JP6685249B2 - Centrifugal blower - Google Patents

Description

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

  In the field of vehicle air conditioners, a two-layer flow type vehicle air conditioner is known. An air conditioner of this type comprises two air ducts, namely a first air duct and a second air duct, which are separated from each other, and a single centrifugal air blower for flowing air through these two air ducts. The first air passage mainly serves to supply conditioned air to the defroster outlet and the vent outlet, and the second air passage mainly serves to supply conditioned air to the foot outlet.

A two-layer flow type centrifugal blower has a scroll housing that accommodates an impeller, and a separation cylinder that is inserted into a suction port of the scroll housing and a space radially inside a blade row of the impeller (for example, Patent Document 1). See 1). The space of the scroll housing radially outside of the blade row of the impeller is divided into upper and lower parts by a partition plate (partition wall), and thereby the first air passage communicating with the first air passage and the second air passage communicating with the second air passage . An air passage is formed. The separation cylinder has a first air flow flowing through the first passage outside the separation cylinder, introduced into the upper half of the blade row, and then flowing into the first air passage , and flowing through the second passage inside the separation cylinder. Two air streams are provided so as to flow into the second air passage after being introduced into the lower half of the blade row.

  Since the installation space of the vehicle air conditioner is limited, there is a demand to reduce the radial size of the scroll housing of the centrifugal blower. Patent Document 2 describes a centrifugal blower having a so-called three-dimensional spreading scroll structure (3D scroll structure) in which both the radial size and the axial size of the scroll housing are increased with an increase in the winding angle. There is. However, the centrifugal blower described in Patent Document 2 is not a two-layer flow type. That is, Patent Documents 1 and 2 do not disclose a configuration for reducing the radial size of the scroll housing of the two-layer flow type centrifugal blower.

JP, 2004-132342, A JP-A-5-195995

  It is an object of the present invention to reduce the radial size of a scroll housing of a two-layer flow type centrifugal blower without sacrificing performance.

According to one embodiment of the present invention, a single-suction type centrifugal blower for a vehicle, which has a motor and a plurality of blades forming a row of blades arranged in a circumferential direction , and is rotated around a rotation axis by the motor. The impeller, which is driven and sucks the air sucked from the one end side in the axial direction into the radially inner space of the blade row toward the outer side in the radial direction, the internal space for accommodating the impeller, and one end side in the axial direction A scroll housing having a suction opening that opens in the interior and a discharge opening that opens in the circumferential direction, a region of the internal space of the scroll housing between the inner peripheral surface of the scroll housing and the outer peripheral surface of the impeller, and the discharge area. A partition wall that divides the internal space of the outlet in the axial direction to form a first air passage and a second air passage, and a radial direction inner side of the suction port and a radial inner side of the blade row of the impeller in the axial direction. Is a separation tube that extends to The flow of the air sucked into the scroll housing from the mouth is provided so as to be divided into a first air flow passing outside the separation cylinder and a second air flow passing inside the separation cylinder, and the first air flow is provided. A separation having an outlet end for diverting the flow radially outward and guiding it into the first air passage and diverting the second air flow radially outward and guiding it into the second air passage. A centrifugal blower including a cylinder is provided.
In this centrifugal blower, when the angle measured along the rotation direction of the impeller from the angular position of the tongue of the scroll housing is called the wrap angle, the meridional section of the scroll housing at the angular position corresponding to each wrap angle. The following relations hold when viewed in.
-The cross-sectional area of the first air passage and the cross-sectional area of the second air passage increase with an increase in the winding angle;
The maximum radial length of the first air passage and the maximum radial length of the second air passage increase with increasing winding angle;
-The axial length of the first air passage increases as the wrap angle increases,
-The axial position of the inner peripheral edge of the partition wall is the same regardless of the winding angle.

  According to the above-described embodiment of the present invention, the radial size of the scroll housing of the double-layer centrifugal fan can be reduced without sacrificing performance.

It is a longitudinal section including a meridional section of a centrifugal fan concerning one embodiment of the present invention. 2 is a schematic cross-sectional view of the centrifugal blower taken along the line II-II in FIG. 1. FIG. 3 is a schematic vertical cross-sectional view of the centrifugal blower taken along the line AA, the line BB, the line CC, the line DD, and the line EE in FIG. 2 in one embodiment of the centrifugal blower. It is an exploded perspective view showing the structure of a scroll housing. It is a longitudinal cross-sectional view showing a detailed structure of the scroll housing. FIG. 3 is a schematic vertical cross-sectional view of the centrifugal blower taken along the line AA, the line BB, the line CC, the line DD, and the line EE in FIG. 2 in another embodiment of the centrifugal blower. It is a schematic diagram showing an example of the composition by the side of the lower stream of the above-mentioned centrifugal blower of an air-conditioner for vehicles containing the above-mentioned centrifugal blower.

