JP2013113480A - Heat pump apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat pump apparatus capable of preventing efficiency of heat exchange from being deteriorated even when frost is generated in an air heat exchanger.SOLUTION: A heat pump apparatus 1 is constituted by arranging a compressor 2 for compressing a refrigerant R, an air heat exchanger 5 for moving heat from external air A to the refrigerant R, and a user side heat exchanger 3 for moving heat from the refrigerant R to the user side on a circulation passage through which the refrigerant R is circulated. The air heat exchanger 5 is a plate fin type heat exchanger configured by laminating a refrigerant plate element 8 for allowing the refrigerant R to pass through the inside thereof and an air plate element 9 for allowing the air A to pass through the inside thereof. On the air plate element 9, a passage allowing the air A to flow therein is obliquely arranged so as to decline in an air flow direction.

Description

  The present invention relates to a heat pump device, and more particularly to an air heat exchanger provided in the heat pump device.

  Conventionally, a heat pump device has been used as a device for transferring heat from a lower temperature to a higher temperature. The configuration of the heat pump device consists of a compressor, a condenser (use side heat exchanger), an expansion valve, an evaporator (air heat exchanger), and a pipe connecting them. However, the refrigerant that evaporates is circulated. The refrigerant absorbs heat from a heat source such as air with an air heat exchanger, evaporates and is sucked into the compressor, is compressed into a high-temperature and high-pressure gas, and is sent to the use-side heat exchanger. Here, the refrigerant releases heat and becomes liquid, and is further depressurized by the expansion valve and returns to the air heat exchanger again.

Regarding the heat pump device and the use side heat exchanger and air heat exchanger used in the heat pump device, various configurations have been developed.
For example, Patent Document 1 discloses a heat pump device that includes a compressor, an air heat exchanger, a use-side heat exchanger, and a switching valve and connects them to form a cold / hot water cycle. In this heat pump device, the use-side heat exchanger is composed of a plate heat exchanger, and the plate-type heat exchanger is provided with a refrigerant gas supply / return passage and a refrigerant liquid supply / return passage to supply the refrigerant liquid. The return passage comprises a refrigerant supply passage having an orifice for distributing the wet refrigerant liquid to each channel of the plate during cooling, and a refrigerant return passage communicating with the outlet side of the orifice through which the refrigerant liquid passes during heating; A cushion tank is provided on the exit side of the return passage.

  The air heat exchanger of the heat pump device described above is a V-type plate fin coil type. That is, the air heat exchanger of Patent Document 1 has a configuration (plate fin coil structure) in which a tube through which a refrigerant liquid to be heat circulates penetrates a plurality of thin plate heat transfer plates. The provided coil element is arranged in a V shape.

JP 2000-161806 A

  In the case of a normal plate fin coil type air heat exchanger as shown in FIG. 3A, the coil elements are often arranged vertically. In this case, during the defrosting operation (when the frost adhered to the air heat exchanger is liquefied), the liquefied frost (water droplets) cannot flow out to the outside, and the water droplets may remain in the coil element. was there. Such residual water droplets or refrosting of the remaining water droplets causes a problem that the heat exchange efficiency is lowered.

  Therefore, it is conceivable to arrange the coil elements in a V shape as shown in Patent Document 1, that is, FIG. However, even if the installation area can be reduced, the V-shaped arrangement of the coil elements is not preferable in terms of design and function because of an unstable shape spreading upward. If the coil elements are arranged in an inverted V shape, there is a problem that the ground contact area increases.

  Therefore, in view of the above problems, the present invention effectively eliminates water droplets generated at the time of defrosting to suppress frost formation and express high heat exchange efficiency, and is excellent in design and function. It aims at providing the heat pump apparatus provided with the air heat exchanger.

