GB2194060A - Lubricant testing apparatus - Google Patents
Lubricant testing apparatus Download PDFInfo
- Publication number
- GB2194060A GB2194060A GB08617869A GB8617869A GB2194060A GB 2194060 A GB2194060 A GB 2194060A GB 08617869 A GB08617869 A GB 08617869A GB 8617869 A GB8617869 A GB 8617869A GB 2194060 A GB2194060 A GB 2194060A
- Authority
- GB
- United Kingdom
- Prior art keywords
- roller
- gear
- planet
- shaft
- lubricant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 239000000314 lubricant Substances 0.000 title claims abstract description 37
- 238000012360 testing method Methods 0.000 title claims abstract description 33
- 238000010998 test method Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 2
- 238000005096 rolling process Methods 0.000 description 10
- 125000004122 cyclic group Chemical group 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N19/00—Investigating materials by mechanical methods
- G01N19/02—Measuring coefficient of friction between materials
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N33/00—Investigating or analysing materials by specific methods not covered by groups G01N1/00 - G01N31/00
- G01N33/26—Oils; Viscous liquids; Paints; Inks
- G01N33/28—Oils, i.e. hydrocarbon liquids
- G01N33/30—Oils, i.e. hydrocarbon liquids for lubricating properties
Landscapes
- Chemical & Material Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Engineering & Computer Science (AREA)
- Health & Medical Sciences (AREA)
- General Health & Medical Sciences (AREA)
- Pathology (AREA)
- Analytical Chemistry (AREA)
- Biochemistry (AREA)
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Immunology (AREA)
- Automation & Control Theory (AREA)
- Chemical Kinetics & Catalysis (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Food Science & Technology (AREA)
- Medicinal Chemistry (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
A lubricant testing apparatus comprising a first roller 4, a second roller 6 which is parallel with and is disposed adjacent the first roller so that the circumferential surfaces of the rollers engage along a line, a drive means for rotating the first roller at a constant angular speed, and a gear means for continuously and cyclicly varying the angular speed of the second roller so that the slide/roll ratio between the rollers 4,6 varies between 100% slide and 100% roll. In operation a drive wheel 10 rotatable with roller 4 rotates the planet ring gear 16 via idler 12. Planet gear 24 on drive shaft 20 carried by ring gear 16 rotates planet gear 2B which 15 secured to roller 6 and roller 6 rotates in the opposite direction to roller 4. Rotation of roller 4 also cause rotation of an eccentric member carried by shaft 8 of roller 4 so that slide 38 is reciprocated in a notch 36 in a rocking arm 34. The arm is thus oscillated over arc theta 2 and causes planet gear 32 to oscillate therewith causing a meshing planet wheel 26 on shaft 20 to oscillate in the opposite direction. This causes the slowing down and speeding up of planet shaft 20 and via the gears 24,28 of the second roller 6. <IMAGE>
Description
SPECIFICATION
Lubricant testing apparatus
The present invention relates to a lubricant testing apparatus and in particular to a socalled "two roller" lubricant testing apparatus.
Two roller lubricant testing machines have been in use for some time for testing lubricants, in particular lubricants for use in traction drives in aircraft, automotive and industrial applications. The output of a traction drive of given design is limited primarily by the coefficient of traction of the lubricant and the two roller lubricant testing machines have been used to test these lubricants in order to try to develop better lubricants. The machines have also been used to simulate gear tooth contacts and the contact between cams and followers.
In a known two roller lubricant testing machine, two steel rollers are mounted one upon the other. The lubricant to be tested covers the roller surfaces. One of the rollers is driven by an electric motor and the other roller engages the driven roller and rotates therewith.
The speed range is typically from 150 to 3000 revolutions per minute and the maximum contact stress of the two rollers is typically 2.8x 106 kN/m2. A gear system is provided which can apply various fixed percentages of slip to the undriven roller. Typically, the slip rates which can be applied are 0, 1, 2, 4, 6 and 8% of the rolling speed of the driven roller. Thus lubricants can be tested under conditions of pure rolling contact or under partial rolling contact with various specified slip percentages.
The known two roller lubricant testing machine suffers from a number of disadvantages.
Primarily, the machine can only employ a number of specific slip percentages. The test is accordingly very artificial since in real-life situations such as gear tooth contact or cam/follower contact the slip varies continuously over a range as the two moving parts move relative to each other. For example, in gear tooth contact, there is pure rolling contact at the pitch point and continuously varying degrees of slip on either side of the pitch point. Thus the known machine cannot simulate accurately the whole range of conditions which can actually occur. Also, the known machine cannot readily be employed to simulate high slip ratios such as occur in cam/follower contact.
