WO2021147593A1 - 消旋结构、混流风机组件及空调器 - Google Patents

消旋结构、混流风机组件及空调器 Download PDF

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Publication number
WO2021147593A1
WO2021147593A1 PCT/CN2020/138198 CN2020138198W WO2021147593A1 WO 2021147593 A1 WO2021147593 A1 WO 2021147593A1 CN 2020138198 W CN2020138198 W CN 2020138198W WO 2021147593 A1 WO2021147593 A1 WO 2021147593A1
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WIPO (PCT)
Prior art keywords
racemization
trajectory
flow channel
swirl
line
Prior art date
Application number
PCT/CN2020/138198
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English (en)
French (fr)
Inventor
刘华
马屈杨
池晓龙
苏玉海
张治平
夏凯
张碧瑶
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2021147593A1 publication Critical patent/WO2021147593A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D23/00—Other rotary non-positive-displacement pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/403—Casings; Connections of working fluid especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the present disclosure relates to the field of fans, in particular to a de-rotation structure, a mixed flow fan assembly and an air conditioner.
  • the air duct system is one of the components used in the air conditioner to accelerate the heat exchange of the air in the area of the air conditioner.
  • the designer selects and matches the appropriate fan according to the actual needs of the different models and specifications of the air conditioner to meet the working quality and comfort of the air conditioner.
  • the air path system of some air conditioners known to the inventor adopts a mixed flow fan.
  • the embodiments of the present disclosure provide an anti-rotation structure, a mixed flow fan assembly, and an air conditioner, which can improve the air supply performance.
  • a racemic structure including:
  • Race wheel cover with a through cavity
  • the racer hub is located in the inner cavity of the racer wheel cover and forms a racer flow channel between the racer wheel cover and the racer wheel cover;
  • the anti-rotation blade is connected between the cavity wall of the inner cavity and the outer wall of the anti-rotation hub;
  • the center trajectory of the anti-rotation flow channel from the inlet to the outlet on the longitudinal section through the axis of the anti-rotation structure has a radial extreme point located between the inlet and the outlet of the anti-rotation flow channel.
  • the center trajectory includes:
  • the first trajectory line includes a pear-shaped quartic curve, and the radial extreme point is located on the pear-shaped quartic curve.
  • the pear-shaped quartic curve equation is:
  • p and q are the radian parameters of the pear-shaped quartic curve
  • x, y are the independent variable and the dependent variable
  • x L*t
  • L is the chord length parameter of the pear-shaped quartic curve
  • t a is 0.6 to 0.8
  • t b is 0.9 to 1.
  • the center trajectory includes a first trajectory, and the first portion of the first trajectory between the entrance of the de-swirl flow channel and the radial extreme point has a radius of curvature smaller than that of the radial extremum.
  • the radius of curvature of the first trajectory line from the radial extreme point to the second part adjacent to the exit side of the de-swirl flow channel.
  • the center trajectory also has an inflection point located between the radial extreme point and the exit of the de-swirl flow channel.
  • the center trajectory further includes:
  • the first trajectory line includes a pear-shaped quartic curve, and the radial extreme point is located on the pear-shaped quartic curve;
  • the second trajectory line is located between the inflection point and the exit of the de-swirl flow channel.
  • the second trajectory line includes a straight line segment on the side of the inflection point adjacent to the outlet of the anti-swirl flow channel.
  • the cross-sectional area of the de-swirl flow channel at each position corresponding to the first trajectory is smaller than that of the de-swirl flow path at each position corresponding to the second trajectory.
  • the projection point of the radial extreme point on the axis of the racemization structure is located at 2/5 to 3 of the length of the projection line of the racemation wheel cover on the axis of the racemization structure. /5.
  • the cavity wall of the inner cavity of the race wheel cover is in the shape of a first revolving body
  • the outer wall of the race wheel hub is in the shape of a second revolving body
  • the raceway flow channel is along the Each cross section in the axial direction is in a circular ring shape.
  • the racemization structure includes 6-25 racemization blades.
  • the racemized structure includes 15 racemized blades.
  • a mixed-flow fan assembly including: a mixed-flow fan; and the aforementioned derotation structure.
  • the mixed flow fan is connected to the de-rotation structure, the air outlet of the mixed flow fan is butted with the inlet of the de-rotation channel, and the air outlet direction of the air outlet is aligned with the center track line The part located at the entrance of the vortex flow channel is parallel.
  • an air conditioner including: the aforementioned mixed flow fan assembly.
  • the radial extremum point located between the inlet and the outlet of the flow channel is set by the center trajectory corresponding to the race flow channel formed between the race wheel cover and the race wheel hub, so that the flow channel
  • the outward oblique airflow entering the channel inlet can be gradually adjusted to the inward oblique direction through the radial extreme point along the de-swirl flow channel, so that the radial distribution of the outlet air on the air outlet side is more uniform, and the pressure head can be further increased. , And then obtain better ventilation performance.
  • the embodiments of the present disclosure can effectively improve the air supply performance of the mixed flow fan.
  • Fig. 1 is a structural schematic diagram of a longitudinal section of some embodiments of a mixed flow fan assembly according to the present disclosure
  • Fig. 2 is a structural schematic diagram of a longitudinal section of some embodiments of a racemization structure according to the present disclosure
  • FIG. 3 is a schematic diagram of a cut-out part of a pear-shaped quartic curve used in some embodiments of the racemization structure of the present disclosure
  • FIG. 4 is a schematic diagram of a three-dimensional structure of some embodiments of a racemized structure according to the present disclosure
  • FIG. 5 is a structural schematic diagram of the racemization blade and racemization hub in some embodiments of the racemization structure according to the present disclosure when viewed in a direction perpendicular to the axis of the racemization structure;
  • Fig. 6 is an enlarged schematic diagram of the racemization blade corresponding to the ellipse G in Fig. 5;
  • FIG. 7 is a schematic diagram of the size of the racemization blade in some embodiments of the racemization structure according to the present disclosure.
  • FIG. 8 is a schematic diagram of the size of the tracer line used in some embodiments of the racemization structure according to the present disclosure.
  • Figures 9 and 10 respectively show the racemization blades and racemization hubs in some embodiments of the racemization structure of the present disclosure when viewed from the inlet side of the racemization channel to the outlet side along the axis direction of the racemization structure, and from the perspective of the elimination.
  • Fig. 11 and Fig. 12 are respectively the vorticity diagrams of the reference racemization structure example and the racemization structure embodiment of the present disclosure.
  • a specific device when it is described that a specific device is located between the first device and the second device, there may or may not be an intermediate device between the specific device and the first device or the second device.
  • the specific device When it is described that a specific device is connected to another device, the specific device may be directly connected to the other device without an intervening device, or may not be directly connected to the other device but with an intervening device.
  • the mixed-flow fan assembly includes a mixed-flow fan 10 and a de-rotation structure, and the de-rotation structure is connected to the mixed-flow fan 10 for guiding the air out of the mixed-flow fan 10.
  • the driving unit for example, a motor
  • the mixed flow fan 10 is installed in a derotation structure, and the axis of the derotation structure coincides with the axis of the mixed flow fan 10.
  • the anti-rotation structure is fixedly arranged, and the hub and blades of the mixed flow fan 10 rotate relative to the anti-rotation structure under the driving action of the driving unit.
  • the outlet direction of the air outlet of the mixed flow fan 10 is at an acute angle with respect to the axis of the mixed flow fan 10, and the anti-rotation flow channel of the anti-rotation structure is butted with the air outlet of the mixed flow fan 10 at the interface S.
