lubricating oil to the oil jet shaft 82 is provided in a clutch cover 10d, and lubricating oil is discharged into a slide part of the piston 14. A connection part 79 having a butting face 96c abutting on a butting face 96d formed in the outside in the radial direction of the oil jet shaft 82 is provided in the clutch cover 10d, and an annular sealing member 97 is assembled into a channel of the butting faces 96c, 96d. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to an engine lubricating device for supplying lubricating oil to a sliding portion of a piston.

  The rough terrain vehicle or ATV (All Terrain Vehicle), also known as a buggy vehicle, is an off-road vehicle for four-wheeled single riders, and it is also used for leisure purposes such as hunting and trail touring, and in some agriculture It is also used as a commercial vehicle. Such vehicular engines including all-terrain vehicles have parts where two members slide relative to each other, such as a contact surface between a piston and a cylinder bore and a contact surface between a piston pin and a connecting rod. Lubricating oil is supplied to these sliding portions so that the contact surfaces do not directly contact each other. Lubricating oil supplied to the sliding portion is housed in the crank chamber, pressurized by an oil pump driven by the crankshaft, and supplied to the sliding portion. The lubricating oil is supplied from the oil pump to the sliding portion. It is necessary to provide an oil supply path to guide the operation.

A part of the oil supply path is formed between the crankcase and the clutch cover attached to the crankcase, and an oil passage pipe connected to the oil supply path between the cases and attached to the crankcase is provided between the piston and the connecting rod. For example, Patent Document 1 discloses a lubricating device in which lubricating oil is sprayed onto the piston pin.
Japanese Patent No. 2629937 (FIGS. 2, 3, and 4)

  When an oil supply path is formed between the crankcase and the clutch cover attached thereto, a long distance oil supply path curved in an arc shape is formed between these mating surfaces. Sealing performance cannot be ensured simply by abutting the case and the cover. In order to secure the sealing performance, when a sealing material curved corresponding to the mating surface of the case is assembled between the case and the cover, the sealing material is a belt-like material extending along the flow direction of the lubricating oil. It is necessary to mount the engine, and an operation of sandwiching a long strip-shaped sealing material at the time of assembling the engine is required, so that the assembling workability of the engine is lowered.

  An object of the present invention is to improve the sealing performance of lubricating oil supplied to a sliding portion of an engine.

  Another object of the present invention is to improve the assembly of an engine having a lubricating device.

  The engine lubrication apparatus of the present invention is an engine lubrication apparatus having a cylinder in which a piston is reciprocally incorporated, and a crankcase in which a crankshaft connected to the piston via a connecting rod is rotatably supported. An oil jet shaft attached to the crank case across a chain chamber formed in the crank case, and a distribution pipe for supplying lubricating oil discharged from an oil pump to the oil jet shaft. A cover member attached to the case; a nozzle attached to the crankcase in communication with the oil jet shaft; and a nozzle that discharges lubricating oil to the piston; and a radially outer side of the oil jet shaft provided on the cover member Abuts against the abutment surface And having a connecting portion having a can mating surface, and an annular sealing member which is accommodated in a groove formed to surround the opening surface of the oil jet shaft to the abutment surface.

  The engine lubrication apparatus according to the present invention is characterized in that an abutting surface of the connection portion and an attachment surface formed on the crankcase and to which the cover member is attached are flush with each other. Further, the cover member is a clutch cover that covers a clutch incorporated in the crankcase.

  In the present invention, a groove is formed on the abutting surface between the crankcase and the cover member so as to surround the opening surface of the oil jet shaft, and the seal material is accommodated in the groove. The sealing performance of the lubricating oil supplied to is improved. The cover member can be assembled to the crankcase in a state in which the sealing material is attached to at least one of the groove formed in the connecting portion and the groove formed in the butting surface of the crankcase, and the assembly of the engine is improved. By making the abutting surface of the connecting portion the same surface as the mounting surface of the crankcase, the assembly of the cover member to the crankcase is improved. The cover member is formed by a clutch cover that covers the clutch.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a perspective view showing a vehicle in which an engine is incorporated. This vehicle is an ATV, which is also called a buggy vehicle, that is, a rough terrain vehicle. As shown in FIG. 1, the vehicle body 1 is provided with front wheels 2 a and 2 b and rear wheels 3 a and 3 b, and a saddle type seat 4 is provided at the center of the vehicle body 1. The occupant gets into the vehicle across the seat 4 and operates by operating the handle 5.

