JPS5899652A - 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 refrigeration device used in a refrigerator or the like.

In small refrigeration equipment that uses a high-pressure container-type compressor such as a general rotary compressor, the inside of the closed container is on the high-pressure side, so a low-pressure container-type hermetic compressor (hereinafter referred to as reciprocating compressor) such as a general reciprocating compressor is used. The amount of refrigerant to be sealed in the refrigeration system is significantly increased compared to the refrigeration system. As an example, in a popular refrigerator-freezer, the amount of refrigerant sealed in a reciprocating type is about 1507, whereas in a rotary type it is about 260f, which is a large increase of more than 0%. A portion of this increase in refrigerant 1002 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 heated in the high-temperature part of the sealed container. The gas becomes a high-temperature, high-pressure superheat gas and flows into the evaporator. That is, the first flow path of the inflow path is from the closed container to the condenser to the throttle device to the evaporator,
Since the heat is radiated by the condenser, it flows in as superheated gas at room temperature, but the temperature difference between it and the evaporator is very large, which has the disadvantage of heating the evaporator and creating a large heat load. In addition, as a second flow path, the closed container → the cylinder chamber of the compression element
The suction line - the superheated gas at high temperature and pressure flows into the evaporator as it is and heats the evaporator 7, which also has the disadvantage of creating a large heat load. The reason why this high-temperature, high-pressure gas in the closed container flows into the cylinder chamber is because existing high-pressure container type compressors such as rotary compressors have cylinder chambers made of mechanical seals using metal surface contact. .

That is, in a refrigeration system using a high-pressure container type compressor such as a rotary compressor, a large amount of high-temperature, high-pressure superheat gas flows into the evaporator, resulting in a large heat load. Therefore, a high-pressure container-type compressor such as a rotary compressor, which has about 20% higher efficiency than a conventional reciprocating compressor, is actually attached to a refrigerator-freezer and measured in the JISC 9607 electric, air-cooled paper storage, and electric refrigerator power consumption test. Even if you do, the effect will be greatly reduced,
The amount of electricity saved was only about 6 units.

In order to increase the amount of reduction in power consumption to an amount equivalent to the efficiency improvement of a high-pressure vessel type compressor such as a 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 installing a check loop in the suction line of the refrigeration system or installing a check loop inside 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 improved by about 6 channels, 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 electric circuit itself consumes electric power.

In view of the above drawbacks, the present invention provides 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 single high-pressure container type compressor such as a rotary compressor. The purpose of this invention is to provide an energy-saving refrigeration system that is designed to achieve the desired results.

An embodiment of the present invention will be described below. 1 is a rotary compressor, 2 is a condenser, 3 is a fluid control valve, 4 is a throttle device, 6 is an evaporator, 6 is a check valve, and 7 is a muffler. The fluid control valve 3 has a substantially cylindrical valve chamber 8 formed therein, and is equipped with a ball valve 9 having an outer diameter that is substantially the same as the inner diameter of the valve chamber 8. A first valve seat 10 and a second valve seat 11 are formed on the lower and upper surfaces of the valve chamber 8, and communicate with a first port 12 and a second port 13, respectively.

14 is a third boat, in which the ball valve 9 is located on the first valve seat 10.
The lower valve chamber 8 of the ball valve 9 is formed when the valve is closed.
It is connected to the position facing a.

In addition, each port 12, 13°1 of the fluid control valve 3
4, the first port 12 is connected to the inlet of the throttle device 4 of the high pressure side piping A of the refrigeration cycle, the second port 13 is connected to one end of the muffler 7 of the low pressure side piping B of the refrigeration cycle via the impulse pipe 16, The three ports 14 are each connected to an outlet of the condenser 2.

Next, the operation of the above configuration will be explained.

Figure 1 shows the state immediately before the device starts up, and Figure 3 shows the state immediately before starting the device.
Corresponds to point A in the figure. The pressure at this time is the first port 12.
The pressure P1o1 of the second port 1a is P2ON, and the pressure P3o of the third port 14 is assumed to be P3o. Also, assuming that the cross-sectional area d1 of the first port 12, the cross-sectional area a of the second port 13, the cross-sectional area a3 of the ball valve 9, and the weight W of the ball valve 19, the ball valve 9 is seated on the first valve seat 1o. the first port 12.
The pressure difference ΔPo−P3o−P2° between the second port 13 and the third port 14 when the valve is opened (hereinafter referred to as an open valve) is determined by the following equation.

ΔP0〉a1/a3・(P3゜−Pl.)+w/a3, the ball valve 9 is slid downward from the state seated on the second valve seat 11, closing the first port 12 (hereinafter The pressure difference ΔP1 when the valve is closed (referred to as valve closing) is determined by the following formula.

ΔP1<W/a2 Therefore, for example, if the ambient temperature is 30'C, the refrigerant R-12, a
l: a2=0.01 cnl, a3==0.5c
ffl, W=0.003t, P1o=1.0
//c-61P3o-6,5KIP/cdG, so the valve opens when ΔP0>0.1/cd.

Further, the valve closes when ΔP1(o, all/cn).

When the system is started in the state shown at point A in FIG. 3, the pressure in the low-pressure side pipe B drops rapidly. Therefore, the pressure at the second port 13, which is communicated with the muffler 7 of the low-pressure side pipe B by the impulse pipe 1F5, and above the Paul valve 9 in the valve chamber 8 also drops rapidly, causing the valve opening pressure point (four points in Fig. 3) to drop. Pass and descend in an instant. As a result, the ball valve 9 opens the first valve seat 10 as shown in FIG. This completely separates the high and pressure side piping A that communicates with the At this time,
Since the first port 12 of the fluid control valve 3 is opened, the refrigerant flows from the compressor 1 to the condenser 2 to the fluid control valve 3 to the throttle device 4 to the evaporator 6 to the check valve 6. The check valve 6 is also opened, and a normal flow from the check valve 6 to the muffler 7 to the compressor 1 is maintained, and the refrigeration operation is performed without any trouble.

