JP7364954B2 - Water heat exchanger and heat pump system equipped with it - Google Patents

Description

The present invention relates to a water heat exchanger in which water and a heat exchange medium exchange heat, and a heat pump system equipped with the same.

BACKGROUND ART Conventionally, in heat pump systems such as hot water heaters, water heat exchangers have been used in which water and a heat exchange medium such as a refrigerant exchange heat. As shown in Patent Document 1 (Japanese Unexamined Patent Publication No. 2010-117102), such a water heat exchanger has a plurality of first channels through which water flows, and a second channel through which a heat exchange medium for exchanging heat with water flows. It has a flow path.

In the conventional water heat exchanger described above, performance can be improved by reducing the cross-sectional area of the first flow path and the second flow path (micro flow path).

However, the water flowing through the first flow path may contain foreign matter such as pipe rust, and such foreign matter can clog the first flow path, reducing the heat exchange capacity of the water heat exchanger. There is a risk that the water may decrease or the drainage performance may decrease.

The water heat exchanger according to the first aspect is connected to a plurality of first flow paths through which water flows, a second flow path through which a heat exchange medium that exchanges heat with water flows, and a first inlet of water. A first inlet header that branches water flowing in from the first inlet into a first flow path. Here, the inlet portion of the first flow path for water from the first inlet header is referred to as the first flow path inlet portion, and the portion of the first flow path downstream of the first flow path inlet portion is referred to as the first flow path inlet portion. One channel main section has a first channel formed such that the channel cross-sectional area at the first channel inlet is smaller than the channel cross-sectional area at the first channel main section.

Here, since the first flow path inlet section can stop foreign objects of a size that could potentially clog the first flow path from flowing in from the first inlet header, clogging of the first flow path due to foreign objects can be prevented. The occurrence can be suppressed.

In the hydrothermal exchanger according to the second aspect, in the hydrothermal exchanger according to the first aspect, the first passage inlet portion is within 10% of the passage length of the first passage among the first passages. This is the part.

Here, the inflow of foreign matter into the first flow path can be reliably stopped near the branch position from the first inlet header.

In the water heat exchanger according to the third aspect, in the water heat exchanger according to the first or second aspect, the flow passage cross-sectional area at the first flow passage inlet portion is the flow passage cross-sectional area at the first flow passage main portion. The number of first flow channels formed to be smaller than the first flow channels is 60% or more of all the first flow channels.

Here, the occurrence of clogging in the first flow path due to foreign matter can be suppressed in the entire water heat exchanger.

A hydrothermal exchanger according to a fourth aspect is a hydrothermal exchanger according to any one of the first to third aspects, in which the first flow path inlet portion is oriented in the flow direction of water flowing from the first inlet header. It has a tapered shape that becomes thinner along the length.

Here, during operation of the water heat exchanger, it is possible to suppress an increase in flow resistance when water passes through the first channel inlet.

A water heat exchanger according to a fifth aspect is a water heat exchanger according to any one of the first to fourth aspects, in which a flow path disconnection occurs at a portion of the first flow path inlet where the flow path cross-sectional area is the smallest. The area is 70% or less of the cross-sectional area of the flow path in the main portion of the first flow path.

Here, it is possible to reliably stop foreign matter of a size that may cause clogging in the first flow path at the first flow path inlet.

A hydrothermal exchanger according to a sixth aspect is the hydrothermal exchanger according to any one of the first to fifth aspects, wherein the first channel is a microchannel.

Here, if the first channel is made into a micro channel with a very small channel cross-sectional area, clogging with foreign matter will easily occur, but as described above, if the channel cross-sectional area at the first channel inlet is made small, By doing so, it is possible to suppress the occurrence of clogging in the first flow path due to foreign matter.

A water heat exchanger according to a seventh aspect is a water heat exchanger according to any one of the first to sixth aspects, wherein the first flow path is such that water flows from the first inlet header to the first flow path inlet part. It is arranged so that it flows upward.

Here, it is possible to make it difficult for foreign matter to reach the first flow path inlet portion of the first flow path from the first inlet header due to gravity.

A water heat exchanger according to an eighth aspect is a water heat exchanger according to any one of the first to seventh aspects, wherein the first inlet header is arranged so that the water flows upward from the first inlet to the first inlet header. It is arranged so that it flows in.

Here, gravity can make it difficult for foreign objects to reach the first inlet header from the first inlet.

A hydrothermal exchanger according to a ninth aspect is the hydrothermal exchanger according to the eighth aspect, in which the first inlet header has a tapered space that becomes narrower toward the first inlet.

Here, when the water heat exchanger is shut down, the foreign matter in the first inlet header can be facilitated to be discharged toward the first inlet by gravity.

The heat pump system according to the tenth aspect includes a compressor that compresses a refrigerant as a heat exchange medium, and a radiator that uses water to cool the refrigerant compressed in the compressor. It has such a water heat exchanger, an expansion mechanism that reduces the pressure of the refrigerant cooled in the water heat exchanger, and an evaporator that evaporates the refrigerant that has been reduced in pressure in the expansion mechanism. In addition, here, contrary to the case where the water heat exchanger functions as a radiator for refrigerant, water is flowed through the water heat exchanger in the order of the first flow path, the first inlet header, and the first inlet. It further has a washing mechanism.

