JP7154372B2 - Radial compressor casing and radial compressor - Google Patents

Description

The present invention relates to a radial compressor casing and a radial compressor.

A radial compressor is known as one type of compressor. In this radial compressor, the gas discharged from the impeller is introduced into a scroll portion having a helically formed flow path, guided in the circumferential direction, and discharged. The outer dimensions of the scroll portion gradually increase from the winding start side toward the discharge side.

Here, like the radial compressors described in Cited Documents 1 and 2, casings of radial compressors used in automobile turbochargers, for example, are sometimes made of resin for weight reduction and the like.

WO2017/168767

However, since resin has a lower thermal conductivity than metal such as aluminum, it is difficult to sufficiently dissipate heat from the casing when the casing is made of resin as in the compressor of Patent Document 1. Therefore, the casing may become hot and the scroll portion of the casing may be greatly deformed due to thermal expansion. Further, the scroll portion is subjected to radially outward pressure from the fluid flowing through the flow path.
In the compressor of Patent Document 1, the flow path is formed by joining the first main body portion and the second main body portion of the casing. Therefore, due to the thermal expansion and the pressure of the fluid, stress is generated in the circumferential direction at the joint between the first main body and the second main body so that the first main body and the second main body separate from each other. The parts may crack and create a gap between the first body part and the second body part. This can result in reduced fatigue strength of the compressor.
Furthermore, when the fluid in the flow path enters the gap between the first body part and the second body part, the first body part and the second body part try to separate further, and the gap increases, resulting in pressure loss of the fluid. It gets bigger.

SUMMARY OF THE INVENTION Accordingly, the present invention provides a casing for a radial compressor capable of improving performance while improving fatigue strength, and a radial compressor.

A casing of a radial compressor according to a first aspect of the present invention has a tubular shape extending along a rotation axis of an impeller and opening in the direction of the rotation axis, an intake section for introducing fluid into the impeller, and the intake air. and a resin scroll portion forming a flow path extending annularly around the rotation axis on the outer peripheral side of the impeller, and integrally formed at one end of the scroll portion in the circumferential direction of the impeller. a discharge portion that extends along and opens and discharges the fluid from the flow path, wherein the scroll portion includes a first body portion arranged on one side of the direction of the rotation axis, and the first body portion a second body portion disposed on the other side of the direction of the rotation axis with respect to the portion; and joining the first body portion and the second body portion in the direction of the rotation axis, and and a joint portion located within a range of the direction of the rotation axis, wherein one of the first body portion and the second body portion has a radial direction with respect to the rotation axis rather than the joint portion. extending inwardly from one of said first body portion and said second body portion to the other beyond said junction and forming a portion of the inner surface of said flow path; A convex portion is provided, and the other of the first main body portion and the second main body portion is provided with a concave portion that is recessed from an inner surface of the flow path and engages with the convex portion, and the first The main body has a first facing surface facing the direction of the rotation axis, the second main body has a second facing surface that is in surface contact with the first facing surface, and the first main body has a first annular recess recessed from the first facing surface in the direction of the rotation axis and extending annularly around the rotation axis; and the second body portion is provided with the first annular recess. A second annular recess is provided that is recessed in the direction of the rotation axis from the second opposing surface at a position corresponding to the second opposing surface and extends annularly around the rotation axis, and the joint portion includes the first annular recess and the second It is a resin member arranged in the space formed by the annular recess .

According to such a casing, there is provided a convex portion that extends in the direction of the rotation axis beyond the joint portion and forms the inner surface of the flow path of the scroll portion. Therefore, even if a crack occurs in the joint portion due to stress in the circumferential direction, the convex portion is pressed radially outward by the pressure of the fluid so as to close the crack. As a result, the crack growth rate can be reduced. Also, even if a crack were to occur, since the protrusion is pressed radially outward, the crack would not go radially outward, but rather would propagate toward the base of the protrusion in the direction of the rotation axis. Cracks do not tend to propagate in the joints, which are weaker than the main body and the second main body, but tend to propagate toward the inside of the strong first main body and the second main body. This can also reduce the growth rate of cracks.
In addition, since the convex portion is pressed radially outward by the pressure of the fluid, the gap between the convex portion and the concave portion tends to close, so that the fluid can be prevented from entering the gap. Therefore, it is possible to reduce the pressure loss of the fluid in the flow path.
Furthermore, the junction is located within the direction of the axis of rotation along which the flow path is formed. Therefore, the joint portion is arranged close to the central position in the direction of the rotation axis in the flow path of the scroll portion. As a result, the influence of the circumferential stress due to the pressure of the fluid increases. However, even in such a case, the projections described above can suppress the propagation of cracks, so that the effect of suppressing damage to the casing can be obtained.
Moreover, by using a resin member for the joining portion, the first body portion and the second body portion can be joined more firmly. Furthermore, since the joining portion can be provided using die slide injection to join the first main body portion and the second main body portion, manufacturing of the casing can be facilitated.

Further, in the above casing, the convex portion has a convex outer surface facing outward in the radial direction, the outer surface of the convex portion is provided with a lateral convex portion projecting outward in the radial direction, and the first main body The other of the portion and the second body portion has an inner surface facing the outer surface of the protrusion, and the inner surface has a lateral recess that is recessed outward in the radial direction and engageable with the lateral protrusion. may be provided.

