JP4729462B2 - Turbocharger fitting - Google Patents

Description

  The present invention provides a turbocharger that is used to attach a turbine housing side portion of a turbocharger that generates supercharging pressure to an internal combustion engine using energy of exhaust gas of the internal combustion engine to a fixing member such as an engine block on the internal combustion engine side. It is related with the fixture for chargers.

  In general, in a diesel engine or a gasoline engine used as an internal combustion engine (engine) of an automobile, a turbocharger in which a turbine side and a compressor side are integrally configured is used.

  In such a turbocharger, by rotating the turbine wheel mounted in the turbine housing by the engine exhaust flow of the internal combustion engine and rotating the compressor wheel mounted in the compressor housing in conjunction with the turbine wheel, The intake air is supercharged into the combustion chamber of the internal combustion engine.

  Such turbine housings for turbochargers include those having a low rigidity configured as a thin cast or a press-formed product of a heat-resistant thin steel plate, in addition to those having a high rigidity configured as a thick casting.

  Furthermore, for low-stiffness turbine housings configured as press-formed products of heat-resistant thin steel plates in turbochargers, the temperature of the exhaust gas on the turbine side from the viewpoint of early activation of the catalyst during cold start of the internal combustion engine It is required to reduce heat absorption without lowering.

  Therefore, in a conventional turbocharger, for example, an inner shell formed of a press-formed product of a heat-resistant thin steel plate is separated by a predetermined distance inside an outer shell of a turbine housing formed of a press-formed product of a heat-resistant thin steel plate. It is constructed in the arranged double pipe structure.

  And in this turbocharger turbine housing, a hollow heat insulating layer is formed between the inner shell and the outer shell to insulate the air, and the air is fed into the inner shell from the exhaust manifold to rotate the turbine. Early activation of the catalyst during cold start of the internal combustion engine by suppressing the heat absorption by the hot exhaust gas contacting the inner wall of the inner shell and guiding the exhaust gas to the catalyst while maintaining the high temperature Has been proposed (for example, see Patent Document 1).

  In addition, when a turbocharger is attached to an internal combustion engine, a portion where a low-rigidity turbine housing configured as a press-formed product of a heat-resistant thin steel plate in the turbocharger is indirectly attached to an engine block, for example, a portion of the turbine housing having low rigidity. A stay seat is provided, and one end portion is fastened to the stay seat with a bolt and a nut, and the other end portion of the mounting bracket is fastened to the engine block with a bolt and a nut and fixed so as to be completely restrained (that is, Fix it so that even the thermal strain cannot be freely deformed).

  Furthermore, piping and members such as exhaust manifolds and turbo elbows connected to supply high-temperature exhaust gas from the engine head to the turbine housing are connected to the turbine housing fixed so as not to move completely. To do.

  When the turbine housing is fixed so as to be completely restrained by the mounting bracket in this way, the heat generated by the turbine housing itself being heated and thermally expanded by the high-temperature exhaust gas sent from the internal combustion engine. Along with stress, when a pipe or member such as an exhaust manifold or a turbo elbow connected to the turbine housing is thermally expanded, the low-rigidity turbine housing is configured as a heat-formed sheet steel press-formed product due to the thermal stress caused by the thermal expansion. There is a risk of damage such as compression yielding and plastic deformation.

  Further, in a turbine housing having low rigidity configured as a heat-formed thin steel plate press-molded product, in order to stably support the turbine housing itself, for example, both end portions of the turbine housing are respectively attached to the internal combustion engine using two mounting brackets. When fixed to the engine block so that it is completely restrained, the thermal expansion of the engine block itself opens the gap between the two mounting brackets, and the heat stress acts on the turbine housing, making it a rigid heat-resistant steel plate press There is a risk that the turbine housing itself having a low height may be damaged by compressive yielding and plastic deformation.

JP 2003-293780 A

  In view of the above-described points, the present invention indirectly attaches a turbine housing portion of a turbocharger installed in an internal combustion engine to a fixing member on the internal combustion engine side in a state where plastic deformation due to thermal stress can be suppressed. An object of the present invention is to provide a new turbocharger fixture.

