CN1278066C - Pressure reducer and its selecting method and cold and hot water supply ystem using said device - Google Patents
Pressure reducer and its selecting method and cold and hot water supply ystem using said device Download PDFInfo
- Publication number
- CN1278066C CN1278066C CN 02104517 CN02104517A CN1278066C CN 1278066 C CN1278066 C CN 1278066C CN 02104517 CN02104517 CN 02104517 CN 02104517 A CN02104517 A CN 02104517A CN 1278066 C CN1278066 C CN 1278066C
- Authority
- CN
- China
- Prior art keywords
- valve
- outlet port
- pressure
- water
- decompressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Control Of Fluid Pressure (AREA)
- Fluid-Driven Valves (AREA)
Abstract
The present invention provides a pressure reducing device, hot and cold water supply system using said pressure reducing device, and method of selecting the pressure reducing device used in said system. The system is provided with a main valve 17 for opening/closing a valve port 11 communicating the primary side pressure chamber 8 and the secondary side pressure chamber 9 provided inside a main body 2 energized in a valve closing direction by a spring 19 and formed by partitioning a diaphragm chamber 14 provided on the back side and the primary side pressure chamber 8 with a diaphragm 13 interlocked with the main valve 17, and a pilot conduit 3 provided between the primary side pressure chamber and the secondary side pressure chamber while interposing a pressure reducing valve 4. In the conduit 3, a branch conduit 3a provided on the primary side of the pressure reducing valve is connected to the diaphragm chamber, and a restrictor 20 is provided on the upstream side of a branch point. Thus, the quantity of water to be passed from the primary side pressure chamber of the main body to a primary side pressure chamber 25 of the pressure reducing valve and the diaphragm chamber is restricted by said restrictor.
Description
Invention field
The present invention relates to a kind of decompressor, a kind of hot and cold water supply system and a kind of system of selection that is used in the decompressor in the said system of using above-mentioned decompressor.
Background technique
For traditional pressure conveying-type hot and cold water supply system, cold feed pipe and hot water service pipe are connected on the combination water nozzle, and the cold/hot water of preset temperature for example water nozzle or shower or shower tap are supplied out from a water tap at the service terminal place of each family (room).
Yet in said system, the variation that appears at cold feed load in cold feed pipe or the hot water service pipe and hot water service load will be accompanied by variation in pressure, therefore can cause the water temperature at the water tap place of each family to change.
Causing a reason of this problem is Directacting reducing valve, and the waste side of its pump in being loaded on every cold feed pipe and hot water service pipe is being connected pipeline.
Because the discharge pressure height of pump, so reduction valve is installed in cold feed pipe and the hot water service pipe in the above described manner, pressure is reduced to the rank that can use at the cold feed tube terminal in the occasions such as each family or hot water service tube terminal place.
Therefore, for above-mentioned decompressor, the amplitude of variation of valve outlet port pressure for the cold/hot water consumption is bigger, and when causing the cold/hot water consumption to change owing to each water tap of use, because the respective valve outlet pressure of cold feed pipe and hot water service pipe changes greatly, therefore the flow rate of the flow rate of the water that flows out based on preset temperature and from the cold feed pipe and the water that flows out from the hot water service pipe will change, thereby the pressure that causes cold feed side or hot water service side in use descends suddenly or rises, and the cold/hot water that therefore causes being below or above preset temperature is supplied out.
Although utilizing this reduction valve is corresponding flow rate in order to ensure hot water and cold water, the diaphragm diameter of reduction valve must be very big with respect to the ratio of valve port diameter, and this can make reduction valve itself become too big, thereby can not drop into practical application.
The present invention's general introduction
An object of the present invention is to provide and relate to a kind of decompressor, a kind of hot and cold water supply system and a kind of system of selection that is used in the decompressor in this system of using this decompressor, thereby make that confined water can be with the stable manner supply, even when consumption changes.
Consider above-mentioned theme, be provided with a main valve in the present invention, one of them main valve that is used to open and close valve port is pushed along closing direction by a spring, valve inlet pressure chamber and valve outlet port pressure chamber that this valve port is used for being located at the main valve body interior take connected state to, and a diaphragm that links to each other with main valve is separated a diaphragm chamber and a valve inlet pressure chamber that is located at the diaphragm rear side; A pilot line that reduction valve is housed is arranged between above-mentioned valve inlet pressure chamber and the valve outlet port pressure chamber, and in above-mentioned pilot line, a take-off line that is located at reduction valve inlet side (upstream side) is connected to above-mentioned diaphragm chamber, and a throttling utensil is installed in the upstream of point of branching, by means of this throttling utensil, can limit from the valve inlet pressure chamber of valve body inlet pressure chamber inflow reduction valve and the water yield the diaphragm chamber, therefore the pressure in the diaphragm chamber can reduce, thereby causes main body to be opened when reduction valve is opened because of water.
That is to say, when water, if valve outlet port pressure drops to below the preset value, then have the water yield identical and flow through main body, so that valve outlet port pressure can not fall sharply with water consumption.Therefore, even consumption changes, also can supply water with pressure stable.
In addition, by decompressor of selecting based on the condition of fixedly installing of equipment in the hot and cold water supply system, can supply the hot water of ideal temperature with stable manner, thereby solve previously described problem.
Therefore, by first aspect of the present invention, because the pilot line 3 of reduction valve 4 is housed to be installed between the valve inlet pressure chamber 8 and valve outlet port pressure chamber 9 of the main body 2 with said structure, and because in pilot line 3, the take-off line 3a that is installed in the valve inlet side of reduction valve 4 is connecting diaphragm chamber 14, and throttling utensil 20 is installed in the upstream of point of branching M, therefore, when the valve outlet port side water owing to main body 2 causes reduction valve 4 to be opened, the valve outlet port pressure P
4Can drop to set pressure P
sBelow, at this moment, owing to flow to the valve inlet pressure chamber 25 of reduction valve 4 and the flow Q of diaphragm chamber 14 from the valve inlet pressure chamber 8 of main body 2
2By 20 restrictions of throttling utensil, that is to say, owing to have such structure, promptly in the valve outlet port pressure P
4From its set pressure P
sDrop to tolerance zone lower limit P
LThe time, the flow rate Q of reduction valve 4
1Be set to the flow rate Q that surpasses by 20 restrictions of throttling utensil
2, therefore, pilot valve inlet pressure P
2Pressure P with diaphragm chamber 14
3Will be immediately sharply descend, so that main valve 17 is along opening that direction moves and opening with diaphragm 13.
Like this, therefore the water yield identical with consumption can flow through valve port 11, and because consumption is consistent basically with the water yield that flows through valve port, so the valve outlet port pressure P
4Can not descend significantly.That is to say, by satisfying above-mentioned condition flow rate Q
1＞flow rate Q
2, can carry out pressure control to decompressor 1 by reduction valve 4, thereby be less than or equal at consumption under the situation of consumption peak Fm, make the valve outlet port pressure P
4Be positioned at and preset the valve outlet port pressure P
sWith tolerance zone lower limit P
LBetween, therefore, with increasing along with consumption and causing the prior art of valve outlet port pressure sharp fall to be compared, the pressure amplitude in the control procedure is constriction significantly.
