JP7001438B2 - Compressor - Google Patents

Description

This disclosure relates to a compressor.

Conventionally, in the case of a compressor such as a turbocharger used for an automobile or a ship, for example, high efficiency and expansion of an operating range have been problems. As one of the countermeasures, a configuration is known in which a bypass flow path is provided in addition to the main flow path in order to reduce the generation limit of the surge generated at a small flow rate. For example, Patent Document 1 discloses a configuration in which a detour flow path formed outside the main flow path upstream of the upstream end of the rotor blade group is opened and closed by an operation lever provided outside.

Japanese Unexamined Patent Publication No. 2005-240696

However, since the compressor disclosed in Patent Document 1 needs to open and close the detour flow path from the outside, there is room for further improvement in terms of mountability to an engine or the like and cost.

In view of the above-mentioned problems, at least one embodiment of the present invention aims to provide a compressor capable of achieving both expansion of an operating region and high efficiency without requiring an external input.

(1) The compressor according to at least one embodiment of the present invention is
A casing including a main flow path and a sub-flow path including a bypass path or a recirculation path provided so as to communicate with the main flow path.
A plurality of blades provided in the main flow path and
A flow path cross-sectional area adjusting member configured to be movable from one of the closed positions where the flow path cross-sectional area of the sub-flow path is smaller than the open position or the open position to the other.
It is provided so as to be exposed in the main flow path so as to receive a fluid force, and when the flow rate of the main flow path is the first flow rate, the flow path cross-sectional area adjusting member is located at the open position, and the flow is the first flow rate. The flow path cross-sectional area adjusting member is configured to apply a driving force due to the fluid force to the flow path cross-sectional area adjusting member so that the flow path cross-sectional area adjusting member is located at the closed position when the second flow rate is larger than one flow rate. Tsubasa and
To prepare for.

According to the configuration of (1) above, when the flow rate in the main flow path is the first flow rate, the flow path cross-sectional area adjusting member is arranged at the open position, and the flow from the sub flow path to the main flow path can be formed. Therefore, the surge that may occur in the compressor can be effectively suppressed, and the lower limit of the operating range can be set lower. On the other hand, in the second flow rate larger than the first flow rate, the flow path cross-sectional area adjusting member is arranged at the closed position to regulate the inflow and outflow of the fluid between the main flow path and the sub flow rate. Therefore, it is possible to realize a highly efficient compressor with less loss such as pressure loss. In this way, the flow path cross-sectional area adjusting member can be moved between the closed position and the open position with respect to the sub flow path by the fluid force in the main flow path, so that the operating region of the compressor does not require an external input. It is possible to achieve both expansion and high efficiency.

(2) In some embodiments, in the configuration described in (1) above,
The subflow path is the bypass path including an outlet located upstream in the main flow path from the leading edge of the rotor blade and an inlet located upstream in the main flow path from the outlet.

According to the configuration of (2) above, a compressor including a sub-flow path composed of a bypass path including an outlet arranged upstream of the leading edge of the rotor blade and an inlet arranged further upstream in the main flow path. In, the effect described in (1) above can be enjoyed. That is, in the case of the first flow rate, which is a relatively small flow rate, the bypass path can be opened by the fluid force in the main flow path regardless of the input from the outside, and the generation of surge can be suppressed by the flow from the bypass path. .. On the other hand, in the case of the second flow rate, which is a relatively large flow rate in the main flow path, the bypass path can be blocked by the fluid force in the main flow path regardless of the input from the outside, and the decrease in compression efficiency can be suppressed. Can be done.

(3) In some embodiments, in the configuration described in (2) above,
Further, a pre-turn nozzle arranged in the bypass path is provided.

According to the configuration (3) above, a swirling flow along the rotation direction of the rotor blade can be positively applied into the main flow path from the bypass path in which the pre-swirl nozzle is arranged inside. That is, at the time of the first flow rate, which is a relatively small flow rate, the flow path cross-sectional area adjusting member is arranged at the open position, and the swirling flow from the pre-swivel nozzle can be forcibly supplied into the main flow rate. , The surge that may occur at a small flow rate in the compressor can be suppressed more effectively.

(4) In some embodiments, in the configuration described in (1) above,
The subchannel includes the recirculation path including an inlet located on the inner wall of the casing facing the blade and an outlet located upstream of the blade front edge in the main channel. Is.

According to the configuration of (4) above, the recirculation path (or recirculation) including the inlet arranged on the downstream side of the leading edge of the rotor blade and the outlet arranged on the upstream side of the leading edge in the main flow path. The effect described in (1) above can be enjoyed in the compressor including the sub-flow path formed by the flow path). That is, in the case of the first flow rate, which is a relatively small flow rate, the recirculation path can be opened by the fluid force in the main flow path regardless of the input from the outside. Then, the lower limit of the operating region can be lowered by suppressing the generation of the surge due to the swirling flow from the recirculation path. On the other hand, in the case of the second flow rate in which the flow rate in the main flow path is relatively large, the recirculation path can be blocked by the fluid force in the main flow path regardless of the input from the outside, and the decrease in compression efficiency can be suppressed. ..

(5) In some embodiments, in the configuration described in any one of (1) to (4) above,
The flow path cross-sectional area adjusting member is arranged so as to open and close the outlet of the sub flow path.
The blade element is attached to the flow path cross-sectional area adjusting member on the downstream side in the main flow path and on the upstream side of the leading edge of the moving blade from the outlet.

