CN104220811B - Gas control valve - Google Patents
Gas control valve Download PDFInfo
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- CN104220811B CN104220811B CN201380018882.8A CN201380018882A CN104220811B CN 104220811 B CN104220811 B CN 104220811B CN 201380018882 A CN201380018882 A CN 201380018882A CN 104220811 B CN104220811 B CN 104220811B
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- Prior art keywords
- mentioned
- control valve
- rotating disk
- transmission
- gas control
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23K—FEEDING FUEL TO COMBUSTION APPARATUS
- F23K5/00—Feeding or distributing other fuel to combustion apparatus
- F23K5/002—Gaseous fuel
- F23K5/007—Details
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N1/00—Regulating fuel supply
- F23N1/005—Regulating fuel supply using electrical or electromechanical means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N5/00—Systems for controlling combustion
- F23N5/24—Preventing development of abnormal or undesired conditions, i.e. safety arrangements
- F23N5/245—Preventing development of abnormal or undesired conditions, i.e. safety arrangements using electrical or electromechanical means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23K—FEEDING FUEL TO COMBUSTION APPARATUS
- F23K2400/00—Pretreatment and supply of gaseous fuel
- F23K2400/20—Supply line arrangements
- F23K2400/201—Control devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23K—FEEDING FUEL TO COMBUSTION APPARATUS
- F23K2900/00—Special features of, or arrangements for fuel supplies
- F23K2900/05002—Valves for gaseous fuel supply lines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N2235/00—Valves, nozzles or pumps
- F23N2235/12—Fuel valves
- F23N2235/18—Groups of two or more valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N2235/00—Valves, nozzles or pumps
- F23N2235/12—Fuel valves
- F23N2235/24—Valve details
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Feeding And Controlling Fuel (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Mechanically-Actuated Valves (AREA)
Abstract
Transmission cutting portion (stop part (25) and engaging portion (26)) is set, this transmission cutting portion is transmitted from motor (28) to the power of rotating disk (13) for cutting off in the range of relief valve operation, by making the rotation of rotating disk stop in the range of relief valve operation, thus avoid producing friction between rotating disk 13 and fixed disk 14.And, also there is the variable portion of clinging force (spring members (27) and transmission lifter cam), the variable portion of this clinging force is used for the clinging force changing rotating disk (13) to fixed disk (14), by make rotating disk (13) to the clinging force of fixed disk (14) flow adjustment range internal ratio in the range of relief valve operation little, it is possible to suppression is the friction of generation between rotating disk (13) and fixed disk (14) in flow adjustment range.
Description
Technical field
The present invention relates to the gas that the quantity delivered of the fuel gas provided to the gas burner of gas-fired equipment is controlled
Body control valve.
Background technology
In general, the gas-fired equipments such as gas furnace are disposed in series the flow of supply flow rate for regulating gas
Regulate valve and for cutting off the relief valve of the supply of gas.
In the past, a useful motor is proposed to carry out the air valve of the opening and closing operations of flow control valve and relief valve (such as,
With reference to patent documentation 1).In the gas valve described in this patent documentation 1, flow control valve possesses the rotation with closing function
Body, should not allow gas communication with the rotary body of closing function in certain rotation angle range of motor.This rotation
Body is made up of rotating disk and fixed disk, and wherein, rotating disk is connected with the rotary shaft of motor, and fixed disk has for regulating gas
The multiple intercommunicating pores varied in size of flow.
Do not allow the rotation angle range of the motor of gas communication be action bars that relief valve is kept from from the beginning of
Proceed to the scope retreated.That is, in the gas valve of patent documentation 1, by electric rotating motivation, first, the rotation of accompanying rotation dish
Turn before making action bars and then open the safety-valve.Then, electric magnet relief valve is made to keep in the on-state, by further
Electric rotating motivation and make action bars retreat.During this period, the position of the intercommunicating pore of rotating disk and the position of the intercommunicating pore of fixed disk are made
Put inconsistent, so that gas flows out not over flow control valve.And then, when further rotating motor, rotating disk
Intercommunicating pore and the intercommunicating pore position consistency of any one size of fixed disk, it is allowed to the gas communication of flow control valve.
Prior art literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2002-323218 publication
Summary of the invention
In the gas valve described in patent documentation 1, it is configured to the rotation with motor and makes rotating disk rotate in linkage, adjoint
Both relief valve and flow control valve are operated by this rotation rotating disk.Though that is, operation relief valve time or
During operation flow control valve, rotating disk always rotates.Further, rotating disk and fixed disk are configured to make dish by means of helical spring
It is close on closing face each other, so that gas does not spills from the gap of two dishes.Therefore, there is problems with: to relief valve and stream
In the operation of adjustable valve, between rotating disk and fixed disk, produce friction all the time, owing to abrasion causes the reliability of closing face
Reduce.