Next, the time of stopping will be explained. FIG. 2 shows the state of the fluid control valve 3 immediately before it is stopped, and corresponds to point C in FIG. 3. When the operation of the compressor 1 is stopped in this state, the gas flow in the low pressure side pipe B is stopped, and the check valve 6 is closed to the valve (not shown).
The valve closes due to its own weight.

At this time, the superheated gas in the compressor 1 flows backward through the compression element of the compressor 1, flows into the downstream side of the check valve 6 in the low-pressure side pipe B, and rapidly increases the pressure. However, since the check valve 6 is closed, the superheat gas is prevented from flowing back into the evaporator 6. On the other hand, at the same time, a second
The pressure inside the boat 13 also rises rapidly, and when the pressure difference ΔP with the pressure inside the third port 14 becomes smaller than o, a Kp /aa (two points in Fig. 3), the ball valve 9 is slid downward by its own weight. Then, the first valve seat 10 is closed and the high pressure side piping A is closed. This also prevents the superheated gas in the condenser 2 from flowing into the evaporator 5 through the throttle device 4. Note that the time t from when the compressor 1 stops until the fluid control valve 3 closes is desirably about 30 seconds or less. This 30 seconds or less depends on the size of the refrigeration equipment,
Although it depends on the size of the compressor 1, the liquid refrigerant condensed in the condenser 2 flows into the throttling device 4 for about 1 minute after the refrigeration system stops.
This is because the fluid control valve 3 only needs to be closed before this occurs because the fluid flows into the fluid and performs a normal refrigeration action.

For this purpose, it is necessary to make the temporal eclipse as small as possible. For this purpose, the second port 13 of the fluid control valve 3 is
When the pressure difference ΔP between the pressure at the third port 14 and the pressure at the third port 14 is large, it is necessary to close the fluid control valve 3. On the other hand, the pressure difference ΔP during operation becomes smaller as the outside air temperature decreases, so if the pressure difference ΔP that opens the fluid control valve 3 is set large, the fluid control valve 3 will not close even during operation. It becomes cold and the freezing action becomes impossible. In this regard,
In the present invention, the size of the ball valve 9, its own weight, and the first port 1
2. By appropriately selecting the cross-sectional area of the second port 13, ΔP when the valve is open = 0.1 Kp/crl, and ΔP when the valve is closed = O-3Kp/a/! This is ideally possible with a simple configuration.

As is clear from the above description, the refrigeration system according to the present invention has a substantially cylindrical valve chamber in which a ball valve is slidably housed, a first valve seat and a first port on the lower surface, and a second valve seat on the upper surface. and a fluid control valve having a second port formed therein, and a third port formed at a position facing a space formed by the lower surface of the ball valve and the valve chamber when the ball valve is seated on the first valve seat. The second port is connected between the check valve connected to the outlet of the evaporator in the cooling system and the low pressure side of the compressor, and the first port and third port are connected to the high pressure side piping of the cooling system. It is less expensive than those controlled by solenoid valves, and also requires no power, no control circuit, and no extra electrical wiring, and operates smoothly, so no noise is generated. It has the following characteristics. In addition, the first valve seat and ball valve respond to the pressure by opening when the pressure in the low-pressure circuit is low and closing when it is high, so when the refrigeration system is in operation, the refrigerant is normally circulated. When the refrigeration equipment is stopped, the second valve seat and the ball valve, which has a check valve function, immediately close, and at the same time, the pressure in the low pressure circuit suddenly increases, and the first valve seat and the ball valve close, causing liquid refrigerant to flow out to the pressure reducing device. Since the valve is closed during a minute period during which the evaporator is closed, superheated gas in the compressor and condenser is prevented from flowing into the evaporator via the suction line and the throttling device. Therefore, the power saving effect is greater than that of one without a fluid control valve, and the configuration of the valve device of the fluid control valve is also very simple, and the selection of its operating characteristics is not based on springs, etc., but on the port diameter, ball valve diameter, ball Since this is done by combining the weights of the valves themselves, there is almost no variation and it is possible to easily assemble products with high precision at low cost.

[Brief explanation of drawings]

Fig. 1 is a refrigeration cycle diagram of a refrigeration system according to an embodiment of the present invention in a state immediately before startup, Fig. 2 is a cross-sectional view of the main part of the fluid control valve before stopping corresponding to Fig. FIG. 2 is a pressure change diagram of the refrigeration device shown in FIG. 1. 1... Compressor S2... Condenser S3...
...Fluid control valve, 4, ..., Throttle 9 device, 5
,,,,, Evaporator, 6... Check valve, 1o...
...First valve seat S11...Port, 13...
,,Second boat,14,,,,,Third port. Name of agent: Patent attorney Toshio Nakao and 1 other person
l11 12 figure

Claims (1)

[Claims] A first valve seat and a first port are formed on the lower surface of a substantially cylindrical valve chamber in which a ball valve is slidably housed, and a second valve seat and a second port are formed on the upper surface, and the ball valve A fluid control valve having a third boat formed at a position facing the space formed by the lower surface of the ball valve and the valve chamber when seated on the first valve seat, a compressor, a condenser, a throttle device, an evaporator, and a reverse valve. A refrigeration system in which the first and third ports are connected to the high-pressure side piping of a cooling system consisting of a stop valve, etc., and the second port is connected to the downstream side of the reverse valve using the low-pressure side piping.