The present disclosure relates to centrifugal compressors. The present application claims the benefit of priority based on Japanese Patent Application No. 2022-143038 filed on Sep. 8, 2022, the content of which is incorporated herein.
A centrifugal compressor includes a compressor housing in which an intake flow path is formed. A compressor impeller is disposed in the intake flow path. When the flow rate of the air flowing into the compressor impeller decreases, the air compressed by the compressor impeller flows backward through the intake flow path, and a phenomenon called surging occurs.
Patent Literature 1 discloses a centrifugal compressor in which a throttle mechanism is included in a compressor housing. The throttle mechanism is disposed on the upstream side of intake air with respect to the compressor impeller. The throttle mechanism includes a movable member. The movable member is movable to a protruding position protruding into the intake flow path and a retracted position retracting from the intake flow path. The throttle mechanism reduces the cross-sectional area of the intake flow path by causing the movable member to protrude into the intake flow path. When the movable member protrudes into the intake flow path, the air flowing backward in the intake flow path is blocked by the movable member. With the air flowing backward in the intake flow path blocked, surging is suppressed.
Patent Literature 1: European Patent Application Publication No. 3530954
In a centrifugal compressor including a movable member for suppressing surging, in a case where strong backflow of air occurs in an intake flow path, the backflow of air may not be sufficiently blocked by the movable member. In this case, the efficiency of the centrifugal compressor decreases.
An object of the present disclosure is to provide a centrifugal compressor capable of suppressing a decrease in efficiency of the centrifugal compressor.
In order to solve the above problems, a centrifugal compressor of the present disclosure includes: an intake flow path connected to an intake port; a compressor impeller disposed in the intake flow path; a movable member provided on the intake port side with respect to the compressor impeller in the intake flow path, the movable member movable to a protruding position protruding into the intake flow path and a retracted position retracting from the intake flow path; a first end that is an end, on the compressor impeller side, of an inner curved surface of the movable member; a second end that is an end, on the intake port side, of the inner curved surface of the movable member; and an extending portion between the first end and the second end, the extending portion extending in a direction corresponding to a rotation axis direction of the compressor impeller.
A curvature radius of the second end may be larger than a curvature radius of the first end.
The curvature radius of the second end may be larger than the thickness of the movable member in the rotation axis direction.
A fillet portion may be formed between the second end and a surface of the movable member facing the intake port side.
A radial distance between an inner circumferential edge of the surface of the movable member facing the intake port side and the extending portion may be less than or equal to 80% of a thickness of the movable member in the rotation axis direction.
A radial distance between an inner circumferential edge of the surface of the movable member facing the intake port side and the extending portion may be greater than or equal to 20% of the thickness of the movable member in the rotation axis direction.
According to the present disclosure, it is possible to suppress a decrease in efficiency of a centrifugal compressor.
Embodiments of the present disclosure will be described below by referring to the accompanying drawings. Dimensions, materials, other specific numerical values, and the like illustrated in the embodiments are merely an example for facilitating understanding, and the present disclosure is not limited thereto unless otherwise specified. Note that, in the present specification and the drawings, components having substantially the same function and structure are denoted by the same symbol, and redundant explanations are omitted. Illustration of components not directly related to the present disclosure is omitted.
As illustrated in
A receiving hole 2a is formed in the bearing housing 2. The receiving hole 2a penetrates through the turbocharger TC in the left-right direction. A bearing 6 is disposed in the receiving hole 2a. The bearing 6 is, for example, a full floating bearing. Incidentally, the bearings 6 may be another radial bearing such as a semi-floating bearing or a rolling bearing. A part of a shaft 7 is disposed in the receiving hole 2a. The shaft 7 is pivotally supported by the bearing 6 in a freely rotatable manner. At a left end of the shaft 7, the turbine blade wheel 8 is provided. The turbine blade wheel 8 is housed in the turbine housing 4 in a freely rotatable manner. At a right end of the shaft 7, a compressor impeller 9 is provided. The compressor impeller 9 is accommodated in the compressor housing 100 in a freely rotatable manner.
