JPH0821671A - Absorption type refrigerator - Google Patents

Abstract

PURPOSE:To obtain cooling capacity corresponding to the cooling load of an absorption type refrigerating cycle despite the increase or decrease of the exhaust heat quantity of a water-cooled engine due to the variation in the generating load of an AC generator. CONSTITUTION:An absorption type refrigerating cycle 8 has a high-temperature regenerator 44, a low-temperature regenerator 45, a refrigerant condenser 46, a refrigerant evaporator 47 and a refrigerant absorber 48 which are operatively combined, uses exhaust gas heat of an engine 2 as the heat source of the regenerator 44, and uses the warm water exhaust heat of engine cooling water as the heat source of the regenerator 45, and comprises a refrigerant compressor 43 which is rotatably driven by the engine 2 to compress the part of the vapor refrigerant generated from the regenerator 44 and to guide it into a refrigerant latent heat recovery coil 58 in the regenerator 44. The suction quantity of the compressor 43 is varied in response to the generating load of an AC generator 3 and to the cooling load of the cycle 8, thereby generating a vapor generation quantity from dilute solution in the generator 44.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an absorption refrigerating machine which effectively uses exhaust heat of engine exhaust heat and hot water exhaust heat.

[0002]

2. Description of the Related Art Conventionally, as an absorption refrigerating machine utilizing engine exhaust heat as a heat source of a regenerator, for example, Japanese Patent Laid-Open No.
There is a technique disclosed in Japanese Patent Publication No. 239354/1993. This conventional technology uses a single-effect absorption refrigeration cycle that uses engine cooling water exhaust heat (hot water exhaust heat) as a heat source for a regenerator and exhaust gas exhaust heat of an engine as a heat source for a high temperature regenerator.
This is a combination with a heavy-effect absorption refrigeration cycle.

[0003]

However, in the prior art, when the exhaust heat amount changes due to the load change of the engine, the air conditioning capacity of the absorption refrigeration cycle also changes accordingly. That is, when the conventional technique is applied to an absorption refrigerator of a cogeneration system that uses exhaust heat of an engine that rotationally drives a generator, when the power output of the generator (engine load) increases, Since the amount of exhaust heat of is increased, the refrigeration capacity of the absorption refrigeration cycle is also increased. Conversely, the power output of the generator (engine load)
When is smaller, the amount of exhaust heat of the engine is smaller, so that the air conditioning capacity of the absorption refrigeration cycle is smaller.

Therefore, in the prior art, the power generation output of the generator and the air conditioning capacity of the absorption refrigeration cycle can be obtained only in a fixed relationship, the power generation output of the generator is small, and the air conditioning load of the absorption refrigeration cycle is small. If it is large, there is a problem that the exhaust heat of the engine is insufficient with respect to the air conditioning load. On the contrary, when the power generation output of the generator (engine load) is large and the air conditioning load of the absorption refrigeration cycle is small, there is a problem that the exhaust heat amount of the engine becomes excessive with respect to the air conditioning load. In this case, it is possible to dissipate excess energy of the air conditioning capacity of the absorption refrigeration cycle by radiating a part of the exhaust heat of the engine, but there is a problem that it is uneconomical in terms of effective use of energy. .

Further, conventionally, a cogeneration system (for example, the technique disclosed in Japanese Patent Laid-Open No. 4-251170 or the technique disclosed in Japanese Utility Model Laid-Open No. 3-129864).
It has been known. This conventional technology includes a generator driven to rotate by an engine, an absorption refrigeration cycle that uses exhaust heat of the engine as a heat source of a regenerator, and an electric refrigerant compressor that is driven by electric power generated by the generator. , A refrigerant condenser, a decompression device, and a vapor compression refrigeration cycle having a refrigerant evaporator.

When the air-conditioning capacity of the absorption refrigeration cycle is insufficient, the vapor compression refrigeration cycle is operated to increase the amount of electric power used, thereby increasing the power generation output of the generator and the resulting exhaust heat amount of the engine. This is a technology that promotes the increase of the air conditioner and improves the air conditioning capacity of the absorption refrigeration cycle. However, in this conventional technique, since a refrigerant condenser, a decompression device, a refrigerant evaporator, etc. dedicated to the vapor compression refrigeration cycle are required, the cogeneration system becomes complicated, and the number of parts and the number of assembling steps increase. This raises the problem of increasing the cost of the system.

It is an object of the present invention to provide an absorption refrigerating machine which can obtain an air conditioning capacity corresponding to the air conditioning load of an absorption refrigeration cycle regardless of the increase / decrease in the exhaust heat amount of the engine due to load fluctuation. Another object of the present invention is to provide an absorption chiller capable of obtaining an air conditioning capacity corresponding to the air conditioning load of an absorption refrigeration cycle regardless of increase / decrease in the exhaust heat amount of the engine due to fluctuations in the load of the generator. . An object of the present invention is to provide an absorption chiller capable of simplifying the system structure by eliminating the refrigerant condenser and the refrigerant evaporator dedicated to the vapor compression refrigeration cycle.

[0008]

According to a first aspect of the present invention, there is provided an engine whose exhaust heat amount increases and decreases due to load fluctuation, a refrigerant compressor which is rotationally driven by the engine, and which compresses and discharges the sucked vapor refrigerant, and an absorbing liquid. A regenerator that produces more vapor refrigerant,
First heat exchange means for exchanging heat between the exhaust heat of the engine and the absorbing liquid in the regenerator to heat the absorbing liquid, the vapor refrigerant discharged from the refrigerant compressor, and the absorbing liquid in the regenerator. Absorption type having a second heat exchange means for exchanging heat to heat the absorbing liquid, and a refrigerant flow path for guiding the vapor refrigerant in the regenerator to the second heat exchange means via the refrigerant compressor. A technical means including a refrigerating cycle and a refrigerant amount adjusting means for adjusting the flow rate of the refrigerant flowing in the refrigerant flow path based on the load of the engine or the air conditioning load of the absorption refrigerating cycle is adopted.

According to a second aspect of the present invention, an engine whose exhaust heat amount increases and decreases due to load fluctuations, a generator that is rotationally driven by this engine to generate electric power, and an electric motor that rotates when the electric power generated by this generator is supplied. A motor, a refrigerant compressor that is driven to rotate by this electric motor, and that compresses and discharges the inhaled vapor refrigerant, a regenerator that generates vapor refrigerant from an absorbing liquid, exhaust heat of the engine and an absorbing liquid in the regenerator. Heat exchanging means for exchanging heat between the refrigerant and the second heat for exchanging heat between the vapor refrigerant discharged from the refrigerant compressor and the absorbing liquid in the regenerator to heat the absorbing liquid. An absorption refrigeration cycle having an exchange means and a refrigerant flow path for guiding the vapor refrigerant in the regenerator to the second heat exchange means via the refrigerant compressor, and a load on the engine or the absorption refrigeration cycle. Air conditioning It was adopted technical means and a refrigerant amount adjusting means for adjusting the flow rate of the refrigerant flowing through the refrigerant passage based on load.

