FI123325B - Reciprocating internal combustion engine supercharging system and method for operating a reciprocating internal combustion engine - Google Patents

Description

CHARGING SYSTEM AND METHOD FOR PISTON IGNITION ENGINES

FOR OPERATING A PISTON ENGINE

TECHNICAL FIELD The present invention relates to a supercharging system for a piston combustion engine comprising a turbocharger having a compressor portion and a turbine portion mechanically connected to each other, and a gas flow control system for controlling the between the compression part, the turbine part and the engine.

The present invention also relates to a method of operating a piston combustion engine wherein the combustion air is pressurized by a turbocharger unit turbine portion and the exhaust gas is directed from the engine to the turbine unit turbine portion and the exhaust gas flow is controlled by at least one fluid flow.

BACKGROUND OF THE INVENTION An internal combustion engine, in particular a piston internal combustion engine, comprises a plurality of fluid circuits having specific control means for controlling fluid flows within the engine circuits. For example, the engine cooling system is typically controlled to maintain the temperature of the cvi 25 engine and its components within the required range. There are other fluid flows that involve at least some type of flow rate control, such as g fuel injection, charge air / exhaust flow, to name but a few.

In general, the control of such fluid flows is accomplished by controlling the flow rate o x at least to some extent. In principle, all fluid flows 30 of a piston internal combustion engine have an effect on its operation, with some fluid flows requiring very precise g control due to their strong influence on operation. The operational requirements of the internal combustion engines become more stringent and thus the accuracy and reliability of the control systems.

In addition to the fuel system, the importance of which has long been recognized, this 2 is associated with virtually all piston combustion engine fluid flow systems that affect the overall engine performance.

One extremely important fluid flow 5 in connection with a piston combustion engine is a charge air to exhaust gas flow system. For efficient piston combustion engines, it is almost normal to use superchargers, especially turbochargers, with the engines. To operate the engine properly and efficiently over a wide load range, devices for controlling the gas flow are required, at least to some extent. Therefore, the turbocharger is often equipped with a so-called wastegate. The waste port is a bypass channel for the turbine section of the 10 turbocharger, through which an adjustable amount of exhaust gas can be conducted without working on the turbine section. The waste port usually has a mechanical valve whose opening / closing depends on the charge air pressure or the motor load. The valve operates in a very demanding environment, which is influenced by temperatures of several hundred degrees Celsius of exhaust gases flowing at high flow rates. Even in load change phases, turbocharger control has a significant impact on engine performance.

It is an object of the invention to provide a fluid flow arrangement for a piston combustion engine in which the control performance is significantly improved compared to prior art solutions.

It is a further specific object of one embodiment of the invention to provide a supercharging system for a piston internal combustion engine in which the control performance is significantly improved compared to prior art solutions.

cvj 25 δ c \ j g Description of the Invention i

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The objects of the invention are substantially achieved by a supercharging system

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30 for reciprocating internal combustion engines comprising a turbocharger unit having a mechanically g-connected compressor part and a turbine part and a turbocharger unit

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A gas flow system connecting the compressor section and the turbine section to the engine, the gas flow system comprising at least one fluid flow control device arranged to control the gas flow between the compression section, the turbine section and the engine 3. The invention is characterized in that the at least one fluid flow control device comprises at least two parallel valve units having two operating positions.

The fluid flow control device 5 according to another embodiment of the invention comprises more than two parallel valve units.

According to a further embodiment of the invention, the fluid flow control device comprises parallel valve units having different flow characteristics.

According to yet another embodiment of the invention, the at least one valve unit has a removable / replaceable throttle element that affects the flow characteristics of the valve unit.

According to another embodiment of the invention, all valve units 15 have a removably mounted throttle element which affects the flow characteristics of the valve unit.

According to another embodiment of the invention, the valve units are identical and the throttling elements differ from each other.

20

According to another embodiment of the invention, the throttling element comprises a removable flange.

According to another embodiment of the invention, the throttle element cvi 25 comprises a pin element which is removably arranged on the valve assembly.

