WO2009083023A1 - Parallelkurbelgetriebe - Google Patents
Parallelkurbelgetriebe Download PDFInfo
- Publication number
- WO2009083023A1 WO2009083023A1 PCT/EP2007/011476 EP2007011476W WO2009083023A1 WO 2009083023 A1 WO2009083023 A1 WO 2009083023A1 EP 2007011476 W EP2007011476 W EP 2007011476W WO 2009083023 A1 WO2009083023 A1 WO 2009083023A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- parallel crank
- combustion engine
- shaft
- internal combustion
- housing
- Prior art date
Links
Classifications
-
- 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
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
-
- 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
- F01B31/00—Component parts, details, or accessories not provided for in, or of interest apart from, other groups
- F01B31/14—Changing of compression ratio
-
- 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
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0043—Arrangements of mechanical drive elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2186—Gear casings
Definitions
- the invention relates to a parallel crank gear, in particular a parallel crank gear for a variable compression ratio internal combustion engine, a variable compression ratio internal combustion engine and a transmission, in particular a manual transmission for a variable compression ratio internal combustion engine.
- EP 1 082 548 B1 describes a parallel crank mechanism designated as a clutch element for an internal combustion engine with a displaceable crankshaft for changing the compression ratio, which has a first and a second coupling body designated as a rotary body and coupling elements designated as crank elements.
- the rotary bodies can each be connected to a first or a second shaft.
- the crank elements are each rotatably mounted on both rotating bodies.
- the two rotary bodies are aligned in parallel planes of rotation and in each case connectable with the mutually associated shaft ends of the crankshaft or output shaft.
- the crankshaft and the output shaft are arranged axially parallel to each other in succession and with an eccentricity, and the crank elements which connect both rotary bodies have a crank radius corresponding to the eccentricity and are arranged at a distance from one another in the circumferential direction.
- the second, connected to the output shaft rotary body has two fixedly interconnected, referred to as disk parts part body, between which the disc-shaped first, is connected to the crankshaft rotating body arranged.
- the two disc parts are firmly connected at their outer edges by means of screws.
- the crank elements are mounted in rolling bearings or in plain bearings on the first rotary body and the two disc parts of the second rotary body.
- this housing-like design of the second rotary body of the space limited by the two disc parts is designed as an oil chamber, which is connected to the engine oil circuit.
- this space fills under the influence of centrifugal force over the entire circumference, so that over each of the individual bearings of the crank elements associated lubrication channels oil is supplied.
- This known parallel crank gear has the disadvantage that the oil remains in the interior of the second rotary body almost to the middle of the crankshaft and generates a correspondingly high friction during operation. It is an object of the present invention to provide a parallel crank gear, which has lower friction losses.
- the invention proposes a parallel crank gear, in particular for a variable compression ratio internal combustion engine, with a first and a second clutch body, which can be connected respectively to a first and a second shaft; with at least one coupling element which is rotatably mounted on both coupling bodies; and a housing surrounding the coupling bodies and coupling elements.
- the housing makes it possible, for example, to modify the parallel crank mechanism described above, which is known from EP 1 082 548 B1, the disclosure of which is incorporated herein by reference in its entirety, in that the known closed box-like configuration of the second coupling body by an open design is replaced.
- This open design can be achieved, for example, starting from the known closed box-like design in that the first disc part or part body, which is close to the second shaft, and / or the second disc part or partial body, which is close to the first shaft, has at least one opening , Through this breakthrough, the oil can leave the limited space of the two disc parts interior.
- the openings may preferably be formed in the end faces and / or peripheral surfaces of the disc parts.
- the housing also makes it possible, for example, to modify the above-described, from EP 1 082 548 B1 known parallel crank mechanism in that the known two-part design of the two disc parts having second coupling body is replaced by a one-piece design, wherein the second, the first shaft Near disc part is omitted.
- the housing may be formed as desired in any manner.
- the housing is formed by a wall of a crankcase of an internal combustion engine or a wall of a transmission housing of a gearbox and by a cover which is connected to the wall.
- the lid is integrally formed with the wall or bolted to the wall.
- the second coupling body is mounted in the region of the first shaft and / or in the region of the second shaft on the housing.
- the storage can be done for example with plain bearings and / or roller bearings.
- the bearings are preferably single row or double row.
