Compressor housing, air circulator housing, and air circulator

Abstract

The present application provides a compressor housing, an air circulation machine housing, and an air circulation machine. The compressor housing includes an intake pipe, a wheel cover, a circular ring section, and a volute tube that are connected in sequence. The inner ring radius of the circular ring section is r0. A first intersection line is formed at the intersection position of the inner peripheral surface of the circular ring section and the wheel cover, and a second intersection line is formed at the intersection position of the inner peripheral surface of the wheel cover and the intake pipe. The plane passing through the first intersection line and perpendicular to the central axis of the wheel cover is the first plane. The distance between the second intersection line and the first plane is z1. Any plane is taken between the second intersection line and the first plane. The distance between this any plane and the first plane is zi. The intersection line of this any plane and the inner peripheral surface of the wheel cover is a circle with a radius of ri. Let the profile line of the wheel cover be y = ri / r0, the variable x = zi / z1, and y = ax6 - bx5 + cx4 - dx3 + ex2 - fx + g, where a = 4.1 to 6.6, b = 15 to 22, c = 20 to 30, d = 14 to 20, e = 5 to 8, f = 1 to 2.5, and g = 0.5 to 1.5. According to the compressor housing of the present application, the structure of the compressor can be optimized, the airflow loss can be reduced, and the performance of the compressor can be improved.

Description

Technical Field

[0001] This application relates to the technical field of aircraft air conditioners, and specifically relates to a compressor housing, an air cycle machine housing, and an air cycle machine. Background Art

[0002] Currently, the power source of the mainstream aircraft cabin air conditioner is the bleed air from the aircraft engine. The high-temperature and high-pressure gas discharged from the engine enters the refrigeration pack unit. Specifically, after the expansion wheel, it drives the compression wheel and the ram air fan to operate. The expansion wheel is mainly used to provide power and generate a low-temperature air flow. The compression wheel is mainly used to increase the pressure of the low-pressure air outside the aircraft at high altitude, and at the same time, there is a temperature increase effect. The main purpose of the ram air fan is to perform heat exchange for the heat exchanger.

[0003] The air cycle machine includes a compressor (also known as a compressor or air compressor). The compressor is composed of main components such as a rotor, a diffuser, and a housing. The housing is assembled from parts such as an intake pipe, a volute pipe, a wheel cover, and an outlet pipe, providing a working cavity for the compression impeller.

[0004] The structural design of the compressor has a great influence on the air flow efficiency. When the structural design is unreasonable, it will cause a large flow loss of the air flow in the compressor, and the flow efficiency will be severely reduced, thereby affecting the compression performance of the compressor. Summary of the Invention

[0005] Therefore, the technical problem to be solved by this application is to provide a compressor housing, an air cycle machine housing, and an air cycle machine, which can optimize the structure of the compressor, reduce the air flow loss, and improve the compressor performance.

[0006] To solve the above problems, this application provides a compressor housing, including an intake pipe, a wheel cover, a circular ring section, and a volute pipe connected in sequence. The inner ring radius of the circular ring section is r0. A first intersection line is formed at the intersection position of the inner circumferential surface of the circular ring section and the wheel cover. A second intersection line is formed at the intersection position of the inner circumferential surface of the wheel cover and the intake pipe. The plane passing through the first intersection line and perpendicular to the central axis of the wheel cover is the first plane. The distance between the second intersection line and the first plane is z1. Take any plane between the second intersection line and the first plane. The distance between this any plane and the first plane is zi. The intersection line of this any plane and the inner circumferential surface of the wheel cover is a circle with a radius of ri. Let the profile line of the wheel cover be y = ri / r0, the variable x = zi / z1, and y = a1x 6 -b1x 5 +c1x 4 -d1x 3 +ex 2 -fx + g, where a1 = 4.1 - 6.6, b1 = 15 - 22, c1 = 20 - 30, d1 = 14 - 20, e = 5 - 8, f = 1 - 2.5, and g = 0.5 - 1.5.

