JPS5852958A - Refrigerator - Google Patents

Abstract

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

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a refrigeration system using a high-pressure container-type hermetic compressor.

In small refrigeration equipment that uses a high-pressure container-type hermetic compressor (hereinafter referred to as a rotary compressor) like a general rotary compressor, the inside of the closed container is on the high-pressure side, so a low-pressure container-type hermetic compressor like a general reciprocating compressor is used. Compared to a hermetic compressor (hereinafter referred to as a reciprocating compressor), the amount of refrigerant sealed in the refrigeration system is significantly increased. As an example, in a popular refrigerator-freezer, the amount of refrigerant filled is about 1,502 liters for a reciprocating type, while for a rotary type, it is about 250 liters of refrigerant.
It becomes about 9, which is a large increase of more than so%. A portion of this 10o1 increase in refrigerant is converted into high-temperature, high-pressure superheat gas, and a portion is dissolved in the refrigerating machine oil and remains in the closed container. These high-temperature, high-pressure refrigerants are in a gas state when the refrigeration equipment is stopped due to the action of the temperature controller of the refrigeration equipment, and those dissolved in the refrigeration oil are vaporized and heated in the high-temperature part of the sealed container. The gas becomes a high-temperature, high-pressure superheat gas and flows into the pumporator. As the first flow path, it flows into the sealed container - condenser capillary - two evaporator, and as the heat is dissipated by the condenser, it flows as superheated gas at room temperature, but the temperature difference with the evaporator is very large, so the evaporator is heated. However, it had the disadvantage of causing a large heat load. In addition, as the second flow path, the high-temperature, high-pressure superheat gas flows into the closed container, the cylinder chamber of the compression element, the suction line, and the evaporator as it is, heating the evaporator, which also has the drawback of causing a large heat load.

The high-temperature, high-pressure gas in the closed container flows into the cylinder chamber because the cylinder chamber of existing rotary compressors is configured with a mechanical seal made of metal surface contact. That is, in the refrigeration system using this rotary compressor, a large amount of high-temperature, high-pressure superheat gas flows into the evaporation lake, resulting in a large heat load. Therefore, we actually installed a rotary compressor, which is about 20% more efficient than a conventional reciprocating compressor, in a refrigerator-freezer and achieved JIS C9.
When measured in power consumption tests of 607 electric refrigerators and electric freezers, the effect was significantly reduced, and the power saving amount was only about 6%. In order to increase the amount of reduction in power consumption equivalent to the efficiency improvement of the rotary compressor, it is necessary to The purpose is to prevent a large amount of superheat gas from flowing into the evaporation lake from the second flow path.

The method currently used in some cases is to improve the second flow path, which is to install 4-check pulp in the suction line of the refrigeration equipment, but since the first flow path has not been improved, its effectiveness is is small, and the reduction in power consumption is only about 5%, which is a total effect of about 10%. In addition, a possible method for improving the first flow path is to install a solenoid valve at the condenser outlet and open and close it in conjunction with the operation of the refrigeration equipment, but solenoid valves are expensive and generate noise during operation. Furthermore, a control circuit for the solenoid valve is required, which complicates the electric circuit, and the valve itself consumes electric power.

In view of the above drawbacks, the present invention is an energy-saving refrigeration system that is inexpensive, does not require electrical control, is quiet, and has an efficiency equal to or higher than that of a rotary compressor alone. The aim is to provide refrigeration equipment.

An embodiment of the present invention will be described below. A rotary compressor 1 is composed of a closed container 2, a compression element 3, and an electric element (not shown).

Actually, this rotary compressor 1 is not equipped with a check valve inside. A refrigeration system c, a rotary compressor 1, a condenser 4, a high pressure circuit 5a of a fluid control valve 5 which is the main part of the present invention, a capillary tube 6, an evaporator 7, a low pressure circuit sb of the fluid control valve 6, a suction line 8. rotary compressor 1
are sequentially connected in a ring. The fluid control valve 5 is arranged substantially vertically so that the high pressure circuit 6a is at the top and the low pressure circuit 6b is at the bottom. The fluid control valve 6 has an outer shell 11 formed by a substantially hollow cylindrical high-pressure side casing 9 and a substantially hollow cylindrical low-pressure side casing 10 to maintain airtightness.

The outer shell 11 is partitioned into a high voltage circuit 6a and a low voltage circuit 5b, and has a bellows 1 that expands and contracts in response to the pressure of the two circuits.
2 are installed. At the center of the lower end of the bellows 12 is a coil spring 1 that urges the bellows 12 upward in the figure.
3, holding the coil spring 13 below it,
It has a retainer 14 that restricts excessive movement of the bellows 12 and prevents damage.

