CN114427756A - Wave rotor and rotary type heat separator - Google Patents
Wave rotor and rotary type heat separator Download PDFInfo
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- CN114427756A CN114427756A CN202011042401.5A CN202011042401A CN114427756A CN 114427756 A CN114427756 A CN 114427756A CN 202011042401 A CN202011042401 A CN 202011042401A CN 114427756 A CN114427756 A CN 114427756A
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- 239000002356 single layer Substances 0.000 abstract description 7
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- 206010022000 influenza Diseases 0.000 abstract description 3
- 239000007789 gas Substances 0.000 description 117
- 238000000034 method Methods 0.000 description 11
- 230000008569 process Effects 0.000 description 11
- 238000005057 refrigeration Methods 0.000 description 8
- 239000000758 substrate Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 5
- 238000012546 transfer Methods 0.000 description 4
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- 238000009825 accumulation Methods 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
Abstract
The invention discloses a wave rotor and a rotary thermal separator. The ripples rotor includes rotor inner tube and rotor urceolus, and rotor inner tube and rotor urceolus are both ends open barrel, and the rotor inner tube sets firmly with the rotor urceolus is coaxial, between rotor inner tube and rotor urceolus, radially along the rotor inner tube be provided with two-layer ring chamber at least, all be provided with many oscillation air flues of leading to long arranging along the axial of this layer of ring chamber in every layer of ring chamber, and many oscillation air flues of same layer of ring chamber distribute along the circumference of this layer of ring chamber. The rotary thermal separator comprises the wave rotor. According to the invention, the problem of low system efficiency of the conventional multistage thermal separator adopting a single-layer channel wave rotor can be effectively solved.
Description
Technical Field
The invention belongs to the technical field of gas jet, and particularly relates to a wave rotor and a rotary thermal separator.
Background
The rotary heat separator is a refrigeration equipment with near isentropic decompression, mainly comprising nozzle, wave rotor and rotary distributor. High-energy gas is sprayed into the oscillating tube of the wave rotor through the nozzle, the gas in the oscillating tube is compressed to raise the temperature, and the temperature rise can reach about 500 ℃. The heat generated by the compression is transferred out of the outer surface of the oscillation tube by natural convection or forced convection. The injection of gas is intermittent, since the machine is equipped with a rotary distributor. When the gas in the oscillating pipe is compressed and heated, the gas inlet is stopped, the gas in the oscillating pipe changes the flowing direction and is subjected to adiabatic expansion and pressure reduction, so that the power gas in the oscillating pipe is cooled and discharged, and the heat separator finishes a working process. At this time, the high-energy gas is sprayed out through the nozzle again, and the second working process is started. As a result of such repetition, the temperature of the power gas can be lowered to-30 to-90 ℃. The degree of refrigeration is related to the pressure drop in and out and the gas composition.
The wave rotor is the most important part of the rotary thermal separator, and the rotary thermal separator realizes the matching of compression waves and expansion waves in an oscillating pipe of the wave rotor by utilizing the high-speed rotation of the wave rotor, so that the energy exchange between gases with different pressures is completed, and the refrigeration effect is realized.
The existing heat separator can be divided into a single-stage heat separator and a multi-stage heat separator.
When the pressure ratio is too large, the speed of the airflow reaches a sonic or supersonic speed state, and the internal energy separation is influenced, namely, the cold-heat separation effect is inhibited. Therefore, the expansion ratio of the existing single-stage thermal separator is generally between 2 and 4. In order to meet the refrigeration requirement under the working condition of high pressure ratio, a mode of connecting a plurality of single-stage heat separators in series is generally adopted to achieve the target requirement. However, in such a system in which a plurality of single-stage heat separators are connected in series, although the expansion ratio of each single-stage heat separator can be controlled within a reasonable range, the pressure of the gas is not efficiently recovered. In addition, the problem of low overall efficiency of the system due to poor matching degree among the heat separators of each stage is also easily caused by the mode that the plurality of single-stage heat separators are connected in series.
