JP2010007955A - Temperature controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a temperature controller, performing defrosting for an evaporator without stopping the operation to thereby make precise temperature control. <P>SOLUTION: This temperature controller 52 includes: a heating circuit in which a heating medium compressed and delivered by a compressor 18 is distributed by a distributor 20 and circulated in the order of a heater 16 (a condenser), an expansion valve 34, an evaporator 32 absorbing heat from an external heating medium as an external heat source and the compressor 18; and a cooling circuit in which the remainder of the heating medium distributed to the heating circuit side by the distributor 20 is distributed, and circulated in the order of a condenser 26 for releasing heat to the external heating medium as an external heat source, an expansion valve 28, a cooler 14 (an evaporator) and the compressor 18, a fluid passed through the heater 16 and the cooler 14 being controlled to reach a predetermined temperature, wherein the evaporator 32 of the heating circuit is functioned as the condenser 26 of the cooling circuit, the condenser 26 of the cooling circuit is functioned as the evaporator 32, and a switching means is provided for switching between both functions. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a temperature control device.

Usually, in the precision processing field such as the manufacturing process of semiconductor devices, most of them are installed in a clean room in which temperature and humidity are controlled.
However, in recent years, in the precision processing field, processes requiring precision processing with higher processing accuracy than before have been emerging.
In a process that requires such high precision processing, it is usually required that the temperature change environment is smaller than that of a clean room. For this reason, a process requiring high precision processing or the like is provided in a space unit in which precise temperature management is performed.

As a temperature adjustment device used for temperature adjustment of such a space unit, a temperature adjustment device as shown in FIG. 10 is disclosed (for example, refer to Patent Document 1).
The temperature control apparatus shown in FIG. 10 includes a compressor 100, a three-way valve 102, a condenser 104, an expansion valve 106, a cooler 108 and a heater 110. And a heating channel provided with a vessel 110.
The cooler 108 and the heater 110 adjust the temperature of the air flow to be adjusted from the fan 112.

  In the temperature adjusting device shown in FIG. 10, the high-temperature heat medium compressed by the compressor 100 is distributed to the cooling channel and the heating channel by the three-way valve 102. The high-temperature heat medium distributed to the cooling channel side is cooled by the condenser 104. The cooled heat medium is adiabatically expanded and cooled by the expansion valve 106, and is supplied to the cooler 108. In the cooler 108, the heat medium that has been heated to absorb the temperature while cooling the air flow to be temperature-adjusted blown from the fan 112 is supplied to the compressor 100.

  On the other hand, the high-temperature heat medium distributed to the heating flow path side is supplied to the heater 110, and the air flow to be temperature-adjusted cooled by the cooler 108 is heated and adjusted to a desired temperature. As described above, the heating medium that is radiated and cooled while heating the air flow to be temperature adjusted in the heater 110 passes through the expansion valve 106 and the cooler 108 and is supplied to the compressor 100.

JP-A 51-97048

In the temperature adjusting device shown in FIG. 10, the entire amount of the high-temperature heat medium compressed by the compressor 100 passes through the expansion valve 106, is adiabatically expanded and cooled, and is supplied to the cooler 108. The amount of cooling energy for cooling the air stream to be temperature-adjusted blown out from the air is constant.
On the other hand, by adjusting the flow rate of the high-temperature heat medium distributed to the heating flow path side by the three-way valve 102, the heating amount in the heater 110 with respect to the air flow to be temperature-adjusted cooled by the cooler 108 can be adjusted.

Therefore, it is possible to adjust the temperature of the air flow to be temperature adjusted that passes through the cooler 108 and the heater 110, and it is possible to perform temperature management in the space unit in a narrow temperature range.
However, in the temperature control apparatus shown in FIG. 10, the entire amount of the high-temperature heat medium compressed by the compressor 100 passes through the expansion valve 106, is adiabatically expanded and cooled, and is supplied to the cooler 108. The temperature adjustment for the air flow to be adjusted from the fan 112 is performed by reheating the high-temperature heat medium compressed by the compressor 100 supplied to the heater 110 exclusively.

As described above, in the temperature control method employed in the temperature adjustment apparatus shown in FIG. 10, the heat medium used for heating also flows through the cooling flow path, so the amount of heat that can be heated is only the amount of heat generated by the power of the compressor, and the cooler 108 And it is difficult to cope with load fluctuations on the heater 110.
For this reason, when the set temperature of the air flow subject to temperature adjustment passing through the cooler 108 and the heater 110 is significantly increased, the temperature of the air flow subject to temperature adjustment does not reach the set temperature or reaches the set temperature. It may take a long time to complete.

  The inventors have conceived a configuration in which the heat medium that has passed through the heater in the heating channel is adiabatically expanded by an expansion valve, and then flows into the evaporator to be evaporated. In such a case, the heat medium flowing into the evaporator absorbs heat from the external heat medium and is then input to the compressor.

Thus, when an evaporator is provided in the heating flow path, the heat medium exchanges heat with an external heat medium such as water or air to raise the temperature. A configuration is also conceivable in which heat exchange is performed.
In such a case, there is a problem that frost adheres to the evaporator when the outside air temperature decreases. If frost adheres to the evaporator, the heat exchange efficiency deteriorates and precise temperature adjustment cannot be performed.

When performing defrosting (defrosting), it is conceivable to perform defrosting by applying temperature-controlled air to the evaporator to which frost has adhered, or forcibly performing defrosting by providing a heater in the evaporator.
However, there is a problem in that temperature control is greatly disturbed when the compressor is operated while defrosting in this way and temperature adjustment is continued.
Further, a method in which the temperature adjusting device is temporarily stopped and a worker removes frost by hand, or a method of waiting for natural frost to be thawed is also conceivable. However, once the apparatus is stopped, there is a problem that it takes time to start operation after defrosting and adjust the temperature again to a stable predetermined temperature.

