JP5768155B2 - Heating and cooling device - Google Patents

Description

  The present invention relates to a heating / cooling device that uses a heat pump to perform heating with respect to a heating load and cooling with respect to a cooling load.

  The thing of the following patent document 1 is known as a heating-cooling apparatus using a heat pump. In this liquid heating / cooling apparatus, a general heat pump is provided with a second cooler that is independent of the heat pump because the amount of heating heat and the amount of cooling heat are linked and the cooling capacity is smaller than the heating capacity.

JP-A-7-167526

  However, in this heating and cooling device, it is difficult to handle when the heating load is excessive with respect to the cooling load, for example, the allowable range for the load is relatively narrow, and it is difficult to perform flexible operation. Select the installation location. Also, with this heating / cooling device, even if an attempt is made to continue the operation when the heating load is excessive with respect to the cooling load, the overcooling causes the low-temperature cooling medium to return to the heat pump, thereby avoiding malfunction of the heat pump. Due to an emergency stop for the cause, it may become impossible to continue. Furthermore, in this heating / cooling device, energy for operating a cold heat source for operating an independent cooler is required.

Accordingly, an object of the present invention is to provide a heating / cooling device that can smoothly start operation at a low cost in a state where energy efficiency is extremely good.

In order to achieve the above object, the first aspect of the present invention provides a first heat pump for heating the first heating medium for heating the first heating load, and a second heating medium for heating the second heating medium for heating the second heating load. 2 heat pumps, and an automatic control device that controls the first heat pump and the second heat pump, the first heat pump can be introduced by cooling a part of the second heating medium, and can be derived. The second heat pump cools a cooling medium that cools a cooling load, and the automatic control device operates the second heat pump before the first heat pump and starts the operation of the first heat pump. the second heating medium, by introducing a part of the first heating medium, it is normally heated to above the operating conditions the lower limit of advance the first pump the first heat medium It is an feature.
According to a second aspect of the present invention, in order to achieve the above object, a first heat pump for heating the first heating medium for heating the first heating load, and a second heating medium for heating the second heating medium for heating the second heating load. 2 heat pumps, and an automatic control device that controls the first heat pump and the second heat pump , the first heat pump can be introduced by cooling a part of the second heating medium, and can be derived. The second heat pump cools a cooling medium that cools a cooling load, and further includes a second heating medium temperature sensor that detects a temperature of the second heating medium, and a second heating medium that adjusts the second heating medium to an arbitrary temperature. 2 heating medium heat amount adjusting means, a first heating load temperature sensor for detecting the temperature of the first heating load, and another heat source for heating the first heating load, wherein the automatic control device includes the first heating load 2 heat The pump while operating earlier than the first pump, the second based on the temperature of the second heating medium obtained from the heating medium temperature sensor, a predetermined temperature by the second heating medium and the second heat medium heat adjusting means was adjusted to, and operate the first pump, said first heating load heated by the first heating medium, further, on the basis of the temperature of the first heating load obtained from the first heating load temperature sensor, The first heating load or the first heating medium is heated by the other heat source so that the first heating load becomes a specific temperature .
In order to achieve the above object, the invention according to claim 3 is characterized in that, in the above invention, the cooling load includes a fluid to be treated in a sterilizer, a processing fluid in a desiccant air conditioner, a stock solution in a stock temperature controller, and a concentrated condenser Cooling water / condensed liquid or concentrated liquid, cleaning apparatus cleaning liquid, drying furnace air, cooling furnace, electrodeposition tank, booth air conditioning, recycling air conditioning, factory air conditioning, office air conditioning, indoor air conditioning, clean room air conditioning, or constant throughout the year It is the cooling load which cools at least any one of the air conditioning for hold | maintaining to this temperature or humidity .

The invention according to claim 4, in order to achieve the above object, a first heating medium to heat the first heat load heat, waste heat is introduced and cooled to be derived by heat pump belonging to the plant, the exhaust An exhaust heat temperature sensor for detecting the temperature of heat, an exhaust heat quantity adjusting means for adjusting the temperature of the exhaust heat, the heat pump, and an automatic control device for controlling the exhaust heat quantity adjustment means , When starting the operation of the heat pump , the automatic control device adjusts the exhaust heat to a predetermined temperature by the exhaust heat quantity adjustment means based on the temperature of the exhaust heat obtained from the exhaust heat temperature sensor, and reduces the exhaust heat . the first to introduce a part of the heating medium, is characterized in that the temperature from rising above normal operating conditions the lower limit of advance the heat pump the first heat medium.
In order to achieve the above object, the invention according to claim 5 is a heat pump capable of heating the first heating medium that heats the first heating load , introducing exhaust heat belonging to the factory, cooling it, and deriving the exhaust. An exhaust heat temperature sensor for detecting the temperature of heat, an exhaust heat quantity adjustment means for adjusting the temperature of the exhaust heat, a first heating load temperature sensor for detecting the temperature of the first heating load, and the first heating load Or an other heat source for heating the first heating medium , and an automatic control device for controlling the heat pump, the exhaust heat quantity adjusting means, and the other heat source , the automatic control device from the exhaust heat temperature sensor Based on the obtained temperature of the exhaust heat, the exhaust heat is adjusted to a predetermined temperature by the exhaust heat quantity adjustment means, the heat pump is operated, and the first heating load is heated by the first heating medium, The first heating load temperature sensor Based on the temperature of the first heating load obtained from, characterized in that heating the first heating load or the first heat medium such that the first heat load is in a specific temperature by the other heat source is there.
The invention according to claim 6, in order to achieve the above object, a first heating medium to heat the first heat load heat, waste heat is introduced and cooled to be derived by heat pump belonging to the plant, the exhaust An exhaust heat temperature sensor that detects the temperature of heat, an exhaust heat quantity adjustment means that adjusts the temperature of the exhaust heat, another heat source that heats the first heating load or the first heating medium, the heat pump, the exhaust heat A heat quantity adjusting means, and an automatic control device for controlling another heat source , wherein the automatic control device converts the waste heat to the waste heat temperature based on the waste heat temperature obtained from the waste heat temperature sensor. The temperature is adjusted to a predetermined temperature by an adjustment means, the heat pump is operated, and the first heating load after being heated by the first heating medium is further heated by the other heat source and evaporated. is there.

The invention described in claim 7 is characterized in that, in order to achieve the above object, in the above invention, the exhaust heat heats the second heating load .
In order to achieve the above object, in the invention described in claim 8, in the above invention, the automatic control device restricts the output of the heat pump when the temperature of the exhaust heat falls below a lower limit temperature, or the The heat pump is stopped, and the temperature of the exhaust heat is maintained or raised .
In order to achieve the above-mentioned object, the exhaust heat of the present invention may be exhausted hot water, makeup water, exhaust gas, exhaust gas, heat dissipation of equipment, heat dissipation of workpieces, heat dissipation of air conditioning, cogeneration, Waste heat, heat from hydraulic fluid, heat transferred to washing water when the product heated by hot water washing is washed in the subsequent washing process, waste heat generated from factory air conditioning, boiler waste heat, equipment It is at least one of cooling water, welding machine cooling water, hydraulic device cooling water, heat radiation from the drying process, mold cooling water, air compressor cooling water, heat from cooling equipment required, and well water. To do.

In order to achieve the above object, a heat pump that heats a heating medium that heats a heating load, a heating medium circuit that circulates the heating medium between the heating load and the heat pump, and A heating load temperature sensor for detecting the temperature of the heating load ; another heat source for heating the heating load; the heat pump; and an automatic control device for controlling the other heat source, wherein the automatic control device includes the heat pump. At the start of operation, the heating load is heated by the other heat source based on the temperature of the heating load obtained from the heating load temperature sensor, and the heating medium between the heated heating load and the heat pump Thus the circulation of the heating medium in the circulation path, especially to raise the temperature of the said heating medium above normal operating conditions the lower limit of the heat pump It is an.
In order to achieve the object described above, the heating load, the first heating load, or the second heating load is the fluid to be processed in the sterilizer, the dehumidification rotor of the desiccant air conditioner, or the like. Regeneration side fluid, undiluted solution temperature control device, condensing and condensing material, washing device washing liquid, pretreatment tank, drying oven air installed in the factory, booth air conditioning, recycling air conditioning, factory air conditioning, office air conditioning, indoor It is characterized by heating at least one of air conditioning, clean room air conditioning, air conditioning for maintaining a constant temperature or humidity throughout the year, and water supply .
In order to achieve the above object, the invention according to claim 12 is the above invention, wherein the other heat source is a heat pump steam / hot water generator, a heat pump that generates only steam, a boiler, steam, an electric heater, or an air-cooled heat pump. It is at least one of these.

  In addition, it is possible to continue the operation with extremely good energy efficiency, adapt to various additional conditions, and continue the operation of the heat pump with extremely good energy saving performance by simple control of switching the operation state. In order to achieve the purpose, the heating medium that heats the heating load is heated, the heat pump that cools the cooling medium that cools the cooling load, the other heat source that assists heating of the heating medium, and the cooling of the cooling medium are assisted The heat pump is capable of heating medium follow-up operation and cooling medium follow-up operation, and switches from the heating medium follow-up operation to the cooling medium follow-up operation when the cooling medium falls below a predetermined temperature. When the heating medium exceeds a specific temperature, it is preferable to switch from the cooling medium following operation to the heating medium following operation. There.

  In addition, an air-cooled heat pump that can heat the cooling medium to ensure the balance and can also cool the cooling medium when the cooling load is relatively increased is provided, and switching the operation of the air-cooled heat pump smoothly and saves energy. In order to achieve the purpose to be performed in a state, a heating pump that heats a heating load and a cooling pump that cools a cooling load and an air cooling heat pump that heats or cools the cooling medium are provided. Preferably, after the medium of the air cooling heat pump is cooled or heated by the cooling medium, the heating or cooling of the medium of the air cooling heat pump is switched.

  Further, in addition to the above object, in order to achieve the object of more smoothly executing the operation switching, the above invention is provided with another auxiliary heat source for heating or cooling the medium, and the medium by the cooling medium. It is preferable to perform cooling or heating by the other auxiliary heat source in accordance with the cooling or heating.

  In addition, in addition to the above object, in order to achieve the object of executing heating of the cooling medium with further energy saving, it is preferable in the above invention that a cooling medium heater for heating the cooling medium is provided.

  In addition, in order to achieve the purpose of providing a heating and cooling device that can continue operation with extremely good energy efficiency and can be adapted to various additional conditions, the heating medium that heats the heating load is heated, It is preferable to include a heat pump that cools the cooling medium that cools the cooling load, and a cooling medium heater that heats the cooling medium.

  Furthermore, in order to achieve the object of providing a heating and cooling device that can continue operation with extremely good energy efficiency and can be adapted to various additional conditions, a first cooling medium that cools the cooling load, and heating A heat pump that heats a heating medium that heats a load and cools a second cooling medium that cools the first cooling medium, a cooling device that cools the first cooling medium using a third cooling medium, and the second cooling It is preferable to include a cooling medium heater that heats the medium.

  Still further, in addition to the above object, in order to achieve the object of providing a heating / cooling device that automatically operates with good efficiency, in the above invention, in the cooling side heating medium and / or the cooling medium, First heat amount adjusting means for adjusting the amount of heat to the cooling medium heater, a temperature sensor for detecting a cold water temperature that is the temperature of the second cooling medium, and adjusting the amount of heat of the third cooling medium from the cooling device It is preferable that the apparatus includes a second heat amount adjusting unit that performs the above operation, and an automatic control device that is connected to the temperature sensor and controls the amount of heat in the first heat amount adjusting unit and the second heat amount adjusting unit according to the cold water temperature.

  In addition to the above object, in order to achieve the object of further improving the overall efficiency while ensuring the heating and cooling performance, in the above invention, a plurality of the heat pumps are installed, and the automatic control The apparatus includes a hot water supply temperature sensor that detects a hot water supply temperature that is a temperature at which the heating medium is supplied from the heat pump, and a temperature at which the heating medium returns to the heat pump. A hot water return temperature sensor that detects a hot water return temperature, a cold water supply temperature sensor that detects a cold water supply temperature that is a temperature when the second cooling medium is supplied from the heat pump, and a heat quantity of the heating medium Connected to the calorimeter, and obtained from the hot water supply temperature obtained from the hot water supply temperature sensor and the hot water return temperature sensor. From the difference between the warm water return temperatures and the current heating capacity obtained from the calorific value obtained from the calorimeter, and the heating capacity during rated operation obtained from the cold water supply temperature obtained from the cold water supply temperature sensor, The load factor in the heat pump is grasped, and when the load factor is equal to or less than a set value, control is performed to stop the operation of a part of the heat pump, and obtained from the hot water supply temperature sensor after the heat pump is stopped. When the hot water supply temperature is equal to or lower than a set value, it is preferable to perform control for restarting the operation of the stopped heat pump.

  In addition to the above object, in order to achieve the object of further improving the overall efficiency by enabling the heat pump to be switched to a more efficient operation, in the above invention, the cooling that is the temperature of the first cooling medium. A cooling medium temperature sensor connected to the automatic control device for detecting a medium temperature is further provided, wherein the automatic control device has a heat amount in the second heat amount adjusting means equal to or less than a set value, and from the cooling medium temperature sensor. When the obtained cooling medium temperature is equal to or lower than a set value, it is preferable to increase the temperature after cooling according to the second cooling medium of the heat pump.

  Furthermore, in addition to the above object, in order to achieve the object of further improving the efficiency as a whole, the heat pump can be switched to an efficient operation mode according to the situation. The apparatus further comprises a heating device capable of supplying a second heating medium to be heated, the heat pump is connected to a cooler capable of cooling the heating medium, and the automatic control device is obtained from the cooling medium temperature sensor. When the cooling medium temperature is equal to or higher than a predetermined value and / or when the flow rate in the second heat quantity adjusting means is equal to or higher than a set value, the heating medium is supplied to the cooler to receive the cooled heating medium; It is preferable that the second heating medium is supplied by the heating device to heat the heating load instead of the heating medium.

  Furthermore, in addition to the above object, in order to achieve the object of simply heating the cooling medium, it is preferable in the above invention that the cooling medium heater is a heating heat pump.

  In addition, the heating medium that heats the heating load is heated in order to achieve the purpose of continuously providing heating or cooling with a heat pump in a simple configuration with low initial costs and running costs and being able to perform heat recovery. And a heat pump that cools the cooling medium that cools the cooling load, and a cooling medium heater that heats the cooling medium, and the heat pump has a cooling amount that exceeds the cooling load amount in the cooling medium following operation. It is preferable to operate with the medium supplied.

  In addition to the above object, in order to achieve the object of executing the heating of the cooling medium more easily and energy savingly, in the above invention, the cooling medium heater introduces the cooling medium and the cooling side heating medium. The heat exchanger is preferably a heat exchanger that heats the cooling medium with the cooling-side heating medium by exchanging heat.

  Furthermore, in order to achieve the purpose of effectively preventing insufficient cooling and overcooling with a simple configuration or operation, a heat pump that heats the heating medium that heats the heating load and cools the cooling medium that cools the cooling load; A heat exchanger that heats the cooling medium with the cooling-side heating medium by introducing the cooling medium and the cooling-side heating medium and exchanging heat; and the cooling-side heating medium includes cooling water in a facility requiring cooling and It is preferable that the cooling water and / or cold water is further cooled to a predetermined temperature and supplied to the cooling medium heater and an equipment cooling water temperature adjusting means.

  Furthermore, in order to achieve the purpose of continuing the operation of the heat pump that is energy saving without performing complicated control, a heat pump that heats the heating medium that heats the heating load and cools the cooling medium that cools the cooling load; A heat exchanger that heats the cooling medium with the cooling-side heating medium by introducing the cooling medium and the cooling-side heating medium and exchanging heat; the cooling-side heating medium is supplied from an air-cooling heat pump; The air-cooled heat pump preferably maintains the cooling side heating medium at a predetermined temperature.

  In addition, in order to achieve the object corresponding to the cooling load in a simple configuration and control in addition to the above object, the cooling side heating medium heat amount adjusting means for adjusting the heat amount of the cooling side heating medium is provided in the above invention. It is preferable that it is installed.

  In addition to the above object, in order to achieve the object of further reducing the energy consumption by utilizing the exhaust heat and simply heating the cooling medium, in the above invention, the cooling side heating medium is an exhaust gas belonging to a factory. Hot water, makeup water, exhaust gas, exhaust gas, cleaning water drainage, equipment heat dissipation, work heat dissipation, air conditioner exhaust heat, return of air conditioning cooling medium or exhaust heat including cogeneration cooling water It is preferable that it contains.

  Furthermore, in addition to the above object, in order to achieve the object of simply heating the cooling medium, in the above invention, the cooling side heating medium is preferably supplied from a cooling side heating medium supply heat pump. .

  Furthermore, in addition to the above object, in order to achieve the object of being able to cope with various scales at low cost and more appropriately introducing heating and cooling using a heat pump excellent in energy efficiency, And it is preferable that there are a plurality of the cooling medium heaters and / or heat exchangers.

  In addition, in addition to the above-mentioned purpose, it is possible to automatically and appropriately perform control related to adjustment of cold water load and prevention of supply of cold water or hot water, and to achieve the purpose of ensuring a more efficient and stable operation. In the above invention, it is preferable to have an automatic control device that switches the number of operating and / or operating modes of the plurality of cooling medium heaters according to the state of the heating medium and / or the cooling medium.

  Furthermore, in addition to the above object, in order to achieve the object of continuing the operation with excellent energy saving by automatically responding to various conditions, in the above invention, the cooling pump for supplying the cooling side heating medium is: It is preferable that there are a plurality of automatic control devices that switch the number of operating heat pumps for supplying the plurality of cooling-side heating media in accordance with the state of the heating media and / or the cooling media.

  In addition to the above object, in order to achieve the object of enabling smoother automatic operation, in the above invention, the automatic control device is configured such that the load related to the cooling medium is less than the load related to the heating medium. In this case, it is preferable that a part of the plurality of cooling-side heating medium supply heat pumps be in an operation standby state.

  Furthermore, in order to achieve the object of providing a heating / cooling device that can be operated with extremely good energy efficiency and can be adapted to various additional conditions, the heating medium that heats the heating load is heated. A heat pump for cooling a cooling medium for cooling a cooling load, a heating load amount adjusting means for adjusting a heating load amount of the heating medium to the heat pump, and a cooling temperature sensor for detecting a cooling temperature as a temperature of the cooling medium And the other heat source for assisting heating of the heating medium, the cold temperature sensor and the other heat source, and the heating load amount in the heating load amount adjusting means according to the cold temperature obtained from the cold temperature sensor. It is preferable to provide an automatic control device that controls and adjusts the heating supply amount by the other heat source.

  In addition, in order to achieve the purpose of providing a heating and cooling device that can continue operation with extremely good energy efficiency and can be adapted to various additional conditions, the heating medium that heats the heating load is heated, A heat pump that cools a cooling medium that cools a cooling load; cooling load amount adjusting means that adjusts a cooling load amount of the cooling medium to the heat pump; a thermal temperature sensor that detects a thermal temperature that is a temperature of the heating medium; A cooling load amount in the cooling load amount adjusting means connected to the other cooling heat source for assisting cooling of the cooling medium, the thermal temperature sensor and the other cooling heat source, and according to the thermal temperature obtained from the thermal temperature sensor And an automatic control device that adjusts the amount of cold heat supplied by the other cold heat source.

  In addition, in addition to the above object, in order to achieve the object of performing control more effectively in a simpler manner, in the above invention, when the temperature of the cooling medium is lowered, the automatic control device is configured to heat the heat pump. It is preferable to reduce the amount of cooling in the heat pump when the temperature of the heating medium is increased.

  Further, in addition to the above object, in order to achieve the object of performing the control smoothly and accurately while being simpler, the automatic control device according to the above invention is configured such that when the temperature of the cooling medium decreases, the heating medium It is preferable that the supply set temperature of the cooling medium is increased when the supply set temperature of the cooling medium is decreased or the temperature of the heating medium is increased.

  Furthermore, in addition to the above object, in order to achieve the object of performing control more simply but effectively, in the above invention, the heating medium that circulates the heating medium in a state where the amount of heat when returning to the heat pump is constant A pump is provided, and the automatic control device preferably increases the supply set temperature of the heating medium when the temperature of the cooling medium decreases.

  Furthermore, in addition to the above object, in order to achieve the object of providing heating and cooling that can suppress the power consumption and can continue the operation of the heat pump, and is further excellent in energy saving and operational stability, The operation mode of the heat pump can be switched between the heating medium following mode and the cooling medium following mode, or the cooling medium following operation is first started for the heat pump, and then the heating medium following operation is switched. Is preferred.

Similarly to the above-described invention , in order to achieve the purpose of smoothly starting the operation that can continue the heat pump at a low cost, when the cooling load is generated in a predetermined amount or more, the operation of the heat pump is started, or the heat pump Before starting the operation, the heating medium of the heat pump is heated by factory exhaust heat, or before the operation of the heat pump, the heating medium of the heat pump is heated by the heating load preheated by the other heat source, It is preferable to do.

  In addition to the above object, in order to achieve the object of enabling the operation of the heat pump to be continued while improving the followability to the temperature change of the heating load, in the above invention, the heating load amount of the heat pump is adjusted. However, it is preferable to control the temperature of the heating medium.

  Furthermore, in addition to the above object, in order to achieve the object of further improving the overall efficiency while ensuring the heating and cooling performance, in the above invention, a plurality of the heat pumps are installed, and the automatic control device Is a hot water supply temperature sensor that detects a hot water supply temperature that is a temperature at which the heating medium is supplied from the heat pump in at least some of the predetermined heat pumps, and a temperature at which the heating medium returns to the heat pump. A hot water return temperature sensor that detects a certain hot water return temperature, a cold water supply temperature sensor that detects a cold water supply temperature that is a temperature when the cooling medium is supplied from the heat pump, and a calorimeter that detects the amount of heat of the heating medium And the hot water supply temperature obtained from the hot water supply temperature sensor and the hot water return temperature sensor obtained from the hot water supply temperature sensor. From the difference in water return temperature and the current heating capacity obtained from the calorific value obtained from the calorimeter, and the heating capacity during rated operation obtained from the cold water supply temperature obtained from the cold water supply temperature sensor, the heat pump When the load factor is less than or equal to a set value, control is performed to stop the operation of a part of the heat pump, and after the heat pump is stopped, the temperature obtained from the hot water supply temperature sensor When the hot water supply temperature is equal to or lower than a set value, it is preferable to perform control for restarting the operation of the stopped heat pump.

  Furthermore, in addition to the above object, in order to achieve the object of further improving the overall efficiency by enabling the heat pump to be switched to an efficient operation mode according to the situation, The heating pump is further connected to a cooler capable of cooling the heating medium, and the automatic control device is obtained from the cold temperature sensor. When the cooling temperature is equal to or higher than a predetermined value, the heating medium is supplied to the cooler to receive the cooled heating medium, and the second heating medium is supplied by the heating device to replace the heating medium. It is preferable to heat the heating load.

  In addition to the above purpose, in order to achieve the purpose of making it possible to switch the heat pump to an efficient operation according to the power consumption, so that the power consumption of the factory or office does not exceed the contract power, etc. The invention further comprises a heating device capable of supplying a second heating medium that heats the heating load, and a power consumption meter that detects power consumption, wherein the heat pump includes a cooler capable of cooling the heating medium; The automatic control device is connected to the power consumption meter, and when the power consumption obtained from the power consumption meter is equal to or higher than a set value, supplies the heating medium to the cooler. It is preferable to receive the cooled heating medium and supply the second heating medium by the heating device to heat the heating load instead of the heating medium.

  In addition to the above-mentioned purpose, in order to achieve the purpose of preventing the lack of heating as a whole by making it possible to replenish this by the heating means even if the heating medium from the heat pump is insufficient, In the invention, the apparatus includes a hot water tank that stores the heating medium from the heat pump, and a heating unit that heats the heating medium in the hot water tank, and heats the heating load by the heating medium from the hot water tank. It is preferable that the second heating medium is heated.

  Furthermore, in addition to the above-mentioned purpose, the objective of introducing extremely efficient heating or cooling using waste water or the like with low cost and low capital investment without providing an automatic control device in addition to the heat pump is achieved. Therefore, in the above invention, the heat pump includes a plurality of heat pumps, a second cooler capable of supplying a fourth cooling medium that cools the cooling load, and further includes a part of the heat pump that supplies the heat. The cooling medium can be switched between the heat exchanger side with the cooling side heating medium and the cooling side of the cooling load, and the part when the heating load is relatively light while the cooling load is relatively heavy While cooling the cooling load with the cooling medium of the heat pump, applying the cooling side heating medium to the remaining cooling medium of the heat pump, the heating load with all the heat pumps When the heating load is relatively heavy while the cooling load is relatively light, the cooling side heating medium is also applied to the cooling medium of the some heat pumps, and the heat pump It is preferable to heat the heating load and cool the cooling load with the fourth cooling medium of the second cooler.

  In addition, in order to achieve the purpose of continuing the energy-saving operation of the heat pump steam generator, the heat pump steam generator is operated using the waste water generated by heat exchange with the factory exhaust heat (exhaust gas) as a heat source. It is preferable to reduce the output of the heat pump steam generator when the amount of heat of the factory exhaust heat is reduced.

  In addition, in order to achieve the purpose of continuing the operation that saves energy while adapting to various load conditions for the heat recovery type heat pump of the double band specification, the heating medium that heats the heating load and the cooling load are achieved. A double-band specification exhaust heat recovery heat pump that cools the cooling medium that further cools the cooling medium and supplies cooling water, and a cooling water cooler that cools the cooling water. The exhaust heat recovery heat pump During the follow-up operation, when the output exceeds a predetermined value and / or the temperature of the cooling medium exceeds a specific value, the supply of the heating medium is stopped or the exhaust heat recovery type heat pump is cooled during the hot water follow-up operation. When it is understood that the cooling is insufficient for the load, the heating medium of the exhaust heat recovery heat pump is cooled by the cooling water cooler and / or the cooling device. It is preferable to or.

  Furthermore, in order to achieve the purpose of enabling the exchange of heat between the heating media related to a plurality of heat pumps and enabling more efficient operation or its continuation as a whole, the heating media for heating the heating load is heated. It is preferable that a plurality of heat pumps for cooling the cooling medium for cooling the cooling load are provided, and a heat exchange heating medium communication circuit capable of exchanging heat between at least two of the heating media is provided.

  Also, in order to achieve the purpose of maintaining the balance between the heat quantity of the heating medium and the cold quantity of the cooling medium and continuing the operation of the heat pump, which is extremely energy saving, the heating medium that heats the heating load is heated and the cooling load is reduced. A heat pump for cooling the cooling medium to be cooled is provided, and the heat pump is preferably capable of following the heating medium, and preferably controls the temperature of the cooling medium of the heat pump during the heating medium following operation.

  According to the present invention, heating and cooling are collectively performed by a heat pump, and heat exchange is performed between the factory exhaust heat, warm water of a separate heat pump or the like (cooling side heating medium) and the cooling medium. Therefore, it is possible to prevent overcooling by applying the cooling side heating medium to the chilled water, and it is possible to secure an extremely efficient and stable operation of the heat pump. In the case where is used, there is an effect that the exhaust heat can be cooled by effectively utilizing the energy of the exhaust heat. Further, the automatic control device operates the second heat pump before the first heat pump, and at the start of the operation of the first heat pump, the temperature of the first heating medium is raised in advance using the exhaust heat of the second heating medium as a heat source. There is an effect that the operation that can be continued in a state where the energy efficiency is extremely good can be smoothly started at a low cost.

It is a block diagram of the heating-cooling apparatus which concerns on the 1st form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the heating-cooling apparatus which concerns on the 2nd form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a flowchart which shows operation | movement of the heating-cooling apparatus which concerns on the 3rd form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 5th form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the heating-cooling apparatus which concerns on the 6th form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the heating-cooling apparatus which concerns on the 7th form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a flowchart which shows operation | movement of the heating-cooling apparatus which concerns on the 8th form of this invention. It is a block diagram which shows the heating-cooling apparatus which concerns on the 9th form of this invention, (a) is in summer etc., (b) is in winter etc. It is a block diagram of the heating-cooling apparatus which concerns on the 10th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 11th form of this invention. It is a block diagram in the case of a heavy cooling load, (b) a block diagram in a case where the cooling load is light, and (c) a block diagram in a case where the cooling load is small. FIG. 17A is a block diagram when there is no cooling load, and FIG. 17B is a block diagram when the heating load is heavy. (A) Block diagram when the cooling load is heavy, (b) Block diagram when the cooling load is light, (c) Block diagram when the cooling load is small. (A), (b) is a block diagram when the air-cooling heat pump fails in the heating / cooling device of FIG. 18, and (c) is a block when the cooling / heating load of the heating / cooling device according to the fifteenth embodiment of the present invention is small. FIG. It is a block diagram in the case of a heavy cooling load, (b) a block diagram in the case where the cooling load is light, and (c) a block diagram in a case where the cooling load is small, in the heating and cooling device according to the sixteenth aspect of the present invention. (A), (b) is a block diagram when there is no cooling load in the heating and cooling apparatus of FIG. 20, (c) is a block diagram when there is no cooling load of the heating and cooling apparatus according to the seventeenth embodiment of the present invention. It is. It is a block diagram of the heating-cooling apparatus which concerns on the 18th form of this invention. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus of FIG. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus which concerns on the 19th form of this invention. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus which concerns on the 20th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 21st form of this invention. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus of FIG. It is a block diagram at the time of (a) heating operation of the air-cooling heat pump in the heating / cooling device concerning the 22nd form of the present invention, (b) at the time of operation switching, and (c) at the time of cooling operation. It is a block diagram of the heating-cooling apparatus which concerns on the 23rd form of this invention. It is a flowchart which shows operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the heating-cooling apparatus which concerns on the 24th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 25th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 26th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 27th form of this invention. It is a block diagram of the heating-cooling apparatus which concerns on the 28th form of this invention. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the heating-cooling apparatus which concerns on the 29th form of this invention. It is a flowchart which concerns on operation | movement of the heating-cooling apparatus of FIG. It is a block diagram of the sterilizer concerning (a) Example 1-1 of the present invention, and (b) Example 1-2. It is a block diagram in (a) summer etc., (b) winter etc. of the desiccant air conditioner concerning Example 2-1 of this invention. It is a block diagram of the stock solution temperature control apparatus which concerns on Example 3-1 of this invention. It is a block diagram of the concentration condenser which concerns on Example 4-1 of this invention. It is a block diagram of the concentration condensing apparatus which concerns on Example 4-2 of this invention. It is a block diagram of winter etc. of the washing | cleaning apparatus which concerns on Example 5-1 of this invention. It is a block diagram of the washing | cleaning apparatus which concerns on Example 5-1 of this invention. It is a block diagram of the drying apparatus which concerns on Example 6-1 of this invention. It is a block diagram of the drying apparatus which concerns on Example 6-2 of this invention. It is a block diagram of the drying apparatus which concerns on Example 6-3 of this invention. It is a block diagram of the drying apparatus which concerns on Example 6-4 of this invention. It is a table | surface which shows the example of simulation of a prior art example and the drying apparatus of FIG. (A), (b) is a block diagram of the coating device which concerns on Example 7-1 of this invention. (A), (b) is a block diagram of the coating device which concerns on Example 7-2 of this invention. It is a block diagram of the coating device which concerns on (a) Example 7-3 and (b) Example 7-4 of this invention. It is a block diagram of the coating device which concerns on Example 7-5 of this invention. It is a block diagram of the coating device which concerns on Example 7-6 of this invention. It is a block diagram of the coating device which concerns on Example 7-7 of this invention. It is a block diagram of the dry cooling apparatus which concerns on (a) Example 8-1 of this invention, and the electrodeposition coating apparatus which concerns on (b) Example 8-2. It is a block diagram of the drying cooling device which concerns on Example 8-3 of this invention. (A) is a block diagram during heat pump stop in Example 8-4 of the present invention, and (b) is a block diagram during heat pump operation in the same example. It is a block diagram of (a) the drying cooling apparatus which concerns on Example 8-5 of this invention, and the electrodeposition coating apparatus which concerns on (b) Example 8-6.

  Hereinafter, an example of an embodiment according to the present invention will be described with reference to the drawings as appropriate. In addition, the said form is not limited to the following example.

[First form]
FIG. 1 is a schematic diagram of a heating / cooling apparatus 1 according to the first embodiment, and the heating / cooling apparatus 1 is installed in a factory or the like where both a heating load (heating target) and a cooling load (cooling target) can exist. .

  The heating and cooling device 1 includes an exhaust heat recovery type heat pump 10 that collectively performs heating with respect to the heating load H and cooling with respect to the cooling load C. The heat pump 10 generates cold water while simultaneously generating hot water using exhaust heat generated at that time, and supplies the hot water to the outside. For example, cold water of about 7 degrees to 30 degrees and about 40 degrees to 70 degrees are used. What was developed recently (high efficiency high temperature take-out machine HEM150HR made by Kobe Steel, Ltd.) which can supply hot water simultaneously is used. The heat pump 10 is required to balance hot / cold water due to the property that hot / cold water is simultaneously supplied, sufficiently absorbed and returned to hot / cold water, and the heat of the hot water is sufficient to extract a large amount of hot water. It is necessary for the water to be absorbed and returned to the target, and a large amount of low-temperature water to be taken out and then returned to the heat. The heat pump 10 may be one that can supply hot water at a maximum of 90 degrees, or one that can supply warm water at 95 degrees with cold water (waste water) at 30 degrees. Also, such a modification can be applied to other embodiments and examples.

  The heat pump 10 includes a pipe 12 that supplies hot water as a heating medium to the heating load H, and a pipe 16 that supplies cold water as a cooling medium to the cooling load C. In addition, it has a pipe 22 for returning hot water from the heating load H to the heat pump 10 and a pipe 26 for returning cold water from the cooling load C to the heat pump 10. Each pipe may be provided with a heat exchanger or a tank (not shown). Further, the arrangement of pipes and the like may be changed as appropriate.

  The heating / cooling device 1 is installed in a factory that generates heat belonging to the factory or factory exhaust heat X (exhaust heat belonging to the factory) as a cooling side heating medium. As factory waste heat X, waste heat water, makeup water, exhaust, exhaust gas, equipment heat release, work heat release, air conditioning exhaust heat (cooling water) or cogeneration exhaust heat, or from various equipment Moved to water for heat dissipation (heat recovery by fan coil, etc.), heat from hydraulic oil, heat dissipation of workpieces after drying, etc., and products that have been heated by hot water washing are washed in the subsequent water washing process Heat, exhaust heat generated from factory air conditioning (cold water return), or a combination thereof.

  Furthermore, a heat exchanger 30 is installed in the pipe 26 from the cooling load C to the heat pump 10 in the heating / cooling device 1. The heat exchanger 30 includes a pipe 32 for introducing the factory waste heat X and a factory after the heat exchange. A pipe 34 for leading the exhaust heat X is connected. The pipe 32 is provided with a flow rate adjusting valve 36 as a cooling side heating amount adjusting unit or a flow rate adjusting unit. As the cooling side heating amount adjusting means or the flow rate adjusting means, in addition to the flow rate adjusting valve 36, a pump or an inverter for adjusting the discharge amount, or a combination thereof may be adopted.

  Further, in the heating load H, an other heat source heat exchanger 42 capable of introducing another heat source Z (steam, electric heater, air-cooled heat pump, or a combination of these) is arranged, and can be heated by the other heat source Z. ing. The pipe 46 connecting the other heat source Z and the other heat source heat exchanger 42 is provided with a flow rate adjusting valve 48 as another heat source heating amount adjusting means capable of adjusting the heating amount.

  In addition, pumps 50 and 52 are sequentially installed on the return pipe 22 on the heating side and the return pipe 26 on the cooling side (closer to the heat pump 10 than the heat exchanger 30 for cooling side heating). In addition, a cold water temperature sensor 54 is installed as a cold temperature sensor for detecting the temperature (heat quantity) of the return cold water in the pipe 26, and the cold water temperature sensor 54 is an automatic control device (not shown) that controls the heating / cooling device 1. And is electrically connected to the heat pump 10. The automatic control apparatus may be common with the control means of the heat pump 10 and the control means of various devices, may be a separate computer, or may be a combination thereof. The chilled water temperature sensor 54 only needs to measure the temperature of the chilled water, and may be disposed in the pipe 16 on the supply side (measurement of chilled heat supply temperature) or a chilled water tank (measurement of chilled water tank temperature) not shown. They may be arranged in combination.

  The pumps 50 and 52 are inverter-controlled by an automatic control device, and adjust the flow rate of hot water or cold water (return hot heat amount adjustment means / return hot water flow rate adjustment means, return cold heat amount adjustment means / return cold water flow rate adjustment means).

  Such a heating / cooling device 1 operates as described below.

