Fluidised flow control valve

FIELD: machine building.

SUBSTANCE: proposed valve 10 has body 12. Said body has valve chamber 18 with valve seat 30 and valve stem 20 with flow channel 22, 24. Valve stem 20 is arranged inside valve chamber 18 ahead of valve seat 30 to rotate about rotational axis A to control fluidised flow flowing through valve 10. Valve comprises spring devices to displace valve stem 20 toward valve seat 30 perpendicular to said rotational axis A to provide for tight contact between stem and seat. Said spring devices comprise at least one cantilever spring 40 mounted in gap 42 opposite valve seat 30. Said spring 40 is secured inside valve body. Spring tail part stays in contact with cylindrical pressure surface to displace valve stem 20 to valve stem 30. Besides valve comprises coal dust injection system for shaft furnace that incorporates above described valve.

EFFECT: higher tightness of valve and furnace irrespective of working conditions and accumulation of finely-dispersed inclusions.

15 cl, 2 dwg

 

The technical field

The present invention relates to regulating flow valve for fluidized material, in particular for use in pneumatic transport systems fluidized material.

The level of technology

In transport systems for fluidized bed material bed material is transported by pipeline in bulk through the fluid carrier, such as carrier gas or carrier fluid. A concrete example of the pneumatic transport of a pneumatic conveying system using a carrier gas is a system of pulverized coal injection small grain through tuyeres in the shaft furnace.

To implement dosing of bulk material in the field of transport of fluidized material is well known to be installed in the pipeline regulating flow valve for controlling the feeding speed of the fluid carrier and, thus, the feed rate passing through the valve of the bulk material.

A common example of regulating flow valve used, for example, pulverized coal, is cork-pass valve. Usually cork pass valve contains a valve body including a valve chamber and a valve seat, and a valve stem with a flowing Cana is om. The valve stem is located within the valve chamber, in front of the saddle, and made with the possibility of rotation around the axis of rotation. Rotation allows you to adjust passing through the valve flow by setting the position of the flow channel of the valve stem against the valve seat.

Obviously, the existence of tight contact between the valve seat and the valve stem is an important requirement for any valve. When regulating the flow valve should be used in a system in which the working temperature of the fluid carrier and/or the ambient temperature and therefore the temperature of the valve subject to significant changes, the achievement of tight contact between the rod and the saddle can be problematic. In fact, the temperature can cause leakage of the valve, for example, due to differing thermal expansion of the valve body and the stem of the valve and/or valve seat. This problem is typical, for example, for a system of pulverized coal injection. In such cases, cork valves are usually installed on the valve spring device, displacing the valve stem and the valve seat to each other in the direction perpendicular to the axis of rotation of the valve stem. The first version of this design involves the saddle, spring shifting relative to the positive terminal. The second option, which is the subject of the present invention involves the rod, a spring move relative to the saddle.

In many known spring shift cork valve spring device consists of coil springs mounted in the guide hole of the valve body thereby to move the rod and the saddle to each other. It was found that this type spring offset valve stem in some cases, guarantees the tightness of the fluid is not fully, especially in the system of pulverized coal injection operating at high temperature and pressure. Moreover, in transport systems for fluidized bed of granular material is particulate matter, which is separated from the stream of fluidized granular material, accumulate in cavities within the valve body and, consequently, also in the guide holes of the coil springs. Thus, the coil spring can be locked in a certain position. As soon as the problems arise when the spring is working, the tightness of the fluid immediately violated, especially when the temperature drops. This is particularly problematic in the pneumatic transport system, which is an important requirement is ageing. Further disastrous consequence possible is lakirovki may be damage to the valve, or, if you have a valve with an actuator, damage to the actuator if the valve in such a locked state.

Technical task

The aim of the present invention to provide regulating flow valve for fluidized material, which improves sealed to the fluid contact between the valve stem and the valve seat regardless of the working conditions and the accumulation of fine-grained inclusions.

