JP4623031B2 - Freezer refrigerator - Google Patents

Description

  The present invention relates to a refrigerator-freezer.

  In a conventional refrigerator-freezer, a capillary tube is used for the expansion process of the refrigeration cycle. The capillary expansion process was an isenthalpy change, resulting in heat loss. In order to solve this problem, heat exchange is performed between the suction pipe and the capillary tube of the compressor.

  On the other hand, an ejector is used for the expansion process of the refrigeration cycle, and it is a decompression means for decompressing the fluid, and it has been reported to improve the cycle efficiency by transporting the fluid by the entrainment action by the working gas ejected at high speed. (See Patent Document 1). This is connected to the gas-liquid separator after the first evaporator is connected to the outlet of the ejector. Then, the gas phase side outlet of the gas-liquid separator is connected to the suction side of the compressor. Furthermore, after connecting a 2nd evaporator to the liquid phase side exit of a gas-liquid separator via a throttle valve, it connects to the suction part of an ejector. This is a configuration in which cold heat generated in the first and second evaporators is utilized for freezing or refrigeration by an ejector cycle that changes isentropically.

JP 2005-37056 A

The ejector cycle described in Patent Document 1 can improve the COP of the entire refrigeration cycle and is an effective refrigeration cycle. However, none of the arrangements in which the ejector was actually incorporated into the refrigeration cycle and mounted in the refrigerator was clearly shown. The structure of the refrigerator-freezer is required to increase the volume of the cooling chamber as much as possible, but it is necessary to mount all the components of the refrigeration cycle, which is spatially strict. Furthermore, while there are pipes and equipment in which the refrigerant becomes hot inside, it is necessary to keep each cooling chamber at a low temperature of about −20 ° C. to 5 ° C. The arrangement of equipment and piping was not easy.
When an ejector is mounted instead of a conventional pressure reducing means such as a capillary, there is a pipe connected to the suction part, and the refrigerant circuit needs to be changed, and the conventional assembly process needs to be changed. Depending on the location of the ejector, the volume of the cooling chamber of the refrigerator-freezer may be reduced. In addition, depending on the location of the ejector, heat loss may occur, and the efficiency may not be improved as expected.

The present invention has been made to solve the above-described problems, and an object thereof is to provide a refrigerator that can improve the efficiency of a refrigeration cycle by mounting an ejector without reducing the volume of the cooling chamber of the refrigerator. It is what.
Another object of the present invention is to obtain a refrigerator that can reduce the heat loss in the ejector as much as possible to improve the efficiency of the refrigeration cycle, and does not require a significant change in the assembly process.

  A refrigerator-freezer according to the present invention includes a compressor that discharges high-pressure refrigerant, a condenser that condenses the refrigerant discharged from the compressor, a throttle device that decompresses the refrigerant condensed by the condenser, and the throttle device A throttle device outlet connection pipe, one of which is connected to the outlet portion of the throttle device, a first evaporator for connecting the other of the throttle device outlet connection pipes to the inlet portion and evaporating the refrigerant decompressed by the throttle device, a condenser and a throttle A drive flow connection pipe branched from between the devices, a suction flow connection pipe connected to one of the outlets of the first evaporator, a drive flow inlet connected to the drive flow connection pipe, and the other of the suction flow connection pipe In the first evaporator through the suction port connecting pipe, the nozzle that decompresses the refrigerant condensed by the condenser flowing in from the driving inlet port through the driving flow connecting pipe, and ejecting the refrigerant at high speed, through the suction flow connecting pipe The evaporated refrigerant is sucked from the suction inlet. And an ejector configured to mix the refrigerant jetted from the nozzle unit, a diffuser unit that increases the pressure of the refrigerant mixed in the mixing unit, and to discharge the refrigerant whose pressure has increased in the diffuser unit from the outlet unit, The ejector outlet connecting pipe, one of which is connected to the outlet of the ejector, and the other of the ejector outlet connecting pipe are connected to the inlet, and the refrigerant from the ejector is evaporated at an evaporation temperature higher than the evaporation temperature of the first evaporator. A first evaporator, and a refrigerant circuit having an evaporator outlet connection pipe for guiding the refrigerant evaporated by the second evaporator from the outlet of the second evaporator to the compressor, and the first evaporator And a cooling chamber to which the cooler air cooled through the second evaporator is supplied, and the cooler air after cooling the cooler chamber is returned from the cooler chamber to the first evaporator and the second evaporator. A return air passage, and the second evaporator is located upstream of the flow of the internal air passing through the first evaporator and the second evaporator again through the return air passage, and the first evaporator is provided The first evaporator is arranged side by side above the second evaporator so as to be on the downstream side, and the internal air passing therethrough exchanges heat with the refrigerant of the second evaporator having a high evaporation temperature first, and the air temperature Heat exchange with the refrigerant of the first evaporator having a low evaporation temperature in a state where the temperature of the refrigerant has decreased, and the passing air in the warehouse passes through the refrigerant from the inlet portion to the outlet portion in each of the first evaporator and the second evaporator. The throttle device outlet connection pipe connected to the inlet of the first evaporator is connected to the lower part of the first evaporator and the suction flow connection pipe connected to the outlet of the first evaporator so as to be parallel to the flow. Located above the first evaporator, the refrigerant flows in an upward flow through the first evaporator, and the inlet of the second evaporator The ejector outlet connecting pipe connected to the second evaporator is located at the lower part of the second evaporator, the evaporator outlet connecting pipe connected to the outlet part of the second evaporator is located at the upper part of the second evaporator, and the refrigerant is connected to the second evaporator. It flows in an upward flow.

According to the present invention, when the in-compartment air passes through the first evaporator and the second evaporator, the temperature difference between the in-compartment air and the refrigerant can be kept at a certain level or more, so that efficient heat exchange is achieved. Therefore, it is possible to obtain a refrigerator-freezer capable of improving the efficiency of the refrigeration cycle in combination with the effect of reducing the compressor power consumption by mounting the ejector.

Embodiment 1 FIG.
1 is a front view showing a refrigerator-freezer 1 according to Embodiment 1 of the present invention. This refrigerator-freezer 1 has, for example, five cooling chambers 1a to 1e, a refrigerating chamber 1a in which the room temperature is maintained at about 5 ° C., and a switching chamber 1b that can be switched between 0 ° C. and −18 ° C., −20 The ice making room 1c is maintained at about 2 ° C., the vegetable room 1d is maintained at about 2 ° C., and the freezing room 1e is maintained at about −18 ° C. FIG. 1 is a front view showing a state in which the refrigerator doors 9 of the cooling chambers 1a to 1e are visible.

