CN210861773U - Compressed air heat exchange system - Google Patents
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- CN210861773U CN210861773U CN201922091780.6U CN201922091780U CN210861773U CN 210861773 U CN210861773 U CN 210861773U CN 201922091780 U CN201922091780 U CN 201922091780U CN 210861773 U CN210861773 U CN 210861773U
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Abstract
The utility model provides a compressed air heat transfer system, include: the air cooling flow path is provided with a first compressor, a second compressor and an expander, the first compressor and the second compressor are used for heating and boosting the air flowing through the air cooling flow path, the expander is used for cooling and depressurizing the air flowing through the air cooling flow path, and an inlet and an outlet of the air cooling flow path respectively form an air return opening and an air outlet of the compressed air heat exchange system; the expander is coaxially connected with the second compressor through a connecting shaft, and an air inlet of the second compressor is communicated with an air outlet of the first compressor. Because the air is used as the refrigerant, the method is safe and pollution-free, does not cause harm to the environment, and is also favorable for reducing the production cost and the later maintenance cost. And the expansion ratio and enthalpy drop of the expansion machine can be improved by double-stage compression, so that the working capacity of the expansion machine is improved, the unit refrigerating capacity is increased, and the heating capacity of the system is also improved.
Description
Technical Field
The utility model relates to an air conditioning equipment technical field particularly, relates to a compressed air heat transfer system.
Background
In the related art, many refrigeration apparatuses such as air conditioners use the latent heat of phase change of a refrigerant to transfer heat to a room to perform heating or to transfer heat from the room to perform cooling. However, most refrigerants (e.g., freon) are environmentally hazardous, such as greenhouse effect, ozone layer depletion, etc.
SUMMERY OF THE UTILITY MODEL
In order to solve at least one of the above technical problems, an object of the present invention is to provide a compressed air heat exchange system.
In order to achieve the above object, the utility model provides a compressed air heat transfer system, include: the air cooling flow path is provided with a first compressor, a second compressor and an expander, the first compressor and the second compressor are used for heating and boosting the air flowing through the air cooling flow path, the expander is used for cooling and depressurizing the air flowing through the air cooling flow path, and an inlet and an outlet of the air cooling flow path respectively form an air return opening and an air outlet of the compressed air heat exchange system; the expander is coaxially connected with the second compressor through a connecting shaft, and an air inlet of the second compressor is communicated with an air outlet of the first compressor.
The utility model provides a compressed air heat transfer system utilizes the air as the refrigerant, and the cooperation of stepping up and the cooling step-down of expander is stepped up in the intensification of process compressor, accomplishes the refrigeration or the heating that use the carrier to rooms etc.. Because the compressed air heat exchange system uses air as the refrigerant, the compressed air heat exchange system is safe and pollution-free, does not cause harm to the environment, saves the cost caused by the traditional refrigerants such as Freon and the like, does not need to supplement the refrigerant regularly, and is favorable for reducing the production cost and the later maintenance cost.
Meanwhile, the air outlet of the first compressor is communicated with the air inlet of the second compressor, so that the air compressed by the first compressor enters the second compressor to be compressed again, and the air flowing through the air refrigeration flow path is subjected to double-stage compression. The expansion ratio and enthalpy drop of the expander can be improved by double-stage compression, so that the working capacity of the expander is improved, and the unit refrigerating capacity is increased. Compared with single-stage compression, the double-stage compression has better energy efficiency, and the heating capacity of a compressed air heat exchange system is also improved.
And compared with the traditional liquid refrigerant, the air refrigerant can reduce the system pressure (less than 3bar), so that the system is more reliable in operation and longer in service life. The air return inlet of the compressed air heat exchange system is directly communicated with the used carrier, so that a heat exchanger on the inner side of the traditional air conditioner room is omitted, the air supply outlet of the room can be designed into other forms according to the needs of a user, and the decoration style of the room is better met.
In addition, the expander is coaxially connected with the second compressor through the connecting shaft, so that the second compressor can recover expansion work of the expander, namely the expansion work of the expander can be used as a power source of the second compressor, and the energy efficiency of the system is further improved.
Moreover, the inlet and the outlet of the air refrigeration flow path respectively form an air return port and an air outlet of the compressed air heat exchange system, and the air outlet and the air return port are channels for air flow exchange between the compressed air heat exchange system and a carrier (such as a room). Therefore, the air in the air refrigeration flow path directly absorbs the air in the using carrier (such as a room) through the air return opening, the air is sent into the using carrier through the air outlet after being refrigerated and heated, and the using carrier is cooled, and the circulation is carried out, so that the air in the air refrigeration flow path only carries out air flow exchange with the air in the using carrier, but not carries out air flow exchange with the external atmosphere (namely, the atmosphere environment outside the using carrier), and the closed circulation is achieved. The closed circulation pipeline layout is relatively simple, the product structure is favorably simplified, the requirement of a compressed air heat exchange system on the installation environment can be reduced, and the influence of the change of the external atmospheric environment is not easily caused.
Additionally, the utility model provides a compressed air heat transfer system among the above-mentioned technical scheme can also have following additional technical characteristics:
in the above technical solution, the compressed air heat exchange system further includes: and the driving motor is coaxially connected with the connecting shaft and is used for assisting the expander to drive the second compressor.
The driving motor is used for assisting the expander to drive the second compressor, so that the second compressor can have two working modes. Specifically, when the expansion work output by the expander can meet the power consumption of the second compressor, the driving motor does not need to work, and the expander directly drives the second compressor; when the expansion work output by the expander is not enough to meet the power consumption of the second compressor, the driving motor outputs mechanical energy to drive the second compressor together with the expander, so that the rotating speed of the turbine is increased, and the temperature drop of the turbine and the refrigerating capacity of the system are increased. Specifically, the drive motor is a high-speed motor.
In the above technical solution, the expander and the second compressor are power-matched to drive the second compressor separately.
The expansion machine is matched with the second compressor in an equal power mode, the expansion work output by the expansion machine can meet the power consumption requirement of the second compressor, a driving motor does not need to be additionally configured, self-sufficiency is achieved, the product structure is simplified, and the product cost is reduced. It will be appreciated that the expander normally provided for a single stage compression is not sufficient to drive the compressor to which it is coaxially connected, and a high speed motor is required to assist in the drive. In the application, the first compressor is additionally arranged, so that the energy consumption of the second compressor which is coaxially connected with the expander can be reduced, and the expander which is coaxially connected with the second compressor can sufficiently drive the second compressor, so that a high-speed motor is omitted.
In the above technical scheme, a dynamic pressure gas bearing is sleeved on the connecting shaft.