  An embodiment of the present invention will be described below with reference to the accompanying drawings.

  As shown in FIG. 1, the centrifugal blower 1 is a single-suction type centrifugal blower. The centrifugal blower 1 has an impeller 2. The impeller 2 has a plurality of blades 3 forming a blade row 3A arranged in the circumferential direction on the outer peripheral portion thereof. The impeller 2 is rotationally driven around a rotation axis Ax by a motor 13, and air sucked into the space inside the blade row of the impeller 2 from the axial upper side (the axial one end side) toward the radial outer side. Blow out.

  In this specification, for convenience of description, the direction of the rotation axis Ax is referred to as an axial direction or a vertical direction, and the upper side and the lower side of FIG. 1 are referred to as an “axial upper side” and an “axial lower side”, respectively. However, this does not mean that the direction of the rotation axis Ax is the same as the vertical direction when the air conditioner is actually installed in the vehicle. Further, in the present specification, unless otherwise specified, the radius direction of a circle drawn on a plane orthogonal to the rotation axis Ax centering on an arbitrary point on the rotation axis Ax is referred to as a radial direction, and The circumferential direction of a circle is called the circumferential direction or the circumferential direction. Further, "Fr" shown in FIG. 2 is a vehicle front, "Rr" is a vehicle rear, "R" is a vehicle right side, and "L" is a vehicle left side for convenience. However, this does not necessarily mean that the air blown out from the discharge port 170 of the centrifugal blower is directed to the right side in the vehicle left-right direction.

  The impeller 2 includes an inner deflection member 9 integrally formed with the impeller 2. The inner deflection member 9 is sometimes called a cone portion. The inner deflecting member 9 is a rotating body in a geometric sense, and has a side peripheral portion 10 and a disc-shaped central portion 11. At the central portion 11, the rotary shaft 12 of the motor 13 is connected to the impeller 2. In this example, the side peripheral portion 10 is curved so that the contour line in the meridional section of the outer peripheral surface of the side peripheral portion 10 becomes steeper as it approaches the central portion 11. In another example not shown, in the side peripheral portion 10, the contour line in the meridional cross section of the outer peripheral surface of the side peripheral portion 10 is not curved from the central portion 11 toward the blade row 3A (the cross section is linear). There is also.

  The impeller 2 is housed in the internal space of the scroll housing 17. The scroll housing 17 has a suction port 22 opening upward in the axial direction and a discharge port 170 (see FIG. 2). When the scroll housing 17 is viewed from the axial direction, the discharge port 170 extends substantially tangentially to the outer peripheral surface of the scroll housing 17. The outlet 170 is not visible in FIG.

The scroll housing 17 has a partition wall 20 extending inward in the radial direction from the outer peripheral wall 17A of the scroll housing 17. The partition wall 20 divides a region between the inner circumferential surface of the scroll housing 17 and the outer circumferential surface of the impeller 2 in the internal space of the scroll housing 17 in the axial direction (up and down) to divide the scroll housing 17 into An upper first air passage (upper scroll) 18 and a lower second air passage (lower scroll) 19 extending in the circumferential direction along the outer peripheral wall 17A are formed.

  The separation cylinder 14 is inserted into the scroll housing 17 through the suction port 22. The cross section of the upper portion 24 of the separation cylinder 14 is substantially rectangular. The cross section from the central portion 15 to the lower portion (end portion on the outlet side) 16 of the separation cylinder 14 is circular or substantially circular. The cross-sectional shape of the separation cylinder 14 smoothly changes from a rectangle to a circle as it approaches the central portion 15 from the upper portion 24. The lower portion 16 of the separation cylinder 14 has a flare shape whose diameter increases as it approaches the lower end.

  The separation cylinder 14 extends axially through a space radially inward of the suction port 22 to a space 4 radially inward of the blade row 3A of the impeller 2. The upper end opening of the separation cylinder 14 is located outside the scroll housing 17 (upper side in the axial direction than the suction port 22). The lower end of the separation cylinder 14 is circular and is located in the space 4 inside the blade row 3A of the impeller 2 in the radial direction.

  The separation cylinder 14 allows the flow of the air sucked into the scroll housing 17 to be a first air flow passing through the first passage 14A outside the separation cylinder 14 and a second air passage passing through the second passage 14B inside the separation cylinder 14. Split with air flow. The first air flow passes through a ring-shaped region outside the outer peripheral surface of the separation cylinder 14 of the suction port 22 of the scroll housing 17, and passes through the upper half portion 5 of the blade row of the impeller 2 (a portion near the suction port 22). Flow into. The second airflow enters the inside of the separation cylinder 14 from the upper end of the separation cylinder 14 and flows into the lower half portion 6 of the blade row of the impeller 2 (the portion far from the suction port 22). Therefore, the ring-shaped region of the suction port 22 of the scroll housing 17 outside the outer peripheral surface of the separation cylinder 14 is the first suction port of the scroll housing 17, and the upper end opening of the separation cylinder 14 is the second suction port of the scroll housing 17. Can also be considered.