  2 is a schematic view showing an engine and a transmission mounted on the vehicle of FIG. 1, and FIG. 3 is a cross-sectional view taken along line AA of FIG. As shown in FIG. 2, a crankshaft 11 is rotatably accommodated through bearings 9a and 9b in a crankcase 10 formed by two case halves 10a and 10b, as shown in FIG. In addition, a cylinder 12 is attached to an opening formed in the upper portion of the crankcase 10, and a cylinder head 13 is mounted on the cylinder 12. A piston 14 is incorporated in the cylinder bore of the cylinder 12 so as to be capable of reciprocating. A connecting rod 16 is connected between a hollow crankpin 15a fixed to the crankshaft 11 at a position eccentric from the rotation center and a piston pin 15b fixed to the piston 14, and the crankpin 15a and the connecting rod 16 are connected to each other. Between them, a needle bearing 16 a is incorporated, and the crankshaft 11 is rotationally driven by the piston 14. The engine formed by the cylinder 12 and the cylinder head 13 is a single-cylinder four-cycle water-cooled engine.

  Two intake ports 18 and two exhaust ports 19 are independently formed in the cylinder head 13 by opening into the combustion chamber 17 formed by the cylinder head 13 and the cylinder 12. An intake valve 21 for opening and closing is mounted on the cylinder head 13, and an exhaust valve 22 for opening and closing each exhaust port 19 is mounted on the cylinder head 13. A carburetor, that is, a carburetor 20 that generates a mixture of air and fuel is connected to the intake port 18, and the mixture is supplied from the carburetor 20 to the combustion chamber 17 through the intake port 18. Two camshafts 23 and 24 for intake valve and exhaust valve are rotatably mounted on the cylinder head 13, and a valve cam 25 is fixed to the camshaft 23. The valve cam 26 is fixed, and the valve cams 25 and 26 are in contact with the base end portions of the cam shafts 23 and 24, respectively. Thus, the illustrated valve mechanism is a direct-acting DOHC type. However, the valve operating mechanism may be a rocker arm type DOHC type or SOHC type in which the intake valve 21 and the exhaust valve 22 are opened and closed by a valve operating cam via a rocker arm. Each of the camshafts 23 and 24 is provided with two intake valves 21 and two exhaust valves 22 corresponding to the two intake ports 18 and the two exhaust ports 19, respectively. Two valve cams 25 and 26 are fixed to 24 each, and this engine is a four-valve type. FIG. 3 shows only one of the intake port 18 and the exhaust port 19 provided in two.

  As shown in FIG. 2, a sprocket 27 is fixed to the crankshaft 11, and a timing chain (not shown) is hung between the sprocket 27 and a sprocket (not shown) fixed to each camshaft 23, 24. The camshafts 23 and 24 are rotationally driven in synchronization with the rotation of the crankshaft 11.

  As shown in FIG. 2, a balancer shaft 31 is rotatably attached to the crankcase 10, and a gear 32b that meshes with a gear 32a fixed to the crankshaft 11 is fixed to the balancer shaft 31, and the balancer shaft 31 is a crankshaft. 11 is rotated in synchronism with this. The balancer shaft 31 is provided with a balance weight 33 as shown in FIG. 3 for smooth rotation of the crankshaft 11. Further, as shown in FIG. 2, a pump impeller 34 is attached to the balancer shaft 31, and this pump impeller 34 is formed in a pump housing formed by a part of the crankcase 10 and a pump cover 35 attached thereto. The engine coolant is supplied from a water pump to a water jacket 12 a formed in the cylinder 12.

