Patent Grant
11262098
This application is a U.S. national stage application of International Application No. PCT/JP2017/039127, filed on Oct. 30, 2017, and is based on International Application No. PCT/JP2016/082241, filed on Oct. 31, 2016, the contents of which are incorporated herein by reference.
The present invention relates to an indoor unit and an air-conditioning apparatus including the same. In particular, the present invention relates to a structure for rectifying gas inside the indoor unit.
There has been disclosed, for example, an indoor unit for an air-conditioning apparatus, which includes a diffuser portion enlarged in a height direction and a width direction from an air outlet of each of spiral casings to the vicinity of a heat exchanger (see, for example, Patent Literature 1).
Patent Literature 1: Japanese Unexamined Patent Application Publication No. 2010-117110
In the related-art ceiling-concealed indoor unit, a width of the heat exchanger is larger than widths of air outlets of an air-sending portion. Therefore, an air velocity distribution of air passing through the heat exchanger is non-uniform in the width direction. Therefore, a pressure loss in the heat exchanger is increased, with the result that, for example, degradation in efficiency of fans or increase in noise may occur. Further, in order to downsize the indoor unit, the heat exchanger is arranged obliquely relative to the air outlets of the spiral casings. Therefore, a distance between the air outlets of the spiral casings and the heat exchanger is increased. As a result, air streams discharged from the fans are influenced by a shape of a wall surface of an air passage in the unit, with the result that, for example, degradation in efficiency of the fans or increase in noise may occur.
For example, through application of the technology described in Patent Literature 1, a difference between the widths of the air outlets of the air-sending portion and the width of the heat exchanger, and a distance from discharge ports of the fans to the heat exchanger are reduced. However, air passages are sharply enlarged at enlarging portions of the diffusers. Therefore, air streams do not sufficiently spread along wall surfaces of the air passages, with the result that a pressure loss may adversely occur. Further, guides are provided to the diffusers so that air streams easily spread. However, there is a problem in that an improvement effect of the enlargement of the diffusers cannot be sufficiently obtained due to a pressure loss in the guides. Further, turbulence of an air stream occurs in a space between the adjacent spiral casings in air outlet passages of the spiral casings. Therefore, a vortex is liable to occur, with the result that a pressure loss may occur.
The present invention has been made in view of the problems described above, and has an object to provide, for example, an indoor unit, which achieves further improvement in efficiency and reduction in noise.
According to one embodiment of the present invention, there is provided an indoor unit, including: an air-sending portion, which includes a casing having a rectangular air outlet and accommodating an impeller including a plurality of blades; a heat exchanger, which is configured to exchange heat with gas sent from the air-sending portion; and a guide portion, which includes an upper guide defining a passage for the gas and being arranged between an upper edge portion of the air outlet and an upper end portion of the heat exchanger, and a lower guide defining a passage for the gas and being provided between a lower edge portion of the air outlet and a lower end portion of the heat exchanger, and which is open at side regions of the guide portion.
Further, according to one embodiment of the present invention, an air-conditioning apparatus includes the indoor unit described above.
According to one embodiment of the present invention, gas sent from the air outlet of the air-sending portion to the heat exchanger is rectified so that the pressure loss can be reduced. Further, a vortex region generated in the vicinity of the air outlet of the air-sending portion can be reduced. Moreover, the side regions are open so that an air velocity distribution of gas flowing into the heat exchanger is uniform. Therefore, for example, further improvement in efficiency and reduction in noise can be attained.
Now, an indoor unit and other apparatus according to embodiments of the present invention are described referring to the drawings. In the drawings referred to below, components denoted by the same reference symbols correspond to the same or equivalent components. This is common throughout the embodiments described below. Further, the forms of the components described herein are merely examples, and the components are not limited to the forms described herein. In particular, the combinations of the components are not limited to only the combinations in each embodiment, and the components described in another embodiment may be applied to still another embodiment. Further, in the following description, the upper part and the lower part of the drawings are referred to as “upper side” and “lower side”, respectively. Further, for ease of understanding, terms indicating directions (for example, “right”, “left”, “front”, and “rear”) are used as appropriate. Those terms are used for description, but do not limit the invention of the present application. Further, in the drawings, the size relationship among components sometimes differs from actual relationships.
