JPS59164869A - 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 system.

In a known refrigeration system, as shown in the system diagram in FIG. street,
After evaporating and vaporizing in the indoor heat exchanger 5, the refrigerant is sucked into the compressor 1 through the gas side operation valve 6. At this time, the expansion valve 3 detects the refrigerant temperature with a temperature sensing tube 7 attached to the suction pipe and cools the refrigerant. Controls the flow of an appropriate amount of refrigerant into the refrigeration circuit to maintain a constant degree of superheating.

The source side operation valve 4 is connected to the inlet pipe A as shown in the vertical cross-sectional view of FIG.
After passing through port E, the refrigerant flows into the indoor heat exchanger 5 through the outlet pipe B. At this time, since the core 13 is screwed into the body 14, insert a wrench into the hexagonal hole F and rotate it. Port E can be opened and closed by moving it. Before the start of operation, it is on the left and closes port E. When starting operation, it is moved to the position shown in the figure 1 to open port E. and \, the cover-17 is attached to the outer pipe 1o to prevent refrigerant leakage.
When the presser foot 18 presses down the body 14 etc., the presser foot 18 also lowers the outer tube 10 and prevents the refrigerant from leaking from the outer periphery.

However, in such a refrigeration system, the source side operation valve 4. Expansion: fP”r The three valves of the gas side operation valve 6 and the temperature sensing cylinder 7 require man-hours to install, connect them, and space to install them, which is an obstacle to downsizing and cost reduction of the refrigeration unit. It has become.

The present invention has been proposed in view of the above circumstances, and provides a refrigeration system that achieves miniaturization and cost reduction by integrating a liquid side operation valve, an expansion valve, a gas side operation valve, and a temperature sensing tube. I take that as a priority.

To this end, the present invention provides a valve main body that is partitioned by a partition plate/ζ first and second chambers, and provided in the first chamber and exposed to the refrigerant flow from the utilization side heat exchanger to the compressor and sealed. A telescoping electrical phase that expands and contracts with a heating medium, a variable orifice provided in the second chamber and through which a refrigerant flow passes from the heat source side heat exchanger to the user side heat exchanger, and a variable orifice provided through the partition plate. The variable orifice is cut 1 according to the expansion and contraction of the expandable member.
The present invention is characterized in that it is equipped with a compound operation valve consisting of an interlocking mechanism that changes the m product.

Embodiments of the present invention will be explained with reference to the drawings. FIG. 3 is a vertical sectional view showing the compound operation valve, FIG. 4 is a system diagram of the embodiment showing a modification of the compound operation valve of FIG. 3, and FIG. FIG. 5 is a system diagram showing an embodiment in which the present invention is applied to a heat pump type air conditioner, and FIG. 6 is a longitudinal sectional view showing a modification of the composite operation valve shown in FIG. 4.

In the above diagram, the same symbols as in Figures 1 and 2 are number 1, respectively.
2 shows the same members as in Figure 2, and 9 is a cylindrical valve body, which is partitioned into the right ventricle and left ventricle by a partition plate 23 to be described later, and the right ventricle is communicated with an inlet pipe A and an outlet pipe B. , an inlet tube C and an outlet tube communicate with the left ventricle. 12A and 12B
are located in the right and left ventricles, respectively) H and L
The port plates 13A and 13B are threaded onto the bodies 14A and 14B of the right and left ventricles, respectively, and the cores 16A and 1GB are threaded onto the bodies 14A and 14B of the right and left ventricles to open and close the ports H and L, respectively. A and 13'B as body 14. A
and 14. O-ring 21 seals against B, and 21 is a bellows filled with a heating medium, and its left end is connected to a plurality of rods 2.
0 is fixed to the port plate 12B. 22 is a nozzle plate 2 that sterilizes the orifice G formed in the partition plate 23.
4 to the right end of the bellows 21, 25
is a spring loaded between the nozzle plate 24 and the port plate 12A. .

In such a device, as shown in the dashed line frame P in FIG.
Inlet pipes A, C and outlet pipes 13, D correspond to pipes A, C and B, respectively, in the figure.

Since the refrigerant is evaporated in the indoor heat exchanger 5, it passes from the inlet pipe C to the boat L and the outlet pipe to the compressor 1.
is inhaled. At this time, the refrigerant that has passed through the po If it gets overheated enough＼
Since the refrigerant returns to the chamber N in a so-called overheated state, the bellows 21 is also overheated and expands.

Here, since the left end of the bellows 21 is fixed to the port L side via the rod 20, the bellows 21 extends only to the right and moves the nozzle plate 24 to the right via the rod 22 against the spring 25. It will push you in the opposite direction.

On the other hand, the refrigerant discharged from the compressor 1 is condensed and liquefied in the outdoor heat exchanger 2, and the inlet pipe AJ:...! 7 The refrigerant passes through the orifice G of the partition plate 23, passes through the port H, passes through the outlet pipe B, and enters the indoor heat exchanger 5. At this time, the passage is narrowed by the orifice G, and as a result, the refrigerant expands adiabatically and becomes low pressure and low temperature.

