Patent Application
20200284310
The present invention relates to a speed reducer, a rotary drive system, and a hydraulic shovel.
Priority is claimed on Japanese Patent Application No. 2018-035843, filed on Feb. 28, 2018, the content of which is incorporated herein by reference.
PTL 1 describes a rotary drive system in which an electric motor and a speed reducer decelerating the rotation of the electric motor are integrally provided. The speed reducer has multi-stage planetary gear mechanisms vertically disposed as a transmission unit. The planetary gear mechanisms are immersed in lubricating oil.
Patent Literature
[PTL 1] Japanese Unexamined Patent Application, First Publication No. 2016-172965
By the way, for a reduction in stirring loss during rotary drive, at least part of the transmission unit of the speed reducer may be, for example, exposed from the lubricating oil without being immersed in the lubricating oil. Even in such a case, it is required to smoothly supply lubricating oil to a sliding portion of the speed reducer that requires lubrication.
The present invention has been made in view of such problems, and an object of the present invention is to provide a speed reducer, a rotary drive system, and a hydraulic shovel allowing lubricating oil to be smoothly supplied to a sliding portion.
A speed reducer according to an aspect of the present invention includes: an output shaft provided below a rotary shaft that has an axis extending vertically and rotates around the axis, and provided to be rotatable around the axis; a transmission unit interconnecting a lower portion of the rotary shaft and the output shaft, decelerating a rotation of the rotary shaft, and transmitting a decelerated rotation of the rotary shaft to the output shaft; an annular member having a cylindrical shape surrounding the axis and rotating around the axis together with the transmission unit, the annular member including an oil sump having a recessed groove recessed in an inner peripheral surface of the annular member and a lubricating oil supply hole extending radially outward from the recessed groove and being opened; and a sliding portion provided on an outer side of the lubricating oil supply hole of the annular member in a radial direction of the axis.
According to the speed reducer configured as described above, the lubricating oil that has reached the inner peripheral surface of the annular member by being supplied from above is temporarily collected in the oil sump and then flows through the lubricating oil supply hole radially outward and in accordance with a centrifugal force. Then, the lubricating oil discharged from the lubricating oil supply hole is supplied to the sliding portion on the radially outer side of the lubricating oil supply hole. As a result, lubricity can be ensured for the sliding portion.
According to the speed reducer, the rotary drive system, and the hydraulic shovel of the above aspect, it is possible to smoothly supply lubricating oil to a sliding portion.
Hereinafter, a first embodiment of the present invention will be described in detail with reference to
As shown in
In addition, the front of the driver's seat in a cab 231 (described later) will be simply referred to as “front” and the rear of the driver's seat will be simply referred to as “rear”.
The undercarriage 210 includes a pair of left and right crawlers 211 and 211 and the hydraulic shovel 200 travels by the crawlers 211 and 211 being driven by a traveling hydraulic motor (not shown).
The swing circle 220 is a member interconnecting the undercarriage 210 and the upper swing body 230 and includes an outer race 221, an inner race 222, and a swing pinion 223. The outer race 221 is supported by the undercarriage 210 and has an annular shape about a swing axis L extending so as to match the vertical direction. The inner race 222 is an annular member coaxial with the outer race 221 and is disposed inside the outer race 221. The inner race 222 is supported so as to be rotatable relative to the outer race 221 around the swing axis L. The swing pinion 223 meshes with the internal teeth of the inner race 222 and the inner race 222 rotates relative to the outer race 221 by the swing pinion 223 rotating.
The upper swing body 230 is disposed so as to be capable of swinging around the swing axis L with respect to the undercarriage 210 by being supported by the inner race 222. The upper swing body 230 includes the cab 231, a work equipment 232, an engine 236 provided behind the cab 231 and the work equipment 232, a generator motor 237, a hydraulic pump 238, an inverter 239, a capacitor 240, and a rotary drive system 1.
The cab 231 is disposed on the front left side of the upper swing body 230 and is provided with the driver's seat for a worker. The work equipment 232 is provided so as to extend in front of the upper swing body 230 and includes a boom 233, an arm 234, and a bucket 235. The work equipment 232 performs various works such as excavation by the boom 233, the arm 234, and the bucket 235 being respectively driven by hydraulic cylinders (not shown).
The shafts of the engine 236 and the generator motor 237 are spline-coupled. The generator motor 237 generates electric power by being driven by the engine 236. The rotary shafts of the generator motor 237 and the hydraulic pump 238 are spline-coupled. The hydraulic pump 238 is driven by the engine 236. Each of the hydraulic cylinders and the traveling hydraulic motor described above are driven by the hydraulic pressure that is generated by the hydraulic pump 238 being driven.
The generator motor 237, the capacitor 240, and the rotary drive system 1 are electrically interconnected via the inverter 239. Another electric power storage device such as a lithium-ion battery may be used instead of the capacitor 240. The output of the rotary drive system 1 is transmitted to the swing pinion 223 meshing with the internal teeth of the inner race 222.
The rotary drive system 1 is disposed such that an axis O as a rotation center extends in the vertical direction. Here, “extends in the vertical direction” means that the direction of the axis O extends in a direction including an upward and downward directions, that is, includes a case where the axis O is inclined with respect to the direction that matches the vertical direction.
The hydraulic shovel 200 drives the rotary drive system 1 with the electric power generated by the generator motor 237 or the electric power from the capacitor 240. The drive force of the rotary drive system 1 is transmitted to the inner race 222 via the swing pinion 223. As a result, the upper swing body 230 swings by the inner race 222 rotating relative to the outer race 221.
When the swinging of the upper swing body 230 is decelerated, the rotary drive system 1 generates electric power as regenerative energy by functioning as a generator. This electric power is accumulated in the capacitor 240 via the inverter 239. The electric power accumulated in the capacitor 240 is supplied to the generator motor 237 when the engine 236 is accelerated. The generator motor 237 assists the output of the engine 236 by the generator motor 237 being driven by the electric power of the capacitor.