- the two-sided bearing so the storage in the region of the first shaft and the second shaft can preferably be used when the parallel crank gear is designed as a dual mass flywheel, wherein the first and the second clutch body form the primary flywheel or the secondary flywheel of the dual mass flywheel.
- a seal preferably by means of a radial shaft sealing ring, is provided to the first shaft; and that the coupling element has a lifetime fat filling.
- the radial shaft seal prevents oil from the main shaft of the first shaft, which is closest to the parallel crank gear, can get into the parallel crank gear. A lubrication of the coupling element bearing with such oil is not necessary because of the life fat filling.
- the housing that surrounds the coupling body and coupling elements also completely eliminated.
- the housing has at least one oil drain opening.
- the oil drain opening may be connected to an oil pan of an internal combustion engine or a transmission housing of a manual transmission.
- the invention also proposes a parallel crank gear, in particular for a variable compression ratio internal combustion engine, having a first and a second clutch body, which can be connected respectively to a first and a second shaft; with at least one coupling element which is connected to both coupling body is rotatably mounted; and with an oil catcher, which completely surrounds the coupling body in the circumferential direction.
- the ⁇ lfang allows, like the housing described above, for example, the above-described open design of the two disc parts having second coupling body and the above-described one-piece design of the second coupling body, in which the second disc part is omitted.
- the oil catcher is sealed by a labyrinth and / or slip rings against the coupling body.
- the invention moreover proposes a parallel crank mechanism, in particular for a variable compression ratio internal combustion engine, with a first and a second clutch body, which can each be connected to a first or a second shaft; with at least one coupling element which is rotatably mounted on both coupling bodies; and with an oil catcher, which surrounds the coupling body in the circumferential direction partially, wherein the first and / or the second coupling body has at least one oil outlet opening; and wherein a closing device is provided for the oil outlet opening, which is designed such that the oil outlet opening, if it sweeps over the oil catcher away, opened and otherwise closed.
- the ⁇ lfang listening allows, as the housing described above and the above described ⁇ lfang leverage, for example, the above-described open design of the two disc parts having the second coupling body and the above-described one-piece design of the second coupling body, in which the second disc part is omitted.
- the oil catcher may be arranged at any position in the circumferential direction as needed. Preferably, it is arranged below the two coupling body. Then, the oil catcher can catch even when the clutch bodies are stationary, the oil that emerges from the oil outlet opening.
- the oil trapping device in each of the proposed oil trapping devices, provision can be made for the oil trapping device to have at least one oil drain opening.
- the oil drain opening may be connected to an oil pan of an internal combustion engine or a transmission housing of a manual transmission.
- each of the proposed parallel crank gear can be provided that extends at least one oil supply passage in the first shaft and the first coupling body to the coupling element.
- the oil supply channel may be connected, for example, with the oil supply for a bearing of the first shaft, and through it the oil passes directly to the coupling element or its bearings in the two coupling bodies.
- each of the proposed parallel crank gear can be provided that the first and / or the second coupling body has at least one breakthrough. Further details on this breakthrough can be found below.
- the second coupling body has a first, near the first shaft part body and a second, the second shaft near partial body which are fastened with at least one fastener tion element to each other, that between their facing surfaces and whose radial distance from the second shaft is less than or equal to the radial distance of at least one coupling element from the second shaft; and that the first coupling body is arranged between the partial bodies and has at least one opening through which the fastening element protrudes.
- the two partial bodies can be shaped as required and are preferably disc-shaped. The two part body having the second coupling body is thus configured in two parts, and further above are closer explanations to find this two-part design.
- each of the proposed parallel crank gear can be provided that it is designed as a flywheel, preferably two-mass flywheel.
- the first and the second clutch body form the primary flywheel mass or the secondary flywheel mass of the dual mass flywheel.
- the invention further proposes a variable compression ratio internal combustion engine having a crankshaft pivotally supported; with an output shaft; and with one of the proposed parallel crank gear between crankshaft and output shaft.
- the invention moreover proposes a variable compression ratio internal combustion engine having a crankshaft which is pivotally supported; with an output shaft; with a parallel crank gear between crankshaft and output shaft; and with a housing surrounding the parallel crank gear.
- the housing is formed by a crankcase of the internal combustion engine.
- the housing is formed by a wall of a crankcase of the internal combustion engine and a lid which is connected to the wall. Then, for example, be provided that the lid is integrally formed with the wall or bolted to the wall.