In order to achieve the above-described object, the present invention takes the following technical means.
The heat pump device according to the present invention includes a compressor that compresses a refrigerant in a circulation channel through which the refrigerant circulates, an air heat exchanger that performs heat transfer from external air to the refrigerant, and heat transfer from the refrigerant to the user side. In the heat pump device provided with a use side heat exchanger for performing the above, the air heat exchanger is formed by laminating a refrigerant plate element through which refrigerant flows and an air plate element through which air flows. A plate fin-type heat exchanger, wherein the air plate element is provided with an inclined channel formed so that air flows and is inclined downward along the air flow direction. It is characterized by being.

Preferably, the inclination angle of the inclined flow path is an angle that can be discharged to the outside of the air plate element when frost attached to the air plate element is liquefied.
Preferably, the fin height of the inclined flow path of the air plate element is set to be higher than the fin height of the straight flow path of the refrigerant plate element.
Preferably, the air plate elements are stacked so that the number of stages of the air plate elements is greater than the number of stages of the refrigerant plate elements.

Preferably, air plate elements are stacked so as to sandwich the refrigerant plate element.
Preferably, the air heat exchanger may be provided with a fan that forcibly introduces air into the air heat exchanger.

  The heat pump device of the present invention effectively eliminates frost even when frost is generated, exhibits high heat exchange efficiency, and is excellent in design and function.

It is the figure which showed typically the heat pump apparatus which concerns on this invention. (A) is the perspective exploded view which showed the structure of the air heat exchanger which concerns on this invention, (b) is the perspective view which showed the external appearance of the air heat exchanger which concerns on this invention. (A) is the schematic diagram which showed the structure of the normal air heat exchanger, (b) is the schematic diagram which showed the structure of the conventional air heat exchanger (patent document 1), (c) These are the schematic diagrams which showed the structure of the air heat exchanger which concerns on this invention. It is the exploded view which showed the structure of the air heat exchanger which concerns on this invention. 1 is an overall view showing the structure of an air heat exchanger according to the present invention. It is the figure which showed typically the cross-section of the air heat exchanger which concerns on this invention. It is the figure which showed the inside of the plate element for refrigerant | coolants which concerns on the modification of this invention.

Hereinafter, a heat pump device according to the present invention will be described with reference to the drawings.
<< Heat pump device >>
The present invention has a characteristic configuration in the air heat exchanger 5 provided in the heat pump device 1. Before describing the air heat exchanger 5, the heat pump device 1 will be described first.

  As shown in FIG. 1, the heat pump device 1 is a device that moves heat from a low temperature side to a high temperature side. The heat pump device 1 includes a compressor 2, a use side heat exchanger 3 (condenser), an expansion valve 4, and an air heat exchanger 5 (evaporator). These compressor 2, use side heat exchanger 3, the expansion valve 4 and the air heat exchanger 5 are connected by a pipe 6. The pipe 6 is a circulation channel through which the refrigerant R circulates.

  The refrigerant R in the pipe 6 absorbs heat by heat transfer from the external air A to the refrigerant R in the air heat exchanger 5, evaporates and is sucked into the compressor 2. The gas is compressed into a high-temperature and high-pressure gas and sent to the use-side heat exchanger 3. Further, the refrigerant R releases heat in the usage-side heat exchanger 3 to become liquid, is reduced in pressure by the expansion valve 4, returns to the air heat exchanger 5 again, and changes in phase from liquid to gas. The refrigerant R is a refrigerant R (alternative chlorofluorocarbon, that is, hydrochlorofluorocarbon (HCFC), hydrofluorocarbon (HFC), etc.) having a property of evaporating even at a low temperature. In the heat pump apparatus 1 of FIG. 1, a fan 7 that forcibly introduces air A into the air heat exchanger 5 is provided in order to increase the efficiency of heat exchange.