  Therefore, the present invention has been made to solve the above-described problems, and the object of the present invention is to adjust the temperature so that defrosting attached to the evaporator can be executed without stopping the operation and precise temperature adjustment can be achieved. To provide an apparatus.

According to the temperature adjusting device of the present invention, the heat medium compressed and sent out by the compressor is distributed by the distributor, and the evaporator absorbs heat from the heater (condenser), the expansion valve, and the external heat medium as the external heat source. A heating circuit that is circulated in the order of the compressor, and a condenser that discharges heat to an external heat medium that is an external heat source, an expansion valve that distributes the remaining heat medium distributed to the heating circuit side by the distributor, A temperature adjusting device that adjusts a fluid passing through the heater and the cooler to a predetermined temperature, and includes an evaporator of the heating circuit. Switching means is provided for switching the functions of the cooling circuit so that it functions as a condenser of the cooling circuit and the condenser of the cooling circuit functions as an evaporator of the heating circuit.
By adopting this configuration, when frost has adhered, the heat exchanger used as the evaporator is used as the condenser of the cooling circuit, and the heat exchanger used as the condenser is used as the heating circuit. Used as an evaporator. For this reason, even if the operation is not stopped, the heat medium of the relatively high-temperature cooling circuit flows into the evaporator with frost, and defrosting can be executed. In addition, since the heat exchanger that has been used as a condenser and has a relatively high temperature is used as an evaporator, it is possible to prevent frost from adhering.
In addition, after the heat medium that has passed through the heater in the heating circuit is adiabatically expanded by the expansion valve, the heat medium flows into the evaporator and evaporates, and the heat medium that flows into the evaporator absorbs heat from the external heat medium, Since it is then input to the compressor, a high heating capacity can be obtained without using an electric heater or the like. Therefore, frost removal at the time of defrosting can be efficiently performed with power saving.

  In addition, the switching means branches first on either the upstream side or the downstream side of the evaporator of the heating circuit, and is connected to either the upstream side or the downstream side of the condenser of the cooling circuit. A second branch path branched from either the upstream side or the downstream side of the condenser of the cooling circuit and connected to either the upstream side or the downstream side of the evaporator of the heating circuit; To cause the heat medium flowing to the evaporator of the heating circuit to flow into the condenser of the cooling circuit so that the condenser of the cooling circuit functions as an evaporator of the heating circuit, and upstream or downstream of the condenser of the cooling circuit. A third branch path branched to one of the upstream side and connected to either the upstream side or the downstream side of the evaporator of the heating circuit, and either the upstream side or the downstream side of the condenser of the heating circuit Branch off at the other end of the cooling circuit. The heating medium flowing to the condenser of the cooling circuit is caused to flow into the evaporator of the heating circuit by evaporating the heating circuit by the fourth branch path connected to either the upstream side or the downstream side of the condenser. It functions as a condenser of the cooling circuit.

  Further, a temperature sensor is provided downstream of the evaporator of the heating circuit, and when the temperature detected by the temperature sensor is equal to or lower than a predetermined temperature, the evaporator of the heating circuit and the condenser of the cooling circuit are The switching means may be provided with control means for controlling so as to switch.

  Further, a pressure sensor for detecting the pressure of the heat medium is provided on the upstream side of the compressor, and when the pressure detected by the pressure sensor falls below a predetermined pressure, the control means Control may be made so that the evaporator and the condenser of the cooling circuit are switched.

  The evaporator of the heating circuit and the condenser of the cooling circuit may be installed outside the room, and the external heat source may be outside air.

  In addition, a humidifier for spraying water is provided between the heater and the cooler, and the fluid passing through the heater and the cooler is adjusted to a predetermined humidity by controlling the spray amount of the humidifier. It is also possible to provide a humidity control means.

  In the temperature adjusting device of the present invention, defrosting of frost adhering to the evaporator can be executed without stopping the operation.

FIG. 1 is a schematic diagram for explaining an example of the temperature adjusting device according to the present invention.
The temperature adjustment device 52 shown in FIG. 1 includes a heater 14 that adjusts the temperature and humidity of air as gas sucked by a fan 12 in a space unit 10 installed in a clean room in which temperature and humidity are adjusted, and A cooler 16 is provided. A heater 14 is disposed on the inlet side of the air flow sucked into the space unit 10, and a cooler 16 is disposed downstream thereof.

In the heating circuit, a part of the heat medium sent out from the compressor 18 is distributed by the distributor 20, and the heat medium in the order of the heater (condenser) 14, the expansion valve 34, the evaporator (heat absorber) 32, and the compressor 18. Is configured to be circulated.
The evaporator 32 of the heating circuit is installed outdoors (including outdoors), and a fan 33 is provided. The evaporator 32 is provided so that the outside air and the heat medium exchange heat by the fan 33, and the heat medium absorbs heat from the outside air.

In the cooling circuit, the heating circuit and the compressor 18 are used in common, and the remainder of the amount distributed to the heating circuit of the heat medium sent out from the compressor 18 is distributed by the distributor 20, the condenser 26, the expansion The valve 28, the cooler (evaporator) 16, and the compressor 18 are circulated in this order.
The condenser 26 of the cooling circuit is also installed outdoors (including outdoors), and a fan 27 is provided. The condenser 26 is provided so that heat is exchanged between the outside air and the heat medium by the fan 27, and the heat medium releases heat to the outside air.

  Examples of the heat medium that flows through the heating circuit and the cooling circuit include hydrocarbons such as propane, isobutane, and cyclopentane, chlorofluorocarbons, ammonia, and carbon dioxide.

Further, the distributor 20 in this embodiment employs a proportional three-way valve.
The heat medium is distributed to the heating circuit side provided with the heater 14 and the cooling circuit side provided with the cooler 16 by the proportional three-way valve 20 as a distributor.
In this proportional three-way valve 20, the total amount of the high temperature heat medium distributed to the heating circuit side and the high temperature heat medium distributed to the cooling circuit side is equal to the amount of the high temperature heat medium discharged from the compressor 18. Distribute.

