JP2010007908A - Air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioning system capable of improving starting characteristics by shortening start time when heat quantity held by a heating medium heated by solar heat is used for starting of an absorption refrigerating machine. <P>SOLUTION: The air conditioning system is provided with the absorption refrigerating machine (20); a solar heat collecting device (8); a solar heat circuit (30) thermally communicated to a dilute solution line (La) of the absorption refrigerating machine (20) via a first heat exchanger (9); an exhaust gas line (absorption refrigerating machine exhaust gas line Lk) for discharging combustion exhaust gas of a combustor (25) of a regenerator (2) of the absorption refrigerating machine (20) to outside of the absorption refrigerating machine (20); and a second heat exchanger (exhaust gas heat exchanger 35) for inputting heat quantity held by the combustion exhaust gas of the combustor (25) of the regenerator (2) made to flow and pass within the exhaust gas line (Lk) to the heating medium circulated within the solar heat circuit (30). <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an air conditioning system that uses solar heat for cooling operation by an absorption refrigeration machine, and more particularly, to a technique for improving operating characteristics at startup in such an air conditioning system.

Absorption refrigerators are widely used as a technique for obtaining cold heat from a heat source (see, for example, Patent Document 1).
And the technique of using the heat | fever of the comparatively low temperature (30 degreeC-120 degreeC) obtained by a solar heat combining an absorption refrigerator and a solar thermal collector (solar thermal collector panel) is proposed (for example, patent document 2). reference). In this case, the solar heat recovered by the solar heat collecting panel has the same effect as a low-temperature regenerator in a double-effect absorption refrigerator or a dedicated exhaust heat regenerator having the same level pressure as the low-temperature regenerator. Further, the heat medium is cooled (by the absorption refrigerator) by consuming the amount of heat held by the heat medium on the absorption refrigerator side.
In the technology that combines an absorption chiller and a solar heat collection panel, the heat that circulates in the solar heat circuit is configured by forming a solar heat circuit that interposes the solar heat collection panel and that is in thermal communication with the dilute solution line of the absorption chiller. The medium is heated by a solar heat collecting panel, and the amount of heat held by the heated heat medium is put into the absorbing solution flowing through the dilute solution line of the absorption refrigerator.

Here, when the absorption refrigerator is heated with a heat medium, a certain amount of heat is required for heating the heat medium at the time of start-up, and the amount of heat for heating the heat medium is completely different from the display of the refrigerating capacity in the absorption refrigerator. Does not contribute. And since the heat capacity in a solar heat collection panel is also quite large, in order to heat the heat medium which circulates a solar thermal circuit to the level required for starting of an absorption refrigerator, it will require a long time.
At that time, the amount of heat recovered by the solar heat collector is not constant, and the amount of heat recovered is not linked to the cooling load at all. Of course, whether the absorption chiller is activated or not is determined. It has nothing to do with the amount of heat recovered by. Therefore, when the heat medium circulating in the solar heat circuit is heated by the solar heat collecting panel, the amount of heat held by the heated heat medium is input to the absorption solution flowing through the dilute solution line of the absorption refrigerator and the absorption refrigerator is started. In this case, it takes a long time to start up, and the start-up characteristics may be deteriorated.
Moreover, there is a problem that the amount of heat required for starting does not contribute to the cooling operation in the air conditioning system at all.
Japanese Patent Laid-Open No. 7-218017

  The present invention has been proposed in view of the above-described problems of the prior art, and is an air conditioning system that uses solar heat for cooling operation by an absorption refrigerator, and absorbs the amount of heat held by the heat medium heated by solar heat. The purpose of the present invention is to provide an air conditioning system that can shorten the start-up time and improve the start-up characteristics when used for starting the refrigerator.

The air conditioning system of the present invention includes an absorption refrigerator (20), a solar heat collector (solar heat collector panel 8), and a solar heat collector, and is thermally coupled to the absorption refrigerator (20). Exhaust gas line (absorption chiller exhaust gas) for discharging the combustion exhaust gas of the combustor (burner 25) of the solar heat circuit (30) communicating with the regenerator (2) of the absorption chiller (20) to the outside of the absorption chiller The amount of heat held by the combustion exhaust gas of the combustion device (25) of the regenerator (2) flowing through the line Lk) and the exhaust gas line (Lk) is input to a heat medium circulating in the solar heat circuit (30). A second heat exchanger (exhaust gas heat exchanger 35), and in the solar heat circuit (30), the second heat exchanger (exhaust gas heat exchanger 35) is the first heat exchanger (solar heat heat exchanger). 9) Solar thermal collector (solar thermal collector panel 8) side (or above) Is characterized in that it is interposed on the side) (claim 1).
Here, as a mode in which the solar thermal circuit (30) is in thermal communication with the absorption refrigerator (20), for example, the amount of heat held by the heat medium flowing through the solar thermal circuit (30) is a heat exchanger (solar heat input heat exchange). It can be configured to be introduced into the absorbing solution (dilute solution) flowing through the diluted solution line (La) of the absorption refrigerator (20) via the vessel 9). Alternatively, the regenerator (solar heat regenerator WE9) may be interposed in the dilute solution line (La), and the refrigerant vapor (gas phase refrigerant) may be regenerated by the amount of heat held by the heat medium flowing through the solar heat circuit (30). Further, a heat exchanger (solar heat input heat exchanger 9) and a regenerator (solar heat regenerator WE9) may be interposed in the dilute solution line (La) of the absorption refrigerator (20).

  In the present invention, the solar heat circuit (30) includes a first bypass line (heat medium bypass line 32) that bypasses the second heat exchanger (exhaust gas heat exchanger 35), and a second flow of the heat medium. And a switching device (for example, a three-way valve V1) for switching between the heat exchanger (exhaust gas heat exchanger 35) side and the first bypass line (heat medium bypass line 32) side. It is preferable that a control device (control unit 10) for switching and controlling the device (for example, the three-way valve V1) is provided (claim 2).

  In the present invention, the exhaust gas line (absorption refrigerator exhaust gas line Lk) includes a second bypass line (exhaust gas bypass line Lkb) that bypasses the second heat exchanger (exhaust gas heat exchanger 35), and combustion. A switching device (for example, a three-way valve) that switches the flow of the combustion exhaust gas of the device (burner 25) to either the second heat exchanger (exhaust gas heat exchanger 35) side or the second bypass line (exhaust gas bypass line Lkb) side V3) and a control device (control unit 10) for switching and controlling the switching device (for example, the three-way valve V3) is preferable.

Here (in the air conditioning system according to any one of claims 2 and 3), a first measuring means (heat medium temperature sensor St1) for measuring the temperature (T _S ) of the heat medium, and a combustion device (burner 25). And a second measuring means (exhaust gas temperature sensor St2) for measuring the temperature (T _E ) of the combustion exhaust gas, and the control device (10) switches and controls the switching devices (three-way valves V1, V3). When the temperature (T _S ) of the heat medium is higher than the temperature (T _E ) of the combustion exhaust gas (T _S > T _E ), the heat medium and / or the combustion exhaust gas is converted into the second heat exchanger (exhaust gas heat). When the temperature of the heat medium (T _S ) is equal to or lower than the temperature (T _E ) of the combustion exhaust gas (T _S ≦ T _E ), the heat exchanger and / or the combustion exhaust gas is subjected to the second heat exchange. It is preferable to have a function of causing the exhaust gas (exhaust gas heat exchanger 35) to flow ( Motomeko 4).

