JP2008038882A - Boost pressure control mechanism for prime engine with supercharger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a prime engine with a supercharger ensuring high torque and high output throughout a wide rotation range of the prime engine by providing a boost pressure control mechanism controlling a boost pressure with respect to the supercharger. <P>SOLUTION: The boost pressure control mechanism is provided with an opening and closing valve 4 in an exhaust pipe between the prime engine and the supercharger, and it is composed of an opening and closing valve control device 14 managing opening closing operation of the opening and closing valve. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a supercharging pressure control mechanism for a supercharged prime mover engine that uses the pressure of exhaust gas discharged from the prime mover engine to improve torque and output in the prime mover engine.

  In the conventional turbocharged engine, the exhaust gas pressure is weak due to insufficient exhaust gas amount and exhaust temperature discharged from the combustion chamber, especially in the low speed rotation region, so that the turbine blades on the turbine side can sufficiently rotate. The compressor-side impeller, which is arranged and fixed on the opposite side of the same rotating shaft as the turbine blade, does not reach high rotation. Since the compression ratio tends to be set lower than that of the equation, there is a drawback that it is difficult to secure a sufficient rotational torque in the low speed rotation region as a result.

As countermeasures, the turbine blades on the turbine side and the impellers on the compressor side were reduced in size and weight.
However, turbine blades with a reduced diameter are effective in the low and medium speed range, but the exhaust gas flow is limited and starts to clog in the high speed range. In order to ensure high output, increasing the diameter of turbine blades and compressor impellers can ensure high output in the high-speed rotation range, but sufficient torque in the low and medium-speed rotation ranges as described above. There were disadvantages such as being unable to ensure.

Problems to be solved by the invention

  As a countermeasure against the above-mentioned problems, a plurality of small blades are provided at the turbine blade turbine blade inlet and the compressor impeller outlet, and continuously variable to the optimum angle corresponding to the engine speed. A supercharger that controls the supercharging pressure has been proposed and put into practical use, but the manufacturing and assembly of the winglet and the wing support processing and drive mechanism are complicated, leading to increased costs. There were also points.

  The present invention has been made in view of the above-described problems in a prime mover equipped with a supercharger, and employs a general-purpose supercharger manufactured in the past, and controls the supercharging pressure for the supercharger. An object of the present invention is to provide a supercharged prime mover engine that secures high torque and high output over a wide rotational range of the prime mover engine by providing a supply pressure control mechanism.

Means for solving the problem

  In order to achieve the above object, according to a first aspect of the present invention, in a prime mover with a supercharger, an open / close valve is provided in an exhaust pipe between the prime mover and the supercharger and is connected to the open / close valve to open / close the valve. And a supercharging pressure control mechanism constituted by an on-off valve control device for controlling

  In order to achieve the above object, the invention according to claim 2 is a magnet support portion in which an N-pole magnet and an S-pole magnet are respectively arranged and fixed at positions opposite to the on-off valve rotation shaft outside the exhaust pipe with the rotation shaft center interposed therebetween. The electromagnet so that both ends of the electromagnet face each other on a circular orbit surface drawn by the N-pole magnet and the S-pole magnet of the magnet support portion that rotate together when the on-off valve rotates. 2. The opening and closing operation according to claim 1, wherein an opening and closing operation of an opening and closing valve is provided, wherein an electromagnet support portion fixed to the base is rotatably attached to a base side and a return spring is provided between the electromagnet support portion and the base side. Valve control device.

The invention's effect

According to the first aspect of the present invention, there is provided a supercharging pressure control comprising an on-off valve provided in an exhaust pipe between the driving engine and the supercharger, and an on-off valve controller connected to the on-off valve to control the opening and closing of the valve. When the on-off valve control device that controls opening and closing of the on-off valve disposed in the exhaust pipe continuously opens and closes by the on-off valve control device that controls the opening and closing of the on-off valve arranged in the exhaust pipe, Close the middle of the exhaust pipe upstream of the turbocharger to stop the exhaust gas flowing continuously to the upstream part of the open / close valve in the exhaust pipe to increase the pressure.When the open / close valve is open, the middle of the exhaust pipe upstream of the supercharger Open the exhaust gas, staying upstream of the on-off valve in the exhaust pipe, and adding exhaust gas that continues to be exhausted from the combustion chamber to the exhaust gas that has increased in pressure, and flowing the exhaust gas that has further increased pressure into the turbine blade on the turbine side By turbine blade Immediately start up the rotation and at the same time the compressor-side impeller placed and fixed at the other end of the same rotating shaft as the turbine blade can quickly start up the rotation, improving the response, and the impeller rotates the intake air at a high speed It is possible to pressurize with high centrifugal force obtained by the above and to supercharge the combustion chamber of the prime mover engine via the intake pipe.
And by supplying fuel in an amount corresponding to the amount of highly supercharged air, the explosion pressure at the time of combustion increases, and the same operation can be repeated in the subsequent rotation.・ Torque output can be improved.

