JP2010117085A - Industrial drying system and drying method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an industrial drying system with high energy efficiency. <P>SOLUTION: The drying system includes a first device (12), a second device (14) and a third device (16). The first device (12) includes a heat pump circuit (20) where a working fluid is made to flow and which has a heat absorbing part (21), a compression part (22), a heat release part (23) and an expansion part (24). The second device (14) includes an evaporation part (42) in which water receiving heat from the working fluid is evaporated and a steam circuit (44) where steam from the evaporation part (42) is made to flow. The third device (16) includes a drying chamber (62) where a drying target is arranged. In the third device (16), heat from the steam is transmitted to at least one of the target and the fluid made to flow toward the target. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an industrial drying system and a drying method.

  As an industrial drying system, a configuration in which an object is dried by burning fuel in a boiler is generally known.

Moreover, there exists a dryer which has the structure which supplies the heating air from an air conditioner to a target object (for example, refer patent document 1).
Japanese Patent No. 3957665

  An object of this invention is to provide the drying system and drying method with high energy efficiency.

  According to an aspect of the present invention, a working fluid flows and a first device having a heat pump circuit having a heat absorbing portion, a compressing portion, a heat radiating portion, and an expanding portion; and water that receives heat from the working fluid evaporates. A second device having an evaporation section and a steam circuit through which steam from the evaporation section flows; and a third device having a drying chamber in which an object to be dried is disposed, wherein heat from the steam is the object And an industrial drying system comprising: the third device that is transmitted to at least one of a fluid flowing toward the object.

  According to another aspect of the present invention, a step of preparing a heat pump circuit through which a working fluid flows, a step of generating steam by transferring heat from the working fluid to water, and an object to dry the heat from the steam And transferring to at least one of the fluids flowing toward the object.

  According to this drying system or drying method, steam is generated using heat from the heat pump, and the object is dried by the heat of the steam. Therefore, the use of steam excellent in heat transfer can improve the thermal efficiency for drying.

  Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic diagram showing a drying system S1 in the first embodiment.

  The drying system S1 includes a heat pump device (first device) 12 having a heat pump (heat pump circuit) 20 through which a working fluid flows, a steam device (second device) 14, and a drying device (third device) for drying an object to be dried. ) 16 and a control device 70. The control device 70 comprehensively controls the entire system. The configuration of the drying system S1 can be variously changed according to design requirements.

  In the present embodiment, the object to be dried is an industrial electrical component. Various objects such as sludge, wood, resin, sand, household waste, industrial waste, paint, industrial clothing, machine parts, and food can be dried.

  In the heat pump device 12, the heat pump 20 is a circuit that transfers heat between a plurality of objects using a change in the state of the working fluid by a cycle composed of steps of evaporation, compression, condensation, and expansion. A heat pump cycle generally has the advantage of being relatively energy efficient.

  In the present embodiment, the heat pump 20 includes a heat absorbing portion 21, a compressing portion 22, a heat radiating portion (a front heat radiating portion 23A, a rear heat radiating portion (heating heat radiating portion) 23Z) 23, and an expansion portion 24. Connected through.

  In the heat absorption part 21, the working fluid flowing in the main path 25 absorbs the heat of the heat source outside the cycle. In the present embodiment, the heat absorption part 21 of the heat pump 20 can absorb the heat of the discharged fluid from the drying device 16 that is discharged along with the drying process.

  In the present embodiment, the heat pump device 12 further includes an exhaust heat recovery unit 29 that pumps at least part of the exhaust heat from the drying device 16 by the heat absorption unit 21 of the heat pump 20. The exhaust heat recovery unit 29 includes a conduit 291 through which the thermal fluid flows, a heat absorption unit 293 through which heat exhausted from the drying device 16 (for example, heat of the exhaust fluid) is transmitted to the thermal fluid, and heat from the thermal fluid in the conduit 291. And a heat radiating portion 295 transmitted to the heat absorbing portion 21 of the heat pump 20. The exhaust heat recovery unit 29 can further include a fluid drive unit such as a pump and a flow rate control unit (not shown) such as a valve, if necessary. The heat absorption part 21 of the heat pump 20 can absorb the heat discharged from the drying device 16 during the drying process. Alternatively, or in addition, the heat absorption unit 21 of the heat pump 20 may be configured to absorb the heat of a heat source (for example, air or a cold heat supply device) other than the fluid discharged from the drying device 16.

  The compression unit 22 compresses the working fluid by a compressor or the like. At this time, the temperature of the working fluid usually increases. In this embodiment, the compression part 22 can have a single stage compression structure or a multistage compression structure. 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 the working fluid is applied. Power is supplied to the compressor. In the compression unit 22 having a multistage compression structure, a multiaxial compression structure or a coaxial compression structure can be applied.

  The heat dissipating part (the front heat dissipating part 23A and the rear heat dissipating part 23Z) 23 has a conduit through which the working fluid compressed by the compressing part 22 flows, and gives the heat of the working fluid flowing in the main path 25 to an object outside the cycle. At least a part of the working fluid flowing through the heat dissipating unit 23 can be in a gas region or a supercritical region. In the present embodiment, the front heat radiating portion 23A and the rear heat radiating portion 23Z are arranged in that order along the flow direction of the working fluid. The number of heat radiation units is set according to the specification of the drying system S1, and is 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more. The front heat radiating portion 23A is disposed at a position downstream of the compression portion 22, and the rear heat radiating portion 23Z is disposed at a position downstream of the front heat radiating portion 23A. Each heat radiating part 23A, 23Z is thermally connected to the steam device 14.

  The expansion unit 24 expands the working fluid by a pressure reducing valve, a turbine, or the like. When a turbine is used, power can be taken out from the expansion unit 24, and the power may be supplied to the compression unit 22, for example. As a working fluid used for the heat pump 20, various known heat media such as a chlorofluorocarbon medium (HFC 245fa, etc.), ammonia, water, carbon dioxide, air, etc. are selected according to the specifications and heat balance of the drying system S1. Is done.

  In the present embodiment, the heat pump 20 further includes a bypass path 27 and a regenerator 28. The inlet end of the bypass path 27 is fluidly connected to a conduit between the front heat dissipating part 23A and the rear heat dissipating part 23Z in the main path 25 of the heat pump 20. The outlet end of the bypass path 27 is fluidly connected to a pipe between the rear heat radiating part 23Z and the expansion part 24 in the main path 25. A flow rate control valve for controlling the bypass flow rate of the working fluid can be provided at the inlet of the bypass passage 27. In the bypass path 27, a part of the working fluid from the front heat radiating portion 23A bypasses the rear heat radiating portion 23Z and joins the working fluid from the rear heat radiating portion 23Z before the expansion portion 24. The remaining working fluid from the front heat radiating portion 23A flows through the rear heat radiating portion 23Z.

  The regenerator 28 has a configuration in which a part of the conduit of the bypass path 27 and a part of the conduit of the main path 25 of the heat pump 20 (the conduit between the heat absorption part 21 and the compression part 22) are thermally connected. Have. For example, both conduits are placed in contact with or adjacent to each other. In the heat pump 20, the working fluid from the front heat radiating unit 23 </ b> A is hotter than the working fluid from the heat absorbing unit 21. In the regenerator 28, the working fluid from the front heat radiating section 23 </ b> A flowing through the bypass path 27 and the working fluid from the heat absorbing section 21 flowing through the main path 25 of the heat pump 20 exchange heat. By this heat exchange, the temperature of the working fluid in the bypass path 27 is lowered, and the temperature of the working fluid in the main path 25 is raised. The regenerator 28 can have a countercurrent heat exchange structure in which a low-temperature fluid (working fluid in the main passage 25) and a high-temperature fluid (working fluid in the bypass passage 27) flow in opposition. Alternatively, the regenerator 28 can have a parallel flow type heat exchange structure in which a high-temperature fluid and a low-temperature fluid flow in parallel.

  As shown in FIG. 1, the steam device 14 includes a heating unit 40, an evaporation unit 42, a steam circuit 44, a fluid drive unit (not shown) such as a pump as necessary, a valve and the like as necessary. A flow rate control unit (not shown).

  The heating unit 40 includes a conduit that is thermally connected to the rear heat dissipation unit 23Z of the heat pump 20 and through which water from a supply source (not shown) flows. A heat exchanger 110 (a warmer, a heat exchange device) is configured including the heating unit 40 and the rear heat dissipation unit 23Z. That is, the heat exchanger 110 has a structure in which a part of the conduit of the steam device 14 (heating unit 40) and a part of the conduit of the main path 25 of the heat pump 20 (rear heat radiating unit 23Z) are thermally connected. Have The heat exchanger 110 may have a countercurrent heat exchange system in which a low-temperature fluid (water in the steam device 14) and a high-temperature fluid (working fluid in the heat pump 20) flow in opposition. Alternatively, the heat exchanger 110 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures for the heat exchanger 110 can be employed. The conduit of the heating unit 40 and the conduit of the rear heat radiating unit 23Z are arranged in contact with or adjacent to each other. For example, the conduit of the rear heat radiating portion 23Z can be disposed around or inside the conduit of the warming portion 40. In the heating unit 40, the temperature of the water in the conduit rises due to the heat transferred from the rear heat radiating unit 23Z of the heat pump 20.

  The evaporation unit 42 may have at least one of a drum type, an evaporation type, a boiling type, and an evaporation + boiling type. In the present embodiment, the evaporation unit 42 includes a tank (drum, steam generation unit) 420 that stores at least a liquid fluid to be heated (water), and a circulation conduit 422 that is fluidly connected to the tank 420. A deaeration tank (not shown) and a fluid drive unit (not shown) such as a pump are disposed between the heating unit 40 and the tank 420 as necessary. The tank 420 can include a level sensor 424 that measures the liquid level and a gas-liquid separator (not shown) as necessary.

