WO2011125745A1 - Drying system equipped with heat pump unit and exhaust heat recovery mechanism - Google Patents
Drying system equipped with heat pump unit and exhaust heat recovery mechanism Download PDFInfo
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- WO2011125745A1 WO2011125745A1 PCT/JP2011/058023 JP2011058023W WO2011125745A1 WO 2011125745 A1 WO2011125745 A1 WO 2011125745A1 JP 2011058023 W JP2011058023 W JP 2011058023W WO 2011125745 A1 WO2011125745 A1 WO 2011125745A1
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- dry
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- exhaust
- dryer
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B23/00—Heating arrangements
- F26B23/001—Heating arrangements using waste heat
- F26B23/002—Heating arrangements using waste heat recovered from dryer exhaust gases
- F26B23/005—Heating arrangements using waste heat recovered from dryer exhaust gases using a closed cycle heat pump system ; using a heat pipe system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F26—DRYING
- F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
- F26B3/00—Drying solid materials or objects by processes involving the application of heat
- F26B3/02—Drying solid materials or objects by processes involving the application of heat by convection, i.e. heat being conveyed from a heat source to the materials or objects to be dried by a gas or vapour, e.g. air
- F26B3/06—Drying solid materials or objects by processes involving the application of heat by convection, i.e. heat being conveyed from a heat source to the materials or objects to be dried by a gas or vapour, e.g. air the gas or vapour flowing through the materials or objects to be dried
- F26B3/08—Drying solid materials or objects by processes involving the application of heat by convection, i.e. heat being conveyed from a heat source to the materials or objects to be dried by a gas or vapour, e.g. air the gas or vapour flowing through the materials or objects to be dried so as to loosen them, e.g. to form a fluidised bed
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/52—Heat recovery pumps, i.e. heat pump based systems or units able to transfer the thermal energy from one area of the premises or part of the facilities to a different one, improving the overall efficiency
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working
Definitions
- the present invention relates to a drying system equipped with a continuous hot air drying device such as a fluidized bed dryer or a rotary drum dryer, and in particular, a dryer requiring a high-temperature drying gas is energy efficient as a whole drying system.
- the present invention relates to a drying system including an operable heat pump unit and an exhaust heat recovery mechanism.
- the band dryer is provided with a plurality of stages of net conveyors in which drying is performed in contact with a dry gas when an object to be processed moves on a track such as a net conveyor disposed in a drying chamber.
- a continuous hot air drying apparatus such as a fluidized bed dryer or a rotary drum dryer that performs processing in a relatively short time, it is not realistic to apply a heat pump unit to the heat source.
- the residence time (processing time) of the object to be processed in the dryer is short, and a high temperature dry gas is required at the initial stage of drying.
- the temperature of the hot air obtained is about 50 ° C., and the temperature necessary for drying in a short time cannot be obtained. Therefore, it is necessary to cope with such as increasing the size of the dryer. Therefore, it is impossible to operate efficiently, which leads to an increase in cost.
- the present applicant makes it possible to apply a heat pump unit as a device for supplying a high-temperature dry gas to a continuous hot-air dryer, and the energy efficiency of the entire drying system is high, and further high energy
- a drying system comprising a novel heat pump unit and a temperature raising device capable of performing an efficient and stable operation has been developed and has already been filed for a patent (see Patent Document 2).
- the applicant has continued to research and develop a drying system including this type of heat pump unit, and has paid particular attention to the effective use of heat contained in the dry exhaust gas.
- it is widely practiced to recover and effectively use the heat in the dry exhaust gas discharged from the hot air dryer, but there are cases where the energy saving effect of the entire system cannot be expected.
- the temperature of the dry exhaust gas is not significantly lower than the temperature of the dry gas supplied to the drying apparatus (for example, when the amount of evaporation is small or when heat treatment is performed), a large amount of heat can be recovered. Therefore, it can contribute to energy saving as the whole system.
- the temperature of the drying exhaust gas is the temperature of the drying gas supplied to the drying device. Since the temperature is significantly lower than the temperature (for example, 160 ° C. ⁇ 90 ° C.), a large energy saving effect is not obtained as a whole system, and heat recovery in the dry exhaust gas has not been usually performed.
- the present invention has been made from such a background, and by applying a heat pump unit as a device for supplying a high-temperature dry gas to a continuous hot air drying device, the energy efficiency of the entire drying system can be improved.
- a new heat pump unit that can further improve energy efficiency by effectively utilizing the heat recovered from the dry exhaust gas in a high drying system that can operate stably with high energy efficiency.
- the technical issue is the development of a drying system with a waste heat recovery mechanism.
- a drying system comprising a heat pump unit and an exhaust heat recovery mechanism according to claim 1 is a drying system comprising a dryer and an air supply mechanism for supplying a drying gas to the dryer.
- the air supply mechanism is provided with a heat pump unit, and the air supply mechanism further includes a temperature rise for heating the dry gas heated by the heat pump unit.
- an exhaust heat recovery mechanism configured to be able to take heat in the dry exhaust gas exhausted from the dryer into the dry gas before being charged into the dryer. It is characterized by this.
- a drying system comprising a heat pump unit and an exhaust heat recovery mechanism according to claim 2 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas to a part of the dry exhaust gas. Are combined with the dry gas so as to be taken into the dry gas.
- the drying system including the heat pump unit and the exhaust heat recovery mechanism according to claim 3 adds to the requirements of claim 1, and the exhaust heat recovery mechanism recovers the heat in the dry exhaust gas by a heat pipe. Then, after that, it is configured to be taken into the dry gas.
- the drying system including the heat pump unit and the exhaust heat recovery mechanism according to claim 4 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas to a heat exchanger. It is characterized in that it is configured to be taken into a dry gas.
- the drying system comprising the heat pump unit and the exhaust heat recovery mechanism according to claim 5 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas into one of the dry exhaust gases.
- the part is taken into the dry gas by being merged with the dry gas, and the heat in the dry exhaust gas is taken into the dry gas using a heat exchanger. It is.
- the heat in the dry exhaust gas exhausted from the dryer is provided between the heat pump unit and the dryer by taking in the dry gas before being charged into the dryer.
- the thermal energy required in the drying gas temperature raising device can be reduced, and the energy efficiency of the entire drying system can be improved.
- the heat contained in the dry exhaust gas can be directly taken into the dry gas together with the dry exhaust gas, and the energy efficiency of the entire drying system can be improved.
- the heat contained in the dry exhaust gas can be taken into the dry gas with high efficiency by the heat pipe, and the energy efficiency of the entire drying system can be improved.
- the heat contained in the dry exhaust gas can be taken into the dry gas with high efficiency by the heat exchanger, and the energy efficiency of the entire drying system can be improved.
- the heat contained in the dry exhaust gas can be directly taken into the dry gas together with the dry exhaust gas, and can be taken into the dry gas with high efficiency by the heat exchanger. Energy efficiency can be improved.
- drying system provided with the heat pump unit and the exhaust heat recovery mechanism of the present invention is as shown in the following examples as an example, but this example is appropriately within the scope of the technical idea of the present invention. It is also possible to make changes.
- a drying system S (hereinafter referred to as a drying system S) including a heat pump unit and an exhaust heat recovery mechanism according to the present invention includes a dryer 1 and an air supply mechanism for supplying a drying gas D to the dryer 1. It consists of. Specifically, the dryer 1 and the heat pump unit 2, the temperature raising device 5, and the exhaust heat recovery mechanism 6 constituting the air supply mechanism are provided as main elements.
- the dry gas D is a general term for the dry gases D1, D2, D3,.
- a hot air dryer is applied as the dryer 1, and the residence time (processing time) of the workpiece H in the dryer 1 is short, and further at the initial stage of drying.
- the drying process by the continuous dryer 1 that requires the high-temperature drying gas D is performed using the heat pump unit 2 with high energy efficiency and in a more stable state.
- description will be made for each embodiment in which the configuration of the exhaust heat recovery mechanism 6 is different.
- the dryer 1 is a continuous fluidized bed dryer which is an example of a hot air dryer.
- the dryer 1 uses the inside of the housing 10 as a processing space for drying.
- the drying gas D is supplied from below the ventilation plate 11 provided so as to divide the processing space vertically, and the ventilation plate 11 is dried while forming a fluidized bed on the workpiece H located on the substrate 11.
- the air inlet 12 is formed in two places as an example in the lower part of the housing
- An exhaust port 14 is formed in the upper part, and an exhaust port 15 is formed for the duct 10a connected to the rear side and above the vent plate 11. Further, the peripheral device of the dryer 1 is provided with a blower fan 16 and an exhaust fan 17, and the connection state thereof will be described in detail later.
- a configuration is adopted in which a dam plate 11a is provided in the middle of the ventilation plate 11, and the workpiece H that has been dried to some extent passes over the dam plate 11a and moves to the next drying stage. I was able to.
- a fluidized bed dryer is adopted as the dryer 1, but other hot air dryers such as a fluidized bed granulator dryer, a band dryer or an air dryer can also be adopted.
- the heat pump unit 2 includes a condenser 21, an expansion valve 22, an evaporator 23, and a compressor 24 to form a heat pump cycle.
- carbon dioxide is used.
- a refrigerant is used.
- the temperature of the dry gas D heated by the heat pump unit 2 can be increased by employing carbon dioxide as the refrigerant.
- the heat pump unit 2 using carbon dioxide as a refrigerant has been put into practical use as being capable of increasing the temperature of the dry gas D, but in the future, a heat pump unit having equivalent performance using other refrigerants will be used. When 2 is put into practical use, this can also be adopted.
- a dedicated heat pump unit 2 may be connected to each air supply port 12.
- the temperature raising device 5 includes, as an example, a plate fin type heat exchanger 50 as a main member, and a plurality of radiating fins 51 are provided inside the heat exchanger 50.
- a pipe 52 provided on the side periphery is arranged. And heat exchange is performed between the fluid (steam etc.) which passes through the inside of the pipe 52, and the fluid (dry gas D1) which contacts the radiation fin 51.
- the inflow amount of steam or the like into the pipe 52 is adjusted by a control valve 54, and thereby the rising temperature of the dry gas D1 is adjusted.
- a direct furnace 55 as shown in FIG. 5 as the temperature raising device 5, which will be described in detail later.
- the drying system S1 is comprised combining the said dryer 1, the heat pump unit 2, and the temperature raising apparatus 5, and the blowing fan 16 is connected to the input side of the temperature raising apparatus 5.
- an exhaust heat recovery mechanism 6 for taking in heat in the dry exhaust gas D4 exhausted from the dryer 1 into the dry gas D1 before being input to the dryer 1 is configured.
- exhaust gas is exhausted. A part of the dry exhaust gas D4 discharged from the port 14 is joined to the dry gas D1 through the return pipe 61, so that the heat in the dry exhaust gas D4 is taken into the dry gas D1.
- the return line 61 is between the line connected to the exhaust port 14 of the dryer 1 and the line connected between the heat pump unit 2 and the temperature raising device 5 (heat exchanger 50). Is provided.
- the return pipe 61 is provided with a damper 61a so that the flow rate of the dry exhaust gas D4 can be adjusted.
- the drying system S1 of the present invention is configured as described above as an example, and the operation mode thereof will be described below.
- the dry gas D is a general term for the heated outside air D0, and a state in which the outside air D0 is heated by the heat pump unit 2 is called a dry gas D1.
- the dry gas D1 in which heat in the dry exhaust gas D4 exhausted from the dryer 1 is taken is referred to as a dry gas D2.
