JP2015190274A - Shovel - Google Patents

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JP2015190274A
JP2015190274A JP2014070439A JP2014070439A JP2015190274A JP 2015190274 A JP2015190274 A JP 2015190274A JP 2014070439 A JP2014070439 A JP 2014070439A JP 2014070439 A JP2014070439 A JP 2014070439A JP 2015190274 A JP2015190274 A JP 2015190274A
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Prior art keywords
turning
planet carrier
brake
carrier
spline
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JP2014070439A
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JP6352021B2 (en
Inventor
一則 平沼
Kazunori Hiranuma
一則 平沼
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住友重機械工業株式会社
Sumitomo Heavy Ind Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a shovel capable of securing braking of an output shaft regardless of the movement of a carrier member.SOLUTION: A shovel comprises a driving source for driving a turning body, a case, a reduction gear having a carrier member journaled to the case and supporting a gear for meshing with an output shaft of the driving source and a brake device having a brake disc of engaging with a spline formed in the case and the carrier member, and when setting the direction of turning to the driving source from the carrier member upward, in an upper part of the carrier member, assuming a minimum clearance dimension of a minimum clearance as C among clearances formed between the carrier member and the case and a distance up to a lower end part of the brake disc and the spline when stopping turning of the turning body as D, it is constituted so as to become D≥C.

Description

  The present invention relates to an excavator having a turning speed reducer.

  The excavator is provided with a turning drive device that drives the upper turning body to turn. This turning drive device often decelerates power from a power source (hydraulic motor, electric motor, etc.) with a turning speed reducer (hereinafter simply referred to as a speed reducer) and turns the upper turning body with increased output torque. .

  As this speed reducer, a planetary gear speed reducer using a sun gear as an input element and a planet carrier of the planetary gear as an output element is frequently used because of its compactness and easy change of the reduction ratio.

  Some reduction gears are provided with a brake mechanism. This brake mechanism has a first brake plate provided on an output shaft (hereinafter simply referred to as an output shaft) of a planetary carrier, and a second brake plate provided on a case of the turning speed reducer. During braking, the first and second brake plates are pressed against each other using a piston or the like, thereby braking the rotation of the output shaft.

  The first brake plate needs to rotate integrally with the output shaft, and the second brake plate needs to be attached integrally to the case. Further, in order for the first and second brake plates to come into pressure contact during braking, each brake plate needs to move in the axial direction of the output shaft. For this reason, the first brake plate and the output shaft and the second brake plate and the case are spline-coupled (for example, Patent Document 1).

JP 2013-227798 A

  By the way, the planet carrier is supported by the case by a bearing (bearing or the like), and thereby the planet carrier is restricted from moving in the axial direction. However, this bearing is considered to deteriorate with time. In addition, there is a risk that a large external force is applied to the upper swing body (for example, bucket, arm, boom, etc.) during excavation.

  If a large external force is applied to the upper swing body while the bearing is deteriorated with time, the planet carrier may move in the axial direction. Since the first brake plate is splined to the output shaft, this movement may cause the first brake plate to come out of the spline. In this case, there is a possibility that proper braking of the output shaft by the brake mechanism cannot be performed.

  One exemplary object of an aspect of the present invention is to provide an excavator that can ensure braking of an output shaft regardless of movement of a carrier member.

According to one aspect of the invention,
A drive source for driving the revolving structure;
A speed reducer having a case and a carrier member supported by the case and supporting a gear meshing with the output shaft of the drive source;
A brake device having a brake plate engaged with a spline formed on the case and the carrier member;
An excavator having
When the direction from the carrier member toward the drive source is the upper direction,
Above the carrier member, among the gaps formed between the carrier member and the case, the minimum gap distance of the smallest gap is C,
When the distance between the brake plate and the lower end of the spline is D when the turning of the turning body is stopped, D ≧ C.

  According to an aspect of the present invention, since the brake plate does not detach from the spline even when the carrier member moves, braking of the output shaft can be ensured regardless of the movement of the carrier member.

It is a side view of the shovel which is one Embodiment of this invention. It is a block diagram which shows the structure of the drive system which is one Embodiment of this invention. It is a block diagram which shows the structure of the turning drive device by one Embodiment of this invention. It is a top view of a turning drive device. It is sectional drawing which follows the VV line in FIG. It is sectional drawing which expands and shows the mechanical brake vicinity of a turning drive device.

