EP1499799A1 - Rotary piston machine - Google Patents
Rotary piston machineInfo
- Publication number
- EP1499799A1 EP1499799A1 EP03722509A EP03722509A EP1499799A1 EP 1499799 A1 EP1499799 A1 EP 1499799A1 EP 03722509 A EP03722509 A EP 03722509A EP 03722509 A EP03722509 A EP 03722509A EP 1499799 A1 EP1499799 A1 EP 1499799A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- housing
- machine according
- pistons
- chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 24
- 230000007423 decrease Effects 0.000 claims abstract description 7
- 230000008901 benefit Effects 0.000 description 17
- 239000000203 mixture Substances 0.000 description 13
- 239000000446 fuel Substances 0.000 description 12
- 238000002485 combustion reaction Methods 0.000 description 11
- 230000006835 compression Effects 0.000 description 6
- 238000007906 compression Methods 0.000 description 6
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- 230000009471 action Effects 0.000 description 2
- 239000003225 biodiesel Substances 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000002996 emotional effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000001404 mediated effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/183—Oval or square cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B15/00—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00
- F01B15/007—Reciprocating-piston machines or engines with movable cylinders other than provided for in group F01B13/00 having spinning cylinders, i.e. the cylinders rotating about their longitudinal axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0079—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having pistons with rotary and reciprocating motion, i.e. spinning pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
- F01B3/045—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces by two or more curved surfaces, e.g. for two or more pistons in one cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders
- F02B75/282—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial cylinders the pistons having equal strokes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/18—Other cylinders
- F02F1/186—Other cylinders for use in engines with two or more pistons reciprocating within same cylinder
Definitions
- the invention relates to a rotary piston machine, with a housing which has a cylindrical housing inner wall, with at least one piston arranged in the housing, which can rotate about a longitudinal central axis of the housing, and thereby executes a reciprocating linear movement by means of a control mechanism which does so serves to periodically enlarge and reduce at least one chamber assigned to the piston.
- a rotary piston machine is known from DE 100 01 962 AI.
- Such a rotary piston machine is preferably used as an internal combustion engine.
- Rotary piston machines generally belong to a type of machine in which one or more pistons revolve in a housing, wherein the orbital movement of the piston or pistons is usually superimposed on another type of movement, around which one or more chambers associated with the piston or pistons usually form the working chambers for a Carnot cycle, periodically increasing and decreasing in volume.
- a plurality of pistons are arranged circumferentially distributed around the central axis of the housing.
- the pistons are mounted so as to be radially movable in the housing, the control mechanism deriving the radially directed reciprocating stroke movement of the pistons from the orbital movement of the pistons.
- the control mechanism of the known rotary piston machine has a stationary curve piece which is arranged approximately in the center of the housing, the pistons each having at least one running member on their side facing the center axis of the housing, with which the pistons are guided along the control curve.
- the control mechanism is also designed so that each adjacent one of the radially movable pistons performs an opposite stroke movement.
- the pistons of the known rotary piston machine each have a toothing on their end faces leading and trailing in the direction of rotation of the pistons, and between the end faces of adjacent pistons there is a co-rotating shaft provided with toothing, which meshes with the teeth of the two adjacent end faces of the pistons Intervention stands.
- rotary piston machine Another type of rotary piston machine is known from WO 98/13583, in which the individual pistons rotating in the housing are designed as pivoting pistons, which additionally perform rocking-like pivoting movements in the housing during their rotational movement.
- the control mechanism for controlling the rocking back and forth swiveling movements of the individual pistons corresponds almost identically to that Control mechanism of the aforementioned known rotary piston machine with linearly radially movable pistons.
- the invention has for its object to provide a new type of rotary piston machine, in which the periodic change in the volume of the at least one chamber is achieved in a different way.
- this object is achieved with respect to the rotary piston machine mentioned at the outset in that the linear movement of the at least one piston takes place parallel to the longitudinal center axis of the housing.
- the at least one piston executes a linear movement parallel to the longitudinal central axis of the housing when it rotates around the longitudinal central axis of the housing.
- the at least one piston has no radially directed movement component.
- the rotary piston machine according to the invention Machine can be designed radially small, since the at least one piston does not have to execute a radial movement or a movement with a radial movement component.
- the rotary piston machine according to the invention is particularly suitable as an internal combustion engine, in which case the at least one chamber then serves as a work chamber for a Carnot cycle in which the work cycles of intake, compression, expansion and ejection take place.
- the rotary piston machine according to the invention preferably has more than one piston, the plurality of pistons then all performing linear movements directed parallel to the longitudinal center axis of the housing when rotating in the housing, as will be described hereinafter with reference to preferred configurations.
- the piston is arranged off-center with respect to the longitudinal center axis of the housing, and in the housing at least one further piston is arranged which rotates around the longitudinal center axis and is arranged on the side facing away from the first piston with respect to the longitudinal center axis of the housing.
- the rotary piston machine according to the invention can be implemented as an at least two-cylinder internal combustion engine, with the at least two pistons, which are opposite in relation to the longitudinal center axis and which do not necessarily have to be axially at the same height, with one identical configuration with respect to the piston the longitudinal center axis axisymmetric mass distribution can be achieved.
