WO2014045998A1

WO2014045998A1 - Second class absorption heat pump, and primary industrial facility and air heating method using second class absorption heat pump

Info

Publication number: WO2014045998A1
Application number: PCT/JP2013/074661
Authority: WO
Inventors: 松本　健
Original assignee: ヤンマー株式会社
Priority date: 2012-09-21
Filing date: 2013-09-12
Publication date: 2014-03-27
Also published as: JP2014062691A

Abstract

Provided is a second class absorption heat pump that uses the earth's heat as a heat source, and a primary industrial facility and an air heating method that use the second class absorption heat pump. A second class absorption heat pump (1) is configured comprising a heater (2), an absorber (3), a regenerator (4), and a condenser (5), and the heat pump achieves a heat output such that the temperature of a medium (T) to be heated is higher than the temperature of a heating medium (H) led into the evaporator (2) or the regenerator (4). The heat pump also has: a atmospheric heat exchanger (6) which has a channel for a cooling medium (C) for cooling refrigerant vapor (Rg) in the condenser (5) and which cools the cooling medium (C) with atmospheric air (A); and an earth's heat exchanger (7) which has a channel for a heating medium (H) for heating a refrigerant liquid (R) in the evaporator (2) and heating an absorbent dilute solution (Sd) in the regenerator (4), and which heats the heating medium (H) with the earth's heat (Gh).

Description

Second type absorption heat pump, and primary industrial facility and heating method using second type absorption heat pump

The present invention relates to a second type absorption heat pump that uses underground heat as a high-temperature heat source, and a primary industrial facility and a heating method using the same.

In general, the second type absorption heat pump generates refrigerant vapor by heating a refrigerant liquid with a heating medium in an evaporator, and the generated refrigerant vapor is absorbed by an absorbing solution in the absorber and is generated at this time. The heated medium is heated by the absorbed heat. In the regenerator, the absorbing solution having a low solute concentration is heated by a heating medium, thereby generating refrigerant vapor and generating an absorbing solution having a high solute concentration.

The condenser is configured such that the refrigerant vapor generated in the regenerator is cooled by a cooling medium to be condensed and liquefied to generate a refrigerant liquid.

Further, the medium to be heated introduced into the absorber is configured to be able to output heat at a temperature higher than the temperature of the heating medium introduced into the evaporator or the regenerator.

Conventionally, such a second type absorption heat pump uses a waste heat of a prime mover such as a gas engine or a diesel engine as a heating heat source of the heating medium, and as a cooling heat source of a cooling medium that cools and condenses the refrigerant vapor. In addition, by using atmospheric air or geothermal heat, it has been performed to take out vapor of 0.4 MPa (saturation temperature 143.62 ° C.) or more which is easy to use (for example, see Patent Document 1).

JP 2010-65862 A

However, in the conventional second type absorption heat pump, a prime mover has to be used in order to obtain exhaust heat that is a heating heat source.
Moreover, in order to take out high temperature steam, the geothermal heat was only considered to be used as a cooling heat source.

The present invention has been made in view of such circumstances, and provides a second type absorption heat pump that uses geothermal heat as a heating heat source, and a primary industrial facility and a heating method using the same. It is aimed.

A second type absorption heat pump according to the present invention for solving the above-described problems is an evaporator that heats a refrigerant liquid and generates refrigerant vapor, and an absorption solution that absorbs the refrigerant vapor generated in the evaporator. An absorber that heats the medium to be heated with absorption heat, and an absorption dilute solution whose solute concentration is reduced by absorbing the refrigerant vapor in the absorber is introduced and heated to generate refrigerant vapor, and at the same time, the solute A regenerator that generates an absorbent solution having a high concentration; and a condenser that cools the refrigerant vapor generated in the regenerator and generates a refrigerant liquid, wherein the temperature of the medium to be heated is the evaporator Or a second type absorption heat pump that obtains a heat output higher than the temperature of the heating medium introduced into the regenerator, having a cooling medium path for cooling the refrigerant vapor of the condenser, and the cooling refrigerant in the atmosphere Cooling atmospheric heat exchanger and Heating the refrigerant liquid in the evaporator, having a path of a heating medium for heating the absorption dilute solution of the regenerator, and has a geothermal heat exchanger for heating the heating medium in the ground heat.

The second type absorption heat pump may include a heating device that uses hot water or hot air obtained from the absorber via a heat exchanger as a heating heat source.

