CN219191867U - Cold storage type automobile heat management device based on air floatation centrifugal compressor - Google Patents
Cold storage type automobile heat management device based on air floatation centrifugal compressor Download PDFInfo
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- CN219191867U CN219191867U CN202320049876.XU CN202320049876U CN219191867U CN 219191867 U CN219191867 U CN 219191867U CN 202320049876 U CN202320049876 U CN 202320049876U CN 219191867 U CN219191867 U CN 219191867U
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Abstract
The utility model relates to a heat-storage type automobile heat management device based on an air-floating centrifugal compressor, which comprises: a refrigeration circuit configured to circulate a refrigerant; a refrigeration system assembly disposed on the refrigeration circuit, wherein the refrigeration system assembly includes an air-bearing centrifugal compressor configured to compress a refrigerant; the two ends of the cold storage branch are communicated with the refrigerating circuit; the cold storage device is arranged on the cold storage branch, and the cold storage assembly comprises a cold storage device and a cold storage throttling element; a heat exchange medium circuit for circulating a heat exchange medium to cool or heat the battery pack and/or the passenger compartment; a first heat exchange device, one part of which is communicated with the refrigeration loop, and the other part of which is communicated with the heat exchange medium loop; a second heat exchange device configured to transfer heat between the refrigeration circuit and the air; and a third heat exchange device configured to transfer heat between the heat exchange medium circuit and the air.
Description
Technical Field
The utility model relates to the technical field of heat management, in particular to a cold storage type automobile heat management device based on an air floatation centrifugal compressor.
Background
At present, the automobile thermal management system controls the operation of parts such as a compressor and the like completely according to the actual refrigeration requirements of a passenger cabin and a battery, and the parts such as the compressor and the like do not actually operate at an optimal efficiency point under a large proportion of working conditions due to the characteristics of the parts, so that the actual coefficient of performance (COP) of the system is lower, and more energy sources are wasted.
In order to meet the requirements of different working conditions and loads, core components such as a compressor, an expansion valve, an electronic fan and the like need to be continuously adjusted to work states, frequent rising and falling speeds or opening degrees exist, even frequent starting and stopping situations exist, and therefore the reliability and the service life of all moving components of the system are greatly affected.
Disclosure of Invention
In order to solve at least some of the above problems in the prior art, the present utility model provides a heat management device for a heat storage type automobile based on an air-floating centrifugal compressor, comprising:
a refrigeration circuit configured to circulate a refrigerant, wherein the refrigerant in the refrigeration circuit is capable of cooling a heat exchange medium in a heat exchange medium circuit, the refrigeration circuit comprising a refrigeration main circuit and a first refrigeration branch and a second refrigeration branch in communication with the refrigeration main circuit;
A refrigeration system assembly disposed on the refrigeration circuit, wherein the refrigeration system assembly includes an air-bearing centrifugal compressor configured to compress a refrigerant;
the two ends of the cold storage branch are communicated with the refrigerating loop;
a cold storage device disposed on the cold storage leg, the cold storage assembly comprising a cold storage device configured to store and release cold, a portion of the cold storage device in communication with the store Leng Zhilu and another portion in communication with the heat exchange medium circuit, and a cold storage throttling element configured to throttle the refrigerant to reduce the temperature and pressure of the refrigerant;
a heat exchange medium loop for circulating a heat exchange medium to cool or heat the battery pack and/or the passenger compartment, the heat exchange medium loop comprising a heat exchange medium main loop and a first heat exchange branch, a heating branch and a second heat exchange branch in communication with the heat exchange medium main loop;
a first heat exchange device having a portion in communication with the refrigeration circuit and another portion in communication with the heat exchange medium circuit 5 and configured to transfer heat between the refrigeration circuit and the heat exchange medium circuit;
a second heat exchange device disposed on the second refrigeration branch and configured to transfer heat between the refrigeration circuit and air;
And a third heat exchange device disposed on the second heat exchange branch and configured to transfer heat between the heat exchange medium circuit and air.
0, the first heat exchange branch, the heating branch and the second heat exchange branch are connected in parallel, and are electrically connected
The pool is arranged on the first heat exchange branch.
Further, the first refrigeration branch circuit and the second refrigeration branch circuit are connected in parallel, and the air-float centrifugal compressor is arranged on the refrigeration main circuit.
Further, the refrigeration system assembly further comprises:
a condenser which is arranged on the refrigeration main path and is communicated with the air floatation centrifugal compressor;
a first throttling element disposed on the first refrigeration branch and in communication with the condenser;
and a second throttling element disposed on the second refrigeration branch and in communication with the condenser.
0, a part of the first heat exchange device is communicated with a refrigeration loop, and the other part of the first heat exchange device is communicated with a refrigeration loop
In communication with a heat exchange medium circuit, wherein the first heat exchange device includes a first inlet and a first outlet for flow of refrigerant therethrough, and a second inlet and a second outlet for flow of heat exchange medium therethrough;
the second heat exchange device comprises a first inlet and a first outlet for the refrigerant to flow through, and
A second inlet and a second outlet for air to flow through;
5 the third heat exchange device comprises a first inlet and a first outlet for air to flow through, and
the second inlet and the second outlet are used for the heat exchange medium to flow through;
the cold storage device comprises a first inlet and a first outlet for the flow of a refrigerant, and a second inlet and a second outlet for the flow of a heat exchange medium.
Further, the electric heater is arranged on the heating branch and is used for heating 0 heat exchange medium.
