JP6182798B2 - Cooling device, temperature control device and temperature control dehumidification system - Google Patents

Description

  The present invention relates to air that is passed between the cooling refrigerant pipe and the cooling fin when air on one side of the cooling core passes through the cooling core and is moved to the other side. The present invention relates to a cooling device, a temperature control device, and a temperature control dehumidification system configured to include a cooler capable of mutually cooling heat in a cooling refrigerant pipe and cooling air.

  For example, in the following patent document, a dehumidifying and warming device 3x configured to be able to supply dehumidified and temperature-controlled air to a supply target (hereinafter, each component related to the conventional “dehumidifying and warming device”, (Explained by adding “x” to the end of the reference numeral). As shown in FIG. 7, the dehumidifying and warming device 3x is provided with an evaporator (cooler) 21x and a condenser (heater) 20x in the heat pump device 22x arranged side by side. The dehumidifying and warming device 3x cools the air guided by the wind circuit 23x in the evaporator 21x to condense the moisture contained in the air and dehumidify it, and then heats it to the target temperature by the condenser 20x. It is configured to be capable of being supplied to a supply target (specifically, a clothing storage portion that can store clothing to be dried by the supplied air).

  In this case, the evaporator 21x is composed of a fin tube type heat exchanger having a plurality of fins Fx and tubes Tx and having a cooling core C21x formed in a thick plate shape, and is upstream in the air movement direction. It is arranged on the side (windward side). The condenser 20x is composed of a fin tube type heat exchanger having a heating core C20x formed in a thick plate shape having a plurality of fins Fx and tubes Tx, and is downstream in the air moving direction. It is arranged on the (leeward side). Further, in the dehumidifying and warming device 3x, the vertical length of the evaporator 21x is formed to be longer than the vertical length of the condenser 20x, and the lower end portion (gravity direction end) of the evaporator 21x. Is disposed below the lower end (gravity direction end) of the condenser 20x, thereby forming a drain pan 170x capable of storing drain water below the evaporator 21x.

  When supplying the dehumidified and temperature-controlled air by the dehumidifying and warming device 3x to the supply target, the heat pump device 22x and a blower (not shown) are operated. At this time, the air blown by the blower is guided to the evaporator 21x through the wind circuit 23x and passed through the evaporator 21x along the thickness direction of the cooling core C21x, and then the heating core C20x. It passes through the condenser 20x along the thickness direction and is supplied to the supply target. Further, by the operation of the heat pump device 22x, the refrigerant compressed by the compressor is pumped to the condenser 20x and condensed. At this time, as a result of the temperature rise of the fins Fx and the tubes Tx of the condenser 20x by the high-temperature refrigerant pumped from the compressor, the condenser 20x is allowed to pass through after being cooled by the evaporator 21x as described later. The heated air is heated up to the target temperature.

  On the other hand, the refrigerant condensed in the condenser 20x is supplied to the evaporator 21x after passing through the expansion valve. At this time, as a result of the temperature of the fins Fx and the tubes Tx of the evaporator 21x being lowered due to the adiabatic expansion of the refrigerant, the air passing through the evaporator 21x is cooled and the moisture in the air is drained (condensed water). Removed as. At this time, the drain water removed from the air drops down to the drain pan 170x through the fins Fx, and is drained outside the dehumidifying and warming device 3x through a drain water discharge port (not shown). Further, the low-temperature and low-humidity air from which moisture has been removed (dehumidified) in the evaporator 21x is raised in temperature to the target temperature when being passed through the condenser 20x as described above. Thereby, the dehumidified and temperature-controlled air is supplied from the dehumidifying and warming device 3x to the supply target.

JP 2008-73407 A (page 6-8, FIG. 1-6)

  However, the conventional dehumidifying / heating apparatus 3x has the following problems to be solved. That is, in the conventional dehumidifying and warming device 3x, when the air guided by the wind circuit 23x is passed through the evaporator 21x along the thickness direction of the cooling core C21x, the air is cooled and moisture is removed, After that, when passing through the condenser 20x along the thickness direction of the heating core C20x, a configuration is used in which the temperature is increased to the target temperature and supplied to the supply target.

  In this case, although there is no specific description in the above patent document, in this type of apparatus, the refrigerant pumped to the cooling core C21x of the evaporator 21x through the expansion valve is, for example, the upper end Tax. When the refrigerant is supplied from the inside to the tube Tx, the refrigerant moving in the tube Tx in the direction of the arrow Dx toward the lower end portion Tbx is gradually exchanged by heat exchange with the air passed through the cooling core C21x. Since the temperature rises, the lower portion of the cooling core C21x has a higher temperature than the upper portion.

  Therefore, when the configuration for supplying the refrigerant from the upper end Tax into the tube Tx is adopted, the temperature of the air guided to the evaporator 21x is high, or the amount of air guided to the evaporator 21x is large. Sometimes, that is, when the burden on the evaporator 21x is large, it may be difficult to suitably cool the air in the lower portion of the cooling core C21x. In such a state, as shown by an arrow A1x in FIG. 7, the air allowed to pass through the upper portion of the evaporator 21x (cooling core C21x) can be sufficiently cooled, but evaporates as shown by an arrow A2x. Air that is allowed to pass through the lower portion of the vessel 21x (cooling core C21x) is difficult to sufficiently cool.

  On the other hand, when the refrigerant pumped through the expansion valve to the cooling core C21x of the evaporator 21x is supplied into the tube Tx from the lower end portion Tbx, for example, in the direction of the arrow Ux toward the upper end portion Tax. Since the refrigerant moving in the tube Tx gradually rises in temperature by heat exchange with the air passing through the cooling core C21x, the upper portion is higher in temperature than the lower portion of the cooling core C21x. .

  Therefore, when the configuration for supplying the refrigerant from the lower end Tbx into the tube Tx is adopted, the air is suitably cooled at the upper portion of the cooling core C21x when the burden on the evaporator 21x is large. May be difficult. In such a state, as shown by the arrow A1x, the air passing through the lower portion of the evaporator 21x (cooling core C21x) can be sufficiently cooled, but as shown by the arrow A1x, the evaporator 21x ( It is difficult to sufficiently cool the air that is allowed to pass through the upper portion of the cooling core C21x).

  As described above, in the conventional dehumidifying and warming device 3x, when the burden on the evaporator (cooler) 21x is large, the refrigerant is supplied into the tube Tx from the lower portion (upper end Tax) of the cooling core C21x. In the upper portion of the cooling core C21x (when the configuration in which the refrigerant is supplied into the tube Tx from the lower end Tbx) is preferably used. Due to the difficulty in cooling, there is a problem that air having a temperature higher than the target temperature range may be discharged from the evaporator 21x toward the condenser 20x.

  The present invention has been made in view of such problems to be solved, and is a cooling device, a temperature control device, and a temperature control device that can suitably cool the air to be processed even when the burden on the cooler is large. The main purpose is to provide a dehumidification system.

  In order to achieve the above object, a cooling device according to claim 1, wherein the cooling device is formed in a spiral shape or a twisted shape and guides the cooling coolant from one end to the other end, and the cooling coolant piping. A cooling fin disposed so as to be in contact with the outer peripheral surface of the thick plate-like cooling core is formed, and air on one surface side of the cooling core is supplied to the cooling refrigerant pipe and the cooling core. When the air passes through the cooling fins and is moved to the other surface side of the cooling core, the air and the cooling refrigerant guided in the cooling refrigerant pipe are connected to the cooling refrigerant pipe and A cooler configured to cool the air by exchanging heat with each other through the cooling fins, a first air direction regulating plate disposed on the one surface of the cooling core, and A second disposed on the other surface of the cooling core; A direction regulating plate, and the cooler has the one end portion of the cooling refrigerant pipe positioned above the other end portion of the cooling refrigerant pipe, and the cooling refrigerant is below the cooler. The first wind direction restricting plate is arranged so that the first length in the vertical direction is the second length in the vertical direction of the second wind direction restricting plate. The second wind direction regulating plate is formed to be shorter than the length and closes the upper part of the one surface of the cooling core, and the second wind direction restricting plate has a lower part of the other surface of the cooling core. Air placed between the cooling refrigerant pipe and the cooling fin from a lower part of the one surface of the cooling core is disposed so as to be closed, and upwards in the cooling core. Move to the other side of the cooling core The air guide path is formed so as to be discharged from the definitive upper part.

