JP5942464B2 - Turbocharger - Google Patents

Description

  The present invention relates to a supercharger, and in particular, a turbine housing that houses a turbine wheel that rotates when exhaust gas of an internal combustion engine is blown, and a gas passage that guides the exhaust gas to the turbine wheel housed in the turbine housing. The present invention relates to a supercharger including a nozzle plate to be formed.

  Conventionally, a turbocharger (supercharger) mounted on a direct injection gasoline engine, a diesel engine, or the like is known (see, for example, Patent Document 1).

  The turbocharger disclosed in Patent Document 1 includes a turbine housing that houses a turbine wheel, a compressor housing that houses a compressor wheel, and a center housing that connects the turbine housing and the compressor housing.

  A storage chamber is provided between the scroll passage of the turbine housing and the center housing, and a nozzle plate, a unison ring, a support ring, and the like are disposed in the storage chamber. The nozzle plate is provided with a plurality of nozzle vanes that form gas passages that guide exhaust gas of the internal combustion engine (engine) from the scroll passage to the turbine wheel. The unison ring functions as a part of a nozzle vane drive mechanism that supports a plurality of nozzle vanes provided on the nozzle plate so as to be tiltable (driveable). The support ring is arranged to support the nozzle plate and the unison ring.

  Further, the storage chamber is arranged by the support ring so as to be divided into a drive chamber (link chamber) in which the nozzle vane drive mechanism is arranged and a drainage chamber located below the drive chamber. A drain hole is provided at the bottom of the support ring, and when moisture is generated in the drive chamber where the nozzle vane drive mechanism is disposed, the moisture is passed through the drain hole of the support ring. It is comprised so that it may discharge | emit to the drainage chamber located below.

  A passage forming flange is formed between the storage chamber and the scroll passage so as to separate the storage chamber and the scroll passage, and a drain hole is formed at the lowermost portion of the passage formation flange. Thereby, the drive chamber communicates with the scroll passage through the drain hole of the support ring, the drain chamber, and the drain hole of the passage forming flange.

  For example, when the temperature of the exhaust gas is low, such as immediately after starting the engine, the exhaust gas of the engine may enter the storage chamber (drive chamber), and the moisture in the exhaust gas may be condensed and liquefied in the drive chamber. In this case, the condensed water liquefied in the drive chamber falls to the bottom of the drive chamber and is discharged to the scroll passage through the drain hole of the support ring, the drain chamber, and the drain hole of the passage forming flange. As a result, in a low temperature environment where the condensed water freezes, the condensed water that has dropped to the bottom of the driving chamber becomes difficult to freeze, so that the nozzle vane driving mechanism housed in the driving chamber is prevented from being damaged by freezing. .

JP 2009-074492 A

  A direct-injection gasoline engine equipped with a turbocharger is configured to inject fuel directly into a cylinder (combustion chamber). In a diesel engine, particulate matter (PM) discharged from the engine is discharged into the exhaust pipe. So that PM accumulated on the filter in the exhaust pipe is burned by adding fuel from an exhaust fuel addition valve installed upstream of the turbocharger and increasing the catalyst bed temperature. It is configured. For this reason, in the turbocharger disclosed in Patent Document 1, the condensed water liquefied in the drive chamber can be discharged to the scroll passage through the drain hole and the drain chamber, while circulating in the scroll passage. It is considered that exhaust gas and fuel (unburned fuel) may flow into the drive chamber through the drain hole and the drain chamber. In this case, there is a concern that the fuel that has flowed into the drive chamber is liquefied, so that the fuel is deposited as deposits in the drive chamber.

  In order to prevent the fuel from flowing into the drive chamber, a method of reducing the gap between the nozzle plate and the turbine housing can be considered. However, the thermal expansion of the nozzle plate and the turbine housing when the temperature inside the turbocharger is relatively high, and the thermal deformation due to the temperature difference between when the temperature inside the turbocharger is relatively high and when it is relatively low are considered. In some cases, a gap is considered necessary between the nozzle plate and the turbine housing.

