Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
  • F01C20/18—Control of, monitoring of, or safety arrangements for, machines or engines characterised by varying the volume of the working chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C9/00—Oscillating-piston machines or pumps
  • F04C9/005—Oscillating-piston machines or pumps the piston oscillating in the space, e.g. around a fixed point

Definitions

• the invention relates to a rotary piston machine, comprising a housing, in which a first and at least a second piston are arranged, which can rotate together in the housing about a housing-fixed axis of rotation, and when revolving about the axis of rotation about a perpendicular to the axis of rotation and through the housing center running piston-fixed pivot axis to each other opposite reciprocating pivotal movements between a first end position and a second end position, wherein the first and at least second piston defining a working chamber, wherein the first piston and / or the at least second piston has at least one running member, which during rotation of the first and / or second piston is guided along at least one control cam in order to generate the pivoting movements of the first and / or at least second piston.
• Such a reciprocating engine is known from the document WO 03/067033 Al.
• Oscillating piston engines and in particular a rotary piston engine according to the present invention can be used as internal combustion engines (internal combustion engines), as pumps or as compressors.
• An oscillating piston engine according to the present invention is preferably used as an internal combustion engine and described as such in the present specification.
• the individual working cycles of the intake, compression, ignition of the combustion mixture and the expending and expelling of the combusted combustion mixture are mediated by reciprocating pivotal movements of the individual pistons between two end positions.
• Enclosure solid as used herein means, for an axis that is to be understood as a geometric axis, that the spatial location of the axis relative to the housing does not change Accordingly, “piston-solid” means a fixed spatial relationship of a geometric axis to a piston.
• a working chamber is formed in each case, so that the known oscillating piston engine has two working chambers. Both working chambers, which are arranged diametrically opposite each other with respect to the housing center, increase and decrease in the same direction in the reciprocating pivotal movement of the piston.
• the pivotal movement of the pistons about the common pivot axis is due to the orbital motion of the pistons about the axis of rotation derives a control mechanism which surrounds two formed in the housing inner wall cams and corresponding running members on the housing inner wall facing sides of the piston.
• the stroke of the pivotal movement of the piston is fixed by the curve of the two cams invariable.
• the known oscillating piston engine thus has a constant displacement, wherein the displacement is the maximum volume or the sum of the maximum volumes of the working chambers.
• the invention is therefore based on the object to provide a rotary piston engine of the type mentioned with variable displacement.
• this object is achieved with respect to the initially mentioned oscillating piston engine in that the control cam is adjustable in position by means of an adjusting mechanism in order to adjust at least one of the first and second end positions of at least one of the first and second pistons.
• the oscillating piston engine according to the invention has a variable displacement, in which the control curve, which is already provided in the known oscillating piston engine, but there is stationary integrated into the housing inner wall, is now configured adjustable in position by means of an adjusting mechanism, whereby the first end position and / or the second end position at least one piston is adjustable.
• the inventive oscillating piston engine does not have the problem of having to install spark plugs or glow plugs or intake and exhaust valves in favor of the variability of the displacement at other locations of the oscillating piston engine, since the control curve even in the known oscillating piston engine already in space Position other than these aforementioned components is arranged, that is, an adjustability of the control cam does not collide with these components.
• the at least one of the first end position and the second end position is continuously adjustable by means of the adjusting mechanism.
• the displacement is continuously variable, whereby a stepless change in the displacement of the oscillating piston engine is made possible.
• the first and second end positions of the first and at least second pistons are adjustable by means of the adjusting mechanism.
• both the so-called top dead center position (TDC position) and the bottom dead center position (TDC position) are variable.
• TDC position the working chamber volume is minimum (ignition), and in the UT position maximum (end of discharge / initial suction).
• the UT position is adjusted in the sense of reducing the working stroke or displacement, it is advantageous to adjust the TDC position to the effect that with reduced working chamber volume (displacement) as high as possible compression in the TDC position is achieved which is achieved by the above-mentioned embodiment, in that both the TDC position and the TDC position are adjustable.
• two portions of the cam are mounted in opposite directions to each other about a housing-fixed pivot axis pivotally mounted on the housing.
• the displacement or the maximum Häcroiumen is adjusted by the control cam, which is formed from the two sections symmetrically to the housing-fixed pivot axis, is pivoted from a first position to a second position.