The scheme uses the dynamic pressure gas bearing, and the dynamic pressure gas die is generated by means of high-speed relative motion between the shaft and the bearing, so that the assembly requirement is low, the rotor is not centered, and the stability is good at high speed. Compared with a static pressure gas bearing and a magnetic suspension bearing, the structure is simpler, the cost is lower, and the device is more suitable for a household air conditioner.
In the above technical solution, the hydrodynamic gas bearing includes a bump foil type foil bearing, and the bump foil type foil bearing includes: the bearing seat is provided with a fixing groove on the inner side wall; the multilayer foil is sleeved on the inner side of the bearing seat and provided with a fixing part, and the fixing part is matched with the fixing groove to fixedly connect the multilayer foil with the bearing seat; the multilayer foil comprises a flat foil and a bubbling foil sleeved on the radial outer side of the flat foil; wherein the mounting direction of each layer of the foil is opposite to the rotation direction of the bearing.
In this technical scheme, the wave foil type foil bearing is chooseed for use to the bearing, through the fixed slot that sets up on the bearing frame, sets up the fixed part on multilayer foil, and the cooperation between accessible fixed slot and the fixed part realizes the fixed of foil and bearing frame to reduce the run-out that takes place at the rotation in-process, in order to influence the normal use of bearing. The multi-layer foil comprises a flat foil and a bubbling foil, and the bubbling foil is sleeved outside the flat foil and is more favorable for generating a pressure air film during rotation, so that support is provided for the connecting shaft, and the stability of the high-speed operation of the connecting shaft is favorably improved.
In addition, the installation direction of the foil is opposite to the rotation direction of the bearing, so that the stable operation of the bearing is ensured. If the foil and the bearing are arranged in the same direction due to installation errors, the foil can be wound on the shaft to be clamped when the bearing is started, and the bearing cannot be used normally.
In the above technical solution, the bubbling foil includes a plurality of arc pieces, the plurality of arc pieces are distributed at intervals along the circumferential direction of the dynamic pressure gas bearing, the number of the flat foils is two, and the flat foil arranged adjacent to the bubbling foil is connected to the plurality of arc pieces; or the bubbling foil is of an integrated structure, and the number of the flat foils is one layer.
In the technical scheme, the bubbling foil can be formed by a plurality of arc sheets which are distributed at intervals along the circumferential direction of the bearing, meanwhile, the flat foil is arranged adjacent to the bubbling foil, and the radial position of the bubbling foil is limited by the flat foil on the basis that the bubbling foil is arranged on the flat foil.
In addition, the bubbling foil can be of an integrated structure, the flat foil on the inner side of the bubbling foil is only one layer, the number of parts during installation can be reduced, the installation efficiency is improved, and meanwhile, the integral weight and the production cost of the bearing can be reduced on the basis of meeting the requirement of rotation.
In any of the above technical solutions, a switching device is disposed on the air cooling flow path, and the switching device is configured to switch a flow direction of the air cooling flow path, so that the compressed air heat exchange system is switched between a cooling mode and a heating mode.
The switching device is arranged, so that the flow direction of the air refrigerating flow path can be switched, the compressed air heat exchange system can be used for refrigerating and heating, the functions of the compressed air heat exchange system are enriched, and the application range of the compressed air heat exchange system is expanded. Of course, the switching device can be cancelled, and the compressed air heat exchange system only has a heating function and can meet the use requirements of regions with low temperature such as cold regions, or only has a refrigerating function and can meet the use requirements of regions with high temperature such as tropical regions.
In any one of the above technical solutions, the switching device includes: the first control valve is connected with the air return inlet, the air inlet of the first compressor, the air inlet of the expander and the outlet of the second control valve and is used for communicating the air return inlet with the air inlet of the expander and communicating the outlet of the second control valve with the air inlet of the first compressor, or communicating the air return inlet with the air inlet of the first compressor and communicating the outlet of the second control valve with the air inlet of the expander; and the second control valve is connected with the air outlet of the second compressor, the air outlet of the expansion machine, the inlet of the first control valve and the air outlet and is used for communicating the air outlet of the second compressor with the air outlet and communicating the air outlet of the expansion machine with the inlet of the first control valve, or communicating the air outlet of the second compressor with the inlet of the first control valve and communicating the air outlet of the expansion machine with the air outlet.
When the first control valve leads to the air inlet of return air inlet and expander and the export that switches on the second control valve and the air inlet of first compressor, and the second control valve switches on the gas outlet and the air outlet of second compressor and the entry that switches on the gas outlet of expander and first control valve, compressed air heat transfer system switches to the mode operation that heats: the return air enters the expander through the return air inlet and the first control valve in sequence, after being cooled and depressurized, enters the first compressor through the second control valve and the first control valve to be heated and pressurized, then enters the second compressor to be compressed for the second time, the temperature is raised to the highest level of the system, the pressure is also raised, the expansion work is recovered, and finally the return air is sent into a use carrier (such as a room) through the second control valve and the air outlet to heat the use carrier.
When the first control valve leads to the air inlet of return air inlet and first compressor and switches on the export of second control valve and the air inlet of expander, and the second control valve switches on the gas outlet of second compressor and the entry of first control valve and switches on the gas outlet and the air outlet of expander, compressed air heat transfer system switches to the operation of refrigeration mode: the return air enters the first compressor through the return air inlet and the first control valve to be heated and boosted, then enters the second compressor to be secondarily compressed, the temperature rises to the highest level of the system, the pressure is also improved, the expansion work is recovered, then the return air enters the expander through the second control valve and the first control valve, and the expansion work is cooled and depressurized, then is sent into a use carrier through the second control valve and the air outlet.
In the technical scheme, a first heat exchanger is arranged on the air refrigeration flow path, the first heat exchanger is provided with a first heat exchange flow path and a second heat exchange flow path, and an inlet and an outlet of the first heat exchange flow path are communicated with the outside atmosphere; and the inlet and the outlet of the second heat exchange flow path are respectively communicated with the outlet of the second control valve and the inlet of the first control valve, and are used for exchanging heat with the first heat exchange flow path by utilizing the air in the air refrigeration flow path.
The second heat exchange flow path of the first heat exchanger is connected to the air refrigeration flow path, so that gas with temperature rise and pressure rise or temperature drop and pressure drop flows through, heat exchange can be carried out with the external atmosphere flowing through the first heat exchange flow path, and the external atmosphere is cooled or heated, so that the energy efficiency of the system is improved.
Specifically, in the refrigeration mode, the air in the air refrigeration flow path enters the expander for temperature reduction and pressure reduction after being cooled by the first heat exchanger, which is equivalent to twice temperature reduction, thereby being beneficial to improving the refrigeration capacity of the system. In the heating mode, air in the air refrigerating flow path enters the first compressor for temperature and pressure rise after being heated by the first heat exchanger and enters the second compressor for temperature and pressure rise, namely, three-time temperature reduction is performed, so that the heating capacity of the system is improved.
Furthermore, a fan is arranged at an outlet of the first heat exchange flow path, so that air flowing of the first heat exchange flow path is facilitated, and air circulation of the first heat exchange flow path is promoted, and the energy efficiency of the system is further improved.
In the above technical solution, the first control valve is a first four-way valve, and four ports of the first four-way valve are respectively communicated with the air return inlet, the air inlet of the first compressor, the air inlet of the expander, and the outlet of the second control valve; or the first control valve includes: the first one-way valve is positioned between the air return opening and the air inlet of the expansion machine and is used for enabling the air return opening to be communicated with the air inlet of the expansion machine in a one-way mode; the second one-way valve is positioned between the outlet of the second control valve and the air inlet of the first compressor and is used for enabling the outlet of the second control valve to be communicated with the air inlet of the first compressor in a one-way mode; the third one-way valve is positioned between the air return opening and the air inlet of the first compressor and is used for enabling the air return opening to be communicated with the air inlet of the first compressor in a one-way mode; and the fourth one-way valve is positioned between the outlet of the second control valve and the air inlet of the expander and is used for enabling the outlet of the second control valve to be communicated with the air inlet of the expander in one way.
The first control valve adopts a four-way valve form, has a simple structure, is convenient to switch, is favorable for saving long pipelines, optimizes the pipeline layout, simplifies the product structure and is convenient to control.
The first control valve adopts the form of four one-way valves, controls the one-way conduction of the four pipelines respectively, and can also realize the switching of refrigeration and heating.
In the above technical solution, the second control valve is a second four-way valve, and four ports of the second four-way valve are respectively communicated with the air outlet of the second compressor, the air outlet of the expander, the inlet of the first control valve, and the air outlet; or the second control valve comprises: the fifth one-way valve is positioned between the air outlet of the second compressor and the air outlet and is used for enabling the air outlet of the second compressor to be communicated with the air outlet in a one-way mode; the sixth one-way valve is positioned between the air outlet of the expansion machine and the inlet of the first control valve and is used for enabling the air outlet of the expansion machine to be communicated with the inlet of the first control valve in a one-way mode; the seventh one-way valve is positioned between the air outlet conducting the second compressor and the inlet of the first control valve and is used for enabling the air outlet conducting the second compressor to conduct towards the inlet of the first control valve in a one-way mode; and the eighth one-way valve is positioned between the air outlet of the expansion machine and the air outlet and is used for enabling the air outlet of the expansion machine to be communicated with the air outlet in a one-way mode.
The second control valve adopts the form of a four-way valve, has a simpler structure, is convenient to switch, is favorable for saving long paths, optimizes the pipeline layout, simplifies the product structure and is convenient to control.
The second control valve adopts the form of four one-way valves, controls the one-way conduction of the four pipelines respectively, and can also realize the switching of refrigeration and heating.
In any of the above technical solutions, a second heat exchanger is disposed on the air cooling flow path, the second heat exchanger is provided with a cooling flow path and a third heat exchange flow path, two ends of the cooling flow path are respectively communicated with the air outlet of the first compressor and the air inlet of the second compressor, and two ends of the third heat exchange flow path are communicated with the outside air for heat exchange with the cooling flow path.
The two ends of the cooling flow path are respectively communicated with the air outlet of the first compressor and the air inlet of the second compressor, so that the air compressed by the first compressor can be properly cooled through the second heat exchanger before entering the second compressor, the temperature of the air entering the second compressor is reduced, the difficulty in compressing the air by the second compressor is reduced, and the improvement of the energy efficiency of the system is facilitated.
In any of the above technical solutions, a first temperature sensor is disposed at the air outlet; and/or a second temperature sensor is arranged at the air return inlet.
The first temperature sensor is arranged at the air outlet, so that the temperature at the air outlet can be conveniently detected in real time, and a basis is provided for regulation and control of the compressed air heat exchange system.
The second temperature sensor is arranged at the air return opening, so that the temperature at the air return opening can be conveniently detected in real time, and a basis is provided for regulation and control of the compressed air heat exchange system.
In any of the above technical solutions, the first compressor is a one-stage or multi-stage compressor; and/or the second compressor is a one-stage or multi-stage compressor; and/or the first compressor is a centrifugal compressor and is driven by a variable speed motor; and/or the second compressor is a booster turbocompressor.
The first compressor may be selected from one or more compressors as desired to precompress the air. The second compressor can also select one-stage or multi-stage compressors (such as a two-stage compressor) according to requirements, and the air is subjected to main compression, so that the compression effect is improved.
The first compressor can be but not limited to a centrifugal compressor, is driven by a variable speed motor and operates independently, does not influence the operation of the second compressor, and has good effect and high reliability. The second compressor can be but is not limited to a booster turbocompressor, and has good effect and high reliability.
In any of the above technical solutions, the working pressure ratio between the air inlet and the air outlet of the expander is greater than 1 and less than or equal to 3; and/or the working pressure ratio between the air outlet and the air inlet of the second compressor is larger than 1 and is smaller than or equal to 3.
In this solution, the operating efficiency of the system can be optimized by defining the above-mentioned operating pressure ratio.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic view of a refrigeration principle of a compressed air heat exchange system according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of the heating principle of the compressed air heat exchange system of FIG. 1;
fig. 3 is a schematic view of a refrigeration principle of a compressed air heat exchange system according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of the heating principle of the compressed air heat exchange system shown in FIG. 3;
fig. 5 is a schematic view of a refrigeration principle of a compressed air heat exchange system according to an embodiment of the present invention;
FIG. 6 is a schematic diagram of the heating principle of the compressed air heat exchange system shown in FIG. 5;
fig. 7 is a schematic view of a refrigeration principle of a compressed air heat exchange system according to an embodiment of the present invention;
FIG. 8 is a schematic diagram of the heating principle of the compressed air heat exchange system shown in FIG. 7;
fig. 9 is a partial schematic view of a connecting shaft according to an embodiment of the present invention cooperating with a hydrodynamic gas bearing;
fig. 10 is a schematic structural view of a hydrodynamic gas bearing according to some embodiments of the present invention;
fig. 11 is an enlarged schematic view of a structure at a in fig. 10.
Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 11 is:
100 air refrigeration flow path, 11 first compressor, 12 second compressor, 13 expander, 14 driving motor, 141 connecting shaft, 15 dynamic pressure gas bearing, 151 bearing seat, 152 bubbling foil, 153 flat foil, 16 first heat exchanger, 161 first heat exchange flow path, 162 second heat exchange flow path, 17 second heat exchanger, 171 cooling flow path, 172 third heat exchange flow path, 18 first control valve, 19 second control valve, 20 first temperature sensor, 21 second temperature sensor, 24 fan, 25 variable speed motor, 102 air outlet, 104 air return inlet, 200 room;
wherein the arrows in fig. 1 to 8 indicate the flow direction of the air.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention more clearly understood, the present invention will be described in further detail with reference to the accompanying drawings and detailed description. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
A compressed air heat exchange system according to some embodiments of the present invention is described below with reference to fig. 1 to 11.
Example one
A compressed air heat exchange system comprising: the air cooling flow path 100. As shown in fig. 1 and 2, the air cooling flow path 100 is provided with a first compressor 11, a second compressor 12, and an expander 13. The first compressor 11 and the second compressor 12 are used to raise and boost the temperature and pressure of the air flowing through the air cooling flow path 100. The expander 13 is used to reduce the temperature and pressure of the air flowing through the air cooling flow path 100. The inlet and outlet of the air cooling flow path 100 form the return air inlet 104 and the outlet 102 of the compressed air heat exchange system, respectively.
The expander 13 is coaxially connected to the second compressor 12 through a connecting shaft 141, as shown in fig. 1 and 2, and an air inlet of the second compressor 12 is communicated with an air outlet of the first compressor 11.
The utility model provides a compressed air heat transfer system utilizes the air as the refrigerant, and the cooperation of stepping up and 13's of expander cooling step-down is stepped up in the intensification of process compressor, accomplishes the refrigeration or the heating that use the carrier to room 200 etc.. Because the compressed air heat exchange system uses air as the refrigerant, the compressed air heat exchange system is safe and pollution-free, does not cause harm to the environment, saves the cost caused by the traditional refrigerants such as Freon and the like, does not need to supplement the refrigerant regularly, and is favorable for reducing the production cost and the later maintenance cost.
Meanwhile, the air outlet of the first compressor 11 is communicated with the air inlet of the second compressor 12, so that the air compressed by the first compressor 11 enters the second compressor 12 to be compressed again, and the air flowing through the air cooling flow path 100 is compressed in two stages. The expansion ratio and enthalpy drop of the expander 13 can be increased by the two-stage compression, so that the work capacity of the expander 13 is improved, and the unit refrigerating capacity is increased. Compared with single-stage compression, the double-stage compression has better energy efficiency, and the heating capacity of a compressed air heat exchange system is also improved.
And compared with the traditional liquid refrigerant, the air refrigerant can reduce the system pressure (less than 3bar), so that the system is more reliable in operation and longer in service life. The return air inlet 104 of the compressed air heat exchange system is directly communicated with the used carrier, so that a heat exchanger on the inner side of the traditional air conditioner room is omitted, the air supply outlet of the room 200 can be designed into other forms according to the needs of users, and the decoration style of the room 200 is better met.
In addition, the expander 13 is coaxially connected to the second compressor 12 through the connecting shaft 141, so that the second compressor 12 can recover the expansion work of the expander 13, that is, the expansion work of the expander 13 can be used as a power source of the second compressor 12, thereby improving the energy efficiency of the system.
Furthermore, the inlet and the outlet of the air cooling flow path 100 form the air return opening 104 and the air outlet 102 of the compressed air heat exchange system, respectively, and the air outlet 102 and the air return opening 104 are channels for the compressed air heat exchange system to exchange air flow with the carrier (e.g., the room 200). Therefore, the air cooling flow path 100 directly absorbs the air in the use carrier (such as the room 200) through the air return opening 104, cools and heats the use carrier by sending the air into the use carrier through the air outlet 102, and circulates in this way, so that the air in the air cooling flow path 100 of the present application is only exchanged with the air in the use carrier, and is not exchanged with the external atmosphere (i.e. the atmosphere outside the use carrier), and the circulation is closed. The closed circulation pipeline layout is relatively simple, the product structure is favorably simplified, the requirement of a compressed air heat exchange system on the installation environment can be reduced, and the influence of the change of the external atmospheric environment is not easily caused.
Further, the compressed air heat exchange system also comprises: the motor 14 is driven as shown in fig. 1 and 2. Wherein it is coaxially connected to the connection shaft 141 for assisting the expander 13 to drive the second compressor 12.
The driving motor 14 is used to assist the expander 13 to drive the second compressor 12, so that the second compressor 12 can have two operation modes. Specifically, when the expansion work output by the expander 13 can satisfy the power consumption of the second compressor 12, the driving motor 14 does not need to work, and the second compressor 12 is directly driven by the expander 13; when the expansion work output by the expander 13 is not enough to meet the power consumption of the second compressor 12, the driving motor 14 outputs mechanical energy to drive the second compressor 12 together with the expander 13, so that the rotating speed of the turbine is increased, and the temperature drop of the turbine and the refrigerating capacity of the system are increased.
Specifically, the drive motor 14 is a high-speed motor.
Further, a switching device is disposed on the air cooling flow path 100, and the switching device is configured to switch a flow direction of the air cooling flow path 100, so as to switch the compressed air heat exchange system between the cooling mode and the heating mode.
Due to the arrangement of the switching device, the flow direction of the air refrigerating flow path 100 can be switched, so that the compressed air heat exchange system can be used for refrigerating and heating, the functions of the compressed air heat exchange system are enriched, and the application range of the compressed air heat exchange system is expanded.
Of course, the switching device can be cancelled, and the compressed air heat exchange system only has a heating function, so that the use requirements of regions with low temperature such as cold regions and the like or the use requirements of the heat preservation device can be met, or only has a refrigerating function, so that the use requirements of regions with high temperature such as tropical regions and the like or the requirements of the refrigerating device can be met.
Specifically, the switching device includes: a first control valve 18 and a second control valve 19, as shown in fig. 1 and 2.
The first control valve 18 is connected to the air return opening 104, the air inlet of the first compressor 11, the air inlet of the expander 13, and the outlet of the second control valve 19, and is configured to conduct the air return opening 104 and the air inlet of the expander 13 and conduct the outlet of the second control valve 19 and the air inlet of the first compressor 11 (as shown in fig. 2), or conduct the air return opening 104 and the air inlet of the first compressor 11 and conduct the outlet of the second control valve 19 and the air inlet of the expander 13 (as shown in fig. 1).
And a second control valve 19, connected to the air outlet of the second compressor 12, the air outlet of the expander 13, the inlet of the first control valve 18, and the air outlet 102, and configured to communicate the air outlet of the second compressor 12 with the air outlet 102 and communicate the air outlet of the expander 13 with the inlet of the first control valve 18 (as shown in fig. 2), or communicate the air outlet of the second compressor 12 with the inlet of the first control valve 18 and communicate the air outlet of the expander 13 with the air outlet 102 (as shown in fig. 1).
When the first control valve 18 connects the air inlet of the air return opening 104 and the expander 13, and connects the outlet of the second control valve 19 and the air inlet of the first compressor 11, and the second control valve 19 connects the air outlet of the second compressor 12 and the air outlet 102, and connects the air outlet of the expander 13 and the inlet of the first control valve 18, the compressed air heat exchange system is switched to the heating mode:
the return air enters the expander 13 through the return air inlet 104 and the first control valve 18 in sequence, after being cooled and depressurized, enters the first compressor 11 through the second control valve 19 and the first control valve 18 to be heated and pressurized, then enters the second compressor 12 to be compressed for the second time, the temperature is raised to the highest temperature of the system, the pressure is also raised, the expansion work is recovered, and finally the return air is sent into a use carrier (such as a room 200) through the second control valve 19 and the air outlet 102 to heat the use carrier.
When the first control valve 18 conducts the air return inlet 104 and the air inlet of the first compressor 11, and conducts the outlet of the second control valve 19 and the air inlet of the expander 13, and the second control valve 19 conducts the air outlet of the second compressor 12 and the inlet of the first control valve 18, and conducts the air outlet of the expander 13 and the air outlet 102, the compressed air heat exchange system is switched to the cooling mode to operate:
the return air enters the first compressor 11 through the return air inlet 104 and the first control valve 18 to be heated and pressurized, then enters the second compressor 12 to be compressed for the second time, the temperature rises to the highest level of the system, the pressure is also improved, the expansion work is recovered, then enters the expander 13 through the second control valve 19 and the first control valve 18, and is cooled and depressurized, and then is sent into the use carrier through the second control valve 19 and the air outlet 102 to cool the use carrier.
Further, the air cooling flow path 100 is provided with a first heat exchanger 16, as shown in fig. 1 and 2. The first heat exchanger 16 is provided with a first heat exchange flow path 161 and a second heat exchange flow path 162. The inlet and outlet of the first heat exchange flow path 161 communicate with the outside atmosphere. The inlet and the outlet of the second heat exchange flow path 162 communicate with the outlet of the second control valve 19 and the inlet of the first control valve 18, respectively, and exchange heat with the first heat exchange flow path 161 by the air in the air cooling flow path 100.
The second heat exchange flow path 162 of the first heat exchanger 16 is connected to the air cooling flow path 100, so that the air with temperature and pressure increased or temperature and pressure decreased flows through, and can exchange heat with the external atmosphere flowing through the first heat exchange flow path 161, and is cooled or heated by the external atmosphere, thereby improving the energy efficiency of the system.
Specifically, in the cooling mode, the air in the air cooling flow path 100 enters the expander 13 for cooling and pressure reduction after being cooled by the first heat exchanger 16, as shown in fig. 1, which is equivalent to cooling twice, so that the cooling capability of the system is improved. In the heating mode, the air in the air cooling flow path 100 is heated by the first heat exchanger 16 and then enters the first compressor 11 for heating and pressure boosting, and then enters the second compressor 12 for heating and pressure boosting, as shown in fig. 2, three times of cooling is performed, which is beneficial to improving the heating capacity of the system.
Further, the fan 24 is disposed at the outlet of the first heat exchange flow path 161, as shown in fig. 1 and fig. 2, which is beneficial to the air flow of the first heat exchange flow path 161, and further promotes the air circulation of the first heat exchange flow path 161, so as to further improve the energy efficiency of the system.
The first heat exchanger 16 is an air-cooled heat exchanger.
Specifically, the first control valve 18 is a first four-way valve, and four ports of the first four-way valve are respectively communicated with the air return opening 104, the air inlet of the first compressor 11, the air inlet of the expander 13, and the outlet of the second control valve 19. The second control valve 19 is a second four-way valve, and four ports of the second four-way valve are respectively communicated with the air outlet of the second compressor 12, the air outlet of the expander 13, the inlet of the first control valve 18, and the air outlet 102.
In this embodiment, the first control valve 18 and the second control valve 19 adopt a four-way valve form, so that the structure is simple, the switching is convenient, the pipeline length is saved, the pipeline layout is optimized, the product structure is simplified, and the control is convenient.
Example two
In addition to the first embodiment, a dynamic pressure gas bearing 15 is further sleeved on the connecting shaft 141, as shown in fig. 3, 4 and 9.
The scheme uses the dynamic pressure gas bearing 15, and a dynamic pressure lubricating pressure gas mould is generated by means of high-speed relative motion between the shaft and the bearing, so that the assembly requirement is low, the rotor misalignment is resisted, and the stability is good at a high speed. Compared with a static pressure gas bearing and a magnetic suspension bearing, the structure is simpler, the cost is lower, and the device is more suitable for a household air conditioner.
Specifically, as shown in fig. 10 and 11, the dynamic pressure gas bearing 15 includes a bump foil type foil bearing including: a bearing housing 151 and a plurality of foils. The inner sidewall of the bearing housing 151 is provided with a fixing groove. The multilayer foil is sleeved on the inner side of the bearing seat 151 and is provided with a fixing portion, and the fixing portion is matched with the fixing groove to enable the multilayer foil to be fixedly connected with the bearing seat 151. The multi-layered foil includes a flat foil 153 and a bubbling foil 152 fitted over a radially outer side of the flat foil 153. Wherein the mounting direction of each layer of foil is opposite to the rotation direction of the bearing.
In this embodiment, the bearing is a bump foil type foil bearing, the fixing portion is disposed on the multilayer foil through the fixing groove disposed on the bearing seat 151, and the fixing of the foil and the bearing seat 151 can be achieved through the cooperation between the fixing groove and the fixing portion, so that the radial runout occurring in the rotation process is reduced, and the normal use of the bearing is affected. The multi-layer foil comprises a flat foil 153 and a bubbling foil 152, and the bubbling foil 152 is sleeved outside the flat foil 153, so that a pressure air film is generated during rotation, support is provided for the connecting shaft 141, and the stability of the high-speed operation of the connecting shaft 141 is improved.
In addition, the installation direction of the foil is opposite to the rotation direction of the bearing, so that the stable operation of the bearing is ensured. If the foil and the bearing are arranged in the same direction due to installation errors, the foil can be wound on the shaft to be clamped when the bearing is started, and the bearing cannot be used normally.
The bubbling foil 152 includes a plurality of arc pieces, the plurality of arc pieces are distributed at intervals along the circumferential direction of the dynamic pressure gas bearing 15, the number of the flat foil 153 is two, and the flat foil 153 adjacent to the bubbling foil 152 is connected to the plurality of arc pieces.
Alternatively, the blister foil 152 is a one-piece structure, and the number of the flat foils 153 is one layer.
In this embodiment, the blister foil 152 may be formed of a plurality of arc pieces spaced apart along the circumferential direction of the bearing, and the flat foil 153 is disposed adjacent to the blister foil 152, and the radial position of the blister foil 152 is limited by the flat foil 153 on the basis that the blister foil 152 is disposed on the flat foil 153.
In addition, the blister foil 152 may be an integrated structure, and the flat foil 153 on the inner side of the blister foil 152 is only one layer, so that the number of parts during installation can be reduced, the installation efficiency can be improved, and the weight and the production cost of the whole bearing can be reduced on the basis of satisfying the rotation.
EXAMPLE three (not shown)
The difference from the first embodiment is that: the first control valve 18 includes: the first check valve, the second check valve, the third check valve and the fourth check valve. The second control valve 19 includes: a fifth check valve, a sixth check valve, a seventh check valve, and an eighth check valve.
The first one-way valve is located between the air return opening 104 and the air inlet of the expander 13, and is used for enabling the air return opening 104 to be communicated with the air inlet of the expander 13 in a one-way mode.
The second check valve is located between the outlet of the second control valve 19 and the air inlet of the first compressor 11, and is used for enabling the outlet of the second control valve 19 to conduct towards the air inlet of the first compressor 11 in a single direction.
The third check valve is located between the air return opening 104 and the air inlet of the first compressor 11, and is used for enabling the air return opening 104 to be communicated with the air inlet of the first compressor 11 in a one-way mode.
The fourth check valve is located between the outlet of the second control valve 19 and the inlet of the expander 13, and is used for making the outlet of the second control valve 19 conduct to the inlet of the expander 13 in a single direction.
The first control valve 18 adopts a four-way valve form, has a simple structure, is convenient to switch, is beneficial to saving long pipelines, optimizes the pipeline layout, simplifies the product structure and is convenient to control.
The first control valve 18 adopts a form of four one-way valves, controls the one-way conduction of four pipelines respectively, and can also realize the switching of refrigeration and heating.
The fifth check valve is located between the air outlet of the second compressor 12 and the air outlet 102, and is configured to enable the air outlet of the second compressor 12 to be communicated with the air outlet 102 in a single direction.
The sixth check valve is located between the outlet of the expander 13 and the inlet of the first control valve 18, and is used for conducting the outlet of the expander 13 to the inlet of the first control valve 18 in a single direction.
The seventh check valve is located between the outlet of the second compressor 12 and the inlet of the first control valve 18, and is used for making the outlet of the second compressor 12 conduct to the inlet of the first control valve 18 in a one-way communication manner.
The eighth check valve is located between the air outlet of the expansion machine 13 and the air outlet 102, and is configured to enable the air outlet of the expansion machine 13 to be communicated with the air outlet 102 in a single direction.
The first control valve 18 and the second control valve 19 adopt the form of four one-way valves, and respectively control the one-way conduction of four pipelines, so that the switching of refrigeration and heating can also be realized.
Example four
The difference from the first embodiment is that: the expander 13 is power matched to the second compressor 12 to drive the second compressor 12 alone as shown in fig. 5 and 6.
EXAMPLE five
The difference from the second embodiment is that: the expander 13 is power matched to the second compressor 12 to drive the second compressor 12 alone as shown in fig. 7 and 8.
In the fourth and fifth embodiments, the expansion machine 13 and the second compressor 12 are power-matched, so that the expansion work output by the expansion machine 13 can meet the power consumption requirement of the second compressor 12, and thus, the driving motor 14 does not need to be additionally configured, and self-sufficiency is realized, thereby simplifying the product structure and reducing the product cost.
It will be appreciated that the expander 13 normally provided for a single stage compression is not sufficient to drive the compressor to which it is coaxially connected, and a high speed motor is required to assist in the drive. In the present application, a first compressor 11 is additionally provided, so that the power consumption of the second compressor 12 coaxially connected to the expander 13 can be reduced, and the expander 13 coaxially connected thereto can sufficiently drive the second compressor 12, thereby eliminating a high-speed motor.
In any of the above embodiments, further, the second heat exchanger 17 is provided on the air cooling flow path 100, as shown in fig. 1 to 8. The second heat exchanger 17 is provided with a cooling flow path 171 and a third heat exchange flow path 172. Both ends of the cooling passage 171 communicate the outlet port of the first compressor 11 and the inlet port of the second compressor 12, respectively. Both ends of the third heat exchange flow path 172 communicate with the outside air to exchange heat with the cooling flow path 171.
The two ends of the cooling flow path 171 are respectively communicated with the air outlet of the first compressor 11 and the air inlet of the second compressor 12, so that the air compressed by the first compressor 11 can be properly cooled by the second heat exchanger 17 before entering the second compressor 12, so as to reduce the temperature of the air entering the second compressor 12, thereby reducing the difficulty in compressing the air by the second compressor 12, and being beneficial to improving the energy efficiency of the system.
Specifically, the second heat exchanger 17 is an air-cooled heat exchanger.
Further, as shown in fig. 3, 4, 7 and 8, a first temperature sensor 20 is disposed at the air outlet 102, and a second temperature sensor 21 is disposed at the air return opening 104.
The first temperature sensor 20 is arranged at the air outlet 102, so that the temperature at the air outlet 102 can be detected in real time conveniently, and a basis is provided for regulation and control of the compressed air heat exchange system.
The second temperature sensor 21 is arranged at the air return opening 104, so that the temperature at the air return opening 104 can be conveniently detected in real time, and a basis is provided for regulation and control of a compressed air heat exchange system.
In any of the above embodiments, the first compressor 11 is a one-stage or multi-stage compressor, and the second compressor 12 is a one-stage or multi-stage compressor.
The first compressor 11 may be selected as one or more stages as desired to precompress the air. The second compressor 12 may also select one or more stages of compressors (e.g., a two-stage compressor) as required to perform main compression on the air, thereby improving the compression effect.
In any of the above embodiments, the first compressor 11 is a centrifugal compressor driven by a variable speed motor 25 and the second compressor 12 is a booster turbo compressor.
The first compressor 11 can be but is not limited to a centrifugal compressor, is driven by the variable speed motor 25, operates independently, does not influence the operation of the second compressor 12, and has good effect and high reliability. The second compressor 12 may be, but is not limited to, a booster turbo compressor, which is effective and reliable.
In any of the above embodiments, the operating pressure ratio between the inlet and outlet of the expander 13 is greater than 1 and less than or equal to 3.
Further, the working pressure ratio between the outlet and inlet of the second compressor 12 is greater than 1 and less than or equal to 3.
In this embodiment, the operating efficiency of the system can be optimized by defining the operating pressure ratio as described above.
The following description specifically describes the cooling and heating of a room by using a compressed air heat exchange system as an air conditioner, and compares the cooling and heating with a conventional air conditioner.
Most of the existing household air-conditioning principles are steam compression type refrigeration, namely, the cold or heat of a room is taken away by utilizing the phase change latent heat of a refrigerant. Most refrigerants are harmful to the environment, such as greenhouse effect and ozone layer holes. Meanwhile, if a person stays in an air-conditioning environment without fresh air for a long time, the health of the person can be affected.
And the principle of the present application is air cooling. The air refrigeration is to use air as refrigerant, and complete the refrigeration or heating of the room through the cooperation of the temperature rise and the pressure rise of the compressor and the temperature reduction and the pressure reduction of the expander.
Specifically, the system mainly comprises an expansion machine, a compressor, a fresh air heat exchanger, an air cooling heat exchanger, a fan and a four-way reversing valve, wherein the compressor comprises a primary compressor and a secondary compressor. The primary compressor is a centrifugal compressor and is driven by a variable speed motor. The secondary compressor is a booster turbine and is coaxial with the expander to recover expansion work.
In other words, the two-stage compressor and the expander form a booster-expander integrated machine. That is, the turboexpander and the centrifugal compressor are coaxially connected. Wherein, the bearing is a dynamic pressure gas bearing. The compressor raises the inlet air pressure and the temperature is increased along with the inlet air pressure; the expander is pushed by the air, through shaft compensation work to the compressor, with a consequent reduction in air temperature.
The switching of the cooling and heating cycles is completed by switching the first four-way valve and the second four-way valve, and the working principle thereof is described below.
Refrigerating: indoor air enters the first-stage compressor through the first four-way valve to be heated and boosted, then enters the air-cooled heat exchanger to dissipate heat (an intermediate cooling process), and then enters the second-stage compressor to be compressed for the second time, the temperature rises to the highest level of the system, the pressure is also improved, the expansion work is recovered, then the indoor air enters the air-cooled heat exchanger through the second four-way valve, is cooled and then enters the expansion machine through the first four-way valve, and is cooled and depressurized and then is sent into a room through the second four-way valve and the air outlet to be cooled.
Heating: indoor air enters the expander through the first four-way valve, enters the air-cooled heat exchanger through the second four-way valve after being cooled and depressurized, enters the primary compressor through the first four-way valve after being heated to raise the temperature and raise the pressure, then enters the air-cooled heat exchanger for heat dissipation (middle cooling process), then enters the secondary compressor to be compressed for the second time, the temperature rises to the highest degree of the system, the pressure is also improved, the expansion work is recovered, and finally the indoor air is sent into a room through the second four-way valve and the air outlet to heat the room.
In one specific example, as shown in fig. 7 and 8, the compressor and the expander are coaxially connected, and the two are matched by equal power, no additional motor drive is needed, and the system is self-sufficient.
In another embodiment, as shown in fig. 3 and 4, a high-speed motor working coaxially is added to the connecting shaft of the turboexpander and the secondary compressor to form a high-speed motor driven air cycle machine assembly, i.e., a supercharging and expanding integrated machine. It has two modes of operation: when the output work of the expansion machine meets the power consumption of the compressor, the high-speed motor does not need to work; otherwise, when the output work of the expansion machine does not meet the power consumption of the compressor, the high-speed motor outputs mechanical energy, the rotating speed of the turbine is increased, and the temperature drop of the turbine and the refrigerating capacity of the system are increased.
The pressure ratio of the expander to the compressor is less than 3, and the optimal system efficiency is ensured. The pressure ratio is larger and the energy efficiency of the system is reduced.
Therefore, the application has the following beneficial effects:
1) the expansion ratio and enthalpy drop of the turboexpander are improved by the two-stage compression, so that the working capacity of the expander is improved, and the unit refrigerating capacity is increased.
2) The air is used as the refrigerant, thereby being safe and polluting and saving the cost of the refrigerant.
3) The system has low pressure (less than 3bar), reliable operation and long service life.
4) The dynamic pressure gas bearing is used, a dynamic pressure lubricating pressure gas film is generated by means of high-speed relative motion between the shaft and the bearing, the assembly requirement is low, the rotor misalignment is resisted, and the stability at high speed is good. Compared with a static pressure gas bearing and a magnetic suspension bearing, the structure is simpler, the cost is lower, and the household air conditioner is used on more trials.
5) The indoor side is not provided with a heat exchanger, and the air supply outlet can be arranged into other forms, so that the indoor air supply system is more suitable for the decoration style of a room.
Of course, the compressed air heat exchange system can also be used as a refrigerating device such as a refrigerator and a freezer or a heating device such as an insulation box, and the used carrier correspondingly serves as a space such as a refrigerating chamber, a freezing chamber and an insulation chamber.
In the present application, the terms "first", "second", "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the term "plurality" means two or more unless expressly limited otherwise. The terms "mounted," "connected," "fixed," and the like are to be construed broadly, and for example, "connected" may be a fixed connection, a removable connection, or an integral connection; "coupled" may be direct or indirect through an intermediary. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.
In the description of the present invention, it should be understood that the terms "upper", "lower", "left", "right", "front", "back", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the device or unit indicated must have a specific direction, be constructed and operated in a specific orientation, and therefore, should not be construed as limiting the present invention.
In the description of the present specification, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (15)
1. A compressed air heat exchange system, comprising:
the air cooling flow path is provided with a first compressor, a second compressor and an expander, the first compressor and the second compressor are used for heating and boosting the air flowing through the air cooling flow path, the expander is used for cooling and depressurizing the air flowing through the air cooling flow path, and an inlet and an outlet of the air cooling flow path respectively form an air return opening and an air outlet of the compressed air heat exchange system;
the expander is coaxially connected with the second compressor through a connecting shaft, and an air inlet of the second compressor is communicated with an air outlet of the first compressor.
2. The compressed air heat exchange system of claim 1, further comprising:
and the driving motor is coaxially connected with the connecting shaft and is used for assisting the expander to drive the second compressor.
3. The compressed air heat exchange system of claim 1,
the expander is isodynamically matched to the second compressor to drive the second compressor alone.
4. A compressed air heat exchange system according to any one of claims 1 to 3,
and a dynamic pressure gas bearing is sleeved on the connecting shaft.
5. The compressed air heat exchange system of claim 4, wherein the hydrodynamic gas bearing comprises a bump foil bearing, the bump foil bearing comprising:
the bearing seat is provided with a fixing groove on the inner side wall;
the multilayer foil is sleeved on the inner side of the bearing seat and provided with a fixing part, and the fixing part is matched with the fixing groove to fixedly connect the multilayer foil with the bearing seat; the multilayer foil comprises a flat foil and a bubbling foil sleeved on the radial outer side of the flat foil;
wherein the mounting direction of each layer of the foil is opposite to the rotation direction of the bearing.
6. The compressed air heat exchange system of claim 5,
the bubbling foil comprises a plurality of arc sheets, the arc sheets are distributed at intervals along the circumferential direction of the dynamic pressure gas bearing, the number of the flat foil sheets is two, and the flat foil sheets adjacent to the bubbling foil are connected with the arc sheets; or
The bubbling foil is of an integrated structure, and the number of the flat foils is one.
7. A compressed air heat exchange system according to any one of claims 1 to 3,
the air cooling flow path is provided with a switching device, and the switching device is used for switching the flow direction of the air cooling flow path so as to switch the compressed air heat exchange system between a cooling mode and a heating mode.
8. The compressed air heat exchange system of claim 7, wherein the switching device comprises:
the first control valve is connected with the air return inlet, the air inlet of the first compressor, the air inlet of the expander and the outlet of the second control valve and is used for communicating the air return inlet with the air inlet of the expander and communicating the outlet of the second control valve with the air inlet of the first compressor, or communicating the air return inlet with the air inlet of the first compressor and communicating the outlet of the second control valve with the air inlet of the expander; and
the second control valve is connected with the air outlet of the second compressor, the air outlet of the expander, the inlet of the first control valve and the air outlet and is used for communicating the air outlet of the second compressor with the air outlet and communicating the air outlet of the expander with the inlet of the first control valve, or communicating the air outlet of the second compressor with the inlet of the first control valve and communicating the air outlet of the expander with the air outlet.
9. The compressed air heat exchange system of claim 8,
the air refrigeration flow path is provided with a first heat exchanger, the first heat exchanger is provided with a first heat exchange flow path and a second heat exchange flow path, and an inlet and an outlet of the first heat exchange flow path are communicated with the outside atmosphere;
and the inlet and the outlet of the second heat exchange flow path are respectively communicated with the outlet of the second control valve and the inlet of the first control valve, and are used for exchanging heat with the first heat exchange flow path by utilizing the air in the air refrigeration flow path.
10. The compressed air heat exchange system of claim 8,
the first control valve is a first four-way valve, and four ports of the first four-way valve are respectively communicated with the air return inlet, the air inlet of the first compressor, the air inlet of the expander and the outlet of the second control valve; or
The first control valve includes:
the first one-way valve is positioned between the air return opening and the air inlet of the expansion machine and is used for enabling the air return opening to be communicated with the air inlet of the expansion machine in a one-way mode;
the second one-way valve is positioned between the outlet of the second control valve and the air inlet of the first compressor and is used for enabling the outlet of the second control valve to be communicated with the air inlet of the first compressor in a one-way mode;
the third one-way valve is positioned between the air return opening and the air inlet of the first compressor and is used for enabling the air return opening to be communicated with the air inlet of the first compressor in a one-way mode; and
and the fourth one-way valve is positioned between the outlet of the second control valve and the air inlet of the expander and is used for enabling the outlet of the second control valve to be communicated with the air inlet of the expander in one way.
11. The compressed air heat exchange system of claim 8,
the second control valve is a second four-way valve, and four ports of the second four-way valve are respectively communicated with the air outlet of the second compressor, the air outlet of the expander, the inlet of the first control valve and the air outlet; or
The second control valve includes:
the fifth one-way valve is positioned between the air outlet of the second compressor and the air outlet and is used for enabling the air outlet of the second compressor to be communicated with the air outlet in a one-way mode;
the sixth one-way valve is positioned between the air outlet of the expansion machine and the inlet of the first control valve and is used for enabling the air outlet of the expansion machine to be communicated with the inlet of the first control valve in a one-way mode;
the seventh one-way valve is positioned between the air outlet conducting the second compressor and the inlet of the first control valve and is used for enabling the air outlet conducting the second compressor to conduct towards the inlet of the first control valve in a one-way mode;
and the eighth one-way valve is positioned between the air outlet of the expansion machine and the air outlet and is used for enabling the air outlet of the expansion machine to be communicated with the air outlet in a one-way mode.
12. A compressed air heat exchange system according to any one of claims 1 to 3,
the air refrigeration system is characterized in that a second heat exchanger is arranged on the air refrigeration flow path, the second heat exchanger is provided with a cooling flow path and a third heat exchange flow path, two ends of the cooling flow path are respectively communicated with an air outlet of the first compressor and an air inlet of the second compressor, and two ends of the third heat exchange flow path are communicated with the external atmosphere for carrying out heat exchange with the cooling flow path.
13. A compressed air heat exchange system according to any one of claims 1 to 3,
a first temperature sensor is arranged at the air outlet; and/or
And a second temperature sensor is arranged at the air return opening.
14. A compressed air heat exchange system according to any one of claims 1 to 3,
the first compressor is a one-stage or multi-stage compressor; and/or
The second compressor is a one-stage or multi-stage compressor; and/or
The first compressor is a centrifugal compressor and is driven by a variable speed motor; and/or
The second compressor is a booster turbocompressor.
15. A compressed air heat exchange system according to any one of claims 1 to 3,
the working pressure ratio between the air inlet and the air outlet of the expansion machine is more than 1 and less than or equal to 3; and/or
And the working pressure ratio between the air outlet and the air inlet of the second compressor is more than 1 and less than or equal to 3.
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| CN201922091780.6U CN210861773U (en) | 2019-11-28 | 2019-11-28 | Compressed air heat exchange system |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112046246A (en) * | 2020-09-14 | 2020-12-08 | 北京航空航天大学 | Energy-saving type refrigeration system of heavy truck |
| CN112556219A (en) * | 2020-11-23 | 2021-03-26 | 珠海格力电器股份有限公司 | Air conditioner |
| CN113154770A (en) * | 2021-02-10 | 2021-07-23 | 西安交通大学 | Refrigeration house refrigerating system |
-
2019
- 2019-11-28 CN CN201922091780.6U patent/CN210861773U/en active Active
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112046246A (en) * | 2020-09-14 | 2020-12-08 | 北京航空航天大学 | Energy-saving type refrigeration system of heavy truck |
| CN112556219A (en) * | 2020-11-23 | 2021-03-26 | 珠海格力电器股份有限公司 | Air conditioner |
| CN112556219B (en) * | 2020-11-23 | 2021-12-24 | 珠海格力电器股份有限公司 | Air conditioner |
| CN113154770A (en) * | 2021-02-10 | 2021-07-23 | 西安交通大学 | Refrigeration house refrigerating system |
| CN113154770B (en) * | 2021-02-10 | 2022-08-05 | 西安交通大学 | Refrigeration house refrigerating system |
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