• 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) having at least one piston ring is arranged in a cylinder liner (2) with at least one sealing element (17) between Cylinder liner (2) and a cylinder head (9). In order to improve the measurement accuracy is provided that an inner circumferential surface (2a) of the cylinder liner (2) relative to the cylinder head (9) is sealed.
    公开号:AT510444A4
    申请号:T1838/2010
    申请日:2010-11-09
    公开日:2012-04-15
    发明作者:Bernhard Dipl Ing Kometter；Olivier Roques；Wolfgang Meldt
    申请人:Avl List Gmbh；
    IPC主号:
    专利说明:

    - 1 - 56096
    The invention relates to a device for kegelelwinkelaufgelösten measurement on a cylinder-piston assembly, wherein a at least one piston ring exhibiting, reciprocating piston is arranged in a cylinder liner, with at least one sealing element between the cylinder liner and a cylinder head.
    From the integration of the forces along the piston raceway 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 JP 60-031037 A a measuring device for measuring the friction of a reciprocating in a cylinder liner piston 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 an annular gap is formed, which is filled by a metallic sealing plate.
    From JP 59-088638 A a device for measuring the piston friction in an internal combustion engine is known, wherein the cylinder liner is arranged in a cylinder, and wherein between the cylinder and the cylinder liner a plurality of O-rings are arranged.
    Known friction measuring devices have the disadvantage that the sealing elements for the cylinder liner, in particular for sealing between cylinder liner and cylinder head, cause forces in the direction of movement of the piston group on the cylinder liner, which falsify the measurement and subsequently the integration of the piston group friction.
    The object of the invention is to avoid these disadvantages and to increase the measuring accuracy in a device for measuring friction of the type mentioned above.
    According to the invention this is achieved in that an inner circumferential surface of the cylinder liner is sealed relative to the cylinder head, wherein preferably a sealing element is arranged between the inner circumferential surface and a protruding into the cylinder liner paragraph of the cylinder head.
    It is particularly advantageous if the sealing element is formed by a sealing ring, preferably a piston ring. The sealing element can be arranged in an annular groove of an outer circumferential surface of the paragraph. - 2 -
    The special sealing by means of the sealing ring and the shoulder in the cylinder head prevents the gas forces from acting axially on the bushing. Thus, these also have no influence on the measurement result and only the frictional forces of the piston or Koibenseitenkräfte be transferred to the sensor.
    The liner is thus decoupled from the basic unit and is connected only by the sealing ring and the sensor.
    It is preferably provided that the cylinder liner is arranged in a liner carrier, wherein the cylinder liner is secured with a retaining ring on the liner carrier. In order to ensure a constant sealing blade between the heel in the cylinder head and the cylinder liner, it is particularly advantageous if two opposite centering holes for receiving a preferably removable centering pin are provided for centering the cylinder head in the bushing.
    In order to avoid distortion of the measurement result by measuring forces due to different thermal expansions of forces acting on the force transducer, the base plate has at least one Konditionierkanai with an inlet and an outlet for cooling fluid through which the base plate and thus the sensor carrier and the screwed thereon Carrying cylinder carrier in the same coolant circuit to the same temperature.
    Furthermore, the force of the sealing element on the cylinder liner and thus the influence of the Ringreibkraft of the sealing element can be reduced to the measurement result when the sealing element in the region of the cylinder liner facing the outer lateral surface has an annular shoulder, which forms a cylinder liner facing outer annular surface whose diameter smaller than the largest diameter of the sealing element. Ideally, a compensation of acting on the sealing element attacking gas forces can be achieved.
    The invention is explained in more detail below with reference to the figures:
    1 shows an inventive device in a section along the line I - I in Fig. 2, Fig. 2 shows this device in a section along the line II -II in Fig. 1, Fig. 3 shows the detail III of FIG. 2, FIG. 4 shows the device in an oblique view, FIG. 5 shows detail V from FIG. 4, FIG. 6 shows a base plate in a section - 3 - according to line VI - VI in FIG. 1 and FIG. 7 shows detail VII from Fig. III in a variant.
