JP2009156563A - Self-balancing condensing and evaporating heat exchanger device, refrigerating cycle incorporating it, and partial recovery device for condensate using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger device capable of generating expansion, evaporation process correlated with condensation and liquefaction of high pressure gas by itself, and capable of maintaining heat balance by a synergistic effect of both generated heat of condensation latent heat and evaporation latent heat during phase change of the high pressure gas. <P>SOLUTION: In the self-balancing condensing and evaporating heat exchanger device, a heat exchange plate is provided in the middle to partition off a primary side and secondary side, both of which are equipped with an inlet and outlet, and it is regarded as a heat exchanger of a composition serially connecting the outlet of the primary side and the inlet of the secondary side by a connection pipe via an expansion valve. High-pressure high-temperature un-condensed gas is introduced into the inlet of the primary side, it is passed through the connection pipe from the primary side, it is decompressed by the expansion valve, the high-pressure high-temperature gas is decompressed and cooled by a throttling expansion effect, it is introduced into the secondary side inlet, a process of cooling the secondary side by the throttling expansion effect to a lower temperature than a condensation temperature of the high-pressure gas is repeated, and an amount of a condensed liquid is increased to maintain the heat balance. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention is a heat exchanger device provided with a heat exchange plate in the middle, and in particular, the heat exchanger device itself can perform gas condensation and evaporation in thermal equilibrium, and attenuates the high pressure of the inflowing gas, When incorporated in a refrigeration cycle, the refrigerator (compressor) can be protected from high pressures to ensure stable operation, and in addition, it is generally possible to easily perform a phase change from gas to liquid. The present invention relates to a self-equilibrating condensation and evaporative heat exchanger device, a refrigeration cycle incorporating the same, and a partial recovery device for condensate (liquefied gas) using the same.

  In general, a heat exchanger apparatus having a heat exchange plate in the middle passes a fluid serving as a heat medium on one side of the intermediate plate, and passes a fluid cooled or heated by the heat medium on the other side. Heat is transferred through the exchange plate and used for use.

  On the other hand, a general refrigeration cycle is a refrigerator (compressor) that discharges high-pressure and high-temperature refrigerant gas, a condenser (condenser) that condenses the refrigerant, and a cooler (evaporator, evaporator) that has an expansion valve on the primary side. ) And sometimes a precooler (intercooler) that precools the refrigerant gas before it flows into the cooler.

  The characteristics required for this refrigerant gas are a low boiling point, that is, a low cooling temperature, a critical temperature of room temperature, that is, condensation at room temperature, a large latent heat of vaporization, that is, per unit weight of the refrigerant. The amount of heat of cooling is large, the vapor density is large, that is, the volume of the apparatus is small, the compression ratio is small, that is, the compression power is small, and finally it is degradable, corrosive, and toxic. It is not.

  Fluorocarbons, propane, and liquefied carbon dioxide are known to meet these conditions, but propane is flammable and liquefied carbon dioxide requires use at high pressure, so it is a special case. In general, chlorofluorocarbons are used except for.

  However, chlorofluorocarbons are restricted from being released into the atmosphere as they lead to the destruction of the global ozone layer. As a result, chlorofluorocarbons cannot be used even in closed environments such as refrigeration equipment due to leakage or disposal. It was.

  Then, the refrigerant mixture which mixes and uses liquefied carbon dioxide gas as an inert material which suppresses the combustibility of propane as an alternative to a Freon system was devised. However, although this mixed refrigerant is indeed effective, there are limits to the cooling and freezing temperatures that can be obtained due to the pressure load regulations in current compression refrigerators, etc. It is impossible.

  In addition, in order to obtain ultra-low temperature using the above-mentioned mixed refrigerant, there is a system in which condensers are used in cascade, and the temperature is lowered stepwise by passing the condenser through the refrigerant forward and backward paths. However, in this case, the apparatus becomes large-scale, and it is quite difficult to actually construct and set.

Furthermore, conventionally, in order to liquefy various gases including air, large-scale and complicated devices and processes are required. For this reason, liquefied gas used in various refrigeration methods is priced. In addition, it has become necessary to accommodate in a cylinder and carry it to the site.
JP 2006-64331 A Japanese Patent Laid-Open No. 2004-361033

  The problem to be solved by the present invention is that in a refrigeration cycle using a conventional compression refrigerator, there is a limit to the low temperature obtained even if a mixed refrigerant is used, and in order to use carbon dioxide as a low boiling point refrigerant This is the point that the pressure load related to the compression refrigerator becomes too large and difficult, and furthermore, conventionally, in order to liquefy the gas, a large-scale and complicated device is required. The self-condensation and liquefaction of the high-pressure gas can be generated, and the expansion and evaporation process can be generated. The heat balance is achieved by the synergistic effect of both the latent heat of condensation during the phase change of the high-pressure gas and the heat generated by both the latent heat of evaporation. There is no heat exchanger device that can maintain the temperature.

