JP5351707B2 - Painting equipment - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To effectively reduce energy consumption in an exhaust gas use type coating apparatus. <P>SOLUTION: The coating apparatus including a wet purifier 9a for bring exhaust air Ea' from a first coating chamber 2 into gas-liquid contact with cleaning water W to clean the exhaust air and second gas feeder 16, 17a, 17b for supplying cleaned exhaust air Ea' by the wet purifier 9a to a second coating chamber 4 as air for ventilation is provided with a cooling dehumidifier 20 for cooling and dehumidifying the cleaned exhaust air Ea' dehumidified by the wet purifier 9a by the heat absorption function of a heat pump 18 and a re-heater 21 for heating to reheat the cleaned exhaust air Ea' dehumidified by the cooling dehumidifier 20 by the heat releasing function of the heat pump 18 which follows the air cooling in the cooling dehumidifier 20 and is constituted so that the cleaned exhaust air Ea" (Sb) having controlled temperature and humidification by the dehumidification and reheating is supplied to the second coating chamber 4 by second air supply means 16, 17a, 17b. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a painting facility, and an air supply means for supplying adjusted air from an air conditioner to a first painting chamber, and exhaust air discharged from the first painting chamber in accordance with air supply by the air supply means. The present invention relates to a painting facility including a wet purification means for purifying by contact with a liquid and provided with a second air supply means for supplying purified exhaust air from the wet purification means to a second painting chamber as ventilation air.

  In general, in coating equipment, exhaust air discharged from the coating room contains unpainted floating paint mist, etc., but this exhaust air is purified by contacting it with washing water and gas-liquid using a wet cleaning means. Is often discharged.

  On the other hand, the painting equipment according to the present invention purifies the exhaust air discharged from the first painting chamber by the wet purification means, and then supplies it to the second painting chamber as the ventilation air by the second air supply means. As a result, exhaust air from the first painting chamber is reused in the second painting chamber as a ventilation air in the second painting chamber, and at the same time, the hot air or cold heat (in other words, residual hot air or residual cold heat of the exhaust air) ) Is also intended.

  Conventionally, in this type of exhaust-use type painting equipment, only a part of the ventilation air supplied to the second painting chamber uses the purified exhaust air by the wet purification means, and there is a considerable excess of the purified exhaust air. The part was discharged outside as before.

  In this partially exhausted type painting facility, external air adjusted by an air conditioner for the second painting chamber (as in the first painting chamber) in parallel with the supply of purified exhaust air to the second painting chamber ( For example, fresh outside air adjusted in temperature and humidity is supplied to the second coating chamber, and the interior of the second coating chamber is adjusted to a required temperature and humidity state by supplying the adjusted external air (see Patent Document 1, for example). In particular, page 4, upper left column, second line to upper right column, lower line to eighth line, and FIGS. 3 and 4).

JP 61-103564 A

  However, in the above-described partially exhausted type painting equipment, purified exhaust air (that is, air that becomes a large dehumidifying load) supplied with high humidity by gas-liquid contact with the cleaning water in the wet purification means is supplied. 2 To adjust the interior of the painting room to the required temperature and humidity, the air conditioner for the second painting room still requires a large capacity air conditioner, and the refrigerator attached to the air conditioner for the second painting room, etc. The heat source equipment and the heat source equipment such as boilers, burners, and electric heaters are also required to have a large capacity, which increases the energy consumption required for adjusting the temperature and humidity of the second coating chamber and increases the equipment cost. In this respect, there is a problem that the exhaust air utilization effect cannot be obtained as a whole.

  On the other hand, in order to promote the use of the purified exhaust air by the wet purification means for this problem, a form in which the purified exhaust air by the wet purification means is used for the entire amount (or most) of the ventilation air supplied to the second painting chamber. A dehumidifier that cools and dehumidifies the purified exhaust air supplied to the second coating chamber, and a reheater that heats and reheats the purified exhaust air following the dehumidification. By supplying purified exhaust air adjusted in temperature and humidity to the second painting chamber, the air conditioner for the second painting chamber whose external air is to be adjusted is omitted, and the interior of the second painting chamber is in the required temperature and humidity state. There is also a painting facility that uses exhaust gas that is completely adjusted.

  However, even in this exhaust system using exhaust gas, a dehumidifier that dehumidifies a large amount of purified exhaust air that has become humid due to gas-liquid contact with the cleaning water in the wet purification means, and a large amount of purification after the dehumidification A reheater that reheats the exhaust air requires a large capacity, and a heat source device such as a refrigerator attached to the dehumidifier, and a heat source device such as a boiler, burner, or electric heater attached to the reheater Each of these requires a large capacity, which also increases the energy consumption required for adjusting the temperature and humidity of the second coating chamber and increases the equipment cost.

  Further, in this exhaust type exhaust type, the retained heat of the purified exhaust air by the wet purification means, particularly the latent heat retained by the high-humidity purified exhaust air (following the original, the exhaust air from the first painting chamber (Holding heat) is discarded to the outside through the dehumidifier and the accompanying cold heat source equipment. From these, even with this all-exhaust type paint equipment, the exhaust air utilization effect is still sufficiently obtained. There was no problem.

  In view of this situation, the main problem of the present invention is to effectively solve the above problems by adopting a rational air conditioning system.

The first characteristic configuration of the present invention relates to a painting facility,
Air supply means for supplying air adjusted by the air conditioner to the first painting chamber, and wet treatment for purifying exhaust air discharged from the first painting chamber in accordance with air supply by the air supply means by bringing it into gas-liquid contact with cleaning water Purification means,
A painting facility provided with a second air supply means for supplying the exhaust gas purified by the wet purification means to the second painting chamber as ventilation air,
Cooling and dehumidifying means for cooling and dehumidifying the purified exhaust air by the wet purification means by a heat absorption function of a heat pump;
Reheat means for heating and reheating the purified exhaust air dehumidified by the cooling and dehumidifying means by means of the heat radiation function of the heat pump accompanying air cooling in the cooling and dehumidifying means,
The purified exhaust air adjusted in temperature and humidity by dehumidification by the cooling dehumidifying means and reheating by the reheating means is configured to be supplied to the second coating chamber by the second air supply means.

  That is, according to this configuration, the purified exhaust air by the wet purification means (that is, the exhaust air from the first painting chamber purified by gas-liquid contact with the cleaning water) is supplied to the second painting chamber as ventilation air. However, since the purified exhaust air whose temperature and humidity have been adjusted by dehumidification by the cooling dehumidifying means and subsequent reheating by the reheating means is supplied to the second painting chamber, the second painting is applied in the same manner as the painting equipment of the exhaust gas utilization type described above. A large amount of purified exhaust air whose temperature and humidity are adjusted while adopting a form in which the purified exhaust air by the wet purification means is used with respect to the total amount of ventilation air supplied to the room (or even a partly large amount). By supplying, the second coating chamber can be adjusted to a required temperature and humidity state.

