KR900003517B1 - Axial multiport rotary valve - Google Patents

Abstract

The unitary disc-axial multiport valve is capable of accomplishing the simultaneous interconnection of conduits in accordance with a previously determined cycle. Any conduit communicates with no more than one other conduit at any one cycle step, or valve index position. The conduits to be interconnected are attached to a hollow stationary body, or stator which is comprised of two sections, or elements, one being cylindrical opening and joined to the cylindrical elemtnt at one end using a flange. There are fluid flow paths in a rotating body, or rotor assembly, which is located partially inside the stator assembly, extending through the central opening in the disc-like element of the stator. The form of the rotor assembly is similar to that of the stator assembly.

Description

Axial Multiport Rotary Valve

1 is a schematic representation of six separation zones with two different fluid flow arrangements associated with a single step of a United States Patent No. 4,402,832 (Gerhold) process, respectively.

2 is a schematic of valves and conduits interconnected by their use as required by the FIG. 1 process.

3 is a schematic illustration of an axial multiport rotary valve with tie pipes and labels in accordance with the FIG. 1 process, with some parts of the figure omitted for convenience.

4 is a partial cross-sectional view of the left end of the FIG. 3 valve including part of the stator end element, part of the rotor end element and the sealing follower.

5 is a view of a rotating seal ring with the zero ring omitted.

6 is a partial cross-sectional view of the third degree valve including a central element portion of the rotor and stator end elements.

7 shows the stator center element with the stator end element and the center seal element.

8 is a cross-sectional view taken along arrow 35 of the central element used in the FIG. 3 valve.

9 is a cross-sectional view of the central seal element taken along arrow 9 in FIG.

10 is a plan view of the central seal element of FIG.

FIG. 11 is a Blauton process (US Pat. No. 2,985,589) showing a vessel comprising a plurality of layers with a conduit connecting the bed and the axial multiport rotary valve and a conduit for fluid flow in and out of the process. Even if.

FIG. 12 is an illustration of an axial multiport rotary valve, labeled according to the FIG. 11 process and showing the conduit arrangement in the same manner as FIG.

* Explanation of symbols for main parts of the drawings

11: stator center element 12,13: stator end element

17,18: rotor end element 19,21: shaft

37,38,166,167 Channel 39 End sealing

40: rotating seal ring 43: fixed sealing ring

53: seal boundary area 55: sealing surface

F: feed flow D: discharge flow

E: extracts R: extractables

FIELD OF THE INVENTION The present invention relates to a device for moving a plurality of fluid flows between different locations, and more particularly, to a monolithic axial multiport rotary valve capable of simultaneously interconnecting multiple conduits in a predetermined periodic order. will be.

US Pat. Nos. 3,040,777 (Carson et al.) And 13,422,848 (Leaveman et al.) Include multiports used to perform the processes of US Pat. No. 2,985,589 (Browton, et al.) And other similar processes. Rotary disk valves are described. However, the valves of these cited examples cannot be used in the performance of a process as described in US Pat. No. 4,402,832, which will be described below. Valves having applications similar to Carson and Ribman's valves are described in US Pat. No. 3,192,954 (Geherford et al.), Which uses a cylindrical rotor in the peripheral stator as illustrated in FIG.

The present invention is an axial multiport valve, useful for moving a number of different fluid streams between different locations along a predetermined period. The fluid flow is received in the conduits connected by the valve. Any one conduit is connected with only one other conduit at any one cycle step, ie at the valve index position. The conduits to be interconnected are connected to a hollow stator assembly consisting of three elements each cylindrical.

There is a rotating body located inside the stator assembly, ie a fluid flow channel in the rotor assembly. The rotor assembly takes various positions depending on the cycle stage and distributes the fluid entering and exiting the valve in different ways for each cycle stage. The space between the rotor and the stator assembly contains sealing means for preventing leakage and for defining a flow passage.

There is often a need to circulate fluids over multiple locations in such a way that the fluid flow is circulated to one location for one time period and then to another location for another time period. The relatively simple problem of circulating a single fluid into multiple locations in a predetermined cycle, ie in a periodic order, can be easily solved with more than one valve, such as a multiturn plug valve. However, where there is a need to circulate one or more fluids simultaneously to multiple destinations, it is highly desirable to use a single device rather than a plurality of individual valves, as described in the Carson patent (US Pat. No. 3,040,777). . An axial multiport rotary valve is such a mechanism.

