Patent Application
20140250936
The present invention relates to a heat exchange unit and a refrigeration device.
A variety of types of heat exchangers conventionally exist, such as the heat exchanger disclosed in Patent Literature 1 (JP-A 2011-99664). In the heat exchanger disclosed in Patent Literature 1, heat is exchanged between a refrigerant flowing in the interior and passing air passing the exterior.
Conventionally, a plurality of heat exchangers may be used in an integrated manner due to a manufacturing problem or the like. For example, if the heat exchanger size intended for use is relatively large so as to present a problem in terms of manufacturing work efficiency during manufacture, heat exchangers divided into a plurality may be arranged in the vertical direction and used as a single heat exchange unit.
However, when a plurality of heat exchangers are assembled, gaps are thought to form between each of the heat exchangers. Therefore, when the heat exchange unit is made to function as an evaporator, condensation water is likely to accumulate at a lower end portion of a heat exchanger disposed at higher position. When the accumulated condensation water turns into frost, there is a concern that the heat exchange efficiency of the heat exchange unit will decrease.
Accordingly, the present invention addresses the problem of providing a heat exchange unit and a refrigeration device in which drainage performance is improved.
A heat exchange unit according to a first aspect of the present invention includes a first heat exchanger, a second heat exchanger, and a water guiding member. The first heat exchanger has a first heat exchange part. The first heat exchange part exchanges heat between a refrigerant flowing in the interior and passing air passing the exterior. The second heat exchanger is integrated with the first heat exchanger and has a second heat exchange part. The second heat exchange part is disposed below the first heat exchange part and adapted for exchanging heat between the refrigerant flowing in the interior and passing air passing the exterior. The water guiding member is disposed between the first heat exchange part and the second heat exchange part and adapted for guiding condensation water generated in the first heat exchange part to the second heat exchange part.
Conventionally, when a plurality of heat exchangers are assembled and used as a single heat exchange unit due to a manufacturing problem or the like, a problem is presented in that gaps form between each of the heat exchangers, therefore making it more likely for condensation water to accumulate at a lower end portion of a heat exchanger disposed at a higher position. When the accumulated condensation water turns into frost, there is a concern that the heat exchange efficiency of the heat exchanger will decrease.
Therefore, in the present invention, a water guiding member is disposed between a first heat exchange part and a second heat exchange part disposed below the first heat exchange part. Condensation water generated on the first heat exchange part is thereby guided to the second heat exchange part. In other words, the condensation water can be guided downwards and thereby inhibited from accumulating at a lower end portion of the first heat exchange part. In other words, it is possible to improve drainage performance in the heat exchange unit and inhibit a decrease in the heat exchange efficiency of the first heat exchange part.
A heat exchange unit according to a second aspect of the present invention is the heat exchange unit according to the first aspect, wherein the first heat exchanger further has a first header connecting to both ends of the first heat exchange part and extending vertically. In addition, the second heat exchanger further has a second header connecting to both ends of the second heat exchange part and extending vertically. In addition, the first header and the second header are of different size.
Even in an instance, such as in the present invention, in which a plurality of heat exchangers are assembled and used as a heat exchange unit due to heads being of different size, since the water guiding member is disposed between the first heat exchange part and the second heat exchange part, it is possible to guide the condensation water generated in the first heat exchange part to the second heat exchange part, i.e., downwards, and improve drainage performance.
A heat exchange unit according to a third aspect of the present invention is the heat exchange unit according to the first or second aspects, wherein the water guiding member is a heat transfer fin.
In the present invention, using heat transfer fins such as those normally used in heat exchangers are used as water guiding members makes it possible to improve drainage performance in a simple manner. In addition, it is possible to further increase the heat transfer area and thereby improve the heat exchange efficiency in the heat exchange unit.
A heat exchange unit according to a fourth aspect of the present invention is the heat exchange unit according to any of first through third aspects of the present invention, wherein the first heat exchange part has a plurality of first flat pipes arranged vertically, and first heat transfer fins disposed between the first flat pipes. In addition, the second heat exchange part has a plurality of second flat pipes arranged vertically, and second heat transfer fins disposed between the second flat pipes. The water guide members are in contact with the first heat transfer fins and the second heat transfer fins.
In the present invention, the water guiding members are in contact with the first heat transfer fins and the second heat transfer fins, whereby condensation water generated in the first heat exchange part can be readily guided to the second heat exchange part, i.e., downwards.
A refrigeration device according to a fifth aspect of the present invention includes the heat exchange unit according to any of first through fourth aspects, a compression mechanism, an intermediate refrigerant pipe, and a switching mechanism. The compression mechanism has a first compression element for compressing the refrigerant and a second compression element for further compressing the refrigerant compressed by the first compression element. The intermediate refrigerant pipe is a pipe for causing the refrigerant compressed by the first compression element to be taken in by the second compression element. The switching mechanism switches a flow of the refrigerant compressed by the second compression element, and is thereby capable of switching between a cooling operation and a heating operation. The second heat exchanger is provided to the intermediate refrigerant pipe, functions during the cooling operation as a heat radiator for the refrigerant compressed in the first compression element and taken in by the second compression element, and functions during the heating operation as an evaporator for the refrigerant compressed by the second compression element. The first heat exchanger functions during the cooling operation as a heat radiator for the refrigerant compressed by the second compression element, and functions during the heating operation, with the second heat exchanger, as an evaporator for the refrigerant compressed by the second compression element.
