JP2006010301A - Cold heat generation system and cold heat generation method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cold heat generation system having a high energy efficiency and capable of operating at a low cost and having a size equivalent to that of a conventional one, and a cold heat generation method for generating cold heat using the cold heat generation system To do.
SOLUTION: A compressor 7, a steam generator 2, an evaporator 3, a condenser 5, and an auxiliary compression mechanism (ejector 4 or the like) are provided, and refrigerant gas discharged from the evaporator 3 is discharged by the compressor 7. A cold heat generation system 1 that pressurizes and pressurizes the pressurized refrigerant gas by an auxiliary compression mechanism that is driven by the refrigerant gas generated from the steam generator 2, and the compressor 7 is used to generate exhaust heat. The steam generator 2 is driven by the exhaust heat generated by the power source (gas engine 30) and generated by the power source.
[Selection] Figure 1

Description

  The present invention relates to a cold energy generation system and a cold energy generation method, and particularly to a cold energy generation system capable of realizing energy saving and generating cold energy at a low cost, and cold energy generation using the cold energy generation system to generate cold energy. Regarding the method.

  FIG. 5 is a block diagram showing a cold heat generation system using a conventional gas engine. The cold heat generation system 40 shown in FIG. 5 is generally called a gas heat pump (gas heat pump).

  The cold heat generation system 40 shown in FIG. 5 first compresses a refrigerant gas such as alternative chlorofluorocarbon by a compressor 41 so as to reach a high temperature and a high pressure. The compressor 41 is driven using the power of the gas engine 42. When the compressor 41 is a rotary type, the shaft power of the gas engine 42 may be used.

First, the refrigerant gas compressed by the compressor 41 is sent to the condenser 43, cooled by cooling water, and liquefied to become a condensate refrigerant. The condensate refrigerant transferred to the expansion valve 44 is decompressed by the expansion valve 44. Thereafter, the decompressed condensate refrigerant is sent to the evaporator 45 and vaporized in the evaporator 45 to become refrigerant gas. Here, since the heat of vaporization is lost when the condensate refrigerant becomes the refrigerant gas, the evaporator 45 is cooled. The cold load is cooled by passing the cold load through the evaporator 45 through a pipe or the like.
The refrigerant gas generated in the evaporator 45 is sent again to the compressor 41 and compressed. By repeating such a cycle, cold heat is continuously generated.

  FIG. 6 is a configuration diagram showing a conventional steam injection refrigeration apparatus (cold heat generation system) (see, for example, Patent Document 1). In the cold heat generation system shown in FIG. 6, both an ejector 52 and a compressor 54 are provided.

The operation of the cold heat generation system shown in FIG. 6 will be described. The refrigerant flowing through the entire cold heat generation system 50 is first heated by hot water or the like by the steam generator 51 to become primary steam (driving steam) and is sent to the ejector 52. In the ejector 52, the refrigerant gas (secondary steam) vaporized by the evaporator 53 and compressed by the compressor 54 is sucked and mixed by injection from the nozzle of the primary steam. At this time, the temperature of the evaporator 53 is lowered by the heat of vaporization of the refrigerant gas, and the cooling load such as water flowing in the evaporator 53 is cooled. In the ejector 52, the mixed gas is pressurized and becomes a condensed liquid refrigerant by the cooling water of the condenser 55, and a part of the condensed liquid refrigerant is sent to the steam generator 51 by the liquid return pump 56. The remaining condensate refrigerant is decompressed by the expansion valve 57 to a state necessary for generating cold heat and sent to the evaporator 53. By repeating such a cycle, cold heat is generated.
JP-A-57-134667 (FIGS. 5 and 7)

  In a conventional cold heat generation system (gas heat pump) using a gas engine, the compressor 41 is driven using the power of the gas engine 42, and exhaust heat is generated from the gas engine 42. However, since this waste heat is generally discarded except for heating during winter, there is a problem that energy efficiency is not so good. Further, it is possible to drive a heat-driven cold heat generation system such as an absorption refrigeration machine using the exhaust heat from the gas engine 42. However, when a heat-driven cold heat generation system is combined with a gas heat pump, the cold heat generation system is 2 Problems arise such as a large installation area, high initial costs, and a heavy maintenance burden.