  2 is a cross-sectional configuration diagram taken along line II-II in FIG. 1, and FIG. 3 is an enlarged cross-sectional configuration diagram illustrating a part of the housing 2 according to the present embodiment. 2 and FIG. 3 are omitted, and the hatched lines indicate the heat insulating material 4. As shown in FIG. 3, the housing 2 of the refrigerator-freezer constituting the container of the refrigerator-freezer 1 is configured to have a cross-sectional material 4 such as urethane between the outer wall 5 and the inner wall 6. The outer wall 5 is made of a steel plate of about 1 mm, for example, and the inner wall 6 is made of a plastic such as ABS of about 2 mm. Actually, the width between the outer wall 5 and the inner wall 6 is, for example, about 35 to 45 mm, and a part of the refrigerant piping of the heat exchanger constituting the condenser is reciprocated once or a plurality of times in the vertical direction or the horizontal direction. The heat insulating material 4 is provided so as to surround the condenser. The heat insulating material 4 between the outer wall 5 and the inner wall 6 is configured so that the heat radiation from the condenser through which the refrigerant of about 30 ° C. flows is not directly transmitted to the outer wall 5 and the inner wall 6. Similarly to the housing 2 shown in FIG. 3, the refrigerator door 9 of each of the cooling chambers 1 a to 1 e is composed of the outer wall 5, the heat insulating material 4, and the inner wall 6. By the heat insulating material 4 provided in the refrigerator door 9, the cooling chambers 1a to 1e and the outside are thermally shielded.

  Furthermore, as shown in FIG. 2, there is a machine room 3 for storing the compressor 15 below the back of the refrigerator 1. For example, a machine room blower 16 and a flow path switching valve 14 are also stored in the machine room 3. The back side of the machine room 3 is usually covered with a removable machine room cover so that it cannot be seen from the outside. Each device stored in the machine room 3 can be easily maintained by removing the machine room cover as needed, such as when there is aging or failure. Since the compressor 15 is stored in the machine room 3, the room of the machine room 3 becomes a high temperature of about 30 ° C. or more during the operation of the refrigerator 1 and is cooled by the machine room blower 16.

FIG. 4 is an explanatory view showing the basic configuration of the refrigerator 1 corresponding to FIG. 2, and includes a housing 2 indicated by diagonal lines, a machine room 3 indicated by diagonal grid lines, an interior 8 indicated by horizontal lines, and white coating. The refrigerator door 9 is shown. FIG. 5 is an explanatory diagram showing the housing 2 as seen from the front of the refrigerator refrigerator 1 with the refrigerator door 9 removed, and the rear surface 2a, the upper surface 2b, and the lower surface 2c of the cooling chambers 1a to 1e by the housing 2 shown by oblique lines. FIG. 2 shows a state in which both side surfaces 2d are surrounded. The installation positions of the ejector 11, the evaporator 12, the low-pressure accumulator 13, and the internal blower 19 in the interior 8 are also indicated by dotted lines.
Here, the housing 2 and the refrigerator door 9 are configured to surround the entire interior 8 which is a portion kept at a low temperature. However, the entire housing 2 is not configured as shown in FIG. 3, and there may be a portion where the heat insulating material 4 is not provided. For example, a part of the condenser is provided on the lower surface 2c of the housing, for example, but the heat insulating material 4 is not provided, and the condenser in this part evaporates water accumulated on the evaporation plate provided on the lower surface. It may be.

  As a transport means for transporting the cooling chambers 1a to 1e to the cooling chambers 1a to 1e, the evaporator 12 that is a part that generates cold heat, and the cold heat obtained by the evaporator 12 to each of the cooling chambers 1a to 1e, for example, a blower, The internal fan 19 and the air paths 31, 32, 33, 34a, and 34b are arranged. Further, return air passages 35 and 36 for returning the air whose temperature has risen after the heat exchange with the air in each room in the cooling chambers 1 a to 1 e to the cold heat generation part are also arranged on the back side of the interior 8. Dampers 21, 22, and 23 are disposed between the air passage 31 directly connected to the air outlet 19 a of the internal fan 19 that blows the cold heat obtained by the evaporator 12 and the other air passages 32, 33, 34 a, and 34 b. The air paths 32, 33, 34a, and 34b are opened and closed by opening and closing the dampers 21, 22, and 23.

  Regions other than the cooling chambers 1a to 1e in the cabinet 8 are installed in a narrow space as much as possible in order to increase the volume of each of the cooling chambers 1a to 1e. The evaporator 12 is installed on the back side of the vegetable compartment 1d and the freezer compartment 1e, for example, and the internal fan 19 is installed in the vicinity of the evaporator 12, for example, on the top of the evaporator 12. The ejector 11 is disposed in the vicinity of the evaporator 12, for example, above the evaporator 12, so as to avoid a portion facing the air outlet 19 a of the internal fan 19. The low-pressure accumulator 13 is installed in the vicinity of the evaporator 12, for example, above the evaporator 12. Here, the low-pressure accumulator 13 and the ejector 11 are arranged in a symmetrical position with respect to the outlet 19 a of the internal fan 19. The low-pressure accumulator 13 adjusts by increasing or decreasing the amount of refrigerant stored in the low-pressure accumulator 13 when the amount of refrigerant circulating in the refrigeration cycle increases or decreases depending on, for example, environmental conditions or operating conditions.

Hereinafter, the flow of cold heat in the refrigerator 8 of the refrigerator 1 will be described.
In FIG. 2, a solid white arrow indicates the flow direction of the cold air from the evaporator 12, and a dotted white arrow indicates the flow of return air to the evaporator 12. By opening / closing the refrigerating room blower damper 21, the switching room blower damper 22, and the freezer compartment blower damper 23, the refrigerating room air passage 32, the switching room air passage 33, and the freezer compartment air passages 34a and 34b are opened and closed. The evaporator 12 exchanges heat between the refrigerant flowing in the evaporator 12 and the ambient air, and cool air is blown from the blower outlet 19 a to the distribution air passage 31 by the internal blower 19. And all or any of each cooling room 1a-1e is cooled through each air path 31, 32, 33, 34a, 34b connected to the distribution air path 31 in a store | warehouse | chamber, and the temperature of cold air rises, and a refrigerator compartment 1. It returns to the periphery of the evaporator 12 through the return air passage 35 or the freezer compartment return air passage 36 shared by the switching chamber 2 and the ice making chamber 3. Further, the returned air exchanges heat with the refrigerant again in the evaporator 12 to become a low temperature, and is blown into the cooling chambers 1 a to 1 e by the internal fan 19. In the present embodiment, the vegetable room 1 d that keeps the temperature relatively high is configured to be cooled by the air passing through the common return air passage 35 of the refrigerating room 1, the switching room 2, and the ice making room 3.

  The present embodiment is characterized in that an ejector 11 is provided in the expansion process of the refrigeration cycle. FIG. 6 is an explanatory diagram showing the configuration and operation of the ejector 11. Here, for example, a cylindrical ejector 11 having a length L of about 20 cm and a width W of about 4 cm or less is used. 6A is an explanatory diagram showing a cross-sectional configuration along the axis of the ejector 11, and FIG. 6B is a graph showing pressure distributions corresponding to positions X1 to X6 in FIG. 6A. The axis shows the ejector position, and the vertical axis shows the pressure P.