According to the configuration of (5) above, since the outlet of the sub-flow path is opened and closed by the flow path cross-sectional area adjusting member, the presence or absence of the flow from the sub-flow path to the main flow path is effectively switched. be able to. Further, since the blade element of the flow path cross-sectional area adjusting member is arranged downstream from the outlet of the subchannel, the fluid force including the influence of the flow from the outlet can be effectively applied to the blade element. ..

(6) In some embodiments, in the configuration described in (5) above,
When the flow path cross-sectional area adjusting member is arranged at the open position, the distance between the upstream end of the blade element and the downstream end of the outlet in the flow direction of the main flow direction is the flow direction. It is configured to be 20% or more of the length of the wing element along the line.

A swirling flow having a swirling component along the rotation direction of the rotor blade is generally supplied from the outlet of the subflow path, and this swirling flow flows diagonally into the main flow path and acts on the rotor blade. According to the configuration of (6) above, since the blade elements are arranged at a distance of 20% or more of the blade length of the blade elements from the outlet of the subchannel, the flow from the outlet is obstructed by the blade elements. It can act on the moving blades.

(7) In some embodiments, in the configuration according to any one of (5) or (6) above.
The flow path cross-sectional area adjusting member is configured to block only a part of the outlet when it is arranged in the closed position.

According to the configuration (7) above, even in a state where the flow path cross-sectional area adjusting member is arranged at the closed position, a part of the flow from the sub flow path can flow into the main flow path. Therefore, at the time of the second flow rate, which is a relatively large flow rate, a turning component along the rotation direction of the moving blade can be added to the flow supplied to the moving blade, so that the compression efficiency can be further improved. can.

(8) In some embodiments, in the configuration according to any one of (1) to (7) above,
The flow path cross-sectional area adjusting member is formed in an annular shape centered on an axis parallel to the flow direction of the main flow path at least in part along the inner wall of the casing defining the main flow path.

According to the configuration of (8) above, the flow path cross-sectional area adjusting member can be aligned with the inner wall of the casing, and the flow path cross-sectional area adjusting member can be integrally configured along the circumferential direction of the inner wall of the casing. Thereby, within the movement range including the closed position and the open position, the flow path cross-sectional area adjusting member can be smoothly guided along the inner wall of the casing. Further, when a plurality of sub-channels are formed in the circumferential direction of the inner wall of the casing, the plurality of sub-channels can be opened and closed at once by the channel cross-sectional area adjusting member formed in an annular shape.

(9) In some embodiments, in the configuration according to any one of (1) to (8) above,
The casing is configured to guide the flow path cross-sectional area adjusting member so that the flow path cross-sectional area adjusting member moves between the closed position and the open position along the flow direction in the main flow path. Including the guide section.

According to the configuration of (9) above, the flow path cross-sectional area adjusting member is guided to the closed position and the open position along the guide portion. When the second flow rate is relatively large in the main flow path, the flow in the main flow path is in a forward flow state, so that the flow path cross-sectional area adjusting member is smoothly moved to the closed position along the forward flow. be able to. Further, by appropriately setting the positions of the upstream end and the downstream end of the guide portion in the flow direction of the main flow path and the positions of the blade elements of the flow path cross-sectional area adjusting member, the flow path cross-sectional area adjusting member can be made. The operating flow rate, that is, the operating range of the compressor can be set arbitrarily.

(10) In some embodiments, in the configuration according to any one of (1) to (9) above,
The blade element includes a convex curved surface facing the upstream side of the main flow path and a concave curved surface facing the downstream side of the main flow path and the upstream side in the rotational direction of the rotor blade.
The length of the blade element is 80% or less of the length of the moving blade with respect to the flow direction of the main flow path.

In the case of the first flow rate, which is a small flow rate in the main flow path, a turn having a turning component in the circumferential direction intersecting the rotation axis of the moving blade due to the flow from the sub flow path and the rotation of the moving blade. The flow can act on the blades. In this respect, according to the configuration of (10) above, since the concave curved surface of the blade is configured to face the downstream side of the main flow path and the upstream side in the rotational direction of the rotor blade, the concave curved surface is received. By guiding the swirling flow to the upstream side of the main flow path, it is possible to obtain a driving force for moving the flow path cross-sectional area adjusting member to the open position. On the other hand, when the flow rate of the main flow path is larger than the first flow rate, the dynamic pressure of the main flow acts on the convex curved surface of the blade element, and the flow path cross-sectional area adjusting member is moved to the closed position. At that time, since the convex curved surface of the blade element faces the upstream side of the main flow path, the flow from the upstream side of the main flow path can be smoothly guided to the downstream side. Therefore, it is possible to suppress the decrease in efficiency due to the pressure loss.

(11) In some embodiments, in the configuration according to any one of (1) to (10) above,
The flow path cross-sectional area adjusting member is
A plate member capable of closing at least a part of the sub-flow path, and
It includes a connecting portion that movably connects the plate member and the blade element in a direction different from the direction of the movement according to the movement of the blade element.

According to the configuration of (11) above, the plate member that blocks the auxiliary flow path can be moved in the direction opposite to that of the blade element in the axial flow direction. This makes it possible to improve the degree of freedom in designing the compressor.

