JP2007315456A - Differential - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce power loss and improve durability in a differential adopting an oil splashing lubricating method in which oil inside a differential case 1 is splashed upward along with rotation of a ring gear 2a, and after the oil is led to the side of two slant contact rolling bearings 5, 6 for supporting a drive pinion gear shaft 4 with respect to the differential case 1, the oil is returned to the ring gear 2a side. <P>SOLUTION: The differential is equipped with a flow rate adjusting mechanism 20 for increasing the oil supply amount for each slant contact rolling bearings 5, 6 when the differential is in a frontward ascending attitude compared to a normal attitude. Thereby, while the oil supply amount to between the two slant contact rolling bearing 5, 6 at a normal attitude is appropriate without excess or deficiency, sufficient oil supply amount can be supplied to between the two slant contact rolling bearings 5, 6 in a frontward ascending attitude. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a differential mounted on a vehicle such as an automobile, and in particular, an oil supply form for two oblique contact rolling bearings supporting the drive pinion gear shaft is improved.

  For example, in the differential, the drive pinion gear shaft that is the input shaft is supported by two oblique contact type rolling bearings separated in the axial direction, but in order to lubricate these oblique contact type rolling bearings, In addition, the oil in the differential case is bounced up by a rotating ring gear and guided to the two oblique contact type rolling bearings (see, for example, Patent Document 1). Such a lubrication form is called an oil splash lubrication system.

  In the above conventional example, the oil pumped up by the ring gear is guided to the oil guide rib provided on the ceiling side through the left and right inclined portions formed on the inner surface of the differential case, and the oil is inclined from the rib. It leads to the tangential rolling bearing side.

  By the way, it is advantageous to supply as much oil as possible to the slanted rolling bearing side in order to improve lubrication and cooling performance. However, if too much oil is added, friction loss due to oil stirring by the slanted rolling bearing will occur. Will increase. In addition, the differential case may be in a forward climbing posture, such as when the vehicle is traveling uphill, but in such a case, the amount of oil supplied to the oblique contact type rolling bearing tends to be insufficient.

  For this reason, it is necessary to set the oil supply amount to the oblique contact type rolling bearing so that a sufficient amount can be ensured in the forwardly raised posture, and it can be said that the oil supply becomes excessive in the normal posture, As described above, the friction loss of the oblique contact type rolling bearing increases, and the power loss of the differential is forced.

On the other hand, an oil reservoir that holds the oil pumped up by the ring gear is installed in the upper space of the differential case, and the oil in this oil reservoir is dripped in a certain amount between the two oblique contact type rolling bearings. (For example, refer to Patent Document 2).
Japanese Utility Model Publication No. 63-48054 JP 07-217725 A

  In the above-mentioned conventional example, although oil can be supplied between the two oblique contact type rolling bearings without excess or deficiency, when the differential case is in a forward rising posture, such as when the vehicle is running uphill, It is thought that the amount of oil supplied between the two oblique contact type rolling bearings tends to be insufficient, and there is room for improvement here.

  In the differential employing the oil splash lubrication system, the oil supply between the two oblique contact type rolling bearings in the normal posture is made appropriate without excess or deficiency, while the two oblique contact in the forward raising posture is achieved. The purpose is to ensure sufficient oil supply between the rolling bearings, to reduce the power loss of the differential and to improve the durability.

  In the present invention, after the oil in the differential case jumps upward with the rotation of the ring gear and is guided to the two oblique contact rolling bearings for supporting the drive pinion gear shaft with respect to the differential case. A differential that uses a splash-lubricated oil system that returns to the ring gear side, and the amount of oil supplied to the slanted-type rolling bearing when compared to a normal posture is higher when the front-up posture is reached. It is characterized by having an increased flow rate adjusting mechanism.

  According to this configuration, even if the oil supply amount between the two oblique contact rolling bearings in the normal posture of the differential is set to an appropriate amount without excess or deficiency, The supply amount is increased compared to the normal posture.

