EP0644981B1 - Machine a piston - Google Patents

Machine a piston Download PDF

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Publication number
EP0644981B1
EP0644981B1 EP93912894A EP93912894A EP0644981B1 EP 0644981 B1 EP0644981 B1 EP 0644981B1 EP 93912894 A EP93912894 A EP 93912894A EP 93912894 A EP93912894 A EP 93912894A EP 0644981 B1 EP0644981 B1 EP 0644981B1
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EP
European Patent Office
Prior art keywords
piston
chamber
running
sealing
machine according
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EP93912894A
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German (de)
English (en)
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EP0644981A1 (fr
Inventor
Manfred Max Rapp
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Individual
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Individual
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    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F01C1/06—Rotary-piston machines or engines of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents of other than internal-axis type

Definitions

  • the invention relates to a piston machine of the type mentioned in the preamble of claim 1.
  • a disadvantage of this known construction is the very large ratio of chamber surface to chamber volume which is sought because of its use as a steam engine and which has an extremely unfavorable thermodynamic effect for use as an internal combustion engine or compressor.
  • a disadvantage of this design is also the course of the force acting on the piston with different Crank angles. Since the piston surface changes only slightly at different crank angles, the force acting on the piston remains almost constant. This is disadvantageous both when used as an internal combustion engine and particularly when used as a compressor, since the piston load becomes extremely high.
  • Another disadvantage is the angle at which the resulting force acting on the piston acts on the crankshaft. Angles in the range of 90 °, which achieve high torque with low bearing loads, would be favorable.
  • a generic piston machine is known from DE-A-1 551 119.
  • the piston machine can be used as a suction pump, for example a vacuum pump, compressor or as an expansion machine.
  • a suction pump for example a vacuum pump, compressor or as an expansion machine.
  • an expansion machine it can be used with external combustion, for example as a steam engine, or with internal combustion as a gasoline or diesel engine.
  • crank pins in the "heads", ie concentrically within the sealing elements of the piston.
  • this extremely limits the design options. Formations other than the four-chamber training shown cannot be constructed or can only be constructed with considerable problems.
  • the position of the crank pins in the "heads” forces the crankshafts to be arranged in the chambers. This leads to considerable sealing problems.
  • the crankshafts must be provided in the parallel walls of the machine housing as eccentric disks that are overrun by the piston.
  • the object of the present invention is to provide a piston machine of the generic type which, with improved design options, in particular enables the provision of more effective sealing elements and in which thermal loads on sealing and bearing points are avoided.
  • the bearing journals are arranged in the piston in a central area in which there is a lot of space available and the bearings of the crank journals can be arranged in a largely free construction, also with regard to the number of crank journals - and thus the crankshafts.
  • the adjacent part of the piston remains free of crankshafts, in particular in the region of the other end of the running surface of the piston.
  • the piston can be designed regardless of the need to attach crank caps.
  • the running surface can end here in any way and the piston part delimiting the running surface can be made very narrow here, which benefits the construction of the running space receiving the piston.
  • a sealing element at this end of the tread which can be designed independently of a crank pin bearing to be attached here according to the prior art.
  • the piston is free of crankpin bearings at both ends of the tread in the manner according to the invention, so that at both The sealing elements can be freely designed at the ends of the running surface and the piston can be constructed very narrow.
  • the displacement of the crankshafts in relation to the known construction of the generic type from the area of the chambers also results from the displacement of the crank pins in the piston in order to enable their storage in the piston at a point remote from the ends of the running surfaces. This displacement of the crankshafts out of the chambers creates the advantage that the crankshafts are no longer overrun by the piston as in the known construction.
  • crank pins and crankshafts creates the possibility of a considerable variety of designs with a largely arbitrary and largely arbitrary number of chambers compared to the generic prior art, which can only be used sensibly for a four-chamber arrangement in single and double arrangement.
  • the features of claim 3 are advantageously provided.
  • the possible variations in the surfaces of the sealing elements are surprisingly diverse.
  • the surface of a sealing element can be very small, so that the sealing element always lies on its mating surface in almost the same line.
  • the surfaces can be enlarged. Then there is an improved barrel wear because it is distributed over the surface of the sealing element. Since the counter surface increases correspondingly with an enlarged surface of the sealing element, a larger chamber also results.
  • the surfaces of the sealing elements can be Claim 2 be circular in cross section, but other curved surface configurations, in particular elliptical shapes, are also possible.
  • the counter-running surfaces of such a sealing element that can be moved in parallel rotation then deviate from the circular shape in accordance with the eccentricity of the surface of the sealing element.
  • the mating surface is also elliptical.
