奥地利专利AT514794A1 Device for friction measurement on a cylinder-piston arrangement

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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 formed by a sealing ring (17) between the cylinder liner (2) and a cylinder head (9), wherein an inner circumferential surface (2a) of the cylinder liner (2) relative to the cylinder head (9) is sealed and the sealing element (17) between the inner circumferential surface (2a) and a in the cylinder liner (2) protruding paragraph (15) of the cylinder head (9) is arranged. In order to improve the measurement accuracy, it is provided that at least one feed channel (32) for a liquid barrier medium (mF) opens into a space (33) adjacent to the sealing element (17).
公开号:AT514794A1
申请号:T507422013
申请日:2013-11-07
公开日:2015-03-15
发明作者:Kurt Dr Salzgeber；Michael Erich Hammer；Bernhard Dipl Ing Kometter
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 having at least one piston ring is arranged in a cylinder liner, with at least one sealing element formed by a sealing element between the cylinder liner and a cylinder head, wherein an inner circumferential surface of the cylinder liner opposite the cylinder head is sealed and the sealing element between the inner circumferential surface and a projecting into the cylinder liner paragraph of the cylinder head is arranged.
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 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.
Known frictional measuring devices have the disadvantage that the cylinder liner sealing elements, in particular for sealing between the cylinder liner and the 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.
From WO 2012/062 725 Al a device for friction measurement on a cylinder-piston arrangement is known, wherein a reciprocating piston having at least one piston ring is arranged in a cylinder liner. Between the cylinder liner and the cylinder head, at least one sealing element is formed, wherein an inner circumferential surface of the cylinder liner is sealed relative to the cylinder head and the sealing element between the inner circumferential surface and a protruding into the cylinder liner paragraph of the cylinder head is arranged. The cylinder liner is largely decoupled from the cylinder head.
However, physical and geometric constraints lead to relative movements between the sealing element and the cylinder liner for the introduction of frictional forces as soon as the radial sealing forces acting on the cylinder liner by the sealing element are greater than zero. However, without direct contact of the sealing element and the cylinder liner, the leaks at combustion pressure would be unacceptably high.
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 at least one feed channel for a liquid barrier medium opens into a space adjoining the sealing element.
The space is preferably tensioned by the sealing element, the cylinder head and the cylinder liner.
The feed channel may advantageously be at least partially formed in the cylinder head, with preferably the mouth of the feed channel being located in the region of the offset.
Another advantageous embodiment of the invention provides that the supply channel is at least partially formed in the cylinder liner, wherein preferably the mouth of the feed channel is arranged in a region facing the shoulder of the inner circumferential surface of the cylinder liner.
The sealing element is preferably arranged in an annular groove of an outer circumferential surface of the shoulder, wherein the mouth of the feed channel may be formed in the region of the annular groove.
The liquid barrier medium, for example engine oil, is fed via the supply channel into the space bounded by the sealing element, the cylinder head and the cylinder liner, optionally via a check valve arranged in a supply line, and fills it at least in the area of the sealing element. Since the barrier medium has a higher viscosity than the fuel gas, a particularly good sealing effect can be achieved with the sealing element without radial sealing forces acting from the sealing element on the cylinder liner. The largest diameter of the sealing element is slightly smaller than the inner diameter of the cylinder liner. Thus, a defined low leakage flow between the sealing element and the cylinder liner is accepted. By doing so, direct contact between the sealing member and the cylinder liner can be avoided while still achieving a high sealing effect for burning gases.
If the smallest diameter of the sealing element is greater than the smallest diameter of the annular recess, the space may extend in the radial direction between the sealing element and the cylinder head. Furthermore, the axial extent of the sealing element may be less than the axial extent of the annular recess, whereby space is also formed in the axial direction between the sealing element and the cylinder head for receiving the liquid barrier medium.
A particularly good sealing effect by the liquid barrier medium can be ensured if the sealing element in the region of the cylinder liner facing the outer lateral surface has an annular recess, which forms a cylinder liner facing outer annular surface, the smallest diameter is smaller than the largest diameter of the sealing element, for example, an annular shoulder forming annular recess may be limited in the axial direction on the side facing away from the combustion chamber of an annular diameter of the first sealing gasket forming the largest diameter.
As an alternative to an annular shoulder limited only by a sealing strip on one side, the annular recess can also form an annular pocket, which is also bounded on the side facing the combustion chamber by an annular second sealing strip whose diameter is smaller than the largest
Diameter of the sealing element and larger than the smallest diameter of the outer annular surface of the recess.
It is particularly advantageous if the sealing element is formed by a piston ring, in particular made of steel.
Due to the special sealing means of the sealing ring and the paragraph in Zy¬linderkopf one hand, and the liquid barrier medium on the other hand prevents the gas forces acting axially on the liner. Thus, these also have no direct influence on the measurement result and primarily the friction forces of the piston or piston side forces are transmitted to the sensors.
The invention will be explained in more detail below with reference to FIGS. Show it:
1 shows a device according to the invention in a section along the line I - I in Fig. 2.
Figure 2 shows this device in a section along the line II - II in Fig. 1.
Fig. 3 shows the detail III of Fig. 2;
4 shows the detail IV of FIG. 3 in a known embodiment,
Fig. 5 shows the detail IV of Fig. 3 in a first invention
Execution,
Fig. 6 shows the detail X of Fig. 5 and
Fig. 7 shows the detail IV of Fig. 3 in a second embodiment of the invention.
The frictional force measuring device 1 between a piston 3 reciprocating in a cylinder liner 2 has a base unit 4, a base plate 5, a sensor carrier 6 for accommodating 3-D force sensors 7, a liner carrier 8, and a cylinder head 9. 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 is a Kühlflüsssmantel12 formed, which is connected to inlet and outlet lines 12a, 12b. Between the cylinder liner 2 and the liner carrier 8, a sealing ring 14 is disposed in a circumferential groove 13. Denoted by reference numeral 20 is a cylinder head carrier.
The cylinder head 9 has a projecting into the cylinder liner 2 disc-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 angeord¬net which is pressed similar to a piston ring by the gas forces against the inner jacket surface 2a of the cylinder liner 2.
The special sealing by means of the annular sealing element 17 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 primarily 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 basic unit 4 and from the cylinder head 9 and is connected to it only by the sealing element 17 and the force sensors 7.
In order to reduce the force acting normal to the piston travel direction on the force sensors 7, which do not originate from the movement of the piston 3 (forces due to different thermal expansions) and which can thus falsify the measurement result in the measurement operation of the engine, it must be ensured that before the start of the measurements the parts acting on the force sensor 7 (bush carrier 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 an unillustrated entry 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.
Further, the force of the seal member 17 on the cylinder liner 2 and thus the influence of the ring friction force of the seal member 17 on the measurement result can be reduced by a recess V having a width a in the seal member 17 forming an annular shoulder 25. An annular shoulder 25 is understood to mean an axially open groove to one side, which has a substantially cylindrical groove bottom and a substantially normal groove flank. As shown in Fig. 4, the sealing member 17 in the region of the cylinder liner 2 facing the outer lateral surface 17a as an open in the direction of the combustion chamber B groove formed annular shoulder 25, for example by a circumferential milling cut can be made. The annular shoulder 25 forms an outer annular surface 25a facing the cylinder liner 2, the smallest diameter dv of which is smaller than the largest diameter D17 of the sealing element 17, the largest diameter Di7 of the sealing element 17 being formed by a first sealing strip 36 adjacent to the annular recess V. The axial extent b of the sealing element 17 is less than the axial extent c of the annular groove 16. The smallest inner diameter di7 of the sealing element 17 is greater than the largest diameter di6 of the annular groove 16. Thus, between the sealing element 17 and the annular groove 16 uniaxial gap 16a and a radial Gap 16b formed so that on the inside of the sealing element 17, the gas pressure p, is applied. Through the shoulder 25 also acts on the annular surface 25a with the height a of the internal gas pressure p. The sealing element 17 thus acts as a result of the internal gas pressure p, the axial force Fgz, the radial force Fgn and the radial force Fgr2. Furthermore, acts in the radial direction, the biasing force Fv of the sealing element 17, and the frictional force FR of the sealing element 17 in the annular groove 16. The resulting relative movement between the cylinder liner 2 and the cylinder head 9 located in the cylinder head 9 disc-shaped shoulder 15 resulting axial force Frl on the cylinder liner 2 results with the friction coefficients μ and pL thus: F rl = Fl * Ml
