JP2011069599A - Air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioning system with very favorable energy efficiency. <P>SOLUTION: The air conditioning system 1 is installed in a factory producing hot drain X, and includes a reheater 18 heating outside air A taken in from an outside air intake port 10, an outdoor unit 2 having a cooling coil 16 cooling the outside air A, a heat pump 4 heating and supplying a heating medium to the reheater 18 and cooling and supplying a cooling medium to the cooling coil 16, and a heat exchanger 40 heating the cooling medium. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an air conditioning system for keeping indoor temperature or humidity constant.

  The painting booth in the factory that is indoors is equipped with an air conditioning system that adjusts the temperature and humidity to be constant while replacing the air inside the booth with the outside air in view of maintaining the quality of the coating film. As a system, an air conditioning system described in Patent Document 1 below is known. In this air conditioning system, the outside air is appropriately cooled and humidified by spraying, then water drops are removed by an eliminator, heated by a heater using high-temperature steam as a heat source, passed through a filter, and introduced into a painting booth by a fan. The Note that exhaust circulation air conditioners described in Patent Documents 2 and 3 below are known as air conditioners that perform recycle air conditioning. For the purpose of energy saving, the exhaust circulation air conditioner sucks and reuses the air conditioning exhaust at other locations and supplies it as adjusted air.

JP 2007-162996 A JP 2005-344918 A JP-A-5-76725

  However, in the air conditioning system of Patent Document 1, heating by the heater or cooling by the spray is performed in an independent state, and thus there is a limit to the degree of improvement in energy efficiency. SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide an extremely energy efficient air conditioning system.

  In order to achieve the above-mentioned object, the invention described in claim 1 includes a heating unit for heating the base air taken in from the base air intake port, an air conditioner having a cooling unit for cooling the base air, and the heating. The heat medium is heated and supplied to the means, and the heat pump is supplied to the cooling means after being cooled, and a cooling medium heater for heating the cooling medium is provided.

  In the present invention, the heat pump may directly heat the heating medium that heats the base air (supply of hot water or a heating refrigerant), or another heating that owns the heating medium that heats the base air. You may heat with a medium (internal heating medium). In the former case, the heating medium directly reaches the heating means. In the latter case, the internal heating medium is heated in the heat pump, and heat exchange between the internal heating medium and the heating medium is performed. Similarly, in the present invention, the heat pump may directly cool the cooling medium that cools the base air (supply of cold water or a cooling refrigerant, etc.) or another cooling medium that cools the base air itself. You may cool with a cooling medium (internal cooling medium).

  In addition to the above-mentioned object, the invention described in claim 2 achieves the object of making it possible to easily carry out heating on the cooling side by, for example, separating an existing circuit in a factory or the like from a circuit added for realizing the present invention. Therefore, in the above invention, the cooling medium heater is 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. To do.

  In addition to the above object, the invention described in claim 3 achieves the object of providing an air conditioning system that is efficient and easy to introduce even in a factory where there is not enough heat of exhaust gas or exhaust hot water. The cooling-side heating medium is supplied from a cooling-side heating medium supply heat pump.

  In order to achieve the object of further improving the efficiency in addition to the above object, the invention according to claim 4 is characterized in that, in the above invention, the cooling side heating medium is exhausted hot water, makeup water, exhaust gas generated from a factory. The exhaust gas, the cleaning water, the heat radiation of the equipment, the heat radiation of the workpiece, the exhaust heat of the air conditioning, or the exhaust heat of the cogeneration are included.

  The invention according to claim 5 is characterized in that, in addition to the above object, in order to achieve the object of further improving the efficiency, in the above invention, the cooling medium heater is a heating tower. is there.

  The invention described in claim 6 is characterized in that, in addition to the above object, in order to achieve the object of further improving efficiency, in the above invention, the cooling medium heater is a heat pump for heating. is there.

  In addition to the above-mentioned object, the invention described in claim 7 makes it easy to control by changing the cooling medium side gently, and enables various systems to be connected to the cooling side, thereby enabling a flexible and expandable system construction. In order to achieve the object, in the above invention, a cooling medium tank is interposed between the heating heat pump and the heat pump.

  In addition to the above object, the inventions according to claims 8 and 9 achieve the object of enabling the highly efficient air conditioning to be executed automatically. In the above invention, the cooling side heating medium and the heat of the cooling medium The cooling-side heating medium heat exchange amount adjusting means for adjusting the exchange amount, a cooling temperature sensor for detecting a cooling medium temperature that is a temperature of the cooling medium, and the cooling temperature sensor are connected to each other, and the temperature obtained from the cooling temperature sensor An automatic control device that controls a heat exchange amount in the cooling side heating medium heat exchange amount adjusting means according to a cooling medium temperature, or the cooling side heating medium heat exchange amount adjusting means includes the cooling side heating medium and And / or a flow rate adjusting means for adjusting a flow rate of the cooling medium to the cooling medium heater, wherein the automatic control device controls a flow rate in the flow rate adjusting means according to the cooling medium temperature. It is characterized in that the or the. The cooling medium temperature (cooling return temperature) may be the temperature of the cooling medium, and this cooling medium is directly cooled by the heat pump (the heat pump refrigerant is used as the cooling medium) or the internal cooling medium of the heat pump. The cooling may be performed at any time (cooling water cooled by an internal cooling medium is used as a cooling medium).

  The invention according to claim 10 adjusts the amount of heating load applied to the heat pump of the heating medium in the invention, in order to achieve the object of automatically executing extremely efficient air conditioning in addition to the object. A heating load amount adjusting means, and a cooling temperature that detects a cooling supply temperature that is a temperature when the cooling medium is supplied from the heat pump and / or a cooling return temperature that is a temperature when the cooling medium returns to the heat pump. A sensor, another heat source for assisting heating of the heating medium, the cold temperature sensor and the other heat source, and the heating according to the cold supply temperature and / or the cold return temperature obtained from the cold temperature sensor The apparatus further comprises an automatic control device for controlling a heating load amount in the load amount adjusting means and adjusting a heating supply amount by the other heat source. It is. The cold temperature sensor includes one that detects the cold water temperature in the cold water tank, and the cold heat supply temperature and / or the cold return temperature includes the cold water temperature in the cold water tank.

  In addition to the above-mentioned object, the invention according to claim 11 adjusts the cooling load amount of the cooling medium to the heat pump in the invention to achieve the object of enabling the highly efficient air conditioning to be automatically executed. A cooling load amount adjusting means, and a heating temperature that detects a heating supply temperature that is a temperature when the heating medium is supplied from the heat pump and / or a heating return temperature that is a temperature when the heating medium returns to the heat pump. A sensor, another cooling source for assisting cooling of the cooling medium, the thermal temperature sensor, and the other cooling source, and depending on the thermal supply temperature and / or the thermal return temperature obtained from the thermal temperature sensor And further comprising an automatic control device for controlling a cooling load amount in the cooling load amount adjusting means and adjusting a cooling heat supply amount by the other cooling heat source. Is shall. The warm temperature sensor includes a sensor that detects the warm water temperature in the warm water tank, and the warm water supply temperature and / or warm return temperature includes the warm water temperature in the warm water tank.

  In addition to the above object, the invention described in claim 12 achieves the object of further improving efficiency when cooling of the base air by the cooling means of the air conditioner is unnecessary in winter or at night. In the invention, when the supply of the cooled cooling medium to the cooling means is unnecessary, the temperature of the cooling medium increases so that the efficiency of the heat pump becomes better.

  In order to achieve the object of the invention described in claim 13 in addition to the above object, it is possible to cope with even a large scale, and to flexibly cope with various scales. A plurality of medium supply heat pumps are provided.

  In addition to the above object, the invention described in claim 14 achieves the object of automatically operating under various conditions in order to continue the operation with excellent energy saving. Or it has an automatic control device which changes the number of operation of the plurality of cooling pumps for supplying the cooling side heating medium according to the state of the cooling medium.

  In addition to the above object, the invention described in claim 15 achieves the object of enabling a smoother automatic operation. In the above invention, the automatic control device is configured such that the load on the cooling medium is the heating medium. When the load decreases with respect to the load, a part of the plurality of cooling-side heating medium supply heat pumps is set in an operation standby state.

  In addition to the above object, the invention described in claim 16 is capable of accommodating various scales at low cost, and is capable of more appropriately introducing booth air conditioning using the heat pump 4 that is excellent in energy efficiency. To achieve this, in the above invention, the number of the cooling medium heaters is plural.

  In addition to the above-mentioned object, the invention described in claim 17 can automatically and appropriately perform control related to adjustment of the cold water load and prevention of supply of cold water or hot water, and ensures a more efficient and stable operation. In order to achieve the object to be achieved, in the above invention, 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 is provided. It is a feature.

  In addition to the above object, the invention described in claim 18 is capable of suppressing power consumption and capable of continuing the operation of the heat pump 4, and providing a booth air conditioner that is further excellent in energy saving and operational stability. In order to achieve this, in the above invention, the operation mode of the heat pump can be switched between a hot water follow-up mode and a cooling mode.

  In order to achieve the object of adjusting the temperature of the heating medium by a simple operation in addition to the above object, the invention described in claim 19 increases or decreases the amount of heating in the cooling medium heater in the above invention. Thus, the temperature of the heating medium is increased or decreased.

  In addition to the above object, the invention described in claim 20 is provided with an air-cooling heat pump that can heat the cooling medium for ensuring balance and can also cool the cooling medium when the cooling load is relatively increased. Furthermore, in order to achieve the purpose of switching the operation of the air-cooled heat pump smoothly and in an energy-saving state, in the above invention, the air-cooled heat pump is provided with an air-cooled heat pump that supplies a medium for heating or cooling the cooling medium. After the medium of the heat pump is cooled or heated by the cooling medium, the heating or cooling of the medium of the air-cooled heat pump is switched.

  In addition to the above-mentioned object, the invention described in claim 21 is provided with the above-mentioned object, in order to achieve the object of more smoothly performing the operation switching, including the other auxiliary heat source for heating or cooling the medium. The cooling or heating by the other auxiliary heat source is performed in accordance with the cooling or heating of the medium by the cooling medium.

  In order to achieve the object of effectively preventing shortage of heat and overcooling with a simple configuration or operation in addition to the above object, the invention according to claim 22 is the above invention, wherein the cooling side heating medium is The cooling water and / or cold water in the facility requiring cooling, further comprising a cooling device for cooling the cooling water and / or the cooling water to a predetermined temperature and supplying the cooling medium heater to the cooling medium heater, and equipment cooling water temperature adjusting means. It is characterized by this.

  In addition to the above object, the invention described in claim 23 achieves the object of continuously providing heating or cooling by a heat pump in a state where the initial cost and running cost are low and heat recovery is feasible in a simple configuration. Therefore, in the above invention, the heat pump is operated in a state in which a cooling medium having a cooling heat amount exceeding a cooling load amount is supplied in the cooling medium following operation.

  In order to achieve the object of continuing the operation of the heat pump that is energy saving without performing complex control in addition to the above object, the invention according to claim 24 is the above invention, wherein the cooling side heating medium is: Supplied from an air-cooled heat pump, the air-cooled heat pump maintains the cooling side heating medium at a predetermined temperature.

  In order to achieve the above-mentioned object, the invention described in claim 25 includes a heating unit for heating the base air taken in from the base air intake port, an air conditioner having a cooling unit for cooling the base air, and the heating. A heat pump that heats and supplies the heating medium to the cooling unit and supplies the cooling medium to the cooling unit by cooling, another heat source that assists heating of the heating medium, and another cooling heat source that assists cooling of the cooling medium The heat pump is capable of heating medium follow-up operation and cooling medium follow-up operation, and when the cooling medium falls below a predetermined temperature, the heating medium follows operation from the heating medium follow-up operation to the cooling medium follow-up operation. When the temperature exceeds a specific temperature, the cooling medium following operation is switched to the heating medium following operation.

In order to achieve the above object, the invention described in claim 26 is a heating means for heating the base air taken in from the base air inlet, an air conditioner having a cooling means for cooling the base air, and the heating. The heating medium is heated and supplied to the means, and the cooling medium is supplied from the heat pump side for heating, exhaust water from the factory, exhaust gas, exhaust gas, makeup water, washing water, heat radiation from the equipment, heat radiation from the work, air conditioning exhaust. A heat pump that can be switched and introduced by cooling from the side containing at least one of heat (air conditioning of another system) or exhaust heat of cogeneration (heat belonging to the factory); 2 a cooling heat pump for supplying a cooling medium, and when the cooling medium is introduced from the heating heat pump side, the heat pump, When at least one of gas or make-up water is commensurate with cooling by the heat pump or has more heat, the cooling medium is removed from the side containing at least one of the exhaust water, exhaust, exhaust gas, or make-up water. It is characterized by switching to be introduced.

  In order to achieve the above object, according to a twenty-seventh aspect of the present invention, there is provided an air conditioner having a heating unit for heating the base air taken in from the base air intake port, and a heating medium is heated and supplied to the heating unit. In addition, for the cooling medium, at least one of exhaust water from the factory, exhaust, exhaust gas, makeup water, washing water, equipment heat dissipation, work heat dissipation, air conditioning exhaust heat (another system air conditioning), or cogeneration exhaust heat A heat pump that can be introduced from the side including one (heat belonging to the factory), cooled, and led out, and a second heating medium supplied to the heating medium and / or second heating means provided in the air conditioner And a heat source for heating the other.

  In order to achieve the object of providing a booth air-conditioner that is more efficient and can cope with various scales in addition to the above object, the invention described in claim 28 is characterized in that The apparatus is characterized by a plurality.

  In addition to the above-mentioned object, the invention according to claim 29 achieves the object of providing booth air-conditioning with further improved energy saving by making it possible to use recycled air-conditioning. It is characterized by including an air conditioner.

  According to the present invention, the heating medium and the cooling medium are collectively heated by the heat pump, and heat exchange is performed between the waste water from the factory, the hot water from a separate heat pump or exhaust (cooling side heating medium), and the cooling medium. Or the cooling medium is heated with a heat pump for heating or the like. Therefore, by applying the cooling side heating medium, it is possible to prevent overcooling according to the amount of heating and to balance the cooling medium with respect to the heating medium, so that the cooling of the heat pump is extremely efficient and stable. There is an effect that it can be continued in a state.

It is a block diagram of an air-conditioning system concerning the 1st form of the present invention. It is a flowchart which shows operation | movement of the air conditioning system of FIG. 2A is an air diagram when the cooling load is relatively large, and FIG. 2B is an air diagram when the cooling load is relatively small. (A) Block diagram of air conditioning system according to second embodiment of the present invention, (b) Block diagram around heat pump during cooling, (c) Block diagram around heat pump when cooling is not required, (d) Air line during cooling Fig. (E) Air diagram when cooling is not required. (A) And (b) is a block diagram when the cooling load of the air conditioning system which concerns on the 3rd form of this invention is large, (c) is a block diagram when the cooling load of the said air conditioning system is small. (A) is a block diagram at the time of cooling unnecessary of the air-conditioning system of FIG. 5, (b) is a block diagram which concerns on the 4th form of this invention. It is a flowchart which shows operation | movement of the air conditioning system of Fig.5 (a)-(c) and Fig.6 (a). (A)-(c) is an air line figure corresponding to Drawing 5 (a) or (b), Drawing 5 (c), and Drawing 6 (a) in order. It is a block diagram when the air-conditioning system according to the fifth embodiment of the present invention has a large cooling load, (b) a block diagram when the cooling load is small, and (c) a block diagram when cooling is not required. It is a block diagram when the air-conditioning system concerning the 6th form of the present invention has a large cooling load, (b) a block diagram when the cooling load is small, and (c) a block diagram when cooling is unnecessary. (A) Block diagram in summer etc., (b) Block diagram in winter etc. of the air conditioning system which concerns on the 7th form of this invention. It is a block diagram of the air conditioning system which concerns on the 8th form of this invention. It is a block diagram of the air conditioning system which concerns on the 9th form of this invention. It is an air line figure which concerns on the air conditioning system of FIG. It is a table | surface which shows the various outputs etc. which concern on the air conditioning system of FIG. It is a table | surface, an airline figure, a block diagram in the summer etc. of the air conditioning system which concerns on 10th form of this invention, and a table | surface in the summer etc. of the air conditioning system which concerns on a conventional system. It is the table | surface / air diagram / block diagram in the mid season etc. of the air conditioning system which concerns on 10th form of this invention, and the table in the mid season etc. of the air conditioning system which concerns on a conventional system. It is a table | surface, an airline figure, a block diagram in the winter etc. of the air conditioning system which concerns on 10th form of this invention, and a table | surface in the winter etc. of the air conditioning system which concerns on a conventional system. It is a table showing the CO ₂ emissions to energy consumption or the like of the air-conditioning system and air conditioning system according to a conventional method according to the tenth embodiment of the present invention. It is a block diagram of the air conditioning system which concerns on the 11th form of this invention. It is a flowchart of the starting control which concerns on the air conditioning system of FIG. It is a flowchart of the cold water load adjustment control which concerns on the air conditioning system of FIG. It is a flowchart of the hot water supply shortage prevention control which concerns on the air conditioning system of FIG. It is a flowchart of the cold water supply shortage prevention control which concerns on the air conditioning system of FIG. It is a block diagram of the air conditioning system which concerns on the 12th form of this invention. It is a flowchart of the starting control which concerns on the air conditioning system of FIG. It is a flowchart of the cold water load adjustment control which concerns on the air conditioning system of FIG. It is a block diagram of the air conditioning system which concerns on the 13th form of this invention. It is a flowchart which concerns on operation | movement of the air conditioning system of FIG. It is a block diagram of the air conditioning system which concerns on the 14th form of this invention. It is a block diagram in case the air-conditioning system which concerns on 15th form of this invention has a large cooling load, (b) It is a block diagram in case a cooling load is small. It is a block diagram in case the air-conditioning system which concerns on 16th form of this invention has a large cooling load, (b) It is a block diagram in case a cooling load is small. (A) The block diagram in case an air-conditioning load is heavy, (b) The block diagram in case an air-conditioning load is light, (c) The block diagram in case an air-conditioning load is small. FIG. 34 is a block diagram when the air conditioning system of FIG. 33 has no (a) cooling load, and (b) a block diagram when the heating load is heavy. (A) A block diagram when the cooling load is heavy, (b) A block diagram when the cooling load is light, (c) A block diagram when the cooling load is small, in the air conditioning system according to the eighteenth aspect of the present invention. (A), (b) is a block diagram when the air cooling heat pump fails in the air conditioning system of FIG. 35, and (c) is a block diagram when the cooling load of the air conditioning system according to the nineteenth embodiment of the present invention is small. is there. (A) The block diagram in case an air-conditioning load concerning a 20th form of this invention is heavy, (b) The block diagram in case an air-conditioning load is light, (c) The block diagram in case an air-conditioning load is small. (A), (b) is a block diagram when there is no cooling load in the air conditioning system of FIG. 37, (c) is a block diagram when there is no cooling load of the air conditioning system according to the twenty-first embodiment of the present invention. . (A) A block diagram when the cooling load is heavy, (b) A block diagram when the cooling load is light, (c) A block diagram when there is no cooling load, of the air conditioning system according to the twenty-second embodiment of the present invention. It is a block diagram of the air conditioning system which concerns on the 23rd form of this invention. It is a flowchart which concerns on operation | movement of the air conditioning system of FIG. It is a flowchart which concerns on operation | movement of the air conditioning system which concerns on the 24th form of this invention. It is a flowchart which concerns on operation | movement of the air conditioning system which concerns on 25th form of this invention. It is a block diagram of the air conditioning system which concerns on the 26th form of this invention. It is a flowchart which concerns on operation | movement of the air conditioning system of FIG. (A) is a block diagram in the winter etc. of the air conditioning system concerning the 27th form of the present invention, and (b) is a block diagram in the winter etc. of the air conditioning system concerning the 28th form of the present invention. (A) is a block diagram in the winter of the air conditioning system according to the twenty-ninth embodiment of the present invention, (b) is a block diagram in the winter of the air conditioning system according to the thirtieth embodiment of the present invention, (c) It is a block diagram of the air conditioning system which concerns on the 31st form of this invention. It is a block diagram at the time of (a) heating operation, (b) operation switching, and (c) cooling operation of the air cooling heat pump in the air conditioning system according to the thirty-second embodiment of the present invention. It is a flowchart which shows (a) block diagram and (b) operation | movement of the air conditioning system which concerns on a 33rd form. It is a block diagram of the air conditioning system which concerns on a 34th form. It is a block diagram of the air conditioning system which concerns on a 35th form.

  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 an air conditioning system 1 according to the first embodiment, and the air conditioning system 1 is used in an automobile painting factory (not shown). The air conditioning system 1 is installed on the basis of booth air conditioning for supplying outside air (fresh air) as base air to various paint booths of automobiles through respective ducts (not shown). The objects to be painted (work) can be automobile body parts (bumpers, side panels, wheel caps, etc.), electrical equipment, communication equipment, building materials, leisure fields or parts thereof. The air conditioning system 1 may be used for air conditioning related to clean rooms such as an electronic factory and a pharmaceutical manufacturing factory, in addition to being used for painting booth air conditioning related to these works.

  The air conditioning system 1 includes an external air conditioner 2 as an air conditioner that takes in outside air A and adjusts air B adjusted as booth air conditioning, and an exhaust heat recovery type heat pump 4 connected to the external air conditioner 2.

  The external air conditioner 2 includes an outside air inlet 10 as a base air inlet, a preheater 12, a washer 14, a cooling coil 16, a reheater 18, and a blower 20 that are arranged in this order from the outside air inlet 10 side. I have. The preheater 12 appropriately heats (preheats) the outside air A taken in from the outside air inlet 10. The washer 14 appropriately blows water to the outside air A that has passed through the preheater 12 to remove dust and cool and humidify the outside air A. The cooling coil 16 as a cooling means applies cold heat to the outside air A that has passed through the washer 14, and appropriately cools and dehumidifies the outside air A. The reheater 18 as a heating unit applies heat to the outside air A that has passed through the cooling coil 16 to heat it again (reheat), and supplies the outside air A as the adjusted air B to the blower 20.

  The heat pump 4 includes a cooling side supply pipe 30 that sends a cooling medium (either refrigerant (gas) or cold water) to the cooling coil 16, a cooling side return pipe 32 that collects the cooling medium from the cooling coil 16, and a heating medium to the reheater 18. It has a heating side supply pipe 34 (a dashed line in the figure) for sending (refrigerant (gas) or warm water), and a heating side return pipe 36 (a dashed line in the figure) for recovering the heating medium from the reheater 18. Each pipe is provided with one or more heat exchangers or tanks (not shown) or flow control valves or pumps (which can be flow control means, load control means, heating load control means, cooling load control means). Sometimes. In addition, the arrangement and the like of the pipes may be appropriately changed, such as branching or gathering in the middle of various pipes.

  The heat pump 4 collectively generates a heating medium supplied to the reheater 18 and a cooling medium supplied to the cooling coil 16. The heat pump 4 generates cold heat (cooling medium) and simultaneously generates heat (heating medium) using exhaust heat generated at that time, and supplies the heat to the outside. Here, 7 degrees (Celsius, The same applies hereinafter) “High F Mini HR” manufactured by Kobe Steel, Ltd., which can supply cold water of about 30 ° C. and hot water of about 70 ° C. at the same time. The heat pump 4 needs to balance hot / cold water due to the characteristics of hot / cold water being supplied at the same time. In order to extract a large amount of high-temperature heat, the high-temperature heat is sufficiently absorbed and returned to the target, and a large amount of cold / heat is also generated. After being taken out, it is necessary to return with sufficient heat. In addition, as the heat pump 4, you may use what can supply the hot water of a maximum of 95 degree | times.

  The air conditioning system 1 is installed here in a factory that also performs body pressing, welding, and the like. From the factory, exhaust heat water X such as compressor cooling water, spot welder cooling water, or cogeneration system cooling water is contributed as heat (exhaust heat) belonging to the factory. In other words, the air conditioning system 1 is installed in a factory that generates the exhausted warm water X as a cooling side heating medium. It is to be noted that the booth air conditioning (temperature-controlled air conditioning) including the painting target (work) exemplified above is generally performed in a factory where the waste water X is installed with other equipment.

  Further, the cooling side return pipe 32 in the air conditioning system 1 is provided with a heat exchanger 40 as a cooling medium heater, and heat exchange introduction for introducing the exhaust hot water X as a cooling medium heating medium into the heat exchanger 40. A pipe 42 and a heat exchange derivation pipe 44 for deriving the exhausted warm water X after the heat exchange are connected. The heat exchanger 40 exchanges the heat of the exhaust hot water X and the cold heat (heat of the cooling medium in the cooling side return pipe 32). The heat exchange introduction pipe 42 or the heat exchange outlet pipe 44 is provided with a flow rate adjustment valve 46 as a flow rate adjustment unit belonging to the cooling side heating medium heat exchange amount adjustment unit. The flow control valve 46 may be installed in the cooling side supply pipe 30 or the like. Further, as the flow rate adjusting means, in addition to the flow rate adjusting valve 46, an inverter pump for adjusting the discharge amount, or a combination thereof may be adopted. Furthermore, as a cooling side heating medium heat exchange amount adjusting means, a means for adjusting the flow rate of the cooling medium entering the heat exchanger 40, a means for interposing a heat absorber or a radiator, or a combination of these may be used. Can be adopted. In addition, instead of the waste water X, exhaust, exhaust gas, makeup water, equipment heat dissipation, work heat dissipation, air conditioning (in this case, factory air conditioning for employees, not booth air conditioning), exhaust heat (return to cold water), or Any combination of these including the waste water X can be used, and heat can be exchanged between these and the cooling medium.