- the dry gas D2 whose temperature is raised by the temperature raising device 5 is referred to as a dry gas D3.
- the dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from the exhaust port 14 as the dry exhaust gas D4.
- the drying system S1 When the drying system S1 is started, the outside air D0 (20 ° C. as an example) is first taken in by the blower fan 16 (5785 kg-dryair / h), and then the temperature is raised in the condenser 21 in the heat pump unit 2 to dry the gas D1. It becomes. Next, dry exhaust gas D4 (7071 kg-dryair / h) is mixed into the dry gas D1 from the return pipe 61 to become a dry gas D2. Next, the temperature of the dry gas D2 is raised in the heat exchanger 50, and the dry gas D2 is fed into the dryer 1 from the air supply port 12 as the dry gas D3.
- the blower fan 16 5785 kg-dryair / h
- the to-be-processed objects H such as a food raw material supplied with respect to the dryer 1
- a fluidized bed is formed with the dry gas D3, and volatile matters, such as a water
- the workpiece H becomes lighter in weight as the drying progresses, gets over the barrier plate 11a, becomes a desired dry state, and is discharged to the outside from the discharge port 15.
- the temperature of the dry gas D3 after acting on the workpiece H decreases and becomes a dry exhaust gas D4, which is exhausted from the exhaust port 14 to the outside of the dryer 1.
- the amount of dry exhaust gas D4 (30 to 50% of the total amount) corresponding to the opening degree of the damper 61a is taken into the return pipe 61, and from here the pipe connected between the heat pump unit 2 and the heat exchanger 50 And mixed with the dry gas D1 here.
- the temperature of the dry gas D when it reaches the steady state is 90 ° C. for the dry gas D1, 87.6 ° C. for the dry gas D2, 170 ° C. for the dry gas D3, and 87.2 ° C. for the dry exhaust gas D4. .
- the opening degree of the damper 61a is preferably adjusted based on this measured value by measuring the temperature of the dry gas D1 with a temperature sensor as appropriate.
- the opening degree of the control valve 54 is preferably adjusted based on the measured value by measuring the temperature of the dry gas D3 with a temperature sensor as appropriate.
- the heat in the dry exhaust gas D4 is directly taken into the dry gas D1 together with the dry exhaust gas D4, whereby the dry gas D2 having a higher temperature than the dry gas D1 can be obtained. Since the load of the heat exchanger 50 that further raises the temperature is reduced as compared with the case where the drying gas D1 is directly heated without using the return pipe 61, the energy efficiency of the entire drying system S1 is improved. Can do.
- the drying system S ⁇ b> 2 shown in this embodiment is configured by replacing the return pipe 61 in the embodiment shown in FIG. 1 with a heat pipe 62, and the other components are the same. It was supposed to be.
- the heat pipe 62 is obtained by sealing a volatile liquid (working fluid) in a pipe 62a made of a material having high thermal conductivity, and a heat absorbing element 62b is provided at one end of the pipe 62a, and at the other end.
- the heat can be transferred by generating a cycle of evaporation of the working fluid by the heat absorbing element 62b (absorption of latent heat) and condensation of the working fluid by the heat dissipating element 62c (release of latent heat). It is a member.
- a heat absorbing element 62b is provided in a pipe line connected to the exhaust port 14 of the dryer 1, and the heat pump unit 2 and the temperature raising device 5 (heat exchanger 50) are connected to each other.
- a heat dissipating element 62c is provided in a pipe line connected therebetween.
- the state in which the outside air D0 is heated by the heat pump unit 2 is referred to as a dry gas D1.
- the dry gas D1 in which heat in the dry exhaust gas D4 exhausted from the dryer 1 is taken is referred to as a dry gas D2.
- the dry gas D2 whose temperature is raised by the temperature raising device 5 is referred to as a dry gas D3.
- the dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from the exhaust port 14 as a dry exhaust gas D4. Further, heat is recovered from the dry exhaust gas D4 by the heat pipe 62 and the temperature. Is reduced and exhausted to the outside as the dry exhaust gas D5.
- the drying system S2 is activated, the outside air D0 (20 ° C.
- the dry gas D1 is first taken in by the blower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
- heat is supplied to the dry gas D1 by the heat pipe 62 and the temperature is raised to become a dry gas D2.
- the dry gas D2 is heated in the heat exchanger 50 to become a dry gas D3.
- the dry gas D3 is fed into the dryer 1 from the air supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D4 from the exhaust port 14 in a state where the temperature is lowered. .
- the dry exhaust gas D4 is deprived of heat by the heat absorbing element 62b in the heat pipe 62, and is discharged to the outside as the dry exhaust gas D5 having a lowered temperature.
- the temperature of the dry gas D when it reaches the steady state is 60 ° C. for the dry gas D1, 74 ° C. for the dry gas D2, 160 ° C. for the dry gas D3, 88.9 ° C. for the dry exhaust gas D4, and D5 for the dry exhaust gas D5.
- the present invention by taking heat in the dry exhaust gas D4 with respect to the dry gas D1, the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of the heat exchanger 50 is reduced as compared with the case where the drying gas D1 is directly heated without using the heat pipe 62, the energy efficiency of the entire drying system S2 can be improved.
- the drying system S3 When the drying system S3 is activated, the outside air D0 (20 ° C. as an example) is first taken in by the blower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
- the dry gas D1 takes in the heat in the dry exhaust gas D4 in the heat exchanger 63 and becomes the dry gas D2.
- the dry gas D2 is heated in the heat exchanger 50 to become a dry gas D3.
- the dry gas D3 is fed into the dryer 1 from the air supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D4 from the exhaust port 14 in a state where the temperature is lowered. .
- the dry exhaust gas D4 is deprived of heat in the heat exchanger 63, and becomes dry exhaust gas D5 having a lowered temperature, and is discharged to the outside.
- the temperature of the dry gas D at the steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C. for the dry gas D2, 180 ° C. for the dry gas D3, 100 to 150 ° C. for the dry exhaust gas D4, and dried.
- the exhaust gas D5 becomes 60 to 80 ° C.
- the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of the heat exchanger 50 is reduced as compared with the case where the drying gas D1 is directly heated without using the heat exchanger 63, the energy efficiency of the entire drying system S3 can be improved.
- the drying system S ⁇ b> 4 shown in this embodiment has a configuration in which a return pipe 61 is added to the drying system S ⁇ b> 3 shown in FIG. 3. Specifically, a pipe line connected between the exhaust port 14 of the dryer 1 and the heat exchanger 63, and a connection between the heat exchanger 63 and the temperature raising device 5 (heat exchanger 50). A return pipe 61 is provided between the pipes. The return pipe 61 is provided with a damper 61a so that the flow rate of the dry exhaust gas D5 can be adjusted.
- the drying system S4 When the drying system S4 is activated, the outside air D0 (20 ° C. as an example) is first taken in by the blower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
- the dry gas D1 takes in the heat in the dry exhaust gas D5 in the heat exchanger 63 and becomes the dry gas D2.
- the dry gas D2 is mixed with an amount of dry exhaust gas D5 corresponding to the opening degree of the damper 61a to become a dry gas D21.
- the temperature of the dry gas D21 is raised in the heat exchanger 50 to become a dry gas D3.
- the dry gas D3 is fed into the dryer 1 from the air supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D5 from the exhaust port 14 in a state where the temperature is lowered. .
- the dry exhaust gas D5 is diverted according to the opening degree of the damper 61a, and a part of it is deprived of heat in the heat exchanger 63 to be discharged to the outside as the dry exhaust gas D6 having a lowered temperature.
- the remaining dry exhaust gas D5 is mixed into the dry gas D2 through the return pipe 61 as described above.
- the temperature of the dry gas D when it reaches a steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C.
- the dry gas D2 98 to 149 ° C. for the dry gas D21, 180 ° C. for the dry gas D3, and dry.
- the exhaust gas D5 is 100 to 150 ° C.
- the dry exhaust gas D6 is 60 to 80 ° C.
- temperature is higher than the dry gas D1.
- the load of the heat exchanger 50 that further raises the temperature of the dry gas D21 increases the temperature of the dry gas D1 directly without using the heat exchanger 63 and the return pipe 61. Therefore, the energy efficiency of the entire drying system S4 can be improved.
- the heat exchanger 50 is employed as the temperature raising device 5, but a direct furnace 55 may be employed as the temperature raising device 5.
- the embodiment shown in FIG. 5 shows a drying system S5 in which the heat exchanger 50 of the drying system S1 shown in FIG. Further, the heat contained in the dry exhaust gas D4, D5, D6 before being exhausted to the outside may be recovered. In this case, for example, the heat is transferred to the water W using the heat exchanger 64, and the water W is further transferred.
- the tank 65 By storing in the tank 65 and using it as a heat source for the evaporator 23 in the heat pump unit 2, it is possible to further improve energy efficiency.
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Abstract
Disclosed is a novel drying system that is equipped with a heat pump unit and an exhaust heat recovery mechanism and is capable of realizing further improvement in energy efficiency by effectively utilizing the heat collected from dry exhaust gas. The drying system, which is equipped with a dryer and an air-supplying mechanism for supplying dry gas to the dryer, is characterized in that the aforementioned dryer is a hot air dryer and the aforementioned air-supplying mechanism is equipped with the heat pump unit, and in that, in the aforementioned air-supplying mechanism, the exhaust heat recovery mechanism, which is configured in a manner capable of incorporating the heat within dry exhaust gas expelled from the aforementioned dryer into the dry gas before pumping into the dryer, is provided in a device comprising a heating device for further heating the dry gas heated by the heat pump unit.
Description
本発明は流動層乾燥機や回転ドラム式乾燥機等の連続式熱風乾燥装置を具えた乾燥システムに関するものであり、特に高温の乾燥気体が必要とされる乾燥機を乾燥システム全体としてエネルギー効率良く運転することのできるヒートポンプユニットと排熱回収機構とを具えた乾燥システムに係るものである。
The present invention relates to a drying system equipped with a continuous hot air drying device such as a fluidized bed dryer or a rotary drum dryer, and in particular, a dryer requiring a high-temperature drying gas is energy efficient as a whole drying system. The present invention relates to a drying system including an operable heat pump unit and an exhaust heat recovery mechanism.
近時、環境保全の取り組みが盛んになってきており、更にいわゆる省エネの観点から、乾燥装置において熱源としてヒートポンプユニットを適用することが試みられている。
具体的には、いわゆるバンド乾燥機に対して、フロン系の冷媒を使用したヒートポンプユニットが適用された装置が開発されている(例えば特許文献1参照)。 In recent years, environmental conservation efforts have become active, and from the viewpoint of so-called energy saving, it has been attempted to apply a heat pump unit as a heat source in a drying apparatus.
Specifically, an apparatus in which a heat pump unit using a chlorofluorocarbon refrigerant is applied to a so-called band dryer has been developed (see, for example, Patent Document 1).
具体的には、いわゆるバンド乾燥機に対して、フロン系の冷媒を使用したヒートポンプユニットが適用された装置が開発されている(例えば特許文献1参照)。 In recent years, environmental conservation efforts have become active, and from the viewpoint of so-called energy saving, it has been attempted to apply a heat pump unit as a heat source in a drying apparatus.
Specifically, an apparatus in which a heat pump unit using a chlorofluorocarbon refrigerant is applied to a so-called band dryer has been developed (see, for example, Patent Document 1).