Now, when adopting a plate fin type heat exchanger as the air heat exchanger 5 of the heat pump device 1 described above, as shown in Patent Document 1 (FIG. 3B), the coil element is arranged in a V shape. Even if the installation area can be reduced, an unstable shape spreading upward is not preferable. On the other hand, when the coil element is arranged vertically instead of V-shaped (FIG. 3 (a)), at the time of defrosting There is a risk that water droplets will not be discharged well, resulting in a decrease in heat exchange efficiency. As described above, even when the frost is generated by arranging the coil elements vertically, it is necessary to effectively eliminate the frost attached to the coil elements to avoid lowering the heat exchange efficiency. is there.

Therefore, even if frost shown in FIGS. 1 to 6 is generated, the plate fin type air heat exchanger 5 that does not decrease the heat exchange efficiency and is excellent in design and function is adopted.
<< Air heat exchanger >>
Hereinafter, based on FIGS. 1-6, the air heat exchanger 5 employ | adopted for the heat pump apparatus 1 of this invention is demonstrated. In the description, the horizontal direction in FIG. 4 is the horizontal direction in the description, and the vertical direction in FIG. 4 is the vertical direction in the description. The penetration direction of the paper surface in FIG. 4 is a front-rear direction in the description.

First, as shown in FIG.3 (c), the air heat exchanger 5 of this invention is provided with the fan 7 which produces the upward forced flow of air upwards. A right core portion and a left core portion constituting the air heat exchanger 5 are disposed below the fan 7 and on both the left and right sides.
Since the internal structures of the right core portion and the left core portion are substantially the same, the description of the structure of the core portion mainly disposed on the right side will be given below.

As shown in FIG. 2 (a), the air heat exchanger 5 (the core portion arranged on the right side) employed in the heat pump device 1 is a plate-like element in which the refrigerant R circulates “the refrigerant plate element. 8 ”and“ air plate element 9 ”which is a plate-like element through which air A circulates, and these are stacked in a plurality of stages.
In the air heat exchanger 5, the number of stages of the air plate elements 9 is set to be larger than the number of stages of the refrigerant plate elements 8. As shown in FIG. 2B, in this embodiment, one air plate element 9 is provided on each side of the one refrigerant plate element 8 in the front-rear direction. In other words, the air plate element 9 is arranged so as to sandwich the refrigerant plate element 8.

The flow of the refrigerant R in the refrigerant plate element 8 and the flow of the air A in the air plate element 9 are as indicated by arrows shown in FIG. As will be described in detail later, the fin portion 10 of the air plate element 9 has an inclination that decreases in the air A flow direction.
As shown in FIG. 3C, the core portion where the refrigerant plate element 8 and the air plate element 9 are laminated is the lower portion of the fan 7 so that the direction in which the inclination of the fin portion 10 of the air plate element 9 is lowered is opposed. Deployed in the left and right direction. For this reason, the air plate element 9 includes a right air plate element 9R for right deployment and a left air plate element 9L for left deployment. 3A is a schematic diagram showing the structure of a normal air heat exchanger, and FIG. 3B is a schematic diagram showing the structure of a conventional air heat exchanger (Patent Document 1). .
<< Plate element for refrigerant >>
As shown in FIGS. 2A and 4, the refrigerant plate element 8 is composed of a fin portion 10 in which concave and convex grooves are formed of aluminum or stainless steel, side bar members 11 arranged in a pair of left and right, and a pair of front and rear. And a deployed separator 12. After the fin portion 10 is sandwiched between the pair of side bar members 11 from the width direction, a separator 12 is attached so as to cover the fin portion 10 and the side bar member 11 from the front and rear direction, and one refrigerant plate element 8 is provided. Is configured.

The refrigerant plate element 8 is placed vertically such that the thickness direction thereof faces the front-rear direction. An inlet 13R for the refrigerant R is provided at the lower end side of the vertically arranged refrigerant plate element 8, and an outlet through which the refrigerant R flowing inside the element flows out to the upper end side of the refrigerant plate element 8 is provided. 14R is provided.
Hereinafter, the detail of each part which comprises the plate element 8 for refrigerant | coolants is demonstrated.