  Further, in a conventional steam injection refrigeration apparatus (cold heat generation system) (see, for example, Patent Document 1), an ejector 52 and a compressor 54 are used to provide necessary cooling capacity. However, since the liquid return pump 56 is used to return the condensate refrigerant to the steam generator 51, power for driving the liquid return pump 56 is required, and a coefficient of performance (COP) representing the efficiency of the cold heat generation system. There has been a problem of lowering. In particular, although the pressure of the refrigerant is increasing recently for the purpose of improving the coefficient of performance, the pressure difference between the steam generator 51 and the condenser 55 increases due to the increase in the pressure of the refrigerant, so that the power for driving the liquid return pump 56 is increased. I had to make it bigger.

  The present invention provides a cold energy generation system having high energy efficiency, capable of operating at low cost, and having a size equivalent to a conventional one, and a cold energy generation method for generating cold energy using the cold energy generation system. The purpose is to provide.

The cold heat generation system according to the present invention includes a compressor, a steam generator, an evaporator, a condenser, and an auxiliary compression mechanism, and pressurizes the refrigerant gas emitted from the evaporator with the compressor. A cold heat generation system that pressurizes the generated refrigerant gas by an auxiliary compression mechanism driven by the refrigerant gas generated from the steam generator, wherein the compressor is driven by a power source that generates exhaust heat and is generated by the power source The steam generator is heated by the exhausted heat.
The compressor is driven by a power source that generates exhaust heat, the steam generator is heated by the exhaust heat generated by the power source to generate refrigerant gas, and the auxiliary compression mechanism (ejector or the like) is driven by this refrigerant gas. . For this reason, exhaust heat can be used effectively, energy efficiency can be improved, and cold heat can be generated at low cost. If this cold heat generation system is configured with one system, the cold heat generation capacity can be increased with the same size as a conventional gas heat pump.

In the cold heat generation system according to the present invention, the power source is a gas engine.
By driving the compressor with, for example, a dedicated gas engine, the driving power of the compressor and the amount of exhaust heat for heating the steam generator can be stably supplied at a constant ratio. It is possible to design at an efficient point, and it is possible to operate the cold heat generation system at a lower cost.
In addition, when the cold energy demand is below the rating, the gas engine is operated at a partial load, but generally the efficiency at the partial load operation is lower than that at the rated operation. Therefore, in the conventional gas heat pump system, the efficiency as a cold heat generation system will also fall. A decrease in efficiency means a higher rate of exhaust heat. Since the exhaust heat is effectively used in the cold heat generation system according to the present invention, it is possible to reduce a decrease in efficiency as the cold heat generation system.

In the cold heat generation system according to the present invention, the auxiliary compression mechanism is an ejector.
By configuring the auxiliary compression mechanism with an ejector, a highly energy efficient cold heat generation system can be obtained.

Further, in the cold heat generation system according to the present invention, the pressure ratio of the ejector is in a range of 1.0 to 1.1.
By designing the ejector pressure ratio in the range of 1.0 to 1.1, it is possible to effectively utilize the exhaust heat of the gas engine and dramatically improve the efficiency of the cold heat generation system according to the present invention. Become.

In the cold heat generation system according to the present invention, the auxiliary compression mechanism includes an expander driven by refrigerant gas generated from a steam generator and an auxiliary compressor driven by power generated by the expander. It is.
By configuring the auxiliary compression mechanism from an expander and an auxiliary compressor, it is possible to obtain a cold energy generation system with high energy efficiency.

Further, the cold heat generation system according to the present invention includes a liquid receiver to which a part of the condensate refrigerant stored in the condenser is transferred, and transfers the condensate refrigerant from the liquid receiver to the steam generator. A dump trap system is adopted.
When the condensate refrigerant is returned to the steam generator, the use of the dump trap system eliminates the need for the liquid return pump and reduces the power of the liquid return pump. In this dump trap system, the receiver is pressurized by sending steam from the steam generator or warm water for heating the steam generator to the receiver, and the steam is sent from the receiver. The condensate refrigerant is returned to the generator.