As illustrated in
A case air-outlet 2 is formed on one surface side among the surfaces of the side surface portion 1c of the case 1. As the shape of the case air-outlet 2, any suitable shape may be employed. In this case, the case air-outlet 2 has a rectangular shape. Further, a case air-inlet 8 is formed in a surface on a side opposite to the surface having the case air-outlet 2 among the surfaces of the side surface portion 1c of the case 1. As the shape of the case air-inlet 8, any suitable shape may be employed. In this case, the case air-inlet 8 has a rectangular shape. Although not particularly limited, for example, a filter for removing dust from gas may be provided to the case air-inlet 8. In the indoor unit, the surface having the case air-outlet 2 is referred to as a front (front surface). Upward and downward directions as viewed from the front side are referred to as a height direction or an upper-and-lower direction. Further, right and left directions are referred to as a width direction or a rotation shaft direction, and front and rear directions are referred to as a front-and-rear direction or a depth direction.
In the case 1, there are accommodated an air-sending portion 20, a fan motor 4, and a heat exchanger 6. The heat exchanger 6 is arranged at a position in a passage of air from an air outflow side of the air-sending portion 20 to the case air-outlet 2. The heat exchanger 6 is configured to adjust at least one of a temperature or a humidity of air sent from the air-sending portion 20. In this case, the heat exchanger 6 has a rectangular shape in conformity with the shape of the case air-outlet 2. A configuration and a mode of the heat exchanger 6 are not particularly limited. The heat exchanger 6 in Embodiment 1 is not a special type, and a publicly-known type is used. For example, a fin-and-tube heat exchanger exchanges heat between air passing through the heat exchanger 6 and refrigerant passing through heat transfer pipes (not shown), to thereby adjust at least one of a temperature or a humidity of air.
The fan motor 4 and the air-sending portion 20 form an air-sending device. The fan motor 4 is driven through supply of electric power to rotate fans 3 inside spiral casings 7. The fan motor 4 is supported by, for example, a motor support 4a fixed to the upper surface portion 1a of the case 1. The fan motor 4 includes a rotation shaft X. The rotation shaft X is arranged to extend in parallel to the width direction along the surface having the case air-inlet 8 and the surface having the case air-outlet 2 among the surfaces of the side surface portion 1c.
The air-sending portion 20 in Embodiment 1 includes one or a plurality of spiral casings 7. As illustrated in
The fans 3 of the air-sending portion 20 each serve as an impeller configured to generate flow of air that is sucked into the case 1 through the case air-inlet 8 and blown out into a target space through the case air-outlet 2. The fans 3 each include a main plate 3a, a side plate 3c, and a plurality of blades 3d. The main plate 3a has a disc shape, and includes a boss portion 3b at a center portion thereof. The rotation shaft X of the fan motor 4 is connected to the center of the boss portion 3b. The fans 3 are rotated through drive of the fan motor 4. A rotation direction of the fans 3 corresponds to the height direction (upper-and-lower direction). The side plate 3c is provided to be opposed to the main plate 3a, and has a ring shape. A hole of the ring of the side plate 3c serves an inflow port into which air flows through the bellmouth 5. The plurality of blades 3d are provided between the main plate 3a and the side plate 3c to surround the rotation shaft X. The plurality of blades 3d have the same shape. The blades 3d are each formed of a forward curved vane in which a blade trailing edge on an outer peripheral side is located forward in the rotation direction relative to a blade leading edge on an inner peripheral side.
The spiral casings (scroll casings) 7 are each configured to receive the fan 3 to surround the fan 3. The spiral casing 7 is configured to rectify air having been blown out from the fan 3. The spiral casing 7 includes a peripheral wall 7a extending along an outer peripheral end of the fan 3. The peripheral wall 7a includes a tongue portion 7b at one portion. An end portion of a portion protruding from the peripheral wall 7a relative to a portion corresponding to the tongue portion 7b serves as a fan air-outlet 7d. Through rotation of the fan 3, air flows through the fan 3 to be sent from the fan air-outlet 7d. The fan air-outlet 7d has a rectangular shape. The fan air-outlet 7d that serves as an air outlet of the air-sending portion 20 is opened toward the heat exchanger 6 and the case air-outlet 2. Therefore, air having been blown out from the air-sending portion 20 generally flows in a direction toward the heat exchanger 6 and the case air-outlet 2.
