JP5531103B2 - Heat exchanger - Google Patents

Description

  Embodiments described herein relate generally to a heat exchanger that performs heat exchange between a refrigerant and a heat medium such as water.

  Conventionally, a water heat exchanger used for hot water supply has a heat transfer tube through which a refrigerant flows and a water heat transfer tube through which water flows are brought into direct contact with each other by brazing, or a heat transfer tube for refrigerant is installed inside the water heat transfer tube. It was inserted to promote heat transfer and exchange heat. This type of technology is disclosed in, for example, Japanese Patent Application Laid-Open No. 2006-317115.

  However, in the structure in which the heat transfer tube in which the refrigerant flows and the water heat transfer tube in which the water flows are in direct contact by brazing, or the structure in which the refrigerant heat transfer tube is inserted inside the water heat transfer tube, the manufacturing method and shape are complicated. become. As a manufacturing method, it is brazing in a furnace, for example. For this reason, a lot of in-process management occurs during production, and productivity is poor. There is a tendency that variations in the brazed portion are likely to occur.

  An object of the present invention is to provide a water heat exchanger that improves heat transfer efficiency, improves manufacturing, reduces costs, and has good space efficiency.

According to this embodiment, the fin group, the heat transfer tube for refrigerant, and the heat transfer tube for heat medium are provided. The fin group includes a plurality of fins that are long in one direction, and the plurality of fins are stacked with a gap therebetween in a posture in which the longitudinal directions are aligned with each other. The refrigerant heat transfer tube penetrates the fins in the laminating direction of the fins and is formed in a meandering shape in the longitudinal direction of the fins, and the refrigerant flows inside. The heat transfer tube for heat medium passes through the fins in the stacking direction of the fins, is adjacent to the heat transfer tube for refrigerant, and is formed in a meandering shape in the longitudinal direction of the fins, and the water flows inside. The refrigerant heat transfer tubes are installed in both side rows of the heat transfer tube along the row direction intersecting the longitudinal direction. The outer diameter of the heat transfer tube for heat medium is D, the outer diameter of the heat transfer tube for refrigerant is d, and the central row of the refrigerant heat transfer tubes passes through both sides of the heat transfer tube for heat medium in the row direction. When the distance is C, D ≧ C−d.

It is the schematic which shows roughly the heat pump type hot water supply apparatus with which the heat exchanger of 1st Embodiment is used. It is a perspective view which shows the state from which the bend pipe | tube for refrigerant | coolants and the bend pipe | tube for water were removed from the heat exchanger shown by FIG. It is a front view which shows the heat exchanger seen from the direction of F3 shown in FIG. It is a top view which shows the heat exchanger shown by FIG. It is a front view which abbreviate | omits and shows the heat exchanger shown by FIG. 2 partially while omitting a heat insulating material. It is sectional drawing of the heat exchanger shown along F6-F6 line shown by FIG. The front view which shows the state which abbreviate | omitted and partially omitted the heat insulating material and the bend pipe | tube for the heat exchanger shown by FIG. It is a top view which shows the range of F8 shown in FIG. It is sectional drawing which shows the state which cut | disconnected the bend pipe | tube for refrigerant | coolants along the F9-F9 line | wire shown by FIG. The graph which shows the temperature of the refrigerant | coolant between the inlet for refrigerant | coolants, and the outlet for refrigerant | coolants in the heat exchanger shown by FIG. It is a front view which shows the state from which the heat insulating material, the refrigerant | coolant bend pipe | tube, and the water bend pipe | tube were removed in the heat exchanger of 2nd Embodiment. It is a top view which shows a part of straight part and a bend pipe | tube for refrigerant | coolants in the heat exchanger tube for refrigerant | coolants of the heat exchanger of 3rd Embodiment. It is sectional drawing which shows the state which cut | disconnected the bend pipe | tube for refrigerant | coolants along the F13-F13 line shown by FIG.

  The heat exchanger which concerns on 1st Embodiment is demonstrated using FIGS. FIG. 1 is a schematic view schematically showing a heat pump type hot water supply apparatus 10 in which the heat exchanger 3 of the present embodiment is used. The heat exchanger 3 is used for the hot water supply apparatus 10 as an example. The heat exchanger 3 is not limited to being used in the hot water supply device 10.

  As shown in FIG. 1, the hot water supply device 10 includes a compressor 1, a heat exchanger 3, an internal heat exchanger 4, an expansion valve 5, an air heat exchanger 6, a water supply pipe unit 8, and a pump 9. And a hot water storage tank 12.

  The compressor 1, the heat exchanger 3, the internal heat exchanger 4, the expansion valve 5, and the air heat exchanger 6 are sequentially connected via the refrigerant pipe portion 2 to constitute a refrigeration cycle 11. The refrigeration cycle 11 uses carbon dioxide (CO2) as an example of a refrigerant.

