JPH02251074A - Refrigerating cold storage device - Google Patents

Abstract

PURPOSE:To obtain a refrigerating cold storage device, favorable in the fluctuation of an inside temperature and efficiency, without being restricted in a layout, constituting multi-temperature band, by a method wherein at least a heat dissipating heat exchanging means among second cooling means is provided in a first space at a position apart from a first cooling means. CONSTITUTION:The discharging port 25B of the cylinder chamber 25 of one of pumps, which becomes a compressor for a gas refrigerating cycle, is communicated with the suction port 26A of the cylinder chamber 26 of another pump, which becomes an expansion machine for the gas refrigerating cycle, through a heat dissipating heat exchanger 13 interposed on the way of a communicating passage 13a as a gas pipeline. On the other hand, the discharging port 26B of the cylinder chamber 26 as the expansion machine is communicated with an air discharging port 18, formed on the inside of a refrigerating chamber 11, through another communicating passage 11a as the gas pipeline and, further, is communicated with an air suction port 17, sucking air warmed by effecting heat exchange between received matters in the refrigerating chamber 11, as well as the suction port 25A of the compressor or the cylinder chamber 25 through the communicating passage 11a.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a freezing and refrigerating apparatus capable of controlling the temperature inside a plurality of refrigerators.

[Conventional technology]

Conventionally, as this type of device, as shown in Japanese Patent Application Laid-open No. 56551, etc., in contrast to the cooling pressure reducing device and cooling evaporator of the refrigeration cycle, there has been a refrigeration pressure reducing device, a refrigeration evaporator, and a refrigerant. Refrigerant refrigerant circuits with backflow prevention valve mechanisms are installed in parallel, and refrigerant alternately flows into the cooling evaporator and the refrigeration evaporator using an electrically controlled valve device. In order to obtain a sufficiently low temperature regardless of the side temperature, there is an intermittent method (hereinafter referred to as the FIR method) that configures multiple temperature zones, and a damper that directs cold air from the cooling device in one refrigerator to the other refrigerator. A damper method is generally known in which a damper is guided to form a multi-temperature zone. The above-mentioned refrigeration systems use a single refrigeration cycle to cool multiple compartments, but there are also refrigeration systems that use the Peltier effect of thermoelectric elements to independently configure multiple temperature zones (hereinafter referred to as refrigeration systems). There is also an electronic refrigeration method). For example, as shown in Japanese Patent Publication No. 62-47730, the heat radiation side of a thermoelectric element is brought into thermal contact with the evaporator of the refrigeration cycle in one refrigerator, and a cooling plate is used to cool the inside of the other refrigerator. Some thermoelectric devices configure multi-temperature zones by increasing the heat absorption effect on the heat absorption side of the thermoelectric elements that are in thermal contact with each other.

[Problem to be solved by the invention] However, with the damper type and FIR type, temperature control and temperature management are difficult due to large temperature fluctuations, and especially when the internal temperature becomes low, the refrigeration cycle cannot be operated at low load. This results in a cooling effect inside other warehouses.

The problem is that the rate drops significantly.

Furthermore, in the electronic refrigeration system, the heat absorption capacity on the heat absorption side of the thermoelectric element largely depends on the temperature on the heat radiation side, so it is difficult to increase the cooling efficiency of the thermoelectric element itself, and the cost I is also high. . There are some devices with improved cooling efficiency, such as the one shown in Japanese Patent Publication No. 62-47730, but they have the problem of being unsuitable for realizing a multi-temperature range for general purposes due to restrictions on the structure and layout. be.