(12) In some embodiments, in the configuration according to any one of (1) to (11) above,
The flow path cross-sectional area adjusting member is
A flow rate regulating unit arranged at the outlet of the sub-flow path in the closed position,
It includes an opening arranged on the upstream side in the moving direction toward the open position with respect to the flow rate regulating portion.

According to the configuration of (12) above, for example, in the flow path cross-sectional area adjusting member, the sub-flow path is opened and closed by using the end portion on the upstream side or the downstream side in the moving direction toward the open position or the closed position. When the width of the outlet of the sub-flow path is larger than the opening, the size of the opening can be restricted. Therefore, the degree of freedom in designing the rotating machine can be improved.

(13) In some embodiments, in the configuration described in (12) above,
The flow path cross-sectional area adjusting member includes the opening, which is smaller than that of the blade element.

According to the configuration of (13) above, by configuring the number of openings to be smaller than the number of blade elements, it is possible to secure each opening larger in the circumferential direction around the axial flow direction. Thereby, for example, the effect of the swirling flow applied to the rotor blade from the sub flow path can be further ensured.

(14) In some embodiments, in the configuration according to any one of (1) to (13) above,
A backflow region where backflow can occur is distributed in the vicinity of the inner circumference of the casing, which is a region including at least the leading edge of the rotor blade and its upstream along the axial flow direction and defines the main flow path.
The flow path cross-sectional area adjusting member is configured such that at least the blade element is arranged in the backflow region.

According to the configuration of (14) above, the fluid force due to the backflow can be reliably applied to the blade element at the time of the first flow rate of a relatively small flow rate. Therefore, since it is possible to obtain a flow path cross-sectional area adjusting member having high responsiveness to changes in the flow rate, it is possible to more reliably achieve expansion of the operating region of the compressor and high efficiency.

(15) In some embodiments, in the configuration according to any one of (1) to (14) above,
The compressor includes a turbocharger.

According to the configuration of (15) above, the effect described in any one of (1) to (14) above can be enjoyed in a turbocharger for automobiles or ships.

According to at least one embodiment of the present invention, it is possible to achieve both expansion of the operating range of the compressor and high efficiency without requiring an external input.

It is a side sectional view which shows the structure of the compressor which concerns on one Embodiment. It is a side sectional view which shows the flow path cross-sectional area adjusting member of the compressor which concerns on one Embodiment, (a) shows the state which was arranged in an open position, (b) shows the state which was arranged in a closed position. It is a side sectional view which shows the structural example of the compressor which concerns on other embodiment. It is a schematic diagram which shows the closed state of the flow path cross-sectional area adjusting member in one Embodiment. It is an axial sectional view of the flow path cross-sectional area adjusting member in one Embodiment. It is a schematic diagram which shows the fluid force acting on a blade element in one Embodiment. It is a schematic diagram which shows the structural example of the flow path cross-sectional area adjusting member in another embodiment, (a) shows an open position, (b) shows a closed position. It is a schematic diagram which shows the structural example of the flow path cross-sectional area adjusting member in another embodiment, (a) shows an open position, (b) shows a closed position. It is a schematic diagram which shows the flow near the moving blade in one embodiment, (a) shows the 1st state of forward flow, and (b) shows the 2nd state where backflow occurs.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, but are merely explanatory examples. do not have.
For example, expressions that represent relative or absolute arrangements such as "in one direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a tolerance or a state of relative displacement at an angle or distance to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the existing state.
For example, the expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or a chamfer within the range where the same effect can be obtained. It shall also represent the shape including the part and the like.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions excluding the existence of other components.

FIG. 1 is a schematic view showing a configuration of a compressor according to an embodiment. FIG. 2 is a side sectional view showing a flow path cross-sectional area adjusting member of a compressor according to an embodiment, in which (a) is arranged in an open position and (b) is arranged in a closed position. show.
As shown in FIGS. 1 and 2, the compressor 1 according to at least one embodiment of the present invention is, for example, a device (centrifugal compressor) for sending compressed air to an internal combustion engine, and has a main flow rate 14 and the mainstream. A casing 2 including a bypass path 20A provided so as to communicate with the path 14 or a sub-flow path 20 including a recirculation path (or recirculation flow path) 20B, and a plurality of motions provided in the main flow path 14. The blade 6 and the flow path cross-sectional area adjusting member 30 configured to be movable from one of the open position P1 or the closed position P2 having a smaller flow path cross-sectional area of the sub-flow path 20 than the open position P1 to the other. It is provided so as to be exposed in the main flow path 14 so as to receive fluid force, and when the flow of the main flow path 14 is the first flow rate, the flow path cross-sectional area adjusting member 30 is located at the open position P1 and the flow is the first flow rate. With the blade element 38 configured to apply the driving force due to the fluid force to the flow path cross-sectional area adjusting member 30 so that the flow path cross-sectional area adjusting member 30 is located in the closed position at the time of the second flow rate larger than , Is equipped.

