JP2001263836A - Secondary refrigerant refrigerating cycle system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve a problem of low heat exchanging efficiency of a secondary refrigerant refrigerating cycle system for contacting a primary refrigerant directly with a secondary refrigerant to heat exchange the primary refrigerant with the secondary refrigerant. SOLUTION: The secondary refrigerant refrigerating cycle system comprises at least a heat exchanging tank 4 for contacting the primary refrigerant directly with the secondary refrigerant to heat exchange the primary refrigerant with the secondary refrigerant. In this case, a metal porous material 20 having a plurality of pores and a specific surface area of 500 m2/m3 or more is disposed in the tank 4 to increase a contact area of the primary refrigerant with the secondary refrigerant to efficiently heat exchange the primary refrigerant with the secondary refrigerant. A boundary wall is provided at a flow-out part of the primary and secondary refrigerants from the tank 4 to accelerate a separation of the primary and secondary refrigerants and to decelerate a flowing velocity, thereby improving a separating performance of the primary and secondary refrigerants.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a secondary refrigerant refrigeration cycle apparatus for performing efficient heat exchange by directly mixing and contacting a primary refrigerant and a secondary refrigerant.

[0002]

2. Description of the Related Art In recent years, the global warming problem has been rapidly attracting attention, and HFCs have a great influence on global warming.
Development of a refrigeration cycle device using a natural refrigerant instead of a system refrigerant is urgently required. In particular, the development of a refrigerator-freezer or an air conditioning system using an HC-based natural refrigerant that does not cause ozone layer destruction and does not affect global warming is promising.

In general, when an HC natural refrigerant is used as a refrigerant in a refrigeration cycle apparatus, a direct expansion type (hereinafter referred to as a direct expansion type) is used in order to avoid the danger of the refrigerant leaking and igniting in case of emergency. In the refrigeration cycle apparatus of the (type), there is a need for measures such as reducing the filling amount of the refrigerant.

However, as the size of the refrigeration cycle apparatus increases, the amount of refrigerant required for the refrigeration cycle apparatus mounted on the system increases. Therefore, an HC-based natural refrigerant is used in addition to a small refrigeration cycle apparatus. System deployment is considered difficult.

Therefore, it has been proposed to use a secondary refrigerant system for a refrigeration cycle device requiring a certain amount or more of HC natural refrigerant. In addition, so far, CFC
A refrigeration cycle device of a secondary refrigerant system using a system, HCFC, or ammonia-based refrigerant as a primary refrigerant is employed in large-scale refrigeration and air-conditioning systems such as fan coil units and chilling units in office buildings and the like.

In general, in a refrigeration cycle apparatus of a secondary refrigerant system, cold or warm heat of a primary refrigeration cycle is transmitted to a secondary heat transfer cycle via a double-pipe or plate type intermediate heat exchanger. Indoor air conditioning is performed by circulating a refrigerant and exchanging heat with a secondary refrigerant at an indoor load. In particular, in the plate-type intermediate heat exchanger, the primary refrigerant and the secondary refrigerant exchange heat with each other via the plate, but the specific surface area of the plate where the primary refrigerant and the secondary refrigerant in the heat exchanger indirectly exchange heat. Is as high as 500 m ² / m ³ , there is an advantage that the amount of heat exchange per volume is large and the volume of the intermediate heat exchanger can be reduced.

However, in the direct expansion type refrigeration cycle apparatus, only heat exchange between the primary refrigerant and the internal load is required, whereas in the secondary refrigerant system, heat exchange between the secondary refrigerant and the internal load and the primary refrigerant are not performed. In order to efficiently exchange heat between the primary refrigerant and the secondary refrigerant through the plate by the plate-type intermediate heat exchanger, the temperature difference between the refrigerants is relatively large. Cost. As a result, compared to a direct expansion type refrigeration cycle device, it is necessary to lower the primary refrigerant evaporation temperature during cooling operation or increase the primary refrigerant condensation temperature during heating operation, and the input of the primary refrigeration cycle increases. Therefore, there is a disadvantage that the efficiency of the entire secondary refrigerant refrigeration cycle apparatus is reduced.

As a method for compensating for this drawback, a highly efficient heat exchange between the primary refrigerant and the secondary refrigerant is performed in comparison with the conventional system in which the primary refrigerant and the secondary refrigerant are indirectly exchanged heat with a plate heat exchanger or the like. A secondary refrigerant refrigeration cycle device of a direct heat exchange type which is considered to be possible was proposed (Japanese Patent Application No. 10-16663).
No. 5).

FIG. 7 shows a system configuration example of a conventional direct heat exchange type secondary refrigerant refrigeration cycle apparatus and a configuration example of a heat exchange tank.
And FIG.

FIG. 7 shows an example of a secondary refrigerant refrigeration cycle apparatus in which propane (R29) of HC natural refrigerant is used as the primary refrigerant.
0) shows a system configuration of a direct heat exchange type secondary refrigerant air conditioning system using fresh water as a secondary refrigerant during a cooling operation.

In FIG. 7, the secondary refrigerant refrigeration cycle apparatus of the direct heat exchange type comprises a primary refrigeration cycle and a secondary heat transfer cycle, and the primary refrigeration cycle comprises a compressor 27, a four-way valve 28, Heat exchanger (hereinafter, referred to as an outdoor heat exchanger) 29, a throttle device (hereinafter, referred to as an expansion valve) 3
0, a heat exchange tank 31, each of which is connected by a primary side connection pipe 32.

On the other hand, the secondary heat transfer cycle includes a heat exchange tank 31, a second heat exchanger (hereinafter, referred to as an indoor heat exchanger) 3.
3. A circulation pump 34, which is connected by a secondary connection pipe 35.

The bold line shows the flow of the primary refrigerant during the cooling operation, and the thin line shows the flow of the secondary refrigerant. Part of the primary refrigeration cycle and the secondary heat transfer cycle are packaged in an outdoor unit. The indoor heat exchanger 33 is packaged inside the indoor unit, and the outdoor unit and the indoor unit are connected by a secondary connection pipe 35 and a signal line (not shown).

For operation of the primary refrigeration cycle during cooling, the compressor 27, the four-way valve 28, the outdoor heat exchanger 29 (acting as a condenser), the expansion valve 30, and the heat exchange tank 31 (as an evaporator) The primary refrigerant flows through the primary connection pipe 32 in the order of the four-way valve 28 and the compressor 27.

For operation of the primary refrigeration cycle during heating, the compressor 27, the four-way valve 28, the heat exchange tank 31 (acting as a condenser), the expansion valve 30, and the outdoor heat exchanger 29 (as an evaporator) The primary refrigerant flows through the primary connection pipe 32 in the order of the four-way valve 28 and the compressor 27.

For operation of the secondary heat transfer system,
Regardless of the cooling operation and the heating operation, the secondary refrigerant flows through the secondary connection pipe 35 in the order of the heat exchange tank 31, the indoor heat exchanger 33, the circulation pump 34, and the heat exchange tank 31. At this time, in the heat exchange tank 31, the primary refrigerant and the secondary refrigerant directly contact each other and exchange heat with each other.

FIG. 8 shows a heat exchange tank 31 of a conventional direct heat exchange type secondary refrigerant refrigeration cycle apparatus.