As shown in
As shown in
As shown in
As shown in
The upper casing 22 has a bottomed cylindrical shape having an upper cylindrical portion 23 having a cylindrical shape and extending in the vertical direction and an upper bottom portion 24 blocking the upper part of the upper cylindrical portion 23.
The lower casing 25 has a bottomed cylindrical shape having a lower cylindrical portion 26 having a cylindrical shape and extending in the vertical direction and a lower bottom portion 27 blocking the lower part of the lower cylindrical portion 26.
The lower bottom portion 27 serves as the bottom portion of the electric motor casing 21. Specifically, as shown in
As shown in
Here, as shown in
The inner peripheral-side communication hole 51 is formed so as to open in the first bottom surface 27b in the lower bottom portion 27 of the lower casing 25 and vertically penetrates the lower bottom portion 27. A plurality of the communication holes 50 arc formed at intervals in the circumferential direction.
As shown in
As shown in
The stator core 31 is configured by a plurality of electromagnetic steel plates being stacked in the vertical direction and has a cylindrical shape about the axis O. The stator core 31 includes a yoke and a plurality of teeth formed at intervals in the circumferential direction of the yoke so as to protrude from the inner peripheral surface of the yoke. The stator core is fixed to the electric motor casing 21.
A plurality of the coils 32 are provided so as to correspond to the respective teeth and wound around the respective teeth. As a result, the plurality of coils 32 are provided at intervals in the circumferential direction.
As shown in
The rotary shaft 40 is a rod-shaped member extending along the axis O. The rotary shaft 40 is disposed in the electric motor casing 21 so as to penetrate the inside of the stator 30 in the vertical direction. The upper end of the rotary shaft 40 protrudes above the upper bottom portion 24 in the upper casing 22. In addition, the upper end of the rotary shaft 40 may be accommodated in the electric motor casing 21.
The upper bottom portion 24 is provided with an upper seal 35 for sealing between the upper bottom portion 24 and the outer peripheral surface of the rotary shaft 40. As a result, liquid tightness is ensured at the upper end inside the electric motor casing 21.
The rotor core 42 has a cylindrical shape about the axis O and an inner peripheral surface 42a is externally fitted on the outer peripheral surface of the rotary shaft 40. The rotor core 42 is configured by a plurality of electromagnetic steel plates being stacked in the vertical direction. In the rotor core 42, a plurality of permanent magnets (not shown) are embedded at intervals in the circumferential direction.
The lower end plate 45 is fixed so as to be stacked on the rotor core 42 from below the rotor core 42.
The upper end plate 46 is fixed so as to be stacked on the rotor core 42 from above the rotor core 42.
The rotor 38 has an intra-rotor flow path F extending downward from the upper end of the rotary shaft 40 and passing between the rotary shaft 40 and the rotor core 42, through the lower end plate 45, through the rotor core 42, and through the upper end plate 46. The intra-rotor flow path F is open from the upper surface of the upper end plate 46 into the upper accommodation space RI.
The upper bottom portion 24 is provided with an upper bearing 36 having an annular shape about the axis O. The rotary shaft 40 is vertically inserted through the upper bearing 36 and the upper portion of the rotary shaft 40 is supported by the upper bearing 36 so as to be rotatable around the axis O.
As shown in
Next, the speed reducer 60 will be described with reference to
The speed reducer casing 61 has a cylindrical shape extending along the axis O and open upward and downward. The upper end of the speed reducer casing 61 abuts the electric motor casing 21 from below. The upper opening of the speed reducer casing 61 is blocked by the lower casing 25 of the electric motor casing 21.
The output shaft 70 has a rod shape extending along the axis O. The rotation of the output shaft 70 becomes the output of the rotary drive system 1. The upper portion of the output shaft 70 is disposed in the speed reducer casing 61 and the lower portion of the output shaft 70 protrudes downward from the speed reducer casing 61. An output shaft bearing 71 supporting the output shaft 70 so as to be rotatable around the axis O is provided below the inner peripheral surface of the speed reducer casing 61. The lower portion of the output shaft 70 that protrudes downward from the speed reducer casing 61 is connected to the swing pinion 223.
A lower seal 72 sealing the annular space between the inner peripheral surface of the speed reducer casing 61 and the outer peripheral surface of the output shaft 70 is provided further below the output shaft bearing 71 on the inner peripheral surface of the speed reducer casing 61. The space in the speed reducer casing 61 that is blocked from below by the lower seal 72 is a lower accommodation space R2. The lower portion of the rotary shaft 40 that protrudes downward from the electric motor casing 21 is positioned above the lower accommodation space R2. Lubricating oil is stored up to a predetermined height position in the lower accommodation space R2. In other words, the lower accommodation space R2 functions as a lubricating oil storage tank.
The transmission unit 80 is provided in the lower accommodation space R2 in the speed reducer casing 61. The transmission unit 80 has a role of reducing the rotational speed of the rotary shaft 40 and transmitting the reduced rotational speed to the output shaft 70.
The transmission unit 80 includes multi-stage planetary gear mechanisms sequentially reducing the rotational speed from the rotary shaft 40 to the output shaft 70. In the present embodiment, the three planetary gear mechanisms of a first stage planetary gear mechanism 90, a second stage planetary gear mechanism 100, and a third stage planetary gear mechanism 110 are provided as the plurality of planetary gear mechanisms.
The first stage planetary gear mechanism 90 is a planetary gear mechanism disposed at a first stage. The first stage planetary gear mechanism 90 includes a first stage transmission shaft (transmission shaft) 91, a first stage planetary gear (planetary gear) 92, and a first stage carrier (carrier) 93.
The first stage transmission shaft 91 is externally fitted from the lower end to the lower portion of the rotary shaft 40. The first stage transmission shaft 91 is rotatable around the axis O integrally with the rotary shaft 40.
More specifically, as shown in
The flange portion 91c is formed so as to overhang radially outward from the lower end of the cylindrical portion 91a. Sun gear teeth 91d as outer gear teeth are formed on the outer peripheral surface of the flange portion 91c.