  The pipes constituting the refrigerant circuit of the refrigeration cycle and connected to the ejector 11 are a drive flow connection pipe 51 connected to the drive inlet section 40, a suction flow connection pipe 52 connected to the suction inlet section 41, and an ejector outlet. There are three ejector outlet connecting pipes 53 connected to the parts. The inside of the ejector 11 includes a suction part 42, a nozzle part 43, a mixing part 44, and a diffuser part 45. The nozzle part 43 further includes a pressure reducing part 43a and a divergent part 43b. The flow passage cross-sectional area is reduced by the pressure reducing portion 43a, and the portion having the smallest opening area is referred to as a throat portion 43c. A divergent portion 43b is formed downstream from the throat portion 43c and continues to the nozzle outlet portion 43d.

  The ejector 11 has, for example, a fixed throttle configuration in which the area ratio (hereinafter referred to as expansion ratio) of the throat portion 43c and the nozzle outlet portion 43d of the internal nozzle is constant, and a refrigerant having a pressure P1 flowing in from the direction of the arrow Y1 is used as a driving fluid ( The position X1) is decompressed and expanded by the decompression section 43a, and the sound velocity of the pressure P2 is obtained by the throat section 43c (position X2). Further, the pressure is reduced to the pressure P3 as supersonic speed at the divergent portion 43b (position X3). At this time, the gas-liquid two-phase state flowing from the direction of the arrow Y2 or the refrigerant of the gas refrigerant is sucked (position X4), and the mixed gas-liquid two-phase refrigerant recovers the pressure in the mixing unit 44 and is in the state of the pressure P4. It becomes a refrigerant (position X5), and further rises to the pressure P5 by the diffuser portion 45 and flows out (position X6).

  When the nozzle portion 43 of the ejector 11 expands under reduced pressure, the change is close to isentropic. That is, there is almost no energy loss generated by a decompression means such as a conventional capillary, and an efficient refrigeration cycle can be configured. In addition, there is an effective point that the volumetric efficiency of the refrigerant is increased and the circulation amount of the refrigerant can be increased by sucking the refrigerant in the evaporator by the suction action and increasing the compressor suction pressure by the pressure raising action.

FIG. 7 is a circuit configuration diagram showing an example of the configuration of the refrigeration cycle according to the present embodiment. FIG. 8 is a Ph diagram of the refrigeration cycle according to the present embodiment. The horizontal axis indicates enthalpy h and the vertical axis indicates. The pressure P is shown. In the present embodiment, for example, R600a is enclosed in the refrigeration cycle as a refrigerant. Alphabet symbols (A to H) in FIG. 7 indicate the state of the refrigerant at that location with the same alphabets (A to H) in the corresponding parts of FIG.
In the present embodiment, the evaporator 12 has, for example, two evaporators (first evaporator 12a and second evaporator 12b), and the first evaporator 12a and the second evaporator 12b evaporate different refrigerants. This is a circuit configuration capable of obtaining temperature.

  In FIG. 7, 17 is a condenser and 18 is a throttle device. The compressor 15, the condenser 17, and the flow path switching valve 14 are sequentially connected by a connection pipe. The flow path switching valve 14 is connected to the ejector 11 by a drive flow connection pipe 51 and is connected to the expansion device 18 in parallel with this. The expansion device 18 is connected to the divided first evaporator 12 a, and the outlet portion of the first evaporator 12 a and the suction portion of the ejector 11 are connected by the suction flow connection pipe 52. The outlet portion of the ejector 11 is connected to the inlet portion of the other divided second evaporator 12b by an ejector outlet portion connecting pipe 53. Further, a pipe is connected to the compressor 15 from the outlet of the second evaporator 12b via the low-pressure accumulator 13, thereby constituting a refrigeration cycle. In the first evaporator 12a, the refrigerant flows in from the expansion device outlet connection pipe 50 and flows out to the ejector suction flow connection pipe 52. In the second evaporator 12b, the refrigerant flows in from the ejector outlet connection pipe 53 and flows out to the evaporator outlet connection pipe 54.

  Next, the refrigeration cycle operation of the present embodiment will be described. The high-temperature and high-pressure refrigerant (B) discharged from the compressor 15 releases heat to the outside of the refrigerator or the like by the condenser 17 to be condensed and liquefied to become a gas-liquid two-phase refrigerant (C). The high-pressure gas-liquid two-phase refrigerant (C) branches in two directions by the flow path switching valve 14. One is boiled under reduced pressure by the expansion device 18 and flows into the first evaporator 12a through the expansion device outlet connection pipe 50 as a low-pressure gas-liquid two-phase refrigerant (D). The first evaporator 12a evaporates and evaporates by cooling the air in the warehouse (E). The vapor refrigerant (E) that has flowed out of the first evaporator 12 a flows into the suction portion of the ejector 11 through the ejector suction flow connection pipe 52.

The other high-pressure gas-liquid two-phase refrigerant (C) branched by the flow path switching valve 14 flows into the ejector 11, expands under reduced pressure at the nozzle portion 43, and becomes a driving fluid that flows out of the nozzle portion 43 at a high speed of about the speed of sound. And ejected to the mixing section 44 of the ejector 11. At this time, the vapor refrigerant (E) from the first evaporator 12 a is sucked as a suction fluid and mixed by the mixing unit 44. Thereafter, the diffuser portion 45 of the ejector expands while decelerating the flow velocity to increase the pressure, and flows into the second evaporator 12b through the ejector outlet connection pipe 53 in a low pressure state (G). The pressure of the refrigerant in the second evaporator 12b is lower than the high pressure state discharged from the compressor 15, but is higher than that of the first evaporator 12a. The second evaporator 12b evaporates and evaporates by cooling the air in the cabinet 8 (H). Thereafter, the refrigerant flows into the compressor 15 through the evaporator outlet connection pipe 54 and the suction pipe (A). The low-pressure vapor refrigerant is compressed by the compressor 15 and flows into the condenser 17 again.
Here, the flow path switching valve 14 merely branches the refrigerant flow in, for example, two directions. When the compressor 15 is stopped, both flow paths are closed.

  As described above, the ejector 11 sucks the refrigerant of the evaporator by the suction action and raises the compressor suction pressure by the pressure raising action. For this reason, by using the ejector 11, cooling at a lower evaporation temperature is possible under the conventional compressor suction pressure and compressor suction temperature conditions, and the refrigeration capacity for cooling the refrigerator is greatly improved. As a result, when the compressor is operated with the same displacement as the conventional compressor, the cooling time is shortened and the power consumption can be reduced. Alternatively, when the compressor is operated with the displacement of the compressor so as to achieve the same cooling capacity as before, there is an effect that the compressor can be downsized. That is, mounting the ejector 11 has an effect of improving the efficiency of the refrigeration cycle.