An intake port 10 is formed in the compressor housing 100. The intake port 10 opens to the right side of the turbocharger TC. The intake port 10 is connected to an air cleaner (not illustrated). A diffuser flow path 11 is formed between the bearing housing 2 and the compressor housing 100. The diffuser flow path 11 pressurizes the air. The diffuser flow path 11 is formed in an annular shape from the inner side to the outer side in the radial direction of the compressor impeller 9 (hereinafter, simply referred to as the radial direction). The diffuser flow path 11 communicates with the intake port 10 via the compressor impeller 9 on the inner side in the radial direction.
In addition, a compressor scroll flow path 12 is formed in the compressor housing 100. The compressor scroll flow path 12 is formed in an annular shape. The compressor scroll flow path 12 is positioned on the outer side in the radial direction with respect to the compressor impeller 9. The compressor scroll flow path 12 communicates with an intake port of the engine (not illustrated) and the diffuser flow path 11. When the compressor impeller 9 rotates, the air is sucked from the intake port 10 into the compressor housing 100. The sucked air is pressurized and accelerated in the process of flowing between blades of the compressor impeller 9. The pressurized and accelerated air is further pressurized by the diffuser flow path 11 and the compressor scroll flow path 12. The pressurized air flows out from a discharge port (not illustrated) and is guided to the intake port of the engine.
As described above, the turbocharger TC includes the centrifugal compressor CC. The centrifugal compressor CC includes the compressor housing 100, the compressor impeller 9, and the link mechanism 200 to be described later.
An exhaust port 13 is formed in the turbine housing 4. The exhaust port 13 opens to the left side of the turbocharger TC. The exhaust port 13 is connected to an exhaust gas purification device (not illustrated). A communication flow path 14 and a turbine scroll flow path 15 are formed in the turbine housing 4. The turbine scroll flow path 15 is positioned on the outer side in the radial direction with respect to the turbine blade wheel 8. A communication flow path 14 is positioned between the turbine blade wheel 8 and the turbine scroll flow path 15.
The turbine scroll flow path 15 communicates with a gas inlet port (not illustrated). Exhaust gas discharged from an exhaust manifold of the engine (not illustrated) is guided to the gas inlet port. The communication flow path 14 communicates the turbine scroll flow path 15 and the exhaust port 13. The exhaust gas guided from the gas inlet port to the turbine scroll flow path 15 is guided to the exhaust port 13 via the communication flow path 14 and spaces between blades of the turbine blade wheel 8. The exhaust gas rotates the turbine blade wheel 8 in the process of flowing therethrough.
The turning force of the turbine blade wheel 8 is transmitted to the compressor impeller 9 via the shaft 7. As described above, the turning force of the compressor impeller 9 causes the air to be pressurized and to be guided to the intake port of the engine.
As illustrated in
The through hole 111 has a parallel portion 111a and a reduced diameter portion 111b. The parallel portion 111a is located on the end surface 113 side with respect to the reduced diameter portion 111b. The inner diameter of the parallel portion 111a is approximately constant in the rotation axis direction. The reduced diameter portion 111b is located on the end surface 112 side with respect to the parallel portion 111a. The reduced diameter portion 111b is continuous with the parallel portion 111a. The inner diameter of a portion of the reduced diameter portion 111b that is continuous with the parallel portion 111a is approximately equal to the inner diameter of the parallel portion 111a. The inner diameter of the reduced diameter portion 111b decreases as it is away from the parallel portion 111a.
A cutout portion 112a is formed on the end surface 112. The cutout portion 112a is recessed from the end surface 112 toward the end surface 113 side. The cutout portion 112a is formed in an outer circumferential portion of the end surface 112. The cutout portion 112a has, for example, a substantially annular shape when viewed from the rotation axis direction.
Furthermore, an accommodation chamber AC is formed on the end surface 112. The accommodation chamber AC is formed in the first housing member 110 on the intake port 10 side with respect to a leading edge LE of blades of the compressor impeller 9. The accommodation chamber AC includes an accommodation groove 112b described later, a bearing hole 112d, and an accommodation hole 115 (see
The accommodation groove 112b is formed on the end surface 112. The accommodation groove 112b is positioned between the cutout portion 112a and the through hole 111. The accommodation groove 112b is recessed from the end surface 112 toward the end surface 113 side. The accommodation groove 112b has, for example, a substantially annular shape when viewed in the rotation axis direction. The accommodation groove 112b communicates with the through hole 111 on the radially inner side.
