JP2010060214A - Refrigeration system - Google Patents

Abstract

A refrigeration apparatus having a water heat exchanger with a simple configuration with a small number of parts is provided.
A refrigeration apparatus includes a water heat exchanger that exchanges heat between a refrigerant pipe a through which refrigerant flows and a water pipe b through which water flows. The refrigerant pipe 22a is a hole 47 formed in the pair of flat tubes 41A and 41B, and the water pipe 22b is formed by using the opposing surfaces 44a of the pair of flat tubes 41A and 41B between the pair of flat tubes 41A and 41B. Space.
[Selection] Figure 5

Description

  The present invention relates to a refrigeration apparatus mainly used as a heating means of a heat pump type hot water supply apparatus.

2. Description of the Related Art Conventionally, as a refrigeration apparatus for a heat pump type hot water supply apparatus, one constituted by a compression refrigeration circuit has been widely used. In the refrigeration circuit, the refrigeration system includes, for example, CO ₂ as a refrigerant and a water heat exchanger. The water heat exchanger has a refrigerant pipe through which a refrigerant flows and a water pipe through which water flows, and makes fluids face each other and exchange heat between them. Specifically, water is heated by performing heat exchange between a high-temperature and high-pressure refrigerant and low-temperature and low-pressure water. As a result, high temperature hot water using the characteristics of the supercritical region of CO ₂ becomes possible.

  As a prior art of the water heat exchanger, a structure in which a refrigerant pipe is spirally wound around a water pipe is known (see, for example, Patent Document 1).

Further, a structure in which a water pipe is a flat pipe and a plurality of refrigerant pipes are in close contact with the side surface is known (see, for example, Patent Document 2).
JP 2007-271213 A JP 2004-218946 A

  The water heat exchanger shown in Patent Document 2 includes a flat first heat transfer tube, a plurality of second heat transfer tubes, and a restraint tube for bringing them into close contact with each other.

  Therefore, the number of parts constituting the water heat exchanger increases and the manufacturing process becomes complicated.

  An object of the present invention is to provide a refrigeration apparatus having a water heat exchanger with a simple configuration with a small number of parts.

  A refrigeration apparatus according to a first aspect of the present invention includes a water heat exchanger that exchanges heat between a first flow path through which a first fluid flows and a second flow path through which a second fluid flows. The first flow passage is a hole formed in the pair of flat tubes, and the second flow passage is a space formed between the pair of flat tubes using the opposing surfaces of the pair of flat tubes.

  In this refrigeration apparatus, in the water heat exchanger, the first fluid flows through the first flow path and the second fluid flows through the second flow path, and as a result, heat exchange is performed between the two fluids. In this water heat exchanger, since the second flow passage is formed using the opposing surfaces of a pair of flat tubes, the number of parts is reduced and the structure is further simplified. The pair of flat tubes can be easily joined by, for example, an adhesive or brazing.

  A refrigeration apparatus according to a second aspect of the present invention is the refrigeration apparatus according to the first aspect of the present invention, wherein the flat tube has a protruding portion that extends toward the other flat tube and forms a side wall as a part of the second flow passage. Is provided.

  In this refrigeration apparatus, in the water heat exchanger, the flat tube itself has a protruding portion serving as a side wall, so the number of parts of the water heat exchanger is reduced. The protruding portion is joined to, for example, the protruding portion of the other flat tube or another portion.

  A refrigeration apparatus according to a third aspect of the present invention is the refrigeration apparatus according to the first aspect of the present invention, which is provided on the side of the pair of flat tubes and has a pair of closures having a plane constituting a side wall as a part of the second flow passage. A member is further provided.

  In this refrigeration apparatus, since the side wall of the second flow passage is realized by the pair of closing members in the water heat exchanger, the structure of the pair of flat tubes can be simplified.

  A refrigeration apparatus according to a fourth aspect of the present invention is the refrigeration apparatus according to any of the first to third aspects of the present invention, wherein a turbulent flow promoting structure is formed on the opposing surface of the flat tube.

