JP5409022B2 - High-temperature heat pump system - Google Patents

Description

  The present invention relates to a high-temperature heat pump system.

  Conventionally, the output temperature of the heat medium in the heat pump system is generally 40 to 50 ° C. As a system having a high output temperature, a configuration is known in which a heated fluid is heated by burning fuel in a boiler (see, for example, Patent Document 1).

JP-A-6-249450

  In recent years, there has been a demand for a heat pump system having a high output temperature in order to replace a system having a boiler.

  An object of this invention is to provide the heat pump system which has high output temperature.

According to an aspect of the present invention, the first fluid flows, includes a first unit including a heat pump including a heat absorbing part, a compressing part, a heat radiating part, and an expanding part, and a path through which the second fluid flows, and from the first fluid A second unit that outputs the second fluid that has received the transfer heat of the heat pump, wherein the heat pump flows in the first fluid from the heat radiating portion , and the liquid first fluid and the gas phase An intermediate part in which the first fluid is temporarily stored and the gas-phase first fluid is supplied to the compression part; the first fluid heading toward the intermediate part; and the first fluid from the intermediate part An intermediate heat exchanging portion that transfers heat from at least one of the first fluid toward the compressing portion and at least one of the first fluid in the middle of the compressing portion, the intermediate heat exchanging portion, The first flow flowing from the heat radiating portion into the intermediate portion Heat from at least a portion of the comprising a first intermediate heat exchanger unit for transmitting from the intermediate portion to the first fluid in the gas phase towards the compression section, a high temperature heat pump system is provided.

  According to the aspect of the present invention, in the intermediate heat exchange part, heat from the first fluid having a relatively high temperature is transmitted to at least one of the first fluid toward the compression part and the first fluid in the middle of the compression part, As a result, the second fluid can be stably heated at a high temperature.

It is the schematic which shows 1st Embodiment. It is the schematic which shows 2nd Embodiment. It is the schematic which shows 3rd Embodiment. It is the schematic which shows 4th Embodiment. It is the schematic which shows 5th Embodiment. It is the schematic which shows 6th Embodiment. It is the schematic which shows 7th Embodiment. It is the schematic which shows 8th Embodiment.

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

  FIG. 1 is a schematic diagram showing a high-temperature heat pump system S1 according to the first embodiment. In FIG. 1, a heat pump system S1 includes a heat pump 10 (first unit) through which a working fluid (working medium, first fluid) flows, and a supply unit 20 (second unit) for a heated fluid (heated medium, second fluid). ) And a control device 70. The control device 70 comprehensively controls the entire system. The configuration of the system S1 can be variously changed according to the design requirements of the system S1.

  In the present embodiment, the fluid to be heated is water. In other embodiments, other media are applicable as the heated fluid. As other examples of the fluid to be heated, high-pressure water (compressed water), low-viscosity oil (for example, silicon oil, propylene glycol, or the like) can be used.

  In the present embodiment, the supply unit 20 has a path (conduit 22) through which the fluid to be heated flows, and the fluid to be heated is supplied from the supply source to the supply unit 20. The output temperature (extraction temperature) of the heated fluid (water) from the supply unit 20 is 80, 85, 90, 95, 100, 105, 110, 115, 120, 125, 130, 135, 140, 145, or 150. ℃ or more. For example, when water is heated to 100 ° C. or higher under atmospheric pressure, steam of 100 ° C. or higher is output from the supply unit 20. In the present embodiment, the fluid to be heated having a low output temperature (less than 70 ° C.) can be taken out as necessary.

  The heat pump 10 is a device that pumps heat from a low-temperature object and applies heat to a high-temperature object by a cycle including evaporation, compression, condensation, and expansion processes. A heat pump generally has the advantage of relatively high energy efficiency and, as a result, relatively low emissions of carbon dioxide and the like.

  In the present embodiment, the heat pump 10 includes a heat absorption unit 11, a compression unit 12, a heat radiation unit 13, and an expansion unit 14, which are connected via a conduit. In the present embodiment, the heat pump 10 further includes an intermediate part 40 and an intermediate heat exchange part 41. Note that various sensors, pumps, valves, and the like (not shown) can be disposed in each part and conduit as needed.

  In the heat absorption part 11, the working fluid absorbs heat from a heat source outside the cycle. In the present embodiment, the heat absorbing unit 11 includes an evaporator that is thermally connected to the heat radiating pipe 91 of the external device 90 and in which the working fluid evaporates. The heat of the medium (refrigerant, etc.) flowing through the heat radiating pipe 91 is absorbed by the heat absorbing part 11 of the heat pump 10. It is also possible to use the exhaust heat of the external device 90 as a heat source. It can also be set as the structure which the heat absorption part 11 absorbs the heat of other heat sources, such as air | atmosphere.

  In the present embodiment, the heat absorbing unit 11 has a region where the liquid phase of the working fluid exists and a region where the gas phase of the working fluid exists. The heat radiating pipe 91 of the external device 90 is disposed in the liquid phase region. Alternatively or additionally, the endothermic part 11 can have a spray structure.