  The air intake part of the air conditioner has a housing 21. The housing 21 will be referred to as an “air intake housing” to distinguish it from the scroll housing 17. The scroll housing 17 and the air intake housing 21 may be integrally molded, or may be separately manufactured and then connected by a method such as screwing, bonding, or fitting. The scroll housing 17 and the air intake housing 21 form part of an air conditioner casing.

  The air intake housing 21 has a first opening 25, a second opening 26, a third opening 27, and a fourth opening 28. Through the first opening 25 and the third opening 27, the inside air (air inside the vehicle) can be introduced into the internal space 23 of the air intake housing 21 from the vehicle interior space 29 (details not shown). Further, through the second opening 26 and the fourth opening 28, into the internal space 23 of the air intake housing 21, from the outlet 30 (details not shown) of the outside air introduction passage provided in the vehicle, outside air (the outside of the vehicle). The air taken in from) can be introduced.

  By rotating the door 31 around the rotation shaft 31A, the inflow of air (inside air) from the first opening 25 into the air intake housing 21 can be permitted or blocked. By rotating the door 32 around the rotation axis 32A, the inflow of air (outside air) from the second opening 26 into the air intake housing 21 can be allowed or blocked. By rotating the switching door 33 around the rotation shaft 33A to switch the position, air (inside air or outside air) is introduced into the air intake housing 21 through either one of the third opening 27 and the fourth opening 28. Can be flowed in.

  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 arranged and the upper end of the separation cylinder 14, dust and particles in the air are contained in the air intake housing 21. A filter 35 is provided for removing contaminants such as. The filter 35 preferably consists of a single filter element.

  Although not clearly shown in FIG. 1, the upper end portion of the separation cylinder 14 is expanded in the vertical direction of the paper surface of FIG. 1, and is substantially rectangular in a plan view as described above. The two short sides of this rectangle are connected to the wall of the air intake housing 21 that faces them.

  Next, the operation of the vehicle air conditioner including the above-mentioned centrifugal blower will be briefly described.

  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 forms the first air flow that passes through the first passage 14A outside the separation cylinder 14 and flows into the upper half portion 5 of the blade row 3A of the impeller 2. Further, the outside air introduced from the fourth opening 28 forms a second airflow that passes through the second passage 14B inside the separation cylinder 14 and flows into the lower half portion 6 of the blade row of the impeller 2. The first operation mode is sometimes called the 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 AE 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 upper half portion 5 of the blade row 3A of the impeller 2. . In addition, the inside air AR introduced from the third opening 27 forms a second air flow that flows through the second passage 14B inside the separation cylinder 14 and flows into the lower half portion 6 of the blade row 3A of the impeller 2. The second operation mode is sometimes called 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 internal air introduced from the first opening 25 forms a first air flow that passes through the first passage 14A outside the separation cylinder 14 and flows into the upper half portion 5 of the blade row 3A of the impeller 2. Further, the inside air introduced from the third opening 27 forms a second airflow that passes through the second passage 14B inside the separation cylinder 14 and flows into the lower half portion 6 of the blade row 3A of the impeller 2. The third operation mode is sometimes called the inside air mode.

  The second operation mode (internal / external air two-layer flow mode) is used, for example, when operating in the bilevel mode. At this time, in order to provide a passenger with a comfortable environment of so-called cold-headed foot heat, relatively low-temperature outside air AE is blown from the vent outlet (not shown) of the passenger compartment toward the upper body of the passenger, and relatively high-temperature inside air AR Is blown toward the feet of passengers from a foot outlet (not shown) in the passenger compartment (this point will be described later with reference to FIG. 7). The second operation mode (internal / external air two-layer flow mode) is a heating operation that quickly warms the interior of the vehicle while preventing the windshield from fogging when the interior of the vehicle is cold, particularly during winter or when the temperature is relatively low. Also used when doing.

  Next, the configuration of the scroll housing 17 will be described in more detail with reference to FIGS.

  As shown in FIG. 2, the scroll housing 17 has a tongue portion 17t. In FIG. 2, a straight line connecting the rotation axis Ax of the impeller 2 (not shown in FIG. 2 for simplification of the drawing) and the tongue portion 17t is called a reference straight line, and the angular position of this reference straight line is An angle (θ) measured in the rotation direction of the impeller 2 (clockwise direction in FIG. 2) as 0 (zero) degree is called a winding angle.

  (A), (B), (C), (D), and (E) of FIG. 3 are AA line, BB line, CC line, DD line, and EE line in FIG. A schematic longitudinal cross-sectional view (meridional cross-sectional view) of the centrifugal blower taken along the line, showing the scroll housing 17, the impeller 2 adjacent to the scroll housing 17, and the separating cylinder 14 together. 3A is near the tongue portion 17, the winding angle θ is the smallest, and the winding angle θ increases in the order of (B), (C), (D), and (E).

