JP2604235B2 - Jet ejector refrigeration system - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to a method for cooling a refrigerant liquid under low pressure, such as water or oil, to approximately 40 to 80 ° C.
Heat by the power of the order below, or the velocity energy of the refrigerant vapor generated by heating with exhaust heat, etc., is used for the jet ejector, and the surrounding low-pressure low-temperature refrigerant vapor is converted into pressure energy as a result, This is radiated to the ambient temperature outside the refrigerator to condense and liquefy, and this condensate is again sent to the low-pressure side of the vessel with a pressure difference, producing saturated steam (boiling steam) corresponding to the pressure in the low-pressure section of the vessel. More specifically, the present invention relates to a refrigeration method and an apparatus for cooling a working medium (water or oil) in a cooler disposed in the liquid in the low-pressure part of the container, and includes a general air conditioner, a refrigerated freezer, a warehouse, an in-car cooler, an indoor cooler, It is used in the refrigeration field.

(Prior Art) In recent years, a refrigerator using a conventional chlorofluorocarbon-based refrigerant has become a serious problem as a cause of global pollution.
In connection with this, wasteful use of energy has come to be regarded as future temperature pollution. And
In the field of utilization of solar thermal energy as clean energy, an adsorption refrigerator that can be used not only as a hot water supply but also as an energy source for cooling, using a low-temperature heat source of 80 ° C or less that is easily obtained with a solar erector Etc. are being developed.

This adsorptive refrigerator uses the adsorption and desorption of refrigerant (water) by a physical adsorbent such as silica gel, and has been known in principle for a long time. It has been put into practical use by the development of heat exchangers and the establishment of physical property data of adsorbents. However, the above-mentioned adsorption refrigerator has the following problems.

(A) The binding force between an adsorbent such as silica gel and a water vapor refrigerant is not only physical adsorption in which the surface and the adsorbed molecule (water vapor) are bonded by van der Waals force, but actually the surface atom and the adsorbed molecule (water vapor) )), It is clear from the experimental data that the adsorbent is evacuated to a weak chemical bond (chemisorption). That is, as seen in the dry system of a sorption pump and a sputter ion pump used to obtain a high vacuum system,
This means that the sorption pump requires a burnout (heat-out) heat source two to three times (44.2 KJ / mol × 2 or 3) the heat of physical adsorption. As described above, in the conventional adsorption refrigerator, the heat energy required for the transfer of the refrigerant requires two to three times the theoretical value (physical heat of adsorption), and the heat efficiency for the mass transfer of the refrigerant is low. .

(B) In an adsorption-type refrigerator using an adsorbent such as silica gel, heating and regeneration of the adsorbent and its cooling are essentially required. Cannot combine the two sets of adsorption refrigeration cycles to form a single refrigeration unit. For this reason, the conventional adsorption type refrigerator becomes large and expensive. In addition, the piping system is complicated due to the necessity of switching and the like.

(C) Further, in the conventional adsorption refrigerator, since the packing of the adsorbent such as silica gel is made denser to lower the transfer efficiency of the refrigerant, the heat exchanger for filling the silica gel between the fins is not filled. In order to make the layer thinner, the size of the heat exchanger has to be increased, and the heat exchanger acting as a condenser has also become relatively larger. In addition, during the adsorbent regeneration operation, a temperature difference occurs between the cooling water inlet and the cooling water outlet on the side of the evaporating condenser, and the thickness of the refrigerant liquid film on the surface of the condenser varies, and the evaporating speed deteriorates. In this case, the refrigeration capacity is reduced due to the drop of the refrigerant liquid to the lower part of the refrigerator body. In order to prevent this, measures such as heating of the bottom of the fuselage are taken, but this does not essentially improve the efficiency of the refrigeration capacity.

(D) Further, in the conventional adsorption refrigerator, it is necessary to cool the adsorbent after heating and regeneration, and a cooling water circuit and a cooling tower for that purpose are essential. For this reason, it is necessary to alternately switch the hot water and cooling water circuits, and it is expensive to install scales by using a closed cycle for the hot water system and cooling water system. And maintenance is required along with the generation of scale sludge due to the internal pressure of the heat exchanger.

And considering the atmosphere of Japan and the necessity of maintenance and inspection of the cooling tower, it was difficult to apply it to ordinary households.