  The cooling device according to claim 2 is the cooling device according to claim 1, wherein the second wind direction regulating plate has a second length that is 1/3 of a third length in the vertical direction of the cooling core. It is formed to be 2 or more.

  The cooling device according to claim 3 is the cooling device according to claim 2, wherein the first wind direction regulating plate and the second wind direction regulating plate have a sum of the first length and the second length. The lower end portion of the first air direction restriction plate and the upper end portion of the second air direction restriction plate are overlapped with each other in the thickness direction of the cooling core. It is arranged like this.

  According to a fourth aspect of the present invention, there is provided a temperature control device that is formed in a spiral or twisted manner with the cooling device according to any one of the first to third aspects and that guides the heating refrigerant from one end to the other end. A thick plate-like heating core is formed having a refrigerant pipe and a heating fin disposed so as to be in contact with the outer peripheral surface of the heating refrigerant pipe, and on one surface side of the heating core. The heating is guided through the air and the heating refrigerant pipe when the air passes between the heating refrigerant pipe and the heating fin and is moved to the other surface side of the heating core. A heating device having a heater configured to heat the air by mutually exchanging heat with the refrigerant via the heating refrigerant pipe and the heating fin, and the other of the cooling cores A surface and the one surface of the heating core The cooler and the heater are disposed so as to face each other with the second air direction restriction plate interposed therebetween, and the air cooled by the cooler is heated by the heater and can be supplied to the supply target. Yes.

  The temperature control device according to claim 5 is the temperature control device according to claim 4, wherein the heating device includes a third air direction regulating plate disposed on the other surface of the heating core, The heating refrigerant pipe is positioned below the other end of the heating refrigerant pipe so that the heating refrigerant is located above the heater in the heating refrigerant pipe. The third air direction restriction plate is formed with a discharge port for discharging the air heated by the heater at a position facing a lower part of the other surface of the heating core. ing.

  A temperature control device according to a sixth aspect is the temperature control device according to the fourth or fifth aspect, wherein a space is formed between the second air direction regulating plate and the one surface of the heating core.

  A temperature control device according to a seventh aspect is the temperature control device according to the sixth aspect, wherein the second wind direction regulating plate is bent at an upper end side portion toward the heating core.

  The temperature control dehumidification system of Claim 8 is equipped with the temperature control apparatus in any one of Claims 4-7, and the air blower which ventilates the said air so that it may pass in order of the said cooling device and the said heating apparatus. Configured.

  In the cooling device according to claim 1, one end portion of the cooling refrigerant pipe is positioned above the other end portion of the cooling refrigerant pipe, and the cooling refrigerant moves in the cooling refrigerant pipe toward the lower side of the cooler. The cooler is arranged so as to be guided, and the first wind direction regulating plate formed with a first length in the vertical direction shorter than a second length in the vertical direction of the second wind direction regulating plate is for cooling. The second wind direction restricting plate is disposed so as to block the lower portion of the other surface of the cooling core, and is disposed so as to block the upper portion of the one surface of the core. The air that has entered between the cooling refrigerant pipe and the cooling fin from the lower portion on the surface of the cooling plate moves upward in the cooling core and is discharged from the upper portion on the other surface of the cooling core. An air duct is formed in the.

  Therefore, according to the cooling device of the first aspect, the burden on the cooler is large, and it is difficult to suitably cool the air in the vicinity of the other end of the cooling refrigerant pipe (the lower portion of the cooling core). Even if it becomes a state, since air is guided from the lower part of the cooling core to the upper part by the first air direction restriction plate and the second air direction restriction plate, the air is preferably used in the upper part of the cooling core. Can be cooled to. Further, by providing the second wind direction regulating plate at the lower end side portion on the other surface of the cooling core, when drain water (condensation water) is generated by cooling by the cooling core, the drain water is cooled. The situation of being discharged to the other surface side of the core for use can be preferably avoided.

  According to the cooling device of the second aspect, the second length of the second air direction restriction plate is formed to be ½ or more of the third length in the vertical direction of the cooling core. Thus, the air that has entered between the cooling refrigerant pipe and the cooling fin from one surface of the cooling core can be reliably guided upward of the cooling core.

  Further, according to the cooling device of the third aspect, the first wind direction regulating plate and the second wind direction regulating plate are arranged so that the sum of the first length and the second length is longer than the third length. The first wind direction regulating plate and the second wind direction are formed so that the lower end side portion of the first wind direction regulating plate and the upper end side portion of the second wind direction regulating plate overlap in the thickness direction of the cooling core. By providing the restriction plate, the air that has entered between the cooling refrigerant pipe and the cooling fin from one surface of the cooling core passes through the cooling core in the thickness direction of the cooling core and passes through the other side. Without causing a situation of being discharged to the surface, it is possible to reliably move the space between the cooling refrigerant pipe and the cooling fin toward the upper side of the cooling core and discharge it to the other surface side.

  According to a fourth aspect of the present invention, the second air direction regulating plate is sandwiched between the other surface of the cooling core in the cooler of the cooling device and the one surface of the heating core in the heater of the heating device. A cooler and a heater are arranged so as to face each other. Moreover, the temperature control dehumidification system of Claim 8 is provided with one of said temperature control apparatuses, and the air blower which ventilates air so that it may pass in order of a cooling device and a heating apparatus. Therefore, according to the temperature regulating device according to claim 4 and the temperature regulating dehumidification system according to claim 8, the air cooled and dehumidified by the cooling device is supplied in a state adjusted by heating by the heating device according to the purpose. The object can be supplied.

  According to the temperature control apparatus of claim 5, one end portion of the heating refrigerant pipe is positioned below the other end portion of the heating refrigerant pipe, and the heating refrigerant moves upward of the heater. The heater is arranged so as to be guided inside, and a discharge port for discharging the air heated by the heater is formed at a position facing the lower part of the other surface of the heating core in the third air direction restriction plate. Thus, in the entire region from the upper end to the lower end of the heater (heating core), heat is suitably generated between the refrigerant in the heating refrigerant pipe and the air around the heating refrigerant pipe and each heating fin. The air to be treated can be heated reliably.

  According to the temperature control device of the sixth aspect, since the space is formed between the second wind direction regulating plate and one surface of the heating core, the space is discharged from above the second wind direction regulating plate to the space. After the heated air spreads from the upper part of the space to the entire lower part, it is made to enter between the heating refrigerant pipe of the heater (heating core) and each heating fin, so that the lower part from the upper part of the heating core. Thus, heat can be exchanged suitably between the refrigerant in the heating refrigerant pipe and the air around the heating refrigerant pipe and each heating fin, so that the air to be treated can be heated more reliably.

  According to the temperature control apparatus of the seventh aspect, the air that has been cooled by the cooler (cooling core) is spaced by bending the upper end portion of the second air direction restriction plate toward the heating core. It can be discharged smoothly.

It is a block diagram which shows the structure of the temperature control dehumidification system 1 which concerns on embodiment of this invention. It is sectional drawing which shows the structure of the dehumidification apparatus 3a in the temperature control dehumidification system 1 which concerns on embodiment of this invention. It is sectional drawing which shows the structure of the heat exchange apparatus 3b in the temperature control dehumidification system 1 which concerns on embodiment of this invention. It is a block diagram which shows the structure of 1 A of temperature control dehumidification systems which concern on other embodiment of this invention. It is sectional drawing which shows the structure of the dehumidification apparatus 3d which concerns on other embodiment of this invention. It is sectional drawing which shows the structure of the cooling device 3e which concerns on other embodiment of this invention. It is sectional drawing which shows the structure of the conventional dehumidification warming apparatus 3x.

  Embodiments of a cooling device, a temperature control device, and a temperature control dehumidification system according to the present invention will be described below with reference to the accompanying drawings.