  As shown in FIG. 2, a starter gear 36 is rotatably attached to the crankshaft 11, and a rotor 37 a having a permanent magnet is fixed to the crankshaft 11 adjacent to the starter gear 36. A power generator cover 10c fixed to the crankcase 10 is attached with a stator 37b having a coil, and the power generator 37 is constituted by the rotor 37a and the stator 37b. A one-way clutch 38 is incorporated between the rotor 37a and the starter gear 36, and the starter gear 36 is connected to a gear of a starter motor (not shown). When the engine is started, the rotation of the starter gear 36 that is rotationally driven by the starter motor is transmitted to the crankshaft 11 via the one-way clutch 38. On the other hand, under the state where the engine is driven, the rotation of the rotor 37a driven by the crankshaft 11 is prevented from being transmitted to the starter gear 36 by the one-way clutch 38.

  As shown in FIG. 2, a hollow main shaft 41 as a transmission input shaft and a counter shaft 42 as a transmission output shaft are rotatably mounted on the crankcase 10 and are parallel to each other. . The drive gear 43a fixed to the crankshaft 11 meshes with a driven gear 43b that is rotatably attached to the main shaft 41, and the driven gear 43b has a vibration damping damper 44 incorporated therein. To the clutch drum 45. On the other hand, a clutch hub 46 is fixed to the main shaft 41. Between the clutch hub 46 and the clutch drum 45, a plurality of clutch disks 45 a mounted inside the clutch drum 45 and on the outside of the clutch hub 46. A plurality of attached clutch disks 46a are incorporated. In this way, the input clutch 47 is constituted by the respective clutch disks 45a and 46a. When the clutch disks 45a and 46a are engaged, the rotation of the crankshaft 11 is transmitted to the main shaft 41 via the input clutch 47 and engaged. Is released to release the power transmission from the crankshaft 11 to the main shaft 41. A clutch cover 10 d that covers the input clutch 47 is attached to the case 10 as a cover member.

  In order to switch the input clutch 47 between the engaged state and the released state, the input clutch 47 is provided with an operating plate 48, and the operating plate 48 is a spring in a direction in which the clutch disks 45a, 46a are brought into close contact with a spring member (not shown). Power is applied. A push rod 49 is incorporated in the hollow hole of the main shaft 41 so as to be slidable in the axial direction, and the push rod 49 is attached to the operation plate 48 via a bearing. As shown in FIG. 1, the push rod 49 is connected to a clutch lever 6 provided on the handle 5 via a wire. When the push rod 49 moves to the left in FIG. The transmission of power to the main shaft 41 of the crankshaft 11 is cut off, and when the clutch lever 6 is released, the input clutch 47 is engaged by the spring force.

  As shown in FIG. 2, a drive gear 51a for the first speed is integrally provided on the main shaft 41, and drive gears 52a and 53a for the second speed and the third speed are provided in the dog clutch D1. The dog clutch D1 constituting the switching sleeve engages with a spline formed on the main shaft 41, rotates integrally with the main shaft 41, and is movable in the axial direction. Further, two gears 54a and 55a for the fourth speed and the fifth speed are rotatably mounted on the main shaft 41 so as to be positioned on both sides of the dog clutch D1. On the other hand, the countershaft 42 is a first-speed driven gear 51b that always meshes with the drive gear 51a to form a transmission gear train, and a second gear that always meshes with the drive gears 52a and 53a to form a transmission gear train. High-speed and third-speed driven gears 52b and 53b are rotatably mounted, respectively. Further, a dog clutch D2 provided with a driven gear 54b for the fourth speed that always meshes with the drive gear 54a to form a transmission gear train, and a fifth speed gear that meshes with the drive gear 55a at all times to form a transmission gear train. The countershaft 42 is provided with a dog clutch D3 provided with the driven gear 55b. Each of the dog clutches D2 and D3 constitutes a switching sleeve, and rotates integrally with the counter shaft 42 and is movable in the axial direction.