Therefore, by the present invention, confined water can be with the stable manner supply, even when consumption changes.
In addition, because decompressor 1 is based on detection threshold outlet pressure P by one
4And the main body 2 that flow rate is regulated in the reduction valve 4 that control main body 2 opens and closes and order according to reduction valve 4 constructs, therefore compare with prior art, the ratio of the effective diameter of the diaphragm 13 of valve port diameter and main body 2 can diminish, and therefore main body 2 can make compactly more.
By second aspect of the present invention, because independent throttling utensil 21 is installed among the take-off line 3a of above-mentioned decompressor 1, therefore, flow between the valve inlet pressure chamber 25 of reduction valve 4 and diaphragm chamber 14 through throttling utensil 21 and the flow of outflow can be limited, thereby make pressure P in the diaphragm chamber 14
3Can not change suddenly, even at the pilot valve inlet pressure P of reduction valve 4
2Because of the water of the valve outlet port side of main body 2 or when stopping water and changing.Along with pressure P
3This variation and therefore the operation of the main valve 17 of the main body 2 that opens and closes can be carried out gradually, thereby can prevent from water attack and other problems to occur because of the upstream side that main valve 17 opens or cuts out suddenly in main body 2.
The 3rd aspect of the present invention provides hot and cold water supply system Z, wherein the cold feed pipe X1 that comes out of the downstream side branch of the decompressor with said structure 1 from cold water feed line X and hot water feed line Y and hot water service pipe Y1 are combined in a combination water nozzle C and are connected to a water tap W, and because each decompressor 1 is selected, thereby be less than or equal at consumption under the situation of consumption peak Fm, make the valve outlet port pressure P
4Be positioned at tolerance zone, even when the consumption of the cold water at each water nozzle C place or hot water changes, therefore, the valve outlet port pressure P
4Only in tolerance zone, change, and the flow rate of cold water that flows out based on preset temperature and from cold water feed line X and the hot water that flows out from hot water feed line Y can not change.Therefore cold/hot water with preset temperature can be supplied out from water tap W with stable manner.
The 4th aspect of the present invention provides hot and cold water supply system Z1, wherein cold feed pipe X1 that branch comes out between the corresponding decompressor 1 with said structure from cool water circulating pipe Xa and hot water circulating pipe Ya and Flow-rate adjustment utensil X3 and the Y3 and hot water service pipe Y1 are combined in a combination water nozzle C and are connected to a water tap W, and because each decompressor 1 is selected, even thereby consumption has surpassed the consumption peak Fm of cold water or hot water, the valve outlet port pressure P
4Also can be positioned at tolerance zone, and corresponding cool water circulating pipe Xa and hot water circulating pipe Ya are set in the flow rate range, this flow rate range is by drawing based on the consumption limit Fs of above-mentioned tolerance zone and the difference that presets between the consumption peak Fm, therefore, even circulation flow-rate is provided with to such an extent that be less than or equal to the difference that consumes between limit Fs and the water consumption peak Fm, be to have surpassed in the scope of consumption limit Fs of cold/hot water consumption peak Fm the valve outlet port pressure P then in maximum value
4Amplitude of variation with respect to consumption also can remain in the tolerance zone.
Because valve outlet port pressure P
4Initial value therefore can reduce and preset the corresponding force value of circulation flow-rate, so valve outlet port pressure P
4Amplitude of variation constriction correspondingly, thereby the preset temperature of the hot water that further flows out based on the cold water that flows out from cold water feed line X with from hot water feed line Y and stablize flow rate and so and makes the supply of cold/hot water of preset temperature more stable.
In addition, by cold water feed line X and the hot water feed line Y of hot and cold water supply system Z, even stop simultaneously in the use of each water tap W, and pilot valve inlet pressure P
2When rising, also can prevent the pressure P of diaphragm chamber 14 because of closing of reduction valve 4
3Raise immediately, and main valve 17 can be opened lentamente by throttling utensil 21, therefore have a kind of like this possibility, promptly because water can be from the valve inlet side inflow valve outlet port side of main body 2 in the time at this spacer segment, so the pressure of the valve outlet port side of main body 2 trends towards being elevated to and presets the valve inlet pressure P
f, close until valve.Yet, for hot and cold water supply system Z1, because (circulation) flow rate among each cool water circulating pipe Xa and hot water circulating pipe Yas the consistently circulation of water to preset be not even therefore in these cases, the pressure of the valve outlet port side of main body 2 can be elevated to yet and preset the valve inlet pressure P
f
Because the water of fixed amount can be therefore and the main body 2 of flowing through consistently, therefore can prevent from when the consumption of certain water tap W hangs down, to produce seismism, and because cold water and hot water cycle through cool water circulating pipe Xa and hot water circulating pipe Ya respectively, the cold/hot water that therefore has preset temperature can use immediately at water tap W place.This just makes water system to want whole day to use in the occasion of cold/hot water usually in hospital, hotel etc. and uses extremely easily and easily.
By the 5th aspect of the present invention, because the flow characteristic curve a to c of the different candidate's main valves shown in the flow characteristic plotted curve II is converted and is presented among the flow characteristic plotted curve I, wherein (cold water or hot water consumption peak Fm preset the valve inlet pressure P to plotted curve I based on the selected project of hot and cold water supply system Z and Z1
f, preset the valve outlet port pressure P
sAnd valve outlet port pressure P
4Amplitude of variation with respect to cold water or hot water consumption) shows the flow characteristic curve A that is connected with the reduction valve 4 of throttling utensil 20 at upstream side, and owing to main valve 2 is selected like this, promptly in the intersecting point coordinate Ra to Rc of the flow characteristic curve a to c of the flow characteristic curve A of above-mentioned reduction valve 4 and candidate's main valve, surpass above-mentioned consumption peak Fm and with respect to presetting the valve outlet port pressure P
sThe difference minimum be the intersecting point coordinate of flow characteristic curve a, like this, main valve 2 corresponding to this curve a is chosen, therefore satisfies the various main valves 2 that condition is set on performance and can be selected simply, and can utilize flow characteristic plotted curve I and the performance of definite decompressor 1.
Particularly when selecting to be used for each decompressor 1 of hot and cold water supply system Z1, if the performance of selected main valve is feasible, even cold water or hot water consumption have surpassed consumption peak Fm, the valve outlet port pressure P
4Also can be positioned at tolerance zone, and based on the consumption limit Fs of tolerance zone and preset the respective cycle flow rate range that difference between the consumption peak Fm can be positioned at cool water circulating pipe Xa and hot water circulating pipe Ya, then the main valve performance can be read from flow characteristic plotted curve I, and therefore circulation flow-rate can be determined in this scope.
