JP2016125590A - Gear device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gear device comprising an input side gear, an output side gear, and an idling helical gear disposed therebetween and engaged to the input side gear and the output side gear, which can reduce thrust generated in an idling helical gear and caused by discharge of oil lubricating between tooth surfaces.MEANS FOR SOLVING THE PROBLEM: On a travel direction of engagement between the tooth surface of a helical gear and the tooth surfaces of an input side gear and an output side gear, disposed is an oil receiving member for receiving oil lubricating between the tooth surfaces.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a gear device, and more particularly to a thrust generated when lubricating oil is discharged in a free-running helical gear that is disposed between an input-side gear and an output-side gear and transmits rotation.

  In general, helical gears are often used for gear devices that transmit power. This helical gear has a twist in the tooth trace. The twist of the tooth traces improves the strength and quietness when meshing. On the other hand, due to the twisting of the tooth traces, oil that lubricates between the tooth surfaces is discharged along the meshing direction during meshing, and thus thrust is generated in the direction opposite to the oil discharging direction.

  In particular, in a free-running helical gear disposed between an input-side gear and an output-side gear and transmitting rotational power, two gears of a helical gear, an input-side gear and an output-side gear, Mesh. For this reason, the thrust due to the discharge of the oil that lubricates between the tooth surfaces increases, and the axial rotation to the washer, thrust bearing, etc., which is disposed on the shaft portion of the idle helical gear and receives this thrust, etc. The load increases. There is a problem that the life of the washer and the thrust bearing is reduced due to the increase of the load in the axial direction.

  Patent Document 1 discloses a lubrication structure using lubricating oil discharged by meshing in a reduction gear using a helical gear. However, the idle rotation does not consider the thrust generated by the oil discharged when the helical gear meshes with the input side and output side gears. For this reason, the axial load of the washer or the like that receives the above-described thrust increases, and the increase in the axial load causes a problem that the washer or the like is worn and the life is shortened.

Japanese Utility Model Publication No.2-113055

  The present invention has been created in view of the above problems, and in a free-running helical gear disposed between an input-side gear and an output-side gear for transmitting rotational power, lubricating oil is discharged when meshing. An object of the present invention is to provide a gear device capable of reducing the thrust generated by the above.

The present invention provides a gear device. This gear device
A gear device comprising an input side gear and an output side gear that are spaced apart from each other in a radial direction, and a free-running helical gear that is disposed between the input side gear and the output side gear, and transmits rotation. An oil receiving member that receives oil that lubricates between the tooth surfaces is provided in the advancing direction of engagement between the tooth surfaces of the output side gear and the helical gear.
The oil receiving member is fixed to the helical gear so as to be substantially perpendicular to the rotational axis of the helical gear.

  According to the hydraulic control device for an automatic transmission of the present invention, oil that receives oil that lubricates between tooth surfaces in a traveling direction of meshing between a helical gear, an input side gear, and an output side gear. A receiving member is disposed. The oil receiving member is fixed to the helical gear approximately perpendicularly to the rotating shaft of the helical gear, and the oil that is lubricated and discharged between the tooth surfaces is the oil receiving member. It is received by the receiving member. As a result, the oil that is discharged presses the oil receiving member, so that the thrust generated in the helical gear can be reduced. As a result, the load in the axial direction on the washer, the thrust bearing and the like described above is reduced, and it is possible to suppress a decrease in the life of the washer and the like.

BRIEF DESCRIPTION OF THE DRAWINGS It is the schematic which illustrates the cross section of the gear apparatus which concerns on one Embodiment of this invention, and the conventional gear apparatus, Comprising: (a) shows the general | schematic cross section of the gear apparatus which concerns on one Embodiment of this invention, (b) These are figures which show the general | schematic cross section of the conventional gear apparatus. It is explanatory drawing of the gear apparatus which concerns on one Embodiment of this invention, Comprising: (a) illustrates meshing | engagement of a pair of helical gear, (b) is one implementation of this invention shown to Fig.1 (a). It is the schematic which looked at the gear apparatus which concerns on a form from the direction of arrow A, (c) is the schematic explaining the advancing direction etc. of the meshing of an input side gear, an idle helical gear, and an output side gear.

