DE2111226A1 - Device for charging water-cooled rotary piston diesel engines - Google Patents

Description

"Device for charging water-cooled rotary piston diesel engines"

In the patent ....... (patent application P 1903.261.2 of

January 23, 196 9) a device for the compensated charging of a conventional diesel engine is proposed, that the possibilities of the increased overpressure of a turbo compressor with the effectiveness at lower Speed of a volumetric compressor, which the latter is connected in series with the turbo compressor by creating a variable speed ratio combined between the engine and the volumetric compressor.

Furthermore, it was proposed in the patent ....... (patent application P 2031,378.M- from June 25, 1970) with this charging system a gasification device (dispositif de fumigation), which to the

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10984

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classic injection an air / fuel premix at low speeds and low loads "

In French patent no. 69 / 41,129 of 11/28/1969 it has been proposed to variably control the volumetric compressor by an ordinary controller to replace, with the effects of the variable control being maintained by that Compressed air is branched off, so that the boost pressure changes depending on the speed and the load on the engine which branch air instead of being lost or being put into circulation again, then in an air funnel is used to cool the cooler.

Finally, in the first additional patent dated February 25, 1970 to the aforementioned patent described a perfecting of the device mentioned, according to which a Fine control of the branch air volume is done by a needle, which the passage cross-section of the * nozzle of the Air funnel based on the boost pressure changed »

It was mentioned that it is possible and particularly advantageous with the proposed arrangement that reduce the volumetric ratio of the motor, for example from 18/1 to 14/1. The main result of this Reduction of the volumetric ratio consists of moderate maximum pressures at a high to generate medium working pressure »

On the other hand, rotary motors or rotary engines are difficult to be used as diesel engines "as it is j ~ impossible to give them a high volumetriaches money, especially because of the considerable

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harmful space as a result of their kinematics, with a ratio of over 10/1, these rotary piston engines have large dimensions and a low degree of mechanical impact,

The object of the invention is to eliminate the aforementioned disadvantages and to use rotary piston engines with low volumetric ratio of for example 8/1 in this! working procedure use.

For this purpose, a turbo compressor is provided according to the invention, which is driven by the exhaust gases, furthermore an air / water heat exchanger and a volumetric one Compressors connected in series with the turbo compressor, which is volumetric compressor is driven at a .Speed which is proportional to that of the motor, and a part the charge air is diverted between the volumetric compressor and the engine to adjust the charge pressure accordingly the speed and the load on the engine.

For a two-stage compression, however, the aforementioned volumetric compressor must be up to ratios compress from '3/1 and even 471. It is not possible under these conditions as a volumetric compressor a well-deserved person with an external link between the To use the Roots type, which, since it has poor adiabatic compression, compression ratios of 2/1 without a major loss of efficiency. In the present case, as volumetric compressor a compressor with internal teeth, for example of the Planche type, which compress adiabatically and with good efficiency

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kungsgtad the desired compression ratios of Can deliver 3/1 to H / l.

This volumetric compressor with two rotors is preferably arranged so that one of the two rotors, the slower one is placed directly on the crankshaft of the rotary piston engine while the other rotor, for example, at twice or one and a half times the speed of the first Rotor rotates · The slow rotor driven by the crankshaft is used as one of the balancing organs of the The rotor of the motor is used, while the other balancing element is used by the one on the other side of the motor located flywheel is formed.

This compressor, which works up to a compression ratio of 4- / 1, can of course be a considerable one have harmful space.

In the device according to the invention are natural the devices available in the aforementioned patent applications are also provided: the pre-gasification device, the heat exchanger for the exhaust gases and the nozzle of variable cross-section of the funnel, wherein the variable cross-section of the nozzle is regulated by a pressure cell that controls the boost pressure the turbo compressor is exposed.

According to a first embodiment, the downstream of the volumetric compressor in an air funnel is used to direct the air that has passed through the engine's water cooler and in which funnel a nozzle opens which is arranged on the neck of a convergent-divergent channel of the air funnel

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According to a second embodiment, the branch air is in the outlet line of the turbine of the exhaust gas turbocharger blown in, which is supplied by the exhaust gases of the engine, which outlet pipe in turn opens into an air funnel which is arranged in the cooling air flow of the cooler.

In this second embodiment, a control device for the amount of branch air is also in the form a needle valve is provided, which is arranged in the branch line. This way there will be an improvement the efficiency of the device by reducing the back pressure in front of the exhaust gas turbine achieved and at the same time a better extraction of the charge air and an increase in the flow rate of the Air funnel and the cooling air of the engine radiator.