  As is clear from FIG. 3, the cross-sectional area of the first air passage 18 and the cross-sectional area of the second air passage 19 increase as the winding angle θ increases. Further, as the winding angle θ increases, the maximum radial length of the first air passage 18 and the maximum radial length of the second air passage 19 increase. Further, as the winding angle θ increases, the axial length of the first air passage 18 (the length measured in the direction of the rotation axis Ax of the impeller) increases, and the axial length of the second air passage 19 also increases. is doing.

  The axial position of the inner peripheral edge 20E (1711) of the partition wall 20 (the position with respect to the direction of the rotation axis Ax) is constant (same) regardless of the winding angle θ. At the axial position of the inner peripheral edge 20E (1711), the air flowing outside the separation cylinder 14 is guided to the first air passage 18, and the air flowing inside the separation cylinder 14 is the second air passage. Since it is determined in relation to the lower end of the separation cylinder 14 so as to be guided to the air passage 19, it does not change as the winding angle θ increases.

  Preferably, the radial position (distance from the rotation axis Ax) of the inner peripheral edge 20E (1711) of the partition wall 20 is also constant (same) regardless of the winding angle θ.

  As described above, as the winding angle θ increases, not only does the maximum radial length of the first air passage 18 and the maximum radial length of the second air passage 19 increase as in a general scroll housing, By increasing the axial length of the first air passage 18 and the axial length of the second air passage 19 as well, the cross-sectional area of the first air passage 18 and the second air passage 19 with the increase of the winding angle θ A desired increase rate (which is one of the factors that determine scroll performance) while suppressing an increase in the radial lengths of the first air passage 18 and the second air passage 19. it can.

Here, the definitions of the above terms will be described with reference to FIG.
-The cross-sectional area of the first air passage 18 (second air passage 19) means the axial direction through the tip 1711 (20E) of the partition wall 20 in the first air passage 18 (second air passage 19) ( It means the area of the region radially outside of the line Lt extending in the direction of the axis of rotation Ax of the impeller.
-The maximum radial length of the first air passage 18 (second air passage 19) means the maximum value of the radial lengths 18R, 19R from the line Lt to the inner surface of the outer peripheral wall 17A of the scroll housing 17.
The axial length of the first air passage 18 (second air passage 19) means the cross-sectional area of the first air passage 18 (second air passage 19) defined above and the first air passage 18 (second It means a value divided by the maximum radial length of the air passage 19).

By the way, as is well known, as shown in FIG. 7, a two-layer flow type air conditioner for a vehicle has a first air passage downstream of the first air passage 18 and the second air passage 19 of the scroll housing 17 and connected to them. It has a passage 112A and a second air passage 112B. The air flowing through the first air passage 112A is mainly blown into the vehicle interior from the defroster outlet 132 and the vent outlet 134, and the air flowing through the second air passage is mainly blown into the vehicle interior from the foot air outlet 136. Note that reference numerals 132D, 134D, and 136D are doors provided at the defroster outlet 132, the vent outlet 134, and the foot outlet 136.

A cooling heat exchanger 126 (also called “evaporator”) and a heating heat exchanger 128 (also called “heater core”) are provided in the first air passage 112A and the second air passage 112B. All of the air flowing through the first air passage 112A and the second air passage 112B passes through the cooling heat exchanger 126. A first temperature control door 130A and a second temperature control door 130B are provided in the first air passage and the second air passage between the cooling heat exchanger 126 and the heating heat exchanger 128, respectively. In each of the air passages 112A and 112B, the flow rate of air passing through the heating heat exchanger 128 and the air bypassing the heating heat exchanger according to the angular positions φA and φB of the temperature control doors 130A and 130B. Of the air flow rate (the flow rate of the air passing through the bypass paths 129A and 129B) is determined.

When the vehicle air conditioner is operated in the above-described bilevel mode (operating mode in which relatively cool air is blown from the vent outlet 134 and relatively warm air is blown from the foot outlet 136), as shown in FIG. In the first air passage 112A, a relatively large portion of air bypasses the heating heat exchanger 128, and in the second air passage 112B, a relatively large portion of air passes through the heating heat exchanger 128. Then, the first temperature control door 130A and the second temperature control door 130B are adjusted. At this time, the ventilation resistance in the second ventilation passage 112B becomes larger than the ventilation resistance in the first ventilation passage 112A by the difference in the ventilation resistance of the heating heat exchanger 128. Therefore, in the bi-level mode, there is a tendency that the air volume at the feet tends to be insufficient, and this tendency is that the difference between the control target temperature and the actual temperature is large and most of the air in the second air passage 112B is heated. It becomes noticeable when flowing through the exchanger. (In the vehicle air conditioner, the detour ratio of the heating heat exchanger 128 in the second air passage 112B is higher than the detour ratio of the heating heat exchanger 128 in the first air passage 112A regardless of the operation mode. It will never happen.)

