JPH0592429U - Supercharger - Google Patents

Abstract

(57) [Abstract] [Purpose] The present invention has an optional specification with an actuator and a standard specification without an actuator to improve fuel efficiency while maintaining good drivability of an internal combustion engine with a supercharger. Its purpose is to be compatible with. The present invention relates to a rotational speed changing device driven by an internal combustion engine, which includes a driving pulley, a driven pulley, a belt wound between both pulleys, a weight provided on at least one of the pulleys, and a spring, and driven by an internal combustion engine. A mechanical supercharger for supercharging the internal combustion engine, comprising a runner shaft with a runner, which is driven by the rotation speed changing device via a speed increasing gear device and rotatably supported in a housing; An input pulley detachably attached to the pulley, wherein the input pulley transmits the driving force from the internal combustion engine and has an actuator inside, and controls the biasing force of the spring; It only transmits driving force, and either one can be selectively attached.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a supercharging device for supercharging to improve the output of an internal combustion engine, and more particularly to a mechanical supercharger in which the rotation speed is controlled by a centrifugal weight type rotation speed changing device. The present invention relates to a supercharging device.

[0002]

[Prior 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, which is rotatably supported by a housing through 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. This will supercharge the internal combustion engine. Although the publication does not disclose the primary pulley (drive pulley) of the rotation speed changing device, this portion has a drive pulley and a driven pulley as disclosed in, for example, Japanese Utility Model Laid-Open No. 1-69400. Each has a fixed sheave (disk) that is staggered, and a movable sheave that allows the V groove to be variable with respect to them. Furthermore, a centrifugal force generating weight (weight) and an urging force generating opposing weight are generated. A spring is used which any one of the pulleys has. With the conventional engine, even if the engine speed changes, the rotation speed changing device controls the rotation speed of the turbocharger so that the rotation speed is almost constant within a predetermined range. The supercharger was operated by the power transmission by the electromagnetic clutch only when the high load required supercharging, and the performance of the internal combustion engine was improved.

[0003]

[Problems to be solved by the device]

 However, the conventional centrifugal weight type CVT-equipped mechanical supercharger has a structure in which the supercharger is controlled to a predetermined constant speed when a certain engine speed is reached regardless of the load of the internal combustion engine. However, there was a problem in that even at partial load where supercharging was not required, the number of revolutions reached (higher number of revolutions), fuel consumption for driving increased, and fuel consumption became poor. In order to solve this problem, the conventional one uses an electromagnetic clutch to cut off the power transmission to the supercharger at the time of partial load, but it is necessary to improve the drivability by the on / off operation at the time of load change. Considering the effect of, the application range of cutting is narrowed, and eventually there is a problem that fuel consumption becomes poor.

In order to solve this problem, it may be considered to install a spring biasing force control actuator. However, if the actuator is simply installed, there is a problem that it is difficult to set a standard specification without an actuator.

Therefore, the present invention aims to solve the above-mentioned problems by proposing a supercharger capable of easily setting a standard specification without an actuator and an optional specification with an actuator. ..

[0006]

[Means for Solving the Problems]

 In order to achieve the above object, the present invention comprises a driving pulley, a driven pulley, a belt wound between both pulleys, a weight provided on at least one of the pulleys, and a spring, and is driven by an internal combustion engine. And a runner shaft with a runner rotatably supported in the housing driven by the rotation speed changing device via a speed increasing gear device. It comprises a feeder and an input pulley detachably attached to the drive pulley.The input pulley transmits the driving force from the internal combustion engine and has an actuator inside, so that the biasing force of the spring is applied. Either the control unit or the one that only transmits the driving force from the internal combustion engine can be selectively installed.

[0007]

[Action]

 In the case of an optional specification in which an actuator is provided on the input pulley, when the load is low during normal operation, the movable sheave of the drive pulley, which is biased by the spring, is resisted against the spring by the actuator of the control device. Since the width is widened, the supercharger is driven in a controlled state on the deceleration side, that is, the low rotation side of the rotation speed changing device. Therefore, fuel consumption is low. Therefore, since the transition from the low rotation side to the high rotation side or vice versa is the transition to the intermediate rotation speed, there is no shock like the conventional power disconnection, and good drivability can be achieved. ..

Further, in the case of the standard specification in which the input pulley is not provided with an actuator, the rotation of the supercharger is maintained constant without the above control. And, it is easy and convenient to set standard specifications and optional specifications by installing or not installing the actuator on the input pulley.

