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THERMAL DEVICES, DEVICES FOR HEATING LIQUID MEDIA AND THEIR APPLICATION
INVENTION
Patent of the Russian Federation RU2143651

METHOD AND DEVICE FOR TRANSFORMATION OF THERMAL ENERGY

The name of the inventor: Samkhan II; Zolotarev G.V.
The name of the patent holder: Samhan Igor Isaakovich
Address for correspondence: 150014, Yaroslavl, B.Oktyabrskaya Str., 73, ap. 87, Samkhan II
Date of commencement of the patent: 1997.07.01

In the method for transforming the heat energy of the heat supply systems, the working medium is vaporized with the input of heat from the low-temperature coolant, compressed, condensed, heated by the heat carrier of the heat supply system, and throttled. In this case, part of the total heat carrier flow of the heat supply system before heating in the condenser is heated by the working body during its compression. In the device implementing this method, the compressor (or its individual stages) is equipped with heat exchange surfaces connected to the condenser's communications for the input of the heating medium of the heat supply system. Communications contain valves for distributing heat carrier flows between the condenser and the heat exchanger surfaces of the compressor. The use of the invention will significantly increase the energy efficiency of conversion of thermal energy.

DESCRIPTION OF THE INVENTION

The invention relates to heat power engineering, in particular, to the processes of converting low-temperature thermal energy into thermal energy of elevated temperature level and cold.

A method for transforming thermal energy using compression-resorption heat pumps is known. In this method, carried out at variable temperatures of desorption (evaporation) and absorption (condensation) of water-ammonia mixtures, it is possible to achieve values ​​of thermal-transformation coefficients exceeding the theoretical values ​​of the Carnot cycle. However, the achieved indicators of thermal transformation are still relatively low due to imperfection of the process and equipment.

A steam-compression thermal transfer method is known, which is closest to the invention in terms of its technical nature.

This method includes a reverse (heat pump, refrigerating) thermodynamic cycle in which the working medium (refrigerant) is vaporized with the input of heat from the low-temperature coolant (TNT), the formed vapors are compressed with the external work supply, cooled and condensed with a high-temperature (TWT) Subsequent throttling or expansion in an expander.

The disadvantage of the method is the relatively low energy efficiency of the process, which is much smaller than the theoretically possible in the Carnot cycle.

The object of the invention is to provide a method for converting thermal energy, which provides a significant increase in energy efficiency.

This goal is achieved by the fact that in a known method of transforming thermal energy, including a cyclic sequence of processes in which the working fluid (refrigerant) is vaporized with the input of heat from the low-temperature coolant (THT), is compressed with external work input, cooled with a heat carrier of high temperature (TBT) And throttled, the refrigerant is additionally cooled while it is being compressed by a high-temperature coolant (TBT).

Another difference of the proposed method is that from 30 to 80% of the TWT is heated during the compression of the refrigerant (and the heating of its remaining part and is carried out by the coolant, but after the completion of the process of compressing the refrigerant).

Another difference of the proposed method is that the reverse flow of refrigerant before throttling or expansion is cooled by a flow of TNT, which is then used to vaporize the refrigerant.

In addition, the differences are:

  • Use of TNT for the initial cooling of the refrigerant during its compression;
  • Regenerative heating of the direct refrigerant flow after evaporation by the return flow of the refrigerant entering the throttling;
  • Use as a coolant of a mixture of substances with different boiling points.

In the device for carrying out the proposed method (heat pump), which includes a circulation circuit with refrigerant lines installed in series, connected to the TNT feed communications, a compressor, a coolant (condenser) of the coolant connected to the TVT feeder and throttle or expander, the compressor (or its individual stages ) Is equipped with (provided) heat exchange surfaces connected to the communications for the supply of TVT and TNT.

Another difference of the device is that the circulation circuit in front of the throttle (along the refrigerant flow) contains a heat exchanger with communications for TNT delivery.

A further difference is that the circuit further comprises a regenerative heat exchanger cooling the reflux of the refrigerant before the throttle and heating the direct refrigerant flow in front of the compressor.

