JP2007255862A - Air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioning system having improved efficiency by supercooling refrigerant in a compression refrigerator, and having compact construction for reducing cost for maintenance or others. <P>SOLUTION: The air conditioning system comprises a compression air-conditioner 100 having a first refrigerant line L1, a branch refrigerant line L3, and a second compressor 12, the branch refrigerant line being mounted with a third heat exchanger 4, and a second refrigerant line L2 mounted with a refrigerant evaporator 6 for evaporating refrigerant with exhaust heat charged from a hear source machine 6, an ejector 7, and a fourth heat exchanger 8 for heat exchange between refrigerant flowing in the second refrigerant line and outside air. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an air conditioning system that performs air conditioning (cooling and heating) using a compression air conditioner (compression refrigerator) that performs a compression cycle using a compressor (compressor).

A compression refrigeration cycle for performing refrigeration using a compressor (compressor) is well known.
When implementing this compression refrigeration cycle, the high-pressure liquid-phase refrigerant condensed in the condenser is supercooled using an absorption refrigeration cycle using exhaust heat as a drive heat source, thereby improving efficiency. Is done in the prior art.
FIG. 28 shows such a prior art.

In FIG. 28, the compression refrigerator 100 includes a compressor 1, an indoor unit 2 that is an evaporator, an outdoor unit 3 that is a condenser, and a refrigerant line L1 that includes a pressure reducing valve CV2.
The high-pressure liquid-phase refrigerant condensed by the condenser 3 is cooled (supercooled) by the evaporator 301 of the hot water-absorbing absorption refrigerator 300 before being decompressed by the decompression valve CV2.
Here, the hot water-fired absorption refrigerator 300 is configured such that the exhaust heat (hot waste water) of the gas engine 5 is supplied to the regenerator 303. On the other hand, the compressor 1 of the compression refrigerator 100 is a mechanical compressor that is driven by transmission of a mechanical output from the drive shaft 51 of the gas engine 5.
In FIG. 28, the code | symbol 302 shows the absorber in the warm water soaking absorption refrigerator 300, and the code | symbol 304 shows the condenser in the warm water soaking absorption refrigerator 300. In FIG.

  In addition, the refrigerant circulation system of the compression refrigerator is branched in the middle, and one of the branched refrigerant circulation pipes communicates with the evaporator of the hot-water absorption absorption refrigerator, and the compression refrigeration flowing through the refrigerant circulation pipe A conventional technique in which the refrigerant of the machine is cooled by an evaporator of a hot water-fired absorption refrigerator has also been proposed by the present applicant (see Patent Document 1).

However, absorption refrigerators are generally large in size and require a large installation space. Therefore, when only a small installation space can be provided, it is difficult to implement the prior art of FIG. 28 or the above-described prior art (Patent Document 1).
In addition, since the refrigerant and absorption solution of the absorption refrigeration machine are different from the refrigerant of the compression refrigeration machine, in order to implement the conventional technique of FIG. 28 or the above-described conventional technique (Patent Document 1), a plurality of media ( Refrigerant (absorbing solution) must be handled, and there is a problem that much labor is required for installation and maintenance.

Furthermore, in the case of an absorption refrigerator, a high degree of vacuum is required, and there is a problem that the labor for installation and maintenance is large.
In addition, in general, absorption refrigerators are more expensive to purchase than compression types.
For the above reasons, there are users who hesitate to implement the prior art of FIG. 28 or the above-described prior art (Patent Document 1).
JP 2000-244102 A

  The present invention has been proposed in view of the above-mentioned problems of the prior art, and it is possible to increase the efficiency by supercooling the refrigerant of the compression refrigerator, while being compact and reducing maintenance and other costs. The purpose is to provide an air conditioning system that can do this.

The air conditioning system of the present invention includes a first heat exchanger (indoor unit 2) that performs heat exchange between the first compressor (11), the refrigerant and indoor air that is to be air conditioned, and heat exchange with outside air. A second heat exchanger (outdoor unit 3) to be performed, a first compressor (11), a first heat exchanger (indoor unit 2), and a second heat exchanger (outdoor unit 3) are interposed. First refrigerant line (L1), a branch refrigerant line (L3) branched from the first refrigerant line (L1), and a second compressor (12) interposed in the branch refrigerant line (L3) And a third heat exchanger (refrigerant supercooler 4) is interposed in the branch refrigerant line (L3), and a third heat exchanger (compressor refrigerator 100) is provided. The second refrigerant line (of the steam injection refrigeration cycle) that exchanges heat with the refrigerant flowing through the branch refrigerant line (L3) in the heat exchanger (refrigerant supercooler 4) The exhaust gas from the heat source device (for example, the gas engine cogeneration system 5) is input to the second refrigerant line (refrigerant line L2 of the vapor injection refrigeration cycle) to evaporate the refrigerant. A refrigerant evaporator (front boiler 6), an ejector (7), and a fourth heat exchanger (8) for exchanging heat between the refrigerant flowing through the second refrigerant line (L2) and the outside air are interposed. The second refrigerant line (L2) communicates with the first branch line (L21) communicating with the refrigerant evaporator (front boiler 6) and the diffuser side suction portion (71) of the ejector (7). Branching to a branch line (L22) (B21), and the third heat exchanger (refrigerant subcooler 4) is interposed in the second branch line (L22) ( Claim 1).
In this specification, an air conditioner having a compression cycle is described as a “compression air conditioner” when it should be considered also during heating operation. However, when only the cooling operation needs to be considered, "Refrigerating machine" or "Compression refrigeration cycle". Similarly, when only the refrigeration cycle needs to be considered for the part that performs the steam injection refrigeration cycle, it is described as a “steam injection refrigeration cycle”. May be written.
Further, in this specification, the term “indoor unit” means a heat exchanger provided indoors, and the term “outdoor unit” means a heat exchanger provided outdoors. The indoor unit functions as an evaporator during cooling, and functions as a condenser during heating. On the other hand, the outdoor unit acts as a condenser during cooling, and acts as an evaporator during heating.

  In the present invention, the second heat exchanger (the outdoor unit 3 of the compression air conditioner) and the fourth heat exchanger (8) are configured separately, and the first refrigerant line (L1). What is the area where the second heat exchanger (compressor air conditioner outdoor unit 3) is interposed in and what is the area where the fourth heat exchanger (8) is interposed in the second refrigerant line (L2) It can be configured separately (claim 2).

  Alternatively, in the present invention, the second heat exchanger (the outdoor unit of the compression air conditioner) and the fourth heat exchanger are integrally formed (38), and the first refrigerant line (L1). The region where the second heat exchanger (compressor air conditioner outdoor unit) is interposed and the region where the fourth heat exchanger is interposed in the second refrigerant line (L2) are integrated (38). (Claim 3).

  In the present invention, a flow path switching device (for example, a four-way valve V4) is interposed in the first refrigerant line (the refrigerant line L1 of the compression air conditioner), and the first refrigerant line (L1) is connected to the first refrigerant line (L1). It is preferable that the direction in which the circulating refrigerant flows can be reversed (thus, the cooling operation and the heating operation can be switched) (claim 4).

  Further, in the present invention, a fifth heat exchange in which the exhaust heat from the heat source device (for example, the gas engine cogeneration system 5) is input to the refrigerant flowing through the first refrigerant line (the refrigerant line L1 of the compression air conditioner). It is preferable to provide a heat exchanger (exhaust heat heat exchanger 9) (Claim 5).

  Furthermore, in the present invention, it is preferable that the second refrigerant line (refrigerant line L2 of the vapor injection refrigeration cycle) has a bypass line (L2b) that bypasses the ejector (7).

According to the present invention having the above-described configuration, the second refrigerant line (the refrigerant line L2 of the vapor injection refrigeration cycle) includes a refrigerant evaporator (front boiler 6), an ejector (7), and a third heat exchanger. (Refrigerant subcooler 4) and the fourth heat exchanger (8) constitute a vapor injection refrigeration cycle, and the compression air conditioner (100) exchanges the first compressor (11) with the first heat. A branched refrigerant line (L3) branched from the first refrigerant line (L1) in which the chamber (indoor unit 2) and the second heat exchanger (outdoor unit 3) are interposed, the branched refrigerant line A third heat exchanger (refrigerant supercooler 4) is interposed in (L3) (claim 1).
Therefore, during the cooling operation, the refrigerant flowing through the branch refrigerant line (L3) of the compression air conditioner (100) generates heat of vaporization in the refrigerant flowing through the steam injection refrigeration cycle side line L22) by the supercooling heat exchanger (4). To cool and condense. And since it merges with the 1st refrigerant | coolant line (L1) (junction point B12), the burden of a 1st compressor (11) becomes small by the part which was cooled and condensed by the supercooling heat exchanger (4). , Cooling efficiency is improved.

