CN104220811A - Gas control valve - Google Patents
Gas control valve Download PDFInfo
- Publication number
- CN104220811A CN104220811A CN201380018882.8A CN201380018882A CN104220811A CN 104220811 A CN104220811 A CN 104220811A CN 201380018882 A CN201380018882 A CN 201380018882A CN 104220811 A CN104220811 A CN 104220811A
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- Prior art keywords
- mentioned
- control valve
- rotating disc
- transferring element
- gas control
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Classifications
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- 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
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- 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
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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
- F23N2235/18—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
A transmission interruption unit (a stopper (25) and a locking part (26)) is set. The transmission interruption unit is used for interrupting power transmission from a motor (28) to the rotary disk (13) in a safety valve operation range to stop the rotation of the rotary disk in the safety valve operation range, thus preventing friction between a rotary disk (13) and a fixed disk (14). Moreover, an adhesion varying unit (a spring member (27) and a carriage ascent/descent cam) for varying the adhesion of the rotary disk (13) to the fixed disk (14) is further provided, and the adhesion of the rotary disk (13) to the fixed disk (14) is made lower in a flow rate adjustment range than in the safety valve operation range, thereby enabling the suppression of the friction produced between the rotary disk (13) and the fixed disk (14) in the flow rate adjustment range.
Description
Technical field
The quantity delivered of the fuel gas that the gas burner that the present invention relates to subtend gas-fired equipment provides carries out the gas control valve controlled.
Background technology
In general, the gas-fired equipments such as gas furnace are in series provided with the flow control valve for the supply flow rate of adjustments of gas and the safety valve for the supply of cutting off gas.
In the past, a useful motor is proposed to carry out the air valve (for example, referring to patent document 1) of the opening and closing operations of flow control valve and safety valve.In the gas valve described in this patent document 1, flow control valve possesses the rotary body with closing function, gas should not allowed to be communicated with the rotary body of closing function in certain rotation angle range of motor.This rotary body is made up of rotating disc and fixed disk, and wherein, rotating disc is connected with the rotating shaft of motor, and fixed disk has the multiple intercommunicating pores varied in size for adjusting gas flow.
The rotation angle range of the motor not allowing gas to be communicated be action bars that safety valve is kept from proceed to the scope of retrogressing.That is, in the gas valve of patent document 1, by turning motor, first, the rotation of accompanying rotation dish makes before action bars and then opens the safety-valve.Then, by electromagnet, safety valve is kept in the on-state, by turning motor further, action bars is retreated.During this period, make the position of the position of the intercommunicating pore of rotating disc and the intercommunicating pore of fixed disk inconsistent, thus gas is not flowed out by flow control valve.And then when further rotating motor, the intercommunicating pore position consistency of the intercommunicating pore of rotating disc and any one size of fixed disk, the gas of permissible flow control valve is communicated with.
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2002-323218 publication
Summary of the invention
In the gas valve described in patent document 1, be configured to make rotating disc rotate in linkage with the rotation of motor, this rotation along with rotating disc operates both safety valve and flow control valve.Though that is, during handling safety valve or operations flows adjustable valve time, always rotating disc rotates.Further, rotating disc and fixed disk are configured to by means of helical spring, dish is close to each other on closing face, do not spill to make gas from the gap of two dishes.Therefore, there is following problem: in the operation to safety valve and flow control valve, between rotating disc and fixed disk, produce friction all the time, because wearing and tearing cause the reliability of closing face to reduce.
The present invention completes to solve such problem, its object is to, reduces the friction produced between rotating disc and fixed disk, thus can suppress the wearing and tearing of closing face.
In order to solve above-mentioned problem, in the present invention, gas control valve is formed as the opening and closing operations of carrying out flow control valve and safety valve with a motor, and there is rotating disc and fixed disk as the rotary body with closing function, should with rotary body of closing function within the scope of relief valve operation not the gas of permissible flow control valve be communicated with, in gas control valve, be provided with for the internal cutting off of relief valve operation scope from motor the transmission cutting portion to the power transmission of rotating disc.