The difference is that the communications for the supply of TVT contain valves for the distribution of the flow values ​​between the cooler (condenser) and the heat exchange surfaces.

The proposed method, compared with similar ones, provides a significant increase in efficiency compared with the theoretical limits of the Carnot cycle.

In particular, cooling of the refrigerant during its compression by a part of TNT and TWT allows, in comparison with the known method:

  • Conduct heating of various parts of TWT at variable temperatures with minimal thermodynamic losses;
  • Avoid overheating of the refrigerant during compression, typical for the traditional method;
  • Reduce the cost of mechanical energy to compress the refrigerant.

Another fundamental difference is the cooling of the return flow of refrigerant before throttling of TNT.

It allows you to:

  • Reduce losses from throttling to a negligible value;
  • Use the energy previously lost when throttling energy in the process of evaporation;
  • Increase the temperature range of thermal transformation with reduced energy costs.

The effects arising in the proposed method lead to an increase in the coefficient of thermal transformation = Q / W, determined by the ratio of the transferred heat Q to the expended work W, by 1.2 - 1.25 times with respect to Carnot cycle even in a relatively narrow temperature range of the thermal transformation from 0 to 70 o C.

The essence of the method is explained by the following figures:

FIG. 1 (a, b) are the diagrams of the existing (a) and proposed (b) methods in the coordinates absolute temperature (T) - entropy (S)

FIG. 2 (a, b) are diagrams of the existing (a) and proposed (b) methods in the coordinates pressure (p) and enthalpy (h)

METHOD AND DEVICE FOR TRANSFORMATION OF THERMAL ENERGY

FIG. 3 is a schematic diagram of an apparatus for implementing a method using a screw compressor

In Fig. 1 and 2 show the operation of changing the state of the refrigerant (see table at the end of the description).

In one embodiment of the inventive method shown in FIG. 1 (b) and 2 (b), operations of the cycle can be implemented instead of operations 7 - 1 and 1 - 2.

7 - 2 '- adiabatic compression of the refrigerant and

2'-2 - compression of the refrigerant in the region of dry steam with cooling of TWT.

The device of FIG. 3 includes a circulating circuit 1 comprising an evaporator 2 with communications for supplying the TNT 3, a compressor 4 with a drive 5, heat exchange surfaces 6, an additional heat exchange means 7 and a feed communication channel TBT 9 and a TNT 3, a cooler (condenser) 8 connected to the TBT feed communications 9 with a control valve 10, a regenerative heat exchanger 11, a heat exchanger 12 with communications for feeding TNT 3 and a throttle (throttle valve) 13.

To implement the method, existing refrigerants such as R12, R22, R717 (ammonia), R502, R13 and others can be used. In the case of refrigerants with a low critical temperature, for example R13, it is possible to realize a method when compressing the refrigerant to pressures above critical.

The method can be implemented as follows.

Example 1
The liquid working medium (refrigerant R12) is evaporated in evaporator 2 at a temperature of 0 ° C., the resulting vapors are heated to 30 ° C. with a regenerative backflow of the refrigerant. The superheated flow of dry refrigerant vapor is compressed in the compressor almost isothermally with simultaneous cooling of the compressor by a part of the TNT, then the refrigerant compression continues in the wet vapor region with cooling of the refrigerant by a part of the TWT. The intensity of the applied cooling of the compressor is determined by the high degree of condensation of the refrigerant, reaching 50-100%.

The refrigerant flow leaving the compressor is further cooled in the cooler (condenser) by another part of the TWT to a temperature of about 33 ° C in the regenerative heat exchanger and throttled. The heating temperature of the TWT is about 65-67 ° C.

Coefficient of thermal transformation In this case is given by

= (Q to + Q ox ) / W k ,

Where Q k , Q ох - respectively, the heat given by TVT in the compressor and cooler; W to is the work consumed by the compressor.

For the example in question = 6.06, the value K for an ideal Carnot cycle in the temperature range 0-70 ° C is

K = T in / (T in -TH) = 343 / (343-273) = 4.9

(T в , T н - the largest and lowest temperature of the cycle).