- the centrifugal forces that affect both pistons cancel each other out advantageously when circulating in the housing.
- the two pistons can be arranged so that the linear movement takes place in opposite directions to one another by means of the control mechanism, or the linear movement of the two pistons can be in the same direction.
- the further piston is arranged axially opposite the first piston at the same height.
- the advantage is achieved that the centrifugal forces of the two pistons can be offset against one another by their axially symmetrical arrangement with respect to the longitudinal center axis.
- two chambers can be formed in this arrangement, which are arranged offset by 180 ° to one another about the longitudinal central axis, so that two full working cycles are completed over a full revolution of the piston arrangement.
- the further piston is firmly connected to the first piston.
- the advantage here is that the two opposing pistons are mutually supported against the centrifugal forces acting on them when rotating and in this way a surface friction of the pistons on the housing is switched off.
- the at least one piston is arranged and runs centrally around the longitudinal central axis around a piston central axis coinciding with the longitudinal central axis in the housing.
- At least one additional piston which is arranged around the longitudinal center axis and is arranged in a straight extension of the first piston is arranged in the housing.
- the advantage of this measure is that several chambers can be implemented in the longitudinal direction of the housing, so that a multi-cylinder rotary piston machine can also be implemented in this way.
- the at least one chamber is formed by the space between facing end faces of the first piston and the further piston.
- the advantage here is that when the two pistons move in opposite directions, the individual strokes of the two pistons add up to an overall stroke, so that when the rotary piston machine according to the invention is used as an internal combustion engine in the common chamber between the two pistons, the fuel / air mixture with a higher pressure can be compressed.
- the linear movement of the first piston is directed in the opposite direction to the linear movement of the second piston, and the space between the mutually facing end faces of the first piston and the further piston forms a common chamber.
- This measure has the advantage that the rotary piston machine according to the invention is in this way also balanced in terms of the linear movement of the at least two pistons, as a result of which vibrations of the rotary piston machine in the longitudinal direction are eliminated.
- At least four pistons are arranged in the housing, two of which are arranged axially at the same height opposite each other with respect to the longitudinal center axis of the housing, and two are each arranged in a linear extension to one another are.
- the two pistons arranged opposite each other axially at the same height with respect to the longitudinal center axis of the housing each form a preferably rigid double piston, the two double pistons then being arranged in an axially linear extension to one another and together in rotate the housing around the longitudinal central axis and perform linear movements in opposite directions.
- the one double piston and the other double piston are preferably each assigned a separate control mechanism for controlling the reciprocating linear movement when rotating in the housing.
- the control mechanism comprises at least one guide element arranged on the at least one first piston and at least one control curve formed in the inner wall of the housing, along which the guide element runs.
- Such a control mechanism has the advantage over the control mechanism of the known rotary piston machine that it is less susceptible to wear, because, unlike the control mechanism of the known rotary piston machine, which comprises a cam piece arranged centrally in the housing and running members provided on the pistons, it does not have the effect of the the rotational movement of the pistons is subject to centrifugal forces.
- the at least one first piston is preferably provided with a shaft projecting radially from the side facing the housing inner wall, on which one or two rollers are arranged, while the control cam is preferably designed as a guide groove formed in the housing inner wall, into which the rollers engage and roll in the housing when the piston rotates.
- a side of the at least one piston facing the housing inner wall is designed in cross section in the form of a partial circle.
- This measure has the advantage that the side facing the housing inner wall of the at least one piston is adapted to the circular inner contour of the housing inner wall, as a result of which the piston can be sealed in an advantageously simple manner by means of seals in the form of circular sections.
- the side of the at least one piston facing the housing inner wall preferably extends over approximately 90 °.
- the at least one piston is guided in its linear movement by a rotor which rotates about the longitudinal central axis together with the piston and is axially immovable.
- a rotor has the advantage that the rotary movement of the at least one piston in the housing can be tapped from the rotor via an output shaft connected to the rotor, for example when the rotary piston machine according to the invention is used as an internal combustion engine in a motor vehicle. In this way, the rotational movement can be centered on the longitudinal central axis of the housing of the rotary piston machine. can be gripped without the need for complex transmission or countershafts.
- a conventional reciprocating piston engine can be simulated with the rotary piston machine according to the invention, compared to which the rotary piston machine according to the invention has the considerable advantage that the rotational energy can be dissipated due to the rotating movement of the at least one piston via the rotor, which is axially immobile.
- the rotor can be designed as a sleeve or as an axis.
- the rotor lies on the longitudinal central axis of the housing Has a central section that separates the chamber assigned to the first piston from the chamber assigned to the further piston.
- the rotor also takes over the function of separating the at least two chambers without additional complex construction measures, which, for example, form working chambers for a Carnot cycle when the rotary piston machine is used as an internal combustion engine.