Furthermore, since the impeller arranged and fixed at the other end of the same rotating shaft as the turbine blade that quickly starts rotating as described above can also start rotating quickly at the same time, the turbine blade on the turbine side and the impeller on the compressor side The outer diameter can be set to a large value, and the turbine blade and impeller that are set to a large size can secure high torque by the above-described supercharging pressure control mechanism in the low speed rotation range, and in the middle and high speed rotation range. The large-diameter turbine blades rotate up to a high rotation range because the exhaust gas flows without clogging, and at the same time, the impeller placed and fixed at the other end of the same rotating shaft also rotates up to the high rotation range and rotates at a high speed. The air pressurized with a high centrifugal force obtained by the above can be supercharged into the combustion chamber.
Therefore, the supercharging pressure can be increased in a wide rotation range from the low speed rotation range to the medium / high speed rotation range, so that it is possible to provide a prime mover engine that ensures high torque and high output in a wide rotation range.

  In addition, if the open / close valve is repeatedly opened and closed immediately after start-up or during idling, the exhaust gas that continues to be discharged from the combustion chamber when the open / close valve is closed is temporarily stopped at the upstream portion of the open / close valve in the exhaust pipe. The exhaust pipe upstream of the on-off valve is warmed by the gas temperature, and the temperature drop of the exhaust gas that continues to be discharged from the combustion chamber can be mitigated. This makes it possible to quickly bring the turbocharger to a high speed and to improve the purification efficiency for the exhaust gas purifying catalyst disposed in the downstream portion of the supercharger.

  According to the second aspect of the present invention, the magnet support portion in which the N-pole magnet and the S-pole magnet are respectively arranged and fixed is fixed to the opening / closing valve rotation shaft outside the exhaust pipe with the rotation shaft center interposed therebetween. The electromagnet is fixed so that both ends of the electromagnet face each other on a circular raceway surface drawn by the N pole magnet and the S pole magnet of the magnet support portion that rotate together when the opening / closing valve rotates. 2. The on-off valve control device according to claim 1, wherein the electromagnet support portion is attached to the base side in a rotatable state, and a return spring is provided between the electromagnet support portion and the base side. Uses the pressure of exhaust gas exhausted from the prime mover as a driving force source when the on-off valve controller opens and closes the valve, simplifying control and structure compared to a driving force source employing a motor, solenoid, etc. Can be opened at low cost. It can provide a closing valve control apparatus which controls the operation.

Hereinafter, a configuration of a supercharging pressure control mechanism for a supercharged prime mover engine according to an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a structural explanatory view showing a first embodiment of a supercharging pressure control mechanism in a supercharged prime mover engine according to the first aspect of the present invention, and FIG. 2 is a first embodiment. FIG. 2 is a configuration explanatory view of a section taken along the line AA ′ in FIG.
1 is the engine. Reference numerals 2 and 3 denote exhaust pipes for guiding exhaust gas after combustion in the combustion chamber of the prime mover engine 1 to the atmosphere side. Reference numeral 2 denotes a front exhaust located between the prime mover engine 1 and a supercharger 8 described later. Reference numeral 3 denotes an exhaust pipe positioned on the rear side of the supercharger 8.
4 is an open / close valve disposed in the front exhaust pipe 2, and a valve shaft 5 fixed and integrated with the open / close valve 4 is rotatably supported by bearings 6a and 6b provided in the front exhaust pipe 2. Then, the opening / closing valve control device 14 described later closes / opens the exhaust pipe 2 on the front side during driving.
The on-off valve 4 starts to open from the outer peripheral side of the housing inner surface 9 of the turbine side 7 so as to start supplying high-pressure exhaust gas from the outer peripheral side of the housing inner surface 9 of the turbine side 7 in the supercharger 8. The one open / close valve 4 rotates so as to move in the flow direction of the exhaust gas flow.
Further, the on-off valve in FIG. 2 shows a state in which the on-off valve is rotated by 90 ° from the position of the on-off valve shown in FIG. further,

In the present embodiment, the bearing portions 6a and 6b are provided on both sides of the exhaust pipe 2, but for simplification, an embodiment in which the bearing portion is set only on one of the exhaust pipe one side is also conceivable.
Further, in this embodiment, the arrangement positions of the bearing portions 6a and 6b of the valve shaft 5 in the on-off valve 4 are set on both sides in the diametrical direction of the front side exhaust pipe 2, but the BB 'cross-sectional portion in FIG. 3 and FIG. When the on-off valve 4a continues to open in the exhaust pipe 2a on the front side, the on-off valve 4a continues to open the exhaust gas flow. Other embodiments in which the bearing portions 6c and 6d of the valve shaft 5a in the on-off valve 4a are set on the side portion extension of the front exhaust pipe 2a or in the vicinity of the side portion extension are also conceivable.
In the on-off valve 4 or on-off valve 4a, when the driving engine rotates within a set rotation range, the front exhaust pipe is repeatedly closed and opened by continuously rotating in one direction.

Further, as shown in FIG. 6 which is a configuration explanatory view of the section 5 and CC ′ cross-section in FIG. 5, the arrangement position of the valve shaft 5b is integrated with one end portion of the on-off valve 4b, and both bearing portions 6e. Further, another embodiment in which 6f is set on the side surface portion of the front side exhaust pipe 2b is also conceivable.
In the on-off valve 4b, when the driving engine is rotating within a set rotation range, the exhaust on the front side is reciprocated within a range of a constant angle αA between the fully open position A and the fully closed position B in FIG. When the engine 2 is repeatedly closed and opened in the pipe 2b, and when the driving engine is rotating in the set rotation range or more, the front-side exhaust pipe 2b is provided so that the on-off valve 4b does not hinder the exhaust gas flow. It is stored on the inner side.