The present invention completes to solve such problem, it is intended that reduce rotating disk and fixed disk it
Between produce friction such that it is able to suppression closing face abrasion.
In order to solve above-mentioned problem, in the present invention, gas control valve is formed as carrying out flow tune with a motor
Joint valve and the opening and closing operations of relief valve, and there is rotating disk and fixed disk as the rotary body with closing function, this band is relevant
The rotary body closing function does not allow the gas communication of flow control valve in the range of relief valve operation, in gas control valve, if
It is equipped with for cutting off the transmission cutting portion transmitted to the power of rotating disk from motor in the range of relief valve operation.
In the alternate manner of the present invention, also have for changing rotating disk variable to the clinging force of the clinging force of fixed disk
Portion, the variable portion of this clinging force makes clinging force different in relief valve operation scope and flow adjustment range.
According to the present invention as constructed as above, due to the rotation of the dish that stops the rotation in the range of relief valve operation, therefore in rotation
Friction is not produced, it is possible to prevent the abrasion of closing face between two dishes between rotating disk and fixed disk.
Further, according to other embodiments of the present invention, it is possible to make the rotating disk clinging force with fixed disk in Flow-rate adjustment
In the range of than in the range of relief valve operation little.Operation relief valve time, make provision against emergencies, need strengthen closing face clinging force with
Gas is avoided downstream to spill from the gap between rotating disk and fixed disk.But, owing to now rotating disk is off, therefore
Even if strengthening clinging force the most do not produce the friction of dish, it is possible to prevent the abrasion of closing face.On the other hand, during operation flow control valve
It is just supply gas when, therefore, it is possible to somewhat weaken the clinging force of rotating disk and fixed disk.Owing to clinging force is little, therefore
Even if rotating disk rotates, it is also possible to reduce the friction produced between rotating disk and fixed disk, suppress closing face between two dishes
Abrasion.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the major part structure of the gas control valve illustrating present embodiment.
Fig. 2 is the profile of the gas control valve of present embodiment.
Fig. 3 is the A-A profile of the gas control valve shown in Fig. 2.
Fig. 4 is the figure of the structure example in the distance variable portion illustrating that the gas control valve of present embodiment had.
Fig. 5 is the figure of the operating state in the distance variable portion illustrating present embodiment.
Fig. 6 is the sequential chart of the action example of the gas control valve illustrating present embodiment.
Fig. 7 is to be shown in the sequential chart of Fig. 6 with I)～the V) figure of the state of the gas control valve in each moment that represents.
Fig. 8 is to be shown in the sequential chart of Fig. 6 with I)～III) and the state of the gas control valve in each moment that represents of ※ 1
Figure.
Fig. 9 is to be shown in the sequential chart of Fig. 6 with I), IV), V) and the gas control valve in each moment of ※ 2, ※ 3 expression
The figure of state.
Figure 10 is to be shown in the sequential chart of Fig. 6 with I), II) figure of the state of the gas control valve in each moment that represents.
Detailed description of the invention
Hereinafter, with reference to the accompanying drawings an embodiment of the invention is illustrated.Fig. 1 is the gas illustrating present embodiment
The schematic diagram of the major part structure of control valve 1.The gas control valve 1 of present embodiment is to be applied to the gas-fired equipments such as gas furnace
, it has flow control valve 11 and relief valve 12, and wherein, flow control valve 11 is for regulating the supply flow rate of gas, safety
Valve 12 is for cutting off the supply of gas.
The gas control valve 1 of present embodiment is formed as carrying out flow control valve 11 and relief valve 12 with a motor 28
Opening and closing operations.Flow control valve 11 possesses the rotary body with closing function, should be with the rotary body of closing function electronic
Machine 28 does not allow gas communication in the range of making the scope i.e. relief valve operation of the anglec of rotation of relief valve 12 action.With closing merit
The rotary body of energy is made up of rotating disk 13 and fixed disk 14, and wherein, rotating disk 13 rotates in linkage with the rotation of motor 28, Gu
Price fixing 14 is set to opposed with this rotating disk 13.
Relief valve 12 has Magnet housing 16.In this Magnet housing 16, it is accommodated with according to the letter from control circuit 29
Number and energized electric magnet and be adsorbed in this suction sheet.Suction sheet connects and has and from Magnet housing 16 downstream pleurapophysis
The valve body 17 gone out.Under the closed mode of relief valve 12, valve body 17 is at the shape exerted a force by back-moving spring (not shown) downstream side
State incision is broken gas flow path.