  • the racemization structure includes a racemization wheel cover 20, a racemization hub 30 and a racemization blade 40.
  • the racer cover 20 has an inner cavity penetrating along the axis of the racer structure, and the racer hub 30 is located in the inner cavity of the racer cover 20 and forms a racer channel with the racer cover 20 50.
  • the cavity wall of the inner cavity of the race wheel cover 20 is in the shape of a first revolution
  • the outer wall of the race wheel hub 30 is in the shape of a second revolution.
  • Each cross section in the axial direction of the racemization structure is circular.
  • the cavity wall of the inner cavity of the race wheel cover 20 and the outer wall of the race wheel hub 30 are not limited to be in the shape of revolution, and may also be in the shape of non-rotation, such as a combination of pyramids of different sizes.
  • each cross section of the racemization flow channel 50 along the axial direction of the racemization structure is a closed ring shape such as a polygon, an ellipse, and the like.
  • the inlet of the anti-rotation flow channel 50 formed between the race-reducing wheel cover 20 and the race-reducing wheel hub 30 is butted with the air outlet of the mixed flow fan 10.
  • the shape of the inlet of the anti-swirl flow channel 50 is configured to be substantially the same as the size and shape of the air outlet of the mixed flow fan, so as to form a close docking relationship and reduce air leakage at the docking interface.
  • the anti-rotation blade 40 is connected between the cavity wall of the inner cavity and the outer wall of the anti-rotation hub 30.
  • the racemization structure includes a plurality of racemization blades 40, optionally includes 6-25 racemization blades, and optionally further includes 15 racemization blades.
  • the surface of the anti-rotation blade adopts a twisted design.
  • the mixed flow fan 10 located on the upper side of FIG. Through the interface S, it is output into the racemization flow channel 50 of the racemization structure.
  • the air flow entering the elimination flow channel 50 changes its flow direction along the trajectory of the elimination flow channel 50 and is discharged downward from the outlet located on the lower side of the elimination flow channel 50.
  • the raceway 50 has a central trajectory line 53 from the inlet 51 to the outlet 52 on the longitudinal section passing through the axis z of the racemization structure
  • the radial extreme point M 2 is located between the inlet 51 and the outlet 52 of the swirling flow channel 50.
  • the center trajectory line 53 also has an inflection point M 3 between the radial extreme point M 2 and the outlet 52 of the de-swirl flow channel 50.
  • the center trajectory line 53 here refers to the midpoint of the connection between each point of the cavity wall of the race wheel cover on the projection line of the longitudinal section and the corresponding point of the outer wall of the race wheel hub on the projection line of the longitudinal section. Reference line.
  • the points of the center trajectory line 53 corresponding to this area and the race wheel Corresponding points of the cavity wall of the inner cavity of the cover and the outer wall of the racemetic hub respectively on the projection line of the longitudinal section are located on the same straight line perpendicular to the axis z.
  • the racer hub 30 has a side adjacent to the inlet end of the racer cover 20 and is used for mounting a motor of the mixed flow fan 10 with a mounting end 31.
  • the projection point z 4 of the mounting end 31 on the axis z of the racemization structure is located within the range of the projection line z 1 z 3 of the racemation wheel cover 20 on the axis z of the racemization structure.
  • the mounting end 31 is located below the connecting end 21 where the race wheel cover 20 and the mixed flow fan are connected in the extending direction of the axis z.
  • the installation end 31 and the connection end 21 enclose the inlet 51 of the anti-swirl flow channel 50.
  • this area corresponds to this area
  • the points of the central trajectory line 53 are the ends of the cavity wall of the inner cavity of the race wheel cover corresponding to the projections that do not overlap, respectively, and the outer wall of the race wheel hub closest to the end of the non-coincident area (for example, in Figure 2 The midpoint of the line perpendicular to the z-axis and passing through the intersection of the z 4 line and the outer wall of the racer hub).
  • the inflection point here refers to the boundary point between the convex arc and the concave arc of the continuous curve.
  • the radial extreme point here refers to the point on the center trajectory that is farthest from the axis z in a direction perpendicular to the axis z.
  • the radial extreme point between the inlet and the outlet of the flow channel is set on the center trajectory, so that the outward oblique airflow entering from the inlet of the flow channel can be gradually adjusted along the de-swirl flow channel through the radial extreme point.
  • the wind out of the racemization structure of this embodiment can be more evenly distributed in the radial direction along the axis of the racemization structure on the wind out side of the racemization structure, thereby Achieve greater air volume, and further increase the pressure head, obtain lower noise under the same air volume, and improve the air supply performance.
  • the anti-rotation structure of this embodiment When the anti-rotation structure of this embodiment is applied to a mixed flow fan, a better air supply state can form a feedback effect on the upstream mixed flow fan, that is, a good air supply also indicates that the fan is at a position close to the best efficiency point, which can also improve the mixed flow.
  • the pressure head of the fan ensures strong resistance to static pressure, which is finally reflected in the air volume, noise, efficiency, pressure head and other air supply performance indicators of the mixed flow fan.
  • the mixed flow fan of this embodiment is applied to an air conditioner, the distribution of the air volume blown by the derotation structure to the surface of the air conditioner heat exchanger can be made more uniform.
  • the air flow after passing the radial extreme point of the center trajectory line flows to the inflection point along the derotation flow channel, so that the obtained wind can be adjusted to be between the axis of the derotation structure
  • the smaller the included angle so as to further make the wind out of the racemization structure more uniform on the outlet side of the racemization structure in the radial direction along the axis of the racemization structure.
  • the center trajectory line 53 includes: a first trajectory line and a second trajectory line.
  • the first trajectory line is located between the inlet 51 of the de-swirl flow channel 50 and the inflection point M 3 , that is, the arc segment of the dashed line from M 1 to M 3 in FIG. 2.
  • the second trajectory line is located between the inflection point M 3 and the exit 52 of the de-swirl flow channel 50, that is, the arc segment of the dashed line from M 3 to M 4 in FIG. 2.
  • the first trajectory line and the second trajectory line are smoothly connected to the inflection point M 3 .
  • the center trajectory line 53 may not include the second trajectory line, but only the first trajectory line.
  • the first trajectory line is a curve, such as a parabola or a hyperbola. In other embodiments, the first trajectory line is a combination of a curve and a straight line, or a combination of multiple curves. 2 and 3, in some embodiments, the first trajectory line includes a pear-shaped quartic curve, and the radial extreme point M 2 is located on the pear-shaped quartic curve.
  • p and q are the radian parameters of the pear-shaped quartic curve
  • x and y are the independent variable and the dependent variable, respectively.
  • the degree of bending of the pear-shaped quartic curve can be adjusted by setting different p and q.
  • x L*t
  • L is the chord length parameter of the pear-shaped quartic curve, 0 ⁇ t ⁇ 1.
  • the overall chord length of the pear-shaped quartic curve can be adjusted by setting different L.
  • the axial size of the elimination structure is reduced, so that the first trajectory line includes a pear-shaped quartic curve.
  • the first trajectory line includes a pear-shaped quartic curve.
  • t a is 0.6 to 0.8
  • t b is 0.9 to 1, so as to obtain the part of the pear-shaped quartic curve where the radial extreme point can be obtained.
  • the projection point z 2 of the radial extremum point M 2 on the axis z of the racemization structure is located on the projection line z 1 of the racetrack wheel cover 20 on the axis z of the racemization structure 2/5 ⁇ 3/5 of the length of z 3.