In alternate manner of the present invention, also have for changing the variable portion of the clinging force of rotating disc to the clinging force of fixed disk, 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 within the scope of relief valve operation, therefore between rotating disc and fixed disk, do not produce friction, the wearing and tearing of the closing face between two dishes can be prevented.
Further, according to other embodiment of the present invention, the clinging force of rotating disc and fixed disk can be made little within the scope of relief valve operation in flow adjustment range internal ratio.During handling safety valve, make provision against emergencies, need to strengthen spilling to downstream from the gap between rotating disc and fixed disk to avoid gas at the clinging force of closing face.But, because now rotating disc stops, even if therefore strengthen the friction that clinging force does not produce dish yet, the wearing and tearing of closing face can be prevented.On the other hand, during operations flows adjustable valve be just when supply gas, therefore, it is possible to weaken the clinging force of rotating disc and fixed disk a little.Because clinging force is little, even if therefore rotating disc rotates, also can reduce the friction produced between rotating disc and fixed disk, suppress the wearing and tearing of the closing face between two dishes.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the major part structure of the gas control valve that present embodiment is shown.
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 that the distance variable portion that the gas control valve of present embodiment has is shown.
Fig. 5 is the figure of the operating state in the distance variable portion that present embodiment is shown.
Fig. 6 is the sequential chart of the action case of the gas control valve that present embodiment is shown.
Fig. 7 illustrates in the sequential chart of Fig. 6 with I) ~ V) figure of the state of the gas control valve in each moment that represents.
Fig. 8 illustrates in the sequential chart of Fig. 6 with I) ~ III) and the figure of the state of the gas control valve in each moment that represents of ※ 1.
Fig. 9 illustrates in the sequential chart of Fig. 6 with I), IV), V) and the figure of the state of the gas control valve in each moment that represents of ※ 2, ※ 3.
Figure 10 illustrates 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
Below, with reference to the accompanying drawings an embodiment of the invention are described.Fig. 1 is the schematic diagram of the major part structure of the gas control valve 1 that present embodiment is shown.The gas control valve 1 of present embodiment is applied to the gas-fired equipments such as gas furnace, and it has flow control valve 11 and safety valve 12, and wherein, flow control valve 11 is for the supply flow rate of adjustments of gas, and safety valve 12 is for cutting off the supply of gas.
The gas control valve 1 of present embodiment is formed as the opening and closing operations of carrying out flow control valve 11 and safety valve 12 with a motor 28.Flow control valve 11 possesses the rotary body with closing function, should make not allow gas to be communicated with within the scope of the scope of the anglec of rotation of safety valve 12 action and relief valve operation with the rotary body of closing function at motor 28.Rotary body with closing function is made up of rotating disc 13 and fixed disk 14, and wherein, rotating disc 13 rotates in linkage with the rotation of motor 28, and fixed disk 14 is set to opposed with this rotating disc 13.
Safety valve 12 has magnet housing 16.In this magnet housing 16, be accommodated with according to the energized electromagnet and be adsorbed in this suction sheet from the signal of control circuit 29.Suction sheet is connected with from magnet housing 16 valve body 17 outstanding to side, downstream.Under the closed condition of safety valve 12, valve body 17 to break gas flow path in the state incision exerted a force to downstream by back-moving spring (not shown).
The opening operation of safety valve 12 is by means of carrying out at the upper movable action bars 18 of the fore-and-aft direction of gas flow path (left and right directions of Fig. 1).This action bars 18 upstream moves side by means of the connecting member 20 rotated in linkage with motor 28, carries out pressing operation, thus, make gas flow path become open state to valve body 17.That is, safety valve is made to become open mode.