  For example, it is assumed that the heating load H is 800 kW (kilowatts) and the cooling load C is 300 kW. In this case, it is necessary to supply 800 kW of hot water from the heat pump 10, but 200 kW is required for electric input for this supply, and 600 kW of cold water is simultaneously supplied. Hot water 800 kW is supplied to the heating load H through the pipe 12, heats the heating target as necessary and circulates from the pipe 22 to the heat pump 10 after the temperature drops. On the other hand, 600 kW of cold water is supplied to the cooling load C through the pipe 16 and sufficiently cools the object to be cooled, but enters the pipe 26 in a state where 300 kW can be cooled. Then, this cold water reaches around the pipe 32 of the factory exhaust heat X in the heat exchanger 30, takes the heat of the factory exhaust heat X by 300 kW by the action of the heat exchanger 30, and circulates to the heat pump 10 in a heated state. . The factory exhaust heat X is also cooled by such heat exchange.

  Further, fluctuations in the heating load H and the cooling load C are dealt with by adjusting the heat pump 10 and the flow rate adjusting valve 36. These adjustments are connected to a chilled water temperature sensor 54 that detects a temperature (cold water return temperature) in the vicinity of the heat pump 10 connection portion of the pipe 26 and a sensor that grasps a temperature (hot water return temperature) in the vicinity of the heat pump 10 connection portion of the pipe 22. Automatically performed by the automatic control device. The various temperature sensors may be arranged in at least one of other pipes (pipe 16, 34, etc.), the heat exchanger 30, and the cold water tank, or may be arranged on the cooling load C side of the pipe 26. Further, the temperature sensor may be arranged on the heating load H side in the cold water load follow-up operation instead of being provided in the hot water load follow-up operation of the heat pump 10.

  That is, as shown in FIG. 2, if the operation of collecting cold water and recovering the heat of the discharged hot water is permitted so as to follow the hot water based on the heating load H, the automatic control device sets the cold water temperature sensor 54 of the pipe 26. Monitor (Yes in step S1). In this monitoring, when the chilled water return temperature falls below the set value (Yes in step S2), the cooling load C is relatively light, so that the flow rate adjustment valve 36 is gradually increased until the chilled water temperature of the pipe 26 rises to the set value. (Steps S3 to S5). On the other hand, when the chilled water return temperature exceeds the set value (No in step S2, Yes in step S6), the cooling load C is relatively heavy, so that the flow control valve until the chilled water temperature of the pipe 26 falls to the set value. 36 is gradually reduced (steps S7 to S9).

  For example, when the heating load H is relatively light (600 kW) in summer or the like, the automatic control device grasps this by the temperature rise of the temperature sensor of the pipe 22 and reduces the amount of heat of the hot water coming out of the heat pump 10 (600 kW). If the amount of heat of the cold water is reduced accordingly (450 kW), the flow rate adjustment valve 36 is throttled as described above, and the amount of heat exchange with the warm water (150 kW) is correspondingly reduced.

  On the other hand, when the heating load H is relatively heavy in the winter season or the like, the automatic control device grasps this due to a temperature shortage from a predetermined value by the temperature sensor of the pipe 22 and increases the amount of heat of the hot water coming out of the heat pump 10. Since the amount of heat of the cold water also increases, the flow rate adjustment valve 36 is opened as described above to increase the amount of heat exchange of the heat exchanger 30.

  A heating-side control valve (three-way valve) (not shown) that adjusts the heat exchange amount between the heating load H and the hot water of the heat pump 10, and a cooling-side control valve that adjusts the heat exchange amount between the cooling load C and the cold water of the heat pump 10. (Three-way valve) supplies necessary hot and cold water. Alternatively, the automatic control device performs inverter control on the pump 50 in the thermal follow-up operation, so that the hot water (60 degrees) according to the heating load H (heating load, thermal load) of the degreasing tank 2 and the chemical conversion tank 4 is obtained. Is supplied via the pipe 12 and returned to the heat pump 10 via the pipe 22. In addition, the automatic control device performs inverter control on the pump 52 to supply cold water (7 degrees) corresponding to the cooling load C (cooling load) via the pipe 16 and heat pump via the pipe 26. You may return to 10.

  The automatic control device adjusts the heat exchange amount of the exhaust heat of the factory exhaust heat X with respect to the chilled water by adjusting the opening degree of the flow control valve 36 (cooling side heating amount adjusting means). By appropriately heating the cold water with the factory exhaust heat X, the following situation can be prevented. That is, when the heating load H is relatively high, the cold heat generated simultaneously by generating the necessary warm heat becomes excessive with respect to the cooling load C, and the cold water is eventually overcooled as it is. This prevents a situation where the balance is lost, and the heat pump 10 is brought to an emergency stop and the operation is not continued.

  Further, when the automatic control device determines that the factory exhaust heat X is equal to or less than a predetermined value and the exhaust heat is insufficient, the return chilled water temperature grasped by the chilled water temperature sensor 54 with respect to the flow rate of the warm water (the amount of heat returned to the heat pump 10). Accordingly, the pump 50 is squeezed and adjusted, and the temperature of the return chilled water is raised while corresponding to the cooling load C (thermal follow-up operation, heating load amount adjusting means) by reducing the heating water heating amount. While warm heat is supplied by the heat pump 10 according to the generation of cold water commensurate with the cooling load C, an excessive temperature drop in the cold water returning to the heat pump 10 is prevented, and the operation of the heat pump 10 is continued. In this case, when the amount of heat of the hot water supplied from the heat pump 10 is insufficient with respect to the heating load H, the automatic control device controls the flow rate adjustment valve 48 to introduce steam or the like into the other heat source heat exchanger 42 to be heated. The other heat source Z is activated to back up the insufficient heat. Note that when the factory exhaust heat X becomes equal to or higher than a specific value (which may be the same as the predetermined value), the automatic control device returns to the thermal follow-up operation in which the factory exhaust heat X is applied to cold water.

  The heating / cooling device 1 is installed in a factory that generates factory waste heat X, heats a heating medium for responding to the heating load H, and cools a cooling medium for responding to the cooling load C. 10 and a heat exchanger 30 as a cooling medium heater that heats the cooling medium with factory exhaust heat X.

  Therefore, although it is going to operate the heat pump 10 according to the heating load H, the cooling load C is too light, cold water does not rise to regulation temperature, and the heat pump 10 stops without being able to balance warm water and cold water. Thus, heating or cooling can be provided by a single heat pump 10.

  In addition, although the system which uses the factory waste heat X for a heating cannot be considered, temperature is low and cannot be heated effectively. On the other hand, in the heating / cooling device 1, since the factory exhaust heat X as the cooling side heating medium is applied to the cold water having a low temperature, the factory exhaust heat X can be effectively used.

  Furthermore, the heating / cooling device 1 is installed in a factory that generates factory waste heat X, and heats the heating medium (hot water) in the pipes 12 and 22 that heat the heating load H, and also cools the cooling load C. The heat pump 10 that cools the cooling medium (cold water) in 16, 26, the pump 50 that adjusts the heating load amount of the heating medium to the heat pump 10, and the cold return temperature that is the temperature when the cooling medium returns to the heat pump 10 The cold water temperature sensor 54 to be detected, the other heat source Z for assisting heating of the heating medium, the cold water temperature sensor 54 and the other heat source Z are connected to the heating load in the pump 50 according to the cold heat return temperature obtained from the cold water temperature sensor 54 While controlling the amount, an automatic control device for adjusting the heating supply amount by the other heat source Z is provided. Instead of adjusting the amount of heat by adjusting the flow rate of the pump 50, a bypass circuit for returning from the pipe 12 to the pipe 22 (inlet of the pump 50) is installed, and a control valve is provided in the bypass circuit so that the heat exchange amount with the heating load H (By increasing the bypass amount, the amount of heat exchange between the hot water and the heating load H decreases and the temperature of the hot water returns to the heat pump 10 without lowering), thereby reducing the output of the heat pump 10 and lowering the cold water temperature. It is also possible to prevent this. When the temperature of the hot water tank is lower than the set temperature, the control to back up with the other heat source Z is effective for operating the exhaust heat recovery type heat pump. That is, in the exhaust heat recovery type heat pump, the hot water supply upper limit temperature and the lower limit temperature are determined by the cold water supply temperature. As an example, when supplying cold water at 15 degrees, operation cannot be performed unless the supply temperature of hot water is 32 degrees or higher. Also, depending on the equipment, when the hot water temperature is low, the warming operation is performed, and the standard operation cannot be performed until the hot water temperature rises, and it takes time to start up the production line.

  Therefore, although it is going to operate the heat pump 10 according to the heating load H, the cooling load C is too light, cold water is too cold, and the situation where the heat pump 10 stops without being able to balance warm water and cold water is avoided. The heat pump 10 can be operated with extremely high efficiency for heating or cooling, and can be covered by one heat pump 10 that emits less carbon dioxide during the operation. Since the other heat source Z is provided, heating of the heating medium by the heat pump 10 fluctuates or heating of the heating medium is insufficient in order to maintain a balance while the heating of the cooling medium of the heat pump 10 is insufficient. However, it can be backed up by the other heat source Z, the operation can be stabilized, the heating capacity of the heat pump 10 can be suppressed, and the initial introduction cost and the running cost can be reduced. Furthermore, the heating and cooling adapted to the heating load H and the cooling load C can be effectively controlled by a relatively simple operation method of adjusting the heating load amount by the pump 50.

  In addition, a flow rate adjustment valve 36 that adjusts the flow rate of the factory exhaust heat X to the heat exchanger 30, and a cold water temperature sensor 54 that detects a cold water return temperature that is a temperature when the cooling medium in the pipe 26 returns to the heat pump 10. The automatic control device is connected to the cold water temperature sensor 54 and controls the flow rate in the flow rate adjustment valve 36 by controlling the opening degree of the flow rate adjustment valve 36 according to the cold water return temperature. The temperature grasped by the cold water temperature sensor 54 may be the temperature of the cold water tank when the cold water tank is installed or the cold water supply temperature in place of or together with the cold water return temperature.

  Therefore, the amount of heat exchange with the factory exhaust heat X can be automatically adjusted so that the return temperature or amount of heat of the cooling medium suitable for the heat pump 10 can be obtained, and efficient heating or cooling can be automatically performed. Can do. In addition, it may replace with what is based on a pump about flow volume adjustment, and you may provide a flow volume adjustment valve in the exit of a pump. Further, a bypass circuit for returning from the hot water outlet of the heat pump 10 to the inlet of the pump 50 may be provided to adjust the bypass flow rate, thereby adjusting the heating load on the heat pump 10, or from the cold water outlet of the heat pump 10 to the inlet of the pump 52. The cooling load on the heat pump 10 may be adjusted by providing a bypass circuit for returning to the above and adjusting the bypass flow rate.

[Second form]
FIG. 3 is a schematic diagram of the heating / cooling device 101 according to the second embodiment, and the heating / cooling device 101 is the same as the first embodiment except for the configuration between the cooling load C and the heat pump 10.

  The heating / cooling device 101 includes a flow control valve 102 in the pipe 16 and a heat exchanger 104 that connects the pipes 16 and 26. The heat exchanger 104 is provided with a pipe 116 from the cooling section of the cooling load C and a pipe 126 that leads the cooling water after heat exchange to the cooling section of the cooling load C. A heat exchanger 130 is interposed in the pipe 126, and a pipe 132 from the cold water chiller 131 as a cooling side cooler (cooling device) and a pipe 134 returning to the cold water chiller 131 are connected to the heat exchanger 130. Yes. The pipe 132 is provided with a flow rate adjustment valve 136. A cooling tower may be used as the cooling side cooler.

  The automatic control device of the heating / cooling device 101 can open and close the flow rate control valve 36 or the flow rate control valve 102 of the factory exhaust heat X according to the monitoring of the chilled water temperature sensor 54 of the pipe 26, and a temperature sensor (not shown) of the pipe 126. The flow control valve 102 can be opened and closed according to the monitoring. The temperature sensor of the pipe 126 may be provided on the heat exchanger 104 side or may be provided on the cooling load C side.

  Such a heating / cooling apparatus 101 operates as described below.

  In the heating / cooling device 101, a chilled water chiller 131 is provided in addition to the heat pump 10, and a pipe circuit for each of the cooling loads C, the heat exchangers 30 and 130, and a temperature sensor are provided, and the cooling water of the heat pump 10 is preferentially cooled. Then, the cold water of the cold water chiller 131 is applied to the cooling load C.

  The automatic control device of the heating / cooling device 101 controls the return temperature (heat amount) of the cold water to the heat pump 10 by controlling the flow rate adjusting valves 36 and 102 as in the first embodiment, and as shown in FIG. The control valve 136 is controlled to control the chilled water temperature on the cooling load C side of the pipe 126.

  That is, if the automatic control device is in the cooling operation for the cooling load C (Yes in step S101), the automatic control device grasps the chilled water return temperature in the pipe 126 by the temperature sensor, and if the temperature is lower than the set value (in step S102). Yes), the flow rate control valve 136 is gradually throttled (steps S103 to S105), and the cooling amount by the chilled water chiller 131 is reduced so that the temperature approaches the set value.

  On the other hand, if the chilled water return temperature exceeds the set value (No in step S102, Yes in S106), the flow control valve 136 is gradually opened (steps S107 to S109), and the amount of cooling by the chilled water chiller 131 is increased to increase the temperature. Move closer to the set value.

  For example, for heating the heating load H, the heat pump 10 supplies hot water of 70 degrees to the pipe 12 and returns to 65 degrees from the pipe 22 after heating, while cold water is supplied at 20 degrees in the pipe 16 to heat exchanger Assuming that the cooling water is returned to 25 degrees after passing through 104 and 30, the cooling water is 29 degrees in the pipe 116. However, the cold water is cooled by the application of the cold water of the heat pump 10 via the heat exchanger 104, and the heat exchanger 130 is further cooled. The cold water is cooled by the application of the cold water chiller 131 through which the cold water is cooled to 27 degrees, and the cooling load C is returned. At this time, the cold water of the heat pump 10 is preferentially applied to the cold water to be cooled, and the cold water is heated by the factory exhaust heat X for efficient supply of hot water by the heat pump 10, so that the efficiency of the heat pump 10 is preferential. Driving in a state that takes into account. In addition, finally, the degree of cooling of the cold water to be cooled is adjusted by the cold water of the cold water chiller 131, and the temperature of the cooling object is maintained in an appropriate range.

  The heating and cooling apparatus 101 described above is installed in a factory that generates factory waste heat X, and heats the first cooling medium in the pipes 116 and 126 that cool the cooling load C and the heating medium that heats the heating load H. At the same time, the heat pump 10 that cools the second cooling medium in the pipes 16 and 26 that cools the first cooling medium (via the heat exchanger 104), and the first cooling medium by the third cooling medium in the pipe 132 (heat A chilled water chiller 131 that cools (via the exchanger 130) and a heat exchanger 30 that heats the second cooling medium with factory exhaust heat X are provided.

  Therefore, the cold water temperature can be individually set on the heat pump 10 side and the cold water chiller 131 side, the cold water of the heat pump 10 is first applied first, and the cold water of the cold water chiller 131 is supplementarily applied. 10 can be operated in an efficient state. Further, the chilled water chiller that is left over from the conventional heating / cooling apparatus that performs heating and cooling individually can be effectively used for the fine cooling control described above.

  Moreover, the 1st flow control valve 36 which adjusts the flow volume to the heat exchanger 30 of the factory waste heat X, and the cold water which detects the cold water return temperature which is the temperature at the time of the 2nd cooling medium in the pipe 26 returning to the heat pump 10 The temperature sensor 54, the second flow rate adjusting valve 136 for adjusting the flow rate of the third cooling medium in the pipe 132 from the chilled water chiller 131, and the chilled water temperature sensor 54 are connected, and the first flow rate according to the chilled water return temperature. And an automatic control device for controlling the flow rates in the first flow rate control valve 36 and the second flow rate control valve 136 by controlling the opening degree of the control valve 36 and the second flow rate control valve 136.

  Therefore, the amount of heat exchange with the factory exhaust heat X can be automatically adjusted so that the return temperature or the amount of heat of the cooling medium suitable for the heat pump 10 can be obtained, and the adjustment of the first cooling medium by the chilled water chiller 131 can be performed. The cooling target can be reliably cooled while realizing stable cooling and making the operation of the heat pump 10 highly efficient and stable.

[Third embodiment]
FIG. 5 is a flowchart showing the operation of the heating / cooling device according to the third embodiment, and the configuration of the heating / cooling device is the same as that of the heating / cooling device 101 of the second embodiment, and only the control of the flow rate control valve 136 is different. (The control shown in FIG. 4 replaces the control shown in FIG. 5).

  That is, if the automatic control device is operating in the hot water follow-up heat recovery mode (Yes in step S151), it is determined whether the opening degree of the flow rate control valve 136 exceeds the upper set value (for example, 70%) (step S152). If it exceeds (Yes), it is determined whether or not the cold water return temperature of the heat pump 10 ascertained by the cold water temperature sensor 54 exceeds a lower limit value (for example, 17 degrees) (step S153). If the lower limit value is exceeded (Yes), the chilled water supply temperature of the heat pump 10 is lowered until the flow rate adjustment valve 136 reaches an opening degree of 65% or less, and the chilled water amount of the chilled water chiller 131 is reduced (steps S154 to S157). As long as the cold water return temperature of the heat pump 10 exceeds the lower limit set value, the automatic control device operates to gradually throttle the flow rate adjustment valve 136 (step S156).

  On the other hand, if the automatic control device determines in step S152 that the opening degree of the flow rate control valve 136 does not exceed the upper set value (No), the opening degree of the flow rate control valve 136 is less than the lower set value (for example, 40%). If it is less than the lower set value (Yes), it is determined whether or not the cold water return temperature of the heat pump 10 is less than an upper limit value (for example, 35 degrees) (step S159). If it is less than the upper limit value, the chilled water temperature of the heat pump 10 is gradually raised until the flow rate adjustment valve 136 reaches an opening degree of 55% or more, and the cooling amount of the chilled water chiller 131 is increased (steps S160 to S163). As long as the cold water return temperature of the heat pump 10 is less than the upper limit set value, the automatic control device gradually releases the flow rate adjustment valve 136 (step S162).

  The heating / cooling device of the third embodiment is the same as that of the second embodiment, and particularly controls not only the flow control valve 36 but also the flow control valve 136 using the cold water return temperature of the heat pump 10.

  Therefore, the same effect as the heating / cooling device 101 of the second embodiment is obtained, and in particular, the opening degree of the flow rate control valve 136 related to the cooling water of the chilled water chiller 131 is controlled according to the operation state (chilled water return temperature) of the heat pump 10. While cooling the cooling load C reliably, a good state of the heat pump 10 (a state where the cold water return temperature is in an appropriate range) can be automatically secured by adjusting the flow rate adjustment valve 136 of the cold water chiller 131.

[Fourth form]
The heating and cooling device according to the fourth embodiment is the same as the second and third embodiments, but the operation of switching the heat pump 10 to a more efficient operation is different when the chilled water chiller 131 has a surplus power.

  That is, the automatic control device has a state in which the opening degree of the flow rate control valve 136 is equal to or less than a predetermined value (for example, 40%, the same applies hereinafter) and the cooling medium return temperature is within a predetermined range (28 degrees ± 1 degree). When it is understood that it continues for a predetermined time (30 minutes or more), the chilled water temperature of the heat pump 10 is controlled to increase (15 to 20 degrees), and the heating capacity and COP (Coefficient of Performance, efficiency) of the heat pump 10 are controlled. (Heating capacity 373 kW to 426 kW, COP 2.94 to 3.37). At this time, for example, after returning to the heat pump 10 at 20 degrees through cooling to be cooled or adjusted application of the factory exhaust heat X, it returns at 25 degrees. Further, although the temperature of the chilled water of the heat pump 10 rises and the efficiency of the heat pump 10 improves, the degree of cooling of the object to be cooled decreases, so the opening degree of the flow control valve 136 is increased by that amount (60%), and the chilled water return temperature is increased. Control is performed so as to be within a predetermined range.

  The heating / cooling device according to the fourth embodiment is the same as the second and third embodiments. In particular, when the chilled water chiller 131 has a surplus capacity, the automatic control device uses the chilled water supply temperature (second cooling medium) for the heat pump 10. To increase the temperature after cooling.

  Therefore, the same effects as those of the second and third embodiments can be obtained, and in particular, the heat pump 10 can be switched according to the situation so that the operation of sending out hot water more efficiently, and the cooling / heating performance of the heating / cooling device can be improved. The overall efficiency can be improved while being sufficient.

[Fifth form]
As shown in FIG. 6, the heating / cooling device 201 according to the fifth embodiment has a plurality of heat pumps added to the first embodiment.

  That is, the heat pumps 210 and 211 are installed, the hot water supply pipe 212 is arranged from the heat pump 210 to the heating load H, and the hot water supply pipe 214 is arranged from the heat pump 211 to the cooling load C. Is done. In addition, a hot water return pipe 222 from the heating load H to the heat pump 210 is arranged, and a hot water return pipe 224 from the heating load H to the heat pump 211 is arranged.

  Further, a cold water supply pipe 216 is arranged from the heat pump 210 to the cooling load C, and a cold water supply pipe 217 is arranged from the heat pump 211 to the cooling load C. Further, a cold water return pipe 226 is arranged from the cooling load C to the heat pump 210, and a cold water return pipe 227 is arranged from the cooling load C to the heat pump 211. The pipe 226 is provided with a heat exchanger 230 for exchanging heat with the factory exhaust heat X guiding pipe 32, and the pipe 227 is provided with a factory exhaust heat related to another system provided in the same manner as the pipe 32. A heat exchanger 231 for exchanging heat with respect to the X guiding pipe 232 is provided. The factory exhaust heat X that has passed through the heat exchanger 230 from the pipe 32 reaches the pipe 34, and the factory exhaust heat X that has passed through the heat exchanger 231 from the pipe 232 reaches the pipe 234. The pipe 32 is provided with a flow rate adjustment valve 36, and the pipe 232 is provided with a flow rate adjustment valve 236.

  FIG. 7 is a flowchart showing the operation of the heating / cooling apparatus 201. When the automatic control device of the heating / cooling device 201 acquires the load factor of one of the heat pumps 211 during the operation of both the heat pumps 210 and 211 and determines that the operation efficiency is poor because it is equal to or less than the set value (50%). The operation is performed so that the load factor of 210 increases and the operation of the heat pump 211 is stopped to reduce the number of units.

  That is, when the operation of discharging cold water is permitted to follow the hot water (Yes in step S251), the automatic control device calculates the load factor of the heat pump 211 and determines whether it is less than the set value (step S252). ).

  Here, the load factor is calculated as follows. That is, the load factor is obtained by dividing the current heating capacity by the heating capacity at the rated (100%) operation, and the rated heating capacity is obtained from the cold water supply temperature according to the correspondence table. The cold water supply temperature is grasped by a sensor connected to the automatic control device and arranged in each of the pipes 216 and 217, and the correspondence table is stored as a database in a storage device of the automatic control device. Examples of correspondence table include 349 kW at 12 degrees, 373 kW at 15 degrees, 426 kW at 20 degrees, 485 kW at 25 degrees, 556 kW at 30 degrees, and if there is no grasped temperature in the correspondence table, The one at the closest temperature is set as the rated heating capacity. For example, if cold water is supplied at 12 degrees and returned at 15 degrees, the heating capacity is 349 kW corresponding to 12 degrees.

  On the other hand, the current heating capacity is calculated by grasping the hot water inlet / outlet temperature difference and the hot water flow rate and multiplying these values. The hot water inlet / outlet temperature is grasped by a temperature sensor arranged in the pipes 214 and 224, and the hot water flow rate is grasped by a flow meter similarly arranged. For example, if the outlet temperature (supply temperature) of the hot water is grasped as 70 degrees by the temperature sensor of the pipe 214 and the inlet temperature (return temperature) of the warm water is grasped as 67 degrees by the temperature sensor of the pipe 224, the temperature difference between the inlet and outlet is It is understood that 70−67 = 3 degrees. The hot water flow rate is assumed to be 1000 cubic meters per minute, for example.

  Then, the current heating capacity is 3 (degrees) × 1000 (per cubic meter per minute) × 60 (minutes) / 860 (kilocalories / kW) = 209 (kW). Therefore, the load factor is calculated as 209/349 = 60%.

  If it is determined that the load factor calculated in this way is less than the set value (Yes in step S252), it is determined whether another heat pump 210 is in operation (step S253). If (Yes), it is determined whether the operation priority of the heat pump 211 is lower than the heat pump 210 (step S254). Here, since the operation priority of the heat pump 211 is lower, the process proceeds to step S255, and the operation is stopped because the load factor of the heat pump 211 is low and the efficiency is relatively poor.

  When the heat pump 211 stops, there is a shortage in the amount of hot water heating stopped, and this is grasped by the automatic control device. Therefore, the automatic control device shall supply hot water at a high temperature for the operating state of the heat pump 210. Therefore, the operating state of the heat pump 210 is high in load factor and efficient.

  Further, the automatic control device checks whether the hot water outlet temperature of the operating heat pump 210 is less than a predetermined value (set value −1 degree) at every set time (every 5 minutes) while the heat pump 211 is stopped (step). S256 to S258). If it is not less than the predetermined value (No in step S257), the stopped heat pump 211 is restarted assuming that the hot water heating is insufficient (step S259).

  In the heating / cooling device of the fifth embodiment described above, a plurality of heat pumps 210 and 211 are installed, and the automatic control device is the temperature at which the heating medium is supplied from the heat pump 211 in at least some of the predetermined heat pumps 211. A hot water supply temperature sensor that detects a hot water supply temperature (hot water outlet temperature), a hot water return temperature sensor that detects a warm water return temperature (hot water inlet temperature) that is a temperature when the heating medium returns to the heat pump 211, and a cooling medium ( The cold water in the pipe 217 is connected to a cold water supply temperature sensor that detects a cold water supply temperature that is a temperature at which the heat pump 211 is supplied, and a flow meter (calorimeter) that detects a flow rate (heat amount) of the heating medium. Difference between the hot water supply temperature obtained from the hot water supply temperature sensor and the hot water return temperature obtained from the hot water return temperature sensor, and a flow meter From the current heating capacity obtained from the obtained flow rate and the heating capacity during rated operation obtained from the cold water supply temperature obtained from the cold water supply temperature sensor, the load factor in the heat pump 211 is grasped and the load factor is set. When the temperature is less than the value, the operation is stopped for the heat pump 211, and after the operation of the heat pump 211 is stopped, the operation is restarted for the stopped heat pump 211 when the hot water supply temperature obtained from the hot water supply temperature sensor is equal to or less than the set value. .

  Accordingly, when the heating load H is sufficiently heated and the cooling load C is sufficiently cooled, the load factor is reduced by each of the plurality of heat pumps, and therefore the overall efficiency is inferior. When the hot water supply temperature is likely to be insufficient, the heat pump 211 related to the reduction control can be automatically restored, and the overall efficiency is ensured while ensuring the heating and cooling performance. Can be further improved.

[Sixth form]
As shown in FIG. 8, the heating / cooling device 301 according to the sixth embodiment adds a cooling tower 302 as a heating side cooler and a boiler 304 as a heating side heater (heating device) to the second embodiment. It consists of Pipes 306 and 308 are arranged between the heat pump 10 and the cooling tower 302 to form a hot water circuit, and can be switched to the hot water circuit of the pipes 12 and 22. Further, a steam supply path 310 for supplying steam (second heating medium) for heating the heating load H from the boiler 304 is formed. Note that a chiller or a combination thereof may be employed as the heating side cooler (cooling device), and an electric heater, a hot water tank, or a combination thereof may be employed as the heating side heating device.

  Then, the automatic control device of the heating / cooling device 301 has a relatively large amount of the cooling load C, such as when the heating load H is relatively low in summer, and the cooling catches up with the heat pump 10 operated according to the heating load H. When there is not, it connects with the cooling tower 302, it switches to the driving | operation in the cooling mode only for cooling, and it controls to cover the heating load H with the boiler 304.

  That is, as shown in FIG. 9, if the heat pump 10 is in operation (Yes in step S351), the automatic control device checks whether the opening degree of the flow rate control valve 136 exceeds the set value (step S352). If it exceeds, the hot water circuit of the heat pump 10 is switched to the cooling tower 302 side (pipe 306, 308 side) (step S353), and the heat pump 10 is operated in the cooling mode. Further, in step S353, the automatic control device allows passage of steam through the pipe 310 in order to introduce steam from the boiler 304 (opens a valve of the pipe 310 (not shown)).

  For example, when the heat pump 10 is operated at a load factor of 60% (cooling capacity 148 kW, rated 246 kW) in accordance with the heating load H in the summer, the flow control valve 136 is sufficiently cooled if the opening degree is 85% or more. The automatic control device confirms that the chilled water temperature is within a predetermined range (28 degrees), switches to the cooling mode for the heat pump 10, and heats the steam of the boiler 304 as a heating load. Applies to H. At this time, since the hot water is sufficiently cooled and returned, the cooling capacity of the heat pump 10 is increased to 450 kW, and the refrigerant to be cooled (first cooling medium) is sufficiently cooled. The opening of 136 is reduced.

  Also in this embodiment, a plurality of heat pumps can be installed, and in this case, an automatic control device is formed so that each of the cooling mode and the normal mode (heat recovery mode) can be switched independently. A temperature sensor can be provided. In addition, an order may be given in advance for each heat pump, and the cooling mode may be switched in order from the lower one. At this time, before switching the mode of the lower heat pump, it may be confirmed whether another heat pump is operating (in the normal mode).

  The heating / cooling device of the sixth embodiment described above further includes a boiler 304 capable of supplying steam for heating the heating load H, the heat pump 10 is connected to a cooling tower 302 capable of cooling hot water, and the automatic control device is When the opening degree of the flow control valve 136 is equal to or larger than the set value, the hot water is supplied to the cooling tower 302 to receive the cooled hot water, and the steam is supplied from the boiler 304 to heat the heating load H instead of the hot water. .

  Accordingly, in summer when the cooling load C is insufficient when the heating load H is adjusted, the heat pump 10 is operated in an efficient cooling mode for cooling, while the boiler 304 existing in the factory is effectively used for heating. In the middle season when the heating load H and the cooling load C are balanced, the heat pump 10 can be efficiently heated and cooled in the heat recovery mode. Can cool the factory exhaust heat X with the cold water of the heat pump 10 and operate the heat pump 10 in an efficient state with a balance between heating and cooling, and automatically selects the appropriate mode according to the situation as a whole device. It is possible to select and carry out extremely efficient operation.

[Seventh form]
The heating / cooling device 401 according to the seventh embodiment shown in FIG. 10 is the same as the sixth embodiment, but the automatic control device further monitors the amount of received power (or the amount of power consumed by the entire device) installed in the factory. It is connected to a demand controller (power consumption meter) that is a computer with a power meter, and is provided with a cold water dedicated operation changeover switch that commands switching the heat pump 10 to a cold water dedicated operation.

  The heating / cooling device 401 includes a hot water tank 402 (for example, 60 degrees hot water) that can be heated by another heat source Z interposed between the heat pump (HP) 10 and the heating load H, and a cooling tower (CT) arranged on the heating side. ) 404, a cold water tank 406 (for example, 17 degrees of cold water) interposed between the heat pump 10 and the cooling load C, and an air cooling heat pump (air cooling HP) 408 for cooling the cold water in the cold water tank 406. A three-way valve 410 that adjusts the flow rate to the hot water warm water tank 402 or the cooling tower 404 is interposed in the pipe 12 on the heating side.

  Further, in this embodiment, a plurality of heat pumps 10 are installed, an automatic control device is formed so that each can switch between the cold water follow mode and the hot water follow mode, and an individual hot water circuit and a temperature sensor are provided. Further, a rank is assigned in advance for each heat pump 10, and the cooling mode is switched in order from the lower one. At this time, as will be described later, before switching the mode of the lower heat pump 10, it is confirmed whether the other heat pump 10 is operating (in the normal mode). Note that one heat pump 10 may be provided.

  And as an operation | movement, it is set as the case where it is set as the case where it is estimated that power consumption exceeds a predetermined value and exceeds the power receiving capability of a factory about the conditions which make the heat pump 10 operate exclusively for cold water. . Note that the cold water dedicated operation changeover switch may be a mode transition switch that sequentially and sequentially changes the mode between the hot water follow-up mode. Further, one of connection with a demand controller or installation of a switch may be omitted. Further, the operations of the sixth embodiment and this embodiment may be performed together.

  That is, as shown in FIG. 10A to FIG. 11, the automatic control device checks whether the heat pump 10 is operating in the heat recovery mode (step S381). It is confirmed whether a signal transmitted when the power is equal to or higher than a set value (contract power or a value slightly smaller (about 0 to 5%) than this) is output from the demand controller (step S382). If a signal indicating that the power consumption is equal to or greater than the set value is output from the demand controller (Yes), it is confirmed whether the other heat pump 10 is operating in the hot water follow-up mode (step S383). If (Yes), it is confirmed whether the operation priority is lower than the other heat pumps 10 (step S384).

  If the operation priority is lower (Yes), the automatic control device changes the hot water tracking mode from the hot water tracking mode to the cold water tracking mode for the heat pump 10 (step S385) and also sets the hot water circuit to the cooling tower as shown in FIG. The temperature is automatically switched to the 404 side by the control of the three-way valve 410, and the hot water temperature set value of the cooling tower 404 is changed from 60 degrees to 32 degrees, for example (step S386). If the signal is not output from the demand controller (No in step S382), it is determined whether or not there is an input to the operation switch for exclusive use of the cold water (step S387). If there is an input (Yes), the hot water circuit is also switched. And the transition to the cold water follow-up mode and the setting change of the cooling tower 404 are performed (step S386).

  For example, while the heat pump 10 is operating in the hot water follow-up mode, hot water is supplied at 70 degrees and collected at 65 degrees, and is supplied at a cold water temperature of 15 degrees and a chilled water supply amount of 246 kW for power consumption of 127 kW (cold water side COP1.94). If the power consumption exceeds the predetermined value, the automatic control device switches the heat pump 10 to the chilled water exclusive operation and reduces the power consumption while maintaining the chilled water supply amount of 246 kW. It shall be 34.5 kW (cold water side COP7.14). On the other hand, the automatic control device heats the heating load H with steam from the boiler 304.

  When the heat pump 10 is in the chilled water follow-up mode, if the power consumption from the demand controller is the same or different below a predetermined value and the power receiving capacity of the factory is sufficient, the automatic control device And switching to the hot water tracking mode may be performed automatically. Also, a hot water follow-up mode changeover switch may be provided, and when there is an input to this, the hot water circuit is switched and the hot water follow-up mode is switched.

  In the heating and cooling apparatus of the seventh embodiment, the boiler 304 that can supply steam for heating the heating load H and the power consumption meter that detects power consumption are further provided, and the heat pump 10 is a cooling tower 302 that can cool hot water. The automatic control device is connected to the power consumption meter, and when the power consumption obtained from the power consumption meter is equal to or higher than the set value, the hot water is supplied to the cooling tower 302 to supply the cooled hot water. At the same time, steam is supplied from the boiler 304 to heat the heating load H instead of hot water.

  Therefore, when the heat pump 10 is heated and cooled, if the power consumption exceeds the contract power, etc., the automatic control device can switch the heat pump to the operation according to the power consumption, and the power consumption of the entire device is the contract power, etc. Can not be exceeded.

[Eighth form]
The heating and cooling apparatus according to the eighth embodiment includes a plurality of heat pumps 210 and 211 as in the fifth embodiment, and further heats the hot water in the hot water tank and the hot water tank that can store the hot water from the heat pumps 210 and 211. In order to do so, a boiler as a heating side heating means for introducing steam into the hot water tank, a second heating medium for heating the heating load H and its pipe, a pipe for hot water (heating medium) from the hot water tank and the second heating And a heat exchanger interposed in the medium pipe. The second heating medium is heated with warm water through the heat exchanger. In the hot water tank, a hot water tank temperature sensor connected to the automatic control device and detecting the temperature of the hot water in the tank is installed. Usually, the heat pump 210 is mainly used, and the heat pump 211 is operated as a spare machine in a low priority state. Note that a steam heater, an electric heater, or an air-cooled heat pump may be used as the heating means.

  And in the heating / cooling device of this embodiment, even if the heating amount is insufficient by heating the heating load H through a hot water tank that can heat the inside, the heating is performed by backing up with another heat source Z. It is possible to continue.

  That is, as shown in FIG. 12, if the heating load H exists (Yes in step S401), the automatic control device determines whether the hot water tank temperature obtained from the hot water tank temperature sensor is less than a set value (68 degrees). If it is confirmed (step S402) and below the set value (Yes), it is confirmed whether one or more heat pumps 210 and 211 are operating in the hot water follow-up mode (step S403). If so (Yes), it is further determined whether or not the heat pump 211 as a spare machine is stopped (step S404). If it is stopped (Yes), the heat pump 211 is additionally automatically activated in the hot water follow-up mode ( Step S405).

