Housings for compressors, compressors and exhaust gas recirculation systems

Abstract

The present invention relates to a housing for a compressor, which accommodates an impeller and allows the impeller to rotate relative to the housing, comprising: a first intake channel, which guides air in a first guide direction; a second intake channel, which extends at least partially circumferentially along the housing and guides exhaust gas in a second guide direction, the second intake channel comprises an inlet section and a relative outlet section, and the outlet section is positioned radially inside the inlet section, the cross-sectional ratio between the inlet cross-sectional area of ​​the inlet section and the outlet cross-sectional area of ​​the outlet section is between 2-10, and at the outlet section, the first angle formed by the second guide direction and the radial direction is in the range of 45 to 90 degrees. This housing allows the mixed gas formed by air and exhaust gas to generate a circumferential velocity, reducing the blade erosion rate without the need to coat the impeller. In addition, the present invention also relates to a compressor and an exhaust gas recirculation system.

Description

Technical Field

[0001] The present invention belongs to the technical field of air compressors and relates to a housing for a compressor. In addition, the present invention also relates to a compressor comprising such a housing and an exhaust gas recirculation system. Background Art

[0002] The engine's low-pressure exhaust gas recirculation (LP-EGR) system is an important engine emission control technology. It reintroduces part of the exhaust gas discharged by the engine into the intake system, mixes it with fresh air, and then re-enters the cylinder for combustion, so as to reduce nitrogen oxide (NOx) emissions in the exhaust gas and improve fuel economy.

[0003] For turbochargers, the water flow from the exhaust pipe after LP-EGR cooling will impact the impeller, especially the impeller blades, at a high speed, resulting in erosion and wear failure mode. In the prior art, a coating is applied to the compressor impeller to prevent erosion, reduce or eliminate erosion or wear of the blades by water droplets, etc.

[0004] However, coating the compressor impeller generally significantly increases the manufacturing and maintenance costs of the impeller. Therefore, there is a need to improve the structure of the compressor so as to provide an improved compressor that can overcome one or more disadvantages of the prior art. Summary of the invention

[0005] The object of the present invention is to avoid or at least partially reduce exhaust gas erosion of the blades of a compressor, while still maintaining the desired compressor power and / or efficiency, without requiring costly coating of the impeller.

[0006] According to a first aspect of the present invention, a housing for a compressor is proposed, which can accommodate an impeller and allow the impeller to rotate relative to the housing; the housing may include: a first intake channel, which guides air in a first guide direction; a second intake channel, which extends at least partially circumferentially along the housing and guides exhaust gas in a second guide direction, the second intake channel includes an inlet section and a relative outlet section, and the outlet section is positioned radially inside the inlet section, wherein a cross-sectional ratio between an inlet cross-sectional area of ​​the inlet section and an outlet cross-sectional area of ​​the outlet section is between 2-10, and at the outlet section, a first angle formed by the second guide direction and the radial direction is in the range of 45 to 90 degrees.

[0007] This type of housing adopts an integral vortex channel design, which can make the mixture formed by air and exhaust gas produce a circumferential velocity, thereby reducing the impact speed of water droplets contained in the mixture on the blades, and then reducing the blade erosion rate. There is no need to apply high-cost coating to the impeller, reducing manufacturing and maintenance costs.

[0008] According to the above aspect of the present invention, preferably, the second intake passage may extend a second angle in the circumferential direction between the inlet section and the outlet section, and the second angle may be in the range of 30 to 180 degrees.

[0009] Based on computational fluid dynamics (CFD) airflow simulation, in a case study with an EGR rate of 23%, through this intake channel arrangement, the maximum circumferential velocity of the EGR mixture can reach 124m / s, and the overall average can reach 67-92m / s, thereby reducing the relative speed with respect to the blades and reducing the impact damage to the blades.

[0010] According to the above aspects of the present invention, preferably, the cross-sectional ratio may be between 3 and 6, and the second angle may be in the range of 50 to 100 degrees. The inventors have found that this arrangement can achieve an unexpected balance in terms of the compressor stage efficiency, stage compression ratio and EGR intake compression ratio, thereby achieving higher compressor performance.

[0011] According to the above aspects of the present invention, preferably, the cross-sectional ratio may be 50:9, and the second angle is 90 degrees. Compared with the compressor of the prior art, this arrangement can obtain a better stage compression ratio and EGR intake compression ratio, in particular, a higher EGR intake compression ratio.