The opening operation of relief valve 12 is by means of direction (left and right directions of Fig. 1) going up activity before and after gas flow path
Action bars 18 carry out.This action bars 18 moves to the upstream side by means of the connecting member 20 rotated in linkage with motor 28,
Valve body 17 is carried out pressing operation, thus, makes gas flow path become open state.That is, relief valve is made to become open mode.
Connecting member 20 is formed through and makes by the action bars 18 of spring 19 downstream side force before and after gas flow path
Retreat on direction, so that relief valve 12 works.That is, when motor 28 rotates, connecting member 20 also rotates in linkage with it,
Before making action bars 18 to the upstream side by means of the connecting rod portion (not shown) prominent to action bars 18 side and then open the safety-valve 12.
Then, according to making relief valve 12 be maintained at open from the electric magnet in the signal exciting magnet housing 16 of control circuit 29
Under the state of state, action bars 18 is made to retreat by making motor 28 opposite direction rotate.
So from action bars 18 start to advance until retreating the anglec of rotation of the motor 28 of the period to initial position
Scope is relief valve operation scope.Additionally, when according to the signal relief from control circuit 29 to the excitation of electric magnet, valve body
17 by the power of back-moving spring and downstream side shifting, and relief valve 12 returns to closed mode.
Fixed disk 14 is provided with the fixing side intercommunicating pore 15 with certain aperture area.On the other hand, rotating
The rotary side intercommunicating pore (not shown) that aperture area is the most different it is provided with on dish 13.When rotating disk 13 rotates
And when making the position consistency of the position of rotary side intercommunicating pore and fixing side intercommunicating pore 15, from the upstream side (right side of Fig. 1 of relief valve 12
Side) to not shown gas burner side, (Fig. 1's is upper via rotary side intercommunicating pore and fixing side intercommunicating pore 15 to supply next gas
Side) flowing.The rotation angle range of the motor 28 when so allowing the gas communication between rotating disk 13 and fixed disk 14 is
Flow adjustment range.
Further, the gas control valve 1 of present embodiment has transferring element 21 between connecting member 20 and rotating disk 13,
This transferring element 21 rotates in linkage with connecting member 20 and the power from motor 28 is delivered to rotating disk 13.This transmission
Parts 21 have power transmission shaft 22 on the face of rotating disk 13 side.On the other hand, rotating disk 13 is in the face of transferring element 21 side
On there is power transmission shaft hold 23.A part for the front of power transmission shaft 22 is intercalated in power transmission shaft holds 23, and
And be configured to the inside that power transmission shaft 22 holds 23 at power transmission shaft and can move in the vertical direction.
Further, the gas control valve 1 of present embodiment has transmission cutting portion, and this transmission cutting portion is for grasping at relief valve
Cut off in the range of work and transmit from motor 28 to the power of rotating disk 13.This transmission cutting portion is such as by stop part 25 and engaging portion
26 are constituted, and wherein, this stop part 25 is arranged on the housing 24 of gas control valve 1, and this engaging portion 26 is arranged on transfer part
On part 21, and engage with stop part 25 and make the rotation of transferring element 21 stop.
By arranging this transmission cutting portion, in the range of relief valve operation, transferring element 21 stops the rotation, connecting member 20
Rotate individually make relief valve 12 work independent of transferring element 21.On the other hand, flow control valve is made at motor 28
In the rotation angle range i.e. flow adjustment range of 11 work, transferring element 21 rotates in linkage with connecting member 20, by electronic
The power of machine 28 is delivered to rotating disk 13.
Further, the gas control valve 1 of present embodiment also has for changing the rotating disk 13 clinging force to fixed disk 14
The variable portion of clinging force so that the clinging force in the range of relief valve operation is different with the clinging force in flow adjustment range.Preferably
It is maximum for making clinging force in the range of relief valve operation, and it is minimum for making clinging force in flow adjustment range.
The variable portion of this clinging force is such as configured to have spring members 27 and distance variable portion, and this spring members 27 is set
Between transferring element 21 and rotating disk 13, this distance variable portion for change between transferring element 21 and rotating disk 13 away from
From.That is, when the distance between transferring element 21 and rotating disk 13 reduces by means of distance variable portion, spring members 27 is received
Contracting, increases the active force of rotating disk 13.Thus, the clinging force of fixed disk 14 is increased by rotating disk 13.
On the other hand, when the distance between transferring element 21 and rotating disk 13 expands by means of distance variable portion, bullet
Spring parts 27 extend, and reduce the active force of rotating disk 13.Thus, the clinging force of fixed disk 14 is reduced by rotating disk 13.Additionally,
The aftermentioned detailed structure example about distance variable portion.