It is therefore an object of the present invention to provide a monolithic mechanical valve which is capable of interconnecting multiple conduits simultaneously according to a given cycle, and wherein any conduit is connected to only one other conduit at the valve index position. Purpose. Another object of the present invention is to provide a valve which is smaller in size than the valve of the prior art and has a low holding condition. A broad embodiment of the invention comprises: (a) a stator assembly comprising a central element, a first end element, and a second end element, each having a hollow interior, each having a cylindrical outer shape: (b) each cylindrical; A central annulus, a first end element and a second end element, wherein a first annular space is formed between the rotor first end element and the stator first end element, the rotor second end element and the stator A second annular space is formed between the second end elements, and is located almost inside the internal hollow of the stator assembly such that a central annular space is formed between the rotor center element and the stator center element, and according to a predetermined cycle. A fluid cylinder formed within the annular space for transferring fluid between the fluid passages, rotating around the longitudinal axis of the rotor and stator assembly in various valve index positions. A rotor assembly having a plurality of internal channels for communication between; (c) a plurality of nozzles located in the stator assembly that connect the conduits to the valve to provide a fluid path between the annular space and the conduit in the stator assembly: (d) prevention of external leakage, of the fluid passage In order to limit and prevent mixing of the fluid flowing through the valve, another pair of nozzles is allowed to communicate at each valve index position according to the predetermined cycle, and the fluid supplied by the nozzle is introduced into the other nozzles so as to flow out through the valve. And a sealing means in the annular space adapted to flow in sequence through the annular space fluid passage, the rotor assembly passage and another annular space fluid passage.

Features of certain embodiments of the present invention are a fluid flow passage and a central stator element passage, referred to herein as a tie pipe. These fluid flow passages enhance the flexibility of the axial multiport rotary valves, making them suitable for many process arrangements that require the connection of multiple conduits. Tie fights communicate between annular spaces formed between the rotor and stator end elements. The stator element passages allow fluid to flow into the valve through a nozzle attached to the stator central element and out through another nozzle attached to the stator central element to bypass the end element of the valve.

Separation of various materials by selective absorption using absorber induced bed simulation is an example of a process using axial multiport rotary valves. One simulated flow absorbency is described in the above-mentioned US Pat. No. 2,985,589 (Browton et al.). 11 shows the process and apparatus of the patent. In carrying out the above process, it is necessary to connect the feed stream to a series of layers firstly and then to several layers, usually in the range 12 to 24, such as the first layer and the second layer. Such layers may be considered parts of a single large layer with simulated movement. Whenever the destination of the feed stream is changed, the destination or origin of at least three other fluid streams that enter or exit the bed, like the feed stream, also need to be changed. The simulated fluidized bed will be briefly described as dividing the bed into a series of fixed beds and moving the inflow and outflow points beyond the series of fixed beds, instead of moving the bed via inlet and outlet points. Can be. The rotary valve used in the Browne process is the simultaneous interconnection of two separate conduits.

Simulation fluidized bed processes have many different process requirements that result in different flow designs and hence variations in rotary valve equipment. For example, in addition to the four basic fluid streams disclosed in US Pat. No. 2,985,589 to Brownton et al., It may be desirable to use one or more fluid streams to clean one or more conduits. The washings are used to prevent the components from mixing unnecessarily. The cleaning material is selected to be preferred for mixing with one of the main fluid streams being cleaned or entering the conduit after the cleaning is completed. See US Pat. No. 3,201,491 (Stine et al.) For information on cleaning conduits applied to the process of US Pat. No. 2,985,589 to Brownton et al. It may be desirable to pass fluid through the bed in a reverse direction from normal flow. Such is generally known as backwashing as handled in US Pat. No. 4,319,292 (Pickel). Multi-port rotary disc valves of various arrangements are based on U.S. Pat.

+피이트(2.6×2.6m)의 평면적을 차지한다. 상기와 같은 밸브들은 상기 밸브 본체에 수력 구동식 작동기를 설치한 형태로 사용되는 별개의 수력장치를 포함하지 않는다. 동일한 기능을 수행하면서도 체적 및 중량이 덜 요구되는 장치를 사용하는 것이 바람직하다는 것을 알 수 있는데, 본 발명은 이와같이 보다 적은 회전밸브를 마련해준다. 두개군으로 도관의 상호연결을 수행할 수 있으며 다음절에 기술된 바와같이 보다 많은 유용성을 갖는다.The multi-rotational disc valves of the devices described in the aforementioned U.S. Patent Nos. 3,040,777 and 3,422,848 are manufactured in various sizes up to valves using rotors of 4 and 1/2 feet (1.37m) diameter. Such a valve has seven concentric circumferential grooves, i.e., twenty-four pots spaced apart around the track and stator circumference. Monolithic valves of this size weigh approximately 26,000 pounds, have an overall height of approximately 15 feet (4.6m) and approximately 8+

It occupies a plane area of + pit (2.6 x 2.6m). Such valves do not include a separate hydraulic device used in the form of installing a hydraulically driven actuator in the valve body. It can be seen that it is desirable to use an apparatus that performs the same function but requires less volume and weight, and the present invention thus provides for fewer rotary valves. The two groups can perform interconnection of conduits and have more utility as described in the next section.

Carson's US Pat. No. 3,040,777 provides a satisfactory design for the simultaneous interconnection of two separate conduit conduit valves, but is not appropriate when the three conduits must be connected simultaneously in the same manner. Referring to Braunton's patent, it can be seen that there are only two groups of conduits required for interconnection when the drawing arrangement of the patent is used. The first group consists of conduits that provide flow through and through the bed, such as feed flow, which flows in and out through the simulated fluid bed adsorbent system. The second group consists of conduits connected to each layer to supply and withdraw fluid from the layers, with one conduit connected between each two layers. Each conduit of the second group does not need to have a conduit for supplying the fluid separately in addition to the conduit for taking out the fluid by performing a dual function of supply and withdrawal.

