KR20140023273A - Steam generation system - Google Patents

Abstract

By reducing the temperature difference drawn up by the heat pump, an efficient steam generation system is provided. The first heat pump 2 has a first evaporator 7 and a second evaporator 8. The second heat pump 3 is connected to the first heat pump 2 via a condenser 10 at the top, which also serves as the first evaporator 7. The heat source fluid passes sequentially through the second evaporator 8 of the first heat pump 2 and the evaporator 12 of the second heat pump 3, and passes through the condenser 5 of the first heat pump 2. Is heated to generate steam.

Description

Steam generation system {STEAM GENERATION SYSTEM}

The present invention relates to a steam generating system for generating steam using a heat pump. This application claims priority based on Japanese Patent Application No. 2011-079370 for which it applied to Japan on March 31, 2011, and uses the content here.

Conventionally, as disclosed in Patent Document 1 below, a heat pump that draws heat from exhaust water and the like in an evaporator and heats water in a condenser to generate steam is known.

In addition, as disclosed in Patent Document 2 below, the heat pump is constituted by a plurality of upper and lower stages, and a heat exchanger (which is a condenser of the lower heat pump and also an evaporator of the upper heat pump) for connecting the upper and lower heat pumps is supplied. And a system for withdrawing steam from the condenser of the uppermost heat pump is also proposed.

Moreover, the apparatus which obtains high temperature water by installing a heat pump in right and left parallel and passing water to the condenser of each heat pump in order as disclosed in the following patent document 3 is also proposed.

Japanese Patent Laid-Open No. 58-40451 (Fig. 2) Japanese Patent Laid-Open No. 2006-348876 (FIGS. 1 and 2) Japanese Utility Model Publication No. 60-23669 (FIG. 2)

However, just using the heat pump of a single stage like the invention of the said patent document 1, the temperature difference which raises heat, ie, the temperature difference of the evaporator side and the condenser side is large, and the efficiency of a heat pump is bad.

In addition, as in the invention described in Patent Document 2, even when the heat pump is simply installed in a plurality of upper and lower stages, in order to draw heat only from the evaporator at the lowermost level, as in the invention described in Patent Document 1, the draw when the heat pump is viewed as a whole There is a limit in improving the efficiency of a heat pump because the temperature difference to raise is large.

In addition, similarly to the invention described in Patent Document 3, even if the heat pumps are installed in parallel to the left and right, the left and right heat pumps have the same configuration, and in drawing up heat only from the lowest evaporator, the same as the invention described in Patent Document 2 above There is a limit in improving the efficiency of a heat pump because the temperature difference to raise is large.

In addition, when the heat source fluid is hot water or exhaust gas, and the heat source is subjected to heat (sensible heat) while it is accompanied by a temperature drop, it is the downstream side just by passing the heat source fluid through the heat pumps arranged in parallel with each other in parallel. In the heat pump, since the temperature of the heat source fluid is lowered, it is necessary to consider this.

The problem to be solved by the present invention is to reduce the lifting temperature difference in the whole system, thereby improving the efficiency of the system. Moreover, when a heat source fluid gives sensible heat to a heat pump, it makes it a subject to provide the steam generation system which can respond also to the temperature fall accompanying it.

The present invention has been made to solve the above problems, the invention described in claim 1 is composed of a single stage or a plurality of stages and a first heat pump having a first evaporator and a second evaporator at least at the bottom, and composed of a single stage or a plurality of stages A heat source provided with a second heat pump connected to said first heat pump via a topmost condenser that also serves as said first bottom evaporator, and being provided to a second evaporator of said first heat pump and a bottom evaporator of said second heat pump. A fluid is passed in order, and it is a steam generation system characterized by heating water in the condenser at the top of the said 1st heat pump to generate | generate steam.

According to the invention described in claim 1, steam can be generated in the condenser at the uppermost end of the first heat pump by drawing heat from the second evaporator of the first heat pump and the lowest evaporator of the second heat pump. At this time, the heat source fluid passes through the second evaporator of the first heat pump and then passes through the evaporator of the lowest end of the second heat pump. As a result, the second heat pump can cover the amount of the heat source fluid cooled in the second evaporator of the first heat pump and draw heat again from the heat source fluid after passing through the second evaporator. Moreover, in the 1st heat pump, the temperature difference which raises can be reduced, and the power of a compressor can be reduced by that much, and the efficiency of a steam generation system can be improved.

The invention according to claim 2, wherein the second heat pump is composed of a single stage heat pump, and draws heat from a heat source fluid passed in sequence to the second evaporator of the first heat pump and the lowest evaporator of the second heat pump. It raises and heats water in the condenser of the uppermost stage of a said 1st heat pump, and produces | generates the steam, The steam generation system of Claim 1 characterized by the above-mentioned.

According to the invention according to claim 2, a heat source fluid is provided to the first evaporator of the first heat pump and the second evaporator of the first heat pump and the lowest evaporator of the second heat pump. As it passes, steam can be generated in the condenser at the top of the first heat pump.

The invention according to claim 3, wherein the first heat pump is composed of a plurality of stage heat pumps, and some or all of the heat pumps include the first evaporator and the second evaporator as evaporators, and each of the first evaporators. Is connected to adjacent upper and lower heat pumps, the heat source fluid is passed through each of the second evaporator in order from the upper heat pump to the lower heat pump in order, characterized in that the steam generating system according to claim 1 or 2 to be.

According to the invention described in claim 3, the entire steam generating system is constituted by three or more stages of heat pumps. Then, the heat source fluid passes through each of the second evaporators of the first heat pump in order from the upper heat pump to the lower heat pump in order, and then passes through the evaporator of the lowermost end of the second heat pump to the top of the first heat pump. Steam can be generated by heating water in the condenser.

The invention according to claim 4 is the steam generation system according to claim 3, wherein the heat pump of each stage constituting the first heat pump includes the first evaporator and the second evaporator as an evaporator.

According to the invention of claim 4, the heat source fluid passes through the second evaporator at each stage of the first heat pump, and then passes through the evaporator at the lowest stage of the second heat pump, thereby efficiently drawing heat in a simple configuration to obtain steam. Can be generated.

The invention according to claim 5, wherein, among the single or multiple stage heat pumps constituting the first heat pump, the heat pump in the stage having the first evaporator and the second evaporator is connected to the refrigerant passage from the expansion valve to the compressor. The first evaporator and the second evaporator are installed in series or in parallel, or the first expansion valve and the first evaporator, the second expansion valve and the second evaporator are installed in parallel in the refrigerant passage from the condenser to the compressor. It is the steam generation system in any one of Claims 1-4 characterized by the above-mentioned.

According to the invention of claim 5, the first evaporator and the second evaporator are provided in series or in parallel, or the first expansion valve and the first evaporator, the second expansion valve and the second evaporator are installed in parallel, and the first heat Heat may be drawn from the second evaporator of the pump and the lowest evaporator of the second heat pump to generate steam in the top condenser of the first heat pump.

The invention according to claim 6, wherein the first heat pump and the second heat pump are connected in any one of the following relations (a) to (c), wherein the steam according to any one of claims 1 to 5 Generation system.

(a) an indirect heat exchanger which receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump and heat exchanges without mixing both refrigerants; It is a condenser and also a first evaporator of the first heat pump.

(b) an intermediate cooler that receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump and directly contacts both refrigerants for heat exchange. It is a condenser of the pump and a first evaporator of the first heat pump.

(c) receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump, and heats the refrigerant by directly contacting both refrigerants, and condenser of both refrigerants and the first heat pump. And an intermediate cooler for exchanging heat without mixing the refrigerant supplied to the expansion valve of the second heat pump without passing through the expansion valve, the intermediate cooler being a condenser of the second heat pump, 1 evaporator.

According to invention of Claim 6, a steam generating system can be comprised by connecting a 1st heat pump and a 2nd heat pump to an indirect heat exchanger or an intermediate | middle cooler.

According to the seventh aspect of the present invention, in the case where the first heat pump and / or the second heat pump have multiple stages, the heat pumps of adjacent stages are connected in any one of the following (a) to (c). It is the steam generation system in any one of Claims 1-6 characterized by the above-mentioned.

(a) an indirect heat exchanger which receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and heat exchanges without mixing both refrigerants, the indirect heat exchanger being the condenser of the lower heat pump and the upper heat Evaporator of the pump.

(b) an intermediate cooler which receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and directly contacts and exchanges both refrigerants, the intermediate cooler being a condenser of the lower heat pump; The top heat pump is an evaporator.

(c) receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and heats them by directly contacting both refrigerants, and without passing through the expansion valve from the condenser of both refrigerants and the upper heat pump. An intermediate cooler for heat exchange without mixing the refrigerant supplied to the expansion valve of the lower heat pump is provided, and the intermediate cooler is the condenser of the lower heat pump and the evaporator of the upper heat pump.

According to invention of Claim 7, a 1st heat pump and / or a 2nd heat pump can be comprised in multiple stages, and the steam generating system is comprised by connecting heat pumps of adjacent stages to an indirect heat exchanger or an intermediate | middle cooler. can do.

The invention according to claim 8 is that when the first heat pump and the second heat pump are connected in the relation of claim 6 (b), the refrigerant from the compressor of the second heat pump is supplied to the intermediate cooler instead. The steam generating system according to claim 6, wherein the steam generator system is supplied to the refrigerant passage from the intermediate cooler to the compressor.

According to invention of Claim 8, the heat exchanger which comprises an intermediate | middle cooler can be comprised small by suppressing putting a refrigerant | coolant from the compressor of a 2nd heat pump into an intermediate | middle cooler. In addition, it is possible to prevent the lubricating oil of the compressor of the second heat pump from accumulating in the intermediate cooler and to prevent the oil from falling out of the compressor of the first heat pump.

The invention according to claim 9 is that when the first heat pump and the second heat pump are connected in the relationship of claim 6 (c), the refrigerant from the compressor of the second heat pump is supplied to the intermediate cooler instead. The steam generating system according to claim 6, wherein the first heat pump is supplied to the refrigerant passage from the intermediate cooler to the compressor or to the refrigerant passage from the expansion valve to the intermediate cooler or the compressor.

According to invention of Claim 9, the heat exchanger which comprises an intermediate | middle cooler can be comprised small by suppressing putting a refrigerant | coolant from the compressor of a 2nd heat pump into an intermediate | middle cooler.

The invention according to claim 10 includes a separator for gas-liquid separation of the refrigerant from the expansion valve of the first heat pump when the first heat pump and the second heat pump are connected in the relation of claim 6 (c). The vapor generation system according to claim 6, wherein the gaseous phase powder separated by the separator is supplied to the refrigerant passage from the second evaporator to the compressor.

