JP2001221457A - Refrigeration apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration apparatus with improved refrigeration performance by reducing a noise level of a freezing apparatus equipped a centrifugal fan, and provide a domestic air conditioner having the same effect, and further a centrifugal fan useable with the same performance and effect for a dehumidifying apparatus, a ventilating apparatus, and a cooling apparatus for instruments. SOLUTION: The amount of turning in an air passage and the height size of the air passage are defined into predetermined values, and an air separation flow in the air passage are reduced to decrease a corrugated flow. Further, a ring extending in a centrifugal direction is provided on an outer periphery on a suction side of a fan, and a discharge flow from a blade constituting the fan is pulled to the suction side to ensure uniform air diffusing from the whole of the blade.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a refrigeration system having a refrigeration cycle and a fan.

[0002]

2. Description of the Related Art Refrigerators include, for example, refrigerators and air conditioners. These refrigerating apparatuses include a use-side heat exchanger, an operation-side heat exchanger, and a compressor, and are provided with a fan for releasing heat generated from these to the inside or outside the room. Types of fans include propeller fans, sirocco fans, centrifugal fans, etc., and by improving the efficiency of these fans, the performance of the refrigeration system is greatly affected, and it is not an exaggeration to improve the performance of the fans. Various improvements have been made.

For example, Japanese Utility Model Laid-Open No. 60-173700 discloses a sirocco fan in which a rib is provided at the tip of a blade to rectify the air flow and increase the air volume.

[0004]

Problems to be Solved by the Invention
The following describes a problem when the conventional fan described in Japanese Patent No. 3700 is mounted on an integrated air conditioner described in Japanese Utility Model Application Laid-Open No. 59-18214, for example.

The integrated air conditioner described in Japanese Utility Model Laid-Open Publication No. 59-18214 is provided with a suction grill at the center of the front surface for sucking room air, and discharges conditioned air into the room on both sides thereof. Outlets are provided at the same opening area and at the same height. An indoor heat exchanger is disposed behind the suction grill, and a centrifugal fan is mounted behind the indoor heat exchanger. This centrifugal fan has the characteristic of sucking air in the axial direction of the fan and discharging the air in the centrifugal direction of the fan. By passing through the exchanger, the conditioned air generated by exchanging heat with the indoor heat exchanger is discharged in the centrifugal direction and discharged from the outlet into the room.

Originally, it is ideal that the above-mentioned integrated air conditioner is provided with symmetrical air passages for the left and right outlets. Since they are arranged at the same height, the air path must be changed so that the air from the centrifugal fan is forced to the left and right outlets. Therefore, it is desirable to increase the air volume of the centrifugal fan to increase the air volume from the outlet as much as possible.However, as a characteristic of the centrifugal fan, the air sucked in the axial direction Is discharged in the centrifugal direction, the discharge air is discharged in a direction deviated in the depth direction of the blade.

[0007] Accordingly, the integrated air conditioner has been described in
It is assumed that a sirocco fan disclosed in Japanese Patent Application No. 0-173700 is mounted. In the first place, the sirocco fan disclosed in Japanese Utility Model Laid-Open Publication No. Sho 60-173700 cannot be mounted on the above-mentioned integrated air conditioner because the wind direction is reversed, but it is assumed that the flow is like a centrifugal fan. When mounted, the ribs protrude from the tips of the blades, so that the ribs hinder air from being drawn in from the mouth ring side, and it cannot be expected to achieve a uniform discharge air volume.

An object of the present invention is to provide a refrigeration apparatus in which the distribution of air discharged from the blades of a centrifugal fan is made uniform to improve the performance.

[0009]

An object of the present invention is to provide a compressor,
In the refrigerating apparatus in which the use side heat exchanger and the working side heat exchanger are sequentially connected and a centrifugal fan is provided in the use side heat exchanger,
Providing a plurality of blades in the outer peripheral direction of the substrate of the centrifugal fan,
This is achieved by providing a fan having a ring extending in the centrifugal direction at the tip of the blade on the air inflow side.