- each of the two end faces of the at least one piston is assigned a chamber which shrink and enlarge in opposite directions, the one chamber being the working chamber for a Carnot cycle and the other chamber serves as a pre-pressure chamber for generating a pre-pressure in order to apply a pre-pressure to the working chamber.
- the working chamber is self-charged without external devices such as a compressor or a turbocharger and without increasing the installation space of the rotary piston machine.
- the pre-pressure chamber into which fresh air can be drawn increases accordingly.
- the working chamber expands after the fuel / air mixture is ignited, the fresh air previously sucked into the pre-pressure chamber is compressed accordingly and can then be pressed into the working chamber under pressure after the burned fuel / air mixture has been expelled, as a result of which the fuel / Air mixture can be compressed with higher pressure in the next cycle.
- the rotary piston machine according to the invention is particularly suitable as an internal combustion engine for operation with diesel or even biodiesel fuels.
- the central section of the rotor on the side of the chambers serving as the pre-pressure chamber is absent or is designed such that two of the chambers serving as the pre-pressure chamber communicate with one another. It is advantageous here that the chambers serving as pre-pressure chambers together form a pre-pressure chamber with a total volume that is larger, preferably four times as large as the volume of the at least one working chamber, as a result of which the air pre-compressed in the pre-pressure chambers enters the at least an even higher pre-pressure a working chamber can be initiated.
- the admission pressure chamber is connected to the working chamber via a line on the outside of the housing, in which a valve, in particular a controllable valve, is preferably arranged.
- the controllable valve can be a solenoid valve, for example, which is opened when a maximum pre-pressure has been generated in the pre-pressure chamber.
- the admission pressure chamber can also be connected to the working chamber directly through the piston, in which case at least one valve, preferably an automatic valve, is then arranged in the piston.
- the advantage of this measure is that there is no need for a connecting line on the outside of the housing between the pre-pressure chamber and the working chamber, as a result of which the rotary piston machine takes up less space.
- the aforementioned automatic valve can, for example, be a flutter valve.
- the two end faces of the at least one piston are each assigned a chamber which shrink and enlarge in opposite directions, both chambers serving as working chambers for a Carnot cycle.
- This measure has the advantage that, for example, two cylinders of a conventional engine can be simulated with only one piston, a further particular advantage being that the expansion of one working chamber after the ignition of the fuel / air mixture, the compression of the other working chamber, who just sucked in the new fuel / air mixture.
- this configuration can be used, for example, to simulate a conventional six-cylinder engine.
- the rotary piston machine according to the invention can be used as an internal combustion engine or as a compressor.
- Figure 1 is a perspective, partially sectioned illustration of a rotary piston machine according to a first embodiment in a first operating position.
- FIG. 2 shows the rotary piston machine in FIG. 1 in a second operating position
- FIGS. 1 and 2 shows the rotary piston machine in FIGS. 1 and 2 in a third operating position
- FIG. 4 shows the rotary piston machine in the operating position shown in FIG. 3 in a partially broken representation
- FIGS. 1 to 4 shows a perspective illustration of an individual part of the rotary piston machine in FIGS. 1 to 4;
- Figures 7a) to d) each have a section along the line VII-VII in Figures 6a) to d);
- Figures 10a) and b) each have a section along the line X-X in Figures 9a) and b);
- Figures 11a) and b) each have a section along the line XI-XI in Figures 9a) and b);
- Figures 13a) to d) each have a section along the line XIII-XIII in Figures 12a) to d);
- Figures 14a) to d) each have a section along the line XIV-XIV in Figures 12a) to d);
- Figures 15a) to d) each have a section along the line XV-XV in Figures 12a) to d);
- FIG. 1 to 8 show a rotary piston machine provided with the general reference number 10 according to a first exemplary embodiment.
- the rotary piston machine 10 is used here as an internal combustion engine.
- the rotary piston machine 10 has a housing 12 which has an essentially cylinder-symmetrical basic shape. At its longitudinal ends, the housing 12 is closed by a housing cover 14 and a housing cover 16, although a different division of the housing 12 can also be considered, as can be seen, for example, from FIG. 6a).
- the housing 12 has a cylindrical housing inner wall 18, which is therefore circular in cross section.
- a longitudinal central axis 20 forms the cylinder axis of the housing inner wall 18.
- first piston 22 there is at least one first piston 22, and in the exemplary embodiment shown there are a further second piston 24, which can only be seen in the perspective representations in FIG. 4, a further third piston 26 and a further fourth piston 28, the can also be seen in the perspective view only in FIG. 4.
- first piston 22 and the third piston 24 which form a first double piston
- second piston 26 and the fourth piston 28 the form a second double piston.
- the first piston 22 is fixedly connected to the third piston 24 via a first connecting piece 30, and the third piston 26 is fixedly connected to the fourth piston 28 via a second connecting piece 32.
- the connecting pieces 30 and 32 each produce a rigid connection between the pistons 22 and 24 or 26 and 28.
- the first piston 22 and the further pistons 24 to 28 run in the housing 12 together around the longitudinal central axis 20 according to an arrow 34, so that the longitudinal central axis 20 can also be referred to as the circumferential axis.