Connecting member 20 is formed through and the action bars 18 by spring 19 exerts a force to downstream is retreated on the fore-and-aft direction of gas flow path, thus safety valve 12 is worked.That is, when motor 28 rotates, connecting member 20 also rotates in linkage with it, makes action bars 18 upstream before side and then open the safety-valve 12 by means of the connecting rod portion (not shown) outstanding to action bars 18 side.Then, according under the state making safety valve 12 remain on open mode from the electromagnet in the signal exciting magnet housing 16 of control circuit 29, by making motor 28 rotate in the other direction, action bars 18 is retreated.
Like this from action bars 18 starts to advance until the rotation angle range retreated to the motor 28 during initial position is relief valve operation scope.In addition, when according to during from excitation to electromagnet of the signal relief of control circuit 29, valve body 17 is subject to the power of back-moving spring and moves to side, downstream, and closed condition got back to by safety valve 12.
Fixed disk 14 is provided with the fixation side intercommunicating pore 15 with certain aperture area.On the other hand, rotating disc 13 is provided with the rotary side intercommunicating pore (not shown) that aperture area is circumferentially different gradually.When rotating disc 13 rotates and makes the position consistency of the position of rotary side intercommunicating pore and fixation side intercommunicating pore 15, the gas come from upstream side (right side of Fig. 1) supply of safety valve 12 flows to not shown gas burner side (upside of Fig. 1) via rotary side intercommunicating pore and fixation side intercommunicating pore 15.The rotation angle range of the motor 28 when the gas between such permission rotating disc 13 and fixed disk 14 is communicated with is flow adjustment range.
Further, the gas control valve 1 of present embodiment has transferring element 21 between connecting member 20 and rotating disc 13, and this transferring element 21 and connecting member 20 rotate and in linkage by the power transmission from motor 28 to rotating disc 13.This transferring element 21 has power transmission shaft 22 on the face of rotating disc 13 side.On the other hand, rotating disc 13 has power transmission bearing 23 on the face of transferring element 21 side.A part for the front of power transmission shaft 22 is intercalated in power transmission bearing 23, and is configured to power transmission shaft 22 and can moves in the vertical direction in the inside of power transmission bearing 23.
Further, the gas control valve 1 of present embodiment has transmission cutting portion, and this transmission cutting portion is used in the internal cutting off of relief valve operation scope from motor 28 to the power transmission of rotating disc 13.This transmission cutting portion is such as made up of stop part 25 and engaging portion 26, wherein, this stop part 25 is arranged on the housing 24 of gas control valve 1, and this engaging portion 26 is arranged on transferring element 21, and engages with stop part 25 and the rotation of transferring element 21 is stopped.
By arranging this transmission cutting portion, within the scope of relief valve operation, transferring element 21 stops the rotation, and connecting member 20 rotates individually independent of transferring element 21 and safety valve 12 is worked.On the other hand, in rotation angle range flow control valve 11 being worked at motor 28 and flow adjustment range, transferring element 21 and connecting member 20 rotate, in linkage by the power transmission of motor 28 to rotating disc 13.
Further, the gas control valve 1 of present embodiment also has the variable portion of clinging force of the clinging force for changing rotating disc 13 pairs of fixed disks 14, to make the clinging force within the scope of relief valve operation different with the clinging force in flow adjustment range.Within the scope of relief valve operation, preferably make clinging force be maximum, in flow adjustment range, make clinging force be minimum.
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 arranged between transferring element 21 and rotating disc 13, and this distance variable portion is for changing the distance between transferring element 21 and rotating disc 13.That is, when the distance between transferring element 21 and rotating disc 13 reduces by means of distance variable portion, spring members 27 shrinks, and increases the active force of rotating disc 13.Thus, the clinging force of rotating disc 13 pairs of fixed disks 14 increases.
