CN1143069C - Direct-acting boost-enhanced pressure regulator - Google Patents

Abstract

A boost-enhanced gas pressure regulator (53) consists of a bonnet (11) and a body (12; main casing) that are secured together so as to capture a diaphragm (13) between both components. An actuator (16) providing a pair of control channels (38) and a relief seat (32) in one component is connected to the diaphragm (13) to be moved with and by the latter. A boost/seat tube (20) has external guide surfaces (49) which serve to guide and control its movement, and it also has an internal gas flow passage (52) in which an elastomeric seat disk (21; valve member) is mounted. The boost/seat tube (20) is restricted to travel in a linear fashion (direct action) with respect to an inlet orifice/valve seat (44) by a plurality of guide surfaces (49) that are an integral part of the orifice insert (44), upon which certain contact areas (70, 72) of the boost/seat tube (20) are slidable.

Description

Direct-acting step-up gas pressure regulator

The present invention can be used in many air pressure regulating applications, however, it is designed especially for use on propane outdoor cookers. For example, when an appliance has an inlet pressure of 250 psi, the unit can provide a constant pressure in the range of 11 inches of water. Many conventional devices used under these conditions suffer from three flow performance shortcomings that are inherent in their design. The first disadvantage is called the "droop characteristic", the pressure drop, and is caused by the change in the effective active area of the diaphragm as it moves, and the loss of load from the diaphragm control spring throughout the movement. These factors combine to cause the delivery pressure (output pressure) to decrease as the flow rate increases. The present invention partially overcomes this shortcoming by using a rate increase to compensate. The increased velocity places the diaphragm at a lower pressure than the controlled downstream pressure, which results in a larger valve opening and higher flow rates. A second disadvantage is hysteresis or backlash, which is caused in part by the change in direction of the friction force over the range of motion of the device. Hysteresis makes the performance of the device inconsistent. The present invention provides a novel floating mount for the valve train and speed increasing components that works with smooth rounded continuous guides and sliding surfaces that provide essentially point-contact control, low-friction contact for mechanism control, reducing the the impact of this shortcoming. This design, together with the new and improved component structure and operating mechanism, provides a device with novel control and operability which significantly improves the consistency of performance. A third disadvantage is due to physical blockage in the direction of the flow channel. The invention can eliminate all unnecessary blockages on the flow.

In summary, the principal object of the present invention is to provide a new and unique gas pressure regulator for use in propane outdoor cooking ranges and the like, which differs from the types commonly used in this field, and which has new and convenient construction and features which can Provides significant improvements. Another object of the present invention is to provide an improved performance single stage regulator valve having novel and convenient mechanical components which together provide a significant and unique improvement enabling the use of very small inlet apertures, small diaphragm diameters, and Small overall regulator size for ease of operation and reduced cost. It is a further specific object of the present invention to provide an improved pressure regulator valve having novel internals which provide speed increasing features in a new and improved manner. Another important object of the present invention is to provide an enhanced performance, low cost regulator which can be efficiently applied to automatic manufacturing equipment and which is easy to assemble. Other objects and other advantages of the invention will become apparent after studying the description.

These and other features, advantages and objects of the present invention will be further appreciated and understood by those skilled in the art upon review of the following specification, claims and drawings.

The following brief description of the drawings, and the drawings themselves, illustrate a specific preferred embodiment of the invention, which constitutes the best form presently contemplated. It can be understood that other embodiments of the present invention and changes and changes to the specific structures in the drawings are undoubtedly possible, and those skilled in the art will have good inspiration after studying the description and the drawings .