According to another embodiment of the invention, the throttling element i g comprises a stopper to limit the range of motion of the valve member of the valve unit.

X

According to another embodiment of the invention, the valve unit is an on / off valve, in accordance with another embodiment of the invention, the valve unit is a flow divider having two operating positions.

35 4

According to another embodiment of the invention, the at least one fluid flow control device is arranged in the exhaust duct and bypass duct to regulate the exhaust gas bypassing the turbine section.

According to another embodiment of the invention, the at least one fluid flow control device is arranged in the intake duct and the second bypass duct to control the amount of gas passed by the engine.

The objects of the invention are substantially achieved by a method of operating a piston combustion engine 10 wherein the combustion air is compressed by compressing air with a turbocharger unit turbine portion, the exhaust gas is directed from the engine to the turbine unit turbine portion and the exhaust gas flow is controlled. The invention is characterized in that the exhaust gas 15 is effected by adjusting the exhaust gas flow to optionally flow through one or more parallel valve units arranged in at least one fluid flow control device.

According to another embodiment of the invention, the pressure upstream of the compressor section is measured and the operating position of each one or more parallel valve units is determined and modified as necessary.

According to another embodiment of the invention, one or more of the plurality of parallel valve units have only two operating positions between which the cvi 25 state thereof is selected whenever steps are taken to monitor upstream pressure of the compressor section and each one or more plurality of plurality of parallel valve units. the operating position is determined and i changed if necessary.

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According to another embodiment of the invention, the exhaust conduction g is controlled by arranging a portion of the combustion air to bypass the engine, in accordance with another embodiment of the invention, the exhaust conduit is adjusted by arranging a portion of the exhaust gas to bypass the turbine portion.

35 5

Brief Description of the Drawings

The invention will now be described with reference to the following exemplary schematic drawings, of which:

Figure 1 shows a fluid flow system in a piston internal combustion engine according to an embodiment of the invention,

Figure 2 shows a preferred embodiment of a fluid flow control device according to the invention,

Figure 3 shows an embodiment of a valve assembly according to the invention,

Fig. 4 shows an embodiment of another valve unit of a fluid flow control device according to the invention,

Fig. 5 shows an embodiment of another valve unit of the fluid flow control device according to the invention,

Figure 6 illustrates a fluid flow system in a piston internal combustion engine according to another embodiment of the invention,

Figure 7 shows another embodiment of the valve assembly of the fluid flow control device of the invention, and Figure 8 shows a fluid flow system of a piston combustion engine according to yet another embodiment of the invention.

DETAILED DESCRIPTION OF THE DRAWINGS Fig. 1 is a schematic representation of a fluid flow system 10 of a piston combustion engine 100 according to an embodiment of the present invention.

The piston combustion engine 100 comprises a turbocharger unit 101 having a compressor portion x102 and a turbine portion 103. In this embodiment, the fluid flow system is a gas exchange system with the engine 30100.

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The gas exchange system includes a main fluid channel, which in this embodiment comprises an exhaust duct 12. The exhaust duct 12 is connected at its first end to the exhaust manifold and further to the engine cylinders 35 16. In the cylinders, exhaust pressure and temperature are increased cyclically by 6 fuel cylinders. The exhaust gas duct is connected at one end to the inlet of the turbine section 103 where the exhaust gas energy is partially used to drive the compressor section 102. The compressor portion 102 is connected to the engine intake manifold via intake duct 11. The turbocharger unit 101 may be of any one known in itself. The gas exchange system or turbocharger unit 101 has a bypass duct 12.2 which connects the engine exhaust duct 12 directly to the exhaust side of the turbocharger unit, particularly its turbine section 103.