  The temperature control / dehumidification system 1 shown in FIG. 1 is an example of a “temperature control / dehumidification system”, and includes a heat pump 2, a dehumidifier 3 a, blowers 4 a and 4 b, and a controller 5. Air that has been temperature-controlled and dehumidified so as to have a humidity within a humidity range can be supplied to a supply target (not shown).

  The heat pump 2 includes a compressor 21, regulating valves 22a and 22b, condensers 23a and 23b, expansion valves 24a and 24b, and evaporators 25a and 25b. The compressor 21 compresses and discharges the refrigerant according to the control of the controller 5. The adjustment valves 22 a and 22 b are constituted by variable flow type electronic valves as an example, and adjust the flow rate of the refrigerant compressed by the compressor 21 to the condensers 23 a and 23 b according to the control of the controller 5. The condensers 23a and 23b condense the refrigerant by exchanging heat between the refrigerant compressed by the compressor 21 and the surrounding air.

  In this case, as shown in FIG. 3, the condenser 23 a is formed in a spiral shape and is cooled from the lower end Tb (an example of “one end”) to the upper end Ta (an example of “other end”). A tube T (an example of a “heating refrigerant pipe”) that guides the pipe and a fin F (an example of a “heating fin”) disposed so as to be in contact with the outer peripheral surface of the tube T. A heating core C23a is formed. Further, the condenser 23b is an example of a “heater”, and as shown in FIG. 2, similarly to the condenser 23a, the condenser 23b is formed in a spiral shape from the lower end Tb to the upper end Ta. A thick plate-like heating core C23b is formed, having a tube T for guiding the refrigerant and fins F arranged so as to be in contact with the outer peripheral surface of the tube T.

  The expansion valves 24a and 24b are constituted by capillary tubes, for example, and discharge the refrigerant condensed in the condensers 23a and 23b toward the evaporators 25a and 25b, respectively. It should be noted that an “expansion valve” composed of an electronic expansion valve may be employed instead of the expansion valves 24a and 24b. The evaporators 25a and 25b cool the surrounding air by exchanging heat between the refrigerant discharged from the expansion valves 24a and 24b and the surrounding air.

  In this case, the evaporator 25a is an example of a “cooler”, and as illustrated in FIG. 2, the evaporator 25a is formed in a spiral shape from the upper end Ta (an example of “one end”) to the lower end Tb ( An example of the “other end portion”) is a tube T that guides the refrigerant (an example of “cooling refrigerant pipe”), and an example of a fin F that is disposed in contact with the outer peripheral surface of the tube T (an example of “cooling fin”). ) And a thick cooling core C25a is formed. Further, the evaporator 25b is another example of the “cooler”, and as shown in FIG. 3, the evaporator 25b is formed in a spiral shape in the same manner as the evaporator 25a described above, and the lower end from the upper end portion Ta. A thick plate-like cooling core C25b having a tube T for guiding the refrigerant to the portion Tb and a fin F disposed so as to be in contact with the outer peripheral surface of the tube T is formed.

  As will be described later, in the temperature control dehumidification system 1 of this example, the evaporator 25a among the components of the heat pump 2 constitutes a “cooling device” together with the casing 10 (see FIG. 2) and the like. At the same time, the “cooling device” and the condenser 23b combine to form a “temperature control device”. In this case, in the heat pump 2 of this example, the compressor 21, the regulating valve 22a, the condenser 23a, and the expansion valve 24a provide a cold source for supplying “cooling refrigerant” to the evaporator 25a as “cooler”. In addition, the compressor 21, the regulating valve 22b, the expansion valve 24b, and the evaporator 25b constitute a heat source for supplying the “heating refrigerant” to the condenser 23b as the “heater”.

  Moreover, in the temperature control dehumidification system 1 of this example, the evaporator 25b of each component of the heat pump 2 is combined with the casing 30 (see FIG. 3) and the like in the condenser 23a which is an example of “supplier”. A “cooling device” for supplying cold air is configured. In this case, in the heat pump 2 of this example, the compressor 21, the regulating valve 22b, the condenser 23b, and the expansion valve 24b provide a cooling source for supplying “cooling refrigerant” to the evaporator 25b as “cooler”. Configure. In the following description, an element including the condenser 23a, the evaporator 25b, the casing 30, and the like is referred to as a heat exchange device 3b. This heat exchange device 3b suitably condenses the refrigerant in the condenser 23a for supplying the “cooling refrigerant” to the evaporator 25a constituting the “cooling device” in the dehumidifying device 3a (improves the condensation efficiency). ) For supplying low-temperature air cooled by the evaporator 25b around the condenser 23a, and the evaporator 25b and the condenser 23a are accommodated in the casing 30 as shown in FIG. It is configured.

  In this case, in this heat exchange device 3b, the refrigerant supplied to the evaporator 25b via the expansion valve 24b moves from the upper end Ta of the tube T toward the lower end Tb (downward of the evaporator 25b). ) The evaporator 25b is erected in the casing 30 so as to be guided in the tube T in the direction of the arrow Db ("one end of the cooling refrigerant pipe" into which "cooling refrigerant" is introduced is "cooling") An example of an arrangement that is positioned above the “other end of the refrigerant pipe”. In the heat exchange device 3b, the refrigerant supplied to the condenser 23a via the regulating valve 22a is directed from the lower end Tb of the tube T to the upper end Ta (upward of the condenser 23a). A condenser 23a is erected in the casing 30 so as to be guided in the tube T in the direction of the arrow Ub.

  The casing 30 includes a bottom plate 31, a top plate 32, a side plate 33, a baffle plate 34, a back plate 35 and a partition plate 36. In this heat exchange device 3b, the baffle plate 34 corresponds to the “first air direction regulating plate” and faces one surface (the right surface in FIG. 3) of the cooling core C25b in the evaporator 25b. Has been placed. Further, in this heat exchange device 3b, the partition plate 36 corresponds to the “second wind direction regulating plate” and is disposed to face the other surface (the left surface in FIG. 3) of the cooling core C25b. . In this case, the upper part of the partition plate 36 is bent toward the heating core C23a.

  In the heat exchange device 3b, the baffle plate 34 has a vertical length L1b (an example of “first length”) that is the vertical length L2b of the partition plate 36 (“second length”). The baffle plate 34 is disposed so as to close the upper portion of the one surface of the cooling core C25b, and the lower side of the baffle plate 34 (the lower end portion of the baffle plate 34). And the bottom plate 31) is formed with an opening 34a. Further, in this heat exchanging device 3b, a partition plate 36 is disposed so as to close the lower portion of the other surface of the cooling core C25b, and above the partition plate 36 (the upper end of the partition plate 36 and the ceiling). A ventilation hole 36a is formed between the plate 32 and the plate 32.

  Further, in this heat exchange device 3b, the length L2b of the partition plate 36 is formed to be equal to or greater than ½ of the length L3b in the vertical direction of the cooling core C25b (an example of “third length”). In addition, the sum of the length L1b of the baffle plate 34 and the length L2b of the partition plate 36 is formed to be longer than the length L3b of the cooling core C25b. Further, in this heat exchange device 3b, the lower end side portion of the baffle plate 34 and the upper end side portion of the partition plate 36 are overlapped by a length L4b in the thickness direction of the cooling core C25b (the left-right direction in the figure). A baffle plate 34 and a partition plate 36 are provided.

  Thereby, in this heat exchange device 3b, the air that has entered between the tube T and each fin F of the cooling core C25b from the lower part (opening 34a) on one surface of the cooling core C25b is cooled. An air guide path is formed in the casing 30 so as to move upward in the C25b as indicated by the arrow Ab and to be discharged from an upper portion (vent 36a) on the other surface of the cooling core C25b. . In this case, in the heat exchange device 3b, as described above, the refrigerant is introduced into the tube T of the cooling core C25b from the upper end portion Ta, and moves in the tube T toward the lower side of the cooling core C25b. It is done. Therefore, in the heat exchange device 3b, the refrigerant flow from the upper side to the lower side and the air flow from the lower side to the upper side face each other (a counter flow is formed) in the cooling core C25b.

