JP2018155151A - Centrifugal blower for vehicular air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide centrifugal blowers (1, 1A, 1B) capable of feeding a sufficient amount of air even in a case where ventilation resistance of a ventilation passage continuing to a foot blowout port becomes high.SOLUTION: Centrifugal blowers (1, 1A, 1B) have a first scroll (18) configured to feed air out to a vent blowout port, and a second scroll (19) configured to feed air out to a foot blowout port. A spread angle of the second scroll (19) between an angular position that advances from a position of a second reference line segment (L02) connecting between a rotational axis line (Ax) and a tongue part (19T) of the second scroll (19) by 200 degrees and an angular position advancing by 300 degrees, is made smaller than a spread angle of the first scroll (18) between an angular position that advances from a position of a first reference line segment (L01) connecting between the rotational axis line (Ax) and a tongue part (18T) of the first scroll (18) by 200 degrees and an angular position advancing by 300 degrees.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a centrifugal blower applied to a two-layer flow type vehicle air conditioner.

  The vehicle air conditioner generally has a defroster outlet, a vent outlet, and a foot outlet. The air conditioner selectively blows out temperature-adjusted air from these outlets according to the difference in the operation mode. For example, in the bi-level mode, air is blown mainly from two locations, a vent outlet and a foot outlet, and wind is applied to the upper body and feet of the occupant. In this case, in order to ensure the thermal comfort of the occupant, the temperature of the air blown out from the foot outlet is adjusted so as to be higher than the temperature of the air blown out from the vent outlet. The temperature adjustment is performed by adjusting the ratio of air passing through the heat exchanger for heating.

  As a vehicle air conditioner, a so-called two-layer flow type air conditioner having two upper and lower air blowing paths is known. The air conditioner can take in outside air through the other air passage while circulating the air in the vehicle interior through one air passage. Therefore, during heating, the interior air already warmed in the lower air flow path is circulated to improve the thermal efficiency, and at the same time, outside air of low humidity is taken in through the upper air flow path and applied to the front window, It is possible to prevent fogging of the windshield due to water vapor contained therein. Such an upper and lower two-layer flow type air conditioner is, for example, as shown in Patent Document 1, a centrifuge having an impeller that blows out air and two scrolls that direct the air blown out from the impeller to each blowing path. It is configured using a blower.

  Now, when the upper and lower two-layer flow type air conditioner as described above is operated in the bi-level mode, the upper and lower two-layer air flow paths are higher in the air flowing through the lower air flow path than the air flowing through the upper air flow path. It is set to pass through the heat exchanger for heating at a rate. For this reason, the ventilation resistance in the lower air blowing path is higher than that in the upper air blowing path. As a result, there has been a concern that the amount of air obtained from the lower air flow path is reduced, and the amount of hot air blown from the foot outlet is insufficient.

Japanese Patent Laid-Open No. 9-024722

  It is an object of the present invention to provide a centrifugal blower for a two-layer flow type air conditioner, which can blow with a sufficient air volume even when the ventilation resistance of a ventilation path leading to a foot outlet increases. Yes.

  According to a preferred embodiment of the present invention, a centrifugal blower for a vehicle has a motor and a plurality of blades forming a circumferential blade row, and is rotated around a rotation axis extending in the axial direction by the motor. A first impeller that is driven to blow out air in a radially inner space of the blade row in a centrifugal direction, a first suction port that opens in the axial direction, and a first discharge port that opens in the circumferential direction. A first scroll for housing the first impeller, wherein air sucked from the first suction port by rotation of the first impeller is defrosted from the first discharge port and / or vented A first scroll that is fed to the air outlet, and a plurality of blades that form a circumferential blade row, and is driven to rotate about the rotation axis by the motor, and the air in the radially inner space of the blade row is centrifugally moved A second impeller that blows out toward the A second scroll that has a second suction port that opens in the axial direction and a second discharge port that opens in the circumferential direction, and houses the second impeller, wherein the second impeller rotates to rotate the second impeller. 2 in a cross section of the second scroll that sends air sucked from the suction port to the foot outlet from the second discharge port and the first scroll that is orthogonal to the rotational axis, and the rotation axis and the tongue of the first scroll A virtual line segment connecting the center point is defined as a first reference line segment, and a virtual line segment connecting the rotation axis and the center point of the tongue of the second scroll in the cross section of the second scroll perpendicular to the rotation axis. Is the second reference line segment, and the angular position advanced by 300 degrees from the angular position advanced by 200 degrees along the rotational direction of the second impeller around the rotation axis from the position of the second reference line segment. Until the first The spread angle of the scroll is between the position of the first reference line segment and the angle position advanced from the angular position advanced by 200 degrees along the rotational direction of the first impeller from the position of the first reference line segment to the angular position advanced by 300 degrees. A centrifugal blower that is smaller than the spread angle of the first scroll is provided.

  According to the above-described embodiment of the present invention, even if the ventilation resistance of the ventilation path following the foot outlet increases, it is possible to blow air to the foot outlet with a sufficient air volume.