There may be an instance in which, as in the present invention, the first heat exchanger and the second heat exchanger perform different tasks during a cooling operation, resulting in the density of the refrigerant at the outlet of the first heat exchanger and the density of the refrigerant at the outlet of the second heat exchanger being different. Therefore, a plurality of heat exchangers may be used as a single heat exchange unit. In the present invention, even under such a circumstance, the water guiding member being disposed makes it possible to improve the drainage performance.
In the heat exchange unit according to the first aspect of the present invention, the drainage performance can be improved.
In the heat exchange unit according to the second aspect of the present invention, the drainage performance can be improved even in an instance in which a plurality of heat exchangers are assembled and used as a single heat exchange unit due to the heads being of different size.
In the heat exchange unit according to the third aspect of the present invention, the drainage performance can be improved in a simple manner.
In the heat exchange unit according to the fourth aspect of the present invention, the condensation water generated on the first heat exchange part can be more readily guided to the second heat exchange part.
In the refrigeration device according to the fifth aspect of the present invention, the drainage performance can be improved.
An embodiment of an air-conditioning device will now be described with reference to the accompanying drawings as an example of a refrigeration device including a heat exchange unit 4 according to the present invention.
The air-conditioning device 1 is a device which has a refrigerant circuit 10 configured so as to be capable of switching between cooling operation and heating operation, and which performs a two-stage compression type refrigeration cycle using a refrigerant that works in the supercritical region (carbon dioxide in the present embodiment).
The refrigerant circuit 10 of the air-conditioning device 1 primarily has a compression mechanism 2, a switching mechanism 3, a heat exchange unit 4 (first heat exchanger 40 and second heat exchanger 60), an expansion mechanism 5, and a usage-side heat exchanger 6. Constituent elements of the refrigerant circuit 10 will now be described below.
(2-1) The compression mechanism 2 comprises a compressor for performing two-stage compression on the refrigerant using two compression elements. The compression mechanism 2 has a sealed structure in which a compression mechanism driving motor 21b, a driving shaft 21c, a first compression element 2c, and a second compression element 2d are housed in a casing 21a. The compression mechanism driving motor 21b is connected to the driving shaft 21c. The driving shaft 21c is connected to the first compression element 2c and the second compression element 2d. In other words, the compression mechanism 2 has a “uniaxial two-stage compression structure” in which the first compression element 2c and the second compression element 2d are connected to the single driving shaft 21c, and the first compression element 2c and the second compression element 2d are both rotationally driven by the compression mechanism driving motor 21b. Each of the first compression element 2c and the second compression element 2d is a rotary-type, a screw-type, or another positive displacement-type compressive element. The compression mechanism 2 is configured to: take in a refrigerant from an intake pipe 2a; compressing, using the first compression element 2c, the refrigerant which has been taken in, and then discharging the refrigerant into an intermediate refrigerant pipe 8 (described further below); and causing the refrigerant discharged into the intermediate refrigerant pipe 8 to be taken in by the second compression element 2d, further compressing the refrigerant, and then discharging the refrigerant into a discharge pipe 2b. The intermediate refrigerant pipe 8 is a refrigerant pipe for causing the refrigerant, which has been compressed by and discharged from the first compression element 2c connected to the upstream side of the second compression element 2d, to be taken in by the second compression element 2d connected to the downstream side of the first compression element 2c. The discharge pipe 2b is a refrigerant pipe for sending the refrigerant discharged from the compression mechanism 2 to the first heat exchanger 40. The discharge pipe 2b is provided with an oil separation mechanism 22 and a check mechanism 23. The oil separation mechanism 22 is a mechanism for separating the refrigeration oil, which accompanies the refrigerant discharged from the compression mechanism 2, from the refrigerant and returning the refrigeration oil to the intake side of the compression mechanism 2, and primarily has: an oil separator 22a for separating, from the refrigerant, the refrigeration oil accompanying the refrigerant discharged from the compression mechanism 2; and an oil return pipe 22b, which is connected to the oil separator 22a and which returns the refrigeration oil separated from the refrigerant to the intake pipe 2a of the compression mechanism 2. The oil return pipe 22b is provided with a depressurization mechanism 22c for depressurizing the refrigeration oil flowing in the oil return pipe 22b. A capillary tube is used for the depressurization mechanism 22c. The check mechanism 23 is a mechanism for allowing the flow of the refrigerant from the discharge side of the compression mechanism 2 to the switching mechanism 3, and blocking the flow of the refrigerant from the switching mechanism 3 to the discharge side of the compression mechanism 2. A check value is used for the check mechanism 23.
As described above, the compression mechanism 2 has two compression elements 2c, 2d, and is configured so that the refrigerant is: compressed by the first compression element 2c, which is the more upstream element of the compression elements 2c, 2d; discharged; and further compressed by the second compression element 2d on the downstream side. The compression mechanism 2 is not limited to a single compression mechanism having a uniaxial two-stage compression structure as in the present embodiment, and may be a compression mechanism having a three-stage compression type or otherwise having more stages than a two-stage compression type. In addition, a multistage compression mechanism may be configured by serially connecting a plurality of compressors incorporating a single compression element and/or compressors incorporating a plurality of compression elements. It is also possible to use a parallel multistage compression-type compression mechanism in which two or more lines of multistage compression-type compressors are connected in parallel.