- the first piston 22 and the further pistons 24 to 28 perform reciprocating linear movements when rotating around the central longitudinal axis 34 of the housing 12 by a control mechanism to be described later, these linear movements being directed parallel to the central longitudinal axis 34, as with a double arrow 36 is indicated.
- the four pistons 22 to 28 are each arranged eccentrically with respect to the longitudinal central axis 20 of the housing 12, as can be seen from the cross-sectional representations in FIGS. 7a) to 7d).
- the further second piston 24 and the further fourth piston 28 are located opposite the first piston 22 with respect to the longitudinal central axis 20, ie on the side of the longitudinal central axis 20 facing away from the first piston 22.
- the further second piston 24 is arranged opposite the first piston 22 at the same axial height, while the further fourth piston 28 is arranged axially offset opposite the first piston 22.
- the further third piston 26 is arranged in the housing in a straight extension to the first piston 22, ie is in the same circumferential position as the first piston 22 with respect to the longitudinal central axis 20.
- the second piston 24 and the fourth piston 28 are circumferential - Direction with respect to the first piston 22 and the third piston 26 arranged offset by 180 °.
- first piston 22 Since the first piston 22 is firmly connected to the further second piston 24, the first piston 22 and the second piston 24 perform linear movements in the same direction parallel to the longitudinal central axis 20 when rotating in the housing 12. Likewise, the further third piston 26 and the further fourth piston 28 perform linear movements in the same direction due to their fixed connection by means of the connecting piece 32 when rotating in the housing 12.
- pistons 22, 24 on the one hand and pistons 26 and 28 on the other hand either move towards or away from each other.
- all four pistons 22 to 28 do not change their rotational position relative to one another when rotating around the longitudinal central axis 20.
- the four pistons 22 to 28 are identical to one another in terms of their geometry and dimensions. Because of the 20 axisymmetric with respect to the longitudinal central axis. The arrangement of the four pistons 22 to 28 completely compensate for the centrifugal forces which occur when the pistons 22 to 28 rotate around the longitudinal central axis 20. In addition, the inertia occurring during the linear movement of the pistons 22 to 28 is also compensated for in the rotary piston machine 10 because the first double piston formed from the pistons 22 and 24 is linearly opposed to the second double piston formed from the pistons 26 and 28 in the housing 12 emotional. As already mentioned, a control mechanism is provided for deriving the linear movement of the individual pistons 22 to 28 from their orbital movement about the longitudinal central axis 20, which is provided in FIGS. 1 to 4 and 6 with the general reference numeral 40, which is subsequently only referred to the piston 22 is described.
- the control mechanism 40 comprises a guide member 42 arranged on the first piston and a control cam 44 formed in the housing inner wall 18, along which the guide member 42 runs.
- the guide member 42 is fixedly connected to the first piston 22 and has an axle 46 and a first roller 48 fastened to the axle 46 and a second roller 50.
- the roller 48 has a smaller outer diameter than the roller 50.
- the control cam 44 is designed in the form of a guide groove 52 formed in the housing inner wall 18.
- the guide groove 52 has a portion 54 of smaller diameter and a portion 56 of larger inner diameter, corresponding to the outer diameter of the roller 48 and the outer diameter of the roller 50.
- the control cam 44 in the form of the guide groove 52 extends completely around the longitudinal central axis 20 and represents a closed control cam which, in order to derive the linear movement of the pistons 22 to 28 from the rotational movement of the pistons around the longitudinal central axis 20, has a correspondingly curved shape, approximately has the shape of a circle bent by a diameter.
- the pitch of the control cam 44 along the longitudinal central axis 20 determines the stroke of the piston 22.
- the second piston 24, as can be seen from Fig. 6a), is equipped with a guide member which is identical to the guide member 42 and on which two rollers are arranged accordingly, the guide member 42 being along the same cam 44, i.e. in the same guide groove 52, runs.
- the control mechanism 40 thus represents a common control mechanism for the double piston formed from the pistons 22 and 24.
- rollers 48 and 50 and correspondingly the guide groove 52 can also be conical.
- a corresponding control mechanism 58 is provided for the further double piston formed from the pistons 26 and 28, which differs from the control mechanism 40 only in that a control curve 60 is mirror-symmetrical with respect to the control curve 44 of the control mechanism 40 with respect to the central cross-sectional plane of the housing 12 ,
- the pistons 22 to 28 are guided in their linear movement by a rotor 62, which is shown in isolation in FIG. 5.
- the rotor 62 generally has a cylindrical shape which is adapted to the inner wall 18 of the housing 12 of the rotary piston machine 10.
- the rotor 62 has two trough-like recesses 64 and 66 (see, for example, FIG. 8a) offset 180 ° with respect to the longitudinal central axis 20 (see, for example, FIG. 8a)), of which only the recess 64 in FIG. 5 you can see.
- the mutually opposite walls of the trough-like recesses 64 and 66 have a partially circular cross section.
- the rotor 62 has a sole or a central section 68 which separates the recesses 64 and 66 from one another.
- two elongated holes 70 and 72 are also recessed, through which the connecting pieces 30 and 32 (see FIG. 4) extend.