  Further, (in the air conditioning system according to any one of claims 2 to 4), fuel (kerosene or other so-called “others”) is added to the combustion device (25) of the regenerator (for example, the high-temperature regenerator 2) of the absorption refrigerator (20). An on-off valve (Vn) is interposed in a fuel supply pipe (fuel supply line Lfg) for supplying “high quality fuel”), and the control device (10) connects the switching device (three-way valves V1, V3). When the on-off valve (Vn) is closed (Vn opening = 0) by switching control, the heat medium and / or combustion exhaust gas bypasses the second heat exchanger (exhaust gas heat exchanger 35). When the on-off valve (Vf) is open (Vf opening ≠ 0), the heating medium and / or the combustion exhaust gas has a function of causing the second heat exchanger (exhaust gas heat exchanger 35) to flow. (Claim 5).

Furthermore (in the air conditioning system according to any one of claims 2 to 5), the apparatus further comprises first measuring means (heat medium temperature sensor St1) for measuring the temperature (T _S ) of the heat medium, and the control device ( 10) switches and controls the switching device (three-way valves V1, V3). When the temperature of the heating medium (T _S ) is equal to or higher than a predetermined temperature (threshold) (T _S ≧ threshold), The medium and / or combustion exhaust gas bypasses the second heat exchanger (exhaust gas heat exchanger 35), and the temperature (T _S ) of the heat medium is lower than a predetermined temperature (threshold) (T _S <threshold). Value), it is preferable to have a function of causing the heat medium and / or the combustion exhaust gas to flow through the second heat exchanger (exhaust gas heat exchanger 35).

  In addition to this (in the air conditioning system according to any one of claims 2 to 6), the fuel supplied to the combustion device (25) of the regenerator (for example, the high temperature regenerator 2) of the absorption refrigerator (20). An air-fuel ratio adjustment mechanism (blower 15 or damper 17) that adjusts the ratio of air (kerosene or other so-called “high-quality fuel”) to air, and the control device (10) has a heat medium and / or combustion exhaust gas as the first. It is preferable that the air-fuel ratio adjusting mechanism (15 or 17) is controlled depending on whether the second heat exchanger (exhaust gas heat exchanger 35) is bypassed or not (claim 7).

In this case (in the air conditioning system of claim 7), the air-fuel ratio adjusting mechanism is an air supply pipe for supplying combustion air to the combustion device (25) of the regenerator (for example, the high-temperature regenerator 2) of the absorption refrigerator (20). It is comprised by the blower (15) interposed by (air supply line Lna), and the said control apparatus (10) is a 2nd heat exchanger (exhaust gas heat exchanger 35) for a heat medium and / or combustion exhaust gas. It is preferable to have a function of increasing the rotational speed of the blower (15) when flowing through the flow.
Alternatively (in the air conditioning system according to claim 7), the air-fuel ratio adjusting mechanism is an air supply pipe for supplying combustion air to the combustion device (25) of the regenerator (for example, the high temperature regenerator 2) of the absorption refrigerator (20). The air supply line Lna) is configured by a mechanism (17: for example, a damper, a throttle, etc.) that adjusts the cross-sectional area of the flow path, and the control device (10) is configured such that the heat medium and / or the combustion exhaust gas is the second heat When flowing through the exchanger (exhaust gas heat exchanger 35), it is preferable to have a function of increasing the cross-sectional area of the air supply pipe (air supply line Lna) (increasing the opening degree of the damper 17).

  In carrying out the present invention, the absorption refrigerator (20) may be a single effect type, a double effect type, a single double effect type, or a multiple effect type of triple effect or more.

The temperature (T _S ) of the heat medium is measured by the first measuring means (heat medium temperature sensor St1) described above, and the combustion of the combustion device (burner 25) is performed by the second measuring means (exhaust gas temperature sensor St2). The step (S1) of measuring the temperature (T _E ) of the exhaust gas, and the switching device (three-way) when the temperature (T _S ) of the heating medium is higher than the temperature (T _E ) of the combustion exhaust gas (T _S > T _E ) A step (S3) of controlling the valves V1 and V3) to bypass the second heat exchanger (exhaust gas heat exchanger 35) of the heat medium and / or combustion exhaust gas, and the temperature (T _S ) of the heat medium combusts. When the temperature of the exhaust gas (T _E ) or less (T _S ≦ T _E ), the switching device (three-way valves V1, V3) is controlled so that the heat medium and / or the combustion exhaust gas becomes the second heat exchanger (exhaust gas heat). And a step (S4) of causing the flow through the exchanger 35).

  Moreover, the control method of the air conditioning system of the present invention (the air conditioning system of claim 5) is provided with fuel (kerosene or other so-called “high”) in the combustion device (25) of the regenerator (for example, the high temperature regenerator 2) of the absorption refrigerator (20). The step (S11) of measuring the valve opening degree of the on-off valve (Vn) interposed in the fuel supply pipe (fuel supply line Ln) for supplying the quality fuel ") and the on-off valve (Vn) are closed ( In the case of Vn opening = 0), the switching device (three-way valves V1, V3) is controlled to bypass the second heat exchanger (exhaust gas heat exchanger 35) of the heat medium and / or combustion exhaust gas ( S13) and when the on-off valve (Vn) is open (Vn opening ≠ 0), the switching device (three-way valves V1, V3) is controlled so that the heat medium and / or the combustion exhaust gas is the second heat exchanger. A step (S14) for causing the exhaust gas heat exchanger 35 to flow. And What it is preferable.

Furthermore, the control method of the air conditioning system of the present invention (the air conditioning system of claim 6) includes a step (S21) of measuring the temperature (T _S ) of the heat medium by the first measuring means (heat medium temperature sensor St1), When the temperature (T _S ) of the medium is equal to or higher than a predetermined temperature (threshold value) (T _S ≧ threshold value), the switching device (three-way valves V1, V3) is controlled so that the heat medium and / or combustion exhaust gas is When the step (S23) of bypassing the second heat exchanger (exhaust gas heat exchanger 35) and the temperature (T _S ) of the heat medium is lower than a predetermined temperature (threshold) (T _S <threshold) A step (S24) of controlling the switching device (three-way valves V1, V3) to cause the heat medium and / or combustion exhaust gas to flow through the second heat exchanger (exhaust gas heat exchanger 35). It is preferable.

  In addition to this, the control method of the air conditioning system of the present invention (the air conditioning system of claim 7) determines whether the heat medium and / or the combustion exhaust gas bypasses the second heat exchanger (exhaust gas heat exchanger 35). Determination step (S32, S42) and fuel supplied to the combustion device (25) of the regenerator (eg, high-temperature regenerator 2) of the absorption refrigerator (20) (kerosene or other so-called “high quality fuel”) And a step (S33 and S34, S43 and S44) for controlling the air-fuel ratio adjustment mechanism (15, 17) for adjusting the ratio of air and air based on the determination result in the determination step (S32, S42). Is preferred.