  As a result, friction loss due to oil agitation by the oblique contact type rolling bearing can be reduced in the normal posture, and the oblique contact type rolling bearing can be improved in lubricity in the forward rising posture. Therefore, it becomes possible to stabilize the operation of the differential and improve the durability.

  Preferably, the flow rate adjusting mechanism has a case for receiving oil splashed by a ring gear, and in this case, a flow path for guiding the received oil between the two oblique contact rolling bearings, An oil reservoir provided in the oil receiving direction from the flow path to store oil, a restricting member that restricts the amount of oil flowing into the flow path in a normal posture, and an oil reservoir in the forward lift posture A collecting member that collects and flows the oil into the flow path.

  In short, in this configuration, a part of the oil received in the normal posture is allowed to flow into the flow path and the rest is stored in the oil reservoir, and the oil that is splashed up from the ring gear when the front-up posture is reached. In addition, the oil stored in the oil reservoir is caused to flow into the flow path.

  As a result, the oil supply between the two oblique contact type rolling bearings is not excessive in the normal posture, and the oil supply between the two oblique contact type rolling bearings is sufficiently ensured in the forward raising posture. It will be.

  In addition, since the flow rate adjusting mechanism is configured to be incorporated as a separate member in the differential case, it can be much simpler and less expensive than when designing the oil supply of the differential itself. It becomes possible.

  Preferably, the flow rate adjusting mechanism has a case for receiving oil splashed by a ring gear, and the case has a flow path for guiding the received oil between the two oblique contact rolling bearings, and a normal posture. A valve element is provided that sometimes reduces the opening area of the flow path while increasing the opening area of the flow path when in a forwardly raised posture.

  According to this configuration, the flow rate is limited so that a part of the oil received in the normal posture flows into the flow path, and a large amount of oil is allowed to flow into the flow path when the front rising posture is reached.

  As a result, the oil supply between the two oblique contact type rolling bearings is not excessive in the normal posture, and the oil supply between the two oblique contact type rolling bearings is sufficiently ensured in the forward raising posture. It will be.

  Furthermore, since the flow rate adjusting mechanism is configured to be incorporated as a separate member in the differential case, the differential itself must be much simpler and less expensive than when designing the oil supply distribution. Is possible.

  Preferably, the valve body is installed in the case so as to be reciprocally displaceable in the oil supply direction, and the opening area of the flow path is minimized by the pressure of oil received in the case in a normal posture. While being displaced to a position, it is displaced to a position that maximizes the opening area of the flow path by its own weight during a front-up posture.

  According to this configuration, since the valve body is automatically displaced according to the differential posture, the configuration is simplified and the equipment is compared with the case where the operation of the valve body is electrically controlled. Cost can be reduced.

  According to the present invention, the oil supply between the two oblique contact rolling bearings in the normal posture is made an appropriate amount without excess or deficiency, while the oil supply between the two oblique contact rolling bearings in the forward rising posture is performed. Since sufficient power can be secured, it is possible to reduce the power loss of the differential and improve the durability.

  Details of the present invention will be described below based on the embodiments shown in FIGS. First, FIG. 1 to FIG. 6 show an embodiment of the present invention.

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

  The differential case 1 includes, for example, a front case 1a and a rear case 1b. A predetermined amount of lubricating oil is stored in the differential case 1.

  The differential speed change mechanism 2 distributes and transmits power input from the drive pinion gear shaft 4 to left and right axles (not shown) as required, and is disposed on the front case 1a side of the differential case 1. . Since this differential transmission mechanism 2 is a part that is not directly related to the features of the present invention, only the ring gear 2a is shown and the detailed illustration and explanation of the other parts are omitted. The configuration is such that a pinion gear or a side gear is used.

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

  The drive pinion gear shaft 4 is rotatably supported at a required position of the rear case 1b of the differential case 1 via oblique contact type rolling bearings 5 and 6, respectively, at two locations separated in the axial direction.

  A flange joint 7 to which a drive shaft (not shown) is connected is provided at the outer end of the drive pinion gear shaft 4. That is, in the differential, the drive pinion gear shaft 4 serves as an input shaft, drives the above-described differential transmission mechanism 2, and thereby outputs a driving force to the wheels.