Also, an air inlet provided at the center of the front surface, an air outlet provided on both sides of the air inlet and at the same height, and a use side provided behind the air outlet. A heat exchanger, and a centrifugal fan provided behind the use-side heat exchanger, and the centrifugal fan discharges air that has passed through the suction port and the use-side heat exchanger from the outlet. This is achieved by providing a plurality of blades in the outer peripheral direction of the substrate of the centrifugal fan, and providing the blades with a ring that extends in the centrifugal direction at the leading end on the air inflow side.

In addition, a bell mouth is provided on the suction side outer periphery of the centrifugal fan, and the diameter of the bell mouth is made equal to the diameter of the outer periphery of a single row of the suction side single part of the centrifugal fan.

Also, an air inlet provided at the center of the front surface, an air outlet provided on both sides of the air inlet and at the same height, and a use side provided behind the air outlet. A heat exchanger, and a centrifugal fan provided behind the use-side heat exchanger, and the centrifugal fan discharges air that has passed through the suction port and the use-side heat exchanger from the outlet. In the refrigeration system, two air paths communicating with the outlet are also floated around the outer periphery of the centrifugal fan, and air path narrowing means is provided downstream of one of the two air paths. Is achieved by

The throttling means is achieved by being provided integrally with the air path.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an integrated air conditioner equipped with a centrifugal fan according to the present invention will be described with reference to FIGS. FIG. 1 is a perspective view of an integrated air conditioner. FIG.
FIG. 2 is a view of the integrated air conditioner with its housing removed and viewed from above. FIG. 3 is a perspective view of the integrated air conditioner illustrating air circulation.

In FIG. 1, reference numeral 1 denotes an air conditioner main body. Reference numeral 2 denotes a casing that forms the outer shape of the main body of the air conditioner 1. Reference numeral 3 denotes a front grille formed of resin or the like, which is provided with a suction port 3a for room air at a central portion, and air outlets 3b on both sides of the suction port 3a. The outlet 3b has the same left and right opening areas and the same height position from the design of the front grille. 3c
Is an operation unit provided below one of the left and right outlets 3b. The surface provided with the operation unit 3c is the front surface of the air conditioner.

In FIG. 2, reference numeral 4 denotes a use side heat exchanger (hereinafter referred to as an indoor heat exchanger) provided on the indoor unit side, which is provided behind the suction port 3a. Although not shown, a filter is provided between the indoor heat exchanger 4 and the suction grill 3a. 5 is a centrifugal fan for the indoor side. Reference numeral 6 is a partition plate for thermally separating the indoor unit side and the outdoor unit side of the integrated air conditioner. On the outdoor unit side, the compressor 7 and the working side heat exchanger (hereinafter, referred to as
And a propeller fan 9 for releasing the heat of the compressor 7 and the outdoor heat exchanger 8 to the outside. Compressor 7, indoor heat exchanger 4, outdoor heat exchanger 8
Are connected by a refrigerant pipe 10 to form a series of refrigeration cycles. 11 is a fan motor. The rotation of the fan motor 11 rotates the propeller fan, and introduces outdoor air from a slit 2 a (shown in FIG. 1) provided on the side surface of the housing 2, blows the air to the outdoor heat exchanger 8 and discharges the outdoor heat. Let it. The fan motor 11 serves as a power source for the indoor centrifugal fan 5 and the outdoor propeller fan 9,
These fans 5, 9 are attached to one rotating shaft. The indoor centrifugal fan 5 is rotated by the fan motor 11, and the indoor air is sucked from the inlet 3a as shown by an arrow A, and the air that has exchanged heat in the housing is blown out by the outlet 3c as shown by an arrow B. From the room.

Next, the configuration of the air passage on the indoor side will be described with reference to FIGS. FIG. 3 is an exploded view of the heat insulating block. FIG. 4 is a front view of the heat insulating block illustrating the shape of the air path.