A lateral protrusion is provided on the outer surface of the protrusion, and a lateral recess engageable with the lateral protrusion is provided on the inner surface facing the outer surface of the protrusion. It is possible to suppress relative movement in the direction of . Therefore, the first body portion and the second body portion can mutually restrict deformation in the direction of the rotation axis, thereby improving the fatigue strength of the casing and avoiding a decrease in fluid compression efficiency due to the deformation of the casing. can.

Further, in the above casing, the other of the first main body portion and the second main body portion is arranged outside in the radial direction with respect to the convex portion, and the first main body portion and the second main body portion are arranged outside the convex portion. and an outer convex portion projecting toward the one from the other of the portions, and the outer convex portion is engaged with the one of the first main body portion and the second main body portion. A possible outer recess may be provided.

By providing the outer convex portion in addition to the convex portion in this manner, the first main body portion and the second main body portion are joined by the joint portion so as to fit together in the direction of the rotation axis. Therefore, it is possible to avoid mutual displacement in the radial direction with respect to the rotation axis, and it is possible to reliably arrange the first body portion and the second body portion coaxially during assembly and operation. As a result, it is possible to improve the compression efficiency of the fluid.

Further, the casing of the radial compressor according to one aspect of the present invention has a cylindrical shape extending along the rotation axis of the impeller and opening in the direction of the rotation axis. and a resin scroll portion forming a flow path extending annularly around the rotation axis on the outer peripheral side of the impeller, and integrally provided at one end of the scroll portion in the circumferential direction of the impeller. a discharge portion that extends along and opens and discharges the fluid from the flow path, wherein the scroll portion includes a first main body portion disposed on one side of the direction of the rotation axis; and the first main body portion. A second main body portion disposed on the other side of the direction of the rotation axis, and the first main body portion and the second main body portion are joined in the direction of the rotation axis, and the flow path is formed a joint located outside the range in the direction of the rotation axis, wherein one of the first main body and the second main body is radially inside the joint with respect to the rotation axis. an annular projection centered on the rotation axis that extends from one of the first body portion and the second body portion toward the other beyond the joint portion and forms a portion of the inner surface of the flow path; and the other of the first body portion and the second body portion is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion, and the first body portion is , a first opposing surface facing the direction of the rotation axis, the second body portion having a second opposing surface that is in surface contact with the first opposing surface, the first body portion having the second A first annular recess that is recessed from one opposing surface in the direction of the rotation axis and extends annularly around the rotation axis is provided, and the second body portion corresponds to the position where the first annular recess is provided. A second annular recess is provided that is recessed in the direction of the rotation axis from the second opposing surface at a position and extends annularly about the rotation axis, and the joint portion is formed by the first annular recess and the second annular recess. It is a resin member arranged in a space formed by.

According to such a casing, even if a crack occurs in the joint portion due to circumferential stress caused by the pressure of the fluid, the convex portion is pressed radially outward by the pressure of the fluid so as to close the crack. can reduce the rate of progression of In addition, even if a crack were to occur, since the convex portion is pressed radially outward, the crack would not go radially outward, but would tend to propagate toward the base of the convex portion in the direction of the rotation axis. It tries to progress toward the inside of the first body portion and the second body portion, which are stronger than the first body portion and the second body portion. This can also reduce the growth rate of cracks.
In addition, since the convex portion is pressed radially outward by the pressure of the fluid, the gap between the convex portion and the concave portion tends to close, so that the fluid can be prevented from entering the gap. Therefore, it is possible to reduce the pressure loss of the fluid in the flow path.
Furthermore, the junction is located outside the direction of the axis of rotation in which the flow path is formed. For this reason, the impact of heat from the compressed fluid and the impact of pressure from the fluid are less likely to reach the joints, making it possible to suppress the occurrence of cracks in the joints due to stress in the circumferential direction, thereby preventing damage to the casing. A suppressing effect is obtained.

Further, the casing of the radial compressor according to one aspect of the present invention has a cylindrical shape extending along the rotation axis of the impeller and opening in the direction of the rotation axis, an intake section for introducing fluid to the impeller,
a scroll portion made of resin that communicates with the intake portion and forms a flow path that extends annularly around the rotation axis on the outer peripheral side of the impeller;
a discharge part integrally provided at one end of the scroll part, extending along the circumferential direction of the impeller and having an opening for discharging the fluid from the flow path;
with
The scroll part
a first body portion arranged in one direction of the rotation axis;
a second body portion arranged on the other side of the direction of the rotation axis with respect to the first body portion; a joint located outside the range of directions of the axis of rotation in which the path is formed, wherein one of the first body portion and the second body portion has more of the axis of rotation than the joint; extending radially inwardly from one of the first body portion and the second body portion toward the other beyond the junction and forming a portion of the inner surface of the flow path. The other of the first main body portion and the second main body portion is provided with a concave portion that is recessed from the inner surface of the flow path and engages with the convex portion, and the The convex portion has a convex outer surface facing outward in the radial direction, the outer surface of the convex portion is provided with a lateral convex portion projecting outward in the radial direction, and the first body portion and the second body portion are provided. The other of the two has an inner surface facing the outer surface of the convex portion, and the inner surface is provided with a lateral recess that is recessed outward in the radial direction and engageable with the lateral protrusion, and the first The other of the main body portion and the second main body portion is arranged outside in the radial direction with respect to the convex portion, and the projection from the other of the first main body portion and the second main body portion to the An outer convex portion protruding toward one side is further provided, and the one of the first body portion and the second body portion is provided with an outer concave portion with which the outer convex portion can be engaged. .

