JPS6229877A - Refrigerator for car - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a regenerator-type refrigerator-freezer for vehicles, and is suitable for use in wagons and the like that are highly oriented for leisure purposes.

[Conventional technology]

Conventionally, as a cold storage type refrigerator for vehicles, Japanese Patent Application Laid-Open No. 59-508
As described in Publication No. 28, the cold storage material in the cold storage device (
A system has been proposed in which water, etc.) is cooled and frozen by an evaporator branched from the refrigeration cycle of a vehicle cooling system, and the frozen cold storage material is used to keep the inside of the refrigerator at a low temperature for a long time even when the vehicle is parked. ing.

[Problem that the invention seeks to solve]

However, since the above-mentioned conventional products only use a single regenerator, it is not possible to obtain the cooling effects of freezing and refrigeration, which have two different cooling temperatures (for example, -10°C and 0°C). Ta.

The present invention has been made in view of the above points, and an object of the present invention is to provide a refrigerator-freezer for a vehicle that can provide freezing and refrigeration functions with an extremely simple configuration.

Another object of the present invention is to make it possible to easily select which of the freezing function and the refrigeration function to prioritize when using a refrigerator-freezer.

[Means for solving problems]

In order to achieve the above-mentioned object, the present invention provides (al) a freezing compartment having a door that can be opened and closed; (bl) a refrigerator compartment having a door that can be opened and closed; (d) a refrigeration evaporator arranged to cool the refrigeration regenerator in the freezer compartment; and (e) a refrigeration regenerator installed in the refrigeration compartment and having a higher freezing temperature than the refrigeration regenerator. (f) a refrigeration evaporator disposed to cool the refrigeration regenerator in the refrigeration chamber; (g) a constant pressure expansion valve as a pressure reduction device for the refrigeration cycle; (h) The refrigeration evaporator is connected to the downstream side of this constant pressure expansion valve, (i) the refrigeration evaporator is connected to the downstream side of this refrigeration evaporator, and (j) the valve body of the constant pressure expansion valve is further connected to the refrigeration evaporator downstream of the constant pressure expansion valve. (k) a sealed chamber formed on one side of the pressure responsive member and filled with a gas that does not condense at room temperature; (i) a gas sealed in the sealed chamber; and (2) a manually operable control means that controls energization of the electric heating means and adjusts the set pressure of the constant pressure expansion valve. Adopt technological measures.

[Effect]

According to the above technical means, since the freezing temperature of the refrigerating cold storage body is set to a higher temperature (for example, 0°C) compared to the freezing temperature of the freezing cold storage body (for example, -11°C), both of the above-mentioned After freezing of the cold storage bodies is completed, even if the compressor of the refrigeration cycle is stopped, the freezing and refrigerating compartments can be maintained at a low temperature near the above-mentioned freezing temperature for a long time, and the freezing function and refrigeration of each cold storage body are maintained. Can perform its functions well.

Moreover, when the calorific value of the electric heating means is adjusted by the manually operable control means, the sealed gas pressure in the sealed chamber is changed, and the set pressure of the constant pressure expansion valve can be changed. If the opening set pressure of the constant pressure expansion valve is set to a low value, the refrigerant evaporation temperature will be sufficiently lower than the freezing temperature of the refrigerating regenerator, and the refrigerating capacity can be exhibited preferentially. Conversely, if the set pressure is set to a high value, the refrigerant evaporation temperature will increase, and the amount of heat exchanged by the refrigerant in the refrigeration evaporator located upstream in the refrigeration cycle will decrease significantly. The refrigerant flows into the downstream refrigeration evaporator as a liquid, allowing the refrigeration capacity to be exerted preferentially.