  Further, in this heat exchange device 3b, between the partition plate 36 disposed on the other surface of the cooling core C25b and one surface of the heating core C23a (the right surface in the figure). A space Sb is formed, and a discharge port 35a is formed in the back plate 35 disposed opposite to the other surface (the left surface in the figure) of the heating core C23a. A blower 4b is formed in the discharge port 35a. It is attached. Thereby, in this heat exchanging device 3b, the air discharged from the air vent 36a to the space Sb is allowed to pass through the heating core C23a as indicated by the arrow Bb and is discharged from the discharge port 35a to the outside of the casing 30. An air guide path is formed in the casing 30.

  On the other hand, as described above, the dehumidifying device 3a is an example of a “temperature control device”, and within a humidity range targeted for a supply target (for example, a manufacturing device such as a semiconductor manufacturing device or a medical machine), And it is comprised so that supply of the air of humidity temperature control within the target temperature range is possible. As shown in FIG. 2, the dehumidifying device 3 a is configured such that an evaporator 25 a and a condenser 23 b are accommodated in a casing 10. In this case, in the dehumidifying device 3a, the evaporator 25a and the casing 10 together constitute a “cooling device”, and the condenser 23b and the casing 10 together constitute a “heating device”.

  In the dehumidifying device 3a, the refrigerant supplied to the evaporator 25a via the expansion valve 24a is directed from the upper end Ta of the tube T to the lower end Tb (downward of the evaporator 25a). The evaporator 25a is erected in the casing 10 so as to be guided in the tube T in the direction of Da (“one end portion of the cooling refrigerant pipe into which“ cooling refrigerant ”is introduced” is “cooling refrigerant”. An example of an arrangement that is located above the “other end of the pipe”. Further, in the dehumidifying device 3a, the refrigerant supplied to the condenser 23b via the regulating valve 22b is an arrow from the lower end Tb of the tube T toward the upper end Ta (upward of the condenser 23b). The condenser 23b is erected in the casing 10 so as to be guided in the tube T in the direction of Ua (the “one end of the cooling refrigerant pipe into which the“ cooling refrigerant ”is introduced” is the “cooling refrigerant”. An example of an arrangement that is positioned below the “other end of the pipe”).

  The casing 10 includes a bottom plate 11, a top plate 12, a side plate 13, a baffle plate 14, a back plate 15, and a partition plate 16. In this dehumidifying device 3a, the baffle plate 14 corresponds to the “first air direction regulating plate” and is disposed opposite to one surface (the left surface in FIG. 2) of the cooling core C25a in the evaporator 25a. Has been. Further, in the dehumidifying device 3a, the partition plate 16 corresponds to the “second wind direction regulating plate” and is disposed to face the other surface (the right surface in FIG. 2) of the cooling core C25a. In this case, the upper end portion of the partition plate 16 is bent toward the heating core C23b. Further, in the dehumidifying device 3a, the back plate 15 corresponds to the “third wind direction regulating plate” and is disposed opposite to the other surface (the right surface in FIG. 2) of the heating core C23b.

  In this case, in the dehumidifying device 3a, the length L1a in the vertical direction of the baffle plate 14 (an example of “first length”) is the length L2a in the vertical direction of the partition plate 16 (“second length”). The baffle plate 14 is disposed so as to close the upper portion of the one surface of the cooling core C25a, and the lower side of the baffle plate 14 (the lower end portion of the baffle plate 14). And the bottom plate 11) is formed with an opening 14a. Further, in the dehumidifying device 3a, the partition plate 16 is disposed so as to close the lower portion of the other surface of the cooling core C25a, and above the partition plate 16 (the upper end of the partition plate 16 and the top plate). 12), a vent hole 16a is formed.

  Further, in the dehumidifying device 3a, the length L2a of the partition plate 16 is formed to be not less than 1/2 of the length L3a in the vertical direction of the cooling core C25a (an example of “third length”). At the same time, the sum of the length L1a of the baffle plate 14 and the length L2a of the partition plate 16 is formed to be longer than the length L3a of the cooling core C25a. Further, in the dehumidifying device 3a, the lower end side portion of the baffle plate 14 and the upper end side portion of the partition plate 16 are obstructed so as to overlap by a length L4a in the thickness direction of the cooling core C25a (the left-right direction in the figure). A plate 14 and a partition plate 16 are provided.

  Thereby, in this dehumidifying device 3a, the air that has entered between the tube T and each fin F of the cooling core C25a from the lower part (opening 14a) on one surface of the cooling core C25a is cooled by the cooling core C25a. An air guide path is formed in the casing 10 so as to move upward as indicated by an arrow Aa and to be discharged from an upper portion (vent 16a) on the other surface of the cooling core C25a. In this case, in the dehumidifying device 3a, as described above, the refrigerant is introduced into the tube T of the cooling core C25a from the upper end portion Ta and moved in the tube T toward the lower side of the cooling core C25a. . Therefore, in this dehumidifier 3a, the flow of the refrigerant from the upper side to the lower side and the flow of the air from the lower side to the upper side face each other (a counter flow is formed) in the cooling core C25a.

  In the dehumidifying device 3a, the other surface of the cooling core C25a and the one surface (the left surface in the figure) of the heating core C23b are evaporated so as to face each other with the partition plate 16 in between. The vessel 25a and the condenser 23b are disposed, and a space Sa is formed between the partition plate 16 and one surface of the heating core C23b. Further, in the dehumidifying device 3a, a discharge port 15a is formed in the back plate 15 at a position facing the lower part of the other surface of the heating core C23b, and the blower 4a is attached to the discharge port 15a. Thereby, in this dehumidification apparatus 3a, the air discharged | emitted from the ventilation port 16a to space Sa is made to pass the heating core C23b as shown by arrow Ba, and is discharged | emitted from the discharge port 15a to the exterior of the casing 10. An air guide path is formed in the casing 10.

  The blower 4a is an example of a “blower”. As described above, the blower 4a is attached to the discharge port 15a of the casing 10 in the dehumidifier 3a, and sucks air in the casing 10 according to the control of the controller 5, thereby 10 outside air (or air collected from the supply target) is sucked into the casing 10 through the opening 14a and passed through the evaporator 25a (cooling core C25a), and then the space Sa and the condenser 23b (heating) Core C23b) is passed in this order and supplied to the supply target.

  Further, as described above, the blower 4b is attached to the discharge port 35a of the casing 30 in the heat exchange device 3b, and sucks the air inside the casing 30 according to the control of the controller 5, thereby removing the air outside the casing 30. After sucking into the casing 30 from the opening 34a and passing through the evaporator 25b (cooling core C25b), the space Sb and the condenser 23a (heating core C23a) are passed in this order to be released to the atmosphere.

  The controller 5 comprehensively controls the temperature control dehumidification system 1. Specifically, the controller 5 controls the blower 4a to suck air into the dehumidifying device 3a (casing 10), and controls the blower 4b to suck air into the heat exchange device 3b (casing 30). . Further, the controller 5 controls the compressor 21 to compress (pump) the refrigerant, and also controls the adjustment valve 22a to adjust the flow rate of the refrigerant from the compressor 21 to the condenser 23a, and the adjustment valve 22b. It controls to adjust the flow rate of the refrigerant from the compressor 21 to the condenser 23b.

  Next, the operation of each part when supplying the air whose temperature is dehumidified by the temperature control dehumidification system 1 to the supply target will be described with reference to the accompanying drawings.

  In this temperature control dehumidification system 1, the controller 5 starts the operation of the heat pump 2 when a start switch of an operation unit (not shown) is operated. At this time, a part of the refrigerant compressed by the compressor 21 passes through the regulating valve 22a and is supplied to the condenser 23a of the heat exchange device 3b. In the heat exchange device 3b, the high-temperature and high-pressure refrigerant pumped from the compressor 21 is introduced from the lower end Tb into the tube T of the heating core C23a in the condenser 23a. While being moved in the tube T toward the upper end Ta (above the condenser 23a) in the direction of the arrow Ub shown in FIG. 6, heat is exchanged with the surrounding air through the tube T and the fins F, and cooling is performed. Is done. Thereby, the refrigerant | coolant supplied in the tube T is condensed.

