JPS5899650A - 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 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 charged is about 16 oy for a reciprocating type, while for a rotary type it is about 26 oy.
This is a huge increase of more than 50%. A portion of this 100 f 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 regulator of the refrigeration equipment, and those dissolved in the refrigeration oil are vaporized and stored in the high-temperature part of the sealed container. It is heated and becomes a high-temperature, high-pressure superheat gas that flows into the Enoku Porator. As the first flow path, it flows from the sealed container to the condenser to the capillary tube to the 3-7 reactor, 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. This has the disadvantage that the evaporator is heated, resulting in a large heat load. In addition, as a second flow path, the high-temperature, high-pressure superheat gas flows into the closed container → the cylinder chamber of the compression element → the suction 2-in → the evaporator as it is, heating the evaporator, which also has the disadvantage 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 evaporator, resulting in large heat negative spinning. Therefore, the only place where a rotary compressor, which is about 20% more efficient than a conventional reciprocating compressor, was actually attached to a refrigerator-freezer and measured in the JIS C9607 power consumption test for electric refrigerators and electric freezers. In order to increase the amount of reduction in power consumption equivalent to the efficiency improvement of the rotary compressor, it is necessary to Second
The purpose is to prevent a large amount of superheated gas from flowing into the evaporator from the flow path. The method currently used in some cases is to improve the second flow path, and is to provide a check pulp in the suction line of the refrigeration equipment.
Since the first flow path has not been improved, the effect is small, and the reduction in power consumption is only about 6%, which is a total effect of about 10%. Another possible method for improving the first flow path is to install a solenoid valve at the outlet of the condenser 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 aims to provide a 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 leaf 6-basin presser alone. The purpose is to provide an energy-saving refrigeration system.

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).

Moreover, this rotary compressor 1 is not equipped with a check valve inside. The refrigeration system c, the rotary compressor 1, the condenser 4, the high pressure circuit 5& of the fluid control valve 6 which forms the main part of the present invention, and the pressure reducer 6. Evaporator 7, low pressure circuit 5b of the fluid control valve 6, suction line 8. The rotary compressor 1 is sequentially connected in an annular manner.

The fluid control valve 6 has a high pressure circuit 6a at the top and a low pressure circuit 6b.
It is arranged almost vertically so that the bottom is at the bottom.

The fluid control valve 6 has a substantially hollow cylindrical high-pressure side casing 9
The outer shell 11 is formed by the low-pressure side casing 1o, which is also approximately hollow and cylindrical, and maintains airtightness. Said outer shell 11.
The inside is partitioned into a high voltage circuit 6a and a low voltage circuit 6b, and the above-mentioned 2
A pressure-responsive body 12 made of a bellows that expands and contracts in response to circuit pressure is provided. A coil spring A13 for biasing the pressure responsive body 12 upward in the figure is provided at the center of the lower end of the responsive body 12, and the coil spring 13 is held below the coil spring A13, and the pressure responsive body 12
It has a retainer 14 that restricts excessive movement of the retainer and prevents damage. The tiner 14 is provided with a plurality of small holes 14a, 14a, . . . for the pressure responsive body 12 to correctly sense the pressure of the low pressure circuit 6b.

This retainer 14 is held between the two parts 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 9c, and a cylindrical plunger 16 is housed in a substantially central shaft 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 15 by caulking to form a high pressure side valve device 17. At the lower end of the plunger 16, there is a plunger 16 and a pressure responsive body 12 at the lower end of the plunger 16.
A recess 15a is provided for integrally mounting the pressure-responsive body 12, and the pressure-responsive body 12 is integrally clamped and supported as shown in page 7. The inlet pipe 10a is still connected to the low pressure side casing 1o,
The outlet pipe 1ob has a lower valve seat 10C at a position opposite to the inlet pipe 10a of the low-pressure side casing 1°, and furthermore, a cut is provided at the upper part facing the lower valve seat 10c to form a gas passage at the outer edge. A notch 18a is provided to movably house a low pressure valve 18 which is a valve. Above the low pressure valve 18 is a valve seat ring 19 that forms the main valve seat 1od of the low pressure valve 1B.
is press-fitted and fixed to the low-pressure side casing 10.

