阅读说明：本技术 离心压缩机及涡轮增压器 (Centrifugal compressor and turbocharger ) 是由 岩切健一郎 藤田豊 林良洋 于 2018-07-06 设计创作，主要内容包括：离心压缩机具备：叶轮；压缩机入口管,其将空气向叶轮引导；涡旋流路,其设置于叶轮的外周侧；旁通流路,其从涡旋流路经由分支口分支,绕过叶轮与压缩机入口管连接；旁通阀,其可开闭设置于旁通流路的阀口,分支口在沿着经过分支口的中心的分支口的法线N1观察时具有非圆形形状。(The centrifugal compressor comprises: an impeller; a compressor inlet duct that guides air toward the impeller; a scroll flow path provided on an outer peripheral side of the impeller; a bypass flow path that branches from the scroll flow path through a branch port and is connected to the compressor inlet pipe while bypassing the impeller; and a bypass valve which can open and close a valve port provided in the bypass flow path, wherein the branch port has a non-circular shape when viewed along a normal N1 to the branch port passing through the center of the branch port.)

1. A centrifugal compressor is provided with:

an impeller;

a compressor inlet duct that directs air toward the impeller;

a scroll flow path provided on an outer peripheral side of the impeller;

a bypass flow path that branches from the scroll flow path via a branch port and is connected to the compressor inlet pipe while bypassing the impeller;

a bypass valve that opens and closes a valve port provided in the bypass flow path;

the branch portal has a non-circular shape when viewed along a normal N1 of the branch portal passing through a center of the branch portal.

2. The centrifugal compressor of claim 1,

when a flow path cross section including the center of the branch port in the scroll flow path is denoted by G, a dimension T of the branch port in a flow direction F orthogonal to the flow path cross section G is smaller than a dimension L of the branch port in a direction H orthogonal to the flow direction F and the normal N1, respectively.

3. The centrifugal compressor according to claim 1 or 2,

the length of the branch port is larger than the caliber of the valve port, and the width of the branch port is smaller than the caliber of the valve port.

4. A centrifugal compressor according to any one of claims 1 to 3,

when the opening area of the valve port is set to S1 and the opening area of the branch port is set to S2,

satisfies 0.8S1 ≦ S2 ≦ 1.2S 1.

5. The centrifugal compressor according to any one of claims 1 to 4,

a width Te of the branch port at an end portion of the branch port in the radial direction of the impeller is smaller than a width Tc of the branch port at a central portion of the branch port in the radial direction of the impeller.

6. The centrifugal compressor according to any one of claims 1 to 5,

the center of the branch port is offset to the inside in the radial direction of the impeller with respect to the center of the valve port.

7. The centrifugal compressor according to any one of claims 1 to 6,

the longitudinal direction of the branch port is orthogonal to the flow direction orthogonal to the flow path cross section of the scroll flow path.

8. The centrifugal compressor according to any one of claims 1 to 7,

in a flow path cross section G including the center of the branch port of the scroll flow path, a vector representing the center position of the branch port with respect to the center position of the flow path cross section G is defined as P,

When a vector representing a flow direction perpendicular to the flow path section G is denoted by Q, an outer product of the vector P and the vector Q is denoted by R (═ P × Q), and a vector parallel to the longitudinal direction of the branch port is denoted by V,

one of an inner product V.R of the vector V and the vector R and an inner product V.Q of the vector V and the vector Q has a positive value, and the other has a negative value.

9. A turbocharger provided with:

the centrifugal compressor of any one of claims 1 to 8, and a turbine sharing a rotational axis with an impeller of the centrifugal compressor.

Technical Field

The present disclosure relates to a centrifugal compressor and a turbocharger.

Background

In a centrifugal compressor for a turbocharger, a bypass valve (also referred to as a bleed valve or a recirculation valve) may be provided at an outlet of the centrifugal compressor in order to avoid an excessive increase in discharge pressure of the compressor. In this configuration, when the discharge pressure of the compressor is excessive, the bypass valve is opened, and the discharge air of the compressor is returned to the inlet side of the compressor via the bypass flow path.