  The two oblique contact rolling bearings 5 and 6 described above are, for example, tapered roller bearings, angular ball bearings, tandem double row ball bearings, etc., but in this embodiment, two tapered roller bearings are used, The two tapered roller bearings are assembled in an outwardly combined state, and a cylindrical spacer 8 is interposed between them to define the relative positions of the two bearings.

  An oil seal 9 is provided between the outer peripheral surface on the outer end side of the drive pinion gear shaft 4 and the inner peripheral surface on the small end side of the rear case 1b of the differential case 1 to prevent oil leakage to the outside. Is installed.

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

  In the differential described above, the oil present on the bottom side of the differential case 1 is splashed by the ring gear 2a and guided to the oblique contact type rolling bearings 5 and 6 and then returned to the ring gear 2a. Lubrication method is adopted.

  In such a differential, as shown in FIG. 3, when the differential is in a front-up position in the space above the two oblique contact rolling bearings 5, 6 on the rear case 1 b side of the differential case 1, A flow rate adjusting mechanism 20 is provided to increase the amount of oil supplied to the oblique contact type rolling bearings 5 and 6 as compared with the normal posture.

  As shown in FIGS. 1 to 6, the flow rate adjusting mechanism 20 has a case 21 that receives oil splashed by the ring gear 2 a.

  The case 21 includes a first passage 22 for guiding the received oil to the front end side of the oblique contact rolling bearing 5 disposed on the differential front end side of the two oblique contact rolling bearings 5 and 6, and the first passage 22. A second passage 23 is provided, which is arranged adjacent to the first passage 22 and leads between the two oblique contact rolling bearings 5 and 6.

  The 1st channel | path 22 is a straight line shape, The ceiling and both ends are opened. The second passage 23 is, for example, a hole having a rectangular cross section, and is provided with a flow path 24 for dropping the oil received on the bottom side in the longitudinal direction between the two oblique contact rolling bearings 5 and 6. Yes. The flow path 24 is a hole formed through the bottom wall of the case 21.

  On the other hand, in the back of the second passage 23, a concave oil reservoir 25 for storing oil is provided. In the oil reservoir 25, the vertical wall 25a on the entrance side is inclined obliquely so that oil accumulated in the oil reservoir 25 can be easily discharged in the forwardly raised posture described below.

  Further, on the bottom surface of the second passage 23, a substantially V-shaped standing wall 26 in plan view is provided so as to cover the flow path 24.

  The standing wall 26 is installed such that the wide side is located on the back side of the second passage 23 and the narrow side is located on the entrance side of the second passage 23. Further, a through hole 27 is provided on the bottom surface side of the standing wall 26 for allowing oil to pass through in the thickness direction.

  In particular, in this embodiment, with respect to the standing wall 26, when the differential is in a normal posture, the limiting function for limiting the amount of oil received in the second passage 23 flows into the flow path 24, and the differential is in a front-up posture. Sometimes, a recovery function for collecting and flowing oil in the oil reservoir 25 into the flow path 24 is realized.

  However, the restriction function and the collection function can be realized by separate members, and such a configuration is also included in the present invention.

  Next, the flow of oil during the above-described differential operation will be described.

  Here, first, in the case where the differential is in a normal posture as shown in FIG. 1, when the ring gear 2a is driven forward, for example, and rotated clockwise as shown by the white arrow in FIG. With the rotation of 2a, the oil stored in the differential case 1 starts to spring up and is sent to the front case 1a side of the differential case 1.

  Thus, the oil splashed upward from the differential case 1 flows into the two passages 22 and 23 in the case 21 of the flow rate adjusting mechanism 20 at a ratio of approximately half.

  All the oil flowing into the first passage 22 is discharged from the opening on the front end side and dropped to the front end side of the oblique contact type rolling bearing 5 on the front end side, and lubricates mainly the inner ring large collar portion of the oblique contact type rolling bearing 5. After cooling, it is returned to the bottom side of the rear case 1 b of the differential case 1 through a return passage (not shown) provided in the side wall portion of the differential case 1.