The apparatus of the present invention is used when it is necessary to interconnect three groups of conduits simultaneously according to a predetermined cycle. An example of a process involving three groups of conduits is described in US Pat. ). As mentioned above, it is highly desirable to solve the problems associated with many separate valves that must be operated simultaneously by using a unitary device.

Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 10. However, this embodiment is not intended to limit the scope of the present invention but merely to aid in understanding the present invention. Therefore, the elements of the present invention may be arranged to form other embodiments, and more or less than or equal to the number of conduits shown in the figures above may be used.

1 illustrates an exemplary process system that will be used to describe the present invention. Such a process system is fully described in the above-mentioned U.S. Patent No. 4,402,832 (Gerhould), which has been described herein for the purpose of understanding the present invention and fluid flow arrangements and systems will be obtained in more detail from the patent. As shown in FIG. 1, there are six separate separation regions indicated by reference numerals 1 to 6. FIG. There are conduits carrying two fluids entering the process system and four fluids flowing out of the process system: four fluid streams: feed, extract, discharge and extract residues. These four fluids are also called process flows. The manner in which the separation units are connected by conduits carrying some fluid streams changes to simulate the separation units in the same direction as the fluid streams.

There are six different arrays of connections specified by the valve in the complete cycle. Two of them are shown in FIG. 1, and from these two steps, the other four steps can be easily understood. As the valve is indexed through each stage of the cycle, the fluid flow is moved to different separation units. The fluid flow is shown to be moved to the left in FIG. 1 to simulate the movement of the separation unit to the right. As shown in step 1 of FIG. 1, the feed stream is supplied to unit 1 during the first stage, the impurity extract is circulated from unit 1 to the inlet, the discharge stream is supplied to unit 4, and the dilution extract residue is It flows from the bottom of unit 4 to the top of unit 5 and circulates the dregs extract in unit 6. At the end of the first stage, the valve is rotated to the second stage position so that the feed stream is supplied to unit 6, and the impure extract stream is extracted from unit 6 and flows to unit 1 as shown in step 2 of FIG. . In the third stage, the feed stream will be introduced into unit 5 and corresponding changes will be made at the source and destination of other fluid streams. During the sixth stage, the feed stream will flow into unit 2 and in the next stage the unit will return to unit 1 and the stroke will repeat infinitely.

FIG. 2 shows the valve as a block, and the flow of fluid in FIG. 1 into and out of the valve is shown as an arrow. Each arrow represents a conduit and the flow direction is as shown. Thus, there are six conduits for delivering fluid to the valves, each of which communicates with the outlet of each separation unit, and six conduits, each for draining fluid from the valve, each of which communicates with the inlet of each separation unit. In addition, there are four conduits corresponding to the above-described process flows. The connected conduits of the valves are classified into three groups: process flows, unit inflows and unit outflows.

In FIG. 3, the hollow stator assembly comprises a central element 11, an end element 12 and an end element 13. In this embodiment of the invention, the end element of the stator assembly is bolted to the central element. Bolts are not shown for simplicity of the drawings). The rotor assembly also comprising a central element and two end elements is generally located inside the hollow of the stator assembly. The rotor or stator assembly may be separated into parts regardless of the terminology used herein, and the use of the word element does not mean that the assembly must be separated into three elements. Each rotor and stator element is cylindrical. In this embodiment, the central element is larger than the diameter of the end element but in other embodiments is not necessarily so. The size is determined taking into account the number, direction, size and mechanical relationships of the fluid flows through the valve. Only part of each rotor element is shown in FIG. 3. The rotor end element 17 protrudes from the stator end element 12, and the rotor end element 18 protrudes from the stator end element 13. The rotor is attached with shafts 19 and 21 and the rotor is supported by the bearing assemblies 22 and 23. Means for rotating the rotor assembly about the axis of rotation are shown at 20. The axis of rotation is the elongated center line of the shafts 19, 21, ie the longitudinal axis of the two assemblies. In a particular embodiment, the rotor rotates in 60 ° increments, and the six stop positions of the rotor are defined as valve index positions and indicate the rotor position during a single cycle step. Means for indexing the shaft, or for rotating it in smaller increments than normal rotation, are known and are hydraulic, electric, or electromechanical. Examples of rotating means are known from US Pat. No. 2,948,168 (Pulse et al.).

Each stator end has a flange 14, to which the sealing driven body 15 is attached by means of a bolt 16. The function of the sealing driven body 15 will be described later. A plurality of nozzles 26 and 27 are attached to the stator to provide a fluid passage between the conduit connected to the nozzle and the interior of the stator. The nozzles 26 represent nozzles in the first group which are located on the stator end assembly, in this case the end element shown on the left. Nozzle 28 represents a second group of nozzles on another stator end element located on the right side of FIG. A third group of nozzles is installed on the central stator element adjacent the left stator end element and includes a nozzle 27. The nozzle 29 represents a fourth group of nozzles attached to the center stator element adjacent the right stator end element. Similarly, stator tiepipes 31 connect nozzles 36 and 78 to provide a fluid passage between the two nozzles. Similarly, stator tie pipe 30 provides a passage for fluid flow between nozzle 26 and nozzle 64. Arrow 35 shows how the eighth figure is taken.