  The water supply pipe section 8 is provided in the heat exchanger 3. The pump 9 is provided on one end side of the water supply pipe portion 8. The hot water storage tank 12 is provided on the other end side of the water supply pipe portion 8. Water W as a heat medium flows through the water supply pipe portion 8 by the pump 9. The water W is stored in the hot water storage tank 12 after undergoing heat exchange through the heat exchanger 3 when passing through the water supply pipe section 8. The structure of the heat exchanger 3 will be described later in detail.

  In the hot water supply apparatus 10, the high-temperature and high-pressure gaseous refrigerant L discharged from the compressor 1 flows into the heat exchanger 3. The refrigerant L exchanges heat with water flowing in the water supply pipe section 8 in the process of flowing in the heat exchanger 3.

  The refrigerant L that has exited the heat exchanger 3 has a reduced temperature due to heat exchange with the water W, and is in a liquid state. This refrigerant L then flows into the internal heat exchanger 4. In the process of flowing through the internal heat exchanger 4, the refrigerant L is heat-exchanged with the refrigerant L that has come out of the air heat exchanger 6 described later, and the temperature further decreases.

  The refrigerant L exiting the internal heat exchanger 4 reaches the expansion valve 5. The refrigerant L is decompressed by the expansion valve 5 and then flows into the air heat exchanger 6 to evaporate into a gaseous state. Next, the refrigerant exiting the air heat exchanger 6 flows into the internal heat exchanger 4. The refrigerant that has flowed into the internal heat exchanger 4 is heated by being exchanged with the refrigerant that has exited the heat exchanger 3. The refrigerant that has exited the internal heat exchanger 4 is sucked into the compressor 1.

  In the hot water supply device 10, the temperature of the water W supplied to the water supply pipe unit 8 is increased by the above operation. The water W whose temperature has risen in the heat exchanger 3 is stored in the hot water storage tank 12.

  Next, the structure of the heat exchanger 3 will be described. FIG. 2 is a perspective view showing a state in which a refrigerant bend pipe 32 and a water bend pipe 42 described later are removed from the heat exchanger 3. In FIG. 2, a heat insulating material 50 described later is indicated by a two-dot chain line.

  FIG. 3 is a front view showing the heat exchanger 3 as seen from the direction F3 shown in FIG. FIG. 3 shows a state in which the refrigerant bend pipe 32 and the water bend pipe 42 are removed from the heat exchanger 3. As shown in FIGS. 2 and 3, the heat exchanger 3 includes a fin group 20, a refrigerant heat transfer tube 30, a water heat transfer tube 40, and a heat insulating material 50.

  The fin group 20 includes a plurality of plate fins 21. The plate fin 21 is an example of a fin. The plate fins 21 may all have the same structure. The plate fins 21 are plate members that are long in one direction, and are rectangular as an example. The plate fin 21 is formed of an aluminum material as an example. The plate fin 21 is not limited to an aluminum material, and may be formed of, for example, copper, and is preferably formed of a material having good heat conductivity.

  In the plate fin 21, the longitudinal direction is indicated by an arrow X. A direction orthogonal to the longitudinal direction X is defined as a width direction Y. The width direction Y is an example of a column direction. Each plate fin 21 is laminated | stacked and arrange | positioned in parallel so that it may not contact mutually. The plate fins 21 have the same posture in the stacking direction, and have the longitudinal direction X aligned and the width direction Y aligned.

  The refrigerant heat transfer tube 30 constitutes a part of the refrigerant tube portion 2, and the refrigerant flows therein. The refrigerant heat transfer tube 30 is connected to the compressor 1 through, for example, a tube member 2a, and is connected to the internal heat exchanger 4 through, for example, a tube member 2b. These pipe members 2 a and 2 b are also part of the refrigerant pipe portion 2.

  The refrigerant heat transfer tube 30 is a portion that passes through the fin group 20 in the refrigerant tube portion 2 described above. The refrigerant heat transfer tube 30 is a single flow path that does not branch, and passes through one end 22 in the width direction Y of each plate fin 21 and the other end 23 in the width direction Y of each plate fin 21. It is provided in a meandering manner and in a meandering manner in the longitudinal direction.

  FIG. 4 is a plan view showing the heat exchanger 3. In FIG. 4, the heat insulating material 50 is indicated by a two-dot chain line. In the fin group 20 shown in FIG. 4, some of the plate fins 21 are illustrated, and the illustration of the plate fins 21 within the range Z indicated by the two-dot chain line is omitted. However, actually, the plate fins 21 are also laminated in the range Z.

  FIG. 4 shows a state in which the portion provided at the one end portion 22 of the refrigerant heat transfer tube 30 passes through the fin group 20. In FIG. 4, a water heat transfer tube 40 described later is omitted. The water heat transfer tube 40 is an example of a heat transfer tube for a heat medium. The other part of the refrigerant heat transfer tube 30 is provided at the other end.

  As shown in FIGS. 2 and 4, the refrigerant heat transfer tube 30 includes a plurality of refrigerant heat transfer tube bodies 31 and a plurality of refrigerant bend tubes 32. The structure of the refrigerant heat transfer tube body 31 is the same. The structure of the refrigerant bend pipe 32 is the same.