On the other hand, when the distance between transferring element 21 and rotating disc 13 expands by means of distance variable portion, spring members 27 extends, and reduces the active force of rotating disc 13.Thus, the clinging force of rotating disc 13 pairs of fixed disks 14 reduces.In addition, 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 that present embodiment is shown.Fig. 2 is the profile of the gas control valve 1 of present embodiment.Fig. 3 is the A-A profile of the gas control valve 1 shown in Fig. 2.Fig. 4 is the figure of the structure example that the distance variable portion that the gas control valve 1 of present embodiment has is shown.Fig. 5 is the figure of the operating state that distance variable portion is shown.In addition, in Fig. 2 ~ Fig. 5, the structural detail with the function identical with the structural detail shown in Fig. 1 is marked identical label.
As shown in Figures 2 and 3, connecting member 20 is connected with motor rotation axis 31, thus rotates in linkage with the rotation of motor 28.Transferring element 21 is connected with connecting member 20, thus rotates in linkage via the rotation of connecting member 20 with motor 28.Connecting member 20 and transferring element 21 are provided with the transmission lifter cam 32 as distance variable portion.This transmission lifter cam 32 also has the linkage function connecting connecting member 20 and transferring element 21.
As shown in Figure 4 and Figure 5, transmit lifter cam 32 to be made up of link cam part 32a and transmission cam part 32b, wherein, this link cam part 32a is arranged on a face (face opposed with transferring element 21) of connecting member 20, and this transmission cam part 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 formed.The end side of recess is formed by substantially vertical face, and another side is formed by the inclined-plane (conical surface) of the angle with regulation.Two protuberances that transmission cam part 32b is formed by the circumferencial direction along transferring element 21 are formed, and the end side of protuberance is formed by substantially vertical face, and another side is formed by the inclined-plane (conical surface) of the angle with regulation.
The recess linking cam part 32a is formed with roughly the same size with the protuberance transmitting cam part 32b, and the conical surface also has roughly the same gradient.Therefore, as shown in Fig. 5 (a), link cam part 32a and be just in time fitted together to transmission cam part 32b, thus, connecting member 20 and transferring element 21 rotate in linkage.Namely, when when the engaging portion 26 of transferring element 21 does not engage with the stop part 25 of housing 24, connecting member 20 and transferring element 21 rotate in linkage, link cam part 32a and transmit cam part 32b and be fitted together to, transferring element 21 becomes and falls state as Fig. 5 (a).
Further, link the conical surface that has of cam part 32a and transmit the cone-shaped that cam part 32b has and become mutually opposing.Therefore, when mutually oppositely acting on the power necessarily along the conical surface, as shown in Fig. 5 (b), transmit cam part 32b and slide along the conical surface, transmit the par not forming link cam part 32a that cam part 32b rises to connecting member 20.Thus, transferring element 21 becomes the state of liter.Now, compared with the state of falling of Fig. 5 (a), spring members 27 becomes the state of contraction.
Namely, in the present embodiment, engage at the stop part 25 of engaging portion 26 with housing 24 by making transferring element 21, even if when motor 28 rotates the rotation stopping that also making transferring element 21, connecting member 20 becomes the state that can rotate individually independent of transferring element 21.Now, by removing the engaging of transmitting lifter cam 32, transmit the par that cam part 32b rises to connecting member 20, transferring element 21 becomes the state of liter.
As shown in Figures 2 and 3, in the present embodiment, motor rotation axis 31 as the pivot of connecting member 20 and transferring element 21 is not present on the extended line of bar shifting axle 33, motor rotation axis 31 is arranged on the position of departing from from bar shifting axle 33, wherein, this bar shifting axle 33 is the axle that action bars 18 moves up in the front and back of gas flow path.With the connecting member 20 that this motor rotation axis 31 is connected, there is the connecting rod portion 20a outstanding to bar shifting axle 33 side.When connecting member 20 rotates in linkage with motor 28, link handle 20a and pressing operation is carried out to slide block 34, thus the action bars 18 be connected with this slide block 34 is retreated on the fore-and-aft direction of gas flow path.