According to such a casing, as described above, it is possible to reduce the propagation speed of cracks by means of the projections, and to reduce the pressure loss of the fluid in the flow path. Furthermore, since the joint is positioned outside the direction of the rotation axis in which the flow path is formed, the joint is less likely to be affected by heat from the compressed fluid and from the pressure from the fluid. Therefore, it is possible to suppress the generation of cracks at the joint portion due to the circumferential stress caused by the pressure of the fluid, thereby obtaining the effect of suppressing damage to the casing.
Furthermore, as described above, the first main body portion and the second main body portion can mutually restrict deformation in the direction of the rotation axis by the lateral protrusions, thereby improving the fatigue strength of the casing and preventing deformation of the casing. It is possible to avoid the accompanying reduction in fluid compression efficiency. Further, as described above, the outer convex portion allows the first main body portion and the second main body portion to be arranged coaxially, thereby improving the compression efficiency of the fluid.

A radial compressor according to an aspect of the present invention includes an impeller, a rotating shaft fitted with the impeller and rotating together with the impeller, and the casing provided to cover the impeller.

In such a radial compressor, even if a crack occurs in the joint portion due to circumferential stress generated by the pressure of the fluid, the propagation speed of the crack can be reduced by the convex portion by providing the above-described casing. In addition, since the gap between the convex portion and the concave portion tends to close due to the pressure of the fluid, it is possible to prevent the fluid from entering the gap and reduce the pressure loss of the fluid in the flow path.

In the casing of the radial compressor and the radial compressor described above, the provision of the projections on the first main body or the second main body makes it possible to improve the performance while improving the fatigue strength.

1 is an overall perspective view of a radial compressor according to a first embodiment of the invention; FIG. 1 is a vertical cross-sectional view of a main part of a casing of a radial compressor according to a first embodiment of the invention; FIG. FIG. 4 is a vertical cross-sectional view of a main part of a casing of a radial compressor according to a first modified example of the first embodiment of the present invention; FIG. 7 is a vertical cross-sectional view of a main portion of a casing of a radial compressor according to a second modified example of the first embodiment of the present invention; FIG. 6 is a vertical cross-sectional view of a main part of a casing of a radial compressor according to a second embodiment of the invention; FIG. 7 is a vertical cross-sectional view of a main part of a casing of a radial compressor according to a third embodiment of the invention; FIG. 11 is a vertical cross-sectional view of main parts of a casing of a radial compressor according to a fourth embodiment of the present invention;

[First embodiment]
A radial compressor 1 according to an embodiment of the present invention will be described below.
A radial compressor 1 (hereinafter simply referred to as compressor 1) is, for example, a compressor for a turbocharger mounted on a vehicle.
As shown in FIG. 1, the compressor 1 is provided so as to cover an impeller 2, a rotating shaft 3 that rotates about a rotation axis O integrally with the impeller 2 by fitting the impeller 2, and the impeller 2. A casing 4 is provided.

Next, the casing 4 will be explained.
The casing 4 includes an intake portion 5 for introducing a gas G (fluid) such as air into the impeller 2 , a discharge portion 6 for discharging the gas G flowing out from the impeller 2 , and an intake portion 5 . A scroll portion 7 communicating with the discharge portion 6 is provided.

The intake part 5 is arranged in one direction of the rotation axis O with respect to the impeller 2, extends in the direction of the rotation axis 3 line, and has a cylindrical shape opening in the other direction of the rotation axis O. As shown in FIG. The intake part 5 sucks the gas G toward the impeller 2 from one side in the direction of the rotation axis O, and introduces the gas G toward a flow path (not shown) inside the impeller 2 . The material of the intake portion 5 is, for example, a resin such as thermoplastic (for example, PPS (polyphenylene sulfide), PPA (polyphthalamide), PA9T, PA46, PA6T (polyamide), PBT (polybutylene terephthalate), etc.). be.

The scroll portion 7 is arranged on the outer peripheral side of the impeller 2 and the intake portion 5 . The scroll portion 7 has a flow path FC annularly extending in the circumferential direction of the impeller 2 and the rotating shaft 3 . The gas G introduced from the intake portion 5 flows through the flow path in the impeller 2 and is compressed, and then flows through the flow path FC of the scroll portion 7 . The scroll portion 7 is made of the same resin as the intake portion 5 . The flow passage FC of the scroll portion 7 has a circular cross section perpendicular to the circumferential direction, and the flow passage cross-sectional area gradually expands toward one side in the circumferential direction. As a result, the outer dimensions of the scroll portion 7 gradually increase toward the discharge portion 6 in one direction in the circumferential direction. The scroll portion 7 may be, for example, a resin injection molded product integrated with the air intake portion 5 , or may be manufactured separately from the air intake portion 5 and joined to the air intake portion 5 .