[0012] According to the above aspects of the present invention, preferably, the cross-sectional ratio may be 10:3, and the second angle is 60 degrees. This arrangement can achieve a better stage compression ratio and EGR intake compression ratio while maintaining substantially the same stage efficiency as the prior art compressor.

[0013] According to the above aspects of the present invention, preferably, the first inlet passage can extend axially relative to the impeller and can have a truncated cone-shaped first surface, and the outlet section of the second inlet passage opens on the first surface. This arrangement can balance the mixed gas flow, circumferential velocity, impact area and compressor stage efficiency.

[0014] According to the above aspects of the present invention, preferably, the inlet section is further away from the impeller than the outlet section in the axial direction. In this way, before the airflow contacts the impeller, the air and the exhaust gas are allowed to mix, so that the exhaust gas flow drives the air flow to generate a circumferential velocity, thereby further reducing the impact of droplets in the mixed airflow on the blades.

[0015] According to the above aspect of the present invention, preferably, the second intake passage may include at least two passages, and the at least two passages may have a common inlet section and separate outlet sections.

[0016] Such an arrangement of two or more swirl passages can further increase the circumferential velocity of the exhaust gas to achieve a better balance between the impact area of ​​the circumferential airflow on the blades and the compressor stage efficiency.

[0017] According to the above aspects of the present invention, in order to better achieve the diversion and guidance of the exhaust gas flow, preferably, the second intake channel can be provided with at least one diverter downstream of the inlet section for guiding the exhaust gas flow entering the inlet section into at least two branch channels.

[0018] According to the above aspects of the present invention, in order to further promote the mixing of air and exhaust gas and make the mixed gas contact the impeller at a certain circumferential speed, preferably, the impeller and the outlet section may have a first spacing in the axial direction.

[0019] According to the above aspect of the present invention, preferably, the air and the exhaust gas can be mixed together at a third angle, and the third angle is in the range of 30 degrees to 90 degrees.

[0020] This mixing angle can better drive the air to rotate, so that the mixed gas has an overall circumferential initial velocity, further reducing the impact of droplets in the mixed airflow on the blades.

[0021] According to the above aspects of the present invention, preferably, the intake direction of the exhaust gas can conform to the rotation direction of the impeller. This arrangement allows the relative speed between the exhaust gas flow and the impeller to be reduced, thereby reducing the magnitude of the impact force.

[0022] According to a second aspect of the present invention, a compressor is provided, which may include the housing for the compressor described in the first aspect. Such a compressor can improve the operating environment of the blades and increase the service life of the blades without the need for high-cost coating of the impeller blades, thereby reducing manufacturing and maintenance costs.

[0023] According to the above aspects of the present invention, in order to further reduce the cost of the compressor, preferably, the material of the impeller may include aluminum or an aluminum alloy.

[0024] According to a third aspect of the present invention, an exhaust gas recirculation system is provided. The exhaust gas recirculation system may include the compressor according to the second aspect.

[0025] According to the above aspects of the present invention, preferably, the exhaust gas recirculation system may also include: an engine; a first pipeline (e.g., an intake pipeline) and a second pipeline (e.g., an exhaust pipeline) connected to the engine; a turbine arranged downstream of the engine along the second pipeline; an exhaust gas treatment device arranged downstream of the turbine, wherein the impeller of the compressor is driven to rotate by the turbine, and wherein the exhaust gas passing through the exhaust gas treatment device at least partially enters the third pipeline and enters the compressor together with the air from the fourth pipeline, is compressed by the compressor and enters the engine through the first pipeline.

[0026] Therefore, the housing for the compressor of the present invention can meet the use requirements, overcome the shortcomings of the prior art and achieve the predetermined purpose. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] In order to further clearly describe the housing for a compressor according to the present invention, the present invention will be described in detail below in conjunction with the accompanying drawings and specific embodiments. In the accompanying drawings:

[0028] Figure 1 shows a schematic diagram of an exhaust gas recirculation system according to a non-limiting embodiment of the present invention;

[0029] Figure 2 A schematic cutaway perspective view of a housing of a prior art compressor is shown;

[0030] Figure 3 A schematic flow mixing simulation diagram of air and exhaust gas of a compressor of the prior art is shown;