- the central section 68 can also have differently shaped openings there, or the central section 68 can be completely absent in this area, i.e. extend with respect to the longitudinal direction of the rotor 62 only over a central portion of the same.
- the rotor 62 is circular in cross section, the two recesses 64 and 66 extending approximately over 90 ° with respect to the longitudinal central axis 20 in the circumferential direction.
- the central section 68 of the rotor 62 extends at its broad ends approximately over 90 ° or a quarter of the full circumference.
- the central section 68 of the axially immovable rotor 62, with which the pistons 22 to 28 rotate together, lies centrally on the longitudinal central axis 20 of the housing 12.
- shaft extensions 74 and 76 are provided, via which the rotor 62 in the housing 12, more precisely in the housing covers 14 and 16, is rotatably mounted.
- the shaft extension 74 projects from the housing 12 with a toothed end piece 78, and likewise the shaft extension 76 projects from the housing with a toothed end piece 80.
- the end piece 80 is omitted and that the housing cover 16 is made closed over the shaft extension 76.
- the orbital movement of the rotor 62 can be tapped as rotational energy via the end piece 78 and / or the end piece 80, ie the end piece 78 and / or the end piece 80 can serve as an output shaft.
- measures for example support rollers, can be provided on the rotor 62 in order to support the rotor 62 against lateral forces in the housing 12 in the case of a large overall length.
- Each of the pistons 22 to 28, as will be described below for the piston 22, has a side 82 facing the housing inner wall 18, which is designed in the form of a partial circle in cross section, so that each of the pistons 22 to 28 is adapted to the outside of the housing inner wall 18 is.
- the side 82 extends over a circular angle of approximately 90 °.
- a side 85 of each piston 22 to 28 facing away from the side 82 and facing the longitudinal central axis 20 is likewise designed in cross section in the form of a partial circle, the center of the circle of which is from the center of the circle of the partial circle is spaced, which forms the side 82 of the pistons 22 to 28, respectively.
- Each piston 22 is thus approximately almond-shaped or lenticular in cross-section.
- Each of the pistons 22 is assigned at least one chamber which periodically decreases and increases in volume due to the reciprocating linear movement of the pistons 22 to 28.
- a first chamber 86 is assigned to the first piston 22 on an end face 84.
- a second chamber 90 is assigned to the piston 22 on a face 88 arranged opposite the face 84.
- the third piston 26 is in turn associated with the chamber 86 on one end 92 facing the end 84 of the first piston 22, so that the chamber 86 is associated with the two pistons 22 and 26 together.
- the pistons 24 and 28 are assigned chambers 98, 100 and 102, which are arranged offset by 180 ° with respect to the chambers 86, 90 and 96 with respect to the longitudinal central axis 20.
- the chambers 86 and 98 are completely separated from one another by the central section 68 of the rotor 62.
- the chamber 86 is separated from the chambers 90 and 96 by means of a seal 104, which seals the piston 22 against the housing inner wall 18 and against the central section 68 of the rotor 62, and a seal 106, which seals the piston 26 against the housing inner wall 18 and the central section 68 of the rotor 62, completely separated.
- the chamber 98 is completely separated from the chambers 100 and 102 via seals 108 and 110 on the pistons 24 and 28, respectively.
- the chambers 90 and 100 communicate with one another via the elongated hole 70, and the chambers 96 and 102 also communicate with one another via the elongated hole 72, which, however, can also be modified in accordance with an embodiment to be described later in that the chambers 90 and 100 or 96 and 102 do not communicate with each other.
- the elongated holes 70 and 72 can also be shaped differently or the central section 68 can be missing at these points, as a result of which the chambers 90 and 100 as well as 96 and 102 likewise communicate with one another and each form a double total volume.
- the chambers 86 and 98 serve as working chambers for a Carnot cycle
- the chambers 90, 100 and 96, 102 serve as pre-pressure chambers for generating a pre-pressure with which the working chambers 86 and 98 act can be.
- the chambers 90 and 100 are connected to the chambers 86 and 98 via an opening 104 in the housing 12 and a connecting line 106, depending on which of the chambers 86 or 98 is in the course of the orbital movement of the pistons 22 to 28 ⁇ m the longitudinal central axis 20 face an inlet opening 108.
- a valve 110 is arranged in the inlet opening 108, which is designed as a controllable valve, in particular a solenoid valve, 112.
- the chambers 96 and 102 are correspondingly connected to the inlet opening 108 via an opening 114 and a connecting line 116 with the interposition of the valve 110.
- the chambers 86 and 98 serving as working chambers are assigned a total of one spark plug 118 for emitting ignition sparks and one injection nozzle 120 for injecting a fuel, for example gasoline, diesel or biodiesel.
- a fuel for example gasoline, diesel or biodiesel.
- the chambers 86 and 98 in the housing are also assigned an outlet opening 122 for ejecting the combusted fuel / air mixture.
- the chambers 96 and 102 serving as pre-pressure chambers are also assigned a common suction opening 124, wherein the corresponding suction opening in the housing 12 is also assigned to the chambers 90 and 100 also serving as pre-pressure chambers.