In this case (in the method for controlling an air conditioning system according to claim 7), the air-fuel ratio adjusting mechanism supplies combustion air to the combustion device (25) of the regenerator (for example, the high-temperature regenerator 2) of the absorption refrigerator (20). In the step (S33, S34) of controlling the air-fuel ratio adjusting mechanism (15), the heat medium and / or the combustion exhaust gas are composed of a blower (15) interposed in the air supply pipe (air supply line Lna). When flowing through the second heat exchanger (exhaust gas heat exchanger 35), it is preferable to increase the rotational speed of the blower (S33).
Alternatively (in the method for controlling an air conditioning system according to claim 7), the air-fuel ratio adjusting mechanism supplies combustion air to the combustion device (25) of the regenerator (for example, the high temperature regenerator 2) of the absorption refrigerator (20). In the step of controlling the air-fuel ratio adjusting mechanism (17) (S43, S44), the mechanism is configured by a mechanism (for example, a damper 17, a throttle, etc.) that adjusts the cross-sectional area of the air supply pipe (air supply line Lna). When the heat medium and / or combustion exhaust gas flows through the second heat exchanger (exhaust gas heat exchanger 35), the flow passage cross-sectional area in the air supply pipe (air supply line Lna) is increased (the damper opening degree is increased). Increase: S43) is preferred.

  According to the present invention having the above-described configuration, the amount of heat held in the combustion exhaust gas of the combustion device (burner 25) of the regenerator (2) is converted into a solar heat circuit by the second heat exchanger (exhaust gas heat exchanger 35). (30) Since it is configured so as to be charged into the heat medium circulating in the interior, even when the temperature of the heat medium circulating in the solar heat circuit (30) is lowered when the air conditioning system is started, the second heat exchanger Since the amount of heat held by the combustion exhaust gas of the combustion device (burner 25) is input to the heating medium of the solar heat circuit (30) by the (exhaust gas heat exchanger 35), the temperature of the heating medium rises early, and the air conditioning system also Startup time is faster.

Here, in the absorption refrigerator (20) that is operated especially in the daytime and is stopped at nighttime, it is expected that the temperature of the heat medium is lowered to the outside temperature at the time of start-up. The temperature difference between the combustion exhaust gas temperature (T _E ) of the (burner 25) and the heating medium temperature (T _S ) is large. Therefore, even if the second heat exchanger (exhaust gas heat exchanger 35) is small, sufficient heat exchange can be performed.
Moreover, since the heat capacity of the solar heat collecting device (solar heat collecting panel 8) interposed in the solar heat circuit (30) is large and requires a large amount of heat at startup, the second heat exchanger (exhaust gas) A large amount of heat of the combustion exhaust gas from the combustion device (burner 25) flowing through the exhaust gas line (absorption refrigerator exhaust gas line Lk) via the heat exchanger 35) is input to the heat medium.
As a result, the high-quality fuel consumed in the combustion device (burner 25) circulates in the solar heat circuit (30) in addition to the regeneration of the gas-phase refrigerant (for example, water vapor) that circulates in the absorption refrigerator (20). It is also used for raising the temperature of the heat medium, and the utilization efficiency of the high quality fuel is improved.

Further, in the solar heat circuit (30), the second heat exchanger (exhaust gas heat exchanger 35) is more solar heat collecting device (solar heat collecting panel 8) than the first heat exchanger (solar heat heat exchanger 9). Since the heat medium that has been heated by the second heat exchanger (exhaust gas heat exchanger 35) has the amount of heat held by the second heat exchanger (or the upstream side), the first heat exchanger (solar heat) It will be charged into the dilute solution line (La) of the absorption refrigerator (20) via the exchanger 9).
That is, the temperature of the absorption solution circulating through the absorption refrigerator (20) is raised by the amount of heat of the combustion exhaust gas from the combustion device (burner 25), and the startup time of the absorption refrigerator (20) is shortened accordingly. .
Thereby, the high quality fuel consumed by the regenerator (high temperature regenerator 2) is further effectively used.

  In other words, according to the present invention, the start-up characteristics in the solar heat collecting device (8) and the air conditioning system are obtained by effectively using the thermal energy held in the combustion exhaust gas of the combustion device (burner 25) that has been discarded conventionally. Can be improved and energy can be saved.

  In the present invention, the heat medium flowing through the solar heat circuit (30) or the combustion exhaust gas from the combustion device (burner 25) can be configured to bypass the second heat exchanger (exhaust gas heat exchanger 35). , Claim 3), when the amount of heat held by the combustion exhaust gas of the combustion device (burner 35) cannot be input to the heat medium flowing through the solar heat circuit (30), the heat medium and / or the combustion exhaust gas is secondly added. By bypassing the heat exchanger (exhaust gas heat exchanger 35), it is possible to prevent a situation in which the amount of heat held by the heat medium flows backward to the combustion exhaust gas.

Here, when the combustion exhaust gas of the combustion device (burner 25) exchanges heat with the heat medium in the second heat exchanger (exhaust gas heat exchanger 35), the second heat exchanger (exhaust gas heat exchanger). 35) and the exhaust gas line (absorption refrigerator exhaust gas line Lk) compared to the case where the second heat exchanger (35) is bypassed due to the pressure loss in 35) and the draft reduction due to the temperature reduction of the exhaust draft. ), Exhaust gas hardly flows.
On the other hand, in the present invention, the control device (10) includes an air-fuel ratio adjusting mechanism depending on whether the heat medium and / or the combustion exhaust gas bypasses the second heat exchanger (exhaust gas heat exchanger 35). If it is configured to have a function of controlling (15, 17) (Claim 7), the air-fuel ratio adjustment mechanism (15, 17) facilitates the flow of the exhaust gas, ensures the exhaust gas flow rate, and the air-fuel ratio. Can be kept constant.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
First, a first embodiment of the present invention will be described based on FIG. 1 and FIG.

In FIG. 1, an air conditioning system using solar heat, indicated as a whole by reference numeral 100, includes an absorption refrigerator 20, a solar thermal circuit 30, and a control unit 10 that is a control means.
Here, in FIGS. 1, 3, 5, 7, 9, and 11, an arrow attached to each line indicates a flow direction of the fluid flowing through the line.

The absorption refrigerator 20 includes an absorber 1, a high temperature regenerator 2, a low temperature regenerator 3, a condenser 4, and an evaporator 5. As the absorption solution in the absorption refrigerator 20, for example, a lithium bromide (LiBr) aqueous solution is used. For example, water (H ₂ O) is used as the refrigerant.
However, the types of the absorbing solution and the refrigerant are not limited to the LiBr aqueous solution and water.

  The high temperature regenerator 2 is equipped with a combustion device (hereinafter referred to as a burner) 25 for heating the absorbing solution in the high temperature regenerator 2, and a fuel supply line Ln is connected to the burner 25, and the fuel supply line Ln High quality fuel such as kerosene is supplied to the burner 25 via The fuel supply line n is provided with an on-off valve Vn so that the supply of high quality fuel supplied to the burner 25 and the supply stop can be controlled. A combustion air supply line (air supply line) Lna is connected to a region of the fuel supply line Ln between the burner 25 and the on-off valve Vn.

The absorber 1 and the high temperature regenerator 2 are connected by a dilute solution line La interposed with an absorption solution pump Pa, and the dilute solution is pumped to the high temperature regenerator 2 by the absorption solution pump Pa. The bottom of the high temperature regenerator 2 and the low temperature regenerator 3 are connected by the first return line Lb of the absorbing solution, and the absorbing solution concentrated by regenerating the steam in the high temperature regenerator 2 is the first return line Lb. Is sent to the low temperature regenerator 3. The low temperature regenerator 3 and the absorber 1 are connected by the second return line Lc of the absorption solution, and the absorption solution further condensed by regenerating the vapor in the low temperature regenerator 3 is absorbed by the second return line Lc. It is configured to be returned to the vessel 1.
In the illustrated embodiment, the absorption refrigerator 20 is configured as a so-called “series flow type”, but may be configured as a “parallel flow type”, a “reverse flow type”, or other types.