In addition, the cold heat generation system according to the present invention includes a second expander that depressurizes the condensate refrigerant and transfers it from the condenser to the evaporator, and a liquid return pump that transfers the condensate refrigerant from the condenser to the steam generator. The liquid return pump is driven by the power generated by the second expander.
Since the second expander and the liquid return pump are provided and the liquid return pump is driven by the power generated by the second expander, power is not wasted and a highly energy efficient cold heat generation system can be obtained.

In the cold heat generation system according to the present invention, the refrigerant flowing through the steam generator and the refrigerant flowing through the evaporator and the compressor are made of the same substance.
If the refrigerant | coolant which flows through a steam generator, an evaporator, and a compressor is made into the same substance, these can be comprised using the same piping system, and the size of a cold-heat generation system can be made small. Moreover, since the same substance is used as the refrigerant, it is not necessary to provide a refrigerant separator in the cold heat generation system, and the cold heat generation system can be configured simply.

The cold heat generation method according to the present invention generates cold heat by any one of the cold heat generation systems described above.
Since cold energy is generated by any one of the above-described cold energy generation systems, energy efficiency is high and cold energy can be generated at low cost.

Embodiment 1. FIG.
FIG. 1 is a configuration diagram illustrating a cold heat generation system according to Embodiment 1 of the present invention. A cold heat generation system 1 shown in FIG. 1 includes an ejector 4 as an auxiliary compression mechanism and a compressor 7, and employs a dump trap system as a liquid return method. In FIG. 1, the portion of the auxiliary compression mechanism is indicated by a dotted line.

  As shown in FIG. 1, the cold heat generation system 1 according to the first embodiment includes a steam generator 2, an evaporator 3, an ejector 4, a condenser 5, an expansion valve 6, and a compressor 7. The condenser 5 is connected to a liquid receiver 8 through a liquid return pipe 11, and a valve 12 is provided in the liquid return pipe 11. Further, a valve 15 is provided in a pipe connecting the steam generator 2 and the liquid receiver 8, and a valve 20 is provided in a pipe connecting the steam generator 2 and the ejector 4. In addition, a receiver 8 is connected to a refrigerant gas pipe 16 connecting the condenser 5 and the steam generator 2 by a branch pipe 17, and the refrigerant gas pipe 16 is connected to both sides of a connection portion of the refrigerant gas pipe 16 and the branch pipe 17. Valves 18 and 19 are provided. Here, the condenser 5, the liquid receiver 8, and the steam generator 2 have a positional relationship in the height direction (vertical direction). The liquid receiver 8 and the steam generator 2 are arranged in this order. In addition, an electromagnetic valve etc. can be used for said valve | bulb 12, valve | bulb 15, valve | bulb 18, valve | bulb 19, and valve | bulb 20. FIG.

The compressor 7 is driven by transmitting the power of the gas engine 30 via the power transmission means 31. When the compressor 41 is a rotary type, the shaft power of the gas engine 30 may be used. Instead of the gas engine 30, another power source that generates exhaust heat may be used. Further, instead of driving the compressor 7 with the shaft power of the gas engine 30, the generator 7 may be rotated to generate power, and the compressor 7 may be driven by an electric motor that is rotated by the generated power. In this case, as the electric power for driving the electric motor, in addition to the electric power generated by the generator, other electric power (for example, purchased electric power from an electric power company) may be added.
The steam generator 2 is heated to generate steam when exhaust heat from the gas engine 30 is sent through the exhaust heat pipe 32. In addition, when sending exhaust heat from the gas engine 30 to the steam generator 2, exhaust gas may be sent directly or warm water or the like may be sent.