The branch air can be fed directly into the outlet line of the Turbine blown in or previously by passing through a heat exchanger in this outlet line be preheated. The branch air is fed into the outlet line either through a central injection nozzle or introduced through an annular injection nozzle,

The performance of this arrangement and of the entire engine can be improved if the compressor is used instead With gears of the Planche type, a rotary piston compressor with a circumferential arc of epicycloid-shaped profile is used, which is in a housing of the appropriate profile and with an additional circumferential bow drenen.

Such compressors allow a considerable and

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regular air pumping of very high pressures, there a harmful space is missing. They adapt perfectly to the mode of operation of rotary motors with trocnoid Runner profile, with which they are a happy combination for the operation of the same as diesel engines form.

This arrangement advantageously combines several factors to improve the efficiency.

- Increase in the flow rate and the pressure of the charge air;

- Reduction of the back pressure upstream of the turbine due to the cooling effect of the gases from the branch air and acceleration of the same by the funnel action of this branch air;

- Increase of the cooling air circulation of the cooler Increase in suction by supplying the turbine outlet flow;

- substantial dilution and cooling of this exit flow prior to its exit into the free atmosphere;

- Attenuation of the noise of the turbine at the outlet.

Further features and advantages of the invention emerge from the following description in conjunction with the accompanying drawings exemplary embodiments of the invention, namely show:

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1 shows an overall view of the device in schematic form Depiction;

2 shows a view of the rotary piston engine in section along the plane AA ¹ ;

3 shows a schematic overall view of the device with injection of the branch air through a central injection nozzle downstream of the turbine;

Fig. H is a schematic view in section of a volumetric Rotatxonskolbenkoinpressors with circumference sbogen *,

Fig. 5 shows another embodiment of the Einricrtung, at which the branch air into the exhaust pipe is blown through a suction funnel with an annular injection nozzle.

In Fig «, 1 a rotary piston diesel engine is shown, which has a housing 1, a rotor 2 and a crankshaft 3, the ends of which are marked on the right and left with 4 ^ and 5 are designated. The injection nozzle of the rotary piston engine is denoted by 6, the inlet by 7 and the Outlet with 8, a flywheel 9 with a counterweight 10 is attached to the right end 4 of the crankshaft 3 arranges. The left end 5 of the crankshaft carries a slow rotor 11 'of a volumetric compressor 11 »which slow runner is provided with a balancing mass 12. The second runner or fast runner is not shown in FIG. 1. The one at the inlet

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Connections of the compressor, a pipe 14 is connected to the centrifugal fan 15 of an exhaust gas turbocharger 16 here. The line IM- is passed through an air / water heat exchanger, which, depending on the operating condition, cools or heats the intake air from the engine's cooling water. One Exhaust line 8 feeds the exhaust gases to a turbine 18 of exhaust gas turbocharger 16. To the delivery opening 19 of the volumetric compressor 11 is connected to a single line 20 which passes through the inlet line 7 of the Rotary piston engine is extended. A branch line 21 is connected to this line, the excess Compressed air into an air / exhaust heat exchanger 22 and then via a line 37 to a nozzle 38. This nozzle opens at the neck 26 of an air funnel with a diverging section 27 and a converging section 28, the latter a Künler 29 of the motor by means of a suitable cover. The opening 40 of the nozzle has one depending on the position Needle 41 has a variable cross-section. This needle 41 is axially controlled by a rod 4 2 through a can 44 which is supported by a return spring 45 is loaded, while the interior of the can 44 is connected to the conveying side of the centrifugal fan 15 via a line 4b is connected and is therefore under the boost pressure.

It should be noted here, ciaio the compression ratio of, for example, 8/1 corresponds to an analog expansion ratio in the rotary piston diesel engine. The pressures the exhaust gases at the time the line 8 is released are higher than in a conventional one Piston diesel engine. In and of itself it would be desirable to extend this relaxation by volumetric means can. Indeed, it is known that it never

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lingt the relaxation by volumetric means below to lengthen a certain pressure «You are essentially at this pressure limit, So that the efficiency is good, it is sufficient that the turbine 18 is designed so that the exhaust gas pressures with the the best possible efficiency can be used.

The pre-gasification devices described in the aforementioned patents, those at the inlet of the volumetric compressor nozzle are of course also in the present one Case usable and is the confluence of the various arrangements at 2 3 in front of the inlet 13 of the volumetric Compressor provided.

