JPH08327169A - Refrigerating equipment - Google Patents

Abstract

PURPOSE: To obtain a refrigerating cycle with a cool storage function which enables efficient execution of a refrigerating operation and a cool storage operation while reducing the cost of a product, by connecting a refrigerant evaporator for refrigeration in series to the downstream side of a refrigerant evaporator for cool storage. CONSTITUTION: A cool storage medium having a melting point of about the same degree as the evaporating temperature (e.g. -25 deg.C) of a refrigerant of a refrigerant evaporator 15 for refrigeration at the time when a refrigerator temperature inside a refrigerator reaches a first prescribed temperature (e.g. -20 deg.C) at which a refrigerating operation is switched over to a cool storage operation is provided in a cool storage pack 5 covering the circumference of a round type tube 25 of a refrigerant evaporator 14 for cool storage. At the time of the refrigerating operation wherein refrigeration in the refrigerator is conducted, the cool storage medium is not brought to a state of freeze and a load on the cool storage medium does not become large. At the time of the cool storage operation wherein only the operation of a refrigerator fan 31 is stopped and the cool storage is made in the cool storage medium is conducted, a temperature difference between the temperature of the cool storage medium and the evaporating temperature of the refrigerant in the refrigerant evaporator 14 for cool storage is brought about properly by a restricting operation of a thermal automatic expansion valve 13.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating apparatus having a cool storage refrigerant evaporator and a refrigerating refrigerant evaporator filled with a cool storage agent, for cooling air in an adiabatic warehouse.

[0002]

2. Description of the Related Art Conventionally, in JP-A-64-6654, as shown in FIG.
1, a refrigerating apparatus for a refrigerating vehicle having a cold storage function (hereinafter, referred to as a conventional example) including an outside air blower 102 and an inside air blower 103 has been proposed. The refrigeration cycle 101 includes the refrigerant compressor 1
04, refrigerant condenser 105, automatic temperature expansion valve 106, 10
7. Refrigerant evaporator 108 for refrigeration, Refrigerant evaporator 109 for cold storage
Further, a gas-liquid separator (accumulator) 110 is connected. The automatic temperature expansion valves 106 and 107 have temperature sensitive tubes 111 and 112 for detecting the refrigerant temperatures at the outlets of the refrigerant evaporators 108 and 109 for freezing and cold storage, capillary tubes, diaphragms, and the like. Further, a liquid receiver (receiver) 115 is connected between the refrigerant condenser 105 and the temperature automatic expansion valves 106 and 107.

In this conventional example, a refrigerant evaporator for refrigeration 108 and a refrigerant evaporator for cold storage 109 are connected in parallel, and two refrigerant refrigerant evaporators 108, 109 for refrigeration and cold storage are respectively installed on the upstream side. The freezing operation and the cold storage operation are performed by the intermittent operation by repeatedly opening and closing the two switching valves 113 and 114. As a result, the cold storage agent filled in the cold storage refrigerant evaporator 109 is melted even when the engine is stopped or the traffic congestion operation is performed, so that the inside of the freezer is kept at a low temperature.

[0004]

However, in the conventional example, it is possible to efficiently operate the freezing operation and the cold storage operation by repeating the opening and closing of the two switching valves 113 and 114. Since the refrigerant evaporator for refrigeration 108 and the refrigerant evaporator for cold storage 109 are connected in parallel, they are used for the refrigeration cycle like the temperature automatic expansion valve 106 or the temperature automatic expansion valve 107, or the two switching valves 113 and 114. The increase in the number of parts of the auxiliary equipment causes a problem that the product cost increases.

In the conventional example, during cold storage operation,
Since the cold storage agent melts from the outside where it easily contacts the air convection in the freezer, the inside cold storage agent near the pipe (tube) of the cold storage refrigerant evaporator 109 is difficult to melt, and the latent heat of fusion of the inside cold storage agent The problem is that it is not being used effectively.

An object of the invention described in claims 1 to 3 is to provide a refrigerating apparatus capable of efficiently operating a refrigerating operation and a cold accumulating operation and reducing the product cost. An object of the invention according to claim 4 is to provide a refrigeration cycle in which a cold storage refrigerant evaporator and a refrigeration refrigerant evaporator are connected in series, and a refrigeration that can prevent the cold storage agent from melting during defrosting operation. To provide a device.

An object of the invention described in claim 5 is to provide a refrigerating apparatus capable of efficiently performing cold storage operation without impairing the cooldown performance. An object of the invention described in claim 6 is to provide a refrigerating apparatus capable of suppressing deterioration of cold insulation performance by a resin container by improving heat absorption performance of a refrigerant flowing in a tube of a refrigerant storage refrigerant evaporator. It is an object of the invention as set forth in claim 7 to provide a refrigerating apparatus capable of improving the cooling performance in the adiabatic storage in the initial stage of the freezing operation after the cold storage operation. Another object of the present invention is to provide a refrigerating apparatus that can effectively utilize latent heat of fusion of the regenerator agent in the vicinity of the regenerator refrigerant evaporator.

[0008]

According to a first aspect of the present invention, there is provided an adiabatic chamber provided with heat insulation from the outside, an air blowing unit for convection air in the adiabatic chamber, and an inside of the adiabatic chamber. A cool storage agent for keeping cold, a cool storage refrigerant evaporator for cooling the cool storage agent, for refrigeration connected in series to the cool storage refrigerant evaporator, and cooling air convection in the adiabatic storage by the operation of the internal ventilation unit. A refrigerant evaporator, and a refrigerating cycle having a temperature automatic expansion valve that is connected in series to the refrigerating refrigerant evaporator and has a temperature automatic expansion valve that adjusts the circulation amount of the refrigerant based on the temperature change of the refrigerant at the outlet of the refrigerating refrigerant evaporator, A freezing operation of freezing the inside of the adiabatic warehouse by the refrigerating refrigerant evaporator by operating the in-compartment air blowing means and stopping the operation of the in-compartment air blowing means and freezing the regenerator by the cold storage refrigerant evaporator. And a control means for performing cold storage operation It adopted the technical means.

According to a second aspect of the present invention, in addition to the refrigerating apparatus according to the first aspect, the control means has an in-compartment temperature detecting means for detecting an in-compartment temperature in the adiabatic chamber, and It is characterized in that the operation of the in-compartment air blowing means is stopped when the in-compartment temperature in the adiabatic warehouse detected by the in-compartment temperature detecting means falls below a predetermined temperature. The invention according to claim 3 is
In addition to the refrigerating apparatus according to claim 2, the cold storage agent has a freezing point that is about the same as the evaporation temperature of the refrigerant in the refrigerant evaporator for refrigeration when the internal temperature of the heat insulation chamber drops below a predetermined temperature. It is characterized by having.

According to a fourth aspect of the present invention, in addition to the refrigerating apparatus according to any one of the first to third aspects, the refrigeration cycle includes a refrigerant compressor, a refrigerant condenser, the temperature automatic expansion valve, The cold storage refrigerant evaporator and the freezing refrigerant evaporator are sequentially connected along the flow direction of the refrigerant, the refrigerant discharged from the refrigerant compressor, the refrigerant condenser, the temperature automatic expansion valve, the A first refrigerant flow path that flows into the freezing refrigerant evaporator via the cold storage refrigerant evaporator, the refrigerant discharged from the refrigerant compressor, bypasses the temperature automatic expansion valve, the cold storage refrigerant evaporator, and It is characterized by having a second refrigerant flow path for flowing into the refrigerating refrigerant evaporator, and a refrigerant flow path switching means for switching between the first refrigerant flow path and the second refrigerant flow path.

According to a fifth aspect of the present invention, in addition to the refrigerating apparatus according to any one of the first to fourth aspects, the refrigerating cycle has a first throttle portion that adiabatically expands the refrigerant only during low load operation. And the temperature automatic expansion valve has the first
A second throttle portion provided downstream of the throttle portion for adiabatically expanding the refrigerant, a refrigerant temperature detecting means for detecting the refrigerant temperature at the outlet of the refrigerating refrigerant evaporator, and a refrigerant temperature detected by the refrigerant temperature detecting means. According to the above, a throttle valve for adjusting the opening degree of the second throttle portion is provided.

According to a sixth aspect of the present invention, in addition to the refrigerating apparatus according to any one of the first to fifth aspects, the cold-storage refrigerant evaporator has a refrigerant for cooling the cold-storage agent inside. A flowing refrigerant flow pipe, and a resin container that covers the periphery of the upper portion of the refrigerant flow pipe with the lower portion of the refrigerant flow pipe projecting downward and that has a regenerator enclosed therein Is characterized by.

According to a seventh aspect of the present invention, in addition to the refrigerating apparatus according to any one of the first to sixth aspects, the control means detects the temperature inside the adiabatic chamber. When the temperature inside the adiabatic chamber detected by the chamber temperature detection unit rises to a predetermined temperature higher than a set temperature or higher, the amount of air blown by the air blower in the chamber is higher than that in a steady state. It is characterized in that it is increased.

[0014]

According to the first aspect of the present invention, when the refrigeration cycle is operated and the air in the adiabatic chamber is forcibly convected through the refrigerating refrigerant evaporator by the operation of the internal air blowing means,
That is, during the refrigeration operation, the refrigerant flowing from the temperature automatic expansion valve in the refrigeration refrigerant evaporator and the air convection in the heat insulation chamber exchange heat with each other, whereby the air convection in the heat insulation chamber is cooled and the inside of the heat insulation chamber is cooled. Is frozen. At this time, the cold storage agent is cooled by heat exchange between the cold storage refrigerant evaporator and the cold storage agent that has flowed in from the temperature automatic expansion valve.

Further, when the refrigeration cycle is operated, the operation of the in-compartment air-blowing means is stopped, and there is no convection of air in the adiabatic warehouse,
That is, during the cold storage operation, heat is not exchanged so much in the refrigeration refrigerant evaporator, and the temperature automatic expansion valve reduces the circulation amount of the refrigerant, so that the evaporation temperature of the refrigerant in the cold storage refrigerant evaporator decreases. As a result, the cold storage agent is further cooled and reaches a frozen state. Further, when the operation of the refrigeration cycle is stopped, the operation of the air blower in the refrigerator is stopped, and there is no convection of the air in the heat insulation warehouse, the cold storage agent is melted, so that the heat insulation interior is kept cool and the heat insulation interior is closed. Maintained at low temperature.

According to the fourth aspect of the present invention, when the defrosting operation is performed, the refrigerant passage switching means switches the first refrigerant passage to the second refrigerant passage. Since the cold storage refrigerant evaporator is connected to the freezing refrigerant evaporator in the upstream side in the flow direction of the refrigerant, the high temperature refrigerant discharged from the refrigerant compressor causes the temperature automatic expansion valve and the cold storage refrigerant evaporator to operate. It becomes possible to flow into the refrigerant evaporator for refrigeration without passing through. As a result, it is possible to prevent the regenerator stored in the regenerator evaporator from melting during the defrosting operation.