The exhaust duct 12 has a fluid flow control device 22 arranged upstream of the turbine portion. The flow control device 22 controls the flow of exhaust gas to the turbine portion 103 and / or the bypass passage of the turbine portion 12.2. Thus, the regulator is and functions as a waste port for the turbocharger unit 101. The flow control device 22, i.e. the wastegate, comprises a plurality of parallel valve units 22.1, ... 22.N. The valve units are connected to the exhaust duct 12 at their inlet sides. Each of the 15 valve units 22.1, ... 22.N has two operating positions to which the valve units can be connected. In the first valve unit operating position it is arranged to connect the engine exhaust duct to the inlet side of the turbine part 103 and in the second valve unit operating position it is arranged to connect the engine to the outlet side of the turbine part 103. Each valve assembly is independently adjustable / adjustable to one of its 20 operating positions. 1

Thus, the combustion air is compressed by compressing the intake air in the compressor section 102.

The compressor part is driven by the turbine part 103 of the turbocharger unit 101, which in turn is driven by the exhaust developed in the engine. The exhaust gas is led through the exhaust gas duct 12 from the engine to the turbine section 103 of the turbocharger unit.

The exhaust passage is controlled 30 by at least one fluid flow control device g 22 such that the exhaust passage is optionally adjusted to flow through at least one of the plurality of x parallel valve units 22.1, ... 22.N arranged in one of the fluid flow control devices.

30 g Each valve unit has different flow characteristics. In practice, this m preferably means that the flow areas of the valve units differ. A control system 30 is also provided in connection with the actuator 22.

The control system 30 is arranged to set the operating position of each valve unit 22.1, ... 22.N 35 to one of the two operating positions between which 7 valve units can be connected. Preferably, the control system is provided with a sensor system 32 that transmits control information about engine operation. Based on the control information, the control system 30 determines the status of each valve unit and sets its operating positions accordingly. Preferably, the control system 5 is also provided with a sensor system 32 which directly or indirectly transmits information about at least supercharging pressure.

During engine operation, the control system receives information related to engine operation and / or performance. Ko. based on the information stored in the data and / or other control system 30 10, it places each valve unit 22.1, ... 22.N in one of its two operating positions. In this way and depending on the condition of the motor, the control system 30 places the control device 22 in various combinations of operating positions of the valve units. In this way, the operation of the turbocharger can be very effectively controlled.

15

The valve units have two operating positions. In the first operating position, the valve units switch the exhaust gas flow to the turbine section 103 and in the second operating position, the valve units switch the exhaust gas flow to bypass the turbine section through bypass channel 12.2. The regulator acts as a waste port for the 101 turbocharger units.

The valve units, i.e., the number of valve units and the flow characteristics of the valve units in the motor, are preferably selected such that substantially identical total flow characteristics of the actuator 22 can be achieved by at least two different combinations of operating positions of the valve units. In this way c3, the actuator and motor can be operated at least temporarily or until the next service outage ig if at least one valve unit is defective.

The present invention makes it possible to effectively control the operation of the turbocharger 30 by setting the amount of exhaust gas to be bypassed by the turbine section 103 by selecting the respective operating positions of the parallel valve units. The wastegate flow control device 22 comprises at least two but preferably at least four parallel valve units.

8

According to a preferred embodiment of the invention, each valve unit has a bottom part 25 and a throttle element 24. Preferably, the throttle element 24 is arranged in the valve unit to strangle the fluid flow. The throttle element 24 is preferably removably mounted on the base member 5 25. The throttle element is a member that strangles the flow characteristics of the valve assembly. More particularly, the throttle element 24 influences the flow resistance of the valve unit, preferably by forming a locally reduced flow area. This is shown in Figure 1 as a ring. Further, it is preferable that the bottom portions 25 of the valve units 22.1, 22.2, ... 22.N are substantially identical, and in particular with respect to the connecting elements 10 by which the throttle element 24 engages the valve unit. The number of valve units may vary, but preferably there are at least four. The throttle element includes means for selecting the flow characteristics of the valve unit when assembled, which means that the throttle elements are advantageously different in different valve units. In this way, the valve units are modulated 15, which allows their flow characteristics to be altered by simply changing the only throttle element 24 of the valve unit.

Throttle elements 24 are preferably selected such that the first valve unit has a relatively effective flow area of 1, the second valve unit has a corresponding flow area of 1/2, a third valve unit of 1/4, etc., i.e. their flow areas are arranged such that the area of the "next" valve unit is half the flow area of the previous unit. If the fluid flow control device comprises four on / off valve units, the ratios of operating station combinations to the flow rate are shown in the following table, which clearly shows the accuracy achieved by four cvi 25 valve units.