The present invention aims to provide a lubricant testing apparatus in which the problems with the known apparatus can be substantially overcome.
Accordingly, the present invention provides a lubricant testing apparatus comprising a first roller, a second roller which is parallel with and is disposed adjacent the first roller so that the circumferential surfaces of the rollers engage along a line, a drive means for rotating the first roller at a particular angular speed, and a gear means for continuously and cyclicly varying the angular speed of the second roller.
Preferably, the gear means comprises a driving shaft which is driven by the drive means, a gear system which is driven by the driving shaft and which drives a shaft on which the second roller is mounted, and speed reduction means for cyclicly reducing the speed of rotation of the gear system.
Preferably, the gear system includes a first planet gear and a second planet gear which are mounted on a common planet drive shaft, a planet driven gear which is mounted on the shaft on which the second roller is mounted and is meshed with the first planet gear, the planet drive shaft being caused to rotate by rotation of the driving shaft, and the speed reduction means comprises an oscillating gear which is meshed with the second planet gear and means for oscillating the oscillating gear back and forth over an angle, the means for oscillating being driven by the driving shaft, thereby to vary the speed of rotation of the planet drive shaft.
Preferably, the means for oscillating comprises a rocking arm having an elongate notch therealong, a drive shaft on which the oscillating gear and the rocking arm are mounted and a slider which is eccentrically mounted on the driving shaft and is disposed in the elongate notch, the arrangement being such that rotation of the driving shaft causes back and forth translation of the slider along the notch and back and forth rotation of the rocking arm and the driven shaft.
The present invention further provides a method of testing a lubricant, the method comprising disposing a lubricant to be tested between a pair of rollers comprising a first roller and a second roller which is parallel with and is disposed adjacent the first roller so that the circumferential surfaces of the rollers engage along a line, rotating the first roller at a particular angular speed and continuously and cyclicly varying the angular speed of the second roller.
An embodiment of the present invention will now be described by way of example only, with reference to the accompanying drawings, in which:
Figure 1 is a schematic perspective view of a lubricant testing apparatus in accordance with the present invention;
Figure 2 is a diagrammatic sectional side view of the gear arrangement which is employed in the lubricant testing apparatus of
Fig. 1;
Figure 3 is a diagrammatic end view of part of the gear arrangement of Fig. 2 showing the slider/rocking arm arrangement;
Figure 4 is a graph showing the relationship between the percentage slip between the two rollers of the lubricant testing apparatus of
Fig. 1 and the angle of rotation (8,) of that roller which is driven at constant angular velocity; and
Figure 5 is a graph showing the relationship between the angle of rotation (63) of the roller which is driven at varying angular velocity by the gear arrangement and the angle of rotation (O,) of that roller which is driven at constant angular velocity.
Referring to Figs. 1 to 3, a lubricant testing machine, designated generally as 2, comprises a pair of opposed rollers, one being an upper roller 4 and the other being a lower roller 6.
The rollers, 4, 6 are typically of hardened steel and, in the preferred embodiment, have a diameter of 152 mm. The load between the rollers is applied by a hand wheel (not shown) and measured by a load cell (also not shown).
The load between the rollers may be varied as desired. The tractive force between the two rollers 4, 6 may be measured by a further load cell (not shown). The upper roller 4 is driven by a thyristor controlied motor (not shown) via a gearbox (not shown) which is adapted to rotate the upper roller 6 at a desired speed or desired speeds. The upper roller 4 is mounted on a driving shaft 8 on which is mounted a driving wheel 10. An idler gear 12, on a stub shaft 14, is mounted below the driving wheel 10 and is meshed therewith. A driven ring gear 16 is mounted on bearings (not shown) around a driven shaft 18 so that the driven ring gear 16 can freely rotate around the driven shaft 18. The driven ring gear 16 is meshed with the idler gear 12 whereby the driving wheel 8, the idler gear 12 and the driven ring gear 16 lie in a common plane.A planet drive shaft 20 is fixed to the driven ring gear 16 by a support member 22 and extends parallel to the axis of the driven ring gear 16 and to the driving shaft 8. First and second planet gears 24, 26 are mounted on the planet drive shaft 20 in spaced relation, with the first planet gear 24, the second planet gear 26 and the driven ring gear 16 lying in respective parallel spaced planes. The first planet gear 24 is located further from the driven ring gear 16 than the second planet gear 26 and is meshed with a planet driven gear 28. The planet driven gear 28 is mounted on a shaft 30 on which the lower roller 6 is coaxially mounted.
