JP2016196208A - Indoor air conditioning unit and air blower - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase miscibility of two kinds of air differing in property by a method other than mixing of the two kinds of air differing in property on a suction side of an air blower.SOLUTION: A scroll casing allowing a plurality of kinds of air blown out from a centrifugal multiblade fan rotating on an axis S of rotation comprises: an upper bottom wall 211 having an opening 21a formed to introduce hot air and cold air that the centrifugal multiblade fan sucks in; a lower bottom wall 212 opposed to the upper bottom wall 211; and an outer peripheral wall 210 connecting the walls 211, 212, a part 213b of an inner surface 213, on the side of the scroll space V, of the lower bottom wall 212 being formed not in parallel with the axis S of rotation so that the plurality of kinds of air blown out from the centrifugal multiblade fan flows in the scroll space V surrounded with the walls 210, 211 and 212 and more distant from the axis S of rotation than from the centrifugal multiblade fan, and a length of the scroll space V in a direction parallel with the axis S of rotation is longer with the distance from the axis S of rotation in the scroll space V.SELECTED DRAWING: Figure 4

Description

  The present invention relates to an indoor air conditioning unit and a blower.

  Conventionally, a technique for mixing two airs having different properties is known. Specifically, Patent Document 1 discloses a technique for improving the mixing of cold air and hot air by causing cold air and hot air that have passed through a heat exchanger and rectified to collide on the suction side of the blower. Yes.

JP 2009-023590 A

  However, when two airs having different properties collide on the suction side of the blower as described above, there is a problem that pressure loss due to the collision occurs and the flow of air entering the blower becomes weak.

  In view of the above problems, an object of the present invention is to provide a technique for improving the mixing property of two airs having different properties by a method other than mixing two airs having different properties on the suction side of the blower.

  In order to achieve the above object, the invention according to claim 1 is characterized in that an air conditioning casing (2) forming a flow path of blown air to be sent into a vehicle interior of a vehicle, and the air conditioning casing are disposed in the air conditioning casing. A blower (20) that sucks and blows out a plurality of types of air (31, 32) having different properties from each other among the blown air, and the blower rotates around the rotation shaft (S), thereby the plurality of types. The centrifugal multiblade fan (23) that sucks in the air and blows out the plural types of air in a direction away from the rotating shaft, and the scroll casing (21) that distributes the plural types of air blown out from the centrifugal multiblade fan The scroll casing has a first bottom formed with an opening (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan. (211), a second bottom wall (212) facing the first bottom wall, and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall, The scroll space (V) surrounded by the bottom wall of the first wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan is blown out from the centrifugal multiblade fan. A plurality of types of air circulate, and the length of the scroll space in the direction parallel to the rotation axis is longer in at least a part of the scroll space as the distance from the rotation axis increases. One or both (213, 214) of the inner surface on the scroll space side and the inner surface on the scroll space side of the second bottom wall (213, 214) are formed non-parallel to the rotation axis. With air conditioning unit That.

  Thus, in the present invention, the length in the direction parallel to the rotation axis of the scroll space is on the scroll space side of the first bottom wall so that the length in at least a part of the scroll space increases with distance from the rotation axis. One or both of the inner surface and the inner surface on the scroll space side of the second bottom wall are formed non-parallel to the rotation axis. In this case, the plurality of types of air blown out from the centrifugal multiblade fan have a main flow along a direction in which the inner surface of the outer peripheral wall extends around the rotation shaft and extends in a spiral shape, and a swirl flow surrounding the main flow. Occur. This swirling flow promotes mixing of a plurality of types of air inside the scroll casing.

  Further, the invention according to claim 5 is an air conditioning casing (2) that forms a flow path of the blown air to be sent into the vehicle interior of the vehicle, and is arranged in the air conditioning casing, and among the blown air in the air conditioning casing, A blower (20) that sucks and blows out a plurality of types of air (31, 32) having different properties, and the blower sucks in the plurality of types of air by rotating around a rotation axis (S), A centrifugal multiblade fan (23) that blows out the plurality of types of air in a direction away from the rotating shaft; and a scroll casing (21) that circulates the plurality of types of air blown out of the centrifugal multiblade fan, The scroll casing includes a first bottom wall (211) formed with openings (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan, A second bottom wall (212) facing the first bottom wall; and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall, wherein the first bottom wall, A scroll space (V) surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan was blown out from the centrifugal multiblade fan. The plurality of types of air circulates, the inner surface of the outer peripheral wall on the scroll space side surrounds the rotating shaft and extends in a spiral shape, and the plurality of types of air blown out from the centrifugal multiblade fan is The scroll casing is formed so that the inner surface of the outer peripheral wall surrounds the rotation shaft and generates a main flow along a spiral extending direction and a swirl flow surrounding the main flow. Indoor air conditioning unit Tsu is a door.

  As described above, in the present invention, a plurality of types of air blown from the centrifugal multiblade fan generates a main flow along the direction in which the inner surface of the outer peripheral wall surrounds the rotation shaft and extends in a spiral shape, and a swirl flow surrounding the main flow. To do. This swirling flow promotes mixing of a plurality of types of air inside the scroll casing.

  The invention according to claim 8 is a centrifugal multiblade fan that sucks the plurality of types of air by rotating around the rotation shaft (S) and blows out the plurality of types of air in a direction away from the rotation shaft. 23) and a scroll casing (21) for circulating the plurality of types of air blown from the centrifugal multiblade fan, wherein the scroll casing introduces the plurality of types of air sucked by the centrifugal multiblade fan A first bottom wall (211) formed with an opening (21a), a second bottom wall (212) facing the first bottom wall, the first bottom wall, and the first An outer peripheral wall (210) that connects two bottom walls, and is surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall, and is further away from the rotating shaft than the centrifugal multiblade fan Scroll space (V The plurality of types of air blown from the centrifugal multiblade fan circulate, and the length of the scroll space in the direction parallel to the rotation axis is separated from the rotation axis in at least a part of the scroll space. One or both of the inner surface of the first bottom wall on the scroll space side and the inner surface of the second bottom wall on the scroll space side are formed non-parallel to the rotation axis so as to be longer. It is a fan characterized by having.

  The invention according to claim 9 is a centrifugal multiblade fan that sucks in the plurality of types of air by rotating around the rotating shaft (S) and blows out the plurality of types of air in a direction away from the rotating shaft. 23) and a scroll casing (21) for circulating the plurality of types of air blown from the centrifugal multiblade fan, wherein the scroll casing introduces the plurality of types of air sucked by the centrifugal multiblade fan A first bottom wall (211) formed with an opening (21a), a second bottom wall (212) facing the first bottom wall, the first bottom wall, and the first An outer peripheral wall (210) that connects two bottom walls, and is surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall, and is further away from the rotating shaft than the centrifugal multiblade fan Scroll space (V The plurality of types of air blown out from the centrifugal multiblade fan circulates, and the inner surface of the outer peripheral wall on the scroll space side surrounds the rotating shaft and extends in a spiral shape, and the centrifugal multiblade fan The scroll casing is formed such that the plurality of types of air blown from the main surface generate a main flow along a direction in which the inner surface of the outer peripheral wall extends around the rotation shaft and extends in a spiral shape and a swirl flow surrounding the main flow. It is the air blower characterized by being made.

  As described above, the features of the present invention can be understood as the features of the blower invention. In addition, the code | symbol in the bracket | parenthesis in the said and the claim shows the correspondence of the term described in the claim, and the concrete thing etc. which illustrate the said term described in embodiment mentioned later. .

