JPS61168765A - Refrigeration cycle device - 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 (Field of Industrial Application) The present invention relates to a refrigeration cycle device that can provide three different functions of cooling, refrigeration, and freezing with one compressor, and is suitable for use in vehicles. It is something.

(Prior art) The present applicant achieved both cooling and refrigeration effects by differentiating the evaporation pressures of the evaporator for cooling the passenger compartment and the evaporator for refrigeration, as disclosed in Japanese Unexamined Patent Publication No. 58-11370. We have previously proposed a refrigeration cycle device that does this.

(Problems to be Solved by the Invention) The above conventional devices all obtain two temperatures by changing the evaporation pressure in two evaporators, but in recent years, vehicles have also been used for leisure purposes such as camping. As a result, it has become desirable to install two evaporators, one for refrigeration and one for freezing, in a refrigerator to obtain two different cooling temperatures within the refrigerator.

SUMMARY OF THE INVENTION In view of the above, an object of the present invention is to provide a refrigeration cycle device that can independently set three temperatures suitable for cooling, refrigeration, and freezing.

(Means for Solving the Problems) In order to achieve the above object, the present invention provides (an al cooling inlet and a refrigerating/freezing inlet independently), and the air is inhaled from each of the two inlets. a compressor configured to compress refrigerant and discharge it from one discharge port; (b) a condenser configured to condense the gas and refrigerant discharged from the compressor into liquid refrigerant; c1 A cooling pressure reducing device and a cooling evaporator provided between the refrigerant outlet side of the condenser and the cooling inlet; A pressure reducing device for a refrigerator and a refrigeration evaporator provided in between, (f) an electric control valve for controlling the refrigerant flow to the refrigeration cooling unit including the refrigeration pressure reduction device and the refrigeration evaporator; and a control circuit for controlling opening and closing of an electric control valve, (hl) The cooling pressure reducing device, the refrigeration pressure reducing device, and the freezing pressure reducing device are configured so that the evaporation pressure decreases in the order of cooling, refrigeration, and freezing. Adopt technical means to do so.

(for production).

According to the above technical means, at the cooling inlet of the compressor,
The gas refrigerant that has passed through the cooling evaporator can be drawn in continuously, and the liquid refrigerant condensed in the condenser can be drawn in by repeatedly opening and closing the electric control valve at predetermined intervals using the electric output signal of the force control circuit. It can be made to flow alternately to the refrigeration evaporator and the freezing evaporator. Thereby, the evaporation pressure in each evaporator can be independently set by each pressure reducing device, and an evaporation temperature suitable for each function of cooling, refrigeration, and freezing can be obtained.

(Example) The present invention will be described below based on an example shown in the drawings. FIG. 1 shows an embodiment in which the present invention is applied to an automobile refrigeration cycle for cooling the passenger compartment and refrigerating articles. Connected to the drive shaft. In this example, the compressor 21 uses a swash plate compressor with 10 cylinders, of which nine cylinders are configured as a main compression section 21a for cooling, and the remaining one cylinder is configured as a sub-compression section 21b for refrigerating and freezing. are doing. In this case, each compressor section 21 of the compressor J1
3.21b is provided with an air-conditioning inlet 21e and a refrigerating/freezing inlet 21f independently, and each compression part 21
a and 21b can independently set different suction pressures. Further, the cooling compression section 21a and the refrigerating/freezing compression section 21b are communicated with each other by a communication path 21d, and the refrigerant (R12) having different pressures sucked from the respective suction ports 21e and 21f is transferred to the compression section 21a, 2
1b, each compression section 21a is communicated with the communication passage 21d, and after the pressure is increased to the pressure of the cooling refrigerant, each compression section 21a
, 21b, and are discharged to the outside of the compressor from a common discharge port 21c.

Next, the specific configuration of the compressor 21 will be explained with reference to FIGS. 2 and 3. A swash plate type that converts force into reciprocating motion of a piston 212 by a swash plate 211,
The swash plate 211 is keyed to the shaft 210 and rotates together with it. Rotation of swash plate 211 is transmitted to piston 212 via shoes 213 and balls 214. There are five pistons 212, and their surfaces are coated with a resin material such as Teflon. These pistons 212 are disposed to be reciprocated in the axial direction within five cylinder bores (one bore 216 is shown in FIG. 1) formed in the cylinder block 215.