In FIG. 8, the heat exchange tank 31 is divided into a left chamber and a right chamber by a partition plate 36 at the center, and there is no partition plate 36 at the lower center of the heat exchange tank 31; linked. A primary refrigerant inflow pipe 37 and a secondary refrigerant inflow pipe 38 are connected to the upper part of the left chamber of the heat exchange tank 31.
A secondary refrigerant outflow pipe 39 is connected to the center of the bottom surface, and a primary refrigerant outflow pipe 40 for cooling is connected to the upper part of the right chamber of the heat exchange tank 31. Outflow pipes 41 are provided respectively. A primary refrigerant and a secondary refrigerant are sealed in the heat exchange tank 31, and are shaded in the heat exchange tank 31 in FIG. 8.

During the heating operation, the primary refrigerant outflow pipe 41 at the time of heating is used.
Is set so as to always come to the liquid refrigerant portion of the primary refrigerant of the right chamber of the heat exchange tank 31 (the shaded portion of the right chamber of the heat exchange tank 31 in FIG. 8). In the right chamber of the heat exchange tank 31, the primary refrigerant changes its phase from a gas state to a liquid state by heat exchange with the secondary refrigerant. Since the primary refrigerant and the secondary refrigerant do not dissolve in each other, and the specific gravity of the liquid primary refrigerant is lower than the water of the secondary refrigerant, in the right chamber of the heat exchange tank 31, the primary refrigerant in the liquid state is upward, The secondary refrigerant is stored in the secondary storage. Therefore, the tip of the primary refrigerant outflow pipe 41 at the time of heating is always in the heat exchange tank 3.
By setting the primary refrigerant to be the liquid refrigerant portion of the primary refrigerant in the right chamber, the primary refrigerant in the liquid state can be selectively discharged from the heat exchange tank 31.

The flow of the primary refrigerant and the secondary refrigerant in the heat exchange tank 31 is such that the primary refrigerant and the liquid secondary refrigerant in the gas-liquid two-phase state flow from above the left chamber of the heat exchange tank 31 during the cooling operation. The thin line in FIG. 8 indicates the flow of the primary refrigerant, and the thick line indicates the flow of the secondary refrigerant). The primary refrigerant and the secondary refrigerant flow downwardly while performing heat exchange by directly contacting each other.
6 moves from the lower part of the left ventricle to the lower part of the right ventricle. At this time, the high-density secondary refrigerant flows out of the secondary refrigerant outflow pipe 39 at the center of the bottom surface of the heat exchange tank 31, and the low-density primary refrigerant completely evaporates by heat exchange with the secondary refrigerant, and the heat exchange tank 31 It moves from the lower part of the right chamber to the upper part of the right chamber, and flows out of the primary refrigerant outflow pipe 40 during cooling.

In the heating operation, the primary refrigerant and the secondary refrigerant exchange heat in the same flow as in the cooling operation, and the secondary refrigerant flows out of the secondary refrigerant outflow pipe 39 and exchanges heat with the secondary refrigerant. Since the primary refrigerant liquefied from the gas state has a lower density than the secondary refrigerant, it moves to the right chamber of the heat exchange tank 31 and the primary refrigerant in the liquid state stays on the secondary refrigerant in the liquid state. It flows out from the refrigerant outflow pipe 41.

[0022]

However, since the interior of the heat exchange tank 31 in the above-described direct heat exchange type secondary refrigerant air conditioning system is divided into left and right parts by the partition plate 36, the primary refrigerant and the secondary refrigerant are not separated. Since the volume of the refrigerant that can exchange heat is about half of the total volume of the heat exchange tank 31, the heat exchange tank 31
However, there is a problem that the heat exchange efficiency between the primary refrigerant and the secondary refrigerant deteriorates with respect to the size of the volume.

Further, in the heat exchange tank 31, heat exchange cannot be performed sufficiently because there is no structure for increasing the contact area between the primary refrigerant and the secondary refrigerant. In order to improve the heat exchange amount, the heat exchange tank 31 is used.
There was a problem such that the volume of the steel had to be increased.

In consideration of the above problems, the present invention increases the area where the primary refrigerant and the secondary refrigerant are in direct contact with each other to efficiently perform heat exchange, and reliably separates the primary refrigerant and the secondary refrigerant. It is an object to provide a secondary refrigerant refrigeration cycle device.

[0025]

Means for Solving the Problems The first invention (claim 1)
Corresponding to), a compressor that compresses the primary refrigerant, a first heat exchanger for performing heat exchange between the primary refrigerant and an external load, and a throttle device that decompresses and expands the primary refrigerant,
The primary refrigerant and the secondary refrigerant flow in, a heat exchange tank for causing the primary refrigerant and the secondary refrigerant to directly contact and perform heat exchange, the compressor, the first heat exchanger, A primary-side refrigeration cycle having at least a throttle device and a primary-side connection pipe connecting the heat-exchange tank, the heat-exchange tank, a circulation pump, and heat exchange between the secondary refrigerant and an internal load. A second heat exchanger, and a secondary heat transfer cycle having a secondary connection pipe connecting the heat exchange tank, the circulation pump and the second heat exchanger, the heat exchange The secondary refrigerant refrigeration cycle apparatus is characterized in that a contact area increasing means having an uneven shape on the surface and / or having a plurality of holes is arranged in the tank.

According to a second aspect of the present invention (corresponding to claim 2), the contact area increasing means is a metal porous body, a packing (metal filling), or a wire mesh. It is a secondary refrigerant refrigeration cycle device according to the invention.

According to a third aspect of the present invention (corresponding to claim 3), the specific surface area indicating the ratio of the surface area of the contact area increasing means to the volume of the heat exchange tank is 500 m ² / m ³ or more. A secondary refrigerant refrigeration cycle apparatus according to the first or second aspect of the present invention.

A fourth aspect of the present invention (corresponding to claim 4) is that the primary refrigerant and / or the secondary refrigerant is subdivided into a plurality of fluxes and the refrigerant is subdivided into the heat exchange tank. The secondary refrigerant refrigeration cycle apparatus according to any one of the first to third aspects of the present invention, characterized by comprising means.

A fifth aspect of the present invention (corresponding to claim 5) is that the refrigerant subdivision means includes a plurality of primary refrigerant inflow pipes connected to the primary connection pipe and / or the secondary connection pipe. The secondary refrigerant refrigeration cycle apparatus according to the fourth aspect of the present invention, wherein the secondary refrigerant inflow pipe is connected to a plurality of secondary refrigerant inflow pipes.

A sixth aspect of the present invention (corresponding to claim 6) is characterized in that the refrigerant subdivision means is a plate-like body provided in the heat exchange tank and provided with a large number of pores. It is a secondary refrigerant refrigeration cycle device according to a fourth aspect of the present invention.

According to a seventh aspect of the present invention (corresponding to claim 7), the heat exchange tank allows the secondary refrigerant to flow out to the outside and a secondary refrigerant outflow pipe to flow into the secondary refrigerant outflow pipe. The secondary refrigerant refrigeration cycle apparatus according to any one of the first to sixth aspects of the present invention, further comprising a secondary refrigerant cross-sectional area enlarging means for enlarging the cross-sectional area of the secondary refrigerant immediately before.