It is a schematic block diagram of the indoor air-conditioning unit 1 in a vehicle air conditioner. It is a perspective view of the air blower 20. FIG. It is III-III sectional drawing of FIG. It is IV-IV sectional drawing of FIG. It is a figure which shows the temperature distribution of the air which flows in from the opening part 21a. FIG. 5 is a view of the same cross section as FIG. 4, and shows the flow of blown air 45 and 46 entering the scroll space V. It is a figure which shows the main flow 30 and the secondary flows 47 and 48 of the blowing air which flow in the scroll space V. FIG. It is a graph which shows the relationship with the temperature difference of the exit space of a scroll casing with respect to an expansion angle. It is a graph which shows the relationship with the temperature difference of the exit space of a scroll casing with respect to an expansion rate. It is a schematic block diagram of the indoor air-conditioning unit 1 of a comparative example. It is sectional drawing of a comparative example. It is a figure which shows the mainstream C30 of the ventilation air which flows in the scroll space CV in a comparative example. It is sectional drawing shown by the same model as FIG. 6 about 2nd Embodiment. It is a figure which shows the air flow in the scroll space of a comparative example. It is a figure which shows the air flow in scroll space in the case of (theta) = 30 degrees. It is a figure which shows the air flow in the scroll space in the case of (theta) = 60 degrees. It is a figure which shows the air flow in scroll space in the case of (theta) = 90 degrees. It is sectional drawing shown by the same model as FIG. 6 about 3rd Embodiment. It is sectional drawing shown by the same model as FIG. 6 about 4th Embodiment. It is sectional drawing shown by the same model as FIG. 6 about 5th Embodiment. It is sectional drawing shown by the same model as FIG. 1 about 6th Embodiment. It is sectional drawing shown by the same model as FIG. 5 about 6th Embodiment. It is III-III sectional drawing of FIG. 1 in 7th Embodiment.

(First embodiment)
The first embodiment will be described below. The vehicle air conditioner according to the present embodiment is mounted on a vehicle and includes an indoor air conditioning unit 1 shown in FIG. The indoor air-conditioning unit 1 includes an air-conditioning casing 2 that internally forms a flow path of blown air to be sent into the passenger compartment, and various members disposed in the air-conditioning casing 2.

  At the air flow upstream end of the air conditioning casing 2, an inside air introduction port 3 for introducing inside air that is air inside the vehicle interior, an outside air introduction port 4 for introducing outside air that is air outside the vehicle compartment, and these An inside / outside air switching door 5 for selectively opening and closing the introduction ports 3 and 4 is provided.

  The inside / outside air switching door 5 is opened and closed by an electric servo motor or the like, and switching between the inside air mode and the outside air mode is realized. The inside air mode is an inside air mode in which the inside air introduction port 3 is fully opened and the outside air introduction port 4 is fully closed to introduce the inside air into the air conditioning casing 2. The outside air mode is a mode in which outside air is introduced into the air conditioning casing 2 with the inside air introduction port 3 fully closed and the outside air introduction port 4 fully opened.

  An evaporator 9 serving as an air cooling means is disposed at the downstream side of the air flow of the inside / outside air switching door 5, and all the blown air introduced from the inside air introduction port 3 or the outside air introduction port 4 is the evaporator 9. Pass through. The evaporator 9 constitutes a well-known refrigeration cycle together with a compressor, a condenser, a gas-liquid separator, an expansion valve, and the like (not shown). And the evaporator 9 evaporates the refrigerant | coolant expanded by the expansion valve after compression with a compressor in a refrigerating cycle, and cools blowing air by heat-exchanging the refrigerant | coolant and blowing air.

  Further, on the downstream side of the air flow of the evaporator 9, the air conditioning casing 2 is arranged to be biased downward in the vertical direction in FIG. 1, and contacts the lower inner surface of the air conditioning casing 2 to contact the heater core 10 (air heating device). The heater core 10 heats the air using engine cooling water or the like that generates the traveling power of the vehicle as a heat source.

  The air conditioning casing 2 is provided with a bypass passage 12 that bypasses the heater core 10. An air mix door 13 is disposed on the upstream side of the air flow of the heater core 10 and the downstream side of the air flow of the evaporator 9. The air mix door 13 is driven by a servo motor or the like, and adjusts the air volume ratio between the air volume of the blown air (hot air 31) passing through the heater core 10 and the air volume of the blown air (cold air 32) passing through the bypass passage 12, Adjust the temperature of the air blown into the passenger compartment.

  Further, on the downstream side of the air flow of the heater core 10, there is disposed a centrifugal blower 20 that sucks the hot air 31 and the cold air 32 at the same time and then blows them out.

  A plurality of outlets 14, 15, and 17 through which the blown air blown out by the blower 20 flows into the passenger compartment are formed on the downstream side of the blower 20 and the most downstream portion of the air conditioning casing 2. Specifically, a face outlet 14 for blowing air-conditioned air to the upper body of a passenger in the vehicle interior, a foot outlet 15 for blowing air to the feet of the passenger in the passenger compartment, and the inner surface of the windshield 16 in the passenger compartment The defroster blower outlet 17 for blowing air toward is formed.

  And the blowing mode switching doors 18, 19, and 20 are disposed at the air upstream side portions of the respective outlets 14, 15, and 17, respectively. The blow mode switching doors 18, 19, and 20 are driven by an electric motor 63 that is a servo motor or by manual operation.

  Hereinafter, the blower 20 will be described with reference to FIGS. 2, 3, and 4. 3 and FIG. 4 represents the same direction of the indoor air-conditioning unit 1 and the left-right direction of FIG.

  The blower 20 is a device that draws in warm air 31 that has been warmed through the heater core 10 and cold air 32 that has passed through the bypass passage 12 and blows it out to an outlet described later. The scroll casing 21, the electric motor 22, and the centrifugal multiblade fan 23. have. The electric motor 22 is a device that rotates the centrifugal multiblade fan 23 around the rotation axis S by electric power.

  The centrifugal multiblade fan 23 is a sirocco fan having a boss portion 230, a large number of blades 231, and a ring portion 232. The boss 230 is a plate-shaped member that rotates around the rotation axis S, is connected to the output shaft of the electric motor 22, and protrudes upward with the rotation axis S as a vertex (opening along the rotation axis S). 21a is convex). A large number of blades 231 are arranged in the circumferential direction around the rotation axis S at the outer peripheral edge of the boss portion 230. The ring portion 232 connects the outer peripheral end portions of the upper ends of the multiple blades 231 in a circumferential shape.

  The boss portion 230, a large number of blades 231, and the ring portion 232 are driven by the electric motor 22 to rotate integrally around the rotation axis S. By this rotation, the centrifugal multiblade fan 23 sucks the warm air 31 and the cool air 32 in the direction substantially parallel to the rotation axis S in the vicinity of the rotation axis S, and air in a direction away from the rotation axis S (outside diameter direction). Blow out. The rotation axis S of the centrifugal multiblade fan 23 is inclined (more specifically, orthogonal) with respect to the longitudinal direction of the indoor air conditioning unit 1.

  The scroll casing 21 is a housing that houses a part of the electric motor 22 and the centrifugal multiblade fan 23, and constitutes a part of the air conditioning casing 2. The scroll casing 21 may be formed integrally with other portions of the air conditioning casing 2 or may be formed as a separate member.

