JP2022048010A - Pump and gear device equipped with pump - Google Patents

Abstract

To improve a flow of a fluid.SOLUTION: A pump includes a pair of a first gear 20 and a second gear 30 engaged with each other, a housing 11 that is formed with storage chambers 16 and 17 rotatably storing the first gear 20 and the second gear 30, a suction port 40 that sucks a fluid into the storage chambers 16 and 17, a discharge port 41 that discharges the fluid from the storage chambers 16 and 17, an opening portion 42 that is provided in the housing 11, communicates the outside of the housing 11 and the storage chambers 16 and 17 in a gear diametrical direction, and exposes a part of gear teeth 31 of the second gear 30 outside the housing 11 to engage with a third gear 65, and a plate member 18 that extends from an end portion facing the opening portion 42 of the housing 11, and covers an engaging portion X between the second gear 30 and the third gear 65 from one end side in a gear rotation axis direction.SELECTED DRAWING: Figure 3

Description

The present disclosure relates to a pump and a gear device comprising the pump.

Generally, a pump for supplying lubricating oil to a meshing element or a sliding element is provided in a case of a gear device such as a transmission. As an example of this type of pump, for example, Patent Documents 1 and 2 disclose an externally meshed gear pump that pumps and circulates lubricating oil in a transmission case.

Japanese Unexamined Patent Publication No. 2010-2472729 Japanese Unexamined Patent Publication No. 2020-002879

According to the structure described in Patent Document 1, one of the pair of meshing gears housed in the housing of the gear pump is fixed to the main shaft of the transmission, so that the driving force can be directly applied from the main shaft. I'm taking it out. Therefore, it is necessary to expand the main shaft in the axial direction by the width of the meshing gear in the gear pump, and it can be said that there is room for improvement in the miniaturization of the entire device.

On the other hand, in the structure described in Patent Document 2, the housing of the gear pump is provided with an opening for partially exposing the gear teeth of one of the meshing gears, and the drive gear is meshed with the gear teeth exposed from the opening. This makes it possible to reduce the size of the entire device. However, a part (for example, about half) of the lubricating oil pumped by the pump is discharged from the opening, and it can be said that there is room for improvement in the flow of the lubricating oil.

The technique of the present disclosure has been made in view of the above circumstances, and an object thereof is to improve the lubrication efficiency by improving the flow of the lubricating oil.

The pumps of the present disclosure include a pair of first and second gears that mesh with each other, a housing in which a housing chamber for rotatably accommodating the first gear and the second gear is formed, and a fluid in the accommodation chamber. A suction port for sucking, a discharge port for discharging a fluid from the storage chamber, and the housing are provided, and the outside of the housing and the storage chamber are communicated with each other in the gear radial direction, and the gear of the second gear is used. An opening in which a part of the teeth is exposed to the outside of the housing to engage with the third gear, and an opening extending from the end of the housing facing the opening, and an engaging portion between the second gear and the third gear. It is characterized by including a plate member that covers the fluid from one end side in the gear rotation axis direction.

Further, the third gear is supported by the shaft, and the plate member extends toward the outer peripheral surface of the shaft, and the tip surface facing the outer peripheral surface is curved along the outer peripheral surface in an arcuate shape. It is preferably formed in.

Further, a fluid collecting portion capable of collecting the fluid is provided inside the shaft, and the outer peripheral surface of the outer peripheral surface of the shaft opposite to the plate member with respect to the third gear. It is preferable that the surface is opened with a fluid intake flow path extending in the shaft in the radial direction and communicating with the fluid collecting portion.

Further, the third gear is formed to have a shorter tooth width than the second gear, and the side surface of the plate member is formed in a stepped shape along the side surface shapes of the second gear and the third gear. Is preferable.

The gear device of the present disclosure is a gear device including the pump, the fluid is a lubricating oil supplied to a lubricating element of the gear device, and the gear device includes a gear case filled with the lubricating oil. The housing is characterized in that one side is formed in an open bottomed tubular shape, and the open side is closed by a side wall of the gear case.

Further, the gear case is a transmission case, and the reverse main gear provided on the main shaft, the reverse counter gear provided on the counter shaft, the reverse main gear and the reverse counter are contained in the transmission case. An idle gear that meshes with the gear is arranged, and it is preferable that the third gear is the idle gear or a gear that can rotate integrally with the idle gear.

According to the technique of the present disclosure, it is possible to improve the lubrication efficiency by improving the flow of the lubricating oil.