  In addition, while adopting the same air-conditioning form as the painting equipment of the exhaust system utilizing all exhaust gas in this way, the heat absorption function of the heat pump (that is, the removal of vaporization heat of the refrigerant) is used to dehumidify and reheat the purified exhaust air by the wet purification means. The purified exhaust air is cooled and dehumidified by the heat absorption function generated by the heat pump, and the purified exhaust air after dehumidification is heated by the heat release function of the heat pump (that is, the heat release function generated by the condensation heat release of the refrigerant). In other words, because the heat exhausted from the purified exhaust air is reheated by the heat pump's endothermic function, the dehumidified purified exhaust air is reheated. Eliminates the need for large-capacity heat source equipment such as refrigerators and large-capacity heat source equipment such as boilers, burners, and electric heaters required for painting equipment Capacity), it is possible to dispense with substantially only equipment the heat pump as equipment cold heat source device.

  Also, according to this configuration, the cooling heat dehumidifying means removes the retained heat of the purified exhaust air by the wet purification means, particularly the latent heat held in large quantities by the purified exhaust air that has become highly humid due to gas-liquid contact with the cleaning water. Recovered by a heat pump with cooling dehumidification, and the recovered heat is returned to the purified exhaust air after dehumidification by reheating by the reheating means (in other words, a large amount of latent heat is retained in the sensible heat state. Combined with the use of purified exhaust air for the total amount (or a proportionately large amount) of ventilation air supplied to the second painting chamber. Further, the utilization degree of the purified exhaust air by the wet purification means (that is, the utilization degree of the exhaust air from the first painting chamber purified by the wet purification means) can be further effectively increased.

  From these things, according to the said structure, the temperature and humidity of a 2nd coating chamber are the state in which the utilization effect in the material surface of the exhaust air from a 1st coating chamber and the utilization effect in the amount of stored heat were fully exhibited. Energy consumption required for adjustment can be effectively reduced, and reduction of equipment cost and space saving can also be effectively realized.

In the implementation of the above configuration, various types of heat pumps such as a compression heat pump, an absorption type and an adsorption type can be used as the heat pump, but the temperature difference between the generated cold heat and the generated hot heat, that is, cooling dehumidification means air cooling temperature (apparatus dew point temperature) and air heating temperature in reheating means in that it can take a large difference in temperature between the (reheat temperature), using supercritical type compression heat pump of the CO ₂ refrigerant in the It is good to do.

The second feature configuration of the present invention specifies an embodiment suitable for the implementation of the first feature configuration.
The reheating means is configured to heat a part of the purified exhaust air dehumidified by the cooling dehumidifying means by the heat release function of the heat pump and to mix the heated air with the remaining purified exhaust air dehumidified by the cooling dehumidifying means. It is in a certain point.

  In other words, in order to heat the purified exhaust air dehumidified by the cooling and dehumidifying means with the heat release function of the heat pump, the entire amount of the purified exhaust air after dehumidification is exchanged with a heat exchanger such as a heat pump refrigerant and a fin tube type or a plate type. Alternatively, a method is generally used in which heat is exchanged with a heat transfer fluid such as a fin tube type or a plate type with the heat transfer fluid heated by the heat dissipation function of the heat pump and the entire amount of purified exhaust air after dehumidification. If the so-called bypass factor in the process of passing through the exchanger is reduced to ensure high heating efficiency, the ventilation resistance of the purified exhaust air in the heat exchanger increases and the transport power of the purified exhaust air increases. To avoid the increase, the heat exchanger becomes larger.

  On the other hand, in the above configuration, a part of the purified exhaust air after dehumidification is intensively heated by the heat exchanger by the heat release function of the heat pump, and the heated air is mixed with the remainder of the purified exhaust air after dehumidification. The remaining part of the purified exhaust air after dehumidification is also heated, and thereby, the entire amount of the purified exhaust air dehumidified by the cooling dehumidifying means is heated and reheated.

  That is, the part of the purified exhaust air after dehumidification is heated by mixing heated air in this way, so that a part of the purified exhaust air after dehumidification is heated by the heat exchanger by the heat dissipation function of the heat pump. As for the reheating means as a whole, the ventilation resistance of the purified exhaust air after dehumidification is reduced while reducing the bypass factor to ensure high heating efficiency and making the heat exchanger compact. The power for transporting the purified exhaust air can be reduced, and the reheat means including the heat exchanger for heating a part of the purified exhaust air after dehumidification can be downsized.

  In addition, if the remaining portion of the purified exhaust air after dehumidification is heated by mixing heated air, the remaining portion of the purified exhaust air after dehumidification can be efficiently heated without a bypass factor generated in the heat exchanger. Therefore, reheating can be performed in combination with ensuring a high heating efficiency by reducing the bypass factor of the part where the part of the purified exhaust air after dehumidification is heated by the heat exchanger with the heat exchanger as described above. The heating efficiency of the whole means can also be ensured high, whereby energy loss caused by low heating efficiency can be effectively suppressed.

  In addition, in the implementation of the above configuration, to mix the heated air with the purified exhaust air after dehumidification, the heated air is supplied and mixed in a state of being evenly dispersed with respect to the purified exhaust air after dehumidification from a number of ejection holes. By doing so, the purified exhaust air after dehumidification can be uniformly heated from the mixing stage of the heated air, and thereby the temperature and humidity adjustment function for the second coating chamber can be achieved in terms of uniformity of temperature and humidity distribution. It can be further enhanced.

  Further, in the implementation of the above configuration, a part of the purified exhaust air after dehumidification that is heated by the heat dissipation function of the heat pump is held at a constant amount (in other words, the heated air mixed in the remaining portion of the purified exhaust air after dehumidification is kept constant). The amount of air (heated air) changes to prevent instability of the delivery air temperature or instability of the delivery air that occurs in the reheating means. The function of adjusting the temperature and humidity for the second coating chamber can be further enhanced in terms of stability.

The third feature configuration of the present invention specifies an embodiment suitable for the implementation of the second feature configuration.
The reheating means heats the mixed air of a part of the purified exhaust air dehumidified by the cooling and dehumidifying means and the external air by the heat release function of the heat pump, and makes the mixed amount of the purified exhaust air in the heated mixed air. A corresponding part is mixed with the remaining portion of the purified exhaust air dehumidified by the cooling and dehumidifying means, and the remaining portion of the heated mixed air is discharged to the outside.

  That is, according to this configuration, basically the same function as the second characteristic configuration can be obtained, but in addition to that, the amount of air heated by the reheating means (that is, without changing the heat dissipation amount of the heat pump) , The amount of reheat) can be changed in various ways.

