• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to a device (1) for friction measurement on a cylinder-piston arrangement, wherein a reciprocating piston (3) in one of a cylinder head (9) decoupled cylinder liner (2) of a bushing unit (23) is arranged and the Bushing unit (23) is arranged in a bearing carrier connected to a sensor carrier (8), which has a concentric to the cylinder axis (21) formed rotationally symmetrical receiving area (13) for the cylinder liner (2), wherein preferably the cylinder liner (2) at least one Kühlflüsssmattermantel ( 12) is assigned. In order to enable a simple replacement of the cylinder liner (2), it is provided that the liner unit (23) is mounted in the liner carrier (8) via a conical seat (14), wherein preferably at least one conical inner circumferential surface of the receiving region (13) has a first seating surface (13). 14a) and a reciprocal to the first seat (14a) shaped conical outer surface (19a, 19b) of the liner unit (23) forms a second seat surface (14b) of the conical seat (14) for receiving and centering the cylinder liner (2).
    公开号:AT514582A4
    申请号:T50639/2013
    申请日:2013-10-04
    公开日:2015-02-15
    发明作者:Michael Erich Hammer；Wolfgang Meldt
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a device for measuring friction on a cylinder-piston arrangement, wherein a reciprocating piston is arranged in a cylinder liner of a bushing unit decoupled from a cylinder head and the liner unit is arranged in a bearing carrier connected to a sensor carrier, which has a rotationally symmetrical receiving region formed concentrically with the cylinder axis for the cylinder liner, wherein preferably at least one cooling jacket is associated with the cylinder liner.
    From the integration of the forces along the piston race in the cylinder direction, the friction between the piston group consisting of piston and piston rings and the cylinder running surface can be determined.
    From WO 2012/062724 Al a device for friction measurement on a cylinder-piston assembly is known, wherein an inner circumferential surface of the cylinder liner is sealed relative to a cylinder head by between the inner circumferential surface and a projecting into the cylinder liner paragraph of the cylinder head, a sealing element is arranged.
    A similar device is disclosed by JP 2010-243390A.
    From JP 60-031037 A, a measuring device for measuring the friction of a piston reciprocating in a cylinder liner is known. In this case, a retaining ring is arranged between the cylinder head and a liner carrier, wherein between the retaining ring and the upper end of the cylinder liner a annular gap is formed, which is filled by a metallic sealing plate.
    From JP 59-088638 A a device for measuring the piston friction of an internal combustion engine is known, wherein the cylinder liner is arranged in a cylinder, and wherein between the cylinder and the cylinder liner more O-rings are arranged.
    In order to be able to test different cylinder liners, in cylinder friction measuring devices of the type mentioned, the cylinder liners must be frequently replaced.
    Known friction measuring devices have the disadvantage that when the cylinder liner is replaced, the liner carrier must be separated from the force sensor. This necessitates recalibration of the sensors every time the cylinder liners are replaced. Furthermore, with every replacement of the cylinder liner, the coolant guide must be leak-proofed with relatively great effort.
    The object of the invention is to avoid these disadvantages and to allow easy replacement of the cylinder liner.
    According to the invention, this is accomplished by supporting the bushing unit via a conical seat in the bushing carrier, wherein preferably at least one conical inner lateral surface of the receiving region, a first seating surface and a tapered outer circumferential surface of the bushing unit reciprocally shaped to the first seating surface form a second seating surface of the conical seat for receiving and centering the cylinder liner.
    As a result, the bushing unit having the cylinder liner can be easily inserted into and removed from the liner carrier without having to disassemble the liner carrier. A change of the cylinder liner can thus take place without having to recalibrate the sensors (force sensors). The conical seat allows easy self-centering of the cylinder liner in the liner carrier transversely to the cylinder axis and ensures a correct installation of the cylinder liner.
    The bushing support may directly or indirectly receive the cylinder liner. In an indirect mount embodiment, the liner assembly includes a bushing frame with the cylinder liner disposed in the bushing frame, and cylinder liner and bushing frame may be fixedly interconnected, in particular non-destructively non-destructively. The socket frame can form the second seat. It is particularly advantageous if the at least one coolant jacket is formed between the sleeve frame, which is preferably sleeve-like, and an outer jacket surface of the cylinder liner. In order to achieve leakage as easy as possible, can
    Cylinder liner and bushing frame be connected by pressing and / or casting together. This allows for a fluid tight connection between the cylinder liner and liner frame without the need for further seals.