  Furthermore, in order to prevent fuel from flowing into the drive chamber, when the gap between the nozzle plate and the turbine housing is completely sealed with a seal member or the like, the condensed water generated in the drive chamber is discharged from the drive chamber. There is an inconvenience that it accumulates in the drive chamber without being. For this reason, the condensed water freezes at a low temperature, the nozzle vane drive mechanism housed in the drive chamber is damaged by freezing, and the nozzle vanes provided on the nozzle plate are fixed. For this reason, it is considered that a gap is necessary between the nozzle plate and the turbine housing in order to discharge condensed water.

  From the above viewpoint, the turbocharger disclosed in Patent Document 1 improves the drainage of condensed water generated in the drive chamber (link chamber), and fuel is contained in the drive chamber (link chamber). It is considered difficult to suppress the inflow. For this reason, there exists a problem that it is difficult to make compatible the discharge property of condensed water, and suppression of fuel inflow.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to improve the drainage of condensed water generated in the link chamber and to prevent fuel from flowing into the link chamber. By suppressing, it is providing the supercharger which can make compatible the discharge | emission property of condensed water, and suppression of fuel inflow.

  As a means for solving the above-described problems, a supercharger according to the present invention is configured as follows.

That is, the turbocharger according to the present invention forms a turbine housing that houses a turbine wheel that rotates when exhaust gas of an internal combustion engine is blown, and a gas passage that guides the exhaust gas to the turbine wheel housed in the turbine housing. And a seal ring member disposed between the nozzle plate and the turbine housing. The seal ring member is a ring member having a joint, and the seal ring member. The joint is opened when the temperature of the exhaust gas is low, and closed when the temperature of the exhaust gas is high . Further, the joint of the seal ring member on the scroll passage side of the turbine housing is positioned on the downstream side of the exhaust gas flowing in the scroll passage with respect to the joint of the seal ring member on the side opposite to the scroll passage side of the turbine housing. It is arranged.

According to the turbocharger having such a configuration, when the exhaust gas temperature is low (when the temperature is relatively low), the seal ring member in the state where the joint is opened is when the exhaust gas temperature is high (when the temperature is relatively high). ), The joint is closed due to the difference in thermal expansion between the seal ring member and the turbine housing. As a result, at a low temperature when fuel (unburned fuel, unburned gas) is unlikely to flow into the link chamber, condensed water generated in the link chamber can be discharged, and fuel can flow into the link chamber. However, when the temperature is high and the joint of the seal ring member is closed, the inflow of fuel into the link chamber can be suppressed. As a result, the condensate drainage generated in the link chamber can be improved, and the fuel can be prevented from flowing into the link chamber. It can be compatible. Further, the fuel flowing into the link chamber and the condensed water generated in the link chamber can be sucked out to the scroll passage side by the ejector effect, and the fuel can be prevented from flowing into the link chamber. As a result, when the joint of the seal ring member is open, it is possible to improve the discharge performance of the fuel and condensate accumulated in the link chamber and to suppress the fuel from flowing into the link chamber. it can.

  As specific configurations of the present invention, the following plural ones are listed.

  In the supercharger according to the present invention, preferably, the abutment of the seal ring member is arranged in a region in a lower direction in a region between the nozzle plate and the turbine housing. With this configuration, the fuel flowing into the link chamber and the condensed water generated in the link chamber are likely to fall downward (gravity direction), so the fuel flowing into the link chamber and the condensed water generated in the link chamber Can be efficiently discharged.

  According to the turbocharger according to the present invention, the condensate drainage generated in the link chamber is improved, and the condensate drainage and the fuel inflow are suppressed by suppressing the fuel from flowing into the link chamber. Can be made compatible.