  In the air conditioning system 1, a cold supply amount adjustment valve 48 as a cooling medium supply flow rate adjustment unit is interposed between the cooling side supply pipe 30 and the cooling side return pipe 32. The cooling heat supply amount adjusting valve 48 sends a part of the cooling medium in the cooling side supply pipe 30 to the cooling side return pipe 32 and sends the other part to the cooling coil 16, whereby the amount of cold heat to the cooling coil 16 is sent. To adjust the degree of cooling and dehumidification of the outside air A passing through the cooling coil 16. The cold supply amount adjustment valve 48 is controlled by an automatic control device. The cooling side return pipe 32 is provided with a temperature sensor (cooling temperature sensor) (not shown) that is electrically connected to the automatic control device, and the temperature sensor detects the temperature of the cooling medium in the cooling side return pipe 32 ( (Cooling medium temperature, cooling return temperature) can be grasped and transmitted to the automatic control device. The cooling medium supply flow rate adjusting means can also be changed in the same manner as the flow rate adjusting means, or can be omitted depending on the type of the external air conditioner such as a type using a washer instead of the cooling coil 16. In addition, although the operation becomes extremely smooth when the cooling medium temperature is the cold return temperature, the cold water temperature that is the cold water temperature in the cooling side supply pipe 30 is adopted, or the cold water in the tank when the cold water tank is provided. The temperature may be adopted, and the installation location of the sensor can be similarly changed.

  In addition, in the air conditioning system 1, a heat supply amount adjustment valve 49 as a heating medium supply flow rate adjusting means is interposed between the heating side supply pipe 34 and the heating side return pipe 36. The warm heat supply amount adjustment valve 49 sends a part of the heating medium in the heating side supply pipe 34 to the heating side return pipe 36 and sends the other part to the reheater 18 and the like, whereby the amount of warm heat to the reheater 18 and the like. And the amount of heat of the outside air A passing through the reheater 18 and the like is adjusted. The heat supply amount adjustment valve 49 is controlled by an automatic control device. The heating-side return pipe 36 is provided with a temperature sensor (not shown) that is electrically connected to the automatic control device, and the temperature sensor detects the temperature of the heating medium in the heating-side return pipe 36 (thermal return temperature). It can be grasped and transmitted to the automatic control device. The heating medium supply flow rate adjusting means can be changed in the same manner as the flow rate adjusting means. As will be described later, the heat pump 4 basically operates following the heat, but the heat supply amount adjustment valve 49 finely adjusts the heating amount. The heat supply amount adjusting valve 49 can be omitted depending on the type of the external air conditioner such as a type using a washer instead of the reheater 18.

  Such an air conditioning system 1 operates as described below.

  The automatic control device is rainy in the middle of summer, spring and autumn, etc., and the thermal load is sufficiently applied together with the thermal load, and when it is easy to balance the thermal load against the thermal load, The amount of heating of the cooling medium in the cooling side return pipe 32 by heat exchange is relatively reduced.

  For example, when the heating load (heating load / thermal load) of the reheater 18 is 800 kW (kilowatt) and the cooling load (cooling load) of the cooling coil 16 is 300 kW, the automatic control device An electric input V of 200 kW is applied to supply 800 kW of heat so as to follow the heat. The 800 kW heat is supplied to the reheater 18 through the heating side supply pipe 34 and used to heat the outside air A. Moreover, the heat pump 4 supplies 600 kW of cold with the supply of warm heat. The cooling heat 600 kW is supplied to the cooling coil 16 through the cooling side supply pipe 30, and the outside air A passing through the cooling coil 16 is sufficiently cooled by the cooling heat of 300 kW, but the cooling side return pipe 32 is still capable of cooling 300 kW. to go into. The automatic control device controls the flow rate adjusting valve 46 (or the cold supply amount adjusting valve 48) so that the 300 kW exhaust hot water X reaches the heat exchanger 40, and the heat pump 4 is heated (heat exchange) by the exhaust hot water X. By taking away 300 kW of cold energy to return to the temperature, it is possible to balance the cold energy even if it follows the heat. The balance between warm and cold heat allows the operation of the heat pump 4 to be continued.

  On the other hand, the automatic control device is in the middle season, winter season, etc., and when the cold load is small relative to the thermal load, the automatic control device is also operated with the heat pump 4 following the warm temperature to supply cold heat, The amount of heating by the exhausted hot water X is increased by the amount that the cooling heat to be circulated to the heat pump 4 increases with a low cooling load, so that the balance between the heating and cooling is maintained. In other words, in order to operate the heat pump 4 to follow a relatively large thermal load, cold heat having a larger amount of cold than the cold load is supplied, and the cooling coil 16 is used to return to the heat pump 4 without sufficiently using the cold heat. On the other hand, heat exchange with the warm heat by the waste hot water X is performed in the heat exchanger 40, and it becomes possible to balance cold with warm heat that is used relatively frequently.

  For example, when the cooling load decreases to 100 kW with respect to the heating load of 800 kW, the automatic control device supplies the heating pump 4 with the heating temperature of 800 kW so as to follow the heating load, and generates the cooling heat of 600 kW. Only 100 kW is used, and 500 kW surplus from the viewpoint of balance. Therefore, the automatic control device controls the flow rate adjusting valve 46 to increase the amount of heating by the exhausted hot water X to 500 kW, cancel the remaining 500 kW of cold, and ensure the balance of cold to hot. It should be noted that a chilled water header (not shown) in the heat pump 4, a cooling medium tank interposed in the cooling side return pipe 32, a return cooling medium (pipe to the cooling side return pipe 32) in the cold heat supply amount adjustment valve 48, or a combination thereof. Heating with the waste water X may be performed.

  That is, fluctuations in the heating load and cooling load (seasonal fluctuations, fluctuations due to changes in the state of the outside air such as temperature and humidity) are dealt with by adjusting the heat pump 4 and the flow rate control valve 46. These adjustments grasp the temperature near the heat pump 4 connection part of the cooling side return pipe 32 (cooling return temperature) and the temperature near the heat pump 4 connection part of the heating side return pipe 36 (heat return temperature). This is automatically performed by an automatic control device (not shown) connected to the sensor. The automatic control device operates the heat pump so as to follow the heat load as a reference, and when the cold energy supplied by such follow-up changes or the cold load fluctuates, the amount of heating with respect to the cold heat is It adjusts by increasing / decreasing the flow volume of the waste water X to the heat exchanger 40 with the flow control valve 46, and it balances cold with respect to heat. The automatic control device may be configured by a control device provided for each of the heat pump 4 and the flow rate control valve 46, or may be an independent separate device. In addition, the temperature sensor may be disposed on at least one of the cooling coil 16, the reheater 18, another pipe, and the heat exchanger 40, or may be disposed on the cooling coil 16 side of the cooling side return pipe 32.

  A specific example of control of the flow control valve 46 by such an automatic control device will be described mainly with reference to FIG. When the automatic control device permits the operation of generating cold heat and recovering the heat of exhaust heat X so as to follow the heat based on the heating load (Yes in step S1), the cold heat supply amount adjustment valve 48 is closed. It is judged whether it is (step S2). The automatic control device sets the set value of the cold return temperature to 40 degrees when the cold supply amount adjustment valve 48 is closed (step S3), and returns to the cold return when the cold supply amount adjustment valve 48 is not closed. The temperature set value is set to 17 degrees (step S4).

  When the cooling return temperature of the heat pump 4 obtained from the temperature sensor falls below the set value minus 2 degrees, the automatic control device executes steps S6a to S6c (Yes in step S5), while the cooling return temperature of the heat pump 4 When the value exceeds the set value plus 1 degree, steps S8a to S8c are executed (No in step S5, Yes in step S7), and the cold return temperature of the heat pump 4 is within a predetermined range including the set value (set value minus 2). If it is above the set value plus 1 degree or less), the operation returns to the start and continues the automatic operation (No in step S7).

  In steps S6a to S6c, in view of the fact that the cooling heat is not sufficiently deprived with respect to the heat, in order to bring the cooling return temperature of the heat pump 4 close to the set value, the cooling medium and the exhaust hot water in the cooling side return pipe 32 The flow rate adjustment valve 46 is gradually opened so as to increase the amount of heat exchange with X.

  On the other hand, in Steps S8a to S8c, in view of the fact that the cooling heat is sufficiently used, the cooling medium in the cooling-side return pipe 32 and the exhaust hot water X are used to bring the cooling return temperature of the heat pump 4 close to the set value. The flow rate adjusting valve 46 is gradually throttled so as to reduce the amount of heat exchange with.

  A specific example of adjustment of outside air A (generation of air B) by the air conditioning system 1 operating in this way will be described mainly based on FIG. 3 which is a schematic air diagram.

  As shown in FIG. 3 (a), the temperature (dry bulb temperature) of the outside air A is relatively high (but lower than air B), and the humidity (absolute humidity) is also commensurate with the temperature (state higher than air B). (White circle in the figure), first, the dust of the outside air A is removed by the washer 14. At this time, the relative humidity of the outside air A that has passed through the washer 14 becomes 100 percent (%), and the temperature slightly decreases. In this state, the outside air A passes through the cooling coil 16, and the cooling coil 16 supplied with the amount of cooling adjusted is cooled to the target humidity (air B). Then, the cooled outside air A passes through the reheater 18 that has received the adjusted amount of heat, and is heated until the target temperature is reached (black circle in the figure).

  On the other hand, when the temperature (dry bulb temperature) of the outside air A is relatively low (lower than the air B) and the humidity (absolute humidity) is in a degree corresponding to the air temperature (a state higher than the air B), As shown in FIG. 3 (b), the amount of cooling used (cooling load) is reduced by reducing the amount of cooling to the cooling coil 16, etc., but the automatic controller reduces the amount of heat exchanged with the waste water X by that amount. Increase and keep a balance between hot and cold.

  The air conditioning system 1 described above is installed in a factory that generates the waste water X, and has an external air conditioner 2 that includes a reheater 18 that heats the outside air A taken in from the outside air inlet 10 and a cooling coil 16 that cools the outside air A. And a heat pump 4 that heats and supplies the heating medium to the reheater 18 and supplies the cooling coil 16 with the cooling medium cooled, and a heat exchanger 40 that heats the cooling medium.

  Accordingly, the heat pump 4 is tried to operate in accordance with the heating load. However, the cooling load is too light and the cooling water does not return in a sufficiently deprived state, and the heat pump 4 does not balance the heating and cooling. The situation of stopping can be avoided, and heating or cooling can be provided by one heat pump 4. In addition, the heat pump 4 is operated in accordance with the cooling load, and it is not necessary to install another heat source as compared with the method of dealing with the insufficient heating load with another heat source such as a steam generator, etc. The air-conditioning system 1 can be reduced, energy for driving other heat sources is unnecessary, the energy of the waste water X that has been exhausted as it is, can be effectively used, and is excellent in energy saving. In addition, the emission of carbon dioxide by driving other heat sources can be reduced.

  It should be noted that the method of using the factory warm water X for heating the reheater 18 is not conceivable, but generally the temperature of the warm water X is about 10 to 50 degrees, and the exhaust warm water X does not have a sufficient temperature and is effective. Can not be heated. On the other hand, in the air conditioning system 1, since the factory waste water X is applied to the cooling medium having a low temperature, the heat of the waste water X can be used effectively.

  Moreover, since the cooling medium of the heat pump 4 is heated by the heat exchanger 40 that introduces the cooling medium and the exhaust warm water X and exchanges heat, the heating with the exhaust warm water X can be reliably performed at low cost, and the energy efficiency is extremely high. A good air conditioning system 1 can be provided appropriately.

  Furthermore, a flow rate adjustment valve 46 that adjusts the flow rate of the waste warm water X to the heat exchanger 40, a cooling temperature sensor that detects a cooling return temperature (cooling medium temperature) that is a temperature when the cooling medium returns to the heat pump 4, and And an automatic control device that is connected to the cold temperature sensor and controls the flow rate of the flow rate adjusting valve 46 in accordance with the cold return temperature obtained from the cold temperature sensor.

  Therefore, the amount of heat exchange with the factory waste water X can be automatically adjusted so that the return temperature or amount of heat suitable for the heat pump 4 can be obtained, and extremely efficient heating or cooling is automatically performed. be able to.

  In addition, since the cold supply amount adjustment valve 48 is installed, the supply amount of the cold heat to the cooling coil 16 of the external air conditioner 2 can be finely adjusted by the cold supply amount adjustment valve 48 and the operation state of the heat pump 4 ( The operation of the heat pump 4 can be continued in a more stable state (cold heat supply state). It should be noted that the heat supply amount adjustment valve 49 also has the same effect regarding heat.

[Second form]
FIG. 4A is a schematic diagram of the air conditioning system 101 according to the second embodiment, and the configuration of the air conditioning system 101 is the same as that of the first embodiment and the modified example except for the configuration on the heating side.

  The air conditioning system 101 includes a second heating side supply pipe 104 branched from the heating side supply pipe 34 and a second heating side return pipe 106 that reaches the heating side return pipe 36. And the preheater 12 is connected to the 2nd heating side return pipe 106 as a heating means. The heating side supply pipe 34 downstream of the branching portion with the second heating side supply pipe 104 is provided with a heat supply amount adjustment valve 108 as a heating medium supply flow rate adjustment means related to the reheater 18 and the second heating. The side supply pipe 104 is provided with a second heat supply amount adjustment valve 109 as a heating medium supply flow rate adjustment means for the preheater 12. The remaining heating medium when the flow rate is adjusted by the heat supply amount adjustment valve 108 and the second heat supply amount adjustment valve 109 is returned to the heating side return pipe 36 by the heating side adjustment pipe 110 connected thereto.

  Such an air conditioning system 101 operates in the same manner as in the first embodiment, and also operates as described below.

  That is, the automatic control device controls the heat pump 4 to supply the heating medium to the second heating side supply pipe 104, and adjusts and supplies the heating medium to the preheater 12 in the same manner as the reheater 18. The preheater 12 receives the adjusted heating medium and preheats the taken-in outside air A.

  Further, the automatic control device closes the cooling heat supply amount adjustment valve 48 in the winter season or the intermediate season when cooling supply is unnecessary, and does not supply the cooling medium of the cooling supply pipe 30 to the cooling coil 16 and returns to the cooling return pipe. 32.

  Furthermore, when the cold supply amount adjustment valve 48 is closed, the automatic control device increases the supply temperature of the cooling medium of the heat pump for the purpose of further improving the efficiency of the heat pump 4. In this case, since cooling with the cooling medium is not performed, the cooling medium going-up temperature may be increased.

  For example, when the cooling by the cooling coil 16 is necessary, the automatic control device sets the cooling medium going temperature of the heat pump 4 to 7 degrees as shown in FIG. The cooling medium passes through the cooling coil 16 and exchanges heat with the outside air A, and is appropriately heated by the exhaust water X and returns to the heat pump 4 at 17 degrees.

  On the other hand, when the cooling by the cooling coil 16 is unnecessary and the cooling heat supply amount adjustment valve 48 is closed, the automatic control device changes the operation state of the heat pump, and as shown in FIG. Is raised to 30 degrees. Further, the automatic control device controls the flow rate adjusting valve 46 to heat the cooling medium by the exhaust hot water X at 1257 kW.

  4B and 4C, when the automatic control device causes the heat pump 4 to supply the heat 1500 kW, the heating medium going-out temperature is 60 degrees, and the return temperature is 50 degrees. In the case of 4 (b), the heating capacity of the heat pump 4 is 380 kW per unit, and the COP (Coefficient of Performance, efficiency) is 3.16, whereas in the case of FIG. 4 (c), the heating capacity of the heat pump 4 is It becomes 685 kW per unit and COP becomes 6.17, so that the heat pump 4 can be operated in a more efficient state.

  The adjustment from the outside air A to the air B in the air conditioning system 101 will be mainly described with reference to FIGS.

  When supplying cold heat to the external air conditioner 2 as shown in FIG. 4B, the outside air A is relatively high temperature (close to the target temperature but may be lower) as shown in FIG. 4D. Therefore, it is not preheated, first it receives an increase in absolute humidity and a temperature decrease by the washer 14, and then it is cooled by the cold supplied to the cooling coil 16 to be dehumidified to the target absolute humidity. 18 is heated to the target temperature (or target relative humidity).

  On the other hand, when it is not necessary to supply cold heat to the external air handler 2 as shown in FIG. First, the preheater 12 preheats, then the washer 14 increases and decreases the absolute humidity to the target humidity, and the reheater 18 further heats the target temperature (or target relative humidity).

  The automatic control device is electrically connected to a sensor (not shown) that grasps the state (temperature and / or humidity) of the outside air A, and the outside air A shifts from a state that requires cooling to a state that does not require cooling (temperature and temperature). And / or when the humidity becomes a predetermined value or less), the cooling heat supply amount adjustment valve 48 is closed to raise the cooling medium going temperature of the heat pump 4 (FIGS. 4A, 4C, and 4E), On the contrary, when the transition is made, the cooling medium going-out temperature of the heat pump 4 is returned and the cold supply amount adjusting valve 48 is opened (FIGS. 4B and 4D).

  The air conditioning system 101 of the second embodiment is the same as that of the first embodiment. Further, the heating medium is supplied to the preheater 12 via the second heat supply amount adjusting valve 109, and the cooling coil 16 is cooled. When supply of the cooling medium is unnecessary, the heat pump 4 is operated in a state where the temperature of the cooling medium is increased so that the COP of the heat pump 4 becomes better.

  Therefore, the same effect as the first embodiment is obtained, and preheating (preheating) is also performed by the heat pump 4, and the preheater 12 is combined with the reheater 18 to increase the operation mode (variation) and increase the efficiency. Furthermore, when the cooling medium circulates on the cooling side of the heat pump 4 and is not used in the cooling coil 16 of the external air conditioner 2, the COP of the heat pump 4 can be regarded as important with respect to the temperature of the cooling medium. Further, it is possible to ensure a more efficient and sustainable operation of the heat pump 4.

[Third embodiment]
FIGS. 5A to 5C and FIG. 6A are schematic views of the air conditioning system 151 according to the third embodiment, and the air conditioning system 151 is the second except for the configuration between the cooling coil 16 and the heat pump 4. It is the same including a form and a modification. In these figures, the circuit on the heating side is not shown.

  The air conditioning system 151 includes an air-cooling heat pump 154 that can perform a heating operation and a cooling operation on the cooling side. The air cooling heat pump 154 is also capable of waiting for heating and cooling. Here, the air cooling heat pump 154 is a group of air cooling heat pumps including four air cooling heat pumps 154a to 154d and other air cooling heat pumps (not shown). The air-cooled heat pump 154 may be a single unit or a plurality of air-cooled heat pump groups such as three or less.

  The air-cooled heat pumps 154a to 154d and the like appropriately include heat exchange introduction pipes 42a to 42d and the like that supply the medium during the heating operation to the common heat exchanger 40 instead of the waste water X, and from the heat exchanger 40, respectively. (See FIG. 5B, FIG. 5C and FIG. 6A for the heat exchange introduction pipe 42c and the heat exchange lead pipe 44c, heat exchange) FIG. 6A shows the introduction pipe 42b and the heat exchange lead-out pipe 44b (other pipes are not shown). The air-cooled heat pumps 154a to 154d and the like that are operated for heating constitute cooling-side heating medium supply heat pumps, and the heating medium supplied by the air-cooling heat pumps 154a to 154d and the like to the heat exchanger 40 constitutes the cooling-side heating medium. .

  Further, the air conditioning system 151 is branched from the cooling side return pipe 32, and the second cooling side return pipes 162a to 162d and the like for introducing the cooling medium into the air cooling heat pumps 154a to 154d and the like (medium inlets during cooling operation) The heat pumps 154a to 154d and the like (medium supply ports at the time of cooling operation) are appropriately provided with merging supply pipes 164a to 164d and the like that send the cooling medium to the cooling side supply pipe 30 (second cooling side return pipe 162b and merging). 5 (a) to 5 (c) for the supply pipe 164b, FIG. 5 (a) for the second cooling side return pipe 162c and the combined supply pipe 164c, and other pipes are not shown).

  Further, the heat exchange introduction pipes 42a to 42d and the second cooling side return pipes 162a to 162d and the like allow the medium to pass through as it is opened to one side and block the medium when closed to the other. Motor valves 43a to 43d as one of the switchable flow path switching means (flow rate adjusting means) are installed, and the heat exchange lead pipes 44a to 44d and the merge supply pipes 164a to 164d have motor valves. 45a-45d etc. are installed similarly. The motor valves 43a to 43d and the motor valves 45a to 45d are disposed on the air cooling heat pumps 154a to 154d and the like side from the common flow rate control valve 46. Further, instead of the motor valves 43a to 43d, etc., the motor valves 45a to 45d, etc., a flow rate adjusting valve capable of adjusting the opening may be used.

  Such an air conditioning system 151 can be heated by a cooling medium heating medium supplied by at least one of the air-cooled heat pumps 154a to 154d that is heated instead of being heated by the waste water X, and is also cooled. At least one of the air-cooled heat pumps 154a to 154d, etc., can take in a part of the cooling medium and cool and circulate it, and these operations can be automatically switched, and the operation is similar to the second mode, for example, It operates as described below. Note that the cooling of a part of the cooling medium by the cooling operation such as the air cooling heat pumps 154a to 154d is not executed, and the air cooling heat pumps 154a to 154d and the like may be dedicated to heating.

  FIG. 5A is a schematic diagram when the cooling load is larger than the heating load in summer and the like, and when the cooling load is relatively large, FIG. 5B is a cooling load than the heating load. FIG. 5 (c) is a schematic diagram when the heat load is relatively small and the cooling load is relatively small. FIG. 5 (c) shows a low temperature and a high humidity with respect to targets such as rainy seasons in summer and mid seasons. FIG. 6A is a schematic diagram in the case where the cooling load is smaller than the heating load such as time, and FIG. 6A is a schematic diagram in the case where only the heating is used without using the cooling in winter.

  That is, in the case of FIG. 5A in which the heat load is 800 kW with respect to the heat load of 800 kW, the automatic control device causes the heat pump 4 to operate following the heat load of 800 kW (electric input V253 kW, forward 60 degrees, Return 50 degrees). Accordingly, the heat pump 4 generates a cooling medium of 547 kW · 7 degrees, and the cooling medium is used for cooling the cooling coil 16, and the second cooling side return pipes 162 a to 162 c are partially formed at 17 degrees. Through the air cooling heat pumps 154a to 154c. The automatic control device grasps that the cooling load is large by monitoring the cooling return temperature, and the air cooling heat pumps 154a to 154d having the capacity (number of units, here three units) necessary for performing cooling corresponding to the cooling load. In order to introduce a part of the cooling medium into the second cooling side return pipes 162a to 162d etc. related to the operated air cooling heat pumps 154a to 154d etc., the second cooling is performed for the corresponding motor valves 43a to 43d etc. Sides such as the side return pipes 162a to 162d are opened.

  The automatic controller cools the air-cooled heat pumps 154a to 154c, cools the received cooling medium, adds cooling heat to the cooling medium (total 653 kW), and opens the motor valve in the same manner as the motor valves 43a to 43d. It supplies to the cooling side supply pipe 30 through the confluence | merging supply pipes 164a-164c which have 45a-45c. Further, the automatic control device cools the remaining part of the cooling medium received by the heat pump 4 by the operation of the heat pump 4 and sends it out from the cooling side supply pipe 30.

  In the case of FIG. 5B in which the thermal load is 800 kW with respect to the thermal load of 800 kW, the automatic control device causes the heat pump 4 to operate following the 800 kW thermal load (electrical input V253 kW, forward 60 degrees, Return 50 degrees). Accordingly, the heat pump 4 generates a cooling medium of 547 kW and 7 degrees, and the cooling medium is used for cooling the cooling coil 16, and becomes 17 degrees, and a part of the second cooling side return pipes 162a and 162b are used. Through the air cooling heat pumps 154a and 154b. That is, the automatic control device performs the cooling operation of the two air-cooling heat pumps 154a and 154b, which is the number necessary for performing the cooling corresponding to the cooling load here, to the second cooling side return pipes 162a and 162b. Part of the cooling medium is introduced.

  The automatic control device performs cooling operation of the air cooling heat pumps 154a and 154b, cools the received cooling medium and adds cooling heat to the cooling medium (total 353 kW), and the confluence supply pipes 164a and the motor valves 45a and 45b are opened. It is made to supply to the cooling side supply pipe 30 through 164b. Further, the automatic control device cools the remaining part of the cooling medium received by the heat pump 4 by the operation of the heat pump 4 and sends it out from the cooling side supply pipe 30.

  Furthermore, when the thermal load approaches the cooling load and the air cooling heat pumps 154a to 154d related to the cooling operation become one unit, the automatic control device does not perform the cooling operation (the operation is stopped). At least one of the heat pumps 154a to 154d is heated. About heating operation, it is the same as that of the case of FIG.5 (c) demonstrated later. The heating operation may be started when the load factor of one of the air cooling heat pumps 154a to 154d related to the cooling operation becomes a predetermined value (for example, 30%) or less, or the air cooling heat pumps 154a to 154a related to the cooling operation. The heating operation may be started when 154d or the like becomes 2 or less. The automatic control device can grasp the load factors of the air-cooled heat pumps 154a to 154d by receiving signals indicating the load factors from the air-cooled heat pumps 154a to 154d and the like. Further, when the number of air-cooling heat pumps 154a to 154d related to the cooling operation becomes one, another air-cooling heat pump 154a to 154d or the like is put into a heating standby state, and further, the load of one air-cooling heat pump 154a to 154d related to the cooling operation, etc. It is also possible to prepare for the heating operation by dividing the standby state and the operation state, such as starting the heating operation when the rate becomes equal to or less than a predetermined value. Then, the motor valves 43a to 43d and the motor valves 45a to 45d are switched at the start of the standby state, immediately before the operation, or at any timing therebetween.

