JPH05321685A - Supercharging device - Google Patents

Abstract

PURPOSE:To form an internal combustion engine compact by providing an actuator including a piston provided in a back surface of a housing, and a rod to be engaged with a movable sheave of a drive pulley in a hydraulic device provided on the side of the drive pulley so as to eliminate rotary seal of the hydraulic device. CONSTITUTION:A rotation speed changing device 58 is composed of a drive pulley 34, a follower pulley 22 provided with a plate spring 41, and a belt 28. The drive pulley 34 comprises a fixed sheave 37, and a movable sheave 38, and a V-groove 39 is formed. An actuator having a piston 46 and a rod 47 inside is provided in a back surface of a housing 2. The piston 46, the rod 47, an arm 50, and the movable sheave 38 are moved by hydraulic oil from a hydraulic oil source 54, so a hydraulic device for the drive pulley 34 is formed. The piston and the cylinder of the hydraulic device are installed to the back surface of the housing 2, and they are not rotated, so need of rotary seal or generation of centrifugal oil pressure is eliminated, thereby compactness of an internal combustion engine is improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a supercharging device for supercharging to improve the output of an internal combustion engine.
The present invention relates to a supercharging device having a mechanical supercharger (supercharger) whose rotational speed is controlled by a rotational speed changing device based on hydraulic control.

[0002]

2. Description of the Related Art Conventionally, a mechanical supercharger whose rotational speed is controlled by a centrifugal weight type rotational speed changing device (also abbreviated as CVT) is known from Japanese Patent Publication No. 3-500564. This type drives a runner shaft with a runner that is rotatably supported by a housing via an electromagnetic clutch and a speed increasing gear device by a secondary pulley (driven pulley) of a rotation speed changing device driven by an internal combustion engine. In this way, the internal combustion engine is supercharged.

Further, a machine in which a hydraulic device is used instead of the centrifugal weight to control the number of revolutions is known from Japanese Patent Laid-Open No. 54-55266. In this system, a hydraulic device including a cylinder and a piston is provided in the rotating portion of the drive and driven pulleys, and thereby the V groove of the pulley is changed to control the rotational speed of the driven pulley.

[0004]

However, the conventional hydraulic type has the following problems when it is used for controlling the supercharger.

That is, it is necessary to provide an oil-tight seal at the relative rotating portion, and if it deteriorates, in the case of a CVT that uses a dry belt, unlike a fluid-utilizing automatic transmission, the belt drive due to oil leakage, and eventually the It adversely affects the feeding performance and causes problems in durability and reliability.

Next, the control becomes difficult due to the generation of centrifugal hydraulic pressure, which causes a problem of unstable supercharging performance.

Further, the hydraulic piping must be installed so as not to interfere with the transmission belt or the like because the hydraulic piping is inevitably the front of the pulley in terms of space, and piping becomes difficult.

Therefore, the present invention provides a supercharging device having a hydraulic rotation speed control device (CVT) which does not require an oil-tight seal at a relative rotating portion, does not generate centrifugal oil pressure, and has easy piping. Therefore, it is an object of the present invention to solve the above problems.

[0009]

In order to achieve the above object, the present invention provides a drive pulley, a driven pulley, a belt wound between both pulleys, a spring provided on at least one of both pulleys, and a drive pulley. And a runner shaft having a runner, which is driven by an internal combustion engine and has a hydraulic device provided on the side thereof, and is rotatably supported in the housing by being driven by the rotation speed changing device via a speed increasing gear device. And a mechanical supercharger for supercharging the internal combustion engine, wherein the hydraulic device includes an actuator with a built-in piston provided on the back surface of the housing, and a rotary support for rotating the drive pulley from the piston. A rod extending through the center hole of the fixed shaft so as to engage with the movable sheave of the drive pulley.

[0010]

In normal operation, when hydraulic pressure MAX is applied by operating a manual lever or the like, the movable sheave of the drive pulley is moved by the rod so as to widen the V groove width and reduce the diameter, and the driven pulley has a narrow V groove width and a large diameter. Turn into. Therefore, the rotation speed changing device is controlled in the low speed ratio range, and the supercharger is also in the low speed range.
At this time, the spring is fully extended. On the contrary, when the hydraulic pressure is small, the high speed ratio range is reached, the supercharger has a high rotation speed, and supercharging performance is exhibited.