  The side bar member 11 constituting the refrigerant plate element 8 is a long rectangular bar formed of aluminum or stainless steel. The side bar member 11 is disposed in a state in which the longitudinal direction is directed in the vertical direction and is separated from the left and right by a predetermined interval. The distance between the pair of side bar members 11 is the width of the refrigerant plate element 8, and the length of the side bar member 11 is the length of the refrigerant plate element 8. The thickness of the side bar member 11 (the thickness in the front-rear direction) is the height of the flow path through which the refrigerant R flows.

As shown in FIGS. 2A and 4, a fin portion 10 for the refrigerant plate element 8 is disposed between the pair of left and right side bar members 11. The fin portion 10 of the present embodiment is composed of a single plate (a single fin member 10R) that fits between a pair of left and right sidebar members 11.
The fin member 10 </ b> R has a rectangular shape, and linear concave and convex grooves are press-formed parallel to the right and left sides of the rectangle. The straight concave / convex grooves serve as the straight flow path 18, the lower end of the straight flow path 18 is connected to the inlet 13 </ b> R of the refrigerant plate element 8, and the upper end of the straight flow path 18 is connected to the outlet 14 </ b> R of the refrigerant plate element 8. ing. Therefore, the refrigerant R that has entered from the inlet 13R flows upward along the longitudinal direction of the linear flow path 18, and is discharged from the outlet 14R to the outside.

  The pair of sidebar members 11 described above and the fin portion 10 sandwiched between the sidebar members 11 in the width direction are sandwiched by a pair of front and rear separators 12. The separator 12 is also formed of aluminum or stainless steel and has a rectangular shape. The concave and convex grooves formed on the fin member 10 </ b> R are configured such that the bottom of the concave portion and the top of the convex portion are in contact with the separator 12.

The side bar member 11, the fin member 10R, and the separator plate 12 are fixed to each other by brazing, diffusion bonding, welding, or the like, and a strongly integrated refrigerant plate element 8 is formed. .
<< Plate element for air >>
On the other hand, as shown in FIGS. 2A and 4, the plate element 9 for air is provided in a fin portion 10 in which concave and convex grooves are formed, a side bar member 11 provided in a pair of upper and lower sides, and a pair of front and rear. And a separator 12. After the fin portion 10 is sandwiched between the pair of side bar members 11 from above and below, a separator 12 is attached so as to cover the fin portion 10 and the side bar member 11 from the front and rear direction, and one air plate element 9 is provided. Is configured.

The air plate element 9 is placed vertically so that the thickness direction thereof faces the front-rear direction. Further, the two core portions in which the refrigerant plate element 8 and the air plate element 9 are laminated so that the outlet 14A from which the air A flowing inside the air plate element 9 flows out are opposed to each other. It is provided as shown in (c).
An inlet 13A for air A serving as a heat source is provided on the right end side of the right air plate element 9R placed vertically on the right side, and air that has flowed inside the element is provided on the left end side of the right air plate element 9R. An outlet 14A through which A flows out is provided. In addition, an air inlet 13A serving as a heat source is provided on the left end side of the left air plate element 9L placed vertically on the left side, and flows inside the element on the right end side of the left air plate element 9L. An outlet 14A through which air A flows out is provided.

Hereinafter, the details of each part constituting the air plate element 9 will be described.
As shown in FIG. 4, the air plate element 9 of the present embodiment is provided with a pair of side bar members 11 arranged vertically. The side bar member 11 is a substantially rectangular bar formed of aluminum, stainless steel, or the like, and is disposed such that the longitudinal direction is directed to the left-right direction. The side bar member 11 disposed below has a trapezoidal shape that is thick vertically on the air A inlet 13A side and thin vertically on the air A outlet 14A side. The side bar member 11 disposed above is thin in the vertical direction on the air A inlet 13 </ b> A side and has a thick trapezoidal shape in the vertical direction on the air A outlet 14 </ b> A side. The difference in thickness corresponds to the inclination angle of the inclined channel 19. The length of the side bar member 11 is the width of the air plate element 9. The thickness of the side bar member 11 (the thickness in the front-rear direction) is the height of the flow path through which the air A passes.