The retainer 14 has a plurality of small holes 14a+ for the bellows 12 to correctly sense the pressure of the low pressure circuit 6b.
14 am-a-am is set. This retainer 14 is held between the sinks 9 and 10. On the other hand, the high-pressure side casing 9 has an inlet pipe 9a, an outlet pipe 9b, and a valve seat 9ci, and a cylindrical plunger 16 is housed substantially in the center so as to be slidable up and down. A high pressure valve 16 made of a ball valve is fixed to the center of the upper end of the plunger 16 by caulking to form a high pressure side valve device 17.

A plunger 16 and a bellows 1 are attached to the lower end of the plunger 15.
A recess 16a is provided for integrally attaching the bellows 12 and the bellows 12 is integrally clamped and supported by caulking. The low pressure side casing 10 also has an inlet pipe 10a, an outlet pipe 1ob, and a valve seat 10c.

A notch 18a forming a gas passage is provided at the outer edge of the shaft.
A low-pressure valve 18 consisting of a leaf valve provided with is movably housed. Above the low-pressure valve 18, a strut 19 is installed in the low-pressure side casing 1 to restrict excessive movement of the low-pressure valve 18.
0 to form a low pressure side valve device 2o.

Next, we will discuss the effect. Figure 1 shows a state diagram when the refrigeration system is in operation.The high pressure side of the refrigeration system is at normal high pressure, and the low pressure side is also at normal low pressure, so the bellows 12 of the fluid control valve 6 is under high pressure. The pressure difference between the circuit 6a and the low pressure circuit 6b pushes down the coil spring 13, and the retainer
It extends until it hits 14. Therefore, the high-pressure valve 16 is pulled away from the valve seat 9C by the sum of the pressure difference between the high-pressure circuit 6a and the evaporator 7 and the biasing force of the coil spring 13 by the plunger 15 that is integrally attached to the bellows 12. The high pressure side valve device 17 is in an open state. On the other hand, the low pressure valve 18 of the low pressure side valve device 20 is blown up by the gas flow flowing in from the evaporator 7 and separated from the valve seat 10c.

It comes into contact with the stopper 19. Gas flows through the gap between the notch 18a on the outer edge of the low pressure valve 18 and the stopper 19 without any problem as shown by the arrow a in the figure, and the low pressure side valve device 2o is in an open state. Therefore, the refrigerant gas discharged from the rotary compressor 1 is transferred to the condenser 4. High pressure circuit 5a of fluid control valve 5, cabil') - cheap 8, evaporation 7
．． Low pressure circuit 6b of fluid control valve 6, Zaku 1 joint line 8
．． It flows without any hindrance to the rotary compressor 1 and performs the refrigeration action.

Next, FIG. 2 shows a state in which the refrigeration equipment is stopped.

This will be explained using FIG. When the rotary compressor 1 stops, the gas flow from the evaporator 7 stops, so the low pressure valve 18 in the low pressure circuit 6b of the fluid control valve 6 falls under its own weight and contacts the valve seat 10C, closing the low pressure side valve device 20. Make it. As a result, the soot heat gas from the rotary compressor 1 is prevented from flowing back into the evaporator 7. As time further passes, the superheated gas in the closed container 2 flows into the cylinder chamber (not shown) of the compression element 3, and further flows into the suction line 8.
Since it flows into the low pressure circuit 6b of the fluid control valve 6 (as indicated by the arrow in the figure), the pressure in the low pressure circuit 6b rapidly increases and becomes approximately the pressure in the high pressure circuit 6a. When the pressures in both circuits 6a and 5b become approximate, the biasing force of the coil nose 13 provided below the bellows 12 overcomes the force generated in the bellows 12 due to the pressure difference between the two circuits 5a and 5b, and the plunger 16 is pushed. ''The high pressure side valve device 17 becomes closed.

Prevents suit gas from flowing into the volley tank from the condenser 4.

Furthermore, the action of the coil spring 13 that urges the bellows 12 upward will be explained using the pressure change diagram of the refrigeration system shown in FIG. In the figure, at the same time as the rotary compressor 1 stops, the low-pressure side valve device 20 becomes closed, and the pressure in the low-pressure circuit 6b rapidly increases due to the superheat gas flowing back from the rotary compressor 1. At this time, the high-pressure side valve device 17 is still in an open state, and the pressures in the capacitor 4 and the high-pressure circuit 5d gradually drop to the same extent. When a minute time t has elapsed after this stop, a force FP (FP-ΔPxS) is generated due to the differential pressure ΔP between the high-pressure circuit 6a and the low-pressure circuit 5b acting on the bellows 12 and the effective area S of the bellows 12.
In contrast, the biasing force FC of the coil spring 13 increases, the plunger 15 is pushed up, and the high pressure side valve device 17 is brought into a closed circuit state.

From this point on, the refrigerant flowing into the high-pressure circuit 6a stops, so the pressure in the outlet pipe 9a of the high-pressure circuit 6a drops rapidly.