It is sectional drawing which shows schematic structure of the state (at the time of low temperature) in which the opening of the seal ring member of the variable capacity | capacitance type turbocharger by a reference example was opened. FIG. 2 is an enlarged view showing a state (at a low temperature) where a joint of a seal ring member of the variable capacity turbocharger shown in FIG. 1 is opened. It is a figure which shows the inner surface of the 1st nozzle plate of the variable nozzle unit in the state (at the time of low temperature) in which the opening of the seal ring member of the variable capacity | capacitance type turbocharger along the 200-200 line | wire of FIG. It is an enlarged view which shows the state (at the time of high temperature) with which the joint of the seal ring member of the variable capacity | capacitance type turbocharger by a reference example was closed. It is a figure which shows the inner surface of the 1st nozzle plate of a variable nozzle unit in the state (at the time of high temperature) in which the joint of the seal ring member of the variable capacity | capacitance type turbocharger shown in FIG. 4 was closed. It is a figure which shows the outer surface of the unison ring of the variable nozzle unit of FIG. 1, and has shown the state which enlarged the nozzle vane opening degree. It is a figure which shows the inner surface of the 1st nozzle plate of the variable nozzle unit of FIG. 1, and has shown the state which enlarged the nozzle vane opening degree. It is a figure which shows the outer surface of the unison ring of the variable nozzle unit of FIG. 1, and has shown the state which made the nozzle vane opening degree small. It is a figure which shows the inner surface of the 1st nozzle plate of the variable nozzle unit of FIG. 1, and has shown the state which made the nozzle vane opening degree small. It is a disassembled perspective view which shows a part of link mechanism of FIG. It is a perspective view which shows a part of link mechanism of FIG. It is a figure which shows the seal ring member of the variable capacity | capacitance type turbocharger by 1st Embodiment of this invention. It is a figure which shows the case where the shape of the joint of the seal ring member of the variable capacity | capacitance type turbocharger by 1st Embodiment of this invention is a step shape. It is a figure which shows the case where the shape of the joint of the seal ring member of the variable capacity | capacitance type | mold turbocharger by 2nd Embodiment of this invention is diagonal shape.

Hereinafter, reference examples will be described with reference to the drawings.

1 to 11 show reference examples . The illustrated variable displacement turbocharger 1 is attached to an internal combustion engine (engine) (not shown).

  As shown in FIG. 1, the variable displacement turbocharger 1 includes a turbine wheel 2, a compressor impeller 3, a bearing housing 4, a turbine housing 5, a compressor housing 6, a variable nozzle (VN) unit 7, and the like.

  The turbine wheel 2 is integrally formed at one end of the turbine shaft 2a in the axial direction. The compressor impeller 3 is integrally attached to the other axial end of the turbine shaft 2a. The turbine shaft 2 a is inserted so as to be rotatable through two radial bearings 8 a and 8 b disposed in the center hole of the bearing housing 4. The two radial bearings 8a and 8b are substantially cylindrical slide bearings called metals and bushes, and are in a floating state in a state where displacement in the axial direction is restricted.

  A turbine housing 5 is attached to one end of the bearing housing 4 in the axial direction. A compressor housing 6 is attached to the other end of the bearing housing 4 in the axial direction. The turbine wheel 2 is accommodated in the turbine housing 5. The compressor impeller 3 is accommodated in the compressor housing 6. Between the bearing housing 4 and the turbine housing 5, a link chamber 9 in which a part of a movable part of an actuator 20 described later is disposed is formed.

  A radially outward flange 4 a is provided at a position closer to the turbine housing 5 than the vicinity of the axial center of the outer peripheral surface of the bearing housing 4. An outer cylinder portion 5c of the turbine housing 5 is coupled to the flange 4a.

  In the turbine housing 5, the inner diameter side region in the side wall on the bearing housing 4 side is a part that communicates the scroll passage 5 a and the link chamber 9 by being opened. The turbine housing 5 is provided with a scroll passage 5a for turning the exhaust gas, and a discharge port 5b for discharging the exhaust gas in the scroll passage 5a to an exhaust pipe (not shown) via the turbine wheel 2. In addition, the link chamber 9 described above is disposed adjacent to the scroll passage 5a on the bearing housing 4 side.