  The structure of the refrigerant heat transfer tube body 31 will be described. The refrigerant heat transfer tube body 31 includes a pair of straight portions 33 and a connecting portion 34 that connects the straight portions 33. The straight portion 33 is an example of a straight portion for refrigerant. The straight portion 33 is straight, and as shown in FIG. 3, the cross-sectional shape perpendicular to the direction in which the straight portion 33 extends is circular for both the inner edge 33a and the outer edge 33b.

  One of the linear portions 33 is disposed at the one end portion 22 and the other is disposed at the other end portion 23 and is disposed in parallel to each other. One straight line portion 33 and the other straight line portion face each other in the width direction Y.

  The connecting portion 34 connects one end of one straight portion 33 and one end of the other straight portion 33 so as to communicate with each other. The connection part 34 is U-shaped. The pair of linear portions 33 and the connecting portion 34 are integrally formed, and are formed, for example, by bending a single pipe member. For this reason, as for the heat exchanger tube main body 31 for refrigerant | coolants, while each linear part 33 is mutually connected via the connection part 34, the planar shape is U-shaped. All the refrigerant heat transfer tube bodies 31 have the same structure as described above.

  The refrigerant heat transfer tube main body 31 of each refrigerant heat transfer tube 30 is provided in the fin group 20 so that each straight portion 33 passes through all the plate fins 21. As shown in FIG. 3, each plate fin 21 is formed with a refrigerant insertion hole 24 through which the straight portion 33 of the refrigerant heat transfer tube body 31 passes. The refrigerant insertion hole 24 has a shape in which the straight portion 33 of the refrigerant heat transfer tube main body 31 is fitted, and the entire area of the edge of the refrigerant insertion hole 24 is in close contact with the peripheral surface of the straight portion 33 of the refrigerant heat transfer tube main body 31. doing. In order to make it adhere, for example, the heat transfer tube main body 31 for refrigerant is expanded. For this reason, the heat of the refrigerant L passing through the refrigerant heat transfer tube 30 is efficiently transmitted to each plate fin 21. The diameter of the refrigerant insertion hole 24 and the outer diameter d of the linear portion 33 are the same value.

  The posture of each straight portion 33 passing through the plate fin 21 is a posture in which each straight portion 33 is parallel to a direction orthogonal to the longitudinal direction X and the width direction Y. That is, the direction in which the center of each linear portion 33 extends is orthogonal to the directions X and Y. That is, the center of the straight portion 33 is the axis of the straight portion 33. For this reason, all the linear parts 33 are mutually parallel. As shown in FIG. 2, each refrigerant heat transfer tube main body 31 is arranged such that the opening 35 at the other end of the linear portion 33 is aligned in the longitudinal direction X. The opening 35 at the other end of the linear portion 33 is an opening to which the connecting portion 34 is not connected.

  Of the openings 35 arranged in the longitudinal direction X, the opening 35 arranged at one end in the longitudinal direction X and at one end in the width direction Y is a refrigerant inlet 36. An opening 35 disposed at the other end in the longitudinal direction X and at one end in the width direction Y is a refrigerant outlet 37. The refrigerant inlet 36 is connected to the pipe member 2a and the refrigerant L flows in. The refrigerant outlet 37 is connected to the pipe member 2b and the refrigerant L flows out.

  FIG. 5 is a front view of the heat exchanger 3 with the heat insulating material 50 omitted and a part of the heat exchanger 3 viewed from the opening 35 side at the other end of the linear portion 33. As shown in FIGS. 4 and 5, the refrigerant bend pipe 32 is connected so as to communicate with the opening 35 of the linear portion 33 of the refrigerant heat transfer pipe main body 31 adjacent in the longitudinal direction X. The pair of straight portions 33 of each heat transfer tube body 31 for each refrigerant are connected to each other in the width direction Y by a connecting portion 34. With this structure, the refrigerant heat transfer tube forms one line, that is, one flow path, that is, one path, that does not branch from the refrigerant inlet 36 to the refrigerant outlet 37. For this reason, as shown in FIG. 5, the refrigerant | coolant bend pipe | tube 32 which connects the linear parts 33 of the refrigerant | coolant heat exchanger tube main body 31 adjacent to the longitudinal direction X is provided alternately by the one end part and the other end part.

  With this structure, the refrigerant inlet 36 and the refrigerant outlet 37 are communicated with each other by the plurality of refrigerant heat transfer tube bodies 31 and the plurality of refrigerant bend tubes 32. Therefore, the refrigerant heat transfer tube 30 is connected to the refrigerant inlet. From the 36 to the refrigerant outlet 37, the fin group 20 is arranged to meander.

  The water heat transfer tube 40 is provided in the fin group 20 so as to meander through the fin group 20 like the refrigerant heat transfer tube 30. The water heat transfer pipe 40 is a part of the water supply pipe section 8, and is connected to the pump 9 through, for example, a pipe member 8a, and is connected to the hot water storage tank 12 through, for example, the pipe member 8b. As shown in FIG. 2, the water heat transfer tubes 40 are provided so as to pass between the refrigerant heat transfer tubes 30 provided at one end 22 and the other end 23 in the width direction Y in each plate fin 21. .