The switching mechanism 3 is a mechanism for switching the direction of refrigerant flow in the refrigerant circuit 10. The switching mechanism 3 is a four-way switch valve connected to the intake side of the compression mechanism 2, the discharge side of the compression mechanism 2, the first heat exchanger 40, and the usage-side heat exchanger 6. During a cooling operation, the switching mechanism 3 connects the discharge side of the compression mechanism 2 and one end of the first heat exchanger 40 to each other, and connects the intake side of the compression mechanism 2 and the usage-side heat exchanger 6 to each other, in order to cause the first heat exchanger 40 to function as a heat radiator for the refrigerant compressed by the compression mechanism 2, and to cause the usage-side heat exchanger 6 to function as an evaporator for the refrigerant which has been caused to release heat in the first heat exchanger 40 (see solid lines in the switching mechanism 3 in
As described above, the switching mechanism 3 is configured so as to be capable of switching between a cooling operation and a heating operation by switching the direction of flow of the refrigerant compressed by the compression mechanism 2 (second compression element 2d).
The heat exchange unit 4 has a plurality of heat exchangers (first heat exchanger 40 and second heat exchanger 60 in the present embodiment). The heat exchange unit 4 exchanges heat between the refrigerant flowing in the interior and passing air A passing the exterior (see
(2-3-1) First Heat Exchanger 40
The first heat exchanger 40 functions as a heat radiator for the refrigerant compressed by the compression mechanism 2 (second compression element 2d) during a cooling operation, and functions as an evaporator for the refrigerant which has been compressed by the compression mechanism 2 (second compression element 2d) and caused to release heat in the usage-side heat exchanger 6 during a heating operation.
One end of the first heat exchanger 40 is connected to the switching mechanism 3, and the other end of the first heat exchanger 40 is connected to the expansion mechanism 5. A specific configuration of the first heat exchanger 40 will be described further below. The passing air passing the exterior of the first heat exchanger 40 is fed by a fan 50 (see
(2-3-2) Second Heat Exchanger 60
The second heat exchanger 60 is disposed below the first heat exchanger 40, and is provided to the intermediate refrigerant pipe 8. The second heat exchanger 60 is configured so that one end is connected to the first compression element 2c and the other end is connected to the second compression element 2d. During a cooling operation, the second heat exchanger 60 functions as a heat radiator for the refrigerant which is at an intermediate pressure in a refrigeration cycle and which is compressed by the first compression element 2c on the upstream side and taken in by the second compression element 2d on the downstream side, in order to improve the performance during a cooling operation. During a heating operation, the second heat exchanger 60 functions, together with the first heat exchanger 40, as an evaporator for the refrigerant which has been compressed by the second compression element 2d and caused to release heat in the usage-side heat exchanger 6, in order to improve the performance during a heating operation. A specific configuration of the second heat exchanger 60 will be described further below. The passing air passing the exterior of the second heat exchanger 60 is fed by a fan 50.
The intermediate refrigerant pipe 8 is further provided with a first electromagnetic valve 17, a second electromagnetic valve 18, and a three-way valve 16 functioning as a switching mechanism. The three-way valve 16 is a valve capable of switching between a first state of connecting the discharge side of the first compression element 2c and one end of the second heat exchanger 60, and a second state of connecting the intake side of the compression mechanism 2 (or more specifically, the intake side of the first compression element 2c) and one end of the second heat exchanger 60. The first electromagnetic valve 17 and the second electromagnetic valve 18 are valves that are controlled so as to open/close in order to cause the second heat exchanger 60 to function as a heat radiator for the refrigerant compressed by the first compression element 2c during a cooling operation only. The first electromagnetic valve 17 is provided to a fifth refrigerant pipe 8e described further below, and the second electromagnetic valve 18 is provided to a second refrigerant pipe 8b described further below.
The intermediate refrigerant pipe 8 has: a first refrigerant pipe 8a for connecting the discharge side of the first compression element 2c of the compression mechanism 2 and the three-way valve 16; the second refrigerant pipe 8b for connecting the three-way valve 16 and one end of the second heat exchanger 60 (refrigerant inlet side during a cooling operation); a third refrigerant pipe 8c for connecting the other end of the second heat exchanger 60 and the intake side of the second compression element 2d of the compression mechanism 2; a fourth refrigerant pipe 8d for connecting the three-way valve 16 and the intake pipe 2a; and a fifth refrigerant pipe 8e for providing a bypass from the second refrigerant pipe 8b to the third refrigerant pipe 8c.
In the present embodiment, in order to cause the second heat exchanger 60 to function as an evaporator during a heating operation, a return pipe 8f is provided on the side of the refrigerant inlet, during a heating operation, of the first heat exchanger 40. Specifically, the return pipe 8f is a refrigerant pipe capable of branching a part of the refrigerant flowing between the usage-side heat exchanger 6 and the first heat exchanger 40 and returning the refrigerant to the third refrigerant pipe 8c, and is configured so as to connect a portion between the expansion mechanism 5 and the first heat exchanger 40 with the third refrigerant pipe 8c. The return pipe 8f is provided with a return valve 19 which can be opened and closed.
