JP2007032898A - Cogeneration output utilization system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To supply heat and electric power which are the output of a cogeneration device while appropriately coping with various energy demand on the using customer side. <P>SOLUTION: This cogeneration output utilization system achieves a high capacity to cope with demand, and high energy efficiency, furthermore compact and natural refrigerant adoption by uniting an expander circuit for driving a compressor, and a refrigerating cycle in a system wherein the compressor of the refrigerating cycle is driven by a power source selecting or combining exhaust heat and electric power which are the output of the cogeneration device, and heat and cold are selectively or simultaneously output by the refrigerating cycle. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

The present invention is a technical invention related to the use and application of electricity and heat output of a cogeneration apparatus, and intends to provide a new technical system that uses the output. In cogeneration equipment, the demand for electricity and heat in each place where it is actually used, especially heating
In order to be able to meet and satisfy the demands of cooling and hot water supply day and night, as long as possible throughout the year, it is possible to convert the output according to the content of the demand, and at the time of the conversion the thermal energy output The technology for realizing a product aiming at increasing the necessity and improving the operating energy efficiency is provided.

  Cogeneration systems have been put into practical use, such as gas engine-driven power generation, petroleum engine-driven power generation, and fuel cell power generation. However, there are many types of cogeneration systems such as those with different principles and different detailed methods and capabilities. Also, the operating conditions are different, for example, the output amount and ratio of electric power and heat amount, the exhaust heat temperature of heat amount, etc. are greatly different, so select the type according to the consumption mode of the user side, equipment that matches the desired performance Is selected before installation, and control adjustments and the like regarding operation conditions and output use are performed during actual operation, but they are not sufficiently adapted to the actual demands of users.

Actually, the power output is adjusted by reverse power flow to a commercial power circuit when it is surplus, or it is adjusted by receiving power distribution when it is insufficient, while the amount of heat is adjusted by storing hot water in a hot water tank. It is generally used for hot water supply or for heating in winter and has a certain effect. In addition, in order to achieve a balance between the demand for heating in the winter and cooling in the summer, technological development and practical application, such as the use of absorption chillers, etc. to convert the heat into cold and use it in the summer, are being implemented. It has been. However, this method has problems such as a slow start-up at the start of use, a large-sized device, and difficult to put into practical use including a cost for home use.

With the current methods and technologies, the above-mentioned adjustable range of energy supply and demand is extremely small, and it cannot cope with actual local demand fluctuations. In the future, in order to accelerate the practical application of cogeneration systems to solve global energy problems and environmental problems, it is possible to arbitrarily select and use either or both of the power and heat output from the cogeneration system. In addition, it is possible to respond to fluctuations in the consumption of heating, cooling, and hot water that are on-site heat demands, and to meet a wide range and flexible response to the overlap of these heat demands in the same time zone. New systems such as providing a simple and compact system with high energy efficiency, and a technology that realizes such a system are expected.

Therefore, the inventor fused the current cogeneration system with high energy conversion efficiency and the heat pump refrigeration cycle having high functions for effective use of low-concentration heat energy, and the basics that support it. The present invention intends to invent and propose a new technology, and the present invention provides a total fusion technology of a cogeneration system and a heat pump refrigeration cycle, a system configuration and control method thereof, a refrigerant circuit used for realizing the system, and a use thereof. This is a technology related to refrigerants.

As described above, most of the methods of using the output of the conventional cogeneration apparatus perform analysis at the reference point based on the peak load and adjustment of model selection at the stage of installation design (for example, non-patent literature) 1). Therefore, in actual use, the capacity and demand do not match in many time zones as described above. In view of this, various devices have been devised relating to control in order to match the demand. (For example, refer to Patent Document 1) Furthermore, in order to improve this point in a large-scale system, utilization of heat output to an air conditioner and a refrigerator has been specifically devised and reported. (For example, Patent Document 2, Non-Patent Documents 2, 3, and 4)

  However, the measures based on the conventional techniques as described above have obtained extremely insufficient improvement results. In other words, for model selection, simple operation control, and hot water tank heat storage, etc., the standard set value of 100% is based on the average daily demand. As far as possible, with regard to the response to the actual fluctuation range of the annual demand, which is significant in electricity, hot water, cooling, heating, etc. The effect is thin. In addition, the above absorption chillers, which are being put into practical use to meet the cooling demand in summer, and the desiccant air conditioning system that has been newly studied, are in principle used to level the balance between summer and winter demand. Although effective, it is not practical in terms of efficiency, cost, device size, etc. and has many problems.

Therefore, techniques aiming at further improvement have been proposed recently. (For example, patent document 4) This drives a Rankine engine using the exhaust heat of a vehicle-mounted fuel cell, and operates a refrigerating cycle, and has led to improvement of several elements. In other words, the refrigeration cycle is operated by using the exhaust heat of the cogeneration apparatus as a heat source to find a more practical improvement. However, this is also only an idea of possibility, and the specific technology for realizing this and the configuration principle of the apparatus have not been studied, and there are many problems such as how to realize it.

Therefore, when many cogeneration devices are installed at present, the power output is used for the power demand at the site, and the surplus is sold to the commercial power circuit. Is done. On the other hand, most of the heat output is used as a hot water heat source, which is used for hot water supply or heating, but the gap between the supply capacity of thermoelectric ratio and demand is large depending on the time of day. At present, there is a shortage of hot water for heating and bath water supply in the severe cold season of winter, and in the hot summer, it relies on air conditioning by commercial power sources, and as a result, the feasibility of the operation effect of the cogeneration system has diminished Yes. Therefore, it is a basic advantage of using cogeneration equipment in the future, both power output and heat output will be used in a balanced manner on-site, thereby realizing total high energy efficiency, thereby achieving an economic effect, There is an urgent need to realize the philosophy of contributing to the reduction of global environmental energy consumption and mitigating global environmental warming.

  The energy efficiency of the cogeneration system is about 70% of the total input energy even if both power and exhaust heat are regarded as output, and the effective output is about 70%, which is higher than the 35% of the single power generation system. However, the remaining 30% is still lost in vain. The aim of the present invention is to realize a technology that can extract 100% or more of output energy by the cogeneration use system in the subject field of the present invention.

  As described above, as a technical field that is currently most expected in this field, Patent Document 3 proposes the principle of driving an expander and further a compressor using heat, and as seen in Patent Document 4, A system has been proposed in which exhaust heat is used to drive an expander and a compressor, thereby operating a refrigeration cycle to generate heat and cold according to the heat pump principle to achieve energy conversion in accordance with demand. The inventor said that the system using this expander is one of the most advantageous systems in terms of energy efficiency, output control, future commercialization and practicality, and cost as a method of using the output energy of the cogeneration system. I catch it. However, even though there is a system that obtains hot / cold heat by operating the refrigeration cycle by evaporating the refrigerant using the cogeneration output heat as the heat source and driving the compressor to Rankine, the proposal is almost also considered for practical use It can be said that the situation has not been done. The biggest reason for this is that, compared to cogeneration heat output temperature, Rankine-driven refrigerant circuit technology is a low-temperature technology, its technical area was different, and Rankine-driven refrigerant circuit and refrigeration cycle system This is probably because there was no technology to connect, so even if it was completed with the conventional technology, the system became too large to be practically used.

Using the cogeneration output heat of around 100 ° C, the Rankine drive cycle is operated at a temperature as high as possible to obtain high efficiency, and the refrigerant system technology used in the heat field of 60 ° C or less is used there. It is necessary to transfer the energy to the refrigeration cycle, which is another refrigerant circuit, and it is combined with technology that pumps heat from outdoor air that also falls below 0 ° C, etc., and the whole is compact and simple, It aims to realize a system that can achieve extremely high energy efficiency, which requires the achievement of unprecedented ideas and technologies. Specifically, when the cogeneration output temperature is 90 ° C. or lower, the critical point temperature of the refrigerant is one important point. For refrigerants with low critical point temperature, even if the cogeneration output temperature is low, the heat exchange temperature exceeds the critical point temperature, so the heat exchange is performed in the sensible heat region, not in the refrigerant evaporation region, so there is a temperature difference. This is a key point in the selection of the refrigerant, as a need arises and a higher exhaust heat temperature heat source is required.

