JP2017141979A - Heat exchanger and heat pump system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger configured to flow supercritical fluid as heat medium to a plurality of flow passages, which can suppress drift between the plurality of flow passages to suppress deterioration of heat exchange performance of the entire heat exchanger.SOLUTION: A heat exchange with supercritical fluid as heat medium includes: a housing into which fluid to be heated is introduced; a plurality of flow passages that are provided in parallel inside the housing, and in which the supercritical fluid flows; an inlet flow passage communicating with upstream ends of the plurality of flow passages; an outlet flow passages communicating with downstream ends of the plurality of flow passages; and an orifice with one stage or multistage provided along a flow direction of the supercritical fluid for each of the plurality of flow passages.SELECTED DRAWING: Figure 1

Description

  The present disclosure relates to a heat exchanger using a supercritical fluid as a fluid to be heated and a heat pump system including the heat exchanger.

As a heat exchanger for air heating used in a dryer or the like, an erotic fin type fin tube heat exchanger using steam or an electric heater is often used. As a heat exchanger for air heating incorporated in a heat pump system, a fin tube type heat exchanger using copper tubes and aluminum fins is used.
In a heat exchanger incorporated in a heat pump system, in order to heat a fluid to be heated to a high temperature, a supercritical fluid having a high thermal conductivity may be used as a heat medium.
For example, Patent Document 1 discloses a heat pump system including a heat exchanger that heats an external fluid with a large temperature difference using a supercritical heat medium.

JP-T-2015-527559

  When performing large temperature difference heating of air with a finned tube heat exchanger, the number of heat medium flow paths can be increased to improve heating performance. When a supercritical heat medium with high thermal conductivity is supplied to multiple flow paths, a supercritical fluid with low kinematic viscosity has low pressure loss in the flow paths, and therefore, drift tends to occur between the multiple flow paths. . As a result, a difference in the flow rate of the heat medium occurs in each flow path, temperature unevenness occurs at the outlet of the heat exchanger, and the heating performance of the heat exchanger may deteriorate.

  In view of the above problems, at least one embodiment of the present invention is a heat exchanger in which a supercritical fluid is allowed to flow as a heat medium in a plurality of flow paths. It aims at suppressing the fall of the heat exchange performance of the whole exchanger.

(1) A heat exchanger according to some embodiments of the present invention includes:
A heat exchanger using a supercritical fluid as a heat medium,
A housing into which the fluid to be heated is introduced;
A plurality of flow paths provided in parallel inside the housing and through which the supercritical fluid flows;
An inlet channel communicating with an upstream end of the plurality of channels;
An outlet channel communicating with the downstream ends of the plurality of channels;
One or more stages of orifices provided along the flow direction of the supercritical fluid in each of the plurality of flow paths;
Is provided.
According to the configuration of (1) above, by providing the orifice in each of the plurality of flow paths through which the supercritical fluid flows, the pressure loss of the supercritical fluid increases in the plurality of flow paths. The difference in pressure loss between the flow paths can be offset. Thereby, since the drift which arises between several flow paths can be suppressed, the flow volume difference of a supercritical fluid is eliminated between each flow path, and the fall of the heat exchange performance of the whole heat exchanger can be suppressed.
In addition, by using a supercritical fluid as a heat medium, there is no condensation process in the process of heating the fluid to be heated, and the temperature changes continuously with heat dissipation. (C.fwdarw.200.degree. C.), high-efficiency heating with low loss of exergy can be performed.

(2) In some embodiments, in the configuration of (1),
The plurality of flow paths are formed in a waveform along the flow direction of the supercritical fluid.
According to the configuration of (2) above, the pressure loss of the supercritical fluid flowing through each flow path can be further increased by forming the flow path of the supercritical fluid in a waveform. For this reason, the pressure loss difference between the plurality of flow paths can be further offset, so that the drift between the plurality of flow paths can be more effectively suppressed.