It is a longitudinal cross-sectional view which shows the structure of the air intake part of an air conditioner, and a centrifugal blower, and contains the meridian cross section of a centrifugal blower. It is a longitudinal cross-sectional view which shows the structure of the air intake part and centrifugal blower of an air conditioner cut | disconnected by the cut surface orthogonal to the cut surface in FIG. It is a cross-sectional view which shows the difference in the expansion angle of the 1st scroll and the 2nd scroll which cut | disconnected the 1st scroll shown in FIG. 1 by the cut surface orthogonal to the rotating shaft line of a centrifugal blower. It is a cross-sectional view which shows the difference in the expansion angle of the 1st scroll and the 2nd scroll which cut | disconnected the 2nd scroll shown in FIG. 1 by the cut surface orthogonal to the rotating shaft line of a centrifugal blower. It is a figure explaining the divergence angle of the said scroll which cut | disconnected the scroll by the cut surface orthogonal to the centerline. It is a longitudinal cross-sectional view containing the meridional section of a centrifugal blower which shows the structure of the centrifugal blower which concerns on other embodiment. It is a longitudinal cross-sectional view including the meridian section of a centrifugal blower which shows the structure of the centrifugal blower which concerns on other embodiment.

  Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings.

  FIG.1 and FIG.2 is sectional drawing which shows the structure of the vicinity of the air intake part and centrifugal blower of an air conditioner for vehicles.

  The centrifugal blower 1 of this embodiment is a centrifugal blower for a two-layer flow air conditioner, and is used for an air conditioner for a vehicle. The air conditioner has a defroster air outlet (not shown), a vent air outlet (not shown), and a foot air outlet (not shown). From each air outlet, the front window of the vehicle and the upper body of the passenger And it blows toward the passenger's feet.

  As shown in FIGS. 1 and 2, the centrifugal blower 1 includes a motor 13, a first impeller 5, a second impeller 6, and a first impeller 5 arranged in the direction of the rotation axis Ax of the motor 13. One scroll 18 and a second scroll 19 that houses the second impeller 6 are provided. The first impeller 5 and the first scroll 18, and the second impeller 6 and the second scroll 19 are located on one side and the other side in the axial direction (upper and lower sides in the example shown in FIG. 1), respectively. ing.

  In this specification, for convenience of explanation, the direction of the rotation axis Ax is referred to as the axial direction or the vertical direction, and the upper side and the lower side in FIGS. 1 and 2 are respectively “one side in the axial direction” or “upper side in the axial direction”. And “the other side in the axial direction” or “the lower side in the axial direction”. However, this does not mean that the direction of the rotation axis Ax coincides with the vertical direction when the air conditioner is actually incorporated in a vehicle. In the present specification, unless otherwise noted, the direction of the radius of a circle drawn on a plane perpendicular to the rotation axis Ax around an arbitrary point on the rotation axis Ax is referred to as a radial direction. The circumferential direction of the circle is called the circumferential direction or the circumferential direction.

  The 1st impeller 5 has the several blade | wing 50 which forms the blade row | line | column 50A arranged in the circumferential direction in the outer peripheral part. The first impeller 5 is rotationally driven by the motor 13 around the rotation axis Ax extending in the axial direction, and blows out air in the radially inner space of the blade row 50A in the centrifugal direction. The first impeller 5 is accommodated in a substantially cylindrical internal space of the first scroll 18.

  The first scroll 18 has a first suction port 22A that opens in the axial direction and a first discharge port 180 that opens in the circumferential direction. The first discharge port 180 extends substantially in the tangential direction of the outer peripheral surface of the first scroll 18 when the first scroll 18 is viewed from the axial direction. The first scroll 18 sends the air sucked from the first suction port 22 </ b> A through the first discharge port 180 to the defroster outlet and / or the vent outlet by the rotation of the first impeller 5.

  The 2nd impeller 6 has the several blade | wing 60 which forms the blade row | line 60A arranged in the circumferential direction in the outer peripheral part. The second impeller 6 is rotationally driven around the rotation axis Ax by the motor 13 and blows out air in the space radially inward of the blade row 60A in the centrifugal direction. The second impeller 6 is accommodated in a substantially cylindrical internal space of the second scroll 19.

  The second scroll 19 has a second suction port 22B that opens in the axial direction and a second discharge port 190 that opens in the circumferential direction. The second discharge port 190 extends substantially in the tangential direction of the outer peripheral surface of the second scroll 19 when the second scroll 19 is viewed from the axial direction. The second scroll 19 sends out air sucked from the second suction port 22 </ b> B by the rotation of the second impeller 6 from the second discharge port 190 to the foot outlet.

  The first impeller 5 and the second impeller 6 are arranged such that the rotation direction G thereof coincides with the spiral rotation direction drawn by the outer peripheral surfaces of the first scroll 18 and the second scroll 19.

  In the example shown in FIG. 1, the first scroll 18 and the second scroll 19 are formed by dividing the internal space of the scroll housing 17 formed integrally with a partition wall 20. More specifically, the partition wall 20 extends radially inward from the outer peripheral wall 17 </ b> A of the scroll housing 17, and the inner peripheral surface of the scroll housing 17 and the impeller 5 in the inner space of the scroll housing 17. 6 is divided in the axial direction (up and down). Then, the first scroll 18 and the second scroll 19 are formed on both sides of the partition wall 20.

