JP2009041590A - Bearing device and differential - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To adjust oil supply to a pair of rolling bearings 5, 6 according to increasing/decreasing change of oil introducing amount to an oil supplying passage 11 of a case 1 so as to be neither too much nor too little, in a bearing device rotatably supporting a rotating shaft 4 to the case 1 through the rolling bearings 5, 6. <P>SOLUTION: An adjusting means 15 is provided, which can supply most or all of oil discharged from the oil supplying passage 11 into between both rolling bearings 5, 6 when the oil introducing amount into the oil supplying passage 11 is small, while, regulates oil supply from the oil supplying passage 11 into between both rolling bearings 5, 6 when the oil introducing amount into the oil supplying passage 11 is large. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a bearing device and a differential using the bearing device. The differential is mounted on a vehicle such as an automobile.

  Generally, a differential mounted on a vehicle such as an automobile is rotatably supported on a differential case by a pair of rolling bearings in which a drive pinion shaft serving as an input shaft thereof is separated in the axial direction.

  Then, the oil in the differential case is sprung up by the rotation of the ring gear, and is guided to the annular space between the pair of rolling bearings through the oil supply passage provided on the ceiling side of the differential case, so that the both rolling bearings are lubricated. (For example, refer to Patent Document 1). Such a lubrication form is called an oil splash lubrication system.

  By the way, when the ring gear rotates at a low speed, the oil supply amount to the pair of rolling bearings tends to be insufficient due to the relationship that the oil splash amount decreases and the oil supply amount to the oil supply path decreases. In that case, the lubrication and cooling performance of the pair of rolling bearings tends to decrease.

  On the other hand, the oil supply amount to the pair of rolling bearings tends to be excessive due to the relation that the oil splash amount increases and the oil supply amount to the oil supply path increases at the middle and high speed rotation of the ring gear. In this case, the lubrication and cooling performance of the pair of rolling bearings becomes higher than necessary, but the friction loss increases, for example, the oil agitation resistance by the pair of rolling bearings increases.

  On the other hand, in the differential as described above, an annular space between the pair of rolling bearings may be used as an oil reservoir chamber, and the oil level of the oil reservoir chamber may be maintained at a substantially constant height. (For example, refer to Patent Document 2).

  In this conventional example, at the entrance of the oil supply path installed on the ceiling side of the differential case, an open / close valve that makes its opening area variable is provided, and a float is floated on the oil level in the oil reservoir chamber, When the float rises as the oil level rises, the amount of oil introduced into the oil supply path is reduced by moving the on-off valve to the closing side through the connecting member, while the oil level drops as the oil level drops. When the float is lowered, the oil introduction amount to the oil supply path is increased by moving the on-off valve to the opening side through the connecting member.

In this configuration, when the oil level in the oil reservoir chamber is low, the inlet of the oil supply passage is enlarged to increase the amount of oil introduced into the oil supply passage as much as possible. When the surface is high, the oil level in the oil reservoir chamber is kept substantially constant by reducing the oil introduction into the oil supply path as much as possible by reducing the inlet of the oil supply path. Yes.
JP 11-48805 A Japanese Utility Model Publication No. 61-11057

  In short, the above-described conventional example adjusts the amount of oil supplied to the oil reservoir chamber by changing the level of the oil level in the oil reservoir chamber provided between the two rolling bearings. In this conventional example, it is necessary to secure a large space between the installation place of the float, that is, the pair of rolling bearings, and there is a concern that the differential becomes large. Further, when it is difficult to secure a sufficient installation space for the float, there is a concern that the movable range of the float becomes small and the adjustment range of the oil level becomes insufficient. There is room for improvement here.

  The present invention relates to a bearing device that rotatably supports a rotating shaft on a case via a pair of rolling bearings, wherein the oil supply to the pair of rolling bearings is excessive or insufficient in accordance with a change in the amount of oil introduced to the oil supply path. The purpose is to make adjustments possible.

  An object of the present invention is to make it possible to adjust the oil supply between the pair of rolling bearings so as not to be excessive or deficient in a differential employing an oil splash lubrication system in accordance with an increase or decrease in the rotational speed of the ring gear. Yes.

  The present invention provides a pair of rolling bearings interposed between the case and the rotating shaft so as to rotatably support the rotating shaft in a horizontal orientation in the case, and between the inner rings of the both rolling bearings. A cylindrical spacer that is externally fitted to the rotary shaft so as to be interposed in the bearing, and the case is provided with an oil supply path for supplying oil between the rolling bearings, When the amount of oil introduced into the oil supply path is small, most or all of the oil discharged from the oil supply path can be supplied between the rolling bearings, while the oil to the oil supply path When the introduction amount is large, there is provided an adjusting means for restricting oil supply from the oil supply path to the two rolling bearings.