  The operation of the cold heat generation system 1 using the ejector 4 and the compressor 7 shown in FIG. 1 will be described. The refrigerant flowing through the whole of the cold heat generation system 1 is first heated by the steam generator 2 by exhaust heat such as exhaust heat gas or hot water from the gas engine 30 to become primary steam (driving steam). In addition, when heating the refrigerant by the steam generator 2, a plate-type heat exchanger that flows exhaust heat to a multi-layer flat plate, even if a shell-and-tube heat exchanger that flows exhaust heat inside a pipe or the like is used. May be used. Further, a plate heat exchanger may be installed outside the steam generator 2 and configured as a so-called boiler.

  The pressure of the steam generator 2 is higher than the pressure of the condenser 5, and the primary steam is guided to the ejector 4. In the ejector 4, the refrigerant gas (secondary steam) generated in the evaporator 3 and pressurized by the compressor 7 is sucked and mixed by injection of the primary steam from the nozzle 21. At this time, the temperature of the evaporator 3 is lowered by the heat of vaporization of the refrigerant gas, and the cooling load such as water flowing in the evaporator 3 is cooled. In addition, the cooling of the cooling load in the evaporator 3 can also utilize a shell and tube type heat exchanger or a plate type heat exchanger (including a boiler type). In the ejector 4, the mixed gas is pressurized and becomes a condensed liquid refrigerant by the cooling water of the condenser 5, and a part of the condensed liquid refrigerant is stored in the liquid receiver 8. The remainder of the condensate refrigerant is decompressed by the expansion valve 6 to a state necessary for generating cold heat, and again evaporated by the evaporator 3 to generate cold heat.

  In the first embodiment, the driving force of the compressor 7 and the driving heat of the ejector 4 are the shaft power and exhaust heat from the gas engine 30, respectively, but the ratio is roughly determined from the efficiency (shaft power) of the gas engine 30. Value. For example, if the efficiency of the gas engine 30 is 33%, the remaining 67% is exhaust heat. It is impossible to effectively use the total amount of exhaust heat, and assuming that half of the total exhaust heat amount can be recovered, the ratio between the shaft power and the recovered exhaust heat amount is about 1: 1.

The ratio ms / mp between the primary steam mass flow rate mp and the secondary steam mass ms in the ejector 4 is a function of the pressure ratio of the ejector 4 (= ejector outlet pressure / secondary steam pressure). / Mp has a small characteristic.
The pressure ratio of the ejector 4 can be designed arbitrarily. As the pressure ratio of the ejector 4 is increased, the pressure increase range of the compressor 7 is reduced, so that the required power of the compressor 7 is reduced and the fuel consumption of the gas engine 30 is reduced. On the other hand, the mass flow rate ms / mp decreases as the pressure ratio increases. Since ms is a value determined from the cold demand, mp increases. As described above, since there is a restriction on the amount of heat recovered from the gas engine that generates primary steam, when the pressure ratio is excessive, an extra fuel is required to make up for the shortage of heat for generating primary steam. This is a reduction in efficiency of the total cold generation system 1.

FIG. 2 is a diagram showing the relationship between the pressure ratio of the ejector 4 shown in FIG. 1 and the fuel consumption. The graph shown in FIG. 2 shows that the efficiency of the gas engine 30 (shaft power of the gas engine 30 / fuel consumption of the gas engine 30) is about 37.5%, and the temperature of exhaust heat recovered from the gas engine 30 is about 80 ° C. In this case, the pressure ratio between the condenser 5 and the evaporator 3 is about 3.0, and the fuel consumption when the pressure ratio of the ejector 4 is 1.0 is set as a reference (1.0).
For example, in FIG. 2, when the amount of exhaust heat recovered from the gas engine 30 / shaft power (both units are KW) is 1.5, compression is performed when the pressure ratio of the ejector 4 is increased in the range of 1.0 to 1.06. The compression work of the machine 7 is reduced and the fuel consumption is reduced. However, if the pressure ratio of the ejector 4 becomes larger than 1.06, the exhaust heat recovered from the gas engine 30 cannot cover the drive heat amount of the ejector 4, and additional fuel is added to the primary steam auxiliary generator (not shown) or the like. Therefore, it is necessary to supplement the primary steam for driving the ejector 4, so that the fuel consumption starts to increase.
Therefore, when the amount of exhaust heat recovered from the gas engine 30 / shaft power is 1.5, the exhaust heat of the gas engine 30 can be most effectively utilized if the pressure ratio of the ejector 4 is about 1.06. The fuel consumption of the engine 30 can be minimized. This means that the efficiency of the cold heat generation system 1 can be maximized.