(3) In some embodiments, in the configuration of (1) or (2),
Each of the plurality of flow paths extends along the flow direction of the heated fluid, and the plurality of flow paths are arranged in parallel in a direction intersecting the flow direction of the heated fluid,
The inlet channel and the outlet channel extend in a direction intersecting with a direction in which the plurality of channels extend,
A heat medium supply channel communicating with the inlet channel at at least both ends of the inlet channel;
A heat medium discharge path communicating with the outlet flow path at at least both ends of the outlet flow path;
Is further provided.
According to the configuration of (3) above, the heat medium supply path communicates with at least both ends of the inlet flow path, so that the distance from the heat medium supply path to each flow path is averaged in the extending direction of the inlet flow path. The difference in pressure loss of the heat medium (supercritical fluid) to the inlet of each flow path can be reduced. Similarly, the heat medium discharge path communicates with at least both ends of the outlet flow path, whereby the distance from the heat medium supply path to each flow path can be averaged in the extending direction of the outlet flow path. A difference in pressure loss of the heat medium from the outlet to the heat medium discharge path can be reduced.
Accordingly, the difference in pressure loss between the plurality of channels from the inlet channel to the outlet channel can be further reduced, so that the drift of the heat medium flowing through the plurality of channels can be effectively suppressed.

(4) In some embodiments, in any one of the configurations (1) to (3),
The plurality of flow paths are
A first plate-like body in which a hole for forming a flow path and a groove for forming the orifice are formed;
A second plate that is bonded to one surface of the first plate and closes one of the holes;
A third plate that is joined to the other surface of the first plate, closes the other opening of the hole, and closes the opening of the groove;
Formed with.
According to the configuration of (4) above, the plurality of flow paths can be formed simply and at low cost by overlapping the first to third plate-like bodies. Further, by arranging the flat and simple plate-like bodies at intervals in the flow path of the fluid to be heated, a large number of flow paths can be arranged to face the fluid to be heated. Thus, the heat exchange performance of a heat exchanger can be improved by forming many flow paths.

(5) In some embodiments, in the configuration of (4),
The hole is formed by double-sided etching.
According to the configuration of (5) above, the fine channel can be accurately formed by forming the hole by double-sided etching.

(6) In some embodiments, in the configuration of (4) or (5),
The groove is formed by single-sided etching.
According to the configuration of (6) above, an orifice can be formed easily and accurately by forming the groove by single-sided etching. Further, by forming an orifice in the flow path by the groove and supporting the flow path with the orifice, the strength of the flow path can be increased, and thereby durability against a high-pressure supercritical fluid can be improved.

(7) In some embodiments, in any one of the configurations (1) to (6),
The plurality of channels are fine channels having a cross-sectional diameter of 1 mm or less.
According to the configuration of (7) above, since the plurality of channels are fine channels called “microchannels” having a cross-sectional diameter of 1 mm or less, a large number of supercritical fluid channels are provided in a narrow space. Since the rows can be formed, the heat exchange amount as a whole heat exchanger can be increased, the heat exchanger can be made compact, and the amount of the heat medium held can be reduced. Furthermore, durability with respect to a high pressure supercritical fluid can be improved by making a some flow path into a fine flow path.
Moreover, the effect of increasing pressure loss can be improved by forming the orifice in the fine flow path.

(8) A heat pump system according to at least one embodiment of the present invention includes:
A circulation path through which the heat medium circulates;
A heat pump cycle component device provided in the circulation path;
With
The heat pump cycle component device is:
A compressor for compressing the heat medium into a high-temperature and high-pressure supercritical fluid;
The heat exchanger according to any one of claims 1 to 7, wherein the supercritical fluid is a heat medium;
An expansion part for decompressing the heat medium after heat exchange in the heat exchanger;
An evaporator for exchanging heat and vaporizing the heat medium and the heat source medium decompressed in the expansion section;
Is provided.
According to the configuration of (8), in the heat exchanger, by providing the orifice in each of the plurality of flow paths through which the supercritical fluid flows, the pressure loss of the supercritical fluid flowing through each flow path is increased, Thereby, the drift which arises between each flow path can be suppressed, and the fall of the heat exchange performance of the whole heat exchanger can be suppressed.
In addition, by using a supercritical fluid as a heat medium, there is no condensation process in the process of heating the fluid to be heated, and the temperature changes continuously with heat dissipation. High-efficiency heating with low loss can be performed.

  According to at least one embodiment of the present invention, in a heat exchanger having a plurality of flow paths in which a supercritical fluid flows and is arranged in parallel, uneven flow is suppressed between the plurality of flow paths, and heat exchange of the entire heat exchanger is performed. A decrease in performance can be suppressed.