  According to the present invention, since the second compressor (12) is interposed in the branch refrigerant line (L3) of the compression refrigeration cycle (Claim 1), the first refrigerant is used during the cooling operation. The temperature in the supercooling heat exchanger (4) can be made higher than the first heat exchanger (indoor unit 2) interposed in the line (L1). Therefore, the load on the steam injection refrigeration cycle side can be reduced, and further miniaturization can be achieved.

Here, in the vapor injection refrigeration cycle, only one type of refrigerant circulates, and chlorofluorocarbon can be used as the refrigerant, so that it is easier to handle than an absorption refrigerator.
Further, since the steam injection refrigeration cycle is composed of only the heat exchangers (6, 8), the ejector (7), and the pipe (L2) (the exhaust heat boiler or the front boiler 6) is a mere heat exchanger. ), Compact, and the manufacturing cost and maintenance cost of the steam injection refrigeration cycle are extremely low.
Therefore, the problem in the air conditioning system (system shown in patent document 1 and FIG. 28) which combined the absorption refrigerator with the compression refrigerator of the prior art can be eliminated.

  Further, the steam injection refrigeration cycle is easy to air-cool, and has the advantage that the problem of crystallization does not occur as in the absorption refrigerator.

Here, it is possible to use the same refrigerant in the vapor injection refrigeration cycle and the compression cycle.
Therefore, in the present invention, a part of the steam injection refrigeration cycle (part of L20) and a part of the compression cycle side (not labeled in the same region as L20) are made common to reduce the number of parts. Various costs can be reduced.
Specifically, in the present invention, the second heat exchanger (the outdoor unit of the compression air conditioner) and the fourth heat exchanger are integrated (38), and the first refrigerant line ( The region where the second heat exchanger (outdoor unit of the compression air conditioner) in L1) is interposed and the region where the fourth heat exchanger is interposed in the second refrigerant line (L2) are integrated. (38) It is possible to do (Claim 3), the structure can be simplified, the number of parts can be reduced, and maintenance and other costs can be reduced.

  Further, in the present invention, the refrigerant flowing in the refrigerant line (first refrigerant line L1) of the compression air conditioner (100) is configured to be reversible so that the cooling operation and the heating operation are switched. Since it can be configured (Claim 4), it is possible to achieve a comfortable indoor environment by performing cooling operation in summer and heating operation in winter.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
Note that members similar to those illustrated in FIG. 28 are denoted by the same reference numerals.
In the illustrated embodiment, the compression type air conditioner 100 is described as “compression type air conditioner” when the heating operation should be considered, but when only the cooling operation needs to be considered, the “compression type air conditioner” is described. "Refrigerator" or "compression refrigeration cycle".
Similarly, when only the refrigeration cycle needs to be considered for the steam injection refrigerator 200, it may be described as a “steam injection refrigeration cycle”.

First, a first embodiment will be described with reference to FIGS.
FIG. 1 is a block diagram showing an overall configuration according to the first embodiment, FIG. 2 shows a state in which the air conditioner system of the first embodiment is in cooling operation, FIG. 3 shows a state in which heating operation is performed, 4 shows the air-conditioning operation control of the first embodiment by a flowchart.

  In FIG. 1, in the air conditioning system of the first embodiment, the absorption cycle of FIG. 28 (prior art) is replaced with a vapor injection refrigeration cycle, and in the compression refrigeration cycle, the refrigerant line branches in the middle and merges. is doing.

The compression type air conditioner 100 exchanges heat between the first compressor 11, a first heat exchanger (indoor unit) 2 that performs heat exchange between the refrigerant and indoor air to be air-conditioned, and the refrigerant and outside air. The 2nd heat exchanger (outdoor unit) 3 which performs and the 1st refrigerant line (refrigerant line of a compression type air conditioner) L1 are provided.
The first compressor 11 is driven by the output shaft 51 of the gas engine 5. As a result, the compression air conditioner 100 of FIG. 1 constitutes a so-called “gas engine heat pump”.

In the first refrigerant line L1, a first branch point B11 and a second branch point B12 are formed. The first refrigerant line L1 branches or merges with the branch refrigerant line L3 at the first and second branch points B11 and S12.
A flow path switching device (four-way valve) V4 for switching the flow path between the cooling operation and the heating operation is interposed in the first refrigerant line L1.
The position of the first branch point B11 and the second branch point B12 will be described in more detail with reference to the time of the refrigeration operation of FIG. 2 (from the indoor unit 2 of the first refrigerant line L1) (at the time of the refrigeration operation). A first branch point B11 (branch point at the time of cooling operation) is provided in a region facing the flow path switching device (four-way valve) V4, and a region facing the indoor unit 2 from the first flow control valve (expansion valve) CV1. A second branch point B12 (confluence point during cooling operation) is provided. Then, the branch refrigerant line L3 branches from the first branch point B11 (branch point during cooling operation), and the branch refrigerant line L3 is the first refrigerant line at the second branch point B12 (confluence point during cooling operation). Join L1.

  In FIG. 1 again, the first refrigerant line L1 includes refrigerant lines L11 to L17, and each refrigerant line communicates with the first compressor 11, the four-way valve V4, the outdoor unit 3, and the indoor unit 2. Thus, a circulation path is formed.

  Here, the line L11 connects the discharge side of the first compressor 11 and the port V4a of the four-way valve V4. The line L12 connects the port V4b of the four-way valve V4 and the outdoor unit 3. Line L13 interposes flow control valve CV1, and connects outdoor unit 3 and second branch point B12, which will be described later. The line L14 connects the second branch point B12 and the indoor unit 2. A line L15 connects the indoor unit 2 and the first branch point B11. The line L16 connects the first branch point B11 and the port V4c of the four-way valve V4. The line L17 connects the port V4d of the four-way valve V4 and the suction side of the compressor 1.

The branch refrigerant line L3 includes a line L31, a line L32, and a line L33, and includes a second compressor 12, a third heat exchanger (refrigerant subcooler) 4, and a flow rate adjustment valve CV2. is doing.
The refrigerant subcooler 4 interposed in the line L32 exchanges heat between the refrigerant circulating in the branch refrigerant line L3 and the refrigerant flowing in the refrigerant line L2 (second refrigerant line) of the vapor injection refrigerator 200 described later. I do.
The second compressor 12 is configured to be driven by, for example, drive transmission means D, and the drive transmission means D engages with the drive shaft 51 for the first compressor 11 to transmit the driving force.
Although not shown, a clutch mechanism is provided in the middle of the drive transmission means D or on the second compressor 12 side, and the drive transmission from the first compressor 11 to the second compressor 12 is cut off.・ It is configured to be freely connectable.

The line L31 is provided with an on-off valve V3 and connects the first branch point B11 and the suction side of the second compressor 12. The line L32 connects the discharge side of the second compressor 12 and the refrigerant subcooler 4. The line L33 is provided with a second flow rate control valve CV2, and connects the refrigerant subcooler 4 and the second branch point B12.
Here, in the refrigerant subcooler 4, during the cooling operation shown in FIG. 2, the refrigerant flowing through the branch refrigerant line L3 flows (in the subcooling heat exchanger 4) through the second refrigerant line L2 on the vapor injection refrigeration cycle side. The refrigerant is given heat of vaporization, cooled and condensed. Then, the cooled and condensed liquid phase refrigerant merges with the low-pressure liquid phase refrigerant flowing through the first refrigerant pipe L1 at the second merge point B12. That is, during the cooling operation shown in FIG. 2, the burden on the first compressor 11 is reduced by the amount cooled and condensed by the supercooling heat exchanger 4, and the cooling efficiency is improved.

Here, when the second compressor 12 is not interposed, the internal temperature of the indoor unit 2 and the supercooling heat exchanger 4 must be approximately the same during the cooling operation. On the other hand, if the second compressor 12 is interposed in the branch refrigerant line L3, the temperature in the supercooling heat exchanger 4 does not need to be the same as the temperature of the indoor unit 2, and the supercooling heat exchange is performed. The temperature inside the chamber 4 can be made higher than the temperature of the indoor unit 2.
If the temperature in the supercooling heat exchanger 4 becomes high, the supercooling heat exchanger 4 flows through the refrigerant line L3 on the compression refrigerator 100 side even if the temperature of the refrigerant circulating in the steam injection refrigeration cycle is not low. The refrigerant can be relatively cooled, and the load on the steam injection refrigeration cycle side can be reduced accordingly. Further, it is possible to further reduce the size of the steam injection refrigeration cycle.