Further, the method further comprises the following steps:
the first three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the first three-way proportional valve is communicated with a second outlet of the first heat exchange device, a second path of the first three-way proportional valve is communicated with a first path of a third three-way proportional valve and the heating branch, and a third path of the first three-way proportional valve is communicated with the first heat exchange branch;
the second three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the second three-way proportional valve is communicated with a second inlet of the first heat exchange device and the first heat exchange branch, a second path of the second three-way proportional valve is communicated with a second outlet of the cold storage device and the second heat exchange branch, and a third path of the second three-way proportional valve is communicated with the heating branch;
the third three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the third three-way proportional valve is communicated with the first path of the first three-way proportional valve and the heating branch, a second path of the third three-way proportional valve is communicated with a second outlet of the cold storage device, and a third path of the third three-way proportional valve is communicated with the second heat exchange branch;
Further, the method further comprises the following steps:
a first water pump disposed on the first heat exchange branch and a second water pump disposed on the second heat exchange branch, the first water pump and the second water pump configured to power a circulating flow of a heat exchange medium;
an electronic fan mounted on the condenser;
and a blower in communication with the second heat exchange device and the third heat exchange device.
Further, the air-floating centrifugal compressor includes:
an electric machine, comprising:
a first chamber and a second chamber are respectively arranged at two ends of the inner part of the shell; and
the rotor is provided with an air-floating radial bearing, the end part of the rotor is provided with a thrust disc, and one side or two sides of the thrust disc are provided with air-floating thrust bearings;
an impeller disposed at an end of the rotor and located within the first and/or second chambers;
an air inlet in communication with the air inlet of the first chamber;
an exhaust port in communication with the air outlet of the second chamber; and
and two ends of the connecting pipe are respectively communicated with the air outlet of the first chamber and the air inlet of the second chamber.
Further, the air-floating centrifugal compressor further includes:
A thrust plate provided at an end of the rotor;
the thrust bearings are arranged on one side or two sides of the thrust disc and are air bearing;
and the interstage air supplementing port is arranged on the connecting pipe.
The utility model has at least the following beneficial effects: the utility model discloses a cold storage type automobile thermal management device based on an air floatation centrifugal compressor, which is provided with a super cold storage device, wherein the compressor always keeps working at a maximum efficiency point according to different environment temperatures and automobile motion states, redundant cold energy is stored in the cold storage device, when the cold energy of the cold storage device is saturated, the compressor stops running, the cold storage device releases the cold energy outwards, the way ensures that the compressor always keeps at an optimal working efficiency point, and the energy utilization rate of the automobile thermal management device is greatly improved; the cold storage device selects cold storage working medium materials with good characteristics, can store more than 5kW of cold energy, can greatly store redundant cold energy, ensures that one-time release can meet the longer-time refrigeration requirement, and avoids frequent start and stop of a compressor; this scheme is when the cold storage device refrigerates, refrigerates to the passenger cabin through the heat exchange core, and this structure still can be used to the heating of passenger cabin simultaneously, and the structure is simplified, has effectively reduced the cost of pipeline. The air-floating centrifugal compressor used in the automobile heat management device adopts an air-floating bearing, so that oil lubrication is not needed, an oil return pipeline is omitted, and the cost of compressor oil is saved; meanwhile, the rotating shaft is not contacted with the bearing when the air bearing works, but the air film is used for suspending the motor rotor, so that the service life of the bearing can be prolonged by at least 1 time, and the reliability of the compressor and the automobile thermal management device is improved; the air bearing is adopted, compressor oil is not used, the heat exchange efficiency of the refrigerant is improved, and compared with a traditional compressor with compressor oil, the refrigerating capacity is improved by more than 5%; after-market maintenance is performed, so that the compressor oil does not need to be supplemented when parts are maintained and replaced; compared with a vortex compressor, the air-floating centrifugal compressor based on the high-speed permanent magnet synchronous motor has the advantages that the volume is reduced by about 30%, the weight is reduced by about 50%, more arrangement space can be saved for the new energy automobile, and the new energy automobile is light.
Drawings
To further clarify the above and other advantages and features of embodiments of the present utility model, a more particular description of embodiments of the utility model will be rendered by reference to the appended drawings. It is appreciated that these drawings depict only typical embodiments of the utility model and are therefore not to be considered limiting of its scope. In the drawings, for clarity, the same or corresponding parts will be designated by the same or similar reference numerals.
Fig. 1 shows a schematic diagram of a heat management device for a cold storage type automobile based on an air-floating centrifugal compressor according to an embodiment of the utility model.
FIG. 2 shows a schematic configuration of an air bearing centrifugal compressor in accordance with an embodiment of the utility model;
FIGS. 3a-3d respectively show schematic configurations of air bearing centrifugal compressors according to other embodiments of the present utility model;
FIGS. 4a-4d are schematic views each showing a configuration of a different rotor system in an air bearing centrifugal compressor according to an embodiment of the utility model;
FIG. 5 shows a schematic diagram of a low-coldness air-bearing centrifugal compressor in accordance with an embodiment of the present utility model; and
fig. 6 shows a schematic cross-sectional view of a low-refrigeration air-bearing centrifugal compressor in accordance with an embodiment of the present utility model.
Detailed Description
It should be noted that the components in the figures may be shown exaggerated for illustrative purposes and are not necessarily to scale.
In the present utility model, the embodiments are merely intended to illustrate the scheme of the present utility model, and should not be construed as limiting.
In the present utility model, the adjectives "a" and "an" do not exclude a scenario of a plurality of elements, unless specifically indicated.
It should also be noted herein that in embodiments of the present utility model, only a portion of the components or assemblies may be shown for clarity and simplicity, but those of ordinary skill in the art will appreciate that the components or assemblies may be added as needed for a particular scenario under the teachings of the present utility model.
It should also be noted herein that, within the scope of the present utility model, the terms "identical", "equal" and the like do not mean that the two values are absolutely equal, but rather allow for some reasonable error, that is, the terms also encompass "substantially identical", "substantially equal".