This pressure drop causes the ball valve 16 to be further attracted to the valve seat 9C, reducing leakage. Furthermore, rotary compressor 1
After stopping, there is a short time t until the high pressure side valve device 17 closes.
must be approximately 30 seconds or less. This 30 seconds or less depends on the size of the refrigeration equipment and the rotary compressor 1.
Approximately 45 seconds to 1 hour after the freezing equipment stops, depending on the size of the
This is because the liquid refrigerant condensed in the condenser 4 flows into the capillary tube 6 and performs a normal refrigeration action for about a minute, so it is sufficient to close the high-pressure side valve device 17 before that time.

For this purpose, it is necessary to make the minute time t as small as possible.

In order to reduce the pressure, when the differential pressure ΔP is large, the high pressure side valve device 1
7 to close the valve. PeCff-, (Since the biasing force of 12 itself is not very large due to its structure, in order to increase it, a coil spring 13 is provided to increase the biasing force, so that even if the differential pressure ΔP is large, the valve closes and the minute time t to 3
It is designed to be compatible with all types of refrigeration equipment as it takes less than 0 seconds. When starting up the refrigeration system, the low pressure circuit 6b
The pressure becomes low instantaneously, the bellows 12 is pulled downward, the ball valve 16 integrated with the bellows 12 via the plunger 15 is lowered, and the high pressure side valve device 17 opens to perform normal refrigeration.

As described above, the refrigeration system of the present invention includes a fluid control valve, and the high pressure side valve device of the fluid control valve is connected between a condenser and a pressure reducer such as a capillary cheese, and the low pressure side valve device has a check pulp function. The device is connected to the suction line between the evaporator and the rotary compressor, and the high-pressure side valve device responds to the pressure by opening when the pressure in the low-pressure circuit is low and closing when it is high. When the equipment is in operation, normal refrigerant circulation occurs, and when the refrigeration equipment is stopped, the low-pressure side valve device, which has a check valve function, immediately closes, and at the same time the pressure in the low-pressure circuit suddenly increases, and the liquid refrigerant depressurizes the high-pressure side valve device. Since the valve is closed during a short period of time when the gas is flowing out into the device, superheated gas in the closed container and the condenser is prevented from flowing into the evaporator via the suction line and the pressure reducing device. Therefore, the power saving effect is greater than that of a device without a fluid control valve, and since both of the valve devices are integrally formed for heat exchange, the low temperature superheat gas, which is the rejected heat flowing out of the evaporator, is used to condense the capacitor. By supercooling the liquid refrigerant flowing out, the refrigeration effect can be increased, and power consumption can be further reduced. In addition, it is less expensive than those controlled by solenoid valves, does not require electric power, does not require a control circuit, does not require extra electrical wiring, and operates smoothly, so it does not generate noise. It has the following characteristics.

In addition, when the refrigeration equipment is stopped, the high-pressure side valve device is closed by installing a coil spring below the bellows that biases the bellows, so the valve closes while the liquid refrigerant is passing through when the high-low pressure circuit is stopped with a large differential pressure. Therefore, C1-, t: This has the advantage that there is no fear that the superheat gas will mix into the evaporator and flow out unlike when it relies on its own biasing force.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view of the main part of a refrigeration system showing an embodiment of the present invention when it is in operation, FIG. FIG. 3 is a pressure change diagram of the refrigeration device shown in FIG. 1. Rotary compressor (hermetic compressor) 4. Capacitor 6.
Pressure reducer, 7°6.060. Evaporator, 5,...
,, fluid control valve, 5a00099. high voltage circuit, s b
,,,00. Low voltage circuit, 12,. aaa++*a bellows, 13,,,,,,, coil spring, 16°00000. High pressure valve, 17,,,,,,
High pressure side valve device, 18°...Low pressure valve, 20...
...Low pressure side valve device. Name of agent: Patent attorney Toshio Nakao and 1 other person 1st
Figure 1 Figure 2

Claims (3)

[Claims] (1) Consists of a high-pressure vessel-type hermetic compressor, a condenser, a pressure reducer, an evaporator, a suction line, a fluid control valve, etc., and the fluid control valve includes a high-pressure side valve device including a high-pressure valve and a high-pressure circuit, a low-pressure valve, and a fluid control valve. a low pressure side valve device including a low pressure circuit, the high pressure side valve device being upstream of the pressure reducer;
The low-pressure side valve devices are each connected to the downstream side of the evaporator, and the high-pressure valve operates based on the pressure difference between the high-pressure circuit and the low-pressure circuit and remains closed when the pressure approaches, and the low-pressure valve is reversely connected. The movable valve body of the high-pressure valve is integrally connected to a pressure-responsive body based on the pressure difference between the high-pressure circuit and the low-pressure circuit by a connecting means, and the pressure-responsive body is connected to the high-pressure side by a spring. A refrigeration device biased in the direction of closing. (2) The refrigeration system according to claim 1, wherein the high-pressure side valve device and the low-pressure side valve device are arranged in a heat exchange relationship. (3) The refrigeration system according to claim 1, wherein the fluid control valve integrally comprises the high-pressure side valve device located above and the low-pressure side valve device located below.