  According to a first aspect of the present invention, there is provided an attachment for a turbocharger, wherein the turbine housing portion of the turbocharger is indirectly attached to a fixed member of an internal combustion engine, and the stay on the exhaust gas intake side in the turbine housing. A first arm portion that is attached to the first arm portion, a second arm portion that is integrally connected to the first arm portion, and is attached to the stay seat of the fixing member, and the stay seat of the fixing member and the exhaust gas intake port The first arm portion is continuously connected to the first arm portion so as to branch from an intermediate predetermined position between the first arm portion and the second arm portion, or the stay of the first arm portion. A third arm portion that is integrally and continuously constructed from a portion attached to the seat, and that is configured as an integrated rigid structure, the free end portion of which is attached to the stay seat near the exhaust gas discharge port, Have And wherein the door.

  By configuring as described above, when an external force is applied from the member on the fixed member side to the exhaust gas inlet side portion of the turbine housing of the turbocharger, the first arm portion integrated in the fixture is changed from the first arm portion. 3 is supported so that the distance between the stay seat on the exhaust gas intake side and the stay seat on the exhaust gas discharge side in the turbine housing does not change (on the exhaust gas intake side). When the first arm portion is displaced on the side of the stay seat, the displacement is supported so that the displacement is transmitted to the third arm portion (for example, supported so that the positional relationship between them does not change). Can be suppressed from yielding to pressure and plastic deformation. Further, in this fixture, since it is attached to the fixing member by only one second arm portion, even if the fixing member is thermally expanded, the stay seat of the exhaust gas discharge port side flange portion in the turbine housing Since the distance between the exhaust gas intake side flange and the stay seat does not change, it is possible to prevent the fixing member from thermally expanding and the turbine housing from yielding pressure and being plastically deformed.

  According to a second aspect of the present invention, in the turbocharger attachment according to the first aspect, the rigidity of the portion continuing from the first arm portion to the second arm portion is greater than the rigidity of the third arm portion. It is characterized by having a high rigidity.

  By configuring as described above, in addition to the operation and effect of the invention according to claim 1, the stress input from the exhaust manifold side is elastically deformed by the first arm portion and the second arm portion. Since it receives, it can suppress that the stress input from the exhaust manifold side acts on a turbine housing main body.

  According to a third aspect of the present invention, in the turbocharger attachment according to the first aspect, the rigidity of the portion continuing from the first arm portion to the third arm portion is greater than the rigidity of the second arm portion. It is characterized by having a high rigidity.

  By configuring as described above, in addition to the operation and effect of the invention according to claim 1, the second arm portion having relatively low rigidity is elastically deformed by the stress input from the exhaust manifold side. In addition, the stress input from the exhaust manifold side is prevented from acting on the turbine housing through a portion of a series of relatively high rigidity from the first arm portion to the third arm portion, thereby improving the durability reliability of the turbine housing. It can be improved.

  According to a fourth aspect of the present invention, in the turbocharger attachment according to the first or second aspect, the rigidity of the third arm portion is lower than the rigidity of the turbine housing portion. It is characterized by that.

  By configuring as described above, in addition to the operation and effect of the invention according to claim 1 or claim 2, the turbine housing itself is thermally expanded, and the stay seat on the exhaust gas intake side and the exhaust gas exhaust are exhausted. When the distance to the stay on the side close to the outlet changes, the third arm portion having low rigidity is elastically deformed and absorbed, so that excessive thermal stress can be suppressed from occurring in the turbine housing. .

  According to the turbocharger fitting of the present invention, the turbine housing portion of the turbocharger installed in the internal combustion engine is indirectly indirectly controlled in a state where it can be prevented from being plastically deformed by thermal stress with respect to the fixing member on the internal combustion engine side. It is possible to install the product, and it is possible to provide an inexpensive product with a simple configuration.

  An embodiment relating to a turbocharger fixture of the present invention will be described with reference to FIGS.

  FIG. 2 is a schematic cross-sectional view showing a schematic structure of the entire turbocharger. In FIG. The turbocharger body 1 is integrally configured to drive a radiant flow type compressor with a radiant flow type turbine.

  Therefore, in the turbocharger main body 1, the turbine housing 3 and the compressor housing 4 are integrally assembled via the center housing 5 to constitute a casing of the entire turbocharger main body 1.

  In the turbocharger body 1, a turbine wheel 6 is mounted inside the turbine housing 3 in order to constitute a radiant flow turbine driven by an engine exhaust flow of an internal combustion engine 2 (shown in FIG. 1).

  In addition, a compressor wheel 7 is mounted inside the compressor housing 4 in order to configure a radiant flow type compressor that supercharges intake air into the combustion chamber of the internal combustion engine 2.