Both end surfaces of the piston 212 cooperate with the cylinder bore 216 to form ten cylinders (cylinder chambers) 217, 217a, and one cylinder 2 of these ten cylinders
17a constitutes the freezing/refrigerating compression section 21b in FIG. 1, and the remaining cylinder 217 constitutes the cooling compression section 21a.

An axial hole for the shaft 21θ and a swash plate chamber 218 that accommodates the swash plate 211 are formed in the center of the cylinder block 215, and the swash plate chamber 218 communicates with the cylinder bore 216. On the other hand, an oil chamber 219 normally filled with lubricating oil is located at the bottom of the cylinder block 215.
is also formed.

An annular valve plate 220 and a suction valve 2 formed from an elastic metal plate are provided on both end surfaces of the cylinder block 215.
End plates 222 and 223 are attached via 21,
These parts 215, 220.221, 222.223
are fastened to each other by through bolts 22.4. left.

The right valve plate 220.220 has the suction boat 22
These suction boats 225 can communicate with ten cylinders 217 and 217a through suction valves 221, respectively.

Both end plates 222 and 223 have the same structure, but one end plate 222 is formed with a refrigerating/freezing inlet 21f, which is a sub-inlet, and the other end plate 223 is formed with a shaft 21.
They differ from each other in that they have a central hole 226 through which 0 rotatably passes. Both end plates 222 and 223 have a dish-like shape, and each has a substantially circular partition wall 227 on its inner surface.
．． 228 is provided to protrude in the axial direction, and these partition walls 227, 22
8 is the discharge chamber 229, and the partition wall 2
A suction chamber 231 is formed between 27, 228 and the outer peripheral wall of each end plate 222, 223. The end plate 222 has a partition wall 233 different from the partition wall 227, and this partition wall 233
It also differs from the end plate 223 in that it partitions the sub-suction chamber 234 from the suction chamber 231 (see FIG. 3). The refrigeration/freezing suction port 21f is opened in the sub suction chamber 234.

The sub-suction chamber 234 communicates with the cylinder 217a through a suction boat 225 corresponding to the cylinder 217a, while the suction chamber 231 communicates with all the remaining cylinders 217. The left and right valve plates 220, 220 are provided with five discharge ports 235 corresponding to the five cylinders, and these discharge ports 235 are opened and closed by discharge valves (not shown), and when opened, the discharge chamber 2
It connects to 29. This discharge chamber 229 is the passage 23 in FIG.
6 communicates with the discharge port 21c in FIG.

As is clear from the above description, one cylinder 217a that can communicate with the sub-suction chamber 234 constitutes the sub-compression section 21b for freezing and refrigeration, and the other nine cylinders 217 constitute the main compression section 21a for cooling. It consists of The cooling inlet 21e, which is the main inlet, is connected to the cylinder block 2 as shown in FIG.
15, and communicates with the swash plate chamber 218 by a structure described later. The swash plate chamber 218 communicates with the left and right suction chambers 231 via a passage formed by a gap between the through port 224 and the bolt hole 224a.

Therefore, the refrigerant flowing into the suction chamber 231 from the swash plate chamber 218 passes through the suction port 225 and is suctioned into all cylinders 217 except the cylinder 217a. On the other hand, the refrigerant flowing into the sub-suction chamber 234 from the refrigerating/freezing suction port 21f flows into the cylinder 2.
17a, and is sucked into this cylinder 217a, that is, the sub compression section 21b.

In order to communicate the cooling inlet 21e with the swash plate chamber 218, the cylinder bore 216 is provided with a cylinder bore 2 on the inner surface thereof.
A communication groove 237 is formed in the axial center of the cylinder bore 216 and extends circumferentially over a portion around the piston 212 within the cylinder bore 216 . This communication groove 237 opens directly into the swash plate chamber 218, and also communicates with the cooling inlet 21e via a communication hole (not shown).

Note that the discharge port 21C (Fig. 1) of the compressor 21 is provided at the upper part of the outer surface of the cylinder bore 215 in line with the cooling suction port 21e, but it is not shown in Fig. 2. . This discharge port 21c is connected to the discharge chamber 229 in the left and right ends Fi222, 223 through the passage 236 shown in FIG.
, 229.