Fig. 2～Fig. 5 is the figure of the concrete structure example of the gas control valve 1 illustrating present embodiment.Fig. 2 is this embodiment party
The profile of the gas control valve 1 of formula.Fig. 3 is the A-A profile of the gas control valve 1 shown in Fig. 2.Fig. 4 is to illustrate this enforcement
The figure of the structure example in the distance variable portion that the gas control valve 1 of mode is had.Fig. 5 is the operating state illustrating distance variable portion
Figure.Additionally, in Fig. 2～Fig. 5, by identical for the structural detail labelling with the function identical with the structural detail shown in Fig. 1
Label.
As shown in Figures 2 and 3, connecting member 20 is connected with motor rotation axis 31, thus joins with the rotation of motor 28
Rotate dynamicly.Transferring element 21 is connected with connecting member 20, thus via connecting member 20 and motor 28 rotation in linkage
Rotate.Connecting member 20 and transferring element 21 are provided with the transmission lifter cam 32 as distance variable portion.This transmission liter
Fall cam 32 also has connection connecting member 20 and the linkage function of transferring element 21.
As shown in Figure 4 and Figure 5, transmission lifter cam 32 is constituted with transmission cam part 32b by linking cam part 32a, wherein,
This link cam part 32a is arranged on a face (face opposed with transferring element 21) of connecting member 20, this transmission cam
Portion 32b is arranged on a face (face opposed with connecting member 20) of transferring element 21.
Two recesses that link cam part 32a is formed by the circumferencial direction along connecting member 20 are constituted.One end of recess
Side is formed by substantially vertical face, and another side is formed by the inclined-plane (conical surface) of the angle with regulation.Transmission cam part 32b by
Two protuberances formed along the circumferencial direction of transferring element 21 are constituted, and the end side of protuberance is formed by substantially vertical face, separately
End side is formed by the inclined-plane (conical surface) of the angle with regulation.
The protuberance of the recess and transmission cam part 32b that link cam part 32a is constituted with roughly the same size, and the conical surface also has
There is roughly the same gradient.Therefore, as shown in Fig. 5 (a), link cam part 32a and transmission cam part 32b is just fitted together to, by
This, connecting member 20 rotates in linkage with transferring element 21.That is, transferring element 21 engaging portion 26 not with housing 24 only
When connecting member 20 rotates in linkage with transferring element 21 in the case of block piece 25 engaging, link cam part 32a and transmission cam
Portion 32b is fitted together to, and transferring element 21 becomes the fall state such as Fig. 5 (a).
Further, the cone-shaped that the conical surface that link cam part 32a has and transmission cam part 32b have becomes mutually opposing.
Therefore, when mutually oppositely acting on the power more than certain along the conical surface, as shown in Fig. 5 (b), transmission cam part 32b is along cone
Sliding in face, transmission cam part 32b rises to the par being formed without linking cam part 32a of connecting member 20.Thus, transmission
Parts 21 become a liter state.Now, compared with the fall state of Fig. 5 (a), spring members 27 becomes the state of contraction.
I.e., in the present embodiment, the stop part 25 in engaging portion 26 with housing 24 by making transferring element 21 engages,
Even if motor 28 rotates when the rotation of transferring element 21 also can be made to stop, connecting member 20 becomes can be independent of transferring element
21 and the state that rotates individually.Now, by releasing the engaging of transmission lifter cam 32, transmission cam part 32b rises to even
The par of knot part 20, transferring element 21 becomes a liter state.
As shown in Figures 2 and 3, in the present embodiment, as the center of rotation of connecting member 20 and transferring element 21
Motor rotation axis 31 is not present on the extended line of bar shifting axle 33, and motor rotation axis 31 is arranged on from bar shifting axle
On the position of 33 deviations, wherein, this bar shifting axle 33 is action bars 18 axle that side moves up before and after gas flow path.With this
The connecting member 20 that motor rotation axis 31 connects has the connecting rod portion 20a prominent to bar shifting axle 33 side.At connecting member
20 with motor 28 rotate in linkage time, link handle 20a slide block 34 is carried out pressing operation, so that being connected with this slide block 34
Action bars 18 before and after gas flow path on direction retreat.
As it has been described above, be provided with the valve body 17 of relief valve 12 in the front (upstream side) of action bars 18, by the behaviour of movement
Make bar 18 and valve body 17 is carried out pressing operation, make gas flow path become open mode.The more front of valve body 17 is provided with electromagnetism
Ferrum 35, this electric magnet 35 is used for making relief valve 12 be maintained at open mode.