For this reason, multi-stage thermal separators are increasingly being used for refrigeration at high pressure ratio conditions. Existing multistage thermal separators are mainly of two types: an oscillating tube one end open type multistage heat separator and a single-layer channel wave rotor type multistage heat separator. Although the multistage heat separator with the opening at one end of the oscillating pipe can realize multistage refrigeration under a high pressure ratio, the phenomenon of liquid accumulation of the oscillating pipe can occur in the working process, and the oscillating pipe can be broken in severe cases. In addition, the multistage thermal separator with the opening at one end of the oscillating pipe has the problems of larger overall size and slower heat dissipation. Although the single-layer channel wave rotor type multistage thermal separator solves the problems of the oscillation tube one-end opening type multistage thermal separator, the wave rotor with the single-layer channel structure is used, gas between channels cannot realize sufficient heat exchange, energy dissipation is serious, and the working efficiency of the whole machine is further influenced.
Disclosure of Invention
The invention aims to solve the problem of low system efficiency of the conventional multistage thermal separator adopting a single-layer channel wave rotor.
In order to achieve the above object, the present invention provides a wave rotor and a rotary thermal separator.
According to a first aspect of the present invention, there is provided a wave rotor, comprising a rotor inner cylinder and a rotor outer cylinder, both of which are open-ended cylinders, the rotor inner cylinder and the rotor outer cylinder being coaxially fixed;
at least two layers of annular cavities are arranged between the rotor inner cylinder and the rotor outer cylinder along the radial direction of the rotor inner cylinder;
and a plurality of oscillating air passages arranged along the axial full length of the ring cavity on the layer are arranged in each ring cavity, and the oscillating air passages in the same ring cavity are distributed along the circumferential direction of the ring cavity on the layer.
Preferably, the wave rotor further comprises a plurality of sleeve type partition plates, and the plurality of sleeve type partition plates divide the gap between the rotor inner cylinder and the rotor outer cylinder into at least two layers of annular cavities.
Preferably, a plurality of strip type partition plates are arranged in each layer of annular cavity, and the strip type partition plates divide the layer of annular cavity into a plurality of oscillating air passages.
Preferably, the number of the layers of the ring cavity is m, and m is more than or equal to 2 and less than or equal to 10.
Preferably, the widths and heights of the plurality of oscillating air passages in the same layer of annular cavity are all equal;
the width of the oscillating air passage is the distance between the two strip type partition plates corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip type partition plate corresponding to the oscillating air passage.
Preferably, the ratio of the height to the width of the oscillating air duct is n, 0.2< n < 5.
According to a second aspect of the present invention there is provided a rotary thermal separator comprising any one of the above-described wave rotors.
Preferably, the rotary thermal separator further comprises a housing, a first end cap, a second end cap, a first nozzle, a second nozzle, and a central shaft;
the two ends of the shell are both opened, and the first end cover and the second end cover are buckled at the two ends of the shell respectively;
the central shaft and the shell are coaxially arranged and are axially and fixedly connected, a first end of the central shaft penetrates through the first end cover and then extends into the shell, and a second end of the central shaft is exposed out of the first end cover;
the wave rotor is arranged in the shell and can synchronously rotate with the central shaft;
the first nozzle and the second nozzle are fixedly arranged in the shell and are respectively positioned at two ends of the wave rotor;
the disc type nozzle comprises a circular base plate, an air inlet and an air outlet which are arranged on the base plate, and the air inlet and the air outlet are both of a laminated structure matched with the laminated ring cavities;
a high-temperature gas discharge cavity and a low-pressure gas inlet cavity are arranged in the first end cover, and a low-temperature gas discharge cavity and a high-pressure gas inlet cavity are arranged in the second end cover;
the high-temperature gas discharge cavity is communicated with the exhaust port of the first nozzle, the low-pressure gas inlet cavity is communicated with the gas inlet of the first nozzle, the low-temperature gas discharge cavity is communicated with the exhaust port of the second nozzle, and the high-pressure gas inlet cavity is communicated with the gas inlet of the second nozzle.
Preferably, the rotary thermal separator further comprises a rotor inner sleeve, the rotor inner sleeve is arranged between the central shaft and the wave rotor, and the wave rotor is linked with the central shaft through the rotor inner sleeve.
Preferably, the rotary thermal separator further comprises a motor and a coupling;
and a rotating shaft of the motor is in transmission connection with the central shaft through the coupler.