The first stage planetary gear 92 has planetary gear teeth 92a on the outer peripheral surface. A plurality of the first stage planetary gears 92 are provided at intervals in the circumferential direction around the first stage transmission shaft 91 such that the planetary gear teeth 92a mesh with the sun gear teeth 91d of the first stage transmission shaft 91. The planetary gear teeth 92a of the first stage planetary gear 92 mesh with first stage inner gear teeth 62a formed on the inner peripheral surface of the speed reducer casing 61.
The first stage carrier 93 supports the first stage planetary gear 92 so as to be capable of rotating and revolving around the axis O. The first stage carrier 93 includes a carrier shaft 161 and a carrier main body 167.
The carrier shaft 161 is a vertically extending rod-shaped member and a plurality of the carrier shafts 161 arc provided so as to correspond to the respective first stage planetary gears 92. The carrier shaft 161 penetrates the center of each first stage planetary gear 92 in the vertical direction and rotatably supports the first stage planetary gear 92. The intermediate portion of the carrier shaft 161 in the vertical direction slides with the inner peripheral surface of the first stage planetary gear 92. In other words, the outer peripheral surface of the intermediate portion of the carrier shaft 161 and the inner peripheral surface of the first stage planetary gear 92 are a sliding surface (sliding portion) S1.
An intra-shaft flow path 162 is formed in the carrier shaft 161. The intra-shaft flow path 162 includes an upper radial flow path 163, an intermediate radial flow path 164, and an axial flow path 165.
The upper radial flow path 163 is a flow path extending along the radial direction of the axis O of the rotary shaft 40 in the upper portion of the carrier shaft 161. The upper radial flow path 163 passes through the carrier shaft 161 in the radial direction of the axis O. The opening in the upper radial flow path 163 that is on the inner side of the radial direction of the axis O of the rotary shaft 40 is a first opening portion 162a of the intra-shaft flow path 162.
The intermediate radial flow path 164 is a flow path extending along the radial direction of the axis O of the rotary shaft 40 in the middle portion of the carrier shaft 161. The upper radial flow path 163 passes through the carrier shaft 161 in the radial direction of the axis O. Both ends of the intermediate radial flow path 164 are open in the sliding surface S1 with respect to the first stage planetary gear 92. The opening in the intermediate radial flow path 164 that is on the radially outer side with respect to the axis O with respect to the axis O of the rotary shaft 40 is a second opening portion 162b of the intra-shaft flow path 162.
The axial flow path 165 is a flow path extending in the vertical direction at the center of the carrier shaft 161. The upper end of the axial flow path 165 communicates with the upper radial flow path 163. The lower end of the axial flow path 165 is blocked without opening on the lower surface of the carrier shaft 161. The intermediate portion of the axial flow path 165 in the vertical direction communicates with the intermediate radial flow path 164.
The carrier main body 167 has a disk shape about the axis O. The carrier main body 167 is disposed below each first stage planetary gear 92 so as to face the first stage planetary gear 92. The carrier main body 167 has a lower fitting hole 167a into which the outer peripheral surface of the lower portion of the carrier shaft 161 is fitted.
As shown in
The third stage planetary gear mechanism 110 includes a third stage transmission shaft 111, a third stage planetary gear 112, and a third stage carrier 113. The third stage transmission shaft 111 is provided below the second stage transmission shaft 101 so as to be rotatable around the axis O and is connected to the second stage carrier 103. The third stage planetary gear 112 meshes with sun gear teeth 111a formed on the third stage transmission shaft 111 and third stage inner gear teeth 62c formed on the inner peripheral surface of the speed reducer casing 61. The third stage planetary gear 112 is supported by the third stage carrier 113 so as to be capable of rotating and revolving around the axis O. The third stage carrier 113 is connected to the output shaft 70.
The transmission unit 80 transmits the rotation of the rotary shaft 40 to the output shaft 70 after decelerating the rotation of the rotary shaft 40 a plurality of times by means of the multi-stage planetary gear mechanisms.
As shown in
The annular plate portion 171 has a disk shape about the axis O. The annular plate portion 171 is disposed above each first stage planetary gear 92 so as to face the first stage planetary gear 92. The annular plate portion 171 has an upper fitting hole (fitting hole) 171a into which the outer peripheral surface of the upper portion of the carrier shaft 161 is fitted. By the carrier shaft 161 being fitted into the upper fitting hole 171a, the annular member 170 can be rotated around the axis O integrally with the first stage carrier 93.
The annular cylindrical portion 172 is a cylindrical member about the axis O and has a lower end integrally fixed to the annular plate portion 171. The annular cylindrical portion 172 has a shape in which the inner peripheral surface and the outer peripheral surface increase in diameter in stages upward.
The uppermost part of the outer peripheral surface of the annular cylindrical portion 172 is a disk support surface 172a forming a cylindrical surface about the axis O.
An upper oil sump 175 and a lower oil sump 176 as oil sumps temporarily storing lubricating oil are formed in the inner peripheral surface of the annular cylindrical portion 172. The upper oil sump 175 and the lower oil sump 176 are disposed at an interval in the vertical direction. The upper oil sump 175 is positioned above the lower oil sump 176.
The upper oil sump 175 and the lower oil sump 176 have recessed grooves 175a and 176a and receiving surfaces 175b and 176b.
The recessed grooves 175a and 176a are annular grooves recessed radially outward from the inner peripheral surface of the annular cylindrical portion 172 and extending over the entire circumferential direction. The receiving surfaces 175b and 176b are annular surfaces extending radially inward from the lower ends of the recessed grooves 175a and 176a and extending in the circumferential direction. The receiving surfaces 175b and 176b have a flat shape orthogonal to the axis O and have an annular shape extending over the entire circumferential direction. The receiving surfaces 175b and 176b protrude radially inward beyond the upper ends of the recessed grooves 175a and 176a to which the receiving surfaces 175b and 176b are connected.
