JPS59115940A - 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 Field of Industrial Application The present invention relates to a refrigeration system such as an air conditioner, and more particularly to a refrigerant control system for starting and stopping the refrigeration system.

Configuration of conventional example and its problems Refrigerant control device when starting and stopping conventional refrigeration equipment 198
2 PURDUE COMPRESSORTECHNO
ANANARYSI of LOGY CONFERENCE
S OF A NEW TYPEREFRIG
ERATION and is shown in Figure 1. In FIG. 1, 1 is a compressor, and a current cutoff element 2, a condenser 3, an on/off element 4, a capillary tube 5, an evaporator 6, and an accumulator 7 are connected in a ring to form a refrigeration system. The current cutoff element 2 and the suction side of the compressor 1 are connected to a bypass circuit 8.
are connected.

During cooling operation, the bypass circuit 8 is closed and the refrigerant is transferred to the compressor 1, current cut-on element 2, condenser 3, on-on element 4, capillary tube 5,
It flows to the evaporator 6, accumulator 7, and again to the compressor 1 to perform a normal cooling action. On the other hand, when stopped, the on/off element 4 is closed, and the current cassette element 2 closes the circuit of the capacitor 3 and opens the bypass circuit 8 to maintain the pressure balance between the high pressure side and the low pressure side of the compressor 1. Make it. Current Kanotoo Element 2
Since the liquid refrigerant in the condenser 3 that has been turned off by the on-off element 4 is maintained in the operating state until the next operation, the cooling start-up during the next operation can be accelerated and energy can be saved.

This is a reduction in so-called starting loss. Although the configuration and effects of the conventional example have been described above, it also has the following drawbacks. When the operation is stopped, the high-pressure side and low-pressure side of the compressor 1 are equalized to equalize the pressure, so the high-temperature and high-pressure gas that remains on the high-pressure side of the compressor 1 flows into the low-temperature evaporator 6 and condenses. (heating and heat load) hinders energy conservation. As the use of rotary compressors (high-pressure container type) has progressed in recent years, the amount of high-temperature, high-pressure gas has increased, which further impedes energy conservation, and also has the disadvantage of increasing the startup loss required to create high pressure inside the closed container. are doing. In addition, the power 1/torque offset element 2 closes the main circuit to the capacitor 3 and opens the bypass circuit 8 when the motor is stopped, so the structure is complicated and expensive.

OBJECTS OF THE INVENTION Therefore, it is an object of the present invention to provide a refrigeration system which is further energy efficient, has a simple structure, and is inexpensive.

Structure of the Invention To achieve this object, the present invention provides a high-pressure valve and a low-pressure valve that are disposed on the upstream and downstream sides of the evaporator of the refrigeration cycle, and are opened when the refrigeration system is in operation and closed when the refrigeration system is stopped. In addition, by providing a bypass valve that bypasses the high-pressure side and low-pressure side of the compressor when the compressor is stopped, and which closes at a predetermined number of rotations of the compressor or less and opens at a speed lower than that, the high-temperature, high-pressure gas on the high-pressure side of the refrigeration equipment is removed when the refrigeration equipment stops. Fig. 9 shows a reduction in the pressure increase time on the high-pressure side of the refrigeration equipment when restarting, a reduction in so-called starting loss, and a reduction in the so-called start-up loss. This makes startup easier by equalizing the pressure on the low pressure side.

DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the accompanying drawings. Second
In the drawings to FIG. 5, reference numeral 11 denotes a high-pressure container-type hermetic compressor (hereinafter referred to as a rotary compressor), which is composed of a hermetic container 12, a compression element 13, and an electric element (not shown). And refrigeration equipment u, rotary compressor 1
1,: I-assay 14, high pressure circuit 15a of fluid control valve 16
, a capillary tube 16, an enoprator 17, a low pressure circuit 15b of the fluid control valve 15, a suction line 18, and a rotary compressor 11, which are successively connected in an annular manner. The fluid control valve 15 has a high pressure circuit ISA at the top;
The low voltage circuit 15b is arranged substantially vertically at the bottom. The fluid control valve 16 has an outer shell 21 formed by a high-pressure side casing 19 having a substantially hollow cylindrical shape and a low-pressure side casing 2o also having a substantially hollow cylindrical shape, and maintains airtightness. Inside the outer shell 21, there is a bellows 22 that partitions the high voltage circuit 15a and the low voltage circuit 15b and expands and contracts in response to the pressure of the two circuits.
has been set up. At the center of the lower end of the bellows 22 is a coil spring 23 that urges the bellows 12 upward in the figure.
A retainer 24 is provided below the retainer 24 for holding the coil spring 23, regulating excessive movement of the bellows 22, and preventing damage. The retainer 24
has a plurality of small holes 24a, 24a, etc. for the bellows 22 to correctly sense the pressure of the low pressure circuit 15b.
is the provision. This retainer 24 has both casings 19
It is held between ゜2o. On the other hand, the high-pressure side casing 19 has an inlet pipe 19a, an outlet pipe 19b, and a valve seat 19C, and a cylindrical plunger 26 is housed in substantially the center so as to be slidable up and down. A high pressure valve 26 made of a ball valve is fixed to the center of the upper end of the plunger 25 by caulking to form a high pressure side valve device 27. A recess 25a is provided at the lower end of the plunger 26 for integrally attaching the plunger 26 and the bellows 22, and the bellows 22 is integrally clamped and supported by caulking. The low pressure side casing 20 also includes an inlet pipe 20 a and an outlet pipe 2 ob.

