JP2887216B2 - Heat pump equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump device used for cooling, heating and the like.

[0002]

2. Description of the Related Art As a conventional heat pump used for cooling, heating, and the like, a heat pump having a structure in which a single refrigerant is used to perform an inverse Carnot cycle operation is often used.

In recent years, heat pumps that operate in a Lorentz cycle using a non-azeotropic mixed refrigerant obtained by mixing two or more types of refrigerants have been receiving attention in connection with improvements in operating efficiency and so-called Freon regulations. This heat pump has the advantage that the efficiency is higher than that of the former using a single refrigerant, and that there is much room for selection of the refrigerant in relation to the above-mentioned regulations on CFCs.

In the latter heat pump, attempts have been made to further improve the efficiency by making it possible to change the mixing ratio of the refrigerant during operation. For example, JP
In the system disclosed in Japanese Patent Application Publication No. 1-66054, a non-azeotropic mixed refrigerant is rectified by heating and cooling in a rectification device to change the mixing ratio, thereby expanding the capacity adjustment range.

[0005]

In the heat pump, the temperature conditions in the cooling operation and the heating operation, particularly the temperature condition of the condenser, are greatly different.
Even if a non-azeotropic refrigerant mixture is used, as long as the cooling operation and the heating operation are performed with the same refrigerant, the optimum conditions of these refrigerants correspond to only one of the cooling and heating sides, and the optimum conditions for the other side. And the predetermined performance cannot be exhibited.

For example, in a heat pump using the refrigerant R22 as a single refrigerant, in cooling operation, cold water of about 7 ° C. can be efficiently obtained by heat exchange in an evaporator. Attempting to obtain hot water of 50 ° C or more by heat exchange at that time, the required pressure of the compressor will be 20 kgf / cm ² G or more, therefore, it is manufactured with the target discharge pressure of 20 kgf / cm ² G A general-purpose compressor cannot be used. That is, with such a refrigerant, 50
It is practically difficult to obtain hot water at a temperature of at least ℃. Conversely, in a heat pump using the refrigerant R12 as a single refrigerant,
Although hot water of not less than ° C. can be obtained using a general-purpose compressor, the cooling operation cannot be performed efficiently. By the way,
This refrigerant R12 is the subject of the above-mentioned Freon regulation.

On the other hand, in the heat pump disclosed in the above publication, the above-mentioned problem can be solved theoretically by appropriately changing the mixing ratio of the non-azeotropic refrigerant mixture between the cooling operation and the heating operation. However, since the mixing ratio of the refrigerant is changed by rectification, the mixing ratio is easily affected by changes in temperature or pressure during operation, and it is difficult to always maintain an appropriate mixing ratio. Therefore, it is practically difficult to maintain high-efficiency operation. An object of the present invention is to solve the above problems.

[0008]

An object of the present invention is to provide a heat pump, which comprises two systems, which are configured to be switchable, and which have different configurations for heating and cooling, respectively. The problem can be solved by the heat pump device of the present invention in which the stored refrigerants and the refrigerant recovery paths corresponding to the respective liquid receivers are configured.

In the above heat pump device, the reverse Carnot cycle operation can be performed using different single refrigerants such as refrigerant R12 for heating and refrigerant R22 for cooling.

In the above heat pump device, the refrigerant is a non-azeotropic mixed refrigerant, and the evaporator and the condenser are of a countercurrent type so that the operation of the Lorentz cycle can be performed.

[0011] As the non-azeotropic mixed refrigerant, a mixed refrigerant of refrigerant R22 and refrigerant R142b can be used.
The mixing ratio of the refrigerant R22 for heating is 20 to 30 mol% and that of the refrigerant R142b is 80 to 70 mol%, and that for cooling is 70 to 85 mol% for the refrigerant R22 and 30 to 15 mol% for the refrigerant R142b.

As the non-azeotropic mixed refrigerant, refrigerants R134a, RC318,
A mixed refrigerant containing R123, R124, etc. as a component can be used. In this case, the mixed refrigerant may be different for only the mixing ratio of the same component as described above for heating and cooling, or for different components. You can also.