  In other words, in a compression heat pump, the amount of heat released is larger than the amount of heat absorbed by the amount of compressor work, but in general, in a series of processes where air is reheated following cooling and dehumidification, the amount of air cooling in the dehumidification step The air heating amount in the heat process is often the same, so if the capacity of the compression heat pump is set so that the heat absorption amount of the compression heat pump and the air cooling amount in the dehumidification process are balanced, the compression heat pump The heat release amount of the heat pump becomes excessive with respect to the air heating amount in the reheating process.

  In addition, it may be necessary to set the air heating amount in the reheating process to be smaller than the heat dissipation amount of the heat pump for various reasons such as the reason for adjusting the temperature and humidity of the second coating chamber.

  On the other hand, according to the above configuration, the remaining portion of the purified exhaust air after dehumidification is used for the remaining air heating for a portion of the heated mixed air heated by the heat release function of the heat pump, corresponding to the mixed amount of the purified exhaust air. Thus, as described above, the remaining portion of the purified exhaust air after dehumidification is heated to heat the entire amount of the purified exhaust air after dehumidification, but the remaining portion of the heated mixed air (that is, the outside of the heated mixed air) The amount corresponding to the amount of air mixed) is discharged to the outside, so only the heat waste due to that discharge (that is, the amount of heat obtained by heating with the heat release function of the heat pump) The amount of air heated by the reheating means can be made smaller than the amount of heat released from the heat pump.

  Therefore, if the mixing ratio between the purified exhaust air (a part of the purified exhaust air after dehumidification) and the external air in the mixed air heated by the heat pump's heat dissipation function is changed, the heat pump's heat dissipation amount is changed without changing the heat pump's heat dissipation amount. The air heating amount (reheating amount) in the reheating means can be variously set and changed within the range of the heat dissipation amount or less.

  In addition, according to this configuration, if the heat pump capacity is changed for some reason, such as a change in the heat pump capacity (change in the heat pump heat absorption amount) according to a change in the air cooling amount in the cooling and dehumidifying means, it is accompanied by that Since the amount of waste heat to the outside also changes with the change in the heat dissipation of the heat pump (change in the amount of mixed air heating), the amount of air heating in the reheating means is a predetermined ratio from the heat dissipation of the heat pump regardless of the change in heat pump capacity. The state made small can also be maintained.

  In the implementation of the above configuration, in order to change the mixing ratio of the purified exhaust air and the external air in the mixed air, the mixing amount of the purified exhaust air is kept constant, and the mixing ratio is changed only by changing the mixing amount of the external air. As described above, as described above, the amount of purified exhaust air mixed (in other words, the amount of heated air mixed in the remaining portion of the purified exhaust air after dehumidification) changes, so that the delivery air generated in the reheating means It is possible to prevent the temperature from becoming unstable and the delivery air quantity from becoming unstable, and the temperature and humidity adjustment function for the second coating chamber can be further enhanced in terms of stability.

  Further, in the implementation of the above configuration, if the remaining heat of the heated mixed air discharged to the outside (that is, part of the heat pump heat release) is recovered and used in other parts, the energy efficiency of the entire equipment Can be further enhanced.

The fourth characteristic configuration of the present invention specifies an embodiment suitable for the implementation of any of the first to third characteristic configurations,
The cooling and dehumidifying means includes a heat medium liquid tank for cooling the stored heat medium liquid to a predetermined temperature by the heat absorption function of the heat pump;
An air cooler that cools the purified exhaust air by exchanging heat between the heat medium liquid circulated between the heat medium liquid tank and the purified exhaust air by the wet purification means;
It is in the point provided with the flow rate adjustment means which adjusts the supply amount of the heat transfer fluid to this air cooler.

  That is, in this configuration, the amount of heat medium liquid supplied to the air cooler is adjusted by the flow rate adjusting means, thereby adjusting the air cooling amount in the air cooler and dehumidifying the purified exhaust air in the cooling dehumidifying means. However, if the heat medium liquid to be circulated with the air cooler is stored in the heat medium liquid tank as described above, and the stored heat medium liquid is cooled to a predetermined temperature by the heat absorption function of the heat pump. In addition, it is possible to make a buffer function by holding the stored heat medium liquid in the heat medium liquid tank against the change in the air cooling amount in the air cooler caused by the adjustment of the heat medium liquid supply amount by the flow rate adjusting means.

  In other words, this buffer function can suppress a sudden change in the heat pump capacity that accompanies a change in the amount of air cooling in the air cooler, thereby improving the stability of the heat pump operation. The function of humidity adjustment can be further enhanced in terms of stability.

  In other words, the buffer function allows the air cooling amount in the air cooler to be changed without waiting for a delay in the response of the heat pump capacity change, and the adjustment of the dehumidifying amount in the air dehumidifying means in the cooling dehumidifying means. Responsiveness (immediate responsiveness) can be enhanced, whereby the temperature and humidity adjustment function for the second coating chamber can be enhanced in terms of responsiveness.

  In the implementation of the above configuration, in order to cool the stored heat transfer medium in the heat transfer medium tank by the heat absorption function of the heat pump, between the heat transfer liquid tank and the heat pump heat sink (evaporator from the refrigerant side). Various methods such as a method of circulating the heat medium liquid and a method of immersing and arranging the heat absorber of the heat pump in the stored heat medium liquid of the heat medium liquid tank can be adopted.

The fifth characteristic configuration of the present invention specifies an embodiment suitable for implementation of any of the first to fourth characteristic configurations,
The cooling and dehumidifying means is configured such that a cooling side combined operation for cooling the purified exhaust air by the wet purification means can be performed by the heat absorption function of the heat pump and the heat absorption function of the auxiliary cooling source device.

  In other words, according to this configuration, the heat pump capacity is set so that the heat dissipation amount of the heat pump and the air heating amount in the reheating means are balanced, or the heat pump capacity reaches the upper limit. In the situation where the heat pump capacity cannot be adjusted to the increase side, the heat pump's heat absorption becomes insufficient with respect to the air cooling amount in the cooling and dehumidifying means. The shortage of heat can be covered by the heat absorption function of the auxiliary cold heat source equipment.

  That is, even in a situation where the capacity of the heat pump cannot be adjusted to the increase side, it is possible to increase the air cooling amount in the cooling dehumidifying means and increase the dehumidifying amount of the purified exhaust air in the cooling dehumidifying means. 2 The humidity adjustment function can be further enhanced in the temperature and humidity adjustment of the painting chamber.

  In the implementation of the above configuration, the cooling-side combined operation is always performed, and either the heat absorption amount of the heat pump or the heat absorption amount of the auxiliary cooling heat source device with respect to the change of the air cooling amount in the cooling and dehumidifying means. Either a method of adjusting one or both of them, or a method of performing the cooling side combined operation when the air cooling amount in the cooling and dehumidifying means cannot be covered by the single operation of the heat pump may be adopted.