  Moreover, in the example shown in FIG. 1, the centrifugal blower 1 is a single suction type centrifugal blower. More specifically, the first suction port 22A of the first scroll 18 opens to one side in the axial direction (the upper side in the axial direction). The second suction port 22B of the second scroll 19 is also open on one side in the axial direction (the upper side in the axial direction). The internal space of the first scroll 18 and the internal space of the second scroll 19 communicate with each other via the second suction port 22B.

  Moreover, in the example shown in FIG. 1, the 1st impeller 5 and the 2nd impeller 6 are integrally formed. The impellers 5 and 6 are integrally formed with an inner deflection member 9. The inner deflection member 9 is sometimes called a cone portion. The inner deflection member 9 is a rotating body in a geometric sense, and has a side peripheral portion 10 connected to the lower end 7 of the second impeller 6 and a disc-shaped central portion 11. In the central part 11, the rotating shaft 12 of the motor 13 is connected to the impellers 5 and 6. In this example, the side peripheral portion 10 is curved such that the contour line in the meridional section of the outer peripheral surface of the side peripheral portion 10 becomes steep as it approaches the central portion 11. In another example (not shown), in the case of the side peripheral portion 10, the contour line in the meridional section of the outer peripheral surface of the side peripheral portion 10 is not curved from the central portion 11 toward the blade row 60A (the cross section is linear). There is also.

  The separation cylinder 14 is inserted into the scroll housing 17 via the first suction port 22A. As can be understood by comparing and contrasting FIGS. 1 and 2, the cross section of the inlet side end (upper part) 24 of the separation cylinder 14 is generally rectangular. The cross section of the central portion 15 of the separation cylinder 14 is circular (or generally circular). The cross-sectional shape of the separation cylinder 14 smoothly changes from a rectangular shape to a circular shape (or a generally circular shape) as it approaches the central portion 15 from the inlet side end portion 24. The outlet side end (lower part) 16 of the separation cylinder 14 has a flare shape that increases in diameter as it approaches the lower end, and the lower end is circular.

  The separation cylinder 14 extends in the axial direction through the radially inner side of the first suction port 22 </ b> A and the radially inner side of the blade row 50 </ b> A of the first impeller 5. The inlet side end 24 of the separation cylinder 14 is located outside the scroll housing 17 (on the upper side in the axial direction than the first suction port 22A). The outlet side end 16 of the separation cylinder 14 is provided so as to be substantially at the same position as the partition wall 20 in the axial direction.

  The entire separation cylinder 14 may be integrally formed by resin injection molding. Alternatively, after the inlet side end (upper part) 24 of the separation cylinder 14 and the central part 15 and the lower outlet side end (lower part) 16 of the separation cylinder 14 are separately molded, they may be connected. .

  The separation cylinder 14 is configured to change the flow of air sucked into the scroll housing 17 into a first air flow passing through the first passage 14A outside the separation cylinder 14 and a second passage passing through the second passage 14B inside the separation cylinder 14. Divide into air flow. The first air flow passes through the ring-shaped region outside the outer peripheral surface 141 of the separation cylinder 14 in the first suction port 22A of the first scroll 18 and flows inward in the radial direction of the blade row 50A of the first impeller 5. To do. The second air flow enters the inside of the separation cylinder 14 from the upper end of the separation cylinder 14 and flows inward in the radial direction of the blade row 60A of the second impeller 6 through the second suction port 22B of the second scroll 19. Therefore, the ring-shaped region outside the outer peripheral surface 141 of the separation cylinder 14 in the first suction port 22A of the first scroll 18 is the first suction port of the scroll housing 17, and the inlet side end 24 of the separation cylinder 14 is the scroll housing. It can also be regarded as 17 second inlets. The outlet side end portion 16 of the separation cylinder 14 turns the inflowing first air flow outward in the radial direction to guide the first scroll 18, and turns the inflowing second air flow outward in the radial direction. Guide to the second scroll 19.

  The air intake part of the air conditioner has a housing 21. The housing 21 is referred to as an “air intake housing” in order to distinguish it from the scroll housing 17. The scroll housing 17 and the air intake housing 21 may be integrally formed, or may be connected by a method such as screwing, bonding, or fitting after being separately manufactured. The scroll housing 17 and the air intake housing 21 form part of the air conditioner casing. In a preferred embodiment, the separation cylinder 14 is a separate component from the scroll housing 17 and the air intake housing 21 and is supported at a predetermined position by the air intake housing 21.

  The air intake housing 21 has a first opening 25, a second opening 26, a third opening 27, and a fourth opening 28. Inside air (vehicle interior air) can be introduced into the internal space 23 of the air intake housing 21 from the vehicle interior space 29 (details are not shown) via the first opening 25 and the third opening 27. That is, the first opening 25 and the third opening 27 are first and second inside air inlets for taking inside air into the air intake housing 21. Further, through the second opening 26 and the fourth opening 28, the outside air (outside of the vehicle) is introduced into the internal space 23 of the air intake housing 21 from the outlet 30 (details not shown) of the outside air introduction path provided in the vehicle. From the air). That is, the second opening 26 and the fourth opening 28 are first and second outside air inlets for taking outside air into the air intake housing 21.