The discharge portion 6 has a cylindrical shape and is provided integrally with one end portion in the circumferential direction of the scroll portion 7. The discharge portion 6 extends in the tangential direction of the scroll portion 7 along the circumferential direction and opens so that the gas G flows through the flow path FC. Dispense from The discharge part 6 is also made of the same resin as the scroll part 7 and the intake part 5 . The discharge part 6 may be, for example, a resin injection-molded product integrated with the scroll part 7 , or may be manufactured separately from the scroll part 7 and joined to the scroll part 7 .

Next, the scroll section 7 will be described in detail with reference to FIG.
The scroll portion 7 is arranged on the other side of the first main body portion 11 and the first main body portion 11 in the direction of the rotation axis O, and forms the inner surface 7a of the flow channel FC together with the first main body portion 11. 12 and a joint portion 13 provided between the first body portion 11 and the second body portion 12 .

The first body portion 11 has an annular shape centered on the rotation axis O. As shown in FIG. The first body portion 11 has an annular convex portion 11a extending protruding from the first body portion 11 in the other direction of the rotation axis O and forming a part of the inner surface 7a of the flow channel FC. is provided. Accordingly, the convex portion 11a is provided in contact with the flow channel FC. The first main body portion 11 is formed with a first opposing surface 11b that faces the other direction of the rotation axis O and is in contact with the convex portion 11a, radially outward from the convex portion 11a. An outer surface 11c of the protrusion 11a facing radially outward is an inclined surface that slopes radially inward toward the other direction of the rotation axis O. As shown in FIG.

The second body portion 12 has an annular shape centered on the rotation axis O. As shown in FIG. The second body portion 12 is provided with an annular recess 12a which is recessed radially outward from the inner surface 7a of the flow channel FC and into which the protrusion 11a is inserted and engaged with the protrusion 11a. Therefore, the inner surface 12c of the concave portion 12a, which faces radially inward, is an inclined surface which is inclined radially inward toward the other direction of the rotation axis O corresponding to the outer surface 11c of the convex portion. The second main body portion 12 is formed with a second opposing surface 12b that faces one direction of the rotation axis O and is in contact with the recessed portion 12a and radially outwardly of the recessed portion 12a. The second opposing surface 12b faces the first opposing surface 11b in the direction of the rotation axis O and is in surface contact with the first opposing surface 11b.

The joint portion 13 is provided on the first opposing surface 11b and the second opposing surface 12b at a radially outer position relative to the convex portion 11a and the concave portion 12a. Therefore, the convex portion 11 a is provided radially inside the joint portion 13 so as to be in contact with the joint portion 13 . Further, the convex portion 11 a extends beyond the joint portion 13 in the other direction of the rotation axis O toward the second main body portion 12 . The joining portion 13 is configured such that the first main body portion 11 and the second main body portion 12 are joined by vibration fusion or ultrasonic wave while the first opposing surface 11b and the second opposing surface 12b are opposed to each other in the direction of the rotation axis O, for example. It is formed as a result of joining using a method such as fusion bonding. Accordingly, the joint portion 13 is formed in an annular shape around the rotation axis O over the entire first opposing surface 11b and the second opposing surface 12b, and is made of the same resin material as the first main body portion 11 and the second main body portion 12.

The joint portion 13 of the present embodiment is arranged along an imaginary line X passing through the center position of the flow channel FC of the scroll portion 7 in the direction of the rotation axis O and extending in the radial direction. However, the joint portion 13 need only be positioned within the range in the direction of the rotation axis O along which the flow path FC is formed, and does not necessarily need to be arranged along the imaginary line X described above.

Since the joint portion 13 is provided only between the first opposing surface 11b and the second opposing surface 12b, it is not provided between the convex portion 11a and the concave portion 12a. As a result, the convex portion 11a and the concave portion 12a are in a state of being close to each other or in contact with each other, but not joined to each other.

In the compressor 1 of the present embodiment described above, the convex portion 11a extending in the direction of the rotation axis O and forming the inner surface 7a of the flow passage FC of the scroll portion 7 is provided on the first body portion 11 . Therefore, even if a crack C (see FIG. 2) occurs in the joint portion 13 due to stress in the circumferential direction, the convex portion 11a is pressed radially outward by the pressure of the gas G so as to close the crack C. As shown in FIG. As a result, the propagation speed of the crack C can be reduced.

In addition, even if a crack C occurs, the crack C does not go radially outward because the convex portion 11a is pressed radially outward, and is formed between the joint portion 13 and the convex portion 11a at the base of the convex portion 11a. At , it tries to progress toward one of the directions of the rotation axis along the convex outer surface 11c. For this reason, cracks C do not occur in the joint portion 13, which is weaker than the first main body portion 11 and the second main body portion 12, and the cracks C are formed by the first main body portion 11 and the second main body portion, which are stronger. Trying to progress towards the interior of 12. This also makes it possible to reduce the growth rate of the crack C.

Moreover, although the convex portion 11a and the concave portion 12a are in a non-bonded state, the convex portion 11a is pressed radially outward against the concave portion 12a by the pressure of the gas G, so that the convex portion outer surface 11c and the concave portion The gap with the inner surface 12c tends to close. Therefore, it is possible to prevent the gas G from entering this gap. Therefore, the pressure loss of the gas G inside the flow path FC can be reduced.