It should also be noted herein that in the description of the present utility model, the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present utility model and simplifying the description, and do not explicitly or implicitly indicate that the apparatus or element in question must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as limiting or implying any relative importance.
In addition, the embodiments of the present utility model describe the process steps in a specific order, however, this is only for convenience of distinguishing the steps, and not for limiting the order of the steps, and in different embodiments of the present utility model, the order of the steps may be adjusted according to the adjustment of the process.
In the present utility model, high temperature > medium temperature > low temperature, high pressure > low pressure.
Fig. 1 shows a schematic diagram of a heat management device for a cold storage type automobile based on an air-floating centrifugal compressor according to an embodiment of the utility model.
As shown in fig. 1, a heat management device 5 for a cold storage type automobile based on an air-floating centrifugal compressor comprises:
the refrigeration loop is used for circulating a refrigerant and comprises a refrigeration main path 10, a first refrigeration branch 11 and a second refrigeration branch 12 which are communicated with the refrigeration main path 10, wherein the first refrigeration branch 11 and the second refrigeration branch 12 are connected in parallel;
a refrigeration system component disposed on the refrigeration circuit;
0 a cold storage branch 20, two ends of which are communicated with the refrigerating circuit and with the first refrigerating branch 11 and the second refrigerating branch
The two refrigeration branches 12 are connected in parallel;
a cold storage assembly provided on the cold storage branch 20, the cold storage assembly including a cold storage device 21 and a cold storage throttling element 22; the cold storage device 21 is configured to store and release cold, and includes
A first inlet and a first outlet for the flow of a refrigerant and a second inlet and a second outlet for the flow of a heat medium of the heat exchanger 5, a part of the cold storage means 21 being in communication with the cold storage branch 20 and another part with the heat exchanger
The heat medium loop is communicated; the cold storage device 21 adopts a heat insulation design, the heat preservation efficiency for 1 hour is more than 95%, the cold storage working medium material with good characteristics is selected and used in the interior, and the cold energy more than 5kW can be stored. The cold storage throttling element 22 is configured to throttle the refrigerant to reduce the temperature and pressure of the refrigerant.
And 0 a heat exchange medium loop for circulating a heat exchange medium to cool or heat the battery pack or the passenger compartment. The heat exchange medium circuit comprises a heat exchange medium main circuit 30, a first heat exchange branch 31, a heating branch 32 and a second heat exchange branch 33 which are communicated with the heat exchange medium main circuit 30, wherein
The first heat exchange branch 31, the heating branch 32 and the second heat exchange branch 33 are connected in parallel. The battery pack 1 is disposed on the first heat exchange branch 31.
5 the refrigeration system assembly includes an air-bearing centrifugal compressor 41, a condenser 42, a first throttling element 43 and a second throttling element 44. The air-floating centrifugal compressor 41 is configured to compress a refrigerant. The condenser 42 is in communication with the air-floating centrifugal compressor 41 and is configured to condense the refrigerant. The first throttling element 43 is arranged on the first refrigerating branch 11. The second throttling element 44 is arranged at the second refrigerating branch
On the road 12. The first throttling element 43 and the second throttling element 44 are both in communication with the condenser 42. The high-temperature high-pressure gas refrigerant discharged by the air 0 floatation centrifugal compressor 41 is condensed into medium temperature by a condenser 42
High pressure liquid. The throttling element has the function of throttling the refrigerant to reduce the temperature and pressure of the refrigerant and change the medium-temperature high-pressure refrigerant into low-temperature low-pressure refrigerant, and comprises an expansion valve, a capillary tube, a throttling pipe and the like. The medium-temperature high-pressure liquid refrigerant becomes a low-temperature low-pressure liquid refrigerant through the first throttling element 43 and the second throttling element 44.
The air-floating centrifugal compressor-based cold storage type automobile heat management device further comprises a first heat exchange device 50, wherein one part of the first heat exchange device 50 is communicated with the refrigeration loop, the other part of the first heat exchange device is communicated with the heat exchange medium loop and is configured to transfer heat between the refrigeration loop and the heat exchange medium loop, the first heat exchange device comprises a first inlet and a first outlet for refrigerant to flow through, and a second inlet and a second outlet for heat exchange medium to flow through; a second heat exchange device 51 disposed in the second refrigeration branch 12 and configured to transfer heat between the refrigeration circuit and the air, wherein the second heat exchange device 51 includes a first inlet and a first outlet for the flow of refrigerant therethrough, and a second inlet and a second outlet for the flow of air therethrough; an electric heater 52 provided on the heating branch 32 for heating the heat exchange medium; a third heat exchange device 53 disposed on the second heat exchange branch 33 and configured to transfer heat between the heat exchange medium circuit and the air, wherein the third heat exchange device 53 comprises a first inlet and a first outlet for the air to flow through, and a second inlet and a second outlet for the heat exchange medium to flow through. The first heat exchange means 50 comprises a plate heat exchanger. The second heat exchanging arrangement 51 comprises an evaporator. The third heat exchanging means 53 comprises a heat exchanging core.
The cold storage type automobile heat management device based on the air floatation centrifugal compressor further comprises a first three-way proportional valve 61, a second three-way proportional valve 62 and a third three-way proportional valve 63 which are arranged on the heat exchange medium main loop 30. Two ends of the first heat exchange branch 31 are respectively connected with a first three-way proportional valve 61 and a heat exchange medium main loop 30; two ends of the heating branch 32 are respectively connected with the second three-way proportional valve 62 and the heat exchange medium main loop 30; the two ends of the second heat exchange branch 33 are respectively connected with a third three-way proportional valve 63 and the heat exchange medium main loop 30.
