JPS58150761A - 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 provides a refrigerator i
Regarding this, the purpose is to obtain uniform frosting and extend the defrosting period by varying the heating temperatures of the refrigerant on the intake side and outlet side of both coolers.

Figure 1 C: The illumination shown is a flat cold 11V yaw case used in general (2);
A metal partition plate (
4), the first and second plate fin type coolers (5) (6), the axial flow blower (7), the cold air vent @f81, the storage room (9), and the opening. The air outlet and suction ports (110υ) are opened across the longitudinal direction C of both opposing edges of the unit, and the machine W (13) at the bottom of the main body includes a refrigerant compressor that constitutes a refrigeration system together with the two coolers. Tank (
1s, plate fin type condenser fl station and axial flow type air blower W
AS etc. are installed, and 1$1 and 2nd double cooler (5
) (Forcibly circulate the cold air heat-exchanged at 61 as shown in the arrow at IJ+71.
! It is for cooling.

As shown in Fig. 42, the refrigeration system consists of a compressor 11103 - a condenser fi number - a liquid receiver fil - a pressure reducing device an such as a thermostatic expansion valve equipped with a temperature sensitive section (1 fi) V - an s2 cooler (6) - The first cooler (5) - A closed circuit C is constructed by forming an annular ma with the high pressure gas pipe fl mounted on the gas-liquid separator fil, the low pressure liquid pipe 12D and the low pressure gas pipe. , the refrigerant circulates as shown by the arrow to form a refrigerant that is compressed, condensed, liquefied, decompressed, and evaporated. Among the two coolers, the first cooler (5) has a large number of plate-like fins (5 members) with rough pips and good heat conduction, and both tubes made by Yukin located on both sides of the fins. Plate (511) (5 m), a plurality of metal refrigerant conduits (
501) (504) and adjacent conduits among these conduits! Mutual (:!KI multiple gold a*V-shaped (5D)
and C;
1gm arrangement 1gi, and the sz cooler (6) has a pip tightly (
A large number of plate-shaped fins (6A) with good heat conduction
), both sides C of this fin; both tube sheets (6B) (6B) of the disposed fins, and a plurality of mWS refrigerant conductors t (601) passing orthogonally through each of the fins and both tube sheets. (604
) and which conduit is adjacent to this conduit? A refrigerant conduit (601) consisting of a plurality of mutually connected U-shaped U-shaped parts 11 (6B) and Beni, arranged on the leeward side C of the 441 cooler (5), and the most downstream refrigerant conduit (601) on the air inlet side. v111 cooler (
It is connected to the most downstream refrigerant conduit (50 m) of the nitrogen discharge row (5) through a communication conduit (to). Note that the white arrow indicates the flow direction Y of the cold air passing through the cooler.

Such a 5m refrigeration system has already been published in Japanese Utility Model Publication No. 15457/1983; it is well known, and the evaporation temperature of the refrigerant passing through both the 41 and s2 coolers (51f6) is as follows from the air outlet side of the lI2 cooler (6). 9 air inlet side 1 of the first cooler (5): The temperature becomes higher on the air inlet side of the first cooler (5), and the temperature of the cold air flow increases from the air inlet side of the s1 cooler (5) to the second cooler (6). Air outlet tiI! lI: gradually becomes (-low), and as a result, the cold air flow is pre-cooled and dehumidified by the first cooler (5), and then C: the second
The action of lowering the temperature to a predetermined temperature with the cooler (6) (from -)
11 frost can be dispersed in both coolers (51 (6) + 2 to lengthen the defrosting interval (2, 111 cooler (5)
It is known that the effect of the pressure reducing device (17) on the air inlet side of the refrigerant is that it can further heat the refrigerant and prevent liquid leakage to the compressor a3.

However, is it cold? 1, the difference between the refrigerant evaporation temperature in the conduit (601) of the lI2 cooler (6) and the refrigerant evaporation temperature in the conduit f(5(z) of the 'I11 cooler i51) is large, and the cooling in the supercooled state is The moisture contained in the airflow is 111?
I? There is a lot of frost on the air inlet side of each fin (5A) of the first cooler (5). This caused the blockage to occur earlier due to frost. In order to avoid this, the fin pitch of the second SI cooler (6) is 41, and the fin pitch of the cooler (5) is closer to the fin pitch of the cooler (5). ), the amount of frost on the plate has decreased, but the island exchange has become worse, and a new drawback has arisen: the cold air I!l! cannot be lowered to the temperature of 1!.