On the other hand, in recent years, in order to alleviate global warming, fundamental changes are also desired for the refrigerant itself used in equipment such as air conditioning, freezing, and refrigeration. For this reason, the use of a new refrigerant with a small GWP value, which is a global warming index, and the amount of enclosed refrigerant are reduced, and the enclosed refrigerant is recovered without leaking into the atmosphere during the installation, use, and disposal of equipment. There is an increasing demand to improve these three factors. From the viewpoint of GWP, which is the global warming index of refrigerants, those that have been conventionally used and that contain a chlorine component and refrigerants that contain a large amount of fluorine components are excluded. Therefore, there is a strong possibility that most non-flammable, scientifically stable and safe refrigerants cannot be used because they contain chlorine and fluorine. For this reason, the emergence of technology that compensates the weaknesses of natural refrigerants on the product side is urgently needed, but this type of business area is established by using working refrigerants by combining a refrigeration cycle with a future cogeneration system. It is assumed that the new system equipment such as the present invention is premised on satisfying the design conditions for fulfilling the above requirements.
JP 2005-16845 A JP 2000-274734 A JP-A-6-137700 JP 2004-60550 A Architectural Institute of Japan “Next Generation Energy Sources of Architecture” Inoue Shoin P26, P27 Japanese architecture academy "next-generation energy bias of architecture" Inoue Shoin P50, Figure 3-9 Japanese architecture academia “next-generation energy bias of architecture” Inoue Shoin P62, photo 4-3 Japanese Architectural Society “Next Generation Energy Concentration in Architecture” Inoue Shoin P20

The output of the cogeneration system is electric power and exhaust heat. Thus, when it is installed and operated at a site that actually uses one cogeneration system, in a certain time zone, there is a surplus of heat due to insufficient power, or a shortage of heat due to excessive power, or both are insufficient, or both are excessive. Many problems occur due to mismatch between supply capacity and demand, etc. in many time periods, and if the exhaust heat amount is excessive supply, the cogeneration system operation is stopped, and if it is insufficient, the use of heat amount must be restricted. In most cases, it is impossible to enjoy the energy efficiency and convenience of the entire cogeneration system as originally planned.

In particular, from the viewpoint of using the output of cogeneration equipment throughout the year, in addition to using it as hot water for hot water supply and heating, the realization of a system that generates cold heat for cooling, cooling, etc. is important for the spread and expansion of cogeneration equipment. It turns out to be an important element. On the other hand, there are systems that operate the refrigeration cycle with an expander using an absorption chiller or high-pressure refrigerant, but the absorption system has a large system volume per unit heat and its configuration is complicated, so it is practically useful for small consumer use. However, energy efficiency is low, and a complicated structure is required for switching between air conditioning and heating, and it takes time to start up performance at the start of operation.

The method using an expander is basically considered to be the best solution, but it is still in the idea stage, how to generate heat and cold, and how to use it, for example, hot water and heating. However, no specific technology regarding the realization strategy, structure, and control of the entire system capable of outputting cooling has been proposed and has not been put into practical use. In view of the above situation, a specific and practical method that uses the power and exhaust heat that are the output of the cogeneration device and converts them to various energy forms at the site that uses it in some way It is necessary for the spread of cogeneration equipment to provide technology that can realize the above.

Therefore, a method for driving the expander using exhaust heat and / or electric power, which are outputs of the cogeneration apparatus, is taken up as the most probable measure for that purpose. In this case, as described above, it is necessary to clarify the technology such as means, structure, and control for concrete realization and practical use. Furthermore, the compressor is driven by the output of the expander, thereby operating the refrigeration cycle. As a result, heat and cold are generated by the heat pump principle and controlled to meet the demand for cooling, heating and hot water throughout the year. In combination with a method to achieve energy conversion, measures and technologies are needed to materialize and put into practical use the entire system. Hereinafter, each specific problem will be further described.

In the method of operating the heat pump refrigeration cycle, when cooling / cooling demand or heating / heating demand is unbalanced, the final warm water or cold water output is excessive and cannot be absorbed by the heat storage tank. It is necessary to establish a practical practical method for stopping the output and continuing the operation that meets the other demand. In other words, it is indispensable for practical use to adjust the output according to actual demands such as hot water supply, heating, cooling, etc. on the output side, both hot and cold water, and cold water. It is a problem to invent. For example, when the date and time after the operation is stopped and the cogeneration apparatus is started again, the exhaust heat temperature is low for a while, and the hot water temperature, the heat, and the cold energy are not sufficiently output. Response to demand during this period is also an issue.

Recently, during cooling and cooling operations that are operated throughout the year, exhaust heat (condensation heat dissipation) is also generated in the refrigeration cycle at the same time, but this is combined with the cogeneration heat output and output as a thermal output. The challenge is to devise and establish a system technology that achieves the results of a further step of producing the effects of increased energy output and improved efficiency. The number of people gathering in buildings in recent years has increased, and there is a demand for cooling throughout the year. If a technology for simultaneous output of heating and hot water is invented, a cogeneration system will create a large market. It becomes power.

If the above-mentioned problems are achieved, in the system that simultaneously realizes heating, hot water supply, heating, cooling, cooling, etc., the total output energy that can be used in the integrated use system of the present invention is the input energy to the cogeneration device. Although there is a possibility of achieving 100% or more, the clarification of this principle, the proposal of a concrete realization technology measure, and the support of its certainty are issues. The technology related to this mainly consists of the relationship between the cogeneration exhaust heat temperature and the characteristics of the refrigerant. In the case of exhaust heat at a sufficiently high temperature, there is no problem in terms of the output of the expander and the related hot / cold heat output characteristics, but in the case of an output temperature lower than 80 ° C. as in the case of a solid polymer fuel cell, the refrigerant characteristics, particularly critical Point temperature is a problem.

It is also an issue to present a concrete concept and a concrete plan that can be realized with the cost, the size of the apparatus, the long-term reliability, and the global environmental safety that can put the above system into practical use. In particular, ensuring the long-term reliability and life of the expander and the safety of the working refrigerant used in the working circuit are important. From the viewpoint of the GWP relating to the refrigerant, those conventionally containing a chlorine component and those containing a large amount of a fluorine component are excluded. Therefore, there is a strong possibility that most of the scientifically stable and safe refrigerants that are difficult to burn cannot be used because they contain a large amount of chlorine and fluorine. For this reason, there is an urgent need to make improvements to compensate for the weaknesses of natural refrigerants on the product side that uses natural refrigerants, but in line with the new refrigerant usage conditions described above, new technologies that can be incorporated into the system of this invention have been established. To do is a challenge.

  In order to solve the above problems, a series of solutions are presented. In the first aspect of the present invention, the exhaust heat (H1), which is the output of the cogeneration system, is used as energy for operating the refrigerant circuit including the refrigeration cycle of the present invention. In order to adapt to various types of demands at various local sites, it is possible to output only the heat or only the cold heat at the same time or, if necessary, both the hot and cold heat forms. Accordingly, as shown in claim 7 and the embodiment, a heat exchanger for exchanging heat with outdoor air is provided in the refrigeration cycle, and any mode can be obtained by switching it to an evaporator or a condenser by switching a control valve. The refrigeration cycle technology that can be realized presents one of the basic technologies of the present invention, and the detailed configuration and technology for that will be described in the section of the invention described later.

The second invention further expands the first invention to adapt to a wider demand pattern at the local site. The power (E1) and exhaust heat (H1) which are the outputs of the cogeneration system, If necessary, the commercial power is selected as an energy source for operating the refrigerant circuit including the refrigeration cycle of the present invention, or used in combination, and the invention provides a synergistic effect with the switching of the refrigeration cycle according to claim 1. The ability to combine, switch, select and use energy sources is important for adapting to a wider range of local demand patterns. Details are given in claim 5 and the examples. As can be seen, this technology presents the second of the fundamental technologies of the present invention. Detailed configuration and technique will be described in the section of the invention described later.

The third invention is a combination of the effects obtained in the first and second inventions, and is selected by combining the selection of the driving method of the compressor and the output mode appropriately combining the thermal output and the cold output. In response to supply and demand, the system is operated in response to the needs of users such as hot water supply using heating and cooling output, heating, cooling and cooling. What is important for practical use is that it can be output to adapt to any demand form and a wide range of demand, and it can be applied to a wide range of demand without taking measures such as large-capacity heat storage using a large tank. Allows the system to continue to operate in accordance with the mode. This is one of the concrete basic technologies for enabling the present invention to be appropriately adapted to many demand forms in the market. Detailed configurations and techniques will be described in the section of the invention and examples below. The fourth invention presents the refrigerant characteristics necessary for operating the refrigeration cycle by effectively utilizing the cogeneration exhaust heat even when the temperature is low. When the exhaust heat temperature of the apparatus is not sufficiently high, the pressure of the high-pressure refrigerant obtained therefrom is low, and the power for driving the expander is insufficient. If the refrigerant circulation flow rate of the expander refrigerant circuit is increased to compensate for this, as a result, a large amount of cogeneration waste heat must be used, and the efficiency of the cogeneration output utilization system is reduced.