The three-way proportional valve can realize the complete opening or the complete closing of three ways, can realize the communication of any two ways, and can also perform proportional adjustment according to the requirements. The third path of the first three-way proportional valve 61 is communicated with the first heat exchange branch 31, the first path thereof is communicated with the second outlet of the first heat exchange device 50, and the second path thereof is communicated with the first path of the third three-way proportional valve 63 and the heating branch 32. The third path of the second three-way proportional valve 62 communicates with the heating branch 32, the first path of which communicates with the second inlet of the first heat exchanging means 50 and the first heat exchanging branch 31, and the second path communicates with the second inlet of the cold storage means 21 and the second heat exchanging branch 33. The third path of the third three-way proportional valve 63 communicates with the second heat exchanging branch 33, the first path of which communicates with the second path of the first three-way proportional valve 61 and the heating branch 32, and the second path communicates with the second outlet of the cold storage device 21.
The air-floating centrifugal compressor-based cold storage type automobile heat management device further comprises a first water pump 34 arranged on the first heat exchange branch 31 and a second water pump 35 arranged on the second heat exchange branch 33, wherein the first water pump 34 and the second water pump 35 are configured to power the circulating flow of the heat exchange medium; an electronic fan 45 mounted on the condenser 42; a blower 46 in communication with the second heat exchange device 51 and the third heat exchange device 53. The blower 46 can suck air and deliver it to the second heat exchange device 51 or the third heat exchange device 53.
The heat exchange medium circulation of the cold storage type automobile heat management device based on the air floatation centrifugal compressor is of a multi-parallel structure, and the first water pump 34 and the second water pump 35 are respectively used as power sources for pushing the battery pack and the passenger cabin to realize heat exchange. The first heat exchange device 50 and the cold storage device 21 are located at two ends of the main heat exchange medium loop 30, and respectively play a role in transferring heat of a refrigerant and a cold storage working medium to a heat exchange medium, the first heat exchange branch 31 and the second heat exchange branch 33 are connected in parallel in the middle, the heating branch 32 is also connected in parallel between the first heat exchange branch 31 and the second heat exchange branch 33, and the flow direction of the heat exchange medium is switched through a three-way proportional valve in the whole loop by the first heat exchange branch 31, the heating branch 32 and the second heat exchange branch 33.
When the air-floating centrifugal compressor-based cold storage type automobile heat management device is operated, the circulation process of the refrigerant is as follows:
the air-floating centrifugal compressor 41 is used as a power source of the refrigerant cycle, compresses the refrigerant, the compressed high-temperature and high-pressure gas refrigerant passes through the refrigeration main circuit 10 to reach the condenser 42, the electronic fan 45 sucks normal-temperature air into the condenser fins, and the condenser 42 exchanges heat between heat of the high-temperature and high-pressure gas refrigerant and the air. The condensed refrigerant may be split into three paths, one entering the first refrigeration branch 11, reaching the first throttling element 43, one entering the second refrigeration branch 12, reaching the second throttling element 44, and the last entering the cold storage branch 20, reaching the cold storage throttling element 20.
When the first throttling element 43 is opened, the first throttling element 43 throttles the flowing refrigerant, the throttled refrigerant rapidly expands to become low-temperature low-pressure liquid refrigerant and enters the first heat exchange device 50, and in the first heat exchange device 50, the throttled refrigerant absorbs heat from the heat exchange medium through the first heat exchange device 50, so that the heat exchange medium is reduced to an expected temperature to meet the cooling requirement of the battery pack, the refrigerant becomes low-temperature low-pressure gas, and then returns to the air-floating centrifugal compressor 41.
When the second throttling element 44 is opened, the second throttling element 44 throttles the flowing refrigerant, the throttled refrigerant rapidly expands to become low-temperature low-pressure liquid refrigerant, the low-temperature low-pressure liquid refrigerant enters the second heat exchange device 51, the throttled and expanded refrigerant exchanges heat with air in the second heat exchange device 51, the refrigerant absorbs heat in the air, so that the air is cooled to the expected temperature, the refrigerating effect is achieved, the refrigerant after evaporation and heat absorption becomes low-temperature low-pressure gas, and the low-temperature low-pressure gas returns to the air-floating centrifugal compressor 41 again.
When the cold storage throttling element 22 is opened, the cold storage throttling element 22 throttles the flowing refrigerant, the throttled refrigerant rapidly expands to become low-temperature low-pressure liquid refrigerant, the liquid refrigerant enters the cold storage device 21, the working medium in the cold storage device 21 exchanges heat with the throttled and expanded refrigerant, the refrigerant absorbs heat in the cold storage working medium, so that the cold storage working medium is reduced to a lower temperature, cold collection of the cold storage device is realized, the refrigerant after evaporation and heat absorption becomes low-temperature low-pressure gas, and the gas returns to the air floatation centrifugal compressor 41 again.
Automobile thermal management device is according to battery package demand refrigeration capacity W Battery cell And passenger compartment demand refrigeration capacity W Passenger compartment The maximum limit refrigeration load is developed and designed to the air-float centrifugal compressor, namely, the air-float centrifugal compressor can meet the condition that the optimal efficiency point can meet the requirement of W Battery cell And W is Passenger compartment And the maximum limit refrigeration load ensures that the air-float centrifugal compressor can be in an optimal running state under any working condition.
The first throttling element 43 in front of the first heat exchange device 50 and the second throttling element 44 in front of the second heat exchange device 51 respectively control the opening state and the opening size in real time according to the cooling requirement of the battery pack 1 and the refrigerating requirement of the passenger cabin, and only one throttling element can be opened or both throttling elements can be opened simultaneously.