  On the other hand, in the case of FIG. 5 (c) where the thermal load is 800 kW with respect to the thermal load 800 kW, the automatic control device causes the heat pump 4 to operate following the 800 kW thermal load (electrical input 253 kW, forward 60 degrees, Return 50 degrees). Accordingly, the heat pump 4 generates a cooling medium of 547 kW · 7 degrees, and the cooling medium is used for cooling the cooling coil 16 and is led to the heat pump 4 at 12 degrees.

  The automatic control device grasps that the cooling load is small (the cooling energy is surplus) by monitoring the cooling return temperature, and the capacity required for heating the cooling medium corresponding to the surplus cooling load ( The number of air-cooling heat pumps 154a to 154d is heated, and heat exchange is performed for the motor valves 43a to 43d and the motor valves 45a to 45d related to the air-cooling heat pumps 154a to 154d and the like that are heated. Switching to the introduction pipes 42a to 42d or the like or the heat exchange outlet pipes 44a to 44d side.

  The automatic control device heats the air cooling heat pumps 154a to 154d and the like (here, the air cooling heat pump 154c), and supplies the cooling medium heating medium to the heat exchanger 40 via the flow rate control valve 46. The automatic control device appropriately controls the cold supply amount adjustment valve 48 and heats the cooling medium via the heat exchanger 40 so that the cooling medium is balanced with the heating medium (247 kW, cooling medium heating medium travel 35 degrees). Return 30 degrees).

  Further, when the cooling load approaches the heating load and the number of air-cooling heat pumps 154a to 154d related to the heating operation becomes one, the automatic control device has at least one of the air-cooling heat pumps 154a to 154d and the like that are not heating. The stand (in this case, the air cooling heat pump 154b) is set in the cooling standby state. When the cooling load exceeds the heating load as shown in FIG. 5B (when the temperature obtained from the temperature sensor of the cooling medium becomes higher than a predetermined value), the cooling operation of the air cooling heat pumps 154a to 154d and the like in the cooling standby state To start. The switching to the cooling standby state or the cooling operation can be changed in the same manner as the switching to the heating standby state or the heating operation.

  On the other hand, in the case of FIG. 6A in which the thermal load is 1500 kW with respect to the thermal load 1500 kW, the automatic control device causes the heat pump 4 to operate following the thermal load of 1500 kW (electric input V334 kW, forward 60 degrees, Return 50 degrees). The heat generated by the heat pump 4 is supplied to the preheater 12 and / or the reheater 18. Accordingly, the heat pump 4 generates a cooling medium of 1166 kW · 20 ° C., and the cooling medium is controlled by the cooling control unit 48 or the motor valves 43a to 43d controlled by the automatic control device. The entire amount returns to the cooling side return pipe 32 without being supplied to the second cooling side return pipes 162a to 162d.

  The automatic control device heats at least one of the air cooling heat pumps 154a to 154d (here, two air cooling heat pumps 154b and 154c) according to the excess cooling load, and supplies the cooling medium heating medium to the heat exchanger 40 Let The automatic controller appropriately controls the cold supply amount adjustment valve 48 and heats the cooling medium via the heat exchanger 40 so as to be balanced with the heating medium (total 1166 kW, cooling medium heating medium going 40 degrees). -Return 35 degrees). In addition, when two or more air-cooled heat pumps 154a to 154d or the like are operated for heating, the automatic control device is provided with at least the air-cooled heat pumps 154a to 154d and the like that are not operated for heating in preparation for surplus cooling heat further increasing. One unit (here, air-cooled heat pump 154d, not shown for each circuit) is shifted to a heating standby state.

  The switching control of the air cooling heat pumps 154a to 154d and the like by such an automatic control device will be described in more detail mainly based on FIG. In FIG. 7, it is assumed that the heat pump 4 is composed of a group of a plurality of exhaust heat recovery type heat pumps (a single unit can be similarly controlled).

  When there is no operation command related to the external air conditioner 2 (NO in step S10), the automatic control device stops the heat pump 4, the air-cooled heat pumps 154a to 154d, etc. (steps S11 and S12) and ends the operation. On the other hand, when there is an operation command related to the external air conditioner 2 (YES in step S10), the automatic control device determines whether the heat pump 4 is operated in the thermal follow-up heat recovery mode (step S13).

  If the heat pump 4 is not operated (NO in step S13), the automatic control device determines whether all the air-cooled heat pumps 154a to 154d are in the heating operation (step S14), and all the units are in the heating operation. If it is (YES), the heat pump 4 is operated (step S16), and if all the units are not in the heating operation (NO), the heating operation is performed for all the units such as the air cooling heat pumps 154a to 154d and the heat pump 4 is operated. (Steps S15 and S16). After this, or when the heat pump 4 is operating (YES in step S13), the process proceeds to step S17.

  In step S17, the automatic control device determines whether or not two or more units such as the air cooling heat pumps 154a to 154d are in the cooling operation. If two or more units are in the cooling operation (YES), all the units are in the cooling operation. If there is an air cooling heat pump 154a to 154d or the like during heating operation, the control is continued by shifting to the cooling standby state (steps S18 and S19).

  On the other hand, if two or more units are not in the cooling operation (NO in step S17), the automatic control device checks whether only one unit is in the cooling operation (step S20).

  If only one unit is in the cooling operation (YES), it checks whether any one of the other units is in the heating operation (step S21). The inside is switched to the heating operation (step S22). After this or when there is a heating operation (YES in step S21), the process proceeds to step S23, where only one unit is in the heating operation and all the remaining are in the cooling operation. It is checked whether it is in the middle (or in cooling standby, both are in cooling mode). If not in such a case, (NO) In the cooling standby state other than those that are operating in the cooling mode and heating mode one by one (Step S24) and control is continued.

  On the other hand, if only one unit such as the air cooling heat pumps 154a to 154d is not in the cooling operation (NO in step S20), the automatic control device grasps whether two or more units are in the heating operation (step S25). If two or more units are in heating operation (YES), only when all units are not in the heating mode (heating operation or standby for heating), one unit that is in the cooling standby state is set in the heating standby state (steps S26 and S27), and control is performed. Continue.

  On the other hand, if two or more units are not in the heating operation (NO in step S25), the automatic control device checks whether only one unit is in the heating operation (step S28). If only one unit is not in the heating operation (NO), one unit is heated and the control is continued (step S29).

  On the other hand, if only one unit is in the heating operation (YES in step S28), only one unit is in the cooling mode and the rest is not in the heating mode, and only one unit is in the cooling mode and the other is in the heating standby state. (Steps S30 and S31), the control is continued.

  The adjustment from the outside air A to the air B in the air conditioning system 151 will be mainly described with reference to FIG.

  When the cold air is added by the air-cooled heat pump as shown in FIG. 5 (a) or FIG. 5 (b), the outside air A has a relatively high temperature as shown in FIG. First, an increase in absolute humidity and a decrease in temperature are received by the washer 14, then cooled by the cold supplied to the cooling coil 16, dehumidified to the target absolute humidity, and further heated to the target temperature by the reheater 18. The

  On the other hand, when it is necessary to supply cold heat to the external air conditioner 2 as shown in FIG. 5 (c), it is not necessary to add cold heat by an air-cooled heat pump, but as shown in FIG. Since it is an air temperature (close to the target temperature), it is not preheated, is first subjected to an increase in absolute humidity and a decrease in temperature by the washer 14, and is then cooled by relatively little cold supplied to the cooling coil 16. The dehumidifier is dehumidified to the target absolute humidity, and further heated to the target temperature by the reheater 18.

  Further, when it is not necessary to supply cold heat to the external air conditioner 2 as shown in FIG. 6A, the outside air A is in a state where the temperature and absolute humidity are lower than the air B as shown in FIG. First, preheating is performed by the pre-heater 12, and then the absolute humidity is increased to the target humidity and the temperature is decreased by the washer 14, and further heated to the target temperature by the reheater 18.

  The automatic control device is electrically connected to a sensor (not shown) that grasps the temperature on the cold water side and / or the temperature in the cold heat supply amount adjusting valve 48, and the automatic control device is changed according to the temperature state. (C) The operation | movement which concerns on either of Fig.6 (a) is performed.

  The air conditioning system 151 of the above third embodiment is the same as that of the first embodiment, and in particular, the cooling medium of the heat pump 4 is heated by the cooling side heating medium supplied from the air cooling heat pump 154.

  Therefore, the air-conditioning system that has the same effect as the first embodiment and that is particularly excellent in energy saving even in a factory without waste hot water or the like because the cooling side heating medium of the air cooling heat pump 154 is supplied to the heat exchanger 40 with the cooling medium. 151 can be introduced.

  In the air conditioning system 151, since the air-cooling heat pump 154 includes a plurality of air-cooling heat pumps 154a to 154d, the number of the air-cooling heat pumps 154a to 154d can be adjusted to various conditions by adjusting according to the scale of the heat load or the heat load. It can be installed flexibly in various places, and the automatic control device performs cooling operation and / or heating operation according to the state of the heating medium and / or cooling medium (heat quantity, temperature, load, etc.). Since the number of air-cooled heat pumps 154a to 154d to be performed is switched, even if the heat load or the heat load changes variously due to the season, weather, day or night, etc., it is possible to continue the operation automatically.

  Furthermore, when the thermal load decreases with respect to the cooling load, the automatic control device sets a part of the air cooling heat pumps 154a to 154d and the like to a cooling standby state as an operation standby state related to cooling, and the cooling load becomes a heating load. In the case of decreasing, on the other hand, a part of the air cooling heat pumps 154a to 154d and the like is set in a heating standby state as an operation standby state related to heating, so that preparation can be made in advance before the cooling or heating needs to be switched. The operation state such as the switching operation can be made extremely smooth.

[Fourth form]
FIG. 6B is a schematic diagram of the air conditioning system 171 according to the fourth embodiment, in which the air cooling heat pump group according to the third embodiment air conditioning system 151 is replaced with an exhaust heat recovery type air cooling heat pump group. Is the same as in the third embodiment. In FIG. 6B, the circuit on the heating side is not shown.

  In the air conditioning system 171, a plurality of exhaust heat recovery type air cooling heat pumps 154x, 154y, and the like are installed. In addition, although 2 units | sets are illustrated in FIG.6 (b), it is good also as 1 unit | set and good also as 3 units | sets or more. In the case of three or more units, a circuit can be similarly formed.

  The cooling side of the exhaust heat recovery type air cooling heat pumps 154x, 154y, etc. are connected to the second cooling side return pipes 162x, 162y, etc. and the merging supply pipes 164x, 164y, etc. The exchange introduction pipes 42x and 42y and the heat exchange lead pipes 44x and 44y are connected to each other. The heat exchange introduction pipe 42x is connected to the heat exchange introduction pipe 42y, and the heat exchange introduction pipe 44x branches from the heat exchange introduction pipe 44y.

  Even in the air conditioning system 171 according to the fourth embodiment, similar to the air conditioning system 151 of the third embodiment, the medium temperature on the heating side or the cooling side of the exhaust heat recovery type air cooling heat pumps 154x, 154y, etc. according to the heating load or the cooling load. (Medium heat amount) is controlled, and the number of operating units is controlled. Therefore, it is possible to automatically follow various operating conditions, and to ensure stable continuation of operation with excellent energy saving.

  In the exhaust heat recovery type air cooling heat pumps 154x, 154y, etc., the automatic control device automatically switches between the heat recovery mode (simultaneous operation of cooling and heating), the heating mode exclusively for heating, and the cooling mode. It is possible to operate in the state of FIG. 6 (b) day and night, all weather, and all seasons without switching modes such as cooling operation or heating operation or switching the flow path. The heat pump 4 can be operated in a relatively simple manner. The balance between cold and warm heat can be maintained and stable operation can be continued.

[Fifth embodiment]
FIG. 9 is a schematic diagram of an air conditioning system 201 according to the fifth embodiment. The air conditioning system 201 has a cooling medium tank 208 and an air cooling heat pump 154 instead of the flow rate control valve 46, and is the same as the second embodiment. The second cooling side return pipe 162 and the merge supply pipe 163 are shared with the heat exchange introduction pipe 42 or the heat exchange derivation pipe 44.

  The cooling medium tank 208 is interposed in the cooling side supply pipe 30 and also in the cooling side return pipe 32, and further connected to the second cooling side return pipe 162 and the merging supply pipe 163 related to the air cooling heat pump 154. Has been. The cooling medium tank 208 can adjust the flow rate of the cooling medium to the cooling side supply pipe 30, the cooling side return pipe 32, and the second cooling side return pipe 162 based on a command from the automatic control device. In addition, the air cooling heat pump 154 can take in the cooling medium from the second cooling side return pipe 162, heat or cool in the heating mode or the cooling mode, and send the cooling medium to the joining supply pipe 163.

  Such an air conditioning system 201 operates in the same manner as in the fourth embodiment, for example, as described below. 9A to 9C sequentially correspond to FIGS. 5A to 5C according to the fourth embodiment.

  In the case of FIG. 9A in which the cooling load is 900 kW with respect to the heating load of 800 kW, the automatic control device causes the heat pump 4 to operate following the heating load of 800 kW (electrical input V253 kW, forward 60 degrees, return 50 Every time). Accordingly, the heat pump 4 generates a cooling medium of 547 kW · 7 degrees, and the cooling medium enters the cooling medium tank 208. The amount of the cooling medium in the cooling medium tank 208 controlled by the automatic control device is used for cooling the cooling coil 16 and returns to the cooling medium tank 208 at 17 degrees. Further, the automatic control device operates the air cooling heat pump 154 in the cooling mode by the electric input V2, and the controlled amount of the cooling medium received from the cooling medium tank 208 is in a state where the balance with the heating medium related to the heat pump 4 is achieved. Cool to a state that can follow the cooling load. Then, the amount of the cooling medium in the cooling medium tank 208 controlled by the automatic control device is returned to the heat pump 4, and the balance between the heat and cold of the heat pump 4 is ensured.

  In the case of FIG. 9B in which the thermal load is 800 kW with respect to the thermal load 800 kW, the automatic control device causes the heat pump 4 to operate following the 800 kW thermal load (electric input 253 kW, forward 60 degrees, Return 50 degrees). Accordingly, the heat pump 4 generates a cooling medium of 547 kW · 7 degrees, which is used for cooling the cooling coil 16 via the cooling medium tank 208 and returns to the cooling medium tank 208 at 12 degrees. . In addition, the automatic control device operates the air cooling heat pump 154 in the heating mode by the electric input V <b> 2, and executes appropriate heating of a part of the cooling medium received from the cooling medium tank 208. Further, the automatic control device causes the cooling medium tank 208 to send the cooling medium to the heat pump 4 in a state where the cooling medium is balanced with respect to the heating medium.

  Further, in the case of FIG. 9C where the thermal load is 1500 kW with respect to the thermal load of 1500 kW, the automatic control device causes the heat pump 4 to operate following the thermal load of 1500 kW (electric input V243 kW, heating medium going 60). Degree, heating medium return 50 degrees, cooling medium return 30 degrees, cooling medium return 40 degrees). The heat generated by the heat pump 4 is supplied to the preheater 12 and / or the reheater 18. Accordingly, the heat pump 4 generates a 1257 kW cooling medium, and the cooling medium enters the cooling medium tank 208. Further, the automatic control device does not supply the cooling medium in the cooling medium tank 208 to the cooling coil 16. In addition, the automatic control device operates the air cooling heat pump 154 in the heating mode by the electric input V2 (264 kW), and heats the cooling medium in the cooling medium tank 208 so as to be balanced with the heating medium (1257 kW, cooling). Medium receiving 30 degrees, returning 40 degrees).

  The automatic control device is electrically connected to a sensor (not shown) that grasps the state (temperature and / or humidity, etc.) of the outside air A, and according to the state of the outside air A, the automatic control device shown in FIGS. The driving | operation which concerns on either is performed.

  In the air conditioning system 201 of the fifth embodiment described above, similarly to the fourth embodiment, it can be made extremely simple and energy efficient, and a cooling medium tank 208 is provided between the air cooling heat pump 154 and the heat pump 4. Since it is interposed, the temperature (cooling amount) of the cooling medium can be comprehensively managed, and the cooling medium having the adjusted cooling amount can be controlled by the cooling coil 16, the air cooling heat pump 154, and the heat pump 4 of the external air conditioner 2. It is possible to carry out a continuous operation with high stability while being easy to control.

[Sixth form]
FIG. 10 is a schematic diagram of an air conditioning system 251 according to the sixth embodiment. The air conditioning system 251 is the same as the fifth embodiment. The cooling medium tank 208 is removed from the fifth embodiment and the air cooling heat pump 154 is used as a heating heat pump. As a cooling side return pipe 32.

  The air-cooling heat pump 154 receives the cooling medium from the cooling coil 16 or the cooling heat supply amount adjustment valve 48, and heats or cools the received cooling medium to return to the heat pump 4 by the operation in the heating mode or the cooling mode.

  Such an air conditioning system 251 operates in the same manner as in the fifth embodiment, for example, as described below. 10A to 10C sequentially correspond to FIGS. 5A to 5C according to the fourth embodiment and FIGS. 9A to 9C according to the fifth embodiment.

  In the case of FIG. 10A in which the cooling load is 900 kW with respect to the heating load 800 kW, the automatic control device causes the heat pump 4 to perform an operation following the 800 kW heating load (electrical input V253 kW). Accordingly, the heat pump 4 generates a cooling medium of 547 kW · 7 degrees, which is used for cooling the cooling coil 16 and enters the air cooling heat pump 154 at 17 degrees. The automatic control device operates the air-cooled heat pump 154 in the cooling mode with the electric input V2 (105 kW), and cools the cooling medium to a state in which the cooling medium can be balanced with the heating medium related to the heat pump 4 or to follow the cooling load ( 353 kW cooling). The temperature of the cooling medium is controlled by the air cooling heat pump 154 based on a command from the automatic control device.

  Further, in the case of FIG. 10B where the cooling load is 150 kW with respect to the heating load of 800 kW, the automatic control device causes the heat pump 4 to operate following the heating load of 800 kW (electrical input 253 kW). Accordingly, the heat pump 4 is set to 547 kW · 7 degrees for each cooling medium, and 150 kW of the cooling medium 547 kW is used for cooling the cooling coil 16, and becomes 9.7 degrees with the remaining 397 kW of cooling air. Enter 154. The automatic control device operates the air-cooled heat pump 154 in the heating mode with the electric input V2 (66 kW), heats the received cooling medium by an amount that eliminates the excess cooling heat 397 kW in order to balance the heating medium, and the heat pump Pass to 4.

  Further, in the case of FIG. 10C where the cooling load is 0 kW with respect to the heating load of 1500 kW, the automatic control device causes the heat pump 4 to perform an operation following the heating load of 1500 kW (electrical input V243 kW). The heat generated by the heat pump 4 is supplied to the preheater 12 and / or the reheater 18. Accordingly, the heat pump 4 generates a cooling medium of 1257 kW · 30 degrees, and the cooling medium enters the entire air-cooled heat pump 154 via the cold supply amount adjustment valve 48 (not supplied to the cooling coil 16). Then, the automatic control device operates the air-cooled heat pump 154 in the heating mode with the electric input V2 (264 kW), and heats the cooling medium so that the cold heat of 1257 kW is eliminated and the heat is balanced (40 degrees). Return to the heat pump 4.

  The automatic control device is electrically connected to a sensor (not shown) that grasps the state (temperature and / or humidity, etc.) of the outside air A, and according to the state of the outside air A, the automatic control device shown in FIGS. The driving | operation which concerns on either is performed.

In such an air conditioning system 251 of the sixth form, in addition to the same effects as the fifth form, the cooling medium of the heat pump 4 is heated by the air cooling heat pump 154 as a heating heat pump, so there is no waste water or the like. Even in the factory, the air conditioning system 251 with extremely good energy efficiency can be provided by simply adding the air cooling heat pump 154 in addition to the heat pump 4.
[Seventh form]
FIG. 11 is a schematic diagram of an air conditioning system 301 according to a seventh embodiment, and the air conditioning system 301 is the same as the first embodiment except for the configuration on the cooling side.

  The air conditioning system 301 includes an air cooling heat pump 308 similar to the air cooling heat pump 154 that supplies the cooling coil 16 of the air conditioner 2 to the cooling coil 16 as the second cooling medium. The air-cooling heat pump 308 supplies the cooling coil 16 with a cooling medium for the air conditioner having the cooling heat necessary for cooling the outside air A based on a command from the automatic control device.

  On the cooling side of the heat pump 4, a waste heat water introduction pipe 312 through which the waste heat water X is directly taken in and out as a cooling medium, a waste heat water lead pipe 314, and a medium introduction that receives the cooling medium from the air cooling heat pump 154 or returns it to the air cooling heat pump 154. A pipe 322 or a medium outlet pipe 324 is connected to each other based on a command from the automatic control device.

  Such an air conditioning system 301 operates as described below, for example.

  In other words, the heat pump 4 operates according to the thermal load (800 kW) and generates cold (670 kW), but the exhaust warm water X is generated by the cooling of the heat pump 4 in the summer when the temperature of the exhaust warm water X is high and the amount of heat is high. In the summer or the like where the heat balances or exceeds the cold heat, the automatic control device sets the cooling side of the heat pump 4 to the exhaust warm water X side (the exhaust warm water introduction pipe 312 or the exhaust warm water as shown in FIG. 11A). Switch to the outlet pipe 314 side), and let the heat pump 4 accept the exhausted hot water X (40 degrees), eliminate the cold 670 kW, and balance the warm temperature. In addition, the waste heat water X (30 degree | times) which came out via the waste heat water derivation | leading-out pipe 314 from the heat pump 4 is processed similarly to the waste water of a normal factory.

  On the other hand, in winter or the like when the temperature of the waste water X is low (the amount of heat is insufficient), the automatic control device sets the cooling side of the heat pump 4 to the air-cooling heat pump 154 side (medium introduction pipe 322 or the like) as shown in FIG. In addition to switching to the medium outlet pipe 324 side, the air cooling heat pump 154 is operated in the heating mode, the cooling medium (30 degrees) received from the medium outlet pipe 324 is heated to eliminate the 670 kW cold, and in a balanced state Supply to the medium introduction pipe 322 (40 degrees).

  In the air conditioning system 301 of the seventh embodiment as described above, the external air conditioner 2 having the reheater 18 that heats the external air A taken in from the external air intake port 10 and the cooling coil 16 that cools the external air A, the reheater 18, the heating medium is heated and supplied, and the cooling medium can be switched between the air-cooled heat pump 154 side and the waste hot water X side generated from the factory, and can be introduced, cooled, and discharged, and the cooling coil. 16 is provided with an air-cooling heat pump 304 for supplying a cooling medium for an air conditioner. When the cooling medium is introduced from the air-cooling heat pump 154 side, the heat pump 4 matches the cooling water X with the cooling by the heat pump 4 or When it has more heat, it switches so that the said cooling medium may be introduced from the waste water X side.

  Therefore, it is possible to eliminate the excessive cold heat when operating to follow the heat temperature of the heat pump 4 by the heat of the waste water X as much as possible, and by using the heat of the waste water X that was originally discarded. It is possible to balance the heat and cold of the heat pump 4, and it is possible to configure the air conditioning system 301 that is extremely excellent in energy saving. Even when the waste water X does not have enough heat to eliminate the cold, the cooling medium heated by the air-cooled heat pump 154 is introduced, so that the operation of the heat pump 4 can be continued.

[Eighth form]
FIG. 12 is a schematic diagram of an air conditioning system 351 according to the eighth embodiment. The air conditioning system 351 is the same as the first embodiment except for the configuration on the cooling side.

  In contrast to the first embodiment, the air conditioning system 351 uses the exhaust Y (cooling medium heating medium) from the drying furnace 352 of the factory instead of the exhaust hot water X, and introduces the exhaust Y from the heat exchange introduction pipe 42 to the heat exchanger 40. Then, the exhaust Y is led out from the heat exchange lead pipe 44. Although the flow rate adjusting valve 46 is not installed here, the heat exchange introducing pipe 42 may be provided with a flow rate adjusting means (an exhaust Y bypass circuit) for adjusting the amount of exhaust Y introduced into the heat exchanger 40. .

  In addition, the air conditioning system 351 includes a flow rate adjustment valve 356 that adjusts the flow rate of the cooling medium to the heat exchanger 40 on the cooling return pipe 32 from the heat exchanger 40 to the external air conditioner 2 side. The air conditioning system 401 includes a third cooling side return pipe 362 extending from the flow rate adjustment valve 356 to the heat exchanger 40 and a fourth cooling side return pipe 364 reaching the cooling side return pipe 32 from the heat exchanger 40. The flow rate adjusting valve 356 is configured to change the heat exchanger through the third cooling-side return pipe 362 for any amount (including 0 or all) of the cooling medium in the cooling-side return pipe 32 based on a command from the automatic control device. 40 and the remainder is sent to the heat pump 4 via the fourth cooling side return pipe 364.

  Such an air conditioning system 351 operates in the same manner as in the first embodiment, for example, as described below.

  That is, the heat pump 4 operates according to the thermal load (800 kW) and generates cold (547 kW). The cold is appropriately used for cooling the outside air A in the external air conditioner 2 (150 kW · 7 degrees to 9.7). The automatic control device controls the flow rate via the flow rate adjustment valve 356 so that the cooling medium receives 397 kW of heat from the heat exchanger 40 in accordance with the remaining cold heat of 397 kW. In the heat exchanger 40, the exhaust heat 397 kW of the exhaust Y and the cooling medium 397 kW of the cooling medium from the flow rate control valve 356 are exchanged, and a part or all of the cooling medium is heated by the exhaust Y (17 degrees, still cooling load) It may not be heated when the weight is heavy). By this heating, the heat pump 4 ensures a balance of cold and hot heat, and the operation of the heat pump 4 is continued.