ところで前記バンド乾燥機は、被処理物が乾燥室内に配されたネットコンベヤ等の軌道上を移動する際に、乾燥気体と接触して乾燥が行われるものであり、ネットコンベヤを多段に具えることにより、長時間での処理が可能とされたものである。
一方、比較的短時間で処理が行われる流動層乾燥機や回転ドラム式乾燥機等の連続式熱風乾燥装置においては、その熱源にヒートポンプユニットを適用することは現実的ではなかった。 By the way, the band dryer is provided with a plurality of stages of net conveyors in which drying is performed in contact with a dry gas when an object to be processed moves on a track such as a net conveyor disposed in a drying chamber. Thus, processing for a long time can be performed.
On the other hand, in a continuous hot air drying apparatus such as a fluidized bed dryer or a rotary drum dryer that performs processing in a relatively short time, it is not realistic to apply a heat pump unit to the heat source.
一方、比較的短時間で処理が行われる流動層乾燥機や回転ドラム式乾燥機等の連続式熱風乾燥装置においては、その熱源にヒートポンプユニットを適用することは現実的ではなかった。 By the way, the band dryer is provided with a plurality of stages of net conveyors in which drying is performed in contact with a dry gas when an object to be processed moves on a track such as a net conveyor disposed in a drying chamber. Thus, processing for a long time can be performed.
On the other hand, in a continuous hot air drying apparatus such as a fluidized bed dryer or a rotary drum dryer that performs processing in a relatively short time, it is not realistic to apply a heat pump unit to the heat source.
具体的には流動層乾燥機等にあっては、被処理物の乾燥機内での滞留時間(処理時間)が短く、更に乾燥初期の段階で高温の乾燥気体が必要とされるため、フロン系の冷媒を使用したヒートポンプでは得られる熱風の温度が50℃程度であり、短時間で乾燥するのに必要な温度が得られないことから、乾燥機を大型化する等して対応する必要があり、効率的な運転をすることができず、かえってコスト上昇を招いてしまうこととなるのである。
Specifically, in fluidized bed dryers, etc., the residence time (processing time) of the object to be processed in the dryer is short, and a high temperature dry gas is required at the initial stage of drying. In the heat pump using the above refrigerant, the temperature of the hot air obtained is about 50 ° C., and the temperature necessary for drying in a short time cannot be obtained. Therefore, it is necessary to cope with such as increasing the size of the dryer. Therefore, it is impossible to operate efficiently, which leads to an increase in cost.
そこで本出願人は、連続式熱風乾燥装置に対して高温の乾燥気体を供給するための機器としてヒートポンプユニットを適用することを可能にするとともに、乾燥システム全体としてのエネルギー効率が高く、更に高エネルギー効率で安定した運転を行うことのできる、新規なヒートポンプユニットと昇温装置とを具えた乾燥システムを開発し、既に特許出願に及んでいる(特許文献2参照)。
そして本出願人は、その後もこの種のヒートポンプユニットを具えた乾燥システムの研究・開発を継続しており、特に乾燥排ガスに含まれる熱を有効に利用することに着目した。
もちろん熱風乾燥装置から排出される乾燥排ガス中の熱を回収して有効利用することは広く行われているが、系全体での省エネルギー効果が期待できない場合もあった。
すなわち、乾燥排ガスの温度が、乾燥装置に供給される乾燥気体の温度よりも大幅に低下しない場合には(例えば蒸発量が少ない場合や熱処理を行う場合)、多くの熱量を回収することができるため、系全体としての省エネルギーに貢献することができる。
一方、被処理物と乾燥気体との接触効率が良い、流動層乾燥機や回転通気式乾燥機等の連続式熱風乾燥装置においては、乾燥排ガスの温度が、乾燥装置に供給される乾燥気体の温度よりも大幅に低下してしまうため(例えば160℃→90℃)、系全体として大きな省エネルギー効果が得られるものではなく、乾燥排ガス中の熱回収は通常、行われていなかった。 Therefore, the present applicant makes it possible to apply a heat pump unit as a device for supplying a high-temperature dry gas to a continuous hot-air dryer, and the energy efficiency of the entire drying system is high, and further high energy A drying system comprising a novel heat pump unit and a temperature raising device capable of performing an efficient and stable operation has been developed and has already been filed for a patent (see Patent Document 2).
The applicant has continued to research and develop a drying system including this type of heat pump unit, and has paid particular attention to the effective use of heat contained in the dry exhaust gas.
Of course, it is widely practiced to recover and effectively use the heat in the dry exhaust gas discharged from the hot air dryer, but there are cases where the energy saving effect of the entire system cannot be expected.
That is, when the temperature of the dry exhaust gas is not significantly lower than the temperature of the dry gas supplied to the drying apparatus (for example, when the amount of evaporation is small or when heat treatment is performed), a large amount of heat can be recovered. Therefore, it can contribute to energy saving as the whole system.
On the other hand, in a continuous hot air drying device such as a fluidized bed dryer or rotary aeration dryer, where the contact efficiency between the object to be processed and the drying gas is good, the temperature of the drying exhaust gas is the temperature of the drying gas supplied to the drying device. Since the temperature is significantly lower than the temperature (for example, 160 ° C. → 90 ° C.), a large energy saving effect is not obtained as a whole system, and heat recovery in the dry exhaust gas has not been usually performed.
そして本出願人は、その後もこの種のヒートポンプユニットを具えた乾燥システムの研究・開発を継続しており、特に乾燥排ガスに含まれる熱を有効に利用することに着目した。
もちろん熱風乾燥装置から排出される乾燥排ガス中の熱を回収して有効利用することは広く行われているが、系全体での省エネルギー効果が期待できない場合もあった。
すなわち、乾燥排ガスの温度が、乾燥装置に供給される乾燥気体の温度よりも大幅に低下しない場合には(例えば蒸発量が少ない場合や熱処理を行う場合)、多くの熱量を回収することができるため、系全体としての省エネルギーに貢献することができる。
一方、被処理物と乾燥気体との接触効率が良い、流動層乾燥機や回転通気式乾燥機等の連続式熱風乾燥装置においては、乾燥排ガスの温度が、乾燥装置に供給される乾燥気体の温度よりも大幅に低下してしまうため(例えば160℃→90℃)、系全体として大きな省エネルギー効果が得られるものではなく、乾燥排ガス中の熱回収は通常、行われていなかった。 Therefore, the present applicant makes it possible to apply a heat pump unit as a device for supplying a high-temperature dry gas to a continuous hot-air dryer, and the energy efficiency of the entire drying system is high, and further high energy A drying system comprising a novel heat pump unit and a temperature raising device capable of performing an efficient and stable operation has been developed and has already been filed for a patent (see Patent Document 2).
The applicant has continued to research and develop a drying system including this type of heat pump unit, and has paid particular attention to the effective use of heat contained in the dry exhaust gas.
Of course, it is widely practiced to recover and effectively use the heat in the dry exhaust gas discharged from the hot air dryer, but there are cases where the energy saving effect of the entire system cannot be expected.
That is, when the temperature of the dry exhaust gas is not significantly lower than the temperature of the dry gas supplied to the drying apparatus (for example, when the amount of evaporation is small or when heat treatment is performed), a large amount of heat can be recovered. Therefore, it can contribute to energy saving as the whole system.
On the other hand, in a continuous hot air drying device such as a fluidized bed dryer or rotary aeration dryer, where the contact efficiency between the object to be processed and the drying gas is good, the temperature of the drying exhaust gas is the temperature of the drying gas supplied to the drying device. Since the temperature is significantly lower than the temperature (for example, 160 ° C. → 90 ° C.), a large energy saving effect is not obtained as a whole system, and heat recovery in the dry exhaust gas has not been usually performed.
本発明はこのような背景からなされたものであって、連続式熱風乾燥装置に対して高温の乾燥気体を供給するための機器としてヒートポンプユニットを適用することにより、乾燥システム全体としてのエネルギー効率が高く、更に高エネルギー効率で安定した運転を行うことのできる乾燥システムにおいて、乾燥排ガスから回収した熱を有効活用することにより、更なるエネルギー効率の向上を実現することのできる、新規なヒートポンプユニットと排熱回収機構とを具えた乾燥システムの開発を技術課題としたものである。
The present invention has been made from such a background, and by applying a heat pump unit as a device for supplying a high-temperature dry gas to a continuous hot air drying device, the energy efficiency of the entire drying system can be improved. A new heat pump unit that can further improve energy efficiency by effectively utilizing the heat recovered from the dry exhaust gas in a high drying system that can operate stably with high energy efficiency. The technical issue is the development of a drying system with a waste heat recovery mechanism.
すなわち請求項1記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システムは、乾燥機と、この乾燥機に乾燥気体を供給するための給気機構とを具えた乾燥システムにおいて、前記乾燥機は熱風乾燥機であり、また前記給気機構はヒートポンプユニットを具えて成るものであり、更に前記給気機構には、ヒートポンプユニットにより昇温された乾燥気体を、更に昇温するための昇温装置が具えられて成り、更に前記乾燥機から排気された乾燥排ガス中の熱を、乾燥機に投入する前の乾燥気体に取り込むことができるように構成された排熱回収機構が具えられていることを特徴として成るものである。
That is, a drying system comprising a heat pump unit and an exhaust heat recovery mechanism according to claim 1 is a drying system comprising a dryer and an air supply mechanism for supplying a drying gas to the dryer. Is a hot air dryer, and the air supply mechanism is provided with a heat pump unit, and the air supply mechanism further includes a temperature rise for heating the dry gas heated by the heat pump unit. And an exhaust heat recovery mechanism configured to be able to take heat in the dry exhaust gas exhausted from the dryer into the dry gas before being charged into the dryer. It is characterized by this.
また請求項2記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システムは、前記請求項1記載の要件に加え、前記排熱回収機構は、乾燥排ガス中の熱を、乾燥排ガスの一部を乾燥気体に合流されることにより、乾燥気体に取り込むように構成されたものであることを特徴として成るものである。
A drying system comprising a heat pump unit and an exhaust heat recovery mechanism according to claim 2 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas to a part of the dry exhaust gas. Are combined with the dry gas so as to be taken into the dry gas.
更にまた請求項3記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システムは、前記請求項1記載の要件に加え、前記排熱回収機構は、乾燥排ガス中の熱を、ヒートパイプによって回収し、その後、乾燥気体に取り込むように構成されたものであることを特徴として成るものである。
Furthermore, the drying system including the heat pump unit and the exhaust heat recovery mechanism according to claim 3 adds to the requirements of claim 1, and the exhaust heat recovery mechanism recovers the heat in the dry exhaust gas by a heat pipe. Then, after that, it is configured to be taken into the dry gas.
更にまた請求項4記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システムは、前記請求項1記載の要件に加え、前記排熱回収機構は、乾燥排ガス中の熱を、熱交換器を用いて乾燥気体に取り込むように構成されたものであることを特徴として成るものである。
Furthermore, the drying system including the heat pump unit and the exhaust heat recovery mechanism according to claim 4 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas to a heat exchanger. It is characterized in that it is configured to be taken into a dry gas.
更にまた請求項5記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システムは、前記請求項1記載の要件に加え、前記排熱回収機構は、乾燥排ガス中の熱を、乾燥排ガスの一部を乾燥気体に合流されることにより乾燥気体に取り込むものであり、且つ乾燥排ガス中の熱を、熱交換器を用いて乾燥気体に取り込むように構成されたものであることを特徴として成るものである。
そしてこれら各請求項記載の発明の構成を手段として前記課題の解決が図られる。 Furthermore, the drying system comprising the heat pump unit and the exhaust heat recovery mechanism according toclaim 5 adds to the requirements of claim 1, and the exhaust heat recovery mechanism converts the heat in the dry exhaust gas into one of the dry exhaust gases. The part is taken into the dry gas by being merged with the dry gas, and the heat in the dry exhaust gas is taken into the dry gas using a heat exchanger. It is.
