WO2018006904A1 - Système pour transférer un fluide sous pression - Google Patents

Système pour transférer un fluide sous pression Download PDF

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Publication number
WO2018006904A1
WO2018006904A1 PCT/DE2017/100552 DE2017100552W WO2018006904A1 WO 2018006904 A1 WO2018006904 A1 WO 2018006904A1 DE 2017100552 W DE2017100552 W DE 2017100552W WO 2018006904 A1 WO2018006904 A1 WO 2018006904A1
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WO
WIPO (PCT)
Prior art keywords
pressure medium
connecting rod
pressure
crank pin
valve
Prior art date
Application number
PCT/DE2017/100552
Other languages
German (de)
English (en)
Inventor
Andreas Nendel
Markus Popp
Original Assignee
Schaeffler Technologies AG & Co. KG
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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2018006904A1 publication Critical patent/WO2018006904A1/fr

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
    • F01M2001/062—Crankshaft with passageways
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/027—Arrangements of lubricant conduits for lubricating connecting rod bearings
    • 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
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/06—Crankshafts

Definitions

  • the invention relates to an arrangement for transmitting a pressure medium between a crankshaft and a connecting rod bearing housing mounted on a crank pin of the crank shaft of a Hubkol- benbrennkraftmaschine, wherein the pressure means with a control pressure from at least one provided in the crankshaft pressure medium inlet into at least one in the connecting rod bearing housing provided pressure medium drainage and at least one control chamber of a hydraulically controlled directional control valve is supplied, which directional control valve with a device for changing the compression ratio of the cylinder unit, which is arranged in the connecting rod cooperates.
  • the invention also relates to a connecting rod for a Hubkolbenbrennkraftmaschi- ne with adjustable compression ratio, the effective length for adjusting the compression ratio is adjustable at least two stages, with at least one hydraulic actuating device, the at least one arranged in a piston rod end of the connecting rod eccentric body, at least two with a Hydraulic fluid acted upon pressure chambers of support cylinders, in each of which a control piston is displaceably guided, and at least two piston rods which each connect an actuating piston with the eccentric body, wherein the actuating device via a directional control valve adjustable and hydraulically lockable in their adjustment positions.
  • the actuating device via a directional control valve adjustable and hydraulically lockable in their adjustment positions.
  • the knocking is an uncontrolled self-ignition of the fuel-air mixture.
  • the compression ratio may be increased to improve the corresponding partial load efficiency without the aforementioned knocking occurring.
  • a change in the compression ratio is also particularly advantageous for supercharged reciprocating internal combustion engines with spark ignition, as these overall in terms of charging a low compression ratio is given, to improve the thermodynamic efficiency in unfavorable areas of a corresponding engine map, the compression is to be increased.
  • devices are known from the prior art, which make an adjustment of the distance between a crank pin of a crankshaft and a piston pin.
  • These are different devices, namely those with which the position of the piston relative to the connecting rod is variable, or those that make a change in position of the connecting rod relative to the crankshaft.
  • the connecting rod is connected to the piston via an adjustable eccentric provided on the connecting rod eye, in which a piston pin bearing and a piston pin are arranged.
  • the corresponding eccentric is adjusted by the engine forces occurring in the cylinder unit between the connecting rod on the one hand and the piston pin or the crank pin on the other hand, ie mass and load forces. In the working cycle of the cylinder unit, the acting forces change continuously.
  • the eccentric is expedient to connect the eccentric with two actuating pistons, which act on this to its rotation and hydraulic locking tabs.
  • the respective function of the adjusting piston is adjustable by a directional control valve which is actuated hydraulically or mechanically and, in the case of a hydraulic actuation, is supplied with pressure medium from a connecting rod bearing via a fluid line.
  • An arrangement for transferring pressure medium between a crankshaft and a connecting rod bearing housing mounted on a crank pin of the crankshaft for a device for changing a compression ratio of a Hubkolbenbrenn- engine and provided with the device connecting rod of the type described in the preamble of each of claims 1 and 10 are known from DE 10th 2013 1 1 1 616 A1 known.