《Helical gear meshing》
First, the meshing of the helical gear will be described with reference to the drawings. 2A and 2B are explanatory views of a gear device according to an embodiment of the present invention, in which FIG. 2A illustrates the meshing of a pair of helical gears, and FIG. 2B illustrates the book shown in FIG. BRIEF DESCRIPTION OF THE DRAWINGS It is the schematic which looked at the gear apparatus which concerns on one Embodiment of the invention from the direction of arrow A, (c) demonstrates the advancing direction etc. of the meshing of an input side gear, a free-wheeling helical gear, and an output side gear. In FIGS. 1 to 2, numbers having the same last two digits indicate members of the same type.

  In the meshing of the pair of helical gears shown in FIG. 2A, the gear 10 is a driving gear (hereinafter also simply referred to as “driving gear”) and the gear 12 is a driven gear (hereinafter simply referred to as “ Also referred to as “driven gear”. The rotation shafts 10a and 12a of the drive gear 10 and the driven gear 12 are parallel to each other.

  Further, the rotation shafts 10a, 12a, and 14a of the input side gear 10, the free-running helical gear 12, and the output side gear 14, which will be described in detail later, are also parallel to each other as shown in FIGS. 2 (b) and 2 (c). It is arranged.

  FIG. 2C is a schematic diagram for explaining the meshing direction of the input side gear, the idle helical gear, and the output side gear, and the input side gear 10 is the drive gear 10 and the idle helical gear. When 12 is a driven gear 12, the driven gear 12 is rotated clockwise by the counterclockwise rotation of the drive gear 10. At this time, for example, it is assumed that the tooth surface 15a of the tooth 15 included in the driving gear 10 and the tooth surface 17a of the tooth 17 included in the driven gear 12 mesh with each other.

  Helical gears are roughly classified into right-handed and left-handed. In general, the right twist and the left twist are the right twist and the left twist that the teeth rise to the right with the rotation axis of the gear being vertical. In the gear shown in FIG. 2 (c), the drive gear 10 is a left-hand thread and the driven gear 12 is a right-hand thread. Further, the output side gear 14 described later in detail is a left-handed screw.

  In addition, it is known that the meshing of the helical gear is generally started from the root of the tooth surface on the acute angle side in the driving gear and from the tooth tip of the tooth surface on the obtuse angle side in the driven gear. This acute angle is an angle formed by the meshing tooth surface and the tooth side surface in the direction opposite to the direction of tooth twisting (left if left-handed twisting) with the gear being vertical, and is shown in FIG. 2 (c). C is shown. Further, the obtuse angle is an angle formed by the meshing tooth surface and the tooth side surface in the same direction as the direction of twisting of the tooth (right if twisting right) with the gear being vertical, as shown in FIG. Corner D is shown.

  As will be described in detail later, when the helical gear 12 is the driving gear 10 and the output gear 14 is the driven gear 12, the tooth surface of the tooth 17 of the driving gear 10 (idling helical gear 12). 17b and the tooth surface 19a of the tooth 19 of the driven gear 12 (output side gear 14) mesh with each other. In this case, similar to the above, the acute angle is an angle formed by the meshing tooth surface in the direction opposite to the direction of the tooth twist (right if it is a right twist) and the tooth side surface with the gear vertical. The angle E shown in c) is shown. Further, the obtuse angle is an angle formed by the meshing tooth surface and the tooth side surface in the same direction as the tooth twist direction (left if left twist) with the gear being vertical, as shown in FIG. Corner G is shown.

  As described above, the meshing between the tooth surface 15a of the drive gear 10 and the tooth surface 17a of the driven gear 12 proceeds from the left to the right in FIG. As described above, oil (not shown) that lubricates between the meshing tooth surfaces is discharged along the meshing direction. Therefore, in FIG. 2C, the drive gear 10 and the driven gear 12 are discharged rightward on the paper surface.