〔Example〕

Hereinafter, the present invention will be explained based on embodiments shown in the drawings. FIG. 1 shows an automobile refrigeration cycle for cooling a vehicle interior and refrigerating articles, and a compressor 21 is connected to a drive shaft of an automobile engine (not shown) via an electromagnetic clutch 20. In this example, the compressor 21 uses a swash plate compressor with 10 cylinders, of which 9 cylinders are configured as a compression section 21a for cooling, and the remaining 1 cylinder is configured as a compression section 21b for refrigerating. There is. In this case, each compression section 21a, 21b of the compressor 21 is independently provided with an air-conditioning suction port 21e and a refrigerating/freezing suction port 21f, and each compression section 21a, 21b independently receives different suction pressures. It is now configurable. For example, a suction pressure of 2.0 kg/csA can be set independently for the cooling suction port 21e (and 0.5 kg/csA for the refrigerating/freezing suction port 21f. The sections 21b are communicated with each other by a communication path 21d, and the refrigerants (R12) of different pressures sucked from the respective suction ports 21e and 21f are transferred to the respective compression sections 21a.

Before being compressed in 21b, each compression part 21 is communicated with the communication passage 21d, and after being raised to the pressure of the cooling refrigerant,
a, 21f, and a common discharge port 21c.
It is designed to be discharged from the compressor to the outside. Such a type of compressor 21 is known from Japanese Patent Application Laid-Open No. 60-48463, which was previously proposed by the applicant of the present invention, so a detailed explanation of its structure will be omitted.

Here, the compressor 21 can be applied not only to the swash plate type multi-cylinder type as described above but also to a vane type compressor. In that case, if the refrigerating/freezing suction port 21f1 and the cooling suction port 21e are opened in descending order of suction pressure along the rotational direction of the rotor, the respective compression sections 21b and 21a will all be at the higher suction pressure of 2.0 kg/-. It is now possible to start compression. As described above, each compression part 21a, 21b of the compressor 21 of this embodiment has an independent suction port 21e.
, 21f are provided, making it possible to independently set the suction pressure of each compression section.

A discharge port 21C of the compressor 21 is connected to a condenser 22, and a discharge side of the condenser 22 is connected to a receiver 23. On the discharge side of the receiver 23, a cooling pressure reducing device, in this example a temperature-operated expansion valve 24, and a cooling evaporator 25 connected to the discharge side of this are provided.
A cooling air blowing fan 50 is disposed on the upstream side of the air conditioner 5. The refrigerant outlet side of the evaporator 25 is connected to the cooling suction port 21e of the compressor 21 through a cooling suction pipe 45.
゛Connected.

On the other hand, a constant pressure expansion valve 2 which is a specific example of a pressure reducing device for refrigeration and freezing
7, a freezing evaporator 28 connected downstream of this constant pressure expansion valve 27, and a refrigeration evaporator 32 connected further downstream of this evaporator 28, the cooling expansion valve 24 and the evaporator 2
5 in parallel. The freezing evaporator 28 and the freezing cold storage body 29 cooled by the freezing evaporator 28 are installed in the freezing compartment 7, which will be described later.
4, and the refrigerating evaporator 32 and the refrigerating cold storage body 31 cooled by the refrigerating evaporator 32 are installed in the refrigerating compartment 75, which will be described later.
is installed inside. On the outlet side of the refrigeration evaporator 32,
A check valve 33 that allows the refrigerant gas to pass only in one direction toward the compressor suction side is connected, and the discharge side of the check valve 33 is connected to the refrigerant/freezer suction pipe 46 of the compressor 21. It is connected to the suction port 21f. Note that the constant pressure expansion valve 27 has a downstream pressure thereof, that is, the refrigeration evaporator 28.
When the pressure drops below the set pressure, for example, 9.5 kg/all, the valve opens and the downstream pressure is maintained at the set pressure.

A communication pipe 47 is provided that directly communicates between the cooling suction pipe 45 and the refrigerating/freezing suction pipe 46. This communication pipe 47 is provided with a solenoid valve 48, and when the solenoid valve is opened on the fourth day, the suction pipe 45 and 46 are in direct communication.