  • an eccentric arranged in a connecting rod eye of a connecting rod is provided with an eccentric piston pin bore, wherein the eccentric device has diametrically extending tabs on which act on eccentric rods piston.
  • Guide cylinders, which receive these pistons, are supplied with hydraulic fluid from a connecting rod bearing via oil feed lines, in each of which a non-return valve is arranged.
  • an oil return line is connected to each of the two guide cylinder, which leads to a fluid-operated via a fluid line switching valve.
  • the switching valve should vent one of the two oil return lines into the fluid line acted upon by the engine oil pressure.
  • the lubricating oil of the internal combustion engine is used, which via a radially extending Olaustrittsbohrung of the crank pin of the crankshaft and a circumferentially extending groove portion of a bearing is guided in the aforementioned oil supply lines and the fluid line.
  • the pressure medium with a control pressure from at least one provided in the crankshaft Druckschzulig in at least one provided in the connecting rod bearing housing pressure medium outflow above.
  • Under the connecting rod bearing housing is the section of the connecting rod, which encloses the crank pin of the crankshaft to form a Pleuellagerauges.
  • the pressure medium is supplied to at least one control chamber of a hydraulically controlled directional valve, which cooperates with a device for changing the compression ratio of the cylinder unit, which is arranged in the connecting rod.
  • the at least one pressure medium inflow in at least one of the two annular surfaces which, radially extending from the crank pin, is formed in at least one of the crank webs of the crankshaft.
  • the cooperating with this at least one pressure medium outlet is arranged in at least one of the two annular end faces of the connecting rod bearing housing, so that during a revolution of the crank pin communicates the respective Druckschzulig at least in phases with this associated pressure medium drain.
  • the pressure medium supply of the adjusting device thus takes place in a region of the crank mechanism, which does not serve for the storage of the connecting rod bearing eye on the Kur- pin.
  • the pressure medium inflow can be arranged in the crank arm such that it is connected exclusively to the pressure fluid outflow of the connecting rod housing within a phase in which the crank pin is in the area of a bottom dead center.
  • the Druckschzul should be formed as concentric with the crank pin outlet groove extending over a portion of the annular surface, and it should be designed as the discharge groove in the axial direction of the crank pin opposite the pressure fluid drain, formed in the connecting rod bearing housing fluid bore.
  • the lateral surface of the respective crank pin usually merges into a radius, which is adjoined by a machined surface of the crank arm, which has an annular outer contour.
  • phased Pressure medium transfer is important in reducing pressure pulsations, which can lead to faulty operations of the directional control valve, as these can be reduced to a minimum.
  • a spool of the preferably designed as a 3 / 2- or 4/2 way valve directional control valve is arranged and that the spool is received by a pressed-in a first receiving bore of the connecting rod bearing housing valve housing.
  • the fluid bore can thus be formed as a valve receiving bore which receives a valve housing of the directional control valve.
  • This valve receiving bore is formed as a through hole, which preferably extends in a stepped manner and parallel to the longitudinal central axis of the connecting rod bearing within the connecting rod bearing housing.
  • valve housing also radially extending return bores, which are connected to the return lines, arranged, and further located in the valve housing radially extending discharge holes through which the outflow of the adjusting pressure medium directly to the connecting rod bearing or this indirectly via the oil supply lines also the connecting rod bearing is supplied .
  • the spool is supported in the valve housing via a valve spring and is acted upon at its side facing away from the valve spring end face with the fluid pressure from the pressure medium transfer.
  • a discharge channel is provided, while in the 4/2 way valve the diverted pressure medium can be fed to two different outflow channels.
  • a sliding seal can be provided between the pressure medium inflow and the pressure medium outflow. By means of the sliding seal leaks in the area of the pressure medium transfer are to be avoided. This seal may optionally enclose the fluid bore or the exit groove.
  • the grinding seal preferably has a sealing element, which is displaceably guided in a valve housing of the directional control valve and resiliently supported relative thereto by means of a biasing spring, wherein the sealing element sealingly abuts the annular surface of the crank arm with a sealing surface facing away from the biasing spring.
