the motor of fig1 is a typical the pmdc motor 10 which has been modified to operate in a wide temperature environment , such as in the engine compartment of a motor vehicle . in such an environment the temperature may vary within a range of − 40 ° c . to + 180 ° c . the motor may be used , for example , to drive the throttle valve or butterfly valve in a carburetor system of the engine . the motor 10 has a deep drawn cup shaped metal housing 11 , supporting permanent magnets 12 forming the stator for the motor . a plastics material end cap 13 closes off the open end of the housing . a rotor 14 , comprising a rotor core 15 mounted on a shaft 16 is disposed within the housing 11 such that the rotor core 15 confronts the magnets 12 across an air gap 17 . the shaft 16 extends through the housing 11 and the end cap 13 and is journalled in bushings 18 , 28 , fitted to the end cap 13 and the closed - end of the housing 11 . the rotor 14 also comprises the commutator 19 fitted to the shaft 16 adjacent a rotor core 15 and windings ( not shown for clarity ) wound around poles of the core and electrically connected to segments of the commutator 19 . the end cap 13 supports brush gear 20 for transferring electrical power to the windings . the brush gear comprises a pair of brush cages 21 slidably securing a respective cage brush 22 electrically connected to a respective motor terminal 23 . the bushing of the end cap 13 , hereinafter referred to as the first bushing 18 , is of the self aligning type , which means that it is pivotably fixed to the end cap . the first bushing 18 has a body portion 24 which is spherical and an axially extending cylindrical portion 25 , forming a shank , which projects towards the commutator 19 . it would be readily realized by persons skilled in the art that a sleeve bushing , with or without the shank could be used in place of the self aligning first bushing 18 . the bushing of the housing 11 , hereinafter referred to as the second bushing 28 , is also a self aligning bushing having a substantially spherical appearance , which is pressed into engagement with a bearing hub 29 formed in or fitted to the closed end of the housing 11 by a spring 30 . a collar 26 is fitted to the shaft 16 to limit axial movement of the rotor and forms an abutment which contacts the second bushing 28 through a low friction washer 29 . it would be readily realized by persons skilled in the art that a sleeve bushing or a ball bearing could be used in place of the self aligning second bushing 28 . a portion of the end cap assembly is shown enlarged in fig2 . the spherical portion 24 of the first bushing 18 mates with a partly spherical bearing recess 31 in the end cap 13 and is urged into engagement by a spring , known as a bearing retainer 32 , which is press fitted into an outer portion of the bearing recess 31 . the bearing retainer 32 has resilient fingers 33 , which engage the spherical portion 24 of the first bushing 18 to retain it . the cylindrical portion 25 projects axially inwardly passed the fingers 33 of the bearing retainer 32 towards the commutator 19 . between the commutator 19 and the first bushing 18 is an oil collector 35 . the oil collector 35 is pressed onto the shaft 16 in an oil tight manner . in the preferred embodiment shown , the oil collector 35 is located abutting an axial face of the commutator through an insulating washer 36 , with a washer 34 of metal or other friction reducing material located between the oil collector 35 and the first bushing 18 . however , the proximity of the oil collector 35 to the commutator 19 is not material to the working of the oil collector 35 and the insulating washer 36 is thus optional . the oil collector 35 has a body portion 37 and oil collecting portion 38 . the body portion 37 is optionally cylindrical with a through hole for receiving the shaft 16 . the body portion 37 is preferably a press fit onto the shaft 16 and is fixed to the shaft 16 in an oil tight manner to prevent oil migrating along the shaft passing between the shaft 16 and the oil collector 35 . bearing adhesive may be used to ensure an oil tight fit . it is , however , highly preferable that the press fit is an oil tight press fit which remains oil tight over the full range of operating temperatures , namely , from − 40 ° c . to + 180 ° c . for the automotive application . the collector portion 38 of the oil collector 35 extends from the body portion 37 in an integral , one - piece , monolithic construction . the radial height of the oil collector 35 is restricted as the oil collector is fitted to the shaft 16 before the rotor 14 is fitted to the end cap 13 , which supports the brush gear 20 , thus the oil collector 35 must pass between the brush cages 21 during assembly . in this embodiment , the brush gear 20 comprises two cage brushes 22 , which make sliding contact with the commutator to transfer electrical power thereto . the cages 21 approach the commutator surface to provide stable support for the brushes 22 but this close support limits the radial height of the oil collector 35 , giving the collector a squat appearance . thus , the oil collector portion 38 has a radial portion 39 , an axial portion 40 and a lip 41 . the radial portion 39 extends radially and from the body portion 37 , preferably , but not necessarily , at an edge of the body portion 37 remote from the bushing 18 to maximize the volume of the oil collector portion 38 . the axial portion 40 extends from the radial portion 39 towards the first bushing 18 . the distal end of the axial portion 40 optionally surrounds at least a portion of the cylindrical portion 25 of the first bushing 18 