Here, foreign matter blocked at the first flow path inlet by operation of the water heat exchanger can be discharged by a cleaning operation using a backwashing mechanism.

In the heat pump system according to the eleventh aspect, in the heat pump system according to the tenth aspect, when the first flow path inlet section allows water to flow in the order of the first flow path, the first inlet header, and the first inlet, 1 It has a tapered shape that becomes narrower along the flow direction of water flowing in from the main part of the flow path.

Here, during the cleaning operation of the water heat exchanger, it is possible to suppress an increase in flow resistance when water passes through the first channel inlet.

1 is a schematic configuration diagram of a radiator as a water heat exchanger and a heat pump system including the radiator according to an embodiment of the present disclosure. It is a perspective view showing the appearance of a radiator. It is a figure which looked at the 1st flow path of a radiator from the front. It is a figure which looked at the 2nd flow path of a radiator from the front. FIG. 3 is a perspective view showing the main parts of the heat exchange section of the radiator. FIG. 4 is an enlarged view of the vicinity of the first flow path entrance portion in FIG. 3; FIG. 3 is a diagram illustrating how foreign matter is blocked at the first flow path entrance. 7 is a diagram showing a radiator according to modification A, and corresponds to FIG. 6. FIG. 4 is a diagram showing a radiator according to modification B, and corresponds to FIG. 3. FIG. FIG. 2 is a schematic configuration diagram of a radiator as a water heat exchanger and a heat pump system equipped with the radiator according to modification C (illustrating the flow of water during a cleaning operation of the radiator). 7 is a diagram showing a radiator according to modification example C, and corresponds to FIG. 6. FIG.

Hereinafter, a water heat exchanger and a heat pump system including the same will be explained based on the drawings.

(1) Heat pump system <Configuration>
FIG. 1 is a schematic configuration diagram of a radiator 12 as a water heat exchanger and a heat pump system 1 including the radiator 12 according to an embodiment of the present disclosure. The heat pump system 1 mainly includes a refrigerant circuit 10 in which a refrigerant as a heat exchange medium circulates, and a water circuit 30 in which water as a heated fluid circulates. This device uses a cycle to heat water and uses the heated water to heat the room.

The refrigerant circuit 10 mainly includes a compressor 11, a radiator 12, an expansion mechanism 13, and an evaporator 14. The refrigerant circuit 10 is filled with HFC refrigerant, HFO refrigerant, and natural refrigerant as refrigerants.

The compressor 11 is a device that compresses refrigerant. The compressor 11 is, for example, a compressor that drives a refrigerant compression element such as a rotary type or a scroll type by a drive mechanism such as a motor.

The radiator 12 is a device that cools the refrigerant compressed in the compressor 11 by water circulating in the water circuit 30. Note that details of the heat radiator 12 will be described later. Further, the discharge port 11b of the compressor 11 and the refrigerant-side inlet (second inlet 12a) of the radiator 12 are connected by a discharge refrigerant pipe 16.

The expansion mechanism 13 is a device that reduces the pressure of the refrigerant cooled in the radiator 12. The expansion mechanism 13 is, for example, an expansion valve or a capillary tube. Furthermore, the refrigerant-side outlet (second outlet 12b) of the radiator 12 and the expansion mechanism 13 are connected by a high-temperature refrigerant pipe 17.

The evaporator 14 is a device that evaporates the refrigerant whose pressure has been reduced in the expansion mechanism 13. The evaporator 14 is, for example, a fin-and-tube heat exchanger that heats the refrigerant with air. Here, a blower fan 15 is provided to obtain a flow of air that serves as a heating source for the refrigerant. The blower fan 15 is a fan that drives a blower element such as a propeller type by a drive mechanism such as a motor. Further, the expansion mechanism 13 and the refrigerant inlet 14a of the evaporator 14 are connected by a low-temperature refrigerant pipe 18, and the refrigerant outlet 14b of the evaporator 14 and the suction port 11a of the compressor 11 are connected to each other by a suction refrigerant pipe 19. connected by.

The water circuit 30 mainly includes a radiator 12, a pump 31, and a user device 32. The water circuit 30 is filled with water.

As described above, the radiator 12 is a device that cools the refrigerant compressed in the compressor 11 by the water circulating in the water circuit 30. In other words, the radiator 12 is a device that heats water with the refrigerant circulating in the refrigerant circuit 10. Note that details of the heat radiator 12 will be described later.

The pump 31 is a device that increases the pressure of water. The pump 31 is, for example, a pump that drives a centrifugal or positive displacement pump element using a drive mechanism such as a motor. Here, the water side outlet (first outlet 12d) of the radiator 12 and the suction port 31a of the pump 31 are connected by an outlet water pipe 33.