Next, the specific structure of the constant pressure expansion valve 27 will be explained with reference to FIGS.
The refrigerant is depressurized by passing through the gap between the valve port 273 and the valve port 273, and becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant.
It then flows to the freezing evaporator 28. On the other hand, diaphragm 2
75 is a pressure-responsive member that drives the valve body 272, and a chamber 277 formed by the diaphragm 275 and the diaphragm holder 276 contains a capillary tube 278 and an inert gas ( For example, the sealing pressure of Nt gas is transmitted. In this example, the above-mentioned chamber 277, tube 278, and expanded tube portion 279 form one sealed chamber 27a. Further, the mounting load of the coil spring 281 set by the adjusting nut 280 is transmitted to the valve body 272 and the valve receiver integrated with the plate 282.
84, further transmitted to the diaphragm 275, and
The refrigerant pressure after depressurization (that is, the refrigerant evaporation pressure of the freezing evaporator 28) is transmitted to the chamber 285 below the diaphragm 275 via a passage 286. Therefore, diaphragm 2
The sum of the mounting load of the spring 2g1 and the refrigerant pressure after pressure reduction is transmitted to the lower part of the spring 75. and diaphragm 275
The diaphragm 275 stops when the forces applied from both the upper and lower directions are balanced, and the valve body 272 comes to rest at a corresponding position.

Therefore, if the pressure of the inert gas and the force of the spring 281 are constant, the pressure of the refrigerant after depressurization is constant, but in the present invention, by additionally installing the electric heater 100 in the expanded pipe section 279, This allows the refrigerant pressure after pressure reduction to be changed.

Next, the structure of the electric heater 100 will be explained in detail with reference to FIGS. 2 and 3. The electric heater 100 is made of a nichrome wire heater in this example, and is arranged on a flat part 279a formed in an expanded pipe part 279 made of metal such as copper. The electric heater 100 has electrodes 100a and 100 on both its upper and lower surfaces.
b, and a T-shaped metal connection terminal 101 is disposed on the upper surface of the upper electrode 100a. Reference numeral 102 denotes a holder, which is made of an electrical insulator (in this example, resin), and is integrally molded with a partition plate portion 104 having a hole 103 through which the terminal 101 passes. The lower surface of this partition plate section 104 connects the electric heater 100 to the flat section 2 of the tube expansion section 279 via the base section of the connection terminal 101.
79a. electric heater 100
The lower electrode 100b is electrically grounded to the vehicle body via the expanded tube portion 279.

Reference numeral 105 denotes a curved bracket made of metal or resin with a certain degree of elasticity, and one end of which is connected to the holder 102.
Tightening is fixed by screws 106. The other end 107 of the bracket 105 is fitted into a hole 108 of the holder 102 and locked.

Chamber 10 above the partition plate portion 104 of the holder 102
The upper part of ゞ9 is open to the outside, and the connector 110
can be inserted. Therefore, the connector 110 and the connection terminal 101 can be electrically connected within the chamber 109. Connector 110 is provided at the tip of electrical wiring 111.

Next, the electric circuit of this embodiment will be explained.

In FIG. 1, l is an on-vehicle battery, and a cooling control circuit 3 is connected to this battery 1 via a cooling switch 2. In FIG. Reference numeral 4 denotes a refrigerator switch, which is connected to the battery 1 via the cooling switch 2. The refrigerator switch 4 is connected to a refrigerator control circuit 5.

Reference numeral 6 denotes a temperature sensor provided on the air outlet side of the cooling evaporator 25, which is composed of a thermistor and is connected to the cooling control circuit 3. In order to prevent the cooling evaporator 25 from freezing, this temperature sensor 6 increases its resistance value when the evaporator outlet temperature falls below the set temperature, and the cooling control circuit 3 senses this change in resistance value, and the electromagnetic clutch The power to the compressor 20 is turned off and the compressor 21 is stopped.

A temperature sensor 7 is provided to sense the surface temperature of the cool storage body 31 cooled by the refrigerating evaporator 32, and is composed of a thermistor. This temperature sensor 7 is connected to a refrigerator control circuit 5, and this refrigerator control circuit 5 is connected to the temperature sensor 7.
When the sensed temperature becomes lower than the set temperature, the electromagnetic valve 48 is cut off and opened.