The bearing hole 112d is formed on a wall surface 112c of the accommodation groove 112b on the end surface 113 side. The bearing hole 112d extends in the rotation axis direction from the wall surface 112c toward the end surface 113 side. Two bearing holes 112d are formed separated from each other in the rotation direction of the compressor impeller 9 (hereinafter, simply referred to as the rotation direction or the circumferential direction). The two bearing holes 112d are arranged at positions shifted by 180 degrees in the rotation direction.
A through hole 121 is formed in the second housing member 120. The second housing member 120 has an end surface 122 on a side close to the first housing member 110. The second housing member 120 also has an end surface 123 on a side away from the first housing member 110. The through hole 121 extends from the end surface 122 to the end surface 123 along the rotation axis direction. That is, the through hole 121 penetrates the second housing member 120 in the rotation axis direction.
The inner diameter of an end of the through hole 121 on the end surface 122 side is approximately equal to the inner diameter of the end of the through hole 111 on the end surface 112 side. A shroud portion 121a is formed on an inner wall of the through hole 121. The shroud portion 121a faces the compressor impeller 9 from the outer side in the radial direction. The outer diameter of the compressor impeller 9 increases as it is farther from leading edges LE of the blades of the compressor impeller 9. The inner diameter of the shroud portion 121a increases as the shroud portion 121a is separated away from the end surface 122.
An accommodation groove 122a is formed on the end surface 122. The accommodation groove 122a is recessed from the end surface 122 toward the end surface 123 side. The accommodation groove 122a has, for example, a substantially annular shape when viewed in the rotation axis direction. The first housing member 110 is inserted into the accommodation groove 122a. The end surface 112 of the first housing member 110 abuts on a wall surface 122b of the accommodation groove 122a on the end surface 123 side. At this point, the accommodation chamber AC is formed between the first housing member 110 (specifically, the wall surface 112c) and the second housing member 120 (specifically, the wall surface 122b).
An intake flow path 130 is formed by the through hole 111 of the first housing member 110 and the through hole 121 of the second housing member 120. That is, the intake flow path 130 is formed in the compressor housing 100. The intake flow path 130 is connected to the intake port 10 on one side and is connected to the diffuser flow path 11 on the other side. The intake port 10 and the diffuser flow path 11 communicate with each other via the intake flow path 130. The intake port 10 side of the intake flow path 130 is defined as an upstream side of intake air, and the diffuser flow path 11 side of the intake flow path 130 is defined as a downstream side of intake air.
The compressor impeller 9 is disposed in the intake flow path 130. The cross-sectional shape of the intake flow path 130 orthogonal to the rotation axis direction is, for example, a circle centered on the rotation axis of the compressor impeller 9. However, the cross-sectional shape of the intake flow path 130 is not limited to a circle and may be, for example, an elliptical shape.
A sealing material (not illustrated) is disposed in the cutout portion 112a of the first housing member 110. The sealing material suppresses the flow rate of the air flowing through a gap between the first housing member 110 and the second housing member 120. However, the cutout portion 112a and the sealing material are not essential.
The first movable member 210 is disposed in the accommodation groove 112b (specifically, the accommodation chamber AC). Specifically, the first movable member 210 is disposed between the wall surface 112c of the accommodation groove 112b and the wall surface 122b (see
The first movable member 210 has a facing surface S1 facing the wall surface 112c of the accommodation groove 112b and a facing surface S2 facing the wall surface 122b of the accommodation groove 122a. The first movable member 210 includes a main body B1. The main body B1 includes a curved portion 211 and an arm portion 212.
The curved portion 211 extends in the circumferential direction of the compressor impeller 9. The curved portion 211 has a substantially arc shape. One end surface 211a and another end surface 211b of the curved portion 211 in the circumferential direction extend in parallel to the radial direction and the rotation axis direction. However, the one end surface 211a and the other end surface 211b may be inclined with respect to the radial direction and the rotation axis direction.
The arm portion 212 is included on the one end surface 211a side of the curved portion 211. The arm portion 212 extends outward in the radial direction with respect to an outer curved surface 211c of the curved portion 211. Furthermore, the arm portion 212 extends in a direction inclined with respect to the radial direction (specifically, in a direction approaching the second movable member 220).