  According to this configuration, when the amount of oil introduced into the oil supply path is small, all or most of the introduced oil is supplied between the rolling bearings, so that it is necessary to supply oil to the rolling bearings. It will be enough. This makes it possible to improve the lubrication and cooling conditions of the double rolling bearing.

  On the other hand, when the amount of oil introduced into the oil supply passage is large, the flow rate is restricted so that the introduced oil is difficult to be supplied between the rolling bearings. Therefore, excessive oil is supplied to the rolling bearings. You do n’t have to. This makes it possible to reduce friction loss associated with oil agitation by the double rolling bearing while maintaining good lubrication and cooling conditions for the double rolling bearing.

  As described above, according to the present invention, the oil supply amount between the rolling bearings can be adjusted so as not to be excessive or insufficient in accordance with the increase / decrease change of the oil introduction amount with respect to the oil supply passage. However, the adjustment of the oil supply amount is arbitrarily set empirically based on an appropriate experiment.

  Preferably, the case is provided with an oil recirculation path for returning the oil existing outside the one rolling bearing to the oil supply source, and the oil recirculation path communicates with the following outer diameter side annular oil path. A bypass passage is provided. The adjusting means is provided so as to cover the spacer, and has an inner diameter side annular oil passage on the inner diameter side that communicates with the inside of the both rolling bearings, and an outer diameter side that communicates with the oil supply path on the inside of the both rolling bearings. A cylindrical member provided with an introduction port for leading the oil discharged from the oil supply passage to the inner diameter side annular oil passage on the top side, And a valve body that is slidably accommodated in the circumferential direction so as to increase or decrease the opening area of the introduction port and the bypass passage in the annular oil passage. When the amount of oil introduced into the oil supply passage is small and the amount of oil supplied from the oil supply passage to the outer-diameter annular oil passage is less than a certain amount, the valve body opens the introduction port fully. While the bypass passage is disposed at a position where it is fully closed, the amount of oil introduced into the oil supply passage is large, and the amount of oil supply from the oil supply passage to the outer annular oil passage increases to a certain amount or more. When this is done, the slide is slid to a position where the inlet is closed and the bypass passage is open.

  In this configuration, the adjustment means is specified as a form in which the valve body is directly and automatically displaced by the amount (pressure) of oil supplied from the oil supply passage to the outer diameter side annular oil passage.

  This specification eliminates the need for a drive source (such as a motor or a hydraulic actuator) for driving the valve body, which is advantageous in reducing equipment costs. Moreover, it is not necessary to secure the installation location of the float as in the conventional example in which the valve body is indirectly displaced through the float due to the above specification, which is advantageous in making the differential compact or increasing the design flexibility. It becomes.

  Preferably, in the middle of the cylindrical member in the axial direction, a projecting portion that projects radially inward so as to divide the inner diameter side annular oil passage into two axial directions is provided continuously in the circumferential direction. The introduction port is provided on the top side of the outer circumferential groove in the annular projecting portion.

  According to this configuration, the oil that has flowed into the inner diameter side annular oil passage from the outer diameter side annular oil path through the introduction port is diverted to both sides of the annular extension portion, and the diverted oil is dammed in the extension portion. With the stopping action, it becomes difficult to be biased toward one of the rolling bearings. This facilitates management so that both the rolling bearings are properly lubricated and cooled.

  Preferably, in the lower half region of the two wall portions arranged to face each other in the axial direction in the annular projecting portion, the outer diameter side annular oil passage and the inner diameter side annular oil passage are respectively penetrated in the thickness direction. A normally open communication path that is communicated and smaller than the introduction port is provided.

  According to this configuration, since the inner diameter side annular oil passage and the outer diameter side annular oil path are always in communication with each other through the communication paths of the two wall portions, according to the oil pressure difference between the two annular oil paths. The oil can be circulated between the two annular oil passages.

  For example, when the oil in the inner diameter side annular oil path is less than the oil in the outer diameter side annular oil path, the oil in the outer diameter side annular oil path flows into the inner diameter side annular oil path through the communication path. Become.

  On the other hand, when the oil in the inner diameter side annular oil passage is larger than the oil in the outer diameter side annular oil passage, the oil is passed through the two communication passages to the inner diameter side by the pressure of the oil in the outer diameter side annular oil passage. It flows into the annular oil passage.

  The oil flowing into the inner diameter side annular oil passage from the communication path of the one wall portion flows toward the one rolling bearing side and flows into the inner diameter side annular oil passage from the communication path of the other wall portion. The oil to flow flows toward the other rolling bearing side.