Claim 4 presents two techniques for reducing this reduction in efficiency. One is to operate the refrigerant temperature in the heat source heat exchanger in a temperature region lower than the critical point temperature, that is, to cause the heat transfer there to be performed in the latent heat region, not in the sensible heat region of the refrigerant. Specifically, assuming that the exhaust heat temperature condition of the cogeneration system is 80 ° C. or higher, the condition of the refrigerant that can sufficiently exchange heat with latent heat of vaporization at a low temperature heat source close to 80 ° C. When the refrigerant is selected in consideration of (high), a refrigerant having a critical point temperature of 90 ° C. or higher is desirable. However, when the exhaust heat temperature is 90 ° C or higher, a refrigerant with a critical point temperature of 90 ° C cannot exchange heat with latent heat of vaporization. Yes, the critical point temperature is less important. The other is to increase the heat contact efficiency and increase the temperature contact factor by allowing the heat source heat exchanger to exchange heat in a counter flow. This is because the refrigerant itself needs to be overheated in order to operate stably in the subsequent expansion stroke of the refrigerant. For this purpose, the refrigerant outlet temperature is set to the highest temperature of the cogeneration exhaust heat source medium. This is because it is effective to bring the temperature as close as possible.

On the other hand, the maximum pressure of the refrigerant in the system is the basis of the structural design and reliability of the entire refrigerant circuit, which is comprehensively selected from the pressure-resistant material characteristics, manufacturability, material cost, etc. of the components of the refrigerant circuit.
The inventor understands that if it is 10 MPa or more, it is extremely impractical. When the pre-expansion pressure of the expander refrigerant circuit is 10 MPa, the post-expansion pressure is calculated to be about 4 MPa due to the cycle configuration of the entire refrigerant circuit. On the other hand, the practical reference temperature output temperature of this system is 60 ° C. assuming a water heater, and the refrigerant condensation temperature of the heat output heat exchanger is calculated as 60 ° C. from this. Therefore, the relationship that the pressure of the refrigerant used needs to be 4 MPa or less at the reference temperature of 60 ° C. is derived. Examples of specific pressure relationships are shown in the examples. In the second, third and fourth inventions, the fifth invention is not limited to exhaust heat (H1), but also uses electric power (E1) or commercial power as an energy source for driving. Further, an electric motor is installed, and the compressor is driven by the motor, for example, by integrally configuring the shaft. Thus, when driven by a motor, the expander cylinder is opened and released as in claim 16, and when driven by an expander, the motor is idled so that no back electromotive force is generated. An induction motor is used. The above is one of the basic techniques for realizing the second, third and fourth inventions. The detailed configuration and technique will be described in the section of the invention described later.

As described above, in order to match the output of this system with the wide-ranging heat demand of the site, it is proposed as Invention 6 to provide a thermal output heat exchanger in the refrigerant circuit and a cold output heat exchanger in the refrigeration cycle. The feature of this function, which is activated simultaneously, for example corresponding to the demand for cooling, heating and hot water supply, which corresponds to the simultaneous heat demand, and also to the increase in thermal demand, is therefore indicated in claim 13. In addition to the compressed gas condensation heat amount (H2) plus the expanded refrigerant condensation heat amount (H3), a refrigeration cycle cold heat amount substantially equal to H2 is obtained. Therefore, if the power (E1) and exhaust heat (H1), which are cogeneration outputs, are plus or minus taking into consideration that (H1) is approximately equal to (H3), this output utilization system will increase the heat (H3). In addition, it means that the amount of heat that can be used is increased by the amount of heat (H2) and cold (= H2). As a result, the total available output heat energy of the output utilization system of the present invention can reach three times the amount of exhaust heat input (H1) with respect to the input energy to the cogeneration apparatus. Consider again the case of the embodiment.

The output energy of this system is output in the unit from a sealed refrigerant circuit installed in the unit. From there, heat is transferred to the outside of the unit using a natural medium such as water that is safe and easy to replenish when it leaks in the middle. This clear technical concept aims to invent an integrated sealed refrigerant circuit housed in an integrated unit and to provide a safe and long-term reliable system. An international organization that currently deliberates refrigerant safety standards around the world has established regulations regarding the amount of refrigerant that can be enclosed in a refrigerant circuit that has a part that comes into contact with indoor air, as a standard for the use of toxic and flammable natural refrigerants. Yes. In other words, there are restrictions on the amount of equipment enclosed such as flammable refrigerant and toxic refrigerant, which is a characteristic of natural refrigerant. However, the refrigerant circuit is not open to the room or has a portion that does not come into contact with the room air, and the method of transporting the heat and cold as output to the room using water or the like as a medium is not affected by this regulation. . Realizing this complete safety is a precondition of the present invention and is summarized in Invention 8.

The technique of claim 6 was invented based on the above idea, but it is aimed at achieving another effect. That is, the hot / cold heat that is output is carried out of the unit in the form of hot / cold water and stored in a tank stored outside the unit. This produces a great effect of being able to respond more flexibly to changes in the user's demand form and usage time. In particular, the effect of being able to store heat easily by using water, which is the heat medium that can handle cold most easily, is extremely large in practice. On the other hand, the heat transfer to the outside of the system may use another natural medium such as CO 2 at one end. This is mainly due to the fact that heat transfer and heat transfer characteristics are excellent.

The final form of demand for users is hot water, cold water, heating, and cooling, and they can be supplied continuously within a certain capacity range, simultaneously or selectively, and without relying on heat storage as described above. There is a need for a technology that materializes a system that can be used. Invention 7 proposes a basic measure and technology for responding to changes in demand on the site finely with respect to the heat and cold obtained in Invention 6. In other words, by installing a heat exchanger that exchanges heat with the outside air in the middle of the refrigerant circuit of the heat output heat exchanger and the heat output heat exchanger, and throwing away any unnecessary heat or cold to the outside air is there. As a result, even when the heat is excessive, it is possible to continue the operation of obtaining the cold while throwing away the heat to the outside air, and vice versa. Combined with the adjustment function according to the invention 7, the function that can selectively use both the electric power and the exhaust heat according to the inventions 2 and 5, and the function that can simultaneously obtain and store the heat and cold of the invention 6 are combined. In this sense, we have realized a cogeneration output utilization system that can adapt to the changes in customer demand over a wide range of years.

The basic concept of the cogeneration output utilization system of the present invention, in addition to the functional aspects described in the above inventions 1-7, is that items such as practicality, installation applicability, safety, and cost for practical use are satisfied. is important. Necessary items for this study are: 1. Refrigerant circuit is integrated and compact. 2. System is compact and can be stored in an integrated unit. 3. Control as a system is completed within the unit. Easy. Therefore, the present invention is considered on the premise of the specifications that can satisfy the above items, and as a result of investigation based on the basic concept, the present invention proposes a unit structure in which all functional parts are incorporated into an integral casing. It is suggested that all the members of the refrigerant circuit have a completely sealed structure, which has no mechanical joint.

In addition, this is the invention described below, selection of natural refrigerant, fairness of refrigerant circuit, ensuring compressor reliability, establishment of overall system control, safety detection, separation and coordination of control with cogeneration system, cost It is an important component that is a prerequisite for realizing many items that cannot be avoided in commercialization, such as reduction and long-term reliability. In invention 9, the same refrigerant is used for the expander cycle and the compressor cycle, and the structure is simplified with the expander, the compressor, and the electric motor as an integral shaft, and both refrigerant cycles are heated from the discharge gas space in the shell to the hot water output heat exchanger. It is an invention in which the refrigerant circuit is integrated between the agitator and the flow dividers of both cycles. This can be achieved by technologies such as selection of refrigerants and lubricants that can be used in a wide temperature range, overall configuration of the refrigeration cycle, and optimal settings for refrigerant flow control of the refrigeration cycle. Has an effect.