Reference numerals in FIG. 3 are the same as those in FIGS. 1, 2 and 8. All conduits have been described with reference to FIGS. 1 and 2, and 16 conduits are connected to the stator assembly by nozzles, but not all are shown in FIG. There are six nozzles in the third group including the nozzles 27. Two of the third group nozzles, not shown in FIG. 3, are located behind the stator central element. The nozzles of the third group are equally spaced around the stator central element at 60 ° intervals, all of which are in a single plane normal to the axis of rotation. The nozzles of the fourth group are arranged in the same way as the third group, and only three of them are shown in FIG.

1, 3 and 8, reference numerals 1T through 6T and 1B through 6B indicate that the specific separation unit and conduit fixed to the unit communicate between the nozzle and the top of separation unit 1, and 3B indicates the nozzle. This means that the conduit attached to it communicates between the nozzle and the lower third of the separation unit. The terms "top" and "bottom" are only used for convenience and the inlet to the separator is shown at the top of the figure.

Referring to FIG. 4, reference numerals used in FIG. 3 are used, wherein the rotor end element 17 is located inside the stator end element 12, and the nozzles 26 and 36 in FIG. It is shown in the figure. Two inner channels 37, 38 are shown in the rotor end element 17. Within the rotor end element 17 there are two additional passages, not shown, all four passages, which extend into the rotor central element (not shown in FIG. 4) forming the first group. . Channel 37 is in communication with nozzle 26 and channel 38 is in communication with nozzle 36. The stator end element 12 has a diameter larger than the outer diameter of the rotor end element 17 to form an annular space between these elements. As shown in FIG. 4, the annular space is filled with sealing. The end sealing ring 39 comes into contact with a portion of the sealing driven member 15 which protrudes into the annular space. Rotating seal ring 40 is positioned adjacent end sealing ring 39, followed by fixed sealing ring 43. Another one-turn seal ring 40 is adjacent to the fixed seal ring 43 on the opposite side. 5 shows a single turn sealing 40. In the same way, an annular space is formed between the rotor end element 18 and the stator end element 13 and between the rotor center element and the stator center element.

All nozzles communicate with the annular space between the rotor assembly and the stator assembly. The sealing is a means by which a fluid passage in the end element annular space is formed and prevents fluid mixing and external leakage in the annular space. For example, fluid flowing into channel 37 and nozzle 26 is separated from fluid in channel 38 and nozzle 36 by sealing. The rotary seal ring 40 extends circumferentially around the rotor end element and has an annular passage in a portion of the annular space between the stator and the rotor end element and between the inner wall of the stator end element and the outer surface on the ring 40. 44) is arranged to form. 5 shows the entire sealing. The zero ring 52 is omitted from the inner surface of the seal ring shown in FIG. A hole 45 in the rotating seal ring 40 shown in FIG. 5 is connected to the channel 37 to allow fluid flow between the channel 37 and the annular passage 44. The annular passage 44 is circumferentially extending 360 ° around the rotor assembly and is always in communication with the nozzle 26 so that the nozzle 26 and the channel 37 are connected. Likewise each other passage of the left rotor end element always communicates with a particular nozzle fixed to the left rotor end element. As shown in FIG. 4, a 0-ring 52 is disposed on each side of the ring 40 so that fluid from the hole 45 and the annular passage 44 can be transferred to the outer surface and the ring 40 of the end element. To prevent it from flowing in the longitudinal direction parallel to the axis of rotation along the inner surface of the

The end sealing ring 39 is not rotated and held in place by a set screw 8 which is inserted through the wall of the stator element and projects into the cavity 42. Rotating seal ring 40 is fixed to the rotor to rotate together. Fixation is achieved by the grooves 41 in each rotating seal ring 40. There is a tongue (not shown) that engages the groove on the end element for each sealing ring 40. The sealing is locked in place by engagement of the tongue and groove. The fixing seal ring 43 is prevented from being rotated by the fixing screw in the same manner as the end sealing ring 39. The zero ring 52 prevents liquid from leaking between the rotor end element and the rotary seal ring 40 as described above, and in the same manner the stator end element and the fixed seal ring 43 or end seal. Prevents fluid leakage between the rings 39. Leakage occurs between the wall of the stator and the rotary seal ring 40. This leak serves as a lubricant and is contained in the seal interface 53 in a plane extending around 60 ° around the rotor end element and perpendicular to the axis of rotation. As the sealing surface at the interface 53, a material well known in the case of supporting the rotating sealing surface by the fixing sealing surface can be used. For example, common pairs of seal face materials include carbon and tungsten. The seal ring 40 may be made entirely of tungsten, and the rings 39 and 43 may be made entirely of carbon only, or carbon and tungsten may be applied to other base ring materials.