On the other hand, the provision of such a bypass flow path also leads to an increase in pressure loss. As shown in fig. 24, although a circulating flow is formed in the bypass flow passage by shearing with the main flow, when almost no flow flows from the main flow into the bypass flow passage, pressure loss hardly occurs. On the other hand, as shown in fig. 25 and 26, when a large amount of the flow from the main flow flows into the bypass flow path, the flow flowing into the bypass flow path may be swirled and may flow out to the main flow again. At this time, the swirling flow flowing out interferes with the main flow to generate a large pressure loss as shown in fig. 25. In this case, the compressor efficiency may be significantly reduced (sometimes 5% or more).

Disclosure of Invention

Problems to be solved by the invention

In order to solve such a problem of an increase in pressure loss, patent document 1 proposes forming a surface of a valve body of a bypass valve in a shape along an inner wall of a scroll passage of a compressor. With this configuration, an increase in pressure loss due to the flow flowing into the bypass flow path can be suppressed.

However, since general-purpose products are often used for the valve, the surface of the valve body needs to be formed into a special shape along the inner wall of the pipe using a special-purpose product, which increases the cost.

At least one embodiment of the present invention has been made in view of the above-described conventional problems, and an object thereof is to provide a centrifugal compressor and a turbocharger capable of suppressing an increase in pressure loss while suppressing complication of the shape of a valve body of a bypass valve.

Means for solving the problems

(1) A control device according to at least one embodiment of the present invention includes:

an impeller;

a compressor inlet duct that directs air toward the impeller;

a scroll flow path provided on an outer peripheral side of the impeller;

a bypass flow path that branches from the scroll flow path via a branch port and is connected to the compressor inlet pipe while bypassing the impeller;

a bypass valve that opens and closes a valve port provided in the bypass flow path;

the branch port has a non-circular shape when viewed along a normal N1 of the branch port passing through a center of the branch port.

According to the configuration described in (1) above, by using the branch port having the noncircular shape when viewed along the normal line of the branch port, the flow entering the bypass flow path can be prevented from forming a vortex, as compared with the configuration of the related art using the branch port having the circular shape. This can suppress an increase in pressure loss caused by the vortex flow flowing out from the bypass flow passage to the vortex flow passage.

Further, as in the configuration described in patent document 1, even if the surface of the valve body of the bypass valve is not formed into a shape along the inner wall of the pipe, an increase in pressure loss can be suppressed. Therefore, the shape of the valve body of the bypass valve can be prevented from being complicated, and an increase in the pressure loss can be prevented while suppressing an increase in the cost.

In the configuration described in patent document 1, if the valve body of the bypass valve is provided along the inner wall of the scroll flow path, a space for installing the valve body and a space for moving the valve body are required to be provided at a position close to the scroll flow path in the bypass flow path, and a restriction is easily imposed on the layout of the bypass flow path that needs to be connected to the inlet of the compressor.

In contrast, according to the configuration of the above (1), since an increase in pressure loss can be suppressed without providing the valve body of the bypass valve along the inner wall of the scroll flow path, it is not necessary to provide a space for the valve body to move in the vicinity of the scroll flow path in the bypass flow path, and the degree of freedom in layout of the bypass flow path connected to the inlet of the compressor can be improved.

(2) In some embodiments, in the control device according to the above (1),

when a flow path cross section of the scroll flow path including the center of the branch port is denoted by G, a dimension T of the branch port in a flow direction F orthogonal to the flow path cross section G is smaller than a dimension L of the branch port in the flow direction F and a direction H orthogonal to the normal N1, respectively.

According to the control device described in the above (2), since the distance required for the flow of the scroll passage to pass through the branch port is shortened by making the dimension T smaller than the dimension L, the entrance of the flow into the bypass passage can be reduced. In addition, the flow entering the bypass flow path can be effectively prevented from forming a vortex.

