JPS60200058A - Heat intensifier - 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 novel heat treatment system that can obtain a large amount of amplified heat from the condenser of the refrigeration cycle by interposing a vortex tube between the compressor and the condenser of the refrigeration cycle. Regarding an amplification device.

Generally, in a refrigeration cycle such as a heat pump, the amount of heat released in the condenser is determined by the amount of heat taken in by the evaporator and the amount of work done by the compressor, and it is not possible to obtain an amount of heat greater than the sum of the amount of heat taken in and the amount of work done by the compressor.

An object of the present invention is to provide a heat amplifying device that can obtain a heat amount greater than the sum of the heat taken in from the heat source and the work of the compressor without expending additional work from the outside in a refrigeration cycle.

Generally, in a refrigeration cycle, the refrigerant in the system becomes high-pressure superheated vapor on the discharge side of the compressor and is sent to the condenser.

On the other hand, a vortex tube is known as a device that supplies high-pressure gas to generate a vortex inside and obtains high-temperature gas by the fluid friction heat of the vortex.

The present inventor focused on the above two points and discovered that heat can be dramatically amplified by further increasing the temperature of the compressed evaporation of the refrigerant in the refrigeration cycle using the characteristics of the vortex tube, and has made the present invention. .

Embodiments of the present invention will be described below based on the drawings.

FIG. 1 shows a flowchart system of a heat amplifying device according to the present invention, and a refrigerant such as Freon 22 is sealed in the system 1.

A feature of the present invention is that a vortex tube device 7 with a low-temperature gas outlet sealed is interposed between the compressor 3 and the first condenser 4 of the refrigeration cycle.

That is, the low temperature gas outlet side 7C of the vortex tube device 7 is connected to the lid member 12.
The vortex tube device 7 formed in this manner is sealed with
The discharge side pipe la of the compressor 3 of the refrigeration cycle is connected to the high pressure gas supply lower a of the refrigeration cycle, and the high temperature side pipe 1b of the condenser 4 of the refrigeration cycle is connected to the high temperature gas output lower b of the vortex tube device 7. It is what it is.

3 and 4 show a more preferable vortex tube device for use in the heat amplifying device of the present invention, and the vortex tube device 7 includes:
A high-temperature gas having a diameter smaller than the cylindrical inner diameter of the case 8 flows through an opening at one end in the axial direction of the hollow case 8, which has a cylindrical hollow part in the inner axial direction and is equipped with a compressed gas supply lower a communicating with the cylindrical interior. A circular vortex generating device 10 is fitted into the cylindrical hollow portion of the case 8 with the pipe 9 connected thereto, and has a through hole 10a extending through the axial center.

The vortex generator 10 has a recess 10b at the center of the end facing the high-temperature gas flow pipe 9, and a plurality of circular curved edges 10c formed around the recess 10b extend in a radially inclined or curved manner. A groove 10d is cut in the case 8, and the groove 10d is arranged in the case 8 so as to face the gas flow pipe 9, and the upper end of the groove 10d communicates with the gas supply lower a of the case 8.

Then, a lid member 12 is screwed and sealed from the back side of the vortex generator 10 via an O-ring 11, and its tip is brought into contact with the opposite side of the vortex generator 10 to fix the vortex generator 10. .

In this way, the compressed gas supplied from the gas inlet into the case 8 at high speed is rapidly rotated by the vortex generation control 10 and turned into a vortex, a special temperature change is generated, and high temperature gas is discharged from the high temperature flow pipe 10. .

In addition, in the vortex tube device 7 shown in the figure, a gap 13 is provided between the tip of the vortex generator 10 installed in the case 8 and the inner end of the hollow case 8 in which the high-temperature gas flow tube 9 is connected.
The tapered surface of the case inner circumferential surface 14 facing this gap 13 is preferably formed at a uniform angle such that its angle is 90°.

A brake member 15 made of a wire formed in a spiral shape may be interposed in the high-temperature gas flow pipe 9.

Make it into a bent shape.

In addition, a plurality of discharge holes 16 may be formed in the peripheral wall at the tip of the high temperature flow pipe 9, and a heat dissipation member 18 having a cap 17 screwed onto the end may be coupled to the end. A high-temperature gas discharge adjustment screw 19 is attached to the inside of the high-temperature gas so that it can be moved back and forth in a self-cleaning manner, and the flow rate can also be adjusted by operating the screw 19.