According to an eighth aspect of the present invention (corresponding to claim 8), the heat exchange tank has at least a plurality of primary refrigerant outflow pipes for allowing the primary refrigerant to flow to the outside. At least one end of the outflow pipe is provided at a position that is equal to or higher than the secondary refrigerant liquid level and equal to or lower than the primary refrigerant liquid level in the heat exchange tank.
To the seventh aspect of the present invention.

According to a ninth aspect of the present invention (corresponding to claim 9), the heat exchange tank has a secondary refrigerant suction preventing means for preventing the secondary refrigerant from being sucked into the primary refrigerant outlet pipe. An eighth aspect of the present invention is the secondary refrigerant refrigeration cycle apparatus according to the present invention.

According to a tenth aspect of the present invention (corresponding to claim 10),
The secondary refrigerant refrigeration cycle according to a ninth aspect of the present invention, wherein at least two flat plates having different openings are provided below the primary refrigerant outflow pipe portion as the secondary refrigerant suction prevention means. Device.

The eleventh invention (corresponding to claim 11) provides:
The secondary refrigerant refrigeration cycle apparatus according to the ninth aspect of the present invention, wherein the secondary refrigerant suction prevention means is a wire mesh provided at a distal end of the primary refrigerant outflow pipe.

The twelfth invention (corresponding to claim 12) provides:
The fifth to the first, wherein the secondary refrigerant inflow pipe is inserted into the heat exchange tank up to near the liquid level of the primary refrigerant and / or the secondary refrigerant in the heat exchange tank.
A secondary refrigerant refrigeration cycle apparatus according to any one of the first to fifth aspects of the present invention.

According to a thirteenth aspect of the present invention (corresponding to claim 13),
In the heat exchange tank, between the distal end of the secondary refrigerant inflow pipe and the distal end of the primary refrigerant outflow pipe, a second for preventing the secondary refrigerant from being sucked into the primary refrigerant outflow pipe. The secondary refrigerant refrigeration cycle apparatus according to any one of the seventh to twelfth aspects of the present invention, wherein a second secondary refrigerant suction preventing means is disposed.

The fourteenth invention (corresponding to claim 14) is:
The secondary refrigerant refrigeration cycle apparatus according to the thirteenth aspect of the present invention, wherein the second secondary refrigerant suction prevention means is a flat plate.

[0039]

Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) As an example of the secondary refrigerant refrigeration cycle apparatus of the present invention, a secondary refrigerant exclusively used for cooling, using propane of HC natural refrigerant as the primary refrigerant and fresh water as the secondary refrigerant. FIG. 1 shows a system configuration of the air conditioning system.

This system comprises a primary refrigeration cycle and a secondary heat transfer cycle. The primary refrigeration cycle includes a compressor 1, a first heat exchanger (hereinafter referred to as an outdoor heat exchanger) 2, a throttle. It comprises an apparatus (hereinafter referred to as an expansion valve) 3, a heat exchange tank 4, an oil separator 5, an accumulator 6, etc., each of which is connected by a primary connection pipe 7, and in which a primary refrigerant and refrigerating machine oil are sealed.

In the secondary heat transfer cycle, a second heat exchanger (hereinafter referred to as an indoor heat exchanger) 8, a circulation pump 9, and a heat exchange tank 4 are connected by a secondary connection pipe 10, The next refrigerant is enclosed.

In FIG. 1, the thick line indicates the flow of the primary refrigerant,
The thin line shows the flow of the secondary refrigerant, and a part of the primary refrigeration cycle and the secondary heat transfer cycle is packaged in the outdoor unit, and the indoor heat exchanger 8 is packaged in the indoor unit. The outdoor unit and the indoor unit are connected by a secondary connection pipe 10 and a signal line (not shown).

The oil separator 5 has an oil return pipe for returning the refrigerating machine oil discharged from the compressor 1 to the suction pipe of the compressor 1 again.

Since the primary refrigerant and the secondary refrigerant are hardly dissolved in each other, and the density of the primary refrigerant is lower than the density of the liquid state of the secondary refrigerant in both the gas state and the liquid state, they are mixed in the heat exchange tank 4. In a short time, the primary refrigerant is at the top, the secondary refrigerant is at the bottom,
It has the property of being separated from each other.

The operation of the primary refrigeration cycle is performed by the compressor 1,
The oil separator 5, the outdoor heat exchanger 2 (acting as a condenser), the expansion valve 3, the heat exchange tank 4 (acting as an evaporator), the accumulator 6, and the compressor 1 are arranged in this order via the primary connection pipe 7. And the primary refrigerant flows.

In the operation of the secondary heat transfer cycle, the secondary refrigerant flows through the secondary connection pipe 10 in the order of the heat exchange tank 4, the indoor heat exchanger 8, the circulation pump 9, and the heat exchange tank 4. .

The primary refrigerant is compressed by the compressor 1, exchanges heat with outdoor air, which is an outdoor load, in the outdoor heat exchanger 2, releases heat and condenses, and is decompressed by the expansion valve 3. At 4, heat exchange is performed with the primary refrigerant to remove heat from the secondary refrigerant, evaporate, and return to the compressor 1.

The secondary refrigerant is cooled by being deprived of heat by the primary refrigerant in the heat exchange tank 4 while being circulated by the circulation pump 9, and is heated by the indoor heat exchanger 8 by depriving the indoor load which is an indoor load of heat. Then, the process returns to the heat exchange tank 4 again.

FIG. 2 shows a configuration of the heat exchange tank 4 according to Embodiment 1 of the present invention.

The heat exchange tank 4 is a cylindrical container, and the flow of the primary refrigerant is indicated by a thick arrow, and the flow of the secondary refrigerant is indicated by a thin arrow. The heat exchange tank 4 includes a primary refrigerant inflow branch portion 11 and a secondary refrigerant inflow branch portion 12, and each refrigerant pipe flowing into the heat exchange tank 4 is branched into, for example, six pipes.

The six-branched primary refrigerant and the secondary refrigerant flow into the heat exchange tank 4 from the six primary refrigerant inflow pipes 13 and the six secondary refrigerant inflow pipes 14, respectively. It flows out from the secondary refrigerant outflow pipe 16.

In the heat exchange tank 4, a primary refrigerant dispersing plate 17 as a means for subdividing the primary refrigerant into a plurality of fluxes, and a primary refrigerant suction preventing plate 18 as a means for expanding the sectional area near the secondary refrigerant outlet. Further, secondary refrigerant suction prevention plates 19a and 19b are provided as first secondary refrigerant suction prevention means, and a metal porous body 20 is provided as a filler in the heat exchange tank 4. The pore diameter of the porous metal body 20 is, for example, about 3 mm.

As described above, the primary refrigerant and the secondary refrigerant are subdivided into a plurality of fluxes and flow into the portion of the metal porous body 20 of the heat exchange tank 4 to mix the primary refrigerant and the secondary refrigerant with each other. This has the effect of promoting heat exchange by increasing the contact area.

The metal porous body 20 has many pores formed in the metal, and has a specific surface area of 500 per volume.
m ² / m ³ or more, and secures a specific surface area equal to or more than that of a plate heat exchanger used in a general indirect heat exchange method.

As a result, the heat exchange performance can be further improved while keeping the outer volume and / or volume equal to or less than that of the plate heat exchanger.

FIG. 3A shows a primary refrigerant dispersion plate 17 as a means for subdividing the primary refrigerant in the heat exchange tank 4 into a plurality of fluxes.
FIG. 4 shows a plan view of a primary refrigerant suction prevention plate 18 as a means for expanding a cross-sectional area near a secondary refrigerant outflow portion.