  On the other hand, as shown by the arrows in FIGS. 2 and 3, a part of the oil that has flowed into the second passage 23 flows into the flow path 24 through the through hole 27 of the standing wall 26, but the rest is the oil pool. It will be stored in the part 25.

  The oil that has flowed into the flow path 24 falls between the two oblique contact rolling bearings 5 and 6, and this oil is pumped by the rotation of the both oblique contact rolling bearings 5 and 6. Thus, the inside of each bearing is fed from the small end side toward the large end side to lubricate and cool each part. The oil that has passed through the bearings 5 and 6 in this way is returned to the bottom side of the rear case 1b of the differential case 1 through the return passage, and is transmitted along the drive pinion gear shaft 4 to the rear case of the differential case 1. It is returned to the bottom side of 1b.

  In this way, when the differential is in a normal posture, the oil supply between the two oblique contact rolling bearings 5 and 6 is set to an appropriate amount without excess or deficiency.

  By the way, when the differential is in a forwardly raised position as shown in FIG. 4, for example, the oil that has been splashed up from the ring gear 2a and flowed into the second passage 23 as shown by the arrows in FIGS. Similarly, in addition to flowing into the flow path 24 through the through hole 27 of the standing wall 26, the oil stored in the oil reservoir 25 overflows and flows to the rear end side through the second passage 23. Then, they are collected by the standing wall 26 and flow into the flow path 24. For this reason, the amount of oil dropped between the two oblique contact type rolling bearings 5 and 6 through the flow path 24 is larger than that in the normal posture.

  In this way, the oil supply between the two oblique contact type rolling bearings 5 and 6 is sufficiently ensured when the differential is in the upwardly rising posture.

  During the operation of the differential, the oil in the differential case 1 is circulated as described above according to the differential posture, and each part in the differential case 1 is lubricated.

  As described above, according to the embodiment to which the present invention is applied, the oil supply amount between the two oblique contact type rolling bearings 5 and 6 in the normal differential posture is set to an appropriate amount without excess or deficiency. Even if it is set, when the differential is in a forward-upward posture, the amount of oil supplied between the two oblique contact rolling bearings 5 and 6 is increased as compared with that in the normal posture.

  As a result, friction loss due to oil agitation by the oblique contact type rolling bearings 5 and 6 can be reduced in the normal posture, and the lubricity of the oblique contact type rolling bearings 5 and 6 can be improved in the forwardly raised posture. It becomes possible. Therefore, it becomes possible to stabilize the operation of the differential and improve the durability.

  Furthermore, since the flow rate adjusting mechanism 20 is configured to be incorporated as a separate member in the differential case 1, the differential itself can be made much simpler and cheaper than when the oil supply distribution is designed. It becomes possible.

  In addition, this invention is not limited only to the said embodiment, Various application and deformation | transformation can be considered.

  7 to 13 show another embodiment of the present invention.

  The flow rate adjusting mechanism 20 of this embodiment has a case 21 for receiving the oil splashed by the ring gear 2a, and the received oil is received in the case 21 on the differential front end side of the two oblique contact type rolling bearings 5 and 6. A first passage 22 for guiding to the front end side of the oblique contact type rolling bearing 5 to be arranged, and a first passage for guiding between the two oblique contact type rolling bearings 5 and 6 arranged adjacent to the first passage 22. The two passages 23 are provided in the same manner as in the above embodiment.

  In this embodiment, the configuration different from the above embodiment is the second passage 23 and will be described in detail below.

  In other words, the second passage 23 is a hole having a circular cross section penetrating in the longitudinal direction, and the received oil is guided between the two oblique contact rolling bearings 5 and 6 on the bottom surface side in the longitudinal direction. A flow path 24 is provided. The second passage 23 is provided with a valve body 28 that reduces the opening area of the flow path 24 when the differential is in a normal posture, and expands the opening area of the flow path 24 when the differential is in a front-up position.