The user device 32 is a device that heats the room using water heated by the radiator 12. The user equipment 32 is, for example, a radiator or a floor heater. Further, the discharge port 31b of the pump 31 and the water inlet 32a of the user device 32 are connected by a discharge water pipe 34, and the water outlet 32b of the user device 32 and the water side inlet (water inlet) of the radiator 12 are connected. 1 inlet 12c) through an inlet water pipe 35.

The components of the heat pump system 1 described above are controlled by a control device 2. The control device 2 is composed of a control board and the like on which a microcomputer, memory, etc. are mounted.

<Operation>
Next, the operation of the heat pump system 1 will be explained using FIG. 1. As described above, the heat pump system 1 is capable of heating water using the refrigerant compression type heat pump cycle in the refrigerant circuit 10 and heating the room with the heated water (heating operation). Note that the heating operation is performed by the control device 2.

In the refrigerant circuit 10 , the refrigerant compressed and discharged by the compressor 11 is sent to the radiator 12 . The refrigerant sent to the radiator 12 exchanges heat with the water circulating in the water circuit 30 to be cooled and condensed. The refrigerant that has radiated heat in the radiator 12 is depressurized by the expansion mechanism 13 and then sent to the evaporator 14 . The refrigerant sent to the evaporator 14 exchanges heat with the air passing through the evaporator 14 by the blower fan 15, and is heated and evaporated. The refrigerant evaporated in the evaporator 14 is sucked into the compressor 11, compressed again in the compressor 11, and discharged.

On the other hand, in the water circuit 30, water is heated by heat radiation of the refrigerant in the radiator 12. Water heated in the radiator 12 is pressurized and discharged by the pump 31. Water discharged from the pump 31 is sent to the user equipment 32. The water sent to the user equipment 32 is cooled by heating the room. The water cooled in the user equipment 32 is sent to the radiator 12, where it is heated again.

(2) Details of radiator Next, details of the radiator 12 as a water heat exchanger will be explained using FIGS. 1 to 6. Here, FIG. 2 is a perspective view showing the appearance of the heat radiator 12. FIG. 3 is a diagram of the first flow path 51 of the radiator 12 viewed from the front. FIG. 4 is a diagram of the second flow path 61 of the radiator 12 viewed from the front. FIG. 5 is a perspective view showing the main parts of the heat exchange section 3 of the radiator 12. FIG. 6 is an enlarged view of the vicinity of the first flow path entrance portion 51a in FIG. In addition, in the following explanation, expressions such as "top", "bottom", "left", "right", "front", and "back" may be used to explain directions and positional relationships. Unless otherwise specified, the direction indicated by the expression follows the direction of the arrow shown in the drawings.

The radiator 12 mainly includes a heat exchange section 41 that exchanges heat between water and a refrigerant as a heat exchange medium, and a casing 42 in which the heat exchange section 41 is provided.

The heat exchange section 41 has a first layer 50 in which a plurality of rows of first channels 51 through which water flows is formed, and a second layer 60 in which a plurality of rows are formed in second channels 61 through which a refrigerant flows. It is made up of. Here, the direction in which the first layer 50 and the second layer 60 are laminated (here, the front-rear direction in FIGS. 2 and 5) is defined as the lamination direction. Further, the direction in which the first channels 51 are lined up (here, the left-right direction) is the direction in which the first channels 51 are arranged, and the direction in which the second channels 61 are lined up (here, the vertical direction) is the direction in which the second channels 61 are arranged. Arrange direction. The first and second channels 51 and 61 are micro channels (channels with an equivalent diameter of 1.5 mm or less) having a very small channel cross-sectional area. That is, the radiator 12 is called a microchannel heat exchanger. When the first layer 50 is viewed along the stacking direction (front-back direction) of the first and second layers 50 and 60, the first flow path 51 is arranged in the arrangement direction (horizontal direction) of the first flow path 51. It extends from near the bottom end of the first layer 50 to near the top end of the first layer 50 along a direction intersecting (in this case, the up-down direction). Moreover, here, the first flow path 51 has a meandering shape in the arrangement direction (left-right direction) of the first flow path 51 when the first layer 50 is viewed along the stacking direction (front-back direction). This is intended to promote heat transfer. Further, the second flow passages 61 are arranged in the arrangement direction (vertical direction) of the second flow passages 61 when the second layer 60 is viewed along the stacking direction (front-back direction) of the first and second layers 50 and 60. It extends from the vicinity of the left end of the second layer 60 to the vicinity of the right end of the second layer 60 along the direction intersecting with (here, the left-right direction). Moreover, here, the second flow path 61 is divided into a plurality of (here, four) flow path groups arranged in the vertical direction, from the flow path group located at the lower left end to the flow path group located at the upper left end. It extends back toward the road group in the left and right direction. Thus, here, the first flow path 51 and the second flow path 61 are arranged to form orthogonal counterflow.