    The coolant jacket may be disposed, at least in part, on and molded into the outer circumference of the cylinder liner and / or the inner periphery of the liner frame.
    Preferably, the first seating surface has an opening angle towards the cylinder head relative to the cylinder axis of the cylinder liner, which is preferably between 5 ° and 15 °, more preferably about 10 °.
    When the cylinder liner is received indirectly by the liner carrier, the liner frame is located between the liner carrier and the cylinder liner. The conical seat is thus formed by the liner carrier and bushing frame. A tapered outer circumferential surface of the bushing frame formed reciprocally to the first seating surface of the conical seat in this case forms a second seating surface of the conical seat.
    On the other hand, when the cylinder liner is directly received by the liner carrier, the tapered seat is formed by the liner carrier and the cylinder liner itself. In this case, a tapered outer surface of the cylinder liner, preferably a bushing collar of the cylinder liner, which is reciprocal to the first seating surface of the tapered seat, forms the second seating surface of the tapered seat.
    The cylinder liner and / or bushing frame may be secured to the liner support via a retainer.
    The invention will be explained in more detail below with reference to the non-limiting exemplary embodiments illustrated in the figures. Show it:
    1 shows a device according to the invention in a longitudinal section in a plane containing the cylinder axis, in a first embodiment variant,
    1a shows the detail I of Fig. 1,
    2 barrel liner and cylinder liner of the first embodiment shown in Fig. 1 in a schematic longitudinal section,
    3 runner carrier and cylinder liner in a second embodiment variant in a schematic longitudinal section,
    Fig. 4 liner carrier and cylinder liner in a third
    Embodiment variant in a schematic longitudinal section and
    Fig. 5 liner carrier and cylinder liner in a fourth embodiment variant in a schematic longitudinal section.
    Functionally identical parts are provided in the following embodiments with the same reference characters.
    The friction force measuring device 1 shown in FIG. 1 between a piston 3 reciprocating in a cylinder liner 2 of a liner unit 23 comprises a base 4, a base 5, a sensor support 6 for receiving 3-D force sensors 7, a liner support 8, and a Cylinder head 9 on. The base plate 5 is fastened to the base unit 4 via screws (not shown). The cylinder liner 2 is fastened to the liner carrier 8 via a retaining ring 10, the retaining ring 10 being screwed to the liner carrier 8 by means of screws 11. The liner carrier 8 is fixedly connected via the force sensors 7 by retaining screws 24 with the sensor carrier 6 andweiters screws 20 with the base plate 5. In the area between the cylinder liner 2 and the liner carrier 8, a coolant jacket 12 is formed, which is connected to not shown inlet and outlet lines. The bushing unit 23 has the cylinder liner 2 forming the cylinder for the piston 3, together with the bushing collar 18, the coolant jacket 12 and, in the embodiments shown in FIGS. 1 and 2, a bushing frame 17 receiving the cylinder liner 2.
    As can be seen in Fig. 1, the cylinder head 9 has a protruding into the cylinder liner 2 disc-shaped shoulder 15, in whose outer circumferential surface an annular groove for receiving an annular sealing element 16 is arranged, which is similar to a piston ring by the gas forces against the inner jacket surface 2a of the cylinder liner 2 is pressed. Between the sealing element 16 and the upper edge 2b of the cylinder liner 2, an axial distance a is provided in which manufacturing tolerances of the cylinder liner 2 and the cylinder head 9 are taken into account (FIG. 1a).
    The special sealing by means of the annular sealing element 16 and the shoulder 15 in the cylinder head 9 prevents the gas forces from acting axially on the cylinder liner 2. Thus, these also have no direct influence on the measurement result and it is mainly the frictional forces of the piston 3 and the piston side forces transmitted to the force sensors 7. The cylinder liner 2 is thus largely decoupled from the base unit 4 and from the cylinder head 9 and only connected thereto by the sealing element 16 and the force sensors 7.