  Preferably, the valve body includes a partial arc-shaped body disposed on the outer periphery of the cylindrical member so as to be slidable in the circumferential direction in a state where the introduction port can be opened and closed, and a circumferential end of the body. The operation piece is provided so as to project outward in the radial direction and has a shape corresponding to the cross-sectional shape of the outer diameter side annular oil passage.

  In the case of the valve body having this configuration, the oil pressure supplied from the oil supply passage to the outer diameter side annular oil passage acts on the front surface of the operation piece. Therefore, for example, when the oil supply amount to the outer diameter side annular oil passage increases and the oil pressure acting on the operation piece increases, the body is gradually slid along the outer periphery of the cylindrical member, The body gradually closes the introduction port, and the operation piece is arranged at a position where the communication area of the bypass passage with respect to the outer diameter side annular oil passage is gradually increased.

  In addition, the valve body having the above-described configuration is advantageous in reducing equipment costs, for example, a product obtained by press-molding a metal plate can be obtained, and mass production can be performed at low cost.

  The differential according to the present invention meshes with a differential case, a differential reduction mechanism provided in the differential case, and a ring gear having a power input shaft connected to the outer end and provided in the differential reduction mechanism at the inner end. A drive pinion shaft on which a drive pinion gear is provided; and a bearing device that rotatably supports the drive pinion shaft on the differential case; and the oil in the differential case is moved upward as the ring gear rotates. A differential is provided with an oil supply path for jumping up and supplying to the bearing device, wherein the bearing device is configured as described above, the drive pinion shaft is configured as the rotary shaft described above, and the differential case is The case described above Are, it is characterized in that.

  According to this configuration, oil can be supplied to the pair of rolling bearings that support the drive pinion shaft without excess or deficiency, so that the lubrication and cooling conditions of the both rolling bearings can be maintained particularly well during low-speed rotation. In addition, during medium and high speed rotation, it is possible to reduce friction loss due to oil agitation by the double rolling bearing.

  This is advantageous for smoothing the operation of each part in the differential and improving durability.

  Further, the differential described above employs an oil splash lubrication system, and therefore does not use an oil supply source such as an oil pump, which is advantageous in reducing equipment costs and installation space.

  According to the bearing device of the present invention, it is possible to adjust the oil supply to the pair of rolling bearings without excess or deficiency according to the increase / decrease change of the oil introduction amount to the oil supply path. Therefore, for example, depending on the rotation state of the rotary shaft, the rolling bearing is improved in lubrication and cooling properties to improve the seizure resistance, or the oil stirring resistance by the rolling bearing is reduced to reduce the friction loss. It becomes possible to be in a state.

  According to the differential according to the present invention, it is possible to adjust the oil supply to the pair of rolling bearings without excess or deficiency in accordance with the change in the rotational speed of the ring gear. Therefore, for example, depending on the rotation state of the drive pinion shaft, the pair of rolling bearings that support the drive pinion shaft can be lubricated and cooled to improve the durability of the differential, and the drive pinion shaft can be reduced in friction loss. It is possible to reduce or increase the smoothness of operation.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the best embodiment of the present invention will be described in detail with reference to the drawings.

  1 to 7 show an embodiment of the present invention. The illustrated differential is an example of a type mounted on a front engine / rear drive (FR) type vehicle.

  Prior to the description of the part to which the features of the present invention are applied, an outline of an automobile differential to which the present invention is applied will be described with reference to FIGS.

  FIG. 1 shows a state in which the differential is a longitudinal section, and FIG. 2 shows a state in which the differential is a transverse section. In the figure, 1 is a differential case (also called a differential carrier), 2 is a differential transmission mechanism, 3 is a drive pinion gear, and 4 is a drive pinion shaft.

  The differential case 1 has a two-piece structure in which a front case 1a and a rear case 1b are combined, for example. A predetermined amount of lubricating oil is stored in the differential case 1.

  The differential transmission mechanism 2 distributes the power input from the drive pinion shaft 4 to the left and right axles (called drive shafts) 10A and 10B as necessary, and outputs the driving force to wheels (not shown). The differential case 1 is disposed on the front case 1a side.

  Although this differential transmission mechanism 2 has a generally known configuration, it is a portion that is not directly related to the features of the present invention. Therefore, only the ring gear 2a is shown in FIG. Detailed illustrations and explanations of pinion gears and side gears are omitted.

  The drive pinion gear 3 is meshed with the ring gear 2 a of the differential transmission mechanism 2, and is integrally formed on the inner end side of the drive pinion shaft 4.

  The drive pinion shaft 4 is rotatably supported at a required position of the front case 1a of the differential case 1 through two rolling bearings 5 and 6 at two locations separated in the axial direction. The drive pinion shaft 4 is in a horizontal posture. In general, when the differential is mounted on a vehicle, the drive pinion shaft 4 is inclined because the differential is in a front-up position as shown in FIG.