The high-temperature regenerator 2 is connected to an absorption refrigerator exhaust gas line (exhaust gas line) Lk that exhausts exhaust gas generated when the fuel is burned by the burner 25 to the outside of the absorption refrigerator 20.
The exhaust gas line Lk has a plurality of pipes (lines) and a three-way valve. Details of the exhaust gas line Lk will be described later.

The high temperature regenerator 2 and the condenser 4 are connected by a refrigerant line Ld, and the vapor (gas phase refrigerant) regenerated by the high temperature regenerator 2 flows through the refrigerant line Ld. Here, the refrigerant line Ld communicates with the condenser 4 via the liquid phase part 32 of the low temperature regenerator 3, and administers the heat held by the gas phase refrigerant to the absorption solution stored in the low temperature regenerator 3. .
After heat is administered by the low temperature regenerator 3, the gas phase refrigerant flowing through the refrigerant line Ld is liquefied and flows into the condenser 4.

The low-temperature regenerator 3 and the condenser 4 are connected by a gas-phase refrigerant line Le, and steam (gas-phase refrigerant) regenerated by the low-temperature regenerator 3 flows through the gas-phase refrigerant line Le and flows into the condenser 4.
The condenser 4 and the evaporator 5 are connected by a liquid phase refrigerant line Lf, and the liquid phase refrigerant condensed by the condenser 4 flows into the evaporator 5 via the line Lf.
A cooling water line Lw passes through the absorber 1 and the condenser 4, and the cooling water line Lw flows through a cooling tower (not shown), the absorber 1, and the condenser 4, and is provided with a cooling water pump Pw. . And the absorption heat in the absorber 1 and the condensation heat in the condenser 4 are removed by the cooling water which flows through the cooling water line Lw.

The liquid phase refrigerant stored in the evaporator 5 is sprayed from the spray pipe 5s to the cold water line Li by a refrigerant pumping line Lg interposed with a liquid medium pump (refrigerant pump) Pg. When the refrigerant sprayed in the evaporator 5 evaporates, heat of vaporization is taken from the cold water flowing through the cold water line Li, thereby cooling the cold water flowing through the cold water line Li.
A chilled water pump (not shown) is interposed in the chilled water line Li, and the chilled water is circulated in the direction of the arrow to supply a cooling load (not shown).

  The evaporator 5 and the absorber 1 are communicated with each other by a gas-phase refrigerant line Lj in the drawing, and the gas-phase refrigerant is sent from the evaporator 5 to the absorber 1. In an actual machine, the evaporator 5 and the absorber 1 are configured to be separated by a partition wall (weir) (not shown) in the same sealed container, and the gas-phase refrigerant generated in the evaporator 5 is opened above the partition wall. It flows into the absorber 1 via the section.

A high temperature solution heat exchanger 6 is interposed in the dilute solution line La and the first return line Lb, and a low temperature solution heat exchanger 7 is interposed in the dilute solution line La and the second return line Lc. Yes.
And in the area | region between the high temperature solution heat exchanger 6 and the low temperature solution heat exchanger 7 of the dilute solution line La, the 1st heat exchanger (solar heat exchanger) 35 is interposed, and solar heat heat exchange is carried out. The amount of heat held by the heat medium flowing through the solar thermal circuit 30 is input to the dilute solution flowing through the dilute solution line La via the vessel 35.

The solar heat circuit 30 includes a heat medium line 31, a solar heat collecting device (solar heat collecting panel) 8, a first bypass line (first heat medium bypass line) 32, and a third bypass line (solar heat exchange). Device bypass line) 33.
A heat medium pump Ph is interposed in the heat medium line 31, and a second heat exchanger (exhaust gas heat exchanger) 35 is interposed on the suction side of the heat medium pump Ph in the heat medium line 31.

In the heat medium line 31, a three-way valve V1 is interposed on the inlet side of the exhaust gas heat exchanger 35 (the side on which the heat medium flows from the solar heat collecting panel 8).
In the three-way valve V <b> 1, the heat medium line 31 branches into a line interposing the exhaust gas heat exchanger 35 and a first heat medium bypass line 32 that bypasses the exhaust gas heat exchanger 35. The line interposing the exhaust gas heat exchanger 35 and the first heat medium bypass line 32 exhaust gas heat exchanger 35 merge at the junction B2.

A three-way valve V2 is interposed in a region between the junction B2 and the heat medium pump Ph in the heat medium line 31. A branch point B3 is formed in a region between the junction B2 and the three-way valve V2.
At the branch point B <b> 3, the heat medium line 31 is branched into a solar heat exchanger bypass line 33 that communicates with the solar heat exchanger 9 and a line that bypasses the solar heat exchanger 9. The solar heat exchanger bypass line 33 and the line bypassing the solar heat exchanger 9 are connected to different ports of the three-way valve V2.

A solar heat exchanger 9 is interposed in the solar heat exchanger bypass line 33.
As described above, in the solar heat exchanger 9, the amount of heat held by the heat medium heated by the solar heat collection panel 8 and flowing through the solar heat exchanger bypass line 33 flows through the dilute solution line La of the absorption refrigerator 20. Administered to absorption solution.

The exhaust gas line (absorption refrigerator exhaust gas line) Lk of the high-temperature regenerator 2 of the absorption refrigeration 20 has a line Lk1 and a line Lk2. A line Lk1 communicating with the high temperature regenerator 2 communicates with the line Lk2 via the three-way valve V3.
The line Lk2 is provided with an exhaust gas heat exchanger 35. In the exhaust gas heat exchanger 35, the amount of heat (exhaust gas of the burner 25) held by the exhaust gas flowing through the line Lk2 (exhaust gas of the burner 25 of the high-temperature regenerator 2). Heat) is applied to the heat medium flowing through the line 31 of the solar heat circuit 30.

A junction B1 is formed on the discharge side of the exhaust gas heat exchanger 35 in the line Lk2. The exhaust gas bypass line Lkb that communicates with the absorption refrigerator exhaust gas line Lk1 that communicates with the high-temperature regenerator 2 via the three-way valve V3 joins the line Lk2 that interposes the exhaust gas heat exchanger 35 at the junction B1. is doing.
By controlling the switching of the three-way valve V3, exhaust gas generated by burning high-quality fuel in the burner 25 of the high-temperature regenerator 2 can flow from the line Lk1 to the exhaust gas heat exchanger 35, or alternatively, the line Lk1 To the second bypass line (exhaust gas bypass line) Lkb.

On the other hand, by switching and controlling the three-way valve V1 interposed on the solar heat circuit 30 side, the heat medium flowing through the heat medium line 31 is caused to flow to the exhaust gas heat exchanger 35 or the heat medium bypass line 32 is caused to flow to the exhaust gas heat. The exchanger 35 can be bypassed.
Furthermore, by switching and controlling the three-way valve V2 interposed on the solar heat circuit 30 side, the heat medium flowing through the heat medium line 31 can be passed to the solar heat exchanger 9 or the solar heat exchanger 9 can be bypassed. I can do it. That is, if the temperature of the heat medium is raised to such an extent that the dilute solution flowing in the dilute solution line La on the absorption refrigerator 20 side can be heated, the three-way valve V2 is switched to the solar heat exchanger 9 to The heat medium flowing through 31 is passed through the solar heat exchanger 9. On the other hand, in order to prevent the heat from flowing back from the absorption refrigerator 20 side to the solar heat circuit 30 side unless the temperature of the heating medium is raised to such an extent that the dilute solution flowing through the dilute solution line La can be heated. The three-way valve V2 is switched to the side bypassing the solar heat exchanger 9.