  Further, as shown in FIGS. 5 and 6, the on-off valve 4b is reciprocated within a range of a constant angle αA between the fully open position A and the fully closed position B within a set rotation range, so that the inside of the exhaust pipe 2b on the front side is reciprocated. In the embodiment in which the closing / opening is performed, the open position of the on-off valve 4b is not fully opened from the fully open position a in FIG. The flow of the opening of the opening / closing valve 4b in the front side exhaust pipe 2b when the opening / closing valve 4b is opened by reciprocating within the range of the limited angle αB with the opening angle narrowed. The exhaust gas flow speed is increased by narrowing the passage, and the increased exhaust gas flow is flowed into the turbine blade 10a on the turbine side 7a, and the turbine blade 10a and the compressor side impeller fixed coaxially with the turbine blade 10a. A method of maintaining the rotational force is also conceivable.

  Further, a combination method in which the rotation center lines of the valve shafts 5, 5 a, 5 b in the respective on-off valves 4, 4 a, 4 b and the rotation shaft 13 center line in the supercharger 8 described later are set in a parallel state on the same plane. Therefore, there are various combinations such as a combination method in which a sandwich angle is given on the same plane, and a combination method that is set in a non-parallel state on the same plane. For the turbine blades, the combination is set in accordance with various conditions, such as opening each on-off valve in the direction that can supply the exhaust gas flow most efficiently.

Various shapes can be considered in the planar shape and cross-sectional shape of the on-off valves 4 and 4a in FIGS. 1 to 4, and the planar shape is based on a circular shape as shown in FIG. 7 and a valve shaft as shown in FIG. A vertically long elliptical shape, a horizontally long elliptical shape with respect to the valve shaft as shown in FIG. 9, and a square shape as shown in FIG. 10 as a basic shape, a vertically long rectangular shape with respect to the valve shaft as shown in FIG. A laterally long rectangular shape or the like is conceivable with respect to the shaft. Further, in each on-off valve based on the square shape as shown in FIGS. 10, 11 and 12, each on-off valve is formed by arc-shaped corner portions. Is also possible.
Further, the cross-sectional shape of each on-off valve in the direction perpendicular to the valve shaft may be the straight shape of FIG. 13, the S-shape of FIG. 14, the elongated oval shape of FIG. 15, or the like. In addition to various cross-sectional shapes, other various planar shapes and various cross-sectional shapes are added, and the combination method most suitable for each condition is set.
Furthermore, the planar shape and cross-sectional shape of the on-off valve 4b in FIGS. 5 and 6 are basically set to a shape in which one side of the on-off valve having the above-described various planar shapes and various cross-sectional shapes and the valve shaft are integrated.

  The rotational speed at which the on-off valves 4 and 4a rotate in the exhaust pipes 2 and 2a on the front side may be a constant speed type or a variable speed type. The ratio of closing the exhaust pipe while maintaining a slight gap formed between the inner surface of the pipes 2 and 2a and the outer periphery of the on-off valves 4 and 4a, and the ratio of opening the other exhaust pipes, The ratio is set in consideration of various conditions such as the specifications of the engine, the supercharger to be combined, and how the engine is used.

Incidentally, in FIG. 16 which is a configuration explanatory view of the DD ′ cross section in FIG. 1 of the first embodiment, the one end D and the other end E of the on-off valve 4 are connected to the rotation center F of the valve shaft 5. In FIG. 16, the on-off valve 4 is continuously fixed in the same direction as the clockwise direction so that exhaust gas is supplied from the outer peripheral side of the inner surface 9 of the housing 7 on the turbine side 7. When the exhaust pipe 2 is closed at a speed, when the position of the one end D of the on-off valve 4 reaches the position of G in the exhaust pipe 2, The side between the G positions is closed, but the position between the I position and the J position on the inner surface of the exhaust pipe 2 continues to be opened until the other end E of the on-off valve 4 reaches the I position. When the end E reaches the position I on the inner surface of the exhaust pipe 2 from the position shown in FIG. Positioned between side closed to the exhaust pipe 2 is closed.
Next, when the exhaust pipe 2 is opened, after the other end E of the on-off valve 4 passes the position I in the exhaust pipe 2 and further passes the position J, the position I of the inner surface of the exhaust pipe 2 and the position J However, the position between the H position on the inner surface of the exhaust pipe 2 and the position between the G position is closed until one end D of the on-off valve 4 reaches the H position and passes through. After the end D passes through the H position, the side between the H position and the G position on the inner surface of the exhaust pipe 2 is also opened, and the inside of the exhaust pipe 2 is opened.
When the one end D of the on-off valve 4 reaches the position I in the exhaust pipe 2, the inside of the exhaust pipe 2 is closed again, and the one end D of the on-off valve 4 is After reaching and passing the position, the inside of the exhaust pipe 2 is opened again, and the opening and closing valve 4 is continuously rotated to repeatedly close and open.

As described above, when the on-off valve 4 is opened, the I position and the J position on the outer peripheral side 9 of the housing inner surface 9 on the turbine side 7 with respect to the position between the H position and the G position in the exhaust pipe 2 in FIG. By opening the space side early, exhaust gas in a high pressure state is first supplied to the outer peripheral side of the inner surface 9 of the housing on the turbine side 7, and the nozzle area center portion of the turbine inlet and the turbine blade 10 at the A / R ratio are abbreviated. As a result, it is possible to increase the speed of the exhaust gas flow on the free vortex and supply it to the turbine blade 10 as a result.
5 and 6, when the on-off valve 4b is opened, the valve shaft 5b side in the exhaust pipe 2b is always closed, so that the exhaust gas flow is the same as the position of the valve shaft 5b in the exhaust pipe 2b. Since the exhaust gas is supplied from the outer peripheral side of the housing inner surface 9a on the opposite turbine side 7a, the exhaust gas flow can be put on the free vortex and further supplied to the turbine blade 10a as a result.