  A flange joint 7 to which a propulsion shaft (not shown) (not shown) is connected is provided on the outer end side of the drive pinion shaft 4. That is, the drive pinion shaft 4 is an input shaft for driving force.

  In the present embodiment, the two rolling bearings 5 and 6 described above are both tapered roller bearings, and the two tapered roller bearings are assembled in an outwardly combined state, and a cylindrical shape is provided between the inner rings (reference numerals omitted). The relative positions of the rolling bearings 5 and 6 are defined by interposing the spacer 8.

  For reference, of the two rolling bearings 5 and 6, the one located on the upstream side in the power transmission direction, that is, on the flange joint 7 side is called the front side (or the tail side), and the downstream side in the power transmission direction, that is, the drive pinion gear 3 The side located on the side is called the rear side (or head side). Generally, the rear-side rolling bearing 6 is larger than the front-side rolling bearing 5 and has a larger load capacity.

  By the way, between the outer peripheral surface on the outer end side of the drive pinion shaft 4 and the inner peripheral surface on the small end side of the front case 1a of the differential case 1, the oil leakage to the outside of the differential case 1 is prevented. An oil seal 9 is attached. Although not shown in detail in the drawing, the oil seal 9 is, for example, a type having a seal lip that contacts the outer peripheral surface of the flange joint 7 on the inner diameter side.

  The differential described above employs an oil splashing lubrication system in which oil existing on the bottom side of the differential case 1 is splashed by the ring gear 2a and guided to the annular space between the pair of rolling bearings 5 and 6.

  As shown in FIG. 1, an oil supply path 11 is provided at the top of the upper half of the front case 1 a of the differential case 1.

  The oil supply path 11 receives oil splashed by the ring gear 2 a and then discharges the oil above the annular space between the pair of rolling bearings 5 and 6.

  Further, as shown in FIG. 2, an oil return path 12 is provided at a predetermined position in the lower half of the front case 1a of the differential case 1 (for example, a region corresponding to the hour hand on the timepiece dial between 6 o'clock and 9 o'clock). Yes.

  The oil recirculation path 12 returns oil existing upstream of the front rolling bearing 5 in the power transmission direction to the rear case 1 b side of the differential case 1.

  In the above-described differential, the differential case 1, the drive pinion shaft 4, the two rolling bearings 5 and 6, the spacer 8, and the like constitute a bearing device.

  Next, portions to which the features of the present invention are applied will be described.

  In short, in the differential described above, the adjusting means 15 for adjusting the oil supply amount to the bearings 5 and 6 is provided between the pair of rolling bearings 5 and 6 on the front case 1a side of the differential case 1.

  This adjusting means 15 is a pair of rolling bearings for most or all of the oil discharged from the oil supply path 11 when the amount of oil introduced into the oil supply path 11 is small, such as when the ring gear 2a is stopped or when rotating at a low speed. When the amount of oil introduced into the oil supply path 11 is large, such as during the middle and high-speed rotation of the ring gear 2a, the pair of rolling bearings 5, 6 It is in a state that regulates the oil supply between them.

  Specifically, the adjusting means 15 includes a cylindrical member 20 and a valve body 30 as shown in FIGS. 1 to 6.

  The cylindrical member 20 is installed in a fixed state on the inner diameter side of the front case 1a so as to cover the spacer 8 in the front case 1a, so that the annular space between the pair of rolling bearings 5 and 6 is radially inward and outward. The outer circumferential side annular oil passage 41 and the inner diameter side annular oil passage 42 are formed by partitioning.

  The outer diameter side annular oil passage 41 communicates with the discharge port of the oil supply passage 11 and does not communicate with the inside of the rolling bearings 5 and 6. On the other hand, both end portions in the axial direction of the inner diameter side annular oil passage 42 communicate with the inside of the rolling bearings 5 and 6.

  In this embodiment, the cylindrical member 20 has a three-step outer diameter with large, medium, and small outer diameters. The large-diameter cylindrical portion 21 on the rear side and the medium-diameter cylindrical portion on the front side. 22 is provided with a small diameter cylindrical portion 23 therebetween.

  The small-diameter cylindrical portion 23 has a shape projecting radially inward so as to divide the inner-diameter annular oil passage 42 into two in the axial direction, and corresponds to the annular projecting portion according to the claims. Is. That is, the small-diameter cylindrical portion 23 removes the oil existing on the rolling bearing 5 side on the front side from the oil flowing from the outer-diameter-side annular oil passage 41 to the inner-diameter-side annular oil passage 42 through the following inlet 24. This is useful in order to make it difficult to flow to the side of the rolling bearing 6 so that a necessary and sufficient amount remains on the side of the rolling bearing 5 on the front side.