  As the oil is discharged, the reaction force (thrust) is generated in the gear. In particular, the idle helical gear 12 is the driven gear 12 that is driven by the driving gear 10 as described above, and is also the driving gear 10 that drives the output gear 14. Even when the idle helical gear 12 drives the output side gear 14, the oil is in the same manner as described above with the tooth surface 17 b of the tooth 17 of the idle helical gear 12 and the tooth 19 of the output side gear 14. Is discharged along the direction of meshing with the tooth surface 19a. That is, the paper is discharged in the right direction on the paper surface of FIG. For this reason, idle rotation increases the thrust generated in the helical gear 12 due to oil discharge.

  FIG. 1 is a schematic view illustrating a cross section of a gear device according to an embodiment of the invention and a conventional gear device, where (a) shows a schematic cross section of the gear device according to an embodiment of the present invention; (B) is a figure which shows the general | schematic cross section of the conventional gear apparatus. Also in the conventional gear device shown in FIG. 1B, the thrust Fs generated in the idle helical gear 12 by the discharge of oil is increased as described above.

  Therefore, an axial load is applied to a thrust load receiving member 24, for example, a washer or a thrust bearing, which is disposed on the shaft portion 22 of the helical gear 12 and receives this thrust (rightward in FIG. 1). (Load from left to right) increases. Thereby, wear of a washer etc. is accelerated | stimulated and the problem that a lifetime will fall arises.

  In the gear device according to the embodiment of the present invention shown in FIG. 1 (a), in order to solve the above-mentioned problem, the tooth surfaces are moved in the direction of meshing between the tooth surfaces, that is, in the oil discharging direction. An oil receiving member 30 is provided for receiving the oil to be lubricated. The oil receiving member 30 is fixed to the helical gear 12 so as to be substantially perpendicular to the rotating shaft 12 a of the helical gear 12.

  The oil receiving member 30 receives the oil discharged by the meshing of the free-running helical gear 12 with the drive side gear 10 and the output side gear 14. Thereby, the free-running helical gear 12 provided with the oil receiving member 30 generates a pressing force Fp from the left side to the right side of FIG.

  By this pressing force Fp, it is possible to reduce or cancel the thrust Fs generated in the helical gear 12 by idle rotation. As a result, the axial load applied to the thrust load receiving member 24 is reduced, and for example, promotion of washer wear is suppressed.

  Although FIG. 1A shows an example in which the oil receiving member 30 is fixed to the idle helical gear 12 via the shaft portion 22 of the idle helical gear 12, the oil receiving member is shown. 30 may be fixed to the helical gear 12 for free rotation. As an example, the oil receiving member 30 is formed to have a L-shaped cross section, and one end surface of the L-shaped oil receiving member 30 (not shown) is a side surface of the helical gear 12 (see FIG. 1 (a) may be welded or bolted to the right side of the drawing.

  FIG. 2B shows an example in which the rotation shafts 10a, 12a, and 14a of the input side gear 10, the free-running helical gear 12, and the output side gear 14 are arranged on a substantially straight line. The rotation axes may be parallel to each other, and the gears may be offset.

  As mentioned above, although embodiment and the concept about the gear apparatus of this invention were demonstrated, this invention is not limited to this, The range which does not deviate from the mind and teaching as described in a claim, a description, etc. It will be understood by those skilled in the art that other variations and improvements can be obtained.

DESCRIPTION OF SYMBOLS 10 Drive side gear 10a Rotation shaft of drive side gear 12 Driven side gear 12a Rotation shaft of driven side gear 14 Output side gear 14a Rotation shaft of output side gear 15 Tooth 15a which drive gear has Tooth tooth surface which drive gear has 17 Teeth 17a of the driven gear Teeth surface of the teeth of the driven gear 22 Shaft of the helical gear 24 Thrust load receiving member 30 Oil receiving member 50 Gear unit C, E Acute angle D, G of the driving gear Obtuse angle of gear Fs Thrust by oil discharge Fp Push by oil receiving

Claims (1)

In a gear device provided with an input side gear and an output side gear arranged to be spaced apart from each other in a radial direction, and an idle helical gear arranged between them to transmit rotation,
An oil receiving member that receives oil that lubricates between the tooth surfaces on the direction of meshing engagement between the tooth surfaces of the input side gear, the output side gear, and the helical gear. Have
The oil receiving member is fixed to the helical gear approximately perpendicularly to the rotational axis of the helical gear;
A gear device characterized by that.