As mentioned above, be provided with the valve body 17 of safety valve 12 in the front (upstream side) of action bars 18, carry out pressing operation by action bars 18 pairs of valve bodies 17 of movement, make gas flow path become open mode.The more front of valve body 17 is provided with electromagnet 35, and this electromagnet 35 remains on open mode for making safety valve 12.
Then, the action of the gas control valve 1 of present embodiment as constructed as above is described.Fig. 6 ~ Figure 10 is the figure of the action case of the gas control valve 1 that present embodiment is shown.Wherein, Fig. 6 is sequential chart.Further, Fig. 7 ~ Figure 10 illustrates in the sequential chart of Fig. 6 with I) ~ 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 reverse (CCW).After motor 28 just rotates, link handle 20a and do not abut with slide block 34 (I with reference to Fig. 8)), as shown in Fig. 6 (d), action bars 18 does not have upstream side to move.Therefore, as shown in Fig. 6 (c), the valve body 17 of safety valve 12 is in closed condition (I with reference to Fig. 8)).
Further, at moment I), link the I of cam part 32a chimeric with transmitting cam part 32b (I with reference to Fig. 7) and Figure 10)), as shown in Fig. 6 (b), transmit lifter cam 32 and be in the state of falling.Further, the I as Fig. 9) shown in, the position being arranged on the fixation side intercommunicating pore 15 on fixed disk 14 is completely inconsistent with the position being arranged on the rotary side intercommunicating pore 41 on rotating disc 13.Therefore, as shown in Fig. 6 (a), flow control valve 11 is in buttoned-up status.
After this, 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, and the rotation stopping of transferring element 21.In this condition, when motor 28 continues reversion further, connecting member 20 continues independent of the transferring element 21 of halted state to rotate individually.Now, as shown in the leading portion portion of the ※ 2 of Fig. 6 (b), slided along the conical surface by transmission cam part 32b and rise to the par of connecting member 20, transmitting the II that lifter cam 32 becomes the state of liter (II with reference to Fig. 7) and Figure 10)).
When transmitting raising cam 32 for rising state, the spring members 27 be arranged between transferring element 21 and rotating disc 13 becomes contraction state.That is, as the I of Figure 10) and II) shown in, be in compared with the length d1 of the spring members 27 when falling state with transmission lifter cam 32, the length d2 transmitting the spring members 27 that lifter cam 32 is in when rising state shortens.Therefore, rotating disc 13 is subject to the brute force from spring members 27.Its result is, with transmission lifter cam 32 be in state is fallen and time compared with, the clinging force of rotating disc 13 pairs of fixed disks 14 strengthens.
Further, when connecting member 20 rotates separately independent of transferring element 21, by the rotation of connecting member 20, connecting rod portion 20a carries out pressing operation to slide block 34, and thus, as shown in the leading portion portion of the ※ 1 of Fig. 6 (d), action bars 18 upstream side moves.Its result is, as shown in Fig. 6 (c), open mode (II with reference to Fig. 8) transferred to by safety valve 12).In this condition, make electromagnet 35 excitation according to the signal from control circuit 29, thus safety valve 12 is remained on open mode.
Then, under the state making safety valve 12 remain on open mode by the power of electromagnet 35, the moment II shown in Fig. 6 (e)), the rotary cutting of motor 28 is changed to rotating forward (CW).Thus, as shown in the back segment portion of the ※ 1 of Fig. 6 (d), action bars 18 retreats to side, downstream.Further, as shown in the back segment portion of the ※ 2 of Fig. 6 (b), transmit cam part 32b and slide to direction contrary before along the conical surface.Its result is, links cam part 32a chimeric with transmission cam part 32b, transmits the I that lifter cam 32 becomes the state of falling (III with reference to Fig. 7) and Figure 10)).