Further, at least one fan air-inlet 9 is formed in a side wall 7c of the spiral casing 7. The bellmouth 5 is arranged along the fan air-inlet 9. The bellmouth 5 is configured to rectify air flowing into the fan 3. The bellmouth 5 is positioned to face the inflow port for air of the fan 3. The partition plate 10 is a plate for partitioning a space between the fan air-inlets 9 and the fan air-outlets 7d. The fan air-inlets 9 of the spiral casings 7 are located in a space on the air-sending unit 16 side, and the fan air-outlets 7d of the spiral casings 7 are located in a space on the main body unit 15 side.
The indoor unit according to Embodiment 1 includes guide portions 11. The guide portions 11 each serve as a wall for guiding air sent from the fan air-outlet 7d of the spiral casing 7 to the heat exchanger 6. In this case, guides are provided at upper and lower edges of the fan air-outlet 7d that intersect the height direction being the rotation direction of the fan 3. In Embodiment 1, an upper guide 11a and a lower guide 11b are provided. The upper guide 11a and the lower guide 11b are formed not merely by extending the upper edge and the lower edge of the fan air-outlet 7d along an orientation of the fan air-outlet 7d, but are installed to enlarge the fan air-outlet 7a from the upper edge portion and the lower edge portion of the fan air-outlet 7d of the spiral casing 7 toward an upper end portion and a lower end portion of the heat exchanger 6.
For example, although it is advantageous to close the side regions when air is to be guided in a set direction, air flowing along the wall is to be blown out while being sharply spread in the width direction after passing along the wall. Therefore, the air flowing into the heat exchanger 6 differs in air velocity in the width direction so that an airflow velocity distribution is not uniform. In contrast, in the indoor unit according to Embodiment 1, walls on the side regions of the guide portion 11 are not extended, and the side regions are opened. Therefore, air having been blown out from the fan air-outlet 7d of the spiral casing 7 spreads evenly in the width direction without stagnation. Thus, the air velocity distribution of air, which flows into the heat exchanger 6, in the width direction is expected to become uniform. A material of the upper guide 11a and the lower guide 11b that form the guide portion 11 is not limited. For example, a material such as polystyrene foam may be employed. Further, the guide portion 11 may have any shape in an extension direction when the guide portion 11 extends toward the upper end portion and the lower end portion of the heat exchanger 6.
Next, description is made of flow of air when the fans 3 of the air-sending portion 20 are rotated. When electric power is supplied, the fan motor 4 is driven so that the fans 3 are rotated. When the fans 3 are rotated, for example, air in a room to be air-conditioned flows into the case 1 through the case air-inlet 8. Air having been sucked into the case 1 passes through the fan air-inlets 9 of the spiral casings 7, and is guided by the bellmouths 5 to flow into the fans 3. Further, the air having flowed into the fans 3 is blown out in a radial direction and an outward direction of the fans 3. The air having been blown out from the fans 3 passes through the spiral casings 7, and then, is blown out through the fan air-outlets 7d of the spiral casings 7. The air having been blown out passes through the heat exchanger 6. The air supplied to the heat exchanger 6 exchanges heat when passing through the heat exchanger 6 to be adjusted in humidity. After that, the air is blown out to the outside of the case 1 through the case air-outlet 2.
In the indoor unit according to Embodiment 1, the air having been blown out from each of the fan air-outlets 7d of the spiral casings 7 flows along the guide portion 11. The guide portion 11 extending to the heat exchanger 6 is provided. Thus, the air having been blown out flows in the depth direction to reach the heat exchanger 6 without being influenced by the shape of the case 1 and being separated from the upper guide 11a and the lower guide 11b. Further, the air having been blown out through the fan air-outlet 7d evenly spreads in the width direction. Therefore, the air velocity can be uniform. As described above, the influence of the shape of the case 1 can be suppressed. Further, an air vortex can be prevented from being generated, for example, in the vicinities of the partition plate 10 and the fan air-outlets 7d.
With the spiral casings 7 in Embodiment 1 each having the configuration described above, the passing air velocity in the heat exchanger 6 is uniformized to suppress a vortex region in the vicinity of the fan air-outlet 7d. Thus, a pressure loss caused by turbulence of an air stream can be reduced so that improvement in efficiency and reduction in noise can be attained due to improvement in air volume and static pressure effect.