The expansion mechanism 5 is a mechanism for depressurizing the refrigerant, and an electric expansion valve is used. One end of the expansion mechanism 5 is connected to the heat exchange unit 40 and the other end of the expansion mechanism 5 is connected to the usage-side heat exchanger 6. During a cooling operation, the expansion mechanism 5 depressurizes the high-pressure refrigerant, which has been caused to release heat in the first heat exchanger 40, prior to sending the refrigerant to the usage-side heat exchanger 6. During a heating operation, the expansion mechanism 5 depressurizes the high-pressure refrigerant, which has been caused to release heat in the usage-side heat exchanger 6, prior to sending the refrigerant to the first heat exchanger 40.
The usage-side heat exchanger 6 is a heat exchanger which may function as an evaporator or a heat radiator for the refrigerant. One end of the usage-side heat exchanger 6 is connected to the expansion mechanism 5 and the other end of the usage-side heat exchanger 6 is connected to the switching mechanism 3. Although not shown, the usage-side heat exchanger 6 is configured so that water and/or air, which functions as a heating source or a cooling source for exchanging heat with the refrigerant flowing in the usage-side heat exchanger 6, is supplied to the usage-side heat exchanger 6.
The air-conditioning device 1 has the control unit 9 for controlling the actuation of various parts constituting the air-conditioning device 1, such as the compression mechanism 2, the switching mechanism 3, the expansion mechanism 5, the fan 50, the three-way valve 16, the first electromagnetic valve 17, the second electromagnetic valve 18, and the return valve 19.
A variety of sensors provided to the air-conditioning device 1 are connected to the control unit 9. The variety of sensors may include, e.g., a first heat exchange temperature sensor 51, a second heat exchange outlet temperature sensor 52, and an air temperature sensor 53. The first heat exchange temperature sensor 51 is a sensor which is provided to the first heat exchanger 40 and which detects the temperature of the refrigerant flowing in the first heat exchanger 40. The second heat exchange outlet temperature sensor 52 is a sensor which is provided to the outlet of the second heat exchanger 60 and which detects the temperature of the refrigerant at the outlet of the second heat exchanger 60. The air temperature sensor 53 is a sensor which is provided to the main body of the air-conditioning device 1 and which detects the temperature of air functioning as a heat source for the first heat exchanger 40 and the second heat exchanger 60.
As shown in
The first heat exchanger 40 is a microchannel heat exchanger primarily having the first heat exchange part 41 for exchanging heat between the refrigerant flowing in the interior and air, and a pair of first headers 42, 42 connected to both ends, in the longitudinal direction (lateral direction in the drawing in
(4-1-1) First Heat Exchange Part 41
The first heat exchange part 41 has a plurality of first flat pipes 43 and first wave-shaped fins 44 disposed between the first flat pipes 43.
(4-1-1-1) First Flat Pipe 43
The first flat pipes 43 are pipe members made from a plate-shaped metal (e.g., aluminum or an aluminum alloy) extending so as to be elongated in a direction (more specifically, a horizontal direction) perpendicular to a longitudinal direction of the first headers 42, 42 (upright direction). The first flat pipes 43 are disposed so as to be arranged along the vertical direction (upright direction) so that large-width flat parts 43b extending in the horizontal direction are facing the vertical direction (upright direction) and a predetermined spacing is present between the first flat pipes 43. Each of the first flat pipes 43 has a plurality of refrigerant channel holes 43a for channeling the refrigerant formed so as to penetrate the first flat pipe 43 in a longitudinal direction thereof (horizontal direction) (see
(4-1-1-2) First Wave-Shaped Fin 44
The first wave-shaped fins 44 are heat transfer fins, made from a metal (e.g., aluminum or an aluminum alloy), having a wave-shaped profile. More specifically, each of the first wave-shaped fins 44 is configured by a plate-shaped member folded into a wave shape along the longitudinal direction of the first flat pipes 43 so that hill portions and valley portions are formed, the plate-shaped member having a greater length (L2) in the width direction (more specifically, a direction orthogonal, in the horizontal direction, to the longitudinal direction of the first flat pipes 43) than the length (L1) of the first flat pipes 43 in the width direction. The first wave-shaped fins 44 being disposed between the flat pipes secures a larger heat transfer area. Therefore, heat is exchanged in an efficient manner between the refrigerant flowing in the first flat pipes 43 (refrigerant channel holes 43a) and the passing air passing the exterior of the first heat exchange part 41.
Each of the first wave-shaped fins 44 is H-shaped when viewed along the longitudinal direction of the first flat pipes 43, and, as shown in
The main fin body 45 is a portion disposed between the first flat pipes 43 (more specifically, between an upper surface 43c, which is an upper surface of the flat part 43b of a first flat pipe 43, and a lower surface 43d, which is a lower surface of the flat part 43b of a first flat pipe 43 vertically adjacent to the former first flat pipe 43). The main fin body 45 is fixed to the first flat pipe 43 so that an upper edge 45a of the hill portion is in contact with the lower surface 43d and a lower edge 45b of the valley portion is in contact with the upper surface 43c. The location of contact between the first flat pipe 43 and the main fin body 45 is bonded by brazing or a similar technique.
The main fin body 45 has a plurality of cut-and-raised portions 45c formed by cutting and raising a vertically central portion of the main fin body 45 in order to improve heat exchange efficiency. The cut-and-raised portions 45c are cut and raised to a louver shape, and formed so that a portion on the upstream side and a portion on the downstream side, with respect to the direction of flow of the passing air A, are inclined in opposite directions with respect to the direction of flow of the passing air A.