The casing 2 has a substantially cylindrical internal space, and the air flowing in from the opening at one end of the central axis 10 of the cylinder is radially radial due to the rotation of the impeller (impeller) 4 arranged at the other end. A flow path (main flow path 14) for compressing and sending air to the compression chamber 12 arranged in the tangential direction of the impeller 4 is defined. An auxiliary flow path 20 may be formed by arranging, for example, an annular member 3 inside the casing 2. In this case, the main flow path 14 is the passage path of the main flow 50 from the opening to the impeller 4 through the inside of the annular member 3, and the bypass path 20A (the bypass path 20A) between the annular member 3 and the casing 2 is used as the auxiliary flow path 20. The flow passing through the inside is a side flow 56).
The impeller 4 is rotatably provided around a rotation axis (not shown) coaxial with the central axis 10. The impeller 4 is provided with a plurality of moving blades 6 (blades) along the circumferential direction.
The rotor blade 6 is formed so as to send out the air flowing in from the upstream in the axial direction in the tangential direction (or the radial direction) on the downstream side.
The flow path cross-sectional area adjusting member 30 is arranged on the upstream side of the leading edge 8 which is the end of the moving blade 6 on the most upstream side in the main flow path 14, and reciprocates between the open position P1 and the closed position P2. It is provided so that it can be moved. For convenience of explanation, the upper half of FIG. 1 shows a state in which the flow path cross-sectional area adjusting member 30 is arranged at the open position P1, and the lower half of FIG. 1 shows the flow path cross-sectional area adjusting member 30 at the closed position P2. It shows the state of being placed in.
The blade element 38 is driven by receiving a fluid force based on a flow (for example, an air flow) in the main flow path 14. For example, the blade element 38 obtains a driving force from a forward flow flowing from the upstream side to the downstream side in the main flow path 14, a backflow from the downstream side to the upstream side, or a swirling flow flowing around the central axis from the upstream side. A driving force toward the downstream, the downstream to the upstream, or the circumferential direction around the central axis 10 can be applied to the flow path cross-sectional area adjusting member 30.

According to the above configuration, when the flow rate in the main flow path 14 is the first flow rate, the flow path cross-sectional area adjusting member 30 is arranged at the open position P1 to form a flow from the sub flow path 20 into the main flow path 14. can. Therefore, since the surge that may occur in the compressor 1 can be effectively suppressed, the lower limit of the operating range can be set lower. The first flow rate can be set so that the flow in the main flow path 14 is relatively slow and a swirling flow or a backflow around the central axis 10 can occur. On the other hand, in the second flow rate larger than the first flow rate, the flow path cross-sectional area adjusting member 30 is arranged at the closed position P2, and the inflow and outflow of the fluid is restricted between the main flow path 14 and the sub flow path 20. Therefore, it is possible to realize a highly efficient compressor 1 with less loss such as pressure loss. In this way, the flow path cross-sectional area adjusting member 30 can be moved to the closed position P2 and the open position P1 with respect to the sub flow path 20 by the fluid force in the main flow path 14, so that no external input is required. It is possible to achieve both expansion of the operating area of the compressor 1 and high efficiency.

In some embodiments, in the above configuration, the subchannel 20 has an outlet 24 located upstream of the leading edge 8 of the blade 6 in the main channel 14 and an outlet 24 upstream of the outlet 24 in the main channel 14. It may be a bypass path 20A including an inlet 22 located at (see, eg, FIG. 1, FIG. 2 and FIG. 8). In this way, in the main flow path 14, the sub-flow path composed of the bypass path 20A including the outlet 24 arranged on the upstream side of the leading edge 8 of the rotor blade 6 and the inlet 22 arranged on the further upstream side in the main flow path 14. The above-mentioned effects can be enjoyed in the compressor 1 including the 20. That is, in the case of the first flow rate, which is a relatively small flow rate, the bypass path 20A can be opened by the fluid force in the main flow path 14 regardless of the input from the outside. Generally, a flow having a turning component along the rotation of the impeller 4 (or blade 6) is supplied from the outlet 24 of the bypass path 20A to the main flow path 14. In this way, by imparting a turning component in the same direction as the rotation of the impeller 4 to the flow flowing into the impeller 4 in advance, the inflow angle to the rotor blade 6 can be made to follow the chord direction of the rotor blade 6. , Peeling is suppressed and surge is suppressed. Therefore, the generation of the surge can be suppressed by the flow from the bypass path 20A. On the other hand, in the case of the second flow rate in which the flow rate in the main flow path 14 is relatively large, the bypass path 20A can be blocked by the fluid force in the main flow path 14 regardless of the input from the outside, so that the compression efficiency is lowered. Can be suppressed.

In some embodiments, the compressor 1 may further include a pre-swivel nozzle 26 located in the bypass path 20A (see, eg, FIG. 2).
The pre-swivel nozzle 26 forcibly applies a swivel component in the same direction as the rotation of the impeller 4 to the flow flowing into the impeller 4 in advance, thereby suppressing a decrease in the rotation efficiency of the impeller 4 and improving the compression efficiency. Is intended. With the configuration provided with the pre-swivel nozzle 26 in this way, the swirl flow 58 along the rotation direction of the rotor blade 6 is positively generated in the main flow path 14 from the bypass path 20A in which the pre-swivel nozzle 26 is arranged. Can be granted. That is, at the time of the first flow rate, which is a relatively small flow rate, the flow path cross-sectional area adjusting member 30 is arranged at the open position P1, and the swirling flow 58 from the pre-swirl nozzle 26 is forcibly supplied into the main flow path 14. Therefore, it is possible to more effectively suppress the surge that may occur when the flow rate is small in the compressor 1.