  The compression unit 12 compresses the working fluid by a compressor or the like. At this time, the temperature of the working fluid usually increases. The compression unit 12 has a structure for compressing the working fluid into a single stage or a plurality of stages. The number of stages of compression is set according to the specification of the system S1, and is 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. Among the various compressors such as an axial flow compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor, a compressor suitable for compressing a working fluid is applied. Power is supplied to the compressor. The compression ratio (pressure ratio) of the compression unit 12 is set according to the specifications of the system S1.

  In the present embodiment, the compression unit 12 has a two-stage compression structure including a first compression unit 12A and a second compression unit 12B. As the working fluid used in the heat pump 10, various known heat mediums such as chlorofluorocarbon media (HFC 245fa, R134a, etc.), ammonia, water, carbon dioxide, air, etc. are used according to the specifications and heat balance of the system S1. It is done. In the present embodiment, when R134a is used as the working fluid, the first compression unit 12A increases the low pressure R134a from the heat absorption unit 11 to an intermediate pressure. The second compression unit 12B boosts R134a from the first compression unit 12A and the intermediate unit 40 to a high pressure (including a supercritical pressure region). The present invention is applicable to both specifications in which at least a part of the working fluid is in a supercritical state and specifications in which the working fluid is not in a supercritical state.

  In the heat radiating part 13, the heat of the working fluid flowing in the main path 15 is given to a heat source outside the cycle. In the present embodiment, the heat dissipating unit 13 is thermally connected to the supply unit 20, and the working fluid dissipates heat therein to become a liquid phase.

  In the present embodiment, when R134a is used as the working fluid, heat exchange is performed between the supercritical state and liquid phase R134a and the water flowing through the supply unit 20, and superheated steam is output from the supply unit 20.

  In the present embodiment, the heat radiating section 13 has a region where a gas phase (or supercritical state) working fluid exists and a region where a liquid phase working fluid exists. The conduit 22 of the supply unit 20 is arranged over both areas. Alternatively or additionally, the heat dissipation part 13 may have a spray structure.

  The expansion unit 14 expands the working fluid by a pressure reducing valve, a turbine, or the like. At this time, the temperature of the working fluid usually decreases. When a turbine is used, power can be taken out from the expansion unit 14, and the power may be supplied to the compression unit 12, for example.

  In the present embodiment, the expansion unit 14 includes a high pressure expansion valve 24 and a low pressure expansion valve 25. The high-pressure expansion valve 24 is disposed on a conduit 26 that fluidly connects the heat radiating part 13 and the intermediate part 40, and reduces the high-pressure working fluid from the heat radiating part 13 to an intermediate pressure. More specifically, the arrangement position of the high-pressure expansion valve 24 is on the conduit 26 and before the working fluid inlet in the intermediate portion 40. The high pressure expansion valve 24 can also control the flow rate of the working fluid.

  The low pressure expansion valve 25 is disposed on a conduit 27 that fluidly connects the intermediate portion 40 and the heat absorbing portion 11, and reduces the working fluid from the intermediate portion 40 to a low pressure. More specifically, the low-pressure expansion valve 25 is disposed on the conduit 27 and before the working fluid inlet in the heat absorbing section 11. The low pressure expansion valve 25 can also control the flow rate of the working fluid.

  The intermediate unit 40 separates the working fluid decompressed to an intermediate pressure into a gas phase and a liquid phase, and stores the working fluid at least temporarily. The gas phase working fluid from the intermediate part 40 is injected into the compression part 12 through the conduit 23. Further, the liquid-phase working fluid from the intermediate portion 40 is guided to the heat absorbing portion 11 via the conduit 27.

  The intermediate heat exchange unit 41 is for giving a part of heat of the working fluid having a relatively high temperature to the working fluid supplied to the compression unit 12. In the present embodiment, in the intermediate heat exchanging unit 41, heat exchange is performed between the working fluid from the heat radiating unit 13 and the working fluid from the intermediate unit 40 toward the compression unit 12. In the following description, an intermediate heat exchange part having a heat exchange function between them is appropriately referred to as a “first intermediate heat exchange part”.

  In the present embodiment, the first intermediate heat exchanging part 41 includes a part of the intermediate part 40 (gas phase part) and a part of the conduit of the main path 15 of the heat pump 10 (conduit between the heat radiation part 13 and the intermediate part 40). 26 part) are thermally connected to each other. In the present embodiment, a part of the conduit 26 is disposed in the gas phase region in the internal space of the intermediate portion 40. The first intermediate heat exchanging part 41 may have a countercurrent heat exchange structure in which a high-temperature fluid (working fluid in the conduit 26) and a low-temperature fluid (working fluid in the intermediate part 40) flow oppositely. it can. Alternatively, the first intermediate heat exchange unit 41 may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  Various heat exchange structures such as a plate heat exchange structure and a fin-and-tube heat exchange structure can be applied to the first intermediate heat exchange unit 41.