The sixth characteristic configuration of the present invention specifies an embodiment suitable for the implementation of any of the first to fifth characteristic configurations,
The reheating means is configured such that a heating side combined operation for heating the purified exhaust air after dehumidification by the cooling dehumidifying means is possible by the heat radiation function of the heat pump and the heat radiation function of the auxiliary heat source device.

  That is, according to this configuration, the heat pump capacity is set so that the heat absorption amount of the heat pump and the air cooling amount in the cooling and dehumidifying means are balanced, or the capacity of the heat pump reaches the upper limit. In the situation where the heat pump capacity cannot be adjusted to the increase side, the heat pump's heat dissipation amount becomes insufficient with respect to the air heating amount in the reheating means. The shortage of heat can be covered by the heat dissipation function of the auxiliary heat source device.

  That is, even in a situation where the capacity of the heat pump cannot be adjusted to the increase side, it is possible to increase the amount of air heating in the reheating means and increase the amount of reheat of the purified exhaust air in the reheating means. 2 The temperature adjustment function can be further enhanced in adjusting the temperature and humidity of the painting chamber.

  In the implementation of the above configuration, the heating-side combined operation is always performed, and any change in the heat radiation amount of the heat pump or the auxiliary cold heat source device is applied to the change in the air heating amount in the reheating means. Either a method of adjusting one or both of them, or a method of performing the heating side combined operation when the air heating amount in the reheating means cannot be covered by the single operation of the heat pump may be adopted.

The seventh feature configuration of the present invention specifies an embodiment suitable for the implementation of the first to sixth feature configurations.
Heating the purified exhaust air after dehumidification by the cooling and dehumidifying means in the reheating means by a part of the heat dissipation function of the heat pump,
The other feature is that the air supplied to the first coating chamber is heated in the air conditioner by the other part of the heat dissipation function of the heat pump.

  In other words, according to this configuration, the heat dissipation function of the heat pump is also used for air heating in the air conditioner for the first painting chamber (that is, also used for adjusting the air supplied to the first painting chamber). (Compressor drive power in the case of a compression heat pump) A form that takes advantage of the heat pump in terms of energy consumption, which can pump up a large amount of heat from a low-temperature heat source to a high-temperature heat source by generating only heat and generate heat. Thus, the energy consumption of the painting facility can be reduced more effectively.

The eighth feature configuration of the present invention specifies an embodiment suitable for the implementation of any of the first to seventh feature configurations,
Cooling the purified exhaust air by the wet purification means in the cooling dehumidification means by a part of the heat absorption function of the heat pump,
The other part of the heat absorption function of the heat pump is to cool the air supplied to the first coating chamber in the air conditioner.

  That is, according to this configuration, the heat absorption function of the heat pump is also used for air cooling in the air conditioner for the first painting chamber (that is, also used for adjusting the air supplied to the first painting chamber). As with the feature configuration, the painting equipment is made to take advantage of the heat pump in terms of energy consumption by generating a large amount of heat from a low-temperature heat source to a high-temperature heat source simply by supplying heat pump drive energy. Energy consumption can be reduced more effectively.

  In addition, it can replace with the 7th, 8th characteristic composition, and can use other parts of the heat dissipation function of a heat pump, and other parts of the heat absorption function of a heat pump besides air heating and air cooling with an air conditioner to the 1st painting room. However, in contrast to this, with the seventh and eighth feature configurations, the cold / hot recovery system can be completed between the first painting chamber and the second coating chamber, and the cold / hot recovery is achieved. The use system can be simplified, and this point is further advantageous in simplifying or downsizing the equipment configuration of the painting facility.

Configuration diagram of painting equipment Circuit diagram around the heat pump showing the first embodiment Circuit diagram around the heat pump showing the second embodiment The enlarged view of the principal part which shows other embodiment

[First Embodiment]
FIG. 1 shows a painting facility. In this painting facility, an operator manually sprays the object B (automobile body in this example), which is sequentially conveyed by the conveying means 1 at a predetermined pitch, using a painting gun. A robot painting in which a first painting chamber 2 is provided as a work room, and the painting robot 3 sprays and coats the object B sequentially conveyed by the conveying means 1 following the spray painting in the first painting chamber 2. A second painting chamber 4 is provided as a work chamber.

  Air supply chambers 5a and 5b are provided in the ceiling portions of the painting chambers 2 and 4, and the regulated airs Sa and Sb supplied to the air supply chambers 5a and 5b are laminarly flowed from the entire ceiling portion through the ceiling filters 6a and 6b. By supplying the paint chambers 2 and 4 in a shape, the paint chambers 2 and 4 are ventilated and the interiors of the paint chambers 2 and 4 are adjusted to a required temperature and humidity state suitable for painting work.

  Further, below the coating chambers 2 and 4, exhaust air Ea and Eb discharged from the coating chambers 2 and 4 through the lattice floors 7a and 7b in accordance with the supply of the adjustment airs Sa and Sb from the ceiling is washed water. Passing through the throttle passages 8a and 8b at a high speed in the state of confluence with W and bringing it into violent gas-liquid contact with the cleaning water W, trapping unwashed floating paint mist and the like contained in the exhaust air Ea and Eb in the cleaning water W Wet purification devices 9a, 9b (an example of wet purification means) for purifying exhaust air Ea, Eb are provided.

  The cleaning water W that has captured the paint mist is removed from the paint contained therein and then supplied again to the wet purification devices 9a and 9b for reuse.

  The air supply chamber 5a of the first painting chamber 2 is supplied with adjusted air Sa adjusted in temperature and humidity by the air conditioner 10 through the air supply path 12 by the air supply fan 11, and these air supply fan 11 and air supply path. Reference numeral 12 denotes an air supply means for supplying the adjusted air Sa from the air conditioner 10 to the first painting chamber 2.

  The air conditioner 10 is equipped with an air inlet 10a, a preburner 10b, a filter 10c, a washer 10d, an air cooler 10e, an afterburner 10f, a steam humidifier 10g, and an air outlet 10h in that order in the air flow direction. It is.

  That is, in the cooling period, in this air conditioner 10, for the external air A (generally fresh outside air) taken from the air intake port 10a, heat insulation humidification by the washer 10d, cooling dehumidification by the air cooler 10e, By performing the cooling mode operation in which reheating (heating) by the afterburner 10f is performed in that order, adjusted air Sa of the set temperature and humidity (set dry bulb temperature ta, set absolute humidity xa) is generated, and this generation adjustment Air Sa is sent out from the air outlet 10 h and supplied to the first coating chamber 2 through the air supply path 12.