The fin fringe parts 46 are portions that protrude outwards with respect to the width direction of the first flat pipes 43 (more specifically, in both widthwise outward directions) from the main fin body 45. The height position of an upper edge of an upper edge part 46a of each of the fin fringe parts 46 is higher than the lower surface 43d of the first flat pipe 43, and the height position of a lower edge of a lower edge part 46b of each of the fin fringe parts 46 is lower than the upper surface 43c of the first flat pipe 43. This is achieved by forming, in advance, incisions along the width direction at both widthwise edge parts of the plate-shaped member, whereby only the main fin body 45 is folded when the plate-shaped member is folded to a wave shape and the first wave-shaped fins 44 are formed. In other words, the above incisions are formed in advance in the plate-shape member, whereby the upper edge part 46a and the lower edge part 46b of each of the fin fringe parts 46 are kept in a cut and raised state without being folded. The upper edge of the upper edge part 46a and the lower edge of the lower edge part 46b of each of the fin fringe parts 46 are configured so as to extend in the horizontal direction.
In the present embodiment, the first wave-shaped fins 44 are configured so that the fin fringe parts 46 of vertically adjacent first wave-shaped fins 44 are in contact with each other (more specifically, so that the upper edges of the upper edge parts 46a of a fin fringe part 46 are in contact with the lower edges of the lower edge parts 46b of another fin fringe part 46).
(4-1-2) First Headers 42, 42
The pair of first headers 42, 42 are disposed so as to be set apart from each other and so that each of the first headers 42, 42 extends in the upright direction. Each of the first headers 42 is a metal (more specifically, aluminum, an aluminum alloy, or the like) member having a cylindrical shape in which upper and lower ends are closed.
An opening 40a for causing the refrigerant to flow into the first heat exchanger 40 or causing the refrigerant to flow out from the first heat exchanger 40 is formed at a lower portion of one of the first headers 42, 42 and an upper portion of the other first header 42. A refrigerant channel 42a which communicates with the opening 40a and which channels the refrigerant is formed in the first header 42. The refrigerant channel 42a is formed so that the refrigerant flows in the vertical direction, and communicates with the refrigerant channel holes 43a formed in the first flat pipes 43.
(4-1-3) Flow of Refrigerant in the First Heat Exchanger 40
During a cooling operation (in an instance in which the first heat exchanger 40 functions as a heat radiator for the refrigerant), the refrigerant flows from the first header 42 on the right side of the drawing in
Meanwhile, during a heating operation (when the first heat exchanger 40 functions as an evaporator for the refrigerant), the refrigerant flows from the first left side header to the first right side header. Specifically, the low-pressure refrigerant in a gas-liquid two-phase state, which has flowed from the expansion mechanism 5, flows into the refrigerant channel 42a of the first left side header through the opening 40a of the first left side header. The refrigerant, which has flowed into the refrigerant channel 42a of the first left side header, is split between the first flat pipes 43, apportioned between the refrigerant channel holes 43a formed in the first flat pipes 43, and caused to flow into the refrigerant channel 42a formed in the first right side header. The low-pressure refrigerant in a gas-liquid two-phase state exchanges heat with the passing air passing the exterior, and is thereby heated and caused to evaporate. The refrigerant which has flowed into the refrigerant channel 42a of the first right side header flows through the opening 40a formed in the first right side header back to the compression mechanism 2.
Thus, the refrigerant flowing in the first heat exchanger 40 flows from above to below during a cooling operation and flows from below to above during a heating operation.
As shown in
(4-2-1) Second Heat Exchange Part 61
The second heat exchange part 61 has a plurality of second flat pipes 63 and second wave-shaped fins 64 disposed between the second flat pipes 63.
(4-2-1-1) Second Flat Pipe 63
The second flat pipes 63 are pipe members made from a plate-shaped metal (e.g., aluminum or an aluminum alloy) extending so as to be elongated in a direction (more specifically, a horizontal direction) perpendicular to a longitudinal direction of the second headers 62, 62 (upright direction). The second flat pipes 63 are disposed so as to be arranged along the vertical direction (upright direction) so that large-width flat parts 63b extending in the horizontal direction are facing the vertical direction (upright direction) and a predetermined spacing is present between the second flat pipes 63. Each of the second flat pipes 63 has a plurality of refrigerant channel holes 63a for channeling the refrigerant formed so as to penetrate the second flat pipe 63 in a longitudinal direction thereof (horizontal direction) (see
(4-2-1-2) Second Wave-Shaped Fin 64
The second wave-shaped fins 64 are heat transfer fins, made from a metal (e.g., aluminum or an aluminum alloy), having a wave-shaped profile. More specifically, each of the second wave-shaped fins 64 is configured by a plate-shaped member folded into a wave shape along the longitudinal direction of the second flat pipes 63 so that hill portions and valley portions are formed, the plate-shaped member having a greater length (L4) in the width direction (more specifically, a direction orthogonal, in the horizontal direction, to the longitudinal direction of the second flat pipes 63) than the length (L3) of the second flat pipes 63 in the width direction. The second wave-shaped fins 64 being disposed between the flat pipes secures a larger heat transfer area. Therefore, heat is exchanged in an efficient manner between the refrigerant flowing in the second flat pipes 63 (refrigerant channel holes 63a) and the passing air passing the exterior of the second heat exchange part 61.