  The refrigerant condensed in the condenser 23a is supplied to the evaporator 25a of the dehumidifying device 3a after passing through the expansion valve 24a. At this time, in the dehumidifying device 3a, the refrigerant passed through the expansion valve 24a is introduced from the upper end portion Ta to the tube T of the cooling core C25a in the evaporator 25a, and this refrigerant is shown in FIG. While moving in the tube T toward the lower end Tb (below the evaporator 25a) in the direction of the arrow Da, heat is exchanged with the surrounding air via the tube T and the fins F, and the temperature rises. The air around the tube T and the fins F is cooled. Further, the refrigerant whose temperature has been increased by heat exchange with the surrounding air in the evaporator 25a is sucked into the compressor 21 and compressed again.

  On the other hand, another part of the refrigerant compressed by the compressor 21 passes through the regulating valve 22b and is supplied to the condenser 23b of the dehumidifying device 3a. In the dehumidifying device 3a, the high-temperature and high-pressure refrigerant pumped from the compressor 21 is introduced from the lower end Tb with respect to the tube T of the heating core C23b in the condenser 23b, and this refrigerant is shown in FIG. While being moved in the tube T toward the upper end Ta (above the condenser 23b) in the direction of the arrow Ua shown, heat is exchanged with the surrounding air via the tube T and the fins F and cooled. The As a result, the refrigerant is condensed in the tube T, and the air around the tube T and each fin F is heated.

  The refrigerant condensed in the condenser 23b is supplied to the evaporator 25b of the heat exchange device 3b after passing through the expansion valve 24b. At this time, in the heat exchange device 3b, the refrigerant passed through the expansion valve 24b is introduced from the upper end portion Ta into the tube T of the cooling core C25b in the evaporator 25b, and this refrigerant is shown in FIG. While being moved in the tube T toward the lower end Tb (below the evaporator 25b) in the direction of the arrow Db shown, heat is exchanged with the surrounding air via the tube T and the fins F. While being raised, the air around the tube T and the fins F is cooled. Further, the refrigerant whose temperature has been increased by heat exchange with the surrounding air in the evaporator 25b is sucked into the compressor 21 and compressed again.

  Further, the controller 5 starts the operation of the blowers 4a and 4b simultaneously with the start of the operation of the heat pump 2 (or when the specified time has elapsed from the start of the operation of the heat pump 2). At this time, in the dehumidifying device 3a, the blower 4a attached to the discharge port 15a of the casing 10 sucks the air in the casing 10, so that the air outside the casing 10 (or the air recovered from the supply target). ) Is introduced into the casing 10 through the opening 14a. Further, as described above, when the air sucked into the casing 10 is passed between the tubes T and the fins F of the cooling core C25a in the evaporator 25a, heat is exchanged with the refrigerant in the tubes T. Is cooled and discharged into the space Sa.

  At this time, when the air introduced from the opening 14a contains a certain amount of moisture, the moisture contained in the air is condensed water (drain water) by cooling the air by the evaporator 25a. Removed from the air (dehumidified). As a result, the air discharged from the vent 16a to the space Sa (air that has been cooled by the evaporator 25a) is in a low temperature and low humidity state. Condensed water (drain water) generated in the evaporator 25a flows down to the lower end of the evaporator 25a through each fin F, and is discharged to the outside of the casing 10 from a drain discharge port (not shown) formed in the bottom plate 11. Is done.

  Further, as described above, the low-temperature and low-humidity air discharged into the space Sa exchanges heat with the refrigerant in the tube T when it is passed between the tube T and the fins F of the heating core C23b in the condenser 23b. After being heated to a temperature within the target temperature range, it is discharged out of the casing 10 through the discharge port 15a. Thereby, dehumidification and temperature control by the dehumidifying device 3a of the air to be supplied to the supply target are completed, and the air discharged from the casing 10 is blown toward the supply target by the blower 4a.

  On the other hand, in the heat exchange device 3b, the blower 4b attached to the discharge port 35a of the casing 30 sucks the air in the casing 30 so that the air outside the casing 30 is introduced into the casing 30 from the opening 34a. Is done. Further, as described above, when the air sucked into the casing 30 is passed between the tubes T and the fins F of the cooling core C25b in the evaporator 25b, heat is exchanged with the refrigerant in the tubes T. Then, it is cooled and discharged into the space Sb. When the air introduced from the opening 34a contains a certain amount of moisture, the air is cooled by the evaporator 25b, so that the moisture contained in the air is condensed water (drain water) from the air. Although being removed (dehumidified), the evaporator 25b is not a heat exchanger that cools air for the purpose of dehumidification, and therefore, description on dehumidification in the evaporator 25b is omitted.

  Further, as described above, the low-temperature air discharged into the space Sb exchanges heat with the refrigerant in the tube T when it is passed between the tube T and the fins F of the heating core C23a in the condenser 23a. As a result, the temperature is raised and discharged from the discharge port 35 a to the outside of the casing 30. Further, as a result of cooling the refrigerant in the tube T in the heating core C23a (the high-temperature and high-pressure refrigerant pumped from the compressor 21) by the heat exchange in the condenser 23a, the refrigerant is supplied to the evaporator 25a of the dehumidifier 3a. A sufficient amount of refrigerant to be condensed is condensed in the condenser 23a.

  In this case, in the dehumidifying device 3a in the temperature control dehumidifying system 1 of the present example, as described above, one surface of the cooling core C25a in the evaporator 25a (the left surface shown in FIG. 2: air to be cooled is introduced) The baffle plate 14 is disposed so as to block the upper part of the surface on the side to be cooled, and the other surface of the cooling core C25a (the right surface shown in FIG. 2: the cooled air is discharged). The partition plate 16 is disposed so as to block the lower portion of the surface to be closed. For this reason, in the dehumidifying device 3a of this example, the air introduced from the opening 14a between the baffle plate 14 and the bottom plate 11 is directed upward in the cooling core C25a as indicated by an arrow Aa in FIG. It moves and is discharged to the space Sa from the vent 16a between the partition plate 16 and the top plate 12.

  Therefore, in the dehumidifying device 3a of this example, for example, when the temperature of the air sucked from the opening 14a is high or when the amount of air is large, that is, when the burden on the evaporator 25a is large, the cooling core Even if it becomes difficult to cool the air suitably in the lower part of C25a, the result is that the insufficiently cooled air is sufficiently cooled and dehumidified when it reaches the upper part of the cooling core C25a. The air discharged from the vent 16a to the space Sa can be set to a humidity within a target humidity range.

  In this case, unlike the dehumidifying device 3a of this example, the sum of the “first length” of the “first wind direction regulating plate” and the “second length” of the “second wind direction regulating plate” is In the “cooling device” formed shorter than the “third length” of the “cooling core”, the lower end portion of the “first wind direction regulating plate” and the upper end of the “second wind direction regulating plate” The part side portion does not overlap in the thickness direction of the “cooling core”. In such a configuration, the air to be cooled in the “evaporator” is between the lower end portion of the “first wind direction restricting plate” and the upper end portion of the “second wind direction restricting plate” (both wind direction restricting plates). In the portion where no plate is present), it passes between the “cooling refrigerant pipe” and the “cooling fin” in the thickness direction of the “cooling core” from one surface of the “cooling core” to the other surface. There is a fear, and it becomes difficult to generate an air flow upward of the cooling core C25a like the dehumidifying device 3a of this example.

  On the other hand, in the dehumidifying device 3a of this example, as described above, the baffle plate so that the lower end portion side portion of the baffle plate 34 and the upper end portion side portion of the partition plate 36 overlap in the thickness direction of the cooling core C25b. 34 and a partition plate 36 are disposed. This avoids a situation in which the air to be cooled in the evaporator 25a passes between the tubes T and the fins F in the thickness direction of the cooling core C25a from one surface of the cooling core C25a toward the other surface. Thus, as described above, it is possible to suitably generate the air flow toward the upper side of the cooling core C25a.