  In order to solve the above problems, the self-equilibrium condensing and evaporating heat exchanger apparatus according to the present invention has a heat exchange plate in the middle and is divided into a primary side and a secondary side, and the primary side and the secondary side Each having an inlet and an outlet, and the primary outlet and the secondary inlet are connected in series with a connecting pipe through an expansion valve in the middle of the heat exchanger. The uncondensed gas that has been compressed at the inlet and is at high pressure and high temperature is introduced. At this time, there is no condensed liquid cooled on the primary side, and the pressure is reduced by the expansion valve from the primary side through the connecting pipe. The high-pressure, high-temperature gas is reduced and cooled by the expansion expansion action, introduced into the secondary side inlet, the secondary side is cooled to a temperature lower than the condensation temperature of the high-pressure gas by the expansion expansion action, and the heat exchange The primary side facing through the plate is cooled, and the primary side is not condensed. The pressure gas is condensed and liquefied, and the uncondensed high-pressure gas is cooled to amplify the latent heat of condensation and produce condensed vapor and condensate cooled on the primary side. The generated condensate and condensate are correlated. The condensed vapor and condensate described above contribute to the amplification of the secondary side latent heat of vaporization, the adiabatic expansion is generated by the expansion valve through the connection pipe, the latent heat of vaporization is amplified, and a complete condensate is generated, It is characterized in that the process is repeated and the amount of condensate increases and evaporative cooling capacity is established over time, and the primary side condensation latent heat is supplemented by the secondary side latent heat, and the secondary side latent heat is the primary side condensation latent heat. The acquisition latent heat on the primary side and the secondary side is complemented by the above, and is characterized by the fact that the effect is expanded over time while continuing to achieve thermal equilibrium while exhibiting a synergistic effect.

  In addition, a refrigeration cycle incorporating the above-described heat exchanger device includes at least a refrigerator, a condenser, and a cooler having an expansion valve on the primary side, and in the refrigeration cycle in which the refrigerant is circulated, It has a bypass path with a switching valve on the secondary side, and the above-described self-equilibrium condensation and evaporation heat exchanger device is incorporated in the bypass path, and the above-described refrigeration cycle includes an intercooler, The refrigerant is fed to the primary side of the intercooler and then sent to the cooler, and the refrigerant from the cooler is returned to the refrigerator through the secondary side of the intercooler, and a switching valve is provided on the primary side of the condenser of the refrigeration cycle. The hot gas line can be switched, and the hot gas is sent from the hot gas line to the cooler. A pressure switch is provided on the primary side of the switching valve for the hot gas line described above, and the pressure switch can be used for both pressure attenuation and switching of the switching valve on the secondary side of the condenser. Thus, the refrigerant flow path is switched.

  Furthermore, the apparatus for recovering a part of the condensate using the heat exchanger apparatus described above is characterized in that a condensate recovery container is connected to a part of the connecting pipe.

  The present invention is configured as described above. According to the first and second aspects of the present invention, self-equilibrating, condensing and evaporating the gas, that is, liquefying and further vaporizing can be realized only by a pumping force by the compressor. The principle is that latent heat of condensation and latent heat of vaporization are generated at the time of phase change in which gas is condensed, liquefied, and evaporated and vaporized from the liquid, and at the same time, a correlated pressure change is also generated at the time of gas temperature change. Therefore, this heat exchanger apparatus can be applied and utilized in a wide variety of industrial fields, and the need for conventional complicated and large-scale apparatuses and systems can be eliminated.

  Moreover, according to the invention of Claim 3 thru | or 6 of this application, the heat exchanger apparatus of Claim 1 and Claim 2 is provided in a bypass, Moreover, a hot gas line is provided and each switching valve is provided. The refrigerant flow path can be switched with the refrigeration cycle, which can reduce the pressure load on the compression refrigerator by performing high-pressure attenuation of the refrigerant gas, and can also serve as the defrosting action of the cooler (evaporator) Can be.

  Further, according to the invention described in claim 7 of the present application, using the heat exchanger device according to claim 1 and claim 2, condensation and liquefaction are performed from a connecting pipe that feeds a circulating fluid from the primary side to the secondary side. The collected gas can be recovered. As a result, the liquefied gas can be easily generated and stored, and other applications such as a dehumidifier can be made by removing the drain from the air.