  6 is a cross-sectional view of the heat exchanger 3 taken along line F6-F6 shown in FIG. FIG. 6 is a plan view of the water heat transfer tube 40 as viewed in the width direction Y as it passes through the fin group 20. A part of the fin group 20 is omitted from the two-dot chain line. Further, from FIG. 6, the refrigerant heat transfer tube 30 provided at the other end 23 is omitted for explanation.

  As shown in FIG. 6, the water heat transfer tube 40 includes a plurality of water heat transfer tube bodies 41 and a plurality of water bend tubes 42. The water heat transfer tube main body 41 has a pair of straight portions 43 and a connecting portion 44 that connects the straight portions 43. The straight line portion 43 is an example of a straight line portion for water. The straight portion 43 is straight, and as shown in FIG. 3, the cross-sectional shape perpendicular to the direction in which the straight portion 43 extends is a circle for both the inner edge 43 a and the outer edge 43 b.

  The connection part 44 is U-shaped. Each linear part 43 is arrange | positioned so that it may mutually become parallel, and the connection part 44 has connected one opening of each linear part 43. FIG. The straight line portion 43 and the connecting portion 44 are formed integrally with each other, and are formed by bending a single pipe member, for example. For this reason, as for the heat exchanger tube main body 41 for water, while each linear part 43 is connected via the connection part 44, the planar shape is U shape.

  The water heat transfer tube main body 41 is provided in the fin group 20 so that each straight portion 43 passes through all the plate fins 21. For this reason, each plate fin 21 is formed with a water insertion hole 25 through which the straight portion 43 of the water heat transfer tube body 41 passes. The water insertion hole 25 has a shape in which the straight portion 43 of the water heat transfer tube main body 41 is fitted. Therefore, the entire area of the edge of the water insertion hole 25 is the circumference of the straight portion 43 of the water heat transfer tube main body 41. It is in close contact with the surface. In order to make it adhere, for example, the heat transfer tube main body 41 for water is expanded. For this reason, the heat of each plate fin 21 is efficiently transmitted to the heat transfer tube 40 for water. The diameter of the water insertion hole 25 and the outer diameter D of the linear portion 43 are the same value.

  As an example, the posture of the straight portion 43 passing through the plate fin 21 is a posture in which the straight portion 43 is parallel to a direction orthogonal to the longitudinal direction X and the width direction Y. That is, the center of the straight line portion 43 extends in a direction orthogonal to the directions X and Y and is parallel to the straight line portion 33. The center of the straight line portion 43 is the axis.

  As shown in FIG. 2, the water heat transfer tubes 40 are arranged so that the other openings 45 of the straight portions 43 of the water heat transfer tube main bodies 41 are aligned in the longitudinal direction X. The other opening 45 of the straight portion 43 of the water heat transfer tube body 41 is an opening to which the connecting portion 44 is not connected.

  The other opening 45 of the water heat transfer tube 40 opens to the same side as the opening 35 of the refrigerant heat transfer tube main body 31. Of the openings 45 arranged in the longitudinal direction X, the opening 45 disposed at the other end in the longitudinal direction X serves as a water inlet 46, and the opening 45 disposed at one end serves as a water outlet 47. ing. The pipe member 8a is connected to the water inlet 46, and the pipe member 8b is connected to the water outlet 47.

  The water bend pipe 42 is substantially U-shaped in plan view. The water bend pipe 42 connects the openings 45 excluding the water inlet 46 and the water outlet 47 adjacent to each other in the longitudinal direction X. With this structure, the water inlet 46 and the water outlet 47 are communicated with each other by the plurality of water heat transfer pipe bodies 41 and the plurality of water bend pipes 42. Therefore, the water heat transfer pipe 40 is connected to the water inlet. The fin group 20 is provided to meander from the water outlet 46 to the water outlet 47.

  In the present embodiment, the inner diameter of the water heat transfer tube 40 is larger than the inner diameter of the refrigerant heat transfer tube 30, and the outer diameter of the water heat transfer tube 40 is larger than the outer diameter of the refrigerant heat transfer tube 30.

  Next, the positional relationship between the refrigerant heat transfer tube 30 and the water heat transfer tube 40 will be specifically described. FIG. 7 is a front view of the heat exchanger 3 showing a state in which the heat insulating material 50 and the bend pipes 32 and 42 are omitted and partially omitted. As shown in FIG. 7, in each refrigerant heat transfer tube main body 31, one linear portion 33 disposed at one end 22 and the other linear portion 33 disposed at the other end 23 are arranged in the width direction Y. The lines that face each other and connect the center P <b> 1 of the linear portion 33 are parallel to the width direction Y.