[0013]

In the above-mentioned present invention, only the receiver that stores the refrigerant for heating is operated as a component of the heat pump to perform the heating operation, and the receiver is switched to be used for cooling. The cooling operation is performed by operating only the liquid receiver storing the refrigerant as a component of the heat pump.

When switching the receiver to be operated,
Prior to this, the refrigerant in the apparatus is collected in a corresponding liquid receiver via a refrigerant collection path. Therefore, different refrigerants for heating and cooling stored in the respective liquid receivers are not mixed, and the heating operation and the cooling operation can be efficiently performed by the refrigerant suitable for each operation. In addition, by using an appropriate refrigerant for each operation as described above, it is possible to perform a heating operation in which the temperature in the condenser is increased without increasing the required pressure of the compressor in the heating operation. .

In the above-mentioned apparatus, the reverse Carnot cycle operation can be performed by using different single refrigerants such as refrigerant R12 for heating and refrigerant R22 for cooling. A non-azeotropic mixed refrigerant is used as the refrigerant, and the evaporator and the condenser can operate in a Lorentz cycle as a configuration for performing counter-current heat exchange. Efficient and efficient heating and cooling operation.

In the latter operation, a non-azeotropic mixed refrigerant, such as refrigerant R22 and refrigerant R142b, having a different mixture ratio of the same component, or a refrigerant mixture having a different refrigerant component is used. In the case of the former mixed refrigerant, the mixing ratio is 20-30 mol of the refrigerant R22 for heating.
%, The refrigerant R142b is 80-70 mol%, and the refrigerant R22 is 70-85 mol% and the refrigerant R142b is 30-15 mol% for cooling.
In this range, the conditions necessary for district heating and cooling can be easily achieved, and hot water of 50 ° C. or higher can be easily obtained using a general-purpose compressor.

In addition, the single refrigerant and the non-azeotropic mixed refrigerant can be appropriately selected according to desired cooling and heating conditions. For example, the refrigerant R22 described above as a component of these refrigerants or mixed refrigerants Refrigerant R142b, refrigerant R134
a, RC318, R123, R124, etc. can be used.

[0018]

Next, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a system diagram showing one embodiment of the configuration of the heat pump device of the present invention. This embodiment shows a configuration for operating a Lorentz cycle using a non-azeotropic mixed refrigerant.

In FIG. 1, reference numeral 1 denotes a compressor, and 2 denotes a drive source 2 for driving the compressor 1, such as an electric motor or an internal combustion engine. An evaporator 3 is connected to a refrigerant path on the suction side of the compressor 1 and a condenser 4 is connected to a refrigerant path on the discharge side. That is, when the evaporator 3 flows from the upstream side to the downstream side in the long tubular refrigerant path 5, the evaporator 3 exchanges heat with the chilled water flowing through the chilled water path 6 from the downstream side to the upstream side. Similarly, when the condenser 4 flows through the long tubular refrigerant path 7 from the upstream side to the downstream side, the condenser 4 flows through the cooling water (or hot water) path 8 from the downstream side to the upstream side with heat and heat. It is a configuration to be replaced.

The refrigerant path downstream of the condenser 4 is 2
Into two paths, each of which is an inlet-side valve 9a,
9b, they are connected to the respective liquid receivers 10a, 10b, and the refrigerant paths downstream of the liquid receivers 10a, 10b are joined via outlet valves 11a, 11b.
The combined refrigerant path is connected to the upstream side of the evaporator 3 via the refrigerant liquid valve 12 and the expansion valve 13. In the embodiment, the liquid receivers 10a and 10b are integrally formed so as to be adjacent to each other via the partition wall 14, but it is a matter of course that the liquid receivers can be formed independently.

Reference numeral 15 denotes a refrigerant recovery device, and the refrigerant recovery device 15 is constituted by a small refrigerating device having a compressor or the like. The refrigerant path on the inlet side of the refrigerant recovery device 15 is connected to the refrigerant path from the compressor 1 to the condenser 4 via the inlet-side valve 16, and the refrigerant path on the outlet side is branched into two paths. Outlet valves 17a, 17 respectively
b, they are connected to the respective liquid receivers 10a and 10b.