[0009]

【Example】

 An embodiment with an actuator (optional specification) according to 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 by 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 includes an internal gear 11 integrated with the input shaft 10, a pinion 12, and a sun gear 13. The pinion 12 is rotatably supported by a shaft 15 on a boss 14 which is sandwiched and fixed between the housing 2 and the shroud 6. Although not shown in the figure, two 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 is rotatably supported by the boss 14 via the spacer 17 by the double-row angular ball bearing 16. 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 at an upper portion of the housing 2 through a bifurcated 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. The 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, and has a V groove 29 around which a belt 28 is wound. Form. A roller (weight) 27 for generating a centrifugal force is held between the back surface of the movable sheave 25 and the conical plate 26 that fixes the input shaft 10. In the figure, 30 is an oil seal.

The housing 2 has a flange 31 extending downward, and a support shaft 32 extending horizontally to the left is fixed to the flange 31 with a bolt 33. The drive pulley 34 is rotatably supported on the support shaft 32 by ball bearings 35, 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 has a tubular portion 36 which holds the outer race of the ball bearings 35, 35 so that the fixed sheave 37 is axially positioned with respect to the support shaft 32 and is rotatable at that position.

The movable sheave 38 is provided with five disc springs 41 between the back surface and the end plate 40 positioned on the tubular portion 36, and is movable in the axial direction by receiving the biasing force thereof. The fixed sheave 37 has an input pulley 42, which is driven by a flat belt 60 by a crankshaft of an internal combustion engine, detachably attached to the left side by a bolt 43. Thus, the drive pulley 34 provided with the disc spring 41, the driven pulley 22 provided with the rollers 27, and the V-belt 28 constitute a rotation speed changing device 58.

The input pulley 42 has a space 61 inside which functions as the actuator 44. That is, the hydraulic cylinder 44a of the actuator 44 is integrally formed in the inner diameter of the input pulley 42 in a concentric cylindrical shape. A piston 46 is reciprocally fitted in the cylinder 44a. The cylinder 44a and the piston 46 rotate together with the input pulley 42. The right side surface of the piston 46 is in contact with a horizontal cylinder 50. After the arm portion of the cylinder 50 penetrates the boss hole 51 of the fixed sheave 37, the right end of the arm portion contacts the movable sheave 38 at the contact surface 52. The left chamber A of the piston 46 of the actuator 44 is provided with an inlet 53 provided at the right end of the support shaft 32, a hole 32a bored along the center line of the support shaft 32, and a radial hole 42b of the central boss 42a. As a result, pressure oil is guided from the hydraulic pressure source 54 by the opening degree of the valve 55. The valve 55 is connected to the regulator 57 so as to be operated by a regulator 57 that makes the opening of the accelerator pedal 56 large when the load is low. As a result, the hydraulic pressure supplied decreases as the load increases, reaching a maximum hydraulic pressure at low load and zero hydraulic pressure at high load.

Thus, the actuator 44, the hydraulic power source 54, the valve 55, and the regulator 57 control the urging force of the disc spring 41 of the drive pulley 34 when the engine is operating under low load or high load. Since the rotation speed of the feeder 1 is controlled so as to be changed, the control device 59 for controlling the rotation speed changing device 58 is configured. In FIG. 1, 46a is a seal device for the piston 46, and 32b is a seal device for the rotating portion of the support shaft 32.

Next, the operation of the above-described embodiment (with optional specifications) will be described with reference to FIG. During operation of the engine, when the accelerator pedal 56 has a small opening and a low load, the valve 57 is fully opened by the regulator 57, and the maximum (MAX) pressure oil is supplied to the hydraulic source 54, the valve 55, the inlet 53, and the hole 32a. , Is supplied to the left chamber A of the piston 46 of the actuator 44 through the hole 42b. Therefore, the piston 46 moves to the right (shown in the upper half of the piston 46 in FIG. 1). As a result, the cylinder 50 is pushed to the right, pushing the movable sheave 38 of the drive pulley 34 to the right, and contracting the disc spring 41 so that it is in a substantially vertical state. Therefore, the driving pulley 34 has a large V groove 39 with a small diameter, and the driven pulley 22 has a large V groove 29 with a large diameter, so that the driven pulley 22 is controlled on the deceleration side, that is, on the low speed rotation side. Then, in this state, when the rotation of the drive pulley 34 increases, the rotation of the driven pulley 22 also increases almost proportionally and changes along the diagonal line a in FIG. Then, the X point is reached.

Therefore, at such a low load, since the rotational speed of the driven pulley 22 is small, the rotational speed of the supercharger 1 is also small, and therefore, the driving torque thereof is also small, and the fuel consumption can be improved. ..

At the time of high load in which the opening degree of the accelerator pedal 56 is large, the valve 55 is fully closed by the regulator 57, and the hydraulic pressure entering the left chamber A of the actuator 44 becomes zero. For this reason, since the piston 46 is not subjected to hydraulic pressure to the right, the movable sheave 38 of the drive pulley 34 narrows the V groove 39 by the biasing force of the disc spring 41 (below the drive pulley 34 in FIG. 1). See half).