When the air-floating centrifugal compressor-based cold storage type automobile heat management device is operated, the refrigeration of the battery pack is preferentially ensured, and the passenger cabin is refrigerated, and when the capacity of the automobile heat management device is surplus, the cold storage throttling element 22 in front of the cold storage device is started. The opening of the cold storage throttling element 22 in front of the cold storage device 21 requires the following two conditions to be met: one is that one or both of the first throttling element 43 and the second throttling element 44 are in an open state; based on the refrigerating capacity W of the air-floating centrifugal compressor 41 Compressor Demand cooling capacity W of battery pack Battery cell And the demanded cooling capacity W of the passenger compartment Passenger compartment Is determined by the relationship of (a). When one or both of the first throttling element 43 and the second throttling element 44 are in an open state, and W Compressor ＞W Battery cell +W Passenger compartment The cold storage throttling element 22 in front of the cold storage device 21 is opened, and the opening proportion of the cold storage throttling element 22 is adjusted in real time according to the difference value of the mass-produced cold quantity. The difference of the volume-to-volume refrigerating capacity refers to the refrigerating capacity W of the air-float centrifugal compressor Compressor And the required cooling capacity W of the battery pack Battery cell And the demanded cooling capacity W of the passenger compartment Passenger compartment And the difference of the sum. The cold storage device 21 adopts a closed heat insulation design, the heat preservation efficiency for 1 hour is more than 95%, the cold storage working medium material with good characteristics is selected and used in the interior, and the cold energy of more than 5kW can be stored.
The state of the ambient temperature and the vehicle running speed etc. changes in real time when the vehicle is actually running. Therefore, according to the difference of the real-time environment temperature and the running state of the vehicle, the air-floating centrifugal compressor always keeps a better pressure ratio, so that the air-floating centrifugal compressor works at an optimal efficiency point to ensure the optimal coefficient of performance (COP) of the automobile thermal management device.
The air-floating centrifugal compressor-based refrigeration operation of the cold storage type automobile heat management device comprises the following steps: the air-floating centrifugal compressor 41 compresses the refrigerant, and then the refrigerant is condensed by the condenser, and the condensed refrigerant is divided into three paths and respectively enters the positions of the first throttling element 43, the second throttling element 44 and the cold storage throttling element 22. The first throttling element 43 and the second throttling element 44 automatically adjust the opening according to the refrigeration demands of the passenger compartment and the battery pack, respectively, if the passenger compartment and the battery pack meet the refrigeration demands, the cold storage throttling element 22 is opened at this time, so that the refrigerant enters the cold storage device 21, and the cold storage device 21 stores the cold. When it is detected that the cooling capacity of the cooling storage device 21 is saturated, the air-floating centrifugal compressor 41 is turned off, the first water pump 34 and/or the second water pump 35 are/is started, the cooling capacity in the cooling storage device 21 is released through the heat exchange medium in the heat exchange medium loop, and the cooling capacity is released to the battery pack 1 and/or the third heat exchange device 53 through the circulation of the heat exchange medium. Under the action of the three-way proportional valve, the heat exchange medium does not pass through the electric heater 52 and the first heat exchange device 50, and at this time, the passenger compartment is not refrigerated by the second heat exchange device 51, but is refrigerated by the third heat exchange device 53.
Specifically, when the air-floating centrifugal compressor is operated, the battery pack is cooled as follows:
the first and third paths of the first three-way proportional valve 61 are opened, and the second path thereof is closed; the first, second and third paths of the second three-way proportional valve 62 are closed; the first, second and third paths of the third three-way proportional valve 63 are closed.
The first throttling element 43 is opened, the first water pump 34 is operated, the first throttling element 43 throttles the flowing refrigerant, the throttled refrigerant rapidly expands and enters the first heat exchange device 50, the refrigerant absorbs heat of the heat exchange medium in the first heat exchange device 50, the heat exchange medium is cooled to a desired temperature, the cooled heat exchange medium enters the first heat exchange branch 31 to cool the battery pack 1, and then enters the first heat exchange device 50 again.
When the air-float centrifugal compressor is running, the process of refrigerating the passenger cabin is as follows: the second throttling element 44 is opened, the second throttling element 44 throttles the flowing refrigerant, the throttled refrigerant rapidly expands and enters the second heat exchange device 51, the blower 46 sucks air and conveys the air to the second heat exchange device 51, the throttled and expanded refrigerant exchanges heat with the air in the second heat exchange device 51, and the refrigerant absorbs heat in the air, so that the air is reduced to the expected temperature, and the refrigerating effect is achieved.
When the air-float centrifugal compressor is turned off, cooling the battery pack and the passenger compartment using the cooling capacity in the cooling device, comprising:
when both the battery pack and the passenger cabin need to be refrigerated, the first path of the first three-way proportional valve 61 is closed, the second path and the third path thereof are opened, the first path and the second path of the second three-way proportional valve 62 are opened, the third path thereof is closed, and the first path, the second path and the third path of the third three-way proportional valve 63 are opened.
When only the battery pack needs to be refrigerated, the first path of the first three-way proportional valve 61 is closed, the second path and the third path of the first three-way proportional valve are opened, the first path and the second path of the second three-way proportional valve 62 are opened, the third path of the second three-way proportional valve is closed, the first path and the second path of the third three-way proportional valve 63 are opened, and the third path of the third three-way proportional valve is closed.
When only the passenger cabin needs to be refrigerated, the first path and the second path of the first three-way proportional valve 61 are closed, the first path and the second path of the second three-way proportional valve 62 are closed, the second path and the third path of the third three-way proportional valve 63 are opened, and the first path is closed.