Figure 1 is a perspective view of an assembled pressure regulator of the present invention, illustrating the external features of a single outlet type of the device;

Fig. 2 is a perspective view of an assembled pressure regulator of the present invention, illustrating a dual outlet type external feature of the device;

Fig. 3 is a three-dimensional sectional view of a regulator of the present invention, illustrating the shape, position and interrelationship of the internal components of the device;

Figure 4 is an enlarged side sectional view of the regulator of the present invention, further illustrating the internal components and their respective features;

Figure 5 is a perspective view of a diaphragm assembly used in the regulator illustrated in the previous figure;

Figure 6 is a perspective view of the internal mechanism of a regulator, illustrating the speed increase/seat tube and its installation and operating mechanism;

Figure 7 is a right side view of the internal mechanism of the regulator shown in Figure 6;

Fig. 8 comprises Fig. 8A and 8B, is two perspective views, has illustrated the transmission member that is used for controlling the valve in the preferred embodiment, and it comprises a part of diaphragm assembly shown in Fig. 5;

Figure 9A is an end view of a preferred booster/seat tube configuration for use in a regulator;

Fig. 9B is a perspective view of an optimal speed increase/valve seat structure;

Figure 10A is a perspective view of a preferred orifice plug for use in a regulator;

Figure 10B is an end view of an optimal plug configuration;

Figure 11 is an enlarged front sectional view illustrating the gas inlet of the valve body and its inlet fittings and seals;

Figure 12 is an enlarged side view of a preferred overdrive/seat tube illustrating the force vectors acting thereon during operation.

Referring to Fig. 4, the regulating valve 53 is composed of a generally circular disc-shaped valve cover 11 and a corresponding valve body 12, and is folded on the flange 55 of the valve cover 11 by mechanically deforming the ring 54 on the valve body 12 , so that the valve cover 11 and the valve body 12 are fixed together. A generally circular fabric-reinforced elastic diaphragm 13 is sealingly secured between the valve cover 11 and the valve body 12 to form an upper chamber 57 and a lower chamber 56, the diaphragm 13 is characterized by a molded rolled Spin 31. The seal is formed by extruding the sealing bead 30, which protrudes from the periphery of the diaphragm 13 between the flange 55 and a sealing groove 28 at the top end of the valve body 12, and is spaced from the diaphragm 13. One. The amount of extrusion required to form the seal is controlled by an annular shoulder 29 which forms a rigid stop providing a seat for flange 55 . Diaphragm 13, diaphragm plate 14, pressure regulating spring (relief spring) 17, spring retainer 15 and transmission member 16 together constitute diaphragm assembly 59 (see FIG. 5).

The drive member 16 has an upstanding central post 42 (Figs. 7 and 8) with a plurality of longitudinal ribs 41 which assist in centering the diaphragm 13 and disc 14 during installation. The spring retainer 15 is a disk with a central hole 36 (FIG. 4) that slides along the post 42 of the drive member 16 and includes an annular skirt or edge 37 (FIG. 5) that Edge 37 presses pressure-adjusting spring 17 against diaphragm disk 14 . Diaphragm assembly 59 is preferably held in place by the operation of an ultrasonically heated rod which operates to position spring retainer 15 on post 42 of transmission member 16 . Transmission member 16 has a lower end 16A which contacts and interacts with speed increaser/seat tube 20 to form the control mechanism for the regulator valve, as will be described below. The control spring 18 ( FIG. 4 ) is compressed and centered between the upper inner surface 60 of the valve cover 11 and the ring 34 of the diaphragm disc 14 .

A valve seat disc 21 (Figs. 4 and 9B) is housed in the booster/valve seat tube 20 through the action of a valve seat bracket 50, which is centrally suspended in a smooth and unobstructed tubular passage 52 by a support rib 51. In (FIG. 9A), the tubular passage 52 extends longitudinally along the booster/seat tube. Speed-up/seat tube 20 is constrained to reciprocate in a linear direction only relative to valve seat 44, which is in-line with valve seat disc 21, which is defined by a plug member 19 (FIGS. 4 and 10). The plug 19 is secured to the valve body 12 by a pair of drive screws 23 and has an O-ring 22 which surrounds the cylindrical lower end 45 of the plug 1926 to form a seal between the plug 19 and the body 12 . The inlet 26 of the valve body 12 is designed to receive an inlet connection 65 (see FIG. 11 ) which connects the regulator valve 53 to a gas source, such as the valve of a propane supply bottle. O-ring 67 forms a seal between inlet fitting 65 and valve body 12 to prevent leakage of gas into the surrounding environment. The inlet fitting 65 is fixed in the valve body 12 by mechanically deforming the inlet protrusion 68 on the valve body 12 so that the material on the protrusion 68 is pressed into the groove 66 .