Since the pistons and cylinders, which are hydraulic devices, are attached to the rear surface of the housing of the supercharger in a stationary state and do not rotate, no rotary seal is required, no centrifugal hydraulic pressure is generated, and piping to the cylinder is easy. It will be.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT An embodiment of the present invention will be described below with reference to FIG. First, the configuration will be described. The mechanical supercharger 1 has a speed increasing gear device 3 and a runner shaft 5 having a runner (impeller) 4 in a housing 2 attached to a structure such as an internal combustion engine (not shown). The housing 2 is integrally assembled with the shroud 6 and the bolt 7. The shroud 6 has a horizontal cylindrical air inlet 8 and a spiral air outlet 9.

The speed increasing gear device 3 comprises an internal gear 11 which is integral with the input shaft 10, a pinion 12 and a sun gear 13. The pinion 12 has a housing 2 and a shroud 6.
It is rotatably supported by a shaft 15 on a boss 14 sandwiched between and fixed. Although not shown in the figure, two pairs of pinions 12 are paired so as to mesh with the sun gear 13 and the internal gear 11, respectively. The sun gear 13 is formed integrally with the runner shaft 5, and has a double row angular ball bearing 1.
6 rotatably supports the boss 14 via the spacer 17. A mechanical seal 18 is provided on the runner shaft 5 on the back surface of the runner 4. Lubricating oil is supplied to the ball bearing 16 from a lubricating oil supply pipe 19 provided in the upper portion of the housing 2 through a forked passage 20.

The input shaft 10 is rotatably supported by the housing 2 on the left side by two ball bearings 21, 21.

The input shaft 10 is integrally assembled with the driven pulley 22 by a nut 23 at the left end. Driven pulley 22
Has a fixed sheave 24 fixed to the input shaft 10 on the right side and a movable sheave 25 axially movable on the left side to form a V groove 29 around which a belt 28 is wound. Disc-shaped disc 26 fixed to the back surface of the movable sheave 25 and the input shaft 10.
The three disc springs 41 are held between and. In the figure, 3
0 is an oil seal.

The housing 2 has a flange 3 extending downward.
1, a fixed shaft 32 extending horizontally to the left is fixed to the flange 31 with a bolt 33. A drive pulley 34 is rotatably supported on the fixed shaft 32 by ball bearings 35. The drive pulley 34 has a fixed sheave 37 on the left side and a movable sheave 38 on the right side, thereby forming a V groove 39.

The fixed sheave 37 is axially positioned with respect to the fixed shaft 32, and is rotatable at that position.
Cylindrical part 36 for holding the outer race of the ball bearings 35, 35
Have integrally.

The movable sheave 38 is movable in the axial direction. The fixed sheave 37 has a pulley 42, which is driven by a flat belt by the crankshaft of the internal combustion engine, attached to the left by bolts 43.

An actuator 44 is fastened to the flange 31 by a bracket 45 together with a bolt 33. The actuator 44 has a piston 46 inside,
It has a horizontal rod 47 extending leftward integrally therewith. The rod 47 penetrates the center hole of the fixed shaft 32, and the left end portion 48 is engaged with a horizontal arm 50 via a thrust bearing 49. After the arm 50 penetrates the hole 51 of the circular boss of the fixed sheave 37, the right end is movable sheave 38.
It is integrated with. Piston 4 of actuator 44
The pressure oil is guided to the left chamber A of No. 6 from the hydraulic pressure source 54 through the inlet 53 by the opening degree of the valve 55. The valve 55 is adjusted by the controller 56 so that the opening degree changes from the minimum hydraulic pressure (zero) to the maximum hydraulic pressure.

Thus, the drive pulley 3 equipped with the hydraulic device
4, the driven pulley 22 and the V-belt 28 including the disc spring 41
Constitutes a rotation speed changing device 58.

Next, the operation of the above embodiment will be described. During normal operation, the valve 55 is fully opened by the control unit 59. Therefore, the maximum (MAX) pressure oil is the hydraulic pressure source 5.
4, the actuator 55 through the valve 55 and the inlet 53
Is supplied to the left chamber A of the piston 46. Therefore, the piston 46 moves to the right and pulls the rod 47 to the right as shown in FIG. 1 (shown in the upper half of the rod 47 in FIG. 1).
This causes the arm 50 to move the movable sheave 3 of the drive pulley 34.
Push 8 to the right. Therefore, the drive pulley 34 has the V groove 39.
Is widened and has a small diameter, and the driven pulley 22 has a large diameter due to the narrow V groove 29, so that the driven pulley 22 is controlled on the deceleration side, that is, on the low speed rotation side. At this time, the disc spring 41 is fully extended (see the lower half of the driven pulley 22 in FIG. 1).
Then, in this state, when the rotation of the drive pulley 34 increases, the rotation of the driven pulley 22 also increases almost proportionally.
Changes along a diagonal line a. Then, the X point is reached.