It is a front view of the heat exchanger which concerns on one Embodiment. It is a side view of the heat exchanger which concerns on one Embodiment. It is the front view to which the A section of the heat exchanger concerning one embodiment was expanded. It is a front view (BB view in Drawing 3) showing one side of a tabular object concerning one embodiment. It is a front view (CC view in FIG. 3) which shows the other surface of the plate-shaped body which concerns on one Embodiment. It is the front view which expanded a part of plate-shaped object concerning one embodiment. It is sectional drawing which follows the DD line | wire in FIG. It is sectional drawing which follows the EE line in FIG. (A) is a graph which shows the pressure loss of the supercritical fluid which concerns on a comparative example, (B) and (C) are graphs which show the pressure loss of the supercritical fluid which concerns on embodiment. It is a systematic diagram of the heat pump system concerning one embodiment. It is a Mollier diagram of a heat pump system concerning one embodiment.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples.
For example, expressions expressing relative or absolute arrangements such as “in a certain direction”, “along a certain direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” are strictly In addition to such an arrangement, it is also possible to represent a state of relative displacement with an angle or a distance such that tolerance or the same function can be obtained.
For example, an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
For example, expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
On the other hand, the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of other constituent elements.

As shown in FIGS. 1 to 3, the heat exchanger 10 according to some embodiments of the present invention uses a supercritical fluid as a heat medium and heats the fluid Fh to be heated by the supercritical fluid. The heat exchanger 10 includes a housing 12 into which a heated fluid Fh heated fluid is introduced.
As shown in FIGS. 4 and 5, a plurality of flow paths 14 through which a supercritical fluid flows as a heat medium are provided in parallel inside the housing 12. In addition, an inlet channel 16 that communicates with the upstream ends of the plurality of channels 14 and an outlet channel 18 that communicates with the downstream ends of the plurality of channels 14 are provided. Furthermore, each of the plurality of flow paths 14 includes one or more stages of orifices 20 provided along the flow direction of the supercritical fluid.

The flow rate Q of the fluid flowing through the flow path is proportional to the 1/2 power of the pressure loss, as shown in the following equation (i).
Q = C _A · ΔP ^1/2 (i)
Here, C _A is the flow rate constant, [Delta] P is the pressure loss.
According to the above configuration, since the orifice 20 is provided in each of the plurality of flow paths 14, the pressure loss of the supercritical fluid flowing through the plurality of flow paths 14 increases, and therefore the pressure loss between the flow paths due to other factors. Can be offset. Thereby, since the drift which arises between several flow paths 14 can be suppressed, the flow volume difference of a supercritical fluid is eliminated between each flow paths, and the fall of the heat exchange performance of the whole heat exchanger can be suppressed.
In addition, by using a supercritical fluid as a heat medium, there is no condensation process in the process of heating the fluid Fh to be heated, and therefore the temperature changes continuously with heat dissipation. (100 ° C. → 200 ° C.), high-efficiency heating with low exergy loss can be performed.

  In the illustrated embodiment, as shown in FIG. 5, the orifices 20 are provided in a plurality of stages along the flow direction of the supercritical fluid.

In some embodiments, as shown in FIGS. 4 to 6, the plurality of flow paths 14 are formed in a waveform along the flow direction of the supercritical fluid Fs.
Thus, by forming the flow path 14 of the supercritical fluid Fs in a waveform, the pressure loss of the supercritical fluid Fs flowing through each flow path can be further increased. Thereby, the pressure loss difference between the plurality of flow paths 14 can be further offset, and the drift between the plurality of flow paths 14 can be further effectively suppressed.
In the illustrated embodiment, the flow direction of the heated fluid Fc and the flow direction of the supercritical fluid Fs are set to be alternating with each other. As a result, the temperature difference during heat exchange between the heated fluid Fc to be heat exchanged and the supercritical fluid Fs can be increased, and the amount of heat exchange can be increased.

In some embodiments, as shown in FIGS. 4 to 6, each of the plurality of channels 14 extends along the flow direction of the heated fluid Fc, and the plurality of channels 14 are heated fluid Fc. Are arranged in parallel in a direction crossing the flow direction. As shown in FIGS. 4 and 5, the inlet channel 16 and the outlet channel 18 extend in a direction intersecting the flow direction of the heated fluid Fc.
As shown in FIG. 4, the supply path 22 for the supercritical fluid Fs communicates with the inlet flow path 16 at at least both ends of the inlet flow path 16, and the discharge path 24 for the supercritical fluid Fs flows at least at both ends of the outlet flow path 18. To the outlet channel 18.
In this way, the supply path 22 communicates with at least both ends of the inlet flow path 16, whereby the distance from the supply path 22 to each flow path 14 can be averaged in the extending direction of the inlet flow path 16. The difference in pressure loss of the supercritical fluid from 16 to the inlet of each flow path 14 can be reduced. Similarly, the discharge path 24 communicates with at least both ends of the outlet flow path 18, so that the supercritical fluid from the outlet of each flow path 14 to the inlet of the discharge path 24 in the extending direction of the outlet flow path 18. The difference in pressure loss can be reduced.
As a result, the difference in pressure loss of the supercritical fluid flowing through each of the plurality of flow paths 14 can be reduced, so that the drift of the supercritical fluid between the plurality of flow paths 14 can be suppressed.