- the parallel crank gear has a first and a second clutch body, which are respectively connected to the crankshaft and the output shaft, and at least one coupling element which is rotatably mounted on both coupling bodies.
- the crank radius of the coupling element may for example be perpendicular to the two waves.
- the parallel crank gear as a flywheel, preferably a dual mass flywheel, is formed.
- a flywheel preferably a dual mass flywheel, between the parallel crank gear and the output shaft is involved.
- the housing has at least one oil drain opening, which is connected to an oil pan of the internal combustion engine.
- the invention moreover proposes a manual transmission, in particular for a variable compression ratio internal combustion engine, having an input shaft which can be connected to a crankshaft which is pivotally mounted; and with one of the proposed parallel crank gear between crankshaft and input shaft.
- the invention also proposes a manual transmission, in particular for a variable compression ratio internal combustion engine, having an input shaft which is connectable to a crankshaft which is pivotally mounted; with a parallel link between crankshaft and input shaft; and with a housing surrounding the parallel crank gear.
- the housing is formed by a transmission housing of the gearbox.
- the housing is formed by a wall of a gear housing of the gearbox and a lid which is connected to the wall. Then, for example, be provided that the lid is integrally formed with the wall or bolted to the wall.
- the parallel crank gear has a first coupling body, which can be connected to the crankshaft, a second coupling body, which is connected to the input shaft, and at least one coupling element, which is rotatably mounted on both coupling bodies ,
- the crank radius of the coupling element may for example be perpendicular to the waves.
- the parallel crank gear as a flywheel, preferably two-mass flywheel is formed.
- each of the proposed transmission can be provided that a flywheel, preferably a two-mass flywheel, is integrated between the crankshaft and the parallel crank gear.
- a starting clutch between the crankshaft and the parallel crank gear or between the parallel crank gear and the input shaft is provided.
- FIG. 1 is a longitudinal sectional view of a first embodiment of a parallel crank gear for a variable compression ratio internal combustion engine
- Fig. 2 is a longitudinal sectional view of a second embodiment of a parallel crank gear for a variable compression ratio internal combustion engine
- Fig. 3 is a longitudinal sectional view of a third embodiment of a parallel crank gear for a variable compression ratio internal combustion engine
- FIG. 4 is a schematic cross-sectional view of FIG. 3; FIG.
- Fig. 5 is a longitudinal sectional view of a fourth embodiment of a parallel crank gear for a variable compression ratio internal combustion engine.
- FIG. 6 shows a schematic cross-sectional view of FIG. 5.
- a parallel crank gear 10 is shown in a first embodiment, which is here attached by way of example to an internal combustion engine 11 with a variable compression ratio.
- the internal combustion engine 11 is only partially shown here and has a crankcase 12 of which only one transmission-side wall 13 is shown here, a crankshaft 14 and eccentric rings, of which only a transmission-side eccentric ring 15 is shown.
- the shaft journal 16 is mounted eccentrically in the eccentric ring 15, which in turn in the Wall 13 is mounted.
- crankshaft axis 18 can be pivoted in a known manner to the defined by the eccentric rings 15, relative to the crankcase 12 stationary output shaft axis 19 of an output shaft, not shown here relative to the crankcase 12. Therefore, a further description is omitted here and reference is made by way of example to the explanations in EP 1 082 548 B1.
- the crankshaft axis 18 and the output shaft axis 19 can not be seen in FIGS. 1 to 4 and 5, since they overlap in these views, but their position in FIGS. 4 and 6 can be clearly seen.
- the parallel crank mechanism 10 here has a first coupling body 20, a second coupling body 21, six coupling elements 22, of which only one is shown in FIG. 1 and which can be seen well in FIGS. 4 and 6, and a housing 23.
- the first coupling body 20 is here disc-shaped and fixedly connected at a central flange region with a flange of the crankshaft 14, which forms the gear-side end of the crankshaft 14 and the shaft journal 16 continues in Fig. 1 to the right.
- the second coupling body 21 is also disc-shaped, but as a crankshaft 14 toward, so in Fig. 1 to the left open hollow disc, in the interior of which the first coupling body 20 is located.
- the hollow disk shape of the second clutch body 21 is achieved here by having a first part body 24 which is close to the crankshaft 14, that is to say left in FIG. 1 and essentially annular, and a second part body 25 which is close to the output shaft
- a first part body 24 which is close to the crankshaft 14, that is to say left in FIG. 1 and essentially annular
- a second part body 25 which is close to the output shaft
- Fig. 1 is right and is substantially disc-shaped.