Here, the heat exchange part 41 having a laminated structure of the first layer 50 and the second layer 60 includes a first plate material 52 having a groove formed on one side forming the first flow path 51 and a second flow path 61. A second plate member 62 having a groove formed on one side thereof is alternately laminated. The first and second plate members 52 and 62 are made of a metal material. The grooves forming the first flow path 51 and the second flow path 61 are formed by, for example, machining or etching the first and second plate materials 52 and 62. After stacking a predetermined number of the first and second plate materials 52 and 62 having such grooves, the first and second plate materials 52 and 62 are bonded together by vacuum brazing or diffusion bonding. As a result, the heat exchange section 41 having a laminated structure of the first layer 50 and the second layer 60 is obtained. Note that here, grooves forming the flow paths 51 and 61 are formed on one side of both the first and second plate members 52 and 62, but the grooves are not limited to this, and the first and second plate members 52 and , 62 may be formed with grooves forming the channels 51, 61, or grooves forming the channels 51, 61 may be formed on both surfaces of both the first and second plates 52, 62. may have been done.

Further, here, notches 53 and 54 are formed at the lower end and upper end of the first plate material 52, and the notches 53 and 54 are formed at the lower end of the first flow path 51 (water inlet), respectively. section) and the upper end (water outlet section). Cutout portions 63 and 64 are also formed at the lower and upper end portions of the second plate member 62 so as to overlap with the cutout portions 53 and 54. Then, by joining the first and second plate materials 52 and 62, the notches 53 and 63 form a first inlet header 13c, which is a space communicating with the lower end of the first flow path 51, and The cutouts 54 and 64 form a first outlet header 13d, which is a space that communicates with the upper end of the first flow path 51. In addition, notches 65 and 66 are formed at the upper left end and lower left end of the second plate material 62, respectively. ) and the lower left end (refrigerant outlet part). Cutout portions 55 and 56 are also formed at the upper left end and lower left end of the first plate member 52 so as to overlap with the cutout portions 65 and 66. Then, by joining the first and second plate members 52 and 62, the notches 55 and 65 form a second inlet header 13a, which is a space communicating with the upper left end of the second flow path 61, The notches 56 and 66 form a second outlet header 13b, which is a space that communicates with the lower left end of the second flow path 61.

The casing 42 is a member in which the heat exchange section 41 is provided. Here, the casing 42 has a substantially rectangular parallelepiped shape. A first inlet 12c, which serves as a water inlet, is formed in the lower surface of the casing 42, and communicates with the first inlet header 13c. An inlet water pipe 35 is connected to the first inlet 12c. A first outlet 12d serving as a water outlet is formed on the upper surface of the casing 42, and communicates with a first outlet header 13d. An outlet water pipe 33 is connected to the first outlet 12d. A second inlet 12a, which serves as an inlet for the refrigerant, is formed in the upper part of the left side of the casing 42, and communicates with the second inlet header 13a. A discharge refrigerant pipe 16 is connected to the second inlet 12a. A second outlet 12b serving as a refrigerant outlet is formed at the lower part of the left side surface of the casing 42, and communicates with the second outlet header 13b. A high temperature refrigerant pipe 17 is connected to the second outlet 12b. Here, each surface portion of the casing 42 is constituted by a metal plate-like member.

Here, each surface portion of the casing 42 is disposed to cover the heat exchange section 41 and is joined to the heat exchange section 41. Here, the heat exchange part 41 and the casing 42 are bonded together by vacuum brazing or diffusion bonding after covering each surface of the casing 42 with a predetermined number of laminated first and second plate materials 52 and 62. This process is performed together with the formation of the heat exchange section 41.

In the radiator 12 having such a configuration, during operation of the heat pump system 1 (during operation of the radiator 12), water flows from the first inlet 12c to the first inlet header 13c, and from the first inlet header 13c. It branches to the inlet portion of the first flow path 51, flows from the bottom to the top within the first flow path 51, is heated by heat exchange with the refrigerant, and is then transferred from the outlet portion of the first flow path 51 to the first outlet header 13d. and flows out from the first outlet 12d. Further, the refrigerant flows into the second inlet header 13a from the second inlet 12a, is branched from the second inlet header 13a to the inlet portion of the second flow path 61, and is turned back and forth in the second flow path 61 from above. It flows downward and radiates heat through heat exchange with water, joins at the second outlet header 13b from the outlet portion of the second flow path 61, and flows out from the second outlet 12b.

Here, the first channel 51 is formed so that the channel cross-sectional area Sa at the first channel entrance portion 51a is smaller than the channel cross-sectional area Sb at the first channel main portion 51b. Here, the first flow path inlet portion 51a is an inlet portion of the first flow path 51 for water from the first inlet header 13c. This is a portion within 10% of the flow path length L. The flow path length L is the flow path length along the water flow direction from the branch position of the first flow path 51 from the first inlet header 13c to the merging position of the first outlet header 13d. That is, the first flow path inlet portion 51a is a portion of the first flow path 51 within 10% of the flow path length L from the position where the first flow path 51 branches from the first inlet header 13c. The first flow path main portion 51b is a portion of the first flow path 51 that is downstream of the first flow path inlet portion 51a, and is a portion that mainly contributes to heat exchange in the first flow path 51. be. Here, for example, by forming the channel width Wa at the first channel inlet portion 51a to be narrower than the channel width Wb at the first channel main portion 51b, the channel cross-sectional area Sa is increased. It is made smaller than the area Sb. In particular, here, the flow in the first flow path inlet portion 51a is set such that the flow path cross-sectional area Sa of the first flow path inlet portion 51a is 70% or less of the flow path cross-sectional area Sb in the first flow path main portion 51b. The passage width Wa is made narrower than the passage width Wb in the first passage main portion 51b.