  The scroll casing 21 has an inner peripheral wall 209, an outer peripheral wall 210, an upper bottom wall 211, and a lower bottom wall 212. The scroll casing 21 is surrounded by the outer peripheral wall 210, the upper bottom wall 211, and the lower bottom wall 212 and is a centrifugal multiblade fan. A scroll space V is formed at a position farther from the rotation axis S than 23.

  The upper bottom wall 211 (corresponding to an example of the first bottom wall) is a plate-like member corresponding to the upper lid of the scroll casing 21, and has an opening 21a at its inner peripheral end. The opening 21a is located at the innermost peripheral end of the bell mouth 211a formed as a part of the upper bottom wall 211 for noise reduction in the inner peripheral portion of the upper bottom wall 211, and the above-mentioned temperature that the centrifugal multiblade fan 23 sucks in. It is a member that forms a hole for introducing the wind 31 and the cold air 32. The lower bottom wall 212 (corresponding to an example of a second bottom wall) is a plate-shaped member that faces the upper bottom wall 211 in the direction of the rotation axis S.

The outer peripheral wall 210 is a plate-shaped member that forms the outer periphery of the scroll casing 21, and is connected to the outer peripheral end of the upper bottom wall 211 at the upper end and to the outer peripheral end of the lower bottom wall 212 at the lower end. Yes. Therefore, the outer peripheral wall 210 is a member that connects the upper bottom wall 211 and the lower bottom wall 212.
Further, the inner surface 210a of the outer peripheral wall 210 on the scroll space V side is from the nose portion N so that the distance from the rotation axis S increases according to a known logarithmic spiral function with respect to the winding angle around the rotation axis S. The outlet space W extends around the rotation axis S in a spiral shape. Accordingly, the nose portion N corresponds to the winding start portion of the outer peripheral wall 210.

  The outlet space W is a space surrounded by the inner peripheral wall 209, the outer peripheral wall 210, the upper bottom wall 211, and the lower bottom wall 212. The hot air 31 and the cold air 32 blown out from the centrifugal multiblade fan 23 circulate in the scroll space V in the direction surrounding the centrifugal multiblade fan 23 from the nose portion N to the outlet space W, and then enter the outlet space W. Thereafter, the air flows into the passenger compartment through an air outlet that is not closed among the air outlets 14, 15, and 17.

  Here, the length of the scroll space V in the direction parallel to the rotation axis S will be described. A direction (thickness direction) parallel to the rotation axis S is a vertical direction on the paper surface in FIG. As shown in FIGS. 2 and 4, the length of the scroll space V in the direction parallel to the rotation axis S is larger than the outer peripheral end of the blade 231 and the bell mouth 211 a on the upper bottom wall 211 when viewed from the rotation axis S. The fan outlet space V1 is h1, and the enlarged space V2 farther from the rotation axis S than the fan outlet space is larger than h1 and at most h2.

  That is, the length in the direction parallel to the rotation axis S in the scroll space V (the thickness direction of the scroll casing 21) is at least a part of the scroll space V (a space including the fan outlet space V1 and the expansion space V2). The distance from the rotation axis S increases. Such a feature is realized by the shapes of the upper inner surface 214 on the scroll space V side of the upper bottom wall 211 and the lower inner surface 213 on the scroll space V side of the lower bottom wall 212. The upper inner surface 214 does not include the surface of the bell mouth 211a on the centrifugal multiblade fan 23 side.

  Specifically, the position of the upper inner surface 214 in the direction parallel to the rotation axis S is the same regardless of the distance from the rotation axis S in the portion facing the fan outlet space V1 and the expansion space V2.

  On the other hand, the position of the lower inner surface 213 in the direction parallel to the rotation axis S is the same regardless of the distance from the rotation axis S in the portion 213a facing the fan outlet space V1.

  However, the position of the lower inner surface 213 in the direction parallel to the rotational axis S is such that the distance from the rotational axis S increases in the portion 213b facing the space V21 on the side connected to the fan outlet space in the enlarged space V2. It becomes low with. That is, the position of the lower inner surface 213 in the direction parallel to the rotation axis S is such that the distance from the rotation axis S increases in the portion 213b facing the space V21 on the side connected to the fan outlet space in the enlarged space V2. At the same time, it is displaced in a direction parallel to the rotation axis S and from the upper bottom wall 211 toward the lower bottom wall 212.

  Further, the position of the lower inner surface 213 in the direction parallel to the rotation axis S is the distance from the rotation axis S in the portion 213c facing the space V22 farther from the rotation axis S than the space V21 in the enlarged space V2. Regardless.

  That is, the portion 213a is a plane orthogonal to the rotation axis S, and the lower inner surface 213 is bent at the boundary between the portion 213a and the portion 213b. Further, the portion 213b is a surface that is inclined so as to escape from the upper inner surface 214 as it is away from the rotation axis S, the lower inner surface 213 is bent at the boundary between the portion 213b and the portion 213c, and the portion 213c is a plane orthogonal to the rotation axis S. .

  Here, the expansion angle θ on the lower inner surface 213 will be described. The enlargement angle θ is an angle formed by a direction in which the lower inner surface 213 extends in a cross section obtained by cutting the lower inner surface 213 in a plane including the rotation axis S with respect to a plane orthogonal to the rotation axis S. This angle becomes positive if the target surface extends downward or obliquely downward in FIG.

  If the extending direction of the lower inner surface 213 is perpendicular to the rotation axis S in a cross section obtained by cutting the lower inner surface 213 on a plane including the rotation axis S, the expansion angle θ is 0 °. If the extending direction of the lower inner surface 213 is parallel to the rotation axis S in a cross section obtained by cutting the lower inner surface 213 on a plane including the rotation axis S, the expansion angle θ is 90 °.

  In the present embodiment, the expansion angle θ of the portions 213a and 213c is 0 ° in the entire range from the nose portion N to the outlet space W by surrounding the centrifugal multiblade fan 23 in the clockwise direction of FIG.

  In the present embodiment, the expansion angle θ of the portion 213b is 30 ° or more and 90 ° or less in the entire range from the nose portion N to the outlet space W surrounding the clockwise centrifugal multiblade fan 23 of FIG. Is formed at an angle.

  The enlargement ratio B / A of the lower inner surface 213 will be described. The enlargement ratio B / A is a value obtained by dividing the axial distance B by the radial distance A. The axial distance B is the portion of the lower inner surface 213 that is the uppermost portion of FIG. 4 (that is, the direction of the rotation axis S and the direction from the lower bottom wall 212 toward the upper bottom wall 211) and the lower inner surface 213. 4 (ie, the direction of the rotational axis S and the direction from the upper bottom wall 211 toward the lower bottom wall 212), the positional deviation amount in the rotational axis S direction.

  In addition, the radial distance A is the most of the part 213a farthest from the rotation axis S in the part 213a farthest above the lower inner surface 213 and the most part 213c of the lower inner face 213 farthest below FIG. This is a positional deviation amount in a direction perpendicular to the rotation axis S with respect to a portion close to the rotation axis S. In this embodiment, the enlargement ratio B / A is set to be larger than 0.6.

  Note that the expansion angle θ and the expansion rate B / A of the portion 213b are defined in any cross section of the blower 20 that includes the rotation axis S and extends radially from the rotation axis S. FIG. 4 illustrates a specific IV-IV cross section among the cross sections including the rotation axis S and extending radially from the rotation axis S. In the present embodiment, among the cross sections extending radially from the rotation axis S, Even if the blower 20 is cut in any cross section from the nose portion N to the outlet space W in the clockwise direction in FIG. 3, the expansion angle θ and the expansion ratio B / A of the portion 213b are constant.