  In one end portion 22, a line connecting the centers P <b> 1 of the linear portions 33 aligned in the longitudinal direction X is parallel to the longitudinal direction X. In the other end portion 23, a line connecting the centers P <b> 1 of the linear portions 33 aligned in the longitudinal direction X is parallel to the longitudinal direction X. The linear portions 33 of the refrigerant heat transfer tube main body 31 adjacent to each other in the longitudinal direction X are arranged at equal intervals in the longitudinal direction X at the one end portion 22 and the other end portion 23. Specifically, the pipe pitch between the linear portions 33 adjacent to each other in the longitudinal direction X at the one end portion 22 and the other end portion 23 is the length B. In other words, the distance between the centers P1 of the linear portions 33 adjacent in the longitudinal direction X is the length B. In all combinations of a pair of linear portions 33 adjacent to each other in the longitudinal direction X, the inter-pitch distance B has the same value.

  A line connecting the centers P <b> 2 of the straight portions 43 of the water heat transfer tube main bodies 41 aligned in the longitudinal direction X is parallel to the longitudinal direction X. The straight line portion 43 is disposed between the straight line portions 33 of the refrigerant heat transfer tube body 31 adjacent to each other in the longitudinal direction X. Specifically, the center P2 of the straight line portion 43 has the straight line portion 43 in the longitudinal direction X. It arrange | positions in the center between center P1 of the linear part 33 of a pair of refrigerant | coolant heat exchanger tube main bodies 31 pinched | interposed, and is arrange | positioned in the center between the centers P1 of a pair of linear part 33 which pinches | interposes the linear part 43 in the width direction Y. .

  Therefore, the straight portions 33 and 43 are arranged in a staggered manner with respect to each other. For this reason, the length of the width direction Y of each plate fin 21 can be shortened. Further, because of the arrangement structure, the water heat transfer tube 40 is disposed adjacent to the refrigerant heat transfer tube 30.

The plurality of linear portions 43 are arranged at equal intervals in the longitudinal direction X. Specifically, the pipe pitch between the straight portions 43 adjacent in the longitudinal direction X is the length A. In other words, the distance between the centers P2 of the linear portions 43 adjacent in the longitudinal direction X is the length A. In all combinations of a pair of linear portions 43 adjacent to each other in the longitudinal direction X, the inter-pitch distance A has the same value. In the present embodiment, the length A is the same length as the length B, that is, A = B.

  Further, in one refrigerant heat transfer tube 30, the center P <b> 1 of one linear portion 33 disposed at the one end portion 22 and the center of the other linear portion 33 disposed at the other end portion 23, which are opposed in the width direction Y. It is separated from P1 by a length C. In all combinations of the pair of linear portions 33 facing in the width direction Y, the center-to-center distance C has the same value.

  In the present embodiment, B> C. Since B> C, the distance between the straight portion 33 and the straight portion 43 adjacent in the width direction Y is shorter than the distance between the straight portions 33 adjacent in the longitudinal direction X. Heat exchange between the straight portions 43 is efficiently performed. If B ≧ C, the distance between the straight portion 33 and the straight portion 43 is shortened, so that heat exchange between the straight portion 33 and the straight portion 43 is performed efficiently. Since all the straight portions 33 and all the straight portions 43 are parallel to each other, the relative positional relationship between the straight portions 33 and 34 shown in FIG. 7 is the same for all the plate fins 21.

  In each plate fin 21, a heat blocking means is provided between adjacent linear portions 33. In the present embodiment, since the straight portion 33 is adjacent to the directions X and Y, a heat blocking means is provided between the straight portions 33 adjacent to each other in the longitudinal direction X and the width direction Y. The heat blocking means has a function of suppressing heat exchange between the straight portions 33 via the plate fins 21. In the present embodiment, as shown in FIG. 2, a cut 26 is formed as an example between the straight portions 33 adjacent to each other in each plate fin 21.

  Each cut 26 formed between the linear portions 33 adjacent in the longitudinal direction X extends in the width direction Y. Each notch 26 formed between the linear portions 33 adjacent in the width direction Y is provided between the linear portions 43 adjacent in the longitudinal direction X and extends in the longitudinal direction X.

  Each cut 26 penetrates the plate fin 21. The cuts 26 suppress heat exchange between the linear portions 33 adjacent to each other via the plate fins 21. The notch 26 does not reach the water insertion hole 25 of the plate fin 21.

  Next, the shape of the refrigerant bend pipe 32 and the shape of the water bend pipe 42 will be specifically described. As described above, A = B> C. The shortest distance E between the refrigerant insertion holes 24 through which the pair of straight portions 33 facing in the width direction Y is passed is shorter than the outer diameter D of the water heat transfer tube body 41. The outer diameter D of the water heat transfer tube main body 41 is the inner diameter D of the water insertion hole 34. Therefore, it is considered that the refrigerant bend tube 32 does not contact the water heat transfer tube 40 and the water bend tube 42 does not contact the refrigerant heat transfer tube 30.

  FIG. 8 is a plan view showing the range of F8 shown in FIG. FIG. 8 shows a part of the refrigerant bend pipe 32 and a pair of linear portions 33 adjacent to each other in the longitudinal direction X. The refrigerant bend pipes 32 are all the same as the structure shown in FIG. 8, and therefore the refrigerant bend pipe 32 shown in FIG. 8 will be described as a representative.