In this refrigeration apparatus, since the turbulent flow promoting structure is formed on the opposed surface of the flat tube, the heat transfer coefficient of the second fluid flowing through the second flow passage is improved, and as a result, heat exchange is promoted. For example, even when the first fluid is CO ₂ and the second fluid is water, the heat transfer coefficient of the second fluid is improved even though the heat transfer coefficient of water is lower than that of CO ₂ . A high-performance water heat exchanger can be obtained.

  A refrigeration apparatus according to a fifth aspect of the present invention is the refrigeration apparatus according to the fourth aspect of the present invention, wherein the turbulent flow promoting structure is a plurality of concave portions or convex portions.

  In this refrigeration apparatus, since the turbulent flow promoting structure is realized by a plurality of concave portions or convex portions, the structure is simple and the manufacturing is easy. The recess may be a groove or a partial recess, and the protrusion may be a protrusion or a partial protrusion extending in a certain direction.

  A refrigeration apparatus according to a sixth aspect of the present invention is the refrigeration apparatus according to any of the first to fifth aspects of the present invention, wherein the flat tube has a hole formed on the opposite side to the opposite flat tube.

  In this refrigeration apparatus, since the hole of the flat tube is biased to the opposite side of the counterpart flat tube, it is easy to make the distance between the hole and the opposing surface longer than the partition wall between the second fluid and the outside. As a result, even if corrosion occurs, the first fluid leaks not to the second fluid side but to the outside, and detection before mixing into the first fluid becomes possible.

  In the refrigeration apparatus according to the first aspect of the invention, the second flow passage is formed using the opposing surfaces of the pair of flat tubes, so the number of parts is reduced and the structure is simplified.

  In the refrigeration apparatus according to the second aspect of the invention, the flat tube itself has a protruding portion serving as a side wall, so the number of parts is reduced.

  In the refrigeration apparatus according to the third aspect of the present invention, the side walls of the second flow path are realized by the pair of closing members, so that the structure of the pair of flat tubes is simplified.

  In the refrigeration apparatus according to the fourth aspect of the invention, since the turbulent flow promoting structure is formed on the facing surface of the flat tube, the heat transfer coefficient of the second fluid flowing through the second flow passage is improved.

  In the refrigeration apparatus according to the fifth aspect of the present invention, since the heat exchange promoting structure is realized by the plurality of concave portions or convex portions, the structure is simple and the manufacture is easy.

  In the refrigeration apparatus according to the sixth aspect of the invention, since the hole of the flat tube is biased to the opposite side of the flat tube on the other side, detection before the second fluid is mixed into the first fluid is possible.

<Configuration of heat pump hot water supply device>
A system of a heat pump hot water supply apparatus including a refrigeration apparatus according to an embodiment of the present invention is shown in FIG. The heat pump type hot water supply apparatus 1 includes a refrigeration apparatus 2 and a hot water storage apparatus 3. The refrigeration apparatus 2 includes a compressor 21, a refrigerant pipe 22 a in the water heat exchanger 22, an expansion valve 23 as a decompression unit, and an air heat exchanger 24 that are annularly connected by a refrigerant pipe 25. 20

  Further, the refrigeration circuit 20 is provided with a gas heat exchanger 26 for heat exchange between the high-pressure and high-temperature refrigerant coming out of the water heat exchanger 22 and the low-pressure and low-temperature refrigerant coming out of the air heat exchanger 24. ing. Specifically, heat exchange is performed between the refrigerant passage connecting the water heat exchanger 22 and the expansion valve 23 and the refrigerant passage connecting the air heat exchanger and the compressor 21.

  The hot water storage device 3 includes a water circulation circuit 30 in which a hot water storage tank 31, a water pipe 22 b in the water heat exchanger 22, and a water circulation pump 32 are annularly connected by a water pipe 35.