On the outlet side of the solar heat collecting panel 8 in the heat medium line 31, a first measuring means (heat medium temperature sensor) St1 for measuring the outlet temperature of the solar heat collecting panel 8 of the heat medium is interposed.
Further, on the inlet side of the exhaust gas heat exchanger 35 in the exhaust gas line Lk2, there is a second measuring means (exhaust gas temperature) for measuring the exhaust gas heat exchanger 35 inlet temperature in the exhaust gas of the burner 25 of the high temperature regenerator 2. Sensor) St2 is interposed.

  The heat medium temperature sensor St1 and the exhaust gas temperature sensor St2 are connected to the control unit 10 by an input signal line Si. The three-way valves V1 and V3 are connected to the control unit 10 by a control signal line So.

With reference to FIG. 2, the control in 1st Embodiment is demonstrated.
In step S1 of FIG. 2, the heating medium temperature sensor St1, measures the heat medium temperature T _S at the outlet side of the solar heat collector panel 8, the exhaust gas temperature sensor St2, the exhaust at the inlet side of the exhaust gas heat exchanger 35 The gas temperature _TE is measured.

In the next step S2, compares the heat medium temperature T _S at the outlet side of the solar heat collector panel 8, an exhaust gas temperature T _E at the inlet side of the exhaust gas heat exchanger 35, the temperature T _S is the temperature T _E It is also determined whether the temperature is also high (whether T _S > T _E ).
For example, if the amount of solar radiation is large, the heating medium is sufficiently heated by the solar heat collecting panel 8, and the temperature T _S is higher than the temperature T _E (T _S > T _E ) (YES in step S2). The process proceeds to step S3.
On the other hand, for example, in the early hours of the morning, the amount of solar radiation is not yet large, the heating medium is not sufficiently warmed by the solar heat collection panel 8, and the temperature T _S is equal to or lower than the temperature T _E (T _S ≦ T _E ). If there is (NO in step S2), the process proceeds to step S4.

In step S3 (T _S > T _E : step S2 is YES), the control unit 10 does not need to raise the temperature of the heat medium flowing through the solar thermal circuit 30 with the exhaust gas of the burner 25 of the high-temperature regenerator 2 (in some cases Judging that the amount of heat held by the heat transfer medium may flow back into the exhaust gas. Then, the three-way valve V <b> 1 is switched and operated so that the heat medium flowing through the heat medium line 31 bypasses the exhaust gas heat exchanger 35. In addition or alternatively, the three-way valve V3 is switched and the exhaust gas from the burner 25 of the high-temperature regenerator 2 is caused to flow through the exhaust gas bypass line Lhb, thereby bypassing the exhaust gas heat exchanger 35.
By step S3, in the exhaust gas heat exchanger 35, the exhaust gas of the burner 25 of the high temperature regenerator 2 and the heat medium flowing through the solar heat circuit 30 do not exchange heat.

In step S4, it is determined that it is necessary to raise the temperature of the heat medium flowing through the solar heat circuit 30 with the exhaust gas of the burner 25 of the high temperature regenerator 2. Then, the three-way valve V1 is switched and controlled so that the heat medium flowing through the heat medium line 31 passes through the exhaust gas heat exchanger 35, and the three-way valve V3 is switched and controlled. The exhaust gas from the burner 25 is allowed to pass through the exhaust gas heat exchanger 35.
In step S4, in the exhaust gas heat exchanger 35, the amount of heat held by the exhaust gas of the burner 25 of the high-temperature regenerator 2 is input to the heat medium flowing through the solar heat circuit 30 to raise the temperature of the heat medium.

  After executing Step S3 and Step S4, the process returns to Step S1 and repeats Step S1 and subsequent steps.

  According to the air conditioning system 100 according to the first embodiment described with reference to FIGS. 1 and 2, the amount of heat held in the combustion exhaust gas of the burner 25 of the high-temperature regenerator 2 is converted by the exhaust gas heat exchanger 35 in the solar heat circuit 30. Since it can be put into the circulating heat medium, even when the temperature of the heat medium circulating in the solar heat circuit 30 is lowered when the air conditioning system 100 is started, the exhaust gas heat exchanger 35 causes the burner 25 of the high-temperature regenerator 2 to Since the amount of heat possessed by the combustion exhaust gas is input to the heating medium of the solar heat circuit 30, the heating medium temperature can be raised quickly, and the startup time of the air conditioning system is shortened.

In particular, when the air-conditioning system is started, it is expected that the heat medium temperature has dropped to about the outside air temperature. Therefore, at the time of the start, the combustion exhaust gas temperature in the burner 25 of the high-temperature regenerator 2 and the heat medium Large temperature difference from temperature. Therefore, even if the exhaust gas heat exchanger 35 is small, the heat quantity of the combustion exhaust gas from the burner 25 can be input in a large amount and sufficiently into the heat medium.
As a result, the high-quality fuel consumed by the burner 25 is used to regenerate the gas-phase refrigerant (for example, water vapor) that circulates in the absorption refrigerator 20, and in addition, the heating medium that circulates in the solar heat circuit 30 rises. Since it is also used for temperature, the utilization efficiency of the high-quality fuel is improved.

Further, in the solar heat circuit 30, the exhaust gas heat exchanger 35 is interposed on the solar heat collection panel 8 side (upstream side) with respect to the solar heat exchanger 9, so that the temperature is raised by the exhaust gas heat exchanger 35. The amount of heat held by the heating medium is input to the dilute solution line La of the absorption refrigerator 20 through the solar heat exchanger 9.
That is, the temperature of the absorption solution circulating through the absorption chiller 20 is raised by the amount of heat of the combustion exhaust gas from the burner 25, and the startup time of the absorption chiller 20 is shortened accordingly. The high-quality fuel that has been used will be used more effectively.

  In other words, according to the first embodiment of FIGS. 1 and 2, the solar heat collection panel 8 and the air conditioning system can be obtained by effectively using the combustion exhaust gas of the burner 25 of the high-temperature regenerator 2 that has been conventionally discarded. The starting characteristics at 100 can be improved and energy saving can be achieved.

Next, a second embodiment of the present invention will be described with reference to FIGS.
The entire air conditioning system according to the second embodiment is denoted by reference numeral 102 in FIG. And when the burner 25 in the high temperature regenerator 2 of the absorption refrigerator 20 is not operating, the air conditioning system 102 according to the second embodiment uses the heat medium circulating in the solar heat circuit 30 as the exhaust gas heat exchanger 35. It is configured to bypass.

The configuration of the air conditioning system 102 (FIG. 3) according to the second embodiment differs from the air conditioning system 100 (FIG. 1) according to the first embodiment in the following points.
In FIG. 3, the three-way valve V3 (three-way valve interposed in the absorption refrigerator exhaust gas line Lk), the exhaust gas bypass line Lkb, and the temperature sensors St1 and St2 provided in the air conditioning system 100 of FIG. 1 are omitted. ing. Then, although detailed in FIG. 4, in the control, the heating medium temperature T _S measured by the temperature sensor St1, and the exhaust gas temperature T _E, which is measured by the temperature sensor St2, as the parameters of the control is adopted Absent.