  The turbine wheel 6 and the compressor wheel 7 are configured to rotate integrally within the casing of the turbocharger body 1 by being connected by a rotor shaft 8. That is, the rotor shaft 8 is integrally configured by fixing the turbine wheel 6 at one end thereof and fixing the compressor wheel 7 at the other end thereof.

  Further, the rotor shaft 8 is supported by a full float bearing 9 disposed in the center housing 5 at an intermediate portion that penetrates the center housing 5. By configuring in this way, the turbine wheel 6, the compressor wheel 7 and the rotor shaft 8 are integrally supported so as to freely rotate.

  A spiral scroll chamber 10 is formed in the turbine housing 3 for constituting a turbulent turbine in the turbocharger main body 1 so as to surround the turbine wheel 6.

  The turbine housing 3 is provided with an inner shell 18 made of a heat-resistant thin steel plate press-formed product for forming the scroll chamber 10 therein, and is press-formed with a heat-resistant thin steel plate so as to be surrounded by a predetermined interval. A so-called double-pipe structure is provided in which an outer shell 19 made of a product is disposed and an air heat insulating layer is formed between the inner shell 18 and the outer shell 19 as a heat insulating layer. As the heat-resistant thin steel plate, for example, stainless steel, Hastelloy (registered trademark), Inconel (registered trademark), or the like can be used.

  The scroll chamber 10 formed inside the inner shell 18 is provided with an exhaust gas intake port 11 that opens in the tangential direction of the rotor shaft 8 and an exhaust gas discharge port 12 that opens in the axial direction of the rotor shaft 8.

  The scroll chamber 10 is formed in a spiral shape such that the distance between the outer peripheral edge and the axis of the rotor shaft 8 decreases from a predetermined portion on the exhaust gas intake 11 side toward the front in the rotational direction of the turbine wheel 6. To do.

  Further, a shroud portion 32 that forms a narrow gap for injecting exhaust gas from the radial direction of the turbine wheel 6 toward the turbine blade portion is formed in the spiral portion of the scroll chamber 10.

  The exhaust gas intake 11 is connected to an exhaust manifold 14 (shown in FIG. 1) of the internal combustion engine 2. Further, the exhaust gas discharge port 12 is connected to an exhaust pipe (not shown) for guiding the exhaust gas to the catalyst through a case 13 formed as a peripheral portion of the discharge port.

  The case 13 is made of a heat-resistant thin steel plate press product similar to the inner shell 18 and the outer shell 19 and is fixed to the side surface of the outer shell 19 by welding. The case 13 is formed with an insertion hole 20 (shown in FIG. 1) through which the portion of the exhaust gas discharge port 12 of the inner shell 18 is inserted.

  Further, in this turbocharger, when the pressure of the exhaust gas supplied into the scroll chamber 10 of the turbine housing 3 exceeds a predetermined value in order to prevent the supercharging pressure for the internal combustion engine from rising more than necessary, A waste gate valve device that exhausts a part of the exhaust gas fed into the scroll chamber 10 from the upstream side in the exhaust gas feed direction from the turbine wheel 6 is mounted.

  Therefore, as shown in FIG. 1, a waste gate nozzle 23 (an escape nozzle, so-called WG nozzle) is provided in a predetermined portion of the turbine housing 3 on the exhaust gas discharge port 12 side. A part of the waste gate nozzle 23 is attached to a WG nozzle insertion hole 24 formed in the case 13.

  Further, the case 13 of the turbine housing 3 is provided with a partition plate 28 between the insertion hole 20 through which the exhaust gas discharge port 12 is inserted and the WG nozzle insertion hole 24. As a result, the internal space of the case 13 has two chambers that are independent from each other: an exhaust chamber 25 in which the exhaust gas discharge port 12 opens and an escape chamber 27 in which the waste gate port 26 at the tip of the waste gate nozzle 23 opens. It is divided into.

  The waste gate nozzle 23 is provided with a waste gate valve 29 (relief valve) configured to open and close the waste gate port 26. Although not shown, the waste gate valve 29 is configured so that, for example, the diaphragm opens the waste gate port 26 when a pressure of supercharged air exceeding a predetermined value is applied to the diaphragm mounted on the supercharged air discharge port 17 side. The operation is configured such that a part of the exhaust gas passing through the scroll chamber 10 is discharged into the escape chamber 27.