[0031] Figure 4 The figure shows a schematic airflow impact force experienced by the impeller of a compressor of the prior art;

[0032] Figure 5 shows a schematic perspective view of a compressor according to a non-limiting embodiment of the present invention;

[0033] Figure 6 A schematic cross-sectional perspective view of a housing of a compressor according to a first embodiment of the present invention is shown;

[0034] Figure 7 Shows Figure 6 A schematic layout of an air intake passage of a compressor housing is shown;

[0035] Figure 8 Shows Figure 6 Schematic flow mixing of air and exhaust gas from the compressor is shown;

[0036] Fig. 9 Shows Figure 6 Another schematic flow mixing of air and exhaust gas from a compressor is shown;

[0037] Fig.10 Shows Figure 6 A schematic cross-sectional view of a compressor is shown;

[0038] Fig.11 Shows Figure 6 A schematic diagram of the mixing of compressor air and exhaust gas is shown;

[0039] Fig.12 Shows Figure 6 Schematic flow impact force experienced by the impeller of the compressor shown;

[0040] Fig.13 A schematic perspective view showing a housing of a compressor according to a second embodiment of the present invention;

[0041] Fig.14 A schematic cross-sectional perspective view of a housing of a compressor according to a second embodiment of the present invention is shown;

[0042] Fig.15 shows another schematic cutaway perspective view of a housing of a compressor according to a second embodiment of the present invention;

[0043] Fig.16 Shows Fig.13 A schematic cross-sectional view of a compressor is shown;

[0044] Fig.17 Shows Fig.13 Another schematic flow mixing of air and exhaust gas from a compressor is shown;

[0045] Fig.18 Shows Fig.13 Another schematic flow mixing simulation diagram of compressor air and exhaust gas is shown;

[0046] Fig.19 shows a simulation comparison of different air flow velocities for the compressor casing;

[0047] Fig. 20 A simulation diagram showing schematic flow mixing of air and exhaust gas of a compressor according to a preferred embodiment of the present invention;

[0048] Fig.21 The figure shows the simulation of the circumferential velocity of the mixed gas obtained after the air and the exhaust gas of the compressor according to the preferred embodiment of the present invention are mixed;

[0049] Fig. 22 shows a schematic flow mixing of air and exhaust gas of a compressor according to another preferred embodiment of the present invention; and

[0050] Fig.23FIG. 4 shows a simulation of the circumferential velocity of a mixed gas obtained by mixing air and exhaust gas of a compressor according to another preferred embodiment of the present invention.

[0051] The above drawings are merely schematic and are not drawn strictly to scale.

[0052] List of reference numerals in the figures and embodiments:

[0053] 1000 - Exhaust Gas Recirculation System, including:

[0054] 200 - Compressor, including:

[0055] 100 - housing;

[0056] 10 - First air intake passage, comprising:

[0057] 10A-first surface;

[0058] 20 - Second air intake passage, including:

[0059] 21 - Entrance section;

[0060] 21A – inlet cross-sectional area;

[0061] 22 - Exit section, including:

[0062] 211 - first outlet section;

[0063] 221 - second outlet section;

[0064] 22A – outlet cross-sectional area;

[0065] 210 - First branch channel;

[0066] 220 - Second branch channel;

[0067] 110 - impeller;

[0068] 300 – engine;

[0069] 400 - turbine;

[0070] 500 - Waste gas treatment device;

[0071] 600 - control valve;

[0072] 700 - filter;

[0073] 800 - heat exchanger;

[0074] L1 – first pipeline;

[0075] L2 – second pipeline;

[0076] L3 – third pipeline;

[0077] L4 – fourth pipeline;

[0078] α – first angle;

[0079] β – second angle;

[0080] γ – the third angle;

[0081] C – circumferential direction;

[0082] R – radial direction;

[0083] S - rotation direction;

[0084] A – axial direction;

[0085] D – first spacing;

[0086] Y1 - first guiding direction;

[0087] Y2 - Second guiding direction. DETAILED DESCRIPTION

[0088] It should be understood that, unless expressly stated otherwise, the present invention may adopt various alternative orientations and step sequences. It should also be understood that the specific devices shown in the drawings and described in the specification are merely exemplary embodiments of the inventive concepts disclosed and defined herein. Therefore, unless otherwise expressly stated, the specific orientations, directions or other features of the various embodiments disclosed should not be considered as limiting.