The invention has the beneficial effects that:
the wave rotor is provided with at least two layers of ring cavities between the rotor inner cylinder and the rotor outer cylinder, and each layer of ring cavity is provided with a plurality of oscillating air passages equivalent to oscillating pipes. Therefore, the wave rotor of the present invention has a multilayer channel structure. The wave rotor based on the multilayer channel structure can realize a plurality of heat exchange processes, namely, realize multi-stage refrigeration under the working condition of large compression ratio. Because the wave rotor is provided with the multiple layers of channels, the wave rotor can be designed independently aiming at partial channels, so that the channels are filled with low-temperature gas or high-temperature gas, and precooling and heat preservation of the channels of the adjacent layers are realized, thereby improving the cold-heat separation efficiency of a target channel, reducing energy dissipation and improving the efficiency of a corresponding heat separator.
The invention also provides a thermal separator which comprises the wave rotor with the multilayer channel structure and has the same beneficial effects as the wave rotor with the multilayer channel structure.
Additional features and advantages of the invention will be set forth in the detailed description which follows.
Drawings
The above and other objects, features and advantages of the present invention will become more apparent by describing in more detail exemplary embodiments thereof with reference to the attached drawings, in which like reference numerals generally represent like parts throughout.
Fig. 1 shows a schematic structural view of a wave rotor according to embodiments 1 to 3 of the present invention.
FIG. 2 shows a schematic perspective structural view of a rotary thermal separator according to embodiments 2 and 3 of the present invention.
Fig. 3 shows a schematic structural view of a first nozzle according to embodiments 2 and 3 of the present invention.
Fig. 4 shows a schematic structural view of a second nozzle according to embodiments 2 and 3 of the present invention.
Detailed Description
Preferred embodiments of the present invention will be described in more detail below. While the following describes preferred embodiments of the present invention, it should be understood that the present invention may be embodied in various forms and should not be limited by the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art.
Example 1: fig. 1 shows a schematic view of the wave rotor structure of the present embodiment. Referring to fig. 1, the wave rotor of the present embodiment includes a rotor inner cylinder 1 and a rotor outer cylinder 2, both the rotor inner cylinder 1 and the rotor outer cylinder 2 are cylinders with open two ends, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially and fixedly arranged;
two layers of annular cavities are arranged between the rotor inner cylinder 1 and the rotor outer cylinder 2 along the radial direction of the rotor inner cylinder 1;
and a plurality of oscillating air passages arranged along the axial full length of the ring cavity on the layer are arranged in each ring cavity, and the oscillating air passages in the same ring cavity are distributed along the circumferential direction of the ring cavity on the layer.
The wave rotor of the embodiment also comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides a gap between the rotor inner cylinder 1 and the rotor outer cylinder 2 into two layers of annular cavities.
A plurality of strip type partition plates 4 are arranged in each layer of annular cavity, and the strip type partition plates 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The width and the height of a plurality of oscillating air passages in the same layer of annular cavity are equal;
the width of the oscillating air passage is the distance between the two strip type partition plates 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip type partition plate 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air duct is 2.
In this embodiment, the ring cavity is an internal channel of the wave rotor. The internal channel of this embodiment with the ripples rotor sets up to two-layerly, sets up through telescopic baffle 3 interval between the two-layer passageway, all is many oscillation air flues through 4 intervals of a plurality of strip formula baffles in every layer of passageway, and compression wave and expansion wave realize matcing in the oscillation air flue.
In engineering practice, the number of layers of the channel of the wave rotor can be adjusted according to actual pressure ratio requirements, and the adjustment range is 2-10 layers. Because when the internal channel of the wave rotor is too many, it is difficult to achieve normal flow of gas in the channel, and the matching difficulty of temperature is significantly increased, heat exchange becomes more complicated, the design difficulty is increased, and the actual effect may be deteriorated.
In engineering practice, the aspect ratio of the oscillating air passages in each layer of channels can be adjusted according to the flow rate of the single layer of air flow and the actual size of the wave rotor, but should generally satisfy the aspect ratio of between 0.2 and 5. Because an oscillating gas channel with an excessive aspect ratio increases the flow loss of gas and reduces the system efficiency.