The communication path 21d shown in FIG.
A circumferential annular groove 23 is formed on the inner peripheral surface of the cylinder 217a over the entire circumference at a position near the bottom dead center of the piston 212 in the cylinder 217a.
8, and this groove 238 is connected to the swash plate chamber 21 through a plurality of axial communication holes 239 that are formed in the circumferential wall of the cylinder 217a surrounding the piston 212 and spaced apart from each other in the circumferential direction.
8 and the communication groove 237 at all times. Therefore, the piston 212 in the cylinder 217a moves in the direction of arrow G in FIG. When the annular groove 238 in the circumferential direction is opened to the cylinder 217a when the circumferential annular groove 238 reaches the vicinity of the point, the low-pressure refrigerant for cooling will pass from the groove 237 and the swash plate chamber 218 through the annular groove 238 and the communication hole 239 forming the communication path 21d. The refrigerant then flows into the cylinder 217a and mixes with the low-pressure refrigerant for refrigeration and freezing in this cylinder. Here, if the pressure of the low-pressure refrigerant for refrigeration and freezing is 0.5 kg/the pressure of the low-pressure refrigerant for IC1 cooling is 2.5 kg/c+JG, the low-pressure refrigerant for cooling flows into the cylinder 217a through the communication path 21d. When mixed with low pressure refrigerant for refrigeration and freezing, this cylinder 21
The pressure of the refrigerant in 7a is equal to the pressure at the start of compression in the other cylinder 217 constituting the main compression section 21a, that is, 2.
It is almost equal to 5kg/c+JG. Therefore, the compression stroke in the cylinder 217a starts from almost the same pressure as the compression start pressure of the other cylinders 217, and the compressed refrigerant is discharged into the common discharge chamber 229 and joins with the refrigerant discharged from the other cylinders 217. , and is discharged toward the condenser 22 from the discharge port 21c in FIG. 1 through the passage 236.

Therefore, the refrigerant compression section 21b for refrigeration/freezing can be compressed by the piston from the same pressure state as the cooling compression section 21a. Comparatively, it saves power.

In addition to the swash plate type multi-cylinder compressor 21 as described above, a vane type compressor can also be used. In that case, if the refrigerating/freezing suction port 21f and the cooling suction port 21e are opened in order of decreasing suction pressure along the rotational direction of the rotor, the respective compression sections 21b and 21a are all connected to the highest suction pressure.
．． Compression can be started when the weight is 0 kg/cj.

As mentioned above, the compression sections 21a and 21b of the compressor 21 of this embodiment are provided with independent suction ports 210° and 21f, making it possible to independently set the suction pressure of each compression section. Become.

The discharge port 21c of the compressor 21 is connected to a condenser 22, as shown in FIG. 1, and the discharge side of the condenser 22 is connected to a receiver 23. A cooling pressure reducing device, in this example a temperature-operated expansion valve 24, and a cooling evaporator 25 connected thereto are provided on the discharge side of the receiver 23. A fan 50 for blowing air is provided. The cooling suction port 2 of the compressor 21 is connected to the refrigerant outlet side of the evaporator 25 by a cooling suction pipe 45.
1e.

On the other hand, the refrigeration cooling unit 26 is provided in parallel with the cooling expansion valve 24 and the evaporator 25. It has a refrigerating evaporator 28a connected thereto, and a check valve 29 that allows refrigerant gas to pass in only one direction toward the compressor suction side. The discharge side of the check valve 29 is connected to the refrigeration/refrigeration suction port 21f of the compressor 21 by a refrigeration/refrigeration suction pipe 46 . The constant pressure expansion valve 27 opens when its downstream pressure, that is, the pressure inside the refrigerating evaporator 28a, drops below a set pressure, for example, 1.2 kg/cliG.

A cooling unit 30 for freezing is provided in parallel with the cooling unit 26 for refrigeration.
1, a refrigeration evaporator 32a connected to this, and a check valve 33 that allows refrigerant gas to pass only in one direction toward the compressor suction side.
It has The discharge side of this check valve 33 is connected to a pipe 47.
It is connected to the refrigerating/freezing suction pipe 46 by.