It is a schematic sectional drawing which shows the pump which concerns on this embodiment, and the gear device provided with a pump. (A) is a schematic cross-sectional view showing the pump according to the present embodiment cut out in the gear radial direction, and (B) is a schematic view showing the pump according to the present embodiment cut out in the gear rotation axis direction. It is a cross-sectional view. It is a schematic sectional drawing explaining the baffle plate which concerns on this embodiment. It is a schematic diagram which looked at the baffle plate which concerns on this embodiment from the direction of a gear rotation axis.

Hereinafter, a pump according to the present embodiment and a gear device including the pump will be described with reference to the accompanying drawings. The same parts are designated by the same reference numerals, and their names and functions are also the same. Therefore, detailed explanations about them will not be repeated.

[overall structure]
FIG. 1 is a schematic cross-sectional view showing a pump 10 according to the present embodiment and a gear device 50 including the pump 10.

As shown in FIG. 1, the gear device 50 is, for example, an output reduction type transmission in which a reduction gear train 75 is arranged on the output side. Lubricating oil is sealed in the transmission case 51 (an example of a gear case) of the transmission 50. Further, in the transmission case 51, an input shaft 52, an output shaft 53, and a counter shaft 54 rotatably supported via bearings (not shown) are arranged.

The input shaft 52 and the output shaft 53 are arranged coaxially. The counter shaft 54 is arranged parallel to the input shaft 52 and the counter shaft 53. Of these shafts 52 to 54, at least the input shaft 52 is provided with an axial oil passage 55 for circulating lubricating oil and a plurality of radial oil passages 56 to 58.

The input shaft 52 is provided with a reverse main gear 60 and a plurality of forward stage main gears 70 in order from the input side. The counter shaft 54 is provided with a reverse counter gear 61 and a plurality of forward stage counter gears 71 in this order from the input side. On the output end side of the counter shaft 54 and the output shaft 53, a pair of gears 76, 77 that are constantly meshed with each other to form a reduction gear train 75 are provided on the shafts 53, 54 so as to be integrally rotatable.

The forward stage main gear 70 and the forward stage counter gear 71 are always meshed with each other. The forward stage main gear 70 is provided on the input shaft 52 so as to be relatively rotatable. The forward stage counter gear 71 is provided so as to be rotatable integrally with the counter shaft 54. The forward stage main gear 70 is configured to be selectively coupled to the input shaft 52 by the synchronization device 90.

The synchronization device 90 has outer peripheral teeth and is integrally rotatable with the hub 91 provided on the input shaft 52 so as to be integrally rotatable, the sleeve 92 having inner peripheral teeth that mesh with the outer peripheral teeth of the hub 91, and the main gear 70. It includes a dog gear 93 provided and a synchronizer ring 94 provided between the hub 91 and the dog gear 93.

In the synchronization device 90, when the synchronizer ring 94 is pressed due to the shift movement of the sleeve 92, a synchronous load is generated between the synchronizer ring 94 and the dog gear 93. When the sleeve 92 and the dog gear 93 are rotationally synchronized by a synchronous load, the sleeve 92 further shifts and meshes with the dog gear 93, so that the main gear 70 is coupled to the input shaft 52. Since the coupling device 98 for reverse is also configured in substantially the same manner as the synchronization device 90, detailed description thereof will be omitted.

The reverse main gear 60 is provided so as to be integrally rotatable with the input shaft 52. The reverse counter gear 61 is provided on the counter shaft 54 so as to be relatively rotatable, and is configured to be selectively coupled to the counter shaft 54 by the coupling device 98. The idle gear 62 (an example of the third gear of the present disclosure) is rotatably supported by an idle shaft 63 (an example of the shaft of the present disclosure) attached to the transmission case 51 via, for example, a needle bearing 64. .. The idle gear 62 always meshes with the reverse main gear 60 and the reverse counter gear 61.

The pump 10 is a so-called circumscribed gear pump, and is attached to the inner wall surface of the side wall 51A of the transmission case 51 which is separated and opposed to the reverse main gear 60 and the idle gear 62.

Specifically, the pump 10 includes a housing 11 and a pair of driven gears 20 and 30 (an example of the first gear and the second gear of the present disclosure) housed in the housing 11. Further, the side wall 51A is provided with a suction port 40, and the housing 11 is provided with a discharge port 41.

