JP7360823B2 - air conditioner - Google Patents

Description

The present invention relates to an air conditioner.

As a cross-flow fan used in an air conditioner, for example, the technique described in Patent Document 1 is known. That is, Patent Document 1 discloses a cross-flow fan that includes a cross-flow fan having an extension part extending from both longitudinal ends of the air outlet in the rotational axis direction, and a collision wall that causes the airflow from the extension part to collide with itself. The harmonizer is described.

JP2012-255628A

In the technology described in Patent Document 1, the above-mentioned collision wall is provided and the stagnation pressure of the air near the collision wall is higher than atmospheric pressure, thereby preventing reverse suction (backflow of air) in the indoor unit. It is prevented. Furthermore, in the technology described in Patent Document 1, in a cross-flow fan, the blade shape of the extension part facing the collision wall is made to be different from the blade shape of the part facing the air outlet. The stagnation pressure of the air near the walls is moderately suppressed to reduce power consumption.

As described above, in the technique described in Patent Document 1, the blades and the collision wall of the cross-flow fan are configured based on the stagnation pressure outside the cross-flow fan (near the collision wall). However, the technique described in Patent Document 1 does not focus on the airflow inside the cross-flow fan, and therefore there is room to further suppress noise caused by unstable airflow.

Therefore, an object of the present invention is to provide an air conditioner that suppresses the noise of a once-through fan.

In order to solve the above problem, an air conditioner according to the present invention includes: a plurality of blades arranged at predetermined intervals in the circumferential direction; a plurality of partition plates that partition the plurality of blades in the axial direction; A cross-flow fan having a pair of end plates installed at both ends in the axial direction of the blade, and a fan motor as a driving source, and a heat exchanger installed near the cross-flow fan, Among the end plates, the end plate installed at one end in the axial direction of the once-through fan includes a boss portion on which a motor shaft of the fan motor is installed, and from a predetermined position axially inner than the boss portion, The inner circumferential angle of the blade in a first predetermined range up to the end plate including the boss portion is smaller than the inner circumferential angle of the blade further axially inward than the first predetermined range, and The ratio of the diameter of the boss portion to the diameter is 0.07 or more and 0.13 or less, and the inner peripheral angle of the blade in the first predetermined range is 70° or more and 90° or less. I decided to do something .

Further, the air conditioner according to the present invention includes a once-through fan including a plurality of fan blocks connected in the axial direction via a partition plate, a heat exchanger installed near the once-through fan, and the once-through fan and a housing base that accommodates the heat exchanger; each of the plurality of fan blocks has a plurality of blades arranged at predetermined intervals in the circumferential direction; An end plate having a boss portion or a shaft portion is installed at the end in the axial direction, and the inner peripheral angle of the blade of the fan block whose end portion is partitioned by the end plate among the plurality of fan blocks is The casing base has a collision wall that causes air blown from the cross-flow fan to collide with itself in an axially inner range of the boss portion. I decided not to . Note that other details will be explained in the embodiment.

According to the present invention, it is possible to provide an air conditioner that suppresses noise from a cross-flow fan.

1 is a configuration diagram of an air conditioner according to an embodiment of the present invention. 1 is a schematic vertical sectional view of an indoor unit included in an air conditioner according to an embodiment of the present invention. 1 is a front view including a cross-flow fan included in an air conditioner according to an embodiment of the present invention. FIG. 4 is an explanatory diagram illustrating the air conditioner according to the embodiment of the present invention, in which the blades in the II-II section of FIG. 3 and the blades in the III-III section of FIG. 3 are superimposed. FIG. 2 is a partially enlarged view schematically showing the relative flow of air inside the once-through fan in the cross section III-III during air conditioning operation in the air conditioner according to the embodiment of the present invention. FIG. 7 is an explanatory diagram schematically showing the relative flow of air inside a once-through fan in cross section II-II during air conditioning operation in an air conditioner according to a comparative example. FIG. 7 is a partially enlarged view of region G1 shown in FIG. 6 in an air conditioner according to a comparative example. FIG. 7 is an explanatory diagram schematically showing the relative flow of air inside a once-through fan in a cross section III-III during air conditioning operation in an air conditioner according to a comparative example. 9 is a partially enlarged view of region G2 shown in FIG. 8 in an air conditioner according to a comparative example. FIG. FIG. 7 is a front view including a cross-flow fan of an air conditioner according to another comparative example.

≪Embodiment≫
<Configuration of air conditioner>
FIG. 1 is a configuration diagram of an air conditioner 100 according to an embodiment.
Note that the solid arrows in FIG. 1 indicate the flow of refrigerant during heating operation.
On the other hand, dashed arrows in FIG. 1 indicate the flow of refrigerant during cooling operation.
The air conditioner 100 is a device that performs air conditioning such as heating operation and cooling operation. As shown in FIG. 1, the air conditioner 100 includes a compressor 11, an outdoor heat exchanger 12, an outdoor fan 13, and an expansion valve 14. Moreover, the air conditioner 100 includes an indoor heat exchanger 15 (heat exchanger), a cross-flow fan 20, and a four-way valve V in addition to the above-described configuration.

The compressor 11 is a device that compresses a low-temperature, low-pressure gas refrigerant and discharges it as a high-temperature, high-pressure gas refrigerant, and includes a compressor motor 11a that is a driving source.
The outdoor heat exchanger 12 is a heat exchanger that performs heat exchange between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent from the outdoor fan 13.