Example 2: fig. 1 is a schematic structural diagram illustrating a wave rotor included in a rotary thermal separator according to this embodiment, and referring to fig. 1, the wave rotor included in the rotary thermal separator according to this embodiment includes a rotor inner cylinder 1 and a rotor outer cylinder 2, both ends of the rotor inner cylinder 1 and the rotor outer cylinder 2 are open, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially and fixedly arranged;
two layers of annular cavities are arranged between the rotor inner cylinder 1 and the rotor outer cylinder 2 along the radial direction of the rotor inner cylinder 1;
and a plurality of oscillating air passages arranged along the axial full length of the ring cavity on the layer are arranged in each ring cavity, and the oscillating air passages in the same ring cavity are distributed along the circumferential direction of the ring cavity on the layer.
The wave rotor of the embodiment also comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides a gap between the rotor inner cylinder 1 and the rotor outer cylinder 2 into two layers of annular cavities.
A plurality of strip type partition plates 4 are arranged in each layer of annular cavity, and the strip type partition plates 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The width and the height of a plurality of oscillating air passages in the same layer of annular cavity are equal;
the width of the oscillating air passage is the distance between the two strip type partition plates 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip type partition plate 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air duct is 2.
Fig. 2 shows a schematic perspective structural view of the rotary thermal separator of the present embodiment. Referring to fig. 2, the rotary thermal separator of the present embodiment includes a casing 6, a first end cap 7, a second end cap 8, a first nozzle 9, a second nozzle 10, and a central shaft 11, in addition to the wave rotor 5;
wherein, both ends of the casing 6 are open, and the first end cover 7 and the second end cover 8 are respectively buckled at both ends of the casing 6;
the central shaft 11 is coaxially arranged with the casing 6 and axially and fixedly connected, a first end of the central shaft 11 penetrates through the first end cover 7 and then extends into the casing 6, and a second end of the central shaft 11 is exposed out of the first end cover 7;
the wave rotor 5 is arranged in the machine shell 6 and can synchronously rotate with the central shaft 11;
the first nozzle 9 and the second nozzle 10 are fixedly arranged in the machine shell 6 and are respectively positioned at two ends of the wave rotor 5;
the first nozzle 9 and the second nozzle 10 are both circular ring type nozzles.
Fig. 3 shows a schematic structural view of the first nozzle 9 of the present embodiment. Referring to fig. 3, the first nozzle 9 of the present embodiment includes a first substrate 91 having a circular ring shape, and a first high-temperature gas outlet 92, a second high-temperature gas outlet 93, a first low-pressure gas inlet 94, and a second low-pressure gas inlet 95 that are disposed on the first substrate 91, where the first high-temperature gas outlet 92, the second high-temperature gas outlet 93, the first low-pressure gas inlet 94, and the second low-pressure gas inlet 95 are all stacked structures that match with stacked ring cavities.
Fig. 4 shows a schematic structural view of the second nozzle 10 of the present embodiment. Referring to fig. 4, the second nozzle 10 of the present embodiment includes a second substrate 101 having a circular ring shape, and a first high-pressure gas inlet 102, a second high-pressure gas inlet 103, a first low-temperature gas outlet 104, and a second low-temperature gas outlet 105 disposed on the second substrate 101, wherein the first high-pressure gas inlet 102, the second high-pressure gas inlet 103, the first low-temperature gas outlet 104, and the second low-temperature gas outlet 105 are all stacked structures matching with the stacked ring cavities.
A high-temperature gas discharge chamber 71 and a low-pressure gas inlet chamber 72 are arranged in the first end cover 7, and a low-temperature gas discharge chamber 81 and a high-pressure gas inlet chamber 82 are arranged in the second end cover 8;
the high-temperature gas discharge chamber 71 of the first end cap 7 is simultaneously communicated with the first high-temperature gas outlet 92 and the second high-temperature gas outlet 93 of the first nozzle 9, and the low-pressure gas inlet chamber 72 of the first end cap 7 is simultaneously communicated with the first low-pressure gas inlet 94 and the second low-pressure gas inlet 95 of the first nozzle 9;
the low-temperature gas discharge chamber 81 of the second end cap 8 is simultaneously communicated with the first low-temperature gas outlet 104 and the second low-temperature gas outlet 105 of the second nozzle 10, and the high-pressure gas inlet chamber 82 of the second end cap 8 is simultaneously communicated with the first high-pressure gas inlet 102 and the second high-pressure gas inlet 103 of the second nozzle 10.