In FIG. 3, reference numeral 12 denotes a heat insulating block, which includes an upper heat insulating block 12a and a lower heat insulating block 12b.
Are formed in combination. The indoor heat exchanger 4 and the indoor centrifugal fan 5 are mounted so as to be sandwiched between the upper heat insulating block 12a and the lower heat insulating block 12b. 12
b and 12c are outlets. When the indoor heat exchanger 4 is viewed from the front side, the outlet 12b is located on the left side, and the outlet 12c is located on the right side. These outlets 12b and 12
c is designed to be at the same position as the outlet 3b of the front grille 3. Reference numeral 12d denotes a mouth ring which covers the outer periphery of the front surface of the centrifugal fan 5. 12e
Denotes a dew tray, which also forms a part of the heat insulating block and is provided at a lower portion of the indoor heat exchanger 4.

In FIG. 4, reference numeral 13 denotes the left outlet 12
Reference numeral 14 denotes an upper air passage for the right outlet 12c. Both air paths 13 and 14 are defined by left and right nose 15 and 16. The upper wind path 13
With the nose 16 as a base point, the curving direction is curved toward the left outlet 12b, and the left outlet 12b is curved.
In order to match the shape of b, it has a sharp outside spread. On the other hand, the lower air passage 14 has the nose 15 as a base point,
The spiral shape is formed toward the right outlet 12d. However, from the nose 15 as a base point, it slightly expands to the vicinity of the nose 16, but the right outlet 12
d, there is no rapid expansion as compared with the upper air path 13, but rather, the right outlet 12d.
Thus, a continuous air path is formed, and accordingly, a long air path is formed.

A description will be given of the flow of air in the upper air passage 13 which is rapidly expanding.

When the centrifugal fan 5 rotates counterclockwise with the nose 16 as a base, air flows in the upper air passage 13 in the direction indicated by the arrow. At this time, the air velocity immediately after being discharged from the blades 5a located at the nose portion 16 decreases as the wind speed is high and the spiral air path 13a widens with the nose 16 as a base point. Decelerated air and blade 5a
When the high-speed air that has just blown out from the outlet joins, the decelerated air is attracted to the high-speed air side, and the pressure increases. On the other hand, since the centrifugal fan 5 has a negative pressure on the axial center side due to the rotation, the high-pressure air flows in the negative pressure direction and the fan 5
May flow backward from the axial center side to the bell mouth 12d side. Therefore, the amount of the discharged air is reduced by the amount of the backflow, and this reduction is repeated, so that a wavy airflow is generated due to a change in the airflow, which also causes noise.

Reference numeral 17 denotes an air path restricting section provided at the end of the spiral section 13a of the upper air path 12. This throttle unit 1
There is no problem if 7 is provided integrally with the upper heat insulating block 12a or separately.

By providing the throttle portion 17, the air that has passed through the spiral portion 13a is throttled, and turbulence due to negative pressure can be prevented.

Next, the centrifugal fan 5 is shown in FIGS.
Will be described. FIG. 5 is a partial cross-sectional view showing a peripheral structure of a centrifugal fan and a mouth ring. FIG. 6 is a partial sectional view showing a peripheral structure of a conventional centrifugal fan and a mouth ring.

In FIG. 5, 5 is a centrifugal fan,
A plurality of blades 5a are provided on the outer periphery. This wing 5a
Are integrally attached to the substrate 5b. Bellmouth 1
2d is provided so as to cover the outer periphery of the centrifugal fan 5 on the air inflow side. Reference numeral 18 denotes a distal end of the row of blades 5a, which is a ring extending in the centrifugal direction. The ring 18 is inclined in the direction of the substrate 5b.

Next, the detailed shapes of the main parts of the air passages 12 and 13 will be further described with reference to FIG. 13a is a spiral portion of the upper air passage 13. The range of the spiral part 13a is indicated by an angle θa. Reference numeral 14a denotes a spiral portion of the lower air passage 14. The range of the spiral part 14a is indicated by an angle θb. The start point of the swirl of these swirl portions 13a and 14a is determined by the upper air passage 13
In the case of, it is from the nose 16 point, and in the case of the lower wind path 14, it is from the nose 15 point.