The outdoor fan 13 is a fan that sends outside air into the outdoor heat exchanger 12. The outdoor fan 13 includes an outdoor fan motor 13 a as a driving source, and is arranged near the outdoor heat exchanger 12 .
The expansion valve 14 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 12 and the indoor heat exchanger 15). Note that the refrigerant whose pressure has been reduced by the expansion valve 14 is guided to the "evaporator" (the other of the outdoor heat exchanger 12 and the indoor heat exchanger 15).

The indoor heat exchanger 15 is a heat exchanger in which heat is exchanged between the refrigerant flowing through the heat transfer tube g (see FIG. 2) and the indoor air (air in the air-conditioned space) sent from the once-through fan 20. It is a vessel.
The cross-flow fan 20 (also referred to as a cross-flow fan or cross-flow fan) is a fan that sends indoor air to the indoor heat exchanger 15 and is arranged near the indoor heat exchanger 15.

The four-way valve V is a valve that switches the refrigerant flow path according to the operation mode of the air conditioner 100. For example, during cooling operation (see the dashed arrow in FIG. 1), the , the refrigerant circulates. On the other hand, during heating operation (see the solid line arrow in Figure 1), the , the refrigerant circulates.

In addition, in the example of FIG. 1, the compressor 11, the outdoor heat exchanger 12, the outdoor fan 13, the expansion valve 14, and the four-way valve V are installed in the outdoor unit Uo. On the other hand, the indoor heat exchanger 15 and the cross-flow fan 20 are installed in the indoor unit Ui. In addition to the compressor 11 and the outdoor fan 13, the expansion valve 14, the cross-flow fan 20, the four-way valve V, and the like are controlled by a control device (not shown).

FIG. 2 is a schematic vertical cross-sectional view of the indoor unit Ui.
In addition to the above-described indoor heat exchanger 15 and cross-flow fan 20, the indoor unit Ui includes a housing base 16, filters 17a and 17b, a front panel 18, left and right wind direction plates 19a, and up and down wind direction plates 19b. We are prepared.

The indoor heat exchanger 15 includes a plurality of fins f and a plurality of heat transfer tubes g passing through the fins f, and is installed near the cross-flow fan 20. In the example of FIG. 2, the indoor heat exchanger 15 includes a front indoor heat exchanger 15a installed in front of the cross-flow fan 20, and a rear indoor heat exchanger 15b installed behind the cross-flow fan 20. , is equipped with. The upper end of the front indoor heat exchanger 15a and the upper end of the rear indoor heat exchanger 15b are connected in an inverted V shape.

The cross-flow fan 20 is a cylindrical cross-flow fan including a plurality of blades wk and partition plates r. The plurality of blades wk are thin plate-like members that give energy to air by their movement, and are curved in an arc shape when viewed in longitudinal section. Further, the plurality of blades wk are arranged at predetermined intervals in the circumferential direction. Note that the spacing (pitch) between the blades in the circumferential direction may be approximately equal intervals, or may be a so-called random pitch. These wings wk are installed substantially perpendicular to the plate surface of the partition plate r.

The partition plates r are annular plates that partition the plurality of blades wk in the axial direction, and a plurality of partition plates r are provided at predetermined intervals in the axial direction (see also FIG. 3). Furthermore, the partition plate r also has a function of fixing the relative positions of the plurality of blades wk. Then, as the fan motor 21 (see FIG. 3) is driven, the plurality of blades wk and partition plate r rotate together around the axis X (see FIG. 3) of the motor shaft 21a (see FIG. 3). It has become.

The housing base 16 shown in FIG. 2 accommodates the indoor heat exchanger 15, the cross-flow fan 20, etc., and includes a front nose 16a and a back nose 16b.
The front nose 16a separates the suction side and the blowout side of the air flow, and is provided at a portion of the housing base 16 near the lower part of the front indoor heat exchanger 15a and close to the cross-flow fan 20. .
The back nose 16b partitions the suction side and the blowout side of the air flow, and is provided in a portion of the housing base 16 near the lower part of the rear indoor heat exchanger 15b and close to the cross-flow fan 20. There is.

The filters 17a and 17b collect dust from the air sucked into the indoor unit Ui. One filter 17a is installed in front of the indoor heat exchanger 15, and the other filter 17b is installed above the indoor heat exchanger 15.
The front panel 18 is a panel installed to cover the front filter 17a, and is rotatable forward about its lower end. Note that a configuration may be adopted in which the front panel 18 does not rotate.

The left-right wind direction plate 19a is a plate-like member that adjusts the flow of air blown into the room in the left-right direction. The vertical wind direction plate 19b is a plate-like member that adjusts the vertical flow of air blown into the room.
The air taken into the indoor unit Ui exchanges heat with the refrigerant flowing through the heat transfer tubes g of the indoor heat exchanger 15, and the heat-exchanged air is guided to the blowout air path h1. The air flowing through the blowout air path h1 is guided in a predetermined direction by the left and right wind direction plates 19a and the up and down wind direction plates 19b, and is blown out into the room.

FIG. 3 is a front view including the cross-flow fan 20. FIG.
The cross-flow fan 20 includes a fan motor 21, a pair of end plates tp and tq, and a bearing 22, in addition to the plurality of blades wk and partition plate r described above.
The fan motor 21 is a drive source for the cross-flow fan 20, and includes a motor shaft 21a that rotates as the fan motor 21 is driven.
The pair of end plates tp and tq are disc-shaped plates installed at both axial ends of the plurality of blades. Of the pair of end plates tp and tq, the end plate tp installed at one axial end (that is, the end on one axial side) of the cross-flow fan 20 includes a boss portion tpa.

The boss portion tpa is a portion on which the motor shaft 21a of the fan motor 21 is installed, and extends inward in the axial direction by a length L1 near the center of the disc-shaped end plate tp. Note that the motor shaft 21a is detachable from the boss portion tpa using a set screw or the like (not shown).