  • the airflow entering the racemization channel can avoid sudden changes in flow direction and cause flow loss, and can also reduce the axial size of the racemization structure.
  • the radius of curvature of the first part of the first trajectory between the inlet 51 of the de-swirl flow channel 50 and the radial extreme point M 2 is smaller than the first trajectory at the point M 2.
  • the radius of curvature of said second portion of the outlet side of the radial extreme points of M 2 to the flow passage 50 racemic, for example the first trajectory located radially to the extreme point of inflection M 2 M 3 between the part.
  • the arc of the part M 1 to M 2 on the first trajectory is larger, while the arc of the part M 2 to M 3 is relatively small, so that the flow direction of the airflow that enters the anti-swirl flow channel obliquely outward can be
  • the part from M 1 to M 2 can be adjusted faster, and the space size of the racemization structure can be reduced.
  • the direction of the air outlet of the mixed-flow fan 10 and the center trajectory 53 are located in the de-rotation channel 50.
  • the part of the inlet 51 is parallel. In this way, the flow loss of the airflow of the mixed flow fan at the inlet of the de-swirl flow channel can be reduced or avoided.
  • the portion of the first trajectory near the inlet 51 may be a straight line segment.
  • the second trajectory line includes a straight line segment.
  • the straight line segment may be located at the part of the second trajectory line after the inflection point M 3 to M 4 .
  • the air flow out of the outlet 52 can be as parallel to the axis z as possible, so as to increase the air flow rate in the central area on the air outlet side, and further make the air outlet distribution more uniform.
  • the cross-sectional area of the de-swirl flow channel 50 at each position corresponding to the straight line is larger than the cross-sectional area of the de-swirl flow path 50 at each position corresponding to the first trajectory. area.
  • the cross-sectional area of the flow channel 50 at a certain position corresponding to the first trajectory line is the area of the part where the plane perpendicular to the axis of the racemization structure and passing through the position of the first trajectory intersects the elimination flow channel. .
  • the cross-sectional area of the flow passage of the raceway 50 at a certain position corresponding to the straight section is the area of the portion where the plane perpendicular to the axis of the raceway structure and passing through the position of the straight section intersects the raceway flow passage.
  • the racer blade 40 is connected between the cavity wall of the inner cavity of the racer wheel cover and the outer wall of the racer hub 30.
  • the intersecting interface of the racer blade 40 and the racer hub 30 is the blade root section 41, and the intersecting interface of the racer blade 40 and the racer wheel cover 20 is the outer edge section 42 of the blade. According to the flow direction v f of the airflow along the z-axis shown in FIG.
  • the edge of the vane 40 located upstream of the airflow is the leading edge 43, which corresponds to the side of the inlet 51 of the vane 50; the vane 40 is located in the airflow
  • the downstream edge is the trailing edge 44, which corresponds to the side of the outlet 52 of the cyclonic flow channel 50.
  • the blade root section 41 and the blade outer edge section 42 can be designed with reference to the aircraft airfoil.
  • the projection of the contour line of at least one of the blade root section 41 and the blade outer edge section 42 on the longitudinal section includes a tracer line.
  • a plurality of race-off blades are connected to the race-off hub 30.
  • the corresponding longitudinal section is the longitudinal section that the race-off blade faces in the direction of the axis.
  • Tractor line is a trajectory line that follows the traction force of the hauling object in the direction of the rope.
  • the angle between the tangent of the trailing edge and the axis of the racem structure corresponding to the trailing edge ⁇ 1 is greater than the angle ⁇ 2 between the tangent of the trailing edge and the axis of the racem structure, so that the airflow is relatively large relative to the axis.
  • the included angle ⁇ 1 enters, and after the racemized blades projected to conform to the tracer line, it is smoothly converted into a smaller included angle ⁇ 2, so that the circumferential component velocity of the airflow is gradually eliminated in this process, so that the exit area of the racemetic structure The air distribution is more even.
  • the tracer line is relatively smooth and its curvature gradually increases in one direction. Therefore, in this embodiment, the airflow changes with the curvature of the tracer line, which can prevent the blade from being bent in part of the area. If the angle is too large, local airflow impact and boundary layer separation are generated, which greatly reduces the flow loss, eliminates the vortex area, and reduces the vortex noise.
  • the angles a, b, and d in Figure 8 are adjusted by the values of the parameters t and k in the equation, where the angle a is the angle between the tangent of one end of the tracer line and the y-axis, and the angle b is the other of the tracer line.
  • the angle between the tangent at one end and the x-axis, and the angle d is the angle between the tangent at both ends of the tracer line.
  • the projection of the contour line of the de-rotation blade on the longitudinal section may include a part taken from the tracer line , In order to reduce or avoid the occurrence of vortex shedding. For example, intercept the part of the curve where t is within the range of t c and t d , that is, t c ⁇ t ⁇ t d .
  • t c is 0 and t d is 0.48 to 0.6.
  • the projected line of the line on the x-axis the intercepted part can correspond to the part of the trailing line corresponding to the length of the projected line from the starting point of the trailing line to the left of the projection point on the x-axis to about 0.3 to 0.45 times the length of the projected line .
  • t d is preferably 0.51, and the intercepted part of the tracer line corresponds to the range from the starting point of the tracer line to the left of the projection point of the x-axis to about 1/3 of the length of the projection line corresponding to the length of the tracer line part.
  • the left contour line 41a and the right contour line 41b of the blade root section 41 both include a tracer line
  • the left contour line 42a and the right contour line 42b of the blade outer edge section 42 both include a tracer line.
  • the circumferential component velocity of the airflow can be gradually reduced from the outer edge of the blade and the root of the blade, so that the airflow distribution in the exit area of the anti-rotation structure is more uniform, the vortex area is eliminated as much as possible, and the vortex noise is reduced.
  • a part of the contour line of the blade root section 41 or the blade outer edge section 42 includes a tracer line
  • the other part of the contour line adopts other straight lines, curves, or a combination of straight lines and curves.
  • E and C in Fig. 7 are the positions where the blade root section 41 and the blade outer edge section 42 correspond to the leading edge 43 respectively, and F and D are the blade root section 41 and the blade outer edge section 42 corresponding to the trailing edge, respectively. 44 parts.
  • the leading edge 43 and the trailing edge 44 are both straight segments.
  • the leading edge 43 or the trailing edge 44 is an arc line segment or a combination of an arc line segment and a straight line segment.
  • the left contour line 41a of the blade root section 41 and the left contour line 42a of the blade outer edge section 42 each include a tracer line, which respectively corresponds to the position of the leading edge 43 of the vane 40.
  • the angle between the tangent line and the projection line of the front edge 43 of the vane 40 on the longitudinal section plane is ⁇ and ⁇ .
  • the left contour line 41a of the blade root section 41 corresponds to the tangent of the trailing edge 44 of the vane 40 and the left contour 41a corresponds to the tangent of the leading edge 43 of the vane 40.
  • the angle is ⁇
  • the left contour line 42a of the outer edge section 42 of the blade corresponds to the tangent to the trailing edge 44 of the vane 40 and the left contour 42a corresponds to the leading edge 43 of the vane 40
  • the angle of the tangent of the part is ⁇ .
  • ⁇ and ⁇ can be adjusted to a preferred range, such as 25° to 75°, and ⁇ and ⁇ can be adjusted to a preferred range, such as 110° -170°.
  • ⁇ and ⁇ can be adjusted to a preferred range, such as 110° -170°.