and the intervening washer 34 , if present . the lip 41 extends radially inward at the distal end of the axial portion 40 . optionally , the lip 41 is partially reentrant , to positively trap migrating oil . the radial portion 39 , axial portion 40 and lip 41 form an annular cavity or oil collecting space 42 , which retains migrating oil rather than slinging it away from the shaft . such slinging usually means the oil coats an inner surface of the end cap and could drip on to the commutator . optionally , the oil collector is adapted to allow the collected oil to return to the bushing 18 . this is achieved through the location of the lip 41 and optionally by the shape of the lip . in the arrangement shown in fig2 , assuming the motor is mounted horizontally as shown , at rest oil 43 will pool to the bottom of the oil collecting space 42 until it reaches the top of the lip 41 at its lowest point has illustrated in fig2 and in the cross - section view of fig3 . as migrating oil is collected , it is retained by the lip 41 and pools at rest in the bottom of the oil collecting space 42 until the oil level rises above the lip 41 , at which time the oil 43 bridges the gap between the lip 41 and the bushing 18 whereby as the bushing cools the oil 43 returns to the bushing 18 under capillary action , thus returning lost oil to the bushing 18 . the oil collector now functions as an oil recirculating system . alternatively , oil may drip from the oil collector onto the first bushing . this ‘ dripping back recirculation ’ works for all positions with shaft horizontal within a deviation of − 45 ° to + 45 ° depending on the chosen shape of the oil collecting space 42 . it will not work for recirculation with the shaft vertical and the bearing on top . in this orientation , the only function is to collect the migrating oil and prevent it from reaching the commutator . however , recirculation will occur when the shaft is vertical if the commutator is above the first bushing . in this situation , any oil collected by the collector can drip directly onto the bushing . the dripping recirculation occurs when the collected oil 43 is on the top side of the oil collecting space which may occur when the motor is rotated and stopped . for example the motor may be rotated through 180 ° or odd multiples there of . the oil may then , under gravity , drip from the lip 41 to the bushing 18 below , especially the shank 25 . some of the oil 43 may remain in the oil collecting space 42 to be dripped out at a future time following operation of the motor . the remaining oil again pools at the bottom of the oil collecting space . fig4 illustrates an alternative lip arrangement . the lip 41 extends radially inwardly and axially outwardly and thus under centrifugal action during rotation of the rotor , still positively holds or retains oil but when stationery delivers the oil further axially along the cylindrical portion 25 of the first bushing 18 . here the lip 41 is located radially about the cylindrical portion 25 of the bushing . this assists the return of collected oil to the bushing . the oil collector 35 is of a high temperature material , preferably bronze , brass or steel , so that the coefficient of thermal expansion can be similar to that of the material the shaft 16 . thus maintaining the oil tight connection between the oil collector and the shaft over a wide temperature range . the outer surface of the oil collector 35 may be treated so as to have or form a oleophobic surface to further prevent oil migration over the outer surface of the oil collector 35 . when the oil collector 35 is made of metal , the body portion 37 may be adapted to make direct contact with the first bushing 18 ( as shown in fig4 ). thus eliminating the need for the low friction washer ( washer 34 of fig2 ) which normally would be provided between the oil collector and the first bushing . the low friction washer can be eliminated also if the oil collector is made of suitable , low friction engineering plastics , but such material may lose the advantage of the similarity of the coefficient of thermal expansion . although the invention has been described with reference to a preferred embodiment , it should be appreciated by those in the art that various modifications are possible within the scope of the invention . therefore , the scope of the invention is to be determined by reference to the claims that follow . for example , while the preferred bushing is shown as a self aligning bushing , a sleeve bushing would be acceptable and it is desirable , although not essential , that the bushing have a shank formed by an axially extending cylindrical portion of diameter generally less than the major diameter of the bushing . sleeve bushings may be directly press fitted into bearing cavities formed in the end cap or motor housing . fig5 illustrates an example where the first bushing 18 is a sleeve bushing having a body portion 24 and a shank formed by an axially extending cylindrical portion 25 . the body portion 24 is cylindrical and pressed into a bearing recess in the end cap 13 . although the invention is described with reference to one or more preferred embodiments , it should be appreciated by those skilled in the art that various modifications are possible . therefore , the scope of the invention is to be determined by reference to the claims that follow . in the description and claims of the present application , each of the verbs “ comprise ”, “ include ”, “ contain ” and “ have ”, and variations thereof , are used in an inclusive sense , to specify the presence of the stated item but not to exclude the presence of additional items .