JPS5899674A - 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 improvements in refrigeration equipment used in refrigerators and the like.

A conventional general refrigeration system has a compressor 2 as shown in Figure 3.
1. Condenser 22. Squeezing device 23. The evaporators 24 are successively connected to form a refrigeration cycle. In the refrigeration cycle, the compressor 2 is controlled by a thermostat (not shown).
1 is under operation control, and this thermostat's JOF
In the Fj, the superheated cold 2, which has no refrigerating effect and remains in the condenser 22, flows into the evaporator 24 through the throttle device 23, heats the evaporator 24, and cools the compressor 21. This has the drawback of increasing the operating rate of the system and increasing power consumption. In addition, in order to eliminate the above-mentioned drawbacks, in recent refrigeration systems, a solenoid valve 33 is installed between the condenser 31 and the throttle device 320, as shown in FIG.
The electromagnetic valve 33 is kept in an open state when the refrigeration system is in operation and the thermostat is set to "ON", and closed when the refrigeration system is stopped when the thermostat is set to 0FFJ. It is known to prevent overheated refrigerant gas from flowing into the evaporator 34, thereby preventing a rise in temperature of the evaporator 34 and reducing power consumption. Note that 36 is a compressor.

However, in a refrigeration system using the above-mentioned solenoid valve 33, the output is 1.
In a small refrigeration system of around 00W, the solenoid valve 33 consumes 5
~6W of power offsets the reduction in power consumption,
On the contrary, it had drawbacks such as increased power consumption.

The present invention improves the above-mentioned drawbacks by providing a refrigeration system employing a fluid control valve that operates a valve system under dynamic pressure caused by the flow of gas hd flowing through a low-pressure circuit.

A refrigeration system according to an embodiment of the present invention will be described below with reference to the drawings.

1 is a compressor, 2 is a condenser, 3 is a throttle device, 4 is a fluid control valve, 6 is an evaporator, and 6 is a suction line, which are sequentially connected in a ring to form a refrigeration cycle.

Next, the configuration of the fluid control valve 4 will be explained.

Reference numeral 7 denotes a casing, in which a control device 8 provided on the downstream side of the evaporator 5 and a valve device 9 provided on the upstream side of the evaporator 6 are provided. The valve device 91 is composed of a valve seat body 10 formed at the lower part of the casing and a valve 11 such as a ball valve, and the port 12 of the valve seat body 10 is connected to the outlet of the throttle device 3. 12'L is connected to the inlet of the evaporator 5. Further, the dynamic pressure device 8 is provided in the upper space of the casing 7, and an inlet portion 13 is provided on the lower side of the five dynamic pressure chambers 12, and an outlet portion 14 is provided on the upper surface. Flange portion 8 formed on the upper outer periphery
The inlet portion 13 and the outlet portion 14 are separated by b. The valve 11 is installed below the operating isa. A bellows 15 hermetically seals the opening of the casing 7, and the outer surface of the bellows 15 is brought into contact with an adjustment screw 16, which is screwed into the threaded portion of the casing 7. A spring 17 biases the actuating portion 8a downward, and is provided between the bellows 15 and the actuating portion 8&. Further, the valve device 9 and the dynamic pressure device 8 are provided in the same space within the casing 7, and the operating portion 8& is approximately the same as the outer diameter of the central portion 8C and the inner circumference of the central guide portion 7a of the casing 7. Since it is made to be able to slide, it is in a roughly divided state. Still, when the operating portion 8a slides upward, the upper convex portion 8d contacts the bellows 16 to prevent excessive movement. The operating portion 8a is a spring 17.
When the valve 11 is slid downward by the urging force of
, the valve device 9 is closed, and the flange portion 8b of the actuating portion 8a is located between the inlet portion 13 and the outlet portion 14b of the dynamic pressure chamber 12, and the actuating portion 81L
When the bellows 81L overcomes the biasing force of the spring 17 and slides upward, and the upper convex portion 81L comes into contact with the bellows 16, the valve device 9 is opened and the actuating portion 8& in the dynamic pressure chamber 12 is opened. Since the flange portion 8b is located above the outlet portion 14, the dynamic pressure device 8 is opened.

Further, the force that causes the operating portion 8a to slide upward is due to the dynamic pressure of the refrigerant flowing within the dynamic pressure chamber 12 from the inlet portion 13 to the outlet portion 14. Since the refrigerant flowing from the inlet portion 13 flows into the guide portion 7& at right angles, it flows evenly upward through the dynamic pressure chamber 12 on the outer circumference of the guide portion 71L and acts uniformly on the entire lower surface of the flange portion 8b of the first operating portion Sa. do. Therefore, the actuating portion 8& is not twisted and moves smoothly. Further, the operation of the actuating portion 51 is controlled by the spring 17.
It is determined by the difference between the urging force of the refrigerant and the dynamic pressure of the refrigerant. Therefore, since this dynamic pressure varies depending on the size and usage condition of the refrigeration system, it is necessary to set the biasing force of the spring 17 appropriately. Since adjustment screw 16 is provided, 1
．． The entire urging force of the spring 17 can be easily adjusted.

Next, the operation of the refrigeration system having the above configuration will be explained.