The second type absorption heat pump may be provided with a cooling device such as a radiant cooler in the cooling medium path of the atmospheric heat exchanger.

The second type absorption heat pump may be one in which the refrigerant liquid is ammonia and the absorption liquid is water.

Moreover, the primary industrial facility of the present invention for solving the above-described problems includes a second-type absorption heat pump including the heating device as a heat source for heating inside the facility main body.

Furthermore, the heating method using the second type absorption heat pump of the present invention for solving the above problem is a heating method using the second type absorption heat pump, and has an atmospheric temperature lower than the underground heat. In the place, the ground heat is used as a heating heat source, a heat output higher than the ground heat is obtained, and the obtained heat output is used as a heating heat source.

According to the present invention, geothermal heat can be effectively used as a heating heat source.

It is a refrigerant circuit figure showing the outline of the whole composition of the 2nd kind absorption heat pump concerning the present invention. (A) And (b) is the schematic which shows other embodiment of the supply path | route of the heating medium in the 2nd type absorption heat pump shown in FIG. It is the schematic which shows the outline of the plant factory which used the 2nd type absorption heat pump shown in FIG. 1 as a heat source.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 1 is a refrigerant circuit diagram showing an outline of the entire configuration of a second type absorption heat pump 1 according to the present invention.

The second type absorption heat pump 1 according to the present invention includes an evaporator 2, an absorber 3, a regenerator 4, and a condenser 5, and an atmospheric heat exchanger that cools the refrigerant vapor Rg of the condenser 5. 6 and a geothermal heat exchanger 7 for heating the refrigerant liquid R of the evaporator 2 and the absorbing diluted solution Sd of the regenerator 4.

The evaporator 2 is configured to generate the refrigerant vapor Rg by heating the refrigerant liquid R with the heating medium H flowing through the underground heat exchanger 7 described later. The evaporator 2 and the condenser 5 are connected by a refrigerant supply path 11 via a refrigerant pump 101. The evaporator 2 and the absorber 3 are connected by a refrigerant vapor supply path 12 via a receiver 102.

As a result, the refrigerant liquid R supplied from the condenser 5 to the evaporator 2 via the refrigerant supply path 11 is heated by the evaporator 2 to become the refrigerant vapor Rg, and then the receiver 102 is supplied from the refrigerant vapor supply path 12. Then, it is supplied to the absorber 3.

The absorber 3 is configured such that the absorbing solution S supplied from the regenerator 4 absorbs the refrigerant vapor Rg supplied from the refrigerant vapor supply path 12 to generate absorption heat. The absorber 3 is configured to heat the heated medium T flowing through the heat exchanger 81 provided in the absorber 3 and obtain a heat output by the absorbed heat. The upper part of the absorber 3 and the bottom part of the regenerator 4 are connected by an absorbing solution supply path 13 via a solution pump 103. The bottom of the absorber 3 and the top of the regenerator 4 are connected via an expansion valve 104 by an absorbing diluted solution recovery path 14. The refrigerant vapor supply path 12 is connected to the upper part of the absorber 3. The absorbing solution supply path 13 and the absorbing dilute solution recovery path 14 are configured to exchange heat with each other by the solution heat exchanger 105.

As a result, the refrigerant vapor Rg supplied from the upper part of the absorber 3 via the refrigerant vapor supply path 12 is similarly absorbed by the absorption solution S supplied from the upper part of the absorber 3 via the absorbent solution supply path 13. The heat exchanger 81 of the medium to be heated T is heated with the absorbed heat. The diluted absorption solution Sd having a reduced solute concentration due to the absorption of the refrigerant vapor Rg is recovered from the bottom of the absorber 3 to the regenerator 4 via the absorption diluted solution recovery path 14. Moreover, since the absorption dilute solution Sd recovered from the absorption dilute solution recovery path 14 to the regenerator 4 does not recover all the absorption heat in the absorber 3 and has unrecovered heat, the solution heat exchanger 105 Heat is exchanged between the absorbing diluted solution recovery path 14 through which the absorbing diluted solution Sd having unrecovered heat flows and the absorbing solution supply path 13 through which the absorbing solution S from the regenerator 4 flows and is supplied to the absorber 3. The temperature of the absorption solution S is increased.

