JP6398621B2 - refrigerator - Google Patents

Description

  The present invention relates to a refrigerator having an evaporator for boiling and evaporating a refrigerant.

  In an adsorption refrigerator or an absorption refrigerator, water is generally used as a refrigerant. In the case of boiling evaporation at atmospheric pressure and 100 ° C., even if a 10 cm head of water is loaded on the boiling evaporation section, the degree of superheat required for the load is very small, but reduced pressure (negative pressure) ) In the case of lower and lower temperatures, a very high degree of superheat is required.

  For example, in the case of an evaporation temperature of 10 ° C., when a head of 10 cm is loaded, a superheat degree close to 10 ° C. is required for boiling evaporation. For this reason, in order to improve the heat exchange efficiency in an evaporator used under reduced pressure and at a low temperature, it is required to wet the heat exchange part as thinly as possible so as not to apply an excessive water head.

  Here, as a refrigerator corresponding to this problem, there is one described in Patent Document 1, for example. The refrigerator described in Patent Document 1 uses a refrigerant dripping pump to feed water to a refrigerant dripping device, and dripping the refrigerant into the heat exchanging part of the evaporator so that the heat exchanging part is always thinly wetted. I have to.

  Patent Document 1 discloses a refrigerator in which glass beads are immersed in a liquid refrigerant in order to generate fine boiling droplets, or a refrigerator in which a fin plate subjected to hydrophilic treatment is joined to a pipe (heat transfer tube). It is disclosed.

JP 2000-227288 A

  However, in a refrigerator using a refrigerant dropping pump, a special pump that can be used under reduced pressure and a refrigerant dropping device are required, which increases costs and in particular tends to cause vacuum leakage from the pump. There is. Moreover, since the dropped water refrigerant flows down without staying on the surface of the heat exchange part, there is also a problem that the heat exchange part is not used effectively.

  On the other hand, in refrigerators that use glass beads, glass beads are not a heat-conducting substance, so they do not work effectively for boiling nucleation. There is a problem that the generation of vacuum causes a decrease in vacuum.

  Furthermore, in a refrigerator using a fin plate that has been subjected to a hydrophilic treatment, depending on the hydrophilic treatment material, there is a problem that the outgassing causes a decrease in the degree of vacuum and an increase in cost.

  In view of the above points, an object of the present invention is to suppress leakage and outgas generation that deteriorate the degree of vacuum and improve heat exchange efficiency in a refrigerator including an evaporator for boiling and evaporating a refrigerant.

In order to achieve the above object, according to the first aspect of the present invention, a part of the heat transfer tube (41) for circulating the heat medium is disposed inside, and the liquid phase refrigerant stored in the lower part and the heat medium An evaporator (40) for boiling and evaporating the refrigerant by heat exchange, a condenser (30) for condensing the gas-phase refrigerant, and a refrigerant return pipe for guiding the gas-phase refrigerant in the condenser into the liquid-phase refrigerant in the evaporator ( 52) and equipped with a,
The refrigerant return pipe is connected to the condenser at a position where only the gas-phase refrigerant in the condenser can be taken out,
A throttle mechanism (53) for adjusting the amount of the gas-phase refrigerant flowing through the refrigerant return pipe is provided in the middle of the refrigerant return pipe .

  According to this, since bubbles are blown out into the liquid phase refrigerant in the evaporator, the liquid phase refrigerant in the evaporator is disturbed to promote boiling nucleation. Therefore, since the conventional refrigerant dripping pump, glass beads, hydrophilic fin plate, etc. are not used, it is possible to improve heat exchange efficiency while suppressing leakage and outgas generation that worsen the degree of vacuum. .

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a whole lineblock diagram showing the refrigerator concerning a 1st embodiment of the present invention. It is a figure which shows the principal part structure of the steam supply piping of FIG. It is a whole block diagram of the refrigerator which shows the modification of 1st Embodiment. It is a time chart with which it uses for operation | movement description of the refrigerator which concerns on 2nd Embodiment of this invention. It is a whole block diagram which shows the refrigerator based on 3rd Embodiment of this invention. It is AA sectional drawing of FIG. It is a time chart with which it uses for operation | movement description of the refrigerator which concerns on 4th Embodiment of this invention. It is a whole block diagram which shows the refrigerator based on 5th Embodiment of this invention. It is an expanded sectional view of the evaporator of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
A first embodiment of the present invention will be described.