  In such an air conditioning system 351 of the eighth form, in addition to the same effect as the first form, the cooling medium of the heat pump 4 is heated by the exhaust Y generated from the factory in particular, so the exhaust heat of the exhaust Y is reduced. The heat pump 4 can be used effectively, and the heat pump 4 can be operated very efficiently.

[Ninth embodiment]
FIG. 13 is a schematic diagram of an air conditioning system 401 according to the ninth embodiment. The air conditioning system 401 is similar to the second embodiment, and a refrigerator 404 is disposed on the cooling side of the heat pump 4 with respect to the configuration of the second embodiment. It consists of Here, hot water is used as the heating medium and cold water is used as the cooling medium, but a refrigerant, gas, or the like may be used.

  Such an air conditioning system 401 operates in the same manner as in the second embodiment, for example, as described below.

  That is, in the mid-season period (spring season, June 22, 2008, near Nagoya City) shown in FIG. 13 (a) in the operating state at 13:00 noon, as shown in FIG. The outside air A before being taken into 2 has a dry bulb temperature of 24.6 degrees Celsius and 86% relative humidity, and the air conditioning system 401 humidifies the outside air A taken in by applying a washer 14 (circle 1 in the figure, relative humidity 100%). Then, the cooling coil 16 filled with cold water is operated until the target absolute humidity is reached and cooled (circle 2 in the figure), and further, the reheater 18 filled with warm water is operated until the target temperature is reached (FIG. 2). Nakamaru 3). Here, the target dry bulb temperature is 25 degrees, and the target relative humidity is 80%. The air volume of the blower 20 of the external air conditioner 2 is 7000 cubic meters / minute.

  The outputs of the heat pump 4 and the refrigerator 404 in this case are shown in one column of the table in FIG. In addition, at 11:00 to 12:00 before 13:00, the state transition shown in the table of “outside air conditions” occurred. The target value of dehumidification by the cooling coil 16 (circle 2 in FIG. 14) is as shown in the column of “Dehumidification target value”. In this case, the “dehumidification target specific enthalpy difference” (kilojoules / kilogram · kJ / kg, dry air · D / A) and “humidification amount” are as shown in the column at 13:00 in the corresponding table. The capacity is as shown in the table of “Exhaust heat recovery type heat pump”.

  According to FIG. 15, the automatic control device causes the reheater 18 to supply hot water of 535 kW to the heat pump 4 at 13:00 to follow the heating load 535 kW of the outside air A, and at the same time, 366 kW of cold water is supplied to the cooling coil 16. To output. Since the cold heat of 366 kW causes a shortage of 402 kW for the cooling load of 768 kW, the automatic control device activates the refrigerator 404 and applies 402 kW of cold heat to the cooling medium. Further, the automatic control device closes the flow rate adjustment valve 46 and does not heat the cold water with the exhausted hot water X.

  On the other hand, in the operating state at 13:00 on the same day shown in FIG. 13 (b), as shown in FIG. 14 and FIG. The relative humidity is 87%, and the air-conditioning system 401 heats the taken-in outside air A by applying the preheater 12 (circle 4 in the figure), and humidifies by applying the washer 14 until the target absolute humidity is reached (circle in the figure). 5) Further, the reheater 18 in which the heating medium is put is applied and heated until the target temperature is reached (circle 6 in the figure). Various target values and air volumes are the same as at 13:00.

  The outputs of the heat pump 4 and the refrigerator 404 in this case are shown in the 24 o'clock column of the table of FIG. According to the same column, the automatic control device causes the preheater 12 and the reheater 18 to supply 1527 kW of hot water to the heat pump 4 at 24:00 to follow the heating load 1527 kW of the outside air A, and 1233 kW of cold water accordingly. Is output to the cooling coil 16. Since the cooling heat is 1233 kW, 1233 kW is excessive with respect to the cooling load of 0 kW. Therefore, the automatic control device opens the flow control valve 46 and introduces the exhaust hot water X into the heat exchanger 40, gives 1233 kW of heat to the cold water, and balances the cold water against the hot water. Take. On the other hand, the automatic control device stops the refrigerator 404 and does not cool the cold water.

  Even in the air conditioning system 401 of the ninth embodiment, it is possible to provide the air conditioning system 401 excellent in energy saving.

[Tenth embodiment]
The air conditioning system according to the tenth embodiment is the same as the ninth embodiment. In the tenth embodiment, the refrigerator of the ninth embodiment is an air-cooled heat pump that operates in the same manner as the refrigerator, and a total of 11 exhaust heat recovery type heat pumps are considered from the viewpoint of the maximum heating capacity (in winter). It is an aggregate of. The automatic control device of the air conditioning system according to the tenth embodiment can switch the operating state or the number of operating exhaust heat recovery type heat pumps so as to follow the hot water load.

  FIGS. 16 to 18 are schematic diagrams, air line diagrams, and the like according to predetermined dates in the summer, middle season, and winter in order in the air conditioning system of the tenth embodiment. Each of FIGS. 16 to 18 shows a table showing transitions of the outside air state, outputs of the heat pump / air-cooling heat pump, and the like, and outputs of the conventional system corresponding to such transitions of the outside air state. Here, as a conventional system, it is assumed that the preheater and the reheater are heated by supplying steam with a city gas steam boiler, while the cooling coil is cooled by supplying a cooling medium with an air cooling heat pump similar to the ninth embodiment. is doing.

  Such an air conditioning system operates in the same manner as in the ninth embodiment, for example, as described below.

  That is, in the summer state shown in FIG. 16 (August 4, 2008, near Nagoya City), the automatic control device is in a state of “cold water load> hot water load” mainly in the daytime for the heat pump. Drive at night and drive at night without "cold water". Then, as in the eighth embodiment, when the output at each time is calculated and the power consumption is further calculated, the total power consumption of the heat pump is 3403 kW / day, and the total power consumption of the air-cooled heat pump is 2489 kW / day.

Further, when this electricity consumption is converted into carbon dioxide (CO ₂ ) emissions, the heat pump is 1548 kg / day, the air-cooled heat pump is 1133 kg / day, and the total is 2681 kg / day. The following are used for efficiency and CO ₂ emission coefficient. In other words, for city gas, the “Calculation / Reporting / Publication System” prepared by the Ministry of the Environment based on the Enforcement Ordinance on Promotion of Global Warming Countermeasures and the Ordinance on Calculation of Greenhouse Gas Emissions Associated with the Business Activities of Specific Emissions using calculation methods and emission computed values from the coefficient list "(11000 kcal per normal cubic meter (kcal / Nm3), 2.3300 kilogram (CO ₂₎ per normal cubic meter _{(kg-CO 2 / Nm3)} ) in, for electricity, 08 fiscal value of Chubu Electric Power Co., Inc. (860 kilocalories per kilowatt-hour _{(kcal / kWh), 0.4550kg-} CO 2 / kWh) is used.

Similarly, calculating the total amount of boiler city gas consumption and air-cooled heat pump power consumption at each hour for the conventional system, the amount of city gas used is 993 N cubic m / day and the power consumption is 4359 kW, which is converted into CO ₂ emissions. City gas boiler 2315kg / day, air-cooled heat pump 1984kg / day, total 4298kg / day.

On the other hand, in the operation state of one day of the intermediate season (May 19, 2008) shown in FIG. 17, the automatic control device operates mainly in the “no cold water” state for the heat pump. Then, when the output at each time is calculated and the power consumption is further calculated, the total power consumption of the heat pump is 8569 kW / day, and the total power consumption of the air-cooled heat pump is 0 kW / day. When this electricity consumption is converted into CO ₂ emission, the heat pump is 3899 kg / day, the air-cooled heat pump is 0 kg / day, and the total is 3899 kg / day.

Similarly, calculating the total amount of boiler city gas consumption and air-cooled heat pump power consumption at each time for the conventional system, the amount of city gas used is 3343 N cubic m / day and the power consumption is 0 kW, which is converted into CO ₂ emissions. City gas boiler 7790 kg / day / air cooling heat pump 0 kg / day / total 7790 kg / day.

On the other hand, in the winter operation (February 22, 2008) shown in FIG. 18, the automatic control device operates mainly in a “no cold water” state for the heat pump. When the output at each time is calculated and the power consumption is calculated, the total power consumption of the heat pump is 16081 kW / day, and the total power consumption of the air-cooled heat pump is 0 kW / day. Further, when this electricity consumption is converted into CO ₂ emission, the heat pump is 7317 kg / day, the air-cooled heat pump is 0 kg / day, and the total is 7317 kg / day.

Similarly, calculating the total amount of boiler city gas consumption and air-cooled heat pump power consumption at each time for the conventional system, the amount of city gas used is 6274N cubic m / day, and electricity consumption is 0 kW, which is converted into CO ₂ emissions. City gas boiler 14619 kg / day, air-cooled heat pump 0 kg / day, total 14619 kg / day.

FIG. 19 shows a table summarizing these power consumption and CO ₂ emission amount. In the upper part of FIG. 19, the conventional system (conventional method) in the day of summer (FIG. 16), intermediate season (FIG. 17), and winter (FIG. 18) and the amount of electricity consumed, the amount of city gas consumed, and the amount of CO ₂ emission of the present invention. Is shown. “HP” is a heat pump.

In addition, the middle part of FIG. 19 shows the total of power consumption, city gas consumption, and CO ₂ emissions in each season. Here, for the sake of simplicity, these amounts are obtained by multiplying the state shown in the upper stage by an average number of operating days in each season. Further, in the lower part of FIG. 19, the total values for all of these quantities are shown. According to such a combined value, in the air conditioning system of the ninth embodiment, the annual CO ₂ emission amount is reduced by 48%, such as 1058 t with respect to 2051 tons (ton, t), compared with the conventional method. Is done. In addition, when converted into crude oil for annual energy consumption (electricity consumption and city gas consumption), the air-conditioning system of the ninth embodiment gives 598 kiloliters (kl), while the conventional example yields 1053 kl, a 43% reduction effect. Appears.

[Eleventh form]
FIG. 20 is a schematic diagram of an air conditioning system 501 according to an eleventh embodiment. The air conditioning system 501 is similar to the ninth embodiment, and a cooling tower (CT) 504a is used instead of the refrigerator 404 in the configuration of the ninth embodiment. 504d and the like, the heat recovery type heat pump 4 as a plurality of heat pumps 4a to 4d and the like, and the external air conditioner 2 as a plurality of external air conditioners 2a to 2d and the like, and a hot water boiler 506 and A hot water tank 508 is installed. Here, hot water is used as the heating medium and cold water is used as the cooling medium, but a refrigerant, gas, or the like may be used. Further, instead of the hot water boiler 506, other heat sources such as an electric heater, an air-cooled heat pump, or a combination thereof may be used.

  The heating water supply pipes 34a to 34d or the heating side return pipes 36a to 36d are connected to the hot water inlets and outlets of the heat pumps 4a to 4d, respectively, and the heating side supply pipes 34a to 34d are gathered together with the heating side supply pipe 34 and heated water boiler 506. The heating side return pipes 36 a to 36 d are branched from the heating side return pipe 36. Motorized valves 510a to 510d are interposed in the heating side supply pipes 34a to 34d, respectively. Further, pipes extending from the heating side supply pipes 34a to 34d to the hot water inlet / outlet of the CTs 504a to 504d are respectively branched, and motor valves 512a to 512d are interposed in the branch pipes, respectively.

  Such an air conditioning system 501 operates in the same manner as in the ninth embodiment, for example, as described below.

  That is, as shown in FIG. 21, when the system is started, the operation of the heat pumps 4a to 4d and the like is started. First, the automatic control device checks whether or not there is an activation command for the external air conditioners 2a to 2d (step S101), and if there is an activation command, determines whether cold water is required or not based on the temperature or humidity of the outside air. Based on the determination (step S102). Then, only when necessary (YES), the heat pump 4 related to the necessary number calculated based on the outside air temperature / humidity, the number of operating days on the previous working day, and the like is cooled (step S103).

  After that, the automatic control device starts operation of the hot water boiler 506 (for example, a set temperature of 58 degrees) in order to cope with the shortage of heat of the exhaust hot water X at the time of starting up the factory due to the start of operation of other devices. Step S104) waits until the predetermined time elapses when the cold water is within 2 degrees above and below the set temperature, and the predetermined time elapses when the hot water is within 2 degrees above and below the set temperature. (Step S105), after the cold / hot water is prepared, the operation of the fan (blower 20) of the external air conditioner is started (Step S106).

  Further, when the additional operation in the cooling mode of the heat pump 4 is necessary, the automatic control device performs one additional operation (steps S107 and S108), and the air volume, temperature, and humidity of the external air conditioner 2 are controlled values (predetermined values). This is repeated as long as the value does not stabilize (step S109).

  Subsequently, the automatic control device determines that the amount of heat related to the heat exchanger 40 of the waste warm water X is equal to or greater than a set value based on the temperature of the waste warm water X, the number of operating compressors that are the sources of the waste warm water X, and the like. After waiting (step S110), one heat pump 4 is operated in the hot water follow-up mode (step S111), and the following processes are looped until the hot water boiler 506 is stopped (step S112).

  That is, if the opening degree of the flow rate adjustment valve 46 related to the discharged hot water X is 60% or less (step S113), the automatic control device additionally operates the heat pump 4 in the hot water follow-up mode (for example, the hot water set temperature 60). Step S114) and wait until the cold water and the hot water are stabilized at several degrees before and after the set temperature, respectively (Step S115). Next, the automatic control device makes it unnecessary to apply heat by the hot water boiler 506 due to the hot water of the heat pump 4 in the hot water follow-up mode, and when the hot water boiler 506 cannot be stopped (NO in step S116), the loop is executed. Continuing (step S112), if possible (YES in step S116), start-up of the external air handler 2 is completed. In this way, by additionally operating the heat pump 4 in the hot water follow-up mode, a necessary amount of hot water is supplied by the heat pump 4, and the hot water boiler 506 is automatically stopped.

  Next, after completion of the system startup, the automatic control device performs the cold water load adjustment control of the heat pump 4 as shown in FIG. 22, the hot water supply shortage prevention control of the heat pump 4 as shown in FIG. Control to prevent insufficient cold water supply.

  That is, when the automatic control device receives a command related to stopping all of the external air conditioners 2 (NO in step S201), the automatic control device stops all of the heat pumps 4 (step S202) and stops the hot water boiler 506. (Step S203), and the control is completed.

  In addition, the automatic control device may change the figure when the opening degree of the flow rate adjustment valve 46 related to the discharged hot water X is not 60% or less (NO in step S204), for example, 80% or more (NO in step S205). 23. If not, the process proceeds to the control by executing steps S206 and S207 as adjustment of the cooling load.

  In Step S206, which is executed when YES is determined in Step S204, the automatic control device is in the hot water follow-up mode in response to the opening degree of the flow rate adjusting valve 46 being 60% or less and the cold water load of the external air conditioner 2 increasing. The allowable number of heat pumps 4 to be operated (the maximum number that can be operated) is increased by one.

  On the other hand, in Step S207, which is executed when YES is determined in Step S205, the automatic control device performs the cold water of the external controller 2 so that the degree of opening of the flow control valve 46 is 80% or more and the warm water X cannot be sufficiently heated. In response to the reduction in load, the allowable number of heat pumps 4 operated in the hot water follow-up mode is reduced by one, and the heat pump 4 operated or waited in the hot water follow-up mode is set to the cooling mode. The corresponding electrically operated valves 512a to 512d are opened and the electrically operated valves 510a to 510d are closed so that the hot water side circuit is set to the CT 504 side so that the hot water of the heat pump 4 can be cooled.

  In the hot water supply shortage prevention control according to FIG. 23, the automatic control device determines whether, for example, the hot water supply temperature is lower than a predetermined value, or the second heat supply amount adjustment valve 109 is fully opened (the opening degree of the predetermined value). It is determined whether or not the amount of heat supplied to the external air conditioner 2 is insufficient (step S301). If it is insufficient, the process proceeds to step S302. Proceed to step S310. Note that if the hot water boiler 506 is operating, the automatic control device proceeds to step S310.

  If the amount of heat supplied to the external air conditioner 2 is insufficient, the automatic control device determines whether or not there is a heat pump 4 waiting in the hot water follow-up mode in step S302, and if there is, the heat pump 4 starts (step S303), returns to the beginning of the process, and if it does not exist, it is further determined whether or not there is a heat pump 4 waiting in the cooling mode (step S304). If not, the hot water boiler 506 is operated as a backup related to the amount of heat of the hot water (step S305), the process returns to the beginning (here, step S201), and if it exists, step S306 and subsequent steps are executed.

  In step S306, the automatic control device opens the corresponding motor-operated valves 510a to 510d and closes the motor-operated valves 512a to 512d for one of the heat pumps 4 waiting in the cooling mode, and externally adjusts the circuit on the hot water side. As the machine 2 side, a transition is made to the hot water follow-up mode. Subsequently, the automatic control device executes step S307, and if the hot water boiler 506 is in operation (YES), starts the operation of the heat pump 4 waiting in the hot water follow-up mode (step S308), and performs the processing. Returning to the beginning, if the hot water boiler 506 is not in operation (NO), the process returns to the beginning of the process, and the operation of the heat pump 4 that has shifted to the mode in step S306 is started by executing the subsequent steps S301 to S303.

  On the other hand, when the amount of heat to the external air conditioner 2 is not short and the process proceeds to step S310, the automatic control device determines whether or not the hot water boiler 506 can be stopped from the set temperature (58 degrees) of the hot water boiler 506. The hot water boiler 506 is stopped as a backup boiler stop control if possible (step S311), and the process proceeds to step S312.

  In step S312, the automatic control device determines whether or not the number of operating heat pumps 4 according to the hot water follow-up mode can be reduced based on whether or not the hot water return temperature is higher than a predetermined value. The operation of one of the heat pumps 4 is stopped (step S313), and the process proceeds to step S314.

  In step S314, the automatic control device checks whether the number of operating heat pumps 4 and the number of standby units in the hot water follow-up mode are equal to or less than the allowable operation number. That is, when the heat pump 4 in the hot water follow-up mode is increased, the supply amount of cold water is increased accordingly, but the heat pump 4 is maintained with a temperature drop that is not more than a predetermined temperature even though the cold water is heated. It is determined whether or not sufficient heating can be performed so as not to cause a return event.

  If NO in step S314, the automatic control device shifts to cold water supply prevention control. On the other hand, if YES in step S314, the automatic control device shifts the heat pump 4 to the hot water follow-up mode and switches the hot water side circuit when the heat pump 4 stands by in the cooling mode exists, and the hot water boiler 506 is switched on. It is confirmed whether or not it is in operation (steps S315 to S317), and when there is no heat pump 4 waiting in the cooling mode, the process proceeds to cold water supply shortage prevention control.

  If it is confirmed in step S317 that the hot water boiler 506 is in operation, the automatic control device operates the heat pump 4 that stands by in the hot water follow-up mode (step S318), and returns to the beginning of the process.

  On the other hand, in the cold water supply shortage prevention control of FIG. 24, the automatic control device determines whether or not the cold water return temperature is higher than a predetermined value as to whether or not the cold heat supplied to the external air conditioner 2 is insufficient. Judgment is made based on whether or not 46 is fully open (more than a predetermined opening) (step S401), and if it is not insufficient, the number of heat pumps 4 operated in the cooling mode can be reduced. In step S402, one of the heat pumps 4 is stopped (step S403), and the process returns to the beginning.

  On the other hand, if the cooling control is insufficient (YES in step S401), the automatic control device checks whether there is a heat pump 4 waiting in the cooling mode (step S404). Operation is started (step S405), and the process returns to the beginning.

  If the automatic control device determines in step S404 that there is no heat pump 4 that waits for cooling, it determines whether there is a heat pump 4 that waits for the hot water follow-up operation (step S406). 4 is switched to the cooling mode (step S407), and the process returns to the beginning. In step S407, when there is no standby device related to the cooling mode, the heat pump 4 related to the warm water mode is switched to the cooling mode to cope with the lack of cold water.

  On the other hand, the automatic control device that has determined that there is no heat pump 4 waiting for the follow-up operation in step S406 starts the operation if the hot water boiler 506 is not in operation (steps S408, S409), and the heat pump 4 in the follow-up operation. One of the units shifts to the cooling mode (step S410), opens the motor-operated valves 512a to 512d, closes the motor-operated valves 510a to 510d, and sets the circuit on the hot water side to the CT 504 side so that the hot water of the heat pump 4 can be cooled ( Step S411), the process returns to the beginning. In step S411, when there is no heat pump 4 related to the cold water mode or the hot water follow-up standby, the heat pump 4 related to the hot water follow-up mode is switched to the cooling mode to cope with the cold water shortage. In addition, when the heat is insufficient due to this switching, the above hot water supply shortage prevention control is used.

  In the air conditioning system 501 according to the eleventh embodiment, since there are a plurality of heat pumps 4a to 4d as cooling medium heaters, any scale factory can be flexibly accommodated at low cost. The booth air conditioner using the heat pump 4 having excellent energy efficiency can be appropriately introduced.

  In the air conditioning system 501, the automatic control device changes the number of operating heat pumps 4 based on the state of cold water or hot water (temperature, heat quantity, flow rate, etc.) or the opening degree of various flow rate control valves corresponding thereto. Or, since the operation mode (warm water follow-up mode or cooling mode) of the heat pump 4 is switched, the control regarding the adjustment of the chilled water load and the prevention of insufficient supply of chilled water or hot water can be performed automatically, and the booth air conditioning is efficient. Can ensure stable operation.

  In the air conditioning system 501, since the hot water boiler 506 is installed, it is possible to perform backup when the amount of heat for generating hot water is insufficient or when the system is started, and the operation can be further stabilized. Instead of the hot water boiler, a steam heater, an electric heater, or an air cooling heat pump may be employed.

[Twelfth embodiment]
FIG. 25 is a schematic diagram of an air conditioning system 601 according to a twelfth embodiment. The air conditioning system 601 is the same as the eleventh embodiment, and is downstream of the heat exchanger 40 related to the exhaust hot water X with respect to the configuration of the eleventh embodiment ( On the cold water return side), an air cooling heat pump 154 (single or plural) and a heat exchanger 640, a heat exchange introduction pipe 642, a heat exchange lead pipe 644, and a flow rate adjustment valve 646 connected thereto are added. . The hot water boiler 506 can be omitted. When there are a plurality of air-cooled heat pumps 154, the automatic control device switches the number of operating units according to the capacity required for cooling the hot water.

  Such an air conditioning system 601 operates in the same manner as in the eleventh embodiment, for example, as described below.

  That is, as shown in FIG. 26, at the time of starting the system, the automatic control device checks whether or not there is a start command for the external air conditioner 2 (step S501), and if there is a start command, the air cooling heat pump 154 is turned on. Operate (step S502). By operating the air-cooled heat pump 154, the cold water temperature of the heat pump 4 can be controlled by supplying the heat exchanger 640 with the heat for the cold water-side heating that is insufficient when the system is started (at the start of operation of the factory). Further, the automatic control device performs the hot water follow-up operation for one heat pump 4 (step S503).

  Next, the automatic control device waits until the temperature of cold water or hot water is stabilized (step S504), and executes a loop that is repeated until the air volume, temperature, and humidity of all the external air conditioners 2 are stabilized by inverter control or the like. (Step S505).

  In the loop, the automatic control device first activates the external air compressor 2 one by one and gradually increases the air volume of the booth air conditioning (step S506). Stability is ensured in the control using the heat pump 4 to which hot water and cold water are simultaneously supplied by increasing the air volume or sequentially starting the external air conditioner 2.

  Next, the automatic control device has insufficient hot water based on criteria such as whether or not the second heat supply amount adjustment valve 109 is fully open (above a predetermined opening degree), whether or not the hot water temperature is below a predetermined value, etc. (Step S507), if it is not insufficient, the process proceeds to step S512, which will be described later. If it is insufficient, step S508 and subsequent steps are executed.

  In step S508, the automatic control device determines whether the opening degree of the flow rate adjustment valve 646 on the air cooling heat pump (air cooling HP) 154 side is 60% or less, for example. Additional activation is performed in the follow-up mode (step S509), and the process returns to step S507. If it is not 60% or less, the hot water boiler 506 is operated when it is stopped (steps S510 and 511), and the process returns to step S507. By executing step S509, first, the heat pump 4 that is operated in accordance with the hot water appears, and the supply of hot water is stabilized. At this time, a balance is secured by the air cooling heat pump 154 with respect to the cold water side. In addition, when there is a shortage of cold in summer or the like, the shortage of cold water is resolved after the next step S512.

  On the other hand, the automatic control device determines whether or not the flow rate control valves 46 and 646 are greater than or equal to a predetermined opening, whether or not the cold water temperature is greater than or equal to a predetermined value, etc. Based on the criteria, it is determined whether or not the cold water is insufficient (step S512). If the cold water is insufficient, the heat pump 4 is additionally activated in the cooling mode (steps S513 and S512), and the cold water is not insufficient. In this case, the loop process is completed (step S514), and the process proceeds to step S515.

  Only when it is determined in step S515 that the opening degree of the flow rate adjustment valve 46 related to the discharged hot water S is 70% or less, the automatic control device stops the air-cooled heat pump 154 assuming that the amount of heat of the discharged hot water X is sufficient ( Step S516), the start-up process of the external air handler 2 is completed.

  Next, after completion of the system startup, the automatic control device performs cold water load adjustment control of the heat pump 4 as shown in FIG. 27, hot water supply shortage prevention control or cold water supply shortage prevention control of the heat pump 4 as in the eleventh embodiment. I do.

  That is, when the automatic control device receives a command related to stopping all of the external air conditioners 2 (NO in step S201), the automatic control device stops all of the heat pumps 4 (step S202) and stops the hot water boiler 506. Then (step S203), the air cooling heat pump 154 is further stopped (step S601), and the control is completed.

