JP2020118061A - Casing for rotary machine, and rotary machine - Google Patents

Abstract

To provide a casing for a rotary machine capable of securing accuracy of positioning between housings, and the rotary machine.SOLUTION: A casing for a rotary machine comprises: a first housing including a first flange part and a recess which is positioned radially inside of the first flange part; a second housing including a second flange part and a projection which is positioned radially inside of the second flange part and can be fitted to the recess; and a fastening member for fastening the first flange part and the second flange part. The first housing is positioned in a radial direction with respect to the second housing by a positioning part which is formed by fitting the recess and the projection. The first housing and the second housing are mutually abutted in the positioning part or in a region radially outside of the positioning part in a case where the first and second housings are made closer in the axial direction in a state before the fastening and at a position of the abutment, a load transmission part is formed for transmitting an axial fastening load by the fastening member.SELECTED DRAWING: Figure 1

Description

The present disclosure relates to a rotating machine casing and a rotating machine.

Turbines, electric motors, pumps, engines, turbochargers and the like are known as rotating machines. Such a rotary machine is generally provided with a casing in which a plurality of housings are fastened.

For example, Patent Document 1 discloses a turbocharger that clamps (fastens) a turbine housing and a bearing housing with a fastener (fastening member) with a back plate sandwiched between the turbine housing and the bearing housing. .. This turbocharger is configured such that, in the state after fastening, an elastic force acts in a direction in which the turbine housing side flange portion and the bearing housing side flange portion are separated from each other.

This turbocharger has a gap between the turbine housing side flange portion and the bearing housing side flange portion in a state before fastening. In the state after fastening, they elastically deform so as to contact each other.

International Publication No. 2017/199364

According to the configuration of Patent Document 1, the turbine housing and the bearing housing do not come into contact with each other before the fastening, and therefore the contact state cannot be known unless they are after the fastening. Further, since the turbine housing and the bearing housing are brought into contact with each other by elastic deformation, the axial positioning state changes due to the elastic deformation. With such a configuration in which the housings are brought into contact with each other by elastic deformation, it is difficult to secure the axial positioning accuracy of the housings in the axial direction.

In view of the above-mentioned circumstances, at least one embodiment of the present invention has an object to provide a casing of a rotary machine and a rotary machine capable of ensuring positioning accuracy between housings in the axial direction.

(1) A casing of a rotary machine according to at least one embodiment of the present invention,
A first housing having a first flange portion and a recess located radially inward of the first flange portion;
A second flange portion, and a second housing having a convex portion that is located radially inward of the second flange portion and that can fit into the concave portion;
A fastening member for fastening the first flange portion and the second flange portion,
The first housing is positioned in the radial direction with respect to the second housing by a positioning portion formed by fitting the concave portion and the convex portion,
When the first housing and the second housing are brought close to each other in the axial direction before fastening, the first housing and the second housing are in contact with each other in the positioning portion or a region radially outside the positioning portion, and the fastening member is in a corresponding contact position. Forming a load transmitting portion for transmitting the fastening load in the axial direction.

According to the above configuration (1), the first housing and the second housing are in contact with each other when they are brought close to each other in the axial direction before fastening, and the load transmitting portion is formed at the contact position. That is, the first housing and the second housing contact each other without elastically deforming. Therefore, a change in the axial positioning state due to elastic deformation can be suppressed, and the axial positioning accuracy of the housings can be ensured.

(2) In some embodiments, in the configuration of (1) above,
The load transmission portion is formed by surface contact between mutually parallel surfaces before fastening.

According to the above configuration (2), the first housing and the second housing are in surface contact with each other. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing can be suppressed. Moreover, the sealing effect can be obtained by the contact of the surface contact.

(3) In some embodiments, in the configuration of (1) or (2) above,
Further equipped with a back plate,
The load transmitting portion is located radially outward of the back plate,
The radial distance between the load transmitting portion and the fastening member is smaller than the radial distance between the back plate and the fastening member.

According to the above configuration (3), the heat shield effect of the back plate can be obtained. Even if the casing includes the back plate, the load can be transmitted at a position radially outside the back plate and having a small radial distance from the fastening member. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing can be suppressed.

(4) In some embodiments, in the configuration of (3) above,
The back plate is held between the first housing and the second housing by an urging force that urges the first housing and the second housing in a direction in which they are separated from each other.

