CS233051B1 - Rotary gas machine for pumping heat - Google Patents

Abstract

The invention solves the problem of pumping heat from one thermal level to another. It concerns a rotary machine of wing or multi-piston type, creating a variable channel of changing circulating chambers in the range of two Sinusoidal cycles and connected to three exchangers - high-temperature, medium-temperature and low-temperature, operating roughly in the Carnot cycle. The machine creates a six-cycle thermal cycle of a figure-of-eight pattern and pumps heat from a low to a medium thermal level due to the heat input at a high thermal level. The invention can be used in a heating or cooling system in conjunction with a heat source such as gas, oil, solar technology, etc.

Description

Rotary gas machine for heat pump

The invention solves heat pumping from one heat level to another. It relates to a rotary machine of the wing or multi-piston, generating a variable channel of changing orbiting chambers over two cycles of Synusoid and connected to three exchangers of high-temperature, medium-temperature and low-temperature, operating roughly in the Carnot cycle. The machine creates an eight-cycle heat cycle of the octal curve and draws heat from low to medium heat level due to heat input at high heat level.

The invention can be used in a heating or cooling system in conjunction with a heat source such as gas, diesel, solar technology and the like.

(52) Int. Cl? F 02 B 53/02

-1233 OSI

The invention relates to the transfer of heat effected by a thermodynamic gas cycle in a rotary-wing or multi-piston gas machine operating roughly according to the Carnot cycle.

Known solutions in the field of thermodynamic heating or cooling are mainly based on the use of a cooling compressor, throttling and cooling or heating in exchangers working with pairs of refrigerants driven by an electric motor. Despite the high heat efficiency of the heat pump, the total heating factor is only slightly above the level of direct heating due to energy conversion losses and the common potential for low-potential energy generation. Furthermore, the gas working is known, where expansion work is also used and the difference between expansion and compression work is added. Systems in which the heat pump is driven by an explosive engine also show good results in this respect, the waste heat from the engine being used for reheating the heating circuit. Positive ignition, mixed and mixed engines do not operate with the best thermal efficiency and are not yet suitable as a direct part of the heating system in terms of noise, overall investment and operational demands. The Erikson-Brayton thermal cycle, which works between two isobars and two adiabatams, was previously used for hot-air machines and now for gas turbines of equal pressure. This solution is used in combination of turbine - rotary compressor with coolant circulation for similar purpose of heat pump. The circulation itself and the use of refrigerants for higher drive circuit temperatures is limited by the low heat resistance of the refrigerants. The two-circuit solution is a benefit in this respect, but the combination of two media complicates regulation, operation and the product itself. The thermal cycle, which is very close to the Carnot cycle, and which would be most suitable for a dual-circuit heating device, can be carried out using a wing machine. U.S. Patent & 3169375 and further the NSR pat

U.S. Pat. No. 2,61832 discloses rotary rotary motors where an attempt is made to perform an i-thermic portion of the circulation, thereby achieving a high carnotization, but the solution is directed in particular to use in an automotive engine. Even here, however, the exchange is not isothermically perfect and is closer to the igobaric change. Ss, AO no

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Thermal machine with circulation

233 051 gas according to the Carnot cycle * 'solves in detail the ixothermic change of the ideal gas in the wing or multi-piston rotary machine, which can be suitable for the design of the machine for heating ·

The drawbacks mentioned in the above-described devices and the positive properties such as quiet operation, high heating factor of the whole device, relative simplicity are solved by the invention, which is based on the realization of the six-cycle thermal gas circulation, e.g. compressed air in a wing or multi-piston rotary machine. The principle of the rotary machine according to the invention is that the variable channel is formed by continuously changing and advancing closed chambers, in the range of two sinusoid cycles, ie in the range of 720 °. . The high temperature and other heat exchanger are connected between 0 ° to about 60 ° in the direction of rotation, the medium temperature between 180 ° to 360 ° and the low temperature between about 420 ° to 540 °. The sections 60 ° to 180 °, 360 ° to 420 ° and 540 ° to 720 ° are insulated. The device is provided with an eccentric bearing of the rotating piston in the rotary bearings of the bearings for the possibility of changing the compression ratios of the sinusoidal channel.