  The refrigeration apparatus 2 includes an outside air temperature sensor 8 that detects the outside air temperature at the installation location, a discharge pipe temperature sensor 9 that detects the discharge pipe temperature of the compressor 21, and a temperature sensor 10 that detects the temperature of the air heat exchanger 24. The detection signals of these sensors are input to the microcomputer 6. Further, the refrigeration apparatus 2 is provided with a refrigerant sensor 11 for detecting refrigerant leakage from the refrigerant pipe 22a.

  The water circulation amount is controlled by the water circulation pump 32 so that the temperature of the water heated by the water heat exchanger 22 becomes 85 ° C. The microcomputer 6 controls the opening degree of the expansion valve 23 in order to ensure the refrigerant temperature necessary for obtaining 85 ° C. water.

<Structure of refrigeration equipment>
FIG. 2 is a cross-sectional view showing the internal structure of the refrigeration apparatus 2. In FIG. 2, the right compartment of the heat insulation wall 2c is the machine room 2a, and the left compartment of the heat insulation wall 2c is the fan room 2b. A compressor 21 and an expansion valve 23 are arranged in the machine room 2a.

  In the fan chamber 2b, a fan 27 is disposed in front of the fan chamber 2b in a front view in FIG. A motor that drives the fan 27 is disposed behind the fan 27 in a state of being fixed to the motor support base 28. A water heat exchanger 22 is disposed below the fan chamber 2b with a heat insulating wall 2d interposed therebetween. In the water heat exchanger 22, heat exchange is performed between the refrigerant flowing through the refrigerant pipe 22a (see FIG. 1) and the water flowing through the water pipe 22b (see FIG. 1).

  In FIG. 2, the air heat exchanger 24 is disposed along the left side wall and the back wall of the fan chamber 2b, and the right end of the air heat exchanger 24 extends to the center of the machine chamber 2a. The control box 4 is disposed so as to straddle the upper part of the machine room 2a and the upper part of the fan room 2b. The control box 4 incorporates a control device 5 equipped with a microcomputer 6 (see FIG. 3) and an inverter 7 (see FIG. 3).

<Operation control of refrigeration equipment>
FIG. 3 is a control block diagram of the refrigeration apparatus 2. The microcomputer 6 sets the target discharge pipe temperature at the target discharge pipe temperature setting unit 62 based on detection signals from the outside air temperature sensor 8 and the temperature sensor 10 of the air heat exchanger 24. The microcomputer 6 controls the opening of the expansion valve 23 via the expansion valve opening controller 63 so that the discharge pipe temperature detected by the discharge pipe temperature sensor 9 approaches the target discharge pipe temperature. Data necessary for setting the target discharge pipe temperature is stored in advance in the target discharge pipe temperature setting unit 62.

  Further, the microcomputer 6 compresses via the inverter control unit 64 in consideration of the influence of the outside air temperature on the cooking capacity of the refrigeration apparatus 2 and further considering that the hot water supply load changes according to the time zone of the day. The operating frequency of the machine 21 is controlled. For example, in a time zone in which the outside air temperature is low and the hot water supply load is large, the operating frequency of the compressor 21 is increased by ignoring the efficiency in order to prevent hot water shortage. On the other hand, in the time zone when the outside air temperature is high and the hot water supply load is small, the operating frequency of the compressor 21 is set to a high efficiency point.

  When the hot water supply load is large, the microcomputer 6 controls the operation of the compressor 21 so that the discharge pipe temperature does not exceed 120 ° C. for the purpose of protecting the compressor 21. Actually, when the discharge pipe temperature is 120 ° C., the internal temperature of the compressor 21 reaches 140 ° C. to 145 ° C. When the internal temperature further rises and exceeds 150 ° C., the magnet inside the compressor 21 The magnetic force of the oil drops and oil deterioration occurs, leading to failure. Therefore, in this embodiment, the upper limit of the discharge pipe temperature is set to 120 ° C.