• the control cam is pivotable about a pivot axis
• a third and a fourth piston are arranged in the housing, which can rotate with the first and the second piston in the housing together about the axis of rotation and thereby perform mutually opposite pivotal movements between a third end position and a fourth end position, and that at least one of the third and the fourth end position is adjustable by means of the adjusting mechanism.
• the oscillating piston engine according to the invention like the known oscillating piston engine, has a total of four pistons and correspondingly two working chambers, wherein the maximum working chamber volume of both working chambers and thus the total stroke space of the oscillating piston engine is variable.
• the at least one of the third end position and the fourth end position is continuously adjustable by means of the adjusting mechanism.
• third and fourth end positions of the third and fourth pistons are adjustable.
• the third piston is diametrically opposite the first piston with respect to the piston-fixed pivot axis, and the third end position is synchronous and adjustable in the same direction to the first end position.
• control cam controls the pivotal movement of all four pistons by these are coupled together accordingly
• the third piston and / or the fourth piston has at least one running member
• the circulation of the third and / or fourth piston is guided along a second control cam to produce the pivoting movements of the third and / or fourth piston
• the second control cam is adjustable by means of the adjusting mechanism to the at least one of the third and fourth end position of the at least one of the third and fourth piston to adjust.
• control cams for the four pistons has the advantage of higher or complete symmetry of the entire oscillating piston engine, which positively influences the running properties of the oscillating piston engine. Accordingly, the second control cam is also adjustable in position, as is also the case for the control cam for the first and second pistons.
• the adjusting mechanism has a first cam element and a second cam element, wherein the first cam element and the second cam element are arranged like a scissor cross over one another in opposite directions to each other and have the first and the second control cam.
• the two control cams for the four pistons are realized by two cam elements, which are arranged like a scissor-like cross over each other in opposite directions to each other, this pivotability of the adjustment of the end positions of the pivoting movements of the piston is used.
• This design is structurally advantageous simple and also allows easy to implement adjustment of the cams, as will be described hereinafter.
• first cam portion of the first cam element with a second cam section of the second cam element, which together form the one of the control curves, is connected relative to this movable.
• a third cam section of the first cam element is movably connected to a fourth cam section of the second cam element, which together form the other of the cam tracks, relative to this.
• the relative mobility of the two mentioned cam sections permits mutually opposite pivoting of the two cam sections for adjusting the end positions of the third and fourth piston and at the same time ensures the formation of a contiguous second cam for the third and fourth piston.
• the relatively movable connection of the first cam section and the second cam section or the third cam section and the fourth cam section is preferably realized by a meshing connection, such as a toothing, these cam sections.
• the adjusting mechanism has at least one drive which is hydraulic, pneumatic and / or electrical.
• the at least one drive is hydraulic, and if a volume-variable chamber which can be acted on with hydraulic fluid is arranged on at least one side of the cam elements facing a housing inner wall of the housing.
• a hydraulic drive has the advantage that hydraulic fluid is substantially incompressible and can be applied with a hydraulic drive and very high forces in order to adjust the cam elements and thus the displacement of the oscillating piston engine safely even at high speeds of rotation of the piston.
• the drive for adjusting the cam elements must be active only in a direction of action, in the effective direction of the reduction of the displacement, while in the effective direction of the increase in the displacement acting on the centrifugal force acting on the piston force acting on the cam is exploited, which can pivot the cam elements to each other when the hydraulic pressure is reduced accordingly.
• the drive can be kept structurally very simple.
• the at least one running member and the at least one control cam are magnetically effective, such that a magnetic attraction acts between the at least one running member and the at least one control cam.
• the running member and the control cam consist of permanent magnetic active substance or have such, or running member and control cam or at least one of these is formed of a magnetizable material or has such of both, that is running member or cam, while doing so should be permanently magnetic, whereby advantageously an additional magnetic field generating element, that is, a magnetic field generator is not required.
• the at least one running member and the associated piston are magnetically effective, such that a magnetic attraction acts between the at least one running member and the associated piston.
• a stable contact between the running member and the associated piston is effected, whereby, for example, a positive connection of the running member can be dispensed with the associated piston.
• the magnetic attraction between the running member and the piston or between the running member and the associated control cam according to the aforementioned embodiment should be such that the free rotation of the running member, which is preferably designed as a ball is not canceled.