The above problems can be solved by using the configuration of the invention described in each of the claims as a means.
そしてこれら各請求項記載の発明の構成を手段として前記課題の解決が図られる。 Furthermore, the drying system comprising the heat pump unit and the exhaust heat recovery mechanism according to
The above problems can be solved by using the configuration of the invention described in each of the claims as a means.
まず請求項1記載の発明によれば、乾燥機から排気された乾燥排ガス中の熱を、乾燥機に投入する前の乾燥気体に取り込むことにより、ヒートポンプユニットと乾燥機との間に設けられる、乾燥気体の昇温装置において必要とされる熱エネルギーを減少させ、乾燥システム全体のエネルギー効率を向上することができる。
First, according to the first aspect of the invention, the heat in the dry exhaust gas exhausted from the dryer is provided between the heat pump unit and the dryer by taking in the dry gas before being charged into the dryer. The thermal energy required in the drying gas temperature raising device can be reduced, and the energy efficiency of the entire drying system can be improved.
また請求項2記載の発明によれば、乾燥排ガスに含まれる熱を、乾燥排ガスとともに直接、乾燥気体に取り込むことができ、乾燥システム全体のエネルギー効率を向上することができる。
Further, according to the invention described in claim 2, the heat contained in the dry exhaust gas can be directly taken into the dry gas together with the dry exhaust gas, and the energy efficiency of the entire drying system can be improved.
更にまた請求項3記載の発明によれば、乾燥排ガスに含まれる熱を、ヒートパイプによって高効率で乾燥気体に取り込むことができ、乾燥システム全体のエネルギー効率を向上することができる。
Furthermore, according to the invention of claim 3, the heat contained in the dry exhaust gas can be taken into the dry gas with high efficiency by the heat pipe, and the energy efficiency of the entire drying system can be improved.
更にまた請求項4記載の発明によれば、乾燥排ガスに含まれる熱を、熱交換器によって高効率で乾燥気体に取り込むことができ、乾燥システム全体のエネルギー効率を向上することができる。
Furthermore, according to the invention of claim 4, the heat contained in the dry exhaust gas can be taken into the dry gas with high efficiency by the heat exchanger, and the energy efficiency of the entire drying system can be improved.
更にまた請求項5記載の発明によれば、乾燥排ガスに含まれる熱を、乾燥排ガスとともに直接、乾燥気体に取り込むとともに、熱交換器によって高効率で乾燥気体に取り込むことができ、乾燥システム全体のエネルギー効率を向上することができる。
Furthermore, according to the invention described in claim 5, the heat contained in the dry exhaust gas can be directly taken into the dry gas together with the dry exhaust gas, and can be taken into the dry gas with high efficiency by the heat exchanger. Energy efficiency can be improved.
本発明のヒートポンプユニットと排熱回収機構とを具えた乾燥システムの形態は、一例として以下の実施例に示すとおりであるが、この実施例に対して本発明の技術的思想の範囲内において適宜変更を加えることも可能である。
The form of the drying system provided with the heat pump unit and the exhaust heat recovery mechanism of the present invention is as shown in the following examples as an example, but this example is appropriately within the scope of the technical idea of the present invention. It is also possible to make changes.
本発明のヒートポンプユニットと排熱回収機構とを具えた乾燥システムS(以下、乾燥システムSと称す)は、乾燥機1と、この乾燥機1に乾燥気体Dを供給するための給気機構とを具えて成るものである。具体的には、乾燥機1並びに給気機構を構成するヒートポンプユニット2、昇温装置5及び排熱回収機構6が主要要素として具えられる。
なお乾燥気体Dとは、外気D0が昇温された状態の乾燥気体D1、D2、D3・・・を総称するものである。
また本発明の乾燥システムSは、乾燥機1として熱風乾燥機が適用されるものであり、乾燥機1内での被処理物Hの滞留時間(処理時間)が短く、更に乾燥初期の段階で高温の乾燥気体Dが必要とされる連続式の乾燥機1による乾燥処理を、ヒートポンプユニット2を用い、エネルギー効率が高く、更に安定した状態で行うことができるようにしたものである。
以下、排熱回収機構6の構成を異ならせた実施例毎に説明を行う。 A drying system S (hereinafter referred to as a drying system S) including a heat pump unit and an exhaust heat recovery mechanism according to the present invention includes a dryer 1 and an air supply mechanism for supplying a drying gas D to the dryer 1. It consists of. Specifically, the dryer 1 and theheat pump unit 2, the temperature raising device 5, and the exhaust heat recovery mechanism 6 constituting the air supply mechanism are provided as main elements.
The dry gas D is a general term for the dry gases D1, D2, D3,.
In the drying system S of the present invention, a hot air dryer is applied as the dryer 1, and the residence time (processing time) of the workpiece H in the dryer 1 is short, and further at the initial stage of drying. The drying process by the continuous dryer 1 that requires the high-temperature drying gas D is performed using theheat pump unit 2 with high energy efficiency and in a more stable state.
Hereinafter, description will be made for each embodiment in which the configuration of the exhaustheat recovery mechanism 6 is different.
なお乾燥気体Dとは、外気D0が昇温された状態の乾燥気体D1、D2、D3・・・を総称するものである。
また本発明の乾燥システムSは、乾燥機1として熱風乾燥機が適用されるものであり、乾燥機1内での被処理物Hの滞留時間(処理時間)が短く、更に乾燥初期の段階で高温の乾燥気体Dが必要とされる連続式の乾燥機1による乾燥処理を、ヒートポンプユニット2を用い、エネルギー効率が高く、更に安定した状態で行うことができるようにしたものである。
以下、排熱回収機構6の構成を異ならせた実施例毎に説明を行う。 A drying system S (hereinafter referred to as a drying system S) including a heat pump unit and an exhaust heat recovery mechanism according to the present invention includes a dryer 1 and an air supply mechanism for supplying a drying gas D to the dryer 1. It consists of. Specifically, the dryer 1 and the
The dry gas D is a general term for the dry gases D1, D2, D3,.
In the drying system S of the present invention, a hot air dryer is applied as the dryer 1, and the residence time (processing time) of the workpiece H in the dryer 1 is short, and further at the initial stage of drying. The drying process by the continuous dryer 1 that requires the high-temperature drying gas D is performed using the
Hereinafter, description will be made for each embodiment in which the configuration of the exhaust
〔排熱回収機構として戻し管路を用いた実施例〕(図1参照)
まず前記乾燥機1は熱風乾燥機の一例である連続式の流動層乾燥機が適用される。この乾燥機1は、筐体10内を乾燥のための処理空間とするものであり、処理空間を上下に分割するように設けられた通気板11の下方から乾燥気体Dが供給され、通気板11上に位置する被処理物Hに流動層を形成させながら乾燥を行うものである。
このため筐体10の下部には、一例として二箇所に給気口12が形成され、また前方(図1中、左側)上部には投入口13が形成され、更に後方(図1中、右側)上部には排気口14が形成され、更に後方且つ通気板11よりも上方の個所に接続されるダクト10aに対して排出口15が形成される。
また乾燥機1の周辺機器として、吹込ファン16び排気ファン17が具えられるものであり、これらの接続状態については後程、詳しく説明する。 [Example using return pipe as exhaust heat recovery mechanism] (See Fig. 1)
First, the dryer 1 is a continuous fluidized bed dryer which is an example of a hot air dryer. The dryer 1 uses the inside of thehousing 10 as a processing space for drying. The drying gas D is supplied from below the ventilation plate 11 provided so as to divide the processing space vertically, and the ventilation plate 11 is dried while forming a fluidized bed on the workpiece H located on the substrate 11.
For this reason, theair inlet 12 is formed in two places as an example in the lower part of the housing | casing 10, and the inlet 13 is formed in the front (left side in FIG. 1) upper part, and also the rear (right side in FIG. 1). ) An exhaust port 14 is formed in the upper part, and an exhaust port 15 is formed for the duct 10a connected to the rear side and above the vent plate 11.
Further, the peripheral device of the dryer 1 is provided with ablower fan 16 and an exhaust fan 17, and the connection state thereof will be described in detail later.
まず前記乾燥機1は熱風乾燥機の一例である連続式の流動層乾燥機が適用される。この乾燥機1は、筐体10内を乾燥のための処理空間とするものであり、処理空間を上下に分割するように設けられた通気板11の下方から乾燥気体Dが供給され、通気板11上に位置する被処理物Hに流動層を形成させながら乾燥を行うものである。
このため筐体10の下部には、一例として二箇所に給気口12が形成され、また前方(図1中、左側)上部には投入口13が形成され、更に後方(図1中、右側)上部には排気口14が形成され、更に後方且つ通気板11よりも上方の個所に接続されるダクト10aに対して排出口15が形成される。
また乾燥機1の周辺機器として、吹込ファン16び排気ファン17が具えられるものであり、これらの接続状態については後程、詳しく説明する。 [Example using return pipe as exhaust heat recovery mechanism] (See Fig. 1)
First, the dryer 1 is a continuous fluidized bed dryer which is an example of a hot air dryer. The dryer 1 uses the inside of the
For this reason, the
Further, the peripheral device of the dryer 1 is provided with a
なおこの実施例では、前記通気板11の中程に堰板11aが設けられ、ある程度乾燥の進んだ被処理物Hがこの堰板11aを乗り越えて次の乾燥段階に移行するような構成が採られるようにした。
またこの実施例では、乾燥機1として流動層乾燥機が採用されたが、流動層造粒乾燥機、バンド乾燥機あるいは気流乾燥機等、他の熱風乾燥機を採用することもできる。 In this embodiment, a configuration is adopted in which adam plate 11a is provided in the middle of the ventilation plate 11, and the workpiece H that has been dried to some extent passes over the dam plate 11a and moves to the next drying stage. I was able to.
Further, in this embodiment, a fluidized bed dryer is adopted as the dryer 1, but other hot air dryers such as a fluidized bed granulator dryer, a band dryer or an air dryer can also be adopted.
またこの実施例では、乾燥機1として流動層乾燥機が採用されたが、流動層造粒乾燥機、バンド乾燥機あるいは気流乾燥機等、他の熱風乾燥機を採用することもできる。 In this embodiment, a configuration is adopted in which a
Further, in this embodiment, a fluidized bed dryer is adopted as the dryer 1, but other hot air dryers such as a fluidized bed granulator dryer, a band dryer or an air dryer can also be adopted.
次に前記ヒートポンプユニット2について説明すると、このものは、凝縮器21と、膨張弁22と、蒸発器23と、圧縮機24とを具えてヒートポンプサイクルを形成するものであり、一例として二酸化炭素を冷媒とするものが採用される。なお前記冷媒として二酸化炭素を採用することにより、ヒートポンプユニット2で昇温される乾燥気体Dの温度を高くすることができるものである。因みに現状では、二酸化炭素を冷媒としたヒートポンプユニット2が、乾燥気体Dの温度を高くすることができるものとして実用化されているが、今後、他の冷媒を用いた同等の性能を有するヒートポンプユニット2が実用化された場合には、これを採用することもできる。
なお個々の給気口12に対してそれぞれ専用のヒートポンプユニット2を接続するようにしてもよい。 Next, theheat pump unit 2 will be described. The heat pump unit 2 includes a condenser 21, an expansion valve 22, an evaporator 23, and a compressor 24 to form a heat pump cycle. As an example, carbon dioxide is used. A refrigerant is used. In addition, the temperature of the dry gas D heated by the heat pump unit 2 can be increased by employing carbon dioxide as the refrigerant. Incidentally, at present, the heat pump unit 2 using carbon dioxide as a refrigerant has been put into practical use as being capable of increasing the temperature of the dry gas D, but in the future, a heat pump unit having equivalent performance using other refrigerants will be used. When 2 is put into practical use, this can also be adopted.