The described system works as follows:

When the power is low, the line 14 is through the centrifugal fan 15 generated pressure weakly. By the volumetric compressor 11, however, this pressure in the inlet line 7 and in the branch line 21 increased significantly. The outlet from the branch line however, it is closed by the needle 41. The low pressure prevailing in line 46 is not sufficient from overcoming the force exerted by the spring 45 on the pressure cell 44, the rod 42 and the needle 41. All the charging that is achieved from the exhaust gas turbocharger 16 and the volumetric compressor 11 can therefore be reserved for motor 1, which needs it at the moment,

When the engine 1 is operating at high power, the AD gas turbocharger 16 delivers a high pressure into the line 14. The volumetric compressor 11 has the loading

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strive to increase this pressure, however, from a certain pressure downstream of the centrifugal fan 15 and thus in the pressure cell 4Λ the spring 45 gives way so that the needle m is raised, whereby the opening UO of the nozzle 38 is opened. The exhaust gas turbocharger 16 and the volumetric compressor therefore deliver simultaneously into the suction line 7 of the engine 1 and into the branch line 21, which branches off the more compressed air the higher the power of the engine.

The ratio of the by the volumetric compressor generated volume to the volume generated by the engine no longer determines its charge and can be proportional become very low. This is generally desirable and is made possible by the variable control achieved, which forms the subject of the aforementioned French patent 1,577,300.

It should be mentioned here that the combination of the air funnel and the heat exchanger 17 is a kind of automatic Represents regulation. Indeed, when the "air funnel does not work adequately, the temperature of the cooling water in the cooler 29 and in the heat exchanger 17 increases. The heat exchanger 17 divides therefore the intake air of the air funnel with more energy, so that the energy in the air funnel increases and the cooling is improved accordingly.

The air / exhaust gas heat exchanger 2 2 heats the intake air through the exhaust. This results in an increase in the suction energy at the nozzle 38,

In another embodiment of the invention, the diverted air into the exhaust pipe of the turbine

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blow.

In Fig. 3, a rotary piston diesel engine is shown, which has a housing 51, a rotor 5 2 and a crankshaft 5 has 3, the right and left ends of which are denoted by 54 and 55, respectively. The injection nozzle of the rotary piston engine is designated with 6 (see Fig. 2), the inlet with 57 and the outlet with 58. At the right end 54 of the crankshaft 5 3 is a flywheel 5 9 with its counterweight 60. The left end 55 of the crankshaft carries the rotor 61 'of a volumetric compressor 61, which is the slow rotor that with a balancing mass 6 2 is sunk. The inlet openings of the compressor are connected to a line 64, that of the centrifugal fan 65 of an exhaust gas turbocharger leads here. Line 64 is through an air / water heat exchanger 67 passed through which, depending on the operating state, the intake air from the cooling water of the engine off cools or heats up. An exhaust line 5 8 supplies the turbine 68 of the exhaust gas turbocharger 6 6 with the Exhaust. The delivery opening 6 9 of the volumetric compressor 61 is in communication with a single line 70 which passes through the inlet line 57 of the rotary piston engine is extended. A branch line 71 is connected to the line 70, the excess Compressed air into an air / exhaust gas heat exchanger 7 2 (Fig. 5) and then via a line 87 to a nozzle 83 of an air funnel 97, which is in the exhaust line 98 Downstream of the turbine 6 8 opens. This line in turn opens into the circular nozzle on the neck 76 an air funnel 99 between a diverging portion 77 and a converging portion 78, which the latter the radiator 79 of the engine by means of a suitable

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Neten shell surrounds.

The volumetric compressor 61 can, for example, be a rotary piston compressor 51 with a circumferential arc 5 2 from be epizykloxdenformigem profile, which is in a housing 5 3 of a corresponding profile with an additional Circumferential arc (Fig. 4) rotates.

The amount of intake air can be changed by the position of a needle 91. The shape of the needle 91 can be conical or be of a profile with a curved generatrix. The needle 91 is supported by a rod 9 2 actuated by a pressure cell 94 against the action of a return spring 95. The inside of the pressurized can 94 is connected to the delivery line via a line 95 of the centrifugal fan 65 in connection and is under the action of the boost pressure, (Fig. 3).

The 'mode of operation of the system described is as follows. At low power (FIG. 3), the pressure generated in line 64 by centrifugal fan 65 is low. By the volumetric compressor 61, however, this pressure is in there? Suction line 57 and in the branch line 71 significantly increased. The outlet from the branch line 71 is closed by the needle 91. The low pressure prevailing in the line 96 is not sufficient to overcome the force exerted by the spring 95 on the pressure cell 94, the rod 92 and the needle 91. All of the running air generated by the exhaust gas turbocharger 6 6 and the volumetric earner 61 is permanently reserved for use by the motor 51, which needs it at that moment.

When the Notor 51 is running at low power, (see also

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the embodiment according to FIG. 5), delivers the exhaust gas turbocharger 66 a high pressure in the line 64. The volumetric compressor 91 tends to to increase this pressure, but there is a certain pressure downstream of the centrifugal fan 65 and thus in the pressure cell 94- to the spring 95, so that the needle 91 executes a downward movement (Fig. 3) or shifts to the left (Fig. 5), whereby the opening 90 for access to the nozzle 83 is opened. The exhaust gas turbocharger 6 6 and the volumetric Compressors 61 therefore deliver simultaneously into the inlet line 57 of the motor 51 and into the Branch line 71, which branches off the more compressed air, the higher the power of the motor.

This air, after it has optionally been preheated in the heat exchanger 72 (FIG. 5), passes through the nozzle 83 is blown into an air funnel 97 in the line 9, in which they the flow there? Exhaust gases accelerated by the double action obtained by the thermal effect and the kinetic energy will. The flow accelerated in this way then enters the annular suction line of the second Air funnel 99, which is in the form of a circumferential ring of sufficient cross-section to avoid any counter pressure to produce, in which it causes the circulation of the cooling air of the cooler 79 as in the case of FIG. 3, but with a much larger amount in circulation.

It should be noted here that the combination of the air funnels and the heat exchanger 67 is an automatic one Represents regulation. Indeed, if the ventilator does not work adequately, the tempe-

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temperature of the cooling water in the cooler 7 9 and in the heat exchanger 6 7 to. The heat exchanger 67 therefore shares more energy the intake air of the air funnel, so that the energy in the air funnel increases and the cooling accordingly is improved.

The invention is of course not limited to the illustrated and described embodiments, but rather can experience various changes within its framework.

Patent claims :

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Patent claims

1J device for charging rotary piston diesel V- / engines with water cooling, characterized by an exhaust gas turbocharger, an air / water heat exchanger and a volumetric compressor connected in series with the exhaust gas turbocharger with the volumetric compressor being driven at a speed proportional to that of the motor is, and some of the charge air is diverted between the volumetric earner and the engine is used to change the boost pressure according to the speed and the load on the engine,

2. Device according to claim 1, characterized in that 4 ^e ^ volumetric compressor has internal teeth and is of the Jauart Planche.

3. Device according to claim 2, characterized in that that the slow runner of the volumetric compressor is arranged on the v-Jelle of the rotary piston engine and forms a balance weight for the rotary piston.

4. Device according to claims 1-3, characterized in that dai6 the branched compressed air in one

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Claims (1)

Air funnel is used to cool the cooler. 5. Device according to claim 4, characterized in that that the nozzle of the air funnel has an adjustable opening that is downstream of the pressure of the charge air of the exhaust gas turbocharger is controlled. B. Device according to claim 5, characterized in that the opening of the nozzle by means of a conical Needle or a needle is variable, the profile of which is formed by a curved generating line, which Needle can be moved by an actuating rod that is loaded by a spring and through a pressure cell can be operated, which is exposed to the boost pressure. 7. Device according to claims 1-6, characterized by the additional use of a pre-gasification device, which opens at the inlet of the volumetric compressor. Device according to claims 1-7, characterized through the additional use of an air / flue gas heat exchanger in the exhaust line of the exhaust gas turbocharger to heat the air funnel supplied Air. 1098-1 / 116Λ Device according to claim 1, characterized in that means for blowing the branch air into the Exhaust pipe of the turbine are provided. 10. Device according to claim 9, characterized in that the exhaust pipe of the turbine in an intake funnel flows out. 11, device according to claim 10, characterized in that that the cooler is arranged upstream of a converging part and a neck in which there is a second funnel, which supplies through the first funnel via the exhaust pipe with a diverging part following the mentioned neck in order to increase the cooling of the cooler to be able to. 12. Device according to claims 9-11, characterized in that that an adjustable opening is provided in the line leading to the first funnel, to be able to regulate the amount of branch air. 13. Device according to claim 10, characterized in that a needle with a conical or a profile a curved generatrix is provided, which needle through a rod against the action of a Return spring can be actuated by a pressure cell which is exposed to the boost pressure. 1098 4 1/116 ^. 2111228 14. Device according to claims 9-13, characterized in that an air / exhaust gas heat exchanger is provided in the exhaust line to heat the branch air for the first air funnel to ensure. 15. Device according to claims 9-14, characterized in that at least the injection organs of the mentioned second air funnel have the shape of an annular circumference. 16. Device according to claims 9-15, characterized in that the volumetric compressor is a rotary piston compressor whose circumferential arcs have an epicycloidal profile and which rotates in a housing of the appropriate profile, which has an additional circumferential arc having. 109841/1164