In addition, when the temperature detected by the temperature sensor 7 drops to another set temperature slightly higher than the above set temperature, the control circuit 5 turns on a display device 8 such as a lamp or LED to indicate that cool storage is complete. .

This display device 8 is installed on the outer surface of a refrigerator case, which will be described later.

Reference numeral 9 denotes a freezing and refrigeration adjustment device constituting a manually operable control means, and in this example, it is composed of a dial 9a for manual operation and a variable resistor 9b whose resistance value changes by rotating the dial 9a. There is. This variable resistor 9b is connected in series with the electric heater 100.
Adjust the voltage applied to the

FIG. 4 illustrates the specific structure of the above-mentioned freezing and refrigeration adjustment device 9, in which the dial 9a is integrally connected to the rotating shaft 9C of the variable resistor 9b, and the dial 9a is configured to rotate this rotating shaft 9C. ing. 9d is a ring-shaped display plate, which is fixed to the case 9e side of the variable resistor 9b. The words "Frozen" and "Refrigerated" are printed on the top surface of the display board 9d, and the indication line 9f of the dial 9a corresponds to "Frozen" on the display board 9d.
When located on the "refrigeration" side 9g, the refrigeration capacity is preferentially exhibited, as will be described later, and conversely, when it is located on the "refrigeration" side 9h, the refrigeration capacity is preferentially exhibited.

Next, the above-mentioned freezing evaporator 28 and refrigeration evaporator 3 are
The specific structure of the vehicle refrigerator-freezer having the following will be described. 5 and 6 illustrate the specific structure of a refrigerator-freezer for a vehicle, and the refrigerator-freezer 6 in this example
0 is made of polyethylene or polypropylene, etc. 2
It has a case 62 with a so-called double wall structure using a heavy resin member 61. Furthermore, a heat insulating material 63 such as hard polyurethane is injected between the double wall structures to improve heat insulation properties. The refrigerator-freezer 60 has a freezer door 68 and a refrigerator door 69 that are made of a double-walled resin member 64, 65 and a heat insulating material 66, 67 such as hard polyurethane, similar to the case 61, and have hinges 70, A rubber member (not shown) containing a built-in magnet is fixed to the periphery of the upper end surface of the case 62, and this rubber member is attached to the door 68. .69 is securely attracted and fixed by magnetic force to an iron plate (not shown) fixed around the periphery.

The interior of the case 62 is partitioned into a freezer compartment 74 and a refrigerator compartment 75 by a flat partition member 73 having the same insulation structure as the case 62. The lower end of this partition member 73 is fitted into the groove 76 of the case 62, while the upper end is pressed and held by the central cover 72. The center cover 72 is fixed to the case 62 while pressing the upper end of the partition member 73 by screwing screws (not shown) into mounting holes 77 (FIG. 6) provided on the upper end surface of the case 62. .

As shown in FIG. 6, the constant pressure expansion valve 27 and the check valve 33 are both disposed within the case 62, and the refrigeration evaporator 28 connected to the downstream side of the constant pressure expansion valve 27 is As shown in the figure, it is composed of a meandering piping 28a having a round cross section, and this piping 28a is arranged along the inner surface of the case 62 so as to surround the periphery of the freezing chamber 74. The refrigerating evaporator 32 is also constructed from a similar piping 32a, and the piping 32a is also arranged along the inner surface of the case 62 so as to surround the periphery of the refrigerating chamber 75. Therefore, case 6
As schematically shown in FIG. 7, piping 28a or 32a is disposed on all four inner surfaces of 2. Piping 2
8a and 32a are made of a material such as copper or aluminum.

A refrigeration regenerator 29 is disposed inside the meandering pipe 28a of the refrigerating evaporator 28 so as to be in close contact with the meandering pipe 28a. A large number of bags with cold storage material sealed inside the bag (
For example, 5 cold storage packs are arranged side by side. As the cold storage material of the freezing cold storage body 29, for example, a 19.7% potassium chloride eutectic solution having a eutectic point (freezing temperature) of -11° C. is used.