  On the other hand, in the case where both the heat pumps 210 and 211 are not operating (No in step S403) or the heat pump 211 is not stopped (No in step S404), the automatic control device determines that the hot water tank temperature is equal to the set value. It is judged whether it falls below another set value (67 degrees) below (step S406), and if it falls below (Yes), steam (other heat source Z) is introduced from the boiler until the hot water tank temperature reaches the set value (68 degrees). Then, warm water is heated (steps S407 to S409).

  The heating / cooling device according to the eighth embodiment includes a hot water tank that stores hot water (heating medium) from the heat pumps 210 and 211, and a boiler that heats the hot water in the hot water tank, and is heated by the hot water from the hot water tank. The second heating medium that heats H is heated.

  Therefore, even if the hot water from the heat pumps 210 and 211 is insufficient, it is possible to prevent the heating as a whole by allowing the boiler to heat it, and a stable heating state is provided by providing a backup circuit for heating. Can be provided.

[Ninth embodiment]
As shown in FIG. 13, the heating / cooling device 501 according to the ninth embodiment includes a plurality of heat pumps 510 and 511 as in the fifth embodiment, and both (second) cooling side coolers with respect to the cooling load C. A cold water chiller 512 or a cooling tower 513 is installed to be switchable for cooling via any of the refrigerants. On the cold water side of the heat pump 510, a heat exchanger for the factory waste heat X of the factory is installed as in the first embodiment, and on the hot water side, as in the first embodiment, hot water for heating the heating load H is installed. Pipes are arranged. On the other hand, on the cold water side of the heat pump 511, a pipe for cooling the cooling load C and a pipe having a heat exchanger for the factory exhaust heat X similar to the heat pump 510 are arranged to be switchable, and the hot water side is the same as the heat pump 510. It becomes.

  The heating / cooling device 501 uses an operation that follows the heating load of the heat pump without using an automatic control device, and heats the heating load H using the factory waste heat X and cools the cooling load C according to the situation. Run.

  That is, as shown in FIG. 13A, when the heating load H is relatively moderate (900 kW) and the cooling load C is relatively heavy (300 kW) in summer and the like, the heat pump 510 is discharged from the factory. The operation is performed by raising the cold water temperature by X (430 kW) (30 degrees is increased to 35 degrees) and hot water (550 kW) is supplied, while the cold water (12 degrees, 220 kW) of the heat pump 511 is used for cooling the cooling load C ( Return at 17 degrees). In addition, about cooling of the cooling load C, the cooling capacity (80 kW) which is insufficient by supplementing the cold water chiller 512 is compensated, and the fluctuation of the cooling load C is dealt with (by applying the cold water chiller 512 to the return temperature of the cold water of the heat pump 511). The operating state of the heat pump 511 is stabilized by keeping it constant).

  On the other hand, as shown in FIG. 13B, when the heating load H is relatively heavy (1100 kW) and the cooling load C is relatively gentle in winter or the like, the heat pumps 510 and 511 are dedicated to heating. . That is, the chilled water side circuit of the heat pump 511 is switched to the heat exchanger side with the factory exhaust heat X, the temperature of the chilled water of both the heat pumps 510 and 511 is increased by the factory exhaust heat X (both from 30 degrees to 35 degrees), and hot water ( Both supply 550 kW) to the cooling load C. In addition, the cooling of the cooling load C is provided only by the cooling tower 513 by switching to the cooling tower 513 and applying it. Moreover, the operation | movement change in summer etc. and winter etc. can be manually performed for every season (twice a year).

  The heating and cooling apparatus 501 of the above ninth embodiment includes a plurality of heat pumps 510 and 511, and includes a chilled water chiller 512 or a cooling tower 513 capable of supplying a (fourth) cooling medium for cooling the cooling load C, Furthermore, the cooling medium supplied by some heat pumps 511 can be switched between the heat exchanger side of the factory exhaust heat X and the cooling side of the cooling load C, and the heating load H is relatively light while the cooling load C is relatively low. The cooling load C is cooled with the cooling medium of some heat pumps 511, while the factory exhaust heat X is applied to the cooling medium of the remaining heat pumps 510, and the heating load H is applied to all the heat pumps 510 and 511. When the heating load H is relatively heavy while the cooling load C is relatively light, the factory exhaust heat X is also applied to the cooling medium of some heat pumps 511. , By heating the heating load H in all of the heat pump 510, 511 to cool the cooling load C in a cold water chiller 512 to the cooling tower 513.

  Therefore, extremely efficient heating or cooling using the factory exhaust heat X can be introduced at low cost and low equipment investment without providing an automatic control device in addition to the heat pump. Moreover, the cold water chiller 512 and the cooling tower 513 which are conventionally installed in a factory can be used effectively.

[Tenth embodiment]
FIG. 14 is a schematic diagram of a heating / cooling device 601 according to the tenth embodiment, and the heating / cooling device 601 is the same as the first embodiment except for the configuration between the cooling load C and the heat pump 10.

  The heating / cooling device 601 includes a flow control valve 602 in the pipe 26, and includes a pipe 604 that guides the flow-adjusted branch cold water to the heat exchanger 30, and a pipe 606 that returns the cold water that has passed through the heat exchanger 30 to the pipe 26. The heat exchanger 30 is introduced with heat radiation from the drying furnace 608 installed in the factory and / or exhaust hot air Y (factory exhaust heat), and the branched cold water is heated.

  The heating / cooling device 601 can be changed as follows. The cooling side is heated by guiding the heat radiation of the work coming out of the drying furnace 608 (for example, about 150 degrees) to the heat exchanger 30. Moreover, even if the heat radiation / exhaust of the drying furnace 608 or the heat radiation of the workpiece is applied to the cooling load C, the heating load H is balanced against the cooling load C which cannot be heated by the heat pump 10 alone. However, the heat pump 10 may be operated in the cold water following mode and the flow rate control valve 602 may be fully opened to the drying furnace 608 side. When the heat pump 10 is operated in accordance with the cold water in this manner, it is possible to appropriately cope with the cooling load C, and the heating medium of the heat pump 10 that is efficiently generated with the generation of the cooling medium with respect to the heating load H It is possible to appropriately cope with other heat sources, and to make it easy to operate without requiring complicated control with low initial cost.

  Further, the heating / cooling device 601 can be modified as follows. That is, when the flow rate control valve 602 is fully open on the drying furnace 608 side and the chilled water supply amount of the heat pump 10 is insufficient (the temperature of the chilled water rises), control is performed to automatically close the drying furnace 608 side of the flow rate control valve 602. Make it feasible and make more efficient and stable operation. Further, in the cold water follow-up operation of the heat pump 10, in order to set the state where the heating amount is insufficient (warm water temperature is low) and the state where the heating amount is excessive (warm water temperature is high) to an appropriate state (proper temperature), The output of the heat pump 10 may be controlled by controlling the amount of heat exchange with the heat exchanger 30 by controlling the opening degree of the flow control valve 602 by an automatic control device. Further, a pump (and a cold water tank) may be provided instead of the flow rate adjustment valve 602, and the heat exchange amount in the heat exchanger 30 may be controlled by controlling the flow rate of the pump. In addition, a cooling tower is connected to the cooling side via a heat exchanger, and when the amount of heat such as exhaust air Y is sufficiently large, the cooling water of the cooling tower and the cold water of the heat pump 10 are heat-exchanged to thereby cool the cold water of the heat pump 10. Cooling is possible, the heat pump 10 is operated following hot water, the flow rate control valve 602 is fully opened to the drying furnace 608 side, the cold water is excessively heated, and the cooling water temperature is controlled by a cooling tower (other cooling heat source) (cooling load) Corresponding to C). In this case, it is possible to control the heat pump 10 without causing surplus in the hot water by the hot water follow-up operation, and it is possible to avoid the stop of the heat pump 10 due to the low temperature of the cold water easily at low cost.

  Even in the above-described heating / cooling device 601 or the like, by applying exhaust heat belonging to the factory to the cold water side, it is possible to maintain the balance of cold against hot and continue operation of the heat pump 10.

[Eleventh form]
As shown in FIG. 15, the heating / cooling device 1151 according to the eleventh embodiment is the same as the first embodiment except for the points described below. The heat pump 10 is connected to a hot water supply pipe 1160 and a hot water return pipe 1162, and a heat exchanger 1164 (heating side heating means) that performs heat exchange between the hot water and the heating medium is connected to these pipes. A heating medium supply pipe 1112 and a heating medium return pipe 1113 are also connected to the heat exchanger 1164, another heat source heat exchanger 1104 is disposed in the heating medium supply pipe 1112, and the heating medium return pipe 1113 is used for heating medium circulation. The pump 1115 is arranged. The heating medium is heated by passing through the heat exchanger 1164, is appropriately heated by the other heat source Z, and is supplied to the heating load H. A hot water pump 1166 is attached to the hot water return pipe 1162.

  For example, the automatic control device introduces a heating medium of 55 degrees into the heat exchanger 1164 and heats it to 58 degrees (374 kW). This heating medium is further heated to 60 degrees by another heat source Z (heating load 249 kW). Warm water for heating medium heating is 70 degrees and 60 degrees return (heating load 374 kW, COP 2.9), while cold water is also generated at 7 degrees and 17 degrees return with this warm water supply, resulting in a cooling load of 245 kW On the other hand, it works in a balanced state (just when cold is used). The automatic controller monitors the heating medium temperature in the heating medium supply pipe 1112 (immediately after the heat exchanger 1164) between the heat exchanger 1164 and the other heat source Z and supplies hot water to the heat pump 10 so that the temperature becomes 60 degrees. Control (warm water 70 degrees).

  Then, the automatic control device monitors the cold water temperature, and when the cooling load decreases to 129 kW and the cold water temperature falls below a predetermined temperature, the hot water supply set temperature of the heat pump 10 is lowered from 70 degrees to 65 degrees. Then, the heating amount of the heat pump 10 is reduced to 187 kW (heating side COP3.2), the heating medium is heated to 56.5 degrees, the cooling heat applied to the cooling water is also reduced, and the cooling water return temperature becomes a predetermined temperature or higher. After returning (12 degrees), the balance of heat and cold is maintained. The heating medium is heated by the other heat source Z at a heating amount of 436 kW, and the heating load H is set to a desired 60 degrees.

  The heat pump 10 may be operated following the warm water temperature (for example, desired heating medium temperature +5 degrees), and even in this case, the amount of cold heat can be lowered by lowering the warm water temperature set value. Alternatively, by increasing the heating amount of the other heat source (lowering the heating temperature set value), it is possible to reduce the heating load of the heat pump 10 and thus reduce the amount of cold heat. Moreover, even if the flow rate of the hot water pump 1166 is reduced by an inverter while keeping the hot water supply temperature constant, the heating amount is lowered and thus the cold heat amount is lowered.

  Even in the third embodiment of the heating / cooling device 1151, as in the first embodiment, the operation balance can be continued by maintaining the supply balance of the heat and cold in the heat pump by a simple method.

[Twelfth embodiment]
The heating / cooling device according to the twelfth embodiment is the same as the eleventh embodiment. The automatic control device performs a constant heat amount operation having a heat amount for generating a predetermined heating medium temperature instead of the constant flow rate operation for the hot water pump 1166. The hot water pump 1166 automatically adjusts the flow rate of the hot water in order to keep the amount of heat constant.

  For example, a heating medium of 45 degrees is heated to 300 degrees by a heat exchanger 1164 (COP 3.6, 60 degrees of warm water flow) to 50 degrees, and the cooling load 217 kW (COP 2.6) is balanced (cold water movement). 7 degrees and 17 degrees returned). The hot water pump 1166 is operated so as to have a hot water heat amount such that the heating medium temperature is 50 degrees with respect to the hot water circulation amount.

  Then, when the cooling load is reduced to 196 kW and the cold water return temperature becomes 16 degrees or lower, the automatic control device raises the hot water supply set temperature of the heat pump 10 to 70 degrees (warm water temperature going back 70 degrees / return 60 degrees). At this time, since the hot water pump 1166 continues the constant heat amount operation, the heating COP of the heat pump 10 is changed from 3.6 to 2.9, and the circulating hot water amount is reduced. By raising the hot water supply temperature, the cold heat generated by the heat pump 10 is also reduced (cold water return temperature 17 degrees, COP 1.9), and the operation of the heat pump 10 can be continued while corresponding to a decrease in cooling load.

[13th form]
FIG. 16A is a schematic diagram when the heating / cooling device 2861 according to the thirteenth embodiment has a heavy cooling load (cooling load C), and FIG. 16B is a schematic diagram when the heating / cooling device 2861 has a relatively light cooling load. FIG. 16 (c) is a schematic diagram when the heating load (heating load H) of the heating / cooling device 2861 exceeds the cooling load, and FIG. 17 (a) is a schematic diagram when there is no cooling load of the heating / cooling device 2861, FIG. 17B is a schematic diagram when the heating / cooling device 2861 has no cooling load and the heating load is relatively large (such as when the production line is started up). The heating / cooling device 2861 is equivalent to the heat pump 10. However, a plurality of heat pumps 2004p, 2004q, 2004r, etc. are used, and an air compressor 2840 is arranged. It is. The heating / cooling device 2861 includes a heat exchanger 2862 that warms hot water in the heating-side supply pipe 2034 of the heat pump 2004, a boiler (not shown) that can supply steam (hot water) ST (other heat source Z) to the heat exchanger 2862, A heat supply amount adjustment valve 2864 that can adjust the supply amount of the steam ST is provided (see FIG. 17B). The heating / cooling device 2861 includes a cooling tower 2832a for cooling the cooling water of the air compressor 2840 and a cooling / heating supply control valve 2866 for adjusting the cooling amount.

  A cooling tower 2832p or the like is connected to the heating side of the heat pump 2004p or the like via a supply-side motor valve 2047p or the like, a return-side motor valve 2049p or the like. In addition, the heating supply pipe 2034p such as the heat pump 2004p can be switched (or adjusted in flow rate) to the heating side supply pipe 2034 side of the heat pump 2004 by the motor valve 2047p. The heating return pipe 2036p such as the heat pump 2004p The valve 2049p can be switched to the heating side return pipe 2036 side of the heat pump 2004 (or the flow rate can be adjusted). Note that any one of the cooling towers 2832p and the like and the cooling tower 2832a may be common. Moreover, instead of switching to the cooling tower 2832a side, or together with this, the cooling water of the cooling tower 2832a and the hot water of the heat pump 2004 may be subjected to heat exchange.

  Further, the cooling side motor valves 2043p, 2045p and the like of the heat pump 2004p and the like can be switched (or the flow rate can be adjusted) between the cooling side of the heat pump 2004 and the air compressor 2840 side in the cooling side circuit. When switched to the air compressor 2840 side, heat exchange with the cooling water of the air compressor 2840 is possible. In addition, motor valves 2043 and 2045 are installed in order on the cooling side supply pipe 2030 and the cooling side return pipe 2032 of the heat pump 2004, and similarly switched between the cooling load C side and the air compressor 2840 side (or flow rate adjustment). It is possible. In FIGS. 16A and 16B, the circuit of the heat pump 2004p is omitted, and in FIG. 16C and FIG. 17A, the heating side circuit of the heat pump 2004p is omitted. These heating side circuits are actually connected to the heating load H.

  Such a heating / cooling device 2861 operates in the same manner as in the first embodiment, for example, as follows.

  That is, in the case of FIG. 16A in the case of heavy heat load or the like, the heat pump 2004 performs heat recovery operation in the hot water follow-up mode. However, it is necessary to supply cold heat to the cooling load C, depending on the cold load. The cooling operation of the heat pump 2004p and the like in the number of units is performed. At this time, the cooling side of the heat pump 2004p or the like is switched to the cooling side of the heat pump 2004, and the heating side of the heat pump 2004p or the like is switched to the cooling tower 2832p or the like side. If a plurality of heat pumps 2004p and the like are in cooling operation, all the heat pumps 2004p and the like are in a cooling operation state or a standby state for cooling operation. However, if there is a sufficient cooling capacity as a whole, one unit is set in a heating standby state.

  For example, cold water is supplied to the cooling load C at 7 degrees by the heat pump 2004, 2004p, etc., and returns to the heat pump 2004 at 12 degrees. At this time, the hot water supply temperature of the heat pump 2004 is 60 degrees, and the warm water return temperature is 55 degrees. The hot water supply temperature of the heat pump 2004p and the like is 35 degrees, and the warm water return temperature is 30 degrees by cooling of the cooling tower 2832p and the like. With the cooling, the heat pump 2004p and the like can continue the cooling operation.

  Further, in the case of FIG. 16B at the time of light and cold load, etc., when there is one heat pump 2004p or the like that performs cooling operation according to the cooling load C, the other heat pumps 2004p and the like are put on standby for cooling. Wait for hot water following operation (heating operation). The heating side of the heat pump 2004p or the like in the warm water follow-up standby mode is switched from the cooling tower 2832p or the like side to the heating side of the heat pump 2004, and the cooling side is switched from the cooling side of the heat pump 2004 to the air compressor 2840 side. When the automatic control device detects a lack of heat, such as when the warm water return temperature or the warm water outlet temperature of the heat pump 2004 becomes equal to or lower than a predetermined value, the automatic control device operates the heat pump 2004p or the like waiting for warm water tracking. When the hot water follow-up operation is started even in one of the heat pumps 2004p or the like, the heat pump 2004p or the like that is in the cooling standby state is switched to the hot water follow-up standby state.

  For example, cold water is supplied to the cooling load C at 7 degrees by the heat pump 2004, the heat pump 2004p that performs cooling operation, and the like, and returns to the heat pump 2004 at 12 degrees. Here, although the hot water supply temperature of the heat pump 2004 is 60 degrees, when the warm water return temperature falls from 55 degrees to 53 degrees or less, the heat pump 2004p or the like waiting for warm water follow-up is operated, and the cold water is cooled to 30 degrees. 2840 and returned at 35 degrees by heat exchange with cooling water. Further, the heat pump 2004p or the like during the hot water follow-up operation heats the hot water returning to the heat pump 2004 to 60 degrees and returns it to the heating side supply pipe 2034 of the heat pump 2004. By applying the exhaust heat of the air compressor 2840 to the heat pump 2004p or the like during the hot water follow-up operation, the heat pump 2004p or the like can continue the heating operation.

  Further, when the cooling load is small and the cooling pump output is less than the minimum cooling output of the heat pump 2004 (or a predetermined output exceeding the cooling pump output), the cooling side of the heat pump 2004 is switched to the air compressor 2840 side as shown in FIG. Then, the cooling heat supply to the cooling load C by the heat pump 2004 is stopped. The cooling supply is performed by one heat pump 2004p or the like that performs cooling operation.

  For example, cold water is supplied to the cooling load C at 7 degrees by the heat pump 2004p or the like that performs cooling operation, and returns to the heat pump 2004 at 12 degrees. The heating side such as the heat pump 2004p that performs cooling operation is cooled by the cooling tower 2832p or the like so that the operation can be continued. The cold water supply temperature of the heat pump 2004 is 30 degrees, and the cold water return temperature is set to 35 degrees by heat exchange with the cooling water of the air compressor 2840, so that the hot water supply by the heat pump 2004 can be continued. On the other hand, the hot water side of the heat pump 2004 is appropriately heated by the heat pump 2004p or the like during the hot water follow-up operation, and the supply temperature is maintained at 60 degrees (the return temperature is around 55 degrees).

  When cooling is not required at the time of starting up the production line, etc., as shown in FIG. 17 (a), the heat pump 2004p or the like is placed in a hot water follow-up operation or a standby state according to the thermal load, and the heat pump 2004 is also cooled. The side is switched to the air compressor 2840 side. However, if the automatic control device determines that chilled water is likely to be required at the cooling load C from the temperature on the cooling side, the opening degree of various motor valves or the production status or their relationship, one of the heat pumps 2004p and the like. Set the stand to the cooling standby state.

  For example, the heating side of the heat pump 2004, 2004p, etc. returns at 55 degrees and is supplied at 60 degrees. The cooling side of the heat pump 2004, 2004p, etc. is heated from 30 degrees to 35 degrees with the cooling water of the air compressor 2840, and the operation of the heat pump 2004, 2004p, etc. is continued using the exhaust heat of the air compressor 2840. can do.

  In addition, when cooling is not required and the thermal load is large, such as when starting up a production line in winter, as shown in FIG. 17B, the heat pump 2004p and the like are operated following hot water, and the cooling side including the heat pump 2004 is air-cooled. It is switched to the compressor 2840 side. Also, steam ST and the like are supplied from the boiler after adjustment by the heat supply amount adjustment valve 2864 by the heat load, and the hot water is heated through the heat exchanger 2862.

  Furthermore, when the amount of exhaust heat from the air compressor 2840 decreases due to a decrease in the air consumption of the factory and the heating on the cooling side such as the heat pumps 2004 and 2004p cannot be sufficiently performed, the cold water such as the heat pumps 2004 and 2004p is left as it is. The return temperature is lowered, and the heat pump 2004, 2004p and the like are stopped (for example, 5 degrees). Therefore, when the chilled water becomes a predetermined temperature (for example, 20 degrees) or less, the automatic control device stops the heat pumps 2004p and the like one by one to enter the warm water follow-up standby state, and maintains the cooling water temperature of the air compressor 2840. The decrease in the heating amount due to the stoppage of the heat pump 2004p or the like is compensated by the heating by the heat exchanger 2862. The output of the heat pump 2004, 2004p, etc. may be reduced by an inverter or the like to prevent the cooling water temperature of the air compressor 2840 from decreasing, or the flow rate of the hot water may be reduced by the inverter of the hot water pump, etc. The output of 2004p or the like may be reduced to prevent the cooling water temperature of the air compressor 2840 from decreasing, and the amount of heat in the heat exchanger 2862 may be increased to reduce the burden on the heat pumps 2004 and 2004p, etc. The amount of cold water heated may be reduced to prevent the cooling water temperature of the air compressor 2840 from decreasing, or the hot water supply temperature setting value of the heat pump 2004, 2004p, etc. may be lowered to reduce the output of the heat pump 2004, 2004p, etc. You may prevent the cooling water temperature of the air compressor 2840 from decreasing.

  In addition, when the amount of exhaust heat from the air compressor 2840 increases due to an increase in factory air consumption, etc., and the heating on the cooling side of the heat pumps 2004, 2004p, etc. becomes excessive, the cold water return from the heat pumps 2004, 2004p, etc. remains unchanged. The temperature rises and becomes a temperature at which the heat pumps 2004, 2004p and the like stop. Therefore, the automatic control device follows the hot water by heating the hot water with the steam ST when the cold water becomes a predetermined temperature or higher or the cooling water temperature of the air compressor 2840 becomes a predetermined temperature (for example, 35 degrees) or higher. If there is a waiting heat pump 2004p or the like, the heat pump 2004p or the like is operated to cool the cooling water, or the cooling tower 2832a is operated to keep the cooling water temperature from rising.

  For example, the cooling side of the heat pumps 2004, 2004p, etc. is supplied at 30 degrees and returns at 35 degrees. Further, the heating side of the heat pumps 2004, 2004p, etc. is supplied from 58 degrees to 60 degrees by the heat of the heat exchanger 2862, and returns at 53 degrees.

  In the heating and cooling device 2861 described above, the cooling side of the heat pumps 2004 and 2004p and the like is automatically switched to the air compressor 2840 side according to the heating load H and the cooling load C, and the heat pump is exchanged with the cooling water of the air compressor 2840 by heat exchange. Since the cold water such as 2004, 2004p is heated, the operation of the heat pump 2004, 2004p, etc. can be continued using the cooling water, and can be operated in a state of high energy saving.

[14th form]
FIG. 18A is a schematic diagram of the heating / cooling device 2871 according to the fourteenth embodiment when the cooling load is extremely large with respect to the heating load (for example, summer daytime), and FIG. 18B shows the cooling heat of the heating / cooling device 2871. FIG. 18C is a schematic diagram when the load is large with respect to the thermal load (for example, summer nighttime), and FIG. 18C is a schematic diagram when the thermal load is large with respect to the thermal load in the heating and cooling device 2871 (for example, winter). FIGS. 19A and 19B are schematic views in the case where an air cooling heat pump fails in the heating and cooling device 2871. The heating and cooling device 2871 is the same as that in the thirteenth embodiment.

  In addition, circuits such as the air cooling heat pump 2154a can be switched between the heating side and the cooling side of the heat pump 2004 by the motor valve 2043a and the motor valve 2045a and the like. 18 and 19, a part of the circuit between the cooling load C and the heat pump 2004 is omitted. The heat pump 2004p and the like can be heated by directly introducing the cold water of the heat pump 2004, and can operate as a heating heat pump for directly heating the cold water. In contrast, a heat pump that heats a medium different from the chilled water of the exhaust heat recovery type heat pump and heats the chilled water through a heat exchanger operates as a cooling-side heating medium supply heat pump.

  In the heating / cooling device 2871, cooling by the air cooling heat pump 2154a is anticipated, and the maximum cooling output of the heat pump 2004 is made smaller than the minimum cooling load.

  Such a heating / cooling device 2871 operates in the same manner as in the thirteenth embodiment, for example, as follows.

  That is, in the case of FIG. 18A at the time of the cold heavy load in summer, it is necessary to supply cold heat to the cooling load C, and the cooling operation of the air-cooled heat pumps 2154a and the like in the number corresponding to the cold load is performed. At this time, the cooling side of the air cooling heat pump 2154a or the like is switched to the cooling side of the heat pump 2004. If a plurality of air-cooling heat pumps 2154a and the like are in cooling operation, all the air-cooling heat pumps 2154a and the like are placed in a cooling operation or cooling operation standby state. However, if there is a sufficient cooling capacity as a whole, one unit is set in a heating standby state.

  For example, chilled water is supplied to the cooling load C at 7 degrees by the heat pump 2004, the air-cooled heat pump 2154a, and the like, and returns to the heat pump 2004, the air-cooled heat pump 2154a, etc. at 12 degrees. At this time, the hot water supply temperature of the heat pump 2004 is 55 degrees, and the warm water return temperature is 50 degrees. Further, the cooling water temperature or the amount of cooling heat is controlled by cooling the returning cold water by the air cooling heat pump 2154a or the like or supplying it to the cooling side supply pipe 2030. For hot water, the temperature of the hot water or the amount of heating is controlled by operating the heat pump 2004 in the hot water follow-up mode (heat recovery operation).

  Further, in the case of FIG. 18B at the time of light and cold load, etc., when the number of air-cooling heat pumps 2154a that perform cooling operation according to the load becomes less than a predetermined number (one), cooling standby for other predetermined units (one) The remaining air-cooled heat pump 2154a and the like are put on standby for heating operation. The heating side of the air-cooled heat pump 2154a or the like that is waiting for heating is switched from the cooling side of the heat pump 2004 to the heating side. When the automatic control device detects a lack of isothermal heat at which the hot water return temperature of the heat pump 2004 is equal to or lower than a predetermined value, the automatic control device operates the air-cooled heat pump 2154a and the like that are on standby for heating. When the heating operation is started on a predetermined unit (one unit) or more of the air cooling heat pump 2154a and the like, the air cooling heat pump 2154a and the like that are on standby for cooling are switched to a heating standby state.

  For example, chilled water is supplied to the heat exchanger of the cooling load C at 7 degrees by the heat pump 2004 or the air-cooled heat pump 2154a that performs cooling operation, and returns to the heat pump 2004, the air-cooled heat pump 2154a, and the like at 12 degrees. Here, although the hot water supply temperature of the heat pump 2004 is 55 degrees, when the warm water return temperature falls from 50 degrees to 48 degrees or less, the air-cooled heat pump 2154a or the like waiting for heating is operated, and the warm water returning to the heat pump 2004 is cooled with the air-cooled heat pump. Heat to 55 degrees with 2154a or the like, and return to the heating side supply pipe 2034 of the heat pump 2004 to eliminate the lack of heat.

  Further, when the cooling load is reduced due to winter or production conditions, etc., as shown in FIG. 18 (c), the cooling by the heat pump 2004 is continued, and the air cooling heat pump 2154a or the like (one of them) is cooled and cooled. Adjust the load. Further, when the air-cooled heat pump 2154a or the like that is on standby for heating is operated according to the thermal load and the air-cooled heat pump 2154a or the like that is on standby for heating is operated, the air-cooled heat pump 2154a or the like that is on standby for cooling is switched to a standby state for heating. In the air cooling heat pump 2154a and the like, a cooling standby unit (one unit) may be provided.

  For example, cold water is supplied to the cooling load C at 7 degrees by the heat pump 2004 or an air-cooled heat pump 2154a that performs cooling operation, and returns to the heat pump 2004 at 12 degrees. The hot water supply temperature by the heat pump 2004 or the air-cooled heat pump 2154a during heating operation is 55 degrees, the warm water return temperature is 50 degrees, and the supply of hot water or cold water by the heat pump 2004 can be continued.

  In addition, when the air-cooling heat pump 2154a or the like during the cooling operation breaks down due to a trip or the like, as shown in FIG. 19A, the air-cooling heat pump 2154a or the like that is in the heating standby mode is switched to the cooling mode to prevent the lack of cooling. To do.

  In the heating and cooling apparatus 2871 described above, the state of the air-cooled heat pump 2154a and the like is switched according to the heating load H and the cooling load C, and the heating and cooling by the heat pump 2004 is assisted. Heating or cooling can be performed, and the operation of the heat pump 2004 can be continued to operate the heating / cooling device 2871 in a state of high energy saving.

[15th form]
FIG. 19 (c) is a schematic view of the heating / cooling device 2881 according to the fifteenth embodiment when the thermal load is larger than the cooling load, etc., and the heating / cooling device 2881 is the same as that of the thirteenth embodiment. The difference is that the maximum cooling output of 2004 is set to be equal to or higher than the minimum cooling load.

  In the heating / cooling device 2881, in the heat pump 2004 during the hot water follow-up operation, the cold load is returned because the cold load is not sufficiently utilized since the cold load is not sufficiently utilized. In such a case, the hot water of the (one) air-cooled heat pump 2154a during the heating operation is switched to the heat exchanger 2040 side, the cold water of the heat pump 2004 is heated by heat exchange, and the cold water of the heat pump 2004 is deprived of the hot water. And the operation of the heat pump 2004 is continued. The circuit on the heating side of the heat pump 2004 may be branched to the heat exchanger 2040 side, and the cold water side of the heat pump 2004 may be heated by the branch circuit or the heat exchanger 2040.

  Even in such a heating / cooling device 2881, the heat pump 2004 can be kept running by maintaining the balance between the cooling and heating of the heat pump 2004, and the heating / cooling device 2881 can be appropriately operated in an energy-saving state. can do.

[16th form]
20A is a schematic diagram in the case where the cooling load is extremely large with respect to the thermal load in the heating / cooling device 2901 according to the sixteenth embodiment, and FIG. 20B is a schematic diagram showing that the cooling load in the heating / cooling device 2901 is relative to the thermal load. 20C is a schematic diagram when the heating / cooling device 2901 has a larger thermal load than the cooling load, etc. FIG. 21A is a heating / cooling device 2901 having no cooling / heating load. FIG. 21B is a schematic diagram in the case where the heating / cooling device 2901 has no cooling load and the heating load is relatively large, and the heating / cooling device 2901 is the same as in the thirteenth embodiment. Note that some circuits are also omitted in FIGS.

  Similarly to the thirteenth embodiment, the heating / cooling device 2901 includes an air compressor 2840 and motor valves 2043 and 2045 for switching the cooling side of the heat pump 2004 to the cooling water (waste water) side of the air compressor 2840. Or a circuit.

  Such a heating / cooling device 2901 operates in the same manner as in the thirteenth embodiment, for example, as follows.

  That is, in the case of FIG. 20A at the time of a heavy heat load or the like, it is necessary to supply cold heat to the cooling load C, and the cooling operation of the air-cooled heat pumps 2154a and the like in the number corresponding to the cold load is performed. At this time, the cooling side of the air cooling heat pump 2154a or the like is switched to the cooling side of the heat pump 2004. If a plurality of air-cooling heat pumps 2154a are in cooling operation, all the air-cooling heat pumps 2154a and the like are placed in a cooling operation or cooling operation standby state. However, if there is a sufficient cooling capacity as a whole, one unit is set in a heating standby state.

  For example, chilled water is supplied to the heat exchanger of the cooling load C at 7 degrees by the heat pump 2004, the air-cooled heat pump 2154a, etc., and returns to the heat pump 2004, the air-cooled heat pump 2154a, etc. at 12 degrees. At this time, the hot water supply temperature of the heat pump 2004 is 65 degrees, and the warm water return temperature is 60 degrees. Further, the cooling load of the heat pump 2004 is reduced by cooling the return chilled water by the air-cooled heat pump 2154a or the like or supplying it to the cooling side supply pipe 2030, and the heat pump 2004 can be continuously operated.

  Further, in the case of FIG. 20B at the time of light and cold load or the like, when there is one air-cooling heat pump 2154a or the like that performs cooling operation according to the load, the other air-cooling heat pump 2154a or the like is put on standby for cooling. Wait for heating operation. The heating side of the air-cooled heat pump 2154a or the like that is waiting for heating is switched from the cooling side of the heat pump 2004 to the heating side. When the automatic control device detects a lack of isothermal heat at which the hot water return temperature of the heat pump 2004 is equal to or lower than a predetermined value, the automatic control device operates the air-cooled heat pump 2154a and the like that are on standby for heating. When heating operation is started even with one of the air cooling heat pumps 2154a and the like, the air cooling heat pump 2154a and the like that are on standby for cooling are switched to a heating standby state.

  For example, chilled water is supplied to the cooling load C at 7 degrees by the heat pump 2004 or the air-cooled heat pump 2154a that performs cooling operation, and returns to the heat pump 2004 or the air-cooled heat pump 2154a at 12 degrees. Here, although the hot water supply temperature of the heat pump 2004 is 55 degrees, when the warm water return temperature falls from 50 degrees to 48 degrees or less, the air-cooled heat pump 2154a or the like that is on standby for heating is operated and the warm water returning to the heat pump 2004 is 55 degrees. To the heating side supply pipe 2034 of the heat pump 2004 to solve the shortage of hot water.

  Furthermore, in the winter season, the cooling load is reduced, and the output of the air cooling heat pump 2154a or the like during the cooling operation is equal to or less than a predetermined value (a value corresponding to a predetermined ratio (25%) of the maximum output), or the cold water return temperature is predetermined. When the value is 10 degrees or less, as shown in FIG. 20C, the cooling side of the heat pump 2004 is switched to the air compressor 2840 side, and one unit such as the air cooling heat pump 2154a is cooled and cooled. Corresponds to C. Further, when the air-cooled heat pump 2154a or the like that is on standby for heating is operated according to the thermal load and the air-cooled heat pump 2154a or the like that is on standby for heating is operated, the air-cooled heat pump 2154a or the like that is on standby for cooling is switched to a standby state for heating. In the air cooling heat pump 2154a and the like, a cooling standby unit (one unit) may be provided.

  For example, the heat pump 2004 supplies hot water of 55 degrees to receive 50 degrees of return warm water, while supplying cold water of 30 degrees to the air compressor 2840 side and receives 35 degrees of return cold water by heat exchange with the cooling water. . Heating of the heating load H is provided by the heat pump 2004, and cooling of the cooling load C is provided by the air cooling heat pump 2154a or the like during the cooling operation (supply 7 degrees, return 12 degrees). The operation of the heat pump 2004 is continued by applying the waste water from the air compressor 2840 to the cooling side of the heat pump 2004.

  On the other hand, the output of the air-cooling heat pump 2154a or the like during the cooling operation becomes a predetermined value (a value corresponding to a predetermined ratio (85%) of the maximum output) or the cold water return temperature becomes a predetermined value (15 degrees) or more. In this case, the heat pump 2004 is temporarily stopped, the cold water side is switched to the cooling water side of the air compressor 2840, hot water of the heating load H is supplied by the air-cooled heat pump 2154a, etc., and then the heat pump 2004 is operated following hot water to supply cold / hot water. To do.

  In addition, when there is no cooling load at the time of starting up the production line, etc., as shown in FIG. 21A, the air cooling heat pumps 2154a and the like are heated by the number corresponding to the heating load, and the rest is set in a heating standby state. In addition, when the opening degree of the cold heat supply amount adjustment valve 2048 exceeds a predetermined value or the production state becomes a predetermined value, the air cooling heat pump 2154a and the like are cooled down in order to cope with the resumption of cold water supply. Switch to standby mode.

  Further, in the case where the thermal load is large, such as when the production line is started up in winter, as shown in FIG. 21B, if the amount of heat of the warm water is small relative to the heating load, the heating side of the heat pump 2004 is connected to the steam ST from the boiler. It is heated by heat exchange to prevent insufficient heating. For example, when the hot water return temperature of the heat pump 2004 is 48 degrees and the hot water supply temperature is raised only to 53 degrees even by the air-cooled heat pump 2154a or the like during heating operation, the automatic control device grasps this case by using a temperature sensor or the like. The supply amount adjustment valve 2864 is operated, and warm water supplied by the steam ST is heated to 55 degrees.