It has a valve seat 20c, and a notch 28a forming a gas passage is provided at the outer edge of the shaft, and a low pressure valve 28, which is a one-flap valve, is movably accommodated. Above the low pressure valve 28, a stopper 29 for regulating excessive movement of the low pressure valve 28 is press-fitted and fixed into the low pressure side casing 2o, and a low pressure side valve device 30 is installed.
is formed.

Next, the rotary compressor 11 will be explained. The suction passage 31 of the compression element 13 is provided with a side passage 33 that communicates with a high pressure space 32 within the closed container 12 . Said side road 33
The upper part of the valve seat 34 has a valve seat 34, and the valve seat 34 has a substantially star-shaped valve 35 whose outer circumference is partially cut out.
Hollow valve stopper 36 that restricts movement due to excessive movement of 5.
has been established. A bypass valve 38 is configured by disposing a spring 37 on the outer peripheral side lower part of the waste valve 36 to bias the valve 35 upward (in the opening direction).

This bypass valve 38 has a synchronous speed of 26~
The dimensions of the side passage 33 and the biasing force of the spring 37 are set so that the circuit is closed at a rotation speed of about 60% and opened at a rotation speed below that.

That is, the force F2 applied to the suction passage 31 side of the valve 35 and the force F2 applied to the suction passage 31 side of the valve 35
The force F1 applied to the high pressure space 32 side of the sealed container 28 is
Following activation of compression element 30, its synchronous speed (e.g. 3
600 rpm), when Fl〉F
2 and closes the valve 35.

In the above configuration, when the refrigeration system is in operation, the electric element of the rotary compressor 21 operates at a speed close to the synchronous speed, so the bypass valve 38 closes and performs a normal compression operation.

Therefore, the high pressure side of the refrigeration system is at the normal high pressure, and the low pressure side is also at the normal low pressure, so the bellows 2 of the fluid control valve 15
2 pushes down the coil spring 23 due to the pressure difference between the high voltage circuit 15a and the low voltage circuit 15b, and extends until it reaches the retainer 24. Therefore, the high pressure valve 26 is operated by the valve seat 19 by the plunger 25 which is integrally attached to the bellows 22.
At c, the pressure difference between the high pressure circuit 15a and the evaporator 17, and the sum of the biasing force of the coil spring 23 separates the adsorbed part, and the high pressure side valve device 27 is in an open state. On the other hand, the low pressure valve 26 of the low pressure side valve device 30 is connected to the evaporator 1
The valve seat 20c is blown up by the gas flow flowing in from 7.
and comes into contact with the stopper 29. Gas flows through the gap between the notch 28a on the outer edge of the low pressure valve 28 and the stopper 29 without any problem as shown by the arrow a in the system, and the low pressure side valve device 30 is in an open state. Therefore, rotary compressor 1
The refrigerant gas discharged from the condenser 14, the high pressure circuit 16a of the fluid control valve 15, the capillary tube 16,
Evaporator 17. low pressure circuit 15b of fluid control valve 15,
It flows without any problem to the suction line 18 and the rotary compressor 11 to perform the refrigeration action.

Next, the state in which the refrigeration system is stopped will be explained.

Since the gas flow from the evaporator 17 is stopped due to the stop of the rotary compressor 21-, the low pressure valve 28 in the low pressure circuit 16b of the fluid control valve 16 falls under its own weight, and the valve seat 20
c is still in contact with the low pressure side valve device 30 to close the circuit. As a result, the superheated gas from the rotary compressor 11 is prevented from flowing backward into the compressor 17. As time further elapses, the superheated gas in the closed container 12 flows into the cylinder chamber 39 of the compression element 13, flows into the suction line 18 via the suction path 31, and flows into the low pressure circuit 15b of the fluid control valve 15 (the first 3), the pressure in the low pressure circuit 15b rises rapidly and becomes approximately the pressure in the high pressure circuit 15a. Both circuits 15
When the pressures in the circuits 15a and 15b are approximated, the biasing force of the coil nut 23 provided below the bellows 22 is applied to both circuits 15a and 15.
The force generated in the bellows 22 due to the pressure difference b is overcome, the plunger 26 is pushed up 2, and the high-pressure side valve device 27 is closed, preventing superheated gas from the condenser 14 from flowing into the evaporator 17. do. At this time, since the pressure in the high pressure space 32 and the pressure in the side passage 33 are approximately equal, the bypass valve 38 is opened by the biasing force of the spring 37 and maintains a waiting state for the next activation.