Further, the evaporator 32 of the heating circuit and the condenser 26 of the cooling circuit are provided so as to be usable by switching.
Specifically, the first branch pipe 54 connecting the expansion valve 34 of the heating circuit and the upstream side of the evaporator 32 and the expansion valve 28 of the cooling circuit and the downstream side of the condenser 26 is provided. Provide. And the 2nd branch pipe 56 which connects between the upstream of the condenser 26 of a cooling circuit and the downstream of the evaporator 32 of a heating circuit is provided.
Further, a third branch pipe 60 that connects the expansion valve 28 of the cooling circuit and the downstream side of the condenser 26 and the downstream side of the evaporator 32 of the heating circuit is provided. And the 4th branch pipe 62 which connects between the expansion valve 34 of a heating circuit and the upstream of the evaporator 32 and between the upstream of the condenser 26 of a cooling circuit is provided.

A first control valve 58 is provided between the first branch pipe 54 and the fourth branch pipe 62 of the heating circuit. A second control valve 59 is provided between the third branch pipe 60 and the second branch pipe 56 of the heating circuit.
A third control valve 64 is provided between the first branch pipe 54 and the third branch pipe 60 of the cooling circuit. A fourth control valve 65 is provided between the second branch pipe 56 and the fourth branch pipe 62 of the cooling circuit.

  Further, each branch pipe is provided with a control valve for opening and closing the branch pipe. The first branch pipe 54 is provided with a fifth control valve 66, the second branch pipe 56 is provided with a sixth control valve 67, and the third branch pipe 60 is provided with a seventh control valve 67. The control valve 68 is provided, and the fourth branch pipe 62 is provided with an eighth control valve 69.

By controlling the opening and closing of the first to eighth control valves described above, switching between the evaporator 32 of the heating circuit and the condenser 26 of the cooling circuit becomes possible. In the present embodiment, the first to eighth control valves and the first to fourth branch pipes described above correspond to the switching means in the claims.
That is, the first control valve 58 and the second control valve 59 are opened on the heating circuit side, the third control valve 64 and the fourth control valve 65 are opened on the cooling circuit side, and the fifth control valve By closing the control valve 66, the sixth control valve 67, the seventh control valve 68, and the eighth control valve 69, the heat medium in the heating circuit flows to the evaporator 32, and the heat medium in the cooling circuit is condensed. Flows to vessel 26.

  At the time of defrosting, the first control valve 58 and the second control valve 59 are closed on the heating circuit side, and the third control valve 64 and the fourth control valve 65 are closed on the cooling circuit side. By opening the control valve 66, the sixth control valve 67, the seventh control valve 68, and the eighth control valve 69, the heat medium of the heating circuit is the first branch pipe 54 and the second branch pipe. The heat medium of the cooling circuit flows to the evaporator 32 via the fourth branch pipe 62 and the third branch pipe 60.

The proportional three-way valve 20 is controlled by a temperature control unit 22. In this temperature control unit 22, the measured temperature measured by the temperature sensor 24 provided at the air outlet of the space unit 10 and the set temperature set (by the operator operating an input switch (not shown), the temperature control unit 22 The distribution ratio of the high-temperature heat medium distributed to the heating circuit side and the cooling circuit side is changed substantially continuously so that the measured temperature matches the set temperature, The air sucked into the space unit 10 is adjusted to a predetermined temperature.
This “substantially continuously changing” means that when the proportional three-way valve 20 is driven by step control, the proportional three-way valve 20 is microscopically driven stepwise, but is continuously continuous as a whole. This includes the case where it is driven.

  The set temperature set in the temperature control unit 22 may be arbitrarily set as described above, or may be stored in advance in storage means in the temperature control unit 22. Furthermore, although the temperature sensor 24 shown in FIG. 1 is installed on the air outlet side, it may be installed on the suction side of the fan 12 or on both the outlet side and the suction side.

Hereinafter, the heating cycle of the heating circuit and the cooling cycle of the cooling circuit will be described.
The high-temperature heat medium distributed to the heating circuit side by the proportional three-way valve 20 is directly supplied to the heater 14, and the air flow sucked into the space unit 10 and cooled by the cooler 16 is heated to a predetermined temperature. adjust. At that time, the high-temperature heat medium is dissipated and cooled to become a heat medium containing condensate.

  On the other hand, the high-temperature heat medium distributed to the cooling circuit side is cooled by the condenser 26 and then adiabatically expanded by the expansion valve 28 and further cooled (for example, cooled to 10 ° C.). The cooled heat medium is supplied to the cooler 16 to cool the air flow sucked into the space unit 10.

  The condenser 26 of such a cooling circuit is arranged outdoors as an outdoor unit, and outside air as an external heat medium is supplied by a fan 27. The outside air is radiated from the heat medium of about 70 ° C. in the condenser 26 and heated to about 30 ° C.

  The evaporator 32 of the heating circuit is arranged outdoors as an outdoor unit, and outside air as an external heat medium is supplied by a fan 33. The outside air supplies heat to the heat medium at about 10 ° C. in the evaporator 32. Thus, in the evaporator 32, the heat medium can absorb heat from the outside air. Note that when the outside air temperature is 0 ° C. to minus, frost adheres to the evaporator 32.

  The heat medium heated by absorbing heat from the outside air by the heat absorber 32 is supplied to the compressor 18 via the accumulator 36. The accumulator 36 is also supplied with a heat medium that absorbs heat from the air flow supplied to the cooler 16 and sucked into the space unit 10. Since the accumulator 36 is a type of accumulator that can store a liquid component and re-supply only the gas component to the compressor 18, it can reliably supply only the gas component of the heat medium to the compressor 18.