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Valve unit 1 Valve unit 2 Valve unit 3 Valve unit 4 Total flow "5 5 Ö Ö 0,000 Ί) Ö Ö i 0,125 Ί) Ö i Ö 0,250“ Ö Ö ii 0,375 “Ö i Ö Ö 0,500 Ί) i Ö i 0,625 Ί) ii Ö Ö75Ö Ί) iii 0,875 Ί Ö Ö 1,000 Ί 1,000 Ö Ö 1,125 Ί Ö i Ö 1,250 Ί Ö ii 1,375 Ί i Ö 1,500 Ί i Ö i 1,625 Ί ii Ö 1750 Ί iii

In this embodiment, the valve unit 1 produces a relative flow rate 5 1, the valve unit 2 produces a relative flow rate 0.5, and so on. It can be seen that four valve units can provide 16 different flow rates. Accordingly, five and six valve units can achieve 32 and 64 different flow rates, respectively.

Since each valve unit can be independently coupled between two operating positions, it is possible to set virtually any fluid flow situation required for O) 9 by arranging and combining the operating positions of the individual valve units. Depending on the valve units of the type, the operating stations may be in the "on" or "off" position or positions that control the flow in either of two possible directions. In the case of Fig. 1 m ^, the valve units have two selectable positions that control the flow of g in either of two possible directions.

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Figure 2 shows a preferred embodiment of the fluid flow control device 22 according to the invention. The fluid flow control device 22 comprises a body portion 25 where the second portion of the fluid flow control device is disposed. The body includes a fluid inlet duct 4 to which the main fluid duct is to be connected. The body portion 25 also includes a plurality of valve spaces 6. The valve spaces 6 are cylindrical in the embodiment of Figure 6. The first end 8 of each space is connected to the fluid inlet duct 5 4. The valve spaces are substantially identical. The valve member has a first outlet 210 and a second outlet 212 in the cylinder portion of the valve space. The first outlet 210 of each valve space is connected to a first first outlet duct 214 for each of the first ports. Similarly, a second outlet duct 10 216 for each valve space.

A valve member 218 is provided in each valve space. The valve member and valve space in this embodiment form a valve assembly. The valve member is movably disposed in the valve space 6 such that the position of the valve member determines the operating position of the valve assembly 15. Valve member 18 'is shown at a position where fluid inlet conduit 4 is in fluid communication with first outlet conduit 214. Reference numeral 218 illustrates valve means in their second position wherein fluid inlet conduit 4 is in fluid communication with second outlet conduit 216.

More specifically, the valve member 218 shown in Figure 5 is a cylindrical substantially hollow sleeve covering a portion of the valve space 6. When the sleeve position is changed, it either covers the first outlet 210 or the second outlet 212, allowing fluid to be guided inside the valve member 218. The valve member and the valve housing each have a cylindrical cross section and a common center line cm 25 18 '. In this case, the movement of the valve member occurs in the direction of the center line 18 '.

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g The valve member is arranged such that only one of the first outlet g 210 and the second outlet 212 may be in fluid communication with the fluid inlet duct x 4.

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In the embodiment shown in Fig. 2, the inner surface of the valve chamber 6 is covered

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sleeve 220, within which valve member 218 is disposed. The inner surface of the sleeve 220 and the counter surface of the valve member 218 form a cylindrical seal by which the fluid flow is directed in the direction determined by the position of the valve member. The sleeve 35 is provided with 11 openings at the first outlet 210 and the second outlet 212. The sleeve 220 is removably and interchangeably assembled so that after service life and / or damage or wear it can be replaced in a non-destructive manner.

At the first end of the valve chamber 8 is a throttling element 24.