- FIGS. 6a), 7a) and 8a) show the rotary piston machine in a first operating position, which corresponds to the operating position in FIGS. 3 and 4, respectively.
- the fuel-air mixture which is maximally compressed, is ignited via the spark plug 118.
- the combusted fuel-air mixture has just been completely ejected from the chamber 98.
- the chambers 96, 102 serving as pre-pressure chambers were through the suction opening 124, in which a corresponding valve, preferably an automatic valve, for example a flap valve, can be arranged completely filled with air.
- the chambers 90 and 100 serving as pre-pressure chambers were completely filled with fresh air through a corresponding suction opening.
- the pistons 22 to 28 rotate clockwise around the longitudinal central axis 20 together with the rotor 62 and have become the operating position in FIGS. 6b), 7b) and 8b) (cf. 1) rotated by about 45 °.
- the fuel / air mixture previously ignited in the chamber 86 now expands in the volume-increasing chamber 86, while in the chamber 98 from the pre-pressure chambers 90, 100 and 96, 102, which decrease in volume and thereby the fresh air previously introduced compress, fresh air is pressed in. As shown in FIG.
- the valve 110 is opened in order to admit the fresh air pre-compressed from the chambers 90, 100 and 96, 102 serving as pre-pressure chambers into the chamber 98. Since the maximum volume of the chambers 90, 96, 100, 102 together is greater than the maximum volume of the chamber 98, namely approximately four times as large, (pre) compression of the air pressed into the chamber 98 occurs.
- the pistons 22 and 24 meanwhile move parallel to the longitudinal central axis 22 according to an arrow 126, and the pistons 26 and 28 move in the opposite direction according to an arrow 128 parallel to the longitudinal central axis 20.
- the operating position shown in FIGS. 6c), 7c) and 8c) (see FIG. 2) is reached, in which the chamber 98 has reached its maximum volume and is filled with pre-compressed fresh air, while the opposite chamber 86, which is not visible in the drawing, likewise assumes its largest volume after the previously ignited fuel / air mixture has completely expanded.
- the chambers 90, 100 and 96, 102 now have their minimum volume.
- FIGS. 9a) and b), 10a) and b) and 11a) and b) show an embodiment of a rotary piston machine 10 'which is slightly modified compared to the previously described embodiment and which differs from the rotary piston machine 10 by the following features.
- the chambers 90 'and 100' assigned to the pistons 22 'and 24' which in turn serve as pre-pressure chambers for supplying the chambers 86 'and 98' with a pre-pressure generated in the chambers 90 'and 100', and the chambers 90 ' and 100 'in turn communicate with each other, are not connected to the chamber 86' or 98 'via the outside of the housing, but directly via the pistons 22' and 24 '.
- the pistons 22 'and 24' are hollow, and a valve 138 is arranged in each of the pistons 22 'and 24', which is designed as an automatic valve, preferably as a flutter valve.
- the chambers 96 'and 102' associated with the pistons 26 "and 28 ' which also communicate with one another, are directly connected to the chambers 86' and 98 'via valves 140 with the chambers 86' and 98 'connected.
- valves 138, 140 in FIG. 9a) are shown in their closed position, the pistons 22 'to 28' in their position which is maximally displaced towards the center of the housing 12 ' move, the valves 138 and 140 in Fig. 9b) are shown in their open position when the pistons 22 'to 28' move in opposite directions and the chambers 90 ', 100 * and 96' and 102 'decrease in volume. In this way, the chamber 98 'ready for suction between the pistons 24' and 28 'can be acted upon by pre-compressed air from the chambers 90', 100 'and 96' and 102 '.
- FIGS. 12a) - d) to 15a) - d) show a further exemplary embodiment of a rotary piston machine provided with the general reference number 10 ′ *, which differs from the rotary piston machine 10 by the following features.
- the rotary piston machine 10 ′′ in turn has four pistons 22 ′′ to 28 ′′, to which chambers 86 ′′, 90 ′′, 96 ′′, 98 ′′, 100 ′′ and 102 ′′ are assigned.
- the chambers 90 ′′, 96 ′′, 100 ′′ and 102 ′′ do not serve as pre-pressure chambers but, like the chambers 86 ′′ and 98 ′′, also serve as working chambers for a Carnot cycle.
- the chambers 90 ′′ and 100 ′′ ′′ do not communicate with one another, but are completely separated from one another via the central section 68 ′′ of the rotor 62 ′′.
- the chambers 96 ′′ and 102 ′′ Completely separated from one another via the central section 68 ′′ of the rotor 62 ′′ and also serve as working chambers for a Carnot cycle.
- the chambers 90 ′′ and 100 ′′ are correspondingly assigned an inlet duct 142 for fresh air and an outlet duct 144 for expelling the combusted fuel-air mixture.
- the chambers 90 ′′ and 100 ′′ are jointly assigned a further spark plug 146 and a further injection nozzle 148.