Of the pair of end plates tp and tq, the end plate tq installed at the other axial end of the cross-flow fan 20 (that is, the other axial end) includes a shaft portion tqa that is supported by the bearing 22. I'm here. The shaft portion tqa is provided near the center of the disc-shaped end plate tq, and protrudes inward in the axial direction from the plate surface of the end plate tq by a length L2.

As shown in FIG. 3, the cross-flow fan 20 includes a plurality of fan blocks Bp, Bk, Bk, . . . , Bk, Bq connected in the axial direction via a partition plate r. Among these fan blocks Bp, Bk, Bk, ..., Bk, Bq, the fan block Bp installed at one end in the axial direction of the cross-flow fan 20 has a plurality of blades wp, and a partition plate r and an end plate tp. We are prepared. The plurality of blades wp included in the fan block Bp are elongated in the axial direction, and one end thereof is installed on the end plate tp, and the other end is installed on the partition plate r.

Note that the partition plate r and the end plate tp are provided with predetermined grooves (not shown) into which the ends of the plurality of blades wp are fitted. The plurality of blades wp may extend parallel to the axial direction, or may be inclined at a predetermined angle with respect to the axial direction.

Another fan block Bk adjacent to the fan block Bp includes a plurality of blades wk and a partition plate r. One end of the plurality of blades wk is installed on the partition plate r of the fan block Bp described above, and the other end is installed on another partition plate r. In this way, the plurality of fan blocks Bp, Bk, Bk, . . . , Bk, Bq are sequentially connected in the axial direction via the partition plate r.

Moreover, in the example of FIG. 3, in the housing base 16, a slight gap j is provided between the side wall 16p on one axial side of the cross-flow fan 20 and the end plate tp. Further, the side wall 16p has a blocking portion 161p that projects inward to the vicinity of the end plate tp so as to block the above-described gap j below the cross-flow fan 20. Note that the same can be said between the other side wall 16q of the housing base 16 and the end plate tq.

The position of the blocking portion 161p in the axial direction of the cross-flow fan 20 substantially coincides with the position of the end plate tp. Similarly, the position of the other blocking portion 161q also substantially coincides with the position of the end plate tq. The space between these blocking parts 161p and 161q functions as an air outlet h1 (see also FIG. 2). Therefore, in the example of FIG. 3, the total length of the cross-flow fan 20 in the axial direction is approximately equal to the length L3 in the lateral direction of the air outlet h1.

Although details will be described later, in the axial direction of the cross-flow fan 20, the airflow inside the cross-flow fan 20 is The flow field is different. Therefore, in this embodiment, the blades wk, wp, and wq of the cross-flow fan 20 are configured as follows to suppress surging (unstable airflow phenomenon) in the region where the boss portion tpa and the shaft portion tqa are present. It is configured.

FIG. 4 is an explanatory diagram in which the blade wk in the II-II section of FIG. 3 and the blade wp in the III-III cross section of FIG. 3 are superimposed.
Note that in FIG. 4, illustration of the partition plate r (see FIG. 3) is omitted.
As shown in FIG. 4, the blade wk included in the fan block Bk (see FIG. 3) is curved in an arc shape when viewed in longitudinal section, and the center of curvature (not shown) is located forward in the rotation direction of the blade wk. are doing. In such a blade wk, the surface facing the center of curvature (not shown) described above is called a "pressure surface", and the surface opposite to this pressure surface is called a "suction surface".

Further, in the thickness direction of the blade wk, an imaginary line connecting the center point between the pressure surface and the suction surface is referred to as a "curvature line ck." The warp line ck extends in an arc shape from the inner end to the outer end of the blade wk. Note that the same can be said of the warp line cp of the blade wp included in the fan block Bp (see FIG. 3) at one end in the axial direction.

The imaginary line mi shown in FIG. 4 is the locus of the inner peripheral side end portions of the blades wk and wp that move as the cross-flow fan 20 rotates. This imaginary line mi is a circular curve that passes slightly inside the inner peripheral edge of the annular partition plate r (not shown in FIG. 4, see FIG. 2) in the radial direction.
The imaginary line mo shown in FIG. 4 is the locus of the outer peripheral side ends of the blades wk and wp that move as the cross-flow fan 20 rotates. This imaginary line mo is a circular curve that passes slightly inside the outer peripheral edge of the annular partition plate r (not shown in FIG. 4, see FIG. 2) in the radial direction.

Further, the angle formed by the circumferential direction of the cross-flow fan 20 and the warp line ck at the inner circumferential end of the blade wk is defined as an "inner circumferential angle θk." To explain in more detail, at the intersection ek of the virtual line mi indicating the movement locus of the inner peripheral end of the blade wk and the warp line ck (however, extended to the inner peripheral side), a tangent to the virtual line mi, and When a tangent to the warp line ck is drawn, the angle formed by these two tangents (not shown) (the angle on the rear side in the rotational direction) is called the inner peripheral angle θk of the blade wk. It is assumed that the plurality of fan blocks Bk, Bk, .

Similarly, regarding the blade wp included in the fan block Bp (see FIG. 3) at one end in the axial direction, the angle between the circumferential direction of the cross-flow fan 20 and the warp line cp at the inner peripheral end of the blade wp is defined as the angle formed by the blade wp. is defined as "inner circumferential angle θp".