At such a low load, the rotational speed of the driven pulley 22 is small, so that the rotational speed of the supercharger 1 is also small. Therefore, the driving torque of the supercharger 1 is small and the fuel consumption can be improved.

When the load is high, the throttle opening, engine speed, etc. are detected and the controller 56 controls the valve 5
The opening degree of 5 is controlled. This controls the hydraulic pressure entering the actuator 44. Therefore, the piston 46 is the rod 4
7, the movable sheave of the drive pulley 34 is pulled to the left to narrow the V groove 39 (see the lower half of the drive pulley 34 in FIG. 1).

As a result, the V-shaped groove 29 of the driven pulley 22 is expanded (see the upper half of the driven pulley 22 in FIG. 1), and eventually the driven pulley 22 is controlled on the speed increasing side, that is, the high speed side. After that, when the hydraulic pressure in the actuator is gradually increased by the controller, the performance curve shown by the line b in FIG. 2 is obtained. When the point X is reached, the line moves on the same line as the line a (the maximum hydraulic pressure).

Therefore, the supercharger 1 sufficiently supercharges the internal combustion engine by the high speed rotation of the driven pulley 22, the input shaft 10, the speed increasing gear device 3, the sun gear 13, the runner shaft 5, and the runner 4, and Improve output.

Since the actuator 44 is attached to the rear surface of the flange 31 of the housing 2 and is in a stationary state, the inner piston 46 is merely a seal for reciprocating motion, and an oiltight seal between relative rotations. It becomes unnecessary. For this reason, the dry V belt 28 does not deteriorate the transmission efficiency due to oil leakage, and thus the durability and reliability can be improved.

The hydraulic pressure (pressure oil) in the actuator 44
Does not rotate, hydraulic pressure due to centrifugal force, that is, hydraulic pressure that changes depending on the number of rotations is not generated, and hydraulic control can be facilitated.
Further, the pipe to the actuator 44 is connected to the inlet 5 of the left ventricle A.
Since it does not have to be carried out from the front surface of the pulley (the left side in FIG. 1), the interference with the rotary belt does not occur at all. According to the present embodiment, the space on the back surface of the flange 31 can be effectively used, and there is an effect that space can be saved and compactness can be realized.

FIG. 3 shows an actuator control system of this embodiment, in which the hydraulic pressure control to the inlet 53 of the left chamber A of the actuator 44 is performed by inputting a load signal A such as an accelerator opening and a speed signal N such as an engine speed. The control unit 59 automatically controls the opening degree of the valve 55 according to the operating state.

FIG. 4 shows another embodiment. This example
The hydraulic pressure control for both the inlet 53 of the left chamber A and the inlet 60 of the right chamber B of the actuator 44 is performed by controlling the opening degree of the three-way valve 61 by the same control unit 59 as in the previous embodiment. Is. The hydraulic operation to the actuator shown in FIGS. 3 and 4 may be performed by a manual changeover switch, and in this case, a supercharging effect suitable for the intention of the vehicle driver is obtained.

[0030]

As described above, according to the present invention, it is possible to improve the reliability, durability and compactness of an internal combustion engine with a supercharger equipped with a hydraulically controlled rotation speed changing device. effective.

[Brief description of drawings]

FIG. 1 is an overall sectional view showing an embodiment of the present invention.

FIG. 2 is a performance curve diagram for explaining the operation of the present invention.

FIG. 3 is a partial view showing an actuator control system of the present invention.

FIG. 4 is a partial view showing another embodiment of the present invention.

[Explanation of symbols]

 1 Supercharger 2 Housing 3 Speed-increasing gear device 4 Runner 5 Runner shaft 6 Shroud 22 Driven pulley 28 V belt 31 Flange 32 Fixed shaft 33 Bolt 34 Drive pulley 41 Disc spring 42 Pulley 46 Piston 47 Rod 48 Left end 49 Thrust bearing 50 Arm 53 Inlet 55 Valve (V) 58 Rotational speed changing device

Claims (1)

[Claims] 1. A drive pulley, a driven pulley, a belt wound between both pulleys, a spring provided on at least one of the two pulleys, and a hydraulic device provided on the drive pulley side, and driven by an internal combustion engine. And a mechanical supercharger for supercharging the internal combustion engine, comprising: a rotation speed changing device; and a runner shaft with a runner, which is driven by the rotation speed changing device through a speed increasing gear device and rotatably supported in a housing. The hydraulic device includes a piston built-in actuator provided on the back surface of the housing, and a movable sheave of the drive pulley that extends from the piston through a central hole of a fixed shaft for rotationally supporting the drive pulley. And a rod extending so as to engage with the supercharging device.