JPH1181934A - Valve spring seat structure for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve spring seat structure which is suitable for a motorcycle. SOLUTION: A valve spring seat 172, having a substantially U-shaped section, is composed of a bottom surface 174 which is abutted against an axial positioning surface 173 formed on a cylinder head 129H, an outer rib 175 and an inner rib 176 bent from the bottom surface 174. The outer rib 175 has a diameter to the extent that it is abutted against a diametral positioning surface 177 formed on the cylinder head 129H. The inner rib 176 has a diameter larger than an outer diameter of a valve guide 163. As a result, a valve stem seal 171 can be arranged on an inner side of the inner rib 176. In addition, a stem 165 can be remarkably shortened compared to a conventional case.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve spring seat structure for an internal combustion engine (hereinafter, referred to as "gasoline engine" or simply "engine"), and more particularly to an engine suitable for a hybrid motorcycle having both an engine and an electric motor. The present invention relates to a valve spring seat structure.

[0002]

2. Description of the Related Art At present, vehicles using a gasoline engine as a drive source are mainly used, but in places where emission of exhaust gas must be avoided, an electric vehicle using a motor as a drive source is required. 2. Description of the Related Art Demand for a hybrid vehicle equipped with both an engine and an electric motor has been increasing due to reasons such as an increase in body weight and a short traveling distance in an electric vehicle.

[0003] For example, Japanese Patent Application Laid-Open No. HEI 8-175577, entitled "A device for switching power between an engine and a motor of a motorcycle or the like" is an invention relating to a hybrid type motorcycle. The engine 10 of the above publication is a simple air-cooled two-cycle engine.

However, some motorcycles are equipped with a four-cycle engine according to various requirements. The four-stroke engine has a problem in that the overall height of the engine is higher than that of the two-stroke engine, and the power unit becomes large when mounted on a hybrid power unit that requires compactness.

FIG. 14 is a view showing a main part of a conventional valve operating mechanism. A valve guide 203 faces an exhaust port 202 of a cylinder head 201, and a stem 205 of a valve 204 can slide on the valve guide 203. By inserting the retainer 206 into the distal end portion of the stem 205 and applying one end of a valve spring 207 to the retainer 206, the valve 204 is urged in the valve closing direction. The valve 204 is pushed out in the valve opening direction, and the valve 204 is returned by the valve spring 207 in the valve closing direction.

Reference numeral 211 denotes a valve stem seal, which is a component for maintaining airtightness between the stem 205 and the valve guide 203. A valve spring seat 212 is a positioning / holding member for one end (the lower end in the figure) of the valve spring 207.

[0007]

The valve spring seat 21 is provided.
Reference numeral 2 denotes a member for positioning in the radial direction by setting an inner rib on a perforated disk and fitting the inner rib to the valve guide 203. When trying to reduce the height of the stem 205 as a part of miniaturization of the hybrid engine, the engaging groove for the valve stem seal 211 comes down. Therefore, it becomes difficult to position the valve spring seat in the radial direction. Therefore, an object of the present invention is to provide a compact valve spring seat structure suitable for a hybrid engine.

[0008]

In order to achieve the above object, a first aspect of the present invention is a valve spring seat interposed between one end of a valve spring for biasing a valve of an internal combustion engine in a closing direction and a cylinder head. This valve spring seat is a ring having a substantially U-shaped cross section including a bottom surface corresponding to an axial positioning surface formed on the cylinder head, and outer and inner ribs bent from the bottom surface, and the outer rib is formed on the cylinder head. The inner rib has a diameter larger than the outer diameter of the valve guide.

Therefore, since the radial position of the valve spring seat is determined by the outer rib and the valve spring is held by the inner rib, the stem height can be reduced and the valve height can be reduced. In addition, the valve mechanism can be made compact, and the valve spring seat can be positioned.

