Pressure regulator

FIELD: machine building.

SUBSTANCE: invention relates to flow regulators, particularly, to flow regulators with bowl-shape seat. Regulator consists of valve body to define fluid flow and valve seat, drive case engaged with valve body, control member arranged in drive case and adapted to displacement relative to valve body and valve seat for regulation of fluid flow at displacement between open position and closed position whereat said control member engages with valve seat, and spring articulated with control member to displace the latter to open position. Said control member has the surface directed to valve seat and furnished with recess. Recess can be reamed, or concave, or conical or have any other suitable surface.

EFFECT: higher reliability, perfected adjustment.

19 cl, 4 dwg

 

The technical field

The present description of the invention, generally, relates to a flow regulator, in particular the flow regulator with a bowl-shaped seat design.

The level of technology

The flow control include various categories of equipment, including control valves/gate valves and regulators. Such regulating devices adapted for inclusion in a process control system from fluid materials, such as chemical handling systems, injection systems for natural gas and others, to control the flow of fluid in them. Each regulating device determines the path of the fluid and includes a management body for the regulation of the size of such a motion path. For example, figure 1 shows a known control unit (10)including a valve housing (12) and the actuator (14). The valve housing (12) defines the path of movement of the thread (16) and contains the channel (18). In figure 1 the regulation unit (10) has a configuration corresponding to a rise of fluid. The actuator (14) has an upper part of the casing (20), the lower part of the casing (22) and the unit diaphragm (30)including a diaphragm (32) and the governing body (24).

The governing body (24) is placed in the upper and lower parts of the actuator (20) and (22) and adapted to the possibilities of bi-directional displacement in response to changes in differential pressure in the actuator diaphragm (30). With t the forge configuration management body (24) controls the flow of liquid through the channel (18). As shown in this figure and is used in most devices that are near to the lower end of the management body (24) surface, as a rule, is convex, and the fluid it is leaking, if the regulation unit (10) is in the open state. In addition, as shown in the drawing, the regulation unit (10) comprises a valve seat (26)located in the channel (18) of the valve body (12). At high pressure output from the valve body (12) of the sealing surface (28) of the management body (24) can tightly lock the valve seat and block the channel (18). Similarly, in the absence of pressure on the actuator (14), or a failure of the diaphragm (32) and helical spring (34)located in the annular space (36) in the upper drive housing (20), shifts the governing body (24) in the closed position. Such a regulator is usually called "valve closing failure".

Valve opens when the control system failure", works similarly to the valve closing failure; however, after the failure of a diaphragm spring of this valve puts the control in open position, not closed. Examples of valves that failure of the control system described in U.S. Patent publication No. 2008/0078460 A1 authors Roper et al. "The installation device for pressure regulators is I", included in this description by reference. Regulators, similar to the one shown Roper et al, the spring may be in the governing body (24) or otherwise be conjugated to translate the governing body (24) to the open position. If the diaphragm or the governing body fails, the fluid continues to flow through the regulator continuously and in an uncontrolled manner, as the spring opens the unit of regulation. Therefore, such a configuration often contain redundant controller controlling the fluid flow when not activated, the valve opens when the failure.

The valve opens when the control system failure, such as described by Roper et al, you may experience performance problems if they are installed in places in which develops high pressure. High inlet pressure in combination with low output pressure can cause problems with control and stability regulators because of the additional uneven forces acting on the tube of the valve. In some cases, these forces can be minimized by increasing the volume of fluid downstream (i.e. increasing the diameter of the pipes for a reference point) and/or limiting the flow to or from the diaphragm chamber of the valve. However, even when using such measures management problems can su is still observed at high flow rates, since the gradient force acting on the stopper of the valve causes problems with management. In these configurations with a large flow rate can be negative gradient of the pressure at which the pressure drop in the valve seat may cause the tube of the first valve will be delayed to the valve seat as long as the spring force will not exceed the magnitude of the force created by the negative pressure gradient, and plug valves can enter into high-frequency oscillations upon actuation of the actuator to control the response of the regulator. Such an unstable condition at the output can be maintained due to the lack of rigidity of the drive system. There is therefore a need for improvement of a valve that is opened by the control system failure, which will provide stable performance in installations with high pressure inlet and low outlet pressure and high flow rate.

Brief description of Figures

Fig. 1 is a side view cross-section of traditional valve closing failure of the control system;

Fig. 2 is a side view cross-section of a valve that is opened by the control system failure, which was constructed on the basis of the principles presented in this description;

Fig. 3 is took the Chennai side view cross section of the channel and Assembly of the valve, depicted in figure 1, in the open position; and

Fig. 4 represents an enlarged side view cross section of the channel and Assembly of the valve shown in figure 1, in the closed position.

The implementation of the invention

Figure 2 presents an embodiment of body adjustment, constructed in accordance with the principles set forth in this description of the invention, including a pressure regulator (100). In the General case, the pressure regulator (100) includes a valve housing (102), valve seat (104) and the actuator (106). The valve housing (102) defines a flow path (108) from the inlet (110) to the outlet (112) and the inside of the actuator (106), as will be discussed below. The actuator (106) includes a control unit (114)that can be moved between an open position, as shown in figure 2, and a closed position (not shown), in which the control unit (114) which uses a valve seat (104). The movement control unit (114) occurs in response to fluctuations in fluid pressure at the inlet (110) and the outlet (112). Accordingly, the position control unit (114) relative to the saddle valve (104) affects the throughput of the pressure regulator (100).