According to the fifth aspect of the present invention, during high load operation, that is, during cool down (freezing operation), the refrigerant is not adiabatically expanded in the first throttle portion and reaches the second throttle portion as liquid refrigerant. . Then, the liquid refrigerant adiabatically expands when passing through the second throttle portion. Further, during high load operation, the refrigerant temperature at the outlet of the refrigerating refrigerant evaporator rises, so that the throttle valve widens the opening degree of the second throttle portion in accordance with the refrigerant temperature detected by the refrigerant temperature detecting means, thereby refrigeration. The circulation amount of the refrigerant in the cycle increases. As a result, a sufficient amount of circulation of the refrigerant corresponding to high load operation can be obtained, and the refrigerant becomes a gas refrigerant having a superheat degree at the outlet of the refrigerant evaporator for refrigeration, and the air inside the adiabatic warehouse is efficiently frozen. It

Further, during the low load operation, that is, during the cold storage operation, the refrigerant temperature at the outlet of the refrigerating refrigerant evaporator decreases, so that the throttle valve is set to the second throttle portion according to the refrigerant temperature detected by the refrigerant temperature detecting means. The opening can be narrowed. Then, when the refrigerant passes through the first throttle portion, it is adiabatically expanded and becomes a refrigerant in a gas-liquid two-phase state. For this reason, even if the amount of circulation of the same refrigerant is the same, the refrigerant flowing into the second throttle portion is in a gas-liquid two-phase state instead of a single-phase state in which only the liquid phase is present, so the passage area of the second throttle portion becomes large Therefore, the throttle valve becomes a controllable region.

According to the sixth aspect of the present invention, when the refrigerant flows through the lower portion of the refrigerant flow path pipe which is not covered with the resin container, it absorbs heat from the air inside the heat insulation chamber to be evaporated and vaporized. Ascends upward in the refrigerant channel pipe. Then, when the refrigerant reaches the upper portion of the refrigerant flow tube covered with the resin container, the heat storage effect is obtained in which the refrigerant is cooled by the regenerator and condensed to radiate heat.

According to the seventh aspect of the present invention, at the beginning of the cold storage operation or the freezing operation after cold storage, that is, the temperature inside the adiabatic chamber detected by the chamber temperature detecting means is higher than a preset temperature, which is higher than a predetermined temperature. When the temperature is rising, the amount of air blown by the air blower in the refrigerator is increased more than in the steady state, so that the evaporation temperature of the refrigerating refrigerant evaporator rises more than the melting point of the regenerator. As a result, the regenerator is melted and the refrigerant enthalpy on the inlet side of the refrigerating refrigerant evaporator is reduced accordingly, so that the cooling performance in the heat insulation chamber is improved.

[0021]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, a refrigerating apparatus of the present invention will be described based on an embodiment applied to a vehicle refrigerating apparatus, particularly a refrigerating vehicle refrigerating apparatus.

[Structure of First Embodiment] FIGS. 1 to 6 show a first embodiment of the present invention. FIG. 1 is a view showing a refrigerating apparatus for a refrigerating vehicle, and FIG. 2 is a refrigerating vehicle thereof. It is the figure which showed the refrigeration vehicle carrying the refrigeration device for vehicles.

The refrigerating machine 1 for a refrigerating vehicle includes a freezer 3 mounted on a refrigerating vehicle 2, a refrigerating cycle 4 with a cool storage function for refrigerating the freezer 3, an in-compartment air blower 6, an outside air blower 7, and each refrigeration. And a control panel 8 for controlling energization of the device. The freezer 3 is the heat insulating box of the present invention, and is formed in a rectangular parallelepiped shape by a heat insulating material (not shown) that insulates the inside and the outside, and stores frozen foods and refrigerated foods inside.

The refrigeration cycle 4 includes a refrigerant compressor 11, a refrigerant condenser 12, a receiver 12a, a temperature automatic expansion valve 13, a cold storage refrigerant evaporator 14, a freezing refrigerant evaporator 15, an accumulator 16 and a refrigerant flow path switching valve 17. Etc. These are connected by a refrigerant pipe.

The refrigerant compressor 11 is a compressor for compressing the gas refrigerant sucked inside from the suction port and discharging the high-temperature, high-pressure gas refrigerant from the discharge port to the refrigeration vehicle 2 via the electromagnetic clutch 18 and the belt 19. It is rotationally driven by the mounted engine 20. Instead of the refrigerant compressor 11, an electric compressor whose rotation speed is controlled by an air conditioner inverter may be used. Alternatively, a variable capacity compressor may be used.

The refrigerant condenser 12 is installed in a place where the running wind of the refrigerating vehicle 2 is easily received, for example, below the freezer 3.
The refrigerant condenser 12 heat-exchanges the high-temperature, high-pressure gas refrigerant flowing from the refrigerant compressor 11 with the outside air blown by the outside-air blower 7 and the traveling wind of the refrigeration vehicle 2 to condense and liquefy the refrigerant. Work as. Receiver 1
Reference numeral 2a is for separating the inflowing refrigerant into gas and liquid, and functions as a gas / liquid separating means for supplying only the liquid refrigerant to the temperature automatic expansion valve 13. The receiver 12a need not be provided as long as the refrigerant is completely liquefied on the outlet side of the refrigerant condenser 12.

The temperature automatic expansion valve 13 is an expansion valve, for example, a valve body 21 formed of a throttle valve,
And a temperature sensitive element 22 for driving the valve body 21 and the like. The valve body 21 rapidly injects the liquid refrigerant flowing from the refrigerant condenser 12 through a small throttle hole (not shown) to rapidly expand it into a low-temperature, low-pressure refrigerant in a gas-liquid two-phase state.

The temperature sensitive element 22 includes a temperature sensitive cylinder 23, a capillary tube 24, a power unit (not shown) such as a diaphragm or a bellows, and the like. The temperature-sensitive cylinder 23 is filled with a gas having the same component as the refrigerant, and the degree of superheat of the gas refrigerant drawn into the refrigerant compressor 11, that is, the refrigerant at the outlet of the refrigerant evaporator 15 for refrigeration. Is a refrigerant temperature detecting means for detecting a temperature change of the. The capillary tube 24 is a pressure guiding means that forms a pressure guiding pipe line that communicates the inside of the temperature sensing cylinder 23 with the pressure chamber on one side of the power unit and guides the pressure change in the temperature sensing cylinder 23 to the power unit. The power unit is a drive unit that drives a valve body that constitutes the throttle valve based on a pressure change in the pressure chamber on one side.

In the temperature automatic expansion valve 13, when the refrigerant temperature at the outlet of the refrigerating refrigerant evaporator 15 rises, the gas in the temperature sensitive tube 23 expands, and the power unit and the valve body move to enlarge the throttle hole. The circulation amount of the refrigerant in the refrigeration cycle 4 is increased. On the contrary, the temperature automatic expansion valve 13 is used for the refrigerating refrigerant evaporator 1
When the temperature of the refrigerant at the outlet of 5 decreases, the gas in the temperature-sensitive cylinder 23 is compressed, and the power unit and the valve element move to reduce the throttle hole to reduce the circulation amount of the refrigerant in the refrigeration cycle 4.

FIG. 3 is a view showing a refrigerant evaporator for cold storage. The cold-storage refrigerant evaporator 14 is installed in the upper part of the center of the freezer 3. The cold-storage refrigerant evaporator 14 is connected in series on the upstream side of the freezing refrigerant evaporator 15. Further, the cold-storage refrigerant evaporator 14 functions as an evaporator that heat-exchanges the gas-liquid two-phase refrigerant flowing from the temperature automatic expansion valve 13 with the cool storage agent to cool the cool storage agent and evaporate the refrigerant.

The refrigerant evaporator for cold storage 14 of this embodiment is used.
Is a plurality of cold storage packs 5 in which a cold storage agent is filled in a resin container having excellent thermal conductivity, and two cold storage packs 5 facing each other.
It is composed of a round tube 25 as a pipe sandwiched therebetween. The round tube 25 is a metallic refrigerant flow path tube having excellent heat conductivity, and includes a plurality of straight tube portions and U
It is arranged in a meandering shape by alternately repeating the character tube portions, and a refrigerant for cooling the regenerator flows inside.

Instead of the round tube 25, a refrigerant passage tube such as a flat tube (flat tube) may be used for the purpose of further improving the heat transfer area and the freezing capacity.
Further, one end of the cold-storage refrigerant evaporator 14 is a refrigerant inlet portion 26 through which the refrigerant flows from the automatic temperature expansion valve 13, and the other end thereof is a refrigerant outlet portion 27 through which the refrigerant flows out to the refrigerating refrigerant evaporator 15. Has been done. Note that fins for improving heat exchange efficiency may be provided around the round tube 25.

As the cold storage agent filled in the cold storage pack 5, brine (an aqueous solution of calcium chloride or salt), ethylene glycol brine, methanol water brine, etc. are used. Further, in this embodiment, the evaporation temperature of the refrigerant in the freezing refrigerant evaporator 15 when the internal temperature of the freezer 3 reaches a first predetermined temperature (for example, −20 ° C.) (for example, −
A cold storage agent having a freezing point and a melting point (e.g., -25 ° C) that are similar to those of 25 ° C is used.

The cold storage agent melts to maintain the inside of the freezer 3 at a low temperature when the refrigeration cycle 4 is stopped, that is, when the electromagnetic clutch 18 of the refrigerant compressor 11 is deenergized (OFF). That is, the cold storage agent keeps the inside of the freezer 3 cool by latent heat of fusion. Although the freezing point and melting point of the regenerator of this example are set to -25 ° C, the amount of solute (salt, etc.) in a certain amount of solvent (water) may be changed, or the set temperature in the refrigerator may be changed. Can change the freezing point and melting point of the cold storage agent.

The refrigerating refrigerant evaporator 15 is provided in the duct of the cooling unit 28 installed in the upper part of the front side of the freezer 3, and a plurality of refrigerant passage tubes each having a tube portion formed between two tank portions are laminated. In the laminated heat exchanger described above, fins are joined between adjacent refrigerant flow passage tubes. The refrigerating refrigerant evaporator 15 is connected in series on the downstream side of the cold storage refrigerant evaporator 14. In addition, the refrigerating refrigerant evaporator 15 is
Refrigerant flowing in from the cold storage refrigerant evaporator 14 and the internal fan 6
It functions as an evaporator that heats and exchanges heat with the air in the refrigerator blown by to cool the air in the refrigerator and evaporates and evaporates the refrigerant.