  As shown in FIG. 4, protrusions 50 are provided at predetermined intervals in the circumferential direction on both end faces of each of the dog clutches D1 to D3. The protrusions 50 are moved in the axial direction so as to correspond to the protrusions 50. When the gears are engaged with the recesses formed in the gears, the engaged gears are in a state of transmitting power through the dog clutches D1 to D3. For example, when the dog clutch D3 is meshed with the first speed driven gear 51b, the driven gear 51b is rotated integrally with the counter shaft 42 by the dog clutch D3, so that the main shaft is connected via the first speed transmission gear train. The power of 41 is transmitted to the countershaft 42. Similarly, when the dog clutch D1 is meshed with the fourth speed drive gear 54a, power is transmitted through the fourth speed transmission gear train, and when the dog clutch D1 is meshed with the fifth speed drive gear 55a, the fifth speed is changed. Power is transmitted through a high speed gear train.

  4 is a cross-sectional view taken along line BB in FIG. 3, FIG. 5 is a cross-sectional view taken along line CC in FIG. 3, and FIG. 6 is a left side view of FIG. Since FIG. 4 is shown in a state where the cross section is developed in a plane, the transmission gear train from the first speed to the fifth speed is shown in a separated state.

  As shown in FIG. 4, a reverse shaft 56 is attached to the crankcase 10. The reverse drive gear 57 a is fixed to the main shaft 41 and rotates integrally therewith, and the countershaft 42 is rotatably mounted. A reverse idler gear 57c, that is, a reverse idler gear 57c that always meshes with the reverse driven gear 57b to form a reverse transmission gear train is mounted on the reverse shaft 56. The dog clutch D2 is engaged with the reverse driven gear 57b, and when these are engaged, the power of the main shaft 41 is reversely rotated by the reverse idler gear 57c and transmitted to the counter shaft 42.

  The counter shaft 42 is connected to the front wheels 2a and 2b and the rear wheels 3a and 3b as driving wheels shown in FIG. 1 via a power transmission member such as a chain (not shown), and the engine power is driven by the counter shaft 42. Transmitted to the wheel.

  In order to rotatably support the reverse idler gear 57 c so as not to be displaced in the axial direction, the reverse shaft 56 is integrally provided with an annular protrusion 58, and the reverse shaft 56 is provided with respect to the protrusion 58. A washer 59 is mounted on the end side in order to restrict the axial displacement of the reverse idler gear 57c by the projection 58. Since the washer 59 is disposed between the reverse idler gear 57 c and the case 10, the washer 59 can be fixed to the reverse shaft 56 without forming a step in the reverse shaft 56. Note that a pin 60 is attached to the reverse shaft 56, and the rotation of the reverse shaft 56 is restricted by inserting the pin 60 into a slit 60 a formed in the case 10.

  Engaging grooves 61a to 61c are formed in the respective dog clutches D1 to D3, and shift forks (not shown) are engaged with the respective engaging grooves 61a to 61c. By operating each of the shift forks, any one of the dog clutches D1 to D3 is engaged with any one of the gears, so that the gear position of the transmission is switched between the first speed to the fifth speed and the reverse speed. It is done.

  The reverse shaft 56 is formed by a hollow shaft having an oil passage 62 therein, and lubricating oil is supplied to the oil passage 62. In order to supply the lubricating oil to the inner peripheral portion of the reverse idler gear 57 c, the reverse shaft 56 is connected to the oil passage 62, and a discharge port 62 a is formed in the reverse shaft 56. A plurality of discharge ports 62b are connected to the reverse shaft 56 in the axial direction so as to communicate with the oil passage 62 so as to be supplied to the outer peripheral portions of 55a, 57a and driven gears 51b to 55b, 57b provided on the countershaft 42. It is formed at predetermined intervals.

  In order to supply lubricating oil to the oil passage 62, an oil pump 63 is attached to the crankcase 10 as shown in FIG. The oil pump 63 has two pump casings 63a and 63b. A pump rotor 64 is rotatably incorporated in the casings 63a and 63b. The pump rotor 64 has a rotor shaft 65 attached thereto. And is driven by the crankshaft 11.

  As shown in FIG. 5, a filter case portion 66 is integrally formed with the clutch cover 10 d attached to the crankcase 10. A filter cover 67 is attached to the filter case portion 66, and a filter element 68 is incorporated in a space formed by the filter case portion 66 and the filter cover 67. The filter case 66 is connected to the discharge port of the oil pump 63 via an oil passage (not shown), and the lubricating oil discharged from the oil pump 63 is supplied into the filter case 66. The lubricating oil supplied into the filter case portion 66 passes through the filter element 68 from the outside to the inside to remove foreign matters, and then is discharged to an oil supply path 69 formed in the filter cover 67.