Further, since the joint portion 13 is provided on the imaginary line X, it is positioned within a range in the direction of the rotation axis O along which the flow path FC of the scroll portion 7 is formed. Therefore, the joint portion 13 is arranged at or close to the central position in the direction of the rotation axis O in the flow channel FC. As a result, the convex portion 11a is pushed radially outward against the concave portion 12a, thereby closing the gap between the convex portion outer surface 11c and the concave portion inner surface 12c.

Therefore, in the compressor 1 of the present embodiment, by providing the casing 4 as described above, it is possible to improve the performance of the compressor 1 while improving the fatigue strength of the casing 4 .

Here, in the present embodiment, the second main body portion 12 may be provided with the convex portion 11a and the first main body portion 11 may be provided with the concave portion 12a. Also, the joint portion 13 may be provided on the first opposing surface 11b and the second opposing surface 12b to a position away from the convex portion 11a. Namely. The joint portion 13 does not have to be in contact with the convex outer surface 11c.

(first modification)
Next, a compressor 1A of a first modified example of the first embodiment of the present invention will be described with reference to FIG.
As shown in FIG. 3, the first main body portion 11 is formed with a first annular recess 11d that is recessed from the first opposing surface 11b toward one side in the direction of the rotation axis O and extends annularly around the rotation axis O. there is The first annular concave portion 11d is formed in contact with the convex portion outer surface 11c. Of the inner surfaces of the first annular recess 11d, a pair of side bottom surfaces 21a and 21b facing in the radial direction are inclined toward a bottom surface 22 facing in the direction of the rotation axis O so as to approach each other. That is, the side bottom surfaces 21a and 21b are provided with a draft during molding.

The second body portion 12 is provided with a second annular recess 12d that is recessed from the second facing surface 12b toward the other direction of the rotation axis O and extends annularly around the rotation axis O. As shown in FIG. Of the pair of radially facing side bottom surfaces 25a and 25b of the inner surface of the second annular recess 12d, the radially inner side bottom surface 25a is provided at a position radially away from the recess 12a. Therefore, it is provided radially outward of the radially inner side bottom surface 21a of the first annular recess 11d. The radially outer side bottom surface 25b of the second annular recess 12d is provided at the same radial position as the radially outer side bottom surface 21b of the first annular recess 11d. Similar to the side bottom surfaces 21a and 21b of the first annular recess 11d, the pair of side bottom surfaces 25a and 25b of the second annular recess 12d are inclined toward the bottom surface 26 facing the direction of the rotation axis O so as to approach each other. there is That is, the side bottom surfaces 25a and 25b are provided with a draft during molding.

The joint portion 23 is a resin member arranged in a space formed by the first annular recess 11d and the second annular recess 12d. The same resin material as that of the scroll portion 7 can be used as the material of the joint portion 23 . The entire outer surface of the joint portion 23 is joined to the first body portion 11 and the second body portion 12 .

According to the compressor 1A of the first modified example of the first embodiment described above, the growth speed of the crack C can be reduced by the convex portion 11a provided on the first main body portion 11, and the gas in the flow path can be reduced. G pressure loss can be reduced. Therefore, it is possible to improve the performance of the compressor 1A while improving the fatigue strength of the casing 4A.

Furthermore, by using a resin member for the joining portion 23, the first main body portion 11 and the second main body portion 12 can be joined more firmly. Furthermore, the first main body portion 11 and the second main body portion 12 can be joined by providing the joint portion 23 using die slide injection, for example. Specifically, after molding the first main body portion 11 and the second main body portion 12, the die slide is performed so that the first annular concave portion 11d and the second annular concave portion 12d face each other in the direction of the rotation axis O, and the joint portion 23 is formed. The casing 4A can be easily manufactured by filling the space between the first annular recess 11d and the second annular recess 12d with the resin material.

(Second modification)
Next, a compressor 1B of a second modified example of the first embodiment of the present invention will be described with reference to FIG.
In the second modification, the shape of the second annular concave portion 32d is different from that in the first modification. As shown in FIG. 4, the radially inner side bottom surface of the second annular recess 32d is the protrusion outer surface 11c. Accordingly, the joint portion 33 is provided between the first main body portion 11 and the second main body portion 12 in contact with the convex outer surface 11c. The entire outer surface of the joint portion 33 is joined to the first body portion 11 and the second body portion 12 .

Also in this modified example, the space between the first annular concave portion 11d and the second annular concave portion 32d is filled with the resin material of the joint portion 33, so that the first main body portion 11 and the second main body portion 12 are made stronger. and the casing 4B can be easily manufactured using, for example, die slide injection.

[Second embodiment]
Next, a compressor 1C according to a second embodiment of the invention will be described with reference to FIG. In the second embodiment described below, the same parts as those in the first embodiment are assigned the same reference numerals, and redundant description is omitted.
In this embodiment, the position of the joint 43 is different from that of the second modification of the first embodiment.

The first opposing surface 41b of the first main body portion 41 and the second opposing surface 42b of the second main body portion 42 are arranged in the direction of the rotation axis O from the imaginary line X passing through the central position of the flow path in the direction of the rotation axis O. placed on one side. The first opposing surface 41b and the second opposing surface 42b are arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed.
Furthermore, the first annular recess 41d and the second annular recess 42d are also arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed. Therefore, the joint portion 43 is also arranged outside the range in the direction of the rotation axis O in which the flow path FC is formed.