The accumulator 16 functions as a gas-liquid separator that separates the refrigerant flowing from the refrigeration refrigerant evaporator 15 into a liquid refrigerant and a gas refrigerant and supplies only the gas refrigerant to the refrigerant compressor 11.

The refrigerant passage switching valve 17 is the refrigerant passage switching means of the present invention, which is installed in the hot gas bypass pipe and switches between the first refrigerant passage 29 and the second refrigerant passage 30. Thus, it is an electromagnetic on-off valve that opens when energized and closes when energized is stopped. Refrigerant flow path switching valve 17
Switches between defrosting operation, freezing operation, and cold storage operation by opening and closing the hot gas bypass pipe.

The first refrigerant flow path 29 is formed by a refrigerant pipe, and the high temperature and high pressure refrigerant discharged from the refrigerant compressor 11 is transferred to the refrigerant condenser 12, the automatic temperature expansion valve 13 and the cold storage refrigerant evaporator 14. It is a refrigerant passage through which the refrigerant for freezing flows into the evaporator 15. In addition, 29a is a check valve.

The second refrigerant passage 30 is formed by a hot gas bypass pipe, and the high temperature and high pressure refrigerant discharged from the refrigerant compressor 11 is transferred to the refrigerant condenser 12 and the temperature automatic expansion valve 1.
3 is a refrigerant passage for bypassing the cold storage refrigerant evaporator 14 and flowing into the freezing refrigerant evaporator 15.

The in-compartment blower 6 is a cooling unit 28.
The internal fan 31 that generates an air flow in the duct, the internal fan motor 32 that rotationally drives the internal fan 31, and the like. The internal fan 31 is rotatably provided in the duct of the cooling unit 28.

When the internal fan 31 is rotationally driven by the internal fan motor 32, the freezer 3 is placed in the duct of the cooling unit 28 as shown by the arrow in FIG.
After sucking the air inside the refrigerator and guiding it to the freezing refrigerant evaporator 15, the air cooled by the freezing refrigerant evaporator 15 is convected into the freezer 3 through the cold storage refrigerant evaporator 14. The internal fan motor 32 is energized (ON) and deenergized (OFF) by the control panel 8. Note that the rotation speed of the internal fan motor 32 may be controlled in two or more steps or steplessly to change the air flow rate of the internal fan 31.

The outside fan 7 is an outside fan 33 for blowing outside air outside the freezer 3 to the refrigerant condenser 12, and an outside fan motor 34 for rotationally driving the outside fan 33.
And so on. The outdoor fan 33 is installed near the refrigerant condenser 12.

The outside fan motor 34 is energized (ON) and deenergized (OFF) by the control panel 8.
Note that, similarly to the in-compartment fan motor 32, the fan speed of the out-of-compartment fan 33 may be changed by controlling the rotation speed of the out-of-compartment fan motor 34 in two or more steps or steplessly.

FIG. 4 is an electric circuit diagram showing the control panel 8. The control panel 8 is the control means of the present invention, and operates when a predetermined voltage is applied from the battery 36 mounted on the refrigeration vehicle 2. The control panel 8 constitutes a microcomputer (control device) including a CPU, a ROM, a RAM and a timer circuit. Further, an operation switch (not shown), an inside temperature setting switch (not shown), a defrost switch (not shown), an inside temperature sensor 37, a cold storage agent temperature sensor 38, etc. are connected to the control panel 8. Has been done.

The control panel 8 controls the energization of the relay coils 39 to 42 based on the output signals of the operation switch, the inside temperature setting switch, the defrost switch, the inside temperature sensor 37 and the cold storage agent temperature sensor 38. Thus, the electromagnetic clutch 18, the refrigerant passage switching valve 17, the internal fan motor 32, and the external fan motor 34 of the refrigerant compressor 11 are controlled.

The operation switch is a refrigeration operation command means for starting the refrigeration operation and the cold storage operation (cold operation) of the refrigeration cycle 4. When the operation switch is turned on, the control panel 8 outputs so as to alternately perform the freezing operation and the cold storage operation. The inside temperature setting switch is an inside temperature setting means for setting the temperature inside the freezer 3 to a desired temperature (for example, -18 ° C).

The defrost switch is a defrosting operation command means for starting the defrosting operation of the refrigeration cycle 4. When the defrost switch is turned on, the control panel 8 turns on (opens) the refrigerant flow path switching valve 17 for a time period (for example, 1 hour) measured by the timer circuit to defrost the refrigeration refrigerant evaporator 15. Output to do.

The in-compartment temperature sensor 37 is an in-compartment temperature detecting means of the present invention. For example, a thermistor or a thermostat is used, and it is installed in the freezer 3 and detects the in-compartment temperature in the freezer 3. When the inside temperature Ta of the inside of the freezer 3 detected by the inside temperature sensor 37 is lowered to the first predetermined temperature T1 (inside inside set temperature Ts-ΔT ° C .: -20 ° C.) or lower, Internal fan motor 32
Is turned off to perform cold storage operation. Further, when the internal temperature Ta of the inside of the freezer 3 detected by the internal temperature sensor 37 rises to the second predetermined temperature T2 (internal set temperature Ts + ΔT ° C .: -16 ° C.) or more, The freezer operation is performed by turning on the internal fan motor 32.

The cold storage agent temperature sensor 38 is, for example, a thermistor or thermostat, is attached to the surface of the cold storage pack 5, and is a cold storage agent temperature detecting means for detecting the temperature Tb of the cold storage agent. In the control panel 8, the temperature Tb of the cold storage agent detected by the cold storage agent temperature sensor 38 is lower than the freezing point Tg of the cold storage agent (freezing point Tg−ΔT ° C .: −2, for example).
When the temperature falls below 5 ° C.-2 ° C.), the electromagnetic clutch 18, the internal fan motor 32, and the external fan motor 34 of the refrigerant compressor 11 are turned off (OFF) and output so as to keep cold.

The relay coils 39 to 42 are used for the refrigerant compressor 1
The relay switches 43 to 46 for energizing the electromagnetic clutch 18, the refrigerant passage switching valve 17, the internal fan motor 32, and the external fan motor 34 are opened and closed. A semiconductor switching circuit such as a transistor may be used instead of such a relay circuit.

Here, the refrigerant flow path switching valve 1 according to each operation mode of the refrigeration cycle 4 by the control panel 8 [freezing operation, cold storage operation, defrosting operation and OFF (cooling)].
Table 1 below shows the energized states of valve No. 7 (valve open state), the electromagnetic clutch 18, the internal fan motor 32, and the external fan motor 34.

[Table 1]

[Operation of First Embodiment] Next, the operation of the control panel 8 of this embodiment will be briefly described with reference to FIGS. 1 to 5. Here, FIG. 5 is a flowchart showing a control program for switching between the freezing operation and the cold storage operation by the control panel 8.

When the operation switch is turned on, first, a temperature (Tg-ΔT ° C) lower than the freezing point is obtained according to the preset freezing point of the regenerator (step S1). Next, the inside temperature setting Ts set by the inside temperature setting switch is read (step S2). Next, the first predetermined temperature T1 and the second predetermined temperature T2 are obtained according to the inside temperature setting Ts set by the inside temperature setting switch (step S3).
Next, the inside temperature Ta detected by the inside temperature sensor 37 and the temperature Tb of the cool storage agent detected by the cool storage agent temperature sensor 38.
Is read (step S4).

Next, it is determined whether or not the inside temperature Ta detected by the inside temperature sensor 37 has dropped below a first predetermined temperature T1 (eg, -20 ° C.) (step S5). If the result of this determination is No, that is, if the internal temperature Ta detected by the internal temperature sensor 37 is the first predetermined temperature T1.
When the temperature is higher than (for example, -20 ° C), it is determined whether or not the internal temperature Ta detected by the internal temperature sensor 37 is equal to or higher than the second predetermined temperature T2 (for example, -16 ° C). Yes (step S6). If the determination result is Yes, the electromagnetic clutch 18, the internal fan motor 32, and the external fan motor 34 of the refrigerant compressor 11 are turned on, the refrigerant flow path switching valve 17 is turned off, and the operation of the refrigeration cycle 4 is performed. The mode is set to the freezing operation (step S7). Then, control of step S2 is performed.

If the result of the determination in step S6 is No, that is, if the in-compartment temperature Ta detected by the in-compartment temperature sensor 37 is lower than the second predetermined temperature T2 (for example, -16 ° C). , And the determination result of step S5 is Y
In the case of es, that is, when the in-compartment temperature Ta has fallen below the first predetermined temperature T1 (for example, -20 ° C), the temperature Tb of the cold storage agent detected by the cold storage agent temperature sensor 38 is detected.
Is lower than the freezing point Tg of the regenerator (freezing point Tg-ΔT
C .: For example, it is determined whether or not it has fallen below -25.degree. C.-2.degree. When the determination result is No, the electromagnetic clutch 18 and the outside fan motor 34 of the refrigerant compressor 11 are turned on, the refrigerant flow path switching valve 17 and the inside fan motor 32 are turned off, and the refrigeration cycle 4 is operated. Set the mode to cold storage operation (cold storage operation) (step S
9). Then, control of step S2 is performed.

If the result of the determination in step S8 is Yes, the refrigerant flow path switching valve 17, the electromagnetic clutch 18 of the refrigerant compressor 11, the internal fan motor 32, and the external fan motor 34 are all turned off, The operation mode of the refrigeration cycle 4 is turned off to keep it cool (step S10). Then, control of step S2 is performed. If the determination result of step S6 is No, the process of step S9 may be performed without performing the determination of step S8.

Next, the operation of the refrigerating apparatus 1 for a refrigerating vehicle of this embodiment will be briefly described with reference to FIGS. 1 to 4 and 6. Here, FIG. 6 is a time chart showing switching control between the freezing operation and the cold storage operation by the refrigeration system 1 for a refrigeration vehicle. When the operation switch is turned on, the refrigerant compressor 11, the internal fan 31, and the external fan 33 start operating. Further, since the refrigerant passage switching valve 17 is turned off, the refrigeration cycle 4 is switched to the first refrigerant passage 29.

Therefore, the high-temperature, high-pressure gas refrigerant discharged from the discharge port of the refrigerant compressor 11 is condensed and liquefied when passing through the refrigerant condenser 12, and then flows into the receiver 12a for gas-liquid separation. Then, only the liquid refrigerant is supplied to the automatic temperature expansion valve 13 from the receiver 12a. Liquid refrigerant is
When passing through the automatic temperature expansion valve 13, it rapidly expands to become a low-temperature, low-pressure atomized refrigerant (refrigerant in a gas-liquid two-phase state).