The valve housing (102) defines a channel (116) between the inlet (110) and output (112). Channel (116) has a stepped portion (118), in which is located and fixed valve seat (104). In one configuration, between the saddle clap is on (104), and a stepped part (118) channel (116) can be o-ring to ensure a tight lock between them.

As indicated above, the actuator (106) includes a control unit (114) and the upper part of the casing of the drive (122) and the lower part of the casing of the actuator (124) and a group of pins (126). The top and bottom of the housing (122) and (124) are attached together by at least one screw connection (119) and the corresponding nut (121). The upper part of the casing of the drive (122) determines the location of the center hole (123), the first regulating inlet (125) (depicted by the dotted line) and the camera move (127). The camera move (127) contains the travel indicator (131), showing the position of the control unit (114) in the actuator (106). The lower part of the casing of the actuator (124) determines the location of the output adjusting holes (129).

Together, the upper and lower part of the casing of the drive (122) and (124) determine the location of the cavity (135) neck (128). Neck (128) is in the hole (115) of the actuator in the valve housing (102). As shown in Fig. 2, the group of pins (126) one end (a) is attached to the neck (128)and second end (126b) is aimed at removing from the centre of the neck (128). In the configuration shown in the drawing, the first ends (a) is screwed into the holes in the wall of the neck (128). The second ends of the rods (126b) is connected with a valve seat (104). Accordingly pins (126), and a stepped portion (118) of the channel (116) is placed between a and axially determine the position and fix the valve seat (104) to pose valve (102). Although the regulator (100) is described as containing a group of pins (126), determining the position of the valve seat (104) relative to the valve housing (102), an alternative configuration of the controller (100) may include a box, located in the channel (116), which determines the position of the valve seat.

Also in Fig. 2 the control unit contains a governing body, such as the hollow shaft (130), the mount (132), block diaphragm (133) and unit positioning device (138). The hollow shaft (130) is tubular, defining a generally cylindrical inner surface (143) and a cylindrical outer surface (147). The inner surface (143) forms the Central hole of the hollow shaft (130), in Addition, the hollow shaft (130) has an upper end (130A) and the bottom (130b). The top end (130A) is located in the cavity (135)and the bottom (130b) is inside the cap (128) the lower part of the casing of the actuator (124). The top end (130A) of the hollow shaft is open and has a circumference, the flange (140)formed on the outer surface (147). In addition, the upper portion (130A) of the hollow shaft (130) includes a threaded portion (141) of the inner surface (143). The bottom end (130b) of the hollow shaft (130) is opened, and it is the site of attachment (132).

As best shown in figure 3 and Figure 4, the mount (132) contains an element fixing or reducing sleeve (142), disc holder (144) and an annular sealing gasket repressivnoi slot (146). In the configuration described in this description of the invention, the transition sleeve (142) has a cylindrical body connecting threaded connection with an open bottom end (130b) of the hollow shaft (130) and containing razzenkovannye part (148). Razzenkovannye part (148) forms a recessed bottom surface of the hollow shaft (130). Razzenkovannye part (148), usually located on the same axis with a hollow shaft (130), and a portion of larger diameter (a) is a side channel of the transition sleeve (142), and a portion of smaller diameter (148b) opens into the interior of the hollow shaft (130). Disc holder (144), typically has a cylindrical housing fixed to the intermediate sleeve (142) one or more tabs (149), and may contain between them a sealing ring (150) for sealing the connection. In the configuration described in this description of the invention, 5 tabs (149) is threaded. Disc holder (144) limits the through hole (151)having a diameter identical to the diameter of the large diameter (a) razzenkovannye portion (148) of the transition sleeve (142), and coaxial with it.

As shown in the drawings, the disk holder (144) may also have protruding outward flange (152)connected to the end surface with the second end (130b) of the hollow shaft (130) and/or o-ring (150). On the lower surface of the disk d is of rates (144) or flange (152), if it is, is an annular groove (154), turned so that it was pressed in the slot (146). Pressed the slot (146), in General, is an annular plate of elastic material, is fixed in the groove (154) disc holder (144). In one of the configurations pressed the slot (146) is mounted in the groove (154) disc holder (144) with glue. Pressed the slot (146) and the groove (154) have a configuration corresponding to the shape of the valve seat (104), and pressed the slot (146) is pressed against the valve seat (104), when the control unit (114) is in the closed position shown in Fig. 4.

In the upper part of the regulator (100)is presented in figure 2, the block diaphragm (133) includes an aperture (134), top plate aperture (a) and lower plate aperture (136b). The upper and lower plates of the diaphragm (a) and (136b) is pressed against the annular flange (140) of the hollow shaft (130). Plate diaphragm (a) and (136b) fastened together by clamps (156), which thus fasten together the hollow shaft (130) and the plate aperture (a) and (136b). In addition, between the plates of the diaphragm (a) and (136b) is mounted radially inner part of the aperture (134). Radially outer part of the diaphragm (134) is mounted between the upper and lower parts of the casing of the drive (122) and (124).