  An introduction port 24 for communicating the outer diameter side annular oil passage 41 and the inner diameter side annular oil passage 42 is provided at one circumferential position (near the top) in the outer circumferential groove of the small diameter cylindrical portion 23. The introduction port 24 is disposed substantially directly below the oil supply path 11. Moreover, although the inlet 24 is a long hole along the circumferential direction, its shape is not particularly limited.

  In addition, in the lower half regions of the two wall portions 27 and 28 that are opposed to each other in the axial direction in the small diameter cylindrical portion 23, the outer diameter side annular oil passage 41 and the inner diameter side annular oil passage penetrate in the thickness direction. Communication passages 25 and 26 for communicating with 42 are provided. The communication passages 25 and 26 have an elliptical shape, but the shape is not particularly limited.

  A bypass passage communicating with the oil return passage 12 is provided at one circumferential position of the region constituting the outer diameter side annular oil passage 41 in the front case 1a (for example, a region corresponding to the hour hand of the clock face between 8 o'clock and 11 o'clock). 13 is provided.

  The valve body 30 is accommodated in the outer circumferential side annular oil passage 41 so as to be displaceable in the circumferential direction, and the opening area of the introduction port 24 and the opening area of the oil return passage 12 are increased or decreased according to the displacement stroke. To be adjusted.

  When the amount of oil supplied from the oil supply passage 11 to the outer diameter side annular oil passage 41 increases by a certain amount or more, the valve body 30 moves in the outer diameter side annular oil passage 41 in one circumferential direction with the pressure of the oil ( For example, it is slid clockwise), and the opening area of the introduction port 24 is increased or decreased, and the opening area of the bypass passage 13 is increased or decreased.

  Specifically, the valve body 30 has a shape in which an operation piece 32 is provided at one end in the circumferential direction (longitudinal direction) of the body 31.

  Although the body 31 has a partial arc shape, the outer diameter is formed along the outer peripheral surface of the cylindrical member 20 having a three-stage outer diameter, and the outer diameter side of the cylindrical member 20, that is, the outer diameter side annular oil passage 41. The outer peripheral surface of the cylindrical member 20 is slidably arranged as a guide rail. That is, the body 31 slides to open and close the introduction port 24 and plays a role of increasing or decreasing the opening area of the introduction port 24.

  The operation piece 32 is provided on the one end side in the circumferential direction of the body 31 so as to project outward in the radial direction. The outer shape of the operation piece 32 is a shape corresponding to the cross-sectional shape of the outer diameter side annular oil passage 41, and the outer dimension is set slightly smaller than the cross-sectional area of the outer diameter side annular oil passage 41. . That is, the operation piece 32 plays a role of increasing or decreasing the opening area of the oil return path 12.

  The valve body 30 protrudes radially inward at a predetermined position on the inner periphery of the front case 1a and a closed stopper 43 provided so as to protrude radially outward at a predetermined position on the outer periphery of the cylindrical member 20. The displacement stroke is regulated by the open-side stopper 44 provided as described above.

  In addition, when the oil discharged from the oil supply passage 11 flows into the outer diameter side annular oil passage 41, the open side stopper 44 is unidirectional in the circumferential direction of the outer diameter side annular oil passage 41 (in FIG. It plays a role of regulating the inflow in the direction of rotation).

  Next, the operation of the adjusting means 15 described above will be described with reference to FIGS.

  First, when the differential is not operating, that is, when the drive pinion shaft 4 and the ring gear 2a are stopped rotating, the oil in the rear case 1b is not splashed up by the ring gear 2a, so that the oil is not introduced into the oil supply passage 11. Become.

  In this state, the oil in the inner diameter side annular oil passage 42 is discharged from the communication passages 25 and 26 to the outer diameter side annular oil passage 41, and the oil in the outer diameter side annular oil passage 41 passes through the bypass passage 13 and It is returned to the rear case 1b through the oil return path 12. Therefore, the oil level in the differential case 1 is set at a position where the communication paths 25 and 26 exist, for example, as indicated by H in FIGS. 1 and 3.

  In this state, the valve element 30 of the adjusting means 15 slides downward due to its own weight, but as shown in FIG. 3, it is received by the closing stopper 43 and stops at that position. In this state, the introduction port 24 is fully opened, and the bypass passage 13 is fully closed, that is, the outer diameter side annular oil passage 41 is hermetically closed with the outer diameter side annular oil passage 41 and the bypass passage 13 not communicating. It has become.

  When the drive pinion shaft 4 rotates, the oil in the rear case 1b is spun up by the ring gear 2a that is driven to rotate by the drive pinion shaft 4 and introduced into the oil supply path 11.