  In addition, if the opening degree of the flow rate adjustment valve 46 related to the discharged hot water X is, for example, 70% or less (YES in step S602), the automatic control device determines whether the cold air is sufficiently used in the external controller 2 or is discharged. Assuming that the temperature of the hot water X is sufficiently high, the air-cooling heat pump 154 is stopped (step S603), the allowable number of heat pumps 4 related to the hot water follow-up mode is increased by one (step S206), and another control is performed.

  On the other hand, if the opening degree of the flow rate control valve 46 related to the waste water X is not 70% or less (NO in step S602), the automatic control device assumes that the cold water cannot be sufficiently heated with the waste water X, and the air cooling heat pump 154 This is operated in the heating mode only when it is stopped (steps S604 and S605), and if the opening degree of the flow rate control valve 646 related to the air cooling heat pump 154 is 80% or more (YES in step S606), the air cooling heat pump Assuming that the cooling heat is not sufficiently eliminated even by the operation of 154, the allowable number of heat pumps 4 operated in the hot water follow-up mode is reduced by one, and the heat pump 4 operated or waited in the hot water follow-up mode is set to the cooling mode. The motorized valves 512a to 512d corresponding to the heat pump 4 are opened and the motorized valves 510a to 510a are opened. As CT504 side circuit of the hot water side to close the 0d, hot water of the heat pump 4 to allow cooling (step S207), and proceeds to other control. In addition, when the heat pump 4 operated by the hot water follow-up operation decreases and the heat becomes insufficient, it is handled by the hot water supply shortage prevention control.

  In addition, if the opening degree of the flow rate adjustment valve 646 related to the air cooling heat pump 154 is not 80% or more (NO in step S606), the automatic control device sets the opening degree of the flow rate adjustment valve 646 related to the air cooling heat pump 154 to 60% or less, for example. Only when the amount of heat for chilled water heating is sufficient, the allowable number of heat pumps 4 that can be operated in the hot water follow-up mode is increased by one (steps S607 and S206), and the process proceeds to another control.

  Even in the air conditioning system 601 according to the twelfth embodiment, as in the eleventh embodiment, by switching the operation state for a plurality of heat pumps 4, it is possible to secure a stable and stable operation with excellent adaptability for booth air conditioning. it can.

  Further, in the air conditioning system 601, since the cold water side is heated by the air-cooled heat pump 154 in addition to the discharged hot water X, it is necessary to install the air-cooled heat pump 154 as compared with the eleventh embodiment, but the presence and state of the discharged hot water X Regardless of this, it is possible to provide booth air conditioning with extremely good energy efficiency by continuous operation of the heat pump 4.

[13th form]
FIG. 28 is a schematic diagram of an air conditioning system 701 according to a thirteenth embodiment. The air conditioning system 701 is similar to the first embodiment, and includes a cooling tower (CT) 754 with respect to the configuration of the first embodiment, and the cold side is cooled. The side supply pipe 30 and the cooling side return pipe 32 and the CT side supply pipe 730 and the CT side return pipe 732 can be switched. The switching is performed by the automatic control device, but may be performed by a switch operation. Here, the heat pump 4 includes a plurality of exhaust heat recovery type heat pumps. The heat pump 4 is provided in a facility such as a factory, monitors the power consumption (amount of power received) of the facility with a sensor, and further controls the device driven by the electric power according to the power consumption or the power consumption. It is electrically connected to a demand controller (not shown) that executes signal transmission. Further, the automatic control device is electrically connected to a mode changeover switch (not shown) relating to the heat pump 4. Further, instead of switching between the pipes 30 and 32 and the CT side supply pipe 730 and the CT side return pipe 732, the cooling water of the cooling tower 754 (pipes 730 and 732) and the hot water of the heat pump 4 (pipes 32 and 30) are exchanged. You may do it.

  Such an air conditioning system 701 operates in the same manner as in the first embodiment, for example, as shown in FIG.

  That is, when there is a heat pump 4 (FIG. 28A) that is operated following hot water (YES in step S701), the automatic control device receives a predetermined amount of power (for example, contract power or slightly lower than this) from the demand controller. If a signal indicating that the value exceeds (value) is output (YES in step S702), the operation priority is lower than the other heat pumps 4 although there are other heat pumps 4 that follow the hot water operation (all the hot water operation is performed). If the operation priority is the lowest among the heat pumps 4 (YES in step S703, YES in step S704) or there is no other heat pump 4 that is operated following the hot water (NO in step S703), the hot water circuit is cooled to the cooling tower. While switching on the 754 side, the heat pump 4 is operated in the cooling mode (step S705). 28 (b)).

  In addition, the automatic control device switches the operation of the heat pump 4 having a low priority to the cooling mode (step S705) when there is no signal from the demand controller but grasps the pressing of the mode switch (YES in step S706).

  As described above, when the operation mode of the heat pump 4 is switched from the hot water follow mode to the cooling mode, the power consumption can be reduced as illustrated below. That is, in the hot water following operation of FIG. 28A, when the heating medium is 60 degrees, the cooling medium is 7 degrees, the cooling heat supply amount is 260 kW, and there is no warming with the waste water X, the power consumption is 120 kW (cooling side COP2. 17). When the cooling operation is switched from this state, the power consumption becomes 37 kW (cooling side COP 7.1) even if the heating medium 37 degrees, the cooling medium 7 degrees, and the cooling heat supply amount 260 kW remain without being heated by the waste water X. Further, it is possible to further improve the efficiency while maintaining the amount of heat and reduce the power consumption. If the heating amount is insufficient during the cooling operation, the heating amount is supplemented with another heat source such as a hot water boiler.

  In the air conditioning system 701 according to the thirteenth embodiment, since the operation mode of the heat pump 4 can be switched between the hot water follow-up mode and the cooling mode, the power consumption can be suppressed by switching from the hot water follow-up mode to the cooling mode. It is possible to prevent the situation exceeding the contract power and continue the operation of the heat pump 4, and to provide booth air conditioning excellent in energy saving and operation stability.

  It should be noted that at least one of the cold water load adjustment control, the hot water supply shortage prevention control, and the cold water supply shortage prevention control as in the twelfth and thirteenth forms is at least a paint drying device (for example, a book drying device) using an exhaust heat recovery type heat pump. An application relating to Japanese Patent Application No. 2008-305017 by the applicant), an electrodeposition coating apparatus using an exhaust heat recovery type heat pump or the like (for example, Japanese Patent Application No. 2008-209954 or an application related to Japanese Patent Application No. 2008-310138 by the applicant), or The present invention can also be applied to temperature control of a molding machine using an exhaust heat recovery type heat pump or the like (for example, Japanese Patent Application No. 2009-276713 by the present applicant).

[14th form]
FIG. 30 is a schematic diagram of an air conditioning system 801 according to the fourteenth embodiment, and the air conditioning system 801 is the same as that of the first embodiment, but is disposed in front of the hand blown booth HB that is manually sprayed by the external air conditioner 2. In addition, an exhaust circulation air conditioner 802 as an air conditioner is provided between the hand-blown booth HB and the automatic painting chamber RB for painting by a robot. The exhaust gas circulation air conditioner 802 includes a cooling coil 816, a heater 818, and a blower 820, which are the same as the external air conditioner 2, respectively. The exhaust circulation air conditioner 802 sucks and reuses the exhaust A1 (base air) of the hand blown booth HB from the base air intake port and supplies it to the automatic painting chamber RB as adjusted air B2 for the purpose of energy saving. When the exhaust A1 is discharged, a water film is stretched on the wall or floor of the exhaust chamber to collect the paint mist, and the exhaust A1 is in a high humidity state. In addition, the exhaust B3 comes out from the automatic painting chamber RB. In addition, it replaces with hand blown booth HB, or an automatic painting chamber may be arrange | positioned with hand blown booth HB, and the exhaust_gas | exhaustion may be recycled.

  Such an air conditioning system 801 operates in the same manner as in the first embodiment. That is, in the winter season or the like, even when the heating load in the exhaust circulation air conditioner 802 is larger than the cooling load and the operation of the heat pump 4 cannot be maintained as it is, the exhausted hot water X is applied to the cooling side. The heating load and the cooling load are balanced, the operation according to the heating load of the heat pump 4 is continued, and the air B2 whose temperature or humidity is adjusted for the exhaust A1 is supplied to the automatic painting chamber RB for reuse. Is possible.

[15th form]
Fig. 31 (a) is a schematic diagram of the air conditioning system 821 according to the fifteenth embodiment in summer and the like, and Fig. 31 (b) is a schematic diagram in winter and the like, and the air conditioning system 821 is a cooling medium tank as in the eleventh embodiment. 208 and a hot water tank 508, and a heat pump 4x is disposed between these tanks. In addition to the external air conditioner 2, an exhaust circulation air conditioner 822 that adjusts the temperature and humidity of the exhaust AH of the manned painting chamber HP and supplies it as an air BA to the automatic painting chamber AP is provided. The exhaust circulation air conditioner 822 includes a cooling coil 826, a heater 828, and a blower 830. The exhaust circulation air conditioner 822 may process the exhaust of the automatic painting chamber for reuse instead of the manned painting chamber HP or together with the manned painting chamber HP.

  The air conditioning system 821 includes a heat pump 4y on the cooling medium tank 208 side, and can cool the cold water in the cooling medium tank 208. The heating medium side circuit of the heat pump 4 y is connected to the cooling tower 832, and the heating medium of the heat pump 4 y can be cooled by the cooling tower 832. Further, a hot water tank 838 is arranged on the heating medium side of the heat pump 4y, and the heating medium side circuit can be switched to the hot water tank 838 side. The turbo chiller 834 (a part thereof) can supply cold heat to the cooling medium tank 208 by a refrigerator cooling circuit 836. The refrigerator cooling circuit 836 is a circuit composed of a supply pipe and a return pipe, but is shown as a bidirectional arrow in the figure, and the same applies to some of the circuits below.

  In addition, the factory is provided with an air compressor 840 that discharges the warm water (cooling water that is heated and discharged). The heat exchanger for heating the cooling medium tank 208 (not shown) is provided for the warm water. 2), the circuit can be switched between the circuit 841 on the side and the cooling side supply pipe 30y and the cooling side return pipe 32y of the heat pump 4y. In addition, it may replace with the waste water of the air compressor 840, or may use the waste heat of the other apparatus which belongs to a factory with the waste water of the air compressor 840. FIG.

  In the factory, a boiler 842 for supplying steam or the like that can heat the hot water in the hot water tank 838 is installed. The boiler 842 is a city gas boiler here, and is connected to the hot water tank 838 via the boiler hot water circuit 843.

  Note that hot water circuits 844 and 845 are sequentially arranged between the hot water tank 508, the reheater 18, and the heater 828. Further, between the cooling medium tank 208 and the cooling coils 16 and 826, chilled water circuits 846 and 847 are sequentially arranged. Further, a hot water circuit 848 is disposed between the hot water tank 838 and the preheater 12. The hot water tank 838 and / or the cooling medium tank 208 may be omitted, and hot water and / or cold water may be supplied directly. In addition, adjustment of the supply amount of the cooling medium and heating medium to the various coils and heaters of the external air conditioner 2 and the exhaust circulation air conditioner 822 is not limited to using a three-way valve, but is controlled by an inverter (the pump controls the flow rate by an inverter). This point can be changed not only in this embodiment but also in any embodiment.

  Such an air conditioning system 821 operates in the same manner as in the eleventh and fourteenth embodiments, for example, as follows.

  That is, in the summer season and the like, as shown in FIG. 31A, heating of the hot water tank 508 (50 degrees) and cooling of the cooling medium tank 208 (7 degrees) are performed with the heat pump 4x following the heating load. . If the cooling is likely to be insufficient when the heating load is matched, the cooling medium is supplied to the cooling medium tank 208 by the heat pump 4y to adjust the temperature of the cold water. The heating medium (37 degrees) generated during the operation of the heat pump 4y is cooled by the cooling tower 832 and circulated. Then, regardless of the operation state of the heat pump 4y, when the chilled water in the cooling medium tank 208 is to be overcooled, the exhaust heat (cooling water 40 degrees) of the air compressor 840 is applied to the cooling medium tank 208 via the circuit 841. Then, warm the cold water and adjust to an appropriate temperature.

  By such operation of the heat pump 4 and the like, the air conditioning system 821 can continue the supply of the adjusted air B and BA to the booth and the automatic painting room AP in a state of high energy saving (external air conditioner 2 35 degree 80% outside air A is changed to 28 degree 80% air B, and the exhaust circulation air conditioner 822 changes 26 degree 90% or more of exhaust AH to 28 degree 80% air BA).

  On the other hand, in the winter season and the like, as shown in FIG. 31 (b), heating of the hot water tank 508 (50 degrees) and cooling of the cooling medium tank 208 (7 degrees) are performed while following the heating load by the heat pump 4x. Do. Further, when the cooling of the cooling medium tank 208 is insufficient, a turbo chiller 834 is used. Further, the heating side of the heat pump 4y is switched to the hot water tank 838 side, and the hot water for the pre-heater 12 is heated with the assistance of the boiler 842 as appropriate (60 degrees). The exhaust heat of the air compressor 840 is applied to the cooling side of the heat pump 4y, and consideration is given to continued operation.

  By such operation of the heat pump 4 and the like, the air conditioning system 821 can continue the supply of the adjusted air B and BA to the booth and the automatic painting room AP in a state of high energy saving even in winter. (In the external air conditioner 2, 2 degrees 80% outside air A is changed to 20 degrees 80% air B, and in the exhaust circulation air conditioner 822, 18 degrees 90% exhaust AH is changed to 20 degrees 80% air BA).

  In the air conditioning system 821, the reheater 18 of the external air conditioner 2 is heated by hot water from the hot water tank 508, while the preheater 12 is heated by hot water from the hot water tank 838, and the reheater 18 and the hot water tank 838 are used. Since the hot water system is independent, appropriate temperature or heat control can be executed on the reheater 18 and the hot water tank 838, respectively, and efficient control can be realized. That is, for example, the control of lowering the warm water temperature (50 degrees) of the reheater 18 with respect to the warm water temperature (60 degrees) of the preheater 12 is executed to improve the capacity of the heat pump 4x and improve the efficiency. it can.

[16th form]
FIG. 32A is a schematic diagram of the air conditioning system 851 according to the sixteenth embodiment in summer and the like, and FIG. 32B is a schematic diagram of winter and the like, and the air conditioning system 851 is the same as that of the fifteenth embodiment. The hot water tank 838 is omitted, the heating side of the heat pump 4y can be switched between the cooling tower 832 side and the hot water tank 508 side, and the cooling side of the heat pump 4y is switched between the cooling medium tank 208 side and the air compressor 840 side. It is possible. The preheater 12 is connected to the hot water tank 508 or the hot water circuit 844 via the hot water circuit 848a.

  Such an air conditioning system 851 operates in the same manner as in the fifteenth embodiment. In particular, in the winter season, the heat pump 4y heats the hot water tank 508 in addition to the heat pump 4x, and the boiler 842 heats the hot water tank 508 (60 degrees). ). Therefore, also in the air conditioning system 851, the supply of the adjusted air B and BA to the booth and the automatic painting room AP can be continued in a state of high energy saving.

[17th form]
FIG. 33A is a schematic diagram when the cooling load of the air conditioning system 861 according to the seventeenth embodiment is heavy, FIG. 33B is a schematic diagram when the cooling load of the air conditioning system 861 is relatively light, and FIG. Is a schematic diagram when the thermal load of the air conditioning system 861 exceeds the cooling load, FIG. 34A is a schematic diagram when there is no cooling load of the air conditioning system 861, and FIG. 34B is no cooling load of the air conditioning system 861. It is a schematic diagram when the thermal load is relatively large, and the air conditioning system 851 is the same as in the third embodiment, but uses heat pumps 4p, 4q, 4r, etc. instead of a plurality of air-cooled heat pumps, and air compression A machine 840 is deployed. The air conditioning system 861 includes a heat exchanger 862 that heats hot water in the heating-side supply pipe 34 of the heat pump 4, a boiler (not shown) that can supply steam (hot water) ST to the heat exchanger 862, and the supply amount of the steam ST. Is provided with a heat supply amount adjustment valve 864 (see FIG. 34B). The air conditioning system 861 also includes a cooling tower 832a that cools the cooling water of the air compressor 840, and a cooling / heating supply control valve 866 for adjusting the cooling amount.

  The heating side of the heat pump 4p or the like is connected to a cooling tower 832p or the like via a supply side motor valve 47p or the like, a return side motor valve 49p or the like. The heating supply pipe 34p such as the heat pump 4p can be switched (or the flow rate adjusted) to the heating side supply pipe 34 side of the heat pump 4 by the motor valve 47p. The heating return pipe 36p such as the heat pump 4p The valve 49p can be switched (or the flow rate can be adjusted) to the heating side return pipe 36 side of the heat pump 4. Note that any of the cooling towers 832p and the like and the cooling tower 832a may be common.

  Further, the cooling side motor valves 43p, 45p and the like of the heat pump 4p and the like allow switching (or flow rate adjustment) between the cooling side of the heat pump 4 and the air compressor 840 side in the cooling side circuit. When switched to the air compressor 840 side, heat exchange with the cooling water of the air compressor 840 is possible. In addition, motor valves 43 and 45 are installed in order on the cooling side supply pipe 30 and the cooling side return pipe 32 of the heat pump 4, and are similarly switched between the external air compressor 2 side and the air compressor 840 side (or flow rate adjustment). ) It is possible. In FIGS. 33A and 33B, the circuit of the heat pump 4p is omitted, and in FIG. 33C and FIG. 34A, the heating side circuit of the heat pump 4p is omitted. These heating-side circuits are actually connected to the reheater 18 of the external air conditioner 2.

  Such an air conditioning system 861 operates in the same manner as in the third embodiment, for example, as follows.

  That is, in the case of FIG. 33 (a), such as during the summer heavy cooling load, it is necessary to supply cold heat to the cooling coil 16 for dehumidification in the external air conditioner 2 (supercooling by the cooling coil 16 or reheating by the reheater 18). Heating), cooling operation of the heat pump 4p and the like in the number corresponding to the cooling load is performed. At this time, the cooling side of the heat pump 4p or the like is switched to the cooling side of the heat pump 4, and the heating side of the heat pump 4p or the like is switched to the cooling tower 832p or the like side. If a plurality of heat pumps 4p are in cooling operation, all of the heat pumps 4p 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 coil 16 at 7 degrees by the heat pumps 4, 4 p and the like, and returns to the heat pump 4 at 12 degrees. At this time, the hot water supply temperature of the heat pump 4 is 60 degrees, and the warm water return temperature is 55 degrees. The hot water supply temperature of the heat pump 4p and the like is 35 degrees, and the warm water return temperature is 30 degrees by cooling of the cooling tower 832p and the like. With the cooling, the heat pump 4p and the like can continue the cooling operation.

  Further, in the case of FIG. 33 (b), such as during summer cooling and light load, when there is one heat pump 4p or the like that performs cooling operation according to the load, the other heat pumps 4p and so on are placed on standby for cooling. Wait for hot water following operation (heating operation). The heating side of the heat pump 4p or the like in the warm water follow-up standby mode is switched from the cooling tower 832p or the like side to the heating side of the heat pump 4, and the cooling side is switched from the cooling side of the heat pump 4 to the air compressor 840 side. Then, when the automatic control device detects a lack of heat, such as when the warm water return temperature or warm water outlet temperature of the heat pump 4 falls below a predetermined value, the automatic control device operates the heat pump 4p and the like that is in the warm water tracking standby. Note that when the hot water follow-up operation is started even in one of the heat pumps 4p and the like, the heat pump 4p and the like that are in the cooling standby state are switched to the hot water follow-up standby state.

  For example, chilled water is supplied to the cooling coil 16 at 7 degrees by the heat pump 4 or the heat pump 4p that performs cooling operation, and returns to the heat pump 4 at 12 degrees. Here, although the hot water supply temperature of the heat pump 4 is 60 degrees, when the warm water return temperature falls from 55 degrees to 53 degrees or less, the heat pump 4p or the like waiting for warm water follow-up is operated, and the cold water is cooled to 30 degrees. It is supplied to 840 and returned at 35 degrees by heat exchange with cooling water. Further, the heat pump 4p or the like during the hot water follow-up operation heats the hot water returning to the heat pump 4 to 60 degrees and returns it to the heating side supply pipe 34 of the heat pump 4. By applying the exhaust heat of the air compressor 840 to the heat pump 4p and the like during the hot water following operation, the heat pump 4p and the like can continue the heating operation.

  Furthermore, when the cooling load (cooling load) is small due to a decrease in the outside air temperature at night in summer, etc., and becomes less than the minimum cooling output (or a predetermined output exceeding this), as shown in FIG. Then, the cooling side of the heat pump 4 is switched to the air compressor 840 side, and the cooling of the external air conditioner 2 by the heat pump 4 is stopped. The external air conditioner 2 is cooled by a single heat pump 4p or the like that performs cooling operation.

  For example, cold water is supplied to the cooling coil 16 at 7 degrees by the heat pump 4p or the like that performs cooling operation, and returns to the heat pump 4 at 12 degrees. The heating side of the heat pump 4p or the like that performs cooling operation is cooled by the cooling tower 832p or the like so that the operation can be continued. Further, the cold water supply temperature of the heat pump 4 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 840, so that the hot water supply by the heat pump 4 can be continued. On the other hand, the hot water side of the heat pump 4 is appropriately heated by the heat pump 4p or the like during the hot water follow-up operation, and the supply temperature is maintained at 60 degrees (return temperature is around 55 degrees).

  Further, when cooling for temperature reduction or dehumidification is not necessary in the intermediate season or winter season, as shown in FIG. 34 (a), the heat pump 4p or the like is in a hot water follow-up operation or a standby state according to the thermal load, The cooling side including the heat pump 4 is switched to the air compressor 840 side. However, when the automatic control device determines that cold water is likely to be required in the external air conditioner 2 based on the cooling side temperature, the opening degree of various motor valves, the outside air temperature, the booth temperature, or the relationship thereof, the heat pump 4p, etc. One of the is set in a cooling standby state.

  For example, the heating side of the heat pumps 4, 4p, etc. returns at 55 degrees and is supplied at 60 degrees. In addition, the cooling side of the heat pumps 4, 4p, etc. is heated from 30 degrees to 35 degrees by the cooling water of the air compressor 840, and the operation of the heat pumps 4, 4p, etc. is continued using the exhaust heat of the air compressor 840. can do.

  In addition, when cooling is unnecessary and the thermal load is large in winter, etc., as shown in FIG. 34 (b), the heat pump 4p and the like are operated following hot water, and the cooling side including the heat pump 4 is switched to the air compressor 840 side. It is done. Further, the steam ST and the like are supplied from the boiler after adjustment by the heat supply amount adjustment valve 864 by the heat load, and the hot water is heated via the heat exchanger 862.

  Furthermore, if the exhaust heat quantity of the air compressor 840 decreases due to a decrease in the air consumption of the factory and the cooling side such as the heat pumps 4 and 4p cannot be sufficiently heated, the cold water such as the heat pumps 4 and 4p is left as it is. The return temperature is lowered and the heat pump 4, 4p, etc. is 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 4p 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 840. The decrease in the heating amount due to the stop of the heat pump 4p or the like is compensated by the heating by the heat exchanger 862. The output of the heat pump 4, 4p or the like may be reduced by an inverter or the like to prevent the cooling water temperature of the air compressor 840 from decreasing, or the flow rate of the hot water may be reduced by a hot water pump or an inverter or the like. The output of 4p or the like may be reduced to prevent the cooling water temperature of the air compressor 840 from decreasing, or the amount of heat in the heat exchanger 862 may be increased to reduce the burden on the heat pumps 4 and 4p, etc. The heating amount of the cold water may be reduced to prevent the cooling water temperature of the air compressor 840 from decreasing. Moreover, the fall of the cooling water temperature may be prevented by lowering the hot water supply temperature set value of the heat pump 4 and reducing the output of the heat pump 4. Instead of the heat exchanger 862, a hot water boiler, an electric heater, or an air-cooled heat pump may be used.

  In addition, when the amount of exhaust heat from the air compressor 840 increases due to an increase in factory air consumption, etc., and the heating on the cooling side of the heat pumps 4, 4p, etc. becomes excessive, the cold water returns to the heat pumps 4, 4p, etc. as they are. The temperature rises and becomes a temperature at which the heat pumps 4, 4p, etc. stop. Therefore, the automatic control device is a heat pump in which the boiler is in operation and is waiting to follow the hot water when the cold water becomes a predetermined temperature or higher or the cooling water temperature of the air compressor 840 becomes a predetermined temperature (for example, 35 degrees) or higher. If there is 4p or the like, the heat pump 4p or the like is operated to cool the cooling water, or the cooling tower 832a is operated to keep the cooling water temperature from rising.

  For example, the cooling side of the heat pumps 4, 4p, etc. is supplied at 30 degrees and returns at 35 degrees. Further, the heating side of the heat pumps 4 and 4p, etc. is supplied from 58 degrees to 60 degrees by heating of the heat exchanger 862, and returns at 53 degrees.

  In the above air conditioning system 861, the cooling side of the heat pumps 4, 4 p and the like is automatically switched to the air compressor 840 side according to the heating load and cooling load, and the heat pumps 4, 4 p are exchanged with the cooling water of the air compressor 840. Therefore, the operation of the heat pumps 4, 4p, etc. can be continued using the cooling water, and the external air conditioner 2 can be operated in a state of high energy saving. Note that heat exchange by the heat exchanger may be performed between the cooling water of the air compressor 840 and the cold water of the heat pump 4.

  Further, in the air conditioning system 861, the reheater 18 and the preheater 12 of the external air conditioner 2 are heated by hot water from the shared hot water tank 508 so that the system is shared, so the number of tanks is reduced and the system is simplified. , The configuration can be simplified.