According to invention of Claim 10, the heat exchanger which comprises these can be comprised small by providing a separator and making a gas phase powder into a structure which does not enter an intermediate | middle cooler and / or a 2nd evaporator.

Invention of Claim 11 is provided with the sub heat exchanger of any one of the following (a)-(d), and is provided with the 1st sub heat exchanger when the condenser and the 1st sub heat exchanger of the uppermost stage of a said 1st heat pump are provided. With respect to the flow order of water or steam, when the first sub heat exchanger is installed, the first sub heat exchanger is set to be in front, and when the second evaporator and the fourth sub heat exchanger of the first heat pump are installed. The fourth sub-heat exchanger, the lowest evaporator of the second heat pump, and the second sub-heat exchanger, when the second sub heat exchanger is installed, The evaporator is set to be backward, the first evaporator of the first heat pump, the third sub heat exchanger and the first heat exchanger when the third sub heat exchanger is installed. When the second evaporator of the pump and the fourth sub heat exchanger are installed, the first evaporator and the second evaporator are arranged in the third sub heat exchanger and the fourth sub for the flow order of the refrigerant to the fourth sub heat exchanger. It is set so that it may become ahead of a heat exchanger, The steam generation system in any one of Claims 1-10 characterized by the above-mentioned.

(a) A first sub heat exchanger of refrigerant and water from the condenser at the top of the first heat pump to the expansion valve.

(b) a second sub-heat exchanger of refrigerant and heat source fluid from the evaporator at the bottom of the second heat pump to the compressor.

(c) when the first evaporator is an indirect heat exchanger, a third sub of refrigerant from the bottommost expansion valve of the first heat pump to the compressor and refrigerant from the compressor of the second heat pump to the first evaporator heat transmitter.

(d) a fourth sub heat exchanger of refrigerant and heat source fluid from the expansion valve at the lowermost end of the first heat pump to the compressor.

According to the invention of claim 11, the first sub-heat exchanger is a supercooler of the refrigerant, the second sub-heat exchanger is a superheater of the refrigerant, the fourth sub-heat exchanger is a superheater of the refrigerant, or the third sub-heat exchanger is appropriately installed. This can improve the efficiency of the steam generation system.

The invention according to claim 12 is the steam generation system according to any one of claims 1 to 11, wherein the heat source fluid is a drain from a steam use facility.

According to the invention described in claim 12, steam can be generated by heat recovery from the drain from the steam use facility.

(Effects of the Invention)

According to the present invention, it is possible to reduce the lifting temperature difference in the case of the whole system, whereby the efficiency of the system can be improved. Moreover, when heat source fluid gives sensible heat to a heat pump, it can respond also to the temperature fall accompanying it.

1 is a schematic view showing Embodiment 1 of a steam generating system of the present invention.
FIG. 2 is a diagram showing a flow sequence of a heat source fluid to a fourth sub heat exchanger, a second evaporator of a first heat pump, a second sub heat exchanger, and an evaporator of a second heat pump.
FIG. 3 is a diagram illustrating a flow order of the refrigerant of the first heat pump to the first evaporator of the first heat pump, the third sub heat exchanger, the second evaporator of the first heat pump, and the fourth sub heat exchanger.
Figure 4 is a graph comparing the coefficient of performance of the steam generating system of the present invention and a conventionally known two-stage heat pump.
5 is a graph comparing the compressor suction volume flow rates of the upper and lower stages of the steam generating system of the present invention and the conventionally known two-stage heat pump.
6A is a TS diagram of an abnormal cycle.
6B is a TS diagram of a conventionally known single stage heat pump (converse Carnot's cycle).
7 is a TS diagram of the steam generating system of this embodiment.
FIG. 8 shows the case where the number of stages of the heat pump is increased in FIG. 7.
9 is a schematic view showing Embodiment 2 of a steam generating system of the present invention.
10 is a schematic view showing a modification of the steam generating system of Example 2. FIG.
11 is a schematic view showing Embodiment 3 of a steam generation system of the present invention.
12 is a schematic view showing a modification of the steam generating system of Example 3. FIG.
13 is a schematic diagram showing Embodiment 4 of a steam generating system of the present invention.
FIG. 14 shows the flow sequence of the refrigerant of the first heat pump to the first evaporator and the third sub heat exchanger of the first heat pump, and the second evaporator and the fourth sub of the first heat pump. It is a figure which shows the circulation procedure of the refrigerant | coolant of the 1st heat pump to a heat exchanger.
15 is a schematic diagram showing Embodiment 5 of a steam generating system of the present invention.
16 is a schematic view showing a modification of the steam generating system of Example 5. FIG.
17 is a schematic diagram showing Embodiment 6 of a steam generating system of the present invention.
18 is a schematic view showing Modification Example 1 of the steam generating system of Example 6. FIG.
19 is a schematic view showing Modification Example 2 of the steam generating system of Example 6. FIG.
It is a figure which shows the combination of installation of a 1st separator, a 2nd separator, and a 3rd separator.
21 is a schematic diagram showing Embodiment 7 of a steam generating system of the present invention.
22 is a schematic diagram showing Embodiment 8 of a steam generating system of the present invention.
23 is a schematic view showing Modification Example 1 of the steam generating system of Example 8. FIG.
24 is a schematic view showing Modification Example 2 of the steam generating system of Example 8. FIG.
25 is a schematic diagram showing Embodiment 9 of a steam generating system of the present invention.
26 is a schematic view showing Modification Example 1 of the steam generating system of Example 9;
27 is a schematic view showing Modification Example 2 of the steam generating system of Example 9;
It is a figure which shows the combination of installation of a 1st separator and a 2nd separator.
It is a schematic diagram which shows an example of the steam generation system of this invention comprised with the heat pump of three or more stages.
FIG. 29B is a TS diagram when the first heat pump is single stage and the second heat pump is two stages. FIG.
FIG. 29C is a TS diagram when the first evaporator and the second evaporator are provided at respective stages of the first heat pump of the plurality of stages, and the second heat pump is used as the stage.
30 is a schematic view showing an example of a steam system using the steam generating system of Example 1. FIG.
FIG. 31 is a schematic diagram illustrating a modification of the steam system of FIG. 30.

The steam generation system of the present invention includes a plurality of stage heat pumps, and some or all of the heat pumps of each stage except the lowest stage include a first evaporator and a second evaporator as evaporators, and each first evaporator The adjacent upper and lower heat pumps are connected. Then, the heat source fluid passes through each of the second evaporators in order from the upper heat pump to the lower heat pump sequentially, and heats water in the upper condenser to generate steam.

Hereinafter, a specific embodiment of the present invention will be described in detail with reference to the drawings.

Example 1

1 is a schematic view showing Embodiment 1 of a steam generating system 1 of the present invention. The steam generating system 1 of the present embodiment has a first heat pump 2 and a second heat pump 3.

The first heat pump 2 is a vapor compression heat pump, and is configured of a single stage heat pump in this embodiment. Specifically, the first heat pump 2 is configured such that the compressor 4, the condenser 5, the expansion valve 6, and the evaporators 7 and 8 are sequentially connected in an annular manner. Here, the first heat pump 2 is provided with two evaporators of the first evaporator 7 and the second evaporator 8 as evaporators, and these evaporators 7 and 8 are connected in series in this embodiment. have. That is, the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the first evaporator 7 and the second evaporator 8 in sequence (or vice versa), and then the compressor 4 Is transferred to).

The compressor 4 compresses the gas refrigerant to high temperature and high pressure. In addition, the condenser 5 condenses and liquefies the gas refrigerant from the compressor 4. In addition, the expansion valve 6 reduces the pressure and temperature of the refrigerant by passing the liquid refrigerant from the condenser 5. The evaporators 7 and 8 plan to evaporate the refrigerant from the expansion valve 6.

Accordingly, the first heat pump 2 vaporizes the refrigerant by taking heat from the outside in the evaporators 7 and 8, and the refrigerant is radiated to the outside in the condenser 5 to condense. Using this, the 1st heat pump 2 draws heat from a heat source fluid etc. in the evaporators 7 and 8, and heats water in the condenser 5, and produces | generates steam.

The heat source fluid (heat source of each heat pump 2, 3) is not particularly relevant, but the sensible heat is applied to each heat pump 2, 3, that is, the heat is applied to each heat pump 2, 3, and the temperature of the heat source fluid itself is increased. Fluids involving degradation are preferably used. For example, a drain from a steam use facility or an exhaust gas from a boiler or the like is used.

In the circuit of the heat pump 2, an oil separator is installed on the outlet side of the compressor 4, a receiver is installed on the outlet side of the condenser 5, or the accumulator is provided on the inlet side of the compressor 4 as desired. Alternatively, a liquid gas heat exchanger may be provided that performs heat exchange without mixing the refrigerant from the condenser 5 to the expansion valve 6 and the refrigerant from the evaporators 7 and 8 to the compressor 4. This is not only the first heat pump 2 but also the second heat pump 3. In addition, when the 1st heat pump 2 or the 2nd heat pump 3 has multiple stages, it is the same also about the heat pump of each stage which comprises it.

The second heat pump 3 is a vapor compression heat pump, and is constituted by a single stage heat pump in this embodiment. The second heat pump 3 is basically the same as the first heat pump 2 described above. That is, the 2nd heat pump 3 is comprised by the compressor 9, the condenser 10, the expansion valve 11, and the evaporator 12 connected in an annular order sequentially. However, the second heat pump 3 does not have to be provided with two kinds of evaporators like the first heat pump 2. The second heat pump 3 draws heat from the heat source fluid in the evaporator 12, heats the refrigerant of the first heat pump 2 in the condenser 10, and tries to condense itself.

The first heat pump 2 and the second heat pump 3 are connected as follows. That is, the indirect heat exchanger 13 which receives the refrigerant from the compressor 9 of the second heat pump 3 and the refrigerant from the expansion valve 6 of the first heat pump 2 and heat-exchanges without mixing both refrigerants is provided. In addition, the indirect heat exchanger 13 is the condenser 10 of the second heat pump 3 and serves as the first evaporator 7 of the first heat pump 2. In addition, the refrigerant | coolants of each heat pump 2 and 3 may be the same, and may differ. In addition, although the refrigerant | coolant to be used does not matter in particular, hydrofluorocarbon (HFC) with 4 or more carbon atoms (for example, R-365mfc) or water and / or a digestive liquid added to this, alcohol [for example, ethyl Alcohol, methyl alcohol or trifluoroethanol (TFE)], or water and / or digestive fluid added thereto, or water (for example, pure water or soft water) is preferably used.