In the illustrated embodiment, as shown in FIGS. 4 and 5, the plurality of flow paths 14 are in a direction orthogonal to the flow direction of the fluid Fc to be heated (the direction of the arrow w in FIG. 1, hereinafter also referred to as “heat exchanger width direction”). Arranged in parallel. Further, the inlet channel 16 and the outlet channel 18 extend in a direction orthogonal to the flow direction of the heated fluid Fc.
1, 2, and 4, the supply path 22 communicates with the inlet flow path 16 at two ends of the inlet flow path 16, and the discharge path 24 has two ends of the outlet flow path 18. To the outlet channel 18.
The supply path 22 opens in the supply section 26 provided at both ends of the heat exchanger width direction (width direction of the flow path of the heated fluid Fh) on the upper surface of the housing 12 at the upstream end in the flow direction of the heated fluid Fh and vertically. And communicate with each of the plurality of inlet channels 16 in the vertical direction.
The discharge passage 24 opens to the discharge portions 28 provided at both ends in the heat exchanger width direction on the upper surface of the housing 12 at the downstream end in the flow direction of the fluid to be heated Fc, and extends in the vertical direction. It communicates with each of the flow paths 18.

In some embodiments, as shown in FIG. 3, the plurality of flow paths 14 include a first plate 30, a second plate 32, and a third plate 34 that are stacked on each other. Is done.
As shown in FIGS. 7 and 8, the first plate-like body 30 has holes (through holes) 36 for forming a plurality of flow paths 14 through which a supercritical fluid flows and grooves 38 for forming the orifices 20. Is formed.
The second plate-like body 32 is joined to one surface of the first plate-like body 30 and closes one opening of the hole 36. The third plate-like body 34 is joined to the other surface of the first plate-like body 30 to block the other opening of the hole 36 and the opening of the groove 38.
According to this configuration, the plurality of flow paths 14 can be configured at a low cost by the flat laminate 40 in which the first to third plate-like bodies 30, 32, and 34 are overlapped. Further, by arranging the simple laminates 40 at intervals in the flow path of the fluid Fc to be heated, a large number of flow paths 14 can be arranged, so that the heat exchange performance of the heat exchanger 10 can be improved.

In the illustrated embodiment, as shown in FIGS. 1 and 3, the first to third plate-like bodies 30, 32, and 34 have substantially the same size and a quadrangular shape. Holes and grooves are not formed in the second plate-like body 32 and the third plate-like body 34.
In addition, a large number of laminated bodies 40 are arranged at intervals in the vertical direction, and corrugated heat radiation fins 42 are interposed between the laminated bodies 40. The first to third plate-like bodies 30, 32, and 34 are joined to each other by diffusion bonding, for example, and both ends of the radiating fins 42 are joined to the laminated body 40 positioned above and below, for example, by brazing.
Between each laminated body 40, the spacer 44 is interposed at the width direction both ends of the heat exchanger 10, and the side surface of the housing 12 is sealed with the spacer 44 as shown in FIG.

In the exemplary embodiment, holes 36 are formed by double-sided etching.
Thereby, the flow path 14 through which the supercritical fluid Fs flows can be accurately formed as a large number of fine flow paths.

In the exemplary embodiment, groove 38 is formed by single-sided etching.
Accordingly, when the flow path 14 is formed as a large number of fine flow paths, the orifice 20 can be easily formed, and the orifice 20 can be formed accurately. Further, the orifice 20 is formed in the flow path 14 by the groove 38, and the strength of the flow path 14 can be increased by supporting the flow path 14 by the orifice 20, and thereby, the durability against the high-pressure supercritical fluid Fs can be increased. Can be improved.