Hereinafter, the entire apparatus of the left rotor end element will be described. Rotating seal ring 40 is located at each of the four nozzles of stator end element 12. The fixed sealing ring 43 is located between the rotating sealing rings. Each end element has three fixing rings, and at each end of the annular space formed by the left end element there is an end seal ring 39. The rotor end element shown on the right side of FIG. 3 is also arranged in the same manner as above. Only one end of the annular space between the end elements is shown in FIG. 4 and the other end is shown in FIG. 6, in which the assembly of the sealing ring is adjacent to the rotor sleeve 51 by the shoulder. It can be seen that it is held above the rotor end element. At the outer end, the ring assembly is fixed in place by the seal driven body 15. In addition, a seal force is applied to the interface by the seal driven body 15. Several bolts 16 are each provided with a spring 25. The spacer 24 presses the spring 25 by the rotation of the bolt 16 and thus pushes the seal driven body 15 into the stator central element thereby providing a force for the seal.

6 shows the other end of the stator element 12, the rotor end element 17, part of the stator center element 11 and part of the rotor center element 46. Rotor central element 46 and rotor end element 17 are secured together by bolts 47 and the like. The rotor sleeve 51 is used as a bearing by providing a gap between the stator element 12 and the rotor element 17. Channels 37 and 38 communicate with the annular space between the rotor central element 46 and the stator central element 11. Fluid flows between nozzle 27 and channel 37 and between nozzle 50 and channel 38. The prevention of mixing of these fluids and other fluids in the central element annular space and the limitation of the fluid passage are achieved by the rotor seal element 48. 9 is a cross-sectional view of the single rotor seal element 48. 10 shows a plan view of the rotor seal element 48 comprising a seal surface.

7 shows a rotor center element 46 with several seal elements 48.

3 shows an arrangement of the left side of the valve in detail, the right side of the valve consisting of the rotor and stator end elements and the right side of the rotor and stator center elements are similar. 4 and 6 show the right side of the valve.

Hereinafter, description will be given with reference to FIGS. 6, 7, 9 and 10. Rotor seal elements are disposed at each end of each channel (described below) in the rotor center assembly and at the end of the central element of each passage. These seal elements establish a fluid passage to prevent mixing of the fluid in the central annular space. In this embodiment, there are eight rotary yarn seal elements 48 in the channel and four in the passageway, a total of twelve. Reference numeral 60 designates a fluid channel. A cylindrical conduit consisting of an elongated cylindrical portion of the rotor seal element 48 is disposed within a portion of the channel 37. This portion of the channel 37 has a larger diameter than the other portions of the passageway so that the shoulder is formed to hold the spring 49. Each rotor seal element has a 0-ring 59 around its outer circumference to prevent leakage between the annular space and the passage wall. The curved approximately right angle plate is secured to the cylindrical portion and covered by the rotor seal element sheet 56.

The spring 49 urges the sealing surface 55 against the inner surface of the stator central element 11 which is smoothly finished to prevent leakage. The sealing surface 55 is part of the rotor seal element sheet 56 formed of a soft elastic material. The rotor seal element sheet 56 is held in connection by two retainers 57 and four screws 58. Rotation of the rotor assembly causes movement of the inner wall circumference of the stator central element and its outer surface resulting in wear of the seal surface 55. The spring 49 provides a force for the seal and allows to maintain the seal in the event of abrasion, but there is a need to replace the rotor element sheet 56 periodically. Since the movement of the rotor seal element 48 in the enlarged portion of the channel 37 is relatively small, such movement does not affect the sealing ability of the 0-ring 59.

4 and 6, the channels 37 and 38 are shown to comprise three parts. One part is perpendicular to the axis of rotation and completely located at the rotor end element. One part is parallel to the axis and is located at the rotor end element and the rotor center element. One part is parallel to the axis and is located completely at the rotor center element. The other six channels (eight channels in total) of this embodiment are similar.

In FIG. 8 all exposures in groups 3 and 4 are shown.

Exposures 1B to 6B are shown in cross section and are arranged uniformly every 60 ° around the stator central element 11 in the plane. The nozzles 1T to 6T, which are connected to the separation region, that is, the upper portion of the separation unit by conduits, are arranged in the same manner as shown in FIG. 1, but are deflected by 30 ° from the nozzles of the third group. The reason for deflecting 30 ° in this embodiment is to provide convenience in connecting the conduit to the stator center element, since the center element can be shortened as compared with the nozzles positioned side by side without being deflected by 30 °. to be. For example, when both the nozzles 29 and 50 are located below, the pipe flanges at the nozzle 29 may interfere with the flanges at the nozzle 50. The direction of rotation of the rotor assembly is shown by arrow 62.

The complete fluid delivery path will now be understood.

For example, in the first step of the six-stage stroke, the extraction residue flows out of the process system by the nozzle 32 and flows into the valve by the nozzle 5B connected to the lower part of the separation unit 5 by a conduit. Pass the nozzle 32 through the channel 61. In the second step of the process, the extract residues flow into the valve from the separating unit 4 through the nozzle 4B. Since the rotor is indexed at 60 ° from the first stage to the second stage, the nozzle 4B is aligned with the channel 61 so that the extract residue flows from the channel 61 to the nozzle 32. In the third, fourth, fifth and sixth stages, the extract residues flow in the same manner as described above.

Between the nozzle and each end of the channel 61, the extract residues flow into the annular space, one between the central element and one between the end elements. The fluid stream is received and prevented from mixing with other fluid streams flowing through the valve by the sealing means described above.