As this accumulator 36, an accumulator type accumulator can be used.
Even if the accumulator 36 is not installed, a heat medium that has been heated by absorbing heat from the air flow by the heat absorber 32 and a heat medium that has absorbed heat from the gas supplied to the cooler 16 and sucked into the space unit 10. And can be re-supplied to the compressor 18.

Note that a temperature sensor 70 that measures the temperature of the heat medium discharged from the evaporator 32 is provided on the downstream side of the evaporator 32. The temperature measured by the temperature sensor 70 is input to the temperature control unit 22 described above.
And the temperature control part 22 can perform opening / closing control of each control valve based on the input temperature, and can perform a defrost.

  For example, when the temperature detected by the temperature sensor is negative, the temperature control unit 22 closes the first control valve 58 and the second control valve 59 on the heating circuit side, and on the cooling circuit side. The third control valve 64 and the fourth control valve 65 are closed, and the fifth control valve 66, the sixth control valve 67, the seventh control valve 68, and the eighth control valve 69 are opened. Thus, the functions of the evaporator 32 and the condenser 26 are switched, and the evaporator 32 with frost is used as the condenser of the cooling circuit, and the condenser 26 is used as the evaporator 32 of the heating circuit. By doing in this way, defrosting can be performed easily without stopping the operation.

In addition, the installation position of a temperature sensor is not limited to providing in the downstream piping of the evaporator 32 as mentioned above, You may provide only so that external temperature may be measured (not shown).
The temperature sensor that measures the outside air temperature inputs the measured outside air temperature to the temperature control unit 22, and the temperature control unit 22 switches between the evaporator 32 and the condenser 26 when the outside air temperature becomes a predetermined temperature or less. Execute.

Further, a pressure sensor 84 for measuring the pressure of the heat medium flowing into the compressor 18 is provided on the upstream side of the compressor 18, and the pressure value measured by the pressure sensor 84 is input to the temperature control unit 22. May be. In the temperature control part 22, when the measured pressure value is below a preset threshold value, each control valve mentioned above is controlled so that the evaporator 32 and the condenser 26 may be switched, and a defrost is performed.
That is, the case where the heat medium discharged from the evaporator 32 is equal to or lower than a predetermined pressure may be that the heat medium cannot be evaporated by the evaporator 32 and remains in a liquid state. This is because frost adhered to the evaporator 32 and the heat exchange function did not work. Therefore, by measuring the pressure of the heat medium on the upstream side of the compressor 18 (that is, on the downstream side of the evaporator 32), the timing for executing the defrost can be measured.

Note that the switching between the evaporator 32 and the condenser 26 for performing defrosting may employ either switching based on the temperature detection of the temperature sensor as described above or switching based on the pressure detection by the pressure sensor. .
Furthermore, both switching based on temperature detection of the temperature sensor and switching based on pressure detection by the pressure sensor may be used in combination.

As described above, in the temperature adjustment device 52, the distribution ratio between the high-temperature heat medium distributed to the heating circuit side and the high-temperature heat medium distributed to the cooling circuit side by the proportional three-way valve 20 is set to the temperature in the space unit 10. Can be changed substantially continuously.
For this reason, in the temperature adjusting device 52, a high-temperature heat medium is always supplied to the heating circuit and the cooling circuit, and the air flow of the temperature / humidity adjustment target passing through the heater 14 of the heating circuit and the cooler 16 of the cooling circuit. The minute load fluctuation can be quickly dealt with by quickly adjusting the distribution ratio of the high-temperature heat medium distributed to the heating circuit and the cooling circuit by the proportional three-way valve 20, and the responsiveness can be improved.

  Outside air is supplied to the condenser 26 of such a cooling circuit by a fan 27. The outside air is heated to about 30 ° C. and discharged by a heat medium of about 70 ° C. in the condenser 26. The outside air discharged from the condenser 26 may be supplied as a heating source to an evaporator (heat absorber) 32 as a heat absorption unit of the heat pump.

  By the way, the heat medium radiated by the heater 14 is adiabatically expanded and cooled by the expansion valve 34, but in the cooling by the adiabatic expansion in the expansion valve 34, the heat between the heat medium and the outside is cooled. There is no exchange. For this reason, the heat medium cooled in an adiabatic manner can absorb heat from outside air as an external heat medium supplied to the heat absorber 32 via the condenser 26 from the outside.

  Therefore, energy absorbed from the outside air supplied from the outside by the heat absorber 32 as a heat pump can be added to the compression power energy by the compressor 18 to the high-temperature heat medium discharged from the compressor 18.

  As described above, in the temperature adjusting device shown in FIG. 1, the heating capacity of the heating circuit can be improved by installing a heat pump, and the proportional three-way valve 20 distributes the high temperature heat medium distributed to the heating circuit side and the cooling circuit side. The distribution ratio with the high-temperature heat medium can be changed substantially continuously according to the temperature in the space unit 10.

(Second Embodiment)
Next, an embodiment in which a humidity adjustment function is added to the above-described first embodiment will be described with reference to FIG. In addition, the same code | symbol is attached | subjected about the component same as embodiment mentioned above, and description may be abbreviate | omitted.
In the present embodiment, a spray nozzle 80 that sprays water is provided between the heater 14 and the cooler 16, and a humidity control unit 82 that performs humidity adjustment by controlling the spray amount of the spray nozzle 80 is provided. ing.

  In the humidity controller 82, the measured humidity measured by the humidity sensor 29 provided at the air outlet of the space unit 10 and the set humidity set (by operating the input switch (not shown) to the humidity controller 82). Input humidity), the water control valve 23 is adjusted so that the measured humidity matches the set humidity, and the amount of water supplied to the spray nozzle 80 is adjusted to be sucked into the space unit 10. Adjust the air to the specified humidity.

Pure water stored in the water tank 120 is supplied to the spray nozzle 80 via the water amount control valve 23 provided in the pump 122 and the water supply pipe 124. The spray nozzle 80 is formed of a two-fluid nozzle that sprays water in the form of a mist with compressed air, and this compressed air is supplied to the spray nozzle 80 via a pipe 128.
The water tank 120 stores pure water obtained by supplying normal water to the deionizer 130. The amount of pure water stored in the water tank 120 is kept constant by a control valve 134 provided in the pure water supply pipe 132.