As is well known in the technical field of centrifugal blowers, the increase rate of the cross-sectional area of the scroll with the increase of the winding angle θ (in a general scroll that is not a 3D scroll, it may be expressed by a parameter called “spread angle”). Many) have a great impact on the performance of centrifugal blowers. When the increase rate is large, the low pressure large flow rate tends to occur, and when the increase rate is small, the high pressure small flow rate tends to occur. In order to solve or alleviate the above problem in the bi-level mode, the increase rate of the cross-sectional area of the scroll accompanying the increase of the wrap angle is kept low in the second air passage 19 that mainly sends the air toward the foot outlet 136. Can be considered.

  In this case, the increase rate of the axial length of the second air passage 19 with the increase of the winding angle θ is made smaller than the increase rate of the axial length of the first air passage 18 with the increase of the winding angle θ. be able to.

  Alternatively, the axial length of the second air passage 19 may be constant regardless of the winding angle θ. That is, the cross-sectional area of the second air passage 19 may be increased as the winding angle θ is increased only by increasing the maximum radial length of the second air passage 19 as the winding angle θ is increased. .

  Check the definition of the term again. The axial length of the first air passage 18 (second air passage 19) means the cross-sectional area of the first air passage 18 (second air passage 19) defined above by the definition of the first air passage 18 (second air passage 19). It means the value divided by the maximum radial length of the passage 19). Under this definition, some of the first air passages 18 (second air passages) (second air passages 18) capable of increasing the axial length of the first air passages 18 (second air passages 19) as the winding angle θ increases. A configuration of the passage 19) is conceivable.

  For the reasons described above, the axial position of the inner peripheral edge 20E (1711) of the partition wall 20 should not be changed as the winding angle θ increases. Therefore, as a method of increasing the axial length of the first air passage 18 with the increase of the winding angle θ, a partition wall other than the inner peripheral edge 20E (1711) when viewed in the meridional section of the scroll housing 17 is used. It is conceivable to change the axial position of 20 according to the winding angle θ.

  Specifically, as shown in FIGS. 3 and 5, the surface 20C (1713) of the partition wall 20 (1712) facing the first air passage 18 is separated from the inner peripheral edge 20E (1711) of the partition wall 20. The partition wall 20 can be configured to have a curved portion such that the axial distance from the suction port 22 of the scroll housing 17 increases as the distance increases and then decreases.

  Alternatively, as shown in FIG. 6, as the surface 20C (1713) of the partition wall 20 (1712) facing the first air passage 18 moves away from the inner peripheral edge 20E (1711) of the partition wall 20, the scroll housing 17 The partition wall 20 can be configured to have a portion (first portion) that is inclined so that the axial distance from the suction port 22 becomes large. The portion of the partition wall 20 radially outside the inclined portion (first portion) may extend in the horizontal direction (direction orthogonal to the rotation axis Ax) as shown in FIG. It may be a portion (second portion) that is gently inclined rather than one portion (inclined portion).

  3, 5 and 6, the surface 20C (1713) of the partition wall 20 (1712) facing the first air passage 18 is an inclined surface or a curved surface that becomes lower as the distance from the separation cylinder 14 or the impeller 2 increases. Has become. This means that the outlet-side end portion 16 of the separation cylinder 14 causes a horizontal direction (radial direction outward) to be diverted (however, it is not completely diverted to the horizontal direction, and has an axially downward velocity component). It is preferable for allowing the first air flow passing through the impeller 2 to smoothly flow into the first air passage 18.

  Further, as shown in FIGS. 3, 5 and 6, in order to increase the axial length of the second air passage 19 as the winding angle θ increases, the partition wall 20 is faced to the second air passage 19 as well. It is possible to change the axial position of the wall body (bottom wall body) 17B (1733) of the scroll housing 17 opposed to the position according to the winding angle θ. In this case, it is preferable that the portion of the wall 17B (1733) that is on the inner side in the radial direction be an inclined surface or a curved surface that becomes lower as the distance from the impeller 2 increases.

  Next, an advantageous configuration example of the scroll housing 17 for forming the scroll housing 17 having the partition wall 20 having the above-described shape will be described with reference to FIGS. 4 and 5.

  The scroll housing 17 is configured by combining at least three members separately manufactured by a resin injection molding technique. Specifically, the scroll housing 17 includes a first member 171 including a partition wall 20, a second member 172 including a portion of the scroll housing 17 closer to the suction port 22 than the partition wall 20, and a scroll member of the scroll housing 17. It is configured by combining with a third member 173 including a portion farther from the suction port 22 than the partition wall 20.