(3) In some embodiments, in the control device according to the above (1) or (2),

the length of the branch port is larger than the caliber of the valve port, and the width of the branch port is smaller than the caliber of the valve port.

According to the control device described in the above (3), the flow entering the bypass flow path is effectively blocked from swirling, and an appropriate bypass flow rate at which the flow is bypassed by opening the bypass valve can be easily secured.

(4) In some embodiments, in the control device of any one of (1) to (3) above,

when the opening area of the valve port is set to S1 and the opening area of the branch port is set to S2,

satisfies 0.8S1 ≦ S2 ≦ 1.2S 1.

The opening area of the branch port is preferably small from the viewpoint of reducing the pressure loss associated with the installation of the bypass flow path as much as possible, but if the opening area of the branch port is too small, a sufficient bypass flow rate may not be secured when the bypass valve is opened to bypass the flow. In contrast, as described in (4) above, by making the opening area S2 of the branch port equal to the opening area S1 of the valve port so as to satisfy 0.8S1 ≦ S2 ≦ 1.2S1, it is possible to suppress the generation of swirl in the bypass flow path while securing a required bypass flow rate.

(5) In some embodiments, in the control device of any one of (1) to (4) above,

a width Te of the branch port at an end portion of the branch port in the radial direction of the impeller is smaller than a width Tc of the branch port at a central portion of the branch port in the radial direction of the impeller.

According to the control device described in the above (5), the diffuser outlet flow flowing out from the diffuser of the centrifugal compressor to the scroll flow path is made to flow easily along the inner wall surface of the scroll flow path, which is the outer side in the radial direction of the impeller. Therefore, it is desirable to reduce the width Te of the end portion from the viewpoint of suppressing the inflow of the diffuser outlet flow to the branch port from the end portion on the outer side in the radial direction of the impeller where the diffuser outlet flow easily flows into the branch port. On the other hand, since the bypass flow path must be eventually smoothly connected to the circular shape of the valve port, the width of the center portion of the branch port needs to be increased to some extent. Therefore, as described above, by making the width Te of the outer end portion smaller than the width Tc of the central portion, the bypass flow path can be smoothly connected to the valve port while suppressing the inflow of the diffuser outlet to the branch port.

(6) In some embodiments, in the control device of any one of (1) to (5) above,

the center of the branch port is offset to the inside in the radial direction of the impeller with respect to the center of the valve port.

As described above, the diffuser outlet flow easily flows into the radially outer end portion of the impeller of the branch port. Therefore, as described in (6) above, by offsetting the center of the branch port inward in the radial direction of the impeller with respect to the center of the valve port, the diffuser exit flow flows along the inner wall surface of the scroll flow path and it becomes difficult to flow from the branch port into the bypass flow path, and an increase in pressure loss can be suppressed.

(7) In some embodiments, in the control device of any one of (1) to (6) above,

the longitudinal direction of the branch port is orthogonal to the flow direction orthogonal to the flow path cross section of the scroll flow path.

According to the control device described in (7) above, the distance required for the flow of the scroll flow path to pass through the branch port is shortened, and therefore, the flow can be prevented from entering the bypass flow path. In addition, the flow entering the bypass flow path can be effectively prevented from forming a vortex.

(8) In some embodiments, in the control device of any one of (1) to (7) above,

in a flow path cross section G including the center of the branch port of the scroll flow path, a vector representing the center position of the branch port with respect to the center position of the flow path cross section G is represented by P, a vector representing a flow direction orthogonal to the flow path cross section G is represented by Q, an outer product of the vector P and the vector Q is represented by R (═ P × Q), and a vector parallel to the longitudinal direction of the branch port is represented by V,

one of an inner product V.R of the vector V and the vector R and an inner product V.Q of the vector V and the vector Q has a positive value, and the other has a negative value.