Referring to Fig. 4, the compressed gas from the gas source is sent to the inlet 26, and the gas flows into the channel 61 through the inlet 26, and passes through the hole 43 (when the valve mechanism is opened), the valve seat disc 21 and the outer periphery of the valve seat bracket 50 and the tubular Speed-increasing channel 52 and output channel 58 are sent on the use device. The initial compression force of the control spring 18 between the valve cover 11 and the diaphragm assembly 59 during assembly makes the valve mechanism fully open before the pressure of the inflowing gas is applied to the inlet 26 . As shown, bore 43 is elongated, preferably at an angle to inlet passage 61 , so that incoming gas flow is directed directly into seat disc 21 and axially along speed boost tube passage 52 . Also, as previously indicated, due to the speed-up effect provided, the diameter of the orifice 43 can be much smaller (only half that size) than would be required to meet the output flow requirements without the device, thereby effectively Helps maintain a satisfactorily low lockup (closed) inlet differential pressure. Therefore, the incoming air flow is obviously accelerated by the restriction of the small inlet. Due to the "shrink section" effect, the air flow increases suddenly around the valve seat disc 21, and accelerates to flow through this circular smooth constraint, axially at an increasing rate. Flow through the speed-increasing channel 52 and enter the outlet channel 58 .

Referring to FIGS. 6-10 , the operating mechanism of the present invention is mainly composed of a transmission member 16 , a speed increasing/valve seat pipe 20 and a hole plug 19 . Transmission member 16 is characterized by a pair of spaced-apart control passages 38 at its lower end 16A and has a straight vertical face 40 . Each control passage 38 also includes a pair of oppositely disposed, identically shaped surfaces 63, 64 that are in contact with the opposite sides of a pair of control pins 48 protruding from both sides of the booster/seat tube 20. One or the other is a sliding fit, forming a cam mechanism. In this way, when the diaphragm assembly 59 moves up and down in response to the air pressure in the chamber 57 and the spring force acting on the diaphragm 13, the transmission member 16 and its control channel 38 are relative to the speed increase/valve seat tube 20 and its control. The movement of the pin 48 causes axial movement of the booster/seat tube. The control channel 38 is preferably designed to have a mechanical gain of about 4:1 when the outflow end does not require gas to ensure the seal between the valve seat disc 21 and the valve seat 44, while at other times during the movement of the valve mechanism, then have a lower mechanical gain to generate and enhance the rate increasing effect. The very slight small area point contact between the shaped surfaces 63, 64 and the control pin 48 helps to reduce hysteresis, but the whole way the booster/seat tube 20 is supported, moved and guided significantly reduces the friction of the whole mechanism, At the same time, the mode of operation of the controller is correspondingly improved, as will be explained further below.

Under the action of the outer end of the control pin 48 and a pair of guide pins 49, the speed increase/valve seat pipe 20 is limited to linear reciprocating movement relative to the valve seat 44, wherein the guide pin 49 is from the speed increase/valve seat pipe 20. Protruding from opposite sides, located at the position (Fig. 6, 7 and 9) separated from the pin 48 along the length direction of the speed-increasing/valve seat tube 20, the guide pin 49 leans against the guide surfaces 47, 70, guides The faces 47, 70 are located on the underside of generally cylindrical guides 72, 73 formed on the projecting ends of the vertical arms 69, 71 of the plug 19 (Figs. 6, 7 and 10). The points of contact between these pins and guides are cylindrical in transverse cross-section, providing rounded smooth point contact surfaces that reduce frictional movement of the booster/seat tube 20 and associated valve mechanism. The hole plug 19 also has two contact points 46 (FIGS. 4 and 10B) which contact the vertical plane 40 of the drive member 16 to provide continuous bi-directional linear motion with low friction.