  Reference will now be made to non-limiting exemplary embodiments of the invention with reference to the accompanying drawings.

  In the description of all attached drawings, the same or corresponding members or parts are denoted by the same or corresponding reference numerals, and redundant description is omitted. Also, the drawings are not intended to show relative ratios between members or parts unless otherwise specified. Accordingly, specific dimensions can be determined by one skilled in the art in light of the following non-limiting embodiments.

  In addition, the embodiments described below are examples, not limiting the invention, and all features and combinations thereof described in the embodiments are not necessarily essential to the invention.

  FIG. 1 shows an excavator 100 that is an embodiment of the present invention.

  In the excavator 100, the upper swing body 3 is mounted on the upper portion of the lower traveling body 1 via the swing mechanism 2. The upper swing body 3 is provided with an engine room 3a, a boom 4, an arm 5, a bucket 6, a cabin 10, and the like.

  The boom 4 has an arm 5 attached to the tip, and the arm 5 has a bucket 6 attached to the tip. The boom 4, the arm 5, and the bucket 6 are hydraulically driven by a boom cylinder 7, an arm cylinder 8, and a bucket cylinder 9, respectively.

  The cabin 10 is provided with an operating device 26 (see FIG. 2) operated by the driver. The engine room 3a is equipped with a power source such as an engine.

  The shovel 100 according to the present embodiment is a so-called hybrid excavator having a power storage device that accumulates electric power to be supplied to the turning drive device. However, the present invention can be applied to, for example, an electrically driven excavator to which charging power is supplied from an external power source, or a hydraulic excavator that drives the turning mechanism 2 by a hydraulic motor if the excavator adopts a mechanical brake described later. It is possible.

  FIG. 2 is a block diagram showing the configuration of the drive system of the excavator 100. In FIG. 2, the mechanical power system is indicated by a double line, the high-pressure hydraulic line is indicated by a thick solid line, the pilot line is indicated by a broken line, and the electric drive / control system is indicated by a thin solid line.

  The drive system of the excavator 100 includes an engine 11, a motor generator 12, a main pump 14, a pilot pump 15, a control valve 17, an operation device 26, a controller 30, a turning drive device 40, a power storage system 120, and the like.

  The engine 11 and the motor generator 12 are connected to two input shafts of the transmission 13, respectively. A main pump 14 and a pilot pump 15 are connected to the output shaft of the transmission 13. Both the main pump 14 and the pilot pump 15 are hydraulic pumps.

  A control valve 17 is connected to the main pump 14 via a high pressure hydraulic line 16. An operation device 26 is connected to the pilot pump 15 via a pilot line 25.

  As described above, in this embodiment, the hybrid excavator 100 is taken as an example. The control valve 17 controls the hydraulic system in the hybrid excavator 100. Therefore, hydraulic motors 1A and 1B for the lower traveling body, boom cylinder 7, arm cylinder 8 and bucket cylinder 9 are connected to the control valve 17 via a high pressure hydraulic line.

  The motor generator 12 is connected to the power storage system 120 via the inverter 18. The power storage system 120 has a capacitor (power storage device) as a power storage device. The power storage system 120 is connected to the turning drive device 40.

  The turning drive device 40 includes a turning electric motor 21, a resolver 22, a mechanical brake 23, a turning speed reducer 24, and the like. The power storage system 120 is connected to the turning electric motor 21 via the inverter 20. The output shaft 21 b of the turning electric motor 21 is connected to the resolver 22 and the turning speed reducer 24. Further, the output shaft 24 </ b> A of the turning speed reducer 24 is connected to the mechanical brake 23.

  The turning electric motor 21 functions as a turning electric motor for driving the upper turning body 3 to turn. The mechanical brake 23 functions as a brake device that mechanically brakes the upper swing body 3.

  The operating device 26 includes a lever 26A, a lever 26B, and a pedal 26C. The lever 26A, the lever 26B, and the pedal 26C are connected to the control valve 17 and the pressure sensor 29 via hydraulic lines 27 and 28, respectively. The pressure sensor 29 is connected to a controller 30 that performs drive control of the electric system.