  • the anti-rotation blades can obtain a better guiding effect, and the circumferential partial velocity of the airflow of the anti-rotation blades is further reduced.
  • both ⁇ and ⁇ are 56°
  • both ⁇ and ⁇ are 159°.
  • the airflow entering the vortex flow channel has a partial velocity along the axial and circumferential directions. After the guiding effect of the surface of the vortex vane, the circumferential partial velocity of the airflow adjacent to the exit of the vortex flow channel can be effectively reduced, and more conversion Is the axial sub-velocity.
  • the angle values of ⁇ and ⁇ may be the same or different according to actual needs, and the angle values of ⁇ and ⁇ may be the same or different.
  • the above-mentioned angle can also be applied to the right contour line 41 b of the blade root section 41 including the tracer line and the right contour line 42 b of the blade outer edge section 42.
  • chord length of the contour line of the blade root section 41 and the blade outer edge section 42 can be selected according to the relevant parameters of the mixed flow fan and the structural size of the elimination structure.
  • the chord of the contour line of the blade root section 41 corresponds to the chord length.
  • the length EF is 53.8 mm
  • the chord length CD corresponding to the contour line of the outer edge section 42 of the blade is 55.5 mm.
  • the projection point of the axis z of the racemization hub 30 on the cross-section of the racemization structure is O
  • the leading edge 43 of the racemization blade 40 is
  • the projection point of the intersection point of the racemization hub 30 on the cross section of the racemization structure is O 1 .
  • the first included angle ⁇ of the line connecting O and O 1 relative to the projection line of the front edge 43 of the racemizing blade 40 on the cross-section of the racemizing structure is -85° ⁇ 85°.
  • the projection point of the intersection point of the trailing edge 44 of the racer blade 40 and the racer hub 30 on the cross section of the racer structure is O 2 , and the line connecting O and O 2 is relative to the racer blade 40
  • the second included angle ⁇ of the front edge 43 of the front edge 43 on the cross-section of the racem structure is -85° to 85°.
  • first included angle ⁇ and the second included angle ⁇ take the same positive value or the same negative value, it means that the leading edge 43 is relative to the connection between O and O 1 under the viewing angle of either of Figures 9 and 10.
  • the line and the trailing edge 44 are both located on the upstream side (or downstream side) of the same clockwise direction relative to the line connecting O and O 2. If the first included angle ⁇ and the second included angle ⁇ take different signs, the leading edge 43 relative to the upstream side and the downstream side (or the upstream side and downstream side) O O O connection with the trailing edge 44 and the connection with the O 1 and O 2 are located in the same clockwise direction.
  • the first included angle ⁇ and the second included angle ⁇ are designed to obtain a more reasonable inlet angle and outlet angle, to avoid the obvious flow separation when the air enters the vane, thus bringing more The large vortex area, in turn, leads to problems such as air volume attenuation and noise increase.
  • the first included angle is 10°-20°, for example 14.41°.
  • the second included angle is 15°-30°, such as 21.63°.