With reference to FIG. 4, the control in 2nd Embodiment is demonstrated.
In step S11 of FIG. 4, the opening degree of the on-off valve Vn interposed in the fuel supply line Ln is checked. Then, it is determined whether or not the on-off valve Vn is fully closed (the opening degree is 0: OFF), that is, whether or not the fuel supply to the burner 25 is interrupted (step S12).
If the on-off valve Vn is fully closed (step S12 is YES), the process proceeds to step S13, and if the on-off valve Vn is not fully closed (step S12 is NO), the process proceeds to step S14.

In step S13 (open / close valve Vn is fully closed: step S12 is YES), it is determined that the heating medium flowing through the solar heating circuit 30 cannot be heated with the combustion exhaust gas of the burner 25 because the burner 25 is not operating. Thus, the three-way valve V1 on the solar thermal circuit 30 side is switched to the bypass 32 side.
On the other hand, in step S14 (the on-off valve Vn is not fully closed: step S12 is NO), the burner 25 is operating, and it cannot be determined that the heating medium flowing through the solar heat circuit 30 with the combustion exhaust gas cannot be heated. Judge. Then, the exhaust gas heat exchanger 35 is not switched to the bypass side, and the three-way valve V1 is not immediately switched, but the switching control of the three-way valve V1 in the immediately preceding control cycle is maintained.
After executing Step S13 or Step S14, the process returns to Step S11.

  In 2nd Embodiment of FIG. 3, it does not have the structure which the combustion exhaust gas of the burner 25 bypasses the exhaust gas heat exchanger 35. FIG. When the fuel supply to the burner 25 is interrupted, the combustion exhaust gas from the burner 25 is not generated, and therefore it is not necessary to bypass the exhaust gas heat exchanger 35. In such a state, even if the heat medium flowing through the solar heat circuit 30 flows through the exhaust gas heat exchanger 35, the combustion exhaust gas of the burner 25 does not exist, so the heat of the heat medium flows backward to the combustion exhaust gas of the burner 25. There is no end to it.

  Other configurations and operational effects of the second embodiment of FIGS. 3 and 4 are the same as those of the first embodiment of FIGS.

Next, a third embodiment of the present invention will be described with reference to FIGS.
In FIG. 5, the entire air conditioning system according to the third embodiment is denoted by reference numeral 103. The air conditioning system 103 of FIG. 5, when the heat medium temperature T _S is equal to or greater than a predetermined value (threshold value), thereby bypassing against heating medium and / or absorption chiller exhaust gas heat exchanger 35 the exhaust gas It is configured as follows.
In the air conditioning system 103 in FIG. 5, the exhaust gas temperature sensor St2 is omitted as compared with the air conditioning system 100 in FIG.

With reference to FIG. 6, the control in 3rd Embodiment is demonstrated.
In step S31 in FIG. 6, the heat transfer medium temperature sensor St1, measures the heat medium temperature T _S at the outlet side of the solar heat collector panel 8. In the next step S22, the measured temperature of the heating medium T _S is equal to or a high temperature of at least the threshold value.
If the temperature T _{S of the} heat medium is higher than the threshold (YES in step S22), the process proceeds to step S23, and if the temperature T _{S of} the heat medium is lower than the threshold (NO in step S22). ) Proceed to step S24.

In step S23 (the temperature T _{S of the} heat medium is higher than the threshold: step S22 is YES), the heat medium flowing through the solar heat circuit 30 is heated to a necessary level, and the burner 25 of the high-temperature regenerator 2 is heated. It is determined that it is not necessary to heat the heat medium with combustion exhaust gas. Then, the three-way valve V <b> 1 is switched and controlled so that the heat medium flowing through the heat medium line 31 bypasses the exhaust gas heat exchanger 35. At the same time, or by switching control of the three-way valve V3, the combustion exhaust gas from the burner 25 flows to the exhaust gas bypass line Lkb so that the exhaust gas heat exchanger 35 is bypassed.

On the other hand, in step S24 (the temperature T _{S of the} heat medium is lower than the threshold value: step S22 is NO), it is determined that it is necessary to raise the temperature of the heat medium flowing through the solar heat circuit 30, and the three-way valve V1 is switched. The heat medium flowing through the heat medium line 31 is controlled to flow through the exhaust gas heat exchanger 35. At the same time, the three-way valve V3 is switched and controlled so that the combustion exhaust gas from the burner 25 passes through the exhaust gas heat exchanger 35.

After executing Step S23 and Step S24, the process returns to Step S21 and repeats Step S21 and subsequent steps.
The threshold value of the heating medium temperature T _S, at the time of startup of the air conditioning system 103, the temperature such as heating medium becomes possible introduce heat held in the absorption refrigerator 20 side is set.

  Other configurations and operational effects in the third embodiment of FIGS. 5 and 6 are the same as those of the embodiments of FIGS.

Next, a fourth embodiment of the present invention will be described with reference to FIGS.
In FIG. 7, the air conditioning system according to the fourth embodiment is denoted by reference numeral 104 as a whole. In the air conditioning system 104, a blower (air-fuel ratio adjusting mechanism) 15 is recalled in the air supply line Lna communicating with the burner 25 in the high-temperature regenerator 2 of the absorption refrigerator 20. The blower 15 supplies air to the burner 25, thereby adjusting the ratio of fuel to air supplied to the burner 25. Then, the rotational speed of the blower 15 is controlled depending on whether the heat medium and / or the exhaust gas bypasses the exhaust gas heat exchanger 35.

  In the air conditioning system 104 of FIG. 7, a blower 15 that is an air-fuel ratio adjusting mechanism is interposed in the air supply line Lna, and the blower 15 and the control unit 10 are connected via a control signal line So. In the air conditioning system 104 of FIG. 7, the temperature sensors St1 and St2 (FIG. 1) are omitted.

With reference to FIG. 8, the control in 4th Embodiment is demonstrated.
In step S31 of FIG. 8, the control unit 10 checks the connection (communication) state of each port of the three-way valve V1 and / or the three-way valve V3. Whether the three-way valve V1 is controlled to be switched to the side bypassing the exhaust gas heat exchanger 35 and / or whether the three-way valve V3 is controlled to be switched to the side bypassing the exhaust gas heat exchanger 35. Is determined (step S32).

If the three-way valve V1 and / or the three-way valve V3 is switched and controlled to bypass the exhaust gas heat exchanger 35 (YES in step S32), the rotational speed of the blower 15 is decreased (step S33), and the three-way valve V1 and If the connection (communication) state of the three-way valve V3 is in communication with the exhaust gas heat exchanger 35 (NO in step S32), the rotational speed of the blower 15 is increased (step S34).
After executing Step S33 or Step S34, the process returns to Step S31.

When the exhaust gas from the burner 25 exchanges heat with the heat medium in the exhaust gas heat exchanger 35, the pressure loss in the exhaust gas heat exchanger 35 is greater than when the combustion exhaust gas bypasses the exhaust gas heat exchanger 35. Further, the exhaust gas is difficult to flow due to a draft decrease due to a decrease in the exhaust gas temperature.
On the other hand, in the fourth embodiment, when the heat medium and / or the combustion exhaust gas flows through the exhaust gas heat exchanger 35, the rotational speed of the blower 15 is increased. Increasing the rotational speed of the blower 15 facilitates the flow of exhaust gas in the exhaust gas line Lk, and even when the heat medium and / or combustion exhaust gas flows through the exhaust gas heat exchanger 35, the exhaust gas flow rate is ensured. It becomes possible to keep the air-fuel ratio constant. In other words, the air flow rate in the exhaust gas can be maintained by increasing the rotational speed of the blower 15.
Other configurations and operational effects in the fourth embodiment of FIGS. 7 and 8 are the same as those of the embodiments of FIGS.

