CN104487341A - Steering gear and ship comprising same - Google Patents
Steering gear and ship comprising same Download PDFInfo
- Publication number
- CN104487341A CN104487341A CN201380039053.8A CN201380039053A CN104487341A CN 104487341 A CN104487341 A CN 104487341A CN 201380039053 A CN201380039053 A CN 201380039053A CN 104487341 A CN104487341 A CN 104487341A
- Authority
- CN
- China
- Prior art keywords
- rudderpost
- gear
- steering engine
- bearing
- anchor shaft
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/26—Steering engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/18—Transmitting of movement of initiating means to steering engine
- B63H25/20—Transmitting of movement of initiating means to steering engine by mechanical means
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
- B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
- B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
- B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
- B60T1/062—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels acting on transmission parts
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H25/00—Steering; Slowing-down otherwise than by use of propulsive elements; Dynamic anchoring, i.e. positioning vessels by means of main or auxiliary propulsive elements
- B63H25/06—Steering by rudders
- B63H25/08—Steering gear
- B63H25/14—Steering gear power assisted; power driven, i.e. using steering engine
- B63H25/34—Transmitting of movement of engine to rudder, e.g. using quadrants, brakes
-
- 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
- F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
- F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
-
- 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
- F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
- F16D63/002—Brakes with direct electrical or electro-magnetic actuation
-
- 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
- F16D65/00—Parts or details
- F16D65/02—Braking members; Mounting thereof
- F16D65/12—Discs; Drums for disc brakes
-
- 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
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/289—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two or more coaxial and identical sets of orbital gears, e.g. for distributing torque between the coaxial sets
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ocean & Marine Engineering (AREA)
- Transportation (AREA)
- Retarders (AREA)
- Braking Arrangements (AREA)
Abstract
Provided are steering gear whereby the rotation of a rudder shaft is braked, and it is possible to appropriately fix a rotation location of the rudder shaft, as well as a ship comprising same. Steering gear which drives a rudder of a ship via a rudder shaft (1) which is coupled to the rudder comprises: a rudder shaft gear (2) which is anchored to an end part of the rudder shaft (1); a drive gear (6c) which transmits drive power to the rudder shaft gear (2) and rotates the rudder shaft (1); a drive source (6a) which drives the drive gear (6c); and an electromagnetic brake (70) which brakes the rotation of the rudder shaft (1), and anchors the rotation location of the rudder shaft (1) in a prescribed location.
Description
Technical field
The present invention relates to a kind of steering engine and possess the boats and ships of this steering engine.
Background technology
All the time, as the steering engine making the rudder of boats and ships carry out action, there will be a known the steering engine of the fluid pressure types such as the steering engine of Lei Boxun slip (Rapson-slide) type.Although the steering engine of fluid pressure type has the advantage that can apply large rotational force to the rudderpost linked with rudder, electric power is converted to hydraulic pressure this respect utilizing electro-motor etc. and there is energy conversion efficiency and to be deteriorated this shortcoming.In addition, also there is working oil and may externally spill and the shortcoming causing marine pollution in the steering engine of fluid pressure type.
In view of the shortcoming of the steering engine of fluid pressure type as above, propose the steering engine of other modes different from fluid pressure type.
Such as, Patent Document 1 discloses a kind of steering engine of gear type, the steering engine of this gear type is via the miniature gears being installed on electrical motor, and the gear making to be located on the pivoted loop fixed at the rudderpost of boats and ships rotates.
At first technical literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2007-8189 publication
Summary of the invention
The problem that invention will solve
Such as, but in the steering engine disclosed in patent documentation 1, there are the following problems.
Although the steering engine disclosed in patent documentation 1 has the mechanism making rudderpost rotate, not there is the mechanism of braking rudderpost, therefore can not brake fully the rotation of rudderpost.
In addition, compared with the steering engine of fluid pressure type, the steering engine of gear type is owing to having backlash (backlash; Play between the flank of tooth), be therefore difficult to the position of rotation of rudderpost and the position of rotation of rudder that links with this rudderpost to be fixed on correct position.
In addition, inferior in the situation applying some external force to rudder, the position of rotation of rudderpost and the position of rotation of rudder linked with this rudderpost likely can change.
The present invention completes in view of such situation, and its object is to provide a kind of can brake the rotation of rudderpost thus suitably fix the steering engine of the position of rotation of rudderpost and possess the boats and ships of this steering engine.
For solving the scheme of problem
In order to achieve the above object, the present invention adopts following scheme.
Steering engine of the present invention drives via the rudderpost linked with this rudder the rudder of boats and ships, and it is characterized in that possessing: rudderpost gear, it is fixed on the end of described rudderpost; Driven wheel, it, to described rudderpost gear transmission propulsive effort, makes described rudderpost rotate; Drive source, it drives described driven wheel; Detent, it is braked the rotation of described rudderpost, and the position of rotation of described rudderpost is fixed on assigned position.
According to steering engine of the present invention, the propulsive effort of drive source, from driven wheel to rudderpost gear transmission, makes rudderpost rotate.In addition, braking the rotation of rudderpost owing to possessing and the position of rotation of rudderpost to be fixed on the detent of assigned position, therefore can provide a kind of can carry out braking to the rotation of rudderpost and suitably fix the steering engine of the position of rotation of rudderpost and possess the boats and ships of this steering engine.
In addition, the feature of the steering engine of the 1st aspect of the present invention is, described drive source is electro-motor, and described detent is the magnet stopper be connected with the S. A. of described electro-motor.Thus, the rotation as the electro-motor of drive source is braked by magnet stopper, and the rotation of the rudderpost caused from the propulsive effort transmission of drive source is also braked, thus the position of rotation of rudderpost can be fixed on assigned position.
In addition, the feature of the steering engine of the 2nd aspect of the present invention is to possess: anchor shaft gear, and itself and described rudderpost are arranged with having same axis, and are fixed on the end of the anchor shaft fixed in hull side; Bearing, it is arranged to rotate around described anchor shaft, and is provided with bearing gear in periphery; Brake disc, itself and described bearing link, described driven wheel is to described bearing gear transmission propulsive effort, this bearing gear is rotated around described anchor shaft, thus to propulsive effort described in described rudderpost gear transmission, described detent is braked via the rotation of described brake disc to described bearing, and the position of rotation of described rudderpost is fixed on described assigned position.