Furthermore, a refrigerating regenerator 31 is disposed in close contact with the inside of the pipe 32a of the refrigerating evaporator 32, and this refrigerant regenerator 31 also has a large number of regenerator punctures arranged side by side in the same way as the refrigerant regenerator 29 described above. However, since water is used as the cold storage material of the cold storage body 31, its freezing point is 0°C.

After arranging the evaporator 28.32 and the cold storage body 29°31 as described above, a cooling plate 78.79 made of a metal with excellent thermal conductivity such as aluminum or stainless steel is placed further inside the cold storage body 29.31. It is disposed in close contact with the cool storage body 29°31. As shown in FIG. 5, the cooling plate 78 for refrigeration is formed into a box-like shape with only the upper surface open, and the portion near the upper end is connected to the case 62 and the partition member 7 by screws 80.
3, the tightening is fixed. In addition, a cooling plate 79 for refrigeration
is formed in the shape of an opening with the upper and lower surfaces open, and a portion near the upper end thereof is fastened to the case 62 and the partition member 73 by screws 80.

The temperature sensor 7 that detects the temperature of the refrigerating regenerator 31 described above is connected to the refrigerant regenerator 31 and the cooling plate 79 located at the most downstream part of the piping 32a of the refrigerating evaporator 32, as shown in FIG. It is tightly fixed between.

Next, the operation of this embodiment will be explained. FIG. 8 is a Moller diagram of a refrigeration cycle, and the cycle indicated by the solid line 90 in the figure is
The operating characteristics of the refrigeration cycle for cooling are shown, and the dashed line 91
shows the operating characteristics of a refrigeration cycle for freezing and refrigeration.

When the cooling switch 2 is turned on, power is supplied to the cooling control circuit 3. However, when the cooling starts, the temperature of the air blown from the cooling evaporator 25 is higher than the set temperature (for example, 3°C), so the control circuit 3 turns on the temperature sensor 6. The detection signal is compared with the reference signal, and a "Hi" level output is output to energize the electromagnetic clutch 20. Then, the electromagnetic clutch 20 becomes connected, and the driving force of the automobile engine is transmitted to the compressor 21.
The compressor 21 rotates and compresses refrigerant gas.

In the above state, when the operation switch 4 of the refrigerator-freezer 60 is further turned on, power is supplied to the control circuit 5, but at the time of starting, the surface temperature of the refrigerating cold storage body 31 is set to the set temperature (for example, -3
℃), the control diagram B5 compares the detection signal of the temperature sensor 7 with the reference signal, outputs a "Hi" level output, and energizes the solenoid valve 48, so the solenoid valve 48 remains closed. Also, since a Lo level output is given to the display device 8, the display device 8 remains off. Since the electromagnetic valve 48 is closed, the cooling refrigerant from the cooling suction pipe 45 flows into the main suction port 21e of the compressor 21, and the refrigerant refrigerant from the refrigerating and freezing suction pipe 46 flows into the sub-compressor 21. They are each independently sucked into the suction ports 21f.

Here, as described above, the refrigerating/freezing compression section 21b of the compressor 21 is connected to the communication path 21b at the end of the suction stroke (near the top dead center).
1d to the cooling compression section 21a, the pressure inside the refrigerating and freezing compression section 21b is equal to that of the cooling compression section 21.
Due to the inflow of refrigerant from a, the pressure rises to the same pressure as on the cooling side, that is, 2.0 kg/cnl (P6-P3 in Fig. 8). Therefore, both compression parts 21a and 21b are 2.0
kg/cfl! Compress the refrigerant at a pressure of (Pz-P in Figure 8)
4) Do. This compressed refrigerant gas is mixed together and discharged from the discharge port 21c, and cooled (
P4''PI in FIG. 8).