As shown in FIG. 4, the inner circumferential angle θp of the blade wp of the fan block Bp (see FIG. 3) located at one end in the axial direction is the inner circumferential angle θp of the blade wk of the fan block Bk (see FIG. 3) located on the inner side in the axial direction. It is smaller than θk (θk>θp). That is, among the plurality of fan blocks Bp, Bk, Bk, ..., Bk, Bq, the inner peripheral angle θp of the blade wp of the fan block Bp whose end is partitioned by the end plate tp is the same as that of the other fan blocks Bk, Bk, ..., is smaller than the inner peripheral angle θk of the blade wk of Bk.

To explain from another point of view, the "first predetermined range Sp" ( The inner circumferential angle θp of the blade wp in FIG.

In the example of FIG. 3, the position of the partition plate r installed at the other end of the blade wp in the axial direction is the predetermined position x1, and the range in which the blade wp extends in the axial direction is referred to as the "first predetermined range Sp". ”. Therefore, the "first predetermined range Sp" regarding the blade wp such that the inner circumferential angle θk>θp (see FIG. 4) is not only the location where the boss portion tpa is provided in the axial direction but also the location of the fan block Bp. It's all over the place.

Further, the same can be said of the blade wq included in the fan block Bq (see FIG. 3) at the other end in the axial direction. That is, the inner circumferential angle θq (not shown) of the blade wq of the fan block Bq (see FIG. 3) located at the other end in the axial direction is smaller than the inner circumferential angle θk of the blade wk of the fan block Bk located on the inner side in the axial direction. (θk<θq). To explain from another point of view, the second predetermined range from a predetermined position x2 (see FIG. 3) axially inner than the shaft portion tqa (see FIG. 3) of the cross-flow fan 20 to the end plate tq including the shaft portion tqa. The inner circumferential angle θq (not shown) of the blade at “Second Predetermined Range Sq” (see FIG. 3) is smaller than the inner circumferential angle θk of the blade wk further inward in the axial direction than the “second predetermined range Sq”.

In the example of FIG. 3, the position of the partition plate r where one end of the blade wq in the axial direction is installed is the predetermined position x2, and the range in which the blade wq extends in the axial direction is referred to as the "second predetermined range Sq". It is said that The functions and effects of the configuration of the blades wp and wq described above will be described later.

Further, as shown in FIG. 4, the angle formed by the circumferential direction of the cross-flow fan 20 and the warp line ck at the outer peripheral end of the blade wk is defined as the "outer peripheral angle θo" of the blade wk. To explain in more detail, at the intersection fo of the virtual line mo indicating the movement locus of the outer peripheral end of the blade wk and the warp line ck (however, extended to the outer peripheral side), the tangent to the virtual line mo and the warp line When a tangent to ck is drawn, the angle formed by these two tangents (not shown) (the angle on the front side in the rotational direction) is called the outer circumferential angle θo of the blade wk.

As shown in FIG. 4, the warp lines ck and cp substantially coincide with each other near the outer peripheral end portions of the blades wk and wp. Therefore, the outer circumferential angle θo of the blade wp of the fan block Bp (see FIG. 3) is approximately equal to the outer circumferential angle θo of the blade wk of the fan block Bk (see FIG. 3). In other words, the outer circumferential angle θo of the blade wp in the first predetermined range Sp (see FIG. 3) is equal to the outer circumferential angle θo of the blade wk in the axially inner side than the first predetermined range Sp.
Similarly, the outer circumferential angle θo of the blade wq in the second predetermined range Sq (see FIG. 3) is equal to the outer circumferential angle θo of the blade wk axially inner than the second predetermined range Sq.

In this way, while the outer circumferential angles θo of the blades wk and wp are equal, as described above, their inner circumferential angles θk and θp are different (θk>θp). As a result, the degree of warpage in the longitudinal section of the blade wp is smaller than that of the blade wk.
Further, the positions of the outer peripheral side ends of the blades wk and wp substantially coincide with each other in a longitudinal cross-sectional view. Further, the chord dp of the blade wp is tilted more rearward in the rotational direction than the chord dk passing through the inner and outer ends of the blade wk. Note that the same can be said about the positional relationship between the wings wk and wq (see FIG. 3).
Next, after explaining a comparative example (see FIGS. 6 to 9), the operation and effect of the present embodiment (see FIG. 5) will be explained.

<Comparative example>
FIG. 6 is an explanatory diagram schematically showing the relative flow of air inside the cross-flow fan 20 in the cross section II-II (see FIG. 3) during air conditioning operation in the air conditioner according to the comparative example.
In the comparative example shown in FIG. 6, it is assumed that the inner peripheral angle (=θk) of the blade wk is the same in all of the plurality of fan blocks (not shown) connected in the axial direction.
Further, the plurality of blades wk located above the straight line u (suction side) passing through the tip of the front nose 16a and the tip of the back nose 16b of the cross-flow fan 20 is referred to as a "suction side blade row wir." On the other hand, the plurality of blades wk located below the above-mentioned straight line U (on the blowout side) are referred to as a "blowout side blade row wor." As shown in FIG. 6, the air flowing in through the suction side blade row wir passes through the inside of the cross-flow fan 20, and is guided to the blowout air path h1 via the blowout side blade row wor.

FIG. 7 is a partially enlarged view of region G1 shown in FIG.
Note that the angle formed by the circumferential direction of the cross-flow fan 20 (the tangential direction of the inner circumferential edge of the partition plate r) and the relative flow of air in the vicinity of the blow-off side blade row wor is defined as an angle θF. As shown in FIG. 7, in the cross section II-II (see FIG. 3) near the axial center of the once-through fan 20, the angle θF when air flows into the blowout side blade row wor and the angle θF of the blade wk of the blowout side blade row wor are shown. The difference between the inner circumferential angle θk and the inner circumferential angle θk is relatively small. Therefore, the airflow flows along the pressure surface wka of the blade wk of the blowout side blade row wor. As a result, unstable airflow hardly occurs near cross section II-II.