Further, the constant pressure expansion valve 31 has a downstream pressure, that is, a pressure inside the refrigeration evaporator 32a, at a set pressure of, for example, 0.5 kg/cd.
When the temperature drops below G, the valve opens.

Note that a solenoid valve 48a is installed upstream of the refrigeration cooling unit 26, and when the solenoid valve 48a closes and blocks the flow of refrigerant to the refrigeration cooling unit 26,
Allows refrigerant to flow to the refrigeration cooling unit 30.

A solenoid valve 48b is provided in a communication passage 49 directly connecting the cooling suction pipe 45 and the refrigerating/freezing suction pipe 46, and when the solenoid valve 48b is opened, the suction pipes 45 and 46 are brought into communication.

Further, the refrigerating evaporator 28a is housed in a regenerator 35 filled with a regenerator 28b, and similarly, the refrigeration evaporator 32a is housed in a regenerator 36 filled with a regenerator 32b. The detailed structure will be described later.

Next, the electric circuit of the refrigeration cycle device configured as described above will be described. Reference numeral 1 denotes an on-vehicle battery, and a cooling control circuit 3 is connected to the battery 1 via a cooling switch 2.

4 is a refrigerator switch, which is connected to the battery l via the cooling switch 2;
A refrigerator control circuit 5 is connected to. 6 is a temperature sensor attached to the air blowing side of the cooling evaporator 25;
It consists 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 temperature of the blown air falls below a set temperature.The cooling control circuit 3 determines this change in resistance value, and The compressor 21 is turned off and the compressor 21 is stopped.

Reference numeral 7 denotes a temperature sensor, which is a thermistor, installed to sense the outer surface temperature of the regenerator 35 in which the refrigerating evaporator 28a is housed. Reference numeral 8 denotes a temperature sensor, which is a thermistor, installed to sense the outer surface temperature of the regenerator 36 in which the refrigerating evaporator 32 is housed. Both temperature sensors 7.8 are connected to the refrigerator control circuit 5.

Both solenoid valves 48a and 48b are connected to the refrigerator control circuit 5.
The opening and closing of the electromagnetic valves 48a and 48b are controlled by output signals from the electromagnetic valves 48a and 48b, and in this example, the electromagnetic valves 48a and 48b have a structure that closes when energized and opens when the energization is cut off. . Further, the refrigerator control circuit 5 controls the lamp, L, and
Display device such as ED9. It is designed to turn on the IO.

Refrigerating regenerator 3 housing the aforementioned refrigerating evaporator 28a
5 and a freezing regenerator 3 that houses a freezing evaporator 32a.
The refrigerator-freezer 60 according to the present invention is installed in a single refrigerator-freezer, and the structure of this refrigerator-freezer will be explained with reference to FIGS. 4 and 5. It is attached by a bracket (not shown) to the upper wall surface of the rear nap seat 72 located behind the nap seat. A door 62 is provided at the front of a case 61 of the refrigerator-freezer 60 so as to be openable and closable. The case 61 of the refrigerator-freezer 60 is a box with a so-called double wall structure using double resin members made of polyethylene or polypropylene, and hard polyurethane is used between the double walls to improve heat insulation. This is done by injecting insulation materials such as door 6
Similarly, the case 2 has a structure combining a double wall structure and a heat insulating material such as hard polyurethane, and is connected to the case 61 by a hinge (not shown) so as to be openable and closable.

The inside of the case of the refrigerator 60 is vertically partitioned by a partition plate 63 made of a hard material with excellent thermal conductivity.