- the outer edges of the two body parts 24, 25 are bent axially relative to each other and secured together with distributed over the circumference screws.
- the coupling elements 22 are designed here as cranks, but can also be realized in other ways, for example by means of gears.
- Each coupling element 22 here has a cylindrical central disk 26 and an eccentrically and axially parallel to this pin 27, which here has a smaller diameter than the central disk 26 and protrudes from both end faces of the central disk 26.
- the central disk axis 28 of the central disk 26 and the pin axis 29 of the pin 27 are parallel to the crankshaft axis 18 and the output shaft axis 18 and have an eccentricity, so a distance between them, which is equal to the eccentricity of the crankshaft axis 18 and the output shaft axis 19. This can be seen well in FIGS. 4 and 6.
- the central disk 26 is mounted in the first coupling body 20, and in Fig.
- the corresponding bearing bores in the two part bodies 24, 25 are designed here as through holes.
- An oil supply channel 30 extends here in the crankshaft 14 from the bearing surface of the shaft journal 16 to the end face of the crankshaft flange, from there through the adjacent end face of the flange of the first coupling body 20 through this radially outwardly to the coupling element 22, more precisely up to the central disk 26th
- lubricating oil that is supplied to the shaft journal 16, through the oil supply passage 30 to the central disk 26 and from there on to the projecting parts of the pin 27 mounted in the through holes are passed.
- the two partial bodies 24, 25 have apertures (not shown here) through which the oil flowing out of the bearing surfaces of the coupling element 22 can leave the interior of the second coupling body 21.
- the housing 23 is formed here by the wall 13 and a lid 31 which is connected by screws to the wall 13.
- the second coupling body 21 is mounted on the housing 23 in the region of the crankshaft 14 and in the region of the output shaft.
- the annular first partial body 24 is supported with its inner edge radially inwardly by means of a first roller bearing 32 in the region of the shaft journal 16 on an axial collar of the wall 13 and the central flange portion of the second body 25 radially outward by means of a second roller bearing 33 an inner peripheral surface of a central passage opening of the lid 31 from.
- the second coupling body 21 is thus mounted on both sides of the first coupling body 20 and thus stable against tilting.
- a sealing ring 34 is provided which prevents the escape of oil from the housing 23 of the parallel crank mechanism 10.
- the lid 31 has, in the bottom area, not shown, on a ⁇ lablauf- opening, not shown, which is connected to an oil pan of the engine 11, not shown. Thus, the oil collected by the housing 23 can be guided through the oil drain opening back to the oil pan.
- a parallel crank gear 10 is shown in a second embodiment, which is similar to the first embodiment, so that in the following only the differences will be described in more detail.
- the two body parts 24, 25 are not connected to each other at their outer edges, as in the first embodiment, but radially further inwardly.
- a plurality of fasteners 35 are provided, of which only one is shown.
- the radial distances of the fastening elements 35 from the output shaft and output shaft axis 19 are smaller here than the radial distance of the coupling elements 22 from the output shaft and output shaft axis 19, ie the fastening elements 35 lie radially inside the coupling elements 22.
- the two partial bodies 24 extend 25 radially outward not further than is necessary for the storage of the pin 27.
- Each fastener 35 here has two aligned elevations 36 which project from the facing inner surfaces of the two body parts 24, 25 axially inwardly and are screwed together.
- the first coupling body 20 arranged between the partial bodies 24, 25 has, in the region of each fastening element 35, an opening 37 through which the corresponding fastening element 35 projects.
- the openings 37 are shaped so that they do not hinder the relative movement between the two coupling bodies 20, 21 during operation and during pivoting of the crankshaft 14.
- a second sealing ring 38 is provided radially inside the first roller bearing 32 between the collar of the wall 13 and the flange of the crankshaft 14. This prevents leakage of engine oil from the crankcase 12 into the parallel crank gear 10.
- the oil supply channel 30 of the first embodiment is omitted here, since the lubrication of the coupling elements 22 takes place here in other ways, for example, by going through an oil sump, not shown, including the oil drain opening provided in the first embodiment, which is connected to the oil pan, deleted here.
- a parallel crank mechanism 10 is shown in a third embodiment, which is similar to the first and second embodiment, so that in the following only the differences will be described in more detail.
- an oil catcher 39 is provided, which completely surrounds the coupling bodies 20, 21 in the circumferential direction.