This liquefied refrigerant is stored in the receiver 23, and the constant pressure expansion valve 2
7 and temperature-activated expansion valve 24 to reduce the pressure (PI
−'PS and P, →P2), then the evaporator 28.3
2 and 25 (P, -P, and pz -P3'), respectively. Here, 21 points represent the state of the high-pressure refrigerant on the inlet side of the temperature-activated expansion valve 24, P2 represents the state of the refrigerant on the discharge side of the expansion valve 24, and P3 represents the state of the refrigerant on the discharge side of the cooling compression section 21a. 21e represents the state of the refrigerant, and P4 represents the state of the refrigerant at the discharge port 2'lc. In the refrigeration/freezing cycle, the setting pressure of the constant pressure expansion valve 27 is appropriately set by the freezing/refrigeration adjustment device 9, so that the state of the refrigerant downstream of the constant pressure expansion valve 27 is set to P.

Specifically, when the dial 9a is rotated so that the indication line 9f of the dial 9a of the device 9 and the intermediate indication line 91 of the display board 9d match, the electric heater 100 is adjusted by the resistance value of the variable resistor 9b. The calorific value is adjusted to a predetermined value, and thereby the pressure of the inert gas sealed in the chamber 277, the capillary tube 278, and the tube expansion part 279 is also adjusted to a predetermined value, and the opening set pressure of the constant pressure expansion valve 27 is adjusted. For example 0.
It is set at 5 kg/cal. And constant pressure expansion valve 27
The evaporation pressure of evaporator 28.32 is 0.5 kg due to the action of
/cnl. As described above, by maintaining the evaporation pressure in the evaporator 28.32 for freezing and refrigerating at 0°5 kg/c+d, the refrigerant evaporation temperature is maintained at -21°C,
It is possible to perform refrigeration and freezing actions.

Here, to explain the refrigeration and freezing effects in detail, the first
In the refrigeration cycle shown in the figure, the refrigeration evaporator 32 is connected in series downstream of the refrigeration evaporator 28, so the constant pressure expansion valve 2
0.5 kg/cJA (evaporation temperature -210) by 7
The low-temperature refrigerant, which has been reduced in pressure to a pressure of Therefore, at first, the evaporated gas refrigerant flows into the refrigeration evaporator 32, so that the degree of cooling of the refrigeration regenerator 31 is small.

When cooling of the freezing cold storage body 29 progresses with the passage of time and the temperature drops to the eutectic point of the cold storage material (for example, −11° C.), freezing of the freezing cold storage body 29 starts. At that time, the cold storage bodies 29 located on the refrigerant inlet side of the pipe 28a of the freezing evaporator 28 are frozen sequentially, and the cold storage bodies 29 on the refrigerant outlet side are frozen.
9 is completed, the difference between the refrigerant evaporation temperature and the temperature of the cold storage body 29 becomes minute, so the amount of heat absorbed by the refrigerant in the freezing evaporator 28 is extremely reduced. It does not evaporate and flows into the refrigeration evaporator 32 in a gas-liquid two-phase state, thereby cooling the refrigeration cold storage body 31. As a result, the temperature of the cold storage body 31 for refrigeration decreases to 0° C. or lower, and freezing of the cold storage material (water) in the cold storage body 31 is started.

Also in this case, the cold storage bodies 31 located on the refrigerant inlet side of the piping 32a of the refrigerating evaporator 32 are frozen in order, and the cold storage bodies 31 on the refrigerant outlet side are frozen last. When the cold storage body 31 on the refrigerant outlet side has completely frozen and the surface temperature of the cold storage body 31 drops to a set temperature, for example, -3°C, the control circuit 5 determines the detection signal of the temperature sensor 7 and displays the In device 8 “
Since a Hi'' level output is given, the display device 8 lights up to indicate the completion of freezing (cool storage) of the cool storage bodies 29 and 31.

When the surface temperature of the refrigerant regenerator 31 on the refrigerant outlet side drops to another set temperature, for example -5°C, which is lower than the above set temperature, the control circuit 5 determines the detection signal of the temperature sensor 7, and the solenoid valve A "Lo" level output is applied to the solenoid valve 48 to open the solenoid valve 48. Then, the communication pipe 47 is opened, so that the refrigerant on the cooling side flows into the refrigerating and freezing suction port 21f of the compressor 21 via the communication pipe 47. As a result, the pressure inside the refrigerating and freezing suction pipe 46 is
Since the refrigerant pressure on the cooling side increases to (2.0 kg/cffl), the constant pressure expansion valve 27 remains closed from then on, and all cylinders of the compressor 21 are used for cooling. Note that the check valve 33 prevents the refrigerant on the cooling side from flowing back into the evaporator 28, 32 for freezing and refrigerating.
．． The inside of 32 remains at a low temperature for a while.