[18th form]
FIG. 35A is a schematic diagram in the case where the cooling load is extremely large with respect to the thermal load in the air conditioning system 871 according to the eighteenth embodiment, and FIG. 35B is the cooling load that is large with respect to the thermal load in the air conditioning system 871. FIG. 35C is a schematic diagram in the case where the thermal load is larger than the cold load in the air conditioning system 871, and FIGS. 36A and 36B are diagrams showing failure of the air cooling heat pump in the air conditioning system 871. The air conditioning system 871 is similar to the third embodiment, and further includes an exhaust circulation air conditioner 822 similar to the fifteenth embodiment. The air conditioning system 871 includes a heat exchanger 862 similar to that in the sixteenth embodiment, a heat supply amount adjustment valve 864, and a boiler that supplies steam ST and the like.

  Further, the heating side or the cooling side of the heat pump 4 is connected to the exhaust circulation air conditioner 822 in addition to the external air conditioner 2. In addition, circuits such as the air cooling heat pump 154a can be switched between the heating side and the cooling side of the heat pump 4 by the motor valve 43a and the motor valve 45a and the like. 35 and 36, the circuit between the external air conditioner 2 and the heat pump 4 and the heating side circuit of the exhaust circulation air conditioner 822 are partially omitted.

  The air conditioning system 871 is provided with an exhaust circulation air conditioner 822. The exhaust circulation air conditioner 822 has a cooling heat load for cooling in order to dehumidify the exhaust AH from which the paint mist has been collected (high humidity) by the water film. It occurs throughout the year and the minimum cooling load in the air conditioning system 871 is also determined. In the air conditioning system 871, cooling by the air cooling heat pump 154a or the like is anticipated, and the maximum cooling power output of the heat pump 4 is made smaller than the minimum cooling load. Since the exhaust AH is used in a manned painting room or the like, the temperature is also stable throughout the year. Therefore, the cooling load in the exhaust circulation air conditioner 822 is stable throughout the year.

  Such an air conditioning system 871 operates in the same manner as the third embodiment, the fifteenth and sixteenth embodiments, and operates as follows, for example.

  That is, in the case of FIG. 35A, such as during the summer heavy cooling load, it is necessary to supply cold heat to the cooling coil 16 for dehumidification in the external air conditioner 2 (supercooling by the cooling coil 16 or reheating by the reheater 18). Heating), cooling operation of the air cooling heat pump 154a and the like in the number corresponding to the cooling load is performed. At this time, the cooling side of the air cooling heat pump 154 a and the like is switched to the cooling side of the heat pump 4. If a plurality of air-cooling heat pumps 154a are in cooling operation, all of the air-cooling heat pumps 154a 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, cold water is supplied to the cooling coils 16 and 826 at 7 degrees by the heat pump 4 or the air-cooled heat pump 154a, and returns to the heat pump 4 or air-cooled heat pump 154a or the like at 12 degrees. At this time, the hot water supply temperature of the heat pump 4 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 154a or the like or supplying it to the cooling side supply pipe 30. For hot water, the temperature of the hot water or the amount of heating is controlled by operating the heat pump 4 in the hot water follow-up mode (heat recovery operation).

  Further, in the case of FIG. 35 (b), such as during summer cold and light loads, when the number of air-cooled heat pumps 154a that perform cooling operation according to the load falls below a predetermined number (one), the other predetermined units (one) Cooling standby is performed, and the remaining air-cooled heat pump 154a and the like are standby for heating operation. The heating side of the air-cooled heat pump 154a or the like that is waiting for heating is switched from the cooling side of the heat pump 4 to the heating side. Then, when the automatic control device detects the lack of isothermal heat at which the hot water return temperature of the heat pump 4 becomes a predetermined value or less, the automatic control device operates the air-cooled heat pump 154a 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 154a and the like, the air cooling heat pump 154a 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 coil 16 at 7 degrees by the heat pump 4 or an air-cooled heat pump 154a that performs cooling operation, and returns to the heat pump 4 or the air-cooled heat pump 154a at 12 degrees. Here, although the hot water supply temperature of the heat pump 4 is 55 degrees, when the warm water return temperature falls from 50 degrees to 48 degrees or less, the air-cooled heat pump 154a or the like that is on standby for heating is operated, and the warm water that returns to the heat pump 4 is removed from the air-cooled heat pump. Heat to 55 degrees by 154a or the like, and return to the heating side supply pipe 34 of the heat pump 4 to eliminate the shortage of hot water.

  Further, when the cooling load is reduced due to a decrease in the outside air temperature at night in the summer, in the middle season or in the winter season, as shown in FIG. 35 (c), the cooling by the heat pump 4 continues and the air cooling heat pump 154a and the like ( The cooling load is adjusted by adjusting the cooling load. Here, as described above, at least in the exhaust circulation air conditioner 822, there is a cooling load throughout the year, so that cooling is not unnecessary. Further, when the air-cooling heat pump 154a or the like that is on standby for heating is operated according to the thermal load and the air-cooling heat pump 154a or the like that is on standby for heating is operated, the air-cooling heat pump 154a or the like that is on standby for cooling is switched to the heating standby state. In the air cooling heat pump 154a and the like, a single cooling standby device may be provided.

  For example, cold water is supplied to the cooling coils 16 and 826 at 7 degrees by the heat pump 4 or an air-cooled heat pump 154 a that performs cooling operation, and returns to the heat pump 4 at 12 degrees. The hot water supply temperature by the heat pump 4 and the air-cooled heat pump 154a during the 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 4 can be continued.

  In addition, when the air-cooling heat pump 154a or the like during the cooling operation fails due to a trip or the like, as shown in FIG. 36 (a), the air-cooling heat pump 154a or the like that is in the heating standby mode is switched to the cooling mode to prevent the lack of cooling. To do.

  Further, when the air-cooling heat pump 154a or the like during the cooling operation fails and there is no standby unit in the air-cooling heat pump 154a or the like, as shown in FIG. 36 (b), the air-cooling heat pump 154a or the like during the heating operation is switched to the cooling operation. Avoid the lack of cold. Here, when the heat is insufficient due to the switching, the shortage is supplemented by heat exchange or the like in the heat exchanger 864 with the steam ST, and the thermal load is backed up.

  In the air conditioning system 871 described above, the state of the air-cooled heat pump 154a and the like is switched according to the heating load and the cooling load, and the exhaust circulation air conditioner 822 is also installed in addition to the external air conditioner 2 in order to assist the heating and cooling by the heat pump 4. Therefore, the heat pump 4 can be continuously operated, and the external air conditioner 2 and the exhaust circulation air conditioner 822 can be operated in a state of high energy saving.

  Further, if the installation space can be secured, a large-capacity preheater 12 or reheater 18 can be installed, and even if the hot water supply temperature is lowered, it can cope with the heating load. On the other hand, in the air-cooled heat pump 154a and the like, the smaller the difference between the outside air temperature and the hot water supply temperature, the better the efficiency. For example, when the former is 5 degrees and the latter is 70 degrees, COP2.1 per unit is obtained. If it is 5 degrees and the latter 55 degrees, it is COP3.0 per unit. Further, basic heating is performed by the heat pump 4, and the air-cooled heat pump 154a and the like operate in an auxiliary manner. Therefore, the air conditioning system 871 can be operated with extremely good efficiency by operating the heat pump 4 and the air-cooled heat pump 154a.

[19th form]
FIG. 36 (c) is a schematic diagram of the air conditioning system 881 according to the nineteenth embodiment when the thermal load is larger than the cold load. The air conditioning system 881 is similar to the eighteenth embodiment, but the heat pump 4 The difference is that the maximum cooling output is set to be equal to or higher than the minimum cooling load.

  In the air conditioning system 881, in the heat pump 4 during the hot water follow-up operation, since the cold load is small, the cold water is returned without being sufficiently used, and the operation is stopped because the balance between the hot and cold is lost. In such a case, the hot water of the air-cooled heat pump 154a or the like during the heating operation is switched to the heat exchanger 40 side, the cold water of the heat pump 4 is heated by heat exchange, and the cold water of the heat pump 4 is deprived of the hot water. And the operation of the heat pump 4 is continued. The circuit on the heating side of the heat pump 4 may be branched to the heat exchanger 40 side, and the cold water side of the heat pump 4 may be heated by the branch circuit or the heat exchanger 40. In addition, a cold water tank is provided so that cold water can be supplied from the heat pump 4 or the air cooling heat pump 154b to the cold water tank, and can be supplied from the cold water tank to the cooling coil 826 by the cold water pump. The return temperature may be monitored, and the cold water may be directly heated by switching the air cooling heat pump 154b from the cooling mode to the heating mode in accordance with the chilled water temperature drop.

  Even in such an air conditioning system 881, the balance between the heat and heat of the heat pump 4 can be maintained and the operation of the heat pump 4 can be continued, and the external air conditioner 2 is appropriately operated in an excellent energy saving state. be able to.

[20th form]
FIG. 37A is a schematic diagram in the case where the cooling load is extremely large with respect to the thermal load in the air conditioning system 901 according to the twentieth embodiment, and FIG. 37B is the cooling load in the air conditioning system 901 that is large with respect to the thermal load. FIG. 37C is a schematic diagram when the thermal load is larger than the cooling load in the air conditioning system 901. FIG. 38A is a schematic diagram when the cooling load is not present in the air conditioning system 901. FIG. 38B is a schematic diagram of the air conditioning system 901 when there is no cooling load and the heating load is relatively large. The air conditioning system 901 is similar to the third embodiment and is similar to the eighteenth embodiment. The circuit connecting the heating side of the heat pump 4 and the air cooling heat pump 154a and the like and the circuit on the cooling side are switchable. Note that some circuits are also omitted in FIGS.

  The air-conditioning system 901 includes an air compressor 840 as in the eighteenth embodiment, and motor valves 43, 45 through 45 that switch the cooling side of the heat pump 4 to the cooling water (waste water) side of the air compressor 840. It has a circuit.

  Such an air conditioning system 901 operates in the same manner as the third and eighteenth embodiments, and operates as follows, for example.

  That is, in the case of FIG. 37 (a), such as during the summer heavy cooling load, it is necessary to supply cold heat to the cooling coil 16 for dehumidification in the external air conditioner 2 (supercooling by the cooling coil 16 or reheating by the reheater 18). Heating), cooling operation of the air cooling heat pump 154a and the like in the number corresponding to the cooling load is performed. At this time, the cooling side of the air cooling heat pump 154 a and the like is switched to the cooling side of the heat pump 4. If a plurality of air-cooling heat pumps 154a are in cooling operation, all of the air-cooling heat pumps 154a 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 coil 16 at 7 degrees by the heat pump 4 or the air-cooled heat pump 154a, and returns to the heat pump 4 or air-cooled heat pump 154a at 12 degrees. At this time, the hot water supply temperature of the heat pump 4 is 55 degrees, and the warm water return temperature is 50 degrees. Moreover, the cooling load of the heat pump 4 is reduced by the cooling of the return cold water by the air cooling heat pump 154a or the like or the supply to the cooling side supply pipe 30, and the heat pump 4 can continue the cooling operation.

  Further, in the case of FIG. 37 (b), such as during summer cooling and light load, when there is one air-cooling heat pump 154a or the like that performs cooling operation according to the load, the other air-cooling heat pump is put on standby for cooling. About 154a etc., it waits for heating operation. The heating side of the air-cooled heat pump 154a or the like that is waiting for heating is switched from the cooling side of the heat pump 4 to the heating side. Then, when the automatic control device detects the lack of isothermal heat at which the hot water return temperature of the heat pump 4 becomes a predetermined value or less, the automatic control device operates the air-cooled heat pump 154a and the like that are on standby for heating. When heating operation is started even with one of the air-cooled heat pumps 154a and the like, the air-cooled heat pump 154a and the like that are on standby for cooling are switched to a standby state for heating.

  For example, chilled water is supplied to the cooling coil 16 at 7 degrees by the heat pump 4 or an air-cooled heat pump 154a that performs cooling operation, and returns to the heat pump 4 or the air-cooled heat pump 154a at 12 degrees. Here, although the hot water supply temperature of the heat pump 4 is 55 degrees, when the warm water return temperature falls from 50 degrees to 48 degrees or less, the air-cooled heat pump 154a or the like that is on standby for heating is operated and the warm water returning to the heat pump 4 is 55 degrees To the heating side supply pipe 34 of the heat pump 4 to solve the shortage of hot water.

  Further, the cooling load is reduced due to a decrease in the outside air temperature at night in the summer, in the middle or winter, and the output of the air cooling heat pump 154a and the like during the cooling operation corresponds to a predetermined value (a predetermined ratio (25%) of the maximum output). When the cooling water return temperature is equal to or lower than a predetermined value (10 degrees), the cooling side of the heat pump 4 is switched to the air compressor 840 side and air cooling is performed as shown in FIG. One unit such as the heat pump 154a is air-cooled to cope with the cooling load of the external air conditioner 2. Further, when the air-cooling heat pump 154a or the like that is on standby for heating is operated according to the thermal load and the air-cooling heat pump 154a or the like that is on standby for heating is operated, the air-cooling heat pump 154a or the like that is on standby for cooling is switched to the heating standby state. In the air cooling heat pump 154a and the like, a single cooling standby device may be provided.

  For example, the heat pump 4 supplies hot water of 55 degrees and receives 50 degrees of return hot water, while supplying cold water of 30 degrees to the air compressor 840 side and receives 35 degrees of return cold water by heat exchange with the cooling water. . Heating of the external air conditioner 2 is performed by the heat pump 4, and cooling is performed by the air cooling heat pump 154a during the cooling operation (supply 7 degrees, return 12 degrees). The operation of the heat pump 4 is continued by applying the waste water of the air compressor 840 to the cooling side of the heat pump 4.

  On the other hand, the output of the air cooling heat pump 154a or the like during the cooling operation is equal to or higher than a predetermined value (a value corresponding to a predetermined ratio (85%) of the maximum output), or the cold water return temperature is equal to or higher than a predetermined value (15 degrees). In this case, the heat pump 4 is temporarily stopped, the cold water side is switched to the external air conditioner 2 side, the hot water of the external air conditioner 2 is covered by the air-cooled heat pump 154a, etc., and then the heat pump 4 is operated following the hot water to supply cold / hot water.

  In addition, in the case of FIG. 38A in which there is no cooling load in the intermediate season or winter season, the air-cooled heat pumps 154a and the like are heated by the number corresponding to the heating load, and the rest is set in the heating standby state. In addition, when the opening degree of the cold heat supply amount adjustment valve 48 becomes a predetermined value or more, or when the relationship between the outside air temperature and the coating booth temperature becomes a predetermined value, in order to cope with the restart of the supply of cold water (one unit ) The air cooling heat pump 154a and the like are switched to the cooling standby state. In the case of entering the cooling standby state, preheating is not necessary, and hot water is not supplied to the preheater 12.

  Also, in the case of FIG. 38B where the thermal load is large in winter, etc., if the amount of heat of the hot water is small relative to the heating load, the heating side of the heat pump 4 is heated by heat exchange with the steam ST from the boiler. And prevent underheating. For example, when the hot water return temperature of the heat pump 4 is 48 degrees and the hot water supply temperature is raised only to 53 degrees by the air-cooled heat pump 154a 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 864 is operated, and warm water supplied by the steam ST is heated to 55 degrees.

  In the air conditioning system 901 described above, the state of the air-cooled heat pump 154a and the like is switched according to the heating load and the cooling load to assist heating and cooling by the heat pump 4, and when there is no cooling load, the cooling side of the heat pump 4 is discharged with hot water. In order to make the air cooling heat pump 154a and the like stand by for cooling as necessary, the external air conditioner 2 is kept in the state of high energy saving by continuing the operation of the heat pump 4 while accurately heating or cooling the external air conditioner 2. Can be activated.

  If a large-capacity preheater 12 or reheater 18 can be installed, the temperature of the hot water can be lowered and the efficiency of the air-cooled heat pump 154a and the like can be improved. In the air conditioning system 901, the efficiency is extremely good. Operation can be continued in the state.

[21st form]
FIG. 38C is a schematic diagram in the case where there is no cooling load in the air conditioning system 911 according to the twenty-first embodiment. The air conditioning system 911 is the same as that in the twentieth embodiment. Instead of using the valves 43 and 45, the heat exchanger 40 performs heat exchange with the cooling water of the air compressor 840, and the flow control valve 46 performs the heat exchange.

  Even in such an air conditioning system 911, for example, the cooling water of 40 degrees of the air compressor 840 can raise the temperature of 25 degrees of cold water of the heat pump 4 to 30 degrees (the cooling water of the air compressor 840 becomes 35 degrees). Therefore, it is possible to continue the operation of the heat pump 4 that maintains a balance between heat and cold and is excellent in energy saving.

[22nd form]
39A is a schematic diagram when the cooling load is heavy in the air conditioning system 951 according to the twenty-second embodiment. FIG. 39B is a schematic diagram when the cooling load is light in the air conditioning system 951. FIG. Is a schematic diagram when there is no cooling load in the air conditioning system 951. The air conditioning system 951 is similar to the sixth embodiment, and further includes a heating tower 954 capable of heating cold water or the like with the heat of the outside air. . The air conditioning system 951 also includes a flow rate adjustment valve 956 that adjusts the flow rate (heat amount) of the cold water to the air cooling heat pump 154 and the heating tower 954. Further, an antifreeze such as brine is allowed to flow in the circuit on the cold water side of the heat pump 4, that is, the cold water is an antifreeze. The antifreeze liquid also enters the cooling coil 16.

  Such an air conditioning system 951 operates in the same manner as in the sixth embodiment, for example, as follows.

  That is, in the case of FIG. 39 (a), such as during the summer heavy heat load, it is necessary to supply cold heat to the cooling coil 16 for dehumidification in the external air conditioner 2 (by overcooling by the cooling coil 16 or by the reheater 18. Reheating), and the antifreeze is supplied to the cooling coil 16 by the heat pump 4. Further, in order to cope with a relatively large cooling load, the cooling operation of the air cooling heat pump 154 is performed, and a part or all of the antifreeze returning to the heat pump 4 is cooled.

  For example, the antifreeze is supplied to the cooling coil 16 at 7 degrees by the heat pump 4 or the air-cooled heat pump 154 and returns to the heat pump 4 at 12 degrees. At this time, the hot water supply temperature of the heat pump 4 is 50 degrees, and the warm water return temperature is 45 degrees. The cooling load of the heat pump 4 is reduced by cooling the return antifreeze by the air-cooled heat pump 154.

  Further, in the case of FIG. 39 (b), such as during summer cold and light load, the automatic control device switches from the air cooling heat pump 154 side to the heating tower 954 side by the flow rate adjustment valve 956 in the cooling side circuit of the heat pump 4. And the heating tower 954 is operated to heat part or all of the antifreeze. The heating tower 954 is operated so that the cooling load becomes lighter than the heating load, and the cooling heat is not sufficiently used in the external controller 2 so that the cooling heat cannot be balanced against the heating heat. It is performed so that it may be heated by the amount until.

  For example, when the hot water supply temperature of the heat pump 4 that performs the hot water follow-up operation is 50 degrees and the return temperature of the hot water is 45 degrees, the supply temperature of the antifreeze liquid is 7 degrees. Is 10 degrees, the supply temperature of the antifreeze liquid is 5 degrees, and since the heat pump cycle is not established, the heat pump 4 stops, and the heating tower 954 returns and raises the temperature of the antifreeze liquid (to 12 degrees). The heating tower 954 heats the antifreeze with the heat of the outside air (26 degrees). With this heating, the heat pump 4 can continue to operate, and can accurately respond to heating or cooling in the external air conditioner 2 in a state of high energy saving.

  Further, in the case of FIG. 39 (c) such as summer nighttime, intermediate season, or winter season, since there is no cooling load, the antifreeze liquid is not supplied to the cooling coil 16 by the cold supply amount control valve 48, and the antifreeze liquid is supplied by the flow rate control valve 956. Lead to heating tower 954 to heat.

  For example, when the hot water supply temperature of the heat pump 4 that performs the hot water follow-up operation is 50 degrees and the warm water return temperature is 45 degrees, when the supply temperature of the antifreeze liquid is -11 degrees, the heating tower 954 causes the outside air (0 degrees). The antifreeze is heated to -8 degrees using the heat of Note that the antifreeze will not freeze even if it is below 0 degrees. With this temperature increase, the operation of the heat pump 4 can be continued, and the external air conditioner 2 can be operated extremely efficiently and accurately.

[23rd form]
FIG. 40 is a schematic diagram of an air conditioning system 1001 according to the 23rd embodiment. The air conditioning system 1001 is the same as that of the 11th embodiment, but the hot water boiler 506 and the hot water tank 508 are arranged on the heating side return pipe 36 side. In addition, cold water pumps 1002a to 1002d or hot water pumps 1006a to 1006d are installed in the cooling side return pipes 32a to 32d or the heating side return pipes 36a to 36d, respectively. Moreover, the heat pump 4a is positioned as a cooling load adjusting machine. In addition, although the external air handler 2 is set to one here, you may install multiple units | sets. Moreover, although the cooling load adjusting machine is one here, you may arrange | position two or more units | sets.

  The automatic control device of the air conditioning system 1001 controls, for example, the heat pump 4b based on its own hot water supply temperature, and controls the heat pump 4a as a cold load adjuster based on its own hot water supply temperature and cold water supply temperature. The boiler 506 is controlled based on the temperature of the hot water tank 508 or the hot water return temperature of the heating side return pipe 36, and the flow rate adjusting valve 46 for adjusting the cold water return temperature is controlled based on the cold water return temperature. Control is performed based on the temperature of the air B output from the air conditioner 2 with respect to the second heat supply amount adjustment valve 109 for adjusting the supply amount or the cold heat supply amount adjustment valve 48 for adjusting the cold water supply amount to the air conditioner 2. These temperatures are detected by the respective temperature sensors and grasped by the automatic control device.

  Such an air conditioning system 1001 operates in the same manner as in the eleventh embodiment, for example, as follows.

  That is, as shown in FIG. 41, if there is a stop command for the external air handler 2 (NO in step S1001), the automatic control device stops the heat pump 4a and the like and the hot water boiler 506 (steps S1002, 1003), and performs processing. Exit.

  On the other hand, if there is no stop command (YES in step S1001), it is determined whether the opening degree of the flow control valve 46 is 60% or less (step S1004). Since there is a surplus in the amount of heat, if the hot water boiler 506 is not in operation, it returns to the beginning (NO in step S1005). In the initial state, the heat pump 4a is operating and the heat pump 4b and the like are stopped.

  On the other hand, if hot water boiler 506 is in operation (YES in step S1005), the process proceeds to loop 1 for increasing the opening degree of flow control valve 46. That is, first, the flow rate in the hot water pump 1006a of the heat pump 4a as the cold load adjusting machine is increased (step S1006). Then, since the hot water supply temperature of the heat pump 4a temporarily falls, the heat pump 4a 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 increases accordingly, and the chilled water temperature decreases as it is, so that the automatic control device increases the opening degree of the flow control valve 46 to a predetermined value (70%), The heat pump 4a and the hot water boiler 506 are set as follows so that the amount of heat exchange with the waste water X (35 degrees) is increased and the cold water return temperature (17 degrees, supply temperature 10 degrees) is maintained. Control.

  That is, the automatic control device checks whether or not the load of the heat pump 4a 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 4a is not less than the predetermined ratio (NO), the heat pump 4b or the like that is not operating is activated (one unit) (step S1008), and the process proceeds to step S1009. If the load of the heat pump 4a 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 4a is increased, the flow rate of warm water to the air conditioner 2 also increases and the return temperature of the warm water rises. Therefore, by reducing the output of the warm water boiler 506 as another heat source, the warm water return temperature can be reduced. An appropriate temperature difference (at the time of maximum output of the heat pump 4a, 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 506 is decreased (step S1010).

  For example, when a thermal load of 450 kW is provided, the heat pump 4a having a temperature difference of 5 degrees at a hot water flow rate of 43 tons provides 250 kW (43 × 5 divided by 860 kW / kcal), and the hot water boiler 506 provides 200 kW. When the hot water flow rate is increased to 60.2 tons per hour from the present state, the hot water supply temperature of the heat pump 4a is temporarily lowered, and the inverter output is 350 kW (60.2 × 5/860) in order to recover the temperature to the set value. Although the warm water return temperature from the external air conditioner 2 rises and the output of the hot water boiler 506 is reduced to 100 kW according to this, the thermal load of 450 kW is maintained while maintaining the difference between the hot water supply and return temperature in the heat pump 4a. It can correspond to.

  In contrast to the above, if the hot water return temperature is not adjusted by the hot water boiler 506, the hot water supply temperature of the heat pump 4a is temporarily lowered even if the flow rate of the return hot water is increased. Increase the hot water supply temperature to the set value (60 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 air conditioner 2 has elapsed so long that the amount of heat consumption does not change. Since the output of the heat pump 4a is reduced by the hot water follow-up operation, it can be assumed that the heating output of the heat pump 4a does not change after all, and therefore 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 when the temperature difference is 5 degrees with the heat water 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 external air conditioner 2 is 450 kW, the hot water is not used and the hot water return temperature rises, the temperature difference from the hot water supply temperature is reduced, and the hot water output of the heat pump 4a is eventually reduced at the external air conditioner 2. Match the load.

  On the other hand, if the opening degree of the flow control valve 46 is not less than the predetermined value (60%) (NO in step S1004), it is further checked whether the opening degree is a specified value (80%) or more exceeding this (step S1004). S1011), if not, return to the top of the process (step S1001), and if so, assume that the amount of heat of the waste water X is insufficient, and set the opening of the flow control valve 46 between the predetermined value and the specific value. Execute loop 3 to reduce the value to 70% (70%).