In the indoor unit according to Embodiment 1 described above, the upper guide 11a and the lower guide 11b are provided at the upper and lower portions of the air outlet of each of the spiral casings 7 so that the air having been blown out from each of the spiral casings 7 is guided to the upper and lower end portions of the heat exchanger 6. In the indoor unit according to Embodiment 2, a wall surface of an air passage in the guide portion 11 extended from each of the spiral casings 7 has protrusions and depressions. In this case, the guide portion 11 has ribs 12. The ribs 12 in
As described above, in the indoor unit according to Embodiment 2, the guide portion 11 has the ribs 12. Thus, flow of air in the guide portion 11 can be rectified. Therefore, in addition to the effects described in Embodiment 1, separation of an air stream can be prevented in the air passage on the air outlet side in the spiral casing 7. Therefore, a pressure loss can be reduced so that improvement in efficiency and reduction in noise can be attained due to improvement in air volume and static pressure effect.
In the indoor unit according to Embodiment 1 described above, the guide portion 11 is provided at the upper and lower portions of the air outlet of each of the spiral casings 7 so that the air having been blown out from each of the spiral casings 7 is guided to the upper and lower end portions of the heat exchanger 6. The wall of the guide portion 11 in the indoor unit according to Embodiment 1 is parallel to the depth direction from the fan air-outlet 7d side to the heat exchanger 6 side.
In the indoor unit according to Embodiment 3, the wall of the guide portion 11 has a shape enlarged in the width (lateral) direction being a direction toward the side wall 7c from the air outlet side toward the heat exchanger 6 side. Therefore, air flowing out from the spiral casing 7 can be sufficiently spread. Further, the air velocity distribution of air, which passes through the heat exchanger 6, in the width direction can further be uniform.
The outer peripheral portion enlarged in the side wall direction may be gradually enlarged in, for example, an arc shape. Further, an angle formed when the outer peripheral portion is enlarged is not limited, and, for example, the outer peripheral portion may be sharply enlarged.
As described above, in the indoor unit according to Embodiment 3, the wall of the guide portion 11 has a shape enlarged in the direction toward the side wall 7c from the air outlet side toward the heat exchanger 6 side. Thus, the air velocity distribution of air, which passes through the heat exchanger 6, in the width direction can be uniform. Therefore, in addition to the effects described in Embodiment 1, a vortex region can further be suppressed in the air passage on the air outlet side in the spiral casing 7. Therefore, improvement in efficiency and reduction in noise can be attained due to improvement in air volume and static pressure effect.
The upper guide 11a and the lower guide 11b of the guide portion 11 in the indoor unit according to Embodiment 4 each include lateral inclined portions 11c being inclined portions, which are formed by bending end portions in the lateral direction thereof. The lateral inclined portions 11c are formed by, for example, bending the end portions in the lateral direction of the upper guide 11a and the lower guide 11b.
Also in the guide portion 11 in Embodiment 4, the side regions are not closed by the lateral inclined portions 11c but are opened. Further, the lateral inclined portions 11c are not perpendicular to the height direction, but each have an inclination. When the end portions in the lateral direction are formed to erect vertically, flow of air that spreads in the width direction is blocked, with the result that, for example, air velocity of air flowing into the heat exchanger 6 may not be uniform. It is preferred that an inclination angle α be 50 degrees or less.
Further, the upper guide 11a and the lower guide 11b may be equal to each other or different from each other in, for example, inclination angle a and length of each of the lateral inclined portions 11c. Further, the shape of each of the lateral inclined portions 11c is not particularly limited. Further, any one of the upper guide 11a and the lower guide 11b may have the lateral inclined portions 11c.
As described above, in the air-conditioning apparatus according to Embodiment 4, the upper guide 11a and the lower guide 11b each include the lateral inclined portions 11c. Thus, separation of an air stream in the direction toward the side wall 7c can be reduced. Therefore, in addition to the effects described in Embodiment 1 to Embodiment 3, a pressure loss can further be reduced so that improvement in efficiency and reduction in noise can be attained due to improvement in air volume and static pressure effect.