In action so far, from action bars 18, upstream advance until the rotation angle range retreated to the motor 28 between initial position is by the relief valve operation scope that ※ 1 represents in Fig. 6 and Fig. 8 in side.And, rise along the conical surface from transmission cam part 32b and become the state of liter to after this again becoming along the conical surface decline state of falling, during this period, the rotation becoming transferring element 21 stops and only having the state that connecting member 20 rotates separately, and the power of motor 28 is not delivered to rotating disc 13 via transferring element 21.This rotation angle range is by the non-transmission scope of power that ※ 2 represents in Fig. 6 and Fig. 9.
After the non-transmission scope of power, motor 28 also continues to rotate forward (CW).Like this, the IV as Fig. 7) and the IV of Fig. 9) shown in, the part being arranged on the fixation side intercommunicating pore 15 of fixed disk 14 is consistent with a part for the rotary side intercommunicating pore 41 being arranged on rotating disc 13.Therefore, as shown in Fig. 6 (a), flow control valve 11 shifts the state (IV with reference to Fig. 7) for allowing gas to be communicated with minimum flow).And then when motor 28 continues to rotate forward, the area be communicated with rotary side intercommunicating pore 41 by fixation side intercommunicating pore 15 increases, and gas flow also increases thereupon.Moment V shown in each figure of Fig. 6, Fig. 7, Fig. 9) represent that the gas flow allowed by connection reaches maximum state.
Like this, the rotation angle range of the motor 28 of the position of fixation side intercommunicating pore 15 with the position consistency of rotary side intercommunicating pore 41 and during allowing gas to be communicated with (gas flow from minimum state to maximum rating during) becomes Fig. 6 and Fig. 9 by the flow adjustment range that ※ 3 represents.Clear and definite from Fig. 6, the flow adjustment range of ※ 3 becomes sizable scope compared with the relief valve operation scope of ※ 1.
As above explain, in the present embodiment, gas control valve 1 possesses rotating disc 13 and fixed disk 14 as the rotary body with closing function, should with rotary body of closing function within the scope of relief valve operation not the gas of permissible flow control valve 11 be communicated with, in gas control valve 1, be provided with for the internal cutting off of relief valve operation scope from motor 28 the transmission cutting portion (stop part 25 and engaging portion 26) to the power transmission of rotating disc 13.
By arranging such transmission cutting portion, within the scope of relief valve operation, making the rotation of rotating disc 13 stop, therefore, between rotating disc 13 and fixed disk 14, do not produce friction, the wearing and tearing of the closing face between two dishes can be prevented.
Further, in the present embodiment, have the variable portion of clinging force (spring members 27 and transmission lifter cam 32), the variable portion of this clinging force is for changing the clinging force of rotating disc 13 relative to fixed disk 14.And, within the scope of relief valve operation, by making transmission lifter cam 32 for rising state and compression spring part 27, make clinging force reach maximum.On the other hand, in flow adjustment range, by making transmission lifter cam 32 for the state of falling and extension spring parts 27, clinging force is made to reach minimum.
When handling safety valve 12, make provision against emergencies, need to strengthen to go out to downstream side leakage from the gap between rotating disc 14 and fixed disk 14 to avoid gas at the clinging force of closing face.In the present embodiment, because rotating disc 13 stops within the scope of this relief valve operation, even if therefore clinging force strengthens the friction also not producing dish, the wearing and tearing of closing face can be prevented.
On the other hand, in the flow adjustment range of operations flows adjustable valve 11, be in fact supply gas time, therefore, it is possible to weaken the clinging force of rotating disc 13 and fixed disk 14 a little.Because clinging force is little, even if therefore rotating disc 13 rotates, also can reduce the friction produced between rotating disc 13 and fixed disk 14, suppress the wearing and tearing of the closing face between two dishes.
In addition, in the above-described embodiment, as shown in Figure 6, be set as that the non-transmission scope of power is larger than relief valve operation scope, but the present invention is not limited thereto.Such as, can be set as that relief valve operation scope and power non-transmission scope is equally large.