- the wall 13 and the eccentric ring 15 are not shown for reasons of clarity.
- the oil-catching device has a first and a second central through-opening 40, 41, which in the side facing to the crankcase, not shown, so in Fig. 3 left side surface or in the opposite the, so in the figure right side surface are formed.
- the first through hole 40 surrounds the eccentric ring, not shown, and the shaft journal 16 and is supported by a slip ring, not shown, on the not shown collar of the wall 13 from.
- the second through-opening 41 surrounds the flange of the second coupling body 21 and is supported thereon by a slip ring 42.
- the second roller bearing 33 of the first and second embodiments is omitted here.
- the two coupling bodies 20, 21 are formed as in the second embodiment, but they may also be formed as in the first embodiment.
- an oil drain opening 43 is provided, which is connected to the oil pan.
- FIGS. 5 and 6 show a parallel crank mechanism in a fourth embodiment, which is similar to the third embodiment, so that in the following only the differences will be described in more detail.
- the oil trap 39 does not completely surround the clutch bodies 20, 21 in the circumferential direction as in the third embodiment, but partially. It is here below the two coupling bodies 20, 21 arranged, and their oil drain opening 43 is in contrast to the third embodiment to the crankcase 12, not shown, so in Fig. 5 offset to the left.
- the second coupling body 21 has a plurality of openings distributed over its circumference, which serve as oil outlet openings 44 for the oil collected in the interior of the second coupling body 21 designed as a hollow disk, as in the first embodiment.
- oil outlet openings 44 are shown in FIG. 5, only the lower and in FIG. 6 those five lower, which are currently in the range of ⁇ lfang sensible 39.
- a closing device 45 is provided, which is designed in such a way that the corresponding oil outlet opening 44, if it sweeps over the oil catching device 39, is opened and otherwise closed.
- a valve pin 46 which cooperates with a radially inwardly projecting from the bottom of the ⁇ lfang noticed 39 ridge 47.
- the valve pin 46 is seated in the oil outlet opening 44 and its diameter is smaller than its diameter.
- valve pins 46 are in operation by the centrifugal force radially outward and thus pressed the shut-off on their valve seats. The valve pins 46 then project with their radial outward, that is, in FIGS. 5 and 6, lower ends far out of the oil outlet openings 44.
- valve pin 46 reaches the area of the oil catcher 39, this outer end comes into contact with the upper edge of the ridge 47 which is continuously radially inwardly in the circumferential direction from the edge of the oil catcher 39 to the center where the oil drain port 43 is located Bottom of oil catcher 39 rises and then also drops radially outward again to the opposite edge of the oil catcher 39.
- the valve pin 46 is pushed further and further radially inwardly as it approaches the oil drain opening 43 or the center of the oil trap 39, so that the shut-off body is lifted out of its valve seat and the oil can flow radially outward through the now open oil outlet opening 44 and from the oil trap 39 is caught.
- this closing device 45 then leaves the oil-catching device 39 again, the shut-off body sinks back onto its valve seat.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ocean & Marine Engineering (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2007/011476 WO2009083023A1 (de) | 2007-12-31 | 2007-12-31 | Parallelkurbelgetriebe |
US12/811,305 US20100294246A1 (en) | 2007-12-31 | 2007-12-31 | Parallel crank drive |
CN2007801021427A CN101910582A (zh) | 2007-12-31 | 2007-12-31 | 平行曲柄传动机构 |
DE112007003715T DE112007003715A5 (de) | 2007-12-31 | 2007-12-31 | Parallelkurbelgetriebe |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP2007/011476 WO2009083023A1 (de) | 2007-12-31 | 2007-12-31 | Parallelkurbelgetriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2009083023A1 true WO2009083023A1 (de) | 2009-07-09 |
Family
ID=39671508