The mist-like refrigerant flows into the round tube 25 of the cold-storage refrigerant evaporator 14, exchanges heat with the cold-storage agent in the cold-storage pack 5 to evaporate and vaporize, and a gas-liquid having more gas components than liquid components. After becoming a two-phase refrigerant, it flows into the refrigerant evaporator 15 for freezing. On the other hand, the temperature of the cool storage agent in the cool storage pack 5 cooled by the heat of vaporization of the refrigerant in the cool storage refrigerant evaporator 14 decreases.

Next, the gas-liquid two-phase refrigerant flowing into the refrigerating refrigerant evaporator 15 is heat-exchanged with the air in the freezer 3 blown by the rotation of the internal fan 31 to be evaporated and vaporized. It flows into the accumulator 16. Then, the refrigerant is separated into gas and liquid by the accumulator 16, and only the gas refrigerant is sucked into the refrigerant compressor 11.

On the other hand, the inside air cooled by the heat of vaporization of the refrigerant in the freezing refrigerant evaporator 15 is blown into the freezer 3 from the duct of the cooling unit 28. Therefore, by performing the refrigerating operation of the refrigeration cycle 4 as described above, as the refrigerant evaporation temperatures of the cold storage refrigerant evaporator 14 and the freezing refrigerant evaporator 15 decrease, the freezer 3
The temperature inside the refrigerator also decreases.

The temperature Ta in the freezer 3 is first
When a predetermined temperature T1 (for example, -20 ° C) is reached, the operation of the control panel 8 turns off only the internal fan motor 32 to stop the internal fan 31 from operating. Then, the cooling storage operation of the refrigeration cycle 4 is performed by continuing the operation of the refrigeration cycle 4 by continuing to energize the electromagnetic clutch 18 and the outdoor fan motor 34. As a result, forced convection in the freezer 3 is eliminated, the heat exchange efficiency between the refrigerant flowing in the freezing refrigerant evaporator 15 and the air in the freezer is reduced, and the freezing refrigerant evaporator 15 hardly functions as an evaporator.

Therefore, the temperature of the gas refrigerant at the outlet of the refrigerating refrigerant evaporator 15 decreases, so that the gas in the temperature sensing cylinder 23 is compressed and the power unit and the valve body move to reduce the size of the throttle hole. Due to the throttling action of the temperature automatic expansion valve 13 as described above, the evaporation pressure of the refrigeration cycle 4 decreases, and the amount of refrigerant flowing into the cold-storage refrigerant evaporator 14 decreases.

The evaporation temperature of the refrigerant circulating in the refrigeration cycle 4, that is, the evaporation temperatures of the refrigerant in the cold storage refrigerant evaporator 14 and the freezing refrigerant evaporator 15 are the following equations (1) and (2). When the operation of the internal fan 31 is stopped, W in the expression of Formula 1 becomes smaller and φ also becomes smaller. As a result, the air-side capacity Qa becomes smaller than the refrigerant-side capacity QR, so that ΔT increases in an attempt to balance, the evaporation temperature of the refrigerant decreases.

[0065]

[Equation 1] Air-side capacity ... Qa = W · φ · ΔT W: A value (kcal /
h · ° C.) φ: Refrigerant evaporator 14 for cold storage and refrigerant evaporator 15 for freezing
(Eg, heat transfer area, heat transfer coefficient) ΔT: Temperature difference (° C) between air temperature (cooled medium temperature) and refrigerant evaporation temperature

[0066]

## EQU00002 ## Refrigerant side capacity ... QR = Gr.multidot..DELTA.i Gr: Refrigerant circulation amount (kg / h) in the refrigeration cycle 4 .DELTA.i: Inlet side of the cold storage refrigerant evaporator 14 and freezing refrigerant evaporator 15 outlet side Enthalpy difference with (kcal / kg)

Therefore, the evaporation temperature of the refrigerant in the cold-storage refrigerant evaporator 14 becomes the first value when the internal fan motor 32 is turned off.
The second evaporation temperature Te2 (e.g., -35 [deg.] C.) is lower than the evaporating temperature Te1 (e.g., -25 [deg.] C.). Therefore, the regenerator in the regenerator pack 5 covering the round tube 25 of the regenerator refrigerant evaporator 14 is further cooled and regenerated.

When the internal temperature Ta in the freezer 3 rises to the second predetermined temperature T2 (eg, -16 ° C.) or higher during the cold storage operation of the refrigeration cycle 4, the control panel 8 is actuated again. When the internal fan motor 32 is turned on, the internal fan 31 is operated to forcibly convect the internal air into the freezer 3 to start the freezing operation.

By repeating the freezing operation and the cold storage operation of the refrigeration cycle 4 alternately, the temperature Tb of the cold storage agent in the cold storage pack 5 is lower than the freezing point Tg of the cold storage agent (freezing point Tg-ΔT ° C .: − 25 ° C.-2 ° C.), it is determined that the freezing of the regenerator has been completed, and thereafter, the electromagnetic clutch 18 is turned on and off to turn the freezing operation on and off.
The inside of the freezer 3 is frozen by repeating. Further, when the internal temperature of the freezer 3 rises by stopping the operation of the refrigeration cycle 4 by stopping the engine 20, the cold storage agent in the cold storage pack 5 melts. Therefore, the interior of the freezer 3 is kept cool by the latent heat of fusion of the regenerator in the regenerator pack 5.

Here, the user turns on the defrost switch, or the detected value of the evaporation pressure or temperature of the refrigerant evaporator 15 for refrigeration, the refrigeration of the refrigeration cycle 4, during the refrigeration / cooling operation of the refrigeration cycle 4, Under a preset condition such as when the cold storage operation is performed for one hour, for example, the control panel 8 operates to turn on the refrigerant flow passage switching valve 17 and the refrigeration cycle 4 causes the first refrigerant flow passage 29 ( The freezing / cooling operation side) is switched to the second refrigerant flow path 30 (defrosting operation side).

As a result, the high-temperature, high-pressure gas refrigerant discharged from the discharge port of the refrigerant compressor 11 becomes the second refrigerant flow path 29.
Since it directly flows into the refrigerant evaporator 15 for freezing through
Defrosting of the frost that has formed on the surface of the refrigerating refrigerant evaporator 15 and defrosting of the ice frozen on the surface of the refrigerating refrigerant evaporator 15 are performed.

[Effects of the First Embodiment] As described above, in this embodiment, the cold storage refrigerant evaporator 14 and the freezing refrigerant evaporator 15 are connected in series, and the temperature automatic expansion valve 13 is used for freezing. The throttle amount is adjusted according to the temperature change of the refrigerant at the outlet of the refrigerant evaporator 15. Further, the cold storage refrigerant evaporator 14
Refrigerant evaporator 1 when the melting point of the regenerator in the regenerator pack 5 reaches the first predetermined temperature in the freezer 3.
The temperature is about the same as the evaporation temperature of the refrigerant of No. 5 (for example, -25 ° C).

By cooling the cool storage agent having such a melting point by the cool storage refrigerant evaporator 14, the cool storage agent does not become frozen in the cool storage refrigerant evaporator 14 during the refrigerating operation of the refrigeration cycle 4. No heavy load. Further, during the cold storage operation, the temperature difference between the temperature of the cold storage agent and the evaporation temperature of the refrigerant of the cold storage refrigerant evaporator 14 is appropriately set by the throttling action of the temperature automatic expansion valve 13. Therefore, in the refrigeration system 1 for a refrigeration vehicle, the freezing operation and the cold storage operation can be efficiently and alternately performed.

Further, in this embodiment, the refrigerating refrigerant evaporator 15 is connected in series on the downstream side of the cold accumulating refrigerant evaporator 14 and the discharge port of the refrigerant compressor 11 is connected to the second refrigerant passage 30. The inlet of the refrigerating refrigerant evaporator 15 is directly connected.
Therefore, during the defrosting operation of the refrigeration cycle 4, that is, during the defrosting of the refrigerating refrigerant evaporator 15, the high-temperature, high-pressure gas refrigerant discharged from the discharge port of the refrigerant compressor 11 is transferred to the refrigerant condenser 1.
2. It bypasses the temperature automatic expansion valve 13 and the cold storage refrigerant evaporator 14, and flows into only the freezing refrigerant evaporator 15. This can prevent the cold storage agent in the cold storage pack 5 of the cold storage refrigerant evaporator 14 from melting.

As described above, the refrigeration cycle 4 with a highly efficient cold storage function can be realized while eliminating the conventional temperature automatic expansion valve 107 and the two switching valves 113 and 114 shown in FIG. Therefore, it is possible to provide an inexpensive refrigerating apparatus 1 for a refrigerating vehicle, which has a reduced number of parts and a reduced product cost.

[Second Embodiment] FIG. 7 shows a second embodiment of the present invention, and is a view showing a cold-storage refrigerant evaporator of a refrigerating apparatus for a refrigerating vehicle. In this embodiment, from the viewpoint of shortening the freezing time of the cold storage agent 51 and reducing the weight of the cold storage refrigerant evaporator 14, a meandering refrigerant flow path pipe is provided in the cold storage agent 51 filled in the cold storage container 52. 53 is buried.

Then, around the refrigerant flow pipe 53, fins 54 such as spiral fins and plate fins for improving heat exchange efficiency are attached. The refrigerant flow pipe 53 has one end serving as a refrigerant inlet 55 through which the refrigerant flows from the automatic temperature expansion valve 13, and the other end serving as a refrigerant outlet 56 through which the refrigerant flows out to the refrigerant evaporator 15 for refrigeration. ing.

[Third Embodiment] FIG. 8 shows a third embodiment of the present invention and is a view showing a cold-storage refrigerant evaporator of a refrigerating apparatus for a refrigerating vehicle. In this embodiment, the cold storage container 52 of the second embodiment is filled with a resin or metal capsule 57 containing a cold storage agent 51.

[Structure of Fourth Embodiment] FIGS. 9 to 11 show a fourth embodiment of the present invention.
FIG. 0 is a diagram showing a temperature automatic expansion valve of the refrigeration system for a refrigeration vehicle. The temperature automatic expansion valve 13 of this embodiment includes a tubular valve body 21, a temperature sensitive element 22 provided on the upper portion of the valve body 21, and two first and first movably arranged inside the valve body 21. The two-ball valve 61, 62, a coil spring 63 for urging the first and second ball valves 61, 62 upward in the drawing, and the like.

The valve body 21 is made of metal such as brass and has a T-shaped cross section. Inside the valve body 21, a refrigerant flow path 64 through which the refrigerant flows is formed in an inverted L shape. The upstream side of the refrigerant flow path 64 communicates with the outlet side of the refrigerant condenser 12 via a refrigerant pipe, as shown in FIG. In addition, the downstream side of the refrigerant flow path 64 communicates with the refrigerant inlet portion 26 of the cold-storage refrigerant evaporator 14 via a refrigerant pipe, as shown in FIG. 1.