According to the control device described in (8) above, the angle formed by the flow direction of the swirling flow of the scroll passage and the longitudinal direction of the branch port at the position of the branch port can be increased as compared with the case where both the inner products V · E and V · Q of the branch port have positive values and the case where both the inner products V · E and V · Q have negative values, and therefore, the inflow of the swirling flows of the branch port and the scroll passage into the branch port can be effectively suppressed.

(9) A turbocharger according to at least one embodiment of the present invention includes:

the centrifugal compressor according to any one of (1) to (8) above, wherein the turbine shares a rotation shaft with an impeller of the centrifugal compressor.

The control device according to the above (9), which is provided with the centrifugal compressor according to any one of the above (1) to (8), can suppress an increase in pressure loss while suppressing an increase in cost by suppressing complication of the shape of the valve body of the bypass valve.

Effects of the invention

According to at least one embodiment of the present invention, there are provided a centrifugal compressor and a turbocharger capable of suppressing increase in pressure loss while suppressing complication of the shape of a valve body of a bypass valve.

Drawings

Fig. 1 is a partial sectional view showing a schematic structure of a turbocharger 2 according to an embodiment.

Fig. 2 is a partially enlarged view of the centrifugal compressor 4 shown in fig. 1.

Fig. 3A is a perspective view schematically showing the shape of the branch port 20 according to an embodiment.

Fig. 3B is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 in fig. 3A.

Fig. 3C is a diagram for explaining the flow direction F of the scroll passage 14.

Fig. 4A is a perspective view schematically showing the shape of a branch port 20c according to the related art.

Fig. 4B is a diagram showing the shape of the branch port 20c and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20c passing through the center O1 of the branch port 20c in fig. 4A.

Fig. 5 is a diagram for explaining the shape of the branch port 20 shown in fig. 3A and 3B, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment.

Fig. 6 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 7 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 8 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 9 is a diagram for explaining the diffuser outlet flow D.

Fig. 10 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 11 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 12 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 13 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 14 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 15 is a diagram for explaining an effect obtained by shifting the center O1 of the branch port 20 inward in the radial direction I of the impeller with respect to the center O2 of the valve port 22.

Fig. 16 is a diagram for explaining the definition of a vector used in the explanation of some embodiments.

Fig. 17 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 18 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment.

Fig. 19 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment.

Fig. 20 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment.

Fig. 21 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 22 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment.

Fig. 23 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

Fig. 24 is a diagram showing a circulation flow in the bypass flow path along with the inflow of the flow from the spiral flow path to the bypass flow path.

Fig. 25 is a diagram for explaining a state in which a swirl flow flowing out from the bypass flow path interferes with the main flow to cause pressure loss.

Fig. 26 is a diagram for explaining a state in which a swirl flow flowing out from the bypass flow path interferes with the main flow to cause pressure loss.

Detailed Description

Hereinafter, some embodiments of the present invention will be described with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the constituent members described as the embodiments or shown in the drawings are not intended to limit the scope of the present invention to these, and are merely illustrative examples.

For example, the expressions indicating relative or absolute arrangements such as "a certain direction", "along a certain direction", "parallel", "orthogonal", "central", "concentric" or "coaxial" indicate not only arrangements in a strict sense but also states of relative displacement with a tolerance or an angle and a distance to the extent that the same function can be obtained.

For example, the expressions indicating "the same", "equal", and "uniform" are equivalent to each other, and not only are the expressions indicating the equivalent to each other strictly, but also the expressions indicating the difference in tolerance or the degree of obtaining the same function.

For example, the expression "a shape such as a square shape or a cylindrical shape" means not only a shape such as a square shape or a cylindrical shape in a strict geometrical sense but also a shape including a concave-convex portion, a chamfered portion, and the like within a range in which the same effect can be obtained.

On the other hand, the expression "having", "equipped", "provided", "including", or "containing" is not an exclusive expression that excludes the presence of other constituent elements.

