WO2020090533A1 - Mécanisme d'admission/échappement et température - Google Patents

Mécanisme d'admission/échappement et température Download PDF

Info

Publication number
WO2020090533A1
WO2020090533A1 PCT/JP2019/041204 JP2019041204W WO2020090533A1 WO 2020090533 A1 WO2020090533 A1 WO 2020090533A1 JP 2019041204 W JP2019041204 W JP 2019041204W WO 2020090533 A1 WO2020090533 A1 WO 2020090533A1
Authority
WO
WIPO (PCT)
Prior art keywords
intake
exhaust
impeller
duct
exhaust device
Prior art date
Application number
PCT/JP2019/041204
Other languages
English (en)
Japanese (ja)
Inventor
静 横手
拓 宇野
将 小山
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to JP2020553793A priority Critical patent/JPWO2020090533A1/ja
Publication of WO2020090533A1 publication Critical patent/WO2020090533A1/fr

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/06—Arrangement in connection with cooling of propulsion units with air cooling
    • 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
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
    • H01L23/00—Details of semiconductor or other solid state devices
    • H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
    • H01L23/46—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids
    • H01L23/467—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids by flowing gases, e.g. air

Definitions

  • the present invention relates to a temperature conditioning unit that performs temperature conditioning of a temperature-controlled object by cooling or heating, and an intake / exhaust device used in the temperature conditioning unit, and more particularly to increasing the output of the intake / exhaust device.
  • An electricity storage device such as a secondary battery and a power conversion device such as an inverter and a converter (hereinafter collectively referred to as a temperature-conditioning object) generate heat due to internal resistance and external resistance when a current flows. If the temperature of the temperature-controlled object becomes excessively high, the performance will not be sufficiently exhibited. Further, even when the ambient temperature is excessively low such as use in a cold region, the performance of the temperature-controlled body is not sufficiently exhibited. That is, the temperature of the temperature-conditioned body has a great influence on the output characteristic or the power conversion characteristic, and further on the life of the temperature-controlled body.
  • These temperature-controlled objects can be installed in hybrid vehicles, electric vehicles (EV, Electric Vehicle), and the like.
  • the cells included in the secondary battery have internal resistance. Further, contact resistance may occur at the connection between cells.
  • contact resistance may occur at the connection between cells.
  • the cell When a current for charging the cell or a current discharged from the cell is applied to the cell having these resistance components, the cell generates heat.
  • the temperature rises due to heat generation side reactions that do not contribute to charge and discharge are likely to occur, leading to a decrease in capacity and an increase in internal resistance.
  • an air-cooling unit that uses an intake and exhaust device (blower) to forcibly cool the secondary battery is used.
  • the temperature conditioning unit is required to supply a predetermined amount of air to the secondary battery in order to suppress a temperature rise of cells included in the secondary battery during normal operation.
  • the temperature conditioning unit is required to add a predetermined amount of heat to the secondary battery so that the secondary battery can exhibit the required performance during operation at extremely low temperatures.
  • the performance of the secondary battery is evaluated after taking these temperature measures into consideration.
  • the power supply system using the secondary battery can improve the performance depending on these temperature countermeasures.
  • the power supply system using the secondary battery can reduce the required number of cells depending on these temperature countermeasures.
  • the installation area for the secondary battery which is the temperature-controlled object, is limited. Therefore, it is difficult to secure a sufficient space for installing the secondary battery in the vehicle in which the secondary battery is used. Miniaturization of the secondary battery is required so that the required performance can be exhibited in a given space. Further, miniaturization of the temperature-conditioned body is also required.
  • the temperature conditioning unit tends to increase in size, and not only the secondary battery, which is the temperature-controlled object, but also the temperature conditioning unit has higher output and smaller size. It is required to be compatible with.
  • a duct is connected to the intake port of a fan case in which a centrifugal fan is arranged.
  • the duct is provided with a rotation suppressing means composed of a concave portion composed of an inclined surface portion and a flat surface portion to prevent the fluid flowing in the duct from rotating in the direction opposite to the direction in which the fan rotates. It's suppressed.
  • One aspect of the present invention is a turbofan having a rotating shaft, an impeller rotating about the rotating shaft, and a tubular fan case having a sidewall surrounding an outer periphery of the impeller, and an intake side of the turbofan.
  • a duct connected to the exhaust side and a bottom part connected to the fan case and connected to the duct are provided, and the fan case is one end of the side wall on the exhaust side or the intake side of the turbofan.
  • Has a first opening, the bottom portion is connected to the fan case so as to close the first opening, and the duct, the bottom portion, and the first opening are perpendicular to the rotation axis.
  • the contour lines of the inner wall surface of the duct and the bottom portion are arc-shaped curves R corresponding to the first openings, and first contour lines extending from both ends of the curve R and And a second contour, wherein the first contour and the second contour, the first linear portion L 1 and the second straight portion L 2 parallel and straight with each other, respectively have, the projection
  • the distance from the center X 0 of the first opening to the first straight line L 1 or the first stretched line E 1 obtained by extending the first straight line L 1 to the bottom side is the first from the center X 0 of the opening of the second straight portion L 2 or the second linear portion longer than the distance of L 2 second to 2 draw line E 2 that extends to the bottom side
  • the first linear portion L 1 The distance between the second straight line L 2 and the second straight line L 2 is W, the diameter of the first opening is D, and the first straight line L 1 and the second straight line are defined from the center X 0 of the first opening.
  • Another aspect of the present invention includes the above-described intake / exhaust device and a housing that accommodates the temperature-controlled object, and cools or heats the temperature-controlled object by blowing air or intake air from the intake / exhaust device. , Relating to the temperature conditioning unit.
  • FIG. 6 is a diagram schematically showing an example of a projected shape in which the duct, the bottom, and the first opening are projected on a plane perpendicular to the rotation axis in the intake and exhaust device according to the present disclosure. It is a perspective view showing the appearance of the intake and exhaust machine concerning one embodiment of this indication.
  • 1 is a side view of an intake / exhaust device according to an embodiment of the present disclosure.
  • FIG. 3 is a top view of the intake and exhaust device according to the embodiment of the present disclosure. It is a perspective view showing the appearance of a turbo fan. It is a longitudinal section showing the inside of a turbofan.
  • An intake / exhaust machine includes a turbo fan having a rotating shaft, an impeller rotating about the rotating shaft, and a tubular fan case having a side wall surrounding an outer circumference of the impeller.
  • the intake / exhaust machine also includes a duct connected to the intake side or the exhaust side of the turbofan, and a bottom portion connected to the fan case and connected to the duct.
  • the fan case has a first opening at one end on the exhaust side or the intake side of the turbofan on the side wall, and the bottom is connected to the fan case so as to close the first opening.
  • the gas sucked by the impeller passes through the space between the side wall of the fan case and the outer circumference of the impeller, passes through the first opening, collides with the bottom, and the direction of the air flow is changed, and the gas is provided on the blower side. Flows into the duct.
  • the gas passes through the duct provided on the intake side, is sucked by the impeller through the first opening, and flows out into the space between the side wall of the fan case and the outer circumference of the impeller.
  • the duct is connected to the side wall of the fan case via the bottom so as to extend in a direction perpendicular to the rotation axis, for example.
  • the duct provided on the air blow side is referred to as “air blow duct”
  • the duct provided on the air intake side is referred to as “air intake duct”.
  • the fan case may have a second opening at the other end of the side wall on the exhaust side or the intake side in addition to the first opening.
