DE2129059A1 - Antnebsmotorsystem, especially with a rotary piston engine - Google Patents

Description

Dr. Ing.Jürgen Schmidt

Dr rer. net Bruno Raitzner

p., r,., r _Jn ,,,. ·, _f . 2129059

H Mi'mJien 2nd HSaS

June 11, 1971 P 4059-1

Patent application

for

Jadwiga Koltermann, 51 Kingston House South, Ennismore Gardens, London, UK

and λ

Oskar Michejda, 2420 Priseilla Lane, Fort Wayne, Indiana,

^V * ^St * ^{A #} concerning

Drive rotor system, in particular with a rotary piston engine

The invention relates to prime movers and, more particularly, to rotary piston engines.

Various prime movers or motors are known which use three rotating pistons and a central rotor that engages the body of each piston * More precisely, the pistons can be rotated within a Piston chamber arranged and provided with a projection for sealing engagement with the wall of the chamber. The middle one The rotor is provided with a recess and is connected to the piston via gears in such a way that the projection on the piston is received by the recess when the projections are in an alignment position with respect to rotate the recess. The piston protrusion and the engagement of the rotor with the piston body define an expanding one Chamber part and a decreasing chamber part within each piston chamber. These prime movers are characterized by various operational defects, both

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for example due to a lack of suitable preventive measures decompression inside the expanding chamber and compression inside the shrinking chamber Chamber, whereby considerable amounts of energy are wasted. Furthermore is the work part the rotation cycle of the piston is quite short in many cases, so that a relatively large prime mover for a given OutputlelBtt! :: y is required.

In addition, compressors and burners for supplying combustion by-product gases in connection with means for obtaining mechanical energy from the combustion by-product gases are known. For example, gas turbine prime movers fall into this category. However, these propulsion engines convert the kinetic energy of the combustion by-product "" gases into mechanical energy, resulting in low torque levels at low air flow speeds, that is, at low turbine speeds. Furthermore, gas turbine prime movers require !! complicated parts with very tight tolerances, which obviously results in high manufacturing costs. In summary, the known prime mover designs, due to various construction and duty cycle deficiencies, are unsuitable for providing a unit which has high thermal efficiency, high torque, high output at low rotational speeds and minimal size and weight, and it is also special no drive machine is known that is cheap, has a wide range of applications and has low pollutant emission values.

According to the invention, a rotary piston drive machine or created a rotary piston engine, the combustion secondary

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product oasis, and the pressure energy of the Incineration by-product gases into useful mechanical energy converts. The rotary piston prime mover is preferred in combination with an air compressor and a fuel burner to deliver the combustion by-product gases used. The prime mover is advantageously characterized in that it is a relative large torque on the output shaft over a wide range of engine rotational speeds including gives off relatively low rotational speeds and that they continue to have substantially complete combustion of the gas solution, so that low emission values from exhaust gas elements show "which cause air pollution".

According to the invention, a rotary piston drive unit is created which has as an additional feature a new type of rotating valve and a channel system that interacts with it. The rotating valve according to the invention and the channel arrangement are designed in such a way that compression of the decreasing volume in the rotary piston chamber and decompression of the increasing volume are prevented and that this advantageous effect is further achieved using an uncomplicated rotating valve part. Ä

The drive machine according to the invention uses parts «the to turn «instead of sloh to and fro and therefore are easy to balance dynamically. In addition, a reduction in fuel consumption is compared with the fuel consumption of common propulsion machines achieved with reciprocating pistons because it uses increased combustion times in a simple manner can be «to achieve a more complete combustion of the oasis

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mixture «which also means low pollution emission values results. As an added benefit, fuels without lead or other can increase the octane number Components are used because there is no fuel ignition system with high compression is used. These benefits come with a relatively simple performance mechanism with a minimal number of parts and accordingly with a less complex mechanism compared to the more complicated drive machines with reciprocating pistons and the extremely expensive gas turbines achieved.