Node positioning device (138) is main the way inside the hollow shaft (130) in order to displace the hollow shaft (130) to the open position represented in figure 2. Node positioning device (138), in General, has a Central rod (186), the first slot of the spring (188), the second socket spring (190), the shifting element, such as a spring (193), and retaining plate (192). The Central rod (186) has one threaded end (a) and the second threaded end (186b). The first threaded end (a) passes through the Central hole (123) of the upper part of the casing of the drive (122). The outer nut (194) wrapped around a first threaded end (a) to limit axial displacement of the Central thrust (186) in a downward direction relative to the orientation of the actuator (100)is presented in figure 2. Intermediate nut (196) wrapped around a first threaded end (a) Central thrust (186) outer nut (194) to limit axial displacement of the Central thrust (186) in the upward direction relative to the orientation of the actuator (100)is presented in figure 2. Accordingly, the first threaded end (a) Central thrust (186) effectively secured to prevent displacement along the axis relative to the upper part of the casing of the actuator 122, and the second threaded end (186b) is included in the actuator (106).

Accordingly, as shown in the drawing, the second threaded end (186b) of the Central rod (186) is included in the hollow shaft (130) and is located next to the second is oncom (130b) of the hollow shaft (130). A pair of retaining nuts (a, 198b) screwed onto the second threaded end 186b of the Central rod (186). Retaining nuts (a, 198b) attach the first slot of the spring (188), spring (193) and the second slot of the spring (192) on the Central rod (186). The first slot of the spring (188) can slide inside the hollow shaft (130), about which more will be said below. More specifically, the first slot of the spring (188) consists of a generally cylindrical plate, coupled with the retaining nuts (a, 198b). Therefore, the spring (193) captures the second slot of the spring (190) to the retaining plate (192) and relative to the hollow shaft (130). In addition, the first slot of the spring (188) is fixed relative to the Central rod (186) and has a Central hole (a) and holes (188b). In the Central hole (a) includes a second end (186b) of the Central rod (186) right next to the retaining nuts (a, 198b). The group of holes 188b reported in a fluid environment with razzenkovannye part (148) and a through hole (151) of the mount (132), and therefore - by the stream (108)

Similarly, the second slot of the spring (190) contains, in General, a cylindrical plate with a Central hole (190A) and multiple holes (190b). In the Central hole (190A) includes a first threaded end (a) of the Central rod (186). The group of holes (190b) communicates via a fluid with a group response the sty (188b) in the first slot of the spring (188), and so - by a thread (108). Accordingly, as shown in the drawing, the spring (193) is located along the axis between the first slot of the spring (188) and the second slot of the spring (190) and concatenated with them. The first slot of the spring (188), a fixed retaining nuts (198) from offset downwards relative to the Central rod (186), holds the spring (193). Thus, the spring (193) supports the second slot of the spring (190).

In addition, the holding plate (192) contains, in General, a cylindrical plate having a Central hole (a), the group of holes (192b) and the threaded part 195. The threaded portion (195) cylindrical plate (192) is attached by a threaded coupling with a threaded part (141) of the inner surface (143) of the hollow shaft (130). Accordingly, the retaining plate (192) and hollow shaft (130) operate as a single structure.

During Assembly, when the upper part of the casing (122) is removed from the bottom of the housing (124) and removed the hollow shaft (130)positioned between the plates (a) and (136b) of the diaphragm holding plate (192) is screwed into the threaded portion (141) of the hollow shaft (130). Then the intermediate nut (196) screwed onto the first threaded end (a) Central thrust (186). The second threaded end (186b) of the Central rod (186) is placed in the Central hole (a) retaining plate (192). Then, putting on a Central rod (186), the second GN the health of a spring (190), spring (193) and the first slot of the spring (188) pull on the Central rod (186) in sequence through the hole in the lower part (130b) of the hollow shaft (130). Then screw the retaining nut (a) and (198b) on the second threaded end (186b) Central thrust (186) as shown in the drawing.

Now the technician or engineer can pre-stretch unit positioning device (138), wrapping or intermediate nut (196), located at the retaining plate (192), or retaining nut (a) and (198b), located next to the first slot of the spring (188). For example, when the intermediate driving nuts (196) of the Central rod (186) extending through the second slot of the spring (190) and retaining plate (192). This leads to the fact that the retaining nut (a) and (198b) apply a force to a first connector of a spring (188) and shift the first slot of the spring (188) in the direction of the second slot of the spring (190). With continued tightening of the intermediate nuts (196) this leads to compression of the spring between the first (188) and second (190) Jack spring.

Alternatively tightening the retaining nuts (a) and (198b), located next to the first slot of the spring (188), shifts the first slot of the spring (188) in the direction of the second slot of the spring (190), compressing the spring (193). It should be recognized that in the embodiment of this invention, represented in the drawing the, retaining nuts (a) and (198b) represent the first retaining nut (a), located directly next to the first slot of the spring (188), and the second retaining nut (198b), located directly next to the first retaining nut (a) opposite the first slot of the spring (188). Accordingly, through the above-described pre-stretching, the technician or engineer must first wrap the first retaining nut (a)to shift the first slot of the spring (188) to compress spring (193). Then a technician or engineer must wrap the second retaining nut (198b) before coupling with the first retaining nut (a) to effectively lock the first retaining nuts (a) at his place on the Central rod (186).