In this embodiment, the first end cap 7 is further provided with a high-temperature gas outlet communicated with the high-temperature gas discharge chamber 71, and a low-pressure gas inlet communicated with the low-pressure gas inlet chamber 72; the second end cap 8 is further provided with a low-temperature gas outlet communicated with the low-temperature gas discharge chamber 81, and a high-pressure gas inlet communicated with the high-pressure gas inlet chamber 82.
High-pressure gas enters the channel of the wave rotor 5 through the high-pressure gas inlet, the high-pressure gas inlet cavity 82 and the second nozzle 10 in sequence, the heat exchange refrigeration process is completed through the matching of the wave system, and then high-temperature gas is discharged through the first nozzle 9, the high-temperature gas discharge cavity 71 and the high-temperature gas outlet. The low-pressure gas enters the channel of the wave rotor 5 through the low-pressure gas inlet, the low-pressure gas inlet cavity 72 and the second nozzle 10 in sequence, and the low-temperature gas is discharged through the first nozzle 9, the low-temperature gas discharge cavity 81 and the low-temperature gas outlet.
By adopting the technical scheme, in the running process of the equipment, the ideal flow process matching is completed by utilizing the multilayer channel rotor, on one hand, aiming at the operation working condition of high pressure ratio, the multistage heat exchange equipment can be integrated into one equipment, and the investment cost is reduced. And on the other side, due to the existence of a plurality of layers of channels, a part of the channels can be set as a precooling layer and a heat-insulating layer, and the temperature in the channels is controlled to be a lower value by setting the boundary conditions of the fluid, so that the energy dissipation to the outside in the heat exchange process of the channels is reduced, and the operation efficiency of the equipment is improved.
The different gas of multiple pressure gets into the multilayer ring chamber in the equipment from the different entry in top and bottom respectively, gets into corresponding certain one deck passageway through the nozzle in, utilizes the rotatory and cooperation of nozzle position of passageway, can realize different wave system structures in the passageway, accomplishes the energy separation to gas temperature between layer can satisfy the process that cold and hot intersection can not appear through the design, avoids promptly because the temperature transfer between layer leads to the efficiency reduction of equipment. And if part of the channels are fully filled with low-temperature gas, precooling of the working channel can be realized, heat preservation can be realized in the operation process of the equipment, and a large amount of heat exchange between the low-temperature gas generated by heat separation and the surrounding environment is reduced, so that energy loss is reduced, and the performance of the equipment is improved.
Example 3: fig. 1 is a schematic structural diagram illustrating a wave rotor included in a rotary thermal separator according to this embodiment, and referring to fig. 1, the wave rotor included in the rotary thermal separator according to this embodiment includes a rotor inner cylinder 1 and a rotor outer cylinder 2, both ends of the rotor inner cylinder 1 and the rotor outer cylinder 2 are open, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially and fixedly arranged;
two layers of annular cavities are arranged between the rotor inner cylinder 1 and the rotor outer cylinder 2 along the radial direction of the rotor inner cylinder 1;
and a plurality of oscillating air passages arranged along the axial full length of the ring cavity on the layer are arranged in each ring cavity, and the oscillating air passages in the same ring cavity are distributed along the circumferential direction of the ring cavity on the layer.
The wave rotor of the embodiment also comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides a gap between the rotor inner cylinder 1 and the rotor outer cylinder 2 into two layers of annular cavities.
A plurality of strip type partition plates 4 are arranged in each layer of annular cavity, and the strip type partition plates 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The width and the height of a plurality of oscillating air passages in the same layer of annular cavity are equal;
the width of the oscillating air passage is the distance between the two strip type partition plates 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip type partition plate 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air duct is 2.