  The tank 420 or the circulation conduit 422 is provided with a water supply port from the heating unit 40 and a steam discharge port. The inlet end and the outlet end of the circulation conduit 422 are each connected to the tank 420. The circulation conduit 422 includes a heated pipe 426 that is thermally connected to the front heat radiating portion 23 </ b> A of the heat pump 20, and, if necessary, a pump (not shown) and a valve (not shown). The pump can be omitted by utilizing the heat convection of the fluid to be heated (water) and / or the differential pressure with the outside.

  A heat exchanger 112 (heat exchange device) is configured including the heated tube 426 and the front heat radiating portion 23A. That is, in the heat exchanger 112, the front heat radiating part 23A of the heat pump 20 and the heated pipe 426 of the evaporation part 42 are thermally connected. Heat from the working fluid flowing through the front heat radiating portion 23 </ b> A is transferred to the water flowing through the heated pipe 426. The heat exchanger 112 can have a countercurrent heat exchange system in which a low-temperature fluid (water in the heated pipe 426) and a high-temperature fluid (working fluid in the heat pump 20) flow in opposition. Alternatively, the heat exchanger 112 may have a parallel flow type heat exchange method in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures of the heat exchanger 112 can be employed. The conduit of the front heat radiating portion 23A of the heat pump 20 and the heated tube 426 are arranged in contact with or adjacent to each other. For example, the conduit of the front heat radiating portion 23 </ b> A of the heat pump 20 can be disposed around or inside the heated tube 426.

  In the evaporation unit 42, the water whose temperature has increased in the heating unit 40 is supplied to the tank 420 through the supply port, and water is stored in the tank 420 and the circulation conduit 422. The amount of water supplied to the tank 420 is controlled so that the liquid level in the tank 420 is within a predetermined range. For example, the amount of water supplied to the tank 420 is controlled based on the measurement result of the level sensor. At least a part of the water in the heated pipe 426 that has received heat from the working fluid flowing through the front heat radiating portion 23A of the heat pump 20 evaporates. The steam from the evaporator 42 flows through the steam circuit 44.

  The steam circuit 44 includes a compression unit 440 and a path 442 through which steam flows. In the present embodiment, the compression unit 440 is fluidly connected to the tank 420 of the evaporation unit 42. The internal space of the tank 420 is sucked by the compression unit 440 through the discharge port of the tank 420 and the duct 425.

  In the present embodiment, the compression unit 440 of the steam circuit 44 has a three-stage compression structure including a first compression unit 440A, a second compression unit 440B, and a third compression unit 440C. The compression unit 440 may have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 440A to 440C are individually controlled. Alternatively, the compression unit 440 can have a coaxial compression structure. In the present embodiment, the compression unit 440 has a coaxial structure with respect to the compression units 440A-440C. As the compressors 440A to 440C, various compressors such as an axial compressor, a centrifugal compressor, a reciprocating compressor, and a rotary compressor are applied, and those suitable for vapor compression are used. The first compression unit 440A compresses the vapor from the tank 420 of the evaporation unit 42. The second compression unit 440B compresses the steam from the first compression unit 440A, and the third compression unit 440C compresses the steam from the second compression unit 440B. The compression ratio (pressure ratio) of each compression part 440A-440C can be set according to the specification of drying system S1. The number of stages of the compression unit is set according to the specification of the drying system S1, and is 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more.

  In the present embodiment, the path 442 of the steam circuit 44 includes auxiliary paths 442A, 442B, 442C, and 442D. A part of the vapor from the tank 420 of the evaporation part 42 flows through the first auxiliary path 442A, and the remaining part enters the first compression part 440A. A part of the compressed steam from the first compression part 440A flows through the second auxiliary path 442B, and the remaining part enters the second compression part 440B. Part of the compressed steam from the second compression unit 440B enters the third compression unit 440C, and the remaining part flows through the third auxiliary path 442C. The compressed steam from the third compression section 440C flows through the fourth auxiliary path 442D. A control valve and a flow control valve can be disposed at each branch position of the path 442. The steam branching ratio at each branching position can be set according to the specifications of the drying system S1.

  In the present embodiment, the path 442 of the steam circuit 44 further includes heat radiation portions 444A, 444B, 444C, and 444D that are thermally connected to the drying device 16. The heat radiating units 444A to 444D have a conduit through which the steam from the tank 420 of the evaporation unit 42 or the steam compressed by the compression units 440A to 440C flows, and gives heat of the steam to an external object. The first heat dissipating part 444A, the second heat dissipating part 444B, the third heat dissipating part 444C, and the fourth heat dissipating part 444D are respectively a first auxiliary path 442A, a second auxiliary path 442B, a third auxiliary path 442C, and a fourth auxiliary path. Part of 442D.

  In the present embodiment, the first heat radiating portion 444 </ b> A is disposed at an upstream position in the drying device 16. A first heat radiating portion 444A, a second heat radiating portion 444B, a third heat radiating portion 444C, and a fourth heat radiating portion 444D are arranged in that order along the flow direction of the drying device 16. The number of heat radiating units is set according to the specification of the drying system S1, and can be 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more.

  In the present embodiment, the first heat radiating part 444A (first auxiliary path 442A), the second heat radiating part 444B (second auxiliary path 442B), the third heat radiating part 444C (third auxiliary path 442C), and the fourth heat radiating part 444D. Steam having different temperatures (saturation temperatures) flows through the (fourth auxiliary path 442D). The temperature of the steam flowing through the first heat radiation part 444A is relatively low, and the temperature of the steam flowing through the fourth heat radiation part 444D is relatively high. The temperature of the steam is higher in the order of the fourth heat radiating portion 444D, the third heat radiating portion 444C, the second heat radiating portion 444B, and the first heat radiating portion 444A according to the number of compression stages. That is, in the path 442 of the steam circuit 44, relatively low temperature steam is supplied to the relatively upstream side in the flow direction of the drying device 16, and relatively high temperature steam is supplied to the relatively downstream side in the flow direction.

  Heat from at least one of the steam flowing through the heat radiating units 444A-444D and the condensed liquid thereof is transmitted to the object in the drying device 16, and at least a part of the steam flowing through the heat radiating units 444A-444D is liquefied. In the present embodiment, the downstream end of the auxiliary path 442A-442D is fluidly connected to the tank 420. Vapor and liquid from the heat radiation portions 444A-444D enter the tank 420. In the auxiliary path 442A-442D, a fluid control valve (pressure reducing valve) or the like can be disposed between the heat radiating portion 444A-444D and the tank 420.

  In the compression units 440A-440C, nozzles 448A, 448B, 448C for supplying water (hot water) to the steam are arranged as necessary. The arrangement positions of the nozzles 448A to 448C are, for example, the interstages, the inlets, and / or the outlets of the compression units 440A to 440B. A piping configuration in which the nozzles 448A to 448C and the liquid phase position of the tank 420 of the evaporation unit 42 are fluidly connected via a conduit 446 can be employed. In this piping configuration, the liquid in the tank 420 is effectively used for supply to the nozzles 448A-448C. For discharging (spraying) the liquid from the nozzles 448A to 448C, a power source such as a pump may be used, or a pressure difference between the inlet and the outlet of the conduit may be used.

  Due to the suction action by the compression unit 440, the internal space at the portion heated by the heat pump 20 in the evaporation unit 42, that is, the internal space of the tank 420 is decompressed. For example, the control valve (flow rate control valve) on the path 442 (complementary path 442A-442D) is set so that the internal pressure of the tank 420 becomes a negative pressure (negative pressure) lower than the atmospheric pressure (1 atm = about 0.1 MPa). , Etc. (not shown), the compression unit 440 and the like are controlled. This control can be performed based on the measurement result of a sensor (not shown) that measures the internal pressure of the tank 420, for example.

  In the present embodiment, the drying device 16 includes a fluid heating unit 61, a drying chamber 62, a fluid discharge unit 63, and a transfer device (not shown). In one example, the transfer device can have various forms such as a conveyor, a transport vehicle, and a transport robot. The object to be dried is put into the drying chamber 62 and taken out from the drying chamber 62 by the transfer device. Alternatively or additionally, the drying device 16 may include an output unit having a gate type, a swivel type, or the like for outputting an object after drying. The output unit of the dried object can have a mechanism for performing a predetermined process such as a chemical process on the dried object as necessary.

  In the present embodiment, the transfer device can move the object to be dried in the drying chamber 62 as necessary. The drying device 16 further includes a dehydrating device (not shown) as necessary, thereby dehydrating the object. During the dehydration, a flocculant can be added to the object as necessary. Various forms such as a centrifugal type, a pressure type, a pressure type, and a vibration type can be applied to the dehydration depending on the object. Dehydration reduces the volume of the object. Moreover, the drying apparatus 16 can further have a preheating chamber for applying heat to the object before entering the drying chamber 62 as necessary.

  In the present embodiment, the drying device 16 has a general cylindrical shape, and the air flows inside along the axial direction as a whole. In the present embodiment, the fluid heating unit 61, the drying chamber 62, and the fluid discharge unit 63 are arranged in that order along the overall air flow direction (hereinafter referred to as the flow direction). Alternatively or additionally, the drying device 16 can take a variety of forms.

  In the present embodiment, the heat radiating portions 444 </ b> A to 444 </ b> D of the steam circuit 44 are arranged in the fluid heating portion 61. As described above, the temperature of the steam is higher in the order of the fourth heat radiating portion 444D, the third heat radiating portion 444C, the second heat radiating portion 444B, and the first heat radiating portion 444A. The air that has flowed into the fluid heating unit 61 of the drying device 16 is sequentially heated by the first heat radiating unit 444A, the second heat radiating unit 444B, the third heat radiating unit 444C, and the fourth heat radiating unit 444D.

  An object to be dried is placed in the drying chamber 62. In the present embodiment, the object in the drying chamber 62 is dried by the heated air. Air (exhaust gas etc.) from the drying chamber 62 is discharged to the outside via the fluid discharge portion 63.

  In the present embodiment, the fluid discharge unit 63 is provided with a heat absorption unit 293 of the exhaust heat recovery unit 29 in the heat pump device 12. At least part of the heat of the air from the drying chamber 62 is supplied to the heat absorption unit 293 of the exhaust heat recovery unit 29.