In the configuration including the back plate, the fastening load can be transmitted not only at the load transmitting portion but also at the position where the back plate is held. When the fastening load is transmitted at a plurality of positions, there is a risk that the fastening state is not stabilized. However, the above configuration (4) is a configuration that does not assume that the relative positional relationship between the first housing and the second housing changes due to the back plate. In this case, the back plate may be applied with an urging force enough to hold it between the first housing and the second housing. Therefore, according to the above configuration (4), the transmission of the fastening load from the back plate can be reduced, and the fastening load can be mainly transmitted by the load transmitting portion to stabilize the fastening state.

(5) In some embodiments, in the configuration of (4) above,
The radially outer portion of the back plate has a V-shape, a C-shape, or a U-shape (Rectangular U-shaped) in a cross section along the axial direction,
The back plate is held between the first housing and the second housing by the biasing force generated by the elastic deformation of the radially outer portion.

With configuration (5) above, the back plate itself produces an urging force by elastic deformation. Therefore, it is not necessary to newly provide an urging member for urging the back plate, and an increase in the number of parts can be suppressed.

(6) In some embodiments, in the configuration of (1) or (2) above,
Further comprising a seal member provided in a gap between the first housing and the second housing,
The load transmitting portion is located radially outward of the seal member,
The radial distance between the load transmitting portion and the fastening member is smaller than the radial distance between the seal member and the fastening member.

With configuration (6) above, the sealing effect of the seal member can be obtained. Even if the casing is provided with the seal member, the load can be transmitted at a position radially outside the seal member and having a small radial distance from the fastening member. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing can be suppressed.

(7) In some embodiments, in the configuration of (6) above,
The seal member is held in the gap by an urging force that urges the first housing and the second housing in a direction in which they are separated from each other.

In the configuration including the seal member, the fastening load can be transmitted not only at the load transmitting portion but also at the position where the seal member is held. When the fastening load is transmitted at a plurality of positions, there is a risk that the fastening state is not stabilized. However, the above configuration (7) is a configuration that does not assume that the relative positional relationship between the first housing and the second housing is changed by the seal member. Therefore, it is sufficient to apply a biasing force to the seal member so as to hold it between the first housing and the second housing. Therefore, according to the configuration of (7) above, the transmission of the fastening load from the seal member can be reduced, and the fastening load can be transmitted mainly by the load transmitting portion to stabilize the fastening state.

(8) In some embodiments, in any one of the configurations (1) to (7) above,
At least one of the first housing and the second housing is provided with a protrusion that protrudes toward the other and at least a portion of which abuts against the other.
The load transmitting portion is formed by abutting the protrusion and the other.

According to the configuration of (8) above, the formation of the load transmission portion can be ensured by the protrusion.

(9) In some embodiments, in any one of the configurations (1) to (7) above,
One of the first housing and the second housing has a first inclined surface that is inclined with respect to the axial direction, and protrudes toward the other, and at least a part of which is in contact with the other. Is provided,
The other has a second inclined surface parallel to the first inclined surface with which the protrusion is fitted,
The load transmitting portion is formed by contact between the first inclined surface and the second inclined surface.

According to the configuration of (9) above, not only the load transmitting portion is formed by the contact between the first inclined surface and the second inclined surface, but also the contact portion is positioned in the radial direction. A centering effect can also be obtained. As a result, the fastening state between the housings is stabilized, and vibration and noise can be suppressed.

(10) In some embodiments, in any one of the configurations (1) to (8) above,
At least one of the first flange portion and the second flange portion is provided with a protrusion portion that protrudes toward the other and at least a portion of the distal end surface along the radial direction abuts against the other.
The other has a flat surface along the radial direction with which the tip end surface abuts,
The load transmitting portion is formed by contact between the tip end surface and the flat surface.

According to the configuration of (10) above, the load transmitting portion is formed between the first flange portion and the second flange portion at the radially outer position, so that the fastening load can be transmitted more effectively. .. Not only the load transmission effect but also the axial positioning effect between the housings can be obtained. Therefore, the fastening state between the housings is stabilized, and vibration and noise can be suppressed. The load transmitting portion is formed by abutting the tip end surface and the flat surface along the radial direction. According to such a load transmitting portion, unlike the abutting of the flat surfaces not along the radial direction, the fastening load in the axial direction by the fastening member can be transmitted without generating a component force. Therefore, the fastening state between the housings is stabilized.