Since the on-off valves 4, 4 a, 4 b are exposed to a high-temperature exhaust gas flow, they are made of a material having excellent heat resistance, and when the valve is stopped in a rotation range above the set rotation range, The on-off valves 4, 4 a, 4 b were stopped in a state parallel to the gas flow direction to cope with the hot exhaust gas flow.
Further, as shown in FIG. 16, for the purpose of reducing the temperature rise ahead of the on-off valve, a protective blade 15 may be installed in the exhaust pipe 2 in front of the valve stop position of the on-off valve 4.

  Returning to FIG. 1, reference numeral 8 denotes a supercharger that forcibly brings the turbine blade 10 on the turbine side 7 to high rotation by the exhaust gas pressure discharged from the prime mover engine 1, and the same rotating shaft as the turbine blade 10. 13 The impeller 12 on the compressor side 11 disposed and fixed at the other end is brought to high rotation, so that the air sucked by the impeller 12 in the previous period is pressurized with centrifugal force by high rotation and supercharged into the combustion chamber of the prime mover 1 To do.

  Reference numeral 14 denotes an opening / closing control device that controls the opening / closing of the on-off valves 4, 4a, 4b. The on-off valves 4, 4a, 4b are connected to the on-off valves 4, 4a, 4b by rod shafts 16 and the like. During the rotation, the on-off valves 4 and 4a arranged in the front exhaust pipes 2 and 2a are continuously rotated so that the front exhaust pipes 2 and 2b are repeatedly closed and opened. Further, the open / close valve 4b disposed in the exhaust pipe 2b on the front side is reciprocated by a constant angle.

The on-off valve control device 14 collects various information signals such as a rotation speed signal and a supercharging pressure signal of the driving engine 1, a cooling water signal, an intake air amount signal, etc., and opens and closes based on the collected various information signals. Judgment and processing of opening and closing timings of the valves 4, 4 a and 4 b, the number of opening and closing times of the on-off valves 4, 4 a and 4 b per rotation speed of the driving engine 1, and the stop positions of the on-off valves 4, 4 a and 4 b It is desirable to have a function to
When the on / off valve control device 14 determines that the on / off valves 4, 4a and 4b are to be opened / closed, an on / off valve on / off start signal is sent to the driving force source in the on / off valve control device 14 and the on / off valves 4 and 4a. When it is determined that the opening / closing stop time of 4b is determined, a signal for stopping the opening / closing valve opening / closing and stopping the opening / closing valves 4, 4a, 4b in parallel with the exhaust gas flow is used as a driving force source in the opening / closing valve control device 14. Shed.
Further, when the on-off valve control device 14 determines to increase or decrease the number of on-off valves 4, 4a, 4b with respect to the rotational speed of the prime mover 1, the on-off valve 4, 4a, 4b is used as a driving force source of the on-off valve control device 14. A signal for instructing increase / decrease in the number of times of opening / closing is sent.
However, although it is desirable to have the various functions described above, other on-off valve control devices that execute a single function or a plurality of limited functions defined from the various functions described above are sufficiently conceivable. Of course, a suitable on-off valve control device is employed.

  The on-off valve control device 14 is conventionally employed as a central control device for a driving engine, and is determined by the driving engine central control device that controls the entire driving engine from a knocking signal, a crank angle signal, and the like in addition to the above signals. A method of controlling the opening / closing of the on-off valves 4, 4a, 4b by combining processing functions is also conceivable.

  As the driving force source for opening / closing the on-off valves 4, 4a, 4b in the on-off valve control device 14, a motor, a solenoid or the like can be considered. When a motor is used, for example, the motor has a speed detection function and a position detection function. When equipped, it is easy to control the number of open / close valves and stop positions per revolution of the engine, and if a stepping motor is used, the number of open / close valves and stop positions per revolution of the engine will depend on the number of pulses supplied. It is easy to control the stop time, etc., and it is possible to temporarily stop the on-off valve when it is closed and open, and especially when it is open, the on-off valve can be quickly moved to a position that does not interfere with the exhaust gas flow. Thus, the exhaust gas can be efficiently poured into the turbine blade on the turbine side.

However, when the on-off valve 4b in the embodiment of FIGS. 5 and 6 is opened / closed by a motor, a crank mechanism is attached to the output shaft of the motor, and the rotary motion of the motor is converted into reciprocating motion by the crank mechanism. Can be reciprocated within the range of a constant angle αA between the fully open position A and the fully closed position B in FIG. 5 to close and open the exhaust pipe 2b on the front side, but the mechanism is complicated and the cost is increased. Therefore, it is preferable to use a solenoid instead of the motor and open and close the on-off valve 4b by reciprocating movement of the solenoid.
Furthermore, when the on-off valves 4 and 4a are opened and closed by a solenoid, a crank mechanism is interposed between the two, so the structure is complicated and the cost is increased. The valves 4 and 4a may be opened and closed.