In addition, here, the number of first channels 51 formed such that the channel cross-sectional area Sa at the first channel inlet portion 51a is smaller than the channel cross-sectional area Sb at the first channel main portion 51b, The number is set to 60% or more of all the first flow paths 51. In particular, all the first channels 51 are formed so that the channel cross-sectional area Sa at the first channel inlet portion 51a is smaller than the channel cross-sectional area Sb at the first channel main portion 51b. There is.

(3) Features Next, the features of the radiator 12 as a water heat exchanger and the heat pump system 1 including the same will be described.

<A>
Here, as described above, the radiator 12 (water heat exchanger) has a plurality of first flow paths 51 through which water flows, and a second flow path 61 through which a refrigerant (heat exchange medium) that exchanges heat with water flows. and a first inlet header 13c that is connected to the first water inlet 12c and branches the water flowing in from the first inlet 12c to the first flow path 51.

Here, the water flowing through the first channel 51 may contain foreign matter such as pipe rust, and such foreign matter may clog the first channel 51 and cause the water heat exchanger 12 to become clogged. There is a risk that the heat exchange capacity of the water and drainage properties may be reduced. In particular, here, the first flow path 51 and the second flow path 61 are made into micro-channels to improve performance, and the first flow path 51 has a very small cross-sectional area. , clogging with foreign matter is more likely to occur. In addition, here, in order to promote heat transfer, the first flow path 51 has a meandering shape in the arrangement direction (left and right direction), so the first flow path 51 is easily clogged with foreign matter. ing.

Therefore, as described above, the first flow channel is formed such that the flow channel cross-sectional area Sa at the first flow channel inlet portion 51a is smaller than the flow channel cross-sectional area Sb at the first flow channel main portion 51b. 51. Here, the first flow path inlet portion 51a is the inlet portion of the first flow path 51 for water from the first inlet header 13c, and the first flow path main portion 51b is the inlet portion of the first flow path 51. This is the portion downstream of the first flow path inlet portion 51b.

As a result, the first flow path inlet portion 51a can prevent foreign matter having a size that may clog the first flow path 51 from flowing in from the first inlet header 13c (see FIG. 7). , the occurrence of clogging in the first flow path 51 due to foreign matter can be suppressed. Furthermore, by suppressing the occurrence of clogging of foreign objects in the first flow path 51, the flow path cross-sectional area Sb in the first flow path main portion 51b of the first flow path 51 can be further reduced. Furthermore, the performance of the water heat exchanger 12 can be improved. Furthermore, it is possible to suppress performance degradation and improve reliability of the heat pump system 1 as a whole.

<B>
Further, here, the first flow path inlet portion 51a is a portion of the first flow path 51 that is within 10% of the flow path length L of the first flow path 51.

Thereby, here, the inflow of foreign matter into the first flow path 51 can be reliably stopped near the branch position from the first inlet header 13c.

<C>
In addition, here, the number of first channels 51 formed such that the channel cross-sectional area Sa at the first channel inlet portion 51a is smaller than the channel cross-sectional area Sb at the first channel main portion 51b is: The number is 60% or more of all the first channels 51.

Thereby, the occurrence of clogging in the first flow path 51 due to foreign matter can be suppressed in the entire water heat exchanger 12 here. In particular, all the first channels 51 are formed so that the channel cross-sectional area Sa at the first channel inlet portion 51a is smaller than the channel cross-sectional area Sb at the first channel main portion 51b. Therefore, the occurrence of clogging in the first flow path 51 due to foreign matter can be reliably suppressed.

<D>
Further, here, the flow passage cross-sectional area Sa at the part of the first flow passage inlet portion 51a having the smallest flow passage cross-sectional area is 70% or less of the flow passage cross-sectional area Sb at the first flow passage main portion 51b. Here, since the first channel inlet 51a has a constant channel cross-sectional area in the water flow direction, any part of the first channel inlet 51a has the "largest channel cross-sectional area". However, if the cross-sectional area of the flow path is not constant with respect to the water flow direction due to changes in the flow path width of the first flow path inlet portion 51a, the first flow path inlet portion The portion of 51a with the smallest channel cross-sectional area becomes the channel cross-sectional area Sa.

Thereby, here, it is possible to reliably stop foreign objects of a size that may clog the first flow path 51 at the first flow path inlet portion 51a.

<E>
Further, here, the first flow path 51 is arranged so that water flows upward from the first inlet header 13c to the first flow path inlet portion 51a.

Thereby, it is possible here to make it difficult for foreign matter to reach the first flow path inlet portion 51a of the first flow path 51 from the first inlet header 13c due to gravity. Further, when the operation of the heat pump system 1 is stopped (when the operation of the water heat exchanger 12 is stopped), the foreign matter blocked at the first flow path inlet part 51a is dropped into the first inlet header 13c, and the first flow path is stopped. It is also possible to keep foreign objects away from the passageway 51.