  • the first opening or the second opening existing on the exhaust side of the side wall of the fan case will be referred to as a “blower”.
  • the first opening or the second opening existing on the intake side of the side wall of the fan case is referred to as an “intake port”.
  • the intake / exhaust device may include either one of a set of a blower port and a blower duct and a set of an intake port and an intake duct, or may include both.
  • a part of the inner wall surface of the side wall of the fan case may face the impeller to form a gas flow path from the intake port to the blower port.
  • the intake and exhaust device achieves high output by forming the duct shape in the vicinity of the connecting portion between the duct and the bottom portion into a shape that is bent or curved in a specific direction according to the rotation direction of the rotating shaft (shaft). To be realized.
  • the duct is routed at a location sufficiently distant from the fan depending on the installation position of the intake / exhaust device, it is possible that the duct extends in any direction.
  • the shape in the vicinity of the connection between the duct and the bottom can be uniquely specified regardless of how the duct is arranged.
  • FIG. 1 is a diagram schematically showing an example of a projection view in which a duct 20, a bottom portion 21, and a first opening 22 (a ventilation port or an intake port) of an intake and exhaust device are projected on a plane perpendicular to a rotation axis. ..
  • the intake / exhaust device will be described with reference to FIG. Consider a projection shape in which the inner wall surface of the duct 20 and the inner wall surface of the bottom portion 21 are projected on a plane perpendicular to the rotation axis.
  • the contour lines of the inner wall surfaces of the duct 20 and the bottom portion 21 are an arc-shaped curve R corresponding to the contour of the first opening 22, and a first contour line C 1 and a second contour line C 2 extending from both ends of the curve R, respectively. And have.
  • the vicinity of the connecting portion between the duct and the bottom usually refers to a region in which the distance from the center position X 0 in the projection view of the first opening is not more than twice the diameter of the first opening, and within this region.
  • the first contour line and the second contour line respectively have a first straight line portion L 1 and a second straight line portion L 2 that are parallel and straight.
  • the one located on the bottom side is the first straight portion L 1 and the second straight portion L 2.
  • the contour of the first opening 22 is equal to a circle (or an ellipse) obtained by projecting the opening end of the blower port or the intake port onto a plane perpendicular to the rotation axis (also referred to as a shaft).
  • the rotation axis is oriented in the direction perpendicular to the paper surface and rotates in the direction indicated by G in the figure.
  • X 0 corresponds to the position of the rotation axis.
  • a center line between the first straight line portion L 1 and the second straight line portion L 2 is an extension line E 0 extending to the bottom side.
  • E 1 be a first stretched line obtained by extending the first straight line portion L 1 to the bottom side
  • E 2 be a second stretched line obtained by extending the second straight line portion L 2 to the bottom side.
  • the distance between the first straight line portion L 1 and the second straight line portion L 2 is W
  • the diameter of the first opening is D
  • the distance from the center X 0 of the first opening to the stretch line E 0 is ⁇ w.
  • the separation distance W means the width of the duct in the plane perpendicular to the rotation axis.
  • a line tangent to and the first opening is perpendicular to the first straight line portion L 1 is a first cross-sectional lines S 1, the second section line a line parallel to the first section lines S 1 through X 0 S Set to 2 .
  • the intersection of the first cross-section line S 1 and the first straight line portion L 1 or the first stretched line E 1 is U 1
  • the first cross-section line S 1 and the second straight line portion L 2 or the second stretched line E 2 the intersection between the U 2
  • the second section line S 2 the intersection of the first linear portion L 1 or the first stretch lines E 1 and U 3.
  • the direction from the intersection U 1 to the intersection U 3 (direction toward the fan) is the first direction
  • the direction opposite to the first direction is the second direction.
  • the duct and the inner wall surface of the bottom portion satisfy the following conditions (1) and (2) in the projected view.
  • the condition (1) simply means that the connection between the duct and the bottom is located at a position biased to the side wall of the fan case.
  • Requirement (2) also means that the separation distance, that is, the width W of the duct, is smaller than the diameter of the first opening. This facilitates downsizing of the intake / exhaust device.
  • the extension line of the duct is represented by the center line between the first straight line portion L 1 and the second straight line portion L 2.
  • the condition (1) means that the center position X 0 of the first opening is out of the stretching line E 0 .
  • the airflow (see FIGS. 2A to 2C, 3A to 3B, and 4) from the space between the side wall of the fan case and the outer periphery of the impeller toward the blower duct through the bottom is at the center of the first opening. Flow from the position X 0 toward the stretch line E 0 .
  • the airflow (see FIGS. 2A to C, FIGS. 3A to B, and FIG. 4) from the intake duct toward the space between the side wall of the fan case and the outer periphery of the impeller flows along the extension line E 0 , It flows toward the center position X 0 of the first opening.
  • the duct and the bottom portion form a curved or bent flow path (a ventilation path or an intake path).
  • a high-output intake / exhaust device is realized.
  • the flow supplied from the ventilation port contains a strong swirling component.
  • a fast air flow with a large swirling component is generated in the downstream of the region where the direction of the swirling component is the same as the air blowing direction of the air blowing duct.
  • a turbulent flow is generated and fluid loss may increase.
  • the flow of the swirling component is small, or a stagnation flow of air flowing in the direction opposite to the air blowing direction occurs. Vortices can be excited by the large difference in velocity between the fast flow of air and the stagnation flow. Fluid loss such as air collision loss and eddy loss is one of the factors that reduce the efficiency of the intake and exhaust devices.
  • the flow from the intake port to the turbo fan also contains swirling components, so fluid loss can occur in the intake duct as well as in the blower duct.
  • the shape of the intake duct and the bottom portion connected to the intake duct as described above, it is possible to prevent the rapid flow of air from colliding with the wall surface of the intake duct. Further, the stagnation flow of air can be reduced. As a result, the fluid loss of the intake / exhaust device is reduced, and a high-output intake / exhaust device can be obtained.
  • At least one of the shape of the intake duct and the bottom portion connected to the intake duct, and the shape of the blower duct and the bottom portion connected to the blower duct may satisfy the above conditions. It is preferable that at least the shape of the air duct and the bottom portion connected to the air duct satisfy the above conditions. It is more preferable that both the shape of the intake duct and the bottom portion connected to the intake duct and the shape of the blower duct and the bottom portion connected to the blower duct satisfy the above conditions.
  • a vector v represents the direction of the airflow flowing in the region between the first straight line portion L 1 and the second straight line portion L 2 of the duct.
  • the rotation direction of the impeller is represented by an angular velocity vector ⁇ .
  • ⁇ is assumed to face the direction in which the right-hand screw advances when the right-hand screw is rotated in the direction of rotation of the impeller, and in the example of FIG. 1, faces ⁇ upward.
  • the duct may be arranged away from the center X 0 in the direction of v ⁇ ⁇ .
  • the first straight line portion L 1 is on the v ⁇ ⁇ direction side. It should be noted that, in FIG. 1, the direction of v is opposite when the duct is the blower duct and when it is the intake duct.
  • the inner wall surface of the duct and the bottom portion satisfy the following condition (3) in addition to the conditions (1) and (2) in the projection view.
  • the condition (3) is that both the first straight line portion L 1 (or the extension line E 1 ) and the second straight line portion L 2 (or the extension line E 2 ) intersect with the contour of the first opening in the projection view. It means to do.
  • the separation distance between the first straight line portion L 1 and the second straight line portion L 2 is defined as the width W of the duct.
  • the center X 0 of the first opening is located at a position displaced by ⁇ w from the duct extension line E 0 .
  • D 1 W / 2 + ⁇ w
  • a D 2 W / 2- ⁇ w
  • condition (3) the distance D 1 of the from X 0 to the first straight line portion L 1 or the first stretch lines E 1
  • the distance D 2 from X 0 to the second straight line portion L 2 or the second stretched line E 2 is shorter than the radius D / 2 of the first opening.