Further, above the valve seat ring 19, a check pulp 20 made of a leaf valve having a notch 20a forming a gas passage at its outer edge is movably housed. Further, a stopper 21 for regulating the movement of the check pulp 2o is press-fitted and fixed into the low pressure side casing 1°. A valve seat 22 is formed on the upper surface of the valve seat ring 19 at a portion facing the check pulp 2o. A spring B23 is provided between the low pressure valve 18 and the low pressure side casing 10 surface forming the lower valve seat 1oC to bias the low pressure valve 1B in the direction of pressing the upper main valve seat 10d. It is set up. Furthermore, an actuating section 24 is a rod that is welded and fixed to the lower surface of the recess 15a in the lower part of the pressure-responsive body 12, passes through the retainer 14, further passes through the check pulp 2°, and reaches the low-pressure valve 18. , forming a low pressure valve device 26.

Next, we will discuss the effect. FIG. 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 pressure responsive body 12 of the fluid control valve 5 The coil spring 13 is pushed down by the pressure difference between the high voltage circuit 6a and the low voltage circuit 5b, and is expanded until it hits the retainer 14. Therefore, the high pressure valve 16 is a plunger 16 integrally attached to the pressure responsive body 12.
As a result, the valve seat 9C that was attracted to the valve seat 9C by the sum of the pressure difference in the high pressure circuit 6a and the evaporator T and the biasing force of the coil spring 13 is separated, and 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 25 is biased toward the main valve seat 10d by the spring B23, and is spaced apart from the valve seat 10c, and the upper surface of the low pressure valve 18 and the operating portion 249 are The low pressure valve 18 and the main valve seat 1od abut at a position where a gap is created between them. Further, the check pulp 20 is blown up in the gas flow, moves away from the valve seat 22, and comes into contact with the stopper 21. The gas passes through the notch 18a on the outer edge of the low pressure valve 18, passes through the valve seat ring 19, and flows without hindrance from the gap between the notch 20a on the outer edge of the check pulp 20 and the stopper 21 as shown by arrow a in the figure. The low pressure side valve device 26 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 6, pressure reducer 6, evaporator 7, low pressure circuit 5b of fluid control valve 5, suction line 8
, flows to the rotary compressor 1 without any hindrance 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 check pulp 20 in the low pressure circuit 5b of the fluid control valve 5 stops.
falls under its own weight and contacts the valve seat 22, temporarily stopping the gas flow.

1o bae.

As time passes, the superheated gas in the closed container 2 flows into the cylinder chamber (not shown) of the compression element 3, further into the suction line 8, and then into the low pressure circuit 5b of the fluid control valve 5 (as indicated by the arrow in the figure). (shown above), the pressure in the low-pressure circuit 5b rises rapidly and becomes approximately the pressure in the high-pressure circuit 6a. When the pressures in both circuits 5a and 5b become approximate, the biasing force of the coil spring 13 provided below the pressure-responsive body 12 overcomes the force generated in the pressure-responsive body 12 due to the pressure difference between the circuits sa and 5b, and the plunger 15 is activated. The high-pressure side valve device 17 is pushed up and becomes a closed circuit state, thereby preventing superheat gas from flowing into the evaporator from the condenser 4. Furthermore, at the same time, the actuating part 24 welded and fixed to the lower surface of the recess 15a at the lower part of the pressure-responsive body 12 is also pulled upward, and its lower end is released from contact with the low-pressure valve 18, and at the same time, the low-pressure valve 18 is released. , main valve seat 1 by spring B23
Pressed to 0d. At that time, the lower end of the actuating part 24 is completely separated from the low pressure valve 18, so the low pressure valve reliably comes into contact with the main valve seat 1 od <, so the leakage is completely stopped at the 11 page and the low pressure side valve device 26 is closed. . As a result, the superheat gas from the rotary compressor 1 is prevented from flowing backward into the evaporator 7.

Furthermore, the action of the coil spring 13 that urges the pressure-responsive body 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 26 becomes temporarily closed, and the pressure in the low-pressure circuit 5b 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 6a are equal and gradually drop.