  By rotating the door 31 around the rotation shaft 31 </ b> A, the inflow of air (inside air) from the first opening 25 into the air intake housing 21 can be allowed or blocked. By rotating the door 32 around the rotation shaft 32A, the inflow of air (outside air) from the second opening 26 into the air intake housing 21 can be allowed or blocked. By switching the position by rotating the door 33 around the rotation axis 33A, air (inside air or outside air) flows into the air intake housing 21 through one of the third opening 27 and the fourth opening 28. Can be made.

  Almost all of the air introduced into the air intake housing 21 from the first opening 25 and / or the second opening 26 passes through the first passage 14A and from the third opening 27 and / or the fourth opening 28. The air intake housing 21 and the separation cylinder 14 are formed so that almost all of the air introduced into the air intake housing 21 passes through the second passage 14B.

  Between the region where the first opening 25, the second opening 26, the third opening 27, and the fourth opening 28 are disposed and the inlet side end 24 of the separation cylinder 14, the air intake housing 21 is in the air. A filter 35 is provided for removing contaminants such as dust and particles. The filter 35 preferably consists of a single filter element.

  FIG. 3 shows a cross section of the first scroll 18 orthogonal to the rotation axis Ax of the first impeller 5. FIG. 4 shows a cross section of the second scroll 19 orthogonal to the rotation axis Ax of the second impeller 6.

  As shown in FIG. 3, a virtual line segment connecting the rotation axis Ax and the center point 18Tp of the tongue 18T of the first scroll 18 is defined as a first reference line segment L01. As shown in FIG. 4, a virtual line segment connecting the rotation axis Ax and the center point 19Tp of the tongue 19T of the second scroll 19 is defined as a second reference line segment L02. Here, the center point of the tongue portion of the scroll is a point that becomes the center of the arc formed by the tip portion of the tongue portion in the section of the tongue portion orthogonal to the rotation axis of the impeller accommodated in the scroll.

  The center point 18Tp of the tongue portion 18T and the center point 19Tp of the tongue portion 19T are preferably at the same position in the axial direction. The radius from the center point 18Tp of the tongue 18T to the tip of the tongue 18T and the radius from the center point 19Tp of the tongue 19T to the tip of the tongue 19T are preferably the same size. There is no step in the tongue portions 18T and 19T of the first scroll 18 and the second scroll 19, and an increase in noise can be suppressed.

  As shown in FIG. 4, the angular position advanced by 200 degrees along the rotational direction G of the second impeller 6 from the position of the second reference line segment L02 around the rotation axis Ax (position indicated by the broken line L12 in FIG. 4). From the position of the first reference line segment L01 to the first impeller 5 around the rotation axis Ax. Of the first scroll 18 from an angular position advanced by 200 degrees along the rotation direction G (a position indicated by a broken line L11 in FIG. 3) to an angular position advanced by a 300 degrees (a position indicated by a broken line L21 in FIG. 3). Smaller than the corner. An angular position advanced by 300 degrees from the position of the second reference line segment L02 around the rotational axis Ax by 200 degrees along the rotational direction G of the first impeller 6 (position indicated by the broken line L12 in FIG. 4). The range up to (a position indicated by a broken line L22 in FIG. 4) is a range that greatly affects the increase in the pressure of the air blown from the second discharge port 190 in the second scroll 19. In this embodiment, since the expansion angle of the second scroll 19 in the range is smaller than the expansion angle of the first scroll 18, the pressure of the air blown from the second discharge port 190 is set to be higher than the air blown from the first discharge port 180. Can also be effectively increased.

ｒ（θ）：巻き始め（図５において回転軸線ＸとスクロールＳの舌部Ｔの中心点Ｔｐとを結ぶ仮想線分Ｌ０で示す位置）を基準とした巻き角θにおけるスクロール半径
ｒ_０：羽根車Ｉの外周面からスクロールＳの巻き始めにおけるスクロールＳの外周壁１７Ｔまでの距離
ｒ_１：羽根車Ｉの半径
ｎ：拡がり角（ラジアン）
θ：巻き始め（図５において破線Ｌ０で示す位置）を基準として、回転軸線Ｘの周りに回転方向Ｃに沿って進んだ任意の角度 Here, the divergence angle will be described with reference to FIG. FIG. 5 is a cross-sectional view of the scroll S cut along a cross section orthogonal to the rotation axis X of the impeller I accommodated in the scroll S. Here, the scroll S is formed with a constant spread angle n. In this case, the spread angle n is a relationship between the distance from the rotation axis X to the outer peripheral wall 17T of the scroll S (hereinafter referred to as “scroll radius”) and the winding angle θ of the scroll S, for example, expressed.

r (θ): scroll radius at the winding angle θ with reference to the start of winding (the position indicated by the imaginary line segment L0 connecting the rotation axis X and the center point Tp of the tongue T of the scroll S in FIG. 5) r ₀ : blade Distance from the outer peripheral surface of the car I to the outer peripheral wall 17T of the scroll S at the beginning of the scroll S r ₁ : Radius of the impeller I n: Spreading angle (radian)
θ: Arbitrary angle that advances along the rotation direction C around the rotation axis X with reference to the start of winding (position indicated by the broken line L0 in FIG. 5)