Although details will be described later, the heat source fluid passes through the second evaporator 8 of the first heat pump 2 and the evaporator 12 of the second heat pump 3. Accordingly, the steam generating system 1 draws heat from the heat source fluid in these evaporators 8 and 12 and heats water in the condenser 5 of the first heat pump 2 to generate steam.

The steam generating system 1 may be provided with any one or more sub-heat exchangers among the various sub-heat exchangers 14 to 17 described below.

(a) The first sub heat exchanger 14 is an indirect heat exchanger of refrigerant and water from the condenser 5 of the first heat pump 2 to the expansion valve 6, and supercools the refrigerant of the first heat pump 2. It functions as a flag.

(b) The second sub heat exchanger 15 is an indirect heat exchanger of the refrigerant and the heat source fluid from the evaporator 12 of the second heat pump 3 to the compressor 9 and the refrigerant of the second heat pump 3. Functions as a superheater

(c) The third sub heat exchanger 16 is a refrigerant from the expansion valve 6 of the first heat pump 2 to the compressor 4 when the first evaporator 7 is an indirect heat exchanger 13. And an indirect heat exchanger of the refrigerant from the compressor 9 of the second heat pump 3 to the first evaporator 7 and function as a superheater of the refrigerant of the first heat pump 2.

(d) The fourth sub heat exchanger 17 is an indirect heat exchanger of the refrigerant from the expansion valve 6 of the first heat pump 2 to the compressor 4 and the heat source fluid, and the refrigerant of the first heat pump 2. Function as a superheater.

Next, the distribution route of water or steam is demonstrated.

Water is supplied to the condenser 5 of the first heat pump 2 and the first sub heat exchanger 14 as desired and steam is drawn out. When the 1st sub heat exchanger 14 is provided with respect to this water or vapor | storage flow sequence, this 1st sub heat exchanger 14 is set so that it may be ahead of the condenser 5 of the 1st heat pump 2. do. Then, saturated steam is usually drawn out from the condenser 5 of the first heat pump 2. In addition, although the condenser 5 and 10 of each heat pump 2 and 3 are each provided in the example of illustration, you may comprise with several heat exchanger in series or in parallel.

Next, the flow path of the heat source fluid will be described.

The second evaporator 8 of the first heat pump 2, the fourth sub heat exchanger 17 provided as desired, the evaporator 12 of the second heat pump 3, and the desired installation Although the 2nd sub heat exchanger 15 is installed in an appropriate order and the heat source fluid passes, any one shown in FIG. 2 is used for the flow path.

2 shows a fourth sub heat exchanger 17 provided as desired, a second evaporator 8 of the first heat pump 2, a second sub heat exchanger 15 provided as desired, 2 is a diagram illustrating a flow sequence of the heat source fluid from the heat pump 3 to the evaporator 12. The number in the figure shows the flow order to each heat exchanger 17, 8, 15, and 12, and the number 0 shows that the heat exchanger is not installed. In addition, although the same number has shown to install in parallel, the heat exchangers of the same number are mutually interchangeable. In addition, although the evaporators 8 and 12 of each heat pump 2 and 3 are each provided in the example of illustration, you may comprise with several heat exchangers in series or in parallel.

A few specific examples are given, for example, 1-2-3-4 in the first row. That is, the fourth sub heat exchanger 17 is 1, the second evaporator 8 of the first heat pump 2 is 2, the second sub heat exchanger 15 is 3, and the evaporator of the second heat pump 3 is used. (12) is four. In this case, the heat source fluid is the fourth sub heat exchanger 17, the second evaporator 8 of the first heat pump 2, the second sub heat exchanger 15, and the evaporator 12 of the second heat pump 3. ) In order.

In the second line, 1-2-1-3 is present. That is, the fourth sub heat exchanger 17 is 1, the second evaporator 8 of the first heat pump 2 is 2, the second sub heat exchanger 15 is 1, and the evaporator of the second heat pump 3 is used. (12) is three. In this case, the heat source fluid passes through the fourth sub heat exchanger 17 and the second sub heat exchanger 15 in parallel, and then the second evaporator 8 of the first heat pump 2 and the second heat pump ( Pass the evaporator 12 of 3) in order.

In the fourth row, there is 1-2-0-3. That is, the fourth sub heat exchanger 17 is 1, the second evaporator 8 of the first heat pump 2 is 2, the second sub heat exchanger 15 is 0, and the evaporator of the second heat pump 3 is used. (12) is three. In this case, the second sub heat exchanger 15 is not installed, and the heat source fluid passes through the fourth sub heat exchanger 17, and then the second evaporator 8 and the second heat pump of the first heat pump 2 are provided. It passes through the evaporator 12 of (3) in order.

In any case, it is preferable to basically set the evaporator 12 of the second heat pump 3 to be behind the flow order of the heat source fluid. In other words, the heat source fluid passes through the second evaporator 8 of the first heat pump 2 and then to the evaporator 12 of the second heat pump 3.

3 shows a first evaporator 7 of the first heat pump 2, a third sub heat exchanger 16, which is provided as desired, a second evaporator 8 of the first heat pump 2, and It is a figure which shows the circulation procedure of the refrigerant | coolant of the 1st heat pump 2 to the 4th sub heat exchanger 17 provided as desired. The number in the figure shows the flow order to each heat exchanger 7, 16, 8, and 17, and the number 0 shows that the heat exchanger is not installed. In addition, the same number has shown installing in parallel.

A few specific examples are given, for example, 1-3-2-3 in the first row. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 3, the 2nd evaporator 8 is 2, and the 4th sub heat exchanger 17 is 3. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the first evaporator 7 and the second evaporator 8 in order, and then the third sub heat exchanger 16 The four sub heat exchangers 17 are passed in parallel and then transferred to the compressor 4.

In the second row, 1-3-2-4 is present. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 3, the 2nd evaporator 8 is 2, and the 4th sub heat exchanger 17 is 4. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 is the first evaporator 7, the second evaporator 8, the third sub heat exchanger 16 and the fourth sub heat exchanger 17. ) Is passed in order to the compressor (4).

In the fourth row, 1-3-2-0 is present. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 3, the 2nd evaporator 8 is 2, and the 4th sub heat exchanger 17 is 0. FIG. In this case, the fourth sub heat exchanger 17 is not installed, and the refrigerant from the expansion valve 6 of the first heat pump 2 is transferred to the first evaporator 7, the second evaporator 8, and the third sub. The heat exchanger 16 is sequentially passed through to the compressor 4.

In any case, basically, the first evaporator 7 and the second evaporator 8 are replaced by the third sub heat exchanger 16 and the fourth sub heat exchanger in the flow order of the refrigerant of the first heat pump 2. It is preferable to set so that it is earlier than 17).

As described above, the steam generating system 1 of the present embodiment uses, for example, a drain as a heat source fluid. As an example, a drain of 158 ° C is supplied to the second evaporator 8 of the first heat pump 2 and discharged at 125 ° C, and then supplied to the evaporator 12 of the second heat pump 3 to 80 ° C. Discharged. The second heat pump 3 has a refrigerant temperature at low temperature side (inlet side of compressor 9) at 75 ° C, and the first heat pump 2 has a refrigerant temperature at low temperature side (inlet side of compressor 4). Is 120 degreeC and the refrigerant | coolant temperature on the high temperature side (outlet side of the compressor 4) becomes 163 degreeC, and the condenser 5 produces | generates 158 degreeC steam.

According to the steam generating system 1 of this embodiment, the heat source fluid passes through the second evaporator 8 of the first heat pump 2 and then to the evaporator 12 of the second heat pump 3. Accordingly, the second heat pump 3 covers the amount of the drain cooled in the second evaporator 8 of the first heat pump 2 and heats again from the drain after passing through the second evaporator 8. Can be raised. Moreover, in the 1st heat pump 2, the temperature difference pulled up can be reduced, and the electric power of the compressor 4 can be reduced by that much, and the efficiency of the steam generation system 1 can be improved.

In other words, the steam generating system 1 as a whole consists of heat pumps 2 and 3 of multiple stages (two stages in this embodiment), and a part (typically half) of the energy drawn up As you pull from the break, you can increase your score. In addition, since the energy drawn up from the bottom end can be reduced (typically halved), the capacity of the compressor 9 of the low stage side (second heat pump 3) can be reduced.

4 is a graph comparing the coefficient of performance of the steam generating system 1 of this embodiment and a conventionally known two-stage heat pump. In the figure, a solid line shows the steam generating system 1 of a present Example, and a broken line shows the conventionally well-known two-stage heat pump. In addition, the case where a drain is used as a heat source fluid is shown here, the final drain temperature after passing the evaporator 12 of the 2nd heat pump 3 is made into the horizontal axis, and the theoretical grade coefficient is made into the vertical axis | shaft. . In addition, the refrigerant | coolant is R-365mfc and the case where steam of 158 degreeC [5 kgf / cm <2> (G)] is produced using the conditions mentioned above, ie, the drain of an initial temperature of 158 degreeC, was examined.

As shown in this figure, regardless of the temperature of the heat source fluid (drain), the steam generation system 1 of this embodiment is more efficient than the conventionally known two-stage heat pump. In addition, the conventionally well-known two-stage heat pump omits installation of the 2nd evaporator 8 in FIG. 1, and raises heat from only the evaporator 12 of the 2nd heat pump 3 of the lowest stage, and Equal

5 is a graph comparing the compressor suction volume flow rates of the upper and lower stages of the steam generating system 1 of the present embodiment and a conventionally known two-stage heat pump. In the figure, a solid line shows the steam generating system 1 of a present Example, and a broken line shows the conventionally well-known two-stage heat pump. In addition, the case where a drain is used as a heat source fluid is shown here, the final drain temperature after passing the evaporator 12 of the 2nd heat pump 3 is made into the horizontal axis, and the compressor suction volume flow volume is made into the vertical axis. .

As shown in this figure, the compressor suction volume flow rate can be reduced by the steam generating system 1 of the present embodiment regardless of the temperature of the heat source fluid (drain). As a result, the steam generation system 1 of the present embodiment is more efficient than the conventionally known two-stage heat pump.

6A shows that the state of the inlet of the fluid to be heated is saturated water of T _h , the state of the outlet of the fluid to be heated is saturated steam of T _h (ie, the fluid to which heat is given latent heat) Ideally, the inlet of the heat-producing fluid is saturated water of T _h , and the outlet of the heat-producing fluid is supercooled water of T _l (that is, the heat-producing fluid loses sensible heat). It is TS diagram in the case of raising (hereinafter, it is called abnormal cycle). In other words, the vertical axis represents temperature and the horizontal axis represents entropy.