Each of the second wave-shaped fins 64 has, as shown in
The main fin body 65 is a portion disposed between the second flat pipes 63 (more specifically, between an upper surface 63c, which is an upper surface of the flat part 63b of a second flat pipe 63, and a lower surface 63d, which is a lower surface of the flat part 63b of a second flat pipe 63 vertically adjacent to the former second flat pipe 63). The main fin body 65 is fixed to the second flat pipe 63 so that an upper edge 65a of the hill portion is in contact with the lower surface 63d and a lower edge 65b of the valley portion is in contact with the upper surface 63c. The location of contact between the second flat pipe 63 and the main fin body 65 is bonded by brazing or a similar technique.
The main fin body 65 has a plurality of cut-and-raised portions 65c formed by cutting and raising a vertically central portion of the main fin body 65 in order to improve heat exchange efficiency. The cut-and-raised portions 65c are cut and raised to a louver shape, and formed so that a portion on the upstream side and a portion on the downstream side, with respect to the direction of flow of the passing air A, are inclined in opposite directions with respect to the direction of flow of the passing air A.
The fin fringe parts 66 are portions that protrude outwards with respect to the width direction of the second flat pipes 63 (more specifically, in both widthwise outward directions) from the main fin body 65. The height position of an upper edge of an upper edge part 66a of each of the fin fringe parts 66 is higher than the lower surface 63d of the second flat pipe 63, and the height position of a lower edge of a lower edge part 66b of each of the fin fringe parts 66 is lower than the upper surface 63c of the second flat pipe 63. This is achieved by forming, in advance, incisions along the width direction at both widthwise edge parts of the plate-shaped member, whereby only the main fin body 65 is folded when the plate-shaped member is folded to a wave shape and the second wave-shaped fins 64 are formed. In other words, the above incisions are formed in advance in the plate-shape member, whereby the upper edge part 66a and the lower edge part 66b of each of the fin fringe parts 66 are kept in a cut and raised state without being folded. The upper edge of the upper edge part 66a and the lower edge of the lower edge part 66b of each of the fin fringe parts 66 are configured so as to extend in the horizontal direction.
In the present embodiment, the second wave-shaped fins 64 are configured so that the fin fringe parts 66 of vertically adjacent second wave-shaped fins 64 are in contact with each other (more specifically, so that the upper edges of the upper edge parts 66a of a fin fringe part 66 are in contact with the lower edges of the lower edge parts 66b of another fin fringe part 66).
In the present embodiment, the first flat pipes 43 of the first heat exchanger 40 and the second flat pipes 63 of the second heat exchanger 60, and the first wave-shaped fins 44 of the first heat exchanger 40 and the second wave-shaped fins 64 of the second heat exchanger 60 have the same configuration. Therefore, length L1 and length L3 are identical, and length L2 and length L4 are identical.
(4-2-2) Second Headers 62, 62
The pair of second headers 62, 62 are disposed so as to be set apart from each other and so that each of the second headers 62, 62 extends in the upright direction. Each of the second headers 62, 62 is a metal (more specifically, aluminum, an aluminum alloy, or the like) member having a cylindrical shape in which upper and lower ends are closed.
An opening 60a for causing the refrigerant to flow into the second heat exchanger 60 or causing the refrigerant to flow out from the second heat exchanger 60 is formed at a lower portion of one of the second headers 62, 62 and an upper portion of the other second header 62. A refrigerant channel 62a which communicates with the opening 60a and which channels the refrigerant is formed in the second header 62. The refrigerant channel 62a is formed so that the refrigerant flows in the vertical direction, and communicates with the refrigerant channel holes 63a formed in the second flat pipes 63.
(4-2-3) Flow of Refrigerant in the Second Heat Exchanger 60
During a cooling operation (in an instance in which the second heat exchanger 60 functions as a heat radiator for the refrigerant), the refrigerant flows from the second header 62 on the right side of the drawing in
Meanwhile, during a heating operation (when the second heat exchanger 60 functions as an evaporator for the refrigerant), the refrigerant flows from the second left side header to the second right side header. Specifically, the low-pressure refrigerant in a gas-liquid two-phase state, which has flowed through the return pipe 8f from the expansion mechanism 5, flows into the refrigerant channel 62a of the second left side header through the opening 60a of the second left side header. The refrigerant, which has flowed into the refrigerant channel 62a of the second left side header, is split between the second flat pipes 63, apportioned between the refrigerant channel holes 63a formed in the second flat pipes 63, and caused to flow into the refrigerant channel 62a formed in the second right side header. The low-pressure refrigerant in a gas-liquid two-phase state exchanges heat with the passing air passing the exterior, and is thereby caused to evaporate. The refrigerant which has flowed into the refrigerant channel 62a of the second right side header flows through the opening 60a formed in the second right side header back to the compression mechanism 2.
Thus, the refrigerant flowing in the second heat exchanger 60 flows from above to below during a cooling operation and flows from below to above during a heating operation.
In the present embodiment, the inside diameter of the second header 62 (i.e., the diameter of a refrigerant channel-forming part forming the refrigerant channel 62a) is set so as to be greater than the inside diameter of the first header 42 (i.e., the diameter of a refrigerant channel-forming part forming the refrigerant channel 42a). In other words, the first headers 42 and the second headers 62 are designed so that they are of different size.