It should be appreciated that the configuration and interrelationship of the slide mechanism described above provides a unique low friction support and guide for the booster/seat tube 20 . More specifically, as mentioned above and shown in FIG. 7 (showing the mechanism in actual operation), when the speed increase/valve seat tube 20 is raised in operation, the control pin 48 and the guide pin 49 lean against the guide pin respectively. The underside of faces 70 and 74, rather than against the top of cylindrical member 72. This is due to the shape and relative position of the components, including the shaped control passage 38, the preload effect of the control spring 18, inlet air pressure and chamber pressure, which act together to maintain the action on the booster/seat tube 20 The force couple makes it take its control pin 48 as the center and counteracts the speed increase/valve seat tube 20 own weight, and the speed increase/valve seat tube 20 is lifted to the guide member 72 just described relative to the hole plug 19 Basically the position where the cantilever "floats". The small frictional sliding contact of pins 48 and 49 along guide surfaces 70 and 49 is the only contact between booster/seat tube 20 and bore plug 19, as shown in Figure 7, the outer ends of pins 48, 49 and 49A are not In contact with the inner surfaces of the adjacent plug arms 69 and 71, the circular outer end 19A of the guide 72 also does not contact the side wall of the adjacent booster/seat tube 20 or the intermediate portion 49B between the pins 49 and 49A. touch.

Figure 12 schematically illustrates the force vectors acting on the booster/seat tube 20 to create the force couple described above, the side of the booster/seat tube 20 is shown. The "contact force" vectors shown in the figure, acting downward on pins 48 and 49, represent the contact of those members with guide surfaces 70 and 47, respectively, wherein the "contact force" vector on pin 48 represents the contact between pin 48 and the forming The contact of the control channel 38 is, in particular, with the surface 63 thereof. The "unbalanced force" essentially represents the inlet air pressure acting on the surface of the valve disc 21 and its annular support 50 . Due to the above factors, the larger area bottom surface of the booster/seat tube 20 never contacts or rests on the adjacent surface of the orifice plug 19, and even the pins 48 and 49A of the booster/seat tube generally remain Above, not in contact with, the top surface of the cylindrical guide 72 of the hole plug 19 (FIG. 7). Therefore, although the speed-up/valve seat pipe 20 is always guided smoothly and rigidly, the sliding friction force generated during the reciprocating movement of the speed-up/valve seat pipe 20 relative to the inlet port of the valve hole 44 and the output passage 58 is very tiny.

It will be appreciated that after the plug 19 is mounted on the body 12 during initial assembly of the operating system, the booster/seat tube 20 can be easily slid into its position between the arms 69, 71 of the plug 19, At this time, the pin 48 is located between the guide projections 72 and 73 , and the pins 48 and 49A are located on top of the guide projection 72 . Because the pin 49A contacts the elongated guide surface 72 at various points, and is used to maintain the front portion of the booster/seat tube 20 in a raised position, in which the seat disc 21 remains in contact with the seat. The /opening 43 is in line, so the axially movable configuration of the pin 49A relative to the pin 49 can limit the amount of inclination allowed for the booster/seat tube 20 under this condition. At this point, the drive member 16 is inserted into position from above with the remainder of the diaphragm assembly 59 and the cam slot 38 slides through and receives the pin 48 . The diaphragm assembly is put into the position above the main body 12 first, and then the valve cover 11 is placed on the diaphragm assembly and fixed in place. When the bonnet 11 is placed and fixed in this way, the top surface 60 of the bonnet 11 contacts the top of the control spring 18 and applies the aforementioned preload to it, while simultaneously pressing the transmission member 16 downward. Due to the engagement of the shaped control passage or cam groove 38 on the guide pin 48, this downward movement of the transmission member 16 and the pressure of the spring 18 moves the control passage 38 downward relative to the control pin 48 so that the overdrive/seat tube 20 Corresponding movement to the right, as shown in Figure 4, moves the seal 21 away from the valve seat 44 and opens the valve.