  • various chamber designs are possible which can be adapted to the individual purpose, for example as an expansion chamber, as a pump chamber or as a chamber of a low-pressure or high-pressure compressor.
  • the sealing elements delimiting a chamber on both sides can be of different sizes or of different shapes.
  • a chamber can be designed such that it is delimited on one side by a very small sealing strip with a circular cross-sectional surface, the counter surface of which is circular in cross section with a radius that is only slightly larger than the crank radius.
  • the sealing strip on the other side of the chamber can be elliptical with very large dimensions and runs on an elliptical counter-running surface which is only slightly larger than the surface of the sealing element. In this way, a large number of very different chambers can be formed, which are adapted to different purposes.
  • the features of claim 4 are advantageously provided.
  • the sealing elements can lie with their plane of symmetry parallel to the plane of symmetry of the adjacent tread, but can also deviate from this angular position. If, as stated in claim 4, they are arranged tilted outwards, this results in an extension of the counter surface and thus a larger maximum chamber volume or a larger compression ratio.
  • the features of claim 5 are also advantageously provided.
  • the chambers can be sealed by means of sealing elements which are designed as rigid integral parts of the piston or the motor housing. Then the sealing elements can only take into account the manufacturing tolerances at a gap are led to their counter surface, which results in leaks that limit, for example, the maximum compression pressure of a compression chamber. For low pressure compressors this can be enough.
  • the sealing elements as spring-loaded sealing strips, as is generally known from engine construction, higher sealing values and thus higher compression pressures can be achieved.
  • the parallel rotation of the piston results in the possibility of simultaneously engaging a running surface provided on the piston with two adjacent running surfaces of the peripheral wall.
  • chambers are formed simultaneously with both running surfaces of the peripheral wall, one of which, depending on the running direction, works as a compression chamber and the other as an expansion chamber.
  • the separation between the compression chamber and the expansion chamber provided in such an internal combustion engine results in cooling advantages with better partial efficiencies of the engine. After the expansion has ended, the combustion chamber opens and the hot gases are immediately blown into the low-pressure outlet with fresh air.
  • the expansion chamber can also be used as a suction pump, eg as a vacuum pump.
  • a piston machine is created in which the compression chamber supplies compressed air, while the expansion chamber works as a vacuum pump. Such a piston machine can be advantageous in certain manufacturing processes in which compressed air and vacuum are required at the same time.
  • the features of claim 11 are also advantageously provided.
  • the power in a manner known, for example, from Wankel engines, the power can be increased in accordance with the number of parallel disks by designing the machine with multiple disks.
  • the degree of uniformity of the machine can be improved, and possibilities can be created to allow compression chambers of one disk to be acted upon directly, without intermediate pressure storage, when the training takes place as an internal combustion engine using the angular offset between the disks.
  • valves are always required in the high-pressure channels. These can advantageously be designed as valves controlled synchronously with the piston run, for example in the form of globe valves or in the form of rotary valves.
  • valves of compression chambers can also be designed as one-way valves, for example as spring-loaded flap valves, their spring load specifying the desired maximum pressure.
  • a piston of this type is cooled as it moves by contact with the gas in the barrel.
  • the piston can be provided with ribs or with openings flushed with gas.
  • FIG. 16 the basic construction of the illustrated embodiment is first explained. It is an internal combustion engine with a housing 1, which is shown in one piece for the sake of simplification of the drawing, but which in a practical embodiment has to be made in several pieces for assembly purposes, for example in a disk-like manner.
  • Two parallel, identical crankshafts 2, 2 ' are mounted in the housing, of which the crankshaft 2' is visible in FIG. 3.
  • the crankshafts penetrate two running spaces 3, 3 'arranged one behind the other in the manner of disks, of which the running space 3 can be seen open in the section of FIG. 2.
  • crankshafts 2, 2 ' have cranks 4 in each running space, on the crank pin 5 of which a piston 6, 6' is mounted in each of the running spaces 3, 3 '.
  • crankshafts 2, 2 ' are identical in terms of their cranks for the piston 6 shown, in particular with the same crank radius and also with an identical angular position.
  • the crankshafts therefore rotate in synchronism with the angle.
  • corresponding gear sets 7, 7 ' are provided on one or both crankshaft ends. From Fig. 1 it can be seen that the crankshaft 2 at its end lying on the gear set 7 passes through the end wall of the housing 1 and carries there, for example, a drive pulley 8 provided.
  • the gear set 7 ' drives an output shaft 8'.
  • FIGS. 2 to 9 show that by the bearing of the piston 6 on the crank pin 5 of the two angularly synchronized crankshafts 2, 2 'the piston executes an orbit which, as shown in several successive orbital phases in FIGS. 2 to 9, can be called parallel rotation.
  • the piston is parallel to its other positions in all angular positions of the crankshafts.
  • Each point of the piston rotates with the radius of the cranks 4, but in each case around its own center. Therefore, more than two crankshafts can also be used to support a piston, as shown in FIG. 13 in an embodiment variant of a piston which runs on the crank pin of three crankshafts coupled in an angularly synchronous manner.
  • the construction is first further explained with reference to FIG. 2.