As another example of the fluid flow path through the valve, impurity extraction residue from the lower part of the separation unit 6 is introduced into the valve through the nozzle 27 (FIG. 1, step 1) via the channel 37. Flow to the nozzle 26 (FIG. 3). Extraction residue from the nozzle 26 flows to the nozzle 64 via the stator tie pipe 30 (FIG. 3). Tie pipe is used herein to mean a conduit communicating between two nozzles of a valve. After that, the impurity extraction debris flows from the nozzle 64 to the nozzle 65 via a passage in the right side of the right rotor end element and the rotor center element. The nozzle 65 is connected to a conduit that delivers a fluid stream to the top of the separation unit 6. In the second stage of the cycle, the rotor is indexed such that the impurity extraction debris from the separating unit 5 flows into the channel 37.

It can be seen that the first set of nozzles communicates with the third set of nozzles by a channel in the first group, a passage in the left annular space between the end elements and a passage in the central annular space. The second set of nozzles communicates with the fourth set of nozzles in a similar manner, and the fluid path includes channels in the second group of channels.

In FIG. 1, the conduit containing the impurity extract from the bottom of the separating unit 1 is connected with the conduit providing the separating unit 2. This is accomplished by the passage 66 in the rotor central element. 8, the first step, the passage 66 is located entirely in the rotor central element to connect the nozzle 67 and the nozzle 68. The passage 66 consists of three parts. The first end is connected to the nozzle 67 as shown in FIG. The second end is not shown in FIG. 8 but in configuration is similar to the first end and connected to the nozzle 68. The third portion of the passage 66 is similar to the two ends and is connected to the nozzle 68. The third portion of the passage 66 is connected with the two ends and is perpendicular to them. The third part is drilled from one side of the rotor center element such that the end element is dismantled from the center element and then the first part of the drilled hole adjacent the end of the center element is blocked. The rotor seal element 48 can be used in the annulus and at the end of the passage 66 in the same way as at the passage end. In the second stage of the stroke, the passage 66 provides a flow path between the nozzle 27 and the nozzle 69, and the same for other stroke stages. Similarly, the passage 70 provides a flow path between the separation units 4 and 5 in the first step or the like. The passages 66 and 70 allow the third set of nozzles to cooperate with the fourth set of nozzles.

In such an embodiment, the fluid flowing through the process is a liquid, requiring a pump at some location. For example, referring to FIG. 1, step 1, a pump is required to deliver the dilute extract stream from the bottom of unit 6 to the top of unit 6. Such a pump is located in the tiepipe 30. This same pump can be used to transfer the liquid between 5B and 5T in the second stage of the stroke as shown in FIG. Similarly, a single pump can be used only when it is necessary to connect to each column and pump the fluid flow associated with that column. Devices such as pumps and compressors used to deliver fluids are no longer mentioned because such devices may be used when such devices are required.

11 and 12 illustrate embodiments in which valves are used to connect multiple conduits in two groups. The process shown is the process of the Braunton patent (US Pat. No. 2,985,589). The process description is detailed above and will be further explained in the next section. The description of such an embodiment will not need to be as detailed as the above-described embodiment since the basic principles of the present invention have been presented from the above-described embodiment. These examples do not limit the scope of the invention. There are twelve layers in the container 71 and one layer 72 is shown in cross section in FIG. Layer 72 is held by layer support means at the bottom of the conical portion. The liquid is evenly distributed on top of the layer by a distributor 73 which is perforated. Liquid flowing through the bed is collected in the reservoir 74. Once the liquid is withdrawn from the reservoir 74, it flows out of the container 71 through an inner conduit 75 that links between the reservoir and the conduit 106. Conduit 106 delivers the liquid to the valve. If no liquid is withdrawn, the flow path is blocked at the valve and the liquid overflows from the reservoir and is distributed to the next lower layer by another distributor 73 through downcomer 77. Once the liquid is added, it is distributed from the valve through the conduit 106 to the next lower layer in the same way as the liquid flowing through the layer 72.

There are four basic fluid streams whose junction points to the container 71 and the bed vary with each administration step. Since there are twelve layers, the liquid flows into a given layer every three cycle steps. For example, liquid flows into conduit 106 every three stages and all fluid flows through downcomer 77 during the other two stages. The layers are classified from B1 to B12 starting from the top of the container 71. Layer 72 is B6.

Twelve conduits should connect the vessel and the valve. This is illustrated by twelve conduits bushed by 101-112 connected to the enlarged central portion of the block representing the valve, with the enlarged central portion indicating the stator central element. In the first stage of administration, the feed stream flows to bed B6.

After that, the extract residue flows from layer B9 and the discharge flows to layer B12, and the extract flows from B3. During the second stage the feed stream flows to B7, the extract residues from B10, the discharge stream to B1 and the extract streams from B4. The fluid flows repeatedly in the same way through the remainder of step 12 of the stroke.