The upper oil sump 175 is positioned radially outward of the lower oil sump 176. The radially inner end portion of the receiving surface 175b of the upper oil sump 175 is connected to the upper end of the recessed groove 176a of the lower oil sump 176 via a connecting inner peripheral surface 177 forming an inner peripheral cylindrical surface about the axis O. In other words, the upper oil sump 175 and the lower oil sump 176 have a stepped shape in which the lower oil sump 176 positioned below is disposed on the radially inner side.
Here, the volume of the recessed groove 175a of the upper oil sump 175 is larger than the volume of the recessed groove 176a of the lower oil sump 176. Further, the radial dimension of the receiving surface 175b of the upper oil sump 175 is larger than the radial dimension of the receiving surface 176b of the lower oil sump 176. In a cross-sectional shape including the axis O, the area in the upper oil sump 175 surrounded by a line segment interconnecting the upper end of the recessed groove 175a of the upper oil sump 175 and the radially inner end portion of the receiving surface 175b is larger than the area in the lower oil sump 176 surrounded by a line segment interconnecting the upper end of the recessed groove 176a of the lower oil sump 176 and the radially inner end portion of the receiving surface 176b. As a result, in a case where the annular cylindrical portion 172 rotates around the axis O, the volume by which the upper oil sump 175 is capable of accommodating lubricating oil is larger than the volume by which the lower oil sump 176 is capable of accommodating lubricating oil.
The annular member 170 has an upper lubricating oil supply hole 180 as a lubricating oil supply hole allowing the bottom portion of the recessed groove 175a of the upper oil sump 175 and the disk support surface 172a to communicate with each other in the radial direction. The upper lubricating oil supply hole 180 extends along a direction orthogonal to the axis O. A plurality of the upper lubricating oil supply holes 180 are formed at intervals in the circumferential direction.
The annular member 170 has a lower lubricating oil supply hole 181 as a lubricating oil supply hole allowing the bottom portion of the recessed groove 176a of the lower oil sump 176 and the inner peripheral surface of the upper fitting hole 171a to communicate with each other. The lower lubricating oil supply hole 181 extends radially outward and downward from the bottom portion of the recessed groove 176a and is open in the inner peripheral surface of the upper fitting hole 171a. The radially outer end portion of the lower lubricating oil supply hole 181 is connected to the first opening portion 162a of the carrier shaft 161. As a result, the lower lubricating oil supply hole 181 communicates with the intra-shaft flow path 162. A plurality of the lower lubricating oil supply holes 181 are formed in accordance with the number of the carrier shafts 161.
In addition, the configuration of the lubricating oil supply hole is not limited to the above and another configuration may be adopted insofar as the lubricating oil supply hole extends in the radial direction. In addition, insofar as the upper oil sump 175 and the lower oil sump 176 arc respectively provided at positions corresponding to the upper lubricating oil supply hole 180 and the lower lubricating oil supply hole 181, the upper oil sump 175 and the lower oil sump 176 may not have the annular shape extending over the entire circumferential direction.
Next, the brake mechanism 120 will be described with reference to
The brake mechanism 120 is disposed above the first stage planetary gear mechanism 90 in the lower accommodation space R2 of the speed reducer casing 61.
The brake mechanism 120 includes a brake disk 122, a brake plate 123, a brake piston 130, and a brake spring 140. The brake mechanism 120 further includes a gutter portion 136.
As shown in
The inner peripheral edge portion of the brake disk 122 may have an uneven shape in which a recessed portion and a projecting portion are continuous in the circumferential direction. The disk support surface 172a may have an uneven shape corresponding to the inner peripheral edge portion of the brake disk 122. And the brake disk 122 may be fixed to the disk support surface 172a by the uneven shapes of the inner peripheral edge portion of the brake disk 122 and the disk support surface 172a fitting together.
The opening position of the upper lubricating oil supply hole 180 in the disk support surface 172a is the height position between the pair of brake disks 122.
The brake plate 123 is an annular member and a plurality of the brake plates 123 (three brake plates 123 in the present embodiment) are disposed at intervals in the vertical direction so as to overhang from the inner peripheral surface of the speed reducer casing 61. The brake plate 123 has a plate shape and the vertical direction is the plate thickness direction of the plate shape. The brake plate 123 is provided so as to overhang from a first sliding contact inner peripheral surface 64a on the inner peripheral surface of the speed reducer casing 61. The first sliding contact inner peripheral surface 64a has an inner peripheral cylindrical surface shape about the axis O.
On the outer peripheral edge portion of the brake plate 123, a plurality of projecting portions protruding radially outward may be formed at intervals in the circumferential direction. In the first sliding contact inner peripheral surface 64a, recessed portions corresponding to the projecting portions of the brake plate 123 may be formed at intervals in the circumferential direction. The brake plate 123 may be provided so as to be immovable in the circumferential direction and movable in the vertical direction by the projecting portion fitting into the recessed portion of the first sliding contact inner peripheral surface 64a.
The plurality of brake plates 123 and the plurality of brake disks 122 are alternately disposed in the order of the brake plates 123 and the brake disks 122 downward from above. The brake plate 123 and the brake disk 122 are capable of abutting each other in the vertical direction. The abutting surface between the brake plate 123 and the brake disk 122 is a sliding contact surface (sliding portion) S2. The outer peripheral edge portion of the brake disk 122 faces the first sliding contact inner peripheral surface 64a at intervals from the radially inner side. The inner peripheral edge portion of the brake plate 123 faces the outer peripheral surface of the disk support surface 172a of the annular member 170 at an interval from the radially outer side.
Here, as shown in
Further, an overhanging portion 65 overhanging radially inward is formed on the inner peripheral surface of the speed reducer casing 61. The overhanging portion 65 has an annular shape about the axis O and a plate shape and the vertical direction is the plate thickness direction of the plate shape. The upper surface of the overhanging portion 65 faces the lowermost brake plate 123 from below. Formed in the upper surface of the overhanging portion 65 is a guiding recessed portion 65a recessed downward and extending in the radial direction at the same circumferential position as the through hole 123a. A plurality of the guiding recessed portions 65a are formed at intervals in the circumferential direction. The guiding recessed portion 65a extends from a first sliding contact outer peripheral surface to the inner peripheral end portion of the overhanging portion 65 and is open radially inward in the inner peripheral end portion.