  Although not shown, the waste gate valve 29 closes the waste gate port 26 when the supercharged air pressure becomes a predetermined value or less, so that the waste gate port 26 is closed and the exhaust gas passing through the scroll chamber 10 is released. The discharge to the chamber 27 is configured to be suppressed.

  As shown in FIGS. 1 and 2, a flange portion 21 is formed in the case 13 of the turbine housing 3 so as to bulge outward from the opening end of the peripheral wall of the case 13. Further, an intake flange 30 is provided at the peripheral portion of the exhaust gas intake 11 in the pipe-shaped member forming the scroll chamber 10 of the turbine housing 3.

  As shown in FIG. 2, a compressor wheel 4 for constituting a radiant compressor that supercharges intake air into the combustion chamber of the internal combustion engine 2 in the turbocharger body 1 is surrounded by a compressor wheel 7. A diffuser 15 having a spiral shape (a spiral structure similar to that of the scroll chamber 10 described above) is formed.

  The diffuser 15 is provided with an intake air intake port 16 that opens in the axial direction of the rotor shaft 8 and a supercharged air discharge port 17 that opens in the tangential direction of the rotor shaft 8. The air intake 16 is connected to an air cleaner (not shown). The supercharged air discharge port 17 is connected to an intake manifold (not shown) of the internal combustion engine 2.

  Next, the operation of the turbocharger main body 1 configured as described above will be described. In the turbocharger main body 1, high-temperature and high-pressure exhaust gas generated in accordance with the operation of the internal combustion engine is blown into the spiral chamber of the scroll chamber 10 from the exhaust gas intake 11.

  The scroll chamber 10 rotates the turbine wheel 6 by injecting the exhaust gas blown into the interior at a high speed in the radial direction from the shroud portion 32 of the scroll chamber 10 to the turbine blade portion of the turbine wheel 6, The exhaust gas is discharged from the exhaust gas outlet 12 to the exhaust pipe.

  The compressor wheel 7 rotates in conjunction with the rotation of the turbine wheel 6 at this time, the pressure of the supply air introduced into the diffuser 15 from the intake air intake port 16 is increased, and the supercharged air discharge port 17 serves as supercharged air. Supplied to the combustion chamber.

  In this turbocharger, when the pressure of the supercharged air flowing through the supercharged air discharge port 17 exceeds a predetermined value, the actuator opens the wastegate port 26 of the wastegate valve 29 and the turbine housing 3 is operated. The pressure of the exhaust gas supplied into the scroll chamber 10 is reduced.

  Thereby, in this turbocharger, the exhaust gas weakens the force for rotating the turbine wheel 6 to reduce the compression rate by the compressor wheel 7 that rotates integrally with the turbine wheel 6, and excessively enters the combustion chamber of the internal combustion engine from the diffuser 15. Suppressing the supply of supercharged air with increased pressure.

  Further, it is possible to prevent the compressor wheel 7 from being adversely affected by preventing the supply air from being excessively compressed by the compressor so that the temperature of the supercharging air does not become higher than a predetermined level.

  Next, in the turbocharger main body 1 configured as described above, the portion of the turbine housing 3 provided with the turbine wheel 6 rotating at high speed and the wastegate valve device is indirectly attached to the internal combustion engine (engine). The configuration will be described.

  In this turbocharger main body 1, in order to indirectly attach the turbine housing 3 portion to the internal combustion engine 2, the stay of the flange portion on the exhaust gas discharge port side projecting in a L-shaped cross section on the flange portion 21 in the case 13 of the turbine housing 3. A seat 22 is provided. This stay seat 22 is drilled with a through hole (not shown) for fastening with a screw component.

  Further, a stay seat 31 of the exhaust gas intake side flange is provided at a predetermined portion of the intake flange 30 of the exhaust gas intake 11 in the turbine housing 3. This stay seat 31 is perforated with a through hole (not shown) for fastening with a screw component.

  In the turbocharger main body 1, the two stay seats may be set at predetermined locations such as the outer shell 19 other than the intake port flange 30 or the flange portion 21, respectively.

  As shown in FIG. 1, in the configuration in which the turbine housing 3 portion is indirectly attached to the internal combustion engine 2, the stay seat 22 of the exhaust gas discharge side flange portion, the stay seat 31 of the exhaust gas intake side flange, and the internal combustion engine 2, the turbine housing 3 portion is supported by the internal combustion engine 2 with the fixture 33 interposed therebetween.