  In the loop 3, the flow rate in the hot water pump 1006a of the heat pump 4a is reduced (step S1012), and it is confirmed whether the load of the heat pump 4a 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 4a is not equal to or greater than the predetermined ratio, the automatic control device stops the operating one (one unit) of the heat pump 4b and the like (step S1014), and proceeds to step S1015. Further, if the load of the heat pump 4a 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 46 reaches a predetermined value, the process returns to step S1001). In the loop 4, if the hot water boiler 506 is not in the automatic operation mode, the mode is set (step S1016, S1017), and the output of the hot water boiler 506 is increased (step S1018).

  By executing the loop 3 or the like, the flow rate of the hot water pump 1006a is reduced and the heating amount by the hot water boiler 506 as another heat source is adjusted to appropriately maintain the temperature difference on the hot water side in the heat pump 4a, thereby cooling load Can respond appropriately.

  For example, in the case where a thermal load of 350 kW is provided, if the heat pump 4a having a temperature difference of 5 degrees at a hot water flow rate of 60.2 tons per hour is reduced from 350 kW to a state where the hot water flow rate is reduced to 43 tons per hour, the heat pump 4a In order to lower the temperature to the set value, the inverter output is reduced to 250 kW, and the warm water return temperature from the external air conditioner 2 is lowered, but with this, the 100 kW heating by the hot water boiler 506 is started. Therefore, it is possible to cope with a 350 kW thermal load while maintaining the difference between the hot water supply and return temperature in the heat pump 4a at a difference of 5 degrees.

  In contrast, if the warm water return temperature is not adjusted by the warm water boiler 506, 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 will eventually widen to 7 degrees and the heating output will be 350 kW. Will not change.

  In the air conditioning system 1001 described above, when the opening degree of the flow rate control valve 46 is equal to or greater than a predetermined value and the amount of heat of the exhaust water X is insufficient, the heat pump 4 is likely to stop because the heat balance is not balanced with the heat load. Is stopped, the output of the hot water boiler 506 is increased, and the opening of the flow control valve 46 is less than a predetermined value (and the hot water boiler 506 is operating), and there is a margin in the amount of heat of the waste water X When the operation by the heat pump 4 is possible, the operation of the heat pump 4 is started sequentially, so that the maximum number of heat pumps 4 can be operated in a state where the operation can be continued while appropriately responding to the thermal load. Improve the operation ratio of the heat pump 4 to other heat sources as much as possible without affecting the air conditioner, even if the thermal load fluctuates, and perform air conditioning with high energy savings. It is possible.

  Further, in the air conditioning system 1001, other heat sources such as the exhaust hot water X and the hot water boiler 506 are installed, and the flow rate of the medium with respect to the heat pump 4 is adjusted by the cold water pump 1002a and the hot water pump 1006a. Moreover, the amount of heat of the medium can be controlled.

  Furthermore, in the air conditioning system 1001, a part of the plurality of heat pumps 4 is a chilled water load adjuster, and the other heat pumps 4 are additionally started and stopped according to the load. It is possible to operate in a state of high load and high efficiency within a range that does not become excessive, and such an appropriate operation can be easily performed based on a simple index of the load of the cold load regulator.

[24th form]
FIG. 42 is a flowchart showing the operation of the air conditioning system according to the twenty-fourth embodiment. The air conditioning system is the same as that of the twenty-third embodiment, but the cooling-side return pipe 32 (the upstream and upstream branches to the cooling-side return pipe 32a). A cold water tank on the side). Further, a cold water chiller (not shown) is connected to the cooling side in the same manner as in a 26th embodiment (see FIG. 44) described later.

  Such an air conditioning system operates in the same manner as in the twenty-third embodiment, but the number of operating heat pumps 4 is changed based on the chilled water return temperature in the chilled water tank or the like instead of the opening degree of the flow rate adjusting valve 46, etc. Increase or decrease the output of the heat source.

  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 506 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 506 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. Note that it is confirmed whether or not the chilled water chiller is operating at the beginning of the loop 3 (step S1024). If the chilled water chiller is operating (NO), one chilled water chiller is stopped and the process proceeds to the end of the loop 3 (step S1025). If not in operation (YES), the process related to the loop 3 as in the twenty-third embodiment is executed.

  In the air conditioning system according to the twenty-fourth embodiment as well, as with the air conditioning system 1001 according to the twenty-third embodiment, the maximum number of heat pumps 4 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 4 to the other heat source as much as possible within a range that does not affect the operation, and to perform air conditioning in a state of high energy saving even if the thermal load fluctuates.

[25th form]
FIG. 43 is a flowchart showing the operation of the air conditioning system according to the 25th embodiment. The air conditioning system is the same as that of the 24th embodiment, but the hot water tank connected to the hot water boiler 506 is connected to the heating side supply pipe 34 and It is interposed in both of the heating side return pipes 36 (between the junction branching portion and the second warm heat supply amount adjustment valve 109), and the heating side supply pipe 34 between the warm water tank and the external air conditioner 2 includes the A pump for supplying hot water from the hot water tank to the external air conditioner 2 (second heat supply amount adjusting valve 109) is installed.

  In the air conditioning system according to the twenty-fifth aspect, one or a plurality of cold water chillers for directly cooling cold water or cooling a medium for cooling the cold water are installed. The cold water side of the cold water chiller is connected similarly to the heat pump 4. The cooling chiller is connected to a cooling tower that is independent of the hot water circuit of the heat pump 4 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 an air conditioning system operates in the same manner as in the twenty-fourth embodiment, but the chilled water temperature can be controlled by the chilled water chiller in addition to (increase or decrease) the number of heat pumps 4.

  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 506 is not in operation (NO in step S1005), the cold water chiller is operated (step S1031). If hot water boiler 506 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, the loop 4 is executed when the hot water tank temperature is equal to or lower than a predetermined value (57 degrees) (step S1033).

  In addition, the process which concerns on the air conditioning system of 25th form can be changed as follows. That is, in step S1006, the hot water temperature setting value of the heat pump 4a or the like as the cold water load adjuster is increased (upper limit can be set, 60 degrees). As a result, the output of the heat pump 4a 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 hot water going to the hot water tank 508 rises and the temperature of the hot water in the hot water tank 508 rises, the output of the other heat source (the hot water boiler 506) 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 4a or the like does not change, and the difference between the hot water going temperature and the hot water return temperature changes. For example, if the hot water flow rate is 43 tons per hour and the temperature difference is 7 degrees when the output of the heat pump 4a, etc., which covers a temperature difference of 5 degrees is 250 kW, and the output of another heat source is 200 kW, the thermal load is 450 kW, the temperature difference is 7 degrees. The output of the heat pump 4a 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 508 is not controlled without using another heat source, the output of the heat pump 4a 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 setting value of the heat pump 4a or the like as the cold water load adjuster is lowered (lower limit can be set, 55 degrees). As a result, the hot water output from the heat pump 4a and the like automatically decreases (inverter output decreases), 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 508 is lowered and the temperature of the hot water in the hot water tank 508 is lowered, the output of the other heat source (hot water boiler 506) is increased to cover a temporary shortage of the amount of heat supplied to the heat load. The hot water temperature in the hot water tank 508 is maintained at a predetermined temperature (60 degrees) by adjusting the heat supply by another heat source, the hot water return temperature of the heat pump 4a or the like does not change, and the difference between the hot water return temperature and the hot water return temperature changes. For example, when the thermal load is 350 kW and the thermal load 350 kW is covered by the heat pump 4 a that covers a temperature difference of 7 degrees at 43 tons per hour, and the hot water flow is the same and the temperature difference becomes 5 degrees, the output of the heat pump 4 a and the like Decreases to 250 kW and the output of the other heat source is automatically increased to 100 kW. In the case where the hot water temperature in the hot water tank 508 is not controlled without using another heat source, the output of the heat pump 4a 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 hot water boiler 506 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 4a and the like control the hot water supply temperature to a set value (60 degrees), the output is automatically increased as the hot water return temperature decreases (the temperature difference from the set value increases from 3 degrees to 4 degrees). by). Further, when the output of the heat pump 4a 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 an output of 150 kW such as a heat pump 4a that covers a temperature difference of 3 degrees at a flow rate of 43 tons per hour and an output of another heat source of 200 kW, the thermal water flow is the same and the temperature difference is 4 degrees. The output of the heat pump 4a etc. is increased to 200 kW, and the output of the other heat source is automatically reduced to 150 kW.

  On the other hand, in step S1012, the hot water temperature setting value of the hot water boiler 506 as another heat source can be increased by a predetermined value (1 degree) (lower limit can be set, 55 degrees). Thereby, the warm water output of the heat pump 4a etc. temporarily falls and the cold water output also falls. Further, when the hot water supply temperature to the reheater 18 rises and the hot water return temperature also rises (55 to 56 degrees), the heat pump 4a and the like control the hot water supply temperature to the set value (60 degrees), so the warm water return temperature rises. To automatically reduce the output (because the temperature difference decreases from 5 to 4 degrees). For example, in the case where the output of 350 kW such as the heat pump 4a 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 is 5 degrees by raising the set temperature of the other heat source, If the output of the heat pump 4a, etc. is reduced to 250 kW, the output of the other heat source is 100 kW, and if the temperature difference of 4 degrees is obtained by raising the set temperature of the other heat source, the temperature difference is 4 degrees, the output of the heat pump 4a, etc. The power is reduced to 200 kW, and the output of the other heat source is 150 kW.

  In the air conditioning system according to the twenty-fifth embodiment, as in the air conditioning system according to the twenty-fourth embodiment, the maximum number of heat pumps 4 can be operated in a state where operation can be continued while appropriately responding to the thermal load. By installing a chilled water chiller, the temperature of the chilled water can be adjusted before the number of heat pumps 4 is reduced, and the operation ratio of the heat pump 4 to other heat sources is improved more finely as much as possible without affecting the operation. Even if it fluctuates, air conditioning can be executed in a state of high energy saving.

[26th form]
FIG. 44 is a schematic diagram of an air conditioning system 1051 according to a twenty-sixth embodiment. The air conditioning system 1051 is the same as the twenty-third embodiment, but a plurality of cold water chillers 1052a and 1052b similar to the cold water chiller of the twenty-fifth embodiment are installed. ing. The cold water chiller 1052a and the like are connected to a cooling tower 504c and the like via a hot heat transfer pipe 1054a and a hot return pipe 1056a and the like. A pump 1057a and the like are disposed in the warm return pipe 1056a and the like. A single cold water chiller may be used. The air conditioning system 1051 has a hot water tank 1058 similar to that in the twenty-fifth embodiment.

  Furthermore, the heat pumps 4a and 4b are capable of following the cold water so that the temperature of the cold water or the cold heat is constant, and the heat pumps 4a and 4b are positioned as the thermal load regulators, but all the units are the thermal load regulators. The heat pump 4 may be single or three or more. Further, the exhaust hot water X, the flow rate adjusting valve 46 and the like are omitted. The external air conditioner 2 is an exhaust circulation air conditioner having a constant cooling load throughout the year.

  The automatic control device of the air conditioning system 1051 performs control based on its own cold water supply temperature and hot water supply temperature, for example, for the heat pumps 4a and 4b as thermal load adjusters, and for the hot water boiler 506, the temperature of the hot water tank 1058 or the heating side supply pipe. 34 is controlled based on the hot water supply temperature 34 and is controlled based on the cold water return temperature for the flow rate adjusting valve 46 that adjusts the cold water return temperature, and adjusts the hot water supply amount to the external air conditioner 2. The cooling / heating supply amount adjusting valve 48 for adjusting the amount of cold water supplied to 109 or the external air conditioner 2 is controlled based on the temperature of the air B output from the external air conditioner 2. These temperatures are detected by the respective temperature sensors and grasped by the automatic control device.

  Such an air conditioning system 1051 operates in the same manner as the twenty-third and twenty-fifth embodiments, for example, as follows.

  That is, as shown in FIG. 45, if the hot water supply temperature of the heat pump 4 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 4 is equal to or higher than the specific temperature (62 degrees) and the hot water boiler 506 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 1002a of the heat pumps 4a and 4b 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 1052a, 1052b is decreased to include the chilled water supply temperature at a predetermined temperature (10 degrees) (including reducing the number of units, step S1054), the loop 2 is executed, and the hot water supply temperature of the heat pump 4 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 506 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 4a is equal to or less than a predetermined value (95% of the maximum load) (step S1057). The output of the hot water boiler 506 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 1002a of the heat pumps 4a and 4b as the thermal load adjuster is increased, the chilled water supply temperature of the heat pumps 4a and 4b temporarily increases, and the chilled water supply temperature of the heat pumps 4a and 4b is increased. The heat pumps 4a and 4b 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 4a and 4b 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 1002a of the heat pumps 4a and 4b (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 1052a and 1052b is increased or the number is increased (step S1065).

  That is, in the loop 3, when the flow rate of the chilled water pump 1002a of the heat pumps 4a and 4b as the thermal load adjuster is decreased, the chilled water supply temperature of the heat pump 4a is temporarily lowered, and the chilled water supply temperature of the heat pumps 4a and 4b is set to a predetermined temperature ( 10 degrees), the heat pumps 4a and 4b automatically reduce the output (inverter output reduction). If the chilled water output of the heat pumps 4a and 4b decreases, the hot water output also decreases, so the chilled water chillers 1052a and 1052b compensate for the lack of cold heat.

  In addition, the process in the air conditioning system 1051 can be changed as follows. That is, in step S1052, the cold water temperature set value of the heat pump 4a or the like that is a hot water load adjuster is lowered. As a result, the output of the heat pump 4a and 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. Further, since the chilled water going-down temperature is lowered and the chilled water return temperature is temporarily lowered, the output of the chilled water chiller 1052 is reduced (step S1054) to balance with the cooling load. On the other hand, in step S1063, the cold water temperature set value of the heat pump 4a or the like that is a hot water load adjuster is increased. As a result, the output of the heat pump 4a and the like is automatically throttled (inverter output decreased), and the hot water output also decreases accordingly, so that the amount of supplied hot heat decreases and the hot water temperature decreases. Further, since the chilled water going-up temperature rises and the chilled water return temperature rises temporarily, the output of the chilled water chiller 1052 is increased (step S1065) to balance the cooling load.

  Further, in step S1052, the amount of factory exhaust heat applied to the cold water may be increased to temporarily raise the cold water temperature, thereby increasing the output of the heat pump 4 and raising the hot water temperature. Furthermore, in step S1063, when the factory waste heat is added to the cold water, the amount of waste heat added to the cold water is reduced by, for example, restricting the flow rate control valve for the factory waste heat, and the cold water temperature is temporarily lowered. Thus, the output of the heat pump 4 may be reduced to lower the hot water supply temperature. In combination with the cold water chiller, a smooth operation can be achieved by setting the heat pump 4 to a temperature setting that preferentially adjusts the output to the cold water temperature (heat pump 4 <cold water chiller).

  Since the air conditioning system 1051 includes the heat pump 4 that performs the cold water tracking operation and the cold water chillers 1052a and 1052b, the cold water tracking operation can be performed while appropriately responding to the thermal load in the air conditioning with the cold load throughout the year. It is possible to carry out air conditioning in an extremely energy-saving state.

  Further, in the air conditioning system 1051, the medium flow rate to the heat pump 4 is adjusted by the cold water pump 1002a or the like, so that the medium temperature or the medium heat amount can be controlled by adjusting the flow rate.

  Furthermore, in the air conditioning system 1051, since the plurality of heat pumps 4 are used as a thermal load adjuster, and the hot water boiler 506 and the like are started and stopped according to the load, the hot water boiler 506 and the like can be operated with good efficiency. In addition, such an appropriate operation can be easily executed based on a simple index of the load of the cooling load adjusting machine.

[27th form]
46A is a schematic diagram of an air conditioning system 1101 according to a twenty-seventh embodiment. The air conditioning system 1101 includes a steam coil 1108 similar to the washer 14, the cooling coil 16, and the heater 18, and a steam heating nozzle that mainly performs humidification. An external air conditioner 1102 having 1109 is provided. Steam ST as a second heating medium supplied from a boiler (not shown) or the like is introduced into the steam coil 1108 and the steam heating nozzle 1109 as the second heating means, and the drain pipe DR is connected to the steam coil 1108. Valves 1113 and 1114 for adjusting the flow rate (supplied heat amount) are installed in the steam pipes 1111 and 1112 of the steam coil 1108 and the steam heating nozzle 1109, respectively. The external air conditioner 1102 takes in the base air AA from the air intake port 1120 and releases the adjusted air B from the blower 20.

  A cooling medium pipe (not shown) is connected to the cooling coil 16 so that the cooling medium is introduced in the summer when cooling is required. On the other hand, the heating medium is not required in the winter and the heating medium is not required for cooling. A heating medium supply pipe 1132 or a heating medium return pipe 1134 is connected to be switchable so that introduction is possible. The heating medium supply pipe 1132 is provided with an inverter pump 1136 that can adjust the flow rate (heating load).

  The heating medium supply pipe 1132 to the heating medium return pipe 1134 are connected to the hot water tank 1138, and the hot water tank 1138 is connected to the heating side of the heat pump 4. The heating side return pipe 36 of the heat pump 4 is provided with a pump 1140 capable of providing a constant flow rate. Further, the cooling side of the heat pump 4 is connected to the exhaust hot water X so that the heat pump 4 can continue to supply the heating medium by the exhaust heat of the exhaust hot water X.

  Such an air conditioning system 1101 operates similarly to the 23rd to 26th embodiments. That is, a heating medium (for example, supply 60 degrees, return 55 degrees) for heating the base air AA is introduced into the cooling coil 16 in the winter season when heating of the base air AA is unnecessary and heating is necessary. Here, when the amount of heat of the waste water X is insufficient (for example, the temperature is 30 degrees to 25 degrees) and the heating amount of the heating medium by the heat pump 4 (warm water follow-up mode) cannot be balanced, the heating load is adjusted. By controlling the inverter pump 1136 as a means to reduce the flow rate, the heat exchange amount between the heating medium and the base air AA is reduced as described in the twenty-third to twenty-sixth aspects, and the amount of heat (temperature) of the heating medium is discharged. Even if the temperature of the hot water X decreases, it can be maintained, and the operation of the heat pump 4 is continued. Furthermore, insufficiency or fluctuation in the heating amount of the heating medium (heat exchange amount with the base air AA) is caused by a steam coil 1108 or a steam heating nozzle 1109 into which steam ST (other heating medium) is introduced from a boiler as another heat source. Correspondence is possible. The amount of heat (heat supply amount) of the steam ST introduced into the steam coil 1108 and the steam heating nozzle 1109 is adjusted by controlling the valves 1113 and 1114 according to the states of various sensors. When the temperature of the waste water X is restored, the automatic control device determines the temperature of the base air AA and the air B so that the heating medium has a heat quantity necessary for adjusting the base air AA with respect to the flow rate of the inverter pump 1136. According to (heat quantity).

  The air conditioning system 1101 supplies an external air conditioner 1102 having a cooling coil 16 that heats the base air AA taken in from the air intake port 1120, and heats and supplies the heating medium to the cooling coil 16. A heat pump 4 that can be introduced from the generated waste water X side, cooled, and led out, and a boiler that heats the steam ST supplied to the steam coil 1108 or the steam heating nozzle 1109 provided in the external air conditioner 1102 are provided. .

  Accordingly, the heating medium supply pipe 1132 or the heating medium return pipe 1134 or the heat pump 4 (and the hot water tank 1138 or the pumps 1136 and 1140) for switching and introducing the heating medium to the cooling coil 14 of the existing external air conditioner 1102 are simply added. This is advantageous in terms of cost and maintenance. Moreover, in the air conditioning system 1101, the base air AA is heated by the heating medium heated by the heat pump 4 using the waste water X before the steam coil 1108 and the steam heating nozzle 1109. It is possible to use the heat pump 4 that is heated with the highly efficient waste water X. Moreover, even if the heat exchange amount by the heat pump 4 changes due to the change in the amount of heat of the exhaust hot water X, it can be appropriately compensated by heating the base air AA with the steam ST. Furthermore, if the heat quantity of the waste water X decreases and the operation is continued as it is, the temperature of the heating medium cannot be effectively increased and the emergency stop is caused. Therefore, the amount of heat exchange with the base air AA can be reduced, the heating load of the heat pump 4 can be reduced, and the balance with the waste water X side can be maintained, and it is possible to continue the operation with high energy savings.

[Twenty-eighth form]
FIG. 46B is a schematic diagram of the air conditioning system 1151 according to the 28th embodiment, and the air conditioning system 1151 is the same as that in the 27th embodiment, but the inverter pump 1136 and the hot water tank 1138 are omitted, and the heating side The supply pipe 34 is provided with a flow rate adjusting valve 1152 as a flow rate adjusting means (heating medium return temperature adjusting means, heating load adjusting means) and a heat supply amount adjusting valve 49.

  Such an air conditioning system 1151 operates similarly to the twenty-seventh embodiment. That is, when the amount of heat of the waste water X is insufficient, the flow rate control valve 1152 is used for heat exchange with the base air AA by increasing the flow rate to the bypass side (the side returning to the heating side return pipe 36). The flow rate of the heating medium is reduced, the thermal load of the heat pump 4 is reduced, and the operation can be continued. Further, when the temperature on the cold water side of the heat pump 4 is restored, the temperature of the heating medium returning to the heat pump 4 is lowered by gradually reducing the flow rate to the bypass side in the flow rate control valve 1152. Also in the air conditioning system 1151, heating with high energy saving performance can be continued at a low cost while responding to a change in the amount of heat of the waste water X.

[29th form]
FIG. 47A is a schematic diagram of an air conditioning system 1161 according to the 29th embodiment. The air conditioning system 1161 is the same as the 27th embodiment, but the hot water tank 1138 is interposed only in the heating side return pipe 36. In addition, a drain tank 1162 and a cooling tower 1164 are arranged on the cooling side. A pump 1172 as a flow rate adjusting means is installed in the pipe 1171 from the drain tank 1162 to the cooling tower 1164, and a pump 1174 as a flow rate adjusting means is installed in the pipe 1173 from the drain tank 1162 to the waste water X side. The cooling side return pipe 32 of the heat pump 4 connected to the drain tank 1162 is provided with a cooling side inverter pump 1176 as a flow rate adjusting means (cooling load adjusting means).

  Such an air conditioning system 1161 operates similarly to the twenty-seventh embodiment. That is, when the temperature of the heating medium rises (for example, 65 degrees), the cooling-side inverter pump 1176 is squeezed to reduce the chilled water flow rate, and the output of the heat pump 4 operated in the chilled water following mode is squeezed to lower the heating medium temperature. . And if the temperature of a heating medium returns (for example, 60 degree | times), the flow volume of the cooling side inverter pump 1176 will be gradually returned to the original flow volume, the output of the heat pump 4 will be increased, and warm water temperature will be maintained. Further, when the temperature of the waste water X is excessively increased, the waste water X is cooled by the cooling tower 1164 and backed up so that the operation of the heat pump 4 is continued. Also in the air conditioning system 1161, heating with high energy saving performance can be continued at a low cost while responding to changes in the amount of heat of the exhaust hot water X.

[30th form]
FIG. 47B is a schematic diagram of the air conditioning system 1181 according to the thirtieth embodiment. The air conditioning system 1181 is the same as the twenty-ninth embodiment, but the drain tank 1162, the pump 1174, and the cooling-side inverter pump 1176 are omitted. In addition, a cooling side valve 1182 as a flow rate adjusting means (cooling load adjusting means) for the cooling tower 1164 of the waste water X is interposed in the cooling side return pipe 32 and connected to a supply pipe 1171 to the cooling tower 1164. The return pipe 1183 of the cooling tower 1164 is connected to the cooling side supply pipe 30.

  Such an air conditioning system 1181 operates similarly to the twenty-ninth embodiment. That is, when the temperature of the heating medium rises (for example, 65 degrees), the opening degree on the bypass side of the cooling side valve 1182 is increased to reduce the chilled water flow rate of the heat pump 4, and the output of the heat pump 4 that performs the chilled water following operation is reduced. And if the temperature of a heating medium returns (for example, 60 degree | times), the opening degree of a bypass side will be decreased gradually, the cold water flow rate of the heat pump 4 will be increased, and the output of the heat pump 4 will be increased (a load will be moved to the cooling tower 1164 side). Also in the air conditioning system 1181, heating with high energy saving performance can be continued at a low cost while responding to changes in the amount of heat of the exhaust hot water X.

[Thirty-first form]
FIG. 47 (c) is a schematic diagram of the air conditioning system 1201 according to the thirty-first embodiment. The air conditioning system 1201 is the same as the twenty-seventh embodiment, but the external air conditioner 2 is the same as the first embodiment. The heating side is connected to the preheater 12 (or reheater 18), the boiler 506 is connected to the hot water tank 1138, and the heating side valve 1202 as a heating load adjusting means is provided on the heating side of the heat pump 4. Yes. The heating side valve 1202 is interposed in the heating side supply pipe 34 and connected to the heating side return pipe 36. A pump 1205 serving as a flow rate adjusting unit is disposed on the pipe 1204 from the hot water tank 1138 to the boiler 506.

  Such an air conditioning system 1201 operates similarly to the twenty-seventh embodiment. That is, when the temperature of the waste water X decreases, the opening degree on the bypass side (heating side return pipe 36 side) is increased in the heating side valve 1202, the temperature of the warm water returning to the heat pump 4 performing the warm water following operation is increased, and the heating of the heat pump 4 Reduce the load and reduce the output of the heat pump 4. When the temperature of the waste water X is restored (for example, 30 degrees), the opening degree on the bypass side is gradually reduced, the temperature of the hot water returning to the heat pump 4 is lowered, and heating by the heat pump 4 is increased. In addition, when the temperature of warm water falls too much, a heating medium is heated with the boiler 506, and the heat quantity shortage of a heating medium is assisted.