In addition, it should be recognized that in one embodiment, block positioning device (138)presented in this description of the invention, the Central rod (186) may have marks along the length of at least one of the threaded parts (a) and (186b), so that a technician or engineer, performing one of the above procedures, pre-tensioning, can wrap the intermediate nut (196) or the retaining nut (a) and (198b) to a particular position on the Central rod (186), thus compressing the spring (193) with a preset force.

With proper tension unit position is ionirovanija (138) o-ring flange (140) of the hollow shaft (130) is in the grip plates (a) and (136b) of the diaphragm, and the lower part of the shaft (130b) is located in the neck (128) the lower part of the casing of the actuator (124). The upper part of the casing of the drive (122) then is located on the lower part of the casing of the actuator (124) so that the first threaded end (a) of the Central rod (186) passed through the Central hole (123). The technician or engineer can then attach the upper part of the casing of the drive (122) to the lower part of the casing of the actuator (124) screw clamps (119). Finally, the technician or engineer's external nut (194) on the first threaded end (a) of the Central rod (186). When tightening the outer nut (194) tightened the Central rod (186), and therefore, the intermediate nut (196) and the first slot of the spring (188) are shifted upward relative to the orientation of the controller (100) in figure 2. Between the outer nut (194) and intermediate nut (196) is the upper part of the casing of the drive (122), as shown in the drawing. In this configuration, the outer nut (194) and intermediate nut (196) fixed Central rod (186) so as to prevent axial displacement relative to the upper part of the casing of the drive (122). In addition, the retaining nut (a) and (198b) fix the first slot of the spring (188), to prevent it from shifting down relative to the orientation of the regulator (100) figure 2.

In the General case, when the node controller (100) is installed in the process control system with fluid is zirovanii materials or in the system of liquid supply, a control unit (114) can be displaced in the cavity (135) and the neck (128) of the actuator (106) depending on the fluid pressure at the inlet (110) and the outlet (112) of the valve body (102). More specifically, the fluid flows from the inlet (110) channel (116). After the liquid will pass through the channel (116), a significant part of the fluid flows to the outlet (112), and the rest of the fluid flows through the through hole (151) and razzenkovannye part of the hole (148) in the disk holder (144) and the transition sleeve (142), respectively. This part of the fluid flows through the hollow shaft (130) through the holes (188b, 190b, 192b) in the first and second socket spring (188) and (190) and retaining plate (192) respectively for trim control unit (114). In a variant of the invention presented in this description of the invention, the holes (190b) in the second slot of the spring (190) are aligned with the holes (192b) in retaining plate (192). It ensures the free flow of fluid under pressure in the regulator (100) through the holes (190b) and (192b) for trim control unit (114). In one embodiment of this invention, one part of the second socket spring (190) or the retaining plate (192) may have a recess in the axially located surface. The second part of the second socket spring (190) or the retaining plate (192) may have a seizure, which must be such deepening. The recess b the children to get into the groove only when the second socket spring (190) and retaining plate (192) will be properly combined to ensure the message on fluid between the holes (190b) and (192b), as shown in the drawing. Alternatively, in another embodiment of this invention, the second slot of the spring (190) and retaining plate (192) may form a single element, thereby eliminating the necessity of combining parts. In another alternative embodiment of this invention, the holes (190b) and (192b) can be elongated hole passing at least partially around the circumference of the socket springs (190) and retaining plate (192). In this configuration, the second socket spring (190) and retaining plate (192) can be positioned differently relative to each other, and still provide the necessary fluid communication environment between the holes (190b) and (192b).

Part of the liquid that flows through the valve housing (102) to the outlet (112), returns to the control system of technological process with fluidized material or system fluid. More specifically, in one configuration, the fluid pressure at the outlet (112) is channelled into another line currents (not shown) and directed to the second regulatory control hole (129) in the lower part of the casing of the actuator (124). Therefore, the pressure at the outlet (112) of the to the of Cusa valve (102) is equal to the pressure at the second regulating the input hole (129), and this pressure, in the end, acts on the lower plate aperture (136b). In other embodiments of this invention can be used in the pressure regulator in the discharge line (not shown)that receives the fluid from the outlet (112) and creates pressure on the second control input (129). In addition, in one configuration, the pressure at the inlet (110) is channelled into another line currents, leading to the control valve (not shown), which, in turn, creates the pumping pressure of the first regulating inlet (125) in the upper part of the casing of the drive (122), and in some embodiments of this invention is to control the pumping pressure.

Regardless of the source of the pressure on the first and second regulating the input holes (125) and (129), the pressure of the first regulating inlet (125) acts on the block diaphragm (133), shifting the pressure regulator (100) towards the closed position and the pressure at the second regulating the input hole (129) and the force of the spring (193) acting on the block of the diaphragm so that the pressure regulator (100) is shifted towards the closed position. Therefore, when the pressure of the first regulating inlet (125) acts on the top plate of the diaphragm (a) with a force that exceeds the force with which the pressure acts on the second regulating the input hole (129) together with the unit position the scan (138), specifically with spring (193) unit positioning device (138), plate diaphragm (a) and (136b) and hollow shaft (130) are shifted down against the bias of a spring (138). More precisely, the plate aperture (a) and (136b) and hollow shaft (130)and retaining plate (192) and the second slot of the spring (190) unit positioning device (138) are shifted down. This shift leads down to the compression spring (193) in the direction of the first connector spring (188). Therefore, we should expect that when the slippage of the hollow shaft (130) down the Central rod (186) and the first slot of the spring (188) remain in the position represented in figure 2, a hollow shaft (130), retaining plate (192) and the second slot of the spring (190) are shifted down, resulting compressed slot (146) in coupling with a valve seat (104), as shown in Fig. 4.