  • the running space 3 is delimited by parallel surfaces 9, which are perpendicular to the crankshafts 2, 2 ', and by a peripheral wall 10, which is perpendicular to the parallel walls 9 everywhere.
  • a tread 11 is provided, which is designed in the form of a half cylinder in the section of FIG. 2, that is to say semicircular.
  • a sealing strip 12 is arranged as a sealing element, which describes a circle during the parallel rotation of the piston 6, as shown in FIGS. 2 to 9, on the upper half of which it slides in contact with the running surface 11.
  • a sealing strip 13 is arranged on the peripheral wall 10 as a further sealing element.
  • a tread 14 in the piston 6 which also has a semi-cylindrical shape with the same radius of the tread 11.
  • a chamber is formed which is enclosed on all sides and is delimited by the parallel surfaces 9 and the running surfaces 11 and 14.
  • This chamber is sealed by the sealing strips 12 and 13 and additionally by a circular provided in the side surfaces of the piston 6 arranged side sealing strips 15, which seal against the parallel surfaces 9.
  • the chamber 11.14 In Fig. 7 the chamber 11.14 is open. It closes in Fig. 8 with maximum volume, which is calculated from the distance between the parallel surfaces 9 and essentially a circular cross section with the circumferential radius of the crank pin 5. If you follow Figs. 9, 2, 3 and 4, you can see that the chamber 11.14 is reduced to substantially zero and then, as shown in FIG. 5, opens again in order to close again in FIG. 8.
  • the direction of rotation of the crankshafts shown clockwise is a compression chamber.
  • the open position (FIGS. 5 to 7) it is connected to the running space 3 and can absorb gas of low pressure, which flows in, for example, through a low-pressure inlet channel 16 in the housing 1. 8, 9, 2 and 3, the gas in the chamber 11.14 is compressed and finally expelled through a high-pressure outlet channel 17, the opening of which in the parallel wall is shown in FIGS. 2 to 9, at a greatly increased pressure.
  • a further running surface 18 is arranged laterally in addition to the previously described running surface 11 in the peripheral wall 10, which is designed mirror-symmetrically to the sealing strip 13 and identical to the running surface 11.
  • the left and right end points of the treads 11 and 18 and the common middle end point lie on a line.
  • a high-pressure inlet channel 20 also opens into the chamber 18.14, which, in contrast to the high-pressure outlet channel 17, is not provided for the outlet of compressed gas, but rather for the inlet of compressed gas, which is relaxed during the working cycle of the chamber 18.14.
  • Air flowing in through the low-pressure inlet duct 16 is enclosed in the chamber 11.14, compressed and fed through the high-pressure outlet duct 17 to a pressure accumulator (not shown). From this, the compressed air is fed through the high-pressure inlet duct 20 to the chamber 18.14 at a point in time of small chamber volume or through the high-pressure inlet duct 20 'to the chamber 18'.14' and brought to an explosion there.
  • fuel e.g. Petrol or diesel fuel supplied with injectors, not shown, e.g. in the form of an intake manifold injection into the high-pressure inlet duct or in the form of a direct injection directly into the chamber.
  • a spark plug or injection nozzle can be arranged in the stepped bore 21 shown. After expansion and opening of the chamber 18.14, the burned gas can escape from a low-pressure outlet channel 22 opposite the low-pressure inlet channel 16.
  • the expansion chamber 18.14 and the compression chamber 11'.14 ' can be omitted, for example in a simpler embodiment. There is then still a compression chamber 11.14 and an expansion chamber 18'.14 'which can work together in the manner described above.
  • the internal combustion engine can also work on the diesel principle.
  • An injection nozzle is then to be provided in the stepped bore 21, which injects compressed air supplied to the chamber 18.14 at the time when the chamber volume is small. Since very large volume changes can be achieved with the chambers 11.14 and 18.14 shown, the chamber 11.14 can be used to bring the air to the required pressure of 30-60 bar, for example.
  • the high-pressure ducts 17 and 20 are arranged in the immediate vicinity of the sealing strip 13 provided between the chambers 11.14 and 18.14 and provided on the peripheral wall 10, that is to say in the region of the minimum chamber volume.
  • the low-pressure channels 16 and 22, which serve for the inlet and outlet, are opposite each other in the area in which the associated chambers 11.14 and 18.14 are to receive or release gas.
  • the rotation of the piston 6 in the clockwise direction favors flushing from the low-pressure inlet channel 16 to the low-pressure outlet channel 22, so that mixing of fresh and exhaust gases is avoided.
  • the high-pressure channels 17 and 20 must have valves which, in the case of the compression chamber 11.14, must be opened at maximum compression for the outlet of the high-pressure gas and, in the case of the expansion chamber 18.14, must close after the high-pressure gas has been admitted.
  • valves controlled in synchronization with the rotation of the crankshafts 2, 2 ' can be provided.
  • FIG. 1 shows rotary valves 23, 23 'which are driven by the respective gear set 7, 7' synchronously with the crankshafts and which control the high-pressure channels, which cannot be seen in the section of FIG. 1.
  • one-way valves which are permeable in the gas direction can also be provided for this purpose, which are designed, for example, as spring-loaded flap valves.
  • sealing strips 12, 13 and 19 will be described with reference to FIG. 3 and in particular FIG. 16. They are essentially identical and are described in detail using the example of the sealing strip 13.
  • the sealing strip 13 has a surface 24 which is circular in cross section, the center 25 of which is on a radius to the center 26 of the running surface 11 which corresponds to the radius of the crank pins 5 of the crankshafts 2, 2 '.
  • the radius of the surface 24 of the sealing strip 13, based on its center point 25, must be added to the circumferential radius of the crank pin 5 to give the radius of the tread 11, based on its center point 26.