The refrigerator 60 is located at the upper left side of the refrigerator interior above the partition plate 63.
A freezer 64 is installed using a double-walled resin member similar to the above, and the inside is made of a heat-insulating member injected with resin-based heat insulating material.The freezer 64 has a similar double-wall structure and a hard polyurethane material. A door 65 is connected to the door 65 by a hinge so that it can be opened and closed. A refrigerating regenerator 36, which is made of a material with excellent thermal conductivity and corrosion resistance, such as stainless steel or aluminum, and has an appropriate internal capacity is disposed at the back of the freezer 64. Inside the freezing regenerator 36, 400 g of a 19.7% eutectic solution of potassium chloride having a melting point of -11'C is sealed as a refrigerating regenerator 32b to maintain the freezing temperature for a long time. A freezing refrigerant evaporator 32a made of a copper pipe or the like bent into a meandering shape is arranged. A constant pressure expansion valve 31 is attached to the refrigerant inlet side of the freezing refrigerant evaporator 32a, and the interior of the freezer 64, excluding the freezing regenerator 36, is partitioned into upper and lower parts by a partition plate 66, and is divided into an upper part and a lower part. The space is used to store the object A to be frozen. On the other hand, on the right side of the upper chamber of the partition plate 63 mentioned above, there is a refrigerating regenerator 35 which is made of a material having excellent thermal conductivity and corrosion resistance and has an appropriate internal capacity, similar to the refrigerating regenerator 36.
is installed, and inside this refrigerating regenerator 35, 000g of hydraulic power is sealed as refrigerating regenerator material 28b, and a refrigerant evaporator 28a for refrigerating, which is bent by a pipe or the like and formed in a meandering shape, is installed. is set up. A constant pressure expansion valve 27 is provided on the refrigerant inlet side of the refrigerant evaporator 28a for refrigeration, and a check valve 29 is provided on the refrigerant outlet side. The interior of the case 61 except for the freezer 64 and the refrigerating regenerator 35 is used as a space for storing objects B to be refrigerated. Four refrigerant pipes are led out from the inside of the case 61 to the outside, and a solenoid valve 48a (shown in FIG. 1) is installed at an appropriate location outside the case 61.

Next, the operation of this embodiment in the above configuration will be explained.

Now, when the cooling switch 2 is turned on while the automobile engine is operating, current flows through the cooling control circuit 3 to the excitation coil of the electromagnetic clutch 20, and the electromagnetic clutch 20 is connected. The driving force of the engine is the compressor 2
1, the compressor 21 rotates and compresses the refrigerant gas.

In the above state, opening/closing of the refrigerator switch 4 and freezing/unfreezing of the cold storage materials 28b, 32b will be sequentially explained.

First, a case will be described in which the refrigerator switch 4 is closed and both the cold storage materials 28b and 32b are not frozen (FIG. 6(A) shows this state).

Here, the degree of freezing of the cold storage materials 28b and 32b is determined by the freezing degree of the cold storage materials 28b and 32b.
5. Experiments have shown that if the surface temperature of 36 is below -2℃ and -12℃, respectively, freezing is sufficient, so the above-mentioned -2℃ and -12℃ are respectively set in the control circuit 5. This set temperature and temperature sensor 7
．． A comparator in the control circuit 5 compares and determines whether the cool storage materials 28b and 32b are frozen or not. When the cold storage materials 28b and 32b are not frozen,
In response to the output of the comparator, the pulse generator in the control circuit 5 operates to generate a rectangular wave pulse signal shown in the lower part of FIG. Open and close (for example, open for 90 seconds and close for 60 seconds). In addition, the solenoid valve 48b receives the output of the comparator and operates as shown in FIG.
As shown in the upper part of A), the valve is always closed.

The refrigerant gas discharged from the compressor 21 is cooled and condensed by the condenser 22, and the liquefied refrigerant is stored in the receiver 23. This liquefied refrigerant is used in a temperature-operated expansion valve 2 for cooling.
4 and by the action of the constant pressure expansion valve 27 for refrigeration (when the solenoid valve 48a is open) or the constant pressure expansion valve 31 for refrigeration (when the solenoid valve 48a is closed),
It becomes a low-temperature, low-pressure gas-liquid two-phase refrigerant, and then the evaporator 25 and evaporator 28a (when the solenoid valve 48a is open)
Alternatively, it evaporates in the evaporator 32a (when the solenoid valve 48a is closed) and takes away heat from the surroundings.

The refrigerant that has passed through the cooling evaporator 25 passes through the pipe 45 and is sucked into the compressor 21 from the cooling suction port 21e.