The second movable member 220 is disposed in the accommodation groove 112b (specifically, the accommodation chamber AC). Specifically, the second movable member 220 is disposed between the wall surface 112c of the accommodation groove 112b and the wall surface 122b (see
The second movable member 220 has a facing surface S1 facing the wall surface 112c of the accommodation groove 112b and a facing surface S2 facing the wall surface 122b of the accommodation groove 122a. The second movable member 220 includes a main body B2. The main body B2 includes a curved portion 221 and an arm portion 222.
The curved portion 221 extends in the circumferential direction of the compressor impeller 9. The curved portion 221 has substantially an arc shape. One end surface 221a and another end surface 221b of the curved portion 221 in the circumferential direction extend in parallel to the radial direction and the rotation axis direction. Incidentally, the one end surface 221a and the other end surface 221b may be inclined with respect to the radial direction and the rotation axis direction.
The arm portion 222 is included on the one end surface 221a side of the curved portion 221. The arm portion 222 extends outward in the radial direction with respect to an outer curved surface 221c of the curved portion 221. Furthermore, the arm portion 222 extends in a direction inclined with respect to the radial direction (specifically, in a direction approaching the first movable member 210).
The curved portion 211 and the curved portion 221 face each other with the rotation center of the compressor impeller 9 interposed therebetween. That is, the curved portion 211 faces the curved portion 221 with the intake flow path 130 interposed therebetween. The one end surface 211a of the curved portion 211 and the other end surface 221b of the curved portion 221 face each other in the circumferential direction. The other end surface 211b of the curved portion 211 and the one end surface 221a of the curved portion 221 face each other in the circumferential direction. In the first movable member 210 and the second movable member 220, as will be described in detail later, the curved portions 211 and 221 are movable in the radial direction.
The coupling member 230 is coupled to the first movable member 210 and the second movable member 220. The coupling member 230 is positioned on the intake port 10 side with respect to the first movable member 210 and the second movable member 220. The coupling member 230 has substantially an arc shape. In the coupling member 230, a first bearing hole 231 is formed on one end side in the circumferential direction, and a second bearing hole 232 is formed on the other end side. The first bearing hole 231 and the second bearing hole 232 are open on an end surface 233 of the coupling member 230 on the side of the first movable member 210 and the second movable member 220. The first bearing hole 231 and the second bearing hole 232 extend in the rotation axis direction. In this example, the first bearing hole 231 and the second bearing hole 232 do not penetrate through. However, the first bearing hole 231 and the second bearing hole 232 may penetrate through the coupling member 230 in the rotation axis direction.
A rod connection portion 234 is formed between the first bearing hole 231 and the second bearing hole 232 in the coupling member 230. The rod connection portion 234 is formed on an end surface 235 of the coupling member 230 on the side opposite to the first movable member 210 and the second movable member 220. The rod connection portion 234 projects from the end surface 235 in the rotation axis direction. The rod connection portion 234 has, for example, a substantially cylindrical shape.
The rod 240 has a substantially cylindrical shape. A planar portion 241 is formed at one end of the rod 240, and a coupling portion 243 is formed at the other end of the rod 240. The planar portion 241 extends in a planar direction substantially orthogonal to the rotation axis direction. A bearing hole 242 opens in the planar portion 241. The bearing hole 242 extends in the rotation axis direction. The coupling portion 243 includes a coupling hole 243a. An actuator 250 (see
In the rod 240, a rod large-diameter portion 244 and two rod small-diameter portions 245 are formed between the planar portion 241 and the coupling portion 243. The rod large-diameter portion 244 is disposed between the two rod small-diameter portions 245. Of the two rod small-diameter portions 245, the rod small-diameter portion 245 on the planar portion 241 side connects the rod large-diameter portion 244 and the planar portion 241. Of the two rod small-diameter portions 245, the rod small-diameter portion 245 on the coupling portion 243 side connects the rod large-diameter portion 244 and the coupling portion 243. The outer diameter of the rod large-diameter portion 244 is larger than the outer diameters of the two rod small-diameter portions 245.
An insertion hole 114 is formed in the first housing member 110. One end 114a of the insertion hole 114 opens to the outside of the first housing member 110. The insertion hole 114 extends, for example, in a planar direction orthogonal to the rotation axis direction. The insertion hole 114 is positioned on the outer side in the radial direction with respect to the through hole 111. The insertion hole 114 is positioned on the outer side in the radial direction with respect to the intake flow path 130. The planar portion 241 side of the rod 240 is inserted into the insertion hole 114. The rod large-diameter portion 244 is guided by an inner wall surface of the insertion hole 114. The movement of the rod 240 in a direction other than the central axis direction of the insertion hole 114 is restricted.