  FIG. 9 is a cross-sectional view showing a state in which the refrigerant bend pipe 32 is cut along the line F9-F9 shown in FIG. As shown in FIGS. 8 and 9, the refrigerant bend pipe 32 has a flat shape in which the maximum width lr <b> 1 in the width direction Y is smaller than the outer diameter d of the refrigerant heat transfer pipe body 31. The maximum width lr1 is set so that the refrigerant bend pipe 32 does not contact the water bend pipe.

  Although the shape of the water bend pipe 42 is different from that of the refrigerant bend pipe 32, the structure is the same. Therefore, the water bend pipe 42 will be described with reference to FIGS. In FIGS. 8 and 9, reference numerals indicating structures related to the water heat transfer tubes 40 are shown in parentheses. As shown in FIGS. 8 and 9, the water bend pipe 42 has a flat shape in which the maximum width lr <b> 2 in the width direction Y is smaller than the outer diameter D of the linear portion 43. The maximum width lr2 is set in consideration so that the water bend pipe 42 does not contact the refrigerant bend pipe 32. Thus, in the present embodiment, the width lr1 of the refrigerant bend pipe 32 and the width lr2 of the water bend pipe 42 are set in consideration of each other as described above. Large changes to the outer diameters d and D are suppressed.

  As shown in FIG. 5, the refrigerant bend pipe 32 connects a pair of linear portions 33 adjacent to each other in the longitudinal direction X so as to avoid the water heat transfer pipe 40, that is, so as not to contact. Similarly, the water bend pipe 42 connects the pair of linear portions 43 adjacent to each other in the longitudinal direction X so as to avoid the refrigerant heat transfer pipe 30, that is, so as not to contact.

  As shown in FIG. 4, in each refrigerant heat transfer tube main body 31, one end of the linear portion 33 facing the width direction Y is connected to each other by a connecting portion 34. The connecting portion 34 is set to have a maximum width smaller than the outer diameter d of the linear portion 33 in the longitudinal direction X so as not to contact the water heat transfer tube 40 like the refrigerant bend tube 32, and is flat. It is.

  As shown in FIG. 2, the heat insulating material 50 is provided so as to cover the entire outer surface of the heat exchanger 3. Furthermore, as shown in FIG. 2, the heat insulating material 50 has a size that covers the heat transfer pipe 30 for refrigerant and the heat transfer pipe 40 for water.

  In FIG. 3, a part of the heat insulating material 50 is sectioned so that the openings 35 and 45 can be seen in the heat exchanger 3. The heat insulating material 50 is formed of a material having low thermal conductivity. In addition, the heat insulating material 50 is not limited to being comprised so that all the surfaces of the heat exchanger 3 may be covered. For example, the heat exchanger 3 may have a shape that opens so that a side surface on the side where the bend pipes 32 and 42 are provided and a side surface on the side where the connecting portions 34 and 44 are provided can be seen from the outside.

  Next, the operation of the heat exchanger 3 will be described. The refrigerant L that has flowed into the heat exchanger 3 flows into the refrigerant heat transfer tube 30 from the refrigerant inlet 36 and flows in the refrigerant heat transfer tube 30 toward the refrigerant outlet 37. Since the refrigerant heat transfer tube 30 is a single flow path, the refrigerant L alternately flows through the one end 22 and the other end 23 of each plate fin 21. At this time, the heat of the refrigerant L is transmitted to the fin group 20, that is, each plate fin 21.

  The water W that has flowed into the heat exchanger 3 flows into the water heat transfer tube 40 from the water inlet 46 and flows in the water heat transfer tube 40 toward the water outlet 47. At this time, since the refrigerant inlet 36 and the water outlet 47 are provided adjacent to each other, and the refrigerant outlet 37 and the water inlet 46 are provided adjacent to each other, the flow of the refrigerant L and the water W The flows are opposite to each other. When the water W flows in the water heat transfer tube 40, the heat of the refrigerant L transmitted to each plate fin 21 is transmitted to the water W.

  The refrigerant L that has exited the refrigerant outlet 37 is then guided to the internal heat exchanger 4. The water W exiting the water outlet 47 is guided to the hot water storage tank 12.

  FIG. 10 is a graph showing the temperature of the refrigerant L between the refrigerant inlet 36 and the refrigerant outlet 37 and the temperature of the water W between the water inlet 46 and the water outlet 47 in the heat exchanger 3. Show. The graph G shows the temperature gradient between the refrigerant L and the water W. In the graph shown in FIG. 10, the horizontal axis indicates the position in the refrigerant heat transfer tube 30 and the water heat transfer tube 40, and the vertical axis indicates the temperature. In the refrigerant L, the temperature of the refrigerant inlet 36 is T1, and the temperature of the refrigerant outlet 37 is T2. In the water W, the temperature of the water inlet 46 is t1, and the temperature of the water outlet 47 is t2.

  By the above operation of the heat exchanger 3, as shown in FIG. 10, the temperature of the refrigerant L decreases in the process of flowing from the refrigerant inlet 36 to the refrigerant outlet 37, that is, T1> T2. The temperature of the water W rises in the process of flowing from the water inlet 46 to the water outlet 47, that is, t2> t1.