In the above configuration, the liquid receivers 10a, 10a,
Each of 10b stores a different refrigerant for heating and cooling, that is, a non-azeotropic refrigerant having a different mixing ratio in this embodiment. For example, a non-azeotropic mixed refrigerant mixed so as to be suitable for heating is supplied to a receiver on the left side (hereinafter referred to as a receiver for heating) and a receiver on the right side (hereinafter, receiver for cooling). ) Stores a non-azeotropic mixed refrigerant mixed so as to be suitable for cooling. These specific examples will be described later.

The configuration shown in FIG. 1 described above shows an embodiment in which the Lorentz cycle is operated using a non-azeotropic refrigerant mixture. However, different units which are appropriately selected for heating and cooling are used. The operation of a reverse Carnot cycle, which is widely used in the past, can also be performed using one refrigerant.
When the reverse Carnot cycle operation is performed, the evaporator 3 and the condenser 4 do not need to have a countercurrent type configuration.

When the heating operation is performed in the above configuration, both the inlet valve 9a and the outlet valve 11a of the cooling liquid receiver 10a are closed, and the inlet side of the heating liquid receiver 10b is closed. The operation is performed with the valve 9b and the outlet valve 11b opened.
At this time, of course, the inlet valve 16 and the outlet valves 17a, 17b of the refrigerant recovery device 15 are all closed.

In the above operation, the refrigerant gas compressed by the compressor 1 reaches the condenser 4 and, when flowing from the upstream side to the downstream side, exchanges heat with the hot water flowing in the hot water path 8 in a countercurrent state. While condensing, it is heated and supplied for heating. Then, the water itself condenses and returns to the liquid receiver 10a for heating.
Next, the refrigerant liquid reaches the evaporator 3 via the refrigerant liquid valve 12 and the expansion valve 13 and, when flowing from the upstream side to the downstream side, evaporates by exchanging heat with the chilled water flowing in the chilled water path 6 in a countercurrent state, Next, it is sucked by the compressor 1 and the above operation is repeated.

Next, when performing the cooling operation, prior to this operation, the operation of operating the refrigerant recovery device 15 to recover the refrigerant in the path to the receiver 10a for heating, that is, so-called pump-down is performed. This collection operation is performed, for example, as follows.

First, in the above-mentioned heating operation, the outlet valve 11a of the heating receiver 10a while the compressor 1 is operated.
Is closed, all the refrigerant in the path from the downstream side of the outlet valve 11a to the upstream side of the compressor 1 is sucked by the compressor 1 and reaches the discharge side. Most of the refrigerant on the discharge side is collected in the heating liquid receiver 10a via the above-described path. Since the refrigerant remains in the path from the compressor 1 to the liquid receiver 10a only by such a recovery operation, the inlet side valve 9a of the liquid receiver 10a for heating is closed after a predetermined time has elapsed. At the same time, the operation of the compressor 1 is stopped. At the same time, by operating the refrigerant recovery device 15 by opening the inlet side valve 16 and the outlet side valve 17a, all the remaining refrigerant can be returned to the heating receiver 10a via the refrigerant recovery path as described above. it can. When the recovery is completed, both the outlet valve 17a and the inlet valve 16 are closed, and the operation of the refrigerant recovery device 15 is stopped.

In the state where all of the refrigerant in the refrigerant path has been collected in the liquid receiver 10a as described above, the inlet valve 9b and the outlet valve 11b of the cooling liquid receiver 10b are opened. In this way, a cooling operation is performed.

In this operation, the cooling liquid receiver 10b is used.
The refrigerant stored in the evaporator 3 circulates through the same path as the above-described heating operation, and in the evaporator 3, takes heat from the chilled water flowing countercurrently through the chilled water path 6 and evaporates itself.
The temperature of the cold water is lowered and the air is cooled. In the condenser 4, heat is applied to the cooling water flowing in the counter-current state in the cooling water path 8 to condense the cooling water itself, and then returns to the cooling receiver 10 b through the inlet valve 9 b. , The above operation is repeated.

