JPS60195331A - O. H. C-type multi-cylinder internal combustion engine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] A0 Object of the Invention (J) Industrial Field of Application The present invention comprises at least two cylinders that house pistons, and a camshaft for valve driving is disposed above each cylinder. 0, Il, C type multi-cylinder internal combustion engine.

(2) Conventional technology Conventionally, this multi-cylinder internal combustion engine has a single common crankshaft, and a timing device is used to connect the crankshaft and a camshaft disposed above each cylinder. It is linked.

(3) Problems to be solved by the invention In such a multi-cylinder internal combustion engine, when trying to arrange both cylinders in a horizontally opposed type or an r-type to reduce vibration,
Both cylinders have to be arranged in a direction that extends away from each other around the crankshaft, which poses a problem in that the compactness of the engine is impaired.

Furthermore, since the distance between the crankshaft and the camshaft is relatively long, the timing devices that are connected to each other are large, which is also a factor that impedes the ability to make the engine more compact.

The present invention has been made in view of the above circumstances, and is capable of reducing vibrations more easily than conventional horizontally opposed or V-type machines, and yet exhibits the same vibration reduction effect as those machines.
Furthermore, it is an object of the present invention to provide the multi-cylinder internal combustion engine in which the timing device can also be constructed in a conventional manner.

B0 Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention provides first and second crankshafts arranged parallel to each other and separated from each other on a horizontal plane; First and second pistons connected to the first and second crankshafts via connecting rods, and a first piston that slidably accommodates the first and second pistons, respectively.
and a second cylinder, first and second camshafts for valve operating disposed above the first and second cylinders in parallel with the crankshaft, and interlocking with the crankshafts. a common output shaft arranged therein, both cylinders are arranged adjacent to each other in the axial direction of the crankshaft, and each of the crankshafts is interlocked with the opposite camshaft via a timing device. The axes of both the crankshafts are arranged in a triangular range connecting the axes of the three axes of the two camshafts and the output shaft.

(2) Effect By arranging both crankshafts on the base of the triangle, that is, on the straight line connecting the axes of both camshafts, and by arranging both cylinders horizontally, like a conventional horizontally opposed engine, 1st
Since the first and second pistons move in opposite directions, it is possible to balance all or most of the secondary inertial forces as well as the primary inertial forces of the first and second piston systems, and eliminate or eliminate vibrations caused by these inertial forces. can be significantly reduced. Moreover, the overall width of the engine is reduced to about half that of a conventional horizontally opposed engine.

Both crankshafts are arranged on the two hypotenuses of the triangle, that is, a straight line connecting the axes of the first camshaft and the output shaft, and a straight line connecting the axes of the second camshaft and the output shaft, or both crankshafts are placed on the By arranging both cylinders in an X shape by arranging them inside the triangle, all you need to do is to properly select the phase of the second piston and attach balance weights to the appropriate positions of the first and second crankshafts. Similar to the conventional V-type machine, vibrations due to primary inertia force can be eliminated or significantly reduced.Furthermore, the overall width of the engine is shorter than that of the V-type machine.

The distance between the first crankshaft and the second camshaft, as well as the distance between the second crankshaft and the first camshaft, is determined by the distance between the crankshaft and the camshaft of the same type due to the adjacent arrangement of both cylinders in the axial direction of the crankshaft. This is shorter than the distance between the shafts, and the timing device that connects the shafts can be made smaller accordingly.

(3) Embodiment Hereinafter, an embodiment of the present invention will be explained with reference to the drawings. First, in FIG. An internal combustion engine E is mounted, and the engine E is located at the lower end of the down tube 1d at a location a, and at two locations above and below the center tube 1C.

It is screwed at three points C.

The structure of the engine E will be explained with reference to FIGS. 2 to 5. The engine E has two crankshafts 21.2□. 22 are arranged parallel to the longitudinal axis of the motorcycle M at equal distances from the longitudinal axis. Let's call it 2 crankshafts.

First and second crankshafts2. ．． 2. The first and second connecting rods3. ．． 32 via the first and second pistons 4.
．． 4. are concatenated respectively. These pistons4. ．． 4
．． first and second cylinders 5. each slidably housing the first and second cylinders 5. ．． 5. is the crankshaft 2. ．． 22 are arranged adjacent to each other in the axial direction.