Also, as shown in FIG. 2, when the amount of exhaust heat recovered from the gas engine 30 / shaft power is 1.0, the fuel consumption of the gas engine 30 is minimized when the pressure ratio of the ejector 4 is about 1.04. It can be seen that when the recovered exhaust heat amount from the gas engine 30 / shaft power is 1.25, the fuel consumption of the gas engine 30 is minimized when the pressure ratio of the ejector 4 is about 1.05. Note that the above condition (the efficiency of the gas engine 30 is about 37.5% or the like) is found in a general gas heat pump.
For this reason, in the first embodiment, by designing the pressure ratio of the ejector 4 in the range of 1.0 to 1.1, the exhaust heat of the gas engine 30 is effectively used, and the efficiency of the cold heat generation system 1 is dramatically improved. It has been improved. The pressure ratio of the ejector 4 is preferably set in the range of 1.02 to 1.08, more preferably in the range of 1.03 to 1.07.
The pressure ratio of the ejector 4 that minimizes the fuel consumption depends on factors other than the ratio of the recovered exhaust heat amount / shaft power from the gas engine 30, such as the exhaust heat temperature of the gas engine 30, the operating conditions of the cold heat generation system, and the accompanying conditions. It also fluctuates due to changes in the efficiency of the ejector 4.

Here, a liquid returning method of the cold heat generation system 1 according to the first embodiment will be described.
First, before the ejector 4 and the compressor 7 are operated and liquid return is performed, the valves 15 and 19 are closed and the valves 12, 18 and 20 are open. At this time, the condenser 5 and the liquid receiver 8 are equal in pressure. A part of the condensate refrigerant condensed in the condenser 5 is guided from the expansion valve 6 to the evaporator 3, but a part thereof is stored in the liquid receiver 8. When the condensate refrigerant in the receiver 8 reaches a liquid level set by a level meter (not shown), the condensate refrigerant in the receiver 8 is transferred to the steam generator 2 by a dump trap method. Specifically, the valves 12 and 18 are closed, the valve 19 is opened, and the high-temperature and high-pressure primary steam in the steam generator 2 is guided to the receiver 8 through the refrigerant gas pipe 16 and the branch pipe 17. The condensate refrigerant in the liquid receiver 8 is heated and pressurized to a pressure at which, for example, its own weight can be supplied. At this time, the valve 20 may be closed so that all the primary steam of the steam generator 2 is directed to the liquid receiver 8. Moreover, the heating amount at this time can be controlled using a timer or a pressure gauge. Subsequently, the valve 15 is opened, and the condensate refrigerant is transferred from the receiver 8 to the steam generator 2 by its own weight supply liquid or the like. Here, the condensate refrigerant may be transferred by using a pump instead of the self-weight supply liquid. In this case, since the liquid receiver 8 and the steam generator 2 have substantially the same pressure, the pump power required for transfer may be very small. Moreover, when using a pump, the positional relationship of the height direction of the liquid receiver 8 and the steam generator 2 can be made arbitrary.

  In order to depressurize the receiver 8 that has been pressurized after the condensate refrigerant has been transferred, the valves 15 and 19 are closed, the valves 12 and 18 are opened, and the refrigerant gas in the receiver 8 is removed from the condenser 5. To lead to. If the valve 20 is closed, the supply of the primary steam to the ejector 4 is resumed by opening the valve 20. In the dump trap system, a check valve may be used instead of the valves 12 and 15.