That is, the inventor of the present application has created a frozen
(ll (knee width 155am, height 1!50Q11. height 5
In 11 countries, the first cooler (5) with fin pips 16■ and the $2 cooler (61) with the same width, length, and height as this s1 cooler but with a fin pitch of 10 mm have a spacing of 5011. The refrigerant 'IkeR-502' was sealed in the refrigeration system, and the refrigerant evaporation temperature in the conduit 61 was set to -40℃,
Evaporation pressure k 0.3 % () 1. Under the conditions of an outside temperature of 24°C and a humidity of 8096, the refrigerant evaporation temperature and cold air flow temperature in both the first and second coolers +51 (6) (= The temperature characteristics shown in Fig. 114 were confirmed through continuous experiments.'@Fig. 6)
is the refrigerant evaporation temperature passing through Jf (6) 1,
((ff5) is the evaporation temperature of the refrigerant passing through the first cooler (5), and the diagonal line (85) (halo) is the sl and second SI cooler t5
) (60;) is the most frosted part.

The refrigerant exits the second cooler (6) at -40°C, enters the lI2 cooler (6), is superheated by 5°C, and cools down at -55°C! ! ! (5) (2. The difference between the refrigerant evaporation temperature and the cold air flow temperature is 12 on the air inlet side of the cooler (5).
℃, 9℃ on the air inlet side of the second cooler (6), and lI
The air inlet side of the second cooler (6), which is long enough to superheat the refrigerant only on the air inlet side of the first cooler (5) and has a large air path resistance, was blocked by frost C2 about 12 to 14 hours after the start of cooling operation. The present invention was made in order to reduce the number of times the defrosting operation was performed, and an example thereof is shown in Fig. 45 below (Fig. 45). The same reference numerals as in Fig. 3 and Fig. 2 are the same.

High pressure liquid refrigerant from the r'41e home liquid receiver! No. 2 same type; flow dividers such as T-shaped pipes, (20A) and (20Ii1) are high-pressure liquid branch pipes, (1
7A) and (17B) are pressure reducing devices such as temperature-type expansion valves connected to the high-pressure liquid branch pipe [two ports are connected to each other and equipped with temperature-sensing parts (17A) and (17B), respectively, and (21A) is the inlet. End l The outlet end of the pressure reducing device (17A), the outlet end of the air outlet side of the second cooler (6), the most downstream conduit (606) (two connected low pressure liquid pipes, (2131) the inlet end of the pressure reducing device (25 people) are II
The most downstream conduit (604) on the air outlet side of the second cooler (6) and the first cooling! +51 air outlet side most downstream conduit (504
) and connecting conduit, (25B) is the 112 cooler (
The most upstream conduit (601) on the air inlet side of 61 and the most downstream conduit (501) on the air inlet side of vessel(
5) 9 Ki Exit I! The most upstream conduit (504), ? The most upstream conduit on the power inlet side (501) C is a low-pressure gas branch pipe with its inlet end connected to both low-pressure gas branch pipes.

Combine the low pressure gas t-, 1 from the low pressure gas pipe @1; lead to a collector such as a T-shaped pipe, and the penalty is a low pressure gas branch pipe (2 1) g
is an evaporation pressure regulating valve that is provided and maintains the refrigerant evaporation temperature t on the 9th inlet side of the second cooler (6) higher than the refrigerant evaporation temperature on the 9th outlet side of this cooler.

According to the refrigeration system 1, the refrigerant that has become a low-pressure liquid by the pressure reducing device (17A) is transferred from the 9th outlet side of the 2nd cooler (6) to the air outlet (II) of the 111th cooler (5) under reduced pressure. Device(
17B) (: The refrigerant that has become a lower pressure liquid is transferred to the 112 cooler (
6) from the air inlet side of the 181 cooler (5), the air inlet side of the 181 cooler (5) is evaporated, and the low pressure gas branch pipe (22A
) < 22B) Repeat the steps A/ to collect at the collector and return to compression III. At this time, the evaporation temperature of the refrigerant on the 9 electric inlet side of the 112 refrigerant Is unit (6) is 1IA4
1 pressure! It is controlled by C2 to obtain superheat higher than the evaporation temperature of the refrigerant flowing into the air outlet side of the second cooler (6).

The results of experiments on the refrigeration system of the present invention under the same conditions as conventional refrigeration systems will be explained using villa diagrams. Incidentally, 4th Si: T(5) (("6) is the evaporation temperature of the refrigerant passing through both the 111 and the second cooler +51+6 of the refrigeration system of the present invention.

According to this experiment C:, the refrigerant evaporation temperature on the air outlet side of the s2 cooler (6) is -40°C, the refrigerant evaporation temperature on the air inlet side is -55°C, and the refrigerant on the air outlet side of the 411 cooler (5). The evaporation temperature is -55℃, and the refrigerant evaporation temperature on the air inlet side is -50℃.
Therefore, the difference between the refrigerant evaporation temperature and the cold air flow temperature is 7°C at the air inlet side of the s1 cooler (5), 4°C at the air inlet OgIA of the second cooler (5), and the difference is evaporation pressure - valve regulation (rotator). ) (2 @2 air inlet of cooler (6) (5 with refrigerant flowing)
℃ superheat obtained air inlet 01 of s2 cooler (6)! In addition to reducing the difference between the refrigerant evaporation temperature and the cold air flow temperature at E, superheating of 5°C (evaporation pressure Q, 45~0.5~G) is obtained on the air inlet side of the first cooler (5). The air inlet of the vs1 cooler (5) [refrigerant evaporation temperature and cold air flow temperature at II42! can be made small, and as a result, ′s
Without reducing the heat exchange of the second cooler (6) (until the blockage between each fin (6A) due to frost), it is possible to cover the space between each fin (6A) without reducing the heat exchange between the ill and the second cooler (6). The frost formation became uniform, and defrosting operation started approximately 20 hours after the start of cooling operation. Note that 1] 11 and 2nd cooler + 5) (61 is tube plate (511) (4B) t' may be standardized.

