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WO2020016247A1 - Mécanisme de commande de pivotement, dispositif de frein, appareil de propulsion de nacelle et système d'alimentation marin - Google Patents

Mécanisme de commande de pivotement, dispositif de frein, appareil de propulsion de nacelle et système d'alimentation marin Download PDF

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Publication number
WO2020016247A1
WO2020016247A1 PCT/EP2019/069156 EP2019069156W WO2020016247A1 WO 2020016247 A1 WO2020016247 A1 WO 2020016247A1 EP 2019069156 W EP2019069156 W EP 2019069156W WO 2020016247 A1 WO2020016247 A1 WO 2020016247A1
Authority
WO
WIPO (PCT)
Prior art keywords
slewing
friction plate
plate assembly
static friction
spring
Prior art date
Application number
PCT/EP2019/069156
Other languages
English (en)
Inventor
Rui Nan WANG
Rui Chun DUAN
Fu Hua QIU
Yong Yang
Da Wei LIU
Zhong Wei TIAN
Original Assignee
Siemens Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Publication of WO2020016247A1 publication Critical patent/WO2020016247A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D69/00—Friction linings; Attachment thereof; Selection of coacting friction substances or surfaces
    • F16D69/04—Attachment of linings
    • F16D69/0408—Attachment of linings specially adapted for plane linings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
    • B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
    • B63H5/125—Arrangements on vessels of propulsion elements directly acting on water of propellers movably mounted with respect to hull, e.g. adjustable in direction, e.g. podded azimuthing thrusters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/02—Fluid pressure
    • F16D2121/04—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure
    • F16D2121/06—Fluid pressure acting on a piston-type actuator, e.g. for liquid pressure for releasing a normally applied brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/20—Electric or magnetic using electromagnets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F16D55/36—Brakes with a plurality of rotating discs all lying side by side
    • F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake

Definitions

  • the present invention relates to the technical field of marine power, in particular to a slewing control mechanism, a brake device, a pod propulsion apparatus and a marine power system.
  • Marine power plants mainly comprise two parts: a slewing unit and a power unit.
  • the slewing unit is fixed to a hull for driving the power unit to slew; and the power unit is responsible for providing a driving force.
  • the circumferential position of the power unit is kept locked primarily by employing mechanical locking or adding an auxiliary slewing drive device to provide sufficient torque.
  • the mechanical locking method uses a hydraulic cylinder to push a pin shaft to lock the power unit and the slewing unit, which not only limits the freedom and arbitrariness of the overall slewing of the pod propulsion apparatus, but also performs locking only in a certain circumferential orientation, and positioning pin holes of the power unit and the slewing unit have high requirements for the degree of coincidence, which brings great inconvenience to an operator.
  • the auxiliary slewing drive device is added, which will increase the production cost, while occupying a large equipment installation space. The equipment power is greater.
  • a slewing brake device, a pod propulsion apparatus and a marine power system are proposed in the embodiments of the present invention to solve the technical problem of damage to the output shaft of the slewing power plant due to the excessive instantaneous load in the prior art marine power system.
  • an embodiment of the present invention provides a slewing control mechanism, comprising:
  • a brake shaft comprising a connecting end and a driving end
  • a static friction plate assembly comprising at least two static friction plates
  • a movable friction plate assembly comprising at least one movable friction plate, the at least one movable friction plate being provided with a first connecting portion connected to the connecting end, wherein the at least two static friction plates of the static friction plate assembly and the at least one movable friction plate of the movable friction plate assembly are alternately arranged;
  • a piston ring comprising a first end face and a second end face opposite each other, the first end face abutting against the static friction plate assembly; and a spring, with one end of the spring abutting against the second end face of the piston ring;
  • the spring is adjustable, and the piston ring applies a second pressure to the static friction plate assembly according to a first pressure applied to the piston ring by the spring; and the static friction plate assembly and the movable friction plate assembly output a rotational torque to the brake shaft under the action of the second pressure.
  • the number of the static friction plate assemblies and the movable friction plate assemblies can be further adjusted according to the requirements of a product for the friction braking performance, and the product designs of the static friction plate assembly and the movable friction plate assembly can be serialized.
  • the static friction plates in the static friction plate assembly and the movable friction plate in the movable friction plate assembly are alternately arranged in sequence in order to further input a rotational torque to the brake shaft .
  • the spring may take one of various structural forms such as a leaf spring and a disc spring, which is not limited herein.
  • the spring is adjusted such that the deformation of the spring generates a first pressure applied to the piston ring, and the piston ring moves to apply a second pressure to the movable friction plate assembly .
  • the slewing control mechanism comprises:
  • a hydraulic control assembly for adjusting the amount of compression of the spring.
  • the slewing control mechanism is provided with the hydraulic control assembly for adjusting the amount of compression of the spring.
  • the piston ring is moved under the action of a first pressure from the spring and an action force generated by the hydraulic control assembly, and applies a second pressure to the movable friction plate assembly to further input a rotational torque to the brake shaft such that a torque is outputted from the brake shaft.
  • the action force generated by the hydraulic control assembly can be adjusted by adjusting the oil pressure of a hydraulic oil in the hydraulic control assembly.
  • the slewing control mechanism comprises:
  • an auxiliary electromagnetic circuit assembly for adjusting the amount of compression of the spring.
  • the slewing control mechanism is provided with the auxiliary electromagnetic circuit assembly for adjusting the amount of compression of the spring.
  • the piston ring is moved under the action of a first pressure from the spring and an action force generated by the auxiliary electromagnetic circuit assembly, and applies a second pressure to the movable friction plate assembly to further input a rotational torque to a brake shaft such that a torque is outputted from the brake shaft.
  • the action force generated by the auxiliary electromagnetic circuit assembly can be adjusted by adjusting related technical parameters such as current and voltage in the auxiliary electromagnetic circuit assembly.
  • a splined connection is formed between the first connecting portion and the connecting end of the brake shaft.
  • the splined connection is made between the first connecting portion of the at least one movable friction plate of the movable friction plate assembly and the connecting end of the brake shaft.
  • first connecting portion and the connecting end may be connected by mating an external involute spline groove with an internal involute spline groove, or by mating an internal involute spline groove with an external involute spline groove, and the specific connection form is not limited herein.
  • the slewing control mechanism further comprises: a first cylinder body and a second cylinder body;
  • the second cylinder body is provided with a second connecting portion connected to the static friction plate assembly; and the brake shaft, the static friction plate assembly, the movable friction plate assembly, the piston ring and the spring are sequentially arranged inside a cavity formed by the first cylinder body and the second cylinder body.
  • the slewing control mechanism is provided with a first cylinder body and a second cylinder body for facilitating the arrangement of the brake shaft, the static friction plate assembly, the movable friction plate assembly, the piston ring and the spring in the slewing control mechanism.
  • the first cylinder body and the second cylinder body also further facilitate the arrangement of the hydraulic control assembly or the auxiliary electromagnetic circuit assembly.
  • a splined connection is formed between the second connecting portion of the second cylinder body and the static friction plate assembly.
  • the second connecting portion of the second cylinder body and the static friction plate may be connected by mating an external involute spline groove with an internal involute spline groove, or by mating an internal involute spline groove with an external involute spline groove, and the specific connection form is not limited herein.
  • an embodiment of the present invention provides a slewing brake device, comprising a slewing control mechanism of any one of the embodiments of the first aspect, and a brake shaft external gear.
  • the brake shaft external gear is connected to the driving end of the brake shaft.
  • the slewing brake device drives the brake shaft external gear by means of the brake shaft to facilitate output of the output torque of the slewing brake device.
  • an embodiment of the present invention provides a pod propulsion apparatus, comprising: a strut, a propeller, a motor housing, a slewing unit and at least one slewing power plant, wherein the pod propulsion apparatus further comprises a slewing brake device of the second aspect.
  • the slewing brake device is adjusted to control the output torque of the brake shaft, so that it is possible to avoid the instantaneous impact on the output shaft of the slewing power plant due to insufficient braking torque of the slewing power plant in the marine power plant, thereby reducing the impact damage to the output shaft in the slewing power plant .