[0010]

Embodiments of the present invention will be described below with reference to the accompanying drawings. The drawings should be viewed in the direction of reference numerals. FIG. 1 is a side view of a motorcycle according to the present invention. The motorcycle 1 has a box-shaped main frame 2 also serving as a battery storage box disposed at the center lower portion, and extends an inverted U-shaped front swing arm 4 from a lower front portion of the main frame 2 via a front pivot shaft 3. Then, the front wheel 5 is rotatably mounted on the front swing arm 4, while the head pipe post 7 extends obliquely upward from the upper front part of the main frame 2, and the head pipe 8 is fixed to the tip of the head pipe post 7. A handle post 9 is rotatably attached to the head pipe 8, a steering arm 11 is attached to a lower end of the handle post 9, and a tip (lower end) of the steering arm 11 is connected to a knuckle 12 attached to the front wheel 5. Further, the power unit 15 can be swung through a rear pivot shaft 13 as a swing shaft on the upper rear portion of the main frame 2. Mounting, mounting the rear wheel 16 to the power unit 15, a rear cushion 17 in front of the rear wheel 16 in the drawing, the back of the rear wheel 16 the air cleaner 18,
An exhaust pipe 19, a muffler 21, and a tail pipe 22 are arranged, and a vehicle body is surrounded by a front fender 25, a front cover 26, a front handle cover 27, a center cowl 28, a rear cowl 29, and a rear fender 31 from front to rear.

Reference numeral 30 denotes a stem shaft, 32 denotes a front brake disk, 33 denotes a caliper, 34 denotes a resin spring, 35 denotes a front damper, 36 denotes a leg shield,
37 is an occupant step, 38 is a side stand, and 39 is a main stand. In the upper part of the drawing, 41 is a horn, 42 is a front lamp, 43 is a handlebar, 44
Is a grip, 45 is a ventilation duct, 46 is a radiator, 4
7 is a fan, 48 is a seat, 49 is a helmet box, 51 is a helmet, 52 is a tail lamp, and 55 is a power unit case. The power unit case 55 includes left and right crankcases 55a and 55b (the right right crankcase 55b is not shown) and a transmission case 55c.
And a motor case 55d and a speed reducer case 55e.

FIG. 2 is a side sectional view of the power unit of the present invention. The power unit 15 comprises a cylinder head having two intake and exhaust camshafts as shown in FIG.
Equipped with cycle engine, and) power unit case 55
A crankshaft 56 is arranged at a lower portion inside the clutch shaft, and a clutch shaft 57 is arranged parallel to and above the crankshaft 56, and a transmission shaft 58 and an electric motor shaft 59 are provided at one end of the clutch shaft 57 with a vehicle longitudinal direction (vehicle longitudinal direction). ), Wherein the clutch shaft 57, the transmission shaft 58, and the electric motor shaft 59 are arranged in series, and these are arranged in parallel with the crankshaft 56 and at a higher position.

Since the clutch shaft 57, the transmission shaft 58, and the motor shaft 59 are arranged in series in the vehicle longitudinal direction, the direction of the force acting on the power unit case 55 is simplified. Therefore, the design of the power unit case 55 becomes easy.
Specifically, the rigidity can be increased in the direction in which the force acts, and the rigidity can be decreased in the direction in which the force does not act. As a whole, the power unit case 55 can be made lighter by the amount of the simplified acting force. As a result, the power unit case 55 can be made compact.

In the figure, 75 is a planetary gear reducer, 76
Is a potentiometer, which is a shift control motor 9 described later.
5 is a device for detecting the rotation angle. 121 is a cam shaft drive pulley, 78 is a water pump driven by the pulley 121, 7
Reference numeral 9 denotes a belt cover, and reference numeral 103a at the lower center of the figure denotes an oil pump case.

The primary drive gear 61, the primary driven gear 62, the centrifugal clutch 67, the transmission 70, and the electric motor shaft 59 (the electric motor 80 when the electric motor 80 assists as a motor) constitute an "power transmission system from the engine". The motor shaft 59 when the motor 80 is operating as a motor serves as a “power transmission system from the motor”. The details of each device related to the clutch shaft 57, the transmission shaft 58, and the motor shaft 59 will be described with reference to another drawing.

FIG. 3 is a plan sectional view of the power unit of the present invention, and the details of the device and the transmission form of the driving force will be described with reference to FIG. A primary drive gear 61 of a crankshaft 56 drives a primary driven gear 62 rotatably mounted on a clutch shaft 57.
7 drives the clutch inner 68 independently of the clutch shaft 57, so that the primary driven gear 62, the clutch outer 64 of the one-way clutch for the starter, and the clutch inner 68 of the centrifugal clutch 67 can be connected by the cylindrical member 66. When the inner speed of the centrifugal clutch 68 becomes equal to or higher than a predetermined number of revolutions, the outer shaft 69 of the centrifugal clutch is rotated, and the clutch shaft 57 starts rotating. The primary drive gear 61 has a structure in which a burr gear 61a and a spring 61b are provided to prevent hitting noise.