On the contrary, when the pressure at the second control input (129), together with the spring (193) applies force to the control node (114), which exceeds the pressure at the first control input (125), a control unit (114) is shifted upward to the open position shown in Fig. 2 and Fig. 3. The sum of the forces acting up and acting on the diaphragm (134), counteracts the pressure at the first control input (125), which serves as the regulatory pressure to position the control unit (114)including a hollow shaft (130) in accordance with the flow necessary to ensure the proper speed downstream. In addition, if you fail aperture (134), for example, due to rupture of the material of the diaphragm spring (193) will apply force to the second slot of the spring (190), which, in turn, will cause the control unit (114) to move to the open position shown in Fig. 2.

Unlike regulators, with flat, convex, or otherwise protruding surface over which fluid flows at an open gate valve, bowl-shaped saddle with a recess on the surface, as in the attachment (132), are illustrated and described in this document, is not experiencing a high-frequency oscillations at high flow rates in systems with high pressure inlet and low pressure outlet. Changes in the mount (132) to use the surface with a recess, respectively, alter the flow path, which passes the fluid in the channel (116), to reduce the pressure gradient acting on the tube of the valve. The pressure drop on the tube the valve is reduced as the negative pressure gradient contributes to the lowering of the tube valve to the valve seat (104). As a result, the controller (100) is more stable at high flow rates without entering in a mode of high-frequency oscillations observed for previous models of pressure regulators.

For specialists in this area it is clear that the regulator pressure is of (100), presented in the drawings and described in this document can be used with different configurations of the mount (132) and/or tubes valve having a Cup-shaped or concave surface. For example, multi-component attachment (132) can be replaced by the element as a whole, which can be screwed or otherwise attached to the lower end (130b) of the hollow shaft (130) and to provide a recess for accommodating and holding the compressed slot (146). Such an element can have razzenkovannye part, similar to those shown for the combination of the transition sleeve (142) and disc holder (144), or the recessed portion may have other geometric features that reduce the pressure gradient in the tube valve, for example, it can have a tapered, rounded and similar form. In addition, the mount (132) can be formed from different combinations of components, or a node may be a single unit with hollow shaft (130), while the lower surface with a recess, channel, providing the message to a fluid between the inlet pressure and the inner surface of the hollow shaft (130), and the surface of the accession pressed nests (146). Finally, it should be recognized that although this description of the invention relates to pressure regulators, the subject of this image is the shadow can be used successfully in the management processes from fluid materials including regulating valves, actuators and any other possible devices.

In light of the above, this description of the invention should be construed only as leading examples of the present invention, therefore, different ways, without deviating from the essence of this invention should be included in the scope of this invention.

1. The regulator consists of:
of the valve body, creating a path of fluid flow and having a valve seat;
the casing of the drive, and connected with a valve housing;
body control located inside the casing of the actuator and adapted for displacement relative to the valve housing and seat the valve for regulating fluid flow through the flow path by moving between an open position in which the governing body is extended from the seat of the valve, and a closed position in which the governing body comes in contact with the valve seat; and
spring functionally associated with body control and bias control in the open position;
thus the bottom surface of body control, directed to the valve seat has a recess, including razzenkovannye part located large diameter closer to the valve seat, and a smaller diameter further from the seat of the valve.

2. The regulator according to claim 1 containing block aperture located in the housing, the actuator is functionally associated with the governing body for movement control in response to changes in pressure at the output of the controller.

3. The regulator according to claim 1, characterized in that the surface of the governing body with the recess is concave or conical surface.

4. The regulator according to claim 1, characterized in that the governing body includes:
hollow shaft and
the mount that is attached to the open end of the hollow shaft, the middle to the valve seat and having a surface with a recess.

5. The regulator according to claim 4, characterized in that the attachment contains:
reducer sleeve attached to the open end of the hollow shaft; and
disc holder connected to the sleeve, in which the surface with a recess defined by a hole in the disk holder and razzenkovannye part of the transition sleeve.

6. The regulator according to claim 5, characterized in that razzenkovannye part of the transition sleeve has a portion of larger diameter near the saddle valve and the portion of smaller diameter further from the seat of the valve, while razzenkovannye portion provides communication between the through current and the inner surface of the hollow shaft in a fluid environment.

7. The regulator according to claim 5, wherein the disk holder has a bottom surface with an annular groove, the fastener Assembly includes an annular support piece located in the groove with the possibility of coupling with a valve seat in the closed position of the management body to prevent fluid flow through the housing is of advice.

8. The mount for the governing body of the regulator consisting of a valve housing, creating a path of fluid flow and having a valve seat; a casing of the actuator, and connected with a valve housing; and a shifting element functionally associated with body control and bias control in the open position, while the governing body is located in the drive housing and can be displaced relative to the valve housing and seat the valve for regulating fluid flow through the flow path when moving between the open position and a closed position in which the governing body is included in the coupling with the valve seat; and the mount, and the mount contains:
the fitting that attaches the mount to the middle to the valve seat end of the governing body; and
surface with a recess directed toward the saddle valve.