  The plate element 9 for air is laminated | stacked on the plate element 8 for refrigerant | coolants mentioned above, and becomes a core part of the air heat exchanger 5 (plate fin heat exchanger). Therefore, the vertical length of the air plate element 9 and the vertical length of the refrigerant plate element 8 are the same, and the width of the air plate element 9 and the width of the refrigerant plate element 8 are the same. Yes.

As shown in FIGS. 2A and 4, a fin portion 10 for the air plate element 9 is disposed between the pair of upper and lower side bar members 11. The fin portion 10 of the present embodiment is composed of a single plate (a single fin member 10A) that fits between a pair of upper and lower side bar members 11.
10A of fin members are exhibiting the rectangular shape, and the linear uneven | corrugated groove | channel is press-formed in parallel with the upper side and lower side of a rectangle. The fin member 10 </ b> A is provided so that the linear uneven groove is inclined with respect to the outer shape of the air plate element 9 (the upper side of the upper side bar member 11 or the lower side of the lower side bar member 11). . Since the fin member 10 </ b> A is provided in this way, the fin member 10 </ b> A functions as the inclined channel 19. The fin member 10 </ b> A is provided on the side bar member 11 so that the inclined direction of the inclined channel 19 gradually decreases with respect to the air A flow. The inclined upper end of the inclined channel 19 is connected to the inlet 13A of the air plate element 9, and the inclined lower end of the inclined channel 19 is connected to the outlet 14A of the air plate element 9.

The inclination angle in the inclined flow path 19 may be an angle that allows the frost attached to the fin member 10A during heat exchange to flow down naturally as water droplets. In addition, since the refrigerant | coolant R flows upwards from the downward direction, the direction below the air plate element 9 tends to be frosted. Thus, it is also preferable to determine the inclination angle in consideration of the degree of frosting.
The pair of sidebar members 11 described above and the fin portion 10 </ b> A sandwiched between the sidebar members 11 are sandwiched between the pair of front and rear separators 12. The separator plate 12 is also formed of aluminum, stainless steel or the like. The concave and convex grooves formed in the fin member 10 </ b> A are configured such that the bottom of the concave portion and the top of the convex portion are in contact with the separator 12.

The side bar member 11, the fin member 10A, and the separator plate 12 are fixed to each other by welding or the like, and the air plate element 9 that is firmly integrated is formed.
In summary, since the air plate element 9 has the inclined flow path 19 extending in the left-right direction, the air A introduced from the inlet 13A flows along the uneven groove until reaching the outlet 14A. The pressure loss is also very low. Furthermore, since the inclined flow path 19 is provided, the frost attached to the fin member 10A during heat exchange can be flown down naturally as water droplets, and a reduction in heat exchange efficiency can be avoided.
<< Core part >>
The refrigerant plate elements 8 and the air plate elements 9 described above are alternately stacked to constitute the air heat exchanger 5 (the core portion of the air heat exchanger 5).

  That is, as shown in FIG. 2 and FIG. 4B, the refrigerant plate element 8 constituting the core portion is configured such that the inlet 13R of the refrigerant R is on the lower side and the outlet 14R of the refrigerant R is on the upper side. It is placed vertically. Then, the air plate elements 9 are stacked in a vertically placed state so as to sandwich the vertically placed refrigerant plate elements 8. The vertically placed air plate element 9 has an inlet 13A and an outlet 14A for air A facing in the left-right direction.