On the other hand, the refrigerant that has passed through the refrigeration evaporator 28a is
, via the piping 46 (when the solenoid valve 48a is open)
, and the refrigerant that has passed through the freezing evaporator 32a is passed through the check valve 33.
, pipes 47 and 46 (when the solenoid valve 48a is closed), and is sucked into the compressor 21 from the refrigerating/freezing suction port 21f. Here, as described above, at the end of the suction stroke, the refrigeration and freezing compression section 21b communicates with the cooling compression section 21a through the communication passage 21d to reduce the pressure of the refrigerant that has passed through the cooling evaporator 25 (for example, 2.5 k g/ctlG)
Therefore, all cylinders of the compressor 21 compress refrigerant having a pressure of 2.5 kg/cdG.

Here, to further explain the behavior of the refrigeration cycle as the solenoid valve 48a opens and closes, when the solenoid valve 48a closes,
Since the flow of refrigerant to the refrigeration cooling unit 26 is stopped,
The pressure in the refrigerating and freezing inlet 21f decreases rapidly and reaches Q, 5 kg/cjG in a short time (1 to 2 seconds).

For this reason, the constant pressure expansion valve 31 of the refrigeration cooling unit 30
(set pressure 0.5 kg/c+aG) is opened, and refrigerant begins to flow into the refrigeration cooling unit) 30. Constant pressure expansion valve 31
Due to the action, the evaporation pressure inside the freezing evaporator 32a is 0.5
kg/c! The total temperature of IC and M becomes −21° C., and the cold storage agent 32b in the cold storage device 36 is frozen. and,
For example, when 60 seconds have passed and the solenoid valve 48a opens, the refrigerant is supplied to the refrigeration cooling unit 26, and the constant pressure expansion valve 27
(set pressure 1.2 kg/cdG), the inside of the refrigerating evaporator 28a becomes in a state of evaporation pressure 1.2 kg/aJG and evaporation temperature -1005°C, and the regenerator 2 in the regenerator 35
8b is frozen. At this time, since a check valve 33 is disposed downstream of the refrigeration evaporator 32a, the refrigerant gas passing through the refrigeration evaporator 28a rapidly increases the pressure inside the refrigeration evaporator 32a. Never. On the other hand, the constant pressure expansion valve 31 has a low pressure side pressure of 0.5 kg/c.
When the temperature rises above dG, it automatically closes, stopping the supply of refrigerant. .

Therefore, the freezing evaporator 32a continues to freeze the cold storage agent 32b while the liquid refrigerant therein gradually evaporates.

Then, when a predetermined period of time elapses, for example, 90 seconds, the solenoid valve 48
a closes again and returns to the previous state.

In this way, by opening and closing the solenoid valve 48a at predetermined intervals, for example, 90 seconds and 60 seconds, the regenerator 28b of each regenerator 35, 36
32b gradually freezes. FIG. 7 is a Mollier diagram of the refrigeration cycle according to the present invention, where 90 indicates the evaporation pressure in the cooling evaporator 25, and 91 indicates the evaporation pressure in the refrigeration evaporator 2.
The evaporation pressure at 8a is shown, and 92 is the refrigeration evaporator 32.
The evaporation pressure at a is shown.

Next, when the refrigerator switch 4 is closed and only the refrigerating regenerator 32b is sufficiently frozen, that is, when the outer surface temperature of the refrigerating regenerator 36 is 112° C. or lower (see Fig. 6). (B) shows this state). At this time, the comparator in the control circuit 5 discriminates the detection signal of the temperature sensor 8, and always cuts off the current to the solenoid valve 48a, so that the solenoid valve 48a always remains open. Also, 1m valve 48
Valve b remains closed. When the solenoid valve 48a is opened, the refrigerant stops flowing to the freezing cooling unit 1-30, and the refrigerant always flows to the refrigeration evaporator 28a, so that the refrigerant cool storage agent 2
Freezing of 8b can be promoted. Further, the control circuit 5 cuts off the power supply to the electromagnetic valve 48a, and also cuts off the power supply to the refrigeration display device 1.
0 is turned on and turned on, indicating that the freezing cold storage agent 32b has finished freezing.

Next, when the refrigerator switch 4 is closed and only the refrigerating regenerator 28b is sufficiently frozen, that is, when the surface temperature of the refrigerating regenerator 35 is -2°C or lower (sixth
Figure (c) shows this state). At this time, the two solenoid valves 48a,
48b is energized to keep both valves 48a and 48b closed at all times.

By doing this, the refrigerant can always flow through the freezing evaporator 32a to promote freezing of the freezing cold storage agent 32b. The control circuit S is such that the outer surface temperature of the refrigerating regenerator 35 is set to a set temperature (-
2° C.) or lower, the detection signal from the temperature sensor 7 is compared and determined, and the refrigeration display device 9 is turned on to indicate the completion of freezing of the refrigeration cold storage agent 28b.

Finally, when the refrigerator switch 4 is closed and both the cold storage agents 28b and 32b are sufficiently frozen, that is, the outer surface temperature of the cold storage cold storage 35 is 12 degrees Celsius or less, and the cold storage for freezing The case will be described when the outer surface temperature of the container 36 is below 112° C. or when the refrigerator switch opening 4 is open (FIG. 6(D) shows this state).

In this case, since there is no need to flow refrigerant to the refrigeration cooling unit 26 and the freezing cooling unit 30, the control circuit 5
The output signal from the output circuit 5 opens the electromagnetic valve 48b to communicate the pipes 45 and 46 via the communication path 49. Thereby, the refrigerant on the cooling side passes through the communication path 49 and the pipe 46 and also flows into the refrigerating/refrigerating compression section 21b from the suction port 21f, so that all cylinders of the compressor 21 can be used for cooling.

At this time, since check valves 29 and 33 are provided downstream of the refrigeration and freezing evaporators 28a and 32a, respectively,
The refrigerant gas that has passed through the cooling evaporator 25 flows back into the refrigeration and freezing evaporators 28a and 32a.
There is no sudden increase in the pressure inside 32a.

On the other hand, the constant pressure expansion valves 27 and 31 automatically close when the low pressure side pressure becomes higher than the set pressure of 1.2°0.5 kg/cdG, thereby stopping the supply of refrigerant. At this time, the display device 9
10 are both lit to indicate the completion of freezing of the cold storage agents 28b and 32b.

In addition, in an automobile air conditioner, the compressor 21 is controlled intermittently by various signals as is well known, but when the compressor 21 is stopped by this intermittent control, the evaporation pressure in the cooling evaporator 25 is gradually increases, but the pressure within the freezing and refrigerating evaporators 28a and 32a does not increase in the same way as above.

As described above, the refrigeration cycle is operated, the cold storage agent 28b,
By freezing 32b, the temperature inside the refrigerator is kept low by the latent heat of fusion even when the refrigeration cycle is stopped, such as when parking, and the contents can be maintained at a low temperature.

Although illustration of the specific configuration of the refrigerator control circuit 5 has been omitted in the above description, it is understood by those skilled in the art that the control circuit 5 can be easily configured by combining well-known comparators, pulse generators, logic circuits, etc. It's pretty self-evident.

The present invention is not limited to the above-described embodiments, but can be implemented in a wide variety of ways, and representative modifications will be listed below.

(1) When using a swash plate type multi-cylinder compressor 21, the number of refrigeration and freezing compression sections 21b is not limited to one cylinder, but may be increased as appropriate depending on the capacity required for the refrigerator-freezer. Of course.

(2) The period of opening and closing of the solenoid valve 48a may be changed depending on the load on the refrigerating evaporator 28a and the freezing evaporator 32a.

(3) The temperature sensor 7.8 that detects the degree of freezing of the cold storage agents 28b and 32b for freezing and refrigeration may detect the temperature inside the freezer and refrigerator, and the temperature sensor 7.8 may be used instead of a thermistor. A temperature switch using a reed switch or the like may also be used.

(4) As a pressure reducing device on the freezing and refrigeration side, the constant pressure expansion valve 27
．． In addition to 31, an ordinary temperature-operated expansion valve or a combination of a solenoid valve and a fixed throttle can be used.

(5) The cooling *Hm circuit 3 and the refrigerator control circuit 5 may be integrated, or both circuits 3.5 may be constructed using a microcomputer.

(6) The opening/closing control of the solenoid valve 48a is not based on fixed opening/closing synchronization, but rather on the degree of freezing of the cold storage agents 28b, 32b or the evaporator 2.
Control may be performed by detecting the cooling degree or evaporation pressure of 8a, 32a and automatically correcting the opening/closing period.