Thus, the rotation of the bearing that the propulsive effort transmission of drive source causes is braked by detent via the brake disc linked with bearing, and the rotation of the rudderpost caused via bearing transmission of drive force is also braked.Further, the position of rotation of rudderpost can be fixed on assigned position.
In addition, the feature of the steering engine of the 3rd aspect of the present invention is to possess limiting unit, and described limiting unit is fixed on described rudderpost, by be fixed on the limiting member of hull side to touching the rotating range limiting described rudderpost.Thus, even if when the rotation of rudderpost suitably could not be braked by detent for some reason, the rotating range of rudderpost also suitably can be limited.
In the steering engine of the 2nd aspect of the present invention, also can be following structure: described bearing has multiple planet axis, described multiple planet axis is respectively by with the first planet gear of described anchor shaft gears meshing with support as rotatable with the second planetary wheel of described rudderpost gears meshing, and the operating pitch circle radius of described rudderpost gear of described second planetary wheel engagement is different from the operating pitch circle radius of the described anchor shaft gear of described first planet gears meshing.
By such structure, the propulsive effort of drive source is from driven wheel to bearing gear transmission, and the second planetary wheel that the multiple planet axis had from bearing support is to rudderpost gear transmission propulsive effort.Like this, by adopting the structure of dividing two stages to transmit to rudderpost the propulsive effort of drive source, and make each gear realize miniaturization, consequently, steering engine realizes miniaturization.In addition, because the operating pitch circle radius of rudderpost gear of the second planetary wheel engagement is different from the operating pitch circle radius of the anchor shaft gear of first planet gears meshing, rudderpost relatively rotates relative to anchor shaft around the rotation of anchor shaft therefore to correspond to bearing.Like this, drive source is via the gear in two stages to rudderpost transmission of drive force, and rudderpost relatively rotates relative to anchor shaft, therefore, it is possible to provide the steering engine driven rudder with high reduction ratio.
In above structure, also described rudderpost gear, described anchor shaft gear, described first planet gear and described second planetary modulus can be made equal, and the summation of the number of teeth of described anchor shaft gear and described first planet gear equals the summation of described rudderpost gear and the described second planetary number of teeth.Thus, when the gear using modulus equal, first planet gear and the second planetary wheel can suitably be supported by same planet axis.
In the steering engine of the 2nd aspect of the present invention, also can possess multiple described drive source, described multiple drive source respectively via described driven wheel to described bearing gear transmission propulsive effort.Thus, the propulsive effort transmitted to bearing strengthens, and when a certain drive source et out of order, other drive sources also can be utilized to bearing transmission of drive force.
In addition, the feature of boats and ships of the present invention is, possesses aforesaid steering engine.
Invention effect
According to the present invention, can provide a kind of can carry out braking to the rotation of rudderpost and suitably fix the steering engine of the position of rotation of rudderpost and possess the boats and ships of this steering engine.
Accompanying drawing explanation
Fig. 1 is the partial, longitudinal cross-sectional of the steering engine of the first embodiment.
Fig. 2 is that the A-A of the steering engine shown in Fig. 1 is to looking sectional elevation.
Fig. 3 is that the B-B of the steering engine shown in Fig. 1 is to looking sectional elevation.
Fig. 4 is rudderpost gear and the second planetary partial enlarged drawing of the first embodiment.
Fig. 5 is the anchor shaft gear of the first embodiment and the partial enlarged drawing of first planet gear.
Fig. 6 is that the C-C of the steering engine shown in Fig. 1 is to looking sectional elevation.
Fig. 7 is the actuating device of the first embodiment and the details drawing of magnet stopper.
Fig. 8 is the partial, longitudinal cross-sectional of the steering engine of the variation of the first embodiment.
Fig. 9 is that the C-C of the steering engine shown in Fig. 8 is to looking sectional elevation.
Figure 10 is the partial, longitudinal cross-sectional of the steering engine of the second embodiment.
Figure 11 represents the brake disc of the second embodiment and the figure of brake clamp.
Figure 12 is the partial, longitudinal cross-sectional of the steering engine of the 3rd embodiment.
Detailed description of the invention
(the first embodiment)
Below, by Fig. 1 ~ Fig. 3, the steering engine 100 of the first embodiment is described.Fig. 1 is the partial, longitudinal cross-sectional of the steering engine 100 of the first embodiment.Fig. 2 is that the A-A of the steering engine 100 shown in Fig. 1 is to looking sectional elevation.Fig. 3 is that the B-B of the steering engine 100 shown in Fig. 1 is to looking sectional elevation.
As shown in Figure 1, the steering engine 100 of the present embodiment device that to be rudder (not shown) to boats and ships drive via the rudderpost 1 linked with rudder.Steering engine 100 possesses: rudderpost 1, rudderpost gear 2, anchor shaft 3, anchor shaft gear 4, bearing (carrier) 5 and actuating device 6.In addition, the boats and ships of present embodiment are that screw rod by being driven by combustion engine (not shown) obtains propulsive force and carries out the boats and ships that advance.And in the boats and ships of present embodiment, steering engine 100 is fixed on hull, by utilizing steering engine 100 pairs of rudders to operate, the direct of travel of boats and ships at random can be controlled.
Rudderpost 1 is the component of the cylindrical shape configured along the center shaft X of vertical, and its bottom and rudder link.In addition, rudderpost gear 2 is fixed with in the upper end of rudderpost 1.Rudderpost gear 2 is such as by bolt etc. and link fastening with rudderpost 1, and when rudderpost gear 2 rotates, the rudderpost 1 being fixed on rudderpost gear 2 also rotates.Therefore, by the rotation of rudderpost gear 2, the rudder linked with rudderpost 1 rotates centered by center shaft X.
Anchor shaft 3 is the components of the tubular having same axis with rudderpost 1 and arrange, the seat stand 7 that its bottom is fixed on as hull side by clamp structures such as bolts.In addition, in the upper end of anchor shaft 3, by clamp structures such as bolts, anchor shaft gear 4 is fixed.The diameter of the inner circumferential of anchor shaft 3 is greater than the diameter of the periphery of rudderpost 1.
Between rudderpost gear 2 and anchor shaft gear 4, be configured with the bearing shell 40 that the load of the axis of rudderpost 1 is supported.Bearing shell 40 is fixed on the upper surface of the peripheral end of anchor shaft gear 4, connects with the lower surface of the peripheral end of rudderpost gear 2.
