JP2010163951A - Exhaust gas turbine generator for automobile - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an exhaust gas turbine generator, capable of reducing a thrust force generated in the shaft direction of a turbine shaft without adding a specific structure to an exhaust gas turbine. <P>SOLUTION: Each of turbines 20 and 30 is a radial turbine configured to introduce exhaust air through a turbine inlet 21, 31 provided in the circumferential direction thereof, to rotate a turbine impeller 23, 33 including a blade 24, 34 raised thereon by the exhaust gas, and to discharge the exhaust gas to a turbine outlet 23, 32 provided in the shaft direction of a rotary shaft 11. At least two turbines and a generator 40 are disposed on the rotary shaft, and at least the two turbines are composed of at least one turbine with a turbine outlet turned to one shaft direction, and at least one turbine with a turbine outlet turned to the other shaft direction opposed to the one shaft direction. The turbine inlets of at least the two turbines are arranged so that the exhaust gas energizes the blades of the respective turbines to rotate at least the two turbines in the same direction. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an exhaust turbine power generator that generates power by exhaust of an internal combustion engine mounted on an automobile (hereinafter simply referred to as a vehicle).

  There has been proposed a method for effectively using, as energy, exhaust discharged after combustion of fuel in an internal combustion engine mounted on a vehicle. For example, there is a method in which an exhaust turbine is provided in an exhaust pipe of an internal combustion engine, exhaust is led to the exhaust turbine, the exhaust turbine is rotated, and the energy of the exhaust is effectively used as electric energy by a power generator connected to the turbine shaft. It has been proposed (see Patent Document 1). Furthermore, in order to increase the efficiency of the exhaust turbine, a scroll turbine that reduces the fluid resistance of the exhaust gas introduced into the exhaust turbine and a variable capacity turbine that appropriately controls the flow rate of the exhaust gas that changes depending on the operating state have been proposed. (See Patent Document 2).

Japanese Utility Model Publication No. 6-67802 JP 2002-195046 A

A turbine of an exhaust turbine power generation device mounted on a vehicle has a limited installation space, and thus a small radial turbine is often used. FIG. 10 shows a cross-sectional explanatory diagram of an example of an exhaust turbine power generator to which the small radial turbine disclosed in Patent Document 1 is applied. As shown in FIG. 10, the radial type turbine introduces exhaust EG from a turbine inlet (turbine scroll) 701 in the circumferential direction. The exhaust EG urges the blades 704 standing on the turbine impeller 703 to rotate the turbine impeller 703. Thereafter, the exhaust EG is discharged from a turbine outlet 702 provided in the axial direction of the turbine shaft 706 along the meridional plane 705 of the turbine impeller 703. When using a radial turbine, the turbine outlet to the turbine wheel 703 high exhaust EG-pressure at the back (back side of the meridian plane 705) of the turbine wheel 703 and flows at a pressure of P ₂ as shown in FIG. 10 Press in the 702 direction. On the other hand, the exhaust EG discharged from the turbine expands to a pressure P ₁ that is smaller than the pressure P _2, and presses the turbine impeller 703 in the direction opposite to the turbine outlet 702. The difference between the pressure P ₂ and the pressure P ₁ is positive, and the thrust force pushes the turbine impeller 703 toward the turbine outlet 702. Therefore, a thrust bearing is required, and problems such as a decrease in turbine efficiency due to the mechanical loss and wear of the thrust bearing occur.

  In order to solve the above-described problem, the technique disclosed in Patent Document 1 is provided with fins on the rear surface of the turbine impeller, and the exhaust is moved in the radial direction by centrifugal force to prevent the inflow of exhaust and reduce the thrust force. . However, the fins are disposed close to the turbine housing and may come into contact with each other by slight swinging of the turbine impeller in the axial direction. In order to prevent this contact with certainty, it was necessary to use a bearing that restricts the axial movement of the turbine wheel as well as the thrust bearing. In addition, the installation of a new fin on the rear surface of the turbine impeller causes a reduction in turbine efficiency and a complicated operation in manufacturing and assembly, which may reduce performance and productivity.