  The compressor housing 6 has an inlet 6a through which intake air from an intake system (not shown) is introduced toward the compressor impeller 3 and intake air whose pressure is increased by the rotation of the compressor impeller 3 (not shown). And a delivery passage 6b for delivery to the vehicle.

  By rotating the turbine wheel 2 using the energy of the exhaust gas discharged from the internal combustion engine to the exhaust manifold (not shown), the air supercharged by the compressor impeller 3 that rotates integrally with the turbine wheel 2 is supplied to the intake manifold ( The fuel is supplied from a not-shown combustion chamber (not shown).

  The variable nozzle (VN) unit 7 is capable of changing the capacity of exhaust gas discharged from the scroll passage 5a of the turbine housing 5 through the turbine wheel 2 to the discharge port 5b. The variable nozzle (VN) unit 7 includes a control unit 10, a pair of first nozzle plate 11 and second nozzle plate 12, a plurality of nozzle vanes 13, and an actuator 20.

  As shown in FIGS. 1, 7, and 9, the first support shaft 14 and the second support shaft 15 are fixed to the nozzle vane 13 so as to be connected in a straight line. The protruding end of the first support shaft 14 is rotatably inserted into and supported by a through hole (reference numeral omitted) of the first nozzle plate 11. Further, the protruding end of the second support shaft 15 is rotatably inserted and supported in a through hole (reference numeral omitted) of the second nozzle plate 12.

The 1st nozzle plate 11 and the 2nd nozzle plate 12 are made into the annular plate, and are arrange | positioned so as to oppose in parallel so that the flow path from the scroll channel | path 5a of the turbine housing 5 to the discharge port 5b may be made. Nozzle vanes 13 are attached to several circumferential places (12 places in the present reference example ) of the flow path formed between the first nozzle plate 11 and the second nozzle plate 12 so that the posture can be changed.

Here, in this reference example , as shown in FIGS. 2 and 4, a groove 11 a having a concave cross-sectional shape is formed in the outer peripheral portion of the first nozzle plate 11. A predetermined gap is formed between the first nozzle plate 11 and the turbine housing 5, and a seal ring member 16 is attached to the groove portion 11 a of the first nozzle plate 11 so as to close the gap.

  A part of the inner peripheral surface (the surface on the turbine shaft 2a side) 16a and the outer side surface (the surface on the scroll passage 5a side and the surface on the link chamber 9 side) 16b of the seal ring member 16 are formed on the inner bottom surface and the inner side surface of the groove 11a. It is arranged so as to be in surface contact.

  The outer peripheral surface 16c of the seal ring member 16 is disposed so as to be in surface contact with the inner surface 5d (see FIG. 1) of the turbine housing 5. Further, the outer peripheral surface 16 c of the seal ring member 16 is disposed so as to protrude by a predetermined height in the outer side direction (radial direction) from the outer peripheral surface 11 b of the first nozzle plate 11.

  Further, as shown in FIGS. 3 and 5, the seal ring member 16 is a C-shaped ring member (C ring) having one joint 161. The abutment 161 of the seal ring member 16 is located in the downward direction of the seal ring member 16 (arrow Z2 direction, a direction along gravity) in a state where the seal ring member 16 is attached to the groove 11a of the first nozzle plate 11. Are arranged as follows.

  Further, the seal ring member 16 is made of a material having a large linear expansion coefficient with respect to the turbine housing 5. The material of the seal ring member 16 is not particularly limited as long as it has a large linear expansion coefficient with respect to the turbine housing 5.

In this reference example , as shown in FIG. 3, when the temperature of the exhaust gas is relatively low, a predetermined gap is formed along the circumferential direction at the joint 161 of the seal ring member 16. Is configured to be open.