Fig. 1 is a partial sectional view showing a schematic structure of a turbocharger 2 according to an embodiment. Fig. 2 is a partially enlarged view of the centrifugal compressor 4 shown in fig. 1.

As shown in fig. 1, the turbocharger 2 includes: a centrifugal compressor 4; a turbine 12 comprising a turbine rotor 10 sharing a rotation axis 8 with the impeller 6 of the centrifugal compressor 4.

The centrifugal compressor 4 includes: an impeller 6; a compressor inlet pipe 40 that guides air toward the impeller 6; a scroll flow path 14 provided on the outer peripheral side of the impeller 6; a bypass flow path 16 that branches from an outlet pipe 38 of the scroll flow path 14 via a branch port 20 and is connected to a compressor inlet pipe 40 while bypassing the impeller 6; and a bypass valve 18 capable of opening and closing a valve port 22 provided in the bypass flow path 16. The bypass valve 18 is opened by the actuator 19 to control the opening and closing operation thereof, and when the discharge pressure of the centrifugal compressor 4 excessively increases, part of the compressed air flowing through the scroll passage 14 is returned to the compressor inlet pipe 40. The valve port 22 is an opening of a valve seat surface 25 that abuts against a valve body 24 of the bypass valve 18.

Fig. 3A is a perspective view schematically showing the shape of the branch port 20 according to an embodiment. Fig. 3B is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 in fig. 3A. Fig. 3C is a diagram for explaining the flow direction F of the scroll passage 14. Fig. 4A is a perspective view schematically showing the shape of a branch port 20c according to the related art. Fig. 4B is a diagram showing the shape of the branch port 20c and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20c passing through the center O1 of the branch port 20c in fig. 4A. In the illustrated exemplary embodiment, the normal N1 of the branch port 20 passing through the center O1 of the branch port 20 coincides with the normal N2 of the branch port 20 passing through the center O2 of the valve port 22, but in other embodiments, the normal N1 and the normal N2 may not coincide with each other. The center O1 of the branch port 20 is the centroid of the branch port 20, and the center O2 of the valve port 22 is the centroid of the valve port 22 (the opening of the valve seat surface 25 that abuts the valve body 24 of the bypass valve 18).

In some embodiments, for example as shown in fig. 3B, the branch port 20 has a non-circular shape that is different from a circular shape when viewed along a normal N1 of the branch port 20 through a center O1 of the branch port 20.

Thus, by using the branch port 20 having a non-circular shape when viewed along the normal N1 of the branch port 20, the flow entering the bypass flow path 16 can be prevented from forming a vortex, compared to the conventional configuration (see fig. 4A and 4B) in which the branch port 20c having a circular shape is used. This can prevent the increase in pressure loss associated with the vortex flow flowing out from the bypass flow path 16 to the vortex flow path 14, which is the problem described with reference to fig. 23 and the like.

In the configuration described in patent document 1, if the valve body of the bypass valve is provided along the inner wall of the scroll flow path, it is necessary to provide an installation space of the valve body and a space in which the valve body moves at a position close to the scroll flow path in the bypass flow path, and restrictions are likely to be imposed on the layout of the bypass flow path connected to the inlet of the compressor.

In contrast, according to the configuration of the above embodiment, since an increase in pressure loss can be suppressed without providing the valve body 24 of the bypass valve 18 along the inner wall of the scroll passage 14, it is not necessary to provide the installation space of the valve body 24 and the space in which the valve body 24 moves at a position close to the scroll passage 14 in the bypass passage 16, and the degree of freedom in layout of the bypass passage 16 connected to the inlet of the compressor 4 can be improved.