  In the heating / cooling device 2901 described above, the state of the air cooling heat pump 2154a and the like is switched according to the heating load H and the cooling load C to assist heating and cooling by the heat pump 2004, and when there is no cooling load, the cooling side of the heat pump 2004 Since the air-cooling heat pump 2154a and the like are put into a cooling standby state if necessary, the operation of the heat pump 2004 is continued while accurately heating or cooling the heating load H or the cooling load C, so that energy saving is high. The heating / cooling device 2901 can be operated in the state.

[17th form]
FIG. 21C is a schematic diagram in the case where there is no cooling load in the heating / cooling device 2911 according to the seventeenth embodiment. The heating / cooling device 2911 is the same as that in the eighth embodiment, but the switching of the cooling side circuit is performed. Instead of using the motor valves 2043 and 2045, the heat control unit 2040 performs heat exchange with the cooling water of the air compressor 2840 using the heat exchanger 2040.

  Even in such a heating / cooling device 2911, for example, the cooling water of 40 degrees of the air compressor 2840 can raise the temperature of 25 degrees of cooling water of the heat pump 2004 to 30 degrees (the cooling water of the air compressor 2840 is 35 degrees). Therefore, it is possible to continue the operation of the heat pump 2004 that maintains the balance between heat and cold and is excellent in energy saving.

[18th form]
FIG. 22 is a schematic diagram of a heating / cooling device 3001 according to the eighteenth embodiment. The heating / cooling device 3001 is the same as that in the thirteenth embodiment, but the hot water boiler 2506 and the hot water tank 2508 are arranged on the heating side return pipe 2036 side. In addition, cold water pumps 3002a to 3002d or hot water pumps 3006a to 3006d are installed in the cooling side return pipes 2032a to 2032d to the heating side return pipes 2036a to 2036d, respectively. Moreover, the heat pump 2004a is positioned as a cooling / heating load adjuster. In addition, although the cooling / heating load adjustment machine is one here, you may arrange | position several.

  The automatic control device of the heating / cooling device 3001 controls, for example, the heat pump 2004b or the like based on its own hot water supply temperature, and controls the heat pump 2004a as a cooling / heating load adjuster based on its own hot water supply temperature and cold water supply temperature, The hot water boiler 2506 is controlled based on the temperature of the hot water tank 2508 or the hot water return temperature of the heating side return pipe 2036, and the flow rate adjusting valve 2046 for adjusting the cold water return temperature is controlled based on the cold water return temperature. The hot water supply amount adjusting valve 2109 (second heat supply amount adjusting means) for adjusting the hot water supply amount or the cold heat supply amount adjusting valve 2048 for adjusting the cold water supply amount to the cooling load C is controlled based on the hot water temperature. These temperatures are detected by the respective temperature sensors and grasped by the automatic control device. The hot water that is not supplied to the heating load H is passed through the branch pipe 2110 from the hot heat supply amount adjustment valve 2109.

  Such a heating / cooling device 3001 operates in the same manner as in the thirteenth embodiment, for example, as follows.

  That is, as shown in FIG. 23, if there is a stop command for the heating load H (NO in step S1001), the automatic control device stops the heat pump 2004a and the like and the hot water boiler 2506 (steps S1002, 1003), and performs processing. finish.

  On the other hand, if there is no stop command (YES in step S1001), it is determined whether the opening degree of the flow rate control valve 2046 is 60% or less (step S1004). If YES, the factory exhaust heat X that heats the cold water X If the hot water boiler 2506 is not in operation, the process returns to the beginning (NO in step S1005). In the initial state, the heat pump 2004a is operating and the heat pump 2004b and the like are stopped.

  On the other hand, if hot water boiler 2506 is in operation (YES in step S1005), the process proceeds to loop 1 for increasing the opening degree of flow control valve 2046. That is, first, the flow rate in the hot water pump 3006a of the heat pump 2004a as the cold load adjusting machine is increased (step S1006). Then, since the hot water supply temperature of the heat pump 2004a is temporarily lowered, the heat pump 2004a automatically increases the output so that the hot water becomes the set temperature (60 degrees) (thermal follow-up operation, inverter output increase).

  As the hot water output increases, the chilled water output also increases accordingly, and the chilled water temperature decreases as it is, so that the automatic control device increases the opening of the flow control valve 2046 to a predetermined value (70%), The heat pump 2004a and the hot water boiler 2506 are set as follows so that the amount of heat exchange with the factory exhaust heat X (35 degrees) is increased and the cold water return temperature (17 degrees, supply temperature 10 degrees) is maintained. To control.

  That is, the automatic control device checks whether or not the load of the heat pump 2004a is equal to or less than a predetermined ratio (95%) with respect to the maximum load (step S1007). If the load of the heat pump 2004a is not less than or equal to a predetermined ratio (NO), one of the heat pumps 2004b or the like that is not operating is activated (step S1008), and the process proceeds to step S1009. If the load of the heat pump 2004a is equal to or less than the predetermined ratio (YES in step S1007), the process proceeds to step S1009 without executing step S1008.

  Further, when the flow rate of the return warm water of the heat pump 2004a is increased, the flow rate of the warm water to the heating load H also increases and the return temperature of the warm water rises. Therefore, by reducing the output of the warm water boiler 2506 as another heat source, the return temperature of the warm water is reduced. An appropriate temperature difference (at the time of maximum output of the heat pump 2004a, a difference of 5 degrees) is ensured.

  That is, in step S1009, the automatic control apparatus monitors whether or not the warm water return temperature has reached a predetermined value (56 degrees) or more. If the warm water return temperature is equal to or higher than the predetermined value, the loop 2 for lowering the warm water return temperature to the predetermined value (55 degrees) is executed. Otherwise, the head of the loop 1 (step S1007) or the head of the process (flow rate control valve) When the opening of 46 reaches a predetermined value, the process returns to step S1001). In the loop 2, the output of the hot water boiler 2506 is decreased (step S1010).

  For example, when a thermal load of 450 kW is covered, the heat pump 2004a, which has a temperature difference of 5 tons at a flow rate of 43 tons per hour, covers 250 kW (43 × 1000 × 5 is divided by 860 kW / kcal), and the hot water boiler 2506 supplies 200 kW. When the hot water flow rate is increased to 60.2 tons per hour from the state covered, the hot water supply temperature of the heat pump 2004a temporarily decreases and 350 kW (60.2 × 1000 × 5) is recovered by the inverter in order to recover the temperature to the set value. Although the warm water return temperature from the heating load H rises and the output of the warm water boiler 2506 is reduced to 100 kW according to this, the hot water supply / return temperature difference in the heat pump 2004a is maintained and 450 kW is maintained. It can cope with thermal load.

  In contrast to the above, if the hot water return temperature is not adjusted by the hot water boiler 2506, the hot water supply temperature of the heat pump 2004a temporarily decreases even if the flow rate of the return hot water is increased. Increase the hot water supply temperature to the set value (70 degrees). Then, although the flow rate of hot water at the set temperature temporarily increases and the amount of heat increases, the amount of heat consumed in the heating load H has elapsed so long that the warm water return temperature rises and there is a difference from the supply temperature. Since the output of the heat pump 2004a is reduced by the hot water following operation, it can be assumed that the heating output of the heat pump 2004a does not change after all, and thus the cooling output does not increase.

  For example, when a heat load of 450 kW is covered, the temperature difference is 3 degrees even if the flow rate is increased to 129 tons per hour when the flow rate is increased to 129 tons per hour when the temperature difference is 5 degrees with the heat pump flow rate of 77.4 tons per hour, and the heating output changes at 450 kW. Absent. That is, when the flow rate is increased, the hot water supply temperature is temporarily lowered to 58 degrees, but the inverter output is increased because the warm water temperature is set to 60 degrees by the hot water follow-up operation, and the output is temporarily increased to 750 kW. However, since the load at the heating load H is 450 kW, the warm water is not used and the warm water return temperature rises, the temperature difference from the warm water supply temperature is reduced, and the warm water output of the heat pump 2004a eventually matches the heating load H. .

  On the other hand, if the opening degree of the flow control valve 2046 is not equal to or less than the predetermined value (60%) (NO in step S1004), it is further checked whether the opening degree is equal to or greater than a specific value (80%) (step S1004). S1011), if not, return to the beginning of the process (step S1001). If so, assume that the amount of heat of the factory exhaust heat X is insufficient, and set the opening of the flow control valve 2046 to the predetermined value and the specific value. Execute loop 3 to lower to a value (70%) in between.

  In the loop 3, the flow rate in the hot water pump 3006a of the heat pump 2004a is reduced (step S1012), and it is confirmed whether the load of the heat pump 2004a is equal to or greater than a predetermined ratio (50%) with respect to the maximum load (step S1013). If the load of the heat pump 2004a is not equal to or greater than the predetermined ratio, the automatic control device stops one of the heat pumps 2004b and the like that is in operation (step S1014), and proceeds to step S1015. Further, if the load of the heat pump 2004a is equal to or greater than the predetermined ratio, the automatic control device proceeds to step S1015 without executing step S1014.

  In step S1015, the automatic control apparatus monitors whether the warm water return temperature has become equal to or lower than a predetermined value (54 degrees). If the hot water return temperature is equal to or lower than the predetermined value, the loop 4 for raising the hot water return temperature to the predetermined value (55 degrees) is executed. Otherwise, the head of the loop 3 (step S1012) or the head of the process (flow rate control valve) When the opening of 2046 reaches a predetermined value, the process returns to step S1001). In loop 4, if the hot water boiler 2506 is not in the automatic operation mode, the mode is set (step S1016, S1017), and the output of the hot water boiler 2506 is increased (step S1018).

  By executing the loop 3 or the like, the flow rate of the hot water pump 3006a is reduced and the heating amount by the hot water boiler 2506 as another heat source is adjusted to appropriately maintain the temperature difference on the hot water side in the heat pump 2004a, and the cooling load Can respond appropriately.

  For example, when supplying a thermal load of 350 kW, if the heat pump 2004a, which has a temperature difference of 5 degrees at a hot water flow rate of 60.2 tons per hour, reduces the hot water flow rate to 43 tons per hour from a state where 350 kW is covered, the heat pump 2004a In order to lower the temperature to the set value, the temperature is reduced to 250 kW by the inverter, and the warm water return temperature from the heating load H is lowered, but with this, heating of 100 kW by the hot water boiler 2506 is started. While maintaining the difference between the hot water supply and return temperature in the heat pump 2004a at a difference of 5 degrees, it is possible to cope with a thermal load of 350 kW.

  In contrast, if the warm water return temperature is not adjusted by the warm water boiler 2506, for example, even if the flow rate of the warm water is reduced from 60.2 tons per hour to 43 tons per hour, the temperature difference eventually increases to 7 degrees and the heating output becomes 350 kW. Will not change.

  In the heating / cooling device 3001 described above, when the opening degree of the flow control valve 2046 is equal to or greater than a predetermined value, the amount of heat of the factory exhaust heat X is insufficient, and it becomes impossible to balance the cooling heat against the heating load. A part of the heat pump 2004 is stopped, the output of the hot water boiler 2506 is increased, and the opening degree of the flow rate control valve 2046 is equal to or less than a predetermined value (and the hot water boiler 2506 is in operation). When there is a margin and the operation by the heat pump 2004 is possible, the operation of the heat pump 2004 is started sequentially, so that the maximum number of heat pumps 2004 can be operated in a state where the operation can be continued while appropriately responding to the thermal load. In the range that does not affect the operation, improve the operation ratio of the heat pump 2004 to the other heat source as much as possible. Load may be subjected to heating and cooling while high energy saving property fluctuates.

  In the heating / cooling device 3001, other heat sources such as factory waste heat X and hot water boiler 2506 are installed, and the flow rate of the medium to the heat pump 2004 is adjusted by the cold water pump 3002a and the hot water pump 3006a. The medium temperature or medium heat quantity can be controlled.

  Furthermore, in the heating / cooling device 3001, a part of the plurality of heat pumps 2004 is used as a chilled water load adjuster, and the other heat pumps 2004 are additionally activated or stopped in accordance with the load, so that one or more heat pumps 2004 are loaded. Therefore, it is possible to operate in a state where the load is high and the efficiency is good as long as the load does not become excessive, and such an appropriate operation can be easily executed based on a simple index of the load of the cooling load adjusting machine.

[19th form]
FIG. 24 is a flowchart showing the operation of the heating and cooling apparatus according to the nineteenth embodiment. The heating and cooling apparatus is the same as that of the eighteenth embodiment, but the cooling side return pipe 2032 (before branching to the cooling side return pipe 32a).・ Equipped with a cold water tank on the upstream side. Moreover, the cold water chiller which is not shown in figure is connected to the cooling side similarly to the 21st form (refer FIG. 26) mentioned later.

  Such a heating and cooling device operates in the same manner as in the eighteenth embodiment, but instead of the opening degree of the flow rate control valve 2046, the number of heat pumps 2004 can be changed based on the cold water return temperature in the cold water tank or the like, Increase or decrease the output of other heat sources.

  That is, if the cold water return temperature is equal to or higher than the specific value (17 degrees) (YES in step S1021) and the hot water boiler 2506 is in operation (YES in step S1005), the cold water return temperature is set to a predetermined value (15 degrees). Run loop 1 to lower. If hot water boiler 2506 is not in operation (NO in step S1005), the cold water chiller is operated (step S1022).

  If the chilled water return temperature is equal to or lower than the specific value (13 degrees) (YES in step S1023), the loop 3 is used to raise the chilled water return temperature to a predetermined value (15 degrees, which may be different from the predetermined value when lowered). Execute. Before step S1012, it is confirmed whether or not the chilled water chiller is in operation (step S1024). If it is in operation (YES), one chilled water chiller is stopped (step S1025) at the end of loop 3. If it shifts and it is not in operation (NO), Step S1012 is executed.

  In the heating / cooling device according to the nineteenth embodiment as well, as in the heating / cooling device 3001 according to the eighteenth embodiment, the maximum number of heat pumps 2004 can be operated in a state where operation can be continued while appropriately responding to the thermal load. It is possible to improve the operation ratio of the heat pump 2004 to the other heat source as much as possible without affecting the operation, and to perform heating and cooling in a state of high energy saving even if the thermal load fluctuates.

[20th form]
FIG. 25 is a flowchart showing the operation of the heating / cooling device according to the twentieth embodiment. The heating / cooling device is the same as that of the nineteenth embodiment, but the hot water tank connected to the hot water boiler 2506 is connected to the heating side supply pipe. 2034 and the heating side return pipe 2036 (between the junction branching portion and the heat supply amount adjustment valve 2109), the heating side supply pipe 2034 between the hot water tank and the heating load H has the hot water A pump for supplying hot water from the tank to the heating load H (hot heat supply amount adjustment valve 2109) is installed.

  In the heating / cooling device of the twentieth embodiment, one or a plurality of cold water chillers for directly cooling the cold water or cooling the medium for cooling the cold water are installed. The cold water side of the cold water chiller is connected in the same manner as the heat pump 2004. The cooling chiller is connected to a cooling tower that is independent from the hot water circuit of the heat pump 2004 in order to cool the heat generated during cooling, but it may be an air cooling type that does not require a cooling tower. An exhaust heat recovery type heat pump (preliminary machine) may be used as a cold water chiller.

  Such a heating / cooling device operates in the same manner as in the nineteenth embodiment, but the chilled water temperature can be controlled by a chilled water chiller in addition to (increase / decrease) the number of heat pumps 2004.

  That is, if the cold water return temperature is equal to or higher than the specific value (17 degrees) (YES in step S1021) and the hot water boiler 2506 is not in operation (NO in step S1005), the cold water chiller is operated (step S1031). If hot water boiler 2506 is in operation (YES in step S1005), loop 1 is executed to lower the cold water return temperature to a predetermined value (15 degrees). In loop 1, the hot water in the hot water tank is When the temperature is equal to or higher than a predetermined value (60 degrees), loop 2 is executed (step S1032). Also in the loop 3, when the temperature of the hot water tank is equal to or lower than a predetermined value (57 degrees), the loop 4 is executed (step S1033).

  In addition, the process which concerns on the heating / cooling apparatus of a 20th form can be changed as follows. That is, in step S1006, the hot water temperature set value of the heat pump 2004a as the chilled water load adjuster is increased (upper limit can be set, 60 degrees). As a result, the output of the heat pump 2004a and the like automatically increases (inverter output increase) and the chilled water output also increases accordingly, so that the chilled water temperature is maintained while temporarily decreasing. Further, since the temperature of the warm water going to the warm water tank 2508 rises and the temperature of the warm water in the warm water tank 2508 rises, the output of the other heat source (warm water boiler 2506) is reduced to balance the heat load and the heat supply amount. The hot water temperature is maintained at a predetermined temperature (60 degrees) by the heat supply adjustment by another heat source, the hot water return temperature of the heat pump 2004a or the like does not change, and the difference between the hot water return temperature and the hot water return temperature changes. For example, suppose that when the thermal load of 450 kW is provided by the output of 250 kW of the heat pump 2004a and the like that covers a temperature difference of 5 degrees at 43 tons / hour and the output of another heat source covers a thermal load of 450 kW, the hot water flow rate is the same and the temperature difference becomes 7 degrees. The output of the heat pump 2004a etc. is increased to 350 kW, and the output of the other heat source is automatically reduced to 100 kW. In the case where the hot water temperature in the hot water tank 2508 is not controlled without using another heat source, the output of the heat pump 2004a or the like does not change even if the hot water temperature is increased.

  On the other hand, in step S1012, the hot water temperature set value of the heat pump 2004a as the chilled water load adjuster is lowered (lower limit can be set, 55 degrees). As a result, the hot water output of the heat pump 2004a or the like automatically decreases (inverter output decrease), and the chilled water output also decreases accordingly, so the chilled water temperature temporarily rises. Further, since the temperature of returning to the hot water tank 2508 is lowered and the temperature of the hot water in the hot water tank 2508 is lowered, the output of the other heat source (hot water boiler 2506) is increased to cover a temporary shortage of the amount of heat supplied to the heat load. The warm water temperature in the warm water tank 2508 is maintained at a predetermined temperature (60 degrees) by adjusting the warm heat supply by another heat source, the warm water return temperature of the heat pump 2004a or the like does not change, and the difference between the warm water return temperature and the warm water return temperature varies. For example, if the temperature of the hot water flow rate is 43 tons per hour and the temperature difference is 5 degrees with the output 350 kW of the heat pump 2004a, etc., which covers a temperature difference of 350 kW, and the temperature difference is 5 degrees, the output of the heat pump 2004a, etc. Decreases to 250 kW and the output of the other heat source is automatically increased to 100 kW. Note that when the hot water temperature in the hot water tank 2508 is not controlled without using another heat source, the output of the heat pump 2004a and the like does not change even if the hot water flow rate is reduced.

  On the other hand, in step S1006, the hot water temperature setting value of the hot water boiler 2506 as another heat source can be lowered by a predetermined value (1 degree, 62 degrees to 61 degrees) (lower limit can be set, 55 degrees). As a result, the hot water supply temperature temporarily decreases and the hot water return temperature also decreases (57 degrees to 56 degrees). In addition, since the heat pump 2004a and the like control the hot water supply temperature to a set value (60 degrees), the output is automatically increased by decreasing the hot water return temperature (by increasing the temperature difference from 3 degrees to 4 degrees). Further, when the output of the heat pump 2004a or the like is increased in order to respond to the increased heating load, the chilled water output increases accordingly, so that the chilled water temperature is lowered and the chilled water temperature is maintained. For example, suppose that when the thermal load is 350 kW with the output 150 kW of the heat pump 2004a etc. that covers a temperature difference of 3 degrees at 43 tons / hour of hot water flow and the output of 200 kW of other heat sources, the hot water flow rate is the same and the temperature difference becomes 4 degrees. The output of the heat pump 2004a etc. is increased to 200 kW, and the output of other heat sources is automatically reduced to 150 kW.

  On the other hand, in step S1012, the hot water temperature setting value of the hot water boiler 2506 as another heat source can be increased by a predetermined value (1 degree) (lower limit can be set, 55 degrees). Thereby, warm water output of heat pump 2004a etc. falls temporarily, and cold water output also falls. In addition, when the hot water supply temperature to the heating load H rises and the hot water return temperature also rises (55 to 56 degrees), the heat pump 2004a and the like control the hot water supply temperature to the set value (60 degrees). The output is automatically reduced by the increase (because the temperature difference decreases from 5 degrees to 4 degrees). For example, in the case where the output of 350 kW such as the heat pump 2004a that covers a temperature difference of 7 tons at a flow rate of 43 tons per hour is covered, and the temperature difference of the heat source becomes 5 degrees by raising the set temperature of the other heat source, If the output of the heat pump 2004a, etc. is reduced to 250 kW, the output of the other heat source is 100 kW, and if the set temperature of the other heat source is further increased, the flow rate of the hot water becomes the same, but the temperature difference becomes 4 degrees, the output of the heat pump 2004a, etc. The power is reduced to 200 kW, and the output of the other heat source is 150 kW.

  In the heating / cooling device according to the twentieth embodiment as well, as with the heating / cooling device according to the nineteenth embodiment, the maximum number of heat pumps 2004 can be operated in a state in which operation can be continued while appropriately responding to the thermal load. In addition, by providing a chilled water chiller, the temperature of the chilled water can be adjusted before the number of heat pumps 10 is reduced, and the operation ratio of the heat pump 2004 to other heat sources is improved more finely as much as possible without affecting the operation. Even if the load fluctuates, heating and cooling can be performed in a state of high energy saving.

[21st form]
FIG. 26 is a schematic diagram of the heating / cooling device 3051 according to the twenty-first embodiment. The heating / cooling device 3051 is similar to the eighteenth embodiment, but a plurality of cold water chillers 3052a and 3052b similar to the chilled water chiller of the twentieth embodiment are provided. is set up. The cold water chiller 3052a and the like are connected to the cooling tower 2504c and the like through a hot heat transfer pipe 3054a and the hot return pipe 3056a and the like. A pump 3057a and the like are disposed on the warm return pipe 3056a and the like. A single cold water chiller may be used. The heating / cooling device 3051 has a hot water tank 3058 similar to that in the eighteenth embodiment.

  Furthermore, the heat pumps 2004a and 2004b can perform a cold water follow-up operation in which the temperature of the cold water or the cold heat is constant, and the heat pumps 2004a and 2004b are positioned as thermal load regulators. The number of heat pumps 2004 may be one or three or more.

  The automatic control device of the heating / cooling device 3051 controls the heat pumps 2004a, 2004b as the thermal load regulators based on their own cold water supply temperature and hot water supply temperature, for example, and supplies the temperature of the hot water tank 3058 or the heating side supply for the hot water boiler 2506. Control based on the hot water supply temperature of the pipe 2034, the hot water temperature for the hot water supply amount adjustment valve 2109 for adjusting the hot water supply amount to the heating load H or the cold water supply amount adjustment valve 2048 for adjusting the cold water supply amount to the cooling load C Control based on. These temperatures are detected by the respective temperature sensors and grasped by the automatic control device.

  Such a heating / cooling device 3051 operates in the same manner as the eighteenth and twentieth embodiments, for example, as follows.

  That is, as shown in FIG. 27, if the hot water supply temperature of the heat pump 2004 is 58 degrees or less (YES in step S1051), the automatic control device loops 1 to raise the hot water supply temperature to a predetermined temperature (60 degrees). If the hot water supply temperature of the heat pump 2004 is equal to or higher than the specific temperature (62 degrees) and the hot water boiler 2506 is stopped (NO in step S1051, YES in steps S1060 and S1061), the hot water supply temperature is set to a predetermined value. Execute loop 3 to lower the temperature (60 degrees). If NO in step S1061, the output of hot water boiler 506 is reduced (step S1062), and the process returns to the beginning.

  In the loop 1, the automatic control device increases the flow rate of the chilled water pump 3002a of the heat pumps 2004a and 2004b as the thermal load adjuster (step S1052), and if the chilled water supply temperature is equal to or lower than the specific temperature (7 degrees) (in step S1053). YES), the output of the chilled water chillers 3052a and 3052b is decreased to include the chilled water supply temperature at a predetermined temperature (10 degrees) (including reducing the number of units, step S1054), and the loop 2 is executed to execute the hot water supply temperature of the heat pump 2004 Is determined to fall within a predetermined temperature range from the predetermined temperature (60 degrees) (step S1055). On the other hand, if “NO” in the step S1053, the process proceeds to the step S1055 without executing the loop 2.

  If “YES” in the step S1055, the output of the hot water boiler 2506 is reduced (step S1056), and the process returns to the beginning of the loop 1. On the other hand, if “NO” in the step S1055, it is confirmed whether or not the load of the heat pump 2004a is equal to or less than a predetermined value (95% of the maximum load) (step S1057). The output of hot water boiler 2506 is increased (step S1058), and the process returns to the beginning.

  That is, in the loop 1, when the flow rate of the chilled water pump 3002a of the heat pumps 2004a and 2004b as the thermal load regulator is increased, the chilled water supply temperature of the heat pumps 2004a and 2004b temporarily rises, and the chilled water supply temperature of the heat pumps 2004a and 2004b is increased. The heat pumps 2004a and 2004b automatically increase the output so as to reach a predetermined temperature (10 degrees) (inverter output increase). If the cold water output of the heat pumps 2004a and 2004b increases, the hot water output also increases, so the hot water temperature is maintained at a predetermined value.

  On the other hand, in the loop 3, the automatic control device reduces the flow rate of the chilled water pump 3002a of the heat pumps 2004a and 2004b (step S1063), and determines whether or not the chilled water supply temperature is equal to or higher than the specific temperature (13 degrees) (step S1064). . If YES, the loop 4 for lowering the cold water supply temperature to a predetermined temperature (10 degrees) is executed, and if NO, the loop 4 is not executed and the process returns to the beginning of the loop 3. In the loop 4, the output of the chilled water chillers 3052a and 3052b is increased or the number is increased (step S1065).

  That is, in the loop 3, when the flow rate of the chilled water pump 3002a of the heat pumps 2004a and 2004b as the thermal load adjuster is decreased, the chilled water supply temperature of the heat pump 2004a is temporarily lowered, and the chilled water supply temperature of the heat pumps 2004a and 2004b is set to a predetermined temperature ( 10 degrees), the heat pumps 2004a and 2004b automatically reduce the output (decrease in inverter output). If the chilled water output of the heat pumps 2004a and 2004b decreases, the hot water output also decreases, so the chilled water chillers 3052a and 3052b compensate for the lack of cold heat.

  In addition, the process in the heating / cooling device 3051 can be changed as follows. That is, in step S1052, the cold water temperature set value of the heat pump 2004a, which is a hot water load adjuster, is lowered. As a result, the output of the heat pump 2004a or the like automatically increases (inverter output increase), and the hot water output also increases accordingly, so the hot water temperature rises and the hot water temperature is maintained. Further, since the chilled water going temperature is lowered and the chilled water return temperature is temporarily lowered, the output of the chilled water chiller is reduced (step S1054) and balanced with the cooling load. On the other hand, in step S1063, the cold water temperature set value of the heat pump 2004a or the like that is a hot water load adjuster is increased. As a result, the output of the heat pump 2004a and the like is automatically throttled (inverter output decreased), and the hot water output is also reduced, so that the amount of supplied hot heat is reduced and the hot water temperature is lowered. Further, since the chilled water going-up temperature rises and the chilled water return temperature rises temporarily, the output of the chilled water chiller is increased (step S1065) to balance with the cooling load C.

  In step S1052, the cold water return pipe 2032a such as the heat pump 2004a which is a hot water load adjuster is heated by the factory exhaust heat X. As a result, the output of the heat pump 2004a or the like automatically increases (inverter output increase), and the hot water output also increases accordingly, so that the hot water temperature rises and the hot water temperature is maintained (cooling load amount adjusting means). Although the chilled water load such as the heat pump 2004a changes, the chilled water supply amount (chilled water temperature) to the cooling load C does not change, so the output of the chilled water chiller does not change (No in step S1053). On the other hand, in step S1063, the amount of heat exchange with the exhaust heat is reduced in the situation where the cold water return pipe 2032a such as the heat pump 2004a that is the hot water load adjuster is heated by the factory exhaust heat X. As a result, the output of the heat pump 2004a or the like is automatically throttled (inverter output decreased), and the hot water output also decreases accordingly, so the amount of supplied hot heat decreases and the hot water temperature decreases (cooling load amount adjusting means). Although the chilled water load of the heat pump 2004a or the like changes, the chilled water supply amount (chilled water temperature) to the cooling load C does not change, so the output of the chilled water chiller also does not change (No in step S1064).

  The heating and cooling apparatus 3051 described above includes the heat pump 2004 that performs the cold water tracking operation and the cold water chillers 3052a and 3052b, and therefore performs the cold water tracking operation while appropriately responding to the thermal load in the heating and cooling that has the cold load throughout the year. Therefore, heating and cooling can be performed in a state of extremely high energy saving.

  In the heating / cooling apparatus 3051, the medium flow rate to the heat pump 2004 is adjusted by the chilled water pump 3002a or the like, so that the medium temperature or the medium heat amount can be controlled by adjusting the flow rate.

  Furthermore, in the heating / cooling device 3051, the plurality of heat pumps 2004 are used as a thermal load adjuster, and the hot water boiler 2506 and the like are started and stopped according to the load, and thus the hot water boiler 2506 and the like are operated in an efficient state. In addition, such an appropriate operation can be easily executed based on a simple index of the load of the cold load regulator.

[22nd form]
FIG. 28 is a schematic diagram of the heating / cooling device 3101 according to the twenty-second embodiment, and the heating / cooling device 3101 is the same as the first embodiment, but is arranged in the singular or plural on the cooling side like the chilled water chiller of the twenty-first embodiment. The air-cooled heat pump 3102 is provided. In the air cooling heat pump 3102, heating operation or cooling operation is possible. On the cooling side, a cold water tank 3104 connected to the pipes 16 and 26 is installed.

  Pipes 3116 and 3126 for the cooling load C are further connected to the cold water tank 3104, a pump 3152 is interposed in the pipe 3116, and a heat exchanger 3130 is interposed in the pipe 3126. A medium supply pipe 3160 for supplying a medium to the heat exchanger 3130 and a medium return pipe 3162 for receiving the medium from the heat exchanger 3130 are connected to the air cooling heat pump 3102. A second heat exchanger 3164 is interposed in the medium supply pipe 3160, and a pump 3166 is interposed in the medium return pipe 3162. In the second heat exchanger 3164, another auxiliary heat source (here, steam) HH as the other heat source Z is introduced through the auxiliary flow rate adjusting valve 3180.

  The heat exchanger 3130 may be installed in the pipe 26 or the cold water tank 3104. Alternatively, the air cooling heat pump 3102 and the tank 3104 may be connected to each other via a dedicated pump, and the air cooling heat pump 3102 may directly exchange heat. Further, the air cooling heat pump 3102 may be directly connected to the pipe 3126 to control the return temperature of the medium at the time of mode switching. In addition, the other auxiliary heat source HH can be a cooler or a coolable / warmable machine.

  The heating / cooling device 3101 according to the twenty-second embodiment operates as follows, for example, in order to smoothly perform switching of heating or cooling operation.

  That is, as shown in FIG. 28 (a), when the heating load H (350 kW) is heavier than the cooling load C (170 kW), the heat pump 10 supplies hot water corresponding to the heating load H, and is additionally generated. Supplied cold water (220 kW). In order to balance the cold water with respect to the hot water, the air-cooled heat pump 3102 is heated to supply a medium (from 30 degrees to 35 degrees) to the heat exchanger 3130 for warm water heating (50 kW). The chilled water temperature (the chilled water temperature in the pipes 16 and 3116) is 20 degrees, the chilled water temperature in the pipe 3126 immediately after returning from the cooling load C is 24 degrees, and the chilled water temperature after passing through the heat exchanger 3130 The cold water return temperature to the heat pump 10 is 25 degrees, and the operation of the heat pump 10 is continued.

  On the other hand, when the thermal load is reduced (becomes 254 kW) and the balance of cooling / heating is not balanced, the automatic control device detects that the chilled water going temperature has reached a predetermined value (22 degrees) or more. This case is grasped, and the air cooling heat pump 3102 is temporarily stopped for operation switching, while the pump 3166 of the medium return pipe 3162 is continuously operated. Switching between the heating mode and the cooling mode in the air-cooling heat pump 3102 is not immediately executable, and needs to be restarted in a different mode after being stopped (device interlock) for a predetermined time (3 minutes). Due to the continuous operation of the pump 3166, heat exchange in the heat exchanger 3130 between the medium and cold water is continued, and the heated medium is cooled with cold water (medium 35 to 28 degrees, cold water return temperature 26 degrees). By cooling the medium when switching the operation, it is possible to more smoothly switch from the heating mode to the cooling mode as compared with the case where the medium is not cooled, so that the cooling operation can be started smoothly.

  That is, in order for the air-cooled heat pump 3102 to start operation in the cooling mode, the chilled water outlet temperature must be, for example, 20 degrees or less in order to establish the heat pump cycle, and if the medium is 35 degrees, first, for example, up to 30 degrees The temperature must be lowered from 30 degrees to 20 degrees in the mode for switching the operation of the air-cooled heat pump 3102 (warming operation) (approximately 30 minutes are required). , Without relying on an external cooler, it can be quickly lowered to 30 degrees by heat exchange between the medium and chilled water, and it is not necessary to shift to warming operation. It can be shortened. If the medium is cooled by using another auxiliary heat source that can be cooled, switching can be performed more quickly.

  Then, as shown in FIG. 28C, when the cooling load (170 kW) is heavy with respect to the heating load (250 kW), the air-cooling heat pump 3102 performs cooling operation and supplies the medium 13 kW cooled to 18 degrees. On the other hand, the heat pump 10 supplies 20 degrees of cold water 157 kW to the cold water tank 3104, and the cold water tank 3104 supplies 20 degrees of cold water to the cooling load C via the pump 3152 according to the cooling load C. The cold water of 24 degrees returned from the cooling load C becomes 23.6 degrees due to the medium (cold heat 13 kW) from the air-cooled heat pump 3102, and returns to the heat pump 10 through the cold water tank 3104. Thus, the cold load 170 kW is covered by cold water (157 kW) and cooling by the medium (13 kW). On the other hand, the heat pump 10 supplies the thermal heat 250 kW corresponding to the cooling load C (157 kW) related to the cold water supply, and corresponds to the thermal load.

  In addition, when the thermal load is relatively increased from the case of FIG. 28B or when switching from cooling to heating, the operation just opposite to the switching from heating to cooling is performed. That is, when the air-cooled heat pump 3102 is switched from the cooling operation to the heating operation in order to prevent the operation stop due to the chilled water temperature drop of the heat pump 10, it takes time to restart due to the device interlock, and the medium temperature is equal to or lower than the predetermined temperature (25 degrees). In order to establish the heat pump cycle, it is necessary to operate in the warming mode before switching the heating mode to 25 degrees (approximately 30 minutes is required). However, in the heating and cooling device 3101, the heat of the medium and the cold water First, it can be quickly raised to about 20 degrees by replacement, and the temperature can be raised from 20 degrees to 25 degrees by heating the medium using another auxiliary heat source HH, so that the operation in the warming mode can be omitted. The time required for this can be greatly reduced. The medium can be heated to 25 degrees only by heating the other auxiliary heat source HH, and the cold water of the heat pump 10 is heated by the other auxiliary heat source HH during the mode switching of the air cooling heat pump 3102 (about 3 minutes). By doing so, it is possible to prevent the heat pump 10 from stopping.

  In the heating and cooling device 3101 described above, the medium of the air-cooled heat pump 3102 is circulated even during the operation switching of the air-cooled heat pump 3102 on the cooling side of the heat pump 10, so that the medium is cooled by the cold water of the heat pump 10 at the time of cooling switching and at the time of heating switching. The medium temperature can be positively adjusted to a state suitable for the mode after switching as compared with the case where the temperature is not changed because the medium is not heated by the cold water, and the operation of the air-cooled heat pump 3102 is switched. And operation after switching can be made extremely smooth.

  In the heating / cooling device 3101, the medium is heated (cooled) at the time of heating (cooling) switching by the other auxiliary heat source HH, so that the operation switching can be further quickly performed.

[23rd form]
A heating / cooling device 3251 according to the twenty-third embodiment shown in FIG. 29 is the same as that of the first embodiment, but includes a hot water tank 3058 and a cold water tank 3104 and another heat source Z (steam, electric heater, etc.) in the hot water tank 3058. In addition, an air-cooled heat pump 2154 (cooling tower, cooling device using well water, exhaust heat, heated air-cooled heat pump, or the like) may be connected to the cold water tank 3104. Moreover, between the heat pump 10 and the hot water tank 3058, the cooling tower 404 and the three-way valve 410 are arrange | positioned similarly to the 7th form. The heating / cooling device 3251 operates in the same manner as in the first embodiment, and also operates as shown in FIG. 30, for example.