  Reference numeral 17 denotes an intake pipe for guiding the air pressurized by the impeller 12 on the compressor side 11 into the combustion chamber of the prime mover engine 1.

Next, another embodiment of the arrangement position of the on-off valve with respect to the exhaust system between the prime mover engine 1 and the supercharger 8 will be described.
For example, in the first embodiment of FIG. 17, the bearing portion 6a of the valve shaft 5 is provided at the rear portion of the exhaust pipe 2 on the front side for the purpose of adopting a general-purpose supercharger manufactured and sold conventionally. , 6b, and the valve shaft 5 is rotatably attached to the bearing portions 6a, 6b, and the on-off valve 4 is fixed to and integrated with the valve shaft 5 with screws or fittings. The space between both ends of the rear part of the pipe 2 and the inlet part of the turbine side 7 of the turbocharger 8 is integrally fixed with a fastener such as a band 18 or a bolt / nut. After the valve shaft is rotatably attached to the bearing portion, the on-off valve is fixed to the valve shaft by screwing or fitting, and is further integrated with the turbine housing front portion on the supercharger side. The rear exhaust pipe rear part is integrally fixed with fasteners such as bands and bolts and nuts. In the former case, the turbocharger adopts a general-purpose product, and in the part related to the on-off valve, it is developed and manufactured by the engine manufacturer as an exclusive part most suitable for the engine. In the latter case, there is an advantage that the turbocharger manufacturer can develop and manufacture an assembly including a part related to the on-off valve.

Further, as shown in FIG. 18, there is provided an intermediate exhaust pipe 2d that is disposed and fixed between both ends of the rear side of the exhaust pipe 2c on the front side and the front side of the turbine side 7 of the supercharger 8 after assembly, In the middle exhaust pipe 2d, bearing portions 6g and 6h of the valve shaft 5c of the on-off valve 4c are provided in advance, and the on-off valve 4c is screwed or fitted to the valve shaft 5c rotatably attached to the bearing portions 6g and 6h. Other embodiments in which the front exhaust pipe 2c, the middle exhaust pipe 2d, and the supercharger 8 are assembled are also conceivable. The length of the middle exhaust pipe 2d includes a portion that closes the inside of the exhaust pipe while maintaining a slight gap formed between the inner surface of the middle exhaust pipe 2d and the outer periphery of the on-off valve 4c at least when the on-off valve 4c rotates. The length is set.
Further, for the purpose of protecting the bearing portions 6g and 6h from the influence of heat during operation of the prime mover 1, between the rear portion of the front exhaust pipe 2c and the front portion of the middle exhaust pipe 2d, and further, the rear portion of the middle exhaust pipe 2d, A gasket having a heat shielding function is sandwiched between the turbine 7 inlets of the supercharger 8 so that the valve shaft 5c of the on-off valve 4c and the bearings 6g and 6h continuously and smoothly rotate. Dealed with.

  5 and 6, when the opening and closing valve 4b is continuously reciprocated at a constant angle to open and close the exhaust pipe 2b on the front side, CC 'in FIG. 5 is taken as a dividing line. The left part of the dividing line CC ′ is constituted by the front exhaust pipe 2b, the right part of the dividing line CC ′ is constituted by the turbine housing, and the bearing parts 6e and 6f of the valve shaft 5b are provided at the front end of the turbine housing. Another embodiment in which the valve shaft 5b is rotatably disposed on the bearing portions 6e and 6f and the on-off valve 4b is fixed, and then the both are integrally fixed with a fastener such as a band or a stopper such as a bolt / nut. Is also possible.

Further, in each of the on-off valves 4, 4a, 4b described above, the valve shafts 5, 5a, 5b are integrated by screws or fittings. However, the present invention is not limited to this, and the valve shaft portion is manufactured in an integrated structure in advance. The valve shaft-equipped on / off valve 4d is also sufficiently considered. In the valve shaft-equipped on / off valve 4d in which the valve shaft 5d is integrated, as shown in the embodiment of FIG. 19, the front exhaust pipe 2e rear end and the supercharger 8a are used. In the connecting portion EE ′ formed between the front end portions of the turbine housing 19 in FIG. 1, bearing portions 6i and 6j for the valve shaft 5d integrated with the on-off valve 4d are provided, and the bearing portions 6i and 6j are provided with valve shafts. After disposing the on-off valve 4d, the rear end of the exhaust pipe 2e on the front side and the front end of the turbine housing 19 are integrated together with screws, nuts, a fixing band, etc., and further connected to the driving force source of the on-off valve controller. Fitting or screwing the lid 21 with the bearing portion 20 of the rod shaft 16a To prevent leakage of exhaust gas Te.
A convex portion or a concave portion is provided on one side of the valve shaft 5d integrated with the on-off valve 4d, and a concave portion or a convex portion that is loosely fitted to the convex portion or concave portion provided on the one side of the valve shaft 5d is provided at the tip of the rod shaft 16a. The part was provided and both were connected.

Next, the operation of the supercharging pressure control mechanism will be described.
In FIG. 1, the on-off valve control device 14 in the supercharging pressure control mechanism collects various information signals such as a cooling water signal, an intake air amount signal, etc., including a rotation speed signal and a supercharging pressure signal of the driving engine 1, When it is determined from the collected information signals that the prime mover engine 1 is rotating within a preset rotation range, the exhaust pipe on the front side is repeatedly closed and opened in the exhaust pipe 2 on the front side. 2 is continuously rotated or reciprocated at a constant angle by the driving force source of the on-off valve controller 14.