When the refrigeration system is next started up, the bypass valve 38 is still open and no compression is performed at low torque of 300 rpm (approximately 9% of the synchronous speed of 3600 rpm), which is called the starting torque or pull-up torque of the electric element. , the speed of the electric element increases rapidly and the torque also increases rapidly. When the rotational speed of the electric element reaches a predetermined speed (25 to 60% of the synchronous speed), the bypass valve 38 closes and starts compression, but the electric element has sufficient torque and no failure to start occurs. The system will return to normal operation. When the rotary compressor 21 shifts to normal operation, the pressure in the suction line 18 decreases, the low pressure side valve device 30 opens, and the pressure in the low pressure circuit 16b decreases, so the bellows 22 extends downward and is connected to the bellows 22. The plunger 25 opens the high pressure side valve device 27. Therefore, the refrigerant discharged from the rotary compressor 11 is
It circulates again to the rotary compressor 11 from the condenser 14, the high pressure circuit 15a of the fluid control valve 15, the capillary tube 16, the evaporator 17, the low pressure circuit 15b of the fluid control valve 16, and the suction line 18, and performs a normal cooling action.

Effects of the Invention As is clear from the above description, the refrigeration system of the present invention includes a fluid control valve, and 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 a check valve is connected between the condenser and a pressure reducer such as a capillary tube. A functional low-pressure side valve device is connected to the suction line between the evaporator and the rotary compressor, and a high-pressure side valve device responds to the pressure by opening when the pressure in the low-pressure circuit is low and closing when the pressure is high. When the refrigeration equipment is in operation, the refrigerant circulates normally, and when the refrigeration equipment is stopped, the low-pressure side valve device with a check pulp function immediately closes, and at the same time the pressure in the low-pressure circuit suddenly increases and the high-pressure side valve device closes immediately. Since the valve is closed, the superheated gas in the closed container and the condenser is prevented from flowing into the evaporation lake via the suction line and the pressure reducing device. In addition to reducing so-called stoppage loss, the effect of preventing the high-temperature, high-pressure superheat gas in the closed container from flowing into the volator is very large.

Since the pressure state and refrigerant state of each part of the refrigeration system are maintained in the operating state while the system is being shut down, the start-up of cooling upon restart is very quick, and so-called startup loss can be reduced. However, since this fluid control valve integrally forms the high-pressure side valve device and the low-pressure side pressure device for heat exchange, the liquid refrigerant flowing out from the condenser is overheated by the low-temperature superheat gas, which is the waste cooling heat flowing out of the evaporator. By performing cooling, the refrigeration effect can be increased, and further power consumption can be reduced to some extent.

In addition, it is equipped with a bypass valve that bypasses the high-pressure side and low-pressure side of the rotary compressor, and the binox valve is configured to close when the rotary compressor exceeds a predetermined rotation speed and open when the rotation speed is lower than that, so it is bypassed when the rotary compressor is started. Since the valve is activated in a no-load state, it is possible to use an inexpensive low-starting-torque motor such as a so-called PSC motor.

[Brief explanation of the drawing]

FIG. 1 is a refrigeration cycle diagram of a conventional refrigeration system, FIG. 2 is a refrigeration cycle diagram of a refrigeration system showing an embodiment of the present invention, and FIG.
The diagram shows the state of the fluid control valve when the refrigeration system in Figure 2 is stopped,
4 is a sectional view of a main part of the compressor shown in FIG. 2, and FIG. 5 is an enlarged sectional view of section A in FIG. 4. 11... High pressure container type hermetic compressor, 14...
... Capacitor, 16 ... Pressure reducer, 17.
・・・・・・Work/borator, 18...Suction line, 21...Fluid control valve, 26...
・High pressure valve, 15a... High pressure circuit, 27...
...High pressure side valve device, 28...Low pressure valve, 15b...
...Low pressure circuit, 30...Low pressure side valve device, 38
...Bypass valve. Name of agent: Patent attorney Toshio Nakao and 1 other person No. 1
Figure 2 Figure 2 4 Figure 3 Figure 4 Figure 1 Figure 5

Claims (1)

[Claims] The fluid control valve is comprised of a high-pressure container-type hermetic compressor, a condenser, a pressure reducer, an evaporator, a suction line, a fluid control valve, etc.; The high-pressure side valve device includes a low-pressure side valve device including a low-pressure valve and a low-pressure circuit, the high-pressure side valve device is connected to the upstream side of the evaporator, the low-pressure side valve device is connected to the downstream side of the evaporator, and the high-pressure valve is connected to the high-pressure side. The low pressure valve operates based on the pressure difference between the high pressure circuit and the low pressure circuit, and maintains a closed state when pressure approaches, the low pressure valve operates as a check valve, and the high pressure valve operates due to the pressure difference between the high pressure circuit and the low pressure circuit. The high pressure valve is integrally connected to the operating pressure responsive body, and the pressure responsive body is connected by a spring to the high pressure valve. The hermetic compressor is biased in the closing direction, and the hermetic compressor is provided with a bypass valve between an internal or external high-pressure side and a low-pressure side that closes at a predetermined rotation speed of the hermetic compressor or more and opens at a rotation speed lower than that. Refrigeration equipment.