  Next, the operation of the indoor air conditioning unit 1 configured as described above will be described. In the present embodiment, the warm air 31 warmed by the heater core 10 by passing through the evaporator 9 and the heater core 10 and the warm air 31 cooled by the evaporator 9 by passing through the evaporator 9 and the bypass passage are heated by the heater core 10. The cold air 32 that has not flowed flows into the vicinity of the rotation axis S of the centrifugal multiblade fan 23 through the hole formed by the opening 21a.

  At this time, when the hole formed by the opening 21a is viewed from the direction of the rotation axis S, the temperature distribution of air in the hole is as shown in FIG. In addition, the left-right direction of FIG. 5 and the left-right direction of FIG. 1 correspond. In FIG. 5, the temperature of the air is represented by black shades, and the darker the temperature, the higher the temperature.

  As shown in FIG. 1, the cool air 32 flows more upward than the warm air 31, so the warm air 31 mainly flows to the left side of the rotation axis S of the hole formed by the opening 21 a and the cool air 32. Mainly flows to the right of the rotation axis S of the hole. Therefore, as shown in FIG. 5, the temperature of the air in the left region where hot air 31 mainly flows is higher than that in the right region where cold air 32 mainly flows.

  In the left region, the temperature of the air is lower as it is closer to the right region, and in the right region, the temperature of the air is higher as it is closer to the left region. This is because the warm air 31 and the cool air 32 slightly mix upstream of the opening 21a.

  The hot air 31 and the cold air 32 that have flowed into the centrifugal multiblade fan 23 with such a temperature distribution are blown away in a direction away from the rotation axis S due to the shape of the boss portion 230 and the rotation of a large number of blades 231.

  That is, as shown in FIG. 4, a part of the hot air 31 and the cold air 32 flowing into the centrifugal multiblade fan 23 enters the space sandwiched between two adjacent blades 231 as the blown air 41 to 44, It blows off in the direction away from the rotation axis S. 4 and the left-right direction in FIG. 1 are the same direction. At this time, the blown air 41 to 44 reflects the temperature distribution of the hot air 31 and the cold air 32 flowing into the centrifugal multiblade fan 23, the blown air 41 is the hottest, and the blown air 42, 43, and 44 are low in order. It will become. That is, even in a space sandwiched between two adjacent blades 231, a temperature change (that is, temperature nonuniformity) of the blown air in the direction of the rotation axis S may occur in some cases.

  However, in this embodiment, as described above, the length in the direction parallel to the rotation axis S in the scroll space V is at least part of the scroll space V (a space including the fan outlet space V1 and the expansion space V2). The distance from the rotation axis S increases. That is, the length of the scroll space V in the thickness direction increases toward the outer radial direction.

  Accordingly, the blown air 41 to 44 that has entered the space sandwiched between the two adjacent blades 231 and blown away from the rotation axis S is mainly composed of blown air 41 and 42 as shown in FIG. A swirling flow is generated such that the blown air 45 surrounds the blown air 46 mainly composed of the blown airs 43 and 44.

  In addition, in any cross section of the blower 20 that includes the rotation axis S and extends radially from the rotation axis S, the length in the thickness direction of the scroll space V increases in the radial direction in the cross section. If this is the case, the swirling flows 45 and 46 are generated.

  As is well known, the blown air blown away from the rotation axis S by the centrifugal multiblade fan 23 follows the logarithmic spiral shape of the inner surface 210a on the scroll space V side of the outer peripheral wall 210 of the scroll casing 21. The scroll space V is circulated so as to turn around the rotation axis S, and proceeds to the exit space W surrounded by the lower bottom wall 212. As described above, the flow 30 (see FIG. 7) along the logarithmic spiral shape of the inner surface 210a on the scroll space V side of the outer peripheral wall 210 and orthogonal to the rotation axis S is the main flow of the blown air.

  Then, the swirl flows 45 and 46 generated as described above become swirl flows 45 and 46 as secondary flows having the direction of the main stream 30 as the axial direction in the scroll space V (see FIG. 7). The swirl flows 45 and 46 promote the mixing of the hot air 31 and the cold air 32 in the scroll space V.

  Since the secondary flow is a flow that is generated perpendicular to the main flow, the direction of the main flow 30 coincides with the direction of the rotating shafts of the swirling flows 45 and 46. However, the direction of the main flow 30 and the positions of the swirling flows 45 and 46 may not match.

  Note that the swirling flows 45 and 46 do not impair the flow of the main flow 30 and thus do not cause pressure loss. The effect of adjusting the flow of the scroll space V improves the fan efficiency of the blower 20 and further reduces the specific noise. Contribute.

  Here, the experimental result which measured the flow of blowing air about several types of cross-sectional shape of the scroll space V is shown in FIG. 8, FIG. In FIG. 8, the absolute value of the difference between the maximum temperature and the minimum temperature in the exit space W is plotted when the expansion angle θ of the portion 213b is 0 °, 30 °, 60 °, and 90 °. In FIG. 9, the maximum temperature and the minimum temperature in the exit space W in each of the cases where the enlargement ratio B / A is 0, 0.6, 1.0 °, 1.7, and infinity (A = 0). The absolute value of the difference is plotted.

  The experimental conditions in FIGS. 8 and 9 are as follows. The air mix opening degree that is the air volume ratio of the hot air 31 and the cold air 32 that changes depending on the position of the air mix door 13 is 50%. In addition, the temperature of the cold air 32 coming out of the evaporator 9 was set to 5 ° C. Moreover, the temperature of the hot air 31 which came out of the heater core 10 was 88 degreeC. Further, a part of the warm air 31 and a part of the cool air 32 are mixed between the heater core 10 and the hole (fan suction port) formed by the opening 21a. Moreover, the minimum temperature of the blowing air in a fan inlet port was 20 degreeC, and the maximum temperature was 60 degreeC. Further, a part of the cool / warm air is mixed inside the centrifugal multiblade fan 23. The minimum temperature of the blown air sterilized from the centrifugal multiblade fan 23 was 30 ° C., and the maximum temperature was 50 ° C.

  In addition, the example of (theta) = 0 degree and the example of expansion ratio B / A = 0 are the air blowers C20 attached to the indoor air-conditioning unit C1 of a comparative example as shown in FIG. 10, 11, and 12, the reference numerals of the constituent elements shown in FIG. 1, FIG. 6, and FIG. 7 of the present embodiment are obtained by adding C to the heads of the corresponding constituent elements. .

  In the comparative example of FIG. 10, since the entire lower inner surface 213 is a plane orthogonal to the rotation axis S, θ = 0 °, that is, the enlargement ratio B / A = 0. That is, the scroll space V does not have a portion in which the length in the direction parallel to the rotation axis S increases as the distance from the rotation axis S increases.

  In such a comparative example, as shown in FIG. 11, unlike the present embodiment, the blown air C41 to C44 flowing between the two blades C231 is the same as the blown air 41 to 44 of FIG. No swirl flow is generated in the inside. Therefore, as shown in FIG. 12, only the main flow C30 along the inner surface C210a of the outer peripheral wall C210 is generated, and no swirl flow is generated. Therefore, mixing of the hot air C31 and the cold air C32 is not promoted inside the scroll space V.