• Figure 1 is an illustration of a rotary piston engine according to the invention in a section along a plane parallel to the axis of rotation and perpendicular to the pivot axis of the piston, wherein the oscillating piston engine is shown in a first operating state of an adjusting mechanism for adjusting the control curves for the piston;
• Figure 2 is the same view as in Figure 1, but in a second operating position of the adjusting mechanism for adjusting the control cams for the piston.
• FIG 3 shows the oscillating piston engine in the same representation as in Figure 1, but without piston and without piston cage.
• Figure 5 shows the curve elements in Figure 4 in a sectional view and in an assembled arrangement
• Figure 6 is an illustration of the oscillating piston engine in Figure 1 in a rotated by about 45 ° about the axis of rotation representation of the housing, and wherein the pistons are pivoted from its BDC position in Figure 1 by about half the stroke in the direction of its TDC position.
• FIG. 7 shows the oscillating piston engine in FIG. 1 in a representation of the housing rotated by 90 ° with respect to FIG. 1, wherein the pistons are now pivoted into their TDC position;
• FIG. 8 shows a further illustration of the oscillating piston engine in FIG. 1, with piston cage, but without piston.
• the oscillating piston engine 10 is designed as an internal combustion engine in the present embodiment.
• the oscillating piston engine 10 has a housing 12, which is composed of two housing halves 14 and 16.
• the housing halves 14 and 16 each have a flange, wherein in the drawing, only the flange 18 of the housing half 14 is shown.
• a plurality of holes 20a to 20h provided for performing screws to screw the two housing halves 14 and 16 together via the flanges.
• the interior of the housing is constructed overall spherical or spherically symmetrical, wherein the ball center is shown in Figure 1 by the reference numeral 22.
• the pistons 24 to 30 can rotate in the housing 12 together about a housing-fixed axis of rotation 32 according to an arrow 34. During this circulating movement, the pistons 24 to 30 perform a pivoting movement about the rotational axis 32 superimposed on a pivot-fixed pivot axis 36 between two end positions, one end position in FIG. 1 (so-called UT position), and the other end position in FIG. so-called TDC position) is shown. In Figure 6, the pistons 24 to 30 are shown in an intermediate position between the UT position and the TDC position. Both the axis of rotation 32 and the pivot axis 36, which are to be understood as geometric axes, pass through the housing center 22 of the housing 12. The pivot axis 36 is always perpendicular to the axis of rotation 32, but runs around the latter, however, according to the orbital motion of the piston 24 to 30 also.
• pistons 24 to 30 are each two pistons with respect to the pivot axis 36 diametrically opposite, in each pivotal position of the piston 24 to 30, these being the pistons 24 and 30 on the one hand and the pistons 26 and 28 on the other.
• the pistons 24 to 30 are individually mounted in the housing 12, that is not rigidly connected in pairs, although this may also be considered within the meaning of the present invention.
• the piston 24 has an end face 38
• the piston 26 has an end face 40
• the piston 28 has an end face 42
• the piston 30 has an end face 44.
• the facing end surfaces 38 and 40 of the pistons 24 and 26 define a working chamber 46
• the facing end surfaces 42 and 44 of the pistons 28 and 30 define a working chamber 48.
• the working hammers 46 and 48 serve as combustion chambers for a Carnot cycle.
• the axis of rotation 32 passes through both working chambers 46 and 48, in each circulating and pivoting position of the pistons 24 and 40.
• the working chambers 46 and 48 are in particular arranged symmetrically to the axis of rotation 32, that is, the axis of rotation 32 passes through the working chambers 46 and 48 always in the middle.
• the piston-back chambers can serve as pre-compression chambers for pre-compression of fresh air, the precompressed air is then passed through suitable inlets into the respective working chamber 46 and 48, as described in WO 03/067033 Al.
• suitable inlets into the respective working chamber 46 and 48, as described in WO 03/067033 Al.
• the pistons 24 and 26 always remain to the left of a line A in FIG. 1 in their circulating and pivoting movement, and the pistons 28 and 30 always to the right of the line A.
• the oscillating-piston engine 10 further has a control mechanism in order to divert the pivoting movements of the pistons 24 to 30 out of the rotational movement of the pistons 24 to 30 about the axis of rotation 32.
• each piston 24 to 30 on a running member and indeed, the piston 24 has a running member 50, the piston 26, a running member 52, the piston 28, a running member 54 and the Piston 30, a running member 56.