The transmission 70 is a cone type continuously variable transmission, and its detailed operation will be described with reference to another figure. The transmission 70 is a device for transmitting power in the order of the transmission shaft 58, the inner disk 71, the cone 72, and the outer cup 73. The rotation is transmitted to the electric motor shaft 59 via the clutch 83. The motor 80 is a coreless motor. A permanent magnet rotor 81 is mounted on a motor shaft 59, and a stator coil 8 is mounted on a motor case 55d.
2 is attached. Therefore, when the centrifugal clutch 67 is turned on, the driving force is transmitted in the order of the clutch shaft 57, the transmission shaft 58, the transmission 70, and the electric motor shaft 59, and the multi-plate torque limiter 84 and the gear reduction mechanism 85 (small gear 86).
The axle 90 is driven via a large gear 87 → a small gear 88 → a large gear 89).

The multi-plate type torque limiter 84 has a motor shaft 59.
A limiter inner 84a that rotates together with the
b, 84c (the disk 84b is attached to the limit inner 84a, and the disk 84c is the limit outer 84d shown below).
Attached to ), A limiter outer 84d, and a spring 84e.
And oneness. Power is limiter inner 84 → disk 8
4b → disc 84c → limiter outer 84d → small gear 86, but if an excessive torque exceeding the set torque acts, the disc slips between the discs 84b and 84c to protect the equipment. The set torque can be adjusted by the spring 84e.

The one-way clutch outer 6 for the starter
Reference numeral 4 denotes a one-way clutch 63 which functions as a flywheel, has a balance weight 91 for balancing the engine, and is combined with the one-way clutch inner 65 for the starter to transmit the rotation of the starter. By rotating the starter driven gear 93 with a starter (not shown), the centrifugal clutch inner 68 is rotated through the one-way clutch inner 65 for the starter and the one-way clutch outer 64 for the starter to start the engine, and the one-way clutch outer 64 for the starter is moved. When the speed becomes higher, the clutch is separated from the starter one-way clutch inner 65 on the lower speed side.

In the figure, a camshaft driving pulley 121 for driving a camshaft and the like is provided at the other end (front end) of the crankshaft 56, and the pulley 121 drives a belt 122. Details of the belt 122 will be described later.

FIGS. 4 and 5 are diagrams showing the construction and operation of the cone type continuously variable transmission according to the present invention. In FIG. 4, the distance (rotation radius) from the center of the cone support shaft 74 to the inner disk 71 is R1, and the distance from the center of the cone support shaft 74 to the outer cup 7 is R1.
The distance (rotation radius) to 3 is R2, and R1> R2. The cone 72 rotates at a low speed to rotate the large diameter (R1) portion of the cone with the inner disk 71, and then the outer cup 73 rotates at a low speed to rotate the outer cup 73 at the small diameter (R2) portion of the cone 72.

Incidentally, the electric motor shaft 59 is connected to the outer cup 73 by the motor shaft 59.
When the rotation of the outer cup 73 becomes faster than that of the electric motor shaft 59 by the one-way clutch 83, the power is transmitted. 70a is the outer cup 73
Is a cam ball that pushes out to the left as viewed in the figure with rotation, and a contact pressure can be applied between the outer cup 73 and the cone 72 by this pushing action. 70
Reference numerals b, 70c, and 70d denote oil seals. The oil seals 70b and 70c form a sealed space for storing transmission oil inside the transmission 70, and the oil seal 70d shuts off oil on the side of the crankcase 55b on the left side in the figure. Therefore, there is no fear that the transmission oil mixes with the oil in the crankcase.