As shown in
An upper surface 130a of the brake piston 130 faces the lower surface 21a of the electric motor casing 21 from below. The lower portion of the outer peripheral surface of the brake piston 130 is a first sliding contact outer peripheral surface 131 having a circular cross-sectional shape orthogonal to the axis O. The first sliding contact outer peripheral surface 131 of the brake piston 130 is slidable in the vertical direction with respect to the first sliding contact inner peripheral surface 64a of the speed reducer casing 61.
The upper portion of the outer peripheral surface of the brake piston 130 is a second sliding contact outer peripheral surface 132 having a circular cross-sectional shape orthogonal to the axis O. The second sliding contact outer peripheral surface 132 is larger in outer diameter than the first sliding contact outer peripheral surface 131. The second sliding contact outer peripheral surface 132 of the brake piston 130 is slidable in the vertical direction with respect to a second sliding contact inner peripheral surface 64b of the speed reducer casing 61. The second sliding contact inner peripheral surface 64b of the speed reducer casing 61 is larger in inner diameter than the first sliding contact inner peripheral surface 64a.
The step portion in the brake piston 130 that is between the first sliding contact outer peripheral surface 131 and the second sliding contact outer peripheral surface 132 is a pressure receiving surface 133 forming a flat shape orthogonal to the axis O, facing downward, and forming an annular shape.
The step portion in the speed reducer casing 61 that is between the first sliding contact inner peripheral surface 64a and the second sliding contact inner peripheral surface 64b is a stepped surface 64c forming a flat shape orthogonal to the axis O, facing upward, and forming an annular shape.
The pressure receiving surface 133 and the stepped surface 64c face each other in the vertical direction and approach and separate from each other as the brake piston 130 moves in the vertical direction. The annular space between the pressure receiving surface 133 and the stepped surface 64c is a hydraulic pressure supply space R4.
The speed reducer casing 61 has a hydraulic pressure supply hole 61a interconnecting the stepped surface 64c and the outside of the speed reducer casing 61. The hydraulic pressure supply space R4 communicates with the outside via the hydraulic pressure supply hole 61a. The hydraulic pressure that is generated by the hydraulic pump 238 is introduced into the hydraulic pressure supply hole 61a in a case where, for example, the swinging lock lever of the hydraulic shovel 200 is released.
On an annular lower surface 130b of the brake piston 130, a plate abutting surface 134 having an annular shape about axis O is formed so as to protrude from the lower surface 130b. The plate abutting surface 134 faces the brake plate 123 from above over the entire circumferential direction.
The upper surface 130a of the brake piston 130 has a piston-side accommodation recessed portion 135 recessed downward from above. A plurality of the piston-side accommodation recessed portions 135 are disposed at intervals in the circumferential direction.
The lower surface 21a of the electric motor casing 21 has a casing-side accommodation recessed portion 28 recessed upward from below. A plurality of the casing-side accommodation recessed portions 28 are disposed at intervals in the circumferential direction. The casing-side accommodation recessed portion 28 is disposed at the circumferential position that corresponds to the second bottom surface 27c. Each casing-side accommodation recessed portion 28 and each piston-side accommodation recessed portion 135 are provided at the same circumferential position so as to correspond to each other in a one-to-one relationship. The electric motor casing 21 has a hole portion 29 allowing the casing-side accommodation recessed portion 28 and the second bottom surface 27c to communicate with each other.
A space defined by the casing-side accommodation recessed portion 28 and the piston-side accommodation recessed portion 135 is defined as a spring accommodation space R3.
In addition, the outer peripheral-side communication hole 52 is open in the lower surface 21a of the electric motor casing 21 radially inward of the brake piston 130.
The brake spring 140 is provided in the spring accommodation space R3 and presses the brake piston 130 in a direction away from the electric motor casing 21.
The brake spring 140 of the present embodiment is a coil spring and is disposed in a posture allowing expansion and contraction in the vertical direction in the spring accommodation space R3. The brake spring 140 is accommodated in a compressed state in the spring accommodation space R3. The upper end of the brake spring 140 abuts against the bottom surface of the casing-side accommodation recessed portion 28 in the electric motor casing 21 and the lower end of the brake spring 140 abuts the bottom surface of the piston-side accommodation recessed portion 135 in the brake piston 130.
At the lower end of the brake piston 130, the gutter portion 136 extending radially inward from the inner peripheral surface of the brake piston 130 is provided integrally with the brake piston 130. A plurality of the gutter portions 136 are provided at intervals in the circumferential direction. For example, in the present embodiment, two gutter portions 136 are provided at an interval of 180° in the circumferential direction. A flow path groove 136a extending in the direction of extension of the gutter portion 136 is formed in the upper surface of the gutter portion 136. The flow path groove 136a is open radially inward in the radially inner end portion of the gutter portion 136. The radially inner end portion of the gutter portion 136 is positioned above the upper end surface of the first stage transmission shaft 91. In other words, the radially inner end portion of the gutter portion 136 is positioned above the fitting portion between the rotary shaft 40 and the first stage transmission shaft 91.
As shown in
The lubricating oil circulation unit 150 includes a lubricating oil flow path 151, a lubricating oil pump 152, a cooling unit 153, and a strainer 154.
The lubricating oil flow path 151 is a flow path formed by a flow path forming member such as piping provided outside the rotary drive device 10. A first end of the lubricating oil flow path 151, which is an upstream side end portion thereof, is connected to the lower accommodation space R2 in the speed reducer casing 61. In the present embodiment, the first end of the lubricating oil flow path 151 is connected to the part in the lower accommodation space R2 that is between the output shaft bearing 71 and the lower seal 72.