  • the sealing element may be made of aluminum or of a plastic, for example PTFE. Since the sealing element is resiliently supported by the biasing spring on the valve housing, it can be tracked under the action of this biasing spring in case of wear.
  • the concentric with the crank pin extending outlet groove in predetermined rotational angles of the crank pin with at least one formed in the annular end surface of the connecting rod bearing housing, concentrically extending inlet groove is connectable, wherein the inlet groove extends outside the region of the fluid bore.
  • the aforementioned entrance groove is formed in the end face of the connecting rod bearing housing.
  • the pressure medium supplied to this inlet groove is provided on the one hand for the lubrication of the connecting rod bearing and on the other hand it is to be supplied to the pressure chambers of support cylinders via oil supply lines running inside the connecting rod shaft.
  • a valve module may be arranged, which receives a check valve for each of the oil inlet holes.
  • the second receiving bore is provided at a relatively small distance from the directional control valve and into which the abovementioned valve module is inserted, which receives the two check valves assigned to the oil inlet bores.
  • the two non-return valves can be used from one end face of the valve module, that is, arranged in different bores.
  • valve module with a single through hole into which the two check valves are each inserted from one of the two end faces.
  • this valve module so that the check valves are arranged in radial bores of the valve housing.
  • Each of the cylinder units running in a main bearing block of a crankcase of the reciprocating internal combustion engine, associated with a lubricant supply line and a signal pressure line, which open so separated from each other in the main bearing, that in the different rotational positions of a shaft journal via an inlet bore provided in this pressure medium from the lubricant supply line or the signal pressure line a leading inside the crank arm to the pressure medium inflow of the pressure medium transfer pressure medium channel is supplied.
  • the lubricant supply line is acted upon with the normal lubricant pressure of the oil pump.
  • the signal pressure line can, starting from a higher control pressure delivering pump via a designed as a 4/2-way valve switching valve acted upon with a control pressure or relieved of pressure from the level of normal lubricant pressure.
  • the switching valve is preferably controlled electromagnetically and provided with a spring return. At the start of the reciprocating internal combustion engine, all the switching valves are in a preferred starting position, in which they are moved over the return spring and in which each of the cylinder units is operated with a high compression.
  • the branching lubricating oil channel promotes a sufficient amount of lubricant in - L ü the radial oil outlet of the crank pin, so that the connecting rod bearing has an uninterrupted oil supply.
  • a connecting rod for a reciprocating internal combustion engine with adjustable compression ratio for adjusting the compression ratio in its effective length should be at least two stages adjustable.
  • This is provided with at least one hydraulic adjusting device for adjusting its effective length, the at least one arranged in a piston rod end of the connecting rod eccentric body, at least two acted upon by a hydraulic fluid pressure chambers of support cylinders, in each of which a control piston is slidably guided, and at least two piston rods, each having an actuating piston connect to the eccentric body has.
  • the adjusting device is adjustable via a directional control valve and hydraulically locked in their adjustment positions.
  • a pressure medium transmission is provided between a pressure medium inflow of a crankshaft and a pressure medium outflow of a connecting-rod bearing housing, which is embodied according to one of the above solutions.
  • FIG. 2 shows a section through a main bearing block with a lubricant supply line and a signal pressure line
  • Figure 3 shows a perspective view of a part of a crankshaft with a longitudinal section through a main bearing block, two crank webs and a
  • crank pin wherein a pressure medium channel passes through one of the crank webs
  • Figure 4 shows a perspective view of a part of a crankshaft with a longitudinal section through a main bearing block, two crank webs and a
  • crank pin wherein a pressure medium channel extends through one of the crank webs and branches off from the pressure medium channel, a lubricating oil passage,
  • Figure 5 shows a section in the region of a transition from a crank arm in the