In the first embodiment, as a liquid returning method to the steam generator 2, the condensate refrigerant of the liquid receiver 8 is transferred to the steam generator 2 by sending the primary steam of the steam generator 2 to the liquid receiver 8. However, for example, the exhaust heat from the gas engine 30 may be branched from the exhaust heat pipe 32 and sent to the liquid receiver 8 to be heated and pressurized. As a result, the steam can be stably supplied from the steam generator 2 to the ejector 4 constantly, and the cold heat generation system 1 can be continuously operated. Further, as a liquid return method, the liquid return to the steam generator 2 may be performed by a liquid return pump as shown in FIG. 3 without using the dump trap method.
For a general dump trap type liquid return method, see, for example, Japanese Patent Application Laid-Open No. 2003-262212 (FIGS. 1 and 2).
In the first embodiment, the cold heat generation system 1 including one ejector is shown. However, for example, a plurality of ejectors may be arranged in parallel, or a plurality of ejectors may be arranged in series.

In the first embodiment, the compressor 7 is driven by a gas engine 30 that generates exhaust heat, and the steam generator 2 is heated by the exhaust heat generated by the gas engine 30 to generate steam, and the ejector 4 is generated by the steam. Drive. Therefore, by effectively using the exhaust heat, the driving power of the compressor 7 is reduced, the fuel consumption for driving the gas engine 30 is reduced, the energy efficiency is improved, and cold can be generated at low cost. It becomes. In addition, since the cold heat generation system 1 according to the first embodiment is configured by one system, the cold heat generation capacity can be increased with the same size as a conventional gas heat pump.
Moreover, since the pressure ratio of the ejector 4 is designed in the range of 1 to 1.1, the exhaust heat of the gas engine 30 can be effectively used, and the efficiency of the cold heat generation system 1 can be dramatically improved. .
Further, when the condensate refrigerant is returned to the steam generator 2, the dump trap system is adopted, so that no liquid return pump is required, and the power of the liquid return pump can be reduced.

Embodiment 2. FIG.
FIG. 3 is a configuration diagram illustrating a cold heat generation system according to Embodiment 2 of the present invention. A cold heat generation system 1 shown in FIG. 3 includes an expander 22 and an auxiliary compressor 23 instead of the ejector 4 as an auxiliary compression mechanism. Moreover, the 2nd expander 24 and the liquid return pump 25 are provided, and the liquid return to the steam generator 2 is performed by these instead of a dump trap system. In FIG. 3, the portion of the auxiliary compression mechanism is indicated by a dotted line.
Other components (such as the evaporator 3) and their operations are substantially the same as those of the cold heat generation system according to the first embodiment, and detailed description thereof is omitted. The same constituent elements will be described with the same reference numerals. In addition, in the cold heat production | generation apparatus 1 which concerns on this Embodiment 2, the expansion valve 6, the liquid receiver 8 and valve | bulb in Embodiment 1 shall not be provided.

  In the cold heat generation system 1 shown in FIG. 3, the primary steam (driving steam) generated by the steam generator 2 is transferred to the expander 22, and the expander 22 is driven by this primary steam. The primary steam is generated when the refrigerant is heated by the exhaust heat of the gas engine 30 as in the first embodiment. Here, for example, when the expander 22 is a rotary type, shaft power is generated. The expander 22 and the auxiliary compressor 23 are connected by a power transmission means 26, and the auxiliary compressor 23 is driven by power generated by the expander 22 (for example, shaft power). The expander 22 and the auxiliary compressor 23 can use general types such as a reciprocating type, a scroll type, a screw type, a rotary type, a vane type, and a centrifugal type. Are not limited to those that transmit shaft power.

  The refrigerant gas (secondary vapor) generated in the evaporator 3 and pressurized by the compressor 7 is further pressurized by the auxiliary compressor 23. The compressor 7 is driven by the power of the gas engine 30 as in the first embodiment, and the cooling principle of the cooling of the cooling load in the evaporator 3 is the same as that in the cold heat generation system 1 according to the first embodiment. . The refrigerant gas that has passed through the expander 22 and the refrigerant gas that has passed through the auxiliary compressor 23 are both transferred to the condenser 5 and become condensed liquid refrigerant by the cooling water of the condenser 5. A part of the condensate refrigerant is transferred to the second expander 24, and the other condensate refrigerant is transferred to the liquid return pump 25.