  • the mixed flow fan assembly embodiments of the present disclosure have improved air volume, efficiency, pressure head and other parameters, aerodynamic performance and wind noise level. Obviously improved.
  • FIG. 11 and FIG. 12 are respectively the vorticity diagrams of the reference racemization structure example known to the inventor and the racemization structure embodiment of the present disclosure.
  • the vorticity diagram can be simulated by fluid dynamics analysis software (such as ANSYS CFD-Post software).
  • the block structure represents the vortex concentration area. The larger the block structure and the denser the distribution means that the vortex is too concentrated, and the vortex concentration increases the degree of flow separation.
  • the internal air ducts of the mixed flow fan and the vortex structure cause the flow to be unsmooth due to the existence of the vortex concentration area, thereby increasing the resistance. Larger, the flow loss increases, which directly leads to the attenuation of the air volume.
  • the various embodiments of the aforementioned derotation structure can be applied to the aforementioned mixed-flow fan assembly, but are not limited to the mixed-flow fan assembly, and can also be applied to various equipment or application scenarios that need to guide airflow.
  • the present disclosure also provides an air conditioner, including any of the foregoing embodiments of the mixed flow fan assembly. Through the mixed flow fan assembly of the present disclosure, the wind speed distribution on the surface of the heat exchanger of the air conditioner can be made more uniform, and the heat exchange performance can be improved.

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Abstract

一种消旋结构、混流风机组件及空调器。消旋结构包括：消旋轮盖(20)，具有贯通的内腔；消旋轮毂(30)，位于消旋轮盖(20)的内腔中，并与消旋轮盖(20)之间形成消旋流道(50)；和消旋叶片(40)，连接在内腔的腔壁和消旋轮毂(30)的外壁之间；其中，消旋流道(50)在通过消旋结构的轴线(z)的纵切面上从进口(51)到出口(52)的中心轨迹线(53)具有邻近消旋流道(50)的出口(52)的拐点(M 3)和位于消旋流道(50)的进口(51)和所述拐点(M 3)之间的径向极值点(M 2)。

Description

消旋结构、混流风机组件及空调器
相关申请的交叉引用
本申请是以CN申请号为202010063851.6，申请日为2020年1月20日的申请为基础，并主张其优先权，该CN申请的公开内容在此作为整体引入本申请中。
技术领域
本公开涉及风机领域，尤其涉及一种消旋结构、混流风机组件及空调器。
背景技术
风路系统是空调器内用于促使空调器作用区域内的空气加快热交换的组成部分之一。在空调器的风路系统中，设计人员根据空调器的不同机型和规格所对应的实际需求，选择和搭配合适的风机以满足空调器的工作品质和使用舒适性。
为满足空调器的风量和压头指标，发明人所知晓的一些空调器的风路系统采用了混流风机。
发明内容
经研究发现，发明人所知晓的一些空调器中的混流风机存在出风倾斜，送风不集中的问题，这对空调器的内部换热器表面的风速分布及换热性能存在不利影响。
有鉴于此，本公开实施例提供一种消旋结构、混流风机组件及空调器，能够改善送风性能。
在本公开的一个方面，提供一种消旋结构，包括：
消旋轮盖，具有贯通的内腔；
消旋轮毂，位于所述消旋轮盖的内腔中，并与所述消旋轮盖之间形成消旋流道；和
消旋叶片，连接在所述内腔的腔壁和所述消旋轮毂的外壁之间；
其中，所述消旋流道在通过所述消旋结构的轴线的纵切面上从进口到出口的中心轨迹线具有位于所述消旋流道的进口和出口之间的径向极值点。
在一些实施例中，所述中心轨迹线包括：
第一轨迹线，包括梨形四次曲线，且所述径向极值点位于所述梨形四次曲线。
在一些实施例中，所述梨形四次曲线方程为：
y 2＝x 3*(p-x)/q 2
其中，p、q为所述梨形四次曲线的弧度参数，x、y分别是自变量和因变量，x＝L*t，L为所述梨形四次曲线的弦长参数，且t a≤t≤t b，t a为0.6～0.8，t b为0.9～1。
在一些实施例中，所述中心轨迹线包括第一轨迹线，所述第一轨迹线位于所述消旋流道的进口到所述径向极值点之间的第一部分的曲率半径小于所述第一轨迹线在所述径向极值点到邻近所述消旋流道的出口一侧的第二部分的曲率半径。
在一些实施例中，所述中心轨迹线还具有位于所述径向极值点和所述消旋流道的出口之间的拐点。
在一些实施例中，所述中心轨迹线还包括：
第一轨迹线，包括梨形四次曲线，且所述径向极值点位于所述梨形四次曲线；和
第二轨迹线，位于所述拐点与所述消旋流道的出口之间。
在一些实施例中，所述第二轨迹线包括在所述拐点邻近所述消旋流道的出口一侧的直线段。
在一些实施例中，所述消旋流道在对应于所述第一轨迹线的各个位置的流道截面积小于所述消旋流道在对应于所述第二轨迹线的各个位置的流道截面积。
在一些实施例中，所述径向极值点在所述消旋结构的轴线的投影点位于所述消旋轮盖在所述消旋结构的轴线的投影线的长度的2/5～3/5。
在一些实施例中，所述消旋轮盖的内腔的腔壁呈第一回转体形，所述消旋轮毂的外壁呈第二回转体形，所述消旋流道沿所述消旋结构的轴线方向的各个横截面均呈圆环形。
在一些实施例中，所述消旋结构包括6～25个消旋叶片。
在一些实施例中，所述消旋结构包括15个消旋叶片。
在本公开的一个方面，提供一种混流风机组件，包括：混流风机；和前述的消旋结构。
在一些实施例中，所述混流风机与所述消旋结构连接，所述混流风机的出风口与所述消旋通道的进口对接，且所述出风口的出风方向与所述中心轨迹线位于所述消旋流道的进口的部分平行。
在本公开的一个方面，提供一种空调器，包括：前述的混流风机组件。
因此，根据本公开实施例，通过在消旋轮盖和消旋轮毂之间形成的消旋流道对应 的中心轨迹线设置位于流道进口和出口之间的径向极值点，使得从流道进口进入的外斜向气流能够沿着消旋流道经过径向极值点逐步调整到内斜方向，从而使得出风在出风侧的径向分布更加均匀，并使压头得以进一步增加，进而获得较好的送风性能。在应用于混流风机时本公开实施例能够有效地改善混流风机的送风性能。
附图说明
构成说明书的一部分的附图描述了本公开的实施例，并且连同说明书一起用于解释本公开的原理。