  In the heat pump system S1 configured as described above, when the heat pump 10 is operated, the water flowing through the supply unit 20 is heated by the heat supplied from the heat pump 10, and as a result, high-temperature water or steam is output from the supply unit 20. .

Hereinafter, the operation of the heat pump system S1 will be described.
In the heat pump 10, the compression unit 12 is driven. The first compression unit 12A compresses the working fluid to an intermediate pressure. The second compression unit 12B compresses the working fluid from the first compression unit 12A and the working fluid from the intermediate unit 40 to a high pressure.

  The compressed working fluid from the compression unit 12 is supplied to the heat dissipation unit 13. In the heat radiating unit 13, heat from the working fluid is transmitted to the heated fluid (water) flowing through the conduit 22 of the supply unit 20. From the supply unit 20, water or steam heated to a high temperature is output. With the heat exchange between the working fluid and the medium to be heated, a part of the working fluid becomes a liquid phase inside the heat radiating unit 13.

  The liquid-phase working fluid from the heat radiating unit 13 is decompressed to an intermediate pressure by the high-pressure expansion valve 24. By controlling the opening degree of the high-pressure expansion valve 24, the liquid level of the heat radiating unit 13 can be controlled.

  The reduced working fluid from the high pressure expansion valve 24 flows into the intermediate portion 40. In the intermediate part 40, the working fluid is separated into a gas phase and a liquid phase. The gas phase working fluid from the intermediate section 40 is supplied to the middle of the compression section 12 (between the first compression section 12A and the second compression section 12B) via the conduit 23.

  The liquid-phase working fluid from the intermediate portion 40 is decompressed to a low pressure by the low-pressure expansion valve 25. By controlling the opening degree of the low-pressure expansion valve 25, the liquid level of the intermediate portion 40 can be controlled.

  The decompressed working fluid from the intermediate unit 40 is supplied to the heat absorbing unit 11. In the heat absorption part 11, the heat of the medium from outside the cycle is transmitted to the working fluid. A part of the working fluid evaporates inside the heat absorbing part 11 with heat exchange between the medium outside the cycle and the working fluid. The gas phase working fluid from the heat absorption unit 11 is supplied to the compression unit 12. In this way, the above cycle is repeated.

  In the present embodiment, when R134a is used as the working fluid, the heat from the R134a is transferred to the heated fluid (water) in the supply unit 20 in the heat radiating section 13, and superheated steam of about 120 ° C. can be generated. It is. The temperature of the critical point of R134a (HFC134a) is in the vicinity of 100 ° C., which is the normal boiling point of water, and the output temperature of R134a from the compression unit 12 can be set to about 150 ° C. Therefore, R134a is suitable as a working fluid for a heat pump cycle in which the medium to be heated is water. Moreover, the output temperature of R134a from the compression part 12 is set to about 150 degreeC, The pressure can be restrained comparatively low to about 4 MPa. This is advantageous in reducing the apparatus cost.

  In the present embodiment, in the first intermediate heat exchange unit 41, heat from the working fluid from the heat radiating unit 13 having a relatively high temperature is transmitted to the working fluid from the intermediate unit 40 toward the compression unit 12. As a result, the working fluid injected between the stages of the compression unit 12 (inlet of the second compression unit 12B) is heated. When the temperature of the injection fluid rises, the output temperature of the working fluid from the compression unit 12 also rises. Therefore, according to the present embodiment, the medium to be heated can be stably heated at a high temperature.

  Note that the heating of the working fluid from the intermediate portion 40 toward the stage of the compression portion 12 is effective in recovering excess heat of the working fluid. As a result, the coefficient of performance (COP) as energy efficiency is increased. It has been confirmed that it is advantageous for improvement.

  In the present embodiment, the output temperature of the working fluid from the compression unit 12 is also increased by heating the working fluid from the intermediate unit 40 toward the stage of the compression unit 12 in the first intermediate heat exchange unit 41. As a result, the thermal output can be effectively increased (an increase in output exceeding the increase in compressor power can be obtained).

  In the present embodiment, the first intermediate heat exchange unit 41 heats the gas-phase working fluid inside the intermediate unit 40. The fact that the first intermediate heat exchanging part 41 and the intermediate part 40 are substantially integrated is advantageous in terms of making the apparatus compact. Alternatively, the intermediate part 40 and the first intermediate heat exchange part 41 can be substantially separated.

  Next, a second embodiment of the present invention will be described with reference to FIG.

  FIG. 2 is a schematic diagram showing a heat pump system S2 according to the second embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 2, in addition to the first intermediate heat exchanging unit 41, the heat pump system S <b> 2 provides two working fluids having a relatively high temperature to the working fluid supplied to the compression unit 12. Intermediate heat exchange units 42 and 43 are provided.

  First, in the intermediate heat exchanging unit 42, heat exchange is performed between the working fluid from the heat radiating unit 13 and the working fluid from the heat absorbing unit 11 toward the compressing unit 12. In the following description, an intermediate heat exchange part having a heat exchange function between them is appropriately referred to as a “second intermediate heat exchange part”.