General description of the invention

To achieve this goal, consider the invention proposes regulating flow valve for a fluid material, comprising a valve body having a valve chamber and a valve seat, the valve stem with the flow channel and the valve stem is located within the valve chamber before the valve seat so that he had the possibility of rotation around the axis of rotation for regulating flow through regulating the flow valve. Regulating flow valve also includes a spring mechanism, clamping the rod to the seat perpendicular to the axis of rotation, to achieve a tight contact between the seat and the valve stem, spring means bias the valve stem to the valve seat perpendicular to the axis of rotation to achieve a tight contact between the valve seat and the valve stem. According to the importance of the WMD aspect of the invention a spring device contain at least one cantilever spring, installed in the gap opposite to the valve seat in order to press the valve stem to the valve seat.

Regulating flow valve according to the invention allows to achieve improved sealing against fluid regardless of the operating condition of the valve. Moreover, the use of bending springs cantilever type eliminates the use of coil springs with guide holes, and thus, the function of the clamping displacement of the valve becomes immune to clogging of finely dispersed inclusions.

In a preferred embodiment of the invention at least one cantilever spring is a spring plunger. A spring-loaded plunger has a first end section which presses the valve stem to the valve seat, and a second end section attached to the valve body. Although it would be possible using other Flexural springs cantilever type, such as a plate spring, spring plungers are preferred.

In order to achieve a more uniform bending stresses along the length of the spring plunger, spring plunger is preferably made tapering in the direction of its first end portion.

Mainly, cantilever spring includes fifth element mounted on the first is the end of the cantilever spring and having a contact surface, the corresponding outer surface of the valve stem. This configuration makes it possible to achieve close surface contact in a specific area between the spring and the rod.

As another advantage of the cantilever springs regulating the flow valve in the preferred embodiment, may include an adjustment device, which is fixed to the second end section of the spring plunger, with the adjusting device allows the installation of the axial position of the spring plunger relative to the valve stem. Because the tension of each cantilever spring, and therefore the contact pressure between the valve stem and the valve seat, can be adjusted, the adjustment feature provides the advantage to guarantee the tightness relative to the fluid. Initial adjustment allows you to adjust the valve for some applications (where different pressure, temperature, type of fluid and the like). The adjustment of the valve during its lifetime allows to take into account changes in the process or, for example, wear of the valve parts. To adjust the axial position of the spring plunger adjusting device preferably includes a working portion for adjustment of the axial position of the spring pusher, if e is ω working part protrudes from the valve body. Thus, it is possible to adjust the valve during operation.

In order to achieve uniform contact between the valve stem and the valve seat, it is preferable to provide two pairs of cantilever springs that are installed in the respective gaps tangentially relative to the valve stem and on opposite sides of the duct through the valve body. In this configuration, the cantilever springs of each pair are installed in parallel, and two cantilever springs any one installed in pairs opposite to each other coaxially ratio.

Mainly, the valve-flow regulator also includes a drive shaft mounted rotatably in the valve body, and the coupling Oldham connecting the valve stem and the drive shaft. This configuration is a simple and reliable way floating installation of the valve stem in the valve chamber in order to give the valve stem can move relative to the valve seat.

In order to facilitate access to the console springs and particularly to an adjusting device, the gap for each of the cantilever spring is preferably perpendicular to the axis of the drive shaft in the valve body.

Despite the fact that a valve with a spherical stopper could also benefit from the use of cantilever springs, prefer the LNO yet especially in pneumatic transport systems that the valve stem contains essentially cylindrical hollow body having a cylindrical sealing surface in contact with a corresponding sealing surface of the valve seat, and a cylindrical clamping surface is in contact with the first end section of the cantilever spring or, if available, the contact surface of the saddle element.

It should be understood that regulate the flow valve according to the present invention is particularly suitable for use in the system of pulverized coal injection for blast furnace.

Brief description of drawings

The following is a description of a preferred variant of the invention with reference to the accompanying drawings on which is shown:

Figure 1: view of regulating the flow valve according to the invention in longitudinal section; and

2 is a view of regulating the flow valve in cross section along the line II-II in figure 1.

Further details and advantages of the present invention will become apparent from the following detailed description.

Detailed description of drawings

Figure 1 shows regulate the flow of fluidized material valve, indicated generally under the reference number 10. Regulating the flow valve is designed for use in the pipeline is the transport system for a fluidized bed of granular material, in particular for use in pneumatic conveying installation, such as the system of pulverized coal injection for blast furnace.