  When the front side exhaust pipe 2 is closed by the on-off valve 4, the front side exhaust pipe 2 is closed, and the exhaust gas continuously flowing into the upstream part of the on-off valve 4 in the exhaust pipe 2 is stopped and exhausted. The pressure in the pipe 2 increases.

  When the on-off valve 4 is opened, an exhaust gas flow that continues to be added to the exhaust gas that remains in the upstream portion of the on-off valve 4 in the exhaust pipe 2 and that continues to be exhausted from the combustion chamber is increased. By being quickly supplied to the outer peripheral side of the inner surface 9 of the turbine housing and flowing into the turbine blade 10 side, the turbine blade 10 quickly started rotating, and at the same time, placed and fixed to the other end of the same rotating shaft 13 as the turbine blade 10. Since the rotation of the impeller 12 on the compressor side 11 quickly rises, the response can be improved, and the impeller 12 pressurizes the air sucked by the high centrifugal force obtained by the high rotation and pressurizes the intake chamber 17 through the combustion chamber of the prime mover engine 1. Supercharge to.

  Even when the on-off valve 4 is closed again and the exhaust pipe 2 is closed, the high-pressure exhaust gas is supplied to the turbine blade 10 on the turbine side 7 when the exhaust pipe 2 is opened. 10, the rotary shaft 13 and the impeller 12 are continuously maintained in rotation without instantaneously decreasing the rotation due to their respective inertial forces, and the impeller 12 on the compressor side 11 can continue to maintain the supercharged state.

Further, while the exhaust pipe 2 is closed, the exhaust gas flow flowing in the exhaust pipe 3 downstream of the on-off valve 4 is continuously reduced and the pressure in the exhaust pipe 3 decreases due to the influence of inertial force. Therefore, the pressure difference from the upstream portion of the on-off valve 4 where the flow-in pressure increases is increased.
When the on-off valve 4 is opened again and the inside of the exhaust pipe 2 is opened, the high-pressure exhaust gas flows into the turbine blade 10 on the downstream side of the on-off valve 4 where the pressure has decreased, and the turbine blade 10 increases its rotation and is coaxial. The impeller 11 that rotates is also pressurized with high centrifugal force obtained by high rotation and continues to be supercharged into the combustion chamber of the prime mover engine 1.

Then, by supplying the fuel in an amount corresponding to the amount of air supercharged in the combustion chamber, the explosion pressure in the combustion chamber is increased, and the torque is improved by pushing down the piston with force, and further exhausted from the combustion chamber. Since the exhaust gas is also discharged in a high pressure state, when the on-off valve 4 is opened again, it flows into the turbine blade 10 side vigorously, increasing the rotation of the turbine blade 10 and at the same time further increasing the rotation of the impeller 11. The air sucked by the centrifugal force is pressurized and continuously supercharged into the combustion chamber of the prime mover 1. .
Thereafter, the same operation is repeatedly performed during the subsequent rotation, and as a result, the torque output in the low-speed rotation region and the response in the low-speed rotation region in the prime mover 1 can be improved.

In addition, since the supercharging pressure control mechanism 14 is provided, the impeller 12 disposed and fixed at the other end of the same rotating shaft 13 as the turbine blade 10 can be quickly started up. 10 and the outer diameter dimension of the impeller 12 on the compressor side 11 can be set to be large, and the turbine blade 10 and the impeller 12 that are set large have a high torque by the above-described supercharging pressure control mechanism 14 in the low speed rotation range. In addition, in the middle and high speed rotation regions, the turbine blade 10 having a large diameter flows smoothly up to the high rotation region because the exhaust gas flows without clogging, and at the same time, the other end portion of the same rotating shaft 13. Since the impeller 12 placed and fixed in the shaft also smoothly rotates up to a high rotation range, a high supercharging pressure can be supplied into the combustion chamber. That.
As described above, by providing an on / off valve in the exhaust pipe between the prime mover and the supercharger, and having a supercharging pressure control mechanism that is connected to the on / off valve and configured to control the on / off valve control device, Since the boost pressure can be increased in a wide range of rotations from low speed to medium and high speeds, high torque and high output can be secured in a wide range of rotations, and response can be improved. It is possible to provide a consideration engine.

    In each of the above-described embodiments, the case where a motor, a solenoid, or the like is employed as a driving force source when the on-off valve control device 14 opens / closes each opening / closing valve has been described. FIG. 21 showing the FF ′ cross section in FIGS. 20 and 20 is an on-off valve according to claim 1, wherein the pressure of the exhaust gas continuously discharged from the driving engine is used as a driving force source when the on-off valve is opened and closed. It is an Example of a control apparatus.

  As shown in FIG. 20, an N-pole magnet and an S-pole magnet are arranged and fixed at a position facing the rotation shaft 5e of the on-off valve 4e protruding outside the exhaust pipe 2f on the front side with the rotation shaft center therebetween. On the same circular raceway surface drawn by the N-pole magnet and the S-pole magnet of the magnet support portion 22 that rotate together when the on-off valve 4e rotates, and on a plane that maintains a certain distance The electromagnet support 25 to which the electromagnet 23 was fixed was attached to the base side 26 in a rotatable state via a return spring 27 so that both ends 24a and 24b of the electromagnet 23 face each other.