Fig. 2 shows a schematic perspective structural view of the rotary thermal separator of the present embodiment. Referring to fig. 2, the rotary thermal separator of the present embodiment includes a casing 6, a first end cap 7, a second end cap 8, a first nozzle 9, a second nozzle 10, and a central shaft 11, in addition to the wave rotor 5;
wherein, both ends of the casing 6 are open, and the first end cover 7 and the second end cover 8 are respectively buckled at both ends of the casing 6;
the central shaft 11 is coaxially arranged with the casing 6 and axially and fixedly connected, a first end of the central shaft 11 penetrates through the first end cover 7 and then extends into the casing 6, and a second end of the central shaft 11 is exposed out of the first end cover 7;
the wave rotor 5 is arranged in the machine shell 6 and can synchronously rotate with the central shaft 11;
the first nozzle 9 and the second nozzle 10 are fixedly arranged in the machine shell 6 and are respectively positioned at two ends of the wave rotor 5;
the first nozzle 9 and the second nozzle 10 are both circular ring type nozzles.
Fig. 3 shows a schematic structural view of the first nozzle 9 of the present embodiment. Referring to fig. 3, the first nozzle 9 of the present embodiment includes a first substrate 91 having a circular ring shape, and a first high-temperature gas outlet 92, a second high-temperature gas outlet 93, a first low-pressure gas inlet 94, and a second low-pressure gas inlet 95 that are disposed on the first substrate 91, where the first high-temperature gas outlet 92, the second high-temperature gas outlet 93, the first low-pressure gas inlet 94, and the second low-pressure gas inlet 95 are all stacked structures that match with stacked ring cavities.
Fig. 4 shows a schematic structural view of the second nozzle 10 of the present embodiment. Referring to fig. 4, the second nozzle 10 of the present embodiment includes a second substrate 101 having a circular ring shape, and a first high-pressure gas inlet 102, a second high-pressure gas inlet 103, a first low-temperature gas outlet 104, and a second low-temperature gas outlet 105 disposed on the second substrate 101, wherein the first high-pressure gas inlet 102, the second high-pressure gas inlet 103, the first low-temperature gas outlet 104, and the second low-temperature gas outlet 105 are all stacked structures matching with the stacked ring cavities.
A high-temperature gas discharge chamber 71 and a low-pressure gas inlet chamber 72 are arranged in the first end cover 7, and a low-temperature gas discharge chamber 81 and a high-pressure gas inlet chamber 82 are arranged in the second end cover 8;
the high-temperature gas discharge chamber 71 of the first end cap 7 is simultaneously communicated with the first high-temperature gas outlet 92 and the second high-temperature gas outlet 93 of the first nozzle 9, and the low-pressure gas inlet chamber 72 of the first end cap 7 is simultaneously communicated with the first low-pressure gas inlet 94 and the second low-pressure gas inlet 95 of the first nozzle 9;
the low-temperature gas discharge chamber 81 of the second end cap 8 is simultaneously communicated with the first low-temperature gas outlet 104 and the second low-temperature gas outlet 105 of the second nozzle 10, and the high-pressure gas inlet chamber 82 of the second end cap 8 is simultaneously communicated with the first high-pressure gas inlet 102 and the second high-pressure gas inlet 103 of the second nozzle 10.
The rotary thermal separator of the embodiment further comprises a rotor inner sleeve 12, wherein the rotor inner sleeve 12 is arranged between the central shaft 11 and the wave rotor 5, and the wave rotor 5 is linked with the central shaft 11 through the rotor inner sleeve 12.
The rotary thermal separator of the embodiment further comprises a motor and a coupling;
the rotating shaft of the motor is in transmission connection with the central shaft 11 through a coupler.
In order to meet the air injection requirements of different layers of channels of the rotor, a separate air inlet and an air outlet need to be designed for each layer of channel, so that a plurality of layers of nozzles need to be designed on the upper side and the lower side of the rotor respectively, the relative position of each layer of nozzles changes due to different states of air flow in the channels, but during the overall design, the deviation is ensured to be not too large as much as possible, and the processing difficulty is reduced.