On the outside face of anchor shaft 3, be fitted together to inner ring inside face to the supporting bearing 8 that the load of bearing 5 supports to be pressed into state.In addition, on the outside face of anchor shaft 3, to be pressed into the inside face that state is fitted together to annular component 9, annular component 9 configures in the below of supporting bearing 8.The lower end of annular component 9 is supported by seat stand 7, and the upper end of annular component 9 connects with the inner ring lower surface of supporting bearing 8.
In the stage portion 5a being located at bearing 5, to be pressed into the outer ring outside face that state is fitted together to supporting bearing 8.Supporting bearing 8 is antifriction-bearing boxs, and as previously mentioned, its inner ring inside face is entrenched on the outside face of anchor shaft 3 with press-in state.Thus bearing 5 is arranged to rotate around anchor shaft 3.
The load of bearing 5 is applied on the outer ring upper surface of supporting bearing 8 via stage portion 5a.The load putting on the bearing 5 on the outer ring upper surface of supporting bearing 8 passes to annular component 9 via the inner ring lower surface of supporting bearing 8.Like this, supporting bearing 8 possesses and to support the load of bearing 5 and to be set to by bearing 5 to rotate this function around anchor shaft 3.
Bearing 5 is cross sectional shapes of center shaft X-direction is circular component, is arranged to rotate around anchor shaft 3.Bearing 5 is provided with bearing gear 5b on the outer peripheral face of the radial direction foreign side of stage portion 5a.Bearing gear 5b is arranged by processing the outer peripheral face of bearing 5.
Bearing gear 5b is engaged with driven wheel 6c, and described driven wheel 6c links with drive source 6a via axle drive shaft 6b.As shown in Figure 7, drive source 6a is made up of electro-motor 6d and retarder 6e, and the rotational force (propulsive effort) of the S. A. of electro-motor 6d passes to retarder 6e via coupling 6f.Retarder 6e makes the rotational force of the S. A. of electro-motor 6d slow down and transmit to axle drive shaft 6b via bevel-gear sett 6g, 6h, and via axle drive shaft 6b, driven wheel 6c is rotated.Driven wheel 6c is to bearing gear 5b transmission of drive force thus bearing 5 is rotated around anchor shaft 3.Drive source 6a drives driven wheel 6c and to bearing gear 5b transmission of drive force.Drive source 6a is arranged on the seat stand 7 being provided with anchor shaft 3.
The S. A. of electro-motor 6d is linked with magnet stopper 70 via coupling 72, and the rotation of electro-motor 6d is braked by magnet stopper 70.Magnet stopper 70 refers to and utilizes the S. A. of electromagnetic force to electro-motor 6d by producing to excitation coil (not shown) energising to brake, thus keeps the device of S. A. at the position of rotation of regulation.The "on" position of excitation coil is by switching from the control command of control part (not shown).In the present embodiment, as magnet stopper 70, use the magnet stopper being carried out the excited work type of action (braking) by the energising carried out to excitation coil, but carry out the magnet stopper of the non-excited work type of action (braking) when also can be used in the energising cut off to excitation coil.
As shown in Figure 1, the steering engine 100 of present embodiment possesses actuating device 60.The propulsive effort of drive source 60a, by the driven wheel 60c linked via axle drive shaft 60b, transmits to bearing gear 5b by actuating device 60.It should be noted that, the structure of actuating device 60 is same with the structure of actuating device 6, thus omits the description.In addition, the S. A. of electro-motor 60d (not shown) is linked with magnet stopper 71 via coupling 73, the rotation of electro-motor 60d (not shown) is braked by magnet stopper 71.Magnet stopper 71 is same structures with aforesaid magnet stopper 70, thus omits the description.
Be provided with two actuating devices (drive source) in the present embodiment, but also can adopt the structure that the wherein actuating device of either party is only set.
Bearing 5 has four planet axis 30a, 30b, 30c, 30d.Fig. 1 is the partial, longitudinal cross-sectional of steering engine 100, shows planet axis 30a and planet axis 30b.Planet axis 30a is the axis-shaped component that top and bottom are individually fixed in bearing 5.Be provided with inner ring with chimeric two antifriction-bearing boxs (not shown) of press-in state at planet axis 30a, planetary wheel 10a and planetary wheel 20a is embedded in the outer ring of two antifriction-bearing boxs with press-in state.Like this, planet axis 30a is by the planetary wheel 10a engaged with anchor shaft gear 4 (first planet gear) and the planetary wheel 20a (the second planetary wheel) that engages with rudderpost gear 2.
Equally, planetary wheel 10b and planetary wheel 20b supports as rotatable by planet axis 30b.Equally, planetary wheel 10c (not shown) and planetary wheel 20c (not shown) supporting is rotatable by planet axis 30c (not shown).Equally, planetary wheel 10d (not shown) and planetary wheel 20d (not shown) supporting is rotatable by planet axis 30d (not shown).Planetary wheel 10a ~ 10d (first planet gear) engages with anchor shaft gear 4, and planetary wheel 20a ~ 20d (the second planetary wheel) engages with rudderpost gear 2.
Fig. 2 is that the A-A of the steering engine 100 shown in Fig. 1 is to looking sectional elevation.As shown in Figure 2, planetary wheel 20a ~ 20d (the second planetary wheel) is configured to separate the interval of each 90 ° respectively in four positions of the circumferencial direction of rudderpost gear 2 and engages with rudderpost gear 2.Along with bearing 5 rotates around anchor shaft 3, planetary wheel 20a ~ 20d still maintains the interval of each 90 ° respectively and rotates relative to anchor shaft 3.
Fig. 3 is that the B-B of the steering engine 100 shown in Fig. 1 is to looking sectional elevation.As shown in Figure 3, planetary wheel 10a ~ 10d (first planet gear) is configured to separate the interval of each 90 ° respectively in four positions of the circumferencial direction of anchor shaft gear 4 and engages with anchor shaft gear 4.Along with bearing 5 rotates around anchor shaft 3, planetary wheel 10a ~ 10d still maintains the interval of each 90 ° respectively and rotates relative to anchor shaft 3.