  At this time, as shown in FIG. 6, the height of the inclined flow path 19 of the air plate element 9 is higher than the height of the straight flow path 18 of the refrigerant plate element 8 (for example, about twice). It is good to do so. It is well known that the heat transfer coefficient of the air A is lower than that of the refrigerant R. By increasing the flow rate of the air A, it is possible to increase the (apparent) heat transfer on the air plate element 9 side. Become.

As shown in FIG. 2, when laminating each element, the separator plate 12 between the refrigerant plate element 8 and the air plate element 9 is used as one sheet, and the refrigerant R is placed on one side of the separator plate 12. The air A flows on the other side of the separator 12.
Now, as shown in FIGS. 3C and 5, the air heat exchanger 5 of the present invention includes a fan 7 that generates an upward flow of air upward, and is below the fan 7 and left and right. On both sides, core portions (the right core portion and the left core portion) are provided.

The right core portion and the left core portion are arranged and configured in a mirror image with respect to the rotation axis of the fan 7. Therefore, the air plate element 9 (right air plate element 9R) constituting the right core portion and the air plate element 9 (left air plate element 9L) constituting the left core portion are for right air. The air A inlet 13A is directed to the right of the plate element 9R, and the air A outlet 14A is directed to the left. The air A inlet 13A is directed to the left of the left air plate element 9L. The outlet 14A of the air A is directed.
<< Operation mode >>
Next, the operation | movement aspect of the air heat exchanger 5 with which the heat pump apparatus 1, especially the heat pump apparatus 1 was equipped is described.

  In the heat pump apparatus 1 of FIG. 1, the refrigerant R that has become a liquid by releasing heat from the use side heat exchanger 3 is decompressed by the expansion valve 4 and returns to the air heat exchanger 5. The returned liquid refrigerant R is guided from the inlet 13R (lower side) of the refrigerant plate element 8 constituting the air heat exchanger 5 to the linear flow path 18 in the refrigerant plate element 8. In the first half of the straight flow path 18, in other words, below the refrigerant plate element 8, the refrigerant R is in a liquid state. The liquid refrigerant R (secondary medium) receives heat from the air A (primary medium) of the air plate element 9 while passing through the straight flow path 18 inside the refrigerant plate element 8. Thus, the refrigerant R is gradually vaporized, and the vaporization is almost completed at the outlet 14R (upper side) of the refrigerant plate element 8.

On the other hand, air A, which is a heat source for supplying heat to the liquid refrigerant R, is arranged so as to be in contact with the refrigerant plate element 8, the inlet 13 </ b> A (right side) of the right air plate element 9 </ b> R and the left air plate element. It is introduced from the 9L inlet 13A (left side) by the forcing force of the fan 7 or the like.
The air A that has entered from the inlet 13A of the right air plate element 9R flows to the left side through the inclined flow path 19, and the fin member 10A and the separator 12 of the right air plate element 9R (the same as the refrigerant plate element 8). Heat is supplied to the refrigerant R through the separator 12), and is discharged to the outside from the outlet 14A (left side) of the right air plate element 9R.

The air A that has entered from the inlet 13A of the left air plate element 9L flows to the right side through the inclined flow path 19, and the fin member 10A and the separator 12 of the left air plate element 9L (the same as the refrigerant plate element 8). Heat is supplied to the refrigerant R through the separator 12), and is discharged to the outside from the outlet 14A (right side) of the left air plate element 9L.
In this case, frost generated in the right-side air plate element 9R and water droplets generated at the time of defrosting flow toward the outlet 14A due to the inclination of the inclined flow path 19, and the central portion of the air heat exchanger 5 (right-side air plate element) 9R and the left air plate element 9L).