Regulating the flow valve 10 consists of a valve housing 12 having an inlet 14 and outlet 16 holes. The valve body 12 defines the boundaries it is located the valve chamber 18 communicating with the inlet 14 and outlet 16 holes. The stem 20 of the valve mounted within the valve chamber 18. The stem 20 of the valve housing is generally cylindrical hollow configuration with the first opening 22 and second opening 24 located on the side in the cylindrical shell of the rod. Holes 22 and 24 form a flow passage through the stem 20 of the valve. The stem 20 of the valve also includes a connecting section 26 of the connecting rod 20 of the valve with a drive shaft 28, mounted with a possibility of rotation in the housing 12 of the valve.

In addition, regulating the flow valve 10 includes a seat 30 of the valve, fixed in the housing 12 of the valve on the edge of the valve chamber 18. Saddle valve 30 has, in General, tubular, cylindrical shape and is installed in the dual slot 32 of the housing 12 of the valve. The seat 30 of the valve forms a further flow channel which connects the valve chamber 18 with the outlet 16. As shown in figure 1, the valve stem 20 is located in front of the valve seat 3. The stem 20 of the valve is made with the possibility of rotation around the axis of rotation And through the drive shaft 28. Currently known way for valve rod type rotating position of the rod 20 relative to the valve seat 30 of the valve allows you to adjust passing through the valve 10 stream by setting the degree of coincidence between the flow channels of the stem 20 of the valve and, accordingly, the seat 30 of the valve. In this regard, it should be noted that the second hole 24 of the stem 20 of the valve has an integral form, in which one part has a conical, essentially, a triangular shape, and the second is essentially semi-circular (when viewed in projection on a plane). This form allows you to better manage the flow by making the cross section of the flow channel is essentially a linear function of the angular position of the rod 20 of the valve (when the match is limited to the first essentially triangular part of the hole 24). As further shown in figure 1, two retaining flange 34, 36 mounted on the housing 12 of the valve in the continuation of the inlet 14 and, accordingly, the final 16 holes.

As is clearly shown in figure 2, the valve stem 20 has a cylindrical section of outer sealing surfaces. However, the stem 20 of the valve need not be cylindrical, it is also possible to other types, such as sferica the Kie stub, though the plot sealing surface is a surface of rotation of a body. The seat 30 of the valve has a sealing area of the surface that closely matches the sealing surface of the stem 20 of the valve so that between them possible intimate contact.

As can be seen further in figure 2, to move the rod 20 relative to the valve seat 30 of the valve in the direction perpendicular to the axis of rotation And a spring device to achieve a tight contact between the seat 30 of the valve stem 20 of the valve. According to the invention, these spring means include a cantilever spring 40. It should be understood that the cantilever spring 40 are bending springs, working at the expense of elasticity in bending. Although you can use other types of cantilever springs, such as plate, cantilever springs are preferably spring loaded plungers 40 round cross-section for the reasons explained below. As seen in figures 1 and 2, four spring-loaded pusher 40 is placed in the appropriate clearances 42, adjacent to the valve chamber 18 and opposite the seat 30 of the valve. Each spring, the pusher 40 has a first end part directed along the tangent to the rod 20 of the valve and spring bias the stem 20 of the valve seat 30 of the valve, and a second end portion attached to the housing 12 CL the pan. As should be clear, the direction of the resultant of the spring bias force F produced by the spring plungers 40, perpendicular to the axis of rotation a and is directed toward the seat 30 of the valve.

As can be seen in figure 2, each spring-loaded plunger 40 has the form of a tapered rod, tapering in the direction of its first end portion. Thus, compared with the pushers cylindrical shape, in this case achieves a more uniform distribution of stress in bending along the entire length of the pusher. To provide surface contact between each spring plunger 40 and the rod 20 of each valve spring plunger 40 is mounted at its first end section fifth element 44. Each truck element 44 has a contact surface corresponding to the outer cylindrical external surface of the stem 20 of the valve.