The valve spaces 22.1, 22.2, ... 22.N of the valve units are substantially identical, in particular with respect to the other parts, except for the throttle element 24. The throttle element is arranged immediately upstream of the sleeve 220 before the valve member. The throttle element 24 is preferably a perforated flange. Here, the hole may be located centrally in the flange. Each valve unit has a different hole diameter. In this way, the flange characteristics of the valve unit are affected by the flange. The valve units may be modulated to allow their flow characteristics to be altered simply by replacing only the flanged throttle element 24 of the valve unit.

According to one embodiment of the invention, at least two of the holes in the valve units have the same diameter.

Each valve unit 22.1, 22.2, ... 22.N is provided with an actuator 225 arranged to move the valve member in the valve space. In the embodiment of Figure 5, the actuator is a double-acting actuator capable of actuating the valve member 218 in two directions to move the valve member between its two operating positions. The actuator may be a solenoid or hydraulically actuated device or a combination thereof, in which case the solenoid system adjusts the hydraulic pressure acting on the actuator 225. Each actuator 225 communicates with the actuator (not shown).

σ> cp g Figure 3 shows an embodiment of valve assembly 22.1 in which fluid x passes from outside of valve member 318 along a recess provided in valve member

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319. The fluid flow control device has a plurality of parallel-mounted valve units 22.1.

The valve chamber 306 is provided with a cylindrical portion with a first outlet opening m ^ 310 and a second outlet opening 312 respectively connected to the first outlet duct 314 and the second outlet duct 316. In this embodiment, the actuator 327 is a single-acting actuator capable of acting on the valve member 35 To move the valve member between its two operating positions 12, a spring element 327 'is provided at an opposite end to the actuator 327 of the valve member 318. The actuator 327 is of the hydraulic / pneumatic type and is capable of moving the valve member 318 in the direction opposite the spring, and after releasing the working pressure, the spring returns the valve member 5 to its original position.

The valve member 22.1 of Figure 3 also has a throttle element 24. The throttle element is provided immediately upstream of the valve member. The throttle element 24 in this embodiment is a sleeve having a central opening.

10 In this way, the sleeve influences the flow characteristics of the valve assembly. The valve units can be modulated, which allows their flow characteristics to be changed by simply changing the valve unit sleeve.

The throttling element can be implemented in many ways. As shown in Figure 4, instead of the flange or sleeve, the throttle element could be a replaceable pin 24 which extends into the fluid flow passage of the valve unit. The valve assembly of Figure 4 corresponds to the details of the throttle element except for the valve assembly of Figure 3. The effect of the throttling element may be altered by changing the pin of a different size as shown by the dotted line 24 '.

20

Figure 5 illustrates yet another embodiment of the invention which substantially corresponds to the embodiment of Figure 3. Fig. 5 shows a throttle element 24 consisting of a stop 24 "against which the valve member 318 is pressed in a position where the fluid is directed to the first outlet 610.

Due to stop 24, the movement of the valve member is limited to limit the flow of £ 3 to the first outlet 310. The valve assembly may also include a g stop at one end to limit the movement of the valve member to its second operating position i g (not shown). Such a stop can be used in various types of x valve assembly.

Fig. 6 illustrates another embodiment of the invention, wherein the piston combustion engine 100 comprises a turbocharger unit 101 having a compressor section o c 102 and a turbine section 103. In this embodiment, the fluid flow system is a gas exchange system with the engine 100.

35 13

The gas exchange system includes a main fluid channel, which in this embodiment comprises an exhaust duct 12. The exhaust gas duct 12 is connected at its first end to the exhaust manifold and further to the engine cylinders 16. In the cylinders, the exhaust pressure and temperature is increased by cyclically burning 5 fuel in the engine cylinders. The exhaust gas duct is connected at one end to the inlet of the turbine section 103 where the exhaust gas energy is partially used to drive the compressor section 102. The turbocharger unit 101 may be of a type known per se. The gas exchange system or turbocharger unit 101 has a bypass duct 12.2 which connects the engine exhaust duct 12 directly to the outlet side of the turbocharger unit 10, particularly its turbine section 103.

The exhaust conduit 12 has a fluid flow control device 22 'arranged upstream of the turbine portion in the bypass conduit 12.2. Thus, the flow control device 22 'controls the flow of exhaust gas through bypass passage 12.2, i.e., allows a portion of the gas 15 from the engine to bypass the turbine portion and thus also regulates the exhaust gas flow to the turbine portion.