参照附图，根据下面的详细描述，可以更加清楚地理解本公开，其中：
图1是根据本公开混流风机组件的一些实施例的纵切面的结构示意图；
图2是根据本公开消旋结构的一些实施例的纵切面的结构示意图；
图3是根据本公开消旋结构的一些实施例中所采用的梨形四次曲线的截取部分的示意图；
图4是根据本公开消旋结构的一些实施例的立体结构示意图；
图5是根据本公开消旋结构的一些实施例中消旋叶片和消旋轮毂在垂直于消旋结构的轴线的方向观看的视角下的结构示意图；
图6是图5中椭圆G对应的消旋叶片的放大示意图；
图7是根据本公开消旋结构的一些实施例中消旋叶片的尺寸示意图；
图8是根据本公开消旋结构的一些实施例中所采用的曳物线的尺寸示意图；
图9和图10分别是根据本公开消旋结构的一些实施例中消旋叶片和消旋轮毂在沿消旋结构的轴线方向从消旋流道进口侧向出口侧观看的视角下和从消旋流道出口侧向进口侧观看的视角下的结构示意图；
图11和图12分别是参考消旋结构实例和本公开消旋结构实施例的涡量图。
应当明白，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。此外，相同或类似的参考标号表示相同或类似的构件。
具体实施方式
现在将参照附图来详细描述本公开的各种示例性实施例。对示例性实施例的描述仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。本公开可以以许多不同的形式实现，不限于这里所述的实施例。提供这些实施例是为了使本公开透彻且 完整，并且向本领域技术人员充分表达本公开的范围。应注意到：除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置、材料的组分、数字表达式和数值应被解释为仅仅是示例性的，而不是作为限制。
本公开中使用的“第一”、“第二”以及类似的词语并不表示任何顺序、数量或者重要性，而只是用来区分不同的部分。“包括”或者“包含”等类似的词语意指在该词前的要素涵盖在该词后列举的要素，并不排除也涵盖其他要素的可能。“上”、“下”、“左”、“右”等仅用于表示相对位置关系，当被描述对象的绝对位置改变后，则该相对位置关系也可能相应地改变。
在本公开中，当描述到特定器件位于第一器件和第二器件之间时，在该特定器件与第一器件或第二器件之间可以存在居间器件，也可以不存在居间器件。当描述到特定器件连接其它器件时，该特定器件可以与所述其它器件直接连接而不具有居间器件，也可以不与所述其它器件直接连接而具有居间器件。
本公开使用的所有术语(包括技术术语或者科学术语)与本公开所属领域的普通技术人员理解的含义相同，除非另外特别定义。还应当理解，在诸如通用字典中定义的术语应当被解释为具有与它们在相关技术的上下文中的含义相一致的含义，而不应用理想化或极度形式化的意义来解释，除非这里明确地这样定义。
对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为说明书的一部分。
如图1所示，是根据本公开混流风机组件的一些实施例的纵切面的结构示意图。参考图1，在一些实施例中，混流风机组件包括混流风机10和消旋结构，消旋结构与混流风机10连接，用于对混流风机10的出风进行引导。在一些实施例中，混流风机10的驱动单元(例如电机)安装在消旋结构内，消旋结构的轴线与混流风机10的轴线重合。在一些实施例中，消旋结构固定设置，而混流风机10的轮毂及叶片在驱动单元的驱动作用下相对于消旋结构转动。在一些实施例中，混流风机10的出风口的出风方向相对于混流风机10的轴线呈锐角，消旋结构的消旋流道与混流风机10的出风口在界面S对接。
参考图1，在一些实施例中，消旋结构包括消旋轮盖20、消旋轮毂30和消旋叶片40。消旋轮盖20具有沿消旋结构的轴线贯通的内腔，消旋轮毂30位于所述消旋轮盖20的内腔中，并与所述消旋轮盖20之间形成消旋流道50。
参考图1，在一些实施例中，消旋轮盖20的内腔的腔壁呈第一回转体形，所述消 旋轮毂30的外壁呈第二回转体形，所述消旋流道50沿所述消旋结构的轴线方向的各个横截面均呈圆环形。在另一些实施例中，消旋轮盖20的内腔的腔壁和消旋轮毂30的外壁不限于呈回转体形，也可以呈非回转体形，例如不同尺寸的棱锥形的组合等。相应地，消旋流道50沿所述消旋结构的轴线方向的各个横截面呈多边形、椭圆形等的闭合环形。
在图1中，消旋轮盖20和消旋轮毂30之间形成的消旋流道50的进口与混流风机10的出风口对接。在一些实施例中，消旋流道50的进口的形状被构造成与混流风机的出风口的尺寸和形状基本相同，以便形成紧密的对接关系，减少气流在对接界面的泄漏。
在图1中，消旋叶片40连接在所述内腔的腔壁和所述消旋轮毂30的外壁之间。在一些实施例中，消旋结构包括多个消旋叶片40，可选包括6～25个消旋叶片，进一步可选包括15个消旋叶片。参考图1，在一些实施例中，消旋叶片的表面采用扭曲设计。在消旋流道50对气流形成轴向和径向的引导作用时，消旋叶片40能够在消旋流道50内对消旋流道50内的气流形成周向上的引导作用。
参考图1中通过多个箭头示意的气流情况，位于图1上侧的混流风机10在转动时能够将轴向进入的气流逐步变为外斜向的周向出风，并将周向出风经界面S输出到消旋结构的消旋流道50内。进入到消旋流道50的气流随着消旋流道50的轨迹线改变流向，并从位于消旋流道50下侧的出口向下排出。
如图2所示，为根据本公开消旋结构的一些实施例的纵切面的结构示意图。参考图2，并结合参考图3-图5，在一些实施例中，消旋流道50在通过所述消旋结构的轴线z的纵切面上从进口51到出口52的中心轨迹线53具有位于所述消旋流道50的进口51和出口52之间的径向极值点M 2。在另一些实施例中，中心轨迹线53还具有位于所述径向极值点M 2和所述消旋流道50的出口52之间的拐点M 3。
这里的中心轨迹线53是指消旋轮盖的内腔的腔壁在纵切面的投影线的各个点与消旋轮毂的外壁在纵切面的投影线上的对应点的连线中点所形成的参考线。对于消旋轮盖和消旋轮毂在轴线z的投影重合的区域(例如图2中z 4到z 3对应的区域)，与该区域对应的中心轨迹线53的部分的各点与消旋轮盖的内腔的腔壁和消旋轮毂的外壁分别在纵切面的投影线上的对应点位于垂直于轴线z的同一直线上。
参考图2，在一些实施例中，所述消旋轮毂30具有邻近所述消旋轮盖20的入口端一侧，且用于安装混流风机10的电机的安装端31。所述安装端31在所述消旋结构 的轴线z的投影点z 4位于所述消旋轮盖20在所述消旋结构的轴线z的投影线z 1z 3的范围内。在图2中，安装端31在轴线z的延伸方向上位于消旋轮盖20与混流风机进行连接的连接端21的下方。安装端31与连接端21围成消旋流道50的进口51。
对于消旋轮盖在轴线z的投影与消旋轮毂不重合的区域(例如图2中z 1到z 4对应的区域，即安装端31与连接端21之间的部分)，与该区域对应的中心轨迹线53的部分的各点为消旋轮盖的内腔的腔壁对应于投影不重合的各点分别与消旋轮毂的外壁最靠近不重合的区域的端部(例如图2中垂直于z轴且通过z 4的直线与消旋轮毂的外壁的交点)的连线的中点。
这里的拐点是指连续曲线的凸弧和凹弧的分界点。这里的径向极值点是指中心轨迹线上沿垂直于轴线z的方向距离轴线z最远的点。
本实施例通过在中心轨迹线设置位于流道进口和出口之间的径向极值点，使得从流道进口进入的外斜向气流能够沿着消旋流道经过径向极值点逐步调整到内斜方向，相比于发明人知晓的一些消旋结构，本实施例的消旋结构的出风能够在消旋结构出风侧沿消旋结构的轴线的径向上更均匀地分布，从而实现更大的风量，并使压头得以进一步增加，获得同风量下较低的噪音，进而改善送风性能。
当本实施例的消旋结构应用于混流风机时，较好的送风状态能够对上游的混流风机形成反馈作用，即送风良好同时表明风机处于靠近最佳效率点的位置，也能提高混流风机的压头，确保较强的抗静压能力，最终体现在混流风机的风量、噪音、效率、压头等各项送风性能的指标上。当本实施例混流风机应用到空调器时，可使得消旋结构向空调换热器的表面吹出的风量分布更加均匀。
对于中心轨迹线还包括拐点的实施例来说，经过中心轨迹线的径向极值点后的气流沿消旋流道流动到拐点后，可使得出风能够调整到与消旋结构轴线之间更小夹角，从而进一步地使消旋结构的出风在消旋结构出风侧沿消旋结构的轴线的径向上更加均匀。
