Multipass valve and apparatus with multipass valve for regenerative thermal oxidation

FIELD: the invention refers to apparatus of regenerative thermal oxidation with multi pass valves.

SUBSTANCE: the apparatus for regenerative thermal oxidation for gas processing has a combustion zone, the first heat exchanging layer keeping heat exchanging surroundings and connecting with the combustion zone; the second heat exchanging layer keeping heat exchanging surroundings and connecting with the combustion zone; a valve for alternate direction of the gas flow between the first and the second heat exchanging layers. At that the valve has the first valve passage and the second valve passage separated from the first valve passage; a flow distributor having an admission passage communicates with the help of fluid medium with the admission opening of the surroundings and an exhaust passage communicates with the help of fluid medium with exhaust opening of fluid surroundings. At that the distributor is fulfilled with possibilities of its the first and the second valve passages between the first position in which the first valve passage communicates with the help of liquid with the admission passage and the second valve passage communicates with the help of liquid surroundings with exhaust passage and the second position in which the indicated the first valve passage communicates with the help of the fluid surrounding with exhaust passage and the second passage of the entry of the valve with the help of liquid surroundings communicates with the admission passage. At that the distributor of flow has a blocking surface which blocks the flow through the first part of the first valve passage and through the second part of the second valve passage when the distributor of the flow is between the first and the second positions and is fulfilled with possibility of its turning to 180o between the first and thesecond positions. At that valve passage is divided as the first so is the second at least into two chambers and the first and the second parts of the valve passages are congruous.

EFFECT: simplifies the construction, provides comfort of controlling and exploitation and deep removal of volatile organic combinations.

22 cl, 12 dwg

 

Background of the invention

Apparatus for regenerative thermal oxidation is commonly used for the destruction of volatile organic compounds (VOCS) in considerable volume, low concentration in the emissions of industrial enterprises and power plants. These machines oxidation typically requires high temperature oxidation to provide a significant degree of destruction of the VOCS. To ensure high efficiency heat recovery to be processed dirty process gas is pre-heated prior to oxidation. Usually for pre-heating use of these gases heat the column. The column typically has a nozzle from the heat transfer material having good heat resistance and mechanical strength, and sufficient thermal mass. In the process, the process gas is fed through a pre-heated heat-exchange column, which in turn heats the process gas to a temperature approaching or reaching temperature oxidation of its LOS. This preheated process gas is then directed to the combustion zone, where usually complete the incomplete oxidation of the VOCS. Processed, now clean, the gas is then directed from the combustion zone and back through the heat exchanger column, or through the second heat exchange column. When passing hot th oxidized gas through the column, it passes its heat to the heat exchange medium in the column, the cooling gas and the pre-heating heat exchange medium, so another batch process gas may be heated prior to oxidizing treatment. Typically, the apparatus for regenerative thermal oxidation has at least two heat-exchange columns that alternately take technological and processed gases. This process is performed continuously, allowing you to effectively handle a large volume of process gas.

Performance of the apparatus for regenerative oxidation can be optimized by improving the efficiency of destruction of VOCS and by reducing operating costs and capital costs. Increase the efficiency of destruction of LOS usually offered by such means as improved oxidation and treatment systems (e.g., catching the camera), and three or more heat exchanger for processing raw gas in the apparatus for oxidation, with their switch. Operating costs can be reduced by increasing the efficiency of heat recovery and reduce the pressure drop in the apparatus for oxidation. Operating costs and capital costs can be reduced by proper design of the apparatus for oxidation and by selection of suitable materials heat transfer nozzle.

An important element of effective staff oxidation are valves, p is reclusa the process gas stream from one heat exchange column to another. Any leakage of the raw process gas in the valve system will reduce the efficiency of the device. In addition, unwanted disturbances and fluctuations in pressure and/or flow in the system can occur during the switching of the valves. The problem is also the wear of the valves, especially in view of the substantial frequency switching valves in the apparatus for regenerative thermal oxidation.

According to one conventional two-column designs use a pair of conical valves, one of which belongs to the first heat exchange column, and the other to the second heat exchange column. Although cone valves which operate quickly during their shift during the cycle, still inevitably leak raw process gas in the vehicle. For example, in a two-chamber apparatus for oxidation is the moment when partially open and the inlet valve(s)and exhaust valve(s). At this point there is no resistance to the flow of process gas, and the flow goes directly from the intake to release, not obrabatyvati. Since the valve system also has its own channels, the volume of raw gas as in the case of the conical valve and in the respective channels is a potential leak. Since the diversion of untreated process gas valves OS which defaults to output from the device, the raw gas, this leak will significantly reduce the efficiency of the destruction device. In addition, conventional valve designs do not eliminate pressure surges when switching, and this fact increases the potential for leakage.