The suction port 40 is connected to the bottom of the transmission case 51 via a first oil passage 80 arranged on the outside of the transmission case 51 (for example, on the clutch housing side). The first oil passage 80 is formed of an oil passage, a hose member, or the like formed in the transmission case 51. The discharge port 41 is connected to the axial oil passage 55 via the second oil passage 81 and the radial oil passage 56. The second oil passage 81 is formed of a piping member or the like that connects the discharge port 41 and the radial oil passage 56.

In the present embodiment, the pump 10 is driven by a drive gear 65 (an example of the third gear of the present disclosure) that can rotate integrally with the idle gear 62. Specifically, the pump 10 is driven by power transmitted from a drive source (not shown) via an input shaft 52, a reverse main gear 60, and an idle gear 62. When the pump 10 is driven, the lubricating oil stored in the bottom of the transmission case 51 is pumped up through the first oil passage 80, and from the second oil passage 81 to the radial oil passage 56 and further to the axial oil passage. By being supplied to 55, lubricating oil is supplied to each lubricating element such as the synchronization device 90 and the bearing in the transmission case 51. Hereinafter, the detailed configuration of the pump 10 according to the present embodiment will be described.

[pump]
FIG. 2A is a schematic cross-sectional view showing the pump 10 according to the present embodiment cut out in the gear radial direction, and FIG. 2B is a schematic cross-sectional view showing the pump 10 according to the present embodiment in the gear rotation axis direction. It is a schematic cross-sectional view shown by notching in.

As shown in FIG. 2, the pump 10 includes a housing 11, a first driven gear 20, and a second driven gear 30. The gear tooth 21 of the first driven gear 20 always meshes with the gear tooth 31 of the second driven gear 30. The number of teeth of each of these gears 20 and 30 is preferably set to the same number.

The housing 11 is formed in a bottomed cylindrical shape with one side open. Specifically, the housing 11 has a housing side wall portion 12 (see FIG. 2B) that faces the side wall 51A of the transmission case 51 and a housing peripheral wall portion 13 that faces the tooth tips of the gear teeth 21 and 31. And have.

A flange portion 15 is provided on the peripheral edge of the housing peripheral wall portion 13. The housing 11 is attached to the transmission case 51 by fixing the flange portion 15 to the side wall 51A of the transmission case 51 with bolts (not shown) or the like. That is, the side wall 51A of the transmission case 51 functions as a lid member that closes the open side of the housing 11. The lid member that closes the open side of the housing 11 may be formed of a member that is separate from the side wall 51A.

Inside the housing 11, the first gear accommodating chamber 16 is defined by a surface of the side wall 51A facing the housing side wall portion 12, a surface of the housing side wall portion 12 facing the side wall 51A, and an inner peripheral surface of the housing peripheral wall portion 13. Further, the second gear accommodating chamber 17 is formed as a delimitation.

The first gear accommodating chamber 16 is formed in a cylindrical hole shape having substantially the same diameter as the outer diameter of the first driven gear 20, and the first driven gear 20 is rotatably accommodated therein. The second gear accommodating chamber 17 is formed in a cylindrical hole shape having substantially the same diameter as the outer diameter of the second driven gear 30, and the second driven gear 30 is rotatably accommodated therein. The first gear accommodating chamber 16 and the second gear accommodating chamber 17 communicate with each other at the meshing portions of the gear teeth 21 and 31.

The first driven gear 20 is provided on the first support shaft 22. The first support shaft 22 is rotatably supported on the side wall portion 12 of the housing on one end side and on the side wall 51A of the transmission case 51 on the other end side.

The second driven gear 30 is provided on the second support shaft 32. The second support shaft 32 is rotatably supported on the side wall portion 12 of the housing on one end side and on the side wall 51A of the transmission case 51 on the other end side.

The side wall 51A is provided with a suction port 40 connected to the first oil passage 80. Further, the side wall portion 12 of the housing is provided with a discharge port 41 connected to the second oil passage 81.

In the present embodiment, the second gear accommodating chamber 17 and the outside (the space inside the transmission case 51) are communicated with each other in the gear radial direction at a portion of the housing peripheral wall portion 13 facing the tooth tip of the drive gear 65. An opening 42 that exposes at least one or more of the gear teeth 31 of the second driven gear 30 is notched. The gear teeth 66 of the drive gear 65 mesh with the gear teeth 31 of the second driven gear 30 exposed from the opening 42.