At this time, as mentioned above, if the indoor load is large,
Since the nozzle plate 24 is pushed to the right, the cross-sectional area of the orifice G is widened, and as the resistance is reduced, more refrigerant flows, and when a large amount of refrigerant is supplied to the indoor heat exchanger 5, The refrigerant is no longer overheated in the heat exchanger 5, the refrigerant temperature in the chamber N decreases, the bellows 21 contracts to the left, and as a result, the nozzle plate 2/I also moves to the left, and the cross-sectional area of the orifice G becomes smaller.

If the orifice G becomes smaller, the resistance increases, so the amount of refrigerant circulated through the orifice G decreases, and the refrigerant becomes overheated again, and the fluctuation of the nozzle plate 2/I becomes smaller and smaller.
Eventually, the balance will be at the right place.

The above describes the case where the indoor cooling load is large and the refrigerant is superheated and the bellows 21 is heated, but the same applies when the indoor cooling load is small, and the refrigerant flows into the chamber N at the saturation temperature, so the bellows When 21 is cooled and contracts, the nozzle plate 24 moves to the left by the spring 25, which narrows the cross-sectional area of the orifice G9.The resistance of the refrigerant increases, so the refrigerant flow rate decreases, causing it to overheat in the indoor heat exchanger 5. Eventually, the balance will be at the right place,
In this case as well, it usually stabilizes after repeating heating and cooling two or three times.

Now, go to the inlet pipe, C2 outlet pipe B, D, press tl'8A
, 18B are all airtightly connected to the valve body 9 with brazing or the like, but normally the inlet pipe C and the outlet pipe B are connected to the valve body 9.
Both are integrally formed by forging, etc., and the tips are each formed as a union.

0-rings 16A and 1.6B are similar to the 0-rings 16 in FIG.
/IA and 14B and is not essential for the operation of the refrigeration system, so the core 13
A, 13B and O-ring 16A.

16'B can be omitted, and in that case, the bodies 14A and 14B are also unnecessary, and the pressers 18A and 18B each become a blind plate.

The gas side operation valve 101 shown in FIG.
3B is omitted, and the gas side operation valve 1o'l is shown in the same figure.
A check valve 100 is inserted between the compressor 1 and the compressor 1.

The present invention can also be applied to a heat pump type air conditioner, as shown in FIG. The expansion valve 3 is opened during heating operation.

Furthermore, in the compound operation valve shown in FIG. 3, as shown in FIG.
05 may be adopted. According to such a composite operation valve, the operation and effect of the source side operation valve, gas side operation valve, temperature sensing cylinder, and expansion valve are also performed, so the assembly man-hours and the lowering distance are reduced to 1 man-hour. Significant reductions in parts prices, required space, etc. will result in a single unit.

In short, according to the present invention, the valve body is partitioned by a partition plate, and the first and second chambers are provided in the first chamber and the refrigerant flow from the utilization side heat exchanger to the compressor is provided. a variable orifice provided in the second chamber that allows the refrigerant to flow from the heat source side heat exchanger to the usage side heat exchanger, and the partition plate. A refrigeration system that achieves miniaturization and cost reduction is obtained by providing a complex operation valve similar to an interlocking mechanism that is provided through the telescopic member and changes the cross section and bond of the variable orifice according to the expansion and contraction of the telescopic member. Therefore, the present invention is extremely useful industrially.

[Brief explanation of drawings]

FIG. 1 is a system diagram showing a known refrigeration system, FIG. 2 is a longitudinal cross-sectional view showing the source-side operating valve of FIG. 1, and FIG. 3 is a longitudinal cross-sectional view showing an example of the composite operating valve according to the present invention. −1 ~
7 --噸7→→→Fig. 4 shows a system of an embodiment including a modification of the composite operation valve shown in Fig. 3, and Fig. 5 shows a system of an embodiment in which the present invention is applied to a heat pump type air conditioner. Figure, 6th
This figure is a longitudinal cross-sectional view showing a modification of the composite operation valve of FIG. 4. 1.Compressor, 2.Outdoor heat exchanger, 5.Indoor heat exchanger, 9.Valve body, 12A, 1213-.Port plate,
13A, 13B...core, 1/iA, '14B...body, 16A, 16B...0 ring, 18'A, 18B...
- Presser foot, 20... Rod, 21... Bellows, 22...
Rod, 23... Partition plate, 24... Nozzle plate, 25...
Spring, 100...Reversal valve, 101...Combined operation valve, 102...Reverse upward valve, 103...Heating capillary.
104... Four-way valve, 105... Diaphragm, A... Inlet pipe, B... Outlet pipe, C... Inlet pipe, D... Outlet pipe, G... Orifice, H... Port, K... Hexagonal hole. , L...Port, M...Hexagonal hole, N...Chamber, P...Combined operation valve, Sub-Agent and Patent Attorney Masafumi Tsukamoto

Claims (1)

[Claims] A first and a second partition formed by a partition plate within the valve body.
2. A retractable member provided in the first chamber and expanded and contracted by the sealed heat medium and exposed to the refrigerant flow from the utilization side heat exchanger to the compressor; and 2. A heat source side heat exchanger provided in the second chamber. a variable orifice through which a refrigerant flow passes from the to the user-side heat exchanger; and an interlocking mechanism that is provided through the partition plate and changes the cross-sectional area of the variable orifice in accordance with expansion and contraction of the expansion and contraction member. A refrigeration system characterized by being equipped with a composite operation valve.