  As shown in FIG. 1, this adsorption refrigerator is configured by arranging a first adsorber 10, a second adsorber 20, a condenser 30 and an evaporator 40 in one vacuum vessel. The vacuum vessel is configured to have a portion for transferring heat to the outside. Note that the inside of the vacuum vessel has a predetermined degree of vacuum below atmospheric pressure, and the vacuum vessel contains a required amount of water as a refrigerant.

  The vacuum vessel is formed in a substantially square shape, and its interior is partitioned into four spaces. Of the two spaces extending in the vertical direction in FIG. 1 in the vacuum vessel, the first adsorber 10 is disposed in the left space, and the second adsorber 20 is disposed in the right space.

  The first and second adsorbers 10 and 20 are configured by holding a large number of granular adsorbents (for example, silica gel, zeolite, etc.) in a case in which air permeability is ensured.

  The first and second adsorbers 10 and 20 use shell-and-tube type heat exchangers, and a part of the heat transfer tubes 11 and 21 through which a fluid for cooling and heating the adsorbent inside is circulated. Is placed inside. The adsorbent has the property of adsorbing gas-phase refrigerant (water vapor in this embodiment) with high capacity in the cooled state and desorbing the adsorbed refrigerant to regenerate the adsorption capacity in the heated state. .

  The condenser 30 is disposed in the upper space of the two spaces extending in the left-right direction in FIG. The condenser 30 uses a shell and tube type heat exchanger, and a part of the condenser heat transfer tube 31 through which cooling water (water or LLC) is circulated is disposed inside. The condenser heat transfer tube 31 penetrates the outer wall of the vacuum vessel in an airtight manner and is led out to the outside. Moreover, the cooling water which distribute | circulates the inside of the heat exchanger tube 31 for condensers is cooled by the cooling means which is not shown in figure. And the condenser 30 performs heat exchange between the cooling water which distribute | circulates the inside of the heat exchanger tube 31 for condensers, and a gaseous-phase refrigerant | coolant, and condenses a gaseous-phase refrigerant | coolant.

  An evaporator 40 is disposed in the lower space of the two spaces extending in the left-right direction in FIG. The evaporator 40 uses a shell-and-tube type heat exchanger, and a part of an evaporator heat transfer tube 41 through which a heat medium (for example, water or LLC) flows is disposed inside. A liquid phase refrigerant is stored in the lower part of the evaporator 40. Furthermore, a part of the lower side of the evaporator heat transfer tube 41 located in the evaporator 40 is immersed in the liquid phase refrigerant in the evaporator 40.

  The evaporator 40 exchanges heat between the heat medium and the liquid phase refrigerant to boil and evaporate the liquid phase refrigerant, and to cool the heat medium by the latent heat of evaporation when the refrigerant evaporates. Yes. The evaporator heat transfer tube 41 is led out through the outer wall of the vacuum vessel in an airtight manner. For example, heat is exchanged between room air and a heat medium to perform cooling.

  The condenser 30 and the evaporator 40 are connected by a liquid phase refrigerant return pipe 50 that returns condensed water (liquid phase refrigerant) condensed by the condenser 30 to the evaporator 40. One end of the liquid phase refrigerant return pipe 50 is connected to the condenser 30 at a position where only the liquid phase refrigerant in the condenser 30 can be taken out. In other words, one end of the liquid-phase refrigerant return pipe 50 is connected to the bottom of the condenser 30.

  In the middle of the liquid-phase refrigerant return pipe 50, a throttle mechanism 51 that adjusts the amount of the liquid-phase refrigerant flowing through the liquid-phase refrigerant return pipe 50 is disposed. In the present embodiment, a capillary tube is used as the throttle mechanism 51.

  The condenser 30 and the evaporator 40 are connected by a refrigerant return pipe 52 that guides the gas-phase refrigerant in the condenser 30 into the liquid-phase refrigerant in the evaporator 40. One end of the refrigerant return pipe 52 is connected to the condenser 30 at a position where only the gas-phase refrigerant in the condenser 30 can be taken out. In other words, one end of the refrigerant return pipe 52 is connected to the upper part of the condenser 30.

  The other end side of the refrigerant return pipe 52 is immersed in the liquid-phase refrigerant in the evaporator 40 and is disposed below the evaporator heat transfer pipe 41. Further, as shown in FIG. 2, a plurality of vapor blowout holes 521 are formed along the longitudinal direction of the refrigerant return pipe 52 at a portion of the refrigerant return pipe 52 that is immersed in the liquid phase refrigerant in the evaporator 40. ing.