  The fluid discharge part 63 can have a countercurrent heat exchange system in which a low-temperature fluid (working fluid in the heat absorption part 293) and a high-temperature fluid (discharged fluid in the fluid discharge part 63) face each other. . Alternatively, the fluid discharge unit 63 may have a parallel flow type heat exchange method in which a high-temperature fluid and a low-temperature fluid flow in parallel. The fluid discharge unit 63 may employ various known ones as a heat exchange structure. Thereby, the heat pump 20 can collect the exhaust heat of the drying device 16. By recovering the exhaust heat, the overall heat utilization of the drying system S1 can be improved. Most of the fluid flowing through the fluid discharge portion 63 is obtained by evaporating moisture in the drying chamber 62 and has latent heat of evaporation. At least a part of the latent heat of evaporation can be recovered by the heat absorption part 293. When the latent heat is recovered, at least a part of the discharged fluid is condensed.

  Next, an example of the drying process of the drying system S1 will be described.

  As shown in FIG. 1, first, steam is generated in the evaporation section 42 of the steam device 14 by heat transfer from the heat pump 20. That is, in the heating unit 40 of the evaporation unit 42, the water from the supply source is heated by the heat transmitted from the rear heat radiating unit 23Z of the heat pump 20. In one example, the water inlet temperature to the heating unit 40 is about 20 ° C., and the water outlet temperature from the heating unit 40 is about 60 ° C. The above numerical value is an example, and the present invention is not limited to this. The heated water from the heating unit 40 is put into the tank 420. The inside of the tank 420 is under a negative pressure due to the suction action by the compression unit 440 and is substantially under a saturation pressure with respect to the water temperature. In response to heat transmitted from the front heat radiating portion 23A of the heat pump 20, the water in the tank 420 changes phase and evaporates.

  The steam from the tank 420 flows in the steam circuit 44 and becomes steam at a relatively high pressure and high temperature by compression by the compression unit 440. That is, the water heated by the heat pump 20 is further heated by the compression in the compression unit 440. In one example, the temperatures of the steam in the first heat radiating part 444A, the second heat radiating part 444B, the third heat radiating part 444C, and the fourth heat radiating part 444D are about 60 ° C., 77 ° C., 97 ° C., and 130 ° C., respectively. . The air flowing into the fluid heating unit 61 of the drying device 16 is sequentially heated by the first heat radiating unit 444A, the second heat radiating unit 444B, the third heat radiating unit 444C, and the fourth heat radiating unit 444D, and then flows into the drying chamber 62. To do. For example, the temperature of the air flowing into the drying chamber 62 is about 120 ° C. In the drying chamber 62, the temperature of the object increases due to heat from the air, and the liquid component contained in the object evaporates. The above numerical value is an example, and the present invention is not limited to this.

  As described above, in the present embodiment, drying is performed using the steam generated using the heat of the heat pump 20. The use of steam excellent in heat transfer can improve the thermal efficiency for drying. Further, by using steam, a drying process in a relatively high temperature region can be performed.

  The energy efficiency of the boiler is generally about 0.7 to 0.8 (70 to 80%), whereas the coefficient of performance (COP) as the energy efficiency of the heat pump is generally 2.5 to 5. 0. The coefficient of performance of the heat pump changes according to the input / output temperature difference of the medium to be heated, and the coefficient of performance tends to decrease at a relatively high input / output temperature difference. In the present embodiment, the heat pump 20 has individual heating parts (rear heat radiating part 23Z and front heat radiating part 23A) corresponding to sensible heat exchange and latent heat exchange, thereby suppressing the temperature difference between the input and output and higher than that of the boiler. Steam can be generated with energy efficiency. For example, when the COP is 3.0, if the power generation efficiency is 40%, heat of 120% of the primary energy can be generated, exceeding 90% in the conventional boiler. This is advantageous for energy saving. The above numerical value is an example, and the present invention is not limited to this.

  In the present embodiment, heat from at least one of the steam flowing through the steam circuit 44 and its condensate is transferred to an object (air) in the drying device 16, and at least a part of the steam in the steam circuit 44 is liquefied. That is, the drying process is performed using the latent heat of steam. This is advantageous for making the drying system S1 more compact and more efficient than a system using silicon oil or compressed water as a heat medium.

  In the present embodiment, the compression unit 440 of the steam circuit 44 has a three-stage compression structure, and the air is relatively cool on the upstream side in the flow direction of the drying device 16, and the air is a relatively low-temperature heat dissipation unit (such as the first heat dissipation unit 444A). Heat exchange is performed, and the air exchanges heat with a relatively high temperature heat radiating section (such as the fourth heat radiating section 444D) on the relatively downstream side. This is advantageous for improving the thermal efficiency.

  FIG. 2 is a schematic diagram illustrating an example of a temperature change of the steam in the steam circuit and the air in the drying apparatus in the present embodiment.

  As shown in FIG. 2, in the vicinity of the inlet of the fluid heating unit 61 (see FIG. 1) of the drying device 16, the air rises in temperature by receiving heat from the first heat radiating unit 444A through which relatively low-temperature steam flows (FIG. 2). Arrow m1). At this time, with the release of latent heat, at least a part of the vapor is liquefied in the first heat dissipating part 444A (arrow n1). The air heated by the first heat radiating part 444A then receives heat from the second heat radiating part 444B and rises in temperature (arrow m2). At this time, with the release of latent heat, at least a part of the vapor is liquefied in the second heat radiating portion 444B (arrow n2). The heat radiation temperature is higher in the order of the fourth heat radiation part 444D, the third heat radiation part 444C, the second heat radiation part 444B, and the first heat radiation part 444A. Thereafter, the air receives heat from the third heat radiating portion 444C and the fourth heat radiating portion 444D in order and rises in temperature (arrows m3 and m4). Further, at least part of the vapor is liquefied in the third heat radiating part 444C and the fourth heat radiating part 444D (arrows n3 and n4). The temperature of the air rises by the first to fourth heat radiation portions 444A-444D (FIG. 1).

  Returning to FIG. 1, in this embodiment, in this embodiment, the heat radiation temperature distribution of the steam circuit 44 in the fluid heating unit 61 of the drying device 16 has an overall gradient along the flow direction. Therefore, gradient heating is realized in which the temperature difference between the steam in the steam circuit 44 and the air in the drying device 16 is suppressed, which contributes to improvement in heat exchange efficiency. In the present embodiment, the steam circuit 44 includes heat radiation portions 444A-444D (complementary paths 442A-442D) through which a plurality of steams having different temperatures (saturation temperatures) flow, and this is a gradient using the latent heat of steam. It is preferably applied to heating.

  In the present embodiment, the compression unit 440 of the vapor circuit 44 fluidly connected to the tank 420 of the evaporation unit 42 has a multi-stage configuration, and as a result, a mode that realizes gradient heating to the air of the drying device 16 is realized. Provided.

  FIG. 3 is a Ts diagram illustrating an example of a state change of water in the evaporation section 42 and the first compression section 440A of the steam circuit 44 illustrated in FIG. As shown in FIG. 3, the temperature of the water rises to near the boiling point in the heating unit 40 (see FIG. 1) of the evaporation unit 42, and then changes in phase while keeping the temperature constant in the tank 420 (FIG. 1) of the evaporation unit 42. . At this time, saturated steam d0 is generated in a state of negative pressure P0 that is lower than atmospheric pressure (P1 = 1 atm = about 0.1 MPa). The temperature of the saturated vapor d0 is lower than the normal boiling point, for example, about 60 ° C.

  Next, the saturated steam d0 at about 60 ° C. from the tank 420 rises in temperature due to compression in the first compression section 440A (see FIG. 1) of the steam circuit 44, and relatively high pressure and high temperature steam (superheated steam e1). )become. By cooling the superheated steam e1 under a constant pressure, a saturated steam of about 77 ° C. can be obtained (dashed line a in FIG. 3). The above numerical value is an example, and the present invention is not limited to this.

  By directly mixing liquid water or hot water into the cooling from superheated steam to saturated steam, the volume of steam is increased. As shown in FIG. 1, in this embodiment, a nozzle 448A is disposed between the first compression unit 440A and the second compression unit 440B (or near the outlet of the first compression unit 440A), and the nozzle 448A is a conduit. It is fluidly connected to the liquid phase position of the tank 420 of the evaporating unit 42 via 446. The liquid in the tank 420 of the evaporation unit 42 is supplied to the superheated steam from the first compression unit 440A through the nozzle 448A.

  Alternatively or additionally, the nozzle 448A can be fluidly connected to the steam circuit 44. As the liquid supplied to the nozzle 448 </ b> A, the liquid (drain) discharged from the heat radiating part (first to fourth heat radiating parts 444 </ b> A to 444 </ b> D) can be used. The liquid from the heat dissipating part (444A-444D) can have a high temperature and is effective for volume increase by water spray. In particular, the liquid discharged from the heat dissipation part 444D can have a relatively high temperature.

  Alternatively, in FIG. 3, the change from relatively low pressure and low temperature saturated steam to relatively high pressure and high temperature saturated steam can be made more direct by optimizing the supply and timing of water or hot water. Can be. For example, when an appropriate amount of water or hot water is supplied to the steam at the inlet of the first compression unit 440A (FIG. 1), the saturated steam d0 at the inlet of the first compression unit 440A becomes the outlet of the first compression unit 440A. It changes to saturated steam d1 (broken lines c1 (spray) and c2 (compression) in FIG. 3). Alternatively, when an appropriate amount of water or hot water is supplied to the steam in the middle of the first compression section 440A, the saturated steam d0 at the inlet of the first compression section 440A becomes the saturated steam d1 at the outlet of the first compression section 440A. It changes (broken line b in FIG. 3).

