Continuous variable suction system

A continuous variable suction system wherein the inner rotor is additionally installed at the inner side of the outer rotor to increase the variable scope of the suction runner length such that the runner length of an optimal suction air passage per speed and load of an engine can be embodied to enhance the engine's performance. A dual rotor structure is formed to reduce the volume of the inner rotor, thereby decreasing the size of the surge tank, whereby lightness of the suction system can be realized and the manufacturing cost can be also saved by minimizing the size of the suction system.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority of Korean Patent Application No. 10-2003-0062659, filed on Sep. 8, 2003, the disclosure of which is incorporated fully herein by reference.

FIELD OF THE INVENTION

The present invention relates to a continuous variable suction system and, more particularly, to a continuous variable suction system adapted for use with a dual rotor to embody the optimum suction runner length in response to the rotating speed and the load of an engine, thereby improving the engine's performance.

BACKGROUND OF THE INVENTION

Conventionally, a so-called variable suction system, in which the suction runner length supplied to the combustion chamber is varied in response to the operating state of an engine, serves to lengthen the suction runner at a low speed and on a low load to increase the inertia force for an increased efficiency, and to shorten a suction runner at a high speed and on a high load to reduce the suction resistance for an increased efficiency.

In order to make the suction runner variable, the surge tank and the suction manifold are increased in size, and the surge tank and the suction manifold are formed in a compact external size, if possible, in terms of engine room layout.

SUMMARY OF THE INVENTION

The present invention provides a continuous variable suction system adapted to obtain a variable scope of the suction runner length under a wide range and simultaneously to reduce the size of the surge tank and suction manifold, thereby providing an optimum suction runner in response to the operating condition of the engine and an efficient engine compartment layout.

In accordance with a preferred embodiment of the present invention, the continuous variable suction system comprises the suction housing formed at one side thereof with an inlet for introducing intake air and formed at a peripheral surface of the suction housing with an outlet communicating with the combustion chamber of an engine. An inner rotor is shaped like a hollow cylinder and rotatably provided in the suction housing and formed at a peripheral surface thereof with an outlet for discharging air. An outer rotor is so positioned in the suction housing as to circumferentially form an air passage between the inner rotor and the suction housing, and formed at a peripheral surface thereof with an outlet for discharging air. Baffles are respectively provided inside the suction housing and the outer rotor to circumferentially form helical suction passages. An inner rotor guide and an outer rotor guide respectively protrude into the outer rotor and the suction housing at the inner rotor and the outer rotor to thereby block a circumferential flow passage between the baffles. A rotational force transferring means is connected from the inner rotor to the outer rotor to transfer rotational force.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

The preferred embodiment of the present invention will now be described in detail with reference to the annexed drawings, where the present embodiment is not limiting the scope of the present invention but is given only as an illustrative purpose.

Referring toFIGS. 1,2and3, the continuous variable suction system according to an embodiment of the present invention includes an inner rotor60and an outer rotor70to form a dual air passage in the suction housing50. The suction housing50, the inner rotors60and outer rotors70have inlets51,61and outlets52,62,72for allowing air to be introduced and discharged.

The inlet51for introducing intake air is formed at one side of the suction housing50. A plurality of outlets52are circumferentially formed along the suction housing50parallel with the inlet51.

The outlet52is connected to a fixed runner53for providing the intake air to the engine combustion chamber. A helical baffle75toward a peripheral direction of the outer rotor70is formed along the inner circumferential surface of the suction housing50.

The inner rotor60, shaped like a hollow cylinder which functions as a surge tank, is rotatably formed in the suction housing50and is circumferentially formed with the outlet62for discharging air. The inner rotor60is disposed toward the inlet51of the suction housing50with the opened inlet61. The inner rotor60is fixed to a motor shaft55connected to the suction housing50for rotation.

The outer rotor70is positioned in the suction housing50to circumferentially form an air passage between the inner rotor60and the suction housing50and is circumferentially formed with an outlet72. A helical baffle65facing toward a peripheral direction of the inner rotor60is formed along the inner circumferential surface of the outer rotor70.

Next, referring toFIG. 5, the inner rotor60and the outer rotor70are circumferentially formed with inner and outer rotor guides66,76, each protruding toward an inner circumferential direction of the outer rotor70and the suction housing50for blocking the air passage from the circumferential direction between the helical baffles65,75.

Furthermore, stoppers79and59for restricting the rotation scope of the inner rotor60and the outer rotor70are respectively formed along the inner circumferential surface and lateral surface of the outer rotor70and the suction housing50.

Meanwhile, between the inner rotor60and the outer rotor60, there is a rotational force transferring means for transferring the rotational force of the inner rotor to the outer rotor within a predetermined scope. The rotational force transferring means includes a resilient member80connected from the shaft55for rotating the inner rotor60to the outer rotor70. Preferably, the resilient member80is made of a rubber member, a coil spring, or the like.