  In the middle of the refrigerant return pipe 52, a throttle mechanism 53 that adjusts the amount of the gas-phase refrigerant flowing through the refrigerant return pipe 52 is disposed. In the present embodiment, a capillary tube is used as the throttle mechanism 53.

  Next, a heating and cooling system for supplying a cooling fluid or a heating fluid to the heat transfer tubes 11 and 21 of the adsorbers 10 and 20 will be described. The heat transfer tubes 11 and 21 are led out through the outer wall of the vacuum vessel in an airtight manner.

  The heating and cooling system includes a heating device 61 that heats water, a cooling device 62 that cools water, and two four-way valves 63 and 64.

  For example, a water-cooled internal combustion engine can be used as the heating device 61, and engine cooling water (hot water) is used as a heating fluid. The heating device 61 may be an internal combustion engine such as a gas turbine, a combustor, a fuel cell, or a means using natural energy such as solar heat.

  On the other hand, as the cooling device 62, a cooling tower or an air-cooled heat exchanger such as a fin and tube can be used, and water cooled by the cooling tower or the air-cooled heat exchanger is used as a cooling fluid.

  One end side of the heat transfer tube 11 of the first adsorber 10 is connected to the first outlet port 63 b of the first four-way valve 63, and the other end side of the heat transfer tube 11 is the second inlet port 64 c of the second four-way valve 64. It is connected to the. On the other hand, one end side of the heat transfer tube 21 of the second adsorber 20 is connected to the second outlet port 63 d of the first four-way valve 63, and the other end side of the heat transfer tube 21 is the first inlet of the second four-way valve 64. It is connected to port 64a.

  The outlet side of the heating device 61 is connected to the first inlet port 63 a of the first four-way valve 63, and the inlet side of the heating device 61 is connected to the second outlet port 64 d of the second four-way valve 64. The outlet side of the cooling device 62 is connected to the second inlet port 63 c of the first four-way valve 63, and the inlet side of the cooling device 62 is connected to the first outlet port 64 b of the second four-way valve 64.

  In FIG. 1, a four-way valve at the time of supplying a heating fluid to the heat transfer tube 11 of the first adsorber 10 (desorption process) and supplying a cooling fluid to the heat transfer tube 21 of the second adsorber 20 (adsorption process). The connection state of each port in 63 and 64 is indicated by a solid line. Here, in the first four-way valve 63, the first inlet port 63a and the first outlet port 63b are connected, and the second inlet port 63c and the second outlet port 63d are connected. In the second four-way valve 64, the first inlet port 64a and the first outlet port 64b are connected, and the second inlet port 64c and the second outlet port 64d are connected.

  Since the heating and cooling system is configured as described above, a high-temperature heating fluid from the heating device 61 is supplied to the heat transfer tube 11 of the first adsorber 10, and after heat exchange with the adsorbent inside, It returns to the heating device 61 again. On the other hand, the low-temperature cooling fluid from the cooling device 62 is supplied to the heat transfer tube 21 of the second adsorber 20, and after returning to the cooling device 62 after exchanging heat with the adsorbent inside.

  In addition, although detailed description is abbreviate | omitted, when performing an adsorption | suction process with the 1st adsorption device 10 contrary to the above, and performing a desorption process with the 2nd adsorption device 20, it is 1st, 2nd four directions The valves 63 and 64 are switched to a state indicated by a broken line in FIG. As a result, the cooling fluid is supplied to the heat transfer tube 11 of the first adsorber 10, and the heating fluid is supplied to the heat transfer tube 21 of the second adsorber 20.

  In the vacuum vessel, a first water vapor valve 71 that controls the communication state between the space in the first adsorber 10 and the space in the condenser 30 is provided. When the pressure in the condenser 30 is lower than the pressure in the first adsorber 10, the first water vapor valve 71 is opened due to the pressure difference.

  In addition, a second water vapor valve 72 for controlling the communication state between the space in the second adsorber 20 and the space in the condenser 30 is provided in the vacuum vessel. Similarly to the first water vapor valve 71, the second water vapor valve 72 is also opened by the pressure difference when the pressure in the condenser 30 is lower than the pressure in the second adsorber 20. .

  Further, a third water vapor valve 73 for controlling the communication state between the space in the first adsorber 10 and the space in the evaporator 40 is provided in the vacuum container. When the pressure in the evaporator 40 is higher than the pressure in the first adsorber 10, the third water vapor valve 73 is opened due to the pressure difference.