In the middle of the coolant channel 64, a first throttle hole (first throttle portion) 65 for reducing the cross-sectional area of the coolant channel 64,
Also, a second throttle hole (second throttle portion) 66 that narrows the cross-sectional area of the refrigerant channel 64 is formed. The inner diameter of the first throttle hole 65 is larger than the inner diameter of the second throttle hole 66. Further, the inner diameters of the first and second throttle holes 65 and 66 are equal to the two first and second inner diameters.
The ball valves 61 and 62 have such a size that they can be reciprocally inserted without coming into contact with the passage walls of the first and second throttle holes 65 and 66.

The temperature sensitive element 22 is provided with a diaphragm cover 67, a temperature sensitive cylinder 23, a capillary tube 24 and the like. In the diaphragm cover 67, a diaphragm 70 as a power unit that divides the inside into an upper pressure chamber 68 and a lower pressure chamber 69 is displaceably arranged. The upper pressure chamber 68 communicates with the inside of the temperature sensing cylinder 23 via the capillary tube 24.

Further, the lower pressure chamber 69 communicates with the inside of the refrigerant pipe between the temperature automatic expansion valve 13 and the cold-storage refrigerant evaporator 14 via the communication hole 21a formed in the valve body 21 and the pressure equalizing pipe 60. are doing. Therefore, the low pressure (= evaporation pressure) of the refrigeration cycle 4 is applied to the lower pressure chamber 69. In addition,
On the side surface of the lower pressure chamber 69 of the diaphragm 70, a disk-shaped stopper 72 that connects the upper end portion of the actuating rod 71 is coaxially attached to the central portion.

The temperature-sensitive cylinder 23 is filled with a gas refrigerant of the same kind as the refrigerant circulating in the refrigeration cycle 4, and contacts the refrigerant pipe on the outlet side of the refrigerating evaporator 15 as shown in FIG. Installed. The temperature-sensitive cylinder 23 is a refrigerant temperature detecting means that converts a temperature change of the refrigerant flowing in the refrigerant pipe into a pressure change and transmits the pressure change into the upper pressure chamber 68 of the temperature-sensitive element 22 via the capillary tube 24. .

The first ball valve 61 is a first valve element and a variable throttle valve fixed to the actuation rod 71, displaceably arranged upstream of the second ball valve 62 in the refrigerant flow path 64. The first ball valve 61 is displaced to a displacement position where the pressure in the temperature sensitive cylinder 23 acting in the upper pressure chamber 68, the low pressure acting in the lower pressure chamber 69, and the spring force of the coil spring 63 are balanced. Then, the first throttle hole 65 of the first ball valve 61
The opening degree of the first throttle hole 65 (valve opening degree of the temperature automatic expansion valve 13) is changed according to the displacement position with respect to.

The second ball valve 62 is the throttle valve of the present invention and is arranged so as to be displaceable downstream of the first ball valve 61 in the refrigerant flow path 64, and the operating rod 71 abuts on the upper side thereof. The second valve body is a variable throttle valve with which the valve seat 73 is in contact with the lower side. This second ball valve 62 is similar to the first ball valve 61 in that the pressure in the temperature sensitive cylinder 23 acting in the upper pressure chamber 68, the low pressure acting in the lower pressure chamber 69 and the coil spring 63. The second ball valve 62 is displaced to a position where it is balanced with the spring force, and the opening degree of the second throttle hole 66 (the temperature automatic expansion valve 13 is changed according to the displacement position of the second ball valve 62 with respect to the second throttle hole 66).
Change the valve opening).

The coil spring 63 has a valve seat 73 at the upper end.
And the lower end is held by the adjusting screw 74 screwed to the lower end of the valve body 21. This coil spring 6
3 urges the diaphragm 70 upward in the drawing via the second ball valve 62, the operating rod 71, and the stopper 72. The adjusting screw 74 is a valve opening pressure adjusting means for changing the valve opening pressure of the second ball valve 62 according to the fixed position of the valve body 21.

[Operation of Fourth Embodiment] Next, the operation of the refrigerating apparatus 1 for a refrigerating vehicle of this embodiment will be briefly described with reference to FIGS. 1 and 9 to 11.

(During Freezing Operation) During cool down (freezing operation) for lowering the temperature inside the freezer 3, the refrigeration load is high, and the gas temperature at the outlet of the refrigerant evaporator 15 for refrigeration is high. Since the gas refrigerant in the warm cylinder 23 expands and the pressure in the upper pressure chamber 68 of the diaphragm cover 67 becomes higher than the pressure in the lower pressure chamber 69, the diaphragm 70 is displaced downward, so that the operating rod 71 is moved. Is also displaced downward. As a result, the first ball valve 61 is displaced downward to a position apart from the first throttle hole 65, that is, to a position where the refrigerant passing through the first throttle hole 65 does not undergo adiabatic expansion, as shown in FIG.

Therefore, the liquid refrigerant flowing from the outlet side of the refrigerant condenser 12 into the refrigerant passage 64 of the automatic temperature expansion valve 13 is not adiabatically expanded when passing through the first throttle hole 65,
The liquid refrigerant reaches the second throttle hole 66 as it is. At this time, the second ball valve 62, as shown in FIG.
It is displaced to a position slightly apart from 6, that is, a position where the opening degree of the second throttle hole 66 is widened so as to increase the circulation amount of the refrigerant in the refrigeration cycle 4. However, the second throttle hole 66 has a smaller inner diameter than the first throttle hole 65, and can independently adiabatically expand the refrigerant.

Therefore, the liquid refrigerant flowing into the second throttle hole 66 undergoes adiabatic expansion when passing through the second throttle hole 66 to become a low-temperature, low-pressure gas-liquid two-phase refrigerant. The refrigerant in the gas-liquid two-phase state is the round tube 25 of the refrigerant evaporator 14 for cold storage.
The refrigerant flows into the inside of the cold storage pack 5 to exchange heat with the cold storage agent to evaporate and vaporize to become a refrigerant in a gas-liquid two-phase state in which the gas component is larger than the liquid component, and then flows into the refrigeration refrigerant evaporator 15. On the other hand, the temperature of the cool storage agent in the cool storage pack 5 cooled by the heat of vaporization of the refrigerant in the cool storage refrigerant evaporator 14 decreases. Next, the atomized refrigerant flowing into the refrigerant evaporator 15 for refrigeration is
It exchanges heat with the air inside the freezer 3 that is blown by the rotation of the internal fan 31 to evaporate and vaporize to become a gas refrigerant having a superheat degree at the outlet of the refrigerating refrigerant evaporator 15.

Further, as described above, the second ball valve 62 widens the opening of the second throttle hole 66, so that the circulation amount of the refrigerant in the refrigeration cycle 4 is suitable for the high load operation such as the refrigeration operation. In addition, since the inside air in the freezer 3 is efficiently cooled, the inside temperature in the freezer 3 decreases.

(During cold storage operation) Only the fan motor 32 in the refrigerator is turned off, and the electromagnetic clutch 18 and the fan motor 34 outside the refrigerator are turned off.
When the cold storage operation is performed by turning on the
The forced convection in the inside disappears, the heat exchange efficiency between the refrigerant flowing in the refrigerating refrigerant evaporator 15 and the air inside the refrigerator decreases, and the refrigerating refrigerant evaporator 15 almost does not function as an evaporator.

Further, since the refrigerating load in the freezer 3 is also reduced, the temperature of the gas refrigerant at the outlet of the refrigerating refrigerant evaporator 15 is lowered, so that the gas in the temperature sensing cylinder 23 is compressed. As a result, the pressure in the upper pressure chamber 68 of the diaphragm cover 67 approaches the pressure in the lower pressure chamber 69, so that the diaphragm 70 is displaced upward and the operating rod 71 is moved.
Is also displaced upward. Therefore, as shown in FIG. 10, the first ball valve 61 enters the first throttle hole 65,
The second ball valve 62 reduces the opening degree of the second throttle hole 66. Due to such throttling action of the second ball valve 62, the evaporation pressure of the refrigeration cycle 4 is reduced, and the circulation amount of the refrigerant in the refrigeration cycle 4 is also reduced.

Therefore, the liquid refrigerant flowing from the outlet side of the refrigerant condenser 12 into the refrigerant passage 64 of the automatic temperature expansion valve 13 is adiabatically expanded when passing through the first throttle hole 65, and is in a gas-liquid two-phase state. It becomes the refrigerant of. Therefore, even if the amount of circulation of the same refrigerant is the same, the refrigerant flowing into the second throttle hole 66 is in the gas-liquid two-phase state instead of the single-phase state of only the liquid phase. Is increased, the second ball valve 62 can be controlled within a range in which the degree of superheat of the refrigerant can be controlled.

[Effects of Fourth Embodiment] Here, in the refrigerating apparatus 1 for a refrigerating vehicle of the first embodiment in which the normal temperature automatic expansion valve (comparative example) b having one throttle hole a is arranged, Since the evaporation temperatures of the two cold-storage and freezing refrigerant evaporators are different, for example, when the capacity and set value (valve opening pressure) of the temperature automatic expansion valve b is matched with the refrigerant evaporator having a higher evaporation temperature, During low load operation such as operation, the necessary circulation amount of the refrigerant circulating in the refrigeration cycle decreases, so the throttle valve moves toward the throttle direction.

At this time, as shown by the broken line (comparative example) in the graph of FIG. 11, the opening degree of the throttle valve (valve opening degree of the temperature automatic expansion valve) sharply decreases. By exceeding the control range, the hunting amount of the throttle valve increases. In addition, the capacity of the temperature automatic expansion valve b and the set value (valve opening pressure) are stored in the cooler refrigerant evaporator having the lower evaporation temperature.
If both are combined, the circulation amount of the refrigerant during the refrigerating operation decreases, and the cooldown performance deteriorates. That is, in the refrigerating apparatus for a refrigerating vehicle including the normal temperature automatic expansion valve b having only one throttle hole a, the refrigerating operation or the cold storage operation cannot be efficiently controlled when the refrigerating cycle having a large load variation difference is used. There was a problem.

However, even in the case where two refrigerant evaporators having different evaporation temperatures such as the refrigerant evaporator 14 for cold storage and the refrigerant evaporator 15 for freezing are provided, as in this embodiment, inside the valve body 21. The refrigerating apparatus 1 for a refrigerating vehicle in which the temperature automatic expansion valve (Example) 13 provided with the two first and second throttle holes 65 and 66 is provided in the refrigerating vehicle has sufficient circulation during freezing operation that is suitable for freezing operation. Since the amount is obtained, it is possible to suppress deterioration of the cooldown performance. Also, during cold storage operation,
As indicated by the straight line (embodiment) in the graph of FIG. 11, the opening degree of the throttle valve (valve opening degree of the temperature automatic expansion valve) gradually decreases, so that the degree of superheat of the refrigerant is controlled in the second throttle hole 66. Since the second ball valve 62 can be moved within a possible range,
The hunting amount of the ball valve 62 can be reduced.

