JPS5895172A - Fluid control valve for 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 a fluid control valve for 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 it is a low-pressure container type like a general reciprocating compressor. 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 1602 for a reciprocating type, while for a rotary type it is about 260.
This is a significant increase of more than 60%. Part of this increase in refrigerant 1002 becomes high-temperature, high-pressure super gas, and part dissolves in the refrigerating machine oil and remains in the closed container. These high-temperature, high-pressure refrigerants are activated by the temperature controller of the refrigeration equipment, and when the refrigeration equipment is stopped, the heat gas is in a gas state, and the dissolved material in the refrigeration oil is vaporized and released into the high-temperature area in the closed container. The gas is heated and becomes a high-temperature, high-pressure superheat gas that flows into the evaporator. As the first flow path, it flows into the sealed container - condenser cabil') - fz - evaporator, and as the heat is dissipated by the condenser, it flows as gas at room temperature, but the temperature difference with the evaporator is very large. Therefore, there was a drawback that the evaporator was heated, resulting in a large heat load. Further, as a second flow path, the high-temperature, high-pressure super-fuel gas flows into the closed container, the cylinder chamber of the compression element, the suction line, and the evaporator as a high-temperature, high-pressure super gas, 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 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.
When measuring the power consumption of C9607 electric refrigerators and electric freezers, the effect was significantly reduced, and the amount of power saved was only about 65%. 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 evaporator from the second flow path. Currently, some methods are used to improve the second flow path, such as providing check pulp in the suction line of the refrigeration equipment, or in the rotary compressor.
However, since the first flow path has not been improved, the effect is small, and the reduction in power consumption is only about 6 inches, 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 this solenoid valve is required, which complicates the electric circuit, and the valve itself has disadvantages such as consuming 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. It is an object of the present invention to provide a fluid control valve for a 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 first valve device 5a of the refrigeration system fluid control valve 6 of the present invention (hereinafter simply referred to as the fluid control valve), the capillary Q-Pro, and the evaporator 7
, the second valve device sb of the fluid control valve 6, the suction line 8, and the rotary compressor 1 are sequentially connected in an annular manner. The fluid control valve 5 includes a first valve device 5a located above, interposed on the high pressure circuit A side, and a second valve device 5b located below, interposed on the low pressure circuit B side, which are arranged substantially vertically. are doing. Further, the fluid control valve 5 has an outer shell 11 formed by a high-pressure side casing 9 having a substantially hollow cylindrical shape and a low-pressure side casing 1o also having a substantially hollow cylindrical shape, and both 9 and 1o are integrated to maintain airtightness. Reference numeral 12 denotes a diamond slam (hereinafter referred to as a pressure responsive element) which is partitioned into a first valve device 6a and a second valve device 6b within the outer shell 11 and moves up and down in response to the pressure of the elevation circuits A and B. be.

A pressure-responsive element 1 is provided at the center of the lower surface of the pressure-responsive element 12.
A coil spring 13 is provided which urges the coil 2 upward in the figure. A retainer 14 holds the lower end of the coil spring 13, and prevents excessive movement of the pressure-responsive element 12 and prevents damage. This refrigerant 14 has a plurality of small holes 14a, 14a, . . . that form a refrigerant flow path.
,,a are provided. Further, this retainer 14 is integrally press-fitted and fixed to a valve seat body 1oC, which will be described later. Next, the above-described first valve device 5a and second valve device 5b will be explained. The high-pressure side casing 9 has an inlet pipe 9a, an outlet pipe 9b, and a valve seat body 9c of the high-pressure circuit A, and the valve seat body 9c and a high-pressure valve 16, which will be described later, form a '1st valve device as a high-pressure valve device. There are some books that form 6a. Specifically, in the center of the path of the pressure responsive element 12, there is a through hole 12a as shown in FIG.
, and the protrusion 15 of the connecting member 16 (hereinafter referred to as holder)
A is inserted and crimped and sealed, and a high pressure valve 16 made of a ball valve is placed in a recess 15b with a flat bottom formed in the center of the upper end of the holder 16, and is crimped so as to be slightly movable with a slight gap 15c between the holder 16 and the holder 16. It is fixed by That is, the gap 150 serves to align the high pressure valve 16 with respect to the valve seat body 9c. Also, the inlet pipe 10 is also connected to the low pressure side casing 1o.
a, outlet pipe 10b.

It has a valve seat body 10c, and the valve seat body 10c and a low pressure valve 18, which will be described later, form a second valve device 6b as a low pressure side valve device. More specifically, a low pressure valve 18 made of a leaf valve having a notch 18a forming a gas passage at its outer edge is movably housed in the middle of the valve seat body 10c.