An oscillating planet 32 is mounted on one end of the driven shaft 18 and is meshed with the second planet gear 26. At the other end of the driven shaft 18 is mounted a rocking arm 34 which extends upwardly towards an extension of the driving shaft 8 which extends from the driving wheel 10. The rocking arm 34 has an elongate notch 36 therealong in which is mounted a slider 38 which can slide up and down the notch 36. The slider 38 is eccentrically mounted on the driving shaft 8 whereby rotation of the driving shaft 8 causes the slider 38 to be translated up and down the notch 36. This in turn causes the rocking arm 34, and also driven shaft 18 and the oscillating planet 32 which are attached thereto, to be rotated back and forth through an arc as shown by the angle 62 in Fig. 1.
As is shown more particularly in Figs. 2 and 3, the eccentric mounting for the slider 38 comprises an eccentric member 40. The eccentric member 40 is mounted on the driving shaft 8 and consists of a slider mount 42, which is spaced from the axis 44 of the driving shaft 8, a slider mounting shaft 46 which is fixed on the slider mount 42 and on which the slider 38 is rotatably carried, and a semicircular counterbalance portion 48 which is on the opposite side of the driving shaft 8 from the slider mount 42.
The operation of the lubricant testing apparatus of Figs. 1 to 3 will now be described.
In operation, the upper roller 4 is driven at constant angular velocity by the motor, the driving shaft 8 is rotated therewith and the driving shaft 8 in turn rotates the driving wheel 10 at constant angular velocity. The driving wheel 10 drives the idler wheel 12 in an opposite angular direction and the idler wheel 12 rotates the driven ring gear 16 and the planet drive shaft 20 mounted thereon in the same angular direction as the driving wheel 10 and at constant angular speed. The first planet gear 24 on planet drive shaft 20 is correspondingly rotated and drives the planet driven gear 28 which is meshed therewith.
The planet driven gear 28 rotates the shaft 30 on which it is mounted and also the lower roller 6 which is mounted on the shaft 30.
Thus by means of the apparatus described above rotation of the upper roller 4 at constant angular speed in a particular angular direction (i.e. that shown by angle 0, in Fig. 1) tends to cause rotation of the lower roller 6 in the opposite angular direction (i.e. that shown by angle 63 in Fig. 1).
It will be appreciated by those skilled in the art that when the upper and lower rollers 4, 6 are rotating in opposite angular directions, (as shown in Fig. 1), and at the same angular speed, then there will be pure rolling contact between the two rollers 4, 6. The operation of the remaining parts of the gear arrangement will now be described to show how the apparatus of the invention can vary the slide/roll ratios between the two rollers 4, 6.
Rotation of the driving shaft 8 causes corresponding rotation of the eccentric member 40 which results in the slider 38 being oscillated up and down the notch 36 in the rocking arm 34. The rocking arm 34 accordingly is rotatably oscillated over an arc, as indicated by the angle 62 in Fig. 1. The oscillating planet 32 is correspondingly rotatably oscillated and the second planet 26 which is meshed therewith is thereby rotated back and forth but in an opposite angular direction. This back and forth rotation of the second planet gear 26 causes a corresponding speeding up and slowing down of the rotation of the planet drive shaft 20, the first planet gear 24 mounted thereon and accordingly the planet driven shaft 28/shaft 30/lower roller 6 assembly.Thus the apparatus is arranged cyclicly to vary the angular velocity of the lower roller 6 while rotating the upper roller 4 at constant angular velocity.
In a preferred embodiment, the lower roller 6 is rotated by the gear arrangement so that during one rotation of the upper roller 4 the lower roller 6 rotates initially at the same angular speed (but in the opposite angular direction) as the upper roller 4. After half a revolution of the upper roller 4, the lower roller 6 is momentarily halted. At the end of one revolution of the upper roller 4 the lower roller 6 is again rotating at the same angular speed (but in the opposite angular direction) as the upper roller 4.
In the preferred embodiment, the various gear wheels have the following number of gear teeth:- driving wheel 10: 34, roller wheel 12: 58; driven ring gear 16: 89; first planet gear 24: 32; second planet gear 26: 20; planet driven gear: 36; and oscillating gear 45.
The relationship between the rotation of the upper and lower rollers 4,6 is illustrated in
Figs. 4 and 5.