The second expander 24 is driven by the condensate refrigerant transferred from the condenser 5, and the condensate refrigerant is decompressed by the second expander 24. For example, when the second expander 24 is a rotary type, shaft power is generated. The second expander 24 and the liquid return pump 25 are connected by a power transmission means 27, and the liquid return pump 25 is driven by the power (for example, shaft power) generated by the second expander 24. The second expander 24 can be of a general type such as a reciprocating type, a scroll type, a screw type, a rotary type, a vane type, a centrifugal type, etc. The method for transmitting power is not limited to the method for transmitting shaft power.
Then, the condensate refrigerant decompressed by the second expander 24 is transferred to the evaporator 3. The condensate refrigerant transferred from the condenser 5 to the liquid return pump 25 is pressurized by the liquid return pump 25 and transferred to the steam generator 2.
Hereinafter, cold is produced | generated by repeating the above cycles.

In the second embodiment, the refrigerant flowing through the steam generator 2 and the expander 22, and the refrigerant flowing through the evaporator 3, the compressor 7, the auxiliary compressor 23, and the second expander 24 are made of the same substance, and The refrigerant gas is condensed by the condenser 5. Note that the refrigerant that flows through the steam generator 2 and the expander 22 and the refrigerant that flows through the evaporator 3, the compressor 7, the auxiliary compressor 23, and the second expander 24 are made of different substances, and the cold heat generation system 1 A refrigerant separator (not shown) may be provided. Also, the refrigerant flowing through the steam generator 2 and the expander 22 and the refrigerant flowing through the evaporator 3, the compressor 7, the auxiliary compressor 23, and the second expander 24 are made of different substances, and the piping system and the condensation A cold heat generation system with a separate vessel will be described in Embodiment 3 below.
In the second embodiment, the compressor 7 and the auxiliary compressor 23 are arranged in series. However, the compressor 7 and the auxiliary compressor 23 may be arranged in parallel.

In the second embodiment, since the auxiliary compression mechanism is composed of the expander 22 and the auxiliary compressor 23, the power of the expander 22 can be used effectively, and the cold energy generation system 1 with high energy efficiency can be obtained. it can.
Further, since the second expander 24 and the liquid return pump 25 are provided, and the liquid return pump 25 is driven by the power generated by the second expander 24, power is not wasted and a high energy-efficient cold heat generation system is obtained. be able to.
Furthermore, since the refrigerant flowing through the steam generator 2, the evaporator 3 and the compressor 7 is made of the same substance, they can be configured using the same piping system, and the size of the cold heat generation system 1 can be reduced. it can.
Other effects are the same as those of the cold heat generation system 1 according to the first embodiment.

Embodiment 3. FIG.
FIG. 4 is a configuration diagram illustrating a cold heat generation system according to Embodiment 3 of the present invention. 4, the refrigerant flowing through the steam generator 2 and the expander 22, and the refrigerant flowing through the evaporator 3, the compressor 7, the auxiliary compressor 23, and the second expander 24 are made of different substances. Thus, the refrigerant gas is condensed by the two condensers 5a and 5b. The piping system of the steam generator 2, the expander 22 and the condenser 5a is separated from the piping system of the evaporator 3, the compressor 7, the auxiliary compressor 23, the condenser 5b and the second expander 24. Note that, in the cold heat generation system 1 according to the third embodiment, as in the cold heat generation system 1 according to the second embodiment, the expander 22 and the auxiliary compressor 23 are connected by the power transmission means 26, and the second expander. 24 and the liquid return pump 25 are connected by a power transmission means 27.
Other components (such as the evaporator 3) and their operations are the same as those of the cold heat generation system according to the second embodiment, and a description thereof is omitted. Moreover, the same code | symbol is attached | subjected to the same component and the part of an auxiliary compression mechanism is shown with the dotted line.
As shown in FIG. 4, the cooling system 2 is separated from the piping system of the steam generator 2 and the expander 22 and the piping system of the evaporator 3, the compressor 7, the auxiliary compressor 23, and the second expander 24. Can also be configured. By separating the piping system in this way, it is possible to independently and arbitrarily select the refrigerant flowing through the piping system of the steam generator 2 and the expander 22. Thereby, a refrigerant | coolant can be selected according to the exhaust heat temperature collect | recovered from the gas engine 30, for example. Other effects are substantially the same as those of the cold heat generation system 1 shown in the first and second embodiments.