A second end of the lubricating oil flow path 151, which is a downstream side end portion thereof, is connected to the opening of the intra-rotor flow path F at the upper end of the rotary shaft 40. The second end of the lubricating oil flow path 151 is connected to the upper accommodation space R1 in the electric motor casing 21 via the intra-rotor flow path F.
The lubricating oil pump 152 is provided in the flow path of the lubricating oil flow path 151 and pumps lubricating oil from the first end toward the second end of the lubricating oil flow path 151, that is, from the lower accommodation space R2 side toward the upper accommodation space R1 side.
The cooling unit 153 is provided at the part of the lubricating oil flow path 151 that is downstream of the lubricating oil pump 152. The cooling unit 153 cools the lubricating oil that flows through the lubricating oil flow path 151 by heat exchange with the external atmosphere.
The strainer 154 is provided at the part of the lubricating oil flow path 151 that is upstream of the lubricating oil pump 152. The strainer 154 has a filter removing dust and dirt from the lubricating oil that passes through the lubricating oil flow path 151. It is preferable that the strainer 154 includes a magnetic filter removing, for example, iron powder generated from the gear teeth of the speed reducer 60.
In the present embodiment, lubricating oil is stored in the second accommodation space R2 in the speed reducer casing 61. And, of the planetary gear mechanisms, the second stage planetary gear mechanism 100 and the third stage planetary gear mechanism 110 are immersed in the lubricating oil. In other words, a liquid surface S of the lubricating oil in the lower accommodation space R2 is positioned between the first stage planetary gear mechanism 90 and the second stage planetary gear mechanism 100.
When the engine 236 of the hydraulic shovel 200 is started, hydraulic pressure is generated by the hydraulic pump 238 being simultaneously driven. Then, by the swinging lock lever being released, the brake of the rotary shaft 40 of the rotary drive system is released and the rotary shaft becomes rotatable.
In other words, the brake piston 130 of the brake mechanism 120 is pressed downward by the brake spring 140. As a result, in a state where no hydraulic pressure is supplied to the hydraulic pressure supply space R4, the brake piston 130 moves downward and presses the brake disk 122 via the brake plate 123. At this time, the rotary shaft 40 is in a non-rotatable brake state by the frictional force between the brake plate 123 and the brake disk 122.
Then, the brake piston 130 that has received the hydraulic pressure on the pressure receiving surface 133 moves upward when the hydraulic pressure is supplied to the hydraulic pressure supply space R4 via the hydraulic pressure supply hole 61a by the swinging lock lever being unlocked. As a result, the pressing of the brake plate 123 and the brake disk 122 by the brake piston 130 is released and the rotary shaft 40 is put into a rotatable brake release state.
Then, the rotary drive system 1 is driven and the upper swing body 230 swings by the swinging lever in the cab 231 being operated.
In other words, when the swinging lever is operated, alternating current electric power is supplied to each coil 32 of the stator 30 of the electric motor 20 via the inverter 239 and the rotor 38 rotates with respect to the stator 30 by each permanent magnet following the rotating magnetic field that is generated by the coils 32. The rotation of the rotary shaft 40 of the rotor 38 is decelerated via the transmission unit 80 in the speed reducer 60 and transmitted to the output shaft 70. In the present embodiment, the deceleration is sequentially performed via the three-stage planetary gear mechanisms. The swinging operation of the upper swing body 230 is performed by the rotation of the output shaft 70.
The electric motor 20 is driven with high torque when the upper swing body 230 swings. Accordingly, the temperatures of the rotor core 42 and the permanent magnet rise due to the iron loss in the rotor core 42 and the eddy current loss in the permanent magnet. At the same time, the temperature of the stator 30 rises due to the copper loss in the coil 32 and the iron loss in the stator core 31. When the temperature of the stator 30 is high, the temperature of the rotor core 42 becomes higher due to the radiant heat of the stator 30. Accordingly, cooling oil is supplied into the electric motor 20 by the lubricating oil circulation unit 150.
When the swinging lever is operated, the lubricating oil pump 152 of the lubricating oil circulation unit 150 is driven together with the drive of the electric motor 20. As a result, the lubricating oil stored by the lower accommodation space R2 being used as a tank is partially introduced into the intra-rotor flow path F of the electric motor 20 via the lubricating oil flow path 151. The lubricating oil cools the rotor core 42 and the permanent magnets in the course of flowing through the intra-rotor flow path F. Then, the lubricating oil discharged from the rotor 38 to the upper accommodation space R1 in the electric motor casing 21 is sprayed radially outward by the centrifugal force resulting from the rotation of the rotor 38 and cools the coil 32 and the stator core 31.
Subsequently, the lubricating oil that has fallen in the upper accommodation space R1 passes through the communication hole 50 penetrating the lower bottom portion 27 of the electric motor casing 21 or passes through the lower bearing 37. Then, the lubricating oil is introduced into the lower accommodation space R2 in the speed reducer casing 61. The lubricating oil passes through the lower bearing 37 and thus lubricity is ensured in the lower bearing 37.
The lubricating oil introduced into the lower accommodation space R2 merges with the lubricating oil stored by the lower accommodation space R2 being used as a tank. In the lower accommodation space R2, each planetary gear mechanism is lubricated by the lubricating oil falling from the electric motor casing 21 or by the stored lubricating oil.
Here, in the present embodiment, the first stage planetary gear mechanism 90, which is one of the plurality of planetary gear mechanisms in the transmission unit 80, is not immersed in the lubricating oil stored in the lower accommodation space R2. In addition, the brake mechanism 120 is not immersed in the lubricating oil. The first stage planetary gear 92 of the first stage planetary gear mechanism 90 and the brake disk 122 of the brake mechanism 120 rotate at a speed higher than the rotation speeds of the planetary gears of the other planetary gear mechanisms. Accordingly, since the first stage planetary gear 92 and the brake disk 122 are not immersed in the lubricating oil, the stirring loss of the lubricating oil as the entire transmission unit 80 can be reduced.