This abnormal cycle, that is, the area of the triangle surrounded by the solid line, becomes the minimum power (ideal power) for realizing the above conditions. Then, the resultant coefficient COP = 2 x [T _h / (T _h -T _l )].

6B is a TS diagram of a conventionally well-known single stage heat pump (reverse carno cycle). 6B shows a case where the heat exchange performance is infinite without ignoring expansion valve outlet loss and compressor overheating loss. In this case, the grade factor COP = T _h / (T _h -T _l ). As shown by the dashed-dotted line A, it is the same also if a heat pump is made into two steps of top and bottom.

Comparing FIG. 6A with FIG. 6B, it can be said that the power of the square of FIG. 6B minus the area of the triangle of FIG. 6A is an extra power compared with an abnormal cycle, and the grade coefficient falls by that much.

7 is a TS diagram of the steam generating system of this embodiment. In this case, the grade factor COP = (4/3) × [T _h / (T _h -T _l )]. That is, it becomes 4/3 times the efficiency of the conventionally well-known single stage heat pump. In addition, it was set as T _m = (T _h + T _l ) / 2 and S _m = (S ₁ + S ₂ ) / 2. Compared with Fig. 6B, the lack of the lower right portion can reduce the power and increase the efficiency.

By the way, although the number of stages was made into 2 stages in FIG. 7, as shown in FIG. 8, the area enclosed by a cycle can be made smaller, and the efficiency of the steam generation system 1 can be improved further. When the number of stages is infinite, theoretically, COP = 2 × [T _h / (T _h -T _l )]. That is, the efficiency of the conventionally known single stage heat pump can be doubled. The specific structure of the steam generation system 1 which increased the number of steps is mentioned later.

[Example 2]

9 is a schematic view showing Embodiment 2 of a steam generating system 1 of the present invention. The steam generating system 1 of the second embodiment is basically the same as the first embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the second embodiment, the configuration of the connection between the first heat pump 2 and the second heat pump 3 is different from that in the first embodiment. In the first embodiment, the first heat pump 2 and the second heat pump 3 are connected to the indirect heat exchanger 13. In the second embodiment, the first heat pump 2 and the second heat pump 3 are connected. ) Is connected to the intermediate cooler 18.

Specifically, an intermediate cooler that receives the refrigerant from the compressor 9 of the second heat pump 3 and the refrigerant from the expansion valve 6 of the first heat pump 2 and heats the heat by directly contacting both refrigerants ( 18), the intermediate cooler 18 is the condenser 10 of the second heat pump 3 and becomes the evaporator 7 of the first heat pump 2. More specifically, a hollow tank (direct heat exchanger) is used as the intermediate cooler 18, and the refrigerant from the compressor 9 of the second heat pump 3 and the expansion valve 6 of the first heat pump 2 are used. By taking in refrigerant from the tank and making direct contact in the tank, condensation of the refrigerant from the compressor 9 of the second heat pump 3 and vaporization of the refrigerant from the expansion valve 6 of the first heat pump 2. Promote. The liquid refrigerant obtained thereby is transferred to the expansion valve 11 of the second heat pump 3, while the gas-liquid mixed refrigerant is passed through the second evaporator 8 of the first heat pump 2 to the compressor 4. It is good to transfer to.

In the second embodiment, the refrigerant from the expansion valve 6 of the first heat pump 2 is basically transferred to the compressor 4 through the intermediate cooler 18 and the second evaporator 8 in order. Also in the 2nd evaporator 8, since a refrigerant | coolant is boiled, the gaseous-phase powder and liquid phase powder are mixed and conveyed from the intermediate | middle cooler 18 to the 2nd evaporator 8 by a predetermined ratio. The mixing ratio is adjusted by, for example, adjusting the opening degree of valves (not shown) respectively provided in the refrigerant flow path for the gaseous phase powder and the liquid flow path for the liquid phase powder from the intermediate cooler 18.

In addition, in the second embodiment, the third sub heat exchanger 16 is not installed. Since other configurations are the same as those of the first embodiment, description thereof is omitted.

Next, the modification of the steam generation system 1 of this Embodiment 2 is demonstrated. At this time, it demonstrates centering around a different point from FIG. 9, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

10 is a schematic view showing a modification of the steam generating system 1 of the second embodiment. In the steam generation system 1 of FIG. 9, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 18, but in the present variant, instead of or to the supply to the intermediate cooler 18. In addition, it is supplied to the refrigerant | coolant flow path from the intermediate | middle cooler 18 of the 1st heat pump 2 to the compressor 4, as shown by the dashed-dotted line A. In addition, in FIG. At this time, the inlet side or the outlet side of the second evaporator 8 may be sufficient, or when the fourth sub heat exchanger 17 is provided, the inlet side of the fourth sub heat exchanger 17 may be an outlet side. In addition, as shown by the dashed-dotted line B, the refrigerant | coolant from the compressor 9 of the 2nd heat pump 3 flows into the refrigerant | coolant flow path from the expansion valve 6 of the 1st heat pump 2 to the intermediate | middle cooler 18. As shown in FIG. May be joined.

[Example 3]

11 is a schematic view showing Embodiment 3 of a steam generation system 1 of the present invention. The steam generating system 1 of the third embodiment is basically the same as the first embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the third embodiment, the configuration of the connection between the first heat pump 2 and the second heat pump 3 is different from that in the first embodiment. In the first embodiment, the first heat pump 2 and the second heat pump 3 are connected to the indirect heat exchanger 13, but in the third embodiment, the first heat pump 2 and the second heat pump 3 are connected. ) Is connected to the intermediate cooler 19.

Specifically, the refrigerant from the compressor 9 of the second heat pump 3 and the refrigerant from the expansion valve 6 of the first heat pump 2 are received, and both refrigerants are brought into direct contact with each other to exchange heat. Intermediate cooler for heat exchange without mixing both the refrigerant and the refrigerant supplied from the condenser 5 of the first heat pump 2 to the expansion valve 11 of the second heat pump 3 without passing through the expansion valve 6 ( 19), the intermediate cooler (19) is the condenser (10) of the second heat pump (3) and the evaporator (7) of the first heat pump (2). More specifically, as the intermediate cooler 19, an indirect heat exchanger for exchanging heat without mixing the respective fluids of the first region 20 and the second region 21 is used, and the second heat pump ( The refrigerant from the compressor 9 of 3) and the refrigerant from the expansion valve 6 of the first heat pump 2 directly exchange heat, while the condenser of the first heat pump 2 is in the second region 21. What is necessary is just to supply a refrigerant | coolant through the expansion valve 11 of the 2nd heat pump 3, without passing through the expansion valve 6 from (5). In this case, the refrigerant from the compressor 9 of the second heat pump 3 is subjected to intermediate cooling by the refrigerant from the expansion valve 6 of the first heat pump 2 in the intermediate cooler 19. In the compressor 4 of the first heat pump 2, the gas refrigerant becomes a high-pressure, high-temperature gas refrigerant, and condenses in the condenser 5 of the first heat pump 2. A portion of the liquid refrigerant is then transferred to the first region 20 of the intermediate cooler 19 through the expansion valve 6 of the first heat pump 2, while the remaining liquid refrigerant is transferred to the intermediate cooler 19. After the pressure is reduced by the expansion valve 11 of the second heat pump 3 through the second region 21 and vaporized in the evaporator 12 of the second heat pump 3, the second heat pump ( It is returned to the compressor 9 of 3).

According to this configuration, in the third embodiment, the third sub heat exchanger 16 is not installed. Since other configurations are the same as those of the first embodiment, description thereof is omitted.

Next, a modification of the steam generating system 1 of the third embodiment will be described. At this time, it demonstrates centering around a different point from FIG. 11, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

12 is a schematic view showing a modification of the steam generation system 1 of the third embodiment. In the steam generation system 1 of FIG. 11, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 19, but in the present variation, or instead of the supply to the intermediate cooler 19. In addition, as shown by the dashed-dotted line A, it is supplied to the refrigerant | coolant flow path from the intermediate | middle cooler 19 of the 1st heat pump 2 to the compressor 4. At this time, the inlet side or the outlet side of the second evaporator 8 may be sufficient, or when the fourth sub heat exchanger 17 is provided, the inlet side of the fourth sub heat exchanger 17 may be an outlet side. Moreover, you may supply to the refrigerant | coolant flow path from the expansion valve 6 of the 1st heat pump 2 to the intermediate | middle cooler 19, as shown by the dashed-dotted line B. As shown in FIG. In addition, when installing the separator 22 mentioned later in the refrigerant | coolant flow path from the expansion valve 6 of the 1st heat pump 2 to the intermediate | middle cooler 19, even if it is a refrigerant | coolant flow path from the expansion valve 6 to the separator 22, it will be. The gas may be supplied to the coolant flow path 23 for the gas phase from the separator 22.

In the present modification, the separator 22 is provided on the outlet side of the expansion valve 6 of the first heat pump 2. In this case, the liquid phase liquid separated from the separator 22 is supplied to the intermediate | middle cooler 19, and a gaseous phase powder is supplied from the intermediate | middle cooler 19 of the 1st heat pump 2 to the compressor 4, as shown by the flow path 23. As shown in FIG. Is supplied to the refrigerant passage. At this time, the inlet side or the outlet side of the second evaporator 8 may be sufficient, or when the fourth sub heat exchanger 17 is provided, the inlet side of the fourth sub heat exchanger 17 may be an outlet side.

In addition, the separator 22 is provided in place of or in addition to the refrigerant flow path from the expansion valve 6 of the first heat pump 2 to the intermediate cooler 19, from the intermediate cooler 19 to the second evaporator. You may install in the refrigerant | coolant flow path to (8). In that case, the liquid phase powder may be supplied to the second evaporator 8, and the gaseous phase powder may be supplied to any place in the refrigerant passage from the second evaporator 8 to the compressor 4.

Example 4

13 is a schematic view showing Embodiment 4 of a steam generating system 1 of the present invention. The steam generating system 1 of the fourth embodiment is basically the same as the first embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the first embodiment, the first evaporator 7 and the second evaporator 8 are installed in series, but in the fourth embodiment, the first evaporator 7 and the second evaporator 8 are installed in parallel. That is, in this embodiment, the refrigerant from the expansion valve 6 of the first heat pump 2 is supplied to the compressor 4 through the first evaporator 7 and the third sub-heat exchanger 16, if desired. It is supplied to the compressor 4, and is supplied to the compressor 4 via the second evaporator 8 and the fourth sub heat exchanger 17, which is installed as desired.