  That is, in the scroll casing C21 that does not have the expansion of the scroll space CV in the direction of the rotation axis S used in the comparative example, the temperature distribution formed in the direction of the rotation axis S is maintained in the scroll space CV. Therefore, in the comparative example, in order to promote the mixing of the hot air and the cold air, a member for promoting mixing such as a rib is provided downstream of the outlet space CW of the scroll casing C21, which causes an increase in pressure loss.

  On the other hand, in this embodiment, it is not necessary to provide a rib for mixing cold air and hot air downstream from the outlet space W, and in the space between the actual outlet space W and the outlets 14, 15, 17. The rib may not be formed or may be formed.

  Further, as shown in FIG. 8, when the expansion angle θ of the portion 213b is 30 ° or more and 90 ° or less, the temperature variation in the outlet space W is remarkably reduced as compared with the comparative example. Moreover, as shown in FIG. 9, when the enlargement ratio B / A is 0.6 or more, the temperature variation in the outlet space W is significantly reduced as compared with the comparative example.

  Thus, in the present embodiment, the lower bottom wall 212 is such that the length of the scroll space V in the direction parallel to the rotation axis S becomes longer as the distance from the rotation axis S increases in part or all of the scroll space V. The inner surface 213 on the scroll space side is bent.

  Further, the portion 213b of the lower inner surface 213 is non-parallel to the rotation axis S so that the length in the direction parallel to the rotation axis S of the scroll space V becomes longer with increasing distance from the rotation axis S in at least a part of the scroll space V. It extends to.

  In this way, the hot air 31 and the cold air 32 blown out from the centrifugal multiblade fan 23 are mainstream 30 along the direction in which the inner surface 210a of the inner surface of the outer peripheral wall 210 extends around the rotation axis S in a spiral shape. And swirl flows 45 and 46 surrounding the main flow 30 are generated. The swirl flows 45 and 46 promote the mixing of two types of air having different properties such as hot air 31 and cold air 32 inside the scroll casing 21.

(Second Embodiment)
Next, a second embodiment will be described. In the present embodiment, the shapes of the upper bottom wall 211 and the lower bottom wall 212 of the scroll casing 21 are changed with respect to the indoor air conditioning unit 1 of the first embodiment.

  Specifically, as shown in FIG. 13, in the first embodiment, the lower inner surface 213 is displaced downward as it moves away from the rotation axis S, whereas in this embodiment, the upper inner surface 214 moves away from the rotation axis S. It is displaced upwards.

  More specifically, the length of the scroll space V in the direction parallel to the rotation axis S is such that the fan outlet space V1 outside the outer peripheral end of the blade 231 and the bell mouth 211a of the upper bottom wall 211 as viewed from the rotation axis S. In the enlarged space V2, which is farther from the rotation axis S than the fan outlet space, is larger than h1 and at most h2.

  That is, the length in the direction parallel to the rotation axis S in the scroll space V becomes longer as the distance from the rotation axis S increases in at least a part of the scroll space V (a space including the fan outlet space V1 and the expansion space V2). Yes. This is the same as in the first embodiment.

  Such a feature is realized by the shapes of the upper inner surface 214 on the scroll space V side of the upper bottom wall 211 and the lower inner surface 213 on the scroll space V side of the lower bottom wall 212.

  Specifically, the position of the lower inner surface 213 in the direction parallel to the rotation axis S is the same regardless of the distance from the rotation axis S in the portion facing the fan outlet space V1 and the expansion space V2.

  On the other hand, the position of the upper inner surface 214 in the direction parallel to the rotation axis S is the same regardless of the distance from the rotation axis S in the portion 214a facing the fan outlet space V1.

  However, the position of the upper inner surface 214 in the direction parallel to the rotation axis S is such that the distance from the rotation axis S is increased in the portion 214b facing the space V21 on the side connected to the fan outlet space in the enlarged space V2. It gets higher with. That is, the position of the upper inner surface 214 in the direction parallel to the rotation axis S is such that the distance from the rotation axis S increases in the portion 214b facing the space V21 on the side connected to the fan outlet space in the enlarged space V2. At the same time, it is displaced in a direction parallel to the rotation axis S and toward the upper bottom wall 211 from the lower bottom wall 212.

  Further, the position of the upper inner surface 214 in the direction parallel to the rotation axis S is a distance from the rotation axis S in the portion 214c facing the space V22 farther from the rotation axis S than the space V21 in the enlarged space V2. Regardless.

  In other words, the portion 214a is a plane orthogonal to the rotation axis S, and the upper inner surface 214 is bent at the boundary between the portion 214a and the portion 214b. Further, the portion 214b is a surface that is inclined so as to escape from the lower inner surface 213 as it is away from the rotation axis S, the upper inner surface 214 is bent at the boundary between the portion 214b and the portion 214c, and the portion 214c is a plane orthogonal to the rotation axis S. .

  Here, the expansion angle θ of the upper inner surface 214 will be described. The enlargement angle θ is an angle formed by an extending direction of the upper inner surface 214 in a cross section obtained by cutting the upper inner surface 214 in a plane including the rotation axis S with respect to a plane orthogonal to the rotation axis S. This angle is positive if the target surface extends upward or obliquely upward in FIG.

  In the present embodiment, the expansion angle θ of the portions 214a and 214c is 0 ° in the entire range from the nose portion N to the outlet space W by surrounding the centrifugal multiblade fan 23 in the clockwise direction of FIG.

  Further, in the present embodiment, the expansion angle θ of the portion 214b is 30 ° or more and 90 ° or less in the entire range from the nose portion N to the outlet space W surrounding the clockwise centrifugal multiblade fan 23 of FIG. Is formed at an angle.

  The enlargement ratio B / A of the upper inner surface 214 will be described. The enlargement ratio B / A is a value obtained by dividing the axial distance B by the radial distance A. The axial distance B is the portion of the upper inner surface 214 that is the lowermost part of FIG. 13 (that is, the direction of the rotation axis S and the direction from the upper bottom wall 211 to the lower bottom wall 212) and the uppermost inner surface 214. 13 is a positional shift amount in the rotational axis S direction with respect to the portion 214c above 13 (that is, in the rotational axis S direction and in the direction from the lower bottom wall 212 toward the upper bottom wall 211).

  Further, the radial distance A is the most distant portion of the upper inner surface 214 in the lower portion 214a in FIG. 13 and the most distant portion 214c in the upper inner surface 214 and the uppermost portion 214c in FIG. This is a positional deviation amount in a direction perpendicular to the rotation axis S with respect to a portion close to the rotation axis S. In the present embodiment, the enlargement ratio B / A is set to be larger than 0.6.

  Note that the expansion angle θ and the expansion ratio B / A of the above-described portion 214b are defined in any cross section of the blower 20 that includes the rotation axis S and extends radially from the rotation axis S. In FIG. 13, a specific cross section is shown among the cross sections including the rotation axis S and extending radially from the rotation axis S, but in this embodiment, which section of the cross section extending radially from the rotation axis S is a blower. Even when 20 is cut, the enlargement angle θ and the enlargement ratio B / A of the portion 214b are constant.

  Next, the operation of the indoor air conditioning unit 1 configured as described above will be described. In the present embodiment, the temperature distribution of the blown air flowing into the centrifugal multiblade fan 23 from the opening 21a is the same as in the first embodiment.

  The blown air (hot air 31 and cold air 32) that has flowed into the centrifugal multiblade fan 23 is blown away in a direction away from the rotation axis S due to the shape of the boss portion 230 and the rotation of a large number of blades 231.