As described above, the adsorption refrigerator using the low-temperature heat source (80 ° C. or lower) as a driving source actually has various problems.

(Technical Problems) The present invention has been made in view of the problems of the prior art, and in particular, has been able to continuously cool and freeze using a low heat input (80 ° C. or lower to 40 ° C.). The technical task is to obtain a refrigerator that can exhibit the excellent effects of simplifying the device, greatly improving energy efficiency, reducing the cost of the device, and preventing the occurrence of pollution compared to the adsorption refrigerator. is there.

(Technical Means) In order to solve the above technical problems, the present invention solves a problem in a refrigerator system represented by a conventional adsorption refrigerator using a low-temperature heat source, and improves energy efficiency. In order to achieve the purpose of continuous cooling as a refrigerator, heat that passes a heater or a heat source side heat medium into a vacuum vessel filled with a predetermined amount of refrigerant such as water, oil, a mixture of water and ethanol, etc. Using the exchanger as an evaporation generator of the jet ejector, the refrigerant vapor is sucked, pressurized, and heated by the ejector effect to promote the evaporation of the refrigerant, cool the refrigerant liquid, and operate the cooler installed in the refrigerant liquid. While cooling the medium, perform condensation of refrigerant evaporation in the vacuum vessel,
It also has a high electric field generating electrode device (insulating coating type electrode) for accelerating the evaporation of the refrigerant liquid in the container, and further has a heat pipe type heat exchanger.

Specifically, as shown in FIGS. 1 to 5, the following configuration is provided.

The refrigerant used in the present invention is water (distilled water) or ester-based DEP (diethyl phthalate) oil, and the like.
Water is used for general cooling and air conditioning, and oil is used for general refrigeration and freezing. Here, water is used as the refrigerant, but the use of oil or the like does not depart from the gist of the present invention in principle.

Reference numeral 1 denotes a jet ejector-type refrigeration apparatus, which includes a high-pressure steam generator chamber 2, a jet ejector body 3, a condensation chamber 4,
It comprises a low pressure evaporation chamber 5 and each chamber. The refrigerant liquid W stored in the inner bottom of the high-pressure steam generator chamber 2
A low heat energy input or an electric heater or the like 6 for heating and evaporating the refrigerant is provided. On the surface of the refrigerant liquid W, a ball tap 8A of a float valve 8 connected to a conduit 7 at the bottom of the condensation chamber 4 is provided. Floating.

Thus, the refrigerant liquid W liquefied and stored in the inner bottom of the condensation chamber 4
Is supplied to the high-pressure steam generator chamber 2 through the conduit 7 under the control of the float valve 8.
Also, since the height difference between the bottom of the condensing chamber 4 and the float valve 8 is kept at about 400 mm or more, the refrigerant liquid W is caused to act by the gravity action with the vapor pressure P ₁ in the high-pressure steam generator chamber 2. The flow is made sufficiently easy against the pressure difference (P ₁ −P _m ) from the vapor pressure P _m in the condensation chamber 4.

As shown in FIG. 2, the jet ejector body 3 has a supersonic primary diffuser 9 in a subsonic diffuser 9 for effectively converting kinetic energy of a fluid into pressure energy and a low-pressure chamber 11 having a suction port 10. An injection nozzle 12 as a nozzle faces coaxially with the opening direction of the subsonic diffuser 9, and flows from the suction port 10 through the high-pressure evaporation supply port 13 having the vapor pressure P ₁ to the low-pressure evaporation chamber. the low-pressure steam having a vapor pressure P ₀ of 5 is for suction.

That is, the high-pressure steam generated from the high-pressure steam generator chamber 2 enters the supply port 13 of the jet ejector body 3 and
The high-pressure steam is ejected from the ejection nozzle 12 formed therein toward the mixing section 14, and the high-pressure steam has a steam pressure P ₀ of the low-pressure steam at the suction port 10.
At the exit of the injection nozzle 12 and at a high speed.

The injected high-pressure steam (steam pressure P ₁ ) and the low-pressure steam sucked from the suction port 10 from the low-pressure evaporation chamber 5 cause an impact at the mixing point M shown in FIG. And is sucked and continuously rushed to the mixing section 14.

Then, mixing takes place in the diffuser 9 when velocity energy is converted to high pressure potential energy.

As shown in FIG. 4, a Mollier diagram (pressure-enthalpy curve diagram) which is a thermodynamic cycle of the jet ejector body 3 firstly shows the adiabatic expansion process of the injected steam in the injection nozzle 12 of A → B and C The enthalpy reduction process along the isentropic curve together with the adiabatic expansion process of the suction gas from the suction port 10 of D, the enthalpy reduction of D → M, and B →
The mixing process (irreversible process) at the mixing point M with the enthalpy increase of M and the adiabatic compression process (enthalpy increase) in the diffuser 9 of M → E are represented.

Reference numeral 15 denotes an insulating coating electrode which is disposed at a position of about 20 to 30 mm on the surface of the refrigerant liquid W and forms a DC or AC high piezoelectric field of about 15 KV which produces the Asakawa effect. As a result, the surface tension and the viscosity of the refrigerant liquid W decrease (the Asakawa effect), and the evaporation of the refrigerant liquid W is promoted.

That is, as shown in FIG.
It is only necessary to use a 15A tip metal electrode 15B coated with polypropylene 15C or the like.

For example, when water is used as the refrigerant liquid, the evaporation rate reaches several tens of times at a temperature of 12 ° C.

On the other hand, the entire jet ejector refrigeration system 1 at this time is grounded.

A condensing heat exchanger 16 for condensing and liquefying the steam injected from the jet ejector body 3 is provided in the condensing chamber 4.
As a heat pipe type heat exchanger. The vapor pressure of the gas intermediate pressure in this condensation chamber 4 is P _m. That is, P ₁ >
P _m > P ₀ . A refrigerant Q is sealed in the condenser heat exchanger 16 and liquefaction and vaporization are repeated.

16A is a boiling section, which is disposed in the condensation chamber 4;
Is disposed in the atmosphere and sends air from the blower 17 to cool the refrigerant Q vapor and liquefy it into the refrigerant Q liquid.

Thus, the steam injected from the jet ejector main body 3 is sent out into the condensing chamber 4, where the steam is liquefied by the above-mentioned condensing heat exchanger 16.

Reference numeral 19 denotes an orifice as a restrictor, which communicates with the low-pressure evaporation chamber 5 via a conduit 18 connected to the conduit 7. Thus,
The differential pressure between the vapor pressure P ₀ of the condensing chamber vapor pressure P _m and the low pressure evaporator chamber 5 in the 4 refrigerant liquid W applied to the orifice 19 is fed in a state of being partially vaporized into the low pressure evaporation chamber 5. Reference numeral 20 denotes a heat pipe type heat exchanger in which a refrigerant Q is filled as a cooler, and
20A faces the refrigerant liquid W in the low-pressure evaporation chamber 5, and the heat absorbing section 20B
Is disposed in the cooled room V. 21 is a blower. Thus, in the heat absorbing portion 20B of the air cooler 20, the refrigerant Q liquid absorbs heat and is vaporized, and the cooled room V is cooled by the vaporization heat at that time.

On the other hand, the vaporized refrigerant Q vapor dissipates heat in the radiating section 20A and is liquefied. At this time, the refrigerant liquid W in the low-pressure evaporation chamber 5 is heated and vaporized.

Similarly, in the low-pressure evaporation chamber 5, the insulating coating electrode 15 for generating a high piezoelectric field of about 15 KV of direct current or alternating current of about 15 KV which generates the Asakawa effect as in the high-pressure steam generator chamber 2 is formed on the surface of the refrigerant liquid W by about 20 cm.
Multiple pieces are arranged at the position of ~ 30mm.

Specifically when employing water as the refrigerant liquid W, the pressure in each chamber is _{P 0 6mmHg (3 ℃ ~5 ℃} ), P 1 ≧ 56mmHg (45 ℃
5050 ° C.), P _m 32 mmHg (30 ° C. or higher).

 The water saturation curve (boiling curve) is as shown in FIG.

(Operation) The above technical means operate as follows.

First, while operating the air blowers (17, 21) of the condensing heat exchanger 16 and the air cooler 20, respectively, applying a high electric field of about 15 Kv to the insulating coating electrode 15 for the Asakawa effect, and applying a low heat input (for example, Hot water obtained from solar thermal energy) or water as the refrigerant liquid W in the high-pressure steam generator chamber 2 is boiled down to about 45 ° C. to 50 ° C. by the electric heater 6 or the like to increase the pressure. (Steam pressure P ₁ ) Next, the high-pressure steam having the steam pressure P ₁ is sent out to the supply port 13 of the jet ejector main body 3 at a speed of about 200 per second.

At that time, since the refrigerant liquid W in the low-pressure evaporation chamber 5 is applied with a high electric field of 15 Kv, the evaporating action is promoted to several tens of times the normal temperature, and the heat from the radiating portion 20A of the air cooler 20 is reduced to the refrigerant liquid W. It begins to evaporate violently to be radiated inside. However, the maximum refrigerant temperature in the low-pressure evaporation chamber 5 is about 30 ° C., which is lower than the vapor pressure P ₁ in the high-pressure steam generator chamber 2. Therefore, the refrigerant W vapor in the low-pressure evaporation chamber 5 is sucked by the jet ejector main body 3, and the evaporation operation can be continued.

Further, for this reason, the temperature of the refrigerant Q liquid in the heat pipe of the heat absorbing portion 20B of the air cooler 20 located on the side of the cooled room V rises because it takes away the evaporation heat from the frozen article, and evaporates (the latent heat of evaporation is reduced). The temperature of the cooled room V is cooled down to near the evaporation temperature of the refrigerant Q, and the vaporized refrigerant Q in the heat pipe is released by the heat radiating portion 20 of the heat pipe of the air cooler 20 in the low-pressure evaporation chamber 5.
The temperature of the refrigerant liquid W immersed around A is raised very quickly, and the refrigerant Q is liquefied again.

Thus, the heat in the cooled chamber V is absorbed by the refrigerant liquid W in the low-pressure evaporation chamber 5.

Next, the injection nozzle 12 of the jet ejector body 3
The steam discharged from the high-pressure steam generator chamber 2 and the low-pressure steam drawn and sucked by the low-pressure evaporation chamber 5 are mixed and sent from the jet ejector main body 3 to the condensation chamber 4.

The sent vapor is absorbed by the refrigerant Q in the boiling portion 16A in the heat exchanger 16 for condensation, is liquefied and liquefied as the refrigerant liquid W, and is stored at the bottom in the condensation chamber 4. or,
The refrigerant liquid W in the condensing chamber 4 is sent into the high-pressure steam generator chamber 2 through the conduit 7 at the inner bottom under control of the ball tap 8A of the float valve 8 while being sent into the low-pressure evaporation chamber 5 respectively. As the air is fed through the orifice 19 as the expansion device, the above-described thermodynamic cycle is repeated, and the cooling and cooling operation is continued.

In addition, the high electric field of the insulating coating electrode 15 causes the surface tension and the viscosity of the water as the coolant liquid W to decrease (the Asakawa effect), and the evaporation of the water is promoted, so that the heat transfer is extremely efficient. Therefore, the thermal energy required to dissociate chemical adsorption (intermolecular bonding), which has been a problem in adsorption refrigerators using an adsorbent, is essentially unnecessary,
The efficiency of use of heat energy is extremely high, and the coefficient of performance COP of the refrigerator becomes approximately 1.1 or more if the contribution by the high electric field is included.

This is an increase of more than about 50%, considering that the COP of the adsorption refrigerator is about 0.7. Furthermore, in the present invention, the cooling state can be continuously maintained, the refrigerator configuration is extremely simple compared to conventional adsorption refrigerators, and switching of piping systems is not necessary, so that general adsorption is not required. The volume of the main body can be reduced to about 1/3 of that of the refrigerator.

In the following embodiments, the same parts as those of the present invention are denoted by the same reference numerals.

(Embodiment 1) As shown in Fig. 6, the feature of this embodiment is that a jet ejector type refrigeration system 1 in which the whole is grounded E is provided in a high-pressure steam generator room 2, a low-pressure evaporation room 5, and a condensation room 4, respectively. The jet ejector main body 3 is provided upright on the upper part of the high-pressure steam generator chamber 2 toward the condensing chamber 4 while the conduit 7 having the float valve 8 and the conduit having the orifice 19 are provided. 18 and the overflow portions protruding into the condensing chamber 4, respectively, are formed in the shape of an inverted U-shaped tube 22 so as to face the front insulating coating electrode 15, while the exchange electric field 15KV
In order to apply AC, a neon transformer 23 of 100 VAC, 50-60 Hz is employed. Thus, the operation and effect based on the specific configuration are substantially the same as those of the present invention.