A similar potential for leakage exists in conventional systems rotary valve. These systems rotary valve usually contain many internal factors that, over time, leaks may occur, and their manufacture and maintenance are costly. For example, in U.S. patent No. 5,871,349, Figure 1, is described apparatus for oxidation with twelve cameras with twelve metal walls, each of which can be a weak point with regard to possible leakage.

Therefore, you must create the device for the regenerative thermal oxidizer, which will be simple and cost-effective two-chamber device, and provide easy to manage deep destruction of VOCS in the system, rotary valves, without the drawbacks to both.

The Invention

The present invention eliminates the disadvantages of the known prior art and provides a single multi-way valve and apparatus for regenerative thermal oxidizer containing multi-way valve. The valve according to this invention has good sealing characteristics and the minimum and the nose. The valve has a sealing plate, which restricts two cameras, each camera is the passage for flow in one of two regenerative layers of the apparatus for oxidation. The valve also contains a switching distributor stream providing alternating the direction of incoming or outgoing process gas in each of the halves of the sealing plate. The valve operates in two modes: stationary mode and move the valve. In stationary mode: gas-tight seal minimizes leakage of process gas or exclude it. Gas-tight seal is also sealed during movement of the valve. The valve has a compact design, thereby eliminating the need to create channels, usually necessary in the constructions according to the prior art. Due to this, reduce the size of the process gas during the circulation, leaving less raw number of dirty process gas during circulation. The proper regulation of the flow direction through the deflection minimizes or eliminates leakage of untreated process gas in the valve during switching. The application of a single valve instead of the usual two or four mean is Ino reduces the area, which must be sealed. The geometry of the switching valve flow reduces the length and number of turns passing the process gas, since the flow distributor may be located near the heat transfer layers. Due to this, reduce the amount of captured raw gas during the switching valve. As the process gas passes through the same passages of the valve in the intake cycle and the discharge cycle, the improved distribution of gas in heat exchange layers.

Is achieved by switching the valve with minimal pressure fluctuations, with good sealing and minimal bypass or not. By eliminating bypass switching, you can exclude the usual catching camera used to store the amount of raw gas in the system during the switching, and thereby to obtain substantial savings.

Brief description of drawings

Figure 1 is a perspective view of the apparatus for regenerative thermal oxidation according to one variant of the present invention;

Figure 2 is a view in perspective, with a spatial separation of parts of the apparatus for regenerative thermal oxidation according to one variant of the present invention;

Figure 3 is a perspective view of the compartment of the cold side in accordance with this izobreteny is m;

4 is a bottom view, in perspective, of the passages of the valve in accordance with this invention;

5 is a bottom view, in perspective, a multi-way valve of the distributor flow in accordance with this invention;

Figa - section of a multi-way valve of the distributor flow in accordance with this invention;

6 is a perspective view of the drive mechanism of a multi-way valve in accordance with this invention;

Figa, 7B, 7C and 7D is a schematic flow through the valve in accordance with this invention;

Fig is a perspective view of a part of the flow distributor in accordance with this invention;

Figure 9 is a horizontal projection of the sealing plate in accordance with this invention;

Figa - section of part of the sealing plate in accordance with this invention;

Figure 10 is a perspective view of the shaft of the distributor flow in accordance with this invention;

11 is a cross - section of the rotary passage according to this invention; and

Fig - section of the lower part of the drive shaft in accordance with this invention.

Detailed description of the invention

Figures 1 and 2 show a two-chamber apparatus 10 for regenerative thermal oxidation (catalytic or non-catalytic), mounted on the frame 12. The apparatus 10 for oxidation contains to what was Joh 15, where the first and second heat exchange chamber, communicating with which is located in the center of the zone of combustion. Burner (not shown) may relate to the zone of combustion; and a blower for combustion can be installed on the frame 12 to supply air for combustion in the burner. The zone of combustion includes a bypass exhaust passage 14 that communicates through a fluid medium with an exhaust pipe 16, typically providing emission into the atmosphere. In the Cabinet 11 are the controls for the apparatus, and it is also preferably mounted on the frame 12. In front of the Cabinet 11 control a fan (not shown) on the frame 12, which provides a supply of process gas into the apparatus 10 for oxidation. The casing 15 has an upper chamber or the roof 17 with one or more hatches 18 access, which gives the operator access into the casing 15. Specialists in the art will understand that here is the description of the apparatus for oxidation is intended for illustrative purposes only, and in the framework of this invention it is also possible other designs, including apparatus for oxidation with the number of cameras more or less than two, oxidants with a horizontally oriented camera(s) and the catalytic apparatus for oxidation.