Furthermore, a retainer is provided above the low pressure valve 18 to restrict excessive movement of the low pressure valve 18 and to hold the coil spring 13.
14 is press-fitted and fixed to the valve seat body 10c. The low-pressure side casing 10 and the valve seat body 10a are fixed with a screw 10d formed on the valve seat body 10c as shown in FIG. It is sealed and kept airtight by brazing.

Next, the operation when the fluid control valve 6 is incorporated into a refrigeration system will be described. 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 element 12 of the fluid control valve 6 The coil spring 13 is pushed down by the pressure difference between the high voltage circuit A and the low voltage circuit B, and is deformed until it hits the retainer 14. Therefore, the high-pressure valve 16 is attached to the pressure-responsive element 12 by the holder 15 that is integrally suspended, so that the force due to the pressure difference between the high-pressure circuit A and the low-pressure circuit B communicating with the evaporator 7 is applied to the valve seat body 9C by the coil spring 13. The force is overcome and the first valve device 6a is in an open state. On the other hand, the low pressure valve 18 of the second valve device 5b is blown up by the gas flow flowing in from the evaporator 7, separates from the valve seat body 10c, and comes into contact with the retainer 14. The gas flows from the gap between the notch 18a on the outer edge of the low pressure valve 18 and the retainer 14 without any hindrance as shown by the arrow in FIG. 1 to the second valve device s.
b is in an open state. Therefore, the refrigerant gas discharged from the rotary compressor 1 is passed through the condenser 4 and the first valve device 6a of the fluid control valve 6.

It flows without any problem to the capillary tube 6, the evaporator 7, the second valve device 6b of the fluid control valve 6, the suction line 8, and the rotary compressor 1 to perform the refrigeration action.

Next, the state in which the refrigeration system is stopped will be explained using FIG. 2. Since the gas flow from the evaporator 7 is stopped due to the stoppage of the rotary compressor 1, the low pressure valve 18 of the second valve device 5b of the fluid control valve 5 is lowered by its own weight and the valve seat body 1
0c to close the second valve device 6b. As a result, the superheat gas from the rotary compressor 1 is prevented from flowing backward into the evaporator 7. As time further elapses, the superheated gas in the closed container 2 flows into the cylinder chamber (not shown) of the compression bag element 3, and further flows into the suction line 8, and the fluid control valve 6
flows into the low-pressure side casing 1o (as indicated by the arrow in the figure), so the pressure inside the casing 1o rises rapidly,
This approximates the pressure inside the high-pressure side casing 9. When the pressures in both the casings 9 and 10 become approximate, the pressure responsive element 1
The biasing force of the coil spring 13 provided below the caning 2 overcomes the force generated in the pressure responsive element 12 due to the pressure difference between the canings 9 and 1o, and the holder 15 is pushed up, and the first valve device 6a is brought into a closed state. This prevents superheat gas from flowing into the evaporator from the condenser 4.

A coil spring 13 further urges the pressure responsive element 12 upward.
The effect will be explained using the pressure change diagram of the refrigeration system shown in FIG. In the figure, the second valve device 6b is closed at the same time as the rotary compressor 1 stops, and the pressure in the suction line 8 of the low pressure circuit B rapidly increases due to the superheat gas flowing back from the rotary compressor 1. At this time, the first valve device 6a is in an open state, and the pressures in the capacitor 4 and the high pressure circuit A gradually drop to the same extent. When a minute time t has elapsed after this stop, a force Fp (Fp = The biasing force FC of the coil spring 13 increases relative to ΔPxS), the holder 16 is pushed up, and the first valve device 6a is brought into a closed state. From this point on, the refrigerant flowing into the high-pressure side casing 9 stops, so the pressure in the outlet pipe 9b of the high-pressure circuit A drops rapidly. This pressure drop causes the high pressure valve 16 to further move to the valve seat body 9.
c, and leakage is reduced. Note that the short time t required for the first valve device 6a to close after the rotary compressor 1 is stopped must be about 30 seconds or less. This 30 seconds or less depends on the size of the refrigeration equipment and the size of the rotary compressor 1, but it takes about 4 seconds after the refrigeration equipment stops.
This is because the liquid refrigerant condensed in the condenser 4 flows into the capillary Q-Pro for about 6 seconds to about 1 degree to perform normal refrigeration, so it is sufficient to close the first valve device 5a before that time. For this purpose, it is necessary to make the minute time t as small as possible, and for this purpose, the differential pressure ΔP
is to close the first valve device 6a when the value is large. On the other hand, when the outside temperature is low, the pressure difference between the inside of the high pressure side casing 9 and the low pressure side casing 10 gradually decreases, and the pressure difference Δ
If P is set large, the first valve device 6a will be in a closed state even when the refrigeration system is in operation, and no refrigeration action will be performed. From the above, the differential pressure ΔP is set to around 2 K//ca. When the refrigeration system is started, the pressure in the low pressure circuit B instantly becomes low, and the pressure responsive element 12 is pulled downward.
The high-pressure valve 16 integrated with the pressure-responsive element 12 via the holder 16 is lowered, and the first valve device 6a- opens to perform normal refrigeration. In particular, regarding the relationship between the connecting member 16 provided on the pressure responsive member 12 that moves up and down, the high pressure valve 16 provided on this connecting member 16, and the valve seat body 9c,
Since the high pressure valve 16 is movable in response to variations in the pressure responsive element 12 or mounting errors between the boulder 15 and the valve seat body 9c, the valve seat body 9c can be reliably closed. Further, since the holder 15 has the protrusion 16a of the pressure-responsive element 12 crimped and fixed in the through hole 1.2a, the pressure-responsive element 12 will not be thermally deformed during assembly, and its characteristics will not change. Furthermore, since the adjusting device for adjusting the biasing force of the coil spring 13 is integrally provided on the valve seat body 10c, the differential pressure ΔP can be set accurately by rotating the screw 1od, and the adjusting device is simple in structure and inexpensive. be.