The primary refrigerant dispersing plate 17 is a donut-shaped disk having a hole for installing a cylindrical primary refrigerant suction preventing plate 18 at the center thereof and having a large number of pores having a diameter of about 1 mm on its surface. It is.

The primary refrigerant suction prevention plate 18 is a cylindrical partition plate, which is inserted into a hole at the center of the primary refrigerant distribution plate 17.

The primary refrigerant dispersion plate 17 and the primary refrigerant suction prevention plate 18 are installed on the bottom of the heat exchange tank 4 in FIG.

FIG. 3B is a schematic view in which the primary refrigerant dispersion plate 17 and the primary refrigerant suction prevention plate 18 are installed on the bottom of the heat exchange tank 4. The primary refrigerant dispersion plate 17 is provided with a certain gap from the bottom inside the heat exchange tank 4, and a cylindrical primary refrigerant suction prevention plate 18 is fitted in the center. The six primary refrigerant inflow pipes 13 are uniformly connected annularly from the bottom of the heat exchange tank 4 to the outside of the primary refrigerant suction prevention plate 18, and the secondary refrigerant outflow pipes 16 are connected to the inside of the primary refrigerant suction prevention plate 18. The heat exchange tank 4 is connected to substantially the center of the bottom surface.

As the first secondary refrigerant suction prevention means, FIG.
FIG. 4A is a plan view of the secondary refrigerant suction prevention plate 19a, and FIG. 4B is a plan view of the secondary refrigerant suction prevention plate 19b.

The secondary refrigerant suction prevention plate 19a is connected to the heat exchange tank 4
Is a disk having a diameter smaller than the inner diameter of the heat exchange tank 4 and is set in a direction perpendicular to the cylindrical axis so that the center substantially coincides with the cylindrical axis of the heat exchange tank 4.

The outer diameter of the secondary refrigerant suction preventing plate 19b is a disk equivalent to the inner diameter of the heat exchange tank 4, but a hole having a diameter smaller than the diameter of the secondary refrigerant suction preventing plate 19a is formed at the center thereof. ing.

FIG. 4C is a schematic diagram showing the secondary refrigerant suction prevention plates 19a and 19b installed on the upper surface of the heat exchange tank 4. The secondary refrigerant suction prevention plates 19a and 19b are fixed with their centers substantially aligned with the central axis of the heat exchange tank 4, and more specifically, below the primary refrigerant outflow pipe 15 and
The liquid refrigerant in the heat exchange tank 4 is installed at a position above the liquid surface of the primary refrigerant and the secondary refrigerant. Primary refrigerant outflow pipe 1
5 is connected to the upper central part of the heat exchange tank 4. The six secondary refrigerant inflow pipes 14 are inserted into the heat exchange tank 4 from the upper part of the heat exchange tank 4, and the tips thereof are located below the secondary refrigerant suction prevention plate 19b.

In the portion where the secondary refrigerant suction preventing plates 19a and 19b interfere with the six secondary refrigerant inflow pipes 14, holes are formed in the secondary refrigerant suction preventing plates 19a and 19b. The next refrigerant inflow pipe 14 penetrates (not shown).

The six secondary refrigerant inflow pipes 14 are inserted from the secondary refrigerant inflow pipe 14 to the front and rear of the liquid mixture of the primary refrigerant and the secondary refrigerant in the heat exchange tank 4. This has the effect of preventing the inflowing secondary refrigerant from jumping on the liquid surface and being sucked into the primary refrigerant outflow pipe 15.

With the configuration of the heat exchange tank 4, the primary refrigerant is branched into six at the primary refrigerant inflow / branch portion 11 and flows in the gas-liquid two-phase state from the lowermost part of the heat exchange tank 4. It is subdivided into a number of fluxes via the dispersion plate 17 and flows into the metal porous body 20 (FIG. 3b, thick arrow).

The primary refrigerant that has passed through the metal porous body 20 from below and received heat from the secondary refrigerant and has changed its phase from the gas-liquid two-phase state to the gas state is the central hole of the secondary refrigerant suction prevention plate 19b. After passing through the portion and passing between the outer edge of the secondary refrigerant suction prevention plate 19a and the inner wall of the heat exchange tank 4, the primary refrigerant outlet pipe 15
More outflow (FIG. 4c, bold arrow).

At this time, since the secondary refrigerant suction prevention plates 19a and 19b overlap with each other, the secondary refrigerant droplets jumping from below will not be drawn straight into the primary refrigerant outflow pipe 15, so It is possible to prevent the refrigerant from flowing out of the primary refrigerant outflow pipe 15.

The secondary refrigerant is branched into six at the secondary refrigerant inflow / branch portion 12 and flows into the upper portion of the metal porous body 20 through the secondary refrigerant inflow pipe 14 inserted from the top of the heat exchange tank 4 ( FIG. 4c, thin line arrow).

The secondary refrigerant, which has passed through the metal porous body 20 from the top to the bottom to be deprived of heat by the primary refrigerant and cooled, passes through the central hole of the primary refrigerant suction prevention plate 18 and passes through the secondary refrigerant outflow pipe. 16
More outflow (FIG. 3b, thin arrow).

At this time, the cylindrical primary refrigerant suction prevention plate 1
8 is provided around the secondary refrigerant outflow pipe 16 at the bottom of the heat exchange tank 4, an effect equivalent to increasing the cross-sectional area near the outflow portion of the secondary refrigerant outflow pipe 16 is obtained. Since the cross-sectional area of the outflow pipe 16 increases, the flow rate of the secondary refrigerant near the primary refrigerant suction prevention plate 18 becomes relatively slow. Since the primary refrigerant in the vicinity of the primary refrigerant suction prevention plate 18 has a low density and is vaporized by heat exchange, the buoyancy above the heat exchange tank 4 is higher than the force sucked from the secondary refrigerant outflow pipe 16 together with the secondary refrigerant. The primary refrigerant flows into the secondary refrigerant outflow pipe 16
Can be prevented from spilling.

As described above, in the heat exchange tank 4, the primary refrigerant flows from below to above while changing from a gas-liquid two-phase state to a gas state, and the secondary refrigerant flows from above to below. The refrigerant and the secondary refrigerant pass through the porous metal body 20,
Utilizing the large specific surface area of the metal porous body 20 and sufficiently exchanging heat using the large contact area with each other, the primary refrigerant is from above the heat exchange tank 4 and the secondary refrigerant is from below the heat exchange tank 4. Each can be separated and drained.

In the present embodiment, the purpose of the porous metal body 20 provided in the heat exchange tank is to subdivide the flux of the primary refrigerant and the secondary refrigerant to increase the contact area between them. The specific surface area of a plate-type heat exchanger in a conventional indirect secondary refrigerant air conditioning system (500 m ² /
m ³ ) If the material has a specific surface area equal to or greater than that of m ³ ), it is possible to secure heat exchange efficiency higher than that of the indirect-type secondary refrigerant air conditioning system using a plate-type heat exchanger. The material is not limited to 20, but may be a material such as steel wool, packing (metal filling), or the like, but is preferably a metal having high heat conduction performance.