A tenth aspect of the present invention relates to a mutual energy recovery technique at a branch point where the expander refrigerant circuit and the refrigeration cycle are separated again in the ninth aspect. An electric liquid pump is usually used to compress the liquid refrigerant that has advanced to the expander refrigerant circuit after the diversion. (Claim 11) On the other hand, the refrigerant that has advanced to the refrigeration cycle is expanded by the electric refrigerant control valve to become low pressure and low temperature, and is sent to the cold output heat exchanger. Invention 10 intends to utilize the expansion energy on the refrigeration cycle side for liquid compression on the expander refrigerant circuit side, and relates to a liquid shunt that includes a rotating body for expansion and compression integrated therefor. .

The power consumption is reduced as long as the power of the electro-hydraulic pump is not used, and the expanded refrigerant on the refrigeration cycle side has its outlet enthalpy reduced by the amount of expansion work applied to the rotating body, resulting in cold output. The cooling capacity in the heat exchanger increases. Both of the improvement effects can be expected to improve energy efficiency by about 5%, which leads to efficiency improvement of 10%. At the same time, in order to optimally perform liquid compression on the side of the expander refrigerant circuit under various operating conditions on site, an auxiliary electric motor is incorporated in the expansion / compression shunt to help drive the rotor. It is practically necessary to control or to supplement and control the liquid compression amount by installing an electric liquid pump in a circuit downstream of the flow divider. The invention 11 is presented in claim 11. In the case of a shunt without an expander and a compressor, it is shown in FIG. 11 that liquid compression is performed by an electric liquid pump.

Invention 12 is an important invention related to the refrigerant circuit along with Invention 9, and the refrigerant circuit structure housed in an integral unit housing is a precondition for realizing a closed refrigerant circuit, and the closed refrigerant circuit is a natural refrigerant. It is a prerequisite for adoption. That is, an integrated refrigerant circuit manufactured in a complete state at a manufacturing base and without a brazing or tightening operation required after shipment and having a low risk of refrigerant leakage is described in claim 19. The integral unit structure that can realize the refrigerant leak detection function is the premise for satisfying strict standards for using natural refrigerants. Of course, the GWP value is preferably zero, but the GWP of the most commonly used chlorofluorocarbon refrigerant is 1300 to 1700 level, and it is necessary to recover 100% of the refrigerant when the product is discarded.
This is incompatible with the actual situation of gas leaks. Selection of GWP150 or less is safer than the use of natural refrigerants (such as propane) in the current general air-conditioner system where piping is performed at the site, assuming that the unit is integrated and the refrigerant circuit is hermetically sealed. I believe that.

In this way, the use of materials and materials that are friendly to the natural environment and the earth in products that take advantage of the high energy efficiency of cogeneration equipment is expected to increase the positioning of the product and increase its distribution life. it can. Of course, even in the case of adopting natural refrigerants, the composition and thermal characteristics suitable for ensuring the merchantability of this system are important conditions for commercialization. For this reason, the specification of claim 12 is assumed.

The invention 13 aims at maximizing the thermal output, and outputs the expansion gas condensation heat quantity (H3) in the expander refrigerant circuit and the compressed gas condensation heat quantity (H2) in the refrigeration cycle together as the heat, and outputs it with the same thermal output heat exchanger. Is. In the case of the ninth aspect described in claim 9, since both refrigerant circuits are already integrated in this portion, the flow of the integrated refrigerant outputs the amount of heat added by the hot water output heat exchanger. become. The demand for heat is generally the highest when the number of consumers increases in winter and demand for heating and hot water overlaps. This is an important function in preparation for that, and realizes countermeasures for it. This is an excellent invention and technology.

Invention 14 relates to lubrication of the mechanical parts of the expander and the compressor. If the shell is filled with high-pressure gas that is an expander inlet refrigerant, it is easy to supply lubricating oil to both cylinders. In that case, the lubricating oil in the shell becomes higher than the gas pressure inside the cylinders of the expander and the compressor. Therefore, if the lubricating oil path necessary for the expander and the compressor is skillfully provided, It is possible to easily reach the inside of each cylinder along the path and lubricate the necessary part. However, although the exhaust heat of cogeneration depends on the system of the cogeneration system, it is about 80 ° C-200 ° C, and the high-pressure gas that uses the exhaust heat also reaches a saturated gas pressure of about 80-150 ° C. Depending on the refrigerant gas to be used, the saturation pressure is extremely high and cannot be adopted in view of the structural pressure resistance of the shell and the safety of the device.

  Therefore, the shell is filled with the refrigerant at the outlet of the expander and the refrigerant at the outlet of the refrigerator, and in order to send the lubricating oil to the expander cylinder, it is necessary to send the lubricating oil to the high-pressure side due to its pressure relationship, which requires new devices and techniques. The Thus, a method of providing an electric oil pump for lubricating oil is one idea, but it is not a good idea from the viewpoint of structure, cost, and reliability. Therefore, in the present invention, the compressor has its own lubrication mechanism in the shell by itself, and the expander pays attention to the liquid pump used in the expansion cycle, and introduces the lubricating oil in the expander shell to the liquid suction part. Then, the pressure is increased together with the refrigerant by the liquid pump and is circulated to the expander by the refrigerant circuit. This is because the amount of lubricating oil flowing out of the shell to the outside can be minimized, and the amount of lubricating oil circulating in the refrigeration cycle circuit, which has a significant effect on performance deterioration, can be minimized.

  At this time, the most important point is the establishment of a technique for stably extracting the lubricating oil with a thin tube. This is because when gas refrigerant, metal powder, or the like is mixed, choke is generated in the thin tube, and the flow rate of the lubricating oil may be remarkably reduced, or the liquid sliding part of the liquid pump and the expander may be damaged. . Therefore, it is necessary to take out the lubricating oil with a small ratio of the metal powder and the gas refrigerant mixed from the bottom of the lubricating oil reservoir in the shell, that is, a portion of 1/3 or less of the oil reservoir height.

In the fifteenth aspect, the refrigerant in the refrigerant circuit is specifically selected. In order to embody the above invention, it is necessary to use a refrigerant that is easy to realize, and as a refrigerant satisfying claims 4 and 12, R152a,
R600a, R290, R717, etc. are applicable. R600a (isobutane C4H10, GWP20, critical point temperature 133 ° C., saturation pressure 60 ° C., 0.8 MPa), R290 (propane C3H8, GWP20, critical point temperature 97 ° C., saturation pressure 60 ° C., 2.0 MPa), R717 ( Ammonia, NH3, GWP2, critical point temperature 132 ° C., 2.0 MPa at saturation pressure 60 ° C.), R152a (low GWP Freon HFC C2H4F2, GWP 140, critical point temperature 113 ° C., saturation pressure 60 ° C., 1.3 MPa) Is selected.

Invention 16 proposes a method for controlling the entire output utilization system of the present invention. Operation start-up status of cogeneration equipment, exhaust heat temperature and exhaust heat amount, and related electric power, hot water and cold water supply in all future systems, total energy demand (electric power demand: exhaust heat demand such as lighting: Select the optimal operation mode by estimating and calculating the excess and deficiency of each energy amount due to the prediction and the current heat storage amount, etc., and the total cost of the future operation mode, etc. To do.

Thus, the operation and stop of the output utilization system is controlled. In the case of operation, whether to use power or exhaust heat as the drive energy source is selected in the output utilization system. In addition, in the refrigeration cycle, it is judged whether or not simultaneous operation of cooling and heating is possible, and switching operation is selected. Output utilization system In the case of a stop, we consider a control system that can select and set the usage method, considering all or part of these factors, such as control for directly outputting the exhaust heat of the cogeneration system as hot water In addition, the user selects at least a time zone in which the power unit price is low according to the priority setting of usage such as electric power, hot water supply, heating, cooling, etc. It is the most practical technology in the system of the present invention that is intended to meet the user's demand form to realize a control system that is set so that priority selection can be made

The invention 17 proposes another technique aimed at maximizing the thermal output. The heat medium that conveys the exhaust heat from the cogeneration apparatus is a liquid medium such as water, and once it is dissipated by the heat exchanger using exhaust heat, most of the energy is lost, and the temperature decreases. Heat exchange with the hot water at the outlet of the heat output heat exchanger is further performed to dissipate heat as additional heat release (H4) as the final heating heat source, and the heat output is further increased in addition to the total heat quantity (H3 + H2) of claim 10. It is a featured cogeneration output utilization system. In this case, in most cases, energy exceeding the energy consumption of the cogeneration apparatus can be output from the output utilization system, and high energy efficiency is achieved. Embodiment FIG. 2 shows an example in which a pipe line is extended from a waste heat medium to a heat output heat exchanger.

The invention 18 relates to a technology that makes it possible to appropriately select a drive source of a compressor. That is, the compressor of the same type as the scroll vane type or rolling piston type expander and the electric motor are installed in the integral shell so as to drive the compressor. Therefore, when the compressor is driven only by the motor, the expander moves the release operation according to claim 5, that is, by moving or operating the entire scroll fixing blade of the expander or the opening / closing passage provided in the expander, so that the inside of the cylinder is set to the outside. In the rolling piston, the high / low pressure partition blade is pushed out of the cylinder and fixed to release the partition of the high / low pressure chamber. On the other hand, when driven by the expander alone, the power circuit output is turned off so that the rotating rotor of the electric motor is idle. Further, when driven by both the expander and the motor, the rotational speed and voltage are controlled so that the motor power supply circuit has an output necessary for supplementing the driving force of the expander. As described above, a specific technique has been invented that can be configured and operated so that the operation can be performed by switching between the drive using only the expander, the drive using only the motor, and the drive using both.

Invention 19 is an invention for enhancing the safety against the leakage of the refrigerant. This is a technique for incorporating the function of detecting the occurrence of a small amount of leak into the control of claim 16 before the natural refrigerant leaked causes damage such as fire and toxicity.

According to the nineteenth aspect of the present invention, during the control of the output utilization system and the cogeneration apparatus of the present invention, one of the systems is abnormal and it is necessary to stop or change the operation. This is a technology for when it is necessary to stop or change operation. This naturally includes the case of a refrigerant leak.

The field of use of the present invention is a cogeneration output utilization system in cooperation with a cogeneration apparatus. The aim is to consistently balance the output of the cogeneration equipment and the energy demand on the user side, and convert it to an energy form that can be used to increase the operation rate of the cogeneration equipment, and to achieve high energy efficiency, power and heat. It combines the excellent characteristics of being able to output both at the same time to the benefit and convenience of the user. In addition, it is a compact, simple system with a low global environmental impact, a system with excellent long-term reliability and excellent practical application. This contributes to the spread and expansion of distributed cogeneration system for business use and home use.

Inventions 1, 2, and 3 present basic concept technologies for converting their energy forms, and show the principle of the above effect. Inventions 4, 5, 6, 7, and 16 present specific methods and techniques for realizing them. Inventions 10, 11, 13, and 17 present specific techniques for increasing energy output and energy efficiency. Inventions 9, 12, and 15 present a new refrigerant and a system configuration for reducing the global environmental load. Inventions 6, 8, 9, and 16 present a basic technology that constitutes a refrigerant circuit hermetically sealed in the present system and an integral and compact unit containing the refrigerant circuit. Inventions 14, 18, and 19 provide techniques for enabling the system to be used safely and for a long time.

As a result, the above objects or the above-mentioned problems can be improved. Conventionally, there is no technology that has the overall effects described above, and technologies that have individual improvement effects are scattered as ideas, but how to materialize them, and the overall system The technique of how to put it together cannot be discovered.

Therefore, a specific effect in the system of the present invention is as follows: 1. A technology that can be used as an operating energy source by selecting both or both of the electric power and the exhaust heat which are cogeneration outputs is presented. 2. A system and technique have been presented that allow users to use hot water supply, heating, and cooling simultaneously or by selecting and continuously using the system of the present invention that utilizes cogeneration output. 3. For the electric power and the amount of exhaust heat that are cogeneration output, a technology that can output by the refrigeration cycle by adding the heat and cold to the amount of exhaust heat to the above-mentioned amount of exhaust heat is added. This is 40% of the refrigeration cycle output heat when the output power is 30% and the exhaust heat quantity is 40% of the input energy 100 of the cogeneration system.
The cooling heat is about 35%. If these are totaled, 145% of usable energy including power output can be output for 100% of input energy. (However, in summer, a day at a site with sufficient cooling capacity and hot water demand is assumed)

Considering that the energy efficiency of centralized power generation systems (such as large-scale power plants) is 40% or less, this is about 3.5 times higher than that of current systems that use conventional cogeneration systems as they are. Double the energy efficiency. The present invention presents specific methods and techniques for actually realizing this high energy efficiency.

As described above, the present invention presents various technologies for solving the above-described problems and realizing an energy efficient and practical output utilization system that can be used by being connected to a cogeneration system. It has the effect that it can contribute to practical use.

  Hereinafter, embodiments of the present invention will be described with reference to FIGS.

  FIG. 1 is an overall view of the system outline of one embodiment of the present invention. A cogeneration system (hereinafter abbreviated as system 1) and a cogeneration output utilization system according to the present invention (hereinafter abbreviated as output utilization system 2). ), And how each of the internal and external components works is shown by clearly showing the refrigerant circuit and water circuit showing the flow with energy, and the power system. FIG. 2 shows the overall configuration and each part of the output utilization system 2 in more detail.

3 and 4 are an overall configuration diagram of a structure of a rolling piston type electric expansion compressor used as an important component of the system 2 and a horizontal sectional view of the expander portion. These expanders and compressors are well-known technologies, but they are intended to show the new detailed technology and applied system technology according to the present invention on how to use and operate the expansion compressor using them. is there. In FIG. 5, an expander and a compressor having a structure in which a helical blade is attached to a cylindrical rotating body are installed therein, and the output from the expansion of the refrigerant is used as power necessary for the compression of the refrigerant to compress and expand. The structure of the refrigerant | coolant flow divider which bears both the function which raises the energy efficiency of the whole system, and improves the energy efficiency of the whole system, and the function of the refrigerant | coolant diversion for comprising the whole system of this invention is shown.

The output utilization system 2 of the present invention can be combined in any manner as long as the system 1 is a thermoelectric supply system, but the output is combined with the exhaust heat source capacity of the system 1, the exhaust heat source temperature, the demand form on the user side, etc. Specifications are set for the usage system. That is, the system 1 may be a gas engine generator or a fuel cell, but here, a micro turbine power generator is considered as an example. The system 1 receives the cogeneration fuel 3 and consumes it, and the AC power 4 (E1) and exhaust heat 100
It is assumed that warm water 5 (heat quantity H1) of around 0 ° C. is output. The power 4 is adjusted in voltage and frequency by the power conditioner 17 and is systematically connected to the commercial power supply 20, and at the same time, the supply circuit 18
, 21, the power consumption at the site, for example, the lighting 22 and the power for the output utilization system 2 are supplied.

In the output utilization system 2, the supply of hot water 5 at 100 ° C. is received, and the high-pressure liquid isobutane sent from the pump 27 evaporates in the heat exciter using exhaust heat, resulting in a high pressure of 1.9 MPa and a high temperature of 97 ° C. The resulting gas reaches the expander 23 in the electric expander 9, expands while driving the expander, and provides power to the shaft 102. Thus, it expands and the pressure drops to 0.78 MPa, is discharged into the shell, and merges with the gas compressed and discharged to the same pressure by the compressor of the refrigeration cycle circuit. At this time, since the compressed gas is superheated, the combined gas is 0
. It becomes overheated (about 65 ° C.) by about 10 ° C. or more with respect to a saturation temperature of 78 MPa (55 ° C.).

The gas joined in the shell condenses itself in the thermal output heat exchanger 12 and becomes liquid while heating 40 ° C. warm water to 60 ° C. This hot water is sent to a hot water tank outside the output utilization system 2 and used for hot water supply, heating and the like. The liquid refrigerant, isobutane, which is liquefied by heat dissipation and cooled to approximately the saturation temperature of 55 ° C., is divided by 50% by the liquid flow divider 26, and one of them is compressed by the compressor 202 in the flow divider and then expanded. It flows into the machine refrigerant circuit 7, returns to the exhaust heat utilization heat exchanger 6 and repeats this. Actually, there are many cases where a sufficient flow rate cannot be ensured by the compressor in the flow divider, and the electric compression pump 27 provided downstream is operated to supplement the amount of the compressed liquid to ensure the necessary amount of the compressed liquid. In other cases, in the case of a simple flow divider that does not incorporate a rotary body for expansion and compression in the liquid flow divider, an electric liquid pump is provided downstream of the flow divider on the expander refrigerant circuit side to power the electric motor. The liquid refrigerant is used to compress and circulate, and the liquid refrigerant flowing to the refrigeration cycle expands at the electric refrigerant control valves 28, 29 to 30.