The opening amount adjusting means for adjusting the opening degree of the refrigerant passage may be used as the refrigerant amount adjusting means.
An opening / closing means for opening / closing the refrigerant flow path may be used as the refrigerant amount adjusting means. Further, as the refrigerant amount adjusting means, a variable capacity type refrigerant compressor capable of changing the flow rate of the vapor refrigerant introduced into the second heat exchange means may be used. Furthermore, as the refrigerant amount adjusting means,
A clutch that disconnects the drive connection between the engine and the refrigerant compressor may be used. Further, as the refrigerant amount adjusting means, an electricity amount adjusting means for adjusting an electricity amount supplied from the generator to the electric motor for driving the refrigerant compressor may be used.

[0011]

According to the first aspect of the invention, when the load of the engine changes due to the change of the rotation speed of the refrigerant compressor or the like, the exhaust heat amount of the engine increases or decreases. Then, the exhaust heat of the engine whose exhaust heat amount has increased / decreased is guided to the first heat exchange means in the regenerator to heat the absorbing liquid in the regenerator, so that the amount of vapor refrigerant corresponding to the exhaust heat amount of the engine is reduced. appear. At this time, since the flow rate of the refrigerant flowing in the refrigerant flow path is adjusted by the refrigerant amount adjusting means based on the load of the engine or the air conditioning load of the absorption refrigeration cycle, the vapor refrigerant discharged from the refrigerant compressor is optimal. A certain flow rate is introduced to the second heat exchange means in the regenerator. Then, by heating the absorbing liquid in the regenerator, the amount of vapor refrigerant generated from the absorbing liquid in the regenerator becomes the amount corresponding to the load of the engine or the air conditioning load of the absorption refrigeration cycle. The air conditioning capacity of the refrigeration cycle corresponds to the air conditioning load of the absorption refrigeration cycle.

According to the second aspect of the invention, when the load of the engine changes due to a change in the electric power load of the electric motor or the like or a change in the power generation output of the generator, the exhaust heat amount of the engine increases or decreases. Then, the exhaust heat of the engine whose exhaust heat amount has increased / decreased is guided to the first heat exchange means in the regenerator to heat the absorbing liquid in the regenerator, so that the amount of vapor refrigerant corresponding to the exhaust heat amount of the engine is reduced. appear. At this time, since the flow rate of the refrigerant flowing in the refrigerant flow path is adjusted by the refrigerant amount adjusting means based on the load of the engine or the air conditioning load of the absorption refrigeration cycle, the vapor refrigerant discharged from the refrigerant compressor is optimal. A certain flow rate is introduced to the second heat exchange means in the regenerator. Then, by heating the absorbing liquid in the regenerator, the amount of vapor refrigerant generated from the absorbing liquid in the regenerator becomes the amount corresponding to the load of the engine or the air conditioning load of the absorption refrigeration cycle. The air conditioning capacity of the refrigeration cycle corresponds to the air conditioning load of the absorption refrigeration cycle.

[0013]

Next, an explanation will be given based on an embodiment in which the absorption refrigerator of the present invention is incorporated in a cogeneration system.

[Structure of First Embodiment] FIGS. 1 to 3 show a first embodiment of the present invention. FIG. 1 is a diagram showing an absorption refrigerator, and FIG. 2 is a diagram showing a cogeneration system incorporating the absorption refrigerator.
The cogeneration system 1 includes a water-cooled engine 2, an AC generator 3, an absorption refrigerator 4, a control device 5, and the like.

The engine 2 is an internal combustion engine (driving means) for rotationally driving the AC generator 3 and a refrigerant compressor 43 described later.
Thus, heat is generated by burning a fuel gas such as natural gas. The engine 2 includes an intake pipe 11, a fuel pipe 12, an exhaust pipe 13, and a cooling water pipe 14. Intake pipe 11
An air cleaner 15 for cleaning the intake air is attached to the.

The fuel pipe 12 has gas cutoff valves 16 and 17 for opening and closing a fuel passage formed in the fuel pipe 12, a regulator valve 18 for adjusting the hydraulic pressure of the fuel gas in the fuel passage to an appropriate pressure, A throttle valve / mixer 19 for mixing intake air from the intake pipe 11 and fuel gas is installed. As fuel, gas fuel such as city gas, diesel oil (light oil) and liquefied petroleum gas (LPG)
You may use liquid fuels, such as.

The exhaust pipe 13 discharges engine exhaust generated during combustion of the engine 2 to the outside through a coil tube (hereinafter referred to as exhaust heat recovery coil) 20 in a high temperature regenerator 44, which will be described later. Exhaust heat recovery coil 20
Is the first heat exchange means of the present invention, which is a high temperature side solution for heating the solution by exhaust heat of exhaust gas by exchanging heat between the high temperature engine exhaust passing therethrough and the solution in the high temperature regenerator 44. It is a heating means.

The cooling water pipe 14 is a coil tube in a low temperature regenerator 45, which will be described later, by discharging the engine cooling water heated in a water jacket (not shown) of the engine 2 by a water pump (not shown). (Hereinafter referred to as hot water exhaust heat recovery coil) 21 and radiator 22 and returned to the water jacket again.

The hot water exhaust heat recovery coil 21 heat-exchanges the hot engine cooling water (hot water) passing through the inside thereof with the solution in the low temperature regenerator 45 to heat the solution by the exhaust heat of the engine cooling water. Solution heating means. Radiator 22
Is a radiator that cools the engine cooling water to an appropriate water temperature by exchanging heat between the air blown by the cooling fan 24 rotatably driven by the cooling fan motor 23 and the engine cooling water.

Next, the AC generator 3 used in this embodiment
The structure will be described with reference to FIGS. 1 and 2. The AC generator 3 is, for example, a synchronous generator that supplies power to a power load (not shown) such as a light-emitting body, a heating body, and a rotating body that consumes power and operates, and a switch is provided between the power generator and the power load. 25 are provided. The AC generator 3 is, for example, 1800r.
Power generation output (AC output) with a frequency of 60 Hz ± 2% in pm
Occurs.

Next, the detailed structure of the absorption refrigerator 4 used in this embodiment will be described with reference to FIG. The absorption chiller 4 is composed of a cooling water cycle 6, a chilled water cycle 7, a single-effect double-effect combined-use absorption refrigeration cycle 8 and the like. In this example, dilute solution (absorption liquid)
Means an aqueous solution in which the solubility of lithium bromide is about 55% by weight. The concentrated solution (absorption solution) means an aqueous solution having a solubility of lithium bromide of about 60% by weight.

The cooling water cycle 6 is constituted by an outdoor fan and an outdoor heat exchanger, and cooling water cooled by an outdoor unit (not shown) such as a cooling tower is coiled in a refrigerant absorber 48 described later. A cooling water circulation means (hereinafter referred to as a cooling coil) 31 and a coil tube (hereinafter referred to as a cooling coil) 32 in a refrigerant condenser 46 described later to return the cooling water to the outdoor unit.