The twelve conduits 101-112 are connected to twelve nozzles attached to the stator central element in the same arrangement as the embodiments described above presented herein. As in the embodiment, five of the conduits are not shown in the diagram of the entire valve shown in FIG. The nozzles of FIG. 12 are categorized into 10 l through 106 and 112 to indicate conduits connected to them. That is, layer B6 is connected to conduit 106. There is a significant difference between this embodiment and the above-described embodiment associated with the Ger-Hold process (US Pat. No. 4,402,832). There is no such thing as the passages 66 and 70 in the rotor central element, and no tiepipes are required. The third difference is that the rotor assembly of this embodiment rotates by 30 ° to conform to the 12 cycle steps.

As an example of the Ger-Hold process, four rotors are fixed to each rotor end element. Each of the four basic fluid streams is directed to each end element. For example, fluid flow in conduit 120 is supplied to each end element by conduits 121 and 122 diverging from conduit 120. In the first stage of the cycle, the feed stream flows into the valve through the nozzle 124 and flows out of the valve through the nozzle 106.

In the first stage of the cycle, the feed stream entering the valve through the nozzle 123 does not flow more than the seal element in the annular space between the rotor and the stator center element, because the center element nozzle is the right rotor end element. This is because it is not aligned with any of the four channels within. In the second stage of the cycle, the rotor assembly is indexed at 30 ° and the feed stream is introduced into the nozzle 123 through passages in the side and right end rotors of the rotor central element and the conduit 107 (FIG. 11). This fixed nozzle flows out from the valve. Conduit 107 provides a feed stream to layer B7.

The feed stream entering the valve through the nozzle 124 during the second stage is blocked in the same way as in the first stage. That is, the channel end in the left side of the rotor center element is closed by the stator center element wall. Other basic fluid streams, i.e., discharge streams, extract streams and extract residues, flow in a similar manner. In this embodiment, the passage shown in FIG. 8 does not exist so that even if the other four nozzles are aligned, the two nozzles on the right side of the center element and the two nozzles on the left side are not always aligned with any channel.

Thus, during the cycle phase, none of the nozzles on one side of the two sides of the central element are in communication with the channel, and only four of the six nozzles on the other side are in communication with the channel so that fluid can flow only at the four nozzles.

Sealing means other than the above sealing may be used. The annular space between the end elements is filled with a conventional shaft packing and compressed by means similar to the sealing driven body 15. A fixed lantern ring is used in place of the rotating seal ring to provide a fluid passage identical to the annular passage 44. The lip seal of the sealing described above may be used. Such may be used alone or in conjunction with rings spaced along the shaft to assist in securing the fluid passage.

The ring is then identical in form to a flat washer. Similarly, a plastic liner or lip seal with self-lubricating properties on the rotor seal element 48 may be replaced. The liner may be made of reinforced or unreinforced tetrafluoro ethylene and has holes in appropriate places to allow fluid flow. Robust holding means are provided at various locations to reduce the tendency for the liner to "clip".

In each of the above embodiments, there are four nozzles in each of the first and second sets of nozzles, and six nozzles in the third and fourth sets. Of course, it is also possible to design valves with different numbers of nozzles to accommodate more or fewer conduits. The number of tiepipes may be varied to connect several groups of nozzles depending on the type of flow required for a particular process. If a tiepipe is used, a pipe expansion joint needs to be placed in the tiepipe to prevent leakage due to expansion caused by the hot fluid flowing through the valve and damage to the valve.

It is preferable to use a cleaning fluid as described above, and nozzles and channels are suitable for this purpose. Indexing of the rotary valve means that the rotor assembly is in operation. The valve index position refers to the position of the rotor assembly that is fixed and in which the opening is in communication. The components of the present invention are made of suitable materials such as metals and plastics. The fluid passage can be easily sized according to one of several standard methods.

An example of a valve dimension is a rotor for a valve that has six separate units and is suitable for use in the above described Gerhould process with reduced flow rates requiring channels of 1 and 1/2 inch (38.1 mm) diameter. The assembly has a total length of 42 inches (1.07 m), a diameter of 5 inches (127 mm) at the end element and a diameter of 10 inches (254 mm) at the central element, and the entire valve including the drive mechanism is about 7 feet in length. (2.13m) or so.

The rotor end element with four 4 inch (102 mm) diameter channels to operate the fluid under moderate pressure may have a diameter of 14 inch (355.6 mm).

In the above embodiment, the nozzle is shown as a short length conduit with a flange and attached to the stator assembly to be connected to the conduits interconnected by the valve. However, the term nozzle is broadly used to denote a means for connecting the conduits and the annular space.

For example, where it is desirable to connect a conduit to a valve by welding, the term nozzle can refer to an opening in the stator assembly wall shaped to receive the conduits to be welded.