A dedicatedheat pump unit 2 may be connected to each air supply port 12.
なお個々の給気口12に対してそれぞれ専用のヒートポンプユニット2を接続するようにしてもよい。 Next, the
A dedicated
また前記昇温装置5は図1に示すように、一例としてプレートフィン式の熱交換器50を主要部材として構成されるものであり、この熱交換器50の内部には、複数の放熱フィン51が側周に具えられたパイプ52が配されている。そしてパイプ52内を通過する流体(蒸気等)と、放熱フィン51に接する流体(乾燥気体D1)との間で熱交換が行われる。なお前記パイプ52への蒸気等の流入量は調節弁54によって調節され、これにより乾燥気体D1の昇温度が調節される。
なお昇温装置5としては図5に示すような直火炉55を採用することも可能であり、これについては後程詳しく説明する。 Further, as shown in FIG. 1, thetemperature raising device 5 includes, as an example, a plate fin type heat exchanger 50 as a main member, and a plurality of radiating fins 51 are provided inside the heat exchanger 50. A pipe 52 provided on the side periphery is arranged. And heat exchange is performed between the fluid (steam etc.) which passes through the inside of the pipe 52, and the fluid (dry gas D1) which contacts the radiation fin 51. The inflow amount of steam or the like into the pipe 52 is adjusted by a control valve 54, and thereby the rising temperature of the dry gas D1 is adjusted.
It is possible to employ adirect furnace 55 as shown in FIG. 5 as the temperature raising device 5, which will be described in detail later.
なお昇温装置5としては図5に示すような直火炉55を採用することも可能であり、これについては後程詳しく説明する。 Further, as shown in FIG. 1, the
It is possible to employ a
そして図1に示すように、前記乾燥機1、ヒートポンプユニット2及び昇温装置5を組み合わせて乾燥システムS1が構成されるものであり、昇温装置5の入力側に吹込ファン16が接続される。
更に前記乾燥機1から排気された乾燥排ガスD4中の熱を、乾燥機1に投入する前の乾燥気体D1に取り込むための排熱回収機構6が構成されるものであり、この実施例では排気口14から排出される乾燥排ガスD4の一部を、戻し管路61を通じて乾燥気体D1に合流させることにより、乾燥排ガスD4中の熱を乾燥気体D1に取り込むようにして構成される。
このため前記戻し管路61は、乾燥機1の排気口14に接続される管路と、ヒートポンプユニット2と昇温装置5(熱交換器50)との間に接続される管路との間に設けられる。
なお前記戻し管路61には、ダンパ61aを具えることにより、乾燥排ガスD4の流量を調整できるようにした。 And as shown in FIG. 1, the drying system S1 is comprised combining the said dryer 1, theheat pump unit 2, and the temperature raising apparatus 5, and the blowing fan 16 is connected to the input side of the temperature raising apparatus 5. As shown in FIG. .
Further, an exhaustheat recovery mechanism 6 for taking in heat in the dry exhaust gas D4 exhausted from the dryer 1 into the dry gas D1 before being input to the dryer 1 is configured. In this embodiment, exhaust gas is exhausted. A part of the dry exhaust gas D4 discharged from the port 14 is joined to the dry gas D1 through the return pipe 61, so that the heat in the dry exhaust gas D4 is taken into the dry gas D1.
Therefore, thereturn line 61 is between the line connected to the exhaust port 14 of the dryer 1 and the line connected between the heat pump unit 2 and the temperature raising device 5 (heat exchanger 50). Is provided.
Thereturn pipe 61 is provided with a damper 61a so that the flow rate of the dry exhaust gas D4 can be adjusted.
更に前記乾燥機1から排気された乾燥排ガスD4中の熱を、乾燥機1に投入する前の乾燥気体D1に取り込むための排熱回収機構6が構成されるものであり、この実施例では排気口14から排出される乾燥排ガスD4の一部を、戻し管路61を通じて乾燥気体D1に合流させることにより、乾燥排ガスD4中の熱を乾燥気体D1に取り込むようにして構成される。
このため前記戻し管路61は、乾燥機1の排気口14に接続される管路と、ヒートポンプユニット2と昇温装置5(熱交換器50)との間に接続される管路との間に設けられる。
なお前記戻し管路61には、ダンパ61aを具えることにより、乾燥排ガスD4の流量を調整できるようにした。 And as shown in FIG. 1, the drying system S1 is comprised combining the said dryer 1, the
Further, an exhaust
Therefore, the
The
本発明の乾燥システムS1は、一例として上述したように構成されるものであり、以下、その作動態様について説明する。
初めに被処理物Hの乾燥に寄与する乾燥気体Dの流れについて説明する。なお乾燥気体Dとは昇温された外気D0を総称するものであり、外気D0がヒートポンプユニット2によって昇温された状態のものを乾燥気体D1と称する。またこの乾燥気体D1に乾燥機1から排気された乾燥排ガスD4中の熱が取り込まれた状態のものを乾燥気体D2と称する。更にまたこの乾燥気体D2が昇温装置5によって昇温されたものを乾燥気体D3と称する。
また前記乾燥気体D3は、乾燥機1内において被処理物Hに作用するものであり、その後、乾燥排ガスD4として排気口14から排気される。 The drying system S1 of the present invention is configured as described above as an example, and the operation mode thereof will be described below.
First, the flow of the dry gas D that contributes to the drying of the workpiece H will be described. The dry gas D is a general term for the heated outside air D0, and a state in which the outside air D0 is heated by theheat pump unit 2 is called a dry gas D1. The dry gas D1 in which heat in the dry exhaust gas D4 exhausted from the dryer 1 is taken is referred to as a dry gas D2. Further, the dry gas D2 whose temperature is raised by the temperature raising device 5 is referred to as a dry gas D3.
The dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from theexhaust port 14 as the dry exhaust gas D4.
初めに被処理物Hの乾燥に寄与する乾燥気体Dの流れについて説明する。なお乾燥気体Dとは昇温された外気D0を総称するものであり、外気D0がヒートポンプユニット2によって昇温された状態のものを乾燥気体D1と称する。またこの乾燥気体D1に乾燥機1から排気された乾燥排ガスD4中の熱が取り込まれた状態のものを乾燥気体D2と称する。更にまたこの乾燥気体D2が昇温装置5によって昇温されたものを乾燥気体D3と称する。
また前記乾燥気体D3は、乾燥機1内において被処理物Hに作用するものであり、その後、乾燥排ガスD4として排気口14から排気される。 The drying system S1 of the present invention is configured as described above as an example, and the operation mode thereof will be described below.
First, the flow of the dry gas D that contributes to the drying of the workpiece H will be described. The dry gas D is a general term for the heated outside air D0, and a state in which the outside air D0 is heated by the
The dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from the
そして乾燥システムS1が起動されると、まず外気D0(一例として20℃)が吹込ファン16により取り込まれ(5785kg-dryair/h)、次いでヒートポンプユニット2における凝縮器21において昇温されて乾燥気体D1となる。
次いで乾燥気体D1には、戻し管路61から乾燥排ガスD4(7071kg-dryair/h)が混入されて乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となって給気口12から乾燥機1内に送り込まれる。 When the drying system S1 is started, the outside air D0 (20 ° C. as an example) is first taken in by the blower fan 16 (5785 kg-dryair / h), and then the temperature is raised in thecondenser 21 in the heat pump unit 2 to dry the gas D1. It becomes.
Next, dry exhaust gas D4 (7071 kg-dryair / h) is mixed into the dry gas D1 from thereturn pipe 61 to become a dry gas D2.
Next, the temperature of the dry gas D2 is raised in theheat exchanger 50, and the dry gas D2 is fed into the dryer 1 from the air supply port 12 as the dry gas D3.
次いで乾燥気体D1には、戻し管路61から乾燥排ガスD4(7071kg-dryair/h)が混入されて乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となって給気口12から乾燥機1内に送り込まれる。 When the drying system S1 is started, the outside air D0 (20 ° C. as an example) is first taken in by the blower fan 16 (5785 kg-dryair / h), and then the temperature is raised in the
Next, dry exhaust gas D4 (7071 kg-dryair / h) is mixed into the dry gas D1 from the
Next, the temperature of the dry gas D2 is raised in the
そして乾燥機1に対して供給された食品原料等の被処理物Hは、乾燥気体D3によって流動層が形成されるとともに、水分等の揮発分が除去される。
やがて被処理物Hは、乾燥の進行とともに自重が軽くなり、堰板11aを乗り越えて所望の乾燥状態となって排出口15から外部に排出される。
一方、被処理物Hに作用した後の乾燥気体D3は温度が低下し、乾燥排ガスD4となって排気口14から乾燥機1の外部に排気される。
そしてダンパ61aの開度に応じた量の乾燥排ガスD4(全量の30~50%)が戻し管路61に取り込まれ、ここからヒートポンプユニット2と熱交換器50との間に接続される管路に送られ、ここで乾燥気体D1に混入されることとなる。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が90℃、乾燥気体D2が87.6℃、乾燥気体D3が170℃、乾燥排ガスD4が87.2℃となる。 And the to-be-processed objects H, such as a food raw material supplied with respect to the dryer 1, a fluidized bed is formed with the dry gas D3, and volatile matters, such as a water | moisture content, are removed.
Eventually, the workpiece H becomes lighter in weight as the drying progresses, gets over thebarrier plate 11a, becomes a desired dry state, and is discharged to the outside from the discharge port 15.
On the other hand, the temperature of the dry gas D3 after acting on the workpiece H decreases and becomes a dry exhaust gas D4, which is exhausted from theexhaust port 14 to the outside of the dryer 1.
Then, the amount of dry exhaust gas D4 (30 to 50% of the total amount) corresponding to the opening degree of thedamper 61a is taken into the return pipe 61, and from here the pipe connected between the heat pump unit 2 and the heat exchanger 50 And mixed with the dry gas D1 here.
As an example, the temperature of the dry gas D when it reaches the steady state is 90 ° C. for the dry gas D1, 87.6 ° C. for the dry gas D2, 170 ° C. for the dry gas D3, and 87.2 ° C. for the dry exhaust gas D4. .
やがて被処理物Hは、乾燥の進行とともに自重が軽くなり、堰板11aを乗り越えて所望の乾燥状態となって排出口15から外部に排出される。
一方、被処理物Hに作用した後の乾燥気体D3は温度が低下し、乾燥排ガスD4となって排気口14から乾燥機1の外部に排気される。
そしてダンパ61aの開度に応じた量の乾燥排ガスD4(全量の30~50%)が戻し管路61に取り込まれ、ここからヒートポンプユニット2と熱交換器50との間に接続される管路に送られ、ここで乾燥気体D1に混入されることとなる。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が90℃、乾燥気体D2が87.6℃、乾燥気体D3が170℃、乾燥排ガスD4が87.2℃となる。 And the to-be-processed objects H, such as a food raw material supplied with respect to the dryer 1, a fluidized bed is formed with the dry gas D3, and volatile matters, such as a water | moisture content, are removed.