The cooling coil 31 is generated when the solution is absorbed in the refrigerant absorber 48 while the solution is easily absorbed in the refrigerant absorber 48 by the low temperature cooling water passing through the inside thereof. The heat removal means removes the absorbed heat. The cooling coil 32 is a refrigerant liquefaction unit that heat-exchanges the cooling water passing through the inside with the vapor refrigerant in the refrigerant condenser 46 to condense and liquefy the refrigerant with the cooling water.

In the cold water cycle 7, used cold water warmed by an indoor unit (not shown) including an indoor fan and an indoor heat exchanger is passed through a coil tube (hereinafter referred to as a cold water coil) 33 in a refrigerant evaporator 47, which will be described later. It is a used cold water circulation means for returning to the indoor unit again. Cold water coil 33
Is a refrigerant vaporization means that heat-exchanges the cooling water passing through the inside and the atomized refrigerant in the refrigerant evaporator 47 to evaporate and vaporize the refrigerant with the use cold water. The indoor unit cools the interior of buildings such as department stores, supermarkets, and convenience stores.

The absorption refrigeration cycle 8 includes a refrigerant circuit 41,
The solution circuit 42, the refrigerant compressor 43, the high temperature regenerator 44, the low temperature regenerator 45, the refrigerant condenser 46, the refrigerant evaporator 47, the refrigerant absorber 48 and the like are included. The refrigerant circuit 41 is
A high temperature side refrigerant pipe 51, a low temperature side refrigerant pipe 54, a liquid refrigerant pipe 55, a refrigerant flow rate adjusting valve 56 and the like are provided.

The high temperature side refrigerant pipe 51 is the refrigerant flow path of the present invention, and the refrigerant compressor 43 is provided through the refrigerant flow rate adjusting valve 56.
To a suction port of the refrigerant (refrigerant flow path) 52a and a coil tube (hereinafter referred to as a refrigerant latent heat recovery coil) 57 in the low temperature regenerator 45 to a refrigerant path (refrigerant flow path) 53a.

The refrigerant path 52a is connected to the refrigerant compressor 4
Refrigerant path (refrigerant flow path) 52b from the discharge port of No. 3 to the coil tube (hereinafter referred to as refrigerant latent heat recovery coil) 58 in the high temperature regenerator 44, and the refrigerant from the refrigerant latent heat recovery coil 58 to the inlet of the refrigerant condenser 46. Path (refrigerant flow path) 52c
Connected in series. The refrigerant path 53a is connected in series to a refrigerant path (refrigerant flow path) 53b that extends from the refrigerant latent heat recovery coil 57 to the inlet of the refrigerant condenser 46. The refrigerant paths 52a to 52c form a first high temperature side refrigerant path. In addition, the refrigerant paths 53a and 53b constitute a second high temperature side refrigerant path.

The low temperature side refrigerant pipe 54 is a refrigerant supply means for connecting the outlet of the low temperature regenerator 45 and the inlet of the refrigerant condenser 46 in series. The liquid-refrigerant pipe 55 is a liquid-refrigerant supply means for connecting the outlet of the refrigerant condenser 46 and the inlet of the refrigerant evaporator 47 in series, and serves as a spraying means for spraying the liquid refrigerant into the refrigerant evaporator 47 at the tip. A nozzle 59 is provided. In addition,
A refrigerant circulation path for recirculating the liquid refrigerant that has accumulated in the lower portion without evaporating in the refrigerant evaporator 47 to the nozzle 59, and a refrigerant pump may be installed in this refrigerant circulation path.

The refrigerant flow rate adjusting valve 56, which is the refrigerant amount adjusting means and the opening / closing means of the present invention, is provided in the refrigerant path 52a of the high temperature side refrigerant pipe 51 and is a control signal (current signal or current signal output from the controller 5). The opening degree (opening degree) of the refrigerant passage 52a of the high temperature side refrigerant pipe 51 is adjusted according to an electric signal such as a voltage signal) to adjust the flow rate of the vapor refrigerant passing through the refrigerant passage 52a of the high temperature side refrigerant pipe 51. The opening degree of the refrigerant flow rate adjusting valve 56 is increased / decreased step by step by an electromagnetic actuator (not shown) as a driving unit.

The refrigerant latent heat recovery coil 57 heat-exchanges the high-temperature, high-pressure vapor refrigerant passing through the inside thereof with the solution in the low-temperature regenerator 45 to heat the solution by the latent heat of the vapor refrigerant. , Solution heating means. The refrigerant latent heat recovery coil 58 is the second heat exchanging means of the present invention, and uses the latent heat of the vapor refrigerant by exchanging heat between the high temperature and high pressure vapor refrigerant passing through the inside and the solution in the high temperature regenerator 44. A high-temperature side refrigerant condensing coil for heating the solution and a solution heating means.

The solution circuit 42 includes concentrated solution pipes 61, 62,
Dilute solution pipe 63, solution pump 64, high temperature solution heat exchanger 6
5 and a low temperature solution heat exchanger 66 and the like. The concentrated solution pipe 61 is a solution supply means that connects the outlet of the high temperature regenerator 44 and the inlet of the low temperature regenerator 45 in series via the high temperature solution heat exchanger 65.

The concentrated solution pipe 62 is a low temperature solution heat exchanger 66.
It is a solution supply means for connecting the outlet of the low temperature regenerator 45 and the inlet of the refrigerant absorber 48 in series via the. A nozzle 67 as a spraying unit for spraying the concentrated solution into the refrigerant absorber 48 is provided at the tip of the concentrated solution pipe 62.

The dilute solution pipe 63 is used for the low temperature solution heat exchanger 6.
6. Solution supply means for connecting the outlet of the refrigerant absorber 48 and the inlet of the high temperature regenerator 44 in series via the high temperature solution heat exchanger 65. The solution pump 64 is, for example, a canned motor pump, and is a solution flow generation unit that is driven to rotate by an electric motor (not shown) and generates a flow of the solution in the solution circuit 42.

The high temperature and low temperature solution heat exchangers 65 and 66 are the high temperature concentrated solution and dilute solution piping 6 which pass through the concentrated solution piping 61.
It is a solution heat exchange means for exchanging heat with a low-temperature dilute solution passing through the inside of 3 to cool the concentrated solution and heating the dilute solution. The high temperature and low temperature solution heat exchangers 65 and 66 enhance the absorption performance of the refrigerant in the refrigerant absorber 48 by cooling the concentrated solution with the diluted solution and heat the diluted solution with the concentrated solution. This enhances the heating performance of the solution in the two regenerators 44 and 45.

The refrigerant compressor 43 is a compressor which is driven to rotate by the engine 2 and compresses and discharges the vapor refrigerant sucked from the high temperature regenerator 44. The high temperature regenerator 44 is
The regenerator of the present invention is composed of an exhaust gas exhaust heat recovery coil 20 of an exhaust pipe 13 of an engine 2, a latent refrigerant heat recovery coil 58 of a refrigerant circuit 41, an atmosphere container 71 containing these recovery coils 20, 58, and the like. Has been done. The high temperature regenerator 44 heats the dilute solution flowing into the atmosphere container 71 from the dilute solution pipe 63 of the solution circuit 42 by the exhaust heat of the engine exhaust passing through the exhaust exhaust heat recovery coil 20 to generate high temperature and high pressure steam. It is a high temperature side vapor refrigerant generating means for generating a refrigerant and concentrating the dilute solution.