At this, the velocity ratio (reduction ratio) of the propulsive effort transmitted from driven wheel 6c to rudderpost gear 2 is in the present embodiment described.In the following description, when anchor shaft gear 4 engages with planetary wheel 10a ~ 10d, the modulus of anchor shaft gear 4 is equal with the modulus of planetary wheel 10a ~ 10d.In addition, when rudderpost gear 2 engages with planetary wheel 20a ~ 20d, the modulus of rudderpost gear 2 is equal with the modulus of planetary wheel 20a ~ 20d.At this, modulus refers to the value that pitch circle diameter obtains divided by the number of teeth.
The steering engine 100 of present embodiment meets following conditional.
i0＝(Zb·Zd)/(Za·Zd) (1)
i1＝(1-i0)/i0 (2)
i2＝Zf/Ze (3)
i3＝i1·i2 (4)
Za+Zb＝Zc+Zd (5)
Za≠Zd (6)
Zb≠Zc (7)
At this, Za: the number of teeth of anchor shaft gear 4, Zb: the number of teeth of planetary wheel 10a ~ 10d, Zc: the number of teeth of planetary wheel 20a ~ 20d, Zd: the number of teeth of rudderpost gear 2, Ze: the number of teeth of driven wheel 6c, Zf: the number of teeth, the i1 of bearing gear 5b: velocity ratio (reduction ratio), the i2 of bearing 5 and rudderpost 1: the velocity ratio (reduction ratio) of driven wheel 6c and bearing 5, i3: the velocity ratio (reduction ratio) of driven wheel 6c and rudderpost 1.
From above conditional, the reduction ratio of driven wheel 6c and rudderpost 1 is determined according to tooth number Z a, the tooth number Z b of planetary wheel 10a ~ 10d of anchor shaft gear 4, tooth number Z c, the tooth number Z d of rudderpost gear 2 of planetary wheel 20a ~ 20d, the tooth number Z f of the tooth number Z e of driven wheel 6c and bearing gear 5b.
It should be noted that, the number of teeth of planetary wheel 10a ~ 10d is identical respectively, and Zb refers to this identical number of teeth.In addition, the number of teeth of planetary wheel 20a ~ 20d is identical respectively, and Zc refers to this identical number of teeth.
Conditional (5) rudderpost 1 and anchor shaft 3 can be arranged with having same axis and the condition that supported by planet axis 30 (30a ~ 30d) of planetary wheel 10 (10a ~ 10d) and planetary wheel 20 (20a ~ 20d).By meeting such condition, rudderpost 1 can be made to equal the axle base of anchor shaft 3 and planet axis 30 with the axle base of planet axis 30.
Conditional (6) and (7) correspond to bearing 5 around the rotation of anchor shaft 3 for making rudderpost 1 relatively carry out the condition rotated relative to anchor shaft 3.When conditional (6) and (7) all do not meet, the tooth number Z a of anchor shaft gear 4 is equal with the tooth number Z d of rudderpost gear 2, and the tooth number Z b of planetary wheel 10 is equal with the tooth number Z c of planetary wheel 20.In this case, although planetary wheel 20 rotates in the circumferential around rudderpost gear 2, rudderpost gear 2 relatively can not rotate relative to anchor shaft gear 4, and keeps static.By the formula of satisfying condition (6) and (7), bearing 5 can be corresponded to and around the rotation of anchor shaft 3, rudderpost 1 is relatively rotated relative to anchor shaft 3.
Above, the situation that the modulus of the anchor shaft gear 4 when anchor shaft gear 4 engages with planetary wheel 10a ~ 10d is equal with the modulus of planetary wheel 10a ~ 10d is described.In addition, the situation that the modulus of the rudderpost gear 2 when rudderpost gear 2 engages with planetary wheel 20a ~ 20d is equal with the modulus of planetary wheel 20a ~ 20d is described.But, also can apply present embodiment when their modulus is different.Steering engine 100 in such cases replaces aforesaid conditional (5) ~ (7) and meets following conditional (8) ~ (10).
r1+r2＝r4+r5 (8)
r1≠r3 (9)
r2≠r4 (10)
At this, as shown in Figures 4 and 5, r1: distance, r2 from the center O1 of rudderpost gear 2 to point of engagement P1: distance, r3 from the center O2 of planetary wheel 20a ~ 20d to point of engagement P1: distance, r4 from the center O3 of anchor shaft gear 4 to point of engagement P2: the distance from the center O4 of planetary wheel 10a ~ 10d to point of engagement P2.
Conditional (8) rudderpost 1 and anchor shaft 3 can be arranged with having same axis and the condition that supported by planet axis 30 (30a ~ 30d) of planetary wheel 10 (10a ~ 10d) and planetary wheel 20 (20a ~ 20d).By meeting such condition, rudderpost 1 can be made to equal the axle base of anchor shaft 3 and planet axis 30 with the axle base of planet axis 30.
Conditional (9) is the conditional representing that the operating pitch circle radius r 1 of the rudderpost gear 2 that planetary wheel 20 (20a ~ 20d) engages is different from the operating pitch circle radius r 3 of the anchor shaft gear 4 that planetary wheel 10 (10a ~ 10d) engages.In addition, conditional (10) is the conditional representing that the operating pitch circle radius r 2 of the planetary wheel 20 (20a ~ 20d) that rudderpost gear 2 engages is different from the operating pitch circle radius r 4 of the planetary wheel 10 (10a ~ 10d) that anchor shaft gear 4 engages.
Conditional (9) and (10) correspond to bearing 5 around the rotation of anchor shaft 3 for making rudderpost 1 relatively carry out the condition rotated relative to anchor shaft 3.When conditional (9) and (10) all do not meet, distance r1 from the center O1 of rudderpost gear 2 to point of engagement P1 is equal to the distance r3 of point of engagement P2 with the center O3 from anchor shaft gear 4, and the distance r2 from the center O2 of planetary wheel 20a to point of engagement P1 is equal to the distance r4 of point of engagement P2 with the center O4 from planetary wheel 10a.In this case, although planetary wheel 20 rotates in the circumferential around rudderpost gear 2, rudderpost gear 2 relatively can not rotate relative to anchor shaft gear 4, and keeps static.By the formula of satisfying condition (9) and (10), bearing 5 can be corresponded to and around the rotation of anchor shaft 3, rudderpost 1 is relatively rotated relative to anchor shaft 3.