with FL = Fv + Fgri-Fgr2-Fgz:!, cM
Ideally, FL is small, consisting essentially of the relatively small biasing force Fv of the sealing element 17, which establishes direct physical contact between the sealing element 17 and the cylinder liner 2. Without these, the leaks in combustion pressure would be unacceptably high.
Another way to achieve a decoupling of the cylinder liner 2 from the cylinder head 9 is described below. In the case of the first embodiment of the invention shown in FIG. 5, at least one supply channel 32 for a liquid blocking medium mF connected to a supply line 31 via a check valve 30 enters the space 33 adjoining the sealing element 17. The space 33 is thereby formed substantially by the axial gap 16 a and the radial gap 16 b between the annular groove 16 and the sealing element 17. The under pressure pi blocking medium mF also penetrates into the region of the annular shoulder 25, and -in particular when increasing the internal gas pressure p, by the combustion pressure -in a radial throttle gap 34 between a first sealing strip 36 of the sealing element 17 and the cylinder liner 2 and flows through this , The gap flow in the radial throttle gap 34 forms a defined leakage of the blocking medium mF, wherein a further radial force Fgr3 of the biasing force Fv counteracts in the throttle gap 34.
The resulting axial force FRL on the cylinder liner 2 is thus determined by the properties of the fluid flow in the throttle gap 34 and no longer by the solid friction between sealing element 17 and cylinder liner 2. The transmitting force is dependent on the local velocity gradient δν / δζ of the flow at the cylinder liner 2, the Viscosity η of the barrier medium mF and the effective annular area A of the throttle gap 34 (see Fig. 6):
Direct body contact between the sealing member 17 and the cylinder liner 2 is not necessary and even undesirable to avoid introducing frictional forces from solid contact into the cylinder liner 2.
Since the liquid barrier medium mF, which may be formed for example by lubricating oil, has a much higher viscosity than the fuel gas, the leaks of the blocking medium mF keep within defined limits. The blocking medium mF acts sealingly on the fuel gases and prevents them from passing through the radial throttle gap 34.
Fig. 7 shows a second embodiment of the invention, which differs from Fig. 5 essentially in that the feed channel 32 is arranged in the cylinder liner 2 and opens into a space 33 bounded by the outside of the sealing element 17 and the inside of the cylinder liner 2. The outer lateral surface 17a of the sealing element 17 has a circumferential circumferential recess V, which forms an annular pocket 35 between a first sealing strip 36 and a second sealing strip 37. The diameter D37 of the second sealing strip 37 is smaller than the largest diameter Di7 of the sealing element 17 and greater than the smallest diameter dv of the outer annular surface 35a (groove bottom) of the pocket 35. The axial extent b of the sealing element 17 is less than the axial extent c of the annular groove 16. The smallest diameter di7 of the sealing element 17 is larger than the largest diameter of the annular groove 16.
Thus, the liquid lock-up medium mF enters the space 33 through the supply passage 32 disposed in the cylinder liner 2, which may be connected to a supply passage 31 having a check valve 30 again, and completely fills the annular pocket 35. The internal gas pressure p, on the side of the combustion chamber B counteracts the outflow in the direction of the combustion chamber B through the throttle gap 34 formed by the first sealing strip 36, so that a small part of the blocking medium mF is pressed in the direction of the lower ambient pressure Po through the radial throttle gap 34 formed by the first sealing strip 36 becomes. The gas internal pressure p acting axially on the side of the second sealing strip 37 axially presses the sealing element 17 in FIG. 7 upwards against the cylinder head 9 and prevents the gas from escaping between the cylinder head 9 and the sealing element 17. As shown in FIG mF that the fuel gas escapes between the sealing element 17 and the cylinder liner 2. As a result, in the case of very small leakages of the blocking medium mF, a high sealing effect against combustion gases and a largely decoupling of the cylinder liner 2 from the cylinder head 9 can be achieved.