The present invention has been made in view of the various problems mentioned above, and provides a freezing and refrigerating device that is advantageous in terms of internal temperature fluctuations and efficiency without being subject to layout constraints when configuring multiple temperature zones. The purpose is to

[Means to solve the problem]

In order to achieve the above object, the invention according to claim 1 includes: (a) a heat insulating box that holds at least two first and second spaces therein; (b) a heat insulating box that holds at least two first and second spaces; a first cooling means for cooling; (c) suctioning and adiabatically compressing the gas in the second space;
It has a heat radiating heat exchange means for cooling the gas whose temperature has risen due to compression, and the gas cooled by the heat radiating heat exchange means is adiabatically expanded to further lower its temperature and discharged into the second space. a second cooling means for cooling the inside of the second space, and at least the heat exchange means for heat radiation of the second cooling means is provided in the first space;
A technical measure has been adopted in which the cooling device is located away from the cooling means.

Furthermore, in the invention according to claim 2, in addition to the above configuration, a first space that detects the temperatures in the first and second spaces, respectively. a second temperature detection means, a communication means for communicating the first and second spaces, and a temperature in the second space detected by the second temperature detection means is transmitted to the first temperature detection means; The first
and communication control means for causing the first and second spaces to communicate with each other by the communication means when the temperature in the space is higher than a predetermined level.

[Function] In the invention according to claim 1, the function of the structure will be explained.

In a heat insulating box that maintains two spaces inside, the first space is cooled by a first cooling means, and the second space is cooled by a first cooling means.
The gas in the second space is sucked into the second cooling means, adiabatically compressed, expanded adiabatically, and discharged into the second space, thereby cooling the gas.

At this time, the heat generated in the compression process of the second cooling means is radiated into the first space cooled by the heat radiating means disposed within the first space.

The compressed gas is thus cooled to the temperature within the first space. Next, in order to further cool the cooled compressed gas by adiabatically expanding it, the temperature in the second space becomes lower than that in the first space.

Further, in the invention as claimed in claim 2, the effects of the configuration will be explained.

The first and second temperature detection means
If the temperature in the second space is higher than the environmental temperature in the first space by a predetermined level or more, the communication control means acts on the communication means. The first space and the second space are communicated with each other by the communication means.

〔Example〕

The present invention will be described below with reference to embodiments shown in the drawings.

FIG. 1 is an overall configuration diagram of a first embodiment in which the present invention is applied to a freezer.

In FIG. 1, when the clutch 2 of the compressor 1 is turned on and the compressor 1 is driven, the following steps occur: compressor 1 → condenser 3 → receiver 5 → expansion valve 6 → evaporator 7 → compressor 1. The refrigerant is circulated through the refrigeration cycle, and the evaporator 7 in the insulation box 9
The refrigerant evaporates, and the latent heat of evaporation causes the insulation box 9 to evaporate.
The air near the evaporator 7 inside, that is, the inside of the refrigerator compartment IO is cooled.

Furthermore, in the refrigerator compartment 10 where the evaporator 7 is located, a heat exchange means 13 for heat radiation of the gas refrigerator 14 using an air cycle is installed, and the air intake port 17 and air discharge port 18 of the gas refrigerator 14 are insulated. It opens toward the freezer compartment 11 of the box 9. Gas refrigerators produce heat by adiabatic compression of gas.
Further, it generates cold heat by adiabatically expanding gas, and includes a heat exchange means for dissipating heat and a heat exchange means for absorbing heat to be cooled by cold heat. The gas refrigerator 14 used in this embodiment is the one proposed in Japanese Patent Application Laid-open No. 6287765, in which a single gas compression reciprocating member serves to compress and expand the gas, and an endothermic heat exchanger is used. This is an extremely compact system with an open cycle that connects the gas inlet and outlet to the internal space of the refrigerator. In the second session, the structure will be explained using FIG.

In FIG. 2, reference numeral 9 denotes a heat insulating box, and the aforementioned freezer compartment 11 is constituted by a partition plate 12 made of a heat insulating material.

A set of reciprocating gas compression pumps 2o in which the gas refrigerator 14 is incorporated, its drive mechanism, and heat exchange means 1 for heat radiation
3 is disposed within the refrigerator compartment lo. As shown in FIG. 2, the heat exchange means 13 for heat dissipation has a structure in which a metal tube is wound so that the plane thereof forms a mouth shape.