(11) In some embodiments, in any one of the configurations (8) to (10) above,
At least one of the protrusion and the other has a shot peened surface at least in part,
The load transmitting portion is formed by abutting the shot peened surface.

With configuration (11) above, the fastening state between the housings is stabilized by the frictional force of the shot peened surface, and vibration and noise can be suppressed.

(12) In some embodiments, in any one of the configurations (1) to (11) above,
The load transmission part is formed at a position within the range of the axial width of the fastening member.

When the load transmitting portion is formed at a position outside the range of the axial width of the fastening member, the fastening load may act as a bending moment on the first housing or the second housing, and the fastening load can be effectively applied in the axial direction. It may not be transmitted. In this regard, according to the above configuration (12), the load transmitting portion is formed at a position within the range of the axial width of the fastening member, so that the fastening load can be effectively transmitted in the axial direction.

(13) In some embodiments, in any one of the configurations (1) to (12) above,
The fastening member has an extending portion that extends in the radial direction along the first flange portion and the second flange portion,
At least a part of the load transmitting portion is formed at a position within the radial width of the extending portion.

According to the configuration of (13) above, since the load transmitting portion is located within the range of the radial width of the extending portion of the fastening member, the line of action between the force point of the fastening member and the action point of the load transmitting portion is The gap becomes smaller. Therefore, the fastening load can be directly transmitted.

(14) A rotary machine according to at least one embodiment of the present invention is
The casing according to any one of (1) to (13) above and the impeller are provided.

According to the configuration of (14) above, the rotary machine includes the casing according to any one of (1) to (13) above. Therefore, it is possible to ensure the axial positioning accuracy between the housings of the rotary machine.

According to at least one embodiment of the present invention, there are provided a casing of a rotary machine and a rotary machine capable of ensuring positioning accuracy between housings in the axial direction.

It is a schematic sectional drawing along the axis of rotation of a rotary machine concerning one embodiment of the present invention. It is a figure which shows the structure of V coupling roughly. It is an expanded sectional view showing the fastening state of the casing of the rotary machine concerning one embodiment. It is an expanded sectional view showing the fastening state of the casing of the rotary machine concerning one embodiment. It is an expanded sectional view showing the fastening state of the casing of the rotary machine concerning one embodiment. It is an expanded sectional view showing the fastening state of the casing of the rotary machine concerning one embodiment.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative positions, and the like of the components described as the embodiments or shown in the drawings are not intended to limit the scope of the present invention thereto, but are merely illustrative examples. Absent.
For example, the expression "relative or absolute" such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric", or "coaxial" is strict. In addition to representing such an arrangement, it also represents a state in which the components are relatively displaced by a tolerance or an angle or a distance at which the same function can be obtained.
For example, expressions such as "identical", "equal", and "homogeneous" that indicate that they are in the same state are not limited to a state in which they are exactly equal. It also represents the existing state.
For example, the representation of a shape such as a quadrangle or a cylindrical shape does not only represent a shape such as a quadrangle or a cylindrical shape in a geometrically strict sense, but also an uneven portion or a chamfer within a range in which the same effect can be obtained. The shape including parts and the like is also shown.
On the other hand, the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one element are not exclusive expressions excluding the existence of other elements.

FIG. 1 is a schematic cross-sectional view taken along a rotation axis of a rotary machine 100 according to an embodiment of the present invention. Here, a case where the rotary machine 100 is a turbocharger will be described as an example. The turbocharger is not particularly limited as long as it is a supercharger for forcibly feeding intake air into the internal combustion engine, and may be, for example, a turbocharger for an automobile or a turbocharger for a ship. .. The rotary machine 100 may be a turbine, an electric motor, a pump, an engine, etc. instead of the turbocharger.

As shown in FIG. 1, a rotary machine 100 includes a turbine rotor 2, an impeller 10 connected to the turbine rotor 2 via a shaft 8, a compressor housing 12 housing the impeller 10, and a shaft 8 rotatably supported. And a casing 30 that houses the turbine rotor 2 and the shaft 8. The casing 30 may be configured to include the compressor housing 12 instead of being separated from the compressor housing 12.

The rotary machine 100 is configured to rotationally drive the turbine rotor 2 by exhaust gas of an engine (not shown), compress the air by the rotation of the impeller 10 provided coaxially with the turbine rotor 2, and supply the compressed air to the engine.