[0089] Figure 1 A schematic diagram of an exhaust gas recirculation system 1000 according to a non-limiting embodiment of the present invention is shown.

[0090] As shown and as a non-limiting example, the exhaust gas recirculation system 1000 may be a low pressure exhaust gas recirculation (LP-EGR) system and may mainly include: a compressor 200 , an engine 300 , a turbine 400 , an exhaust gas treatment device 500 and corresponding connecting lines.

[0091] The compressor 200 may be a centrifugal compressor and may compress gas (eg, a mixture of exhaust gas and fresh air) entering the engine 300 to a certain pressure to help improve combustion efficiency and / or reduce combustion temperature and may reduce generation of nitrogen oxides (NOx).

[0092] The engine 300 may be any type of internal combustion engine known in the art, and converts the chemical energy of the fuel into mechanical energy by burning the fuel in a combustion chamber. The fuel may be, for example, gasoline, diesel, ethanol, hydrogen, etc.

[0093] The gas compressed by the compressor 200 may enter the engine 300 through a first pipeline (or intake pipeline) L1 to be mixed with fuel for combustion. The exhaust gas / exhaust after combustion may enter a second pipeline (or exhaust pipeline) L2.

[0094] The turbine 400 may be arranged downstream of the engine 300 along the second line L2 , may be powered by exhaust gas flowing through the second line L2 , and the compressor 200 is connected to the turbine 400 , such that the impeller 110 of the compressor 200 may be driven to rotate by the turbine 400 .

[0095] An exhaust gas treatment device 500 may be arranged downstream of the turbine 400, for example, for capturing particulate matter or reducing catalysis of exhaust gas, so as to reduce harmful substances in the exhaust gas.

[0096] A portion of the exhaust gas passing through the exhaust treatment device 500 may be discharged to the surrounding environment, while another portion may enter the third line L3 and enter the compressor 200 together with the air from the fourth line L4 , be compressed by the compressor 200 and may enter the engine 300 through the first line L1 .

[0097] A control valve 600 may be disposed downstream of the exhaust treatment device 500 to change the volume or flow rate of the exhaust gas entering the third line L3 to achieve a desired EGR ratio.

[0098] Preferably, a filter 700 may be provided in the third pipeline L3 to further remove or reduce the amount of particulate matter contained in the exhaust gas.

[0099] In addition, one or more heat exchangers 800 may be provided to reduce the temperature of the exhaust gas or the mixed gas to further improve the combustion efficiency. Figure 1 In the illustrated embodiment, a heat exchanger 800 may be provided in each of the first pipeline L1 and the third pipeline L3 .

[0100] Figure 2 A schematic cutaway perspective view of a housing 100 of a prior art compressor 200 is shown; Figure 3 A schematic flow mixing simulation diagram of air and exhaust gas of a compressor 200 of the prior art is shown; and Figure 4 Schematic diagram of the airflow impact force experienced by the impeller 110 of the prior art compressor 200 is shown.

[0101] like Figure 2As shown, such a compressor 200 may not have a separate inlet mixer, which is generally complex in structure and may increase the cost of the compressor 200. The housing 100 may accommodate the impeller 110 and allow the impeller 110 to rotate relative to the housing 100. The housing 100 may include a first intake passage 10 and a second intake passage 20. For example, the first intake passage 10 may guide air in a first guide direction Y1, and the second intake passage 20 may be used to guide exhaust gas.

[0102] This type of LP-EGR (Exhaust Gas Recirculation) without a compressor inlet mixer is widely used in low-pressure applications. For the compressor (also called compressor or turbocharger), due to the exhaust gas line (such as Figure 1 For example, for the impeller 110 of the compressor 200, the higher speed is mainly due to the higher rotation speed of the impeller 110. The erosion position of the impeller of the compressor 200 is usually at the tip area of ​​the blade edge with a higher rotational linear speed.

[0103] like Figure 3 and 4 As shown, the exhaust gas flow Fr can be guided in the second guide direction Y2, and the air flow Fa can be guided in the first guide direction Y1, and the flow directions of the exhaust gas flow Fr and the air flow Fa can form a large obtuse angle or be substantially perpendicular to each other. The impeller 110 can rotate in the rotation direction S shown by the arrow, and the first guide direction Y1 can be substantially perpendicular to the rotation plane of the impeller 110, that is, substantially along the direction of the rotation axis of the impeller 110.