9. The fastening Assembly of claim 8, characterized in that the surface with the deepening of the governing body is concave or conical.

10. The fastening Assembly of claim 8, characterized in that the surface with the recess has razzenkovannye part of a larger diameter near the saddle valve and the portion of smaller diameter away from the saddle valve.

11. The fastening Assembly of claim 8, characterized in that the governing body includes a hollow shaft, and connecting h is here attached to the open end of the hollow shaft, located closer to the valve seat.

12. The mount according to claim 11, containing:
reducer sleeve having a connecting part that is attached to the open end of the hollow shaft; and
disc holder attached to the intermediate sleeve, in which the surface with a recess defined by a hole in the disk holder and razzenkovannye part of the holes of the transition sleeve.

13. The mount according to item 12, wherein razzenkovannye part of the holes of the transition sleeve consists of a larger diameter, located near the seat of the valve, and a portion of smaller diameter, located at a distance from the seat of the valve, and razzenkovannye part communicates via a fluid with the inner surface of the hollow shaft.

14. The mount according to item 12, wherein the disk holder has a bottom surface with an annular groove, and a fastening Assembly includes an annular support piece located in the groove with the possibility of entering the coupling with the valve seat in the closed position of the management body to prevent fluid flow through the valve housing.

15. A method of manufacturing a positioning device and a bypass valve that contains a positioning device, including:
ensuring the governing body, hollow inside and having on one end surface with a recess;
ensure the giving body displacement;
attaching the retaining plate to the inner part of the governing body;
screw intermediate the nuts on the first threaded end of the Central rod;
the placement of the second threaded end of the Central rod in the Central hole of the holding plate;
the installation of the Central rod, carried out through the shift element and the hole in the nest in the spring so that the shifting element located between the retaining plate and the socket springs;
screw the first screw nut on the second threaded end of the Central rod;
preliminary tensioning device positioning; and
the accession of the positioning device to the bypass valve.

16. The method according to item 15, wherein the pre-tensioning device includes positioning the driving intermediate the nut and the first threaded nut.

17. The method according to item 15, characterized in that it further includes navertyvanija second threaded nuts on the second threaded end of the Central rod.

18. The method according to item 15, characterized in that it further includes driving the intermediate nuts to the specified position defined by one or more marks on the Central rod.

19. The method according to item 15, wherein attaching the positioning device to the controller includes the scene is of an annular flange on the outer surface of the governing body between the two plates of the diaphragm in the casing of the actuator.



 

Same patents:

FIELD: electricity.

SUBSTANCE: reference sample comprises a metal base with a central zone of reference complex stressed condition through the base thickness. At the edges of the base at one or different sides there is one or several zones of pad welds from another metal, coefficient of linear expansion and yield point of which is lower than the coefficient of linear expansion and yield point of the base metal. The base is first exposed to high-temperature tempering, afterwards control marks or a grid of measurement bases are applied onto surfaces of the central zone of the base at two sides, for two test measurements after high-temperature tempering of the base before applying pad welds and in the end of thermal treatment of the base already with pad welds. The form of the base, locations of pad welds and the mode of thermal treatment are defined in advance as a result of computer simulation modelling by the method of finite elements with account of grades of the base metal and pad welds metals and the required reference complex stressed condition of the central zone of the base through its thickness.

EFFECT: increased validity of results of measurements of mechanical stresses in cross sections of various thick-walled metal structures.

2 cl, 5 dwg

FIELD: electricity.

SUBSTANCE: method of determining tangential stress in steel pipelines involves making a sample in form of a hollow cylinder from the same material as the structure; step by step loading of the sample; measuring coercitive force indicators at each loading step, with a defined orientation of magnetic flux generated in the coersimeter relative the sample; obtaining a relationship between the coercitive force indicators and values of stress in the sample; measuring the coercitive force indicators of the metal of the structure; determining stress values using the obtained relationship; tangential stress in the sample is generated by applying torque to the sample; the coercitive force is measured along the axis of the sample or the pipeline twice, while directing magnetic flux in opposite directions. The coercitive force indicator used when determining tangential stress is the magnitude of the difference between measured values of the coercitive force.

EFFECT: high accuracy of determining tangential stress in surface steel pipelines.

1 dwg, 1 tbl, 1 ex

FIELD: measurement equipment.

SUBSTANCE: method for determining residual hardening stresses involves hardening of samples and determination of residual hardening stresses; at that, a pack is formed of plates of similar size, which are numbered and marked in advance; then, the above pack is subject to hardening; after that, plate bending deformations are measured in two planes, as per which residual hardening stresses are calculated.

EFFECT: improving accuracy of determination of residual hardening stresses.

6 dwg

FIELD: measurement technology.

SUBSTANCE: invention relates to determination of the stress-strain state of metal structures of high-risk facilities in the oil, gas and chemical industry, transportation systems and oil and gas processing using brittle strain-sensitive coatings, which enables to obtain a clear picture of the highest stress concentration and obtain data for evaluating strength of potentially hazardous structures. The brittle coating for deformation and stress analysis is made from a mixture containing water and sugar, with the following ratio of components, wt %: water 65-75, sugar 25-35.