  Returning to FIG. 1, in one example, similarly, the superheated steam from the second compression section 440B is cooled by the liquid from the nozzle 448B, and as a result, saturated steam at about 97 ° C. is obtained. Also, the superheated steam from the third compression unit 440C is cooled by the liquid from the nozzle 448C, and as a result, saturated steam at about 130 ° C. is obtained. Alternatively or additionally, nozzle 448B and / or nozzle 448C may be fluidly connected to steam circuit 44. As the liquid supplied to the nozzle 448B and / or the nozzle 448C, the liquid (drain) that has exited from the heat radiating section (first to fourth heat radiating sections 444A to 444D) can be used. The above numerical value is an example, and the present invention is not limited to this.

  FIG. 4 shows an example of a form in which hot water from the steam circuit 44 is mixed into steam from the compression unit (440A-440C). In FIG. 4, the conduit through which the fluid exiting the fourth heat radiating portion 444D of the steam circuit 44 flows includes a conduit 446A that fluidly connects the fourth heat radiating portion 444D and the tank 420, and a branch conduit 446B branched from the conduit 446A. And have. At least a part of the fluid exiting the fourth heat radiating portion 444D can flow through the branch conduit 446B. A nozzle 448A is disposed between the first compression section 440A and the second compression section 440B (or in the vicinity of the outlet of the first compression section 440A), and the nozzle 448A is fluidly connected to the branch conduit 446B. Similarly, a nozzle 448B is disposed between the second compression unit 440B and the third compression unit 440C (or in the vicinity of the outlet of the second compression unit 440B), and the nozzle 448B is fluidly connected to the branch conduit 446B. Yes. A nozzle 448C is disposed near the outlet of the third compression section 440C, and the nozzle 448C is fluidly connected to the branch conduit 446B. A power source such as a pump and a valve such as a flow control valve are arranged as necessary. A fluid having a relatively high temperature from the fourth heat radiating unit 444D is supplied to the vapor from the first compression unit 440A through the nozzle 448A. Similarly, the fluid from the fourth heat radiating unit 444D is supplied to the steam from the second compression unit 440B and the third compression unit 444C via the nozzle 448B and the nozzle 444C, respectively. Alternatively or additionally, a configuration may be applied in which fluid from at least one of the other heat dissipation portions 444A-444C of the vapor circuit 44 is mixed into the vapor from at least one of the compression portions (440A-440C).

  Returning to FIG. 1, in the present embodiment, the pressure of the heat medium in the heat radiating section (first to fourth heat radiating sections 444A to 444D) disposed in the drying device 16 can be set to be relatively low by using steam. . On the other hand, in the system in which the heat of the working fluid of the heat pump 20 is directly applied to the object in the drying device 16, the pressure of the working fluid may be about several tens of atmospheres. In this embodiment, the piping cost can be reduced.

  In the present embodiment, the steam (liquefied component and steam) in each auxiliary path 442A-442D in the steam circuit 44 returns to the tank 420. Therefore, the steam circuit 44 can perform a circulating operation. During the implementation of the circulating operation, the supply of water from the supply source to the tank 420 can be reduced or eliminated. By using the heat supplied to the heating unit 40 (heat of the heat radiating unit 23Z of the heat pump 20) in other parts of the system, further improvement in thermal efficiency can be achieved.

  Alternatively or additionally, at least a portion of the fluid from the first to fourth heat radiating portions 444A to 444D (auxiliary path 442A to 442D) toward the tank 420 can be heated as necessary. For example, the fluid from the first heat radiation part 444A having a relatively low temperature can be heated. For heating the return fluid from the vapor circuit 44 to the evaporation unit 42 (tank 420), for example, heating in the heating unit 40 can be used. By heating the return fluid, the temperature in the tank 420 is more appropriately maintained.

  FIG. 5 shows an example of a mode in which the return fluid is heated. In FIG. 5, the conduit for fluid from the first heat radiating portion 444A of the steam circuit 444A has a conduit 446E that fluidly connects the outlet portion of the first heat radiating portion 444A to the vicinity of the inlet of the heating portion 40. A power source such as a pump and a valve such as a flow control valve are arranged as necessary. In general, the fluid exiting from the first heat radiating portion 444A has a lower temperature than that of the other heat radiating portions 444B-444D. The return fluid from the first heat radiating unit 444A flows through the heating unit 40 via the conduit 446E, and the temperature rises due to the heat transferred from the rear heat radiating unit 23Z of the heat pump 20 in the heating unit 40, and then enters the tank 420. In FIG. 5, all of the fluid from the first heat radiating unit 444 </ b> A flows through the heating unit 40 and is heated. Alternatively, a form in which a part from the first heat radiation unit 444A flows through the heating unit 40 may be employed. Alternatively or additionally, a form in which at least a part of the fluid from the other heat radiation units 444B to 444D of the steam circuit 44 flows through the heating unit 40 and is heated may be employed.

  Returning to FIG. 1, in the present embodiment, the heat pump device 12 (20) recovers the exhaust heat of the drying device 16. This is also advantageous for improving thermal efficiency.

  In the present embodiment, in the heat pump 20, since a part of the working fluid bypasses the heat radiating portion 23Z via the bypass path 27, the flow rate of the working fluid entering the heat radiating portion 23Z is optimized. This is advantageous in appropriately controlling the heat radiation temperature with respect to the heating unit 40 and effectively using the retained heat of the working fluid.

  In the present embodiment, the working fluid flowing through the bypass path 27 exchanges heat with the working fluid from the heat absorbing portion 21 flowing through the main path 25 of the heat pump 20 in the regenerator 28. By this heat exchange, the temperature of the working fluid in the bypass path 27 is lowered, and the temperature of the working fluid in the main path 25 of the heat pump 20 is raised. Due to the increase in the initial input temperature of the working fluid to the compression unit 22, the power of the compression unit 22 is reduced. The bypass amount of the working fluid is determined according to the drying conditions such as the type and amount of the object to be dried.

  In the present embodiment, in the heat pump 20, the working fluid in the bypass path 27 whose temperature has dropped in the regenerator 28 joins the working fluid from the heat radiating section 23 </ b> Z flowing through the main path 25 of the heat pump 20 before the expansion section 24. . The output temperature of the working fluid from the heat radiating portion 23Z is set to be relatively low. The liquid gas ratio of the working fluid is optimized by lowering the input temperature of the working fluid to the expansion unit 24. As a result, the heat absorption unit 21 effectively absorbs heat from the heat source (exhaust fluid) outside the cycle.

  FIG. 6 is a schematic diagram showing a drying system S2 in the second embodiment. In the following description, for the drying system S2, the same elements as those in the drying system S1 shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 6, in the drying system S <b> 2 in the present embodiment, a part of the heat radiation part of the steam circuit 44 is disposed in the drying chamber 62 of the drying device 16.

  Specifically, the steam circuit 44 includes first to fourth heat radiating portions 444A to 444D through which steam having different temperatures (saturation temperatures) flow, and the first to third heat radiating portions 444A to 444C are provided for the drying device 16. Arranged in the fluid heating unit 61, the fourth heat radiating unit 444 </ b> D is arranged in the drying chamber 62 of the drying device 16. The temperature of the steam is higher in the order of the fourth heat radiation part 444D, the third heat radiation part 444C, the second heat radiation part 444B, and the first heat radiation part 444A. Alternatively, the heat radiation temperature of the third heat radiation part 444C can be higher than the heat radiation temperature of the fourth heat radiation part 444D, and the heat radiation temperature of the third heat radiation part 444C and the fourth heat radiation part 444D can be made substantially the same. Also in the present embodiment, in the path 442 of the steam circuit 44, relatively low temperature steam is supplied to the relatively upstream side in the flow direction of the drying device 16, and relatively downstream in the flow direction (the drying chamber 62 and the fluid heating unit). A relatively high temperature steam is supplied to the downstream portion of 61.

In the present embodiment, the air flowing into the fluid heating unit 61 of the drying device 16 is sequentially heated by the first heat radiating unit 444A, the second heat radiating unit 444B, and the third heat radiating unit 444C, and then flows into the drying chamber 62. . In the drying chamber 62, the temperature of the object increases due to the heat of the heated air from the fluid heating unit 61 and the heat from the fourth heat radiating unit 444D, and the liquid component contained in the object evaporates. The temperature of the air rises by the first to third heat radiation parts 444A-444C
The object is dried by the fourth heat radiating portion 444D.

  Also in the present embodiment, the steam (liquefied component and steam) in each auxiliary path 442A-442D in the steam circuit 44 returns to the tank 420. Therefore, the steam circuit 44 can perform a circulating operation. During the implementation of the circulating operation, the supply of water from the supply source to the tank 420 can be reduced or eliminated. By using the heat supplied to the heating unit 40 (heat of the heat radiating unit 23Z of the heat pump 20) in other parts of the system, further improvement in thermal efficiency can be achieved. Alternatively or additionally, at least a portion of the fluid from the first to fourth heat radiating portions 444A to 444D (auxiliary path 442A to 442D) toward the tank 420 can be heated as necessary. For example, the fluid from the first heat radiation part 444A having a relatively low temperature can be heated. For example, heat from the heating unit 40 can be used to heat the return fluid from the vapor circuit 44 to the evaporation unit 42 (tank 420). By heating the return fluid, the temperature in the tank 420 is more appropriately maintained.

  7, 8, and 9 show examples of the configuration of the drying chamber 62.

  In FIG. 7, the drying chamber 62 includes a conveyor 510 that conveys an object, and a heating unit 512 that corresponds to the fourth heat radiating unit 444D and applies heat to the object on the conveyor 510. The drying chamber 62 is supplied with heated air from the fluid heating unit 61 (FIG. 6). The drying chamber 62 can have a configuration in which heat is substantially indirectly transmitted from the heating unit 512 (fourth heat radiating unit 444D) to the target object via a member of the conveyor 510 in contact with the target object. Alternatively, in the drying chamber 62, the member of the conveyor 510 that is in contact with the object is substantially the heating unit 512 (fourth heat radiation unit 444D), and the target is substantially directly from the heating unit 512 (fourth heat radiation unit 444D). A structure in which heat is transmitted to an object can be provided.