[0007] Preferably, a1 = 4.3 - 5.5, b1 = 15.5 - 18, c1 = 21.5 - 25, d1 = 15 - 17, e = 5.5 - 7, f = 1.5 - 2, g = 0.8 - 1.2.

[0008] Preferably, a1 = 4.6242, b1 = 16.148, c1 = 22.349, d1 = 15.716, e = 6.3092, f = 1.8136, g = 0.9998.

[0009] Preferably, when x = 0, y = 1; when x = 0.1, y = [0.85, 0.88]; when x = 0.2, y = [0.77, 0.83]; when x = 0.3, y = [0.71, 0.79]; when x = 0.4, y = [0.66, 0.76]; when x = 0.5, y = [0.62, 0.74]; when x = 0.6, y = [0.59, 0.72]; when x = 0.7, y = [0.56, 0.71]; when x = 0.8, y = [0.54, 0.7]; when x = 0.9, y = [0.52, 0.7]; when x = 1, y = [0.51, 0.7].

[0010] Preferably, the circular ring section is perpendicular to the central axis of the wheel cover.

[0011] Preferably, the scroll tube has a scroll tongue. In the cross - section passing through the central axis of the scroll tube, the cross - sectional area of one - side flow channel of the scroll tube is A2, the intake width of the scroll tube is W, the distance between the intake port of the scroll tube and the central axis of the scroll tube is R. In the cross - section perpendicular to the central axis of the scroll tube, taking the position where the connecting line between the end point of the scroll tongue of the scroll tube and the central axis of the scroll tube is located as the starting position, and the rotation angle of the connecting line around the central axis of the scroll tube along the air - flow direction relative to the starting position is α, the scroll - tube profile satisfies: A / (W*R)=a2α 3 +b2α 2 +c2α + d2, where the value range of a2 is - 0.004 - - 0.002, the value range of b2 is + 0.001 - + 0.003, the value range of c2 is 0.1 - 1, and the value range of d2 is 0.1 - 1.1.

[0012] Preferably, a2 = - 0.003, b2 = 0.0022, c2 = 0.5322, d2 = 0.6707.

[0013] Preferably, the scroll tube is symmetric about a plane perpendicular to the central axis of the scroll tube.

[0014] Preferably, in a cross-section passing through the central axis of the vortex tube, the cross-section of the single-side flow channel of the vortex tube includes a first circular arc segment, a first straight segment, a first curved segment, a second curved segment, a second straight segment, and a second circular arc segment connected in sequence.

[0015] Preferably, an angle β is formed between the first straight segment and / or the second straight segment and a plane perpendicular to the central axis of the vortex tube, and the value range of β is 15° to 45°.

[0016] Preferably, the first end of the circular ring segment is tangent to the vortex tube at the connection position, and the second end of the circular ring segment is tangent to the wheel cover at the connection position.

[0017] According to another aspect of the present application, an air circulation machine housing is provided, including the above-mentioned compressor housing.

[0018] Preferably, the air circulation machine housing further includes a fan housing and a bearing seat, and at least one of the fan housing and the bearing seat is separately formed and fixedly connected to the compressor housing.

[0019] Preferably, a first flange is provided on one side of the compressor housing facing the bearing seat, a second flange is provided on one side of the bearing seat facing the compressor housing, and the first flange and the second flange are fixedly connected by bolts.

[0020] Preferably, a first axial protrusion is provided on one side of the bearing seat facing the compressor housing, a first shaft hole is provided on the first flange, and the first axial protrusion is sleeved in the first shaft hole.

[0021] Preferably, a third flange is provided on one side of the compressor housing facing the fan housing, a fourth flange is provided on one side of the fan housing facing the compressor housing, and the third flange and the fourth flange are fixedly connected by bolts.

[0022] Preferably, a second axial protrusion is provided on one side of the compressor housing facing the fan housing, a second shaft hole is provided on the fourth flange, and the second axial protrusion is sleeved in the second shaft hole.

[0023] According to another aspect of the present application, an air circulation machine is provided, including the above-mentioned compressor housing or the above-mentioned air circulation machine housing.