  • both the first and second contour lines can be connected to the curve R at a position closer to the second direction side than the second cross section line S 2 .
  • connection position between the first straight line portion L 1 and the curved line R (when the first straight line portion L 1 is not directly connected to the curved line R, the crossing position between the first stretched line E 1 and the curved line R) is as against 2 section line S 2 away in the second direction from the connection position, while the fast flow occurs in the direction facing obliquely with respect to the first straight line portion L 1, along a first straight line portion L 1
  • a region where the flow velocity is slow is likely to occur, and a stagnation flow is likely to occur.
  • connection position of the first straight line portion L 1 and the curved line R (or the crossing position of the first stretched line E 1 and the curved line R) is arranged so as to be close to the second sectional line S 2. By doing so, the stagnation flow is reduced.
  • the direction of the swirling component is likely to be opposite to the air blowing direction of the duct.
  • the connection position between the second straight line portion L 2 and the curved line R (when the second straight line portion L 2 is not directly connected to the curved line R, the crossing position between the second stretched line E 2 and the curved line R) is the second.
  • the stagnation flow can be reduced because the direction of the swirling component is oriented in the direction perpendicular to the air blowing direction of the duct and the component in the direction opposite to the air blowing direction is reduced as the distance to the second direction side with respect to the cross section line S 2 increases. ..
  • the first straight line portion L 1 and the curved line R are directly connected, and the second straight line portion L 2 and the curved line R are directly connected.
  • the first contour line may have a first connecting portion whose one end is connected to the first straight line portion L 1 and whose other end is connected to the curved line R.
  • the first connecting portion is formed of a curved line, and it is more preferable that the first connecting portion is a curved line that is in contact with the first straight line portion L 1 at one end and is in contact with the curved line R at the other end.
  • the second contour line may have a second connecting portion whose one end is connected to the second straight line portion L 2 and whose other end is connected to the curved line R.
  • the second connecting portion be formed of a curved line, and it is more preferable that the second connecting portion be a curve that is in contact with the second straight line portion L 2 at one end and is in contact with the curve R at the other end.
  • the output W out of the intake and exhaust device can be expressed by the product of the static pressure P and the air volume Q.
  • static pressure can be increased and high output can be achieved.
  • n S r ⁇ ⁇ Q / (H / ⁇ ) 3/4 (In the formula, r is the rotation speed (/ min), Q is the flow rate (m 3 / min), H is the pressure (mmH 2 O), and ⁇ is the density (kg / m 3 ).) Required by.
  • the intake / exhaust device of the present disclosure can be suitably realized by using a fan having a specific speed n S represented by the above formula 1 in the range of 200 to 300, and a turbofan can be preferably used.
  • FIG. 2A is a perspective view showing the appearance of the intake / exhaust device 10 according to the present embodiment.
  • FIG. 2B is a side view of the intake / exhaust device 10.
  • FIG. 2C is a view of the intake and exhaust device 10 as viewed from above.
  • the intake / exhaust device 10 includes a turbo fan 100, a blower duct 200, an intake duct 210, and bottom portions 220 and 230.
  • the bottom portion 220 is connected to the fan case 120 so as to close the blower outlet 123 of the turbo fan, and is also connected to the blower duct 200.
  • the bottom portion 230 is connected to the fan case 120 so as to close the intake port 122 of the turbo fan, and is also connected to the intake duct 210.
  • FIG. 3A is a perspective view showing an external appearance of the turbo fan 100 (also referred to as a rearward facing fan).
  • FIG. 3B is a vertical cross-sectional view showing the inside of the turbofan 100.
  • the turbo fan 100 includes an impeller 110, a fan case 120, and a rotary drive device 130.
  • the impeller 110 includes an impeller disk 111 and a plurality of rearward facing blades (hereinafter referred to as moving blades 112).
  • the fan case 120 includes a side wall 121, an intake port 122, and a blower port 123.
  • the rotary drive device 130 includes a rotary shaft (shaft) 131 and a rotary drive source 132 that rotates the shaft 131.
  • the specific configuration of the turbofan including the impeller 110 will be described later.
  • FIG. 4 is a projection view in which the blower duct 200 and the bottom 220 of the intake and exhaust device 10 are projected on a plane perpendicular to the rotation axis 131.
  • FIG. 4 also shows the position when the impeller of the turbofan is projected on a plane perpendicular to the rotation axis 131. The impeller rotates counterclockwise in the figure.
  • the air duct 200 extending in a substantially straight line is connected to the fan case 120 at the bottom 220.
  • the extension line E 0 of the blower duct 200 is arranged so as to be offset from the center X 0 of the contour of the blower opening by ⁇ w.
  • W be the inner diameter of the blower duct 200 in the projection view (the inner diameter of the duct in the plane perpendicular to the rotation axis 131).
  • W is a separation distance between the first straight line portion L 1 and the second straight line portion L 2 .
  • the distance from X 0 to the first straight line portion L 1 (or its extension line E 1 ) is W / 2 + ⁇ w.
  • the distance from X 0 to the extension line E 2 of the second straight line portion L 2 is W / 2 ⁇ w.
  • the inner diameter W of the blower duct 200 is smaller than the inner diameter (diameter) D of the blower opening.
  • the contour lines of the inner wall surfaces of the blower duct 200 and the bottom portion 220 include a first straight line portion L 1 , a curve R corresponding to the blower opening 123, and a second straight line portion L 2 .
  • the first straight line portion L 1 and the second straight line portion L 2 are perpendicular to the extension line E 0 of the blower duct 200, are closer to the blower duct 200 than the straight line passing through X 0 (the second cross section line S 2 ), and are curved lines R. Connect with.
  • the extension line E 0 of the intake duct 210 is also displaced from the center of the contour of the intake port.
  • the inner diameter of the intake duct 210 (the inner diameter of the duct in the plane perpendicular to the rotating shaft 131) is smaller than the inner diameter of the intake port.
  • the impeller 110 includes an impeller disk 111 and a plurality of moving blades 112.
  • the impeller 110 may further include a shroud 113.
  • FIG. 5A is a perspective view showing the impeller 110 of the turbofan 100.
  • FIG. 5B is a top view of the moving blade 112 provided on the impeller 110.
  • the impeller disk 111 has a surface extending in a direction intersecting with the rotation axis 131 (preferably, a direction perpendicular to the rotation axis 131) and is substantially circular.
  • a plurality of moving blades 112 are erected from one main surface of the impeller disk 111.
  • a part of the central portion 111C of the impeller disk 111 is open.
  • a part of the outer peripheral portion 111P of the impeller disk 111 may be bent toward the air outlet 123.
  • the impeller is set such that the outer peripheral side is closer to the blower opening than the inner peripheral side.
  • the disc tilts in the axial direction of the rotating shaft 131. As a result, the gas taken into the intake / exhaust device 10 smoothly flows to the blower port 123.
  • the shroud 113 is a ring-shaped plate material and is arranged so as to face the impeller disk 111 via the moving blade 112.
  • the outer peripheral edge of the impeller disk 111 and the outer peripheral edge of the shroud 113 are substantially coincident with each other, and a part of the outer peripheral portion 111P of the impeller disk 111 is covered by the shroud 113.
  • the inner peripheral edge of the shroud 113 faces the intake port 122.
  • a part of the rotor blade 112 is joined to the shroud 113.
  • the gas taken into the impeller 110 flows along the moving blades 112, then flows out from the outer peripheral edge of the impeller disk 111, collides with the side wall 121, and is guided to the blower port 123.
  • the shroud 113 suppresses the gas flowing out from the outer peripheral edge of the impeller disk 111 from flowing out from the intake port 122.
  • the shroud 113 suppresses the gas flowing out from the inter-blade flow path formed by the two adjacent moving blades 112 from entering the inter-blade flow path adjacent to this.
  • the shroud 113 preferably has a funnel shape or a taper shape which is narrowed toward the intake port 122 and has a smooth curved surface in that turbulence of the air flow is suppressed.
  • the outer peripheral end of the shroud in the direction parallel to the rotating shaft 131 is located closer to the impeller disk than the inner peripheral end of the shroud (separated in the direction from the shroud toward the impeller disk) in the direction parallel to the rotating shaft 131.
  • the inner peripheral end of the shroud is located closer to the impeller disk than the inner peripheral end of the shroud (separated in the direction from the shroud toward the impeller disk) in the direction parallel to the rotating shaft 131.