  During the heating period, in the air conditioner 10, the external air A taken in from the air intake port 10a is preheated by the preburner 10b, heat-insulated humidification by the washer 10d, heating by the afterburner 10f, and the steam humidifier 10g. By performing the heating mode operation in which the humidification is performed in that order, the adjusted air Sa of the set temperature and humidity ta, xa is generated, and this generated adjusted air Sa is sent out from the air outlet 10h and passed through the air supply path 12 Supply to the first painting chamber 2.

  In general, the set temperature and humidity ta and xa of the adjusted air Sa are often different between the cooling period and the heating period, and the adjustment air Sa is also used in the intermediate period in which the cooling mode operation or the heating mode operation is selectively performed. The set temperature and humidity ta and xa are often different.

  Reference numeral 13 denotes a refrigerator that cools a heat transfer liquid for air cooling supplied to the air cooler 10e through the circulation path 13a, 14 denotes a fuel supply path to the afterburner 10f and the preburner 10b, and 15 denotes a steam supply path to the steam humidifier 10g. Yes, 13b, 14a, 14b, 15a are valve devices for adjusting the flow rate installed in the respective paths 13a, 14, 15;

  That is, the valve devices 13b, 14a, 14b, and 15a adjust the supply amount of the cooling heat transfer fluid C to the air cooler 10e, the fuel supply amount to the afterburner 10f and the preburner 10b, and the steam supply amount to the steam humidifier 10g. Then, by adjusting the air cooling amount by the air cooler 10e, the air heating amount by the afterburner 10f and the preburner 10b, and the air humidification amount by the steam humidifier 10g, the temperature and humidity of the production adjustment air Sa are set to the set temperature and humidity. Adjust to ta, xa.

  In addition, about the ventilation of the 1st painting chamber 2 by supply of adjustment air Sa, since the frequency | count of ventilation is set up considerably large, the room | chamber interior of the 1st painting chamber 2 is supplied of adjustment air Sa by the supply of the said adjustment air Sa. The temperature and humidity are adjusted and held substantially the same as the set temperature and humidity ta and xa.

  On the other hand, for the second coating chamber 4, the purified exhaust air Ea ′ sent from the wet purification device 9 a of the first coating chamber 2 (that is, the first coating purified by removing paint mist and the like in the wet purification device 9 a). A relay path 16 is provided for guiding the exhaust air from the chamber 2 to the air supply chamber 5b of the second painting chamber 4, and a relay fan 17a and a second air supply fan 17b are interposed in the relay path 16.

  That is, the entire amount of ventilation air supplied to the second painting chamber 4 is supplied to the second painting chamber 4 through the relay path 16 as purified exhaust air Ea ′ by the wet purification device 9a as ventilation air. The passage 16, the relay fan 17a, and the second air supply fan 17b constitute second air supply means for supplying the exhaust gas Ea ′ purified by the wet purification device 9a to the second painting chamber 4 as ventilation air.

  Then, by supplying the purified exhaust air Ea 'from the wet purification device 9a to the second coating chamber 4 in this way, the purified exhaust air Ea' from the wet purification device 9a is used as ventilation air in the second coating chamber 4 in terms of material. In the second coating chamber 4, the cool and warm heat possessed by the purified exhaust air Ea ′ is also used.

Further, in the relay path 16, between the relay fan 17a and the second air supply fan 17b, a residual foreign matter removing filter 19 and purified exhaust air Ea 'that has passed through the filter 19 are converted into a heat pump 18 (CO in this example). ₍₂ ) A cooling / dehumidifying device 20 (an example of cooling / dehumidifying means) that cools and dehumidifies by an endothermic function of a refrigerant (supercritical compression heat pump) is provided, and purified exhaust air Ea ′ dehumidified by the cooling / dehumidifying device 20 Is equipped with a reheating device 21 (an example of a reheating means) that reheats and reheats.

  In other words, the second coating chamber 4 is provided with purified exhaust air Ea ″ adjusted in temperature and humidity by dehumidification by the cooling and dehumidifying device 20 and reheating by the reheating device 21 as the adjusted air Sb. Adjust to the temperature and humidity state of.

  In the supercritical compression heat pump, the condensation process of the refrigerant r is in a high pressure range from the critical point, and no clear refrigerant condensation phenomenon is observed. A refrigerant phenomenon that occurs in a process portion corresponding to a condensation process of a compression heat pump is referred to as condensation as in a general compression heat pump.

  As shown in FIG. 2, the cooling and dehumidifying device 20 circulates between the heat medium liquid tank 22 that cools the stored heat medium liquid C to a predetermined temperature by the heat absorption function of the heat pump 18, and the heat medium liquid tank 22. An air cooler 25 that circulates the heat medium liquid C by the circulation pump 24 through the passage 23 is provided, and a valve device 26 (flow rate) composed of a shunt type three-way valve that adjusts the supply amount of the heat medium liquid C to the air cooler 25 An example of adjusting means) is provided.

  That is, the cooling and dehumidifying device 20 cools and dehumidifies the purified exhaust air Ea ′ by exchanging heat with the cooling heat medium liquid C in the air cooler 25, and the cooling heat medium liquid for the air cooler 25 by the valve device 26. The dehumidification amount of the purified exhaust air Ea ′ is adjusted by adjusting the supply amount of C and adjusting the air cooling amount in the air cooler 25.

  And as a structure which cools the stored heat-medium liquid C of the heat-medium liquid tank 22 with the heat absorption function of the heat pump 18, it is between the heat-absorber 18a (from the refrigerant side, evaporator) of the heat pump 18 and the heat-medium liquid tank 22. A circulation path 28 for circulating the heat medium liquid C by the circulation pump 27 is provided. In the heat medium liquid circulation in the circulation path 28, the heat medium liquid C taken out from the heat medium liquid tank 22 is received by the heat absorber 18 a of the heat pump 18. Heat is exchanged with the low-pressure side refrigerant r in the heat pump 18 to cool by taking vaporization heat accompanying the evaporation of the low-pressure side refrigerant r, and the cooling heat medium liquid C is returned to the heat medium liquid tank 22, whereby the heat medium liquid tank 22 The stored heat transfer medium C is cooled.

  Further, as described later, the coating equipment of this example employs a method of adjusting the ability of the heat pump 18 so as to balance the heat radiation amount of the heat pump 18 and the air heating amount (reheat amount) in the reheating device 21. There may be a situation in which the heat absorption amount of the heat pump 18 is insufficient with respect to the air cooling amount in the cooling and dehumidifying device 20, but as a countermeasure against this, heat is generated by the circulation pump 30 through the circulation path 29 with the heat medium liquid tank 22. An auxiliary refrigerator 31 (an example of an auxiliary cooling heat source device) that circulates the medium C and cools the stored heat medium liquid C in the heat medium liquid tank 22 together with the heat pump 18 is provided.