  In the drying chamber 62 of FIG. 7, the heat of the heated air from the fluid heating unit 61 may be transmitted to the object prior to the heat from the heating unit 512 (fourth heat radiating unit 444D), and the heat from the heating unit 512 May be transmitted to the object prior to the heat of the heated air, or both heats may be transmitted to the object at the same time. Alternatively or additionally, the drying chamber 62 may have a configuration in which heated air using the fourth heat radiating unit 444D as a heat source is blown to the object in addition to the heated air from the fluid heating unit 61.

  In FIG. 8, the drying chamber 62 includes a rotatable drum 520 and a heating unit 522 that corresponds to the fourth heat radiating unit 444 </ b> D and applies heat to the object in the drum 520. The drying chamber 62 is supplied with heated air from the fluid heating unit 61 (FIG. 6). The rotation axis of the drum 520 is arranged substantially horizontally, vertically, or diagonally. As the drum 520 rotates, the object in the drum 520 can move at least in the axial direction.

  The drying chamber 62 can have a configuration in which at least a part of the inner peripheral surface of the drum 520 is in direct or indirect contact with the object to be heated. For example, in the drying chamber 62, at least a part of the inner wall of the drum 520 is the heating unit 522 (fourth heat radiation unit 444D), and the target is substantially directly or indirectly from the heating unit 522 (fourth heat radiation unit 444D). A structure in which heat is transmitted to an object can be provided.

  In the drying chamber 62 of FIG. 8, for example, at least a part of the inner peripheral surface of the drum 520 is a heating surface. The heat of the heated air from the fluid heating unit 61 may be transmitted to the object prior to the heat from the fourth heat radiating unit 444D, and the heat from the fourth heat radiating unit 444D is prior to the heat of the heated air. Or both heats may be transferred to the object at the same time. Alternatively or additionally, the drying chamber 62 may have a configuration in which heated air using the fourth heat radiating unit 444D as a heat source is blown to the object in addition to the heated air from the fluid heating unit 61.

  In FIG. 8, the drying chamber 62 can additionally have a stirring mechanism (not shown) that stirs the object. The stirring mechanism can include a blade mechanism having blades that can rotate or move, a vibration mechanism that vibrates the object, and / or a rocking mechanism that rocks the object.

  When a stirring mechanism is provided, the drying chamber 62 can have a configuration in which the drum 520 does not rotate. In this case, the stirring mechanism can have a function of moving the object. When the inner peripheral surface of the drum 520 is a heating surface, a wide range of the inner peripheral surface can be used for heating by arranging the drum 520 vertically.

  In FIG. 9, the drying chamber 62 includes a chamber 530 having a fluidized bed, a hot air device 532 having a nozzle for blowing hot air, and a heating unit 540 corresponding to the fourth heat radiating unit 444D and applying heat to an object in the chamber 530. And have. The hot air device 532 can supply the heated air from the fluid heating unit 61 into the chamber 530. The object is stirred and heated by the heated air from the hot air device 532.

  The drying chamber 62 can have a configuration in which at least a part of the inner peripheral surface of the chamber 530 is in direct or indirect contact with the object to be heated. For example, in the drying chamber 62, a part of the inner wall of the chamber 530 is a heating unit 540 (fourth heat radiation unit 444D), and the object is substantially directly or indirectly from the heating unit 540 (fourth heat radiation unit 444D). It is possible to have a configuration in which heat is transmitted to

  In the drying chamber 62 of FIG. 9, for example, at least a part of the inner peripheral surface of the chamber 530 is a heating surface. Alternatively or additionally, the drying chamber 62 adds another hot air to the object in addition to the hot air device 532 that blows the heated air from the fluid heating unit 61 onto the object, and the heated air using the fourth heat radiation part 444D as a heat source. You can have a device.

  In addition, the drying chamber 62 may have a mechanism for stirring the object separately from the hot air device 532. Note that the chambers 530 can be arranged in multiple stages.

  FIG. 10 is a schematic diagram showing a drying system S3 in the third embodiment. In the following description, with respect to the drying system S3, the same elements as those in the drying system S1 shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  As shown in FIG. 10, in the drying system S3 in this embodiment, the compression unit 22 of the heat pump 20 has a multistage compression structure that compresses the working fluid into a plurality of stages, that is, the first compression unit 22A and the second compression. It has a two-stage compression structure including the portion 22B. The number of compression stages is set according to the specification of the drying system S3, and is 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 the working fluid is applied. Power is supplied to the compressor. The compression unit 22 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 22A and 22B are individually controlled. Alternatively, the compression unit 22 can have a coaxial compression structure. The compression ratio (pressure ratio) of the compression unit 22 is set according to the specifications of the drying system S3.

  In the present embodiment, the heat radiating portion 23 includes a two-stage front heat radiating portion (a first front heat radiating portion 23A and a second front heat radiating portion 23B) and a first stage rear heat radiating portion 23Z. In the present embodiment, the three heat radiating portions 23A, 23B, and 23Z are arranged substantially in series along the flow direction of the working fluid. The number of heat radiation units is set according to the specification of the drying system S3, and is 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more. The first front heat dissipating part 23A is disposed between the compression parts 22A and 22B, the second front heat dissipating part 23B is disposed at a downstream position of the compression part 22B, and the rear heat dissipating part 23Z is connected to the second front heat dissipating part 23B. It is arranged at the downstream position.

  In the present embodiment, the heat exchanger 112 (heat exchange device) is configured including the heated pipe 426 of the evaporation unit 42 and the first and second front heat radiation units 23A and 23B of the heat pump 20. That is, in the heat exchanger 112, the first front heat radiating part 23A and the second front heat radiating part 23B of the heat pump 20 and the heated pipe 426 of the evaporation part 42 are thermally connected. Heat from the working fluid flowing through the first front heat radiating portion 23A and the second front heat radiating portion 23B is transferred to the water flowing through the heated pipe 426. The heat exchanger 112 can have a countercurrent heat exchange system in which a low-temperature fluid (water in the heated pipe 426) and a high-temperature fluid (working fluid in the heat pump 20) flow in opposition. Alternatively, the heat exchanger 112 may have a parallel flow type heat exchange method in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures of the heat exchanger 112 can be employed. The conduit of the first front heat radiating portion 23A or the second front heat radiating portion 23B of the heat pump 20 and the heated tube 426 are arranged in contact with or adjacent to each other. For example, the conduit of the first front heat radiating portion 23 </ b> A or the second front heat radiating portion 23 </ b> B of the heat pump 20 can be disposed on the outer peripheral surface or inside of the heated tube 426.

  In the present embodiment, the heated pipe 426 of the evaporation unit 42 uses the two heat radiation units (the heat radiation unit 23A and the heat radiation unit 23B) of the heat pump 20 as heat sources. That is, in the heat pump 20, the working fluid compressed by the first compression unit 22 </ b> A flows through the heat radiating unit 23 </ b> A and gives heat to the water in the heated pipe 426. The working fluid deprived of heat falls in temperature. The working fluid whose temperature has decreased from the heat radiating unit 23A enters the second compression unit 22B. The working fluid compressed by the second compression unit 22B flows through the heat radiating unit 23B and gives heat to the object in the heated tube 426.

  By setting the input temperature of the second compression unit 22B to be low, the compression efficiency of the second compression unit 22B can be improved. That is, the heat of the heat radiating portion 23A between the stages is deprived, thereby suppressing the temperature rise of the working fluid in the process of compressing the working fluid. As a result, the compression efficiency of the compression portion 22 is improved and the power of the compressor is reduced. Is planned.

  In other words, in this embodiment, the compression part 22 of the heat pump 20 has a multistage compression structure, and the heat from the heat radiating part 23A located between the stages is used for latent heat heating of water in the evaporation part 42. The working fluid is substantially cooled in the heat dissipating part 23A located between the stages. Interstage cooling prevents the working fluid flowing through the heat pump 20 from excessively rising in temperature due to compression, in addition to improving the compression efficiency. By appropriately controlling the heat radiation temperature, the heat transfer efficiency between the heat radiation portions 23A and 23B of the heat pump 20 and the water can be improved. That is, appropriately controlled heat can be supplied to the water.

  Thus, in this embodiment, the heat pump 20 of a multistage compression structure is employ | adopted, and the several thermal radiation part 23A, 23B including the thermal radiation part (radiation part 23A) between stages is used as the heat source of the latent heat heating of water. This is advantageous in applying the heat pump to the steam generation process.

  Also in the present embodiment, the steam (liquefied component and steam) in each auxiliary path 442A-442D in the steam circuit 44 returns to the tank 420. Therefore, the steam circuit 44 can perform a circulating operation. During the implementation of the circulating operation, the supply of water from the supply source to the tank 420 can be reduced or eliminated. By using the heat supplied to the heating unit 40 (heat of the heat radiating unit 23Z of the heat pump 20) in other parts of the system, further improvement in thermal efficiency can be achieved. Alternatively or additionally, at least a portion of the fluid from the first to fourth heat radiating portions 444A to 444D (auxiliary path 442A to 442D) toward the tank 420 can be heated as necessary. For example, the fluid from the first heat radiation part 444A having a relatively low temperature can be heated. For example, heat from the heating unit 40 can be used to heat the return fluid from the vapor circuit 44 to the evaporation unit 42 (tank 420). By heating the return fluid, the temperature in the tank 420 is more appropriately maintained.

  FIG. 11 is a schematic diagram showing a drying system S4 in the fourth embodiment. In the following description, with respect to the drying system S4, elements similar to those in the drying system S1 shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the present embodiment, the heat pump 20 has four heat radiating portions (a first front heat radiating portion 23A, a second front heat radiating portion 23C, a first rear heat radiating portion 23Z, and a second rear heat radiating portion 23B). Four heat radiating portions 23A, 23B, 23C, and 23Z are arranged substantially in series along the flow direction of the working fluid, and the first front heat radiating portion 23A, the second rear heat radiating portion 23B, the second front heat radiating portion 23C, And the first rear heat radiating portion 23Z is arranged in that order. Alternatively or additionally, the number of heat dissipation units is set according to the specifications of the drying system S4 and is 3, 4, 5, 6, 7, 8, 9, 10, or 11 or more.