[0024] The compressor housing provided by the present application includes an intake pipe, a wheel cover, a circular ring section, and a scroll tube that are connected in sequence. The inner ring radius of the circular ring section is r0. A first intersection line is formed at the intersection position of the inner circumferential surface of the circular ring section and the wheel cover, and a second intersection line is formed at the intersection position of the inner circumferential surface of the wheel cover and the intake pipe. The plane passing through the first intersection line and perpendicular to the central axis of the wheel cover is the first plane. The distance between the second intersection line and the first plane is z1. Any plane is taken between the second intersection line and the first plane. The distance between this any plane and the first plane is zi. The intersection line of this any plane and the inner circumferential surface of the wheel cover is a circle with a radius of ri. Let the profile line of the wheel cover be y = ri / r0, the variable x = zi / z1, and y = a1x 6 -b1x 5 +c1x 4 -d1x 3 +ex 2 -fx + g, where a1 = 4.1 - 6.6, b1 = 15 - 22, c1 = 20 - 30, d1 = 14 - 20, e = 5 - 8, f = 1 - 2.5, and g = 0.5 - 1.5. By optimizing the profile line of the wheel cover, the structure of the compressor housing can be optimized. Considering the air flow velocity magnitude and flow velocity uniformity at the intake port of the compressor comprehensively, the intake section of the wheel cover is made to be in balance with the flow velocity, reducing the air flow loss and improving the air flow performance, thereby improving the compressor performance. Description of the Drawings

[0025] Figure 1 is a schematic diagram of the dimensional relationship structure of the compressor housing according to an embodiment of the present application;

[0026] Figure 2 is a schematic diagram of the partial cross-sectional structure of the compressor housing according to an embodiment of the present application;

[0027] Figure 3 is a schematic diagram of the cross-sectional structure of the compressor housing according to an embodiment of the present application;

[0028] Figure 4 is a schematic diagram of the side view structure of the compressor housing according to an embodiment of the present application;

[0029] Figure 5 is a schematic diagram of the three-dimensional structure of the air circulation machine according to an embodiment of the present application;

[0030] Figure 6 is a schematic diagram of the cross-sectional structure of the air circulation machine according to an embodiment of the present application;

[0031] Figure 7 is a schematic diagram of the exploded structure of the air circulation machine housing according to an embodiment of the present application.

[0032] The reference signs are shown as:

[0033] 1. Scroll tube; 2. Scroll tongue; 3. First arc segment; 4. First straight segment; 5. First curve segment; 6. Second curve segment; 7. Second straight segment; 8. Second arc segment; 9. Wheel cover; 10. Ring segment; 11. Air outlet pipe; 12. Compressor housing; 13. Bearing seat; 14. Fan housing; 15. First flange; 16. Second flange; 17. Third flange; 18. Fourth flange; 19. First axial protrusion; 20. Second axial protrusion; 21. First shaft hole; 22. Second shaft hole; 23. Relief groove; 24. Air inlet pipe. Detailed implementation mode

[0034] Referring to Figures 1 to 7 As shown, according to the embodiment of the present application, the compressor housing includes an air inlet pipe 24, a wheel cover 9, a ring segment 10, and a scroll tube 1 connected in sequence. The inner ring radius of the ring segment 10 is r0. A first intersection line is formed at the intersection position of the inner peripheral surface of the ring segment 10 and the wheel cover 9, and a second intersection line is formed at the intersection position of the inner peripheral surface of the wheel cover 9 and the air inlet pipe 24. The plane passing through the first intersection line and perpendicular to the central axis of the wheel cover 9 is the first plane. The distance between the second intersection line and the first plane is z1. Any plane is taken between the second intersection line and the first plane. The distance between this any plane and the first plane is zi. The intersection line of this any plane and the inner peripheral surface of the wheel cover 9 is a circle with a radius of ri. Let the profile line of the wheel cover 9 be y = ri / r0, the variable x = zi / z1, and y = a1x 6 - b1x 5 + c1x 4 - d1x 3 + ex 2 - fx + g, where a1 = 4.1 - 6.6, b1 = 15 - 22, c1 = 20 - 30, d1 = 14 - 20, e = 5 - 8, f = 1 - 2.5, g = 0.5 - 1.5.