Further, in this reference example , as shown in FIG. 5, when the temperature of the exhaust gas is relatively high (when the temperature of the exhaust gas is about 280 ° C. or higher), the joint 161 of the seal ring member 16 is a seal ring. The member 16 and the turbine housing 5 are closed by being closed due to a difference in thermal expansion. In this reference example , when the joint 161 of the seal ring member 16 is closed, the joint of the seal ring member 16 on the scroll passage 5a side of the turbine housing 5 and the link chamber 9 side of the seal ring member 16 (the turbine housing 5). ) On the opposite side to the scroll passage 5a side, and is formed so as to overlap on a straight line when viewed from the axial direction of the turbine shaft 2a. The detailed function of the seal ring member 16 will be described later.

  Further, as shown in FIG. 1, a seal member 17 is attached to the inner peripheral surface of the second nozzle plate 12 so as to close a gap between the inner peripheral surface of the second nozzle plate 12 and the turbine housing 5. Yes.

  The actuator 20 changes the postures of all the nozzle vanes 13 at a time, and includes a unison ring 21, a drive source 22, a link mechanism 23, and the like.

  First, the unison ring 21 is arranged on the compressor impeller 3 side of the first nozzle plate 11 so as to be adjacent to the first nozzle ring 11 in a non-contact state with a predetermined interval. The unison ring 21 is supported by the first nozzle plate 11 so as to be rotatable in both directions along the circumferential direction (both clockwise and counterclockwise when viewed from the axial direction). Therefore, as shown in FIGS. 6, 8, and 10, a plurality of rollers 31 are rotatably attached to the first nozzle plate 11 via support shafts 32. Each roller 31 is disposed so as to contact the inner peripheral surface of the unison ring 21.

  As shown in FIG. 1, the drive source 22 is not shown in detail, but a DC motor (DC motor) that generates rotational power and the link rod 24 of the link mechanism 23 pushes and pulls the rotational power of the DC motor. And a power conversion mechanism (for example, a gear mechanism, a worm mechanism, etc.) for converting into a linear motion.

  The link mechanism 23 transmits power generated by the drive source 22 to the unison ring 21 as rotational power, and includes a link rod 24, a link arm 25, a first link pin 26, a second link pin 27, and an operation lever 28. And a vane arm 29 and the like.

  As shown in FIGS. 6, 8, and 11, grooves 21 a are provided at several locations on the inner circumference of the unison ring 21. Each groove 21a is engaged with one operating lever 28 and a plurality of vane arms 29.

  Each of the plurality of vane arms 29 is provided in the same number as the nozzle vanes 13, and the protruding ends of the first support shafts 14 are individually fixedly attached to the tilting fulcrums of the vane arms 29. The operation lever 28 is tilted by a predetermined angle in a predetermined direction by the actuator 20, so that the unison ring 21 is rotated by a predetermined angle in a predetermined direction, and the vane arms 29 are collectively linked by the unison ring 21 and tilted by a predetermined angle in the predetermined direction. It is configured.

  One end of the second link pin 27 is fixed to the tilting fulcrum of the operation lever 28, and one end side of the link arm 25 is fixed to the other end of the second link pin 27. One end of the first link pin 26 is fixed to the other end of the link arm 25, and one end of the link rod 24 is fixed to the other end of the first link pin 26. An output member (not shown) of the power conversion mechanism of the drive source 22 is connected to the other end of the link rod 24. The second link pin 27 is inserted so as to be rotatable in a cylindrical bush 33 (see FIG. 1) penetratingly attached to the flange 4a of the bearing housing 4.

  As shown in FIG. 1, the control unit 10 controls the actuator 20 and is, for example, an existing engine control computer (ECU) that is essential for various operation controls of an engine (not shown). The control unit 10 composed of such an existing ECU includes a function for controlling the supercharging capability of the turbocharger 1 and a function for removing deposits (deposits) adhering to the movable part of the actuator 20 at an appropriate timing. And at least equipped.

  Although not shown in detail, the control unit 10 includes a CPU (central processing unit), a ROM (program memory), a RAM (data memory), a backup RAM (nonvolatile memory), and the like. It is said. The ROM stores various control programs, maps that are referred to when the various control programs are executed, and the like. The CPU executes arithmetic processing based on various control programs and maps stored in the ROM. The RAM is a memory that temporarily stores calculation results in the CPU, data input from each sensor, and the backup RAM is a non-volatile memory that stores data to be saved when the engine is stopped. It is.