The positional relationship between the spiral portion 13a of the upper air passage 13 and the left air outlet 12b is abrupt because the final shape of the air passage 13 must be adjusted to the shape of the outlet 12b because the deviation is small. A large enlarged portion 13b occurs.
When the air from the centrifugal fan 5 passes through the enlarged portion 13b, the air in the enlarged portion 13b is drawn to the air side where the air passes, so that a vortex is generated. θa is in the range of 90 ° to 140 ° with respect to the range from the vertex of the narrowed portion 17 to the nose 16. This range is larger than the conventional range, and the distance C from the end of the spiral portion 13a to the blade 5a of the fan 5 is reduced by the increase.

On the other hand, the lower air passage 14 is
Since c is higher than the spiral part 14a,
A sudden expansion portion does not occur, and a flow disturbance such as a rapid expansion loss or separation due to an insufficient amount of air winding hardly occurs. Therefore, the angle θ from the nose 15 to the nose 16 about the fan axis
By setting b in the range of 135 ° to 200 °, the blowing speed distribution from the right outlet 12c is improved, and the air volume balance between the upper air passage 13 and the lower air passage 14 is improved.

The enlarged portion 13b of the upper air passage 13 will be described. In the case of a single air path, it is generally known that increasing the internal volume of the air path can sufficiently exert the performance of the fan. However, the present invention provides an upper air path 13 and a lower air path 14. , The distance C from the outer periphery of the row of blades 5a of the centrifugal fan 5 to the inner wall of the upper air passage 13
Is set in the range of 20% to 40% with respect to the outer diameter of the row of blades 5a, the distance E from the thick portion 17 to the fan 5 is reduced, and the air that has exited the spiral portion 13a is At 17, the generation of wavy air is suppressed, so that noise can be reduced and air volume can be increased.

The spiral portion 14a of the lower air passage 14 also has a distance D from the outer periphery of the row of blades 5a to the inner wall of the spiral portion.
Is set in the range of 30% to 50% with respect to the outer diameter of the row of blades 5a. The winding amounts of these spiral portions 13a and 14a satisfy θa <θb. Further, the distance C from the outer periphery of the row of blades 5a of the upper wind path 13 to the inner wall of the spiral part (conventionally, about 9
In this embodiment, the distance D from 0 mm is set to a range of 20 to 30 mm), and the distance D from the outer periphery of the blade row of the lower air passage 13 to the inner wall of the spiral portion is set to C <D, so that the stability is further improved. This allows two-way blowing. In addition, the distance D from the nose 16 to the position immediately before the right outlet 12c is equal to the distance D.
Is D <F.

The centrifugal fan 5 of the present invention is provided with a ring 18 extending in the centrifugal direction from the tip of the row of blades 5a on the suction side in the axial direction and having a width of 70% to 200% with respect to the thickness of the circle of the rows of blades 5a. Since a negative pressure portion is generated on the inner surface of the ring 18, the air discharged from the blades is drawn toward the inner surface of the ring 18, so that the turbulence of the blown air can be reduced as shown by the broken line in FIG.

FIG. 6 shows the blown air in the case where a conventional centrifugal fan without the ring 18 is attached, by a broken line.
Since the air discharged from the blade 5a is not provided with the ring 18 on the tip side of the blade 5a, the air is not drawn to the tip side of the blade 5a, but is discharged in a direction deviated in the depth direction of the blade, as indicated by a broken line. In addition, the air discharge is disturbed.

By the way, as a result of actual measurement using the integrated air conditioner equipped with the centrifugal fan of the present invention, the wavy sound is reduced, the noise level is reduced by 3 dB, and the air volume is reduced by 8%.
%, And the fan operating voltage could be lowered by 4%. In this way, the increase in the air volume also achieves a synergistic effect of increasing the distance between the heat exchanger and the bell mouth, which is important for the present invention to improve the flow condition around the blade inlet outlet. This is an important element.

In order to enhance the effect, the vertical cross section of the pressure boost ring 18 is deviated rearwardly at an angle of 5 ° to 30 ° with respect to the direction perpendicular to the axis as going outward. The negative pressure generated on the side surface becomes large, and the effect of expanding the discharge region from the blade 5a toward the suction side can be achieved.