Note that the temperature at which the display device 8 is turned on (for example, -3°C
) to open the solenoid valve 48 (e.g. -5°C
) is set lower in order to prevent a problem in which the surface temperature of the cool storage body 31 rises in a short time due to the opening of the electromagnetic valve 48 and the display device 8 returns to the unlit state.

As mentioned above, the freezing cold storage body 29 and the refrigeration cold storage body 31
When the freezing is completed, the vehicle engine stops like when parking, and even if the compressor 21 stops, the inside of the freezer compartment 74 and the refrigerator compartment 75 will be kept for a long time (for example, if the amount of cold storage material for freezing is 700g)
(about 3 hours) can be maintained at a low temperature near the freezing temperature of the cold storage material.

The above operation explanation is based on the dial 9a of the refrigeration adjustment device W9.
is rotated to the position of the intermediate indicator line 91 on the display board 9d (normal operation mode), but when starting the refrigerator-freezer 60, if you want to preferentially cool the freezer compartment 74 side,
In other words, when setting the freezing priority mode, the above device 9
Rotate the dial 9a to the position of the refrigeration side indication line 9g on the display board 9d. As a result, the resistance value of the variable resistor 9b increases, and the voltage applied to the electric heater 100 decreases.
Since the amount of heat generated by the electric heater 100 decreases, the temperature of the enclosed inert gas decreases. Here, in the law of pv=nRT, since the temperature T decreases under the condition that the volume V is constant, the sealing pressure P of the inert gas decreases. On the other hand, in the constant pressure expansion valve 27, the above-mentioned sealing pressure and the spring 281
Since the zero force and the sum of the refrigerant pressure after depressurization are kept in balance, and the force of the spring 281 remains unchanged, the diaphragm 275 is pressed upward in FIG. The degree of opening of the body 272 is reduced, whereby the refrigerant pressure after depressurization becomes low (for example, 0.3 kg/co) and balance is maintained again.

Since the refrigerant evaporation temperature at the above-mentioned refrigerant pressure of 0.3 kg/ctA is -24°C, the temperature difference between the freezing regenerator 29 and cold chamber 74 and the freezing evaporator 28 becomes large. The cooling capacity (cool-down performance) is increased, and the inside of the freezing cold storage body 29 and the freezer compartment 74 can be quickly cooled.

However, due to the characteristics of the compressor 1, if the suction pressure, that is, the refrigerant pressure after depressurization, decreases, the refrigerant gas specific weight decreases and the circulating refrigerant weight decreases, so the refrigerant is almost evaporated in the freezing evaporator 28. The refrigeration evaporator 32
cooling capacity decreases.

On the other hand, when setting the refrigeration priority mode, the dial 9a of the device 9 is rotated to the position of the refrigeration side indication line 9h on the display board 9d. As a result, the resistance value of the variable resistor 9b decreases, the voltage applied to the electric heater 100 increases, and the amount of heat generated by the electric heater 100 increases, so that the temperature T of the inert gas increases. Therefore, the pressure P of the inert gas increases, the valve opening of the constant pressure expansion valve 27 increases, the set pressure increases to, for example, 1.2 kg/cffl, and the refrigerant evaporation temperature increases to 110°C. , Refrigerating cold storage body 29
(-11°C), and the amount of heat exchanged by the refrigerant on the freezing side decreases. Moreover, since the weight of the circulating refrigerant also increases at this time, a considerable amount of the refrigerant flows into the downstream refrigerating evaporator 32 in a liquid state, and the refrigerating capacity can be exerted preferentially.