[0035] By optimizing the profile line of the wheel cover, the structure of the compressor housing can be optimized. Considering the air flow velocity magnitude and flow velocity uniformity at the air inlet of the compressor comprehensively, the inlet section of the wheel cover is made flow velocity balanced, the air flow loss is reduced, the air flow performance is improved, and thus the compressor performance is improved.

[0036] If the value of ri / r0 is too small, it is equivalent to a small inlet section. Under the same flow rate requirement, the flow velocity is large, and the flow loss is proportional to the square of the flow velocity, so the flow loss is large; if the value of ri / r0 is too large, it is equivalent to a large inlet section, that is, a large inlet diameter. Then when the flow direction of the fluid changes from the inlet axial direction to the outlet radial direction, the curvature radius is small, and there is a local loss caused by the side wall change involved in the fluid mechanics theory, which exacerbates the flow velocity non-uniformity.

[0037] In one embodiment, a1 = 4.3 - 5.5, b1 = 15.5 - 18, c1 = 21.5 - 25, d1 = 15 - 17, e = 5.5 - 7, f = 1.5 - 2, g = 0.8 - 1.2, which can make the selection of the hub profile of the compressor housing more accurate, the optimization efficiency of the hub structure higher, further ensure the improvement effect of the hub optimization on the air flow, and reduce the air flow loss.

[0038] In one embodiment, a1 = 4.6242, b1 = 16.148, c1 = 22.349, d1 = 15.716, e = 6.3092, f = 1.8136, g = 0.9998.

[0039] In one embodiment, when x = 0, y = 1; when x = 0.1, y = [0.85, 0.88]; when x = 0.2, y = [0.77, 0.83]; when x = 0.3, y = [0.71, 0.79]; when x = 0.4, y = [0.66, 0.76]; when x = 0.5, y = [0.62, 0.74]; when x = 0.6, y = [0.59, 0.72]; when x = 0.7, y = [0.56, 0.71]; when x = 0.8, y = [0.54, 0.7]; when x = 0.9, y = [0.52, 0.7]; when x = 1, y = [0.51, 0.7]. The values of y corresponding to x are shown in Table 1 below.

[0040] Table 2 Turbine Disk Profile Parameter Table

[0041]

[0042] Table 1 is the hub profile parameter table designed by using the above formula of the present application.

[0043] In one embodiment, the circular ring section 10 is perpendicular to the central axis of the hub 9. In this case, the plane where the circular ring section 10 is located is the first plane, which is more convenient for the profile design of the hub 9.

[0044] The volute 1 has a volute tongue 2. On the cross-section passing through the central axis of the volute 1, the unilateral flow channel cross-sectional area of the volute 1 is A2, the intake width of the volute 1 is W, the distance between the intake port of the volute 1 and the central axis of the volute 1 is R. On the cross-section perpendicular to the central axis of the volute 1, taking the position of the connection line between the end point of the volute tongue 2 of the volute 1 and the central axis of the volute 1 as the starting position, and the rotation angle of the connection line around the central axis of the volute 1 along the air flow direction relative to the starting position as α, the volute 1 profile satisfies: A / (W*R) = a2α 3 +b2α 2+c2α + d2, where the value range of a2 is from -0.004 to -0.002, the value range of b2 is from +0.001 to +0.003, the value range of c2 is from 0.1 to 1, and the value range of d2 is from 0.1 to 1.1.

[0045] The compressor housing of the present application optimizes the scroll profile, making the cross-sectional area of the single-side flow path of the scroll related to the air inlet position of the scroll, so that the structure of the scroll profile can be more reasonable, effectively improving the gas flow efficiency in the scroll, reducing the airflow loss, and improving the working performance of the compressor.

[0046] When the value of A / (W*R) of the scroll profile is too small, the flow velocity in the scroll is too large, resulting in large flow losses; when the value of A / (W*R) of the scroll profile is too large, the scroll size is large, which is not convenient for structural arrangement. A / (W*R) increases with the increase of the α value to adapt to the flow rate change, but it cannot increase infinitely or suddenly. Infinite increase will lead to limited space in structure implementation, and sudden increase will lead to flow disorder, increasing the flow loss.