  Further, in the example shown in FIG. 3 and FIG. 4, an angular position (broken line L02 in FIG. 4) is advanced from the position of the second reference line segment L02 around the rotation axis Ax by 0 degrees along the rotation direction of the second impeller 6. From the position of the first reference line segment L01 around the rotation axis Ax, the angle of divergence of the second scroll 19 from the angle position advanced by 300 degrees to the angle position (position indicated by the broken line L22 in FIG. 4). A first scroll between an angular position advanced by 0 degrees along the rotation direction of the impeller 5 (a position indicated by a broken line L01 in FIG. 3) and an angular position advanced by a 300 degrees (a position indicated by a broken line L21 in FIG. 3). Although it is smaller than the divergence angle of 18, it is not limited to this. That is, 300 degrees advanced from the position of the second reference line segment L02 around the rotation axis Ax by 200 degrees along the rotational direction G of the second impeller 6 (position indicated by the broken line L12 in FIG. 4). The divergence angle of the second scroll 19 up to the angular position (the position indicated by the broken line L22 in FIG. 4) is the rotational direction G of the first impeller 5 around the rotation axis Ax from the position of the first reference line segment L01. If the angle is smaller than the divergence angle of the first scroll 18 between the angle position advanced by 200 degrees along the line (position indicated by the broken line L11 in FIG. 3) and the angle position advanced by 300 degrees (position indicated by the broken line L21 in FIG. 3). The relationship between the spread angles of the first scroll 18 and the second scroll 19 at other angular positions is arbitrary. For example, from the position of the second reference line segment L02, it has advanced by 200 degrees from the angular position (position indicated by the broken line L02 in FIG. 4) advanced by 0 degrees along the rotation direction G of the second impeller 6 around the rotation axis Ax. The divergence angle of the second scroll 19 up to the angular position (the position indicated by the broken line L12 in FIG. 4) is the rotational direction G of the first impeller 5 around the rotational axis Ax from the position of the first reference line segment L01. Even if it is equal to the divergence angle of the first scroll 18 from the angle position advanced by 0 degrees along the line (position indicated by the broken line L01 in FIG. 3) to the angle position advanced by 200 degrees (position indicated by the broken line L11 in FIG. 3) Good.

  However, as shown in FIGS. 3 and 4, an angular position (indicated by a broken line L <b> 12 in FIG. 4) advanced by 200 degrees in the rotation direction of the second impeller 6 around the rotation axis Ax from the position of the second reference line segment L <b> 02. The angle of divergence of the second scroll 19 (the angle of divergence in the range of the wrap angle of the second scroll 19 from 0 degrees to 200 degrees) between the position of the first reference line segment L01 and the rotation axis Ax. The divergence angle of the first scroll 18 between the angular position advanced by 200 degrees in the rotational direction G of the first impeller 5 (the position indicated by the broken line L11 in FIG. 3) (the winding angle of the first scroll 18 is 0 to 200 degrees). The pressure of the air blown out from the second discharge port 190 can be made higher than that of the air blown out from the first discharge port 180. .

  The first scroll 18 and the second scroll 19 do not have to be formed at a certain spread angle as long as the above-described spread angle conditions are satisfied.

  As can be seen from FIGS. 1 to 4, the width W2 of the plurality of blades 60 of the second impeller 6 is larger than the width W1 of the plurality of blades 50 of the first impeller 5. Further, as can be seen from FIGS. 3 and 4, the number of the plurality of blades 60 of the second impeller 6 is larger than the number of the plurality of blades 50 of the first impeller 5.

  Next, the operation of the vehicle air conditioner shown in FIGS.

  In the first operation mode of the vehicle air conditioner, the second opening 26 and the fourth opening 28 are opened, and the first opening 25 and the third opening 27 are closed. This state is not shown. In this case, the outside air introduced from the second opening 26 passes through the first passage 14 </ b> A outside the separation cylinder 14 to form a first air flow that flows into the blade row 50 </ b> A of the first impeller 5. The outside air introduced from the fourth opening 28 passes through the second passage 14 </ b> B inside the separation cylinder 14, and forms a second air flow that flows into the blade row 60 </ b> A of the second impeller 6. The first operation mode may be referred to as an outside air mode.

  In the second operation mode, the second opening 26 and the third opening 27 are opened, and the first opening 25 and the fourth opening 28 are closed. This state is shown in FIGS. In this case, the outside air FE introduced from the second opening 26 forms a first air flow that passes through the first passage 14A outside the separation cylinder 14 and flows into the blade row 50A of the first impeller 5. Further, the inside air FR introduced from the third opening 27 forms a second air flow that passes through the second passage 14B inside the separation cylinder 14 and flows into the blade row 60A of the second impeller 6. The second operation mode may be referred to as an inside / outside air two-layer flow mode.