One set of reciprocating gas compression pumps 2o has a structure as schematically shown in FIG. 3, which is a side sectional view thereof. 1
The housing of the gas compression pump is a hermetically sealed body formed by pasting together two plate-shaped bodies 21A and 21B made of metal or other rigid material by caulking or welding, with the inner surfaces of the plates facing each other. It is a hollow disk body with a structure, and a diaphragm 22 made of a rubber elastic plate or a bellow-shaped metal plate is incorporated as a reciprocating member for gas compression so that the inner space is divided into two in the flat direction. . 23 and 24 are reinforcing plates that sandwich the central portion of the diaphragm 22 from both sides to prevent deformation of the central portion and serve as a mounting base for the piston rod 28 to give the diaphragm 22 swing in the membrane surface direction. Both levers are fastened together by rivets or the like. 27 is a flexible joint for connecting one end of the piston rod 28 to the reinforcing plate 24, and 29 is for airtightly sealing the gap in the insertion hole of the piston rod 28 bored in the dish-shaped body 21B constituting the pump housing wall. of,
It is a bellows-shaped packing made of rubber elastic material.

As described above, the inner space of the hollow disc-shaped pump housing for one set of pumps is airtightly divided into two by the diaphragm 22 in the swinging direction of the diaphragm, and each of the independent spaces 25 and 26 is , are provided with a gas inlet 25A or 26A and a gas outlet 25B or 26B, respectively. The discharge port 25B of the cylinder chamber 25 of one of the pumps serving as the compressor of the gas refrigeration cycle is connected to a heat exchanger for heat dissipation interposed in the middle of the communication path 13a as gas piping, as shown in FIG. 13, it is connected to the suction port 26A of the cylinder chamber 26 of the other pump, which serves as the expander of the gas refrigeration cycle. Further, as shown in FIG. 2, the discharge port 26B of the cylinder chamber 26 as an expander is connected to the air discharge port 18 formed inside the freezer compartment 11 by following the communication path 11a as a gas pipe. An air intake port 17 that is open to the inside of the freezer compartment 11 and exchanges heat with the stored items inside to suck in warm air, and a cylinder chamber 25 that serves as a compressor via a communication path 11a.
The air intake port 25A is connected to the air intake port 25A.

Therefore, in this embodiment, there is an open cycle in the middle of the communication path connecting the discharge port 26B of the cylinder chamber 26 of the other pump as an expander and the suction port 25A of the cylinder chamber 25 of one pump as the compressor. A heat exchange means for absorbing heat is interposed, and the freezer compartment 11 provided in the heat insulating box 9 constitutes this opening cycle. Check valves 30 and 31 are provided at the inlet port 25A and the outlet port 25B of the cylinder chamber 25, respectively, and the inlet port 26A of the cylinder chamber 26 is provided with check valves 30 and 31, respectively.
is provided with a suction valve 32 as a differential pressure valve that is opened in response to the movement of the diaphragm 22 when the diaphragm 22 moves to the dual point, and a discharge valve 33 as a micro-pressure valve is provided in the discharge port 26B. It is being

40 is a motor for driving the piston rod 28 for swinging the diaphragm 22, 42 is a helical wheel fitted on the output shaft 41 for recovering cooling work, and 43 and 44 are a set of gears forming a crank mechanism. The piston rod 28 is reciprocated with an arbitrary circumference. 45 is the piston pin.