Then, use Fig. 1 and Fig. 6, illustrate in the present embodiment to the structure that the rotating range of rudderpost 1 limits.Fig. 6 is that the C-C of the steering engine 100 shown in Fig. 1 is to looking sectional elevation.
Debooster 80 (80a, 80b) is the component analysing and observe observation circular being fixed on rudderpost 1, and the direction that the center shaft X with rudderpost 1 is orthogonal extends.Limiting member 90 (90a, 90b) is being fixed with as on the seat stand 95 of hull side.The position that limiting member 90a is fixed on when rudderpost 1 deasil have rotated predetermined angular α from reference position, limiting member 90a and debooster 80a occurs to touching.In addition, the position that limiting member 90b is fixed on when rudderpost 1 has rotated in the counterclockwise predetermined angular α from reference position, limiting member 90b and debooster 80b occurs to touching.
Like this, debooster 80 (limiting unit) is fixed on rudderpost 1, make it support and touch in the limiting member 90 fixing in hull side, thus, the rotating range of rudderpost 1 is constrained to the rotating range (-α ° ~+α °) of regulation relative to reference position.As the rotating range of regulation, suitably can set according to the kind of boats and ships, performance etc., such as, set the scope of-35 ° ~+35 ° relative to reference position.
Like this, steering engine 100 according to the present embodiment, the propulsive effort of drive source 6a, 60a transmits from driven wheel 6c, 60c to rudderpost gear 2, and rudderpost 1 is rotated.In addition, owing to possessing the magnet stopper 70,71 braked the rotation of rudderpost 1 and the position of rotation of rudderpost 1 is fixed on assigned position, can brake the rotation of rudderpost 1 and the steering engine 100 that the position of rotation of rudderpost 1 is suitably fixed and the boats and ships possessing this steering engine 100 therefore, it is possible to provide a kind of.
In addition, in the steering engine 100 of present embodiment, drive source 6a, 60a are electro-motor 6d, 60d, and detent is the magnet stopper 70,71 be connected with electro-motor 6d, 60d.Thus, rotation as electro-motor 6d, 60d of drive source 6a, 60a is braked by magnet stopper 70,71, and the rotation of the rudderpost 1 caused from the propulsive effort transmission of drive source 6a, 60a is also braked, thus the position of rotation of rudderpost 1 can be fixed on assigned position.
In addition, the steering engine of present embodiment possesses debooster 80a, 80b (limiting unit), described debooster 80a, 80b be fixed on rudderpost 1 and by be fixed on limiting member 90a, 90b of hull side to touching the rotating range limiting rudderpost 1.Thus, even if when the rotation of rudderpost 1 suitably could not be braked by magnet stopper 70,71 for some reason, the rotating range of rudderpost 1 can also suitably be limited.
In addition, in the steering engine 100 of present embodiment, possess multiple drive source, multiple drive source 6a, 60a are respectively via the structure of driven wheel 6c to bearing gear 5b transmission of drive force.Thus, the propulsive effort transmitted to bearing 5 strengthens, even and if when a certain drive source et out of order, other drive sources also can be utilized to bearing 5 transmission of drive force.
Then, use Fig. 8 and Fig. 9, the variation of the first embodiment is described.
Debooster 80 shown in Fig. 6 is provided at the structure at two positions of rudderpost 1.In contrast, as shown in Figure 8, this variation only arranges debooster 81 at rudderpost 1 position.Fig. 9 is that the C-C of the steering engine 100 ' shown in Fig. 8 is to looking sectional elevation.
Debooster 81 is the components analysing and observe observation circular being fixed on rudderpost 1, and the direction that the center shaft X with rudderpost 1 is orthogonal extends.Limiting member 91 (91a, 91b) is being fixed with as on the seat stand 95 of hull side.The position that limiting member 91a is fixed on when rudderpost 1 deasil have rotated predetermined angular α from reference position, limiting member 91a and debooster 81 occur to touching.In addition, the position that limiting member 91b is fixed on when rudderpost 1 has rotated in the counterclockwise predetermined angular α from reference position, limiting member 91b and debooster 81 occur to touching.
Like this, debooster 81 (limiting unit) is fixed on rudderpost 1, make it support and touch in fixing limiting member 91a, the 91b of the seat stand 95 in hull side, thus the rotating range of rudderpost 1 is constrained to the rotating range (-α ° ~+α °) of regulation relative to reference position.As the rotating range of regulation, suitably can set according to the kind of boats and ships, performance etc., such as, set the scope of-35 ° ~+35 ° relative to reference position.
(the second embodiment)
Then, use Figure 10, Figure 11, the steering engine 200 of the second embodiment is described.Figure 10 is the partial, longitudinal cross-sectional of the steering engine 200 of the second embodiment.Figure 11 represents the brake disc of the second embodiment and the figure of brake equipment.
The steering engine 100 of the first embodiment is braked by the rotation of magnet stopper 70, the 71 pairs of rudderposts 1 linked with the S. A. of electro-motor 6d, the 60d as drive source.In contrast, the steering engine 200 of the second embodiment is braked by the rotation of the brake disc 75 that links with bearing 5 and brake equipment (brake device) 210 pairs of rudderposts 1.
It should be noted that, the second embodiment is the variation of the first embodiment, and except the situation of following special version, other structures are identical with the first embodiment, therefore omit the following description.
As shown in Figures 10 and 11, brake disc 75 is thickness constant and overlooks the component into ring-type.Brake disc 75 is such as metal, is linked with bearing 5 by bolt 79.Figure 10 illustrates bolt 79a and bolt 79b, but be configured with other bolts on multiple positions of the circumferencial direction of bearing 5.As shown in Figure 10, brake clamp 76a is configured to the periphery of clamping brake disc 75.A pair caliper opening piston 77a, 77b is provided with in brake clamp 76a.The front end of caliper opening piston 77a, 77b is configured with slipper 78a, 78b respectively.
Caliper opening piston 77a, 77b indicate according to the braking from control part (not shown), slipper 78a, 78b are extruded relative to brake disc 75.The brake disc 75 clamped by slipper 78a, 78b is braked by the friction force produced between slipper 78a, 78b, weakens the rotational force of the bearing 5 linked with brake disc 75.The bearing 5 that rotational force reduces due to the braking of brake equipment 210 finally stops the rotation, and is fixed on assigned position.In addition, bearing 5 is via planetary wheel 20a to rudderpost 1 transmission of drive force, and therefore when the rotation of bearing 5 stops, the position of rotation of rudderpost is fixed on assigned position.