In FIG. 5, the distance (rotation radius) from the center of the cone support shaft 74 to the inner disk 71 is R3, the distance (rotation radius) from the center of the cone support shaft 74 to the outer cup 73 is R4, and R3 <R4. And The cone 72 rotates at a high speed to turn the small diameter (R3) portion of the cone with the inner disk 71, and then the outer cup 73 rotates at a high speed to turn the outer cup 73 at the large diameter (R4) portion of the cone 72. By moving the cone 72 in this manner, the transmission 70 exhibits functions of deceleration, constant speed, and speed increase.

For this purpose, in FIG. 4, the transmission control motor 95 controls the control gear 9 via the gears 96a, 96b, 96c.
Turn 7. The control gear 97 has a trapezoidal female thread 9 on the boss.
The trapezoidal female screw portion 99 is meshed with a trapezoidal male screw portion 98 fixed to the case 55 side.
7 moves to the left in the figure. By this movement, the cone 72 moves to the left in the figure together with the cone support shaft 74, for example, as shown in FIG.

What is important here is that the trapezoidal male / female thread 9
8 and 99 are provided not on the outer cup 73 side but on the inner disk 71 side. The cone 72 is pushed leftward in the figure by the reaction of the outer cup 73. As a result, the force of the arrow acts on the control gear 97. The arrow corresponds to the direction moving from low speed to high speed. Therefore, by adopting the structure of the present embodiment, it is possible to shift to a high speed side with a small torque, and it is also possible to reduce the capacity of the shift control motor 95.

Next, the lubrication system will be described. FIG. 6 is an explanatory diagram of the engine lubrication system according to the present invention, and the arrows indicate the flow of oil. The power unit case 55 has a lower oil tank 101 at a lower part and an upper oil tank 10 at an upper part.
2, a first oil pump 103, a second oil pump 104, and a third oil pump 105 are coaxially arranged at one end (right end) of the crankshaft 56. First, the oil in the lower oil tank 101 is supplied to the strainer 106 and the second oil pump 105. Pumped up by the first oil pump 103 through one oil passage 107,
The oil is supplied to the upper oil tank 102 via the second oil passage 108. Next, the oil in the upper oil tank 102
The oil reaches the second oil pump 104 via the oil passage 109, and the oil pressurized by the second oil pump 104 is supplied to the fourth oil passage 1
11. After lubricating the main journals 56a, 56a of the crankshaft 56, the connecting rod large end 56b, and other parts (particularly, a valve operating chamber (not shown)) via the filter 112, the fifth oil passage 113, the lower oil tank 101 Return.
112a is a filter cover.

FIG. 7 is an explanatory view of a transmission lubrication system according to the present invention. Transmission oil is supplied from a transmission oil tank 115 separately provided below the power unit case 55 via a sixth oil passage 116 to a third oil. Pumped up by pump 105,
The oil is sent to the transmission shaft 58 via a seventh oil passage 117, and the oil is supplied to the transmission 70 via an oil passage 118 in the transmission shaft 58. The oil is supplied to the transmission oil tank 11 as indicated by the arrow in the figure.
5 and is pumped up by the third oil pump 105 via the strainer 119.

FIG. 8 is a front view of a power unit showing a camshaft drive mechanism as a valve train drive mechanism according to the present invention. The left crankcase 55a is mounted on the right side of the cylinder block 129B integrated with the right crankcase 55b, the electric motor 80 is arranged above the crankshaft 56, and the cylinder head 129H is mounted on the left side of the cylinder block 129B. The muffler 21 is attached to the end of the exhaust pipe 19 extending from 129H.
This shows that the intake manifold 129M is connected to the cylinder head 129H from the air cleaner 18 at the upper left in the figure via the carburetor 129C. 129S is a starter motor mounting hole.

In the figure, since the belt cover 79 has been removed, the cam unit drive pulley 121, the belt 122, the intake side cam shaft pulley 1
23, exhaust side camshaft pulley 124 and tensioner 125
Drive mechanism 120 as a valve train drive mechanism composed of
Can be seen. Note that the belt 122 is a chain,
Since the pulleys 121, 123, and 124 can be sprockets, the belt 122 is a timing belt,
"Wrapping means" such as a V-belt, a roller chain, etc., a "camshaft driving rotating body" in which the camshaft driving pulley 121 is rotated by the wrapping means, and "cam" in which the camshaft pulleys 123 and 124 are rotated by the winding means. It is called a “shaft rotating body”, and the selection of parts is arbitrary.

