BG63668B1 - System for piston engine compression and ejection - Google Patents

Abstract

The system is used in transport, the power industry and in every field of engineering when engines are used. It enables the formation of a steam-air thermodynamic cycle by increasing the thermal efficiency to 80-85%. The steam is used only for offsetting the losses of energy in the reversibility of the cycle at mass discharge of about 20 to 30% and not in the full operating volume of the engine as is the case in the steam engine and the steam turbine. The system consists of a steam generator (G), ejector (E), piston engine (PE), steam-and-air turbine (T) ,air compressor (AC),heat exchanger (HE), condenser (C), piston pump for the condensate (PP), moisture separation tank (ST) and control valves (V). 4 claims, 3 figures

Description

(54) PISTON ENGINE COMPRESSION AND EJECTION SYSTEM

Technical field

The invention relates to a system for compressing and ejecting piston engines with a field of application in transport, energy and any field of technology where engines are used.

BACKGROUND OF THE INVENTION

In thermodynamics, it is known that the most perfect cycle of a steam power plant is the Carnot cycle, performed at set temperatures, with the highest thermal efficiency of the possible thermodynamic cycles, but in the steam power plants the modified cycle proposed by Rankin has been applied.

Steam and gas combinations of combustion gases and water vapor in gas turbine plants are also known, but the thermal efficiency cannot be greater than the efficiency of each of the component cycles. In some cases, following the model of a binary mercury-water plant, the steam-gas cycle contains a gas turbine stage in the high temperature region and a steam turbine in the low temperature region. In this case, the thermal efficiency is greater than each of the constituent cycles (gas and steam), therefore larger than the two individually, but this complicates significantly the power plant.

RU 2054563 C1 discloses a steam-gas engine comprising a direct-current steam generator whose output is coupled to the active nozzle of a mixing chamber, wherein the guiding apparatus is mounted at the outlet of a Laval nozzle, the inlet of which is aligned with the active nozzle located in the mixing nozzle. a chamber where steam is mixed with the exhaust gases and which drive the blades of the centrifugal turbine, which are firmly coupled to a heat-conducting disk, etc.

EP 0619417 A1 discloses a regenerative gas turbine cycle in which the gas turbine in the kit includes a compressed air compressor, a combustion chamber for combustion, a combustion-driven turbine and a drive compressor. Air is supplied to the steam mixer and steam and air are mixed. A heat exchanger is installed after the turbine to heat the mixed gas from the mixer with the heat from the exhaust gases. The air line supplies one compressed air from the compressor to the combustion chamber and another to the compressed air from the mixer. Mixed gas from the mixer is fed into the combustion chamber through the heat exchanger. The mixer may include either a steam turbocharger or an ejector.

WO 94/10427 also discloses a water-steam engine that uses a working fluid consisting of a mixture of compressed non-combustible air components, combustion products and steam. In the described new cycle, the working fluid is supplied with constant temperature and pressure. Compressed air is supplied adiabatically by a single or multi-stage compressor. At least 40% of the supply air is combusted. Inert components are injected at high pressure and steam is produced, thereby cooling the turbine or other type of system internally.

The main disadvantage of the patents described above is that the use of air is done by passing through the combustion chamber of the engines and the circuit lacks a condenser, which almost does not increase the thermal efficiency, and that the gas turbine engines do not work effectively at low rpm and low operating pressures fluid.

Other disadvantages of steam power plants are known: large steam boiler, large condensing units due to high enthalpy of exhaust steam, low thermal efficiency, high weight and volumes due to unavoidable steam lines, which necessitated them exclusively for use in coal fired power plants. For these reasons, their use in transport is limited.

SUMMARY OF THE INVENTION

It is an object of the invention to provide a piston engine compression and ejection system that performs a steam-air thermodynamic cycle as opposed to previously used steam, gas and steam-gas thermodynamic cycles.

The problem is solved by interconnecting a steam generator (PG), an ejector (E), a piston engine (SG), an air turbine (T), an air compressor (K), a heat exchanger (TO), a condenser (CN), a piston pump for condensate (BP), water tank (RH) and control and regulating devices (CR), all together representing the piston engine compression and ejection system.