In FIG. 1, a steam injection refrigerator 200 that performs a steam injection refrigeration cycle includes a heat source unit (for example, a gas engine) 5, a refrigerant evaporator (front boiler) 6 that evaporates a refrigerant, an ejector 7, and a second refrigerant line. L4 and a fourth heat exchanger (condenser) 8 that performs heat exchange between the refrigerant flowing through the second refrigerant line L2 and the outside air. Here, in the front boiler 6, exhaust heat from the gas engine 5 is input through the exhaust heat line Lw to evaporate the internal liquid phase refrigerant.
In FIG. 1, the code | symbol P1 shows a water supply pump, and the water supply pump P1 circulates the cooling water holding the exhaust heat of the gas engine 5 in the exhaust heat line Lw.

Between the fourth heat exchanger (condenser) 8 of the steam injection refrigerator 200 and the outdoor unit 3 that is the second heat exchanger of the compression air conditioner 100, although not clearly shown in the figure, the wind A path A and an air path B are formed.
In the air path A, the outside air heated by the condenser 8 (by exchanging heat with the refrigerant circulating in the refrigerant line L2) does not pass through the outdoor unit 3 of the compression type air conditioner 100 and circulates in the compression type air conditioner 100. It is an air path (flow path) comprised so that heat exchange may not be carried out with the refrigerant | coolant to perform. This is because the air path A is selected during the cooling operation (see FIG. 2) and the condensation capacity in the outdoor unit 3 is prevented from being reduced by the outside air heated by the condenser 8.
On the other hand, the air passage B is an air passage through which the outside air whose temperature has been raised in the condenser 8 (heat exchanged with the refrigerant circulating in the refrigerant line L2) passes through the outdoor unit 3. During the heating operation (FIG. 3), the air passage B is selected, and a larger amount of heat is supplied to the refrigerant on the compression air conditioner 100 side that flows through the outdoor unit 3.

  The second refrigerant line L2 of the steam injection refrigerator 200 includes a line L20 including a pressure sensor 10, an on-off valve V1, an ejector 7, and a fourth heat exchanger (condenser) 8, and a line L20 at a branch point B21. It consists of a first branch line L21 and a second branch line L22 branched at. The first branch line L21 communicates with the front boiler 6 via the refrigerant pump P2. The second branch line L22 is provided with the pressure reducing valve V2 and the refrigerant subcooler 4 and communicates with the side suction portion 71 of the ejector 7.

  In the steam injection refrigerator 200, the liquid refrigerant (liquid phase CFC) evaporates in the CFC boiler 6 into which the exhaust heat of the gas engine 5 is input. The vapor-phase refrigerant (fluorocarbon vapor) generated by evaporation is sucked into the ejector 7 through the refrigerant line L20 (the left side of the ejector 7 in the figure) and from the ejector 7 at a high speed (in the figure, the ejector 7). Injected from the right). At that time, the gas-phase refrigerant (Freon vapor) flowing through the second branch line L22 is sucked from the side suction portion 71 of the ejector 7, and the gas-phase refrigerant sucked through the line L20 inside the ejector 7 It merges and is injected into the condenser 8 of the line L20.

The gas-phase refrigerant injected from the ejector 7 is condensed by the condenser 8 to become a liquid-phase refrigerant, and then branches to the first line L21 and the second line L22 at the branch point B21.
The liquid-phase refrigerant that has flowed into the first line L21 is returned to the front boiler 6 via the refrigerant pump P2.
The liquid-phase refrigerant flowing into the second line L22 from the branch point B21 is depressurized by the pressure reducing valve V2, and then from the side suction portion 71 via the refrigerant subcooler 4 that is the third heat exchanger. It is sucked into the ejector 7. In the cooling operation of FIG. 2, the liquid-phase refrigerant that has flowed into the second line L22 from the branch point B21 evaporates by taking heat of vaporization from the refrigerant circulating on the compression refrigerator 100 side in the refrigerant subcooler 4. To do.

  In the vapor injection refrigeration cycle used in the configuration shown in FIG. 1, the circulating fluid is only one type of refrigerant (Freon in FIG. 1). The fluid does not circulate. In the vapor injection refrigeration cycle, the same refrigerant as the compression refrigerator can be used, and of course, chlorofluorocarbon can be used as the refrigerant.

Here, the COP of the steam injection refrigeration cycle is, for example, 0.15, and the steam-fired single effect absorption COP is, for example, 0.7.
That is, the COP of the steam injection refrigeration cycle is very low compared to the steam-fired single effect absorption type.

  As described above, in an air conditioning system (system shown in Patent Document 1 and FIG. 28) in which an absorption refrigerator is combined with a compression refrigerator, the size of the absorption refrigerator is large, and a large installation space is required. Are expensive, and the fluid (refrigerant, absorbing solution) circulating through the absorption chiller is different from the refrigerant of the compression chiller, which increases the handling and maintenance costs. And have.

On the other hand, if it is a steam injection refrigeration cycle like embodiment of FIG. 1, it is comprised only with a heat exchanger (a waste heat boiler or a front boiler 6), the ejector 7, and piping (line L20, L21, L22). Therefore, it is compact and the manufacturing cost of the steam injection refrigeration cycle is extremely low.
Therefore, the problems related to “installation space” and “price” in the air conditioning system (the system shown in Patent Document 1 and FIG. 28) in which the absorption refrigerator is combined with the compression refrigerator of the prior art can be solved.

Further, as described above, the refrigerant used in the vapor injection cycle and the compression refrigerator can be the same refrigerant, so in the illustrated embodiment, an absorption refrigerator is added to the conventional compression refrigerator. In the combined air conditioning system (the system shown in Patent Document 1 or FIG. 28), the problem of “labor and labor associated with maintenance” can be solved.
Furthermore, it is possible to share the refrigerant and share a part of the vapor injection cycle and the compression refrigeration cycle, the details of which are described in the second and subsequent embodiments.

In addition to this, the vapor injection refrigeration cycle has an advantage that it is easy to air-cool against the absorption refrigerator that is difficult to air-cool because of the problem of crystallization.
Therefore, the condenser in the vapor injection refrigeration cycle and the outdoor unit of the compression refrigerator (condenser during cooling operation and evaporator during heating operation) can be integrated to perform air cooling, that is, heat exchange with outside air. .

  Further, in the illustrated embodiment using the steam injection refrigeration cycle, maintenance or the like is easy because the vacuum level is not as high as that of the absorption refrigerator.

In the first embodiment shown in FIG. 1, since the refrigerant line L1 on the compression refrigerator 100 side is branched L3, the supercooling heat of the steam injection refrigeration cycle during the cooling operation described later with reference to FIG. The exchanger 4 takes heat of vaporization, reduces the temperature of the refrigerant flowing through the branch refrigerant line L3 of the compression refrigerator 100, condenses, and condenses the refrigerant condensed at a low temperature at the junction B12 at the first refrigerant pipe. It merges with road L1. Then, in the supercooling heat exchanger 4 of the steam injection refrigeration cycle, the heat of vaporization is taken to lower the refrigerant temperature, and the amount of the first compressor 11 on the compression refrigerator 100 side (cooling) is reduced by the amount of refrigerant condensed at a lower pressure. ) The load is reduced and energy saving is achieved.
And at the time of the heating mentioned later with reference to FIG. 3, since the air heated with the condenser 8 of the steam injection refrigerating machine cycle heats the refrigerant | coolant by the side of the compression type air conditioner 100 which flows through the outdoor unit 3, only that much. The load on the compression air conditioner 100 side is reduced.

In 1st Embodiment shown in FIG. 1, not only cooling operation but heating operation is also possible. In other words, the first embodiment of FIG. 1 is configured to be capable of switching between the cooling and heating operations.
FIG. 2 shows the flow of refrigerant, the opening and closing of lines and various valves when the cooling operation is performed in the first embodiment. Hereinafter, the flow of the refrigerant during the cooling operation will be described with reference to FIG.
In FIG. 2 and subsequent figures, the direction of the arrow drawn on each refrigerant line indicates the direction of refrigerant flow.

First, the opening and closing of various sides and the flow of refrigerant on the compression refrigeration cycle side during the refrigeration operation will be described.
During the cooling operation, in the four-way valve V4, the port V4a and the port V4b communicate with each other, and the port V4c and the port V4d communicate with each other.
The high-pressure gas-phase refrigerant discharged from the first compressor 11 enters the line L12 from the line L11 via the ports V4a and V4b of the four-way valve V4, and the outdoor unit (condenser in the refrigeration operation of FIG. 2) 3 The gas-phase refrigerant condenses into a high-pressure liquid-phase refrigerant and exits the outdoor unit 3.

  The high-pressure liquid phase refrigerant exiting the outdoor unit 3 flows through the line L13 and is expanded by the flow rate control valve (expansion valve) CV1 to become a low-pressure liquid phase refrigerant. The second branch point B12 (confluence point during cooling operation), the line It flows into the indoor unit 2 (evaporator during cooling operation) 2 via L14. In the indoor unit 2, the low-pressure liquid-phase refrigerant takes vaporization heat from the indoor air to be cooled and evaporates, cools the indoor air, and then flows through the line L15 as a low-pressure gas-phase refrigerant. The low-pressure gas-phase refrigerant passes through the first branch point B11 (branch point during cooling operation), the line L16, the ports V4c and V4d of the four-way valve V4, and the line L17 to the suction side of the first compressor 11. Return.

Here, at the first branch point B11 (a branch point during cooling operation), a part of the low-pressure gas-phase refrigerant flows through the line L31 side and is compressed by the second compressor 12 to become a high-pressure gas-phase refrigerant. . And it flows in into the refrigerant subcooler 4 via line L32.
The high-pressure gas-phase refrigerant flowing in the line L32 is cooled (supercooled) by heat exchange with the gas-phase refrigerant flowing in the second refrigerant line L2 on the vapor injection refrigerator 200 side in the refrigerant subcooler 4, and condensed. Thus, it becomes a high-pressure liquid-phase refrigerant and flows into the line L33.
The liquid-phase refrigerant flowing through the line L33 is decompressed by the flow control valve CV2, and merges with the liquid-phase refrigerant flowing through the refrigerant line L1 (line L13) at the branch point B12 (confluence), and the indoor unit ( It flows into the evaporator 2.

  In the cooling operation of FIG. 2, as described above, the refrigerant flowing through the branch refrigerant line L3 causes the subcooling heat exchanger 4 to generate heat of vaporization in the refrigerant flowing through the second refrigerant line L2 on the steam injection refrigeration cycle side. Since it is cooled by being cooled (supercooled), condensed, and merged into the first refrigerant pipe L1, the burden on the first compressor 11 is reduced by the amount cooled (supercooled) by the supercooling heat exchanger 4. Thus, the cooling efficiency is improved.

Next, the opening and closing of various valves on the evaporative injection refrigeration cycle side (evaporative injection refrigeration machine 200 side) and the flow of refrigerant will be described.
When the cooling operation is started, the water pump P1 interposed in the line Lw starts to operate, and the exhaust heat from the gas engine 5 circulates through the front boiler 6 via the line Lw. Then, the liquid phase refrigerant in the front boiler 6 is heated.
Here, immediately after the start of cooling, the on-off valve V1 remains closed. On the other hand, the pressure reducing valve V2 of the line L22 is opened.

  As described above, the air path A is selected during the cooling operation, and the air heated by the condenser 8 does not exchange heat with the outdoor unit 3 of the compression refrigeration machine 100 and inhibits the condensation function of the outdoor unit 3. There is no.

  Since exhaust heat is input to the front boiler 6, the liquid refrigerant evaporates into a gas phase refrigerant, but the on-off valve V1 is closed, so that the pressure in the front boiler 6 measured by the pressure sensor 10 gradually increases. . When the pressure in the front boiler 6 exceeds a predetermined value (threshold value), the on-off valve V1 of the line L20 is opened, and the refrigerant pump P2 interposed in the line L21 is activated.

  The gas-phase refrigerant in the front boiler 6 is sucked into the suction side of the ejector 7 (the left side of the ejector 7 in the drawing) via the refrigerant line L20 and is injected at a higher speed than the injection side of the ejector 7 (the right side of the ejector 7 in the drawing). Is done. At that time, due to the negative pressure effect of the ejector 7, the gas-phase refrigerant on the line L22 side is sucked from the side suction portion 71 of the ejector 7, and merges with the gas-phase refrigerant sucked via the line L20 (Freon vapor).

The gas-phase refrigerant injected from the ejector 7 is condensed by the condenser 8 which is the fourth heat exchanger to become a liquid-phase refrigerant, and then branches and flows into the line L21 and the line L22 at the branch point B. .
The liquid-phase refrigerant that has flowed into the line L22 from the branch point B21 is depressurized by the pressure reducing valve V2, and then the refrigerant subcooler 4 that is the third heat exchanger in the compression refrigerator 100 side (refrigerant line L3 The vaporized heat is taken from the refrigerant (flowing) and evaporated to become a gas-phase refrigerant, which is sucked into the ejector 7 from the side suction portion 71.

  In the cooling operation shown in FIG. 2, as described above, the first refrigerant line L1 on the compression refrigerator 100 side is branched, so that the refrigerant flowing through the branch line L3 is deprived of heat of vaporization in the supercooling heat exchanger 4. Thus, the energy consumption of the compression refrigerator 100 is saved by the amount of temperature.

Next, the heating operation will be described with reference to FIG.
First, the opening and closing of various valves on the compression air conditioner 100 side and the flow of the refrigerant will be described.
During the heating operation, a clutch (not shown) on the second compressor 12 side is disengaged and the second compressor 12 is not operated, and only the first compressor 11 is operated.

During the heating operation, the port V4a and the port V4c of the four-way valve V4 communicate with each other, and the port V4b and the port V4d communicate with each other.
The high-pressure gas-phase refrigerant discharged from the first compressor 11 passes through the line L11 via the port V4a and the port V4c of the four-way valve V4, the line L16, the first branch point B11 (the branching and joining are performed during heating) No), it flows into the indoor unit 2 via the line L15.
In the indoor unit (condenser at the time of heating), the high-pressure gas-phase refrigerant is supplied to the indoor air to be heated and condensed to become a liquid-phase refrigerant. The liquid phase refrigerant condensed in the indoor unit 2 flows through the line L14 and the branch point B12 (not branched or merged during heating), and is decompressed by the flow rate adjustment valve CV1 to become a low-pressure liquid phase refrigerant. The low-pressure liquid-phase refrigerant flows through the line L13 and flows into the outdoor unit 3 (evaporator during heating).
During the heating operation, the on-off valve V3 interposed in the branch refrigerant line L3 is closed, so that no refrigerant flows on the branch refrigerant line L3 side.

In the outdoor unit 3, heat of vaporization from warm air (outside air heated by the condenser 8) flowing from the fourth heat exchanger 8 through the air passage B (switched to the air passage B during heating as described later). The low-pressure liquid-phase refrigerant evaporates into a low-pressure gas-phase refrigerant.
The low-pressure gas-phase refrigerant exiting the outdoor unit 3 is sucked into the compressor 11 via the line L12, the ports V4b and V4d of the four-way valve V4, and the line L17, compressed by the compressor 11, and discharged again to the indoor unit 2 side. Is done.

Next, the opening and closing of various valves and the flow of the refrigerant on the evaporative injection refrigerator 200 side will be described.
When heating is started, the water pump P1 interposed in the line Lw is activated, and the exhaust heat from the gas engine 5 is input to the front boiler 6 via the line Lw to heat the liquid-phase refrigerant. Immediately after the start of heating, the on-off valve V1 remains closed.
During the heating operation, the pressure reducing valve V2 of the line L22 remains closed, and no refrigerant flows on the line L22 side.

  Here, at the time of heating, as shown in FIG. 3, the air path B between the condenser 8 and the outdoor unit 3 is selected as the air path B, and the condenser 8 is heated by being supplied with heat of vaporization. The warm outside air exchanges heat with the refrigerant (low pressure liquid phase refrigerant) flowing through the line L13 flowing into the outdoor unit 3. That is, since the outside air heated by the condenser 8 passes through the outdoor unit 3, the amount of heat input to the refrigerant of the compression type air conditioner 100 in the outdoor unit 3 increases by the amount of heat of vaporization input by the condenser 8. To do. As a result, the refrigerant evaporation capacity in the outdoor unit 3 is improved.

  On the vapor injection refrigerator 200 side, the liquid phase refrigerant heated in the front boiler 6 evaporates to become a gas phase refrigerant, but initially the on-off valve V1 is closed, so the inside of the front boiler 6 measured by the pressure sensor 10 is used. The pressure gradually increases. When the pressure in the front boiler 6 exceeds a predetermined value (threshold value), the on-off valve V1 of the line L20 is opened and the refrigerant pump P2 is started.

  When the on-off valve V1 is opened, the gas-phase refrigerant generated in the front boiler 6 flows through the refrigerant line L20 and is sucked into the ejector 7, and from the injection side of the ejector 7 (the right side of the ejector 7 in the drawing) at a high speed. It is injected to the condenser 8 side. As described above, the heat of vaporization is radiated to the outside air by the condenser 8.

Next, control in the air conditioning operation of the first embodiment will be described with reference to FIG.
In FIG. 4, in step S1, it is determined whether the operation mode is cooling or heating. If the cooling operation is to be performed (“cooling operation” in step S1), the process proceeds to step S2. If the heating operation is to be performed (“heating operation” in step S1), the process proceeds to step S7.