As is apparent from FIG. 8, the cylinder shaft 12
6 is substantially horizontal (for example, the inclination angle α = + 10 with respect to the ground)
゜), the body is laid down in the vehicle width direction, so that the center of gravity can be reduced and the cylinder length can be accommodated within the vehicle width.

The figure corresponds to a view from the front wheel to the rear wheel. At this time, the crankshaft 56 and the clutch shaft 57 are arranged on the right side of the figure from the vehicle body center 127, and the cylinder head is located on the left side of the figure from the vehicle body center 127 129H are arranged. A power transmission system including a transmission shaft 58 and an electric motor shaft 59 is provided behind the clutch shaft 57 in the drawing.
Are connected as shown in FIGS.

FIG. 9 is an arrangement diagram of the AI reed valve and the water pump according to the present invention. Reference numeral 150 denotes an AI reed valve. AI is an abbreviation for air injection, and is a check valve provided in a system for promoting purification of exhaust gas by blowing an appropriate amount of air into an exhaust port. The structure of the AI reed valve 150 will be described with reference to FIG. 11, but since the AI reed valve 150 is provided in front of the cylinder head 129H, it is easy to remove the belt cover just as when checking the camshaft drive mechanism 120. Can be maintained. Further, with the above arrangement, the reed valve 150 can always be protected by the belt cover AI.

The common pulley 125 also serves as a pump pulley and a tensioner for adjusting the tension of the belt 122, and is rotatably mounted on the pump housing 131 of the water pump 78, and will be described later in detail. The pump housing 131 not only houses the pump rotor 132 but also has two adjusting slots 133 and 134. 1
Reference numerals 35... (... Indicate a plurality of units; the same applies hereinafter) are assembly screws for the housing. On the other hand, the cylinder block 129
B, two projecting ridges 128a are projected in parallel with each other, and a guide groove 128b is provided between them.

FIGS. 10 (a) and 10 (b) are sectional views of the water pump according to the present invention and a mounting view of a common pulley. In (a), a water pump 78 includes a pump rotor 132 and an inner magnet 136 attached to the pump rotor 132.
A rotor support shaft 137 rotatably supporting the pump rotor 132, a housing cover 131a supporting one end of the rotor support shaft 137, a housing base 131b supporting the other end of the rotor support shaft 137, and a housing base 131b. Shaft part 131c, and this shaft part 131c
139 mounted on bearings 138, 138 via bearings 138, 138
And an outer magnet 141 attached to the inner peripheral surface of the cup 139, and a common pulley 125 attached to the outer peripheral surface of the cup 139. The pump housing 131 includes a housing cover 131a, a housing base 131b, and a shaft 131c.

By the action of the belt 122, the common pulley 125,
When the cup 139 and the outer mag nut 141 rotate, the lines of magnetic force of the outer mag nut 141 pass through the housing base 131b to reach the inner magnet 136, and apply a rotational force to the inner magnet 136. Therefore, the pump rotor 132 starts to rotate. Therefore, the water pump 78
Pump water from the suction passage 142 to the pump rotor 13
2, and is supplied to the water inlet 146 of the cylinder block through the discharge passage 143 and the eccentric fitting 145. The eccentric pipe joint 145 is a joint whose inlet and outlet are eccentric by δ as shown in FIG.

Therefore, in FIG.
Is turned 90 degrees, the water pump 78 can be translated by Δ with respect to the water inlet 146 of the cylinder block as shown in FIG.

Returning to FIG. 9, by loosening the bolts 147, 147, turning the eccentric fitting 145 as shown by the arrow and moving the common pulley 125 as shown by the arrow, the tension of the belt 122 is increased, and after the adjustment, the bolt is adjusted. 147,1
Tighten 47. Since the water pump 78 is stopped by the shaft 131c (see FIG. 10B) fitted into the guide groove 128b and the two bolts 147, 147, the water pump 78 does not move except during adjustment.

FIG. 11 is a sectional view taken along line 11-11 of FIG. 9. The AI reed valve 150 is provided with an exhaust port through which an air blown from an air inlet 151 is passed through an AI port 153 opened to the reed valve 152 and the cylinder head 129H. Send to When the pressure on the AI port 153 side increases, the reed valve 152 closes, so that there is no fear that air or exhaust gas flows back to the air inlet 151.