  This was realized by configuring as illustrated in the drawings and described in the examples.

  Next, the mechanism and principle of the self-equilibrium condensation / evaporation heat exchanger apparatus according to the present invention will be described with reference to FIGS. 1 to 3. FIG. 4 shows the refrigeration cycle, and FIG. 5 shows a part of the liquefied gas. The recovery device will be described. FIG. 1A is a diagram showing an initial state of a self-equilibrium condensation and evaporation heat exchanger apparatus according to the present invention, FIG. 1B is a ph diagram of that state, and FIG. FIG. 2 (B) is a ph diagram of the state, FIG. 3 (A) is a diagram showing a complete condensate generation state after change with time, and FIG. 3 (B) is the same. FIG. 4 is a circuit diagram showing a refrigeration cycle incorporating this self-equilibrium condensation and evaporative heat exchanger apparatus.

  First, in FIGS. 1 to 3, EX denotes a self-equilibrium condensation / evaporation heat exchanger apparatus. This heat exchanger apparatus EX includes a heat exchange plate K in the middle, and is divided into a primary side B (cooling condensing part) and a secondary side H (evaporation vaporizing part). First, uncondensed compressed high-pressure gas 1a is introduced from an inlet A on the primary side B through a precooler (condenser) J. There is no cooled condensate C in the initial state (see FIG. 1A). The gas that has passed through the primary side B becomes high-pressure gas 2a that has been cooled and condensed over time, is discharged from the outlet D on the primary side B, passes through the connection pipe E, and is decompressed by the expansion valve F. The high-pressure high-temperature gas is decompressed and cooled by the expansion expansion action by the expansion valve F (see FIG. 1B). In FIG. 1B, p1 indicates the set pressure reduction pressure, and p2 indicates the high pressure at the initial stage of operation of the apparatus.

  The low-pressure gas 3a expanded and evaporated by the expansion valve F is introduced from the inlet G on the secondary side H. The secondary side H is cooled to a temperature lower than the condensing temperature of the gas by the expansion action, and condenses and liquefies the high-pressure gas flowing into the opposing primary side B via the heat exchange plate K (FIG. 2A). reference). At this time, on the primary side B, the uncondensed gas is cooled to increase the latent heat of condensation. Then, on the primary side B, a cooled condensed evaporation condensate C is generated (see FIG. 2B). The cooled condensate C faces through the heat exchange plate K and contributes to the increase of the latent heat of vaporization on the secondary side H that is correlated.

  The cooled condensate C passes through the connecting pipe E, generates adiabatic expansion by the expansion valve F, increases the latent heat of vaporization, and generates a complete condensate (see FIGS. 3A and 3B). This process is repeated while sequentially sending high-pressure gas, and changes over time lead to the increase of the condensate and evaporative cooling capacity.

  In this self-equilibrium condensation and evaporative heat exchanger apparatus EX, the latent heat of condensation on the primary side B is supplemented by the latent heat of evaporation on the secondary side H, and the latent heat of evaporation on the secondary side H is supplemented by the latent heat of condensation on the primary side B. That is, the latent heat acquired by the primary side B and the secondary side H is in thermal equilibrium while exhibiting a synergistic effect, and changes with time and expands continuously.

  That is, FIGS. 1 to 2 are steps for generating the condensate C from a state where there is no condensate C, and FIG. 3 is a step for establishing a state in which both phase changes of condensation and evaporation are sufficiently exhibited and can be continued.

  In each ph diagram, p1 is the decompression pressure set as described above, that is, the correlated evaporation temperature, p2 is the high pressure at the time of expansion of the expansion, that is, the initial operation of the apparatus, and p3 is the throttle pressure. After the condensate liquefaction has increased by expansion and cooling, the high pressure at which the wet evaporation adiabatic expansion has started, p4 indicates the high pressure when the high pressure gas is sufficiently condensed and liquefied and adiabatic expansion and evaporation are continued, and the relationship between the pressures The equation is p2> p3> p4, which is achieved by condensing and decompressing the high-pressure gas on the primary side B. All the high-pressure gas pressures are attenuated to the same pressure p4.

  Next, a refrigeration cycle incorporating the heat exchanger apparatus 11 (EX) described above will be described with reference to FIG. This refrigeration cycle has a compression refrigerator 1, and discharges high-pressure and high-temperature refrigerant gas from the compression refrigerator 1. During the normal cooling operation, the refrigerant gas discharged from the compression refrigerator 1 is guided to the normal flow path (A1) through a switching valve 2 for defrosting described later, and is condensed by the condenser 3. (Flow path A2), enters the expansion valve 5 through the primary side of the intercooler (precooler) 4 (flow path A3), where it is depressurized and cooled, and flows into the cooler (evaporator) 6. The cooler 6 performs the cooling action.