In other words, rotation of the two rotors60and70is effected by a motor shaft55directly connected to the inner rotor60. The inner rotor60and outer rotor70are connected by the resilient member80such that when there is a small rotational force, the inner rotor60and outer rotor70are integrally rotated as shown inFIG. 4. But when the outer rotor70is hitched by the stopper59, only the inner rotor60is rotated.

In an embodiment of the present invention, the variable scope of the suction runner length is very large. The cross-sectional area of the variable runner embodied by the outer rotor70and the cross-sectional area of the variable runner embodied by the inner rotor60can be differently set up, as depicted inFIG. 3.

Generally, as illustrated inFIG. 3, since the radius of the curvature (R1) of the outer runner is larger than that (R2) of the inner runner, it is advantageous to use the outer runner for high speed and use the inner runner for low speed.

Consequently, it is advantageous that the height (H1) of the outer runner is made higher than that (H2) of the inner runner. A larger cross-sectional area for the variable runner is obtained by integrally rotating the inner and outer rotors60and70at a high speed, and the length thereof is made variable. Preferably, it is advantageous for the inner rotor60to be additionally rotated while the length of the outer runner is maximized at a low speed to additionally embody an inner variable runner of a small cross-sectional area.

For example, if the maximum radius of the suction system formed on an engine room layout is approximately 200 mm, then the maximum length is 500 mm, H1=H2=40 mm, and each wall is 3 mm for a high output of an engine, R1=77 and R2=34. If the rotational scope of the inner and outer runners is 260 degrees, sufficient variable lengths of respectively 350 mm and 154 mm can be obtained.

Next, the operation of the continuous variable suction system as constructed above will be described.

Referring again toFIG. 3which features a minimum runner length, outlets62,72of the inner and outer rotors60,70are so positioned as to be directly connected to an entry of the fixed runner53such that the shortest oil passage can be formed from the center of the surge tank (S) to the fixed runner53.

Referring toFIG. 4, the inner and outer rotors60and70are integrally rotated clockwise from the state ofFIG. 3to allow a variable runner to be formed between the suction housing50and the outer rotor70.

Referring toFIG. 5, only the inner rotor60is rotated clockwise from the state ofFIG. 4, to allow a second variable runner to be formed between the outer rotor70and the inner rotor60, thereby forming a maximum runner length.

Because the stopper59is disposed at the inner side of the suction housing50, the outer rotor70cannot be rotated clockwise over the stopper's59position inFIG. 4by the stopper. Likewise, the stopper59disposed inside the outer rotor70prevents the inner rotor60from rotating over the stopper's59position inFIG. 5.

It should be noted that for the convenience of explanation of the present invention's operation, according to the basic position ofFIG. 3, a length change of the dual variable runner is explained only by the rotation of the inner and outer rotors60and70and rotation of the inner rotor.

However, it is advantageous to control the length of the runner in an actual engine by rotating the inner rotor60in a clockwise direction to reduce the length state of the runner inFIG. 5to that of a runner inFIG. 4and by rotating the inner and outer rotors60,70in a clockwise direction to reduce the length state of the runner inFIG. 4to that of the runner ofFIG. 3, where the maximum runner length state ofFIG. 5is given as the basic state.

In case there is a small engine displacement, the required cross-sectional area of the suction pipe is small, but the required length is long. Under this circumstance, in order to satisfy suction conditions of low, intermediate, and high speeds, it is necessary to have a runner length of large variable scope. In the suction system of the present invention, the inner rotor60is mounted onto the inner side of the outer rotor70to provide a runner length of a large variable scope such that the suction condition necessary in a small engine displacement as described above can be also satisfied.

As apparent from the foregoing, there is an advantage in the continuous variable suction system as described according to an embodiment of the present invention in that the inner rotor is additionally installed at the inner side of the outer rotor to increase the variable scope of the suction runner length such that the runner length of the optimal suction oil passage per speed and load of the engine can be embodied to enhance the engine's performance.

There is another advantage in that the dual rotor structure reduces the volume of the inner rotor, thereby decreasing the size of the surge tank such that lightness of the suction system can be realized and the manufacturing cost can be also saved by minimizing the size of the suction system when compared with other conventional suction systems that provide the same variable scope of the suction runner.

The foregoing description of the preferred embodiment of the present invention has been presented for the purpose of illustration and description. It is not intended to be exhaustive or to limit the invention to the precise form disclosed, and modifications and variations are possible in light of the above teachings or may be acquired from practice of the invention. It is intended that the scope of the invention be defined by the claims appended hereto and their equivalents.