Fig. 4 shows, as line A, the relationship between the percentage slip between the two rollers 4, 6 and the angle 0, in degrees which is the angle through which the upper roller 4 has turned. Fig. 3 shows, as line B, the relationship between the angle 63 in degrees through which the lower roller 6 has turned and the angle 0, in degrees through which the upper roller 4 has turned. Each graph reprsents one revolution of the upper roller 4.
Initially, at 0,=0 the gradient of the 63/61 plot is 45" (as shown by line C which is a plot of 0, against 0,) which indicates that 0, and 63 are varying with 6 at the same rate. Thus, initially the upper and lower rollers 4, 6 rotate at the same angular speed (but in the opposite direction) and the contact between the two rollers is pure rolling contact (i.e. 0% slip). As the rotation of the rollers proceeds, the angular speed of the lower roller 6 decreases, as shown by the reduction in gradient of the 63/61 plot until at 0,= 180 the gradient of the 63/61 plot is zero.This indicates that after the upper roller 4 has been rotated through half a revolution the angular speed of the lower roller 6 is reduced to zero to give a pure slip contact (i.e. 100% slip) between the rollers 4, 6. Over the next half revolution of the upper roller 4 the angular speed of the lower roller 6 increases again. At the end of the revolution of the upper roller 4, the lower roller 6 is again rotating at the same angular speed as the lower roller 6 and accordingly the contact between the two rollers 4, 6 is again pure rolling contact (i.e. 0% slip). It may be seen that the plot of 63 against 0, varies sinusoidally about line D which is a plot of 03=0.382 0,.
The lubricant testing apparatus of the preferred embodiment of the invention therefore permits the contact between the upper and lower rollers 4, 6 to vary cyclicly and continuously from pure rolling contact, to pure slip contact and then back to pure rolling contact over one revolution of the upper roller 4. This permits the whole spectrum of slip/roll ratios to be simulated by the lubricant testing apparatus over a continuous range. The lubricant testing apparatus can therefore be employed to simulate both cam/follower contact which can have a high slip ratio and gear tooth contact which tends to have lower slip ratios (from O to about 40% slip). In gear tooth contact there is pure rolling contact at the pitch point and varying degrees of slip contact on either side of the pitch point.The apparatus of the invention, by simulating a range of slip/roll ratios, can simulate the various contacts which occur between gear teeth.
The cyclic variation of slip in the apparatus of the preferred embodiment provides a particular advantage over the known apparatus, namely after a test period the upper roller has regions which were subjected to constant percentages of slip throughout the test. This is achieved by operating the apparatus in the manner shown in Figs. 4 and 5 in which the slip ratio varies in one cycle over one revolution of the upper roller. The surface of the upper roller may be examined after the test in different regions so as to determine the efficacy of the lubricant under test at different slip/roll ratios.
The present invention is not limited to the embodiment which is illustrated. In particular, the gear arrangement could be adapted to give slip ranges other than the range of 0% to 100% shown in Fig. 4. Also, the gear arrangement could be adapted to rotate the lower roller in a cycle which is different from the cyclic rotation of the upper roller. Furthermore, in some lubrication tests it would be required to reverse the torque of the lower roller so that at a point in the test it rotated in the same angular direction as the upper roller-this would result in a slip ratio of greater than 100%.
Claims (7)
1. A lubricant testing apparatus comprising a first roller, a second roller which is parallel with and is disposed adjacent the first roller so that the circumferential surfaces of the rollers engage along a line, a drive means for rotating the first roller at a particular angular speed, and a gear means for continuously and cyclicly varying the angular speed of the second roller.
2. A lubricant testing apparatus according to Claim 1 wherein the gear means comprises a driving shaft which is driven by the drive means, a gear system which is driven by the driving shaft and which drives a shaft on which the second roller is mounted, and speed reduction means for cyclicly reducing the speed of rotation of the gear system.
3. A lubricant testing apparatus according to Claim 2 wherein the gear system includes a first planet gear and a second planet gear which are mounted on a common planet drive shaft, a planet driven gear which is mounted on the shaft on which the second roller is mounted and is meshed with the first planet gear, the planet drive shaft being caused to rotate by rotation of the driving shaft, and the speed reduction means comprises an oscillating gear which is meshed with the second planet gear and means for oscillating the oscillating gear back and forth over an angle, the means for oscillating being driven by the driving shaft, thereby to vary the speed of rotation of the planet drive shaft.
4. A lubricant testing apparatus according to Claim 3 wherein the means for oscillating comprises a rocking arm having an elongate notch therealong, a driven shaft on which the oscillating gear and the rocking arm are mounted and a slider which is eccentrically mounted on the driving shaft and is disposed in the elongate notch, the arrangement being such that rotation of the driving shaft causes back and forth translation of the slider along the notch and back and forth rotation of the rocking arm and the driven shaft.