In addition, draw though the flow characteristic curve A of the reduction valve 4 that shows in flow characteristic plotted curve I utilizes upstream side at reduction valve 4 to connect the result who measures behind the throttling utensil 20, and this reduction valve is to preset the valve outlet port pressure P
sBe positioned at and select under this condition of pressure regulation range, and its layout makes, in the valve outlet port pressure P
4Arrive tolerance zone lower limit P
LThe time, satisfy (flow rate of reduction valve 4) Q
1＞(by the supply flow rate of throttling utensil 20 restrictions) Q
2, but because at Q
1＞Q
2Condition under, the flow characteristic curve A is a straight line that has to the right the gradient of declivity slightly and be basically parallel to the x axle of plotted curve I, and because this gradient is basic fixed for any reduction valve 4, therefore it is just enough simply to depict a flow characteristic curve A, and this curve is with the valve outlet port pressure P
4In flow rate 0 o'clock preset value P
sBe starting point, and have above-mentioned gradient.
By the 6th aspect of the present invention,, the flow characteristic curve A of the reduction valve 4 that shows passes valve outlet port pressure P as previously mentioned in flow characteristic plotted curve I because being one basically
4Tolerance zone lower limit P
LHorizontal linear (the x axle that is parallel among the plotted curve I expression flow rate), even therefore the flow characteristic curve A is replaced the represented straight line of dot and dash line by the length among Fig. 9 and replaces, when selecting main valve 2, do not have problem yet.Therefore, can provide significant practical effect, for example make that the plotted curve I that uses is easier to prepare or the like in this selection.
The accompanying drawing summary
Fig. 1 is a kind of sectional view of decompressor.
Fig. 2 is the amplification view of main valve.
Fig. 3 is the amplification view of reduction valve.
Fig. 4 has been to use the pipeline schematic representation of the hot and cold water supply system of decompressor.
Fig. 5 has been to use the pipeline schematic representation of the circulating hot and cold water supply system of decompressor, wherein (a) is with the pipeline schematic representation of needle-valve as the system of Flow-rate adjustment utensil, (b) is with needle-valve and the relief valve combination pipeline schematic representation as the system of Flow-rate adjustment utensil.
Fig. 6 is its flow characteristic plotted curve when having only reduction valve to be used in the decompressor.
Fig. 7 is the flow characteristic plotted curve of decompressor.
Fig. 8 is flow characteristic plotted curve I, shows connecting the throttling utensil and having the respective flow characteristic curve that difference presets the corresponding reduction valve of valve outlet port pressure.
Fig. 9 is flow characteristic plotted curve I, and a flow characteristic curve wherein shown in Figure 8 is called in, and respective flow characteristic curve shown in Figure 10 is converted and shows.
Figure 10 is flow characteristic curve II, shows the flow characteristic curve of each candidate's main valve.
Figure 11 is a conversion table.
Figure 12 is based on the flow characteristic plotted curve of the measured value of the decompressor that has used each candidate's main valve.
Figure 13 is the flow characteristic plotted curve of prior art.
Preferred embodiment is described in detail
Based on accompanying drawing one embodiment of the present of invention are described below.
A kind of guide has been shown among Fig. 1 has made the dynamic formula decompressor.This decompressor 1 mainly comprises main valve main body 2, and it is installed on every cold feed pipe and the hot water service pipe, and a reduction valve 4, and it is connecting main body 2 by a pilot line 3.
The clack box 5 that is arranged in the main body 2 has inlet 6 and the outlet 7 that is open in its right side and left side respectively, and is arranged in the clack box 5 with inlet 6 and outlet 7 valve inlet pressure chambers 8 that are communicated with and valve outlet port pressure chamber 9 respectively.Valve inlet pressure chamber 8 and valve outlet port pressure chamber 9 are separate and be respectively formed at the outside and the inboard of clack box 5 inside by a partition 10.One is formed in the partition 10 along the valve port 11 of direction points upwards with inlet 6 quadratures, and valve inlet pressure chamber 8 and valve outlet port pressure chamber 9 can reach by this valve port 11 and communicate with each other.
In addition, an opening 5a who is communicated with valve inlet pressure chamber 8 and valve port 11 is arranged on the top of clack box 5, and this opening 5a is by a diaphragm 13 sealing, and this diaphragm is clipped between clack box 5 and the bonnet 12 that covers on the clack box 5.
On the lower surface of diaphragm 13, a main valve 17 is disposed such out, the lower surface that is diaphragm 13 stretches out in the mode of general toroidal, thereby it is corresponding with a valve seat 16 along the periphery setting of valve port 11, and by the main valve 17 of formation with diaphragm 13 one, main valve 17 is coupled with diaphragm 13.
Roughly discoidal diaphragm pressing plate 18 and 18a correspond respectively on the upper surface that main valve 17 is combined in diaphragm 13 and in main valve 17 inboards and are combined on the lower surface of diaphragm 13.
A spring 19 is clipped between the top and diaphragm pressing plate 18 of diaphragm chamber 14 with compressive state, and main valve 17 is pushed to closing direction by this spring 19.
In the valve outlet port pressure P
4From its set pressure P
sDrop to tolerance zone (hot and cold water can with the scope of steady pressure supply) lower limit P
LThe time, flow (the flow rate Q of reduction valve 4
1) be set to supply (the flow rate Q that surpasses by 20 restrictions of throttling utensil
2).
That is to say that reduction valve is set to and meets the following conditions: Q
1＞Q
2
Therefore, the hot and cold water supply system that decompressor 1 is housed preset consumption peak Fm or when following, decompressor 1 makes the valve outlet port pressure P
4Can be controlled in the tolerance zone.
Be provided with an edge on the top of clack box 22 upward to the roughly recessed portion 29 of dish that opens wide.The part of the bottom of this recessed portion 29 be open wide and be communicated with valve outlet port pressure chamber 26, and recessed portion 29 is by 31 sealings of a diaphragm, this diaphragm is clipped between recessed portion 29 and the spring cup 30 that covers on the recessed portion 29.
Being provided with an opening 36 with valve port 28 corresponding recessed portion 29 lower central, be used for being communicated with valve inlet pressure chamber 25, also have a cylindrical shape part 37 to be set to from opening 36 extension downwards continuously with predetermined length.
Simultaneously, a valve rod 38 that passes cylindrical shape part 37 and valve port 28 is formed on diaphragm 31 central authorities in sagging mode, and valve plug 39 that is used to open and close valve port 28 is arranged on the lower end of valve rod 38.
Valve plug 39 is arranged in such a way, and promptly can attach with valve seat 40 and separate, and this valve seat is arranged on the periphery of valve port 28, absorbs valve inlet pressure to open direction along valve, and valve plug 39 open by the mobile control of diaphragm 31.
In addition, a piston 41 that slides along the inwall of cylindrical shape part 37 is located on the intermediate portion of valve rod 38 in outwards outstanding mode, an O shape circle 42 is loaded on the periphery of piston 41, so that valve inlet pressure chamber 25 and recessed portion 29 (valve outlet port pressure chamber 26) are isolated in the mode of water tightness.
The operation of decompressor 1 is described based on Fig. 1 now.
Following content at first is described below:
The valve inlet pressure P
1Be the pressure of the upstream side that links to each other with the valve inlet pressure chamber 8 of main body 2,
The valve outlet port pressure P
4Be the pressure in the downstream side that links to each other with the valve outlet port pressure chamber 9 of main body 2,
Pilot valve inlet pressure P
2Be the pressure of the upstream side that links to each other with the valve inlet pressure chamber 25 of reduction valve 4 in the pilot line 3,
The diaphragm chamber pressure P
3Be the pressure in the diaphragm chamber 14 of main body 2, and
P
f(below be called and preset the valve inlet pressure P
f) be the set pressure of the valve inlet side of main body 2,
P
s(below may also be referred to as and preset the valve outlet port pressure P
s) be the valve outlet port pressure P that is provided with by reduction valve 4
4(pressure) value, as shown in Figure 1.
When the valve outlet port side closure of main body 2, main body 2 and reduction valve 4 are closed respectively, and the every pressure among Fig. 1 keeps following condition:
P
1=P
2=P
3=P
f, and P
4=P
s
After the valve outlet port side is opened from above-mentioned closed condition, because the valve outlet port pressure P
4From its set pressure P
sDescend, so reduction valve 4 will open, thereby cause pilot valve inlet pressure P
2From presetting the valve inlet pressure P
fDescend, and in reduction valve 4, form mobile.
In this state, because the flows that flow to the valve inlet pressure chamber 25 of reduction valve 4 from upstream side (the valve inlet pressure chamber 8 of main body 2) are subjected to the restriction of throttling utensil 20, therefore in the valve outlet port pressure P
4Drop to and be lower than set pressure P
sAfter, be in (guide) valve inlet pressure P of the reduction valve 4 of open mode
2To sharply descend immediately, that accompanies therewith is the diaphragm chamber pressure P of main body 2
3To descend too, and main valve 17 will move and open along opening direction, thereby cause valve inlet pressure chamber 8 and valve outlet port pressure chamber 9 to be communicated with, and water will be through main body 2 and from the valve inlet effluent to the valve outlet port side.
Because the flows that flow to the valve inlet pressure chamber 25 of reduction valve 4 from diaphragm chamber 14 are subjected to the restriction of throttling utensil 21, therefore above-mentioned diaphragm chamber pressure P
3Pressure reduce and to carry out to such an extent that relax than valve inlet pressure chamber 25.
The opening therefore but carry out gradually of main valve 17, and can prevent from water attack and other problems to occur because of the upstream side that main valve 17 is opened in main body 2.
Here, in the valve outlet port pressure P
4Drop to tolerance zone lower limit P
LThe time, above-mentioned condition Q
1＞Q
2To be satisfied, this be because, by decompressor 1, only in the valve outlet port pressure P
4Drop to tolerance zone lower limit P
LCould supply consumption peak Fm afterwards, and in this case, in order to open main body 2 so that from decompressor 1 supply consumption peak Fm, unless in the valve outlet port pressure P
4Drop to tolerance zone lower limit P
LAfter make flow (the flow rate Q of reduction valve 4
1) surpass from supply (the flow rate Q of throttling utensil 20 outflows
2), otherwise the valve inlet pressure P
2Pressure drop that main valve 17 is opened can not appear being enough in expection.Therefore, by above-mentioned condition is set, be less than or equal at consumption under the situation of consumption peak Fm, in the valve outlet port pressure P
4Be positioned at and preset the valve outlet port pressure P
sTo tolerance zone lower limit P
LScope in, decompressor 1 can be implemented stable control by means of reduction valve 4.
Fig. 6 has only single reduction valve selected (not connecting throttling utensil 20) and presets the valve outlet port pressure P
sIts flow characteristic plotted curve during for 0.30MPa (the x axle is consumption (flow rate), and the y axle is a valve outlet port pressure).When the valve outlet port pressure P
4Tolerance zone lower limit P
LDuring for 0.27MPa,, from Fig. 6, can leave, because reduction valve 4 is in the valve outlet port pressure P supplying under the situation of consumption peak Fm
4Flow rate Q during for 0.27MPa
1Be 8l/min, therefore by flow rate Q with 20 restrictions of throttling utensil
2Be arranged on less than 8l/min, can implement the control of aforesaid way.
So, if cause the valve outlet port pressure P because of valve outlet port side water
4Drop to set pressure P
sBelow, then the valve port 11 of main body 2 will be opened, so that flow through valve port 11 with the water of consumption equivalent, and because consumption is consistent with the water yield that flows through valve port basically, so the valve outlet port pressure P
4It is too many can not descend, and the amplitude of variation of this pressure is compared therefore and significantly constriction with the reduction valve of prior art.
Also can be expressly understood the flow characteristic plotted curve (Figure 13) that concerns between the flow characteristic plotted curve (Fig. 7) of this relation between the consumption (x axle) that shows decompressor 1 and valve outlet port pressure (y axle) and the consumption (x axle) that shows Directacting reducing valve of the prior art (below be called " prior art ") and the valve outlet port pressure (y axle).
Plotted curve among Fig. 7 and 13 is based on the measurement result of following condition: consumption peak is set to 300l/min, presets the valve inlet pressure P
fBe set to 0.50MPa, the reduction valve 4 of decompressor 1 and prior art reduction valve preset the valve outlet port pressure P
sBe set to 0.30MPa.
For decompressor 1 (Fig. 7), valve outlet port pressure P
4Valve outlet port pressure P when the amplitude of variation in consumption is 0 to 300l/min scope equals 0l/min
4Valve outlet port pressure P when (=0.30MPa) and 300l/min
4Difference between the (=0.27MPa), promptly about 0.03MPa.
In contrast, for prior art (Figure 13), the valve outlet port pressure P during 0l/min
4Valve outlet port pressure P when (=0.30MPa) and 300l/min
4Difference between the (=0.10MPa) is approximately 0.20MPa, and is very obvious, the valve outlet port pressure P of decompressor of the present invention
4Amplitude of variation narrower than prior art.
Opening when above-mentioned flowing water state stops of valve outlet port side, preset the valve outlet port pressure P at flowing water time ratio
sLow valve outlet port pressure P
4Will be owing to raising from main body 2 supply water, and reach at this pressure and to preset the valve outlet port pressure P
sThe time, the valve plug 39 of reduction valve 4 will be closed in the identical moment, and since this closing, pilot valve inlet pressure P
2Can rise to and preset the valve inlet pressure P
f
Here, the throttling utensil 21 that is branched among the pipeline 3a owing to the water yield that flows through diaphragm 14 limits, so the diaphragm chamber pressure P
3To rise gradually, main valve 17 will be accompanied by that this pressure raises and slowly move along the closing direction of diaphragm 13, when the diaphragm chamber pressure P
3Equal to preset the valve inlet pressure P
fThe time, main valve 17 cuts out, to stop passing through of water.
Used the pipeline schematic representation of the hot and cold water supply system Z of decompressor 1 to be shown among Fig. 4.
For this hot and cold water supply system Z, be equipped with decompressor 1 respectively among cold water feed line X and the hot water feed line Y, and in the downstream side of decompressor 1, many cold feed pipe X1 and hot water service pipe Y1 come out from cold water feed line X and hot water feed line Y branch respectively.Cold feed pipe X1 and the hot water service pipe Y1 from hot water feed line Y from cold water feed line X is combined in a combination water nozzle C place and is connected to a water tap W.
For cold water feed line X, constant current rate and proposed for variable flow rate pump XP1 and XP2 are parallel-connected to, perhaps arbitrary pump XP1 and XP2 are connected to the supply side of water storage tank X2, and the inlet 6 of the main body 2 of decompressor 1 is connecting the waste side of pump XP1 and XP2, and export 7 downstream sides that are connected to cold water feed line X.
The line arrangement of hot water feed line Y and foregoing basic identical.That is to say that constant current rate in parallel and proposed for variable flow rate pump YP1 and YP2 or arbitrary pump YP1 and YP2 and decompressor 1 begin to install according to said sequence from the supply side of water storage tank Y2, water storage tank Y2 is equipped with heating equipment H, for example electric water heater, boiler or the like.
For cold water feed line X and hot water feed line Y, the device (not shown) that is used for detection pressure or flow rate variation is installed in the position of the upstream side of the waste side that is positioned at pump XP1, XP2, YP1 and YP2 and main body 2, and by these sniffers, the quantity of pump XP1, XP2, YP1 and the YP2 of running can increase or reduce, perhaps can change the running time of pump XP1, XP2, YP1 and YP2, to change flow rate and pressure.
The operation of the decompressor 1 among the hot and cold water supply system Z is described based on Fig. 1 and 4 below.
Be used in each decompressor 1 in this hot and cold water supply system and be based on that the system of selection described hereinafter selects, so that when the cold/hot water consumption is less than or equal to the cold/hot water consumption Fm of setting, make the valve outlet port pressure P
4Be positioned at tolerance zone (cold/hot water can with the scope of steady pressure supply).
Here, the decompressor 1 with flow shown in Figure 7 is used under the following condition: maximum cold/hot water consumption is set to 300l/min, presets valve inlet pressure and is set to 0.50MPa, presets valve outlet port pressure and is set to 0.30MPa.
Be appreciated that (see figure 7), for decompressor 1, as long as maximum cold/hot water consumption is set to 300l/min or following, the valve outlet port pressure P with above-mentioned flow
4Amplitude of variation with respect to the cold/hot water consumption just can suitably remain in the tolerance zone (approximately 0.03MPa).
Therefore, after the water tap W of this hot and cold water supply system Z is opened, will be in combination water nozzle C mixing by foregoing same operation with cold water and the hot water supplying out from cold water feed line X and hot water feed line Y based on the suitable flow rate of preset temperature.
At this moment, even change (in the scope of the consumption peak Fm of 300l/min) because of another water nozzle C place water causes the cold/hot water consumption, but because consistent with consumption basically flow rate will flow through main body 2, to keep the valve outlet port pressure P
4Amplitude of variation (approximately 0.03MPa), therefore the flow rate of the flow rate of the cold water that flows out from cold water feed line X and the hot water that flows out from hot water feed line Y can not change, thereby the cold/hot water with preset temperature will be supplied out from water tap W.
After each water tap W stopped from previously described flowing water state, main valve 17 was to cut out with identical mode noted earlier, and to stop to pass through of water, the running of pump XP1, XP2, YP1 and YP2 is then stopped by unshowned pressure or flow rate detection device.
Next will describe a kind of hot and cold water supply system Z1 based on Fig. 5, it is the retrofit case of hot and cold water supply system Z.
For hot and cold water supply system Z1, cold water feed line X among the above-mentioned hot and cold water supply system Z and the respective downstream end portion of hot water feed line Y are connected to the reflux side of water storage tank X2 and Y2, to form cool water circulating pipe Xa and hot water circulating pipe Ya.The parts identical with corresponding part among the hot and cold water supply system Z are represented with identical reference character, and are no longer described.
Have near Flow-rate adjustment utensil X3 and the Y3 of reflux side that is connected water storage tank X2 and Y2 among cool water circulating pipe Xa and the hot water circulating pipe Ya.
Flow-rate adjustment utensil X3 shown in Fig. 5 (a) and Y3 are needle-valve N, and they are placed the flow rate that presets of being fixed water is back to water storage tank X2 and Y2 consistently.
Each Flow-rate adjustment utensil X3 shown in Fig. 5 (b) and Y3 respectively by one forming with needle-valve N and a pressure-relief valve R who is installed in the bypass line that identical mode noted earlier is installed, this bypass line comes out and is connected to the reflux side of water storage tank X2 or Y2 from Circulation pipe Xa or Ya branch at some place, the upstream of needle-valve N.By this structure, flow rate in being back to water storage tank X2 or Y2 can not be supplied by needle-valve N, and the end side of Circulation pipe Xa or Ya becomes when equaling preset value, and pressure-relief valve R will open, so that water is back among water storage tank X2 or the Y2 consistently with the fixing flow rate that presets.
For respectively at the hot and cold water supply system Z1 shown in Fig. 5 (a) and 5 (b), Flow-rate adjustment utensil X3 and Y3 be not limited to previously described those, as long as it is just enough that the Flow-rate adjustment utensil possesses following function, promptly water can be back to water storage tank X2 or the Y2 from cool water circulating pipe Xa and hot water circulating pipe Ya consistently to preset flow rate.
The pressure or the flow rate detection device that are equipped among the hot and cold water supply system Z are not to install.
The operation of the decompressor 1 among the hot and cold water supply system Z1 is described based on Fig. 1 and 5 below.
For hot and cold water supply system Z1, be set up owing to be back to flow rate among water storage tank X2 or the Y2 (below be called circulating water flow), so the hot and cold water of preset value will cycle through cool water circulating pipe Xa and hot water circulating pipe Ya (no matter water tap W opens or closes) consistently by Flow-rate adjustment utensil X3 and Y3.
Be used in each decompressor 1 among this hot and cold water supply system Z1 and be based on that the system of selection described hereinafter selects, even, also can make the valve outlet port pressure P so that surpassed cold water or hot water consumption peak Fm
4Be positioned at tolerance zone (cold water or hot water can with the scope of steady pressure supply), and corresponding cool water circulating pipe Xa and hot water circulating pipe Ya be set in the flow rate range, and this flow rate range is by drawing based on the consumption limit Fs of tolerance zone and the difference that presets between the consumption peak Fm.
Here, the decompressor 1 with flow shown in Figure 7 is used under the following condition: consumption peak Fm is set to 300l/min, presets valve inlet pressure and is set to 0.50MPa, presets valve outlet port pressure and is set to 0.30MPa.
Be appreciated that (see figure 7), for decompressor 1, if circulation flow-rate is arranged on about 120l/min, even then consumption surpasses consumption peak Fm and reaches up to 420l/min (consuming limit Fs) the valve outlet port pressure P with above-mentioned flow
4Amplitude of variation with respect to consumption also can remain in the tolerance zone (approximately 0.03MPa), and above-mentioned circulation flow-rate is the difference that consumes between limit Fs and the consumption peak Fm.
Here, when each cool water circulating pipe Xa and hot water circulating pipe Ya are set to 50l/min, because the valve outlet port pressure P
4Under this flow rate about 0.29MPa, shown in the plotted curve among Fig. 7, so the valve outlet port pressure P of hot and cold water supply system Z1 when the cold/hot water consumption is 0 to 300l/min
4Amplitude of variation equal the valve outlet port pressure P of decompressor 1 when 0l/min
4(=approximately 0.29MPa) and valve outlet port pressure P when 300l/min
4The 0.27MPa of (=approximately) in other words the difference between, equals about 0.02MPa.The valve outlet port pressure P
4Amplitude of variation therefore and can be than the further constriction of above-mentioned hot and cold water supply system Z.
The system of selection of decompressor 1 is described below.
By this system of selection, used the hot and cold water supply system Z of decompressor 1 or Z1 consumption peak Fm, preset valve inlet and outlet pressure P
fAnd P
sAnd valve outlet port pressure P
4Amplitude of variation (tolerance zone lower limit P with respect to the cold/hot water consumption
L) be determined out, afterwards, will identify project based on these and implement following selection course.
Here, for purposes of illustration, will select under following condition: maximum cold/hot water consumption Fm is 300l/min, presets the valve inlet pressure P
fBe 0.50MPa, preset the valve outlet port pressure P
sBe 0.30MPa, and the valve outlet port pressure P
4With respect to set pressure P
sTolerance zone lower limit P
LBe 0.27MPa.
1. selection reduction valve
(1) select a reduction valve 4, it presets the valve outlet port pressure P
sBe arranged in pressure regulation range (specification of reduction valve can be indicated the valve outlet port pressure range that can be provided with).
(2) next, prepare a flow characteristic plotted curve I, this there is shown the flow rate of this reduction valve 4 under the following conditions and the relation between the valve outlet port pressure, and promptly throttling utensil 20 is connected the upstream side of reduction valve 4, and in the valve outlet port pressure P
4From its set pressure P
sDrop to tolerance zone lower limit P
LThe time, flow (the flow rate Q of reduction valve 4
1) be set to supply (the flow rate Q that surpasses by 20 restrictions of throttling utensil
2).
Shown based on the setting of valve outlet port pressure with the form of curve among the flow characteristic plotted curve I and be the valve outlet port force value that 0 beginning measures when increasing flow rate gradually that wherein flow rate and valve outlet port pressure are represented with x axle among the plotted curve I and y axle respectively from flow rate.
By the flow characteristic curve A among the actual measurement profile figure I, wherein the flow characteristic curve of reduction valve 4 is the above-mentioned condition (Q that caused by throttling utensil 20
1＞Q
2) measure down, now confirmed, although cause the final plant closure pressure of each reduction valve 4 to differ from one another, be less than or equal under the situation that presets consumption peak Fm the valve outlet port pressure P at consumption because of the self-characteristic of reduction valve 4 is different
4All present to the right the gradient of declivity slightly, promptly from set pressure P
sDrop to tolerance zone lower limit P
L(one pass allowable pressure value P
LThe approximate horizontal straight line), and this gradient is actually fixing for any reduction valve 4.
Therefore,, can determine that also reduction valve 4 flow characteristic curve A under these conditions has the gradient of fixing declivity to the right, promptly roughly approach substantially horizontal (being parallel to the x axle), no matter and preset the valve outlet port pressure P even do not do measurement
s(see figure 8) how, and when selection main valve as described later, one is roughly parallel to the x axle and passes tolerance zone threshold pression value (allowable pressure value) P
LStraight line can be used as flow characteristic curve A (dot and dash line that the length among Fig. 9 replaces).
By the flow characteristic curve A among Fig. 8 with above-mentioned gradient, with flow rate be 0 o'clock corresponding a plurality of valve outlet port pressure P
4The value of setting P
s[0.40,0.30,0.20,0.10 (MPa)] is revealed, and based on relative set value P
sAnd the flow characteristic curve A with same slope is revealed.Here, since hot and cold water supply system Z or Z1 preset the valve outlet port pressure P
sBe confirmed as 0.30MPa, therefore, will preset the valve outlet port pressure P
sFlow characteristic plotted curve I after flow characteristic curve A during for 0.30MPa is called among Fig. 9 is used.
2. selection main valve
(1) obtain a plurality of candidate's main valves that are suitable for using, they have aforesaid same principle construction, and the main difference part is the diameter of valve port 11.
(2) prepare a flow characteristic plotted curve II (Figure 10), this there is shown the valve inlet pressure P of each candidate's main valve
1(valve inlet pressure P
1With the valve outlet port pressure P
4Between pressure reduction) and flow rate between relation.
Illustrated from valve port 11 in the form of flow characteristic plotted curve II with curve and be set at open mode, in other words, be set at 0 o'clock from valve outlet port pressure, flow-rate measurement result when improving valve inlet pressure gradually again, and valve inlet pressure (equaling the pressure reduction between valve inlet pressure and the valve outlet port pressure, because valve outlet port pressure is 0) and flow rate are represented with x axle among the plotted curve II and y axle respectively.
Flow characteristic plotted curve II among Figure 10 shows the flow characteristic curve a to c of corresponding candidate main valve.
(3) the flow characteristic curve a to c among the flow characteristic plotted curve II is converted and is presented among the flow characteristic plotted curve I that has described the flow characteristic curve A.
In plotted curve II, what the flow rate of valve inlet pressure during for 0.20MPa for example represented is the valve inlet pressure P
1Be 0.20MPa valve outlet port pressure P
4It is 0 o'clock flow rate.In other words, Ci Shi flow rate can be thought the valve inlet pressure P
1With the valve outlet port pressure P
4Between the flow rate of pressure reduction when being 0.20MPa.
Therefore, for flow characteristic curve a, when pressure reduction is 0.20MPa, that is to say, when the valve inlet pressure P
1Be 0.50MPa valve outlet port pressure P
4During for 0.30MPa, flow rate is 440l/min.
Presetting the valve inlet pressure P by what said procedure was changed out
fValve outlet port pressure P during for 0.50MPa
4With the results are shown in the table among Figure 11 of flow rate.
In the table in Figure 11,
α represents (the valve inlet pressure P of the pressure shown in the plotted curve II
1With the valve outlet port pressure P
4Between pressure reduction),
β represents to preset the valve inlet pressure P
fValve outlet port pressure P during for 0.50MPa
4,
In other words, β=P
f-α,
γ represent with plotted curve II in the corresponding flow rate of α (flow).
β shown in the above-mentioned conversion table and γ are plotted among the plotted curve I, to change and to be shown as flow curve a.
Equally, for flow characteristic curve b and the c among the plotted curve II, can prepare out conversion table (not shown) and conversion and be presented among the plotted curve I.
The result of the flow characteristic curve a to c that representative conversion is in the above described manner come out is presented among the flow characteristic plotted curve I that has described the flow characteristic curve A, as shown in Figure 9.
(4) in flow characteristic plotted curve I, flow characteristic curve A and conversion and the coordinate that demonstrates the intersection point Ra to Rc between the respective flow characteristic curve a to c are Ra (0.27,420), Rb (0.26,605) and Rc (0.26,680), even and these intersecting point coordinates Ra to Rc consumes flow rate variation also can implement the break point that steady pressure supplies water under corresponding situation, these situations are: selected reduction valve 4 is combined with different candidate's main valves, and is based on previously described terms and conditions use.
In plotted curve I shown in Figure 9, the flow characteristic curve A linked to each other with respective flow characteristic curve a to c and the curve that forms corresponding to the flow characteristic curve of the decompressor 1 that is combined to form by reduction valve 4 and main body 2.
In the break point Ra to Rc of each candidate's main valve, when having surpassed above-mentioned consumption peak Fm=300l/min, with respect to presetting the valve outlet port pressure P
s=0.30MPa difference minimum be the intersecting point coordinate Ra (0.27,420) of flow characteristic curve a.Therefore, chosen corresponding to the main valve 2 of this curve a.
By use the decompressor 1 that is formed by reduction valve of selecting by the way 4 and main body 2 combinations in hot and cold water supply system Z or Z1, even consumption changes, cold/hot water also can be with the pressure stable supply.
Relevant flow rate and valve outlet port pressure P under the corresponding situation when the reduction valve of selecting in the above described manner 4 being shown among Figure 12 making up with each candidate's main valve
4The flow characteristic plotted curve of measured value, wherein maximum cold/hot water consumption Fm is set to 300l/min, presets the valve inlet pressure P
fBe set to 0.50MPa, preset the valve outlet port pressure P
sBe set to 0.30MPa.
Flow characteristic curve J1, the J2 of each decompressor shown in Figure 12 and J3 in fact with the flow characteristic curve of the corresponding decompressor shown in Fig. 9 (A～a), (A～b) and (A～c) identical.Therefore can confirm,, needn't measure each decompressor that is combined to form by reduction valve 4 and candidate's main valve again by said method.
Claims (6)
1. decompressor, it is characterized in that, this device is provided with a main valve, wherein respectively be open in position, main valve main body both sides in entrance and exit the valve inlet pressure chamber and the valve outlet port pressure chamber that are communicated be formed on body interior in separate mode, valve inlet pressure chamber and valve outlet port pressure chamber can reach connected state by a valve port, one is arranged to output the main valve that opens and closes above-mentioned valve port and is pushed along closing direction by a spring, a diaphragm that links to each other with main valve is separated a diaphragm chamber and a valve inlet pressure chamber that is located at the diaphragm rear side, the pilot line that reduction valve is housed is arranged between above-mentioned valve inlet pressure chamber and the valve outlet port pressure chamber, and in above-mentioned pilot line, there is a take-off line that is installed in the reduction valve inlet side connecting above-mentioned diaphragm chamber, and there is a throttling utensil to be installed in the upstream of point of branching, dropped to from its set pressure under the state of tolerance zone lower limit at valve outlet port pressure, the flow rate in the reduction valve is set to and surpasses the flow rate that is limited by the throttling utensil.
2. decompressor as claimed in claim 1 is characterized in that, an independent throttling utensil is arranged in the take-off line.
3. hot and cold water supply system, it is characterized in that, arranging a cold water feed line in this system, wherein there are a pump and decompressor as claimed in claim 1 or 2 to be installed with said sequence since the supply side of a water storage tank, also arranging a hot water feed line in this system, wherein there are a pump and a decompressor as claimed in claim 1 or 2 to be equipped with the supply side of the water storage tank of heating equipment to be installed with said sequence since one, cold feed pipe and hot water service Guan Zaiyi the combination water nozzle that comes out from the downstream side branch of the corresponding decompressor of cold water feed line and hot water feed line is bonded to each other respectively, be connected on the water tap, and owing to each decompressor is selected like this, promptly, dropped under the state of tolerance zone lower limit from its set pressure at valve outlet port pressure, flow rate in the reduction valve is set to and surpasses the flow rate that is limited by the throttling utensil, thereby main valve reaches maximum opening, and the consumption of cold water or hot water equals the consumption peak that presets of cold water or hot water.
4. hot and cold water supply system, it is characterized in that, arranging a cool water circulating pipe in this system, a pump is wherein arranged, the reflux side of water storage tank installed and is connected to by decompressor as claimed in claim 1 or 2 and Flow-rate adjustment utensil with said sequence since the supply side of a water storage tank, also arranging a hot water circulating pipe in this system, a pump is wherein arranged, the reflux side of water storage tank installed and is connected to by decompressor as claimed in claim 1 or 2 and Flow-rate adjustment utensil with said sequence since a supply side that is equipped with the water storage tank of heating equipment, cold feed pipe and hot water service Guan Zaiyi the combination water nozzle that comes out from branch between the corresponding decompressor of cold water feed line and hot water feed line and the Flow-rate adjustment utensil is bonded to each other respectively, be connected on the water tap, because the respective cycle current among cool water circulating pipe and the hot water circulating pipe are set in the flow rate range, this flow rate range is less than or equal to the consumption limit under the above-mentioned valve outlet port pressure tolerance zone lower limit state and the difference between the set pressure consumption peak, and each decompressor is selected like this, promptly, dropped under the state of tolerance zone lower limit from its set pressure at valve outlet port pressure, flow rate in the reduction valve is set to and surpasses the flow rate that is limited by the throttling utensil, thereby main valve reaches maximum opening, and the consumption of cold water or hot water can equal the consumption limit of cold water or hot water.
5. the method for the selection decompressor in having used the hot and cold water supply system of decompressor as claimed in claim 1 or 2, it is characterized in that, the consumption peak of cold/hot water, preset valve inlet and valve outlet port pressure and valve outlet port pressure and be determined with respect to the amplitude of variation of cold/hot water consumption; A kind of reduction valve is chosen so that determine preset the pressure regulation range that valve outlet port pressure is positioned at valve; The flow characteristic curve of the different candidate's main valves that show in the rating curve figure of a relation of having described pressure reduction between valve inlet side and the valve outlet port side and flow rate is converted and is shown in one and described in the above-mentioned reduction valve flow rate and the flow characteristic plotted curve of the relation of valve outlet port pressure under the following conditions, this condition is promptly: a throttling utensil is connected the reduction valve upstream side, and dropped under the tolerance zone in limited time from its set pressure at valve outlet port pressure, the reduction valve flow rate is set to and surpasses the flow rate that is limited by the throttling utensil; For a certain candidate's main valve, if the intersecting point coordinate of the flow characteristic curve of the flow characteristic curve of reduction valve and this candidate's main valve has surpassed above-mentioned consumption peak, and the intersection point of the flow characteristic curve of the flow characteristic curve of reduction valve and this candidate's main valve is with respect to the difference minimum that presets valve outlet port pressure, and then this main valve is chosen.
6. the method for selection decompressor as claimed in claim 5, it is characterized in that, the reduction valve flow characteristic curve that shows in the flow characteristic plotted curve of the relation of the flow rate of having described reduction valve and valve outlet port pressure is made into straight line, this straight line parallel is in the x axle of expression flow rate in above-mentioned flow characteristic plotted curve, and the tolerance zone lower-limit point of passing valve outlet port pressure.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001182666A JP2002373024A (en) | 2001-06-18 | 2001-06-18 | Pressure reducing device, cold/hot water supply system using the same, and method for selecting pressure reducing device to be used for the system |
| JP182666/2001 | 2001-06-18 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1392357A CN1392357A (en) | 2003-01-22 |
| CN1278066C true CN1278066C (en) | 2006-10-04 |
Family
ID=19022718
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 02104517 Expired - Fee Related CN1278066C (en) | 2001-06-18 | 2002-02-08 | Pressure reducer and its selecting method and cold and hot water supply ystem using said device |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP2002373024A (en) |
| CN (1) | CN1278066C (en) |
| HK (1) | HK1052962B (en) |
| SG (1) | SG111040A1 (en) |
| TW (1) | TW576902B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2620733C1 (en) * | 2016-08-04 | 2017-05-29 | Закрытое акционерное общество "ЮГГАЗСЕРВИС" | Automatic emergency closing of the crane of the gate of the gas pipe |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103821982B (en) * | 2014-03-06 | 2016-03-16 | 北京航空航天大学 | Pressure regulator valve |
| CN105443844B (en) * | 2015-12-19 | 2018-06-19 | 无锡锡压压缩机有限公司 | For the vacuum conditions valve gear of positive-displacement vacuum pump |
| CN106090369B (en) * | 2016-08-26 | 2019-03-19 | 天津市国威给排水设备制造有限公司 | A kind of piloted reducer |
| IT201800007629A1 (en) * | 2018-07-30 | 2020-01-30 | Pietro Fiorentini Spa | PRESSURE REDUCING SYSTEM WITH TWO OR MORE LINES OPERATING IN PARALLEL |
| EP3667181A1 (en) * | 2018-12-12 | 2020-06-17 | E.ON Sverige AB | Distribution pump arrangement for a hydraulic distribution system having changing flowing direction |
| CN113404919B (en) * | 2021-07-29 | 2022-09-06 | 四川长仪油气集输设备股份有限公司 | Controller subassembly has sealed voltage regulator of level four throttle |
| KR102599787B1 (en) * | 2021-11-30 | 2023-11-09 | (주) 삼진정밀 | Pulsation relief and pressure reducing ratio fixed type pressure reducing valve used in piping |
| CN115007530B (en) * | 2022-06-15 | 2024-01-05 | 宁波富斯乐机械制造有限公司 | Pressure regulating type high-pressure water cleaning machine and pressure regulating method thereof |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5142963A (en) * | 1991-10-25 | 1992-09-01 | Spectra-Physics Laserplane, Inc. | Load referenced pressure reducing valve |
| EP0701189A1 (en) * | 1994-08-13 | 1996-03-13 | DruVa-Armaturen GmbH | Pressure reducer |
-
2001
- 2001-06-18 JP JP2001182666A patent/JP2002373024A/en active Pending
- 2001-12-25 TW TW90132152A patent/TW576902B/en not_active IP Right Cessation
- 2001-12-27 SG SG200108066A patent/SG111040A1/en unknown
-
2002
- 2002-02-08 CN CN 02104517 patent/CN1278066C/en not_active Expired - Fee Related
-
2003
- 2003-07-15 HK HK03105095.0A patent/HK1052962B/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2620733C1 (en) * | 2016-08-04 | 2017-05-29 | Закрытое акционерное общество "ЮГГАЗСЕРВИС" | Automatic emergency closing of the crane of the gate of the gas pipe |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2002373024A (en) | 2002-12-26 |
| TW576902B (en) | 2004-02-21 |
| HK1052962A1 (en) | 2003-10-03 |
| HK1052962B (en) | 2007-01-26 |
| SG111040A1 (en) | 2005-05-30 |
| CN1392357A (en) | 2003-01-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1278066C (en) | Pressure reducer and its selecting method and cold and hot water supply ystem using said device | |
| CN1589369A (en) | Dual fuel injection valve and method of operating a dual fuel injection valve | |
| CN1745689A (en) | Optimize the pressure cooking appliance of decompression | |
| CN106151595B (en) | Water-saving spool and its fluid feed system | |
| EP2664830A1 (en) | Single-handle dual-control thermostatic faucets | |
| SG196845A1 (en) | Choke assembly | |
| CN102506180A (en) | Micro-flow regulating valve | |
| CN203395279U (en) | Small multi-channel combined type gas proportional valve | |
| CN101718358B (en) | Self-heating metal thermostatic tap | |
| CN1637358A (en) | Hot water storing and hot water supplying apparatus | |
| CN202901376U (en) | Constant temperature water mixing valve | |
| CN101509559A (en) | Thermostatic controlled valve | |
| CN105605300B (en) | Bypass constant-temperature water mixing valve | |
| CN1847732A (en) | Gas burning range | |
| CN104132166B (en) | Pressure regulator | |
| CN201715026U (en) | Constant-temperature faucet | |
| CN201547280U (en) | Constant temperature valve core and self-heating metal constant temperature faucet made of same | |
| CN206319366U (en) | Pull gondola water faucet module and Concealable tap and tank combining structure | |
| GB0911690D0 (en) | Constant temperature and balanced pressure pipeline valve | |
| US20180195629A1 (en) | Structure of energy-saving precision pressure adjusting valve | |
| CN202195576U (en) | Instant-heating type electric water heating device | |
| CN106151587B (en) | The valving and its fluid feed system of bilateral constant flow | |
| CN202812297U (en) | Water mixing valve | |
| CN209587146U (en) | A kind of high-temperature high-pressure regulating valve | |
| CN202955283U (en) | Thermostatic faucet |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20061004 Termination date: 20140208 |