[0055] There is also a second bypass channel 613 which connects the compressor portion 102 of the pressure side directly to the engine exhaust gas passage 12. The second bypass passage 613 20 connection point is a fluid flow control device 22 " '. The fluid flow control device 22 is arranged to allow a portion of the charge air to flow into the turbine portion of the control system 30 to be adjusted. In other respects, the fluid flow control device and its operation corresponds to that shown in Fig. 1.

Figure 7 shows an advantageous embodiment of the fluid flow control device 22 of the invention. The fluid flow control device 22 comprises a body section 25, in which other parts of the fluid flow control device are arranged. The body has a g fluid inlet duct 4 to which the main fluid duct is to be connected. The body also has a fluid outlet duct 716.

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The body 25 also includes a plurality of valve members 18 which separate

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^ inlet and outlet ducts. A valve member o 318 is provided in each valve space. The valve member is movable such that the position of the valve member determines the operating position of the valve unit.

35 14

More specifically, the valve member 718 shown in Fig. 7 is a disk valve. When the reel position is changed, it either closes or opens the connection between the inlet and outlet ducts.

Fig. 7 schematically illustrates a further embodiment of the invention, wherein each valve member 22.1, 22.2, ... 22.N is provided with a manual locking system 719 which allows the valve member of each valve unit to be locked in either of their operating positions. The manual locking system 719 comprises locking means provided with each valve unit such that, for example, in the event of a malfunction, the valve unit can be locked. The locking devices are also arranged to permit manual change of the operating position. Although this is illustrated herein with reference to Figure 7, the manual locking system may, of course, be provided in other embodiments of the valve units of the invention.

15

The fluid flow control device 22 has a throttle element 24 associated with each valve member. The throttle element 24 is also arranged to act as a valve seat, mating with the control surface of the valve member. The valves are substantially identical, in particular with respect to the other parts, except for the throttle element 24. It is obvious that the throttle element may also be separate from the valve seat. The valve assemblies can be modulated, which allows their flow characteristics to be altered simply by changing only the throttle element 24 of the valve assembly.

Each valve member of the valve unit is provided with an actuator, here is a common actuator system 727 arranged to move each g valve member independently in the valve space.

Fig. 8 illustrates yet another embodiment of the invention in which

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The piston combustion engine 100 comprises a turbocharger unit 101 having a compressor portion g 102 and a turbine portion 103. In this embodiment, the fluid flow system is also

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a gas exchange system with engine 100.

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The gas exchange system includes a main fluid passage, which in this 35 embodiment comprises an exhaust passage 12. The exhaust passage 12 is at first 15 connected to the exhaust manifold and further to the engine cylinders 16. In the cylinders, exhaust pressure and temperature are increased by cyclically burning fuel in the engine cylinders. The exhaust duct is connected at one end to the inlet of the turbine section 103, where the exhaust energy is partially used to drive the compressor section 102. The turbocharger unit 101 may be of a type known per se. The gas exchange system or turbocharger unit 101 is provided with a recirculation duct 12.1 that links the engine exhaust duct 12 directly to the inlet side of the engine. The recirculation duct 12.1 has a fluid flow control device 22 '". Thus, the flow control device 22"' directs part of the exhaust gas 10 along the recirculation channel 12.1 to the intake side of the engine, i.e. allowing some of the engine exhaust gas to be recirculated back to the engine.

In other respects, the fluid flow control device and its operation are as shown in Figure 1.

15

While the invention has been described by way of example herein in the context of what are currently considered to be the most preferred embodiments, it is to be understood that the invention is not limited to the disclosed embodiments but is intended to cover various combinations or variations thereof. applications as defined in the appended claims. The details mentioned in any of the embodiments described above may be used in connection with another embodiment, provided that the combination is technically feasible.

