EP2764229A1 - Ensemble piston pour une chambre de combustion présentant un taux de compression variable, d'un moteur à combustion interne - Google Patents

Ensemble piston pour une chambre de combustion présentant un taux de compression variable, d'un moteur à combustion interne

Info

Publication number
EP2764229A1
EP2764229A1 EP12756660.2A EP12756660A EP2764229A1 EP 2764229 A1 EP2764229 A1 EP 2764229A1 EP 12756660 A EP12756660 A EP 12756660A EP 2764229 A1 EP2764229 A1 EP 2764229A1
Authority
EP
European Patent Office
Prior art keywords
piston
pin
piston pin
internal combustion
combustion engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12756660.2A
Other languages
German (de)
English (en)
Other versions
EP2764229B1 (fr
Inventor
Dieter Nowak
Tilmann RÖMHELD
Michael Wagenplast
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.)
Mercedes Benz Group AG
Original Assignee
Daimler AG
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 Daimler AG filed Critical Daimler AG
Publication of EP2764229A1 publication Critical patent/EP2764229A1/fr
Application granted granted Critical
Publication of EP2764229B1 publication Critical patent/EP2764229B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F02F3/00—Pistons 
    • F02F3/0015—Multi-part pistons
    • F02F3/0069—Multi-part pistons the crown and skirt being interconnected by the gudgeon pin
    • 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
    • F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
    • 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