权利要求:
Claims (18)
[1]
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 cylinder liner (2) with at least one sealing element formed by a sealing ring (17) between cylinder liner (2) and a cylinder head (9), wherein an inner jacket surface (2a) of the cylinder liner (2) is sealed against the cylinder head (9) and the sealing element (17) between the inner circumferential surface (2a) and one in the Cylinder liner (2) projecting shoulder (15) of the cylinder head (9) is arranged, characterized in that at least one feed channel (32) for a liquid barrier medium (mF) opens into a space adjacent to the sealing element (17) space (33).
[2]
2. Device (1) according to claim 1, characterized in that the space (33) by the sealing element (17), from the cylinder head (9) and the cylinder liner (2) is clamped.
[3]
3. Device (1) according to claim 1, characterized in that the supply channel (32) is at least partially formed in the cylinder head (9).
[4]
4. Device (1) according to claim 2, characterized in that the mouth of the feed channel (32) in the region of the shoulder (15) is arranged.
[5]
5. Device (1) according to one of claims 1 to 4, characterized in that the feed channel (32) is at least partially formed in the cylinder liner (2).
[6]
6. Device (1) according to claim 5, characterized in that the mouth of the feed channel (32) in a the shoulder (15) facing portion of the inner circumferential surface (2a) of the cylinder liner (2) is arranged.
[7]
7. Device (1) according to one of claims 1 to 6, characterized in that the sealing element (17) in an annular groove (16) in an outer circumferential surface (15 a) of the shoulder (15) is arranged, wherein preferably the mouth of the feed channel (32 ) is formed in the region of the annular groove (16).
[8]
8. Device (1) according to one of claims 1 to 7, characterized in that the sealing element (17) in the region of the cylinder liner (2) facing the outer lateral surface (17 a) an annular recess (V) which one of the cylinder liner (2) facing outer annular surface (25a, 35a) is formed whose smallest diameter (dv) is smaller than the largest diameter (D) of the sealing element (17).
[9]
9. Device (1) according to claim 8, characterized in that the annular recess (V) in the axial direction on the combustion chamber (B) facing away from the side of the largest diameter (Di7) of the sealing element (17) forming the first sealing strip (36) is.
[10]
10. Device (1) according to claim 8 or 9, characterized in that the annular recess (V) forms an annular shoulder (25).
[11]
A device (1) according to claim 8 or 9, characterized in that the annular recess (V) forms an annular pocket (35).
[12]
12. Device (1) according to claim 11, characterized in that the dieringförmige pocket (35) in the axial direction on the combustion chamber (B) side facing by a second sealing strip (37) is limited.
[13]
Device (1) according to claim 12, characterized in that the diameter (D37) of the second sealing strip (37) is smaller than the largest diameter (Di7) of the sealing element (17) and larger than the smallest diameter (dv) of the outer ring surface (D). 35a).
[14]
14. Device (1) according to one of claims 1 to 13, characterized in that the smallest diameter (di7) of the sealing element (17) is greater than the largest diameter (Di6) of the annular groove (16).
[15]
15. Device (1) according to one of claims 7 to 14, characterized in that the axial extent (b) of the sealing element (17) is smaller than the axial extent (c) of the annular groove (16).
[16]
16. Device (1) according to one of claims 1 to 15, characterized in that the largest diameter (D) of the sealing element (17) is smaller than the inner diameter (d2) of the cylinder liner (2).
[17]
Device (1) according to any one of Claims 1 to 16, characterized in that the supply channel (32) is connected to a supply line (31) having at least one check valve (30).
[18]
18. Device (1) according to one of claims 1 to 17, characterized in that the sealing element (17) is formed by a piston ring.

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同族专利:

公开号 | 公开日

AT514794B1|2015-06-15|

引用文献:

公开号 | 申请日 | 公开日 | 申请人 | 专利标题

US20020083913A1|2000-12-28|2002-07-04|Kyoung-Pyo Ha|Liner mounting structure for measuring piston friction|

WO2004092621A1|2003-04-09|2004-10-28|Dimitrios Dardalis|Hydrodynamic seal and method for sealing a rotating sleeve engine|

WO2012062725A1|2010-11-09|2012-05-18|Avl List Gmbh|Device for friction measurement|AT516996B1|2015-03-30|2017-11-15|Avl List Gmbh|DEVICE FOR MEASURING THE FRICTION OF A CYLINDER PISTON ARRANGEMENT|

法律状态:

优先权:

申请号 | 申请日 | 专利标题

ATA50742/2013A|AT514794B1|2013-11-07|2013-11-07|Device for friction measurement on a cylinder-piston arrangement|ATA50742/2013A| AT514794B1|2013-11-07|2013-11-07|Device for friction measurement on a cylinder-piston arrangement|

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