• the running members 50 to 56 are balls which are each mounted in a ball socket formed on the rear face of each piston 24 to 30 facing away from the respective end face 38 to 44.
• the running members 50 to 56 in the form of balls are freely rotatably mounted in the ball sockets and may be held in the ball sockets by adhesion by means of a lubricating film, or the running members 50 to 56 may be held in a form-fitting manner in the ball sockets, to which then the ball sockets on the Extend diameter of the balls 50 to 56 out.
• the balls 50 to 56 are in any case freely rotatable about their center of the sphere in all directions.
• the running members 50 to 56 are not limited to the embodiment as balls and may in particular be designed as rollers, which are mounted rotatably about an axis on the respective associated piston rear sides.
• the running members 50 to 56 as best seen in Figure 3, associated with a total of two cams 58 and 60, in which the running members 50 to 56 run run.
• the running members 50 to 56 and the pistons 24 to 30 are not shown for ease of understanding, so that the control cams 58 and 60 can be seen exposed. It is understood that only one half of the cams 58 and 60 can be seen in Figure 3 according to the sectional view.
• the cams 58 and 60 rather extend over a full circumference of 360 ° in the housing.
• the running members 50 and 52 run during rotation of the pistons 24 and 26 about the axis of rotation 32 in the control cam 58, and the Laufor- gane 54 and 56 of the pistons 28 and 30 along the control cam 60th
• the contouring of the control cams 58 and 60 is selected such that, when the running members 50 to 56 travel along the control cams 58 and 60 during the orbital movement of the pistons 24 to 30 about the axis of rotation 32, the pivoting movements of the pistons 24 to 30 are diverted about the pivot axis 36 ,
• portions 70 and 72 (and correspondingly over a full circumference of the cams 58 and 60 seen over 30 ° corresponding in the sectional view not visible portions of the cams 58, 60) from the line A and thus from the aforementioned level on farthest apart and determine the TDC position of the pistons 24 to 30th
• the position of the sections 62 and 64 thus define a first end position of the pistons 24 and 26 shown in Figure 1, and the position of the section 70 determines the second end position of the pistons 24 and 26 shown in Figure 7.
• the position of the portions 66 and 68 determines the third end position of the pistons 28 and 30, which corresponds to the first end position of the pistons 24 and 26, and which is shown in Figure 1
• the position of the portion 72 determines the fourth end position of the pistons 28 and 30, which corresponds to the second end position of the pistons 24 and 26, and which is shown in Figure 7.
• the cams 50 and 60 are adjustable in position by means of an adjusting mechanism 74, so as to adjust the aforementioned first, second, third and fourth end positions of the piston, that is their TDC position and their UT position, and thus the maximum volumes of the working chambers 46 and 48 and thus to adjust the displacement of the oscillating piston engine 10.
• the adjusting mechanism comprises two cam members 76 and 78, on which the control cams 58 and 60 are formed.
• the cam elements 76 and 78 are arranged with respect to a housing-fixed pivot axis 79 like a scissors crosswise, as also apparent from Figure 3.
• the cam element 76 has a first cam section 80 and a second cam section 82
• the cam element 78 has a first cam section 84 and a second cam section 86.
• the cam sections 80 and 86 together form the control cam 58 and the cam sections 84 and 82 together the cam 60.
• the cam elements 76 and 78 do not run around the axis of rotation 32, that is, the pivot axis 79 is fixed to the housing in contrast to the pivot axis 36. In each case two piston positions about the axis of rotation 32, the pivot axes 36 and 79 coincide, one of which is shown in Figure 1.
• the cam members 76 and 78 are in the housing 12 of the oscillating piston engine 10 about the pivot axis 79 in opposite directions pivoted, as indicated by a double arrow 88 and a double arrow 90.
• the cam sections 80 and 86 and 84 and 82 are relatively movably connected by mating connections 92 and 94 in the sections 70 and 72 of the cams 58 and 60.
• the intermeshing connection is realized in the illustrated embodiment in that the cam portion 84 has an extension 96 which engages in a recess or recess 98 in the cam portion 82 and is movable in the direction of the extension 96.
• the connection 92 is designed accordingly, wherein in FIG. 4 b) an extension 100 can be seen, which belongs to the connection 92. It can also be seen in FIGS. 4 a) and b) that the control cam 60 and also the control cam 58, although not visible in FIG. 4, extend in the assembled state of the cam elements 58 and 60 over a full circumference of 360 °.