  The refrigerant that has passed through the cooler 6 flows into the secondary side of the intercooler 4 through the switching valve 7 during defrosting described later (flow path A4), and after passing through the intercooler 4, returns to the compression refrigerator 1 ( The flow path A5) is circulated.

  In addition, the switching valves 2, 7, and 10 are assumed to be solenoid valves, with 2 having 3 ports on the discharge side and 7 having 3 ports on the suction side. When the pressure switch 9 provided on the primary side of the switching valve 2 detects a high pressure for non-condensation of the discharge gas from the compression refrigerator 1, the switching valve 10 is opened and the refrigerant flow path is added to the normal A2 A part of the refrigerant is also branched and guided to the bypass C1. When the heat exchanger device 11 (EX) is incorporated by the switching valve 10 and the bypass passage C1, a low-boiling point refrigerant (carbon dioxide gas or non-azeotropic refrigerant mixture) that is at room temperature and cannot be condensed below a safe pressure is used. Thus, it is suitable for the purpose of obtaining an ultra-low temperature. The refrigerant gas branched to the heat exchanger apparatus 11 (EX) passes through the flow paths A1 to C1 to perform the above-described action, and from the secondary side outlet of the heat exchanger apparatus 11 (EX) to the normal flow path A5. And is sucked into the compression refrigerator 1.

  This refrigerant flow is condensed by the high-pressure side gas by the heat exchanger device 11 (EX) and attenuated to a low pressure as a whole of the high-pressure circuit. When the switching valve 10 is opened and the high pressure side becomes low pressure by the action of the heat exchanger device 11 (EX), the switching valve 10 is closed by the detection of the pressure switch 9 and is restored to the normal refrigeration cycle, and the cooling action is made safe pressure Continue on. The refrigerant that passes through the heat exchanger apparatus 11 (EX) and is sucked into the compression refrigerator 1 is a gas that has completed the refrigeration cycle that has been condensed and evaporated from the high-pressure and high-temperature gas to become a low-pressure and low-temperature gas. There is no obstacle to the refrigerator 1.

  Further, this refrigeration cycle can defrost the cooler 6 by opening the switching valve 2. When performing the defrosting operation, when the switching valve 2 is opened, the hot gas discharged from the compression refrigerator 1 passes through the hot gas line 8 and directly flows into the cooler 6 as it is. Heat and defrost (flow path B1). The gas that has finished the defrosting action is guided to the flow path B2 by the switching valve 7 and sent to the primary side of the heat exchanger apparatus 11 (EX) (flow path B3). Then, the gas that has passed through the heat exchanger device 11 (EX) enters the flow path 5 through the flow path B4 that is the same as the flow path C2, and is sucked into the compression refrigerator 1.

  This defrosting method saves energy by using the compression work heat of the compression refrigerator 1 and the compressed high-temperature gas and condensation latent heat of the refrigerant, and does not require any additional heating device such as an electric heater. It becomes a device, and the refrigerant refrigeration cycle can be performed safely and continuously.

  Furthermore, with reference to FIG. 5, the apparatus which collect | recovers a part of condensate using the self-equilibrium condensation and evaporative heat exchanger apparatus which concerns on this invention is demonstrated. FIG. 5 is a view showing the above-described apparatus, and corresponds to FIG. 3A. In FIG. 5, a compressor K1 and a gas inlet L are added. The gas sucked and discharged from the gas inlet L by the compressor K1 is precooled by a precooler (condenser) J. The precooling temperature at this time can be determined according to the physical properties of the gas to be liquefied by adding another cooling device, passed through the self-equilibrium condensation and evaporative heat exchanger device EX, and on the primary side B A condensate recovery container (cylinder) is connected to a part of the connection pipe E before vaporizing the condensed liquid C by the expansion valve F, that is, a part of the condensate is recovered. The unrecovered condensate becomes evaporating gas on the secondary side H of the heat exchanger apparatus EX and is discharged from the secondary side outlet I.

  By using a device that recovers a part of this condensate, liquefaction of gas, including air, can be realized easily and inexpensively. When applied to air conditioning equipment, it can function as a dehumidifier that removes drainage. It will be possible.

  The self-equilibrium condensing and evaporating heat exchanger apparatus according to the present invention is configured as described above. As an example, a refrigeration cycle incorporating this and an apparatus for recovering a part of the condensate have been shown, but in addition to this, a gas-liquid phase change is forcibly realized and the latent heat generated during the phase change is used. It can be applied to a wide range of devices and systems, and can be implemented in a wide variety of industrial fields.