  • the plurality of moving blades 112 are erected from the impeller disk 111. As shown in FIG. 5B, the moving blade 112 extends from the central portion 111C of the impeller disk 111 toward the outer peripheral portion 111P in an arc shape protruding in the rotation direction G of the shaft 131.
  • the number of blades 112 is not particularly limited, and may be appropriately set in consideration of the size of the impeller 110, the air volume and pressure of the intake and exhaust machines, and the like.
  • the number N of blades 112 is, for example, 5 to 30, and 8 to 15.
  • the moving blade 112 protrudes in the rotation direction G of the rotating shaft 131 from an arbitrary point of the central portion 111C as a starting point 112s toward an arbitrary point (end point 112e) of the outer peripheral portion 111P. It extends in an arc shape. Since the rotor blade 112 is provided with the convex portion projecting in the rotation direction G, the gas taken into the intake / exhaust device 10 moves from the central portion 111C to the outer peripheral portion 111P along the convex portion without significantly disturbing the air flow. Can flow out.
  • the central portion 111C of the impeller disk 111 is, for example, a circle having a radius of 1/2 ⁇ r concentric with the impeller disk 111, and the outer peripheral portion 112P of the impeller disk 111 is , A donut-shaped region surrounding the central portion 111C.
  • the moving blade 112 can be elongated in the radial direction of the impeller disk 111.
  • the end point 112e is preferably located in the vicinity of the outer peripheral edge of the impeller disk 111 in that the fluid energy is likely to become larger.
  • the starting point 112s is preferably located near the center C (for example, inside a circle having a radius of 1/3 ⁇ r concentric with the impeller disk 111).
  • the shape of the moving blade 112 is not particularly limited as long as it has the above-mentioned convex portion.
  • the straight line Ls connecting the starting point 112s of the moving blade 112 and the center C of the impeller disk 111 is equal to the end point 112e of the first moving blade 112 and the center of the impeller disk 111. It may be located at a position advanced in the rotation direction G with respect to the straight line Le connecting with C.
  • a stator When using an electric motor as the rotation drive device 130, a stator is arranged in the electric motor.
  • the number of poles of the stator is usually an even number. Therefore, when the number N of moving blades is an even number, the vibrations of the rotary drive device 130 and each of the intake and exhaust devices are excited together to excite each other, and noise may increase. Therefore, in this case, the number N of moving blades is preferably an odd number.
  • the number of poles is the number of magnetic poles generated in the rotary drive device 130.
  • the number of slots of the stator and the number N of moving blades are the same or have an integral multiple relationship, noise may increase. Therefore, the number N of the blades 112 does not match the number of slots, and does not satisfy an integer multiple relationship (in other words, the number N of blades and the number of slots are relatively prime). It is preferable to set.
  • the intake / exhaust units installed in the temperature conditioning unit are It is preferable that the number of blades 112 be different so that the number of blades 112 is relatively prime.
  • the difference in the number of moving blades in the plurality of intake / exhaust devices is not particularly limited and may be 1 or more.
  • the difference in the number of moving blades is preferably 1 or more and 5 or less in consideration of the air volume and pressure of each intake and exhaust unit.
  • BPF noise is aerodynamic noise due to a moving blade, which is also referred to as discrete frequency noise.
  • the frequency Fb (Hz) when the energy of the BPF noise reaches a peak is calculated by the following Expression 3.
  • Fb m ⁇ r / 60 ⁇ N
  • m is an integer of 1 or more
  • r is the number of revolutions (rpm) of the impeller
  • N is the number of moving blades.
  • the peak frequency Fb of the sound (BPF noise) generated by at least one of the intake and exhaust devices is the same as the BPF noise generated by the other intake and exhaust devices.
  • the peak frequency Fb changes depending on the number N of the blades 112 and the rotation speed r of the impeller 110.
  • the number N of the moving blades may be changed and the rotational speed r of the impeller may be changed.
  • the obtained air volume also changes.
  • the air volumes of the plurality of intake and exhaust devices arranged in one temperature conditioning unit are approximately the same.
  • the maximum diameter of the plurality of intake / exhaust machines when viewed from the axial direction of the shaft may be different. The air volume can be adjusted to the same degree by increasing the number of rotations of the impeller including the impeller disk having the smaller maximum diameter than the other.
  • the fan case 120 includes a side wall 121 that surrounds the impeller 110.
  • the fan case 120 has an intake port 122 at the intake side end of the side wall 121, and has a blower port 123 at the exhaust side end of the side wall 121.
  • the intake port 122 and the blower port 123 are arranged so as to face each other in the axial direction of the shaft 131.
  • the side wall 121 has, for example, a substantially cylindrical shape with the rotating shaft 131 as the center, and the distance from the rotating shaft 131 to the side wall 121 is substantially constant.
  • the side wall 121 has a step 121S near the opening end portion on the intake port 122 side. Due to the step 121S, the diameter on the intake port 122 side is smaller than the diameter on the opening end on the blower port 123 side.
  • the intake port 122 has, for example, a substantially circular shape centered on the rotation shaft 131.
  • the blower port 123 has, for example, a donut shape centering on the rotation shaft 131 and surrounding the impeller disk 111. In the illustrated example, the intake port 122 is closed by the bottom portion 230 and communicates with the intake duct 210. The blower port 123 is closed by the bottom portion 220 and communicates with the blower duct 200.
  • the side wall 121 and the bottom portion 230 of the fan case 120, and / or the intake duct 210 may be integrally formed. In that case, it may be considered that the size and shape of the intake port 122 cannot be specified. In that case, the size and shape of the intake port 122 can be evaluated by the position of the end portion of the impeller 110 that is closest to the bottom portion 230 side in the direction along the rotation axis 131. The size and shape of the intake port 122 are evaluated by the inner peripheral shapes of the side wall 121 and the bottom portion 230 in a cross section that passes through the end position of the impeller 110 and is perpendicular to the rotation axis 131.
  • the inner peripheral edge of the shroud 113 may be regarded as the peripheral edge of the intake port 122.
  • the side wall 121 and the bottom portion 220 of the fan case 120 and / or the blower duct 200 are integrally formed, it is possible that the size and shape of the blower outlet 123 cannot be specified. In that case, the size and shape of the blower port 123 are evaluated by the inner peripheral shapes of the side wall 121 and the bottom portion 220 that have the largest cross-sectional areas in the cross section perpendicular to the rotation axis 131.
  • the air inlet 122 and the air outlet 123 are arranged so as to face each other in the axial direction of the rotary shaft 131.
  • the gas (usually air) around the intake port 122 is taken in from the intake port 122 by the rotation of the moving blade 112, and is given energy to accelerate the speed and along the moving blade 112, the outer peripheral edge of the impeller disk 111. Drained from. Subsequently, the gas collides with the side wall 121 of the fan case 120 to change its direction, and then further collides with the bottom part 220 to change its direction, and flows into the blower duct.
  • the step 121S is preferably formed by a gentle curved surface in that turbulence of the air flow is suppressed.
  • the distance from the rotating shaft 131 is shorter on the upstream side (intake port side) of the gas flow path than on the downstream side (blower port side).
  • the inner wall surface may be curved.
  • the turbo fan 100 may include a guide section 140 between the blower port 123 and the impeller 110.
  • the guiding part 140 faces the inner wall surface of the side wall 121 in a partial region.
  • the surface of the guide portion 140 facing the inner wall surface is such that the blower port side is longer from the rotary shaft 131 than the intake port side (the distance from the inner wall surface is shorter) in the surface including the axis of the rotary shaft 131. It is inclined.
  • the airflow flowing out of the impeller 110 is smoothly guided to the blower port 123 via the inclined surface 140a of the guiding portion 140.
  • the turbulence of the air flow is further suppressed, and the fan efficiency can be further improved.
  • the turbofan may further include a plurality of vanes arranged between the side wall 121 and the moving blade 112.
  • FIG. 6 shows, as an example, a cross-sectional perspective view of the turbofan 101 including the vanes 141.
  • FIG. 7 is a perspective view showing the impeller 110 and the vanes 141 of the turbofan 101.