Similar patterns are also characteristic of other working bodies. In particular, for the conditions of the example given, the thermal transfer coefficient When using R22 refrigerant is 5.85, and for R717 (ammonia) it is 6.26.

Example 2
The R12B1 refrigerant after evaporation at 0 ° C. is compressed adiabatically to a temperature of 30 ° C. The refrigerant is then compressed polytropically with TWT cooling first in the region of dry steam and then of wet steam.

During the compression process, the refrigerant is heated to 70 ° C and condensed by 50-90%. The released thermal energy is transferred to one of the TBT streams, which in turn heats up with an increase in temperature from about 30 to 66-68 ° C.

The refrigerant after the compressor at a temperature of about 70 ° C is then cooled to about 30 ° C by another part of the TWT, which in turn is heated to 66-68 ° C.

The refrigerant stream is further cooled to about 5-10 ° C by a flow of TNT, throttled to 0 ° C. and evaporated. Evaporation of the refrigerant is carried out by a stream of preheated TNT.

The calculated coefficient of thermal transformation in this process is = 6.12.

Taking into account that the practical coefficient of thermal transformation is usually less than the theoretical coefficient by 25-35%, it can make up values ​​that are significantly higher than those already achieved in vapor compression systems.

The proposed method and device can be realized not only with screw compressors, but also with other types of compressors, for example, multi-stage piston or centrifugal. In this case, cooling of the refrigerant in the process of compression by the heat carriers TBT and TNT can be carried out both at individual compression stages and in the intervals between them.

In addition, for intermediate heat transfer media, for example, oil having thermal contact with TBT and TNT, heat exchange may be used in the process of compressing the refrigerant. These intermediate heat transfer fluids can be injected into the compressor.

Thus, the proposed method and device are novel, useful and can be implemented.

CLAIM

1. A method for transforming the heat energy of a heat supply system, comprising a cyclic sequence of processes in which the working fluid is vaporized with the input of heat from the low-temperature heat transfer medium, compressed with the supply of external work, condensed, heating the heat carrier of the heat supply system, and throttled, characterized in that before heating in the process Condensation of the working fluid part of the total heat carrier flow of the heat supply system is heated by the working body during its compression.

2. A method according to claim 1, characterized in that during the compression of the working fluid, from 30 to 70% of the total amount of the heat carrier of the heat supply system is heated.

3. The method according to claims 1 and 2, characterized in that the low-temperature heat carrier is heated by the return flow of the working fluid entering the throttling (or expansion).

4. A method according to claims 1 to 3, characterized in that the cooling of the working fluid during compression is initially carried out by a low-temperature coolant.

5. Method according to claims 1 and 2, characterized in that the working body after heating is regenerated regeneratively by the flow of the working fluid entering the throttling.

6. Method according to claims 1-5, characterized in that mixtures of substances with different boiling points are used as the working fluid.

7. A device for transforming the heat energy of a heat supply system, comprising a circulating circuit including a sequentially installed evaporator with low-temperature coolant supply communications, a compressor, a condenser having communications for the input and output of the heat transfer medium of the heat supply system, and a thermostatic valve, characterized in that the compressor Its stages) is equipped with (provided) heat exchange surfaces connected to the communications of the condenser for the input of the heating medium of the heat supply system, and these communications contain valves for distributing heat carrier flows between the condenser and the heat-exchange surfaces of the compressor.

8. The device according to claim 7, characterized in that, before the heat exchange surfaces (along the working medium), the compressor comprises an additional heat exchange means communicating with the low-temperature coolant.

9. The device according to claims 7 and 8, characterized in that the circulation circuit is provided with a heat exchanger in front of the thermostatic valve with communications communicating with the low-temperature coolant.

10. Apparatus according to claim 7, characterized in that the circulation circuit further comprises a regenerative heat exchanger cooling the working medium before the thermostatic valve and heating it in front of the compressor.

print version
Date of publication 30.12.2006гг