  That is, by providing the auxiliary refrigerator 31, the cooling side combined operation of cooling the purified exhaust air Ea 'by the heat absorption function of the heat pump 18 and the heat absorption function of the auxiliary refrigerator 31 in the air cooler 25 of the cooling and dehumidifying device 20 is performed. In this way, the auxiliary refrigerator 31 covers the shortage of the heat pump heat absorption amount with respect to the air cooling amount in the cooling and dehumidifying device 20.

  The heat pump side circulation path 28 and the auxiliary refrigerator side circulation path 29 with respect to the heat medium liquid tank 22 are each a valve device comprising a shunt type three-way valve for adjusting the return amount of the heat medium liquid C to the heat medium liquid tank 22. 32a and 32b are provided, and based on the detection information of the temperature sensor 33 that detects the temperature of the stored heat transfer medium C in the heat transfer liquid tank 22, the valve controllers 32a and 32b of the circulation paths 28 and 29 are controlled by the valve controller 34. Is automatically operated to adjust the temperature of the stored heat transfer medium C in the heat transfer liquid tank 22 to a predetermined temperature.

  On the other hand, as shown in FIG. 2, the reheater 21 takes out a part ea ′ of the purified exhaust air Ea ′ after being dehumidified by the cooling dehumidifier 20 from the relay passage 16 by a bleeder fan 35 by a constant amount. The extraction passage 36 that leads to the radiator 18b (condenser from the refrigerant side) of the heat pump 18 and the extracted partial air ea 'are disposed downstream of the extraction passage connecting portion in the relay passage 16 from the radiator 18b of the heat pump 18. The return air passage 37 returning in part and the return air ea 'returning through the return air passage 37 are jetted and supplied in a state of being evenly dispersed with respect to the remainder of the purified exhaust air Ea' after dehumidification from the numerous jet holes 38a. And a mixer 38 for mixing.

  In other words, the reheat device 21 conducts heat exchange with the high-pressure side refrigerant r in the heat pump 18 by guiding a part ea ′ of the purified exhaust air Ea ′ after dehumidification to the radiator 18 b of the heat pump 18 through the extraction passage 36, thereby increasing the pressure. Dehumidification is achieved by heating by condensation heat release accompanying the condensation of the side refrigerant r, and mixing this heated air ea 'as return air with the remainder of the purified exhaust air Ea' after dehumidification by the mixer 38 through the return air passage 37. The remainder of the subsequent purified exhaust air Ea ′ is also heated, whereby the entire amount of the purified exhaust air Ea ′ dehumidified by the cooling dehumidifier 21 is reheated, and the purified exhaust air whose temperature is adjusted by reheating following humidity adjustment by dehumidification Ea ″ is generated.

  At the downstream side of the mixer 38 in the relay path 16, purified exhaust air Ea ″ (that is, adjusted air Sb supplied to the second coating chamber 4) adjusted in temperature and humidity by the cooling and dehumidifying device 20 and the reheating device 21. A temperature sensor 39 and a humidity sensor 40 for detecting the temperature t and the humidity x are provided, and the temperature sensor 39 is used as a controller for controlling the heat pump 18, the cooling / dehumidifying device 20, and the reheating device 21 in this painting facility. And the second painting chamber in which the valve device 26 for the air cooler 25 is automatically operated based on the detection information of the humidity sensor 40 and the capacity (specifically, the rotational speed of the compressor) of the heat pump 18 is automatically adjusted by inverter control or the like. An air conditioning controller 41 is provided.

  Then, the air conditioning controller 41 for the second coating chamber adjusts the dehumidification amount by the cooling dehumidifying device 20 by adjusting the valve device 26 for the air cooler 25 based on the detection information of the humidity sensor 40, 2 Adjusting the humidity x of the adjusted air Sb (= Ea ″) supplied to the coating chamber 4 to the set absolute humidity xb, and adjusting the capability of the heat pump 18 based on the detection information of the temperature sensor 39, the reheating device 21, the temperature of the heated air ea ′ ejected from the ejection hole 38a of the mixer 38 is adjusted (ie, the amount of reheat by the reheat device 21 is adjusted), and the adjusted air Sb (= Ea) supplied to the second coating chamber 4 The temperature t ") is adjusted to the set dry bulb temperature tb.

  As with the first painting chamber 2, the ventilation rate of the second painting chamber 4 by supplying the adjusted air Sb (= Ea ″) is set to be considerably large, so that the supply of the adjusted air Sb is performed. As a result, the interior of the second painting chamber 4 is adjusted and held in substantially the same temperature and humidity state as the set temperature and humidity tb, xb of the adjusted air Sb.

  The exhaust air Eb discharged from the second painting chamber 4 with the supply of the adjustment air Sb (= Ea ″) is purified by the wet purification device 9b of the second painting chamber 4 and then externally by the exhaust fan 43 through the exhaust passage 42. To discharge.

  In this example, the filter 19, the air cooler 25 of the cooling / dehumidifying device 20, and the mixer 38 of the reheating device 21 are provided in one device case 44. However, the filter 19, the air cooler 25, the mixer 38 may be interposed in the relay path 16 in a state of being installed in each separate device case.

[Second Embodiment]
In said 1st Embodiment, although the coating equipment of the system which adjusts the capability of the heat pump 18 was shown so that the heat radiation amount of the heat pump 18 and the air heating amount (reheating amount) in the reheating apparatus 21 may be balanced, In the second embodiment, conversely, a coating facility of a system in which the capacity of the heat pump 18 is adjusted so as to balance the heat absorption amount of the heat pump 18 and the air cooling amount in the cooling and dehumidifying means 20 is shown.

  That is, in this second embodiment, the cooling / dehumidifying device 20 shown in FIG. 1 is used to transfer the heat transfer fluid C between the heat absorber 18a of the heat pump 18 and the air cooler 25 through the circulation path 23 'as shown in FIG. The circulation pump 24 'is configured to circulate directly.

  That is, in the cooling and dehumidifying device 20, the heat medium liquid C cooled by the heat absorber 18a of the heat pump 18 and the purified exhaust air Ea 'that has passed through the filter 19 in association with circulation of the heat medium liquid in the circulation path 23'. By performing heat exchange at 25, the purified exhaust air Ea 'is cooled and dehumidified.

  Further, in this cooling and dehumidifying device 20, a circulation device 23 ′ is equipped with a valve device 26 ′ (an example of a flow rate adjusting means) composed of a split type three-way valve that adjusts the supply amount of the cooling heat transfer medium C to the air cooler 25. By adjusting the supply amount of the cooling heat transfer fluid C to the air cooler 25 by this valve device 26 ', the air cooling amount in the air cooler 25 is adjusted to adjust the dehumidification amount of the purified exhaust air Ea'. To do.