The packing is a small piece of metal formed by winding a metal wire into a spring or forming a wire net into a cylindrical shape. The small piece is filled in, for example, a rectification tower or the like, and has a very large specific surface area. It has the feature of being large.

In the present embodiment, the primary refrigerant is divided into a number of fluxes by means of the primary refrigerant, and the primary refrigerant inflow branch pipe and the multi-hole dispersion plate are used. If the refrigerant can be subdivided, the method is not limited to this method, and the flow path of the primary refrigerant into the heat exchange tank 4 may be further divided and flown, and not limited to the bottom surface of the heat exchange tank 4,
It may be a method such as flowing from the bottom side surface or the like.

Further, in the present embodiment, the secondary refrigerant inflow branch pipe is used as means for subdividing the secondary refrigerant into a number of fluxes. However, the secondary refrigerant may be subdivided. If possible, the method is not limited to this method, and a method in which the secondary refrigerant flows in from the tip of the secondary refrigerant inflow pipe with a shower nozzle may be used.

Further, in the present embodiment, two secondary refrigerant suction preventing plates whose openings are shifted from each other are used as means for preventing the secondary refrigerant from flowing out from the primary refrigerant outflow pipe. However, the present invention is limited to this method. Instead, a method of installing a wire mesh near the primary refrigerant outflow pipe to repair water drops may be used.

(Second Embodiment) As an example of another secondary refrigerant refrigeration cycle apparatus according to the present invention, the primary refrigerant is H
FIG. 5 shows a system configuration of a secondary refrigerant air conditioning system for both cooling and heating, using propane as a C-based natural refrigerant and fresh water as a secondary refrigerant.

This system comprises a primary side refrigeration cycle and a secondary side heat transfer cycle. The primary side refrigeration cycle includes a compressor 1, a first heat exchanger (hereinafter referred to as an outdoor heat exchanger) 2, a throttle. Device (hereinafter referred to as expansion valve) 3, heat exchange tank 4, oil separator 5, accumulator 6, first four-way valve 21, second four-way valve 22, three-way valve 23, primary refrigerant outflow pipe 24 for cooling, and heating for heating It comprises a primary refrigerant outflow pipe 25 and the like, each of which is connected by a primary side connection pipe 7 and in which a primary refrigerant and a refrigerating machine oil are sealed.

In the secondary heat transfer cycle, a second heat exchanger (hereinafter referred to as an indoor heat exchanger) 8, a circulating pump 9, and a heat exchange tank 4 are connected by a secondary connection pipe 10, The next refrigerant is enclosed.

In FIG. 5, the bold line shows the flow of the primary refrigerant during the heating operation, and the thin line shows the flow of the secondary refrigerant. A part of the primary refrigeration cycle and the secondary heat transfer cycle is inside the outdoor unit. The indoor heat exchanger 8 is packaged in an indoor unit, and the outdoor unit and the indoor unit are connected by a secondary connection pipe 10 and a signal line (not shown).

The oil separator 5 has an oil return pipe for returning the refrigerating machine oil discharged from the compressor 1 to the suction pipe of the compressor 1 again.

Since the primary refrigerant and the secondary refrigerant are hardly dissolved in each other, and the density of the primary refrigerant is lower than the density of the liquid state of the secondary refrigerant in both the gas state and the liquid state, they are mixed in the heat exchange tank 4. In a short time, the primary refrigerant is at the top, the secondary refrigerant is at the bottom,
It has the property of being separated from each other.

During the heating operation of the primary refrigeration cycle, the compressor 1, the oil separator 5, the first four-way valve 21, the second four-way valve 22, the heat exchange tank 4 (acting as a condenser), Refrigerant outlet pipe 25, three-way valve 23, second four-way valve 2
2, expansion valve 3, outdoor heat exchanger 2 (acting as an evaporator), first four-way valve 21, accumulator 6, compressor 1
In this order, the primary refrigerant flows through the primary connection pipe 7.

During the cooling operation of the primary refrigeration cycle, the compressor 1, the oil separator 5, the first four-way valve 21, the outdoor heat exchanger 2 (acting as a condenser), the expansion valve 3, and the second four-way valve 22, a heat exchange tank 4 (acting as an evaporator), a cooling primary refrigerant outflow pipe 24, a three-way valve 23, a second four-way valve 2
2. The primary refrigerant flows in the order of the first four-way valve 21, the accumulator 6, and the compressor 1 via the primary connection pipe 7, respectively.

The operation of the secondary heat transfer cycle is performed regardless of the heating operation or the cooling operation, regardless of the operation of the heat exchange tank 4, the indoor heat exchanger 8,
The secondary refrigerant flows through the secondary connection pipe 10 in the order of the circulation pump 9 and the heat exchange tank 4.

During the heating operation, the primary refrigerant is compressed by the compressor 1, exchanges heat with the primary refrigerant in the heat exchange tank 4, transfers heat to the secondary refrigerant, condenses, and is depressurized by the expansion valve 3. The outdoor heat exchanger 2 exchanges heat with outdoor air, which is an outdoor load, receives heat, evaporates, and returns to the compressor 1.

While being circulated by the circulation pump 9, the secondary refrigerant receives heat from the primary refrigerant in the heat exchange tank 4 and is heated, and the indoor heat exchanger 8 removes heat to the indoor load, which is an indoor load, and is cooled. Then, the process returns to the heat exchange tank 4 again.

During the cooling operation, the primary refrigerant is compressed by the compressor 1, exchanges heat with the outdoor air as an outdoor load in the outdoor heat exchanger 2, releases heat, condenses, and is decompressed by the expansion valve 3. Then, heat exchange is performed with the primary refrigerant in the heat exchange tank 4 to remove heat from the secondary refrigerant, evaporate, and return to the compressor 1.

While being circulated by the circulation pump 9, the secondary refrigerant is deprived of heat by the primary refrigerant in the heat exchange tank 4 and cooled, and is heated by the indoor heat exchanger 8 by depriving the indoor load which is an indoor load of heat. Then, the process returns to the heat exchange tank 4 again.

FIG. 6 shows a configuration of the heat exchange tank 4 according to the second embodiment of the present invention.

The heat exchange tank 4 is a cylindrical container, and the flow of the primary refrigerant during the heating operation is indicated by a thick arrow, and the flow of the secondary refrigerant is indicated by a thin arrow. The heat exchange tank 4 includes a primary refrigerant inflow branch portion 11 and a secondary refrigerant inflow branch portion 12, and each refrigerant pipe flowing into the heat exchange tank 4 is branched into, for example, six pipes.

The six-branched primary refrigerant and the secondary refrigerant flow into the heat exchange tank 4 from the six primary refrigerant inflow pipes 13 and the six secondary refrigerant inflow pipes 14, respectively, and are respectively cooled during the cooling. 24 (for cooling) or primary refrigerant outlet pipe 25 for heating
During heating, the refrigerant flows out of the secondary refrigerant outflow pipe 16.

The cooling-purpose primary refrigerant outflow pipe 24 is connected to the uppermost part of the heat exchange tank 4, and the heating-purpose primary refrigerant outflow pipe 25 has a distal end connected to the secondary refrigerant in the heat exchange tank 4 during the heating operation. It is set in advance so as to be located at a portion that is equal to or higher than the refrigerant liquid level and equal to or lower than the primary refrigerant liquid level. In the heat exchange tank 4, a primary refrigerant dispersion plate 17 as a means for subdividing the primary refrigerant into a plurality of fluxes, a primary refrigerant suction prevention plate 18, a first refrigerant The secondary refrigerant suction prevention plates 19a and 19b as the secondary refrigerant suction prevention means, and the secondary refrigerant suction prevention plate 1 as the second secondary refrigerant suction prevention means
9c, a metal porous body 20 is provided as a filler in the heat exchange tank 4.