Compartment 20 cold side forms the base of the casing 15, as clearly shown in Fig.. Corresponding reference grating 19 is located on the compartment 20 of the cold side and it has a heat-exchange matrix in each heat exchange column according to the following more detailed description. In the illustrated embodiment, the heat exchange chambers are separated from each other by a dividing wall 21, preferably insulated. Also in this embodiment, the flow through the heat exchange layers is vertical, process gas enters into the layers of the passages of the valve located in the compartment 20 of the cold side goes up (to the roof 17) in the first layer, enters the zone of the combustion chamber connected to the first layer out of the combustion zone and enters the second chamber, where it passes down through the second layer to compartment 20 cold side. Specialists in the art it will be clear that also can be used in other locations, including the horizontal location at which the heat-exchange columns facing each other and separated in the center of the zone of combustion.

Figure 3 shows the compartment 20 of the cold side. The compartment 20 has a floor 23, which preferably has a downward inclination from the outer walls 20A, 20B in the direction of the passages 25 of the valve to ensure that the distribution of the gas stream. On the floor 23 has plenty of dividing baffles 24 and spacers 124 camera. Dividing deflec the ora 24 share the passages 25 of the valve and provide reduction of pressure fluctuations when switching valve. The dividers 124 cameras are divided heat-exchange chamber. Separators 124A beaches and D, E and N camera can connect to each other or to be separated. Passage 25A of the valve is limited between the separator 124A beaches chamber and baffle 24; pass 25V valve is limited between the deflectors 24 and 24C, the passage 25 of the valve is limited between the baffle 24C and separator D chamber; passage 25D valve is limited between the separator A chamber and baffle 24F; the passage 25TH valve is limited between the deflectors 24F and 24G; and the passage 25F valve is limited between the deflector 24G and separator N camera. The number of dividing baffles 24 depends on the number of passages 25 of the camera. In the preferred embodiment, there are six passages 25 of the valve, although you can use less or more. For example, in the variant with four passages of the valve will only need one spacer deflector.

Regardless of the number of passages of the valve and the corresponding separation of the vent symmetry of the holes of the valve preferably have the same shape.

The height of the baffles is preferably such that the upper surface of the baffles together limits the level of the horizontal plane. In the illustrated embodiment, the portion of the vent, which is the farthest from the passages of the valve is very short to accommodate Pol compartment cold side, which, as stated above, is on a slope. Level thus formed horizontal plane is preferred to have the heat exchange medium in each heat exchange column, according to the more detailed description below. In six passages of the valve according to the illustrated variant of the deflectors 24, 24C, 24F and 24G preferably have an angle of about 45° relative to the longitudinal center line L-L of the compartment 20 cold side when they pass from the passages 25 of the valve, and then they are essentially parallel to the longitudinal center line L-L, passing to the outer walls 20A and 20B, respectively. Baffles 24A, 24D, 24TH and 24N preferably have an angle of about 22.5aboutrelative to the latitudinal center line N-N of the compartment 20 cold side, when run from the passages 25 of the valve, and then are essentially parallel to the latitudinal line H-H in their passage to the outer walls 20C and D, respectively.

The deflectors 24, 24C, 24F and 24G, and the side walls 20A, 20B, 20C and D compartment 20 cold side preferably contain the ledge 26, passing slightly below the horizontal plane bounded by the upper surface of the deflector 25. The protrusion 26 is provided as a variant of the supporting bars 19 cold side, which is also based on it (figure 2); on Reshetnev turn is heat-exchange medium in each column. If the heat exchange medium contains the environment in the form of any attachments, such as ceramic saddles, spheres or other shapes, the baffles 24 may pass above for the separation of this environment. But a perfect seal between the vent is not required in contrast to conventional constructions rotary valve.

Figure 4 shows the passages 25 below. The plate 28 has two opposite symmetrical passages 29A and 29B, which together with the deflectors 26 restrict the passages 25 of the valve. Each passage 25 of the valve has, as a variant, the rotary blade 27. In each rotary blade 27 of the first end attached to the plate 28, and a second end separated from the first end attached to the baffle 24 on each side (as shown in figure 3). Each rotary blade 27 extends from its first end toward its second end, and is under an upward angle and then is flattened in the horizontal 27A, according to figure 3 and 4. Rotary blade 27 directs the flow of process gas coming from the passages of the valve, in the direction of the passages of the valve to provide the distribution in the compartment cold side during operation. The same distribution in the cold compartment 20 to provide equal distribution through the heat-exchange medium for the optimal efficiency of heat exchange.