  Specifically, the second passage 23 has a small inner diameter in a substantially half region on the front end side and a large diameter in a substantially half region on the rear end side. In addition, the code | symbol 23a is attached | subjected to the small diameter area | region, and the code | symbol 23b is each attached | subjected to the large diameter area | region.

  The valve body 28 is a cylindrical member, and is inserted into the large diameter region 23b of the second passage 23 so as to be slidable in the longitudinal direction. A retaining ring 30 for retaining the valve element 28 is attached to the opening side of the large diameter region 23b of the second passage 23. The retaining ring 30 is, for example, a C-shaped snap ring or the like, and is mounted in a snap fit state in a circumferential groove provided near the entrance side opening of the second passage 23.

  The majority of the flow path 24 is arranged in the large diameter area 23 b of the second passage 23, and only a part is set in the small diameter area 23 a of the second passage 23. Accordingly, when the valve body 28 slides to a position where it contacts the stepped portion 23c at the boundary between the small diameter area 23a and the large diameter area 23b in the second passage 23, the opening area of the flow path 24 is minimized, while the valve body 28 When the slider slides to a position where it comes into contact with the stopper ring 30, the opening area of the flow path 24 is maximized.

  Here, the operation in the embodiment will be described.

  For example, when the differential is in a normal posture as shown in FIG. 7, it flows into the two passages 22 and 23 in the case 21 of the flow rate adjusting mechanism 20 at a ratio of approximately half.

  Here, all of the oil that has flowed into the first passage 22 is discharged from the opening on the front end side and dropped to the front end side of the oblique contact type rolling bearing 5 on the front end side, and mainly the inner ring large collar portion of the oblique contact type rolling bearing 5. Is then lubricated and cooled, and then returned to the bottom side of the rear case 1b of the differential case 1 through a return passage (not shown) that is normally provided in the side wall portion of the differential case 1.

  On the other hand, the oil flowing into the second passage 23 is displaced in the second passage 23 by the pressure of the oil received in the case 21 to the differential front end side as shown in FIGS. The two passages 23 come into contact with the step portion 23c at the boundary between the small diameter region 23a and the large diameter region 23b, and the opening area of the flow path 24 is minimized.

  As a result, a part of the received oil flows into the flow path 24, but the rest is discharged from the front end side opening in the same manner as the first passage 22 to the front end side of the oblique contact type rolling bearing 5 on the front end side. It will be dropped.

  The oil that has flowed into the flow path 24 falls between the two oblique contact rolling bearings 5 and 6, and this oil is respectively pumped by the rotation of both the bearings 5 and 6. Is passed through the bearing toward the large end side to lubricate and cool each part. The oil that has passed through both the bearings 5 and 6 is returned to the bottom side of the rear case 1b of the differential case 1 through the return passage, and is also transmitted to the bottom side of the rear case 1b of the differential case 1 through the drive pinion gear shaft 4. Returned to

  In this way, when the differential is in a normal posture, the amount of oil supplied between the two oblique contact rolling bearings 5 and 6 is set to an appropriate amount without excess or deficiency.

  By the way, when the differential is in a forwardly raised posture as shown in FIG. 11, for example, the valve body 28 is displaced toward the side of increasing the opening area of the flow path 24 by its own weight as shown in FIGS. For example, when the inclination angle of the forward rising posture is equal to or greater than a predetermined angle, the valve element 28 is displaced to a position where it contacts the retaining ring 30 and the opening area of the flow path 24 is maximized.

  As a result, most of the oil that has flowed into the second passage 23 flows into the flow path 24 and does not pass to the front end side. Therefore, when the differential is in the front-up position, the two oblique contact-type rolling bearings 5, 6 are used. As a result, sufficient supply of oil to the gap is ensured, and the oblique contact type rolling bearings 5 and 6 are sufficiently lubricated and cooled.

  According to this embodiment, the same operation and effect as in the above embodiment can be obtained.