For example, in the air-conditioning apparatus according to Embodiment 1, as illustrated in
In view of this, in the air-conditioning apparatus according to Embodiment 5, the guide portions 11 are mounted to an inner wall of the case 1 on the main body unit 15 side so that the guide portions 11 are accommodated on the main body unit 15 side. Further, when the main body unit 15 and the air-sending unit 16 are to be combined with each other, the tongue portions 7b and the guide portions 11 are joined to each other. The guide portions 11 may be formed integrally with the partition plate 10 or other portions.
As described above, in the air-conditioning apparatus according to Embodiment 5, the guide portions 11 are formed on the main body unit 15 side so that assembly of the indoor unit that achieves the effects in Embodiment 1 to Embodiment 4 can easily be carried out.
Further, in Embodiment 1 to Embodiment 5 described above, description is made assuming that the heat exchanger 6 is a fin-and-tube heat exchanger. However, the present invention is not limited thereto. For example, in order to humidify air, a humidification member configured to allow water to drip is provided as a heat exchanger.
The indoor unit according to Embodiment 7 includes upper guides 11d in place of the upper guides 11a. As illustrated in
As in the indoor unit according to Embodiment 7, the upper guide 11d has a shape, which protrudes downward in the course of extending from the fan air-outlet 7d toward the heat exchanger 6, in the extension direction. Thus, the wall surface extends continuously with the fan air-outlet 7d and the upper guide 11d. Therefore, an abrupt spread loss of air blown out from the fan air-outlet 7d can be reduced.
Further, in the indoor unit according to Embodiment 7, the upper guide 11d has a shape, which protrudes downward, in the extension direction. Thus, air sent from the fan air-outlet 7d can be guided upward. As illustrated in
The indoor unit according to Embodiment 8 includes lower guides 11e in place of the lower guides 11b. As illustrated in
As in the indoor unit according to Embodiment 8, the lower guide 11e has a shape, which protrudes downward in the course of extending from the fan air-outlet 7d toward the heat exchanger 6, in the extension direction. Thus, the wall surface extends continuously with the fan air-outlet 7d and the lower guide 11e. Therefore, an abrupt spread loss of air blown out from the fan air-outlet 7d can be reduced.
Further, in the indoor unit according to Embodiment 8, the lower guide 11e has a shape, which protrudes downward, in the extension direction. Thus, air sent from the fan air-outlet 7d can be guided upward. As illustrated in
In the guide portion 11 of the indoor unit according to Embodiment 9, when the air-sending portion 20 is viewed from the fan air-outlet 7d side, the upper guide 11a and the lower guide 11b each have an arc shape. Therefore, a curved surface is formed on each of the upper guide 11a and the lower guide 11b. The upper guide 11a and the lower guide 11b each have an arc shape so that the lateral portions of each of the upper guide 11a and the lower guide 11b are inclined in the upper-and-lower direction. The side regions are not completely covered by the inclined portions of each of the upper guide 11a and the lower guide 11b but are opened.
The upper guide 11a and the lower guide 11b may be equal to each other or different from each other in, for example, curvature and bending degree of the curved surfaces of the upper guide 11a and the lower guide 11b. Further, the shape of each of the curved surfaces is not particularly limited. Further, any one of the upper guide 11a and the lower guide 11b may have an arc shape.
As described above, in the air-conditioning apparatus according to Embodiment 9, there are provided the upper guide 11a and the lower guide 11b each having an arc shape inclined at the side regions. Thus, separation of an air stream on the side regions can be reduced. A pressure loss caused by turbulence of an air stream can be reduced so that improvement in efficiency and reduction in noise can be achieved due to improvement in air volume and static pressure effect. Further, a pressure loss can further be reduced so that improvement in efficiency and reduction in noise can be achieved due to improvement in air volume and static pressure effect.
The indoor unit 200 includes a load-side heat exchanger 201 and a load-side air-sending device 202. Similarly to the heat exchanger 6 in Embodiment 1 to Embodiment 9, the load-side heat exchanger 201 is configured to exchange heat between refrigerant and air. For example, the load-side heat exchanger 201 functions as a condenser during a heating operation. The load-side heat exchanger 201 is configured to exchange heat between refrigerant flowing in from the gas pipe 300 and air so that the refrigerant is condensed and liquified (or brought into a two-phase gas-liquid state), and to allow the refrigerant to flow out to the liquid pipe 400 side. Meanwhile, the load-side heat exchanger 201 functions as an evaporator during a cooling operation. The load-side heat exchanger 201 is configured to exchange heat between refrigerant brought into a low-pressure state by, for example, an expansion device 105 and air so that the refrigerant receives heat of the air to be evaporated and gasified, and to allow the refrigerant to flow out to the gas pipe 300 side.