The regenerator 4 generates the refrigerant vapor Rg by heating the absorption dilute solution Sd by the heating medium H flowing through the underground heat exchanger 7 described later, and generates the refrigerant solution S having a high solute concentration. It is configured. The upper part of the regenerator 4 and the upper part of the condenser 5 are connected by a refrigerant vapor supply path 15. An absorbing diluted solution recovery path 14 is connected to the upper part of the regenerator 4. The absorption diluted solution recovery path 14 is connected to a refrigerant vapor recovery path 16 connected to the bottom of the receiver 102 from a branch point a between the expansion valve 104 and the regenerator 4. The refrigerant vapor recovery path 16 is also provided with an expansion valve 106. A bypass path 17 to the refrigerant supply path 11 is provided from the branch point b of the refrigerant vapor recovery path 16 between the expansion valve 106 and the receiver 102. The bypass path 17 is provided with an on-off valve 107, which is normally “closed”.

As a result, the diluted absorbent solution Sd supplied from the absorber 3 to the regenerator 4 via the absorbed diluted solution recovery path 14 is heated by the regenerator 4 and is transferred to the condenser 5 from the refrigerant vapor supply path 15 to the refrigerant vapor Rg. Is supplied. The absorption solution S having a higher solute concentration due to the supply of the refrigerant vapor Rg is supplied from the absorption solution supply path 13 to the absorber 3 by the solution pump 103.

The condenser 5 is configured to condense and liquefy the refrigerant vapor Rg supplied from the regenerator 4 via the refrigerant vapor supply path 15 by a cooling medium C flowing through an atmospheric heat exchanger 6 described later. A refrigerant vapor supply path 15 is connected to the upper part of the condenser 5. A refrigerant supply path 11 is connected to the bottom of the condenser 5.

Thus, the refrigerant vapor Rg supplied from the regenerator 4 through the refrigerant vapor supply path 15 to the condenser 5 is cooled by the condenser 5 to become the refrigerant liquid R, and then the refrigerant pump 101 from the refrigerant supply path 11. After that, it is supplied to the evaporator 2.

The atmospheric heat exchanger 6 is connected to a heat exchanger 61 provided in the condenser 5 by a circulation path 62 of the cooling medium C. The cooling medium C is configured to be circulated between the atmospheric heat exchanger 6 and the heat exchanger 61 by a circulation pump 60 provided in the circulation path 62.

Thereby, after the cooling medium C cooled by the atmosphere A in the outdoor atmospheric heat exchanger 6 cools the refrigerant vapor Rg in the heat exchanger 61 in the condenser 5 via the circulation path 62 and condenses and liquefies, The flow is again returned to the atmospheric heat exchanger 6 through the circulation path 62, and thereafter, this circulation is repeated by the circulation pump 60.

In the underground heat exchanger 7, the heat exchanger 71 provided in the evaporator 2 and the heat exchanger 72 provided in the regenerator 4 are connected by a circulation path 73 of the heating medium H. The heating medium H is configured to be circulated among the underground heat exchanger 7, the heat exchanger 71, and the heat exchanger 72 by a circulation pump 70 provided in the circulation path 73. At this time, the underground heat exchanger 7 is provided at a depth of 5 m or more underground so that the underground heat Gh having a relatively stable temperature of 15 ° C. to 20 ° C. can be obtained.

Thus, the heating medium H heated by the underground heat exchanger 7 is regenerated after the refrigerant liquid R is heated to the refrigerant vapor Rg by the heat exchanger 71 in the evaporator 2 through the circulation path 73. After the absorption dilute solution Sd is heated by the heat exchanger 72 in the vessel 4 to generate the refrigerant vapor Rg, it is returned again to the underground heat exchanger 7 through the circulation path 73, and thereafter the circulation pump 70. This cycle is repeated.

In FIG. 1, the heat exchanger 71 provided in the evaporator 2 and the heat exchanger 72 provided in the regenerator 4 are connected in series, but are connected in parallel as shown in FIG. Alternatively, as shown in FIG. 2B, the circulation pump 70 and the underground heat exchanger 7 may be connected to correspond to the

heat exchangers

71 and 72, respectively.