When a minute time t has elapsed after this stop, a force Fp (7
The biasing force F of the coil spring 13 with respect to p=ΔPx S
The sib gear 15 with a large c is pushed up, and the high pressure side valve device 17 is brought into a closed state. At this point, the high voltage circuit 6a
Since the refrigerant flowing into the outlet pipe 9 of the high pressure circuit 6a is stopped,
The pressure at a drops rapidly. This pressure drop causes the high pressure valve 16 to be further attracted to the valve seat 9C, reducing leakage. Note that after the rotary compressor 1 stops, the high pressure side valve device 17
The minute time t required for the circuit to close needs to be about 30 seconds or less. This 30 seconds or less depends on the size of the refrigeration equipment,
Depending on the size of the rotary compressor 1, the liquid refrigerant condensed in the condenser 4 flows into the capillary tube 6 for about 46 seconds to 1 minute after the refrigeration system stops, and normal refrigeration occurs. This is because it is sufficient to close the high pressure side valve device 17. For this purpose, it is necessary to make the minute time t as small as possible, and for this purpose, the high pressure side valve device 17 is closed when the differential pressure ΔP is large. The biasing force of the pressure-responsive body 12 itself is not very large due to its structure, so 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 is It is designed to be compatible with all types of refrigeration equipment as it takes less than 30 seconds. When the refrigeration system is started, the pressure in the low pressure circuit 6b instantly becomes low, the pressure responsive body 12 is pulled down, and the high pressure valve 16 integrated with the pressure responsive body 12 via the plunger 15 is lowered. However, when the high-pressure side valve device 17 opens, the actuator 24 simultaneously pushes the low-pressure valve 18 downward, creating a gap between it and the upper valve seat 10d, allowing normal refrigeration to occur. Although a spring B23 is provided to bias the low pressure valve 18 in the direction of pressing the upper valve seat 10d, the same effect can be achieved even if the low pressure valve 18 and the actuating part 24 are formed integrally. It is.

As described above, the refrigeration system of the present invention includes a fluid control valve, the high pressure side valve device of the fluid control valve is connected between a condenser and a pressure reducer such as a capillary tube, and the low pressure side valve device having a check pulp function is It is connected to the suction line between the evaporator and the rotary compressor, and the high-pressure side valve device opens when the pressure in the low-pressure circuit is low and closes when it is high, so the refrigeration equipment can operate. The refrigerant circulates normally inside, and the refrigeration system stops 4
・ .

The low-pressure side valve device, which has a check pulp function in the soil, closes immediately, and at the same time, the pressure in the low-pressure circuit suddenly increases, and the high-pressure side valve device closes during the minute period when liquid refrigerant flows out to the pressure reducing device. Prevent superheated gas in the closed container and condenser from flowing into the evaporator via the suction line and pressure reducer. Therefore, the power saving effect is greater than that of a device without a fluid control valve, and since both valve devices are integrally formed for heat exchange, the low-temperature super heat scum, which is the waste cold heat flowing out of the evaporator, is used to condense the capacitor. The liquid-refrigerant that flows out is supercooled, increasing the refrigeration effect and further reducing power consumption. 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. Furthermore, when the low-pressure side valve device opens and closes, the high-pressure side valve device opens the valve, and the actuating section presses the low-pressure valve downward, the low-pressure side valve device opens, and when the high-pressure side valve device closes, the operating section is pulled upward, and the low pressure valve closes the low pressure side valve device, so the high and low pressure side valve devices operate reliably in conjunction with each other, and the operating time is constant, so a stable operating effect can be achieved. It is something that can be obtained.

Furthermore, since the valve closing action is performed in conjunction with the pressure responsive body on the high pressure side and the pressure responsive body on the low pressure side, a reliable operating effect can be obtained regardless of the installation state.

[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 during operation, Fig. 2 is a cross-sectional view of the main part of the fluid control valve during stop operation corresponding to Fig. 1, and Fig. 3 is a cross-sectional view of the main part of the fluid control valve during operation. FIG. 2 is a pressure change diagram of the refrigeration system shown in FIG. 1; 1... Rotary compressor (hermetic compressor), 4... Capacitor, 6... Pressure reducer S7... Evaporator, 5... Fluid control valve, 5a1111@1111@high pressure circuit, 5b,
, , , ,Low voltage circuit, 12 , ,. ...Pressure-responsive body, 13...3 illumination spring, 18.
...0. High pressure valve, 17, high pressure side valve device,
1 B... Low pressure valve, 24... Actuation part, 25... Low pressure side valve device. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 4 WA2 diagram

Claims (1)

[Claims] A cooling system is formed by a hermetic compressor, a condenser, a pressure reducer, an evaporator, a suction line, a fluid control valve, etc., and the fluid control valve is connected to the upstream side of the pressure reducer to stop the flow of high-pressure refrigerant, as well as a high-pressure A high-pressure side valve device including a circuit, a low-pressure valve connected to the downstream side of the evaporator to prevent backflow, and a low-pressure side valve device including a low-pressure circuit, and the low-pressure side valve device is provided between the low-pressure circuit and the high-pressure circuit when the pressure difference becomes large. A pressure-responsive body that opens the high-pressure valve and closes the high-pressure valve when the pressure difference becomes small; A refrigeration device comprising an operating part that can be moved to a different position.