(7) Also, in case it is desired to rapidly cool either the refrigerator or the freezer, a manual switch may be provided to continuously open or close the solenoid valve 48a.

(8) The mounting position of the solenoid valve 48a is not limited to the illustrated position, and may be provided at any position in the refrigeration cooling unit 26 (for example, it may be provided downstream of the check valve 29).

Furthermore, the solenoid valve 48a may be of a three-way valve type.

(9) The set pressure of the constant pressure expansion valve 27.31 can be freely changed depending on the temperature at which the inside of the refrigerator is desired to be cooled, the freezing temperature of the cold storage agents 28b, 32b, etc.

Any material may be used as the Ql regenerators 28b and 32b, and the regenerator 28b is in the regenerators 35 and 36.

The method is not limited to filling the evaporator pipes 32b and immersing the evaporator piping in it, but also using a refrigerant sealed in a thin, easily deformable bag made of aluminum foil or resin.
It may also have a structure in which it is crimped onto the pipe a.

The ON evaporators 28a, 32a are not limited to those that cool the cold storage agents 28b, 32b, but can also be applied to those that directly cool the air inside the refrigerator, and in that case, it does not matter whether or not an internal fan is used.

The refrigeration cycle shown in Figure 1 has two cooling units (26.30) for refrigeration and freezing on the refrigerator side, and in parallel with these are a solenoid valve, a constant pressure expansion valve, an evaporator, and a reverse cooling unit. A cooling unit provided with a stop valve and its connecting pipe may be further added, and the number of cooling units is not limited at all.

Instead of the α1 solenoid valves 48a and 48b, it is also possible to use an electrically controlled valve that opens and closes the valve body by displacement of a piezoelectric element, or a motor-operated valve.In short, any electrically controlled valve can be used. Can be used.

(Effect of the invention) As mentioned above, according to the present invention, one compressor, one
It has the excellent effect of being able to achieve three different functions: cooling, refrigeration, and freezing, with a simple refrigeration cycle that uses two condensers in common.

[Brief explanation of the drawing]

All drawings show embodiments of the present invention, and the first
The figure is a refrigeration cycle diagram of the present invention, including an electric circuit. 2 is a vertical cross-sectional view of the compressor 21 shown in FIG. 1, FIG. 3 is a partial cross-sectional side view of FIG. The figure is a transparent perspective view of the refrigerator-freezer with the door open, and FIG. 6 is a solenoid valve 48a.
, 48b, and FIG. 7 is a Mollier diagram of the refrigeration cycle. 21...Compressor, 21C...Discharge port, 21e...
Cooling inlet, 21f...Refrigerating and freezing inlet, 22.
... Condenser, 24... Pressure reducing device for cooling, 25... Evaporator for freezing, 27... Pressure reducing device for cooling room, 28a...
Evaporator for refrigeration, vessel, 31...Reducing pressure device for refrigeration, 32a.
... Refrigeration evaporator, 48a... Electric control valve, 5...
control circuit. Figure 3 Figure 4 Figure 5 Figure 6 (A) (a) (c) (o) Figure 7, i (kca view/to 8)

Claims (1)

[Scope of Claims] (a) A cooling suction port and a refrigerating/freezing suction port are provided independently, and the refrigerant sucked from each of the two suction ports is compressed and discharged from one discharge port. (b) a condenser provided to condense gas refrigerant discharged from the compressor into liquid refrigerant; (c) a refrigerant outlet side of the condenser and the cooling inlet; (d) a refrigeration pressure reduction device and a refrigeration evaporator provided between the refrigerant outlet side of the condenser and the refrigeration/freezing inlet; and (e) a refrigeration pressure reducing device and a refrigeration evaporator provided in parallel with the refrigeration pressure reducing device and the refrigeration evaporator between the refrigerant outlet side of the condenser and the refrigeration/freezing inlet. (f) an electric control valve that controls the flow of refrigerant to the refrigeration cooling unit including the refrigeration pressure reducing device and the refrigeration evaporator; and (g) a control circuit that controls opening and closing of the electric control valve. (h) A refrigeration cycle device, characterized in that the cooling pressure reducing device, the refrigerator pressure reducing device, and the freezing pressure reducing device are configured such that the evaporation pressure decreases in the order of cooling, refrigeration, and freezing.