Claims (6)

Stator assembly 11-13 having a hollow interior, multiple nozzles 26-36, 50, 64, 65, 78 for connecting the conduit to the valve, rotor assembly 46 located in the interior hollow of the stator assembly Axial multi-port rotary valves comprising a plurality of conduits simultaneously interconnecting a plurality of conduits at predetermined intervals such that one conduit is connected to any other conduit by means of a valve at one index position (A) The stator assembly comprises a coaxial central cylindrical element (11), a first end element (12) and a second end element (13), the end elements being at both ends of the central element. (B) the first set of nozzles 26-36, 50, 64, 65, 78 for connecting the conduits to the valve is attached to the stator first end element 12 26, 32, 34, 36, a second set 28, 33, 64, 78 attached to the stator second end element 13, the fastening A third set (27,50) attached to the stator central element (11) adjacent to the first end element (12), and to the stator central element (11) adjacent to the stator second end element (13). Classified into a fourth set 29 to be attached; (c) the rotor assembly comprises a central element 46, a first end element 17, and a second end element 18, each coaxial, wherein the end elements are located at both ends of the central element, A first annular space is formed between the rotor end element 17 and the stator full element 12, and a second annular space is formed between the rotor center element 46 and the stator central element 11. Wherein the rotor assembly rotates around the rotational axis, the longitudinal axis of the rotor and stator assembly, at various valve index positions according to the predetermined period, the rotor assembly being a portion located within the rotor first end element. Having a plurality of internal channels 37,38 classified into a first group 37,38 comprising a channel having a channel and a second group comprising a channel having a portion located within the second rotor end element. Nozzles 26, 32, 34, 38 of the first nozzle set A channel in the first channel group, a passage in the first annular space, and a passage in the central annular space, connected to the third set of nozzles 27, 50, and the second set of nozzles 28, 33, 64,78 are connected to the fourth set of nozzles 29 by a second group of channels, a passage in the second annular space, and a passage in the central annular space: (d) the rotor assembly 17 In order to limit the fluid passages interconnected with the inner channels 37 and 38 of the valve 18, to prevent mixing of the fluid flowing through the valve, and to prevent external leakage, a pair of nozzles may be provided at each valve index position. Interconnected in cycles, one of the annular fluid channel, the rotor assembly passage and another of the annular fluid channel before the fluid supplied by the nozzle enters another nozzle and exits the valve. In order to flow Is comprises means (39,40,43,45,48) in said annular space; (e) means (66,70) for interconnecting the second set of at least one nozzle with the third set of nozzles. 2. The apparatus of claim 1, wherein said means for interconnecting said second set of at least one nozzle and said third set of nozzles comprises at least one passageway (66, 70) located entirely within the rotating central element (46). And the passage has a first end portion that mates with one nozzle attached to the stator central element at each valve index position and a second end portion that mates with another nozzle attached to the stator central element at each valve index position. An axial multi-port rotary valve characterized in that it has. 3. A rotor according to claim 1 or 2, wherein each of the plurality of internal channels (37,38) in the rotor assembly is subdivided, ie perpendicular to the axis of rotation and entirely located on the rotor end element, parallel to the axis. And a portion located at both the stator end element and the rotor center element, and portions perpendicular to the axis and entirely positioned within the rotor center element. 2. The annular space of claim 1, wherein the means in the annular space comprises a rotating seal ring (40) attached in a form extending around the circumference of the rotor end element, the ring (40) being annular between the rotor and the stator end element. It is approximately the same height as the width of the space and has a length sufficient to include a hole 45 and an annular passage 44 providing a fluid flow path between the channel and the nozzle, wherein the annular passage 44 is formed around the ring. Extends 360 ° to one side of the stator end assembly, the other side abuts the ring, and the ring 40 contacts the outer surface of the rotor end element from the aperture 45 and the channel. And sealing means 52 for preventing fluid from flowing in a longitudinal direction parallel to the axis of rotation along the interface of the inner surface of the ring, and the ring being located in a plane perpendicular to the axis of rotation. The lubrication has two lubricated rotating seal surfaces extending 360 [deg.], Wherein lubrication of the surfaces is provided by the leakage of fluid from the annular passageway along the interface between the outer surface of the ring and the inner surface portion of the stator end element. Axial multiple port rotary valve, characterized in that the. 2. A stator sealing ring according to claim 1, wherein the means in the annular space comprises stator sealing rings (39, 43) attached to the stator end elements in a form extending around the rotor end elements. A seal having a height approximately equal to the width of the annular space between the end elements, for preventing fluid from flowing in a longitudinal direction parallel to the axis of rotation along the interface of the outer surface of the stator sealing element and the inner surface of the stator end element; A ring means 52 and having at least one stationary seal surface extending 360 ° around the ring in a plane perpendicular to the axis of rotation and lubricated by fluid leakage from the annular fluid passageway. Axial multi-port rotary valve. The cylindrical conduit of claim 1, wherein the means in the annular space is located entirely at the rotor central element and at least partially within the enlarged diameter end of the channel perpendicular to the axis of rotation. An outer rotor conduit at one end, the rotor seal element 48 comprising a rotor seal element 48, and having a radius of curvature perpendicular to the longitudinal axis of the conduit and substantially equal to the radius of curvature of the inner surface of the stator central element 11. And a curved plate that is hermetically attached in a form enclosing the fluid, and further comprising fluid flowing in a direction parallel to the longitudinal axis of the conduit along the interface of the enlarged channel portion surface and the outer surface of the conduit. Sealing means 59 for preventing the fluid from leaking along the interface between the curved plate and the inner surface of the stator central element. Axial direction, characterized in that it comprises a spring means (49) for contacting the curved plate against the inner surface of the stator central element (11) such that fluid flows by the cylindrical conduit between the channel and the nozzle thereby. Multi-port rotary valve.

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