Then, the action to the gas control valve 1 of present embodiment as constructed as above illustrates.Fig. 6～Figure 10 is to show
Go out the figure of the action example of the gas control valve 1 of present embodiment.Wherein, Fig. 6 is sequential chart.Further, Fig. 7～Figure 10 is to be shown in
With I in the sequential chart of Fig. 6)～V) and the figure of the state of the gas control valve 1 in each moment that represents of ※ 1～※ 3.
First, as shown in Fig. 6 (e), at moment I), make motor 28 invert (CCW).After motor 28 just rotates,
Link handle 20a and do not abut (with reference to the I of Fig. 8) with slide block 34), as shown in Fig. 6 (d), action bars 18 moves the most to the upstream side.
Therefore, as shown in Fig. 6 (c), the valve body 17 of relief valve 12 is closed (with reference to the I of Fig. 8)).
Further, at moment I), link cam part 32a and transmission cam part the 32b chimeric I of Fig. 7 (reference) and Figure 10
I)), as shown in Fig. 6 (b), transmission lifter cam 32 is in fall state.Further, such as the I of Fig. 9) shown in, it is arranged on fixed disk 14
On the position of fixing side intercommunicating pore 15 the most inconsistent with the position of the rotary side intercommunicating pore 41 being arranged in rotating disk 13.
Therefore, as shown in Fig. 6 (a), flow control valve 11 is in the completely closed state.
Hereafter, when motor 28 continues reversion, the engaging portion 26 of transferring element 21 abuts with the stop part 25 of housing 24
And locking, thus, the rotation of transferring element 21 stops.In this condition, when motor 28 continues to reversion, linking part
Part 20 continues to rotate independent of the transferring element 21 of halted state individually.Now, such as the institute of leading portion portion of ※ 2 of Fig. 6 (b)
Showing, being slided along the conical surface by transmission cam part 32b and rise to the par of connecting member 20, transmission lifter cam 32 becomes
The state of liter (with reference to the II of Fig. 7) and the II of Figure 10)).
When transmission raising cam 32 is for liter state, the spring members 27 being arranged between transferring element 21 and rotating disk 13
Become contraction state.That is, such as the I of Figure 10) and II) shown in, the spring members 27 when being in fall state with transmission lifter cam 32
Length d1 compare, length d2 of the spring members 27 when transmission lifter cam 32 is in liter state shortens.Therefore, rotating disk 13
By the strength from spring members 27.Its result is, the when of being in fall state with transmission lifter cam 32 compared with, rotating disk
The clinging force of 13 pairs of fixed disks 14 strengthens.
Further, when connecting member 20 individually rotates independent of transferring element 21, by the rotation of connecting member 20, link
Bar portion 20a carries out pressing operation, thus, as shown in the leading portion portion of the ※ 1 of Fig. 6 (d), action bars 18 upstream sidesway to slide block 34
Dynamic.Its result is, as shown in Fig. 6 (c), open mode (with reference to the II of Fig. 8) transferred to by relief valve 12).In this condition, according to
Signal from control circuit 29 makes electric magnet 35 excitation, thus relief valve 12 is maintained at open mode.
Then, when making relief valve 12 be maintained at open mode by the power of electric magnet 35, shown in Fig. 6 (e)
Moment II), it is changed to the rotary cutting of motor 28 rotate forward (CW).Thus, as shown in the back segment portion of the ※ 1 of Fig. 6 (d), action bars
18 downstream side retrogressings.Further, as shown in the back segment portion of the ※ 2 of Fig. 6 (b), transmission cam part 32b along the conical surface to phase before
Slide in anti-direction.Its result is, links cam part 32a chimeric with transmission cam part 32b, and transmission lifter cam 32 becomes dropping shape
State (with reference to the III of Fig. 7) and the I of Figure 10)).
In action so far, from action bars 18 start to advance up to the upstream side to retreat between initial position electronic
The rotation angle range of machine 28 is the relief valve operation scope represented with ※ 1 in Fig. 6 and Fig. 8.Further, from transmission cam part 32b
Start to be raised becoming liter state along the conical surface and again become fall state to thereafter along conical surface decline, during this period, become
Rotating of transferring element 21 stops and state that only connecting member 20 individually rotates, and the power of motor 28 is not via transmission
Parts 21 are delivered to rotating disk 13.This rotation angle range is the power non-transmission scope represented with ※ 2 in Fig. 6 and Fig. 9.