  In the present embodiment, the second intermediate heat exchanging part 42 is a part of the heat absorbing part 11 (gas phase part) and a part of the conduit of the main path 15 of the heat pump 10 (conduit between the heat radiating part 13 and the intermediate part 40). 26 part) are thermally connected to each other. In the present embodiment, a part of the conduit 26 is disposed in the gas phase region in the internal space of the heat absorbing unit 11. The second intermediate heat exchanging unit 42 may have a countercurrent heat exchange structure in which a high-temperature fluid (working fluid in the conduit 26) and a low-temperature fluid (working fluid in the heat absorption unit 11) face each other. it can. Alternatively, the second intermediate heat exchange unit 42 may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  In the present embodiment, a part of the conduit 26 that fluidly connects the heat radiating unit 13 and the intermediate unit 40 is disposed in both the first intermediate heat exchange unit 41 and the second intermediate heat exchange unit 42. That is, the conduit 26 disposed in the first intermediate heat exchange unit 41 and the conduit 26 disposed in the second intermediate heat exchange unit 42 are fluidly connected. The liquid-phase working fluid from the heat dissipating unit 13 flows through the conduit 26 arranged in the first intermediate heat exchange unit 41 first, and then flows through the conduit 26 arranged in the second intermediate heat exchange unit 42. Further, the working fluid from the second intermediate heat exchange unit 42 is guided to the intermediate unit 40 via the high-pressure expansion valve 24.

  Next, in the intermediate heat exchange unit 43, heat exchange is performed between the working fluid from the intermediate unit 40 and the working fluid from the heat absorption unit 11 toward the compression unit 12. In the following description, an intermediate heat exchange part having a heat exchange function between them is appropriately referred to as a “third intermediate heat exchange part”.

  In the present embodiment, the third intermediate heat exchanging unit 43 includes a part of the endothermic part 11 (gas phase part) and a part of the conduit of the main path 15 of the heat pump 10 (conduit between the intermediate part 40 and the endothermic part 11). 27) are thermally connected to each other. In the present embodiment, a part of the conduit 27 is disposed in the gas phase region in the internal space of the heat absorbing unit 11. The third intermediate heat exchanging unit 43 may have a countercurrent heat exchange structure in which a high-temperature fluid (working fluid in the conduit 27) and a low-temperature fluid (working fluid in the heat absorption unit 11) face each other. it can. Alternatively, the third intermediate heat exchange unit 43 may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  Various heat exchange structures such as a plate-type heat exchange structure and a fin-and-tube heat exchange structure can be applied to the second and third intermediate heat exchange units 42 and 43.

  In the heat pump system S2 having the above configuration, in addition to the first intermediate heat exchange unit 41, two intermediate heat exchange units (a second intermediate heat exchange unit 42 and a third intermediate heat exchange unit 43) are provided, In each of the first, second, and third intermediate heat exchange units 41, 42, 43, the surplus heat of the working fluid is effectively used.

  In the third intermediate heat exchange unit 43, the heat from the working fluid from the intermediate unit 40 having a relatively high temperature is transmitted to the working fluid from the heat absorption unit 11 toward the compression unit 12. Further, in the second intermediate heat exchanging section 42, heat from the heat radiating section 13 having a relatively high temperature (the working fluid from the first intermediate heat exchanging section 41) is transferred to the working fluid from the heat absorbing section 11 toward the compressing section 12. .

  As a result, the working fluid injected between the stages of the compression unit 12 (inlet of the second compression unit 12B) is heated, and the working fluid introduced into the inlet of the compression unit 12 (first compression unit 12A) is heated. Is done. When the temperature of the injected fluid and the introduced fluid (the inlet temperature of the working fluid in the compression unit 12) increases, the output temperature of the working fluid from the compression unit 12 also increases. Therefore, according to the present embodiment, the medium to be heated can be stably heated at a high temperature.

  In the present embodiment, since the heat of the working fluid from the intermediate portion 40 is taken away by the third intermediate heat exchanging portion 43, the input temperature of the working fluid to the low pressure expansion valve 25 and the heat absorbing portion 11 is lowered. As a result, the liquid-gas ratio of the working fluid is optimized, and heat is effectively absorbed from the heat source outside the cycle in the heat absorption unit 11.

  In the present embodiment, the second and third intermediate heat exchange units 42 and 43 heat the gas-phase working fluid inside the heat absorbing unit 11. The fact that the second and third intermediate heat exchange parts 42 and 43 and the heat absorption part 11 are substantially integrated is advantageous in terms of downsizing of the apparatus. Alternatively, the heat absorption part 11 and the second and third intermediate heat exchange parts 42 and 43 can be substantially separated.

  Next, a third embodiment of the present invention will be described with reference to FIG.