FIG. 3 is a side sectional view showing a configuration example of a compressor according to another embodiment.
As illustrated in FIG. 3 without limitation, in some embodiments, the subchannel 20 has an inlet 22 located on the inner wall of the casing 2 facing the rotor blade 6 and a leading edge 8 of the rotor blade 6. It may be a recirculation path 20B including an outlet 24 arranged on the upstream side of the main flow path 14.
That is, the recirculation path 20B has an inlet 22 arranged on the downstream side in the main flow path 14 from the leading edge 8 of the rotor blade 6 and an outlet arranged on the upstream side in the main flow path 14 from the leading edge 8 of the rotor blade 6. It may be a return path including 24.
When the recirculation path 20B as described above is provided in the compressor 1, a flow having a swirling component accompanying the rotation of the impeller 4 from the inlet 22 arranged on the outer peripheral side of the rotating impeller 4 (secondary flow 56). Is sent to the upstream side and returned to the mainstream 50 from the outlet 24. Therefore, the apparent flow rate is increased in the main flow path 14, and the flow velocity is increased. As a result, the inflow angle to the rotating rotor blade 6 can be made along the cord direction of the rotor blade 6, so that the peeling is suppressed and the surge is suppressed.
According to the above configuration, in the recirculation path 20B including the inlet 22 arranged on the downstream side of the leading edge 8 of the rotor blade 6 and the outlet 24 arranged on the upstream side of the leading edge 8 in the main flow path 14. The above-mentioned effect can be enjoyed in the compressor 1 including a certain sub-channel 20. That is, in the case of the first flow rate, which is a relatively small flow rate, the recirculation path 20B can be opened by the fluid force in the main flow path 14 regardless of the input from the outside. Then, by suppressing the generation of the surge in the swirling flow 58 from the recirculation path 20B, the lower limit of the operating region can be lowered. On the other hand, when the second flow rate is relatively large in the main flow path 14, the recirculation path 20B is blocked by the fluid force in the main flow path 14 regardless of the input from the outside, and the decrease in compression efficiency is suppressed. be able to.

In some embodiments, in any of the above configurations, the flow path cross-sectional area adjusting member 30 may be arranged to open and close the outlet 24 of the sub-flow passage 20 (eg, FIGS. 1 to 3 and). See FIG. 8). Further, the blade element 38 may be attached to the flow path cross-sectional area adjusting member 30 on the downstream side of the main flow path 14 from the outlet 24 and on the upstream side of the leading edge 8 of the moving blade 6 (for example, FIG. 1). See ~ 3). With this configuration, the outlet 24 of the sub-flow path 20 is opened and closed by the flow path cross-sectional area adjusting member 30, so that the presence or absence of a flow from the sub-flow path 20 to the main flow path 14 is effective. Can be switched to. Further, since the blade element 38 of the flow path cross-sectional area adjusting member 30 is arranged downstream of the outlet 24 of the auxiliary flow path 20, the blade element 38 effectively exerts the fluid force including the influence of the flow from the outlet 24. Can act on.
In another embodiment, for example, the inlet 22 of the sub-flow path 20 may be configured to be opened and closed by the flow path cross-sectional area adjusting member 30. With such a configuration, it is possible to obtain the same effect as the configuration in which the outlet 24 is opened and closed by the flow path cross-sectional area adjusting member 30. Further, in another embodiment, both the inlet 22 and the outlet 24 of the sub-flow path 20 may be opened and closed by the flow path cross-sectional area adjusting member 30.

In some embodiments, the flow path cross-sectional area adjusting member 30 is arranged in the open position P1 as illustrated in FIGS. 2 (a) and 2 (b), for example, when the main flow path is arranged. A blade whose distance L1 between the upstream end 38A of the blade element 38 (see FIG. 2B) and the downstream end 24B of the outlet 24 (see FIG. 2A) in the flow direction of 14 is along the flow direction. It may be configured to be 20% or more of the length (wing element length) L2 of the element 38.
A swirling flow 58 (see FIG. 4) having a swirling component along the rotation direction of the rotor blade 6 is generally supplied from the outlet 24 of the subflow path 20, and the swirling flow 58 is obliquely flowed into the main flow path 14 to move. It acts on the blade 6. Therefore, by arranging the blade element 38 on the downstream side at a distance of 20% or more of the blade length L2 of the blade element 38 from the outlet 24 of the auxiliary flow path 20, the flow from the outlet 24 is caused by the blade element 38. It can act on the moving blade 6 without hindering it.

FIG. 4 is a schematic view showing a closed state of the flow path cross-sectional area adjusting member in one embodiment.
As illustrated in FIG. 4 without limitation, in some embodiments, in the configuration according to any one of the above, the flow path cross-sectional area adjusting member 30 exits when it is arranged at the closed position P2. It may be configured to block only a part of 24. With this configuration, even in a state where the flow path cross-sectional area adjusting member 30 is arranged at the closed position P2, a part of the flow from the sub flow path 20 can flow into the main flow path 14. Therefore, at the time of the second flow rate, which is a relatively large flow rate, a turning component along the rotation direction of the moving blade 6 can be added to the flow supplied to the moving blade 6, so that the compression efficiency can be further improved. be able to.