Further, in the above-described embodiment, be illustrated having the structure transmitting cutting portion and the variable portion both sides of clinging force, but the present invention is not limited thereto.Such as, the structure only having and transmit cutting portion can be adopted, make the clinging force of rotating disc 13 pairs of fixed disks 14 be in clinging force identical when rising state with transmission lifter cam 32.In this case, the friction produced between rotating disc 13 and fixed disk 14 at least can be suppressed within the scope of relief valve operation.
Further, in the above-described embodiment, to motor rotation axis 31 and bar shifting axle 33 to be set on the position that deviates and to make motor 28 be illustrated rotating and reverse the example that this both direction rotates, but the present invention is not limited thereto.That is, if for having the structure transmitting cutting portion and the variable portion of clinging force, then there is no need certain motor rotation axis 31 and bar shifting axle 33 being set on the position that deviates, motor 28 can be made to carry out action with the rotation in a direction.
In addition, above-mentioned embodiment is only implement a concrete example of the present invention, and being not limited by this property of technical scope of the present invention is explained.That is, only otherwise depart from purport of the present invention or its principal character, the present invention can be implemented in many ways.
Claims (8)
1. a gas control valve, it is formed as the opening and closing operations of carrying out flow control valve and safety valve with a motor, and this flow control valve is used for the supply flow rate of adjustments of gas, and this safety valve is for cutting off the supply of gas, and the feature of this gas control valve is,
Above-mentioned flow control valve possesses the rotary body with closing function, should make not allow gas to be communicated with within the scope of the rotation angle range of above-mentioned safety valve work and relief valve operation at above-mentioned motor with the rotary body of closing function, should be made up of rotating disc and fixed disk with the rotary body of closing function, the rotation of this rotating disc and above-mentioned motor rotates in linkage, this fixed disk is set to opposed with this rotating disc
Above-mentioned gas control valve has transmission cutting portion, and this transmission cutting portion is used in the internal cutting off of above-mentioned relief valve operation scope from above-mentioned motor to the power transmission of above-mentioned rotating disc.
2. gas control valve according to claim 1, is characterized in that,
Above-mentioned gas control valve also has for changing the variable portion of the clinging force of above-mentioned rotating disc to the clinging force of above-mentioned fixed disk, makes the clinging force within the scope of above-mentioned relief valve operation and above-mentioned motor make the clinging force in the rotation angle range of above-mentioned flow control valve work and flow adjustment range different.
3. gas control valve according to claim 2, is characterized in that,
Within the scope of above-mentioned relief valve operation, make above-mentioned clinging force maximum, in above-mentioned flow adjustment range, make above-mentioned clinging force minimum.
4. the gas control valve according to Claims 2 or 3, is characterized in that,
Above-mentioned gas control valve has transferring element between connecting member and above-mentioned rotating disc, this transferring element and above-mentioned connecting member rotate and in linkage by the power transmission from above-mentioned motor to above-mentioned rotating disc, wherein, above-mentioned connecting member is formed as, by with above-mentioned motor linkage rotate and action bars retreated, make above-mentioned safety valve work thus
The variable portion of above-mentioned clinging force is formed as having spring members and distance variable portion, and this spring members is arranged between above-mentioned transferring element and above-mentioned rotating disc, and this distance variable portion is for changing the distance between above-mentioned transferring element and above-mentioned rotating disc.
5. gas control valve according to claim 1, is characterized in that,
Above-mentioned gas control valve has transferring element between connecting member and above-mentioned rotating disc, this transferring element and above-mentioned connecting member rotate and in linkage by the power transmission from above-mentioned motor to above-mentioned rotating disc, wherein, above-mentioned connecting member is formed as, by with above-mentioned motor linkage rotate and action bars retreated, make above-mentioned safety valve work thus
Above-mentioned transmission cutting portion is made up of the stop part be arranged on above-mentioned gas control valve housing and the engaging portion be arranged on above-mentioned transferring element, and above-mentioned engaging portion is formed as engaging with above-mentioned stop part and the rotation of above-mentioned transferring element being stopped.