[0104] At this time, under the experimental conditions set by the inventor, at the selected tip (or end) point of the impeller 110, the relative rotation speed between the impeller 110 and the exhaust gas flow Fr may reach about 190 meters per second, and the speed of the air flow Fa may be about 60 meters per second, so that the speed of the mixed flow F1 containing droplets here may reach about 199.2 meters per second. The relative speed at the rest of the impeller 110 may be slightly lower, but it still allows the impeller to operate in a harsh impact environment. In order to extend the service life of the impeller, in the prior art, it is usually necessary to apply a coating on the compressor impeller to prevent erosion, which increases production and maintenance costs.

[0105] Figure 5 2 shows a schematic perspective view of a compressor 200 according to a non-limiting embodiment of the present invention; and Figure 6 A schematic cross-sectional perspective view of a housing 100 of a compressor 200 according to a first embodiment of the present invention is shown.

[0106] As shown in the figure, the first air intake passage 10 can be connected to Figure 2 The structures shown are the same, so that the air flow Fa can be guided in a first guiding direction Y1 , for example, substantially in the axial direction A.

[0107] and Figure 2 The structure shown is different in that the second air intake passage 20 may extend at least partially circumferentially along the housing 100 and guide the exhaust gas in the second guide direction Y2. It should be understood that the flow direction of the exhaust gas is the actual direction of movement, and since the second air intake passage 20 at least partially extends circumferentially, the description "second guide direction Y2" herein may be different at different positions along the second air intake passage 20. For example, for a spiral air intake passage, the flow direction of the exhaust gas at a selected position may follow the direction of the tangent at that point.

[0108] like Figure 6 As schematically shown in FIG. 1 , the second intake passage 20 may include an inlet section 21 and an opposite outlet section 22 , and the outlet section 22 may be positioned radially inward of the inlet section 21 so that the exhaust gas flow flows radially inward.

[0109] Figure 7 Shows Figure 6 A schematic arrangement of an intake passage of a housing 100 of a compressor 200 is shown.

[0110] like Figure 7 As schematically shown in FIG. 2 , the inlet section 21 of the second intake passage 20 may have an inlet cross-sectional area 21A, and the outlet section 22 may have an outlet cross-sectional area 22A. According to the inventive concept of the present invention, the inlet cross-sectional area 21A may be greater than the outlet cross-sectional area 22A, so that the second intake passage 20 tapers along the flow direction of the exhaust gas.

[0111] Preferably, the cross-sectional ratio between the inlet cross-sectional area 21A and the outlet cross-sectional area 22A is between 2 and 10. This arrangement is advantageous, in particular, it can accelerate the exhaust gas flow Fr through the second intake passage 20, thereby minimizing the relative speed difference between the exhaust gas flow Fr and the blades of the impeller 110, thereby reducing the impact on the blades.

[0112] The second inlet passage 20 forms a swirling exhaust gas flow Fr, so that the exhaust gas flows in a certain tangential direction at the outlet section 22 of the second inlet passage 20. It is particularly advantageous that the exhaust gas intake direction is arranged to follow the rotation direction of the impeller 110.

[0113] Specifically, Figure 7As schematically shown in FIG. 1 , at the outlet section 22, the first angle α formed by the second guide direction Y2 and the radial direction R (i.e., the radius or diameter direction of the impeller 110) may be in the range of 45 to 90 degrees. According to the inventive concept of the present invention, it is ideal to make the first angle α about 90 degrees so that the exhaust gas flow Fr flows in the tangential direction.

[0114] exist Figure 7 Schematically shows the extension angle of the second intake channel 20 in the circumferential direction C. The angle is measured between the inlet section 21 (e.g., at its midpoint) and the outlet section 22 (e.g., at its midpoint) of the second intake channel 20. As an example, the second intake channel 20 may extend at a second angle β in the circumferential direction C, and the second angle β may be in the range of 30 to 180 degrees.

[0115] Figure 8 Shows Figure 6 Schematic flow mixing of air and exhaust gas of compressor 200 shown; and Fig. 9 Shown from different perspectives Figure 6 Another illustrative flow mixing of air and exhaust gas from compressor 200 is shown.