In the compressor 1C of the present embodiment described above, the growth rate of cracks can be reduced by the protrusions 41a provided on the first body portion 41, and the pressure loss of the gas G in the flow path FC can be reduced. can be done. Therefore, it is possible to improve the performance of the compressor 1C while improving the fatigue strength of the casing 4C.

Furthermore, the joint portion 43 is positioned outside the range in the direction of the rotation axis O in which the flow path FC is formed. For this reason, the influence of heat from the compressed gas G and the influence of pressure from the gas G are less likely to affect the joint 43, and cracks C at the joint 43 due to stress in the circumferential direction can be suppressed. . Therefore, the effect of suppressing damage to the casing 4C is obtained.

[Third embodiment]
Next, a compressor 1D according to a third embodiment of the invention will be described with reference to FIG. In the third embodiment described below, the same parts as those in the first embodiment and the second embodiment are denoted by the same reference numerals, and redundant description is omitted.

Contrary to the first embodiment and the second embodiment, the projection 52a is provided on the second body portion 52, and the recess 51a into which the projection 52a is inserted and engaged with the projection 52a is provided on the first body portion 51. It is

Further, a lateral convex portion 52f that protrudes radially outward is provided on the convex portion outer surface 52c, which is a surface facing radially outward in the convex portion 52a. The lateral protrusions 52f may be provided in an annular shape around the rotation axis O, or may be provided in plurality at intervals in the circumferential direction.

Further, a lateral recess 51f that is recessed radially outward and into which the lateral protrusion 52f is inserted and engaged is provided on the recess inner surface 51c facing radially inward in the recess 51a. The horizontal recessed portion 51f may have a ring shape centered on the rotation axis O, or may be provided in plurality at intervals in the circumferential direction.

In the second main body portion 52, in addition to the convex portion 52a, the second opposing surface 52b of the second main body portion 52 is arranged radially outwardly with respect to the convex portion 52a and spaced apart from the convex portion 52a in the radial direction. An outer convex portion 52e is provided that protrudes toward one side of the rotation axis O, that is, toward the first main body portion 51. As shown in FIG. The second opposing surface 52b is a surface that is in contact with the convex portion 52a, is disposed radially outward of the convex portion 52a, and faces one direction of the rotation axis O. As shown in FIG. A surface of the outer convex portion 52e facing radially outward serves as a dividing surface D between the first main body portion 51 and the second main body portion 52 extending in the direction of the rotation axis O. As shown in FIG.

The first main body portion 51 is provided with an outer concave portion 51e that is concave in one direction in the direction of the rotation axis O from the first opposing surface 51b that faces the second opposing surface 52b so that the outer convex portion 52e can be inserted and engaged. ing.

The joint portion 53 is arranged on the other side in the direction of the rotation axis O with respect to the imaginary line X passing through the central position in the direction of the rotation axis O of the flow path FC, and is the range in the direction of the rotation axis O in which the flow path FC is formed. placed outside. The entire outer surface of the joint portion 53 is joined to the first body portion 51 and the second body portion 52 .

Here, the first main body portion 51 and the second main body portion 52 face each other on the dividing plane D in the radial direction. The first main body portion 51 is provided with a first annular concave portion 51d which is open to the end surface facing the other direction of the rotation axis O and which is concave radially outward from the dividing surface D and has an annular shape centered on the rotation axis O. It is The second main body portion 52 has a second annular recess 52d which is open on the end surface facing the other direction of the rotation axis O and which is recessed radially inward from the dividing surface D and forms an annular shape centered on the rotation axis O. is provided. The first annular recess 51d and the second annular recess 52d are provided at the same position in the direction of the rotation axis O. As shown in FIG. Also, the first annular recess 51d and the second annular recess 52d are located outside the range in the direction of the rotation axis O in which the flow path FC is formed.

The joint portion 53 is arranged in a space formed by the first annular recess 51d and the second annular recess 52d. Therefore, the joint portion 53 is also located outside the range in the direction of the rotation axis O in which the flow path FC is formed.

In the compressor 1D of the present embodiment described above, as described above, the projections 52a can reduce the growth rate of cracks and reduce the pressure loss of the gas G in the flow path FC. Furthermore, since the joint portion 53 is located outside the range in the direction of the rotation axis O in which the flow path FC is formed, the influence of heat from the compressed gas G and the influence of pressure from the gas G are exerted on the joint portion. It becomes difficult to reach 53. Therefore, it is possible to suppress the occurrence of cracks in the joint portion 53 due to the stress in the circumferential direction, thereby obtaining the effect of suppressing damage to the casing 4D.

Further, by providing the outer convex portion 52e in addition to the convex portion 52a, the first main body portion 51 and the second main body portion 52 are joined by the joint portion 53 so as to be fitted in the direction of the rotation axis O. . Therefore, it is possible to avoid positional displacement with respect to the rotation axis O, and the first main body portion 51 and the second main body portion 52 can be arranged coaxially during assembly and operation. That is, coaxiality can be improved. As a result, the compression efficiency of the gas G can be improved.