FIG. 14 shows the circulation of the refrigerant of the first heat pump 2 to the first evaporator 7 of the first heat pump 2 and the third sub-heat exchanger 16 which is desired. In addition to showing the procedure, a diagram showing the flow order of the refrigerant of the first heat pump 2 to the second evaporator 8 of the first heat pump 2 and the fourth sub-heat exchanger 17 as desired. to be. The number in the figure shows the flow order to each heat exchanger 7, 16, 8, and 17, and the number 0 shows that the heat exchanger is not installed. In addition, the same number has shown installing in parallel.

A few specific examples are given, for example, 1-2-1-2 in the first row. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 2, the 2nd evaporator 8 is 1, and the 4th sub heat exchanger 17 is 2. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the refrigerant passage passing through the first evaporator 7 and the third sub heat exchanger 16 in sequence, and the second evaporator 8. And the refrigerant passage passing through the fourth sub heat exchanger 17 in this order in parallel, and are transferred to the compressor 4.

In the second line, 1-2-1-3 is present. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 2, the 2nd evaporator 8 is 1, and the 4th sub heat exchanger 17 is 3. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the first evaporator 7 and the second evaporator 8 in parallel, and then the third sub heat exchanger 16 The four sub heat exchangers 17 are sequentially passed to the compressor 4. Alternatively, the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the first evaporator 7 and the third sub heat exchanger 16 in order, and in parallel therewith, the second evaporator 8. After passing through), both are joined and transferred to the compressor 4 through the fourth sub heat exchanger 17.

In addition, it is 1-0-1-1 in the 4th line. That is, the 1st evaporator 7 is 1, the 3rd sub heat exchanger 16 is 0, the 2nd evaporator 8 is 1, and the 4th sub heat exchanger 17 is 1. In this case, the third sub heat exchanger 16 is not installed, and the refrigerant from the expansion valve 6 of the first heat pump 2 passes through the first evaporator 7, the second evaporator 8, and the fourth sub. After passing through the heat exchanger 17 in parallel, it is conveyed to the compressor 4.

In any case, basically, the first evaporator 7 and the second evaporator 8 are replaced by the third sub heat exchanger 16 and the fourth sub heat exchanger in the flow order of the refrigerant of the first heat pump 2. It is preferable to set so that it is earlier than 17). Since other configurations are the same as those of the first embodiment, description thereof is omitted.

[Example 5]

15 is a schematic view showing Embodiment 5 of a steam generating system 1 of the present invention. The steam generating system 1 of the fifth embodiment is basically the same as the second embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the second embodiment, the gaseous phase liquid and the liquid phase powder from the intermediate cooler 18 are supplied to the compressor 4 through the second evaporator 8 and the fourth sub-heat exchanger 17, which is desired, at a predetermined mixing ratio. In the fifth embodiment, a refrigerant flow path connecting the gas phase part of the intermediate cooler 18 and the compressor 4 and a refrigerant flow path connecting the liquid phase part of the intermediate cooler 18 and the compressor 4 are provided in parallel. The latter refrigerant path is provided with a second evaporator 8 and a fourth sub heat exchanger 17 as desired. In addition to supplying the refrigerant for the gaseous phase powder from the intermediate cooler 18 directly to the inlet side of the compressor 4, the fourth sub-heat exchanger 17 is provided as shown by the dashed-dotted line A. FIG. In that case, you may supply it in front of it.

The relationship of the fifth embodiment with respect to the fourth embodiment corresponds to the relationship of the second embodiment with respect to the first embodiment. Since the other structure is the same as that of Example 2, description is abbreviate | omitted.

Next, the modification of the steam generating system 1 of Example 5 is demonstrated. At this time, it demonstrates centering around difference with FIG. 15, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

16 is a schematic view showing a modification of the steam generating system 1 of the fifth embodiment. In the steam generation system 1 of FIG. 15, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 18, but in the present variant, instead of or to the supply to the intermediate cooler 18. In addition, it is supplied to the refrigerant | coolant flow path of the gaseous-phase fraction from the intermediate cooler 18 to the compressor 4, as shown by the dashed-dotted line A, or from the intermediate | cooler 18 as shown by the dashed-dotted line B. It supplies to the refrigerant | coolant flow path of liquid content to the compressor 4. In the latter case, the inlet side or the outlet side of the second evaporator 8 may be sufficient, or when the fourth sub heat exchanger 17 is provided, the inlet side of the fourth sub heat exchanger 17 may be either the outlet side or the outlet side. good. In addition, as shown by the dashed-dotted line C, the refrigerant | coolant from the compressor 9 of the 2nd heat pump 3 flows into the refrigerant | coolant flow path from the expansion valve 6 of the 1st heat pump 2 to the intermediate | middle cooler 18. As shown in FIG. May be joined.

[Example 6]

17 is a schematic diagram showing Embodiment 6 of a steam generating system 1 of the present invention. The steam generating system 1 of the sixth embodiment is basically the same as the third embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the third embodiment, the refrigerant from the expansion valve 6 of the first heat pump 2 is supplied to the compressor 4 through the intermediate cooler 19 and the second evaporator 8, but in the sixth embodiment, The refrigerant from the expansion valve 6 of the first heat pump 2 is supplied to the compressor 4 via the intermediate cooler 19 but not the second evaporator 8, and in parallel therewith to the intermediate cooler 19. ) Is supplied to the compressor 4 via the second evaporator 8 without passing through.

As indicated by the dashed-dotted line A, the supply of the refrigerant from the expansion valve 6 of the first heat pump to the intermediate cooler 19 is controlled by the intermediate cooler 19 from the compressor 9 of the second heat pump 3. May be combined with a coolant to In addition, as shown by the dashed-dotted line X, the refrigerant | coolant from the intermediate | middle cooler 19 to the compressor 4 may be supplied to the front of the 4th sub heat exchanger 17 as needed.

The relationship of the sixth embodiment with respect to the fourth embodiment corresponds to the relationship of the third embodiment with respect to the first embodiment. Since the other structure is the same as that of Example 3, description is abbreviate | omitted.

Next, a modification of the steam generating system 1 of the sixth embodiment will be described. At this time, it demonstrates centering around a different point from FIG. 17, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

18 is a schematic view showing a modification 1 of the steam generation system 1 of the sixth embodiment. In the steam generation system 1 of FIG. 17, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 19, but in the present variant, instead of or to supply to the intermediate cooler 19. In addition, as shown by the dashed-dotted line A, you may join the refrigerant flow path from the expansion valve 6 of the 1st heat pump 2 to the intermediate | middle cooler 19, and as shown by the dashed-dotted line B, Similarly, the refrigerant flow path from the expansion valve 6 to the compressor 4 through the second evaporator 8 may be supplied, or the refrigerant flow path from the intermediate cooler 19 to the compressor 4 as indicated by the dashed-dotted line C. You may supply to.

19 is a schematic view showing a modification 2 of the steam generation system 1 of the sixth embodiment. In this modification, separators 22 (22A to 22C) are provided on the outlet side of the expansion valve 6 of the first heat pump 2. The refrigerant from the expansion valve 6 of the first heat pump 2 branches into the flow passage 25 to the second evaporator 8 and the flow passage 26 to the intermediate cooler 19 through the common flow passage 24. You may provide the separator 22 in any place. What is provided in the common flow path 24 is installed in the flow path 26 to the 2nd separator 22B and the intermediate | middle cooler 19 provided in the flow path 25 to the 1st separator 22A and the 2nd evaporator 8. It can be provided in the combination shown in FIG. 20 as 22 C of 3rd separators. In Fig. 20, 1 indicates installation and 0 indicates no installation.

In FIG. 20, no separator is provided in the first line pattern. In the second pattern, only the first separator 22A is provided. In this case, the liquid phase powder separated by the separator 22A is supplied to the intermediate | middle cooler 19 and the 2nd evaporator 8, and a gaseous phase powder is shown by the dashed-dotted line A from the 2nd evaporator 8 to the compressor 4 ) Is supplied to any one of the locations.

In the third row of patterns, only the second separator 22B is provided. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 is supplied to the intermediate cooler 19 and the separator 22B, and the liquid component separated from the separator 22B is supplied to the second evaporator 8. The gaseous phase powder is supplied to any one of the locations from the second evaporator 8 to the compressor 4 as indicated by the dashed-dotted line A. FIG.

In the fourth row of patterns, only the third separator 22C is provided. In this case, the refrigerant from the expansion valve 6 of the first heat pump 2 is supplied to the second evaporator 8 and the separator 22C, and the liquid component separated from the separator 22C is supplied to the intermediate cooler 19. The gaseous phase powder is supplied to any one of the locations from the second evaporator 8 to the compressor 4 as indicated by the dashed-dotted line A. FIG.

In addition, as shown in the fifth row pattern, both the second separator 22B and the third separator 22C may be provided. In any case, by providing the separator 22 so that the gas phase powder does not enter the intermediate cooler 19 or the second evaporator 8, the heat exchanger constituting these can be made small.

[Example 7]

21 is a schematic diagram showing Embodiment 7 of a steam generating system 1 of the present invention. The steam generating system 1 of the seventh embodiment is basically the same as that of the fourth embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the fourth embodiment, the first evaporator 7 and the second evaporator 8 are installed in parallel, and the refrigerants through the common expansion valve 6 are respectively passed. However, in the seventh embodiment, the first heat pump 2 Refrigerant from the condenser (5) is a refrigerant passage including a first expansion valve (6A) and a first evaporator (7), and a refrigerant passage including a second expansion valve (6B) and a second evaporator (8). After passing in parallel, it is supplied to the compressor 4. Since other configurations are the same as those of the fourth embodiment, description thereof is omitted.

[Example 8]

22 is a schematic diagram showing Embodiment 8 of a steam generating system 1 of the present invention. The steam generating system 1 of the eighth embodiment is basically the same as that of the fifth embodiment. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the fifth embodiment, the refrigerant flow path for the gas phase powder and the liquid flow path for the liquid phase powder from the intermediate cooler 18 are installed in parallel, and the refrigerant flows through the common expansion valve 6, respectively. The refrigerant from the condenser 5 of the first heat pump 2 is supplied to the intermediate cooler 18 via the first expansion valve 6A, and in parallel therewith the second evaporator through the second expansion valve 6B. It is also supplied to (8). And the gaseous-phase part of the intermediate | middle cooler 18 and the compressor 4 are connected by the refrigerant | coolant flow path. On the other hand, the refrigerant from the second expansion valve 6B is supplied to the compressor 4 through the second evaporator 8 or the fourth sub heat exchanger 17 provided as desired. Since other configurations are the same as those in the fifth embodiment, the description is omitted.