[0116] like Figure 8 and 9 As shown, at the outlet section 22 of the second intake passage 20, the air and the exhaust gas may be mixed together at a third angle γ, and the third angle γ may be in the range of 30 degrees to 90 degrees. Fig. 9 As shown more clearly, at the outlet section 22 of the second intake passage 20, the guiding direction of the exhaust gas flow Fr may be biased toward the impeller 110, that is, at Fig. 9 Guided in the downward and left direction.

[0117] Fig.10 Shows Figure 6 The cross-sectional schematic diagram of the compressor 200 is shown. Fig.10 As schematically shown in FIG. 1 , the first inlet passage 10 may extend axially (e.g., along the axial direction A) relative to the impeller 110 and have a substantially truncated cone-shaped first surface 10A, and the first surface 10A may form a substantially smooth guide surface. Preferably, the inlet cross section of the first inlet passage 10 may be larger than the outlet cross section, that is, Fig. 9 The opening size of the right side portion of the first intake passage 10 shown in FIG. 1 may be larger than the opening size of the left side portion.

[0118] The outlet section 22 of the second intake passage 20 may open on the first surface 10A. Fig.10 It is also shown that the inlet section 21 can be further away from the impeller 110 along the axial direction A than the outlet section 22. Fig.10 As shown, the impeller 110 may have a first distance D from the outlet section 22 in the axial direction A. Fig.10 It is also shown in FIG. 5 that the axial direction A may be substantially parallel to the first guiding direction Y1 .

[0119] Fig.11 Shows Figure 6 A simulated diagram of illustrative gas flow mixing of air and exhaust gas from compressor 200 is shown.

[0120] As shown in the figure, the exhaust gas flow Fr flowing in the second guide direction Y2 forms a vortex airflow, and drives at least a part of the air flow Fa to flow in the circumferential direction C, so that the mixed mixed airflow also forms a vortex airflow (that is, at least partially flows in the circumferential direction C), so that the intake direction of the mixed airflow containing the exhaust gas and air also roughly conforms to the rotation direction of the impeller 110.

[0121] Fig.12 Shows Figure 6 Schematic illustration of the airflow impact forces experienced by the impeller 110 of the compressor 200 is shown.

[0122] As shown in the figure, Figure 4 Under the same experimental conditions, that is, at the same rotation speed and direction of the impeller 110 of the compressor 200, at the selected tip point of the impeller 110, the circumferential speed of the impeller 110 of the compressor can also be 190 meters per second, while the circumferential speed of the exhaust gas flow can be 124 meters per second, and the direction of the exhaust gas flow Fr conforms to the rotation direction of the impeller 110. At this time, the relative rotation speed between the impeller 110 and the exhaust gas flow Fr may be reduced to about 66 meters per second (i.e., 190-124=66). The speed of the air flow Fa can also be about 60 meters per second, so that the speed of the mixed flow F2 containing droplets here may be reduced from 190 meters per second to about 89.2 meters per second. It can be seen that the arrangement of the second air inlet channel 20 according to the present invention can significantly reduce the impact erosion of the mixed flow F2 containing droplets on the impeller 110. At this time, the impeller 110 can be made of aluminum or aluminum alloy, etc., thereby further reducing the manufacturing cost.

[0123] Fig.13 1 is a schematic perspective view of a housing 100 of a compressor 200 according to a second embodiment of the present invention; and Figure 14-16 A schematic cross-sectional perspective view of a housing 100 of a compressor 200 according to a second embodiment of the present invention is shown.

[0124] In addition to the following description, refer to Figure 13-16 A second non-limiting embodiment of the housing 100 of the compressor 200 is shown with reference to Figure 5-12The first non-limiting embodiment of the housing 100 of the compressor 200 is shown to be substantially the same or similar. Therefore, for the sake of brevity, repeated descriptions of the same or similar components are omitted, and the same or similar components are marked with the same or similar reference numerals.

[0125] exist Figure 13-16 In the illustrated embodiment of the housing 100, the second air inlet passage 20 may include two passages, namely a first branch passage 210 and a second branch passage 220. The two passages may have a common inlet section 21 and separate outlet sections 22, namely a first outlet section 211 and a second outlet section 221. For example, the first outlet section 211 and the second outlet section 221 may be spaced apart by a predetermined angle in the circumferential direction C to achieve a desired airflow guiding effect.