Next, the operation of this gas refrigerator 14 will be explained. When the power switch of the device (not shown) is turned on, the drive motor 40
starts. As the drive motor 40 rotates, the crank mechanism causes the diaphragm 22 of the gas compression pump 20 to swing at a predetermined period, so that the cylinder chamber 25 of one of the pumps acts as a gas (air in this case) compressor. and the cylinder chamber 26 of the other pump, which acts as a gas expander, undergoes compression and expansion strokes alternately. The operation of the suction valve 32 and discharge valve 33 provided in the cylinder chamber 26 is such that when the diaphragm 22 moves to the top dead center of the cylinder chamber 26, the suction valve 32 is pushed by the movement of the diaphragm 22. Open the valve. Next, while the diaphragm 22 reversely moves toward the bottom dead center, the suction valve 32, which is released from the above-mentioned pressing force, is closed by the valve closing biasing spring. When the diaphragm 22 reaches the bottom dead center, the pressure inside the cylinder chamber 26 opens and the freezing chamber 1 inside the insulation box 9 acts as an endothermic heat exchange means constituting a cycle.
Since the pressure decreases to almost the same as 1, the discharge valve 33 as a small pressure valve is opened.

Therefore, during the expansion process of one pump, the air sucked into the cylinder chamber 25 from the freezer compartment 11 becomes high temperature and high pressure in the next compression process, and is sent out from the discharge port 25B toward the heat exchanger 13 for heat radiation. . The high-pressure air cooled by the heat exchanger 13 for heat radiation flows into the cylinder chamber 26 through the opened intake valve 32 and expands adiabatically as the diaphragm 22 moves backward, thereby causing the diaphragm 22 to operate. The cold air is cooled and returned to normal pressure while recovering part of the power consumed by the cold air, and is pushed out from the opened discharge valve 33 toward the freezing compartment 11 with the next forward movement of the diaphragm 22. The inside of the freezer compartment 11 is cooled by the retained cold heat. Conversely, the incoming air, which has been warmed by being transferred with the heat retained in the freezer compartment 11, is sucked into the cylinder chamber 25 again in the suction process of one of the pumps, and thereafter, such a cycle is repeated, and the inside of the freezer compartment 11 is heated by the equipment. It is gradually cooled within the limits of its heat exchange capacity.

Therefore, in FIG. 1, the inside of the refrigerator compartment 10 is maintained at a constant temperature
When controlled to ``C'', the heat exchanger 13 of the gas refrigerator 14 in the air cycle exchanges heat with the outside air of O'C, and the temperature in the freezer compartment II is controlled by the action of the gas refrigerator 14. A temperature lower than the temperature inside the refrigerator compartment 10 (for example, -20
°C).

FIG. 4 and FIG. 5 show the temperature fluctuation range vs. temperature characteristics inside the freezing chamber 11 of the air refrigeration method of the present invention and the conventional technology (damper method, FIR method, electronic refrigeration method), respectively.

The efficiency-temperature characteristics inside the freezer compartment 11 are shown. Curve A, BC
, D indicate the characteristics of the air refrigeration method, damper method, FIR method, and electronic refrigeration method, respectively. In addition, in FIG. 4, FIG. 1, and FIG. 5, the temperature inside the refrigerator compartment 10 is set to 5=0 ('C),
The characteristics are shown when the temperature inside the freezer compartment 11 is controlled to be below S ("C).

From FIG. 4, it can be seen that in terms of temperature fluctuation range, the air refrigeration method and the electronic refrigeration method do not have much effect even if the temperature inside the freezer compartment 11 is lowered, and are superior to the other two methods. Also, from Section 5, even if the temperature inside the freezer compartment 11 is lowered, the effectiveness of the air refrigeration method does not deteriorate much, and the other 3
It can be seen that this method is superior to the other methods. From the above, it can be said that the air refrigeration method is comprehensively advantageous in terms of temperature fluctuation range and efficiency.