  That is, the heat pump 10 is operated to supply cold water at the cold water supply temperature set value (12 degrees) in the cold water follow-up mode, and is operated with priority over the air-cooled heat pump 2154. The heat pump 10 is operated so as to supply hot water at the hot water supply temperature set value (60 degrees) in the hot water follow-up mode, and is operated with priority over the introduction of the other heat source Z. On the other hand, the air-cooled heat pump 2154 supplies cold water having a first specified temperature (15 degrees, a value higher than the heat pump 10 cold water supply temperature set value) to the cold water tank 3104, and the other heat source Z has the hot water tank 3058 at the second specified temperature (50 degrees). , Heat pump 10 is supplied when the temperature is lower than the warm water supply temperature set value). Hot water returns to the heat pump 10 at 55 degrees, for example, and cold water returns to the heat pump 10 and the air-cooled heat pump 2154 at 17 degrees, for example.

  Then, the automatic control device first activates the heat pump 10 in the hot water follow-up mode (or cold water follow-up mode) (step S1301), and only when the monitored cold water supply temperature is lower than the first predetermined temperature (10 degrees). (YES in step S1302), the operation mode of the heat pump 10 is changed to the cold water follow-up mode (step S1303). Further, the automatic control device changes from the cold water tracking mode to the hot water tracking mode for the heat pump 10 only when the monitored hot water supply temperature exceeds the specific temperature (62 degrees) (YES in step S1304) (step S1305). Note that the automatic control apparatus repeats the processing from step S1302 (NO in step S1306) unless there is a stop command for the heat pump 10 by pressing the stop push button (stop PB) or the like (YES in step S1306). ), The heat pump 10 is stopped (step S1307).

  In step S1302, the mode may be switched when the state where the cold water supply temperature is lower than the predetermined temperature continues for a predetermined time (ascertained by a timer connected to the automatic control device). Further, step S1304 can be similarly changed. In addition, instead of monitoring the cold water supply temperature, the cold water return temperature, the temperature of the cold water tank 3104, or a combination thereof may be monitored, and the hot water temperature can be similarly changed.

  Furthermore, if the result of the determination in step S1302 is NO, the automatic control device checks whether the chilled water supply temperature is lower than the second predetermined temperature (15 degrees) (step S1308), and if it is lower than the second predetermined temperature (YES), step S1304. If it is not less than the second predetermined temperature (NO), the hot water follow-up mode is switched to the cold water follow-up mode (step S1309).

  Subsequently, the automatic control device checks whether the cold water supply temperature exceeds the second predetermined temperature (15 degrees) (step S1310), and stops the hot water supply by the heat pump 10 only when the temperature exceeds the second predetermined temperature (YES). At the same time (step S1311), the warm water temperature set value of the cooling tower 404 is changed from the first warm water cooling set temperature (65 degrees) to the second warm water cooling set temperature (32 degrees) (step S1312). The process is repeated unless the stop PB is turned on (step S1313).

  In such a heating / cooling device 3251 of the twenty-third form, when the supply cold heat becomes excessive with respect to the cooling load C due to switching of the operation mode of the heat pump 10 or the other heat source Z / other heat source (air-cooled heat pump 2154), Appropriately corresponds to the cooling load C as the follow-up mode, and corresponds to the heating load H with hot water and another heat source Z, and appropriately corresponds to the heating load H as the hot-water follow-up mode when supply heat is excessive with respect to the heating load H In addition, the cooling load C is handled by cold water and other cold heat sources. Therefore, it is possible to continue the operation of the heat pump 10 with a very good energy saving performance.

[24th form]
The heating / cooling device 3301 according to the twenty-fourth embodiment shown in FIG. 31 is the same as the first embodiment except for the circuit relating to the heat exchanger 30. In the heating / cooling device 3301, the pipe 32 to the heat exchanger 30 serves as a supply pipe for a cooling tower 3302 as a cooler for exhaust heat, and the pipe 34 from the heat exchanger 30 requires cooling of a compressor or the like belonging to the factory. It is a pipe to the cooling required equipment 3304 as the cooling required equipment. A pipe 3306 for guiding the medium from the former to the latter is passed between the cooling required apparatus 3304 and the cooling tower 3302, and the medium flow rate adjusting valve 3308 as medium heat amount adjusting means (equipment cooling water temperature adjusting means) is passed to the pipe 3306. And the branch side of the medium flow rate adjustment valve 3308 is connected to the pipe 32. A plurality of cooling towers 3302 may be installed, or a cooling device using a refrigerator, an air cooling heat pump, or well water may be installed instead of or together with the cooling tower 3302. Further, the cooling required equipment 3304 may be replaced with air conditioning equipment that is cooling equipment or equipment that requires temperature adjustment (such as a molding machine or a stock solution such as urethane).

  The heating / cooling device 3301 operates in the same manner as in the first embodiment, for example, as follows.

  That is, when the chilled water temperature is relatively low (the amount of chilled water is large), the heat pump 10 follows the warm water, supplies 7 degrees of chilled water to the cooling load C, and 10 degrees of chilled water is discharged from the cooling load C. . A coolant having a predetermined temperature (15 degrees) is supplied from the cooling tower 3302 to the heat exchanger 30, and the cold water temperature is raised to 12 degrees by heat exchange. The temperature of the medium after the heat exchange is lowered to 13 degrees, introduced as cooling water into the cooling required equipment 3304, heated to 31 degrees by heat exchange during cooling, and introduced into the cooling tower 3302 as appropriate. The coolant (medium) is adjusted by the medium flow rate adjustment valve 3308 so as to reach a predetermined temperature in the pipe 32.

  On the other hand, when the temperature of the chilled water is relatively high (the amount of chilled water is small), the heat pump 10 follows the warm water, supplies 18 degrees of chilled water to the cooling load C, and 21 degrees of chilled water is discharged from the cooling load C. . A coolant having a predetermined temperature is supplied from the cooling tower 3302 to the heat exchanger 30, and the cold water temperature is lowered to 19 degrees by heat exchange. The temperature of the medium after the heat exchange rises to 17 degrees, is introduced as cooling water into the required cooling equipment 3304, is heated to 25 degrees by heat exchange during cooling, and is appropriately introduced into the cooling tower 3302. The coolant (medium) is adjusted by the medium flow rate adjustment valve 3308 so as to reach a predetermined temperature in the pipe 32.

  In the heating / cooling device 3301, the cooling water (medium) before cooling of the cooling side of the heat pump 10 and the required cooling equipment 3304 belonging to the factory is adjusted by the medium flow rate adjustment valve 3308 (or the cooling tower 3302) so as to reach a predetermined temperature. If the cold water is colder than the medium at the predetermined temperature, the cold water can be heated by heat exchange. If the cold water is warmer than the medium at the predetermined temperature, the cold water can be cooled by heat exchange. It is not necessary to monitor the chilled water return temperature of the heat pump 10 or the like, and it is not necessary to provide a control valve on the chilled water side of the heat pump 10, and it is effective for insufficient cooling and overcooling with a simple configuration or operation. Therefore, it is possible to naturally stabilize the cold water temperature of the heat pump 10.

  Note that the twenty-fourth embodiment may be modified as follows. That is, only the air cooling heat pump is connected to the heat exchanger 30 so that the cooling side heating medium is supplied from the air cooling heat pump. The air-cooled heat pump is operated so as to maintain the cooling side heating medium at a predetermined temperature (20 degrees) (a heating operation is performed if the temperature is lower than the predetermined temperature, and a cooling operation is performed if the temperature is equal to or higher than the predetermined temperature). Therefore, the cold water of the heat pump 10 is brought close to a predetermined temperature by heat exchange with the cooling side heating medium, that is, the cold water is heated by the cooling side heating medium (cooling side medium) if the temperature falls below the predetermined temperature, and on the cooling side if the temperature exceeds the predetermined temperature. It is cooled by the heating medium (cooling side medium), and it is possible to continue the operation of the heat pump, which is energy-saving, without performing complicated control only by the automatic operation that keeps the medium of the air-cooled heat pump at a predetermined temperature. In combination with the twenty-second embodiment, more stable temperature control can be performed.

[25th form]
The heating / cooling device 3351 according to the twenty-fifth embodiment shown in FIG. 32 is the same as the first embodiment except for the circuit according to the heat exchanger 30. In the heating / cooling device 3351, the pipe 32 to the heat exchanger 30 extends from the washing tank 3356 and includes a pump 3352, and the pipe 34 to the heat exchanger 30 reaches the washing tank 3356 for washing the workpiece W with warm water. . The cooling side of the heat pump 10 is heated via the heat exchanger 30 by a medium that collects exhaust heat from the washing tank 3356 and distributes it through the pipes 32 and 34. Even in the heating / cooling device 3351, as in the first embodiment, it is possible to continue the operation of the heat pump 10 with extremely high energy saving performance. Note that the heat exchanger 30 may be attached after the shower pump in the washing tank 3356. Further, not only in the hot water follow-up mode but also in the cold water follow-up mode, the exhaust heat of the cleaning tank 3356 can be effectively used for heating the heating load H.

  Further, the twenty-fifth embodiment can be changed as follows. That is, a heat exchanger is provided in any one of the pipes 12 and 22, and a cooling tower is connected to the heat exchanger, and a circuit for dissipating the heated hot water is installed. Then, when the heat pump 10 is operated in the cold water follow-up mode and the hot water generated at the same time has a shortage of heat and the other heat source Z is introduced (in winter, etc.), the heat exchange amount with the cold water by the heat exchanger 30 is increased. As a result, the cooling load C is increased, and the heating supply amount is increased accordingly, so that the usage amount of the other heat source Z used to cope with the heating load H is reduced and the energy used is saved. In addition, a cold water tank can be interposed. Furthermore, the heat exchange with the cold water in the heat exchanger 30 may be performed by heat belonging to the factory, instead of using the exhaust heat of the heating load H, or together with the exhaust heat. Further, the pump connected to the pipe 32 is provided on the condition that the heating by the heat pump 10 is excessive and the heat radiation from the cooling tower is radiated or the temperature of the hot water exceeds a set value (for example, 65 degrees). 3352 is stopped or the flow rate is adjusted by inverter control (cooling side heating medium heat amount adjusting means using the flow rate adjusting means) to adjust the amount of heat of the cooling side heating medium or the amount of heat exchange with the cold water. Adjust the cooling load C. In addition, when the return temperature of the cold water (pipe 26) or the going-out temperature (pipe 16) rises and exceeds a set value (for example, 22 degrees), the pump 3352 is stopped or the flow rate is adjusted by inverter control. Good. Further, the adjustment of the heat exchange amount with the heating load H and the factory exhaust heat may be performed by a flow rate control valve instead of or together with the inverter-controlled pump.

[26th form]
A heating / cooling device 3401 according to the twenty-sixth embodiment shown in FIG. 33 is the same as the twenty-third embodiment, but is connected to the chilled water tank 3104 via a factory exhaust heat source and a heat exchanger so as to exchange factory exhaust heat X. , 3404 are connected, a pump 3406 is interposed in a pipe 3402 to a factory exhaust heat source, a cooling tower 3302 (other cooling heat source) is installed in place of the air cooling heat pump, and a cooling tower 3302 and a cold water tank 3104 A pipe 3408 and a flow rate adjusting valve 3410 as a cooling heat amount adjusting unit are interposed in the intermediate pipe 34.

  The heating / cooling device 3401 operates as follows, for example. That is, the heat pump 10 is operated in the chilled water follow-up mode, and by creating a condition for supplying 350 kW of (excessive) chilled water exceeding the cooling load 200 kW, hot water 500 kW is supplied from the heat pump 10 and corresponds to the heating load 600 kW. . The heating load of 100 kW that cannot be covered with hot water is adjusted by supplying another heat source Z (100 kW), which is another heat source.

  In order to supply 350 kW of chilled water by the automatic control device, the pump 3406 is operated at the maximum flow rate, and maximum heat exchange is performed with the factory exhaust heat X (chilled water heating is 300 kW, the temperature is raised from 17 ° C. to 20 ° C.) . If it remains as it is, the heat of 150 kW is excessive due to the response to the cooling load C and the heat exchange with the factory waste heat X, and the chilled water temperature continues to rise, so the chilled water is cooled by the cooling tower 3302 (cooling 150 kW, chilled water Temperature drop from 17 degrees to 15 degrees). The automatic control device controls the cooling tower 3302, the pump 3408, and the flow rate adjustment valve 3410 so that the temperature of the chilled water in the chilled water tank 3104 becomes a predetermined temperature (17 degrees) (so that the amount of chilled water becomes a predetermined amount). To do. The amount of heat of the medium related to the factory exhaust heat X (the amount of heat exchange with the factory exhaust heat X) may be adjusted by inverter control of the pump 3406 or a flow rate adjusting valve installed instead.

  And an automatic control apparatus respond | corresponds as follows to the factory waste heat X from which calorie | heat amount fluctuates. That is, if the factory exhaust heat X increases, the cooling amount in the cooling tower 3302 increases accordingly. On the other hand, if the factory exhaust heat X decreases, the cooling amount in the cooling tower 3302 is reduced accordingly. Similarly, the cooling load C can be dealt with.

  The heating / cooling device 3401 includes a heat exchanger that heats the cold water by introducing the cold water of the heat pump 10 and the factory exhaust heat X and exchanging heat, and the heat pump 10 has a cooling medium that has a cooling heat amount that exceeds the amount of the cooling load C. The cooling medium follow-up operation is performed in a state where the gas is supplied. The excess amount of cold heat is applied to the factory waste heat X, and when the factory waste heat X is large and the cooling by the cold water is insufficient, it is adjusted by the cooling tower 3302 which is another cooling heat source for assisting the cooling by the cooling medium. In addition, the other heat source Z respond | corresponds to the fluctuation | variation of a heating load.

  Therefore, heating or cooling by the heat pump 10 is continuously provided in a simple configuration at a low initial cost (cost for connecting the existing heating device / cooling device with the heat pump 10 and providing a circuit for the factory exhaust heat X) and running cost. In addition, it is possible to provide a heating / cooling device 3401 excellent in energy saving by simply performing heat recovery of the factory exhaust heat X. Note that a cooling device using well water may be used instead of or together with the cooling tower 3302.

[27th form]
The heating / cooling device 3501 according to the 27th embodiment shown in FIG. 34 is the same as the 1st embodiment, but on the heating side, the warm water temperature (warm water return temperature, warm water supply temperature, warm water tank temperature at the time of warm water tank installation, etc.) is set. It is different in that a hot water temperature sensor (not shown) to be measured is provided, and a cooling tower 404 and a heat exchanger 3502 for exchanging heat between the cooling water and the hot water of the heat pump 10 are provided.

  The heat pump 10 is operated in the cold water follow-up mode. For example, in order to supply 800 kW of hot water commensurate with the heating load H, in addition to the cooling load C 300 kW, the heat exchanger 30 heats the cold water with 300 kW of the factory exhaust heat X (35 degrees) (electric input 200 kW). The automatic control device adjusts the opening of the cooling-side flow rate adjustment valve 36 (the amount of heat of the factory exhaust heat X introduced into the heat exchanger 30) so that the hot water supply temperature becomes 70 degrees. The cold water supply temperature of the heat pump 10 is 10 degrees here, and the cooling load C comes out at 15 degrees, but passes through the heat exchanger 30 and is heated to 20 degrees.

  Then, when the hot water temperature (monitored by the hot water temperature sensor) rises to 72 degrees, the automatic control device throttles the opening of the flow control valve 36 (decreases the warming amount of the cold water by the factory exhaust heat X). The cold water return temperature is lowered, and the output of the heat pump 10 is reduced so that the hot water temperature is lowered to a set value (70 degrees). On the other hand, when the hot water temperature falls to 68 degrees, the opening degree of the flow control valve 36 is increased (the amount of warm water heated by the factory exhaust heat X is increased) to raise the cold water return temperature, and the output of the heat pump 10 is increased. The hot water temperature is raised to the set value (70 degrees).

  In the heating / cooling device 3501, since the heat pump 10 is operated in the cold water follow-up mode, the cold water supply temperature is controlled in the heat pump 10. Therefore, the emergency stop of the heat pump 10 due to the cold water temperature drop is rare. Further, if the hot water temperature rises too much, the heat pump 10 stops urgently, but in order to prevent such an operation stop, the automatic control device controls the cooling tower 404 to suppress an excessive rise in the hot water temperature.

  It should be noted that the flow rate adjustment by a pump (inverter control) may be performed instead of or together with the heat amount adjustment by the flow rate adjustment valve 36. Further, a cold water tank may be provided on the cold water side, and heat exchange between the cold water in the cold water tank and the factory exhaust heat X may be performed. Further, the amount of heat exchange with the factory exhaust heat X may be adjusted so that the heating load H is set to a predetermined temperature without controlling the hot water temperature (for example, the warm air in the drying furnace is set to 60 degrees). In this case, the supply amount adjusting means for the heating load H of the hot water can be omitted.

[Twenty-eighth form]
The heating / cooling device 3601 according to the twenty-eighth embodiment shown in FIG. 35 is the same as the seventh embodiment, but differs in that a double-band specification exhaust heat recovery heat pump 3610 is used instead of the heat pump 10. That is, the heat pump 3610 includes two hot water circuits.

  One side of the hot water circuit is connected to the hot water tank 402. The circuit is provided with a three-way valve 3612 and a hot water pump 3613. The other of the hot water circuits (which is also a cooling water circuit) is connected to a cooling tower 404 as a cooling water cooler. The circuit is provided with a three-way valve 3614 and a cooling water pump 3616.

  As an operation, in the hot water follow-up mode, as shown in FIG. 35A, the heat pump 3610 supplies hot water of 65 degrees to the hot water tank 402 and maintains the hot water temperature in the hot water tank 402 at 60 degrees. Hot water from the hot water tank 402 returns to the heat pump 3610 by driving the hot water pump 3613. On the other hand, the cold water temperature in the cold water tank 406 is controlled to 17 degrees by the cold water supply by the heat pump 3610 and the operation of the air cooling heat pump 408. The other heat source Z is basically not used, and the flow rate adjustment valve 48 is closed. Further, hot water is not supplied to the cooling water circuit on the cooling tower 404 side.

  On the other hand, when hot water is supplied in the cold water follow-up mode, as shown in FIG. 35 (b), hot water is supplied as cooling water to the cooling water circuit on the cooling tower 404 side by driving the cooling water pump 3616. The hot water temperature is controlled to a predetermined value (65 degrees) by a three-way valve 3614 (hot water temperature adjusting means, hot water calorie adjusting means). The cold water tank 406 is supplied with 10 degrees of cold water, and the air-cooling heat pump 408 controls the temperature of the cold water in the cold water tank 406 to 17 degrees. In addition, 65 degree warm water is sent to the warm water tank 402.

  On the other hand, when there is no supply of hot water in the cold water follow-up mode, as shown in FIG. 35 (c), the hot water (32 degrees) is heated in the hot water circuit on the hot water tank 402 side by the three-way valve 3612 so that the hot water tank 402 is disconnected. It is switched to the bypass side so as to return to the heat pump 3610 without reaching the tank 402, the hot water pump 3613 related to the heat pump 3610 is stopped, and the hot water temperature in the hot water tank 402 is maintained at 60 degrees by the other heat source Z. . The hot water temperature (cooling water temperature) in the hot water circuit (cooling water circuit) on the cooling tower 404 side is also set to 32 degrees on the heat pump 3610 side by the three-way valve 3614. When the hot water temperature is changed from 65 degrees to 32 degrees, the temperature change rate is set to be within a limit value (for example, a decrease of 1 degree per minute) allowed by the heat pump 3610.

  Switching control and the like in these cases are performed as shown in FIG. That is, the automatic control device determines whether or not the heat pump 3610 is operating in the hot water follow-up mode (step S1401). If not (No), the automatic control device is further controlling the hot water temperature to 65 degrees. (Yes in step S1402), it is determined that the hot water temperature is controlled by the cooling tower 404 in the chilled water follow-up mode, and the process proceeds to step S1409, which will be described later. If not (No), the cooling mode is set and the process is terminated.

  On the other hand, if it is determined in step S1401 that the hot water follow-up operation is being performed (Yes), it is determined whether the heat is insufficient (here, the temperature of the cold water is 20 degrees or more) (step S1403). If the heat is not insufficient (No), it is further confirmed whether there is a permission input for switching the chilled water follow-up mode (in this case, the switch button is pressed) (step S1404). If there is an input (Yes), it is determined that the heat is insufficient. If it is (Yes in step S1403), the process proceeds to the next step S1405. If there is no input (No in step S1404), the process returns to the beginning (step S1401).

  In step S1405, the cooling water pump 3616 of the cooling water circuit on the cooling tower 404 side and the cooling tower 404 are operated. Further, the automatic control device (three-way valve 3614) starts control to set the hot water temperature to 65 degrees (step S1406). Since the hot water temperature is the same as the cooling water temperature, the three-way valve 3614 has a hot water temperature of 65 degrees if the cooling water temperature is controlled to 65 degrees. In addition, for the heat pump 3610, the hot water follow mode is switched to the cold water follow mode (step S1407, from FIG. 35 (a) to FIG. 35 (b)). When the mode is switched, the output is stabilized for a predetermined time (1 minute) (loop 1, step S1408).

  In step S1409, it is determined whether or not the output of the heat pump 3610 is greater than or equal to a set value (90%), and the process does not proceed to the next step S1410 (loop 2) unless it is Yes. In other words, it is determined whether there is a shortage of cold water.

  If it is predicted that the cold water will be further short, in step S1410 (loop 2), the hot water tank 402 is switched to be disconnected in the hot water circuit (from FIG. 35 (b) to FIG. 35 (c)). The water tank is heated by the steam. Thereafter, loop 3 (step S1411) is executed, and the control of the three-way valve 3614 is performed so that the hot water temperature is changed from 65 degrees to 32 degrees. That is, if the cooling water is controlled to 32 degrees with the three-way valve 3614, the hot water temperature becomes 32 degrees. As a result, the amount of heat supplied by the cold water is further increased, and a shortage of cold water can be prevented.

  In this way, the temperature of the hot water related to the three-way valve 3614 is changed to 32 degrees. Thereafter, the hot water pump 3613 is stopped (step S1413).

  In the heating / cooling device 3601 according to the twenty-eighth aspect, since the double-band specification exhaust heat recovery heat pump 3610 is used, the operation mode of the heat pump 3610 can be switched smoothly, and a lack of cold water supply can be prevented. Also, in the heating / cooling device 3601, when there is a further lack of chilled water supply in the chilled water follow-up mode, the hot water tank 402 is disconnected, or the hot water temperature is (gradually) lowered to a specific value, so that the cooling load C can be changed. While possible, it is possible to drive efficiently.

[29th form]
The heating / cooling device 3701 according to the 29th embodiment shown in FIG. 37 is the same as the 28th embodiment, but the three-way valves 3612 and 3614 are omitted. The operation is the same as that in the twenty-eighth embodiment, and the following description will be mainly based on FIG.

  When the heat pump 3610 is switched to the chilled water follow-up mode, the automatic control device monitors the amount of chilled heat (chilled water temperature) and determines that it exceeds a predetermined value (the chilled water temperature becomes 20 degrees or higher) (Yes in step S1451). ), The following loop 4 is executed. Note that the automatic control device does not execute the loop 4 when the specific time (3 minutes) has not elapsed after the cold water follow-up mode operation (No in step S1451).

  In the loop 4, in order to make the cooling water pump 3616 have a rated output in the loop 4, the automatic control device first controls the cooling water pump 3616 with an inverter and gradually increases the flow rate (step S1452). Next, it is confirmed whether the hot water temperature in the hot water tank 402 is equal to or higher than the hot water supply temperature of the heat pump 3610 (step S1453). If yes (Yes), the operation of the hot water pump 3613 is stopped. That is, all the heat of the heat pump 3610 is radiated by the cooling water pump and the cooling tower 404. The hot water tank 402 may be omitted, and the hot water of the heat pump 3610 may be directly exchanged with the heating load H.

  In the heating / cooling device 3701 according to the twenty-ninth embodiment, when the hot water temperature in the hot water tank 402 is equal to or higher than the hot water supply temperature of the heat pump 3610, the hot water pump 3613 is stopped, so that the hot water tank 402 is easily disconnected in the cold water follow-up mode. The heating and cooling can be performed in an extremely energy-saving state while appropriately responding to each load.

  The double-band specification exhaust heat recovery type heat pump according to the 28th and 29th embodiments can be used instead of or in combination with the heat pump (single-band specification) in the other embodiments described above. In particular, in the seventh embodiment, the twenty-third embodiment, and the twenty-seventh embodiment, by connecting the cooling tower 404 to the second hot water circuit (cooling water circuit) side (while omitting the three-way valve 410), the same effects as in this embodiment are obtained. Can be played.

[30th form]
The heating / cooling device according to the thirtieth embodiment is the same as the twenty-eighth embodiment, and the operation is slightly different. Hereinafter, an example of the operation will be described mainly based on FIGS. 35 (a) and 35 (b). The heat pump 3610 is operated in the hot water follow-up mode, and the air cooling heat pump 408 compensates for the lack of cold water. For a heating load H of 800 kW, the heat pump 3610 supplies 800 kW of hot water and simultaneously supplies 600 kW of cold water. In order to cope with the cooling load C, the air cooling heat pump 408 supplies 400 kW of cold water.

  If the heating load H is reduced to 600 kW from this state, the heat pump 3610 follows this to supply 600 kW of hot water, and accordingly, the output of cold water is reduced to 450 kW. Then, in order to cope with the cooling load C of 1000 kW, it is necessary to supply an additional 150 kW for the shortage of cold water. However, if the cooling capacity of the air-cooled heat pump 408 is (maximum) 500 kW, only 100 kW can be added, and eventually 50 kW of cold water is insufficient, and the temperature of the cold water tank rises as it is.

  Therefore, the cooling tower 404 and the cooling water pump 3616 are operated on condition that the chilled water temperature exceeds the set value (20 degrees) (and a predetermined time has elapsed), and the heat of the heat pump 3610 is discharged to the atmosphere by the three-way valve 3614 to 67 kW. Dissipate as much as possible. Then, the heat of the heat pump 3610 becomes 667 kW for 600 kW of hot water and 67 kW of cooling water, and the cold water outputs 500 kW, so that it becomes possible to cope with the cooling load C of 1000 kW together with the cold water of 500 kW of the air cooling heat pump 408. . That is, the automatic control device that controls the three-way valve 3614 monitors the temperature of the chilled water tank, and when the chilled water is insufficient, the heat of the heat pump 3610 is cooled by the cooling tower 404 (released to the atmosphere), thereby increasing the chilled water output. To correspond to the cooling load C. Note that a dedicated device (cooling device) for cooling the heat of the heat pump 3610 may be provided instead of or together with the cooling tower 404 (or the three-way valve 3614).

  In the heating and cooling apparatus according to the thirtieth embodiment, when the heat pump 3610 is in the hot water following operation and grasps that the cooling load C becomes insufficiently cooled by the cold water temperature being less than a predetermined value, the cooling tower 404 (cooling water cooler) Thus, the hot water (heating medium) of the heat pump 3610 is cooled. Therefore, even when the cooling load C is relatively large with respect to the heating load H, it is possible to cope with the cooling load C, and it is possible to continue the operation of the heat pump 3610 that is extremely energy saving.

[Other forms]
In the above embodiment, various types of heat (factory exhaust heat, etc.) belonging to the factory is used as the cooling side heating medium applied to the cooling side of the heat pump that performs heating and cooling. Or in conjunction with this, heat from other types of factories can be used, such as: In other words, other exhaust and exhaust heat generated in the factory, heat from various equipment, heat from hydraulic oil, heat from the work after drying, and products heated by hot water washing are washed in the subsequent water washing process. In this case, the heat transferred to the washing water, the exhaust heat generated from the factory air conditioning (cold water return), the exhaust heat including the cogeneration cooling water, or a combination thereof is used. Further, instead of or together with the various heats, the heat of hot water generated by a separate heat pump (cooling side heating medium supply heat pump) may be used. In this case, the energy used for the operation of the cooling-side heating medium supply heat pump increases, but the increase is less than the energy required when the heat from the heating / cooling heat pump is discarded. It is possible to obtain a favorable heating / cooling apparatus. Furthermore, the hot water of the cooling side heating medium supply heat pump and the exhaust heat of the factory and the cold water of the heat pump for heating and cooling are introduced into the heat exchanger, and the hot water and the exhaust heat are combined and applied to the cold water of the heat pump for heating and cooling. good. Still further, as the cooling-side heating medium, boiler steam, an electric heater, or the like, or a combination of various heat (exhaust hot water) belonging to the factory or the hot water of the cooling-side heating medium supply heat pump can be used. In addition, various controls and switching by the automatic control device can be performed manually. In addition, regarding the adjustment of the heating amount of the cold water (heating amount adjusting means), instead of the adjustment of the branch amount to the heat exchanger, the adjustment of the amount of exhaust gas hitting the cooling medium heating heat exchanger, these A combination may be used. Furthermore, an inverter pump may be used in adjusting the branch amount of the cold water (heat exchange amount adjusting means). Further, the number of elements may be changed as appropriate, such as a combination of a plurality of heat pumps and coolers.

  Furthermore, a separate heat pump (heating heat pump) may be provided that directly takes in and heats the refrigerant of the heat pump that performs heating and cooling and returns the heat to the heat pump. In addition to this, the above-described various heat exchangers for heating the refrigerant of the heat pump can also be installed. In addition, for the cold water side of the heat pump that performs heating and cooling, the cold water from the heat pump is treated at the factory in the same manner as the exhaust hot water, and the hot hot water higher than the cold water is returned directly to the heat pump (after being appropriately treated), Or the pipe | tube of waste water can be arrange | positioned so that flow path switching is possible so that waste water may enter into a heat pump in this way.

  In addition, the same effect as described above can be obtained by using an air-cooled heat recovery type heat pump (air-cooled heat pump type / cold / warm water simultaneous extraction type) instead of (or with) the exhaust heat recovery type heat pump. . In other words, the air-cooled heat recovery heat pump automatically balances the air (air) as the heat source when the heat balance between cold water and hot water is lost (heat is removed from the atmosphere when the heat is insufficient, and heat is returned to the air when the cold is insufficient. However, there is a limitation in efficiency because of the heat exchange with the atmosphere. Therefore, if the cooling side of the air-cooled heat recovery type heat pump is heated by factory exhaust heat or the like, the above-described effects such as continuing efficient operation in the air-cooled heat recovery type heat pump can be achieved. In particular, in winter when the outside air temperature is low (5 degrees), when the cooling side is not heated, the efficiency of extracting hot water of 70 degrees using air as a heat source is about COP2.1. The efficiency can be improved to about COP 3.8 by heating up to a degree. Further, the above forms (particularly the twenty-second to twenty-seventh forms) can also be applied to coating equipment as disclosed in JP-A-5-31417.

  Next, examples according to the above-described embodiment of the present invention will be described based on the drawings as appropriate. In addition, the said Example is not limited to the following. In addition, although the explanation is omitted step by step, each embodiment may include those to which the above embodiments are applied. Furthermore, application object is not limited to the following, For example, various factories, establishments, etc., such as institutional cultivation, aquaculture, dairy farming, food manufacture, chemical product manufacture, and plating processing, can be mentioned.

  In the first embodiment of the present invention, the heating / cooling device is applied to the sterilization process and used as a sterilization device. In the sterilization process for sterilizing processed fluids such as processed foods and beverages (liquids, milky bodies, fluids, etc.), heat sterilization performed before filling the containers in the production line and cooling after this heating are performed. In order to perform heating and cooling, the heating and cooling device is configured as a sterilizing device. JP-A-2007-202446 is exemplified as a document related to the conventional example.

[Example 1-1]
FIG. 39A is a schematic diagram of the sterilization apparatus 4001 according to Example 1-1. The sterilization apparatus 4001 is a heating heat exchanger 4001H that heats and cools a fluid to be treated (such as oolong tea) and cooling heat. An exchange 4001C is provided. The heating heat exchanger 4001H is connected to the hot water side of a plurality (here, two) of the heat pumps 10 connected in series, and the cooling heat exchanger 4001C is connected to the cold water side of the heat pump 10 connected in series. It is connected via a cold water circuit. The chilled water circuit (first chilled water circuit) and the second chilled water circuit of the heat pump 10 are adjacent to each other via the heat exchanger 4002. A heat exchanger 4004 that performs heat exchange with the cooling water of the cooling tower 3302 is disposed in the first cold water circuit. In the case where importance is placed on hygiene management, the fluid to be treated is cooled with tap water or the like via the cooling heat exchanger 4001C, and the heated tap water or the like is heated after the first cold water is heated via the heat exchanger 4002. It may be drained. Further, in order to operate in the hot water follow-up mode so that the temperature difference between the hot water inlet and outlet is within 10 degrees, in particular, the heat pump 10 is connected in series on the hot water side.

  The automatic control device controls the hot water temperature to 88 degrees for the heat pump 10. The hot water is heated to 97 degrees by another heat source Z (heating of 267 kW), introduced into the heat exchanger 4001H for heating, and used for heat sterilization of the fluid to be treated by heat exchange. It is led out from the exchanger 4001H and returns to the heat pump 10 through the hot water tank 3058 (the to-be-processed fluid is 10 tons per hour, the heating load of the heat pump 10 is 297 kW · 10 degrees, the average heating side COP3). The fluid to be treated is heated from 20 degrees to 94 degrees (heating load H of 860 kW).

  On the other hand, the automatic control device controls the cold water temperature to 18 degrees for the heat pump 10. The first cold water of 27 tons per hour passes through the heat exchanger 4002, reaches 50 degrees to the heat exchanger 4004, and becomes 38 degrees by 35 degrees of cooling water (load 232 kW, temperature rise to 48 degrees) of the cooling tower. Return to 10 (cooling load of 198 kW each, cooling by 10 degrees, average cooling side COP2). The second cold water is cooled from 62 degrees to 20 degrees in the heat exchanger 4002 at a flow rate of 12.9 tons per hour, and the temperature is increased to 62 degrees corresponding to the cooling load C of 628 kW in the cooling heat exchanger 4001C. The fluid to be treated is cooled from 94 degrees to 40 degrees.

[Example 1-2]
FIG. 39B is a schematic diagram of the sterilizer 4101 according to Example 1-2. The sterilizer 4101 is the same as that of Example 1-1, but the hot water side is the second hot water in the same manner as the cold water side. Or the structure which provided the heat exchanger 4102 and the structure which inserted the air compressor 2840 as a factory waste heat source in the cooling water circuit of the cooling tower 3302 differ. According to the former configuration, it is possible to prevent a situation where impurities such as lubricating oil in the refrigerant of the heat pump 10 enter the first hot water and further enter the fluid to be processed. The other heat source Z is incorporated in the second hot water circuit here.

  In addition, regarding the latter configuration, etc., the operation in the case where the heating load H (872 kW, processed fluid temperature 10 degrees → 85 degrees) is larger than the cooling load C (407 kW, processed fluid temperature 85 degrees → 50 degrees) will be described. To do.

  The automatic control device controls the first hot water temperature to 90 degrees for the heat pump 10. The first hot water passes through the heat exchanger 4102 and returns to the heat pump 10 at 70 degrees (heating for each 436 kW). The second hot water is heated from 56 degrees to 88 degrees in the heat exchanger 4102 and returns to the heat exchanger 4102 at 56 degrees after being heated in the heating heat exchanger 4001H.

  On the other hand, the automatic control device controls the first cold water temperature to 18 degrees for the heat pump 10. 17.5 tons of 1st chilled water passes through the heat exchanger 4002 and reaches 32 degrees and reaches the heat exchanger 4004. However, if it returns at 32 degrees as it is, it is overcooled and it becomes difficult to continue the operation of the heat pump 10. Therefore, the cooling water temperature of the air compressor 2840 is controlled to 40 degrees, and the first cold water is heated to 38 degrees by heat exchange (heating of 174 kW) to prevent the operation from being stopped due to overcooling. When the first cold water temperature is raised (to 40 degrees), the cooling water temperature of the air compressor 2840 can be lowered (to 35 degrees) to stabilize the temperature of the first cold water.

  The automatic control device also sets the first hot water supply setting of the heat pump 10 when the cooling water temperature of the air compressor 2840 decreases due to a decrease in the air compression load or the like and sufficient heating of the first cold water becomes impossible. By reducing the temperature from 90 degrees, the output of the heat pump 10 is reduced, and the amount of chilled water supplied is lowered to prevent the operation from being stopped due to the chilled water temperature drop. Note that the lack of supply temperature for the heating load H is covered by the other heat source Z. Further, instead of the cooling tower 3302 and the air compressor 2840, hot water (40 degrees) may be produced by an air-cooled heat pump to control the first cold water temperature. Furthermore, since a food factory generally has a clean room, cold water or hot water may be sent simultaneously as an air conditioning heat source. In addition, instead of or together with the exhaust heat recovery type heat pump that generates high-temperature water, a heat pump type steam / hot water generator that generates steam and high-temperature water may be used. In this case, the generated high-temperature water is heated by the heat exchanger 4102 and the generated steam is mixed with the other heat source Z or used, or heated by the heat pump steam alone. A heat pump that generates only steam may be used.

  In the second embodiment of the present invention, the heating and cooling device is applied to a desiccant air conditioner and used as a desiccant air conditioner. In desiccant air conditioning, heating of the regeneration side fluid (outside air, etc.) of the dehumidification rotor installed across the processing side and regeneration side, and cooling of the processing side fluid (outside air, indoor return air, etc.), etc. are performed. In order to perform cooling, the heating and cooling device is configured as a desiccant air conditioner. Desiccant air conditioning is suitable for air conditioning in a dry air atmosphere, and is performed in a dry room of a lithium ion battery manufacturing factory. JP-A-2009-133594 is exemplified as a document related to the conventional example.

[Example 2-1]
FIG. 40A is a schematic diagram of the desiccant air conditioner 5001 according to Example 2-1, for example, in summer, and FIG. 40B is a schematic diagram of the desiccant air conditioner 5001, for example, in winter, which includes the desiccant air conditioner 5001. Is installed so as to be rotatable over the processing side flow channel 5002 through which the mixed air of the processing outside air and the indoor return air flows, the regeneration side flow channel 5004 through which the regeneration outside air flows, and the processing side flow channel 5002 and the regeneration side flow channel 5004. And a dehumidifying rotor 5006 to which a dehumidifying agent is applied. The directions of the processing side flow channel 5002 and the regeneration side flow channel 5004 are opposite to each other, and a processing side fan 5008 and a regeneration side fan 5009 are sequentially installed.

  The mixed air in the processing side channel 5002 first passes through the processing side coil 5010 installed in the channel. The processing side coil 5010 is connected to the cooling side of the heat pump 10 in the case of FIG. 40 (a) to become a cooling load C (part of), and in the case of FIG. 40 (b), on the heating side of the heat pump 10. It is connected by switching and becomes a heating load H (part). Note that a three-way valve 5011 as a heat amount adjusting means is disposed in the circuit of the processing side coil 5010. An air cooling heat pump 408 is disposed in the cooling side circuit.

  Next, the mixed air passes through the dehumidifying rotor 5006 and is dehumidified by receiving moisture in the air by the dehumidifying agent. The dehumidification rotor 5006 retains moisture due to moisture adsorption and generates heat. The mixed air is introduced indoors for air conditioning after passing through the processing side adjustment coil 5012. The processing side adjustment coil 5012 is connected to the cooling side of the heat pump 10 in the case of FIG. 40 (a) and becomes (part of) the cooling load C, and in the case of FIG. 40 (b), the heating side of the heat pump 10 The heating load H is (part of) connected by switching to. Note that a three-way valve 5013 as a heat amount adjusting means is arranged in the circuit of the processing side adjusting coil 5012. In the case of FIG. 40B, a heat exchanger 5014 capable of introducing the other heat source Z is installed, and the hot water can be heated by the other heat source Z. Furthermore, a humidifier 5016 is disposed between the dehumidification rotor 5006 and the processing side adjustment coil 5012, and in the case of FIG. 40B, the mixed air can be humidified.

  On the other hand, the outside air in the regeneration side channel 5004 first passes through the regeneration side coil 5020 installed in the channel. The reproduction side coil 5020 is connected to the heating side of the heat pump 10 in the case of FIG. In the case of FIG. 40B, the cooling side of the heat pump 10 is switched to be connected to the factory exhaust heat X via the heat exchanger 5022, and the cooling load C is for cooling the factory exhaust heat X. On the other hand, since the heating side is switched to the processing side, cold water or hot water is not supplied to the reproduction side coil 5020.

  In the case of FIG. 40A, the outside air is heated by the regeneration side coil 5020 and reaches the dehumidifying rotor 5006. The heating amount of the outside air is appropriately assisted by a regeneration side adjustment coil 5024 that can introduce the other heat source Z.

  Then, including the case of FIG. 40 (a), the outside air that has reached the dehumidification rotor 5006 is regenerated so that the dehumidification rotor 5006 can sufficiently adsorb moisture again, for example, by skipping the moisture retained by the dehumidification rotor 5006. After the outside air passes through the dehumidifying rotor 5006, it is discharged as exhaust. The regenerated dehumidification rotor 5006 (part) is sent to the processing side by rotation, and the dehumidification rotor 5006 (part) used for processing the mixed air is sent to the reproduction side by rotation.

  The processing side adjustment coil 5012, the reproduction side adjustment coil 5024, the air cooling heat pump 408, the humidifier 5016, the factory exhaust heat X, and the other heat source Z may be omitted, replaced with various heat pumps, cold water chillers, cooling towers, etc. It may be connected to a heat pump, a cold water chiller, a cooling tower or the like alone or in common.

The desiccant air conditioner 5001 operates, for example, as follows. In the case of summer or the like in FIG. 40A, the indoor temperature is controlled to 25 degrees and the humidity is 50%. The outside air on the regeneration side is introduced at a flow rate of 9000 cubic meters per hour (m ³ / h), a temperature of 35 degrees, and a steam amount of 0.0190 kilograms (kg / kg (DA)) per kilogram of outside air, and 47.0 kW in the regeneration side coil 5020 Is heated to 50 degrees by the heating load H, and is used to regenerate the dehumidifying rotor 5006, and is discharged in the same amount as the introduction amount. The heat pump 10 supplies hot water (COP 3.6) of 60 degrees for the heating load H.

The mixed air on the processing side is a total of 6000 m ³ / h · 32 of 4200 m ³ /h·35°·0.0190 kg / kg (DA) of outside air and 1800 m ³ /h·26°·0.0105 kg / kg (DA) of return air. .3 degrees and 0.0165 kg / kg (DA), cooled to 20 degrees by the cooling load C of 38.3 kW in the processing side coil 5010 (0.0140 kg / kg (DA)), and with the dehumidifying rotor 5006 Dehumidified (0.0100 kg / kg (DA) · 35 degrees), and further cooled to 25 degrees by a cooling load C of 21.2 kW in the processing side adjustment coil 5012 (relative humidity 50%). Supplied indoors in quantity. The heat pump 10 supplies 34.0 kW of cold water (COP 2.6) for the cooling load C. In addition, 25.5 kW of cold water is cooled by the air cooling heat pump 408.

  Also, if the outside air temperature becomes 27 degrees and humidity 70% from this state, the cooling load C with respect to the heating load H is too low, and the hot water follow-up operation may not be continued. The possibility is grasped by detecting that it has become, and the following operation is performed.

That is, the heat pump 10 is switched to the cold water following operation. Or in order to hold | maintain the balance of the cold / hot water regarding the supply of the heat pump 10, the hot water supply set temperature is lowered while keeping the hot water follow-up operation, the output is reduced to prevent the cold water temperature from being lowered, and the insufficient heat is dealt with by other heat sources. Alternatively, the air-cooled heat pump 408 shown in FIG. 40 (a) is heated to heat the cold water. For example, for the regeneration side outside air of 9000 m ³ / h · 27 degrees · 0.0159 kg / kg (DA) (70%) and the heating load H71.4 kW (heating to 50 degrees / warm water 60 degrees), A total of 6000 m ³ /h·26.7°·0,0200 m ³ / h · 27 degrees · 0.0159 kg / kg (DA) and return air 1800 m ³ / h · 26 degrees · 0.0105 kg / kg (DA). It is introduced at 0143 kg / kg (DA), and is processed in the same manner as described above by the cooling load C of 2.9 kW in the processing side coil 5010 and the cooling load C of 21.2 kW in the processing side adjustment coil 5012. Although the entire cooling load C is 24.1 kW, heating of 71.4 kW in the heat pump 10 involves cooling of 51.6 kW. Therefore, the cooling water is heated by 27.5 kW by the air cooling heat pump 408 to balance the cooling water against the hot water. .

On the other hand, the indoor temperature is controlled to 25 degrees and the humidity is 50% in the case of the winter season of FIG. In winter, cooling and dehumidification are unnecessary, and heating and humidification on the processing side are necessary. Humidification is performed by a humidifier 5016, heating is performed by connecting the heating side of the heat pump 10 to the processing side coil 5010, and the cold energy accompanying the heating is used for cooling the factory exhaust heat X. For example, the mixed air on the processing side is a total of 6000 m ³ / h of outside air 4200 m ³ / h · 0 degree · 0.0023 kg / kg (DA) and return air 1800 m ³ / h · 26 degrees · 0.0105 kg / kg (DA). Introduced at 7.8 degrees and 0.0048 kg / kg (DA), heated to 33.7 degrees with a heating load H of 52.7 kW in the processing side coil 5010 (0.0048 kg / kg (DA)), It is humidified by a humidifier 5016 (0.0099 kg / kg (DA) · 21 degrees), and further heated to 25 degrees by a heating load H of 8.2 kW in the processing side adjustment coil 5012 (relative humidity 50%). The heat pump 10 supplies 60.9 kW hot water (COP 5.9) for the heating load H. On the other hand, the cold water of 50.6 kW · 25 degrees cools the factory exhaust heat X (compressor cooling water, etc.) of 40 degrees to 35 degrees and returns to 35 degrees (cold water COP 4.9).

In this case, the power consumption of the heat pump 10 is 10.3 kilowatts (kWh) per hour, and the carbon dioxide (CO ₂ ) emission is 4.7 tons (ton / h) per hour. On the other hand, if the same heating load H is provided by the boiler as usual, the boiler efficiency is 80% and the other loss is 20%, the city gas consumption is 7.0 m ³ / h, and the CO ₂ emissions are hourly. 16.3 tons (ton / h). Therefore, in the desiccant air conditioner 5001 of the present invention, the amount of CO ₂ used can be reduced by 70% or more compared to the conventional one. The CO ₂ emission factor was prepared by the Ministry of the Environment for city gas, based on the Enforcement Ordinance on Promotion of Global Warming Countermeasures and the Ministerial Ordinance on Calculation of Greenhouse Gas Emissions Associated with the Business Activities of Specific Emissions. Calculated values from the list of calculation methods and emission factors in the calculation, reporting and publication system (normal calorie per 11000 kilocalories (kcal / Nm ³ ), normal cubic meters per 2.3300 kilograms (CO ₂ ) (kg-CO ₂ / Nm ³ )) was used, electricity for 08 fiscal value of Chubu electric Power Co., Inc. (860 kilocalories per kilowatt-hour (kcal / kWh), was used _0.4550kg-CO 2 / kWh).

  In addition, when the factory exhaust heat X at the time of factory startup etc. is not sufficient (when the chilled water temperature is lower than the set value), the hot water supply temperature set value of the heat pump 10 is lowered to reduce the output, and the hot / cold water balance of the heat pump 10 is adjusted. It may be ensured that the insufficient heat is handled by the other heat source Z. In the same case, when the heat pump 10 is operated following the cold water, the insufficient heat is handled by the other heat source Z, and the factory exhaust heat X becomes sufficient (the factory exhaust heat X temperature, amount of heat, or hot water temperature is a predetermined value). If it becomes above, you may be allowed to perform warm water follow-up operation. Or, continue the cold water follow-up operation, reduce the supply amount of factory waste heat X so that the hot water temperature does not rise when the hot water supply temperature exceeds a specific value, or adjust the hot water temperature by controlling the cold water supply set temperature You can do it.

Further, the cooling side of the heat pump 10 may be connected to an air-cooled heat pump 408 that heats cold water (heating 50.6 kW · COP 5.0). In this case, the power consumption of the air-cooled heat pump 408 is 10.1 kWh, and when combined with the power consumption of the heat pump 10, the power consumption is 20.4 kWh, and the CO ₂ emission amount is 9.3 ton / h, which is 40% or more of the conventional amount. Can also be reduced.

  In addition, as factory waste heat X, boiler heat dissipation (boiler room temperature 50 degrees), cogeneration cooling water (45 degrees), exhaust gas (170 degrees), equipment cooling water (35 degrees), welding machine cooling water (35 degrees) , Hydraulic device cooling water (35 degrees), heat radiation of the workpiece after drying (80 degrees), heat radiation from the drying process (60 degrees around the furnace) can be exemplified. The heat recovery of each heat radiation (warming of cold water) may be performed by using existing air conditioning equipment (cold water piping, air handling unit, etc.) to cool water. Further, the cold water can be replenished from makeup water or well water (15 degrees), used for cooling the mold (25 degrees), or used for indoor air conditioning in factory air conditioning or office air conditioning. Furthermore, the hot water can be used for a washing process (80 degrees), a drying process (hot air 80 degrees), and a mold heating (40 degrees).

  In the third embodiment of the present invention, the heating / cooling device is applied to maintain the temperature of the stock solution and used as a temperature control device for the stock solution. In stock solution temperature adjustment, a medium in a specific temperature range is supplied to the stock solution tank in order to keep the stock solution in a specified temperature range. The medium is adjusted with hot water and cold water, and heated and cooled to heat and cool those hot water and cold water. The apparatus is configured as a stock solution temperature control apparatus. Examples of documents related to the prior art include JP-A-10-110056, JP-A-8-131091, and JP-A-6-79221.

[Example 3-1]
FIG. 41 is a schematic diagram of a stock solution temperature control device 6001 according to Example 3-1. The stock solution temperature control device 6001 mainly uses the 23rd form, and further in the cold water tank 3104 as in the 26th form. The exhaust heat X is connected. Cold water from both the hot water tank 3058 and the cold water tank 3104 is introduced into the adjusting means 6002 and mixed by an appropriate amount so that it is supplied as a medium in a specific temperature range to the undiluted liquid tank 6004 (the heat exchanger thereof), and the temperature of the raw material is maintained. After being used, it is returned to the cold water tank 3104 and the hot water tank 3058 as appropriate. Examples of raw materials include chemicals (foaming agents and paints) and foods (wheat flour and buckwheat flour). A cooling tower may be installed instead of or together with the air-cooled heat pump 2154. Further, the cooling side of the heat pump 10 may be heated by the factory exhaust heat X or the air cooling heat pump 2154.

  As an operation example, the hot water set value is 32 degrees and the cold water set value is 17 degrees, the medium temperature is adjusted to 24 degrees (± 1 degree) by the adjusting means 6002 and supplied to the raw material tank 6004, and the raw material is 24 degrees (± 1 Degree). When the hot water temperature of the hot water tank 3058 becomes 30 degrees (a value lower than the hot water supply temperature set value of the heat pump 10) or lower, the hot water is heated by the other heat source Z and cooled by the cooling tower 404 so as not to be 45 degrees or higher. The cold water is also cooled by the air-cooled heat pump 2154 (17 degrees, higher than the set temperature of the cold water supply of the heat pump 10), and in winter when the heat is insufficient, the cold water is discharged into the factory X (20 degrees, 17 degrees after heating) The amount of heating of the heat pump 10 is increased by heating with, for example, and the heating by the other heat source Z is minimized.

  The heat pump 10 is activated in a hot water follow-up mode (or a cold water follow-up mode), and switches to the cold water follow-up mode (cool water supply set temperature 17 ° / priority over the air-cooled heat pump 2154) when the chilled water temperature falls below a predetermined value (12 degrees). The other heat source Z backs up the heating. In addition, when the hot water temperature becomes a predetermined value (40 degrees) or more during the cold water follow-up operation, the operation is switched to the hot water follow-up operation (warm water supply set temperature 35 degrees, priority operation over the other heat source Z), and cooling is backed up by the air-cooled heat pump 2154. The

  In the fourth embodiment of the present invention, the heating / cooling device is used as a condensing and condensing device. The heating and cooling device performs heating of the raw material for concentration and condensation and cooling for evaporating the raw material into a condensate with a condenser, thereby forming a condensing and condensing device. JP-A-2005-111320 is exemplified as a document related to the conventional example.

[Example 4-1]
FIG. 42 is a schematic diagram of the condensing and condensing device 7001 according to Example 4-1. The condensing and condensing device 7001 includes a raw material tank 7002, a heating can 7004 that heats the raw material sent from the raw material tank 7002, and steam. An evaporator 7006 connected to the raw material tank 7002 and the heating can 7004 to evaporate the raw material, a condenser 7008 connected to the evaporator 7006 for receiving the evaporated raw material, a separating means 7010 connected to the condenser 7008 to separate gas and liquid, A vacuum pump 7012 that is connected to the separation unit 7010 and sends the separated gas, and an exhaust unit 7014 that is connected to the vacuum pump 7012 and discharges the sent gas.

  The heat pump 10 is connected to a heat exchanger 1164 (heating load 7001H) that preheats the raw material from the raw material tank 7002 to the evaporator 7006 on the heating side, and a heat exchanger that precools cooling water that cools the condenser 7008 on the cooling side. 104 (cooling load 7001C). A cooling tower 3302 is provided in the cooling water circuit that cools the condenser 7008. The heating can 7004 is connected to another heat source Z.

  As an example of operation, when a raw material having a liquid temperature of 20 degrees in the raw material tank 7002 and a water content of 89% is sent at 1000 kilograms (kg / h) per hour, the raw material is 60 degrees by heating 47 kW of the heat pump 10 operated in a hot water following operation. To reach the evaporator 7006 (warm water flow 70 degrees, return 60 degrees, heating side COP 3.5). The heating can 7004 generates steam by heating at 583 kW by the other heat source Z, and circulates it to the evaporation can 7006. In the evaporator 7006, the raw material is evaporated at 65 degrees in a vacuum atmosphere, and the evaporated raw material is sent to the condenser 7008. By supplying the raw material heated in advance to the evaporator 7006, the heat quantity of the other heat source Z is reduced. The liquid accumulated in the evaporator 7006 is taken out through the concentrate pipe 7016 as a concentrate (60 degrees).

  In the condenser 7008 which is a vacuum, the evaporation stock solution is condensed by cooling with cooling water to become a liquid (64 degrees), and the vacuum in the condenser 7008 is maintained. The cooling water is cooled to 33 degrees and returned to 40 degrees by cooling the heat pump 10 by 33 kW (cool water going back 30 degrees and returning 35 degrees) and the cooling tower 3302 by 547 kW, and is used for cooling the condenser 7008. The cooling amount of the cooling tower 3302 is reduced by the cooling of the heat pump 10. The liquid from the condenser 7008 is taken out through the condensate pipe 7018 as a condensate (60 degrees).

  In the condensing and condensing device 7001, the heating can 7004 (evaporator 7006) side and the cooling tower 3302 side are connected to the heating side or the cooling side of the heat pump 10, so that the heat discarded in the cooling tower 3302 can be recovered. The amount of Z input can be reduced. Note that the cooling tower 3302 and the other heat source Z may be started up when the condensing and condensing device 7001 is started, and the heat pump 10 may be operated following the hot water when the cooling water temperature of the cooling tower 3302 becomes a predetermined temperature or higher. Alternatively, the hot water supply temperature may be set to 80 degrees, and the stock solution may be heated to 80 degrees.

[Example 4-2]
FIG. 43 is a schematic diagram of the condensing and condensing device 7101 according to Example 4-2. The condensing and condensing device 7101 is the same as the condensing and condensing device 7001, but includes a cold water tank 3104 and a connection destination of the heat pump 10. Is changing.

  The heating side of the heat pump 10 is connected to a heating can 7004. The pipe 12 that supplies hot water includes a heat exchanger 7102 that performs heat exchange with another heat source Z. On the other hand, the cooling side of the heat pump 10 is connected to a cold water tank 3104. The cold water tank 3104 includes a heat exchanger 7116 provided in the concentrate pipe 7016, a heat exchanger 7118 provided in the condensate pipe 7018, a cooling tower 3302, and a condenser. 7008 is connected. One or both of the heat exchangers 7116 and 7118 may be omitted.

  As an example of operation, a raw material having a liquid temperature of 20 degrees and a water content of 89% in a raw material tank 7002 is charged into an evaporation can 7006 at 1000 kg / h, and the heating can 7004 is heated by heating 630 kW of the heat pump 10 operated in accordance with hot water. (Warm water 90 degrees, return 80 degrees, heating side COP3.2). The hot water for the heating can 7004 is backed up by another heat source Z and held at 90 degrees. The raw material is evaporated in the same manner as the concentration condenser 7001 and reaches the condenser 7008. The condenser 7008 receives cold water of 35 degrees from the cold water tank 3104 (return 40 degrees), and the raw material is condensed in the same manner. 433 kW of cold heat is supplied from the heat pump 10, and the cooling tower 3302 cools 147 kW. Further, cold water of 35 degrees is supplied from the cold water tank 3104 to the heat exchangers 7116 and 7118 (return 50 degrees), and the concentrated liquid and condensate liquid are cooled by 60 degrees.

  When the input amount of the raw material is increased, the output of the heat pump 10 is also increased, but since the cold energy is left (heat exchange in the condenser 7008 is delayed), the heat exchange amount in the heat exchangers 7116 and 7118 is increased. The factory exhaust heat X may be connected to the cooling side so that heat exchange is possible, and the cold water or the cooling water may be heated. On the other hand, when the input amount of the raw material is decreased, the output of the heat pump 10 is also decreased. The decrease is covered by an increase in the cooling amount of the cooling tower 3302.

  At the time of start-up, since the factory exhaust heat X and the amount of heat of the concentrate / condensate are not sufficient, the heat pump 10 is operated following the cold water, and the heating side corresponds to the hot water of the heat pump 10 and the other heat source Z. Then, when heating can be provided only with the hot water of the heat pump 10 (when the hot water becomes a predetermined temperature or higher), the operation is switched to the hot water follow-up operation. In addition, a heat pump steam / hot water generator that generates steam and high temperature water may be used instead of or in addition to the high temperature water generation type for the exhaust heat recovery type heat pump. In this case, the generated hot water is used for heating the raw material (heat exchanger 7001H), and the generated steam is used as a heat source for the heating can 7004. The shortage of steam is covered by other heat sources Z such as boilers. If it does in this way, since it can introduce without updating the existing concentration apparatus, cost reduction will be attained.

  The fifth embodiment of the present invention uses a heating / cooling device as a cleaning device. The heating / cooling device is configured as a cleaning device in order to heat the cleaning solution and to cool the regenerated cleaning solution (together with the new cleaning solution) for use in cleaning. JP-A-2004-186208 is exemplified as a document related to the conventional example.

[Example 5-1]
FIG. 44 is a schematic diagram of the cleaning device 8001 according to Example 5-1, such as in winter (when the heating load H is greater than the cooling load C), and FIG. 45 illustrates the heating load H in the cleaning device 8001 from the cooling load C. FIG. 6 is a schematic diagram when switching from a large case to a case where the cooling load C becomes larger than the heating load H (intermediate season, etc.). The cleaning apparatus 8001 uses a cleaning liquid as a workpiece W (semiconductor product (substrate / glass substrate / wafer)). ) Etc.) is dropped into each tank (the cleaning tank 8006 or the pre-cleaning tank 8008 having the pre-cleaning nozzle 8004, the conveyor 8010 for transporting the work W, and the cleaning liquid adhering to the cleaned work W). An air knife 801 as a blower that blows air from the air compressor 2840 in order to suppress cleaning liquid remaining in the workpiece W). And a pre-air knife 8014 as a pre-blower, a recovery tank 8016 for storing the recovered cleaning liquid from the pre-cleaning tank 8008, a new liquid tank 8018 containing a new cleaning liquid, and a regeneration for regenerating the recovered cleaning liquid from the cleaning tank 8006 A device 8020 is provided.

  The recovery tank 8016 and the new liquid tank 8018 are provided with heat exchangers 8016h and 8018h for heating, and a hot water tank 3058 having a heater 3058z as another heat source is connected to the heat exchangers 8016h and 8018h. The collection tank 8016 is connected to the cleaning nozzle 8002. The heat exchanger 8016h heats the recovered liquid to liquefy it. The heat exchanger 8018h heats the new liquid so as not to solidify.

  The regenerator 8020 has a stock solution tank 8022 for storing the recovered cleaning solution (stock solution), a first processing tube 8024 and a second processing tube 8026 for processing the stock solution from the stock solution tank 8022, and a degassing unit for degassing the treated stock solution. A gas treatment tube 8028 and a treatment liquid tank 8030 connected to a pre-cleaning nozzle 8004 for storing the degassed treatment liquid are provided.

  The stock solution tank 8022 and the first processing tube 8024 are provided with heat exchangers 8022c and 8024c for cooling, and a cold water tank 3104 is connected to the heat exchangers 8022c and 8024c (FIG. 45). A plurality of air-cooled heat pumps 2154 are connected to each other (FIG. 45). The heat exchanger 8022c cools the stock solution so that the stock solution does not solidify and has a temperature suitable for regeneration. The heat exchanger 8024c is cooled to maintain a constant temperature, for example, in order to increase the solubility of the gas and prevent the gas from being decomposed.

  On the other hand, heat exchangers 8028h and 8030h for heating are arranged in the deaeration treatment tube 8028 and the treatment liquid tank 8030, and a hot water tank 3058 is connected to the heat exchangers 8028h and 8030h. The heat exchanger 8028h is heated for preheating the cleaning liquid or promoting gas decomposition and degassing, and the heat exchanger 8030h is heated to make the processed cleaning liquid suitable for supply.

  The heat pump 10 is installed between the hot water tank 3058 and the cold water tank 3104 (FIG. 45). On the cooling side, the heat of the cooling water of the air compressor 2840 as the factory exhaust heat X can be applied via the heat exchanger 30 (FIG. 44). A cooling tower 3302 that supplies cooling water is connected to the air compressor 2840. Further, between the hot water tank 3058 and the cold water tank 3104, cold / hot water supply means 8040 for air conditioning is interposed.

  As an operation example, when the heating load H is larger than the cooling load C in winter or the like, as shown in FIG. 44, the heat pump 10 is operated to follow the hot water and the hot water temperature is controlled to 90 degrees. Hot water is supplied to each device including air conditioning via a hot water tank 3058, the temperature in the recovery tank 8016 is 80 degrees, the temperature in the new liquid tank 8018 is 45 degrees, and the temperature in the deaeration pipe 8028 of the regenerator 8020 is At 60 degrees, the temperature in the processing liquid tank 8030 is controlled to 80 degrees. The cleaning liquid and the pre-cleaning liquid are set to 80 degrees. Note that at least one of the devices may be omitted.

  On the other hand, the cold water is supplied to each device including the air conditioner at 10 degrees, and the internal temperature of the stock solution tank 8022 and the first processing pipe 8024 is set to 45 degrees. Further, the heat of the cooling water (18 degrees) of the air compressor 2840 is applied to (returned) cold water (returns at 16 degrees), and the temperature is raised from 15 degrees to 17 degrees. For example, a semiconductor factory is equipped with a clean room that is maintained at a constant temperature and humidity throughout the year, and cold water is required to maintain it. If the heat pump 10 that performs the hot water follow-up operation stops urgently because the cold water is overcooled as it is, the balance of the cooling load C with respect to the heating load H is achieved by heating the cold water with the cooling water of the air compressor 2840. Thus, the emergency stop of the heat pump 10 can be prevented, and the operation of the heat pump 10 can be continued while appropriately responding to heating and cooling.

  Even if the cooling load C temporarily exceeds the heating load H, the cooling water side of the heat pump 10 is cooled with the cooling water at a predetermined temperature (18 degrees) of the air compressor 2840, so that there is no shortage of cooling heat supply. When the chilled water (return) temperature rises above a predetermined temperature, the chilled water temperature can be controlled to be stable by lowering the temperature of the chilled water to a specific temperature (15 degrees).

  On the other hand, when switching to cope with the case where the heating load H becomes smaller than the cooling load C (or vice versa), as shown in FIG. 45, when the heating load H is larger than the cooling load C (in winter, etc.). ), The cooling side can be heated by an air-cooled heat pump 2154a or the like that is operated for heating, so that the operation stop of the heat pump 10 can be prevented. Further, when the cooling load C becomes larger than the heating load H (summer season, etc.), it is possible to cool the chilled water by the air-cooled heat pump 2154a or the like that is air-cooled.

  Further, regarding each of the air cooling heat pumps 2154a and the like, since it takes time to switch from the cooling operation to the heating operation (at least about 3 minutes), a plurality of air cooling heat pumps 2154a and the like are installed, and one is in the cooling operation. Then, other air cooling heat pumps 2154a and the like (preliminary machines) are set in a heating standby state so that switching from cooling to heating can be performed very smoothly. In addition, when only one unit is in the heating operation, the spare unit is set in the cooling standby.

  In addition, if there is a delay in switching from cooling to heating, the chilled water temperature decreases and the heat pump 10 stops if it remains as it is, so the chilled water temperature of the heat pump 10 that performs the hot water follow-up operation is less than a predetermined value. By monitoring this, the case is grasped, the hot water supply set temperature is lowered (90 degrees to 88 degrees), and the output of the heat pump 10 is reduced to prevent the cold water temperature from being lowered. When the hot water temperature decreases, the electric heater 3058z as another heat source backs up.

  Example 6 of the present invention uses a heating / cooling device as a drying device. Since the air introduced (circulated) into the drying furnace is cooled by a cooling coil for dehumidification and heated by a heating coil for setting the drying temperature, the heating / cooling device is configured as a drying device. The drying target may be anything as long as it needs to be dried. For example, wood, fish, seaweed, vegetables, clothing, fiber, gelatin, plants, fruits, fermented brewed products, printed materials, peat, sludge, rubber products. , Resin, adhesives, pottery, tiles, liquid crystal materials, semiconductors, films, pharmaceuticals, chemicals, paper, pulp, work (automobile parts, construction engineering machinery, special vehicles, steel furniture, steel fittings, automatic sales Machine, electrical equipment, communication equipment, switchboard, air conditioner, etc., or parts thereof). JP-A-2006-78015 is exemplified as a document related to the conventional example.

[Example 6-1]
FIG. 46 is a schematic diagram of a drying apparatus 9001 according to Example 6-1. The drying apparatus 9001 has a drying furnace 9002 for drying a work and a blower 9003, and is dried from an air outlet port of the drying furnace 9002. An air flow path 9004 leading to the air introduction port of the furnace 9002, a cooling coil 9010 for cooling air disposed in the air flow path 9004, and a first air for heating air disposed in the air flow path 9004 after the cooling coil 9010 A heating coil 9012 to a second heating coil 9014 are provided.

  The cooling side of the heat pump 10 is connected to the cooling coil 9010, the heating side is connected to the first heating coil 9012, and another heat source Z such as steam is connected to the second heating coil 9014. A heat exchanger 30 for applying the factory exhaust heat X is installed on the cooling side of the heat pump 10. Note that an air-cooled heat pump or a combination thereof may be connected to the heat exchanger 30.

  Further, on the cooling side of the heat pump 10, a cold supply amount adjustment valve 2048 that adjusts the degree of cooling or dehumidification of air by adjusting the amount of cold supplied to the cooling coil 9010 (flow rate of cold water) is disposed. In addition, on the heating side of the heat pump 10, a heat supply amount adjustment valve 2109 that adjusts the degree of heating of the air by adjusting the amount of heat supplied to the first heating coil 9012 (flow rate of hot water) is disposed. In addition, a flow rate adjustment valve 48 that adjusts the amount of heat introduced from the other heat source Z to the second heating coil 9014 is disposed.

As an example of operation, the heat pump 10 is operated following hot water to supply hot water of 70 degrees to the first heating coil 9012 and cold water to the cooling coil 9010. When the cold heat is left, the cold water is heated by the heat exchanger 30 related to the factory exhaust heat X or the air-cooled heat pump, and the operation of the heat pump 10 can be continued while maintaining the balance of the cold / hot water. The cooling coil 9010 cools the air to 20 degrees, and the relative humidity is 95% to reduce the water vapor content. The air is heated to 60 degrees by the first heating coil 9012 and the second heating coil 9014 introduced with another heat source Z (for example, steam of 5 kg / m ³ ), and dried in a state where the relative humidity is lowered (15%). It is introduced into the furnace 9002.

  If there is no factory exhaust heat X or an air-cooled heat pump cannot be installed, the cold water supply set temperature is lowered, or the supply amount (cold water (return) temperature) is adjusted by the cold heat supply amount adjustment valve 2048, or the first heating coil 9012 is used. This is done by lowering the outlet temperature setting and lowering the heating load H to reduce the output of the heat pump 10 so that the operation of the heat pump 10 can be continued.

  Furthermore, since the drying furnace 9002 is cold even when the heat pump 10 is started up in the hot water follow-up mode when starting up, the cooling load C is small and the factory exhaust heat X is also small. Accordingly, since it is difficult to balance the cold / hot water when the hot water follow-up mode is started as it is, the heat pump 10 is started in the cold water follow-up mode (or the cooling mode), heating is provided by the other heat source Z, and the cooling load C is set to the set value (drying furnace When the air temperature from 9002, the load factor of the heat pump 10, the inlet / outlet temperature of the chilled water, the temperature difference, or the like) is exceeded, or the heating load H of the heat pump 10 is a set value (warm water temperature, temperature difference, heat supply amount control valve 2109 When the adjustment amount (opening) or warm air temperature, etc.) is reached, the mode is switched to the hot water follow-up mode. Note that the heat pump 10 may be switched to the cold water follow-up mode and the hot water may be cooled by the cooling tower in order to reduce the power consumption based on a signal such as a power demand cut signal.

[Example 6-2]
FIG. 47 is a schematic diagram of a drying device 9101 according to Example 6-2. The drying device 9101 is the same as the drying device 9001, but the other heat source Z is connected to the first heating coil 9012, and the second heating coil. 9014 is different in that the heating side of the heat pump 10 is connected to 9014.

  As an example of operation, the heat pump 10 is operated following hot water to supply hot water of 70 degrees to the second heating coil 9014 and cold water to the cooling coil 9010. If there is excess cold heat, the temperature of the air at the inlet of the second heating coil 9014 containing hot water is raised by the other heat source Z instead of the operation similar to that of the drying device 9001 or at least one of the operations (other heat source Z The supply amount is increased), and the heating load H of the heat pump 10 is lowered by lowering the load of the second heating coil 9014 to balance the cooling and heating.

[Example 6-3]
FIG. 48 is a schematic diagram of a drying device 9201 according to Example 6-3. The drying device 9201 is the same as the drying device 9101, but a heating coil 9202 is installed instead of the second heating coil 9014, and the first The heating coil 9012 is omitted, and the other heat source Z is different in that the hot water is heated via the heat exchanger 42.

  As an example of operation, the heat pump 10 is operated following hot water to supply hot water of 70 degrees to the heating coil 9202 and cold water to the cooling coil 9010. If there is excess cold heat, the hot water return temperature of the heat pump 10 is raised at the other heat source Z (increasing the supply amount of the other heat source Z) instead of the operation similar to that of the drying device 9101 or at least one of the operations. Narrow down the output to balance the heat and cold. The balance may be maintained by raising the hot water supply temperature of the heat pump 10 and lowering the cold water capacity. In addition, the supply amount of cold heat or warm heat may be adjusted by adjusting the flow rate of the pump with an inverter instead of or together with adjustment by the flow rate control valve. Furthermore, a cold water tank may be arranged on the cold water side, the cold water in the cold water tank may be heated by the factory exhaust heat X or the like, a hot water tank is arranged on the hot water side, and another heat source Z is applied to the hot water tank. You can do it.

[Example 6-4]
FIG. 49A is a schematic diagram of a drying apparatus 9401 according to Example 6-4. The drying apparatus 9401 uses, as existing equipment, another heat source Z (main steam) shared in the factory in the drying furnace 9002. A steam pipe 9407 to be introduced into a drying heat exchanger 9416 for heating air (90 degrees) is installed, or a hot air temperature control valve 9408 is interposed in the steam pipe 9407, or an air duct for introducing air (20 degrees). 9409 is also installed, and the drying device 9401 is formed by adding to these existing facilities. The warm air temperature control valve 9408 adjusts the temperature of air in the drying furnace 9002 by adjusting the amount of steam introduced into the drying heat exchanger 9416.

  The drying device 9401 introduces a heat pump steam / hot water generator 9410 that introduces a heat source medium heated by the factory exhaust heat X, uses the heat as a heat source, and generates steam and hot water using separately supplied water (medium). I have. A heat exchanger 9411 is installed in the passage of the factory exhaust heat X, and a pipe for supplying a heat source medium (50 to 95 degrees) to the latter between the heat exchanger 9411 and the heat pump steam / hot water generator 9410 A pipe 9414 for returning the heat source medium 9412 to 4512 to the former is provided, and the heat exchanger 9411 exchanges the factory exhaust heat X with the heat of the heat source medium. The heat pump steam / hot water generator 9410 is connected to a soft water pipe 9417 and a water supply pipe 9418 for introducing water supply.

