WO2015155167A2 - Moteur à pistons - Google Patents

Moteur à pistons Download PDF

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Publication number
WO2015155167A2
WO2015155167A2 PCT/EP2015/057474 EP2015057474W WO2015155167A2 WO 2015155167 A2 WO2015155167 A2 WO 2015155167A2 EP 2015057474 W EP2015057474 W EP 2015057474W WO 2015155167 A2 WO2015155167 A2 WO 2015155167A2
Authority
WO
WIPO (PCT)
Prior art keywords
piston
control line
support cylinder
connecting rod
support
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2015/057474
Other languages
German (de)
English (en)
Other versions
WO2015155167A3 (fr
Inventor
Christoph Müller
Markus Podworny
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FEV Europe GmbH
Original Assignee
FEV GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by FEV GmbH filed Critical FEV GmbH
Priority to DE112015001700.3T priority Critical patent/DE112015001700A5/de
Publication of WO2015155167A2 publication Critical patent/WO2015155167A2/fr
Publication of WO2015155167A3 publication Critical patent/WO2015155167A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines
    • 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
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods

Definitions

  • the present invention relates to a piston engine with variable compression (VCR piston engine) with a connecting rod, which carries a compression piston, wherein the connecting rod has an adjusting mechanism for adjusting the compression piston.
  • the adjusting mechanism has a first support piston in a first support cylinder of the connecting rod and a second support piston in a second support cylinder of the connecting rod, wherein the first and the second support cylinder are each connected to a first control line via which a medium in the respective support cylinder and can flow out, specifically for adjusting the respective support cylinder.
  • a method for operating a VCR piston engine is proposed.
  • Adjustable variable compression ratios are known in reciprocating engines, such as in internal combustion engines.
  • EP-A-1 426 584 describes a connecting rod for use in a reciprocating engine of variable compression ratio by pivoting an eccentric, whereby the effective length of the connecting rod is variable.
  • the eccentric is fixed in one or the other end position of the swivel range.
  • This fixation is described in the description, inter alia, as a mechanical fixation by means of pawl.
  • DE-A-10 2005 055 199 likewise shows the mode of operation of a length-variable connecting rod, with which the transition between different NEN compression ratios occurs.
  • the realization takes place via an eccentric in the small connecting rod eye whose position is fixed by two hydraulic cylinders with variable resistance.
  • the switch positions mentioned in this document refer to a two-stage system.
  • Object of the present invention is to provide a piston engine with a multi-stage, d .h. more than two-stage adjustable compression ratio, so that an approximation of the benefits in CO 2 emissions of a continuous system with continuous adjustment of the compression ratio is achieved at the same time still low structural complexity.
  • the adjusting mechanism has a first support piston in a first support cylinder and a second support piston in a second support cylinder of the connecting rod, wherein the first and second support cylinders are each connected to a first, separate for each support cylinder control line through which a medium in the respective support cylinder flows in and out for adjusting the respective support cylinder, wherein in at least one of the two support cylinders at least one further, second control line for at least draining the medium for adjusting the associated support cylinder opens.
  • the two first control lines open into the bottom of the respective support cylinder, so that a medium both in and out of the Support cylinder can flow in and out.
  • the VCR piston engine can be designed, for example, as shown, for example, in each of DE-A-10 2005 055 199, DE-A-10 2011 056 298, DE-A-10 2012 014 917, DE-A-10 2011 108 790, DE-A-10 2010 061 360, DE-A-10 2010 061 359, DE-A-10 2010 061 361 and / or DE-A-10 2008 005 467, to which reference is made in the context of the disclosure in relation to the possible construction of the connecting rod with eccentric adjustment of the compression piston, the adjusting mechanism and the support cylinder or support piston and their operation is pointed out.
  • the contents of these documents are hereby incorporated by reference into the subject of the present application.
  • the invention makes it possible, starting from a two-stage length-variable connecting rod, to provide an extension to at least one further stage.
  • This is realized via at least one additional second control line, which unlike the first control lines for a two-stage system, which preferably opens at a bottom of a support piston, can preferably be arranged in a stroke region of the support cylinder.
  • the second control line opens along a travel path of the associated support piston in the support cylinder.
  • the lower edge of the support piston in the support cylinder can be used as a control edge.
  • the first and second control lines can each be introduced in the form of bores in the connecting rod.
  • the connecting rod in the manufacture for example, casting, the holes have specified as channels.
  • a subsequent manufacturing of the control lines is possible.
  • the control lines may also be located inside the connecting rod.
  • a further embodiment provides that a part of the control line is arranged on the connecting rod, for example as a line connected to the connecting rod is arranged outside. This may be a subsequently attached line as well as an integrated manufactured line.
  • a further embodiment of the VCR piston engine provides that in the first and the second support cylinder in each case at least two control lines open for selectively flowing and admitting the medium into or out of the respective support cylinder.
  • at least one control line opens into the respective support cylinder along the travel path of the control piston, so that the control piston passes over the junction of the at least one control line during displacement within the support cylinder.
  • a first control line opens into a bottom region of the control piston, while the at least one second control line opens into the support cylinder at a point along the travel path.
  • the second control line is provided laterally in the support cylinder at a height opening, which is in a range between one third and two thirds of the travel of the control piston.
  • two second control lines open laterally into a control cylinder
  • one of the two control lines is arranged, for example, in a region comprising a first half of the travel path and the other in a region comprising a second half of the travel path into the support cylinder.
  • more than two second control lines are provided laterally into the support cylinder, they open in an equidistant manner along the travel path according to one embodiment.
  • Another embodiment provides that these open laterally with each other at different distances along the travel in the support cylinder. In this way, for example, a four- or multi-stage adjustment of the compression piston can be achieved. It is preferred if in the region of that support cylinder which supports the inertial mass force of the compression piston, at least one control line is more open than at the other support cylinder, which supports the compression piston at gas side occurring due to the combustion (gas forces.
  • the VCR piston engine is constructed such that the or each second control line is opened or blocked by the support piston in the respective support cylinder.
  • the support piston with one of its edges can not only serve as a control piston. Rather, this allows not only a complete opening as well as a complete closing of the lateral junction and the only partial opening or closing a laterally opening control line.
  • the VCR piston engine has a switch which is in operative connection with the second control line, wherein the second control line is opened or closed by means of the switch.
  • This switch is preferably part of the adjusting mechanism and particularly preferably arranged on or in the connecting rod.
  • the switch is able to allow or prevent an inflow or outflow of the medium, in particular oil of the piston engine, into or out of the respective support cylinder.
  • a multi-way valve is used as a switch over which, for example, a plurality of control lines can be switched simultaneously.
  • the valve system can comprise, for example, a 3/2, a 3/3, a 4/2 or even a 4/3 directional control valve, in particular a valve system, as is apparent from DE-A-10 2012 020 999, to which reference is made in the context of the disclosure of the invention, so that the content of this document is the subject of the present application.
  • a single switch can be provided, which, depending on the position, ensures that the medium can flow in or out of the respective support cylinders.
  • the switch is able to achieve an intermediate position of the adjustable over the eccentric compression piston by activating or deactivating a control line, which opens laterally into one of the support cylinders.
  • a further embodiment of the invention provides that the switch is part of an actuation unit which provides for an independent actuation of the switch for the second control line in relation to a blocking or releasing of the respective first control line.
  • a further embodiment of the invention provides that the switch is part of an actuation unit, which provides an interdependent actuation for opening and locking of each first and second control line.
  • the VCR piston engine has provided a control unit, which in each case coordinates opening and closing of respectively first and at least second control lines in order to set different compression ratios.
  • WO-A-2014/019684 as well as DE-A-10 2012 020 999 each describe VCR systems or actuation units, by means of which the mechanical actuation of the adjusting mechanism for a VCR engine is made possible.
  • the connecting rod its function with the adjustable compression piston, with respect to the adjustment system as well as the Aktuianssaku in the context of the disclosure of the invention proposed here, reference is fully made to these two documents, so that the contents of these two documents belong to the subject of the present application.
  • a method for operating a VCR piston engine wherein a stroke adjustment of a compression piston by means of an adjustment mechanism of a connecting rod, by means of which the compression piston and thus the effective length of the connecting rod is adjusted, wherein a support piston of the adjusting mechanism opens or closes at least one control line which laterally opens into the support cylinder in one (possibly two) support cylinders during the process.
  • an effective (compressor piston) mass inertia force is used, which is utilized for the adjustment.
  • Figure 1 shows a detail of an internal combustion engine in the form of a connecting rod shown schematically as a 3-point connecting rod, which allows three different densities.
  • FIG. 4 is a schematic view of another embodiment of a 3-point connecting rod with outgoing control channels
  • FIG. 1 shows a part of an internal combustion engine, namely a connecting rod with two-stage variability of the compression ratio of the internal combustion engine.
  • This already existing two-stage variant of a length-variable connecting rod is extended according to the invention by at least one further stage.
  • FIG. 1 shows an embodiment by means of which an adjustable change of a compression ratio in a piston machine 1 in the form of a reciprocating internal combustion engine is made possible.
  • the connecting rod 17 has a large connecting rod bearing eye 3 (stroke bearing) and a small connecting rod bearing eye 2 (piston bearing).
  • an eccentric 5 is arranged, which is rotatably mounted.
  • the eccentric 5 has a bore 18 for receiving a bolt 6, a compression piston 7, which in a cylinder indicated at 8 (or up) and back (or ab-) is movable on.
  • the eccentric 5 On an outer surface, the eccentric 5 has a toothing 19. With this toothing 19 of the eccentric 5 is connected to a lever system 20 which acts as a support mechanism and preferably also as a backstop.
  • the lever system 20 has a first lever 21 and a second lever 22.
  • the two levers 21, 22 are fixedly coupled together.
  • the levers 21, 22 are also connected to the eccentric 5 so as to be non-rotatable via the teeth 19.
  • the lever system 20 with the levers 21, 22 is arranged in a recess 23 in the connecting rod 17.
  • Fig. 1 it can also be seen that the lever system 20 is axially guided in the recess 23. Furthermore, the lever system 20 connection joints 24. About the connecting joints 24 rods 25 are hinged. In the second connecting rod 17 turn support cylinder bores 26 are arranged. In these support piston 27 are guided, where the rods 25 are articulated. By this arrangement, a respective stroke of the two support piston is in direct relation to a rotation angle of the eccentric 5.
  • the support cylinder bores 26 in the connecting rod 17 are closed by check valves 28 to the large connecting rod eye 3, so that in each case a working space 29 is formed.
  • the working space 29 can thus serve as a damping volume as well as a support in the case of a backstop.
  • Pleuellagerschalen 30 are arranged.
  • the connecting rod bearing shells 30 are with Openings 31 provided. Since the bearing shells 30 are provided with a circumferential groove, which is in communication with an oil supply via the crankshaft, is in the groove at any time to an oil pressure. This oil pressure is transferred at any time to the check valves 28. These open or are closed depending on the working pressure present in the working chamber 29.
  • the exact sequence of a possible change in the compression ratio is more apparent from the above-cited prior art, in particular, for example, from DE-A-10 2005 055 199.
  • a Switch instead of switching over the working pressure also a Overall circuit of control lines and control channels is made possible by, for example, a switch.
  • the connecting rod 17 for setting a different compression ratio will be explained below by way of example by setting a low compression ratio as an example.
  • the first support cylinder 31.1 or the second support cylinder 31.2 by at least one additional control line 32, for example in the form of a channel, which does not open into the bottom of the support cylinder, another locking stage and thus a further compression stage of the internal combustion engine introduced.
  • the control line 32 arranged in the stroke region of the second support cylinder 31.2 can be controlled, for example, with a variable resistor.