  FIG. 3 is a schematic diagram showing a heat pump system S3 according to the third embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 3, in the heat pump system S3, the heat radiating part 13 of the heat pump 10 includes a main heat radiating part 13A and a supplementary heat radiating part 13B.

  In the present embodiment, the main heat radiating portion 13A and the auxiliary heat radiating portion 13B are arranged adjacent to each other. A supplementary heat radiating portion 13B is arranged at a downstream position of the main heat radiating portion 13A. The main heat radiating portion 13A and the auxiliary heat radiating portion 13B are fluidly connected to each other. The working fluid from the main heat radiating part 13A is introduced into the auxiliary heat radiating part 13B.

  The main heat radiating portion 13 </ b> A is thermally connected to the supply unit 20. In the present embodiment, the main heat radiating portion 13A has a region where a gas-phase (or supercritical) working fluid exists and a region where a liquid-phase working fluid exists. The conduit 22A of the supply unit 20 is disposed over both regions of the main heat radiating portion 13A. Alternatively or additionally, the main heat dissipating part 13A may have a spray structure.

  The auxiliary heat radiating portion 13 </ b> B is also thermally connected to the supply unit 20. In this embodiment, it has the area | region where the working fluid of a liquid phase exists. The conduit 22B of the supply unit 20 is disposed in the liquid phase region of the main heat radiating portion 13A.

  In the present embodiment, the main heat radiating portion 13A has a countercurrent heat exchange structure in which a high-temperature fluid (working fluid in the main heat radiating portion 13A) and a low-temperature fluid (heated fluid in the conduit 22A) face each other. Can have. Alternatively, the main heat radiating portion 13A may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel. Similarly, the main heat radiating part 13B can have a countercurrent heat exchange structure or a parallel flow heat exchange structure.

  Along with the heat exchange between the working fluid and the fluid to be heated (water) in the main heat radiating portion 13A, a part of the heat of the working fluid is taken away by the main heat radiating portion 13A. Therefore, the temperature of the working fluid in the auxiliary heat radiating portion 13B is lower than the temperature of the working fluid in the main heat radiating portion 13A.

  In the present embodiment, the conduit 22A and the conduit 22B are fluidly connected to each other. The heated fluid (water) from the source first flows through the conduit 22B and then flows through the conduit 22A. Therefore, the heated fluid is heated (preheated) with relatively low heat in the auxiliary heat radiating portion 13B before being heated with relatively high heat in the main heat radiating portion 13A.

  In the heat pump system S3 configured as described above, the fluid to be heated is heated at a relatively low temperature in the auxiliary heat radiating portion 13B and heated at a relatively high temperature in the main heat radiating portion 13A. Preheating in the auxiliary heat radiating part 13B makes it possible to stably heat the medium to be heated at a high temperature. That is, in the present embodiment, surplus heat of the working fluid is effectively used in each of the first, second, and third intermediate heat exchange units 41, 42, 43, and the auxiliary heat dissipation unit 13B.

  Next, a fourth embodiment of the present invention will be described with reference to FIG.

  FIG. 4 is a schematic diagram showing a heat pump system S4 according to the fourth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 4, in the heat pump system S <b> 4, the heat pump 10 further includes a branch portion 50 in which the working fluid from the main heat radiating portion 13 </ b> A bypasses the auxiliary heat radiating portion 13 </ b> B and heads toward the first intermediate heat exchange portion 41.

  In this embodiment, the branch part 50 is provided between the main heat radiating part 13A and the auxiliary heat radiating part 13B. The first outlet of the branch part 50 is fluidly connected to the auxiliary heat dissipation part 13B. The second outlet of the branch part 50 is fluidly connected to the first intermediate heat exchange part 41 via the conduit 26. A part of the working fluid from the main heat radiating portion 13A flows through the auxiliary heat radiating portion 13B and is then introduced into the heat absorbing portion 11 through the auxiliary low pressure expansion valve 28. The remainder of the working fluid from the main heat radiating unit 13A flows in the order of the first intermediate heat exchange unit 41, the second intermediate heat exchange unit 42, the intermediate unit 40, and the third intermediate heat exchange unit 43, and then the low pressure expansion valve 25. Is introduced into the heat absorption part 11. The branch part 50 can include, for example, a branch pipe and a flow rate control valve that controls each branch flow rate.

  In the heat pump system S4 having the above-described configuration, surplus heat of the working fluid is effectively used in each of the first, second, and third intermediate heat exchange units 41, 42, 43, and the auxiliary heat dissipation unit 13B. Furthermore, according to the present embodiment, the working fluid from the main heat radiating portion 13A is branched through the branching portion 50, so that it is possible to appropriately distribute surplus heat.