The casing 30 includes a first housing 4 that serves as a turbine housing that houses the turbine rotor 2, and a second housing 16 that serves as a bearing housing that houses the bearing device 14.

In this example, the first housing 4 is a turbine housing and the second housing 16 is a bearing housing. However, the first housing 4 and the second housing 16 are not limited to such housings. For example, the second housing 16 may be a turbine housing, and the first housing 4 may be a bearing housing. The first housing 4 and the second housing 16 may be housings not illustrated here.

In the following description, the axial direction of the turbine rotor 2 is simply referred to as “axial direction”, the radial direction of the turbine rotor 2 is simply referred to as “radial direction”, and the circumferential direction of the turbine rotor 2 is simply referred to as “circumferential direction”. A position closer to the rotation axis of the rotating machine 100 is called “radially inside”, and a position further away from the rotation axis of the rotating machine 100 is called “radially outside”.

The first housing 4 has a first flange portion 6 on the outer peripheral side, and has a concave portion 26 located inside the first flange portion 6 in the radial direction. The second housing 16 has a second flange portion 18 facing the first flange portion 6 of the first housing 4 on the outer peripheral side, and has a convex portion 28 located inside the second flange portion 18 in the radial direction. The convex portion 28 is configured to be fittable into the concave portion 26.

The casing 30 also includes a fastening member 20 that fastens the first housing 4 and the second housing 16 by fastening the first flange portion 6 and the second flange portion 18. The fastening member 20 may be, for example, the V coupling shown in FIG. V coupling is also referred to as V band clamp, G coupling and the like.

FIG. 2 schematically shows the structure of V coupling. The V coupling connects one end with a link 56 and the other end with a bolt 58 in a state where the ends of a pair of clamp pieces 52, 54 formed in a semi-circular shape are aligned with each other. The first flange portion 6 (see FIG. 1) and the second flange portion 18 (see FIG. 1) are fastened by tightening with. The V-coupling tightens the bolt 58 as described above, and as a result of exerting a surface pressure toward the center line O over the entire circumferential direction of the V-coupling (clamp pieces 52, 54 ), the first flange. It is configured to sandwich the portion 6 and the second flange portion 18. The fastening member 20 is not limited to the configuration that fastens the first housing 4 and the second housing 16 by sandwiching the first flange portion 6 and the second flange portion 18 like the V coupling. For example, the fastening member 20 may be a bolt, a nut, or the like for bolting the first flange portion 6 and the second flange portion 18 together. The second housing 16 and the compressor housing 12 are connected by a bolt (not shown).

FIG. 3 is an enlarged cross-sectional view showing a fastening state of the casing 30 of the rotary machine 100 according to the embodiment. FIG. 4 is an enlarged cross-sectional view showing a fastening state of the casing 30 of the rotary machine 100 according to the embodiment. FIG. 5: is an expanded sectional view which shows the fastening state of the casing 30 of the rotary machine 100 which concerns on one Embodiment. FIG. 6 is an enlarged cross-sectional view showing a fastening state of the casing 30 of the rotary machine 100 according to the embodiment.

In some embodiments, as shown in FIGS. 3-6, the first housing 4 has a positioning portion 40 formed by the fitting of the recess 26 and the projection 28 in a radial direction with respect to the second housing 16. Be positioned at. The first housing 4 and the second housing 16 are in contact with each other in a region radially outside the positioning portion 40 when they are brought close to each other in the axial direction before fastening. At this abutting position, the load transmitting portion 32 that transmits the axial fastening load of the fastening member 20 is formed.

According to this structure, the first housing 4 and the second housing 16 contact each other when they are brought close to each other in the axial direction before fastening, and the load transmitting portion 32 is formed at the contact position. That is, the first housing 4 and the second housing 16 contact each other without elastically deforming. Therefore, a change in the axial positioning state due to elastic deformation can be suppressed, and the axial positioning accuracy of the housings can be ensured.

According to the knowledge of the inventor of the present application, the fastening state between the housings of the casing 30 is stable in the configuration in which the fastening load in the axial direction of the fastening member 20 is transmitted at the position radially inward of the position positioned in the radial direction. Sometimes it doesn't. As a result, vibration and noise of the casing 30 may occur while the rotary machine 100 is operating. Therefore, it is preferable that the axial fastening load of the fastening member 20 be transmitted at a position where the housings are positioned in the radial direction or a position radially outside of the position.