参考图2，在一些实施例中，所述中心轨迹线53包括：第一轨迹线和第二轨迹线。第一轨迹线位于所述消旋流道50的进口51与所述拐点M 3之间，即图2中M 1到M 3的虚线的弧线段。第二轨迹线位于所述拐点M 3与所述消旋流道50的出口52之间，即图2中M 3到M 4的虚线的弧线段。第一轨迹线和第二轨迹线平滑连接于拐点M 3。在另一些实施例中，中心轨迹线53可不包括第二轨迹线，而只包括第一轨迹线。
在一些实施例中，第一轨迹线为曲线，例如抛物线、双曲线。在另一些实施例中， 第一轨迹线为曲线和直线的组合，或者多种曲线的组合。参考图2和图3，在一些实施例中，第一轨迹线包括梨形四次曲线，且所述径向极值点M 2位于所述梨形四次曲线。这样当气流在消旋流道内对应第一轨迹线的部分流动时，能够沿梨形四次曲线平滑地从相对于轴线呈较大外斜向角度过渡到较小的内斜向角度，从而有效地降低或避免气流在消旋流道内方向突变带来的流动损失，提高流动效率。
参考图3，在一些实施例中，梨形四次曲线方程为：y 2＝x 3*(p-x)/q 2。在该方程中，p、q为所述梨形四次曲线的弧度参数，x、y分别是自变量和因变量。通过设定不同的p和q可以调整梨形四次曲线的弯曲程度。x＝L*t，L为所述梨形四次曲线的弦长参数，0≤t≤1。通过设定不同的L可以调整梨形四次曲线的整体弦长。
在一些实施例中，为了在消旋流道50内实现平滑的较大角度的气流方向转换，减小消旋结构的轴向尺寸，使第一轨迹线包括从梨形四次曲线上截取的一部分。例如截取t在t a和t b的范围内的曲线部分，即t a≤t≤t b。在一些实施例中，t a为0.6～0.8，t b为0.9～1，以获取梨形四次曲线中能够取得径向极值点的部分。
在图2中，所述径向极值点M 2在所述消旋结构的轴线z的投影点z 2位于所述消旋轮盖20在所述消旋结构的轴线z的投影线z 1z 3的长度的2/5～3/5。这样可使得进入消旋流道的气流避免流向突变而造成流动损失，也能够降低消旋结构的轴向尺寸。
参考图2，在一些实施例中，第一轨迹线位于所述消旋流道50的进口51到所述径向极值点M 2之间的第一部分的曲率半径小于第一轨迹线在所述径向极值点M 2到所述消旋流道50的出口一侧的第二部分的曲率半径，例如第一轨迹线位于径向极值点M 2到所述拐点M 3之间的部分。换句话说，第一轨迹线上M 1到M 2的部分的弧度更大，而M 2到M 3的部分弧度相对较小，这样可使得外斜向进入消旋流道的气流流向能够在M 1到M 2的部分更快的调整，并缩小消旋结构的空间尺寸。
参考图1和图2，在一些实施例中，将消旋结构与混流风机10进行连接时，混流风机10的出风口的出风方向与所述中心轨迹线53位于所述消旋流道50的进口51的部分平行。这样可减少或避免混流风机的气流在消旋流道的进口的流动损失。在一些实施例中，第一轨迹线靠近进口51的部分可以为直线段。
参考图2，在一些实施例中，所述第二轨迹线包括直线段。直线段可以位于第二轨迹线在拐点M 3之后到M 4的部分。这样从出口52流出的气流能够尽量与轴线z平行，以增加出风侧在中心区域的气流量，进一步使出风分布更加均匀。在一些实施例中，消旋流道50在对应于所述直线段的各个位置的流道截面积大于所述消旋流道50 在对应于所述第一轨迹线的各个位置的流道截面积。消旋流道50在对应于第一轨迹线的某个位置的流道截面积为垂直于消旋结构的轴线且经过第一轨迹线的该位置的平面与消旋流道相交的部分的面积。消旋流道50在对应于直线段的某个位置的流道截面积为垂直于消旋结构的轴线且经过直线段的该位置的平面与消旋流道相交的部分的面积。这相当于在消旋流道50靠近出口52的位置设置了直线扩压段，以便在出口侧进一步扩压，以提升压头，确保实际需要的静压值。在另一些实施例中，也可以取消这个直线扩压段。
参考图2、图5和图6，在一些实施例中，消旋叶片40连接在消旋轮盖的内腔的腔壁和所述消旋轮毂30的外壁之间。消旋叶片40与所述消旋轮毂30的相交界面为叶片根部截面41，所述消旋叶片40与所述消旋轮盖20的相交界面为叶片外缘截面42。根据图7所示的气流沿z轴的流动方向v f，消旋叶片40位于气流上游的边缘为前缘43，其对应于消旋流道50的进口51一侧；消旋叶片40位于气流下游的边缘为尾缘44，其对应于消旋流道50的出口52一侧。
叶片根部截面41和所述叶片外缘截面42可参考飞机翼型进行设计。在一些实施例中，叶片根部截面41和所述叶片外缘截面42中的至少一个的轮廓线在所述纵切面上的投影包括曳物线。消旋轮毂30上连接有多个消旋叶片，对于任一个消旋叶片来说，其对应的纵切面是该消旋叶片朝向轴线的方向所正对的纵切面。曳物线是遵从曳拉物体受绳线方向牵引力作用的运动轨迹线。
在图7中，曳物线对应于前缘部位的切线与消旋结构的轴线的夹角μ1大于尾缘部位的切线与消旋结构的轴线的夹角μ2，这样气流以相对于轴线较大的夹角μ1进入，经过投影符合曳物线的消旋叶片之后被平滑地转化成较小的夹角μ2，从而在这个过程中逐步地消除气流周向分速度，使得消旋结构的出口区域气流分布更加均匀。并且相比于轮廓线的投影呈折线的方案，曳物线比较平滑，且其曲率沿一个方向逐渐增加，因此在本实施例中气流随着曳物线的曲率变化，能够避免叶片部分区域弯曲角度过大而产生局部气流冲击和边界层分离，从而大幅降低流动损失，消除涡区，减低涡流噪音。
参考图8，在一些实施例中，曳物线的方程包括：x＝k/(e t+e -t)；y＝t-(e t-e -t)/(e t+e -t)，其中e是数学常数，x、y是图8中曲线在x轴和y轴的取值，且0≤t≤1。图8中的角度a、b和d由方程中的参数t和k的取值进行调整，其中角度a为曳物线的一端的切线与y轴的夹角，角度b为曳物线的另一端的切线与x轴的夹角，角度d为曳物线 两端的切线的夹角。通过将消旋叶片的轮廓线在纵切面的投影设计成包括曳物线，使得经过消旋叶片的气流的周向分速度能够逐渐减小或消除，避免因消旋叶片的部分区域弯曲角度过大而产生的局部气流冲击和边界层分离的现象，从而大幅地降低气流在消旋结构内的流动损失。
对于图8所示的曳物线来说，从角度a对应的一端到角度b对应的另一端的曲线弧度的整体趋势是递增的。为了使消旋叶片的轮廓线与消旋流道内的气流流动和分布方向更加贴近，在一些实施例中，可使消旋叶片的轮廓线在纵切面的投影包括从曳物线上截取的一部分，以减少或避免漩涡脱落的发生。例如截取t在t c和t d的范围内的曲线部分，即t c≤t≤t d。在一些实施例中，t c为0，t d为0.48～0.6。参考图8，以图8中曳物线右侧端点为曳物线的起始点(对应于t＝0)，左侧端点为曳物线的终止点(对应于t＝1)，参考曳物线在x轴的投影线，被截取的部分可对应于从曳物线起始点在x轴的投影点向左到投影线长度的大约0.3～0.45倍长度的范围所对应于曳物线的部分。进一步，t d优选为0.51，曳物线被截取的部分对应于从曳物线起始点在x轴的投影点向左到投影线长度的大约1/3长度的范围所对应于曳物线的部分。
在图6中，叶片根部截面41的左侧轮廓线41a和右侧轮廓线41b均包括曳物线，叶片外缘截面42的左侧轮廓线42a和右侧轮廓线42b均包括曳物线。这样从叶片外缘与叶片根部都能使气流的周向分速度逐渐减小，从而使得消旋结构的出口区域气流分布更加均匀，尽量消除涡区，降低涡流噪声。在另一些实施例中，叶片根部截面41或叶片外缘截面42的一部分轮廓线包括曳物线，另一部分轮廓线采用其他直线、曲线或直线和曲线的组合。
参考图6，图7中的E和C分别为叶片根部截面41和叶片外缘截面42对应于前缘43的部位，F和D分别为叶片根部截面41和叶片外缘截面42对应于尾缘44的部位。在一些实施例中，前缘43和尾缘44均为直线段。在另一些实施例中，前缘43或尾缘44为弧线段或弧线段与直线段的组合。
在图7中，叶片根部截面41的左侧轮廓线41a和叶片外缘截面42的左侧轮廓线42a均包括曳物线，其分别对应于所述消旋叶片40的前缘43的部位的切线与所述消旋叶片40的前缘43在所述纵切面的投影线之间的夹角为θ和δ。叶片根部截面41的左侧轮廓线41a对应于所述消旋叶片40的尾缘44的部位的切线与左侧轮廓线41a对应于所述消旋叶片40的前缘43的部位的切线的夹角为ε，叶片外缘截面42的左侧轮廓线42a对应于所述消旋叶片40的尾缘44的部位的切线与左侧轮廓线42a对应于所 述消旋叶片40的前缘43的部位的切线的夹角为γ。
在一些实施例中，通过调整前述曳物线方程中的参数k和t，θ和δ能够被调整为优选范围，例如25°～75°，ε和γ能够被调整为优选范围，例如110°-170°。这样可使消旋叶片获得更良好的引导作用，更进一步减少消旋叶片的气流的周向分速度。例如θ和δ均为56°，ε和γ均为159°。进入消旋流道的气流具有沿轴向和周向的分速度，经过消旋叶片表面的引导作用，使得邻近消旋流道出口的气流的周向分速度得以有效减少，而更多地转化为轴向分速度。