FIG. 8 is an explanatory diagram schematically showing the relative flow of air inside the cross-flow fan 20 in the cross section III-III (see FIG. 3) during air conditioning operation in the air conditioner according to the comparative example.
As shown in FIG. 8, in the cross section III-III, a boss portion tpa is provided near the center of the end plate tp (see FIG. 3). Therefore, the air that has flowed into the cross-flow fan 20 via the suction side blade row wir flows around the boss portion tpa, and then heads toward the blowout side blade row wor at a steep slope.

FIG. 9 is a partially enlarged view of region G2 shown in FIG.
As described above, in the comparative example, the inner peripheral angles (=θk) of the blades wk are the same in all fan blocks (not shown) of the cross-flow fan 20. That is, in the cross-section III-III (see FIG. 3) and the cross-section IV-IV (see FIG. 3), the inner peripheral angle of the blade wk is θk, similarly to the cross-section II-II (see FIG. 3).

For example, in the cross section III-III (see Figure 3), when the airflow flows around the boss part tpa, the angle θFa between the circumferential direction of the cross-flow fan 20 and the relative flow becomes the angle θF in the cross-section II-II (see Figure 3). (see 7). Therefore, the difference between the angle θFa and the inner peripheral angle θk of the blade wk of the blowout side blade row wor becomes large. As a result, while the airflow flows toward the negative pressure surface wkb of the blade wk, the airflow that cannot follow the blade wk separates at the pressure surface wka.

Incidentally, if dust accumulates on the once-through fan 20 (see FIG. 2), the indoor heat exchanger 15 (see FIG. 2), the wall of the air outlet h1 (see FIG. 2), etc., ventilation resistance increases. As a result, the angle θFa between the circumferential direction of the cross-flow fan 20 and the relative flow becomes even smaller, and surging becomes more likely to occur. Note that surging is also likely to occur in the cross section IV-IV (see FIG. 3) where the shaft portion tqa (see FIG. 3) of the cross-flow fan 20 exists.

<Actions, effects, etc. of this embodiment>
FIG. 5 is a partially enlarged view schematically showing the relative flow of airflow inside the cross-flow fan 20 in the cross section III-III during air conditioning operation in the air conditioner according to the embodiment.
Note that, in this embodiment, the relative flow of airflow in the cross section II-II (see FIG. 3) is the same as that in FIGS. 6 and 7, so a description thereof will be omitted.
As mentioned above, in the cross section III-III (see Fig. 3), the angle θFa when air flows into the blowout side blade row wor changes to the cross-section II-II (see Fig. 3) due to the influence of the boss portion tpa (see Fig. 3). ) is smaller than the angle θF (see FIG. 7).

Here, in the present embodiment, the inner peripheral angle θp of the blade wp included in the fan block Bp (see FIG. 3) at one end in the axial direction is the same as the inner circumferential angle θp of the blade wk included in the fan block Bk (see FIG. 3) located on the inner side in the axial direction. It is smaller than the inner peripheral angle θk (θk>θp: see FIG. 4). Therefore, the difference between the angle θFa at which air flows into the blow-off side blade row wor and the inner peripheral angle θp of the blade wp becomes relatively small. As a result, the airflow flows along the pressure surface wpa of the blade wp, so separation of the airflow on the pressure surface wpa of the blade wp can be suppressed.
Note that when the ventilation resistance increases, the angle θFa becomes even smaller, but as mentioned above, since the inner circumferential angle θp of the blade wp is relatively small, it takes a long time before separation occurs on the pressure surface wpa of the blade wp. There is enough room.

Further, in this embodiment, while the inner circumferential angles of the blades wk and wp are different (θk>θp: see FIG. 4), the outer circumferential angles θo of the blades wk and wp are substantially the same (see FIG. 4). Therefore, the direction of the airflow blown out through the blowout side blade row wor of the cross-flow fan 20 is made uniform in the axial direction, so that deterioration in air blowing performance can be suppressed. The same can be said of the fan block Bq (see FIG. 3) located at the other end of the cross-flow fan 20 in the axial direction.

As described above, according to the present embodiment, the angle θFa (see FIG. 5) of the airflow flowing into the blow-off side blade row wor is influenced by the boss portion tpa (see FIG. 3) and the shaft portion tqa (see FIG. 3) of the cross-flow fan 20. ) becomes smaller, separation of the airflow on the pressure surfaces of the blades wp and wq can be suppressed. Therefore, noise caused by surging of the cross-flow fan 20 can be suppressed, and stable ventilation can be performed.

Further, in the fan block Bp (see FIG. 3) at one end in the axial direction, the inner peripheral angle θp (see FIG. 4) of the blade wp is substantially constant in the axial direction. Further, in the fan block Bq at the other end in the axial direction (see FIG. 3), the inner peripheral angle θq (not shown) of the blade wq is substantially constant in the axial direction. In other words, since the blades wp, wq have a shape without "twisting", the labor required to manufacture the blades wp, wq is reduced compared to a configuration with a "twist" in which the inner peripheral angle of the blade changes in the axial direction. and costs can be reduced.

Further, a first predetermined range Sp (see FIG. 3) in which the blade wp has a predetermined inner peripheral angle θp (see FIG. 4) is provided from a predetermined position x1 axially inner than the boss portion tpa to the end plate tp. There is. Therefore, even if the influence of the airflow that goes around the boss part tpa extends to the inside of the boss part tpa in the axial direction, surging can be appropriately suppressed. Note that the same can be said of the second predetermined range Sq (see FIG. 3) in which the blade wq is provided.