[Fifth Embodiment] FIGS. 12 and 13 show a fifth embodiment of the present invention, and FIG. 12 is a view showing a refrigerating cycle of a refrigerating apparatus for a refrigerating vehicle. In this embodiment, a temperature automatic expansion valve (having a second throttle portion inside) 13
Is a normal refrigerant condenser 12 of the refrigeration cycle 4
An electromagnetic valve 76 having a bleed port 75 is provided in the middle of a refrigerant pipe that connects the outlet side of the above and the inlet side of the automatic temperature expansion valve 13.

As shown in FIG. 13, the solenoid valve 76 is a needle valve (valve valve) for opening and closing a valve housing 78 having a bleed port 75 and a refrigerant passage 77 formed therein, and a passage hole 79 provided in the middle of the refrigerant passage 77. (Body) 80, a plunger 81 made of a magnetic material that holds the needle valve 80, an electromagnetic coil 82 that drives the plunger 81, and the like. The bleed port 75 functions as a first throttle portion or a fixed throttle portion that narrows the cross-sectional area of the refrigerant passage 77 during the cold storage operation. Reference numeral 83 is a return spring that biases the needle valve 80 in the direction in which it is seated on the valve seat 84.

In this embodiment, at the time of low load operation such as cold storage operation, the electromagnetic coil 82 is turned off (OFF) and the passage hole 79 is closed by the needle valve 80 so that the temperature automatic expansion valve from the refrigerant condenser 12 is closed. The liquid refrigerant toward 13 flows through the bleed port 75. Therefore, the liquid refrigerant that has flowed into the bleed port 75 undergoes adiabatic expansion when passing through the bleed port 75 and becomes a gas-liquid two-phase refrigerant. In addition, during high load operation such as refrigeration operation, the electromagnetic coil 8
2 is turned on and the needle valve 80 is used to turn the passage hole 7
By opening 9, the refrigerant flowing out of the refrigerant passage 77 remains as the liquid refrigerant, and the circulation amount of the refrigerant in the refrigeration cycle 4 is increased. Thereby, the same operation and effect as those of the fourth embodiment can be provided.

[Sixth Embodiment] FIGS. 14 and 15 show a sixth embodiment of the present invention, which is a diagram showing a temperature automatic expansion valve of a refrigerating apparatus for a refrigerating vehicle. In the temperature automatic expansion valve 13 of this embodiment, a disk-shaped plate 85 is attached in the middle of the operating rod 71, and the second throttle hole 6 formed in the partition plate 86.
A partition plate 87 is attached on the upstream side of 6. In the partition plate 87, a passage hole 88 having an opening area larger than that of the second throttle hole 66, and a plurality of first throttle holes (orifices) 65 are formed around the passage hole 88. Note that one first throttle hole 65 has an opening area smaller than that of the second throttle hole 66, and adiabatically expands the passing refrigerant.

In this embodiment, during low load operation such as cold storage operation, as shown in FIG.
Is displaced upward, the operating rod 71 is also displaced upward, and the plate 85 closes the passage hole 88. Therefore, the liquid refrigerant that has flowed into the refrigerant flow path 64 has a plurality of first throttle holes 65.
Flowing through. Therefore, the liquid refrigerant that has flowed into the plurality of first throttle holes 65 undergoes adiabatic expansion and becomes a refrigerant in a gas-liquid two-phase state on the upstream side of the second throttle holes 66. Further, during a high load operation such as a freezing operation, as shown in FIG. 15, the diaphragm 70 is displaced downward, so that the operating rod 71 is also displaced downward, and the plate 85 opens the passage hole 88. By opening the passage hole 88, the liquid refrigerant remains on the upstream side of the second throttle hole 66, and the circulation amount of the refrigerant in the refrigeration cycle 4 increases. Thereby, the same operation and effect as those of the fourth embodiment can be provided.

[Structure of Seventh Embodiment] FIGS. 16 to 18
Shows a seventh embodiment of the present invention, and FIG. 16 is a view showing a refrigerating vehicle equipped with a refrigerating device for a refrigerating vehicle. The cold-storage refrigerant evaporator 14 of this embodiment is mounted above the freezer 3 mounted on the refrigeration vehicle 2, and has a plurality of cold-storage packs 5 filled with a cold-storage agent in a resin container having excellent thermal conductivity, and a plurality of cold-storage packs 5. The straight tube portion is composed of a round tube 90 extending in the up-down direction.

The round tube 90 is the refrigerant channel tube of the present invention, and as shown in part in FIG. 17, a plurality of straight pipe portions and U-shaped pipe portions are alternately repeated to form a meandering shape. Placed,
For example, an endothermic pipe portion (lower side portion) 91 having an outer diameter of φ15.8 and not sandwiched between two opposing cold storage packs 5 and 2
It has a heat radiating pipe portion (upper portion) 92 that is sandwiched between two cold storage packs 5.

The heat absorbing tube portion 91 of the round tube 90 is used.
Is, for example, 0.6 m to 0.7 from the lower end surface of the cold storage pack 5.
It projects downward by m. Also, the refrigerant evaporator for cold storage 1
4 has a refrigerant inlet portion 93 and a refrigerant outlet portion 94. The heat absorption tube portion 91 of the round tube 90 may be a finned tube to improve the heat exchange efficiency. Alternatively, the heat absorbing portion of the round tube 90 may be a tube with spine fins to increase the heat transfer area to improve the cold insulation performance.

[Operation of Seventh Embodiment] Next, the operation of the refrigerating apparatus 1 for a refrigerating vehicle of this embodiment will be briefly described with reference to FIGS. 16 to 18.

When the engine 20 is turned off due to a problem of exhaust gas or noise, that is, at the time of cold keeping to keep the inside of the freezer 3 at a low temperature even when the refrigerant does not circulate inside the refrigeration cycle 4, the inside of the round tube 90 enters. As shown in FIG. 17, the refrigerant is evaporatively vaporized by absorbing heat from the inside air at −10 ° C. in the endothermic tube portion 91 in which the round tube 90 is not sandwiched by the plurality of regenerator packs 5. ), And rises to the heat dissipation pipe portion 92 of the round tube 90. Then, for example, a heat pipe effect of condensing and radiating heat by condensing and liquefying in the heat radiating pipe portion 92 sandwiched by the plurality of cold storage packs 5 frozen at −25 ° C. is provided.

[Effect of Seventh Embodiment] In recent years, in a refrigerating apparatus for a refrigerating vehicle, the engine 20 has a problem due to exhaust gas and noise.
In response to a request to keep the inside of the freezer at a low temperature even when the power is turned off, the cold storage agent enclosed in the metal container is frozen at night with electricity, and the latent heat of fusion of the cold storage agent is used to cool the inside of the freezer 3 during delivery. There is a technique of keeping cold, but it is disadvantageous in weight and cost because of the metal container. Therefore,
There is a refrigerating device 1 for a refrigerating vehicle equipped with a cold-storage refrigerant evaporator 14 which is advantageous in weight and cost by resinizing a container of the cold-storage agent (first embodiment). However, since the container for the cold storage agent is made of resin, there is a problem that the heat resistance is large and the cold insulation performance is inferior to that of the metal container.

In order to solve the above problem, in this embodiment, the refrigerating apparatus 1 for a refrigerating vehicle equipped with the cold storage refrigerant evaporator 14 capable of maintaining the inside of the freezer 3 at a low temperature even when the engine 20 is turned off. In the above, the round tube 90 of the cold-storage refrigerant evaporator 14 is formed into a heat pipe during cold storage.
As a result, the heat absorption performance of the cold-storage refrigerant evaporator 14 is improved, so that the cold-retention performance can be improved even if the cold-storage pack 5 in which the container for the cold-storage agent is made of resin is used.

In this embodiment, the longitudinal direction of the round tube (refrigerant flow passage pipe) 90 is the vertical direction, but if the heat radiating portion on the cold storage pack 5 side is not inclined downward from the horizontal, the refrigerant flow passage Even if the longitudinal direction of the tube is set to be substantially horizontal, a similar heat pipe effect can be obtained in the refrigerant flow path tube during cold insulation.

[Experimental Results of Seventh Example] Next, the outside temperature 3
When the temperature is 5 ° C, the size of the freezer (insulator) is 2960 in length.
An experiment for investigating the cold insulation performance of a refrigerating machine for a refrigerating vehicle of mm, width 1600 mm, height 1690 mm, and thickness 75 mm will be described.

In the experiment, a refrigerating apparatus for a refrigerating vehicle having a refrigerant storage refrigerant evaporator having a heat pipe effect during cold storage (comparative example) and a round tube 90 having a heat pipe effect during cold storage for cold storage The refrigeration system for a refrigerating vehicle (Example) 1 equipped with the refrigerant evaporator 14 was investigated to find out how the internal cold storage temperature of the regenerator changes, and the experimental results are shown in the graph of FIG. It was shown to.

As can be seen from the graph of FIG. 18, in the example, the internal temperature was kept at a value lower than −5 ° C. after 60 minutes, but in the comparative example, 6
It can be seen that the temperature inside the refrigerator reaches a value higher than −5 ° C. before 0 minutes has elapsed. Therefore, in the example,
It can be confirmed that the cold insulation performance is superior to that of the comparative example.

[Eighth Embodiment] FIG. 19 shows an eighth embodiment of the present invention and is a view showing a cold-storage refrigerant evaporator. The cold-storage refrigerant evaporator 14 of this embodiment is installed on the side surface of the freezer 3 mounted on the refrigeration vehicle 2. And
The cold-storage refrigerant evaporator 14 includes six cold-storage packs 5 in which a resin container having excellent thermal conductivity is filled with a cold-storage agent, and a circular shape in which the longitudinal directions of a plurality of straight pipe portions are extended in the width direction. It is composed of a round tube 95. In addition, round tube 9
Instead of 5, a refrigerant passage tube such as a round tube 90 may be used for the purpose of further improving the heat transfer area and the freezing ability.

The six regenerator packs 5 are round tubes 95.
Are provided so as to sandwich the four straight pipe parts, and two are arranged in parallel in the vertical direction and two in the vertical direction. FIG.
In FIG. 9, the five cold storage packs 5 are omitted. The cold-storage refrigerant evaporator 14 is attached to the side surface (side surface inside the refrigerator) of the freezer 3 by the attaching device 200.

The mounting device 200 comprises two end fixing jigs 2.
01, two middle section fixing jigs 202, six back side fixing jigs 203, three front side fixing jigs 204, coupling between them and screws for attaching these to the side surface of the freezer 3. , A plurality of fasteners 205 such as bolts and nuts.