Fig. 5 is a diagram for explaining the shape of the branch port 20 shown in fig. 3A and 3B, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment. Fig. 5 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment. Fig. 6 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment. Fig. 7 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment. Fig. 8 is a diagram showing another example of the shape of the branch port 20, and shows the shape of the branch port 20 and the shape of the valve port 22 as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

In some embodiments, as shown in fig. 5 to 8, for example, the swirl flow path 14 has a laterally elongated shape in which the dimension T of the branch port 20 in the flow direction F is smaller than the dimension L of the branch port 20 in the direction H perpendicular to the flow direction F and the normal N1. The flow direction F of the scroll flow path 14 here is a flow direction F perpendicular to the flow path cross section G when the flow path cross section including the center O1 of the branch port 20 of the scroll flow path 14 is denoted by G as shown in fig. 3C. The branch port 20 may have an elliptical shape when viewed from the normal N1 direction as shown in fig. 5 to 7, for example, or may have a rectangular shape as shown in fig. 8. The shape of the branch port 20 illustrated in fig. 5 and 6 is a slit shape when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 5 is a rounded rectangle (a shape formed by two parallel lines of equal length and two semicircles) when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 6 is oval when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 7 is a diamond shape with rounded corners when viewed from the direction of the normal N1.

By making the dimension T smaller than the dimension L in this way, the distance required for the flow of the scroll flow path 14 to pass through the branch port 20 is shortened, and therefore, the inflow of the flow into the bypass flow path 16 can be reduced. In addition, the flow flowing into the bypass flow path 16 can be effectively prevented from forming a vortex.

In some embodiments, as shown in fig. 5 to 8, for example, the length of the branch port 20 (dimension L in direction H in the illustrated exemplary embodiment) is greater than the aperture R of the valve port 22, and the width of the branch port 20 (dimension T in direction F in the illustrated exemplary embodiment) is less than the aperture R.

This effectively prevents the flow entering the bypass flow path 16 from swirling, and makes it easy to ensure an appropriate bypass flow rate when the bypass valve 18 is opened to bypass the flow.

In some embodiments, for example, as shown in fig. 3A, when the opening area of the valve port 22 is set to S1 and the opening area of the branch port 20 is set to S2, 0.8S1 ≦ S2 ≦ 1.2S1 is satisfied.

The opening area of the branch port 20 is preferably small from the viewpoint of reducing the pressure loss associated with the provision of the bypass flow path 16 as much as possible, but if the opening area of the branch port 20 is too small, a sufficient bypass flow rate may not be secured when the bypass valve 18 is opened to bypass the flow. In contrast, as described above, by making the opening area S2 of the branch port 20 equal to the opening area S1 of the valve port 22 so as to satisfy 0.8S1 ≦ S2 ≦ 1.2S1, it is possible to suppress the generation of swirl in the bypass flow path 16 while securing a required bypass flow rate.

In some embodiments, for example, as shown in fig. 5 to 7, the width Te of the end 26 of the branch port 20 on the outer side in the radial direction I of the impeller 6 is smaller than the width Tc of the central portion 28 of the branch port 20.

As shown in fig. 9, the diffuser outlet flow D flowing out from the diffuser 30 of the centrifugal compressor 4 to the scroll flow path 14 easily flows along the inner wall surface 32 on the outer side in the radial direction I of the impeller 6 among the inner wall surfaces of the scroll flow path 14. Therefore, it is desirable to reduce the width Te of the end portion 26 from the viewpoint that the diffuser outlet flow D easily flows into the end portion 26 of the branch port 20 on the outer side in the radial direction I of the impeller 6 and the diffuser outlet flow D is suppressed from flowing into the branch port 20. On the other hand, since the bypass flow path 16 must be smoothly connected to the circular shape of the valve port 22, the width Tc of the central portion 28 of the branch port 20 needs to be increased to some extent. Therefore, as described above, by making the width Te of the outer end portion 26 smaller than the width Tc of the central portion 28, the bypass flow passage 16 and the valve port 22 can be smoothly connected while suppressing the diffuser outlet flow D from flowing into the branch port 20.