  • the radius of the running surface 14 of the piston is identical to that of the running surface 11. The same applies to the already described running surface 18.
  • the sealing strips 12, 13 and 19, which are essentially identical to one another, are, as explained in FIGS. 3 and 16 using the example of the sealing strip 13, displaceably mounted with a slide 27 in a sliding guide and form a piston 28 at their end opposite the surface 14 that slides in a cylinder with spaces 29 and 30.
  • springs are applied to the piston 28 from above and below (indicated schematically in FIG. 16 with wavy lines) which hold the sealing strip in a defined central position.
  • the space 30 located outside the piston 28 can be connected to one of the adjacent chambers by a bore, not shown, in order to be acted upon by the latter with high pressure gas, which presses the sealing strip against its running surface with additional prestress for the sealing contact.
  • a bore 100 is shown in dashed lines in FIG. 17. It serves to pressurize the sealing strip 120.
  • FIGS. 1 to 9 thus forms an internal combustion engine which has two compression chambers and two expansion chambers per disc, that is to say a total of four compression and four expansion chambers.
  • 1 shows, the cranks 4 of the crankshafts in the running spaces 3 and 3 'are angularly offset from one another.
  • the pistons 6, 6 'thus run with a phase shift. This makes it possible, for example, for the compression chambers of one disk to release high-pressure gas at a point in time when the expansion chambers of the other disk require high-pressure gas.
  • an internal combustion engine can also have more than the two disks shown.
  • a double-chamber arrangement with chambers 11.14 and 18.14 can also be provided in a pane, for example.
  • a corresponding piston with only one running surface 14 is shown in FIG. 10.
  • only one counter running surface for example the running surface 11, can be provided in the peripheral wall 10.
  • a pure compressor that has to be driven externally and that has only one compression chamber per disc.
  • such a pure compressor per disk can also have two compression chambers (but no expansion chambers).
  • only expansion chambers can be provided in one pane and only compression chambers in another pane.
  • the invention offers considerable scope for variation.
  • a self-propelled compressor can be designed such that, for example, in the two disks shown in FIG. 1, only one disk has an expansion chamber which drives the compressor according to the internal combustion principle, but each disk has two compression chambers. As calculations show, one expansion chamber is sufficient to drive four compression chambers.
  • More than two chamber arrangements can also be provided on the circumference of a running space, each of which can consist of either an expansion chamber or a compression chamber or an expansion and a compression chamber. This is shown by the illustrations in FIGS. 10 to 15.
  • FIG. 10 shows a piston with only one running surface 14, with which a single or double chamber arrangement can be provided.
  • 13 shows a piston with three running surfaces for three such chamber arrangements.
  • FIG. 11 shows the piston described in FIGS. 1 to 9 for two such chamber arrangements.
  • FIG. 12 shows a piston with two running surfaces, which, however, when compared with FIG. 11, are arranged obliquely to the connecting line of the crankshafts.
  • 14 and 15 show that larger numbers of chamber arrangements are easily possible. The geometric conditions only need to be taken into account in terms of space requirements. The parallel rotational movement of the piston enables a largely arbitrary number of chamber arrangements per piston.
  • the center of the running surface is marked in the running surface 14 of the piston shown as an intersection of the tangent T created at this point and the perpendicular S to it.
  • the two lines T and S form the four quadrants labeled with the Roman numerals I, II, III and IV.
  • the two crank pins 5 in the piston are located on the other side of the line T, ie in the central part of the piston, from the chamber which can be formed by the running surface 14.
  • the piston can be made very narrow and with spring-loaded sealing strips with small sealing strip radii. In the construction of the piston in the region of the two ends of the running surface 14, it is not necessary to take account of any crank pin bearings to be arranged here.
  • FIGS. 11 to 15 clearly show the same geometric relationships for each of the running surfaces 14 present in these with respect to the arrangement of the bearings of the crank pins 5. These geometric relationships also apply to the other piston constructions shown in FIGS. 1 to 18.
  • the chamber arrangement with the chambers 11.14 and 18.14 can be arranged inclined at an angle to the connecting line of the crankshafts 2, 2 '.
  • the connecting line of the sealing strips 12 and 19 of the piston 6 is then at an angle to the connecting line of the crankshafts 2, 2 '.
  • the running surfaces 11 and 14 are to be arranged tilted at an angle such that the connecting line of their end points is parallel to the connecting line of the sealing strips 12 and 19 of the piston 6.
  • FIG. 17 shows an embodiment variant whose differences from the construction described above can be seen in comparison with FIG. 16 are.
  • the same parts are provided with the same reference numerals.
  • the sealing strip 120 seated at the left end of the running surface 14 of the piston 6 is greatly enlarged, as the comparison with the sealing strip 12 of the construction according to FIG. 16 shows.
  • it is doubled in its radius, that is to say in its overall dimensions.
  • the left stationary tread 110 is enlarged compared to the tread 11 shown in dashed lines, which corresponds to that of the construction of FIG. 16.
  • the center point of the original tread 11 was at 26.
  • the center point of the new tread 110 was at 260.
  • the magnification to the left is clearly asymmetrical, as the lateral shift of the center points 26 and 260 shows.
  • the newly formed enlarged chamber 110.14 is distinguished from the original construction according to FIG. 16 by a maximum volume increased by 25% in the exemplary embodiment and a correspondingly increased maximum compression ratio. Otherwise the mode of operation of the overall construction remains unchanged.
  • the sequence in the individual phases according to FIGS. 2 to 9 is unchanged.
  • the enlarged sealing strip 120 can also be designed differently from the sealing strips 13 and 19, for example with other dimensions even bigger or a little smaller. The size of the new tread 110 must be adjusted accordingly.
  • Fig. 18 shows a variant of the construction of Fig. 17 in the same representation. Matching parts are provided with the same reference numerals. The reference numbers of modified parts have also been retained, but with a comma.
  • the change relates to the sealing strip 120 'located at the left end of the chamber 110'.14, that is to say at the left end of the running surface 14 of the piston 6.
  • the enlarged sealing strip 120 of FIG. 17 is viewed again, it can be seen that, like the sealing strip 19 located at the right end of the running surface 14 of the piston, its plane of symmetry lies exactly parallel to the plane of symmetry of the adjacent running surface 14. As shown in FIG. 17, this results in a maximum circumferential angle of the counter surface 110 of the chamber of approximately 180 °. Even in the case of the smaller sealing strip 12 shown in dashed lines, the corresponding smaller counter-running surface 11 can only be traveled over about 180 °. This limits the maximum chamber size shown in FIG. 17.
  • Fig. 18 it is shown that there the enlarged sealing strip 120 'with its dash-dotted plane of symmetry under one Oblique angle ⁇ is arranged opposite the plane of symmetry of the tread 14 adjacent to it, which is also shown with a dash-dotted line.
  • the comparison with FIG. 17 shows that the circular sector surface of the sealing strip 120 'is formed over a somewhat larger angular range. This results in the possibility of guiding the sealing strip 120 'into an abutment on the correspondingly lengthened counter-running surface 110' over an angular range likewise increased by a beyond 180 °.
  • the maximum chamber volume as the comparison of FIGS. 17 and 18 shows, can be increased considerably again without changing the crankshafts.
  • the left chamber 110'.14 can again be greatly enlarged, while the right chamber 18.14 is kept small, since the sealing strip 19 is arranged at 90 ° and also has a much smaller surface area of its circular sector .
  • the smaller sealing strip 12 ' is also shown (dashed) within the enlarged sealing strip 120' at the same angle.
  • the other angular arrangement results in a correspondingly enlarged counter-running surface 11 ′ with a corresponding enlargement of the chamber.
  • the tightness of a sealing strip can be improved, for example in the sealing strip 120 of FIG. 17, if the lifting is prevented.
  • Lifting usually occurs when the sealing strip vibrates or rattles in its resilient mounting in the event of smooth running malfunctions. Such vibration movements can be prevented by shock absorption.
  • shock-absorbing devices can be provided in the resilient bearing seat of a sealing strip, for. B. hydraulic damping devices in the manner of conventional hydraulic piston shock absorbers.
  • heat can be dissipated, for example by Water cooling channels in the housing near the treads provided there and by liquid cooling of the piston, which can be done, for example, with oil channels in the piston, which are connected to the two crankshafts via the bearings.
  • air cooling in the housing is also possible, for example by means of external ribbing.
  • the piston can also be adequately cooled with gas cooling alone.
  • the piston 6 shown there is seen it can be seen that it rotates continuously in the running space and is in intensive gas contact with the constantly flowing cool fresh gas. If the piston is heavily ribbed outside its running surfaces 14 and 14 ', for example in its surface, sufficient gas cooling of the piston can be brought about.
  • the piston can also be provided with openings, for example (see FIG. 2) an opening that runs approximately in the imaginary line between the openings 16 and 22 of the housing 1 in the upper part of the piston 6 between its tread 14 and the bearings on the crank pin 5 passes and which is flowed through by air when the piston rotates.
  • the sealing elements that delimit a chamber are always shown to be significantly smaller than the crank radius of the piston.
  • the sealing strips 13 and 19 have a surface radius which is approximately a quarter of the crank radius.
  • the larger sealing strip 120 has a surface radius that is approximately half the size of the crank radius.
  • the sealing strips are always spring-loaded, as is also shown in FIG. 17.
  • the sealing elements can be designed with significantly larger surfaces compared to the crank radius, and they can also be designed as rigid parts of the piston or the housing wall without suspension. This is explained in an example in FIG. 19.
  • FIG. 19 shows a cross-section of the housing 501, in which a piston 506 for parallel rotation is mounted on crank pins 505 of three crankshafts.
  • a very large running surface 530 is formed on the peripheral wall of the running space shown, which has the shape of a circular section in cross section and on one end of which a sealing strip 531 of small cross section is arranged on the housing side.
  • a running surface 532 serving as a counter surface for the sealing strip 531 is provided on the piston 506. This extends from the corner at the location of the sealing strip 531 to the circumferential point marked with a line 533, that is to say over almost 180 °. It connects a part of the piston 506 which is circular in cross section, namely between the marking line 533 and the corner 534.
  • This surface part of the piston which is circular in cross section forms the sealing element 535 which runs on the running surface 530 when the piston 506 rotates in parallel. and that with parallel rotation of the piston 506 clockwise between the start of the tread 530 at the low pressure inlet channel 516 to the end of the tread 530 at the sealing strip 531.
  • a working chamber 530.532 is hereby formed, which is delimited by the running surfaces 530 and 532 and the sealing elements 531 and 535.
  • the sealing element 535 runs on the running surface 530 while forming a chamber, while the sealing strip 531 runs on the running surface 532.
  • the same chamber formation conditions are present as are described in the previous embodiments.
  • only the ratio of the surfaces of the sealing elements is chosen to be very large, and the sealing element 535 has a surface radius that is very much larger than the crank radius.
  • the sealing element 535 is not cushioned in this embodiment. It can only seal against its counter surface 530 with a gap required due to play.
  • the chamber 530.532 can therefore essentially only be used as a low-pressure compression chamber, but has a very large chamber volume and can therefore be used to compress large amounts of air to low pressures.
  • the compressed gas can be obtained through an outlet channel 536 with valve 537.
  • the chamber 530.532 is combined with the two chambers 110.14 and 18.14 of the embodiment of FIG. 18.
  • the tread 14 is provided on the piston 506, on both ends of which the sealing lines 19 and 120 'are seated.
  • the housing 501 forms the running surfaces 110 ′ and 18 here. Details of these two chambers have been omitted for the sake of simplifying the drawing.
  • the chamber 530.532 can be used as a low-pressure compression chamber, while the chamber pair 110'.14, 18.14 forms an internal combustion engine in the manner described above, which drives the compressor.
  • the low-pressure compression chamber 530.532 can also serve as a pre-compression chamber, the gas pre-compressed in it being suitably supplied to the compression chamber 110'.14 for post-compression.
  • the result would be a two-stage compressor that can reach very high outlet pressures.
  • the expansion chamber 18.14 could be omitted.
  • the chamber 18.14 forms the expansion chamber in the clockwise direction of movement of the piston. After opening this chamber, in the position of the piston 506 shown in FIG. 19, the burned exhaust gas is to leave the machine through the low-pressure outlet channel 522, if possible without mixing with the fresh gas of the low-pressure inlet channel 516.
  • a running surface 540 is formed on the separating web between the low-pressure channels 516 and 522 and on one Nose 541 of the piston 506 a sealing element 542, which runs sealingly on the tread 540 during the critical crank angle range in which the expansion chamber 18.14 opens and creates a gas seal between the low-pressure channels 522 and 516, so that exhaust gas is mixed in this critical time range and fresh gas is avoided.
  • the sealing elements or sealing strips are always designed with surfaces which are circular in cross section.
  • the running surfaces are surfaces that are circular in cross-section and are coated by these sealing elements during the parallel rotation.
  • the compressor has a housing 601, in which a piston 606 rotates clockwise on three crank pins 605.
  • the revolving curves of the crank centers are shown with circles.
  • a sealing element 635 with a cross-sectional elliptical surface, which extends from the marking line 633 to the marking line 634 enough. It connects to a circular cross-sectional tread 632 at 633.
  • a sealing strip 631 with a small circular cross section is arranged on the peripheral wall of the housing 601 and runs on the running surface 632 of the piston.
  • a running surface 630 is then formed on the sealing strip 631, which extends from the sealing strip 631 to a low-pressure inlet channel 616.
  • the sealing element 635 which is designed as an elliptical section, runs from the angular position shown in FIG. 20, in which it comes into first contact with the running surface, to the contact with the sealing strip 631 and forms the sealing boundary of the chamber 630,632. At its other end, this chamber is sealed by the sealing strip 631 in contact with the tread 632.
  • High pressure gas from this chamber is discharged in the direction of the arrow through an outlet duct 636 with valve 637.
  • a second chamber 630'.632 ' is provided symmetrically on the upper side of the piston 606 and operates alternately with the chamber 630.632 described first when the piston 606 rotates.
  • the sealing elements 535 and 635 which have very large dimensions in relation to the crank radius, form a considerable peripheral part of the piston 506 and 606, respectively.
  • These sealing elements 535, 635 are therefore surfaces which are rigidly connected to the piston trained and can only seal with a gap seal against their counter surface.
  • crank pins in the piston is also explained in FIGS. 19 and 20, as shown in FIG. 10.
  • crank pins 505 of the piston lie outside the quadrants I and IV. In the case of the tread 532, this only applies to the quadrant I. No crank pin is mounted on this end of the tread 532 opposite the sealing element 532. It can therefore be constructed freely; in the exemplary embodiment shown, the running surface 532 merges at a right angle into an adjacent surface. Crank pins are not provided in this area.
  • FIG. 20 shows the quadrant arrangement for the tread 632 ', which also applies in a corresponding manner to the tread 632, which is arranged completely symmetrically. It can be seen that a crank pin 605 can be arranged in quadrant IV, but not in quadrant I, in which the tread 632 'is delimited by the piston 606 in a very narrow configuration, which benefits the closely matched design of the piston chamber surrounding the piston .
  • crankshafts are always outside of the chambers formed when the sealing elements engage the treads.
  • the tread 632 is not in chamber engagement.
  • the tread 632 is in engagement with the maximum chamber size with the tread 630.
  • All crankshafts, which in this illustration are in the center of the illustrated circles of the crank pins 605, are outside the chamber 630.632 and thus protected against heat attack and against attack by compressed gases.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Reciprocating Pumps (AREA)

Claims (16)

  1. Machine à piston faisant fonction de machine à expansion, de pompe aspirante ou de compresseur pour fluides compressibles équipée d'au moins un piston (6, 6'; 506; 606) logé dans un espace de course formé par deux parois parallèles (9) et une paroi périphérique (10) perpendiculaire à celles-ci, le piston étant logé sur les manetons (5; 505; 605) d'au moins deux vilebrequins (2) rotatifs identiques perpendiculaires aux parois parallèles et couplés de façon à en assurer la synchronisation angulaire, le piston et la paroi périphérique étant chacun muni d'un élément d'étanchéification (12, 13, 19; 120,13, 19; 120', 13, 19; 531, 535; 631, 635) orienté perpendiculairement aux parois parallèles, ces éléments d'étanchéification étant respectivement logés - relativement au sens de la marche - à l'une des extrémités d'une surface de chambre usinée dans le piston et à l'autre extrémité d'une surface de chambre usinée dans la paroi périphérique, et permettant au piston et à la paroi périphérique lorsqu'ils entrent en contact formant chambre de coulisser l'un contre l'autre sur des surfaces de glissement (11, 13, 18; 110, 14, 18; 110', 14, 18; 532, 530; 632, 630) formées de façon à pouvoir être balayées par les éléments d'étanchéification lors de leur rotation parallèle, et équipée d'un canal pour gaz à haute pression (17, 20; 537; 637) muni d'une soupape et d'au moins un canal pour gaz à basse pression (16, 16', 22, 22'; 516; 616) aboutissant en dehors de la chambre dans l'espace de roulement, les surfaces de la chambre formant dans leur totalité des surfaces de glissement (11, 14, 18; 110, 14, 18; 110', 14, 18; 532, 530; 632, 630) avec, à l'une de leurs extrémités les éléments d'étanchéification (12, 13, 19;120, 13, 19; 120', 13, 19; 531, 535; 631, 635), le canal pour gaz à haute pression (17, 20; 537; 637) débouchant à proximité des éléments d'étanchéification (13; 531; 631) agencés à l'extrémité de la surface de glissement (11, 18; 110, 18; 110', 18; 530; 630) de la paroi périphérique (10), caractérisée en ce que les manetons (5) sont placés dans une zone centrale du piston (6, 506, 606) à l'extérieur d'au moins l'un des quadrants (I,IV) formés par la tangente (T) touchant la surface de glissement (14, 532, 632) du piston (6, 506, 606) en son centre et par la droite (S) passant par ce centre et orthogonale à la tangente (T) et extérieurs à la tangente (T), à savoir celui (I) dans lequel se trouve - relativement au sens de marche - l'autre extrémité de la surface de glissement (14, 532, 632), et en ce que les vilebrequins (2, 2') sont agencés à l'extérieur des chambres (11.14, 18.14, 11'.14', 18'.14', 530.532, 630.632) formées lors du contact des éléments d'étanchéification avec les surfaces de glissement.
  2. Machine à piston selon la revendication 1, caractérisée en ce que les éléments d'étanchéification (12, 120) présentent des surfaces destinées à assurer un contact coulissant et dont la section est en forme de secteur de cercle avec un centre (25; 250) dont la distance par rapport à l'axe de cylindre (26; 260) de la surface de glissement opposée (11, 110) est égal au rayon de rotation, le rayon de la surface de glissement opposée (10, 110) étant égal au rayon de rotation plus le rayon de la surface (24) de l'élément d'étanchéification (12, 120).
  3. Machine à piston selon la revendication 2, caractérisée en ce que les surfaces des éléments d'étanchéification (120, 13, 19; 531, 535; 631, 635) sont différents, la forme des surfaces de glissement opposées correspondantes (110, 14, 18; 532, 530; 632, 630) y étant adaptée.
  4. Machine à piston selon l'une des revendications 2 ou 3, caractérisée en ce que l'un au moins (12', 120') des éléments d'étanchéification (12', 120', 19) du piston (6) forme par le plan de symétrie de sa surface avec le plan de symétrie de la surface de glissement (14) voisine un angle α supérieur à 0°, la surface de glissement opposée (11', 110') étant prolongée en conséquence.
  5. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que les éléments d'étanchéification il 2, 13, 19) sont des baguettes d'étanchéité (12, 13, 19; 120) logés sur ressorts.
  6. Machine à piston selon la revendication 5, caractérisée en ce que les baguettes d'étanchéité sont guidés avec un piston (28) dans des rainures faisant fonction de cylindre (29, 30) et communiquant par l'intermédiaire de canaux avec les surfaces de glissement correspondantes (11, 18).
  7. Machine à piston selon l'une des revendications 5 ou 6, caractérisée en ce que les logements des baguettes d'étanchéité sont munis de dispositifs amortisseurs.
  8. Machine à piston selon l'une des revendications 5 à 7, caractérisée en ce que les baguettes d'étanchéité (12, 13, 19; 120) sont élargies en forme de champignon par rapport à leur partie (27) logée dans la surface de glissement.
  9. Machine à piston selon l'une des revendications précédentes, caractérisée en ce qu'à la périphérie (10) de l'espace de course (3, 3') sont prévues deux surfaces de glissement (11, 18) avec un élément d'étanchéification médian commun (13) et formant avec une surface de glissement (14) du piston (6) munie à ses deux extrémités d'éléments d'étanchéité (12, 19) deux chambres voisines (11.14, 18.14) dont l'une fait fonction de chambre de compression (11.14) lors de la rotation du piston, l'autre faisant simultanément fonction de chambre d'expansion (18.14).
  10. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que plusieurs agencements de chambres (11.1, 18.14, 11'.14', 18'.14', 530.532, 630.632) sont prévus à intervalles sur la périphérie.
  11. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que dans des espaces de course parallèles (3, 3') sont prévus des pistons (6, 6') sur les mêmes vilebrequins (2, 2'), les manetons (5) et/ou les surfaces de glissement étant le cas échéant décalés d'un certain angle d'une chambre à l'autre.
  12. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que la commande de la soupape (23, 23') est synchronisée avec la course du piston.
  13. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que la soupape d'une chambre de compression est une soupape à voie unique.
  14. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que les vilebrequins (2, 2') sont accouplés par des jeux d'engrenages.
  15. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que le piston (6) présente à l'extérieur de sa surface de course (14) une surface conformée de façon à améliorer le contact avec l'air lors du mouvement du piston.
  16. Machine à piston selon l'une des revendications précédentes, caractérisée en ce que le piston n'est logé qu'unilatéralement.
EP93912894A 1992-06-09 1993-06-04 Machine a piston Expired - Lifetime EP0644981B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4218847A DE4218847A1 (de) 1992-06-09 1992-06-09 Kolbenmaschine
DE4218847 1992-06-09
PCT/EP1993/001422 WO1993025801A1 (fr) 1992-06-09 1993-06-04 Machine a piston