In step S2 (cooling operation: see FIG. 2), the water pump P1 is activated, the on-off valve V1 is closed, and the pressure reducing valve V2 and the on-off valve V3 are opened. The flow control valve CV1 on the first refrigerant line L1 side is also opened to such an extent that it can operate as a pressure reducing valve, and the flow control valve CV2 on the branch refrigerant line L3 side is also opened.
Then, the ports V4a and V4b of the four-way valve V4 are communicated, and the ports V4c and V4d are communicated to switch to the cooling operation side (step S3).
Next, clutches (not shown) of the first compressor 11 and the second compressor 12 are connected so that the rotational force of the gas engine 5 is transmitted. That is, both the first compressor 11 and the second compressor 12 are put into an operating state (step S4: labeled “connected” in FIG. 4). And the flow path of the external air between the condenser 8 and the outdoor unit 3 is switched to the air path A (step S5).

  In step S6, the pressure (pressure in the front boiler 6) measured by the pressure sensor 10 interposed in the refrigerant line L20 of the steam injection refrigerator 200 is compared with the threshold value. The system waits until the pressure measured by the pressure sensor 10 is equal to or higher than the threshold (step S6 is NO), and when the measured value is equal to or higher than the threshold (step S6 is YES), the on-off valve V1 is opened. Then, the refrigerant pump P2 is activated.

In step S8 (heating operation: see FIG. 3), the water pump P1 is started, the on-off valve V1, the pressure reducing valve V2, the on-off valve V3, and the pressure regulating valve CV2 are closed, and the flow control valve on the first refrigerant line L1 side. CV1 is opened.
In the next step S9, the ports V4a and V4c of the four-way valve V4 are communicated, the ports V4b and V4d are communicated, and the heating operation side is switched.
Here, during the heating operation, only the first compressor 11 is operated (step S10), and the flow path of the outside air between the condenser 8 and the outdoor unit 3 is switched to the air path B (step S11).

  In step S12, the pressure (pressure in the front boiler 6) measured by the pressure sensor 10 interposed in the refrigerant line L20 of the steam injection refrigerator 200 is compared with the threshold value. The system waits until the pressure measured by the pressure sensor 10 is equal to or higher than the threshold (NO in step S12). When the measured value is equal to or higher than the threshold (YES in step S12), the on-off valve V1 is opened. Then, the refrigerant pump P2 is activated.

As described above, in the illustrated embodiment, a part of the compression air conditioner 100 and a part of the steam injection refrigerator 200 can be shared.
In the second embodiment shown in FIGS. 5 to 9, a part of the refrigerant line L <b> 3 of the compression air conditioner 100 and the refrigerant line L <b> 2 of the steam injection refrigerator 200 in the first embodiment of FIGS. This is an embodiment.
The second embodiment will be described below with reference to FIGS.

The structure of 2nd Embodiment of FIG. 5 is the 2nd heat exchanger (outdoor unit of the compression type air conditioner 100) 3 in 1st Embodiment of FIGS. 1-4, and 4th heat exchanger (evaporation injection). The condenser 200 on the refrigerator 200 side) is integrated with the heat exchanger 38. A part of the line L12 and the line L13 of the compression air conditioner 100 is shared with the line L2 of the steam injection refrigerator 200.
In FIG. 5, a line L12 that communicates with the port V4b of the four-way valve V4 merges with the line L20 of the refrigerant line L2 at a branch point B22 (a branch or merge point) and is shared. A heat exchanger 38 and a flow rate adjusting valve CV3 are interposed in a line common to the line L12 and the line L20, and at a branch point B23 (a branch or merge point), the compression air conditioner 100 side is provided. It is divided into a line L13 and a line L22 on the steam injection refrigerator 200 side.
A branch point B21 is provided between the flow rate adjusting valve CV3 and the branch point B23, and a part of the refrigerant flowing through the common line of the line L12 and the line L20 is interposed in the pump P2, It flows through a refrigerant line L21 that communicates with the front boiler 6.

  The second embodiment shown in FIG. 5 has substantially the same configuration as the first embodiment of FIG. 1 except for the configuration described above.

FIG. 6 is a Mollier diagram showing the cycle of the second embodiment shown in FIG. The Mollier diagram of FIG. 6 is a cycle in which a compression refrigeration cycle and a steam injection refrigeration cycle are combined.
For the Mollier diagram of FIG. 6, the corresponding members and lines of FIG. 5 are displayed. Here, the point p2 ′ is a suction inlet portion of the ejector 7, the point pm is an intermediate portion of the ejector 7, and the point p3 is a discharge portion of the ejector 7.

The refrigerant flow and the like during the cooling operation in the second embodiment will be described with reference to FIG.
Except that the refrigerant flows through a line between the branch point B22 and the branch point B23 (a line common to the line L12 and the line L20), the refrigerant flow and the valve opening / closing in the second embodiment Is basically the same as FIG.
However, in the second embodiment, the outdoor unit 3 of the compression air conditioner 100 in FIG. 1 (first embodiment) and the condenser 8 on the evaporation injection refrigerator 200 side are integrated to form a heat exchanger 38. Therefore, as in the first embodiment shown in FIG. 1 to FIG. 4, there are not two types of external air flow paths of the air path A and the air path B. There is no need to select (or switch to wind path A).
Further, if the opening degree is reduced to such an extent that the flow rate adjusting valve CV3 operates as a pressure reducing valve, a part of the liquid phase refrigerant condensed in the heat exchanger 38 (condenser) may be vaporized, and the line L21 is There is a possibility that gas phase refrigerant is mixed in the flowing refrigerant. And if a gaseous-phase refrigerant | coolant mixes with the refrigerant | coolant which flows through the line L21, the pump P2 will be in the so-called "it bites air" state, and may be damaged. In order to eliminate such a situation, during the cooling operation, the flow rate adjustment valve CV3 is fully opened so as not to operate as a pressure reducing valve.

The refrigerant flow and the like during the heating operation in the second embodiment are shown in FIG.
The refrigerant is basically the same as in the heating operation (see FIG. 3) in the first embodiment except that it flows through the common part of the line.
However, as described above, the second embodiment does not have the switchable air passage A and the air passage B, and therefore there is no need to select (or switch) the air passage B during the heating operation.
Moreover, if the opening degree is reduced to such an extent that the flow rate adjusting valve CV1 operates as a pressure reducing valve, a part of the liquid-phase refrigerant condensed in the indoor unit 2 (condenser) may be vaporized, and the line L13 is There is a possibility that gas phase refrigerant is mixed in the flowing liquid phase refrigerant. When the refrigerant flowing in the line L13 becomes a gas-liquid mixed flow, the gas-liquid mixed flow flows through the line L21 via the branch point B23 and the branch point B21, so that the pump P2 interposed in the line L21 The so-called “air biting” state may occur and damage may occur. In order to eliminate such a situation, during heating operation, the flow rate adjustment valve CV1 is fully opened so that it does not operate as a pressure reducing valve.

Next, the control of the air-conditioning operation of the second embodiment will be described based on FIG.
First, in step S20, it is determined whether the operation mode is a cooling operation or a heating operation. If the operation mode is the cooling operation (step S20 is “cooling operation”), the process proceeds to step S21. If the operation mode is the heating operation (step S20 is “heating operation”), the process proceeds to step S26.

In step S21 (cooling operation: see FIG. 7), the water pump P1 is activated, the on-off valve V1 is closed, and the pressure reducing valve V2 and the on-off valve V3 are opened. The flow control valve CV1 interposed in the refrigerant line L1 on the compression refrigerator 100 side and the flow control valve CV2 interposed in the branch refrigerant line L3 are opened to the extent that they can operate as pressure reducing valves. And CV3 intervened in the refrigerant line (area | region of branch point B22-branch point B23) shared by the compression-type refrigerator 100 side and the vapor injection refrigerator 200 side does not show a pressure reduction effect | action. Fully open.
Steps S22 to S25 are substantially the same control as in the first embodiment of FIG. However, in 2nd Embodiment of FIGS. 5-9, the condenser by the side of the vapor | steam injection refrigerator 200 and the outdoor unit by the side of the compression refrigerator 100 are integrated (38). Since there is no need to switch B, a step corresponding to “switch to wind path A” (step S5) in FIG. 4 is not provided in FIG.

In step S26 (heating operation), the water pump P1 is activated, and the on-off valve V1, the pressure reducing valve V2, the on-off valve V3, and the flow rate adjusting valve CV2 are closed.
CV3 interposed in the refrigerant line (region of branch point B22 to branch point B23) shared by the compression refrigerator 100 side and the vapor injection refrigerator 200 side is open to the extent that it operates as a pressure reducing valve. To do.
The flow control valve CV1 interposed in the refrigerant line L1 on the compression refrigerator 100 side is fully opened so as not to act as a pressure reducing valve.
Steps S27 to S30 are substantially the same control as in the first embodiment of FIG. However, in the second embodiment of FIGS. 5 to 9, there is no need to switch the air path A and the air path B, and therefore the steps corresponding to “switch to the air path B” (step S <b> 11) in FIG. Is not provided.