Eventually, the workpiece H becomes lighter in weight as the drying progresses, gets over the
On the other hand, the temperature of the dry gas D3 after acting on the workpiece H decreases and becomes a dry exhaust gas D4, which is exhausted from the
Then, the amount of dry exhaust gas D4 (30 to 50% of the total amount) corresponding to the opening degree of the
As an example, the temperature of the dry gas D when it reaches the steady state is 90 ° C. for the dry gas D1, 87.6 ° C. for the dry gas D2, 170 ° C. for the dry gas D3, and 87.2 ° C. for the dry exhaust gas D4. .
なお前記ダンパ61aの開度は、適宜温度センサによって乾燥気体D1の温度を測定し、この測定値に基づいて調節するようにすることが好ましい。
また前記調節弁54の開度は、適宜温度センサによって乾燥気体D3の温度を測定し、この測定値に基づいて調節されるようにすることが好ましい。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を、乾燥排ガスD4とともに直接取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を戻し管路61を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS1全体のエネルギー効率を向上することができる。 The opening degree of thedamper 61a is preferably adjusted based on this measured value by measuring the temperature of the dry gas D1 with a temperature sensor as appropriate.
The opening degree of thecontrol valve 54 is preferably adjusted based on the measured value by measuring the temperature of the dry gas D3 with a temperature sensor as appropriate.
As described above, according to the present invention, the heat in the dry exhaust gas D4 is directly taken into the dry gas D1 together with the dry exhaust gas D4, whereby the dry gas D2 having a higher temperature than the dry gas D1 can be obtained. Since the load of theheat exchanger 50 that further raises the temperature is reduced as compared with the case where the drying gas D1 is directly heated without using the return pipe 61, the energy efficiency of the entire drying system S1 is improved. Can do.
また前記調節弁54の開度は、適宜温度センサによって乾燥気体D3の温度を測定し、この測定値に基づいて調節されるようにすることが好ましい。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を、乾燥排ガスD4とともに直接取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を戻し管路61を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS1全体のエネルギー効率を向上することができる。 The opening degree of the
The opening degree of the
As described above, according to the present invention, the heat in the dry exhaust gas D4 is directly taken into the dry gas D1 together with the dry exhaust gas D4, whereby the dry gas D2 having a higher temperature than the dry gas D1 can be obtained. Since the load of the
〔排熱回収機構としてヒートパイプを用いた実施例〕(図2参照)
次いで排熱回収機構6としてヒートパイプ62を用いた実施例について説明する。この実施例で示す乾燥システムS2は図2に示すように、図1で示した実施例における戻し管路61をヒートパイプ62に置き換えて構成されるものであり、その他の構成要素については同様のものとした。
ここで前記ヒートパイプ62は、熱伝導性が高い材質からなるパイプ62a中に揮発性の液体(作動液)を封入したものであり、パイプ62aの一端に吸熱素子62bが具えられ、他端に放熱素子62cが具えられることにより、吸熱素子62bによる作動液の蒸発(潜熱の吸収)と、放熱素子62cによる作動液の凝縮(潜熱の放出)のサイクルを発生させて熱を移動することのできる部材である。
そしてこの実施例で示す乾燥システムS2においては、乾燥機1の排気口14に接続される管路に吸熱素子62bが設けられ、またヒートポンプユニット2と昇温装置5(熱交換器50)との間に接続される管路に放熱素子62cが設けられる。そしてこのような構成が採られることにより、乾燥排ガスD4中の熱は、作動液を媒介して乾燥気体D1に取り込まれることとなる。 [Example using heat pipe as exhaust heat recovery mechanism] (See Fig. 2)
Next, an embodiment using aheat pipe 62 as the exhaust heat recovery mechanism 6 will be described. As shown in FIG. 2, the drying system S <b> 2 shown in this embodiment is configured by replacing the return pipe 61 in the embodiment shown in FIG. 1 with a heat pipe 62, and the other components are the same. It was supposed to be.
Here, theheat pipe 62 is obtained by sealing a volatile liquid (working fluid) in a pipe 62a made of a material having high thermal conductivity, and a heat absorbing element 62b is provided at one end of the pipe 62a, and at the other end. By providing the heat dissipating element 62c, the heat can be transferred by generating a cycle of evaporation of the working fluid by the heat absorbing element 62b (absorption of latent heat) and condensation of the working fluid by the heat dissipating element 62c (release of latent heat). It is a member.
In the drying system S2 shown in this embodiment, aheat absorbing element 62b is provided in a pipe line connected to the exhaust port 14 of the dryer 1, and the heat pump unit 2 and the temperature raising device 5 (heat exchanger 50) are connected to each other. A heat dissipating element 62c is provided in a pipe line connected therebetween. By adopting such a configuration, the heat in the dry exhaust gas D4 is taken into the dry gas D1 through the hydraulic fluid.
次いで排熱回収機構6としてヒートパイプ62を用いた実施例について説明する。この実施例で示す乾燥システムS2は図2に示すように、図1で示した実施例における戻し管路61をヒートパイプ62に置き換えて構成されるものであり、その他の構成要素については同様のものとした。
ここで前記ヒートパイプ62は、熱伝導性が高い材質からなるパイプ62a中に揮発性の液体(作動液)を封入したものであり、パイプ62aの一端に吸熱素子62bが具えられ、他端に放熱素子62cが具えられることにより、吸熱素子62bによる作動液の蒸発(潜熱の吸収)と、放熱素子62cによる作動液の凝縮(潜熱の放出)のサイクルを発生させて熱を移動することのできる部材である。
そしてこの実施例で示す乾燥システムS2においては、乾燥機1の排気口14に接続される管路に吸熱素子62bが設けられ、またヒートポンプユニット2と昇温装置5(熱交換器50)との間に接続される管路に放熱素子62cが設けられる。そしてこのような構成が採られることにより、乾燥排ガスD4中の熱は、作動液を媒介して乾燥気体D1に取り込まれることとなる。 [Example using heat pipe as exhaust heat recovery mechanism] (See Fig. 2)
Next, an embodiment using a
Here, the
In the drying system S2 shown in this embodiment, a
またこの実施例では、外気D0がヒートポンプユニット2によって昇温された状態のものを乾燥気体D1と称する。またこの乾燥気体D1に、乾燥機1から排気された乾燥排ガスD4中の熱が取り込まれた状態のものを乾燥気体D2と称する。更にまたこの乾燥気体D2が昇温装置5によって昇温されたものを乾燥気体D3と称する。
そして前記乾燥気体D3が乾燥機1内において被処理物Hに作用するものであり、その後、乾燥排ガスD4として排気口14から排気され、更に乾燥排ガスD4からヒートパイプ62によって熱が回収されて温度が低下するものであり、乾燥排ガスD5として外部に排気される。
そして乾燥システムS2が起動されると、まず外気D0(一例として20℃)が吹込ファン16により取り込まれ、次いでヒートポンプユニット2における凝縮器21において昇温されて乾燥気体D1となる。
次いで乾燥気体D1には、ヒートパイプ62により熱が供給されて昇温され、乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD4として排出される。
乾燥排ガスD4はヒートパイプ62における吸熱素子62bによって熱が奪われ、温度の低下した乾燥排ガスD5となって外部に排出される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が74℃、乾燥気体D3が160℃、乾燥排ガスD4が88.9℃、乾燥排ガスD5が70℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1をヒートパイプ62を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS2全体のエネルギー効率を向上することができる。 In this embodiment, the state in which the outside air D0 is heated by theheat pump unit 2 is referred to as a dry gas D1. The dry gas D1 in which heat in the dry exhaust gas D4 exhausted from the dryer 1 is taken is referred to as a dry gas D2. Further, the dry gas D2 whose temperature is raised by the temperature raising device 5 is referred to as a dry gas D3.
The dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from theexhaust port 14 as a dry exhaust gas D4. Further, heat is recovered from the dry exhaust gas D4 by the heat pipe 62 and the temperature. Is reduced and exhausted to the outside as the dry exhaust gas D5.
When the drying system S2 is activated, the outside air D0 (20 ° C. as an example) is first taken in by theblower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
Next, heat is supplied to the dry gas D1 by theheat pipe 62 and the temperature is raised to become a dry gas D2.
Next, the dry gas D2 is heated in theheat exchanger 50 to become a dry gas D3.
Then, the dry gas D3 is fed into the dryer 1 from theair supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D4 from the exhaust port 14 in a state where the temperature is lowered. .
The dry exhaust gas D4 is deprived of heat by theheat absorbing element 62b in the heat pipe 62, and is discharged to the outside as the dry exhaust gas D5 having a lowered temperature.
As an example, the temperature of the dry gas D when it reaches the steady state is 60 ° C. for the dry gas D1, 74 ° C. for the dry gas D2, 160 ° C. for the dry gas D3, 88.9 ° C. for the dry exhaust gas D4, and D5 for the dry exhaust gas D5. Becomes 70 ° C.
As described above, according to the present invention, by taking heat in the dry exhaust gas D4 with respect to the dry gas D1, the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of theheat exchanger 50 is reduced as compared with the case where the drying gas D1 is directly heated without using the heat pipe 62, the energy efficiency of the entire drying system S2 can be improved.
そして前記乾燥気体D3が乾燥機1内において被処理物Hに作用するものであり、その後、乾燥排ガスD4として排気口14から排気され、更に乾燥排ガスD4からヒートパイプ62によって熱が回収されて温度が低下するものであり、乾燥排ガスD5として外部に排気される。
そして乾燥システムS2が起動されると、まず外気D0(一例として20℃)が吹込ファン16により取り込まれ、次いでヒートポンプユニット2における凝縮器21において昇温されて乾燥気体D1となる。
次いで乾燥気体D1には、ヒートパイプ62により熱が供給されて昇温され、乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD4として排出される。
乾燥排ガスD4はヒートパイプ62における吸熱素子62bによって熱が奪われ、温度の低下した乾燥排ガスD5となって外部に排出される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が74℃、乾燥気体D3が160℃、乾燥排ガスD4が88.9℃、乾燥排ガスD5が70℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1をヒートパイプ62を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS2全体のエネルギー効率を向上することができる。 In this embodiment, the state in which the outside air D0 is heated by the
The dry gas D3 acts on the workpiece H in the dryer 1 and is then exhausted from the
When the drying system S2 is activated, the outside air D0 (20 ° C. as an example) is first taken in by the
Next, heat is supplied to the dry gas D1 by the
Next, the dry gas D2 is heated in the
Then, the dry gas D3 is fed into the dryer 1 from the
The dry exhaust gas D4 is deprived of heat by the
As an example, the temperature of the dry gas D when it reaches the steady state is 60 ° C. for the dry gas D1, 74 ° C. for the dry gas D2, 160 ° C. for the dry gas D3, 88.9 ° C. for the dry exhaust gas D4, and D5 for the dry exhaust gas D5. Becomes 70 ° C.