[0047] As a preferred embodiment, preferably, a2 = -0.003, b2 = 0.0022, c2 = 0.5322, and d2 = 0.6707.

[0048] Table 2 Preferred parameter table of scroll profile

[0049]

[0050] Table 2 is the preferred parameter table of the scroll profile designed by using the above formula of the present application.

[0051] As a preferred embodiment, when α = 0, the value range of A / (W*R) is [0.33, 1.00]; when α = π / 4, the value range of A / (W*R) is [0.55, 1.64]; when α = π / 2, the value range of A / (W*R) is [0.76, 2.27]; when α = π3 / 4, the value range of A / (W*R) is [0.97, 2.90]; when α = π, the value range of A / (W*R) is [1.18, 3.53]; when α = 5π / 4, the value range of A / (W*R) is [1.39, 4.16]; when α = 3π / 2, the value range of A / (W*R) is [1.60, 4.79]; when α = 7π / 4, the value range of A / (W*R) is [1.80, 5.41]. During the calculation process, in order to facilitate the calculation of A / (W*R), when taking the value of α, π = 3.1416 is taken.

[0052] The design of the scroll profile has a great influence on the performance of the compressor. Therefore, by optimizing the scroll profile, a better effect can be achieved in improving the performance of the compressor. In this embodiment, when the value of the scroll profile A / (W*R) is too small, the flow velocity in the scroll is too large, resulting in large flow losses. When the value of the scroll profile A / (W*R) is too large, the scroll size is large, and the structural design is not convenient for layout. Matching the position of the scroll profile in the air flow path with the scroll profile can comprehensively consider the requirements of air flow losses and size space, and obtain a better scroll profile structure.

[0053] In one embodiment, the scroll 1 is symmetric about a plane perpendicular to the central axis of the scroll 1, making the scroll 1 a symmetric structure, which can ensure better flow performance of the air flow in the scroll 1, further reduce the flow loss, and at the same time save the axial space, making the overall structure of the compressor housing more compact.

[0054] In one embodiment, on the cross-section passing through the central axis of the scroll 1, the single-side flow passage cross-section of the scroll 1 includes a first arc segment 3, a first straight segment 4, a first curve segment 5, a second curve segment 6, a second straight segment 7 and a second arc segment 8 connected in sequence. According to the analysis of the cross-section geometric characteristics, it can be known that the first arc segment 3 and the second arc segment 8 ensure that during the process of gas flowing into the scroll, the radial through-flow cross-sectional area smoothly transitions from small to large, which can effectively reduce the local flow loss.

[0055] As a preferred embodiment, adjacent segments are tangent at the connection positions, which can make the connection positions between different segments smoothly transition, further reducing the air flow loss.

[0056] Preferably, an angle β is formed between the first straight segment 4 and / or the second straight segment 7 and the plane perpendicular to the central axis of the scroll 1, and the value range of β is 15° to 45°. As a preferred embodiment, the value range of β is 25° to 35°, and preferably 30°. During the process of gas flowing into the scroll, the radial through-flow cross-sectional area changes from small to large. If the value of β is too small, the first curve segment 5 and the second curve segment 6 of the scroll are far from the central axis, resulting in a large radial size of the scroll and a long radial flow path, increasing the flow friction loss. If the value of β is too large, the change of the radial through-flow cross-sectional area from small to large is too drastic, and a deceleration and pressurization area is likely to appear, generating a vortex area, increasing the energy loss. The value of β is reasonable, thereby reducing the ability of fluid local loss and reducing the air flow loss.

[0057] In one embodiment, the compressor housing further includes a wheel cover 9 and a ring section 10. The first end of the ring section 10 is connected to the inlet end of the scroll tube 1, and the second end of the ring section 10 is connected to the wheel cover 9. The first end of the ring section 10 is tangent to the scroll tube 1 at the connection position, and the second end of the ring section 10 is tangent to the wheel cover 9 at the connection position. In this embodiment, the inner wall surface of the ring section 10 is a circular ring section, and this circular ring section is tangent to the arc surface of the first arc section of the scroll tube 1.