The low-temperature regenerator 45 is composed of the hot water exhaust heat recovery coil 21 of the cooling water pipe 14, the refrigerant latent heat recovery coil 57 of the refrigerant circuit 41, the vacuum container 72 accommodating these recovery coils 21, 57 and the like. There is. The low-temperature regenerator 45 is provided by connecting the dilute solution pipe 63 of the solution circuit 42 to the vacuum container 7
The dilute solution flowing into 2 is heated by the exhaust heat of the engine cooling water passing through the hot water exhaust heat recovery coil 21 and the latent heat of the high temperature vapor refrigerant passing through the refrigerant latent heat recovery coil 57 to cool the low temperature and low pressure vapor refrigerant. Is a vapor refrigerant generating means on the low temperature side for generating the gas and condensing the dilute solution.

The refrigerant condenser 46 is composed of the cooling coil 32 of the cooling water cycle 6, a vacuum container 73 for accommodating the cooling coil 32, and the like. This refrigerant condenser 46
Is condensed and liquefied by the cooling water passing through the cooling coil 32 to condense and liquefy the vapor refrigerant flowing from the high temperature side refrigerant pipe 51 into the vacuum container 73 and the vapor refrigerant flowing from the low temperature side refrigerant pipe 54 into the vacuum container 73. And a cooling water heating means for heating the refrigerant.

The refrigerant evaporator 47 is composed of the cold water coil 33 of the cold water cycle 7, a vacuum container 74 for housing the cold water coil 33, and the like. This refrigerant evaporator 47
Is a refrigerant vaporizer that heat-exchanges the atomized refrigerant sprayed on the cold water coil 33 from the nozzle 59 of the liquid refrigerant pipe 55 with the used cold water passing through the cold water coil 33 to evaporate the refrigerant and cool the used cold water. Means, used cold water cooling means.

The refrigerant absorber 48 is composed of the cooling coil 31 of the cooling water cycle 6 and the vacuum container 74 which accommodates the cooling coil 31 and is the same as the refrigerant evaporator 47. The refrigerant absorber 48 absorbs the vapor refrigerant generated in the refrigerant evaporator 47 into the concentrated solution sprayed on the cooling coil 31 from the nozzle 67 of the concentrated solution pipe 62.

Next, the control device 5 used in this embodiment will be described in detail with reference to FIG. The control device 5 is the control means of the present invention, and has a built-in computer that includes a CPU (arithmetic processing means), a ROM (storage means), and a RAM (storage means) inside. (Not shown), engine speed sensor 81, throttle opening sensor 82, cold water temperature sensor 83, cooling water temperature sensor 84, valve opening sensor 85, etc. based on input signals input from engine 2, indoor fan, outdoor fan,
The control devices such as the throttle valve / mixer 19, cooling fan 24, refrigerant flow rate adjusting valve 56, and solution pump 64 are controlled.

The engine speed sensor 81 is an engine load detecting means for detecting the rotational speed of the output shaft of the engine 2 that rotationally drives the refrigerant compressor 43. The throttle opening sensor 82 is an engine load detecting means that detects the opening of the throttle valve / mixer 19 (hereinafter referred to as the throttle opening). The cold water temperature sensor 83 is attached to the cold water pipe downstream of the cold water coil 33 of the cold water cycle 7, that is, the cold water pipe connecting the cold water outlet of the refrigerant evaporator 47 and the indoor unit. The cold water temperature sensor 83 is a cold water temperature detecting means for detecting the water temperature of the used cold water flowing out from the cold water coil 33 of the cold water cycle 7. In this embodiment, a thermistor or the like that detects the water temperature of the used cold water by utilizing the resistance change is used.

The cooling water temperature sensor 84 connects the cooling water piping of the cooling water piping 14 on the downstream side of the hot water exhaust heat recovery coil 21, that is, the cooling water outlet of the low temperature regenerator 45 and the cooling water inlet of the engine 2. It is attached to the cooling water pipe. This cooling water temperature sensor 84 is used for cooling the temperature of the engine cooling water discharged from the high temperature regenerator 44 (so-called engine 2
It is a cooling water temperature detecting means for detecting (return temperature to).
In this embodiment, a thermistor or the like is used which detects the cooling water temperature by utilizing the resistance change. The valve opening degree sensor 85 is a refrigerant flow rate detecting means for detecting the opening degree of the refrigerant flow rate adjusting valve 56.

FIG. 3 is a flow chart showing an example of the main control program of the control device 5. This flowchart is executed every predetermined time (for example, 2 seconds to 60 seconds) while the operation switch (not shown) is turned on.

First, the CPU detects the engine speed NE from the engine speed sensor 81, the chilled water temperature TRw from the chilled water temperature sensor 83, and the engine cooling water temperature TEw from the cooling water temperature sensor 84 to the CPU and reads them into the RAM ( Step S1). Next, the engine speed NE read in the RAM is compared with the set speed (eg, 1800 rpm) NEs stored in the ROM in advance. For example, it is determined whether the engine speed NE is higher than the set speed NEs (NE> NEs) (step S2).

If the determination result of step S2 is Yes, the throttle valve / mixer 19 is driven to the side where the throttle opening θE is closed (throttled) (step S).
3). If the result of the determination in step S2 is No, the throttle valve / mixer 19 is driven to open the throttle opening θE (step S4). Next, in order to determine whether or not the air conditioning load of the absorption refrigeration cycle 8 is large, the used cold water temperature TRw read in the RAM is compared with the set water temperature TRws stored in the ROM in advance. For example, it is determined whether the used cold water temperature TRw is higher than the set water temperature TRws (TRw> TRws) (step S5).

When the result of the determination in step S5 is Yes, that is, when the air conditioning load of the absorption refrigeration cycle 8 is large, the throttle opening θE is detected (input) from the throttle opening sensor 82 to the CPU. Read into RAM (step S6). Next, in order to determine whether the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is large, the throttle opening θE read in the RAM and the ROM are stored in advance in the ROM. The maximum throttle opening (throttle fully open) θEmax is compared. For example, the throttle opening θE is the maximum throttle opening θEma
It is determined whether or not x has been reached (θE = θEmax) (step S7).

When the result of the determination in step S7 is Yes, that is, when the load of the engine 2 (the power generation load of the AC generator 3) is large and the air conditioning load (cooling load) of the absorption refrigeration cycle 8 is large. To return. Further, when the determination result in step S7 is No, that is, the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is small and the air conditioning load of the absorption refrigeration cycle 8 (cooling). When the load is large, the refrigerant flow rate adjusting valve 56 is driven in a direction in which the opening degree of the refrigerant passage 52a of the high temperature side refrigerant pipe 51 is opened by one step (step S
8) The rotation speed NP of the solution pump 64 is increased by one step (step S9). And it returns.