  The present invention has been made in view of the above problems, and without adding a special configuration to the exhaust turbine, reducing the thrust force generated in the axial direction of the turbine shaft, reducing the turbine efficiency, and reducing the engine load. An object of the present invention is to provide an exhaust turbine generator that operates sufficiently even when the temperature is low.

  The present invention relates to an exhaust turbine power generator that generates power by rotating a turbine with exhaust from an internal combustion engine. The turbine introduces the exhaust gas from a turbine inlet provided in a circumferential direction, rotates a turbine impeller having blades erected by the exhaust gas, and discharges the exhaust gas to a turbine outlet provided in an axis direction of a rotating shaft. It is a radial type turbine that discharges The rotating shaft includes at least two turbines and a generator. The at least two turbines include at least one turbine having the turbine outlet directed in one axial direction, and the turbine outlet has the turbine outlet. And at least one turbine directed in the other axial direction opposite to the one axial direction. The turbine inlet is arranged such that exhaust urges the blades of each turbine such that the at least two turbines rotate in the same direction.

  In such a configuration, since at least two turbines having turbine outlets facing each other are provided on the same rotating shaft, the thrust force generated by each turbine by exhaust gas introduced into the turbine and discharged from the turbine outlet is generated. Can cancel each other.

  The said structure WHEREIN: The said rotating shaft can be comprised so that one turbine, a generator, and another turbine may be arrange | positioned in order. Further, the exhaust system of the internal combustion engine can be divided into two systems, one system introducing exhaust into the one turbine, and the other system introducing exhaust into the other turbine. .

  The said structure WHEREIN: It is preferable that the said turbine is a twin scroll type | mold provided with the flow path of 2 or more systems which introduces exhaust_gas | exhaustion to the said turbine inlet_port | entrance. Further, the turbine is a variable capacity turbine, a jet turbo turbine having a variable flap at the turbine inlet, a turbine provided with a valve mechanism that can be opened and closed in each flow path of the twin scroll type, and the turbine blade An exhaust turbine power generator can be configured by selecting one of variable vane type turbines having a plurality of vanes whose angles are variable around the vehicle.

  According to the present invention, without adding a special configuration to the exhaust turbine, the thrust force generated in one of the turbine shafts in the axial direction can be reduced, and the turbine efficiency can be sufficiently reduced even when the engine load is low. An exhaust turbine generator that operates can be provided.

FIG. 2 is a layout diagram of an exhaust turbine power generator, showing an embodiment in which an exhaust turbine power generator is provided in a 6-cylinder engine. It is sectional drawing showing the structure of an exhaust turbine power generator. It is sectional drawing of the turbine seen from the arrow X of FIG. 2, Comprising: A scroll type turbine is demonstrated. It is sectional drawing of the turbine seen from the arrow X of FIG. 2, Comprising: A twin scroll type turbine is demonstrated. It is sectional drawing of the turbine seen from the arrow X of FIG. 2, Comprising: A jet turbo type turbine is demonstrated as an example of a variable capacity type turbine. It is sectional drawing of the turbine seen from the arrow X of FIG. 2, Comprising: A variable twin scroll type turbine is demonstrated as an example of a variable capacity type turbine. It is sectional drawing of the turbine seen from the arrow X of FIG. 2, Comprising: A variable vane type turbine is demonstrated as an example of a variable capacity type turbine. It is explanatory drawing concerning one modification of this invention. It is explanatory drawing concerning one modification of this invention. It is a section explanatory view of an example of an exhaust turbine power generator to which a small radial type turbine concerning the prior art is applied.

  DESCRIPTION OF EMBODIMENTS Hereinafter, an embodiment in which an exhaust turbine power generation device that generates power by exhaust of an internal combustion engine mounted on a vehicle according to the present invention is applied to a vehicle will be described with reference to the drawings. FIG. 1 is a layout diagram of an exhaust turbine power generator, and shows an embodiment in which an exhaust turbine power generator is provided in a 6-cylinder internal combustion engine (engine). FIG. 2 is a cross-sectional view showing the structure of the exhaust turbine power generator. FIG. 3 is a cross-sectional view of the turbine as viewed from the arrow X in FIG. 2 and illustrates the scroll turbine.