[0126] It should be understood at this point that the outlet cross-sectional area 22A mentioned above may be the sum of the outlet cross-sectional areas of the first outlet section 211 and the second outlet section 221 .

[0127] like Fig.13 As can be seen more clearly in FIG. 2 , the second intake channel 20 is provided with a splitter 23 downstream of the inlet section 21 for splitting the exhaust gas entering the inlet section 21 into the first branch channel 210 and the second branch channel 220 .

[0128] It should be understood that although in conjunction with Figure 13-16 In the embodiment of the housing 100 shown, the second intake passage 20 includes two passages and the outlet sections 22 are shown as two, but in an alternative embodiment, the second intake passage 20 includes more passages and may have a corresponding number of outlet sections 22, in which case corresponding flow dividers 23 may also be provided to divide and guide the exhaust gas entering the inlet section 21 into multiple passages. As a non-limiting example, the individual outlet sections 22 may be spaced apart at any angle in the circumferential direction C.

[0129] Fig.17 Shows Fig.13 Another schematic flow mixing of air and exhaust gas of compressor 200 is shown; and Fig.18 Shows Fig.13 Another illustrative flow mixing simulation of air and exhaust gas of compressor 200 is shown.

[0130] As shown, the exhaust gas flow Fr may be mixed with the air flow Fa at the first outlet section 211 and the second outlet section 221 , respectively, so that the mixed gas flow has a desired circumferential velocity and distribution profile.

[0131] Fig.19 A simulation comparison of different air flow velocities for the housing 100 of the compressor 200 is shown.

[0132] exist Fig.19 The axial velocity and axial velocity profile of the airflow of the reference structure are shown in (a) and (b); Fig.19 The axial velocity and axial velocity profile of the airflow having a second air inlet passage 20 are shown in (c) and (d); and Fig.19 (e) and (f) show the axial velocity and axial velocity profile of the airflow having the first branch channel 210 and the second branch channel 220. It can be seen that the housing 100 according to the concept of the present invention can significantly increase the circumferential velocity of the airflow along the periphery of the housing 100.

[0133] Thus, by integrating one, two or more swirl channels, the circumferential velocity of the water droplet flow from the LP-EGR can be generated and increased, and the relative velocity between the water droplet flow and the compressor impeller can be reduced during rotation, thereby reducing the water droplet erosion rate.

[0134] As an example, the air flow channels may be manufactured by casting or the like. For example, the air flow channels may be integrally formed during the casting process of the housing 100 .

[0135] Based on the inventive concept of the present invention, the inventors can obtain a better airflow guiding effect by cleverly designing the shape of the second intake passage 20. In particular, the inventors found that it is particularly advantageous if the cross-sectional ratio between the inlet cross-sectional area 21A and the outlet cross-sectional area 22A is between 3 and 6, and the second angle β is in the range of 50 to 100 degrees. Specifically, this arrangement can achieve an unexpected balance in terms of the compressor stage efficiency, stage compression ratio and EGR intake compression ratio, thereby achieving higher compressor performance.

[0136] When the cross-sectional ratio is 50:9 and the second angle β is 90 degrees, the simulation diagram of the air flow mixing of the air and the exhaust gas of the compressor 200 according to the present invention and the circumferential velocity simulation of the mixed gas obtained are shown in FIG. Fig. 20 and 21 It is schematically shown in FIG.

[0137] When the cross-sectional ratio is 10:3 and the second angle β is 60 degrees, the simulation diagram of the air flow mixing of the air and the exhaust gas of the compressor 200 according to the present invention and the circumferential velocity simulation of the mixed gas obtained are shown in FIG. Fig. 22 and 23 It is schematically shown in FIG.

[0138] As used herein, the terms "upper", "lower" and "first", "second", etc., which indicate positions or orientations, and the terms "first", "second", etc., which indicate order, are intended only to enable those skilled in the art to better understand the concept of the present invention as shown in the form of a preferred embodiment, and are not intended to limit the present invention. Unless otherwise specified, all orders, positions or orientations are only used for the purpose of distinguishing one element / component / structure from another element / component / structure, and do not represent any particular order, order of operation, direction or orientation unless otherwise specified. For example, in an alternative embodiment, "air" may be "exhaust gas".

[0139] As used herein, unless otherwise indicated, the terms "substantially" and "approximately" are interpreted to mean plus or minus five percent of the value or range of values, or to mean a deviation of plus or minus five percent of the shape and / or position.