[0058] In one embodiment, the compressor housing further includes an air outlet pipe 11, and the air outlet pipe 11 is connected to the outlet position of the scroll tube 1.

[0059] Referring to Figures 3 to 6 As shown, in one embodiment, the air circulation machine housing includes the above-mentioned compressor housing 12.

[0060] In one embodiment, the air circulation machine housing further includes a fan housing 14 and a bearing seat 13, and at least one of the fan housing 14 and the bearing seat 13 is separately formed and fixedly connected to the compressor housing 12. In this embodiment, since at least one of the fan housing 14 and the bearing seat 13 is separately formed from the compressor housing 12, the entire air circulation machine housing can be divided into several parts. In this way, the air circulation machine housing does not need to be integrally formed, and each part can be processed separately. This not only reduces the geometric complexity of the outer shape, but also exposes the internal structure due to the cutting of each part. Therefore, the processing difficulty and production cost of the inner cavity of each part are reduced, it is easier to ensure the internal processing accuracy of each part, and at the same time, the maintainability of the air circulation machine housing is improved.

[0061] In one embodiment, the air circulation machine housing may further include an expander housing, and the expander housing is connected to the side of the bearing seat 13 away from the compressor housing 12. That is to say, the compressor housing 12 and the expander housing are connected through the bearing seat 13, so that the compressor housing 12, the bearing seat 13 and the expander housing can become three independent components. In this way, the inner cavities of the compressor housing 12 and the expander housing can be exposed and directly processed. Therefore, the processing difficulty of the inner cavities of the compressor housing 12 and the expander housing can be greatly reduced, the processing efficiency can be improved, and the processing cost can be reduced.

[0062] In one embodiment, a first flange 15 is provided on one side of the compressor housing 12 facing the bearing housing 13, and a second flange 16 is provided on one side of the bearing housing 13 facing the compressor housing 12. The first flange 15 and the second flange 16 are fixedly connected by bolts. To ensure the sealing performance between the compressor housing 12 and the bearing housing 13, a sealing gasket can be provided between the flange surface of the first flange 15 and the flange surface of the second flange 16, thereby effectively eliminating the leakage between the compressor housing 12 and the bearing housing 13.

[0063] In this embodiment, a plurality of threaded holes are provided along the circumferential direction on both the first flange 15 and the second flange 16. The threaded holes on the first flange 15 and the second flange 16 are correspondingly arranged, and then the compressor housing 12 and the bearing housing 13 are fastened together by screwing bolts into the threaded holes.

[0064] As a preferred embodiment, a first axial protrusion 19 is provided on one side of the bearing housing 13 facing the compressor housing 12, and a first shaft hole 21 is provided on the first flange 15. The first axial protrusion 19 is sleeved in the first shaft hole 21. In this embodiment, the first axial protrusion 19 is a cylindrical protrusion, and the first shaft hole 21 is a cylindrical shaft hole, wherein the diameter D1 of the first shaft hole 21 is 0.01 mm to 0.05 mm larger than the diameter d1 of the first axial protrusion 19, thereby facilitating the quick positioning and installation between the compressor housing 12 and the bearing housing 13.

[0065] In one embodiment, a third flange 17 is provided on one side of the compressor housing 12 facing the fan housing 14, and a fourth flange 18 is provided on one side of the fan housing 14 facing the compressor housing 12. The third flange 17 and the fourth flange 18 are fixedly connected by bolts. To ensure the sealing performance between the compressor housing 12 and the fan housing 14, a sealing gasket can be provided between the flange surface of the third flange 17 and the flange surface of the fourth flange 18, thereby effectively eliminating the leakage between the compressor housing 12 and the fan housing 14.

[0066] In this embodiment, a plurality of threaded holes are provided along the circumferential direction on both the third flange 17 and the fourth flange 18. The threaded holes on the third flange 17 and the fourth flange 18 are correspondingly arranged, and then the compressor housing 12 and the fan housing 14 are fastened together by screwing bolts into the threaded holes.