After power non-transmission scope, motor 28 also continues to rotate forward (CW).So, such as the IV of Fig. 7) and the IV of Fig. 9) institute
Show, be arranged on a part for the fixing side intercommunicating pore 15 of fixed disk 14 and the rotary side intercommunicating pore 41 being arranged on rotating disk 13
A part consistent.Therefore, as shown in Fig. 6 (a), flow control valve 11 transfer is the state allowing gas communication with minimum flow
(with reference to the IV of Fig. 7)).And then, when motor 28 continues to rotate forward, connect by fixing side intercommunicating pore 15 and rotary side intercommunicating pore 41
Logical area increases, and gas flow also increases therewith.Moment V shown in each figure of Fig. 6, Fig. 7, Fig. 9) represent and permitted by connection
The gas flow permitted reaches maximum state.
So, the position of fixing side intercommunicating pore 15 and the position consistency of rotary side intercommunicating pore 41 and allow the phase of gas communication
Between the rotation angle range of motor 28 of (gas flow is from the period of minimum state to maximum rating) become Fig. 6 and Fig. 9
The flow adjustment range represented with ※ 3.From Fig. 6 clearly, the flow adjustment range of ※ 3 becomes the relief valve operation model with ※ 1
Enclose and compare sizable scope.
As above explaining, in the present embodiment, gas control valve 1 possesses rotating disk 13 and fixed disk 14 as band
There is the rotary body of closing function, should not allow flow control valve 11 in the range of relief valve operation with the rotary body of closing function
Gas communication, in gas control valve 1, be provided with for cutting off in the range of relief valve operation from motor 28 to rotating disk
The transmission cutting portion (stop part 25 and engaging portion 26) of the power transmission of 13.
By arranging such transmission cutting portion, the rotation of rotating disk 13 is made to stop in the range of relief valve operation, therefore,
Friction is not produced, it is possible to prevent the abrasion of closing face between two dishes between rotating disk 13 and fixed disk 14.
Further, in the present embodiment, having the variable portion of clinging force (spring members 27 and transmission lifter cam 32), this is tight
The variable portion of patch power is for changing the rotating disk 13 clinging force relative to fixed disk 14.And, in the range of relief valve operation, pass through
Make transmission lifter cam 32 for liter state compression spring part 27 so that clinging force reaches maximum.On the other hand, adjust at flow
In adjusting range, by making transmission lifter cam 32 stretch spring members 27 for fall state so that clinging force minimizes.
When operating relief valve 12, make provision against emergencies, need enhancing at the clinging force of closing face to avoid gas from rotating disk
The downstream side leakage of gap between 14 and fixed disk 14 goes out.In the present embodiment, due in this relief valve operation scope inward turning
Rotating disk 13 is off, even if therefore clinging force strengthens the friction the most not producing dish, it is possible to prevent the abrasion of closing face.
On the other hand, operation flow control valve 11 flow adjustment range in, be actually supply gas when, because of
This can somewhat weaken the clinging force of rotating disk 13 and fixed disk 14.Owing to clinging force is little, even if therefore rotating disk 13 rotates, also
The friction produced between rotating disk 13 and fixed disk 14 can be reduced, suppress the abrasion of closing face between two dishes.
Additionally, in the above-described embodiment, as shown in Figure 6, it is set as that power non-transmission scope is than relief valve operation scope
Greatly, but the invention is not restricted to this.For example, it is possible to it is big as being set as relief valve operation scope and power non-transmission scope.
Further, in the above-described embodiment, the structure with transmission cutting portion and clinging force variable portion both sides is carried out
Illustrate, but the invention is not restricted to this.It is for instance possible to use only have the structure of transmission cutting portion, make rotating disk 13 to fixing
The clinging force that the clinging force of dish 14 is identical when being to be in liter state with transmission lifter cam 32.In this case, at least in safety
The friction produced between rotating disk 13 and fixed disk 14 can be suppressed in valve opereating specification.
Further, in the above-described embodiment, it is set in, to by motor rotation axis 31 and bar shifting axle 33, the position deviated
Put and make motor 28 be illustrated rotating and reverse the example that the two side rotates up, but the invention is not restricted to
This.That is, if having transmission cutting portion and the structure in the variable portion of clinging force, then there is no need certain by motor rotation axis 31
It is set on the position deviated with bar shifting axle 33, motor 28 can be made to make with the action that is rotated in a direction.
Additionally, above-mentioned embodiment is only the concrete example implementing the present invention, the technical scope of the present invention is not by this
Limited explanation.That is, without departing from purport or its principal character of the present invention, it is possible to implement the present invention in many ways.