The spray nozzle 80, the water amount control valve 23, and the like constitute a humidifier.
Note that the spray nozzle 80 of the humidifier may not be a two-fluid nozzle, but may be a nozzle (ultrasonic humidifier) that sprays water by ultrasonic waves, or in some cases, jets water vapor due to factory exhaust heat or the like. It may be a nozzle (steam humidifier).

  Note that the set humidity set in the humidity control unit 82 may be arbitrarily set as described above, or may be stored in advance in the storage unit of the humidity control unit 82. Furthermore, although the humidity sensor 29 is installed on the air outlet side, it may be installed on the suction side of the fan 12 or on both the outlet side and the suction side.

  In addition, the condenser 26 and the evaporator 32 of this embodiment are piped so that switching is possible for defrosting. The switching between the evaporator 32 and the condenser 26 for performing the defrosting is either switching based on temperature detection of the temperature sensor or switching based on pressure detection by the pressure sensor, as in the first embodiment. It may be adopted. Furthermore, both switching based on temperature detection of the temperature sensor and switching based on pressure detection by the pressure sensor may be used in combination.

(Third embodiment)
Further, in place of the proportional three-way valve 20 as the distributing means used in the temperature adjusting device 52, two-way valves 38a and 38b as two two-way valves can be used as shown in FIG. Each of the two two-way valves 38 a and 38 b is controlled by the temperature control unit 22. The distribution ratio for adjusting the opening degree of each of the two-way valves 38a and 38b by the temperature control unit 22 and distributing the gaseous high-temperature heat medium compressed and heated by the compressor 18 to the heating circuit and the cooling circuit. Are adjusted substantially continuously to control the air flow through the heater 14 and cooler 16 to a predetermined temperature.
At that time, the total amount of the high-temperature heat medium distributed to the heater 14 and the high-temperature heat medium distributed to the cooler 16 becomes equal to the high-temperature heat medium discharged from the compressor 18. As described above, the opening of the two-way valves 38a and 38b is adjusted to be continuously proportionally distributed.

  As shown in FIG. 4, the relationship between the valve opening and the flow rate in each of the two-way valves 38a and 38b is not linear. Therefore, the temperature control unit 22 holds the flow rate characteristic data for each of the two-way valves 38a and 38b shown in FIG. 4, and the temperature control unit 22 determines the flow rate characteristics of the two-way valves 38a and 38b. An opening signal is transmitted to each two-way valve 38a, 38b.

(Fourth embodiment)
In the temperature adjustment of the air flow as the temperature adjustment target by the heater 14 and the cooler 16 in the temperature adjusting device described above, for example, when the air flow is on the cooling side with respect to the air flow of the temperature adjustment target, the air temperature is stabilized. In the operation state, the air flow cooled by the cooler 16 is heated by the heater 14 as shown in FIG. In such an operation state, the energy heated by the heater 14 may be larger than the energy A required for cooling the airflow. In this case, as shown in FIG. 5B, if the overlapping energy between the cooler 14 and the heater 16 can be reduced as much as possible, energy saving can be achieved.

On the other hand, when it is on the heating side with respect to the air flow to be adjusted, in the operation state where the temperature of the air flow is stable, the air heated by the heater 14 is cooled by the cooler 16 as shown in FIG. It is cooling. In the operation state shown in FIG. 6A, the energy to be cooled by the cooler 16 may be larger than the energy B required to heat the airflow. In this case, as shown in FIG. 6B, if the overlapping energy of the cooler 16 and the heater 14 can be reduced, energy saving can be achieved.
However, if the supply of the high-temperature heat medium to the heater 14 and the cooler 16 is turned on and off in order to make the amount of heat canceling each other out, the operation of the temperature adjusting device 52 becomes unstable and the air flow is predetermined. It takes time to stabilize at temperature. For this reason, to the extent that the temperature adjustment device 52 can be stably operated, it is necessary that the amount of heat that cancels each other out of the amount of heating applied to the heater 14 and the amount of cooling applied to the cooler 16 must be present at a minimum. .
The minimum necessary amount of heat that cancels each other is somewhat different depending on the temperature adjusting device, and is preferably obtained experimentally.

As described above, in the temperature adjustment device shown in FIG. 7, the heating amount applied to the heater 14 and the cooling amount applied to the cooler 16 can be reduced so that the overlapping energy between the cooler 16 and the heater 14 can be reduced. The rotation speed of the compressor 18 is controlled by the second controller 22b via the inverter 19 so as to reduce the amount of heat that cancels each other out as much as possible.
Of the constituent members constituting the temperature adjusting device shown in FIG. 7, the same members as those of the temperature adjusting device shown in FIG. 1 are denoted by the same reference numerals as those in FIG. .

The second control unit 22b cooperates with the first control unit 22a that controls the proportional three-way valve 20, and out of the heating amount applied to the heater 14 and the cooling amount applied to the cooler 16, cancels each other out. Precise temperature control of air flow is performed while minimizing as much as possible.
The control of the proportional three-way valve 20 by the first controller 22a and the control of the rotational speed of the compressor 18 by the second controller 22b are shown in the flowchart of FIG.

When the temperature adjusting device shown in FIG. 7 was trial run, when operating on the cooling side with respect to the air flow, as the amount of heating applied to the heater 14, the first high temperature to the heater 14 side by the proportional three-way valve 20. It has been found that the heat medium distribution ratio is preferably 5 to 15% (the distribution ratio of the high temperature first heat medium to the cooler 16 side by the proportional three-way valve 20 is 95 to 85%) from the standpoint of stable operation. .
On the other hand, when operating on the heating side with respect to the air flow, the distribution ratio of the high-temperature first heat medium to the heater 14 side by the proportional three-way valve 20 is 95 to 85 as the heating amount applied to the heater 14 side. % (The distribution ratio of the high-temperature first heat medium to the cooler 16 side by the proportional three-way valve 20 is 5 to 15%) from the viewpoint of stable operation.