Referring to Figures 4, 7 and 12, the valve arrangement is shown in the previously described fully open position with gas entering through inlet 61, flowing through opening 43, and entering the adjacent end of booster/seat tube 20 around the valve. The seat plate 21 flows through, enters the speed-increasing tube passage 52, and then enters the outlet passage 58. Between passages 52 and 58, part of the gas enters chamber 56, where the pressure of the gas is exerted on the effective area of diaphragm 13, thus counteracting the force of control spring 18 and making the diaphragm assembly 59 moves upward, so when the control channel 38 moves upward to contact the control pin 48 and press the speed increase/seat tube 20 and seat disc 21 to the seat 44, a restriction can be formed to control the air flow to meet the outlet flow Require. In addition, the inflow gas pressure acting on the seat disc 21 creates an "unbalanced force" shown in FIG. 12 . This force vector is generally aligned with the axis of overdrive/seat tube 20 , below control pin 48 , as shown. This effect is achieved by turning the booster/seat tube 20 to the position shown in FIG. In this position, the top of pin 48 engages the lower surface 70 of guide 73 and the top of pin 49 engages the lower surface 47 of guide 72, thereby producing the low friction smooth guiding described above.

It should be noted that once gas is not required at the output, the gas pressure in chamber 56 continues to increase until seat disc 21 forms a seal over seat 44, resulting in zero flow and a locked condition. In this regard, the invention also includes a safety feature commonly referred to as a pressure valve. When the pressure in the chamber 56 increases to a certain percentage greater than the lock-up pressure, it acts on the effective area of the diaphragm 13, counteracting the force of the control spring 18 and the pressure regulating spring 17, so that the diaphragm disc 14 of the diaphragm 13 And the safety seal 32 moves upward, away from the safety seat 39, so that the gas flows through the safety holes 33 and 35 on the diaphragm 13 and the diaphragm disc 14 in sequence. This gas flow can leak from chamber 57 to the environment through the air holes 25 in the valve cover 11, reducing the pressure to a level that allows the components to reseal and operate normally. In addition, if the mechanism is deflected due to some reasons, the diaphragm assembly 59 moves upward without the resistance of the locked state, the post 42 of the transmission member 16 is designed to contact the surface 60 of the valve cover 11, preventing the upward movement, and enable the safety device to operate as described above.

As previously stated, the device is designed to control the flow of air to meet the requirements at the outlet. When an increase in flow is required, the outlet pressure drops causing the diaphragm 13 and associated components including the transmission member 16 to move downward, moving the valve seat disc 21 away from the valve seat 44 to allow more gas to flow through the device , so as to meet the new requirements. This process continues until the requirements are met and an equilibrium state is reached. On the contrary, if it is required to reduce the air flow, the operation of the above-mentioned elements is reversed. A change in inlet pressure and/or demand will cause the valve assembly to open or close according to the new conditions, compensating the equipment, and re-establishing a state of equilibrium. Since the seat disc 21 and its seat support 50 are integrally connected with the booster/seat tube 20 and become part of it, it can be appreciated that with the corresponding movement of the seat disc 21, the entire booster/seat tube 20 reciprocates relative to the valve seat 44. During the increase in gas flow in the device, as the seat disc 21 moves away from the valve seat 44, the end of the booster/seat tube 20 located closest to the inlet of the outlet passage 58 moves closer to the inlet of the outlet passage 58 , thereby increasing the compressed gas flow to and through passage 58. This has the effect that a large amount of gas is sucked out of the chamber 56 , reducing the pressure exerted under the diaphragm 13 . Conversely, when the gas flow decreases, the booster/seat tube 20 and seat disc 21 move in reverse, moving the end of the booster/seat tube 20 out of the way to the outlet passage 58 so that it is open to the chamber 56. The widening of the opening reduces the acceleration/pressure pumping effect and increases the pressure inside the chamber 56 . The speed-up effect provided by the speed-up/seat tube 20 is thus varied and enhanced. By employing increased speed up and reduced hysteresis, the present invention provides a significantly improved pressure regulator.

Bonnet 11 (aluminum), body 12 (zinc), diaphragm disc 14 (steel plate), spring retainer 15 (steel plate), control spring 18 (stainless steel), pressure regulating spring 17 (stainless steel) and drive screw 23 (stainless steel) Preferably all rigid metal components. Diaphragm 13, valve seat disc 21 and O-ring 22 are all flexible elastic components, and transmission member 16, speed-up/valve seat tube 20 and hole plug 19 are preferably made of rigid engineering thermoplastic resin, such as acetal, polyethylene terephthalate. Referring to Fig. 2, the main body 112 has an integrally formed barbed second outlet 124, which has a through hole 158, which can be used to have both a main burner and a small capacity auxiliary burner. Propane cookers for outdoor cooking provide airflow.