On the other hand, on the refrigeration cycle side, the isobutane liquid that has flowed to the expander 204 of the flow divider 26 drives the expander while expanding, and moves toward the electric refrigerant control valve 29 downstream of the expander. The flow rate is adjusted by a control valve 29 controlled by an unillustrated). As a result, the refrigerant pressure, temperature, etc. of each part of the refrigeration cycle are controlled to an appropriate state. Then, it flows to the cold output heat exchanger 10, cools the cold water 11 and evaporates, returns to the compressor 25, is compressed and discharged into the shell, and this is repeated. The cold water 11 is stored in a cold tank provided outside the output utilization system, and is used for cooling, cooling, slow humidity, and the like.

In the refrigeration cycle 8, an outdoor air heat exchanger 14 is installed in parallel with the refrigerant control valve 29. This heat exchanger is configured to exchange heat with outdoor air 15 blown by a fan (not shown). Thus, when the thermal output is excessive and the cold output is insufficient, the fan is operated, the valve 29 is closed, the valve 28 is fully opened, and the valve 30 is controlled to adjust the refrigerant flow rate and the like. Thus, by operating the outdoor heat exchanger 14 as a condenser heat radiator to dissipate the heat to the outdoor air 15, the output of the heat output heat exchanger 12 can be greatly reduced. At this time, the refrigerant that has exited the heat exchanger using the exhaust heat source is controlled so that about 50% of the refrigerant becomes a gas component on a weight basis. Therefore, the gas component is separated by the gas-liquid separation gas 34 before the liquid distributor 26. After being separated, it is sent to the refrigerant control valve 28 and the outdoor heat exchanger 14 where it dissipates heat and becomes liquid refrigerant.

When the thermal output is insufficient and the cold output is excessive or unnecessary, the fan is operated, the valve 29 is closed, the valve 28 adjusts the refrigerant flow rate, etc., the valve 30 is fully opened, and the heat exchanger 14 Can be operated as an evaporative heat sink, and cooling can cool the outdoor air 15 to significantly reduce or stop the output of the cooling output heat exchanger. At this time, heat is absorbed from the outdoor air, and the heat is output by the heat output heat exchanger 12. The above are specific examples of claims 1, 3, 4, 6, 7, 9, 10, 11, and 13.

  The above operation basically uses the exhaust heat output of the system 1, but in the embodiment, the expander 23, the compressor 25, and the electric motor 24 are driven by one shaft in the electric expansion compressor 9. We have established a relationship where we can. By using this, both the exhaust heat source 5 and the electric power 16 can be selectively or simultaneously used. This is an operation mode that uses only exhaust heat, and, in extreme cases, various energy supply modes such as output power 4 or a mode that uses commercial power even when exhaust heat cannot be used, or a mode that uses both. It is to be able to respond using.

  Therefore, even when the exhaust heat output 5 is insufficient or the temperature falls below 100 ° C., when it is necessary to output the heat and cold, the power 16 is supplied and the refrigeration cycle is fully operated to output the output system. 2 can be activated.

As shown in the case of the rolling piston type of the electric expansion compressor of FIGS. 3 and 4, the high-pressure gas 112 is supplied from the high-pressure gas supply line 110 and passes through a shaft center path 118 provided at the center of the shaft 102. An expansion chamber inside the cylinder passes through a path formed by connecting a fan-shaped high-pressure gas supply path (crank) 117 provided in the crank portion of the shaft and a fan-shaped high-pressure gas supply path (roller) 116 provided in the roller 109. To be supplied. After the crank rotates about 70 degrees, the communication path is cut off and the gas is not supplied, the gas in the expansion cylinder 108 continues to expand and drives the crank and shaft while expanding the internal volume of the cylinder. After the expansion is completed, the air is discharged from the cylinder into the expansion compressor 9 case as indicated by the arrow. During this time, the shaft 102 drives the roller 109 of the compressor and sucks the low-pressure gas evaporated in the cold output heat exchanger into the compression cylinder 114 from the refrigeration cycle suction line 106 and discharges it into the case of the expansion compressor 9. To activate the refrigeration cycle.

If a cogeneration system having an exhaust heat temperature lower than 100 ° C. is used, the evaporating pressure of isobutane gas is lower than 1.9 MPa, and the driving force of the expander is reduced. The increased dimensions are set so that the compressor cylinder can be driven sufficiently. This is the case where the total heat quantity of exhaust heat of the system 1 is the same, and the amount of hot water circulation is increased by the amount of temperature drop.

When the compressor 25 is driven only by the expander 23, the rotor 103 of the motor 24 rotates integrally with the shaft, but the power source of the induction motor type motor 24 is stopped, and the rotor 103 has a rotational reaction force. It doesn't occur and goes around. On the contrary, when the compressor 25 is driven only by the electric motor 24, the partition blade 115 of the expander is pulled upward and fixed. As a result, the high and low pressure partitions are removed from the expander cylinder, so that even if the crank and the roller rotate, gas does not expand and the roller is idle. In addition, when driven by both the expander and the electric motor, the output voltage and frequency of the electric motor are adjusted by an inverter control device (not shown), and the optimum operating state, that is, the total driving force, the rotational speed, the total Control is performed to obtain an optimum state of energy consumption. A power supply control device 19 including the inverter control device is operated with electric power supplied from a power supply 21.

On the other hand, with regard to the scroll type electric expansion compressor having extremely excellent characteristics as an expander, several related devices have been proposed for driving the expander by the evaporated high pressure gas. The technology of driving and controlling the motor and expander complementing each other and the specific measures for that are unclear and could not be realized in the past, but the shaft connection structure, its operation control, release function, etc. The same idea as above. The above are specific examples of claims 2, 5, and 18.

As can be seen from FIG. 2, the output utilization system 2 of this example is configured in an integral unit, and all the refrigerant circuits are accommodated therein. In addition, only the hot water 5 for the exhaust heat source, the power source 21 for the power supply controller, the cold water output 11, the hot water output 13, the outdoor air 15 and the signal line (not shown) to the system 1 have the effect of entering and leaving the outside. Accordingly, the installation work at the site does not require any work related to the refrigerant circuit, but only the work related to the water circuit and the connection adjustment of the power supply circuit and the air flow path.

By realizing this simplified and integrated overall system, not only can it flexibly respond to the customer's annual heat supply and demand, but also provide an extremely high thermal efficiency system, as well as batch production of the entire output utilization system Enables high quality and low cost by shipping, enables the use of natural refrigerants that have problems with local installation work safety, improves the quality of local installation work, reduces costs, and withstands long-term use The system is realized. This is a specific case of claims 6, 8, 9, 12, and 15.

The movement of thermal energy will be described with reference to FIG. The thermal energy (H5) given to the hot water output 13 output by the output utilization system 2 is the standard operation by the output utilization system 2 (the electric expansion compressor 9 is driven only by the expander and the outdoor air fan 15 is stopped). Is the sum of the cogeneration exhaust heat output (H1) and the cold water output (C1) at the cold output heat exchanger from the equation of total heat. (H5 = H1 + C1)

Here, when the exhaust heat output temperature of the system 1 is as high as 100 ° C. or higher and the refrigerant pressure in the expander refrigerant circuit is high, and therefore the expansion power is sufficiently retained, If the refrigerant condensing pressure is set to a substantially intermediate point in terms of pressure ratio, and the refrigerant flow rates of both the expander refrigerant circuit and the refrigeration cycle are made substantially equal, the expansion output work of the expander 23 and the compression work of the compressor 25 are almost equal. It becomes equal and the whole system is established. At this time, (H1) and (C1) corresponding to the heat of evaporation of the expansion circuit and the refrigeration cycle are substantially equal to each other. Therefore, as a result, (H5) can obtain approximately twice as much heat as (H1). At this time, as for those temperatures, H1 assumes 100 degreeC and H5 assumes 60 degreeC.

In this case, the ratio of the amount of output hot water when the output of the system 1 is directly used as the thermal output and the amount of output hot water of the output utilization system 2 is about four times. For home use, office use, and store use, hot water of 60 ° C. is often sufficient, and even when output directly from the system 1, the temperature of 100 ° C. hot water is eventually adjusted to about 60 ° C. with tap water. Therefore, when the comparison is made with the same temperature (60 ° C.), the ratio of the amount of available hot water that can be used is approximately doubled. (H5 = 2 * H1) That is, twice the heating amount can be obtained as compared with the case of the cogeneration system alone. As can be seen from this embodiment, the present invention is effective at a site where there is a large demand for hot water and heating, and a site where there is a demand for cold water and cooling. Naturally, in the case of a site where such demand is not large, the present output utilization system 2 can reduce the operation time of the cogeneration system, and as a result, the fuel consumption can be reduced.

As a method for increasing the heat output (H5) and further improving the heat efficiency, as shown in FIG. 2, after the heat from the exhaust heat source hot water output 5 is radiated by the heat exchanger 6 using the exhaust heat source, the heat output heat exchanger is further heated. There is a method of increasing the total amount of (H1) by adding a heating circuit 32 that dissipates heat at 12. This method is also friendly in maintaining the hot output hot water temperature at the target 60 ° C. even when the exhaust heat temperature of the system drops to 90 ° C. and further to 80 ° C. Further, in the flow divider 26, there is a method in which the expansion energy of the refrigerant to be expanded toward the refrigeration cycle 8 is used as the compression power of the refrigerant to be compressed toward the expander circuit. Further, as a method for increasing H5, if a decrease in the chilled water output is allowed, there is a method of receiving heat from the outdoor air by operating the outdoor air heat exchanger as an evaporator.

As the liquid refrigerant pump (liquid compressor), there are known ones such as a scroll type, a rolling piston type, a helical blade type, and a gear type in this case. In this case, a flow divider 26 having a liquid compressor and a liquid expander inside is proposed as an invention that serves as a trump card for improving energy efficiency. The expansion energy is absorbed during the expansion process of the liquid in the refrigeration cycle, and the enthalpy of the expanded liquid gas refrigerant is decreased to increase the refrigerating capacity. At the same time, the energy is used for the liquid compression energy of the expander refrigerant circuit 7. Thus, the power consumption of the electric motor used as the driving power for the liquid pump 27 can be reduced, and the energy efficiency improvement effect of two birds with one stone can be expected.

The diversion ratio of the diverter 26 is roughly determined by the size and shape of the expansion / compression portion. In the shunt of this embodiment, as shown in FIG. 5, a cylindrical rotor with a helical blade that revolves without rotating itself while contacting the outer periphery with the inner wall of the cylinder is used as a compressor and an expander. It uses a so-called helical compressor / expander, in which helical blades made of resin are wound around continuous grooves formed in a helical shape on the rotor, and the liquid flow ratio is 50% / 50 depending on the setting of the pitch dimension between the blades. % Is set.

Therefore, when the exhaust heat temperature of the system 1 decreases or when the output chilled water temperature of the utilization system 2 decreases, the thermal output temperature decreases and becomes lower than the above-described 60 ° C. In order to maintain and continue this output temperature even when the output temperature is lowered, it is necessary to adjust the refrigerant circuit. For this purpose, the electric liquid compression pump 27 is operated, and the compression-side flow rate is adjusted so as to obtain an appropriate diversion ratio. Increase the operating condition of the refrigerant circuit. The liquid compression pump 27 is a gear pump driven by an electric motor, and is effectively used when the exhaust heat temperature of the system 1 is lowered to 90 ° C. or less. The above are specific examples of claims 10, 11, and 13.

There are two problems in realizing this embodiment. This corresponds to the lubrication of the expander 23 and the failure, wear prevention, and response to natural refrigerant leakage. The cylinder of the expander 23 contains a high-pressure gas, and has a high pressure and a high temperature. Therefore, a wide range of temperature characteristics of the lubricating oil for lubricating it (with a kinematic viscosity of 7.0 mm / s or more at 100 ° C. and a pour point of − 25 degrees C or less) and the characteristic which is hard to deteriorate is required. At the same time, how to supply the lubricating oil 111 to the sliding portion of the cylinder in a high pressure state is a big problem. The technique of claim 14 is invented as a simple and reliable method, and a specific example thereof is shown by the installation of the lubricating oil pipe 31. This has the advantage of bypassing the lubricating oil when it passes through the hot water output heat exchanger 12 which is a condenser, so that the condensation performance is lowered. In addition, the effect of stabilizing the compression characteristics by the oil seal function of the sliding portion is also produced, and the lubricating oil is reliably circulated as long as the expander refrigerant circuit 7 is operating.

Natural refrigerants, unlike fluorocarbon refrigerants, are superior in terms of environmental impact, but there are basic problems in handling due to high pressure, combustibility, explosiveness, and toxicity to human bodies as familiar problems. In the present invention, the output utilization system 2 is selected based on the superiority of the previous operation, and a basic countermeasure technique is invented to solve the problems described later. That is, as can be seen from the embodiment of FIG. 2, the refrigerant circuit is a hermetically sealed type, and the system is housed in an integral housing unit and has no influence on leakage in installation work on site. Further, as shown in claim 19, the power supply controller incorporates various safety monitoring and specific measures in case of emergency. In addition, it is installed in an outdoor space separated from the use side, particularly the indoor side, and is embodied on the basic concept of transporting hot and cold heat by water or the like. The overall concept of the output utilization system 2 proposed by the present invention and many items related to its realization are assembled based on the basic technical concept described above.

Overview of the entire cogeneration system using an embodiment of the present invention Output utilization system schematic diagram showing an embodiment of the present invention Schematic diagram of the electric expansion compressor used in the system Horizontal cross-sectional structure schematic of the expander part Schematic structure of the liquid shunt used in the system

Explanation of symbols

1 Cogeneration system (System 1)
2 Cogeneration output utilization system (Output utilization system 2)
3 Cogeneration Fuel 4 Electric Output 5 Waste Heat Source Hot Water Output 6 Waste Heat Utilization Heat Exchanger 7 Expander Refrigerant Circuit 8 Refrigeration Cycle 9 Electric Expansion Compressor 10 Cold Output Heat Exchanger 11 Cold Water 12 Heat Output Heat Exchanger 13 Hot water 14 Outdoor heat exchanger 15 Outdoor air 16 Motor power supply 17 Power conversion device 18 Output power reverse power flow point 19 Power supply controller 20 Commercial line power supply 21 Supply power supply 22 Illuminating lamp 23 Expander 24 Motor 25 Compressor 26 Liquid shunt ( (Including expander and compressor)
27 Liquid pump 28 Electric refrigerant control valve (for heating / cooling output)
29 Electric refrigerant control valve (for thermal output)
30 Electric refrigerant control valve (for cold output)
31 Lubricating oil pipe 32 Heating circuit 33 Refrigerant circuit (consisting of 7 and 8)
101 motor stator 102 shaft 103 motor rotor 104 discharge pipe 105 flame 106 refrigeration cycle suction pipe 107 shell 108 expander cylinder 109 roller 110 high pressure gas supply line 111 lubricating oil 112 high pressure gas 113 expander compressor center flame 114 compressor cylinder 115 partition blade 116 high pressure gas supply point (roller)
117 High pressure gas supply point (crank)
201 liquid refrigerant inlet 202 rotating body (compressor)
203 High pressure liquid outlet 204 rotator (expander)
205 Low pressure refrigerant outlet 206 Helical blade 207 shaft (liquid shunt)
208 cranks

Claims (19)