It is a figure which shows the initial state of the self-equilibrium condensation and evaporation heat exchanger apparatus which concerns on this invention. It is a ph diagram in this state. It is a figure which shows a condensation evaporation production | generation start state. It is a ph diagram in this state. It is a figure which shows the complete condensate production | generation state after a time-dependent change. It is a ph diagram in this state. It is a circuit diagram which shows the refrigerating cycle incorporating this self-equilibrium condensation and evaporative heat exchanger apparatus. It is a figure which shows the apparatus which collect | recovers some condensates using a self-equilibrium condensation and evaporative heat exchanger apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compression refrigerator 2 Switching valve 3 Condenser 4 Intercooler 5 Expansion valve 6 Cooler 7 Switching valve 8 Hot gas line 9 Pressure switch 10 Switching valve 11 Self-equilibrium condensation, evaporative heat exchanger apparatus 12 Expansion valve 1a Compression, high pressure gas 2a Cooled and condensed high pressure gas 3a Expanded and evaporated low pressure gas 4a Cooling process finished low pressure gas EX Self-equilibrium condensation and evaporative heat exchanger device A Heat exchanger primary side inlet B Primary side C Cooled condensate D Heat exchanger primary outlet E Connection pipe F Expansion valve G Heat exchanger secondary inlet H Secondary side I Heat exchanger secondary outlet K Heat exchange intermediate plate K1 Compressor L Gas inlet M Condensate Collection container

Claims (7)

  It has a heat exchange plate in the middle and is divided into a primary side and a secondary side, and has an inlet and an outlet on the primary side and the secondary side, respectively, and the primary side outlet and the secondary side inlet are on the way The heat exchanger is configured to be connected in series with a connecting pipe via an expansion valve, and the uncondensed gas that is compressed and compressed into the primary inlet is introduced into the primary side at this point. There is no cooled condensate, and the pressure is reduced by the expansion valve from the primary side through the connecting pipe described above, the high pressure and high temperature gas is reduced and cooled by the expansion expansion action, and this is introduced into the secondary side inlet. The secondary side is cooled to a temperature lower than the condensing temperature of the high-pressure gas by a constriction expansion action, the primary side opposed through the heat exchange plate is cooled, and the uncondensed high-pressure gas on the primary side is condensed and liquefied. As the uncondensed high-pressure gas is cooled, the latent heat of condensation is amplified and the primary Condensed vapor and condensate cooled in this way are generated, and the generated condensate vapor and condensate contribute to the amplification of the correlated latent heat of vaporization, and the condensed vapor and condensate expand through the connecting pipe. Self-equilibrium characterized by generating adiabatic expansion with a valve, amplifying latent heat of vaporization and generating complete condensate, repeating the above process, and increasing the amount of condensate over time and establishing evaporative cooling capacity Condensing, evaporating heat exchanger device.   The primary side condensation latent heat is supplemented by the secondary side latent heat, the secondary side latent heat is complemented by the primary side condensation latent heat, and the acquired latent heats of the primary side and the secondary side are in thermal equilibrium while exhibiting a synergistic effect. 2. The self-equilibrium condensing and evaporating heat exchanger device according to claim 1, wherein the effect is expanded with the lapse of time while continuing.   In a refrigeration cycle that includes at least a refrigerator, a condenser, and a cooler having an expansion valve on the primary side, and circulates the refrigerant, a switching valve is provided on the secondary side of the condenser, and a bypass path is provided. A refrigerating cycle comprising the self-equilibrium condensing and evaporating heat exchanger device incorporated in the bypass path.   The refrigeration cycle is provided with an intercooler, and the refrigerant is passed through the primary side of the intercooler and then sent to the cooler, and the refrigerant from the cooler is returned to the refrigerator through the secondary side of the intercooler. The refrigeration cycle described.   A switching valve is provided on the primary side of the condenser of the refrigeration cycle described above so that it can be switched to a hot gas line. By sending hot gas from the hot gas line to the cooler, the defrosting action and the high-pressure attenuation of the refrigerant can be achieved. 5. The refrigerant cycle according to claim 3, wherein the refrigerant cycle can be shared by switching of the secondary side switching valve.   6. A pressure switch is provided on the primary side of the switching valve for the hot gas line, and the refrigerant flow path is switched by detecting a high pressure with the pressure switch. The refrigeration cycle described in 1.   An apparatus for recovering a part of a gas condensate using a self-equilibrium condensing and evaporating heat exchanger device, wherein a condensate recovery container is connected to a part of the connecting pipe.

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