As a result, the V groove 29 of the driven pulley 22 expands (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. .. In this state, the hydraulic pressure on the line b in FIG. 2 is zero.

Therefore, the supercharger 1 performs sufficient supercharging to the internal combustion engine by 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.

Further, at the time of transition from low load to high load or vice versa, in the present embodiment, the difference H between the lines a and b in FIG. 2 is sufficient and the change is continuous. Is less and improves drivability.

On the other hand, the conventional electromagnetic clutch has a large difference H ₀ up to the line b in FIG. 2, so that the shock is great and the drivability is adversely affected.

From the above, during normal operation from a low load to a high load, what is shown by the portion between the ab lines in FIG.

Thus, in the above-described embodiment, the hydraulic cylinder 44a is formed in the input pulley 42 driven by the flat belt 60 by the crankshaft of the internal combustion engine, and the piston 44 is incorporated into the hydraulic cylinder 44a to mount the actuator 44 in the hydraulic cylinder 44a. Since it is configured, there is an advantage that the extra space does not need to be increased by effectively utilizing the space inside the input pulley.

Further, the input pulley 42 is usually changed at the same time when the type of engine changes, but at that time, the internal piston 46 is also changed as a set, and it is convenient because it can be a control device according to the type of engine. is there.

Furthermore, since the input pulley 42 can be used as an input pulley regardless of the formation or non-formation of the hydraulic cylinder, the actuator in the input pulley is removed, or a simple input pulley without an actuator is used. It is convenient because it is compatible with the standard specification without an actuator, as opposed to the option specification with the control device with built-in piston. In other words, options can be set easily and variety will increase.

Also, if the type of engine changes, the input pulley will also change, and at that time, since the input pulley is detachably mounted on the drive pulley, if a pulley without an actuator is used, the standard specifications will be obtained. This is convenient because it can be done.

An embodiment using a simple pulley without an actuator (standard specification) will be described below with reference to FIG. Since the driven side of this embodiment is the same as the optional specification of the previous embodiment, it is omitted and only the lower half of the drive side is shown in FIG. Therefore, to explain this different part, the inside of the input pulley 42 that is detachably attached to the drive pulley 34a with the bolts 43 is a space 61a without an actuator, and the support shaft 32a is a solid shaft and is driven. The movable sheave 38a and the fixed sheave 39a that form the pulley 34a have a structure in which the former can only move axially on the cylindrical portion 36a of the latter. The movable sheave 38a and the fixed sheave 39a constitute the V groove 39a, the movable sheave 38a is biased by the disc spring 41, and the drive pulley 34a is rotatably supported by the support shaft 32a. , 35 are the same as in the previous embodiment.

Next, the operation of this embodiment (standard specification) will be described with reference to FIG. 3 and FIG. Since the control device including the actuator of the previous embodiment is not provided in this device, the driven pulley 22 and the supercharger 1 (see FIG. 1) are maintained at a substantially constant rotation speed regardless of the load of the engine. It That is, as shown in FIG. 4, if the rotation of the driven pulley 22 is further increased after the number of rotations of the drive pulley reaches the point c, the centrifugal force of the rollers 27 causes the driven pulley 22 to have a large diameter. If the drive pulley 34a becomes smaller in diameter and decelerates, and conversely decelerates, the speed will be reversed and the speed will increase, and even if the rotational speed of the drive pulley 34a changes, it will move along the straight line d and become constant. Is. Since there is no load control in this embodiment, it is simplified and simplified accordingly.

[0032]

[Effect of the device]

 As described above, according to the present invention, it is possible to easily change the setting from the standard specification without the actuator to the optional specification with the actuator, or vice versa. is there.

[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 embodiment of the present invention.

FIG. 3 is a partial sectional view showing another embodiment of the present invention.

FIG. 4 is a performance curve diagram for explaining the operation of 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 Support shaft 32a hole 33 Bolt 34 Drive pulley 41 Disc spring 42 Input pulley 44 Actuator 44a Cylinder 46 Piston 50 Cylindrical 52 contact surface 53 inlet 55 valve (V) 58 rotational speed changing device 59 controller 60 flat belt 61 space

Claims (1)

[Scope of utility model registration request] 1. A rotation speed changing device driven by an internal combustion engine, comprising a drive pulley, a driven pulley, a belt wound between both pulleys, and a weight and a spring provided on at least one of the pulleys. A mechanical supercharger for supercharging the internal combustion engine, comprising a runner shaft with a runner that is rotatably supported in a housing and is driven by the rotation speed changing device via a speed increasing gear device; An input pulley detachably attached to the input pulley, wherein the input pulley transmits a driving force from an internal combustion engine and has an actuator inside, and controls an urging force of the spring.
A supercharging device characterized by being selectively mounted with only one transmitting a driving force from an internal combustion engine.