  • the number of the vanes 141 is not particularly limited, and may be appropriately set in consideration of the size of the intake / exhaust machine, the desired air volume, and the like.
  • the number of the vanes 141 is, for example, 5 to 30, and 8 to 15.
  • the number of the stationary blades 141 is larger than the number of the moving blades 112.
  • the difference between the number of stationary blades and the number of moving blades is not particularly limited, and may be 1 or more.
  • the difference between the number of stationary blades and the number of moving blades is, for example, 1 or more and 5 or less.
  • the arrangement of the stationary vanes 141 is not particularly limited, and may be set appropriately according to the maximum diameter of the impeller disk 111, the arrangement of the moving blades 112, and the like. Above all, the vanes 141 may be arranged such that the main surface thereof is along the air flow C (see FIG. 5) generated by the moving blades 112 in that the wind flowing out from the impeller 110 is efficiently decelerated. preferable. In other words, the vanes 141 are preferably arranged so as to advance in the rotation direction of the rotation shaft 131 toward the outer circumference. In this case, the size of the vanes 141 is not particularly limited, and may be appropriately set so that the air is blown between the vanes 141 at a desired air volume and pressure.
  • the vane 141 may be attached to the diffuser plate.
  • the plurality of stationary blades 141 are arranged between the side wall 121 and the moving blade 112 in a state of being erected at equal intervals from the main surface of the diffuser plate on the intake port 122 side.
  • the diffuser plate 142 is attached to the inclined surface 140 a of the guiding section 140.
  • the vane 141 may be further joined to the inside of the side wall 121.
  • the diffuser plate 142 is a ring-shaped plate material and has an inner diameter larger than the maximum diameter of the impeller disk 111.
  • the materials for the impeller disk, the moving blade, the shroud, the side wall, and the stationary blade are not particularly limited, and may be appropriately selected according to the application.
  • Examples of the material include various metal materials, resin materials, and combinations thereof.
  • the rotary drive device 130 includes a rotary shaft 131 and a rotary drive source 132 that rotates the rotary shaft 131.
  • the impeller 110 rotates and gas is taken into the fan case 120 from the intake port 122.
  • the rotary drive device 130 is, for example, an electric motor.
  • An electric motor is a power device that outputs a rotational motion by utilizing a force due to an interaction (Lorentz force) between a magnetic field and an electric current.
  • the rotary drive source 132 includes a rotor and a stator (not shown) that generates a force for rotating the rotor.
  • the shape and material of the rotor and the stator are not particularly limited, and any known motor may be used.
  • the output of the electric motor is not particularly limited and may be appropriately set according to a desired air flow rate, pressure, and the like. For example, when the temperature conditioning unit is mounted on a hybrid vehicle, the output of the electric motor is about several tens of watts.
  • Stator winding (not shown) is wound around the stator. When a current flows through this stator winding, a magnetic field is formed around the stator winding. As a result, the magnetic field generated by the stator causes the rotor to rotate.
  • the material of the stator winding is not particularly limited as long as it has conductivity. Among them, the stator winding preferably contains at least one selected from the group consisting of copper, copper alloys, aluminum and aluminum alloys from the viewpoint of low resistance.
  • a temperature conditioning unit includes the intake / exhaust device of the present embodiment described above and a housing that houses the temperature-conditioned body.
  • the temperature-conditioning unit cools or heats the temperature-controlled body by blowing air or sucking air from an intake / exhaust device. Only one intake or exhaust device may be provided in the temperature conditioning unit, or a plurality of intake and exhaust devices may be provided.
  • FIG. 8A is a perspective view showing the appearance of the temperature conditioning unit 300 according to the present embodiment.
  • FIG. 8B is a view of the temperature conditioning unit 300 as viewed from above.
  • the temperature conditioning unit 300 includes a first intake / exhaust device 10A, a second intake / exhaust device 10B, and a housing 310.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B correspond to the intake / exhaust device 10 described above, and are arranged such that the extending line of the air duct is displaced from the center of the contour of the air outlet, and The extension line of is shifted from the center of the contour of the intake port.
  • the configuration of the turbofan such as the number of moving blades 112 and the number of rotations of the moving blades, may be the same between the first intake / exhaust device 10A and the second intake / exhaust device 10B, or may be multiple.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B may be different from each other so that a desired air flow and pressure can be obtained in the entire intake / exhaust device.
  • the housing 310 accommodates a temperature-controlled body (not shown).
  • the housing 310 is provided with at least one inlet 310a for taking in external gas and at least one outlet 310b for discharging the gas in the housing 310.
  • each of the exhaust ports 310b communicates with the intake duct 210 of the first intake / exhaust device 10A or the second intake / exhaust device 10B.
  • the inside of the housing 310 provided with the temperature-conditioned body is provided with, for example, an intake side chamber having an intake port 310a and an exhaust side chamber having an exhaust port 310b, and the intake side chamber and the exhaust side chamber are temperature-controlled. It is divided by the body.
  • the intake chamber 310, the temperature-controlled body, and the exhaust chamber are sequentially passed from the intake port 310a.
  • a gas flow reaching the discharge port 310b is formed.
  • the temperature-controlled body is cooled or heated.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B are arranged close to each other, and the first intake / exhaust device 10A and the second intake / exhaust device 10B are
  • the rotating shafts 131 of the fan are parallel to each other, the rotating directions of the impeller 110 are opposite, and when one rotates clockwise, the other rotates counterclockwise.
  • the separation distance between the blower ducts 200 can be shortened as compared with the case where the rotation directions of the impellers 110 are the same. Therefore, the area occupied by the two air ducts 200 can be reduced.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B may be arranged so that their impellers 110 rotate in the same direction.
  • the temperature conditioning unit 301 shown in FIG. 10 is the temperature conditioning unit 300 in which the air ducts 200 of the first intake / exhaust device 10A and the second intake / exhaust device 10B are connected to the intake port 310a of the housing 310. ..
  • the gas supplied by the intake / exhaust devices 10A and 10B flows into the intake chamber via the blower duct and the intake port 310a, passes through the temperature-controlled body and the exhaust chamber in order, and then reaches the exhaust port 310b. A flow of gas through is formed. At that time, the temperature-controlled body is cooled or heated.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B are arranged close to each other, and the first intake / exhaust device 10A and the second intake / exhaust device 10B are connected.
  • the rotation axes 131 of the fans are parallel to each other, but the rotation directions of the impellers 110 are opposite.
  • the separation distance between the intake ducts 210 can be shortened as compared with the case where the rotation direction of the impeller 110 is the same. Therefore, the area occupied by the two intake ducts 210 can be reduced.
  • the first intake / exhaust device 10A and the second intake / exhaust device 10B may be arranged such that the impellers 110 rotate in the same direction.
  • the discharge port 310b of the housing 310 communicates with the intake duct 210.
  • the intake port 122 of the fan case to the exhaust port 310b without providing an intake duct in the first intake / exhaust device 10A and the second intake / exhaust device 10B.
  • the intake port 310a of the housing 310 communicates with the blower duct 200, but the first intake / exhaust device 10A and the second intake / exhaust device 10B are not provided with the ventilation duct, and the fan is not provided. It is also possible to directly connect the air blow port 123 of the case to the intake port 310a.
  • the configuration of the temperature conditioning unit 300 is not limited to this.
  • the number of the intake ports 310a may be one, or may be two or more.
  • the arrangement of the temperature-controlled body is not particularly limited, and may be appropriately set depending on the application, the type of the temperature-controlled body, and the like.
  • the temperature-controlled object can be cooled by, for example, an intake / exhaust device using a turbo fan (backward fan) 100 or 101, or a frontward fan. Therefore, the turbo fan 100 and the forward fan are compared.