  • FIG. 7 shows a schematic view of a crankshaft with connecting rods for cylinder units I, II and III arranged on its crank pin, FIG.
  • FIG. 8 shows a longitudinal section through a connecting rod arranged on a crank pin, the connecting rod bearing housing having on its front side both the directional valve and a concentrically running inlet groove for the pressure medium which can be supplied to the oil supply lines,
  • FIG 9 shows a hydraulic scheme according to the invention, which is connected to the pressure medium drainage of the pressure medium transmission and Figure 10 shows the hydraulic diagram whose connection to the pressure medium transfer and the different overlaps of the pressure medium outflow are shown with the pressure medium inflow.
  • FIG. 1 denotes a connecting rod for a cylinder unit of a reciprocating internal combustion engine, which consists of a connecting rod upper part 3, partly designed as a connecting rod shank 2, and a connecting rod lower part 4.
  • the connecting rod upper part 3 and the Pleuelunterteil 4 together form a connecting rod bearing housing 5 with a connecting rod bearing eye 5a, via which the connecting rod 1 can be mounted on a crank pin, not shown, a crankshaft.
  • the connecting rod upper part 3 is provided with a connecting rod eye 6 in which an eccentric body 7, a piston pin not shown in detail in FIG. 1, can be arranged in a piston pin bearing eccentrically extending within the eccentric body 7.
  • piston pin a likewise not shown working piston of a cylinder unit of Hubkolbenbrennkraft- machine is guided on the eccentric body 7, wherein a rotation of the eccentric body 7 in a direction to set a relatively low compression ratio and its rotation in the opposite direction to adjust a higher compression ratio leads.
  • the eccentric body 7 is adjusted by the engine forces occurring in the cylinder unit between the connecting rod 1 on the one hand and the piston pin bearing 8 and the crank pin on the other hand, ie mass and gas forces. During the working process of the cylinder unit, the acting forces change continuously.
  • the adjusting pistons 14 and 15 together with cylinder bores 17 and 18, in which they are guided, support cylinders 19 and 20, each support cylinder 19 and 20 having a pressure chamber 21 and 22, respectively.
  • the support cylinder 19 is, as the diameter can be seen, provided on the mass force side, while the support cylinder 20 of the gas force side support of the eccentric lever 9 is used.
  • In the pressure chambers 21 and 22 may from the connecting rod bearing housing 5 serving as a hydraulic medium lubricating oil of the reciprocating internal combustion engine via oil supply lines 24 and 25 flow.
  • the connecting rod bearing eye 5a adjacent a directional control valve 26 is arranged in the connecting rod bearing housing 5, whose longitudinal axis is parallel to a longitudinal central axis 23 of the connecting rod bearing eye 5a.
  • a valve module 27 which receives two check valves 28 and 29, each of which is assigned to one of the oil supply lines 24 and 25.
  • the check valves 28 and 29 lead portions 24a and 25a of the oil supply lines 24 and 25 to the connecting rod bearing eye 5a.
  • an oil return line 30 branches off, which leads to the directional control valve 26.
  • a corresponding region of the oil feed line 25 is connected via an oil return line 31 to the directional control valve 26.
  • a main bearing block 32 is shown in section, wherein the latter has a bearing block upper part 33, which is designed jointly with a crankcase, not shown, and a bearing block lower part 34 which can be screwed thereto.
  • the same arrangement is shown in a perspective partial view, also in section, in FIG.
  • a shaft journal 35 of a crankshaft 36 is mounted relative to the crankcase, for which the main bearing block 32 receives a two-part sliding bearing 38, that is, two bearing shells 39 and 40.
  • FIG. 2 also shows the arrangement of a working piston 79 of the reciprocating internal combustion engine. machine, which is connected via a piston pin 80 with the eccentric body 7, out.
  • the crankshaft 36 also has a crank pin 37.
  • the bearing shells 39 and 40 are provided with recesses 41 and 42, which emerge in detail from the figure 10 and are explained for this. These provide in phases a connection between a signal pressure line 43 and a lubricant supply line 44 on the one hand and a radial inlet bore 45 in the shaft journal 35 on the other hand.
  • the inlet bore 45 is connected to a within a crank arm 46 of the crankshaft 37 extending pressure medium passage 47.
  • a further crank arm 46 ' is connected to a crank web 46 on which the pressure medium channel 47 ends as a pressure medium inlet 49.
  • This pressure medium inflow 49 is, as also apparent from the other figures, phased with a fluid bore 50 in connection, in which the directional control valve 26 mentioned in Figure 1 is arranged. Above this directional valve 26, as further shown in the figure 3, a valve module 52 is provided.