In the present embodiment, the ejector 11 is disposed in the vicinity of the evaporator 12 in the interior 8. Specifically, the ejector 11 is positioned above the evaporator 12 so as to be biased to the right side or the left side so as to avoid the portion facing the air outlet 19a of the internal fan 19 provided in the vicinity of the evaporator 12. is set up. In other words, it installs so that it may not overlap with the rotation part of the blade | wing of the internal fan 19 installed in the center part seeing from the front.
FIG. 9 is an explanatory diagram schematically showing the connection state of the ejector 11 according to the present embodiment, and shows the flow of refrigerant in the refrigeration cycle together with the flow of air in the refrigerator around the evaporators 12a and 12b. In the figure, solid arrows indicate the direction of refrigerant flow, and white arrows indicate the direction of air flow in the refrigerator. In order to make the connection state of the ejector 11 easy to understand, the ejector 11 is shown shifted from the installation position in this figure, and is actually arranged at the portion of the ejector indicated by a dotted line.

  As shown in the figure, the first evaporator 12a is installed on the downstream side in the air flow direction, and the second evaporator 12b is installed on the upstream side in the air flow direction. The throttle device outlet connection pipe 50 is connected to the lower part of the first evaporator 12a so that the refrigerant flows in an upward flow toward the ejector suction flow connection pipe 52 located at the upper part of the first evaporator 12a. Further, the ejector outlet connecting pipe 53 is connected to the lower part of the second evaporator 12b, and the refrigerant forms an upward flow toward the evaporator outlet connecting pipe 54 at the upper part of the second evaporator 12b.

  The refrigerant circuit in the present embodiment includes a compressor 15-> condenser 17-> flow path switching valve 14-> throttle device 18-> first evaporator 12 a-> suction part of the ejector 11 as indicated by solid arrows. And a flow path switching valve 14-> ejector 11-> second evaporator 12 b-> low pressure actuator 13-> compressor 15. The condenser 17 is provided between the outer wall 5 and the inner wall 6 of the housing 2. For example, the condenser 17 flows in the order of the bottom surface-> right side surface-> back surface-> left side surface-> top surface-> front surface, and the flow path switching valve. 14 is connected. As described above, it is desirable that each device is connected by the refrigerant pipe over the machine room 3, the casing 2, and the inside of the cabinet 8, and the length of the connection pipe is as short as possible and is simple. Of course, this circulation order is an example, and the present invention is not limited to this.

  In this embodiment, since the ejector 11 is installed in the vicinity of, for example, the upper part of the evaporator 12, the lengths of the ejector suction flow connection pipe 52 and the ejector outlet connection pipe 53 that are pipes connecting the ejector 11 and the evaporator 12. You can shorten it. Further, when the shaft of the cylindrical ejector 11 is installed in a state where it is inclined so that the horizontal or upstream side is on the upper side, the driving flow inside the ejector becomes a horizontal flow or a downward flow with respect to gravity instead of an upward flow. For this reason, bubbles are easily subdivided and the efficiency of the ejector is improved.

  In the three pipes connected to the ejector 11, the ejector drive inlet 40 and the flow path switching valve 14 are connected by the ejector drive outlet connection pipe 51, and the first evaporator 12 a outlet pipe and the suction are connected by the ejector suction outlet connection pipe 52. The inlet part 41 is connected, and the ejector outlet part and the second evaporator 12 b inlet pipe are connected by the ejector outlet connecting pipe 53. In the configuration of the present embodiment, the evaporators 12a and 12b and the flow path switching valve 14 are arranged such that the first evaporator 12a is the uppermost, and then the second evaporator 12b and the flow path switching valve 14 are the machine room 3. Arranged at the bottom. Therefore, when the cylindrical ejector 11 is tilted so that the suction inlet 41 is located above the ejector outlet, the connection of the ejector 11 with the ejector suction connection pipe 52 is connected to the ejector outlet connection pipe 53. Therefore, the vertical relationship between the first evaporator 12a and the second evaporator 12b to which the respective pipes 52 and 53 are connected is the same. For this reason, the length of the piping 52 and 53 can be shortened, and the handling of the piping can be simplified.

  Thus, shortening the connection distance of the connection pipe constituting the refrigerant circuit has an effect of reducing the refrigerant pressure loss in the connection pipe. Further, simplifying the handling of the connecting pipe facilitates the brazing operation of the connecting pipe to the ejector 11 during the manufacturing process, and has the effect of simplifying the assembly process and reducing the manufacturing cost.

  FIG. 10 is a graph showing a change in the temperature of the refrigerant flowing through the evaporator 12 and a change in the air temperature in the interior 8 passing through the evaporator 12 according to the present embodiment. In the figure, the horizontal axis indicates the positions of the second evaporator 12b and the first evaporator 12a, the left side being the lower inflow side and the right side being the upper outflow side. The vertical axis represents temperature (° C.). In the figure, a broken line arrow represents a temperature change of the air in the warehouse 8 passing through the evaporators 12a and 12b, and a solid line arrow represents a temperature change in the flow direction of the refrigerant in the evaporators 12a and 12b. The suction air temperature of the second evaporator 12b is about −15 ° C., the refrigerant is supplied to the second evaporator 12b from the ejector outlet connection pipe 53, the refrigerant temperature at the inlet is about −25 ° C., and the second evaporator 12b Cool by exchanging heat with the air that passes around. At the outlet of the second evaporator 12b, the refrigerant temperature decreases with a pressure loss to about -26 ° C. On the other hand, the passing air is cooled from about −15 ° C. to about −23 ° C. and flows into the first evaporator 12a. A refrigerant of about −30 ° C. flows from the expansion device outlet connection pipe 50 into the inlet portion of the first evaporator 12a to exchange heat with the passing air. The refrigerant at the outlet of the first evaporator 12a is reduced to about −31 ° C. due to pressure loss. The passing air is cooled from about −23 ° C. to about −27 ° C. by the first evaporator 12a, sucked into the internal fan 19, and passed through the distribution air passages 31, 32, 33, 34a, 34b to each cooling chamber 1a. To 1e.

  When the pressure loss occurs in the flow direction of the refrigerant, the evaporating temperature of the refrigerant is lowered. Considering this temperature drop, the temperature difference between the passing air and the parallel flow, that is, the passing air and the refrigerant is always more than a certain value, for example, 3 The flow of the refrigerant is configured to be about ℃ or higher. For this reason, the cold heat of the refrigerant is efficiently transferred to the passing air, and the generated cold heat can be used without waste. For example, if the first evaporator 12a is disposed upstream and the second evaporator 12b is disposed downstream of the air flow in the cabinet 8, the air temperature is substantially the same on the outflow side of the second evaporator 12b. , Cold heat is not transferred to the passing air well. Further, if the refrigerant flows in the evaporators 12a and 12b from the upper side to the lower side as opposed to the air flow, the change in the refrigerant temperature in FIG. In this case as well, there is a portion where the difference between the refrigerant temperature and the air temperature is small, and the cold heat is not successfully transferred to the passing air.

  In the present embodiment, by passing the air in the refrigerator from the refrigerant inflow side to the refrigerant outflow side of the evaporators 12a and 12b, the temperature difference between the air and the refrigerant can be maintained, and the evaporator is downsized. it can.

  Furthermore, two evaporators 12a and 12b are provided, and each is operated to have different evaporation temperatures. Then, first, heat exchange is performed between the refrigerant of the second evaporator 12b having a high evaporation temperature and the internal air, and heat exchange is performed with the refrigerant of the first evaporator 12a having a low evaporation temperature in a state where the air temperature is lowered. Thereby, efficient heat exchange is possible, maintaining a temperature difference, and the evaporator 12 can be further reduced in size.