In this respect, according to the above configuration, the load transmitting portion 32 that transmits the fastening load in the axial direction by the fastening member 20 has a diameter larger than that of the positioning portion 40 that positions the first housing 4 in the radial direction with respect to the second housing 16. It is located in the area outside the direction. Therefore, the fastening state between the housings of the casing 30 is stabilized, and the vibration and noise of the casing 30 can be suppressed.

In some embodiments, as shown in FIGS. 3 to 6, the load transmitting portion 32 is formed by surface contact between mutually parallel surfaces in a state before fastening.

According to this structure, the first housing 4 and the second housing 16 are in surface contact with each other. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing 30 can be suppressed. Moreover, the sealing effect can be obtained by the contact of the surface contact. In this case, the casing 30 may be configured not to include the seal member 34 and the back plate 24, which will be described later, or may be configured to obtain a sealing effect by abutting surface contact.

The term “parallel” here is not limited to strict parallel, and may be any shape that can be said to be surface contact. Therefore, for example, “parallel” includes a case where there is a slight angle difference of 10 degrees or less between the surfaces and a case where a part of the surfaces is not parallel but the other parts are parallel.

In some embodiments, as shown in FIGS. 3, 4 and 6, the casing 30 has an annular shape provided along the back surface of the turbine rotor 2 between the turbine rotor 2 and the second housing 16. The back plate 24 is provided. The back plate 24 is held between the first housing 4 and the second housing 16. The back plate 24 functions as a heat shield plate for suppressing heat transfer from the high temperature exhaust gas flowing in the first housing 4 to the bearing device 14 side and improving the sealing property. As shown in FIGS. 3, 4, and 6, the load transmitting portion 32 is located radially outside the back plate 24. The radial distance between the load transmitting portion 32 and the fastening member 20 is smaller than the radial distance between the back plate 24 and the fastening member 20.

With this configuration, the heat shield effect of the back plate 24 can be obtained. Even if the casing 30 includes the back plate 24, the load can be transmitted at a position radially outward of the back plate 24 and close to the fastening member 20. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing 30 can be suppressed.

The casing 30 may not have the back plate 24 as shown in FIG. Further, in FIG. 6, the back plate 24 is shown by an imaginary line. This means that the back plate 24 is not essential as long as the sealing effect can be sufficiently obtained by the surface contact abutment as described above.

In some embodiments, as shown in FIGS. 3, 4 and 6, the back plate 24 is separated from the first housing 4 by an urging force that urges the first housing 4 and the second housing 16 in the direction of separating them. It may be held between the second housing 16.

Generally, in the configuration including the back plate 24, the fastening load can be transmitted not only at the load transmission portion 32 but also at the position where the back plate 24 is held. When the fastening load is transmitted at a plurality of positions, there is a risk that the fastening state is not stabilized. However, the above-described configuration does not assume that the relative positional relationship between the first housing and the second housing is changed by the back plate 24. In this case, the back plate 24 may be applied with a biasing force that can be held between the first housing 4 and the second housing 16. Therefore, according to the above configuration, the transmission of the fastening load from the back plate 24 can be reduced, and the fastening load can be mainly transmitted by the load transmitting portion 32 to stabilize the fastening state.

In some embodiments, as shown in FIGS. 3, 4 and 6, the radially outer portion of the back plate 24 has a rectangular U-shaped section in a cross section along the axial direction. doing. The radially outer portion of the back plate 24 may have a V-shape or a C-shape in a cross section along the axial direction. In this case, the back plate 24 is held between the first housing 4 and the second housing 16 by the urging force generated by the elastic deformation of the radially outer portion.

According to this structure, the back plate 24 itself produces an urging force by elastic deformation. Therefore, it is not necessary to newly provide an urging member for urging the back plate 24, and an increase in the number of parts can be suppressed.

In some embodiments, the casing 30 may include a seal member 34 provided in a gap g between the first housing 4 and the second housing 16 as shown in FIG. 5, for example. In this case, in the casing 30, the load transmitting portion 32 is located radially outside the seal member 34, and the radial distance between the load transmitting portion 32 and the fastening member 20 is equal to the diameter of the seal member 34 and the fastening member 20. It is configured to be smaller than the directional distance.