The present invention provides a consistent and repeatable performance over a wide range of inlet pressures and flow rates, while also significantly reducing the inlet diameter (half the size) and size of the diaphragm and overall regulator, e.g., compared to conventional Compared with the traditional diaphragm regulator, its size is only nearly 1/3 the size. The foregoing description is only one preferred embodiment, and in this embodiment, the specific shape and characteristics of at least some of the components (especially the orifice plug 19 and the speed increase/seat tube 20) are based at least in part on manufacturing (such as molding) convenience. and considerations, and based on matters related to assembly and operation. Those skilled in the art, as well as those who have studied the embodiments of the invention, will be able to make certain modifications to the invention, and these modifications and alternative embodiments can be conveniently made in accordance with the invention. Therefore, it can be understood that the embodiments described in the drawings and the above descriptions are only for illustrative purposes, and do not limit the scope of the present invention. According to patent regulations and the principle of equivalents, the scope of the present invention is defined by the following claims.

Claims (41)

1, a kind of direct acting acceleration type barostat, it comprises:

A main body, this main body have a regulator chamber with a gas access and outlet, and compressed thus gas communicates described chamber with flowing also between described entrance and exit;

A variable valve device and a pressure response spare, they with described chamber in gas communication and be connected with control valve unit, can control the throughput between described entrance and exit according to the pressure size in the described chamber;

A velocity hooster structure that is positioned at described chamber, it comprises that has a velocity hooster element that is generally tubular conduit, this element is installed between the described entrance and exit movably, form one according to different the opening and pass and adjustable continuous closed channel of described control valve unit, its regulative mode is: when described control valve unit changes, pressure change in the described chamber

A connection set that is directly connected on described pressure response spare and the described velocity hooster element is used for moving described velocity hooster according to the air pressure size of described chamber.

2, barostat as claimed in claim 1 is characterized in that, described velocity hooster structure is connected with described variable valve device, with this collaborative moving.

3, barostat as claimed in claim 2 is characterized in that, described variable valve device comprises a valve element, links to each other associated movement with described velocity hooster element.

4, barostat as claimed in claim 3 is characterized in that, described valve element operably is positioned at described common passage in a tubular form.

5, barostat as claimed in claim 4, it is characterized in that, described control valve unit comprises a valve seat, described valve element can with respect to described valve seat relative to and move in opposite directions, thereby change the air-flow of described entrance and exit, described common passage to small part in a tubular form extends to described valve seat, and around this valve seat, like this, velocity hooster element to small part shroud ring this seat and peripheral region thereof.

6, barostat as claimed in claim 4 is characterized in that, described common passage in a tubular form forms the free-flow zone of described velocity hooster interelement gas around described valve element.

7, barostat as claimed in claim 6, it is characterized in that, described control valve unit comprises a valve seat, described valve element can move back and forth with respect to described valve seat, thereby change the air-flow between described entrance and exit, described tubular conduit to small part extends to described valve seat, and around this seat, like this, described element to small part shroud ring this seat and peripheral region.

8, barostat as claimed in claim 1 is characterized in that, described inlet, outlet and the movable velocity hooster element of installing have formed an open channel that leads to described chamber interior.

9, barostat as claimed in claim 8 is characterized in that, the size of described opening is variable according to the motion of described velocity hooster element.

10, barostat as claimed in claim 1, it is characterized in that, described velocity hooster structure comprises the low friction of the described movable installation velocity hooster element mounting mechanism that suspends, this mounting mechanism comprises a plurality of axially extended separation and spaced guiding elements along described tubular conduit element, and outside described velocity hooster element, stretch out and with the slidably connecting element of described guide contacts, like this, when described tubular conduit element moved with respect to described entrance and exit, described tubular conduit element was along the described guiding element longitudinal sliding motion on the described link.

11, barostat as claimed in claim 10 is characterized in that, comprises an inlet opening structure that is installed on the described main body, and it provides described isolated guiding element.