Figure 5 and 5A shows the races is redemittel 50 thread located in the nozzle 51 with the inlet passage 48 for the process gas and the exhaust passage 49 for the process gas (although the element 48 may be a bleed hole, and 49 - inlet hole, for illustrative purposes, here is the first option). The dispenser 50 stream preferably contains a hollow cylindrical drive shaft 52 (figa, 10), which is connected with a drive mechanism. To the drive shaft 52 is connected to the element 53 in the form of a partially truncated cone. The element 53 includes interfacing plate, made of two opposite segment sealing surfaces 55, 56, each of which is connected with round outer edges 54 and passes outward from the drive shaft 52 at an angle of 45about, resulting in a void bounded by two sealing surfaces 55, 56 and the outer edge 54, restricts the first route or passage 60 of gas. Similarly, the second path or passage 61 gas limited sealing surfaces 55, 56 opposite the first passage and located in three angled side plates: opposite and spaced angled side plates 57A, 57B, and the Central angled side plate S. Angled side plates 57 separate passage 60 from the passage 61. The top of these passages 60, 61 corresponds to the configuration of the symmetric p is the wasted 29A, 29B in the plate 28, and in the assembled condition, each passage 60, 61 corresponds to the holes 29A and 29B.

The passage 61 through the fluid is communicated only with the inlet hole 48; and the passage 60 through the fluid is communicated only with the outlet 49 through the compartment 47, regardless of the location of the distributor 50 flow at any given time. Process gas flowing in the pipe 51 through the inlet 48, passes only through the passage 61; and process gas flowing in the passage 60 from the holes 25 of the valve passes only through the outlet 49 through the compartment 47.

The sealing plate 100 (Fig.9) is connected to the plate 28, bounding the passages 25 of the valve (figure 4). Between the upper surface of the distributor 50 and thread sealing plate 100 preferably uses an air-tight seal. The flow distributor is configured to rotate around a vertical axis with the drive shaft 52 relative to the fixed plate 28. This rotation moves the sealing surfaces 55, 56 into and out of blocking alignment with the portions of the passages 29A, 29B, according to the following more detailed description.

Figure 6 shows the corresponding drive mechanism to actuate the dispenser 50 thread. The drive mechanism 70 includes the basis of the W 71 and is supported on the frame 12 (Fig 1). With the base 71 are connected by a pair of bearings 73A and V for gear racks and bearing 74 of the cylinder. Cylinders 75A, 75V rely on the support cylinder 74 and result in a corresponding movement of the toothed rail 76A, B. Each toothed rack has lots of grooves corresponding to the shape of teeth 77A on the cylindrical toothed wheel 77. The drive shaft 52 of the distributor 50 flow associated with a cylindrical toothed wheel 77. The action of the cylinders 75A, 75V moves the corresponding attached toothed rack 76 which in turn rotates the cylindrical gear wheel 77 which rotates the drive shaft 52 and the valve 50 of the thread attached to it, around a vertical axis. The design of the rack and the gear wheel is preferably can be rotated forward and backward by 180aboutthe drive shaft 52. Specialists in the art it will be clear that within the framework of this invention it is also possible to realize the drive of the distributor flow at full turn 360°. Other preferred drivers are hydraulic actuators and rotary tables.

On figa-7D schematically shows the direction of flow during a typical cycle of the switching valve with two inlet passage and two outlet passages. In these schemes, the camera And the Ki the inlet chamber, and the camera In the exhaust chamber two-column apparatus for oxidation. On figa shows the valve in its fully open stationary position. Passages 25A and 25V valve are fully open inlet and passages 25C and 25D of the valve are fully open exhaust mode. Process gas enters the chamber And through the passages 25A and 25V valve, passes through the heat exchanging medium in the chamber A, where it is heated, passes through the zone of combustion chamber connected with the camera And where not yet oxidized oxidized volatile components; cooled while passing through the chamber In the chamber connected with the combustion zone, and then exits from the passages 25C and 25D in the exhaust pipe, from which he is released into the atmosphere. Usually this mode lasts from 1 to 4 minutes, preferably, about 3 minutes

On FIGU shows the beginning of the regime change, when the valve is rotated 60°and it takes approximately from 0.5 to 2 seconds. In the position shown, the passage 25V valve is closed, and thus the flow in or out of the camera And in this passage is blocked; and the passage 25C valve is closed, and thus the flow in or out of camera locked in this passage. Passages 25A and 25D of the valve remain open.