Next, a fifth embodiment of the present invention will be described with reference to FIGS.
In FIG. 9, the entire air conditioning system according to the fifth embodiment is denoted by reference numeral 105. The air conditioning system 105 includes a damper (air-fuel ratio adjusting mechanism) 17 in the air supply line Lna that communicates with the burner 25 in the high-temperature regenerator 2 of the absorption refrigerator 20, and the damper 17 is a burner of the high-temperature regenerator 2. The ratio of the fuel and air supplied to 25 is adjusted. In the air conditioning system 105, the opening degree (damper opening degree) of the damper 17 is controlled depending on whether the heat medium circulating in the solar heat circuit 30 and / or the combustion exhaust gas of the burner 25 bypasses the exhaust gas heat exchanger 35. is doing.

In FIG. 9, in the air conditioning system 105, a damper 17 that is an air-fuel ratio adjusting mechanism is interposed in the air supply line Lna, and the damper 17 and the control unit 10 are connected by a control signal line So.
Unlike the air conditioning system 100 (FIG. 1), in the air conditioning system 105 of FIG. 9, the temperature sensors St1 and St2 are omitted.

With reference to FIG. 10, the control in 5th Embodiment is demonstrated.
In step S41 of FIG. 10, the control unit 10 checks the connection (communication) state of each port of the three-way valve V1 and / or the three-way valve V3. Whether the three-way valve V1 is controlled to be switched to the side bypassing the exhaust gas heat exchanger 35 and / or whether the three-way valve V3 is controlled to be switched to the side bypassing the exhaust gas heat exchanger 35. Is determined (step S42).

If the three-way valve V1 and / or the three-way valve V3 is switched and controlled to bypass the exhaust gas heat exchanger 35 (YES in step S42), the opening degree of the damper 17 is decreased (step S43).
On the other hand, if the three-way valve V1 and / or the three-way valve V3 is controlled to be switched to the side where the heat medium and / or the combustion exhaust gas of the burner 25 flows to the exhaust gas heat exchanger 35 (NO in step S42), the damper 17 The opening is increased (step S44).
After executing Step S43 or Step S44, the process returns to Step S41, and Step S41 and subsequent steps are repeated again.

  9 and 10, the mechanism for increasing and decreasing the amount of air supplied to the burner 25 of the high-temperature regenerator 2 is not limited to the damper. For example, a configuration (variable throttle mechanism or the like) that changes the cross-sectional area of a line that supplies air to the burner 25 of the high-temperature regenerator 2 or various flow rate adjustment mechanisms (flow rate adjustment valves or the like) may be provided instead of the damper. Is possible.

According to the fifth embodiment, as in the fourth embodiment, when the exhaust gas becomes difficult to flow due to the pressure loss in the exhaust gas heat exchanger 35 and the draft decrease due to the decrease in the exhaust gas temperature, the damper 17 To increase the flow rate of the exhaust gas. Thereby, even when the heat medium and / or the combustion exhaust gas flows through the exhaust gas heat exchanger 35, the exhaust gas flow rate is ensured and the air-fuel ratio can be kept constant.
Other configurations and functions and effects of the fifth embodiment shown in FIGS. 9 and 10 are the same as those of the fourth embodiment shown in FIGS.

Next, a sixth embodiment of the present invention will be described with reference to FIGS.
The sixth embodiment shown in FIGS. 11 and 12 is configured by combining the first to fifth embodiments shown in FIGS.
In FIG. 11, the entire air conditioning system according to the sixth embodiment is denoted by reference numeral 106.

Next, the control in the sixth embodiment will be described mainly with reference to FIG.
In step S51 of FIG. 12, the heat medium temperature sensor St1 measures the temperature of the heating medium T _S, the exhaust gas temperature sensor St2 measures the exhaust gas temperature T _E, the opening of the on-off valve Vn which is interposed in the fuel supply line Ln Check the degree.

In the next step S52, the heating medium temperature T _S is equal to or less than the exhaust gas temperature T _E. If the heat medium temperature T _S is equal to or lower than the exhaust gas temperature T _E (T _S ≦ T _E : Step S52 is YES), the process proceeds to Step S53. On the other hand, if the heat medium temperature T _S is higher than the exhaust gas temperature T _E (T _S > T _E : Step S52 is NO), the process proceeds to Step S57.

In step S53 (T _S ≦ T _E : step S52 is YES), it is determined whether or not the on-off valve Vn of the fuel supply line Ln is not fully closed. If the on-off valve Vn of the fuel supply line Ln is not fully closed (Vn ≠ 0: YES in step S53), the process proceeds to step S54. On the other hand, if the on-off valve Vn of the fuel supply line Ln is fully closed (Vn = 0: step S53 is NO), the process proceeds to step S57.

Step S54: In (Vn ≠ 0 step S53 is YES), the control unit 10, the heat medium temperature _{T S} is equal to or lower than the threshold value. If low temperatures than the heat transfer medium temperature _{T S} is the threshold _{(T S} <Threshold: step S54 is YES), the process proceeds to step S55. On the other hand, if the heat medium temperature is higher than the threshold value (T _S ≧ threshold value: NO in step S53), the process proceeds to step S57.

In step S55 (T _S <threshold: step S54 is YES), the three-way valve V1 and / or the three-way valve V3 is communicated with the exhaust gas heat exchanger 35 side. In step S56, the rotational speed of the blower 15 is increased and the opening degree of the damper 17 is increased.

On the other hand, if T _S > T _E (step S52 is NO), Vn ≠ 0 (step S53 is YES), or T _S ≧ threshold (step S53 is NO), step S57 The three-way valve V1 and / or the three-way valve V3 are communicated with the bypass side. In step S58, the rotational speed of the blower 15 is decreased and / or the opening degree of the damper 17 is decreased.
After executing Step S56 and Step S58, the process returns to Step S51 and repeats Step S51 and subsequent steps.

  Although not clearly shown, the first to sixth embodiments of FIGS. 1 to 12 can be arbitrarily combined.

In the first to sixth embodiments of FIGS. 1 to 12, the solar heat circuit 30 is connected to the dilute solution line La of the absorption refrigerator 20 as an aspect in which the solar heat circuit 30 is in thermal communication with the absorption refrigerator 20. In the solar heat input heat exchanger 9, heat exchange is performed between the heat medium flowing in the solar heat circuit 30 and the absorption solution (dilute solution) circulating in the absorption refrigerator 20.
However, the aspect in which the solar thermal circuit 30 is in thermal communication with the absorption refrigerator 20 is not limited to that using the solar heat exchanger 9.

For example, as shown in the seventh embodiment of FIG. 13, a solar heat regenerator WE9 is provided, and the absorption solution in the solar heat regenerator WE9 is heated by the amount of heat held by the heat medium flowing through the solar heat circuit 30, and refrigerant vapor ( (Gas-phase refrigerant) may be regenerated. In FIG. 13, the solar heat regenerator WE <b> 9 is a dilute solution line Lab branched from the branch point WB in the region between the low temperature solution heat exchanger 7 and the high temperature solution heat exchanger 6 of the dilute solution line La in the absorption refrigerator 20. Communicating with
The gas-phase refrigerant regenerated by the solar heat regenerator WE9 flows into the condenser 4 via the refrigerant line LW. The absorption solution (concentrated solution) after regenerating the gas-phase refrigerant by the solar heat regenerator WE9 flows through the concentrated solution line Lcb, and a junction WG in the region between the low temperature regenerator 3 and the low temperature solution heat exchanger 7. To join the concentrated solution line Lc.
The position where the solar heat regenerator WE9 is interposed is set as appropriate according to various conditions such as the solution cycle (for example, series flow, parallel flow, reverse flow) in the absorption refrigerator 20 and the heat medium temperature of the solar heat circuit 30. It should be, and is not limited to the position shown in FIG.
Other configurations and operational effects in the seventh embodiment of FIG. 13 are the same as those of the embodiments of FIGS.