FIG. 1 shows a state diagram during operation. Due to the operation of the compressor 1, the refrigerant in the evaporator 6 passes through the suction line 6 to the compressor 1.
flowing to. At this time, since the refrigerant flowing in the suction line 6 is a low-pressure gas, its specific volume is about 10 degrees higher than that of high-pressure gas, and the flow rate of the refrigerant gas is also about 10 times faster. Therefore suction line 6
The dynamic pressure of the gas refrigerant flowing in the dynamic pressure device 8 of the fluid control valve 4, which is interposed in a part of the fluid control valve 4, is about 10 times as large as that on the high pressure side. Due to this operation, the operating part 8 & spring 17
It is able to overcome the urging force of , and is forced to slide upward.
As a result, the valve device 9 is also opened. In other words, the refrigerant is compressor 1-? Condenser 2 → Squeezing device 3-? The flow is as follows: valve device 9 of the fluid control valve 4 → evaporator 5 → suction line 6 → dynamic pressure device 7 of the fluid control valve 4 → suction/line 6 → compressor 1^, and normally performs a cooling action.

Next, FIG. 2 shows a state diagram when the compressor 1 is stopped. When the compressor 1 is stopped, the refrigerant flowing in the dynamic pressure device 8 of the fluid control valve 4 is stopped. Therefore, the dynamic pressure of the gas refrigerant in the dynamic pressure device 8 disappears, and the urging force of the first spring 17 causes the engine operating portion 8a to slide downward, and the valve device 9 closes. If the stopped state continues in this state, the pressure at the outlet of the throttle device 3, that is, the pressure in the port 12 of the valve device 9 will also become the same pressure as the high pressure side, but the force relationship acting on the actuation 'Nr8''L is F>
The biasing force of the spring 17 is set so that (PH-PL)X. Here, the biasing force of the F nisprin 17, PH: high pressure, PL: low pressure, and A: cross-sectional area of the port 12. Therefore, the high-temperature, high-pressure refrigerant in the condenser 2 flows to the port 12, but since the valve device 9 is closed, it does not flow into the evaporator 6 and does not heat the four generators 5.

Next, a description will be given of when the compressor 1 is restarted from this state (the state shown in FIG. 2). When the compressor is started in this state, the pressure in the suction line 6 on the downstream side of the fluid control valve 4 drops rapidly. At this time, the dynamic pressure chamber 12 of the fluid control valve 4
A flange portion 8b of the actuating portion 8a is located between the inlet portion 13 and the outlet portion 14 of the actuating portion 8a. Therefore, the upstream side of the flange section 8b, which is the inlet section 13 side, remains at the same internal pressure of the evaporator 5 at the time of stop, and the pressure on the downstream side of the flange section 8b, which is the outlet section 14 side, is rapidly reduced by the compressor 1. This pressure difference causes the operating portion 8a to slide upward, the valve device 9 to open, and the circulation of the refrigerant to begin. In response to the dynamic pressure caused by the flow of the refrigerant, the dynamic pressure device 8 is further slid upward, and becomes the state shown in FIG. 1, and enters the normal cooling operation state.

In addition, in the operating state, in this embodiment, the pressures of the valve device 9 and the dynamic pressure device 8 are both low pressure circuits and there is no pressure difference, so a short circuit phenomenon from the valve device 9 to the dynamic pressure device 8 does not occur. Of course, the central part 8C of the actuating part 8a and the inside of the guide part a are approximately the same, and this slight gap creates a very large resistance to the refrigerant flow, and the valve device 9 at the inlet of the throttling device 30, the refrigerant will not be short-circuited and will have the same effect as the present embodiment.

As is clear from the above description, the refrigeration system according to the present invention is composed of a compressor, a condenser, a throttling device, an evaporator, a saxy line, and a fluid control valve, and the fluid control valve is a low-pressure The circuit is constituted by a valve device operated by the dynamic pressure of the flowing gas refrigerant, this valve device is interposed on the upstream side of the evaporator, and the flow amount of the refrigerant is detected by the dynamic pressure device to close the valve device. The valve device opens the circuit due to the dynamic pressure of the low-pressure gas refrigerant at the outlet of the evaporator, which is a low-pressure circuit, which has a very large specific volume and large kinetic energy, and closes the circuit when the gas refrigerant almost stops. Therefore, it is possible to reliably open the valve device during operation and close it when stopped, reducing the heat load on the evaporator by cutting off the high temperature refrigerant flowing into the evaporator when stopped. This makes it possible to achieve energy savings 101, -.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of the main parts of the refrigeration system according to the present invention in the operating state, Fig. 2 is a sectional view of the main parts in the stopped state corresponding to Fig. 1, and Fig. 3 is a refrigeration cycle diagram of the conventional example. Figure 4 shows a conventional improved refrigeration system, Figure 9. 1... Compressor, 2... Condenser, 3...
... Throttle device, 4... Fluid control valve, 5...
...Evaporator, 6...Suction line/, 2
8...Dynamic pressure device, 9...Valve device, 11
・・・・・・Operating part. Name of agent: Patent attorney Nakao Sekio (Nakao) 1 person 1
Figure 11-5 Figure 2

Claims (1)

[Claims] It consists of a compressor, a condenser, a throttle device, an evaporator, and a fluid control valve, and the fluid control valve is provided upstream of the evaporator and closes the flow of cold rod from the condenser; A refrigeration system equipped with a valve of a valve device and a control device that opens and closes the valve according to the flow rate of a low pressure circuit.