The drive gear 65 is provided so as to be integrally rotatable with the gear hub 62A of the idle gear 62. Specifically, as shown in FIG. 2B, the gear hub 62A is formed in a substantially cylindrical shape, and on the inner peripheral side thereof, a cylindrical boss portion extending toward the side wall 51A of the transmission case 51 62B is formed. The inner peripheral surface of the drive gear 65 is integrally rotatably fixed to the outer peripheral surface of the boss portion 62B by spline fitting or the like.

The drive gear 65 and the idle gear 62 are separated from each other in the gear rotation axis direction and face each other, and a predetermined space S1 is provided between them. Further, the drive gear 65 and the side wall 51A are separated from each other in the gear rotation axis direction and face each other, and a predetermined space S2 is provided between them. A predetermined gap is secured between the boss portion 62B of the idle gear 62 and the side wall 51A of the transmission case 51, and a part of the outer periphery of the idle shaft 63 is exposed to the space S2.

The idle shaft 63 is formed in a hollow shaft shape, and the internal space S3 (an example of the fluid collecting portion of the present disclosure) functions as an oil catch tank capable of temporarily collecting lubricating oil.

Specifically, in the portion of the idle shaft 63 exposed to the space S2, the oil intake flow path 63A (in the present disclosure) that penetrates the outer peripheral portion of the idle shaft 63 in the radial direction and communicates the space S2 and the internal space S3. An example of a fluid intake flow path) is provided. Further, at a portion of the idle shaft 63 that supports the needle bearing 64, an oil supply flow path 63B that penetrates the outer peripheral portion of the idle shaft 63 in the radial direction and communicates the internal space S3 and the needle bearing 64 is provided. .. That is, the lubricating oil collected from the space S2 via the oil intake flow path 63A into the internal space S3 is appropriately supplied to the needle bearing 64 and other lubricating elements via the oil supply flow path 63B and the like. It has become.

In the present embodiment, the number of teeth of the gear teeth 66 of the drive gear 65 is preferably set to be larger than the number of teeth of the gear teeth 31 of the second driven gear 30. That is, when the drive gear 65 is integrally rotated with the idle gear 62, the second driven gear 30 is rotated at an increased speed by the drive gear 65, and the first driven gear 20 is also configured to be rotated at an increased speed accordingly.

As shown by the arrow R in FIG. 2A, when the driven gears 20 and 30 rotate, they are taken in from the suction port 40 and taken in from the suction port 40 as shown by the broken line A in the figure, and the first driven gear 20 and the first pump. The lubricating oil flowing through the gap with the accommodation chamber 16 is pumped from the discharge port 41 toward the second oil passage 81 (see FIG. 2B). On the other hand, as shown by the broken line B in FIG. 2A, the lubricating oil taken in from the suction port 40 and flowing through the gap between the second driven gear 30 and the second pump accommodating chamber 17 is the second from the opening 42. It flows into the meshing portion X between the driven gear 30 and the drive gear 65, and is pushed out in the gear rotation axis direction by the meshing of each of the gears 30 and 65.

As shown in FIG. 2B, the end portion of the side wall portion 12 of the housing extends from the end portion toward the boss portion 62B (or the idle shaft 63) of the idle gear 62, and the gears 30 and 65 mesh with each other. A baffle plate 18 (plate member of the present disclosure) formed so as to cover the portion X from one end side (space S1 side) in the gear rotation axis direction is provided. The baffle plate 18 functions as a guide plate that blocks the lubricating oil pushed out from the meshing portion X to the space S1 side and positively guides the lubricating oil to the space S2 side. Hereinafter, the detailed configuration of the baffle plate 18 will be described.

[Baffle plate]
FIG. 3 is a schematic cross-sectional view illustrating the baffle plate 18 according to the present embodiment, and FIG. 4 is a schematic view of the baffle plate 18 according to the present embodiment as viewed from the gear rotation axis direction.

As shown in FIG. 3, the baffle plate 18 projects from the end of the housing side wall portion 12 facing the opening 42 toward the outer peripheral surface of the boss portion 62B of the idle gear 62, and is integrated with or separate from the housing side wall portion 12. It is provided on the body. When the baffle plate 18 is separated from the side wall portion 12 of the housing, the baffle plate 18 may be fixed to a non-rotating member such as a transmission case 51.