Next, a modification of the steam generating system 1 of the eighth embodiment will be described. At this time, it demonstrates centering around a different point from FIG. 22, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

FIG. 23 is a schematic view showing a modification 1 of the steam generation system 1 of the eighth embodiment. In the steam generation system 1 of FIG. 22, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 18, but in the present variation, or instead of the supply to the intermediate cooler 18. In addition, it may supply to the refrigerant | coolant flow path from the intermediate | middle cooler 18 to the compressor 4, as shown by the dashed-dotted line A, and from the 2nd expansion valve 6B, as shown by the dashed-dotted line B. FIG. You may supply to any place of the refrigerant | coolant flow path to the compressor 4 through the 2nd evaporator 8. As shown in FIG. Alternatively, the refrigerant from the compressor 9 of the second heat pump 3 merges with the refrigerant from the first expansion valve 6A of the first heat pump 2 as indicated by the dashed-dotted line C. You may supply to the cooler 18.

24 is a schematic view showing a modification 2 of the steam generation system 1 of the eighth embodiment. In the present modification, the separator 22 is provided in the refrigerant passage from the second expansion valve 6B to the second evaporator 8. As a result, the refrigerant from the second expansion valve 6B is gas-liquid separated in the separator 22, the liquid component is supplied to the second evaporator 8, and the gas phase component is represented by the dashed-dotted line A. 2 is supplied to any one of the refrigerant | coolant flow paths from the evaporator 8 to the compressor 4.

[Example 9]

25 is a schematic view showing Embodiment 9 of a steam generating system 1 of the present invention. The steam generating system 1 of Example 9 is basically the same as that of Example 6. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In the sixth embodiment, in the first heat pump 2, the refrigerant from the common expansion valve 6 is passed in parallel to the intermediate cooler 19 and the second evaporator 8 and supplied to the compressor 4. In the ninth embodiment, the refrigerant from the condenser 5 of the first heat pump 2 is supplied to the intermediate cooler 19 via the first expansion valve 6A and in parallel therewith the second expansion valve 6B. It is also supplied to the second evaporator 8 through. In addition, as shown by the dashed-dotted line A, the refrigerant | coolant from the 2nd expansion valve 6B may join with the refrigerant | coolant from the compressor 9 of the 2nd heat pump 3, and may supply it to the intermediate | middle cooler 19. As shown in FIG. . Since other configurations are the same as those in the sixth embodiment, the description is omitted.

Next, a modification of the steam generating system 1 of the ninth embodiment will be described. At this time, it demonstrates centering around a different point from FIG. 25, and abbreviate | omits description about the same structure. In addition, it demonstrates by attaching | subjecting the same code | symbol to the corresponding location.

Fig. 26 is a schematic diagram showing a modification 1 of the steam generation system 1 of the ninth embodiment. In the steam generation system 1 of FIG. 25, the refrigerant from the compressor 9 of the second heat pump 3 is supplied to the intermediate cooler 19, but in the present variant, instead of or to supply to the intermediate cooler 19. In addition, as shown by the dashed-dotted line A, you may join the refrigerant flow path from the 1st expansion valve 6A to the intermediate | middle cooler 19, and as shown by the dashed-dotted line B, the intermediate | middle cooler 19 is shown. From the second expansion valve 6B to the compressor 4 via the second evaporator 8 as shown by the dashed-dotted line C. You may supply.

27 is a schematic view showing a modification 2 of the steam generation system 1 of the ninth embodiment. In the present modification, the first separator 22A is provided in the refrigerant passage from the second expansion valve 6B to the second evaporator 8. Accordingly, the refrigerant from the second expansion valve 6B is gas-liquid separated in the first separator 22A, the liquid phase is supplied to the second evaporator 8, and the gas phase is represented by the dashed-dotted line A. Similarly, it is supplied to any one place of the refrigerant | coolant flow path from the 2nd evaporator 8 to the compressor 4. Moreover, you may provide the 2nd separator 22B in the refrigerant | coolant flow path from the 1st expansion valve 6A to the intermediate | middle cooler 19. As shown in FIG. As a result, the refrigerant from the first expansion valve 6A is gas-liquid separated in the second separator 22B, the liquid component is supplied to the intermediate cooler 19, and the gas phase component is indicated by the dashed-dotted line B. As shown in FIG. It is supplied to any one place of the refrigerant | coolant flow path from the 2nd evaporator 8 to the compressor 4.

FIG. 28: is a figure which shows the combination of installation of the 1st separator 22A and the 2nd separator 22B. In this figure, 1 represents installation and 0 represents no installation. As shown in this figure, both separators 22A and 22B may be provided, only one separator may be installed, and the installation of both separators may be omitted.

[Example 10]

In each said embodiment, although the 1st heat pump 2 was comprised by single stage and the 2nd heat pump 3 was also comprised by single stage, the number of stages of each heat pump 2 and 3 can be changed suitably. In other words, in each of the above embodiments, when the first stage heat pump 2 and the second stage heat pump 3 are combined, the steam generation system 1 as a whole is shown as an example of a two stage heat pump. Although the number of stages of the heat pump which comprises the steam generating system 1 can be changed suitably. In addition, the multistage (multistage) heat pump includes a multistage (multistage) heat pump as shown in FIG. 1, or a heat pump in combination of both, in addition to the one-stage multistage heat pump as shown in FIG. 9.

For example, FIG. 29A has shown the example which comprised the 1st heat pump 2 by 2 steps, and the 2nd heat pump 3 by 1 step. In other words, the steam generating system 1 is comprised by the heat pump of three stages. The second heat pump 3 may also be configured in two or more stages as in the conventionally known two-stage heat pump.

In the steam generating system 1 of FIG. 29A, the first evaporator is used as the evaporator of each heat pump (first heat pumps 2A and 2B in each stage) except for the lowermost heat pump (second heat pump 3). 7A, 7B and 2nd evaporator 8A, 8B are provided, the heat pumps which are adjacent up and down adjacent to the 1st evaporator 7A, 7B are connected, and a heat source fluid passes through 2nd evaporator 8A, 8B. do. At this time, adjacent upper and lower heat pumps may be connected in any relationship described in the above embodiments. That is, the heat pumps adjacent to the upper and lower sides are connected to the indirect heat exchangers 13 (13A, 13B) in the illustrated example, but may be connected to the intermediate coolers 18 and 19 as described above. In addition, the heat pump of each stage which comprises the 1st heat pump 2 is not limited to the structure of the said Example 1, It is good also as a structure of another Example. Then, the heat source fluid typically passes each second evaporator 8 (8A, 8B) in order from the top heat pump sequentially to the bottom heat pump.

When the steam generating system 1 is constituted by three or more stages of heat pumps (in other words, when the first heat pump 2 is provided in multiple stages), the lowermost heat pump [second heat pump 3] is excluded. In the first heat pumps 2A and 2B of all stages, the first evaporators 7A and 7B and the second evaporators 8A and 8B are provided as evaporators, and the first and second evaporators 7A and 7B are provided. Adjacent heat pumps are connected to each other, and it is preferable that the heat source fluid passes sequentially through the second evaporators 8A and 8B from the upper end to the lower end.

The reason for this configuration is preferable as follows. That is, FIG. 29B is a TS diagram in which the first heat pump 2 is single stage and the second heat pump 3 is two stages, and FIG. 29C is the first heat pump 2 having two stages, and each stage thereof. It is TS diagram when the 1st evaporator 7A, 7B and the 2nd evaporator 8A, 8B are provided, and the 2nd heat pump 3 is made single. When FIG. 29B and FIG. 29C are compared, the area of the loss which hatched was made smaller in FIG. 29C. Therefore, it is preferable that the steam generation system 1 is provided with the 2nd evaporator 8A, 8B in the heat pump 2A, 2B of each stage except the heat pump 3 of the lower stage, and let a heat source fluid pass. .

In this way, when the steam generating system 1 is constituted by three or more stages of heat pumps (in other words, when the first heat pump 2 is provided in multiple stages), the first sub heat exchanger 14 is to be installed. In this case, the first sub heat exchanger 14 may be installed at a heat pump at the uppermost stage (heat pump 2A at the uppermost stage of the first heat pump 2).

In addition, in the case where the steam generating system 1 is constituted by three or more stages of heat pumps, when the second sub heat exchanger 15 is to be installed, the second sub heat exchanger 15 is the lowest heat pump [second The lowermost heat pump of the heat pump 3].

In addition, in the case where the steam generating system 1 is constituted by three or more stages of heat pumps, when the third sub heat exchanger 16 and / or the fourth sub heat exchanger 17 are to be installed, the third sub heat exchanger 17 The 16 and / or 4th sub heat exchanger 17 can be installed in the 1st heat pump 2 (2A, 2B) of each stage. In this case, in the lowermost first heat pump 2B, the third sub-heat exchanger 16 is a refrigerant from the expansion valve 6B at the lowermost end of the first heat pump 2 to the compressor 4B, and the second. It becomes an indirect heat exchanger of the refrigerant from the compressor 9 of the heat pump 3 to the first evaporator 7B, but in each first heat pump 2A above it, the third sub heat exchanger 16 Indirect heat exchange of the refrigerant from the expansion valve 6A of the first heat pump 2A to the compressor 4A and the refrigerant from the compressor 4B of the first lower heat pump 2B to the first evaporator 7A. It's a spirit.

30 is a schematic view showing an example of a steam system 27 using the steam generating system 1 of the first embodiment. Here, for convenience of description, the second evaporator 8 of the first heat pump 2, the fourth sub heat exchanger 17 provided as desired, the evaporator 12 of the second heat pump 3, The second sub heat exchanger 15 provided as desired will be referred to as a heat raising heat exchanger 8, 17, 12, 15. In addition, the condenser 5 of the 1st heat pump 2 and the 1st sub heat exchanger 14 installed as desired are called heat exchangers 5 and 14 for steam generation.

The steam system 27 has a steam generating system 1 and a boiler 28.

Although the steam generating system 1 uses the structure of Example 1, you may use the structure of the other Example mentioned above. In any case, the steam generating system 1 draws up the heat of the drain in the heat raising heat exchanger 8, 17, 12, 15, and heats the water in the steam generating heat exchanger 5, 14. To generate steam. Therefore, the drain from the steam use facility 29 passes through the heat exchanger heat exchanger 8, 17, 12, 15. The method of passing the drain to each of the evaporators 8 and 12 and the sub heat exchangers 17 and 15 as the heat raising heat exchangers 8, 17, 12 and 15 is as described with reference to FIG. 2.