• the running members 50 to 56 run in the control cams 58 and 60, which are correspondingly formed in cross-section part-circular, with minimal friction.
• connections 92 and 94 each with an extension and a recess or recess may also be configured differently, for example, other types of Kämm or teeth may be provided, as long as the relative mobility between the cam sections 80 and 86 and 84 and 82nd and a continuous control curve for the running members 50 to 56 is given.
• this relative mobility also serves to adjust the second or fourth end position of the pistons 24 to 30, that is to say their TDC position.
• This adjustment of the TDC position occurs automatically when also the BDC position is changed, in the sense that the minimum volume of the working chambers 46 and 48 in the TDC position of the pistons 24 to 30 is also reduced when the UT position or the maximum volume of the working chambers 46 and 48 reduced becomes.
• a sufficient compression pressure is achieved when igniting the fuel-air mixture compressed in the working chambers 46 and 48.
• the adjusting mechanism 74 has a drive 102 for adjusting the cam elements 76 and 78 about the pivot axis 79.
• the drive 102 is a hydraulic drive.
• the cam elements 76 and 78 on a side of the cam elements 76 and 78 facing a housing inner wall 104 have a variable-volume chamber 106 and 108 that can be acted upon by hydraulic fluid.
• a valve device 110 and in the chamber 108, a valve device 112 is arranged, which serves the inlet and outlet of a hydraulic fluid in the chambers 106, 108 and from the chambers 106, 108.
• the cam members 58 and 60 By acting on the chambers 106 and 108, the cam members 58 and 60 are pivoted apart about the pivot axis 36, and as the hydraulic pressure in the chambers 106 and 108 decreases, the cam members 58 and 60 pivot as the pistons 24 to 30 rotate thereover acting centrifugal forces, which are transmitted via the control cams 58 and 60 on the cam members 76, 78, toward each other.
• the drive 102 for adjusting the displacement can be operated during operation of the oscillating piston engine 10
• a corresponding control device may be provided, which adjusts the cam elements 76 and 78 in dependence on the rotational speed of the pistons 24 to 30 about the axis of rotation 32.
• the displacement of the oscillating piston engine 10 is reduced, and vice versa.
• the pistons 24 to 30 are mounted in the housing 12 in a piston cage 114 which revolves around the axis of rotation 32 together with the pistons 24 to 30.
• the piston cage 114 is shown without the piston 24 to 30.
• the piston cage 114 is in the embodiment shown, and preferably a one-piece component, but instead of a one-piece construction, however, a multi-piece construction is conceivable.
• the piston cage 114 extends along the axis of rotation 32 over the entire length of the housing 12, wherein shaft extensions 116 and 118 of the piston cage 114 protrude from the housing 12.
• the piston cage 114 in each case has a main bearing section 120 or 122 adjoining the shaft extensions 116 and 118, via which the piston cage 114 in the housing 12 is mounted rotatably about the axis of rotation 32.
• the bearing sections 120 and 122 are connected at the housing center via a middle section 124, which extends along the pivot axis 36 having peg-like portion 126.
• the pistons 24 to 30 are mounted to the housing center 22 and to the pivot axis 36 out.
• the piston cage 114 has two bores 128 and 130 in which the pistons 24 to 30 are slidably mounted. More specifically, in the bore 128, the pistons 24 and 26 and in the bore 130, the pistons 28 and 30 slidably mounted.
• the holes 128 and 130 are circular in cross-section, and accordingly, the end surfaces 38 to 44 of the pistons 24 to 30 are also circular in shape.
• the pistons 24 to 30 are mounted in the bores 128 and 130 by means of piston rings for sealing the working chambers 46 and 48, as shown in Figure 1, in which, for example, for the piston 24 seals 132 and 134 is shown.
• the bores 128 and 130 define, together with the end surfaces 38 to 44 of the pistons 24 to 30, the working chambers 46 and 48.
• the pistons 24 to 30 In the bores 128 and 130 of the piston cage 114, the pistons 24 to 30 with respect to the rotation axis 32 rotatably connected to the piston cage 114, so that the pistons 24 to 30 rotate together with the piston cage 114 about the rotation axis 32, while the piston 24 to 30 are slidably movable in the bores 128 and 130 according to their thereby carried out pivotal movements about the pivot axis 36 to perform the individual cycles of the intake, compression, expansion and ejection.