In the illustrated example, the second cylinder 5. is the first cylinder 5
．． It is located on the front F side of the vehicle.

The engine body 6 of the engine E includes a central block 6C, and left and right blocks 6 which are superposed on each other with gaskets 7.7 sandwiched between the left and right ends of the central block 6C and are connected by a plurality of bolts 8, respectively.
1.6r.

The first and second cylinders 5, .
5. is formed, and a second piston 4 is formed in the right block 6r.
1 defining a first combustion chamber 91 between the first cylinder head 10. and a second crankcase 112 that accommodates the second crankshaft 21 in cooperation with the center block 6c are integrally formed, and the left block 61 has a second piston 4.
a second cylinder head 102 defining a second combustion chamber 92 therebetween; and a first crankcase 11. which accommodates the first crankshaft 21 in cooperation with the central block 6c. are formed integrally. In this case, the left and right blocks 61.6r have the same shape for compatibility.

First crankshaft2. For support of central block 6C
and the first crankcase 11. The first crankshaft 2. A pair of bearings 12 attached to both ends of
+, each pair of half-moon-shaped bearing walls 13. which sandwich 12r.
．． 131 ; 141 and 141 are respectively formed, and for supporting the second crankshaft 22, a central block 6c is formed.
and second crankcase 11. A pair of bearings 12 mounted on both ends of the second crankshaft 220 are mounted on the opposite surface of the
2.

Each pair of half-moon-shaped bearing walls 132°13 sandwiching 122
□ ; 14□ and 142 are formed, respectively.

Each cylinder head has a corresponding combustion chamber 9. ．． Intake port connected to 92)15. .

15□ and exhaust boat 16. ．． 162 are formed respectively. At that time, the intake port 15. ．． The inlet of 152 is directed upwards and the exhaust boat 16. ．． The 16° outlet opens downward (see Figure 2).

Intake port 15. ．． 15. At the inlet of the vaporizer 17. .

172 are respectively attached. These intake ports 15,
, i52 and vaporizer 17. ．． 17□ has two independent intake systems 18□, 18. and both intake systems 18. ．． 18
．． Using the space 19 between them, a starting motor 20 is disposed with its drive shaft 20a parallel to the crankshafts 21+22. In particular, the starting motor 20 is disposed approximately at the apex of an isosceles triangle whose base is a straight line connecting the axes of both crankshafts 2+ and 2t, and an installation surface 21 formed in a trapezoid shape at the center of the upper surface of the central block 6C. and fixed with bolts 22.

Suction and exhaust ports 15. ．． 15. ;16. ．． 16. Suction and exhaust valves 23. ．． 23. ;241°24v is the corresponding cylinder head 10. ．． 102, and these valves 23+, 232: 24+ -2
4 are biased in the valve closing direction by valve springs 25+, 25t: 26+, 262, respectively.

Each cylinder head 10. ．． 10. There is a valve train chamber 27 between it. ．． 27. A head cover 28. ．． 2
8. are polymerized with the backings 29 and 29 in between, and are fastened together with a plurality of bolts (not shown).

Each valve operating chamber 27+, 27. In the intake and exhaust valves 23,
．． 23□ ;24. ．． 24. Valve operating device 30. ．． 30. are each configured.

That is, the camshaft 31.22 is arranged parallel to the crankshaft 21.22. ．． 312 is a pair of bearings 32. .

32+;322. 322 through cylinder head io,, 1oz and head cover 28. ．． 28t, and the camshaft 31. ．． 31. intake cam 31L
, 31L and intake valve 23. ．． 232, there are intake otsuka arms 33i, 33i, and exhaust cams 31e, 3
Exhaust rocker arms 33e, 33e are disposed so as to bridge between the exhaust valves "I, 24!" and the exhaust valves "I", 24!, respectively.These rocker arms 33E, 33e are connected to the corresponding head cover 281.

It is swingably supported by rocker shafts 34t and 34e supported by 28 and 28, respectively. Here, the camshaft 31. on the side where the first cylinder head 1 is attached. will be referred to as a first camshaft, and the camshaft 312 on the second cylinder head 102 side will be referred to as a second camshaft.

The engine body 6 has one head cover 28. The transmission chamber 35 extends from the other head cover 282 to both cylinders 5.
, 52. In this transmission chamber 35, both crankshafts 2. .

2 and 2 are interlocked via a synchronizer 36 so that they can rotate synchronously with each other. A synchronizer 36 is provided for each crankshaft 2. ,2
．． First and second drive gears 3 of the same diameter are respectively fixed to
γ,,37. And these gears 37, . 37□ and a driven gear 38 which has a larger diameter and meshes with both of them.

Further, in the transmission chamber 35, the second crankshaft 22 and the first camshaft 31. The first timing device 39. linked via
Furthermore, the first crankshaft 2. and the second camshaft 312 are the second
It is interlocked via a timing device 392. First timing device 39
．． is the second drive gear 372 and the first camshaft 31. The drive gear 37. The drive gear 37 meshes with the
Timing gear 40 with twice the number of teeth than 2. It consists of
The second timing device 392 is connected to the first driving gear 371 and the second timing device 392.
Cam shaft 31. The drive gear 37. is fixed to the drive gear 37. and meshes with the drive gear 3γ1. Timing gear 40□ with twice the number of teeth
It consists of Therefore, the first and second drive gears 37. ．． 372 is the synchronizer 36 and the first . Second timing device 39. ．． It serves as both components of 392.

Each timing device 39. ．． In order to eliminate the backlash of 392, each timing gear 4o, 4o is divided into two gears 40α, 40h that can rotate slightly relative to each other, and between these two gears 40ct, 40b, An elastic member 41 that exerts elastic force so as to shift the phase is interposed.

In addition, in order to absorb torque fluctuations between the synchronizer 36 and one output shaft 43 (described later), the driven gear 38 is divided into an outer ring 38α on the tooth side and an inner ring 38b on the boss side, which can rotate relative to each other within a specified range. At the same time, a torque member 42 is interposed between the two wheels 38Q and 384, which deforms when a rotational torque of a predetermined value or more is applied.

As shown in FIG. 5, the inner ring 38b of the driven gear 38 passes through the front half of the central block 6c from the transmission chamber 36 and passes through the crankshaft 2. ．． 2. The output shaft 43 is spline-coupled to the rear end of a hollow output shaft 43 that extends parallel to the output shaft 43, and an input member of the multi-disc friction clutch 440, that is, a clutch outer 44α, is spline-coupled to the front end of the hollow output shaft 43. In this way, the clutch 44 is disposed at the forefront of the front of the engine E in the vehicle. Therefore, the clutch 44 is effectively cooled by the traveling wind.

The front end of the output shaft 43 is supported by the center block 6c via a bearing 45, and the rear end is supported by a speed change input shaft 49, which will be described later, via a bearing sleeve 46 fitted into a hollow portion of the output shaft 43.

Here, both crankshafts 2. ．． 22 axis is both camshaft 3
1. , 31□ and the output shaft 43.
(See Figure 2). In this case, the base α of triangle A, that is, both camshafts 31, . If both crankshafts 21.2□ are arranged on a straight line connecting the axes of cylinders 5. .

52 horizontal configurations are obtained, the two hypotenuses of triangle A.

C1, that is, the straight line connecting the axes of the second camshaft 312 and the output shaft 111143, the first camshaft 312 and the straight line C1 connecting the axes of the first camshaft 311 and the output shaft 43. Second crankshaft 2. ．． 2
□ respectively, or both crankshafts 2. ,2. If placed inside the triangle, both cylinders 5. ,5. X of
A shaped device is obtained.

A transmission chamber 47 is provided on the lower surface of the center block 6C between it and the lower surface of the center block 6C.
A transmission case 48 defining a transmission chamber 4 is connected to the transmission case 48.
At 7, a transmission T is constructed.

That is, the output shaft 49.50 is the crankshaft 2. .

A multi-stage gear train 51.2 is arranged in parallel with the shafts 49.50 and has different gear ratios. ．． 512...51
n is provided.

In the illustrated example, the manual speed change shaft 49 has a pair of front and rear bearings 52. between the central block 6C and the transmission case 4B.
52', and the transmission output shaft 50 is supported by the transmission case 48 via a pair of front and rear bearings 53, 53'.

The speed change input shaft 49 is formed long so that its front end protrudes from the front end surface of the output shaft 43 through a bearing sleeve 46 fitted in the hollow portion of the output shaft 43, and the clutch is attached to the front end. 44 output member, i.e. clutch inner 44h
are connected by splines.

A speed change output shaft 5 protruding from the rear surface of the mission case 48
At the rear end of 0, there is a propeller shaft for rear wheel drive of motorcycle M (
A final output shaft 54 that drives a motor (not shown) is connected via a torque lever mechanism 55.

As shown in FIG. 5, the first crankshaft 2. At the rear end of
An end plate 57α of a rotor 57 in the alternating current generator 56 is tapered fitted and fixed with a bolt 58.

A starting speed reduction device 59 for amplifying and transmitting the starting torque of the starting motor 20 to the first crankshaft 2□ is disposed between the end plate 57a and the central block 6C. The output gear 59a of the device 59 is connected to the first crankshaft 2. It is fitted to the end plate 57a so as to be relatively rotatable therein, and is connected to the end plate 57a via a roller type opening/closing member 60.

As shown in FIG. 3, a central block 6C and a cylinder head 10. ．． 102 includes a cylinder 5. .

52 and combustion chamber 9. ．． 92) 61. ．． 61. are formed respectively, and these water jackets 61. ．． 61. A water pump drive gear 63 for driving a water pump (not shown) that supplies cooling water to the
is fixed to the clutch outer 44α as shown in FIG.

An oil pump 64 is attached to the transmission case 48 as shown in FIG.
Oil pump drive gear 6 for driving this oil pump 64
5 is fixed to the rear end of the output shaft 43 adjacent to the driven gear 38, as shown in FIG.

In addition, 66 in FIG. 5 covers the clutch 44 and is fixed to the front surface of the central block 6C. A front cup <-166r covers the starting/decelerating device 59, the generator 56, and the torque damper 55 and is fixed to the rear surface of the central block 6C. This is the rear cover.

Next, the operation of this embodiment will be explained.

Both crankshafts 21 are placed on the base α of the triangle A.

2, if both cylinders 5+ and 52 are arranged horizontally, the first and second pistons 41+42 move in opposite directions like in a conventional horizontally opposed engine. Similar to a type engine, this alone balances not only the primary inertial force of the first and second piston 41°42 systems, but also all or most of the secondary inertial force,
Vibrations caused by these inertial forces can be eliminated or significantly reduced. Moreover, in this case, the total width of the engine L can be reduced to about half that of a conventional horizontally opposed engine.

On the two hypotenuses of triangle A, the first. The second crankshafts 21.2□ are arranged respectively, or both crankshafts 21.2□ are arranged inside the triangle Δ. ．． 2t, both cylinders 51, 5. If they are arranged in an X shape, the first and second
Piston 4. ．． By appropriately selecting a phase of 4°, the first and second crankshafts 2, . Just by attaching a balance weight to the appropriate position of 22, it is possible to eliminate or significantly reduce the vibration caused by the primary inertial force, similar to the conventional V-type machines. The overall width of the engine in this case is shorter than that between V-type machines. In particular, the first. Second crankshaft 21 .

22 on the two oblique sides and c of the triangle A, the second camshaft 316, the first crankshaft 21 and the output shaft 43, and the first camshaft 312 and the second crankshaft 'tl
lI2 and the output shaft 43, the distance between adjacent axes is minimized, and the timing device 39. ．． 392 and synchronizer 36
can be made more compact.

Now, if the starting motor 20 is started to start the engine E, the starting torque of the drive shaft 20α is
9 and is amplified at the first crankshaft 2.9 via the overrunning clutch 60 and the end plate 57.2 of the rotor 57. is transmitted to the second crankshaft 22 via the synchronizer 36, and is transmitted to the second crankshaft 22 via the synchronizer 36. ,2. Since both are cranked at the same time, engine E can be started.

During operation of the engine E, the first and second crankshafts 2, 122 rotate synchronously to drive the respective drive gears 37. .

372, the driven gear 38 is decelerated and driven. The rotational torque of the driven gear 38 is sequentially transmitted to an output shaft 43, a clutch 44, and a speed change input shaft 49, and then to a multi-stage gear train 51.
．． The output is transmitted to the transmission output shaft 50 and the final output qll154 through a gear train selected from the gear train 51, and is further transmitted to the rear wheel Wr of the motorcycle M through a propeller shaft (not shown) to drive it. . The relatively large torque fluctuation that occurs during this time is absorbed by the buffering action of the torque damper mechanism 55 and the torsional action of the output l111I43 and the speed change input shaft 49.