  • the brake shaft external gear of the slewing brake device is connected to a slewing bearing ring gear of the slewing unit .
  • the at least one slewing power plant is connected to the slewing bearing ring gear of the slewing unit.
  • the brake shaft external gear of the slewing brake device is linked to the slewing bearing ring gear of the slewing unit in a meshing manner.
  • the slewing brake device maintains a certain braking torque, such that gear teeth of the slewing power plant and the slewing bearing ring gear are pressed tightly to avoid frequent collisions between the gear teeth and the gear teeth generated when the load changes.
  • an embodiment of the present invention provides a marine power system comprising: a slewing control mechanism of any one of the embodiments of the first aspect; or a slewing brake device of the second aspect; or a pod propulsion apparatus of any one of the embodiments of the third aspect .
  • the slewing control mechanism comprises: a brake shaft, a static friction plate assembly, a movable friction plate assembly, a piston ring, and a spring.
  • the amount of compression of the spring is adjusted such that the piston ring is moved under the action of a first pressure from the spring and an action force generated by a hydraulic control assembly, and applies a second pressure to the static friction plate assembly to further input a rotational torque to the brake shaft such that an output torque from the brake shaft is adjusted accordingly.
  • Embodiments of the present invention further provide a slewing brake device and a pod propulsion apparatus.
  • the embodiments of the present invention have compact structures and are inexpensive, and can reduce the impact on a drive shaft of a slewing power plant in a marine power plant, thereby avoiding damage due to an excessive instantaneous load.
  • Fig. 1 is a schematic structural view of a slewing control mechanism in an embodiment of the present invention
  • Fig. 2 is a schematic structural view of a slewing brake device in an embodiment of the present invention
  • Fig. 3 is a schematic view of an application of a slewing brake device in an embodiment of the present invention.
  • Fig. 4 is a schematic view of the mechanical drive of an application of a slewing brake device in an embodiment of the present invention
  • Fig. 5 is a schematic structural view of a static friction plate of a slewing brake device in an embodiment of the present invention
  • Fig. 6 is a schematic structural view of a movable friction plate of a slewing brake device in an embodiment of the present invention
  • Fig. 7 is a schematic structural view of a pod propulsion apparatus in an embodiment of the present invention.
  • Fig. 8 is a schematic view showing the installation of a pod propulsion apparatus in an embodiment of the present invention .
  • a slewing brake device, a pod propulsion apparatus and a marine power system are provided in the embodiments of the present invention to solve the technical problem of damage to the output shaft of the slewing power plant due to the excessive instantaneous load in the prior art marine power system.
  • Fig. 1 shows a schematic structural view of a slewing control mechanism in an embodiment of the present invention, the slewing control mechanism comprising: a brake shaft 15 (not shown, see Fig. 2 for the specific structure of the brake shaft), a static friction plate assembly 17, a movable friction plate assembly 18, a piston ring 19 and a spring 20.
  • the brake shaft 15 comprises a connecting end 151 and a driving end 152.
  • the static friction plate assembly 17 comprises at least two static friction plates 171, 172.
  • the movable friction plate assembly 18 comprises at least one movable friction plate 181.
  • the at least one movable friction plate 181 is provided with a first connecting portion 1811 connected to the connecting end 151.
  • the at least two static friction plates 171, 172 of the static friction plate assembly 17 and the at least one movable friction plate 181 of the movable friction plate assembly 18 are alternately arranged in sequence .
  • the piston ring 19 comprises a first end face 191 and a second end face 192 opposite each other.
  • the first end face 191 abuts against the static friction plate assembly 17.
  • One end of the spring 20 abuts against the second end face 192 of the piston ring 19, and the other end of the spring 20 abuts against an inner wall of a first cylinder body 13.
  • the spring 20 is adjustable, and the piston ring 19 applies a second pressure to the static friction plate assembly 17 according to a first pressure applied to the piston ring by the spring 20; and the static friction plate assembly 17 and the movable friction plate assembly 18 output a torque to the brake shaft 15 under the action of the second pressure.
  • the number of the static friction plates and the movable friction plates in the static friction plate assembly 17 and the movable friction plate assembly 18 can be adjusted, and the specific number can be further adjusted according to the requirements of the slewing control mechanism for the friction braking performance, which is not specifically limited herein.
  • two static friction plates 171, 172, and one movable friction plate 181 are provided, the first end face 191 of the piston ring 19 abuts against the static friction plate 171 of the static friction plate assembly 17, and the static friction plate 171, the movable friction plate 181 and the static friction plate 172 are sequentially arranged such that the structure is formed in which the static friction plates in the static friction plate assembly 17 and the movable friction plate in the movable friction plate assembly 18 are alternately arranged in sequence to facilitate the conversion of the second pressure into the output torque.
  • the static friction plate assembly 17 comprises three or more static friction plates 171, 172, 173, and the movable friction plate assembly 18 comprises two or more movable friction plates 181, 182, the static friction plate 171, the movable friction plate 181, the static friction plate 172, the movable friction plate 182, and the static friction plate 173 are sequentially arranged after ensuring that the static friction plate 171 abuts against the first end face 191 of the piston ring 19.
  • the structure is formed in which there are static friction plates at two ends, and the static friction plates in the static friction plate assembly 17 and the movable friction plate in the movable friction plate assembly 18 are alternately arranged in sequence to facilitate the conversion of the second pressure into the output torque.
  • the adjustable design of the number of the static friction plates in the static friction plate assembly 17 and the movable friction plates in the movable friction plate assembly 18 facilitates further serialization of the product designs of the slewing control mechanism.
  • the slewing control mechanism may be further provided with a hydraulic control assembly 21 and an auxiliary hydraulic assembly 22, the auxiliary hydraulic assembly 22 cooperating with the hydraulic control assembly 21 to adjust the amount of compression of the spring 20.
  • the auxiliary hydraulic assembly 22 and the piston ring 19 construct a working chamber for the hydraulic control assembly 21 to output a control oil, to drive the movement of the piston ring 19.
  • the specific structural form of the auxiliary hydraulic assembly 22 is not limited herein .
  • the piston ring 19 is moved under the action of the first pressure of the spring 20 and an action force generated by the hydraulic control assembly 21, and applies a second pressure to the static friction plate assembly 17. Further, the static friction plate assembly 17 and the movable friction plate assembly 18 input a rotational torque to the brake shaft 15 under the action of the second pressure, such that the brake shaft 15 outputs a braking torque to the outside.
  • the action force generated by the hydraulic control assembly 21 can be adjusted by adjusting related parameters such as the pressure of a hydraulic oil in the hydraulic control assembly 21.
  • the adjustment of the amount of compression of the spring 20 by the slewing control mechanism may also be performed by providing an auxiliary electromagnetic circuit assembly 21a.