  The cold heat generation system and the cold heat generation method according to the present invention are not limited to the above-described Embodiments 1, 2, and 3, and can be changed within the scope of the idea of the present invention. For example, in the cold heat generation system 1 of the first embodiment, an expansion machine and a liquid return pump (second expansion machine 24 and liquid return pump 25 in the second embodiment) are used for the steam generator 2 instead of the dump trap system. Liquid return may be performed. Further, for example, in the second and third embodiments, the second expander 24 and the liquid return pump 25 may not be connected by the power transmission means 27. In this case, for example, the generator may be rotated by the power generated by the second expander 24 to generate power, and the liquid return pump 25 may be driven by the generated power.

The block diagram which showed the cold-heat generation system which concerns on Embodiment 1 of this invention. The figure which showed the relationship between the pressure ratio of the ejector shown in FIG. 1, and fuel consumption. The block diagram which showed the cold heat generation system which concerns on Embodiment 2 of this invention. The block diagram which showed the cold-heat generation system which concerns on Embodiment 3 of this invention. The block diagram which shows the cold heat generation system using the conventional gas engine. The block diagram which shows the conventional vapor injection type refrigeration apparatus (cold heat generation system).

Explanation of symbols

1 cold heat generation system, 2 steam generator, 3 evaporator, 4 ejector, 5 condenser, 6 expansion valve, 7 compressor, 8 liquid receiver, 11 liquid return pipe, 12 valve, 15 valve, 16 refrigerant gas pipe, 17 branch pipe, 18 valve, 19 valve, 20 valve, 21 nozzle, 22 expander, 23 auxiliary compressor, 24 second expander, 25 liquid return pump, 26 power transmission means, 27 power transmission means, 30 gas engine 31 Power transmission means, 32 Waste heat piping.

Claims (9)

A compressor, a steam generator, an evaporator, a condenser, and an auxiliary compression mechanism, pressurizing a refrigerant gas from the evaporator by the compressor, and supplying the pressurized refrigerant gas to the A cold heat generation system that pressurizes the auxiliary compression mechanism driven by the refrigerant gas generated from the steam generator,
A cold heat generating system, wherein the compressor is driven by a power source that generates exhaust heat, and the steam generator is heated by the exhaust heat generated by the power source.   The cold power generation system according to claim 1, wherein the power source is a gas engine.   The cold heat generation system according to claim 1, wherein the auxiliary compression mechanism is an ejector.   4. The cold heat generation system according to claim 3, wherein a pressure ratio of the ejector is in a range of 1.0 to 1.1.   3. The auxiliary compression mechanism includes an expander driven by a refrigerant gas generated from the steam generator and an auxiliary compressor driven by power generated by the expander. Cold heat generation system.   A receiver for transferring a part of the condensate refrigerant stored in the condenser, and adopting a dump trap system to transfer the condensate refrigerant from the receiver to the steam generator; The cold heat generation system according to any one of claims 1 to 5.   A second expander that depressurizes the condensate refrigerant and transfers it from the condenser to the evaporator; and a liquid return pump that transfers condensate refrigerant from the condenser to the vapor generator. The cold heat generation system according to claim 1, wherein the cold heat generation system is driven by power generated by the second expander.   The refrigerant generating system according to any one of claims 1 to 7, wherein the refrigerant flowing through the steam generator and the refrigerant flowing through the evaporator and the compressor are made of the same substance. A cold heat generating method, wherein the cold heat generating system according to any one of claims 1 to 8 generates cold heat.

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