A lateral protrusion 52f is provided on the protrusion outer surface 52c, and a lateral recess 51f engageable with the lateral protrusion 52f is provided on the recess inner surface 51c facing the protrusion outer surface 52c. Relative movement in the direction of the rotation axis O with the body portion 52 can be suppressed. Therefore, the first main body portion 51 and the second main body portion 52 can mutually restrict the deformation in the direction of the rotation axis O, thereby improving the fatigue strength of the casing 4D and reducing the gas G caused by the deformation of the casing 4D. reduction in compression efficiency can be avoided. In particular, even if one of the first main body portion 51 and the second main body portion 52 is likely to reach a high temperature and the amount of thermal deformation is large, the heat generated by the first main body portion 51 and the second main body portion 52 is reduced. The smaller amount of deformation can suppress the deformation of the larger amount of thermal deformation. Therefore, it is possible to improve the fatigue strength of the casing 4D and avoid the deterioration of the compression efficiency of the gas G due to the deformation of the casing 4D.

In this embodiment, only one of the outer protrusion 52e (outer recess 51e) and the lateral protrusion 52f (lateral recess 51f) may be provided.

[Fourth embodiment]
Next, a compressor 1E according to a fourth embodiment of the invention will be described with reference to FIG. In the fourth embodiment described below, the same parts as those in the first to third embodiments are denoted by the same reference numerals, and overlapping descriptions are omitted. In this embodiment, the position of the joint 63 is different from that in the third embodiment.

For example, as shown in FIG. 7, the first main body portion 61 is provided with a first annular recess 61d that is recessed in one direction of the rotation axis O from the outer recess 51e. The second main body portion 62 is provided with a second annular recess 62d that is recessed in the other direction of the rotation axis O from the outer protrusion 52e and has an annular shape with the rotation axis O as the center. The first annular recess 61d and the second annular recess 62d are provided at the same position in the radial direction. The first annular recessed portion 61d and the second annular recessed portion 62d are positioned within a range in the direction of the rotation axis O in which the flow path FC is formed.

The joint portion 63 is arranged in a space formed by the first annular recess 61d and the second annular recess 62d. Therefore, the joint portion 63 is also located within the range in the direction of the rotation axis O in which the flow path FC is formed.

According to the compressor 1E of the present embodiment described above, the joint portion 63 is positioned within the range in the direction of the rotation axis O in which the flow path FC is formed. Therefore, the joint portion 63 is arranged close to the central position (virtual line X) in the direction of the rotation axis O in the flow channel FC. As a result, the influence of the stress in the circumferential direction due to the pressure of the gas G increases, but even in such a case, the protrusions 52a can suppress the cracks from progressing, thereby suppressing damage to the casing 4E. is obtained.

In the present embodiment, the position of the joint portion 63 is not limited to the above case, and the joint portion 63 may be positioned at least within a range in the direction of the rotation axis O along which the flow path FC is formed.

As described above, the embodiments of the present invention have been described in detail with reference to the drawings. , substitutions, and other modifications are possible. Moreover, the present invention is not limited by the embodiments, but only by the claims.

For example, the materials of the scroll portion 7, the intake portion 5, and the discharge portion 6 do not have to be the same. Further, at least the scroll portion 7 should be made of resin. Here, the term "made of resin" includes not only products made purely of resin but also products made of resin containing materials other than resin such as fillers. The intake part 5 and the discharge part 6 may be made of a metal such as aluminum, carbon fiber, a composite material containing a metal filler, or the like.

According to the radial compressor casing and the radial compressor described above, it is possible to improve performance while improving fatigue strength.

1, 1B, 1C, 1D, 1E compressor
2 impeller
3 Axis of rotation
4, 4B, 4C, 4D, 4E Casing
5 Intake
6 discharge part
7 scroll part
7a inner surface
11, 41, 51, 61 first main body
11a, 41a, 52a Convex part
11b, 41b, 51b first opposing surface
11c, 52c convex outer surface
11d, 41d, 51d, 61d first annular concave portion 12, 42, 52, 62 second body portion
12a, 51a concave portion
12b, 42b, 52b second facing surface
12c, 51c inner surface of recess
12d, 32d, 42d, 52d, 62d Second annular recess
13, 23, 33, 43, 53, 63 Joints
21a, 21b, 25a, 25b side bottom surfaces 22, 26 bottom surface 51e outer concave portion 51f lateral concave portion 52e outer convex portion 52f lateral convex portion 61 first main body portion 62 second main body portion X virtual line
G gas
O Axis of rotation FC Channel C Crack D Parting surface

Claims (6)