  In other words, the flow rate is limited so that a part of the oil received in the normal posture flows into the flow path 24, and a large amount of oil is allowed to flow into the flow path 24 when the forward posture is reached. In the normal posture, the oil supply between the two oblique contact rolling bearings 5 and 6 is not excessive, and in the forward raising posture, the oil supply between the two oblique contact rolling bearings 5 and 6 is sufficient. Will be secured.

  In addition, since the flow rate adjusting mechanism 20 is incorporated in the differential case 1 as a separate member, the differential itself can be made much simpler and cheaper than when the oil supply distribution is designed. It becomes possible.

  In particular, in this embodiment, since the valve body 28 is configured to be automatically displaced in accordance with the differential posture, the configuration of the valve body 28 is compared with a case where the operation of the valve body 28 is electrically controlled. Simplification and reduction of equipment costs are possible, which is preferable.

It is a longitudinal cross-sectional view which shows one Embodiment of the differential which concerns on this invention. It is a figure for demonstrating the flow of the oil in the normal attitude | position of FIG. 1, and has expanded and shown the flow volume adjustment mechanism in FIG. It is the figure which made the flow volume adjustment mechanism of FIG. 2 the cross section in the horizontal direction. It is a figure which shows the state which the differential of FIG. FIG. 4 is a diagram for explaining the flow of oil in the forwardly rising posture of FIG. 3, and shows an enlarged flow rate adjusting mechanism in FIG. 4. It is the figure which made the flow volume adjustment mechanism of FIG. 5 the cross section in the horizontal direction. It is a longitudinal cross-sectional view which shows other embodiment of the differential which concerns on this invention. It is a figure for demonstrating the flow of the oil in the normal attitude | position of FIG. 7, and has expanded and shown the flow volume adjustment mechanism in FIG. It is the figure which made the flow volume adjustment mechanism of FIG. 8 the cross section in the horizontal direction. FIG. 10 is a cross-sectional view taken along line (10)-(10) in FIG. 9. It is a figure which shows the state which the differential of FIG. It is a figure for demonstrating the flow of the oil in the front rising attitude | position of FIG. 11, and has expanded and shown the flow volume adjustment mechanism in FIG. It is the figure which made the flow volume adjustment mechanism of FIG. 12 the cross section in the horizontal direction.

Explanation of symbols

1 Differential case
2 Differential transmission mechanism
2a Ring gear
3 Drive pinion gear
4 Drive Pinion Gear Shaft 5, 6 Diagonal Rolling Bearing 20 Flow Control Mechanism 21 Case 23 Second Passage 24 Channel 25 Oil Pool 26 Standing Wall

Claims (4)

The oil in the differential case jumps upward as the ring gear rotates, and is guided to the two oblique contact rolling bearings for supporting the drive pinion gear shaft with respect to the differential case. The oil returned to the side is a differential that uses a splash lubrication system,
A differential comprising a flow rate adjusting mechanism that increases an oil supply amount between the two oblique contact type rolling bearings when in a forwardly raised posture as compared with a normal posture. The differential according to claim 1,
The flow rate adjusting mechanism has a case for receiving oil splashed by a ring gear;
In this case, there are a flow path for guiding the received oil between the two oblique contact type rolling bearings, and an oil reservoir portion that is provided on the back side in the oil receiving direction from the flow path to store the oil. And a restricting member that restricts the amount of oil flowing into the flow path in a normal posture, and a recovery member that collects and flows oil in the oil reservoir into the flow channel in a forwardly raised posture. Differential. The differential according to claim 1,
The flow rate adjusting mechanism has a case for receiving oil splashed by a ring gear;
In this case, there are a flow path for guiding the received oil between the two oblique contact rolling bearings, and an opening area of the flow path in the forward rising position while reducing the opening area of the flow path in the normal posture. A differential having a valve body that expands an area. The differential of claim 3,
The valve body is installed in the case so as to be reciprocally displaceable in the oil supply direction, and is displaced to a position where the opening area of the flow path is minimized by the oil pressure received in the case in a normal posture. On the other hand, the differential is characterized in that it is displaced to a position where the opening area of the flow path is maximized by its own weight in the forward rising posture.

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