- the inlet passage 142, the outlet passage 144, the spark plug 146 and the injection nozzle 148 are in relation to the corresponding inlet passage 108 ′′, outlet passage 122 ′′, the spark plug 118 ′′ and the injection nozzle 120 ′′, which are the chambers 86 ′′ and 98 '' are arranged offset by 90 ° about the longitudinal central axis 20 ''.
- the chambers 96 ′′ and 102 ′′ are assigned a further inlet duct 150, outlet duct 152, a spark plug 154 and an injection nozzle 156, which are in the same circumferential position as the inlet duct 142, the outlet duct 144, and the spark plug 146 and injector 148 associated with chambers 90 "and 100".
- a six-cylinder engine is simulated by means of the rotary piston machine 10 ′′, the work cycles of intake, compression, expansion and ejection in the chambers 90 ′′, 100 ′′ and 96 ′′, 102 ′′ compared to the corresponding work cycles in the chambers 86 "and 98" are offset by 90 °.
- FIGS. 12a) - d) to 15a) - d) show four operating positions of the rotary piston machine 10 ′′, in which the pistons 22 ′′ to 28 ′′ have moved a total of 135 ° about the longitudinal central axis 20 ′′ A full rotation of the pistons 22 "to 28"'over 360 ° around the longitudinal central axis 20 "becomes a full working cycle in the chambers 86" and 98 " carried out, likewise in each of the chambers 90 ′′ and 100 ′′ and 96 ′′ and 102 ′′, so that a total of six complete working cycles in the rotary piston machine 10 ′′ take place with one full revolution.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Reciprocating Pumps (AREA)
- Toys (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Rotary Pumps (AREA)
- Superconductive Dynamoelectric Machines (AREA)
- Valve Device For Special Equipments (AREA)
- Supercharger (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03722509A EP1499799B1 (en) | 2002-04-19 | 2003-04-17 | Rotary piston machine |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP02008814A EP1355053B1 (en) | 2002-04-19 | 2002-04-19 | Rotary piston engine |
EP02008814 | 2002-04-19 | ||
EP03722509A EP1499799B1 (en) | 2002-04-19 | 2003-04-17 | Rotary piston machine |
PCT/EP2003/004067 WO2003089769A1 (en) | 2002-04-19 | 2003-04-17 | Rotary piston machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1499799A1 true EP1499799A1 (en) | 2005-01-26 |
EP1499799B1 EP1499799B1 (en) | 2008-10-22 |
Family
ID=28459500
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02008814A Expired - Lifetime EP1355053B1 (en) | 2002-04-19 | 2002-04-19 | Rotary piston engine |
EP03722509A Expired - Lifetime EP1499799B1 (en) | 2002-04-19 | 2003-04-17 | Rotary piston machine |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02008814A Expired - Lifetime EP1355053B1 (en) | 2002-04-19 | 2002-04-19 | Rotary piston engine |
Country Status (9)
Country | Link |
---|---|
US (1) | US6986328B2 (en) |
EP (2) | EP1355053B1 (en) |
JP (1) | JP4237068B2 (en) |
AT (2) | ATE260404T1 (en) |
DE (2) | DE50200261D1 (en) |
DK (1) | DK1355053T3 (en) |
ES (2) | ES2213721T3 (en) |
PT (1) | PT1355053E (en) |
WO (1) | WO2003089769A1 (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050211418A1 (en) * | 2002-11-01 | 2005-09-29 | Cooligy, Inc. | Method and apparatus for efficient vertical fluid delivery for cooling a heat producing device |
ITSA20030001A1 (en) * | 2003-01-07 | 2003-04-07 | Capossela Davide | INNOVATION IN THE PISTON MOTOR OPPOSED IN A SINGLE ROTATING CYLINDER. |
DE102005026661A1 (en) * | 2005-05-31 | 2006-12-07 | Hüttlin, Herbert, Dr. h.c. | Rotary piston engine |
US7240645B2 (en) * | 2005-10-28 | 2007-07-10 | Reisser Heinz-Gustav A | Internal combustion engine |
DE102006046011B4 (en) * | 2006-09-28 | 2008-07-10 | Alois Tradler | Compressive engine, in particular internal combustion engine, with a ring structure |
EP2088283A1 (en) * | 2008-02-08 | 2009-08-12 | Lorenzo Merayo Gonzalez | Reciprocating rotary internal combustion engine |
ES2382265T3 (en) * | 2008-06-25 | 2012-06-06 | Griend Holding B.V. | Drive system with a rotating power transmission element |
US9032917B1 (en) * | 2011-04-21 | 2015-05-19 | Mark McNitt | Barrel cam rotating cylinder engine |
NL2007987C2 (en) * | 2011-12-16 | 2013-06-18 | Griend Holding B V | Rotary drive system having a cam follower with detachable wheel support. |
NL2007988C2 (en) * | 2011-12-16 | 2013-06-18 | Griend Holding B V | Cam follower with an angled axis of rotation. |
US10458324B2 (en) * | 2016-05-26 | 2019-10-29 | Daniel J Edwards | Rotary piston engine |
JP2019214236A (en) * | 2018-06-11 | 2019-12-19 | トヨタ自動車株式会社 | Hybrid vehicle |
JP2019214943A (en) * | 2018-06-11 | 2019-12-19 | トヨタ自動車株式会社 | Internal combustion engine |
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US1255664A (en) * | 1916-12-15 | 1918-02-05 | Alexander P Syger | Internal-combustion engine. |
US1613136A (en) * | 1925-06-11 | 1927-01-04 | Schuyler Schieffelin | Internal-combustion motor. |
US1736822A (en) * | 1927-06-23 | 1929-11-26 | Charles A Dreisbach | Piston mechanism for engines and pumps |
US2472647A (en) * | 1945-05-09 | 1949-06-07 | Covins Meyer | Double-acting reciprocating pump |
FR2079555A5 (en) * | 1970-02-05 | 1971-11-12 | Henry Max | |
GB1502171A (en) * | 1975-01-03 | 1978-02-22 | Direct Power Ltd | Opposed piston internal combustion engines |
JPS56173781U (en) * | 1980-05-26 | 1981-12-22 | ||
JPS5725181U (en) * | 1981-06-22 | 1982-02-09 | ||
DE3224482C2 (en) * | 1981-09-23 | 1991-11-21 | Prodromos Bekiaroglou | PISTON MACHINE |
US4543919A (en) * | 1981-12-28 | 1985-10-01 | Carson Douglas T | Engine |
JPS5929765U (en) * | 1982-08-18 | 1984-02-24 | 住友重機械工業株式会社 | Swash plate type hydraulic pump/motor rotation detection device |
FR2546232A1 (en) * | 1983-05-19 | 1984-11-23 | Cannebotin Robert | Four-stroke internal combustion engine with revolving cylinder block |
JPS6282236A (en) * | 1985-10-05 | 1987-04-15 | Shigeyoshi Karasawa | Opposed-piston type coaxial engine |
WO1993008372A1 (en) * | 1991-10-15 | 1993-04-29 | Mansour Almassi | Internal combustion rotary piston engine |
US5351657A (en) * | 1992-09-28 | 1994-10-04 | Buck Erik S | Modular power unit |
US5517952A (en) * | 1995-03-16 | 1996-05-21 | Wielenga; Thomas J. | Rotating shuttle engines with integral valving |
US5623894A (en) * | 1995-11-14 | 1997-04-29 | Caterpillar Inc. | Dual compression and dual expansion engine |
DE19639503C1 (en) * | 1996-09-26 | 1998-01-15 | Herbert Huettlin | Rotary piston engine |
US6662775B2 (en) * | 1999-03-23 | 2003-12-16 | Thomas Engine Company, Llc | Integral air compressor for boost air in barrel engine |
DE10001962B4 (en) | 2000-01-18 | 2004-07-22 | Hüttlin, Herbert, Dr.h.c. | Rotary piston engine |
-
2002
- 2002-04-19 PT PT02008814T patent/PT1355053E/en unknown
- 2002-04-19 AT AT02008814T patent/ATE260404T1/en not_active IP Right Cessation
- 2002-04-19 ES ES02008814T patent/ES2213721T3/en not_active Expired - Lifetime
- 2002-04-19 DE DE50200261T patent/DE50200261D1/en not_active Expired - Lifetime
- 2002-04-19 EP EP02008814A patent/EP1355053B1/en not_active Expired - Lifetime
- 2002-04-19 DK DK02008814T patent/DK1355053T3/en active
-
2003
- 2003-04-17 ES ES03722509T patent/ES2314198T3/en not_active Expired - Lifetime
- 2003-04-17 WO PCT/EP2003/004067 patent/WO2003089769A1/en active Application Filing
- 2003-04-17 DE DE50310676T patent/DE50310676D1/en not_active Expired - Lifetime
- 2003-04-17 JP JP2003586467A patent/JP4237068B2/en not_active Expired - Fee Related
- 2003-04-17 AT AT03722509T patent/ATE412113T1/en not_active IP Right Cessation
- 2003-04-17 EP EP03722509A patent/EP1499799B1/en not_active Expired - Lifetime
-
2004
- 2004-10-19 US US10/968,647 patent/US6986328B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO03089769A1 * |
Also Published As
Publication number | Publication date |
---|---|
JP4237068B2 (en) | 2009-03-11 |
PT1355053E (en) | 2004-07-30 |
DE50200261D1 (en) | 2004-04-01 |
ES2314198T3 (en) | 2009-03-16 |
WO2003089769A1 (en) | 2003-10-30 |
EP1499799B1 (en) | 2008-10-22 |
JP2005523400A (en) | 2005-08-04 |
ES2213721T3 (en) | 2004-09-01 |
EP1355053A1 (en) | 2003-10-22 |
ATE412113T1 (en) | 2008-11-15 |
US20050066917A1 (en) | 2005-03-31 |
ATE260404T1 (en) | 2004-03-15 |
DE50310676D1 (en) | 2008-12-04 |
EP1355053B1 (en) | 2004-02-25 |
US6986328B2 (en) | 2006-01-17 |
DK1355053T3 (en) | 2004-03-29 |
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