The side surfaces of the baffle plate 18 facing the gears 30 and 65 are formed in a stepped shape along the side surface shapes of the gears 30 and 65. More specifically, the tooth width of the drive gear 65 is formed shorter than the tooth width of the driven gear 30, so that the side surface of the drive gear 65 is offset from the side surface of the driven gear 30 in a direction away from the baffle plate 18. It has become. The baffle plate 18 of the present embodiment has a stepped shape in which the tip portion 18B protrudes toward the drive gear 65 from the base end portion 18A so as to narrow the gap (opposing space) with the gears 30 and 65. It is configured.

As a result, the flow of the lubricating oil extruded from the meshing portions X of the gears 30 and 65 toward the space S1 side is effectively blocked by the side surface of the baffle plate 18. The amount of protrusion of the tip 18B is determined by the peripheral configuration such as the difference in tooth width between the drive gear 65 and the driven gear 30 within the range where the protruding end surface of the tip 18B does not interfere with the side surface of the drive gear 65. It may be set appropriately according to specific dimensions.

As shown in FIG. 4, the baffle plate 18 is formed to have a length substantially equal to the opening width of the opening 42 that exposes the driven gear 30, and the meshing portion X of each of the gears 30 and 65 is oriented in the gear rotation axis direction. It is provided so as to surely cover from one end side of the. Further, the tip surface of the baffle plate 18 facing the outer peripheral surface of the boss portion 62B is formed in an arcuate shape curved along the outer peripheral surface of the boss portion 62B. That is, by making the tip surface of the baffle plate 18 into an arcuate surface, the gap (opposing space) between the boss portion 62B and the outer peripheral surface is effectively narrowed.

As a result, it is possible to effectively suppress the leakage of the lubricating oil that is pushed out from the meshing portion X of each of the gears 30 and 65 and flows into the gap between the drive gear 65 and the baffle plate 18 to the space S1 side. The clearance between the tip surface of the baffle plate 18 and the outer peripheral surface of the boss portion 62B may be appropriately set as long as the baffle plate 18 and the boss portion 62B do not interfere with each other.

In the illustrated example, the tip surface of the baffle plate 18 has been described as facing the outer peripheral surface of the boss portion 62B, but if the idle gear 62 has a structure that does not include the boss portion 62B, the tip surface of the baffle plate 18 is provided. May directly face the outer peripheral surface of the idle shaft 63. In this case, the tip surface of the baffle plate 18 may be formed in an arcuate shape along the outer peripheral surface of the idle shaft 63.

According to the pump 10 of the present embodiment described in detail above, the end portion of the side wall portion 12 of the housing facing the opening 42 extends from the end portion toward the outer peripheral surface of the boss portion 62B of the idle gear 62, and each gear. By providing the baffle plate 18 that covers the meshing portions X of 30 and 65 from the space S1 side in the gear rotation axis direction, the flow of lubricating oil pushed out from the meshing portion X indicated by the arrow Y1 toward the space S1 side in FIG. It is configured to block the.

As a result, the flow rate of the lubricating oil from the meshing portion X indicated by the arrow Y2 in FIG. 3 toward the space S2 increases, and as shown by the arrow Y3 in FIG. 3, the idle shaft 63 functions as an oil catch tank. The amount of lubricating oil supplied to the internal space S3 can be effectively secured, and the lubrication efficiency of the pump 10 can be reliably improved.

Further, the housing 11 of the pump 10 is provided with an opening 42 for communicating the second gear accommodating chamber 17 and the outside in the gear radial direction, and the drive gear 65 is meshed with the second driven gear 30 exposed from the opening 42. As a result, the driving force is taken into the housing 11 from the gear radial direction. As a result, the axial length of the transmission 50 can be effectively shortened as compared with the conventional structure in which the driving force is taken in from the rotation axis direction, and the transmission 50 can be downsized.

Further, by taking in the driving force from the gear radial direction, connecting parts such as a shaft for transmitting the driving force from the rotation axis direction to the gear (20 or 30) in the housing 11 become unnecessary, and the number of parts is effectively reduced. Can be reduced.

Further, by engaging the second driven gear 30 of the pump 10 with the drive gear 65 provided integrally with the idle gear 62 for reverse, the vibration accompanying the rotation of the idle gear 62 causes the pressing force of the second driven gear 30. It becomes possible to effectively reduce the noise and the like of the reverse gear trains 60 to 62.

[others]
It should be noted that the present disclosure is not limited to the above-described embodiment, and can be appropriately modified and implemented without departing from the spirit of the present disclosure.