An accommodation hole 115 is formed in the first housing member 110. The accommodation hole 115 opens to the wall surface 112c of the accommodation groove 112b. The accommodation hole 115 is recessed from the wall surface 112c toward the intake port 10. The accommodation hole 115 is positioned on a side away from the intake port 10 with respect to the insertion hole 114. The accommodation hole 115 has a substantially arc shape when viewed from the rotation axis direction. The accommodation hole 115 extends longer in the circumferential direction than the coupling member 230. The accommodation hole 115 is spaced apart from the bearing hole 112d in the circumferential direction.
A communication hole 116 is formed in the first housing member 110. The communication hole 116 communicates the insertion hole 114 and the accommodation hole 115. The communication hole 116 is formed in the accommodation hole 115 in an approximately middle portion in the circumferential direction. The communication hole 116 is, for example, an elliptical hole extending approximately in parallel to the extending direction of the insertion hole 114. The width of the communication hole 116 in the longitudinal direction (specifically, in the extending direction) is wider than the width of the communication hole 116 in the lateral direction (specifically, a direction orthogonal to the extending direction). The width of the communication hole 116 in the lateral direction is larger than the outer diameter of the rod connection portion 234 of the coupling member 230.
The coupling member 230 is accommodated in the accommodation hole 115. In this manner, the first movable member 210, the second movable member 220, and the coupling member 230 are arranged in the accommodation chamber AC formed in the first housing member 110. The circumferential length of the accommodation hole 115 is longer than the circumferential length of the coupling member 230. The radial width of the accommodation hole 115 is also wider than the radial width of the coupling member 230. Therefore, the movement of the coupling member 230 in a planar direction orthogonal to the rotation axis direction is allowed inside the accommodation hole 115.
The rod connection portion 234 is inserted from the communication hole 116 into the insertion hole 114. The planar portion 241 of the rod 240 is inserted into the insertion hole 114. The bearing hole 242 of the planar portion 241 faces the communication hole 116. The rod connection portion 234 is inserted into the bearing hole 242 for connection. The rod connection portion 234 is pivotally supported by the bearing hole 242.
The outer diameter of the coupling shaft 213 is smaller than the inner diameter of the first bearing hole 231 of the coupling member 230. The coupling shaft 213 is inserted into the first bearing hole 231. The coupling shaft 213 is pivotally supported by the first bearing hole 231 in a freely rotatable manner. The outer diameter of the rotation shaft 214 is smaller than the inner diameter of the bearing hole 112d of the first housing member 110. The rotation shaft 214 is inserted into the bearing hole 112d on the vertically upper side (namely, the side close to the rod 240) of the two bearing holes 112d. The rotation shaft 214 is pivotally supported by the bearing hole 112d in a freely rotatable manner.
The second movable member 220 includes a coupling shaft 223 and a rotation shaft 224. The coupling shaft 223 and the rotation shaft 224 protrude in the rotation axis direction from the facing surface S1 (see
The outer diameter of the coupling shaft 223 is smaller than the inner diameter of the second bearing hole 232 of the coupling member 230. The coupling shaft 223 is inserted into the second bearing hole 232. The coupling shaft 223 is pivotally supported by the second bearing hole 232 in a freely rotatable manner. The outer diameter of the rotation shaft 224 is smaller than the inner diameter of the bearing hole 112d of the first housing member 110. The rotation shaft 224 is inserted into the bearing hole 112d on the vertically lower side (namely, the side separated away from the rod 240) of the two bearing holes 112d. The rotation shaft 224 is pivotally supported by the bearing hole 112d in a freely rotatable manner.
As described above, the link mechanism 200 has four links. The four links are the first movable member 210, the second movable member 220, the first housing member 110, and the coupling member 230. Since the link mechanism 200 has four links, the link mechanism 200 has a limited chain, which gives one-degree-of-freedom, thereby making it easy to control.