  The controller 30 is a control device as a main control unit that performs drive control of the hybrid excavator. The controller 30 is composed of an arithmetic processing unit including a CPU (Central Processing Unit) and an internal memory. The controller 30 executes predetermined drive control by the CPU executing a drive control program stored in an internal memory.

  Specifically, the controller 30 converts a signal supplied from the pressure sensor 29 into a speed command, and performs drive control of the turning electric motor 21 based on this signal. At this time, the signal supplied from the pressure sensor 29 is a signal representing the amount of operation by which the driver has operated the operating device 26 to turn the turning mechanism 2.

  The controller 30 controls the operation of the motor generator 12. Here, the operation control of the motor generator 12 refers to control for switching between electric (assist) operation and power generation operation.

  Furthermore, the controller 30 performs charge / discharge control of a capacitor provided in the power storage system 120. Specifically, the controller 30 performs switching control between the step-up / step-down operation of the step-up / step-down converter of the power storage system 120 based on the charge state of the capacitor, the operation state of the motor generator 12, and the operation state of the turning motor 21. Do.

  In the present embodiment, the operation state of the motor generator 12 has two operation states of an electric (assist) operation state and a power generation operation state. Moreover, as the driving | running state of the electric motor 21 for turning, it has two driving | running states, a power running operation and regenerative operation. Note that the controller 30 also controls the amount of charging (charging current or charging power) of the capacitor as will be described later.

  The excavator 100 having the above-described drive system drives the turning electric motor 21 with electric power supplied via the inverter 20 when the upper turning body 3 is driven to turn. The rotational force of the output shaft 21b of the turning electric motor 21 is transmitted to the output shaft 40A of the turning drive device 40 via the turning speed reducer 24.

  FIG. 3 is a block diagram of the turning drive device 40 mounted on the excavator 100 according to the embodiment of the present invention. The turning drive device 40 includes a turning electric motor 21, a resolver 22, a mechanical brake 23, a turning speed reducer 24, an output shaft 40A, and the like.

  The turning electric motor 21 is an electric motor. The turning speed reducer 24 is connected to the output shaft side of the turning electric motor 21. This turning speed reducer 24 has a three-stage configuration of a first turning speed reducer 24-1, a second turning speed reducer 24-2, and a third turning speed reducer 24-3. The first turning speed reducer 24-1, the second turning speed reducer 24-2, and the third turning speed reducer 24-3 are each constituted by a planetary speed reducer.

  The first stage first turning speed reducer 24-1 is assembled to the turning electric motor 21. The planetary carrier 46 serving as the output shaft of the first turning speed reducer 24-1 is provided with a mechanical brake 23.

  Further, the second stage second turning speed reducer 24-2 is assembled to the first turning speed reducer 24-1 with the mechanical brake 23 interposed therebetween. Further, the third-stage third turning speed reducer 24-3 is assembled to the second turning speed reducer 24-2. The output shaft of the third turning speed reducer 24-3 becomes the output shaft 40A of the turning drive device 40.

  Although not shown, the output shaft 40A of the turning drive device 40 is connected to the turning mechanism 2, and the turning mechanism 2 is driven by the rotational force of the output shaft 40A.

  Next, a specific configuration of the turning drive device 40 will be described with reference to FIGS.

  FIG. 4 is a top view of the turning drive device 40, and a broken line in FIG. 4 represents a hide line of main components of the first turning speed reducer 24-1. FIG. 5 is a cross-sectional view taken along line VV in FIG. FIG. 6 is an enlarged sectional view showing the vicinity of the first turning speed reducer 24-1 and the mechanical brake 23 in the turning drive device 40.

  As shown in FIG.4 and FIG.5, the 1st rotation speed reducer 24-1 is comprised with the planetary gear mechanism which has the sun gear 42, the planetary gear 44, the planetary carrier 46, the internal gear 48, etc. FIG. As shown in FIG. 5, the second turning speed reducer 24-2 includes a planetary gear mechanism having a sun gear 82, a planetary gear 84, a planet carrier 86, an internal gear 88, and the like. Similarly, the third turning speed reducer 24-3 includes a planetary gear mechanism having the sun gear 102, the planetary gear 104, the planet carrier 106, the internal gear 108, and the like.