On the other hand, water can be supplied to the heat exchangers 5 and 14 for steam generation by the feed water pump 30, and the desired amount of water is stored in the heat exchangers 5 and 14 for steam generation. Specifically, pure water or soft water, or instead of or mixed with it, the drain from the steam using facility 29 passes through the feed pump 30, the feed water valve 31, the check valve 32, and the heat exchanger for steam generation. It is supplied to (5, 14). The method of passing water or steam to the condenser 5 and the first sub heat exchanger 14 as the steam generating heat exchangers 5 and 14 is also as described in each of the above embodiments.

Boiler 28 is typically a fuel fired boiler or an electric boiler. A fuel combustion boiler is a device that vaporizes water by combustion of a fuel, and the presence or absence of combustion is adjusted so as to maintain a desired vapor pressure. Moreover, an electric boiler is an apparatus which vaporizes water with an electric heater, and the presence or absence of the electric power feeding to an electric heater is adjusted so that steam pressure may be desired. Water can be supplied to the boiler 28 through the feed pump 33 and the check valve 34, and the water level in the cylinder of the boiler 28 is desired.

The steam path 35 from the steam generating heat exchangers 5 and 14 and the steam path 36 from the boiler 28 are configured to join. This joining can also be performed using a steam header. Moreover, the check valve 37 is provided in the steam path 35 from the heat exchangers 5 and 14 for steam generation upstream rather than a confluence part. Thereby, while the steam generating system 1 is stopped, the steam from the boiler 28 is prevented from flowing back to the steam generating heat exchangers 5 and 14.

Moreover, the boiler steam supply valve 38 is provided in the steam path 36 from the boiler 28 upstream rather than a confluence part. The boiler steam supply valve 38 becomes a magnetic pressure reducing valve (secondary pressure regulating valve) in the example of illustration. Further, the upstream side of the boiler steam supply valve 38 is maintained at a higher pressure by the boiler 28 than the downstream side.

Steam from the steam generating systems 5, 14 or boiler 28 is sent to one or a plurality of steam using facilities 29. The drain of the steam using facility 29 is discharged to the separator tank 40 of a hollow container shape through the 1st steam trap 39. The first flow passage 41 is connected to the upper part of the separator tank 40, and the second flow path 42 is connected to the lower part of the separator tank 40.

The heat flow-up heat exchangers 8, 17, 12, 15 and the second steam trap 43 are provided in the first flow path 41 in order from the side of the separator tank 40. Due to this configuration, the drain of the steam using facility 29 is discharged under low pressure by the first steam trap 39 and then passed through the heat raising heat exchanger 8, 17, 12, 15 and then the second. By the steam trap 43 it is discharged further under low pressure (typically under atmospheric pressure). That is, the drain of the steam using equipment 29 is discharged through the first steam trap 39 to become flash steam and its condensed water, and passes through the heat-up heat exchanger 8, 17, 12, 15 to cool ( And subcooled) and then exit from the second steam trap 43. In such a configuration, in the heat raising heat exchanger 8, 17, 12, 15, the fluid that heats the refrigerant is a pressure exceeding atmospheric pressure and can be maintained at a temperature exceeding 100 ° C. In addition, the wastewater from the 2nd steam trap 43 may be discarded as it is, may be supplied to the water supply tank 44 to the boiler 28 and / or the heat exchangers 5 and 14 for steam generation, and such a water supply tank 44 It may be used as feed water to the heat exchangers 5 and 14 for steam generation without passing through).

On the other hand, the discharge valve 45 is provided in the second flow passage 42. The discharge valve 45 is a magnetic pressure reducing valve (primary pressure regulating valve) in the illustrated example. With such a configuration, the drain of the steam using facility 29 is discharged under low pressure by the first steam trap 39, and then discharged further under low pressure (typically under atmospheric pressure) by the discharge valve 45. do. And the fluid from the discharge valve 45 may be discarded as it is, may be supplied to the water supply tank 44 to the boiler 28 and / or the heat exchangers 5 and 14 for steam generation, and this water supply tank 44 may be supplied. It may be used as water supply to the heat exchangers 5 and 14 for steam generation without passing through.

In addition, for emergency or power failure, the normally closed solenoid valve 46 is provided in the first flow path 41 between the separator tank 40 and the heat raising heat exchanger 8, 17, 12, 15. On the other hand, it is preferable to provide a normally open solenoid valve 47 in the second flow path 42 in parallel with the discharge valve 45. In this case, normally, the solenoid valve 46 of the 1st flow path 41 is kept open, and the solenoid valve 47 of the 2nd flow path 42 is kept closed. In the event of an emergency or a power failure, the solenoid valve 46 of the first flow passage 41 is closed and the solenoid valve 47 of the second flow passage 42 is opened, so that the drain from the steam using facility 29 attracts heat. It is discharged without passing through the raising heat exchanger (8, 17, 12, 15).

The steam generating heat exchangers 5 and 14 are supplied with pure water or soft water, a drain from the steam using facility 29, or a mixture of these drains with pure water or soft water. Although a water supply system for it does not matter in particular, it can be set as the following structures, for example. In addition, the drain from the steam using facility 29 may not only be in a liquid state but also in a gas-liquid two-phase state (flash steam generated when a drain exceeding the atmospheric pressure is released at a lower pressure than that) and the condensate thereof. .

(A) As shown by the dashed-dotted line A, the drain which consists of the liquid isolate | separated from the separator tank 40 is supplied from the upstream side to the inlet side of the feed water pump 30 rather than the discharge valve 45. FIG.

(B) As shown by the dashed-dotted line B, the water supply pump 30 drains the drain after passing through the heat | fever heat exchanger 8, 17, 12, 15 from the upstream rather than the 2nd steam trap 43. FIG. Supply to the inlet side of the. In addition, although the heat raising heat exchangers 8, 17, 12, and 15 are constituted by a plurality of heat exchangers, as shown by the two-dot chain line B ', after passing through some of the heat exchangers, the drain is branched to supply a water feed pump ( You may supply to the inlet side of 30).

(C) As shown by the dashed-dotted line C, the drain after passing through the heat | fever heat exchanger 8, 17, 12, 15 is supplied from the downstream of the 2nd steam trap 43 to the feed pump 30 from the downstream side. Is supplied to the inlet side.

(D) As shown by the broken-line area | region of FIG. 30 lower part, the drain from the 2nd steam trap 43 and / or the drain from the discharge valve 45 are once gathered in the feed water tank 44, and this feed water tank The water in 44 is supplied to the inlet side of feed water pump 30. Pure water or soft water may be appropriately supplied to the water supply tank 44 in addition to the drain from the steam use facility 29.

(E) The combination of any two or more of the above-mentioned A-D may be sufficient. In this case, two or more water supply passages join and feed water to the steam generating heat exchangers 5 and 14. However, when the pressures in the water supply passages are different, the water supply pump 30 is not installed after each of the supply passages joins. It is good to provide a water supply pump in each water supply path in front of a confluence part.

The first sensor 48 which consists of a pressure sensor is provided in the position which can detect the pressure of the steam of the steam from the heat exchanger 5 and 14 for steam generation, and the steam from the boiler 28. Further, a second sensor 49 made of a pressure sensor or a temperature sensor is provided so as to be able to detect the pressure or temperature of the fluid passing through the heat raising heat exchanger 8, 17, 12, 15. And the steam generation system 1 is controlled based on the detection value of one or both of the 1st sensor 48 and the 2nd sensor 49. As shown in FIG.

For example, the compressor of the uppermost heat pump (compressor 4 of the first heat pump) is controlled based on the detected pressure of the first sensor 48, and the compressor of each heat pump lower than that is controlled. The compressor 9 of the two heat pumps 3 may be controlled based on the pressure of the refrigerant in the condenser 10 at the stage or the evaporators 7 and 8 at the upper end.

Alternatively, the heat pump of the lowermost heat pump (compressor 9 of the second heat pump 3) is controlled based on the detected pressure or the detected temperature of the second sensor 49, and each heat pump above it. The compressor (compressor 4 of the first heat pump 2) may be controlled based on the pressure or temperature of the refrigerant in the evaporators 7 and 8 at the stage or the condenser 10 at the lower stage.

FIG. 31 is a schematic diagram illustrating a modification of the steam system 27 of FIG. 30. The steam system 27 of FIG. 31 is basically the same as FIG. Therefore, below, it demonstrates centering around the difference of both, and demonstrates the same place attaching | subjecting the same code | symbol.

In this modification, the drain of the steam use installation 29 is once collected in the buffer tank 50 as a drain storage part. The drain of the buffer tank 50 can be supplied to the heat-exchanging heat exchangers 8, 17, 12, and 15 by the first flow path 41, and is also heated by the third flow path 51. It becomes possible to discharge | emission without going through the heat exchanger 8,17,12,15.

Specifically, the first flow passage 41 is connected to the lower portion of the buffer tank 50, and the third flow passage 51 is connected to the upper portion thereof. The first flow passage 41 is provided with an introduction valve 52, a heat raising heat exchanger 8, 17, 12, 15, and a second steam trap 43 in order from the side of the buffer tank 50. Introducing valve 52 is a magnetic pressure reducing valve (secondary pressure regulating valve) in the present modification.

With this configuration, the drain of the steam using facility 29 is discharged under low pressure by the inlet valve 52, and then passes through the heat raising heat exchanger 8, 17, 12, 15 and then the second steam trap. By 43, it is discharged further under low pressure (typically under atmospheric pressure). And the wastewater from the 2nd steam trap 43 may be discarded as it is, may be supplied to the water supply tank 44 to the boiler 28 and / or the heat exchangers 5 and 14 for steam generation, and such a water supply tank 44 It may be used as feed water to the heat exchangers 5 and 14 for steam generation without passing through).

On the other hand, a third steam trap 53 is provided in the third flow path 51. Since the 3rd flow path 51 is connected above the 1st flow path 41 with respect to the buffer tank 50, the drain which overflows from the buffer tank 50 is discharged | emitted from the 3rd flow path 51. As shown in FIG. The wastewater is discharged through the third steam trap 53. And the waste water from the 3rd steam trap 53 may be discarded as it is, may be supplied to the water supply tank 44 to the boiler 28 and / or the heat exchangers 5 and 14 for steam generation, and such a water supply tank 44 It may be used as feed water to the heat exchangers 5 and 14 for steam generation without passing through).

In addition, it is preferable to provide a normally closed solenoid valve 46 in the first flow path 41 between the inlet valve 52 and the buffer tank 50 for emergency or power failure. In this case, normally, the solenoid valve 46 of the 1st flow path 41 is kept open. Since the solenoid valve 46 of the first flow passage 41 is closed during an emergency or a power failure, the drain of the steam using facility 29 is heated up by the third flow passage 51. 12, 15, but not through.