Moreover, as shown in 8th Embodiment of FIG. 14, the solar heat input heat exchanger 9 and the solar heat regenerator WE9 can also be provided. In FIG. 14, the solar heat input heat exchanger 9 is interposed in a region between the low temperature solution heat exchanger 7 and the high temperature solution heat exchanger 6 of the dilute solution line La of the absorption refrigerator 20. The solar heat regenerator WE9 communicates with the dilute solution line Lab. The dilute solution line Lab is a branch point WB in the region between the solar heat input heat exchanger 9 and the high temperature solution heat exchanger 6, and the dilute solution line La. Branch from. And the bypass line 33 branched from the branch point B3 in the heat medium line 31 of the solar heat circuit 30 passes through the solar heat regenerator WE9, the solar heat input heat exchanger 9, and then the heat medium by the three-way valve V2. It merges with the line 31.
Here, the positions of the solar heat input heat exchanger 9 and the solar heat regenerator WE9 are not limited to the configuration shown in FIG. 14, and the solution cycle (for example, series flow, parallel flow, reverse flow) in the absorption refrigerator 20 It is appropriately set according to various conditions such as the heat medium temperature of the solar heat circuit 30.
Other configurations and operational effects in the eighth embodiment of FIG. 14 are the same as those of the embodiments of FIGS.

It should be noted that the illustrated embodiment is merely an example, and is not a description to limit the technical scope of the present invention.
For example, the technique which arbitrarily combined 1st Embodiment-8th Embodiment of FIGS. 1-14 is also contained in the technical scope of this invention.

The block diagram of 1st Embodiment of this invention. The flowchart which shows the control in 1st Embodiment. The block diagram of 2nd Embodiment of this invention. The flowchart which shows the control in 2nd Embodiment. The block diagram of 3rd Embodiment of this invention. The flowchart which shows the control in 3rd Embodiment. The block diagram of 4th Embodiment of this invention. The flowchart which shows the control in 4th Embodiment. The block diagram of 5th Embodiment of this invention. The flowchart which shows the control in 5th Embodiment. The block diagram of 6th Embodiment of this invention. The flowchart which shows the control in 6th Embodiment. The block diagram of 7th Embodiment of this invention. The block diagram of 8th Embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Absorber 2 ... High temperature regenerator 3 ... Low temperature regenerator 4 ... Condenser 5 ... Evaporator 6 ... 1st heat exchanger 7 by the side of an absorption refrigerator Absorption refrigerator side second heat exchanger 8 ... solar heat collection panel 9 ... first heat exchanger / solar heat exchanger 10 ... control means / control unit 20 ... absorption refrigeration Machine 25 ... burner 30 ... solar heating circuit 31 ... heating medium line 32 ... first bypass line / heating medium bypass line 33 ... third bypass line / bypass line 35 for solar heat exchanger ... second heat exchanger / exhaust gas heat exchanger 100 ... air conditioning system La ... absorbing solution line / dilute solution line Lb ... absorbing solution first return line Lc ... absorbing solution Second return line Li ... cold water line Lkb ... second bypass line Exhaust gas bypass line Lw ... cooling water line Pa ... absorbing solution pump Pw ... cooling water pump St1 ... first measuring means / heating medium temperature sensor St2 ... second measuring means / exhaust gas Temperature sensor

Claims (7)

  An absorption refrigerator (20), a solar heat collector (8), a solar heat circuit (30) interposing the solar heat collector and in thermal communication with the absorption refrigerator (20), and absorption An exhaust gas line (Lk) for discharging the combustion exhaust gas of the combustion device (25) of the regenerator (2) of the refrigerating machine (20) to the outside of the absorption refrigerating machine, and a regenerator flowing through the exhaust gas line (Lk) A second heat exchanger (35) that inputs the amount of heat held by the flue gas of the combustion apparatus (25) of (2) into a heat medium circulating in the solar heat circuit (30), and in the solar heat circuit (30) An air conditioning system characterized in that the second heat exchanger (35) is interposed closer to the solar heat collector (8) than the first heat exchanger (9).   The solar heat circuit (30) includes a first bypass line (32) that bypasses the second heat exchanger (35), and the flow of the heat medium to the second heat exchanger (35) side and the first bypass. The air conditioning system according to claim 1, further comprising a control device (10) that is provided with a switching device (V1) for switching to any one of the line (32) sides and that controls the switching device (V1).   The exhaust gas line (Lk) includes a second bypass line (Lkb) that bypasses the second heat exchanger (35) and the flow of the combustion exhaust gas from the combustion device (25) to the second heat exchanger (35). ) Side and a switching device (V3) for switching to either the second bypass line (Lkb) side, and a control device (10) for switching control of the switching device (V3). Item 1. Air conditioning system. First measurement means (St1) for measuring the temperature (T _S ) of the heat medium, and second measurement means (St2) for measuring the temperature (T _E ) of the combustion exhaust gas of the combustion device (25), The control device (10) switches and controls the switching devices (V1, V3), and when the temperature of the heat medium (T _S ) is higher than the temperature of the combustion exhaust gas (T _E ), the heat medium and / or When the combustion exhaust gas bypasses the second heat exchanger (35) and the temperature of the heat medium (T _S ) is equal to or lower than the temperature of the combustion exhaust gas (T _E ), the heat medium and / or the combustion exhaust gas is the second heat. The air conditioning system according to any one of claims 2 and 3, wherein the air conditioning system has a function of causing the exchanger (35) to flow.   The fuel supply pipe (Ln) for supplying fuel to the combustion device (25) of the regenerator (2) of the absorption refrigerator (20) is provided with an on-off valve (Vn), and the control device (10) When the on-off valve (Vn) is closed by controlling the switching devices (V1, V3), the heat medium and / or combustion exhaust gas bypasses the second heat exchanger (35) and opens and closes. 5. The device according to claim 2, wherein when the valve (Vn) is open, the heating medium and / or the combustion exhaust gas has a function of causing the second heat exchanger (35) to flow. Term air conditioning system. A first measuring means (St1) for measuring the temperature (T _S ) of the heat medium is provided, and the control device (10) controls the switching devices (V1, V3) to control the temperature of the heat medium (T _The heating medium and / or combustion exhaust gas bypasses the second heat exchanger (35) when _S ) is equal to or higher than a predetermined temperature, and the heating medium when the temperature (T _S ) of the heating medium is lower than the predetermined temperature. The air conditioning system according to any one of claims 2 to 5, which has a function of causing the combustion exhaust gas to flow through the second heat exchanger (35).   An air-fuel ratio adjustment mechanism (15 or 17) for adjusting the ratio of fuel to air supplied to the combustion device (25) of the regenerator (2) of the absorption chiller (20) is provided, and the control device (10) includes: The air-fuel ratio adjusting mechanism (15 or 17) is controlled depending on whether the heat medium and / or the combustion exhaust gas bypasses the second heat exchanger (35). The air conditioning system according to any one of the above.

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