  • the control channels 33.1, 33.2 in the bottom of the two support cylinders are closed with open control line 32 in the stroke range of a support cylinder.
  • the open control line 32 causes a flow of oil from the second support cylinder 31.2 until the control line 32 is closed by a control edge, which preferably corresponds to the lower edge of the piston.
  • a control edge which preferably corresponds to the lower edge of the piston.
  • Additional compression stages can be achieved by further analogously designed control lines in the stroke region of the support cylinders, preferably in the second support cylinder 31.2.
  • the blocking of the respective control channels 33.1, 33.2 or the control line 32 or of a plurality of control lines is preferably realized by means of a switch 34.
  • both support cylinders can be filled with oil from the stroke bearing, a check valve assigned to each support cylinder prevents the oil from flowing out.
  • a 3/2-way switching valve can open either the GKS or the MKS. This combination of check valves and switching valves forms a hydraulic freewheel whose direction can be selected. In the case of the selected high compression ratio position, also referred to as “ high ", the moments which have a mathematically positive effect on the eccentric are based on the GKS oil column.
  • intermediate positions are required in accordance with the additional compression levels.
  • the sum of intermediate positions and end positions must correspond to the number of compression stages and thus the number of control lines 32 and control channels 33.1, 33.2, wherein the switch 34, preferably a mechanical switch, in each of the positions exactly one control channel 33.1, 33.2 or control line 32 either release itself or open via a valve and the other control channels 33.1, 33.2 or control lines 32 should close.
  • the locking of the respective control channels or control lines can be done for example by a mechanical switch 34, as shown by way of example from FIG. 2, wherein in FIG. 3 of the mechanical switch by way of example
  • the mechanical switch 34 can correspond as closely as possible to the modes of operation shown in DE-A-10 2005 055 199 and described in WO-A-2014/019684.
  • a switching operation of the switch 34 it is moved in the direction of the arrow according to the arrow in the switch 34 along the illustrated ramp of a cam member 35, while the connecting rod, not shown, moves in the direction of the arrow arranged perpendicular thereto.
  • a width of a camshaft element 35 can only be selected to be slightly wider than that of the mechanical switch 34.
  • the inner width of the cam member 35 must be at least as large to prevent tilting or jamming of the mechanical switch 34 in the cam member 35, but may be selected to be as wide as possible that the mechanical switch 34 in the desired intermediate position and not in the next intermediate or final position engages.
  • the catch can be achieved in the intermediate position of the mechanical switch 34 but also via other mechanisms.
  • a blocking of the adjustment in an intermediate position is conceivable, which automatically unlocks after completion of the adjustment and releases a further adjustment. This blockage can be triggered, for example, by centrifugal or acceleration forces. At standstill of the mechanical switch 34 in the intermediate position, the blocking is then released again due to the lack of driving centrifugal or acceleration force.
  • FIG. 4 shows by way of example a simplified, schematic representation of a further possible embodiment of a connecting rod with adjustable compression ratios.
  • the control line opens 32.3 turn laterally into one of the support cylinder, while the control channels 33.1, 33.2 of the respective support cylinder lead into the bottom of the support cylinder.
  • the remaining reference symbols in principle designate identical or similar structural components, as they also appear from FIG. In the following, a sequence of the displacement of the respective support cylinders will be explained in a schematic representation.
  • Fig. 5 shows a first state as a final state "£ high " due to a stop situation in one of the two support cylinders, with a high compression ratio is set.
  • the schematic diagram shows a completely hydraulically locked gas-fired power cylinder GK, wherein a control channel not shown in detail is locked at the bottom of the gas-power cylinder GK as well as at the bottom of the mass cylinder MK.
  • the filling with oil of the gas power cylinder GK is indicated by hatching.
  • a laterally outgoing control line of the mass cylinder MK is locked by its associated piston.
  • Fig. 6 shows an average compression position "£ mi d" on. This is achieved by the mass flow cylinder and the gas power cylinder whose two channels are locked at the bottom of the inertia and gas power cylinder, however, the side-opening control line is just completely closed. As a result, the hatched oil cushion can flow to the height of the junction of the control line.