  In the third operation mode, the first opening 25 and the third opening 27 are opened, and the second opening 26 and the fourth opening 28 are closed. This state is not shown. In this case, the inside air introduced from the first opening 25 forms a first air flow that passes through the first passage 14 </ b> A outside the separation cylinder 14 and flows into the blade row 50 </ b> A of the first impeller 5. Further, the inside air introduced from the third opening 27 forms a second air flow that passes through the second passage 14B inside the separation cylinder 14 and flows into the blade row 60A of the second impeller 6. The third operation mode may be referred to as an inside air mode.

  The second operation mode (internal / external air two-layer flow mode) is used, for example, when operation is performed in the differential foot mode or the bi-level mode. At this time, in order to provide the passenger with a comfortable environment of so-called chills, relatively low-temperature conditioned air flows from the defrost outlet of the passenger compartment to the front window of the vehicle or from the vent outlet (both not shown) of the passenger's upper body. A relatively hot conditioned air is blown out toward the passenger's feet from a foot outlet (not shown) of the passenger compartment.

  By the way, when the operation in the above-described bilevel mode is performed, the outside air FE flowing into the blade row 50 </ b> A of the first impeller 5 is supplied to the vent outlet through the first scroll 18. Further, the inside air FR that flows into the blade row 60 </ b> A of the second impeller 6 is supplied to the foot outlet through the second scroll 19. At this time, the temperature of the air supplied from the second scroll 19 is adjusted to be higher than that of the air supplied from the first scroll 18. Specifically, the rate at which the air heating heat exchanger (not shown) supplied from the second scroll 19 passes through the air heating heat exchanger supplied from the first scroll 18 It arrange | positions between the position of the 1st air mix door (not shown) arrange | positioned between the 1st scroll 18 and the vent blower outlet, and between the 2nd scroll 19 and the foot blower outlet so that it may become high compared with. The position of the second air mix door (not shown) is adjusted. As a result, the ventilation resistance of the ventilation path between the second scroll 19 and the foot outlet is higher than that of the ventilation path between the first scroll 18 and the vent outlet. There is a risk that it may be difficult to send air toward the foot outlet.

  However, if the expansion angle of the second scroll 19 is made smaller than the expansion angle of the first scroll 18 as in the above embodiment, the ventilation resistance of the air flow path between the second scroll 19 and the foot outlet is increased. However, a sufficient air volume can be supplied to the air flow path. In particular, it is 300 degrees from an angular position (position indicated by a broken line L12 in FIG. 4) advanced by 200 degrees along the rotation direction G of the second impeller 6 around the rotation axis Ax from the position of the second reference line segment L02. The divergence angle of the second scroll 19 up to the advanced angular position (the position indicated by the broken line L22 in FIG. 4) is the rotational direction of the first impeller 5 around the rotation axis Ax from the position of the first reference line segment L01. More than the divergence angle of the first scroll 18 from the angular position advanced by 200 degrees along G (position indicated by the broken line L11 in FIG. 3) to the angular position advanced by 300 degrees (position indicated by the broken line L21 in FIG. 3) If it is made small, the amount of air blown from the foot outlet can be secured sufficiently.

  Further, it is preferable that the width W2 of the plurality of blades 60 of the second impeller 6 is larger than the width W1 of the plurality of blades 50 of the first impeller 5. When the blade width is large, the ability to push air to the downstream side of the blower is improved. Thereby, even if the ventilation resistance of the ventilation path between the 2nd scroll 19 and a foot blower outlet becomes high, it can supply sufficient air volume to the said ventilation path.

  Further, it is preferable that the number of the plurality of blades 60 of the second impeller 6 is larger than the number of the plurality of blades 50 of the first impeller 5. When the number of blades is large, the ability to push air to the downstream side of the blower is improved. Thereby, even if the ventilation resistance of the ventilation path between the 2nd scroll 19 and a foot blower outlet becomes high, it can supply sufficient air volume to the said ventilation path.

  By the way, the configuration of the centrifugal blower for establishing the relationship that the expansion angle of the second scroll 19 is smaller than the expansion angle of the first scroll 18 between the above-described angular positions is as shown in FIGS. Is not limited.

  For example, the 1st impeller 5 and the 2nd impeller 6 may be formed separately, and the 1st scroll 18 and the 2nd scroll 19 may be spaced apart like the centrifugal blower 1A shown in FIG. In the example shown in FIG. 6, the first impeller 5 and the second impeller 6 are disposed on one side (the upper side in the axial direction) and the other side (the lower side in the axial direction) of the motor 13, respectively. The scroll 18 is located on one side in the axial direction and accommodates the first impeller 5, and the second scroll 19 is located on the other side in the axial direction and accommodates the second impeller 6. The first impeller 5 and the second impeller 6 each have an inner deflection member 9. The first suction port 22A of the first scroll 18 opens to one side in the axial direction, while the second suction port 22B of the second scroll 19 opens to the other side in the axial direction. In the example shown in FIG. 6, the first air flow and the second air flow are respectively supplied from the first suction port 22A of the first scroll 18 and the second suction port 22B of the second scroll 19 to the first impeller 5. It flows inwardly in the radial direction of the blade row 50A and radially inward of the blade row 60A of the second impeller 6.

  Also in this case, if the relationship that the spread angle of the second scroll 19 is smaller than the spread angle of the first scroll 18 between the above-described angular positions is established, the centrifugal fan 1 of the above-described embodiment is the same. The effect of can be obtained.