The second type absorption heat pump 1 configured as described above uses the underground heat Gh as a heating heat source and uses the atmosphere A as a cooling heat source. Therefore, in an environment where the temperature of the atmosphere A is lower than the underground heat Gh. used. Specifically, it is used in an area where the temperature of the atmosphere A is lower than this temperature against the geothermal heat Gh that is stable at 15 ° C. to 20 ° C. In this case, even if the temperature of the atmosphere A is lower than the geothermal heat Gh, if the temperature difference is too small, a heat pump cycle cannot be configured, so the temperature of the atmosphere A is 15 ° C. or higher than the geothermal heat Gh. It is preferable to use in areas with low temperature differences. Further, even in a region where the annual average temperature of the atmosphere A is higher than the temperature of the geothermal heat Gh, for example, if the temperature in winter is low, it can be used in winter.

Thereby, the second type absorption heat pump 1 can obtain a heat output at a temperature of about 22 ° C. to 30 ° C. higher than the underground heat Gh. For example, when the temperature of the ground heat Gh is 17 ° C. and the temperature of the atmosphere A is 0 ° C., a heat output of 26 ° C. can be obtained.

Even in extremely cold regions where the cooling is severe, since the temperature of the underground heat itself is stable, according to the second type absorption heat pump 1, it is always about 22 ° C. to 30 ° C. higher than the underground heat Gh. The heat output of the temperature of can be obtained. The heat output of 22 ° C. to 30 ° C. can be used as an auxiliary heat source for heating people in extremely cold regions. Moreover, it can be used as hot water or hot air for auxiliary air conditioning in cold regions or severe winter seasons, in addition to use in people in extremely cold regions. For example, FIG. 3 uses the heat output of the second-type absorption heat pump 1 for auxiliary heating of a plant factory 10 as a primary industrial facility that is required to manage plants at a constant temperature. The plant factory 10 connects a heating device 8 provided in the factory and a heat exchanger 81 provided in the absorber 3 of the second type absorption heat pump 1 by a circulation path 82 to be heated medium T. And the heat output from the absorber 3 of the second type absorption heat pump 1 is used in the plant factory 10 via the heating device 8. In this case, the heating device 8 may be one that emits warm air into the plant factory 10 by a fan (not shown) or may be used for water temperature management in hydroponics. However, it may be used for radiant heat heating. When used for water temperature management of hydroponics, the culture medium itself of hydroponics may be used as the heated medium T.

In addition, as a primary industrial facility other than the plant factory 10 described above, for example, in a livestock breeding facility, it is used for auxiliary heating to prevent food, drinking water, and the facility from freezing, or fishery such as a ginger or a fish tank. It can be used for auxiliary heating for water temperature management in equipment, or as auxiliary heating for preventing frostbite and freeze-drying due to freezing of stored items stored in a warehouse. In the case of a breeding facility, the heating device 8 may be one that emits warm air in the breeding facility, or warms the food and drinking water so that they are not frozen, and controls the temperature of the food and drinking water. It may be used, or may be used for radiant heating of a floor or wall surface of a facility. In the case of a ginger or an aquarium, the heating device 8 may be one that emits warm air into the space provided with the ginger or the aquarium, or directly warms the water in the ginger or the aquarium, and the ginger or the aquarium. It may be used for water temperature management. In the case of a warehouse, the heating device 8 may be one that emits warm air into the warehouse, or may be one that is used for radiant heating of the floor or wall surface of the warehouse.

In addition, the heating heat source in the second type absorption heat pump 1 is not obtained by fuel consumption, such as engine exhaust heat, but is obtained from nature, so that heat output can be obtained at low cost. it can.

Further, if the geothermal heat Gh is used as it is, even if it is a very cold region or a cold region where the heat capacity is insufficient and cannot be effectively used, according to the second type absorption heat pump 1 of the present invention, the ground The heat capacity can be increased up to about 1.5 times the maximum amount of medium heat Gh. Therefore, it is possible to promote the use of the geothermal heat Gh even in extremely cold regions and cold regions where the heat capacity has been insufficient so far and the geothermal heat Gh cannot be used.

The geothermal heat Gh is configured to pass the heating medium H through the geothermal heat exchanger 7 embedded in the ground and absorb the geothermal heat Gh. A stable heat source in the ground or on the ground may be used. For example, water that flows through sewage or rivers including factory wastewater or domestic wastewater and the heating medium H may be heat-exchanged and absorbed. Industrial wastewater and domestic wastewater have a certain temperature, and are drained through a sewer pipe buried in the ground, so that a temperature equivalent to the underground heat Gh can be obtained. Since the water flowing through the river passes through the ground and groundwater veins and is warmed by the underground heat Gh, the temperature equivalent to the underground heat Gh can be obtained in rivers that are not frozen in winter. In addition, the excrement of livestock collected as farmland fertilizer and the heating medium H may be heat-exchanged. Since such livestock manure is fermented, even if heat is absorbed by the heating medium H, a relatively stable temperature can be obtained.