  • the forward fan has forward blades protruding in the opposite direction to the rotation direction. That is, the forward blades protrude in a direction opposite to the moving blades (rearward blades) 112 of the turbofan 100.
  • the major difference between the turbofan 100 and the forward-facing fan is the configuration of its blades.
  • FIG. 11 is an explanatory diagram showing the air flow C generated by the moving blade 112.
  • FIG. 12 is an explanatory diagram showing an airflow C 912 generated by the forward facing blade 912.
  • the end point 112e of the moving blade 112 is located near the outer peripheral edge of the impeller disk 111, and in FIG. It is located near the outer edge.
  • the airflow C generated by the rotor blade 112 flows at an angle ⁇ 1 with respect to the tangent line Li at the end point 112e of the impeller disk 111.
  • the forward blade 912 is rotated, as shown in FIG. 12, the airflow C 912 generated by the forward blade 912 flows at an angle ⁇ 2 with respect to the tangent line Lif at the end point 912e of the impeller disk 911.
  • the angle ⁇ 1 is larger than the angle ⁇ 2.
  • the component Cb flowing in the direction of the tangent line Lb at the end point 112e of the moving blade 112 is larger than the component Cf flowing in the direction of the tangent line Lf at the end point 912e of the forward blade 912. Therefore, when the moving blade 112 is used, the fluid energy generated from the impeller 110 is larger than that when the forward facing blade 912 is used.
  • FIG. 13 is a graph showing the relationship between the air volume Q and the air pressure P.
  • the moving blade (backward blade) 112 can be elongated in the radial direction of the impeller disk 111.
  • the rotor blades 112 are long in the radial direction of the impeller disk 111, when the impeller 110 rotates, the flow velocity difference between the start point 112s and the end point 112e becomes large. Therefore, as shown in FIG. 13, the intake / exhaust device 10 including the moving blades 112 can blow air at a high pressure regardless of the shape of the fan case.
  • an intake / exhaust machine provided with the forward blades 912 usually has a scroll-shaped fan case to increase the wind pressure. That is, the intake / exhaust device 10 including the moving blades 112 can be downsized. Further, since it has a high pressure, it is suitable for cooling or heating a temperature-controlled body having a high pressure resistance due to its small size.
  • FIG. 14 shows the relationship between the specific speed n S of the intake and exhaust device and the fan efficiency ⁇ (%) when the moving blade (rearward blade) 112 is used and when the forward blade 912 is used.
  • the energy loss increases as the specific speed n S increases, and the fan efficiency ⁇ decreases.
  • the moving blade 112 when the moving blade 112 is used, the energy loss increases as the specific speed n S increases, but the fan efficiency ⁇ is higher than that when the forward blade 912 is used.
  • FIG. 15 shows the relationship between the flow coefficient ⁇ and the pressure coefficient ⁇ when the moving blade (backward blade) 112 is used and when the forward blade 912 is used.
  • the pressure coefficient ⁇ of the intake / exhaust device is higher than when the moving blade 112 is used, regardless of the flow coefficient ⁇ .
  • the pressure coefficient ⁇ greatly fluctuates on the plus side and the minus side, and the tendency is not constant.
  • the pressure coefficient ⁇ only gradually decreases even if the flow coefficient ⁇ increases. That is, since the intake / exhaust device 10 including the moving blades 112 exhibits a stable pressure coefficient ⁇ without being greatly affected by the flow rate coefficient ⁇ , it is possible to rotate at high speed to increase the air volume.
  • the temperature conditioning unit 300 (301) may include a blower control unit that controls the first intake and exhaust device 10A and the second intake and exhaust device 10B.
  • the blower control unit controls, for example, the rotation speed of each impeller, the amount of gas supplied to each intake port, and the like.
  • the blower control unit may be, for example, provided in the housing 310, included in the temperature-conditioned body, and temperature-controlled by an intake / exhaust device.
  • the temperature-controlled object is not particularly limited.
  • Examples of the temperature-conditioned body include various devices mounted on vehicles such as electric vehicles and hybrid vehicles. Examples of such equipment include power storage devices such as secondary batteries, power conversion devices such as inverters and converters, engine control units, and electric motors.
  • a power storage device or a power conversion device usually includes a circuit board for controlling a secondary battery, an inverter, or the like.
  • the inverter and the circuit board may include semiconductor devices. Therefore, it is important to control the temperature of these secondary batteries, circuit boards, and / or semiconductor elements.
  • the temperature-conditioned body may include a radiator and / or a relay.
  • the power storage device is composed of, for example, a battery pack in which a plurality of secondary batteries are combined. At this time, a gap is formed between the adjacent secondary batteries, and gas passes through this gap. Similarly, in the case of the power conversion device, a gap is formed between the components of the power conversion device, and gas is allowed to pass through this gap.
  • the temperature-conditioning body accommodated in the housing 310 may be one or more, and may be two or more. When two or more temperature-controlled objects are accommodated in the housing 310, the inside of the housing 310 may be divided according to the number of temperature-controlled objects. Further, the air passage for the gas blown from the first intake / exhaust device 10A and the air passage for the gas blown from the second intake / exhaust device 10B may be independent or may be connected. Good. The air passages of the first intake / exhaust device 10A and / or the second intake / exhaust device 10B may be branched depending on the number of temperature-controlled objects.
  • FIGS. 16A to 19B show the results of simulating the air flow flowing inside the air duct 200 and around the bottom 220 in the intake and exhaust device 10.
  • the blower duct and the bottom part are designed so that the contour line of the inner wall surface satisfies the following conditions in a projection view projected on a plane perpendicular to the rotation axis. That is, when W / 2 + ⁇ w ⁇ D / 2, the first straight line portion L 1 is directly connected to the curved line R corresponding to the blower opening, and when W / 2 + ⁇ w> D / 2, the straight connecting portion (inclination) It is connected to the curve R via the part L 3 ).
  • the inclined portion is connected to the first straight line portion L 1 at an intersection of the first straight line portion L 1 (extended line E 1 ) and the second cross section line S 2, and is in contact with the curve R at a connection end with the curved line R. I did it.
  • the second straight line portion L 2 was directly connected to the curve R.
  • the deviation amount ⁇ w of the extension line E 0 of the blower duct 200 from the inner diameter W of the blower duct 200 in a plane perpendicular to the rotation axis 131 and the center X 0 of the contour of the blower outlet with respect to the inner diameter D of the blower outlet is calculated. While changing the flow velocity distribution, the flow velocity distribution at a height of 1/2 of the total height of the blower duct 200 was obtained.
  • 16A, FIG. 17A, FIG. 18A, and FIG. 19A are contour line plots of the absolute value of the flow velocity, and the higher the flow velocity, the darker the gray.
  • the numerical values in the figure represent the relative magnitude of the flow velocity at each position. 16B, 17B, 18B, and 19B show the direction of the flow velocity vector at each position, and the magnitude of the vector is constant regardless of the flow velocity.
  • the connection position between the first straight line portion L 1 and the curved line R is on the duct side with respect to the center X 0 of the blower opening, the connection position is in a direction oblique to the first straight line portion L 1 . , A fast flow is occurring.
  • the air duct 200 of the blower duct 200 is arranged so that the second straight line portion L 2 approaches the center X 0 of the contour of the blower opening (the first straight line portion L 1 moves away from X 0 ).
  • the stretched line E 0 so as to deviate from the center X 0 of the blower port, generation of a region having a slow flow velocity is suppressed.
  • the temperature control unit of the present invention is particularly useful as a vehicle-mounted device because it is equipped with a plurality of intake and exhaust devices and has low noise. While the present invention has been described in terms of its presently preferred embodiments, such disclosure should not be construed as limiting. Various variations and modifications will no doubt become apparent to those skilled in the art to which the present invention pertains upon reading the above disclosure. Therefore, the appended claims should be construed to cover all variations and modifications without departing from the true spirit and scope of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • General Engineering & Computer Science (AREA)
  • Condensed Matter Physics & Semiconductors (AREA)
  • General Physics & Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Power Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Abstract