Definitions

  • Piston assembly for a variable compression ratio having
  • the invention relates to a piston assembly for a changeable
  • Compression ratio having combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • DE 33 46 967 C2 discloses a plunger with variable compression height for internal combustion engines, wherein the piston crown with at least a portion of the
  • Piston ring section axially displaceable on the piston pin receiving the lower part is arranged.
  • the plunger two fillable with pressure oil, interconnected chambers are provided, the respective volume at
  • a first chamber is located as a control chamber directly below the piston head, while a second chamber is arranged as a damping chamber below the control chamber.
  • the pressure oil is guided via valves, one of which is designed as a pressure-limiting valve and arranged between the control chamber and an open space to the crankcase. It is provided that the damping chamber is arranged divided inside the piston and is limited by an emanating from the center of the piston crown approach, a central
  • DE 36 38 783 C2 is a device for controlling the oil supply in a
  • the control chamber is between an inner piston part and arranged on this slidably guided outer piston part.
  • the control chamber is arranged via an oil bore arranged in the inner piston part, in the course of which a non-return valve opening in the direction of the control chamber is inserted, which opens into an oil groove in a connecting rod bushing of the connecting rod articulated on the inner piston part via a hollow piston pin forming an oil reservoir and which is connected to one of the Oil groove through through the shaft of a through
  • Pleuellager worn connecting rod up to a disputedölnutin longitudinal oil hole and a crank pin between the control oil and a main oil hole extending transverse bore connected to the lubricating oil circuit of the internal combustion engine.
  • DE 10 2009 048 172 A1 discloses a piston for an internal combustion engine having a variable compression ratio.
  • the piston comprises a first piston part and a second piston part, which are coupled relative to each other while forming at least a first, with a pressure medium, in particular a pressurized fluid, acted upon and variable in volume chamber. It is provided that at least one switchable
  • Valve means is disposed on the inside of a piston skirt of the piston, by means of which a volume of the pressure medium in the first chamber is adjustable.
  • Combustion chamber is possible.
  • Such a piston arrangement for a combustion chamber having a variable compression ratio, in particular a cylinder, of an internal combustion engine designed in particular as a reciprocating internal combustion engine, in particular of a motor vehicle comprises a piston and a device for variably setting the compression ratio assigned to the combustion chamber
  • the piston assembly further includes a piston pin.
  • the piston pin is coupled to the piston via respective connection areas.
  • the piston pin for example, in receiving openings, in particular
  • the piston received at least partially.
  • the piston pin is the piston with a connecting rod of the internal combustion engine
  • the piston can be articulated via the piston pin and the connecting rod with a crankshaft of the internal combustion engine, so that translational
  • Movements of the piston in the combustion chamber can be converted relative to this in a rotational movement of the crankshaft.
  • the device comprises the piston pin. It has the
  • Piston pin at least one with respect to the connection region of the piston pin eccentrically arranged eccentric element, via which the piston can be coupled to the connecting rod. If the piston pin is coupled to the connecting rod via the eccentric element and the piston pin becomes about the longitudinal central axis of the eccentric element formed at least substantially in the form of a right circular cylinder relative to the connecting rod and about the longitudinal center axis of at least one, at least substantially in the form of a straight circular cylinder connecting portion the piston pin is rotated relative to the piston, so causes this rotation of the piston pin relative to the connecting rod and relative to the piston due to the eccentric arrangement of the piston
  • Compression ratio is realized in a particularly simple and thus cost and space-saving manner. Moreover, it is possible by means of the piston assembly according to the invention to adjust the compression ratio as needed and to different
  • the piston assembly further has not only a very high compactness but also a very high equal part ratio compared to a conventional piston assembly, which allows no adjustment of the compression ratio on. This benefits the low cost.
  • the device comprises at least one control element.
  • the control is movable on the piston relative to the piston and relative to the piston pin between at least two positions.
  • the control element is displaceable obliquely or perpendicular to the longitudinal extent of the piston pin, which is why the control is also referred to as a control slide.
  • the control in the first position, the control causes depending on the rotational position of the piston pin locking of the piston pin or rotation of the piston pin relative to the piston. So either the compression ratio can be maintained or changed
  • Piston arrangement preferably due to centrifugal or inertial forces of the moving piston in the combustion chamber and / or due to prevailing in the combustion chamber and acting on the piston pressure forces.
  • Fig. 1 is a schematic perspective view of a piston pin with a
  • FIG. 2 shows a schematic perspective view of the piston pin according to FIG. 1;
  • Fig. 3 shows a detail of a schematic side view of a piston assembly for a variable compression ratio
