JPS5888577A - 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 device such as a refrigerator that uses 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 combiner) like a general rotary compressor, the inside of the closed container is on the high-pressure side, so the pressure is low like a general reciprocating compressor. Compared to a container-type 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 in is about 150g for a reciprocating type, while for a loader type it is about 25g.
0'';!9, which is a large increase of more than 50 inches.

Of this 100 g increase in refrigerant, a portion 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 controlled by the temperature controller of the refrigeration system.When the refrigeration system is stopped, the superheat gas is in a gas state, and the dissolved gas in the refrigeration oil is vaporized and released into the high-temperature area inside the closed container. The gas is heated at 2 and flows into the evaporator as a superheated gas at high temperature and high pressure. As the first flow path, it flows from the sealed container → condenser → capillary tube → evaporator, and the heat is dissipated by the condenser, so it flows as room temperature superheat gas, but the temperature difference with the evaporator is very large, so it heats the evaporator. However, it had the disadvantage of causing a large heat load. In addition, as the second flow path, a closed container -
There was a drawback that the high temperature, high pressure superheat gas flowed from the cylinder chamber of the compression element to the suction line to the evaporator and heated the evaporator, resulting in 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 installed a rotary compressor, which is about 20 cm more efficient than a conventional reciprocating compressor, in a refrigerator and refrigerator.
When measured in a power consumption test of the C9607 electric refrigerator and electric freezer, the effect was significantly reduced, and the power saving amount was only about 6 factors. 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 super heat scum from flowing into the evaporator from the second flow path. The method currently used in some cases is to improve the second flow path, which is to install check pulp in the suction line of the refrigeration equipment, but since the first flow path has not been improved, its effectiveness is limited. Small and reduces power consumption by 6
This is an effect of about 10 inches in total, with only a slight improvement in the number of points. In addition, a 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 This has the disadvantages of generating noise, requiring a control circuit for the solenoid valve, requiring a complicated electrical circuit, and consuming power itself.

In view of the above-mentioned drawbacks, the present invention provides a fluid that is inexpensive, does not require electrical control, is quiet, and aims to achieve high efficiency as a refrigeration system that is equivalent to or higher than that of a rotary compressor. The purpose is to provide a control valve.

An embodiment of the present invention will be described below. Reference numeral 1 denotes a port-to-tally compressor, which is composed of a closed container 2, a compression element 3, and an electric element (not shown).

Additionally, this rotary compressor 1 is not equipped with a check valve inside. The refrigeration system includes a rotary compressor 1, a condenser 4, a high pressure circuit 5a of a fluid control valve 5 for a refrigeration system of the present invention (hereinafter simply referred to as a fluid control valve), a capillary tube 6, an evaporator 7, and a low pressure circuit of the fluid control valve 5. 5b, suction line 8, and rotary compressor 1 are sequentially connected in an annular manner. The fluid control valve 5 includes a first valve device 5A located above including a high pressure circuit 6a, and a second valve device 5B located below including a low pressure circuit 6b, which are arranged substantially vertically. The fluid control valves 6 each have an independent substantially hollow cylindrical high pressure side casing 9.
and the low-pressure side casing 10, which is also approximately hollow and cylindrical, form an outer shell 11-, and the two are integrated to maintain airtightness. 12 is a high voltage circuit 5 inside the outer shell 11.
It is a pressure-responsive element (hereinafter referred to as a bellows) that is partitioned into a low-pressure circuit 5b and a low-pressure circuit 5b, and expands and contracts in response to the pressure of the two circuits. A coil nozzle 13 is provided at the center of the lower end of the bellows 12 to urge the bellows 12 upward in the figure.

Reference numeral 14 is an adjustment member (hereinafter referred to as a retainer) that holds the lower end of the coil spring 13, and restricts excessive movement of the bellows 12 and prevents damage. This retainer
14 has a plurality of small holes 14a, 14a... for the bellows 12 to correctly sense the pressure of the low pressure circuit 6b.
A screw 14b is provided on the outer periphery. This retainer 14 is screwed into a threaded portion 9d provided on the inner surface of the casing 9, and after the biasing force of the spring 13 is adjusted to a predetermined value, it is fixed by an appropriate method. On the other hand, the high pressure side casing 9
The valve has an inlet pipe 9a, an outlet pipe 9b, and a valve seat 9c, and a cylindrical plunger 16 is housed in the 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 16 by caulking to form a high pressure side valve device 17. A recess 15a is provided at the lower end of the plunger 16 for connecting the plunger 15 and the bellows 12, and the bellows 12 is connected and supported by sizing. In addition, the sizing process is performed by providing a gap 16b for centripeting the high-pressure valve 16 to the valve seat 9C.The low-pressure side casing 10 also has an inlet pipe 10a, an outlet pipe 10b, and a valve seat 10C.
A notch 18a for forming a gas passage is provided at the outer edge of the shaft, and a low pressure valve 18 consisting of a one-flange valve is movably housed. Above the low pressure valve 18 is a low pressure valve 1.
A stopper 19 for regulating excessive movement of the valve 8 is press-fitted and fixed into the low-pressure side casing 1o to form a low-pressure side valve device 2o.