  Referring to FIG. 1, intake IG introduced from intake pipe 53 is divided into six systems and flows into intake ports of cylinders (not shown) provided in internal combustion engine 50. The intake air mixed with the fuel burns in the cylinder, and exhaust EG is discharged to the exhaust pipe. The exhaust pipe is divided into two systems that are aggregated into one exhaust pipe 51, 52 for every three cylinders. The exhaust pipe 51 sends the exhaust EG to one turbine 20 of the exhaust turbine power generator 10, and the exhaust pipe 52 sends the exhaust EG to the other turbine 30 of the exhaust turbine power generator 10.

  The turbines 20 and 30 are so-called radial turbines. As an exhaust turbine power generator for a vehicle, a radial turbine that is easy to manufacture in order to reduce the size and cost is widely applied. The exhaust EG is introduced from turbine inlets 21 and 31 arranged in the circumferential direction of the respective turbines 20 and 30. Referring also to FIG. 2, the exhaust EG rotates the turbine impellers 23 and 33 provided with the blades 24 and 34, and discharges them to the turbine outlets 22 and 32 provided in the axial direction of the rotary shaft 11. The turbine inlets 21 and 31 are arranged so that the exhaust EG urges the blades 24 and 34 provided upright on the turbine impellers 23 and 33 so that the turbines 20 and 30 rotate in the same direction. Has been. A generator 40 is disposed between the turbines 20 and 30.

  Referring to FIG. 2, the generator 40 is accommodated in a generator housing 41, and the rotor 42 of the generator 40 is directly connected to the rotating shaft 11. A stator 43 corresponding to the rotor 42 is fixed to the inner peripheral surface of the generator housing 41. In such a configuration, when the turbines 20 and 30 are rotated by the exhaust gas, the rotor 42 is rotated and electric power can be generated. The generated electric power is used to recover the energy of the exhaust gas, and can be charged, for example, or supplied to an electric motor provided in the engine drive system.

  The turbines 20 and 30 are accommodated in turbine housings 26 and 36. Between the turbine housings 26 and 36 and the generator housing 41, bearing mechanisms 60 and 60 that support the rotary shaft 11 are provided. Then, in order to prevent the exhaust EG from leaking from the turbine housings 26, 36 to the generator 40, the seal ring 61 is provided between the bearing mechanism 60 and the turbines 20, 30 so as to cover the periphery of the rotary shaft 11. The turbine housings 26 and 36 and the generator housing 41 between the bearing mechanism 60 and the generator 40 are provided.

  Referring to FIG. 3, the turbines 20 and 30 viewed from the arrow X in FIG. 2 are configured such that the exhaust EG is introduced into the turbine inlets 21 and 31 from the same direction. The exhaust EG is gradually throttled from the turbine inlets 21 and 31 and blown out from the blowout ports 25 and 35 to the blades 24 and 34 (see FIG. 2) provided upright on the turbine impellers 23 and 33. The exhaust gas EG is introduced from the blowout ports 25 and 35 to the blades 24 and 34 (see FIG. 2) so as to go around the turbine impellers 23 and 33 as indicated by arrows. The flow path through which the exhaust EG passes is a scroll SC whose cross-sectional area is gradually reduced, and the fluid resistance is reduced to improve the efficiency of the turbines 20 and 30. With this configuration, the turbines 20 and 30 directly connected to the rotating shaft 11 can be rotated in the same direction.

In the turbines 20 and 30 in operation, a thrust force similar to the thrust force pushing the turbine impeller 703 in the direction of the turbine outlet 702 generated by the difference between the pressure P ₂ and the pressure P ₁ shown in FIG. 10 is generated. However, since the thrust force in the left direction of FIG. 1 is generated in the turbine 20 and the thrust force in the right direction of FIG. 1 is generated in the turbine 30, both cancel each other. Thus, this embodiment can reduce a thrust force effectively with a simple structure, without adding a special structure.