  That is, as shown in FIG. 13, a part of the hot air 31 and the cold air 32 flowing into the centrifugal multiblade fan 23 enters the space sandwiched between the two adjacent blades 231 as the blown air 41 to 44, It blows off in the direction away from the rotation axis S. The temperature distribution of the blown air 41 to 44 is also the same as in the first embodiment.

  In the present embodiment, as described above, the length in the direction parallel to the rotation axis S in the scroll space V is the rotation axis in at least a part of the scroll space V (a space including the fan outlet space V1 and the expansion space V2). The longer the distance from S, the longer. That is, the length of the scroll space V in the thickness direction increases toward the outer radial direction.

  That is, in the present embodiment, the scroll space of the upper bottom wall 211 is set such that the length in the direction parallel to the rotation axis S of the scroll space V becomes longer as the distance from the rotation axis S increases in part or all of the scroll space V. The inner surface 214 on the side is bent. Further, the portion 214b of the upper inner surface 214 is not parallel to the rotation axis S so that the length in the direction parallel to the rotation axis S of the scroll space V becomes longer as the distance from the rotation axis S increases in at least a part of the scroll space V. It extends to.

  Therefore, the blown air 41 to 44 that has entered the space sandwiched between the two adjacent blades 231 and blown away from the rotation axis S is mainly composed of blown air 43 and 44, as shown in FIG. A swirling flow is generated such that the blown air 46 surrounds the blown air 45 mainly composed of the blown airs 41 and 42.

  In addition, in any cross section of the blower 20 that includes the rotation axis S and extends radially from the rotation axis S, the length in the thickness direction of the scroll space V increases in the radial direction in the cross section. If this is the case, the swirling flows 45 and 46 are generated.

  Then, the swirl flows 45 and 46 generated as described above become swirl flows 45 and 46 as secondary flows in the scroll space V in the same manner as in the first embodiment with the direction of the main flow as the axial direction. . The swirl flows 45 and 46 promote the mixing of the hot air 31 and the cold air 32 in the scroll space V. Thereby, this embodiment can exhibit an effect equivalent to 1st Embodiment.

  Here, the distribution of the air flow in the scroll space in the centrifugal multiblade fan as a comparative example is shown in FIG. 14, and when the enlarged angle θ of the portion 214b is variously set for the centrifugal multiblade fan 23 in the present embodiment. The air flow distribution in the scroll space V is shown in FIGS.

  The fine arrows described in FIGS. 14 to 17 represent the flow velocity vector of the blown air, and the thick arrows schematically represent the general flow direction of the blown air in the scroll space V.

  The comparative example of FIG. 14 represents the case where the enlargement angle θ of the portion 214b is 0 °, that is, the enlargement ratio B / A is zero. In this case, no swirling flow is generated in the scroll space V.

  The example of FIG. 15 represents a case where the enlargement angle θ of the portion 214b is 30 °, that is, the enlargement ratio B / A is 0.6. In this case, the swirl flow does not completely appear in the scroll space V, but the blown air tends to swirl as compared with the comparative example of FIG.

  The example of FIG. 16 represents a case where the enlargement angle θ of the portion 214b is 60 °, that is, the enlargement ratio B / A is 1.7. In this case, the swirling flow appears completely in the scroll space V. The example of FIG. 17 represents a case where the enlargement angle θ of the portion 214b is 90 °, that is, the enlargement ratio B / A is infinite. Also in this case, the swirling flow appears completely in the scroll space V.

(Third embodiment)
Next, a third embodiment will be described. In the present embodiment, as shown in FIG. 18, the upper bottom wall 211 is changed to the upper bottom wall 211 of the second embodiment with respect to the indoor air conditioning unit 1 of the first embodiment. Even in this case, the length in the direction parallel to the rotation axis S in the scroll space V is separated from the rotation axis S in at least a part of the scroll space V (a space including the fan outlet space V1 and the expansion space V2). It is getting longer.

  In the present embodiment, the temperature distribution of the blown air flowing into the centrifugal multiblade fan 23 from the opening 21a is the same as in the first embodiment. The blown air (hot air 31 and cold air 32) that has flowed into the centrifugal multiblade fan 23 is blown away in a direction away from the rotation axis S due to the shape of the boss portion 230 and the rotation of a large number of blades 231.

  That is, as shown in FIG. 13, a part of the hot air 31 and the cold air 32 flowing into the centrifugal multiblade fan 23 enters the space sandwiched between the two adjacent blades 231 as the blown air 41 to 44, It blows off in the direction away from the rotation axis S. The temperature distribution of the blown air 41 to 44 is also the same as in the first embodiment.

  The blown air 41 to 44 that has entered the space sandwiched between the two adjacent blades 231 and is blown away in the direction away from the rotation axis S is on the upper inner surface 214 side of the scroll space V as shown in FIG. A swirling flow is generated such that the blown air 42 surrounds the blown air 41. Further, as shown in FIG. 18, a swirling flow is generated such that the blown air 44 surrounds the blown air 44 on the lower inner surface 213 side of the scroll space V.

  Then, the swirl flows 41 to 44 generated as described above become swirl flows as secondary flows in the scroll space V in the same manner as in the first embodiment, with the direction of the main flow being the axial direction. Due to this swirling flow, mixing of the hot air 31 and the cold air 32 is promoted inside the scroll space V. Thereby, this embodiment can exhibit an effect equivalent to 1st Embodiment.

(Fourth embodiment)
Next, a fourth embodiment will be described. In the present embodiment, the shapes of the outer peripheral wall 210 and the lower bottom wall 212 are changed with respect to the first embodiment. Specifically, as shown in FIG. 19, the portions 213a and 213b of the lower inner surface 213 are the same as those of the first embodiment, but the portion 213c is not bent with respect to the portion 213b and smoothly curves. Connected to the portion 213b. Further, the inner surface 210 a of the outer peripheral wall 210 is also smoothly curved and connected to the portion 213 c and the upper inner surface 214.

  Even in such a case, the expansion angle θ and the expansion ratio B / A of the lower inner surface 213 can be defined. Also in this embodiment, the enlargement angle θ of the portion 213b is a constant value of 30 ° or more and 90 ° or less, and the enlargement ratio B / A is 0.6 or more. Further, the enlargement angle θ of the portion 213c is not a constant value of 0 °, and is gradually changed from the same value as the enlargement angle θ of the portion 213b to 0 ° while being away from the rotation axis S. Therefore, the maximum value of the expansion angle θ of the lower inner surface 213 in the present embodiment is a value of 30 ° or more and 90 ° or less, similarly to the expansion angle of the portion 213c. Therefore, this embodiment can also obtain the same effect as the first embodiment. The enlargement ratio B / A is the same as that in the first embodiment.

(Fifth embodiment)
Next, a fifth embodiment will be described. In the present embodiment, the centrifugal multiblade fan 23 is changed from a sirocco fan to a turbo fan having a boss portion 230 ′, a large number of blades 231 ′, and a ring portion 232 ′ with respect to the indoor air conditioning unit 1 of the second embodiment. Is.

  Whether the centrifugal multi-blade fan 23 is a sirocco fan or a turbo fan, the centrifugal multi-blade fan 23 sucks the hot air 31 and the cold air 32 and blows them away from the rotation axis S. If the cold air 32 enters the scroll space V, an effect equivalent to that of the second embodiment can be obtained.

  Note that the scroll casing 21 of the present embodiment is configured so that the shape of the upper bottom wall 211 covers the upper portion of the blade 231 ′ in a wider range as shown in FIG. 20 in accordance with the shape of the ring portion 232 ′ of the turbofan. Furthermore, it extends from the second embodiment in the direction of the rotation axis S (right direction in FIG. 20).