[0067] As a preferred embodiment, a second axial protrusion 20 is provided on one side of the compressor housing 12 facing the fan housing 14. A second axial hole 22 is provided on the fourth flange 18, and the second axial protrusion 20 is sleeved in the second axial hole 22. In this embodiment, the second axial protrusion 20 is a cylindrical protrusion, and the second axial hole 22 is a cylindrical axial hole, wherein the diameter D2 of the second axial hole 22 is 0.01 mm to 0.05 mm larger than the diameter d2 of the second axial protrusion 20, so as to facilitate the quick positioning and installation between the compressor housing 12 and the bearing seat 13.

[0068] As a preferred embodiment, an avoidance groove 23 is provided on the outer peripheral wall of the second axial protrusion 20. In this embodiment, the avoidance groove on the outer peripheral wall of the second axial protrusion 20 occupies 1 / 3 to 9 / 10 of the total axial length of the second axial protrusion 20, so that while ensuring the structural strength of the second axial protrusion 20, the frictional resistance during the process of inserting the second axial protrusion 20 into the second axial hole 22 can be minimized, and the installation difficulty of inserting the second axial protrusion 20 into the second axial hole 22 can be reduced.

[0069] According to the embodiments of the present application, the air circulator includes the above-mentioned compressor housing or the above-mentioned air circulator housing.

[0070] It is easy for those skilled in the art to understand that, on the premise of no conflict, the above-mentioned advantageous ways can be freely combined and superimposed.

[0071] The above are only the preferred embodiments of the present application, and are not intended to limit the present application. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present application shall be included in the protection scope of the present application. The above is only the preferred implementation manner of the present application. It should be pointed out that for those of ordinary skill in the art, without departing from the technical principle of the present application, several improvements and modifications can be made, and these improvements and modifications should also be regarded as the protection scope of the present application.

Claims

1. A compressor housing, characterized in that, It includes an air inlet pipe (24), a wheel cover (9), a circular ring section (10) and a volute (1) connected in sequence. The inner ring radius of the circular ring section (10) is r0. A first intersection line is formed at the intersection position of the inner circumferential surface of the circular ring section (10) and the wheel cover (9). A second intersection line is formed at the intersection position of the inner circumferential surface of the wheel cover (9) and the air inlet pipe (24). The plane passing through the first intersection line and perpendicular to the central axis of the wheel cover (9) is the first plane. The distance between the second intersection line and the first plane is z1. Any plane is taken between the second intersection line and the first plane. The distance between this any plane and the first plane is zi. The intersection line of this any plane and the inner circumferential surface of the wheel cover (9) is a circle with a radius of ri. Let the profile line of the wheel cover (9) be y = ri / r0, the variable x = zi / z1, and y = a1x 6 -b1x 5 +c1x 4 -d1x 3 +ex 2 -fx + g, where a1 = 4.1 - 6.6, b1 = 15 - 22, c1 = 20 - 30, d1 = 14 - 20, e = 5 - 8, f = 1 - 2.5, g = 0.5 - 1.

5.

2. The compressor housing according to claim 1, characterized in that, a1 = 4.3 to 5.5, b1 = 15.5 to 18, c1 = 21.5 to 25, d1 = 15 to 17, e = 5.5 to 7, f = 1.5 to 2, g = 0.8 to 1.

2.

3. The compressor housing according to claim 2, wherein, a1 = 4.6242, b1 = 16.148, c1 = 22.349, d1 = 15.716, e = 6.3092, f = 1.8136, g = 0.9998.

4. The compressor housing according to claim 1, characterized in that, When x = 0, y = 1; when x = 0.1, y = [0.85, 0.88]; when x = 0.2, y = [0.77, 0.83]; when x = 0.3, y = [0.71, 0.79]; when x = 0.4, y = [0.66, 0.76]; when x = 0.5, y = [0.62, 0.74]; when x = 0.6, y = [0.59, 0.72]; when x = 0.7, y = [0.56, 0.71]; when x = 0.8, y = [0.54, 0.7]; when x = 0.9, y = [0.52, 0.7]; when x = 1, y = [0.51, 0.7].