  For this reason, in the control shown in the flowchart of FIG. 8, the amount of heating applied to the heater 14 side, specifically, the distribution ratio of the high-temperature first heat medium to the heater 14 side by the proportional three-way valve 20, When operating on the cooling side, the rotational speed of the compressor 18 is controlled so as to be 5 to 15%, and when operating on the heating side with respect to the air flow, the distribution ratio is 95 to 85%. Thus, the rotational speed of the compressor 18 is controlled.

  In the flowchart shown in FIG. 8, after starting the compressor 18 in step S10, based on the temperature signal measured by the temperature sensor 24 provided in the space unit 10 so that the air flow is set to a predetermined temperature in step S12. Thus, the distribution ratio of the high-temperature heat medium distributed to the heater 14 side and the cooler 16 side by the proportional three-way valve 20 is continuously changed, and the air flow sucked into the space unit 10 is adjusted to a predetermined temperature. .

  In step S14, it is determined whether the air flow reaches a predetermined temperature and is stable. If the temperature of the air flow is not stable, the process returns to step S12 and the heater 14 side and the cooler by the proportional three-way valve 20 are returned. The distribution ratio of the high-temperature heat medium distributed to the 16 side is continuously changed. Steps S12 and S14 are performed by the first controller 22a.

On the other hand, when the air flow in the space unit 10 reaches a predetermined temperature and is stable, the distribution ratio of the high-temperature heat medium distributed to the heater 14 side in steps S16 to S22 is within a predetermined range. Determine whether or not. Steps S16 to S22 are performed by the second controller 22b.
The average distribution rate of the high temperature first heat medium shown in FIG. 8 is not uniform because the distribution ratio of the high temperature heat medium distributed to the heater 14 side varies. In the following, it may be simply referred to as an average distribution ratio of the heat medium.

First, in step S16 and step S18, when it is assumed that the air flow is on the cooling side, it is determined whether the average distribution ratio of the heat medium to the heater 14 side is within 5 to 15%.
Here, when the average distribution ratio of the heat medium to the heater 14 side is within 5 to 15%, it is on the cooling side with respect to the air flow and is within a range in which the operation of the temperature adjusting device is stable. Then, the process passes through step S16 and returns from step S18 to step S16.

  On the other hand, when the average distribution ratio of the heat medium to the heater 14 side is less than 5%, the average distribution ratio of the heat medium to the heater 14 side is too low, and the operation of the temperature adjusting device becomes unstable. easy. For this reason, in order to increase the average distribution ratio of the heat medium to the heater 14, the process proceeds from step S16 to step S24, and the rotational speed of the compressor 18 is increased. In step S24, an increase signal is transmitted from the second control unit 22b to the inverter 18 to increase the rotational speed of the compressor 18 set in the inverter 18 with a minimum change amount. This is because the temperature adjusting device can be stably operated by increasing the rotation speed of the compressor 18 with the minimum change amount.

Since the minimum change amount for changing the rotation speed of the compressor 18 varies depending on the temperature adjusting device, it is preferably obtained experimentally. However, when the rotation speed of the compressor 18 is 2000 to 5000 rpm, the minimum change amount is determined. Is preferably in the range of 3 to 10%.
Further, when the average distribution ratio of the heat medium to the heater 14 side exceeds 15%, it is determined that the air flow is not on the cooling side through steps S16 and S18, and step S20. The process proceeds to step S22. In step S20 and step S22, when it is assumed that the air flow is on the heating side, it is determined whether or not the average distribution ratio of the heat medium to the heater 14 side is within 95 to 85%.
Here, when the average distribution ratio of the heat medium to the heater 14 side is within 85 to 95%, the air flow is on the heating side and the operation of the temperature adjusting device is within a stable range, so the step Pass S20 and return from step S22 to step S16.

  On the other hand, when the average distribution ratio of the heat medium to the heater 14 side exceeds 95%, the average distribution ratio of the heat medium to the heater 14 side is too high, and the operation of the temperature adjusting device becomes unstable. easy. For this reason, in order to reduce the average distribution ratio of the heat medium to the heater 14, the process proceeds from step S20 to step S24, and the rotation speed of the compressor 18 is increased. In step S24, an increase signal is transmitted from the second control unit 22b to the inverter 18 to increase the rotational speed of the compressor 18 set in the inverter 18 with a minimum change amount.

  When the average distribution ratio of the heat medium to the heater 14 side is less than 85%, in step S22, the air flow is neither the heating side nor the cooling side, that is, the heating amount applied to the heater 14. Among the cooling amounts applied to the cooler 44, it is determined that there is a large amount of heat that cancels each other. For this reason, it transfers to step S26 and the rotation speed of the compressor 18 is reduced. In step S <b> 26, a lowering signal for lowering the rotational speed of the compressor 18 set in the inverter 18 by the minimum change amount is transmitted from the second control unit 22 b to the inverter 18. This is because the rotation speed of the compressor 18 is reduced by the minimum change amount and the air flow is shifted to the heating side or the cooling side.

  Next, the process proceeds to step S28 after passing through step S24 or step S26, and it is determined whether or not the compressor 18 is in operation. If the compressor 18 is in operation, the process returns to step S14. In step S14, in step S24 or step S26, it is determined whether the air flow in the space unit 10 reaches a predetermined temperature and is stable in a state where the rotation speed of the compressor 18 is increased or decreased by the minimum change amount. . When the air flow in the space unit 10 reaches a predetermined temperature and is stable, the average distribution rate of the heat medium to the heater 14 side is within the predetermined range again in steps S16 to S26. Judge whether or not.