EFFECT: reduced harmful effect on the environment.

FIELD: transport.

SUBSTANCE: invention relates to machine building. Load limiter comprises force transducer and electronic device to generate warning signal of interlocking the load lifting mechanism actuator in machine reloading. Force transducer converts the force acting threat into pressure and, further, into electric signal and comprises base and loose piston separated by layer of elastomer. Transducer is composed of, particularly, false cradle of automatic hydro lifter or is adapted for fitting under traveler winch drum support body and may be shaped to a ring or parallelepiped with holes for attached at the machine. Said transducer can incorporate several pressure transducers to define mean load and load application point with generation of data or control signals. Clearance between sidewall of loose piston and base inner sidewall is selected to prevent extrusion of elastomer while its length is selected to protect against lateral loads. Electronic device is built around microcontroller and incorporates output device and wire or wireless interface.

EFFECT: impact and vibration resistance, expanded applications, higher safety.

8 cl, 1 dwg

FIELD: measurement equipment.

SUBSTANCE: device includes a sensor base, the maximum thickness of which is much less than two other measurements, a sensing element of elongated shape, which encloses the base with spiral coils so that a short section of each of spiral coils passes throughout the thickness of the base. Short sections of spiral coils are intended for orientation in the plane almost perpendicular to direction of interference effect, and long sections of spiral coils are intended for orientation in the plane almost perpendicular to direction of measured effect.

EFFECT: improving interference resistance of the sensor at performance of measurements.

18 cl, 4 dwg

FIELD: measurement equipment.

SUBSTANCE: according to one method, measurement of stretching forces acting at a rail may be realised as follows. The rail is fixed in two or more points, on the rail between fixation points a weight of large mass is suspended, and a signal depending on the stretching force is frequency of internal oscillations of the produced system, formed by the specified rail and the suspended weight. According to the second method, the amplitude-frequency characteristic is measured in the similar system of a rail and a suspended weight. The device comprises a massive frame, including two and more grips of rails, a device of excitation of weight oscillations, in one or more weights installed on the rail, comprising vibration sensors. The device may be installed on an electric locomotive, a diesel locomotive, a gasoline locomotive, a track repair machine or a laboratory car.

EFFECT: possibility to measure stretching forces acting at a rail, without installation of sensors on a rail.

6 cl, 2 dwg

FIELD: measurement equipment.

SUBSTANCE: device consists of strain gauges and an independent decoding device of signals from strain gauges. Strain gauges are fixed on a removable process component with cross sectional area providing maximum full use of functional capabilities of strain gauges. The removable component is fixed on a pull-rod at two points equally spaced throughout its length with quick-detachable clips providing compression force preventing sliding of pressed ends of the removable component relative to the pull-rod in the specified measurement range of tension forces.

EFFECT: higher measurement accuracy.

3 dwg

FIELD: measurement equipment.

SUBSTANCE: multicomponent displacement sensor includes a housing and a sensitive element with piezoelectric detectors. Force-receiving element is made of two longitudinally connected elastic bars, the end faces of which are connected by means of a ball hinge, on which a force transfer element is arranged, which is made in the form of a ball bearing installed with its inner race on force-receiving element in maximum deflection zone; sensitive element is made in the form of a deformed outer race of the above bearing, which is located concentrically to inner race. On internal surface of deformed race there are openings for arrangement of piezoelectric elements, and bearing cage is fixed against annular displacement relative to support ring so that each ball of the bearing contacts the working surface of piezoelectric element so that centres of balls coincide with direction of radial movements of sensitive element of the sensor.

EFFECT: enlarging functional capabilities of the device.

3 dwg

FIELD: measurement equipment.

SUBSTANCE: force-measuring sensor includes a force-measuring washer with one flat surface and another spherical concave surface and a face-mounted washer with one mating spherical convex surface and another flat surface. Winding of a measuring resistance strain gauge is rigidly fixed on external cylindrical surface of force-measuring washer by means of an adhesive joint. Force-measuring sensor is located on the attached part on the threaded bar and pressed to the attached part by means of a nut.

EFFECT: increasing the operating time of the device; improving measurement accuracy of threaded joint force; simplifying the design.

2 cl, 6 dwg

FIELD: mechanical engineering; crane-manipulator plants.

SUBSTANCE: invention relates to load-lifting machines with boom equipment and it can be used for evaluation of strength of structural members of grab-type mounted devices used with cranes and selection of material, geometric, mass-inertia and power parameters of said devices. According to proposed method, analytic dependences are used relaying geometric, mass-inertia and kinematic parameters of structural members of crane-manipulator plant and load with value of determined forces and moments.

EFFECT: increased accuracy of determination of dynamic loads acting onto structural members of crane-manipulator plant handling long-cut loads.

2 cl, 1 tbl, 5 dwg

FIELD: testing engineering.

SUBSTANCE: method comprises using bolts-meters as a structure to be tested and recording deformations or displacements of the bolt head or displacement of the movable member mounted inside the bolt during loading. Before and after the run, the stress-strain condition of the bolt-meter is calculated with regard to the deformation of butt parts for different values of axial loading applied to the bolt in the study range.

EFFECT: enhanced accuracy.

2 cl, 9 dwg

FIELD: measuring technique.

SUBSTANCE: method comprises measuring the radius of curvature of rod article producing by plastic deformation and determining the amplitude of variation of axial residual stress in the peripheral direction of the rod article, which characterizes the asymmetry of the residual stress according to the formula proposed.

EFFECT: enhanced accuracy of measurements.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: bench comprises the frame and carriage that is mounted for permitting reciprocation in horizontal guides. The carriage is kinematically connected with the drive and is provided with changeable roller bearing for permitting cooperation with freely suspended section of conveyor belt. One end of the conveyor belt is spring-loaded. The H-shaped lever is pivotally connected with the frame for permitting cooperation with the top surface of the section of the conveyor belt. The H-shaped lever is provide with a damper mounted in the zone of the pivot. The changeable weights are mounted on the axle.

EFFECT: expanded functional capabilities.

3 cl, 3 dwg

Flow meter // 2303768

FIELD: measuring technique.

SUBSTANCE: flow meter comprises device for measuring mean velocity of fluid flow that has blade, device for measuring the level of the fluid flow, lever with float, axles, sensors for measuring the angle of rotation of the blade and measuring the angle of float movement, and electronic unit for processing data. The blade and the lever with float are secured to the axles of their sliding bearings. The blade is mounted in the plane of the central longitudinal axis of the flow. The units for fastening the sliding bearing of the blade and lever with float are made for permitting rotation in the horizontal plane. The diameter of the float and the parameters of the blade depend on the width of the passage, mass of the float, mass of the lever, density of the fluid, mean flow velocity, depth of detachment of the float in calm water, and distance from the axle of the fastening of the blade to the bottom of the passage, and are determined from the formulae proposed.

EFFECT: enhanced precision and reliability.

4 cl, 2 dwg

FIELD: the invention refers to the field of nondestructive control.

SUBSTANCE: on the surface of the detail they measure with the aid of the nondestructive mode a physical parameter according to whose meanings one can judge about the values of tensions in the corresponding zone of measurements. In quality of a physical parameter it is possible to choose the work of the output measured with the aid of the nondestructive method of contact difference of potentials, according to the minimal value of which one can discover the zone with maximal tensions on the surface of the detail.

EFFECT: possibility quickly and accurately discover dangerous zones on the surface of details.

FIELD: physics.

SUBSTANCE: process of torque measurement is based on periodic impact of measured torque μ on resonance oscillating system with threshold of sensitivity μn and frequency equal to the system resonance frequency ω. So when μ<μn, the oscillating system is brought into excited state by external force much higher than μn, then it is brought into forced-oscillation regime by the measured torque μ with a lag between it and damping system oscillations consequently taking form of Δβ=nπ, where n=0, 1, 2, .... The sought torque value is defined by the amplitude difference of these phases, Δϕn, according to the formula: where k is stiffness coefficient of oscillating system, and α is its damping rate.

EFFECT: higher measuring sensitivity.

5 dwg

FIELD: physics; measurement.

SUBSTANCE: present invention pertains to force-measuring technology. The load measuring device, working on three mutually perpendicular axes, and moments about these axes, comprises four elastic elements, fixed to a base at corners of a square, made in form of separate bars with a cannular cross-section, on which tensoresistors are put, a rigid force transmission plate and a base, joined by elastic elements. All tensoresistors are put on elastic elements along their formations. For each measured load, two tensoresistors are put on each elastic element. Tensoresistors are put on diametrically opposite sides of the elastic element. The centres of the tensoresistors for measuring loads, lying in the plane of the force transmission plate on all four elastic elements lie in the same plane, parallel to the plane of the force transmission plates. The centres of tensoresistors for measuring loads, perpendicular to the plane of the force transmission plate, as well, lie in the same plane, parallel to the plane of the force transmission plate.

EFFECT: increased accuracy and wider range of load measurements.

4 dwg

FIELD: physics, measurements.

SUBSTANCE: invention is related to methods for detection of residual stresses in axisymmetric tubular products after plastic deformation. Available experimental method is used to identify tangential residual stress in surface layer of tubular product, value of which is used to detect distribution of residual stresses in the whole section of tubular product by the following formulas:

where σr, σθ, σz are accordingly radial, tangential and axial residual stresses; is value of tangential residual stress in surface layer of tubular product; R1 and R2 are accordingly external and internal radiuses of pipe; is nondimensional parametre, which characterises relative thickness of pipe wall; r is radial coordinate; µ is Poisson ratio of pipe material.

EFFECT: improved accuracy and expansion of method potential by determination of all components of residual stress tensor in the whole section of axisymmetric tubular products.

Dynamometre // 2370738

FIELD: physics.

SUBSTANCE: dynamometre has a torque sensor, a weighting device and a unit for connecting the sensor to the weighting device. The weighting device is in form of two support bearings, each with two rings. The support bearings are in line, the ring of one of them is in contact with the ring of the other and these rings are joined together, and the unit for connecting the sensor with the weighting device is on the joined bearing rings. The torque sensor can be made in form of a flexible rod, which grasps the joined bearing rings and is attached by one end to the said rings, and a dynamometre, connected to the second end of the rod. The dynamometre measures load on different types of mine working supports.

EFFECT: possibility of monitoring manifestation of rock pressure on places with combined support with high accuracy.

2 cl, 2 dwg

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