For example, the drive gear 65 has been described as meshing with the second driven gear 30, but the first driven gear 20 is exposed from the opening 42 according to the layout or the like, and the drive gear 65 meshes with the first driven gear 20. It may be configured to cause.

Further, the gear that transmits the driving force to the pump 10 is not limited to the drive gear 65, and the idle gear 62 is meshed with the second driven gear 30 (or the first driven gear 20) and directly from the idle gear 62. It may be configured to take out the driving force.

Further, the second driven gear 30 (or the first driven gear 20) may be meshed with the main gear 60 fixed to the input shaft 52, or the second driven gear 30 (or the first driven gear 20) may be engaged. The driving force of the pump 10 may be taken out by engaging the counter shaft 54 with the counter gear 71 that can rotate relative to the counter shaft 54.

Further, the transmission 50 is not limited to the output reduction type, and may be an input reduction type. In the case of the input reduction type, the pump 10 may be arranged on the inner wall on the output side in the transmission case 51 so as to take out the driving force from the adjacent gear on the output side.

Further, although the housing 11 of the pump 10 has been described as being closed by the side wall 51A of the transmission case 51, the housing 11 may be configured to separately include a lid member. When the lid member is provided, the pump 10 can be arranged at an arbitrary place in the transmission case 51.

Further, the application of this embodiment is not limited to the transmission 50, and can be widely applied to other gear devices including a gear case for containing lubricating oil, such as a differential gear device and a transfer device. Further, the fluid pumped by the pump 10 is not limited to the lubricating oil, and may be another liquid such as cooling water.

10 Pump 11 Housing 12 Housing side wall 13 Housing peripheral wall 16 1st gear accommodation chamber (accommodation chamber)
17 2nd gear accommodation room (accommodation room)
18 Baffle plate (plate member)
18A Base end 18B Tip 20 First driven gear (first gear)
21 Gear tooth 30 2nd driven gear (2nd gear)
31 Gear teeth 40 Suction port 41 Discharge port 42 Opening 50 Transmission (gear device)
51 Transmission case (gear case)
52 Input shaft 54 Counter shaft 60 Reverse main gear 61 Reverse counter gear 62 Idle gear (3rd gear)
63 Idle shaft (shaft)
63A Oil intake channel (fluid intake channel)
S3 internal space (fluid collector)
65 Drive gear (3rd gear)

Claims (6)

A pair of first and second gears that mesh with each other,
A housing in which a storage chamber for rotatably accommodating the first gear and the second gear is formed, and
A suction port for sucking fluid into the storage chamber,
A discharge port for discharging fluid from the storage chamber and
In addition to being provided in the housing, the outside of the housing and the accommodation chamber are communicated with each other in the gear radial direction, and a part of the gear teeth of the second gear is exposed to the outside of the housing and meshes with the third gear. With an opening to let
A pump comprising: extending from an end of the housing facing the opening and a plate member covering the meshing portion of the second gear and the third gear from one end side in the gear rotation axis direction. The third gear is supported by the shaft and is supported by the shaft.
The pump according to claim 1, wherein the plate member extends toward the outer peripheral surface of the shaft, and the tip surface facing the outer peripheral surface is formed in an arcuate shape curved along the outer peripheral surface. A fluid collecting portion capable of collecting the fluid is provided inside the shaft.
On the outer peripheral surface of the outer peripheral surface of the shaft, which is opposite to the plate member with respect to the third gear, a fluid intake flow path extending in the shaft in the radial direction and communicating with the fluid collecting portion is provided. The pump according to claim 2, which opens. The third gear is formed to have a shorter tooth width than the second gear.
The pump according to any one of claims 1 to 3, wherein the side surface of the plate member is formed in a stepped shape along the side surface shapes of the second gear and the third gear. A gear device including the pump according to any one of claims 1 to 4.
The fluid is a lubricating oil supplied to the lubricating element of the gear device.
The gear device includes a gear case filled with the lubricating oil.
The housing is a gear device characterized in that one side is formed in an open bottomed cylindrical shape and the open side is closed by a side wall of the gear case. The gear case is a transmission case.
In the transmission case, a reverse main gear provided on the main shaft, a reverse counter gear provided on the counter shaft, and an idle gear that meshes with the reverse main gear and the reverse counter gear are arranged. Cage,
The gear device according to claim 5, wherein the third gear is an idle gear or a gear that can rotate integrally with the idle gear.

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