  Accordingly, the shape of the upper inner surface 214 is also changed from the second embodiment. Specifically, only the portion 214a among the portions 214a, 214b, and 214c of the upper inner surface 214 is changed. Specifically, the portion 214a bends smoothly and is smoothly connected to the upper inner surface 214b.

  Even in such a case, the expansion angle θ and the expansion ratio B / A of the lower inner surface 214 can be defined. Also in this embodiment, the enlargement angle θ of the portion 214b is a constant value of 30 ° or more and 90 ° or less, and the enlargement ratio B / A is 0.6 or more. Further, the enlargement angle θ of the portion 214a is not a constant value of 0 °, and is away from the rotation axis S in the portion farther from the rotation axis S than the centrifugal multiblade fan 23 and is the same as the enlargement angle θ of the portion 213b from 0 °. It gradually changes to the value. Therefore, the maximum value of the expansion angle θ of the upper inner surface 214 in the present embodiment is a value of 30 ° or more and 90 ° or less, similar to the expansion angle of the portion 214c. Therefore, this embodiment can also obtain the same effect as the second embodiment. The enlargement ratio B / A is the same as that in the second embodiment.

(Sixth embodiment)
Next, a sixth embodiment will be described. In the present embodiment, the position of the heater core 10 is changed with respect to the first to fifth embodiments, and the air mix door 13 is further changed to air mix doors 131a, 131b, 131c, and 131d.

  Specifically, the heater core 10 of the present embodiment is disposed on the downstream side of the air flow of the evaporator 9 and in the central portion of the air conditioning casing 2 in the vertical direction (direction parallel to the rotation axis S) in FIG. Furthermore, the heater core 10 is disposed at the center in the depth direction of FIG.

  As a result, the bypass passage 12 that bypasses the heater core 10 is disposed so as to surround the heater core 10 on the upper side, the lower side, the front side in the depth direction, and the rear side in the depth direction of the heater core 10.

  As a result, when the hole formed by the opening 21a is viewed from the direction of the rotation axis S, the temperature distribution of the air in the hole is concentric as shown in FIG. Distribution. Even in such a case, similarly to the first to sixth embodiments, air having non-uniform temperature enters between two adjacent blades of the centrifugal multiblade fan 23 and blows out from the centrifugal multiblade fan 23. Later, in the scroll space V, a swirl flow is generated together with the main flow. Therefore, an effect equivalent to that of the first to fifth embodiments can be obtained.

(Seventh embodiment)
Next, a seventh embodiment will be described. This embodiment changes the shape of the scroll casing 21 with respect to the indoor air-conditioning unit 1 of 1st Embodiment. Specifically, the scroll casing 21 of the present embodiment has another outlet space W ′ in addition to the outlet space W, as shown in FIG. The exit space W ′ is a space surrounded by the inner peripheral wall 209 ′, the outer peripheral wall 210, the upper bottom wall 211, and the lower bottom wall 212.

  The outer peripheral wall 210 of the present embodiment, on the one hand, exits from the nose portion N to the exit space W ′ such that the distance from the rotational axis S increases according to a known logarithmic spiral function with respect to the winding angle about the rotational axis S. The spiral extends around the rotation axis S. On the other hand, the scroll casing 21 rotates from the nose portion N ′ to the exit space W so that the distance from the rotation axis S increases according to a known logarithmic spiral function with respect to the winding angle about the rotation axis S. It surrounds the axis S and extends spirally. Accordingly, like the nose portion N, the nose portion N ′ corresponds to the winding start portion of the outer peripheral wall 210.

  Therefore, in the present embodiment, a part of the warm air 31 and the cold air 32 blown out from the centrifugal multiblade fan 23 forms the scroll space V in the direction surrounding the centrifugal multiblade fan 23 from the nose portion N to the outlet space W ′. After the circulation, it enters the exit space W ′, and then flows into the passenger compartment through the air outlets that are not closed among the air outlets 14, 15, and 17. Further, the other part of the warm air 31 and the cool air 32 blown out from the centrifugal multiblade fan 23 circulated in the scroll space V from the nose portion N ′ to the outlet space W in the direction surrounding the centrifugal multiblade fan 23. After that, it enters the exit space W, and then flows into the passenger compartment through the air outlets that are not closed among the air outlets 14, 15, and 17.

  Also in this embodiment, the scroll space V is the first in the range from the nose portion N ′ to the exit space W and from the nose portion N to the exit space W ′ in the clockwise direction of FIG. It is surrounded by an upper bottom wall 211, a lower bottom wall 212, a lower inner surface 213 (parts 213a, 213b, 213c), and an upper inner surface 214 having the same configuration as that of the embodiment (FIG. 4 and the like).

  Therefore, also in this embodiment, in the scroll space V from the nose portion N ′ to the exit space W and in the scroll space V from the nose portion N to the exit space W ′, the main flow and the swirl flow similar to those in the first embodiment are used. (Secondary flow) occurs. Therefore, the same effect as that of the first embodiment can be obtained.

(Other embodiments)
In addition, this invention is not limited to above-described embodiment, In the range described in the claim, it can change suitably. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of the component, etc., the shape, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to the positional relationship or the like. The present invention also allows the following modifications to the above embodiments. In addition, the following modifications can select application and non-application to the said embodiment each independently. In other words, any combination of the following modifications can be applied to the above-described embodiment.

(Modification 1)
In each of the above embodiments, the expansion angle θ of the portions 213b and 214b is constant in the scroll casing 21. However, this is not necessarily the case. For example, in the same cross section including the rotation axis S, the expansion angle θ of the portions 213b and 214b may be gradually changed. Alternatively, in the scroll space V, from the start to the end of scrolling (from the nose portion N to the exit space W and from the nose portion N ′ to the exit space W ′), the expansion angle θ of the portions 213b and 214b is It may be gradually changed.

  Even in that case, if the lower inner surface 213 or the upper inner surface 214 surrounding the scroll space V is always 30 ° or more and 90 ° or less in the range from the start to the end of the scroll, the same effect as each of the above embodiments can be obtained. be able to. In this range, if the maximum value of the lower inner surface 213 or the upper inner surface 214 surrounding the scroll space V is 30 ° or more and 90 ° or less, the effect of improving the mixing property of the air entering between the two blades is exhibited to some extent. The

(Modification 2)
In each of the above embodiments, the enlargement ratio B / A of the scroll space V is constant in the scroll casing 21. However, this is not necessarily the case. For example, in the scroll space V, the enlargement ratio B / A gradually changes from the start to the end of scrolling (from the nose portion N to the exit space W and from the nose portion N ′ to the exit space W ′). It may be.

  Even in that case, if the enlargement ratio B / A of the scroll space V is always 0.6 or more in the range from the start to the end of the scroll, the same effects as those of the above embodiments can be obtained. In this range, if the maximum value of the expansion rate B / A of the scroll space V is 0.6 or more, the effect of improving the mixing property of the air entering between the two blades is exhibited to some extent.

(Modification 3)
In the above embodiments, hot air 31 and cold air 32 having different temperatures (for example, average temperature) are illustrated as two types of air having different properties and simultaneously sucked by the centrifugal multiblade fan 23. However, the two types of air having different properties are not limited to cold air and hot air, and may be inside air and outside air, or may be two types of air having different average humidity.