  On the other hand, in the conventional dehumidifying and heating device 3x described above, moisture in the air is removed as drain water (condensation water) when it passes through the evaporator 21x, and this drain water drops on the drain pan 170x through the fin Fx. The structure which falls and drains out of the dehumidification warming apparatus 3x from the drain water discharge port is employ | adopted. However, in the conventional dehumidifying / warming device 3x, for example, when the amount of air blown through the wind circuit 23x is large (when the speed of the air passing through the evaporator 21x is high), or through the evaporator 21x. When the generated air contains a large amount of moisture (when the humidity is high), the drain water generated in the upper part of the evaporator 21x separates from the fins Fx before dripping down to the lower end of the evaporator 21x. The drain water may ride on the air flow and reach the condenser 20x. At this time, as a result of the drain water coming into contact with the high-temperature condenser 20x and volatilizing it, the air supplied through the condenser 20x to the supply target despite being dehumidified in the evaporator 21x. Humidity will rise.

  On the other hand, in the temperature control dehumidification system 1 (dehumidification device 3a) of the present example, the partition plate 16 is disposed on the other surface (surface on the side from which air is discharged) of the cooling core C25a of the evaporator 25a. Thus, the lower end portion of the cooling core C25a is closed by the partition plate 16. Therefore, even if a large amount of drain water is generated in the upper portion of the evaporator 25a (cooling core C25a), the drain water is dripped down along the fin F toward the lower side of the evaporator 25a (cooling core C25a). During this time, it is possible to avoid a situation where the fin F is detached and discharged to the condenser 23b side (the space Sa between the evaporator 25a and the condenser 23b).

  In this case, as described above, in the temperature control / dehumidification system 1 (dehumidification device 3a) of this example, the length L2a of the partition plate 16 is sufficiently long, specifically, the length L1a of the baffle plate 14, specifically, Since the cooling core C25a is formed to have a length that is 1/2 or more of the length L3a, the drain water generated in the cooling core C25a is more reliably discharged to the condenser 23b side (space Sa). Has been avoided.

  Moreover, in the dehumidifying device 3a in the temperature control dehumidifying system 1 of this example, as described above, the partition plate 16 disposed on the other surface of the cooling core C25a in the evaporator 25a and the heating core in the condenser 23b. A space Sa is provided between one side of C23b (the left side shown in FIG. 2: the side on which air to be heated is introduced). In this case, although it is different from the dehumidifying device 3a of this example, the “second wind direction regulating plate” is formed without generating a space between the “second wind direction regulating plate” and the “heater (heating core)”. ”And“ heater (heating core) ”are arranged in close contact with each other, the air exhausted from the upper part of the“ second wind direction regulating plate ”is placed in the upper part of the“ heater (heating core) ”. Although entering, there is a possibility that the air discharged from the upper part of the “second wind direction regulating plate” does not enter the lower part of the “heater (heating core)”.

  In contrast, in the dehumidifying device 3a of the present example, the air discharged from the upper part of the partition plate 16 (vent 16a) to the space Sa spreads from the upper part of the space Sa to the entire lower part. As indicated by arrow Ba in FIG. 2, air is caused to enter between the tube T and each fin F of the heating core C23b from the entire region from the upper part to the lower part on one surface of the condenser 23b (heating core C23b). Thus, it can be suitably heated.

  Further, in the dehumidifying device 3a of this example, as described above, the outlet 15a is provided in the back plate 15 at a position facing the lower portion of the condenser 23b (heating core C23b). Therefore, the situation where the air discharged from the vent 16a to the upper part of the space Sa is discharged from the casing 10 without reaching the lower part of the heating core C23b is avoided. As a result, the air to be supplied to the supply target can be reliably heated to a temperature within the target temperature range by the condenser 23b.

  Further, in the heat exchange device 3b in the temperature control / dehumidification system 1 of the present example, as described above, one surface of the cooling core C25b in the evaporator 25b (the right surface shown in FIG. 3: air to be cooled is introduced). The baffle plate 34 is disposed so as to close the upper portion of the surface to be cooled), and the other surface of the cooling core C25b (the left surface shown in FIG. 3: the air that has been cooled is discharged. The partition plate 36 is disposed so as to block the lower part of the surface to be closed. For this reason, in the heat exchange device 3b of this example, the air introduced from the opening 34a between the baffle plate 34 and the bottom plate 31 is directed upward in the cooling core C25b as indicated by an arrow Ab in FIG. Thus, the air is discharged from the vent 36a between the partition plate 36 and the top plate 32 to the space Sb.

  Therefore, in the heat exchange device 3b of this example, for example, when the temperature of the air sucked from the opening 34a is high, that is, when the burden on the evaporator 25b is large, or the amount of refrigerant supplied to the evaporator 25b Even when the amount of refrigerant required in the evaporator 25a of the dehumidifying device 3a is small (when the amount of refrigerant required in the evaporator 25a of the dehumidifying device 3a is large) As a result of sufficient cooling when the insufficiently cooled air reaches the upper portion of the cooling core C25b, the temperature of the air discharged from the vent 36a to the space Sb is suitably condensed in the condenser 23a. It is possible to make the temperature sufficiently low within the target temperature range that can be achieved.

  In the heat exchange device 3b of this example, as described above, the partition plate 36 disposed on the other surface of the cooling core C25b in the evaporator 25b and the one surface of the heating core C23a in the condenser 23a. A space Sb is provided between (a right surface shown in FIG. 3 and a surface on which air for improving the refrigerant condensing efficiency is introduced). As a result, in the heat exchange device 3b of the present example, the air discharged from the upper part (ventilation hole 36a) of the partition plate 36 to the space Sb spreads from the upper part of the space Sb to the entire lower part. As shown by an arrow Bb, air enters between the tube T and each fin F of the heating core C23a from the entire region from the upper part to the lower part on one surface of the condenser 23a (heating core C23a), Thereby, the refrigerant can be suitably cooled and condensed in the entire region from the lower end Tb to the upper end Ta of the tube T.

  Further, in the heat exchange device 3b of this example, as described above, the outlet 35a is provided in the back plate 35 at a position facing the lower part of the condenser 23a (heating core C23a). Therefore, the situation where the air discharged from the vent 36a to the upper portion of the space Sb does not reach the lower portion of the heating core C23a and is discharged from the casing 30 is avoided. As a result, the refrigerant in the tube T is reliably cooled and condensed in the heating core C23a, and the necessary amount of refrigerant can be reliably supplied to the evaporator 25a of the dehumidifier 3a.

  Thus, in the “cooling device” in the temperature control dehumidification system 1, one end of the tube T (upper end Ta in this example) is the other end of the tube T (lower end Tb in this example). The evaporators 25a and 25b are arranged so that the cooling refrigerant is guided in the tube T toward the lower side of the evaporators 25a and 25b, and the lengths L1a and L1b in the vertical direction are arranged. The baffle plates 14 and 34, which are formed shorter than the vertical lengths L2a and L2b of the partition plates 16 and 36, are disposed so as to close the upper portion of one surface of the cooling cores C25a and C25b. The partition plates 16 and 36 are disposed so as to close the lower portion of the other surface of the cooling cores C25a and C25b, and the lower portion (opening portions 14a and 34) of one surface of the cooling cores C25a and C25b. ) From between the tubes T and the fins F move upward in the cooling cores C25a and C25b, and the upper part (the vent holes 16a and 36a) on the other surface of the cooling cores C25a and C25b. ) To the spaces Sa and Sb.

  Therefore, according to the “cooling device” in the temperature control dehumidification system 1, the burden on the evaporators 25a and 25b is large, and in the vicinity of the lower end portion Tb of the tube T (below the cooling cores C25a and C25b). Even if it becomes difficult to cool the air appropriately, the air is guided from the lower part to the upper part of the cooling cores C25a, C25b by the baffle plates 14, 34 and the partition plates 16, 36. The air can be suitably cooled at the upper part of the cooling cores C25a and C25b. Moreover, when drain water (condensation water) is generated by cooling by the cooling cores C25a and C25b by providing the partition plates 16 and 36 on the lower end side portion on the other surface of the cooling cores C25a and C25b, The situation where this drain water is discharged to the other surface side of the cooling cores C25a and C25b can be suitably avoided.