  In the present embodiment, the steam device 14 includes two heating units (first heating unit 40A and second heating unit 40B), two evaporation units (first evaporation unit 42A and second evaporation unit 42B), and , A steam circuit 44, a fluid drive unit (not shown) such as a pump, if necessary, and a flow rate control unit (not shown) such as a valve, if necessary.

  In the present embodiment, the water path (supply path) from the supply source includes the branching part 427A, the branching path 428A for guiding the water from the branching part 427A to the first evaporation part 42A, and the water from the branching part 427A. 2 and a branch path 428B leading to the evaporation section 42B.

  40 A of 1st heating parts are arrange | positioned adjacent to the 1st back heat radiation part 23Z of the heat pump 20, and contain the conduit | pipe through which the water from a supply source (not shown) flows. The heat exchanger 110 is configured including the first heating unit 40A and the first rear heat radiating unit 23Z. In the first heating unit 40A, the temperature of water rises due to heat transfer from the first rear heat radiating unit 23Z of the heat pump 20.

  The second heating unit 40B is disposed in the branch path 428B. The second heating unit 40B includes a conduit that is disposed adjacent to the second rear heat dissipation unit 23B of the heat pump 20 and through which water from the first heating unit 40A flows. The heat exchanger 114 is configured including the second heating unit 40B and the second rear heat radiating unit 23B. In the second heating unit 40B, the temperature of the water in the branch path 428B rises due to heat transfer from the second rear heat radiating unit 23B of the heat pump 20.

  The heat exchangers 110 and 114 may have a countercurrent heat exchange system in which a low-temperature fluid (water in the supply path) and a high-temperature fluid (working fluid in the heat pump 20) flow in opposition. The heat exchangers 110 and 114 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures for the heat exchangers 110 and 114 can be employed. For example, the piping of the heat radiating part 23Z or the heat radiating part 23B of the heat pump 20 can be disposed on the outer peripheral surface and / or the inside of the pipe of the first heating part 40A or the second heating part 40B.

  In this embodiment, a pump can be arrange | positioned between the branch part 427A and the 2nd heating part 40B in the branch path 428B. The amount of water per unit time flowing through the branch path 428A and the branch path 428B (the amount of water distributed to the evaporators 42A and 42B) is controlled by a pump and / or a flow control device (not shown) (not shown). The arrangement position of the pump is not limited between the branching part 427A and the second heating part 40B.

  42 A of 1st evaporation parts have the 1st tank 420A (steam generation part) which stores water, and the 1st circulation conduit 422A fluidly connected to the 1st tank 420A. That is, the inlet end and the outlet end of the first circulation conduit 422A are fluidly connected to the first tank 420A. The first tank 420A is provided with a water supply port from the first heating unit 40A and a steam discharge port. The first tank 420A includes a level sensor 424A that measures the liquid level and a gas-liquid separator (not shown) as necessary. The first circulation conduit 422A includes a heated pipe 426A disposed adjacent to the second front heat radiating portion 23C of the heat pump 20, and a pump (not shown) as necessary.

  Similar to the first evaporator 42A, the second evaporator 42B has a second tank 420B (steam generator) for storing water and a second circulation conduit 422B fluidly connected to the second tank 420B. . That is, the inlet end and the outlet end of the second circulation conduit 422B are fluidly connected to the second tank 420. The second tank 420 is provided with a water supply port from the second heating unit 40B and a steam discharge port. The second tank 420B includes a level sensor 424B that measures the liquid level and a gas-liquid separator (not shown) as necessary. The second circulation conduit 422B includes a heated pipe 426B disposed adjacent to the first front heat radiating portion 23A of the heat pump 20 and, if necessary, a pump (not shown).

  In the present embodiment, the first evaporator 42A (first tank 420A, heated pipe 426A) and the second evaporator 42B (second tank 420B, heated pipe 426B) are substantially connected to the water supply path. Are arranged in parallel. Note that the second evaporator 42B is an upstream position and the first evaporator 42A is a downstream position with respect to the flow direction of the working fluid in the heat pump 20.

  A heat exchanger 115 is configured including the heated tube 426A and the second front heat radiating portion 23C. Similarly, the heat exchanger 113 is configured including the heated tube 426B and the first front heat radiating portion 23A. The heat exchangers 113 and 115 have a countercurrent heat exchange system in which a low-temperature fluid (water in the heated pipes 426A and 426B) and a high-temperature fluid (working fluid in the heat pump 20) flow in opposition. Can do. The heat exchangers 113 and 115 may have a parallel flow type heat exchange system in which a high-temperature fluid and a low-temperature fluid flow in parallel. Various known heat exchange structures for the heat exchangers 113 and 115 can be employed. For example, the pipes of the heat radiating portions 23C and 23A of the heat pump 20 can be disposed on the outer peripheral surface and / or inside of the heated tubes 426A and 426B.

  In the first evaporation section 42A, the water whose temperature has increased in the first heating section 40A is supplied to the first tank 420A through the supply port, and water is stored in the first tank 420A and the first circulation conduit 422A. The amount of water supplied to the first tank 420A is controlled so that the liquid level in the first tank 420A is within a predetermined range. For example, the amount of water supplied to the first tank 420A is controlled based on the measurement result of the level sensor 424A. The water in the heated tube 426A is heated by heat transfer from the second front heat radiating portion 23C of the heat pump 20, and at least a part of the water evaporates. The first tank 420A is fluidly connected to the steam circuit 44 via a duct 425A. The steam in the first tank 420A flows in the duct 425A toward the steam circuit 44.

  In the second evaporation section 42B, the water whose temperature has risen in the first and second heating sections 40A and 40B is supplied to the second tank 420B through the supply port, and water is supplied into the second tank 420B and the second circulation conduit 422B. Is stored. The amount of water supplied to the second tank 420B is controlled so that the liquid level in the second tank 420B is within a predetermined range. For example, the amount of water supplied to the second tank 420B is controlled based on the measurement result of the level sensor 424B.

  In the present embodiment, the state (pressure etc.) of the working fluid differs between the first front heat radiating part 23A and the second front heat radiating part 23C. The controllability of the heat balance can be improved by individually controlling the flow rate per unit time of the water flowing through the heated tubes 426A and 426B corresponding to the heat radiating portions 23A and 23C.

  FIG. 12 shows an example of a configuration for controlling the flow rate of water in the heated tube 426B. In the heat pump 20, a sensor 471 for measuring the outlet temperature of the heat radiating unit 23A is provided. Based on the measurement result of the sensor 471, the control device 70 controls the flow rate of water per unit time flowing through the heated pipe 426B via the fluid drive unit (pump 474, etc.) of the heated pipe 426B. Thereby, the exit temperature of the working fluid in the heat radiating portion 23A can be set to the target value. You may use the sensor 472 which measures the inlet_port | entrance temperature of the thermal radiation part 23A. A configuration similar to this can be employed for the heated tube 426A shown in FIG.

  Returning to FIG. 11, the water in the heated pipe 426B is heated by heat transfer from the first front heat radiating portion 23A of the heat pump 20, and at least a part of the water evaporates. The second tank 420B is fluidly connected to the steam circuit 44 via a duct 425B. The steam in the second tank 420B flows toward the steam circuit 44 in the duct 425B.

  The steam circuit 44 includes a path 442 through which steam flows, and a pressure control device (not shown) that controls the pressure in the path as necessary.

  In the present embodiment, the path 442 of the steam circuit 44 includes an auxiliary path 442F and an auxiliary path 442G. The auxiliary path 442F corresponds to the first evaporator 42A, and the auxiliary path 442G corresponds to the second evaporator 42B. The steam from the first tank 420A of the first evaporator 42A flows through the auxiliary path 442F. Vapor from the second tank 420B of the second evaporator 42B flows through the auxiliary path 442G.

  The complementary path 442F and the complementary path 442G are independent of each other. The internal spaces of the auxiliary paths 442F and 442G are set to different pressures. This setting is performed using, for example, a pressure control device. The pressure control device may have at least one of a vacuum manufacturing function and a compression function. The pressure control device may be detachable with respect to the auxiliary paths 442F and 442G.

  In the present embodiment, the path 442 of the steam circuit 44 further includes heat radiation portions 444F and 444G that are thermally connected to the drying device 16. The heat dissipation part 444F has a conduit through which steam from the first tank 420A of the first evaporation part 42A flows. The heat radiation part 444G has a conduit through which steam from the second tank 420B of the second evaporation part 42B flows. The heat dissipating part 444F and the heat dissipating part 444G are part of the auxiliary path 442F and the auxiliary path 442G, respectively.

  In the present embodiment, the heat dissipating part 444F is arranged at the upstream position in the drying device 16 rather than the heat dissipating part 444G. That is, the heat dissipating part 444F and the heat dissipating part 444G are arranged in that order along the flow direction of the drying device 16.

  In the present embodiment, the pressures in the first and second tanks 420A and 420B of the first and second evaporators 42A and 42B are determined according to the setting of the internal pressures of the auxiliary paths 444F and 444G of the steam circuit 44. In the present embodiment, the internal pressures of the first tank 420A and the second tank 420B may be in accordance with the input temperatures of water to the first and second evaporators 42A and 42B, respectively.

  In the present embodiment, the water heated by the first heating unit 40A is supplied to the first tank 420A, and the second heating unit 40B is supplied to the second tank 420B in addition to the heating by the first heating unit 40A. Water heated at 40B is supplied. In one example, the water inlet temperature to the second tank 420B is higher than that of the first tank 420A, and accordingly, the internal pressure of the second tank 420B is set higher than that of the first tank 420A. The pressure in each tank 420A, 420B can be a negative pressure (negative pressure) lower than atmospheric pressure (1 atm = about 0.1 MPa) or a positive pressure (positive pressure) higher than atmospheric pressure.