If the determination result of step S5 is No, that is, if the air conditioning load of the absorption refrigeration cycle 8 is small, the valve opening degree θV of the refrigerant flow rate adjusting valve 56 is changed from the valve opening degree sensor 85. The CPU detects (inputs) and reads it into the RAM (step S10). Next, in order to determine whether or not the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is large, the valve opening degree θV of the refrigerant flow rate adjustment valve 56 read in the RAM and the The minimum valve opening degree θVmin of the refrigerant flow rate adjusting valve 56 stored in the ROM is compared. For example, it is determined whether the valve opening θV has reached the minimum valve opening θVmin (θV = θVmin) (step S11). The valve opening degree of the refrigerant flow rate adjusting valve 56 may be determined by the value of the electric current supplied to the refrigerant flow rate adjusting valve 56.

When the result of the determination in step S11 is No, that is, the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is small, and the air conditioning load of the absorption refrigeration cycle 8 is small. When the (cooling load) is small, the opening degree of the refrigerant passage 52a of the high temperature side refrigerant pipe 51 is set to 1
The refrigerant flow rate adjusting valve 56 is driven in the direction of closing by only one step (step S12), and the rotation speed NP of the solution pump 64 is reduced by one step (step S13). And
To return. Further, the determination result of step S11 is Yes.
In the case of s, that is, when the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is small and the air conditioning load (cooling load) of the absorption refrigeration cycle 8 is small, The rotation speed NP of the solution pump 64 is reduced by one step (step S14).

Next, the engine cooling water temperature TEw read in the RAM and the set water temperature TEw stored in the ROM in advance.
Compare with s. For example, it is determined whether the engine cooling water temperature TEw is higher than the set water temperature TEws (TEw> TEws) (step S15). This step S1
If the determination result of 5 is Yes, the cooling fan motor 2
3 is energized (ON, ON) (step S16). And it returns. When the result of the determination in step S15 is No, the energization of the cooling fan motor 23 is stopped (OFF, OFF) (step S17). And it returns.

Here, step S5 constitutes the air conditioning load determination means of the control device 5, steps S7 and S11 constitute the engine load determination means (generation load determination means) of the control device 5, and steps S6 and S10 control. The engine load detection means (power generation load detection means) of the device 5 is configured. Further, step S1 constitutes the cooling water temperature detecting means and the cooling water temperature detecting means of the control device 5, and steps S2, S5, S7, S1.
Reference numerals 1 and S15 respectively constitute comparison means of the control device 5.

Steps S3 and S4 constitute the throttle opening control means of the control device 5, and step S6 is the control device 5.
Of the throttle opening degree detecting means, and step S10 constitutes the valve opening degree detecting means of the refrigerant flow rate adjusting valve 56 of the control device 5. Then, steps S8 and S12 constitute the refrigerant flow rate control means of the control device 5, and steps S9, S13 and S
Reference numeral 14 constitutes a solution flow rate control means of the controller 5. Further, steps S16 and S17 constitute cooling fan control means of the control device 5.

The set water temperature of the chilled water to be used and the engine cooling water is newly provided with an input means such as a water temperature setting switch.
The set water temperature may be changed by manually operating the input means. In addition, the operating state of the engine 2 and the low temperature regenerator 45
It is possible to predict the cooling water temperature by detecting the operating state of No. 1 and calculating the detected value by the arithmetic processing means (CPU).
The engine speed may be set to a new value by newly providing input means such as a speed setting switch and manually operating the input means. Also,
Instead of the engine speed, the load of the engine 2 may be detected by detecting the exhaust temperature of the engine 2, the power generation output of the AC generator 3, and the power load.

[Operation of First Embodiment] Next, the operation of the cogeneration system 1 of this embodiment will be briefly described with reference to FIGS. 1 and 2. When the operation switch is turned on, the operation of the engine 2 is started, the AC generator 3 is rotationally driven to generate electric power, the supply of electric power to the electric power load is started, and the refrigerant compressor 43 is rotationally driven. When the refrigerant flow rate adjusting valve 56 is not yet opened, the refrigerant compressor 43 is in a no-load operation, and the load on the engine 2 is small. That is, the load of the engine 2 is the AC generator 3
When the power generation load is large and the opening of the refrigerant flow rate adjusting valve 56 is large, the maximum (throttle opening θEmax) is reached, the power generation load of the alternator 3 is small, and the opening of the refrigerant flow rate adjusting valve 56 is small. Minimum (throttle opening θ
Emin).

On the other hand, the high-temperature (for example, about 500 ° C.) engine exhaust gas generated in the engine 2 when the engine 2 starts operating passes through the exhaust pipe 13 and the exhaust heat recovery coil 20 in the high temperature regenerator 44. Be guided inside. The engine exhaust gas introduced into the exhaust gas exhaust heat recovery coil 20 is discharged to the atmosphere after heating the dilute solution in the high temperature regenerator 44 when passing through the exhaust gas exhaust heat recovery coil 20.

Further, the engine cooling water of high temperature (for example, 85 ° C. to 90 ° C.) warmed in the water jacket of the engine 2 when the engine 2 starts to operate is operated by a water pump (not shown). Low temperature regenerator 45
It is guided to the inside of the hot water exhaust heat recovery coil 21. The engine cooling water introduced into the hot water exhaust heat recovery coil 21 is
When passing through the hot water exhaust heat recovery coil 21, the low temperature regenerator 4
Heat the dilute solution in 5. And the engine cooling water is
It is cooled to a low temperature (for example, 75 ° C. to 80 ° C.), passed through the radiator 22 and returned to the inside of the water jacket to cool the engine 2 to an appropriate temperature. At this time, when the engine cooling water temperature is higher than an appropriate water temperature, the cooling fan 24 is rotated to exchange heat with the cooling air in the radiator 22 to cool the engine.

On the other hand, the dilute solution in the high temperature regenerator 44 flows in the exhaust heat of the high temperature engine exhaust flowing in the exhaust gas exhaust heat recovery coil 20 of the exhaust pipe 13 and in the refrigerant latent heat recovery coil 58 of the high temperature side refrigerant pipe 51. The latent heat of the vapor refrigerant is recovered and heated to generate high-temperature and high-pressure vapor refrigerant, which is concentrated. The concentrated high temperature concentrated solution passes through the concentrated solution pipe 61 to exchange heat with the low temperature dilute solution in the high temperature solution heat exchanger 65, and then is fed into the low temperature regenerator 45.

Then, when the refrigerant flow rate adjusting valve 56 is closed, the high temperature generated in the high temperature regenerator 44 (for example, 10
All of the 0 ° C.) vapor refrigerant is introduced into the refrigerant latent heat recovery coil 57 in the low temperature regenerator 45 through the refrigerant passage 53 a of the high temperature side refrigerant pipe 51. Further, when the refrigerant flow rate adjusting valve 56 is open, a part of the high-temperature (for example, 100 ° C.) vapor refrigerant generated in the high-temperature regenerator 44 is part of the high-temperature side refrigerant pipe 5.
It is guided into the refrigerant latent heat recovery coil 57 in the low temperature regenerator 45 through the first refrigerant path 53a. Then, the high-temperature vapor refrigerant introduced into the refrigerant latent heat recovery coil 57 heats the dilute solution in the low temperature regenerator 45 when passing through the refrigerant latent heat recovery coil 57 to remove the dilute solution from the low temperature regenerator 45. After increasing the amount of generated steam and condensing itself, it is sent to the refrigerant condenser 46 through the refrigerant path 53b.