  • the auxiliary electromagnetic circuit assembly 21a replaces the hydraulic control assembly 21 and the auxiliary hydraulic assembly 22, and adjusts the first pressure applied by the piston ring 19 to the static friction plate assembly 17 and the movable friction plate assembly 18, to further adjust the output torque of the brake shaft 15.
  • the specific process of adjusting the amount of compression of the spring 20 by the auxiliary electromagnetic circuit assembly 21a is similar to the way in which the hydraulic control assembly 21 adjusts the amount of compression of the spring 20, and details are not described herein again.
  • the slewing control mechanism may be provided with a first cylinder body 13 and a second cylinder body 14.
  • a housing for arranging the brake shaft 15, the static friction plate assembly 17, the movable friction plate assembly 18, the piston ring 19, and the spring 20 of the slewing control mechanism is formed by providing the first cylinder body 13 and the second cylinder body 14.
  • the first cylinder body 13 and the second cylinder body 14 also further facilitate the arrangement of the hydraulic control assembly 21 or the auxiliary electromagnetic circuit assembly 21a.
  • Fig. 2 is a schematic structural view of a slewing brake device in an embodiment of the present invention.
  • the slewing brake device comprises a slewing control mechanism 91 and a brake shaft external gear 10.
  • the brake shaft external gear 10 is driven by the driving end 152 of the brake shaft 15 to realize the output of the output torque of the slewing brake device 9.
  • the first pressure generated by the spring 20 due to compression acts in conjunction with the action force generated by the hydraulic control assembly to urge the piston ring 19 to move.
  • the piston ring 19 applies the second pressure to the static friction plate assembly 17.
  • the static friction plate assembly 17 cooperates with the movable friction plate assembly 18 to output a braking torque to the brake shaft 15.
  • Fig. 3 is a schematic view of an application of a slewing brake device in an embodiment of the present invention
  • Fig. 4 is a schematic view of the mechanical drive of an application of a slewing brake device in an embodiment of the present invention.
  • the slewing power plant 8 and the slewing brake device 9 are respectively mounted to the power unit 7, and a drive shaft external gear 11 of the slewing power plant 8 is connected to a slewing bearing ring gear 12 in a meshing manner, to drive the power unit 7 to rotate.
  • the brake shaft external gear 10 connected to the brake shaft 15 of the slewing brake device 9 is connected to the slewing bearing ring gear 12 in a meshing manner, and the slewing brake device 9 provides a torque for deceleration braking or locking to the power unit 7 by means of gear meshing between the brake shaft external gear 10 and the slewing bearing ring gear 12.
  • the slewing brake device 9 undertakes the braking torque originally undertaken by the slewing power plant 8, reducing the load on the drive shaft of the slewing power plant 8.
  • the slewing power plant 8 drives the power unit 7 to slew by means of gear transmission, and the driving gear of the slewing power plant 8 is in close contact with the driven gear of the slewing bearing ring gear 12, so as to avoid the frequent collisions between gear teeth caused by the gap between the gears as the load changes.
  • the hydraulic control assembly 21 for adjusting the amount of compression of the spring 20 as an example, when the power unit 7 performs deceleration or locks the circumferential position, the oil pressure in the hydraulic control assembly 21 is lowered, and the first pressure generated by the spring 20 due to compression is less offset by the pressure in the hydraulic control assembly 21, so that the pressure acting on the piston ring 19 is relatively great; and the piston ring 19 moves downward to apply the second pressure to the movable friction plate assembly 18. Due to the increase in the positive pressure between the friction plates in the static friction plate assembly 17 and the movable friction plate assembly 18, the output torque of the slewing brake device 9 is transferred to the power unit 7 via the brake shaft external gear 10. The slewing brake device 9 undertakes part of the braking torque originally undertaken by a slewing motor, further reducing the load on a shaft of the slewing motor and protecting the shaft of the slewing motor.
  • Fig. 5 is a schematic structural view of a static friction plate of a slewing brake device provided in an embodiment of the present invention.
  • the static friction plate 171 of the static friction plate assembly 17 is machined with an external involute spline groove, and an inner cavity of the second cylinder body 14 is machined with an interior involute spline groove, the external involute spline groove mating with the interior involute spline groove to complete the transfer of torque.
  • connection between the static friction plate assembly 17 and the second cylinder body 14 may also use another structural form, which is not limited herein.
  • a splined connection is formed between the static friction plate assembly 17 and the lower cylinder body 14 to facilitate the second pressure applied by the piston ring 19 to output torque by means of the brake shaft 15.
  • Fig. 6 is a schematic structural view of a movable friction plate of a slewing brake device provided in an embodiment of the present invention.
  • the first connecting portion 1811 of the movable friction plate assembly 18 is an interior involute spline groove, and the connecting end 151 of the brake shaft 15 is machined with an exterior involute spline groove.
  • the connection between the movable friction plate assembly 18 and the brake shaft may also use another structural form, which is not limited herein.
  • a splined connection is formed between the movable friction plate assembly 18 and the connecting end 151 of the brake shaft 15 to facilitate the movable friction plate assembly 18 to output the second pressure outputted from the piston ring 19 by means of the brake shaft 15, to further drive the brake shaft external gear .
  • Fig. 7 is a schematic structural view of a pod propulsion apparatus in an embodiment of the present invention
  • Fig. 8 is a schematic view showing the installation of a pod propulsion apparatus provided in an embodiment of the present invention.
  • the pod propulsion apparatus 2 comprises: a strut 3, a propeller 4, a motor housing 6, two slewing power plants 8, a slewing unit 7, and a slewing brake device 9.
  • the pod propulsion apparatus 2 is mounted outside a hull 1 to provide thrust to the hull 1.
  • the pod propulsion apparatus 2 comprises a power unit composed of a strut 3, a propeller 4, and a motor housing 6, to provide power for the navigation of the ship; and the slewing unit 7 is fixed to the hull and can drive the power unit to slew circumferentially by means of the slewing power plant.
  • the power unit is connected to the slewing unit via a strut end 5.
  • the amount of the output torque of the brake shaft 15 is further controlled, so that it is possible to avoid the instantaneous impact on the output shaft of the slewing power plant 8 due to insufficient braking torque of the slewing power plant in the marine power plant, thereby reducing the impact damage to the output shaft in the slewing power plant 8.
  • the number of the slewing power plants 8 is not limited to two, and the number of the slewing brake devices 9 can be further adjusted according to requirements, which is not limited herein.
  • the brake shaft external gear 10 of the slewing brake device 9 is connected to the slewing bearing ring gear 12 of the slewing unit 7.
  • One slewing power plant 8 is connected to the slewing bearing ring gear 12 of the slewing unit 7.
  • the brake shaft external gear 10 of the slewing brake device 9 meshes with the slewing bearing ring gear 12 of the slewing unit 7.
  • the slewing brake device 9 maintains a certain braking torque, such that gear teeth of the slewing power plant 8 and the slewing bearing ring gear 12 are pressed tightly to further avoid frequent collisions between the gear teeth and the gear teeth generated when the load changes.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

La présente invention concerne un mécanisme de commande de pivotement qui comprend : un arbre de frein (15), un ensemble plaque de friction statique (17), un ensemble plaque de friction mobile (18), une bague de piston (19) et un ressort (20). La quantité de compression du ressort est ajustée, de sorte que la bague de piston soit déplacée sous l'action d'une première pression provenant du ressort et d'une force d'action produite par un ensemble de commande hydraulique (21) et applique une seconde pression à l'ensemble plaque de friction statique pour fournir en outre un couple de rotation à l'arbre de frein, de sorte qu'un couple de sortie de l'arbre de frein soit ajusté en conséquence. Les modes de réalisation ont des structures compactes et sont peu coûteux et peuvent réduire l'impact sur un arbre d'entraînement d'une centrale électrique tournante dans une centrale électrique marine, ce qui permet d'éviter des dommages dus à une charge instantanée excessive.
PCT/EP2019/069156 2018-07-17 2019-07-16 Mécanisme de commande de pivotement, dispositif de frein, appareil de propulsion de nacelle et système d'alimentation marin WO2020016247A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810783823.4 2018-07-17
CN201810783823.4A CN110725881B (zh) 2018-07-17 2018-07-17 回转控制机构、制动装置、吊舱推进器及船舶动力系统

Publications (1)