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2007/011476 WO2009083023A1 (de) | 2007-12-31 | 2007-12-31 | Parallelkurbelgetriebe |
Country Status (4)
Country | Link |
---|---|
US (1) | US20100294246A1 (de) |
CN (1) | CN101910582A (de) |
DE (1) | DE112007003715A5 (de) |
WO (1) | WO2009083023A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011114561A1 (de) | 2011-09-30 | 2013-04-04 | Fev Gmbh | Verbesserung einer Ölführung in einem Parallelkurbelgetriebe an einer Verbrennungskraftmaschine |
DE102011114562A1 (de) | 2011-09-30 | 2013-04-04 | Fev Gmbh | Ölversorgungssystem für ein Parallelkurbelgetriebe,insbesondere für eine Brennkraftmaschine mit variablem Verdichtungsverhältnis |
CN106715938A (zh) * | 2014-08-05 | 2017-05-24 | 科特雷恩控股有限公司 | 一比一扭矩联轴器 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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WO2000057074A1 (de) * | 1999-03-24 | 2000-09-28 | Fev Motorentechnik Gmbh | Kupplungselement zur verbindung von zwei gleichachsig hintereinander und mit querabstand zueinander angeordneten achsparallelen wellen |
EP1245803A1 (de) * | 2001-03-30 | 2002-10-02 | Gomecsys B.V. | Brennkraftmaschine mit variablem Verdichtungsverhältnis |
WO2004044451A1 (de) * | 2002-11-14 | 2004-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Vorrichtung zur kopplung zweier wellen |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
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AT352485B (de) * | 1974-06-29 | 1979-09-25 | Chivari Ilie | Kupplung zum kuppeln achsversetzter umlaufender wellen |
US4612882A (en) * | 1983-04-11 | 1986-09-23 | Bonfilio Roberto L | Rotating cylinder internal combustion engine |
US6167851B1 (en) * | 1998-07-15 | 2001-01-02 | William M. Bowling | Movable crankpin, variable compression-ratio, piston engine |
DE10051271B4 (de) * | 2000-10-16 | 2015-07-16 | Fev Gmbh | In ihrem Verdichtungsverhältnis einstellbare Kolbenbrennkraftmaschine mit integriertem Verstellaktuator |
FR2844856B1 (fr) * | 2002-09-24 | 2005-12-30 | Valeo Embrayages | Filtre pour transmission a changement de rapport automatise, continu ou non, notamment pour vehicule automobile |
WO2005059330A2 (en) * | 2003-12-11 | 2005-06-30 | Dow Glendal R | Variable crankshaft |
-
2007
- 2007-12-31 CN CN2007801021427A patent/CN101910582A/zh active Pending
- 2007-12-31 US US12/811,305 patent/US20100294246A1/en not_active Abandoned
- 2007-12-31 WO PCT/EP2007/011476 patent/WO2009083023A1/de active Application Filing
- 2007-12-31 DE DE112007003715T patent/DE112007003715A5/de not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2000057074A1 (de) * | 1999-03-24 | 2000-09-28 | Fev Motorentechnik Gmbh | Kupplungselement zur verbindung von zwei gleichachsig hintereinander und mit querabstand zueinander angeordneten achsparallelen wellen |
EP1245803A1 (de) * | 2001-03-30 | 2002-10-02 | Gomecsys B.V. | Brennkraftmaschine mit variablem Verdichtungsverhältnis |
WO2004044451A1 (de) * | 2002-11-14 | 2004-05-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Vorrichtung zur kopplung zweier wellen |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011114561A1 (de) | 2011-09-30 | 2013-04-04 | Fev Gmbh | Verbesserung einer Ölführung in einem Parallelkurbelgetriebe an einer Verbrennungskraftmaschine |
DE102011114562A1 (de) | 2011-09-30 | 2013-04-04 | Fev Gmbh | Ölversorgungssystem für ein Parallelkurbelgetriebe,insbesondere für eine Brennkraftmaschine mit variablem Verdichtungsverhältnis |
CN106715938A (zh) * | 2014-08-05 | 2017-05-24 | 科特雷恩控股有限公司 | 一比一扭矩联轴器 |
EP3177841A4 (de) * | 2014-08-05 | 2018-05-16 | Ker-Train Holdings Ltd. | Eins-zu-eins-drehmomentkupplung |
US10704604B2 (en) | 2014-08-05 | 2020-07-07 | Ker-Train Holdings Ltd. | One-to-one torque coupling |
CN112253648A (zh) * | 2014-08-05 | 2021-01-22 | 科特雷恩控股有限公司 | 一比一扭矩联轴器 |
US11867238B2 (en) | 2014-08-05 | 2024-01-09 | Ker-Train Holdings Ltd. | One-to-one torque coupling |
Also Published As
Publication number | Publication date |
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US20100294246A1 (en) | 2010-11-25 |
CN101910582A (zh) | 2010-12-08 |
DE112007003715A5 (de) | 2010-11-18 |
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