It is desirable that the gas supply lower a of the case 8 be provided at a position slightly offset from the axis.

The vortex tube device 7 shown in FIGS. 3 and 4 is a vortex tube device with far superior performance compared to conventional ones due to the above-mentioned features.
Although a patent application has been filed under No. 181, the vortex tube device used in the present invention is not limited to the one shown in the figure, and the low temperature gas outlet of a known vortex tube is covered with a lid member 12.
Of course, it is possible to use a sealed one.

In either case, the compressor 3 and the vortex tube device 7 are
A relative relationship is maintained such that the function of the vortex tube device 7° is not impaired and a vortex flow having a flow velocity necessary for generating high and low temperatures is generated.

Fig. 1 shows an example in which one vortex tube device 7 is used for the compressor 3, but as mentioned above, the function of the compressor 3 is not impaired, and each vortex tube device 7 is required to generate high-temperature gas. For example, a plurality of vortex tube devices 7 can be used in parallel with the compressor 3 as shown in FIG. 2, provided that a compressed refrigerant flame is supplied.

In this case, the discharge capacity Q1 of the compressor 3 and the total supply capacity NQ2 of the plurality of vortex tube devices 7-7'n are set so as to maintain the relationship Ql>Q2.

In order to increase the fluid friction in the vortex tube device 7 and make its characteristics efficient < fib, a relatively small device is desirable, so in order to obtain an effective heat amplification device, the Therefore, it is more preferable to use a plurality of small-sized vortex tube devices 7.

In addition, when a plurality of vortex tube devices 7 are set in parallel in this way, the high temperature gas outlet lower b of each vortex tube device 7 may be directly connected to the shared condenser 4 via a pipe, but preferably. As shown in FIG. 2, each vortex tube device 7 is provided with an individual condenser 4, and the high temperature gas output lower b of each vortex tube device 7 is connected to the corresponding individual condenser 4 via a pipe. The outlet pipe of the condenser 4 is further connected to another common condenser 4', and the heat exchange medium such as water that has undergone the primary heat exchange in the common condenser 4' is further transferred to the individual condensers 4'. A heat exchange medium circuit is provided so that the heat exchange medium is sequentially circulated through the condenser 4 for heat exchange.

Since the refrigerant on the outlet side of each condenser 4 still retains residual heat, this configuration allows the generated heat to be extracted without wasting it, and the second condenser 4'
The heat exchange medium heated in advance is sent to the high-temperature condenser 4 placed immediately after each swirl tube device 7, so the heat-exchanged endothermic medium becomes higher in temperature, improving heat exchange efficiency. There is.

Next, the operation of the present invention will be explained.

The refrigerant in the refrigeration cycle system 1 takes in heat from a heat source such as water W in the evaporator 2, evaporates, and is sucked into the compressor 3.

The superheated vapor of the refrigerant compressed in the compression ta3 becomes a high-speed vortex in the process of passing from the supply lower a of the vortex tube device 7 through the groove 10d of the vortex generator 1°, and due to the temperature change characteristics of the vortex tube device 7, the vortex Superheated vapor of the refrigerant is discharged from the output lower b of the device 7.

Since the high-pressure refrigerant vapor supplied to the vortex tube device 7 is compressed by the compressor 3 of the refrigeration cycle, from the viewpoint of the entire refrigeration cycle, the refrigerant vapor is discharged from the high temperature side lower b of the vortex tube device 7. The increased temperature of the steam is increased heat without expending additional work.

In this way, the high-pressure refrigerant superheated vapor that has been thermally amplified by the vortex tube device 7 enters the condenser 4 from the outlet of the high-temperature flow tube 9, radiates heat through heat exchange with water W, etc., and then is depressurized by the expansion valve 6. It is then circulated to the evaporator 2 again.

As described above, in the present invention, the superheated vapor of the refrigerant that has been compressed and heated in the compressor 3 is further heated in the vortex tube device 7 and then condensed, so the amount of heat obtained in the condenser 4 by repeating the above cycle is This will be significantly increased.

Test Example Hereinafter, a test example of a refrigeration cycle using the heat amplification device of the present invention will be explained.