  In this embodiment, the structure which controls each branch flow volume based on the output of a predetermined sensor is employable. For example, information related to the amount of heat from the outside supplied to the heat absorbing unit 11 (for example, information related to the temperature and / or flow rate of the heat medium supplied to the heat absorbing unit 11) is sent to the control device 70. The control device 70 drives a flow rate control valve that controls the branch flow rate based on at least the information. The information for heat distribution is not limited to the information from the heat absorption part 11, For example, other information, such as the information regarding the output temperature from the supply unit 20, can be utilized. The control device 70 determines the necessary heat in the auxiliary heat radiating unit 13B and the intermediate heat exchange units (first, second, and third intermediate heat exchange units 41, 42, and 43), and according to each determined necessary heat The flow rate control valve is driven to control the branch flow rate ratio. By heat distribution, the heat balance of the heat pump system S4 can be optimized. In addition, in order to control the heat distribution more finely, it is possible to adopt a configuration in which the flow rate of the working fluid is controlled at a place other than the branch portion 50.

  Here, the thermal efficiency in the above-described system was evaluated. From the numerical calculation, it was confirmed that in the heat pump system S1 shown in FIG. 1, the first intermediate heat exchange unit 41 improves the COP by about 2%. In the heat pump system S2 shown in FIG. 2, it was confirmed that the third intermediate heat exchange unit 43 improves the COP by about 5%. The combination of the first intermediate heat exchange part 41 and the third intermediate heat exchange part 43 improves the COP by about 6%, and further, the first intermediate heat exchange part 41, the second intermediate heat exchange part 42, and the third intermediate heat exchange part 43 It was confirmed that the combination of the heat exchange parts 43 improves COP by about 5%. It was confirmed that the heat pump system S2 shown in FIG. 2 can achieve COP of about 3.4 under predetermined conditions.

  Next, a fifth embodiment of the present invention will be described with reference to FIG.

  FIG. 5 is a schematic diagram showing a heat pump system S5 according to the fifth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 5, in the heat pump system S5, the path 20 in the supply unit 20 is added to the heat pump 10 in addition to the first path (conduit 22A, conduit 22B) thermally connected to the heat radiating portions 13A and 13B of the heat pump 10. The 2nd path | route (conduit 29) connected thermally in the middle of the compression part 12 of this is included.

  In the present embodiment, the fluid to be heated (water) from the supply source flows through the conduit 22 </ b> B, is preheated by the auxiliary heat radiating unit 13 </ b> B, and is then branched by the branching unit 51. The first outlet of the branch portion 51 is fluidly connected to a conduit 22A that is thermally connected to the main heat radiating portion 13A. The second outlet of the bifurcation 51 is fluidly connected to a conduit 29 that is thermally connected to the compressor 12. A part of the heated fluid preheated by the auxiliary heat radiating portion 13B is heated at a relatively high temperature by the main heat radiating portion 13A. The remaining preheated fluid is heated at a relatively high temperature by receiving heat from the working fluid between the stages of the compression unit 12.

  In the heat pump system S5 configured as described above, the working fluid between the stages of the compression unit 12 of the heat pump 10 can be cooled. By suppressing the input temperature of the second compression unit 12B, the compression efficiency of the second compression unit 12B can be improved. That is, as a result of suppressing the temperature rise of the working fluid in the process of compressing the working fluid, the compression efficiency of the compression unit 12 is improved and the power of the compressor is reduced. In addition, the interstage cooling prevents the working fluid flowing through the heat pump 10 from excessively rising in temperature due to compression in addition to the improvement in compression efficiency. By appropriately controlling the heat radiation temperature, the heat transfer efficiency between the heat radiation portion 13 of the heat pump 10 and the heated fluid (water) can be improved. That is, appropriately controlled heat can be supplied to the water.

  Next, a sixth embodiment of the present invention will be described with reference to FIG.

  FIG. 6 is a schematic diagram showing a heat pump system S6 according to the sixth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 6, in the heat pump system S6, the compression unit 12 of the heat pump 10 includes a first compression unit 12A, a second compression unit 12B, a third compression unit 12C, and a fourth compression unit 12D. Have Accordingly, the heat pump 10 includes three high-pressure expansion valves 24A, 24B, 24C, three intermediate portions 40A, 40B, 40C, three first intermediate heat exchange portions 41A, 41B, 41C, and three second intermediate portions. Heat exchange parts 42A, 42B, and 42C are included. The supply unit 20 includes three conduits 29A, 29B, and 29C that are thermally connected to the compression unit 12 of the heat pump 10.

  In the heat pump system S6 configured as described above, the compression unit 12 of the heat pump 10 has a four-stage compression structure, and the output temperature of the fluid to be heated from the supply unit 20 can be improved. Further, the system S6 has various options for changing the route of the working fluid and the fluid to be heated and controlling the flow rate in each route, and can more appropriately distribute surplus heat and improve the heat balance of the entire system. Alternatively, the number of stages of the compression unit 12 is not limited to 2 and 4, and can be other stages.

  Next, a seventh embodiment of the present invention will be described with reference to FIG.

  FIG. 7 is a schematic diagram showing a heat pump system S7 according to the seventh embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 7, in addition to the third intermediate heat exchange unit 43, the heat pump system S <b> 7 provides intermediate heat exchange that gives a part of the heat of the working fluid having a relatively high temperature to the working fluid in the middle of the compression unit 12. Part 44 is provided.

  In the intermediate heat exchange unit 44, heat exchange is performed between the working fluid from the heat radiating unit 13 and the working fluid in the middle of the compression unit 12 (between the first compression unit 12A and the second compression unit 12B). . In the following description, an intermediate heat exchange part having a heat exchange function between them is appropriately referred to as a “fourth intermediate heat exchange part”.

  In the present embodiment, the fourth intermediate heat exchanging unit 44 is a part of the conduit between the interstage part of the compression part 12 and the main path 15 of the heat pump 10 (part of the conduit 60 between the heat radiation part 13 and the intermediate part 40). ) And are thermally connected. The fourth intermediate heat exchange unit 44 may have a countercurrent heat exchange structure or a parallel flow heat exchange structure.

  Various heat exchange structures such as a plate-type heat exchange structure and a fin-and-tube heat exchange structure can be applied to the fourth intermediate heat exchange unit 44.

  In the heat pump system S7 configured as described above, a fourth intermediate heat exchange unit 44 is provided in addition to the third intermediate heat exchange unit 43, and each of the third and fourth intermediate heat exchange units 43 and 44 operates. The surplus heat of the fluid is effectively used.

  In the fourth intermediate heat exchange unit 44, heat from the working fluid from the heat radiating unit 13 having a relatively high temperature is transmitted to the working fluid between the stages of the compression unit 12. Furthermore, in the third intermediate heat exchange unit 43, heat from the working fluid from the intermediate unit 40 having a relatively high temperature is transmitted to the working fluid from the heat absorbing unit 11 toward the compression unit 12.

  As a result, the working fluid injected between the stages of the compression unit 12 (inlet of the second compression unit 12B) is heated, and the working fluid introduced into the inlet of the compression unit 12 (first compression unit 12A) is heated. Is done. When the temperature of the injected fluid and the introduced fluid (the inlet temperature of the working fluid in the compression unit 12) increases, the output temperature of the working fluid from the compression unit 12 also increases. Therefore, according to the present embodiment, the medium to be heated can be stably heated at a high temperature.

  In the present embodiment, in the fourth intermediate heat exchanging unit 44, the heat of the working fluid from the intermediate unit 40 is deprived, so that the input temperature of the working fluid to the low pressure expansion valve 25 and the heat absorbing unit 11 decreases. As a result, the liquid-gas ratio of the working fluid is optimized, and heat is effectively absorbed from the heat source outside the cycle in the heat absorption unit 11. In addition, a configuration including at least one of the first intermediate heat exchange unit and the second intermediate heat exchange unit described above may be employed as necessary.

  Next, an eighth embodiment of the present invention will be described with reference to FIG.

  FIG. 8 is a schematic diagram showing a heat pump system S8 according to the eighth embodiment. In the following description, the same components as those in the above embodiment are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  The heat pump system S8 is a modification of the heat pump system S7 shown in FIG. As shown in FIG. 8, in the heat pump system S8, the heat radiating part 13 of the heat pump 10 includes a main heat radiating part 13A and a supplementary heat radiating part 13B.

  In the present embodiment, the main heat radiating portion 13A and the auxiliary heat radiating portion 13B are arranged adjacent to each other. A supplementary heat radiating portion 13B is arranged at a downstream position of the main heat radiating portion 13A. The main heat radiating portion 13A and the auxiliary heat radiating portion 13B are fluidly connected to each other. The working fluid from the main heat radiating part 13A is introduced into the auxiliary heat radiating part 13B.

  The main heat radiating portion 13 </ b> A is thermally connected to the supply unit 20. In the present embodiment, the main heat radiating portion 13A has a region where a gas-phase (or supercritical) working fluid exists and a region where a liquid-phase working fluid exists. The conduit 22A of the supply unit 20 is disposed over both regions of the main heat radiating portion 13A. Alternatively or additionally, the main heat dissipating part 13A may have a spray structure.

  The auxiliary heat radiating portion 13 </ b> B is also thermally connected to the supply unit 20. In this embodiment, it has the area | region where the working fluid of a liquid phase exists. The conduit 22B of the supply unit 20 is disposed in the liquid phase region of the main heat radiating portion 13A.

  In the present embodiment, the main heat radiating portion 13A has a countercurrent heat exchange structure in which a high-temperature fluid (working fluid in the main heat radiating portion 13A) and a low-temperature fluid (heated fluid in the conduit 22A) face each other. Can have. Alternatively, the main heat radiating portion 13A may have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel. Similarly, the main heat radiating part 13B can have a countercurrent heat exchange structure or a parallel flow heat exchange structure.

  Along with the heat exchange between the working fluid and the fluid to be heated (water) in the main heat radiating portion 13A, a part of the heat of the working fluid is taken away by the main heat radiating portion 13A. Therefore, the temperature of the working fluid in the auxiliary heat radiating portion 13B is lower than the temperature of the working fluid in the main heat radiating portion 13A.