  Further, as in the centrifugal blower 1B shown in FIG. 7, if the spread angle of the second scroll 19 is smaller than the spread angle of the first scroll 18 between the above-mentioned angular positions, the rotation of the second scroll 19 in the range is performed. The dimension in the cross section orthogonal to the axis Ax may be larger than the dimension in the cross section orthogonal to the rotation axis Ax of the first scroll. In the example shown in FIG. 7, the first impeller 5 and the second impeller 6 are integrally formed. The first scroll 18 and the second scroll 19 are formed on both sides of the partition wall 20 in the axial direction by dividing the internal space of the integrally formed scroll housing 17 in the axial direction by the partition wall 20. Yes. The first scroll 18 is positioned on one side in the axial direction (the upper side in the axial direction), and the first suction port 22A is open on one side in the axial direction. On the other hand, the second scroll 19 is located on the other side in the axial direction (the lower side in the axial direction), and the second suction port 22B is opened on the other side in the axial direction.

  In the example shown in FIG. 7, the motor 13 is inserted into the second scroll 19 via the second suction port 22 </ b> B. The motor 13 extends to the inside of the blade row 50 </ b> A of the first impeller 5 through the radially inner side of the blade row 60 </ b> A of the second impeller 6. The rotating shaft 12 of the motor 13 is connected to the impellers 5 and 6 in an inner deflection member 9 formed integrally with the first impeller 5. In this case, the second air flow passes through a ring-shaped region outside the outer peripheral surface 131 of the motor 13 in the second suction port 22B of the second scroll 19 and is radially inward of the blade row 60A of the second impeller 6. Flow into. The ring-shaped region is made sufficiently large, and a region between the outer peripheral surface 131 of the motor 13 and the inner peripheral surface of the blade row 60A of the second impeller 6 and the inner peripheral surface of the second scroll 19 is sufficient. In order to increase the size, the dimension of the cross section orthogonal to the rotation axis Ax of the second scroll 19 is designed to be larger than the dimension of the cross section orthogonal to the rotation axis Ax of the first scroll 18.

  More specifically, as shown in FIG. 7, any angle advanced by an arbitrary angle in the rotation direction G of the second impeller 6 around the rotation axis Ax from the second reference line segment L02 between the above-described angular positions. The width D2 of the second scroll 19 in the meridional section of the second scroll 19 at the angular position is the same angle as described above in the rotation direction G of the first impeller 5 around the rotation axis Ax from the first reference line segment L01. It may be larger than the width D1 of the first scroll 18 in the meridional section of the first scroll 18 at the advanced angular position.

  Even in this case, if the relationship that the spread angle of the second scroll is smaller than the spread angle of the first scroll is established between the above-described angular positions, the centrifugal blower 1 of the above-described embodiment and Similar effects can be obtained.

DESCRIPTION OF SYMBOLS 1 Centrifugal blower 5 1st impeller 50 1st impeller blade | wing 6 2nd impeller 60 2nd impeller blade | wing 13 Motor 14 Separation pipe | tube 16 Outlet side edge part 17 Scroll housing 18 1st scroll 180 1st discharge port 19 Second scroll 190 Second discharge port 20 Partition wall 21 Air intake housing Ax Rotation axis

According to a preferred embodiment of the present invention, a centrifugal blower for a vehicle has a motor and a plurality of blades forming a circumferential blade row, and is rotated around a rotation axis extending in the axial direction by the motor. A first impeller that is driven to blow out air in a radially inner space of the blade row in a centrifugal direction, a first suction port that opens in the axial direction, and a first discharge port that opens in the circumferential direction. A first scroll for housing the first impeller, wherein air sucked from the first suction port by rotation of the first impeller is defrosted from the first discharge port and / or vented A first scroll that is fed to the air outlet, and a plurality of blades that form a circumferential blade row, and is driven to rotate about the rotation axis by the motor, and the air in the radially inner space of the blade row is centrifugally moved A second impeller that blows out toward the A second scroll that has a second suction port that opens in the axial direction and a second discharge port that opens in the circumferential direction, and houses the second impeller, wherein the second impeller rotates to rotate the second impeller. A second scroll for sending air sucked from the two suction ports to the foot outlet from the second discharge port, and in the cross section of the first scroll perpendicular to the rotation axis, the rotation axis and the first scroll An imaginary line segment connecting the center point of the tongue is defined as a first reference line segment, and the rotation axis and the center point of the tongue of the second scroll are connected in the cross section of the second scroll perpendicular to the rotation axis. When the imaginary line segment is the second reference line segment, it advances by 300 degrees from an angular position advanced by 200 degrees along the rotation direction of the second impeller from the position of the second reference line segment around the rotation axis. Between the angle position The spread angle of the second scroll is from the position of the first reference line segment to the angle position advanced by 300 degrees from the angular position advanced by 200 degrees along the rotation direction of the first impeller around the rotation axis. A centrifugal blower that is smaller than the spread angle of the first scroll in between is provided.