(1) Type of heat pump refrigerant Freon 22 Refrigerant situation Compressor piston displacement capacity - 46 i/hr Refrigerant circulation amount G = 301 kg/hr (volume efficiency = 0.85) Compressor rated output = 1.5 kw/hr Using 12 vortex tube devices, arranged in parallel as shown in the example in Fig. 2 Heat source part Heat release part where water at 16°C was supplied to the evaporator at a flow rate of 151/min and heat exchanged Water at 16°C (2) The pressure and temperature of the refrigerant in each state in the heat pump system during operation of the device were as follows.
μ%4. The 16°C water (15j/min) has become 6°C cooling water, and the 16°C water supplied to the condenser has become 6°C cooling water. The water (307!/min) at 74°C was discharged as hot water at 74°C.

Therefore, the amount of heat released from the condenser is (74-16)'C x 301 x 60 minutes = 104,400 Kcal/hour The amount of heat absorbed from the heat source is (16-6)'C x 15 J x 60 minutes = 9,000 Kcal/hour Its work What is the amount of heat? ,5KWX860Kcal/hour-
Since the output of the compressor used is 7.5KW, and the amount of heat absorbed from the outside air of the heat pump is 5.0OOKcal/hour, this is the result empirically measured in the refrigeration cycle of this test example. The coefficient is 1 4400- 9000+5000 7.5 (KW) x 860 (Kcal/hour) 904
00 14.0 450.

(3) When the changes in the refrigerant in each state in the table above are expressed on a Mollier diagram, it is as shown in Figure 5. (Since the pressure in the table is gauge pressure, 1 atmosphere is added to the Mollier diagram. ing).

If we add the enthalpy at each state change from this figure, we get AA+B---11K cal/
kgC-p-------13K cal
/ kg, however, since 12 vortex tube devices are used, the enthalpy between C and D is 8X12=96Kcal/kg as a whole.C~E---60 Kcal/k
g Therefore, the coefficient of performance calculated from the change in the state of the refrigerant is 8x12
+60 = 156 514.111 11, which almost matches the energy balance based on the empirical calculation.

In the above test example, it was demonstrated that 90,400 Kcal of heat could be obtained from the heat utilization side per hour, but as is clear from Figure 5, the enthalpy of each of A-B and B-E is about 11
and 61, the coefficient of performance of the conventional heat pump according to the same standard is #5.5 1, and the amount of heat obtained is (7.5KW x 860Kcal/hour) x 5.55g3
It remains at 5.475 Kcal/hour.

Therefore, the difference in the amount of heat of approximately 55,000 Kcal/hour is obtained by the amplification effect of the device of the present invention without expending any additional energy. A large amount of heat, which far exceeds the sum of the heat obtained by the work of heat and pressure [11], can be amplified and obtained without expending any additional work.

It is for use.

[Brief explanation of drawings]

FIG. 1 is a flowchart of a heat amplifying device according to the present invention, FIG. 2 is a flowchart of main parts of another embodiment, and FIGS. 3 and 4 are preferred embodiments of a vortex tube device used in the present invention. FIG. 3 is an explanatory diagram of its assembly, and FIG. 4 is a longitudinal cross-sectional view. FIG. 5 is an operational explanatory diagram showing a test example of the device of the present invention on a Mollier diagram. 2・・−・−−−1−−−Evaporator 3−・−・−・−
Compressor 4----------Condenser 5------
Liquid receiver 6・・−・−・−・・・Expansion valve 7−・−・
- Vortex tube device 8 --- Vortex generator 13
········Gap 14······Tapered inner circumferential surface 15····Brake member patent applicant Janchik Co., Ltd. Agent Patent attorney Nao Sato Handwriting 1 Figure 2

Claims (2)

[Claims] (1) Connect the low temperature gas outlet side 7C of the vortex tube device 7 to the lid member 12.
The discharge side vibrator 1a of the compressor 3 in the refrigeration cycle is connected to the high pressure gas supply lower a of the vortex tube device 7, and the high temperature side pipe 1 of the condenser 4 of the refrigeration cycle is connected.
b is connected to the high temperature gas ratio lower b of the vortex tube device 7. (2) The heat amplification device according to claim 1, characterized in that a plurality of vortex tube devices 7 are interposed in parallel between the compressor 3 and the condenser 4 of the refrigeration cycle system 1.