  • FIG. 7 shows a further end position, namely a compression position "£
  • a completely hydraulically locked mass force cylinder MK in which the control line as well as the opening into the ground control channel of the mass cylinder are locked.
  • FIGS. 5 to 7 illustrate the sequence which is possible in the adjustment from one end position to the other end position, taking into account at least one intermediate position, which may be arranged, for example, centrally as well as off-center to the respective end positions.
  • Fig. 8 shows again in an enlarged view the Fig. 6 with an intermediate compression "£ mid " to show it a special feature that can occur depending on the design.
  • the control line is again partially released, since the piston edge in the mass force cylinder MK rises in accordance with the kinematic conditions during this sagging.
  • oil flows in, for example, through the control channel in the ground.
  • oil sucked in during the gas force action is then discharged again through the control line which has been opened by the raised piston due to inertial force, and the control line is lowered again as a result of the piston descending.
  • the eccentric via which the two pistons of the mass force cylinder and the gas power cylinder are connected to one another, oscillates about one position, for example a middle position.
  • FIGS. FIGS. 9, 10 and 11 show the feasible switching sequences which are possible laterally on the grounding force cylinder MK in the illustrated embodiment with two control channels at the bottom and a single control line.
  • an adjustment is possible as follows: a) Adjustment of £
  • control line of the mass-produced cylinder and control channel of the gas power cylinder blocked; If necessary, the control line of the mass-flow cylinder should be closed by the piston, but must be completely blocked at the latest when switching over to avoid the intake of air.
  • the respective switch positions for the respective compression settings from Figs. 9 to FIG. 11 are shown by way of example in FIGS. 12 to 14 shown.
  • the respective control channels which open into the bottom of the mass force cylinder and the gas-power cylinder, are indicated as the channel MK or the channel GK with the location "down".
  • the control line in turn is referred to as channel MK intermediate position.
  • the respective position of the arrow indicates the respective circuit status: "T" indicates a blocking position, while an arrow indicates the possibility of flow.
  • T indicates a blocking position
  • an arrow indicates the possibility of flow.
  • An actuation for a third switching position provides, for example, to move a stop of the switch.
  • the shifting can be effected beforehand, for example, by the switching operation or else by an actuation unit.
  • a sequential design of the switch allows, for example, the use of a rotary switch. Also allows a sequential design of the switch to realize a middle position via a mechanical latch, which prevents, for example, further drainage of oil through a control channel.
  • an intake of air is prevented, preferably by circuitry. Possibly accidentally an air supply z. B. via a control line, namely, if it inadvertently absorbs air. Such uncontrolled air can cause a malfunction in the system.
  • an air outlet can be provided.
  • a collection point is structurally provided in the system, at which air, in particular also entrained air bubbles accumulate. The collected air can then be drained off via the collection point, for example by means of a valve circuit. It can also be provided that there is another vent through which air can escape from the system.
  • it can be provided to prevent the penetration of air into the system, preferably constructively, namely to prevent it by a valve, for example.
  • a valve for example.
  • this may be provided for a built-in control line check valve.