  Furthermore, the heat pump steam / hot water generator 9410 uses steam (100 to 120) by heating the water supply (25 degrees) from the soft water pipe 9417 and the water supply pipe 9418 using the heat of the heat source medium (50 to 95 degrees). Degree) and / or high temperature water (85 to 95 degrees), a steam pipe 9420 for providing the generated steam and a hot water pipe 9421 for providing high temperature water are connected. The steam pipe 9420 is connected to an ejector 9424 interposed in the steam pipe 9407, and the ejector 9424 is steam supplied by the main steam (for example, 5 kilograms (kg) per square centimeter) and a heat pump steam / hot water generator 9410. And the steam is supplied to the drying heat exchanger 9416.

  On the other hand, the hot water pipe 9421 is arranged so as to return to the water supply pipe 9418 (return temperature 40 degrees), and the hot water pipe 9421 or the air duct 9409 preheats the air by exchanging heat between the hot water and the air. A heat exchanger 9426 is interposed. Note that the air in the drying furnace 9002 is partially returned to the air duct 9409 (from the heat exchanger 9426 to the drying furnace 9002 side) by a pipe 9428 with a blower (80 degrees). As shown in FIG. 49B, drying heat exchangers 9416 and 9416a are provided in the steam pipes 9407 and 9420, respectively, and the drying heat exchanger 9416a is finally heated before air is heated by the drying heat exchanger 9416. The air may be heated and the ejector 9424 may be omitted. In the drying apparatus shown in FIG. 49 (b), the steam pipe 9407 (from the hot air temperature control valve 9408 side of the drying heat exchanger 9416) and the steam pipe 9420 are connected by a separate pipe, and a backup valve is provided on the pipe. May be. In this case, by opening the backup valve when the heat pump steam / hot water generator 9410 stops, the heat of the steam pipe 9407 can be introduced also into the drying heat exchanger 9416a, and the heat pump steam / hot water is generated. There is no need to increase the capacity of the drying heat exchanger 9416 in preparation for the stop of the apparatus 9410, and the capacity of the drying heat exchanger 9416 can be reduced.

  In such a drying apparatus 9401, the operation of generating steam for heating air and high-temperature water in the drying furnace 9002 using the factory exhaust heat X for the heat pump steam / hot water generator 9410 can be continued. In addition, high-temperature water can be returned to the water supply of the heat pump steam / warm water generator 9410 in a state where heat has been removed by using heat pre-heated by the heat exchanger 9426, and as a whole, a drying device 9401 with extremely good energy efficiency. Can be provided.

  For example, in the above-mentioned example, a simulation related to energy use is performed together with the conventional example (example in which only steam generated by a city gas boiler is introduced into the drying heat exchanger 9416), and the annual energy use amount is grasped and these are used. When compared, as described below with reference to FIG. 50, the amount of energy used by the drying device 9401 is small (good efficiency).

That is, the power consumption of the heat pump steam / hot water generator 9410 (HP steam / hot water generator, HP, heat source medium is about 80 degrees in FIG. 49) is 20 kWh (when kW), and the efficiency of the conventional city gas boiler is increased. 90 percent (%). The efficiency of electricity is 860 kilocalories per kilowatt hour (kcal / kWh), and the carbon dioxide (CO ₂ ) emission coefficient and the individual efficiency are as described above.

When considering per hour, the load of the heat pump steam / hot water generator 9410 is 146880 kcal / h, and the load of the boiler used in combination is 39204 kcal / h. Therefore, the electricity consumption of the heat pump steam / hot water generator 9410 is 20 kWh, the boiler city gas consumption is 4.0 N cubic m, and the CO ₂ emission is 9.1 kg / h based on the use of electricity and Based on the use of city gas, the total is 8.3 kg / h, which is 18.3 kg / h. On the other hand, the load of the boiler of the conventional example is 185868 kcal / h, the amount of city gas used is 18.8 N cubic m, and the CO ₂ emission amount is 43.7 kg / h based on the use of city gas.

Next, consider the total for one year. Here, the operation time per day is set to 16 hours, and the annual operation days are set to 250 days. Then, the electricity consumption of the heat pump steam / hot water generator 9410 is 80000 kWh, the city gas consumption of the boiler used together is 15840 Nm3, and the CO ₂ emission is 36.4 tons (t ) And 36.9 tons based on the use of city gas. On the other hand, the amount of city gas used by the conventional boiler is 75098 Nm3, and the CO ₂ emission amount is 175.0 t based on the use of city gas.

According to the results of grasping the energy usage status based on such simulation, the drying device 9401 can reduce the annual CO ₂ emission amount by 58% compared to the conventional example. In addition, when converted into crude oil per year, the amount of energy consumed is 39 kiloliters (kl) in the drying device 9401, and 89 kl in the conventional example, which shows a reduction effect of 56%.

  In the drying apparatus 9401, existing equipment such as the steam pipe 9407 can be used, and the existing equipment is not wasted and the introduction cost can be reduced. Note that the present invention can also be applied to a drying furnace using all fresh air (warm air) without returning warm air (for the pipe 9428) from the drying furnace.

  Further, when the amount of heat of the factory exhaust heat X decreases, the hot water temperature of the pipe 9412 decreases, and when the temperature drops to a certain set temperature, the heat pump steam / hot water generator 9410 stops. In this case, when the steam flow rate control valve is provided in the steam pipe 9420 and the temperature of the pipe 9412 is lowered (for example, lowered to 55 degrees or less), the steam flow rate control valve is throttled to reduce the amount of generated steam. The output of the generator 9410 is reduced, and the temperature of the pipe 9412 can be raised (the same control as in the nineteenth embodiment). In addition, when the amount of heat of the factory exhaust heat X increases and the hot water temperature of the pipe 9412 rises (for example, rises to 65 degrees or more), the heat pump steam / hot water generator is restored by returning the steam flow control valve to the original opening degree. The output of 9410 increases. In addition, instead of adjusting the heat pump output by the steam flow control valve, lowering the steam supply pressure set value (decreasing output) (increasing output) or lowering the steam supply temperature set value (decreasing output) (increased output) Alternatively, the output of the heat pump may be adjusted by decreasing (output decreasing) or increasing (output increasing) the steam supply flow rate setting value.

  Furthermore, a device that generates only steam may be used as the heat pump steam / hot water generator 9410. In addition, the heat pump 9411 generates hot water from the factory exhaust heat X and moves the heat pump, but the heat pump steam / hot water generator 9410 may be moved by exhaust heat belonging to the factory. Further, instead of or in addition to the method of making hot water from the factory waste heat X by the heat exchanger 9411, hot water may be made by an exhaust heat recovery type heat pump or an air cooling heat pump.

  Thus, about the process which can utilize cold water and warm water simultaneously, an energy-saving driving | operation can be continued by utilizing the exhaust heat recovery type heat pump and maintaining the supply balance of cold / hot water. Note that the air compressor and heat pump disclosed in Japanese Patent Application Laid-Open No. 2010-8000 can also be used effectively, and moreover, energy saving and stable operation can be performed throughout the year.

  In Example 7 of the present invention, the heating / cooling device is used as a coating device. The coating device is used in a coating factory. The heating and cooling device is used to heat the pretreatment liquid in the pretreatment tank and the air to the drying furnace and to cool the air conditioning / cooling furnace / electrodeposition tank. Configure as. In addition, if there is a temperature difference in the hot water supplied to multiple heating objects, it can be used for heating belonging to factories other than painting factories, for example, high temperature / low temperature drying, air conditioning, heating of food, etc., or a combination of these Can be used.

[Example 7-1]
FIGS. 51A and 51B are schematic views of a coating apparatus A001 according to Example 7-1. The coating apparatus A001 includes a plurality (two in this case) of exhaust heat recovery type heat pumps A002a and A002b. ing. Fig. 51 (b) shows a method of using the exhaust heat recovery type heat pump which is usually considered, and Fig. 51 (a) shows an efficient usage of the exhaust heat recovery type heat pump with different supply temperatures.

  51 (a) and 51 (b), the coating apparatus A001 has a pretreatment tank A003 (heating load H) containing a pretreatment liquid and a drying furnace A004 (drying furnace A004 (for drying workpieces) on the hot water circuit side. Heating load H), a hot water tank A005, a pretreatment side heat exchanger A006 that can introduce hot water to heat the pretreatment liquid, and a dry side heat exchanger A007 that can introduce hot water to heat fresh air to the drying furnace A004. ing. 51 (a) is different from that in FIG. 51 (b), and is further interposed between the heat pump A002a (return pipe) and the hot water tank A005 (circuit provided for heat exchange). A communication circuit side heat exchanger A008 is provided.

  51 (a) and 51 (b), the heat pump A002a and the drying-side heat exchanger A007 are connected by a hot water circuit, and the heat pump A002b and the hot water tank A005 are connected by another hot water circuit. Further, the hot water tank A005 and the pretreatment side heat exchanger A006 are connected by a separate hot water circuit, and another hot water circuit (a hot water communication circuit A055 for heat exchange) is provided between the hot water return pipe to the heat pump A002a and the hot water tank A005. Is installed.

  In addition, in order to enable heating by the other heat source (here, steam), the steam heat exchanger A009 as the other heat source heat exchanger on the pretreatment side is connected to the pretreatment tank A003 so that steam can be introduced, In the drying furnace A004, the steam heat exchanger A010 serving as a drying-side other heat source heat exchanger is a steam to enable heating from the air outlet port to the air introduction port by other heat source (here, steam). Connected to be able to introduce. Moreover, the pump is installed in the following location. That is, the hot water going pipe from the hot water tank A005 to the pretreatment side heat exchanger A006, and the hot water return pipe of the heat pump A002b (the going pipe when viewed from the hot water tank A005). In addition, in the thing of Fig.51 (a), the hot water outgoing pipe of heat pump A002a and the hot water outgoing pipe to the communication circuit side heat exchanger A008 in the hot water communication circuit A055 for heat exchange of the hot water tank A005 (the pump here is) This is a hot water communication pump A056 for heat exchange).

  On the other hand, each coating apparatus A001 of FIGS. 51 (a) and 51 (b) includes a cooling load C related to cooling of an air conditioning and a cooling furnace / electrodeposition tank related to a coating factory, and an air cooling heat pump A011 on the cold water circuit side. Yes.

  The outgoing pipe of the heat pump A002b is connected to the outgoing pipe to the cooling load C of the heat pump A002a, the outgoing pipe of the air cooling heat pump A011 is connected to the outgoing pipe of the heat pump A002b, and the return pipe of the heat pump A002b from the cooling load C of the heat pump A002a is connected. A return pipe is connected, a return pipe of the air-cooled heat pump A011 is connected to a return pipe of the heat pump A002b, and a cold water pump is interposed in these return pipes.

  Hereinafter, an operation example of the coating apparatus A001 will be described. The set temperature of the heating target (pretreatment liquid) for the pretreatment tank A003 (degreasing process / chemical conversion process) is usually 35 to 60 degrees, and the temperature of the hot water for the heating is set 2 to 20 degrees higher than the set temperature. Is done. Here, the set temperature of the hot water for the pretreatment tank A003 (pretreatment liquid set temperature 45 degrees) is 57 degrees. On the other hand, the set temperature in the oven of the drying furnace A004 is 60 to 180 degrees depending on the process, and the temperature of the hot water for heating is set to be about 10 degrees higher than the set temperature. Here, the set temperature of the hot water for the fresh air to the drying furnace A004 is 90 degrees.

  The automatic control device of the coating apparatus A001 operates the heat pumps A002a and A002b and supplies hot water of 90 degrees to the drying side heat exchanger A007 by the former (equipment capacity: heating 270 kW / unit / cooling 170 kW / unit). (Capacity: heating 350 kW / unit / cooling 250 kW / unit) to supply hot water of 55 degrees to the hot water tank A005. From the warm water tank A005, warm water of 57 degrees is supplied to the pretreatment side heat exchanger A006.

  In FIG. 51 (b), the heating heat source of the hot water tank A005 is only the heat pump A002b, and there is no communication circuit side heat exchanger A008, heat exchange hot water communication pump A056, and heat exchange hot water communication circuit A055. In the case of FIG. 51B, the pretreatment liquid is held at 45 degrees by heat exchange (heating 350 kW) in the pretreatment side heat exchanger A006, and the hot water returns to the hot water tank A005. In addition, since the heating capacity of the heat pump A002b is 350 kW, the shortage of 70 kW is provided by supplying steam to the steam heat exchanger A009. The hot water returns from the hot water tank A005 to the heat pump A002b. At this time, the heat pump A002b is operating at a cooling rate of 250 kW.

  On the other hand, the air (outside air) is heated to 80 degrees by heat exchange (heating 200 kW) in the drying side heat exchanger A007, mixed with the circulating hot air from the drying furnace A004, and further receives the heat of steam as appropriate. The warm air to A004 is kept at 90 degrees. And the warm water which became 82.5 degree | times returns to heat pump A002b. The heat pump A002a has a heating capacity of 270 kW and is operated with a remaining power of 70 kW (74% operation). On the other hand, steam is put into the pretreatment tank A003. Therefore, as a whole, the heat pump A002a is in a state in which other heat sources are input while remaining power, and there is room for reduction in energy consumption. In addition, the heat pump A002a has an output of 126 kW of cold water, and has 44 kW of remaining power. The output of the air-cooled heat pump A011 (124 kW of cold water) increases accordingly, and there is still room for reduction in energy consumption.

  On the other hand, in the coating apparatus A001 of FIG. 51 (a), the hot water communication pump A056 for heat exchange has a specific value when the hot water temperature in the hot water tank A005 becomes a predetermined value (56 degrees) or less. It is driven so as to be greater than (57 degrees). For example, when the hot water on the hot water tank A005 side entering the communication circuit side heat exchanger A008 is 56 degrees, it is heated by the 82.5 degrees hot water on the drying side heat exchanger A007 side entering the communication circuit side heat exchanger A008 and dried. The warm water on the side heat exchanger A007 side becomes 80 degrees and returns to the heat pump A002a. By the heat exchange in the communication circuit side heat exchanger A008, the temperature of the return hot water on the drying furnace A004 side that requires a high temperature is lowered by the hot water on the relatively low temperature hot water tank A005 side (pretreatment side), and the heating load H is reduced. By increasing the cooling water output of the heat pump A002a by that amount (from 126 kW to 170 kW), the cooling by the air cooling heat pump A011 is reduced from 124 kW to 80 kW, and the cooling load C can be efficiently handled. . Further, since the hot water temperature of the hot water tank A005 rises, a surplus heat source for the drying furnace A004 can be turned to the pretreatment tank A003 side, the operation of the heat pumps A002a and A002b can be linked, and energy can be saved.

  On the other hand, if the heating load H of the drying furnace A004 is increased and there is no surplus power on the drying furnace A004 side and there is surplus heating power on the pretreatment tank A003 side (by increasing the hot water temperature setting of the heat pump A002b) The temperature is raised to 90 degrees, and the reverse heat exchange is performed by the hot water communication circuit A055 for heat exchange. From the pretreatment tank A003 side (hot water tank A005 side) with sufficient power to the drying furnace A004 side with little power. Heat transfer occurs, the operation of the heat pumps A002a and A002b is linked, and energy is saved.

  In addition, by controlling the hot water communication pump A056 for heat exchange with an inverter, the flow rate of hot water on the hot water tank A005 side may be adjusted to adjust the amount of heat exchange in the communication circuit side heat exchanger A008. Alternatively, a three-way valve may be installed together with the pump, and the amount of hot water entering the communication circuit side heat exchanger A008 may be adjusted to adjust the heat exchange amount in the communication circuit side heat exchanger A008.

  On the other hand, on the cooling side, 7 degrees and 80 kW of cold water is supplied by the air-cooled heat pump A011 that performs auxiliary and adjustment operations, and 7 degrees and 250 kW of cold water is supplied by the heat pump A002b and combined with the cold water. Cold water of 7 degrees and 170 kW is supplied by A002a, combined with these cold water, and supplied to the cooling load C.

  The operating conditions of the heat exchange hot water communication pump A056 may be changed as follows. That is, the operation is performed when the heat pump A002a has a surplus capacity. For example, when the difference ΔTh between the warm water going temperature and the return temperature is within a set value (10 degrees), or the warm water return temperature is set to the set temperature (80 degrees). ) When it is above. Alternatively, the cold water temperature of the heat pump A002a or the difference ΔTc between the cold water going-back temperature and the return temperature may be monitored in the same manner as the hot water. Or you may make it judge that the load factor of heat pump A002a is below a predetermined value.

  In the coating apparatus A001 described above, the heat exchange hot water communication circuit A055 (for heat exchange) that communicates the high temperature (or heat quantity) supplied to the heating load H (drying furnace A004) and the low temperature (pretreatment tank A003). A hot water communication pump A056, a communication circuit side heat exchanger A008) is provided. Therefore, as shown in FIG. 51 (b), the heat exchange hot water communication circuit A055 is not provided, and the heat pumps A002a and A002b individually provide the heating load H as compared with the case where the heating load H is individually provided. It becomes.

  That is, when the heating load H is individually covered, hot water having a temperature suitable for each heating target is supplied. On the other hand, there is a surplus power, and on the other hand, there is no surplus power, and there is a state where there is a lot of backup due to steam due to insufficient heat. And at least consumes energy for backup. On the other hand, in the coating apparatus A001, the hot water on the side with no surplus power is heated by the hot water on the side with surplus power, so that no backup is required, or the output of the heat pump for adjusting the chilled water load (here, the air cooling heat pump A011) is output. This can save energy and save energy. Moreover, the partial load characteristics of the exhaust heat recovery type heat pump are generally worse than 100% operation, and the efficiency is improved by about 2 to 10% when the load factor of the heat pump A002a is changed from 74% to 100% operation. Furthermore, it becomes energy saving.

  When the hot water temperature of the heat pump A002a decreases due to some cause (for example, failure or increase of the heating load H) and the hot water temperature of the hot water tank A005 is cooled, the heat exchange hot water communication pump A056 is stopped as a protection circuit. Can do. Further, when the hot water temperature in the hot water tank A005 falls to a set temperature (for example, 53 degrees), the heat exchange hot water communication pump A056 may be stopped as a protection circuit. Further, as a heating target, instead of or together with the pretreatment tank A003 and the drying furnace A004, a booth air conditioner (reheat / preheat) or a first reheat of the booth air conditioner (for example, heated hot water 50 degrees) -It can be set as 2nd reheat (for example, heating warm water 60 degree | times). In addition, the hot water tank A005 is not provided, and the hot water of the heat pump A002b and the hot water of the heat pump A002a may be directly heat-exchanged. Moreover, instead of the communication circuit side heat exchanger A008, the heat pump A002a may be of a double band specification, and the hot water communication circuit A055 for heat exchange may be provided in the cooling water circuit (cooling side) in the 29th embodiment. In the double-band specification, in the heat recovery operation in the cold water follow-up mode, the hot water temperature of the exhaust heat recovery type heat pump is not controlled by the cooling tower, but the hot water of the exhaust heat recovery type heat pump is set to 90 degrees with the hot water of the hot water tank A005. It is also possible to use hot water more effectively without waste than to dissipate heat to the atmosphere with a cooling tower.

[Example 7-2]
FIGS. 52A and 52B are schematic views of the coating apparatus A101 according to the embodiment 7-2. The coating apparatus A101 is an air conditioning apparatus A102 as a heating target with respect to the coating apparatus A001 according to the embodiment 7-1. The reheater (heating coil) A103 is added. In the coating apparatus A101, a heat recovery type heat pump A002c and a hot water tank A105 are further added. Note that the modified example of the coating apparatus A001 according to Example 7-1 can also be applied to the coating apparatus A101 according to Example 7-2. Fig. 52 (b) shows a conceivable usage of the exhaust heat recovery type heat pump, and Fig. 52 (a) shows a more efficient usage of the exhaust heat recovery type heat pump with different hot water temperatures for the heating target.

  The hot water return pipe and the hot water return pipe (with pump) of the heat pump A002c are connected to the hot water tank A105, the hot water return pipe (with pump) from the hot water tank A105 to the reheater A103 extends, and the reheater A103 to the hot water tank A105. The hot water return pipe extends. The hot water tank A105 is provided with another heat source heat exchanger A106 for heating with another heat source (steam) as a backup.

  Further, in the case of FIG. 52 (a), two hot water communication pipes constituting the second heat exchange hot water communication circuit A155 (with hot water communication pumps A156 and A157, respectively) are provided between the hot water tanks A105 and A005. ) Is provided.

  On the other hand, on the cold water side, the cold water return pipe / return pipe (with pump) of the heat pump A002c is connected to the cold water return pipe / return pipe of the heat pump A002b.

  Fig. 52 (b) shows an example of the operation of the heat pump A002a (equipment capacity: heating 270kW / unit / cooling 170kW / unit) heating the fresh air in the drying furnace A004 at 90 degrees hot water (200kW, 74% operation). The cold water output is adjusted to 126 kW. The heat pump A002b (equipment capacity: heating 350 kW / unit / cooling 250 kW / unit) is heated at 55 degrees hot water (300 kW, 86% operation), heats the pretreatment tank A003 via the hot water tank A005, and is operated at a cold water output of 214 kW. ing. The heat pump A002c (equipment capacity: heating 500 kW / unit / cooling 400 kW / unit) supplies hot water 45 degrees (500 kW, 100% operation) to the hot water tank A105 and is operated at a cold water output 400 kW. In order to cope with the cooling load C (900 kW), the air-cooled heat pump A011 is operated with 160 kW of cold water. The heat pumps A002a and A002b are not 100% operated but have a surplus power, but the heat pump A002c is 100% operated and is in a state of heating the hot water tank A105 with steam (100 kW) in order to cope with the heating load H. , There is room for reducing energy consumption.

  On the other hand, FIG. 52 (a) shows an example of the operation of the coating apparatus A101, 90 degrees from the heat pump A002a (equipment capacity: heating 270 kW / unit / cooling 170 kW / unit, power consumption 100 kW), similar to the coating apparatus A001. Of warm water is supplied to the drying side heat exchanger A007, and air at 25 degrees becomes warm air at 80 degrees. The drying side heat exchanger A007 consumes 200 kW, the hot water enters 82.5 degrees, enters the communication circuit side heat exchanger A008, consumes 50 kW, reaches 80.7 degrees, and returns to the heat pump A002a (total 250 kW). At this time, 7 degrees and 157 kW of cold water is supplied from the heat pump A002a to the cooling load C (93% operation).

  In addition, 55 ° C / 350kW hot water is supplied to the hot water tank A005 from the heat pump A002b (equipment capacity: heating 350kW / unit / cooling 250kW / unit, power consumption 100kW), and 55 ° C / 300kW hot water is pretreated from the hot water tank A005. Supplied to side heat exchanger A006. At this time, 7 degrees and 250 kW of cold water is supplied to the cooling load C from the heat pump A002b.

  Furthermore, 45 degrees and 500 kW of hot water is supplied from the heat pump A002c (warm water follow-up mode, equipment capacity: heating 500 kW / unit, cooling 400 kW / unit, power consumption 100 kW) to the hot water tank A105, and hot water of 47 degrees from the hot water tank A105. It is supplied to the reheater A103 of the air conditioner A102 and consumed 600 kW, returning to 40 degrees. At this time, 7 degrees and 400 kW of cold water is supplied to the cooling load C from the heat pump A002c. In addition, cold water is supplied to the cooler (cooling coil) A107 of the air conditioner A102 from the cold water circuit.

  In the coating apparatus A101, the second heat exchange hot water communication circuit A155 can exchange heat (50 kW) between the heat on the pretreatment tank A003 side generated by the heat pump A002b and the heat on the air conditioner A102 side. The operation can be performed with the output of A002b increased from 86% to 100%, and the amount of cold water supplied by the heat pump A002b can be increased (from 214 kW to 250 kW).

  Further, by adding the first heat exchange hot water communication circuit A055, it is possible to heat the hot air for generating the hot air to the air conditioner A102 side to heat the hot water for air conditioning (50 kW), and the heat pump A002a is heated by the heating. The warm water temperature decreases to increase the heating load, the output of the heat pump A002a increases (from 74% to 93%), and the amount of cold water supplied by the heat pump A002a also increases (from 126 kW to 157 kW).

  As the amount of cold water supplied increases, the output of the air-cooled heat pump A011 as a cold backup device decreases (160 kW) compared to the case where there is no heat exchange hot water communication circuit A055, A155 as shown in FIG. To 93 kW), saving energy, reducing the equipment capacity of the air-cooled heat pump A011 to be prepared, and reducing the cost.

  Further, in general, the heat capacity and efficiency of the exhaust heat recovery type heat pump become better as the hot water temperature is lower. However, the heat pump A002a has a higher hot water temperature and becomes a hot water side COP 2.7, and the heat pump A002b has an intermediate hot water temperature and a hot water side COP3. 5, the heat pump A002c has a low hot water temperature and becomes a hot water side COP 5.0. Accordingly, in the coating apparatus A101, the heat pump A002c and the heat pump A002b can be preferentially operated by increasing the output of the heat pump A002c and the heat pump A002b as much as possible. By moving the heat using A155, it is possible to supply appropriate heat to each heating target. That is, in the coating apparatus A101, the heat exchange hot water communication circuit is arranged so that the heat pump A002b having excellent efficiency is operated with priority.

  Note that the chilled water circuit can be set individually such that the chilled water circuit of the heat treatment pumps A002a to A002c is not made common, and the chilled water circuit (cold water feed 15 degrees, etc.) is independent from the pretreatment tank. In this case, in view of the fact that the higher the chilled water temperature is, the higher the equipment efficiency and the cooling / heating capacity are, the operation priority may be determined based on the chilled water temperature (and the hot water temperature).

[Example 7-3]
FIG. 53 (a) is a schematic diagram of a coating apparatus A201 according to Example 7-3, and the coating apparatus A201 has a configuration in which the pretreatment tank or its hot water circuit and heat pump are removed from the coating apparatus of FIG. 52 (b). Alternatively, the pretreatment tank A003 or its hot water circuit, the heat pump A002b, and the heat exchange hot water communication circuits A055, A155 are removed from the coating apparatus A101 of FIG. 52 (a), which is characterized by control on the cooling side.

  That is, first, in the coating apparatus as shown in FIG. 52 (b), the hot water follow-up operation is performed in order to operate each exhaust heat recovery type heat pump efficiently. However, because of the hot water follow-up operation, the cooling situation depends on the heating situation, and the cold water temperature is not stable. In particular, with regard to cooling in an air conditioner for booth air conditioning or recycle air conditioning or cooling of a cooling furnace, the accuracy of the cold water supply temperature is required, and thus the instability of the cold water temperature is not preferable. For example, the set temperature of booth air conditioning changes in summer 28 degrees, mid-season 25 degrees, winter 20 degrees, the heat supply amount fluctuates accordingly, the cold supply amount changes, and the load of recycle air conditioning also depends on the season Change.

  Therefore, in order to stabilize the chilled water supply temperature of the exhaust heat recovery type heat pump, the automatic control device monitors the chilled water return temperature (and / or the chilled water return temperature) of the heat pumps A002a and A002b, and the chilled water pump in each chilled water return pipe. The flow rate at A202, A203 (the amount of cold water returning to each heat pump A002a, A002b) is controlled by inverter control or the like to stabilize the cold water supply temperature at each heat pump A002a, A002b. In general, in heat pumps, there are upper and lower limit values of the chilled water flow rate, so the characteristics of the chilled water pumps A202 and A203 (the relationship of the current to the flow rate) depend on the upper and lower limit values for the input of the pump inverter. An upper limit and a lower limit are provided, and stoppage of the heat pump due to exceeding the upper limit and lower limit by adjusting the flow rate is prevented. Further, regarding the characteristics of the pump, a flow meter may be installed instead of the relationship of the current with respect to the flow rate, and the flow rate may be adjusted with this flow meter.

  For example, the heat pump A002c generates 400 kW of cold water by heating 500 kW in the summer by hot water following operation, and generates 280 kW of cold water by heating 350 kW in the winter.

  Here, in the summer, when the cooling load C is large and the cold water return temperature is 17 degrees, the flow rate of the cold water pump A203 is set to 573 liters per minute in order to set the cold water supply temperature to 7 degrees. On the other hand, if the cooling load C is small and relatively little heat is taken away, and the chilled water return temperature is 15 degrees, the chilled water supply temperature is maintained at 7 degrees, so the flow rate of the chilled water pump A203 is 717 liters per minute. And

  Further, the heat pump A002a supplies 90 ° hot water to generate 80 ° hot air from 20 ° air in winter, and heats 270 kW by hot water following operation to generate 170 kW cold water.

  At this time, the chilled water return temperature to the heat pump A002a varies depending on the cooling load C, but the flow rate of the chilled water pump A202 is adjusted by inverter control. For example, when the cooling load C is large and the cold water return temperature is 17 degrees, the flow rate is 244 liters per minute. On the other hand, when the cooling load C is small and the cold water return temperature is 15 degrees, the flow rate is set to 305 liters per minute. In any case, the cold water going temperature is set to 7 degrees.

  In the coating apparatus A201, since the amount of cold water returning to the heat pumps A002a and A002c is adjusted, the cooling water supply temperature of the heat pumps A002a and A002c is stabilized, and the cooling load C can be accurately cooled while saving energy.

  In the case of recycled air conditioning, the cooling load C and heating load H are relatively stable. Therefore, manually adjust the chilled water flow rate of each heat recovery heat pump according to the set temperature / humidity and season of the booth air conditioning. For example, it can be adjusted by manually switching the pump inverter, manually changing the opening of the valve, or the like.

[Example 7-3-1]
As a modification of the coating apparatus A201 according to Example 7-3, a coating apparatus according to Example 7-3-1 in which the cold water temperature control is different will be described. The structure of the coating apparatus of Example 7-3-1 is equivalent to the structure of the coating apparatus A201 according to Example 7-3 shown in FIG.

  The flow rate of each chilled water pump related to the heat pumps A002a and A002c is made constant, the chilled water temperature of the air-cooled heat pump A011 is automatically raised and lowered, and the chilled water temperature sent to the cooling load C is controlled to 7 degrees. As an example, the heat pump A002c is operated at a chilled water return temperature of 12 degrees and a chilled water return temperature of 9 degrees (478 liters / minute · 100 kW), and the heat pump A002a is operated at a chilled water return temperature of 12 degrees and a chilled water return temperature of 8 degrees (717 liters). If the cooling water returned at 12 degrees of the air cooling heat pump A011 is supplied at 5 degrees (837 liters / minute 409 kW), it is 7 degrees 2032 liters for the cooling load C of 709 kW. It is possible to respond by supplying cold water per minute. When the chilled water supply temperature of the heat pumps A0002a and A002c is lower than 7 degrees, the chilled water supply temperature of the air-cooled heat pump A011 can be raised to supply chilled water of 7 degrees to the cooling load C.

  In addition, as in Example 7-3, when there is an upper and lower limit of the chilled water flow rate of the heat pumps A002a, A002c, when the chilled water temperature cannot be changed to the target value by changing the chilled water flow rate due to the limitation, As in Example 7-3-1, by changing the chilled water temperature of the air-cooled heat pump A011, the chilled water having the target temperature can be supplied to the cooling load C, and the control range can be expanded.

[Example 7-4]
FIG. 53 (b) is a schematic diagram of a coating apparatus A301 according to Example 7-4. The coating apparatus A301 is similar to the coating apparatus A201 of Example 7-3, but is replaced with an air-cooled heat pump A011. Two air-cooled heat pumps A302 and A303 serving as refrigerators for cooling are provided in order on the forward pipe of the heat pump A002a and the forward pipe of the heat pump A002c.

  The coating apparatus A301 basically operates in the same manner as in the embodiment 7-3. However, by providing the air cooling heat pumps A302 and A303, the temperature of the cold water from the heat pumps A002a and A002c becomes higher than the set temperature (7 degrees). Even if it is, it becomes possible to cool cold water to that temperature, and the cold water supply temperature to the cooling load C is stabilized.

  Moreover, even if the temperature of the chilled water discharged from the heat pumps A002a and A002c is higher than the set temperature, it is possible to cope with the cooling load, so that the chilled water return temperature can be increased accordingly, and the heating capacity and efficiency of the heat pumps A002a and A002c Can be improved. For example, when producing hot water of 45 degrees and 566 kW in the heat pump A002c, if cold water of 7 degrees and 456 kW is discharged, the power consumption is 110 kW, but if cold water of 9 degrees and 486 kW is discharged, The power consumption drops to 109 kW. The cold water at 9 degrees is lowered to 7 degrees by the air cooling heat pump A303.

[Example 7-5]
FIG. 54 is a schematic diagram of a coating apparatus A401 according to Example 7-5. The coating apparatus A401 is similar to the coating apparatus A201 of Example 7-3, but a chilled water tank A402 is further installed on the cooling circuit side. ing. The cold water tank A402 is disposed between the heat pumps A002a and A002c, the air cooling heat pump A011, and the cooling load C.

  The chilled water discharged from the heat pumps A002a and A002c is temporarily stored in the supply part A403 of the chilled water tank A402, the flow rate is adjusted by the pump, and the chilled water going temperature is adjusted by the air-cooled heat pump A011, and then supplied to the cooling load C. The air-cooled heat pump A011 is not used as a backup, but is used for adjusting the cold water supply temperature from the cold water tank A402 to the cooling load C (adjustment refrigerator).

  Further, the chilled water that has been deprived of the cold load by the cooling load C is temporarily stored in the return portion A404 of the chilled water tank A402, the flow rate is adjusted by the chilled water pumps A202 and A203, and the flow returns to the heat pumps A002a and A002c.

  In the coating apparatus A401 according to Example 7-5, since the cold water tank A402 is provided, the cold water supply temperature with respect to the cooling load C is stabilized. Further, the flow rate of the chilled water can be adjusted to match that of the air cooling heat pump A011, and the operation can be performed even if the flow rates do not match between the heat pumps A002a and A002c and the air cooling heat pump A011.

[Example 7-6]
FIG. 55 is a schematic diagram of a coating apparatus A501 according to Example 7-6. The coating apparatus A501 includes a drying furnace A004 and an air conditioner A102 similar to those in the above embodiment, and also deodorizes exhaust from the drying furnace A004. A deodorizing furnace A502 to be performed, an exhaust heat exchanger A503 that heats hot water by heat exchange between the deodorized exhaust (a part of which the amount of heat is adjusted), a steam generation heat pump A504 that generates steam using the hot water as a heat source, steam A steam absorption refrigerating machine A505 that generates cold water using a heat source, a steam boiler A506 as a steam backup, and a hot water tank A507. Here, the air conditioner A102 relates to recycle air conditioning.

  Hot water (85 degrees) is sent to the exhaust heat exchanger A503 through a pump from a low temperature section A508 (for example, 85 degrees warm water storage section) of the hot water tank A507, heated to 95 degrees, and heated to a high temperature section A509 ( For example, it is stored in a 95 ° hot water storage unit). For example, the exhaust from the drying furnace A004 is 180 degrees, and the exhaust from the deodorizing furnace A502 is 400 degrees, and the temperature is lowered by heating hot water.

  From the high temperature section A509, 95 degrees of hot water is sent to the reheater A103 of the air conditioner A102 via a pump and a three-way valve (flow rate adjustment valve / supplied heat amount adjustment means), and the hot water that has reached 85 degrees is discharged from the reheater A103. It returns to the low temperature part A508.

  The hot water in the high temperature part A509 is sent to the steam generating heat pump A504 after adjusting the flow rate through the pump, and the steam generating heat pump A504 generates steam using this hot water and supplies it to the steam path. The steam path leads to the steam absorption refrigerator A505 and the steam heat exchanger A010 of the drying furnace A004, and has a steam boiler A506. In addition, the warm waste water which steam generation heat pump A504 outputs at the time of steam generation is returned to the low temperature part A508 of the hot water tank A507. In addition, a pipe for returning a part of the steam as warm water to the warm water tank A507 (the high temperature part A509) is connected to the steam path.

  Air of 25 degrees is guided from the booth air conditioner to the drying furnace A004, passed through the steam heat exchanger A010, heated to 90 degrees and introduced. On the other hand, the vapor absorption refrigeration machine A505 cools cold water using steam (7 degrees). The cold water is supplied to the cooler A107 of the air conditioner A102, is used as cold heat for air conditioning, and returns to the vapor absorption refrigerator A505.

  In the coating apparatus A501, when the hot water temperature in the hot water tank A507 (its high temperature part A509) is lowered to a predetermined value (for example, 80 degrees) or less, the heating capacity (reheat) of the booth air conditioning is likely to be lowered and air conditioning becomes impossible. As described above, by reducing or stopping the output of the steam generating heat pump A504, the amount of heat used is reduced and the hot water temperature is maintained or raised.

  In other words, in the coating apparatus A501, the hot water heated by the exhaust heat can be used for the generation of steam by the steam generation heat pump A504 within a range that does not interfere with the air conditioning, and the heat recovered from the exhaust can be used up without waste. It becomes.