The actuator 250 is an electric actuator and is driven by electricity. The actuator 250 is, for example, an electric cylinder having a motor (not illustrated). In this case, the rotational power of the motor is converted into power in a linear traveling direction and transmitted to the driving shaft 251. As a result, the driving shaft 251 moves in the axial direction. When the rotation direction of the motor is switched, the moving direction of the driving shaft 251 is switched.
In the arrangement illustrated in
As illustrated in
When the rod 240 moves, the coupling member 230 also moves upward in
As described above, the link mechanism 200 has four links. The coupling member 230, the first movable member 210, and the second movable member 220 behave in one-degree-of-freedom with respect to the first housing member 110. Specifically, the coupling member 230 slightly swings in the left-right direction while slightly rotating counterclockwise in
The rotation shaft 214 of the first movable member 210 is pivotally supported by the first housing member 110. The movement of the rotation shaft 214 in the planar direction orthogonal to the rotation axis direction is restricted. The coupling shaft 213 is pivotally supported by the coupling member 230. Since the movement of the coupling member 230 is allowed, the coupling shaft 213 is movable in the planar direction orthogonal to the rotation axis direction. As a result, with the movement of the coupling member 230, the first movable member 210 rotates clockwise about the rotation shaft 214 as the rotation center in
Similarly, the rotation shaft 224 of the second movable member 220 is pivotally supported by the first housing member 110. The movement of the rotation shaft 224 in the planar direction orthogonal to the rotation axis direction is restricted. The coupling shaft 223 is pivotally supported by the coupling member 230. Since the movement of the coupling member 230 is allowed, the coupling shaft 223 is movable in the planar direction orthogonal to the rotation axis direction. As a result, with the movement of the coupling member 230, the second movable member 220 rotates clockwise about the rotation shaft 224 as the rotation center in
The first movable member 210 and the second movable member 220 move in a direction of separating from each other in the order from
As described above, the first movable member 210 and the second movable member 220 are provided on the intake port 10 side with respect to the compressor impeller 9 in the intake flow path 130. The first movable member 210 and the second movable member 220 are provided in such a manner as to cover the intake flow path 130. The first movable member 210 and the second movable member 220 are movable to the protruding position protruding into the intake flow path 130 and the retracted position retracting from the intake flow path 130. In the present embodiment, the first movable member 210 and the second movable member 220 move in the radial direction of the compressor impeller 9. Incidentally, without being limited thereto, the first movable member 210 and the second movable member 220 may rotate around the rotation axis of the compressor impeller 9. For example, the first movable member 210 and the second movable member 220 may be shutter blades having two or more blades.
Since the first movable member 210 and the second movable member 220 do not protrude into the intake flow path 130 when located at the retracted position, the pressure loss of the air flowing through the intake flow path 130 can be reduced.
As illustrated in
In the centrifugal compressor CC, as the flow rate of the air flowing into the compressor impeller 9 decreases, the air compressed by the compressor impeller 9 may flow backward through the intake flow path 130. That is, the air compressed by the compressor impeller 9 may flow from the downstream side toward the upstream side.
As illustrated in
In addition, since the flow path cross-sectional area of the intake flow path 130 decreases, the flow rate of the air flowing into the compressor impeller 9 increases. As a result, it is possible to suppress occurrence of surging in the centrifugal compressor CC. That is, the centrifugal compressor CC of the present embodiment can expand the operating region of the centrifugal compressor CC to a small-flow-rate side by forming the protruding position state.
As described above, the first movable member 210 and the second movable member 220 are configured as a throttle member that throttles the intake flow path 130. That is, in the present embodiment, the link mechanism 200 functions as a throttle mechanism for throttling the intake flow path 130. The first movable member 210 and the second movable member 220 can change the flow path cross-sectional area of the intake flow path 130 with the link mechanism 200 driven.
In the centrifugal compressor CC, in a case where a strong backflow of air occurs in the intake flow path 130, the backflow of air may not be sufficiently blocked by the first movable member 210 and the second movable member 220 which are movable members. In this case, the efficiency of the centrifugal compressor CC decreases. In the present embodiment, devising the shape of the movable members achieves effectively suppressing the backflow of air and effectively suppressing the decrease in the efficiency of the centrifugal compressor CC.