The invention is explained in more detail below with reference to exemplary embodiments shown in the drawing.

In the drawing show:

1 shows a functional overview diagram of an exemplary embodiment of the drive machine system according to the invention;

Flg. 2 is a side cross-sectional view of an exemplary embodiment of a rotary piston drive machine; which are for use with the drive system according to Flg. 1 suitable and has a novel valve and inlet and outlet port arrangement;

3 shows a cross section through the end of the rotary piston drive machine according to Flg. 2 along the line 2-3 to illustrate the rotary lobes in their operating positions;

Flg. 4 shows a further cross section of one end of the rotary piston drive machine according to FIG. 2

♦ /.

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along the line 4-4 to illustrate the gear transmission of the prime mover;

Flg. 5 is another cross-section through one end of FIG Rotary piston drive machine according to Fig. 2 along the line 5-5 to explain the itself rotating valve of the prime mover;

Flg. 6 shows a further cross-section through one end of the rotary piston drive shaft according to FIG. 2 taken along line 6-6 to show the channels downstream of the rotating valve of FIG. 5j

FIG. 7 is a Bndansicht of the rotary piston prime mover according to FIG. 2 in the direction of FIG Arrows 7-7 seen to explain the inlet channel the prime mover;

Flg. 8 is another end view of the rotary piston prime mover according to Fig. 2 in the direction of arrows 8-8 to explain the exhaust channels and the Auslaßrauraes of the prime mover.

1 shows an illustration of an exemplary embodiment of a drive machine system 10 according to the invention System 10 includes a rotary piston prime mover 12 an output shaft for delivering mechanical energy to the driven wheels of a motor vehicle, for example and an accessory shaft for driving an air compressor generally designated 14. A burner also designated with 14 is compressed

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Aerated air is supplied from the compressor and fuel from a fuel pump 6 to produce elevated pressure combustion by-product oaee which are supplied to the rotary piston drive engine 12.

In Fig. 2 is a design of a rotary piston drive machine 12, which is suitable for use in the drive unit 10 according to FIG. The rotary piston engine 12 has a housing 18 on, which has an inlet opening 20 for the supply of combustion by-product gases from the burner and an exhaust or exhaust port 22 for exhausting spent gases from the Prime mover 12 includes. The rotary piston drive machine 12 also has a main output shaft 24 Rotation of the driven wheels of a vehicle or other power receiving device as well as a Auxiliary shaft 26 for actuating, for example, the compressor and the propellant pump of the system 10, with which they united 1st.

The Drehkolben-Antriehsmaschin® 12 and the housing 18 have generally has a layered structure to provide an arrangement which can be built at a low cost and is to wait. More specifically, from left to right in FIG. 2, the housing 18 may include an inlet end plate 28, a Valve enclosing plate 30, a valve channel plate 32, a left bearing support plate 34, a left rotary piston sealing plate 36, a rotary piston chamber section 38, a right rotary piston seal plate 40, a right Bearing support plate 42, a gear transmission housing 44, an outlet end plate 46 and an outlet space cover lock in.

With reference to Flg. 3 let us recognize that the

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Piston prime mover 12 has three identical rotary lobes 50, 52 and 54 extending through at each end (as shown on best to be seen from Fig. 2 1st) are rotatably mounted in such a way that the axes of rotation at the vertices of a imaginary equilateral triangle * The rotary pistons 50 to 54 each consist of cylindrical Body parts and protruding parts 56, 58 or 60, which are sealingly engaged with the wall of the cylindrical chambers 62, 64 and 66. The protrusions 56 to 60 can be provided with radially outwardly biased sealing elements to create a seal between the To cause projection and the chamber wall, as is common with Wankel engine rotors. It's a mean one Drum 68 is provided with a diameter which is equal to the body diameters of the pistons 50 to 54, wherein this drum is also rotatably mounted in bearings at each end, as shown in FIG. the Arrangement of the rotary pistons 50 to 54 and the central drum 68 is designed so that there is sealing contact between the central drum and the body parts the rotary piston 50 to 54 results. The middle drum 68 is provided with a recess 70, the formation of which in is generally adapted to individually receive each protrusion 56-60 in cyclic order.

From Fig. 2 it can be seen that the central drum 68 is a main output shaft formed integrally with it and an accessory drive shaft 26. Each of the rotary pistons 50-54 can rotate clockwise while the central drum 68 rotates counterclockwise. As a result of this Drehscheraas and the like Diameters of the body parts of the rotary lobes 50-54 and the central drum 68 become a slip-free seal between the central drum 68 and each rotary piston

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works. It follows that the wear of the pistons 50 to 54 and the drum 68 becomes minimal.

It is from Flg. 3 to see that each of the rotary lobes 50 to 54 .an annular chamber or an annular Forms volume that is divided into two parts, each by the contact of the projection with the wall and the contact between the middle drum and the Rotary pistons are defined.

From FIGS. 2 and J> it can be seen that there is provided a number of inlet channels 80, 66 connect with an inlet conduit 82 which is the rotary piston chamber in turn with an inlet space 84 at selected times in the compound represented by the rotational position of the disc 86 of the rotating valve are determined. The inlet space 84 is in communication with the inlet opening 20 at all times. In the same way, a number of inlet channels 88 for the piston chamber 62 and a number of inlet channels 90 for the piston chamber 64 are provided. The inlet channels 88 and 90 are connected to inlet conduits 92 and 94, respectively, which are also in communication with the inlet chamber 84 at selected times according to the rotational position of the disc 86 of the rotating valve. From Fig. 6 it can be seen that the inlet lines 82, 92 and 94 have openings which are equidistant from the axis of the central drum 68 in the radial direction and are spaced apart at rotation intervals of 120 °. From FIGS. 2 and 3 it can also be seen that a number of outlet channels 96 are provided for the rotary piston chamber 64, which are in communication with an outlet line 98 which in turn is in communication with the outlet opening 22 to all tents. In the same way are outlet channels 100 and 102 for the

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Chambers 62 and 66 are provided with outlet lines and 106 are connected. The outlet conduits 104 and 106 are connected to the outlet port 22 at all times Connected via an outlet space within the cover 48, as can best be seen from FIG. As can be seen from the drawings are the inlet ports 80, 88 and 90 and the Auelaß channels 96, 100 and located at opposite rarities of contact between the central drum 68 and the respective piston and they are also placed close to this contact for reasons to be explained. Preferred catfish should the rotation interval from the inlet ducts to the outlet ducts, be as large as possible, for example at least { 180 ° and preferably about 270 °.

The rotary valve 86 is attached to a shaft 108 which is integral with and rotatable with the auxiliary output shaft 26 and the central drum 68. As can best be seen from FIG. 5, the valve disc 86 has an arcuate opening 110 extending over an arc of approximately 180 ° which is radially aligned with the openings of the inlet conduits 82, 92 and 94. A raised portion or protrusion 112 surrounds the arcuate opening 110 on each side of the disc 86. A closed recess portion 114 is provided radially opposite the opening 110 to facilitate dynamic balancing of the valve disc. The protrusion 112 of the valve plate 86 cooperates closely with the sealing plates 28 and 32 on each side of the valve plate 86 so that a good flow-tight seal is achieved therebetween. In the position shown in FIG. 5, the valve disk 86 connects the loading space 84 to the inlet line 94 (also shown in FIG. 6) of the rotary piston chamber

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Accordingly, oases with high pressure from the burner to Rotary piston chamber 64 out. Then comes the opening 110 in the position shown in FIG. 5 almost in alignment with the inlet line 92 for the rotary piston chambers 62. For at least part of the working cycle, both rotary piston chambers 62 and 64 are exposed to gases high pressure supplied from the inlet space 84.

As can be seen from the Zei & Im-Jngen, the rotary piston drive machine is 12 preferably provided with a number of cooling passages 114 extending through the prime mover extend and suitable for receiving a cooling solution or a cooling flow therethrough are.