FIG. 5 is an axial cross-sectional view of the flow path cross-sectional area adjusting member in one embodiment.
As illustrated in FIG. 5, in some embodiments, in any of the above configurations, the flow path cross-sectional area adjusting member 30 is along the inner wall of the casing 2 that defines the main flow path 14. Further, at least a part thereof may include an annular portion 34 formed in an annular shape centered on an axis parallel to the flow direction of the main flow path 14. With this configuration, the flow path cross-sectional area adjusting member 30 can be aligned with the inner wall of the casing 2, and the flow path cross-sectional area adjusting member 30 can be integrally configured over the circumferential direction of the inner wall of the casing 2. .. As a result, the flow path cross-sectional area adjusting member 30 can be smoothly guided along the inner wall of the casing 2 within the moving range including the closed position P2 and the open position P1. Further, when a plurality of sub-flow paths 20 are formed in the circumferential direction of the inner wall of the casing 2, the plurality of sub-flow paths 20 can be opened and closed at once by the flow path cross-sectional area adjusting member 30 formed in an annular shape.
The flow path cross-sectional area adjusting member 30 may be formed in an arc shape instead of a perfect annular shape in the axial direction.

In some embodiments, the casing 2 has a flow path cross-sectional area adjusting member 30 such that the flow path cross-sectional area adjusting member 30 moves between the closed position P2 and the open position P1 along the flow direction in the main flow path 14. May include a guide section 40 configured to guide (see, for example, FIGS. 2 and 5). Such a guide portion 40 is formed in, for example, a groove-shaped recess formed in either one of the inner wall of the casing 2 and the facing surface of the flow path cross-sectional area adjusting member 30 facing the inner wall, and the other. It may be composed of a convex engaging portion that is slidably (sliding) engaged with the concave portion. With the configuration including the guide portion 40 in this way, the flow path cross-sectional area adjusting member 30 is guided to the closed position P2 and the open position P1 along the guide portion 40. For example, in the case of the second flow rate in which the flow rate in the main flow path 14 is relatively large, the flow in the main flow path 14 is in a forward flow state, so that the flow path cross-sectional area adjusting member 30 is closed along the forward flow. It can be smoothly moved to P2. Further, the positions of the upstream end 40A (see FIG. 2B) and the downstream end 40B (see FIG. 2A) of the guide portion 40 in the flow direction of the main flow path, and the flow path cross-sectional area adjusting member. By appropriately setting the position of the blade element 38 of 30, the flow rate at which the flow path cross-sectional area adjusting member 30 operates, that is, the operating range of the compressor 1 can be arbitrarily set.
The moving direction of the flow path cross-sectional area adjusting member 30 by the guide portion 40 is not limited to the flow direction in the main flow path 14, and depends on the driving force generated by the blade element 38 that has received the flow in the main flow path 14. It may be in the same direction. For example, as illustrated in FIG. 4 without limitation, in a direction that receives a swirling flow 58 from an upstream side to a downstream side in the main flow path 14 and a swirling flow 58 from the sub flow path 20 and intersects the main flow 50. The blade element 38 may be configured to generate a driving force. That is, for example, it may be in the flow direction of the mainstream 50 or in a direction orthogonal to the central axis 10 (circumferential direction of the central axis 10), or may be a driving force in the flow direction of the mainstream 50 or in an oblique direction with respect to the central axis 10. May be configured to generate.

FIG. 6 is a schematic view showing the fluid force acting on the blade element in one embodiment.
As illustrated in FIG. 6 without limitation, in some embodiments, the blade element 38 has a convex curved surface 38B facing the upstream side of the main flow path 14 and a moving blade 6 downstream of the main flow path 14. The length of the blade element 38 includes the concave curved surface 38C facing the upstream side in the rotation direction of the blade, and the length of the blade element 38 with respect to the flow direction of the main flow path 14 (the direction from the upstream side to the downstream side along the central axis 10). It may be configured to be 80% or less of the length of the rotor blade 6.
In the case of the first flow rate, which is a small flow rate in the main flow path 14, it has a turning component in the circumferential direction intersecting the central axis 10 due to the flow from the sub flow path 20 and the rotation of the rotor blade 6. The swirling flow 58 (see FIG. 4) can act on the blade element 38. In this respect, if it is configured as described above, the concave curved surface 38C of the blade element 38 is configured to face the downstream side of the main flow path 14 and the upstream side in the rotational direction of the moving blade 6, so that the concave curved surface 38C By guiding the swirling flow 58 received in the above to the upstream side of the main flow path 14, it is possible to obtain a driving force for moving the flow path cross-sectional area adjusting member 30 to the open position P1. On the other hand, when the flow of the main flow path 14 is larger than the first flow rate, the dynamic pressure of the main flow (forward flow) 50 acts on the convex curved surface 38B of the blade element 38, and the flow path cross-sectional area adjusting member 30 Is moved to the closed position P2. At that time, since the convex curved surface 38B of the blade element 38 faces the upstream side of the main flow path 14, the flow from the upstream side in the main flow path 14 can be smoothly guided to the downstream side. Therefore, it is possible to suppress the decrease in efficiency due to the pressure loss.