  • Cylinder of a reciprocating internal combustion engine with a piston shown in transparent, which is articulated via the piston pin of Figures 1 and 2 with a connecting rod of the piston assembly, wherein the piston assembly comprises means by which the compression ratio is adjustable.
  • FIG. 4 is a schematic side view of the piston of FIG. 3 with a control of the device in its first position;
  • FIG. 5 shows a further schematic side view of the piston according to FIG. 4;
  • Figure 6 is another schematic side view of the piston of Figures 4 and 5 with the control in its second position;
  • FIG. 7 shows a further schematic side view of the piston according to FIG. 6;
  • FIG. 10 shows a detail of a further schematic perspective view of the piston according to FIG. 9;
  • FIG. 10 shows a detail of a further schematic perspective view of the piston according to FIG. 9;
  • FIGS. 9 and 10 are schematic perspective views of the piston according to FIGS. 9 and
  • FIGS. 8a-e show a piston pin 10 of a piston assembly 12 (Fig. 3), via which a piston 14 of the piston assembly with a connecting rod 16 is designed to be designed as a reciprocating internal combustion engine engine articulated.
  • the internal combustion engine comprises a crankshaft 18 which is rotatably mounted in a crankcase about an axis of rotation 20 relative to the crankcase.
  • the crankshaft 18 includes a crank pin on which the connecting rod 16 is articulated via a large connecting rod.
  • the connecting rod 16 further comprises a small connecting rod eye, in which the piston pin 10 is partially received.
  • the piston pin 10 is coupled to the piston 14 via respective connection portions 22.
  • the connecting portions 22 of the piston pin 10 are through a
  • Connecting regions are formed at least substantially in the form of a right circular cylinder.
  • the connecting portions 22 are formed at least partially in each case, in this case as
  • the piston pin 10 is indirectly connected to the piston 14.
  • the piston assembly 12 comprises a
  • Piston pin bushing 28 in which the right connection portion 22 of the piston pin 10 is arranged.
  • the piston pin bushing 28 in the corresponding
  • the piston pin bushing 28 acts as Stop for the piston pin 10 and allows easy mounting of the
  • the piston pin 10 has an eccentric element 23, which at least in
  • the piston pin 10 which has a longitudinal extent indicated by a directional arrow 30, has a receiving opening 32, which is designed, for example, as a passage opening.
  • Receiving opening 32 extends at least substantially perpendicular to the longitudinal extent (direction arrow 30) of the piston pin 10th
  • a locking element in the form of a locking bolt 34 is received in the receiving opening 32.
  • the locking pin 34 is guided in the receiving opening 32 perpendicular to the longitudinal extent of the piston pin 10 relative to the piston pin 10 slidably.
  • FIG. 3 it can be seen that at least the piston pin 10 and the locking pin 34 of a device 36 of
  • Piston assembly 12 are assigned. By means of the device 36, it is possible to adjust the compression ratio of the piston assembly 12 associated cylinder of the internal combustion engine variable.
  • the device 36 also includes a control in the form of a spool 38.
  • the spool 38 is held on the piston 14 and displaceable relative to the piston 14 and relative to the piston pin 10 between two positions.
  • the spool 38 is displaceable only between the two positions.
  • the spool 38 is thus a so-called bistable control piston.
  • a first position shown in particular in FIGS. 4 and 5, of the control slide 38, the latter is held by means of a first magnet.
  • the first magnet is arranged on the piston 14.
  • the spool 38 In the second position shown in particular in FIGS. 3, 6 and 7, the spool 38 is held by means of a second magnet, wherein also the second magnet is held on the piston 14.
  • a sleeve 44 of the device 36 can be seen, in which the spool 38 is slidably received.
  • a movement of the locking bolt 34 between a release position and a locking position of the locking bolt 34 can be effected or prevented or locked.
  • the displacement of the spool 38 between its two positions can in turn be done by means of an actuator, such as an electromagnet or by means of oil pressure.
  • the spool 38 is moved by means of oil pressure.
  • the piston 14 in its piston skirt 40 has two passage openings 42 lying opposite one another.
  • a biasing member 46 for example, an oil spray nozzle, lubricating oil of the internal combustion engine in the grooves 43 and in the
  • the spool 38 By applying the one end face of the spool 38, the spool 38 is displaced in the direction of the other end face, which is not acted upon by lubricating oil.
  • an oil spray nozzle 47 can also be seen, by means of which the piston 14 is sprayed with lubricating oil and thus can be cooled.
  • the biasing element 46 is arranged in the cylinder bore of the cylinder. In other words, the application or the control of the spool 38 takes place from outside the piston 14 via the cylinder bore and thus from outside the piston 14 ago.
  • the grooves 43 which may also be formed as elongated holes serve to receive the lubricating oil via the rotation of the crankshaft 18 and thus over the translational movement of the piston 14 in the cylinder and guide the lubricating oil to the through holes 42 and over to the spool 38th ,
  • the spool 38 serves for the so-called pilot control of lubricating oil of the internal combustion engine, by means of which the locking bolt 34 between at least one release position and at least one locking position of the
  • Locking bolt 34 is moved.
  • the lubricating oil for adjusting the locking bolt 34 is transferred via bearings of the crankshaft 18 on the crankcase to the crankshaft 18 and via appropriate channels on to the connecting rod 16. From the connecting rod 16, the lubricating oil flows to an outer circumferential side circumferentially completely circumferential first groove 48 of the piston pin 10. From the first groove 48, the lubricating oil flows through at least one corresponding connecting channel to a second groove 50 of the piston pin 10, which in the circumferential direction of the piston pin 10 outside circumference just as completely revolving. From the second groove 50, the lubricating oil can flow to corresponding channels 56, 58 in the piston 14.
  • Fig. 5 shows the spool 38 in its first position.
  • the locking bolt 34 is initially in its blocking position, in which it on the side of - relative to the image plane of FIG. 5 - right groove 43 cooperates with the piston 14 and prevents rotation of the piston pin 10 relative to the piston 14.
  • the piston pin 10 can only be rotated in the small connecting rod eye of the connecting rod 16 about the longitudinal central axis of the eccentric element 23 relative to the connecting rod 16, so that the piston 14 is pivotally coupled via the piston pin 10 to the connecting rod 16.
  • the locking pin 34 is partially received in the receiving opening 32 and partially in a arranged on the side of the right groove 43 first receptacle in the piston 14.
  • the first channel 56 in the piston 14 can be supplied with lubricating oil.
  • a supply of the second channel 58 in the piston 14 with lubricating oil is prevented by the spool 38. 5
  • the lubricating oil flows in the first position of the spool 38 from the connecting rod 16 via the grooves 48, 50 in the right first channel 56 and from there on to a right in this position of the piston pin 10 first end side 52nd of the locking bolt 34. This means that the first end face 52 is acted upon by the lubricating oil.
  • the lubricating oil now pushes the locking pin 34 in the radial direction of the piston pin 10 in the receiving opening 32 and so from its blocking position in his
  • a spring element may be arranged, via which the locking pin 34 is supported on the piston pin 10 under Federkraftbeetzung.
  • the spring force is directed in the radial direction of the piston pin 10 to the outside. This means that then the lubricating oil pushes the locking bolt 34 against the spring force into the receiving opening 32 and out of the first receptacle. If the locking pin 34 is completely moved out of the first receptacle, it is in its release position. In the release position, the locking bolt 34 can no longer prevent a relative rotation of the piston pin 10 to the piston 14.
  • the piston pin 10 can then be rotated in the small connecting rod eye of the connecting rod 16 about the longitudinal center axis of the eccentric element 23 relative to the connecting rod 16 and in the receiving openings 26 about the respective longitudinal center axes of the connecting portions 22 relative to the piston 14.
  • Such a relative rotation for example, by mass and / or centrifugal and / or prevailing in the cylinder and acting on the piston 14 compressive forces due to eccentric arrangement of the eccentric member 23 relative to the connecting portions
  • the distance between the piston 14 and the rotation axis is reduced or increases the distance between the piston 14 and a combustion chamber roof of the cylinder, whereby the compression ratio ( ⁇ ) is reduced.
  • the distance between the piston 14 and the rotation axis 20 is increased by pulling the piston 14 away from the rotation axis. This sets a higher compression ratio.
  • the pressing and pulling of the piston 14 causes via its coupling with the
  • Piston pin 10 the rotation of the piston pin 10 relative to the piston 14 and relative to the connecting rod 16 when the locking pin 34 is in its release position.
  • the piston pin 10 rotates by 180 degrees - with respect to the image plane of FIG. 5 - to the left, ie counterclockwise. If the receiving opening 32 is formed as a passage opening, the lubricating oil then acts via the first right channel 56 on a second end face 54 of the first end 52 remote from the first end 52
  • Locking bolt 34 and pushes the locking pin 34 together with the spring force of the spring element in the radial direction outwardly of the receiving opening 32 addition.
  • the locking pin 34 is thus moved from its release position back to its blocking position. Then the locking pin 34 acts on the side of the - related to the image plane of Fig. 5 - left groove 43 with the piston 14 together, so that then again a rotation of the piston pin 10 is prevented relative to the piston 14.
  • the piston pin 10 is locked.
  • the locking bolt 34 is, for example, partially in the receiving opening 32 and partially arranged in a side of the left groove 43 second
  • the lubricating oil is not only used to move the locking bolt 34 but also to lock this in the locked position and thus also fulfills a locking function.
  • the supply of the right-hand first channel 56 is ended with lubricating oil.
  • the left second passage 58 is supplied with lubricating oil.
  • the lubricating oil can then flow from the connecting rod 16 via the grooves 48, 50 in the left second channel 58 and from there to the left in the current position of the piston pin first end face 52. This means that now again the first end face 52 (not the second Face 54) is acted upon with lubricating oil.
  • the lubricating oil pushes the
  • Locking bolt 34 again in its release position.
  • the piston pin can turn 180 degrees again, only this time to the right, so clockwise. This in turn is not caused by an active actuator but essentially passive by the centrifugal and / or mass and / or pressure forces.
  • Piston assembly 12 can be displayed. It can be provided at least one further spool as the spool 38, so that by means of the other
  • Compression ratios is the piston pin 10, for example, over its two
  • Piston pin 10 is mounted. Analogous to the rotation of the piston pin 10 relative to the piston 14 by moving the spool 38 can then
  • Spool be effected so that thereby the piston 14 is adjusted relative to the axis of rotation 20 and relative to the combustion chamber roof.