  Further, according to the “cooling device” in the temperature control dehumidification system 1, the lengths L2a and L2b of the partition plates 16 and 36 are not less than ½ of the vertical lengths L3a and L3b of the cooling cores C25a and C25b. By being formed in this manner, the air that has entered between the tubes T and the fins F from one surface of the cooling cores C25a and C25b can be reliably guided upward of the cooling cores C25a and C25b. it can.

  Further, in the “cooling device” in the temperature regulating dehumidification system 1, the baffle plate 14 and the partition plate 16 are formed so that the sum of the length L1a and the length L2a is longer than the length L3a. In addition, the baffle plate 14 and the partition plate 16 are arranged so that the lower end side portion of the baffle plate 14 and the upper end portion side portion of the partition plate 16 overlap each other by the length L4a in the thickness direction of the cooling core C25a. The baffle plate 34 and the partition plate 36 are formed so that the sum of the length L1b and the length L2b is longer than the length L3b, and the lower end side portion of the baffle plate 34 and the partition plate The baffle plate 34 and the partition plate 36 are disposed so that the upper end portion side portion 36 overlaps the length L4b in the thickness direction of the cooling core C25b.

  Therefore, according to the “cooling device” in the temperature control and dehumidification system 1, the air that has entered between the tubes T and the fins F from one surface of the cooling cores C25a and C25b has a thickness of the cooling cores C25a and C25b. Without moving the cooling cores C25a and C25b in the direction and being discharged to the other surface, the other is surely moved between the tubes T and the fins F toward the upper side of the cooling cores C25a and C25b. It can be discharged to the surface side.

  Further, in the dehumidifying device 3a in the temperature control dehumidifying system 1, the other surface of the cooling core C25a in the evaporator 25a and the one surface of the heating core C23b in the condenser 23b face each other across the partition plate 16. Thus, an evaporator 25a and a condenser 23b are provided. Moreover, in this temperature control dehumidification system 1, it passes in order of said dehumidification apparatus 3a, the "cooling apparatus" comprised with the evaporator 25a, and the "heating apparatus" comprised with the condenser 23b. And a blower 4a for blowing air. Therefore, according to the dehumidifying device 3a and the temperature control / dehumidifying system 1, the air cooled and dehumidified by the cooling device can be supplied to the supply object in a state in which the temperature is adjusted by heating the air by the heating device according to the purpose.

  Furthermore, according to the dehumidifying device 3a in the temperature control dehumidifying system 1, one end portion (the lower end portion Tb in this example) of the tube T is connected to the other end portion (the upper end portion Ta in this example) of the tube T. The condenser 23b is arranged so that the heating refrigerant is guided in the tube T toward the upper side of the condenser 23b, and the lower side of the other surface of the heating core C23b in the baffle plate 14 is arranged. Since the discharge port 15a for discharging the air heated by the condenser 23b is formed at a position opposite to the part, the refrigerant in the tube T in the entire region from the upper end to the lower end of the condenser 23b (heating core C23b). Heat exchange between the tube T and the air around the fins F, and the air to be treated can be reliably heated.

  Further, according to the dehumidifying device 3a in the temperature control dehumidifying system 1, since the space Sa is formed between the partition plate 16 and one surface of the condenser 23b, the partition plate 16 can be viewed from above (vent 16a). Since the air exhausted into the space Sa spreads from the upper part of the space Sa to the entire lower part and is made to enter between the tubes T and the fins F of the condenser 23b (heating core C23b), the heating core C23b In the entire region from the upper part to the lower part, heat exchange can be suitably performed between the refrigerant in the tube T and the air around the tube T and the fins F, so that the air to be processed can be heated more reliably.

  Further, according to the dehumidifying device 3a in the temperature control dehumidifying system 1, the cooling by the evaporator 25a (cooling core C25a) is completed by bending the upper end portion of the partition plate 16 toward the heating core C23b. The discharged air can be smoothly discharged into the space Sa.

  Note that the configurations of the “cooling device”, the “temperature control device”, and the “temperature control dehumidification system” are not limited to the configuration examples of the temperature control dehumidification system 1 described above.

  For example, an example of the “cooling device” configured by the evaporator 25a of the heat pump 2 and the casing 10 and the example of the “temperature control device” configured by the “cooling device” and the condenser 23b of the heat pump 2 have been described. However, the circuit configuration of the refrigeration cycle (heat pump) constituting the “evaporator (cooler)” and the “condenser (heater)” constituting the “cooling device” and the “temperature control device” is similar to that of the heat pump 2. The circuit configuration is not limited. Specifically, a circuit configuration such as a heat pump 2a in the temperature control / dehumidification system 1A (another example of the “temperature control / dehumidification system”) illustrated in FIG. 4 can be employed. In addition, about the component similar to temperature control dehumidification system 1A (heat pump 2) mentioned above in this temperature control dehumidification system 1A (heat pump 2a), the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

  In the heat pump 2a of the temperature control dehumidification system 1A, the expansion valve 24b and the evaporator 25b in the heat pump 2 described above do not exist, and the condenser 23b of the dehumidifier 3a is connected to the evaporator 25a via the expansion valve 24a. Moreover, in this temperature control dehumidification system 1A, it replaces with the heat exchange apparatus 3b in the temperature control dehumidification system 1, and is equipped with the condenser 23a which radiates the heat | fever of a refrigerant | coolant to air | atmosphere. A device for exchanging heat between them). Also in the temperature control / dehumidification system 1A including the heat pump 2a employing such a circuit configuration, the dehumidification device 3a is configured in the same manner as the dehumidification device 3a of the temperature control / dehumidification system 1 described above. The effect similar to the effect show | played by the "cooling device" in the 1 dehumidification apparatus 3a can be show | played.

  Further, the lower end portion side portion of the baffle plate 14 corresponding to the “first air direction restriction plate” and the upper end portion side portion of the partition plate 16 corresponding to the “second air direction restriction plate” of the cooling core C25a. The dehumidifying device 3a in which the baffle plate 14 and the partition plate 16 are disposed so as to overlap by the length L4a in the thickness direction, and the lower end side portion of the baffle plate 34 corresponding to the “first wind direction regulating plate”; Heat in which the baffle plate 34 and the partition plate 36 are arranged such that the upper end side portion of the partition plate 36 corresponding to the “second wind direction regulating plate” overlaps the length L4b in the thickness direction of the cooling core C25b. The specific example of the configuration of the “cooling device” and the “temperature control device” has been described by taking the exchange device 3b as an example. The configuration of the “cooling device” and the “temperature control device” includes the dehumidifying device 3a and the heat The configuration is not limited to the example of the exchange device 3b.

  For example, a dehumidifying device 3d shown in FIG. 5 is another example of a “temperature adjusting device” that can be used in place of the dehumidifying device 3a in the temperature control dehumidification system 1 or 1A, and is used as a “first wind direction regulating plate”. The corresponding length L1d of the baffle plate 14 (another example of “first length”) is slightly shorter than the length L1a of the baffle plate 14 in the dehumidifying device 3a, and is the “second wind direction regulating plate”. The dehumidifying device 3a, except that the corresponding length L2d of the partition plate 16 (another example of “second length”) is slightly shorter than the length L2a of the partition plate 16 in the dehumidifying device 3a. It is configured in the same way. In addition, about the component which has the same function as the dehumidifier 3a in this dehumidifier 3d, the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

  In this dehumidifier 3d, the sum of the length L1d of the baffle plate 14 and the length L2d of the partition plate 16 is formed to be shorter than the length L3a (third length) of the cooling core C25a. . Further, in this dehumidifying device 3d, a region where the lower end side portion of the baffle plate 14 and the upper end portion side portion of the partition plate 16 do not overlap in the thickness direction of the cooling core C25a (the left-right direction in the figure) is only the length L5d. The baffle plate 14 and the partition plate 16 are arrange | positioned so that it may arise. In this dehumidifier 3d, the length L2d of the partition plate 16 is formed to be equal to or greater than 1/2 of the length L3a in the vertical direction of the cooling core C25a. Even if it becomes difficult to cool the air suitably in the vicinity of the lower end portion Tb at T (the lower portion of the cooling core C25a), the baffle plate 14 and the partition plate 16 are used to lower the cooling core C25a. As a result of the air being guided from the part toward the upper part as indicated by the arrow Aa, the air can be suitably cooled in the upper part of the cooling core C25a.