This is because, as described above, the first heat exchanger 40 and the second heat exchanger 60 perform different tasks during a cooling operation. Specifically, during a cooling operation, the density of the refrigerant at the outlet of the first heat exchanger 40 (i.e., the refrigerant that has flowed out to the exterior from the first left side header) is about four times higher than the density of the refrigerant at the outlet of the second heat exchanger 60 (i.e., the refrigerant that has flowed out to the exterior from the second left side header). Therefore, the inside diameter of the second header 62 is set so as to be larger than the inside diameter of the first header 42 in order to reduce the loss of pressure of the refrigerant.
In the present embodiment, as described above, the first headers 42, 42 of the first heat exchange part 41 and the second headers 62, 62 are of different size (more specifically, have different inside diameters). There may be instances in which a plurality of heat exchangers are assembled and used as a single heat exchange unit due to the density of the refrigerant passing through the respective heat exchangers being different as described above. However, when a plurality of heat exchangers are arranged in the vertical direction and used as a single heat exchange unit, a gap is formed between the heat exchangers (in the present embodiment, between the first heat exchange part of the first heat exchanger and the second heat exchange part of the second heat exchanger).
During a heating operation (i.e., when the first heat exchanger and the second heat exchanger are caused to function as evaporators for the refrigerant), condensation water may be generated on the surface of the first heat exchanger and the second heat exchanger by air passing the exterior of the first heat exchanger and the second heat exchanger losing heat to the refrigerant flowing through the interior of the flat pipes.
Therefore, when there is a gap between the first heat exchanger and the second heat exchanger, the condensation water generated on the first heat exchanger may flow downwards and accumulate at a lower end portion of the first heat exchanger. When the condensation water is cooled further, turns into frost, and adheres to the surface of the lower end portion of the first heat exchanger, there is a concern that the heat exchange efficiency of the first heat exchanger will decrease.
Therefore, the heat exchange unit 4 of the present embodiment has, in addition to the first heat exchanger 40 and the second heat exchanger 60, water guiding fins 70 functioning as water guiding members for guiding condensation water generated on the first heat exchange part 41 to the second heat exchange part 61 and further to a condensation water storage part (not shown) for storing the condensation water, located below the second heat exchange part 61.
The water guiding fins 70 are thermally conductive heat transfer fins disposed between the first heat exchange part 41 and the second heat exchange part 61. In the present embodiment, the same fins as those used as the wave-shaped fins 44, 64 in the first heat exchanger 40 and the second heat exchanger 60 are used for the water guiding fins 70. Specifically, each of the water guiding fins 70 has: a main fin body 75 disposed between the first flat pipe 43 disposed at the lowermost level from among the plurality of the first flat pipes 43 and the second flat pipe 63 disposed at the uppermost level from among the plurality of the second flat pipes 63 (more specifically, between the lower surface 43d of the first flat pipe 43 disposed at the lowermost level of the first heat exchange part 41 and the upper surface 63c of the second flat pipe 63 disposed at the uppermost level of the second heat exchange part 61); and fin fringe parts 76 protruding in both outward directions with respect to the width direction of the flat pipes 43, 63. The main fin body 75 has a plurality of cut-and-raised portions 75c formed by cutting and raising a vertically center portion of the main fin body 75 in order to improve heat exchange efficiency.
In the present embodiment, disposing the water guiding fins 70 between the first heat exchange part 41 and the second heat exchange part 61 makes it possible to fill the gap between the first heat exchange part 41 and the second heat exchange part 61. In addition, it becomes possible to more readily guide the condensation water generated on the first heat exchange part 41 downwards.
Since the water guiding fins 70 have the same configuration as that of the wave-shaped fins 44, 64, an upper edge of an upper edge part 76a of each of the fin fringe parts 76 of the water guiding fins 70 is positioned higher than the lower surface 43d of the first flat pipe 43, and a lower edge of a lower edge part 76b of each of the fin fringe parts 76 is positioned lower than the upper surface 63c of the second flat pipe 63. Specifically, each of the water guiding fins 70 can be positioned so as to be in contact with a first wave-shaped fin 44 of the first heat exchanger 40 (more specifically, the first wave-shaped fin 44 positioned at the lowermost level) and a second wave-shaped fin 64 of the second heat exchanger 60 (more specifically, the second wave-shaped fin 64 positioned at an uppermost level). More specifically, each of the water guiding fins 70 can be disposed so that the upper edge of the upper edge part 76a of each of the fin fringe parts 76 of the water guiding fin 70 is in contact with the lower edge of the lower edge part 46b of each of the fin fringe parts 46 of the first wave-shaped fin 44 disposed at the lowermost level from among the first wave-shaped fins 44, and so that the lower edge of the lower edge part 76b of each of the fin fringe parts 76 of the water guiding fin 70 is in contact with the upper edge of the upper edge part 66a of each of the fin fringe parts 66 of the second wave-shaped fin 64 disposed at the uppermost level from among the second wave-shaped fins 64. It thereby becomes possible to more readily guide the condensation water generated on the first heat exchange part 41 downwards. In addition, since the water guiding fins 70 are heat transfer fins, the heat transfer area can be increased and the performance can be improved.
In the present embodiment, thus using, for the water guiding members, similar fins as those used as the wave-shaped fins 44, 64 in the first heat exchanger 40 and the second heat exchanger 60 makes it possible to guide the condensation water downwards in a simple manner.
