JPH04116348A - Nearly reverse ericsson cycle refrigerating machine - Google Patents

Abstract

PURPOSE:To improve COP and compact the size of equipment by spraying different circulation oil in a respective actuation gas flow of a compressor and an expander and separating gas from said circulation oil directly after it is sprayed, and using the gas and the oil separately for radiation and refrigeration, and allowing both the gas and oil to be recirculated by a jet pump. CONSTITUTION:Cyclones 12, 13 for air and oil separation are installed to gas outlet passages 10 and 11 from a compressor 1 and an expander 2 respectively. A greater portion of liquid droplet is arranged to flow from flow down pipes 1 and 15. Then, the gas which has dropped most droplet at the cyclones 12 and 13 is introduced into an expander inlet passage 8 and a compressor inlet passage 6 by way of flow passages 18, 19, 20, and 21, 22, and 13. The circulation oil which flows down in the flow down pipe 14 from the cyclone 12 is fed again into a jet nozzle 7 from a compressor side oil jet pump 27 by way of a radiator 26 and a recirculated. The circulation oil which flows down in the flow down pipe 15 from the cyclone 13 is fed back to a jet nozzle 9 by way of an oil jet nozzle 29.

Description

[Detailed description of the invention] (1) Industrial application field There is currently a demand for a refrigerator that is CFC-free and has a high COP.
The present invention realizes an approximate Ericsson cycle refrigerator suitable for this purpose, and is intended to be used in all fields of home and commercial refrigeration and air conditioning.

(2) Conventional technology and its challenges The Rixon cycle has been studied as a theoretically brilliant, CFC-free, and high COP refrigerator, but the biggest challenge in its realization is compression. It is difficult to make the change in the state of the gas inside the expander and the expander an isothermal change.
, rather, it is closer to an adiabatic change with a large temperature change,
The various heat exchangers that dissipate heat and utilize the heat from the gas have become too large due to the low heat transfer coefficient of the gas.

゛(3) Means for Solving Problems and Problems 1. The present invention injects circulating oil of non-volatile I'4 low dried bamboo into the gas of a compressor and an expander as a fine spray, and its specific heat is Take advantage of the fact that it is big,
This makes the gas compression and expansion processes extremely close to isothermal changes (in addition, a set of circulating oil separated and collected in the air-oil separator immediately after the outlet of the compressor and expander can also be used for heat radiation and cooling. Since oil has a higher heat transfer coefficient than gas, the heat exchanger is also compact.

(4) Explanation based on an embodiment FIG. 1 is an explanatory diagram of an embodiment of the present invention using a diagram,
Fig. 2 (I) The state changes of the working gas and circulating oil in the embodiment shown in Fig. 1 will be explained by comparing them with the conventional cycle.] ~S
It is a (temperature-entropy) diagram. In Figure 1, 1 is a compressor (COM) and 2 is ]-kispanda = (EXP)
The type can be any type, but displacement types such as scroll type, rotary type, and twin screw type are considered to be the most suitable.

Reference numeral 3 denotes an electric motor (M) which supplies power to the compressor 1 and recovers power from the expander 2, and is sealed in a sealed gauging 4 together with the compressor 1 and the expander 2. Further, 5 is a counterflow regenerative heat exchanger (HX).

Now, as a feature of the present invention, the compressor gas person L-] (A
The injection nozzle 7 on the compression side is removed from the F path 6.

In addition, the expander's gas cylinder [injection nozzle 9 on the expander side in channel 8] is installed (respectively, non-volatile and low viscosity circulating oil is sprayed in fine droplets). blown into the gas stream as a compressor] and expander 2
There are people inside. In addition, the gas outlet L-1 channels 1° and 11 from the compressor 1 and expander 2 are provided with zykes 12 and 13 for separating gas and oil, respectively, to separate droplets present in the gas flow. Separate and collect most of the
It flows down from the C flow pipes 14 and 15.

Here, 16.17 is the liquid level inside the cyclone 12.13.

Next, the gas from which most of the oil droplets fell in cyclone 12 passes through the flow path 18.1.9.20 and reaches the expander person ``1' (
Directed to Ilt path 8. In addition, the gas coming out of the cycle E1-13 is guided through the flow paths 21, 22, and 23 to the compressor air flow path 6 (the flow path 6).
The flow path exiting from the gas radiator 24. The gas that passes through the counterflow regenerative heat exchanger 5 midway and exits the latter Ikron 13 passes through the cold heat utilization heat exchanger 25 that cools the brine with the cold heat of the gas, and the opposite flow regenerative heat exchanger 5 in the opposite direction. pass from.

In addition, the circulating oil, which has reached a slightly high temperature and flows down from the cyclone 12 to the downflow pipe 14, is cooled down to approximately the ambient temperature through the radiator 26, and then introduced into the compressor-side oil injection pump 27 and sent to the injection nozzle 7 again. It is configured to be circulated.