  Next, a modification of the present embodiment will be described with reference to the drawings. FIG. 4 is a cross-sectional view of the turbine as viewed from the arrow X in FIG. 2 and illustrates a twin scroll turbine. FIG. 5 is a cross-sectional view of the turbine as viewed from an arrow X in FIG. 2 and illustrates a jet turbo turbine as an example of a variable capacity turbine. FIG. 6 is a cross-sectional view of the turbine as viewed from an arrow X in FIG. 2 and illustrates a variable twin scroll turbine as an example of a variable capacity turbine. FIG. 7 is a cross-sectional view of the turbine as viewed from an arrow X in FIG. 2, and illustrates a variable vane turbine as an example of a variable capacity turbine. In addition, the modification demonstrated here differs in the form of a turbine, and does not change the fundamental structure of the exhaust-turbine power generator shown in FIG. 1 or FIG.

  Referring to FIG. 4, the twin scroll turbine 120 divides the exhaust EG flow path between the turbine inlet 121 and the outlet 125 into two systems. The internal combustion engine 50 (see FIG. 1) of the vehicle is a reciprocating engine, and the exhaust EG is discharged intermittently (pulsed), and the discharge timing is different for each cylinder. For this reason, the exhaust EG collects in the exhaust pipe 51 (see FIG. 1), and the exhaust EGs interfere with each other, resulting in a problem of reducing the efficiency of the turbine. The twin scroll turbine 120 includes two scrolls SC1 and SC2 having different flow path lengths, thereby adjusting the time for the exhaust to reach the turbine impeller 24 and passing through the exhaust EG1 and the scroll SC2 passing through the scroll SC1. The pulse effect of exhaust EG2 is effectively used. With this configuration, it is possible to prevent a decrease in turbine efficiency.

  Next, a modified example in which the variable capacity turbine is applied to the present embodiment will be described. The variable displacement turbine changes the flow passage cross-sectional area of the exhaust sent to the turbine in accordance with the amount of exhausted gas. Referring to FIG. 5, a jet turbo turbine 220 which is one of variable displacement turbines is provided with a movable flap VF at the outlet 225. As shown in FIG. 5A, when the gas amount of the exhaust EG is small, the movable flap VF is moved in the direction in which the blowout port 225 is throttled. And as shown in FIG.5 (b), when there are many gas amounts of exhaust_gas | exhaustion EG, the movable flap VF is moved in the direction where the blower outlet 225 is expanded. By moving the movable flap VF, the jet turbo turbine 220 increases the flow rate of the exhaust gas EG by reducing the flow passage cross-sectional area when the gas amount is small, and increases the flow passage cross-sectional area when the gas amount is large. The exhaust gas EG is adjusted so that the flow rate of the EG does not become excessive, and the appropriate exhaust EG is introduced into the turbine impeller 24.

  Referring to FIG. 6, a variable twin scroll turbine 320, which is one of the variable capacity turbines, flows to each of the two scrolls SC1 and SC2 having different flow path lengths of the twin scroll turbine 120 described in FIG. Valves SCV1 and SCV2 that are movable so as to open and close the path are provided. As shown in FIGS. 6 (a) and 6 (b), the variable twin scroll turbine 320 adjusts the channel cross-sectional area in the same manner as the jet turbo turbine 220 by opening and closing these valves SCV1 and SCV2. A simple exhaust EG is introduced into the turbine impeller 24.

  Referring to FIG. 7, a variable vane turbine 420 that is one of variable displacement turbines is provided with variable vanes VV that are movable blades around the impeller 24. As shown in FIG. 7A, when the gas amount of the exhaust gas EG is small, the movable vane VV is moved so as to narrow the cross-sectional area of the exhaust gas EG. Then, as shown in FIG. 7B, when the gas amount of the exhaust EG is large, the movable vane VV is moved so as to widen the cross-sectional area of the exhaust EG. The variable vane turbine 420 moves the movable vane VV so that when the gas amount is small, the flow passage cross-sectional area is reduced to increase the flow velocity of the exhaust EG, and when the gas amount is large, the flow passage cross-sectional area is increased. The exhaust gas EG is adjusted so that the flow rate of the EG does not become excessive, and the appropriate exhaust EG is introduced into the turbine impeller 24.