  When the temperature efficiency is ε, ε = (t2−t1) / (T1−t1), and ε is promoted by the above structure.

  In the heat exchanger 3 configured as described above, the refrigerant heat transfer tube 30 is connected to the fin group 20, that is, each plate fin 21, and the water heat transfer tube 40 is connected to the fin group 20, that is, each plate fin 21. Thus, heat transfer from the refrigerant L to the water W is performed via the fin group 20.

  Further, the pipe pitch B between the straight portions 33 arranged side by side in the longitudinal direction X is larger than the length C between the straight portions 33 arranged in the width direction Y. For this reason, since the distance between the linear parts 33 arranged in the width direction Y becomes smaller than the distance between the linear parts 33 adjacent to each other in the longitudinal direction X, the heat transfer efficiency is improved. The same effect can be obtained even when B ≧ C.

  Further, since it is not necessary to directly connect the refrigerant heat transfer tube 30 and the water heat transfer tube 40, the productivity in producing the heat exchanger 3 is improved, and the cost can be reduced.

  In this embodiment, the ratio between the heat capacity flow rate of the refrigerant L and the heat capacity flow rate of the water W is approximately 1: 1 so that the total area in the tube of the refrigerant heat transfer tube 30 and the total area in the tube of the heat transfer tube for refrigerant are The outer diameter of the refrigerant heat transfer tube 30 is made smaller than the outer diameter of the water heat transfer tube 40 by taking advantage of the characteristic that the pressure loss of the refrigerant L is low so that the ratio is approximately 1: 1. Is sandwiched in the width direction Y by a pair of refrigerant heat transfer tubes 30. Further, by making the pipe pitch B of the straight line portion 33 and the pipe pitch A of the straight line portion 43 the same in the longitudinal direction X, the heat exchanger 3 has a structure in which the balance of the heat transfer amount is improved, and therefore, the heat transfer amount. Thermal efficiency is increased.

  Moreover, when the connection part 34 of the refrigerant | coolant heat exchanger tube 30 is made flat, when inserting each water heat exchanger tube main body 41 and each refrigerant | coolant heat exchanger tube main body 31 in each plate fin 21, it becomes a refrigerant | coolant heat exchanger tube. Since the connection part 34 of the main body 31 does not interfere with the water heat transfer tube 40 or the like, the working efficiency can be improved.

  Similarly, since the refrigerant bend pipe 32 and the water bend pipe 42 are flat, the refrigerant bend pipe 32 does not interfere with the water heat transfer pipe 40 and does not interfere with the water bend pipe. Since 42 does not interfere with contact with the refrigerant heat transfer tube 30 or the like, the efficiency of attaching the refrigerant bend tube 32 and the water bend tube 42 is improved. Furthermore, since the refrigerant heat transfer tube 30 and the water heat transfer tube 40 can be brought closer to each other, the heat transfer efficiency is improved.

  In addition, the refrigerant heat transfer tube 30 has a structure having a single flow that alternately flows through the one end portion 22 and the other end portion 23 of each plate fin 21, and therefore, the one end portion 22 across the water heat transfer tube 40. The amount of refrigerant L flowing through the other end 23 is the same. For this reason, heat exchange is performed efficiently.

  Further, the refrigerant inlet 36 and the water outlet 47 are provided at one end in the longitudinal direction X of the fin group 20 so as to be adjacent to each other, and the refrigerant outlet 37 and the water inlet 46 are arranged in the longitudinal direction X of the fin group 20. By providing at the other end and adjoining each other, the refrigerant flow and the water flow are opposite to each other. For this reason, heat transfer from the refrigerant L to the water W can be efficiently promoted.

  Moreover, in each plate fin 21, the linear part 33 of the refrigerant | coolant heat exchanger tube 30 and the linear part 43 of the water heat exchanger tube 40 are arrange | positioned in zigzag form, The length of the width direction Y of each plate fin 21 is made. Can be shortened. Furthermore, since the one linear part 43 comes to oppose the two linear parts 33 by arrange | positioning in zigzag form, the heat transfer efficiency from the refrigerant | coolant L to the water W improves.

  Further, the slits 26 are formed in each plate fin 21 between the linear portions 43 adjacent to each other in the longitudinal direction X and between the linear portions 33 adjacent to each other in the width direction Y, whereby the condensation latent heat of the refrigerant L is Since heat is efficiently transferred only to the water heat transfer tube 40, the heat exchange performance is improved.

  Further, the heat insulating material 50 suppresses heat exchange between the fin group 20 and the surrounding air. For this reason, heat exchange between the refrigerant L and the water W via the fin group 20 is efficiently performed.

  Next, a heat exchanger according to the second embodiment will be described with reference to FIG. In the present embodiment, configurations having functions similar to those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted. In the present embodiment, the relative positional relationship between the straight portion 33 of the refrigerant heat transfer tube 30 and the straight portion 43 of the water heat transfer tube 40 is different from that of the first embodiment. Other structures may be the same as those in the first embodiment. The above different points will be specifically described.