In some embodiments, for example as shown in fig. 8, the width T of the branch port 20 is constant from one end side to the other end side in the length direction of the branch port 20. That is, in the embodiment shown in fig. 8, the branch port 20 has a rectangular shape when viewed from the direction of the normal N1.

According to this configuration, the increase in pressure loss associated with the installation of the bypass flow path 16 can be suppressed by the branch port 20 having a simple configuration.

In some embodiments, for example as shown in fig. 5-8, the length direction of the branch port 20 is orthogonal to the flow direction F of the swirling flow path 14 at the center position O1 of the branch port 20.

According to this configuration, the distance required for the flow of the scroll passage 14 to pass through the branch port 20 is shortened, and therefore, the flow entering the bypass passage 16 can be reduced. In addition, the flow entering the bypass flow path 16 can be effectively prevented from forming a vortex.

In the embodiments shown in fig. 5 to 8, the configuration in which the center O1 of the branch port 20 and the center O2 of the valve port 22 coincide with each other when viewed from the direction of the normal N1 is exemplified, but the center O1 of the branch port 20 and the center O2 of the valve port 22 may not coincide with each other when viewed from the direction of the normal N1.

In some embodiments, for example as shown in fig. 10-14, the center O1 of the branch port 20 is located inward of the center O2 of the valve port 22 in the radial direction I of the impeller. In this configuration, the center O1 of the branch port 20 is offset downstream of the center O2 of the valve port 22 with respect to the circumferential flow (diffuser outlet flow D) in the flow path cross section of the scroll flow path 14. In this configuration, as shown in fig. 10 to 14, when viewed from the direction of the normal N1, the distance L1 between the outer end 34 of the branch port 20 and the center O2 of the valve port 22 in the radial direction of the impeller 6 is smaller than the distance L2 between the inner end 36 of the branch port 20 and the center O2 of the valve port 22 in the radial direction of the impeller 6.

The branch port 20 shown in fig. 10 has a rounded rectangular shape similar to the branch port 20 shown in fig. 5. The shape of the branch port 20 shown in fig. 11 is an elliptical shape similar to the branch port 20 shown in fig. 6. The shape of the branch port 20 shown in fig. 12 is a diamond shape with rounded corners, similar to the branch port 20 shown in fig. 7. The shape of the branch port 20 shown in fig. 13 is a rectangular shape similar to the branch port 20 shown in fig. 8. The shape of the branch port 20 shown in fig. 14 is an asymmetric diamond shape with rounded corners, and the length of the inner sides in the radial direction I of the impeller is longer than the length of the outer sides.

As described with reference to fig. 9, the diffuser outlet flow D easily flows into the end portion 26 of the branch port 20 on the outer side in the radial direction I of the impeller 6. Therefore, by offsetting the center O1 of the branch port 20 inward in the radial direction I of the impeller with respect to the center O2 of the valve port 22, it becomes difficult for the diffuser exit flow D to flow along the inner wall surface 32 of the scroll flow path 14 and flow from the branch port 20 into the bypass flow path 16, as shown in fig. 15, and an increase in pressure loss can be suppressed.

Next, other embodiments will be described. The actual flow flowing through the scroll passage 14 becomes a swirling flow that describes a spiral trajectory in which a component orthogonal to the passage cross section of the scroll passage 14 and a swirl component in the passage cross section of the scroll passage 14 are blended. In the embodiment described below, an inclination angle is provided at the branch port 20 in order to effectively suppress the swirling flow of the scroll flow path 14 from flowing from the branch port 20 into the bypass flow path 16.

Fig. 16 is a diagram for explaining definitions of vectors used in the following description of the respective embodiments. First, as shown in fig. 16, in a flow path cross section G including the center O1 of the branch port 20 of the scroll flow path 14, a vector indicating the position of the center O1 of the branch port 20 with respect to the position of the center O3 of the flow path cross section G is denoted by P, a vector indicating a flow direction (flow direction F of the scroll flow path 14) perpendicular to the flow path cross section G is denoted by Q, and an outer product of the vector P and the vector Q is denoted by E (═ P × Q). In this way, a vector J indicating the swirling flow of the scroll passage 14 at the position of the center O1 of the branch port 20 can bE represented as J ═ aQ + bE. Hereinafter, some embodiments will be described based on the definition of these vectors.