  Further, in this dehumidifying device 3d, in the same manner as the dehumidifying device 3a described above, the partition plate 16 is provided at the lower end side portion on the other surface of the cooling core C25a, so that the drain water is cooled by the cooling core C25a. When (condensation water) occurs, it is possible to suitably avoid a situation in which this drain water is discharged to the other surface side of the cooling core C25a. In addition, although illustration and description are omitted, instead of the heat exchange device 3b in the temperature control dehumidification system 1, the same “first wind direction restriction plate” and “second wind direction restriction plate” as those of the dehumidification device 3d described above are provided. By disposing the provided heat exchange device, the same effect as the temperature control dehumidification system 1 provided with the heat exchange device 3b can be obtained.

  Further, the configuration of the dehumidifying devices 3a and 3d and the heat exchange device 3b in which the “cooling device” and the “heating device” are integrally combined has been described as an example, but even when the “cooling device” is configured as a single unit. , By disposing a “first air direction restriction plate” on one surface of the “cooling core” and disposing a “second air direction restriction plate” on the other surface of the “cooling core”, The same effect as the effect exhibited in the “cooling device” in the dehumidifying device 3a and the heat exchanging device 3b can be obtained. Specifically, as an example, the cooling device 3e shown in FIG. 6 is configured in the same manner as the “cooling device” in the dehumidifying devices 3a and 3d described above, the condenser 23b in the dehumidifying devices 3a and 3d does not exist, and The configuration is the same as that of the dehumidifying devices 3a and 3d except that a casing 40 is provided instead of the casing 10. In addition, about the component which has the function similar to each component of the dehumidifier 3a, 3d in this cooling device 3e, the same code | symbol is attached | subjected and the overlapping description is abbreviate | omitted.

  In this case, the casing 40 includes a bottom plate 41, a top plate 42, and a side plate (not shown) instead of the bottom plate 11, the top plate 12, and the side plate 13 in the casing 10. A back plate 45, which is another example of the “wind direction regulating plate”, is disposed on the other surface of the cooling core C25a in the evaporator 25a and is exhausted above the back plate 45 (between the back plate 45 and the top plate 42). An outlet 45a is formed. Further, the length and arrangement of the baffle plate 14 and the back plate 45 in the cooling device 3e are the same as the arrangement and length of the baffle plate 14 and the partition plate 16 of the dehumidifying device 3a, as shown in FIG. Therefore, according to this cooling device 3e, the flow of air toward the upper side of the cooling core C25a in the same manner as the “cooling device (device comprising the evaporator 25a, the baffle plate 14 and the partition plate 16)” in the dehumidifying device 3a. Therefore, the same effect as that produced by the “cooling device” in the dehumidifying device 3a can be obtained.

  In addition, the configuration having the tube T formed in a spiral shape as the “cooling refrigerant pipe” or the “heating refrigerant pipe” has been described as an example. However, instead of such a configuration, the tube T is formed in a twisted shape. These tubes can also be employed as “cooling refrigerant piping” or “heating refrigerant piping” (not shown). Further, the configuration in which the blowers 4a and 4b are disposed on the downstream side in the air flow direction has been described as an example. It is also possible to adopt a configuration in which “blowers” are arranged in the portions 14a, 34a, etc. (not shown).

DESCRIPTION OF SYMBOLS 1,1A Temperature control dehumidification system 2,2a Heat pump 3a, 3d Dehumidifier 3b, 3c Heat exchange device 3e Cooling device 4a, 4b Blower 5 Controller 10, 30, 40 Casing 11, 31, 41 Bottom plate 12, 32, 42 Top plate 13, 33 Side plate 14, 34 Baffle plate 14a, 34a Opening 15, 35, 45 Back plate 15a, 35a, 45a Discharge port 16, 36 Partition plate 16a, 36a Vent 21 Compressor 22a, 22b Regulating valve 23a, 23b Condensation 24a, 24b Expansion valve 25a, 25b Evaporator C23a, C23b Heating core C25a, C25b Cooling core F Fin L1a-L4a, L1b-L4b, L1d, L2d, L5d Length Sa, Sb Space T Tube Ta Upper end Tb Lower end

Claims (8)

A cooling refrigerant pipe that is formed in a spiral shape or a kink shape and guides the cooling refrigerant from one end to the other end, and a cooling fin that is disposed so as to be in contact with the outer peripheral surface of the cooling refrigerant pipe. Thus, a thick plate-shaped cooling core is formed, and the air on one surface side of the cooling core passes between the cooling refrigerant pipe and the cooling fin and passes through the other of the cooling cores. When the air is moved to the surface side, the air and the cooling refrigerant guided through the cooling refrigerant pipe exchange heat with each other via the cooling refrigerant pipe and the cooling fin. A cooler configured to be coolable,
A first air direction regulating plate disposed on the one surface of the cooling core;
A second air direction restriction plate disposed on the other surface of the cooling core,
In the cooler, the one end portion of the cooling refrigerant pipe is positioned higher than the other end portion of the cooling refrigerant pipe, and the cooling refrigerant moves toward the lower side of the cooler. Arranged to be guided in the piping,
The first wind direction restricting plate is formed so that a first length in the vertical direction is shorter than a second length in the vertical direction of the second wind direction restricting plate, and the upper side on the one surface of the cooling core. Arranged to occlude the site,
The second air direction restriction plate is disposed so as to close a lower portion of the other surface of the cooling core,
Air that has entered between the cooling refrigerant pipe and the cooling fin from a lower part of the one surface of the cooling core moves upward in the cooling core, and the cooling core A cooling device in which an air guide path is formed so as to be discharged from an upper portion of the other surface.   2. The cooling device according to claim 1, wherein the second air direction regulating plate is formed such that the second length is equal to or more than ½ of a third length in the vertical direction of the cooling core.   The first wind direction restriction plate and the second wind direction restriction plate are formed such that a sum of the first length and the second length is longer than the third length. The cooling device according to claim 2, wherein a lower end portion side portion of the wind direction regulating plate and an upper end portion side portion of the second wind direction regulating plate are arranged so as to overlap in a thickness direction of the cooling core. The cooling device according to any one of claims 1 to 3,
A heating refrigerant pipe which is formed in a spiral shape or a distorted shape and guides the heating refrigerant from one end to the other end, and a heating fin disposed so as to be in contact with the outer peripheral surface of the heating refrigerant pipe are provided. Thus, a thick plate-shaped heating core is formed, and the air on one surface side of the heating core passes between the heating refrigerant pipe and the heating fin, and the other of the heating cores When the air is moved to the surface side, the air and the heating refrigerant guided in the heating refrigerant pipe exchange heat with each other via the heating refrigerant pipe and the heating fin. A heating device having a heater configured to be capable of heating,
The cooling device and the heating device are disposed so that the other surface of the cooling core and the one surface of the heating core are opposed to each other with the second air direction restriction plate interposed therebetween. The temperature control apparatus comprised so that the air cooled with the vessel could be heated with the said heater and supplied to a supply object. The heating device includes a third wind direction regulating plate disposed on the other surface of the heating core,
In the heater, the one end portion of the heating refrigerant pipe is positioned below the other end portion of the heating refrigerant pipe, and the heating refrigerant moves upward of the heater. Arranged to be guided in the piping,
5. The temperature control according to claim 4, wherein the third air direction restriction plate is formed with a discharge port for discharging air heated by the heater at a position facing a lower portion of the other surface of the heating core. apparatus.   The temperature control device according to claim 4 or 5, wherein a space is formed between the second air direction regulating plate and the one surface of the heating core.   The temperature control device according to claim 6, wherein the second wind direction regulating plate is bent at an upper end side portion toward the heating core. A temperature control device according to any one of claims 4 to 7,
A temperature control dehumidification system comprising a blower that blows the air so as to pass through the cooling device and the heating device in this order.

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