As described above, in the present invention, two systems of liquid receivers are constructed, and appropriate refrigerants are stored for heating and cooling, respectively, and the liquid receivers to be operated are switched to operate correspondingly. When the receivers to be operated are switched, prior to this, the refrigerant in the device is recovered to the corresponding receivers via the refrigerant recovery path. Different stored refrigerants do not mix. Therefore, the heating operation and the cooling operation can be efficiently performed by selecting and storing the appropriate refrigerant for each operation, and in the heating operation, the condenser pressure can be increased without increasing the required pressure of the compressor. 4 can perform the heating operation in which the temperature is increased.

Next, a specific operation example of the heat pump device of the present invention will be described. In this operation example, for example, as a necessary condition for district cooling and heating, in the cooling operation, the change in the temperature of the chilled water used for cooling is 12 → 7 ° C.,
In the heating operation, the temperature change of the hot water used for heating is assumed to be 60 → 71 ° C., and the change of the cold water temperature as the heat source water is assumed to be 12 → 7 ° C. in the heating operation.

FIGS. 2 and 3 are TS diagrams showing the specific operation of the heat pump apparatus of the present invention in the case where the above-described necessary conditions for cooling and heating are satisfied by performing the reverse Carnot cycle operation with different single refrigerants. It is represented in FIG. The single refrigerant uses refrigerant R12 as a refrigerant for heating and refrigerant R22 as a refrigerant for cooling.

First, FIG. 2 relates to a cooling operation. In the condenser 4, the refrigerant R22 exchanges heat with the cooling water flowing through the cooling water path 8 at a constant temperature Tk = 40 ° C. to reduce the temperature of the cooling water. Td = 32
From Te. C. to Te = 37.degree. C., and in the evaporator 3, the refrigerant R22 exchanges heat with the chilled water flowing through the chilled water passage 6 at a constant temperature To = 2.degree. Ta = 7 from 12 ℃
The temperature is lowered to ° C and the air is cooled. The theoretical coefficient of performance in this cooling operation is the cooling performance coefficient COPc = 7.24. The required discharge pressure of the compressor is 14.6 kgf / cm ² G, and the above-described general-purpose compressor can be used.

FIG. 3 relates to a heating operation. In the condenser 4, the refrigerant R12 is heated at a constant temperature Tk = 74.degree.
Heat exchange with the hot water flowing through the (cooling water path)
= 60 ° C to Te = 71 ° C for heating. In the evaporator 3, the refrigerant R12 is cooled at a constant temperature To = 2 ° C with cold water as heat source water flowing through the cold water path 6 and heat. By exchanging heat from here, the temperature of cold water is lowered from Tb = 12 ° C to Ta = 7 ° C. The coefficient of performance in this heating operation is heating result count COPh = 4.82. The required discharge pressure of the compressor is 19.9 kgf / cm ² G, and the above-described general-purpose compressor can be used.

Next, FIG. 4 shows the operation in the case of performing the heating operation using the refrigerant R22. This operation is performed in order to raise the temperature of the refrigerant in the condenser 4 more. Discharge pressure of 20.7kgf / cm ² G, about the maximum pressure of general-purpose machines
It shows the operation in the case where the operation is performed while being raised to the maximum. As shown in FIG. 4, at the above-mentioned discharge pressure, the temperature of the refrigerant R22 in the condenser 4 can only be increased up to about 52 ° C., and therefore, the temperature of the hot water which exchanges heat only rises from 45 ° C. to 50 ° C. I can't let it. If the refrigerant T22 is used to obtain the temperature Tk = 74 ° C. of the condenser 4 in the operation using the refrigerant R12, the discharge pressure of the compressor needs to be 31.8 kgf / cm ² G. However, the general-purpose machine described above cannot operate. In fact, in practice, the heat pump apparatus using the refrigerant R22 usually operates by lowering the temperature of the condenser 4 in the heating operation.

As described above, in the heat pump apparatus of the present invention, efficient operation can be performed by performing each operation of heating and cooling by using an appropriate single refrigerant. It can be seen that in the operation, the heating operation in which the temperature in the condenser 4 is increased can be performed without increasing the required pressure of the compressor.