Also in this modified example, the heat exchangers 5 and 14 for steam generation are supplied with pure water or soft water, the drain from a steam use installation, or the mixed water of such drain and pure water or soft water. Although a water supply system for it does not matter in particular, it can be set as the following structures like the case of FIG. 30, for example.

(A) As shown by the dashed-dotted line A, the drain from the buffer tank 50 is located upstream than the inlet valve 52 (in the case of providing the solenoid valve 46, the upstream side or the downstream side thereof). Either way, it is supplied to the inlet side of the feed water pump 30.

(B) As shown by the dashed-dotted line B, the drain after passing through the heat | fever heat exchanger 8, 17, 12, and 15 is supplied from the upstream side to the water supply pump 30 from the 2nd steam trap 43 upstream. Is supplied to the inlet side. In addition, although the heat raising heat exchangers 8, 17, 12, and 15 are constituted by a plurality of heat exchangers, as shown by the two-dot chain line B ', after passing through some of the heat exchangers, the drain is branched to supply a water feed pump ( You may supply to the inlet side of 30).

(C) As shown by the dashed-dotted line C, the drain after passing through the heat | fever heat exchanger 8, 17, 12, 15 is supplied from the downstream of the 2nd steam trap 43 to the feed pump 30 from the downstream side. Is supplied to the inlet side.

(D) As shown by the broken-line area | region of FIG. 31 lower part, the drain from the 2nd steam trap 43, the drain from the 3rd steam trap 53, etc. are once collected in the water supply tank 44, Water in the water supply tank 44 is supplied to the inlet side of the water supply pump 30. Pure water or soft water may be appropriately supplied to the water supply tank 44 in addition to the drain from the steam use facility 29. In addition, although the water supply tank 44 is a case of FIG. 30, you may make it possible to store a drain by the pressure exceeding atmospheric pressure, without opening upward.

(E) The combination of any two or more of the above-mentioned A-D may be sufficient. In this case, two or more water supply passages join and feed water to the steam generating heat exchangers 8, 17, 12, and 15, but when the pressures in the respective supply passages are different, the water supply pump 30 is joined after each of the supply passages joins. It is good to install a water supply pump in each water supply path in front of a confluence part rather than installing it.

The steam generating system 1 of this invention is not limited to the structure of each said Example, It can change suitably. For example, although the steam system 27 shown in FIG. 30 and FIG. 31 was used as an application example of the steam generation system 1, it cannot be overemphasized that it is applicable also to systems other than this. In addition, although the example which used the drain from the steam use installation 29 as a heat source of the steam generating system 1 was demonstrated, it is not limited to the drain, For example, the exhaust gas from a boiler etc. and the water used as cooling water of the exhaust gas are mentioned. , Water used as cooling water in an oil cooler of an engine (drive device such as a compressor), water used as cooling water of an engine jacket, etc. may be used.

In addition, the steam generation system 1 is not limited to the case where steam is generated by the heat while lowering the temperature of the heat source fluid. For example, the exhaust gas from the steam use facility 29 may be used as the heat source fluid. In that case, for example, in FIG. 1, the exhaust steam passes through the fourth sub heat exchanger 17 and the second evaporator 8 of the first heat pump 2, and passes through the second evaporator 8. After that, the pressure may be reduced by a steam trap, an orifice or a pressure reducing valve, and passed through the second sub heat exchanger 15 and the evaporator 12 of the second heat pump 3. A steam trap or the like may or may not be provided on the outlet side of the evaporator 12 of the second heat pump 3 in the flow path of the exhaust steam. That is, the steam passing through the evaporator 12 of the second heat pump 3 may be in a state exceeding atmospheric pressure or may be atmospheric pressure. It goes without saying that one or both of the fourth sub heat exchanger 17 and the second sub heat exchanger 15 can be omitted.

1: steam generation system 2: first heat pump
3: second heat pump 4: compressor (of first heat pump)
5: condenser (of first heat pump) 6: expansion valve (of first heat pump)
7: the first evaporator (of the first heat pump)
8: 2nd evaporator (of 1st heat pump) 9: 2nd evaporator (of 2nd heat pump)
10: condenser (of second heat pump) 11: expansion valve (of second heat pump)
12: evaporator (of the second heat pump) 13: indirect heat exchanger
14: first sub heat exchanger 15: second sub heat exchanger
16: third sub heat exchanger 17: fourth sub heat exchanger
18: intermediate cooler 19: intermediate cooler
22 separator 27: steam system
29: steam equipment

Claims (12)

A first heat pump composed of a single stage or a plurality of stages and having a first evaporator and a second evaporator at least at the bottom;
A second heat pump composed of a single stage or a plurality of stages and connected to the first heat pump via a topmost condenser serving as the first stage evaporator;
The heat source fluid is sequentially passed through the second evaporator of the first heat pump and the lowest evaporator of the second heat pump,
A steam generating system, characterized in that to generate steam by heating water in the condenser at the top of the first heat pump. The method of claim 1,
The second heat pump is composed of a single stage heat pump,
Draws heat from the heat source fluid passed in order to the second evaporator of the first heat pump and the lowest evaporator of the second heat pump,
A steam generating system, characterized in that to generate steam by heating water in the condenser at the top of the first heat pump. 3. The method according to claim 1 or 2,
The first heat pump is composed of a plurality of stage heat pumps, some or all of which are provided with the first evaporator and the second evaporator as evaporators,
Each said 1st evaporator connects adjacent upper and lower heat pumps,
And a heat source fluid passes sequentially through each of the second evaporators from the upper heat pump to the lower heat pump in order. The method of claim 3, wherein
The heat pump of each stage constituting the first heat pump includes the first evaporator and the second evaporator as evaporators. The method according to any one of claims 1 to 4,
Of the heat pumps of the single stage or the multiple stages which comprise the said 1st heat pump, the stage heat pump which has the said 1st evaporator and the said 2nd evaporator has the said 1st evaporator and the said 1st in the refrigerant | coolant flow path from the expansion valve to a compressor. 2, wherein the evaporator is installed in series or in parallel, or the first expansion valve and the first evaporator and the second expansion valve and the second evaporator are installed in parallel in the refrigerant passage from the condenser to the compressor. . 6. The method according to any one of claims 1 to 5,
And the first heat pump and the second heat pump are connected in any one of the following relations (a) to (c).
(a) an indirect heat exchanger which receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump and heat exchanges without mixing both refrigerants; It is a condenser and also a first evaporator of the first heat pump.
(b) an intermediate cooler that receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump and directly contacts both refrigerants for heat exchange. It is a condenser of the pump and a first evaporator of the first heat pump.
(c) receives the refrigerant from the compressor of the second heat pump and the refrigerant from the expansion valve of the first heat pump, and heats the refrigerant by directly contacting both refrigerants, and condenser of both refrigerants and the first heat pump. And an intermediate cooler for exchanging heat without mixing the refrigerant supplied to the expansion valve of the second heat pump without passing through the expansion valve, the intermediate cooler being a condenser of the second heat pump, 1 evaporator. 7. The method according to any one of claims 1 to 6,
When the said 1st heat pump and / or the said 2nd heat pump are multiple stages, the heat pumps of adjacent stages are connected in the relationship in any one of following (a)-(c). .
(a) an indirect heat exchanger which receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and heat exchanges without mixing both refrigerants, the indirect heat exchanger being the condenser of the lower heat pump and the upper heat Evaporator of the pump.
(b) an intermediate cooler which receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and directly contacts and exchanges both refrigerants, the intermediate cooler being a condenser of the lower heat pump; The top heat pump is an evaporator.
(c) receives the refrigerant from the compressor of the lower heat pump and the refrigerant from the expansion valve of the upper heat pump and heats them by directly contacting both refrigerants, and without passing through the expansion valve from the condenser of both refrigerants and the upper heat pump. An intermediate cooler for heat exchange without mixing the refrigerant supplied to the expansion valve of the lower heat pump is provided, and the intermediate cooler is the condenser of the lower heat pump and the evaporator of the upper heat pump. The method according to claim 6,
When the first heat pump and the second heat pump are connected in the relation of (b), the refrigerant from the compressor of the second heat pump is supplied to the intermediate cooler instead of or in addition to the intermediate cooler. A steam generating system, characterized by supplying a refrigerant passage from a cooler to a compressor. The method according to claim 6,
When the first heat pump and the second heat pump are connected in the relation of (c), the refrigerant from the compressor of the second heat pump is instead of or in addition to supplying to the intermediate cooler; 1 A steam generating system characterized by being supplied to a refrigerant passage from an intermediate cooler to a compressor of a heat pump, or to a refrigerant passage from an expansion valve to an intermediate cooler or a compressor. The method according to claim 6,
A separator for gas-liquid separation of the refrigerant from the expansion valve of the first heat pump when the first heat pump and the second heat pump are connected in the relation of (c),
The vapor generation system which supplies the gas phase powder isolate | separated by this separator to the refrigerant flow path from a said 2nd evaporator to a compressor. 11. The method according to any one of claims 1 to 10,
Any one or more of the following (a) to (d) sub-heat exchangers,
When the condenser and the first sub heat exchanger at the uppermost stage of the first heat pump are installed, the first sub heat exchanger is installed when the first sub heat exchanger is installed in order to distribute water or steam to the first sub heat exchanger. Set to be forward,
When the second evaporator of the first heat pump and the fourth sub heat exchanger are installed, the fourth sub heat exchanger, the lowest evaporator of the second heat pump, and the second sub heat exchanger when the second sub heat exchanger is installed. The lowest evaporator of the second heat pump is set to be behind the flow order of the heat source fluid to the sub-heat exchanger,
When the first evaporator of the first heat pump and the third sub heat exchanger are installed, the third sub heat exchanger, the second evaporator of the first heat pump, and the fourth sub heat exchanger are installed when the third sub heat exchanger is installed. And the first evaporator and the second evaporator are set to be ahead of the third sub heat exchanger and the fourth sub heat exchanger with respect to the flow order of the refrigerant to the sub heat exchanger.
(a) A first sub heat exchanger of refrigerant and water from the condenser at the top of the first heat pump to the expansion valve.
(b) a second sub-heat exchanger of refrigerant and heat source fluid from the evaporator at the bottom of the second heat pump to the compressor.
(c) when the first evaporator is an indirect heat exchanger, a third sub of refrigerant from the bottommost expansion valve of the first heat pump to the compressor and refrigerant from the compressor of the second heat pump to the first evaporator heat transmitter.
(d) a fourth sub heat exchanger of refrigerant and heat source fluid from the expansion valve at the lowermost end of the first heat pump to the compressor. 12. The method according to any one of claims 1 to 11,
And the heat source fluid is a drain from a steam use facility.

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