  Other configurations and operational effects in the second embodiment of FIGS. 5 to 9 are the same as those of the first embodiment of FIGS.

Next, a third embodiment will be described with reference to FIGS.
10 to 13, as in the first embodiment of FIGS. 1 to 4, a first heat exchanger (outdoor unit) 3 of a compression type air conditioner is interposed. The refrigerant line and the refrigerant line in which the fourth heat exchanger (condenser) 8 of the vapor injection refrigerator is interposed are provided separately and are not shared.
In the third embodiment of FIGS. 10 to 13, the exhaust heat heat exchanger 9 is provided on the compression refrigeration cycle side to improve the exhaust heat utilization efficiency during the heating operation.

In FIG. 10, an exhaust heat exchanger 9 is interposed in the line L17 of the first refrigerant line L1 on the compression air conditioner 100 side, and branched exhaust heat is discharged from the exhaust heat line Lw1 on the steam injection refrigerator 200 side. The line Lw2 is branched and the branch line Lw2 communicates with the exhaust heat exchanger 9.
In the exhaust heat line Lw1, a three-way valve Vw3 is provided between the water pump P1 and the front boiler 6, a branch point Bw is provided in the region between the gas engine 5 and the front boiler 6 in the exhaust heat line Lw1, and the branch exhaust heat line Lw2 Communicates with the three-way valve Vw3, the exhaust heat exchanger 9, and the branch point Bw.
The configuration of the third embodiment shown in FIG. 10 is the same as that of the first embodiment of FIG. 1 except for the points described above.

FIG. 11 shows the open / close states of various valves and the flow of the refrigerant during the cooling operation in the third embodiment. The flow of the refrigerant during the cooling operation of the third embodiment shown in FIG. 11 (indicated by an arrow in the refrigerant line of FIG. 11) is the same as described in FIG.
However, since the three-way valve V3 closes the exhaust heat exchanger 9 side, the refrigerant flows only to the front boiler 6 side Lw1, and no refrigerant flows through the exhaust heat line Lw1 and the branch exhaust heat line Lw2.

The open / close states of various valves and the flow of refrigerant during the heating operation in the third embodiment are shown in FIG.
During the heating operation, on the compression air conditioner 100 side, the second compressor 12 is stopped, the on-off valve V3 of the branch refrigerant line L3 is closed, and the refrigerant does not flow through the branch refrigerant line L3. During the heating operation of the third embodiment, the refrigerant flow in the first refrigerant line L1 of the compression air conditioner 100 is the same as that of the first example of FIG.
On the steam injection refrigerator 200 side, the three-way valve Vw3 closes the front boiler 6 side and opens only the exhaust heat exchanger 9 side, so the exhaust heat of the gas engine 5 is exhausted from the exhaust heat line Lw1 and the branched exhaust heat line Lw2. Is supplied to the exhaust heat exchanger 9 and the exhaust heat is administered to the refrigerant on the compression air conditioner 100 side that flows through the refrigerant line L1 side (the line L17).
Further, no exhaust heat is input to the front boiler 6 side, and no gas phase refrigerant (Freon vapor) is generated from the front boiler 6, so that no refrigerant flows into the refrigerant line L2 of the vapor injection refrigerator 200 during the heating operation.

Next, based on FIG. 13, control of the air-conditioning operation of 3rd Embodiment is demonstrated.
First, in step S31, it is determined whether the operation mode is a cooling operation or a heating operation. If the cooling operation is to be performed (step S31 is “cooling operation”), the process proceeds to step S32. If the heating operation is to be performed (step S31 is “heating operation”), the process proceeds to step S39.

About step S32-S35 which shows control of air_conditionaing | cooling operation, it is the same as that of step S2-S5 in 1st Embodiment of FIG.
In FIG. 13, the state in which the first compressor 11 and the second compressor 12 are driven by the gas engine 5 is indicated as “connected” (steps S34 and S41).

In step S36 of FIG. 13, the three-way valve Vw3 of the exhaust heat line is switched to the front boiler 6 side, and the exhaust heat from the exhaust gas engine 5 is input to the front boiler 6.
Steps S37 and S38 are the same as steps S6 and S7 in the control (FIG. 4) of the first embodiment.

About step S39-S41 which shows control of heating operation, it is the same as that of step S8-S10 in 1st Embodiment of FIG.
During the heating operation of the third embodiment, no refrigerant flows through the refrigerant line L2 on the steam injection refrigerator 200 side, and no heat exchange is performed in the condenser 8, so step S11 in FIG. 4 (step of switching to the air path B). The process corresponding to is not present in FIG.
In step S42 of FIG. 13, the three-way valve Vw3 of the exhaust heat line is switched to the exhaust heat exchanger 9 side, and the exhaust heat from the gas engine 5 is input to the exhaust heat exchanger 9 via the exhaust heat lines Lw1 and Lw2. To do.

  Steps S43 and S44 in FIG. 13 are the same as steps S12 and S13 in the control of the first embodiment (FIG. 4).

  Other configurations and operational effects in the third embodiment of FIGS. 10 to 13 are the same as those of the first embodiment of FIGS.

Next, a fourth embodiment will be described with reference to FIGS.
The fourth embodiment shown in FIGS. 14 to 17 is similar to the second embodiment shown in FIGS. 5 to 9 and the branch refrigerant line L3 of the compression air conditioner 100 in the first embodiment shown in FIGS. This is an embodiment in which a part of the refrigerant line L2 of the injection refrigerator 200 is shared.
And in 4th Embodiment of FIGS. 14-17, the exhaust-heat heat exchanger 9 is provided in the compression-type refrigerating cycle side, and the exhaust-heat utilization efficiency at the time of heating operation is improved.
Hereinafter, the fourth embodiment will be described with reference to FIGS. 14 to 17.

In FIG. 14, as described above, the second heat exchanger (outdoor unit of the compression air conditioner 100) 3 and the fourth heat exchanger (evaporative injection refrigerator) in the first embodiment of FIGS. 200-side condenser) 8 is integrated into a heat exchanger 38. A part of the line L12 and the line L13 of the compression air conditioner 100 is shared with the line L2 of the steam injection refrigerator 200.
14, the exhaust heat exchanger 9 is interposed in the line L17 on the compression air conditioner 100 side, and the branch exhaust heat line Lw2 is branched from the exhaust heat line Lw1 on the steam injection refrigerator 200 side. The branch line Lw2 communicates with the exhaust heat exchanger 9. The exhaust heat line Lw1 is provided with a three-way valve Vw3 and a branch point Bw is provided. The branch exhaust heat line Lw2 communicates with the three-way valve Vw3, the exhaust heat exchanger 9 and the branch point Bw. Yes.
The configuration of the fourth embodiment shown in FIG. 14 is the same as that of the second embodiment of FIG. 5 except for the points described above.

Regarding the flow of the refrigerant, the cooling operation (FIG. 15) is the same as that of FIG. 7 of the second embodiment.
On the other hand, during heating operation (FIG. 16), the exhaust heat from the gas engine 5 flows through the exhaust heat lines Lw1 and Lw2 and is input to the exhaust heat exchanger 9, so that the common refrigerant line (branch point B22) And the refrigerant line L20 to L22 of the steam-injection refrigerator 200, except for the region between and the branch point B23). About the others, the flow of the refrigerant | coolant at the time of the heating operation of FIG. 16, etc. are the same as that of FIG. 8 in 2nd Embodiment.

The control of the air conditioning operation of the fourth embodiment shown in FIG. 17 is basically the same as the control of the air conditioning operation of the second embodiment of FIG.
In FIG. 17, the air-conditioning operation mode is selected (step S31), and in the case of cooling operation (step S31 is “cooling operation”), the process proceeds to step S32A, and in the case of heating operation (step S31 is “heating operation”), step S39A. Proceed to
About step S32A-S34 which shows control of air_conditionaing | cooling operation, it is the same as that of step S21-S23 in 2nd Embodiment of FIG.
In step S36 in the fourth embodiment of FIG. 17, the three-way valve Vw3 of the exhaust heat line is switched to the front boiler 6 side, and the exhaust heat from the exhaust gas engine 5 is input to the front boiler 6.
Steps S37 and S38 are the same as steps S24 and S25 in the control (FIG. 9) of the second embodiment.
About step S39A-S41 which shows control of heating operation, it is the same as that of step S26-S28 in 2nd Embodiment of FIG.
In step S43 in FIG. 17, the three-way valve Vw3 of the exhaust heat line is switched to the exhaust heat exchanger 9 side, and the exhaust heat from the gas engine 5 is input to the exhaust heat exchanger 9 through the exhaust heat lines Lw1 and Lw2. To do.
Steps S44 and S45 are the same as steps S29 and S30 in the control (FIG. 9) of the second embodiment.
Other configurations and operational effects in the fourth embodiment of FIGS. 14 to 17 are the same as those of the second embodiment of FIGS.