Upon further rotation of the distributor flow even at 60aboutaccording pigs, passages 25A and 25D valve is now blocked. But the passage 25V valve aperiodic, but it is in the exhaust mode, providing the output of process gas from the chamber and through the passage 25 and the exhaust pipe or similar device. The passage 25 of the valve is now opened, but is in the intake mode, providing a flow of process gas into the chamber (not from the camera In as in exhaust mode according figa).

The final twist on the 60° distributor flow shown in Figg. Luggage And now is in the fully open discharge mode, and the camera is in the fully open inlet mode. Thus, the passages 25A, 25V, 25C and 25D of all valve fully open and the flow distributor is not valid. When a thread must again turn back, the thread allocator preferably is returned to the position according Figa through 180aboutin reverse to the previous direction, although continue to rotate 180aboutin the same direction as the previous turn, it is envisaged within the scope of this invention.

System with six passages of the valve according to figure 3 will operate similarly. That is, each pass valve will have 45°and 60°. When the passages 25A, 25V and 25C of the valve according to figure 3 are in the intake mode and fully open, and the passages 25D, 25TH and 25F valve located in the exhaust mode and on the TV, the first stage of the cycle is that the valve turn on 45° (clockwise), blocking the flow in the passage 25 of the valve and passage 25F valve. Passages 25A and 25V valve remains in the inlet open position, and passes 25D and 25TH valve remain in the final open position. During rotation of the distributor flow even at 45aboutclockwise passage 25C of the valve is now in the open discharge position, the passage 25 of the valve is blocked and the passage 25A of the valve remains in the open inlet position. Similarly, the passage 25F valve is now open inlet position, the passage 25TH valve is blocked and the passage 25D valve remains in the open discharge position. During rotation of the distributor flow even at 45about: passages 25C and 25V valve are now in the open discharge position, and the passage 25A of the valve is blocked. Similarly, the passages 25F and 25TH valve are now open inlet position, and the passage 25F valve blocked. In the final position: allocator thread is rotated another 45° and stops, all of the passages 25A, 25V and 25C of the valve are in the open discharge position, and all the passages 25D, 25V and 25F are open inlet position.

From the above it follows that one significant advantage of the present invention in comparison with about CNAME rotary valves is the proposed directional flow most of the time stationary. He moves only during the change cycle, the intake-release, and this movement lasts only seconds (typically from 0.5 to 4 seconds) compared to the minute, when he is stationary, when one of the chambers a or b is in the intake mode and the other in the exhaust. In contrast, many conventional rotary valves are constantly moving, and it accelerates the wear of the various elements of the apparatus and may cause leaks. An additional advantage of this invention is the presence of a large physical space separating the cleaned gas from yet purified process gas in the valve chamber (the space 80 (figure 3) between the delimiters E and D camera and dividers N and 124A beaches), and a double wall formed by the separators E, N and 124A beaches, D camera. In this case, since the valve has only one Executive system, the valve will function, if it moves quickly or slowly, in contrast to the valve known from the prior art, where together there are several Executive systems. In particular, in the prior art, if one cone valve is slowed down relative to another, can occur, for example, leakage or loss of process flow or significant skacha the pressure.

Another advantage of this invention is the resistance that is present during the switchover operation. In conventional valves, for example in the above-mentioned cone valve, the flow resistance approaches zero, when both valves are partially open (i.e. when one closes and the other opens). Therefore, the gas flow per unit of time can actually increase, even more increasing the leakage of gas in both open the valve during switching. In contrast, as a guiding device for the stream according to the present invention gradually closes the inlet (or release), simultaneously closing only partially, the resistance does not decrease to zero during the switching, and in fact increases, thereby limiting the flow of process gas in the passages of the valve during switching and minimizing leakage.

The preferred method of sealing the valve hereinafter described with reference to figure 5, 8 and 9. The dispenser 50 flow is air cushion to minimize or eliminate wear when you move the thread allocator. Specialists in the art will understand that you can in the air to use other gases, although air is preferred, and for purposes of explanation used it. Air cushion not only TP is no valve, but also provides movement of the distributor flow without friction or essentially without friction. Working at a pressure conveying system, such as a fan or the like, which may be the same fan that supplies air for combustion in the burner combustion zone, or any other fan that delivers air to the drive shaft 52 of the distributor 50 flow through the corresponding channel (not shown) in the compartment 64. According pig air passes out of the channel in the drive shaft 52 through one or more openings 81, is made in the case of the drive shaft 52 above the base 82 of the drive shaft 52, which is connected to the drive mechanism 70. The exact location of the opening(s) 81 in a certain way is not limited, although preferably the openings 81 are symmetrically located around the shaft 52 and are the same size. With the excess pressure of the air rises along the shaft, as shown by the arrow on Fig, and some is included in one or more radial channels 83, which are communicated with one or more seals in the form of a piston ring located in the annular rotary passage 90, further described below. The portion of air, which is not included in the radial channels 83, continues to move up the drive shaft 52 until it reaches the passages 94, which distribute the air in the chute having a floor is Alzenau part 95 and part, limited segmental wedges 55, 56.