  In the present embodiment, in the heat exchanger 110 (first heating unit 40A), the temperature of water from the supply source rises due to heat transfer from the heat radiating unit 23Z of the heat pump 20. The flow of water from the first heating unit 40A is divided into a branch path 428A and a branch path 428B via the branch part 427A. The water flowing through the branch path 428A is directed to the first evaporator 42A (first tank 420A). In the first tank 420A, water has a temperature close to the boiling point (first boiling point). In the heat exchanger 115, the water in the heated tube 426A changes in phase due to heat transfer from the heat radiating portion 23B and evaporates.

  The water flowing through the branch path 428B goes to the heat exchanger 114 (second heating unit 40B). In the heat exchanger 114 (second heating unit 40B), the temperature of the water in the branch path 428B further rises due to heat transfer from the heat radiating unit 23Y of the heat pump 20. In one example, the internal pressure of the second tank 420B is higher than that of the first tank 420A. In the second tank 420B, the water has a temperature close to the boiling point (second boiling point). The temperature of the water in the second tank 420B is higher than the water in the first tank 420A. In the heat exchanger 113, the water in the heated pipe 426B undergoes a phase change and evaporates due to heat transfer from the heat radiating portion 23A.

  In this embodiment, water is sensible heat heated in the heat exchangers 110 and 114 (first and second heating units 40A and 40B), and water is latent heat in the heat exchangers 115 and 113 (heated tubes 426A and 426B). Heated. The heat exchangers 110 and 114 are in a form suitable for sensible heat exchange and the heat exchangers 115 and 113 are in a form suitable for latent heat exchange. Steam is generated.

  Thus, in the present embodiment, a plurality of evaporators 42A and 42B set in different environments are provided. Saturated steam is generated under a relatively low pressure in the first tank 420A of the first evaporator 42A, and saturated steam is generated under a relatively high pressure in the second tank 420B of the second evaporator 42B.

  FIG. 13 schematically shows an example of a temperature change between water and the working fluid of the heat pump in the present embodiment.

  As shown in FIG. 13, in the first heating unit 40A (see FIG. 11), the temperature of water from the supply source rises near the first boiling point due to heat exchange with the working fluid (arrow m1 in FIG. 13). . In the first evaporation part 42A, the phase of water changes from liquid to vapor at a temperature near the first boiling point by heat exchange with the working fluid (arrow m2). In the second heating unit 40B, the temperature of water rises near the second boiling point due to heat exchange with the working fluid (arrow m3). In the second evaporation part 42B, the phase of water changes from liquid to vapor at a temperature near the second boiling point due to heat exchange with the working fluid (arrow m4).

  Moreover, as shown in FIG. 13, the temperature of the working fluid from the compression part 22 (refer FIG. 11) falls by the heat exchange with water (arrow n1 of FIG. 13). The working fluid undergoes a phase change to a liquid by heat exchange with water (arrow n2). Furthermore, the temperature of the working fluid decreases due to heat exchange with water (arrow n3).

  In the present embodiment, by generating steam using two evaporation units set in different environments, the temperature difference between the working fluid and water during heat exchange can be suppressed, and heat exchange efficiency can be increased.

  In the present embodiment, steam having different temperatures (saturation temperatures) flows through the heat dissipating part 444F (auxiliary path 442F) and the heat dissipating part 444G (auxiliary path 442G). The temperature of the steam flowing through the heat radiating portion 444F is relatively low, and the temperature of the steam flowing through the heat radiating portion 444G is relatively high. That is, in the path 442 of the steam circuit 44, relatively low temperature steam is supplied to the relatively upstream side in the flow direction of the drying device 16, and relatively high temperature steam is supplied to the relatively downstream side in the flow direction.

  Heat from at least one of the steam flowing through the heat radiating units 444F and 444G and the condensed liquid thereof is transmitted to the object in the drying device 16, and at least a part of the steam flowing through the heat radiating units 444F and 444G is liquefied. In the present embodiment, the downstream end of the auxiliary path 442F is fluidly connected to the first tank 420A. Further, the downstream end of the auxiliary path 442G is fluidly connected to the second tank 420B. Vapor and liquid from the heat dissipating part 444F and the heat dissipating part 444G enter the first tank 420A and the second tank 420B, respectively. In the auxiliary paths 442F and 442G, a fluid control valve (pressure reducing valve) or the like can be disposed between the heat radiation units 444A and 444G and the tanks 420A and 420B.

  Also in this embodiment, the steam (liquefied component and steam) in the auxiliary path 442F and the auxiliary path 442G in the steam circuit 44 returns to the first tank 420A and the second tank 420B, respectively. Therefore, the steam circuit 44 can perform a circulating operation. During the implementation of the circulating operation, the supply of water from the supply source to the first and second tanks 420A and 420B can be reduced or eliminated. By using the heat supplied to the first and second heating units 40A and 40B (heat of the first rear heat radiation part 23Z and the second rear heat radiation part 23B of the heat pump 20) in other parts of the system, further Improvement of thermal efficiency is achieved.

  In the present embodiment, the heat radiating units 444F and 444G of the steam circuit 44 are arranged in the fluid heating unit 61 of the drying device 16. The air that has flowed into the fluid heating unit 61 of the drying device 16 is sequentially heated by the heat dissipation unit 444F and the heat dissipation unit 444G.

  An object to be dried is placed in the drying chamber 62. In the present embodiment, the object in the drying chamber 62 is dried by the heated air. Air (exhaust gas etc.) from the drying chamber 62 is discharged to the outside via the fluid discharge portion 63.

  As described above, also in the present embodiment, drying is performed using the steam generated using the heat of the heat pump 20.

  Alternatively, a part of the heat radiation portions 444F and 444G of the steam circuit 44 of FIG. 11 can be disposed in the drying chamber 62 of the drying device 16 as in the drying system S2 of FIG.

  14, FIG. 15, and FIG. 16 are schematic views showing modifications of the heat pump device 12 (heat pump 20) and the steam device 14 (evaporating section 42) in the drying system S4 of FIG. In the following description, the same reference numerals are given to the same elements as those in the system shown in FIG. 11, and the description thereof is omitted or simplified.

  In FIG. 14, the compression unit 22 of the heat pump 20 has a structure that compresses the working fluid in a plurality of stages (two stages). In this embodiment, the compression part 22 has the 1st compression part 22A arrange | positioned in front of the thermal radiation part 23A, and the 2nd compression part 22B arrange | positioned in the middle stage of the thermal radiation part 23A. Instead of or in addition to the second compression part 22B, a compression part can be provided in the middle stage of the heat dissipation part 23C. The number of compression stages is set according to the specification of the drying system S4, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The compression unit 22 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 22A and 22B are individually controlled. Alternatively, the compression unit 22 can have a coaxial compression structure. The compression ratio (pressure ratio) of each compression part 22A, 22B is set according to the specification of drying system S4.

  In this embodiment, since the compression part 22 is a multistage type, the energy efficiency is improved. That is, the heat between the stages of the multistage compression unit 22 is deprived, thereby suppressing an increase in the temperature of the working fluid during the compression process of the working fluid. As a result, the compression efficiency of the compression unit 22 is improved and the power of the compressor is increased. Can be reduced. In the present embodiment, the point that the input temperature of the working fluid to the multistage compression unit 22 is increased by the regenerator 28 is also advantageous in reducing the power of the compression unit 22.

  Next, in FIG. 15, the steam device 14 includes first, second, and third heating units 40A, 40B, and 40C, and first, second, and third evaporation units 42A, 42B, and 42C. . In the present embodiment, the water supply path includes branch portions 427A and 427B and branch paths 428A, 428B, 428C, and 428D. In the water supply path, a branching part 427B is located between the second heating part 40B and the second tank 420B. The branch path 428C guides water from the branch part 427B to the second evaporation part 42B. The branch path 428D guides water from the branch part 427B to the third evaporation part 42C.

  In the present embodiment, six heat radiating portions 23E, 23F, 23A, 23B, 23C, and 23Z are arranged in series along the flow direction of the working fluid. A heat radiating portion 23E, a heat radiating portion 23F, a heat radiating portion 23A, a heat radiating portion 23B, a heat radiating portion 23C, and a heat radiating portion 23Z are arranged in this order along the flow direction of the working fluid.

  The third heating unit 40C is disposed in the branch path 428D. 40C of 3rd heating parts are arrange | positioned adjacent to the thermal radiation part 23F of the heat pump 20, and contain the piping through which the water from the 2nd heating part 40B flows. The heat exchanger 116 is configured including the third heating unit 40C and the heat radiating unit 23F. In the third heating unit 40C, the temperature of the water in the branch path 428D rises due to heat transfer from the heat radiating unit 23F of the heat pump 20.

  In the present embodiment, a pump can be disposed between the branch portion 427B and the third heating unit 40C in the branch path 428D. The amount of water per unit time flowing through the branch path 428C and the branch path 428D (the amount of water distributed to the evaporation units 42B and 42C) is controlled by a pump and / or a flow control device (not shown) (not shown). The arrangement position of the pump is not limited between the branching part 427B and the third heating part 40C.

  Similarly to the first and second evaporators 42A and 42B, the third evaporator 42C includes a third tank 420C for storing water and a third circulation conduit 422C fluidly connected to the third tank 420C. . That is, the inlet end and the outlet end of the third circulation conduit 422C are fluidly connected to the third tank 420C. The third tank 420C is provided with a water supply port from the third heating unit 40C and a steam discharge port. The third tank 420C includes a level sensor 424C that measures the liquid level and a gas-liquid separator (not shown) as necessary. The third circulation conduit 422C includes a heated pipe 426C disposed adjacent to the heat radiating unit 23E of the heat pump 20, and a fluid drive unit such as a pump and a flow rate control unit (not shown) such as a valve as necessary. .

  In the present embodiment, the first evaporator 42A (first tank 420A, heated pipe 426A), the second evaporator 42B (second tank 420B, heated pipe 426B), and the third evaporator 42C (third tank 420C, The heated tube 426C) is arranged substantially in parallel with the water supply path. The first, second, and third heating units 40A, 40B, and 40C are disposed substantially in series with respect to the water supply path. Note that the third evaporator 42C is an upstream position, the second evaporator 42B is an intermediate position, and the first evaporator 42A is a downstream position with respect to the flow direction of the working fluid in the heat pump 20. A heat exchanger 117 is configured including the heated tube 426C and the heat radiating portion 23E.