In addition, in the above-mentioned embodiment, the cold storage body 29.31
A bag with a cold storage material sealed inside it is used, and this is placed in close contact with the evaporator 28, 32 for freezing and refrigerating.
Of course, the present invention can also be implemented in a similar manner even if the structure is such that a cold storage material and an evaporator for freezing and refrigeration are respectively enclosed in a metal cold storage container for freezing and refrigeration.

In addition, as the electric heater 100, a thermoelectric element is used instead of the nichrome wire, and the inert gas is heated with this thermoelectric element.
Alternatively, the set pressure of the constant pressure expansion valve 27 may be adjusted within a wide range by cooling.

In addition, the configuration of the refrigeration cycle uses a compressor 21 having two suction ports 216.21f as shown in FIG.
In addition to the system that allows refrigerant to flow continuously between the cooling side and the freezer/refrigerator side, as shown in Japanese Patent Laid-Open No. 59-50828, a solenoid valve is intermittently opened and closed to flow the refrigerant between the cooling side and the freezer/refrigerator side. The structure may be changed to one in which the refrigerant is intermittently circulated.

Further, as the gas sealed in the sealed chamber extending from the chamber 277 above the diaphragm 275 to the expanded pipe portion 279, other than an inert gas may be used as long as it does not condense at room temperature.

〔Effect of the invention〕

As described above, according to the present invention, even after the refrigeration cycle is stopped, the two-temperature cold preservation function of freezing and refrigeration can be performed with a relatively simple configuration.

Furthermore, when starting up the refrigerator, it is possible to easily manually select whether to prioritize the freezing function or the refrigeration function.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a diagram of a refrigeration cycle of the present invention, including an electric circuit. FIG. 2 is a detailed vertical cross-sectional view of the constant pressure expansion valve 27 shown in FIG. 1, and FIG.
4 is an exploded perspective view of the adjustment device 9 that adjusts the set pressure of the constant pressure expansion valve 27. FIG. 5 is a longitudinal sectional view of the refrigerator-freezer with the door open. Figure 6 is a partially cutaway perspective view of Figure 5 with the door section removed;
FIG. 7 is a schematic perspective view showing the form of piping of an evaporator in a refrigerator-freezer, and FIG. 8 is a Mollier diagram of a refrigeration cycle. 21... Compressor, 27... Constant pressure expansion valve, 27a...
- Sealed room, 28... Evaporator for freezing, 29... Cold storage body for freezing. 31... Cold storage body for refrigeration, 32... Evaporator for refrigeration, 6
4゜65...Door, 74...Freezing room, 75...Refrigerating room, 100...Electric heater, 272...Valve body, 2
75...Diaphragm (pressure responsive member), 277.2
78,279... A chamber forming a sealed chamber, a capillary tube. Pipe expansion section, 9... A freezing and refrigeration adjustment device constituting a control means. Representative Patent Attorney Takashi Okabe Figure 2 Figure 3 a So○ Figure 4

Claims (1)

[Scope of Claims] (a) A freezing compartment having a door that can be opened and closed; (b) A refrigerator compartment having a door that can be opened and closed; (c) A cold storage body for freezing installed in the freezing compartment; (d)
) a refrigeration evaporator arranged to cool the refrigeration regenerator in the freezer compartment; (e) a refrigeration regenerator installed in the refrigeration compartment and having a higher freezing temperature than the refrigeration regenerator; , (f) a refrigeration evaporator arranged to cool the refrigeration regenerator in the refrigeration chamber, (g) a constant pressure expansion valve as a pressure reduction device for the refrigeration cycle, and (h) the constant pressure. Connecting the refrigeration evaporator to the downstream side of the expansion valve, (i) connecting the refrigeration evaporator to the downstream side of the refrigeration evaporator, and (j) further driving the valve body of the constant pressure expansion valve. (k) a sealed chamber formed on one side of the pressure responsive member and filled with a gas that does not condense at room temperature; (l) heating the sealed gas in the sealed chamber; (m) manually operable control means for controlling energization of the electric heating means and adjusting the set pressure of the constant pressure expansion valve. A refrigerator-freezer for vehicles.