The rest of the high temperature (for example, 100 ° C.) vapor refrigerant generated in the high temperature regenerator 44 is sucked into the refrigerant compressor 43 through the refrigerant passage 52a of the high temperature side refrigerant pipe 51 and compressed. , Even higher temperature (eg 180 ℃ ~ 2
It becomes a vapor refrigerant of 00 ° C). Then, the high temperature vapor refrigerant discharged from the discharge port of the refrigerant compressor 43 is introduced into the refrigerant latent heat recovery coil 58 in the high temperature regenerator 44 through the refrigerant path 52b of the high temperature side refrigerant pipe 51. Then, the high-temperature vapor refrigerant introduced into the refrigerant latent heat recovery coil 58 heats the dilute solution in the high temperature regenerator 44 when passing through the refrigerant latent heat recovery coil 58, so that the high temperature vapor refrigerant is removed from the dilute solution in the high temperature regenerator 44. After increasing the amount of generated steam of the refrigerant and condensing itself, the refrigerant path 53
It is sent to the refrigerant condenser 46 through c.

Further, the dilute solution in the low temperature regenerator 45 flows in the exhaust heat of the engine cooling water flowing in the hot water exhaust heat recovery coil 21 of the cooling water pipe 14 and in the refrigerant latent heat recovery coil 57 of the high temperature side refrigerant pipe 51. The latent heat of the vapor refrigerant is recovered and heated to generate a vapor refrigerant having a lower temperature and a lower pressure than the vapor refrigerant generated in the high temperature regenerator 44, and is condensed. The concentrated concentrated solution passes through the concentrated solution pipe 62 and the low temperature solution heat exchanger 6
After exchanging heat with the low temperature dilute solution in 6, it is sent to the refrigerant absorber 48. Further, the vapor refrigerant generated in the low temperature regenerator 45 is sent into the refrigerant condenser 46 through the low temperature side refrigerant pipe 54.

The vapor refrigerant and the liquid refrigerant sent into the refrigerant condenser 46 are dispersed on the cooling coil 32 in the refrigerant condenser 46 to give heat to the cooling water flowing in the cooling coil 32 of the cooling water cycle 6. Is condensed and liquefied. The liquid refrigerant liquefied in the refrigerant condenser 46 is supplied from the nozzle 59 at the tip of the liquid refrigerant pipe 55 to the cold water coil 33 in the refrigerant evaporator 47.
Heat is taken from the used cold water that is sprayed on and flows through the cold water coil 33 of the cold water cycle 7 to evaporate and evaporate, and becomes a low temperature and low pressure vapor refrigerant from the low temperature regenerator 45. Therefore, the used cold water circulating in the cold water cycle 7 is cooled by applying heat to the liquid refrigerant, and the used cold water is guided to the indoor heat exchanger of the indoor unit, and the indoor fan is operated to operate the department store, supermarket, convenience store. The interior of the building is cooled.

Then, the vapor refrigerant generated in the refrigerant evaporator 47 is introduced into the refrigerant absorber 48, and is transferred to the refrigerant absorber 48.
It is cooled by the cooling water flowing through the cooling coil 31 inside to become a liquid refrigerant, which is absorbed by the concentrated solution sprayed on the cooling coil 31 inside the refrigerant absorber 48 from the nozzle 67 of the concentrated solution pipe 62. Therefore, the concentrated solution is diluted to become a diluted solution, which temporarily accumulates in the lower portion of the refrigerant absorber 48. And
The dilute solution accumulated in the lower portion of the refrigerant absorber 48 is pumped up by the action of the solution pump 64 and introduced into the low temperature and high temperature solution heat exchangers 66 and 65 through the dilute solution pipe 63. The dilute solution introduced into the low-temperature and high-temperature solution heat exchangers 66 and 65 is heated by exchanging heat with the high-temperature concentrated solution, and is heated in the high-temperature regenerator 4.
Sent to 4. By repeating the above cycle again, the cooling operation of the absorption refrigeration cycle 8 is performed.

Here, the load of the engine 2 (AC generator 3
Power generation load, electric power load, refrigerant compressor 43 load), and the air conditioning load (cooling load) of the absorption refrigeration cycle 8
Is small, the amount of exhaust heat of the engine 2 is increased because the load of the engine 2 is large, and the heat input in the high temperature regenerator 44 and the low temperature regenerator 45 of the absorption refrigeration cycle 8 is increased. Amount of steam generated from dilute solution and low temperature regenerator 4
Since the amount of vapor generated from the dilute solution in 5 increases and the flow rate of the refrigerant increases in the absorption refrigeration cycle 8 as a whole, the air conditioning capacity (cooling capacity) against the air conditioning load of the absorption refrigeration cycle 8 is increased.
Will increase.

At this time, in this embodiment, the flow rate of the dilute solution into the high temperature regenerator 44 is reduced by reducing the opening of the refrigerant flow rate adjusting valve 56 and decelerating the rotation speed of the solution pump 64. Refrigerant path 52a of the high temperature side refrigerant pipe 51
I try to narrow down the opening. Therefore, the high temperature regenerator 4
The suction amount of the vapor refrigerant generated in the refrigerant compressor 43 into the refrigerant compressor 43 is reduced, and the discharge amount to the refrigerant latent heat recovery coil 58 in the high temperature regenerator 44 is also reduced.

Therefore, the amount of steam generated from the dilute solution in the high temperature regenerator 44 decreases, and the flow rate of the refrigerant in the absorption refrigeration cycle 8 decreases, so that the air conditioning capacity (cooling capacity) of the absorption refrigeration cycle 8 decreases. To do. Therefore, even when the load of the engine 2 is large and the amount of exhaust heat of the engine 2 is increased, it is possible to adjust the air conditioning capacity (cooling capacity) corresponding to the air conditioning load (cooling load) of the absorption refrigeration cycle 8. That is, as compared with the conventional technique of discarding excess energy with respect to the air conditioning load (cooling load) of the absorption refrigeration cycle 8,
It is possible to use energy effectively and it is excellent in economic efficiency.

On the contrary, when the load of the engine 2 (the power generation load of the AC generator 3 and the load of the refrigerant compressor 43) is small and the air conditioning load (cooling load) of the absorption refrigeration cycle 8 is large, the engine 2 Since the load on the engine 2 is small, the amount of exhaust heat of the engine 2 decreases,
The heat input in the low temperature regenerator 45 is reduced, and the absorption refrigeration cycle 8
Since the flow rate of the refrigerant is reduced as a whole, the air conditioning capacity (cooling capacity) is insufficient with respect to the air conditioning load of the absorption refrigeration cycle 8.