By carrying out the six-cycle cycle according to the invention in the layout of the sections so that it exceeds the energy-clockwise - motor part of the thermal circulation over the left-handed section - thermo-pumping by total losses, a heat pump can be obtained without exhausting the drive shaft. The engine is driven by the combustion heat and then by the heat pump itself, whereby the waste heat from the engine and the heat obtained by the heat pump from the low heat level are removed by one exchanger to the medium temperature storage tank. Serial connection of both circuits facilitates regulation of the whole system, by changing the ratio of right to left-hand power it is possible to find the most suitable heating efficiency under different circulation conditions. With sufficient medium temperature heat, the lower power level can be increased above the upper power level, including losses, thus changing the function of the engine and heat pump. This makes it possible to pump heat into the high temperature storage tank and store heat at low volume and high temperature.

233 051

The accompanying drawings show the main ideas of the overall arrangement of the machine according to the invention. Figures 1 and 2 show the completed octal cycles of a heat machine for pumping heat in a pressure p-V and entropy T * s diagram. The mechanical arrangement of the putée machine of the invention is shown in Fig. 3 as an elliptical, winged single cylinder embodiment. The twin-cylindrical, rotary solution is shown in Fig. 4, where only a variable, chamber-divided channel is shown, but which can be implemented as a multi-wing or multi-piston design. Control of changes in the compression ratios of the driving and driven parts for radial arrangement is shown in Fig. 5 *

The thermal machine itself is a roughly elliptical single cylinder with a centrally located rotary piston) which carries the sealing wings and thus forms a roughly sinusoidal variable channel of closed chambers twice in one turn. A similar course of the channel can be realized by two simple rotary cylinders with eccentrically mounted rotary pistons carrying the wings, where the two cylinders are interconnected at the point of minimum volume, before and at the top dead center, and are synchronously coupled to each other. Generally a possible solution of the basic circulation is any formation of a channel of sinusoidal changing chambers of rotationally driven, for example radially or axially oriented piston cylinders, carried in a rotating rim, or axially sliding wings guided by a driving rim between sinusoidal ground faces in the rotating annulus and

chambers carried around standing heat exchangers. The iXothermic exchangers themselves are connected to the circulating chambers by means of inflated orifices, if the gas is supplied to the rotating part of the chambers, or are simply connected when the gas is supplied to a stationary face or circumferential rim. When orienting the position during two sinusoid cycles, the position will be indicated by an angle from the minimum stroke point, ie from 0 ° to 720 °. These two sinusoidal variable channel cycles are divided into 6 sections in terms of heat supply and dissipation, i.e. in terms of connection of thermothermal exchangers; the section between points 1 and 2 located between 0 ° and

60 °, section between point 2 and point J positioned at 180 °, section between point J and point 2 located at 360 °, section between point 4 and point 2 located at about 420 °, section between point 2 and a point 6 positioned at an angle of 540 ° and a section between points 6 and 1 that closes the two sine cycle. A section between points 1 and 2 is provided izothermickým high-temperature heat exchanger and executes a heated expansion, the section between points 2 and 2 on ^e zařxolovaný and performs an adiabatic expansion, the section between points 2 and £ is provided izothermickým středoteplotním exchanger and realizes compression cooling, the section between the points 4 ^{and the} section between points 6 and 6 is provided with an isothermal low temperature exchanger and provides a heated expansion, the section between points 6 and 1 is insulated and provides adiabatic compression. In operation, the right-hand drive part of the circulation alternates with the left-hand drive part of the closed octal circulation. Both heat supply and heat dissipation are assumed to be ixothermic. Exchangers are obtained whose branches heat or cool the transverse flow of the main circulation by exchange in individual chambers, utilizing the pressure drop generated between the chambers. However, the resistance of the branches must be such that no blowdown losses occur. The control can be solved on a continuously variable compression ratio and thus the power of the driving ff and the driven part of the circulation.