  When the reheater A103 side opening degree of the three-way valve related to the reheater A103 becomes a predetermined value (90%) or more (when the amount of heat supplied to the reheater A103 becomes a predetermined value or more), the output of the steam generating heat pump A504 is reduced or stopped. When the specific value (70%) or less is reached, the output recovery (increase) / resumption of operation of the steam generating heat pump A504 may be performed.

  Further, since the coating apparatus A501 uses the vapor absorption refrigeration machine A505, cold water can be easily generated in the presence of the steam path (steam generation heat pump A504). Here, what supplies cold water with a hot water absorption refrigerator is considered as a comparative example. In this comparative example, it is difficult to say that the equipment efficiency of the hot water absorption refrigerator is as low as COP 0.65 and is energy saving. Moreover, in this comparative example, it is necessary to newly lay hot water piping to the hot water absorption refrigerator. On the other hand, in the coating apparatus A501, cold water can be generated using the COP1.35 and the vapor absorption refrigerator A505 having good efficiency. In addition, the existing steam pipes can be used in the painting factory, which is advantageous in terms of cost.

[Example 7-7]
FIG. 56 is a schematic diagram of a coating apparatus A601 according to Example 7-7. The coating apparatus A601 is the same as that of Example 7-7 except that the vapor absorption refrigerator A505 is removed from the coating apparatus A501 according to Example 7-6. -2 is added with the configuration of the coating apparatus A101.

  That is, the exhaust heat recovery type heat pump A002c is connected to the air conditioner A102 via the hot water tank A105. Further, an exhaust heat recovery type heat pump A002b is connected to the pretreatment tank A003 via a hot water tank A005. The hot water tank A005 is connected to the hot water tank A507 (from the high temperature portion A509 to the hot water tank A005 and from the hot water tank A005 to the low temperature portion A508), and the hot water in the hot water tank A005 can be heated by steam. . Further, the hot water tank A507 is also connected to the hot water tank A106 (from the high temperature portion A509 to the hot water tank A106, and from the hot water tank A106 to the low temperature portion A508). Note that there is mainly no exhaust heat recovery type heat pump A002a for air heating in the drying furnace A004, and a steam generating heat pump A504 or the like is arranged instead.

  The steam is generated by a steam generation heat pump A504 and a backup steam boiler A506, and the other heat source heat of the steam heat exchanger A009 of the pretreatment tank A003, the steam heat exchanger A010 of the drying furnace A004, the hot water tank A005, and the hot water tank A105. It is supplied to the exchange A106.

  The cooling sides of the heat pumps A002b and A002c are grouped in the forward and backward directions, and an air-cooled heat pump A011 for cold water cooling backup is incorporated as in the coating apparatus A101 according to Example 7-2. The cold water is supplied to the cooler A107 of the air conditioner A102 related to the booth air conditioning, a cooling furnace (not shown), or the like (cooling load C).

  Although it is an operation example of the coating apparatus A601, the automatic control apparatus preferentially operates the steam generation heat pump A504 with emphasis on steam humidification and air heating by the steam heat exchanger A010 of the drying furnace A004. In general, the steam generating heat pump A504 can be operated at a heat source hot water temperature of 50 ° C. or higher. Therefore, the temperature of the hot water in the hot water tank A005 serving as a heat source is increased.

  The hot water heated by the exhaust heat is used for the operation of the steam generating heat pump A504, the hot water temperature rise in the hot water tank A005 for heating the pretreatment liquid in the pretreatment tank A003, and the hot water for the reheater A103 of the air conditioner A102. This is used to increase the temperature of the hot water in the tank A105, thereby suppressing the operation of the heat pumps A002b and A002c. For example, when the temperature of the hot water tank A105 for air conditioning becomes 50 ° C. or less, the pump is driven to send hot water from the hot water tank A507 that has recovered exhaust heat to the hot water tank A105. When the hot water temperature in the hot water tank A105 reaches 80 degrees or more, the pump is stopped and the movement of the hot water is stopped. On the other hand, when the warm water temperature of the pretreatment warm water tank A005 becomes 60 degrees or less, the pump is driven to send warm water from the warm water tank A507 that has recovered the exhaust heat to the warm water tank A005. When the hot water temperature in the hot water tank A005 reaches 80 degrees or higher, the pump is stopped and the movement of the hot water is stopped.

  Further, when the automatic control device determines that the hot water temperature of the hot water tank A507 (the high temperature portion A509) is equal to or lower than a predetermined value and the heat quantity is insufficient, the automatic control device sends hot water from the hot water tank A507 to the hot water tank A105 in view of overall efficiency. The flow rate of hot water is reduced by the pump, or the operation of the pump is stopped to stop the supply of hot water.

  Further, when the automatic control device determines that the hot water temperature of the hot water tank A507 (the high temperature portion A509) is lower than a specific value lower than the predetermined value and further determines that the amount of heat is further insufficient, the heat pump A002b for the next efficient pretreatment is used. The output is controlled to increase the operating rate of the heat pump A002b. That is, the automatic control device throttles the flow rate of the hot water using the pump for sending the hot water from the hot water tank A507 to the hot water tank A005, or stops the operation of the pump to stop the supply of the hot water. Thus, when the amount of exhaust heat of the deodorizing furnace A502 is small, the heat exchange between the hot water tanks A105, A005 and the hot water tank A507 is reduced, and the hot water temperature of the high temperature part A509 is kept high, thereby operating the steam generating heat pump A504. Continuing, it becomes possible to use up the excess hot water in the high temperature part A509 by booth air conditioning or pretreatment.

  In the coating apparatus A601 according to Example 7-7, when the amount of heat is sufficient for the hot water having heat recovered from the exhaust, it is preferentially used as a heat source of the steam generating heat pump A504, and the surplus is pretreated or Since it is used for heating in air conditioning, the heat recovered from the exhaust can be used up, which is extremely energy saving. In addition, when the heat quantity of the exhaust is insufficient, the heat quantity of the hot water for pretreatment or air conditioning and the output of the heat pumps A002b and A002c can be appropriately adjusted by exchanging the heat of the hot water, It is possible to cope with fluctuations accurately.

  In Example 8 of the present invention, the heating / cooling device is used as a drying / cooling device. The drying cooling device is used in coating factories, etc., and the heating / cooling device is configured as a drying cooling device to heat the air (warm air) to the drying furnace and to cool the air (cool air) to the cooling furnace. To do. In addition, you may employ | adopt or add things other than warm air as a heating object (heating load), and you may employ | adopt or add things other than cold air as a cooling object (cooling load). As in the other embodiments, this embodiment can be applied to other apparatuses such as an electrodeposition coating apparatus, and some of the following embodiments include those for other apparatuses.

[Example 8-1]
FIG. 57A is a schematic diagram of the drying and cooling apparatus B001 according to Example 8-1. The drying and cooling apparatus B001 includes the exhaust heat recovery type heat pump 10, and also includes the drying furnace B002 and the cooling furnace B004. Yes. In the drying cooling apparatus B001, for example, the workpiece after painting is dried by the warm air of the drying furnace B002, and then the heated workpiece is transported to the cooling furnace B004 and cooled by the cold air. In addition, you may heat or cool a separate workpiece | work in drying furnace B002 or cooling furnace B004.

  On the hot water side of the heat pump 10, a heat exchanger B008 disposed in the hot air circulation path B006 in the drying furnace B002 is installed, and the hot air is heated by heat exchange with the hot water. Further, the other heat source heat exchanger 42 is disposed in the hot air circulation path B006, and the steam ST as the other heat source Z is connected to the other heat source heat exchanger 42 via the pipe 46 and the flow rate control valve 48. ing. The warm air is heated from, for example, 70 degrees after returning (immediately after the introduction of the warm air circulation path B006) to 80 degrees (immediately before the hot air circulation path B006 is derived), and the hot water is set at a supply temperature of 90 degrees, for example. Note that fresh air may be mixed in the warm air circulation path B006 in a predetermined or controlled amount (ratio), or only fresh air may be introduced.

  On the other hand, a heat pump B010 for air conditioning is arranged on the cold water side of the heat pump 10, and a supply pipe B012 includes a branch pipe to the cooling load C, a pipe 16 from the heat pump 10, and three-way as a cooling / heating control means. The valve B016 is arranged, and the return pipe B020 is arranged with a pipe 26 to the heat pump 10, a branch pipe from the three-way valve B016, a pipe from the cooling load C, and a chilled water pump B022. And between the supply pipe B012 and the return pipe B020, the heat exchanger B028 arrange | positioned at the cold wind circulation path B026 in cooling furnace B004 is installed. The cold water supply temperature is set to 7 degrees, for example. Note that fresh air may be mixed in the cold air circulation path B026 in a predetermined or controlled amount (ratio), or only fresh air may be introduced. Further, instead of or together with the air-conditioning heat pump B010, a water-cooled heat pump, an exhaust heat recovery heat pump, an air-cooled heat pump, or a combination thereof may be arranged.

  In such a drying cooling apparatus B001, when cooling is performed in the post-drying process, the cooling load C is extremely light or completely absent until the work reaches the cooling furnace B004 after the drying starts, during which the heat pump 10 Even if it is simply operated, the balance between cold water cooling and hot water heating is not balanced and the operation cannot be continued. Further, for example, in the winter season, the environmental temperature (room temperature) is sufficient for cooling, so there may be a case where the cooling load C is not generated. In such a case, even if the heat pump 10 is simply operated, the operation cannot be continued. It becomes.

  Furthermore, regardless of the presence or absence of the cooling load C, it is conceivable that a situation in which the operation cannot be continued due to the relationship with the air conditioning heat pump B010 may occur. That is, in order to reduce the energy loss of hot water or cold water due to heat radiation, the heat pump 10 may be disposed adjacent to the drying furnace B002 or the cooling furnace B004, and the air conditioning heat pump B010 and the heat pump 10 may be separated. Then, since the piping from the heat pump 10 is longer than the cooling furnace B004 (heat exchanger B028) side, it is difficult for the cold water to flow to the air conditioning side (the cooling load C side in FIG. 57 (a)) where the piping resistance is relatively large. It will flow preferentially to the B028 side. Since cold water flows preferentially to the cooling furnace B004, there may be a situation where the cold heat is not sufficiently used and the heat pump 10 is returned to the heat pump 10, and the balance between the heat and cold may be lost and the operation may not be continued. There is.

  Therefore, the drying and cooling apparatus B001 operates as follows. That is, until the work reaches the cooling furnace B004 after the startup, the warm air is heated by the steam ST, and the work reaches the cooling furnace B004, and a cooling load related to the heat exchanger B028 is generated (a predetermined amount or more). The operation of the heat pump 10 is started. The hot water generated together with the cold water is supplied to the drying furnace B002 (heat exchanger B008), and the amount of heating by the steam ST is controlled so that the hot air becomes a predetermined temperature (within range). By starting the operation of the heat pump 10 in this way, the heat pump 10 can be operated in a state where the load on the cold water side of the heat pump 10 is sufficient, and the cold water supply amount of cold water is larger than the hot water supply amount. It is possible to prevent a situation in which the operation of the heat pump 10 becomes excessive and cannot be continued. Here, the start of operation includes activation of the heat pump 10, or includes the start of supply of hot water or cold water after the heat pump 10 finishes preparation for activation.

  Note that the return cold air temperature (the air temperature in the cold air circulation path B026) of the cooling furnace B004 becomes equal to or higher than a predetermined value (for example, 25 degrees) instead of or together with the generation of the cold load (greater than a predetermined amount). The difference between the cold air supply temperature and the cold air return temperature is a predetermined value (for example, a temperature difference of 5 degrees) or more, the cold water return temperature related to the cooling furnace B004 is a predetermined value (for example, 12 degrees) or more, The difference between the chilled water supply temperature and the chilled water return temperature may be a predetermined value (for example, a temperature difference of 5 degrees) or a combination thereof, or the operation start condition of the heat pump 10 may be used.

  Further, the operation of the heat pump 10 may be started when a timer capable of grasping the time or time at which a cooling load is expected to occur in the cooling furnace B004 grasps the time or time.

  Further, the operation of the heat pump 10 can be performed as follows. That is, when the factory is started up (at the start of the drying process), the heat pump 10 is operated in the cold water follow-up mode, and when the hot water reaches a predetermined temperature (for example, 70 degrees) or more, the heat pump 10 is switched to the hot water follow-up mode. Since the cooling load related to the cooling furnace B004 is small until the work reaches the cooling furnace B004 after the start of drying, the heat pump 10 is operated at a relatively low output, and when the work reaches the cooling furnace B004, the cooling furnace B004 is operated. Since the cooling load related to the heat pump 10 increases, the output of the heat pump 10 in the chilled water follow-up mode increases accordingly, the hot water output also increases, the hot water temperature rises, and the operation can be continued even in the hot water follow-up mode. Switch to mode. In addition, instead of grasping that the hot water is equal to or higher than the predetermined temperature, or together with this, the temperature of the hot air in the hot air circulation path B006 of the drying furnace B002 is higher than the predetermined temperature, or the temperature of the supply hot air and the return hot air The difference may be a predetermined value or more, the temperature difference between the supply hot water, the return hot water, and the return hot air may be a predetermined value or a combination thereof.

  In the above drying cooling apparatus B001, the drying heat pump 10 is operated after the cooling load related to the cooling furnace B004 is generated, and the heating load in the drying furnace B002 is appropriately handled by another heat source. Even before, or regardless of the cooling load C of the air conditioning heat pump B010, the operation of the heat pump 10 can be continued.

[Example 8-2]
FIG. 57B is a schematic diagram of the electrodeposition coating apparatus B101 according to Example 8-2, and the electrodeposition coating apparatus B101 is obtained by applying the drying cooling apparatus B001 of Example 8-1 to the electrodeposition coating apparatus. It is.

  That is, the pretreatment tank B102 (a hot water washing tank, a degreasing tank, a chemical conversion tank, etc., for example, 45 degree pretreatment liquid) is heated with steam ST before production, and the workpiece is flowed after the temperature rise is completed. There is an electrodeposition process in the electrodeposition tank B104 after the pretreatment process, and Joule heat is generated when the workpiece enters the electrodeposition tank B104 and current flows through the electrodeposition liquid, and the electrodeposition liquid is heated. Since the tank B104 and the cold water tank usually have a large amount of water retention, it takes a relatively long time from the start of energization to the temperature rise of the electrodeposition liquid. Therefore, although the generation of the cooling load related to the electrodeposition tank B104 is delayed from the start of the pretreatment, if the heat pump 10 is operated in the same manner as in Example 8-1 (for example, hot water supply temperature 65 degrees, hot water tank temperature 60 degrees, cold water tank Temperature 15 degrees, electrodeposition liquid temperature 30 degrees), it is possible to prevent the heat pump 10 from stopping due to imbalance between hot and cold, and it is possible to continue the operation of the heat pump 10 which is energy saving.

[Example 8-3]
FIG. 58 is a schematic diagram of the drying and cooling apparatus B201 according to Example 8-3. The drying and cooling apparatus B201 is similar to the drying and cooling apparatus B001 of Example 8-1, except that the heat exchanger B008 on the hot water side is fresh. In addition to being disposed in the air path B202, a flow rate adjusting valve B204 as a heat amount adjusting means is disposed in the pipe 12, and the pipe 12 branches toward the pipe 22 in front of the flow rate adjusting valve B204. The difference is that a flow rate adjusting valve B208 is arranged in the branch pipe B206.

  In the drying cooling apparatus B201, as described in Example 8-1, when the operation of the heat pump 10 is started after the cooling load related to the cooling furnace B004 is generated, the drying furnace B002 is already in operation. The operation is started in a state where air (for example, 25 degrees) is flowing. However, in this state, the hot water is cooled by fresh air during the start of operation, and the lower limit value of the hot water temperature, which is a normal operation condition of the heat pump 10 (for example, when the hot water supply temperature is as high as 70 degrees or more, for example, 40 May not be able to operate without raising the temperature. In addition, although it may be possible to operate for a short time even if it is less than the lower limit value of the hot water temperature, the heating capacity of the heat pump 10 may be less than that during normal operation (for example, to about 1/10) if the hot water temperature is low. Therefore, since the amount of cooling by fresh air exceeds the amount of heat of the heat pump 10, the hot water temperature does not rise, and the heat pump 10 cannot be operated normally.

  As a countermeasure against such a situation, in the drying and cooling apparatus of FIG. 58 in which the flow rate adjusting valves B204 and B208 and the branch pipe B206 are omitted, an electric heater as the other heat source Z is installed in the pipe 12 for supplying hot water, and the heat pump 10 It is conceivable to warm the hot water with an electric heater before starting. However, it is necessary to add another heat source Z, and the capacity needs to be large enough to cope with the amount of cooling by fresh air, which increases the size of the apparatus and increases the cost including the introduction cost.

  Therefore, in the drying cooling device B201, the operation of the heat pump 10 can be continued by controlling as follows. That is, by controlling the flow rate adjusting valves B204 and B208, at the start of the drying process (before the operation of the heat pump 10), the amount of water flow to the branch pipe B206 is increased, the amount of hot water to the heat exchanger B008 is decreased, and the hot water is exchanged with fresh air. The whole amount is cooled by heat exchange so as not to return to the heat pump 10. When the hot water temperature becomes equal to or higher than a predetermined value (for example, 50 ° C. or more), the amount of water flow to the branch pipe B206 is reduced, the amount of hot water to the heat exchanger B008 is increased, and the amount of heating to the fresh air is increased ( Gradually) to increase and allow the heat pump 10 to continue operating.

  Instead of reducing the amount of hot water supplied to the heat exchanger B008, or at the same time, at the start of the drying process (before the operation of the heat pump 10), fresh air may not be introduced and the air volume may be zero (slightly introduced). Including the case where there is a slight air volume). In this state, the operation of the heat pump 10 is started, and the warm water can be heated up so that the warm water is not cooled (excessively) by the fresh air, and the heat pump 10 is operated (when the warm water exceeds the lower limit value, the normal operation is performed). Continue driving. When the hot water temperature reaches a predetermined value (for example, 50 degrees or more) (fresh lower limit value), fresh air is introduced (gradually) so that the operation of the heat pump 10 can be continued.

  In addition, the amount of fresh air introduced may be reduced by, for example, inverter-controlling a fan for introducing fresh air, and the amount of heat exchange in the heat exchanger B008 may be reduced. Also in this case, when the hot water temperature reaches a predetermined value, the amount of fresh air introduced is (gradually) increased. Furthermore, a bypass is provided to prevent the introduced fresh air from passing through the heat exchanger B008 by a damper or the like so that the fresh air is bypassed until the hot water temperature reaches a predetermined value. May be heated through the heat exchanger B008.

  Hereinafter, a more detailed operation example of the drying and cooling apparatus B201 will be described. First, the operation of the fan of fresh air and the fan of the hot air circulation path B006 is started, the steam ST is input, and the operation of the drying furnace B002 is started. Next, the operation of the fan of the cold air circulation path B026 is started, and the operation of the cooling furnace B004 is started (although its cooling load is 0).

  Subsequently, the work is started to flow, dried in the drying furnace B002, and then flows to the cooling furnace B004. Then, the cooling load of the cooling furnace B004 is generated, the generation of the cooling load is grasped by detecting the rise in the warm water return temperature, and the operation of the heat pump 10 is started. At this time, hot water of 20 degrees passes through the branch pipe B206 side, and is gradually heated to 45 degrees (specific value) by heating with the heat pump 10.

  When the warm water reaches 45 degrees or more, the flow rate adjustment valve B204 is gradually opened, and the warm water is gradually passed to the heat exchanger B008 side. The flow rate adjustment valves B204 and B208 have their flow rates adjusted so that the hot water temperature becomes 70 degrees (predetermined value). When the temperature of the hot water reaches 70 degrees or more, the flow rate adjustment valve B208 of the branch pipe B206 is gradually closed, and the control of the flow rate adjustment valves B204 and B208 starts with the hot water temperature set to a predetermined (range) value. Switch to a temperature that falls within the set (range) value. If the heat pump 10 is operated in the warm water follow-up mode, the temperature of the fresh air can be kept within a predetermined value (for example, about warm water +10 degrees) without performing control switching.

  In this way, 80 degrees of fresh air is supplied to the hot air circulation path B006, and the temperature of the hot water reaches a normal value (for example, 90 degrees), and the normal operation is continued.

  In the above-described drying and cooling apparatus B201, the amount of heat exchange with the heating target (heating load / fresh air), the heating target and / or hot water until the hot water temperature and / or the heating target reaches a predetermined temperature (predetermined heat amount) or higher. Since it decreases by bypassing, the heating load H is relatively large at the start of operation, the hot water temperature of the heat pump 10 does not rise, and the heat pump 10 can be prevented from being stopped, and the operation of the heat pump 10 is smooth. After the start of operation, the heat exchange amount is set to a normal (maximum) state, and heating that is energy saving can be continued together with cooling.

  When the heating load of the heat pump 10 increases and the hot water temperature decreases due to a decrease in fresh air supply temperature or an increase in air volume, etc., except at the start of operation (during normal operation), the flow control valve B208 is opened and the heat exchanger B008 is opened. By reducing the amount of water passing through (decreasing the amount of heat exchange), it is possible to prevent the temperature of the hot water from decreasing and continue the operation of the heat pump 10.

[Example 8-4]
FIG. 59 (a) is a schematic diagram of the drying cooling device B301 according to Example 8-4 when the heat pump 10 is stopped, and FIG. 59 (b) is a schematic diagram of the drying cooling device B301 during operation of the heat pump 10, The drying cooling apparatus B301 is configured by further adding a cooling tower B302 to the drying cooling apparatus B201 of Example 8-3.

  That is, the hot water supply pipe B304 of the air conditioning heat pump B010 is branched and connected to the cold water return pipe 26 of the heat pump 10, and the hot water return pipe B306 includes an introduction pipe B310 and a discharge pipe B312 to the cooling tower B302, and A flow rate adjusting valve B314 as a heat amount adjusting unit and a pump B315 are connected, and a flow rate adjusting valve B316 as a heat amount adjusting unit is arranged in the introduction pipe B310. The amount of cooling of warm water (exhaust heat) for air conditioning is adjusted depending on whether or not the flow rate adjusting valves B314, B316 and / or the cooling tower B302 are operated.

  Further, a branch pipe B320 from the cold water return pipe 26 to the hot water return pipe 22 (from the pump 50 to the heat exchanger B008 side) comes out, and the branch pipe B320 is provided with a flow rate adjusting valve B322 as a heat amount adjusting means. Has been. Further, a flow rate adjusting valve B324 as a heat amount adjusting means is arranged on the heat exchanger B008 side from the connection point of the branch pipe B320 in the pipe 26. Still further, a branch pipe B330 to the pipe 16 that goes to the chilled water exits from the heat exchanger B008 side of the flow rate adjustment valve B324 in the pipe 22, and a flow rate adjustment valve B332 as a heat amount adjustment means is arranged in the branch pipe B330. Yes. The pipe 16 is connected to the warm water return pipe B306 on the upstream side of the introduction pipe B310 of the cooling tower B302.

  Such a drying cooling device B301, by the operation of the automatic control device or the like exemplified below, by starting the operation of the heat pump 10, by using the exhaust heat (waste water) as a heat source, the temperature of the hot water of the heat pump 10 is raised in advance, The operation start for continuing the operation of the heat pump 10 can be performed.

  That is, as shown in FIG. 59 (a), first, the air conditioning heat pump B010 is operated, and the air conditioner is heated to 50 degrees hot water (air conditioning reheat heating in the heating load H) and 7 degrees cold water (in the cooling load C). Air conditioning cooling coil cooling). Then, the flow rate adjustment valve B322 and the flow rate adjustment valve B332 are fully opened, the flow rate adjustment valve B324 is fully closed, and the hot air for air conditioning (50 degrees) is passed through the hot water return pipe 22 of the heat pump 10. The hot water for air conditioning passes from the pipe 12 to the heat exchanger B008 through the stopped heat pump 10, and returns to the hot water return pipe B306 for air conditioning through the pipe 16 through the branch pipe B330. By passing the hot water for air conditioning, the hot water temperature of the heat pump 10 becomes equal to or higher than the lower limit value (40 degrees) of the normal operation condition. When the hot water of the heat pump 10 becomes equal to or higher than the lower limit value (and a predetermined time elapses), the operation of the drying furnace B002 is started, that is, fresh air and hot air fans and steam ST are input. The air conditioning heat pump B010 may be operated after the drying furnace B002 is operated, and the hot water of the air conditioning heat pump B010 may be passed through the heat pump 10.

  Next, as shown in FIG. 59 (b), the operation of the heat pump 10 (or pumps 50, 52) is started, and the flow rate adjustment valve B324 is gradually opened until it is fully opened. Since the heat pump 10 is started to operate in a state where the hot water is set to the lower limit value or more by the hot water for air conditioning (exhaust heat appropriately discharged from the cooling tower B302), the heat pump 10 is started smoothly and the operation is continued. Note that the flow rate adjustment valve B324 may be opened before the heat pump 10 is operated.

  Subsequently, the flow rate adjustment valve B322 and the flow rate adjustment valve B332 are gradually closed until they are fully closed, and fresh air (80 degrees) is supplied. Then, the amount of steam put into the heat exchanger 42 is reduced, and energy saving operation becomes possible. Instead of the hot water of the air conditioning heat pump B010, waste heat belonging to the factory (exhaust hot water, equipment cooling water, cogeneration cooling water, or a combination thereof) may be used.

  In the above-described drying and cooling apparatus B301, since the exhaust heat (hot water for air conditioning) that has already been generated is introduced to the hot water side of the heat pump 10 before the operation is started, the heat pump 10 starts operation smoothly due to insufficient temperature of the hot water. The situation that cannot be prevented can be prevented.

[Example 8-5]
FIG. 60A is a schematic diagram of a drying cooling apparatus B401 according to Example 8-5. In the drying cooling apparatus B401, the cooling side of the drying cooling apparatus B001 of Example 8-1 is only the cooling furnace B004, and the fresh cooling apparatus B401 is fresh. The air path B202 is added. The cooling side may be the same as that of the drying cooling device B001 or the like, and the fresh air path B202 may not be provided.

  This is an example of the operation of the drying and cooling device B401. With the heat pump 10 stopped, the drying furnace B002 (the fan of the hot air circulation path B006 and the fresh air path B202) is operated, and the steam ST is supplied to apply the hot air. Warm up. Next, the pump 50 is operated so that the hot water of the heat pump 10 is heated by the air of the hot air circulation path B006 through the heat exchanger B008. Subsequently, when the hot water temperature becomes equal to or higher than a normal operation condition lower limit value or more (or a predetermined time elapses), the operation of the heat pump 10 is started and the hot water is heated until it reaches a set temperature (90 degrees). Then, it is supplied to the heat exchanger B008 and the hot air is heated by heat exchange. And according to the heating amount of the warm air by the warm water grasped by the warm air temperature or the like, the introduction of the steam ST is refrained.

  Such a drying / cooling apparatus B401 has the following merits compared to, for example, the apparatus described below. That is, a comparison is made with a device in which a heat exchanger for the steam ST is separately provided in the hot water return pipe 22, the warm water is heated by the steam ST, the heat pump 10 is started, and the operation of the drying path B002 is started. If the hot water side pipe of the heat pump 10 is 125 A and the total length is 40 m, it means that about 450 liters of hot water is contained, and the temperature is raised by the steam ST from the initial hot water temperature of 10 degrees to the lower limit value of 40 degrees under normal operating conditions. The amount of heat required for this is 15.7 kW. In this equipment, in order to complete heating in 20 minutes from the start of temperature rise (steam ST input), another heat source (steam ST, its piping, heat exchanger, steam flow rate adjustment) having a heating capacity of 47.1 kW Valve / control device) is required, the introduction cost and maintenance cost of the device are increased, and a space for the installation is also required. The drying cooling device B401 has an advantage that the cost and space in the device are not necessary.

  In the drying / cooling device B401, the hot water is heated by a heating target (heating load / warm air) preheated by another heat source (steam ST), and the hot water is set to a predetermined temperature or higher, and then the operation of the heat pump 10 is started. Therefore, the initial heating related to the heating target and the hot water of the heat pump 10 can be performed with another heat source, and the heat pump 10 can be started smoothly and the operation that is energy saving can be continued while heating the heating target quickly.

[Example 8-6]
FIG. 60B is a schematic diagram of an electrodeposition coating apparatus B501 according to Example 8-6, and the electrodeposition coating apparatus B501 is obtained by applying the drying cooling apparatus B401 of Example 8-5 to the electrodeposition coating apparatus. It is.

  That is, before the heat pump 10 is started, the pretreatment tank B102 or the hot water for heating is heated with the steam ST (pump operation), and the hot water of the heat pump 10 (pump 50) is exchanged with the hot water via the heat exchanger B008. Heating). Then, when the hot water of the heat pump 10 reaches a predetermined value equal to or higher than the lower limit value, the operation of the heat pump 10 is started.

  Also in the above electrodeposition coating apparatus B501, the heat pump 10 can be started smoothly and the operation which is energy saving can be continued similarly to the drying cooling apparatus B401.

1,101,201,301,401,501,601,1151,2861,2871,2881,2901,2911,3001,3051,3101,3251,3301,3351,3401,3501,3601,3701 Heating / cooling device 10, 210, 211, 510, 511, 2004, A002 Heat pump 30, 230, 231, 660, 661, 662, 663 Heat exchanger 36, 236, 630 (first) flow control valve 131, 3052 Chilled water chiller (cooling device)
136 (Second) Flow Control Valves 302, 404, 513, 2504, 2832, 3302 Cooling Tower 408, 2154 Air Cooling Heat Pump C Cooling Load H Heating Load

Claims (12)

A first heat pump for heating a first heating medium for heating a first heating load;
A second heat pump for heating a second heating medium for heating the second heating load;
An automatic control device for controlling the first heat pump and the second heat pump;
The first heat pump can be introduced by cooling by introducing a part of the second heating medium,
The second heat pump cools a cooling medium that cools a cooling load;
The automatic control device operates the second heat pump before the first heat pump, and introduces the second heating medium as a part of the first heating medium when starting the operation of the first heat pump. Then, the heating and cooling apparatus is characterized in that the temperature of the first heating medium is raised in advance to a normal operation condition lower limit value of the first heat pump . A first heat pump for heating a first heating medium for heating a first heating load;
A second heat pump for heating a second heating medium for heating the second heating load;
An automatic control device for controlling the first heat pump and the second heat pump ;
The first heat pump can be introduced by cooling by introducing a part of the second heating medium,
The second heat pump cools a cooling medium that cools a cooling load;
Furthermore, a second heating medium temperature sensor for detecting the temperature of the second heating medium, a second heating medium heat amount adjusting means for adjusting the second heating medium to an arbitrary temperature, and a temperature of the first heating load are detected. A first heating load temperature sensor, and another heat source for heating the first heating load,
The automatic control device operates the second heat pump prior to the first heat pump , and based on the temperature of the second heating medium obtained from the second heating medium temperature sensor, converts the second heating medium to the first heat pump . 2 Adjusting to a predetermined temperature by the heating medium heat amount adjusting means , operating the first heat pump , heating the first heating load with the first heating medium, and further obtaining the temperature obtained from the first heating load temperature sensor The heating / cooling, wherein the first heating load or the first heating medium is heated by the other heat source so that the first heating load becomes a specific temperature based on the temperature of the first heating load. apparatus. The cooling load includes the fluid to be treated in the sterilizer, the processing fluid in the desiccant air conditioner, the stock solution in the stock solution temperature controller, the cooling water / condensate or concentrate in the condensing condenser, the cleaning fluid in the cleaning equipment, the air in the drying furnace, the cooling Cooling load that cools at least one of furnace, electrodeposition tank, booth air conditioning, recycling air conditioning, factory air conditioning, office air conditioning, indoor air conditioning, clean room air conditioning, or air conditioning to maintain a constant temperature or humidity throughout the year is there
The heating / cooling device according to claim 1 or 2, wherein the heating / cooling device according to claim 1 or 2 is provided. A heat pump that heats the first heating medium that heats the first heating load , introduces exhaust heat belonging to the factory, cools the heat pump, and can derive the heat pump ;
An exhaust heat temperature sensor for detecting the temperature of the exhaust heat;
Waste heat calorie adjusting means for adjusting the temperature of the exhaust heat;
An automatic control device for controlling the heat pump and the exhaust heat calorie adjusting means ,
The automatic control device adjusts the exhaust heat to a predetermined temperature by the exhaust heat quantity adjustment means based on the temperature of the exhaust heat obtained from the exhaust heat temperature sensor when starting the operation of the heat pump. Is introduced as a part of the first heating medium , so that the temperature of the first heating medium is raised in advance to a normal operation condition lower limit value or more of the heat pump . A heat pump that heats the first heating medium that heats the first heating load , introduces exhaust heat belonging to the factory, cools the heat pump, and can derive the heat pump ;
An exhaust heat temperature sensor for detecting the temperature of the exhaust heat;
Waste heat calorie adjusting means for adjusting the temperature of the exhaust heat;
A first heating load temperature sensor for detecting a temperature of the first heating load;
Another heat source for heating the first heating load or the first heating medium;
The heat pump, the exhaust heat calorie adjusting means, and an automatic controller for controlling other heat sources ,
The automatic control device adjusts the exhaust heat to a predetermined temperature by the exhaust heat calorie adjusting means based on the temperature of the exhaust heat obtained from the exhaust heat temperature sensor , operates the heat pump, and performs the first heating. While heating the first heating load with a medium, based on the temperature of the first heating load obtained from the first heating load temperature sensor, the first heating load or The heating / cooling device, wherein the first heating medium is heated by the other heat source . A heat pump that heats the first heating medium that heats the first heating load , introduces exhaust heat belonging to the factory, cools the heat pump, and can derive the heat pump ;
An exhaust heat temperature sensor for detecting the temperature of the exhaust heat;
Waste heat calorie adjusting means for adjusting the temperature of the exhaust heat;
Another heat source for heating the first heating load or the first heating medium;
The heat pump, the exhaust heat calorie adjusting means, and an automatic controller for controlling other heat sources ,
The automatic control device adjusts the exhaust heat to a predetermined temperature by the exhaust heat temperature adjusting means based on the temperature of the exhaust heat obtained from the exhaust heat temperature sensor , operates the heat pump, and performs the first heating. The heating / cooling apparatus , wherein the first heating load after being heated with a medium is further heated with the other heat source to be evaporated . The exhaust heat heats the second heating load
The heating / cooling device according to any one of claims 4 to 6, wherein When the temperature of the exhaust heat falls below a lower limit temperature, the automatic control device throttles the output of the heat pump or stops the heat pump to maintain or increase the temperature of the exhaust heat.
The heating / cooling apparatus according to claim 7. The exhaust heat is a subsequent process for waste water, makeup water, exhaust, exhaust gas, equipment heat release, work heat release, air conditioning heat release, cogeneration exhaust heat, heat from hydraulic oil, hot water washing product The heat transferred to the washing water in the washing process, waste heat generated from factory air conditioning, boiler exhaust heat, equipment cooling water, welding machine cooling water, hydraulic equipment cooling water, heat radiation from the drying process, gold It is at least one of mold cooling water, air compressor cooling water, heat from required cooling equipment, well water
The heating / cooling device according to any one of claims 4 to 8, wherein A heat pump for heating a heating medium for heating a heating load;
A heating medium circulation path for circulating the heating medium between the heating load and the heat pump;
A heating load temperature sensor for detecting the temperature of the heating load;
Other heat sources that heat the heating load,
An automatic control device for controlling the heat pump and the other heat source;
The automatic control system will strike operation start of the heat pump, based on said temperature of the heating load the heating load obtained from the temperature sensor, wherein the other heat source heated the heating load, the temperature is increased said heating load wherein in the heating medium circulation path depending on circulation of the heating medium, heating and cooling apparatus, characterized by raising the temperature of the said heating medium above normal operating conditions the lower limit of the heat pump between the heat pump. The heating load, the first heating load, or the second heating load includes: a fluid to be treated in a sterilizer, a regeneration side fluid in a dehumidification rotor in a desiccant air conditioner, a stock solution in a stock temperature controller, a raw material in a concentration condenser, and a cleaning device. Cleaning liquid, pretreatment tank, drying furnace air installed in the factory, booth air conditioning, recycling air conditioning, factory air conditioning, office air conditioning, indoor air conditioning, clean room air conditioning, air conditioning to maintain a constant temperature or humidity throughout the year, Or heating at least one of the water supplies
The heating / cooling device according to any one of claims 1 to 10, wherein the heating / cooling device according to any one of claims 1 to 10 is provided. The other heat source is at least one of a heat pump steam / hot water generator, a heat pump that generates only steam, a boiler, steam, an electric heater, and an air-cooled heat pump.
The heating / cooling device according to any one of claims 2, 3, 5 to 11.

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