An expander refrigerant circuit including an expander that expands a high-temperature high-pressure gas refrigerant obtained by heating with exhaust heat that is an output of a cogeneration apparatus, and a compressor that is driven by the output of the expander In a system in which the refrigerant circuit is configured by a refrigeration cycle,
It is configured to output warm heat from both the condensation heat of the refrigerant after expansion in the expander refrigerant circuit and the condensation heat of the refrigerant after compression in the refrigeration cycle, and to output cold heat from the evaporation heat of the refrigerant in the refrigeration cycle. And a mode that outputs cold and heat at the same time, and a mode that switches the circuit of the refrigeration cycle so that one of the heat and cold heat is exchanged with outdoor air and only the other heat is output. Cogeneration output utilization system characterized by An expander refrigerant circuit including an expander that expands a high-temperature high-pressure gas refrigerant obtained by heating with exhaust heat that is an output of a cogeneration apparatus, and a compressor that is driven by the output of the expander In a system in which the refrigerant circuit is configured by a refrigeration cycle,
The compressor can be driven not only by the output of the expander but also by the output of an electric motor using cogeneration output power or commercial power, and the output of the expander or the output of the electric motor A cogeneration output utilization system characterized in that the compressor is driven by appropriately selecting one of the outputs obtained by combining either or both, thereby enabling the refrigeration cycle to operate. A selection mode in which one of the compressor driving methods shown in claim 2 is selected and one of the output modes related to heating and cooling shown in claim 1 is selected and the two options are freely combined. The cogeneration output utilization system is characterized in that the system can be operated with the selection mode changed or continued as necessary. As the working medium of the refrigerant circuit, a refrigerant having a critical point temperature of 90 ° C. or higher and a saturation pressure at 60 ° C. of 4.0 MPa or lower is used, and exhaust gas for exchanging heat between the cogeneration exhaust heat transfer fluid and the refrigerant is used. The cogeneration output utilization system according to any one of claims 1, 2, and 3, wherein in the heat utilization heat exchanger, both fluids are made to flow in the form of a counter flow to promote heat exchange. . For the purpose of using not only the exhaust heat output of the cogeneration apparatus but also the power output or commercial power of the cogeneration apparatus as a power source for driving the compressor, the expander and the compressor are installed in a shell. Furthermore, the electric motor is installed, the expander is configured to be switched to a release mode in which gas is not expanded or compressed even when rotated in the expansion mode, and the electric motor employs an induction electric motor and the input power It is configured so that the compressor can be driven by selecting either the expander alone, or both of the expander and the electric motor, or only the electric motor. The cogeneration output utilization system according to any one of claims 2 and 3, wherein The refrigerant circuit in the previous period is provided in an integral casing unit, and is a so-called closed closed circuit that does not communicate with the outside, and a thermal output heat exchanger that dissipates the heat of refrigerant condensation provided on the circuit, and the refrigerant Heat and cold are output by a cold output heat exchanger provided in the refrigeration cycle in the circuit and cooled by refrigerant evaporative heat, and the heat and water are nonflammable and nontoxic natural heat medium such as water and carbon dioxide By implementing heat transfer to a machine body or device that stores or uses hot / cold heat provided outside the unit, etc., it is realized by any one of cooling, heating, hot water supply and cooling, or a combination thereof. The cogeneration output utilization system according to any one of 2, 3, 4, and 5 In the first refrigeration cycle, the thermal output heat exchanger, the cold output heat exchanger are installed, and an air heat exchanger that exchanges heat with outdoor air is installed in the middle of the refrigerant circuit of both heat exchangers, Change and adjust the temperature of the air heat exchanger by controlling the front and back control valves, etc., switching its function to three ways: heat release to the outside air, heat absorption from the outside air, and no heat exchange, The cooling capacity and heating capacity of the refrigeration cycle can be adjusted, and the system can output by switching only three types of modes, that is, only cold heat, only warm heat, and both warm and cold, respectively. The cogeneration output utilization system according to any one of 2, 3, 5, and 6. 6. The exhaust heat utilization heat exchanger for transferring heat to the expander refrigerant circuit, the expansion compressor or the electric expansion according to claim 4 or 5, wherein the refrigerant circuit and components constituting the refrigerant circuit, that is, the heat generated by the cogeneration apparatus are transferred to the expander refrigerant circuit. The compressor, the thermal output heat exchanger that outputs the heat from the refrigerant circuit, the outdoor air heat exchanger that is provided in the refrigeration cycle and exchanges heat with the outdoor air, and the cold output that outputs the cold from the refrigeration cycle All parts such as a heat exchanger are incorporated into an integral housing unit as an integral refrigerant circuit, and the entire refrigerant circuit is configured only by an integral material and their brazing and welding joints, that is, a machine. The cogeneration output utilization system according to any one of claims 1, 2, 3, 4, 5, 6, and 7, wherein the system does not have a mechanical coupling portion.   The same refrigerant is used as a circulation medium in the expander refrigerant circuit and the refrigeration cycle, and the expander and the compressor are installed in the shell in a state of being connected by an integral shaft, and the expander and the The expanded and compressed gas refrigerant from the compressor is discharged into the shell and joined together, and it is led integrally from the shell to the outside, and both heats of condensation are radiated by the thermal output heat exchanger, 9. The system according to claim 4, 5, 6, 7, or 8, wherein a portion between the output of the heat and the branching of the expander refrigerant circuit and the refrigeration cycle by a liquid flow divider is an integrated refrigerant circuit. The cogeneration output utilization system according to any one of the above. In the liquid diverter, an expander and a compressor are used to recover power from refrigerant expansion from the refrigerant toward the refrigeration cycle and to use it as power for increasing the pressure of the refrigerant toward the expander refrigerant circuit. 10. An expansion / compression diverter having a structure in which two rotating bodies operating as a child are connected and held in a housing is used, thereby diverting to the expander refrigerant circuit and the refrigeration cycle. Cogeneration output utilization system described. The liquid pump is installed in a circuit on the side of the expander refrigerant circuit downstream of the liquid flow divider incorporating the rotating body as the expander and the compressor, and complements the compression function of the compressor as necessary. The liquid pump is installed in a circuit on the side of the expander refrigerant circuit downstream thereof using a liquid shunt that does not have a rotating body that operates inside, and the liquid refrigerant is formed only by the liquid pump. The cogeneration output utilization system according to any one of claims 9 and 10, wherein the system is compressed. The refrigerant circulating in the refrigerant circuit is a so-called natural refrigerant having a global warming potential, that is, a GWP value of less than 150, that is, a refrigerant having a chlorine content of zero and a fluorine-containing molecular weight of less than that of hydrogen. The cogeneration output utilization system according to any one of claims 4, 5, 6, 7, 8, and 9, wherein a refrigerant mainly comprising carbon, hydrogen, nitrogen, or the like is used. The high-pressure gas refrigerant generated by heating in the expander refrigerant circuit expands itself and drives the expander, and is then compressed by the compressor in the refrigeration cycle and pressurized by the refrigerant gas discharged into the shell 6. The refrigerant gas discharged into the shell after being discharged from the shell together and condensed in the thermal output heat exchanger causes the heat output from the heat to be output by hot water or the like. The cogeneration output utilization system according to any one of 9 and 9. Lubricating oil is sealed in the expander and the shell in which the compressor operates to lubricate the expansion and compression mechanism, and a pipe line communicating from the outside of the shell to the lubricating oil near the bottom of the shell is installed. Thereby removing the lubricating oil, while connecting the other end of the conduit to the inlet of the liquid pump in the expander refrigerant circuit or the inlet of the liquid compressor in the flow divider, thereby 14. The expander refrigerant circuit is circulated together with the refrigerant in the expander refrigerant circuit, and the expander cylinder is lubricated by the circulated lubricant oil. The cogeneration output utilization system according to item 1. 13. The cogeneration output utilization system according to claim 4, wherein isobutane, propane, ammonia, Freon C 2 H 4 F 2 or a mixed refrigerant containing 50% or more by weight of these components is used as the cycle refrigerant. A control device for controlling the system is provided, and setting control of the entire operation mode is performed, and among them, at least a user sets usage priorities such as power, hot water supply, heating, and cooling, or commercial power 3. A control system in which a method using the electric motor of the compressor driving method is set to be automatic or can be selected according to a user's request according to a fee-based fee preferential system is incorporated. The cogeneration output utilization system according to any one of 3 and 8. With the thermal output medium that has been heated by the thermal output heat exchanger and then increased in temperature after the thermal heat that is a medium of the exhaust heat source of the cogeneration apparatus is radiated by the exhaust heat utilization heat exchanger and the temperature is lowered. The heat output is further increased by further exchanging heat with certain warm water and the like, further heating the warm water as the thermal output medium to increase the temperature, and further increasing the heat output in addition to the total amount of heat of claim 13. 14. The cogeneration output utilization system according to any one of items 13 to 13. 6. The scroll blade type or rolling piston type expander, the compressor and the electric motor are installed in the shell in such a relationship that the expander and the electric motor can drive the compressor. Therefore, when the compressor is driven only by the electric motor, the expander moves or operates in the release operation according to claim 5, that is, in the scroll type of the expander, the entire fixed blade or the open / close passage provided therein. In the rolling piston type, the high and low pressure partition blades are pushed out of the cylinder and fixed to release the partition of the high and low pressure chambers. On the other hand, when driven by the expander alone, the power circuit output is turned off so that the rotary rotor of the front electric motor is idle. When both the expander and the electric motor are driven, both the rotational speed and the voltage are controlled and adjusted so that the power supply circuit of the motor has an output necessary for supplementing the driving force of the expander. 5. The construction and operation according to claim 2, wherein the driving is performed by switching only at least two of the driving by the expander, the driving by the electric motor, and the driving by both. 5. The cogeneration output utilization system described in any one of 5 above. The system is provided with a refrigerant leak detection device, and when it detects a refrigerant leak, the control system according to claim 15 adopts safety measures such as operation stop and power shut-off, and abnormality in the cogeneration device. The cogeneration system according to any one of claims 4, 5, 7, 9, 10, 12, and 15, wherein a control system for issuing a request for stopping or the like, or incorporating a control system such as a warning display by an emergency power source is incorporated. Rate output system

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