And (3) cooling the battery pack: the first water pump 34 is operated, and the heat exchange medium exchanges heat with the cold storage working medium in the cold storage device 21, so that the temperature of the heat exchange medium is reduced to a desired temperature, and the cooled heat exchange medium enters the first heat exchange branch 31 to cool the battery pack 1, and then enters the cold storage device 21 again.
Cooling the passenger compartment: the second water pump 35 operates, the heat exchange medium cooled by the cold storage working medium in the cold storage device 21 enters the second heat exchange branch 33 to reach the third heat exchange device 53, the air blower 46 sucks air and conveys the air to the third heat exchange device 53, and in the third heat exchange device 53, the heat exchange medium exchanges heat with the air, and the heat exchange medium absorbs heat in the air, so that the air is cooled to the expected temperature, and the refrigerating effect is realized.
The air-floating centrifugal compressor-based heating operation of the cold storage type automobile heat management device comprises the following steps:
when the battery pack and the passenger cabin have heating requirements, the first path of the first three-way proportional valve 61 is closed, the second path and the third path of the first three-way proportional valve 61 are opened, the first path, the second path and the third path of the second three-way proportional valve 62 are opened, the first path and the third path of the third three-way proportional valve 63 are opened, and the second path is closed.
When only the battery pack has a heating requirement, the first path of the first three-way proportional valve 61 is closed, the second path and the third path of the first three-way proportional valve 61 are opened, the first path and the third path of the second three-way proportional valve 62 are opened, the second path is closed, and the first path of the third three-way proportional valve 63 is closed.
When only the passenger cabin has a heating requirement, the second path of the first three-way proportional valve 61 is closed, the first path of the second three-way proportional valve 62 is closed, the second path and the third path are opened, the first path and the third path of the third three-way proportional valve 63 are opened, and the second path is closed.
The air-floating centrifugal compressor 41 and the cold storage device 21 are closed, the electric heater 52 is started to heat the heat exchange medium, the heat exchange medium heated by the electric heater 52 can heat the battery pack 1 or the passenger cabin, and the battery pack 1 and the passenger cabin can be heated simultaneously by dividing the heat exchange medium into two paths.
The first water pump 34 is turned on, and the heat exchange medium heated by the electric heater 52 enters the first heat exchange branch 31 to heat the battery pack 1.
The second water pump 35 is turned on, the heat exchange medium heated by the electric heater 52 enters the second heat exchange branch 33 to reach the third heat exchange device 53, and the air blower 46 sucks air and conveys the air to the third heat exchange device 53, and in the third heat exchange device 53, the heat exchange medium exchanges heat with the air to heat the passenger cabin. The first heat exchange branch 31 and the second heat exchange branch 33 are in a completely parallel state, and when the air-floating centrifugal compressor-based cold storage type automobile heat management device heats, the heat exchange medium does not pass through the first heat exchange device 50 and the cold storage device 21 under the action of the three-way valve proportional valve.
The air-float centrifugal compressor compresses low-temperature and low-pressure gas entering through the air inlet into high-temperature and high-pressure gas, and discharges the high-temperature and high-pressure gas from the air outlet. The structure and the working principle of the air-floating centrifugal compressor are described in detail below.
In embodiments of the present utility model, the term "main gas path" refers to a gas path through which gas enters a compressor along a gas inlet, is compressed, and exits through a gas outlet. The term "high pressure side" refers to the side of the compressor where the air pressure is higher, i.e. the side where the last stage impeller is located, and the term "low pressure side" refers to the side of the compressor interior opposite to the high pressure side. Under normal conditions, the gas flows from the high pressure side to the low pressure side through the air bearing and then returns to the main gas path.
Fig. 2 and 3a-3d show schematic configurations of air-bearing centrifugal compressors according to various embodiments of the utility model. As shown, in an embodiment of the utility model, the air bearing centrifugal compressor includes a motor and impeller 200. The rotor system of the motor comprises a radial air bearing 111, when the motor shaft rotates, the radial air bearing sucks gas to form a gas film to support the rotor to rotate at a high speed, and meanwhile, the thrust bearing (if any) also forms a gas film, so that the thrust shaft is not contacted with the bearing, the bearing is almost free from abrasion, and mechanical loss and noise can be greatly reduced or even eliminated. As shown, an impeller 200 is provided at an end of the rotor 101 for compressing a low-temperature low-pressure refrigerant gas to form a high-temperature high-pressure refrigerant gas to be discharged into a condenser. Herein, the terms "radial" and "axial" refer to the radial and axial directions of the rotor or its rotational axis.
Figures 4a-4d show schematic views of different rotor systems in an air bearing centrifugal compressor according to an embodiment of the utility model, respectively. As shown, in the embodiment of the present utility model, the rotor system 101 includes two radial bearings, which have a certain distance therebetween and may be symmetrically distributed on the rotor. In one embodiment of the utility model, the radial bearing adopts a foil type dynamic pressure air bearing, and when air is introduced into the bearing position, an air film can be formed, so that the air floatation effect is achieved.
In order to withstand the axial thrust forces generated during operation of the compressor, in one embodiment of the utility model, a thrust disc 112 and a thrust bearing 113 are also provided in the rotor system. Thrust disc 112 and thrust bearing 113 are optional. As shown in fig. 4a-4d, the thrust disc 112 may be disposed at either end of the rotor, or one thrust disc 112 may be disposed at each end of the rotor. When only one thrust disc is provided, one thrust bearing 113 may be provided on each side of the thrust disc 112, as shown in the figure, the acting surfaces of the two thrust bearings 113 face the thrust disc 112, so that axial thrust forces in different directions can be respectively borne, specifically, the axial thrust directions that the two thrust bearings 113 can bear are opposite. When two thrust disks are provided, one thrust bearing 113 may be respectively provided on two opposite sides of the two thrust disks 112, or on two sides far away from each other, as shown in the drawing, the acting surfaces of the two thrust bearings 113 are both directed toward the thrust disks 112, so that axial thrust in different directions can be respectively borne, and specifically, the axial thrust directions borne by the two thrust bearings 113 are opposite. In one embodiment of the utility model, the thrust bearing adopts a foil type dynamic pressure air bearing, and when air is introduced into the bearing position, an air film can be formed, so that the air floatation effect is achieved.