As described above, in the heat pump apparatus having the configuration shown in FIG. 1, the operation of the Lorentz cycle using the non-azeotropic refrigerant mixture is more efficient than the operation of the reverse Carnot cycle using a single refrigerant. Can be improved.

Two kinds of refrigerants having different boiling points (high boiling point refrigerant,
In the case of a non-azeotropic refrigerant mixture obtained by mixing low boiling point refrigerants, the dew point and the boiling point change as shown by the dew point curve and the boiling point curve in the isobaric gas-liquid equilibrium diagram of FIG. 5 according to the respective mixing ratios. I do. That is, in the non-azeotropic refrigerant mixture, the temperature changes as shown by the dew point curve and the boiling point curve during the phase change in the evaporation and condensation processes under a constant pressure. For example, when evaporating the refrigerant having the illustrated mixing ratio a in the evaporator 3, the refrigerant starts to evaporate from a point on the boiling point curve (temperature T ₂ ) and reaches a point on the dew point curve (temperature T ₁ ). The evaporation ends.
When condensing in the condenser 4, condensing starts at a point on the dew point curve (temperature T ₁ ) and ends at a point on the boiling point curve (temperature T ₂ ).

In the heat pump device, a non-azeotropic mixed refrigerant having such characteristics is used, and the evaporator 3 and the condenser 4 are of a countercurrent type as shown in FIG.
A so-called Lorentz cycle operation can be performed. As will be described later, as shown in FIGS. 6 and 7, in the Lorentz cycle, the temperature of the refrigerant at the inlet side of the cold water and the cooling water (hot water) in the evaporator 3 and the condenser 4 is lower than that at the outlet side. Inverted Carnot cycle using a single refrigerant by reducing the temperature difference between two fluids exchanging heat at the inlet side of the refrigerant, ie, refrigerant, cold water and cooling water (hot water), thus reducing irreversible loss It is possible to improve the efficiency more than the operation of.

In the non-azeotropic refrigerant mixture, the above-mentioned temperatures T ₁ and T ₂ can be changed on the dew point curve and the boiling point curve by changing the mixing ratio. By adjusting the mixing ratio so as to be substantially equal to the temperature difference between the inlet and outlet of the cooling water (hot water) in the condenser 4 and the temperature difference between the outlet and the inlet of the cold water in the evaporator 3 in accordance with each of the conditions, An efficient Lorentz cycle operation can be performed. Also the mixing ratio, it is possible to increase the high-boiling component-rich side, for example, the condensation temperature of the at dew point curve to the condenser 4 by adjusting the mixing ratio b in FIG up T _3, thus at the heating operation Can obtain high-temperature hot water without increasing the discharge pressure of the compressor.

Next, an operation example of the above-described Lorentz cycle in the heat pump device of the present invention will be described with reference to the drawings. In this operation example, similarly to the above-described operation example of the reverse Carnot cycle, the operation condition is a necessary condition for district cooling and heating. In addition to changing the temperature of the water from 32 ° C to 37 ° C, in the heating operation, change the temperature of the hot water used for heating from 60 to 71 ° C, and change the temperature of the cold water as the heat source water to 12 →
7 ° C is assumed.

That is, FIGS. 6 and 7 show a specific example in the case where the Lorentz cycle operation is performed by using the non-azeotropic mixed refrigerant having a different mixing ratio in the heat pump device of the present invention to satisfy the above-described cooling and heating requirements. The operation is represented by a TS diagram. The non-azeotropic mixed refrigerant is obtained by mixing refrigerant R22 at a ratio of 30 mol% and refrigerant R142b at a ratio of 70 mol% for heating (first mixed refrigerant), and refrigerant R22 for cooling.
A mixture in which 83 mol% and refrigerant R142b were mixed at a ratio of 17 mol% (second mixed refrigerant) was used. The refrigerant temperature and pressure in the subsequent Lorentz cycle are values obtained by estimating physical properties during mixing.