  The oil introduced into the oil supply path 11 is discharged to the upper approximate center in the axial direction between the pair of rolling bearings 5 and 6.

  Here, when the ring gear 2a is rotating at a low speed, the oil splashing action by the ring gear 2a is weak, so the amount of oil introduced into the oil supply path 11 is reduced. At this time, as shown by the arrows in FIG. 3, most of the oil discharged from the oil supply passage 11 flows into the inner diameter side annular oil passage 42 from the introduction port 24 of the adjusting means 15.

  When the inner diameter side annular oil passage 42 is filled with oil in this way, excess oil also flows into the outer diameter side annular oil passage 41. As long as the amount of oil flowing into the outer diameter side annular oil passage 41 is small, the valve body 30 of the adjusting means 15 is in a state of closing the bypass passage 13 as described above. The oil gradually accumulates in the annular oil passage 41 as well. Accordingly, the oil in the outer diameter side annular oil passage 41 flows into the inner diameter side annular oil passage 42 from the normally open communication passages 25 and 26.

  The oil flowing into the inner diameter side annular oil passage 42 lubricates and cools the pair of rolling bearings 5 and 6. Thereafter, the oil that has passed through the rear rolling bearing 6 is directly discharged to the rear case 1 b, but the oil that has passed through the front rolling bearing 5 is returned to the rear case 1 b through the oil return path 12.

  In this way, when the drive pinion shaft 4 rotates at a low speed, the amount of oil introduced into the oil supply passage 11 is small, but most or all of the oil discharged from the oil supply passage 11 is fed from the inlet 24 to the inner diameter side annular oil passage 42. In addition, the oil existing in the outer diameter side annular oil passage 41 is also allowed to flow into the inner diameter side annular oil passage 42 from the communication passages 25 and 26. A necessary and sufficient amount of oil can be supplied.

  Thereby, it becomes possible to make it the state which improves lubrication and cooling property of a pair of rolling bearings 5 and 6, and it becomes possible to improve seizure resistance.

  Next, when the drive pinion shaft 4 and the ring gear 2a rotate at medium and high speeds, the oil splashing action by the ring gear 2a becomes stronger, so that the amount of oil introduced into the oil supply path 11 increases.

  Therefore, a large amount of oil discharged from the oil supply passage 11 flows into the inner diameter side annular oil passage 42 from the introduction port 24 of the adjusting means 15, so that the inside of the inner diameter side annular oil passage 42 becomes oil within a relatively short time. Will be filled.

  Thus, after the inside of the inner diameter side annular oil passage 42 is filled with oil, a large amount of oil discharged from the oil supply passage 11 is divided into the inner diameter side annular oil passage 42 and the outer diameter side annular oil passage 41. become.

  Here, the oil flowing into the inner diameter side annular oil passage 42 lubricates and cools the pair of rolling bearings 5 and 6 and then returns to the rear case 1b.

  On the other hand, a large amount of oil flows into the outer diameter side annular oil passage 41 which is in a sealed state at the present time, but when the oil inflow amount into the outer diameter side annular oil passage 41 increases to a certain amount or more. The oil pressure acts on the operation piece 32 of the valve body 30, and the valve body 30 is slid in one circumferential direction (clockwise direction).

  As the valve body 30 slides, the body 31 of the valve body 30 gradually closes the inlet 24 and the opening area of the inlet 24 is gradually reduced. At the same time, the opening area of the bypass passage 13 is reduced. It becomes gradually increased. Finally, as shown in FIG. 4, when the operation piece 32 of the valve body 30 is brought into contact with the opening-side stopper 44, the introduction port 24 is fully closed, and the bypass passage 13 is fully opened.

  In this state, oil discharged from the oil supply passage 11 cannot flow into the inner diameter side annular passage 42, so that all of it flows into the outer diameter side annular oil path 41. That is, the oil supply into the inner diameter side annular passage 42 is regulated so as not to be excessive.

  And most of the oil flowing into the outer diameter side annular oil passage 41 is returned to the rear case 1b through the bypass passage 13 and the oil return passage 12, but a part of the communication passage 25 is normally open. 26 flows into the inner diameter side annular oil passage 42.

  As described above, when the drive pinion shaft 4 rotates at a medium to high speed, the amount of oil introduced into the oil supply passage 11 increases, so that oil cannot be supplied from the inlet 24 to the inner diameter side annular passage 42, so By restricting the oil in the oil passage 41 through the communication passages 25 and 26 to the inner diameter side annular oil passage 42 in an appropriate amount, the oil is prevented from being excessively supplied to the pair of rolling bearings 5 and 6. Yes.