FIG. 12 is a view showing a main part of the valve train according to the present invention. The intake valve and the exhaust valve are different in shape, material, etc., but have the same basic configuration. The valve guide 163,1 is connected to the intake port 161 or the exhaust port 162 of the cylinder head 129H.
63 and the valve 1 to the valve guides 163 and 163
64, 164 of the stems 165, 165 are slidably inserted, and retainers 166, 166 are attached to the distal ends of the stems 165, 165.
166, and the valve spring 16 is attached to the retainers 166 and 166.
7 and 167, the valves 164, 16
4 is urged in the valve closing direction, and the valves 164, 1 are lifted through lifter buckets 169, 169 by a cam (not shown).
64 is pushed out in the valve opening direction, and the valves 164, 164 are returned in the valve closing direction by the valve springs 167, 167.

FIG. 13 is an enlarged view of a main part of FIG.
Reference numeral 1 denotes a valve stem seal, which is a component for maintaining airtightness between the stem 165 and the valve guide 163. 172 is a valve spring seat. This valve spring seat 172 is formed on an axial positioning surface 173 formed on the cylinder head 129H.
, And a ring having a substantially U-shaped cross section including an outer rib 175 and an inner rib 176 bent from the bottom surface 174. The outer rib 175 has a diameter corresponding to a radial positioning surface 177 formed on the cylinder head 129H. The inner rib 176 has a diameter larger than the outer diameter of the valve guide 163 so as to leave a gap. As a result,
The valve stem seal 171 can be arranged inside the inner rib 176, and the stem 165 can be significantly shortened as compared with the conventional case.

The valve spring seat 1 of the present invention having a substantially U-shaped cross section.
72 is suitable for small engines, but may be used for medium and large engines.

[0042]

According to the present invention, the following effects are exhibited by the above configuration. According to claim 1, the radial position of the valve spring seat is determined by the outer rib, and the valve spring is held by the inner rib.
The stem height can be shortened, the valve height can be shortened, the valve operating mechanism can be made compact, and the valve spring seat can be positioned.

[Brief description of the drawings]

FIG. 1 is a side view of a motorcycle according to the present invention.

FIG. 2 is a side sectional view of the power unit of the present invention.

FIG. 3 is a plan sectional view of the power unit of the present invention.

FIG. 4 is a configuration diagram and operation diagram of a cone type continuously variable transmission according to the present invention.

FIG. 5 is a configuration diagram and operation diagram of a cone type continuously variable transmission according to the present invention.

FIG. 6 is an explanatory diagram of an engine lubrication system according to the present invention.

FIG. 7 is an explanatory diagram of a transmission lubrication system according to the present invention.

FIG. 8 is a front view of a power unit showing a camshaft drive mechanism as a valve train drive mechanism according to the present invention.

FIG. 9 is a layout diagram of an AI reed valve and a water pump according to the present invention.

FIG. 10 is a cross-sectional view of a water pump according to the present invention and a mounting diagram of a common pulley.

FIG. 11 is a sectional view taken along line 11-11 of FIG. 9;

FIG. 12 is a diagram showing a main part of a valve train according to the present invention.

FIG. 13 is an enlarged view of a main part of FIG. 12;

FIG. 14 is a diagram showing a main part of a conventional valve train.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Motorcycle, 15 ... Power unit, 129H ... Cylinder head, 163 ... Valve guide, 164 ... Valve, 167 ... Valve spring, 171 ... Valve stem seal, 1
72: Valve spring seat, 173: Axial positioning surface, 17
4 ... Bottom of valve spring seat, 175 ... Outer rib of valve spring seat, 176 ... Inner rib of valve spring seat, 177 ... Radial positioning surface.

Claims (1)

[Claims] 1. A valve spring seat interposed between one end of a valve spring for urging a valve of an internal combustion engine in a closing direction and a cylinder head, the valve spring seat being provided on an axial positioning surface formed on the cylinder head. A ring having a substantially U-shaped cross-section comprising a bottom surface, an outer rib bent from the bottom surface, and an inner rib. The outer rib has a diameter corresponding to a radial positioning surface formed on the cylinder head. A valve spring seat structure for an internal combustion engine, characterized in that the diameter is larger than the diameter.