12, barostat as claimed in claim 11 is characterized in that, described inlet opening structure also provides a valve seat for described control valve unit.

13, barostat as claimed in claim 11 is characterized in that, described control valve unit comprises a valve element, and it is mounted to and can moves back and forth with respect to described valve seat, thereby changes the throughput through described inlet.

14, barostat as claimed in claim 13 is characterized in that, described valve element is connected associated movement with described velocity hooster element.

15, barostat as claimed in claim 14 is characterized in that, described valve seat is positioned near the end of a projection, and described tubular conduit at least a portion telescopically extends on described projection, to cover described valve seat.

16, barostat as claimed in claim 15 is characterized in that, the described telescopic extension part of described tubular conduit element can be slided with respect to described valve seat.

17, barostat as claimed in claim 10, it is characterized in that, comprise a pressure measuring element that is positioned at described chamber to small part, and driving component that can move described control valve unit and link to each other according to variation in pressure to small part by described pressure measuring element measurement with described pressure measuring element, described driving component is connected with described velocity hooster element, transmit motion on it,, make it along the low friction slip of described guiding element simultaneously also with described velocity hooster structural orientation.

18, barostat as claimed in claim 17, it is characterized in that, described driving component comprises a pair of spaced camming surface, described velocity hooster structure comprises the cam follower that a pair of corresponding interval is opened, the described camming surface that each cam follower is corresponding with one respectively cooperates, to move described velocity hooster element according to the motion of described driving component.

19, barostat as claimed in claim 18 is characterized in that, described camming surface and cam follower acting in conjunction and described control valve unit partly come together to move described velocity hooster structure and described velocity hooster element.

20, barostat as claimed in claim 19 is characterized in that, it comprises an inlet opening structure that is installed on the described main body, and partly provides a valve seat for described control valve unit.

21, barostat as claimed in claim 20 is characterized in that, described valve seat is installed near the end of a projection, and described velocity hooster element at least a portion telescopically is installed on the described projection, to cover described valve seat.

22, barostat as claimed in claim 21 is characterized in that, the part of the scalable installation of described velocity hooster element can be slided with respect to described valve seat.

23, barostat as claimed in claim 3, it is characterized in that, comprise a pressure measuring element that is positioned at described chamber to small part, and a driving component that directly is connected with described pressure measuring element, described driving component can move described valve element according to the variation in pressure that described pressure measuring element is measured.

24, barostat as claimed in claim 23, it is characterized in that, described driving component comprises a pair of spaced cam face, described velocity hooster structure comprises a pair of corresponding cam follower at interval, the described camming surface that each cam follower is corresponding with one respectively cooperates, to move described valve element according to the motion of described driving component.

25, maintenance unit, it comprises:

A main body, it has a pressurized gas inner chamber with an inlet and an outlet;

A regulator chamber is communicated with the pressurized gas that flows to described outlet from described inlet by a channel region, and a certain amount of gas is controlled under the certain pressure;

A variable valve device, it comprises a movable valve element, can be according to gas pressure value in the described chamber, control is from the described throughput of the described described outlet that enters the mouth;

A moveable element can change the size of described passage area effectively, is communicated with situation thereby change with the air pressure of described regulator chamber;

A low friction slip mounting mechanism that is used on the described moving element, it comprises that at least one pair of separately and the guiding element of space, these guiding elements stretch out along the predetermined pathway linearity that moving element moves, comprise that also at least one pair of is positioned at the slider of the corresponding interval on the described moving element, described slider and described guiding element are slidingly matched, and move along guiding element, move in strict accordance with described predetermined pathway to guarantee described moving element.

26, barostat as claimed in claim 25, it is characterized in that, described guiding element spaced apart from each other comprises the elongated slide rail shape part that is supported on the described main body, described slider is positioned at the outside of described slip closure member, with described slide rail shape part friction sliding contact, the slip of described slider makes described closure member move along described slide rail shape part.