Next, the operation when the above-mentioned fluid control valve is incorporated into a refrigeration system will be described. 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 5 is under high pressure. The pressure difference between the circuit 6a and the low pressure circuit 6b pushes down the coil spring 13,
It extends until it hits. Therefore, the high pressure valve 16 is operated by the plunger 16 integrally attached to the bellows 12.
- is attracted to the valve seat 9C by the sum of the pressure difference between the high pressure circuit 5a and the evaporator 7 and the biasing force of the coil spring 13;
The high pressure side valve device 17 is now 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, separates from the valve seat 1oC, and comes into contact with the stopper 19. The gas flows without any problem from the gap between the notch 18a on the outer edge of the low pressure valve 18 and the stopper 19 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 discharged from the rotary compressor 1 is transferred to the condenser 4, the high pressure circuit 5a of the fluid control valve 6, the capillary valve 6, the evaporator 7, the low pressure circuit sb of the fluid control valve 6, the suction line 8, and the rotary It flows to the compressor 1 without any trouble and performs the refrigeration action.

Next, the state in which the refrigeration system is stopped will be explained using FIG. 2. When the rotary compressor 1 stops, the gas flow from the evaporator 7 stops, so the low pressure valve 18 in the partial pressure circuit 5b of the fluid control valve 6 falls under its own weight, and the valve seat 10C
The low pressure side valve device 20 is brought into a closed state. As a result, the superheat gas from the rotary compressor 1 is prevented from flowing back into the eno (bore tuff). As time passes, the super heat gas in the sealed container 2 flows into the cylinder chamber (not shown) of the compression element 3. inflow,
Further, it flows into the suction line 8 and into the low pressure circuit 6b of the fluid control valve 5 (as indicated by the arrow in the figure), so the pressure in the low pressure circuit 5b rises rapidly and becomes similar to the pressure in the high pressure circuit 5a. 0 When the pressures in both circuits 5a and 5b become approximate, the biasing force of the coil spring 13 provided below the bellows 12 overcomes the clamping force generated in the piperose 12 due to the pressure difference between the two circuits sa and sb, and the plunger 16 is pushed up. As a result, the high pressure side valve device 17 enters a closed circuit state, and prevents superheat gas from flowing into the evaporator port 7 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 in an open state, and the pressures in the capacitor 4 and the high-pressure circuit 5a gradually drop equally. When a minute time t has elapsed after this stop, a force FP (FP=JPxS) is generated due to the differential pressure JP between the high-pressure circuit 6a and the low-pressure circuit 6b acting on the bellows 12 and the effective area S of the bellows 12.
On the other hand, the biasing force FC of the coil spring 13 pushes up the shiblunger 16, and the high pressure side valve device 17 is closed. From this point on, the refrigerant flowing into the high pressure circuit 5a stops, so that the outlet pipe 9a of the high pressure circuit 5a is closed. The pressure drops rapidly. This pressure drop causes the ball valve 16 to further move to the valve seat 9.
C is adsorbed, and leakage is reduced. Note that the short time t required for the high pressure side valve device 17 to close after the rotary compressor 1 stops is approximately 30 seconds or less. These 30
Less than a second depends on the size of the refrigeration equipment and the size of the rotary compressor 1, but from about 46 seconds to 1 minute after the refrigeration equipment has stopped, the liquid refrigerant condensed in the condenser 4 flows into the capillary Q-Pro. This is because the high-pressure side valve device 17 can be closed before the inflow and the normal refrigeration action is performed. 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 dP is large. However, the differential pressure d that causes the high pressure side valve device 17 to close
If P is set too large, the difference between the pressure of the condenser 4 and the pressure of the evaporator 7 during operation is small when the temperature is low such as in winter, so a pressure difference sufficient to open the high pressure side valve device 17 will not be obtained. First, the high-pressure side valve device 17 remains closed regardless of the operation of the rotary compressor 1, resulting in a state in which refrigeration cannot be performed. The ideal differential pressure dP setting value for a household refrigerator-freezer is 2 ± 0.2%.
The extent is very small. Therefore, the coil spring 13
Key 1 of the biasing force corresponding to manufacturing variations in the spring constant of
Precision in the joints and manufacturing process requires adjustment inspection,
This will be described later using FIG. 4. Furthermore, when the refrigeration system is started, the pressure in the low pressure circuit 5b instantly becomes low, the bellows 12 is pulled down, the ball sensor 16 integrated with the bellows 12 via the plunger 15 is lowered, and the high pressure side valve device 17 is opened. and performs normal freezing action.