In operation, combustion by-product gases are introduced into inlet port 20 at elevated pressure and are then passed to one or two inlet channels 80, 88 or 90 according to the position of the rotary valve 86. When the piston chamber 62 according to FIG. 3 is considered, it is true recognize »that an annular, through the projection 56 and the contact of the piston body with the rotating drum 68 defines chamber portion II6, the combustion byproduct Gases are supplied from the inlet channels 88. The pressure of the gas in the chamber II6 acts on the rotary piston 50 in such a way that it calibrates in a clockwise direction rotates so that the volume .116 expands. Ss 1st can also be seen that an annular, also through the projection 56 and the contact of the piston body Chamber part 118 defined by the rotating drum 68 decreases in size during the rotation of the rotary piston 50. When the rotary piston 50 rotates; becomes a useful torque and a useful power to the output shafts 24 and 26 via the associated spur gear 74 and the

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Spur gear 72 of the central drum 68 essentially corresponding to the pressure energy of the chamber 62 supplied Transferring gases. The outlet channels 100, as noted above always open to Auslafkanal 22 « an increase in pressure in the shrinking chamber part 118, so that unnecessary waste of energy is avoided will. After a rotation of approximately 180 °, the passage from the inlet opening 22 to the inlet channels 88 through the valve disc 86 is closed. At this time, the oases of increased pressure cause the protrusion to rotate further 86 on the rotary piston 50 until it passes the outlet channels 100 after additional work, | the pressure within expanding annular chamber portion 116 via outlet port 22 to atmosphere to be balanced out. The valve disc keeps the inlet channels 88 closed with respect to the inlet opening, when the protrusion 56 is clockwise continues along the recess 70 until it reaches the rear edge of the inlet channels 88, wherein at this time the annular slot 110 of the valve disc 86 is again arranged so that it prevents the inflow of Enables oases under high pressure in the expanding annular chamber part II6. Find the same work cycles in relation to the other rotary lobes 52 and 54, but each with an operating delay of 120 ° or 240 °, " so that a power output is essentially in accordance with the pressure energy supplied to the piston chambers 64 or 66 Combustion by-product oasis results. It will be understood that the power output of the rotary pistons 50 to 54 by engaging the gears 72 to 76 with the middle gear 78 is combined so that a combined power output to the shafts 24 and 26 takes place.

Looking at the above description it is understandable

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that created by the invention a prime mover that has a high torque output and a high power output has a wide range of rotational speeds. Furthermore, this prime mover has lower Pollutant emission values than usual prime movers with calibrated reciprocating piston. The inventive Driving machine has with common driving machines reciprocating pistons comparable manufacturing costs. Furthermore, the prime mover provides the advantages a turbine prime mover, as it uses rotating parts instead of reciprocating parts, however, does not have the disadvantage of turbine prime movers in terms of low torque output at low Rotation speeds.

It is understandable that the above according to the invention Teachings are sized to enable one skilled in the art to understand the method of making a preferred To recognize embodiment of the invention. However, it is understood that the invention varies as modified and may be changed without departing from the scope of the invention as defined by the appended claims will.

Claims t

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Claims (1)