In addition, the inventors have found that the larger the diameter of the boss portion tpa (see FIG. 3), the smaller the angle θFa (see FIG. 5) of the airflow flowing into the blowout side blade row wor (see FIG. 5). This was discovered through experiments.
For example, when the ratio ε (=D2/D1) of the diameter D2 of the boss portion tpa to the diameter D1 of the cross-flow fan 20 is 0.07 or more and 0.13 or less, the first predetermined range Sp (Fig. The inner peripheral angle θp (see FIG. 5) of the blade wp in the blade wp (see FIG. 3) is preferably 70° or more and 90° or less. Note that the diameter D1 of the cross-flow fan 20 means the diameter of a circle drawn by the movement locus of the outer peripheral end of the blade wp.

As a result, the angle θFa (see FIG. 5) of the airflow that goes around the boss part tpa (see FIG. 3) and flows into the blow-off side blade row wor (see FIG. 5) can be made closer to the inner peripheral angle θp of the blade wp. can. Therefore, separation of airflow on the pressure surface wpa of the blade wp can be effectively suppressed.

Further, when the ratio ε (D2/D1) of the diameter D2 of the boss portion tpa to the diameter D1 of the cross-flow fan 20 is larger than 0.13 and smaller than 0.20, the first predetermined range The inner peripheral angle θp of the blade wp at Sp (see FIG. 3) is preferably larger than 50° and smaller than 70°.
It should be noted that the larger the above-mentioned ratio ε is, the steeper the airflow flows into the blow-off side blade row wor (see FIG. 5), and as a result, the above-mentioned angle Fa becomes smaller. Therefore, it can be said that the magnitude of the ratio ε indicates the degree of influence that the presence of the boss portion tpa has on the airflow. By appropriately adjusting the inner peripheral angle θp of the blade wp at the design stage of the cross-flow fan 20 based on the magnitude of this ratio ε, it is possible to effectively suppress separation of airflow at the pressure surface wpa of the blade wp.

Note that the same can be said of the fan block Bq (see FIG. 3) at the other end in the axial direction. That is, when the ratio δ (=D3/D1) of the diameter D3 of the shaft portion tqa (see FIG. 3) to the diameter D1 of the cross-flow fan 20 is 0.07 or more and 0.13 or less, the second The inner peripheral angle of the blade wq in the predetermined range Sq (see FIG. 3) is preferably 70° or more and 90° or less. Thereby, separation of the airflow on the pressure surface of the blade wq can be effectively suppressed.

Further, the ratio δ (=D3/D1) of the diameter D3 of the shaft portion tqa (see FIG. 3) to the diameter D1 of the cross-flow fan 20 is larger than 0.13 and smaller than 0.20. In this case, the inner peripheral angle θq (not shown) of the blade wq in the second predetermined range Sq (see FIG. 3) is preferably larger than 50° and smaller than 70°. Thereby, separation of the airflow on the pressure surface of the blade wq can be effectively suppressed.

<Another comparative example>
FIG. 10 is a front view including a cross-flow fan 20E of an air conditioner according to another comparative example.
In the comparative example shown in FIG. 10, the inner peripheral angles (=θk) of the blades wk are equal in all fan blocks Bk, Bk, . . . , Bk of the cross-flow fan 20E. Further, unlike the embodiment (see FIG. 3), a collision wall zp is provided near the side wall 16p of the housing base 16 (see FIG. 2), and a collision wall zq is provided near the other side wall 16q. ) is different from Note that other aspects are the same as those in the embodiment.

The collision wall zp shown in FIG. 10 increases the pressure of the air by causing the air blown out from the fan block Bk at one end in the axial direction to collide with itself. This collision wall zp protrudes inward in the axial direction from the blocking portion 161p of the side wall 16p, and faces the fan block Bk at one end in the axial direction in the radial direction.

The other collision wall zq increases the pressure of the air by causing the air blown from the fan block Bk at the other end in the axial direction to collide with itself. This collision wall zz protrudes inward in the axial direction from the blocking portion 161q of the side wall 16q, and faces the fan block Bk at the other end in the axial direction in the radial direction.

When the collision walls zp and zq are provided as in the comparative example, the pressure of the air blown out from near both ends of the cross-flow fan 20E in the axial direction is increased, and surging is suppressed. On the other hand, the ratio of the lateral length of the air outlet h1 to the lateral width of the indoor unit Ui becomes smaller. As a result, the opening area of the air outlet h1 becomes smaller, resulting in a decrease in air blowing performance and an increase in power consumption.

In contrast, in the present embodiment (see FIG. 3), the housing base 16 (see FIG. 2) does not have the collision wall zp in the range (first predetermined range Sp) axially inner than the boss part tpa. Furthermore, the collision wall zz is not provided in a range (second predetermined range Sq) axially inner than the shaft portion tqa. In this way, in this embodiment, there is no need to provide the collision walls zp, zq as in the comparative example, so that a sufficient opening area of the blowout air passage h1 can be ensured. This is because, even without providing the collision walls zp, zq, surging can be appropriately suppressed by appropriately adjusting the inner peripheral angles of the blades wp, wq at the design stage of the fan blocks Bp, Bq.