La présente invention concerne un mécanisme d'admission/échappement (10) qui est doté d'un turbo-ventilateur présentant un carter de ventilateur tubulaire (120), des conduits (200, 210) raccordés à un côté d'admission ou à un côté d'échappement du turbo-ventilateur et des parties inférieures (220, 230) raccordées au carter de ventilateur et aux conduits. Le carter de ventilateur présente une première ouverture dans une partie d'extrémité sur le côté d'échappement ou le côté d'admission, et les parties inférieures se raccordent au carter de ventilateur de manière à fermer la première ouverture. Dans une vue projetée dans laquelle les conduits, les parties inférieures et la première ouverture sont projetés sur une surface perpendiculaire à un axe de rotation d'une turbine, des lignes de contour des surfaces de paroi interne des conduits et des parties inférieures comprennent une courbe arquée (R) correspondant à la première ouverture, des première et seconde parties linéaires L1 et L2 qui sont parallèles l'une à l'autre et linéaires. La distance du centre de la première ouverture à la première partie linéaire L1 ou une ligne d'extension E1 sur un côté inférieur de celle-ci est supérieure à la distance du centre de l'ouverture à la seconde partie linéaire L2 ou une ligne d'extension E2 sur un côté inférieur de celle-ci.
PCT/JP2019/041204 2018-10-31 2019-10-18 Mécanisme d'admission/échappement et température WO2020090533A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2020553793A JPWO2020090533A1 (ja) 2018-10-31 2019-10-18 吸排気機および温度調和ユニット