Claims (7)

A centrifugal blower (1, 1A, 1B) for a vehicle,
A motor (13);
A plurality of blades (50) that form a circumferential blade row (50A), and are driven to rotate about a rotation axis (Ax) extending in the axial direction by the motor (13), and the radius of the blade row (50A) A first impeller (5) that blows out air in a direction-inside space toward the centrifugal direction;
A first scroll (18) having a first suction port (22A) opening in the axial direction and a first discharge port (180) opening in the circumferential direction and accommodating the first impeller (5). The first scroll that sends out the air sucked from the first suction port (22A) to the defroster outlet and / or the vent outlet by the rotation of the first impeller (5). (18)
A plurality of blades (60) forming a circumferential blade row (60A), and driven to rotate about the rotation axis (Ax) by the motor (13) to be radially inward of the blade row (60A); A second impeller (6) for blowing out air in the space in the centrifugal direction;
The second scroll (19) has a second suction port (22B) that opens in the axial direction and a second discharge port (190) that opens in the circumferential direction, and houses the second impeller (6). A second scroll (19) for sending out air sucked from the second suction port (22B) by rotation of the second impeller (6) from the second discharge port (190) to the foot outlet;
In the cross section of the first scroll (18) orthogonal to the rotation axis (Ax), the virtual axis connecting the rotation axis (Ax) and the center point (18Tp) of the tongue (18T) of the first scroll (18). A line segment is defined as a first reference line segment (L01), and the rotation axis (Ax) and the tongue of the second scroll (19) in the cross section of the second scroll (19) orthogonal to the rotation axis (Ax). When the imaginary line segment connecting the center point (19Tp) of (19T) is defined as the second reference line segment (L02), from the position of the second reference line segment (L02) around the rotation axis (Ax) The divergence angle of the second scroll (19) between the angular position advanced by 200 degrees and the angular position advanced by 300 degrees along the rotation direction of the second impeller (6) is the first reference line segment ( L01) from the position of the rotation axis Ax) is smaller than the divergence angle of the first scroll (18) between the angular position advanced by 200 degrees and the angular position advanced by 300 degrees along the rotational direction of the first impeller (5), Centrifugal blower (1, 1A, 1B). The first impeller (5) and the second impeller (6) are integrally formed,
The first scroll (18) and the second scroll (19) are divided in the axial direction by dividing the internal space of the integrally formed scroll housing (17) by the partition wall (20). Formed on both sides of the partition wall (20),
The first scroll (18) is located on one side of the axial direction,
The first suction port (22A) opens to one side in the axial direction,
The second scroll (19) is located on the other side in the axial direction,
The second suction port (22B) opens to one side in the axial direction,
The internal space of the first scroll (18) and the internal space of the second scroll (19) communicate with each other via the second suction port (22B),
The centrifugal blower (1) further includes:
A separation tube (14) extending in the axial direction through a radially inner side of the first suction port (22A) and a radially inner side of the blade row (50A) of the first impeller (5), The flow of air sucked into the scroll housing (17) from the first suction port (22A) is passed through the first air flow passing outside the separation cylinder (14) and the inside of the separation cylinder (14). The first air flow is provided so as to be divided into a second air flow, and the first air flow is turned outward in the radial direction to guide the first scroll (18). The centrifugal blower (1) according to claim 1, comprising a separation cylinder (14) having an outlet side end (16) that turns in a direction and guides it to the second scroll (19). The first impeller (5) and the second impeller (6) are formed separately,
The first scroll (18) and the second scroll (19) are spaced apart from each other,
The first scroll (18) is located on one side of the axial direction,
The first suction port (22A) opens to one side in the axial direction,
The second scroll (19) is located on the other side in the axial direction,
The centrifugal blower (1A) according to claim 1, wherein the second suction port (22B) opens to the other side in the axial direction. The first impeller (5) and the second impeller (6) are integrally formed,
The first scroll (18) and the second scroll (19) are divided in the axial direction by dividing the internal space of the integrally formed scroll housing (17) by the partition wall (20). Formed on both sides of the partition wall (20),
The first scroll (18) is located on one side of the axial direction,
The first suction port (22A) opens to one side in the axial direction,
The second scroll (19) is located on the other side in the axial direction,
The centrifugal blower (1B) according to claim 1, wherein the second suction port (22B) opens to the other side in the axial direction.   From the position of the second reference line segment (L02) to the angular position advanced by 300 degrees from the angular position advanced by 0 degrees along the rotational direction of the second impeller (6) around the rotational axis (Ax) The divergence angle of the second scroll (19) is 0 along the rotation direction of the first impeller (5) around the rotation axis (Ax) from the position of the first reference line segment (L01). The centrifugal blower (1) according to any one of claims 1 to 4, wherein the centrifugal blower (1) is smaller than a spread angle of the first scroll (18) between an angular position advanced by 300 degrees and an angular position advanced by 300 degrees.   The width (W2) of the plurality of blades (60) of the second impeller (6) is larger than the width (W1) of the plurality of blades (50) of the first impeller (5). The centrifugal blower (1, 1A, 1B) according to any one of 1 to 5.   The number of the plurality of blades (60) of the second impeller (6) is greater than the number of the plurality of blades (50) of the first impeller (5). The centrifugal blower described in (1, 1A, 1B).

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