The two end fixing jigs 201 are made of a metal plate having a U-shaped cross section, and have a round tube 95.
With the U-shaped pipe portion of the above protruding outward, the end portions of the plurality of straight pipe portions are held. The end fixing jig 201 is formed with round holes 211 and 212 through which screws and bolts are inserted. The round hole 211 has a larger opening area than the round hole 212.

The two intermediate fixing jigs 202 are arranged between the two end fixing jigs 201 and are made of a metal plate having a substantially Z-shaped cross section. These intermediate fixing jigs 2
02 is the middle part of the eight straight pipe parts of the round tube 95.
Hold in place. The intermediate fixing jig 202 is formed with a round hole 213 through which a screw and a bolt are inserted.

The six rear side fixing jigs 203 are arranged between the cold-storage refrigerant evaporator 14 and the side surface of the freezer 3, and are made of metal plates having a predetermined cross-sectional shape. The back side fixing jig 203 has round holes 214, 2 through which the fastener 205 is inserted.
15 is formed. Three front side fixing jigs 204
Is arranged on the front side of the six regenerator packs 5 and the round tube 95, and is made of a metal plate having a predetermined cross-sectional shape. Round holes 216 and 217 through which the fastener 205 is inserted are formed in the front side fixing jig 204.

The fastener 205 is also screwed into the round holes 214 and 215 of the six fixing jigs 203 so as to be interposed between the six rear side fixing jigs 203 and the three front side fixing jigs 204. The cold storage pack 5 and a plurality of straight pipe portions of the round tube 95 are attached to the side surface of the freezer 3 in a state where they are fastened and fixed.

[Structure of Ninth Embodiment] FIGS. 20 to 22.
FIG. 9 is a view showing a ninth embodiment of the present invention and showing a cold-storage refrigerant evaporator. The cold-storage refrigerant evaporator 14 of this embodiment includes a ceiling portion 300 of the freezer 3 mounted on the refrigeration vehicle 2.
It is installed in. Then, the cold-storage refrigerant evaporator 14 is
A cool storage pack group 301 in which a plurality of cool storage packs 5 (12 in this example) filled with a cool storage agent in a resin container are arranged on a plane
A round tube 95 as a refrigerant evaporation pipe for cooling the regenerator, an elastic plate member 302 arranged between the regenerator pack group 301 and the ceiling part 300, and these are attached to the ceiling part 300 of the freezer 3. And a box-shaped body 303 for Instead of the round tube 95, a refrigerant flow tube such as the round tube 90 may be used for the purpose of further improving the heat transfer area and the freezing capacity.

The elastic plate member 302 is made of a substantially flat plate-like elastic body such as sponge, air cushion, rubber, and leaf spring. As shown in FIGS. 20 and 21, the elastic plate member 302 is provided at the top plate portion 311 sandwiched between the cold storage pack group 301 and the ceiling portion 300, and at both ends of the top plate portion 311 in the longitudinal direction. It also has a pair of side wall portions 312 and a pair of side wall portions 313 provided at both ends of the top plate portion 311 in the width direction. Side wall portion 312 and side wall portion 31
3 is extended below the end of the top plate 311 so as to be sandwiched between the outer side surface of the cold storage pack group 301 and the side wall portion 321 and the side wall portion 322 of the box-shaped body 303.

The box-shaped body 303 is formed into a bottomed container shape by pressing a metal plate having excellent thermal conductivity, and has a pair of side wall portions 321 opposed to each other in the longitudinal direction and a pair of side walls opposed to each other in the width direction. Side wall portion 322 and the pair of side wall portions 3
It has a rectangular bottom wall portion 323 that connects the lower end portion of 21 and the lower end portions of the pair of side wall portions 322. Side wall 321
A flange portion 324 for fastening the box-shaped body 303 to the ceiling portion 300 with screws, bolts or the like is formed on the upper end portion of the so as to extend along the surface direction of the ceiling portion 300.

The bottom wall 323 has a round tube 9
The long groove portion 3 having a semi-circular opening shape into which the lower end side of 5 is fitted.
25 are formed. The long groove portion 325 is provided so as to meander along the plurality of straight pipe portions and the U-shaped pipe portion of the round tube 95. It should be noted that the one side wall portion 321 has a through hole 326 through which the inlet side end portion of the round tube 95 penetrates,
Further, a through hole 327 through which the outlet side end of the round tube 95 penetrates is formed.

[Effect of Ninth Embodiment] In the eighth embodiment, a large number of fixing jigs are used for the purpose of installing the cold storage refrigerant evaporator 14 having the cold storage pack 5 and the round tube 95 on the side surface of the freezer 3. However, since the number of parts is large and the number of man-hours is large, the mounting cost is increased.
Further, since the cold storage pack 5 is firmly sandwiched between the fixing jigs, the volume expansion of the cold storage agent when the cold storage agent is frozen cannot be absorbed, and the resin container of the cold storage pack 5 is damaged.

However, in this embodiment, a plurality of regenerator packs 5 are housed in the box-shaped body 303 in which the round tube 95 is arranged.
Then, the elastic plate member 302 is put on the cold storage packs 5 and fastened to the ceiling portion 300 of the freezer 3, so that the elastic plate members 302 are fixed in the upward and lateral directions and the cold storage packs are gravity-oriented in the downward direction. The group 301 is fixed. As a result, since the cold storage pack group 301 can be fixed without using a large number of fixing jigs as in the eighth embodiment, the number of work steps for mounting the cold storage pack group 301 in the freezer 3 is reduced, and the mounting cost is reduced. You can Therefore, since the low-cost refrigerant evaporator 14 for cold storage can be provided, the price of the refrigerating device for a refrigerating vehicle can be reduced.

Further, as shown in FIG. 22, even when the cold storage agent in the cold storage pack 5 freezes and the volume of the cold storage agent expands,
The elastic plate member 302 absorbs the volume expansion of the cold storage agent. Moreover, even if the refrigerating vehicle 2 vibrates greatly during traveling, the elastic plate member 302 absorbs the vibration, so that no shock is transmitted to the cold storage pack 5. Therefore, there is no concern that the resin container forming the cold storage pack 5 will be damaged.

[Structure of Tenth Embodiment] FIGS. 23 to 2
6 shows a tenth embodiment of the present invention, FIG. 23 is a view showing a refrigerating device for a refrigerating vehicle, and FIG. 24 is an electric circuit diagram showing a control panel.

In the control panel 8 of this embodiment,
In addition to the configuration of the first embodiment, a relay coil 47 is connected. The relay coil 47 is a relay switch 48 for energizing the in-compartment fan motor 32 of the in-compartment blower 6.
Open and close. In addition, the relay switch 45 has a fixed resistor 4
9 are connected in series. Therefore, in the internal fan 31 of the internal fan 6, when the relay switch 45 is closed and the relay switch 48 is opened, the internal fan motor 32 is operated at a low speed, and the blown air amount is a weak air amount (small air amount, Lo air amount). Become. On the contrary, when the relay switch 45 is opened and the relay switch 48 is closed, the internal fan motor 32 is operated at a high speed, and the blown air amount becomes a strong air amount (large air amount, Hi air amount).
Further, when both relay switches 45 and 48 are opened, they stop.

The energizing circuit of the internal fan motor 32 may be replaced with a relay circuit as described above and a semiconductor switching circuit such as a transistor may be used. In addition, the energization amount of the internal fan motor 32 is not only changed stepwise by changing the energization amount of the internal fan motor 32 by the fixed resistance 49, but also the energization amount of the internal fan motor 32 is changed. May be continuously changed by a variable resistor or the like to continuously change the rotation speed (the amount of air blown from the internal fan 31).

[Operation of Tenth Embodiment] Next, the operation of the control panel 8 of this embodiment will be briefly described with reference to FIGS. 23 to 26. Here, FIG. 25 is a flowchart showing a control program for switching between the freezing operation and the cold storage operation by the control panel 8. It should be noted that the same control as that in the flowchart of FIG.

After performing the control of step S2, the first predetermined temperature T1, the second predetermined temperature T2 and the third predetermined temperature T3 are set in accordance with the inside temperature set temperature Ts set by the inside temperature setting switch. Obtained (step S11). After that, the control of step S4 is performed.

Further, when the result of the determination in step S6 is Yes, it is determined whether it is the steady state or the cooldown after the cold storage operation or the cold storage (the initial stage of the cold storage operation or the freezing operation after the cold storage). That is, the inside temperature Ta detected by the inside temperature sensor 37 is higher than the set inside temperature Ts by about a certain temperature (for example, 10 degrees) α by a third predetermined temperature T3 (=
It is determined whether or not it has risen above Ts + Δα) (step S12).

If the determination result in step S12 is No, the electromagnetic clutch 18 of the refrigerant compressor 11 and the outside fan motor 34 are turned on, the refrigerant passage switching valve 17 is turned off, and the inside fan motor 32 is turned on. Is operated at a low speed to change the air flow rate of the internal fan 31 to the air flow rate in a steady state (Lo air flow rate),
The operation mode of the refrigeration cycle 4 is set to the refrigeration operation (step S13). Then, control of step S2 is performed.

The determination result of step S12 is Yes.
In the case of, that is, when the internal temperature Ta rises above the third predetermined temperature T3, the electromagnetic clutch 18 of the refrigerant compressor 11 and the outside fan motor 34 are turned on to switch the refrigerant flow path. With the valve 17 turned off, the internal fan motor 3
2 is operated at a high speed to increase the air flow rate of the internal fan 31 to be larger than that in the steady state (Hi air flow rate), and the operation mode of the refrigeration cycle 4 is set to the freezing operation (step S14). After that,
The control of step S2 is performed. If the determination result of step S6 is No, the process of step S9 may be performed without performing the determination of step S8.

[Effects of the Tenth Embodiment] Therefore, at the time of cooldown of the refrigerating operation after the cold storage operation or the cold keeping, that is, after the freezing operation is started, there is not much time elapsed,
When the temperature inside the freezer 3 is considerably higher than the set temperature Ts inside the refrigerator (when the temperature Ta inside the chamber is higher than the third predetermined temperature T3), the internal fan 31 of the internal blower 6 By increasing the amount of air blown from the steady state (the amount of Hi air flow), the evaporation temperature of the refrigerant evaporator 15 for refrigeration rises above the melting point of the regenerator.

As a result, among the cool storage agents in the cool storage pack 5, the cool storage agent near the round tube (pipe) 25 of the cool storage refrigerant evaporator 14 is melted. Along with that, the refrigerating refrigerant evaporator 1
As the refrigerant enthalpy on the inlet side of No. 5 decreases,
It is possible to improve the cooling performance (cooldown performance, in-chamber cooling performance) in the freezer 3 during the cooldown of the freezing operation in FIG. 26C than in the steady state of the freezing operation in FIG. it can.