Further, although the cooling medium A is configured to directly take in the outside air, the outside air or antifreeze liquid that has passed through a cooling device such as a radiant cooler may be used as a cooling heat source. The second type absorption heat pump has a property that the temperature of the heated medium T at the absorber outlet increases as the temperature of the cooling medium A decreases. Therefore, by providing the cooling medium A with the cooling device, the effect of the present invention can be obtained more greatly.

Further, the second type absorption heat pump 1 of the present invention considers that the geothermal heat Gh that is stable at 15 ° C. to 20 ° C. is used as a heating heat source, and the refrigerant liquid R is ammonia and the absorption liquid S is water. It is preferable to use the ammonia-water medium. However, depending on the installation location, the geothermal heat Gh is increased due to the volcanic activity, the river water is hot springs, and the factory effluent is hot. A suitable refrigerant liquid R and absorption liquid S suitable for the temperature range can be used.

Note that the present invention can be implemented in various other forms without departing from the spirit or main features thereof. For this reason, the above-described embodiments are merely examples in all respects and should not be interpreted in a limited manner. The scope of the present invention is indicated by the claims, and is not restricted by the text of the specification. Furthermore, all modifications and changes belonging to the scope of the claims are within the scope of the present invention.

1 Type 2 absorption heat pump 10 Plant factory (primary industrial facility)
2 Evaporator 3 Absorber 4 Regenerator 5 Condenser 6 Atmospheric Heat Exchanger 7 Geothermal Heat Exchanger 8 Heating Device 81 Heat Exchanger A Atmosphere C Cooling Refrigerant H Heating Refrigerant Sd Absorbing Dilute Solution S Absorbing Solution T Heated Medium Tp Heat output R Refrigerant Rg Refrigerant vapor Gh Underground heat

Claims

An evaporator for heating the refrigerant liquid and generating refrigerant vapor;
An absorber that heats the medium to be heated with absorption heat when the absorbing solution absorbs the refrigerant vapor generated in the evaporator;
A regenerator that introduces an absorbing dilute solution having a reduced solute concentration by absorbing the refrigerant vapor in the absorber, generates refrigerant vapor by heating, and simultaneously generates an absorbing solution having a high solute concentration;
A condenser for cooling the refrigerant vapor generated in the regenerator and generating a refrigerant liquid,
A second type absorption heat pump that obtains a heat output in which the temperature of the heated medium is higher than the temperature of the heating medium introduced into the evaporator or the regenerator,
An atmospheric heat exchanger having a cooling medium path for cooling the refrigerant vapor of the condenser and cooling the cooling refrigerant in the atmosphere;
And a ground heat exchanger that heats the refrigerant liquid of the evaporator and heats the absorption dilute solution of the regenerator, and has a ground heat exchanger that heats the heating medium with ground heat. Seed absorption heat pump.
The second type absorption heat pump according to claim 1, further comprising a heating device using hot water or hot air obtained from the absorber via a heat exchanger as a heating heat source.
The second type absorption heat pump according to claim 1, further comprising a cooling device in a cooling medium path that absorbs heat from the condenser via the heat exchanger.
The second type absorption heat pump according to claim 2, wherein the cooling medium path is configured to absorb heat from the condenser via the heat exchanger.
The second type absorption heat pump according to claim 1, wherein the refrigerant liquid is ammonia and the absorption liquid is water.
The second type absorption heat pump according to claim 2, wherein the refrigerant liquid is ammonia and the absorption liquid is water.
The second type absorption heat pump according to claim 3, wherein the refrigerant liquid is ammonia and the absorption liquid is water.
The second type absorption heat pump according to claim 4, wherein the refrigerant liquid is ammonia and the absorption liquid is water.
A primary industrial facility comprising the second type absorption heat pump according to any one of claims 1 to 8 as a heat source for heating inside the facility main body.
A heating method using the second type absorption heat pump according to any one of claims 1 to 8, wherein the underground heat is used as a heating heat source in a place where the atmospheric temperature is lower than the underground heat. A heating method using a second type absorption heat pump, wherein a higher heat output is obtained and the obtained heat output is used as a heating heat source.