  • the check valve is integrated in the above circuit. Then there is the possibility with such a switch, in addition to the interconnection of the control line to avoid the suction of air.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un moteur à pistons (1) comportant une bielle qui présente un piston de compression, la bielle présentant un mécanisme de déplacement servant au déplacement du piston de compression et le mécanisme de déplacement présentant un premier piston d'appui (27.1) dans un premier cylindre d'appui (31.1) et un deuxième piston d'appui (27.2) dans un deuxième cylindre d'appui (31.2) de la bielle. Le premier et le deuxième cylindre d'appui (31.1, 31.2) sont reliés respectivement à une première conduite de commande par laquelle un fluide entre et sort du cylindre d'appui concerné pour déplacer le cylindre d'appui concerné (31.1, 31.2), et au moins une deuxième conduite de commande (32) supplémentaire débouche dans au moins un des deux cylindres d'appui (31.2) au moins pour la sortie du fluide servant à déplacer le cylindre d'appui concerné (31.2). L'invention concerne également un procédé permettant de faire fonctionner un moteur à pistons (1), de préférence un moteur VCR selon une des revendications, selon lequel un déplacement vertical d'un piston de compression est effectué au moyen d'un mécanisme de déplacement d'une bielle par lequel le piston de compression est déplacé, un piston d'appui (27.2) du mécanisme de déplacement ouvre ou ferme une conduite de commande (32) débouchant latéralement dans un cylindre d'appui (31.2). L'invention concerne par ailleurs un procédé selon lequel une conduite de commande (32) débouchant latéralement sur un côté forces d'inertie est ouverte ou fermée pour obtenir une position intermédiaire du piston de compression déplaçable.
PCT/EP2015/057474 2014-04-07 2015-04-07 Moteur à pistons Ceased WO2015155167A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112015001700.3T DE112015001700A5 (de) 2014-04-07 2015-04-07 Kolbenmaschine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014004987.6 2014-04-07
DE102014004987.6A DE102014004987A1 (de) 2014-04-07 2014-04-07 VCR-Kolbenmaschine mit VCR-Pleuel

Publications (2)

Publication Number Publication Date
WO2015155167A2 true WO2015155167A2 (fr) 2015-10-15
WO2015155167A3 WO2015155167A3 (fr) 2016-02-18

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WO (1) WO2015155167A2 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017113521A1 (de) 2016-07-28 2017-08-10 FEV Europe GmbH Hubkolbenmaschine, insbesondere als Verbrennungskraftmaschine, mit veränderbarem Verdichtungsverhältnis
DE102017116014A1 (de) 2016-07-29 2017-08-31 FEV Europe GmbH Hubkolbenmaschine mit einstellbarem Verdichtungsverhältnis, insbesondere Hubkolbenbrennkraftmaschine, und Pleuel für eine derartige Hubkolbenmaschine
DE102017120528A1 (de) 2017-09-06 2017-10-19 FEV Europe GmbH VCR-Hubkolbenmaschine
DE102017123726A1 (de) 2017-10-12 2017-11-23 FEV Europe GmbH VCR-Hubkolbenmaschine
DE102017130742A1 (de) 2017-12-20 2018-02-15 FEV Europe GmbH Hubkolbenmaschine mit veränderlichem Verdichtungsverhältnis
US11028770B2 (en) 2018-06-27 2021-06-08 FEV Europe GmbH Connecting rod of an internal combustion engine for changing the compression ratio

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT517511A1 (de) 2015-08-10 2017-02-15 Avl List Gmbh Hubkolbenmaschine, insbesondere brennkraftmaschine
CN108603438B (zh) 2015-12-14 2022-01-25 Avl 里斯脱有限公司 长度可调节的连杆、往复式活塞发动机和车辆
DE102016107967A1 (de) * 2015-12-14 2017-06-14 Hilite Germany Gmbh Pleuel für eine variable Verdichtung einer Brennkraftmaschine
AT519011B1 (de) 2016-05-31 2018-03-15 Avl List Gmbh Hubkolbenmaschine
DE102016008306A1 (de) 2016-07-06 2018-01-11 Avl List Gmbh Pleuel mit verstellbarer Pleuellänge
AT519360B1 (de) * 2017-02-24 2018-06-15 Avl List Gmbh Verfahren zum Betrieb einer Hubkolbenmaschine mit wenigstens einer hydraulisch längenverstellbaren Pleuelstange
DE102017107067A1 (de) 2017-04-03 2017-06-29 FEV Europe GmbH Vorrichtung zum Ändern eines Verdichtungsverhältnis einer Verbrennungskraftmaschine

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EP1426584A1 (fr) 2002-11-27 2004-06-09 FEV Motorentechnik GmbH Bielle pour machine à pistons alternatifs avec taux de compression variablement réglable
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