  In each of the above embodiments, only two types of air having different properties and being simultaneously sucked by the centrifugal multiblade fan 23 are used. However, three or more types of air having different properties are separated by the centrifugal multiblade fan 23. They may be sucked at the same time.

  For example, four different types of air, that is, cold air and hot air of outside air, and cold air and hot air of inside air may be simultaneously sucked by the centrifugal multiblade fan 23. Even in this case, in the blower 20 having the structure as in the above embodiment, the swirl flow is generated, so that the mixing property of these four types of air is enhanced.

(Modification 4)
In each of the above-described embodiments, the inner surface 213 or a part of the inner surface 214 is formed such that the length in the direction parallel to the rotation axis S of the scroll space V becomes longer with increasing distance from the rotation axis S in only a part of the scroll space V. It extends non-parallel to the rotation axis S. However, the entire inner surface 213 or the entire inner surface 214 is not connected to the rotation axis S so that the length of the scroll space V in the direction parallel to the rotation axis S increases as the distance from the rotation axis S increases in the entire scroll space V. You may extend in parallel.

DESCRIPTION OF SYMBOLS 1 Indoor air conditioning unit 2 Air conditioning casing 20 Blower 21 Scroll casing 21a Opening part 23 Centrifugal multiblade fan 210 Outer peripheral wall 211 Upper bottom wall 212 Lower bottom wall S Rotating shaft V Scroll space

Claims (9)

An air-conditioning casing (2) that forms a flow path of blown air to be sent into the vehicle interior of the vehicle;
A blower (20) that is arranged in the air conditioning casing and sucks and blows out a plurality of types of air (31, 32) having different properties from among the blown air in the air conditioning casing,
The blower rotates around the rotating shaft (S), sucks the plural types of air, and blows out the plural types of air in a direction away from the rotating shaft, and the centrifugal multi-blade fan (23). A scroll casing (21) for circulating the plurality of types of air blown from the blade fan;
The scroll casing is opposed to the first bottom wall (211) formed with openings (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan, and the first bottom wall. A second bottom wall (212) and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall;
A scroll space (V) surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan is blown out from the centrifugal multiblade fan. The multiple types of air circulate,
An inner surface on the scroll space side of the first bottom wall so that a length of the scroll space in a direction parallel to the rotation axis becomes longer with increasing distance from the rotation axis in at least a part of the scroll space; One or both (213, 214) of the inner surface on the scroll space side of the second bottom wall are formed non-parallel to the rotation axis, and the indoor air conditioning unit.   The inner surface of the second bottom wall on the scroll space side so that the length of the scroll space in the direction parallel to the rotation axis becomes longer with increasing distance from the rotation axis in at least a part of the scroll space ( The indoor air conditioning unit according to claim 1, wherein 213) is formed non-parallel to the rotation axis.   The inner surface of the first bottom wall on the scroll space side so that the length of the scroll space in the direction parallel to the rotation axis becomes longer with increasing distance from the rotation axis in at least a part of the scroll space ( The indoor air conditioning unit according to claim 1 or 2, wherein 214) is formed non-parallel to the rotating shaft.   The direction in which the inner surface extends in a cross section obtained by cutting the inner surface of the first bottom wall on the scroll space side or the inner surface of the second bottom wall on the scroll space side with a plane including the rotation axis, An angle formed with respect to a plane orthogonal to the rotation axis, and a positive angle if the inner surface extends in a direction that increases the length of the scroll space in the rotation axis direction as the distance from the rotation axis increases. The indoor air conditioning unit according to any one of claims 1 to 3, wherein a maximum value of the expansion angle is 30 ° or more and 90 ° or less when (θ) is set. An air-conditioning casing (2) that forms a flow path of blown air to be sent into the vehicle interior of the vehicle;
A blower (20) that is arranged in the air conditioning casing and sucks and blows out a plurality of types of air (31, 32) having different properties from among the blown air in the air conditioning casing,
The blower rotates around the rotating shaft (S), sucks the plural types of air, and blows out the plural types of air in a direction away from the rotating shaft, and the centrifugal multi-blade fan (23). A scroll casing (21) for circulating the plurality of types of air blown from the blade fan;
The scroll casing is opposed to the first bottom wall (211) formed with openings (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan, and the first bottom wall. A second bottom wall (212), and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall, the first bottom wall,
A scroll space (V) surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan is blown out from the centrifugal multiblade fan. The multiple types of air circulate,
The inner surface on the scroll space side of the outer peripheral wall extends around the rotating shaft in a spiral shape,
The plurality of types of air blown from the centrifugal multiblade fan generate a main flow along a direction in which the inner surface of the outer peripheral wall extends around the rotation shaft and extends in a spiral shape, and a swirl flow surrounding the main flow. The indoor air conditioning unit characterized in that the scroll casing is formed.   The indoor air conditioning unit according to any one of claims 1 to 5, wherein the plurality of types of air have different temperatures. An evaporator (9) disposed in the air conditioning casing and for cooling the blown air introduced into the air conditioning casing;
A heater core (10) that is disposed within the air conditioning casing and that heats the blown air introduced into the air conditioning casing;
The temperature of the air blown into the vehicle interior is adjusted by adjusting the air volume ratio between the air volume of the blown air passing through the heater core and the air volume of the blown air passing through the bypass passage (12) bypassing the heater core in the air conditioning casing. An air mix door (13),
The blower is arranged at the downstream side of the evaporator, the heater core, and the air mix door, and is warm air (31) that is blown air heated through the heater core and blown air that has passed through the bypass passage. The indoor air conditioning unit according to claim 6, wherein cold air (32) is sucked and blown out as the plurality of types of air. A centrifugal multiblade fan (23) that sucks the plurality of types of air by rotating around the rotation shaft (S) and blows out the plurality of types of air in a direction away from the rotation shaft;
A scroll casing (21) for circulating the plurality of types of air blown from the centrifugal multiblade fan,
The scroll casing is opposed to the first bottom wall (211) formed with openings (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan, and the first bottom wall. A second bottom wall (212) and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall;
A scroll space (V) surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan is blown out from the centrifugal multiblade fan. The multiple types of air circulate,
An inner surface on the scroll space side of the first bottom wall so that a length of the scroll space in a direction parallel to the rotation axis becomes longer with increasing distance from the rotation axis in at least a part of the scroll space; One or both of the inner surfaces on the scroll space side of the second bottom wall are formed non-parallel to the rotating shaft. A centrifugal multiblade fan (23) that sucks the plurality of types of air by rotating around the rotation shaft (S) and blows out the plurality of types of air in a direction away from the rotation shaft;
A scroll casing (21) for circulating the plurality of types of air blown from the centrifugal multiblade fan,
The scroll casing is opposed to the first bottom wall (211) formed with openings (21a) for introducing the plurality of types of air sucked by the centrifugal multiblade fan, and the first bottom wall. A second bottom wall (212) and an outer peripheral wall (210) connecting the first bottom wall and the second bottom wall;
A scroll space (V) surrounded by the first bottom wall, the second bottom wall, and the outer peripheral wall and further away from the rotating shaft than the centrifugal multiblade fan is blown out from the centrifugal multiblade fan. The multiple types of air circulate,
The inner surface on the scroll space side of the outer peripheral wall extends around the rotating shaft in a spiral shape,
The plurality of types of air blown from the centrifugal multiblade fan generate a main flow along a direction in which the inner surface of the outer peripheral wall extends around the rotation shaft and extends in a spiral shape, and a swirl flow surrounding the main flow. The blower characterized in that the scroll casing is formed.

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