27, barostat as claimed in claim 26, it is characterized in that, described moving element is located between the described slide rail shape part loosely, it comprises a driving component, when the motion of described moving element changes the size of described passage area effectively, driving component can support described closure member at least in part in the pre-position, described slider only is set to a part of friction ground sliding contact with described slide rail shape part, and do not contact the rubbing action when reducing practical operation with other slide rail shape parts.

28, barostat as claimed in claim 27, it is characterized in that, described moving element is an elongated shape, comprise a pair of isolated end, described driving component supports described moving element from the position of a more close end, and described element is that cantilevered fashion is suspending when motion basically.

29, barostat as claimed in claim 28 is characterized in that, described moving element at least a portion is being supported by effect couple thereon, and this force couple role is in the position of a described more close end.

30, barostat as claimed in claim 29 is characterized in that, described control valve unit is connected on the described closure member, under described driving component effect and the closure member associated movement.

31, in a speedup barostat, this regulator has a regulator chamber with an inlet and an outlet, a variable valve device of controlling air-flow between described entrance and exit according to the amount of gas pressure in the described chamber, a speedup tubular structure that movably is installed between described entrance and exit, the opening that between entrance and exit, forms a variable cross-section according to the working method and the corresponding stream condition between described entrance and exit of described control valve unit, its improvement is, described speedup tubular structure comprises an elongated element, this elongated element has the air-flow path and the drive mechanism of an inside, in view of the above, described element can vertically move back and forth with respect to described outlet, described drive mechanism comprises a counterpart at least, counterpart is fixed on the described elongate articles and has horizontal outwardly directed part from the described elongate articles, also comprise a driving component element, be used for engaging with described at least one counterpart and driving it, thereby make described elongate articles with respect to the vertical to-and-fro motion of described outlet.

32, the improvement structure of speedup barostat as claimed in claim 31 is characterized in that, described outside drive mechanism comprises a projection of stretching out at least outside described elongate articles; Described driving component element comprises a camming surface, is used for being slidingly matched with described at least one projection, and is applied to it, thereby drive described projection and described elongate articles by described camming movement.

33, the improvement structure of speedup barostat as claimed in claim 32 is characterized in that, described camming surface is shaped, and can be on the different motion position of described elongate articles described projection be had in various degree mechanical gain.

34, the improvement structure of speedup barostat as claimed in claim 32, it is characterized in that, described camming surface and convex design are can be under practical operation when camming movement, described projection is applied a moment of rotation, thereby when described cam makes described elongate articles produce longitudinal movement, just described elongate articles is applied a horizontal detent force.

35, the improvement structure of speedup barostat as claimed in claim 34 is characterized in that, described camming surface comprises at least one groove, and it is arranged between a pair of cam face also spaced apart from each other opposite one another.

36, the improvement structure of speedup barostat as claimed in claim 35 is characterized in that, described projection comprises a pin linear element, and this element has a cross section that can match with described groove.

37, the improvement structure of speedup barostat as claimed in claim 34, it is characterized in that, comprise that also at least one is positioned at the slider on the described elongate articles outside, described follower is set to and the elongated guide face sliding contact of stretching out outside the outside of described elongate articles, and the effect of described located lateral power makes described at least one slider and the friction sliding contact at least of described guide surface.

38, the improvement structure of speedup barostat as claimed in claim 34, it is characterized in that, described located lateral power drives described elongate articles when described element longitudinal movement, described elongate articles to small part is not contacted with adjacent structure in the described chamber.

39, the improvement structure of speedup barostat as claimed in claim 38, it is characterized in that, also comprise a slider that is positioned at the described elongate articles outside at least, the elongated guide face sliding contact of stretching out outside the outside of it and described elongate articles, described located lateral power make the friction ground sliding contact at least of described slider and described guide surface.

40, the improvement structure of speedup barostat as claimed in claim 39 is characterized in that, described camming surface comprises at least one groove, and this groove has a pair of mutually opposed and cam face that is spaced laterally apart.

41, the improvement structure of speedup barostat as claimed in claim 31, it is characterized in that, described internal channel has smooth, a continuous and common continual peripheral wall, it does not have airflow limitation, it comprises a valve element, this element is arranged in the described passage, separates with described peripheral wall, provides the open region of minimum airflow limitation between the two.

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