  FIG. 11 is a schematic diagram showing the evaporator 12 housed in the warehouse 8, the internal fan 19, and a member K to which a part of the air path is integrally attached, and FIG. 11A is viewed obliquely. FIG. 11B is a sectional view taken along line XIIB-XIIB in FIG. In the assembly process of the refrigerator 1, a member K to which the internal fan 19 and the evaporator 12 are attached is formed in advance, and the member K is fitted into the internal space 8 surrounded by the housing 2 from the front side, for example. Thereafter, the interior 8 can be easily formed by fitting the cooling chambers 1a to 1e in the same manner.

  The member K is, for example, ABS, and an internal fan 19 is installed in the vicinity of the evaporator 12, for example, above, and unevenness for forming an air passage is formed on the back and upper sides of the peripheral fan 19. . The operation area of the internal fan 19 and the air outlet 19a are circular when viewed from the front, and the ejector 11 is installed on the left side of the internal fan 19, for example, and the low-pressure accumulator 13 is installed on the right side. If the ejector 11 and the low-pressure accumulator 13 are previously attached to the member K in the assembly process, as with the evaporator 12 and the internal fan 19, the refrigerator-freezer equipped with the ejector 11 can be assembled with high productivity. It also leads to reduction.

In this Embodiment, the ejector 11 is arrange | positioned in the vicinity of the evaporator 12 using the space of the circumferential part formed by the circular shape of the internal fan 19. For this reason, the ejector 11 can be mounted and an efficient refrigeration cycle can be realized without affecting the volume of the cooling chamber.
In addition, the vicinity of the evaporator 12 which arrange | positions the ejector 11 means the area | region near the evaporator 12 in the upper part of the evaporator 12, the lower part, the right side, the left side, the front surface, and the back surface, and the distance with the evaporator 12 is 10 cm-15 cm. It is an area close to the extent. The interior 8 has almost no room in space, and the configuration shown in FIG. 2 uses a space formed between the blower 19 above the evaporator 12. Moreover, the vicinity of the evaporator 12 which arrange | positions the air blower 19 in a store | warehouse | chamber is the area near the evaporator 12 in the upper part, the lower part, the right side, the left side, the front surface, and the back surface of the evaporator 12, and the distance with the evaporator 12 is 10 cm- It is a close region of about 15 cm. Since the internal blower 19 is disposed between the evaporator 12 and the air path 31, it is installed above the evaporator 12 in the configuration shown in FIG. 2.

  FIG. 12 is an explanatory view showing a connection state of the ejector 11 according to another configuration of the refrigerator-freezer of the present embodiment. In the figure, the portion of the heat insulating material 7 is indicated by oblique lines. The ejector drive flow connection pipe 51 connected to the drive inlet 40 is about 30 ° C., the ejector suction flow connection pipe 52 connected to the suction inlet 41 is about −30 ° C., and the ejector connected to the ejector outlet The outlet connection pipe 53 is about -25 ° C. The temperature of the inside 8 is about −15 ° C. or less, and is about −27 ° C. in the vicinity of the evaporator 12 storing the ejector 11. Therefore, in FIG. 12, the heat insulating material 7 is provided around at least the connection pipe stored in the interior 8 of the drive flow connection pipe 51 connected to the drive inlet port 40 of the ejector 11.

  In consideration of the ambient temperature at the position where the ejector 11 is disposed and the refrigerant temperature passing through the connection pipe, the ejector suction flow connection pipe 52 and the ejector outlet connection pipe 53 are low in temperature and have no problem, but the ejector drive flow connection pipe 51 is high in temperature. Therefore, if the heat is radiated from the connection pipe, the internal temperature rises. Then, the heat-insulating material 7 is provided at least around the portion of the ejector drive flow connection pipe 51 stored in the interior 8 to prevent the interior temperature from rising.

  Furthermore, the refrigerant flowing through the ejector drive flow connection pipe 51 is a high-pressure gas-liquid two-phase refrigerant that flows out of the condenser 17. If it is made to flow in the nozzle part 43 of an ejector in this state, a refrigerant | coolant will boil easily in the throat part 43c, and the droplet of the refrigerant | coolant flow which ejects from the nozzle exit part 43d will be atomized. For this reason, nozzle efficiency can be improved by the speed difference of a gas-liquid reducing in the mixing part 44, and becoming a homogeneous flow. On the other hand, when the ejector drive flow connection pipe 51 is exposed to the interior 8, the refrigerant flowing through the interior is cooled to become a supercooled state and becomes a liquid refrigerant. When the liquid refrigerant flows into the nozzle portion 43 as the driving fluid, the mixing fluid decreases in the mixing portion 44 and the mixing rate. This leads to a reduction in the efficiency of the ejector 11. In the configuration shown in FIG. 12, since the heat insulating material 7 is provided around the ejector drive flow connection pipe 51, the state of the refrigerant flowing inside the ejector drive flow connection pipe 51 is maintained in a gas-liquid two-phase state, and the ejector efficiency decreases. Can be prevented.

  Of course, if there is a difference between the temperature of the interior 8 and the refrigerant temperature in the connection pipe depending on the operating conditions, at least one of or both of the ejector suction flow connection pipe 52 and the ejector outlet connection pipe 53 is in the interior 8. A heat insulating material may be provided around the portion to be stored.

  In the configuration of FIG. 12, the back side of the ejector 11 is an inner wall 6 constituting the back surface 2 a of the housing 2. Therefore, the ejector drive flow connection pipe 51 connected to the flow path switching valve 14 is stored between the inner wall 6 and the outer wall 5 of the casing 2, and the ejector drive flow connection pipe 51 is connected to the rear casing 2 a until it is close to the ejector 11. Alternatively, it may be guided between the inner wall 6 and the outer wall 5 and immediately before being connected to the drive inlet 40 of the ejector 11. If comprised in this way, while the length of the ejector drive flow connection piping 51 exposed in the store | warehouse | chamber 8 can be shortened, it can prevent that the refrigerant | coolant which flows through the inside is cooled with the cold air of the store | warehouse | chamber 8 It is possible to prevent the heat loss that is radiated to the inside 8. Therefore, a refrigeration cycle with high ejector efficiency can be configured. In addition, when the ejector drive flow connection piping 51 exposed to the inside 8 is short, for example about 10 mm or less, it is not necessary to provide the heat insulating material 7 around the piping. However, when it becomes long for the convenience of piping, it is better to provide the heat insulating material 7 around the piping 51 of the part exposed to the inside 8 of a store | warehouse | chamber.

  Further, if the ejector 11 is installed in contact with, for example, the inner wall 6 of the rear casing 2a, the length of the ejector drive flow connection pipe 51 exposed to the inside 8 can be further shortened, and the ejector efficiency can be prevented from being lowered. Heat loss can be reduced.