Therefore, in this embodiment, by opening the refrigerant flow rate adjusting valve 56 and increasing the rotation speed of the solution pump 64, the flow rate of the dilute solution into the high temperature regenerator 44 is increased and the high temperature side Since the opening of the refrigerant passage 52a of the refrigerant pipe 51 is opened, the amount of the vapor refrigerant generated in the high temperature regenerator 44 sucked into the refrigerant compressor 43 increases, and the high temperature regenerator 44 is increased.
The amount of discharge to the latent heat recovery coil 58 of the refrigerant also increases.

Therefore, as described above, the refrigerant compressor 43
In comparison with a case where the discharge capacity of the absorption refrigeration cycle is suppressed, the amount of vapor generated from the dilute solution in the high temperature regenerator 44 increases, and the flow rate of the refrigerant increases in the absorption refrigeration cycle 8 as a whole. Capacity (cooling capacity) increases. At this time, in the engine 2, the amount of decrease in the power generation load of the AC generator 3 becomes the load that drives the refrigerant compressor 43, so the total load is substantially constant, and the amount of exhaust heat decreases due to the small power generation load. There is no such thing.

Next, the load of the engine 2 (the power generation load of the AC generator 3, the power load, the load of the refrigerant compressor 43) is small, and the air conditioning load (cooling load) of the absorption refrigeration cycle 8 is set.
Is small, the load of the engine 2 that rotationally drives the AC generator 3 is reduced, so that the exhaust heat amount of the engine 2 is reduced. Therefore, as described above, the heat input to the high temperature regenerator 44 and the low temperature regenerator 45 of the absorption refrigeration cycle 8 is reduced, so that the air conditioning capacity (cooling capacity) of the absorption refrigeration cycle 8 is reduced.
Is reduced.

In this case, since the refrigerant temperature and the amount of heat of the vapor refrigerant generated in the high temperature regenerator 44 decrease, the solution temperature of the dilute solution in the low temperature regenerator 45 also decreases, so the hot water exhaust heat recovery coil 21 Since the engine cooling water passing therethrough may be overcooled, the rotation speed of the solution pump 64 is reduced to reduce the circulation amount of the dilute solution circulating in the high temperature regenerator 44 and the low temperature regenerator 45. As a result, the high temperature regenerator 4
Since the refrigerant temperature of the vapor refrigerant generated in 4 rises and the solution temperature of the dilute solution in the low temperature regenerator 45 rises, the engine 2
The return temperature of the engine cooling water to is also increased. Therefore, it is possible to prevent the deterioration of the operating efficiency and the supercooling of the engine cooling water. When the air conditioning load (cooling load) of the absorption refrigeration cycle 8 further decreases, the heat of the engine cooling water is radiated by the radiator 22 to reduce the heat input to the absorption refrigeration cycle 8.

Further, the load of the engine 2 (the power generation load of the AC generator 3, the power load, the load of the refrigerant compressor 43) is large and the air conditioning load (cooling load) of the absorption refrigeration cycle 8 is large.
Is large, the amount of exhaust heat of the engine 2 increases and the heat input to the high temperature regenerator 44 and the low temperature regenerator 45 of the absorption refrigeration cycle 8 increases, so the air conditioning capacity (cooling capacity) of the absorption refrigeration cycle 8 is increased. Will increase. Therefore, the refrigerant flow rate adjusting valve 5
6 is closed and the refrigerant compressor 43 is operated without load, all the shaft power of the engine 2 is used for power generation (the power output of the AC generator 3 is 100%), and the air conditioning in the room is performed by the engine 2.
The absorption refrigeration cycle 8 is operated only with the exhaust heat of exhaust gas and the exhaust heat of hot water.

[Effects of First Embodiment] As described above, in the cogeneration system 1 of this embodiment, particularly the absorption refrigerator 4, the load of the refrigerant compressor 43 relative to the power generation load of the AC generator 3 is applied. By changing the opening degree of the refrigerant flow rate adjusting valve 56, the power generation output of the AC generator 3 and the air conditioning capacity of the absorption refrigeration cycle 8 can be adjusted.
Moreover, the absorption type refrigeration cycle 8 can be adjusted to have an air conditioning capacity corresponding to the air conditioning load of the absorption type refrigeration cycle 8 regardless of the power generation output of the AC generator 3.

That is, a conventional example (JP-A-1-23935).
4), the air conditioning capacity of the absorption refrigeration cycle 8 increases as the power output of the generator increases from 0% to 100%, as shown in the graph of FIG. It was a thing. However, in this embodiment, as shown in the graph of FIG. 4, the power output of the AC generator 3 is 0% to 1%.
The opening degree of the refrigerant flow rate adjusting valve 56 is reduced as it increases to 00% to obtain the air conditioning capacity of the absorption refrigeration cycle 8.

Further, when the power output of the AC generator 3 is 0%, the refrigerant flow rate adjusting valve 56 is fully opened to absorb the amount of latent heat recovered from the refrigerant latent heat recovery coil 58 in the high temperature regenerator 44. The air conditioning capacity of the cycle 8 is increasing, and even when the power generation output of the AC generator 3 is 100%, it has the same capacity as the air conditioning capacity of the conventional absorption refrigeration cycle. Therefore, in this embodiment, it is understood that the air conditioning capacity of the absorption refrigeration cycle 8 is significantly improved regardless of the load variation of the engine 2 in comparison with the conventional example.

Further, this embodiment does not require a refrigerant condenser, a decompression device, and a refrigerant evaporator dedicated to the vapor compression refrigeration cycle as compared with the conventional technique in which the absorption refrigeration cycle and the vapor compression refrigeration cycle are combined. Therefore, the structure of the cogeneration system 1 can be greatly simplified. Therefore, the cogeneration system 1
The number of parts of refrigeration equipment in
Since the overall assembling workability is significantly improved, the cost of the cogeneration system 1 can be reduced.

[Second Embodiment] FIG. 5 shows a second embodiment of the present invention, and is a view showing the main part of a cogeneration system incorporating an absorption refrigerator. In this embodiment, the electric power generated by the AC generator 3 is supplied to the AC motor (electric motor) 49 via the energization control circuit 26, whereby the refrigerant compressor 43 of the absorption refrigeration cycle 8 is supplied.
Is driven to rotate.

[Modification] In this embodiment, the present invention is applied to the absorption refrigerator 4 having a single-effect, double-effect absorption refrigeration cycle. However, a single-effect absorption refrigeration cycle, double-effect or more multiplex The present invention may be applied to an absorption refrigerator having an effect absorption refrigeration cycle. The hot water exhaust heat recovery coil 21 in the low temperature regenerator 45 may be used as the first heat exchange means, and the second heat exchange means may be provided in the low temperature regenerator 45. In this case, the vapor refrigerant generated in the low temperature regenerator 45 is sucked into the refrigerant compressor 43, compressed, and guided to the second heat exchange means.

In this example, an aqueous solution having a solubility of lithium bromide of about 55% by weight was used as the dilute solution, and an aqueous solution having a solubility of lithium bromide of about 60% by weight was used as the concentrated solution. The solubility of the absorbent may be freely changed. In addition to the lithium bromide aqueous solution as the absorbing liquid, lithium iodide aqueous solution, lithium chloride aqueous solution,
Aqueous ammonia solution may be used. In the case of an aqueous ammonia solution, the absorbent is water and the refrigerant is ammonia.