an intake section extending along the rotation axis of the impeller and having a tubular shape opening in the direction of the rotation axis for introducing fluid into the impeller;
a scroll portion made of resin that communicates with the intake portion and forms a flow path that extends annularly around the rotation axis on the outer peripheral side of the impeller;
a discharge part formed integrally with one end of the scroll part, extending along the circumferential direction of the impeller and having an opening for discharging the fluid from the flow path;
with
The scroll part
a first body portion arranged in one direction of the rotation axis;
a second body portion disposed on the other side of the direction of the rotation axis with respect to the first body portion;
a joint portion that joins the first main body portion and the second main body portion in the direction of the rotation axis and is located within a range in the direction of the rotation axis where the flow path is formed;
has
One of the first main body portion and the second main body portion is provided with a radially inner side of the joint portion with respect to the rotation axis from one of the first main body portion and the second main body portion to the other. an annular projection centered on the axis of rotation extending toward and beyond the junction and forming a portion of the inner surface of the channel;
The other of the first body portion and the second body portion is provided with a recess that is recessed from the inner surface of the flow path and engages with the protrusion ,
The first body portion has a first opposing surface facing the direction of the rotation axis,
The second body portion has a second opposing surface that is in surface contact with the first opposing surface,
The first body portion is provided with a first annular recess that is recessed from the first opposing surface in the direction of the rotation axis and extends annularly around the rotation axis,
The second body portion has a second annular recess that is recessed in the direction of the rotation axis from the second opposing surface at a position corresponding to the position where the first annular recess is provided and that extends annularly around the rotation axis. is provided,
The radial compressor casing , wherein the joint portion is a resin member arranged in a space formed by the first annular recess and the second annular recess . The convex portion has a convex outer surface facing outward in the radial direction,
A horizontal convex portion protruding outward in the radial direction is provided on the outer surface of the convex portion,
the other of the first main body portion and the second main body portion has an inner surface facing the outer surface of the convex portion;
2. A casing for a radial compressor according to claim 1 , wherein said inner surface is provided with lateral recesses which are recessed outward in said radial direction and engageable with said lateral protrusions. The other of the first main body portion and the second main body portion is arranged on the outer side in the radial direction with respect to the convex portion and the one of the first main body portion and the second main body portion An outer protrusion projecting from the other toward the one is further provided,
3. The radial compressor casing according to claim 1, wherein said one of said first main body portion and said second main body portion is provided with an outer concave portion with which said outer convex portion can be engaged. an intake section extending along the rotation axis of the impeller and having a tubular shape opening in the direction of the rotation axis for introducing fluid into the impeller;
a scroll portion made of resin that communicates with the intake portion and forms a flow path that extends annularly around the rotation axis on the outer peripheral side of the impeller;
a discharge part integrally provided at one end of the scroll part, extending along the circumferential direction of the impeller and having an opening for discharging the fluid from the flow path;
with
The scroll part
a first body portion arranged in one direction of the rotation axis;
a second body portion disposed on the other side of the direction of the rotation axis with respect to the first body portion;
a joint portion that joins the first body portion and the second body portion in the direction of the rotation axis and is positioned outside the range in the direction of the rotation axis where the flow path is formed;
has
One of the first main body portion and the second main body portion is provided with a radially inner side of the joint portion with respect to the rotation axis from one of the first main body portion and the second main body portion to the other. an annular projection centered on the axis of rotation extending toward and beyond the junction and forming a portion of the inner surface of the channel;
The other of the first main body portion and the second main body portion is provided with a concave portion that is concave from the inner surface of the flow path and engages with the convex portion,
The first body portion has a first opposing surface facing the direction of the rotation axis,
The second body portion has a second opposing surface that is in surface contact with the first opposing surface,
The first body portion is provided with a first annular recess that is recessed from the first opposing surface in the direction of the rotation axis and extends annularly around the rotation axis,
The second body portion has a second annular recess that is recessed in the direction of the rotation axis from the second opposing surface at a position corresponding to the position where the first annular recess is provided and that extends annularly around the rotation axis. is provided,
The radial compressor casing, wherein the joint portion is a resin member arranged in a space formed by the first annular recess and the second annular recess. an intake section extending along the rotation axis of the impeller and having a tubular shape opening in the direction of the rotation axis for introducing fluid into the impeller;
a scroll portion made of resin that communicates with the intake portion and forms a flow path that extends annularly around the rotation axis on the outer peripheral side of the impeller;
a discharge part integrally provided at one end of the scroll part, extending along the circumferential direction of the impeller and having an opening for discharging the fluid from the flow path;
with
The scroll part
a first body portion arranged in one direction of the rotation axis;
a second body portion disposed on the other side of the direction of the rotation axis with respect to the first body portion;
a joint portion that joins the first body portion and the second body portion in the direction of the rotation axis and is positioned outside the range in the direction of the rotation axis where the flow path is formed;
has
One of the first main body portion and the second main body portion is provided with a radially inner side of the joint portion with respect to the rotation axis from one of the first main body portion and the second main body portion to the other. an annular projection centered on the axis of rotation extending toward and beyond the junction and forming a portion of the inner surface of the channel;
The other of the first main body portion and the second main body portion is provided with a concave portion that is concave from the inner surface of the flow path and engages with the convex portion,
The convex portion has a convex outer surface facing outward in the radial direction,
A horizontal convex portion protruding outward in the radial direction is provided on the outer surface of the convex portion,
the other of the first main body portion and the second main body portion has an inner surface facing the outer surface of the convex portion;
The inner surface is provided with a lateral recess that is recessed outward in the radial direction and that can be engaged with the lateral protrusion,
The other of the first main body portion and the second main body portion is arranged on the outer side in the radial direction with respect to the convex portion and the one of the first main body portion and the second main body portion An outer protrusion projecting from the other toward the one is further provided,
A casing for a radial compressor, wherein said one of said first main body portion and said second main body portion is provided with an outer concave portion with which said outer convex portion can be engaged. an impeller;
a rotating shaft on which the impeller is fitted and which rotates together with the impeller;
A casing according to any one of claims 1 to 5 provided to cover the impeller;
A radial compressor with

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