  FIG. 13 is an explanatory diagram showing an installation state of the ejector 11 in another configuration of the refrigerator-freezer according to the present embodiment. In the figure, the installation state of the ejector 11 is shown with respect to the cross-sectional configuration of the housing 2a on the back surface. Here, the left side of the housing 2a is the inside 8 and the right side is the outside. The hatched lines indicate the heat insulating material 4 constituting the housing 2, and the ejector 11 is installed so as to contact the inner wall 6 of the housing 2a on the back surface. Then, the ejector suction flow connection pipe 52 and the ejector outlet connection pipe 53 that are pipes connected to the evaporator 12 stored in the inside 8 are connected to the respective evaporators 12 through the inside 8 as they are. The ejector drive flow connection pipe 51 connected to the drive inlet port 40 of the ejector 11 is guided outside the interior 8 through the inner wall 6 with which the ejector 11 is in contact, and further through the heat insulating material 4 of the housing 2a. Pipe is passed through the outer wall 5 side of the heat insulating material 4. In this state, it leads to the vicinity of the machine room 3 and is connected to the flow path switching valve 14 stored in the machine room 3.

In this configuration example, since the main body of the ejector 11 is installed so as to be in contact with the inner wall 6 as described above, the portion exposed to the interior 8 of the ejector drive flow connection pipe 51 can be minimized. For this reason, a decline in ejector efficiency can be prevented and heat loss can be reduced.

  Further, if the inlet portion of the ejector 11 is disposed above the outlet portion, the ejector 11 becomes a downward flow and the efficiency of the ejector can be improved. It may be installed horizontally or inclined so that the entrance side is above the horizontal.

  Furthermore, an ejector suction inlet port portion that is a connection portion with the ejector suction flow connection piping 52 is set to be higher than an ejector outlet portion that is a connection portion with the ejector outlet connection piping 53. In the arrangement of the evaporator 12 according to the present embodiment, the first evaporator 12 a connected to the ejector suction connection pipe 52 is installed above the second evaporator 12 b connected to the ejector outlet connection pipe 53. For this reason, if the ejector suction inlet 41 is disposed above the ejector outlet, the lengths of the ejector suction connection pipe 52 and the ejector outlet connection pipe 53 can be shortened, and the pressure loss can be reduced. , Piping can be simplified.

  Further, the refrigerant circuit is configured so that the driving flow connection pipe 51 connected to the driving inlet 40 of the ejector 11 passes through the outer wall 5 side of the heat insulating material 4 of the housing 2. For this reason, the heat insulating material 4 is provided inside the drive flow connection pipe 51, and the heat of the drive flow connection pipe 51 through which the high-temperature refrigerant flows can be prevented from affecting the interior 8.

  In addition, as shown in FIG. 14, you may comprise the drive flow connection piping 51 so that the ejector drive flow connection piping 51 may pass through the heat insulating material 4 of the housing | casing 2a of a back surface. By passing the inside of the heat insulating material 4, it is possible to prevent the heat of the driving flow connection pipe 51 through which the high-temperature refrigerant flows from affecting the inside 8 and the outside.

  Further, as shown in FIG. 15, in order to connect the ejector drive flow connection pipe 51 to the ejector 11, a heat insulating material 7 indicated by hatching may be provided around the refrigerant pipe exposed in the interior 8. The heat insulating material 7 is, for example, urethane, and similarly to the above, heat loss can be prevented and reduction in ejector efficiency can be prevented.

  Further, in FIGS. 13, 14, and 15, the ejector 11 is stored so that the cylindrical axis is in the vertical direction, but the present invention is not limited to this, and the axis of the ejector 11 is in the oblique direction. It may also be horizontal. Further, although the ejector 11 is disposed in the vicinity of the evaporator 12 so as to come into contact with the inner wall 6 of the housing 2a on the back surface, the present invention is not limited to this. Depending on the installation state of the evaporator 12, the side housing 2d may be close. The ejector 11 may be disposed near or in contact with the nearest inner wall 6 constituting the housing 2 in the vicinity of the evaporator 12. The ejector drive flow connection pipe 51 may be configured to pass between the outer wall 5 and the inner wall 6 of the housing 2 so as not to be exposed to the interior 8 as much as possible.

  Moreover, in the said embodiment, although the refrigerant circuit was comprised so that the ejector drive flow connection piping 51 might pass between the outer wall 5 and the inner wall 6 of the housing | casing 2a which comprises the back surface of a refrigerator-freezer, it is not restricted to this. . For example, even if the refrigerant circuit is configured so as to pass between the outer wall 5 and the inner wall 6 of the housing 2d constituting the left and right side surfaces of the refrigerator, it is possible to prevent heat loss from occurring.

  FIG. 16 is an explanatory diagram showing an installation state of the ejector 11 according to another configuration of the refrigerator-freezer of the present embodiment. In this configuration, the ejector 11 is installed in the partition wall 10 between the cooling chambers 1 a to 1 e in the interior 8. The adjacent portions of the cooling chambers 1a to 1e are separated by a partition wall 10 of about 2 to 3 cm, and the inside of the partition wall 10 is a space. In FIG. 16, the structural example which installs the ejector 11 using the space in this partition wall 10 is shown. For example, the ejector 11 is stored in the partition wall 10 between the vegetable compartment 1d and the freezer compartment 1e, which is the partition wall 10 closest to the evaporator 12.

  As shown in FIG. 2, it is the structure by which the air path is provided in the back side of the cooling chambers 1a-1e. Of the three connection pipes connected to the ejector 11 stored in the partition wall 10, the ejector suction flow connection pipe 52 and the ejector outlet connection pipe 53 are provided on the rear side of the cooling chambers 1 a to 1 e. Even if it passes, there is not much problem in temperature. The ejector drive flow connection pipe 51 through which the high-temperature refrigerant flows is, for example, passed through the inner wall 6 of the side casing 2d and through the heat insulating material 4 of the side casing 2d or the outer wall 5 side of the heat insulating material 4. Guide the piping. If comprised in this way, it can prevent heat radiating from the ejector drive flow connection piping 51 to the inside 8 and heat loss can be reduced.

  Further, for the convenience of connection with the ejector 11, by providing the heat insulating material 7 around the portion of the pipe stored in the partition wall 10 of the ejector drive flow connection pipe 51, the ejector drive flow connection pipe 51 is further connected to the inside of the chamber. 8 can be prevented from radiating heat and heat loss can be reduced. Moreover, it can prevent that a refrigerant | coolant becomes overcooling with the heat insulating material 7 provided in the ejector drive flow connection piping 51, and can prevent that ejector efficiency falls.

  Although the ejector 11 is disposed above the evaporator 12, it may be disposed in a space existing in the vicinity of the evaporator 12. There is an effect that heat loss can be prevented without reducing the volume of the cooling chamber.