Claims (8)
1. a gas control valve, its opening and closing operations being formed as carrying out flow control valve and relief valve with a motor, should
Flow control valve is for regulating the supply flow rate of gas, and this relief valve is for cutting off the supply of gas, the spy of this gas control valve
Levy and be,
Above-mentioned flow control valve possesses the rotary body with closing function, should be with the rotary body of closing function at above-mentioned motor
Gas communication is not allowed in the range of making the rotation angle range i.e. relief valve operation that above-mentioned relief valve works, should be with closing function
Rotary body be made up of rotating disk and fixed disk, this rotating disk rotates in linkage with the rotation of above-mentioned motor, this fixed disk quilt
It is set to opposed with this rotating disk,
Above-mentioned gas control valve have be formed as with above-mentioned motor linkage rotate and the linking part that makes above-mentioned relief valve work
Part,
Above-mentioned gas control valve has transferring element between above-mentioned connecting member and above-mentioned rotating disk, and this transferring element is with above-mentioned
Connecting member rotates in linkage and the power from above-mentioned motor is delivered to above-mentioned rotating disk,
Above-mentioned gas control valve has transmission cutting portion, and this transmission cutting portion is for stopping in the range of above-mentioned relief valve operation
State the rotation of transferring element, enable above-mentioned connecting member to rotate individually.
Gas control valve the most according to claim 1, it is characterised in that
Above-mentioned gas control valve also has for changing the above-mentioned rotating disk variable portion of clinging force to the clinging force of above-mentioned fixed disk,
Make the rotation angle range that the clinging force in the range of above-mentioned relief valve operation makes above-mentioned flow control valve work with above-mentioned motor
I.e. clinging force in flow adjustment range is different.
Gas control valve the most according to claim 2, it is characterised in that
Make above-mentioned clinging force maximum in the range of above-mentioned relief valve operation, make above-mentioned clinging force in above-mentioned flow adjustment range
Little.
4. according to the gas control valve described in Claims 2 or 3, it is characterised in that
The variable portion of above-mentioned clinging force is formed as having spring members and distance variable portion, and this spring members is arranged on above-mentioned transmission
Between parts and above-mentioned rotating disk, this distance variable portion is for changing the distance between above-mentioned transferring element and above-mentioned rotating disk.
Gas control valve the most according to claim 2, it is characterised in that
Above-mentioned transmission cutting portion is controlled the stop part on valve housing by being arranged on above-mentioned gas and is arranged on above-mentioned transmission
Engaging portion on parts is constituted, and above-mentioned engaging portion is formed as engaging with above-mentioned stop part and making the rotation of above-mentioned transferring element stop
Only.
Gas control valve the most according to claim 5, it is characterised in that
The variable portion of above-mentioned clinging force is formed as having spring members and distance variable portion, and this spring members is arranged on above-mentioned transmission
Between parts and above-mentioned rotating disk, this distance variable portion is for changing the distance between above-mentioned transferring element and above-mentioned rotating disk.
Gas control valve the most according to claim 6, it is characterised in that
Above-mentioned distance variable portion is made up of the transmission lifter cam being arranged on above-mentioned connecting member and above-mentioned transferring element,
When being engaged with above-mentioned stop part by above-mentioned engaging portion and stop the rotation of above-mentioned transferring element, above-mentioned transmission lifting is convex
Wheel becomes a liter state, and on the other hand, when above-mentioned engaging portion does not engages with above-mentioned stop part, above-mentioned transmission lifter cam becomes
Fall state.
Gas control valve the most according to claim 7, it is characterised in that
Above-mentioned transmission lifter cam is by the link cam part being arranged on above-mentioned connecting member and is arranged on above-mentioned transfer part
Transmission cam part on part is constituted,
When above-mentioned transmission lifter cam is in fall state, above-mentioned link cam part engages with above-mentioned transmission cam part, thus becomes