  • FIG. 4 relates to an exemplary embodiment of the invention, which is modified compared to the exemplary embodiment of FIG. 3, in that a lubricating oil channel 53 branches off from the pressure medium channel 47 and is connected to a radial oil outlet 54 in the crank pin 37. Via this radial oil outlet 54, a connecting rod bearing 55 shown in FIG. 3 is lubricated. From the figure 5 is due to a section through the crank arm 46 in the region of the transition into the crank pin shown that the Druckschzumann 49 may be formed as a segmental recess 56, wherein in the illustration a position of the crank arm 46 is shown to the connecting rod bearing housing 5, in an overlap between this segment-like recess 56 and a fluid bore 50 formed as the pressure fluid drain 57 comes about.
  • segment-like recess 56 may also emanate a not shown exit groove which extends over a portion of the annular surface 48 of the crank arm 46.
  • the position of the valve module 52 within the connecting rod shaft 2 is apparent from this illustration. For this purpose is within the connecting rod 2 a likewise parallel to the longitudinal central axis 23 extending receiving bore 58 is provided.
  • FIG. 6 shows in a section the arrangement of the directional control valve 26 in the connecting rod bearing housing 5.
  • the directional control valve 26 has a valve housing 59 and a control slide 60 guided longitudinally displaceably in said valve.
  • a longitudinally extending stepped bore 61 is formed, in which the spool 60 is displaceable under the pressure of the fluid bore 50 against a trained as a compression spring valve spring 62.
  • the spool has a circumferential cam groove 63, via which, depending on the position of the spool 60, one of two return channels 64 and 65 is selectively connectable to a discharge channel 66.
  • the control slide 60 is displaced by the valve spring 62 into a position in which the return passage 64 is connected to the discharge passage 66.
  • An increase in the control pressure in the fluid bore 50 causes the spool 60 is displaced against the force of the valve spring 62 in a position in which it connects the return passage 65 with the discharge channel 66.
  • the return channel 64 is connected to the oil return line 31, while the return channel 65 is to be connected to the oil return line 30.
  • a respective aperture 67 and 68 is provided between the oil return lines 30 and 31 and the return channels 65 and 64.
  • the entire directional control valve 26 is arranged in a receiving bore 69 of the connecting rod bearing housing 5.
  • a sealing element 70 is arranged, which abuts with a sealing surface 71 on the annular surface 48 and is biased in the axial direction via a biasing spring 72.
  • FIG. 7 shows, on the basis of a hydraulic diagram, the pressure medium supply of a total of four main bearing blocks via which the crankshaft 36 is mounted, wherein only the shaft journals 35, 35 ', 35 "and 35"' of the crankshaft are shown.
  • It is a reciprocating internal combustion engine with 3 cylinder units I, II, and III.
  • main bearing blocks, which are associated with shaft journals 35, 35 'and 35 " by means of the pressure medium supply described above, the pressure medium in the Fluid bore 50 and are promoted in the oil supply lines 24 and 25 of the adjustment, in addition, the lubrication and cooling of the corresponding main bearing and connecting rod bearing is to be ensured.
  • a variable displacement pump 73 which promotes the pressure medium to a trained as a 3/2 way valve switching valve 74 which is electromagnetically actuated and via a compression spring 75 assumes a switching position, in all cylinder units a high Compression ratio is set. In this position, the switching valve 74 is held by the compression spring 75 even after stopping the reciprocating internal combustion engine, ie in the de-energized state of the electromagnet, so that the subsequent starting process is also carried out with a high compression ratio.
  • the signal pressure line 43 leads to the main bearing block of the shaft journal 35 and from this also branch off further signal pressure lines 76 and 77 leading to the shaft journals 35 'and 35 ".
  • the variable displacement pump 73 is parallel to this valve arrangement via the lubricant supply line 44
  • FIG. 8 shows a longitudinal section through the connecting rod 1, wherein, as already described, the directional control valve 26 is arranged in the connecting rod housing 5 within the fluid bore 50 and the valve module 52 is located above the latter in the receiving bore 58.
  • the two check valves 28 and 29 are arranged in parallel bores.
  • the connecting rod bearing housing 5 is provided at the end with a concentric inlet groove 78 through which the pressure medium, starting from the Druckstoffzul 49 both in the two oil feed lines 24 and 25 and for lubrication in the connecting rod bearing 45 is performed ,