  Some of the movable parts of the actuator 20 (the unison ring 21, the second link pin 27 of the link mechanism 23, the operation lever 28 and the vane arm 29) are in a link chamber 9 provided between the bearing housing 4 and the turbine housing 5. Has been placed. On the other hand, the drive source 22 of the actuator 20, the link rod 24 of the link mechanism 23, the link arm 25, and the first link pin 26 are arranged in a state of being exposed outside the flange 4 a of the bearing housing 4.

  Next, the operation of the variable nozzle unit 7 will be described with reference to FIGS. 1 and 6 to 9.

  By pulling the link rod 24 in the direction of the arrow X1 shown in FIG. 6 or pushing it in the direction of the arrow Y1 shown in FIG. 8 by the actuator 20 (see FIG. 1), the link arm 25 is rotated in a predetermined direction by a predetermined angle. . Then, the operation lever 28 is tilted by the link arm 25. As a result, the unison ring 21 is rotated by a predetermined angle in the arrow X2 direction (clockwise direction) shown in FIG. 6 or in the arrow Y2 direction (counterclockwise direction) shown in FIG. 8, and each vane arm 29 is synchronized. Tilted.

  As the vane arms 29 tilt, the nozzle vanes 13 are tilted synchronously via the first support shaft 14 as shown in FIGS. Then, the facing interval (flow path area or throat area) of each nozzle vane 13 is adjusted.

  Specifically, by pulling the link rod 24 in the direction of the arrow X1 shown in FIG. 6, the interval between the plurality of nozzle vanes 13 is maximized as shown in FIG. On the other hand, when the link rod 24 is pushed in the direction of the arrow Y1 shown in FIG. 8, the facing interval (flow channel area or throat area) of each of the plurality of nozzle vanes 13 is minimized as shown in FIG.

  Note that, in the low rotation range of the internal combustion engine, the flow rate of the exhaust gas is increased by adjusting the posture of the nozzle vane 13 so that the facing interval (flow path area or throat area) of the adjacent nozzle vanes 13 is reduced. A high supercharging pressure can be obtained from the rotation range.

  Next, the function of the seal ring member 16 attached to the groove 11a of the first nozzle ring 11 will be described in detail with reference to FIGS.

  For example, conventionally, when the temperature of the exhaust gas is low, such as immediately after the engine is started, the moisture in the exhaust gas in the turbocharger 1 is condensed, and the exhaust gas is directed to the portion where the scroll passage 5a and the link chamber 9 communicate with each other. In order to enter the link chamber 9 from the attachment gap of the first nozzle plate 11, the moisture in the exhaust gas is liquefied in the link chamber 9. The water liquefied in the link chamber 9 falls to the bottom in the link chamber 9. When the engine is stopped immediately after starting the engine in a low temperature environment in which water freezes, the water that has dropped to the bottom of the link chamber 9 freezes at the bottom of the link chamber 9, and the link The movable parts of the actuator 20 (the unison ring 21, the second link pin 27 of the link mechanism 23, the operation lever 28, and the vane arm 29) are frozen on the inside of the chamber 9, and these movable parts are damaged when the engine is restarted.

Therefore, in this reference example , when the temperature of the exhaust gas is low (when the temperature of the exhaust gas is relatively low), the joint 161 of the seal ring member 16 is in an open state (see FIGS. 2 and 3). It is configured as follows. Thereby, at the time of low temperature, the water liquefied in the link chamber 9 can be discharged to the scroll passage 5a through the gap of the joint 161 of the seal ring member 16 (discharge route shown in FIG. 2). As a result, water that has fallen to the bottom of the link chamber 9 is less likely to freeze at the bottom of the link chamber 9, so that it is possible to prevent the movable parts from being damaged when the engine is restarted.