  The first turning speed reducer 24-1 is housed inside the first gear case 50 and the second gear case 52.

  The sun gear 42 is fixed to the output shaft 21 b of the turning electric motor 21. In this embodiment, three planetary gears 44 are engaged with (engaged with) the sun gear 42.

  Each planetary gear 44 is rotatably supported by a pin 44 a erected on the planet carrier 46. Each planetary gear 44 meshes with an internal gear 48 formed on the inner surface of the first gear case 50.

The first gear case 50 in which the internal gear 48 is formed is fixed to the end plate 21 a of the turning electric motor 21. Therefore, the internal gear 48 (first gear case 50) cannot rotate by itself.
On the other hand, the lower part of the planetary carrier 46 becomes an output shaft of the first turning speed reducer 24-1. The planet carrier 46 serving as an output shaft is rotatably supported by a second gear case 52 fixed to the first gear case 50 via a bearing 56.

  Note that the first turning speed reducer 24-1 described above is lubricated by the lubricating oil LB1. Specifically, the first turning speed reducer 24-1 has a sealed space sealed by the end plate 21a, the output shaft 21b, the first gear case 50, the second gear case 52, and the planetary carrier 46 of the turning electric motor 21. The sealed space is filled with lubricating oil LB1 (shown by fine dots in FIGS. 5 and 6). Therefore, the first turning speed reducer 24-1 is configured to be lubricated by the lubricating oil LB1.

  In the first turning speed reducer 24-1 configured as described above, when the output shaft 21b of the turning electric motor 21 rotates and the sun gear 42 rotates, the planetary gear 44 rotates (spins). The planetary gear 44 meshes with an internal gear 48 formed on the inner surface of the first gear case 50. Therefore, the first gear case 50 in which the internal gear 48 is formed tends to rotate due to the rotational force of the planetary gear 44.

  However, since the first gear case 50 is fixed to the end plate 21a of the turning electric motor 21 as described above, the first gear case 50 cannot rotate. On the other hand, the planet carrier 46 is configured to be rotatable with respect to the second gear case 52.

  As a result, the rotational force of the planetary gear 44 acts as a force for rotating the planetary carrier 46, whereby the planetary carrier 46 rotates. As a result, the rotation of the output shaft 21 b of the turning electric motor 21 is decelerated by the first turning speed reducer 24-1 and output from the planet carrier 46.

  In the present embodiment, the sun gear 42, each planetary gear 44, and the internal gear 48 are constituted by helical gears. With this configuration, it is possible to reduce the occurrence of noise and vibration in the nuclear gears 42, 44, 48 and the like constituting the first turning speed reducer 24-1 and to facilitate the meshing of the teeth.

  Next, the second turning speed reducer 24-2 will be described. The sun gear 82 of the second turning speed reducer 24-2 is fixed to the planet carrier 46 as an output shaft of the first turning speed reducer 24-1. The sun gear 82 meshes with a plurality of planetary gears 84. Further, the planetary gear 84 meshes with an internal gear 88 formed on the inner wall of the third gear case 54. Therefore, the planetary gear 84 revolves while rotating between the sun gear 82 and the internal gear 88.

  In the present embodiment, the second turning speed reducer 24-2 has three planetary gears 84. Each planetary gear 84 is rotatably supported by the planetary carrier 86 via a pin 84a, and rotates the planetary carrier 86 by revolving while rotating. This planet carrier 86 constitutes the output shaft of the second turning speed reducer 24-2.

  Next, the third turning speed reducer 24-3 will be described. The sun gear 102 of the third turning speed reducer 24-3 is fixed to a planet carrier 86 as an output shaft of the second turning speed reducer 24-2. The planet carrier 86 engages with a plurality of planet gears 104. Further, the planetary gear 104 meshes with an internal gear 108 formed on the inner wall of the third gear case 54. Therefore, the planetary gear 104 revolves while rotating between the sun gear 102 and the internal gear 108.

  In the present embodiment, the third turning speed reducer 24-3 has three planetary gears 104. Each planetary gear 104 is rotatably supported by the planetary carrier 106 via a pin 104a, and rotates the planetary carrier 106 by revolving while rotating. The planet carrier 106 constitutes the output shaft 40A of the third turning speed reducer 24-3.