The refrigerant R vaporized in the air heat exchanger 5, that is, the refrigerant R discharged from the outlet 14 </ b> R of the refrigerant plate element 8 is sucked into the compressor 2 through the pipe 6. The gas is compressed and sent to the use side heat exchanger 3.
As described above, in the present invention, even when frost is generated using the air heat exchanger 5 employing the air plate element 9 provided with the inclined flow path 19 that enables the inclined flow of the air A, the efficiency is high. The heat pump device 1 is realized. Further, the air plate element 9 itself is not inclined and disposed, but the fin portion 10 provided inside the air plate element 9 is obliquely disposed and the air plate element 9 itself is disposed without being inclined. For this reason, an air heat exchanger excellent in design and function can be realized.
<< Modified example of plate element for refrigerant >>
The refrigerant plate element 8 described above has a straight flow path extending in the vertical direction, but the configuration is not limited to this.

Thus, hereinafter, modifications of the refrigerant plate element will be described. The inside of the refrigerant plate element according to this modification is shown in FIG. In addition, the same code | symbol is attached | subjected about the same structure as the structure mentioned above, and the same description is not repeated.
As shown in FIG. 7, an inlet 13R for the refrigerant R is provided at the lower end side of the refrigerant plate element 8, and the refrigerant R flowing inside the element is externally provided at the upper end side of the refrigerant plate element 8. An outlet 14 </ b> R is provided to flow out.

  Inside the refrigerant plate element 8, a meandering flow path 15 is provided which is narrower than the refrigerant plate element 8 and is formed to meander. The meandering channel 15 communicates with an inlet 13R provided on the lower end side of the refrigerant plate element 8 and communicates with an outlet 14R, and the refrigerant R flows through the channel. The meandering channel 15 operates as a refrigerant speed increasing means for increasing the flow rate of the refrigerant R flowing inside.

  On the lower end side of the side bar member 11, a closing bar member 17 having a length that is approximately half the distance between the side bar members 11 is provided. The closing bar member 17 is a long rectangular bar formed of aluminum or stainless steel. The closing bar member 17 is arranged so that the longitudinal direction thereof is directed in the left-right direction, and the right end of the closing bar member 17 is in contact with the right side bar member 11. Therefore, a space is generated between the left end of the closing bar member 17 and the left side bar member 11, and this space serves as the inlet 13 </ b> R for the refrigerant R. That is, the closing bar member 17 facing in the left-right direction closes the right side of the lower end portion of the refrigerant plate element 8, thereby forming the inlet 13 </ b> R having a width that is approximately ½ of the width of the refrigerant plate element 8. Yes.

A space is also formed between the upper ends of the pair of sidebar members 11, and this space serves as an outlet 14 </ b> R for the refrigerant R.
As shown in FIG. 7, between the pair of sidebar members 11, a fin portion 10 formed by bending a plate made of aluminum, stainless steel or the like into an uneven shape is provided. The fin portion 10 of this embodiment is configured by combining a plurality of fin members 16.

  The fin member 16 has a triangular or parallelogram shape. The triangular fin member 16 is bent in parallel to the base of the triangle to form an uneven groove parallel to the base. The parallelogram-shaped fin member 16 is bent in parallel to the upper side and the lower side, and concave and convex grooves parallel to the upper side and the lower side are formed. The pitch of the concave and convex grooves of each fin member 16 is the same.

  As shown in FIG. 7, a triangular fin member 16 formed so that the concave and convex grooves are directed in the vertical direction is connected to the inlet 13 </ b> R of the refrigerant plate element 8. Further, the triangular fin member 16 is connected to a parallelogram fin member 16 formed so that the concave and convex grooves are directed in the left-right direction. The left and right widths of the triangular fin members 16 are the same as the vertical widths of the parallelogram fin members 16 and are about ½ of the width of the refrigerant plate element 8.

The parallelogram-shaped fin member 16 described above is further connected to the triangular fin member 16, and the repetition continues to the upper end side of the refrigerant plate element 8, that is, the outlet 14R.
Thus, the meandering flow path 15 extending from the inlet 13R to the outlet 14R is formed by a series of concave and convex grooves formed by a combination of the plurality of fin members 16. The flow path width of the meandering flow path 15 is determined by the width of the fin member 16. The width of the meandering flow path 15 is about ½ of the width of the refrigerant plate element 8, in other words, the vertical flow path provided in the conventional refrigerant plate element. In addition, the flow path length of the meandering flow path 15 is about 2 times the vertical length of the refrigerant plate element 8, in other words, the flow path length of the straight flow path that is provided in the conventional refrigerant plate element. It has been doubled.