5. The compressor housing according to claim 1, characterized in that, The circular ring segment (10) is perpendicular to the central axis of the wheel cover (9).

6. The compressor housing according to any one of claims 1 to 5, characterized in that, The scroll tube (1) has a scroll tongue (2). In a cross-section passing through the central axis of the scroll tube (1), the cross-sectional area of one-sided flow path of the scroll tube (1) is A2, the intake width of the scroll tube (1) is W, the distance between the intake port of the scroll tube (1) and the central axis of the scroll tube (1) is R. In a cross-section perpendicular to the central axis of the scroll tube (1), taking the position where the connection line between the end point of the scroll tongue (2) of the scroll tube (1) and the central axis of the scroll tube (1) as the starting position, and taking the rotation angle of the connection line around the central axis of the scroll tube (1) along the air flow direction relative to the starting position as α, the scroll tube (1) profile satisfies: A / (W*R) = a2α 3 +b2α 2 +c2α + d2, where the value range of a2 is -0.004 to -0.002, the value range of b2 is +0.001 to +0.003, the value range of c2 is 0.1 to 1, and the value range of d2 is 0.1 to 1.

1.

7. The compressor housing according to claim 6, wherein, a2 = -0.003, b2 = 0.0022, c2 = 0.5322, d2 = 0.6707.

8. The compressor housing according to any one of claims 1 to 5, characterized in that The scroll tube (1) is symmetric about a plane perpendicular to the central axis of the scroll tube (1).

9. The compressor housing according to any one of claims 1 to 5, characterized in that, In the cross-section passing through the central axis of the scroll tube (1), the unilateral flow passage cross-section of the scroll tube (1) includes a first circular arc segment (3), a first straight segment (4), a first curved segment (5), a second curved segment (6), a second straight segment (7) and a second circular arc segment (8) connected in sequence.

10. The compressor housing according to claim 9, characterized in that, An included angle β is formed between the first straight segment (4) and / or the second straight segment (7) and the plane perpendicular to the central axis of the scroll tube (1), and the value range of β is 15° to 45°.

11. The compressor housing according to any one of claims 1 to 5, characterized in that, The circular ring segment (10) is tangent to the scroll tube (1) at the connection position, and the circular ring segment (10) is tangent to the wheel cover (9) at the connection position.

12. An air circulation machine housing, characterized in that, Including the compressor housing according to any one of claims 1 to 11.

13. The air circulation machine housing according to claim 12, characterized in that, The air circulation machine housing further includes a fan housing (14) and a bearing seat (13), and at least one of the fan housing (14) and the bearing seat (13) is separately formed and fixedly connected to the compressor housing (12).

14. The air circulation machine housing according to claim 13, characterized in that, A first flange (15) is provided on one side of the compressor housing (12) facing the bearing seat (13), a second flange (16) is provided on one side of the bearing seat (13) facing the compressor housing (12), and the first flange (15) and the second flange (16) are fixedly connected by bolts.

15. The air circulation machine housing according to claim 14, wherein, A first axial protrusion (19) is provided on one side of the bearing seat (13) facing the compressor housing (12), a first shaft hole (21) is provided on the first flange (15), and the first axial protrusion (19) is sleeved in the first shaft hole (21).

16. The air circulation machine housing according to claim 13, characterized in that, On one side of the compressor housing (12) facing the blower housing (14), a third flange (17) is provided. On one side of the blower housing (14) facing the compressor housing (12), a fourth flange (18) is provided. The third flange (17) and the fourth flange (18) are fixedly connected by bolts.

17. The air circulation machine housing according to claim 16, wherein, On one side of the compressor housing (12) facing the blower housing (14), a second axial protrusion (20) is provided. On the fourth flange (18), a second axial hole (22) is provided. The second axial protrusion (20) is sleeved in the second axial hole (22).

18. An air circulation machine, characterized in that, It includes the compressor housing (12) according to any one of claims 1 to 11 or the air circulation machine housing according to any one of claims 12 to 17.

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