  As shown in FIGS. 1 and 2, in the configuration in which the turbine housing 3 portion is indirectly attached to the internal combustion engine 2, the interval between the two attachment positions (positions of the two stay seats 22 and 31) provided on the turbine housing 3 side is as follows. The turbine housing 3 is set to be longer than the distance at which the turbine housing 3 can be stably supported.

  At the same time, in the configuration in which the turbine housing 3 portion is attached to the internal combustion engine 2 via the attachment 33, the first arm of the attachment 33 arranged so as to bridge between two attachment positions provided on the turbine housing 3 side. The amount of the portion 34 and the second arm portion 35 that are heated and thermally expanded during operation of the internal combustion engine 2 and the interval between the two mounting positions provided in the turbine housing 3 are increased in temperature and thermally expanded during operation. It is set so that the difference from the amount falls within an allowable range and is within a distance that does not cause damage such as yield deformation due to pressure between the two mounting positions in the turbine housing 3 and plastic deformation.

  Further, in the configuration in which the turbine housing 3 portion is attached to the internal combustion engine 2 by the fixture 33, the turbocharger main body 1 including the turbine wheel 6 that rotates at a high speed and the wastegate valve device having a precise structure is caused to malfunction. It is configured not to give a plastic deformation.

  The illustrated fixture 33 is configured to have a rigid structure that is an integrated rigid body so that the three arm portions 34, 35, and 36 diverge and extend in a substantially tridental shape as a whole. Each of the three arms 34, 35, and 36 includes a long member (angle member) having an L-shaped cross section, a long member having a substantially U-shaped cross section, a circular cross section, a polygonal cross section, or a tubular shape. A material obtained by cutting a long member having a cross-sectional shape into a predetermined length can be used.

  As described above, the fixture 33 has a simple configuration in which the first arm portion 34, the second arm portion 35, and the third arm portion 36 are integrated, so that it can be easily manufactured and an inexpensive product can be provided.

  Since the first arm portion (exhaust manifold side arm portion) 34 of the fixture 33 is fastened to the stay seat 31 of the exhaust gas intake side flange at the tip end portion thereof, the first arm portion (exhaust manifold side arm portion) 34 is largely bent at a portion near the tip end. A fastening through hole 38A (shown in FIG. 6) is drilled at a predetermined position.

  The first arm portion (exhaust manifold side arm portion) 34 has a fastening through hole 38A at the tip thereof in communication with the through hole of the stay seat 31 of the exhaust gas intake side flange, such as a bolt and a nut. The screw part 37 is fastened.

  The second arm portion (internal combustion engine 2 main body side arm portion) 35 of the fixture 33 is fastened to a stay seat (not shown) formed at a predetermined position in the engine block 2A, which is a fixing member. And a fastening through hole 38B (shown in FIG. 5) is drilled at a predetermined position of the tip.

  The fixing member to which the second arm portion 35 of the fixture 33 is attached may be a cylinder block, a cylinder head, a transmission housing, or an oil pan in addition to the engine block 2A described above.

  And the 2nd arm part (internal combustion engine 2 main body side arm part) 35 is the state which made the through-hole 38B for fastening of the front-end | tip part connected with the through-hole (not shown) drilled in the stay seat of the engine block 2A. Then, it is fastened with screw parts 37 such as bolts and nuts.

  The third arm portion (turbine side arm portion) 36 of the fixture 33 is bent largely at a predetermined portion in the middle portion thereof in order to fasten the tip portion thereof to the stay seat 22 of the flange portion on the exhaust gas discharge port, A fastening through hole 38C (shown in FIG. 6) is drilled at a predetermined position of the portion.

  The third arm portion (turbine side arm portion) 36 has bolts, nuts and the like in a state where the fastening through hole 38C at the tip thereof is communicated with the through hole of the stay seat 22 of the exhaust gas discharge port side flange portion. The screw part 37 is fastened.

  As shown in FIG. 1, the flange portion of the free end portion of the exhaust manifold 14 extending from the engine head 2B is fastened to the intake flange 30 of the exhaust gas intake port 11 in the turbocharger main body 1, thereby The exhaust gas of the engine 2 is connected so as to be supplied from the exhaust gas intake 11 through the exhaust manifold 14.

  Further, an exhaust pipe for guiding exhaust gas to an exhaust gas purification catalyst (not shown) is connected to the flange portion 21 of the exhaust gas discharge port 12.

  In the configuration in which the turbine housing 3 portion of the turbocharger body 1 is attached to the internal combustion engine 2 using the fixture 33 as described above, the exhaust gas intake side flange stay seat 31 and the exhaust gas at a position separated by a predetermined distance. Three points of the stay seat 22 (not shown) provided at a predetermined position of the engine block 2A and the three arm portions 34, 35, and 36 are branched into a substantially trifurcated shape as a whole. Thus, the structure is fixed by a fixture 33 which is an integrated rigid body.

  In a state where the turbine housing 3 portion is indirectly attached to the engine block 2A with such an attachment structure using the attachment 33, the engine head 2B and the intake flange 30 of the turbine housing 3 are connected to each other. When the exhaust manifold 14 is heated by the exhaust gas of the internal combustion engine 2 and thermally expands, thermal stress in the direction of pressing the intake flange 30 of the turbine housing 3 acts.

  At this time, when the exhaust manifold 14 is cast and has high rigidity, the amount of thermal displacement of the exhaust manifold 14 is absorbed on the turbine housing 3 side.

  In this case, the portions of the first arm portion 34 and the third arm portion 36 which are integrated in the fixture 33 are connected to the stay seat 22 and the exhaust gas intake port of the exhaust gas discharge port side flange portion in the turbine housing 3. The distance between the side flange and the stay seat 31 is supported so as not to change (the displacement of the first arm 34 due to the thermal stress on the exhaust manifold 14 side is transmitted to the third arm 36). Therefore, it is possible to suppress the exhaust manifold 14 from thermally expanding and compressing and yielding the turbine housing 3 to be plastically deformed.

  Further, in this case, the first arm portion 34 and the third arm portion 36 move integrally (synchronously move) when subjected to thermal stress on the exhaust manifold 14 side, so that the first arm The portion 34 and the third arm portion 36 move in different directions to slightly rotate the turbine housing 3 supported by the portions 34 and the third arm portion 36, thereby preventing stress concentration in the torsional direction from occurring between the mounting portion of the exhaust manifold 14. it can.

  Further, in this fixture 33, the first arm portion 34 and the third arm portion 36 that are integrated are attached to the engine block 2A by one second arm portion 35, and will be described later. Even if the engine block 2A is thermally expanded as in the structure supported by two spaced apart fixtures, the stay seat 22 of the exhaust gas exhaust side flange portion and the exhaust gas intake side flange of the turbine housing 3 Since the distance from the stay seat 31 does not change, it is possible to suppress the engine block 2A from thermally expanding and compressing and yielding the turbine housing 3 to be plastically deformed.

  Here, the above-described operation of the fixture 33 is performed by separating the stay seat 31 of the exhaust gas intake side flange in the turbine housing 3 and the stay seat 22 of the exhaust gas exhaust side flange from each other. This will be described in comparison with the structure supported by the fixture.

  In the case of a structure in which the turbine housing 3 is supported by this separate mounting tool, when the exhaust manifold 14 is thermally expanded, one mounting tool that supports the stay seat 31 of the exhaust gas intake side flange is deformed to deform the turbine housing. Thermal stress acts on the 3 side.

  At this time, the thermal stress acting from the exhaust manifold 14 acts on the main body of the turbine housing 3 and is received by the other fixture that supports the stay seat 22 of the flange portion on the exhaust gas discharge port side.

  That is, in the turbine housing 3, the thermal stress acting when pushed by the thermally expanded exhaust manifold 14 is transmitted to the turbine housing 3 main body by deforming one of the fixtures close to the exhaust manifold 14, and the other This is transmitted to the fixture, and thermal stress is received by the other fixture.

  Accordingly, the turbine housing 3 is subject to external forces in the direction of being crushed by the thermal stress pressed from the exhaust manifold 14 side and the reaction force acting from the other fixture side. There is a risk of damage due to plastic yielding and plastic deformation.

  Moreover, two separate points of the engine block, the corresponding stay seat 31 of the exhaust gas intake side flange, and the stay seat 22 of the exhaust gas discharge side flange portion are separately provided. In the case of the structure supported by the fixture, when the engine block is thermally expanded and the interval between the attachment locations of the two fixtures is increased, the stay seat 31 of the exhaust gas intake side flange and the exhaust gas exhaust side flange portion are There remains a risk that the thermal stress in the direction of widening the distance from the stay seat 22 acts, and the turbine housing 3 is damaged by being pulled and plastically deformed by a pulling force.

  As described above, when the turbine housing 3 portion is indirectly attached to the engine block 2A with the attachment structure using the attachment 33 according to the present embodiment, thermal stress relating to members other than the turbine housing 3 acts. It can be understood that the turbine housing 3 can be satisfactorily suppressed from being damaged by yielding to an external force and plastically deforming.

  In addition, you may comprise the fixture 33 mentioned above by bending one rod-shaped member. In this case, although not shown in the drawing, one end of a rod-like member bent into a predetermined shape is attached to the engine block 2A, its intermediate predetermined position is attached to the stay seat 31 of the exhaust gas intake side flange, and the other end The portion is attached to the stay seat 22 of the exhaust gas discharge port side flange portion.

  In such a configuration, the portion of the rod-shaped member bent into a predetermined shape from the one end portion attached to the engine block 2A to the intermediate predetermined position attached to the stay seat 31 of the exhaust gas intake side flange is the second portion. The arm portion 35 serves as the first arm portion 34, and the third arm portion 36 is bent from an intermediate predetermined position attached to the stay seat 31 to reach the other end portion.

  Next, another configuration example of the fixture 33 will be described with reference to FIGS. 1 to 3, 5, and 6.

  In the configuration example of the fixture 33 shown in FIGS. 1 to 3, 5, and 6, the rigidity of a series of portions from the first arm portion 34 to the second arm portion 35 is set to the third arm portion 36. The third arm portion 36 is configured to have a rigidity lower than that of the turbine housing 3.

  In this fixture 33, the first arm portion 34 and the second arm portion 35 are each composed of a long member (angle material) having an L-shaped cross section having higher rigidity than the third arm portion 36, The third arm portion 36 is constituted by a long member (angle material) having an L-shaped cross section having a lower rigidity than the first arm portion 34 and the second arm portion 35.

  The first arm portion 34 and the second arm portion 35 in the fixture 33 are formed of a single long member having an L-shaped cross section having a relatively high rigidity.

  Further, the third arm portion 36 of the fixture 33 has a relatively low rigidity (here, the rigidity is reduced by narrowing the width of the L-shaped section), and the base of the long member having the L-shaped section. The end portion is fixed to an arbitrary position of a relatively long L-shaped long member having a series of the first arm portion 34 and the second arm portion 35 by welding or the like. Thus, the entire fixture 33 is configured to be a rigid body.

  In the configuration example in which the rigidity of the series of parts from the first arm part 34 to the second arm part 35 is made stronger than the rigidity of the third arm part 36, the stress input from the exhaust manifold 14 side is applied. Since the first arm portion 34 and the second arm portion 35 are elastically deformed and received, the stress input from the exhaust manifold 14 side can be suppressed from acting on the turbine housing 3 body.

  In the configuration example in which the rigidity of the series of portions from the first arm portion 34 to the second arm portion 35 is higher than the rigidity of the third arm portion 36, the third arm configured to have low rigidity. The closer the base end portion of the portion 36 is to the stay seat 31 of the exhaust gas intake side flange, the shorter the distance of the portion of the first arm portion 34 where the thermal stress of the exhaust manifold 14 acts, The influence of the deformation of the arm portion 34 can be reduced.

  Further, in the configuration example in which the rigidity of the series of portions from the first arm portion 34 to the second arm portion 35 is made stronger than the rigidity of the third arm portion 36, the turbine housing 3 itself is thermally expanded. When the distance between the stay seat 31 of the exhaust gas intake side flange and the stay seat 22 of the exhaust gas exhaust side flange changes, the third arm portion 36 having low rigidity is elastically deformed. Therefore, excessive thermal stress can be prevented from being generated in the turbine housing 3.

  In the configuration example in which the rigidity of the series of parts from the first arm part 34 to the second arm part 35 is higher than the rigidity of the third arm part 36, the third arm part 36 is further increased. Since the influence of the external force acting on the turbine housing 3 can be reduced because the rigidity of the portion is made weaker than the rigidity of the turbine housing 3, it is possible to suppress plastic deformation due to thermal stress.

  Therefore, in the configuration example in which the rigidity of the series of parts from the first arm part 34 to the second arm part 35 is made stronger than the rigidity of the third arm part 36, the turbine housing 3 is made thin or thin. Thus, even when the strength is low, the durability reliability of the turbine housing 3 can be improved.

  Next, still another configuration example of the fixture 33 will be described with reference to FIG. In the configuration example of the fixture 33 shown in FIG. 4, the rigidity of the series of parts from the first arm part 34 to the third arm part 36 is configured to be stronger than the rigidity of the part of the second arm part 35. .

  In the configuration example in which the rigidity of the series of parts from the first arm part 34 to the third arm part 36 is made stronger than the rigidity of the second arm part 35, the stress input from the exhaust manifold 14 side is applied. A portion of the second arm portion 35 having relatively low rigidity is elastically deformed and absorbed, and further, a series of rigidity from the first arm portion 34 to the third arm portion 36 is applied by the stress input from the exhaust manifold 14 side. It can suppress acting on the turbine housing 3 through a comparatively high part.

  Further, in the configuration example in which the rigidity of the series of parts from the first arm part 34 to the third arm part 36 is made stronger than the rigidity of the second arm part 35, the first arm part 34. The distance between the free end portion of the second arm portion 36 and the free end portion of the third arm portion 36 can be prevented from changing due to the stress input from the exhaust manifold 14 side.

  Therefore, a linear distance connecting the two fastening portions of the stay seat 31 and the stay seat 22 at both ends in a series of portions from the first arm portion 34 to the third arm portion 36, and an exhaust gas intake port in the turbine housing 3 By reducing the relative displacement between the stay seat 31 of the side flange and the distance between the stay seat 22 of the exhaust gas discharge port side flange portion, the influence of the external force applied to the turbine housing 3 can be reduced. Therefore, it is possible to suppress the plastic deformation of the turbine housing 3 due to an external force, and it is possible to improve the durability reliability of the turbine housing 3.

  The present invention is not limited to the above-described embodiment, and can be applied to a turbocharger turbine housing such as a gasoline engine or a diesel engine as an internal combustion engine, and does not depart from the gist of the present invention. Of course, various other configurations can be adopted within the scope.

It is a front view which shows the part which attaches a turbocharger to an internal combustion engine via the attachment tool for turbochargers which concerns on embodiment of this invention. It is a schematic sectional drawing which shows the turbine housing part of the turbocharger attached to an internal combustion engine via the attachment tool for turbochargers which concerns on embodiment of this invention. It is a front view which shows the other structural example of the attachment tool for turbochargers which concerns on embodiment of this invention. It is a front view which shows the other structural example of the fixture for turbochargers which concerns on embodiment of this invention. It is a side view of the attachment tool for turbochargers shown in Drawing 1 concerning an embodiment of the invention. FIG. 2 is a plan view of the turbocharger fixture shown in FIG. 1 according to the embodiment of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Turbocharger main body 2 Internal combustion engine 3 Turbine housing 6 Turbine wheel 8 Rotor shaft 11 Exhaust gas intake port 12 Exhaust gas discharge port 13 Case 14 Exhaust manifold 18 Inner shell 19 Outer shell 20 Insertion hole 21 Flange part 22 Exhaust gas discharge port side flange Stay seat 30 of intake part 31 flange flange 31 stay seat 33 of exhaust gas intake side flange 1st arm part 35 2nd arm part 36 3rd arm part 37 Screw parts

Claims (4)

In a fixture for indirectly attaching a turbine housing portion of a turbocharger to a fixing member of an internal combustion engine,
A first arm portion attached to a stay seat on the exhaust gas intake side in the turbine housing;
A second arm portion configured to be integrally continuous with the first arm portion and attached to a stay seat of the fixing member;
Branching from a predetermined intermediate position of a continuous portion from the first arm portion to the second arm portion, which is disposed between the stay seat of the fixing member and the stay seat on the exhaust gas inlet side. Or a continuous structure integrally from the portion attached to the stay seat of the first arm portion, and the whole is integrated into a rigid structure, the free end portion of which is an exhaust gas discharge port A third arm portion attached to a stay seat on the side close to
A turbocharger fitting characterized by comprising:   2. The structure according to claim 1, wherein a rigidity of a portion continuing from the first arm portion to the second arm portion is higher than a rigidity of the third arm portion. Turbocharger fitting.   2. The structure according to claim 1, wherein a rigidity of a portion continuous from the first arm portion to the third arm portion is higher than a rigidity of the second arm portion. Turbocharger fitting.   The turbocharger fitting according to claim 1 or 2, wherein the rigidity of the third arm portion is configured to be lower than the rigidity of the turbine housing portion.

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