The metal porous body 20 has many pores opened in the metal, and has a specific surface area of 500 m ² / volume.
m ³ or more, which secures a specific surface area equal to or greater than that of a plate-type heat exchanger used in a general indirect heat exchange method.

Thus, the heat exchange performance can be further improved while keeping the outer volume and / or the volume equal to or less than that of the plate heat exchanger.

The structures of the primary refrigerant dispersion plate 17 and the primary refrigerant suction prevention plate 18 are the same as those of the first embodiment shown in FIGS. 3A and 3B.

Also, the structure of the first secondary refrigerant suction prevention plates 19a and 19b is the same as that of the first embodiment shown in FIGS.
And FIG. 4c.

Further, the second secondary refrigerant suction prevention plate 19c has a cylindrical shape and is installed so as to surround the primary refrigerant outflow pipe 25 at the time of heating. The refrigerant can be prevented from being sucked into the primary refrigerant outflow pipe 25 during the heating operation.

Due to the configuration of the heat exchange tank 4, during the heating operation, the primary refrigerant is supplied to the primary refrigerant inflow / branch 11 in advance.
Then, it is branched into six and flows in a gaseous state from the lowermost part of the heat exchange tank 4, further divided into a number of fluxes through the primary refrigerant dispersion plate 17 and flows into the metal porous body 20.

The primary refrigerant, which has passed through the porous metal body 20 from below and applied heat to the secondary refrigerant to change the phase from the gas state to the liquid state, has a lower density than the secondary refrigerant and does not dissolve in each other. Because of the feature, the primary refrigerant in the liquid state stays on the secondary refrigerant in the liquid state after phase separation. By operating this system stably, the location of the primary refrigerant in the liquid state in the heat exchange tank 4 is specified. The primary refrigerant in the liquid state can be selectively discharged from the primary refrigerant outflow pipe 25 at the time of heating by setting the primary refrigerant at a portion where the primary refrigerant flows.

At this time, the secondary refrigerant suction preventing plate 19c prevents the secondary refrigerant flowing from the secondary refrigerant inflow pipe 14 from being mixed with the liquid primary refrigerant retained in the upper part of the heat exchange tank 4. In addition, the secondary refrigerant can be prevented from flowing out of the primary refrigerant outflow pipe 25 during heating.

On the other hand, the secondary refrigerant is branched into six at the secondary refrigerant inflow / branch section 12 in advance, and the secondary refrigerant inflow pipe 14 inserted from the top of the heat exchange tank 4 is used to form the metal porous body 2.
Flow into the top of 0.

The secondary refrigerant, which has passed through the metal porous body 20 from the top down and received heat from the primary refrigerant and has been heated, passes through the central hole of the primary refrigerant suction prevention plate 18 and passes through the secondary refrigerant outflow pipe 16.
More outflow.

At this time, the cylindrical primary refrigerant suction prevention plate 1
8 is provided around the secondary refrigerant outflow pipe 16 at the bottom of the heat exchange tank 4, an effect equivalent to increasing the cross-sectional area in the vicinity of the outflow portion of the secondary refrigerant outflow pipe is obtained. Tube 16
, The flow rate of the secondary refrigerant near the primary refrigerant suction prevention plate 18 becomes relatively slow. Since the primary refrigerant near the primary refrigerant suction prevention plate 18 has a low density, the heat exchange tank 4
Since the upward buoyancy exceeds the force sucked from the secondary refrigerant outflow pipe 16 together with the secondary refrigerant, the primary refrigerant can be prevented from flowing out of the secondary refrigerant outflow pipe 16.

During the cooling operation, the primary refrigerant is branched into six at the primary refrigerant inflow / branch portion 11 and flows in the gas-liquid two-phase state from the bottom of the heat exchange tank 4. After passing through 17, the flux is subdivided into a number of fluxes and flows into the metal porous body 20 (FIG. 3 b, thick arrow).

The primary refrigerant that has passed through the metal porous body 20 from below and received heat from the secondary refrigerant and has changed its phase from the gas-liquid two-phase state to the gas state is the central hole of the secondary refrigerant suction prevention plate 19b. After passing through the portion and passing between the outer edge of the secondary refrigerant suction prevention plate 19a and the inner wall of the heat exchange tank 4, it flows out from the primary refrigerant outflow pipe 24 during cooling (FIG. 4c, thick line arrow).

At this time, since the secondary refrigerant suction preventing plates 19a and b overlap each other, the droplets of the secondary refrigerant that jump from below are not drawn straight into the primary refrigerant outflow pipe 15 during cooling. It is possible to prevent the primary refrigerant from flowing out of the primary refrigerant outflow pipe 15.

On the other hand, the secondary refrigerant is branched into six at the secondary refrigerant inflow / branch portion 12 in advance, and the secondary refrigerant inflow pipe 14 inserted from the top of the heat exchange tank 4 inserts the metal porous body 2 into the metal refrigerant.
Flow into the top of 0.

The secondary refrigerant, which has passed through the metal porous body 20 from the top to the bottom to be deprived of heat by the primary refrigerant and cooled, passes through the central hole of the primary refrigerant suction prevention plate 18 and passes through the secondary refrigerant outflow pipe. 16
More outflow.

At this time, the cylindrical primary refrigerant suction prevention plate 1
8 is provided around the secondary refrigerant outflow pipe 16 at the bottom of the heat exchange tank 4, an effect equivalent to increasing the cross-sectional area in the vicinity of the outlet of the secondary refrigerant outflow pipe is obtained, and the secondary refrigerant outflow occurs. Tube 16
, The flow rate of the secondary refrigerant near the primary refrigerant suction prevention plate 18 becomes relatively slow. Since the primary refrigerant in the vicinity of the primary refrigerant suction prevention plate 18 has a low density and is vaporized by heat exchange, the buoyancy above the heat exchange tank 4 is higher than the force sucked from the secondary refrigerant outflow pipe 16 together with the secondary refrigerant. As a result, the primary refrigerant can be prevented from flowing out of the secondary refrigerant outflow pipe 16.

As described above, in the heat exchange tank 4, the primary refrigerant changes from the lower side to the upper side, changes from the gas-liquid two-phase state to the gas state during the cooling operation, and changes during the heating operation. Each flows while changing from the gas state to the liquid state,
The secondary refrigerant flows downward from above, and the primary refrigerant and the secondary refrigerant pass through the porous metal body 20 and utilize the large specific surface area of the porous metal body 20 to sufficiently utilize the large contact area with each other. Heat exchange is performed, and the primary refrigerant is
The secondary refrigerant can flow out separately from below the heat exchange tank 4.

In the present embodiment, the purpose of the metal porous body 20 installed in the heat exchange tank 4 is to subdivide the primary refrigerant and the secondary refrigerant to increase the contact area between them.
The specific surface area is the specific surface area (500 m ² / m ³ ) of the plate heat exchanger in the conventional indirect secondary refrigerant air conditioning system.
If the substance has a specific surface area equal to or greater than that of the indirect type secondary refrigerant air conditioning system using a plate heat exchanger, it is possible to secure heat exchange efficiency higher than that of a metal porous body. , Steel wool, packing, and other substances may be used, but it is preferable that the material be a metal having high heat conductivity.