≪Modification example≫
Although the air conditioner 100 according to the present invention has been described above using the embodiments, the present invention is not limited to these descriptions, and various changes can be made.
For example, in the embodiment, in the fan blocks Bp, Bq at both axial ends (see FIG. 3), the inner circumferential angle of the blades wp, wq is set to be smaller than the inner circumferential angle θk of the blade wk of the axially inner fan block Bk. Although the configuration for reducing the size has been described, the configuration is not limited to this.
That is, for the fan block Bp at one end in the axial direction, the inner circumferential angle θp of the blade wp is made smaller (θk>θp), and for the fan block Bq at the other end in the axial direction, the inner circumferential angle θq of the blade wq is reduced by the fan block Bk. may be approximately the same as the inner peripheral angle θk of the blade wk. Even with this configuration, surging can be suppressed compared to a case where the inner peripheral angle of the blades of all fan blocks is θk.
Incidentally, since the diameter of the boss portion tpa (see FIG. 3) is larger than that of the shaft portion tqa (see FIG. 3), reducing the inner circumferential angle θp of the blade wp of the fan block Bp including the boss portion tpa will prevent surging. It is particularly effective in suppressing

Similarly, for the fan block Bq at the other end in the axial direction, the inner circumference angle θq (not shown) of the blade wq is made smaller (θk>θq), and for the fan block Bp at one end in the axial direction, the inner circumference angle θq (not shown) of the blade wq is made smaller (θk>θq). The angle θp may be made substantially the same as the inner peripheral angle θk of the blade wk of the fan block Bk. Even with this configuration, surging can be suppressed compared to a case where the inner peripheral angle of the blades of all fan blocks is θk.

Furthermore, in the embodiment, a configuration has been described in which the outer circumferential angle θo of the blades of the fan blocks Bp and Bq located at both ends in the axial direction is approximately the same as the outer circumferential angle θo of the blade of the fan block Bk located on the inner side in the axial direction. may be different.

Further, in the embodiment, the blade wp of the fan block Bp (see FIG. 3) installed at one axial end of the cross-flow fan 20 is not provided in a range exceeding the first predetermined range Sp (see FIG. 3). Although explained above, it is not limited to this. That is, the fan block Bp may include the first predetermined range Sp in the axial direction and may be further provided to the inside of the first predetermined range Sp in the axial direction. Even in this configuration, since the inner peripheral angle θp of the blade wp is relatively small (θk>θp) in the first predetermined range Sp, surging can be suppressed similarly to the embodiment.
The same can be said about the relationship between the fan block Bq at the other end in the axial direction and the second predetermined range Sq (see FIG. 3).

Further, in the embodiment, a configuration has been described in which the blades wp, wk, and wq of the cross-flow fan 20 are provided separately for each fan block Bp, Bk, and Bw, but the configuration is not limited to this. For example, a plurality of holes (not shown) may be provided in the partition plate r, and the wings may pass through these holes and extend in an axial direction.
Furthermore, in the embodiment, a configuration has been described in which the boss portion tpa (see FIG. 3) is provided on one side in the axial direction of the cross-flow fan 20, but the present invention is not limited to this. That is, boss portions (not shown) may be provided on both sides of the cross-flow fan 20 in the axial direction.

Further, in the embodiment, a configuration has been described in which one indoor unit Ui (see FIG. 1) and one outdoor unit Uo (see FIG. 1) are provided, but the present invention is not limited to this. For example, a plurality of indoor units connected in parallel may be provided, or a plurality of outdoor units connected in parallel may be provided.

Further, in the embodiment, the wall-mounted air conditioner 100 has been described, but the present invention can also be applied to other types of air conditioners. For example, the embodiments can be applied to various types of air conditioners such as package air conditioners, building multi-air conditioners, and integrated air conditioners.

Further, each embodiment is described in detail to explain the present invention in an easy-to-understand manner, and the present invention is not necessarily limited to having all the configurations described. Furthermore, it is possible to add, delete, or replace some of the configurations of each embodiment with other configurations.
Further, the mechanisms and configurations described above are those considered necessary for explanation, and not all mechanisms and configurations are necessarily shown in the product.

100 Air conditioner 11 Compressor 12 Outdoor heat exchanger 13 Outdoor fan 14 Expansion valve 15 Indoor heat exchanger (heat exchanger)
16 Housing base 20 Cross-flow fan 21 Fan motor 21a Motor shaft 22 Bearing Bk, Bp, Bq Fan block h1 Air outlet r Partition plate Sp First predetermined range Sq Second predetermined range tp, tq End plate tpa Boss part tqa Shaft part Uo Outdoor unit Ui Indoor unit V Four-way valve x1, x2 Predetermined position wk, wp, wq Blade zp, zq Collision wall θk, θp, θq Inner circumference angle θo Outer circumference angle

Claims (10)