In the cool-down of the refrigerating operation as described above, contrary to the cold-storage operation in which the cold storage agent outside the cold-storage pack 5 preferentially melts, the round tube (pipe) of the cold-storage refrigerant evaporator 14 is arranged. Since the regenerator in the vicinity of 25 melts, the latent heat of fusion of the regenerator is recovered by the refrigerant flowing through the round tube 25, so that the latent heat of fusion of the regenerator is not only used during cold storage operation or cold storage, but also during the cold storage operation or It can be effectively used even during freezing operation after keeping cold.

[Modification] In this embodiment, the freezer mounted on the refrigerating vehicle is used as the heat insulating compartment, but a refrigerator mounted on the refrigerating vehicle may be used as the heat insulating compartment. Moreover, you may use the cold-and-warm warehouse which can also heat-retain as an adiabatic warehouse. further,
The present invention may be applied not only to automobiles but also to refrigeration systems for railway vehicles. Then, the present invention may be applied to a cold storage device in a container, a freezing device such as a stationary freezer or a refrigerator, or a freezing device such as various regenerators.

[0141]

According to the invention described in claim 1, since the refrigerant evaporator for cold storage and the refrigerant evaporator for refrigeration are connected in series, refrigeration of the refrigeration cycle is achieved while reducing the number of accessories for the refrigeration cycle. The operation and the cold storage operation can be efficiently operated.

According to a fourth aspect of the present invention, a refrigerating refrigerant evaporator is connected to the downstream side of the cold accumulating refrigerant evaporator, and the high temperature and high pressure refrigerant discharged from the refrigerant compressor is evaporated into the cold accumulating refrigerant. Since the device is bypassed and the refrigerant refrigerant is directly flown into the refrigerant refrigerant evaporator for freezing, it is possible to defrost the refrigerant evaporator for freezing without melting the cold storage agent in the refrigerant evaporator for cold storage.

According to the fifth aspect of the present invention, since a sufficient circulation amount corresponding to the high load operation can be obtained during the high load operation, the inside air in the heat-insulated warehouse is sufficiently refrigerated It is possible to suppress deterioration of down performance. Further, even during low load operation, the throttle valve can be moved in the second throttle portion within a range in which the degree of superheat of the refrigerant can be controlled, so that hunting of the throttle valve can be prevented.

According to the sixth aspect of the present invention, in contrast to the conventional heat absorption method of absorbing heat only on the surface of the resin container, by adding heat pipe heat absorption by the refrigerant passage pipe, It is possible to improve the cold insulation performance of air. The invention according to claim 7 can improve the cooling performance in the heat insulation chamber by melting the cold storage agent in the initial stage of the cold storage operation or the freezing operation after the cold storage. At this time, the evaporation temperature of the refrigerant evaporator for refrigeration rises, so that the cold storage agent melts from the vicinity of the refrigerant evaporator for cold storage. As a result, the latent heat of fusion of the cold storage agent can be effectively used.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing a refrigeration cycle of a first embodiment of the present invention.

FIG. 2 is a perspective view showing a refrigeration vehicle equipped with the first embodiment of the present invention.

FIG. 3 is a perspective view showing a cold-storage refrigerant evaporator according to the first embodiment of the present invention.

FIG. 4 is an electric circuit diagram showing the control panel of the first embodiment of the present invention.

FIG. 5 is a flowchart showing the operation of the control panel according to the first embodiment of the present invention.

FIG. 6 is a time chart showing the operation of the first embodiment of the present invention.

FIG. 7 is a sectional view showing a cold-storage refrigerant evaporator according to a second embodiment of the present invention.

FIG. 8 is a sectional view showing a cold-storage refrigerant evaporator according to a third embodiment of the present invention.

FIG. 9 is a sectional view showing a thermostatic expansion valve according to a fourth embodiment of the present invention.

FIG. 10 is a sectional view showing a thermostatic expansion valve according to a fourth embodiment of the present invention.

FIG. 11 is a graph showing the relationship between the valve opening degree of the automatic temperature expansion valve and the refrigerant circulation amount according to the fourth embodiment of the present invention.

FIG. 12 is a configuration diagram showing a refrigeration cycle of a fifth embodiment of the present invention.

FIG. 13 is a sectional view showing a solenoid valve with a bleed port according to a fifth embodiment of the present invention.

FIG. 14 is a sectional view showing a thermostatic expansion valve of a sixth embodiment of the present invention.

FIG. 15 is a sectional view showing a thermostatic expansion valve according to a sixth embodiment of the present invention.

FIG. 16 is a sectional view showing a refrigeration vehicle equipped with a seventh embodiment of the present invention.

FIG. 17 is an enlarged view showing a main part of a cold-storage refrigerant evaporator according to a seventh embodiment of the present invention.

FIG. 18 is a graph showing the cold insulation performance after freezing the cold storage agent of the seventh embodiment of the present invention.

FIG. 19 is a schematic view showing a cold-storage refrigerant evaporator according to an eighth embodiment of the present invention.

FIG. 20 is an exploded view showing a cold-storage refrigerant evaporator according to a ninth embodiment of the present invention.

FIG. 21 is a sectional view schematically showing a cold-storage refrigerant evaporator according to a ninth embodiment of the present invention.

FIG. 22 is a sectional view showing the outline of a cold-storage refrigerant evaporator according to a ninth embodiment of the present invention.

FIG. 23 is a configuration diagram showing a refrigeration cycle of a tenth embodiment of the present invention.

FIG. 24 is an electric circuit diagram showing a control panel of a tenth embodiment of the present invention.

FIG. 25 is a flow chart showing the operation of the control panel of the tenth embodiment of the present invention.

FIG. 26 is an explanatory diagram showing the control characteristics of the tenth embodiment of the present invention.

FIG. 27 is a configuration diagram showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Refrigerating device for refrigerating vehicles (refrigerating device for vehicles) 3 Freezer (insulator) 4 Refrigeration cycle 5 Cooling pack (resin container) 6 Blower (air blowing means) 8 Control panel (control means) 11 Refrigerant compressor 12 Refrigerant condenser 13 Automatic temperature expansion valve 14 Refrigerant evaporator for cold storage 15 Refrigerant evaporator for refrigeration 17 Refrigerant flow path switching valve (refrigerant flow path switching means) 23 Temperature sensitive tube (refrigerant temperature detection means) 29 First refrigerant flow path 30 Second Refrigerant Channel 37 Internal Temperature Sensor (Internal Temperature Detection Means) 51 Cold Storage Agent 61 First Ball Valve 62 Second Ball Valve (Throttle Valve) 65 First Throttle Hole (First Throttle Portion) 66 Second Throttle hole (second throttle part) 75 Bleed port (first throttle part) 76 Solenoid valve 90 Round tube (refrigerant passage pipe)

Front page continuation (72) Inventor Kiyoshi Kase 1-1, Showa-cho, Kariya city, Aichi prefecture

Claims (7)

[Claims] 1. A heat-insulating cabinet provided so as to be heat-insulated from the outside, (b) an in-compartment air-blowing means for convection of air in the heat-insulating cabinet, and (c) a cool storage agent for keeping the inside of the heat-insulating cabinet cool. And (d) a cold storage refrigerant evaporator that cools the cold storage agent, and a freezing refrigerant that is connected in series to the cold storage refrigerant evaporator and that cools the air that convects inside the adiabatic storage by the operation of the internal ventilation unit. An evaporator and a refrigerating cycle having a temperature automatic expansion valve that is connected in series to the refrigerating refrigerant evaporator and that adjusts the circulating amount of the refrigerant based on the temperature change of the refrigerant at the outlet of the refrigerating refrigerant evaporator; ) A freezing operation of freezing the inside of the adiabatic chamber by the refrigerating refrigerant evaporator by operating the in-compartment air blowing means and a stop of the operation of the in-compartment air blowing means, and the regenerator by the cold storage refrigerant evaporator. And a refrigerating apparatus having a control means for performing a cold storage operation for freezing Place. 2. The refrigerating apparatus according to claim 1, wherein the control means has a compartment temperature detection means for detecting a compartment temperature in the heat insulation compartment, and the compartment temperature detection means detects the compartment temperature. A refrigerating apparatus, which stops the operation of the in-compartment air-blowing means when the temperature inside the heat-insulated warehouse falls below a predetermined temperature. 3. The refrigerating apparatus according to claim 2, wherein the cold storage agent has the same evaporation temperature as the refrigerant in the refrigerating refrigerant evaporator when the temperature inside the heat insulating warehouse drops below a predetermined temperature. A refrigerating device having a freezing point of a certain degree. 4. The refrigerating apparatus according to claim 1, wherein the refrigerating cycle includes a refrigerant compressor, a refrigerant condenser, the temperature automatic expansion valve, the cold storage refrigerant evaporator, and the refrigerating machine. Refrigerant evaporator is sequentially connected along the flow direction of the refrigerant, the refrigerant discharged from the refrigerant compressor, the refrigerant condenser,
The temperature automatic expansion valve, the first refrigerant flow path that flows into the freezing refrigerant evaporator through the cold storage refrigerant evaporator, the refrigerant discharged from the refrigerant compressor, the temperature automatic expansion valve, the cold storage refrigerant A second refrigerant flow path that bypasses the evaporator and flows into the refrigeration refrigerant evaporator; and a refrigerant flow path switching unit that switches between the first refrigerant flow path and the second refrigerant flow path. Characterizing refrigeration equipment. 5. The refrigerating apparatus according to claim 1, wherein the refrigeration cycle has a first throttle portion that adiabatically expands the refrigerant only during low load operation, and the temperature automatic expansion valve. Is a second throttle portion which is provided on the downstream side of the first throttle portion and adiabatically expands the refrigerant, a refrigerant temperature detecting means for detecting the refrigerant temperature at the outlet of the refrigerating refrigerant evaporator, and the refrigerant temperature detecting means. A refrigerating apparatus having a throttle valve for adjusting the opening degree of the second throttle portion in accordance with the refrigerant temperature detected in step. 6. The refrigerating apparatus according to claim 1, wherein the cold-storage refrigerant evaporator has a refrigerant flow pipe through which a refrigerant for cooling the regenerator flows, and the refrigerant. A refrigerating apparatus comprising a resin container which covers the periphery of an upper portion of the refrigerant flow passage pipe in a state where a lower portion of the flow passage pipe is projected downward and which has a regenerator enclosed therein. 7. The refrigerating apparatus according to any one of claims 1 to 6, wherein the control means has a compartment temperature detection means for detecting a compartment temperature in the heat-insulated compartment, and A refrigerating apparatus characterized in that, when the temperature inside the adiabatic chamber detected by the temperature detecting means rises above a predetermined temperature higher than a set temperature, the amount of air blown by the inside air blowing means is increased from that in a steady state. .