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Claims (18)

A supercharging system for a reciprocating internal combustion engine (100) comprising a turbocharger unit (101) having a mechanically connected compressor portion (102) and a 5 turbine portion (103), and a gas flow system connecting the compressor portion (102) and turbine portion (103) to the engine; the gas flow system comprising at least one fluid flow control device arranged to control the gas flow between the compression part (102), the turbine part (103) and the engine (100), characterized in that the at least one fluid flow control device (22) comprises at least two parallel valve units (22.1-22). N), each with two operating positions. A reciprocating supercharging system according to claim 1, characterized in that the valve units (22.1 to 22.N) have different flow characteristics. 15 Compression system for reciprocating internal combustion engine according to claim 1 or 2, characterized in that the fluid flow control device (22) comprises more than two parallel valve units (22.1 to 22.N). Compression system for reciprocating internal combustion piston engine according to claim 1, characterized in that at least one of the valve units is provided with a replaceable throttle element (24) which affects the flow characteristics of the valve unit. Compression system for reciprocating internal combustion engine according to claim 4, cm 25, characterized in that all valve units are provided with a replaceable throttle element (24) which affects the flow characteristics of the valve unit. σ> cp Compression system for reciprocating internal combustion engine according to claim 4, characterized in that the valve units (22.1 to 22.N) are identical and the throttle elements 30 (24) differ from one another. LO CO LO ^ A fluid flow control device for a piston combustion engine o cm according to claim 4, characterized in that the throttling element (24) comprises a replaceable flange. Compression system for reciprocating internal combustion engine according to claim 4, characterized in that the throttling element (24) comprises a replaceable pin element arranged in the valve unit. A reciprocating supercharging system for a reciprocating internal combustion engine according to claim 4, characterized in that the throttle element (24) comprises a sliding stop (24 ') to limit the range of motion of the valve member (318) of the valve unit. A reciprocating supercharging system for a reciprocating internal combustion engine 10 according to claim 1, characterized in that the at least one fluid flow control device is arranged in the exhaust duct and bypass duct (12.2) to control the amount of exhaust gas passing the turbine part (103). A reciprocating supercharging system for a reciprocating internal combustion engine 15 according to claim 1, characterized in that at least one fluid flow control device is provided in the intake duct (11) and the second bypass duct (613) to control the amount of gas passing by the engine (100). A method of operating a reciprocating internal combustion engine (100) wherein the combustion air is compressed by compressing air with the compressor portion (102) of the turbocharger unit (101) and operating the turbine portion (103) on the turbocharger unit (101) at least one fluid flow regulator, characterized in that the exhaust gas flow is effected by directing (22) the exhaust gas flow cvi 25 through one or more parallel valve units (22.1 - 22.N) g optionally arranged in at least one fluid flow regulator (22, 22 ', 22 "). no A method for operating an internal combustion engine (100) according to claim 12, characterized in that the pressure g upstream of the compressor section is measured and the operating position of each one or more parallel valve units (22.1 - \ n ^ 22.N) is determined and changed, δ C \ J The method of operating an internal combustion engine (100) 35 according to claim 13, characterized in that each one or more of the plurality of parallel valve units (22.1 to 22.N) has only two operating positions between which a state is selected whenever the step of claim 13 is performed. A method for operating an internal combustion engine (100) according to claim 12, characterized in that the exhaust conduction is controlled (22) by providing a portion of the combustion air to bypass the engine. A method for operating an internal combustion engine (100) according to claim 12, characterized in that