Hereinafter, details of the shape of the movable members for more effectively suppressing the backflow of air will be described with reference to
The first end 216 is an end on the compressor impeller 9 side (left side in
The second end 217 is an end of the inner curved surface S3 on the intake port 10 side (the right side in
The extending portion 218 is included between the first end 216 and the second end 217. That is, the first end 216 and the second end 217 are connected by the extending portion 218. The extending portion 218 has an annular shape centered on the rotation axis of the compressor impeller 9. The extending portion 218 extends in a direction corresponding to the rotation axis direction of the compressor impeller 9. In the example of
The first end 216 connects the facing surface S2 and the extending portion 218. In the example of
In the example of
The second end 217 connects the facing surface S1 and the extending portion 218. In the example of
At the connection position between the second end 217 and the fillet portion F1, the tangential direction of the second end 217 coincides with the tangential direction of the fillet portion F1. However, at the connection position between the second end 217 and the fillet portion F1, the tangential direction of the second end 217 may be different to some extent from the tangential direction of the fillet portion F1. At the connection position between the fillet portion F1 and the facing surface S1, the tangential direction of the fillet portion F1 coincides with the extending direction of the facing surface S1. However, at the connection position between the fillet portion F1 and the facing surface S1, the tangential direction of the fillet portion F1 may be different to some extent from the extending direction of the facing surface S1. The fillet portion F1 may not be formed between the second end 217 and the facing surface S1.
In the example of
As described above, the centrifugal compressor CC includes the first end 216 that is the end on the compressor impeller 9 side on the inner curved surface S3 of the movable member (in the above example, the first movable member 210), the second end 217 that is the end on the intake port 10 side of the inner curved surface S3 of the movable member, and the extending portion 218 included between the first end 216 and the second end 217 and extending in the direction corresponding to the rotation axis direction of the compressor impeller 9.
With the extending portion 218 included between the first end 216 and the second end 217, the flowing direction of the air flowing from the intake port 10 toward the compressor impeller 9 can be guided in the rotation axis direction of the compressor impeller 9. As a result, the flow direction of the air flowing from the intake port 10 toward the compressor impeller 9 can be suppressed from being excessively inclined radially inward as the air approaches the compressor impeller 9. When the flowing direction of the air flowing from the intake port 10 toward the compressor impeller 9 is inclined as described above, a backflow region of the air on the compressor impeller 9 side with respect to the movable members (namely, a region where a backflow of air is occurring) tends to expand radially inward. Therefore, by guiding the flowing direction of the air flowing from the intake port 10 toward the compressor impeller 9 in the rotation axis direction of the compressor impeller 9, the backflow region of the air on the compressor impeller 9 side with respect to the movable members can be suppressed from expanding radially inward. Therefore, even in a case where a strong backflow of air occurs in the intake flow path 130, the backflow of air can be sufficiently blocked by the movable members, and the backflow of air can be effectively suppressed. Therefore, it is achieved to effectively suppress a decrease in efficiency of the centrifugal compressor CC.
In particular, in the centrifugal compressor CC, the second curvature radius R2, which is the curvature radius of the second end 217, is larger than the first curvature radius R1, which is the curvature radius of the first end 216.
By reducing the first curvature radius R1 of the first end 216, it is possible to suppress the air flowing backward from the compressor impeller 9 toward the movable members from flowing backward to the upstream side along the first end 216. That is, the air flowing backward from the compressor impeller 9 toward the movable members can be effectively blocked by the facing surface S2. From the viewpoint of effectively blocking the backward-flowing air by the facing surface S2, the first curvature radius R1 of the first end 216 is preferably as small as possible. For example, the first curvature radius R1 is preferably less than or equal to 1 mm and, more preferably, less than or equal to 0.1 mm. The first curvature radius R1 may be 0 mm.
By increasing the second curvature radius R2 of the second end 217, the air flowing from the intake port 10 toward the compressor impeller 9 easily flows along the second end 217. As a result, separation of the air at the second end 217 is suppressed, and thus the position on the inner curved surface S3 of the movable member at which the air is separated can be set on a further downstream side. When the air is separated on an upstream side on the inner curved surface S3 of the movable member, the backflow region of the air on the compressor impeller 9 side with respect to the movable member tends to expand radially inward. Therefore, by setting the position where the air is separated on the inner curved surface S3 of the movable member to the further downstream side, it is possible to suppress radially inward expansion of the backflow region of the air on the compressor impeller 9 side with respect to the movable member.