On the other hand, if it is determined in step S14 that the temperature of the air flow in the space unit 10 is not stable, the process returns to step S12, and heat is distributed to the heater 14 side and the cooler 16 side by the proportional three-way valve 20. Continuously change the media distribution ratio. After the air flow in the space unit 10 reaches a predetermined temperature and stabilizes, the process proceeds to steps S16 to S26.
In step S28, when the compressor 18 is not in an operating state, the control by the first control unit 22a and the second control unit 22b is stopped.
As described above, in the flowchart shown in FIG. 8 described above, the first control unit 22a performs control while paying attention to the average distribution ratio of the heat medium to the heater 14 side, but the heat medium to the cooler 16 side is controlled. You may control by paying attention to an average distribution rate.

  In addition, the condenser 26 and the evaporator 32 of this embodiment are piped so that switching is possible for defrosting. The switching between the evaporator 32 and the condenser 26 for performing the defrosting is either switching based on temperature detection of the temperature sensor or switching based on pressure detection by the pressure sensor, as in the first embodiment. It may be adopted. Furthermore, both switching based on temperature detection of the temperature sensor and switching based on pressure detection by the pressure sensor may be used in combination.

(Fifth embodiment)
In the temperature adjusting apparatus described above, the temperature adjustment target is an air flow, but the present invention can also be applied to a temperature adjustment apparatus that uses a coolant used in a machine tool or the like as a temperature adjustment target. An example of a temperature adjustment device for the coolant as the temperature adjustment target is shown in FIG. In addition, the same code | symbol is attached | subjected about the component same as the component of embodiment mentioned above, and description may be abbreviate | omitted.

In the temperature control apparatus for the coolant shown in FIG. 9, the high-temperature heat medium compressed by the compressor 18 controlled to rotate at a predetermined number of revolutions by the inverter 19 is heated by a proportional three-way valve 20 as a distribution means. And the cooling circuit.
The proportional three-way valve 20 is configured such that the total amount of the high-temperature heat medium amount distributed to the heating circuit side and the high-temperature heat medium amount distributed to the cooling circuit side is equal to the high-temperature heat medium amount discharged from the compressor. The high-temperature heat medium compressed by the compressor 18 is proportionally distributed. The proportional three-way valve 20 is controlled by a temperature control unit 22 and, as will be described later, based on a signal from a temperature sensor 42 that measures the temperature of the coolant at the outlet of the temperature adjusting device 52, the heating circuit and cooling The distribution ratio of the high-temperature heat medium distributed to the circuit is continuously changed to adjust the coolant to a predetermined temperature.

  In the cooling circuit in which a part of the high-temperature heat medium discharged from the compressor 18 is distributed, as a cooling means for cooling the distributed high-temperature heat medium, a condenser 26 that condenses the high-temperature heat medium, and a condenser An expansion valve 28 is provided as expansion means for adiabatically expanding and further cooling the heat medium condensed by the container 26, and a cooler 44 to which the cooled heat medium is supplied. The cooler 44 is cooled by the temperature adjustment target coolant returned from the USER stored in the storage tank 46 by the pump 47. The heat medium whose temperature has been absorbed by the cooler 44 returns to the accumulator 36 and is supplied to the compressor 18.

The heating circuit is provided with a heater 48 as a heating means to which a high-temperature heat medium is supplied. The heater 48 is supplied with the temperature adjustment target cooling liquid cooled by the cooler 44, adjusted to a predetermined temperature by the supplied high-temperature heat medium, and sent to the USER.
Such a heating circuit is provided with an evaporator (heat absorber) 32 of heat pump means. The heat absorber 32 is supplied with the heat medium which has been radiated and condensed by the heater 48 in an adiabatic manner by an expansion valve 34 as an expansion means, and is further cooled. The heat medium that has absorbed heat from the outside air returns to the accumulator 36 and is supplied to the compressor 18.

  In addition, the condenser 26 and the evaporator 32 of this embodiment are piped so that switching is possible for defrosting. The switching between the evaporator 32 and the condenser 26 for performing the defrosting is either switching based on temperature detection of the temperature sensor or switching based on pressure detection by the pressure sensor, as in the first embodiment. It may be adopted. Furthermore, both switching based on temperature detection of the temperature sensor and switching based on pressure detection by the pressure sensor may be used in combination.

  In the coolant temperature adjusting device shown in FIG. 9, two gate valves 38a and 38b as two two-way valves can be used instead of the proportional three-way valve 20, as shown in FIG.

  As described above, the temperature control device shown in FIG. 9 is also provided with the second control unit 22b in the same manner as the temperature control device shown in FIG. 7 so that the overlapping energy between the cooler 44 and the heater 46 can be reduced. The rotational speed of the compressor 18 may be controlled via an inverter 19 that controls the compressor 18. Also in this case, the amount of heat that cancels each other out of the amount of heating applied to the heater 48 and the amount of cooling applied to the cooler 44 in accordance with the flowchart shown in FIG. The temperature of the coolant to be adjusted is controlled precisely.

Moreover, the heaters 14 and 48, the coolers 14 and 44, the condenser 26, and the heat absorber 32 used in the temperature control apparatus shown in FIGS. 1 to 9 are configured so that two fluids having a temperature difference are countercurrent or cocurrent. Flowing known heat exchangers can be used. For example, a double tube, a finned tube, a plate heat exchanger, or the like can be suitably used.
As the heat absorber 32 for which thermal efficiency is required, a plate heat exchanger in which a plurality of heat transfer tubes are inserted in a laminated body in which a plurality of plate-like fins are stacked can be suitably used.

In each of the above-described embodiments, four branch pipes and eight control valves are used between the evaporator 32 and the condenser 26 to flow into the evaporator 32 without stopping the operation of the compressor 18. The defrosting was performed by switching the evaporator 32 and the condenser 26 by flowing the heat medium that should be performed into the condenser 26 and the heat medium that should be flowing into the condenser 26 into the evaporator 32.
However, according to the present invention, the heat medium that should flow into the evaporator 32 without stopping the operation of the compressor 18 using the four-way valve without using the eight control valves is caused to flow into the condenser 26. The evaporator 32 and the condenser 26 may be switched by causing the heat medium that should flow into the condenser 26 to flow into the evaporator 32 (not shown).