  In the present embodiment, the conduit 22A and the conduit 22B are fluidly connected to each other. The heated fluid (water) from the source first flows through the conduit 22B and then flows through the conduit 22A. Therefore, the heated fluid is heated (preheated) with relatively low heat in the auxiliary heat radiating portion 13B before being heated with relatively high heat in the main heat radiating portion 13A.

  In the heat pump system S8 configured as described above, the fluid to be heated is heated at a relatively low temperature in the auxiliary heat radiating portion 13B, and is heated at a relatively high temperature in the main heat radiating portion 13A. Preheating in the auxiliary heat radiating part 13B makes it possible to stably heat the medium to be heated at a high temperature. That is, in the present embodiment, surplus heat of the working fluid is effectively used in each of the third and fourth intermediate heat exchange units 43 and 44 and the auxiliary heat dissipation unit 13B.

  The numerical value used in the above description is an example, and the present invention is not limited to this.

  The preferred embodiments of the present invention have been described above, but the present invention is not limited to these embodiments. The numerical value used in the above description is an example, and the present invention is not limited to this. Additions, omissions, substitutions, and other modifications can be made without departing from the spirit of the present invention. The present invention is not limited by the above description, but only by the appended claims.

  S1, S2, S3, S4, S5, S6, S7, S8 ... heat pump system, 10 ... heat pump, 11 ... heat absorption part, 12 ... compression part, 12A ... first compression part, 12B ... second compression part, 13 ... heat dissipation , 13A... Main heat radiating part, 13B. ... supplementary low pressure expansion valve (expansion part), 40 ... intermediate part, 41 ... first intermediate heat exchange part, 42 ... second intermediate heat exchange part, 43 ... third intermediate heat exchange part, 44 ... fourth intermediate heat exchange part 50, 51 ... branching unit, 70 ... control device.

Claims (10)

A first unit including a heat pump including a heat pump including a heat absorption unit, a compression unit, a heat dissipation unit, and an expansion unit;
A second unit that includes a path through which the second fluid flows, and that outputs the second fluid that has received heat transferred from the first fluid.
The heat pump
The first fluid from the heat radiating section flows, temporarily stores the liquid-phase first fluid and the gas-phase first fluid, and supplies the gas-phase first fluid to the compression section. The middle part,
Heat from at least one of the first fluid toward the intermediate portion and the first fluid from the intermediate portion is at least one of the first fluid toward the compression portion and the first fluid in the middle of the compression portion An intermediate heat exchange section transmitted to
The intermediate heat exchanging portion transmits a heat from at least a part of the first fluid flowing into the intermediate portion from the heat radiating portion to the first fluid in the gas phase from the intermediate portion toward the compression portion. A high-temperature heat pump system including a heat exchange unit. The heat pump includes an expansion portion that expands the first fluid before the first fluid flows from the heat dissipation portion into the intermediate portion,
The first intermediate heat exchange unit transfers heat from at least a part of the first fluid from the heat radiating unit to the expansion unit to the gas phase first fluid from the intermediate unit to the compression unit.
The high-temperature type heat pump system according to claim 1.   The intermediate heat exchange part further includes a second intermediate heat exchange part in which heat from at least a part of the first fluid from the heat radiating part is transferred from the heat absorption part to the compression part. The high-temperature type heat pump system according to claim 2.   The intermediate heat exchange part is a conduit that is partly disposed in the first intermediate heat exchange part and the second intermediate heat exchange part, from the first intermediate heat exchange part to the second intermediate heat exchange part. The high-temperature heat pump system according to claim 3, further comprising: the conduit through which at least a part of the first fluid from the heat radiating portion flows.   The intermediate heat exchange part further includes a third intermediate heat exchange part in which heat from at least a part of the first fluid from the intermediate part is transferred from the heat absorption part to the compression part. The high temperature type heat pump system according to any one of claims 2 to 4, wherein:   6. The heat radiating portion includes a main heat radiating portion and a supplementary heat radiating portion through which the first fluid from the main heat radiating portion flows and preheats the second fluid. 6. The high-temperature heat pump system according to item.   The heat pump further includes a branching portion in which at least a part of the first fluid from the main heat radiating portion bypasses the auxiliary heat radiating portion and heads toward the intermediate portion or the intermediate heat exchange portion. 6. The high-temperature heat pump system according to 6.   The path in the second unit includes a first path thermally connected to the heat radiating part of the heat pump and a second path thermally connected to the compression part of the heat pump. The high temperature type heat pump system according to any one of claims 1 to 7.   The intermediate heat exchange part further includes a fourth intermediate heat exchange part in which heat from at least a part of the first fluid from the heat radiating part is transferred to the first fluid in the middle of the compression part. The high temperature type heat pump system according to any one of claims 1 to 8.   10. The output temperature of the second fluid from the second unit is 80, 90, 100, 110, 120, 130, 140, or 150 ° C. or more, 10. The high-temperature heat pump system according to item.

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