First, FIG. 6 relates to a cooling operation. When the second mixed refrigerant moves the condenser 4 from the upstream side to the downstream side, the second mixed refrigerant flows in the cooling water path of the condenser 4 in a countercurrent manner. Condenses while exchanging heat with the cooling water flowing in
Tk '= 36 ° C from 41 ° C and the temperature of the cooling water
The temperature has risen from d = 32 ° C to Te = 37 ° C.
In the above, heat exchange is performed with the cold water flowing through the cold water path 6, the temperature of the cold water is decreased from Tb = 12 ° C. to Ta = 7 ° C., and the temperature of the cold water is reduced to To ′ = 3 ′ from To = 3.76 ° C. It has risen to 9 ° C. The theoretical coefficient of performance in the cooling operation is the cooling performance coefficient COPc = 8.17, which is larger than the above-described value of the reverse Carnot cycle operation COPc = 7.24. The required discharge pressure of the compressor is 11.5 kgf / cm ² G, and the above-mentioned general-purpose compressor can be used.

FIG. 7 relates to a heating operation. In the condenser 4, the first mixed refrigerant is condensed while exchanging heat with hot water flowing countercurrently in the hot water path in the condenser 4. Then, the temperature of itself drops from Tk = 73.5 ° C. to Tk ′ = 66.8 ° C., and the temperature of the hot water is raised from Td = 60 ° C. to Te = 71 ° C. for heating, and the evaporator 3 In this case, heat exchanges with cold water as a heat source water flowing countercurrently through the cold water path 6 to evaporate while removing heat therefrom, and to raise the temperature of itself from To = 5.13 ° C. to T
o '= raised to 10 ° C. The theoretical coefficient of performance in this heating operation is a heating result coefficient COPh = 5.48, which is larger than the above-described value of the reverse Carnot cycle operation COPh = 4.82. The required discharge pressure of the compressor is 14.4kgf / cm
^The general-purpose compressor of ² G, which is also described above, can be used.

Refrigerants R22 and R14 as non-azeotropic refrigerant mixtures
In the case of using the mixed refrigerant of 2b, the refrigerant R22 contains 20 to 30 mol of the refrigerant R22 for heating, including the mixing ratio in the above embodiment.
%, The refrigerant R142b is 80-70 mol%, and the refrigerant R22 is 70-85 mol% and the refrigerant R142b is 30-15 mol% for cooling.
In this range, the above-described conditions required for district heating and cooling can be easily achieved, and hot water of 50 ° C. or higher can be easily obtained using a general-purpose compressor. still,
The above-described conditions of district heating and cooling are merely examples, and the present invention selects a refrigerant in accordance with appropriate conditions,
Heating and cooling operations can be performed under optimal conditions.

[0046]

The heat pump apparatus of the present invention is as described above, so that the heating operation and the cooling operation can be efficiently performed by using a refrigerant suitable for each operation, and thus the operation is performed for each operation. By using a suitable refrigerant,
In the heating operation, there is an effect that the heating operation in which the temperature in the condenser is increased can be performed without increasing the required pressure of the compressor.

In these operations, the efficiency can be further increased by performing the Lorentz cycle operation using a non-azeotropic mixed refrigerant as the refrigerant as compared with the case of performing the reverse Carnot cycle operation. There is an effect that there is much room for selection of the refrigerant in relation to the regulations on CFCs.

In particular, in the present invention, the switching of the refrigerant is performed by switching the receiver to be operated. Therefore, in applying the Lorentz cycle, the mixture ratio of the refrigerant is changed as compared with the case of performing the rectification by changing the mixing ratio of the refrigerant. Further, there is an effect that the operation is very simple and the switching can be performed reliably.

[Brief description of the drawings]

FIG. 1 is a system diagram showing one embodiment of a configuration of a heat pump device of the present invention.

FIG. 2 is a TS diagram showing an operation of the heat pump apparatus of the present invention when performing a cooling operation in a reverse Carnot cycle with a single refrigerant R22.

FIG. 3 is a TS diagram showing an operation of the heat pump device of the present invention when a heating operation of a reverse Carnot cycle is performed by a single refrigerant R12.