The operation of the piston engine in the pv diagram (Fig. 1) involves the following processes: the high pressure steam enters the steam generator at pressure p ₁ (item 1) and flows from the nozzle of the ejector at high speed, expanding into the diffuser to pressure p ₂ , entraining and compressed air with pressure p ₆ to pressure p ₂ in the piston engine cylinders. From (2) to (3), the air mixture is isobarically expanded in the engine, performing work to overcome the external resistances. At the end of the piston stroke (ppm), an outlet is opened, whereby the vapor mixture with pressure p ₃ (item 3) is expanded adiabatically into the turbocharger impeller to atmospheric pressure (p ₄ ) (t 4). From (4) to (5) the air mixture passes through a condenser cooled by the suction air from the compressor. The condenser cools the exhaust steam until it condenses, and the air leaves the condenser at a temperature of up to 70 + 80 ° C. The compressed heated air from (p. 5) to (p. 6) is mixed in the mixing chamber of the ejector with the inlet steam and increases its pressure to p ₂ (p. 2) in front of the piston engine cylinders.

The diagram shows that the closure of the 2 - 3 - 4 - 5 - 2 loop is impossible in the 6-2 compressor adiabat due to the loss of energy in the turbocharger. This requires that the compression pressure be increased in order to use the compressed air energy to operate the piston engine. The steam jet ejector is used for this purpose, which is essentially a jet compressor and has the simplest device.

The described path of operation of a piston engine with a compression and ejection system shows a very complete use of the steam enthalpy in a cascading manner, namely the 1-2-3-4 pathway consisting of two adiabats and one isobar. The use of a mixed steam cycle allows the abrupt use of steam in the engine in its first volume, which significantly increases the thermal efficiency of the engine, minimizes the size of the steam generator and the condenser and increases its mobility.

The advantage of a compression and ejection system is that it uses instead of exhaust gas the air from the atmosphere, which cools the condenser and returns to the engine the heat released by the condensation of steam and the cooling of the air from the vapor mixture. This contributes to a sharp increase in the reversibility ratio of the cycle and hence to an increase in thermal efficiency, given that steam is only used to compensate for energy losses in the reversibility of the cycle, (mass flow rate of about 20- 30%) , and not in the full engine capacity, as in the steam engine and steam turbine. This allows 80 + 85% thermal efficiency to be achieved, which would reduce fuel costs by 2 to 3 times the current operating values.

Despite the low values of the operating pressure and temperature, the power of the compression and ejection engines is comparable to that of the corresponding gasoline and diesel engine due to the fact that the working pressure is equivalent to the effective pressure p _is of the internal combustion engines and the work process is two-stroke. It also avoids engine cooling and the need for mechanical transmission to transmit torque to the wheels. Other important advantages are the high durability of compression and ejection engines, as well as quiet operation.

Description of the attached figures

An exemplary embodiment of the invention is shown in the accompanying drawings, of which:

Figure 1 represents the thermodynamic process of compressing and ejecting piston engines in a p-v diagram;

Figure 2 is a schematic representation of the compression and ejection system;

Figure 3 is a detailed view of the compression and ejection system;

FIG. 3 to 3f are the corresponding sections and views of FIG. 3.

Examples of carrying out the invention

The invention is explained in more detail with reference to FIG. 3.