  Further, a fourth water vapor valve 74 for controlling the communication state between the space in the second adsorber 20 and the space in the evaporator 40 is provided in the vacuum vessel. Similarly to the third water vapor valve 73, the fourth water vapor valve 74 is also opened by the pressure difference when the pressure in the evaporator 40 is higher than the pressure in the second adsorber 20. .

  Next, the operation will be described. First, the operation when the first adsorber 10 is in the desorption process and the adsorber 20 is in the adsorption process will be described.

  In this case, the connection state of each port in the four-way valves 63 and 64 is shown by a solid line. Therefore, the heating fluid heated by the heating device 61 is supplied to the heat transfer tube 11 of the first adsorber 10 by a pump (not shown), while the cooling fluid cooled by the cooling device 62 is supplied to another pump (not shown). To the heat transfer tube 21 of the second adsorber 20.

  As a result, the adsorbent in the first adsorber 10 is heated, the moisture adsorbed by the adsorbent in the first adsorber 10 is desorbed, and the pressure in the first adsorber 10 increases. When the pressure in the first adsorber 10 is increased, the first water vapor valve 71 is opened, the gas-phase refrigerant in the first adsorber 10 flows into the condenser 30, and the gas-phase refrigerant is used for the condenser. Heat exchange with cold water flowing through the heat transfer tube 31 condenses. At this time, since the pressure in the first adsorber 10 is higher than the pressure in the evaporator 40, the third water vapor valve 73 is closed.

  On the other hand, since the adsorbent in the second adsorber 20 is cooled, the pressure in the second adsorber 20 is lowered, so the fourth water vapor valve 74 is opened, and the gas-phase refrigerant in the evaporator 40 is second. The gas-phase refrigerant flows into the adsorber 20 and is adsorbed by the adsorbent in the second adsorber 20. Further, since the liquid-phase refrigerant in the evaporator 40 evaporates, the heat medium flowing in the evaporator heat transfer tube 41 is cooled by the latent heat of evaporation. At this time, since the pressure of the second adsorber 20 is lower than the pressure of the condenser 30, the second water vapor valve 72 is closed.

  As described above, after the moisture of the adsorbent in the first adsorber 10 is sufficiently desorbed and the adsorbent in the second adsorber 20 sufficiently adsorbs the moisture, each port in the four-way valves 63 and 64 is The connection state is switched as shown by a dotted line in FIG. Thereby, the 1st adsorption machine 10 serves as an adsorption process, and the 2nd adsorption machine 20 serves as a desorption process. At this time, the second steam valve 72 and the third steam valve 73 are opened, and the first steam valve 71 and the fourth steam valve 74 are closed.

  In this way, by alternately switching the adsorption process and the desorption process of the first adsorber 10 and the second adsorber 20, a cold water output can be continuously obtained from the evaporator heat transfer tube 41.

  During the above operation, the refrigerant condensed in the condenser 30 is returned to the evaporator 40 through the liquid-phase refrigerant return pipe 50. Here, since the pressure of the condenser 30 is higher than that of the evaporator 40, the liquid phase refrigerant in the condenser 30 surely flows to the evaporator 40, but if the liquid phase refrigerant in the condenser 30 disappears, the condenser 30 condenses. Since the gas-phase refrigerant in the vessel 30 flows to the evaporator 40 and causes a system loss, the throttle mechanism 51 is adjusted so that the amount of liquid-phase refrigerant returned to the evaporator 40 is appropriate.

  Further, during the above operation, the gas-phase refrigerant in the condenser 30 is guided into the liquid-phase refrigerant in the evaporator 40 by the refrigerant return pipe 52, and the gas-phase refrigerant bubbles are introduced into the evaporator 40 from the vapor outlet hole 521. It is blown out into the liquid phase refrigerant. As a result, the liquid-phase refrigerant in the evaporator 40 can be disturbed and the formation of boiling nuclei can be promoted, so that high boiling evaporation performance can be obtained under reduced pressure and low temperature. Here, if the gas-phase refrigerant is returned excessively, a system loss occurs, and therefore, the throttle mechanism 53 is adjusted so that an appropriate supply amount is obtained.

  As described above, according to the present embodiment, bubbles are blown out into the liquid phase refrigerant in the evaporator 40, so that the liquid phase refrigerant in the evaporator 40 is disturbed to promote boiling nucleation. Can do. Therefore, since the conventional refrigerant dripping pump, glass beads, hydrophilic fin plate, etc. are not used, it is possible to improve heat exchange efficiency while suppressing leakage and outgas generation that worsen the degree of vacuum. .