Illustrate only brake equipment 210a in Figure 10, but as shown in figure 11, be configured in multiple positions of the circumference of brake disc 75.Three position these examples of three of arrangement brake device 210a, 210b, 210c of circumference at brake disc 75 have been shown in Figure 11.Brake equipment is not limited to three positions, also can be configured at arbitrary position.At this, brake equipment 210a, 210b, 210c shown in Figure 11 are fixed on hull side, even if bearing 5 rotates, the position of brake equipment 210a, 210b, 210c is also still fixed.In addition, the structure of brake equipment 210b, 210c is identical with the structure of brake equipment 210a, therefore omits the description.
Like this, steering engine 200 according to the present embodiment, the rotation of the bearing 5 that the propulsive effort transmission of drive source 6a, 60a causes is braked by brake equipment (detent) 210a via the brake disc 75 linked with bearing 5, and the rotation of the rudderpost 1 caused via bearing 5 transmission of drive force is also braked.And, the position of rotation of rudderpost 1 can be fixed on assigned position.
(the 3rd embodiment)
Then, use Figure 12, the steering engine 300 of the 3rd embodiment is described.Figure 12 is the partial, longitudinal cross-sectional of the steering engine 300 of the 3rd embodiment.
A slice brake disc 75 that the steering engine 200 of the second embodiment is linked by brake equipment 210a, 210b, 210c pair and bearing 5 is braked.In contrast, multi-disc brake disc 85a, 85b that the steering engine 300 of the 3rd embodiment is linked by multi-disc brake disc 88a, 88b, 88c pair and bearing 5 being fixed on brake clamp 86a brake.
It should be noted that, the 3rd embodiment is the variation of the second embodiment, and except the situation of following special version, other structures are identical with the first embodiment and the second embodiment, thus omit the following description.
Brake disc 85a, 85b shown in Figure 12 are thickness constant and overlook the component into ring-type.Brake disc 85a, 85b are such as metal, are linked by bolt (not shown) and bearing 5.As shown in figure 12, brake clamp 86a is configured to the periphery of clamping brake disc 85a, 85b.A pair caliper opening piston 87a, 87b is provided with in brake clamp 76a.
Multi-disc brake disc 85a, 85b is configured with between multi-disc brake disc 88a, 88b, 88c.The upper surface of brake disc 88a is opposed with the front end face of caliper opening piston 87a, and the lower surface of brake disc 88b is opposed with the front end face of caliper opening piston 87b.
Caliper opening piston 87a indicates according to the braking from control part (not shown), is extruded by the upper surface of its front end face relative to brake disc 88a.In addition, caliper opening piston 87b indicates according to the braking from control part (not shown), is extruded by the lower surface of its front end face relative to brake disc 88c.The narrower intervals of brake disc 88a, 88b, 88c and brake disc 85a, 85b corresponding to the extrusion of the front end face of caliper opening piston 87a, 87b.Connected with brake disc 85a, 85b by brake disc 88a, 88b, 88c and produce friction force between coiling.And the rotational force of the bearing 5 linked with brake disc 85a, 85b weakens, and bearing 5 is braked.The bearing 5 that rotational force reduces due to the braking of brake equipment 310a finally stops the rotation, and is fixed on assigned position.In addition, bearing 5 is via planetary wheel 20a to rudderpost 1 transmission of drive force, and therefore when the rotation of bearing 5 stops, the position of rotation of rudderpost is fixed on assigned position.
Illustrate only brake equipment 210a in Figure 10, but be configured in multiple positions of the circumference of brake disc 75.Brake equipment such as can be configured in three positions, but is not limited to three positions, also can be configured at arbitrary position.At this, brake equipment 310a is fixed on hull side, even if bearing 5 rotates, the position of brake equipment 310a is also still fixed.
Like this, steering engine 200 according to the present embodiment, the rotation of the bearing 5 that the propulsive effort transmission of drive source 6a, 60a causes is braked by brake equipment (detent) 310a via the brake disc 75 linked with bearing 5, and the rotation of the rudderpost 1 caused via bearing 5 transmission of drive force is also braked.And, the position of rotation of rudderpost 1 can be fixed on assigned position.
(other embodiments)
First embodiment employs magnet stopper 70,71 as the detent of braking the rotation of rudderpost 1.In addition, the second embodiment and the 3rd embodiment employ brake equipment 210,310 as the detent of braking the rotation of rudderpost 1.As above, in each embodiment, employ either party in magnet stopper and brake equipment, but also they also can be used.Such as, magnet stopper 70,71 can be used in the steering engine 200 of the second embodiment shown in Figure 10.In addition, such as, also magnet stopper 70,71 can be used in the steering engine 300 of the 3rd embodiment shown in Figure 12.
As the caliper opening piston 77 of the second embodiment and the caliper opening piston 87 of the 3rd embodiment, piston in various manners can be made.Such as, also can adopt by air pressure, oil pressure, hydraulic pressure isobaric go out the mode of piston.In addition, such as, also can adopt and extrude piston by the application force of spring, and use the mode that the application force of magnetic clutch to spring limits.In this case, as long as to the application force removing spring during magnetic clutch service voltage, even if when electric power supply is cut off for some reason, also piston can be extruded by the application force of spring, be fixed the position of rotation of rudderpost.That is, can suitably prevent when electric power supply is cut off, the situation of the unfixing and uncontrollable boats and ships in direction of rudder.
The sensors such as the coder of the position of rotation that can detect rudderpost also can be set in the steering engine of present embodiment.Thus, such as, suitably can control drive source according to the output of sensor to the driving of bearing and detent to the braking of bearing, thus the position of rotation of rudderpost is fixed on assigned position exactly.
Driven wheel 6c, 60c that the steering engine of the first embodiment is linked by drive source 6a, 60a pair and axle drive shaft 6b, 60b drive, and via bearing 5 and planetary wheel 20 to rudderpost gear 2 transmission of drive force, but also can be other modes.Such as, also can make driven wheel 6c, 60c of linking with axle drive shaft 6b, 60b and engage with the rudderpost gear 2 that axle drive shaft 6b, 60b link, directly transmitting the propulsive effort of drive source 6a, 60a from drive source 6a, 60a to rudderpost 1.