  FIG. 11 is a front view showing a state in which the heat insulating material 50, the refrigerant bend pipe 32, and the water bend pipe 42 are removed in the heat exchanger 3 of the present embodiment. As shown in FIG. 11, in the present embodiment, the relative positional relationship between the linear portion 33 and the linear portion 43 is D ≧ C−d instead of the relative positional relationship where B ≧ C.

  When the relative positional relationship between the straight portion 33 and the straight portion 43 satisfies D ≧ Cd, the straight portion 33 approaches the water heat transfer tube 40. For this reason, in this embodiment, the same operation and effect as those of the first embodiment can be obtained. Further, the relative positional relationship between the straight line portion 33 and the straight line portion 43 may be satisfied simultaneously with B ≧ C described in the first embodiment and D ≧ C−d described in the present embodiment.

  Next, a heat exchanger according to the third embodiment will be described with reference to FIGS. In addition, the structure which has the same function as 1st Embodiment attaches | subjects the code | symbol same as 1st Embodiment, and abbreviate | omits description. In the present embodiment, the refrigerant bend pipe 32, the water bend pipe 42, and the connecting portion 34 are different from those of the first embodiment. Other structures may be the same as those in the first embodiment. The different structure will be specifically described.

  FIG. 12 is a plan view showing a part of the straight portion 33 and the refrigerant bend pipe 32 in the refrigerant heat transfer pipe 30 of the present embodiment. FIG. 12 shows a part of the straight portion 33 and the refrigerant bend pipe 32 as in FIG. 8 used in the first embodiment. FIG. 13 is a cross-sectional view showing a state in which the refrigerant bend pipe 32 is cut along the line F13-F13 shown in FIG. As shown in FIG. 13, in the present embodiment, the refrigerant bend pipe 32 is not flat but has a circular cross section. The outer diameter dr1 of the bend pipe 32 for refrigerant is smaller than the outer diameter d of the straight portion 33. That is, d> dr1. The outer diameter dr1 of the refrigerant bend pipe 32 is set in consideration so that the refrigerant bend pipe 32 does not contact the water heat transfer pipe 40.

  Although the shape of the water bend pipe 42 is different from that of the refrigerant bend pipe 32, the structure is the same. For this reason, the water bend pipe 42 will be described with reference to FIGS. In FIGS. 12 and 13, reference numerals indicating structures related to the water heat transfer tubes 40 are shown in parentheses.

  As shown in FIGS. 12 and 13, the water bend pipe 42 has a circular cross section. The outer diameter dr <b> 2 of the water bend pipe 42 is smaller than the outer diameter D of the linear portion 43. The outer diameter dr2 of the water bend pipe 42 is set in consideration so that the water bend pipe 42 does not contact the refrigerant heat transfer pipe 30.

  In each refrigerant heat transfer tube main body 31, the connecting portion 34 that connects one end of the linear portion 33 facing the width direction Y has a circular cross section. The outer diameter of the connecting portion 34 is set in consideration so that the refrigerant bend pipe 32 does not contact the water heat transfer pipe 40.

  In the present embodiment, the same operation and effect as in the first embodiment can be obtained. The structures of the refrigerant bend pipe 32, the water bend pipe 42, and the connecting portion 34 described in the present embodiment may be used in the heat exchanger 3 described in the second embodiment. In this case, the same operation and effect as in the second embodiment can be obtained.

  According to the first to third embodiments, it is possible to improve heat transfer efficiency, improve manufacturing, and provide a heat exchanger with low cost and good space efficiency.

  Although several embodiments of the present invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

Claims (3)

A plurality of fins that are long in one direction, and the plurality of fins are stacked with a gap between each other in a posture in which the longitudinal directions are aligned with each other; and
A refrigerant heat transfer tube that penetrates the fin in the laminating direction of the fin and is formed in a meandering shape in the longitudinal direction of the fin, and in which the refrigerant flows;
A heat transfer tube for a heat medium that passes through the fin in the laminating direction of the fin and is adjacent to the heat transfer tube for the refrigerant, and is formed in a meandering shape in the longitudinal direction of the fin and the heat medium flows inside. And
The refrigerant heat transfer tubes are installed on both side rows of the heat transfer tube along the row direction intersecting the longitudinal direction,
The outer diameter of the heat transfer tube for the heat medium is D,
The outer diameter of the refrigerant heat transfer tube is d,
In the refrigerant heat transfer tube, when the distance between the central rows of the portions passing through both sides of the heat transfer tube for the heat medium in the row direction is C,
A heat exchanger, wherein D ≧ Cd. The refrigerant heat transfer tube is formed of a single flow path that penetrates all the fins in the laminating direction of the fins and that the portions installed in the both side rows communicate with each other.
The heat transfer tube for the heat medium penetrates all the fins in the stacking direction of the fins and is formed by one flow path.
The heat exchanger according to claim 1. When the pipe pitch of the refrigerant heat transfer tubes arranged in the longitudinal direction is B,
B ≧ C
The heat exchanger according to claim 1 or 2, characterized in that.

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