Next, a fifth embodiment will be described with reference to FIGS.
The fifth embodiment shown in FIGS. 18 to 21 is similar to the first embodiment shown in FIGS. 1 to 4 and is similar to the first embodiment shown in FIGS. The refrigerant line in which the heat exchanger (outdoor unit) 3 is interposed and the refrigerant line in which the fourth heat exchanger (condenser) 8 of the steam injection refrigerator is interposed are provided separately. It is not standardized.
In the fifth embodiment shown in FIGS. 18 to 21, a line L2b that bypasses the ejector 7 is provided in the refrigerant line L2 in the steam injection refrigeration cycle, and the exhaust heat supplied to the front boiler 6 of the steam injection refrigeration cycle during heating operation is It is comprised so that it may contribute to the heating operation of a compression-type cycle, without losing when passing 7.

In FIG. 18, a three-way valve V3b is interposed in the region between the on-off valve V1 and the ejector 7 in the second refrigerant line L20, and the ejector 7 (injection side thereof) and the fourth heat exchanger 8 in the line L20 A branch point B24 is provided between the three-way valve V3b and the branch point B24.
Other configurations of the fifth embodiment shown in FIG. 18 are the same as the configurations of the first embodiment of FIG.

  In the fifth embodiment, the refrigerant flow in the compression air conditioner 100 is the refrigerant on the compression air conditioner side in the first embodiment both during the cooling operation (see FIG. 19) and during the heating operation (see FIG. 20). This is the same as the flow (see the cooling operation in FIG. 2 and the heating operation in FIG. 3).

In 5th Embodiment, the flow of the refrigerant | coolant at the time of the air_conditionaing | cooling operation in the vapor injection refrigerator 200 side is demonstrated with reference to FIG.
The refrigerant flow during the cooling operation on the vapor injection refrigerator 200 side shown in FIG. 19 is basically the same as the cooling flow in FIG. 2 (during the cooling operation of the first embodiment).
However, during the cooling operation shown in FIG. 19, the three-way valve V3b interposed in the line L20 is switched to the ejector 7 side, so that the gas-phase refrigerant generated in the front boiler 6 does not flow through the bypass L2b and flows to the ejector 7. Inhaled and injected.

The flow of the refrigerant during the heating operation on the vapor injection refrigerator 200 side in the fifth embodiment will be described with reference to FIG.
The refrigerant flow during the heating operation on the side of the vapor injection refrigerator 200 shown in FIG. 20 is basically the same as the cooling flow in FIG. 3 (during the heating operation of the first embodiment).
However, during the heating operation shown in FIG. 20, the three-way valve V3b interposed in the line L20 is switched to the bypass line L2b side. The gas-phase refrigerant generated in the front boiler 6 reaches the condenser 8 without passing through the ejector 7, and is condensed by exchanging heat with the outside air. Here, since the gas-phase refrigerant does not pass through the ejector 7, heat is vaporized to the outside air by the condenser 8 without receiving a pressure loss due to passing through the ejector 7, so that the outdoor unit flows through the air passage B. The outside air that exchanges heat with the refrigerant on the compression air conditioner 100 side in 3 is increased in temperature by an amount that can avoid the pressure loss in the ejector 7.
Therefore, in the outdoor unit 3, the efficiency of vaporizing the low-pressure liquid refrigerant on the compression air conditioner 100 side is improved.

Next, the control of the air conditioning operation of the fifth embodiment will be described based on FIG.
As shown in FIG. 21, the air conditioning operation control of the fifth embodiment is basically the same as the operation control of the first embodiment shown in FIG.
Steps S52 to S55 in FIG. 21 showing the cooling operation (see FIG. 19) control of the fifth embodiment are the same as steps S2 to S5 in the first embodiment of FIG.
In step S56 of FIG. 21, the three-way valve V3b of the line L20 is switched to the ejector 7 side.
Steps S57 and S58 in FIG. 21 are the same as steps S6 and S7 in FIG.

Steps S59 to S62 in FIG. 21 showing the heating operation (see FIG. 20) control of the fifth embodiment are the same as steps S8 to S11 in the first embodiment of FIG.
In step S63 of FIG. 21, the three-way valve V3b of the line L20 is switched to the bypass L2b side.
Steps S64 and S65 in FIG. 21 are the same as steps S12 and S13 in FIG.
Other configurations and operational effects in the fifth embodiment of FIGS. 18 to 21 are the same as those of the first embodiment of FIGS.

The fifth embodiment shown in FIGS. 18 to 21 and the third embodiment shown in FIGS. 10 to 13 can be combined.
That is, in the first embodiment of FIGS. 1 to 4, the exhaust heat exchanger 9 is provided on the compression refrigeration cycle side, and the line L <b> 2 b that bypasses the ejector 7 on the steam injection refrigeration cycle side is provided. It is possible to improve the efficiency.

When the fifth embodiment of FIGS. 18 to 21 and the third embodiment of FIGS. 10 to 13 are combined, the three-way valve Vw3 of the exhaust heat line Lw1 is switched to the front boiler 6 side during cooling operation. In addition, the bypass valve V3b of the line L20 is switched to the ejector 7 side.
About others, it is the same as that of step S2-S7 in 1st Embodiment of FIG.

When the fifth embodiment of FIGS. 18 to 21 and the third embodiment of FIGS. 10 to 13 are combined, the three-way valve Vw3 of the exhaust heat line Lw1 is placed on the exhaust heat exchanger 9 side during heating operation. In addition, the bypass valve V3b of the line L20 is switched to the bypass line L2b side.
About others, it is the same as that of step S8-S13 in 1st Embodiment of FIG.

Next, a sixth embodiment will be described with reference to FIGS.
As in the second embodiment of FIGS. 5 to 9, the sixth embodiment of FIGS. 22 to 25 also includes the branch refrigerant line L <b> 3 of the compression air conditioner 100 in the first embodiment of FIGS. This is an embodiment in which a part of the refrigerant line L2 of the injection refrigerator 200 is shared.
In the sixth embodiment shown in FIGS. 22 to 25, a line L2b that bypasses the ejector 7 is provided in the refrigerant line L2 in the steam injection refrigeration cycle, and the exhaust heat supplied to the front boiler 6 of the steam injection refrigeration cycle during heating operation is It is comprised so that it may contribute to the heating operation of a compression-type cycle, without losing when passing 7.

In FIG. 22, a three-way valve V3b is interposed in the region between the on-off valve V1 and the ejector 7 in the second refrigerant line L20, and the ejector 7 (injection side thereof) and the fourth heat exchanger 8 in the line L20 A branch point B24 is provided between the three-way valve V3b and the branch point B24.
The other configuration of the sixth embodiment shown in FIG. 22 is the same as that of the second embodiment of FIG.

  The refrigerant flow during the cooling operation in the sixth embodiment shown in FIG. 23 is the same as that during the cooling operation in the second embodiment shown in FIG. In the cooling operation shown in FIG. 23, on the steam injection refrigerator 200 side, the gas-phase refrigerant generated in the front boiler 6 is sucked into the ejector 7 and injected without flowing through the bypass line L2b side.

  The refrigerant flow during the heating operation in the sixth embodiment shown in FIG. 24 is such that the vapor-phase refrigerant generated in the front boiler 6 is bypassed from the three-way valve V3b without passing through the ejector 7 on the steam injection refrigerator 200 side. It differs from the second embodiment of FIG. 8 in that it flows on the L2b side.

By flowing through the bypass line L2b, the gas-phase refrigerant generated in the front boiler 6 flows into the heat exchanger (integrated heat exchanger) 38 without causing pressure loss, and performs heat exchange. The efficiency at the time of heating operation is improved by the amount of no loss.
The heating operation in the sixth embodiment shown in FIG. 24 is the same as the heating operation in the second embodiment in FIG. 8 except for the above.

FIG. 25 showing the air conditioning operation control in the sixth embodiment is basically the same as the air conditioning operation control (see FIG. 9) in the second embodiment.
During the cooling operation (see FIG. 23), steps S52A to S54 in FIG. 25 are the same as steps S21 to S23 in the second embodiment (FIG. 9).
In the cooling operation control in the sixth embodiment (FIG. 25), the three-way valve V3b of the line L20 is switched to the ejector 7 side in step S56.
Steps S57 and S58 in FIG. 25 are the same as steps S24 and S25 in FIG.

During the heating operation (see FIG. 24), Steps S59A to S61 in FIG. 25 are the same as Steps S26 to S28 in the second embodiment (FIG. 9).
In the heating operation control in the sixth embodiment (FIG. 25), the three-way valve V3b of the line L20 is switched to the bypass line L2b side in step S63.
Steps S64 and S66 in FIG. 25 are the same as steps S29 and S30 in FIG.