Nomenclature:
1 rudderpost
2 rudderpost gears
3 anchor shafts
4 anchor shaft gears
5 bearings
5b bearing gear
6,60 actuating devices
6a, 60a drive source
6b, 60b axle drive shaft
6c, 60c driven wheel
6d electro-motor
6e retarder
6f coupling
7 seat stands
10 planetary wheels (first planet gear)
20 planetary wheels (the second planetary wheel)
30 planet axis
40 bearing shells
70,71 magnet stoppers
75,85 brake discs
76,86 brake clamps
77,87 caliper opening pistons
80,81 deboosters (limiting unit)
90,91 limiting members
100,100 ', 200,30 steering engines
210 brake equipments
Claims (8)
1. a steering engine, it drives via the rudderpost linked with this rudder the rudder of boats and ships, it is characterized in that possessing:
Rudderpost gear, it is fixed on the end of described rudderpost;
Driven wheel, it, to described rudderpost gear transmission propulsive effort, makes described rudderpost rotate;
Drive source, it drives described driven wheel;
Detent, it is braked the rotation of described rudderpost, and the position of rotation of described rudderpost is fixed on assigned position.
2. steering engine according to claim 1, is characterized in that,
Described drive source is electro-motor,
Described detent is the magnet stopper be connected with the S. A. of described electro-motor.
3. steering engine according to claim 1, is characterized in that, possesses:
Anchor shaft gear, itself and described rudderpost are arranged with having same axis, and are fixed on the end of the anchor shaft fixed in hull side;
Bearing, it is arranged to rotate around described anchor shaft, and is provided with bearing gear in periphery;
Brake disc, itself and described bearing link,
Described driven wheel, to described bearing gear transmission propulsive effort, makes this bearing gear rotate around described anchor shaft, thus to propulsive effort described in described rudderpost gear transmission,
Described detent is braked via the rotation of described brake disc to described bearing, and the position of rotation of described rudderpost is fixed on described assigned position.
4. steering engine according to any one of claim 1 to 3, is characterized in that,
Described steering engine possesses limiting unit, and this limiting unit is fixed on described rudderpost, by be fixed on the limiting member of hull side to touching the rotating range limiting described rudderpost.
5. steering engine according to claim 3, is characterized in that,
Described bearing has multiple planet axis,
Described multiple planet axis respectively by with the first planet gear of described anchor shaft gears meshing with support as rotatable with the second planetary wheel of described rudderpost gears meshing,
The operating pitch circle radius of described rudderpost gear of described second planetary wheel engagement is different from the operating pitch circle radius of the described anchor shaft gear of described first planet gears meshing.
6. steering engine according to claim 5, is characterized in that,
Described rudderpost gear, described anchor shaft gear, described first planet gear and described second planetary modulus are equal,
The summation of the number of teeth of described anchor shaft gear and described first planet gear equals the summation of described rudderpost gear and the described second planetary number of teeth.
7. the steering engine according to claim 5 or 6, is characterized in that,
Described steering engine possesses multiple described drive source,
Described multiple drive source respectively via described driven wheel to described bearing gear transmission propulsive effort.
8. boats and ships, is characterized in that, possess the steering engine according to any one of claim 1 to 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610898692.5A CN107054606B (en) | 2012-10-03 | 2013-10-03 | Steering engine and the ship for having the steering engine |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012221347A JP6004876B2 (en) | 2012-10-03 | 2012-10-03 | Steering machine and ship equipped with the same |
| JP2012-221347 | 2012-10-03 | ||
| PCT/JP2013/076924 WO2014054725A1 (en) | 2012-10-03 | 2013-10-03 | Steering gear and ship comprising same |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610898692.5A Division CN107054606B (en) | 2012-10-03 | 2013-10-03 | Steering engine and the ship for having the steering engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104487341A true CN104487341A (en) | 2015-04-01 |
| CN104487341B CN104487341B (en) | 2017-03-08 |
Family
ID=50435045
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380039053.8A Active CN104487341B (en) | 2012-10-03 | 2013-10-03 | Steering engine and the ship possessing this steering engine |
| CN201610898692.5A Active CN107054606B (en) | 2012-10-03 | 2013-10-03 | Steering engine and the ship for having the steering engine |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610898692.5A Active CN107054606B (en) | 2012-10-03 | 2013-10-03 | Steering engine and the ship for having the steering engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP6004876B2 (en) |
| KR (1) | KR101757992B1 (en) |
| CN (2) | CN104487341B (en) |
| WO (1) | WO2014054725A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104520182A (en) * | 2012-10-18 | 2015-04-15 | 三菱重工业株式会社 | Steering gear and ship provided therewith |
| CN105673732A (en) * | 2016-04-15 | 2016-06-15 | 中国中元国际工程有限公司 | Double-acting friction braking device |
| CN106763515A (en) * | 2016-12-31 | 2017-05-31 | 深圳市优必选科技有限公司 | Steering engine |
| CN109591996A (en) * | 2017-09-30 | 2019-04-09 | 西门子公司 | Control device, the method for coming about and system of coming about |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5826164B2 (en) * | 2012-12-28 | 2015-12-02 | 三菱重工業株式会社 | Steering machine |
| KR101784751B1 (en) * | 2015-09-10 | 2017-10-12 | 훌루테크 주식회사 | Finding method for locked steering apparatus and navigation method by the same and unlocking process for the locked steering apparatus by the same |
