JPS5941746A - 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 cycle performed by connecting component equipment to improve refrigeration capacity and efficiency, and the main components of a conventional refrigeration cycle with 46 vapor pressure angles. The refrigerant system was as shown in Figure 1. In FIG. 1, (1) is a refrigerant compressor 1, (2) is a condenser, (3) is an expansion valve, and (4) is an evaporator. Figure 2 shows this refrigeration cycle in terms of pressure (P) and enthalpy (I), and is plotted on P-I, where points (a) to (b) are compression.

(b) to (C) condensate, (c) to (d) expand, (d
) to (a) show the evaporation process. In this figure (a
) to (d) are Ia, Ib, Ic,
Id Kcal/kg, and the refrigerant circulation amount is G kg/'
If Hr is the cooling capacity=(Ia-1cl)XG, the pressure required for turning the hook is (Ib-Ia)XG.

The explanation of the conventional refrigeration cycle is continuous, but the cylindrical cycle will be explained below. In Figure 1, the condenser (2
) is the Akane performance, and the state of C is supercooled to the state shown by G', and the cooling capacity car (Ia Id')
becomes G, and the ability increases by (Id-Id')XG.

Figure 8 shows that in order to make the supercooling of the refrigerant liquid larger than before,
Another refrigeration system with 10% of the main circuit compression M (1) is used in parallel. In the figure, 01) is the secondary compressor, 0 is the secondary condenser, and 0 is the secondary expansion 111B valve.

θ4 is a supercooler, which includes a heat exchanger (c) for supercooling the high-pressure liquid in the main circuit.

FIG. 4 is a P-1 diagram of this cycle. The refrigerant liquid is supercooled to Ic', which is greater than the supercooling performed in a normal condenser (2), so the refrigerating capacity - (Ia - I
d') Becomes XG and ability increases.

(Id-Id')XG=(Ia'-Id)XG' holds true. G' is the amount of refrigerant circulated in the secondary refrigeration system. The required power of the secondary compressor is (Ib'-1a') XG
'is. Since the evaporation pressure Pd in the secondary circuit is better than the evaporation pressure Pd' in the main circuit, the obtained refrigeration capacity per unit required power is large, and the efficiency of the entire refrigeration system consisting of the main and secondary circuits is improved.

Since the conventional refrigeration equipment is constructed as described above, it has the following drawbacks.

(1) In the method shown in FIG. 1, the condenser using water or closed air does not provide sufficient supercooling.

(2) Since the method shown in FIG. 8 requires two independent systems of refrigeration, it requires two condensers and a large number of pipes, resulting in a refrigeration system of the same price but with poor design.

This invention was made in order to eliminate the above-mentioned drawbacks of the conventional technology, and is a compact, inexpensive, and high-pressure refrigerant liquid superfluous system that uses two compressors with different capacities and a common condenser 18. The purpose of this invention is to provide a refrigeration system that can perform sufficient cooling.

An embodiment of the present invention will be described below with reference to the drawings.

In Fig. 5, (101) is the main circuit refrigerant compression (3+5
．． , (102) is the refrigerant compressor of the secondary circuit, (3) is the expansion valve of the main circuit, (4) is the evaporator of the main circuit, and (2) is the discharge for the secondary circuit J1. Condensed with Kas ゛lη゛ +'i
:<' (Connected to 21. Sub circuit Cφ expansion valve U
The side is straddled in the middle of an arrangement that connects the condenser (2) and the supercooler (1). α9 is a suction pipe exclusively for the slave circuit.

Next, in the refrigeration system according to the present invention, the refrigerant scum sucked in from the main circuit and the subcircuit will be explained as follows.
% (tot) and (102), respectively, and the discharge pipe (6)
Learn from condenser (2) through . The refrigerant liquid liquefied in the condenser (2) is divided into the main and cold circuits.
is circulated inside the heat exchanger (A) with supercooling of 4 circles, and the cooling of the slave circuit (1) is 7''
The refrigerant is steamed outside the S unit (to) and is sucked into several circuits of the refrigerant pressure knitting machine (102) through the suction pipe 09 of the subcircuit. On the other hand, the refrigerant liquid in the main circuit is supercooled and the main circuit l1g expansion valve C3)
The refrigerant is sucked into the refrigerant compressor (101) of the main circuit via the evaporator (4) to perform a cycle.