As shown in fig. 2 and 3a-3d, in various embodiments of the present utility model, single, double or multi-stage impellers may be provided according to practical requirements. Specifically, when only a single-stage impeller is provided, as shown in fig. 2 and 3a, the impeller 200 may be provided at either end of the rotor, and the side on which the impeller is provided may be referred to as the high-pressure side, while the side on which the impeller is not provided may be referred to as the low-pressure side. When two-stage impellers are provided, as shown in fig. 3b and 3c, the two impellers may be provided at both ends of the rotor, or may be provided at any one end of the rotor, and when the two impellers are provided at both ends of the rotor, one side provided with the impeller of the previous stage may be referred to as a low pressure side, and one side provided with the impeller of the subsequent stage may be referred to as a high pressure side, and when the two impellers are provided at one end of the rotor, one side provided with the impeller may be referred to as a high pressure side, and one side not provided with the impeller may be referred to as a low pressure side. Similarly, as shown in fig. 3d, when the multi-stage impellers are provided, the plurality of impellers may be equally or unequally provided at both ends of the rotor, or may be provided at either end of the rotor, and when the multi-stage impellers are provided at both ends of the rotor, one side provided with the impeller of the previous stage may be referred to as a low pressure side, and one side provided with the impeller of the subsequent stage may be referred to as a high pressure side, and when the multi-stage impellers are provided at one end of the rotor, one side provided with the impeller may be referred to as a high pressure side, and one side not provided with the impeller may be referred to as a low pressure side. Based on this, as shown in fig. 2 and 3a-3d, when the rotor rotates, a part of the high pressure gas compressed by the impeller in the main gas path enters the radial bearing on the high pressure side under the pressure, then enters the radial bearing on the low pressure side through the air gap between the motor stator and the rotor, and returns to the main gas path. When the thrust disc and the thrust bearing are arranged, the high-pressure gas also forms a gas film through the thrust bearing to bear axial thrust. In order to effectively reduce the axial thrust force applied to the thrust bearing, in one embodiment of the present utility model, the impeller at the low pressure side and the impeller at the high pressure side are disposed in a back-to-back manner, so that the axial thrust directions of the impellers at the high pressure side and the low pressure side are opposite to each other to cancel each other. In one embodiment of the utility model, the impeller is a shrouded impeller. In one embodiment of the utility model, the impeller is secured to the rotor by a lock nut.
The specific structure and working principle of the air-floating centrifugal compressor according to the embodiment of the utility model will be described in detail below by taking the configuration shown in fig. 3b as an example. It should be understood that the structure and the working principle of the air-floating centrifugal compressor adopting other configurations are basically the same as those of the embodiment, and only the number and positions of the impellers and/or the number and positions of the thrust disks are different, and are not described herein.
Fig. 5 and 6 show a schematic structural view and a schematic sectional view of a small-cooling-capacity air-floating centrifugal compressor according to an embodiment of the utility model. As shown, a low-coldness air-floating centrifugal compressor includes a motor 100, an impeller, an air inlet 301, an air outlet 302, and a connection pipe 303.
The motor 100 includes a rotor 101, a stator 102, and a housing 103. The stator 102 is fixed inside the housing 103, and the central axis of the rotor 101 coincides with the central axis of the stator 102. The rotor 101 is provided with two radial air bearing 111, and at the same time, a thrust disc 112 is provided at one side close to the air inlet 301, and two sides of the thrust disc are respectively provided with an air bearing 113, and the two thrust bearings are oppositely arranged to respectively bear axial thrust directed to the low pressure side or the high pressure side.
As shown, the two ends of the interior of the housing 103 are respectively provided with a first chamber and a second chamber. The air inlet of the first chamber is communicated with the air inlet 301 of the compressor, and it can be understood that the air inlet 301 is the air inlet of the first chamber, the first impeller 201 is disposed in the first chamber, and the first impeller 201 is fixed at the first end of the rotor 101. A connecting pipe 303 is arranged between the first chamber and the second chamber, and the gas compressed by the first impeller 201 flows out from the gas outlet of the first chamber into the connecting pipe 303 and then enters the second chamber through the gas inlet of the second chamber. The second impeller 202 is disposed in the second chamber, the second impeller 202 is fixed at the second end of the rotor 101, most of the gas compressed by the second impeller 202 flows out from the gas outlet of the second chamber, and the gas outlet of the second chamber is communicated with the gas outlet 302 of the compressor, which can be understood as the gas outlet 302 is the gas outlet of the second chamber. As shown in the drawing, in the embodiment of the present utility model, the air outlets of the first chamber and the second chamber are further provided with a first end cover 135 and a second end cover 136, a gap exists between the first end cover 135 and the second end cover 136 and the rotor 101, meanwhile, a certain gap exists between the first end cover 135 and the first impeller 201, the air flowing through the air bearing can return to the main air path through the gap, a certain gap also exists between the second end cover 136 and the second impeller 202, and a part of the air compressed by the second impeller 202 can enter the air bearing through the gap under the action of pressure. In one embodiment of the present utility model, the first impeller 201 and the second impeller 202 are closed impellers, and the closed impellers can effectively eliminate the secondary flow from the blade pressure surface to the suction surface caused by the blade tip clearance, so as to effectively improve the aerodynamic efficiency of the compressor. In one embodiment of the present utility model, as shown in the foregoing, the first impeller 201 and the second impeller 202 adopt a back-to-back design, so that the axial thrust directions of the first impeller and the second impeller are opposite, and offset each other, thereby effectively reducing the axial thrust received by the thrust bearing. In one embodiment of the present utility model, the first impeller 201 and the second impeller 202 are fixed to the rotor 101 by a first lock nut 211 and a second lock nut 221, respectively.