As described above, since the second curvature radius R2, which is the curvature radius of the second end 217, is larger than the first curvature radius R1, which is the curvature radius of the first end 216, the backflow of air can be sufficiently blocked by the movable members, and the backflow of air can be more effectively suppressed. Therefore, it is possible to more effectively suppress a decrease in efficiency of the centrifugal compressor CC.
In particular, in the centrifugal compressor CC, the second curvature radius R2, which is the curvature radius of the second end 217, is larger than the thickness T1 of the movable member (in the above example, the first movable member 210) in the rotation axis direction. As a result, the air flowing from the intake port 10 toward the compressor impeller 9 further easily follows along the second end 217. Therefore, since separation of the air at the second end 217 is further suppressed, the position on the inner curved surface S3 of the movable member at which the air is separated can be set on the further downstream side. Therefore, the backflow region of the air on the compressor impeller 9 side with respect to the movable member can be further suppressed from expanding radially inward.
In particular, in the centrifugal compressor CC, a fillet portion F1 is formed between the second end 217 and a surface of the movable member (in the above example, the first movable member 210) facing the intake port 10 (in the above example, the facing surface S1). As a result, as compared with the case where the fillet portion F1 is not formed, separation of the air at the connection position between the second end 217 and the facing surface S1 is suppressed. Therefore, it is appropriately implemented that the position, where the air is separated on the inner curved surface S3 of the movable member, be set on a downstream side. Therefore, it is appropriately implemented that the backflow region of the air on the compressor impeller 9 side with respect to the movable member be suppressed from expanding radially inward.
In particular, in the centrifugal compressor CC, a radial distance D1 between an inner circumferential edge E1 of the surface of the movable member (in the above example, the first movable member 210) facing the intake port 10 side (in the above example, the facing surface S1) and the extending portion 218 is less than or equal to an upper limit value corresponding to the thickness T1 of the movable member in the rotation axis direction and is greater than or equal to a lower limit value corresponding to the thickness T1 of the movable member in the rotation axis direction. However, only the upper limit value or only the lower limit value may be set for the radial distance D1.
In a case where the radial distance D1 is excessively long, it becomes difficult to guide the flow direction of the air flowing from the intake port 10 toward the compressor impeller 9 in the rotation axis direction of the compressor impeller 9. Therefore, the upper limit value of the radial distance D1 is set as appropriate from the viewpoint of implementing that the flow direction of the air flowing from the intake port 10 toward the compressor impeller 9 be guided in the rotation axis direction of the compressor impeller 9. For example, the upper limit value of the radial distance D1 may be set to 80% of the thickness T1. By setting the radial distance D1 to less than or equal to the upper limit value (for example, less than or equal to 80% of the thickness T1), it is appropriately implemented that the flow direction of the air flowing from the intake port 10 toward the compressor impeller 9 be guided in the rotation axis direction of the compressor impeller 9.
In a case where the radial distance D1 is excessively short, the air is easily separated on the upstream side of the inner curved surface S3 of the movable member. Therefore, the lower limit value of the radial distance D1 is set as appropriate from the viewpoint of implementing that the position at which the air is separated on the inner curved surface S3 of the movable member be set on the further downstream side. For example, the lower limit value of the radial distance D1 can be set to 20% of the thickness T1. By setting the radial distance D1 to greater than or equal to the lower limit value (for example, greater than or equal to 20% of the thickness T1), it is appropriately implemented that the position where the air is separated on the inner curved surface S3 of the movable member be set on the further downstream side.
In particular, in the modification illustrated in
Although the embodiments of the present disclosure have been described with reference to the accompanying drawings, it is naturally understood that the present disclosure is not limited to the above embodiments. It is clear that those skilled in the art can conceive various modifications or variations within the scope described in the claims, and it is understood that they are naturally also within the technical scope of the present disclosure.
Number | Date | Country | Kind |
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2022-143038 | Sep 2022 | JP | national |
This application is a continuation application of International Application No. PCT/JP2023/014077, filed on Apr. 5, 2023, which claims priority to Japanese Patent Application No. 2022-143038, filed on Sep. 8, 2022, the entire contents of which are incorporated by reference herein.
Number | Date | Country | |
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Parent | PCT/JP2023/014077 | Apr 2023 | WO |
Child | 19010262 | US |