As described above, according to the present invention, by taking heat in the dry exhaust gas D4 with respect to the dry gas D1, the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of the
〔排熱回収機構として熱交換器を用いた実施例〕(図3参照)
次いで排熱回収機構6として熱交換器63を用いた実施例について説明する。この実施例で示す乾燥システムS3は図3に示すように、外気D0がヒートポンプユニット2によって昇温されて乾燥気体D1となり、この乾燥気体D1が昇温装置5(熱交換器50)によって昇温される前の段階で、乾燥排ガスD4中の熱を乾燥気体D1に取り込むように構成されるものである。
具体的には、乾燥機1の排気口14に接続される管路に熱交換器63が設けられ、この熱交換器63と、ヒートポンプユニット2における凝縮器21の出力側との間が管路で接続され、更に熱交換器63の出力側と、熱交換器50の入力側との間が管路で接続されて構成されるものである。 [Example using heat exchanger as exhaust heat recovery mechanism] (See Fig. 3)
Next, an embodiment using aheat exchanger 63 as the exhaust heat recovery mechanism 6 will be described. In the drying system S3 shown in this embodiment, as shown in FIG. 3, the outside air D0 is heated by the heat pump unit 2 to become a dry gas D1, and this dry gas D1 is heated by the temperature raising device 5 (heat exchanger 50). In the stage before being performed, the heat in the dry exhaust gas D4 is configured to be taken into the dry gas D1.
Specifically, aheat exchanger 63 is provided in a pipe line connected to the exhaust port 14 of the dryer 1, and the pipe line is between the heat exchanger 63 and the output side of the condenser 21 in the heat pump unit 2. In addition, the output side of the heat exchanger 63 and the input side of the heat exchanger 50 are connected by a pipe line.
次いで排熱回収機構6として熱交換器63を用いた実施例について説明する。この実施例で示す乾燥システムS3は図3に示すように、外気D0がヒートポンプユニット2によって昇温されて乾燥気体D1となり、この乾燥気体D1が昇温装置5(熱交換器50)によって昇温される前の段階で、乾燥排ガスD4中の熱を乾燥気体D1に取り込むように構成されるものである。
具体的には、乾燥機1の排気口14に接続される管路に熱交換器63が設けられ、この熱交換器63と、ヒートポンプユニット2における凝縮器21の出力側との間が管路で接続され、更に熱交換器63の出力側と、熱交換器50の入力側との間が管路で接続されて構成されるものである。 [Example using heat exchanger as exhaust heat recovery mechanism] (See Fig. 3)
Next, an embodiment using a
Specifically, a
そして乾燥システムS3が起動されると、まず外気D0(一例として20℃)が吹込ファン16により取り込まれ、次いでヒートポンプユニット2における凝縮器21において昇温されて乾燥気体D1となる。
次いで乾燥気体D1は、熱交換器63において乾燥排ガスD4中の熱を取り込み、乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD4として排出される。
次に乾燥排ガスD4は熱交換器63において熱が奪われ、温度の低下した乾燥排ガスD5となって外部に排出される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が80~130℃、乾燥気体D3が180℃、乾燥排ガスD4が100~150℃、乾燥排ガスD5が60~80℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を熱交換器63を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS3全体のエネルギー効率を向上することができる。 When the drying system S3 is activated, the outside air D0 (20 ° C. as an example) is first taken in by theblower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
Next, the dry gas D1 takes in the heat in the dry exhaust gas D4 in theheat exchanger 63 and becomes the dry gas D2.
Next, the dry gas D2 is heated in theheat exchanger 50 to become a dry gas D3.
Then, the dry gas D3 is fed into the dryer 1 from theair supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D4 from the exhaust port 14 in a state where the temperature is lowered. .
Next, the dry exhaust gas D4 is deprived of heat in theheat exchanger 63, and becomes dry exhaust gas D5 having a lowered temperature, and is discharged to the outside.
As an example, the temperature of the dry gas D at the steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C. for the dry gas D2, 180 ° C. for the dry gas D3, 100 to 150 ° C. for the dry exhaust gas D4, and dried. The exhaust gas D5 becomes 60 to 80 ° C.
As described above, according to the present invention, by taking heat in the dry exhaust gas D4 with respect to the dry gas D1, the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of theheat exchanger 50 is reduced as compared with the case where the drying gas D1 is directly heated without using the heat exchanger 63, the energy efficiency of the entire drying system S3 can be improved.
次いで乾燥気体D1は、熱交換器63において乾燥排ガスD4中の熱を取り込み、乾燥気体D2となる。
次いで乾燥気体D2は、熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD4として排出される。
次に乾燥排ガスD4は熱交換器63において熱が奪われ、温度の低下した乾燥排ガスD5となって外部に排出される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が80~130℃、乾燥気体D3が180℃、乾燥排ガスD4が100~150℃、乾燥排ガスD5が60~80℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD4中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D2とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を熱交換器63を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS3全体のエネルギー効率を向上することができる。 When the drying system S3 is activated, the outside air D0 (20 ° C. as an example) is first taken in by the
Next, the dry gas D1 takes in the heat in the dry exhaust gas D4 in the
Next, the dry gas D2 is heated in the
Then, the dry gas D3 is fed into the dryer 1 from the
Next, the dry exhaust gas D4 is deprived of heat in the
As an example, the temperature of the dry gas D at the steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C. for the dry gas D2, 180 ° C. for the dry gas D3, 100 to 150 ° C. for the dry exhaust gas D4, and dried. The exhaust gas D5 becomes 60 to 80 ° C.
As described above, according to the present invention, by taking heat in the dry exhaust gas D4 with respect to the dry gas D1, the dry gas D2 having a temperature higher than that of the dry gas D1 can be obtained. Since the load of the
〔排熱回収機構として戻し管路及び熱交換器を用いた実施例〕(図4参照)
次いで排熱回収機構6として戻し管路61及び熱交換器63を用いた実施例について説明する。この実施例で示す乾燥システムS4は図4に示すように、図3に示した乾燥システムS3に対して、戻し管路61を追加した構成となっている。
具体的には、乾燥機1の排気口14と熱交換器63との間に接続される管路と、熱交換器63と昇温装置5(熱交換器50)との間に接続される管路との間に、戻し管路61が設けられる。
なお前記戻し管路61にダンパ61aを具えることにより、乾燥排ガスD5の流量を調整できるようにした。 [Example using return pipe and heat exchanger as exhaust heat recovery mechanism] (See Fig. 4)
Next, an embodiment using thereturn pipe 61 and the heat exchanger 63 as the exhaust heat recovery mechanism 6 will be described. As shown in FIG. 4, the drying system S <b> 4 shown in this embodiment has a configuration in which a return pipe 61 is added to the drying system S <b> 3 shown in FIG. 3.
Specifically, a pipe line connected between theexhaust port 14 of the dryer 1 and the heat exchanger 63, and a connection between the heat exchanger 63 and the temperature raising device 5 (heat exchanger 50). A return pipe 61 is provided between the pipes.
Thereturn pipe 61 is provided with a damper 61a so that the flow rate of the dry exhaust gas D5 can be adjusted.
次いで排熱回収機構6として戻し管路61及び熱交換器63を用いた実施例について説明する。この実施例で示す乾燥システムS4は図4に示すように、図3に示した乾燥システムS3に対して、戻し管路61を追加した構成となっている。
具体的には、乾燥機1の排気口14と熱交換器63との間に接続される管路と、熱交換器63と昇温装置5(熱交換器50)との間に接続される管路との間に、戻し管路61が設けられる。
なお前記戻し管路61にダンパ61aを具えることにより、乾燥排ガスD5の流量を調整できるようにした。 [Example using return pipe and heat exchanger as exhaust heat recovery mechanism] (See Fig. 4)
Next, an embodiment using the
Specifically, a pipe line connected between the
The
そして乾燥システムS4が起動されると、まず外気D0(一例として20℃)が吹込ファン16により取り込まれ、次いでヒートポンプユニット2における凝縮器21において昇温されて乾燥気体D1となる。
次いで乾燥気体D1は、熱交換器63において乾燥排ガスD5中の熱を取り込み、乾燥気体D2となる。
次いで乾燥気体D2には、ダンパ61aの開度に応じた量の乾燥排ガスD5が混入され、乾燥気体D21となる。
次いで乾燥気体D21は熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD5として排出される。
次いで乾燥排ガスD5は、ダンパ61aの開度に応じて分流され、その一部が熱交換器63において熱が奪われ、温度の低下した乾燥排ガスD6となって外部に排出される。また残りの乾燥排ガスD5は上述したように戻し管路61を通じて乾燥気体D2に混入される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が80~130℃、乾燥気体D21が98~149℃、乾燥気体D3が180℃、乾燥排ガスD5が100~150℃、乾燥排ガスD6が60~80℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD5中の熱を取り込むとともに、乾燥気体D2に対して乾燥排ガスD5中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D21とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を熱交換器63及び戻し管路61を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS4全体のエネルギー効率を向上することができる。 When the drying system S4 is activated, the outside air D0 (20 ° C. as an example) is first taken in by theblower fan 16, and then heated in the condenser 21 in the heat pump unit 2 to become the dry gas D1.
Next, the dry gas D1 takes in the heat in the dry exhaust gas D5 in theheat exchanger 63 and becomes the dry gas D2.
Next, the dry gas D2 is mixed with an amount of dry exhaust gas D5 corresponding to the opening degree of thedamper 61a to become a dry gas D21.
Next, the temperature of the dry gas D21 is raised in theheat exchanger 50 to become a dry gas D3.
Then, the dry gas D3 is fed into the dryer 1 from theair supply port 12, acts on the workpiece H to dry it, and is discharged as dry exhaust gas D5 from the exhaust port 14 in a state where the temperature is lowered. .
Next, the dry exhaust gas D5 is diverted according to the opening degree of thedamper 61a, and a part of it is deprived of heat in the heat exchanger 63 to be discharged to the outside as the dry exhaust gas D6 having a lowered temperature. Further, the remaining dry exhaust gas D5 is mixed into the dry gas D2 through the return pipe 61 as described above.
As an example, the temperature of the dry gas D when it reaches a steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C. for the dry gas D2, 98 to 149 ° C. for the dry gas D21, 180 ° C. for the dry gas D3, and dry. The exhaust gas D5 is 100 to 150 ° C., and the dry exhaust gas D6 is 60 to 80 ° C.
Thus, according to this invention, while taking in the heat in dry exhaust gas D5 with respect to the dry gas D1, and taking in the heat in dry exhaust gas D5 with respect to the dry gas D2, temperature is higher than the dry gas D1. Compared to the case where the load of theheat exchanger 50 that further raises the temperature of the dry gas D21 increases the temperature of the dry gas D1 directly without using the heat exchanger 63 and the return pipe 61. Therefore, the energy efficiency of the entire drying system S4 can be improved.