  On the other hand, as shown in FIG. 3, the reheat device 21 shown in FIG. 1 is different from the reheat device 21 shown in FIG. 2 in the dehumidified purified exhaust air Ea ′ taken out from the relay passage 16 to the extraction passage 36. A mixed path 45 that mixes external air a that has been removed by the filter 45a with respect to a part ea ', and a mixed air ma that returns from the radiator 18b of the heat pump 18 to the relay path 16 through the return air path 37 (that is, to the extraction path 36). An exhaust passage 46 for discharging a part ma ″ of the extracted purified exhaust air ea ′ and the mixed air of the outside air a from the mixing passage 45) to the outside is added.

  In addition, the reheat device 21 has a mixing-side damper device 47 that adjusts the mixing amount of the external air a from the mixing passage 45 and a discharge amount of the partial air ma ″ that is discharged to the outside through the exhaust passage 46. The exhaust-side damper device 48 to be adjusted is provided, and the exhaust-side damper device 48 is detected by the air volume sensor 49 installed downstream of the connection portion of the exhaust passage 46 in the return air passage 37. Based on the adjustment, the exhaust side damper device 48 is adjusted to adjust the discharge amount of the partial air ma ″ discharged from the exhaust passage 46 to the outside, so that the mixing supplied to the mixer 38 of the relay passage 16 through the return air passage 37 A damper controller 50 that automatically adjusts the amount of air ma ′ to a set amount (here, an amount equal to the amount of air taken out (design amount) into the bleed passage 36) is provided.

  That is, in the reheating device 21, the mixed air ma led to the radiator 18b of the heat pump 18 through the bleed passage 36 is heated by the heat dissipation function of the heat pump 18, and the mixed amount of the purified exhaust air ea 'in the heated mixed air ma. Is mixed with the remainder of the purified exhaust air Ea ′ by the mixer 38 so that the remainder of the purified exhaust air Ea ′ is also heated and dehumidified by the cooling dehumidifier 20. Reheat the entire amount of Ea ′.

  And while the capability of the heat pump 18 is adjusted so that the heat absorption amount of the heat pump 18 and the air cooling amount in the cooling and dehumidifying means 20 are balanced, the air heating in the reheating device 21 out of the heat radiation amount of the heat pump 18. The surplus in (reheating) is discarded outside as retained heat of the heated mixed air ma ″ discharged outside through the exhaust passage 46.

  On the other hand, with respect to the air conditioning controller 41 for the second coating chamber that controls the heat pump 18, the cooling and dehumidifying device 20, and the reheating device 21, a control method for balancing the heat absorption amount of the heat pump 18 and the air cooling amount in the cooling and dehumidifying means 20. As described above, by adjusting the valve device 26 'for the air cooler 25 based on the detection information of the humidity sensor 40, the amount of air dehumidification in the cooling and dehumidifying device 20 is adjusted, and the adjusted air Sb supplied to the second coating chamber 4 The humidity x of (= Ea ″) is adjusted to the set absolute humidity xb.

  Further, by adjusting the mixing-side damper device 47 based on the detection information of the temperature sensor 39 and adjusting the mixing amount of the external air a from the mixing passage 45, the air from the exhaust passage 46 by the exhaust-side damper device 48 associated therewith is adjusted. The amount of waste heat to the outside is adjusted by adjusting the amount of discharge (that is, the amount of reheat in the reheat device 21 is adjusted), and the temperature t of the adjusted air Sb (= Ea ″) supplied to the second coating chamber 4 is set. It is configured to adjust to dry bulb humidity tb.

  The heat pump 18 has a self-adjusting function for adjusting the heat pump capacity by inverter control or the like so that the temperature of the heat transfer fluid C supplied to the cooling and dehumidifying device 20 is adjusted and maintained at the set outlet temperature. When the supply amount of the cooling heat medium liquid C to the vessel 25 is adjusted by the adjustment valve 26 ′, the capacity of the heat pump 18 is automatically adjusted following the adjustment, whereby the heat absorption amount of the heat pump 18 and the cooling dehumidifying means 20 are adjusted. The capacity of the heat pump 18 is adjusted so that the amount of air cooling is balanced.

  Moreover, in this 2nd Embodiment, the surplus part in the air heating (reheating) in the reheating apparatus 21 among the heat dissipation of the heat pump 18 is discarded outside together with the heated mixed air ma ″ discharged from the exhaust passage 46. However, instead of this, the heated mixed air ma ″ discharged from the exhaust passage 46 is taken in from the air intake port 10a in the air conditioner 10 for the first coating chamber as shown by the broken line in FIG. The air conditioner 10 may be used for preheating the air.

  About others, it is the same as that of 1st Embodiment.

[Another embodiment]
Next, another embodiment of the present invention will be listed.
The wet purification means for purifying the exhaust air Ea by bringing the exhaust air Ea from the first painting chamber 2 and the cleaning water W into gas-liquid contact is not limited to the wet purification device 9a shown in the above-described embodiment, but has various structures. For example, the structure may be such that the cleaning water W is sprayed by a nozzle or the like on the exhaust air Ea from the first coating chamber 2 so that both are in gas-liquid contact.

  The cooling and dehumidifying means for cooling and dehumidifying the purified exhaust air Ea ′ by the wet purification means 9a is not limited to the cooling and dehumidifying device 20 shown in the above-described embodiment, and the purified exhaust air Ea is cooled and dehumidified by the heat absorption function of the heat pump 18. If so, various structures can be adopted. For example, the purified exhaust air Ea ′ obtained by the wet purification means 9a and the low-pressure side refrigerant of the heat pump 18 are directly heat-exchanged by a heat exchanger, and purified exhaust. The structure etc. which cool and dehumidify air Ea 'may be sufficient.

  Similarly, the reheating means for heating and reheating the purified exhaust air Ea dehumidified by the cooling and dehumidifying means 20 is not limited to the reheating device 21 shown in the above-described embodiment, but for cooling the air by the cooling and dehumidifying means 20. As long as the purified exhaust air Ea ′ after dehumidification is reheated by the heat radiation function of the accompanying heat pump 18, various structures can be adopted, for example, the total amount of the purified exhaust air Ea ′ after dehumidification and the high pressure side of the heat pump 18. A structure in which heat is directly exchanged with the refrigerant in the heat exchanger to reheat the purified exhaust air Ea ′ after dehumidification, a heat transfer medium heated by the heat release function of the heat pump 18 and the purified exhaust air Ea ′ after dehumidification May be configured such that the purified exhaust air Ea ′ after dehumidification is reheated by exchanging heat with a heat exchanger.