Giant. 1 and 2 show the idealized circulation in p-V and T-s diagrams. Its characteristic octal course has 6 cycles. Section between points 1 and 2 shows 32> othermic expansion section between points 2 - J is adiabatic (polythropic) expansion, section between points J - 4 is 12 pthermic compression, between points 4 · * £ is adiabatic (polythropic) expansion, section between points 6 and 6 is a low temperature and thermothermic heating; finally, the section between points 6 and 1 is adiabatic (polytropic) compression. Ixothermic changes are carried out in cooperation of adjacent exchangers, adiabatic sections are insulated. The area between points 0-1-2-3-0 characterizes the right-handed part of the engine, the area Ο-4-5-6-Ο the left-handed part of the heat pump, assuming that the first surface is greater by losses over the second surface. At the opposite ratio, heat can be pumped from medium to high temperature

233 051 exchanger and accumulator.

Fig. 3 shows an example of a rotary, roughly elliptical single-cylinder winged machine with segmentation of the perimeter.

Marking of points on the machine is consistent with marking in the diagrams.

At the minimum volume point 1, at an angle of 20 80 ° in the direction of rotation, point 2, then at the maximum volume of the first cycle of sinusoids, point 2 » ^at the minimum volume at transition to the second cycle of sinusoids 480 ° point 2 »in the place of max. volume of the second cycle of the sinusoid, i.e. at an angle of 540 ° with 6. between points 1 and 2 are each chamber discharge into the ends of the branches 2 high temperature heat exchanger 8. between points 2 ^and £ is again iaothermický středoteplotní exchanger Whose branches 2 are each introduced between two adjacent chambers 11 '. Between points 2 and 6 an isothermal low temperature exchanger 10 is connected according to the same principle.

FIG. 4 shows the same connection of the heat exchangers 8, 10pf of the same designation.

The heating of the section between points 1 and 2 is feasible by gas, oil heating or other high-temperature source (concentrated solar radiation, from accumulators, etc.). The section exchanger between points 21 ^and 18 is medium temperature cooling by the exchanger 6 into the storage tank. The section between two points ^{Λ έ} J ^e low-temperature heating, the change from the low temperature source (air, absorbers, collectors, waste water, ground heat) collects heat for free. " The principle of pumping from top to bottom or bottom to top is the size of the bottom and top of the circulation pattern. This is achieved by varying the compression ratios of the two parts of the octal circulation, which can be accomplished simply by eccentrically mounted the main shaft 12 in the housing 13 and by rotating the housing change the compression ratios of the pressure peaks - see Fig. 5.

SUBJECT V YN / L E Z ϋ

Claims (1)

Rotary heat pump for pumping heat created by wing rotary roughly elliptical single cylinder with multi-wing rotary piston, or two circular wing relative to each other 233 051 by interconnected single cylinders, or by two multi-piston machines axially or radially oriented and forming a rotating channel of variable chambers, in connection with heat exchangers, characterized in that the channel of rotating chambers (11) is continuous within two cycles, sinusoids, ie * within angles 0 ° to 720 °, is circumferentially divided into six sections, namely the section from the first point (1) at the point of minimum volume to the second point (2) located in the direction of rotation in angles of 20 80 °, the section from the second point (2) to a third point (3) positioned at 180 °, a section from the third point (3) to a fourth point (4) positioned at 360 °, a section from the fourth point (4) to a fifth point (5) located within an angle range 400 to 480 °, the section from the fifth point (5) to the sixth point (6) positioned at an angle of 540 ° and the section from the sixth point (6) to the first point (1), wherein the section from the first point (1) to the second point ( 2) is connected to the high-temperature isothermal heat exchanger (8), the section from the third point (3) to the fourth point (4) with the medium-temperature i-xothermal heat exchanger (9), the section from the fifth point (5) to the sixth point (6) isothermal exchanger (10), sections between the second and third points (2, 3), the fourth and fifth points (4, 5) and the sixth and first points (6, 1) are insulated and standing iltothermic exchangers (8, 9, 10) they are connected with their branches (?) in each case between two adjacent rotating chambers (11) and the shaft (12) of the rotary wing piston (14) is located eccentrically in the rotary bushing (13) to change the compression ratios. 3drafts 233 051