Interfacing surface of the distributor 50 flow, in particular interfacing surface of the segmental wedges 55, 56 and the outer annular edge 54, made with lots of openings 96, as shown in figure 5. Having excessive pressure air from the chute 95 extends through these openings 96, as shown by the arrows on Fig, and creates an air cushion between the upper surface of the distributor 50 flow and stationary sealing plate 100, shown in Fig.9. The sealing plate 100 includes an annular outer edge 102, the width of which corresponds to the upper surface 54 of the distributor 50 thread, and a pair of segmental elements 105, 106, corresponding in shape segment wedges 55, 56 of the distributor 50 thread. It corresponds to the form (if they join) plate 28 (figure 4) passage of the valve. In the opening 104 includes a pin shaft 59 (Fig), connected to the dispenser 50 thread. The lower side of the annular outer edge 102 facing the distributor stream contains one or more annular grooves 99 (figa), which are aligned with openings 96 on the interfacing surface of the distributor 50 thread. Preferably there are two concentric series of grooves 99 and two corresponding series of openings 96. Grooves 99 provide the output of air from the openings 96 on the upper surface 54, to establish who the earplug between the mating surface 54 and an annular outer edge 102 of the sealing plate 100. In addition, the air emerging from the openings 96 in the segment parts 55, 56, forms an air cushion between the segmental portions 55, 56 and segment parts 105, 106 of the sealing plate 100. These air cushion minimize or eliminate leakage of the process gas that has not been cleaned, the flow of clean process gas. Relatively large segmental wedges dispenser 50 of the thread and the sealing plate 100 provides a long way on the upper part of the distributor 50 flow, which will be held the raw gas to leak. Because the dispenser flow during operation most of the time stationary, so between all mating surfaces of the valve creates an impenetrable air cushion. When you want the thread allocator moved, airbag, used to seal the valve, in this case also eliminates any high pressure contact, to eliminate wear between the valve 50 and pressure sealing plate 100.

Air under pressure is preferably served by a fan, not a fan of feeding the process gas into the apparatus, which is equipped with a valve and therefore the pressure sealing air is higher than the pressure of the process gas at the inlet or release, resulting in a positive the first seal.

The dispenser 50 pressure contains the rotary passage, shown in figure 10 and 11. Having the form of a truncated cone section 53 of the distributor 50 flow rotates around an annular cylindrical wall 110, which acts as an external o-ring seal. The wall 110 has an external annular flange 111, the centering wall 110 and clamping it to the nozzle 51 (also shown in figure 5). E-shaped element 116 inner o-ring is preferably made of metal) is connected to the dispenser 50 thread, and it made the pair separated from each other by the interval of parallel grooves A, 115V. Piston ring A installed in the recess A, and piston ring 112 VDC is installed in the recess 115V. Each piston ring 112 is shifted to the wall 110 of the outer annular seal and remains stationary even when rotated the distributor 50 thread. Having excessive pressure air (or gas) passes through the radial channels 83, indicated by arrows figure 11, and through the openings 84, communicating with each radial channel 83, enters the channel 119 between the piston rings A, 112 VDC, and also in the clearance between each piston ring 112 and the inner o-ring seal 116. During rotation of the distributor of the flow relative to the stationary cylindrical wall 110 (and piston rings A, 112 VDC) air in the channel 119 POPs the AET excess pressure in the space between the two piston rings A, 112 VDC, creating a continuous and without friction seal. The clearance between the piston rings 112 and inner piston seal 116, and the gap 85 between the inner piston seal 116 and the wall 110 accept any movement (axial or another) in the drive shaft 52, arising out of thermal expansion or other factors. Specialists in the art will understand that although the depicted double o-ring seal, for additional seals can also use three or more piston rings. For sealing can be a positive or negative pressure.

On Fig shows how the compartment 64, which applies to the shaft 52 having a gauge pressure of the air, condense relative to the drive shaft 52. This condensation is carried out similarly described above, the rotary passage; except that the seal is not under pressure and only one piston ring must be used for each seal above and below the compartment 64. For example, using a seal above the compartment 64-shaped inner annular seal 216 made it a Central bore groove. A stationary annular cylindrical wall 210, which acts as an external annular seal includes an external annular flange 211 used for antiroman the wall 210 and pressure to compartment 64. Stationary piston ring 212 is installed in the groove made in the C-shaped inner annular seal 216, and moves to the wall 210. Clearance between piston ring 212 and the bore of a C-shaped inner seal 216, and also the gap between the C-shaped inner seal 216 and the outer cylindrical wall 210 accept any movement of the drive shaft 52, caused by thermal expansion or other factors. A similar cylindrical wall 310, C-shaped inner seal 316 and piston ring 312 is used on the opposite side of the compartment 64, as shown in Fig.