  Therefore, the oil agitation resistance by the pair of rolling bearings 5 and 6 is suppressed to a necessary minimum, and it becomes possible to reduce useless friction loss.

  Incidentally, regarding the volume of the inner diameter side annular oil passage 42 and the outer diameter side annular oil passage 41, etc., an appropriate oil amount for stabilizing the lubrication and cooling conditions of the front side rolling bearing 5 and the rear side rolling bearing 6 is set. The amount of oil supplied to the front-side rolling bearing 5 and the rear-side rolling bearing 6 should not be less than the minimum necessary and should not be excessively supplied in any operating condition. Is set.

  As described above, according to the embodiment to which the present invention is applied, when the amount of oil introduced into the oil supply passage 11 is small, such as when the ring gear 2a is stopped and when rotating at a low speed, the pair of rolling bearings 5 and 6 are applied. Since a necessary and sufficient amount of oil can be supplied, it is possible to improve the lubrication and cooling performance of the pair of rolling bearings 5 and 6, while the oil is used at the middle and high speed rotation of the ring gear 2 a. When the amount of oil introduced into the supply passage 11 is large, the supply of oil to the pair of rolling bearings 5 and 6 is regulated so as not to be excessive. Therefore, friction loss due to oil agitation by the pair of rolling bearings 5 and 6 is reduced. It becomes possible to make it the state to reduce.

  Further, in the above embodiment, the adjusting means 15 is simply incorporated as a separate member in the differential case 1, so that the differential itself is simpler and less expensive than the case where the oil supply distribution is designed in consideration. This is preferable because it can be done with something.

  Further, in the above-described embodiment, the valve body 30 of the adjusting means 15 is configured to be displaced directly and automatically by the amount (pressure) of oil. Therefore, a drive source (motor) for driving the valve body 30 is used. And a hydraulic actuator are not required, which makes it possible to simplify the configuration and reduce equipment costs. In addition, unlike the conventional example in which the valve body is indirectly displaced through the float, it is not necessary to secure a place for installing the float, which is advantageous in making the differential compact or increasing the degree of freedom in design.

  In addition, this invention is not limited only to the said embodiment, All the deformation | transformation and application included in the range equivalent to the claim and the said range are possible. Examples are given below.

  (1) In the above embodiment, an example is given in which both the pair of oblique contact type rolling bearings 5 and 6 are tapered roller bearings. However, both of the rolling bearings 5 and 6 are both angular ball bearings or tandem double rows. It is possible to use a ball bearing or the like, or a combination of a front side rolling bearing 5 as an angular ball bearing or a tandem double row ball bearing and a rear side rolling bearing 6 as a tapered roller bearing. is there.

  (2) In the above embodiment, a differential mounted on an FR (front engine / rear drive) type vehicle is taken as an example. However, the present invention can also be applied to differentials mounted on FF (front engine / front drive) type vehicles and 4WD (four wheel drive) type vehicles.

  (3) In the above embodiment, in the small diameter cylindrical portion (annular projecting portion) of the cylindrical member 20 of the adjusting means 15, the communication paths 25 and 26 are provided in the two wall portions 27 and 28 that face each other in the axial direction. However, the formation positions of the communication passages 25 and 26 are not particularly limited.

  For example, as shown in FIG. 8, in the tubular member 20, the communication passages 25 and 26 are provided separately on the large diameter cylindrical portion 21 and the medium diameter cylindrical portion 22 on both sides of the small diameter cylindrical portion 23, It is included in the present invention.

  Also in this case, the oil flowing into the inner diameter side annular oil passage 42 from the front side communication passage 25 provided in the medium diameter cylindrical portion 22 is directed to the front side rolling bearing 5 in the same manner as in the above-described embodiment. On the other hand, the oil flowing into the inner diameter side annular oil passage 42 from the rear side communication path 26 provided in the large diameter cylindrical portion 21 is directed to the rear side rolling bearing 6, so that the oil is in the inner diameter side annular shape. It is avoided that the oil passage 42 is biased in one axial direction.

  (4) In the above embodiment, the cylindrical member 20 of the adjusting means 15 is provided with the small-diameter cylindrical portion 23 (annular projecting portion). However, an annular projecting portion such as the small-diameter cylindrical portion 23 is provided. Those not included are also included in the present invention.

  In accordance with the change of the cylindrical member 20, the shape of the body 31 of the valve body 30 also needs to be a shape that follows the outer peripheral shape of the cylindrical member 20. In that case, since the valve body 30 becomes a comparatively simple shape, it can contribute to reduction of manufacturing cost. In such a case, basically the same operations and effects as the above-described example can be obtained.

  (5) The valve body 30 of the adjusting means 15 in the above embodiment is not particularly limited, and although not shown, it can be implemented in various forms.