Also, figure 2 shows that each spring-loaded plunger mounted on the valve body 12 by means of respective adjusting device 46. The second end portion associated with it a spring pusher 40 is fixed in the adjusting device 46, which allows its installation, with the adjustment of the axial position of this spring follower 40 relative to the stem 20 of the valve and, thus, the touch point on the tangent between them. How would the ü clear the axial location of the spring pusher 40 can reduce or increase the distance between its first end portion and the axis of rotation And keeping contact tangentially with the stem 20 of the valve. Thus, thanks to the adjusting device 46 has the opportunity to adjust the bending of the spring plunger 40 and, consequently, the magnitude of the force F, i.e. the degree of spring deflection. To that end, each adjusting device 46 has a hollow cylindrical sleeve 48 mounted in the hole, which is a continuation of the corresponding gap 42 and extending outward from the housing 12 of the valve inside the clutch 48 is installed sleeve 50 with internal thread. The clutch 48 communicates with a corresponding external thread 52 of the second end portion of the spring plunger 40 and is screwed on the external thread 52 to a stop with the clutch 48 by nut 54. When loosening the lock nuts 54 axial position of the spring plunger 40 can be accurately adjusted by turning, i.e. screw spring plunger 40 using, for example, the torque wrench. For this purpose the housing of the spring plunger 40 has a rotational-symmetric form with a circular cross section, tapering towards the anterior end. It should be understood that the adjusting device 46 has an operating section 55 formed by the nut 54 and the outer section and the coupling 48 and the spring pusher 40, extending from the valve body 12. With this design, it is possible to control the adjusting device 46 without disassembling the valve body 12, i.e. during its operation, for example, in order to re-adjust the pressure tight contact or to exit the lock status. It should also be understood that in addition to adjusting the design of the setting device 46 is easy to dismantle and remove the spring plunger 40, for example, for maintenance or inspection. In the valve body 12 is provided with two locking pins 56, in order to avoid displacement of the rod 20 of the valve when removing the spring plungers 40. In order to maintain contact between the saddle elements 44 and the stem 20 of the valve in any axial position and during rotation, each truck element 44 fixed at its spring plunger 40 so as to be rotatable around the longitudinal axis of the spring plunger 40 and preferably slightly turn away from the axis parallel to the axis. And, for example, by a spherical connection.

As should be clear from figure 1 and figure 2, two pairs of spring-loaded pushers 40 are located on opposite sides passing through the body 12 of the valve flow passage in the respective gaps 42 tangentially relative to the rod 20 of the valve. Spring plungers 40 to the each pair are parallel (i.e. are parallel to the longitudinal axis and assume no contact with each other). Two spring-loaded plunger 40 of each pair are of opposite coaxial relationship, as shown in figure 2. This arrangement of four spring-loaded pushers 40 provides uniform contact pressure on the sealing surface of the seat 30 of the valve stem 20 of the valve.

As shown in figure 1, the stem 20 of the valve is connected with a drive shaft 28 by means of the coupling element 60. The connecting member 60 has a generally disk shape and design of the coupling Oldham. With this purpose, the connecting element 60 has a longitudinal recess at the first side coincident with the paired protrusion of the drive shaft 28, and a longitudinal protrusion on the second side, perpendicular to the groove on the first side and is coincident with the mating recess on the connecting section 26 of the stem 20 of the valve. This configuration makes it possible floating rods 20 of the valve in the valve chamber 18 in order to prevent a displacement of the axis of rotation a of the stem 20 of the valve and the axis of the drive shaft 28. This configuration of the coupling Oldham in combination with a suitable support rod 20 valve, located on the opposite the connecting element 26 side, saves a parallel arrangement of the two axes.

As further shown is figure 1, mainly cylindrical gaps 42 are placed in the housing 12 of the valve perpendicular to the axis of the drive shaft 28. Due to this arrangement facilitates access of personnel to the adjusting devices 46.

As for the preferred materials, it is necessary to understand that all spring plungers made of spring steel. The stem 20 of the valve seat 30 of the valve and seat elements 44 are made, in turn, made of hard metal or hard metal. The valve body itself may be made of any suitable material, for example, from steel.

In conclusion, it remains to mention some of the important advantages achieved by regulating the flow valve 10 according to the invention:

The use of cantilever bending of the springs 40 in combination with the appropriate clearances 42 gives the required function of the spring deflection is much greater reliability and virtually insensitive to clogging and blockage caused by the accumulation of finely dispersed inclusions.

As a result, regulating the flow valve 10 is more reliable impermeability to fluid actually in all conditions and therefore can be used in terms of safety critical applications and/or in difficult conditions, as, for example, in the system of pulverized coal into a blast furnace.

Due to cantilever bending springs 40, which regulates the flow valve 10 has an improved resistance to different thermal expansion of the composite material of the body 12 of the valve stem 20 of the valve and/or seat 30 of the valve.

In combination with the adjusting device 46 cantilever bending of the spring 40 to allow precise and optimal setting of the pressure tight contact. This allows you to adjust the valve 10 for different operating conditions and to reduce the wear rod 20 and the seat 30. In addition, can be reduced to the desired time of operation compared to conventional valves, which for security purposes, often characterized by excessive offset.

Design regulating the flow valve 10 and the adjusting device 46 in particular allows you to set the pressure tight contact during operation, thus avoiding downtime.

Because it dramatically reduces the risk of locking rod 20 of the valve in a certain position, it also reduces the risk of damage to the valve and damage, if any, of his servo.

Design regulating the flow valve 10 and the adjusting device 46 in particular facilitates maintenance of the internal parts of the valve 10 as compared with a conventional spring-loaded valve that uses a coil spring.

1. Regulating the flow of LAPAN for fluidized material, comprising a valve body having a valve chamber and a valve seat, the valve stem with the flow channel and the valve stem is located within the valve chamber before the valve seat with the possibility of rotation around the axis of rotation for regulating flow through regulating flow valve, and a spring mechanism, displacing the valve stem to the valve seat perpendicular to the axis of rotation to achieve a tight contact between the valve seat and the valve stem, wherein the valve stem comprises a cylindrical clamping surface, and a spring device contain at least one cantilever spring mounted in the gap opposite the valve seat, and cantilever spring mounted on the valve body, and its end portion is in contact with the cylindrical clamping surface to move the valve stem to the valve seat.

2. Regulating flow valve according to claim 1, in which at least one cantilever spring is a spring loaded plunger with a first end section, a spring bias the valve stem to the valve seat and the second end section attached to the valve body.

3. Regulating flow valve according to claim 2, in which spring-loaded plunger is made tapering in the direction of its first end portion.

4. Adjustable lighting angle is a first flow valve according to claim 3, in which the cantilever spring includes fifth element mounted on the first end section of the cantilever spring and having a contact surface corresponding to the outer cylindrical clamping surface of the valve stem.

5. Regulating flow valve according to any one of claim 2 to 4, including adjusting device, which is fixed to the second end section of the spring plunger, with the adjusting device allows the installation of the axial position of the spring plunger relative to the valve stem.

6. Regulating flow valve according to claim 5, in which the adjusting device includes a working portion for adjustment of the axial position of the spring plunger, while working part protrudes from the valve body.

7. Regulating flow valve according to any one of claims 1 to 4, in which two pairs of cantilever springs are installed in the respective gaps tangentially relative to the valve stem and on opposite sides of the duct through the valve body.

8. Regulating flow valve according to claim 7, in which the cantilever springs of each pair are installed in parallel, and two cantilever springs any one installed in pairs opposite to each other coaxially ratio.

9. Regulating flow valve according to claim 6, in two pairs of cantilever springs are installed in the respective gaps along the tangential the th relative to the valve stem and on opposite sides of the duct through the valve body, when this cantilever springs of each pair are installed in parallel, and two cantilever springs any one installed in pairs opposite to each other coaxially ratio.

10. Regulating flow valve according to any one of claims 1 to 4, also includes a drive shaft mounted rotatably in the valve body, and the coupling Oldham connecting the valve stem and actuator stem.

11. Regulating the flow valve of claim 10, in which the gap is perpendicular to the axis of the drive shaft in the valve body.

12. Regulating flow valve according to claim 9, also comprising a drive shaft mounted rotatably in the valve body, and the coupling Oldham connecting the valve stem and the drive shaft, and the gap is perpendicular to the axis of the drive shaft in the valve body.

13. Regulating flow valve according to any one of claims 1 to 4, in which the valve stem contains essentially cylindrical hollow body having a cylindrical sealing surface in contact with a corresponding sealing surface of the valve seat.

14. Regulating the flow valve 12, in which the valve stem contains essentially cylindrical hollow body having a cylindrical sealing surface in contact with a corresponding sealing surface of the valve seat.

15. the system of pulverized coal injection for blast furnace, containing regulating flow valve according to any one of the preceding paragraphs.



 

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3 dwg

FIELD: pneumatic transport.