With this configuration, the sealing effect of the seal member 34 can be obtained. Even if the casing 30 includes the seal member 34, the load can be transmitted at a position radially outside the seal member 34 and having a small radial distance from the fastening member 20. Therefore, the fastening state between the housings is stabilized, and the vibration and noise of the casing 30 can be suppressed.

In some embodiments, the seal member 34 may be held in the gap g by a biasing force that biases the first housing 4 and the second housing 16 in the direction of separating the seal member 34, for example, as shown in FIG. 5. ..

Generally, according to the configuration including the seal member 34, the fastening load can be transmitted not only at the load transmission portion 32 but also at the position where the seal member 34 is held. When the fastening load is transmitted at a plurality of positions, there is a risk that the fastening state is not stabilized. However, the above-described configuration does not assume that the relative positional relationship between the first housing 4 and the second housing 16 is changed by the seal member 34. Therefore, it is sufficient to apply a biasing force to the seal member 34 such that the seal member 34 is held between the first housing 4 and the second housing 16. Therefore, according to the above configuration, the transmission of the fastening load from the seal member 34 can be reduced, and the fastening load can be transmitted mainly by the load transmitting portion 32, and the fastening state can be stabilized.

In some embodiments, at least one of the first housing 4 and the second housing 16 is provided with a protrusion 36 that protrudes toward the other and at least a portion of which abuts the other, and the load transfer portion 32 is , The protrusion 36 and the other contact. For example, in FIGS. 3 to 6, the first housing 4 is provided with the projecting portion 36, and the projecting portion 36 contacts the second housing 16 to form the load transmitting portion 32. The protrusion 36 is continuously provided along the circumferential direction.

The projecting portion 36 may be provided in the second housing 16 so as to abut the first housing 4. The protrusion 36 may be provided in each of the first housing 4 and the second housing 16, and may be configured such that they abut each other. Further, the protruding portion 36 is not limited to the configuration that is continuously provided along the circumferential direction, and may be provided intermittently along the circumferential direction.

According to this structure, the protrusion 36 can ensure the formation of the load transmission portion 32.

In some embodiments, one of the first housing 4 and the second housing 16 has a first inclined surface 42 that is inclined with respect to the axial direction, and protrudes toward the other and is at least partially Is provided with a protrusion 36 that abuts the other, and the other has a second inclined surface 44 that is parallel to the first inclined surface 42 into which the protrusion 36 is fitted. For example, in FIGS. 3 and 4, the first housing 4 is provided with the protrusion 36 having the first inclined surface 42, and the second housing 16 is provided with the first inclined surface 42 parallel to the first inclined surface 42 into which the protrusion 36 is fitted. It has two inclined surfaces 44. The load transmitting portion 32 is formed by the contact between the first inclined surface 42 and the second inclined surface 44.

According to this structure, the contact between the first inclined surface 42 and the second inclined surface 44 not only forms the load transmission portion 32 but also positions the contact portion in the radial direction. The effect can also be obtained. As a result, the fastening state between the housings is stabilized, and vibration and noise can be suppressed.

In some embodiments, at least one of the first flange portion 6 and the second flange portion 18 projects toward the other, and at least a portion of the distal end surface 46 along the radial direction abuts the other. The part 36 is provided, and the other has a flat surface 48 along the radial direction with which the tip surface 46 abuts. The load transmitting portion 32 is formed by contact between the tip end surface 46 and the flat surface 48. For example, in FIGS. 5 and 6, the first housing 4 is provided with the protrusion 36 having the distal end surface 46 extending in the radial direction. The second housing 16 also has a flat surface 48 along the radial direction with which the tip end surface 46 abuts. The load transmitting portion 32 is formed by the contact between the tip end surface 46 and the flat surface 48.

According to this configuration, the load transmission portion 32 is formed between the first flange portion 6 and the second flange portion 18 which are located at the radially outer position, so that the fastening load can be transmitted more effectively. Further, in the load transmitting portion 32, not only the load transmitting effect but also the axial positioning effect between the housings can be obtained. Therefore, the fastening state between the housings is stabilized, and vibration and noise can be suppressed. The load transmitting portion 32 is formed by abutting the tip end surface 46 and the flat surface 48 along the radial direction. According to such a load transmitting portion 32, unlike the contact between the planes that do not extend in the radial direction, the axial fastening load of the fastening member 20 can be transmitted without generating a component force. Therefore, the fastening state between the housings is stabilized.