  In the present embodiment, the third turning speed reducer 24-3 is a final stage speed reducer. Therefore, the output shaft 40A of the third turning speed reducer 24-3 becomes the output shaft 40A of the turning speed reducer 24.

  Further, the turning drive device 40 has a sealed space sealed by the planet carrier 46, the second gear case 52, the third gear case 54, and the planet carrier 106. This sealed space is filled with lubricating oil LB2 (shown by a coarse dot pattern in FIGS. 5 and 6).

  Moreover, each gear which comprises the 2nd and 3rd turning reduction gears 24-2 and 24-3 is accommodated in this sealed space. Therefore, each gear constituting the second and third turning speed reducers 24-2 and 24-3 is lubricated by the lubricating oil LB2.

  With the above-described configuration, the turning drive device 40 increases the torque of the output shaft 40A by reducing the rotation speed of the output shaft 21b of the turning electric motor 21.

  In the present embodiment, spur gears are used as the gears constituting the second and third turning speed reducers 24-2 and 24-3. This is because the gears constituting the second and third turning speed reducers 24-2 and 24-3 have a lower rotational speed and lower noise level and vibration level than the gears constituting the first turning speed reducer 24-1. Because. The gears constituting the second and third turning speed reducers 24-2 and 24-3 may be helical gears as in the first turning speed reducer 24-1.

  Next, the mechanical brake 23 will be described.

  The mechanical brake 23 is a disc brake having a brake disc 60 and a brake plate 62. The mechanical brake 23 is provided between the second gear case 52 that is a fixed portion and the planet carrier 46.

  The brake disc 60 has a disk shape, and a hole into which the planet carrier 46 is inserted is formed at the center. Spline teeth are formed on the inner periphery of the hole.

  A spline 70 is formed on the outer peripheral portion of the planet carrier 46 (the portion where the brake disc 60 is mounted). The spline 70 is formed on the outer periphery of the planet carrier 46 so as to extend in the vertical direction (directions indicated by arrows Z1 and Z2 in FIGS. 5 and 6).

  In the following description, a direction from the planet carrier 46 toward the turning motor 21 is referred to as an upper direction (arrow Z1 direction), and an opposite direction to the direction from the planet carrier 46 toward the turning electric motor 21 is below (arrow Z2 direction). Let's say.

  The spline teeth formed on the brake disc 60 are configured to engage with the splines 70 formed on the planet carrier 46. Therefore, when the brake disc 60 is attached to the planet carrier 46, the brake disc 60 and the planet carrier 46 are spline-connected.

  In this manner, when the brake disk 60 and the planet carrier 46 are spline-connected, the brake disk 60 extends from the planet carrier 46 outward in the rotational radius direction. The brake disk 60 cannot rotate with respect to the planet carrier 46, but is movable in the axial direction of the planet carrier 46 (in the directions of arrows Z1 and Z2).

  The brake plate 62 is disposed on both upper and lower sides of the brake disc 60. The brake plate 62 also has a disk shape. Spline teeth are formed on the outer periphery of the brake plate 62.

  A spline 72 is formed on the annular inner wall portion (the portion where the brake plate 62 is mounted) of the second gear case 52. The spline 72 is formed on the inner wall of the second gear case 52 so as to extend in the vertical direction (directions indicated by arrows Z1 and Z2 in FIGS. 5 and 6).

  The spline teeth formed on the brake plate 62 are configured to engage with the splines 72 formed on the second gear case 52. Therefore, when the brake plate 62 is attached to the second gear case 52, the brake plate 62 and the second gear case 52 are spline-connected.

  In this way, when the brake plate 62 and the second gear case 52 are spline-connected, the brake plate 62 extends from the second gear case 52 inward in the rotational radius direction. The brake plate 62 cannot rotate with respect to the second gear case 52, but is movable in the axial direction of the planet carrier 46 (in the directions of arrows Z1 and Z2).

  Further, above the brake plate 62, the piston 64 is disposed in a state in which the piston 64 can move in the axial direction of the planetary carrier 46 (arrow Z1, Z2 direction). The piston 64 is pressed by the spring 66 and is always pressed against the upper brake plate 62. In the present embodiment, a coil spring is used as the spring 66, but a multi-stage conical spring that can obtain a high output with a small displacement can also be used.