  The refrigeration cycle configuration of the refrigerator / refrigerator is not limited to the refrigerant circuit of FIG. 7, but may be other refrigerant circuits. For example, the configuration does not have to include the expansion device 18, the low pressure actuator 13, and the flow path switching valve 14, and the evaporator may be configured with one. If the configuration of the refrigerant circuit is different, the three connecting pipes connected to the ejector 11 may be connected to different devices, but at least ejector suction regardless of the configuration of the refrigeration cycle. The flow connection pipe 52 is connected to the outlet side of the evaporator 12. For this reason, when the ejector 11 is disposed in the vicinity of the evaporator 12, the length of the connection pipe can be shortened, the pressure loss can be reduced, and the piping can be easily handled.

In addition, although the plurality of evaporators 12a and 12b are arranged side by side here, the plurality of evaporators may be arranged at positions separated from each other. In this case, the ejector 11 may be installed in the vicinity of the evaporator that flows out the refrigerant sucked into the ejector 11 as a suction fluid among the plurality of evaporators. By installing the ejector 11 in the vicinity of the evaporator, the distance of the connecting pipe connected to the evaporator can be shortened, the piping can be simplified, and the heat loss can be reduced. Also, a plurality of ejectors may be provided in the same manner as the evaporator.
Further, wherever the evaporator 12 is disposed, when the blower 19 is installed in the vicinity of the evaporator 12, the space formed on the circumferential side of the blower 19 is provided at the outlet 19 a of the blower 19. If the ejector 11 is arranged so as to avoid the opposing portions, the space in the interior 8 can be used effectively, and a refrigeration cycle equipped with the ejector can be configured without reducing the volume of the cooling chambers 1a to 1e.

Moreover, the structure of the ejector 11 is not restricted to FIG. Here, the driving fluid flows in from the axial direction, but a driving fluid connection pipe may be provided on the side surface in the same manner as the suction fluid. Also, a plurality of suction fluid inflow portions may be provided around the ejector cylinder. In this case, the suction fluid is sucked in evenly with respect to the driving flow and is easily mixed in the mixing portion. Improving the mixing performance in the mixing section of the ejector leads to an improvement in the efficiency of the ejector 11, and can further improve the performance of the refrigeration cycle.
In the configuration of FIG. 6, a fixed ejector having a constant expansion ratio is used. However, even if an expansion ratio change type variable throttle ejector that changes the cross-sectional area of the throat using a needle or the like is used, There is an effect. However, the fixed ejector does not cause overexpansion or underexpansion depending on the operation state, compared to the variable throttle ejector. For example, loss due to shock waves can occur when overexpanded, but this can be prevented, so that the droplets ejected from the nozzle can be made as fine as possible, and mixing can be promoted to maintain high ejector efficiency. Can do.

  In the present embodiment, R600a is used as the refrigerant. However, the present invention is not limited to this, and other natural refrigerants such as carbon dioxide as well as HFC refrigerants have the same effect.

Moreover, although the Example applied to the refrigerator-freezer which has five cooling chambers 1a-1e was described here, it is not restricted to this, The number of cooling chambers may be how many, and the freezer which has only a freezer, Even if it is applied to a refrigerator without a freezer, the same effect is obtained. Further, the arrangement of the cooling chambers 1a to 1e is not limited to that shown in FIG. 1 and may be arranged in any manner.
Moreover, although urethane was used as the heat insulating material between the outer wall 5 and the inner wall 6 of the housing 2, for example, this is not restrictive. For example, if a vacuum heat insulating panel is provided in a part, the heat insulating effect can be improved.

Although the compressor 15, the flow path switching valve 14, and the machine room blower 16 are arranged in the machine room 3 in the arrangement of the devices constituting the refrigerator 1 in the above, the present invention is not limited to this. Another device may be arranged, or a configuration without the flow path switching valve 14 may be employed.
Moreover, although the machine room 3 which stores the compressor 15 was provided in the downward direction on the back, it is not restricted to this, The machine room may be provided anywhere, such as above the back. Moreover, although the evaporator 12 was installed in the back side of the freezer compartment 1e and the vegetable compartment 1d, it is not restricted to this and may be installed anywhere.

  As described above, in the present invention, the compressor 15 that discharges the high-pressure refrigerant, the condenser 17 that condenses the high-pressure refrigerant from the compressor 15, and the refrigerant condensed in the condenser 17 is decompressed. Then, the suction fluid is sucked and mixed by the driving fluid that flows out at a high speed, and then the ejector 11 that is expanded and flows out in a low-pressure state, the evaporator 12 that evaporates the low-pressure refrigerant from the ejector 11, and the compression A refrigerant circuit that circulates the refrigerant by connecting the machine 15, the condenser 17, the ejector 11, and the evaporator 12 by refrigerant piping, and wind that transports the cold heat obtained by the evaporator 12 to the cooling chambers 1a to 1e. Passages 31, 32, 33, 34a, 34b and the blower 19, and a machine room 3 for storing the compressor 15, the cooling chambers 1a to 1e, the evaporator 12, the air passages 31, 32, 33, 4a, 34b, the blower 19, and the ejector 11 are housed in the cabinet 8, and the ejector 11 is disposed in the vicinity of the evaporator 12, so that the ejector is mounted without reducing the volume of the cooling chambers 1a to 1e. And the refrigerator-freezer which can aim at the improvement of the efficiency of a refrigerating cycle is obtained.

  Further, the volume of the cooling chambers 1a to 1e is reduced by arranging the blower 19 in the vicinity of the evaporator 12 and arranging the ejector 11 so as to avoid the portion facing the blower outlet 19a of the blower 19. A refrigerator-freezer that can be mounted with an ejector and can improve the efficiency of the refrigeration cycle can be obtained.

  In addition, among the drive flow connection pipes 51 connected to the drive inlet port 40 of the ejector 11, the heat insulating material 7 is provided at least around the connection pipes stored in the interior 8, so that the heat in the pipes 51 can be obtained. It is possible to obtain a refrigerator-freezer that can reduce loss, prevent a decrease in ejector efficiency, and improve the efficiency of the refrigeration cycle.

  The housing 2 surrounding the interior 8 is constituted by an outer wall 5, an inner wall 6, and a heat insulating material 4 provided between the outer wall 5 and the inner wall 6, and the ejector 11 in the interior 8. By configuring the refrigerant circuit so that the driving flow connection pipe 51 connected to the driving inlet port 40 of the casing 2 passes between the outer wall 5 and the inner wall 6 of the housing 2, heat loss in the pipe 51 is reduced. Thus, a refrigerator-freezer capable of preventing the decrease in ejector efficiency and improving the efficiency of the refrigeration cycle can be obtained.

  Further, by installing the ejector 11 in contact with the inner wall 6, the drive flow connecting pipe 51 can be shortened, heat loss in the connecting pipe 51 can be reduced, and the efficiency of the refrigeration cycle can be prevented by lowering the ejector efficiency. A refrigerator-freezer capable of improving efficiency is obtained.

  Further, the refrigerant circuit is configured such that the driving flow connection pipe 51 connected to the driving inlet port 40 of the ejector 11 passes between the heat insulating material 4 of the housing 2 or the outer wall 5 side of the heat insulating material 4. As a result, it is possible to obtain a refrigerator-freezer that can reduce heat loss in the pipe 51, can prevent a decrease in ejector efficiency, and can improve the efficiency of the refrigeration cycle.