  Further, since the amount of the liquid-phase refrigerant returned to the evaporator 40 is appropriately adjusted by the throttle mechanism 51, the liquid-phase refrigerant in the condenser 30 disappears, and the gas-phase refrigerant in the condenser 30 is transferred to the evaporator 40. It can be prevented from flowing and system loss can be suppressed.

  In addition, since the amount of the gas-phase refrigerant returned to the evaporator 40 is appropriately adjusted by the throttle mechanism 53, system loss due to excessive return of the gas-phase refrigerant can be suppressed.

  In the above embodiment, the liquid phase refrigerant return pipe 50 and the refrigerant return pipe 52 are used, but the liquid phase refrigerant return pipe 50 may be eliminated. In this case, as in the modification shown in FIG. 3, one end of the refrigerant return pipe 52 is connected to the condenser 30 at a position where both the gas-phase refrigerant and the liquid-phase refrigerant in the condenser 30 can be taken out. By adjusting so that a small amount of the gas-phase refrigerant is mixed, the bubbles of the gas-phase refrigerant can be blown out from the vapor blowing holes 521 to promote the formation of boiling nuclei.

  Moreover, in the said embodiment, although the shell and tube type heat exchanger was used as the condenser 30, the condenser 30 may be a fin and tube air-cooled heat exchanger.

  In the above-described embodiment, a capillary tube is used as the throttle mechanism 51 that adjusts the amount of the liquid-phase refrigerant flowing through the liquid-phase refrigerant return pipe 50. However, the throttle mechanism 51 includes a needle valve, an electromagnetic valve, and an electric valve. Etc. may be used.

  In the above embodiment, a capillary tube is used as the throttle mechanism 53 for adjusting the amount of the gas-phase refrigerant flowing in the refrigerant return pipe 52. However, the throttle mechanism 53 includes a needle valve, an electromagnetic valve, an electric valve, and the like. It may be used.

(Second Embodiment)
A second embodiment of the present invention will be described. Only the parts different from the first embodiment will be described below.

  In the present embodiment, as the throttle mechanisms 51 and 53 (see FIG. 1), electromagnetic valves or electric valves that open and close the passages in the liquid-phase refrigerant return pipe 50 or the refrigerant return pipe 52 are used.

  As shown in FIG. 4, immediately after the adsorption process and the desorption process of the first adsorber 10 and the second adsorber 20 are switched, the capabilities of the evaporator 40 and the condenser 30 become high (that is, the evaporator 40). The amount of evaporation in the condenser 30 increases and the amount of condensation in the condenser 30 increases.) Thereafter, the capacities of the evaporator 40 and the condenser 30 gradually decrease.

  Therefore, after the adsorption process and desorption process of the first adsorber 10 and the second adsorber 20 are switched, the throttle mechanisms 51 and 53 are opened during the region where the capability of the evaporator 40 and the condenser 30 is high. By returning a large amount of the liquid-phase refrigerant and the gas-phase refrigerant to the valve state, the evaporator 40 and the condenser 30 are made to exhibit high performance.

  On the other hand, when the capacities of the evaporator 40 and the condenser 30 decrease, the throttle mechanisms 51 and 53 are closed to stop the return of the liquid-phase refrigerant and the gas-phase refrigerant. Eliminate system loss due to return.

  According to the present embodiment, as in the first embodiment, since a conventional refrigerant dripping pump, glass beads, a hydrophilic fin plate, etc. are not used, leakage and outgas generation that worsen the degree of vacuum are suppressed. However, the heat exchange efficiency can be improved.

  Moreover, since the refrigerant | coolant flow returned to the evaporator 40 is intermittent according to the capability at that time of the evaporator 40 and the condenser 30, while being able to demonstrate the high capability to the evaporator 40 and the condenser 30, excess System loss due to the return of a simple gas-phase refrigerant can be eliminated.

(Third embodiment)
A third embodiment of the present invention will be described. Only the parts different from the first embodiment will be described below.

  As shown in FIGS. 5 and 6, in the present embodiment, the refrigerant return pipe 52 and the throttle mechanism 53 are eliminated.

  One end of the liquid-phase refrigerant return pipe 50 is connected to the condenser 30 at a position where only the liquid-phase refrigerant in the condenser 30 can be taken out. The other end side of the liquid-phase refrigerant return pipe 50 is arranged above the evaporator heat transfer pipe 41 located in the evaporator 40, and a plurality of liquid-phase refrigerants are dropped on the upper part of the refrigerant suction member described later. A hole (not shown) is formed.