  In the third evaporation section 42C, the water whose temperature has increased in the first, second, and third heating sections 40A, 40B, and 40C is supplied to the third tank 420C through the supply port, and the third tank 420C and the third tank Water is stored in the circulation conduit 422C. The amount of water supplied to the third tank 420C is controlled so that the liquid level in the third tank 420C is within a predetermined range. For example, the amount of water supplied to the third tank 420C is controlled based on the measurement result of the level sensor 424C. The water in the heated pipe 426C is heated by heat transfer from the heat radiating portion 23E of the heat pump 20, and at least a part of the water evaporates.

  In the present embodiment, the water flowing through the branch path 428D goes to the heat exchanger 116 (third heating unit 40C). In the heat exchanger 116 (third heating unit 40C), the temperature of the water in the branch path 428D further rises due to heat transfer from the heat radiating unit 23F of the heat pump 20. The internal pressure of the third tank 420C is higher than that of the first and second tanks 420A and 420B. In the third tank 420C, the water has a temperature close to the boiling point (third boiling point). The temperature of the water in the third tank 420C is higher than the water in the first and second tanks 420A and 420B. In the heat exchanger 117, the water in the heated pipe 426C changes in phase due to heat transfer from the heat radiating portion 23E and evaporates.

  In this embodiment, the compression unit 22 of the heat pump 20 has a structure that compresses the working fluid in a plurality of stages (in this example, two stages). In this embodiment, the compression part 22 has 22 A of 1st compression parts arrange | positioned in front of the thermal radiation part 23E, and 2nd compression part 22B arrange | positioned in the middle stage of the thermal radiation part 23E. Instead of or in addition to the second compression part 22B, a compression part can be provided in the middle stage of the heat radiation part 23A and / or the middle stage of the heat radiation part 23C.

  In the present embodiment, saturated steam is generated under a relatively low pressure in the first tank 420A of the first evaporator 42A, and saturated steam is generated under a relatively high pressure in the third tank 420C of the third evaporator 42C. In the second tank 420B of the second evaporator 42B, saturated steam is generated under an intermediate pressure.

  Next, in FIG. 16, in this embodiment, the compression part 22 of the heat pump 20 has a structure that compresses the working fluid in a plurality of stages (in this example, two stages). In this embodiment, the compression part 22 has the 1st compression part 22A arrange | positioned in front of the thermal radiation part 23A, and the 2nd compression part 22C arrange | positioned between the thermal radiation part 23B and the thermal radiation part 23C. In addition to the second compression unit 22C, a compression unit may be provided in the middle stage of the heat dissipation unit 23A and / or the heat dissipation unit 23C. The number of compression stages is set according to the specifications of the steam generation system, and is 2, 3, 4, 5, 6, 7, 8, 9, or 10 or more. The compression unit 22 can have a multiaxial compression structure in which the rotation speeds corresponding to the compression units 22A and 22C are individually controlled. Alternatively, the compression unit 22 can have a coaxial compression structure. The compression ratio (pressure ratio) of each compression part 22A, 22C is set according to the specification of a steam generation system.

  FIG. 17 is a schematic diagram showing a drying system S5 in the fifth embodiment. In the following description, with respect to the drying system S5, elements similar to those in the drying system S1 shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

  In the present embodiment, the path 442 of the steam circuit 44 has one steam circulation route. The path 442 includes a heat radiating portion 444J that is thermally connected to the drying device 16. The heat radiation part 444J has a conduit through which steam from the tank 420 of the evaporation part 42 flows. The heat dissipation part 444J is a part of the path 442.

  In the present embodiment, the internal space of the path 442 of the steam circuit 44 is set to a predetermined pressure as necessary. This setting is performed using, for example, a pressure control device. The pressure control device may have at least one of a vacuum manufacturing function and a compression function. The pressure control device may be detachable with respect to the path 442.

  In the present embodiment, the fluid heating unit 61 of the drying device 16 has a counter-current heat exchange method in which a low-temperature fluid (air) and a high-temperature fluid (steam in the heat dissipation unit 444J) flow opposite to each other. That is, in the path 442 of the steam circuit 44, relatively low temperature steam is supplied to the relatively upstream side in the flow direction of the drying device 16, and relatively high temperature steam is supplied to the relatively downstream side in the flow direction.

  In this embodiment, the steam flowing through the path 442 can be saturated steam or superheated steam. The superheated steam is generated, for example, by compressing steam from the tank 420 of the evaporation unit 42 by a compression unit (not shown). By using the superheated steam, the air in the drying device 16 is heated using at least the sensible heat of the steam. In this case, the heat radiation temperature distribution of the steam circuit 44 in the fluid heating unit 61 of the drying device 16 can have an overall gradient along the flow direction.

  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.

It is the schematic which shows 1st Embodiment. It is a schematic diagram which shows an example of the temperature change of the vapor | steam in the steam circuit in 1st Embodiment, and the air in a drying apparatus. It is a Ts diagram which shows an example of the state change of the water by a steam generation system. It is a partial schematic diagram which shows an example of the form which mixes the warm water from a steam circuit with the steam from a compression part. It is the modification of the form of FIG. 1, and is the schematic which shows an example of the form which heats a return fluid. It is the schematic which shows 2nd Embodiment. It is a schematic diagram which shows the structural example of a drying chamber. It is a schematic diagram which shows another structural example of a drying chamber. It is a schematic diagram which shows another structural example of a drying chamber. It is the schematic which shows 3rd Embodiment. It is the schematic which shows 4th Embodiment. It is a schematic diagram which shows an example of the structure which controls the flow volume of the water in an evaporation pipe. It is a figure which shows typically an example of the temperature change of water and the working medium of a heat pump. It is a schematic diagram which shows the modification of a heat pump apparatus (heat pump) and a vapor | steam apparatus (evaporation part). It is a schematic diagram which shows another modification of a heat pump apparatus (heat pump) and a steam apparatus (evaporation part). It is a schematic diagram which shows another modification of a heat pump apparatus (heat pump) and a steam apparatus (evaporation part). It is the schematic which shows 5th Embodiment.

Explanation of symbols

  S1, S2, S3, S4, S5 ... drying system, 12 ... heat pump device (first device), 20 ... heat pump (heat pump circuit), 21 ... heat absorption part, 22 ... compression part, 24 ... expansion part, 25 ... main path , 27 ... bypass path, 28 ... regenerator, 16 ... drying device (third device), 61 ... fluid heating unit, 62 ... drying chamber, 63 ... fluid discharge unit, 70 ... control device.

Claims (17)

A first device having a heat pump circuit in which a working fluid flows and having a heat absorption part, a compression part, a heat dissipation part, and an expansion part;
A second device having an evaporation section where water that has received heat from the working fluid evaporates, and a vapor circuit through which the vapor from the evaporation section flows;
A third device having a drying chamber in which an object to be dried is arranged, wherein the heat from the steam is transferred to at least one of the object and a fluid flowing toward the object;
An industrial drying system comprising:   The industrial drying system according to claim 1, wherein at least a part of the steam is liquefied in the steam circuit. At least one of the object and the fluid flows along a flow direction;
The steam circuit has a path in which the relatively low temperature steam is supplied to a relatively upstream side in the flow direction and the relatively high temperature steam is supplied to a relatively downstream side in the flow direction. The industrial drying system according to claim 1 or 2.   The steam circuit is a plurality of auxiliary paths through which a plurality of steams having different saturation temperatures flow, and heat from at least one of the plurality of steams and the condensate thereof is supplied to at least one of the object and the fluid, respectively. The industrial drying system according to any one of claims 1 to 3, wherein the plurality of auxiliary paths are provided.   The industrial drying system according to claim 4, wherein the steam circuit further includes a plurality of compression units constituting multiple stages.   The industrial drying system according to claim 5, wherein the steam circuit further includes a nozzle for supplying water to the compressed steam.   The industrial drying system according to claim 6, wherein the nozzle is fluidly connected to at least one of the evaporation unit and the vapor circuit of the second device.   The industrial drying system according to any one of claims 1 to 7, wherein the evaporation section has at least one of a drum type, an evaporation type, a boiling type, and an evaporation and boiling type.   The said evaporation part is a some steam generation part, Comprising: The said several steam generation part which each transmits the heat of the said working fluid of the said heat pump circuit to the said water is further characterized by the above-mentioned. An industrial drying system according to any of the above. The plurality of steam generation units each have a plurality of different internal pressures,
The industrial drying system according to claim 9, wherein a plurality of steams having different saturation temperatures are supplied from the plurality of steam generating units to the steam circuit.   The third device is a fluid heating unit fluidly connected to the drying chamber, wherein the fluid heating unit transmits heat from at least one of the steam and its condensate to the fluid flowing toward the drying chamber. The industrial drying system according to any one of claims 1 to 10, further comprising:   The said 1st apparatus further has an exhaust heat recovery part which the said heat absorption part of the said heat pump circuit pumps up at least one part of the exhaust heat from the said 3rd apparatus, The any one of Claims 1-11 characterized by the above-mentioned. Industrial drying system as described in.   The industrial drying system according to any one of claims 1 to 12, wherein the compression section of the heat pump circuit has a multistage structure.   The industrial drying according to any one of claims 1 to 13, wherein the heat pump circuit further includes a heating heat dissipating unit that supplies heat for heating water supplied to the evaporation unit. system.   The industrial drying system according to claim 14, wherein the heating heat dissipating unit can heat at least a part of the steam and its condensate returning from the steam circuit to the evaporation unit.   The heat pump circuit further includes a regenerator in which heat from the working fluid is transmitted to the working fluid between the heat absorption unit and the compression unit. Industrial drying system. Preparing a heat pump circuit through which the working fluid flows;
Transferring heat from the working fluid to water to generate steam;
Transferring heat from the vapor to at least one of a drying object and a fluid flowing toward the object;
An industrial drying method comprising:

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