  The air conditioning system 1201 heats and supplies a heating medium to the external heater 2 having the preheater 12 (or the reheater 18) for heating the outside air A taken in from the outside air inlet 10, the preheater 12 and the like, and is cooled. The medium includes a heat pump 4 that can be introduced from the side of the waste water X generated from the factory, cooled, and led out, and a boiler 506 that heats the heating medium. Accordingly, it is possible to continue heating with high energy saving at a low cost while responding to a change in the amount of heat of the waste water X.

  It should be noted that at least one of the cold water load adjustment control, the hot water supply shortage prevention control, and the cold water supply shortage prevention control as in the fourteenth to thirty-first embodiments is a paint drying apparatus (for example, a book drying device) using an exhaust heat recovery heat pump or the like. An application relating to Japanese Patent Application No. 2008-305017 by the applicant), an electrodeposition coating apparatus using an exhaust heat recovery type heat pump or the like (for example, Japanese Patent Application No. 2008-209954 or an application related to Japanese Patent Application No. 2008-310138 by the applicant), or The present invention can also be applied to temperature control of a molding machine using an exhaust heat recovery type heat pump or the like (for example, Japanese Patent Application No. 2009-276713 by the present applicant).

  Moreover, in the form using a warm water boiler, it can replace with a warm water boiler, and can use an air-cooling heat pump, an electric heater, or these combination, and can control warm water return temperature or warm water tank temperature by these.

[Thirty-second form]
FIG. 48 is a schematic diagram of an air conditioning system 3101 according to the thirty-second embodiment. The air conditioning system 3101 is the same as the first embodiment, but one or more air-cooled heat pumps are arranged on the cooling side as in the third embodiment. 3102. 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 30 and 32 is installed. The cooling side return pipe 32 is provided with a cold water pump 1002 similar to the cold water pumps 1002a to 1002d.

  Pipes 3116 and 3126 for the cooling coil 16 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. Another auxiliary heat source (steam here) H is introduced into the second heat exchanger 3164 via the auxiliary flow rate adjustment valve 3180.

  The heat exchanger 3130 may be installed in the pipe 32 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. Furthermore, the air cooling heat pump 3102 may be directly connected to the pipe 3126, and the return temperature of the medium may be controlled by switching the operation mode (cooling mode / heating mode). In addition, the other auxiliary heat source H can be a cooler or a coolable / warmable machine.

  The air conditioning system 3101 according to the thirty-second form mainly operates as follows, for example, in order to smoothly perform switching of heating or cooling operation.

  That is, as shown in FIG. 48 (a), when the heating load (350 kW) is heavier than the cooling load (170 kW), the heat pump 4 supplies hot water corresponding to the heating load, and the accompanying cold water is generated. (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 (cold water temperature in the pipes 16 and 3116) is 10 degrees, the chilled water temperature in the pipe 3126 immediately after returning from the cooling coil 16 is 14 degrees, and the chilled water temperature after passing through the heat exchanger 3130 The cold water return temperature to the heat pump 4 is 15 degrees, and the operation of the heat pump 4 is continued.

  On the other hand, as shown in FIG. 48 (b), when the thermal load decreases (becomes 254 kW) or the like, and the cooling / heating balance becomes unbalanced, the automatic control device sets the chilled water going temperature to a predetermined value (12 degrees). ) This case is grasped by detecting the above, 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, the heat exchange in the heat exchanger 3130 between the medium and the cold water is continued, and the heated medium is cooled with the cold water (the medium 35 to 18 degrees, the cold water return temperature 16 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 cooling heat pump 3102 by an external cooler or the like (requiring about 30 minutes), but the air conditioning system 3101 depends on the external cooler. In addition, the temperature can be quickly lowered to 20 degrees by heat exchange between the medium and the cold water, and the transition to the switching mode can be made unnecessary, and the time required for the result switching can be greatly shortened. If the medium is cooled by using another auxiliary heat source that can be cooled, switching can be performed more quickly.

  As shown in FIG. 48 (c), when the cooling load (170 kW) is heavy with respect to the heating load (250 kW) (due to the balance of heat pump cooling / heating water supply), the air cooling heat pump 3102 is cooled and cooled to 8 degrees. Supplied medium 13 kW. On the other hand, the heat pump 4 supplies cold water 157 kW of 10 degrees to the cold water tank 3104, and the cold water tank 3104 supplies cold water of 10 degrees to the cooling coil 16 via the pump 3152 according to the cooling load. The cold water of 14 degrees returned from the cooling coil 16 becomes 13.6 degrees by the medium (cold heat 13 kW) from the air-cooled heat pump 3102, and returns to the heat pump 4 through the cold water tank 3104. Thus, the cooling load 170 kW of the cooling coil 16 is covered by cold water (157 kW) and cooling by the medium (13 kW). On the other hand, the heat pump 4 supplies a heat of 250 kW commensurate with the cooling load 157 kW related to the cold water supply, and corresponds to the heat load.

  In this case, when the thermal load is relatively increased or when switching from cooling to heating, an operation just opposite to the switching from heating to cooling described above 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 heat pump 4 from shutting down due to the chilled water temperature drop, it takes time to restart after the device interlock, and the medium temperature is the predetermined temperature (25 degrees). In order to establish a heat pump cycle below, it is necessary to operate in the warming mode before switching to the heating mode to 25 degrees (approximately 30 minutes are required). However, in the air conditioning system 3101, the heat of the medium and the cold water First, the temperature can be quickly raised to 25 degrees by replacement, and the operation in the warming mode can be omitted, so that the time required for the result switching can be greatly shortened. If the medium is heated using the other auxiliary heat source H, the switching can be performed more quickly.

  In the air conditioning system 3101 described above, since the medium of the air cooling heat pump 3102 is circulated even during the operation switching of the air cooling heat pump 3102 on the cooling side of the heat pump 4, the medium is cooled by the cold water of the heat pump 4 at the time of cooling switching, and 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 without being heated by the water, and the operation of the air-cooled heat pump 3102 can be switched. The operation after switching can be made extremely smooth.

  In the air conditioning system 3101, since the medium is heated (cooled) by the other auxiliary heat source H at the time of heating (cooling) switching, the operation switching can be performed more quickly.

[33rd form]
The air conditioning system 3251 according to the thirty-third embodiment shown in FIG. 49A is the same as the first embodiment, but includes a hot water tank 3058 and a cold water tank 3104, and the hot water tank 3058 has steam Z ( An electric heater or an air-cooled heat pump may be introduced), and an air-cooled heat pump 2154 (cooling tower, exhaust heat, heated air-cooled heat pump or the like) may be connected to the chilled water tank 3104. The air conditioning system 3251 operates in the same manner as in the first embodiment, and also operates as shown in FIG. 20B, for example.

  That is, the heat pump 4 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 4 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 steam 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 4 cold water supply temperature setting value) to the cold water tank 3104, and the steam Z is supplied from the hot water tank 3058 to the second specified temperature (50 degrees, Heat pump 4 is supplied when the temperature is lower than the warm water supply temperature set value). Hot water returns to the heat pump 4 at 55 degrees, for example, and cold water returns to the heat pump 4 or the air-cooled heat pump 2154 at 17 degrees, for example.

  Then, the automatic control device first activates the heat pump 4 in the hot water follow-up mode (step S1301), and only when the monitored cold water supply temperature is less than a predetermined temperature (7 degrees) (YES in step S1302). 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 4 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 device repeats the processing from step S1302 unless there is a stop command for the heat pump 4 by pressing a stop button or the like (NO in step S1306), and if there is a stop command (YES in step S1306), the heat pump 4 is turned on. Stop (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. Furthermore, in step S1301, when the factory exhaust heat is low, such as when the production line is started up, and the hot water load is larger than the cold water load when the air conditioning equipment is started up (cold water load <warm water load), the heat pump 4 is You may start in follow-up mode, and it can be set as a more stable driving | operation in this case.

  In such an air conditioning system 3251 of the thirty-third form, when the supply cold heat becomes excessive with respect to the cooling load due to switching of the operation mode of the heat pump 4 or other heat source (steam Z) / other cooling heat source (air cooling heat pump 2154). Appropriately responds to the cooling load as the cold water follow-up mode and responds to the heating load with hot water and other heat sources, and appropriately responds to the heating load as the hot water follow-up mode when the supply heat is excessive with respect to the heating load Correspond with cold water and other cold heat sources. Therefore, it is possible to continue the operation of the heat pump 4 with a very good energy saving performance.

[34th form]
The air conditioning system 3301 according to the thirty-fourth form shown in FIG. 50 is the same as the first form except for the circuit according to the heat exchanger 40. In the air conditioning system 3301, the pipe 42 to the heat exchanger 40 is a supply pipe for a cooling tower 3302 as a cooler, and the pipe 44 from the heat exchanger 40 is a cooling facility that requires cooling of a compressor or the like belonging to a factory. It is a pipe to the equipment 3304 requiring cooling. 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 control valve 3308 is connected to the pipe 42. A plurality of cooling towers 3302 may be installed, or a refrigerator or an air cooling heat pump 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).

  This air conditioning system 3301 operates in the same manner as in the first embodiment, for example, as shown below.

  That is, when the chilled water temperature is relatively low (the amount of chilled water is large), the heat pump 4 follows the warm water, supplies 7 degrees of chilled water to the cooling coil 16, and 10 degrees of chilled water is discharged from the cooling coil 16. . A coolant having a predetermined temperature (15 degrees) is supplied from the cooling tower 3302 to the heat exchanger 40, 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 42.

  On the other hand, when the temperature of the chilled water is relatively high (the amount of chilled water is small), the heat pump 4 performs a hot water follow-up operation, supplies 18 degrees of chilled water to the cooling coil 16, and 21 degrees of chilled water is discharged from the cooling coil 16. . A coolant having a predetermined temperature is supplied from the cooling tower 3302 to the heat exchanger 40, 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 air conditioning system 3301, heat is exchanged between the cooling side of the heat pump 4 and the cooling water (medium) before cooling of the cooling equipment 3304 belonging to the factory, and the cooling water before cooling is transferred by the medium flow rate adjustment valve 3308 (or the cooling tower 3302). In order to adjust to a predetermined temperature, when the cold water is colder than the medium at the predetermined temperature, the cold water can be heated by heat exchange, and when the cold water is warmer than the medium at the predetermined temperature, the cold water can be cooled by heat exchange. In any case, the chilled water can be brought close to a predetermined temperature, there is no need to monitor the chilled water return temperature of the heat pump 4, etc., and there is no need to provide a control valve on the chilled water side of the heat pump 4. Insufficiency in cooling and overcooling can be effectively prevented by operation, and the temperature of the chilled water of the heat pump 4 can be naturally stabilized.

  The thirty-fourth form may be changed as follows. That is, only the air cooling heat pump is connected to the heat exchanger 40 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). Accordingly, the chilled water of the heat pump 4 is brought close to a predetermined temperature by heat exchange with the cooling side heating medium, that is, the chilled water is heated by the cooling side heating medium (cooling side medium) if the temperature falls below the predetermined temperature, and 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 thirty-second form, more stable temperature control can be performed.

[Thirty-fifth embodiment]
The air conditioning system 3401 according to the thirty-fifth embodiment shown in FIG. 51 is the same as the thirty-third embodiment, but is further connected to the chilled water tank 3104 via a factory waste heat source and a heat exchanger, and factory waste heat XX (waste heat belonging to the factory). Are connected to each other, 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 is further provided. The pipe 34 between 3302 and the cold water tank 3104 is provided with a pump 3408 and a flow rate adjusting valve 3410 as a cold heat amount adjusting means.

  The air conditioning system 3401 operates as follows, for example. That is, the heat pump 4 is operated in the chilled water follow-up mode, and by creating a condition for supplying 350 kW of cold water exceeding (excess) the cooling load 200 kW, hot water 500 kW is supplied from the heat pump 4 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 steam Z (100 kW) as another heat source.

  In order to supply 350 kW of chilled water by the automatic control device, the pump 3406 is operated at a maximum flow rate, and maximum heat exchange is performed with the factory exhaust heat XX (chilled water heating 300 kW, chilled water heating from 17 degrees to 20 degrees) . If it remains as it is, heating of 150 kW is surplus due to the response to the cooling load of the cooling coil 16 and heat exchange with the factory exhaust heat XX, and the chilled water temperature continues to rise, so the chilled water is cooled by the cooling tower 3302 (cooling) 150 kW, cold water 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. Note that the amount of heat of the medium related to the factory exhaust heat XX (the amount of heat exchange with the factory exhaust heat XX) may be adjusted by inverter control of the pump 3406 or a flow rate adjustment valve installed instead.

  And an automatic control apparatus respond | corresponds as follows to the factory waste heat XX from which calorie | heat amount fluctuates. That is, if the factory waste heat XX increases, the cooling amount in the cooling tower 3302 increases accordingly. On the other hand, if the factory exhaust heat XX decreases, the cooling amount in the cooling tower 3302 is reduced accordingly. Similarly, the cooling load of the cooling coil 16 can be dealt with.

  The air conditioning system 3401 includes a heat exchanger that heats the cold water by introducing the cold water of the heat pump 4 and the factory exhaust heat XX and exchanging heat, and the heat pump 4 supplies a cooling medium that has a cold heat amount that exceeds the cooling load amount. The cooling medium following operation is performed in the state. The excess amount of cooling heat is applied to the factory exhaust heat XX, and when the factory exhaust heat XX is large and the cooling by the cold water is insufficient, it is adjusted by the cooling tower 3302 that is another cooling heat source that assists the cooling by the cooling medium. In addition, the fluctuation | variation of a heating load respond | corresponds with the vapor | steam Z as another heat source.

  Therefore, in a simple configuration, heating or cooling by the heat pump 4 is continuously provided at a low initial cost (expense for connecting the existing heating device / cooling device with the heat pump 4 and providing a circuit for the factory exhaust heat XX) and running cost. In addition, it is possible to simply perform the heat recovery of the factory exhaust heat XX and provide an air conditioning system 3401 excellent in energy saving.

  Furthermore, the thirty-fifth embodiment can be changed as follows. That is, a heat exchanger is provided in one of the pipes 34 and 36, and a circuit for radiating hot water is installed by connecting a cooling tower to the heat exchanger. Then, when the heat pump 4 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 steam Z (other heat source) is introduced (in winter, etc.), heat from the cold water by the factory exhaust heat XX By increasing the exchange amount, the cooling load is increased, and the heating load is increased accordingly, thereby reducing the amount of steam Z used to cope with the heating load and saving energy used. The cold water tank may be omitted and connected to the return pipe (pipe 32) of the heat pump 4. Also, the pump connected to the pipe 3402 on the condition that the heating by the heat pump 4 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). 3406 is stopped or the flow rate is adjusted by inverter control (cooling side heating medium heat exchange amount adjusting means using the flow rate adjusting means) to adjust the heat amount of the cooling side heating medium or the heat exchange amount with the cold water. Therefore, the cooling load is adjusted. In addition, when the return temperature of the cold water (pipe 32) or the going-out temperature (pipe 30) rises and exceeds a set value (for example, 22 degrees), the pump 3406 is stopped or the flow rate is adjusted by inverter control. Good. Further, the adjustment of the heat exchange amount with the factory exhaust heat XX may be performed by a flow rate adjusting valve instead of or together with the inverter-controlled pump. In addition, about the adjustment of the heat exchange amount with waste water in the combination of the heat pump 4 and the cold water chiller (other heat sources), it is possible to perform similarly to the 26th form.

[Other forms]
In some of the above forms, various types of heat belonging to the factory are used as the cooling side heating medium applied to the cooling side of the heat pump that performs heating and cooling, but instead of the various types of heat, or Along with this, heat belonging to other types of factories as described below can be used. That is, other exhaust and exhaust heat generated in the factory, heat from various equipment (fan coil, etc.), heat from hydraulic oil, heat from the work after paint drying, etc. The heat transferred to the washing water in the case of the washing step, which is a step, the exhaust heat generated from the factory air conditioner (returning cold 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 achieve a favorable air conditioning system. 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, steam of the boiler or the like, or a combination of this with exhaust hot water or 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.

  In addition, a separate heat pump (heating heat pump) may be provided that directly takes in and heats the refrigerant of the exhaust heat recovery type heat pump that performs heating and cooling and returns it to the heat pump. In addition to this, the above-mentioned various heat exchangers for heating the refrigerant of the exhaust heat recovery type heat pump can also be installed. In addition, on the cold water side of the exhaust heat recovery type 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 water at a temperature higher than the cold water is returned directly to the heat pump (after being appropriately treated). Alternatively, the exhaust water pipe can be arranged so that the flow path can be switched so that the exhaust water enters the heat pump.

  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.

  In addition, arrangement | positioning, control, etc. of said heat pump are the coating-drying apparatuses (refer Japanese Patent Application 2008-305017 etc. by this applicant) and the electrodeposition coating apparatus (refer Japanese Patent Application 2010-14669 etc.) which respectively utilized the heat pump. It can also be applied to a temperature control system of a molding machine (see Japanese Patent Application No. 2009-276713, etc.).

1,101,151,171,201,251,301,351,401,501,601,701,801,821,851,861,871,881,901,911,951,1001,1051,1101,1151, 1161, 1181, 1201, 3101, 3251, 3301, 3401 Air conditioning system 2,1102 Air conditioner (air conditioner)
4 Heat pump (exhaust heat recovery type)
10 Outside air intake (base air intake)
12 Preheater 16 Cooling coil 18 Reheater 40, 640 Heat exchanger 46, 646 Flow control valve (flow control means, cooling-side heating medium heat exchange control means)
154, 2154, 3102 Air cooling heat pump 208 Cooling medium tank 802, 822 Exhaust air conditioner (air conditioner)
954 Heating Tower 1110 Air intake (base air intake)
3302 Cooling Tower (Cooler)
3304 Cooling required equipment 3308 Medium flow rate adjusting valve (equipment cooling water temperature adjusting means)
A Outside air X Waste heat water Y Exhaust Z Steam (other heat sources, etc.)
XX Factory waste heat

Claims (29)

An air conditioner having heating means for heating the base air taken in from the base air intake, and cooling means for cooling the base air;
A heat pump that heats and supplies a heating medium to the heating means, and supplies a cooling medium that is cooled and supplied to the cooling means;
An air conditioning system comprising a cooling medium heater for heating the cooling medium. The said cooling medium heater is a heat exchanger which heats the said cooling medium with the said cooling side heating medium by introduce | transducing the said cooling medium and a cooling side heating medium, and exchanging heat. Air conditioning system. The air conditioning system according to claim 2, wherein the cooling side heating medium is supplied from a cooling pump for supplying a cooling side heating medium. The cooling side heating medium includes at least one of waste water generated from a factory, makeup water, exhaust gas, exhaust gas, cleaning water, heat radiation of equipment, heat radiation of a workpiece, waste heat of air conditioning, or waste heat of cogeneration. The air conditioning system according to claim 2, wherein the air conditioning system is a thing. The air conditioning system according to any one of claims 1 to 4, wherein the cooling medium heater is a heating tower. The air conditioning system according to any one of claims 1 to 5, wherein the cooling medium heater is a heat pump for heating. The air conditioning system according to claim 6, wherein a cooling medium tank is interposed between the heating heat pump and the heat pump. A cooling side heating medium heat exchange amount adjusting means for adjusting a heat exchange amount between the cooling side heating medium and the cooling medium;
A cooling temperature sensor for detecting a cooling medium temperature which is a temperature of the cooling medium;
An automatic control device connected to the cold temperature sensor and controlling a heat exchange amount in the cooling-side heating medium heat exchange amount adjusting means according to the cooling medium temperature obtained from the cold temperature sensor; The air conditioning system according to any one of claims 1 to 7. The cooling side heating medium heat exchange amount adjusting means is a flow rate adjusting means for adjusting a flow rate of the cooling side heating medium and / or the cooling medium to the cooling medium heater,
The air conditioning system according to claim 8, wherein the automatic control device controls a flow rate in the flow rate adjusting unit according to the cooling medium temperature. A heating load amount adjusting means for adjusting a heating load amount of the heating medium to the heat pump;
A cold temperature sensor that detects a cold supply temperature that is a temperature when the cooling medium is supplied from the heat pump and / or a cold return temperature that is a temperature when the cooling medium returns to the heat pump; and
Another heat source for assisting heating of the heating medium;
The cooling load is connected to the cooling temperature sensor and the other heat source, and controls the heating load amount in the heating load amount adjusting means according to the cooling supply temperature and / or the cooling return temperature obtained from the cooling temperature sensor. The air conditioning system according to any one of claims 1 to 9, further comprising an automatic control device that adjusts a heating supply amount by a heat source. Cooling load amount adjusting means for adjusting a cooling load amount of the cooling medium to the heat pump;
A thermal temperature sensor that detects a thermal supply temperature that is a temperature when the heating medium is supplied from the heat pump and / or a thermal return temperature that is a temperature when the heating medium returns to the heat pump; and
Another cooling heat source for assisting cooling of the cooling medium;
The thermal load sensor is connected to the thermal temperature sensor and the other cold heat source, and controls the cooling load amount in the cooling load amount adjusting means according to the hot supply temperature and / or the hot return temperature obtained from the thermal temperature sensor, and The air conditioning system according to any one of claims 1 to 10, further comprising an automatic control device that adjusts a cooling heat supply amount by another cooling heat source. 12. The temperature of the cooling medium is increased so that the efficiency of the heat pump is improved when supply of the cooled cooling medium to the cooling unit is unnecessary. The air conditioning system according to any one of the above. The air conditioning system according to any one of claims 3 to 12, wherein a plurality of the cooling side heating medium supply heat pumps are provided. The air conditioning system according to claim 13, further comprising an automatic control device that switches 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. The automatic control device sets a part of the plurality of cooling-side heating medium supply heat pumps to an operation standby state when a load related to the cooling medium decreases with respect to a load related to the heating medium. The air conditioning system according to claim 14. The air conditioning system according to any one of claims 1 to 15, wherein there are a plurality of the cooling medium heaters. The air conditioning system according to claim 16, further comprising: an automatic control device that switches an operation number and / or an operation mode of the plurality of cooling medium heaters according to a state of the heating medium and / or the cooling medium. . The air conditioning system according to any one of claims 1 to 17, wherein an operation mode of the heat pump can be switched between a heating mode and a cooling mode. The air conditioning system according to any one of claims 1 to 18, wherein a temperature of the heating medium is increased or decreased by increasing or decreasing a heating amount in the cooling medium heater. An air-cooled heat pump for supplying a medium for heating or cooling the cooling medium,
20. The air conditioning system according to claim 1, wherein after the medium of the air-cooled heat pump is cooled or heated by the cooling medium, heating or cooling of the medium of the air-cooled heat pump is switched. . Another auxiliary heat source for heating or cooling the medium;
21. The air conditioning system according to claim 20, wherein cooling or heating by the other auxiliary heat source is performed in accordance with cooling or heating of the medium by the cooling medium. The cooling side heating medium is cooling water and / or cold water in a facility requiring cooling,
21. The apparatus according to claim 2, further comprising: a cooler that cools the cooling water and / or cold water to a predetermined temperature and supplies the cooling medium heater to the cooling medium heater and an equipment cooling water temperature adjusting unit. The air conditioning system described in Crab. The air conditioning system according to any one of claims 1 to 22, wherein the heat pump is operated in a state in which a cooling medium having a cooling heat amount exceeding a cooling load amount is supplied in the cooling medium following operation. The cooling side heating medium is supplied from an air cooling heat pump,
24. The air conditioning system according to claim 2, wherein the air cooling heat pump maintains the cooling side heating medium at a predetermined temperature. An air conditioner having heating means for heating the base air taken in from the base air intake, and cooling means for cooling the base air;
A heat pump that heats and supplies a heating medium to the heating means, and supplies a cooling medium that is cooled and supplied to the cooling means;
It includes both another heat source that assists heating of the heating medium and another cooling heat source that assists cooling of the cooling medium,
The heat pump is capable of heating medium following operation and cooling medium following operation,
When the cooling medium falls below a predetermined temperature, the heating medium following operation is switched to the cooling medium following operation,
When the heating medium exceeds a specific temperature, the cooling medium following operation is switched to the heating medium following operation. An air conditioner having heating means for heating the base air taken in from the base air intake, and cooling means for cooling the base air;
The heating medium is heated and supplied to the heating means, and the cooling medium is supplied from the heating heat pump side, exhausted hot water, exhaust gas, exhaust gas, makeup water, washing water, heat radiation from the equipment, heat radiation from the work, air conditioning. A heat pump that can be switched and introduced by cooling from the side including at least one of exhaust heat of cogeneration or exhaust heat of cogeneration, cooled, and
A cooling heat pump for supplying a second cooling medium to the cooling means,
When the heat pump introduces the cooling medium from the heating heat pump side, at least one of the exhaust hot water, exhaust gas, exhaust gas, or make-up water is commensurate with cooling by the heat pump or more heat. When it has, the air-conditioning system characterized by switching so that the said cooling medium may be introduce | transduced from the side containing at least any one of the said waste water temperature, exhaust_gas | exhaustion, waste gas, or make-up water. An air conditioner having a heating means for heating the base air taken in from the base air intake port;
The heating medium is heated and supplied to the heating means, and for the cooling medium, waste water generated from the factory, exhaust gas, exhaust gas, makeup water, washing water, heat radiation of the equipment, heat radiation of the work, exhaust heat of the air conditioning, or cogeneration A heat pump that can be introduced from the side including at least one of the exhaust heat, cooled, and led out;
An air conditioning system comprising: the heating medium and / or another heat source that heats a second heating medium supplied to second heating means provided in the air conditioner. 28. The air conditioning system according to claim 1, wherein there are a plurality of the air conditioners. The air conditioning system according to any one of claims 1 to 28, wherein the air conditioner includes an exhaust circulation air conditioner.

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