在一些实施例中，根据实际需要，θ和δ的角度值可以相同，也可以不同，ε和γ的角度值可以相同，也可以不同。上述角度也可以适用于包括曳物线的叶片根部截面41的右侧轮廓线41b和叶片外缘截面42的右侧轮廓线42b。
叶片根部截面41和叶片外缘截面42的轮廓线的弦长可根据混流风机的相关参数以及消旋结构的结构尺寸进行选择，例如在一些实施例中，叶片根部截面41的轮廓线对应的弦长EF为53.8mm，叶片外缘截面42的轮廓线对应的弦长CD为55.5mm。
参考图9和图10，在一些实施例中，所述消旋轮毂30的轴线z在所述消旋结构的横截面的投影点为O，所述消旋叶片40的前缘43与所述消旋轮毂30的交点在所述消旋结构的横截面的投影点为O 1。O与O 1的连线相对于所述消旋叶片40的前缘43在所述消旋结构的横截面的投影线的第一夹角α为-85°～85°。所述消旋叶片40的尾缘44与所述消旋轮毂30的交点在所述消旋结构的横截面的投影点为O 2，O与O 2的连线相对于所述消旋叶片40的前缘43在所述消旋结构的横截面的投影线的第二夹角β为-85°～85°。
这里第一夹角α和第二夹角β如果同取正值或同取负值，则表示在图9和图10中的任一个的视角下，前缘43相对于O与O 1的连线和尾缘44相对于O与O 2的连线均位于同一时针方向的上游侧(或下游侧)，如果第一夹角α和第二夹角β取值为异号，则前缘43相对于O与O 1的连线和尾缘44相对于O与O 2的连线分别位于同一时针方向的上游侧和下游侧(或者下游侧和上游侧)。
根据实际需要，通过设计第一夹角α和第二夹角β的取值来获得更为合理的进气角和出气角，避免气流进入消旋叶片时产生明显的流动分离，从而带来较大的涡流区，进而导致风量衰减，噪音提升等问题。在一些实施例中，第一夹角为10°～20°，例如14.41°。在一些实施例中，所述第二夹角为15°～30°，例如21.63°。
参考图1-图10，为了进一步说明本公开混流风机组件相比于发明人知晓的一些混 流风机(例如下表中的参考混流风机实例)的优点，提供一些作为参考的仿真数据，如下表：
Figure PCTCN2020138198-appb-000001
通过上述表格的仿真数据可知，在相同转速(例如3200rpm)下，相比于参考混流风机实例，本公开混流风机组件实施例在风量、效率和压头等参数都有所提升，气动性能和风噪水平得到明显改善。
如图11和图12所示，分别为发明人知晓的参考消旋结构实例和本公开消旋结构实施例的涡量图。该涡量图可通过流体动力学分析软件(例如ANSYS CFD-Post软件)仿真得出，在图中块状结构代表涡流集中区域。块状结构越大、分布越密表示涡量过于集中，而涡量集中使得流动分离程度增加，混流风机及消旋结构的内部风道因涡流集中区域的存在而导致流动不顺畅，从而阻力增大，流动损失增大，进而直接导致出风风量衰减。
比较图11和图12可以发现，图11对应的参考消旋结构实例的内部存在密集且较大的涡流集中区域，而图12中本公开消旋结构实施例内部的涡流集中区域尺寸较小，且比较分散。这说明了本公开消旋结构实施例的内部流动状况比较好，不会存在过多的涡区，这样可以大幅降低气流的流动损失，提高流动效率，并且能够降低涡流噪声和离散噪声。当混流风机处于最佳效率点附近时，在同转速下风量得以有效提升，获得更好的抗静压能力，并表现为更高的压头。当混流风机组件的出口存在较大阻力时，风量的衰减幅度也能够相对较小。
上述消旋结构的各个实施例可应用于前述的混流风机组件，但不仅限于应用在混流风机组件，其还可以应用于各类需要引导气流的设备或应用场景。另外，本公开还提供了一种空调器，包括前述任一种混流风机组件的实施例。通过本公开的混流风机组件，能够使空调器的换热器表面的风速分布更加均匀，提高换热性能。
至此，已经详细描述了本公开的各实施例。为了避免遮蔽本公开的构思，没有描述本领域所公知的一些细节。本领域技术人员根据上面的描述，完全可以明白如何实 施这里公开的技术方案。
虽然已经通过示例对本公开的一些特定实施例进行了详细说明，但是本领域的技术人员应该理解，以上示例仅是为了进行说明，而不是为了限制本公开的范围。本领域的技术人员应该理解，可在不脱离本公开的范围和精神的情况下，对以上实施例进行修改或者对部分技术特征进行等同替换。本公开的范围由所附权利要求来限定。

Claims (15)

  1. 一种消旋结构，包括：
    消旋轮盖(20)，具有贯通的内腔；
    消旋轮毂(30)，位于所述消旋轮盖(20)的内腔中，并与所述消旋轮盖(20)之间形成消旋流道(50)；和
    消旋叶片(40)，连接在所述内腔的腔壁和所述消旋轮毂(30)的外壁之间；
    其中，所述消旋流道(50)在通过所述消旋结构的轴线(z)的纵切面上从进口(51)到出口(52)的中心轨迹线(53)具有位于所述消旋流道(50)的进口(51)和出口(52)之间的径向极值点(M 2)。
  2. 根据权利要求1所述的消旋结构，其中，所述中心轨迹线(53)包括：
    第一轨迹线，包括梨形四次曲线，且所述径向极值点(M 2)位于所述梨形四次曲线。
  3. 根据权利要求2所述的消旋结构，其中，所述梨形四次曲线方程为：
    y 2＝x 3*(p-x)/q 2，
    其中，p、q为所述梨形四次曲线的弧度参数，x、y分别是自变量和因变量，x＝L*t，L为所述梨形四次曲线的弦长参数，且t a≤t≤t b，t a为0.6～0.8，t b为0.9～1。
  4. 根据权利要求2或3所述的消旋结构，其中，所述中心轨迹线(53)包括第一轨迹线，所述第一轨迹线位于所述消旋流道(50)的进口(51)到所述径向极值点(M 2)之间的第一部分的曲率半径小于所述第一轨迹线在所述径向极值点(M 2)到邻近所述消旋流道(50)的出口(52)一侧的第二部分的曲率半径。
  5. 根据权利要求1所述的消旋结构，其中，所述中心轨迹线(53)还具有位于所述径向极值点(M 2)和所述消旋流道(50)的出口(52)之间的拐点(M 3)。
  6. 根据权利要求5所述的消旋结构，其中，所述中心轨迹线(53)包括：
    第一轨迹线，包括梨形四次曲线，且所述径向极值点(M 2)位于所述梨形四次曲线；和
    第二轨迹线，位于所述拐点(M 3)与所述消旋流道(50)的出口(52)之间。
  7. 根据权利要求6所述的消旋结构，其中，所述第二轨迹线包括在所述拐点(M 3)邻近所述消旋流道(50)的出口(52)一侧的直线段。
  8. 根据权利要求7所述的消旋结构，其中，所述消旋流道(50)在对应于所述 直线段的各个位置的流道截面积大于所述消旋流道(50)中对应于所述第一轨迹线的各个位置的流道截面积。
  9. 根据权利要求1所述的消旋结构，其中，所述径向极值点(M 2)在所述消旋结构的轴线(z)的投影点(z 2)位于所述消旋轮盖(20)在所述消旋结构的轴线(z)的投影线(z 1z 3)的长度的2/5～3/5。
  10. 根据权利要求1所述的消旋结构，其中，所述消旋轮盖(20)的内腔的腔壁呈第一回转体形，所述消旋轮毂(30)的外壁呈第二回转体形，所述消旋流道(50)沿所述消旋结构的轴线方向的各个横截面均呈圆环形。
  11. 根据权利要求1所述的消旋结构，其中，所述消旋结构包括6～25个消旋叶片(40)。
  12. 根据权利要求11所述的消旋结构，其中，所述消旋结构包括15个消旋叶片(40)。
  13. 一种混流风机组件，包括：
    混流风机(10)；和
    权利要求1～12任一所述的消旋结构。
  14. 根据权利要求13所述的混流风机组件，其中，所述混流风机(10)与所述消旋结构连接，所述混流风机(10)的出风口与所述消旋通道的进口(51)对接，且所述出风口的出风方向与所述中心轨迹线(53)位于所述消旋流道(50)的进口(51)的部分平行。
  15. 一种空调器，包括：
    权利要求13或14所述的混流风机组件。
PCT/CN2020/138198 2020-01-20 2020-12-22 消旋结构、混流风机组件及空调器 WO2021147593A1 (zh)

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