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-206166 2018-10-31
JP2018206166 2018-10-31

Publications (1)

Publication Number Publication Date
WO2020090533A1 true WO2020090533A1 (fr) 2020-05-07

Family

ID=70463168

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2019/041204 WO2020090533A1 (fr) 2018-10-31 2019-10-18 Mécanisme d'admission/échappement et température

Country Status (2)

Country Link
JP (1) JPWO2020090533A1 (fr)
WO (1) WO2020090533A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4711804U (fr) * 1971-03-10 1972-10-12
JP2003510524A (ja) * 1999-09-28 2003-03-18 ロイヤル アプライアンス マニファクチャリング カンパニー 騒音を低減し空気流を改善した羽根車・筺体組立体
WO2018116942A1 (fr) * 2016-12-21 2018-06-28 パナソニックＩｐマネジメント株式会社 Unité de conditionnement de température, système de conditionnement de température, et véhicule

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4711804U (fr) * 1971-03-10 1972-10-12
JP2003510524A (ja) * 1999-09-28 2003-03-18 ロイヤル アプライアンス マニファクチャリング カンパニー 騒音を低減し空気流を改善した羽根車・筺体組立体
WO2018116942A1 (fr) * 2016-12-21 2018-06-28 パナソニックＩｐマネジメント株式会社 Unité de conditionnement de température, système de conditionnement de température, et véhicule

Also Published As

Publication number Publication date
JPWO2020090533A1 (ja) 2021-10-07

Similar Documents

Publication Publication Date Title
JP6064179B2 (ja) 温度調和ユニット、温度調和システムおよび温度調和ユニットを備えた車両
CN110073540B (zh) 温度调节单元、温度调节系统以及车辆
KR20170048308A (ko) 송풍장치 및 이를 포함하는 공기조화기의 실외기
JP6931774B2 (ja) 温度調和システム、車両
US10731881B2 (en) Fan coil unit with shrouded fan
JP6678302B2 (ja) 温度調和ユニット、温度調和システム、車両
US10644363B2 (en) Temperature conditioning unit, temperature conditioning system, and vehicle
JP6931778B2 (ja) 温度調和システムおよび車両
JP7029593B2 (ja) 温度調和ユニット
WO2020090533A1 (fr) Mécanisme d'admission/échappement et température
WO2020090532A1 (fr) Machine d'admission/d'échappement et unité de régulation de température
JP7153834B2 (ja) 温度調和ユニット
JP2006220021A (ja) 送風ファンおよび電子機器
JP6685433B2 (ja) 送風機及び空気調和装置
CN220673571U (zh) 一种电机外风扇结构及电机
JP2019090342A (ja) ブロワ装置
WO2022201218A1 (fr) Roue à aubes et soufflante à aubes multiples

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19879803

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020553793

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19879803

Country of ref document: EP

Kind code of ref document: A1