  A receiving groove 1721 is formed on a surface of the peripheral portion of the second member 172 facing the first member 171, and a protrusion 1716 that fits into the receiving groove of the second member 172 is formed on the peripheral portion 1715 of the first member 171. Are formed. In addition, a receiving groove 1731 is formed on a surface of the peripheral portion of the third member 173 facing the first member 171, and a protrusion that fits into the receiving groove 1731 of the third member 173 is formed on the peripheral portion 1715 of the first member 171. 1717 is formed. A receiving groove may be formed in the first member 171, and a protrusion may be formed in the second member 172 and the third member 173.

  Plural (four in this example) screw receiving bosses 1722 and 1732 are provided on the peripheral portions of the second member 172 and the third member 173, respectively. With the protrusions 1716, 1717 of the first member 171 fitted in the corresponding receiving grooves 1721 of the second member 172 and the receiving groove 1731 of the third member 173, screws that are fastening members at the respective screw receiving bosses 1722, 1723. The second member 172 and the third member 173 are fastened using 174. Accordingly, the first member 171 is held by the second member 172 and the third member 173 while being sandwiched by the second member 172 and the third member 173 that are fastened to each other.

  In addition, in FIG. 4, a member indicated by reference numeral 1725 is a screw receiving boss for fixing the air intake housing 21 to the scroll housing 17.

  By adopting the above configuration, the degree of freedom in shape of the partition wall 20 (1712) is dramatically improved. That is, since the first member 171 including the partition wall 20 (1712) has a planar shape as a whole, the sectional shape of the partition wall 20 (1712) is considered from the viewpoint of the mold manufacturing technology for resin injection molding. As described above, it is very easy to give the partition wall 20 (1712) an inclination and a curve in order to change the angle according to the winding angle θ. Therefore, the shape of the lower partition wall 20 can be easily realized.

  Preferably, as shown in FIGS. 3 and 6, the radial position of the outer peripheral wall 17A of the scroll housing 17 corresponding to the first air passage 18 is set to the second air passage 19 regardless of the value of the winding angle θ. It is the same as the corresponding radial position of the outer peripheral wall 17A of the scroll housing 17. With this configuration, the scroll housing 17 can be easily manufactured. Such a configuration is particularly advantageous in adopting the structure shown in FIG.

1 Centrifugal Blower 2 Impeller Ax Rotational Axis 3 Blade 3A Circumferential Blade Row 13 Motor 14 Separation Cylinder 17 Scroll Housing 17A Scroll Housing Outer Wall 17t Scroll Housing Tongue 17B, 1733 Scroll Housing Wall 171, 172, 173 Scroll First to third members of housing 1721, 1731 Receiving groove 1715 Peripheral part of first member 1716, 1717 Projection 18 First air passage 19 Second air passage 20, 1712 Partition wall 20C, 1713 Partition wall surface 20E, 1711 Partition Inner edge of wall 22 Suction port of scroll housing θ Wrap angle

Claims (12)