  A refrigerant suction member 42 that guides the liquid phase refrigerant in the evaporator 40 to the surface of the evaporator heat transfer tube 41 by a capillary phenomenon is joined to the surface of the evaporator heat transfer tube 41 located in the evaporator 40. Liquid phase refrigerant is stored in the lower part of the evaporator 40, and a part of the refrigerant suction member 42 on the lower side is immersed in the liquid phase refrigerant in the evaporator 40.

  The refrigerant suction member 42 can be formed of sintered metal, foam metal, mesh, or the like. Then, the refrigerant suction member 42 is designed so that a predetermined capillary force is obtained, in other words, the liquid phase refrigerant at the lower part of the evaporator 40 is sucked up to the upper part of the refrigerant suction member 42 so that the pore diameter and the pores are increased. The rate has been adjusted.

  In the above configuration, the liquid-phase refrigerant in the lower part of the evaporator 40 is sucked up by the capillary force of the refrigerant sucking member 42, and the evaporator heat transfer tube located in the upper part as well as the surface of the evaporator heat transfer pipe 41 located in the lower part. 41 is wetted. Further, the liquid phase refrigerant is dropped from the liquid phase refrigerant return pipe 50 to the upper portion of the refrigerant suction member 42, and the surface of the evaporator heat transfer tube 41 located at the upper portion is more reliably wetted.

  Then, heat exchange is performed between the heat medium flowing in the evaporator heat transfer tube 41 and the liquid phase refrigerant on the surface of the evaporator heat transfer tube 41, and the liquid phase refrigerant evaporates and evaporates when the refrigerant evaporates. The heat medium is cooled by the thermal latent.

  According to the present embodiment, the heat transfer area of the evaporator heat transfer tube 41 can be used effectively, and the refrigerant suction member 42 acts as a heat transfer fin, so that the substantial heat transfer area is increased and boiling nuclei are easily generated. The state can be easily maintained, and further, the effect of reducing the influence of the water head load by thinly wetting the entire surface of the evaporator heat transfer tube 41 can be obtained, and a high boiling evaporation performance under reduced pressure and low temperature can be obtained. Therefore, since the conventional refrigerant dripping pump, glass beads, hydrophilic fin plate, etc. are not used, it is possible to improve heat exchange efficiency while suppressing leakage and outgas generation that worsen the degree of vacuum. .

  Moreover, since the amount of the liquid phase refrigerant stored in the lower part of the evaporator 40 can be reduced and the heat capacity corresponding to the decrease in the liquid phase refrigerant can be reduced, the effect of improving the responsiveness of the cold water output can also be obtained.

  Further, since the amount of the liquid-phase refrigerant returned to the evaporator 40 is appropriately adjusted by the throttle mechanism 51, the liquid-phase refrigerant in the condenser 30 disappears, and the gas-phase refrigerant in the condenser 30 is transferred to the evaporator 40. It can be prevented from flowing and system loss can be suppressed.

  As the throttle mechanism 51, a capillary tube, a needle valve, a solenoid valve, an electric valve, or the like can be used.

(Fourth embodiment)
A fourth embodiment of the present invention will be described. Only the parts different from the third embodiment will be described below.

  In the present embodiment, as the throttle mechanism 51 (see FIG. 5), an electromagnetic valve or an electric valve that opens and closes the passage in the liquid-phase refrigerant return pipe 50 is used.

  As shown in FIG. 7, immediately after the adsorption process and the desorption process of the first adsorber 10 and the second adsorber 20 are switched, the capability of the evaporator 40 becomes high (that is, the evaporation amount of the evaporator 40 is increased). After that, the capacity of the evaporator 40 gradually decreases.

  Then, during the region where the capacity of the evaporator 40 is high, the amount of evaporation is larger than the amount of refrigerant sucked by the refrigerant sucking member 42, and as shown by the broken line in FIG. The height tends to be low, and the surface of the evaporator heat transfer tube 41 located at the top cannot be wetted.

  Therefore, during the region where the capability of the evaporator 40 is high after the adsorption process and the desorption process of the first adsorber 10 and the second adsorber 20 are switched, the throttle mechanism 51 is opened so that the liquid A liquid phase refrigerant is dropped from the phase refrigerant return pipe 50 onto the refrigerant suction member 42. Thereby, as shown by the solid line in FIG. 7, the refrigerant suction height by the refrigerant suction member 42 is increased, and the surface of the evaporator heat transfer tube 41 located at the upper part can also be reliably wetted.