In some embodiments, the protrusion 36 has a shot peened surface at least in part, and the load transfer portion 32 is formed by abutting the shot peened surface. For example, in the example shown in FIG. 6, the tip end surface 46 of the protrusion 36 is shot peened.

Note that the shot peened surface may be provided on the other housing at a position where the projection 36 abuts instead of the projection 36 provided on the one housing. For example, in the example shown in FIG. 6, the second housing 16 may be provided at a position where the tip surface 46 of the protrusion 36 abuts instead of the tip surface 46. Further, the shot peening processed surface may be provided at both the protruding portion 36 provided on one housing and the position where the protruding portion 36 abuts on the other housing. That is, the shot peened surface may be provided on at least one of the first housing 4 and the second housing 16 at the position of the load transmission portion 32.

With this configuration, the frictional force of the shot peened surface stabilizes the fastening state between the housings, and vibration and noise can be suppressed.

In some embodiments, as shown in FIGS. 3 to 6, the load transmission portion 32 is formed at a position within the range of the axial width W1 of the fastening member 20.

When the load transmitting portion 32 is formed at a position outside the range of the axial width W1 of the fastening member 20, the fastening load may act as a bending moment on the first housing 4 or the second housing 16, and the fastening in the axial direction is performed. The load may not be transmitted effectively. In this regard, according to the above configuration, since the load transmitting portion 32 is formed at a position within the range of the axial width W1 of the fastening member 20, the fastening load can be effectively transmitted in the axial direction.

In some embodiments, as shown in FIGS. 3-6, the fastening member 20 has an extending portion 50 that extends radially along the first flange portion 6 and the second flange portion 18. There is. At least a part of the load transmitting portion 32 is formed at a position within the radial width W2 of the extending portion 50.

According to this configuration, the load transmitting portion 32 is located within the range of the radial width W2 of the extending portion 50 of the fastening member 20, so that the action point of the fastening member 20 and the action point of the load transmitting portion 32 act. The deviation of the line becomes small. Therefore, the fastening load can be directly transmitted.

The present invention is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these forms as appropriate.

For example, in the example shown in FIGS. 3 to 6, the positioning portion 40 for positioning in the radial direction is a portion where the convex portion 28 is fitted into the concave portion 26, and the convex portion 28 is not the protruding portion 36. However, the protrusion 36 may be configured to also serve as the protrusion 28 that forms the positioning portion 40. For example, as shown in FIGS. 3 and 4, it is possible to perform the radial positioning only by contacting the first inclined surface 42 and the second inclined surface 44 of the protruding portion 36. In this case, the load transmitting portion 32 is formed at the contact position between the first inclined surface 42 of the protruding portion 36 also serving as the convex portion 28 and the second inclined surface 44 also serving as the concave portion 26. That is, the load transmission portion 32 is formed on the positioning portion 40.

Even with such a configuration, the fastening state between the housings of the casing 30 is stabilized and vibration and noise of the casing 30 are reduced compared to a configuration in which the fastening load is transmitted at a position radially inward of the position for radial positioning. Can be suppressed. That is, when the first housing 4 and the second housing 16 are brought close to each other in the axial direction in the state before fastening, the first housing 4 and the second housing 16 come into contact with each other in the positioning portion 40 or a region radially outside the positioning portion 40, and the load is applied at the corresponding contact position. The transmission part 32 may be formed.

The shot peening processed surface described with reference to FIG. 6 may be provided on at least a part (for example, the first inclined surface 42 or the tip end surface 46) of the protrusion 36 shown in FIGS. 3 to 5, and the shot peening thereof. The load transmission part 32 may be formed by abutting the processed surface. Further, a shot peening processed surface may be provided at a position where the protrusion 36 abuts, for example, a shot peening processed surface may be provided on the second inclined surface 44.

The back plate 24 and the seal member 34 are not limited to the examples shown in FIGS. 3 to 6 as long as they are located radially inward of the load transmission portion 32, and may be provided at other positions. Further, in the configurations shown in FIGS. 3 to 6, the configuration may be modified to include the seal member 34 instead of the back plate 24, or may be modified to include the back plate 24 instead of the seal member 34. ..

In the example shown in FIGS. 3 and 4, the inclined surface on the radially outer side of the protrusion 36 forms the first inclined surface 42. However, the inclined surface on the radially inner side of the protruding portion 36 may be configured to form the first inclined surface 42. In this case, an inclined surface parallel to the radially inner inclined surface of the protruding portion 36 is provided as the second inclined surface 44 in the other housing having no protruding portion 36.