<F>
Also, here, the first inlet header 13c is arranged such that water flows upward from the first inlet 12c into the first inlet header 13c.

Here, gravity can make it difficult for foreign matter to reach the first inlet header 13c from the first inlet 12c. Furthermore, when the operation of the heat pump system 1 is stopped (when the operation of the water heat exchanger 12 is stopped), the foreign matter present in the first inlet header 13c is dropped to the first inlet 12c, and the foreign matter is removed from the first flow path 51. You can also keep it away.

(4) Modification example <A>
In the embodiment described above, the first channel inlet portion 51a has a shape with a constant channel cross-sectional area along the flow direction of water flowing in from the first inlet header 13c (see FIG. 6). However, this shape of the first flow path inlet portion 51a increases the flow resistance when water passes through the first flow path inlet portion 51a during operation of the radiator 12 (water heat exchanger).

Therefore, here, as shown in FIG. 8, the first flow path inlet portion 51a has a tapered shape that becomes narrower along the flow direction of the water flowing in from the first inlet header 13c.

Thereby, during operation of the water heat exchanger 12, an increase in flow resistance when water passes through the first channel inlet portion 51a can be suppressed.

<B>
In the embodiment described above, the first inlet header 13c has a substantially rectangular space communicating with the first inlet 12c (see FIG. 3). However, with this shape of the first inlet header 13c, foreign matter in the first inlet header 13c tends to remain in the first inlet header 13c when the radiator 12 (water heat exchanger) is stopped.

Therefore, here, as shown in FIG. 9, the first inlet header 13c has a tapered space that becomes narrower toward the first inlet 12c.

Thereby, when the operation of the water heat exchanger 12 is stopped, the foreign matter in the first inlet header 13c can be promoted to be discharged toward the first inlet 12c by gravity.

<C>
In the embodiment described above, clogging of the first flow path 51 with foreign objects can be suppressed by damming up foreign objects at the first flow path entrance portion 51a by operating the radiator 12 (water heat exchanger). The foreign matter blocked at the flow path inlet portion 51a remains in the first inlet header 13c of the water heat exchanger 12 and in the water circuit 30.

Therefore, as shown in FIG. 10, in contrast to the case where the water heat exchanger 12 functions as a radiator for the refrigerant, the water heat exchanger 12 is connected to the first flow path 51 and the first inlet header. 13c and the first inlet 12c in this order.

The backwash mechanism 36 mainly includes a first bypass water pipe 36a having a first valve 36b, a second bypass water pipe 36c having a second valve 36d, a third valve 36e, a fourth valve 36f, and a fifth valve 36g. and a drain pipe 36h having a sixth valve 36i and a drain pump 36j. Here, the first to sixth valves 36b, 36d, 36e, 36f, 36g, and 36i may be electromagnetic valves that can be opened and closed by the control device 2, or may be manual valves. Further, the drain pump 36j may also be a pump that can be driven and controlled by the control device 2, or may be temporarily connected to the drain pipe 36h only when in use (during cleaning operation of the water heat exchanger 12) and manually operated. It may also be a pump driven by

The first bypass water pipe 36a is a water pipe whose one end is connected to the middle part of the inlet water pipe 35 and the other end is connected to the middle part of the outlet water pipe 33. The first valve 36b is provided in the first bypass water pipe 36a.

The second bypass water pipe 36c is a water pipe whose one end is connected to the middle part of the inlet water pipe 35 and the other end is connected to the middle part of the outlet water pipe 33, like the first bypass water pipe 36a. However, one end of the second bypass water pipe 36c is connected to a part of the water heat exchanger 12 closer to the first inlet 12c than the part where one end of the first bypass water pipe 36a is connected to the inlet water pipe 35. The other end of the first bypass water pipe 36a is connected to a portion closer to the first outlet 12d of the water heat exchanger 12 than the other end of the second bypass water pipe 36c is connected to the inlet water pipe 35. The second valve 36d is provided in the second bypass water pipe 36c.

The third valve 36e is provided in a portion of the inlet water pipe 35 between a portion to which the first bypass water pipe 36a is connected and a portion to which the second bypass water pipe 36c is connected.

The fourth valve 36f is provided in a portion of the outlet water pipe 33 between a portion to which the first bypass water pipe 36a is connected and a portion to which the second bypass water pipe 36c is connected.

The fifth valve 36g is provided in a portion between the portion of the outlet water pipe 33 to which the second bypass water pipe 36c is connected and the suction port 31a of the water pump 31.

The drain pipe 36h is a water pipe whose one end is connected to a portion of the outlet water pipe 33 between the portion to which the second bypass water pipe 36c is connected and the fifth valve 36g, and whose other end is open. The sixth valve 36i is provided in the drain pipe 36h. The drain pump 36j is provided at the other end of the drain pipe 36h from the portion where the sixth valve 36i is provided.

Such a backwash mechanism 36 closes the first valve 36b, the second valve 36d, and the sixth valve 36i, and closes the third valve 36i when the heat pump system 1 is operating (when the water heat exchanger 12 is operating). The valve 36e, the fourth valve 36f, and the fifth valve 36g are set in an open state. As a result, the same operation (heating operation) as in the above embodiment is performed.

If the water heat exchanger 12 is operated for a long time in this manner, foreign matter blocked at the first flow path inlet portion 51a may remain in the first inlet header 13c of the water heat exchanger 12 or in the water circuit 30. Become.

Therefore, here, a cleaning operation of the water heat exchanger 12 is performed using the backwash mechanism 36.

During the cleaning operation of the water heat exchanger 12, the backwash mechanism 36 closes the third valve 36e, the fourth valve 36f, and the fifth valve 36g, contrary to the operation of the water heat exchanger 12, and The first valve 36b, the second valve 36d, and the sixth valve 36i are set in an open state. When the drain pump 36j is driven in this state of the water circuit 30, the water in the water circuit 30 flows through the inlet water pipe 35, the first bypass water pipe 36a, and the outlet water pipe 33, as shown by the arrows indicating the flow of water in FIG. The water flows to the first outlet 12d of the water heat exchanger 12 through the portion near the water heat exchanger 12. Next, this water is transferred to the first outlet header 13d, the first flow path main part 51b of the first flow path 51, and the first flow path of the first flow path 51, contrary to the operation of the water heat exchanger 12. It flows in this order through the main portion 51b, the first flow path inlet portion 51a of the first flow path 51, and the first inlet header 13c to the first inlet 12c of the water heat exchanger 12 (see FIGS. 3 and 6). Next, this water flows through the part of the inlet water pipe 35 closer to the water heat exchanger 12, the second bypass water pipe 36c, and the part of the outlet water pipe 33 closer to the pump 31 to the drain pipe 36h, and is drained into the water circuit by the drain pump 36j. It is discharged to the outside of 30.

Thereby, here, the foreign matter blocked at the first flow path entrance portion 51a due to the operation of the water heat exchanger 12 can be discharged by the cleaning operation using the backwash mechanism 36. Further, the first flow path 51 of the water heat exchanger 12 can be returned to a state close to the initial state of use. By performing such a cleaning operation of the water heat exchanger 12 regularly, even if the heat pump system 1 is operated (the water heat exchanger 12 is operated) for a long time, the water heat exchanger 12 may be clogged with foreign matter. It is possible to suppress the deterioration of the heat exchange performance of the heat pump system 12, and in turn, the deterioration of the performance of the heat pump system 1 as a whole.

Further, as shown in FIGS. 3 and 9, during operation of the water heat exchanger 12, water flows upward through the first flow path 51 from the first inlet header 13c to the first flow path inlet portion 51a. The structure is arranged so that the water flows into the air. Therefore, in the cleaning operation of the water heat exchanger 12, the foreign matter adhering to the first flow path inlet portion 51a is allowed to fall into the first inlet header 13c to promote discharge from the water heat exchanger 12. I can do it.

Furthermore, as shown in FIGS. 3 and 9, during operation of the water heat exchanger 12, water flows upward from the first inlet 12c into the first inlet header 13c. The structure is arranged as follows. Therefore, in the cleaning operation of the water heat exchanger 12, it is possible to promote the discharge of foreign substances in the first inlet header 13c toward the first inlet 12c. . Moreover, as shown in FIG. 9, when the water heat exchanger 12 is in operation, if the first inlet header 13c has a tapered space that becomes narrower toward the first inlet 12c, the water heat exchanger 12 can be operated. In the cleaning operation of the container 12, it is possible to further promote the discharge of foreign matter in the first inlet header 13c toward the first inlet 12c.

Further, here, the first flow path inlet portion 51a has a shape in which the cross-sectional area of the flow path is constant along the flow direction of water flowing in from the first inlet header 13c (see FIG. 6), or the first flow path inlet The portion 51a has a tapered shape (see FIG. 8) that becomes narrower along the flow direction of water flowing in from the first inlet header 13c. However, this shape of the first flow path inlet portion 51a increases the flow resistance when water passes through the first flow path inlet portion 51a during the cleaning operation of the radiator 12 (water heat exchanger).

Therefore, here, as shown in FIG. 11, when water flows through the first flow path inlet portion 51a in the order of the first flow path 51, the first inlet header 13c, and the first inlet 12c (the water heat exchanger 12 During a cleaning operation), the first flow path main portion 51b has a tapered shape that becomes narrower along the flow direction of water flowing in from the first flow path main portion 51b. Specifically, when the first flow path inlet portion 51a is viewed from the first inlet header 13c side, the flow path first has a tapered shape, and after obtaining the minimum flow path cross-sectional area Sa. , this time, the flow path has a tapered shape in which the flow path becomes larger toward the first flow path main portion 51b.

Thereby, during the cleaning operation of the water heat exchanger 12, an increase in flow resistance when water passes through the first channel inlet portion 51a can be suppressed.

<D>
In the above embodiment, the heat pump system 1 using a refrigerant compression type heat pump cycle has been described as an example, so in the radiator 12 (water heat exchanger), the heat exchange medium that exchanges heat with water is a refrigerant. However, the present invention is not limited thereto, and may be a water heat exchanger that uses water as a heat exchange medium.

<E>
In the above embodiment, the heat pump system 1 that performs heating operation has been described as an example, so the configuration is such that water is heated by heat exchange between water and a refrigerant as a heat exchange medium in the radiator 12 (water heat exchanger). However, the present invention is not limited to this, and may be a water heat exchanger having a configuration in which water is cooled by heat exchange between water and a heat exchange medium.

<F>
In the above embodiment, the first flow path 51 has a meandering shape, but is not limited to this, and may have another shape such as a straight shape.

<G>
In the above embodiment, the second flow path 61 has a shape that is folded back at three places left and right, but the shape is not limited to this, and the number of folded back spots may be two or four, or there may be no folded back spots. It may be a shape. Further, the second flow path 61 may have a meandering shape similar to the first flow path.

<H>
In the above embodiment, the headers 13a to 13d of the radiator 12 (water heat exchanger) are formed by the cutouts 53 to 56, 63 to 66 of the first and second plate materials 52, 62 that constitute the heat exchange section 41. However, the present invention is not limited thereto, and the headers 13a to 13d may be formed on a member constituting the casing 40.

<I>
The arrangement of the inlets and outlets 12a to 12d of the radiator 12 (water heat exchanger) is not limited to the above embodiment, and may be arranged as appropriate depending on the flow path configuration and the like.

<J>
In the embodiment described above, the pump 31 provided in the water circuit 30 is connected to the water outlet 12d side of the radiator 12 (water heat exchanger), but it may be connected to the water inlet 12c side.

Although the embodiments of the present disclosure have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the present disclosure as described in the claims. .

The present disclosure is widely applicable to a water heat exchanger in which water and a heat exchange medium exchange heat, and a heat pump system equipped with the same.

1 Heat pump system 11 Compressor 12 Heat radiator (water heat exchanger)
13 Expansion mechanism 14 Evaporator 51 First channel 61 Second channel 12c First inlet 13c First inlet header 36 Backwash mechanism 51a First channel inlet section 51b First channel main section

Japanese Patent Application Publication No. 2010-117102

Claims (11)

a plurality of first channels (51) through which water flows;
a second flow path (61) through which a heat exchange medium that exchanges heat with the water flows;
a first inlet header (13c) that is connected to the first inlet (12c) of the water and branches the water flowing from the first inlet into the first flow path;
It is equipped with
An inlet portion of the water from the first inlet header in the first flow path is defined as a first flow path inlet portion (51a), and the first flow path inlet portion is integrally made of the same member as the first flow path. If a portion of the first flow path downstream of the first flow path inlet is defined as a first flow path main portion (51b), the flow cross-sectional area at the first flow path inlet is The first flow path is formed to be smaller than the cross-sectional area of the first flow path main portion.
Water heat exchanger (12). The first flow path inlet portion is a portion of the first flow path that is within 10% of the flow path length of the first flow path.
The water heat exchanger according to claim 1. The number of the first channels formed such that the channel cross-sectional area at the first channel inlet part is smaller than the channel cross-sectional area at the main part of the first channel is equal to 60% or more of the number of
The water heat exchanger according to claim 1 or 2. The first flow path inlet portion has a tapered shape that becomes narrower along the flow direction of the water flowing in from the first inlet header.
The water heat exchanger according to any one of claims 1 to 3. A channel cross-sectional area at a portion of the first channel inlet portion with the smallest channel cross-sectional area is 70% or less of a channel cross-sectional area in the first channel main portion.
The water heat exchanger according to any one of claims 1 to 4. the first channel is a microchannel;
The water heat exchanger according to any one of claims 1 to 5. The first flow path is arranged such that the water flows upward from the first inlet header into the first flow path inlet portion.
The water heat exchanger according to any one of claims 1 to 6. the first inlet header is arranged such that the water flows upwardly from the first inlet to the first inlet header;
The water heat exchanger according to any one of claims 1 to 7. The first inlet header has a tapered space that becomes narrower toward the first inlet.
The water heat exchanger according to claim 8. a compressor (11) that compresses a refrigerant as a heat exchange medium;
The water heat exchanger according to any one of claims 1 to 9, which is a radiator that cools the refrigerant compressed in the compressor with water;
an expansion mechanism (13) that reduces the pressure of the refrigerant cooled in the water heat exchanger;
an evaporator (14) that evaporates the refrigerant reduced in pressure in the expansion mechanism;
Contrary to the case where the water heat exchanger functions as a radiator for the refrigerant, the water is supplied to the water heat exchanger in the order of the first flow path, the first inlet header, and the first inlet. a backwashing mechanism (36) that flushes;
It is equipped with
Heat pump system (1). When the water flows in the order of the first flow path, the first inlet header, and the first inlet, the first flow path inlet portion is arranged such that the water flows in the flow direction of the water flowing from the first flow path main portion. It has a tapered shape that becomes thinner along the
The heat pump system according to claim 10.

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