Further, the indoor unit 200 includes the load-side air-sending device 202 configured to adjust flow of air in order to efficiently perform heat exchange between refrigerant and air. The load-side air-sending device 202 is a device having the same function as that of the air-sending portion 20 including, for example, the fans 3 in Embodiment 1 to Embodiment 9. The load-side air-sending device 202 is driven to rotate at a velocity determined, for example, through setting of air volume by a user.
Meanwhile, in Embodiment 10, the outdoor unit 100 includes a compressor 101, a four-way valve 102, an outdoor-side heat exchanger 103, an outdoor-side air-sending device 104, and the expansion device (expansion valve) 105.
The compressor 101 is configured to compress and discharge sucked refrigerant. The compressor 101 includes, for example, an inverter device so that a capacity of the compressor 101 (amount of refrigerant sent per unit time) can be finely changed by suitably changing an operating frequency. The four-way valve 102 is configured to switch flow of refrigerant during the cooling operation and flow of refrigerant during the heating operation based on an instruction from a controller (not shown).
Further, the outdoor-side heat exchanger 103 is configured to exchange heat between refrigerant and air (outdoor air). For example, the outdoor-side heat exchanger 103 functions as an evaporator during the heating operation. The outdoor-side heat exchanger 103 is configured to exchange heat between low-pressure refrigerant flowing in from the liquid pipe 400 and air so that the refrigerant is evaporated and gasified. Further, the outdoor-side heat exchanger 103 functions as a condenser during the cooling operation. The outdoor-side heat exchanger 103 is configured to exchange heat between refrigerant having been compressed in the compressor 101 and flowed in from the four-way valve 102 side and air so that the refrigerant is condensed and liquified. The outdoor-side heat exchanger 103 includes the outdoor-side air-sending device 104. Also in the outdoor-side air-sending device 104, a rotation speed of a fan may be finely changed by suitably changing an operating frequency of the fan motor 4 by an inverter device. Further, the air-sending portion 20 in Embodiment 1 to Embodiment 9 may be used as the outdoor-side air-sending device 104. The expansion device 105 is provided to adjust, for example, a pressure of refrigerant by changing an opening degree.
As described above, the air-conditioning apparatus according to Embodiment 10 includes the indoor unit described in Embodiment 1 to Embodiment 9. Thus, improvement in efficiency and reduction in noise can be attained due to improvement in air volume and static pressure effect.
Although the details of the present invention are specifically described above with reference to the preferred embodiments, it is apparent that persons skilled in the art may adopt various modifications based on the basic technical concepts and teachings of the present invention.
In Embodiment 1 to Embodiment 10 described above, application to the air-conditioning apparatus is described. However, the present invention is not limited to those apparatus, and may be applied to, for example, other refrigeration cycle apparatus such as a freezing machine or a water heater, which form a refrigerant circuit, and are configured to perform cooling, dehumidification, or humidification.
| Number | Date | Country | Kind |
|---|---|---|---|
| PCT/JP2016/082241 | Oct 2016 | WO | international |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2017/039127 | 10/30/2017 | WO | 00 |
| Publishing Document | Publishing Date | Country | Kind |
|---|---|---|---|
| WO2018/079776 | 5/3/2018 | WO | A |
| Number | Name | Date | Kind |
|---|---|---|---|
| 6105383 | Reimann et al. | Aug 2000 | A |
| 20090145583 | Han | Jun 2009 | A1 |
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| Chinese Office Action dated Mar. 1, 2021, issued in corresponding Chinese Patent Application No. 201780064743.7 (and English Machine Translation). |
| Decision of Rejection dated Jun. 25, 2021, issued in corresponding Korean Patent Application No. 10-2019-7006330 (and English Machine Translation). |
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| Office Action dated May 28, 2020 issued in corresponding CN patent application No. 201780064743.7 (and English translation). |
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| Number | Date | Country | |
|---|---|---|---|
| 20190242612 A1 | Aug 2019 | US |