According to the invention, the compression and ejection system consists of: a condenser 22 on the core of which air guide caps 31 are mounted, the rear ones are fixed and the front ones are mounted via bimetallic coil springs 29, lever 30 and spring 28 (see view C). A heat exchange coil 23 is attached at the top of the condenser, and a condensate tank 25 is mounted in the bottom, in which a float 26 and a needle valve 27 are mounted and connected to a tube with a reservoir 3 into which a condensing coil 2 is formed. at the outlet of which is adjustable valve 7. The steam generator 14 is connected to the high-pressure part of the ejector 12, the outlet of which is connected to the suction port of the piston engine 24, whose outlet is connected to the air turbine 5. On the condenser 22 are mounted wounds the air compressor 4 and the air turbine 5, representing in one turbocharger and connected through openings with the condenser 22, that of the compressor is closed by a valve 1 connected to the air directing covers 31. The compressor 4 is connected through the heat exchanger 6 to the low pressure diffuser 10 of the ejector 12, which low-pressure diffuser is pressed by the tare spring 8 and is enclosed by the sealing ring 9, which houses the profile low-pressure rollers 17 having on their cylindrical surface, semi-cylindrical channels with prom 18. Smaller sized high-pressure rollers 16 are mounted in the high-pressure diffuser 11, which accommodates the piston pins 15, with the diffuser lying pressed by a spring 13. On the axis of the crankshaft of the piston motor 24 is fitted with an eccentric washer 35 which contacts the piston pump for condensate 32, mounted on a carrier 21, which is mounted on the axis 20. The condensate pump 32 is connected to a drive mechanism 33 which is engaged to a screw with a right thread 40 mounted in right-hand nut 39 and which is connected to a screw with a left thread 44, inserted into a nut with a left thread 42, through a connecting sleeve 41. Nuts 39 and 42 are mounted simultaneously in a slot of the body of the regulator 43 and in two sloping slots in the triangular plates 45, which are connected to the pressure regulator 34 via the steam generator tube 14 and the four-blade mechanism 19, which is mounted with the four-blade ejector 36, the weight 37 and the wedge support 38. The inlet of the piston pump 32 is engaged with the condensate tank 25 and the outlet is connected in series with heat exchange the coil 23, the heat exchanger 6 and the steam generator 14.

To demonstrate the advantages of the present invention, the theoretical cycle of a piston engine with compression and ejection is described below.

The thermodynamic cycle (Fig. 1) consists of the following processes: 1 - 2 - adiabatic expansion of steam in the ejector; 2 - 3 - isobaric expansion of the air mixture in a piston engine; 3 - 4 - adiabatic expansion of the steam mixture in the turbine; 4 - 5 - isobaric condensation of steam; 5 - 6 - adiabatic compressor air.

If we follow the processes according to the p-v diagram (Fig. 1), it can be seen that the piston engine operates with one steam, one air and three mixed air cycles. The thermodynamic processes occurring in a piston engine with a compression and ejection system are described below.

The performance of the piston engine is equal to the sum of the work of the compressor and the ejector ^L ..- ^{L. +} kV, <m, -tr + sx, - σ, -τ ",>, j / s where cp ⁿ is the specific heat of steam at constant pressure, cf ^c is the specific heat of air at constant pressure or L _c = p ₂ V _s , J / s, where V _s is the second engine volume equal to the sum of the partial volumes of steam and air in the vapor mixture

V = V + V »or

S S 5 'η V, V ---, m>

where - liter volume of the engine w ³ , and η - engine revolutions per minute.

The power of the engine can be divided by the formula:

^L »Ν _β = ------, kW

1000

The energy conservation law serves as the basis for drawing up the energy balance. For an open thermodynamic system it states: the sum of the incoming energy flows is equal to the sum of the outgoing ones.

EW = EW

The relationship between technical (deformation) and absolute performance in the piston engine can be written

1 = 1 ,, or 1 + 1. = 1, J / kg d b 'e to b' °

Then by multiplying the left side of the equation with the mass flow, respectively, of steam and air, y, _n and m _in is obtained:

^t „L ^{+ t} D = C.>

H ⁺ H ⁼ H · 'J / s

In order to determine the two unknown - .masoviyat steam engine t _n and the mass flow of air m _in, must be drawn and a second equation, namely the ratio of the adiabatic work in the turbocharger, where is the relationship between the m _n and m _in and is replaced by equation (1) ^m . k = V ^m . 1 / ^{+ m} n k) (2>

or L. = η. L k 'tk t

In the circular process of the piston engine with compression and ejection, it can be seen that the heat input into the engine comes from the heat introduced by the steam into the ejector and the heat introduced by the compressor for 5 air, using the heat from the exhaust air mixture.

Or if you sign up for the heat input, you get:

q _n = l - 1 ', J / kg Q _n ^{= m} nO "- ^f) ' ^{J / s} where i is the enthalpy of dry saturated steam, ί 'is the enthalpy of the injected water in the steam generator.

The heat returned to the engine produces:

q = s (T, - T), J / kg Q = m s * (T, - T,), J / s * - 0 p o atm '

2θ The thermal efficiency is used to evaluate the thermal cycle (tr

Q-Q.