Landscapes

  • 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)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

Ensemble piston (12) pour une chambre de combustion, en particulier un cylindre, présentant un taux de compression variable, d'un moteur à combustion interne, qui comporte un piston (14), un dispositif (36) pour le réglage variable du taux de compression associé à la chambre de combustion, et un axe de piston (10) qui est accouplé au piston (14) par l'intermédiaire de zones de liaison (22, 24), et grâce auquel le piston (14) peut être accouplé à une bielle (16) du moteur à combustion interne. Selon l'invention, le dispositif (36) comporte l'axe de piston (10) qui comprend au moins un élément excentrique (23) placé excentriquement par rapport aux zones de liaison (22) de l'axe de piston (10) et par l'intermédiaire duquel l'axe de piston (10) peut être accouplé à la bielle (16).
EP20120756660 2011-10-08 2012-09-04 Ensemble piston pour une chambre de combustion présentant un taux de compression variable, d'un moteur à combustion interne Not-in-force EP2764229B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011115417A DE102011115417A1 (de) 2011-10-08 2011-10-08 Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Brennraum einer Verbrennungskraftmaschine
PCT/EP2012/003700 WO2013050100A1 (fr) 2011-10-08 2012-09-04 Ensemble piston pour une chambre de combustion présentant un taux de compression variable, d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2764229A1 true EP2764229A1 (fr) 2014-08-13
EP2764229B1 EP2764229B1 (fr) 2015-05-06

Family

ID=46829699

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20120756660 Not-in-force EP2764229B1 (fr) 2011-10-08 2012-09-04 Ensemble piston pour une chambre de combustion présentant un taux de compression variable, d'un moteur à combustion interne

Country Status (6)

Country Link
US (1) US9309831B2 (fr)
EP (1) EP2764229B1 (fr)
JP (1) JP5917702B2 (fr)
CN (1) CN103874837B (fr)
DE (1) DE102011115417A1 (fr)
WO (1) WO2013050100A1 (fr)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
DE102018205406A1 (de) 2018-04-11 2019-10-17 Hyundai Motor Company Kolbenanordnung und interner verbrennungsmotor
DE102018205404A1 (de) 2018-04-11 2019-10-17 Hyundai Motor Company Kolbenanordnung und interner verbrennungsmotor

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CN104533636A (zh) * 2014-11-05 2015-04-22 张素英 发动机可变压缩比系统及其控制方法
DE102015014887A1 (de) 2015-11-17 2016-07-21 Daimler Ag Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Brennraum einer Verbrennungskraftmaschine
DE102015015884A1 (de) 2015-12-08 2016-08-11 Daimler Ag Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Brennraum einer Verbrennungskraftmaschine
DE102015015882A1 (de) 2015-12-08 2016-08-11 Daimler Ag Kolbenanordnung für einen veränderbares Kompressionsverhältnis aufweisenden Brennraum einer Verbrennungskraftmaschine
CN105604728B (zh) * 2016-01-20 2017-12-26 吉林大学 电机驱动滑块式压缩比活塞
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DE102016005973A1 (de) 2016-05-13 2017-02-16 Daimler Ag Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Zylinder einer Hubkolbenmaschine
DE102016005950A1 (de) 2016-05-13 2017-02-16 Daimler Ag Kolbenanordnung für einen ein veränderbares Kompressionsverhältnis aufweisenden Zylinder in der Hubkolbenmaschine
CN105840303B (zh) * 2016-05-13 2018-07-20 吉林大学 一种偏心轴套传动的可变压缩比活塞连杆组件
CN107489525B (zh) * 2016-12-24 2020-01-10 北汽福田汽车股份有限公司 发动机及车辆
KR20190126504A (ko) * 2018-05-02 2019-11-12 현대자동차주식회사 가변압축비 엔진

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Publication number Priority date Publication date Assignee Title
DE102018205406A1 (de) 2018-04-11 2019-10-17 Hyundai Motor Company Kolbenanordnung und interner verbrennungsmotor
DE102018205404A1 (de) 2018-04-11 2019-10-17 Hyundai Motor Company Kolbenanordnung und interner verbrennungsmotor

Also Published As

Publication number Publication date
WO2013050100A1 (fr) 2013-04-11
CN103874837B (zh) 2016-08-17
US20140311439A1 (en) 2014-10-23
JP2014529038A (ja) 2014-10-30
US9309831B2 (en) 2016-04-12
DE102011115417A1 (de) 2013-04-11
CN103874837A (zh) 2014-06-18
JP5917702B2 (ja) 2016-05-18
EP2764229B1 (fr) 2015-05-06

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