In particular, the output shaft 43 and the speed change λ motor! 1t1149 is formed long so as to pass through the front half of the central groove 6c,
The clutch 4 is fitted into each other and is connected to the clutch 4 at the front end.
4, so in effect, the central block 6
A long transmission shaft corresponding to twice the distance of the penetration section c is constructed, and an effective torsional action can be exerted.

The above gear shifter, output i11+49.50 and hii[l'l
Since the transmission bsT consisting of +51° to 5112 is located directly below the central block 6C, even if the transmission 7 is a heavy object, it will not upset the left-right balance of the engine E when mounted on the vehicle. Moreover, since the transmission T does not protrude to the left and right sides of the engine E, it does not restrict the left and right bank operation of the motorcycle AI.

Further, the first and second crankshafts 21+22 are connected to the first and second timing devices 39. , 392 to rotate the second and first camshafts 312.31 degrees of mutually opposite systems, thereby actuating both the valve actuators 3 and 3o2 to operate the intake and exhaust valves 23, 392.
p”+1232.

242 is opened and closed.

By the way, the first crankshafts 2. and the second camshaft 311, as well as the distance between the second crankshaft 22 and the first camshaft 31, are determined by the distance between the two cylinders 5, . 52, the distance between each timing device 39. , 392 can be made compact, and errors in valve opening/closing timing can be reduced.

In the illustrated example, the synchronizer 36 and the timing device 39. .

39 is configured as a gear type, but it can also be configured as a chino or belt type. Further, the synchronizer 36 may be connected to both crankshafts 2. ,2. It may also be configured to rotate in the opposite direction.

C゛00 Invention As described above, according to the present invention, first and second crankshafts are arranged parallel to each other and separated from each other on a horizontal plane, and connecting rods are connected to these first and second crankshafts, respectively. first and second pistons that are connected to each other; and first and second pistons that slidably accommodate the first and second pistons, respectively.
a cylinder, first and second camshafts for valve operating disposed above the first and second cylinders in parallel with the crankshaft, and disposed on both the crankshafts in conjunction with the camshafts; The two cylinders are arranged adjacent to each other in the axial direction of the crankshaft, and each of the crankshafts is interlocked with the opposite camshaft via a timing device. Since the axis of the crankshaft is located within the triangular range connecting the three axes of the camshaft and the output shaft, it is more compact than the conventional horizontally opposed or V-type machines, and yet has the same size. A multi-cylinder internal combustion engine that can exhibit vibration reduction effects can be provided. Furthermore, since the distance between the crankshaft and camshaft of the opposite system is very short, the timing device that connects the shafts can be constructed compactly, thus making the engine even more compact and lightweight. Discrepancies in the opening and closing timing of the valve can be made extremely small.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention, and FIG. 1 shows an embodiment of the present invention. If, a side view of a motorcycle equipped with a C-type multi-cylinder internal combustion engine, Figure 2 is a cross-sectional rear view of the engine, and Figure 3 is a side view of a motorcycle equipped with a C-type multi-cylinder internal combustion engine.
4 is a sectional view taken along the line IV--IV in FIG. 3, and FIG. 5 is a longitudinal developed view of the engine.

Claims (1)

[Claims] first and second crankshafts arranged parallel to each other and separated from each other on a horizontal plane, first and second pistons connected to the first and second crankshafts via connecting rods, respectively; and first and second cylinders that slidably accommodate second pistons, and first and second cylinders for valve operating that are respectively disposed above the first and second cylinders in parallel with the crankshaft. a camshaft; and a common output shaft disposed on both the crankshafts in conjunction with the camshafts, the two cylinders are arranged adjacent to each other in the axial direction of the crankshafts, and each of the crankshafts has an opposite output shaft. Q characterized in that the crankshafts are interlocked with the camshaft of the system via a timing device, and the axes of the two crankshafts are arranged in a triangular range connecting the axes of the two camshafts and three axes of the output shaft. , 11. C-type multi-cylinder internal combustion engine.