  Other configurations and operational effects in the sixth embodiment of FIGS. 22 to 25 are the same as those of the second embodiment of FIGS.

In addition, it is possible to comprise combining 6th Embodiment of FIGS. 22-25, and 4th Embodiment of FIGS. 14-17.
In other words, in the second embodiment of FIGS. 5 to 9, the exhaust heat exchanger 9 is provided on the compression refrigeration cycle side, and the line L <b> 2 b that bypasses the ejector 7 in the steam injection refrigeration cycle is provided. It is possible to further improve the efficiency.

  When the sixth embodiment of FIGS. 22 to 25 and the fourth embodiment of FIGS. 14 to 17 are configured in combination, during cooling operation, the three-way valve Vw3 of the exhaust heat line Lw1 is switched to the front boiler 6 side, and The bypass valve V3b of the line L20 is switched to the ejector 7 side. About others, it controls similarly to step S21-step S25 in 2nd Embodiment of FIG.

  At the time of heating operation when the sixth embodiment of FIGS. 22 to 25 and the fourth embodiment of FIGS. 14 to 17 are combined, the three-way valve Vw3 of the exhaust heat line Lw1 is switched to the exhaust heat exchanger 96 side. And the bypass valve V3b of the line L20 is switched to the bypass line L2b side. About others, it controls similarly to step S26-step S30 in 2nd Embodiment of FIG.

Next, a seventh embodiment will be described with reference to FIG.
In any of the first to sixth embodiments shown in FIGS. 1 to 25, the compressor 1 in the compression cycle is driven by mechanically transmitting the output of the gas engine 5 that is an exhaust heat source by the drive shaft 51. ing.
On the other hand, in the seventh embodiment of FIG. 26, the exhaust heat source is a cogeneration system (for example, a gas engine cogeneration system 5C) that supplies both electricity and heat, and the compressors 11E and 12E of the compression cycle are electrically connected. It is driven. Then, the output power from the power generator 60 of the gas engine cogeneration system 5C is supplied to and driven by the electric drive type compressors 11E and 12E of the compression cycle via the power transmission cable Le.
In FIG. 26, reference numeral 52 denotes a driving shaft of the gas engine, which is connected to a rotating shaft of a power generator 60 (not shown).

In the seventh embodiment in which the compressors 11E and 12E of the compression cycle are electrically driven, only FIG. 26 in which the compressors 11 and 12 in FIG. 1 of the first embodiment are electrically driven is illustrated.
However, in all the drawings of the second to sixth embodiments, the compressors 11 and 12 of the compression cycle can be electrically driven as in FIG.

Next, an eighth embodiment will be described with reference to FIG.
In all of the first to seventh embodiments of FIGS. 1 to 26, the second compressor 12 is interposed in the branch refrigerant line L3 of the compression air conditioner 100, and flows into the branch refrigerant line L3. The gas-phase refrigerant thus pressurized is pressurized by the second compressor 12 and merges into the refrigerant line L1 via the supercooling heat exchanger 4.
On the other hand, in the eighth embodiment of FIG. 27, instead of installing a compressor in the branch refrigerant line L3 of the compression air conditioner 100, a pump P3 is provided downstream of the supercooling heat exchanger 4. In the cooling operation, the liquid phase refrigerant cooled and condensed by the supercooling heat exchanger 4 is pushed into the junction B12.

In the eighth embodiment in which the liquid refrigerant pump P3 is interposed in the branch refrigerant line L3 on the compression air conditioner 100 side, the branch refrigerant line is used instead of the second compressor 12 in FIG. 1 of the first embodiment. Only FIG. 27 showing a state where a pump is interposed in L3 is shown.
However, in all the drawings of the second embodiment to the seventh embodiment (FIGS. 5 to 24), similarly to FIG. 27, the branch refrigerant line L3 of the compression cycle is used (in place of the second compressor 12). It is possible to interpose a pump P3.

  It should be noted that the illustrated embodiment is merely an example, and is not a description to limit the technical scope of the present invention.

The block diagram which shows the whole structure of 1st Embodiment of this invention. The state diagram which shows the action | operation at the time of the air_conditionaing | cooling operation of 1st Embodiment. The state figure which shows the action | operation at the time of the heating operation of 1st Embodiment. The flowchart which shows the control method of 1st Embodiment. The block diagram which shows the whole structure of 2nd Embodiment of this invention. The Mollier diagram which shows the cycle of 2nd Embodiment. The state diagram which shows the action | operation at the time of the air_conditionaing | cooling operation of 2nd Embodiment. The state figure which shows the action | operation at the time of the heating operation of 2nd Embodiment. The flowchart which shows the control method of 2nd Embodiment. The block diagram which shows the whole structure of 3rd Embodiment of this invention. The state figure which shows the action | operation at the time of the air_conditionaing | cooling operation of 3rd Embodiment. The state figure which shows the action | operation at the time of the heating operation of 3rd Embodiment. The flowchart which shows the control method of 3rd Embodiment. The block diagram which shows the whole structure of 4th Embodiment of this invention. The state figure which shows the action | operation at the time of the air_conditionaing | cooling operation of 4th Embodiment. The state figure which shows the action | operation at the time of the heating operation of 4th Embodiment. The flowchart which shows the control method of 4th Embodiment. The block diagram which shows the whole structure of 5th Embodiment of this invention. The state diagram which shows the action | operation at the time of the air_conditionaing | cooling operation of 5th Embodiment. The state figure which shows the action | operation at the time of the heating operation of 5th Embodiment. The flowchart which shows the control method of 5th Embodiment. The block diagram which shows the whole structure of 6th Embodiment of this invention. The state figure which shows the action | operation at the time of the air_conditionaing | cooling operation of 6th Embodiment. The state figure which shows the action | operation at the time of the heating operation of 6th Embodiment. The flowchart which shows the control method of 6th Embodiment. The block diagram which shows the whole structure of 7th Embodiment of this invention. The block diagram which shows the whole structure of 8th Embodiment of this invention. The block diagram which showed the whole structure of the prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor 2 ... 1st heat exchanger / indoor unit 3 ... 2nd heat exchanger / outdoor unit 4 ... 3rd heat exchanger / refrigerant subcooler 5 .... -Heat source machine / gas engine 6 ... Refrigerant evaporator / front boiler 7 ... Ejector 8 ... Fourth heat exchanger (condenser)
DESCRIPTION OF SYMBOLS 9 ... Waste heat exchanger 10 ... Pressure sensor CV1, CV2 ... Flow control valve L1 ... 1st refrigerant line L2 ... 2nd refrigerant line L3 ... Branch refrigerant line P1 ... Water pump P2 ... Refrigerant pump V1 ... Open / close valve V2 ... Pressure reducing valve V3 ... Open / close valve V4 ... Flow path switching device / four-way valve

Claims (6)

  A first heat exchanger that exchanges heat with the refrigerant and indoor air that is to be air-conditioned, a second heat exchanger that exchanges heat with the outside air, a first compressor, A first refrigerant line in which a first heat exchanger and a second heat exchanger are interposed; a branch refrigerant line branched from the first refrigerant line; and a second refrigerant line interposed in the branch refrigerant line A compression air conditioner including a compressor, and a third heat exchanger is interposed in the branch refrigerant line, and heat exchange with the refrigerant flowing through the branch refrigerant line in the third heat exchanger The second refrigerant line has a second refrigerant line, a refrigerant evaporator that evaporates the refrigerant when exhaust heat from the heat source unit is input, an ejector, and a refrigerant that flows through the second refrigerant line. A fourth heat exchanger that exchanges heat with outside air is interposed, and the second refrigerant line communicates with the refrigerant evaporator. It branches into the branch line and the 2nd branch line connected to the diffuser side suction part of an ejector, The 3rd heat exchanger is inserted in the 2nd branch line, It is characterized by the above-mentioned. Air conditioning system.   The second heat exchanger and the fourth heat exchanger are configured separately from each other, in a region where the second heat exchanger is interposed in the first refrigerant line and in the second refrigerant line The air conditioning system of Claim 1 comprised separately from the area | region which interposed the said 4th heat exchanger.   The second heat exchanger and the fourth heat exchanger are configured integrally, and the region in the first refrigerant line in which the second heat exchanger is interposed and the second refrigerant line in the second refrigerant line The air conditioning system according to claim 1, wherein the air conditioning system is configured integrally with an area interposing the fourth heat exchanger.   The flow path switching device is interposed in the first refrigerant line, and the flow direction of the refrigerant circulating through the first refrigerant line can be reversed. Air conditioning system.   The air conditioning system according to any one of claims 1 to 4, further comprising a fifth heat exchanger that inputs the exhaust heat from the heat source unit into the refrigerant flowing through the first refrigerant line.   The air conditioning system according to any one of claims 1 to 5, wherein the second refrigerant line has a bypass line that bypasses the ejector.

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