In the above-described switching control of the eight control valves, all (eight) control valves may be once fully opened, and then each control valve may be switched gradually to a desired state. .
By doing so, a rapid change in the flow of the heat medium can be mitigated, and smoother switching can be achieved.

  Further, in the switching control of the eight control valves at the time of defrost execution, when the eight control valves are switched, the rotation speed of the compressor is increased for a certain period, and the heating capacity of the heating circuit does not decrease due to the influence of the defrost execution. You may control as follows.

  Furthermore, in each embodiment mentioned above, the case where defrosting was carried out in the air-cooling type temperature control apparatus with which an evaporator and a condenser heat-exchange with external air has been demonstrated. However, even in a water cooling type temperature control device, there is a possibility that the cooling water may freeze in a cold district or the like. In such a situation, even when the freezing is removed, the evaporator of the heating circuit and the condenser of the cooling circuit may be switched by the switching means of the present invention.

It is the schematic explaining 1st Embodiment of the temperature control apparatus which concerns on this invention. It is the schematic explaining 2nd Embodiment of the temperature control apparatus which concerns on this invention. It is explanatory drawing explaining another distribution means. It is a graph which shows the flow characteristic of the two-way valve used with a distribution means. FIG. 2 is an explanatory diagram for explaining the principle of energy saving in the temperature adjustment apparatus shown in FIG. 1 when it is on the cooling side. In the temperature control apparatus shown in FIG. 1, it is explanatory drawing explaining the principle of energy saving when it exists in the heating side. It is the schematic explaining the other example of the temperature control apparatus which concerns on this invention. It is a flowchart for demonstrating the control procedure by the 1st control part 22a and the 2nd control part 22b of the temperature control apparatus shown in FIG. It is the schematic explaining the other example of the temperature control apparatus which concerns on this invention. It is the schematic explaining the conventional temperature control apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Spatial unit 12 Fan 14,48 Heater 16,44 Cooler 18 Compressor 20 Distributor 22 Temperature control part 23 Water quantity control valve 24 Temperature sensor 26 Condenser 27 Fan 28 Expansion valve 29 Humidity sensor 32 Heat absorber 32 Evaporator 33 Fan 34 Expansion valve 36 Accumulator 38a, 38b Two-way valve 42 Temperature sensor 46 Water tank 47 Pump 52 Temperature adjusting device 54, 56, 60, 62 Branch pipe 58, 59, 64, 65, 66, 67, 68, 69 Control valve DESCRIPTION OF SYMBOLS 70 Temperature sensor 80 Spray nozzle 82 Humidity control part 84 Pressure sensor 120 Water tank 122 Pump 124 Water supply piping 128 Pipe 130 Pure water device 132 Pure water supply piping 134 Control valve

Claims (6)

A heating medium that is compressed by the compressor and sent out is distributed by a distributor, a heating circuit (condenser), an expansion valve, an evaporator that absorbs heat from an external heat medium that is an external heat source, and a heating circuit that is circulated in the order of the compressor; ,
The remainder of the heat medium distributed to the heating circuit side is distributed by the distributor, and the condenser, the expansion valve, the cooler (evaporator), and the compressor are circulated in this order to release heat to the external heat medium that is an external heat source. A cooling circuit,
In a temperature adjustment device that adjusts the fluid passing through the heater and the cooler to a predetermined temperature,
Switching means for switching between the functions is provided so that the evaporator of the heating circuit functions as a condenser of the cooling circuit, and the condenser of the cooling circuit functions as an evaporator of the heating circuit. A characteristic temperature control device. The switching means is
A first branch that branches on either the upstream side or the downstream side of the evaporator of the heating circuit and is connected to either the upstream side or the downstream side of the condenser of the cooling circuit; and the cooling circuit Branching on either the upstream side or the downstream side of the condenser, and a second branch path connected to either the upstream side or the downstream side of the evaporator of the heating circuit. The heat medium flowing to the evaporator is caused to flow into the condenser of the cooling circuit so that the condenser of the cooling circuit functions as an evaporator of the heating circuit,
A third branch branched from either the upstream side or the downstream side of the condenser of the cooling circuit and connected to either the upstream side or the downstream side of the evaporator of the heating circuit; and the heating circuit A fourth branch path that branches from either the upstream side or the downstream side of the condenser of the cooling circuit and is connected to either the upstream side or the downstream side of the condenser of the cooling circuit. 2. The temperature adjusting device according to claim 1, wherein the heat medium flowing to the condenser is caused to flow into the evaporator of the heating circuit so that the evaporator of the heating circuit functions as a condenser of the cooling circuit. A temperature sensor is provided downstream of the evaporator of the heating circuit;
Control means for controlling the switching of the evaporator of the heating circuit and the condenser of the cooling circuit when the temperature detected by the temperature sensor falls below a predetermined temperature is provided in the switching means. The temperature adjusting device according to claim 1 or 2, wherein A pressure sensor for detecting the pressure of the heat medium is provided on the upstream side of the compressor,
The control means controls to switch between an evaporator of the heating circuit and a condenser of the cooling circuit when the pressure detected by the pressure sensor becomes a predetermined pressure or less. The temperature control apparatus of any one of Claims 1-3. The evaporator of the heating circuit and the condenser of the cooling circuit are installed outdoors,
The temperature adjusting device according to any one of claims 1 to 4, wherein the external heat source is outside air. A humidifier for spraying water is provided between the heater and the cooler,
The humidity control means for adjusting the fluid passing through the heater and the cooler to a predetermined humidity by controlling the spray amount of the humidifier is provided. The temperature control apparatus of any one of Claims.

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