| CN108528673B (en) * | 2018-04-03 | 2019-12-31 | 武汉船用机械有限责任公司 | Rudder mechanism of full-rotation rudder propeller and control method thereof |
| KR102400973B1 (en) * | 2021-05-20 | 2022-05-20 | 권오완 | deceleration device with self-locking function without ring gear |
| CN115158627B (en) * | 2022-07-06 | 2024-02-13 | 中国舰船研究设计中心 | Rotary swing cylinder coupling electric rudder driving mechanism |
| JP2024034869A (en) * | 2022-09-01 | 2024-03-13 | 大将 石村 | Method and device for extracting piston from cylinder provided in caliper of disc brake |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3796292A (en) * | 1972-04-13 | 1974-03-12 | Nemo Corp | Steering system |
| DE2452066A1 (en) * | 1973-11-02 | 1975-05-07 | Skf Svenska Kullagerfab Ab | Steering control with flexible shafts - incorporates separate reduction gearings and shafts for each wheel or rudder |
| JP3363163B2 (en) * | 1991-09-30 | 2003-01-08 | 東芝エンジニアリング株式会社 | Variable pitch propeller drive |
| JP2745274B2 (en) * | 1992-12-29 | 1998-04-28 | 東海旅客鉄道株式会社 | Multi disc brake device |
| JP3633749B2 (en) * | 1997-04-24 | 2005-03-30 | 大洋製器工業株式会社 | Container connector |
| CN2369951Y (en) * | 1999-03-26 | 2000-03-22 | 荆孝仁 | Automatic steering machine for ship mechanism |
| JP2001114194A (en) * | 1999-10-19 | 2001-04-24 | Ishikawajima Harima Heavy Ind Co Ltd | Four-rudder independent steering device of underwater sailing body |
| DK176054B1 (en) * | 2003-06-04 | 2006-02-27 | Schmidt S Marine El As A | Steering mechanism for a ship |
| JP2007008189A (en) * | 2005-06-28 | 2007-01-18 | Oshima Shipbuilding Co Ltd | Electrically driven steering gear |
| CN1893230A (en) * | 2005-07-01 | 2007-01-10 | 温州三联集团有限公司 | Speed-changing braking motor |
| CN2917726Y (en) * | 2006-07-12 | 2007-07-04 | 苑洪祥 | Small-sized helm gear capable of automatically returning to centre |
| JP2008120291A (en) * | 2006-11-14 | 2008-05-29 | Jtekt Corp | Steering device for vehicle |
| JP2009132306A (en) * | 2007-11-30 | 2009-06-18 | Honda Motor Co Ltd | Steering device |
| JP2011179593A (en) * | 2010-03-01 | 2011-09-15 | Icomes Labo:Kk | Power transmission device |
| CN202175196U (en) * | 2011-07-08 | 2012-03-28 | 南京高精船用设备有限公司 | Rudder propeller steering mechanism with planetary speed reducer |
| CN202381685U (en) * | 2011-10-19 | 2012-08-15 | 中国神华能源股份有限公司 | Shaft seal structure and electromagnetic brake |
| JP2013112090A (en) * | 2011-11-28 | 2013-06-10 | Mitsubishi Heavy Ind Ltd | Energy storage type steering apparatus |
| CN102632988B (en) * | 2012-04-05 | 2014-04-16 | 西北工业大学 | Steering engine for underwater vehicle |
-
2012
- 2012-10-03 JP JP2012221347A patent/JP6004876B2/en active Active
-
2013
- 2013-10-03 WO PCT/JP2013/076924 patent/WO2014054725A1/en active Application Filing
- 2013-10-03 CN CN201380039053.8A patent/CN104487341B/en active Active
- 2013-10-03 CN CN201610898692.5A patent/CN107054606B/en active Active
- 2013-10-03 KR KR1020157001568A patent/KR101757992B1/en active IP Right Grant
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104520182A (en) * | 2012-10-18 | 2015-04-15 | 三菱重工业株式会社 | Steering gear and ship provided therewith |
| CN104520182B (en) * | 2012-10-18 | 2017-03-08 | 三菱重工业株式会社 | Steering wheel and the ship possessing this steering wheel |
| CN105673732A (en) * | 2016-04-15 | 2016-06-15 | 中国中元国际工程有限公司 | Double-acting friction braking device |
| CN105673732B (en) * | 2016-04-15 | 2018-05-15 | 中国中元国际工程有限公司 | Double acting friction stopping device |
| CN106763515A (en) * | 2016-12-31 | 2017-05-31 | 深圳市优必选科技有限公司 | Steering engine |
| WO2018121749A1 (en) * | 2016-12-31 | 2018-07-05 | 深圳市优必选科技有限公司 | Steering engine |
| CN106763515B (en) * | 2016-12-31 | 2020-03-27 | 深圳市优必选科技有限公司 | Steering engine |
| CN109591996A (en) * | 2017-09-30 | 2019-04-09 | 西门子公司 | Control device, the method for coming about and system of coming about |
Also Published As
| Publication number | Publication date |
|---|---|
| KR101757992B1 (en) | 2017-07-13 |
| KR20150021125A (en) | 2015-02-27 |
| JP2014073728A (en) | 2014-04-24 |
| CN104487341B (en) | 2017-03-08 |
| CN107054606A (en) | 2017-08-18 |
| JP6004876B2 (en) | 2016-10-12 |
| CN107054606B (en) | 2018-12-04 |
| WO2014054725A1 (en) | 2014-04-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104487341A (en) | Steering gear and ship comprising same | |
| US9541172B1 (en) | Gearboxes with compound planet gears and methods of operating thereof | |
| US9140335B2 (en) | Shift gearbox for use with an electric machine | |
| KR101041553B1 (en) | Electronic parking brake actuator | |
| CN102310757B (en) | For the input shaft of hybrid transmissions | |
| CN103089930A (en) | Decelerator and motor brake with the same | |
| CN102341617A (en) | Multi-stage transmission | |
| US10408317B2 (en) | Geared transmission unit | |
| JP2005273768A5 (en) | ||
| KR20120098812A (en) | Electric drive system | |
| JP6066402B2 (en) | Power transmission unit and magnetic fluid clutch for electric drive device | |
| ES2900474T3 (en) | Gear assembly, vehicle power train and electric wheel hub with the same | |
| CN104520182A (en) | Steering gear and ship provided therewith | |
| US10286772B2 (en) | Powertrain including an electric machine, an internal combustion engine and a continuously variable transmission | |
| CN101517258B (en) | Mechanical torque converter | |
| US8517881B2 (en) | Micro-traction drive | |
| CN104553819B (en) | Brake apparatus for electric corner module | |
| KR101757567B1 (en) | Steering device | |
| CN102287495A (en) | Planet gear-orbiting reducer with two transmission ratios | |
| CN105264265A (en) | A gear assembly | |
| GB2377733A (en) | An electric motor gear actuator with harmonic drive | |
| CN111542708A (en) | Cone pulley assembly for a conical wound transmission with nested components | |
| CN108612816A (en) | Two-speed gear component | |
| CN203868177U (en) | Friction joint type electronic control power take-off | |
| US11614149B2 (en) | Gear speed change device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |