CN1095108C

CN1095108C - Pressure adjusting apparatus balanced by press-spring-press

Info

Publication number: CN1095108C
Application number: CN 96106136
Authority: CN
Inventors: 蒋元元
Original assignee: Individual
Current assignee: Individual
Priority date: 1996-04-18
Filing date: 1996-04-18
Publication date: 2002-11-27
Anticipated expiration: 2016-04-18
Also published as: CN1162778A

Abstract

The present invention relates to a pressure-spring-pressure balanced pressure regulator. Both ends of a pressure regulating spring assembly are respectively pressed against an upper membrane and a lower membrane, the other sides of the two membranes are respectively provided with an air chamber communicated with an air path needing pressure regulation and are provided with an intake valve linked with the upper membrane and an exhaust valve linked with the lower membrane to form two sets of pressure-spring balance mechanisms, wherein the two sets of pressure-spring balance mechanisms share the same spring, but are relatively and mutually independent and respectively control the generation and the exhaust of unloading air. Therefore, the pressure-spring-pressure balanced pressure regulator can save energy, can make the two valves which are completely independent in design and arrangement flexibly act, can keep the two valves reliably synchronous and harmonious and can ensure the reliable operation of a pneumatic system.

Description

Pressure-spring-pressure balance type regulator

The present invention relates to the regulator that the pressure of gas that source of the gas in the pneumatic system is exported is controlled, relate in particular to the regulator of employing pressure-spring balancing mode.

In pneumatic system, pressure stability is the prerequisite of system stability.Therefore, the pressure of the gas of exporting for the source of the gas of air compressor machine in the pneumatic system etc. must effectively be controlled.The existing regulator that carries out this kind control generally adopts pressure-spring balancing regulator, this kind device utilizes the balancing component of pressure spring and diaphragm and so on, makes regulator realize the purpose of control automatically in the balance-unbalanced change procedure of spring and gaseous tension.At present, this kind regulator is broadly divided into two classes.Employed regulator in the Pneumatic braking system of a kind of for example the Yellow River NJ150 type automobile, this kind regulator generally is provided with: spirality pressure spring by compression, be fixed in the voltage regulation diaphragm of this pressure spring one end, be located at the opposite side of this voltage regulation diaphragm and the work air chamber that communicates with the air tank of storing from the pressure gas of air compressor machine, the off-load air chamber that is connected with the relief arrangement that makes above-mentioned air compressor machine off-load, the tiny air hole that this off-load air chamber is communicated with atmosphere, and constitute valve block by described voltage regulation diaphragm, open or close the diaphragm valve of the connected entrance between described work air chamber and the described off-load air chamber.Its principle of work is, after air compressor machine is started working, the pressurized air that air compressor machine produces charges into the work air chamber that air tank enters this regulator again through retaining valve, atmospheric pressure acts on above-mentioned voltage regulation diaphragm and passes to pressure spring through voltage regulation diaphragm, gaseous tension in the gaseous tension in the air tank is promptly worked air chamber reaches set pressure when (being about 0.68-0.70MPa), act on that gaseous tension on the voltage regulation diaphragm forces voltage regulation diaphragm and pressure spring one end that presses with it produces the displacement that makes the pressure spring compression, thereby the diaphragm valve between work air chamber and the off-load air chamber is opened, pressurized air enters the off-load air chamber and enters relief arrangement again, the work of promotion relief arrangement, relief arrangement makes the air compressor machine outlet pipe communicate with atmosphere, realize the off-load dry run, thereby the air pressure of air tank is no longer risen, promptly remain above-mentioned set pressure.After this, with the consumption of braking and the ease stream of air hole, also promptly the work air pressure of air chamber of the air pressure of air tank descends gradually, when air pressure falls after rise to 0.68MPa when following, the elastic force of pressure spring resets diaphragm valve and closes, thereby cut off the path of work air chamber and off-load air chamber, the air pressure of off-load air chamber descends rapidly because of the ease stream of air hole, thereby makes air compressor machine recover to inflate to air tank.

This regulator has only one group of pressure-spring equalizing device, and action is sensitive, can be pressure control (about 0.02MPa) within very little fluctuation range.But, because it only implements valve control to the generation of off-load air pressure, and the off-load gas purging is not carried out valve control, that is, all the time by air hole effusion off-load pressure gas, so must cause the loss of energy.

Another kind of regulator also has one group of pressure-spring equalizing device, but it is designed to valve can control the combination valve of air inlet, exhaust, with generation and the discharge that the gas admittance valve part and the vent valve part of interlock are controlled off-load gas respectively, cancelled the air hole that effusion off-load gas is used simultaneously.This device is owing to the discharging to the off-load compressed gas has also realized valve control, so help energy-conservation.But the regulator of the more above-mentioned employing separate valve of its sensitivity structure is for poor.Because in the ordinary course of things, the balancing component for example area that is subjected to gas pressure of diaphragm and valve will directly influence the action sensitivity of device.Diaphragm is subjected to the area of gas pressure big more, and then Zhuan Zhi action is sensitive more, but increases the increase that diaphragm diameter must cause the device overall dimension, therefore correspondingly then must consider to reduce as far as possible the diameter of valve.In the regulator of above-mentioned employing separate valve structure, owing to can adopt rational valve mechanism, and can under condition feasible on the technology, do valve as much as possible little, with the compression area of relative increase diaphragm, so can improve the sensitivity of diaphragm valve.But concerning the regulator that adopts combination valve, owing between its pressure regulation work air chamber and the off-load air chamber slipper seal must be set, and the structure of its inlet and outlet form and valve etc. can influence the size of valve, cause the actual air pressure active area that is subjected to of diaphragm less relatively, influence its action sensitivity, so the fluctuation range of its controlled pressure is big (greater than 0.1MPa).

The objective of the invention is to, provide a kind of to the off-load compressed gas generation and discharging can both be controlled thereby energy loss is little and the fluctuation of pressure can be controlled at more among a small circle in regulator.

Regulator provided by the invention is a kind of pressure-spring-pressure balance type regulator, comprise and be roughly columnar housing and be located at the interior one group of pressure-spring balancing mechanism of this housing, this group pressure-spring balancing mechanism has in the end of being located at described housing, the housing inner chamber is divided into the air inlet side air chamber that communicates with the gas circuit of required pressure regulation and with atmosphere the first elasticity voltage regulation diaphragm of the exhaust cavity of intercommunicating pore is arranged, be located at the interior spirality compression pressure spring of exhaust cavity of described housing, adjusting the adjustment screw of the compression pretightning force of this pressure spring pays, the off-load air chamber that links to each other with the relief arrangement of outside by gas passage, and described off-load air chamber is connected or mutually open close with described air inlet side air chamber to send or to cut off the off-load gas gas admittance valve of off-load gas by the described first elasticity voltage regulation diaphragm mobile, it is characterized in that, the other end at described housing, also be provided with a crossbeam across housing both sides sidewall, on this crossbeam, be provided with and make the exhaust hole that is connected with described exhaust cavity towards the gas passage of described off-load air chamber, and, relative configuration with described one group of pressure-spring balancing mechanism and shared same pressure spring and one are adjusted another group pressure-spring balancing mechanism that screw is paid, described another group pressure-spring balancing mechanism also is provided with the other end of relatively being located at described housing with the described first elasticity voltage regulation diaphragm, the housing inner chamber is separated out again the second elasticity voltage regulation diaphragm of the exhaust side air chamber that is connected with described air inlet side air chamber by the gas passage in the housing, with and foot strides across described crossbeam and the described second elasticity voltage regulation diaphragm presses, its bridge floor portion and described adjustment screw are paid the bridge bracket of crossing that presses and can be seated at described crossbeam, and, side at described exhaust hole is provided with a vent valve valve seat, one vent valve valve body is fixed in the described second elasticity voltage regulation diaphragm directly or indirectly, and close or open described exhaust hole, thereby constitute vent valve by this vent valve valve seat and vent valve valve body with moving up and down of this voltage regulation diaphragm.

Pressure-spring provided by the invention-pressure balance type regulator, because be provided with two groups of shared same springs pressure-spring balancing mechanism independently relatively mutually again, and control mutually the independently gas admittance valve of off-load gas and the vent valve of off-load gas respectively with these two groups of balanced controls, make the design of one of them valve and the influence that configuration can not be subjected to another valve fully, also slipper seal needn't be set, therefore, not only can all realize control completely to the generation and the discharging of off-load gas, and, two valves that move along with same spring both can keep stablizing fully of its action and synchronous reliably and coordination, can reduce this two back pressures that valve is subjected to by design again as far as possible, promptly, increase the actual area that is subjected to gas pressure of diaphragm relatively, thereby the sensitivity that improves valve event is worked reliably to guarantee pneumatic system.

Below, further specify design feature of the present invention and action effect by the accompanying drawing illustrated embodiment.

Brief description:

Fig. 1 is the cut-open view of regulator first embodiment of the present invention.

Fig. 2 is the course of action key diagram of regulator shown in Figure 1.

Fig. 3 is the cut-open view of regulator second embodiment of the present invention.

Following with reference to description of drawings one embodiment of the present of invention.

As shown in Figure 1, the housing of regulator of the present invention is made up of loam cake 1, middle shell 2 and lower cover 3, clamping upper diaphragm (i.e. the first elasticity voltage regulation diaphragm) 4 and following diaphragm (i.e. the second elasticity voltage regulation diaphragm) 5 between loam cake 1 and the middle shell 2 and between middle shell 2 and lower cover 3 respectively, and formation first air chamber is an air inlet side air chamber 6 between loam cake 1 and upper diaphragm 4, and forming second air chamber between lower cover 3 and following diaphragm 5 is exhaust side air chamber 7.In the bottom of the through hole (not shown) of loam cake 1 is fixed with, establish the valve seat 8 of through hole 8a, be fixed with the interface 9 of giving vent to anger that is connected with outside relief arrangement, be provided with filter screen 10 in the through hole 9a of the interface 9 of giving vent to anger on the top of the through hole of loam cake 1.Upside at upper diaphragm 4 is provided with steel valve block (not shown), constitute diaphragm type gas admittance valve 12 by upper diaphragm 4, steel valve block and valve seat 8, the through hole 8a and the through hole 9a that are positioned at these gas admittance valve 12 downstreams become the first off-load air chamber and the second off-load air chamber that communicates with outside relief arrangement respectively.Middle shell 2 is roughly cylindrical, connect the crossbeam 2a of relative sidewall but be provided with one in its underpart, and on sidewall, be provided with an air hole (not shown) cavity in the middle shell 2 is communicated with ambient atmosphere all the time, therefore, this cavity is in atmospheric pressure all the time, becomes exhaust cavity 2b.Be provided with pressure spring assembly 14 in the exhaust cavity 2b of middle shell 2, spring tray 14b, pressure regulating screw that this pressure spring assembly 14 comprises spiral fashion compression pressure spring 14a, be located at pressure spring 14a upper and lower end are paid 14c and are crossed bridge bracket 14d.The upper end of pressure spring 14a is pressed against on the upper diaphragm 4 by the spring tray 14b of its upper end and the diaphragm support (not shown) of upper diaphragm 4 downsides, and the spring tray 14b of lower end by its lower end is pressed against pressure regulating screw and pays on the adjustment nut (not shown) of 14c.Be provided with to look up in the lower end that pressure regulating screw is paid 14c and be criss-cross lug boss 14e, corresponding, on the face relative of the bridge floor portion (not shown) of crossing bridge bracket 14d with cruciform lug boss 14e, be provided with to overlook and be criss-cross groove (not shown), cross bridge bracket 14d and pressure regulating screw and pay 14c and press mutually, thereby prevented that pressure regulating screw from rotating with the state of this groove and lug boss 14e tabling.Crossing the crossbeam 2a that shank 14f that bridge bracket 14d stretches out strides across middle shell 2 downwards is resisted against down on the diaphragm support (not shown) of diaphragm 5.Therefore, whole pressure spring assembly 14 is quick condition, and its upper and lower end can move up and down with upper and lower diaphragm 4,5 respectively.In addition, offer the adjustment window of using for the pretightning force of adjusting pressure spring 14a (not shown) on the sidewall of the exhaust cavity 2b in the middle shell 2, and be provided with the dust cap (not shown) of this adjustment window of sealing.

Substantial middle position at the crossbeam 2a of middle shell 2, be provided with the exhaust hole 2c of above-below direction, below this exhaust hole 2c, offer and communicate with it and groove 2d that diameter is bigger, sealed lid 17 gas-tight seals of the lower openings of groove 2d form vent valve cavity 2g between gland bonnet 17 and groove 2d.And the lower periphery of exhaust hole 2c forms the seam formula valve seat 2f of ring-type downwards promptly to vent valve cavity 2g internal projection.Section is that exhaust valve 15 15a of its bar portion of inverted T-shape (see that Fig. 2 a) passes exhaust hole 2c from bottom to top from groove 2d, its upper end was fixed on the bridge bracket 14d by being threaded, therefore, exhaust valve 15 can be with crossing moving up and down and moving up and down of bridge bracket 14d, make its valve body part 15b (see that Fig. 2 a) is close to or leaves seam formula delivery valve seat 2f, 2c closes or opens with this exhaust hole, therefore, constitutes vent valve 16 by seam formula delivery valve seat 2f and exhaust valve 15.In addition, the vent valve cavity 2g that forms between gland bonnet 17 and groove 2d is on the one hand by the exhaust hole 2c of above-mentioned above-below direction can communicate with the exhaust cavity 2b middle shell 2 in (when vent valve 16 unlatchings), on the other hand, gas passage 2h by being located at horizontal stroke and perpendicular direction in the middle shell 2 and be located at gas passage 1h in the loam cake 1 is that the second off-load air chamber 9a is connected all the time with the through hole of the interface 9 of giving vent to anger.

In addition, in the lower through-hole of lower cover 3, be provided with intake interface 18 and filter screen 19.Be in the exhaust side air chamber 7 by this filter screen 19 with second air chamber that the through hole 18a of intake interface 18 communicates all the time, the lower end of spirality auxiliary spring 20 by compression is pressed against on the inner end wall of lower cover 3, and the upper end is pressed against down on the diaphragm 5 by the diaphragm support of following diaphragm 5.Again, second air chamber 7 is by being located at the first gas passage 3h in the lower cover 3 and being located at the second gas passage 2j in the middle shell 2 and being located at the 3rd gas passage 1j in the loam cake 1, is connected all the time with first air chamber 6 in the loam cake 1.

The following course of action that regulator of the present invention is described with reference to Fig. 2.

When the pressure of the Pneumatic braking system that regulator of the present invention is used for motor vehicle, control brake system, as shown in Figure 2, the intake interface of regulator is connected with the air tank of storage from the pressure gas of air compressor machine, and the interface of giving vent to anger of regulator is connected with the relief arrangement that makes the air compressor machine off-load, and pays the set pressure that makes regulator and be set at needed pressure by adjusting pressure regulating screw.Because first air chamber 6 and second air chamber 7 are connected with inlet channel in the intake interface 18 all the time, so, first and first air chamber 6 that is connected, promptly be full of pressure gas in 7 from air tank, like this, pressure spring assembly 14 be subjected to first respectively, the upper diaphragm 4 of the gaseous tension in second air chamber, following diaphragm 5 and gas admittance valve 12, vent valve 16 just forms pressure-spring-pressure equilibrium mechanism, promptly, form one group of pressure-spring balancing mechanism that contends with by spring force and gaseous tension substantially and form in the upper end of pressure spring assembly 14, organize the pressure-spring balancing mechanism that contends with by spring force and gaseous tension substantially and form and form another in the lower end of pressure spring assembly 14, the shared same pressure spring 14a of these two groups of mechanisms, and can distinguish on the controlling Design fully independently gas admittance valve 12 and vent valve 16.

When air compressor machine is not started working thereby air pressure is zero when being atmospheric pressure as yet, though or air compressor machine has been started working but the interior gaseous tension of the pressure of gas also promptly is connected in the air tank first air chamber 6 and second air chamber 7 when not reaching set pressure as yet, because the effect of the pretightning force of pressure spring 14a, pressure spring 14a both direction up and down opens, thereby shown in Fig. 2 (a), upper diaphragm 4 is pressed against on the valve seat 8, promptly, gas admittance valve 12 is in closed condition, and first air chamber 6 does not communicate with first, second off-load air chamber 8a, the 9a and the gas passage 21 that lead to relief arrangement.Meanwhile, same because the effect of the pretightning force of pressure spring 14a, the bottom that makes pressure spring assembly 14 is promptly crossed bridge bracket 14d and is in the minimum position that makes vent valve 16 standard-sized sheets (when air pressure equals atmospheric pressure), promptly, cross bridge bracket 14d and be seated on the crossbeam 2a that is provided with valve seat 2f this moment, the valve seat 2f distance that the valve body 15 that was fixed in bridge bracket 14d leaves vent valve 16 farthest, perhaps, made bridge bracket 14d be in lower position (when air pressure is higher than atmospheric pressure), also make the valve body 15 that was fixed on the bridge bracket 14d leave the seam formula valve seat 2f of vent valve 16 this moment, promptly, this moment, vent valve 16 was in opening, therefore, lead in the gas passage 21 of relief arrangement with middle shell in exhaust cavity 2b interior the same, be in atmospheric pressure, relief arrangement is failure to actuate, so air compressor machine works on, the gaseous tension in the air tank is risen.

When the gaseous tension in the air tank reaches set pressure, though upper diaphragm 4 equates with the total area of following diaphragm 5, but because valve seat 8 is close on the upper diaphragm 4, the actual air pressure that is subjected to that makes upper diaphragm 4 is added the acting force of auxiliary spring 20 less than the following diaphragm 5 actual air pressure that are subjected to, so, following diaphragm 5 at first is pushed upwardly, and then promoted bridge bracket 14d and drove valve body 15 to move up, be pressed against on the seam formula valve seat 2f until valve body 15, vent valve 16 is closed.This moment is shown in Fig. 2 (b), gas admittance valve 12 all is in closed condition with vent valve 16, therefore, first air chamber 6 reaches the gas passage 21 that leads to relief arrangement with first, second off-load air chamber 8a, 9a and does not still communicate, the vent valve cavity 2g that communicates with the second off-load air chamber 9a then no longer be in atmospheric pressure under the exhaust cavity 2b (see figure 1) that communicates, no longer communicate thereby make with ambient atmosphere towards first, second off-load air chamber 8a, 9a and the gas passage 21 of relief arrangement.

The rising of the gaseous tension in first and second air chamber that causes along with the work because of air compressor machine, pressure spring 14a is further compressed.At this moment, because of the bottom of pressure spring assembly 14 by spacing can not further the moving up of seam formula valve seat 2f, so the upper end of pressure spring assembly 14 is promoted and moves down by air pressure, that is, upper diaphragm 4 is pushed away valve seat 8, and gas admittance valve 12 is opened.So the pressure gas in first air chamber 6 becomes off-load gas and enters relief arrangement by gas admittance valve 12, first, second off-load air chamber 8a, 9a and gas passage 21, so the relief arrangement action makes air compressor machine do the off-load dry run.This state is shown in Fig. 2 (c), that is, gas admittance valve 12 is in opening; And this moment, though the gaseous tension of diaphragm 4,5 is equal about acting on, but because the vent valve cavity 2g in the crossbeam 2a is connected with the second off-load air chamber 9a, be full of off-load gas in it at this moment, make the valve body 15 of vent valve 16 be subjected to upward to back pressure, add the acting force that makes progress of auxiliary spring 20, so, valve body 15 still is pressed against on the valve seat 2f, and vent valve 16 still is in closed condition.At this moment, the air pressure in the air tank also is that the air pressure in the Pneumatic braking system is done the off-load air transport because of air compressor machine then no longer risen, and keeps original pressure substantially.

Along with braking waits the compressed-air actuated consumption that forms, the air pressure of air tank descends gradually.The decline of air pressure makes pressure spring 14a desire two ends extension up and down, but because in the bottom, valve body 15 be subjected to off-load gas upward to the effect of back pressure, and down diaphragm 5 be subjected to auxiliary spring 20 upward to acting force, so, temporarily still does not uphold downwards the bottom of pressure spring 14a, vent valve 16 temporarily still keeps closed condition, and pressure spring 14a upholds at first upward, with upper diaphragm 4 jack-up upwards, make on its valve seat that is pressed against gas admittance valve 12 8, thereby gas admittance valve 12 cuts out.The state of this moment is identical with state shown in Fig. 2 (b).

Because gas admittance valve 12 has cut out, upper diaphragm 4 has been pressed against on the valve seat 8, so pressure spring 14a can not continue upwards to uphold again.But the off-load air pressure in the gas passage 21 of off-load this moment gas still exists, and makes air compressor machine still do the off-load dry run, causes the air pressure of air tank still to continue to descend because of can not get replenishing.The continuation of air pressure descends pressure spring 14a is further shunk, and because of can not upwards upholding, so uphold, makes the valve body 15 of vent valve 16 2f that lifts off a seat downwards, and vent valve 16 unlatchings are in atmospheric exhaust cavity 2b release off-load gas to all the time.So relief arrangement makes air compressor machine restart the inflation action because of the effect that no longer is subjected to the off-load pressure gas stops the off-load action, and the gaseous tension in the air tank is gone up again.That is, return to the state shown in Fig. 2 (a) this moment.After this, repeat above-mentioned process again, the gas circuit of need pressure regulation is controlled automatically from Fig. 1 (a) to Fig. 1 (c).

Aforesaid regulator, because be provided with fully independently gas admittance valve and vent valve, so, not only can control the generation and the discharging of off-load gas respectively, do not waste energy, and the size shape of gas admittance valve and vent valve and position configuration etc. can not be subjected to the other side's influence, and the degree of freedom of design is big, therefore the sensitivity that can improve response valve.Again because when vent valve 16 is closed, as long as have off-load gas in the off-load air chamber, vent valve valve body 15 just can be subjected to upward to back pressure, so, at state shown in Fig. 2 (c), when the consumption air pressure with pressure gas descends gradually, when pressure spring is desired both direction stretching, extension up and down, though the suffered air pressure of two voltage regulation diaphragms is equally big, but since exhaust side to add also that exhaust valve 15 is subjected to upward to back pressure, even do not establish auxiliary spring 20, pressure spring also always stretches at first upward, to guarantee at first to close gas admittance valve 12, guarantees can stably make in certain air pressure range air compressor machine to do the off-load dry run.Therefore, regulator of the present invention can not established auxiliary spring.Vent valve valve body 15 be subjected to upward to back pressure mutability is arranged when vent valve is being opened, promptly vent valve can be opened quickly, avoids producing like the Kai Feikai state, thereby can avoid occurring jitter phenomenon, makes the air pressure of the gas circuit of being controlled more stable.Present embodiment is provided with auxiliary spring, then can make more reliable in above-mentioned course of action, the action stably of above-mentioned gas admittance valve and vent valve.

Fig. 3 shows the second embodiment of the present invention.As can be seen from Figure 3, the first half of the regulator among this embodiment and above-mentioned identical is so omit explanation to it.Different is the structure of header portion and vent valve.Specifically be, on the upper side of crossbeam 2a, there is not connected entrance with exhaust cavity 2b, the exhaust hole 2c that communicates with gas passage 2h is opened on the downside of crossbeam 2a, be fixed with the valve seat 2f that establishes through hole on this opening, and vent valve valve body 15 is fixed on directly relatively on the second elasticity voltage regulation diaphragm 5 with valve seat 2f by nut (not shown) etc.The vent valve 16 that is made of such vent valve valve body 15 and vent valve valve seat 2f also can be the same with the vent valve among above-mentioned first embodiment, when vent valve 16 is being opened, moving up of the second elasticity voltage regulation diaphragm that its valve body can cause along with the rising because of the air pressure in the gas circuit of need control, until exhaust hole 2c is closed fully, equally, when vent valve 16 is being closed, moving down of the second elasticity voltage regulation diaphragm that its valve body can cause along with the decline because of the air pressure in the gas circuit of need control, therefore, the course of action of the device among its course of action and above-mentioned first embodiment is basic identical.This valve body 15 directly is fixed on vent valve on the diaphragm, compares with the vent valve among above-mentioned first embodiment, its structure is simpler, and the part number is less, assembles more convenient.But because when exhaust valve closure, valve body 15 is subjected to the off-load air pressure that downward direction is the opening of valves direction, is the assurance device correct operation, generally auxiliary spring 20 should be set.

In two above-mentioned embodiment, the housing of regulator is divided into loam cake, middle shell and lower cover three parts, and upper and lower diaphragm is installed in respectively between loam cake and middle shell and lower cover and the middle shell, this spline structure is simpler, is convenient to processing and manufacturing.But the present invention is not limit by this, and the assembly structure of housing and diaphragm can be taked other forms.

In two above-mentioned embodiment, the adjustment screw of regulator was paid bridge bracket and was pressed mutually with the state of cross groove tabling with cruciform lug boss provided thereon respectively, make the adjustment screw pay bridge bracket not only in the axial direction, and on rotation direction, also be combined into one, for example when adjusting the pretightning force of pressure spring, adjust screw and promptly can not rotate with the rotation of adjusting nut.Certainly, the present invention is not restricted to the described embodiments, and for example can make the adjustment screw pay bridge bracket with square indentations with square boss portion yet and combine.

Claims

1. pressure-spring-pressure balance type regulator comprises being roughly columnar housing and the one group of pressure-spring balancing mechanism that is located in this housing, and this group pressure-spring balancing mechanism has:

Be located in the end of described housing, the housing inner chamber be divided into the air inlet side air chamber (6) that communicates with the gas circuit of required pressure regulation and with atmosphere the first elasticity voltage regulation diaphragm (4) of the exhaust cavity (2b) of intercommunicating pore arranged,

Be located at the interior spirality compression pressure spring (14a) of exhaust cavity (2b) of described housing,

Adjust the adjustment screw of the compression pretightning force of this pressure spring (14a) and pay (14c),

The first off-load air chamber (8a) and the second off-load air chamber (9a) that link to each other with the relief arrangement of outside by gas passage, and,

The described first off-load air chamber (8a) and the second off-load air chamber (9a) are connected or mutually open close with described air inlet side air chamber (6) by the described first elasticity voltage regulation diaphragm (4) mobile, it is characterized in that to send or to cut off the off-load gas gas admittance valve (12) of off-load gas:

The other end at described housing, also be provided with a crossbeam across the housing two side (2a), on this crossbeam (2a), be provided with and make the exhaust hole (2c) that is connected with described exhaust cavity (2b) towards the gas passage (2h) of the described first off-load air chamber (8a) and the second off-load air chamber (9a), and

A relative configuration with described one group of pressure-spring balancing mechanism and a shared pressure spring (14a) and one are adjusted another group pressure-spring balancing mechanism that screw is paid,

Described another group pressure-spring balancing mechanism also is provided with:

Relatively be located at the other end of described housing with the described first elasticity voltage regulation diaphragm (4), the housing inner chamber be separated out the second elasticity voltage regulation diaphragm (5) of the exhaust side air chamber (7) that is connected with described air inlet side air chamber (6) by first gas passage (3h) in the housing, second gas passage (2j) and the 3rd gas passage (1j) again, and

Its foot (14f) strides across that described crossbeam (2a) and the described second elasticity voltage regulation diaphragm (5) press, its bridge floor portion pays the mistake bridge bracket (14d) that (14c) pressed and can be seated at described crossbeam (2a) with described adjustment screw,

And, side at described exhaust hole (2c) is provided with a vent valve valve seat (2f), one vent valve valve body (15) is fixed in the described second elasticity voltage regulation diaphragm (5) directly or indirectly, and close or open described exhaust hole (2c), thereby constitute vent valve (16) by this vent valve valve seat (2f) and vent valve valve body (15) with moving up and down of this voltage regulation diaphragm (5).

2. pressure-spring according to claim 1-pressure balance type regulator, it is characterized in that, in described crossbeam (2a), be provided with a vent valve cavity (2g) that communicates with described gas passage (2h), described exhaust hole (2c) is opened in the top of this vent valve cavity (2g), described valve seat (2f) is made of to the annular projection of lower convexity the lower periphery from described exhaust hole (2c), the section of described vent valve valve body (15) is roughly inverted T-shape, and the bar portion (15a) of this valve body (15) runs through this exhaust hole (2c) from bottom to top and is fixed in the described bridge bracket (14d) of crossing.

3. pressure-spring according to claim 1-pressure balance type regulator, it is characterized in that, described exhaust hole (2c) is opened on the downside of described crossbeam (2a), be fixed with described valve seat (2f) on it, described vent valve valve body (15) relatively is fixed in the described second elasticity voltage regulation diaphragm (5) with described valve seat (2f), and, in described exhaust side air chamber (7), also be provided with auxiliary spring (20), one end of this auxiliary spring (20) withstands on the described second elasticity voltage regulation diaphragm (5), and the other end withstands on the medial surface of described shell end.

4. pressure-spring according to claim 1 and 2-pressure balance type regulator, it is characterized in that, also be provided with auxiliary spring (20) in the described exhaust side air chamber (7), one end of this auxiliary spring (20) withstands on the described second elasticity voltage regulation diaphragm (5), and the other end withstands on the medial surface of described shell end.

5. according to each described pressure-spring-pressure balance type regulator among the claim 1-3, it is characterized in that, described housing is made up of loam cake (1), middle shell (2) and lower cover (3), the described first elasticity voltage regulation diaphragm (4) is installed between described loam cake (1) and the described middle shell (2), and the described second elasticity voltage regulation diaphragm (5) is installed between described lower cover (3) and the described middle shell (2).

6. according to each described pressure-spring-pressure balance type regulator among the claim 1-3, it is characterized in that, offer the adjustment window that the pretightning force of adjusting described pressure spring (14a) is used on the sidewall of the exhaust cavity (2b) of described housing, and be provided with and close the used dust cap of this adjustment window.

7. according to each described pressure-spring-pressure balance type regulator among the claim 1-3, it is characterized in that described adjustment screw is paid (14c) and pressed mutually and be integral with the described cross groove and the cruciform lug boss (14e) of bridge bracket (14d) by tabling of crossing.