Further, in this embodiment, the primary refrigerant is divided into a number of fluxes by means of the primary refrigerant, and the primary refrigerant inlet branch pipe and the primary refrigerant dispersion plate having a large number of holes are used. If the primary refrigerant can be subdivided, the method is not limited to this method, and the flow path of the primary refrigerant into the heat exchange tank may be further divided and flown into the heat exchange tank. It is also possible to use a method of inflowing water from the inside.

Further, in the present embodiment, the secondary refrigerant inflow branch pipe is used as means for subdividing the secondary refrigerant into a number of fluxes. However, the secondary refrigerant may be subdivided. If possible, the method is not limited to this method, and a method in which the secondary refrigerant flows in from a tip of the secondary refrigerant inflow / outflow pipe with a shower nozzle may be used.

In this embodiment, two secondary refrigerant suction prevention plates having different openings are used as means for preventing the secondary refrigerant from flowing out of the primary refrigerant outflow pipe. However, the present invention is not limited to this method. Alternatively, a method in which a wire mesh is installed near the primary refrigerant outflow pipe to collect water droplets may be used.

Further, in the present embodiment, in the primary side refrigeration cycle, the secondary refrigerant flows from the lower part of the heat exchange tank 4 and flows out of the upper part of the heat exchange tank 4 during both the cooling operation and the heating operation. Although the flow path of the primary refrigerant is switched using the four-way valve 22, the flow path is not limited to the four-way valve, and the flow path may be switched by a plurality of valves or the like.

In this embodiment, in order to increase the contact area between the primary refrigerant and the secondary refrigerant in the heat exchange tank 4, the metal porous body, the packing (metal filler), or the wire mesh is heat-exchanged. Although it is assumed that the primary refrigerant and the secondary refrigerant are arranged in the heat exchange tank 4 and the traveling directions of the primary refrigerant and the secondary refrigerant are complicated, the primary refrigerant and the secondary refrigerant in the heat exchange tank 4 are arranged. The contact area with the refrigerant may be increased.

As described above, in the above embodiment,
For example, by arranging a metal porous body, a packing, a wire mesh, or an object having an uneven surface on the surface thereof having a specific surface area of 500 m ² / m ³ or more in the heat exchange tank 4, The heat exchange between the refrigerant and the secondary refrigerant is promoted, and without increasing the capacity of the heat exchange tank 4,
A highly efficient secondary refrigerant refrigeration cycle device can be provided.

Further, in the above-described embodiment, since the means for subdividing at least one of the primary refrigerant and the secondary refrigerant into a plurality of fluxes before contacting each other is provided, the primary refrigerant in the heat exchange tank 4 is provided. The heat exchange is promoted by increasing the contact area of the secondary refrigerant and the secondary refrigerant, and a secondary refrigerant refrigeration cycle device with high efficiency can be provided without increasing the capacity of the heat exchange tank 4.

In the above embodiment, each of the primary refrigerant and the secondary refrigerant flows into the heat exchange tank 4 as means for subdividing the primary refrigerant and the secondary refrigerant into a plurality of fluxes. A primary refrigerant inflow pipe and a secondary refrigerant inflow pipe are provided, at least one of which branches into a plurality of flow paths and flows into a heat exchange tank, whereby contact between the primary refrigerant and the secondary refrigerant in the heat exchange tank 4 is established. The area is increased, heat exchange is promoted, and a highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4.

In the above embodiment, at least one of the primary refrigerant and the secondary refrigerant is supplied to the heat exchange tank 4 as means for subdividing the primary refrigerant and the secondary refrigerant into a plurality of fluxes.
After flowing into the heat exchange tank 4, the contact area between the primary refrigerant and the secondary refrigerant in the heat exchange tank 4 is increased and heat exchange is promoted, and the capacity of the heat exchange tank 4 is increased. , And a highly efficient secondary refrigerant refrigeration cycle device can be provided.

In the above embodiment, the heat exchange tank 4
The secondary refrigerant outlet pipe near the secondary refrigerant outlet connected to the heat exchange tank 4 and having a larger cross-sectional area, thereby mixing and separating the primary refrigerant and the secondary refrigerant. Promotes,
A highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4. As the secondary refrigerant cross-sectional area enlarging means, for example, a cylinder installed at the bottom portion in the heat exchange tank and having a larger diameter than the secondary refrigerant outflow pipe can be used. Since the secondary refrigerant outflow speed at the end of the outflow portion is reduced by increasing the cross-sectional area at the secondary refrigerant outflow portion, it becomes difficult to suck the primary refrigerant together with the secondary refrigerant.

Further, in the above embodiment, the heat exchange tank 4 has the first primary refrigerant outflow pipe and / or the second primary refrigerant outflow pipe, and the tip of the first primary refrigerant outflow pipe is the heat exchange tank. It is connected to the upper part, and since the tip of the second primary refrigerant outflow pipe is connected to a position in the heat exchange tank 4 that is equal to or higher than the secondary refrigerant liquid level and equal to or lower than the primary refrigerant liquid level, the primary refrigerant and the secondary refrigerant mixture·
Separation is promoted, and a high-efficiency secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4.

In the above embodiment, the first secondary refrigerant suction preventing means is provided between the end of the first primary refrigerant outflow pipe and the primary refrigerant liquid level in the heat exchange tank 4 in the heat exchange tank 4. Is provided, the mixing and separation of the primary refrigerant and the secondary refrigerant are promoted, and a highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4.

Further, at least two flat plates having different openings are used in the vicinity of the primary refrigerant outlet pipe as the first secondary refrigerant suction preventing means, so that the primary refrigerant and the secondary refrigerant can be mixed and separated. , And a highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4.

Alternatively, by using a wire mesh at least in the vicinity of the primary refrigerant outlet pipe as the first secondary refrigerant suction preventing means, the mixing and separation of the primary refrigerant and the secondary refrigerant is promoted, and the heat exchange tank is prevented. Thus, a highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the fourth refrigerant cycle.

Further, since the secondary refrigerant inflow pipe is inserted into the heat exchange tank 4 up to the vicinity of either the primary refrigerant liquid level or the secondary refrigerant liquid level in the heat exchange tank 4, the secondary refrigerant is connected with the primary refrigerant. Mixing / separation of the secondary refrigerant is promoted, and a secondary refrigerant refrigeration cycle device with high efficiency can be provided without increasing the capacity of the heat exchange tank 4.

Further, the provision of the second secondary refrigerant suction preventing means between the secondary refrigerant inflow pipe and the second primary refrigerant outflow pipe promotes mixing and separation of the primary refrigerant and the secondary refrigerant. Thus, a highly efficient secondary refrigerant refrigeration cycle apparatus can be provided without increasing the capacity of the heat exchange tank 4.

As the second secondary refrigerant suction prevention means,
By using a flat plate disposed between the secondary refrigerant inflow pipe and the second primary refrigerant outflow pipe, the mixing and separation of the primary refrigerant and the secondary refrigerant are promoted, and the heat exchange tank 4 is increased without increasing the capacity. An efficient secondary refrigerant refrigeration cycle device can be provided.