  As shown in FIGS. 5 and 6, the clutch cover 10 d is integrally formed with a distribution pipe 72 having an oil supply path 71 communicating with the oil supply path 69, and a connection plug 73 is attached to the tip of the distribution pipe 72. Is connected to an oil supply pipe 74. As shown in FIG. 6, this oil supply pipe 74 branches into an oil supply pipe 74a for a valve operating cam and an oil supply pipe 74b for a transmission, and the oil supply pipe 74a for the valve operating cam is a valve operating mechanism. Lubricating oil is supplied to sliding parts such as camshafts 23 and 24 and valve cams 25 and 26 constituting the motor. On the other hand, the transmission oil supply pipe 74b is connected to a connection plug 75 attached to the crankcase 10, and the oil supply pipe 74b communicates with the oil supply port 76 shown in FIG. The oil supply port 76 communicates with the oil passage 62 of the reverse shaft 56, and the lubricating oil discharged from the oil pump 63 is supplied to the oil passage 62 through the oil supply port 76, and the reverse idler gear 57c is supplied from the discharge ports 62a and 62b. Lubricating oil is supplied to the inner peripheral sliding portion, the meshing sliding portion of the main shaft 41 and the gear mounted on the counter shaft 42, and the sliding portions of the dog clutches D1 to D3.

  As shown in FIG. 4, an oil passage 77 is formed inside the countershaft 42, and lubricating oil is also supplied to the oil passage 77 via an oil supply pipe 74. Lubricating oil is supplied to the inner peripheral surfaces of the respective driven gears 51b, 52b, 53b, and 57b attached to the counter shaft 42 from a plurality of discharge ports 77a formed in the counter shaft 42 so as to communicate with the oil passage 77. Is done. Further, the lubricating oil is also supplied to the oil passage 80 formed by the gap between the main shaft 41 and the push rod 49 via the oil supply pipe 74, and each of the oil passages 80 mounted on the main shaft 41. Lubricating oil is supplied to the inner peripheral surfaces of the drive gears 54 a and 55 a from a plurality of discharge ports 80 a formed in the main shaft 41 in communication with the oil passage 80.

  As shown in FIG. 5, the clutch cover 10d is integrally formed with a connecting portion 79 having a communication hole 78 communicating with the oil supply passage 71, and the crankcase 10 straddles a chain chamber 81 formed therein. An oil jet shaft 82 is fixed, and a communication hole 83 communicating with the communication hole 78 of the connection portion 79 is formed in the oil jet shaft 82. As shown by a two-dot chain line in FIG. 5, a timing chain 84 that is hung on the sprocket 27 is accommodated in the chain chamber 81. The timing chain 84 is camshafts 23, 24 shown in FIG. It is hung on the sprocket attached to. A nozzle 86 having a discharge port 85 is attached to the crankcase 10, and the discharge port 85 of the nozzle 86 communicates with the communication hole 83 and opens toward the sliding portion between the piston pin 15 b and the connecting rod 16. doing. Therefore, the lubricating oil discharged from the oil pump 63 is slid between the piston pin 15b and the connecting rod 16 and the piston 14 and the cylinder bore as shown by the broken arrows in FIG. Supplied toward the surface.

  The crankpin 15a is formed by a hollow pin having an oil supply passage 87 therein, and the oil supply passage 87 is closed by caps 88a and 88b fixed to both ends of the crankpin 15a. A discharge port 89 that opens toward the bearing 9 a is formed in one cap 88 a, and an oil supply path 91 that communicates with the oil supply path 87 is formed in the crankshaft 11 so as to open to the end surface of the crankshaft 11. . The clutch cover 10 d is formed with a communication hole 92 that communicates with the oil supply passage 91. A cylindrical connection portion 93 formed in the clutch cover 10 d is formed at the end of the crankshaft 11 so as to surround the communication hole 92. The seal member 94 is incorporated in the connecting portion 93 to seal between the crankshaft 11 and the rotating crankshaft 11. Therefore, the lubricating oil discharged from the oil pump 63 is supplied to the bearing 9 a via the oil supply paths 91 and 87. Further, as shown in FIG. 5, the crankshaft 11 is formed with a branch passage 95 communicating with the oil supply passage 91, and the lubricating oil discharged from the branch passage 95 is directed toward the end face of the needle bearing 16a. Discharged.