The state that can rotate in linkage with above-mentioned connecting member for above-mentioned transferring element, on the other hand, at above-mentioned transmission lifter cam
When being in liter state, above-mentioned link cam part is released from the engaging of above-mentioned transmission cam part, thus becomes above-mentioned connecting member
The state that can rotate independent of above-mentioned transferring element.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012087026A JP6016418B2 (en) | 2012-04-06 | 2012-04-06 | Gas control valve |
| JPJP2012-087026 | 2012-04-06 | ||
| JP2012-087026 | 2012-04-06 | ||
| PCT/JP2013/058957 WO2013150934A1 (en) | 2012-04-06 | 2013-03-27 | Gas control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104220811A CN104220811A (en) | 2014-12-17 |
| CN104220811B true CN104220811B (en) | 2016-12-14 |
Family
ID=49300424
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380018882.8A Active CN104220811B (en) | 2012-04-06 | 2013-03-27 | Gas control valve |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP2835583B1 (en) |
| JP (1) | JP6016418B2 (en) |
| KR (1) | KR102061063B1 (en) |
| CN (1) | CN104220811B (en) |
| ES (1) | ES2825040T3 (en) |
| TW (1) | TWI601898B (en) |
| WO (1) | WO2013150934A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| PL3211308T3 (en) * | 2016-02-24 | 2019-12-31 | Copreci, S.Coop. | Regulating valve for a gas cooking and gas cooking appliance incorporating said regulating valve |
| CN108267558A (en) * | 2018-01-19 | 2018-07-10 | 五矿勘查开发有限公司 | Water environment monitoring device and method |
| JP7132145B2 (en) * | 2019-02-06 | 2022-09-06 | リンナイ株式会社 | Electric gas valve device |
| JP2021021560A (en) * | 2019-07-30 | 2021-02-18 | リンナイ株式会社 | Fire power control device for cooking stove burner |
| JP7538693B2 (en) | 2020-11-05 | 2024-08-22 | リンナイ株式会社 | Forced opening device for solenoid safety valve |
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|---|---|---|---|---|
| GB2258288A (en) * | 1991-07-31 | 1993-02-03 | Mannesmann Ag | Control valve |
| JP2000257738A (en) * | 1999-03-10 | 2000-09-19 | Yoshimine Itou | Flow rate control valve |
| CN1414272A (en) * | 2001-10-24 | 2003-04-30 | 株式会社三国 | Fluid valve device |
| CN1503888A (en) * | 2001-04-18 | 2004-06-09 | Explosion preventing device for portable gas range | |
| CN1537199A (en) * | 2001-08-03 | 2004-10-13 | 株式会社三国 | Fuel feeder |
| JP2010266151A (en) * | 2009-05-15 | 2010-11-25 | Rinnai Corp | Fire power regulating device |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002303418A (en) * | 2001-03-30 | 2002-10-18 | Rinnai Corp | Gas valve |
| JP3830357B2 (en) * | 2001-04-26 | 2006-10-04 | リンナイ株式会社 | Gas valve |
| JP3750061B2 (en) * | 2002-09-10 | 2006-03-01 | リンナイ株式会社 | Gas flow control device |
| JP4160522B2 (en) * | 2004-03-11 | 2008-10-01 | リンナイ株式会社 | Electric valve device |
| JP4317143B2 (en) * | 2005-02-03 | 2009-08-19 | リンナイ株式会社 | Flow control device |
| JP2008064210A (en) * | 2006-09-08 | 2008-03-21 | Matsushita Electric Ind Co Ltd | Gas flow control device |
| JP5473695B2 (en) * | 2010-03-18 | 2014-04-16 | リンナイ株式会社 | Motor safety valve |
-
2012
- 2012-04-06 JP JP2012087026A patent/JP6016418B2/en active Active
-
2013
- 2013-03-27 ES ES13772967T patent/ES2825040T3/en active Active
- 2013-03-27 KR KR1020147028027A patent/KR102061063B1/en active IP Right Grant
- 2013-03-27 EP EP13772967.9A patent/EP2835583B1/en active Active
- 2013-03-27 WO PCT/JP2013/058957 patent/WO2013150934A1/en active Application Filing
- 2013-03-27 CN CN201380018882.8A patent/CN104220811B/en active Active
- 2013-04-03 TW TW102112174A patent/TWI601898B/en active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2258288A (en) * | 1991-07-31 | 1993-02-03 | Mannesmann Ag | Control valve |
| JP2000257738A (en) * | 1999-03-10 | 2000-09-19 | Yoshimine Itou | Flow rate control valve |
| CN1503888A (en) * | 2001-04-18 | 2004-06-09 | Explosion preventing device for portable gas range | |
| CN1537199A (en) * | 2001-08-03 | 2004-10-13 | 株式会社三国 | Fuel feeder |
| CN1414272A (en) * | 2001-10-24 | 2003-04-30 | 株式会社三国 | Fluid valve device |
| JP2010266151A (en) * | 2009-05-15 | 2010-11-25 | Rinnai Corp | Fire power regulating device |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2835583A1 (en) | 2015-02-11 |
| TW201341695A (en) | 2013-10-16 |
| KR20150004338A (en) | 2015-01-12 |
| WO2013150934A1 (en) | 2013-10-10 |
| ES2825040T3 (en) | 2021-05-14 |
| TWI601898B (en) | 2017-10-11 |
| JP2013217539A (en) | 2013-10-24 |
| CN104220811A (en) | 2014-12-17 |
| EP2835583A4 (en) | 2015-11-11 |
| KR102061063B1 (en) | 2020-02-20 |
| JP6016418B2 (en) | 2016-10-26 |
| EP2835583B1 (en) | 2020-08-26 |
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