It is a front view which shows the refrigerator-freezer which concerns on Embodiment 1 of this invention. FIG. 2 is a cross-sectional configuration view taken along line II-II in FIG. 1 according to the first embodiment of the present invention. It is sectional drawing which expands and shows a part of housing | casing which concerns on Embodiment 1 of this invention. It is explanatory drawing which concerns on Embodiment 1 of this invention and shows the basic composition of a refrigerator-freezer. It is explanatory drawing which concerns on Embodiment 1 of this invention and removes the refrigerator door and shows the housing | casing seen from the front of the refrigerator-freezer. It is explanatory drawing which shows the structure and operation | movement of the ejector which concerns on Embodiment 1 of this invention, FIG. 6 (a) is explanatory drawing which shows the cross-sectional structure along the axis | shaft of an ejector, FIG.6 (b) is FIG. It is a graph which shows the pressure distribution corresponding to each position of X1-X6. It is a circuit block diagram which shows the refrigerating cycle structure which concerns on Embodiment 1 of this invention. It is a Ph diagram of the refrigerating cycle concerning Embodiment 1 of the present invention, and the horizontal axis shows enthalpy h and the vertical axis shows pressure P. It is explanatory drawing which shows the connection state of the ejector which concerns on Embodiment 1 of this invention, and shows the flow of the refrigerant | coolant of a refrigerating cycle with the flow of the air in the refrigerator around an evaporator. It is a graph which concerns on Embodiment 1 of this invention and shows the change of the refrigerant temperature which flows through an evaporator, and the change of the air temperature in the store | warehouse | chamber which passes an evaporator. BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which concerns on Embodiment 1 of this invention, and simplifies and shows the member which attached the evaporator in the store | warehouse | chamber, the fan in a store | warehouse | chamber, and a part of air path integrally. It is explanatory drawing which shows the connection state of the ejector which concerns on another structure of the refrigerator-freezer by Embodiment 1 of this invention. It is explanatory drawing which concerns on another structure of the refrigerator-freezer by Embodiment 1 of this invention, and shows the installation state of an ejector. It is explanatory drawing which concerns on another structure of the refrigerator-freezer by Embodiment 1 of this invention, and shows the installation state of an ejector. It is explanatory drawing which concerns on another structure of the refrigerator-freezer by Embodiment 1 of this invention, and shows the installation state of an ejector. It is explanatory drawing which concerns on another structure of the refrigerator-freezer by Embodiment 1 of this invention, and shows the cross section of the ejector storage part vicinity of a housing | casing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigeration refrigerator 1a-1e Cooling room 2 Case 3 Machine room 4 Heat insulation material 5 Outer wall 6 Inner wall 7 Heat insulation material 8 Inside 9 Refrigerator door 10 Partition wall 11 Ejector 12, 12a, 12b Evaporator 15 Compressor 17 Condenser 18 Restriction Device 19 Blower 31, 32, 33, 34a, 34b Air passage 35, 36 Return air passage 40 Drive inlet portion 41 Suction inlet portion 42 Suction portion 43 Nozzle portion 44 Mixing portion 45 Diffuser portion 50 Throttle device outlet connection piping 51 Drive Flow connection piping 52 Suction flow connection piping 53 Ejector outlet connection piping 54 Evaporator outlet connection piping

Claims (5)

A compressor that discharges high-pressure refrigerant;
A condenser for condensing the refrigerant discharged from the compressor;
A throttle device for depressurizing the refrigerant condensed in the condenser;
A throttle device outlet connection pipe, one of which is connected to the outlet portion of the throttle device,
A first evaporator for connecting the other end of the expansion device outlet connection pipe to an inlet portion and evaporating the refrigerant decompressed by the expansion device;
A driving flow connection pipe branched from between the condenser and the throttle device;
A suction flow connection pipe, one of which is connected to the outlet of the first evaporator;
A driving inlet part to which the driving flow connection pipe is connected; a suction inlet part to which the other of the suction flow connection pipes is connected; and the condenser that flows from the driving inlet part through the driving flow connection pipe nozzle portion for ejecting at a high speed the condensed refrigerant by decompression, sucks the refrigerant evaporated in the first evaporator through the suction flow connection pipe from the suction inlet unit is mixed with the refrigerant jetted from the nozzle portion An ejector that comprises a mixing section, a diffuser section that increases the pressure of the refrigerant mixed in the mixing section, and that discharges the refrigerant whose pressure has increased in the diffuser section from the outlet section ;
Ejector outlet connection piping that one side connects to the outlet of this ejector,
The other of the ejector outlet connection pipe is connected to the inlet, the refrigerant from the ejector, and a second evaporator Ru evaporated in high evaporation temperature than the evaporation temperature of the first evaporator,
An evaporator outlet connection pipe for guiding the refrigerant evaporated in the second evaporator from the outlet portion of the second evaporator to the compressor ;
A refrigerant circuit having
A cooling chamber to which the internal air cooled by passing through the first evaporator and the second evaporator is supplied ;
A return air passage for returning the air in the cabinet after cooling the cooling chamber from the cooling chamber to the first evaporator and the second evaporator ,
The second evaporator is on the upstream side and the first evaporator is on the downstream side with respect to the flow of the internal air passing through the first evaporator and the second evaporator again through the return air passage. As described above, the first evaporators are arranged side by side above the second evaporator, and the passing air passes through the heat exchange with the refrigerant of the second evaporator having a high evaporation temperature first, and the air temperature Heat exchange with the refrigerant of the first evaporator having a low evaporation temperature in a state where the
In the first evaporator and the second evaporator , the flow of the internal air passing therethrough is parallel to the refrigerant flow from the inlet portion toward the outlet portion. The expansion device outlet connection pipe connected to the inlet of the evaporator is located in the lower part of the first evaporator, and the suction flow connection pipe connected to the outlet of the first evaporator is located in the upper part of the first evaporator. Then, the refrigerant flows in an upward flow through the first evaporator, and the ejector outlet connection pipe connected to the inlet portion of the second evaporator is disposed at the lower portion of the second evaporator, and the outlet of the second evaporator. the evaporator outlet connection pipe is positioned above the second evaporator, refrigerator characterized by flow Rukoto in refrigerant upward flow of the second evaporator connected to the part. Refrigerator according to claim 1, wherein the pre-Symbol ejector is characterized in that it is placed above the first heat exchanger. The ejector has a cylindrical shape and is installed in an inclined state so that the drive inlet portion is positioned above the ejector outlet portion, and the refrigerant flowing from the drive inlet portion descends in the ejector. The refrigerator-freezer according to claim 1 or 2, wherein the refrigerator is a flow . Before SL ejector refrigerator of any crab according to claim 1乃Optimum 3 the suction inlet unit is characterized that you have placed so as to be positioned above said ejector outlet portion. A plurality of the cooling chambers in a cabinet, comprising a partition wall that separates the adjacent cooling chambers;
The refrigerator-freezer according to any one of claims 1 to 4 , wherein the ejector is stored in the partition wall .

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