Now, considering the characteristics shown in FIG. 5 again, when the temperatures of the refrigerator compartment 10 and the freezing compartment 11 are close, the damper method and the FIR method are superior in efficiency. Taking the L point distribution into consideration, FIG. 6 shows an overall configuration diagram of the second embodiment. In the first embodiment,
The main body of the gas refrigerator 614, the drive mechanism, and the heat exchanger 13 for heat radiation were also arranged in the refrigerator compartment 10, but the second
In the embodiment, only the heat exchanger 13 for heat radiation is placed inside the refrigerator compartment 10, and the gas refrigerator 14 and the drive mechanism are placed outside the heat insulating box 9. Note that the heat exchanger 13 for heat radiation has a piping structure similar to the first embodiment. In addition, a blower 15 is installed and forced convection is carried out inside the refrigerator compartment 10 to create a heat exchanger 1 for heat dissipation.
It promotes the heat exchange ability of 3. Furthermore, in the freezer compartment 11, the air discharge port 18 is disposed below the air intake port 17, thereby realizing an effective cold air distribution path. Further, a damper 16 is provided on the partition plate 12. Further, 50 is a thermistor for detecting the temperature T1 in the refrigerator compartment 10, 51 is a thermistor for detecting the temperature T2 in the freezing compartment 11, and 54.55 is a relay 56 for operating the gas refrigerator 14 and the blower 15, respectively, for driving the damper 16. actuator, 57 is a pilot lamp, 58 is a power supply, 53
52 is a control device consisting of a microcomputer and the like that controls the damper 16 and the blower 15.

Next, the control of the damper 16 and the blower 15 will be explained using the flowchart of FIG. 7 showing the arithmetic processing of the control device 52. When the activation switch 53 is turned on, each electric circuit including the control device 52 is activated, and the control device 52 starts its calculation process in step 701. Step 7
At 02, the relay 54 is turned on to start the operation of the gas refrigerator 14. In the next step 703, the actuator 56
A command signal to open the head damper 16 is generated.

Therefore, the actuator 56 opens the damper 16,
Freezer compartment 11 and refrigerator compartment 10 communicate with each other. In the next step 704, the relay 55 is turned on.

Therefore, the blower 15 operates to force convection of the air in the refrigerator compartment 10 to promote heat exchange in the heat exchanger 13 for heat radiation of the gas refrigerator 14.

In the next step 705, the thermistors 50 and 5
The temperature T in the refrigerator compartment 10 and the freezer compartment II is determined by the detection signal from 1. Compare the size of T2.

When the temperature inside the freezer compartment 11 is lower than that inside the refrigerator compartment 10,
That is, when T>72, the process proceeds to step 706, in which the actuator 56 is driven to close the damper 16, and the process proceeds to the next step 707. on the other hand,
If the judgment in step 705 does not satisfy TI>T2, the damper 16 is set to the open state (step 709), and the blower 15 is set to the operating state (step 710) & then step 7
Return to 05.

In step 707, the freezer compartment l detected by the thermistor 51
It is determined whether or not the humidity temperature 2 has reached the target temperature 'r. When the temperature T2 inside the freezer compartment 11 is below the target temperature TA,
The determination in step 707 is YIE S, and in step 70B, the operation of the air blower [15 is stopped, and the process returns to step 705. On the other hand, if the determination in step 707 is NOl, that is, the inside of the freezer compartment 11 has not been cooled to the target temperature TA,
The process advances to step 711, where the blower 15 is activated, and the process returns to step 707. That is, the indoor temperatures of the refrigerator compartment 1o and the freezer compartment 11 are compared, and if the temperature in the freezer compartment II side is lower, the damper 16 is closed, and if the temperature in the freezer compartment 11 is lower than the target temperature TA, the blower 15 is closed. stops operating, and gas refrigeration 1!114 resumes steady operation.

Next, FIG. 8 is a graph showing the elapsed time from when the operating switch 53 is turned on until the temperature T2 in the freezer compartment 11 reaches the target temperature TA. In FIG. 8, curve E shows the characteristics when the damper 16 is not provided, and curve F shows the characteristics when the damper 16 is provided and the above control is performed. It can be seen from FIG. 8 that by providing the damper 16, the temperature inside the freezer compartment 11 can be quickly stabilized at the target temperature TA.

Note that in the first and second embodiments described above, the first space is the refrigerator compartment 10. The second space is the freezer compartment 11. The first cooling means is the evaporator 7 of the refrigeration cycle. The second cooling means is a gas refrigerator 14. The heat exchange means for heat radiation is a heat exchanger 13 for heat radiation. The first and second temperature detection means are thermistors 50 and 51, respectively, and the communication means is a damper 16. The communication control means is the control device 52. The predetermined level is OoC.