FIG. 7 shows the centrifugal fan viewed from the front. The portion of the blade 5a indicated by the solid line is the tip of the blade 5a, and the portion indicated by the broken line is the shape in the depth direction. Therefore, the blade 5a is tapered from the depth side to the tip side, and is curved in the rotation direction (counterclockwise rotation direction) of the blade 5a.

FIG. 8 is a diagram showing the shape of the blade 5a with respect to the rotation of the blade 5a in the N direction. As shown in FIG. 8A, the inner peripheral side of the suction side tip of the blade 5a is formed in an arc shape. FIG. 8B shows the blade 5a shown in FIG.
It is a cross section of the part that is not an arc of
Since the shape is square, the overall shape of the blade 5a is substantially sword-shaped. With this shape, the lift can be increased, and the air volume can be increased.

As described above, according to the present invention, the air flows smoothly into the blades constituting the centrifugal fan, the air volume discharged from the blades is averaged, and the air volume discharged from the left and right outlets Is reduced.

[0038]

According to the present invention, it is possible to provide a refrigeration apparatus in which the distribution of air discharged from the centrifugal fan is made uniform and the cooling performance is improved.

[Brief description of the drawings]

FIG. 1 is a perspective view of an integrated air conditioner equipped with the present invention.

FIG. 2 is a top sectional view of the integrated air conditioner.

FIG. 3 is an exploded structural view of an indoor air passage of the integrated air conditioner.

FIG. 4 is a front view of an indoor air passage.

FIG. 5 is a detailed partial cross-sectional view of an upper air passage provided with the present invention.

FIG. 6 is a detailed partial cross-sectional view of a conventional upper air passage.

FIG. 7 is a front view of a centrifugal fan showing a blade shape.

8A and 8B are partial cross-sectional views of a blade.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Integrated air conditioner, 2 ... Housing, 3 ... Front grille, 4
... indoor heat exchanger, 5 ... centrifugal fan, 6 ... partition plate, 7 ...
Compressor, 8 ... outdoor heat exchanger, 9 ... propeller fan, 10
... refrigerant pipe, 11 ... fan motor, 123 heat insulating block, 12 ... upper air path, 14 ... lower air path, 15, 16 ... nose, 17 ... throttle, 18 ... ring.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Hiroshi Maruyama 800 Tomita, Ohira-cho, Ohira-machi, Shimotsuga-gun, Tochigi Prefecture F-term in the Refrigeration Division, Hitachi, Ltd. 3L049 BB05 BB08 BB10 BC01 BD01

Claims (5)

[Claims] In a refrigerating apparatus in which a compressor, a use-side heat exchanger, and an operation-side heat exchanger are sequentially connected, and a centrifugal fan is provided in the use-side heat exchanger, an outer circumferential direction of a substrate of the centrifugal fan is provided. A refrigerating apparatus comprising: a plurality of blades; a ring extending in a centrifugal direction at an end of the blade on an air inflow side. 2. An air inlet provided at a central portion of the front surface,
An air outlet provided on both sides of the air inlet and at the same height, a use-side heat exchanger provided behind the air outlet, and provided behind the use-side heat exchanger. A centrifugal fan, wherein the centrifugal fan discharges the air that has passed through the suction port and the use-side heat exchanger from the outlet port. And a refrigeration apparatus having a centrifugal ring at the tip of the blade on the air inflow side. 3. A bell mouth is provided on the outer periphery of the suction side of the centrifugal fan, and the diameter of the bell mouth is made equal to the diameter of the outer periphery of the single row of the suction side of the centrifugal fan. Refrigeration equipment. 4. An air inlet provided at a central portion of the front surface,
An air outlet provided on both sides of the air inlet and at the same height, a use-side heat exchanger provided behind the air outlet, and provided behind the use-side heat exchanger. A refrigerating apparatus having a centrifugal fan and discharging the air passed through the suction port and the use-side heat exchanger from the outlet by the centrifugal fan, and communicating with the outlet at an outer periphery of the centrifugal fan. A refrigeration system in which two air paths are floated, and air path narrowing means is provided downstream of one of the two air paths. 5. The refrigeration apparatus according to claim 4, wherein said throttle means is provided integrally with said air passage.