During operation in the first mode: raw (dirty) process gas passes into the inlet hole 48 through the passage 61 of the distributor 50 flow and any relevant passages 25 of the valve, which in the open position are communicated with a passage 61 in this mode. The raw process gas then flows upward through the hot heat transfer medium located in the compartment 20 of the cold side, and through the combustion zone, where it is treated; and now the clean gas is then cooled as it passes down through the cold heat transfer medium in the second column, through the passages 25 of the valve, communicating with the passage 60, and out of the compartment 47 and the exhaust passages 49. After the cold heat transfer medium relative to the load, which is, cycle POWERCIAT on the back due to actuation of the drive mechanism 70, which rotates the drive shaft 52 and the valve 50 of the flow. In this second mode, the raw process gas is routed back into the intake hole 48 through the passage 61 of the distributor 50 thread, and this passage has now reported with other passages 25 of the valve, which was connected by a fluid medium only with the passage 60, thus directing the raw process gas into the now heated heat-exchange column and then through the combustion zone where the process gas is subjected to processing. The cleaned gas is then cooled as it passes down through the, now cold, the heat exchanging medium in the other column, through the passages 25 of the valve, which is now communicated with the passage 60, and out of the compartment 47 and outlet 69. If necessary, this cycle is repeated usually every 1-4 minutes.

1. The valve contains a first pass through the valve and a second passage of the valve separated from the first passage of the valve, the flow distributor having an inlet passage which is connected through the fluid inlet hole of the environment, and an exhaust passage which is connected through the fluid with the outlet of the fluid when the dispenser is configured to move relative to p is pout and second passages of the valve between the first position, in which the first passage of the valve is communicated through the fluid inlet passage and the second passage of the valve is communicated through the fluid output passage and a second position, wherein said first passage of the valve is communicated through the fluid output passage and the second passage of the valve inlet through the fluid inlet passage, and the flow distributor has a blocking surface that blocks flow through the first portion of the first passage of the valve and through the second part of the second passage of the valve when the flow distributor is located between the first and second positions.

2. The valve according to claim 1, in which the first and second valve passages, each of them separated by at least two cameras.

3. The valve according to claim 1, in which the first and second valve passages, each of them separated by at least three cameras.

4. The valve of claim 1, wherein the flow distributor is configured to rotate 180° between the first and second positions.

5. The valve according to claim 1, in which the first and second parts of the valve passages are congruent.

6. The valve according to claim 1, which further includes a drive shaft connected to the dispenser flow, at least one radial channel which is connected through a fluid medium to the drive shaft and passing him happy in the real direction, and the turning passage containing an outer ring, inner ring, separated from the outer annular seal and having a number of holes, and at least one piston ring, and at least one piston ring is installed on the same hole of the many holes in the inner annular seal and is shifted to the outer ring seal.

7. The valve according to claim 6, which further comprises means, guiding the flow of gas through the drive shaft through at least one radial channel and between the at least one piston ring and the inner ring seal.

8. The valve according to claim 6, which further comprises a set of piston rings, and means guiding the flow of gas through the drive shaft through at least one radial channel and between a set of piston rings.

9. The valve according to claim 1, which further comprises a sealing plate, and the flow distributor further comprises a mating surface having multiple openings through which the gas, creating a cushion of gas between the fillet surface and the sealing plate.

10. The valve according to claim 9, in which the sealing plate comprises at least one annular groove, combined with at least one opening from the centre of the VA of openings.

11. The valve according to claim 1, which further comprises means actuator to move the valve flow between the first and second positions.

12. The valve according to claim 11, in which the tool drive comprises a gear wheel which is connected to the flow distributor, and the gear wheel has a lot of teeth and at least one toothed rack having multiple grooves, which includes a lot of teeth, and the movement of rail provides corresponding movement of the gear wheel, which turns the thread allocator.