Claims hl engine system, characterized by a source of fuel, fuel from the Trelbstoffquelle receiving means for combustion of the fuel for the supply of combustion by-product gases at elevated pressure, and rotating drive machinery means include at least a rotary piston and a chamber for said piston, said piston chamber the combustion by-product oasis can be pulled to rotate the piston to provide a mechanical power output substantially in accordance with the pressure energy of the gas. 2. Drive machine system according to claim 1, characterized in that further compressor devices for supplying an oxygen-containing gas at an increased pressure to the burner means for burning the Fuel are provided. 3. drives machine system according to claim 2, characterized by LeistungeUbertragungsvor- g directions for transmission of power from the rotating drive machine resources to the Kompressorvorrlohtungen, to drive them. 4. Drive machine system according to claim 3, characterized characterized in that the power transmission device is a mechanical connection between the rotary piston and the Kompressorvorriohtung. 109851/1318 ' ^{/ #} 5. Antriebmasohinensystem according to claim 1, characterized characterized in that the rotating drive machine means sowing a number of rotary lobes, each one the burns byproduct gaee each piston receiving chamber for rotation, the pistons being interconnected to form a combined one Power output essentially corresponding to the total pressure energy of the acting on the number of pistons Oases to deliver. 6. Drive machine system according to claim 1, characterized characterized in that the rotating drive means comprises: a housing assembly with an inlet opening for supplying the combustion by-product oasis, with an outlet port and with one resulting in a generally cylindrical rotary piston chamber Inner wall; a rotary piston rotatably mounted within the chamber and having a cylindrical body and an off this outstanding protrusion «of a good gas-tight seal with the chamber wall, the body defining a substantially annular chamber defined by the protrusion is interrupted; a sealing device rotating and engaged with the piston body a recess for receiving the projection, the rotating sealing device corresponding to the rotation of the rotary piston is rotatable in order to ensure that the projection is received in the recess with each revolution of the rotary piston, and wherein the rotating sealing device and the protrusion comprise an expanding annular chamber portion and a decreasing annular chamber portion define; Inlet channel arrangements in the chamber wall, which are connected to the expanding annular chamber part in To be connected; Outlet channel arrangements in the chamber wall 109851/1318 for connecting the decreasing ring-shaped chamber part with the housing outlet, the outlet channel means from the inlet channel means through a predetermined interval of rotation are separated; and rotary valve means having an opening connecting the housing inlet to the inlet channel assemblies for at least a portion of the period of rotation between a position of the protrusion in the vicinity of the intake passage arrangement and an arrangement of the projection in the vicinity of the outlet channel arrangement so connect that the pressure of the combustion by-product oasis supplied to the inlet port becomes a causes pressure-dependent rotation of the rotary piston. 7. drives machine system according to claim 6 »characterized _s that the Drehventilvorrlohtung is a plate having provided therein an opening which is rotatable in response to rotation of the piston for connecting the combustion by-product gas with which aisdehnenden annular chamber portion. Θ. Drive machine system according to Claim 7, characterized > That the valve has a generally arcuate opening and an arcuate one Length that connects the combustion by-product gas with the expanding annular chamber (| part for a considerable part of the Arbeitsperlode results. 9 * drive machine system according to claim 6, characterized in that the rotating Drive means include: a number of rotary pistons, the housing assembly being a number of inner walls that provide a generally cylindrical piston chamber for each of the rotary lobes where-5. each of the rotary pistons rotatable within one of the chambers 109851/1318 is attached and has a cylindrical body and one of these protruding projection, which has a good provides a gas-tight seal with the wall of the chamber and wherein the body forms a substantially annular chamber, which is interrupted by the projection; rotating engaged with the body of each of the pistons Sealing devices, which, like each piston, are rotatable around a Receipt of the protrusions in the recess with every rotation to yield, with the rotating sealing devices and the protrusions an expanding annular Chamber portion and a decreasing annular chamber portion in each of the chambers; Inlet channel arrangements in each of the chamber walls communicating with the expanding annular chamber portion; Exhaust duct arrangements in each of the chamber walls to connect the decreasing annular chamber part with the Housing outlet, the outlet channel arrangements from the inlet channel arrangements for each chamber by a given Rotation interval are separated; and rotary valve devices having an opening connecting the housing inlet to the inlet passage arrangement for each chamber for at least part of the period of rotation between a position of the projection in the proximity of the inlet duct arrangement and a position of the pre-jump in the vicinity of the outlet duct arrangement of each chamber connects such that the pressure transmitted to the inlet port causes a pressure-dependent rotation of each rotary piston causes the individual rotary lobes of the number of rotary lobes with each other and with the rotating sealing devices are connected to rotate the rotating sealing devices and have a combined power output to create substantially corresponding to the total pressure energy of the gas acting on the number of pistons. 1 09851/1318 10. Drive machine system according to Anspruoh 9, characterized in that the rotate * de sealing device has an output shaft attached to it for outputting the combined power output. 11. Antriebmasohinensystem according to claim 9, characterized characterized in that it has three rotary lobes. 12. Rotating prime mover according to one of the preceding Claims, characterized by a housing arrangement with an inlet opening, with an outlet opening and with an inner wall forming a generally cylindrical rotary piston chamber, a rotary piston mounted rotatably within the chamber and having a cylindrical body and a projection protruding therefrom which provides a good gas-tight seal with the chamber wall, wherein the body forms a substantially annular chamber which is interrupted by the projection, a rotating sealing device which is in engagement with the piston body and which has a recess for receiving the projection and which is rotatable in accordance with the rotation of the rotary piston to accommodate the projection for each rotation of the rotary piston to ensure, with the \ rotating seal apparatus and the projection define an expanding annular chamber portion and a decreasing fled annular chamber portion arranged in the chamber and with which ausdehenden annular Kam Inlet channel arrangements arranged in the wall and connecting the decreasing annular chamber part to the housing outlet, which are separated from the inlet channel arrangements by a predetermined rotation interval, and 109851/1318 Rotary valve devices with a housing inlet with the inlet channel arrangements for at least part of the Rotary perlode between a position of the projection in the vicinity of the inlet channel arrangement and a position of the Voraprunges in the vicinity of the exhaust channel arrangements like this connect so that the pressure supplied to the inlet opening causes a pressure-dependent rotation of the rotary piston. 15. Drive machine system according to Claim 12, characterized in that the rotary valve device has a plate with one disposed therein The opening is a function of the rotation of the piston for connecting the housing inlet opening with the expanding annular chamber part is rotatable 14. A prime mover system according to claim 13, characterized in that the valve has a generally arcuate opening and an arcuate length connecting the housing inlet opening to the expanding annular chamber portion for a substantial portion of the period of rotation. 15. Drive machine system according to claim 12, characterized in that the rotating Propulsion engine means comprise the following parts: a number of rotary pistons, with the oehftus means a number of having a generally cylindrical rotary piston chamber for each of the rotary pistons yielding interior walls, wherein further, each of the rotary lobes is rotatably mounted within a chamber and has a cylindrical body and a of this protruding protrusion which gives a good gas-tight seal with the wall of the chamber and • A 1 09851/1318 the body defining a substantially annular chamber interrupted by the projection; rotating sealing devices which are in engagement with the body of each of the pistons and which, like the pistons, are rotatable in accordance with the rotation of the rotating pistons to cause the projections to be received in the recess with each rotation, the rotating sealing devices and the projections becoming one expanding annular chamber portion and a decreasing annular chamber portion in each of the chambers define inlet duct arrangements in each of the chamber walls communicating with the expanding annular chamber portion; Outlet duct assemblies in each of the chamber walls like for connecting each of the decreasing annular chamber portion with the housing outlet, wherein the outlet duct arrangements of the inlet channel devices are separate for each chamber by a predetermined rotation interval; and rotary valve means having an opening connecting the housing inlet to the inlet passage arrangements for each chamber for at least a portion of the period of rotation between a position of the projection proximate the inlet passage means and a position of the projection proximate the outlet passage formations of each chamber, that the pressure supplied to the inlet opening causes a pressure-dependent rotation of each rotary piston, the number of rotary pistons being connected to one another and to the rotating sealing device, in order to rotate the rotating Abdiohtvorrlohtung and a combined power output substantially corresponding to the total pressure energy of the to deliver gas acting on the number of pistons. 16. Drive machine system according to claim 15 » characterized in that the rotating sealing device has an output 1 098 51/1318 wave for delivering the combined output power * 17 · Propulsion system according to claim 15 « characterized in that it has three rotary pistons. 1 0 9 8 B 1/1 3 1 8