SUBSTANCE: proposed device 2 for delivering stiff loose material into delivery pipeline has swirl chamber 4 made for connection of feed pipeline 6 from outside and forming inlet hole 8 for loose material in side wall of swirl chamber 4, and also device to build gas flow inside swirl chamber 4 which is directed to side of said inlet hole 8. Porous plate is fitted in side wall of swirl chamber 4 additionally close to periphery of inlet hole 8 through which loosening gas can be delivered into swirl chamber 4.

EFFECT: prevention of formation of material bridges in zone of inlet hole.

10 cl, 5 dwg

FIELD: pneumatic transport facilities.

SUBSTANCE: invention is designed for transportation of loose materials. Proposed plant for handling caking and lump powder materials has discharge device with ripper for breaking bridge formed in container, charger with bucket-wheel feeder for breaking lumps, reception of uniform dispensing, device for rubbing through and bringing material into aerated state in aerochamber combined with rubbing through device. According to invention, discharge device is essentially hydraulic cylinder on rod of which platform is secured with fitted on drive whose output shaft is connected with vertical shaft of ripper. Ripper is installed for lowering by means of hydraulic cylinder with cut-in drive and automatic movement upwards after reaching of limit switch in lower position with subsequent disconnection of ripper drive. Charger consists of cylindrical housing, upper cover, pneumovibrator with screen and aerobottom. Pneumovibrator of screen is brought out of housing behind its wall through flexible diaphragm flexible diaphragm. Aerobottom of charger is truncated cone lined from inner side with gas distributing needle-pierced rubber cloth and divided by means of pressure strip into two horizontal sections, each provided with union to feed compressed dried air. Upper cover is provided with charging hatch and branch pipe with filter to let out air into wet dust trap system. Rubbing through device consists of cylindrical housing with round holes in lower part and shaft passing in center of housing with elastic blades attached to cross-members to adjust distance from blades to wall of housing equipment with receiving hopper enclosing over perimeter part of housing with holes and assembled with said aerochamber for fluidizing said material getting into said pipeline.

EFFECT: provision of stable and unfailing operation of plant.

3 cl, 4 dwg

FIELD: material handling facilities; pneumatic transportation.

SUBSTANCE: according to invention, tightness of pneumatic transportation plant is checked before starting and periodically in process of operation by creating vacuum gauge pressure of at least 0.08 MPa in pipeline and air line by vacuum pump, and residual pressure not higher than 0.02 MPa in unloader with subsequent revealing degree of air suction after closing of evacuation line. Reduction of vacuum gauge pressure in 10 min in pipeline should not exceed 0.005 MPa and in air line, not exceed 0.02 Mpa and rise of residual pressure in unloader should not exceed 0.0025 MPa in 5 min.

EFFECT: provision of reliable tightness of system and drying the system before starting and in process of operation.

3 cl, 1 tbl, 4 dwg

FIELD: transportation of loose materials.

SUBSTANCE: proposed feeder contains rectangular section confuser-diffuser housing with feed port in zone of mating of its confuser and diffuser parts. Charging funnel with control gate arranged in lower part of funnel is placed over feed port. Hosuing is connected by its confuser and diffuser parts with confuser and diffuser which are connected, accordingly, with air duct and material duct of plant. Louver grating is arranged in housing over its entire width under feed port in diffuser part, louver slats being tilted in direction of transportation of material. Turnable valve is installed for turning on end part of louver grating over entire width of housing.

EFFECT: reduced losses of air pressure for accelerating particles of material to be transported after its delivery into feeder, reduced specific power losses of pneumotransport plant.

2 cl, 1 dwg

FIELD: metallurgy, chemical construction and other industries.

SUBSTANCE: invention relates to pneumatic transport and it can be used in handling of hot and cold loose materials. Proposed device for pneumatic transportation of loose materials contains air line with holes consisting of separate links laid inside transport pipeline. Pressure and thrust members for air line are hermetically mounted in holes in bottom of transport pipeline and are arranged in its inner space. End of air line provided with shutter. Initial section of each link is made in form of outer conical surface, and end is furnished with bell-type branch pipe with inner conical surface. Conical surfaces widen in direction of air flow. Longitudinal slots forming holes for air line are made on conical surface of each link.

EFFECT: reduced abrasive wear and power consumption at transportation of loose material, improved reliability of device, enlarged sphere of application.

4 cl, 7 dwg

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