The actuation of the air-conditioning device 1 will now be described with reference to FIGS. 1 and 5-8. Operation control for the cooling operation and heating operation below is performed by the abovementioned control unit 9. In the following description, “high pressure” represents the high pressure in the refrigeration cycle (i.e., the pressure at points d and e in
During a cooling operation, the switching mechanism 3 is controlled to the state represented by solid lines in
When the compression mechanism 2 is driven with the refrigerant circuit 10 being in the state described above, the low-pressure refrigerant (see point a in
During a heating operation, the switching mechanism 3 is controlled to the state represented by dotted lines in
When the compression mechanism 2 is driven with the refrigerant circuit 10 being in the state described above, the low-pressure refrigerant (see point a in
In the present embodiment, the water guiding fins 70 functioning as water guiding members are disposed between the first heat exchange part 41 and the second heat exchange part 61.
It is thereby possible to fill the gap between the first heat exchange part 41 and the second heat exchange part 61, guide the refrigerant water generated on the first heat exchange part 41 to the second heat exchange part 61 positioned below the first heat exchange part 41, and guide the condensation water to the condensation water storage part. In other words, the drainage performance of the heat exchange unit 4 can be improved. The condensation water can be thereby prevented from accumulating between the first heat exchange part and the second heat exchange part, making it possible to suppress a decrease in the heat exchange efficiency in the first heat exchange part 41.
In the present embodiment, thermally conductive heat transfer fins are used as the water guiding fins 70. It thereby becomes possible not only to guide the condensation water downwards but also secure a larger heat transfer area and further improve the heat transfer efficiency in the heat exchange unit 4.
In addition, in the present embodiment, fins that are similar to the first wave-shaped fins 44 and the second wave-shaped fins 64 are used as the water guiding fins 70.
It thereby becomes possible to bring the water guiding fins 70 into contact with the first wave-shaped fins 44 of the first heat exchanger 40 and the second wave-shaped fins 64 of the second heat exchanger 60 as described above. Accordingly, the condensation water generated on the first heat exchange part 41 is more readily guided downwards along the water guiding fins 70, and condensation water flowing downwards along the water guiding fins 70 is more readily guided downwards along the second wave-shaped fins 64. The drainage performance of the heat exchange unit 4 can thereby be further improved.
Although an embodiment of the present invention is described above with reference to the drawings, specific configurations are not limited to the above embodiment, and can be modified without departing from the scope of the invention.
In the above embodiment, a description is given for an instance in which heat exchangers of different size, due to the usage conditions being different, are used as a single heat exchange unit. However, there may be other instances in which a plurality of heat exchangers are used as a single heat exchange unit due to, e.g., a manufacturing problem or the like.
An example is an instance in which the heat exchanger intended for use is relatively large so as to present a problem in terms of work efficiency during manufacture. In such an instance, a plurality of heat exchangers may be used as a single heat exchange unit due to it being more efficient to manufacture a plurality of heat exchangers that are a fraction of the size of the heat exchanger intended for use.
In the above embodiment, it is described that the water guiding fins 70 are in contact with the first wave-shaped fins 44 and the second wave-shaped fins 64. However, it is also possible to use water guiding fins 170 that are not in contact with the first wave-shaped fins 44 and the second wave-shaped fins 64, as shown, e.g., in
If the water guiding fins 170 are not in contact with the first wave-shaped fins 44 and the second wave-shaped fins 64, an upper edge of an upper edge part 176a of each fin fringe part 176 of the water guiding fin 170 is preferably parallel to the lower edge part 46b of each of the fin fringe parts 46 of the first wave-shaped fins 44 when viewed along the longitudinal direction of the flat pipes 43, 63, and a lower edge of a lower edge part 176b of each of the fin fringe parts 176 is preferably parallel to the upper edge of the upper edge part 66a of each of the fin fringe parts 66 of the second wave-shaped fins 64 when viewed along the longitudinal direction of the flat pipes 43, 63, as shown in
In the above embodiment, it is described that the fin fringe parts 46, 66, 76 of the first wave-shaped fins 44, second wave-shaped fins 64, and water guiding fins 70 are configured so that the respective upper edge and the lower edge extend in the horizontal direction. However, this is not provided by way of limitation.
For example, as a configurational different to the above embodiment, fin fringe parts 246 of the first wave-shaped fins 244 and fin fringe parts 266 of the second wave-shaped fins 264 may be configured, as shown in
In addition, the first wave-shaped fins 44, the second wave-shaped fins 64, and the water guiding fins 70 may also be fins in which one of the two shapes set forth in the present modification example C is employed as appropriate, or may be an appropriate combination of fins having the two shapes.
In the above embodiment, it is assumed that the respective size of the first right side header and the first left side header, and the respective size of the second right side header and the second left side header, are the same. However, this is not provided by way of limitation.
For example, since the density of the refrigerant at the outlet of the first heat exchanger 40 during a cooling operation is approximately four times the density of the refrigerant at the outlet of the second heat exchanger 60, an arrangement is also possible in which, among the second headers 62 of the second heat exchanger 60, only the second header 62 on the side of the outlet during a cooling operation is larger than the first headers 42. In other words, the size of the first header 42 and the second header 62 on the side of the inlet during a cooling operation may be the same.
The present invention is suited to a variety of potential applications in a heat exchange unit obtained by assembling a plurality of heat exchangers and a refrigeration device in which a plurality of heat exchangers are used as a single heat exchange unit.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2011-223322 | Oct 2011 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2012/075810 | 10/4/2012 | WO | 00 | 4/2/2014 |