In addition, the somewhat low-temperature circulating oil flowing down from the cyclone 13 to the downflow pipe 15 passes through the cold heat utilization heat exchanger 28 that cools the brine with its cold heat and the expander side oil injection pump 29, and then is returned to the injection nozzle 9 and recirculated. It is configured like this.

The flow rate of the circulating oil is such that the total specific heat of the circulating oil injected per unit time is several times to 1 times the total specific heat of the gas flowing per unit time.
It is adjusted so that it becomes 0 times.

(5) Explanation of functions and effects The functions and effects of the embodiment in Figure 1 are explained below at T-8 (temperature ~
entropy) diagram. In the same figure, the curve ■] and the curve p += are the pressure P on the low pressure side of the gas and the pressure P on the high pressure side,
, i) shows isobaric entropy curves in 2. Also,
To represents the environmental temperature, and T represents the freezer temperature.

Now, point A indicates the state of the gas in the inlet [-1 flow path 7 of the compressor 1, point I3+,,l indicates the state of the gas in the outlet 1-j flow path 10 of the compressor, and A B l+l fil is inside the compressor. It is marked as (COM).

In the present invention, a large amount of circulating oil is injected into the inflow gas of the compressor at point A, and due to the presence of its specific heat, the inside of the compressor (C
The compression of the gas between OM) is close to an isothermal change, and the temperature is only -1-1 as shown in the figure. Point C is the state of the gas immediately after the gas radiator 24 exit L1, and point 5 is the state of the gas just before the inlet of the expander 2 after being cooled through the counterflow regenerative heat exchanger 5. The space between DE and E is marked with the symbol of the regenerative heat exchanger (1-IX). Point E indicates the state of the gas immediately after the outlet of the expander 2, and the space between DE and E is marked with the symbol of the expander (EXP).

Here, since a large amount of circulating oil is injected into the gas from point D when the expander 2 is turned on, the expansion of the gas in the expander causes the temperature to drop only slightly as shown in the figure. Point F indicates the state of the gas at the outlet of the gas brine cooler 25. Then, by passing through the regenerative heat exchanger (HX) again, the amount of heat obtained by the gas from point F to point A is regenerated by the amount of heat released from the gas from point C to point A.

Below 1. As shown in [V], the cycle through which the gas passes through the device becomes the ABCDEFA shown in Figure 2, which is very close to the reverse Ericsson cycle ACDF of ideal isothermal change, and the required power is sufficiently small, so the COP is extremely small. Recognize. If no circulating oil is used at all, adiabatic changes will occur in the compressor and expander, so the no-cycle will have a large area like AdDi, not indicated by the dotted line in Figure 2, and the required power will be correspondingly large. It is shown that the COP of the present invention is far superior to CJ since its COP is low.

Therefore, an approximate inverse Ericsson cycle with a higher COP than the present invention (J) is formed.Also, most of the amount of heat radiation and cooling is handled by the heat exchanger through which the circulating oil passes, but the heat transfer coefficient of the oil Since the heat transfer coefficient is higher than the heat transfer coefficient of gas, each heat exchanger is sufficiently compact to have a roaring effect.

In addition, in Fig. 2, the temperature of the circulating oil on the compression pj side is A.
The temperature of the circulating oil on the expander side is D.
You can think of it as going back and forth between E and E.

The compressor and expander used in the present invention are preferably of the volumetric type as described above, but they are of the velocity type because the relative velocity of the oil droplets and the gas flow is small (the relative velocity of the gas and the oil droplets). The loss would probably be too large, and the most recent types, such as the nuclear type and the twin screw type, seem to be most suitable.

As described above, the approximate inverse Ericsson refrigerator of the present invention can be used as a high-efficiency, CFC-free refrigerator or heat pump, and future development can be expected.

[Brief explanation of the drawing]

Fig. 1 is a diagram of an embodiment of the present invention (an explanatory diagram) Fig. 2 is a diagram illustrating changes in the state of the working gas and circulating oil in the embodiment of Fig. ~S (temperature ~ end L1 be) diagram. 1. Compressor 2, expander 5; counterflow regenerative heat exchanger 7.8; injection nozzle 12, +3; , 28; heat exchanger using heat

Claims (1)

[Claims] In a closed-cycle reverse Ericsson cycle refrigerator whose main parts are a compressor, an expander, and a regenerative heat exchanger, separate injection pumps are provided in the working gas flows of the compressor and expander, respectively. A large amount of non-volatile circulating oil is injected as fine droplet spray to make the compression and expansion processes of the gas sufficiently close to isothermal changes, and immediately after the compressor and expander, a gas-oil separation device such as a cyclone can be installed. The structure is such that not only the working gas but also the separated and collected two sets of circulating oil are used separately for heat dissipation and refrigeration, and the two sets of circulating oil are used independently. Approximate reverse Ericsson cycle refrigerator in which the fuel is recirculated to the injected injection pump. However, this refrigerator can be freely used as a heat pump, and the type of compressor, expander regenerative heat exchanger, gas-oil separator, working gas, circulating oil, etc. can be selected freely.