Q ²⁵ where Q is the amount of heat input equal to Q _n is the heat input by steam from the steam generator, Q _o is the amount of heat extracted from the engine equal to: Q _n (L _e + L _k ), ie. the difference between the heat input and the work done in the ejector plus the work from the compressor.

Substituted in the thermal efficiency formula, it is obtained:

Q „- {Q _B - (4 ⁺ 4)} W ⁺ W η = ---------------------- = --------- - =

Q Q

If we analyze the formula for the thermal efficiency of the piston engine with compression and ejection, it will be seen that the efficiency increases with increasing the efficiency of the turbocharger and with decreasing evaporation heat r = i ”- f, which in turn depends from the nature of the working body (water, alcohol, ammonia, freq »m s; (T, -T _d ) ₊ m c / ^ - T ^) m _B (i” -V) it, etc.), and by the degree of preheating of the working fluid for injection into the steam generator.

In this case, a new cycle reversibility factor can be introduced, ie. of the ratio of heat returned from the compressor and condenser in the engine to the steam input.

I, W. ώ. ^ ΓΓ, -Τ ^ ώ, ^ ίΤ, -Τ ^.) Ώ, ν (Τ, -Τ _Μ )

Q 'I. m (i' -i ')

Comparing the efficiency and the thermodynamic parameters of the engine with the compression and ejection system compared to the gasoline and diesel engines, it can be seen that η ₍ is at least twice that of the internal combustion engines, the maximum cylinder pressure is 5 -NX lower, maximum temperature is also 10-15x lower, and speeds are 4 + 16x lower, respectively, than in gasoline and diesel engines.

Use of the invention

The compression and ejection system works as follows:

The drive mechanism 33, actuated by the accelerator pedal 24, rotates the right-hand screw 40 and through the connecting sleeve 41 and the left-hand screw 44, which, when rotated in the respective nuts 39 and 42, approximates the brackets 21 to which they are secured. condensate piston pumps 32 and through the eccentric washer 35, the condensate is sucked in from the condensate tank 25 and pressurized through the heat exchanger 23 and the heat exchanger 6 into the steam generator 14. The steam generated by the steam generator enters high pressure. the ejector space 12, where it acts on the piston pins 15, forcing them under pressure to the low pressure diffuser 10, thus creating a gap δ (see B-B) through which the low pressure air flow from the air compressor 4 passes. The movement of the piston pins 15 is strictly determined depending on the tare spring 8. In the movement of the piston pins 15, the high pressure rollers 16 are rotated through the grooved part, which by changing the cross section of the opening formed during their rotation provides high vapor flow rate from the diffuser 11 into the diffuser 10. Similarly, the fluted pins 18 act on the wall of the ejector 12 in the movement of the diffuser 10 to rotate the low pressure rollers 17, which at any time depending on the the engine load is ensured automatically by the optimum performance of the ejector. The air-mixture thus obtained, with precisely defined parameters of pressure, temperature and volume, is supplied throughout the entire stroke of the engine 24, providing it with a power exactly corresponding to the external resistances.

During the exhaust stroke of the piston, the exhaust port connected to the tube with the air turbine 5 is opened, which drives the compressor 4. The exhaust air mixture passes through the condenser 22, where the water vapor condenses and collects into the condensate tank 25, float 26 and needle valve 27 are maintained at a constant level. The moist air from the condenser passes through the condensation coil 2 into the reservoir - moisture separator 3, where additional moisture from the air condenses. The air thus dried leaves the system or enters the steam generator 14 through the adjustable valve 7.

The air in the compression and ejection system is sucked in by the air compressor 4 through the air guide caps 31, which are automatically actuated by a spiral bimetallic spring 29 heated by the air mixture inside the condenser 22, lever 30 and spring 28. When moving, the moving air valves are started. 31 are in the lower position (see view C). In this situation, the cooling air enters only one cooling sector in the condenser 22. When the upper spiral bimetallic spring 29 is heated, it bends and moves the lever 30 upwards as the spring 28 locks the lid tightly against the wall of the radiator. In this situation, the cooling air enters through the three cooling sections of the condenser 22. And the last position is when the second bimetallic spring 29 is heated to the predetermined temperature and the second air guide 31 is moved upwards. The cooling air then passes through all five cooling sections of the condenser 22 (see section AA). The faucet 1 serves to switch the compressor 4 to suction in addition to air from the atmosphere, as well as a vapor mixture of the condenser into a specific mode of operation of the engine, as in a fully encapsulated compression and ejection system using the engine in vacuum.