It is a longitudinal cross-sectional view which shows the differential for motor vehicles which is one Embodiment of this invention. It is a cross-sectional view of the differential of FIG. It is an arrow view of the (3)-(3) cross section of FIG. 1, and is a figure for demonstrating the state of the adjustment means at the time of a stop or low speed rotation. It is a figure for demonstrating the state of the adjustment means at the time of medium-high speed rotation in FIG. It is a perspective view which shows the adjustment means of FIGS. It is the perspective view which changed the direction which sees the adjustment means of FIG. It is a perspective view which takes out and shows only the outer diameter side annular oil path of FIG. It is a longitudinal cross-sectional view which shows the differential which is other embodiment of this invention.

Explanation of symbols

1 Differential case
2 Differential transmission mechanism
2a Ring gear
3 Drive pinion gear
4 Drive pinion shaft 5, 6 Rolling bearing 11 Oil supply path 12 Oil recirculation path 13 Bypass path 15 Adjustment means 20 Cylindrical member 23 Small diameter cylindrical portion (overhanging portion) of cylindrical member
24 Introducing port of cylindrical member 25, 26 Communication path 30 Valve body 31 Body of valve body 32 Operation piece of valve body

Claims (6)

A pair of rolling bearings interposed between the case and the rotating shaft so as to rotatably support the rotating shaft in a horizontal orientation in the case, and between the inner rings of both rolling bearings. A cylindrical spacer that is externally fitted to the rotary shaft so that the case is provided with an oil supply path for supplying oil between the rolling bearings,
When the amount of oil introduced into the oil supply path is small, most or all of the oil discharged from the oil supply path can be supplied between the rolling bearings,
A bearing device comprising adjusting means for restricting oil supply from the oil supply path to the two rolling bearings when the amount of oil introduced into the oil supply path is large. The bearing device according to claim 1,
The case is provided with an oil return path for returning the oil existing outside the one rolling bearing to the oil supply source, and a bypass path communicating the oil return path with the outer diameter side annular oil path described below. Is provided,
The adjusting means is provided so as to cover the spacer, and has an inner diameter side annular oil passage on the inner diameter side that communicates with the inside of the both rolling bearings, and an outer diameter side that communicates with the oil supply path on the inside of the both rolling bearings A cylindrical member provided with an introduction port for guiding the oil discharged from the oil supply passage to the inner diameter side annular oil passage on the top side,
A valve body that is slidably housed in a circumferential direction so as to increase or decrease the opening area of the introduction port and the bypass passage in the outer diameter side annular oil passage,
When the amount of oil introduced into the oil supply passage is small and the amount of oil supplied from the oil supply passage to the outer-diameter annular oil passage is less than a certain amount, the valve body opens the introduction port fully. While placed in a position where the bypass passage is fully closed,
When the amount of oil introduced into the oil supply passage is large and the amount of oil supply from the oil supply passage to the outer diameter side annular oil passage increases to a certain amount or more, the introduction port is closed and the bypass passage is The bearing device is characterized by being slid to a position where is opened. The bearing device according to claim 2,
In the middle of the cylindrical member in the axial direction, a projecting portion that projects radially inward so as to divide the inner annular oil passage into two axial directions is provided continuously in the circumferential direction. The bearing device, wherein the introduction port is provided on the top side of the outer circumferential groove in the overhanging portion. The bearing device according to claim 3,
In the lower half regions of the two wall portions disposed opposite to each other in the axial direction in the annular projecting portion, the outer diameter side annular oil passage and the inner diameter side annular oil passage are communicated with each other through in the thickness direction. A bearing device characterized in that a normally-open communication path smaller than the introduction port is provided. The bearing device according to any one of claims 2 to 4,
The valve body includes a partially arcuate body that is slidably disposed on an outer periphery of the tubular member in a state in which the introduction port can be opened and closed, and a radially outer end on one end side in the circumferential direction of the body. A bearing device comprising an operation piece provided so as to project in a direction and having a shape corresponding to a cross-sectional shape of the outer annular oil passage. A differential case, a differential reduction mechanism provided in the differential case, and a drive pinion shaft provided with a drive pinion gear that is coupled to a power input shaft at the outer end and meshes with a ring gear provided in the differential reduction mechanism at the inner end. And a bearing device that rotatably supports the drive pinion shaft on the differential case, and the differential case splashes upward with the rotation of the ring gear and supplies the oil in the differential case to the bearing device. A differential provided with an oil supply path for
The bearing device is configured as described in any one of claims 1 to 5, the drive pinion shaft is a rotating shaft according to any one of claims 1 to 5, and the differential case is claimed. The differential according to any one of Items 1 to 5, wherein the differential is characterized in that

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