JPS62189327A - Supercharger of engine - Google Patents

Abstract

PURPOSE:To improve the response of an exhaust turbo supercharger, the output and fuel consumption in high rotation region and provide a compact mechanical supercharger by interposing the mechanical supercharger in a first intake path. CONSTITUTION:A bypass valve 19 is closed under the running condition in low rotation and low load, and a mechanical supercharger 17 is stopped so that respective cylinders I-VI are subjected to supercharging intake by an exhaust turbo supercharger 11. Under the running condition in low rotation and high load is closed the bypass valve 19 while the mechanical supercharger 17 is driven so that the cylinders I, III and V in a first intake path 1A are further supercharged with the addition of supercharging pressure due to the mechanical super charger 17.

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to improvements in engine supercharging devices.

(Prior art) Conventionally, in a supercharged engine, an exhaust turbo supercharger (
A mechanical supercharger (supercharger) is added to the turbocharger to improve responsiveness during acceleration in the low rotation range (see proposal).

However, in this supercharged engine, the exhaust turbo supercharger and mechanical supercharger independently supercharge all cylinders, so each supercharger becomes larger, and as the size increases, the responsiveness increases. There was a problem in that the performance was lowered and there was also a disadvantage in terms of mountability.

(Purpose of the Invention) The present invention has been made to solve the above-mentioned conventional problems, and it improves the response of the exhaust turbo supercharger, improves the output in the high rotation range, improves fuel efficiency, and improves the performance of the mechanical supercharger. The purpose is to reduce the size.

(Structure of the Invention) Therefore, the present invention includes an exhaust turbo supercharger driven by exhaust gas, and a first intake passage that communicates an intake passage downstream of the supercharger with some cylinders; It is characterized in that it is divided into a second intake passage that communicates with the remaining cylinders, and that a mechanical supercharger that is driven by the drive shaft of the engine is interposed in the first intake passage.

According to the present invention, the exhaust turbo supercharger provided in the intake passage supercharges some of the cylinders through the first intake passage, supercharges the remaining cylinders through the second intake passage, and supercharges the remaining cylinders through the second intake passage. A mechanical supercharger installed in the first intake passage provides additional supercharging to the negative cylinder.

As a result, the response of the exhaust turbo supercharger is improved due to the suction force of the mechanical supercharger, and as a result, a large exhaust turbo supercharger can be used, increasing the output in the high rotation range. , fuel efficiency will improve.

Furthermore, since the mechanical supercharger only supercharges the negative cylinder, it can be made smaller and can be more easily mounted.

(Embodiments) Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 shows an example of a 6-cylinder engine E, in which cylinder 1
．． I[[, V and cylinders n, IV, and VT are arranged in parallel.

Each intake boat for cylinders +, m, and v has a first intake passage I branched from the main intake passage I on the downstream side of the air cleaner 7.
The branch passages 1a, 3a, and 5a of A are connected to each other, and the cylinders It, ! Each intake boat of V and Vl has a second
Branch passages 2a and 4a of intake passage IB.

6a are connected to each other.

Each exhaust boat for the cylinders n, IV, and Vl has a second exhaust passage 2 branched from the main exhaust passage 2 on the upstream side of the catalyst 8.
B branch passages 2b, 4b, and 6b are connected to each other, and the cylinders 1. Branch passages 1b, 3b, and 5b of the first exhaust passage 2A are connected to each exhaust boat of I[[, V, respectively.

Fuel injection valves 1c to 6c are provided in the intake side branch passages 1a to 6a of the cylinders 1 to 2, respectively.

Throttle valves 10A and IOB are provided midway between the first intake passage IA and the second intake passage IB, respectively.

The main intake passage 1 is provided with a compressor lla of the exhaust turbo supercharger 11, the main exhaust passage 2 is provided with a turbine llb of the exhaust turbo supercharger 11, and the turbine llb and the compressor lla are connected to each other. is the drive shaft lie
are connected with.

A bypass passage 13 is provided that communicates the downstream and upstream sides of the turbine Ilb of the main exhaust passage 2, and the bypass passage 13 has a wastegate valve 14 that opens and closes the passage 13.
is provided.

A mechanical supercharger 17 is provided in the first intake passage IA between the branch part of the main intake passage 1 and the throttle valve lOA,
A bypass passage 18 is provided that communicates the upstream and downstream sides of the mechanical supercharger 17 in the first intake passage IA, and the bypass passage 18 is provided with a bypass valve 19 that adjusts the opening degree of the passage 13. It is being

The in-vehicle controller (CPU) 16 includes each intake passage I.
Pressure sensors 20 and 21 are connected to detect the pressure on the downstream side of the throttle valves 10A and 10B of A and IB, and the actuator 22
．． 28 connects the wastegate valve 14 and the bypass valve 1.
9 is controlled to open and close.

No. 7 electromagnetic clutches 24 are connected.

Furthermore, a detection signal of the engine rotational speed is also input to the controller I6.

In the low rotation and high load range (indicated by hatching) as shown in FIG. 2(a), the electromagnetic clutch 24 is turned on and the mechanical supercharger 17 is driven, while as shown in FIG. 2(b)
As shown in , the bypass valve 19 is controlled to be closed in a low rotation range and opened in a high rotation range.

With the above configuration, in the operating state in the low rotation and low load range, the bypass valve 19 is closed and the mechanical supercharging @ 17 is also stopped, so each cylinder 1 to ■ is subjected to exhaust turbo supercharging! 11
11 supercharges and intakes the air.

On the other hand, in the operating state in the low rotation and high load range, the bypass valve 19
is closed (see Fig. 2(b)), but since the mechanical supercharger 17 is driven (see Fig. 2(a)), the solid line T/C in Fig. 2(C) Since the supercharging by the exhaust turbo supercharger 11 shown in FIG. 12 and the supercharging pressure by the mechanical supercharger 17 shown by the chain line S/C are added, it becomes the first intake.

By driving this Ja acupuncture supercharger 17, a suction horn acts on the turbine Ila of the exhaust turbo supercharger 11, so that the response of the exhaust turbo supercharger II is improved. With this improvement in response, a large-sized exhaust turbo supercharger 11 can be used, so it is possible to improve output and fuel efficiency, especially in high-speed ranges.

Furthermore, since the exhaust turbo supercharger 11 is driven by the exhaust gas from the cylinders I, III, and V that is charged by the mechanical supercharger 17, transient response is also improved.

Then, the opening degree of the bypass valve 19 is adjusted according to the operating state, and the supercharging pressure of the mechanical supercharger 17 is controlled.

Note that in a high rotation range, the electromagnetic clutch 24 may be disengaged to stop the mechanical supercharger 17. In this case, since the pulley ratio of the mechanical supercharger 17 can be increased, the supercharging pressure in the low to medium rotation range can be increased.

The exhaust turbo supercharger 11 is driven by exhaust gas from cylinders n, IV, and Vl that are supercharged by the exhaust turbo supercharger 11.

Therefore, during high rotation, cylinders n, 1, and 2 can be supercharged more efficiently.

[Brief explanation of drawings]

Fig. 1 is a configuration diagram of an engine supercharging device according to the present invention, Fig. 2 (a) is a graph showing the operating range of the mechanical supercharger, and Fig. 2 (b) shows the opening degree of the bypass valve. Graph, Figure 2 (
c) is a graph showing changes in supercharging pressure. 1～■...Ki L E...Engine, IA,
IB...Intake passage, 2A, 2B...Exhaust passage, 11
...exhaust turbo supercharger, 16...controller, 17...mechanical supercharger,
18...Bypass passage, 19 Bypass valve.

Claims (1)

[Claims] (1) Equipped with an exhaust turbo supercharger driven by exhaust gas, the intake passage downstream of the supercharger is divided into a first intake passage that communicates with some of the cylinders and a second intake passage that communicates with the remaining cylinders. 1. A supercharging device for an engine, characterized in that the first intake passage is divided into a first intake passage, and a mechanical supercharger driven by a drive shaft of the engine is interposed in the first intake passage.