[0140] In summary, the housing 100 for a compressor according to the embodiment of the present invention overcomes the shortcomings of the prior art and achieves the intended purpose of the invention.

[0141] Although the housing for a compressor of the present invention is described above in conjunction with the preferred embodiments, those skilled in the art should recognize that the above examples are only for illustration and cannot be used as limitations of the present invention. Therefore, various modifications and variations can be made to the present invention within the spirit of the claims, and these modifications and variations will fall within the scope required by the claims of the present invention.

Claims

1. A housing (100) for a compressor, the housing accommodating an impeller (110) and allowing the impeller to rotate relative to the housing; the housing (100) comprising: a first air intake passage (10), the first air intake passage guiding air in a first guiding direction (Y1); a second intake passage (20), the second intake passage extending at least partially circumferentially along the housing (100) and guiding the exhaust gas in a second guiding direction (Y2), the second intake passage comprising an inlet section (21) and an opposite outlet section (22), and the outlet section (22) being positioned radially inward of the inlet section (21), The cross-sectional ratio between the inlet cross-sectional area (21A) of the inlet section (21) and the outlet cross-sectional area (22A) of the outlet section (22) is between 2 and 10, and at the outlet section (22), the first angle (α) formed by the second guide direction (Y2) and the radial direction (R) is within the range of 45 to 90 degrees.

2. The housing (100) for a compressor according to claim 1, characterized in that: The second inlet passage (20) extends between the inlet section (21) and the outlet section (22) in the circumferential direction (C) at a second angle (β), the second angle being in the range of 30 to 180 degrees.

3. The housing (100) for a compressor according to claim 2, characterized in that: The cross-sectional ratio is between 3 and 6, and the second angle (β) is in the range of 50 to 100 degrees.

4. The housing (100) for a compressor according to claim 3, characterized in that: The cross-sectional ratio is 50:9, and the second angle (β) is 90 degrees.

5. The housing (100) for a compressor according to claim 3, characterized in that: The cross-sectional ratio is 10:3, and the second angle (β) is 60 degrees.

6. The housing (100) for a compressor according to claim 1, characterized in that: The first inlet passage (10) extends axially relative to the impeller (110) and has a first surface (10A) in a truncated cone shape, and the outlet section (22) of the second inlet passage (20) opens on the first surface (10A).

7. The housing (100) for a compressor according to claim 1, characterized in that: The inlet section (21) is further away from the impeller (110) along the axial direction (A) than the outlet section (22).

8. The housing (100) for a compressor according to any one of claims 1 to 7, characterized in that: The second air inlet passage (20) comprises at least two passages, wherein the at least two passages have a common inlet section (21) and separate outlet sections (22).

9. The housing (100) for a compressor according to claim 8, characterized in that: The second air intake passage (20) is provided with at least one flow splitter (23) downstream of the inlet section (21) for splitting the exhaust gas entering the inlet section (21) and directing it into the at least two passages.

10. The housing (100) for a compressor according to any one of claims 1 to 7, characterized in that: The impeller (110) has a first spacing (D) from the outlet section (22) in the axial direction (A).

11. The housing (100) for a compressor according to any one of claims 1 to 7, characterized in that: The air and the exhaust gas are mixed together at a third angle (γ), and the third angle is in a range of 30 degrees to 90 degrees.

12. The housing (100) for a compressor according to any one of claims 1 to 7, characterized in that: The intake direction of the exhaust gas complies with the rotation direction of the impeller (110).

13. A compressor (200), comprising the housing (100) for a compressor according to any one of claims 1-12.

14. An exhaust gas recirculation system (1000), comprising the compressor (200) according to claim 13.

15. The exhaust gas recirculation system (1000) according to claim 14, characterized in that Also includes: Engine (300); A first pipeline (L1) and a second pipeline (L2) connected to the engine (300); a turbine (400) arranged downstream of the engine (300) along the second line (L2); an exhaust gas treatment device (500) arranged downstream of the turbine (400), wherein the impeller (110) of the compressor (200) is driven to rotate by the turbine (400), and The exhaust gas passing through the exhaust gas treatment device (500) at least partially enters the third pipeline (L3) and enters the compressor (200) together with the air from the fourth pipeline (L4), is compressed by the compressor (200) and enters the engine (300) through the first pipeline (L1).

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