the exhaust conduction is controlled (22) 10 by providing a portion of the exhaust gas to bypass the turbine portion (103). CM δ CM σ> oimo X cc CL δ co m δ CM 20 1. Överladdningssystem för en förbränningskolvmotor (100) innefattande en turboladdarenhet (101) med en kompressordel (102) och en turbindel (103) 5 förenade med varandra, och ett gas strömningssystem som förenar turboladdarenhetens (101) compressor (102) och turbindel (103) med motorn, glow gasströmningssystem innefattar ätminstone en regleranordning för fluidströmning anordnad att reglera gasströmningen mellan kompressordelen (102), turbindelen (102) This is the case with 10 regleranordning (22) för fluidströmning innefattar ätminstone in parallel with the ventenheter (22.1 - 22.N), var och en av lively function functions. 2. Överladdningssystem för en förbränningskolvmotor enligt patentkravet 1, a rotary decnat av att ventilenheterna (22.1-22N), a rotating flange design. 3. The Överladdningssystem för en förbränningskolvmotor enligt patentkravet 1 eller 2, a rotary encoder av att regleranordningen (22) för fluidströmning innefattar flera un para ventenheter (22.1-22N). 20 4. The Överladdningssystem för en förbränningskolvmotor enligt patentkravet 1, a rotary tongue and anchoring device (24) som päverkar ventilenhetens flödesegenskaper. 1 Överladdningssystem för en förbränningskolvmotor enligt patentkravet 4, cvi 25 kännetecknat av att samtliga ventenheter and försedda med et utbytbart ° strypningselement (24) som päverkar ventilenhetens flödesegenskaper. i O) cp g 6. Överladdningssystem för en förbränningskolvmotor enligt patentkravet 4, i kännetecknat av att ventenheterna (22.1 - 22.N) och strypningselementen “30 (24) was available. LO CO LO ^ 7. Överladdningssystem för en förbränningskolvmotor enligt patentkravet 4, o c \ j kännetecknat av att strypningselementet (24) innefattar en utbytbar fläns. 21 8. The Överladdningssystem för en förbränningskolvmotor enligt patentkravet 4, the rotary knob av att strypningselementet (24) innefattar et utbytbart the puncturing element for ventilation and ventilation. 9. The Överladdningssystem för en förbränningskolvmotor enligt patent kravet 4, the rotation mechanism (24) innefattar en glidande stoppare (24 ') för att begränsa rörelsemänen av ventenhetens ventorgan (318). 10. Överladdningssystem för en förbränningskolvmotor enligt patentkravet 1,10, kännetecknat av att ätminstone en regleranordning för fluidströmning and anordnad i avgaskanalen och i en förbiledningskanal (12.2) för att reglera playden avgaser som passer. 11. Överladdningssystem för en förbränningskolvmotor enligt patentkravet 1, 15 kännetecknat av att ätminstone en regleranordning för fluidströmning i inloppskanalen (11) och i en andra förbiledningskanal (613) för att regler playden. 12. Förfarande för att driva en förbränningskolvmotor (100), dör förbränningsluften 20, ørladd genome att trycksätta luften i en compressor (102) av en turboladdarenhet (101), och kompressordelen drivs av turboladdarenhetens (101), turbindel (101) account turboladdarenhetens turbindel (103) och ledandet av avgasen regleras (22) med ätminstone en regleranordning för fluidströmning, kännetecknat av att ledandet av avgasen utförs genome att styra cm 25 (22) avgasflödet att flöda selen genen en eller flera -er ^ (22.1-22.N) som är anordnad / -ei etminstone en regleranordning för fluidströmning § (22, 22 ', 22 ”). imox 13. Förfarande för att driva en förbränningskolvmotor (100) enligt patentkravet 12, 30 rotatecknat av att trycket som räder uppströms om kompressordelen belt heater £ 2 och functions avget och en av nl flera parallell / -a ventenhet (22.1 - 22.N) fastställs och ändras, om behövligt. δ C \ J 14. Förfarande för att driva en förbränningskolvmotor (100) enligt patentkravet 13, 35 kännetecknat av att var och en av ndernen flera parallell / - ventenhet / -er 22 (22.1 - 22.N) har bara tvä funktionslägen, mellan livka dess go out express shade gang stare enligt patentkravet 13 utförs. Förfarande för att driva en förbränningskolvmotor (100) enligt patentkravet 12, 5 kännetecknat av att ledandet av avgasen regleras (22) genomic att anordna en del av förbränningsluften att passera motorn. 16. Förfarande för att driva en förbränningskolvmotor (100) enligt patentkravet 12, kännetecknat av att ledandet av avgens regleras (22) genomic att anordna en del 10 av avgens att passer turbindelen (103). C \ l o C \ J O) o lo o X cc CL LO CO LO O C \ l