  In the first embodiment described above, the cooling and dehumidifying means 20 is dehumidified by cooling the purified exhaust air Ea 'by the wet purification means 9a by the heat absorbing function of the heat pump 18 and the heat absorbing function of the auxiliary cooling source device 31 (auxiliary refrigerator). Although the cooling side combined operation is possible, instead of this, or in combination with this, the reheating means 21 is made by the cooling and dehumidifying means 20 by the heat radiation function of the heat pump 18 and the heat radiation function of the auxiliary heat source device. You may make it the structure in which the heating side combined use operation which heats and reheats purified exhaust air Ea 'after dehumidification is possible.

  In the second embodiment described above, the heated mixed air ma ″ discharged from the exhaust passage 46 is mixed with the external air A taken in from the air intake port 10a in the air conditioner 10 for the first painting chamber, and the air in the air conditioner 10 is mixed. As represented by the configuration used for air preheating, the reheat means 21 heats and reheats the purified exhaust air Ea ′ after dehumidification by the cooling and dehumidification means 20 by a part of the heat radiation function of the heat pump 18, and this is also performed. And you may make it utilize the other part of the thermal radiation function of the heat pump 18 for the heating (preheating and reheating) of the air Sa supplied to the 1st coating chamber 2 in the air conditioner 10 for 1st coating chambers.

  Similarly, the cooling dehumidification means 20 cools and dehumidifies the purified exhaust air Ea ′ by the wet purification means 9a by a part of the heat absorption function of the heat pump 18, and at the same time, other parts of the heat absorption function of the heat pump 18 are provided. The air conditioner 10 for the first painting chamber may be used for cooling (precooling or cooling) of the air Sa supplied to the first painting chamber 2.

  In the implementation of the painting facility according to the present invention, the article W to be coated is not limited to an automobile body, and the article to be coated may be an automobile part, a case or part of an electrical product, a steel sheet, or the like. .

  Further, the first painting chamber is not limited to a manual painting work room in which an operator paints an object to be coated. Similarly, the second painting room is also restricted to a robot painting work room in which a painting robot paints an object to be coated. Each of the first and second painting rooms may be either a manual painting work room or a robot painting work room, and is a painting work room in which manual painting work and robot painting work are performed in parallel. May be.

  In the above-described embodiment, the configuration is such that the workpiece W painted in the first coating chamber 2 is subsequently coated in the second coating chamber 4 (that is, the second coating chamber 4 is first coated on the transport path of the coating W). In contrast to this, a mode in which the first coating chamber 2 is positioned on the lower side of the second coating chamber 4 on the conveyance path of the article W, You may employ | adopt the form which arrange | positions the 1 coating chamber 2 and the 2nd coating chamber 4 in parallel on a to-be-coated article conveyance path | route.

  Furthermore, the first coating chamber 2 and the second coating chamber 4 may be coating chambers for coating different articles W to be coated.

  INDUSTRIAL APPLICABILITY The present invention can be used in a painting facility including a plurality of painting rooms that require adjustment air in painting various objects such as automobile bodies.

DESCRIPTION OF SYMBOLS 10 Air conditioner Sa Adjusted air 2 1st coating chamber 11, 12 Air supply means Ea Exhaust air W Washing water 9a Wet purification means Ea 'Purified exhaust air 4 2nd coating chamber 16 2nd air supply means 17a, 17b 2nd air supply Means 18 Heat pump 20 Cooling dehumidification means 21 Reheating means Ea ″ (Sb) Purified exhaust air ea ′ adjusted in temperature and humidity ea ′ Part of purified exhaust air dehumidified, heated air a External air ma Mixed air ma ′ Part of heated mixed air ma ″ The remainder of the heated mixed air C Heat medium liquid 22 Heat medium liquid tank 25 Air cooler 26, 26 ′ Flow rate adjusting means 31 Auxiliary cold heat source equipment

Claims (8)

Air supply means for supplying air adjusted by the air conditioner to the first painting chamber, and wet treatment for purifying exhaust air discharged from the first painting chamber in accordance with air supply by the air supply means by bringing it into gas-liquid contact with cleaning water Purification means,
A painting facility provided with a second air supply means for supplying the exhaust gas purified by the wet purification means to the second painting chamber as ventilation air,
Cooling and dehumidifying means for cooling and dehumidifying the purified exhaust air by the wet purification means by a heat absorption function of a heat pump;
Reheat means for heating and reheating the purified exhaust air dehumidified by the cooling and dehumidifying means by means of the heat radiation function of the heat pump accompanying air cooling in the cooling and dehumidifying means,
A painting facility configured to supply purified second exhaust air whose temperature and humidity are adjusted by dehumidification by the cooling and dehumidifying means and reheating by the reheating means to the second painting chamber.   The reheating means is configured to heat a part of the purified exhaust air dehumidified by the cooling dehumidifying means by the heat release function of the heat pump and to mix the heated air with the remaining purified exhaust air dehumidified by the cooling dehumidifying means. The coating equipment according to claim 1.   The reheating means heats the mixed air of a part of the purified exhaust air dehumidified by the cooling and dehumidifying means and the external air by the heat release function of the heat pump, and makes the mixed amount of the purified exhaust air in the heated mixed air. The coating equipment according to claim 2, wherein a corresponding part is mixed with the remaining portion of the purified exhaust air dehumidified by the cooling and dehumidifying means, and the remaining portion of the heated mixed air is discharged to the outside. The cooling and dehumidifying means includes a heat medium liquid tank for cooling the stored heat medium liquid to a predetermined temperature by the heat absorption function of the heat pump;
An air cooler that cools the purified exhaust air by exchanging heat between the heat medium liquid circulated between the heat medium liquid tank and the purified exhaust air by the wet purification means;
The coating equipment according to any one of claims 1 to 3, further comprising a flow rate adjusting means for adjusting a supply amount of the heat medium liquid to the air cooler.   The cooling dehumidifying means is configured to be capable of performing a cooling side combined operation for cooling the purified exhaust air by the wet purification means by the heat absorbing function of the heat pump and the heat absorbing function of the auxiliary cooling source device. The coating equipment according to claim 1.   The reheating unit is configured to be capable of heating side combined operation for heating the purified exhaust air after dehumidification by the cooling dehumidifying unit by the heat dissipation function of the heat pump and the heat dissipation function of the auxiliary heat source device. The coating equipment according to any one of 5. Heating the purified exhaust air after dehumidification by the cooling and dehumidifying means in the reheating means by a part of the heat dissipation function of the heat pump,
The painting equipment according to any one of claims 1 to 6, wherein the air supplied to the first painting chamber is heated in the air conditioner by the other part of the heat radiation function of the heat pump. Cooling the purified exhaust air by the wet purification means in the cooling dehumidification means by a part of the heat absorption function of the heat pump,
The coating equipment according to any one of claims 1 to 6, wherein air supplied to the first coating chamber is cooled in the air conditioner by the other part of the heat absorption function of the heat pump.

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