    In order to reduce the normal forces acting on the force sensors 7 in the measuring operation of the engine, which do not stem from the movement of the piston 3 (forces due to different thermal expansions) and which can thus falsify the measurement result, it must be ensured that before commencement the measurements have the force acting on the force sensor 7 parts (liner holder 8, sensor carrier 6) have similar temperatures. In this way, similar thermal expansions of these parts can be realized and thus the influence of the resulting transverse forces on the force sensors 7 can be reduced.
    For this purpose, the base plate 5 is provided with Konditionierkanälen 22 with a not shown inlet and an outlet for cooling liquid to bring the base plate 5 and thus screwed thereon sensor carrier 6 and arranged in the same Kühlflüssigkeitskreislauf liner carrier 8 to the same Tem¬peratur.
    The liner carrier 8 has a rotationally symmetrical receiving region 13 for the cylinder liner 2. The inner diameter D of the receiving region 13 is greater in at least one first portion 13a near the cylinder head than the inner diameter d of the receiving portion 13 in a cylinder head second portion 13b.
    In particular, the receiving area 13 may be formed conically, wherein a conical inner circumferential surface of the receiving area 13 forms a first seat surface 14aein Kegelsitzes 14 for receiving the cylinder liner 2. A tapered outer circumferential surface of the cylinder liner 2, in particular a bushing collar 18 of the cylinder liner 2 (FIGS. 3 to 5) or the bushing frame 17 (FIG. 2) formed reciprocally relative to the first seating surface 14 a forms a second seating surface 14 b of the cone seat 14.
    The tapered first and second seating surfaces 14a, 14b each have an opening angle α opening in the direction of the cylinder head 9 with respect to the cylinder axis 21.
    Between the cylinder liner 2 and the cylinder head 9, a gap s in the axial direction is necessary, which results from the manufacturing tolerances of the liner unit 23, in particular the cylinder liner 2 and the liner support 8. The choice of the opening angle α depends, on the one hand, on the radial manufacturing tolerances of the bushing unit 23, in particular the cylinder liner 2 and the bushing frame 17, and of the bush carrier 8, and the axial displacements of the bushing unit 23 that occur therewith.
    With the production-related maximum possible radial deviation sL of the bushing unit 21 and the maximum possible radial deviation sc of the bushing frame 17 from the design value, the following results for the opening angle α:
    On the other hand, self-locking of the tapered first and second seats 14a, 14b is undesirable.
    To avoid self-locking, the opening angle α should be: a > arctan μΗ, where μΗ is the coefficient of static friction between the first and second seating surfaces 14a, 14b.
    In consideration of these conditions, the opening angle α should be between about 5 ° and 15 °, more preferably about 10 °.
    In the first embodiment shown in FIGS. 1 and 2, the cylinder liner 2 is arranged in a sleeve-like bushing frame 17, which surrounds the cylinder liner 2. The cylinder liner 2 is cylindrical. The inner surface of the bushing frame 17 is formed isotriform and receives the cylinder liner 2. The tapered second seat surface 14b is formed by the outer jacket 19a of the female frame 17 which is tapered corresponding to the first seating surface 14a. The bushing frame 17 does not need to extend in the axial direction over the full length of the cylinder liner 2, it is sufficient if the cylinder liner 2 is supported by the bushing frame 17 in an upper part facing the cylinder head 9, for example the upper half. The coolant jacket 12 is disposed between the cylinder liner 2 and the female frame 17. In the illustrated first embodiment, the cooling liquid jacket 12 is formed by an annular recess 17 a of the bushing frame 17. It is also possible, however, to arrange the coolant jacket 12 in the cylinder liner 2, partially in the cylinder liner 2 and partially in the liner frame 17. The bushing frame 17 is liquid-tightly connected to the cylinder liner 2, for example, pressed. But there are also soldering, welding and / or adhesive joints possible.
    Figs. 3 to 5 show embodiments without a separate socket frame, which differ only by the position of the coolant jacket 12 from each other. The second seat surface 14b of the conical seat 14 is formed in each of these variants by the outer circumferential surface 19b of the bushing collar 18 of the cylinder liner 2.
    In the second and third embodiment variants shown in FIGS. 3 and 4, the coolant jacket 12 is arranged in each case in the sleeve collar 18 of the cylinder liner 2.