  As shown in FIG. 5, the clutch cover 10 d is formed with an attachment surface 96 a that is attached to an attachment surface 96 b that is formed on the crankcase 10, and the clutch cover 10 d is attached to an end surface of the crankcase 10. Are fastened with bolts. The connecting portion 79 provided in the clutch cover 10d is formed with an abutting surface 96c so as to be in contact with the abutting surface 96d of the crankcase 10, and the abutting surface 96c is the same surface as the mounting surface 96a. It is the same surface as 96b. A sealing groove is formed on the butting surface 96c of the clutch cover 10d so as to surround the oil jet shaft 82, and a sealing groove is similarly formed on the butting surface 96d of the crankcase 10 so as to surround the oil jet shaft 82. A seal material 97 is incorporated between the clutch cover 10d and the crankcase 10 so as to enter the seal groove, thereby preventing leakage of lubricating oil from between the connecting portion 79 and the crankcase 10. Note that a seal groove may be formed in one of the butted surface 96c and the butted surface 96d, and the seal material 97 may be incorporated in the seal groove.

  Thus, the lubricant supplied to the nozzle 86 via the oil jet shaft 82 is incorporated into a seal groove formed in both or one of the clutch cover 10d and the crankcase 10 so as to face each other. Since the seal is made with 97, the sealing performance of the lubricating oil is improved. Further, the sealing surface is formed by a flat abutting surface 96c formed on the inner surface of the clutch cover 10d and a butting surface 96d on the crankcase 10 side in contact with the abutting surface 96d, and each abutting surface 96c, 96d is a mounting surface 96a. 96b, the clutch cover 10d can be easily attached to the crankcase 10 by using bolts, and the assembly of the clutch cover 10d is improved.

  The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention. For example, in the illustrated case, a dog clutch type switching sleeve is used as the switching sleeve, but a synchromesh type switching sleeve may be used.

It is a perspective view which shows the vehicle in which an engine is integrated. It is the schematic which shows the engine and transmission which are mounted in the vehicle of FIG. It is sectional drawing which follows the AA line of FIG. It is sectional drawing which shows the cross section in alignment with the BB line in FIG. It is sectional drawing which follows the CC line in FIG. FIG. 6 is a left side view of FIG. 5.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Crankcase 10d Clutch cover 11 Crankshaft 41 Main shaft 42 Counter shaft 51a-55a, 57a Drive gear 51b-55b, 57b Driven gear 56 Reverse shaft 57c Reverse idler gear 62a, 62b Discharge port 63 Oil pump 76 Oil supply port 96a, 96b Mounting surface 96c, 96d Abutting surface 97 Sealing material D1-D3 Dog clutch (switching sleeve)

Claims (3)

An engine lubrication device comprising: a cylinder in which a piston is reciprocally incorporated; and a crankcase in which a crankshaft connected to the piston via a connecting rod is rotatably supported;
An oil jet shaft attached to the crankcase across a chain chamber formed in the crankcase;
A distribution pipe for supplying lubricating oil discharged from an oil pump to the oil jet shaft, and a cover member attached to the crankcase;
A nozzle that is connected to the crankcase in communication with the oil jet shaft, and that discharges lubricating oil to the piston;
A connecting portion provided on the cover member and having a butting surface that abuts against a butting surface formed radially outward of the oil jet shaft;
An engine lubrication device comprising: an annular seal member housed in a groove formed on the butting surface so as to surround an opening surface of the oil jet shaft. 2. The engine lubrication apparatus according to claim 1, wherein the abutting surface of the connecting portion and the mounting surface formed on the crankcase and to which the cover member is attached are flush with each other. 3. The engine lubrication apparatus according to claim 1, wherein the cover member is a clutch cover that covers a clutch incorporated in the crankcase.

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