a plurality of blades arranged at predetermined intervals in the circumferential direction;
a plurality of partition plates that partition the plurality of blades in the axial direction;
a pair of end plates installed at both axial ends of the plurality of wings;
A cross-flow fan having a fan motor as a driving source, and
comprising a heat exchanger installed near the once-through fan,
Of the pair of end plates, the end plate installed at one axial end of the cross-flow fan includes a boss portion on which a motor shaft of the fan motor is installed;
The inner peripheral angle of the blade in a first predetermined range from a predetermined position axially inner than the boss portion to the end plate including the boss portion is the inner circumferential angle of the blade further axially inner than the first predetermined range. smaller than the inner circumferential angle of
The ratio of the diameter of the boss portion to the diameter of the cross-flow fan is 0.07 or more and 0.13 or less, and the inner peripheral angle of the blade in the first predetermined range is 70° or more and An air conditioner with a temperature of 90 degrees or less . a plurality of blades arranged at predetermined intervals in the circumferential direction;
a plurality of partition plates that partition the plurality of blades in the axial direction;
a pair of end plates installed at both axial ends of the plurality of wings;
A cross-flow fan having a fan motor as a driving source, and
comprising a heat exchanger installed near the once-through fan,
Of the pair of end plates, the end plate installed at one axial end of the cross-flow fan includes a boss portion on which a motor shaft of the fan motor is installed;
The inner peripheral angle of the blade in a first predetermined range from a predetermined position axially inner than the boss portion to the end plate including the boss portion is the inner circumferential angle of the blade further axially inner than the first predetermined range. smaller than the inner circumferential angle of
The ratio of the diameter of the boss portion to the diameter of the cross-flow fan is larger than 0.13 and smaller than 0.20, and the inner peripheral angle of the blade in the first predetermined range is An air conditioner that is larger than 50° and smaller than 70° . a plurality of blades arranged at predetermined intervals in the circumferential direction;
a plurality of partition plates that partition the plurality of blades in the axial direction;
a pair of end plates installed at both axial ends of the plurality of wings;
A cross-flow fan having a fan motor as a driving source, and
comprising a heat exchanger installed near the once-through fan,
Of the pair of end plates, the end plate installed at one axial end of the cross-flow fan includes a boss portion on which a motor shaft of the fan motor is installed;
Of the pair of end plates, the end plate installed at the other axial end of the cross-flow fan includes a shaft portion supported by a bearing,
The inner peripheral angle of the blade in a first predetermined range from a predetermined position axially inner than the boss portion to the end plate including the boss portion is the inner circumferential angle of the blade further axially inner than the first predetermined range. smaller than the inner circumferential angle of
The inner peripheral angle of the blade in a second predetermined range from a predetermined position axially inner than the shaft portion to the end plate including the shaft portion is the inner circumferential angle of the blade further axially inner than the second predetermined range. smaller than the inner circumferential angle of
The ratio of the diameter of the shaft to the diameter of the cross-flow fan is 0.07 or more and 0.13 or less, and the inner peripheral angle of the blade in the second predetermined range is 70° or more and An air conditioner with a temperature of 90 degrees or less . a plurality of blades arranged at predetermined intervals in the circumferential direction;
a plurality of partition plates that partition the plurality of blades in the axial direction;
a pair of end plates installed at both axial ends of the plurality of wings;
A cross-flow fan having a fan motor as a driving source, and
comprising a heat exchanger installed near the once-through fan,
Of the pair of end plates, the end plate installed at one axial end of the cross-flow fan includes a boss portion on which a motor shaft of the fan motor is installed;
Of the pair of end plates, the end plate installed at the other axial end of the cross-flow fan includes a shaft portion supported by a bearing,
The inner peripheral angle of the blade in a first predetermined range from a predetermined position axially inner than the boss portion to the end plate including the boss portion is the inner circumferential angle of the blade further axially inner than the first predetermined range. smaller than the inner circumferential angle of
The inner peripheral angle of the blade in a second predetermined range from a predetermined position axially inner than the shaft portion to the end plate including the shaft portion is the inner circumferential angle of the blade further axially inner than the second predetermined range. smaller than the inner circumferential angle of
The ratio of the diameter of the shaft portion to the diameter of the cross-flow fan is larger than 0.13 and smaller than 0.20, and the inner peripheral angle of the blade in the second predetermined range is An air conditioner that is larger than 50° and smaller than 70° . a plurality of blades arranged at predetermined intervals in the circumferential direction;
a plurality of partition plates that partition the plurality of blades in the axial direction;
a pair of end plates installed at both axial ends of the plurality of wings;
A cross-flow fan having a fan motor as a driving source, and
a heat exchanger installed near the once-through fan ;
a housing base that accommodates the once-through fan and the heat exchanger,
Of the pair of end plates, the end plate installed at one axial end of the cross-flow fan includes a boss portion on which a motor shaft of the fan motor is installed;
The inner peripheral angle of the blade in a first predetermined range from a predetermined position axially inner than the boss portion to the end plate including the boss portion is the inner circumferential angle of the blade further axially inner than the first predetermined range. smaller than the inner circumferential angle of
In the air conditioner, the housing base does not have a collision wall that causes air blown from the cross-flow fan to collide with itself in a range axially inner than the boss portion. Of the pair of end plates, the end plate installed at the other axial end of the cross-flow fan includes a shaft portion supported by a bearing,
The inner peripheral angle of the blade in a second predetermined range from a predetermined position axially inner than the shaft portion to the end plate including the shaft portion is the inner circumferential angle of the blade further axially inner than the second predetermined range. The air conditioner according to claim 1 , wherein the inner circumferential angle is smaller than the inner circumferential angle of the air conditioner. The cross-flow fan includes a plurality of fan blocks connected in the axial direction via the partition plate,
Claims 1 to 5, wherein the blade of the fan block installed at one axial end of the cross-flow fan among the plurality of fan blocks extends over the first predetermined range. The air conditioner described in any one of the above . The air conditioner according to claim 7 , wherein the blade of the fan block installed at one axial end of the cross-flow fan is not provided in a range exceeding the first predetermined range. The outer peripheral angle of the blade in the first predetermined range is equal to the outer peripheral angle of the blade in the axial direction inner side than the first predetermined range , according to any one of claims 1 to 5. air conditioner. a once-through fan comprising a plurality of fan blocks connected in the axial direction via a partition plate;
a heat exchanger installed near the once-through fan ;
A housing base that accommodates the once-through fan and the heat exchanger ,
Each of the plurality of fan blocks has a plurality of blades arranged at predetermined intervals in the circumferential direction,
An end plate having a boss portion or a shaft portion is installed at the end of the cross-flow fan in the axial direction,
Among the plurality of fan blocks, the inner peripheral angle of the blade of the fan block whose end portion is partitioned by the end plate is smaller than the inner peripheral angle of the blade of the other fan blocks,
In the air conditioner, the housing base does not have a collision wall that causes air blown from the cross-flow fan to collide with itself in a range axially inner than the boss portion.

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