6. gas control valve according to claim 5, is characterized 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 between above-mentioned transferring element and above-mentioned rotating disc, and this distance variable portion is for changing the distance between above-mentioned transferring element and above-mentioned rotating disc.
7. gas control valve according to claim 6, is characterized in that,
Above-mentioned distance variable portion is made up of the transmission lifter cam be arranged on above-mentioned connecting member and above-mentioned transferring element,
When stopping the rotation of above-mentioned transferring element being engaged with above-mentioned stop part by above-mentioned engaging portion, above-mentioned transmission lifter cam becomes the state of liter, and on the other hand, when above-mentioned engaging portion does not engage with above-mentioned stop part, above-mentioned transmission lifter cam becomes the state of falling.
8. gas control valve according to claim 7, is characterized in that,
Above-mentioned transmission lifter cam is made up of the link cam part be arranged on above-mentioned connecting member and the transmission cam part be arranged on above-mentioned transferring element,
Above-mentioned transmission lifter cam be in state is fallen and time, above-mentioned link cam part engages with above-mentioned transmission cam part, become the state that above-mentioned transferring element can rotate in linkage with above-mentioned connecting member thus, on the other hand, above-mentioned transmission lifter cam be in rise state time, above-mentioned link cam part is removed with the engaging of above-mentioned transmission cam part, becomes the state that above-mentioned connecting member can rotate independent of above-mentioned transferring element thus.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPJP2012-087026 | 2012-04-06 | ||
| JP2012-087026 | 2012-04-06 | ||
| JP2012087026A JP6016418B2 (en) | 2012-04-06 | 2012-04-06 | Gas control valve |
| PCT/JP2013/058957 WO2013150934A1 (en) | 2012-04-06 | 2013-03-27 | Gas control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104220811A true CN104220811A (en) | 2014-12-17 |
| CN104220811B CN104220811B (en) | 2016-12-14 |
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| 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) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108267558A (en) * | 2018-01-19 | 2018-07-10 | 五矿勘查开发有限公司 | Water environment monitoring device and method |
| CN108463669A (en) * | 2016-02-24 | 2018-08-28 | 科佩西西班牙集团有限公司 | For gas cooker adjustment valve and include it is described adjustment valve gas cooker |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
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- 2012-04-06 JP JP2012087026A patent/JP6016418B2/en active Active
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2013
- 2013-03-27 CN CN201380018882.8A patent/CN104220811B/en active Active
- 2013-03-27 WO PCT/JP2013/058957 patent/WO2013150934A1/en active Application Filing
- 2013-03-27 KR KR1020147028027A patent/KR102061063B1/en active IP Right Grant
- 2013-03-27 ES ES13772967T patent/ES2825040T3/en active Active
- 2013-03-27 EP EP13772967.9A patent/EP2835583B1/en active Active
- 2013-04-03 TW TW102112174A patent/TWI601898B/en active
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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 |
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| CN108463669A (en) * | 2016-02-24 | 2018-08-28 | 科佩西西班牙集团有限公司 | For gas cooker adjustment valve and include it is described adjustment valve gas cooker |
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| CN108267558A (en) * | 2018-01-19 | 2018-07-10 | 五矿勘查开发有限公司 | Water environment monitoring device and method |
Also Published As
| Publication number | Publication date |
|---|---|
| TWI601898B (en) | 2017-10-11 |
| JP2013217539A (en) | 2013-10-24 |
| WO2013150934A1 (en) | 2013-10-10 |
| EP2835583A1 (en) | 2015-02-11 |
| JP6016418B2 (en) | 2016-10-26 |
| TW201341695A (en) | 2013-10-16 |
| CN104220811B (en) | 2016-12-14 |
| KR102061063B1 (en) | 2020-02-20 |
| EP2835583B1 (en) | 2020-08-26 |
| EP2835583A4 (en) | 2015-11-11 |
| ES2825040T3 (en) | 2021-05-14 |
| KR20150004338A (en) | 2015-01-12 |
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