CN114427756B - Wave rotor and rotary heat separator - Google Patents
Wave rotor and rotary heat separator Download PDFInfo
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- CN114427756B CN114427756B CN202011042401.5A CN202011042401A CN114427756B CN 114427756 B CN114427756 B CN 114427756B CN 202011042401 A CN202011042401 A CN 202011042401A CN 114427756 B CN114427756 B CN 114427756B
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- 239000000758 substrate Substances 0.000 claims description 12
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 230000005540 biological transmission Effects 0.000 claims description 3
- 230000008878 coupling Effects 0.000 claims description 2
- 238000010168 coupling process Methods 0.000 claims description 2
- 238000005859 coupling reaction Methods 0.000 claims description 2
- 239000010410 layer Substances 0.000 abstract description 68
- 239000002356 single layer Substances 0.000 abstract description 7
- 239000007789 gas Substances 0.000 description 114
- 238000005192 partition Methods 0.000 description 23
- 238000000034 method Methods 0.000 description 11
- 230000008569 process Effects 0.000 description 11
- 238000005057 refrigeration Methods 0.000 description 7
- 230000006835 compression Effects 0.000 description 5
- 238000007906 compression Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 5
- 230000010355 oscillation Effects 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 3
- 238000004321 preservation Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000006837 decompression Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 241000521257 Hydrops Species 0.000 description 1
- 206010030113 Oedema Diseases 0.000 description 1
- 239000000306 component Substances 0.000 description 1
- 239000008358 core component Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Classifications
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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 heat separator. The wave rotor comprises a rotor inner cylinder and a rotor outer cylinder, wherein the rotor inner cylinder and the rotor outer cylinder are both open-ended cylinders, 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, a plurality of oscillating air passages which are arranged along the axial through length of each layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of each layer of annular cavity. The rotary heat separator comprises the wave rotor. According to the invention, the problem of low system efficiency of the existing multistage heat separator adopting the single-layer channel wave rotor can be effectively solved.
Description
Technical Field
The invention belongs to the technical field of gas jet flow, and particularly relates to a wave rotor and a rotary heat separator.
Background
The rotary heat separator is one kind of refrigerating equipment with near isentropic decompression and consists of mainly nozzle, wave rotor and rotary distributor. The high-energy gas is sprayed into the oscillating tube of the wave rotor through the nozzle, the existing gas in the oscillating tube is compressed to raise the temperature, and the temperature rise can be up to about 500 ℃. The heat generated by compression is transferred from the outer surface of the oscillating tube by natural convection or forced convection. The injection of gas is intermittent due to the rotary distributor mounted on the machine. When the gas in the oscillating tube is compressed and heated, the air inlet is stopped, the gas in the oscillating tube changes the flow direction, and the air is subjected to adiabatic expansion and decompression, so that the power gas in the air is cooled and discharged, and the heat separator completes 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 motive gas can be reduced to-30 to-90 ℃. The refrigeration degree is related to the pressure drop of the inlet and outlet air and the gas composition.
The wave rotor is the most important component of the rotary heat separator, the rotary heat separator utilizes the high-speed rotation of the wave rotor to realize the matching of compression wave and expansion wave in the oscillating tube of the wave rotor, and the energy exchange between gases with different pressures is completed, thereby realizing the refrigeration effect.
Existing heat separators can be divided into single-stage and multi-stage separators.
When the pressure ratio is too large, the speed of the air flow reaches a sonic or supersonic state, and the energy separation in the single-stage heat separator is influenced, namely the cold-hot separation effect is inhibited. Therefore, the expansion ratio of the existing single-stage heat separator is generally between 2 and 4. In order to meet the refrigeration requirement under the working condition of large pressure ratio, a mode of connecting a plurality of single-stage heat separators in series is generally adopted to meet the target requirement. However, in this manner, the expansion ratio of each single-stage heat separator can be controlled within a reasonable range, but the pressure energy of the gas is not effectively recovered. In addition, the mode of connecting a plurality of single-stage heat separators in series is easy to cause the problem of lower overall efficiency of the system due to poor matching degree among the heat separators at each stage.
For this reason, multi-stage heat separators are increasingly being used for refrigeration under high pressure ratio conditions. The existing multi-stage heat separator mainly comprises two types: an oscillating tube with one end open type multi-stage heat separator and a single-layer channel wave rotor type multi-stage heat separator. The multistage heat separator with one end open of the oscillating tube can realize multistage refrigeration under a large pressure ratio, but the phenomenon of oscillation tube hydrops can occur in the working process, and the oscillating tube is broken when serious. In addition, the oscillating tube with one end open type multistage heat separator has the problems of larger whole machine volume and slower heat dissipation. The single-layer channel wave rotor type multi-stage heat separator solves the problems of the oscillating tube with one end open type multi-stage heat separator, but the wave rotor with a single-layer channel structure is used, so that the gas between channels cannot realize sufficient heat exchange, the energy dissipation is serious, and the working efficiency of the whole machine is further affected.
Disclosure of Invention
The invention aims to solve the problem of low system efficiency of the existing multi-stage heat 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 heat 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;
a plurality of oscillating air passages which are arranged along the axial through length of the layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of the layer of annular cavity;
all the vibration air passages correspond to the corresponding air inlets and air outlets on the nozzles of the rotary heat separator respectively.
Preferably, the wave rotor further comprises a plurality of sleeve type partition plates, and the sleeve type partition plates divide a 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 divide the layer of annular cavity into a plurality of oscillating air passages.
Preferably, the number of layers of the annular cavity is m, and m is more than or equal to 2 and less than or equal to 10.
Preferably, the multiple oscillation air passages in the same layer of annular cavity have the same width and the same height;
the width of the oscillating air passage is the distance between the two strip-type clapboards corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip-type clapboards corresponding to the oscillating air passage.
Preferably, the ratio of the height to the width of the oscillating air passage is n,0.2< n <5.
According to a second aspect of the present invention there is provided a rotary heat separator comprising any one of the wave rotors described above.
Preferably, the rotary heat separator further comprises a casing, a first end cover, a second end cover, a first nozzle, a second nozzle and a central shaft;
both ends of the shell are opened, and the first end cover and the second end cover are respectively buckled at both ends of the shell;
the central shaft is coaxially arranged with the shell and is axially fixedly connected with the shell, a first end of the central shaft extends into the shell after penetrating through the first end cover, 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 first nozzle and the second nozzle are annular nozzles, the annular nozzles comprise annular substrates, and an air inlet and an air outlet which are arranged on the substrates, and the air inlet and the air outlet are of laminated structures matched with laminated annular 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 air 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 air inlet of the second nozzle.
Preferably, the rotary heat separator further comprises a rotor inner sleeve, wherein 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 heat separator further comprises an electric motor and a coupling;
the 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 of the invention is provided with at least two layers of annular cavities between the rotor inner cylinder and the rotor outer cylinder, and a plurality of oscillation air passages equivalent to oscillation tubes are arranged in each layer of annular cavity. From this, the wave rotor of the present invention has a multilayer channel structure. The wave rotor with the multi-layer channel structure can realize a plurality of heat exchange processes, namely, multistage refrigeration under the working condition of large compression ratio. Because the wave rotor provided by the invention is provided with the multi-layer channels, the wave rotor can be independently designed aiming at part of the channels, so that the channels are filled with low-temperature gas or high-temperature gas, and further, the pre-cooling and heat preservation of the channels on the adjacent layers are realized, thereby improving the cold-hot separation efficiency of the target channels, reducing the energy dissipation and improving the efficiency of the corresponding heat separator.
The invention also provides a heat 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 foregoing and other objects, features and advantages of the invention will be apparent from the following more particular descriptions of exemplary embodiments of the invention as illustrated in the accompanying drawings wherein like reference numbers generally represent like parts throughout the exemplary embodiments of the invention.
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 view of the structure of the rotary heat 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 preferred embodiments of the present invention are described below, it should be understood that the present invention may be embodied in various forms and should not be limited to 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 diagram 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 of the rotor inner cylinder 1 and the rotor outer cylinder 2 are open-ended cylinders, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially fixed;
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 which are arranged along the axial through length of the layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of the layer of annular cavity.
The wave rotor of the embodiment further comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides the 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 boards 4 are arranged in each layer of annular cavity, and the plurality of strip-type partition boards 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The widths and the heights 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 boards 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip-type partition boards 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air passage is 2.
In this embodiment, the annular cavity is the internal channel of the wave rotor. In the embodiment, the internal channels of the wave rotor are arranged in two layers, the two layers of channels are arranged at intervals through the sleeve type partition plates 3, a plurality of oscillating air passages are arranged in each layer of channels at intervals through the plurality of strip type partition plates 4, and compression waves and expansion waves are matched in the oscillating air passages.
In engineering practice, the number of layers of the channels of the wave rotor can be adjusted according to the actual pressure ratio requirement, and the adjustment range is 2 layers to 10 layers. Because when the internal channels of the wave rotor are too many, it is difficult to achieve normal flow of gas in the channels, and the matching difficulty of temperature is remarkably increased, heat exchange becomes more complicated, design difficulty is improved, 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 air flow and the actual size of the wave rotor, but the aspect ratio should be generally between 0.2 and 5. Since an oscillating gas channel with an excessively large aspect ratio increases the flow loss of gas, the system efficiency is reduced.
Example 2: fig. 1 shows a schematic structural diagram of a wave rotor included in a rotary heat separator according to the present embodiment, and referring to fig. 1, the wave rotor included in the rotary heat separator according to the present embodiment includes a rotor inner cylinder 1 and a rotor outer cylinder 2, both of which are open-ended cylinders, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially fixed;
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 which are arranged along the axial through length of the layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of the layer of annular cavity.
The wave rotor of the embodiment further comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides the 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 boards 4 are arranged in each layer of annular cavity, and the plurality of strip-type partition boards 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The widths and the heights 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 boards 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip-type partition boards 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air passage is 2.
Fig. 2 shows a schematic perspective view of the structure of the rotary heat separator of the present embodiment. Referring to fig. 2, the rotary heat separator of the present embodiment includes a casing 6, a first end cover 7, a second end cover 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 opened, 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 shell 6 and is axially fixedly connected, a first end of the central shaft 11 extends into the shell 6 after penetrating through the first end cover 7, 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 shell 6 and can rotate synchronously with the central shaft 11;
the first nozzle 9 and the second nozzle 10 are fixedly arranged in the casing 6 and are respectively positioned at two ends of the wave rotor 5;
the first nozzle 9 and the second nozzle 10 are both annular 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 circular ring-shaped first substrate 91, 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 provided on the first substrate 91, 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 being stacked structures matching the stacked annular chambers.
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 circular ring-shaped second substrate 101, 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 provided on the second substrate 101, each of 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 being a laminated structure matching with a laminated annular cavity.
A high-temperature gas discharge chamber 71 and a low-pressure gas inlet chamber 72 are provided in the first end cover 7, and a low-temperature gas discharge chamber 81 and a high-pressure gas inlet chamber 82 are provided in the second end cover 8;
the high temperature gas discharge chamber 71 of the first end cap 7 communicates with both 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 communicates with both 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 communicates with both 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 communicates with both 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 cover 7 is further provided with a high-temperature gas outlet communicating with the high-temperature gas discharge chamber 71, and a low-pressure gas inlet communicating with the low-pressure gas inlet chamber 72; the second end cap 8 is further provided with a low temperature gas outlet communicating with the low temperature gas discharge chamber 81 and a high pressure gas inlet communicating with the high pressure gas inlet chamber 82.
The high-pressure gas sequentially 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, the heat exchange refrigeration process is completed through the matching of wave systems, and then the 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 sequentially enters the channels of the wave rotor 5 through the low-pressure gas inlet, the low-pressure gas inlet cavity 72 and the second nozzle 10, 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 multi-layer channel rotor, and on one hand, the multi-stage heat exchange equipment can be integrated into one piece of equipment aiming at the operating condition of a large pressure ratio, so that the input cost is reduced. And the other side can be provided with a pre-cooling layer and a heat-insulating layer due to the existence of the multi-layer channels, 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 channel heat exchange process is reduced, and the operation efficiency of the equipment is improved.
The gas with different pressures respectively enters the multilayer annular cavity in the equipment from different inlets at the top and the bottom, enters a certain layer of corresponding channels through the nozzles, and can realize different wave system structures in the channels by utilizing the rotation of the channels and the matching of the positions of the nozzles so as to finish energy separation, and the gas temperature between the layers can meet the process that cold and hot junction cannot occur through design, namely the efficiency reduction of the equipment caused by the temperature transfer between the layers is avoided. And if the working channel is fully filled with low-temperature gas by utilizing part of the channels, the working channel can be pre-cooled, heat preservation can be realized in the running 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 the energy loss is reduced, and the equipment performance is improved.
Example 3: fig. 1 shows a schematic structural diagram of a wave rotor included in a rotary heat separator according to the present embodiment, and referring to fig. 1, the wave rotor included in the rotary heat separator according to the present embodiment includes a rotor inner cylinder 1 and a rotor outer cylinder 2, both of which are open-ended cylinders, and the rotor inner cylinder 1 and the rotor outer cylinder 2 are coaxially fixed;
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 which are arranged along the axial through length of the layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of the layer of annular cavity.
The wave rotor of the embodiment further comprises a sleeve type partition plate 3, and the sleeve type partition plate 3 divides the 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 boards 4 are arranged in each layer of annular cavity, and the plurality of strip-type partition boards 4 divide the layer of annular cavity into a plurality of oscillating air passages.
The widths and the heights 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 boards 4 corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip-type partition boards 4 corresponding to the oscillating air passage.
In this embodiment, the ratio of the height to the width of the oscillating air passage is 2.
Fig. 2 shows a schematic perspective view of the structure of the rotary heat separator of the present embodiment. Referring to fig. 2, the rotary heat separator of the present embodiment includes a casing 6, a first end cover 7, a second end cover 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 opened, 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 shell 6 and is axially fixedly connected, a first end of the central shaft 11 extends into the shell 6 after penetrating through the first end cover 7, 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 shell 6 and can rotate synchronously with the central shaft 11;
the first nozzle 9 and the second nozzle 10 are fixedly arranged in the casing 6 and are respectively positioned at two ends of the wave rotor 5;
the first nozzle 9 and the second nozzle 10 are both annular 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 circular ring-shaped first substrate 91, 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 provided on the first substrate 91, 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 being stacked structures matching the stacked annular chambers.
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 circular ring-shaped second substrate 101, 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 provided on the second substrate 101, each of 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 being a laminated structure matching with a laminated annular cavity.
A high-temperature gas discharge chamber 71 and a low-pressure gas inlet chamber 72 are provided in the first end cover 7, and a low-temperature gas discharge chamber 81 and a high-pressure gas inlet chamber 82 are provided in the second end cover 8;
the high temperature gas discharge chamber 71 of the first end cap 7 communicates with both 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 communicates with both 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 communicates with both 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 communicates with both the first high pressure gas inlet 102 and the second high pressure gas inlet 103 of the second nozzle 10.
The rotary heat separator of the present embodiment further includes a rotor inner sleeve 12, the rotor inner sleeve 12 is disposed 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 heat separator of the embodiment also comprises a motor and a coupler;
the rotating shaft of the motor is connected with the central shaft 11 in a transmission way through a coupler.
In order to meet the air injection requirements of different layers of channels of the rotor, independent air inlet and air outlet are required to be designed for each layer of channels, multiple layers of nozzles are required to be respectively designed on the upper side and the lower side of the rotor, the relative position of each layer of nozzles can be changed due to different air flow states in the channels, and when the overall design is carried out, the deviation of the nozzles should be ensured not to be too large as much as possible, so that the processing difficulty is reduced.
The rotary heat separator of the embodiment changes the original single-layer channel into a multi-layer channel by improving the structure of an inner core component, namely, a wave rotor. By utilizing the wave rotor with the multi-layer channel structure, a plurality of heat exchange processes can be completed in one wave rotor, namely, under the condition of large compression ratio, the original multi-stage heat exchange is integrated into one device, and the device utilization rate is improved. Meanwhile, in the multilayer 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 heat and cold dissipation is reduced. Therefore, the rotary heat separator of the embodiment has good energy transfer efficiency, small dissipation loss and very broad market prospect.
The foregoing description of embodiments of the invention has been presented for purposes of illustration and description, and is not intended to be exhaustive or 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 various embodiments described.
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 open-ended cylinders, 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;
a plurality of oscillating air passages which are arranged along the axial through length of the layer of annular cavity are arranged in each layer of annular cavity, and a plurality of oscillating air passages in the same layer of annular cavity are distributed along the circumferential direction of the layer of annular cavity;
all the oscillating air passages correspond to the corresponding air inlets and air outlets on the nozzles of the rotary heat separator respectively.
2. The wave rotor of claim 1, further comprising a plurality of sleeve-type baffles dividing the gap between the rotor inner and outer cylinders into at least two layers of annular cavities.
3. The wave rotor of claim 1, wherein a plurality of strip-type baffles are disposed within each layer of the annular chamber, the plurality of strip-type baffles dividing the layer of the annular chamber into a plurality of oscillating air passages.
4. The wave rotor of claim 1, wherein the number of layers of the annular cavity is m, 2.ltoreq.m.ltoreq.10.
5. A wave rotor according to claim 3, characterized in that the plurality of oscillating air passages in the same layer of annular cavity are all equal in width and height;
the width of the oscillating air passage is the distance between the two strip-type clapboards corresponding to the oscillating air passage, and the height of the oscillating air passage is the width of the strip-type clapboards corresponding to the oscillating air passage.
6. The wave rotor of claim 5, wherein the ratio of the height to the width of the oscillating air channel is n,0.2< n <5.
7. A rotary heat separator comprising the wave rotor of any one of claims 1-6.
8. The rotary heat 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;
both ends of the shell are opened, and the first end cover and the second end cover are respectively buckled at both ends of the shell;
the central shaft is coaxially arranged with the shell and is axially fixedly connected with the shell, a first end of the central shaft extends into the shell after penetrating through the first end cover, 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 first nozzle and the second nozzle are annular nozzles, the annular nozzles comprise annular substrates, and an air inlet and an air outlet which are arranged on the substrates, and the air inlet and the air outlet are of laminated structures matched with laminated annular 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 air 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 air inlet of the second nozzle.
9. The rotary heat separator according to claim 8 further comprising a rotor inner sleeve disposed between said central shaft and said wave rotor, said wave rotor being coupled to said central shaft by said rotor inner sleeve.
10. The rotary heat separator according to claim 8 further comprising an electric motor and a coupling;
the rotating shaft of the motor is in transmission connection with the central shaft through the coupler.
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| CN114427756A (en) | 2022-05-03 |
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