13. Apparatus for regenerative thermal oxidation processing gas containing the combustion zone, the first heat transfer layer containing a heat-exchange medium and is connected with the zone of combustion, the second heat transfer layer containing a heat-exchange medium and is connected with the zone of combustion, a valve for alternating the direction of gas flow between the first and second heat transfer layers, the valve contains a first pass through the valve which is connected through a fluid medium to the first heat exchanger layer, and the second passage of the valve separated from the first passage of the valve and is connected through a fluid medium from the second heat exchanger layer, the flow distributor having an inlet passage and outlet passage, this thread allocator is arranged to move relative to the positive of the first and second passages of the valve between the first position, in which the gas is included in the intake passage, flows into the first heat exchange column through the first passage of the valve and of the exhaust passage through the second heat exchange column and the second passage of the valve, and a second position in which the gas entering the first inlet passage, flows into the second heat exchange column through the second passage of the valve and of the exhaust passage through the first heat exchanger column and the first passage of the valve, and the flow distributor includes a blocking part for blocking gas flow through a portion of the first and second passages of the valve when the flow distributor is located between the first and second positions.

14. Apparatus for regenerative thermal oxidation according to item 13, which further comprises a compartment cold side containing at least one deflector for separating the first and second valve passages on many cameras.

15. Apparatus for regenerative thermal oxidation 14, in which each cell is congruent.

16. Apparatus for regenerative thermal oxidation in item 13, in which the flow distributor is installed in the pipe with the inlet pipe and the outlet pipe and inlet pipe delivers the message through the fluid with the first pass of the distributor flow, and the release of the second hole of the socket provides a message through the fluid with the second passage of the distributor of the stream.

17. Apparatus for regenerative thermal oxidation according to item 13, which further comprises a drive shaft connected to the dispenser flow, at least one radial channel which is connected through a fluid medium to the drive shaft and passing from it in the radial direction, and the rotary passage containing an outer ring, inner ring, separated from the outer annular seal and having a number of holes, and at least one piston ring, and at least one piston ring set for one pass of the many holes in the inner annular seal and is shifted to the outer ring seal.

18. Apparatus for regenerative thermal oxidation at 17, which further comprises means guiding the gas flow to the drive shaft, at least one radial channel and between the at least one piston ring and the inner ring seal.

19. Apparatus for regenerative thermal oxidation according to item 13, which further comprises a sealing plate, and a flow distributor also includes a mating surface having multiple openings through which the gas, creating a cushion of gas between the fillet surface and the sealing plate.

p> 20. Apparatus for regenerative thermal oxidation according to claim 19, in which the sealing plate comprises at least one annular groove, combined with at least one opening from a variety of openings.

21. Apparatus for regenerative thermal oxidation according to item 13, which further comprises means actuator to move the valve flow between the first and second positions.

22. Apparatus for regenerative thermal oxidation on item 21, in which the tool drive comprises a gear wheel which is connected to the flow distributor, and the gear wheel has a lot of teeth and at least one toothed rack having multiple grooves, which includes a lot of teeth, and the movement of rail provides corresponding movement of the gear wheel, which turns the thread allocator.



 

Same patents:

FIELD: structural members of tube furnaces of the petroleum refining industry, in particular, construction of the lining of the smoke flue of the vertical multichamber radiant-convective furnace used in installation of catalytic reforming, hydrofining and aromatization.

SUBSTANCE: the construction has vertical walls: an inner wall engageable with the working space of the furnace radiant chambers and having holes for passage of flue gases, and an outer wall located on the side of the furnace jacket, made of tongued refractory products laid in rows in a broken joint and with expansion joints of the tongued refractory products and having on the side of the flue mirror-located projecting rows of supporting products positioned one under another in height of the flue, the connecting partitions are made of refractory shaped members installed on the projecting rows forming the horizontal tunnels of the flue, and a heat insulation adjoining the jacket. The novelty is in the fact that each member of the partitions is made in the form of two refractory shaped products installed for independent displacement relative to each other in the vertical axis of the flue at a thermal expansion of the lining walls and interconnected by means of L-shaped bulges made on the ends of the products, facing the flue axis and built in the vertical walls by other tongued ends laid on the supporting beveled products of the projecting row, the outer wall is made tied to the jacket for displacement in the vertical axis of the flue at a thermal expansion of the lining by means of successively engageable shaped members with holes positioned in rows in the lining of the outer wall at an interval of 6 to 9 rows, shackles with one end installed in the hole of the product, and with the other - in the hole of the angle piece welded to the jacket; all the products of the lining are dry laid, with the vertical expansion joints between each product. The outer and inner vertical walls with built-in refractory shaped members of the partitions are made of materials with a different coefficient of linear thermal expansion, larger one at the outer wall.

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4 cl, 2 ex, 5 dwg

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3 cl, 3 dwg, 1 ex, 1 tbl

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EFFECT: enhanced economical efficiency of use of vapor-and-gas cycle.

2 cl, 1 dwg

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