  As described above, both the brake disc 60 and the brake plate 62 are movable in the axial direction of the planet carrier 46. Therefore, when the brake plate 62 is pressed by the piston 64, the brake disc 60 is pressed between the upper and lower brake plates 62. When the brake disc 60 is sandwiched and pressed by the brake plate 62, a braking force is generated in the mechanical brake 23 so as to prevent the brake disc 60 from rotating.

  As described above, the brake disk 60 cannot be rotated with respect to the planet carrier 46. For this reason, the braking force acting on the brake disk 60 becomes a braking force (braking force) that stops the rotation of the planet carrier 46.

  A hydraulic space 68 capable of supplying hydraulic oil is formed between the piston 64 and the second gear case 52. A brake release port 69 is connected to the hydraulic space 68. Further, a seal member 91 such as an O-ring is disposed between the piston 64 and the second gear case 52 to seal the hydraulic oil in the hydraulic space 68 from leaking out.

  The brake release port 69 is connected to the operation device 26. When the hydraulic pressure is supplied from the pilot pump 15 to the hydraulic space 68 via the operating device 26, the hydraulic line 27a (see FIG. 2), and the brake release port 69, the piston 64 is pushed up by the hydraulic pressure. Thereby, the force which presses the brake plate 62 is lost, and the mechanical brake 23 is in a released state.

  The mechanical brake 23 configured as described above is controlled so that the brake is released when the upper swing body 3 is turned and the brake is activated when the upper swing body 3 is stopped.

  Here, the movement of the planetary carrier 46 in the first gear case 50 and the second gear case 52 in the axial direction (arrow Z1, Z2 direction) generated in the turning drive device 40 having the above-described configuration will be considered.

  The planetary carrier 46 is positioned in the first gear case 50 and the second gear case 52 by being regulated by a bearing 56 or the like in a state where the turning drive device 40 is not deteriorated with time (hereinafter referred to as a normal state). It is located in the predetermined mounting position.

  However, when the shovel 100 is used for a long time, the bearing 56 may be deteriorated with time. The state in which the bearing 56 has deteriorated with time is, for example, a state in which the planetary carrier 46 can no longer be regulated to a normal position while maintaining the function of the bearing 56 to rotatably support the planetary carrier 46. .

  When the bearing 56 is deteriorated with time, the planet carrier 46 may move in the axial direction (arrow Z1, Z2 direction) of the planet carrier 46 from the normal position inside the first and second gear cases 50, 52.

  On the other hand, the excavator 100 is used in a harsh environment, and a large external force is applied to the upper swing body 3 and each component (for example, the boom 4, the arm 5, and the bucket 6) provided in the operation. There is a risk of being applied. When this external force is applied to the turning drive device 40, the planetary carrier 46 may move in the axial direction (arrow Z1, Z2 direction). In particular, when a large external force as described above is applied in a state where the bearing 56 has deteriorated with time, the amount of movement of the planet carrier 46 in the axial direction increases.

  When the planetary carrier 46 moves, the brake disk 60 is detached from the spline 70, and there is a possibility that the planetary carrier 46 (output shaft 40A) is not properly braked by the mechanical brake 23.

  Next, the movement range in which the planet carrier 46 moves in the axial direction inside the first and second gear cases 50 and 52 will be considered mainly with reference to FIGS. 5 and 6.

  First, the movement range when the planet carrier 46 moves upward will be considered. The upward movement of the planet carrier 46 is restricted because the upper surface of the planet carrier 46 (hereinafter referred to as the carrier upper surface) is disposed above the planet carrier 46 (hereinafter referred to as the upper structure). ).

  The position where the carrier upper surface and the upper component abut is the position where the gap distance between the carrier upper surface and the upper component is the shortest (hereinafter referred to as the upper minimum gap position). Therefore, the upper minimum clearance position is obtained in the turning drive device 40. In the following description, the position where the lower end portion of the output shaft 21b and the upper surface of the planetary carrier 46 face each other is the upper minimum gap position, and the minimum gap distance is C (see FIG. 6).