2 turbine rotor 4 first housing (turbine housing)
6 1st flange part 8 Shaft 10 Impeller 12 Compressor housing 14 Bearing device 16 2nd housing (bearing housing)
18 2nd flange part 20 Fastening member 22 Contact part 24 Back plate 26 Convex part 28 Recessed part 30 Casing 32 Load transfer part 34 Seal member 36 Projection part 40 Positioning part 42 1st inclined surface 44 2nd inclined surface 46 Tip surface 48 Flat surface 50 Extension parts 52, 54 Clamp piece 56 Link 58 Bolt 100 Rotating machine O Center line g Gap W1 Axial width W2 Radial width

Claims (14)

A first housing having a first flange portion and a concave portion located radially inward of the first flange portion;
A second flange portion, and a second housing having a convex portion positioned radially inside the second flange portion and capable of being fitted into the concave portion;
A fastening member that fastens the first flange portion and the second flange portion,
The first housing is positioned in the radial direction with respect to the second housing by a positioning portion formed by fitting the concave portion and the convex portion,
When the first housing and the second housing are brought close to each other in the axial direction before fastening, the first housing and the second housing are in contact with each other in the positioning portion or a region radially outside the positioning portion, and the fastening member is in the position of the corresponding contact. A casing of a rotary machine that forms a load transmitting portion that transmits a fastening load in the axial direction. The casing for a rotary machine according to claim 1, wherein the load transmission portion is formed by abutting mutually parallel surfaces before fastening. Further equipped with a back plate,
The load transmitting portion is located radially outward of the back plate,
The casing of a rotary machine according to claim 1, wherein a radial distance between the load transmitting portion and the fastening member is smaller than a radial distance between the back plate and the fastening member. The rotary machine according to claim 3, wherein the back plate is held between the first housing and the second housing by an urging force that urges the first housing and the second housing in a direction in which the first housing and the second housing are separated from each other. Casing. The radially outer portion of the back plate has a V-shape, a C-shape, or a U-shape in a cross section along the axial direction,
The casing of the rotary machine according to claim 4, wherein the back plate is held between the first housing and the second housing by the biasing force generated by elastic deformation of the radially outer portion. Further comprising a seal member provided in a gap between the first housing and the second housing,
The load transmitting portion is located radially outward of the seal member,
The casing of a rotary machine according to claim 1, wherein a radial distance between the load transmitting portion and the fastening member is smaller than a radial distance between the seal member and the fastening member. The casing of the rotary machine according to claim 6, wherein the seal member is held in the gap by an urging force that urges the first housing and the second housing in a direction in which the first housing and the second housing are separated from each other. At least one of the first housing and the second housing is provided with a protrusion that protrudes toward the other and at least a portion of which abuts against the other.
The casing for a rotary machine according to claim 1, wherein the load transmitting portion is formed by contact between the protrusion and the other. One of the first housing and the second housing has a first inclined surface that is inclined with respect to the axial direction, and protrudes toward the other, and at least a part of which is in contact with the other. Is provided,
The other has a second inclined surface parallel to the first inclined surface with which the protrusion is fitted,
The casing for a rotary machine according to any one of claims 1 to 7, wherein the load transmitting portion is formed by contact between the first inclined surface and the second inclined surface. At least one of the first flange portion and the second flange portion is provided with a protrusion portion that protrudes toward the other and at least a portion of the distal end surface along the radial direction abuts against the other.
The other has a flat surface along the radial direction with which the tip end surface abuts,
The casing for a rotary machine according to claim 1, wherein the load transmitting portion is formed by contact between the tip end surface and the flat surface. At least one of the protrusion and the other has a shot peened surface at least in part,
The casing for a rotary machine according to any one of claims 8 to 10, wherein the load transmitting portion is formed by abutting the shot peened surface. The casing for a rotary machine according to claim 1, wherein the load transmitting portion is formed at a position within a range of an axial width of the fastening member. The fastening member has an extending portion that extends in the radial direction along the first flange portion and the second flange portion,
The casing for a rotary machine according to claim 1, wherein at least a part of the load transmitting portion is formed at a position within a range of a radial width of the extending portion. A rotary machine comprising the casing according to any one of claims 1 to 13 and an impeller.

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