[0133]

As is apparent from the above description, the present invention increases the area where the primary refrigerant and the secondary refrigerant are in direct contact with each other to efficiently perform heat exchange, A secondary refrigerant refrigeration cycle device that reliably separates the refrigerant can be provided.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a configuration diagram of a secondary refrigerant refrigeration cycle dedicated to cooling in Embodiment 1 of the present invention.

FIG. 2 is a configuration diagram of a heat exchange tank of a secondary refrigerant refrigeration cycle dedicated to cooling in Embodiment 1 of the present invention.

FIG. 3 is a configuration diagram of components in a heat exchange tank of the secondary refrigerant refrigeration cycle according to Embodiment 1 of the present invention.

FIG. 4 is a configuration diagram of components in a heat exchange tank of the secondary refrigerant refrigeration cycle according to Embodiment 1 of the present invention.

FIG. 5 is a configuration diagram of a secondary refrigerant refrigeration cycle dedicated to cooling in Embodiment 2 of the present invention.

FIG. 6 is a configuration diagram of a heat exchange tank of a secondary refrigerant refrigeration cycle dedicated to cooling in Embodiment 2 of the present invention.

FIG. 7 is a configuration diagram of an example of a conventional secondary refrigerant refrigeration cycle.

FIG. 8 is a configuration diagram of a heat exchange tank in an example of a conventional secondary refrigerant refrigeration cycle.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 compressor 2 first heat exchanger (outdoor heat exchanger) 3 expansion device (expansion valve) 4 heat exchange tank 5 oil separator 6 accumulator 7 primary connection pipe 8 second heat exchanger (indoor heat exchanger) Reference Signs List 9 circulation pump 10 secondary connection pipe 11 primary refrigerant inflow / branch part 12 secondary refrigerant inflow / branch part 13 primary refrigerant inflow pipe 14 secondary refrigerant inflow pipe 15 primary refrigerant outflow pipe 16 secondary refrigerant outflow pipe 17 primary refrigerant distribution plate 18 Primary refrigerant suction prevention plate 19a, b, c Secondary refrigerant suction prevention plate 20 Metal porous body 21 First four-way valve 22 Second four-way valve 23 Three-way valve 24 Primary refrigerant outflow pipe for cooling 25 Primary refrigerant outflow pipe for heating 27 Compressor 28 Four-way valve 29 First heat exchanger (outdoor heat exchanger) 30 Throttling device (expansion valve) 31 Heat exchange tank 32 Primary connection pipe 33 Second heat exchanger (Indoor heat exchanger) 34 Circulation Pump 35 secondary side connecting pipe 36 partition plate 37 primary refrigerant inlet pipe 38 secondary coolant inlet pipe 39 the secondary refrigerant outlet pipe 40 primary refrigerant outlet pipe 41 Heating during the primary refrigerant outlet pipe during cooling

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Noriho Okaza 1006 Kazuma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd.

Claims (14)

[Claims] A compressor for compressing the primary refrigerant, a first heat exchanger for exchanging heat between the primary refrigerant and an external load, a throttle device for decompressing and expanding the primary refrigerant, The primary refrigerant and the secondary refrigerant flow in, a heat exchange tank for causing the primary refrigerant and the secondary refrigerant to directly contact and perform heat exchange, the compressor, the first heat exchanger, A primary-side refrigeration cycle having at least an expansion device and a primary-side connection pipe connecting the heat exchange tank; and causing heat exchange between the heat exchange tank, the circulation pump, the secondary refrigerant, and an internal load. A second heat exchanger for
A secondary heat transfer cycle having a secondary connection pipe connecting the heat exchange tank, the circulation pump and the second heat exchanger, and the heat exchange tank has an uneven shape on its surface. ,and/
Alternatively, a secondary refrigerant refrigeration cycle apparatus, wherein a contact area increasing means having a plurality of holes is arranged. 2. The secondary refrigerant refrigeration cycle apparatus according to claim 1, wherein the contact area increasing means is a metal porous body, a packing (metal filling), or a wire mesh. 3. A specific surface area indicating a ratio of a surface area of the contact area increasing means to a volume of the heat exchange tank is 500.
^{3. The structure according} to claim 1, wherein the ratio is at least m ² / m ^3.
2. The secondary refrigerant refrigeration cycle device according to item 1. 4. A refrigerant subdivision means for subdividing the primary refrigerant and / or the secondary refrigerant into a plurality of fluxes and flowing into the heat exchange tank. 4. The secondary refrigerant refrigeration cycle device according to any one of items 1 to 3. 5. The plurality of primary refrigerant inflow pipes connected to the primary side connection pipe and / or the plurality of secondary refrigerant inflow pipes connected to the secondary side connection pipe. The secondary refrigerant refrigeration cycle apparatus according to claim 4, wherein: 6. The secondary refrigerant refrigeration cycle apparatus according to claim 4, wherein the refrigerant subdivision means is a plate-like body provided in the heat exchange tank and provided with a large number of pores. . 7. The heat exchange tank enlarges a cross-sectional area of the secondary refrigerant outflow pipe for allowing the secondary refrigerant to flow out, and a cross-sectional area of the secondary refrigerant immediately before flowing into the secondary refrigerant outflow pipe. The secondary refrigerant refrigeration cycle apparatus according to any one of claims 1 to 6, further comprising a secondary refrigerant cross-sectional area expanding means. 8. The heat exchange tank has at least a plurality of primary refrigerant outflow pipes for allowing the primary refrigerant to flow out, and at least one of the plurality of primary refrigerant outflow pipes has a tip, The secondary refrigerant refrigeration cycle device according to any one of claims 1 to 7, wherein the secondary refrigerant refrigeration cycle device is provided at a position in the heat exchange tank that is equal to or higher than the secondary refrigerant liquid level and equal to or lower than the primary refrigerant liquid level. . 9. The secondary heat exchanger according to claim 8, wherein the heat exchange tank has secondary refrigerant suction prevention means for preventing the secondary refrigerant from being sucked into the primary refrigerant outlet pipe. Refrigerant refrigeration cycle device. 10. The secondary refrigerant according to claim 9, wherein the secondary refrigerant suction prevention means includes at least two flat plates having different openings below the primary refrigerant outlet pipe. Refrigerant refrigeration cycle device. 11. The secondary refrigerant refrigeration cycle apparatus according to claim 9, wherein the secondary refrigerant suction prevention means is a wire mesh provided at a tip end of the primary refrigerant outflow pipe. 12. The heat exchanger according to claim 1, wherein the secondary refrigerant inflow pipe is inserted into the heat exchange tank up to near a liquid level of the primary refrigerant and / or the secondary refrigerant in the heat exchange tank. The secondary refrigerant refrigeration cycle device according to claim 5. 13. In the heat exchange tank, the secondary refrigerant is sucked into the primary refrigerant outflow pipe between a distal end of the secondary refrigerant inflow pipe and a distal end of the primary refrigerant outflow pipe. The secondary refrigerant refrigeration cycle apparatus according to any one of claims 7 to 12, further comprising a second secondary refrigerant suction preventing means for preventing the refrigerant from being drawn. 14. The secondary refrigerant refrigeration cycle apparatus according to claim 13, wherein said second secondary refrigerant suction prevention means is a flat plate.