Fig. 17 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment. Fig. 18 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment. Fig. 19 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment. Fig. 20 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to an embodiment. Fig. 21 is a diagram showing the shape of the branch port 20 and the shape of the valve port 22, as viewed along a normal N1 of the branch port 20 passing through the center O1 of the branch port 20 according to the embodiment.

In some embodiments, for example, as shown in fig. 17-21, the branch port 20 extends from the fourth quadrant a4 toward the second quadrant a2 with the center O2 of the valve port 22 as the origin, the direction indicated by the vector Q as the x-axis direction, and the direction indicated by the vector E as the y-axis direction. That is, if a vector parallel to the longitudinal direction of the branch port 20 is denoted by V, one of the inner product V · E of the vector V and the vector E and the inner product V · Q of the vector V and the vector Q has a positive value, and the other has a negative value. In the embodiment shown in fig. 17 to 21, the angle θ 1 formed by the longitudinal direction of the branch port 20 and the direction indicated by the vector E is 0 ° < θ 1 < 90 °, preferably 30 ° < θ 1 < 60 °, and may be, for example, θ 1 equal to 45 °.

According to this configuration, compared to a case where the branch port 20 extends from the third quadrant A3 toward the first quadrant a1 (a case where both of the inner products V · E and V · Q have positive values or a case where both of the inner products V · E and V · Q have negative values), the angle θ 2 formed by the flow direction of the swirling flow of the scroll passage 14 (the direction indicated by the vector J) at the position of the branch port 20 and the longitudinal direction of the branch port 20 can be made close to a right angle, and therefore, the inflow of the swirling flow of the branch port 20 and the scroll passage 14 into the branch port 20 can be effectively suppressed.

In the embodiment in which the branch port 20 is provided with the inclination angle, the shape of the branch port 20 may be, for example, an elliptical shape when viewed from the normal N1 direction as shown in fig. 17 to 20, or a rectangular shape when viewed from the normal N1 direction as shown in fig. 21. The shape of the branch port 20 illustrated in fig. 17 and 18 is a slit shape when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 17 is a rounded rectangle when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 18 is an elliptical shape when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 19 is a rhombic shape with rounded corners when viewed from the direction of the normal N1. The shape of the branch port 20 illustrated in fig. 20 is an asymmetric rhomboid shape with rounded corners when viewed from the direction of the normal N1.

In the embodiment shown in fig. 17 to 21, the embodiment in which the center O1 of the branch port 20 is offset inward in the radial direction I of the impeller with respect to the center O2 of the valve port 22 is exemplified, but even when the branch port 20 is provided with an inclination angle, the center O1 of the branch port 20 may coincide with the center O2 of the valve port 22 as viewed from the normal N1 direction.

The present invention is not limited to the above-described embodiments, and includes embodiments in which modifications are added to the above-described embodiments and embodiments in which these embodiments are appropriately combined.

For example, the shape of the branch port 20 is not limited to the above shape, and may be a bent shape ("く" shape) in which a straight line shape is bent as shown in fig. 22, or may be a curved shape (arcuate shape) in which a straight line shape is curved as shown in fig. 23, when viewed along a normal line N1 of the branch port 20 passing through the center O1 of the branch port 20.

Description of the reference numerals

2 turbo charger

4 centrifugal compressor

6 impeller

8 rotating shaft

10 turbine rotor

12 turbine

14 swirl flow path

16 bypass flow path

18 bypass valve

19 actuator

20 branch port

22 valve port

24 valve core

25 seat surface

26 end of the tube

28 center part

30 diffuser

32 inner wall surface

34 outer end

36 inner end