7A and 7B are schematic views showing a configuration example of a flow path cross-sectional area adjusting member in some embodiments, in which FIG. 7A shows an open position and FIG. 7B shows a closed position. 8A and 8B are schematic views showing a configuration example of a flow path cross-sectional area adjusting member in another embodiment, in which FIG. 8A shows an open position and FIG. 8B shows a closed position.
As illustrated in FIGS. 7 and 8, in some embodiments, the channel cross-sectional area adjusting member 30 includes a plate member 32 capable of closing at least a part of the subchannel 20 and the plate. The member 32 and the blade element 38 may include a connecting portion 44 that movably connects the plate member 32 in a direction different from the direction of the movement according to the movement of the blade element 38.
The "direction different from the moving direction of the blade element 38" may be, for example, an oblique direction with respect to the moving direction of the blade element 38, or may be a direction opposite to the moving direction of the blade element 38.
For example, as illustrated in FIG. 7, the plate member 32 and the blade element 38 may be connected via the wire 45 as the connecting portion 44 and the support portion 46 of the wire 45. In this case, for example, when the blade element 38 moves from the downstream side to the upstream side of the main flow path 14 due to the fluid force of the backflow 52 when the inside of the main flow path 14 is the first flow rate, the plate is passed through the wire 45 and the support portion 46. The member 32 is pulled in the opposite direction, that is, toward the downstream side and driven, and the flow path cross-sectional area adjusting member 30 is arranged at the open position P1 (see FIG. 7A). On the other hand, at the time of the second flow rate, the blade element 38 is driven to the downstream side, and the plate member 32 is driven to the upstream side and arranged at the closed position P2 (see FIG. 7B). In some embodiments, an elastic member (eg, a spring or the like) for urging such a plate member 32 toward the closed position P2 may be provided.
Further, as shown in FIG. 8 without limitation, a link mechanism 47 that guides the plate member 32 and the blade element 38 in the opposite directions may be adopted as the connecting portion 44. In this case, the other ends of the link, one end of which is connected to the plate member 32 and the blade element 38, are rotatably connected to each other so that each node moves along a predetermined trajectory. The 38 and the plate member 32 can be moved in different directions. Further, by appropriately setting the length of each link, the movement distance of the blade element 38 and the movement distance of the plate member 32 due to the movement of the blade element 38 can be configured to be different from each other.
According to the configuration including the connecting portion 44 as described above, the plate member 32 that closes the auxiliary flow path 20 can be moved in a direction different from the moving direction of the blade element 38. This makes it possible to improve the degree of freedom in designing the compressor 1.

In some embodiments, in any of the above configurations, the flow path cross-sectional area adjusting member 30 has a flow rate control section 32A arranged at the outlet 24 of the sub-flow rate 20 at the closed position P2 and the flow rate control. It may include an opening 36 arranged on the upstream side in the moving direction toward the open position P1 with respect to the portion 32A (see, for example, FIGS. 2 and 3).
According to the configuration in which the flow path cross-sectional area adjusting member 30 includes the opening 36, for example, the upstream or downstream end of the flow path cross-sectional area adjusting member 30 in the moving direction toward the open position P1 or the closed position P2. Compared to a configuration in which the sub-flow path 20 is opened and closed using a portion (see, for example, FIGS. 1, 4, and 7), for example, when the width of the outlet 24 of the sub-flow path 20 is larger than that of the opening 36, the opening is widened. It can be regulated by the size of the part. Therefore, the degree of freedom in designing the compressor 1 can be improved.
The opening area of the opening 36 may be larger than the cross-sectional area of the outlet 24 of the subchannel 20. Further, such an opening 36, the blade element 38, and the moving blade 6 of the impeller 4 may be arranged at equal intervals along the circumferential direction of the central axis 10.

In some embodiments, the flow path cross-sectional area adjusting member 30 may include a smaller number of openings 36 than the blade element 38. By configuring the number of openings 36 to be smaller than the number of blade elements 38 in this way, it is possible to secure a larger number of openings 36 in the circumferential direction around the rotation axis of the rotor blade 6. Thereby, for example, the effect of the swirling flow 58 applied to the rotor blade 6 from the sub flow path 20 can be further ensured.

9A and 9B are schematic views showing the flow near the rotor blade in one embodiment, where FIG. 9A shows a first state of forward flow and FIG. 9B shows a second state in which backflow occurs.
In some embodiments, a region including at least the leading edge 8 of the rotor blade 6 and its upstream along the axial flow direction due to the rotation of the rotor blade 6 and near the inner circumference of the casing 2 defining the main flow path 14. The backflow region 54 in which the backflow 52 can occur is distributed (see FIG. 9B), and the flow path cross-sectional area adjusting member 30 may be configured such that at least the blade elements 38 are arranged in the backflow region 54. With this configuration, the fluid force due to the backflow can be reliably applied to the blade element 38 at the time of the first flow rate, which is a relatively small flow rate. Therefore, since the flow path cross-sectional area adjusting member 30 having high responsiveness to the change in the flow rate can be obtained, it is possible to more reliably achieve the expansion of the operating region of the compressor 1 and the improvement of efficiency.

In some embodiments, the compressor 1 may include a turbocharger. That is, the compressor 1 may be a turbocharger compressor that is arranged on the intake side of the internal combustion engine and rotates the impeller 4 by a rotation shaft common to the exhaust turbine that rotates using the exhaust energy of the internal combustion engine. By doing so, it is possible to enjoy the effect described in any of the above in a turbocharger for automobiles or ships.