(Embodiment 2) As shown in Fig. 7, the feature of this embodiment lies in that the structure of an oil diffusion pump used as a vacuum device is adopted as the device of the present invention, and a jet system 24 having orifices 24A at various places is provided. Supersonic steam jet through the water cooling pipe 25
In the cycle in which the water is cooled and condensed and solidified on the inner wall of the pump vessel and returned to the high-pressure steam generator chamber 2,
The jet ejector main body 3 guides the refrigerant vapor in the low-pressure evaporation chamber 5 on the suction port side 10 into the condensation chamber 4 on the discharge port side, and the refrigerant vapor W on the surface of the refrigerant liquid W in the high-pressure steam generator chamber 2. Has an insulating coating electrode 15 for generating the Asakawa effect.

At that time, the refrigerant liquid W injected by the jet system 24
Since the direction of is determined, there is no worry about backflow. Thus, the operation and effect based on the specific configuration are substantially the same as those of the present invention.

(Embodiment 3) As shown in Fig. 8, the feature of the present embodiment lies in that the structure of the Hickman pump which is a vacuum apparatus utilizing the concept of fractionation is adopted as the apparatus of the present invention. That is, refrigerant vapor such as oil ejected from the first, second, and third injection nozzles (12A, 12B, 12c) is condensed and liquefied in the diffuser 9, and the second boiler 26B, the third boiler 26C, The evaporated fractions of the four boilers 26D are all returned to the first boiler 26A through the return pipe 27. One end 28A of the steam return pipe 28 is the high pressure steam generator chamber 2 side, the high vacuum side pipe 29 side is the low pressure evaporation chamber 5 side, and the low vacuum side pipe
The 30 side corresponds to the condensation chamber 4 side.

Further, an insulating coating electrode 15 for guiding the Asakawa effect is provided on the liquid level in each of the boilers (26A, 26B, 26C, 26D).

Thus, the operation and effect based on the specific configuration are substantially the same as those of the present invention.

(Effects) Thus, the present invention has the following specific effects. In particular, based on the jet ejector type refrigeration apparatus according to the present invention,
Cooling can be continuously performed using low heat input, which can achieve the excellent effects of simplified equipment and greatly improved efficiency compared to conventional adsorption refrigerators, and can reduce equipment costs. No pollution occurs.

[Brief description of the drawings]

1 to 5 show the apparatus of the present invention, FIG. 1 is a principle view of the method of the present invention, FIG. 2 is a sectional view for explaining the principle of the jet ejector body, and FIG. FIG. 4 is a Mollier diagram of the jet ejector body, in which the vertical axis represents pressure and the horizontal axis represents enthalpy. FIG. 5 is a state diagram showing a saturation curve of water, in which the vertical axis represents pressure and the horizontal axis represents temperature. FIG. 6 shows the first embodiment. FIG. 7 shows a second embodiment. FIG. 8 shows a third embodiment.

Claims (3)

(57) [Claims] 1. A high-pressure steam generator chamber 2 filled with a predetermined amount of refrigerant liquid W, a jet ejector main body 3 for receiving high-pressure steam from the high-pressure steam generator chamber 2, and a low-pressure steam generated by the suction force of the jet ejector main body 3. A low-pressure evaporating chamber 5 into which steam is sucked, a condensing chamber 4 for receiving medium-pressure mixed vapor ejected from the jet ejector body 3, and a low-pressure chamber for receiving the refrigerant liquid W liquefied in the condensing chamber 4. The cooling chamber 20 includes an evaporating chamber 5, a high-pressure steam generator chamber 2, and a cooler 20 disposed in the low-pressure evaporating chamber 5. The cooling chamber V is cooled by timing vaporization or liquefaction of the refrigerant liquid W.
A jet ejector type refrigeration system in which an insulating coating electrode 15 for generating a high electric field for promoting evaporation is disposed on the surface of the refrigerant liquid W in the high-pressure steam generator chamber 2 and the low-pressure evaporation chamber 5. 2. The jet ejector type refrigeration system according to claim 1, wherein said jet ejector body 3 is replaced with an oil diffusion pump structure. 3. A jet ejector type refrigeration system according to claim 1, wherein said jet ejector body 3 is replaced with a structure of a Hickman pump.