As is clear from the above description, the fluid control valve for a refrigeration system of the present invention includes a first valve device interposed on the high pressure circuit side;
a second valve device interposed on the low pressure circuit side, and the first valve device and the second valve device are partitioned by a pressure responsive element that responds to a pressure difference between the high pressure circuit and the low pressure circuit. The first valve device is configured with a high-pressure valve that opens and closes the high-pressure circuit, and a connecting member that is connected to the pressure responsive element and holds the high-pressure valve, and the second valve device is configured to operate as a check valve. and the pressure responsive element is configured to close the first valve device when the pressure difference is below a predetermined value,
Furthermore, since the high-pressure valve held by the connecting member is movable over a short distance, the first valve device opens when the pressure in the low-pressure circuit is low and closes when the pressure is high. Since it is designed to respond to pressure, normal refrigerant circulation occurs when the refrigeration system is in operation, and when the refrigeration system is stopped, the second valve device, which has a check valve function, immediately closes and simultaneously reduces the pressure in the low-pressure circuit. The temperature rises rapidly and the first valve device is closed during the minute period when the liquid refrigerant is flowing out to the pressure reducing device, so the superheated gas in the sealed container and condenser flows into the evaporator via the suction line and the pressure reducing device. prevent Therefore, it has a greater power saving effect than a type without a fluid control valve, and is cheaper than a type controlled by a solenoid valve.Furthermore, it does not require power for control, does not require a control circuit, and requires no extra electrical wiring. It is characterized by not requiring any noise, and because it operates smoothly, it does not generate noise. In addition, the high-pressure valve is movably fixed to the holder with a small gap, so even if there is a misalignment between the valve seat body and the holder, the high-pressure valve will close centripetally to the valve seat body, preventing leakage. Less valve function can be retained. In addition, for the first valve device, the pressure-responsive element is made with a through hole, the protrusion of the holder is inserted, and then the holder is crimped and sealed, so there is less change in characteristics due to heat compared to fixing by welding or brazing. It is simple, inexpensive, and can reliably maintain airtightness.

[Brief explanation of the drawing]

FIG. 1 is a refrigeration cycle diagram of a refrigeration system equipped with a fluid control valve for a refrigeration system according to an embodiment of the present invention, and is a sectional view of the main parts during operation;
Fig. 2 is a sectional view of the main part of the fluid control valve at rest, equivalent to Fig. 1, Fig. 3 is a sectional view of the main part of the high pressure valve section, Fig. 4 is a sectional view of the main part of the spring biasing force adjustment device, FIG. 5 is a pressure change diagram of the refrigeration system shown in FIG. 1. A...High voltage circuit SB...Low voltage circuit 16
......Fluid control valve 6a...1st
valve device, 5b... second valve device) 12...
...Pressure responsive element 15, holder (connecting member), 15c, . Gap -16...High pressure valve 0 Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure q Figure 2 Figure 3〆a

Claims (2)

[Claims] (1) It has a first valve device interposed on the high pressure circuit side and a second valve device interposed on the low pressure circuit side, and the first valve device and the second valve device are connected to the high pressure circuit side. A high-pressure valve that opens and closes the high-pressure circuit, and a connection that is connected to the pressure-responsive element and holds the high-pressure valve, dividing the first valve device with a pressure-responsive element that responds to a pressure difference between the circuit and the low-pressure circuit. The second valve device is configured to perform a check valve operation, and the pressure responsive element is configured to cause the first valve device to close when the pressure difference is below a predetermined value. A fluid control valve for a refrigeration system, wherein the high pressure valve held by the connecting member is movable over a short distance. (2) The fluid control valve for a refrigeration system according to claim 1, wherein the connecting member has a protrusion, and the protrusion is inserted into a through hole provided in the pressure responsive element and fixed by pressure.