  Next, the movement range when the planet carrier 46 moves downward will be considered. The downward movement of the planet carrier 46 is restricted because the lower surface of the planet carrier 46 (hereinafter referred to as the carrier lower surface) is disposed below the planet carrier 46 (hereinafter referred to as the lower structure). ).

  The position where the carrier lower surface and the lower component abut is the position where the gap distance between the carrier lower surface and the lower component is the shortest (hereinafter referred to as the lower minimum gap position). Therefore, in the turning drive device 40, the lower minimum clearance position is obtained. In the following description, the position where the lower surface of the planetary carrier 46 and the upper surface of the second gear case 52 face each other in the vicinity of the bearing 56 is the upper minimum gap position, and the minimum gap distance is E (see FIG. 6). .

  When the minimum clearance distance at the upper minimum clearance position is C and the minimum clearance distance at the upper minimum clearance position is E as in the example described above, the planet carrier 46 is located inside the first and second gear cases 50 and 52. It can be moved by a distance C in the upward direction (arrow Z1 direction), and can be moved by a distance E in the downward direction (arrow Z2 direction). That is, the distance obtained by adding the distance C and the distance E is the moving range of the planet carrier 46 in the first and second gear cases 50 and 52.

  In order to make the mechanical brake 23 function (brake processing) regardless of the movement of the planet carrier 46, the brake disc 60 and the brake plate 62 are separated from the splines 70 and 72 even if the planet carrier 46 moves within the movement range. What is necessary is just to comprise.

  Therefore, in the present embodiment, when the upper swing body 3 stops turning, the distance from the lowermost brake disk 60 among the plurality of stacked brake disks 60 to the lower end of the spline 70 (indicated by an arrow D in the figure). The distance) is set to be the same as or larger than the minimum gap dimension (the dimension indicated by the arrow C in the drawing) at the upper minimum gap position (D ≧ C).

  Therefore, in the present embodiment, the length of the spline 70 is set such that the brake disk 60 is not detached from the spline 70 even if the planetary carrier 46 moves inside the first and second gear cases 50 and 52.

  Specifically, the dimension from the lowermost brake disk 60 among the plurality of stacked brake disks 60 to the end of the spline 70 is the same as or larger than the upward movement range of the planetary carrier 46. Is set. Therefore, even if the planet carrier 46 moves in the axial direction, the brake disc 60 does not come off from the spline 70.

  Further, in the present embodiment, when the upper swing body 3 stops turning, the distance from the uppermost brake disk 60 to the upper end of the spline 70 among the plurality of stacked brake disks 60 (indicated by an arrow F in the figure). The distance) is set to be the same as or larger than the minimum gap dimension (the dimension indicated by the arrow E in the figure) at the upper minimum gap position (F ≧ E).

  Therefore, in this embodiment, the dimension of the spline 70 extending upward from the brake disk 60 positioned at the uppermost position is the same as or larger than the downward movement range of the planetary carrier 46. For this reason, even when the planetary carrier 46 moves downward, the brake disk 60 is not detached from the spline 70.

  The brake plate 62 attached to the spline 72 formed in the second gear case 52 is prevented from being detached from the spline 70 by the piston 64 provided at the upper part.

  Thus, in the shovel 100 of the present embodiment, the length of the spline 70 is such that even if the planetary carrier 46 moves inside the first and second gear cases 50 and 52, the brake disks 60 and 62 are separated from the splines 70 and 72. Since the length is set so as not to be detached, the upper swing body 3 can be reliably braked by the mechanical brake 23.

  Even if the bearing 56 is damaged by any chance, the brake disks 60 and 62 are kept engaged (engaged) with the splines 70 and 72. Therefore, even when the bearing 56 is damaged, the upper swing body 3 can be reliably braked by the mechanical brake 23.

  In the above-described embodiment, the upper minimum gap position is a position where the lower end portion of the output shaft 21b and the upper surface of the planet carrier 46 face each other, and the lower minimum gap position is the lower surface of the planet carrier 46 and the upper surface of the second gear case 52. The example which is a position which opposes was demonstrated. However, the upper minimum gap position and the lower minimum gap position are not limited to the positions shown in the present embodiment.

  That is, the turning drive device 40 has various types depending on the type of excavator (for example, a large machine or a small machine). Accordingly, the upper minimum clearance position and the lower minimum clearance position in the turning drive apparatus are as follows. Different positions. Therefore, it is necessary to individually determine the upper minimum clearance position and the lower minimum clearance position for each turning drive device.