In the exemplary embodiment, the flow path 14 and the orifice 20 are formed in a fine flow path having a cross-sectional diameter of 1 mm or less.
In this way, since the flow path 14 is formed of so-called “microchannels” having a cross-sectional diameter of 1 mm or less, a large number of rows of the flow paths 14 can be formed in a narrow space. The amount of heat exchange as a whole can be increased. Furthermore, durability with respect to the high-pressure supercritical fluid Fs can be improved by making the plurality of channels into fine channels.
Moreover, the effect of increasing pressure loss can be improved by configuring the orifice 20 with the same fine flow path.

FIG. 9 is a graph schematically showing the pressure loss of the supercritical fluid in the multiple flow paths 14 arranged in parallel in the width direction of the housing 12 of the heat exchanger 10 so as to face the heated fluid Fc. In the figure, ΔP ₁ indicates the pressure loss of the supercritical fluid in the inlet channel 16, ΔP ₂ indicates the pressure loss of the supercritical fluid in the channel 14, and ΔP ₃ indicates the pressure loss of the supercritical fluid in the outlet channel 18. Indicates.

FIG. 9A shows a case where the supply path 22 communicates with one end of the inlet flow path 16 and the discharge path 24 communicates with one end of the outlet flow path 18. 20 shows an example (comparative example) in which 20 is not provided and the flow path 14 extends linearly in the flow direction of the heated fluid Fh instead of a waveform.
In this comparative example, a pressure gradient is generated in the heat exchanger width direction in the inlet channel 16 and the outlet channel 18, and a pressure loss difference is generated between the channels 14. Moreover, since the pressure loss of the supercritical fluid in the flow path 14 is small, the pressure loss difference between the flow paths 14 is not offset. Therefore, a large difference occurs in the flow rate of the supercritical fluid Fs in each flow path 14, and a drift occurs. Due to this drift, temperature unevenness of the heated fluid Fh occurs at the outlet of the heat exchanger 10, and the heat exchange performance may be deteriorated.

FIG. 9B shows a case where the supply path 22 communicates with one end of the inlet flow path 16 and the discharge path 24 communicates with one end of the outlet flow path 18. An example (one embodiment) in which 20 is provided is shown.
In this embodiment, since the pressure loss in the flow path 14 is large, the pressure loss difference between the flow paths 14 between the inlet flow path 16 and the outlet flow path 18 is larger than that in FIG. 9A. Has been killed. Therefore, uneven flow between the flow paths 14 is suppressed, and temperature unevenness is less likely to occur at the outlet of the heat exchanger 10.

FIG. 9C shows a case where the supply path 22 communicates at two ends of the inlet channel 16 and the discharge path 24 communicates at two ends of the outlet channel 18. Shows an example (one embodiment) in which an orifice 20 is provided.
In this embodiment, the pressure loss difference between each flow path 14 in the inlet flow path 16 and the outlet flow path 18 is reduced. Therefore, the difference in pressure loss between the inlet channel 16 and the outlet channel 18 between the channels 14 is further offset than in the embodiment shown in FIG. 9B. Therefore, the occurrence of drift between the flow paths 14 is less likely to occur.

As shown in FIG. 10, the heat pump system 50 according to some embodiments includes a circulation path 52 through which the heat medium circulates and heat pump cycle components provided in the circulation path 52.
The heat pump cycle component device provided in the circulation path 52 includes a compressor 54, the heat exchanger 10 having the above configuration, an expansion unit 56, and an evaporator 58. The compressor 54 compresses the heat exchange medium into a high temperature and high pressure supercritical fluid. The heat medium that has become a supercritical fluid heats the fluid to be heated by the heat exchanger 10. After heating the fluid to be heated, the heat medium is depressurized by the expansion unit 56, and then is evaporated by exchanging heat with the heat source fluid Wh by the evaporator 58.
According to this configuration, the heat exchanger 10 includes the orifice 20 in each of the plurality of flow paths 14 through which the heat medium that has become a supercritical fluid flows, thereby canceling the difference in pressure loss between the plurality of flow paths 14. it can. Thereby, since the drift which arises between several flow paths 14 can be suppressed, the exit temperature nonuniformity of the heat exchanger 10 can be suppressed, and the fall of heat exchange performance can be suppressed.
In addition, since there is no condensation process in the process of heating the fluid Fh to be heated by using a supercritical fluid as a heat medium, the temperature changes continuously with heat dissipation. High-efficiency heating with low exergy loss can be performed.