Next, the adjustment of the biasing force of the coil spring 13, precise adjustment and inspection in the manufacturing process, which are the main points of the present invention, will be explained using FIG. Reference numeral 30 denotes an air pump for producing compressed air for inspection, and the pressure regulating valve 31, the high pressure side valve device 17 of the fluid control valve 5, the resistance pipe 33, and the flow meter 34 are connected in sequence, and the pressure regulating device 31 and the high pressure side valve device 17 are connected in sequence. The fluid control valve 5 with the pressure gauge 32 connected therebetween is a semi-finished product that does not incorporate the low pressure side valve device 20. With this device, the retainer 14 is adjusted so that the high pressure side valve device 17 opens and closes when the differential pressure dP reaches the set value of 2±0.2. - To explain an example, the pressure of the pressure gauge 32 is adjusted to 2.2%-G by the pressure adjustment unit 13, and the predetermined flow rate flows to the flow meter 34 by adjusting the rotation of the retainer 14, thereby confirming that the valve is open. Next, the pressure is lowered to 1.8~ by the pressure regulator 31, and the adjustment is completed when the flow rate of the flowmeter 34 is below the specified value and the valve is closed.

As described above, the differential pressure ΔP can be precisely adjusted and inspected before completion.

As described above, in the fluid control valve of the present invention, the high pressure side valve device of the fluid control valve is connected between the condenser and a pressure reducer such as a capillary tube, and the low pressure side valve device having a check loop function is connected to the evaporator and the rotary compressor. The high-pressure side valve device opens when the pressure in the low-pressure circuit is low and closes when the pressure is high, so that when the refrigeration equipment is in operation, , perform normal refrigerant circulation, and shut off when the refrigeration equipment is stopped.
.

The low-pressure side valve device, which has a nick pulp function, 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 a short period of time when liquid refrigerant flows out to the pressure reducing device. Prevent superheated gas in the condenser from flowing into the evaporator via the suction line and pressure reducing device. 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 superheat gas, which is the waste cold 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 cheaper than those controlled by solenoid valves, and it also does not require electric power to control, does not require a control circuit, and does not require any extra electrical wiring.It operates smoothly and generates noise. It has the characteristics that it does not.

Furthermore, the differential pressure dP between the high pressure circuit and the low pressure circuit of the fluid control valve
The differential pressure adjustment that regulates the opening and closing of the high-pressure side valve device is provided in the outer shell where the pressure-responsive element and the high-pressure side valve device are integrally attached, and can be adjusted without the low-pressure side valve device being incorporated. Since inspection is possible, the differential pressure dP can be set very accurately and easily, so the high pressure side valve device must be closed while the liquid refrigerant is flowing out from the condenser immediately after the rotary compressor has stopped, and superheat gas can be mixed in with the evaporator. This has the advantage that there is no fear of leakage.

[Brief explanation of drawings]

FIG. 1 is a sectional view showing an embodiment of a refrigeration system using a fluid control valve for a refrigeration system according to the present invention, FIG. 2 is a sectional view of a main part of a stopped fluid control valve corresponding to FIG. The figure is a pressure change diagram of the refrigeration system shown in FIG. 1, and FIG. 4 is a diagram showing an example of a method for adjusting and inspecting the spring biasing force of the high-pressure side valve device of the fluid control valve. 5... Fluid control valve for refrigeration equipment, 5A...
・First valve device, 5B...Second valve device, 12
...Pressure responsive element (bellows), 13...
・-/(ne, 14...adjustment member (retainer)
', 15b...A...Gap, 16...High pressure valve. Figure 1 Figure 2! s3 diagram Katama - Figure 4

Claims (3)

[Claims] (1) A first valve device and a second valve device, each independent of each other, are integrally configured, the first valve device and the second valve device are separated by a pressure responsive element, and the first valve device and the second valve device are separated by a pressure responsive element, and A high-pressure valve of the valve device is connected to the pressure-responsive element, and the pressure-responsive element is biased in a direction to close the high-pressure valve by a spring supported via an adjustment member provided on the first valve device. The second valve device is a fluid control valve for a refrigeration system that performs a check valve operation. (2) The first valve device is disposed at the top, the second valve device is disposed at the bottom, and the second valve device is a non-return valve that is biased by the weight of a plate valve, a ball valve, or the like. A fluid control valve for a refrigeration system according to claim 1, which performs a valve operation. (3) The fluid control valve for a refrigeration system according to claim 1, wherein the high-pressure valve and the pressure-responsive element are connected with each other with as much clearance as possible.