    In the second embodiment shown in Fig. 3, the coolant jacket 12 is formed by an annular cavity 18a within the sleeve collar 18. This cavity 18a may be formed, for example, by a lost core. A separate sealing of the coolant jacket 12 is not required. The second embodiment variant thus represents a low-part further development of the first embodiment variant.
    In contrast, in the third embodiment of the invention shown in Fig. 4, the cooling liquid jacket 12 is formed by a groove-like annular recess 18b in the outer jacket of the bushing collar 18.
    FIG. 5 shows a further embodiment in which the coolant jacket 12 is formed by an annular recess 8a in the receiving region 13 of the liner carrier 8.
    With correspondingly fine machining of the first and second seat surfaces 14a, 14b of the conical seat 14, the coolant jacket 12 is self-sealing upon insertion of the cylinder liner 2 into the conical seat 14 in the third and fourth embodiments shown in Figs. 4 and 5, without the need for further sealing elements.
    Each of the illustrated embodiments has the advantage that for tests of different cylinder liners 2, these can be exchanged very easily, without the retaining screws 24 or screws 20 connecting the liner carrier 8 and the sensor carrier 6 having to be loosened. This saves extravagant calibration work. For an exchange of the cylinder liner 2, this - in the first embodiment - together with the bushing frame 17 - pulled out of the liner carrier 8 and replaced by another cylinder liner 2. The new cylinder liner 2 centers itself in the conical seat 14 itself. The self-centering conical seat 14 allows easy separation of the cylinder liner 2 from the liner carrier 8.
    权利要求:
    Claims (11)
    [1]
    1. A device (1) for friction measurement on a cylinder-piston arrangement, wherein a reciprocating piston (3) in a cylinder head (2) decoupled from a cylinder liner (2) of a bushing unit (23) is arranged and the bushing unit (23) is disposed in a liner carrier (8) connected to a sensor carrier, which has a rotationally symmetrical receiving area (13) for the cylinder liner (2) concentric with the cylinder axis (21), and wherein at least one cooling liquid jacket (12) is associated with the cylinder liner (2), characterized in that the bushing unit (23) is mounted over a conical seat (14) in the liner carrier (8), preferably at least one tapered inner surface of the receiving area (13), a first seating surface (14a) and a tapered outer circumferential surface formed reciprocally to the first seating surface (14a) (19a, 19b) of the bushing unit (23) has a second seat bottom surface (14b) of the conical seat (14) for receiving and centering the cylinder liner (2).
    [2]
    A device (1) according to claim 1, characterized in that the bushing unit (23) comprises a bushing frame (17), the cylinder bushing (2) being located in the bushing frame (17), and preferably comprising a cylinder liner (2) and bushing frame (17) , Particularly preferably insoluble, are interconnected.
    [3]
    A device (1) according to claim 2, characterized in that the second seat surface (14b) is formed by the bushing frame (17).
    [4]
    4. Device (1) according to claim 2 or 3, characterized in that between the - preferably substantially sleeve-like bushing frame (17) and the cylinder liner (2) of the coolant jacket (12) is formed.
    [5]
    5. Device (1) according to one of claims 2 to 4, characterized in that cylinder liner (2) and bushing frame (17) are connected to each other by pressing and / or casting.
    [6]
    6. Device (1) according to one of claims 1 to 5, characterized in that the coolant jacket (12) at least partially in the cylinder liner (2) is formed.
    [7]
    7. Device (1) according to one of claims 1 to 6, characterized in that the cooling liquid jacket (12) - at least partially - in the socket frame (17) is formed.
    [8]
    8. Device (1) according to one of claims 1 to 7, characterized in that the cooling liquid jacket (12) - at least partially - in the liner carrier (2) is formed.
    [9]
    9. Device (1) according to one of claims 1 to 8, characterized in that the first seat surface (14a) with respect to the cylinder axis (21) in the direction of the cylinder head (9) opening angle (a), which preferably between 5 ° and 15 °, more preferably about 10 °.
    [10]
    Device (1) according to any one of Claims 6 to 9, characterized in that the second seat (14b) is formed by the cylinder liner (2).