Figure 45 shows another embodiment of the present invention, two compressors (15 people) (1511) and a condenser (14 people) (141).
1), liquid receiver (16A) (1611), gas-liquid separator (1)
8A) (18B) Ite 1g for V! The refrigerant flows from the outlet side of the cooler (6) to the air outlet side of the s1 cooler (5), and from the air inlet side of the second cooler (6) to the first cooler (5).
The refrigerant hidden on the air inlet side of the 1-car compression 111 (15
A) (15B) has the same amount of work or both coolers (51
(61 air inlet Oa refrigerant supply compression fi (15B
) has a smaller amount of work than the other.

According to the configuration (:), the evaporation temperature of the refrigerant flowing on both the air inlet side and the outlet side of the cooler (6) is equal to C.
Even when the temperature is set to 0℃, the air inlet side of the cold airflow that is exchanged with both refrigerants is higher than the outlet side, and the refrigerant evaporation temperature on the air inlet side is -55℃, which is higher than the air outlet side. Same effect as C: More s1 cooling! The refrigerant evaporation temperature on the air inlet side of 1f5) is higher (-30°C) than on the air outlet side, and it is possible to obtain the temperature characteristics shown in Figure 114 (port "5) (CF3H: By superheating the refrigerant on the air inlet side of 6), the difference between the refrigerant evaporation temperature and the cold air flow temperature can be reduced on the air inlet side of both coolers +51+61, and the heat conversion of the 1JI2 cooler (6) is achieved. This allows for a longer period of time for the two fins (6 fins) to close without damaging the frost, and evens out the frost formation on both coolers. By making it longer, I was able to reduce the number of defrosting cycles.

As described above, in the present invention, the coarse s1 cooler of the finpip and the fine 112 cooler of the finpip are installed side by side with an interval of t, and the cold air flows from the 11 cooler to the 2 cooler (2, Refrigerant! In the refrigeration system from the air outlet side of the second cooler to the air inlet side of the St cooler, there are at least two pressure reducing devices that reduce the pressure of the high-pressure liquid refrigerant, and the reduced pressure of the refrigerant is $2 From the air outlet side of the cooler F) 18m Air outlet side of the cooler - 2, from the air inlet side of the other refrigerant t'i 12 cooler to the air inlet side of the s1 cooler (= one equipped with a snow path for each to flow) Therefore, when the refrigerant is heated in the opposite direction to the flow direction of the cold air, there is an opening [1] from the air outlet side of the two-car cooler to the
g:, C two slopes so that it becomes higher! C;
, without impairing the heat exchange of the s2 cooler (the time for frost blockage between each fin can be lengthened), the frost formation on each of the two coolers can be made uniform, and the number of times of removal can be reduced. can.

[Brief explanation of drawings]

Ill is a longitudinal cross-sectional view of a commonly used refrigerant case, s2 is a conventional refrigeration system, and the T refrigerant circuit is
The third factor shows the embodiment of the refrigeration system of the present invention, T refrigerant circuit factor, i
Figure '44 is a characteristic diagram showing the cold current and refrigerant evaporation temperature in the refrigeration apparatus of the present invention and the conventional one, and Figure 4m5 is a refrigerant circuit diagram showing another embodiment of the present invention. 15)...First cooler, (5A)...Fin, (5
01)~(504)...Conduit, (6)...42 Cooler, (6A)"・°Fin, (601~C604)...
・Conduit, (17A) (17B) - = pressure reducing device, (25A
) (25B)...Communication conduit. 1117Figure 1 11I4Figure ρJ11'1 *2Figure 11!3Figure 115m1 廿

Claims (1)

[Claims] t A first cooler with a coarse fin pitch and a cooler with a coarse fin pitch of 42 are installed side by side with a gap between them, and the cold air fits.
-41 cooler to 11g2 cooler outlet, refrigerant t' $2 From the 9 liner outlet side of the cooler to s1 cooler air inlet fil (:f
In the refrigeration system, there are at least two pressure reducing devices that reduce the pressure of high-pressure liquid refrigerant, and one refrigerant whose pressure has been reduced is transferred from the air outlet side of the second cooler to the air outlet side of the first cooler, and the other refrigerant is From the air inlet side of the second cooler to the air inlet side of the first cooler (-respectively, the refrigeration device is equipped with a flow T pipe and a metal.