  By applying the scroll turbine and variable displacement turbine described above to the exhaust turbine generator according to this embodiment, the exhaust turbine generator can be moved reliably even when the internal combustion engine has a low rotational speed and a small amount of exhaust gas. Can be made. Further, the variable capacity turbine adjusts the amount of exhaust gas introduced into the left and right turbines 20 and 30 shown in FIG. 1 to balance the thrust forces generated by the turbines 20 and 21, respectively. Can be adjusted to cancel each other.

  As described above in the embodiments of the present invention, the present invention can effectively reduce the thrust force generated in the axial direction of the turbine shaft without adding a special configuration to the exhaust turbine. In this embodiment, a 6-cylinder internal combustion engine has been described, but it goes without saying that the present invention can be applied to a 4-cylinder or 8-cylinder internal combustion engine. This is the end of the description of the specific embodiment, but the aspect of the present invention is not limited to the above embodiment. For example, as shown in an explanatory view according to the modification 500 of the present invention in FIG. 8, a configuration may be adopted in which one turbine 520, another turbine 530, and a generator 540 are arranged on the rotating shaft 511 in this order. With such a configuration, a seal ring that prevents the exhaust gas from leaking to the generator 540 may be provided between the other turbine 530 and the generator 540. Also in the modified example 500, the thrust force generated by one turbine 520 and the other turbine 530 can be offset.

  In addition, as shown in the explanatory view according to the modified example 600 of the present invention in FIG. At this time, the exhaust outlets of the turbines 620 and 621 arranged on the left side of FIG. 9 are in the direction of arrow L, and the exhaust outlets of the turbines 630 and 631 arranged on the right side are in the direction of arrow R. The thrust force generated by the left and right turbines can be offset.

DESCRIPTION OF SYMBOLS 10 Exhaust turbine power generator 11 Rotating shaft 20, 30 Turbine 21, 31 Turbine inlet 22, 32 Turbine outlet 23, 33 Turbine impeller 24, 34 Blade 25, 35 Outlet 26, 36 Turbine housing 40 Generator 41 Generator housing 42 Rotor 43 Stator 50 Internal combustion engine 51, 52 Exhaust pipe 53 Intake pipe 60 Bearing mechanism 61 Seal ring

Claims (6)

An exhaust turbine power generator that generates power by rotating a turbine with exhaust from an internal combustion engine,
The turbine introduces the exhaust gas from a turbine inlet provided in a circumferential direction, rotates a turbine impeller having blades erected by the exhaust gas, and discharges the exhaust gas to a turbine outlet provided in an axis direction of a rotating shaft. Is a radial type turbine that exhausts
At least two turbines and a generator are disposed on the rotating shaft,
The at least two turbines include at least one turbine with the turbine outlet directed in one axle direction, and at least one turbine axis with the turbine outlet directed in the other axle direction facing away from the one axle direction. The turbine, and
The exhaust turbine generator according to claim 1, wherein the turbine inlet is arranged such that the exhaust urges the blades of each turbine such that the at least two turbines rotate in the same direction.   The exhaust turbine power generator according to claim 1, wherein one turbine, a generator, and another turbine are arranged in order on the rotating shaft.   The exhaust system of the internal combustion engine is divided into two systems, one system introduces exhaust into the one turbine, and the other system introduces exhaust into the other turbine. The exhaust turbine power generator described in 1.   The exhaust turbine power generator according to any one of claims 1 to 3, wherein the turbine is of a twin scroll type having two or more flow paths for introducing exhaust gas to the turbine inlet.   The exhaust turbine power generator according to any one of claims 1 to 4, wherein the turbine is a variable capacity turbine.   The variable capacity turbine includes a jet turbo turbine having a variable flap at least at the turbine inlet, a turbine provided with a valve mechanism that can be opened and closed in each flow path of the twin scroll type, and an angle around the turbine impeller The exhaust turbine power generation device according to claim 5, wherein the exhaust turbine power generation device is any one of a variable vane type turbine including a plurality of variable vanes.

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