In the illustrated embodiment, a heat medium heat exchanger 60 is provided in the circulation path 52. The heat medium heat exchanger 60 exchanges heat between the heat medium on the compressor 54 inlet side and the heat medium on the heat exchanger 10 outlet side, and heats the heat medium on the compressor inlet side. The compressor 54 is rotationally driven by a motor 62, and an expansion valve is used as the expansion unit 56. The heated fluid Fh is, for example, air, and the heat source fluid Wh is, for example, heat source water.
FIG. 11 shows a Mollier diagram of the heat pump system according to this embodiment. Points a to f in the figure correspond to a to f given in FIG. 10 and indicate the state quantities of those locations. Δh in the figure indicates the amount of enthalpy with which the heat medium exchanges heat in the heat medium heat exchanger 60.
As the heat medium, for example, NH ₃ , CO ₂ , alternative chlorofluorocarbon, HC system (for example, normal butane), or the like, a heat medium usually used in a heat pump, a refrigerator, or the like can be used.
According to this embodiment, the large temperature difference heating which heats 100 degreeC air to 180 degreeC using the comparatively low temperature heat source water of about 80 degreeC is attained.

  According to at least one embodiment of the present invention, in a heat exchanger that includes a plurality of flow paths that are arranged in parallel and through which a heat medium flows as a supercritical fluid, uneven flow is suppressed between the plurality of flow paths, and the entire heat exchanger The deterioration of the heating performance can be suppressed, and for example, it can be applied to an air heating heat exchanger used in a dryer or the like.

DESCRIPTION OF SYMBOLS 10 Heat exchanger 12 Housing 14 Flow path 16 Inlet flow path 18 Outlet flow path 20 Orifice 22 Supply path 24 Discharge path 26 Supply part 28 Discharge part 30 1st plate-shaped body 32 2nd plate-shaped body 34 3rd board Form 36 Hole 38 Groove 40 Laminate 42 Radiation Fin 44 Spacer 50 Heat Pump System 52 Circulation Path 54 Compressor 56 Expansion Part 58 Evaporator 60 Heat Medium Heat Exchanger 62 Motor Fh Heated Fluid Fs Supercritical Fluid Wh Heat Source Fluid ΔP ₁ , ΔP ₂ , ΔP ₃ Pressure loss

Claims (8)

A heat exchanger using a supercritical fluid as a heat medium,
A housing into which the fluid to be heated is introduced;
A plurality of flow paths provided in parallel inside the housing and through which the supercritical fluid flows;
An inlet channel communicating with an upstream end of the plurality of channels;
An outlet channel communicating with the downstream ends of the plurality of channels;
One or more stages of orifices provided along the flow direction of the supercritical fluid in each of the plurality of flow paths;
A heat exchanger comprising:   The heat exchanger according to claim 1, wherein the plurality of flow paths are formed in a waveform along the flow direction of the supercritical fluid. Each of the plurality of flow paths extends along the flow direction of the heated fluid, and the plurality of flow paths are arranged in parallel in a direction intersecting the flow direction of the heated fluid,
The inlet channel and the outlet channel extend in a direction intersecting with a direction in which the plurality of channels extend,
A heat medium supply channel communicating with the inlet channel at at least both ends of the inlet channel;
A supercritical fluid discharge channel communicating with the outlet channel at at least both ends of the outlet channel;
The heat exchanger according to claim 1, further comprising: The plurality of flow paths are
A first plate-like body in which a hole for forming a flow path and a groove for forming the orifice are formed;
A second plate that is bonded to one surface of the first plate and closes one of the holes;
A third plate that is joined to the other surface of the first plate, closes the other opening of the hole, and closes the opening of the groove;
The heat exchanger according to claim 1, wherein the heat exchanger is formed by:   The heat exchanger according to claim 4, wherein the hole is formed by double-sided etching.   The heat exchanger according to claim 4 or 5, wherein the groove is formed by single-side etching.   The heat exchanger according to any one of claims 1 to 6, wherein the plurality of channels are fine channels having a cross-sectional diameter of 1 mm or less. A circulation path through which the heat medium circulates;
A heat pump cycle component device provided in the circulation path;
With
The heat pump cycle component device is:
A compressor for compressing the heat medium into a high-temperature and high-pressure supercritical fluid;
The heat exchanger according to any one of claims 1 to 7, wherein the supercritical fluid is a heat medium;
An expansion part for decompressing the heat medium after heat exchange in the heat exchanger;
An evaporator for exchanging heat and vaporizing the heat medium and the heat source medium decompressed in the expansion section;
A heat pump system comprising:

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