Figure 8 shows the cycle of this invention in a PI diagram, where a-+b→C'→d' is the main circuit.3'→l)'→(
−+ d indicates a slave circuit.

In addition, in the refrigeration system according to the invention of T., the evaporation temperature of the main circuit is -1
Is it particularly effective when used in the range of 5 to -35℃?The effect is most pronounced fti! (!The factor is the ratio of the refrigerant pressure in the main and slave circuits, f1?Lin's piston displacement (ratio of the main to slave ratio (hereinafter referred to as R)), and the refrigerant compressor displacement in the circuit (144). It is valid that fTtJ T&.

This is because when the ratio R described in IJ is large, supercooling becomes large, but the evaporation specific power of the sub circuit approaches the evaporation pressure of the main circuit, and the coefficient of performance does not improve. When R is small, there is little supercooling, so it approaches t+'<, which is the conventional case of insufficient supercooling shown in FIG.

In the actual example, a heat exchanger was used in which the supercooler was divided into main and sub-circuits, but all the liquid at the condenser outlet was transferred to the expansion valve 0.
3), the liquid component is supplied to the expansion valve (3) of the main circuit, and the gas component is sucked into the secondary compressor (102).

As described above, according to this invention, the refrigerant circulating in the main and sub-circuits is pressurized and then liquefied in a shared condenser, so it is possible to avoid the supercooling cycle using two independent refrigeration systems as in the past. There is a %J f, which can be done relatively cheaply and cheaply.

[Brief explanation of drawings]

Figure 1 is a cold storage piping system diagram of a conventional refrigeration system, Figure 2 is a P-I diagram of the refrigeration system shown in Figure 1, and Figure 3 is a combination of conventional refrigeration systems, Frozen% to perform supercooling of
Fig. 4 is a refrigerant piping system diagram for the refrigeration system shown in Fig. 3.
The I″-■ line diagram of FIG.
FIG. 6 is a P-I diagram of the cold east device shown in FIG. In the figure, (2) is a 6 [reduced type] that is shared by the main and slave circuits, and (3
) is the main circuit expansion 11P-valve, (4) is the 7-circuit power generator, 9 is the aeration cooler, and the track is the heat exchanger, (101) is the main circuit cold compressor, (102 ) is the refrigeration compression analysis of the slave circuit,
θ3 is an expansion valve of the slave circuit. Note that the same reference numerals in the figures refer to the same or corresponding parts. Figure 1 Figure 3 Figure 5 Figure 2 Figure 4 Figure 6

Claims (4)

[Claims] (1) A first refrigerant compressor, a second refrigerant compressor having a smaller valley than the first refrigerant compressor, and the first and second refrigerant compressors.
Refrigerant ffE H<? 4.9 is the condensation type that condenses the gas discharged off the coast, and is it liquefied in this condenser? ``i'j supercooling means for supercooling the refrigerant, and the gas refrigerant turned into scum by the supercooling means is heated to the second layer.
A refrigeration system characterized in that the supercooled liquid refrigerant is supplied to the first compressor through a first expansion valve and an evaporator. (2) The supercooling means includes a second expansion valve that reduces the pressure of a part of the liquid refrigerant liquefied in the condenser, and a low-temperature, low-pressure liquid refrigerant whose pressure is reduced by the second expansion valve. 2. The refrigeration system according to claim 1, further comprising a supercooler for subcooling by exchanging heat with. (3) A refrigeration system characterized in that the subcooling means comprises a second expansion valve that depressurizes all of the liquid refrigerant liquefied in the condenser, and a tank that receives the refrigerant depressurized by the second expansion valve. . (4) The ratio of the piston displacement of the first and second refrigerant compressors, where the ratio of the second refrigerant compressor to the first refrigerant compressor is the piston displacement of the first refrigerant compressor. Approximately 1
The refrigeration system f/M according to any one of claims 1 to 3, characterized in that the f/M ratio is 0.