    The device 1 for friction measurement of the frictional forces between a reciprocating in a cylinder liner 2 piston 3 comprises a base unit 4, a base plate 5, a sensor carrier 6 for receiving 3-D force sensors 7, a liner carrier 8 and a cylinder head. 9 on. The cylinder liner 2 is attached via a retaining ring 10 on the liner carrier 8, wherein the retaining ring 10 is screwed by means of screws 11 on the retaining ring carrier 8. Between the cylinder liner 2 and the liner carrier 8 a Kühiflüssigkeitsmantel 12 is ausgebiidet, which is connected to inlet and outlet lines 12a, 12b. Between the Zylinderiaufbuchse 2 and the liner carrier 8, a sealing ring 14 is disposed in a circumferential groove 13. Reference numeral 20 denotes a cylinder head carrier.
    The cylinder head 9 has a projecting into the Zylinderiaufbuchse 2 disk-shaped shoulder 15, in whose outer lateral surface 15a an annular groove 16 is formed. In the annular groove 16, an annular sealing element 17 is arranged, which is pressed similar to a piston ring by the gas forces against the inner circumferential surface 2 a of the Zylinderiaufbuchse 2.
    Due to the special sealing by means of the annular sealing element 17 and the shoulder 15 in the cylinder head 9 prevents the gas forces acting axially on the Zylinderiaufbuchse 2. Thus, these also have no influence on the measurement result and only the frictional forces of the piston 3 or the piston side forces are transmitted to the force sensors 7. The Zylinderiaufbuchse 2 is thus completely decoupled from the basic unit 4 and the cylinder head 9 and is connected to this only by the sealing element 17 and the force sensors 7,
    In order to ensure a constant sealing gap 18 between the shoulder 15 of the cylinder head 9 and the inner lateral surface 2a of the cylinder liner 2, between the liner carrier 8 and the cylinder head 9 is a centering device 19 consisting of a first centering bore 19a in the liner carrier 8 and a second centering bore 19b in the cylinder head 9, as well as a centering pin 19c introduced into the centering bores 19a, 19b. Each centering pin 19c is removed after assembly of the cylinder head 9 again.
    In order to reduce the forces acting normal to the piston running direction on the force sensors 7 in the measuring operation of the engine, which does not originate from the movement of the piston 3 (forces due to different thermal expansions) and thus - 4 - can reduce the measurement result must be ensured in that prior to the measurements, the parts acting on the force sensor 7 (liner carrier 8, sensor carrier 6) have similar temperatures. This allows similar thermal expansion of these parts 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 Konditionierkanäten 22 with an inlet 23 and an outlet 24 for cooling fluid to bring the base plate 5 and thus screwed thereon sensor carrier 6 and arranged in the same Kühiftüssigkeitskreislauf liner carrier 8 to the same temperature (Fig. 6).
    Furthermore, the force of the sealing element 17 on the cylinder liner 2 and thus the influence of the Ringreibkraft of the sealing element 17 can be reduced to the measurement result by a shoulder 25 with the height a in the sealing element 17, ideally even a balance of the attacking gas forces can be achieved. As shown in Fig. 7, the sealing element 17 In the region of the cylinder liner 2 facing outer surface 17a an annular shoulder 25 has on the side of the piston 3 a step-like shoulder 25, which may be formed for example by a circumferential milled recess. The annular shoulder 25 forms a cylinder liner 2 facing the outer annular surface 25a, the diameter d is smaller than the largest diameter D of the sealing element 17. Between the sealing element 17 and the annular groove 16 is an axial and a radial gap 16a, 16b, so on the inside of the sealing element 17 of the gas pressure pi is applied. By paragraph 25 also acts on the annular surface 25a with the height a of the internal gas pressure p. The preload force Fv of the sealing element 17, as well as the frictional force FR of the sealing element 17 in the annular groove 16, thus act on the sealing element 17 as a consequence of the internal gas pressure p (the axial force Fgz, the radial force Fgn, and the radial force Fgr2 The resulting force FL on the cylinder liner 2 results with the coefficient of friction μ thus:
    F l = Fv + F 9rl * Fg, 2 "Fgz * P
    Ideally, FL = FV so that only the relatively small biasing force Fv of the sealing element 17 remains.