  However, when the outside air temperature t1 is −20 ° C. or less, the compressor 21 is likely to be overloaded. Therefore, as a further safety measure, the correction value of the detection value of the discharge pipe temperature sensor 9 is increased, and the actual discharge pipe temperature is reduced. Before reaching 120 ° C., the detection value of the discharge pipe temperature sensor 9 needs to be 120 ° C. Therefore, the correction amount when the outside air temperature t1 is −20 ° C. or less is obtained experimentally and stored in the second correction means 61b of the temperature correction unit 61 of the microcomputer 6.

  In the temperature range of the outside air temperature t1> −20 ° C., the correction is made by the first correcting means 61a.

<Structure of water heat exchanger>
FIG. 4 is a piping diagram of the water heat exchanger 22. In this figure, the water heat exchanger 22 is schematically represented.

  The water heat exchanger 22 has a refrigerant pipe 22a and a water pipe 22b, and performs heat exchange between fluids flowing through the refrigerant pipe 22a and the water pipe 22b. As a specific structure, the water heat exchanger 22 is mainly composed of a pair of flat tubes 41A and 41B.

  As shown in FIG. 5, the pair of flat tubes 41 </ b> A and 41 </ b> B includes a flat portion main body 44 and a pair of projecting portions 45 and 46 extending from the end of the main body 44 to the other side. The flat portion main body 44 extends long as shown in FIG. 4, and the pair of projecting portions 45 </ b> A and 45 </ b> B also extend along the main body 44. The flat portion main body 44 has a facing surface 44a facing each other and an opposite side surface 44b on the opposite side. A plurality of (four in this embodiment) holes 47 are formed in a row in the flat portion main body 44. Thus, by forming a plurality of holes in the flat tube to form a refrigerant tube, the heat transfer coefficient on the refrigerant side is improved. The protrusions 45 and 46 are formed on both the flat tubes 41A and 41B and have the same length.

  The flat tubes 41A and 41B are made of, for example, copper, aluminum, stainless steel, or the like. Each flat tube 41A, 41B is manufactured by drawing or extruding.

  The pair of protrusions 45A and 45B are brazed at the ends to the pair of protrusions 45A and 45B of the flat tubes 41A and 41B on the other side. Thereby, the water pipe 22b is secured between the pair of flat tubes 41A and 41B. In other words, the water pipe 22b is formed by the opposed surfaces 44a of the pair of flat tubes 41A and 41B and the inner side surfaces 45a of the pair of projecting portions 45A and 45B. In addition, since the length of the protrusion parts 45 and 46 is the same in each flat tube 41A and 41B, each flat tube 41A and 41B forms the water pipe 22b by half. The cross-sectional shape of the water pipe 22b is a flat shape in which the side on the facing surface 44a side is longer than the side wall.

  As shown in FIG. 4, the pair of flat tubes 41 </ b> A and 41 </ b> B is bent in parallel and has a meandering shape. For example, in FIG. 4, the meandering shape is such that a linear portion extending in a straight line and a bent portion bent in a hairpin shape are alternately repeated, and as a result, a plurality of linear portions are arranged close to each other. Refers to the shape. In other words, it arrange | positions so that a several linear part may mutually overlap. Thus, since the whole shape of the water heat exchanger 22 has a meandering shape, a compact structure is realized.

  In addition, each of the flat tubes 41A and 41B has their straight portions close to each other in the stacking direction, but has a gap 43 therebetween. The size of the gap 43 is set to such an extent that adjacent portions of flat tubes (tubes having different temperatures) do not perform heat exchange by heat conduction. As a result, the water heat exchanger 22 can discharge hot water as a result without reducing the overall heat exchange efficiency. Further, the influence of thermal deformation can be suppressed to a small level, and the reliability is improved.

  By making the distance between the hole 47 and the opposed surface 44a longer than the partition wall (45A, 45B) between the water and the outside, even if corrosion occurs, the water leaks to the outside instead of the refrigerant side, before being mixed into the refrigerant. Detection is possible.