  On the other hand, when the capacity of the evaporator 40 is reduced, the amount of evaporation is smaller than the amount of refrigerant sucked by the refrigerant sucking member 42 and the refrigerant sucking height by the refrigerant sucking member 42 is increased. The mechanism 51 is closed and the dropping of the liquid phase refrigerant from the liquid phase refrigerant return pipe 50 is stopped. Thereby, the increase of the water head load by wetting the surface of the heat exchanger tube 41 for evaporators excessively is suppressed.

  According to the present embodiment, as in the third embodiment, since a conventional refrigerant dripping pump, glass beads, a hydrophilic fin plate, etc. are not used, leakage and outgas generation that worsen the degree of vacuum are suppressed. However, the heat exchange efficiency can be improved.

  In addition, since the flow of the refrigerant to be dropped on the upper part of the refrigerant suction member 42 is interrupted according to the current capacity of the evaporator 40, the evaporator 40 can exhibit high performance and the evaporator heat transfer tube. It is possible to suppress an increase in water load due to excessive wetting of the surface of 41.

  Moreover, since the amount of the liquid phase refrigerant stored in the lower part of the evaporator 40 can be reduced and the heat capacity corresponding to the decrease in the liquid phase refrigerant can be reduced, the effect of improving the responsiveness of the cold water output can also be obtained.

(Fifth embodiment)
A fifth embodiment of the present invention will be described. Only the parts different from the first embodiment will be described below.

  By the way, when the liquid refrigerant is boiled and evaporated in the evaporator 40, not only water vapor but also water droplets and splashes thereof are scattered. Originally, in the evaporator 40, it is necessary to boil and evaporate the liquid refrigerant on the surface of the evaporator heat transfer tube 41, and to cool the heat medium flowing in the evaporator heat transfer tube 41 by the latent heat of evaporation at that time. The However, water droplets and splashes generated in the evaporator 40 reach, for example, a path connecting the evaporator 40 and the adsorbers 10 and 20 and the adsorbers 10 and 20, and evaporate in the paths and adsorbers 10 and 20. As a result, the latent heat of vaporization cannot be taken out as the output of the heat medium (cold water) flowing through the evaporator heat transfer tube 41, resulting in heat loss on the system. The present embodiment reduces the system loss.

  As shown in FIGS. 8 and 9, a plate-shaped tray 54 is provided below the opening position of the liquid-phase refrigerant return pipe 50 on the evaporator 40 side and above the evaporator heat transfer tube 41 in the evaporator 40. Is arranged. By the receiving tray 54, the inside of the evaporator 40 is divided into a space in which liquid refrigerant is stored and a heat transfer pipe 41 for the evaporator is accommodated, and a space communicating with the adsorbers 10 and 20.

  The receiver 54 has a large number of liquid-phase refrigerant passage holes 541 for supplying the liquid-phase refrigerant accumulated on the upper surface of the receiver 54 to the space in which the evaporator heat transfer tube 41 is stored, and the space in which the evaporator heat transfer tube 41 is stored. A plurality of gas-phase refrigerant passage holes 542 for allowing the gas-phase refrigerant to flow through the adsorbers 10 and 20 are formed.

  A plate-like baffle plate 55 that covers the gas-phase refrigerant passage hole 542 is disposed above the gas-phase refrigerant passage hole 542. The baffle plate 55 covers the entire opening of the gas-phase refrigerant passage hole 542 when viewed in the vertical direction. In addition, a gap is formed between the outer peripheral side lower surface of the baffle plate 55 and the upper surface of the peripheral portion of the gas-phase refrigerant passage hole 542 in the tray 54 so as to allow the gas-phase refrigerant to pass therethrough.

  In the above configuration, when water vapor, water droplets, and droplets generated in the evaporator 40 pass through the gas-phase refrigerant passage hole 542 and flow toward the adsorbers 10 and 20, the water droplets and droplets are baffle plates. After colliding with 55, it drops onto the space in which the evaporator heat transfer tube 41 is accommodated or the receiving tray 54, and only water vapor flows toward the adsorbers 10 and 20.

  Thus, since the baffle plate 55 prevents the water droplets and splashes generated in the evaporator 40 from flowing into the adsorbers 10 and 20, the above system loss can be reduced.

  Water droplets and splashes dropped on the tray 54 and liquid phase refrigerant dropped on the tray 54 from the liquid-phase refrigerant return pipe 50 pass through the liquid-phase refrigerant passage hole 541 and pass through the evaporator heat transfer tube 41 located above. Drip on the surface.

  According to this embodiment, the same effect as the first embodiment can be obtained.

  Further, since water droplets and splashes generated in the evaporator 40 are prevented from flowing to the adsorbers 10 and 20, the system loss can be reduced.

  Further, since the liquid-phase refrigerant dropped on the tray 54 is dropped on the surface of the evaporator heat transfer tube 41 located at the upper part, a wide area on the surface of the evaporator heat transfer tube 41 can be utilized, and the evaporator 40 It is possible to improve the heat exchange efficiency by lowering the water level of the liquid-phase refrigerant stored in the lower part.

  The tray 54 may use a metal mesh. For the throttle mechanisms 51 and 53, a capillary tube, a needle valve, a solenoid valve, an electric valve, or the like can be used.

(Other embodiments)
In each said embodiment, although the example which applies this invention to an adsorption-type refrigerator was shown, this invention is applicable also to an absorption refrigerator.

  In addition, this invention is not limited to above-described embodiment, In the range described in the claim, it can change suitably.

  Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible.

  In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily essential unless explicitly stated as essential and clearly considered essential in principle. Yes.

  Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case.

  Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of the component, etc., the shape, unless otherwise specified and in principle limited to a specific shape, positional relationship, etc. It is not limited to the positional relationship or the like.

30 Condenser 40 Evaporator 41 Heat Transfer Tube 52 Refrigerant Return Pipe

Claims (5)

An evaporator (40) in which a part of the heat transfer pipe (41) for circulating the heat medium is disposed inside and boil-evaporates the refrigerant by heat exchange between the liquid phase refrigerant stored in the lower part and the heat medium,
A condenser (30) for condensing the gas-phase refrigerant;
A refrigerant return pipe (52) for guiding the gas-phase refrigerant in the condenser into the liquid-phase refrigerant in the evaporator ,
The refrigerant return pipe is connected to the condenser at a position where only the gas-phase refrigerant in the condenser can be taken out,
A refrigerating machine comprising a throttle mechanism (53) for adjusting the amount of gas-phase refrigerant flowing in the refrigerant return pipe in the middle of the refrigerant return pipe . A liquid phase refrigerant return pipe (50) connected to the condenser at a position where only the liquid phase refrigerant in the condenser can be taken out and returning the liquid phase refrigerant in the condenser to the evaporator;
Is disposed in the middle of the liquid refrigerant return pipe, as claimed in claim 1, characterized in that it comprises a stop mechanism (51) to adjust the amount of liquid refrigerant flowing through the liquid refrigerant return the pipe refrigerator. An evaporator (40) in which a part of the heat transfer pipe (41) for circulating the heat medium is disposed inside and boil-evaporates the refrigerant by heat exchange between the liquid phase refrigerant stored in the lower part and the heat medium,
A condenser (30) for condensing the gas-phase refrigerant;
A refrigerant return pipe (52) for guiding the gas-phase refrigerant in the condenser into the liquid-phase refrigerant in the evaporator ;
A liquid phase refrigerant return pipe (50) connected to the condenser at a position where only the liquid phase refrigerant in the condenser can be taken out and returning the liquid phase refrigerant in the condenser to the evaporator;
A refrigerating machine comprising: a throttle mechanism (51) that is arranged in the middle of the liquid phase refrigerant return pipe and adjusts an amount of the liquid phase refrigerant flowing through the liquid phase refrigerant return pipe . An evaporator (40) in which a part of the heat transfer pipe (41) for circulating the heat medium is disposed inside and boil-evaporates the refrigerant by heat exchange between the liquid phase refrigerant stored in the lower part and the heat medium,
A condenser (30) for condensing the gas-phase refrigerant;
A refrigerant return pipe (52) for guiding the gas-phase refrigerant in the condenser into the liquid-phase refrigerant in the evaporator ,
The refrigerant return pipe is connected to the condenser at a position where both the gas-phase refrigerant and the liquid-phase refrigerant in the condenser can be taken out,
A refrigerating machine comprising a throttle mechanism (53) for adjusting an amount of refrigerant flowing in the refrigerant return pipe in the middle of the refrigerant return pipe . The refrigerator according to any one of claims 1 to 4, wherein the throttling mechanism interrupts the flow of the refrigerant according to the capacity of the evaporator and the condenser at that time.

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