Therefore, the flow rate of the refrigerant R flowing into the refrigerant plate element 8 of the present embodiment increases as compared with the conventional refrigerant plate element. That is, the meandering channel 15 acts as a refrigerant speed increasing means.
The pair of sidebar members 11 described above and the fin portion 10 sandwiched between the sidebar members 11 in the width direction are sandwiched by a pair of front and rear separators 12. The separator 12 is also formed of aluminum or stainless steel and has a rectangular shape. Fin member 16
As for the concave and convex grooves formed in, the bottom part of the concave part and the top part of the convex part are configured to be in contact with the separator plate 12.

The side bar member 11, the fin member 16, and the separator plate 12 are fixed to each other by brazing, diffusion bonding, welding, or the like, and the plate element 8 for refrigerant that is firmly integrated is formed. .
In the refrigerant plate element 8 configured as described above, by causing the flow path of the refrigerant R to meander, the flow rate of the refrigerant R flowing through the flow path is increased and the heat transfer characteristics are improved. In addition, since the distance through which the refrigerant R flows from the inlet 13R to the outlet 14R becomes longer, the contact area between the refrigerant R and the separator 12 increases, and heat transfer can be increased.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. In particular, in the embodiment disclosed this time, matters that are not explicitly disclosed, for example, operating conditions and operating conditions, various parameters, dimensions, weights, volumes, and the like of a component deviate from a range that a person skilled in the art normally performs. Instead, values that can be easily assumed by those skilled in the art are employed.

DESCRIPTION OF SYMBOLS 1 Heat pump apparatus 2 Compressor 3 Use side heat exchanger 4 Expansion valve 5 Air heat exchanger 6 Piping 7 Fan 8 Refrigerating plate element 9 Air plate element 9R Right air plate element 9L Left air plate element 10 Fin part 10R (For refrigerant) fin member 10A (for air) fin member 11 side bar member 12 separator 13R (refrigerant) inlet 13A (air) inlet 14R (refrigerant) outlet 14A (air) outlet 15 meandering channel 16 ( (For refrigerant according to modification) Fin member 17 Blocking bar member 18 Straight flow path 19 Inclined flow path R Refrigerant (secondary medium)
A Air (Primary medium)

Claims (6)

A compressor that compresses the refrigerant in a circulation path through which the refrigerant circulates, an air heat exchanger that performs heat transfer from the external air to the refrigerant, and a use-side heat exchanger that performs heat transfer from the refrigerant to the use side In the heat pump device provided with
The air heat exchanger is a plate fin type heat exchanger in which a refrigerant plate element through which refrigerant flows and an air plate element through which air flows are laminated.
2. A heat pump device according to claim 1, wherein the air plate element is provided with an inclined flow path formed so that air flows and is inclined downward along the air flow direction.   2. The heat pump device according to claim 1, wherein the inclination angle of the inclined flow path is an angle that can be discharged to the outside of the air plate element when frost attached to the air plate element is liquefied. .   3. The heat pump device according to claim 1, wherein a height of the inclined flow path of the air plate element is set to be higher than a fin height of the straight flow path of the refrigerant plate element. 4.   The heat pump device according to any one of claims 1 to 3, wherein the air plate elements are stacked such that the number of stages of the air plate elements is larger than the number of stages of the refrigerant plate elements.   The heat pump device according to any one of claims 1 to 4, wherein an air plate element is stacked so as to sandwich the refrigerant plate element.   The heat pump device according to any one of claims 1 to 5, wherein the air heat exchanger is provided with a fan for forcibly introducing air into the air heat exchanger.