A single suction centrifugal fan (1) for a vehicle, comprising:
A motor (13),
It has a plurality of blades (3) forming a blade row (3A) lined up in the circumferential direction, and is rotationally driven around a rotation axis (Ax) by the motor, and the blade row (3A) is from one end side in the axial direction. An impeller (2) that blows out the air sucked into the radially inner space of the
A scroll housing (17) having an internal space for accommodating the impeller, a suction port (22) opening at one end in the axial direction, and a discharge port (170) opening in the circumferential direction;
Of the internal space of the scroll housing (17), the region between the inner peripheral surface of the scroll housing (17) and the outer peripheral surface of the impeller (2), and the internal space of the discharge port (170). A partition wall (20) which is divided in the axial direction to form a first air passage (18) and a second air passage (19),
A separation cylinder (14) extending in the axial direction through a radial inner side of the suction port and a radial inner side of the blade row of the impeller (2), the scroll housing (14) extending from the suction port (22). 17) is provided so as to divide the flow of air sucked into the inside into a first air flow passing through the outside of the separation cylinder and a second air flow passing through the inside of the separation cylinder, and the first air flow An outlet side for diverting a flow radially outward to guide it to the first air passage (18) and diverting a second air flow radially outward to guide it to the second air passage (19). A separation tube (14) having an end (16),
Equipped with
When the angle measured from the angular position of the tongue portion (17t) of the scroll housing (17) along the rotation direction of the impeller (2) is called a winding angle (θ), it corresponds to each winding angle. When viewed in the meridional section of the scroll housing (17) in the angular position, the following relationship:
The cross-sectional area of the first air passage (18) and the cross-sectional area of the second air passage (19) increase with an increase in the winding angle;
The maximum radial length (18R) of the first air passage (18) and the maximum radial length (19R) of the second air passage (19) increase as the winding angle increases;
The axial length of the first air passage (18) increases as the winding angle increases, and
Regardless of the winding angle, it is established that the axial position of the inner peripheral edge (20E, 1711) of the partition wall (20) is the same ,
By changing the axial position of the partition wall (20) other than the inner peripheral edge (20E, 1711) when viewed in a meridional section of the scroll housing (17) according to the winding angle (θ). A centrifugal blower , wherein the axial length of the first air passage (18) is increased with an increase in the winding angle .   The centrifugal blower according to claim 1, wherein the axial length of the second air passage (19) increases as the winding angle (θ) increases.   The increase rate of the axial length of the second air passage (19) with the increase of the winding angle (θ) is the axial length of the first air passage (18) with the increase of the winding angle (θ). The centrifugal blower according to claim 2, which has a smaller rate of increase in height. The axial position of the wall body (17B, 1733) of the scroll housing (17) facing the second air passage (19) and facing the partition wall (20) is changed according to the winding angle (θ). by, and the axial length of the second air passage (19) is increased with the increase of the winding angle, the centrifugal blower according to claim 1, wherein. The surface (20C, 1713) of the partition wall (20) facing the first air passage (18) moves away from the inner peripheral edge (1711) of the partition wall (20), and the suction port (22). The centrifugal blower according to any one of claims 1 to 4 , wherein the centrifugal blower has a portion that is inclined so as to increase an axial distance from the. The surface (20C, 1713) of the partition wall (20) facing the first air passage (18) is axial from the suction port (22) as it goes away from the inner peripheral edge of the partition wall (20). The centrifugal blower according to any one of claims 1 to 4 , having a curved portion such that the directional distance increases and then decreases. Regardless of the value of the wrap angle (θ), the radial position of the outer peripheral wall (17A) of the scroll housing (17) corresponding to the first air passage (18) is in the second air passage (19). Centrifugal blower according to any one of claims 1 to 6 , which is the same as the radial position of the outer peripheral wall (17A) of the corresponding scroll housing (17). A single suction centrifugal fan (1) for a vehicle, comprising:
A motor (13),
It has a plurality of blades (3) forming a blade row (3A) lined up in the circumferential direction, and is rotationally driven around a rotation axis (Ax) by the motor, and the blade row (3A) is from one end side in the axial direction. An impeller (2) that blows out the air sucked into the radially inner space of the
A scroll housing (17) having an internal space for accommodating the impeller, a suction port (22) opening at one end in the axial direction, and a discharge port (170) opening in the circumferential direction;
Of the internal space of the scroll housing (17), the region between the inner peripheral surface of the scroll housing (17) and the outer peripheral surface of the impeller (2), and the internal space of the discharge port (170). A partition wall (20) which is divided in the axial direction to form a first air passage (18) and a second air passage (19),
A separation cylinder (14) extending in the axial direction through a radial inner side of the suction port and a radial inner side of the blade row of the impeller (2), the scroll housing (14) extending from the suction port (22). 17) is provided so as to divide the flow of air sucked into the inside into a first air flow passing through the outside of the separation cylinder and a second air flow passing through the inside of the separation cylinder, and the first air flow An outlet side for diverting a flow radially outward to guide it to the first air passage (18) and diverting a second air flow radially outward to guide it to the second air passage (19). A separation tube (14) having an end (16),
Equipped with
When the angle measured from the angular position of the tongue portion (17t) of the scroll housing (17) along the rotation direction of the impeller (2) is called a winding angle (θ), it corresponds to each winding angle. When viewed in the meridional section of the scroll housing (17) in the angular position, the following relationship:
The cross-sectional area of the first air passage (18) and the cross-sectional area of the second air passage (19) increase with an increase in the winding angle;
The maximum radial length (18R) of the first air passage (18) and the maximum radial length (19R) of the second air passage (19) increase as the winding angle increases;
The axial length of the first air passage (18) increases as the winding angle increases, and
Regardless of the winding angle, it is established that the axial position of the inner peripheral edge (20E, 1711) of the partition wall (20) is the same ,