The rotary thermal separator of the embodiment changes the original single-layer channel into a multi-layer channel by improving the structure of the inner core component, namely the wave rotor. Utilize the ripples rotor of multilayer channel structure, can be so that accomplish a plurality of heat transfer processes among a ripples rotor, under the condition of big compression ratio promptly, integrate equipment utilization ratio in with the multistage heat transfer originally. Meanwhile, in the multi-layer channels of the wave rotor, heat preservation and precooling between layers can be realized by adjusting the pressure ratio between the channels of different layers, so that the heat exchange efficiency of the equipment is obviously improved, and the dissipation of heat and cold is reduced. Therefore, the rotary heat separator has the advantages of good energy transfer efficiency, small dissipation loss and wide market prospect.
Having described embodiments of the present invention, the foregoing description is intended to be exemplary, not exhaustive, and not limited to the embodiments disclosed. Many modifications and variations will be apparent to those of ordinary skill in the art without departing from the scope and spirit of the described embodiments.
Claims (10)
1. The wave rotor is characterized by comprising a rotor inner cylinder and a rotor outer cylinder, wherein the rotor inner cylinder and the rotor outer cylinder are both cylinders with two open ends, and the rotor inner cylinder and the rotor outer cylinder are coaxially and fixedly arranged;
at least two layers of annular cavities are arranged between the rotor inner cylinder and the rotor outer cylinder along the radial direction of the rotor inner cylinder;
and a plurality of oscillating air passages arranged along the axial full length of the ring cavity on the layer are arranged in each ring cavity, and the oscillating air passages in the same ring cavity are distributed along the circumferential direction of the ring cavity on the layer.
2. The wave rotor of claim 1 further comprising a plurality of telescoping baffles dividing a gap between the rotor inner and outer barrels into at least two annular chambers.
3. The wave rotor of claim 1 in which a plurality of bar-type partitions are disposed within each layer of the annulus, the bar-type partitions dividing the layer of the annulus into a plurality of oscillating gas passages.
4. The wave rotor according to claim 1, characterized in that the number of layers of the ring cavity is m, 2 ≦ m ≦ 10.
5. The wave rotor of claim 3 in which the oscillating air passages in the same layer of ring cavity are all equal in width and height;
the width of the oscillating air passage is the distance between the two strip type partition plates corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip type partition plate corresponding to the oscillating air passage.
6. The wave rotor of claim 5 in which the ratio of the height to width of the oscillating gas duct is n, 0.2< n < 5.
7. A rotary thermal separator, comprising a wave rotor according to any of claims 1-6.
8. The rotary thermal separator according to claim 7, further comprising a housing, a first end cap, a second end cap, a first nozzle, a second nozzle, and a central shaft;
the two ends of the shell are both opened, and the first end cover and the second end cover are buckled at the two ends of the shell respectively;
the central shaft and the shell are coaxially arranged and are axially and fixedly connected, a first end of the central shaft penetrates through the first end cover and then extends into the shell, and a second end of the central shaft is exposed out of the first end cover;
the wave rotor is arranged in the shell and can synchronously rotate with the central shaft;
the first nozzle and the second nozzle are fixedly arranged in the shell and are respectively positioned at two ends of the wave rotor;
the disc type nozzle comprises a circular base plate, an air inlet and an air outlet which are arranged on the base plate, and the air inlet and the air outlet are both of a laminated structure matched with the laminated ring cavities;
a high-temperature gas discharge cavity and a low-pressure gas inlet cavity are arranged in the first end cover, and a low-temperature gas discharge cavity and a high-pressure gas inlet cavity are arranged in the second end cover;
the high-temperature gas discharge cavity is communicated with the exhaust port of the first nozzle, the low-pressure gas inlet cavity is communicated with the gas inlet of the first nozzle, the low-temperature gas discharge cavity is communicated with the exhaust port of the second nozzle, and the high-pressure gas inlet cavity is communicated with the gas inlet of the second nozzle.
9. The rotary thermal separator according to claim 8, further comprising a rotor inner sleeve disposed between said central shaft and said wave rotor, said wave rotor being in linkage with said central shaft through said rotor inner sleeve.
10. The rotary thermal separator according to claim 8, further comprising an electric motor and a coupling;
and a rotating shaft of the motor is in transmission connection with the central shaft through the coupler.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011042401.5A CN114427756B (en) | 2020-09-28 | 2020-09-28 | Wave rotor and rotary heat separator |
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| CN114427756B (en) | 2024-02-23 |
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