As a water temperature sensor for detecting the temperature of cold water or the temperature of engine cooling water, a thermocouple temperature sensor, a thermistor, a thermal noise temperature sensor, an NQR temperature sensor, a crystal temperature sensor, a transistor temperature sensor, a radiation thermometer, a thermal image. You may use an infrared camera etc. which take. Further, the water temperature sensor may be installed by putting it in the cooling water pipe, by contacting it with the outer surface of the cooling water pipe, or by mounting it separately from the cooling water pipe. Further, the temperature of the cold water may be predicted from the evaporation temperature and the evaporation pressure of the vapor refrigerant generated in the evaporator.

As the refrigerant amount adjusting means, a physical quantity relating to the engine load or the temperature of the cold water (for example, the amount of electricity such as current value, voltage value or power value or temperature or pressure of the temperature sensitive medium).
A flow rate adjusting valve such as a temperature actuated or electromagnetic variable throttle valve whose opening changes according to the above may be used. As the flow rate adjusting valve, an electric flow rate adjusting valve, an electrohydraulic type flow rate adjusting valve, an electric air type flow rate adjusting valve, an electric steam type flow rate adjusting valve, a hydraulic type flow rate adjusting valve, an air type flow rate adjusting valve, an air hydraulic type flow rate adjusting valve. A regulating valve, a diaphragm type flow regulating valve, a cylinder type flow regulating valve, or a lever type flow regulating valve may be used.

Instead of this synchronous generator, another generator such as an induction generator or a direct current generator may be used. Further, as the rotating body that is rotationally driven by the engine 2, a driven unit such as an air compressor, a pump, or a blower may be used instead of the generator. Further, a mechanism for converting the rotational motion of the output shaft into a reciprocating motion may be attached to the output shaft of the engine 2 so that the engine 2 drives a driven unit such as a reciprocating machine. The present invention may be used in an absorption refrigeration cycle in which engine exhaust water is heat-recovered in engine cooling water (hot water) to heat the solution in the regenerator. Further, the solution circuit 42 is not limited to the series flow shown in FIG.
It may be a parallel flow. Further, the control of the engine 2 does not have to be the constant rotation speed control.

[0082]

According to the invention of claim 1 and the invention of claim 2, when the load of the engine is small and the air conditioning load of the absorption refrigeration cycle is large, even if the exhaust heat amount of the engine is insufficient with respect to the air conditioning load. By adjusting the flow rate of the refrigerant by the refrigerant flow rate adjusting means to increase the amount of steam generated in the regenerator, the air conditioning capacity of the absorption refrigeration cycle can be increased. In addition, when the engine load is large and the air conditioning load of the absorption refrigeration cycle is small, even if the engine exhaust heat amount is excessive with respect to the air conditioning load, the refrigerant flow rate adjusting means adjusts the refrigerant flow rate to reproduce. By reducing the amount of steam generated in the unit, the air conditioning capacity of the absorption refrigeration cycle can be reduced. Therefore, it is possible to obtain the air conditioning capacity corresponding to the air conditioning load of the absorption refrigeration cycle regardless of the increase / decrease in the exhaust heat amount of the engine due to the load change.

The invention of claim 1 and the invention of claim 2 are
By simply adding a refrigerant compressor to the absorption refrigeration cycle, it is possible to obtain the same air conditioning capacity as that of the absorption refrigeration machine that combines the absorption refrigeration cycle and the vapor compression refrigeration cycle. In addition, the refrigerant condenser and refrigerant evaporator for the vapor compression refrigeration cycle can be eliminated to simplify the system structure, reducing the number of parts and improving the workability of assembly of the absorption refrigerator. Therefore, the cost of the system can be reduced.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing an absorption refrigerator according to a first embodiment of the present invention.

FIG. 2 is a schematic diagram showing a cogeneration system incorporating the first embodiment of the present invention.

FIG. 3 is a flow chart showing an example of the operation of the control device of the first embodiment of the present invention.

FIG. 4 is a graph showing the relationship between the air conditioning capacity of the absorption refrigeration cycle and the power generation output of the generator.

FIG. 5 is a schematic diagram showing a main part of a cogeneration system incorporating a second embodiment of the present invention.

[Explanation of symbols]

 1 Cogeneration System 2 Engine 3 Alternator (Generator) 4 Absorption Refrigerator 8 Absorption Refrigeration Cycle 20 Exhaust Heat Recovery Coil (First Heat Exchange Means) 43 Refrigerant Compressor 44 High Temperature Regenerator (Regenerator) 49 AC motor (electric motor) 51 High temperature side refrigerant pipe (refrigerant flow path) 56 Refrigerant flow rate adjusting valve (refrigerant amount adjusting means) 58 Refrigerant latent heat recovery coil (second heat exchanging means)

Claims (4)

[Claims] Claims: (a) An engine in which the amount of exhaust heat increases and decreases due to load fluctuations; (b) a refrigerant compressor that is rotationally driven by this engine to compress and discharge the inhaled vapor refrigerant; and vapor refrigerant is generated from an absorbing liquid. A regenerator, first heat exchange means for exchanging heat between the exhaust heat of the engine and the absorbing liquid in the regenerator to heat the absorbing liquid, the vapor refrigerant discharged from the refrigerant compressor and the regenerator Second heat exchanging means for exchanging heat with the absorbing liquid to heat the absorbing liquid, and a refrigerant flow path for guiding the vapor refrigerant in the regenerator to the second heat exchanging means via the refrigerant compressor. An absorption type refrigeration cycle having: (c) a refrigerant amount adjusting means for adjusting the flow rate of the refrigerant flowing in the refrigerant flow path based on the load of the engine or the air conditioning load of the absorption type refrigeration cycle. refrigerator. 2. An engine in which the amount of exhaust heat increases or decreases due to load fluctuations, (b) a generator that is rotationally driven by this engine to generate electric power, and (c) is supplied with the electric power generated by this generator. And (d) a refrigerant compressor that is rotationally driven by this electric motor to compress and discharge the inhaled vapor refrigerant, a regenerator that generates vapor refrigerant from an absorbing liquid, the exhaust heat of the engine and the First heat exchange means for exchanging heat with the absorbing liquid in the regenerator to heat the absorbing liquid, and absorbing heat by exchanging heat between the vapor refrigerant discharged from the refrigerant compressor and the absorbing liquid in the regenerator. A second heat exchange means for heating the refrigerant, and an absorption type refrigeration cycle having a refrigerant flow path for guiding the vapor refrigerant in the regenerator to the second heat exchange means via the refrigerant compressor, (e) The engine load or the absorption formula Absorption refrigerating machine provided with a refrigerant amount adjusting means for adjusting the flow rate of the refrigerant flowing through the refrigerant passage based on the air conditioning load of the freezing cycle. 3. An absorption refrigerating machine, wherein the refrigerant amount adjusting means is an opening adjusting means for adjusting the opening of the refrigerant passage. 4. The absorption refrigerator according to claim 1 or 2, wherein the refrigerant amount adjusting means is an opening / closing means for opening / closing the refrigerant flow path.