Note that in the second embodiment, the predetermined level is OoC, but it may be, for example, -1°C.

In addition, in the various embodiments described above, the position of the partition plate 12 may be set arbitrarily, so that the volume inside the freezer compartment 11 can be arbitrarily changed according to the shape of the stored articles.

Further, in the first embodiment, the partition plate 12 and the gas refrigerator 14 may be made detachable. This product has the advantage of being able to configure multiple temperature zones depending on the purpose of use.

Furthermore, when the present invention is used for simple multi-room temperature control for a vehicle, it can be used in conjunction with the conventional FIR method to configure multiple temperature zones from cooling and refrigeration to freezing.

- As an example, a schematic configuration diagram thereof is shown in FIG. In Fig. 7, 7 is a cooling evaporator, 7' is a refrigeration evaporator, and 19 is a cooling evaporator.
A is an electric control valve, and 19B is a check valve.

[Effect of the invention] As stated above, in the invention according to claim 1, the second
A second cooling means is used to cool the space in which the gas in the second space is adiabatically compressed and then adiabatically expanded.In this cooling process, the adiabatic compression causes the temperature to rise. The heat exchange means for heat dissipation of the second cooling means provided for cooling the gas is arranged in a first space cooled by the first cooling means at a position apart from the first cooling means. Since the first name is the same, there is an excellent effect that there are no restrictions on the layout when configuring a multi-temperature zone.

Furthermore, in the invention according to claim 2, at least when the temperature in the second space is higher than the temperature in the first space by a predetermined level or more, the second space and the first space are communicated with each other. Therefore, there is an excellent effect that the temperature in the second space can be stabilized at a target temperature lower than the temperature in the first space at an early point in time.

[Brief explanation of drawings]

Figure 1 is an overall configuration diagram showing the first embodiment of the present invention, Figure 2 is a configuration diagram of the gas refrigerator shown in Figure 1, Figure 3 is a diagram showing the structure of the gas refrigerator, and Figure 4 is a temperature FIG. 5 is a characteristic diagram of the temperature in the freezing room with a fluctuation range. FIG. 5 is a characteristic diagram of the efficiency-temperature in the freezing room. FIG. 6 is an overall configuration diagram showing the second embodiment of the present invention. FIG. 7 is a diagram showing the control device in the second embodiment. Flowchart showing control of 8th
The figure is a characteristic diagram for explaining the operation of the second embodiment, and FIG. 9 is a schematic configuration diagram showing the third embodiment of the present invention. 7... Evaporator, 13... Heat radiation heat exchanger, 14...
・Gas refrigerator, 9...Insulation box, 10...Refrigerating room, 1
DESCRIPTION OF SYMBOLS 1... Freezer room, 12... Partition plate, 15... Blower, 16... Damper, 52... Control device.

Claims (2)

[Claims] (1) (a) At least two first and second
(b) a first cooling means for cooling the inside of the first space; (c) adiabatically compressing the gas in the second space;
It has a heat radiating heat exchange means for cooling the gas whose temperature has risen due to compression, and the gas cooled by the heat radiating heat exchange means is adiabatically expanded to further lower its temperature and discharged into the second space. a second cooling means for cooling the inside of the second space, and at least the heat exchange means for heat radiation of the second cooling means is provided in the first space;
A freezing and refrigerating device characterized in that it is arranged at a location away from a cooling means. (2) first and second temperature detection means for detecting the temperatures in the first and second spaces, respectively; communication means for communicating the first and second spaces; and the second temperature detection means. The temperature in the second space detected by the means is equal to the temperature detected by the first temperature detection means.
2. The freezing and refrigerating apparatus according to claim 1, further comprising communication control means for causing the first and second spaces to communicate with each other by the communication means when the temperature in the space is higher than a predetermined level.