The four-stage mechanism 19 and the pressure regulator 34 serve to limit the speed and pressure in the piston engine. They act separately and together, depending on the mode of operation of the engine. For example, at low speeds and high loads, only the pressure regulator acts, and at high speeds both work together. Both are connected to the triangular plates 45, which have two sloping slots into which the guide nuts 39 and 42 enter. As the pressure in the steam generator 14 increases above the set point, it acts through the tube of the pressure regulator 34 and pushes the plate 45 up. thus separating the nuts 39 and 42 moving in the slot of the body of the regulator 43, they in turn push the screws 40 and 44 clamped to the supports 21. This reduces the stroke of the condensate piston pumps 32 and reduces the amount of water injected into the pas 14. As the speed increases above the permissible centrifugal force created by the weights 37 acts on the wedge supports 38, they in turn displace the four-link mechanism 36, thereby pulling the four-link mechanism 19 upwards by the plate 45 and thereby separating the nuts 39 and 42, and thus the piston pumps 32 of the eccentric washer 35, thereby reducing the amount of condensate injected.

Claims (4)

Claims 1. A piston engine compression and ejection system comprising a steam generator (14), an ejector (12), a piston engine (24), an air turbine (5), an air compressor (4), a heat exchanger (6), a condenser (22), condensate piston pump (32), moisture separator tank (3) and control valves (1 and 7), characterized in that the steam generator (14) is connected to the high-pressure portion of the ejector (12), the output of which is connected to the inlet port of the piston engine (24), the outlet port of which is connected to the air turbine (5) that is mounted of one shaft with the compressor (4), both of which are arranged together on the condenser (22), with the outlet of the turbine (5) connected to the inside of the condenser (22) and the inlet of the compressor (4) connected to the air guides ( 31) and the inside of the condenser (22) through a tap (1), wherein the lower end of the condenser (22) is connected to a tube for a water separator (3) into which a condensing coil (2), 5, is mounted at the outlet of which has a control valve (7) mounted and the compressor outlet (4) is connected in series with the heat exchanger (6) and with a low pressure s part of the ejector (12), the inlet of the piston pump (32) is connected to the tank 10 for the condensate (25) and the output is connected in series with the heat exchange coil (23), the heat exchanger (6) and the steam generator (14). 2. Compression and ejection system- 15 not on reciprocating motors according to claim 1, characterized in that the ejector (12) is composed of a low-pressure diffuser (10) with profile low-pressure rollers (17) connected to the grooved pins (18) 20 and pressed by tare spring (8) and enclosed by a sealing ring (9) and by a high-pressure diffuser (11) with high-pressure profile rollers (16) connected thereto by piston pins (15), which is pressed 25 by a spring (13). 3. A piston engine compression and ejection system according to claim 1, characterized in that air guides are mounted on the condenser (22) 30 covers (31), rear fixed, and front ones connected to bimetallic coil springs (29), lever (30) and spring (28), in the upper part a heat exchange coil (23) is made and the lower part is shaped as 35 a condensate tank (25) in which a float (26) and a needle valve (27) are mounted. Compression and ejection system for piston engines according to claim 1, characterized in that 40. The eccentric washer (35) is mounted on the piston engine lynch shaft (24), in which the condensate piston pump (32) is mounted, mounted on a carrier (21), mounted on a shaft (20) and connected to a drive mechanism (33). ), 45 which is engaged to a right-hand screw (40) mounted in a right-hand nut (39) and which is connected to a left-hand screw (44) mounted in a left-hand nut (42) by a connecting sleeve (42). 41), with nuts (39) and (42) being placed 50 in the slot of the regulator body (43) and in two sloping slots of the triangular plates (45) that are connected to the pressure regulator not (34), in turn, by means of a steam generator tube (14) and by means of triangular tiles (45) with a four-link mechanism (19), which is mounted in conjunction with a four-stage push-out mechanism (36), a weight (37) and presses wedge supports (38). Attachment: 3 figures 4 (7 water