  Conventionally, when a predetermined time has elapsed since the engine was started (when the temperature is high (when the temperature of the exhaust gas is about 280 ° C. or higher)), the exhaust gas and fuel (unburned) flowing through the scroll passage 5a are used. (Fuel, unburned gas) may flow into the link chamber 9 from the attachment gap of the first nozzle plate 11 to the portion where the scroll passage 5a and the link chamber 9 communicate with each other. Here, in general, in a direct injection gasoline engine equipped with a turbocharger, fuel is directly injected into a cylinder, and in a diesel engine, particulate matter (PM) discharged from the engine is used. ) Is collected by a filter in the exhaust pipe, and fuel is added from an exhaust fuel addition valve installed on the upstream side of the turbocharger to raise the catalyst bed temperature, so that the PM deposited on the filter in the exhaust pipe is increased. It is configured to burn. For this reason, at high temperatures, exhaust gas and fuel (unburned fuel, unburned gas) flowing through the scroll passage easily flow into the link chamber 9. When such an inflow is repeated, a part of the movable parts of the actuator 20 (the unison ring 21, the second link pin 27 of the link mechanism 23, the operation lever 28, and the vane arm) which are liquefied and arranged in the link chamber 9 are obtained. By adhering to and depositing on 29), deposits can interfere with the movement of the moving parts.

Therefore, in this reference example , when the temperature of the exhaust gas is high, the joint 161 of the seal ring member 16 is closed due to a difference in thermal expansion between the seal ring member 16 and the turbine housing 5 (see FIGS. 4 and 5). ) Is configured as follows. Thereby, when the high temperature is high, the joint 161 of the seal ring member 16 is in a closed state, so that the exhaust gas and fuel flowing through the scroll passage 5a communicate with the first nozzle with respect to the portion where the scroll passage 5a and the link chamber 9 communicate with each other. The flow into the link chamber 9 from the attachment gap of the plate 11 is suppressed. As a result, the deposit (deposit) is prevented from adhering to or depositing on the movable parts of the actuator 20 arranged in the link chamber 9, so that the movement of the movable parts is hardly hindered.

As described above, in the present reference example , as described above, the exhaust gas temperature is high in the seal ring member 16 in which the abutment 161 is open when the temperature of the exhaust gas is low (when the temperature is relatively low). At this time (when the temperature is relatively high), the abutment 161 is closed due to a difference in thermal expansion between the seal ring member 16 and the turbine housing 5. As a result, at a low temperature when the possibility of fuel flowing into the link chamber 9 is low, the condensed water generated in the link chamber 9 can be discharged, and the fuel is highly likely to flow into the link chamber 9. Sometimes, the inflow 161 into the link chamber 9 can be suppressed by closing the joint 161 of the seal ring member 16. As a result, the condensate drainage generated in the link chamber 9 can be improved, and the fuel can be prevented from flowing into the link chamber 9. It is possible to achieve both suppression.

Further, in the present reference example , as described above, the joint 161 of the seal ring member 16 is disposed in a region in the downward direction (direction along the gravity) in the region between the first nozzle plate 11 and the turbine housing 5. By doing so, the fuel that has flowed into the link chamber 9 and the condensed water generated in the link chamber 9 are likely to fall downward (in the direction along the gravity), so the fuel that has flowed into the link chamber 9 and the link chamber The condensed water generated in 9 can be efficiently discharged.

In the reference example, as an example of the seal ring member, it showed seal ring member having one abutment is not limited to Re this. For example, a seal ring member having two or more joints may be used as long as it is in a state where the joint is opened at a low temperature and the joint is closed at a high temperature.