Publication Number Publication Date
WO2020016247A1 true WO2020016247A1 (fr) 2020-01-23

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PCT/EP2019/069156 WO2020016247A1 (fr) 2018-07-17 2019-07-16 Mécanisme de commande de pivotement, dispositif de frein, appareil de propulsion de nacelle et système d'alimentation marin

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US20040074707A1 (en) * 2002-10-21 2004-04-22 Sauer-Danfoss Holding A/S Brake appliance for gerotor motors
DE202015005568U1 (de) * 2014-08-21 2015-08-25 Caterpillar Inc. (n.d.Ges.d. Staates Delaware) Wartbares Lenkbremssystem für eine Schiffspropellergondel
CN106979261A (zh) * 2017-04-28 2017-07-25 徐工集团工程机械有限公司 减速机
WO2018002414A1 (fr) * 2016-07-01 2018-01-04 Abb Oy Unité de propulsion dotée d'un agencement de direction

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DE102006001893B4 (de) * 2006-01-14 2023-05-11 Zf Friedrichshafen Ag Parkbremse für ein Kraftfahrzeug
US8631913B2 (en) * 2007-10-15 2014-01-21 Deere & Company Brake assembly for final drive

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Publication number Priority date Publication date Assignee Title
JPS5973634A (ja) * 1982-10-20 1984-04-25 Okakakuhei Shoten:Kk スプリング制動式固定ブレ−キ
WO2000015495A1 (fr) * 1998-09-14 2000-03-23 Abb Azipod Oy Agencement et procede de mise en rotation d'une unite de propulsion
US20040074707A1 (en) * 2002-10-21 2004-04-22 Sauer-Danfoss Holding A/S Brake appliance for gerotor motors
DE202015005568U1 (de) * 2014-08-21 2015-08-25 Caterpillar Inc. (n.d.Ges.d. Staates Delaware) Wartbares Lenkbremssystem für eine Schiffspropellergondel
WO2018002414A1 (fr) * 2016-07-01 2018-01-04 Abb Oy Unité de propulsion dotée d'un agencement de direction
CN106979261A (zh) * 2017-04-28 2017-07-25 徐工集团工程机械有限公司 减速机

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