It is necessary to ensure the lubricity of the first stage planetary gear 92 and the brake disk 122 that are not immersed in the lubricating oil as described above. In the present embodiment, lubricating oil is supplied to the sliding surface S1 between the first stage planetary gear 92 and the first stage carrier 93 and the sliding contact surface S2 between the brake disk 122 and the brake plate 123 via the annular member 170.
In other words, as shown in
The lubricating oil accommodated in the upper oil sump 175 flows through the upper lubricating oil supply hole 180 in accordance with the centrifugal force and is discharged from the disk support surface 172a. As a result, the lubricating oil is supplied to the sliding contact surface S2 between the brake disk 122 and the brake plate 123 and lubricity is ensured on the sliding contact surface S2. The lubricating oil guided to the brake disk 122 and the brake plate 123 passes through the through hole 123a of the brake plate 123 and flows downward. Then, the lubricating oil passes through the guiding recessed portion 65a of the overhanging portion 65 and further flows downward from the radially inner end portion of the guiding recessed portion 65a.
The lubricating oil accommodated in the lower oil sump 176 flows through the lower lubricating oil supply hole 181 in accordance with the centrifugal force and is introduced into the intra-shaft flow path 162 of the carrier shaft 161 from the first opening portion 162a. The lubricating oil that has flowed through the intra-shaft flow path 162 is discharged from the second opening portion 162b of the intra-shaft flow path 162 and is supplied to the sliding surface S1 between the carrier shaft 161 and the first stage planetary gear 92. As a result, the lubricity of the sliding surface SI is ensured.
As described above, in the present embodiment, the lubricating oil that has reached the inner peripheral surface of the annular member 170 by being supplied into the speed reducer casing 61 from above is temporarily collected in the oil sump and then flows through the lubricating oil supply hole toward the outer peripheral side in accordance with the centrifugal force. Then, the lubricating oil discharged from the lubricating oil supply hole is supplied to the sliding portion on the radially outer side of the lubricating oil supply hole. As a result, lubricity can be ensured for the sliding portion.
In addition, the lower oil sump 176 positioned below is positioned radially inward of the upper oil sump 175 positioned above. Accordingly, the lubricating oil that the upper oil sump 175 has failed to accommodate drips down from the upper oil sump 175 and is introduced into the lower oil sump 176. As a result, it is possible to smoothly supply the lubricating oil to both the upper oil sump 175 and the lower oil sump 176.
Further, the upper oil sump 175 and the lower oil sump 176 have the receiving surfaces 175b and 176b, respectively. Since there are no other structures other than the annular member 170 above the receiving surfaces 175b and 176b, the lubricating oil falling from the communication hole 50 of the electric motor casing 21 can be received by the receiving surfaces 175b and 176b. The lubricating oil received by the receiving surfaces 175b and 176b is accommodated in the recessed grooves 175a and 176a in accordance with the centrifugal force of the rotating annular member 170. In addition, the lubricating oil that has received the centrifugal force is capable of remaining on the receiving surfaces 175b and 176b. In other words, it is possible for the receiving surfaces 175b and 176b themselves to be functioned as lubricating oil storage portions. As a result, the upper oil sump 175 and the lower oil sump 176 are capable of accommodating more lubricating oil than in a case where only the receiving surfaces 175b and 176b are formed.
In addition, in the present embodiment, a configuration in which lubricating oil is supplied from the upper oil sump 175 and the lower oil sump 176 is adopted, and thus it is possible to reliably lubricate the sliding portions of the first stage planetary gear mechanism 90 and the brake mechanism 120.
In particular, even in a case where the hydraulic shovel 200 is on a slope, it is possible to more reliably lubricate the first stage planetary gear mechanism 90 and the brake mechanism 120 by guiding lubricating oil radially outward from the upper oil sump 175 and the lower oil sump 176 by means of the centrifugal force.
Here, the brake mechanism 120 needs to ensure more lubricity than the first stage planetary gear mechanism 90. In other words, the brake disk 122 and the brake plate 123 may be in contact with each other at all times, and thus it is preferable that a large amount of lubricating oil is supplied to the sliding contact surface S2 between the brake disk 122 and the brake plate 123. In this regard, in the present embodiment, the volume by which lubricating oil can be accommodated in the upper oil sump 175 is larger than the volume by which lubricating oil can be accommodated in the lower oil sump 176. As a result, lubricity can be sufficiently ensured for the brake disk 122 to which lubricating oil is guided via the upper oil sump 175. It is possible to supply an appropriate amount of lubricating oil to the first stage planetary gear mechanism 90 via the lower oil sump 176.
Here, the fitting portion between the lower end of the rotary shaft 40 and the first stage transmission shaft 91 rotates at a high speed. Accordingly, fretting wear may occur in the fitting portion.
In the present embodiment, the gutter portion 136 is provided integrally with the brake piston 130. The lubricating oil introduced into the lower accommodation space R2 via the communication hole 50 of the electric motor casing 21 partially reaches the gutter portion 136, flows through the flow path groove 136a, and falls from above the fitting portion. Lubricity is ensured for the fitting portion by the lubricating oil being supplied to the fitting portion. The fretting wear can be suppressed as a result.
Although the embodiment of the present invention has been described above, the present invention is not limited thereto and can be appropriately changed without departing from the technical idea of the present invention.
Described in the embodiment is an example in which the annular member 170 is provided integrally with the first stage carrier 93 of the first stage planetary gear mechanism 90. However, the present invention is not limited thereto. For example, the annular member 170 may be provided integrally with another component of the transmission unit 80 or may be provided integrally with the rotary shaft 40.
Although an example in which both the upper oil sump 175 and the lower oil sump 176 are formed in the annular member 170 has been described in the embodiment, only one of the upper oil sump 175 and the lower oil sump 176 may be formed. Correspondingly, only one of the upper lubricating oil supply hole 180 and the lower lubricating oil supply hole 181 may be formed.
The brake mechanism 120 is not limited to the example of being disposed above the first stage planetary gear mechanism 90. For example, the brake mechanism 120 may be disposed at another location, examples of which include the location between the first stage planetary gear mechanism 90 and the second stage planetary gear mechanism 100 and the location between the second stage planetary gear mechanism 100 and the third stage planetary gear mechanism 110.