  The preferred embodiments of the present invention have been described in detail above. However, the present invention is not limited to the specific embodiments described above, and various modifications can be made within the scope of the present invention described in the claims. It can be modified and changed.

DESCRIPTION OF SYMBOLS 1 Lower traveling body 1A, 1B Hydraulic motor 2 Turning mechanism 3 Upper turning body 11 Engine 12 Motor generator 13 Transmission 14 Main pump 15 Pilot pump 16 High pressure hydraulic line 17 Control valve 18, 20 Inverter 21 Turning electric motor 21a End plate 21b Output shaft 22 Resolver 23 Mechanical brake 24 Turning speed reducer 24-1 First turning speed reducer 24-2 Second turning speed reducer 24-3 Third turning speed reducer 25 Pilot line 26 Operating device 29 Pressure sensor 30 Controller 40 Swing drive device 40A Output shaft 42, 82, 102 Sun gears 44, 84, 104 Planetary gears 46, 86, 106 Planetary carriers 48, 88, 108 Internal gear 50 First gear case 52 Second gear case 54 Third gear case 56 Bearing 57 Oil seal 60 brake Disc 62 Brake plate 64 Piston 66 Spring 70, 72 Spline 70
120 Power storage system

Claims (3)

  1. A drive source for driving the revolving structure;
    A gear reducer in which a sun gear, a planetary gear, an internal gear, and a planet carrier that supports the planetary gear are arranged inside the case;
    Splines formed on the planet carrier;
    A brake device having a brake plate that engages with the spline, and performing rotational braking of the planet carrier via the brake plate;
    An excavator having
    The shovel is characterized in that the spline has a length that maintains engagement with the brake plate when the planet carrier moves in the case.
  2. When the direction from the planet carrier toward the drive source is set upward,
    The spline is
    The distance between the engagement position of the brake plate with the spline and the lower end of the spline is set to be longer than the minimum gap formed between the planet carrier and the case above the case. The excavator according to claim 1, wherein the excavator is characterized.
  3. When the direction opposite to the direction from the planetary carrier toward the driving source is the lower side,
    The spline is
    The distance between the engagement position of the brake plate with the spline and the upper end of the spline is set to be longer than the minimum gap formed between the planet carrier and the case below the case. The excavator according to claim 1, wherein the excavator is characterized.
JP2014070439A 2014-03-28 2014-03-28 Excavator Active JP6352021B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2014070439A JP6352021B2 (en) 2014-03-28 2014-03-28 Excavator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2014070439A JP6352021B2 (en) 2014-03-28 2014-03-28 Excavator

Publications (2)

Publication Number Publication Date
JP2015190274A true JP2015190274A (en) 2015-11-02
JP6352021B2 JP6352021B2 (en) 2018-07-04

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Family Applications (1)

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Country Status (1)

Country Link
JP (1) JP6352021B2 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003222170A (en) * 2002-01-25 2003-08-08 Hitachi Constr Mach Co Ltd Wet type multiple disk brake device, wet type multiple disk clutch device, and winding apparatus for crane therewith
JP2006025580A (en) * 2004-06-07 2006-01-26 Kobelco Contstruction Machinery Ltd Vertical motor drive with brake, and working machine
JP2012077859A (en) * 2010-10-04 2012-04-19 Hitachi Constr Mach Co Ltd Wet brake device
JP2013227798A (en) * 2012-04-26 2013-11-07 Kobelco Contstruction Machinery Ltd Construction machine drive device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003222170A (en) * 2002-01-25 2003-08-08 Hitachi Constr Mach Co Ltd Wet type multiple disk brake device, wet type multiple disk clutch device, and winding apparatus for crane therewith
JP2006025580A (en) * 2004-06-07 2006-01-26 Kobelco Contstruction Machinery Ltd Vertical motor drive with brake, and working machine
JP2012077859A (en) * 2010-10-04 2012-04-19 Hitachi Constr Mach Co Ltd Wet brake device
JP2013227798A (en) * 2012-04-26 2013-11-07 Kobelco Contstruction Machinery Ltd Construction machine drive device

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