• the pistons 24 to 30 are formed substantially arcuate, and the working hammers 46 and 48 have approximately the shape of a curved or curved cylinder, wherein the curvature is concentric with the pivot axis 36.
• piston cage 114 The arrangement of piston cage 114, the piston 24 to 30 together with the running members 50 to 56 forms the "inner engine” of the oscillating piston engine 10, that is to say this arrangement comprises all moving parts of the oscillating piston engine 10.
• race members 50-56 and the cams 58, 60 are magnetically effective such that a magnetic force of attraction acts between the race members 50-56 and the respective associated cam 58, 60.
• the cams 58 and 60 are preferably made of a "negative” -magnetizing or Magnetic ceramic or carbon fiber composite material manufactured.
• the pistons 24 to 30 are preferably made of a "positive" magnetizing or magnetized aluminum or magnesium alloy, and in this way there is also a magnetic attraction between the race members 50 to 56 and the associated pistons 24 to 30.
• the oscillating piston engine 10 also has inlet and outlet ports for admitting fuel-air mixture and for discharging the burnt mixture, which will not be described in more detail here. These inlet and outlet ports are assigned to the respective working chambers 46 and 48.
• each working chamber 46 and 48 is associated with an ignition or glow plug 148 and 150, which are arranged on the rotation axis 32 and rotate together with the piston cage 114 about the rotation axis 32.
• ignition or glow plug 148 and 150 which are arranged on the rotation axis 32 and rotate together with the piston cage 114 about the rotation axis 32. The operation of the oscillating-piston engine 10 will be described below.
• the oscillating piston engine 10 is shown in an operating position in which the pistons 24 to 30 are in their UT position.
• an operating position of the oscillating piston engine 10 is shown in Figure 1, in which the cam members 76 and 78 are maximally pivoted toward each other. This means that the displacement of the oscillating piston engine 10, that is, the maximum volumes of Ulka ⁇ unern 46 and 48, are at a maximum.
• FIG. 2 shows an operating state of the oscillating-piston engine 10 in which the pistons 24 to 30 are also in their BDC position, in which the working chambers 46 and 48 are maximally open, however, the cam elements 76 are in the operating position shown there and 78 pivoted apart by about 20 °, so that the maximum volumes of the working chambers 46 and 48 in the UT position of the pistons 24 to 30 are smaller than in Figure 1, that is, the displacement of the oscillating piston engine 10 is smaller in Figure 2 than in the operating state in Figure 1.
• the pivoting position of the cam elements 76 and 78 shown in FIG. 2 is thereby also the maximum possible pivoting position of the cam elements 76 and 78 in which the cam elements 76 and 78 bear in the corresponding recess in the housing inner wall 104 at the end.
• FIG. 6 shows an operating state of the oscillating piston engine 10 in which the pistons 24 to 30 have made approximately a 45 ° rotation about the axis of rotation 32. wherein the pistons 24 to 30 have pivoted toward each other by about half, wherein this pivoting movement, as explained above, from the orbital motion of the pistons 24 to 30 about the axis of rotation 32 by the leadership of the running members 50 and 56 on the correspondingly contoured cam 56th or 58 was derived.
• control cams 58 and 60 can be pivoted about the pivot axis 79 both in the idle state and during the running of the oscillating piston engine 10 in order to adjust the displacement of the oscillating piston engine 10, as already described above.
• the adjustment of the displacement of the oscillating piston engine 10 can in particular be speed dependent, and that is rather reduced to higher rotational speeds of the displacement of the oscillating piston engine, and rather increased toward lower speeds, which is controlled or regulated by corresponding pressurization of the chambers 106 and 108 with hydraulic fluid can be.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Transmission Devices (AREA)
• Valve Device For Special Equipments (AREA)
• Reciprocating Pumps (AREA)

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• 2005
  • 2005-05-17 DE DE200510023721 patent/DE102005023721B3/de not_active Expired - Fee Related
  • 2005-07-22 CN CNB2005100874459A patent/CN100480489C/zh not_active Expired - Fee Related
• 2006
  • 2006-05-04 EP EP06742795A patent/EP1882082A1/de not_active Withdrawn
  • 2006-05-04 WO PCT/EP2006/004173 patent/WO2006122658A1/de not_active Application Discontinuation

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