FIG. 4 is a TS diagram showing an operation of the heat pump device of the present invention when performing a heating operation in a reverse Carnot cycle with a single refrigerant R22.

FIG. 5 is an isobaric vapor-liquid equilibrium diagram of a non-azeotropic refrigerant mixture obtained by mixing two types of refrigerants having different boiling points.

FIG. 6 is a graph showing the relationship between R22 and R22 in the heat pump device of the present invention.
T representing the operation when the cooling operation of the Lorentz cycle is performed by the non-azeotropic refrigerant mixture for cooling mixed with 142b.
It is a -S diagram.

FIG. 7 is a graph showing the relationship between R22 and R22 in the heat pump device of the present invention.
T representing the operation when the heating operation of the Lorentz cycle is performed by using a non-azeotropic refrigerant mixture for heating mixed with 142b.
It is a -S diagram.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor 2 Drive source 3 Evaporator 4 Condenser 5 Refrigerant path 6 Cold water path 7 Refrigerant path 8 Cooling water (or hot water) path 9a, 9b Inlet side valve 10a, 10b Receptacle 11a, 11b Outlet side valve 12 Refrigerant liquid Valve 13 Expansion valve 14 Partition wall 15 Refrigerant recovery device 16 Inlet side valve 17a, 17b Outlet side valve

──────────────────────────────────────────────────続 き Continuation of the front page (72) Inventor Norio Ota 4-12-1 Nishikoya, Ota-ku, Tokyo (56) References JP-A-2-263056 (JP, A) JP-A-63-315865 (JP, A) ) JP-B-57-31056 (JP, B2) (58) Fields investigated (Int. Cl. ⁶ , DB name) F25B 1/00 395 F25B 13/00

Claims (14)

(57) [Claims] The present invention relates to a heat pump, comprising two systems of liquid receivers, which are switchable, storing different refrigerants for heating and cooling, respectively. A heat pump device comprising a refrigerant recovery path corresponding to a liquid receiver. 2. The heat pump device according to claim 1, wherein
Heat pump device characterized in that the refrigerant is operated as a reverse single Carnot cycle as a different single refrigerant. 3. A single refrigerant in the heat pump device according to claim 2, wherein the refrigerant R12 is used for heating and the refrigerant R22 is used for cooling.
Heat pump device characterized by using 4. The heat pump device according to claim 1, wherein
A heat pump device wherein the refrigerant is a non-azeotropic mixed refrigerant and the evaporator and the condenser are configured to operate in a Lorentz cycle as a countercurrent type. 5. The heat pump device according to claim 4, wherein
The non-azeotropic refrigerant mixture is a non-azeotropic refrigerant mixture of the same component having a different mixing ratio. 6. The heat pump device according to claim 5, wherein the non-azeotropic refrigerant mixture is a refrigerant mixture of the refrigerant R22 and the refrigerant R142b. 7. The heat pump device according to claim 6, wherein
The mixing ratio of the refrigerant R22 and the refrigerant R142b in the non-azeotropic mixed refrigerant is as follows.
42b is 80-70 mol%, and the refrigerant R22 is used for cooling.
A heat pump device characterized in that the amount of the refrigerant R is 70 to 85 mol% and the refrigerant R142b is 30 to 15 mol%. 8. The heat pump device according to claim 4, wherein
A heat pump device wherein the non-azeotropic mixed refrigerant is a non-azeotropic mixed refrigerant having different components. 9. The heat pump device according to claim 5, wherein the non-azeotropic mixed refrigerant contains a refrigerant R22 as a component. 10. The heat pump apparatus according to claim 5, wherein the non-azeotropic mixed refrigerant contains a refrigerant R142b as a component. 11. The heat pump device according to claim 5, wherein the non-azeotropic mixed refrigerant contains a refrigerant R134a as a component. 12. The heat pump device according to claim 5, wherein the non-azeotropic mixed refrigerant contains a refrigerant RC318 as a component. 13. The heat pump device according to claim 5, wherein the non-azeotropic mixed refrigerant contains refrigerant R123 as a component. 14. The heat pump device according to claim 5, wherein the non-azeotropic mixed refrigerant contains a refrigerant R124 as a component.