The scroll housing (17) is configured by combining at least three members manufactured separately, and the at least three members include a first member (171) including the partition wall (20), A second member (172) including a portion of the scroll housing (17) closer to the suction port (22) than the partition wall (20), and the partition wall (20) of the scroll housing (17). ) And a third member (173) including a portion farther from the suction port (22) than the suction port (22), and increasing the axial length of the first air passage (18) can increase the partition wall ( Centrifugal blower, characterized in that the cross-sectional shape of (20, 1712) is changed according to the winding angle (θ) . A fastening member (174) for fastening the second member (172) and the third member (173) is further provided, and the first member (171) is configured by the second member and the third member fastened to each other. The centrifugal blower according to claim 8 , which is held by the second member and the third member by being sandwiched. A receiving groove (1721) or a protrusion is formed on a surface of the second member (172) facing the first member (171), and the second groove is formed on the peripheral edge of the first member (171). A protrusion (1716) or a receiving groove that fits into the receiving groove or the protrusion of the member (172) is formed, and is received on a surface of the peripheral portion of the third member (173) facing the first member (171). A groove (1731) or a protrusion is formed, and a projection (1717) or a receiving groove that fits into the receiving groove or the protrusion of the third member (173) is formed on the peripheral edge portion of the first member (171). The centrifugal blower according to claim 9 . A single suction centrifugal fan (1) for a vehicle, comprising:
A motor (13),
It has a plurality of blades (3) forming a blade row (3A) lined up in the circumferential direction, and is rotationally driven around a rotation axis (Ax) by the motor, and the blade row (3A) is from one end side in the axial direction. An impeller (2) that blows out the air sucked into the radially inner space of the
A scroll housing (17) having an internal space for accommodating the impeller, a suction port (22) opening at one end in the axial direction, and a discharge port (170) opening in the circumferential direction;
Of the internal space of the scroll housing (17), the region between the inner peripheral surface of the scroll housing (17) and the outer peripheral surface of the impeller (2), and the internal space of the discharge port (170). A partition wall (20) which is divided in the axial direction to form a first air passage (18) and a second air passage (19),
A separation cylinder (14) extending in the axial direction through a radial inner side of the suction port and a radial inner side of the blade row of the impeller (2), the scroll housing (14) extending from the suction port (22). 17) is provided so as to divide the flow of air sucked into the inside into a first air flow passing through the outside of the separation cylinder and a second air flow passing through the inside of the separation cylinder, and the first air flow An outlet side for diverting a flow radially outward to guide it to the first air passage (18) and diverting a second air flow radially outward to guide it to the second air passage (19). A separation tube (14) having an end (16),
Equipped with
When the angle measured from the angular position of the tongue portion (17t) of the scroll housing (17) along the rotation direction of the impeller (2) is called a winding angle (θ), it corresponds to each winding angle. When viewed in the meridional section of the scroll housing (17) in the angular position, the following relationship:
The cross-sectional area of the first air passage (18) and the cross-sectional area of the second air passage (19) increase with an increase in the winding angle;
The maximum radial length (18R) of the first air passage (18) and the maximum radial length (19R) of the second air passage (19) increase as the winding angle increases;
The axial length of the first air passage (18) increases as the winding angle increases, and
Regardless of the winding angle, it is established that the axial position of the inner peripheral edge (20E, 1711) of the partition wall (20) is the same ,
As the winding angle (θ) increases, the axial length of the second air passage (19) also increases,
The increase rate of the axial length of the second air passage (19) with the increase of the winding angle (θ) is the axial length of the first air passage (18) with the increase of the winding angle (θ). Centrifugal blower characterized by being smaller than the rate of increase in height. A single suction centrifugal fan (1) for a vehicle, comprising:
A motor (13),
It has a plurality of blades (3) forming a blade row (3A) lined up in the circumferential direction, and is rotationally driven around a rotation axis (Ax) by the motor, and the blade row (3A) is from one end side in the axial direction. An impeller (2) that blows out the air sucked into the radially inner space of the
A scroll housing (17) having an internal space for accommodating the impeller, a suction port (22) opening at one end in the axial direction, and a discharge port (170) opening in the circumferential direction;
Of the internal space of the scroll housing (17), the region between the inner peripheral surface of the scroll housing (17) and the outer peripheral surface of the impeller (2), and the internal space of the discharge port (170). A partition wall (20) which is divided in the axial direction to form a first air passage (18) and a second air passage (19),
A separation cylinder (14) extending in the axial direction through a radial inner side of the suction port and a radial inner side of the blade row of the impeller (2), the scroll housing (14) extending from the suction port (22). 17) is provided so as to divide the flow of air sucked into the inside into a first air flow passing through the outside of the separation cylinder and a second air flow passing through the inside of the separation cylinder, and the first air flow An outlet side for diverting a flow radially outward to guide it to the first air passage (18) and diverting a second air flow radially outward to guide it to the second air passage (19). A separation tube (14) having an end (16),
Equipped with
When the angle measured from the angular position of the tongue portion (17t) of the scroll housing (17) along the rotation direction of the impeller (2) is called a winding angle (θ), it corresponds to each winding angle. When viewed in the meridional section of the scroll housing (17) in the angular position, the following relationship:
The cross-sectional area of the first air passage (18) and the cross-sectional area of the second air passage (19) increase with an increase in the winding angle;
The maximum radial length (18R) of the first air passage (18) and the maximum radial length (19R) of the second air passage (19) increase as the winding angle increases;
The axial length of the first air passage (18) increases as the winding angle increases, and
Regardless of the winding angle, it is established that the axial position of the inner peripheral edge (20E, 1711) of the partition wall (20) is the same ,
The surface (20C, 1713) of the partition wall (20) facing the first air passage (18) is axial from the suction port (22) as it goes away from the inner peripheral edge of the partition wall (20). A centrifugal blower having a curved portion such that the directional distance increases and then decreases .

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