    [11]
    11. Device (1) according to one of claims 1 to 10, characterized in that the cylinder liner (2) and / or the bushing frame (17) via a retaining ring (10) on the liner carrier (8) is attached.
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    EP3052794B1|2018-12-26|
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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPH09280976A|1996-04-10|1997-10-31|Nippon Soken Inc|Apparatus for measuring force acting between piston and cylinder of internal combustion engine|
    JPH118801A|1997-06-19|1999-01-12|Hitachi Ltd|Image pickup device|
    US20020083913A1|2000-12-28|2002-07-04|Kyoung-Pyo Ha|Liner mounting structure for measuring piston friction|
    JP2009236562A|2008-03-26|2009-10-15|Honda Motor Co Ltd|Engine frictional force measuring device|
    CN103293005A|2013-05-31|2013-09-11|中国兵器工业集团第七0研究所|Floating cylinder liner mechanism for friction test of cylinder liner and piston in ignition state|AT516996B1|2015-03-30|2017-11-15|Avl List Gmbh|DEVICE FOR MEASURING THE FRICTION OF A CYLINDER PISTON ARRANGEMENT|DE3134768C2|1981-09-02|1984-12-20|Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn|Piston-cylinder unit for internal combustion piston machines, in particular for gasoline and diesel engines|
    US4562799A|1983-01-17|1986-01-07|Cummins Engine Company, Inc.|Monolithic ceramic cylinder liner and method of making same|
    CN2066981U|1989-12-29|1990-12-05|武汉工学院|Suspending integrate ring type wear simulation test machine for engine cylinder jacket-piston ring|
    JPH08151924A|1994-11-28|1996-06-11|Isuzu Ceramics Kenkyusho:Kk|Gas engine having combustion chamber in piston outer periphery|
    DE19861213B4|1997-07-21|2005-06-09|Cummins Inc., Columbus|Replaceable cylinder liner for internal combustion engine with cylinder head and engine block - involves locating it's axial position within engine block by midstop, flowing coolant into passage and sealing cooling passage with interference fit between liner and block|
    AT2906U1|1998-06-18|1999-06-25|Avl List Gmbh|CYLINDER RIFLE FOR A LIQUID-COOLED INTERNAL COMBUSTION ENGINE|
    JP2005201084A|2004-01-13|2005-07-28|Toyota Motor Corp|Cylinder block|
    US7975601B2|2008-10-17|2011-07-12|Caterpillar Inc.|Engine cylinder liner|
    JP2010243390A|2009-04-08|2010-10-28|Honda Motor Co Ltd|Engine-friction force measuring instrument|
    AT510444B1|2010-11-09|2012-04-15|Avl List Gmbh|DEVICE FOR CRANKSHAFT-LOADED MEASUREMENT|
    DE102011102203A1|2011-05-21|2012-11-22|Mahle International Gmbh|Cylinder liner and assembly of at least one cylinder liner and a crankcase|DE102015109332B3|2015-06-11|2016-12-15|Gottfried Wilhelm Leibniz Universität Hannover|Device and method for friction force measurement|
    JP6454782B2|2016-07-19|2019-01-16|Ｔｐｒ株式会社|Internal combustion engine manufacturing method, internal combustion engine, and connecting cylinder|
    KR101960449B1|2017-05-24|2019-03-20|국민대학교 산학협력단|Apparatus for measuring friction|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA50639/2013A|AT514582B1|2013-10-04|2013-10-04|Device for friction measurement on a cylinder-piston arrangement|ATA50639/2013A| AT514582B1|2013-10-04|2013-10-04|Device for friction measurement on a cylinder-piston arrangement|
    US15/023,239| US10073027B2|2013-10-04|2014-10-02|Device for measuring friction on a cylinder/piston arrangement|
    EP14780839.8A| EP3052794B1|2013-10-04|2014-10-02|Device for measuring friction on a cylinder/piston arrangement|
    JP2016520015A| JP6434966B2|2013-10-04|2014-10-02|Device for measuring friction in cylinder piston structures|
    CN201480054602.3A| CN106414980B|2013-10-04|2014-10-02|For measuring the device to rub on cylinder-piston arrangements|
    PCT/EP2014/071138| WO2015049330A1|2013-10-04|2014-10-02|Device for measuring friction on a cylinder/piston arrangement|
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