    权利要求:
    Claims (8)
    [1]
    * · · · * * * *

    - 5 -

    1. A device (1) for friction measurement on a cylinder-piston arrangement, wherein a reciprocating piston (3) having at least one piston ring is arranged in a cylindrical bushing (2), with at least one sealing element (17) between the cylinder bushing (2) and a cylinder head, characterized in that an inner circumferential surface (2a) of the Zylinderiaufbuchse (2) relative to the cylinder head (9) is sealed.
    [2]
    2. Device (1) according to claim 1, characterized in that between the inner circumferential surface (2a) and in the Zylinderiaufbuchse (2) projecting shoulder (15) of the Zyiinderkopfes (9), a sealing element (17) is arranged.
    [3]
    3. Device (1) according to claim 2, characterized in that the sealing element (17) is formed by a sealing ring, preferably a piston ring.
    [4]
    4. Device (1) according to claim 2 or 3, characterized in that the sealing element is arranged in a Ringnot an outer circumferential surface (15 a) of the shoulder (15).
    [5]
    5. Device (1) according to one of claims 1 to 4, characterized in that the Zylinderiaufbuchse (2) in a bushing carrier (8) is arranged, wherein the Zylinderiaufbuchse (2) with a retaining ring (10) attached to the liner carrier (8) is.
    [6]
    6. Device (1) according to claim 5, characterized in that for centering the cylinder head (9) in the Zylinderiaufbuchse (2) of the cylinder head (9) and the liner carrier (8) opposite centering holes (19 a, 19 b) for receiving a preferably removable Centering pin (19c) has.
    [7]
    7. Device (1) according to one of claims 1 to 6, characterized in that the base plate (5) has at least one conditioning channel (22) with an inlet (23) and an outlet (24) for a cooling liquid.
    [8]
    8. Device (1) according to one of claims 1 to 7, characterized in that the sealing element (17) in the region of its Zylinderiaufbuchse (2) facing the outer lateral surface (17 a) has an annular shoulder (25) which one of the Zylinderiaufbuchse (25 2) facing outer ring surface (25a) forms whose diameter (d) is smaller than the largest diameter (D) of the sealing element (17). 2010 11 09 Fu / St



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    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JPH0242189B2|1982-11-15|1990-09-20|
    JPH0259941B2|1983-07-30|1990-12-13|Hino Jidosha Kogyo Kk|
    JPH0340541U|1989-08-30|1991-04-18|
    JPH11108801A|1997-10-08|1999-04-23|Nippon Soken Inc|Measuring apparatus for frictional force of internal-combustion engine|
    JP2002156298A|2000-11-15|2002-05-31|Nippon Soken Inc|Measuring method of piston frictional force and its device|
    KR100394635B1|2000-12-28|2003-08-14|현대자동차주식회사|A mounting structure of floating liner for measuring friction of piston|
    JP2010243390A|2009-04-08|2010-10-28|Honda Motor Co Ltd|Engine-friction force measuring instrument|AT514582B1|2013-10-04|2015-02-15|Avl List Gmbh|Device for friction measurement on a cylinder-piston arrangement|
    AT514794B1|2013-11-07|2015-06-15|Avl List Gmbh|Device for friction measurement on a cylinder-piston arrangement|
    CN106153485A|2015-04-22|2016-11-23|南京理工大学|A kind of experimental provision simulating piston ring-cylinder liner abrasion|
    DE102015109332B3|2015-06-11|2016-12-15|Gottfried Wilhelm Leibniz Universität Hannover|Device and method for friction force measurement|
    CN105675423B|2016-01-04|2018-03-16|武汉理工大学|A kind of Cylinder Liner Piston Ring in Engine friction pair friction and wear test system|
    CN105842156B|2016-05-12|2018-07-24|哈尔滨工程大学|It is a kind of can consecutive variations piston ring domain machinery loading device|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    ATA1838/2010A|AT510444B1|2010-11-09|2010-11-09|DEVICE FOR CRANKSHAFT-LOADED MEASUREMENT|ATA1838/2010A| AT510444B1|2010-11-09|2010-11-09|DEVICE FOR CRANKSHAFT-LOADED MEASUREMENT|
    EP11779414.9A| EP2638379B1|2010-11-09|2011-11-08|Device for friction measurement|
    JP2013538154A| JP5900861B2|2010-11-09|2011-11-08|Friction measuring device|
    PCT/EP2011/069594| WO2012062725A1|2010-11-09|2011-11-08|Device for friction measurement|
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