次いで乾燥気体D1は、熱交換器63において乾燥排ガスD5中の熱を取り込み、乾燥気体D2となる。
次いで乾燥気体D2には、ダンパ61aの開度に応じた量の乾燥排ガスD5が混入され、乾燥気体D21となる。
次いで乾燥気体D21は熱交換器50において昇温され、乾燥気体D3となる。
そして乾燥気体D3は、給気口12から乾燥機1内に送り込まれ、被処理物Hに作用してこのものを乾燥させ、温度が低下した状態で排気口14から乾燥排ガスD5として排出される。
次いで乾燥排ガスD5は、ダンパ61aの開度に応じて分流され、その一部が熱交換器63において熱が奪われ、温度の低下した乾燥排ガスD6となって外部に排出される。また残りの乾燥排ガスD5は上述したように戻し管路61を通じて乾燥気体D2に混入される。
なお定常状態となったときの乾燥気体Dの温度は一例として、乾燥気体D1が60℃、乾燥気体D2が80~130℃、乾燥気体D21が98~149℃、乾燥気体D3が180℃、乾燥排ガスD5が100~150℃、乾燥排ガスD6が60~80℃となる。
このように本発明によれば、乾燥気体D1に対して乾燥排ガスD5中の熱を取り込むとともに、乾燥気体D2に対して乾燥排ガスD5中の熱を取り込むことにより、乾燥気体D1よりも温度が高い乾燥気体D21とすることができ、このものを更に昇温する熱交換器50の負荷が、仮に乾燥気体D1を熱交換器63及び戻し管路61を利用しないで直接昇温する場合に比べて減少するため、乾燥システムS4全体のエネルギー効率を向上することができる。 When the drying system S4 is activated, the outside air D0 (20 ° C. as an example) is first taken in by the
Next, the dry gas D1 takes in the heat in the dry exhaust gas D5 in the
Next, the dry gas D2 is mixed with an amount of dry exhaust gas D5 corresponding to the opening degree of the
Next, the temperature of the dry gas D21 is raised in the
Then, the dry gas D3 is fed into the dryer 1 from the
Next, the dry exhaust gas D5 is diverted according to the opening degree of the
As an example, the temperature of the dry gas D when it reaches a steady state is 60 ° C. for the dry gas D1, 80 to 130 ° C. for the dry gas D2, 98 to 149 ° C. for the dry gas D21, 180 ° C. for the dry gas D3, and dry. The exhaust gas D5 is 100 to 150 ° C., and the dry exhaust gas D6 is 60 to 80 ° C.
Thus, according to this invention, while taking in the heat in dry exhaust gas D5 with respect to the dry gas D1, and taking in the heat in dry exhaust gas D5 with respect to the dry gas D2, temperature is higher than the dry gas D1. Compared to the case where the load of the
〔昇温装置として直火炉を用いた実施例〕
また上述した複数の実施例においては、昇温装置5として熱交換器50を採用したが、昇温装置5として直火炉55を採用することもできる。
具体的には図5に示す実施例は、図1に示した乾燥システムS1の熱交換器50を、直火炉55に置き換えた乾燥システムS5を示すものである。
更に外部に排気される前の乾燥排ガスD4、D5、D6に含まれる熱を回収してもよく、この場合、例えば熱交換器64を用いて熱を水Wに移動させ、更にこの水Wをタンク65に貯留するとともに、ヒートポンプユニット2における蒸発器23の熱源とすることにより、更なるエネルギー効率の向上を図ることもできる。 [Example using a direct furnace as a temperature raising device]
In the above-described embodiments, theheat exchanger 50 is employed as the temperature raising device 5, but a direct furnace 55 may be employed as the temperature raising device 5.
Specifically, the embodiment shown in FIG. 5 shows a drying system S5 in which theheat exchanger 50 of the drying system S1 shown in FIG.
Further, the heat contained in the dry exhaust gas D4, D5, D6 before being exhausted to the outside may be recovered. In this case, for example, the heat is transferred to the water W using theheat exchanger 64, and the water W is further transferred. By storing in the tank 65 and using it as a heat source for the evaporator 23 in the heat pump unit 2, it is possible to further improve energy efficiency.
また上述した複数の実施例においては、昇温装置5として熱交換器50を採用したが、昇温装置5として直火炉55を採用することもできる。
具体的には図5に示す実施例は、図1に示した乾燥システムS1の熱交換器50を、直火炉55に置き換えた乾燥システムS5を示すものである。
更に外部に排気される前の乾燥排ガスD4、D5、D6に含まれる熱を回収してもよく、この場合、例えば熱交換器64を用いて熱を水Wに移動させ、更にこの水Wをタンク65に貯留するとともに、ヒートポンプユニット2における蒸発器23の熱源とすることにより、更なるエネルギー効率の向上を図ることもできる。 [Example using a direct furnace as a temperature raising device]
In the above-described embodiments, the
Specifically, the embodiment shown in FIG. 5 shows a drying system S5 in which the
Further, the heat contained in the dry exhaust gas D4, D5, D6 before being exhausted to the outside may be recovered. In this case, for example, the heat is transferred to the water W using the
S 乾燥システム
S1 乾燥システム
S2 乾燥システム
S3 乾燥システム
S4 乾燥システム
S5 乾燥システム
1 乾燥機
10 筐体
10a ダクト
11 通気板
11a 堰板
12 給気口
13 投入口
14 排気口
15 排出口
16 吹込ファン
17 排気ファン
2 ヒートポンプユニット
21 凝縮器
22 膨張弁
23 蒸発器
24 圧縮機
5 昇温装置
50 熱交換器
51 放熱フィン
52 パイプ
54 調節弁
55 直火炉
6 排熱回収機構
61 戻し管路
61a ダンパ
62 ヒートパイプ
62a パイプ
62b 吸熱素子
62c 放熱素子
63 熱交換器
64 熱交換器
65 タンク
D 乾燥気体
D0 外気
D1 乾燥気体
D2 乾燥気体
D21 乾燥気体
D3 乾燥気体
D4 乾燥排ガス
D5 乾燥排ガス
D6 乾燥排ガス
H 被処理物
W 水 S Drying System S1 Drying System S2 Drying System S3 Drying System S4 Drying System S5 Drying System 1Dryer 10 Housing 10a Duct 11 Ventilation Plate 11a Dam Plate 12 Air Supply Port 13 Input Port 14 Exhaust Port 15 Exhaust Port 16 Blow Fan 17 Exhaust Air Fan 2 Heat pump unit 21 Condenser 22 Expansion valve 23 Evaporator 24 Compressor 5 Temperature raising device 50 Heat exchanger 51 Radiation fin 52 Pipe 54 Control valve 55 Direct-fired furnace 6 Waste heat recovery mechanism 61 Return line 61a Damper 62 Heat pipe 62a Pipe 62b Heat absorption element 62c Heat radiation element 63 Heat exchanger 64 Heat exchanger 65 Tank D Dry gas D0 Outside air D1 Dry gas D2 Dry gas D21 Dry gas D3 Dry gas D4 Dry exhaust gas D5 Dry exhaust gas D6 Dry exhaust gas S H Workpiece W Water
S1 乾燥システム
S2 乾燥システム
S3 乾燥システム
S4 乾燥システム
S5 乾燥システム
1 乾燥機
10 筐体
10a ダクト
11 通気板
11a 堰板
12 給気口
13 投入口
14 排気口
15 排出口
16 吹込ファン
17 排気ファン
2 ヒートポンプユニット
21 凝縮器
22 膨張弁
23 蒸発器
24 圧縮機
5 昇温装置
50 熱交換器
51 放熱フィン
52 パイプ
54 調節弁
55 直火炉
6 排熱回収機構
61 戻し管路
61a ダンパ
62 ヒートパイプ
62a パイプ
62b 吸熱素子
62c 放熱素子
63 熱交換器
64 熱交換器
65 タンク
D 乾燥気体
D0 外気
D1 乾燥気体
D2 乾燥気体
D21 乾燥気体
D3 乾燥気体
D4 乾燥排ガス
D5 乾燥排ガス
D6 乾燥排ガス
H 被処理物
W 水 S Drying System S1 Drying System S2 Drying System S3 Drying System S4 Drying System S5 Drying System 1
Claims (5)
- 乾燥機と、この乾燥機に乾燥気体を供給するための給気機構とを具えた乾燥システムにおいて、前記乾燥機は熱風乾燥機であり、また前記給気機構はヒートポンプユニットを具えて成るものであり、更に前記給気機構には、ヒートポンプユニットにより昇温された乾燥気体を、更に昇温するための昇温装置が具えられて成り、更に前記乾燥機から排気された乾燥排ガス中の熱を、乾燥機に投入する前の乾燥気体に取り込むことができるように構成された排熱回収機構が具えられていることを特徴とするヒートポンプユニットと排熱回収機構とを具えた乾燥システム。 In a drying system comprising a dryer and an air supply mechanism for supplying dry gas to the dryer, the dryer is a hot air dryer, and the air supply mechanism comprises a heat pump unit. Further, the air supply mechanism is provided with a temperature raising device for further raising the temperature of the dry gas heated by the heat pump unit, and further the heat in the dry exhaust gas exhausted from the dryer. A drying system comprising a heat pump unit and an exhaust heat recovery mechanism, comprising an exhaust heat recovery mechanism configured to be able to take in the dry gas before being introduced into the dryer.
- 前記排熱回収機構は、乾燥排ガス中の熱を、乾燥排ガスの一部を乾燥気体に合流されることにより、乾燥気体に取り込むように構成されたものであることを特徴とする請求項1記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システム。 The exhaust heat recovery mechanism is configured to take heat in the dry exhaust gas into the dry gas by joining a part of the dry exhaust gas into the dry gas. Drying system equipped with a heat pump unit and exhaust heat recovery mechanism.
- 前記排熱回収機構は、乾燥排ガス中の熱を、ヒートパイプによって回収し、その後、乾燥気体に取り込むように構成されたものであることを特徴とする請求項1記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システム。 2. The heat pump unit and the exhaust heat recovery according to claim 1, wherein the exhaust heat recovery mechanism is configured to recover heat in the dry exhaust gas by a heat pipe and then take it into a dry gas. Drying system with mechanism.
- 前記排熱回収機構は、乾燥排ガス中の熱を、熱交換器を用いて乾燥気体に取り込むように構成されたものであることを特徴とする請求項1記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システム。 2. The heat pump unit and the exhaust heat recovery mechanism according to claim 1, wherein the exhaust heat recovery mechanism is configured to take heat in the dry exhaust gas into the dry gas using a heat exchanger. Drying system with
- 前記排熱回収機構は、乾燥排ガス中の熱を、乾燥排ガスの一部を乾燥気体に合流されることにより乾燥気体に取り込むものであり、且つ乾燥排ガス中の熱を、熱交換器を用いて乾燥気体に取り込むように構成されたものであることを特徴とする請求項1記載のヒートポンプユニットと排熱回収機構とを具えた乾燥システム。 The exhaust heat recovery mechanism takes heat in the dry exhaust gas into the dry gas by joining a part of the dry exhaust gas to the dry gas, and uses the heat exchanger to heat the dry exhaust gas. 2. A drying system comprising a heat pump unit and an exhaust heat recovery mechanism according to claim 1, wherein the drying system is configured to take in a dry gas.
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JP2014119132A (en) * | 2012-12-13 | 2014-06-30 | Okawara Mfg Co Ltd | Dryer adapted for voc (volatile organic compound) exhaust |
CN104215058A (en) * | 2013-05-30 | 2014-12-17 | 中国科学院工程热物理研究所 | Solid material drying device |
CN106091606A (en) * | 2016-06-27 | 2016-11-09 | 安庆市微知著电器有限公司 | A kind of exsiccator with tail gas treating function |
CN106123509A (en) * | 2016-06-27 | 2016-11-16 | 安庆市微知著电器有限公司 | A kind of drier |
CN106196895A (en) * | 2016-06-27 | 2016-12-07 | 安庆市微知著电器有限公司 | A kind of exsiccator |
CN107873835A (en) * | 2017-12-16 | 2018-04-06 | 安徽热风环保科技有限公司 | Net gas improvements grain heat-drying centring system using heat pump as thermal source |
CN107906944A (en) * | 2017-12-16 | 2018-04-13 | 安徽热风环保科技有限公司 | The anti-cold air reflux of heat pump dryer condensation end |
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JP6063257B2 (en) | 2017-01-18 |
JPWO2011125745A1 (en) | 2013-07-08 |
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