Abstract

L'invention concerne un système permettant de transférer un fluide sous pression entre un vilebrequin (37) et un corps de palier de bielle (5) d'une bielle (1) d'un moteur à combustion interne à pistons alternatifs, associée à une unité de cylindre, ledit corps de palier de bielle étant monté sur un maneton (37) du vilebrequin (36). Le fluide sous pression est transféré à une pression de commande, d'au moins une amenée de fluide sous pression (49) agencée dans le vilebrequin (36), à une sortie de fluide sous pression (57) agencée dans le corps de palier de bielle (5). Le fluide sous pression est acheminé jusqu'à au moins une chambre de commande d'un distributeur (26) à commande hydraulique, ledit distributeur (26) coopérant avec un dispositif destiné à modifier le rapport de compression de l'unité de cylindre, qui se trouve dans la bielle (1). Afin d'améliorer la charge admissible du coussinet de bielle et la commande hydraulique du distributeur, ladite au moins une amenée de fluide sous pression (49) est réalisée dans au moins une des deux surfaces (48) circulaires qui s'étendent radialement à partir du maneton (37), dans au moins un des flasques (46) du vilebrequin (36), la au moins une sortie de fluide sous pression (57) étant agencée dans au moins une des deux surfaces latérales circulaires du corps de palier de bielle (5), et l'amenée de fluide sous pression (49) concernée communiquant au moins momentanément avec la sortie de fluide sous pression (57) associée pendant une révolution du maneton (37).
PCT/DE2017/100552 2016-07-08 2017-06-30 Système pour transférer un fluide sous pression WO2018006904A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016212466.8 2016-07-08
DE102016212466.8A DE102016212466A1 (de) 2016-07-08 2016-07-08 Anordnung zur Übertragung eines Druckmittels

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WO2018006904A1 true WO2018006904A1 (fr) 2018-01-11

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Cited By (2)

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EP3546723A1 (fr) * 2018-03-29 2019-10-02 ECO Holding 1 GmbH Bielle pour un moteur à combustion interne à compression variable
US10954850B2 (en) 2018-03-29 2021-03-23 ECO Holding 1 GmbH Connecting rod for a variable compression internal combustion engine

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Publication number Priority date Publication date Assignee Title
CN111271150B (zh) * 2020-03-12 2021-01-05 天津大学 应变式机油泵控制系统

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US20120111143A1 (en) * 2009-07-17 2012-05-10 Nissan Motor Co., Ltd. Crankshaft of internal combustion engine provided with multi link-type piston-crank mechanism and multi link-type piston-crank mechanism of internal combustion engine
DE102013210494A1 (de) * 2013-06-06 2014-12-11 Schaeffler Technologies Gmbh & Co. Kg Umschalteinrichtungen für Schaltventile
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DE2920076A1 (de) 1979-05-18 1980-11-20 Kloeckner Humboldt Deutz Ag Anordnung zur oelversorgung eines pleuellagers
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WO2007085738A1 (fr) * 2006-01-26 2007-08-02 Vianney Rabhi Vilebrequin pour moteur a rapport volumetrique variable
US20120111143A1 (en) * 2009-07-17 2012-05-10 Nissan Motor Co., Ltd. Crankshaft of internal combustion engine provided with multi link-type piston-crank mechanism and multi link-type piston-crank mechanism of internal combustion engine
DE102013210494A1 (de) * 2013-06-06 2014-12-11 Schaeffler Technologies Gmbh & Co. Kg Umschalteinrichtungen für Schaltventile
DE102013111616A1 (de) 2013-10-22 2015-04-23 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Umschaltventil und Verbrennungsmotor mit einem solchen Umschaltventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3546723A1 (fr) * 2018-03-29 2019-10-02 ECO Holding 1 GmbH Bielle pour un moteur à combustion interne à compression variable
US10954850B2 (en) 2018-03-29 2021-03-23 ECO Holding 1 GmbH Connecting rod for a variable compression internal combustion engine

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