(First embodiment)
In the above reference example , in the state where the joint 161 of the seal ring member 16 is closed, the joint of the seal ring member 16 on the scroll passage 5a side of the turbine housing 5 and the link chamber 9 side of the seal ring member 16 (scroll of the turbine housing 5). The example in which the abutment on the side opposite to the passage 5a side is arranged so as to overlap on a straight line when viewed from the axial direction of the turbine shaft 2a is shown . In the first embodiment shown in FIGS . 12 and 13, the seal ring member 116 is configured to have a stepped joint 116 a . 12 is a view of the seal ring member 116 as seen from the axial direction of the turbine shaft, and FIG. 13 is a view as seen from the P direction shown in FIG. As shown in FIG. 12, when the flow direction of the exhaust gas flowing through the scroll passage 5a is the counterclockwise direction, as shown in FIG. 13, the joint of the seal ring member 116 on the scroll passage 5a side of the turbine housing 5 is formed. 116b may be disposed on the downstream side of the exhaust gas flowing in the scroll passage 5a with respect to the joint 116c on the link chamber 9 side of the seal ring member 116. That is, since the fuel (unburned fuel) flows along the swirling flow of the exhaust gas, the fuel / exhaust gas is assembled by assembling the joint 116b of the seal ring member 116 in a direction in which the swirling flow of the exhaust gas hardly flows. Is less likely to flow into the link chamber 9 side from the joint 116b of the seal ring member 116. As a result, the fuel that has flowed into the link chamber 9 due to the ejector effect and the condensed water generated in the link chamber 9 can be sucked out to the scroll passage 5a side, and the fuel can be prevented from flowing into the link chamber 9. be able to. As a result, when the joint 116a of the seal ring member 116 is in an open state, it is possible to improve the discharge performance of the fuel and condensed water accumulated in the link chamber 9, and the fuel flows into the link chamber 9. Can be suppressed.

(Second Embodiment)
Furthermore, in the present invention, as in the second embodiment shown in FIG. 14, the seal ring member 216 may be configured to have an obliquely shaped joint 216a. In this case, as shown in FIG. 14, exhaust gas flowing in the scroll passage 5 a from the joint 216 b on the scroll passage 5 a side of the turbine housing 5 of the seal ring member 216 with respect to the joint 216 c on the link chamber 9 side of the seal ring member 216. You may arrange | position so that it may be located in the downstream of gas. As a result, as in the first embodiment described above, the fuel flowing into the link chamber 9 due to the ejector effect and the condensed water generated in the link chamber 9 can be sucked out to the scroll passage 5a side, and the link chamber 9 The fuel can be prevented from flowing into the inside. As a result, when the joint 216a of the seal ring member 216 is in an open state, the fuel and condensate collected in the link chamber 9 can be improved, and the fuel flows into the link chamber 9. Can be suppressed.

  INDUSTRIAL APPLICABILITY The present invention can be used for a supercharger, and more specifically, a turbine housing that houses a turbine wheel that rotates by being blown with exhaust gas of an internal combustion engine, and exhausts the turbine wheel that is housed in the turbine housing. It can utilize for a supercharger provided with the nozzle plate which forms the gas channel which guides gas.

2 Turbine wheel 5 Turbine housing 5a Scroll passage 11 First nozzle plate (nozzle plate)
16, 116, 216 Seal ring member 161, 116a, 216a

Claims (2)

A turbine housing that houses a turbine wheel that rotates by blowing exhaust gas of an internal combustion engine; a nozzle plate that forms a gas passage that guides the exhaust gas to the turbine wheel housed in the turbine housing; and the nozzle A turbocharger comprising a seal ring member disposed between a plate and the turbine housing;
The seal ring member is a ring member having a joint,
Wherein said seal ring member abutment, together with a state where the temperature of the exhaust gas is opened when the temperature is low, Ri Do the state where the temperature of the exhaust gas is closed at a high temperature,
The joint of the seal ring member on the scroll passage side of the turbine housing is on the downstream side of the exhaust gas flowing in the scroll passage with respect to the joint of the seal ring member on the side opposite to the scroll passage side of the turbine housing. A turbocharger arranged to be positioned . The turbocharger according to claim 1, wherein
The supercharger according to claim 1, wherein the abutment of the seal ring member is arranged in a lower region of a region between the nozzle plate and the turbine housing.

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