The position of the electromagnet support 25 when the prime mover is stopped is such that one of the on-off valves 4e is connected to the turbine housing as shown in FIG. 21 so that the exhaust gas flow can be supplied from the outer peripheral side of the inner surface of the turbine housing after the prime mover is started. It opens and stops in the same direction as the outer peripheral side of the inner surface, and is set at a position that rotates in the same direction as the arrow direction in which the exhaust gas flows, and the return spring 27 is in a non-elastic state between the electromagnet support 25 and the base side 26. The electromagnet support portion 25 is stopped at a fixed position on the base side 26 by using the elastic force of the return spring 27 as a resistance force.
Further, the opening / closing valve 4e has a magnetic force of the N-pole magnet and the S-pole magnet of the magnet support portion 22 disposed and stopped at positions opposed to both ends 24a and 24b of the electromagnet 23 in the electromagnet support portion 25 that stops at a fixed position. By continuing to attract both ends 24a and 24b of the electromagnet 23, the home position is maintained.
In addition, the electromagnet support portion 25 attached to the base side 26 in a rotatable state starts to rotate in the fully open direction in conjunction with the accelerator system when the driving engine reaches a certain rotation range, and passes through the exhaust pipe 2f. The angle of attack of the on-off valve 4e with respect to the flowing exhaust gas flow is varied.

Next, the operation will be described.
When the ignition engine is switched from the ignition-off state to the ignition-on state in order to start the prime mover, current supply to the electromagnet 23 is started at the same time, both ends 24a and 24b of the electromagnet are magnetized, and the on-off valve 4e is set. Continue to stop in position.
However, it is not necessary to supply current to the electromagnet 23 as long as the stop valve 4e can be continuously stopped at the set position by the magnetic force of the N pole magnet and the S pole magnet respectively arranged and fixed on the magnet support portion 22. .
Then, the current supply to the electromagnet 23 is stopped after the starting engine is started by a starter or the like, and the on-off valve 4e is rotated in the same direction as the clockwise direction in FIG. 21 by the pressure of the exhaust gas. At this time, a method of supplying a current to the electromagnet 23 may be considered in order to optimize the rotation speed of the on-off valve 4e.
The rotating on-off valve 4e repeatedly closes and opens the inside of the exhaust pipe 2f on the front side, and can obtain the same effect as the above-described embodiment.

  Next, when the rotational speed of the driving engine passes the upper limit of the set rotational range and reaches the medium speed rotational range, the current is again supplied to the electromagnet 23 to magnetize the electromagnet both ends 24a and 24b and arrange them on the magnet support 22 The fixed N-pole magnet and S-pole magnet are attracted, the rotating magnet support 22 and the on-off valve 4e are stopped at fixed positions, and high-pressure exhaust gas is supplied to the outer peripheral side of the inner surface of the turbine housing. In the ratio, the distance R between the center of the nozzle area at the turbine inlet and the center of the turbine blade is increased, and the exhaust gas flow is put on the free vortex to increase the speed and is supplied to the turbine blade.

Further, when the rotational speed of the prime mover engine becomes higher than the medium speed, the electromagnet support 25 linked to the accelerator system is counteracted by the elasticity of the return spring 27 so that the exhaust gas flow smoothly flows to the turbine blade. The interlocking on-off valve 4e is rotated to the fully open position in the same direction as the exhaust gas flow.
At this time, the current is continuously supplied to the electromagnet 23, and both are generated by the magnetic forces of the both end portions 24 a and 24 b of the electromagnet 23 fixed to the electromagnet support portion 25 and the magnetic forces of the N-pole magnet and the S-pole magnet arranged and fixed on the magnet support portion 22. Integrate and rotate in the same direction.

  Also, when the accelerator is returned to lower the rotational speed of the prime mover and the medium / high speed rotation is changed to the middle speed rotation range again, the electromagnet support portion 25 is returned to a fixed position by the elasticity of the return spring 27, and the magnetic force The magnet support part 22 integrated and interlocked is also returned, and the on-off valve 4e stops at a fixed position.

Further, when the rotational speed of the prime mover engine enters the set rotation range, the current supply to the electromagnet 23 is stopped, and the on-off valve 4e is rotated in the same direction as the clockwise direction in FIG.
The rotating on-off valve 4e is repeatedly closed and opened, and the same effect as the above-described embodiment can be obtained.

When an ignition-off signal is received when the driving engine is stopped, the rotating on-off valve 4e is stopped at a fixed position, so that a current is supplied to the electromagnet 23 from a delay circuit that can supply current to the electromagnet 23 for a certain period of time. 22 is stopped at a fixed position, and the on-off valve 4e interlocked with the magnet support portion 22 is stopped at a fixed position.
After the prime mover is stopped, the electromagnet ends 24a and 24b of the electromagnet support 25 that stops at a fixed position continue to be attracted by the magnetic force of the N-pole magnet and the S-pole magnet arranged and fixed on the magnet support 22, and the on-off valve 4e The engine is stopped at a fixed position and kept in this state to prepare for restarting the engine.
As described above, the magnet support portion in which the N-pole magnet and the S-pole magnet are respectively arranged and fixed is fixed to the rotation shaft of the on-off valve, and on the circular raceway surface drawn by the N-pole magnet and the S-pole magnet when the on-off valve rotates. An electromagnet support portion fixed to the electromagnet so that both ends of the electromagnet face each other on a plane maintaining a certain distance is attached to the base side in a rotatable state, and a return spring is provided between the electromagnet support portion and the base side. Can boost the boost pressure in a wide range of rotation from low to mid- and high-speed ranges, ensuring high torque and high output over a wide range of rotations, and improving response to fuel economy and environment It is possible to provide an engine that considers

  Furthermore, in the supercharging pressure control mechanism of a prime mover with a supercharger according to the present invention, it can be adopted not only in a reciprocating type such as a gasoline type or a diesel type, but also in a rotary type such as a bankel type, Adoption as a fuel pump for rocket-type engines such as liquid oxygen / liquid hydrogen is also conceivable.