The planetary gear mechanisms are not limited to three stages and may be replaced with a single-stage planetary gear mechanism or those with a plurality of stages such as two stages and four or more stages. In addition, the brake mechanism 120 may be disposed at any position with respect to the planetary gear mechanisms.
Another sliding portion may be adopted although the sliding surface S1 between the first stage planetary gear 92 and the carrier shaft 161 and the sliding contact surface S2 between the brake disk 122 and the brake plate 123 have been described as examples of the sliding portion in the embodiment. In other words, lubricating oil may be supplied to another sliding portion requiring the lubricating oil via the oil sump of the annular member 170 and the lubricating oil supply hole.
Three or more oil sumps may be formed in the annular member with three or more lubricating oil supply holes formed so as to correspond to the oil sumps. In this case, the oil sump disposed lower than another one may be provided radially inward than the other one. In this manner, the lower oil sump also can be appropriately supplied with the lubricating oil that has flowed downward from the upper oil sump.
A plurality of lubricating oil supply holes guiding lubricating oil to different sliding portions may be formed with respect to one oil sump.
Although the rotary drive system 1 of the present embodiment is configured to use the electric motor 20, a hydraulic motor or the like may be applied instead of the electric motor 20 or a configuration in which the electric motor 20 and a hydraulic motor are combined may be applied.
Although an example in which the present invention is applied to the rotary drive system 1 of the hydraulic shovel 200 as a work machine has been described in the embodiment, the present invention may be applied to the rotary drive system 1 as a mechanism swinging or rotating part of another work machine. The present invention may be applied to a speed reducer alone as well as the rotary drive system 1 including the electric motor 20 and the speed reducer 60.
According to the speed reducer, the rotary drive system, and the hydraulic shovel of the above aspect, it is possible to smoothly supply lubricating oil to a sliding portion.
1: Rotary drive system
10: Rotary drive device
20: Electric motor
21: Electric motor casing
21
a: Lower surface
22: Upper casing
23: Upper cylindrical portion
24: Upper bottom portion
25: Lower casing
26: Lower cylindrical portion
27: Lower bottom portion
27
a: Lower through hole
27
b: First bottom surface
27
c: Second bottom surface
27
d: Stepped portion
28: Casing-side accommodation recessed portion
30: Stator
31: Stator core
32: Coil
35: Upper seal
36: Upper bearing
37: Lower bearing
38: Rotor
40: Rotary shaft
42: Rotor core
45: Lower end plate
46: Upper end plate
50: Communication hole
51: Inner peripheral-side communication hole
52: Outer peripheral-side communication hole
60: Speed reducer
61: Speed reducer casing
61
a: Hydraulic pressure supply hole
62
a: First stage inner gear teeth
62
b: Second stage inner gear teeth
62
c: Third stage inner gear teeth
64
a: First sliding contact inner peripheral surface
64
b: Second sliding contact inner peripheral surface
64
c: Stepped surface
65: Overhanging portion
65
a: Guiding recessed portion
70: Output shaft
71: Output shaft bearing
72: Lower seal
80: Transmission unit
90: First stage planetary gear mechanism
91: First stage transmission shaft (transmission shaft)
91
a: Cylindrical portion
91
b: Upper end
91
c: Flange portion
91
d: Sun gear teeth
92: First stage planetary gear (planetary gear)
92
a: Planetary gear teeth
93: First stage carrier (carrier)
100: Second stage planetary gear mechanism
101: Second stage transmission shaft
101
a: Sun gear teeth
102: Second stage planetary gear
103: Second stage carrier
110: Third stage planetary gear mechanism
111: Third stage transmission shaft
111
a: Sun gear teeth
112: Third stage planetary gear
113: Third stage carrier
120: Brake mechanism
122: Brake disk
123: Brake plate
123
a: Through hole
130: Brake piston
130
a: Upper surface
130
b: Lower surface
131: First sliding contact outer peripheral surface
132: Second sliding contact outer peripheral surface
133: Pressure receiving surface
134: Plate abutting surface
135: Piston-side accommodation recessed portion (recessed portion)
136: Gutter portion
136
a: Flow path groove
140: Brake spring
150: Lubricating oil circulation unit
151: Lubricating oil flow path
152: Lubricating oil pump
153: Cooling unit
154: Strainer
161: Carrier shaft
162: Intra-shaft flow path
162
a: First opening portion
162
b: Second opening portion
163: Upper radial flow path
164: Intermediate radial flow path
165: Axial flow path
167: Carrier main body
167
a: Lower fitting hole
170: Annular member
171: Annular plate portion
171
a: Upper fitting hole (fitting hole)
172: Annular cylindrical portion
172
a: Disk support surface
175: Upper oil sump (oil sump)
175
a: Recessed groove
175
b: Receiving surface
176: Lower oil sump (oil sump)
176
a: Recessed groove
176
b: Receiving surface
177: Connecting inner peripheral surface
180: Upper lubricating oil supply hole (lubricating oil supply hole)
181: Lower lubricating oil supply hole (lubricating oil supply hole)
200: Hydraulic shovel
211: Crawler
210: Undercarriage
220: Swing circle
221: Outer race
222: Inner race
223: Swing pinion
230: Upper swing body
231: Cab
232: Work equipment
233: Boom
234: Arm
235: Bucket
236: Engine
237: Generator motor
238: Hydraulic pump
239: Inverter
240: Capacitor
L: Swing axis
O: Axis
S: Liquid surface
R1: Upper accommodation space
R2: Lower accommodation space
R3: Spring accommodation space
R4: Hydraulic pressure supply space
F: Intra-rotor flow path
S1: Sliding surface (sliding portion)
S2: Sliding contact surface (sliding portion)
| Number | Date | Country | Kind |
|---|---|---|---|
| 2018-035843 | Feb 2018 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2019/001931 | 1/22/2019 | WO | 00 |