Publications (2)

Publication Number Publication Date
EP0644981A1 EP0644981A1 (fr) 1995-03-29
EP0644981B1 true EP0644981B1 (fr) 1997-08-27

Family

ID=6460630

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93912894A Expired - Lifetime EP0644981B1 (fr) 1992-06-09 1993-06-04 Machine a piston

Country Status (7)

Country Link
US (1) US5681156A (fr)
EP (1) EP0644981B1 (fr)
AT (1) ATE157426T1 (fr)
AU (1) AU4323193A (fr)
DE (2) DE4218847A1 (fr)
ES (1) ES2109503T3 (fr)
WO (1) WO1993025801A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10131819C1 (de) * 2001-06-30 2002-10-24 Manfred Max Rapp Rotationskolbenmaschine
DE102008025185A1 (de) 2008-05-23 2009-11-26 Manfred Max Rapp Massenausgleich für eine Drehkolbenmaschine
DE102008025186A1 (de) 2008-05-23 2009-12-03 Manfred Max Rapp Drehkolbenmaschine

Families Citing this family (10)

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Publication number Priority date Publication date Assignee Title
DE19500774A1 (de) * 1995-01-13 1996-07-18 Adolf Dr Ing Hupe Rotationskolbenmaschine
DE19614477A1 (de) * 1996-04-12 1997-10-16 Juergen Walter Drehkolbenmaschine
JP3924817B2 (ja) * 1996-09-20 2007-06-06 株式会社日立製作所 容積形流体機械
US6941103B2 (en) * 2002-10-21 2005-09-06 Eastman Kodak Company Release agent management system with anilox roller
US6926505B2 (en) * 2003-07-23 2005-08-09 Joaseph A. Sbarounis Rotary machine housing with radially mounted sliding vanes
JP2008232129A (ja) * 2007-03-19 2008-10-02 Yoshio Abe 足付シール
JP2008286183A (ja) * 2007-05-20 2008-11-27 Yoshio Abe ロータのシール。
WO2009076757A2 (fr) * 2007-12-14 2009-06-25 David Mcconnell Conversion du vent en énergie électrique avec stockage hydraulique
US9771931B2 (en) * 2013-10-09 2017-09-26 Chart Inc. Spin pump with spun-epicyclic geometry
ES2582011B2 (es) * 2016-05-11 2017-07-07 Manuel ÁLVAREZ LÓPEZ Máquina de fluido polivalente.

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DE314185C (fr) *
FR597611A (fr) * 1925-05-05 1925-11-25 Pompe à capsule pour la filature de la soie artificielle
US1864699A (en) * 1927-12-31 1932-06-28 Varley Cromwell Hanford Rotary engine, pump, and the like
CH369540A (de) * 1959-04-02 1963-05-31 Rawyler Ehrat Ernst Maschine mit mindestens einem umlaufenden Organ, das mit einem andern Organ zur Scheidung zweier Räume zusammenwirkt
DE1131703B (de) * 1960-04-05 1962-06-20 Reinald Picker Drehkolbenkraft- oder -arbeitsmaschine mit periodisch veraenderlichem Hubraum
FR1528601A (fr) * 1966-06-03 1968-06-14 Compresseurs, moteurs, pompes volumétriques
US4280798A (en) * 1979-01-24 1981-07-28 Gurley James R Work machine
JPH03275996A (ja) * 1990-03-26 1991-12-06 Ebara Corp 旋回型圧縮・膨張機
US5123820A (en) * 1990-07-31 1992-06-23 John Deere Technologies, International, Inc. Pressure assisted apex seal with stepped slot

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10131819C1 (de) * 2001-06-30 2002-10-24 Manfred Max Rapp Rotationskolbenmaschine
DE102008025185A1 (de) 2008-05-23 2009-11-26 Manfred Max Rapp Massenausgleich für eine Drehkolbenmaschine
DE102008025186A1 (de) 2008-05-23 2009-12-03 Manfred Max Rapp Drehkolbenmaschine
DE102008025186B4 (de) * 2008-05-23 2010-04-29 Manfred Max Rapp Drehkolbenmaschine

Also Published As

Publication number Publication date
DE4218847A1 (de) 1993-12-16
WO1993025801A1 (fr) 1993-12-23
DE59307216D1 (de) 1997-10-02
ATE157426T1 (de) 1997-09-15
AU4323193A (en) 1994-01-04
EP0644981A1 (fr) 1995-03-29
ES2109503T3 (es) 1998-01-16
US5681156A (en) 1997-10-28

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