According to at least one embodiment of the present invention, it is possible to achieve both expansion of the operating region of the compressor 1 and high efficiency without requiring an external input. Further, by not requiring an input from the outside, for example, it is possible to improve the mountability on an engine or the like, and it is possible to simplify the configuration and reduce the cost.

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

1 Compressor (turbocharger)
2 Casing 3 Circular member 4 Impeller 6 Blade 8 Leading edge 10 Rotating shaft 12 Compression chamber 14 Main flow path 20 Sub flow path 20A Bypass path 20B Recirculation path 22 Inlet 24 Outlet 24B Downstream side end 26 Pre-swivel nozzle 30 Flow path disconnection Area adjustment member 32 Plate member 32A Flow control part 34 Circular part 36 Opening part 38 Wing element 38A Upstream side end part 38B Convex curved surface 38C Concave curved surface 40 Guide part 40A Upstream side end part 40B Downstream side end part 42 Engaging part (Convex part)
44 Connecting part 45 Wire 46 Support part 47 Link mechanism 50 Forward flow 52 Backflow 54 Backflow area 56 Side flow 58 Swirling flow P1 Open position P2 Closed position L1 Distance between the downstream end of the outlet and the upstream end of the blade element (open) position)
L2 wing element length

Claims (15)

A casing including a main flow path and a sub-flow path including a bypass path or a recirculation path provided so as to communicate with the main flow path.
A plurality of blades provided in the main flow path and
A flow path cross-sectional area adjusting member configured to be movable from one of the closed positions where the flow path cross-sectional area of the sub-flow path is smaller than the open position or the open position to the other.
It is provided so as to be exposed in the main flow path so as to receive a fluid force, and when the flow rate of the main flow path is the first flow rate, the flow path cross-sectional area adjusting member is located at the open position, and the flow is the first flow rate. The flow path cross-sectional area adjusting member is configured to apply a driving force due to the fluid force to the flow path cross-sectional area adjusting member so that the flow path cross-sectional area adjusting member is located at the closed position when the second flow rate is larger than one flow rate. Tsubasa and
Equipped with
The flow path cross-sectional area adjusting member is characterized in that it can move from one of the open position or the closed position to the other by the fluid force acting on the blade element without depending on an external input. Compressor. The subflow path is the bypass path including an outlet located upstream in the main flow path from the leading edge of the rotor blade and an inlet located upstream in the main flow path from the outlet. The compressor according to claim 1. The compressor according to claim 2, further comprising a pre-swirl nozzle arranged in the bypass path. The subchannel includes the recirculation path including an inlet located on the inner wall of the casing facing the blade and an outlet located upstream of the blade front edge in the main channel. The compressor according to claim 1, wherein the compressor is characterized by being. The flow path cross-sectional area adjusting member is arranged so as to open and close the outlet of the sub flow path.
Claims 1 to 1, wherein the blade element is attached to the flow path cross-sectional area adjusting member on the downstream side in the main flow path from the outlet and on the upstream side of the leading edge of the moving blade. The compressor according to any one of 4. When the flow path cross-sectional area adjusting member is arranged at the open position, the distance between the upstream end of the blade element and the downstream end of the outlet in the flow direction of the main flow direction is the flow direction. The compressor according to claim 5, wherein the compressor is configured to have a length of 20% or more of the blade element according to the above. The aspect according to any one of claims 5 or 6, wherein the flow path cross-sectional area adjusting member is configured to close only a part of the outlet when it is arranged in the closed position. Compressor. The flow path cross-sectional area adjusting member is characterized in that at least a part thereof is formed in an annular shape centered on an axis parallel to the flow direction of the main flow path along the inner wall of the casing defining the main flow path. The compressor according to any one of claims 1 to 7. The casing is configured to guide the flow path cross-sectional area adjusting member so that the flow path cross-sectional area adjusting member moves between the closed position and the open position along the flow direction in the main flow path. The compressor according to any one of claims 1 to 8, wherein the compressor includes a guide portion. The blade element includes a convex curved surface facing the upstream side of the main flow path and a concave curved surface facing the downstream side of the main flow path and the upstream side in the rotational direction of the rotor blade.
The compressor according to any one of claims 1 to 9, wherein the length of the blade element is 80% or less of the length of the moving blade with respect to the flow direction of the main flow path. The flow path cross-sectional area adjusting member is
A plate member capable of closing at least a part of the sub-flow path, and
Claims 1 to 10 include a connecting portion that movably connects the plate member and the blade element in a direction different from the direction of the movement according to the movement of the blade element. The compressor according to any one of the above. The flow path cross-sectional area adjusting member is
A flow rate regulating unit arranged at the outlet of the sub-flow path in the closed position,
The compressor according to any one of claims 1 to 11, wherein the compressor includes an opening arranged on the upstream side in a moving direction toward the open position with respect to the flow rate regulating portion. The compressor according to claim 12, wherein the flow path cross-sectional area adjusting member includes a smaller number of openings than the blade element. Backflow of the flow of the main flow path may occur in the vicinity of the inner circumference of the casing which defines the main flow path at least in the region including the leading edge of the rotor blade and its upstream along the axial flow direction of the main flow path. Backflow area is distributed,
The compressor according to any one of claims 1 to 13, wherein the flow path cross-sectional area adjusting member is configured such that at least the blade elements are arranged in the backflow region. The compressor according to any one of claims 1 to 14, wherein the compressor includes a turbocharger.

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