  Incidentally, the supercharging pressure control mechanism of the prime mover-equipped engine according to the present invention can be appropriately changed without departing from the gist of the present invention, and the present invention extends to the modified one. It is natural.

  BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory diagram showing a configuration of a first embodiment of a supercharging pressure control mechanism in a supercharged prime mover engine according to the first aspect of the present invention;   Structure explanatory drawing which looked at the AA 'cross section part in FIG. 1 which shows the form of a 1st Example from the supercharger side.   Structure explanatory drawing which shows the form of the other Example which set the bearing part of the valve shaft in an on-off valve on the side part extension of the front side exhaust pipe, or on the side part extension vicinity.   Structure explanatory drawing of the BB 'cross section in FIG.   The structure explanatory drawing which shows the form of the other Example which integrates the arrangement position of a valve shaft in the one end part of an on-off valve, and sets both bearing parts to the side part of a front side exhaust pipe.   FIG. 6 is a configuration explanatory view of a CC ′ cross section in FIG. 5.   The external view which shows the Example whose planar shape in an on-off valve is circular.   The external view which shows the Example whose planar shape in an on-off valve is a vertically long ellipse shape.   The external view which shows the Example whose planar shape in an on-off valve is a horizontally long ellipse shape.   The external view which shows the Example whose planar shape in an on-off valve is square shape.   The external view which shows the Example whose planar shape in an on-off valve is a vertical rectangular shape.   The external view which shows the Example whose planar shape in an on-off valve is a horizontal rectangular shape.   The external view which shows the Example whose cross-sectional shape in an on-off valve is a linear shape.   The external view which shows the Example whose cross-sectional shape in an on-off valve is S-shaped.   The external view which shows the Example whose cross-sectional shape in an on-off valve is an elongate elliptical shape.   FIG. 2 is a configuration explanatory view of a DD ′ cross section in FIG. 1 and a cross-sectional configuration explanatory view showing closing and opening in the exhaust pipe on the front side when the on-off valve rotates.   Explanatory drawing explanatory drawing of the on-off valve and turbine side vicinity in FIG. 1 which shows the form of a 1st Example.   An intermediate exhaust pipe is provided between the front exhaust pipe and the supercharger, an open / close valve is disposed in the intermediate exhaust pipe, and an exhaust system having another configuration including the front exhaust pipe, the intermediate exhaust pipe, and the supercharger The structure explanatory view showing the example.   Structure explanatory drawing which shows the Example of the exhaust system of the other structure which has arrange | positioned the on-off valve in the connection part between the exhaust pipe of the front side, and a supercharger.   FIG. 3 is a configuration explanatory view showing a first embodiment according to the invention of claim 2 in which the pressure of exhaust gas is used as a driving force source when the on-off valve is opened and closed.   FIG. 21 is an explanatory diagram of the configuration when the direction of the arrow is viewed from the FF ′ cross section in FIG. 20.

Explanation of symbols

1 prime mover engine 2, 2a, 2b, 2c, 2d, 2e, 2f front exhaust pipe 3 rear exhaust pipes 4, 4a, 4b, 4c, 4d, 4e on-off valves 5, 5a, 5b, 5c, 5d, 5e Valve shaft 6a, 6b, 6c, 6d, 6e, 6f, 6g, 6h, 6i, 6j Bearing portion 7, 7a Turbine side 8, 8a Turbocharger 9, 9a, 9b, 9c Turbine side housing inner surface 10, 10a, 10b Turbine blade 11 Compressor side 12 Compressor side impeller 13 Supercharger rotating shaft 14 On-off valve control device 15 Protective vanes 16 and 16a Rod shaft 17 Intake pipe 18 Fixed band 19 Turbine side housing 20 Rod shaft bearing portion 21 Lid 22 Magnet support portion 23 Electromagnets 24a, 24b Both end portions 25 of electromagnet Electromagnet support portion 26 Base side 27 Return spring

Claims (2)

  In a prime mover engine provided with a supercharger in the middle of an exhaust pipe, an open / close valve is provided in the exhaust pipe between the prime mover engine and the supercharger, and the open / close valve control device controls the open / close operation of the open / close valve. The supercharging pressure control mechanism of a prime mover with a supercharger.   The magnet support part which fixes the N pole magnet and the S pole magnet which are respectively arranged and fixed to a position opposed to the on / off valve rotation axis outside the exhaust pipe with the rotation axis center therebetween, and rotates together with the on / off valve rotation. The electromagnet support, to which the electromagnet is fixed, is attached to the base side in a rotatable state so that both ends of the electromagnet face each other on a circular raceway surface drawn by the N-pole magnet and the S-pole magnet. The on-off valve control device according to claim 1, wherein a return spring is provided between the electromagnet support portion and the base side to control the on-off operation of the on-off valve.

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