5. A lubricant testing apparatus substantially as hereinbefore described with reference to the accompanying drawings.
6. A method of testing a lubricant, the method comprising disposing a lubricant to be tested between a pair of rollers comprising a first roller and a second roller which is parallel with and is disposed adjacent the first roller so that the circumferential surfaces of the rollers engage along a line, rotating the first roller at a particular angular speed and continuously and cyclicly varying the angular speed of the second roller.
7. A method of testing a lubricant substantially as hereinbefore described with reference to the accompanying drawings.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08617869A GB2194060A (en) | 1986-07-22 | 1986-07-22 | Lubricant testing apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08617869A GB2194060A (en) | 1986-07-22 | 1986-07-22 | Lubricant testing apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8617869D0 GB8617869D0 (en) | 1986-08-28 |
| GB2194060A true GB2194060A (en) | 1988-02-24 |
Family
ID=10601492
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08617869A Withdrawn GB2194060A (en) | 1986-07-22 | 1986-07-22 | Lubricant testing apparatus |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2194060A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5388442A (en) * | 1992-10-13 | 1995-02-14 | Tranergy Corporation | Lubrication and adhesion testing machine |
| WO2001027609A3 (en) * | 1999-10-11 | 2001-08-16 | Torotrak Dev Ltd | Traction-force measuring apparatus with two friction rollers in adjustable planes |
| US6644094B1 (en) * | 1999-04-13 | 2003-11-11 | Nsk Ltd. | Traction coefficient measurement device |
| US7013713B2 (en) * | 2003-06-13 | 2006-03-21 | Advanced Engine Technology Ltd. | Lubricity tester for diesel fuels |
| US9714892B2 (en) | 2014-08-29 | 2017-07-25 | Caterpillar Inc. | Wear testing machine |
| DE102016015529A1 (en) * | 2016-12-24 | 2018-06-28 | Peter Tenberge | model test |
| US20220316975A1 (en) * | 2019-09-08 | 2022-10-06 | Pcs Instruments Ltd | A traction or friction measurement apparatus and method of calibration |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110865024A (en) * | 2019-11-16 | 2020-03-06 | 佛山市铂索润滑材料有限公司 | Metal cutting fluid performance testing equipment and using method |
| CN112816217B (en) * | 2021-01-05 | 2023-06-23 | 隆鑫通用动力股份有限公司 | Shock testing device |
-
1986
- 1986-07-22 GB GB08617869A patent/GB2194060A/en not_active Withdrawn
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5388442A (en) * | 1992-10-13 | 1995-02-14 | Tranergy Corporation | Lubrication and adhesion testing machine |
| US6644094B1 (en) * | 1999-04-13 | 2003-11-11 | Nsk Ltd. | Traction coefficient measurement device |
| US6691551B2 (en) | 1999-04-13 | 2004-02-17 | Nsk, Ltd. | Traction coefficient measurement device |
| WO2001027609A3 (en) * | 1999-10-11 | 2001-08-16 | Torotrak Dev Ltd | Traction-force measuring apparatus with two friction rollers in adjustable planes |
| GB2371371A (en) * | 1999-10-11 | 2002-07-24 | Torotrak Dev Ltd | Test apparatus |
| GB2371371B (en) * | 1999-10-11 | 2003-11-12 | Torotrak Dev Ltd | Test apparatus |
| US7013713B2 (en) * | 2003-06-13 | 2006-03-21 | Advanced Engine Technology Ltd. | Lubricity tester for diesel fuels |
| US9714892B2 (en) | 2014-08-29 | 2017-07-25 | Caterpillar Inc. | Wear testing machine |
| DE102016015529A1 (en) * | 2016-12-24 | 2018-06-28 | Peter Tenberge | model test |
| WO2018114950A1 (en) | 2016-12-24 | 2018-06-28 | Peter Tenberge | Model test stand for the tribological examination of disk-shaped, non-circular test specimens |
| DE102016015529B4 (en) | 2016-12-24 | 2018-09-27 | Peter Tenberge | model test |
| US20220316975A1 (en) * | 2019-09-08 | 2022-10-06 | Pcs Instruments Ltd | A traction or friction measurement apparatus and method of calibration |
| US12510431B2 (en) * | 2019-09-08 | 2025-12-30 | Pcs Instruments Ltd | Traction or friction measurement apparatus and method of calibration |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8617869D0 (en) | 1986-08-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |