CN107940080B - Drain valve drive - Google Patents
Drain valve drive Download PDFInfo
- Publication number
- CN107940080B CN107940080B CN201710945994.8A CN201710945994A CN107940080B CN 107940080 B CN107940080 B CN 107940080B CN 201710945994 A CN201710945994 A CN 201710945994A CN 107940080 B CN107940080 B CN 107940080B
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- gear
- clutch gear
- clutch
- conical surface
- revolving part
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- 230000007246 mechanism Effects 0.000 claims description 71
- 238000012216 screening Methods 0.000 claims description 18
- 230000002093 peripheral effect Effects 0.000 claims description 13
- 239000011347 resin Substances 0.000 claims description 7
- 229920005989 resin Polymers 0.000 claims description 7
- 230000001174 ascending effect Effects 0.000 claims description 4
- 229920006324 polyoxymethylene Polymers 0.000 claims description 4
- 229930182556 Polyacetal Natural products 0.000 claims description 3
- 230000005540 biological transmission Effects 0.000 claims 1
- 230000006698 induction Effects 0.000 description 31
- 230000000694 effects Effects 0.000 description 10
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 8
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 4
- 229910052802 copper Inorganic materials 0.000 description 4
- 239000010949 copper Substances 0.000 description 4
- 230000005674 electromagnetic induction Effects 0.000 description 4
- 229910052742 iron Inorganic materials 0.000 description 4
- 239000000203 mixture Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- DHKHKXVYLBGOIT-UHFFFAOYSA-N 1,1-Diethoxyethane Chemical compound CCOC(C)OCC DHKHKXVYLBGOIT-UHFFFAOYSA-N 0.000 description 1
- 239000011354 acetal resin Substances 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 230000005307 ferromagnetism Effects 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001144 postural effect Effects 0.000 description 1
- 230000003449 preventive effect Effects 0.000 description 1
- 230000000979 retarding effect Effects 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- -1 stainless steels Chemical class 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
-
- 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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/44—Mechanical actuating means
- F16K31/53—Mechanical actuating means with toothed gearing
-
- 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
- F16D41/00—Freewheels or freewheel clutches
-
- 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
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
-
- 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
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/08—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet
- F16K31/082—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid using a permanent magnet using a electromagnet and a permanent magnet
-
- 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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/06—Use of materials; Use of treatments of toothed members or worms to affect their intrinsic material properties
- F16H2055/065—Moulded gears, e.g. inserts therefor
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Thermal Sciences (AREA)
- Detail Structures Of Washing Machines And Dryers (AREA)
- Retarders (AREA)
- Gears, Cams (AREA)
- Mechanical Operated Clutches (AREA)
- Electrically Driven Valve-Operating Means (AREA)
Abstract
A kind of draining valve drive, the draining valve drive are able to achieve the miniaturization of device, and can steadily maintain the state of the drain valve after driving.It is solved by draining valve drive below, the draining valve drive includes clutch, the transmitting of motor drive power can be switched to " logical " state or " disconnected " state by the clutch, above-mentioned clutch includes trip(ping) lever, which carries out reciprocating action according to the open and-shut mode of above-mentioned drain valve；One revolving part, the revolving part constitute a part of power transfer path；And clutch gear, the clutch gear is adjacent with the slave end of above-mentioned revolving part gear part in above-mentioned power transfer path, above-mentioned trip(ping) lever also has locking piece, the locking piece prevents above-mentioned clutch gear from inverting after drain valve driving, and state when drain valve driving being maintained to complete, above-mentioned clutch gear has engaged piece, which engages with above-mentioned locking piece.
Description
Technical field
The present invention relates to a kind of draining valve drives.
Background technique
In following patent documents 1, describing is made by the pinion gear 20 that can be axially moveable to external load application
The geared motor 1 of the transmitting on-off of motor drive power.
Existing technical literature
Patent document
Patent document 1: Japanese Patent Laid-Open 2010-276093 bulletin
Make the postural change and dimension of the external load with the recuperability towards original state in the driving force by motor
In the case where the posture of external load after holding the variation, to need include the on off mechanism of motor drive power, to external load weight
The mechanism etc. that original state is prevented is gone back to, device is easy complication, enlargement.
In addition, in the geared motor 1 of patent document 1, compression helical spring 21 active force relative to outside
In the case that the recuperability of load is inadequate, because pinion gear 20 with generate between the input gear 17a that engages of pinion gear 20
Resistance to sliding and cause pinion gear 20 that can not be transferred to the state locking by trip(ping) lever 22, there are external loads to return original state
A possibility that.
Summary of the invention
In view of the above problems, technical problem to be solved by the invention is to provide a kind of draining valve drive, the drainings
Valve drive is able to achieve the miniaturization of device, and can steadily maintain the state of the drain valve after driving.
In order to solve the above-mentioned technical problem, draining valve drive of the invention includes: motor, which is driving source；
The driving force of said motor is transferred to driven member i.e. drain valve by power transfer path, the power transfer path；And clutch
Mechanism, which is switched to " logical " state or " disconnected " state for the transmitting of the driving force of above-mentioned power transfer path, above-mentioned
Clutch includes trip(ping) lever, which carries out reciprocating action according to the open and-shut mode of above-mentioned drain valve；One revolving part,
The revolving part constitutes a part of above-mentioned power transfer path；And clutch gear, the clutch gear are transmitted in above-mentioned power
The gear part adjacent with the slave end of above-mentioned revolving part in path, above-mentioned revolving part and the configuration of above-mentioned clutch gear are in same axis
On line, above-mentioned clutch gear can move on the axis, configured with force structure between above-mentioned revolving part and above-mentioned clutch gear
Part, the biasing member exert a force to above-mentioned revolving part and above-mentioned clutch gear towards detaching direction, above-mentioned revolving part by it is above-mentioned from
The end face for closing gear side is formed with driving side engagement pawl, which is outstanding convex towards above-mentioned clutch gear side
Portion is formed with slave end engagement pawl in the end face by above-mentioned revolving part side of above-mentioned clutch gear, which is
Towards above-mentioned revolving part side protrusion outstanding, above-mentioned trip(ping) lever has a ramp, the ramp to above-mentioned revolving part and it is above-mentioned from
The interval closed between gear is controlled, which has the conical surface, and in the driving of above-mentioned drain valve, the conical surface is by above-mentioned clutch
Gear presses towards above-mentioned revolving part side and engages above-mentioned slave end engagement pawl with above-mentioned driving side engagement pawl, in above-mentioned draining
When valve driving is completed, which releases the pressing and separates above-mentioned slave end engagement pawl from above-mentioned driving side engagement pawl, above-mentioned
Trip(ping) lever also has locking piece, which prevents above-mentioned clutch gear from inverting after the driving of above-mentioned drain valve, and maintains the row
State when water valve driving is completed, above-mentioned clutch gear have engaged piece, which engages with above-mentioned locking piece.
By including above structure, being driven with the recuperability towards original state can be realized by simple structure
The maintenance of state after the completion of the driving of part and the driving is able to achieve the miniaturization of draining valve drive.
Furthermore it is preferred that the size that there is above-mentioned biasing member the elongation for making the biasing member will not be interfered by resistance to sliding
Active force, above-mentioned resistance to sliding refer in above-mentioned clutch gear and the cunning that generates between other components for contacting of the clutch gear
Dynamic resistance.Specifically, it is preferable that above-mentioned revolving part is rotor axle sleeve, rotor axle sleeve composition is supported to relative to rotor fulcrum
The rotor of the said motor rotated freely, the above-mentioned clutch gear also side can be moved on the axis direction of above-mentioned rotor fulcrum
Formula configuration, above-mentioned biasing member are in the above-mentioned driving side engagement pawl for being formed in above-mentioned rotor axle sleeve and to be formed in above-mentioned clutch tooth
The helical spring of above-mentioned rotor fulcrum, the size energy of the active force of above-mentioned helical spring are wound between the slave end engagement pawl of wheel
It resists in above-mentioned clutch gear and the resistance to sliding that is generated between other components for contacting of the clutch gear and makes above-mentioned clutch
Gear is moved along above-mentioned rotor fulcrum.In this case, it can constitute are as follows: the active force of above-mentioned helical spring is enough to resist upper
Clutch gear is stated with the resistance to sliding generated between the input gear that engages of above-mentioned clutch gear and in above-mentioned clutch gear
The resistance to sliding generated between above-mentioned rotor fulcrum keeps above-mentioned clutch gear mobile towards detaching direction and makes above-mentioned slave end card
Pawl is closed to separate from above-mentioned driving side engagement pawl.
In the case where the active force of biasing member is inadequate relative to the recuperability of driven member, due to clutch gear with
The resistance to sliding generated between other gear parts of clutch gear engagement, clutch gear can not promptly be transferred to engaged
State (state that the reversion of clutch gear is prevented by trip(ping) lever), a possibility that returning original state there are driven member.Pass through
The active force for the size for making biasing member that there is the elongation of the biasing member will not be interfered by above-mentioned resistance to sliding, can prevent above-mentioned
Unfavorable condition.
Furthermore it is preferred that protrusion length of the above-mentioned engaged piece on the axis direction of above-mentioned clutch gear be not with it is above-mentioned
Maximum length in the range of the above-mentioned ramp contact of trip(ping) lever.
The reversion of clutch gear in order to prevent, it is expected that after the completion of the driving of driven member clutch gear be immediately transferred by
Locking state.By making the protrusion maximum length of the axis direction of engaged piece, locking piece and the clutch of trip(ping) lever can be shortened
Interval between the engaged piece of gear, so as to engage engaged piece more quickly with locking piece.In addition, even if in clutch
In the case that the engaged piece of gear and the locking piece of trip(ping) lever forcefully collide and clutch gear made to rebound downward, also can
Ensure the fastening state of above-mentioned engaged piece and above-mentioned locking piece to greatest extent.
Furthermore it is preferred that above-mentioned revolving part is the output shaft of said motor, above-mentioned power transfer path has train of reduction gears.
Specifically, above-mentioned revolving part can be set as rotor axle sleeve, rotor axle sleeve composition is supported to rotate certainly relative to rotor fulcrum
The rotor of said motor such as.
In power transfer path, by by clutch gear configure in the smallest position of torque of effect, can reduce from
The resistance to sliding closing gear and being generated between other gear parts for engaging of the clutch gear.Whereby, clutch gear can be made more
Promptly it is transferred to engaged state.
Furthermore it is preferred that above-mentioned power transfer path has planetary gear mechanism, above-mentioned planetary gear mechanism includes two layered cylinder
The sun gear member of structure, the sun gear member be outer cylinder with inner cylinder in the end of the side of the outer cylinder and the inner cylinder in conjunction with
Made of, the outer peripheral surface of above-mentioned outer cylinder is formed with spur gear i.e. input gear, and above-mentioned inner cylinder is sun gear；And planetary wheel carrier
Component, the carrier member be made of planet supporting part is integrated with output gear, and above-mentioned planet supporting part is on multiple
It states planetary gear to be supported, above-mentioned output gear is stretched out from above-mentioned planet supporting part towards the external of above-mentioned planetary gear mechanism
, rotation center commutating tooth wheel portion identical with above-mentioned planet supporting part, above-mentioned clutch gear is upper with above-mentioned sun gear member
State input gear engagement.
The planetary gear mechanism of big retarding ratio can be obtained by configuring in power transfer path, and in the planetary gear machine
The input side of structure configures clutch gear, can reduce the resistance to sliding generated between clutch gear and input gear.Whereby, can make
Clutch gear is more quickly transferred to engaged state.
Furthermore it is preferred that draining valve drive further includes sorting mechanism, when which only rotate forward said motor
Driving force is transferred to above-mentioned power transfer path, and above-mentioned planetary gear mechanism also has heretofore, heretofore tool
Have screening gear, which is the external spur gear exposed towards above-mentioned planetary gear mechanism, the heretofore it is interior
Circumferential surface is formed with internal gear, by only said motor rotate forward when by the rotation of above-mentioned screening gear locking, above-mentioned sorting mechanism
Driving force when only rotating forward said motor is transferred to above-mentioned power transfer path.
By also comprising sorting mechanism, the malfunction of drain valve caused by the reversion because of motor can be preventive from possible trouble.
Furthermore it is preferred that when the above-mentioned conical surface of above-mentioned ramp is separated from above-mentioned revolving part with above-mentioned clutch gear with it is above-mentioned
The contact portion of clutch gear contact being contacted with above-mentioned clutch gear when engaging towards above-mentioned revolving part with above-mentioned clutch gear
Contact portion successively has first conical surface and second conical surface, and the surface location of above-mentioned first conical surface is gradually got higher, above-mentioned second conical surface
Surface location be gradually lower via top, the surface of the reduction amount of the surface location of above-mentioned second conical surface than above-mentioned first conical surface
The ascending amount of position is small.Specifically, can constitute are as follows: above-mentioned first conical surface is the above-mentioned slave end for making above-mentioned clutch gear
Above-mentioned driving side engagement pawl engaging or the isolated conical surface of the engagement pawl relative to above-mentioned revolving part, second conical surface is for maintaining
State the conical surface of the fastening state of the above-mentioned slave end engagement pawl of clutch gear and the above-mentioned driving side engagement pawl of above-mentioned revolving part.
When engaging revolving part with clutch gear, supported by second conical surface of the reversed dip towards first conical surface from
Gear is closed, whereby, clutch gear can be inhibited to reduce due to the spring such as vibration of device along first conical surface.
Furthermore it is preferred that above-mentioned clutch gear and other gear parts engaged with the clutch gear are by polyacetal resin structure
At.
By the resin for using high sliding property in clutch gear and other gear parts engaged with the clutch gear
Material can inhibit the resistance to sliding generated between clutch gear and other gear parts, so as to keep clutch gear rapider
Ground is transferred to engaged state.
Draining valve drive according to the present invention is able to achieve the miniaturization of device, and after steadily capable of maintaining driving
Drain valve state.
Detailed description of the invention
Fig. 1 is the top view for indicating the internal structure of draining valve drive of embodiment.
Fig. 2 is the expansion cross-sectional view for draining valve drive.
Fig. 3 is the side view cutaway drawing for indicating motor configuration.
Fig. 4 is the side view cutaway drawing for indicating the structure of planetary gear mechanism.
Fig. 5 is the top view of the movement of sorting mechanism when indicating motor reversion.
Fig. 6 is the top view for indicating the movement of sorting mechanism when motor rotates forward.
Fig. 7 is the top view of the action state of clutch when indicating driving drain valve.
Fig. 8 is the side view of the action state of clutch when indicating driving drain valve.
Fig. 9 is the top view for indicating the action state of clutch when maintaining the open state of drain valve.
Figure 10 is the side view for indicating the action state of clutch when maintaining the open state of drain valve.
(symbol description)
900 draining valve drives
P1First path (power transfer path)
P2Second path
C clutch
F sorting mechanism
V drain valve
100 motors
122 rotor axle sleeves (output shaft (revolving part) of motor)
122a driving side engagement pawl
The upper surface 122s (by the end face of clutch gear side)
131 rotor fulcrums
150 induction revolving parts
153 shaft sleeve parts
153a gear part
200 clutch gears
The lower surface 200s (by the end face of revolving part side)
210 slave end engagement pawls
220 gear parts
230 engaged pieces
250 helical springs (biasing member)
300 planetary gear mechanisms
310 sun gear members
310a inner cylinder
310b outer cylinder
311 input gears
312 sun gears
320 heretofores
321 screening gears
322 internal gears
330 carrier members
331 planetary gears
332 planet supporting parts
333 output gears
500 trip(ping) levers
510 ramps
511 conical surfaces
First conical surface of 511a
Second conical surface of 511b
520 locking pieces.
Specific embodiment
(structural outline)
Hereinafter, being illustrated using embodiment of the attached drawing to draining valve drive of the invention.Fig. 1 is to indicate this reality
Apply the top view of the internal structure of the draining valve drive 900 of mode.Fig. 2 is the expansion section view for draining valve drive 900
Figure.In addition, the "up" and "down" in following explanation refers to the up and down direction in Fig. 2.
Draining valve drive 900 is the device that drain valve V is opened by the driving force of motor 100.Present embodiment
Drain valve V close in its initial state, and by force application mechanism (not shown), effect has court always in drain valve V
The active force in the direction for closing drain valve V.Draining valve drive 900 is by resisting above-mentioned active force and drawing drain valve V
And keep drain valve V open, and maintain the open state.In addition, the form of drain valve of the invention is not limited to drain
The form of valve V then may be used as long as switching the open and-shut mode of the drain valve by the traction and release of draining valve drive
To be the drain valve for having active force towards open direction effect always.
Draining valve drive 900 includes: motor 100, which is driving source；First path P1, the first path
P1It is that the driving force of motor 100 is transferred to the driven member i.e. power transfer path of drain valve V；Clutch C, the clutch
Structure C is by first path P1The transmitting of driving force be switched to " logical " state or " disconnected " state；Sorting mechanism F, sorting mechanism F is only
Driving force when rotating forward motor 100 is transferred to first path P1；And second path P2, second path P2It is by motor 100
Driving force be transferred to the power transfer path of sorting mechanism F.
(motor)
Fig. 3 is the side view cutaway drawing for indicating the structure of motor 100.Motor 100 is prevented by aftermentioned sorting mechanism F
Direction of rotation control is the alternating current motor in a direction by reverse function.
Motor 100 is made of motor shell 190, stator 110, rotor 120 and induction revolving part 150, said motor shell
Body 190 is in generally cup-shaped shape, and is metal, and upper opening, said stator 110 are in annulus shape, and along motor shell
The inner peripheral surface of body 190 configures, and above-mentioned rotor 120 is configured at the inside of stator 110, and above-mentioned induction revolving part 150 is configured at rotor
In 120, and above-mentioned induction revolving part 150 is rotation center revolving part identical with rotor 120.
Motor shell 190 has rotor fulcrum 131, which can rotate the bearing of rotor 120.Rotor branch
Axis 131 is the fixing axle formed by metals such as stainless steels, and motor shell 190 is fixed in the base end part indentation of the rotor fulcrum 131
Bottom center.In addition, being vertically equipped with fulcrum and bearing in the upper surface of stator 110, the fulcrum and bearing drive to drain valve is constituted
Other rotating members or revolving member of dynamic device 900 are supported.
Rotor 120 is made of rotor magnet 121, rotor axle sleeve 122 and magnetic induction magnet 123.
Rotor magnet 121 is the component for the substantially cylindrical shape being made of permanent magnet.Rotor magnet 121 is so that the rotor magnetic
The outer peripheral surface of body 121 mode opposite with the inner peripheral surface of stator 110 configures, and is rotated by the magnetic field that stator 110 generates.This
Outside, the upper end of rotor magnet 121 is provided with reverse rotating brake portion 121a, which constitutes the one of sorting mechanism F
Part.Reverse rotating brake portion 121a extends to the upper surface than stator 110 and locates against the top.
Rotor axle sleeve 122 is the axis body with the resin of rotor magnet 121 together insert-molding, is the output of motor 100
Axis.Rotor axle sleeve 122 has the axis hole 122b penetrated through along the radial center of the rotor axle sleeve 122, inserts in axis hole 122b
There is rotor fulcrum 131, rotor axle sleeve 122 is rotatably supported by rotor fulcrum 131.Rotor axle sleeve 122 and rotor magnet 121
Be incorporated in from the lower end part that another party radially extends towards each other of the rotor axle sleeve 122 He the rotor magnet 121
Together, above-mentioned engaging portion constitutes the bottom 120a of rotor 120.Whereby, the annulus of upper opening is formed in the inside of rotor 120
The space of shape.In addition, it is formed with driving side engagement pawl 122a in the upper surface of rotor axle sleeve 122, the driving side engagement pawl
122a is that the driving force of motor 100 is transferred to the gear part adjacent with the slave end of rotor axle sleeve 122 i.e. clutch gear 200
Multiple protrusions.
Magnetic induction magnet 123 is the annular permanent magnets for being pasted on the inner peripheral surface of rotor magnet 121.
In the inside of magnetic induction magnet 123 configured with induction revolving part 150.Incude revolving part 150 by induction ring portion R and
Shaft sleeve part 153 is constituted, and above-mentioned shaft sleeve part 153 is the axis body of the resin of insert-molding together with induction ring portion R.Incude revolving part
150 rotate the electromagnetic induction effect of generated eddy current by magnetic induction magnet 123 come as rotor 120 rotates.
Induction ring portion R is made of the iron pipe 152 of the copper pipe 151 of substantially cylindrical shape and substantially cylindrical shape, above-mentioned iron
Pipe 152 is pressed into the cylinder of copper pipe 151.Copper pipe 151 is the induction pieces being made of non-magnetic conductor i.e. copper.Iron pipe 152 is ferromagnetism
Body, that is, component made of iron is the support yoke portion for the magnetic attraction that effect has magnetic induction magnet 123.
Shaft sleeve part 153 has the axis hole 153b penetrated through along the radial center of the shaft sleeve part 153, inserts in axis hole 153b
There is rotor axle sleeve 122.Shaft sleeve part 153 is supported in thrust direction and in the radial direction by rotor axle sleeve 122.In addition, shaft sleeve part 153
It is not fixed to rotor axle sleeve 122.Therefore, induction revolving part 150 is only more than in the electromagnetic induction effect to induction revolving part 150
It is just rotated as rotor 120 rotates when incuding the rotational resistance of revolving part 150.In addition, being provided in the upper end of shaft sleeve part 153
Gear part 153a, gear part 153a are the spur gears for constituting a part of sorting mechanism F.
(first path)
Hereinafter, referring to Figures 1 and 2, to first path P1Structure be illustrated.First path P1Be by motor 100 just
Driving force when turning and the outgoing route that drain valve V is drawn using line 450.
First path P1From driving source side towards the side drain valve V by the rotor 120 of motor 100, clutch gear 200,
Planetary gear mechanism 300, the 4th gear 410 (hereinafter referred merely to as " gear 410 ") of first path, the 5th gear 420 of first path
(hereinafter referred merely to as " gear 420 "), winch component 430 and line 450 are constituted.In addition, online 450 front end is fixed with fastening
Part 451, the fastener 451 are installed on the side drain valve V.
It is set to the driving side engagement pawl 122a of 122 upper surface of rotor axle sleeve of rotor 120 and under clutch gear 200
Multiple protrusions outstanding, that is, slave end engagement pawl 210 engages downward on surface, and whereby, the driving force of motor 100 is transferred to clutch
Gear 200.
It is formed in the spur gear i.e. input unit of gear part 220 and planetary gear mechanism 300 of the outer peripheral surface of clutch gear 200
I.e. input gear 311 engages.Input gear 311 is the diameter gear bigger than the diameter of clutch gear 200, whereby, motor 100
Rotation is decelerated and input planet gear mechanism 300.Then, motor 100 be rotated in it is further in planetary gear mechanism 300
Slow down and exports.
The large diameter gear portion 411 of gear 410 is engaged on output section, that is, output gear 333 of planetary gear mechanism 300,
The large diameter gear portion 421 of gear 420 is engaged in the small-diameter gear portion 412 of gear 410.The sawtooth portion 422 of gear 420 and shape
Chimeric at the through hole 431 in winch component 430, gear 420 is integrally rotated with winch component 430 towards circumferential.Whereby, motor
100 rotation is further slowed down, and is transferred to drain valve V via line 450.
(planetary gear mechanism)
Planetary gear mechanism 300 constitutes first path P1A part, and it is differential using the planetary gear mechanism 300
Gear structure constitutes a part of aftermentioned sorting mechanism F.Fig. 4 is the diagrammatic side-view cross-sectional for indicating the structure of planetary gear mechanism 300
Figure.Planetary gear mechanism 300 is by sun gear member 310, heretofore 320, three planetary gears 331 and planetary wheel carriers
Component 330 is constituted.
Sun gear member 310 is inner cylinder 310a and outer cylinder 310b in the upper end one of inner cylinder 310a and outer cylinder 310b
The gear part of double-tube structure made of body, above-mentioned inner cylinder 310a are formed with sun gear 312, and above-mentioned outer cylinder 310b is outside
Circumferential surface is formed with the input unit i.e. input gear 311 of planetary gear mechanism 300.The input gear 311 and clutch tooth of outer cylinder 310b
The gear part 220 of wheel 200 engages, inside and three planet teeth of the sun gear 312 of inner cylinder 310a in sun gear member 310
331 engagement of wheel.Whereby, the rotation of clutch gear 200 is transmitted to above-mentioned planet tooth via sun gear 312 from input gear 311
Wheel 331.
Heretofore 320 is to be formed with the substantially cap shaped of internal gear 322 in the inner peripheral surface of the heretofore 320
Gear part.The top of heretofore 320 is embedded in the outer cylinder 310b of sun gear member 310, in heretofore 320
Slave sun gear member 310 expose lower end be formed with screening gear 321.Screening gear 321 is from heretofore 320
Lower end radially outside with annular shape stretch out flange shape spur gear.The internal gear 322 and planet of heretofore 320
Gear 331 engages, screening gear 321 and the second path P of aftermentioned composition2The 4th gear 720 of the second path (hereinafter referred merely to as
" gear 720 ") small-diameter gear portion 722 engage.
Carrier member 330 is component, above-mentioned planet made of planet supporting part 332 is integrated with output gear 333
Supporting part 332 is to support planetary gear 331 for revolvable framework, and above-mentioned output gear 333 is from 332 court of planet supporting part
Output section that lower section is stretched out, planetary gear mechanism 300.The output gear 333 and composition first path of carrier member 320
P1Gear 410 large diameter gear portion 411 engage.
In planetary gear mechanism 300, it is defeated whether the rotation of the i.e. sun gear 312 of rotation of input gear 311 is transferred to
Gear 333 out are determined by the way that whether the angle position of screening gear 321 is fixed.If screening the rotation of gear 321 by tooth
Wheel 720 small-diameter gear portion 722 it is locking, then the angle position of the internal gear 322 of heretofore 320 also with screening gear 321
It fixes together.When screening gear 321 is fixed, if sun gear 312 rotates, which can be transferred to planetary gear 331, row
Star gear 331 revolves along fixed internal gear 332, rotates output gear 333 together with planet supporting part 332.Another party
Face, when screening gear 321 is unlocked, the rotation of sun gear 312 is via planetary gear 331 from transferring by internal gear 322
Idle running consumption, so that output gear 333 will not be transferred to.
That is, only fixed when motor 100 rotates forward screen gear 321, whereby, when motor 100 can only be made to rotate forward
Driving force is transferred to first path P1, and the driving force when reversion of motor 100 can be made to disappear by the idle running of internal gear 322.
(the second path and sorting mechanism)
Hereinafter, referring to Fig. 5, Fig. 6 and Fig. 2, to the second path P2It is illustrated with the specific structure of sorting mechanism F.Sieve
Selecting mechanism F is that the driving force being modified to the motor 100 when motor 100 inverts when rotating forward and only rotating forward motor 100 is transmitted
To first path P1Mechanism.Second path P2It is the outgoing route for making above-mentioned sorting mechanism F movement.
Sorting mechanism F and the second path P2From driving source side towards 300 side of planetary gear mechanism by induction revolving part
150, sector gear 600, the second path third gear 710 (hereinafter referred merely to as " gear 710 "), (the second path the 4th of gear 720
Gear 720) and planetary gear mechanism 300 heretofore 320 constitute.
Sector gear 600 is with the generally fan-shaped of the teeth portion 610 engaged with the gear part 153a of induction revolving part 150
Gear part.The lower surface of the front end of the end of side counterclockwise is formed in Fig. 5 of sector gear 600 dashes forward downward
Locking piece 620 when protrusion out inverts.In addition, there is 630 court of axis body of cylindrical shape from the center of rotation portion of sector gear 600
Top is stretched out.The locking piece 635 when the top of axis body 630 is formed with rotating forward, locking piece 635 is towards axis body 630 when the rotating forward
Radial outside protrusion outstanding.In addition, from the center of rotation portion of sector gear 600 there are also rodlike bar portion 640 towards induction revolve
The substantially opposite direction for turning 150 side of part is stretched out.One end of helical spring 690, helical spring are installed in the front end of bar portion 640
690 other end is installed on pin 135, which is arranged on the stator 110.
The outer peripheral surface of gear 710 at an upper portion thereof is formed with multiple engaging protrusions 711, and multiple engaging protrusion 711 can be with fan
Locking piece 635 engages when the rotating forward of shape gear 600.In addition, the lower part of gear 710 is provided with spur gear i.e. gear part 712.
Gear 720 be the large diameter gear 721 that is coaxially overlapped and small-diameter gear 722 it is integrally formed made of compound gear.Tooth
The large diameter gear 721 of wheel 720 is engaged with the gear part 712 of gear 710, the small-diameter gear 722 and heretofore of gear 720
320 screening gear 321 engages.
Fig. 5 is the top view for indicating the movement of sorting mechanism F when motor 100 inverts.In addition, the horse in present embodiment
Rotating forward up to 100 refers to that rotor 120 rotates clockwise in Fig. 5, and the reversion of motor 100 refers to rotor 120 in Fig. 5 counterclockwise
Rotation.
If motor 100 inverts, incudes revolving part 150 and rotated counterclockwise as the motor 100 rotates.Then, with sense
The sector gear 600 for answering the gear part 153a of revolving part 150 to engage rotates clockwise.If sector gear 600 turns to sector
The position that the side of wheel 600 is abutted with the base end part of gear 710, then sector gear 600 can not be rotated further.Then, with fan
Further rotating for the induction revolving part 150 that shape gear 600 engages is also locking by sector gear 600.
As described above, the shaft sleeve part 153 of induction revolving part 150 is not fixed to rotor axle sleeve 122, revolving part 150 is incuded
Only when the electromagnetic induction effect to induction revolving part 150 is more than the rotational resistance of induction revolving part 150 just as rotor 120 revolves
Then rotation.Therefore, after the rotation of induction revolving part 150 is locking by sector gear 600, rotor 120 continues to invert.
In the state of turning to the position that sector gear 600 is abutted with the base end part of gear 710, if rotor 120 inverts,
Then locking piece 620 collides when the reversion of the reverse rotating brake portion 121a of rotor 120 and sector gear 600.Pass through above-mentioned impact, rotor
120 direction of rotation is corrected for rotating forward.
Fig. 6 is the top view for indicating the movement of sorting mechanism F when motor 100 rotates forward.If motor 100 rotates forward, incude
Revolving part 150 is rotated clockwise as the motor 100 rotates.Then, it is engaged with the gear part 153a of induction revolving part 150
Sector gear 600 rotates counterclockwise.In addition, at this point, helical spring 690 is stretched and applied to sector gear 600 by sector gear 600
Power, so that sector gear 600 returns to original position.
If locking piece 635 is abutted with the outer peripheral surface of gear 710 when sector gear 600 turns to the rotating forward of sector gear 600
Position, then sector gear 600 can not be rotated further.Then, engaged with sector gear 600 induction revolving part 150 into
The rotation of one step is also locking by sector gear 600.In addition, in this case, rotor 120 also continues rotating forward.
If locking piece 635 is abutted with the outer peripheral surface of gear 710 when the rotating forward of sector gear 600, the engaging of gear 710 is prominent
It plays 711 to engage with locking piece 635 when rotating forward, whereby, the rotation of gear 710 is engaged.In addition, when motor 100 rotates forward, gear
710 are intended to rotate clockwise by from the driving force of screening 321 anti-pass of gear.
If rotating clockwise for gear 710 is engaged, link therewith, gear 720 and screening (the internal gear structure of gear 321
Part 320) rotation be also engaged.Whereby, the driving force of motor 100 is transferred to first path P1。
(clutch)
Hereinafter, being illustrated referring to Fig. 7 to Figure 10 to the clutch C of draining valve drive 900.Fig. 7 is to indicate to drive
The top view (figure from the direction arrow B when Fig. 8) of the action state of clutch C when dynamic drain valve V, Fig. 8 is to indicate
The side view (figure from the direction arrow A when Fig. 7) of the same action state of clutch C.It is filled in addition, being driven in drain valve
When setting 900 stopping, clutch C also becomes Fig. 7 and state shown in Fig. 8.Fig. 9 is the open state for indicating to maintain drain valve V
When clutch C action state top view (figure from the direction arrow B when Figure 10), Figure 10 is to indicate clutch
The side view (figure from the direction arrow A when Fig. 9) of the same action state of C.In addition, omitting gear in figure 8 and figure 10
420 record.
Clutch C is by first path P1The transmitting of driving force of motor 100 be switched to " logical " state or " disconnected " shape
The mechanism of state.Clutch C is mainly made of the rotor axle sleeve 122 of motor 100, clutch gear 200 and trip(ping) lever 500, on
Stating clutch gear 200 is in first path P1In the gear part adjacent with the slave end of rotor axle sleeve 122, above-mentioned trip(ping) lever
500 be generally fan-shaped tabular component.Trip(ping) lever 500 is according to the open and-shut mode of drain valve V and with the cardinal extremity of the trip(ping) lever 500
The fulcrum 136 in portion is the component that center of rotation moves back and forth in the horizontal direction within the scope of predetermined angular.
Rotor axle sleeve 122 and clutch gear 200 are supported on the same axis by rotor fulcrum 121.The axis of clutch gear 200
It is not fixed to position, clutch gear 200 can move along the vertical direction on rotor fulcrum 131.Rotor axle sleeve 122 by from
Close end face, that is, upper surface 122s of 200 side of gear and end face, that is, lower surface by 122 side of rotor axle sleeve of clutch gear 200
Helical spring 250 is configured between 200s in a manner of being wound in rotor fulcrum 131, which is to above-mentioned upper table
The biasing member that face 122s and above-mentioned lower surface 200s exert a force towards detaching direction.
It is formed with driving side engagement pawl 122a in the upper surface 122s of rotor axle sleeve 122, driving side engagement pawl 122a is
Towards 200 side of clutch gear multiple protrusions outstanding.Also, slave end card is formed in the lower surface 200s of clutch gear 200
Pawl 210 is closed, which is towards 122 side of rotor axle sleeve multiple protrusions outstanding.Pass through slave end engagement pawl
210 engage with driving side engagement pawl 122a, and the driving force of motor 100 is transferred to clutch gear 200.That is, first path P1Become
" logical " state.In addition, by the engaging for releasing above-mentioned slave end engagement pawl 210 and driving side engagement pawl 122a, first path P1
Become state of " breaking ".
Clutch gear 200 has the driven shaft 240 of tubular, gear part 220 of the driven shaft 240 from the clutch gear 200
It protrudes upward.Trip(ping) lever 500 has ramp 510 in its lower surface, which is to rotor axle sleeve 122 and clutch
The cam that interval between gear 200 is controlled.Ramp 510 have the conical surface 511, the driven shaft 240 of clutch gear 200 with
The conical surface 511 contact.Ramp 510 by driven shaft 240 of the conical surface 511 to clutch gear 200 by being pressed, to control
The axial position of clutch gear 200.More specifically, when drain valve V is open, being reduced by pressing clutch gear 200 should
The axial position of clutch gear 200 engages slave end engagement pawl 210 with driving side engagement pawl 122a, completes opening for drain valve V
It puts, when maintaining the open state, releases pressing, separate slave end engagement pawl 210 from driving side engagement pawl 122a.
In addition, as shown in Figure 10, when the conical surface 511 of ramp 510 is separated from rotor axle sleeve 122 with clutch gear 200
The driven shaft when position (left side in Figure 10) of driven shaft 240 engages towards above-mentioned rotor axle sleeve 122 with above-mentioned clutch gear 200
240 position (right side in Figure 10) successively has the first conical surface 511a and the second conical surface 511b, the table of above-mentioned first conical surface 511a
Face position is gradually got higher, and the surface location of above-mentioned second conical surface 511b is gradually lower via top.In addition, on the second conical surface 511b
Surface location reduction amount D it is smaller than the ascending amount U of the surface location on the first conical surface 511a.For example, as shown in figure 8, making
When rotor axle sleeve 122 engages with clutch gear 200, pass through court's direction inclined second conical surface opposite with the first conical surface 511a
511b supports driven shaft 240, whereby, it is suppressed that clutch gear 200 is due to vibration of device etc. is bounced along first conical surface
511a is reduced.That is, the first conical surface 511a is (to make slave end engagement pawl for engaging clutch gear 200 with rotor axle sleeve 122
210 engage with driving side engagement pawl 122a) or separate clutch gear 200 from rotor axle sleeve 122 (to make slave end engagement pawl
210 from driving side engagement pawl 122a separate) the conical surface, the second conical surface 511b is for maintaining clutch gear 200 and rotor axle sleeve
The conical surface of 122 fastening state (fastening state of slave end engagement pawl 210 and driving side engagement pawl 122a).
As shown in figures 7 and 9, the upper surface 420a of gear 420 is provided with cam path 423, which is by this
The circumferential position of gear 420 changes groove width and the groove portion of substantially circular shape that is formed.On the other hand, under trip(ping) lever 500
Surface, the part Chong Die with gear 420 of position in the horizontal direction are formed with driven shaft 530, which is downward
Axle portion outstanding.The driven shaft 530 of trip(ping) lever 500 and the cam path 423 of gear 420 are chimeric.That is, gear 420 and from
It closes bar 500 and constitutes surface cam.Trip(ping) lever 500 is the cam follower of gear 420, which follows turning for gear 420
It moves and is moved back and forth within the scope of predetermined angular in the horizontal direction.
In addition, being formed with guide hole 540 in trip(ping) lever 500, which is the length inserted for rotor fulcrum 131
Hole.Guide hole 540 is with the overall length in the movable range of trip(ping) lever 500 throughout the part Chong Die with the position of rotor fulcrum 131
Mode formed.In addition, guide hole 540 is also formed in ramp 510, therefore, ramp 510 is formed as overlooking in substantially U-shaped
Shape.That is, being formed with cricoid protrusion in the mode surrounded around guide hole 540, clutch gear 200 is leaned in the cricoid protrusion
The face of side is formed with the conical surface 511 (the first conical surface 511a and the second conical surface 511b) of ramp 510.Due to being located at ramp
Insert has a rotor fulcrum 131 in the guide hole 540 of 510 insides, thus the driven shaft 240 of clutch gear 200 with relative to rotor
The conical surface 511 that fulcrum 131 is located at two sides is slidably connected, and along the axial movement of rotor fulcrum 131.
In addition, being formed with locking piece 520 in the lower surface of trip(ping) lever 500, which is outstanding convex downward
Portion.Also, engaged piece 230 is provided on clutch gear 200, which is from the driven of the clutch gear 200
The protrusion that radially outside is stretched out of axis 240.When drain valve V is open, the engaged piece 230 and trip(ping) lever 500 of clutch gear 200
Locking piece 520 engage in the circumferential, whereby, the rotation of clutch gear 200 is engaged.In addition, clutch gear 200 is engaged
There are two piece 230 is formed in a manner of overlooking point-symmetrically.The reversion of clutch gear 200 is prevented by trip(ping) lever 500, whereby,
After drain valve V is open, the active force of drain valve V itself can be resisted and maintain the open state of drain valve V.
As shown in Figure 7 and Figure 8, in open drain valve V, by the ramp 510 of trip(ping) lever 500 by clutch gear 200
It presses downward, whereby, slave end engagement pawl 210 engages with driving side engagement pawl 122a.Whereby, first path P1Become " leading to "
State, drain valve V are opened by the driving force of motor 100.
As shown in Figure 9 and Figure 10, after drain valve V is open, when maintaining the open state of drain valve V, trip(ping) lever 500 is right
The pressing of clutch gear 200 releases, and slave end engagement pawl 210 is separated from driving side engagement pawl 122a.Whereby, first path P1Become
For " disconnected " state, rotor axle sleeve 122 dallies.Then, the engaged piece 230 of clutch gear 200 in the circumferential with trip(ping) lever 500
Locking piece 520 engages, and the reversion of clutch gear 200 is prevented from.Whereby, it resists the active force of drain valve V itself and maintains to drain
The open state of valve V.
Here, helical spring 250 have its elongation will not by clutch gear 200 with and the row that engages of clutch gear 200
The resistance to sliding that is generated between the input gear 311 of star gear mechanism 300 and clutch gear 200 and rotor fulcrum 131 it
Between the active force of size that interferes of the resistance to sliding that generates.That is, the active force of helical spring 250 is enough to resist in clutch gear
200 with the resistance to sliding generated between the input gear 311 of planetary gear mechanism 300 that engages of clutch gear 200 and
The resistance to sliding generated between clutch gear 200 and rotor fulcrum 131, keep clutch gear 200 mobile towards detaching direction and make from
Dynamic side engagement pawl 210 is separated from driving side engagement pawl 122a.Specifically, the helical spring 250 as present embodiment, uses
Line footpath φ is 0.23, spiral internal diameter is φ 1.8, drift 8.5mm, effective turn 8, total number of turns 10, crush pad
For 2.53mm, spring load are 50-85gf, helical spring that spring constant is 0.3N/mm or more.In helical spring 250
Active force relative to the active force of drain valve V itself it is inadequate in the case where, due to above-mentioned resistance to sliding, clutch gear 200 can not
It is promptly transferred to engaged state (state that the reversion of clutch gear 200 is prevented by the locking piece 520 of trip(ping) lever 500), is deposited
A possibility that drain valve V is closed by the active force of drain valve V.The helical spring 250 of present embodiment has its elongation not
The active force for the size that can be interfered by above-mentioned resistance to sliding can prevent above-mentioned unfavorable condition whereby.
In addition, for example, as shown in Figure 10, the protrusion length of the engaged piece 230 on the axis direction of clutch gear 200 is set
For maximum length in the range of not contacted with the ramp 510 of trip(ping) lever 500.The reversion of clutch gear 200 in order to prevent,
It is expected that clutch gear 200 is immediately transferred into engaged state after drain valve V is open.In the present embodiment, it is engaged piece 230
The protrusion maximum length of axis direction can be shortened the locking piece 520 of trip(ping) lever 500 with clutch gear 200 by card whereby
Interval between stator 230, so that engaged piece 230 be made more quickly to engage with locking piece 520.In addition, even if in clutch tooth
The engaged piece 230 of wheel 200 and the locking piece 520 of trip(ping) lever 500 forcefully collide and clutch gear 200 are made to rebound downward
In the case where, it can also ensure the fastening state of above-mentioned engaged piece 230 and above-mentioned locking piece 520 to greatest extent.
In addition, the clutch gear 200 of present embodiment and the sun gear member 310 engaged with clutch gear 200 are by gathering
Acetal resin is constituted.By being used in clutch gear 200 and the sun gear member 310 engaged with the clutch gear 200
The resin material of high sliding property can inhibit the resistance to sliding generated between clutch gear 200 and sun gear member 310.Separately
Outside, in the present embodiment, clutch gear 200 is engaged with output shaft, that is, rotor axle sleeve 122 of motor 100, and the clutch tooth
200 configuration of wheel is including the outlet side of the train of reduction gears of planetary gear mechanism 300.In first path P1In, clutch gear 200
Configuration is in the smallest position of torque of effect, and whereby, the resistance to sliding generated between clutch gear 200 and input gear 311 is most
Smallization.In the present embodiment, according to above structure, clutch gear 200 can be made more quickly to be transferred to engaged state.
In this way, clutch C is pacified by simple structure in the draining valve drive 900 of present embodiment
Dress, whereby, it can be achieved that the miniaturization of draining valve drive 900.
(movement of draining valve drive)
Hereinafter, being illustrated to the movement of draining valve drive 900.In the following description, valve drive will be drained
900 movement is divided into movement when opening the drain valve V positioned at original state (closed position) and makes to be located at open state
Drain valve V close when movement be illustrated.
(1) drain valve opening operation
Drain valve V is located at closed position under original state (state that line 450 is not wound in winch component 430).This
When, trip(ping) lever 500 pushes clutch gear 200 by its ramp 510, and the slave end engagement pawl 210 of clutch gear 200 is in
The state engaged with the driving side engagement pawl 122a of rotor axle sleeve 122.That is, clutch C is in Fig. 7 and state shown in Fig. 8,
First path P1In " logical " state.
If from the state, drive motor 100, clutch gear 200 rotate together with rotor axle sleeve 122 toward the forward direction.So
Afterwards, induction revolving part 150 of the configuration in rotor 120 is rotated also with rotor 120 and is rotated.If incuding revolving part 150 to rotate,
The sector gear 600 then engaged with the gear part 153 of the induction revolving part 150 rotates.At this point, sector gear 600 resists spiral
The active force of spring 690 is rotated towards locking piece 635 when rotating forward close to the direction of gear 710 (engaging protrusion 711).
If locking piece 635 engages with engaging protrusion 711 when rotating forward, the rotation of gear 710 is engaged.If gear 710
Rotation is engaged, then the rotation with 710 meshed gears 720 of gear is also engaged.If the rotation of gear 720 is engaged, with
The screening gear 321 that gear 720 engages is that the rotation of heretofore 320 is also engaged.That is, by sorting mechanism F, internal gear
The angle position of component 320 is fixed, first path P1Become to transmit the state of the forward drive power of motor 100.In addition,
Sector gear 600 engages with gear 710 and becomes induction revolving part 150 after can not rotating, and rotor 120 also continues to revolve with induction
Turn part 150 non-synchronously to rotate forward.
The gear part 220 of clutch gear 200 is engaged with the input gear 311 of planetary gear mechanism 300.Clutch gear 200
Rotation be transferred to sun gear 312 via input gear 311, thus make sun gear 312 rotate.
Sun gear 312 is engaged in the inside of planetary gear mechanism 300 with three planetary gears 331.In addition, above-mentioned planet
Gear 331 is also engaged with the internal gear 322 of heretofore 320.As described above, heretofore 320 is in its angle position
It is screened the fixed state of mechanism F.Therefore, if sun gear 312 rotates, planetary gear 331 is along heretofore 320
Internal gear 322 revolves around sun gear 312.If planetary gear 331 revolve, the output gear 333 of planetary gear mechanism 300 with
The carrier member 330 supported to planetary gear 331 rotates together.
In addition, sorting mechanism F is not locking by the rotation of heretofore 320 when motor 100 inverts, therefore, even if
Sun gear 312 rotates, and the rotation of the sun gear 312 also can be via planetary gear 331 certainly then by heretofore 320
Idle running consumption.This is because via first path P on the output gear 333 of planetary gear mechanism 3001Effect has draining
The active force of valve V itself, the driving force for being transferred to input gear 311 are conducted to the lesser heretofore 320 1 of rotational resistance
Side.
It is engaged with gear 410 on output gear 333, gear 420 is engaged on gear 410.In the upper table of gear 420
Face is equipped with winch component 430, and integrally court rotates in a circumferential direction the winch component 430 with gear 420.If winch component 430 rotates,
The line 450 then connecting with winch component 430 is wound.Online 450 are fixedly arranged at the front end with drain valve V, and whereby, drain valve V is opened
It puts.
If gear 420 turns to specified position (if line 450 wind specified amount), the cam follower of gear 420 i.e. from
Bar 500 is closed to move towards from the direction that gear 420 leaves.That is, clutch C becomes Fig. 9 and state shown in Fig. 10.
By the movement of trip(ping) lever 500, the pressing of clutch gear 200 is released from, and clutch gear 200 passes through helical spring
250 active force and move upward.Whereby, the driving of the slave end engagement pawl 210 of clutch gear 200 and rotor axle sleeve 122
The engaging of side engagement pawl 122a is released from, and the driving force for being accordingly changed into motor 100 will not be transferred to the state of clutch gear 200.
That is, first path P1Become state of " breaking ".
In addition, by the above-mentioned movement of trip(ping) lever 500, the engaged piece 230 of clutch gear 200 and it is set to trip(ping) lever
500 locking piece 520 abuts in the circumferential.That is, the state that the rotation for becoming clutch gear 200 is locking by trip(ping) lever 500.If from
The rotation for closing gear 200 is engaged, then constitutes first path P1Clutch gear 200 after the angle position of component also consolidated
It is fixed.In addition, at this point, sorting mechanism F is also locking by the rotation of heretofore 320, and in first path P1Middle effect has draining
The active force of valve V itself.But since the rotation of clutch gear 200 is locking by trip(ping) lever 500, clutch gear 200 will not
Reversion.Whereby, it resists the active force of drain valve V itself and maintains the open state of drain valve V.
(2) drain valve closing motion
After the completion of draining, when closing drain valve V, stop powering to motor 100.By stopping powering to motor 100,
The electromagnetic induction power of 100 pairs of motor induction revolving parts 150 disappears.Whereby, sector gear 600 yields to the work of helical spring 690
It is firmly back to original position, subsequently enters gear 710, gear 720 and the locking pass for screening gear 321 from sector gear 600
System is released from.That is, sorting mechanism F fails, heretofore 320 becomes the state that can be dallied.
In drain valve V, effect has active force always on the direction for closing drain valve V.Therefore, if sorting mechanism F
Failure, heretofore 320 become to dally, then maintain the tractive force of the open state of drain valve V because of heretofore 320
It dallies and disappears.Whereby, drain valve V is closed by the active force of drain valve V itself.
In addition, if gear 420 towards drain valve V closing direction rotate, trip(ping) lever 500 towards close to gear 420 direction
It is mobile.That is, clutch C becomes Fig. 7 and state shown in Fig. 8 from Fig. 9 and state shown in Fig. 10.Whereby, clutch gear 200
Slave end engagement pawl 210 engage with the driving side engagement pawl 122a of rotor axle sleeve 122, be accordingly changed into the driving force of motor 100
It is transferred to the state of clutch gear 200.That is, first path P1Become " leading to " state.
Embodiments of the present invention are described in detail above, but the present invention is not limited to above embodiment, it can
Various changes are carried out without departing from the scope of the subject in the invention.
Claims (15)
1. a kind of draining valve drive characterized by comprising
Motor, the motor are driving sources；
The driving force of the motor is transferred to driven member i.e. drain valve by power transfer path, the power transfer path；And
The transmitting of the driving force of the power transfer path is switched to " logical " state or " disconnected " shape by clutch, the clutch
State,
The clutch includes trip(ping) lever, which carries out reciprocating action according to the open and-shut mode of the drain valve；One
Revolving part, the revolving part constitute a part of the power transfer path；And clutch gear, the clutch gear are described dynamic
The gear part adjacent with the slave end of the revolving part in power transmission path,
On the same axis, the clutch gear can move on the axis for the revolving part and clutch gear configuration,
Biasing member is configured between the revolving part and the clutch gear, the biasing member is to the revolving part and the clutch tooth
Wheel exerts a force towards detaching direction,
It is formed with driving side engagement pawl in the end face by the clutch gear side of the revolving part, which is
Towards the clutch gear side protrusion outstanding, it is formed in the end face by the revolving part side of the clutch gear driven
Side engagement pawl, the slave end engagement pawl be towards the revolving part side protrusion outstanding,
The trip(ping) lever has ramp, which controls the interval between the revolving part and the clutch gear
System, the ramp have the conical surface, and in drain valve driving, which presses the clutch gear towards the revolving part side
It presses and engages the slave end engagement pawl with the driving side engagement pawl, when the drain valve drives completion, the conical surface solution
The slave end engagement pawl is separated from the driving side engagement pawl except the pressing,
The trip(ping) lever also has locking piece, which prevents the clutch gear from inverting after drain valve driving, and
State when drain valve driving being maintained to complete, the clutch gear have engaged piece, the engaged piece and the locking piece
Engaging.
2. draining valve drive as described in claim 1, which is characterized in that
The active force for the size that there is the biasing member elongation for making the biasing member will not be interfered by resistance to sliding, the cunning
Dynamic resistance refers in the clutch gear and the resistance to sliding that generates between other components for contacting of the clutch gear.
3. draining valve drive as claimed in claim 2, which is characterized in that
The engaged piece is not and described in the trip(ping) lever in the protrusion length on the axis direction of the clutch gear
Maximum length in the range of ramp contact.
4. draining valve drive as claimed in claim 3, which is characterized in that
The revolving part is the output shaft of the motor, and the power transfer path has train of reduction gears.
5. draining valve drive according to any one of claims 1 to 4, which is characterized in that
The power transfer path has planetary gear mechanism,
The planetary gear mechanism includes the sun gear member of double-tube structure, which is outer cylinder and inner cylinder
It is combined into the end of the outer cylinder He the side of the inner cylinder, the outer peripheral surface of the outer cylinder is formed with spur gear and inputs tooth
Wheel, the inner cylinder is sun gear；And
Carrier member, the carrier member are the planet branch made of planet supporting part is integrated with output gear
Bearing portion supports multiple planetary gears, and the output gear is from the planet supporting part towards the planetary gear mechanism
Outside is stretched out, rotation center commutating tooth wheel portion identical with the planet supporting part,
The clutch gear is engaged with the input gear of the sun gear member.
6. draining valve drive as claimed in claim 5, which is characterized in that
The draining valve drive further includes sorting mechanism, driving force transmitting when which only rotate forward the motor
The extremely power transfer path,
The planetary gear mechanism also has heretofore, which has screening gear, which is court
The external spur gear exposed of the planetary gear mechanism, the inner peripheral surface of the heretofore are formed with internal gear,
By only the motor rotate forward when by it is described screening gear rotation it is locking, the sorting mechanism only makes the motor just
Driving force when turning is transferred to the power transfer path.
7. draining valve drive according to any one of claims 1 to 4, which is characterized in that
Being contacted with the clutch gear when conical surface of the ramp is separated from the revolving part with the clutch gear
The contact portion that with the clutch gear contacts of contact portion when engaging towards the revolving part with the clutch gear successively have
There are first conical surface and second conical surface, the surface location of first conical surface is gradually got higher, the surface location warp of second conical surface
It is gradually lower by top,
The reduction amount of the surface location of second conical surface is smaller than the ascending amount of the surface location of first conical surface.
8. draining valve drive as claimed in claim 7, which is characterized in that
First conical surface is for making the slave end engagement pawl of the clutch gear relative to described in the revolving part
The engaging of driving side engagement pawl or the isolated conical surface,
Second conical surface is for maintaining the slave end engagement pawl of the clutch gear and the drive of the revolving part
The conical surface of the fastening state of dynamic side engagement pawl.
9. draining valve drive according to any one of claims 1 to 4, which is characterized in that
The clutch gear and other gear parts engaged with the clutch gear are made of polyacetal resin.
10. draining valve drive as described in claim 1, which is characterized in that
The revolving part is rotor axle sleeve, which constitutes the horse for being supported to rotate freely relative to rotor fulcrum
The rotor reached, the clutch gear are also configured in a manner of it can move on the axis direction of the rotor fulcrum,
The biasing member is in the driving side engagement pawl for being formed in the rotor axle sleeve and to be formed in the clutch gear
Slave end engagement pawl between be wound in the helical spring of the rotor fulcrum,
The size of the active force of the helical spring can resist the clutch gear with and other structures for contacting of the clutch gear
The resistance to sliding that is generated between part and move the clutch gear along the rotor fulcrum.
11. draining valve drive as claimed in claim 10, which is characterized in that
The power transfer path has planetary gear mechanism,
The planetary gear mechanism includes the sun gear member of double-tube structure, which is outer cylinder and inner cylinder
It is combined into the end of the outer cylinder He the side of the inner cylinder, the outer cylinder is formed with spur gear in outer peripheral surface and inputs tooth
Wheel, the inner cylinder is sun gear；And
Carrier member, the carrier member are the planet branch made of planet supporting part is integrated with output gear
Bearing portion supports multiple planetary gears, and the output gear is from the planet supporting part towards the planetary gear mechanism
Outside is stretched out, rotation center commutating tooth wheel portion identical with the planet supporting part,
The clutch gear is engaged with the input gear of the sun gear member.
12. draining valve drive as claimed in claim 11, which is characterized in that
The active force of the helical spring be enough to resist the clutch gear with and the input engaged of the clutch gear
The resistance to sliding generated between gear and the resistance to sliding generated between the clutch gear and the rotor fulcrum, make institute
Stating clutch gear separates the slave end engagement pawl from the driving side engagement pawl towards detaching direction movement.
13. draining valve drive as claimed in claim 12, which is characterized in that
Being contacted with the clutch gear when conical surface of the ramp is separated from the revolving part with the clutch gear
The contact portion that with the clutch gear contacts of contact portion when engaging towards the revolving part with the clutch gear successively have
There are first conical surface and second conical surface, the surface location of first conical surface is gradually got higher, the surface location warp of second conical surface
It is gradually lower by top,
The reduction amount of the surface location of second conical surface is smaller than the ascending amount of the surface location of first conical surface.
14. draining valve drive as claimed in claim 13, which is characterized in that
First conical surface is for making the slave end engagement pawl of the clutch gear relative to described in the revolving part
The engaging of driving side engagement pawl or the isolated conical surface,
Second conical surface is for maintaining the slave end engagement pawl of the clutch gear and the drive of the revolving part
The conical surface of the fastening state of dynamic side engagement pawl.
15. the draining valve drive as described in any one of claim 10 to 14, which is characterized in that
The clutch gear and other gear parts engaged with the clutch gear are made of polyacetal resin.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-201411 | 2016-10-13 | ||
| JP2016201411A JP6772022B2 (en) | 2016-10-13 | 2016-10-13 | Drain valve drive device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107940080A CN107940080A (en) | 2018-04-20 |
| CN107940080B true CN107940080B (en) | 2019-07-12 |
Family
ID=61935180
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710945994.8A Active CN107940080B (en) | 2016-10-13 | 2017-10-12 | Drain valve drive |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6772022B2 (en) |
| KR (1) | KR102022774B1 (en) |
| CN (1) | CN107940080B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP7228339B2 (en) * | 2018-05-31 | 2023-02-24 | 日本電産サンキョー株式会社 | valve drive |
| JP7150483B2 (en) | 2018-05-31 | 2022-10-11 | 日本電産サンキョー株式会社 | valve drive |
| JP7137452B2 (en) * | 2018-12-03 | 2022-09-14 | 日本電産サンキョー株式会社 | valve drive |
| JP7137451B2 (en) | 2018-12-03 | 2022-09-14 | 日本電産サンキョー株式会社 | valve drive |
| CN110645322A (en) * | 2019-09-28 | 2020-01-03 | 于永利 | Internal-meshing planetary gear type power machine |
| CN112664699B (en) * | 2020-11-17 | 2023-07-14 | 江苏新扬机电设备有限公司 | Double-speed electric air valve actuating mechanism |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4144774A (en) * | 1977-11-21 | 1979-03-20 | Westran Corporation | Actuator device |
| JP2968204B2 (en) * | 1996-03-15 | 1999-10-25 | 株式会社シマノ | Interior hub with reverse braking device |
| KR100420051B1 (en) * | 2000-06-26 | 2004-02-25 | 가부시기가이샤 산교세이기 세이사꾸쇼 | Rotation suppressing mechanism and geared motor |
| JP4128894B2 (en) * | 2003-03-25 | 2008-07-30 | 日本電産サンキョー株式会社 | Valve body drive device |
| JP5372606B2 (en) | 2009-05-28 | 2013-12-18 | 日本電産サンキョー株式会社 | Gear device |
| CN201818872U (en) * | 2009-12-22 | 2011-05-04 | 特福隆集团有限公司 | Valve electric actuator |
| CN102848745A (en) * | 2011-06-27 | 2013-01-02 | 鸿富锦精密工业（深圳）有限公司 | Clutch device |
| JP2015175404A (en) * | 2014-03-14 | 2015-10-05 | 日本電産サンキョー株式会社 | Drain valve driving device |
-
2016
- 2016-10-13 JP JP2016201411A patent/JP6772022B2/en active Active
-
2017
- 2017-10-12 CN CN201710945994.8A patent/CN107940080B/en active Active
- 2017-10-13 KR KR1020170132951A patent/KR102022774B1/en active IP Right Grant
Also Published As
| Publication number | Publication date |
|---|---|
| JP2018062987A (en) | 2018-04-19 |
| KR102022774B1 (en) | 2019-09-18 |
| KR20180041076A (en) | 2018-04-23 |
| JP6772022B2 (en) | 2020-10-21 |
| CN107940080A (en) | 2018-04-20 |
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