In this water heat exchanger 22, CO ₂ flows in the refrigerant pipe 22a, and water flows in the water pipe 22b in a direction opposite to the CO ₂ . As a result, heat exchange is performed between the fluids flowing in the both, and water is heated. Here, since the heat transfer area is increased using a flat tube, the heat exchange performance is high. Moreover, since the wall surface which shields both fluids is single, it is hard to produce the increase in thermal resistance by the fall of the adhesiveness of several piping.

<Features>
(1)
The refrigeration apparatus 2 includes a water heat exchanger 22 that exchanges heat between a refrigerant pipe 22a through which refrigerant flows and a water pipe 22b through which water flows. The refrigerant pipe 22a is a hole 47 formed in the pair of flat tubes 41A and 41B, and the water pipe 22b is formed by using the opposing surfaces 44a of the pair of flat tubes 41A and 41B between the pair of flat tubes 41A and 41B. Space.

  In the refrigeration apparatus 2, in the water heat exchanger 22, the refrigerant flows through the refrigerant pipe 22a and the water flows through the water pipe 22b, and as a result, heat exchange is performed between both fluids. In this water heat exchanger 22, the water pipe 22b is formed using the opposed surfaces 44a of the pair of flat tubes 41A and 41B, so the number of parts is reduced and the structure is further simplified. In particular, the pair of flat tubes 41A and 41B can be easily joined together by, for example, an adhesive or brazing.

(2)
The flat tubes 41A and 41B are provided with projecting portions 45A and 45B that extend toward the mating flat tubes 41A and 41B and constitute side walls as a part of the water tube 22b.

  In this refrigeration apparatus 2, since the flat tubes 41A and 41B themselves have the protruding portions 45A and 45B serving as side walls, the number of parts is reduced. The protrusions 45A and 45B are joined to, for example, the protrusions 45A and 45B and other parts of the other flat tubes 41A and 41B.

<Other embodiments>
As mentioned above, although one Embodiment of this invention was described, this invention is not limited to the said embodiment, A various change is possible in the range which does not deviate from the summary of invention.

(1)
The water heat exchanger 52 shown in FIGS. 6 and 7 performs heat exchange between the refrigerant pipe 52a through which the refrigerant flows and the water pipe 52b through which water flows. The refrigerant pipe 52a is a hole 57 formed in the pair of flat tubes 53A and 53B, and the water pipe 52b is formed by using the opposing surfaces 56a of the pair of flat tubes 53A and 53B between the pair of flat tubes 53A and 53B. Space. In addition, the flat part main body 56 has the opposing surface 56a which mutually opposes, and the opposite side surface 56b of the opposite side.

  In this refrigeration apparatus, in the water heat exchanger 52, the refrigerant flows through the refrigerant pipe 52a and the water flows through the water pipe 52b. As a result, heat exchange is performed between both fluids. In this water heat exchanger 52, the water pipe 52b is formed using the opposed surfaces 56a of the pair of flat tubes 53A and 53B, so the number of parts is reduced and the structure is simplified.

  In this embodiment, the water heat exchanger 52 further includes a pair of closing members 54A and 54B that are provided on the sides of the pair of flat tubes 53A and 53B and have a plane that forms a side wall as a part of the water tube 52b. ing. The pair of closing members 54A and 54B are flat plates as shown in FIG. 6, and have a quadrangular shape so as to cover the entire sides of the pair of flat tubes 53A and 53B. The shape of the closing member can be changed according to the shape of the pair of flat tubes.

  The side surfaces of the pair of flat tubes 53A and 53B and the inner side surfaces 54a of the pair of closing members 54A and 54B are fixed to each other by brazing or bonding.

  In this water heat exchanger 52, since the side wall of the water pipe 22b is realized by the pair of closing members 54A and 54B, the structure of the pair of flat tubes 53A and 53B can be simplified. That is, the pair of flat tubes 53A and 53B does not require a structure for forming a side wall such as a protruding portion.

(2)
The pair of flat tubes 58a of the water heat exchanger 58 shown in FIG. 8 are bent in parallel to form a spiral shape. More specifically, the pair of flat tubes 58a are rectangular spirals, and have a first header 58b on the outside and a second header 58c on the inside.

  A predetermined gap 58d is secured between the flat tubes 58a in the radial direction.

  In this apparatus, since the flow passage has a spiral shape, the entire hydrothermal exchanger is compact. And since the clearance gap 58d is ensured between the mutually adjacent locations of the flow path, the heat exchange efficiency of the water heat exchanger is improved while being compact.

(3)
The pair of flat tubes 59a of the water heat exchanger 59 shown in FIG. 9 are bent in parallel to form a spiral shape. More specifically, the pair of flat tubes 59a are circular spirals and have an outer first header 59b and an inner second header 59c.

  In addition, a predetermined gap 59d is secured between the flat tubes 59a in the radial direction.

  Also in this embodiment, the same effect as that of the above embodiment can be obtained.

(4)
The water heat exchanger shown in FIG. 10 is realized by a step structure in which a pair of water heat exchangers 59 are stacked in the vertical direction. As is clear from the figure, the water heat exchangers 59 are integrated with each other by a connecting portion 59e on the center side.

  As a method of manufacturing the water heat exchanger 59, there are a method of integrally forming a two-stage flat tube and a method of preparing a two-stage flat tube and joining them. Specifically, in the first method, the flat tube 59a is formed by winding one step in parallel and then changing the step and winding the next one step in parallel. When the first stage is wound from the inside, the second stage is wound from the outside. When the first stage is wound from the outside, the second stage is wound from the inside. Secondly, in the method, the inner ends or the outer ends of the two-stage flat tubes are connected.

  A gap 60 is secured between the pair of water heat exchangers 59 as shown in the figure. The size of the gap 60 is set so that undesirable heat exchange is not performed between the pair of water heat exchangers 59.

  In this water heat exchanger, the length of the flow path can be secured long while maintaining a sufficiently compact shape. Further, the capacity can be easily changed by using a plurality of spiral shapes.

(5)
The water heat exchanger 22 shown in FIG. 11 has a refrigerant pipe 22a and a water pipe 22b, and performs heat exchange between fluids flowing through the refrigerant pipe 22a and the water pipe 22b. As a specific structure, the water heat exchanger 22 is mainly composed of a pair of flat tubes 41A and 41B.

  The pair of flat tubes 41 </ b> A and 41 </ b> B includes a flat portion main body 44. A plurality of (four in this embodiment) holes 47 are formed in a row in the flat portion main body 44. The refrigerant pipe 22a is a hole 47 formed in the pair of flat tubes 41A and 41B, and the water pipe 22b is formed by using the opposing surfaces 44a of the pair of flat tubes 41A and 41B between the pair of flat tubes 41A and 41B. Space.

  In this refrigeration apparatus, in the water heat exchanger 22, the refrigerant flows through the refrigerant pipe 22a and the water flows through the water pipe 22b. As a result, heat exchange is performed between both fluids. In this water heat exchanger 22, the water pipe 22b is formed using the opposed surfaces 44a of the pair of flat tubes 41A and 41B, so the number of parts is reduced and the structure is further simplified.

  In this embodiment, the water heat exchanger 22 is further provided with a pair of closing members 66A and 66B which are provided on the sides of the pair of flat tubes 41A and 41B and have a plane which forms a side wall as a part of the water tube 22b. ing. The pair of closing members 66A and 66B are flat plates as shown in FIG. 11, and have a shape along the extended shape of the pair of flat tubes 41A and 41B so as to cover the sides of the pair of flat tubes 41A and 41B. is doing.

  In this water heat exchanger 22, as shown in FIG. 12, a groove 44c (concave portion) as a turbulent flow promoting structure is formed on the opposing surface 44a of the main body 44 of the flat tubes 41A and 41B. As is apparent from the drawing, the groove 44c has a herringbone shape. As the turbulent flow promoting structure, a plurality of protrusions 44d (convex portions) may be formed as shown in FIG. The opposite side surface 44b of the main body 44 is not formed with grooves or protrusions, and is a flat surface.

In this water heat exchanger 22, since the grooves 44c and the protrusions 44d as the turbulent flow promoting structure are formed on the opposed surfaces 44a of the flat tubes 41A and 41B, the water flow in the water tube 22 becomes turbulent and high. Heat transfer characteristics can be obtained. In other words, the heat transfer coefficient of water flowing through the water pipe 22b is improved, and as a result, heat exchange is promoted. Although water has a lower heat transfer coefficient than CO ₂ , the heat transfer coefficient of water is improved, so that a high-performance water heat exchanger can be obtained.

  Moreover, in this water heat exchanger, since the turbulent flow promoting structure is realized by the plurality of grooves 44c or the protrusions 44d, the structure is simple and the manufacture is easy.

(6)
The basic structure of the water heat exchanger 22 shown in FIG. 14 is the same as that of the said embodiment (FIG. 5). In the water heat exchanger 22, the holes 47 of the flat tubes 41 </ b> A and 41 </ b> B are formed so as to be biased to the opposite side to the counterpart flat tubes 41 </ b> A and 41 </ b> B. In other words, the distance between the hole 47 and the opposite side surface 44b is shorter than the distance between the hole 47 and the opposing surface 44a.

  In this water heat exchanger 22, the distance between the hole 47 and the opposed surface 44a is longer than the partition wall (45, 46) between water and the outside, so that even if corrosion occurs, water leaks to the outside rather than to the refrigerant side. In addition, it is possible to detect before mixing in the refrigerant. Further, by making the flat tubes 41A and 41B thick only on the surfaces that come into contact with water, it is possible to ensure a safe thickness against corrosion leakage without causing unnecessary costs.

(7)
The basic structure of the water heat exchanger 52 shown in FIG. 15 is the same as that of the embodiment (FIG. 7). In this water heat exchanger 52, the holes 57 of the flat tubes 53A and 53B are formed so as to be biased to the opposite side of the flat tubes 53A and 53B on the other side. In other words, the distance between the hole 57 and the opposite side surface 56b is shorter than the distance between the hole 57 and the opposing surface 56a.

In this water heat exchanger 52, the distance between the hole 57 and the facing surface 56a is longer than the partition wall (54A, 54B) between the water and the outside, so that even if corrosion occurs, water leaks to the outside instead of the refrigerant side. In addition, it is possible to detect before mixing in the refrigerant. Further, by making the flat tubes 53A and 53B thick only on the surfaces that come into contact with water, it is possible to ensure a safe thickness against corrosion leakage without causing unnecessary cost.
<Modification>
(1)
In the said embodiment, although the protrusion part extended from a pair of flat tube is formed in the same length in both flat tubes, this invention is not limited to this. For example, in the pair of flat tubes, the lengths of the protruding portions may be different, or the protruding portions may be formed only in one of the flat tubes.

(2)
In the said embodiment, although a closing member is a flat plate, this invention is not limited to this. The closing member should just have the plane which comprises the side wall of a 2nd flow path, and the whole may not be a flat plate.

(3)
In the said embodiment, although the four holes are formed in a line in the flat tube, this invention is not limited to this. The number and arrangement of holes may be arbitrarily set.

(4)
In the said embodiment, although a pair of flat tubes or flat tubes and a closure member are joined by brazing, this invention is not limited to this. For example, you may join each member using an adhesive material.

(5)
In the embodiment (FIG. 10), the water heat exchangers are stacked in two stages, but the present invention is not limited to this. For example, three or more stages of water heat exchangers may be stacked.

(6)
In the above embodiment, CO ₂ is used as the refrigerant, but the present invention is not limited to this. For example, hydrocarbons or chlorofluorocarbon refrigerants may be used as the high-temperature and high-pressure refrigerant.

(7)
In the said embodiment, although the flat tube was the multi-hole structure formed in the integral member, this invention is not limited to this. For example, a plurality of thin tubes may be joined to form one flat tube.

(8)
In the said embodiment, although the hole of the flat tube was made into the refrigerant | coolant pipe | tube and the space between flat tubes was made into the water pipe | tube, this invention is not limited to this.

  As described above, according to the present invention, the number of parts is reduced and the structure is simplified, which is useful for a refrigeration apparatus of a heat pump type hot water supply apparatus.

The system of the heat pump type hot water supply apparatus containing the freezing apparatus which concerns on one Embodiment of this invention. Sectional drawing which shows the internal structure of a freezing apparatus. The block diagram of the control apparatus of a freezing apparatus. The internal piping figure of the water heat exchanger of refrigeration equipment. Sectional drawing of a pair of flat tube before joining. The internal piping figure of the water heat exchanger of the freezing apparatus in other embodiment. Sectional drawing of a pair of flat tube before joining. Furthermore, the internal piping figure of the water heat exchanger of the freezing apparatus in other embodiment. Furthermore, the internal piping figure of the water heat exchanger of the freezing apparatus in other embodiment. Furthermore, the internal piping figure of the water heat exchanger of the freezing apparatus in other embodiment. Furthermore, the internal piping figure of the water heat exchanger of the freezing apparatus in other embodiment. The perspective view of the opposing surface side of a flat tube. The perspective view of the opposing surface side of a flat tube. Furthermore, sectional drawing of a pair of flat tube before joining in other embodiment. Furthermore, sectional drawing of a pair of flat tube before joining in other embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat pump type hot water supply apparatus 2 Refrigeration apparatus 2a Machine room 2b Fan room 6 Microcomputer 20 Compression type refrigeration circuit 21 Compressor 22 Water heat exchanger 22a Refrigerant pipe (first flow path)
22b Water pipe (second flow passage)
23 Expansion valve 24 Air heat exchanger 25 Refrigerant piping 27 Fan 35 Water piping 41A, 41B Flat tube 43 Gap 44 Flat portion main body 44a Opposing surface 44b Opposite side surface 44c Groove (concave portion)
44d Projection (convex part)
45A, 45B Protruding portion 45a Inner side surface 47 hole 52 Hydrothermal exchanger 52a Refrigerant tube 52b Water tube 53A, 53B Flat tube 54A, 54B Closing member 54a Inner side surface 56 Flat portion main body 56a Opposing surface 56b Opposite side surface 57 hole

Claims (6)

A refrigeration apparatus comprising a water heat exchanger (22) in which heat exchange is performed between a first flow path (22a) through which the first fluid flows and a second flow path (22b) through which the second fluid flows. 2)
The first flow passage is a hole (47) formed in a pair of flat tubes (41A, 41B), and the second flow passage is an opposing surface of the pair of flat tubes between the pair of flat tubes. (44a) is a space formed using
Refrigeration equipment.   The said flat tube (41A, 41B) is provided with the protrusion part (45A, 45B) which extends toward the other party flat tube and comprises the side wall as a part of said 2nd flow path. The refrigeration apparatus according to 1.   The pair of closing members (54A, 54B) provided on the side of the pair of flat tubes and having a plane that forms a side wall as a part of the second flow passage. Refrigeration equipment.   The refrigeration apparatus according to any one of claims 1 to 3, wherein a turbulent flow promoting structure (44c, 44d) is formed on the facing surface of the flat tube.   The refrigeration apparatus according to claim 4, wherein the turbulent flow promoting structure is a plurality of concave portions (44c) or convex portions (44d).   The refrigeration apparatus according to any one of claims 1 to 5, wherein the hole (47) of the flat tube is formed so as to be biased to the opposite side of the flat tube on the other side.

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