As shown in the figure, the outer sides of the two ends of the motor are also respectively provided with a first pressure shell 131 and a second pressure shell 132, a first sealing ring 133 is arranged between the first pressure shell 131 and the first impeller 201, and a second sealing ring 134 is arranged between the second pressure shell 132 and the second impeller 202, so that the backflow effect from the outlets to the inlets of the first impeller and the second impeller can be obviously reduced by the first sealing ring and the second sealing ring, and the efficiency of the compressor can be further improved.
In order to reduce the compression power consumption of the second impeller 202, in an embodiment of the present utility model, an inter-stage air-compensating hole 331 is further provided on the connecting pipe 303 to access the exhaust air from the economizer, and cool the air compressed by the first impeller, so as to achieve the purposes of reducing the compression power consumption of the high-pressure impeller and improving the efficiency of the system.
In one embodiment of the present utility model, motor 100 is a high-speed permanent magnet synchronous motor, the bearings of which operate as non-contact bearings and thus can withstand higher rotational speeds than conventional ball bearings, according to the compressor euler formula Δh=u 2 Cu 2 -U 1 Cu 1 It is known that the larger the rotation speed is, the smaller the radial dimension is, and therefore, the power density of the compressor can be improved by adopting the permanent magnet synchronous motor.
The working principle of the air-float centrifugal compressor is as follows: the gas compressed by the second impeller enters the second radial bearing at the high pressure side through the gap between the second impeller and the second end cover and the gap between the second end cover and the rotor, then enters the first radial bearing at the low pressure side through the gap between the stator and the rotor, then sequentially passes through the two thrust bearings through the gap between the thrust disc and the motor shell and the gap between the thrust disc and the first end cover, finally sequentially passes through the gap between the first end cover and the rotor and the gap between the first impeller and the first end cover, and enters the first chamber, namely the exhaust port of the first impeller, and returns to the main gas path to realize internal circulation. Compared with a static pressure air bearing, the air bearing centrifugal compressor can omit an external air supplementing channel, simplify the system structure and improve the reliability.
While certain embodiments of the present utility model have been described herein, those skilled in the art will appreciate that these embodiments are shown by way of example only. Numerous variations, substitutions and modifications will occur to those skilled in the art in light of the present teachings without departing from the scope of the utility model. The appended claims are intended to define the scope of the utility model and to cover such methods and structures within the scope of these claims themselves and their equivalents.
Claims (10)
1. An air-floating centrifugal compressor-based cold storage type automobile heat management device, which is characterized by comprising:
a refrigeration circuit configured to circulate a refrigerant, wherein the refrigerant in the refrigeration circuit is capable of cooling a heat exchange medium in a heat exchange medium circuit, the refrigeration circuit comprising a refrigeration main circuit and a first refrigeration branch and a second refrigeration branch in communication with the refrigeration main circuit;
a refrigeration system assembly disposed on the refrigeration circuit, wherein the refrigeration system assembly includes an air-bearing centrifugal compressor configured to compress a refrigerant;
the two ends of the cold storage branch are communicated with the refrigerating loop;
a cold storage assembly disposed on the cold storage leg, the cold storage assembly comprising a cold storage device configured to store and release cold, a portion of the cold storage device in communication with the store Leng Zhilu and another portion in communication with the heat exchange medium circuit, and a cold storage throttling element configured to throttle the refrigerant to reduce the temperature and pressure of the refrigerant;
a heat exchange medium loop for circulating a heat exchange medium to cool or heat the battery pack and/or the passenger compartment, the heat exchange medium loop comprising a heat exchange medium main loop and a first heat exchange branch, a heating branch and a second heat exchange branch in communication with the heat exchange medium main loop;
A first heat exchange device having a portion in communication with the refrigeration circuit and another portion in communication with the heat exchange medium circuit and configured to transfer heat between the refrigeration circuit and the heat exchange medium circuit;
a second heat exchange device disposed on the second refrigeration branch and configured to transfer heat between the refrigeration circuit and air;
and a third heat exchange device disposed on the second heat exchange branch and configured to transfer heat between the heat exchange medium circuit and air.
2. The air-floating centrifugal compressor-based heat management device for a cold storage type automobile according to claim 1, wherein the first heat exchange branch, the heating branch and the second heat exchange branch are connected in parallel, and the battery pack is arranged on the first heat exchange branch.
3. The air-floating centrifugal compressor-based cold storage type automobile thermal management device according to claim 1, wherein the first refrigeration branch and the second refrigeration branch are connected in parallel, and the air-floating centrifugal compressor is arranged on the refrigeration main path.
4. The air-floating centrifugal compressor-based cold storage type automotive thermal management device of claim 3, wherein the refrigeration system assembly further comprises:
the condenser is arranged on the refrigeration main path and is communicated with the air floatation centrifugal compressor;
A first throttling element disposed on the first refrigeration branch and in communication with the condenser;
and a second throttling element disposed on the second refrigeration branch and in communication with the condenser.
5. The air-floating centrifugal compressor-based cold storage automotive thermal management device of claim 2, wherein a portion of the first heat exchange device is in communication with a refrigeration circuit and another portion is in communication with a heat exchange medium circuit, wherein the first heat exchange device includes a first inlet and a first outlet for refrigerant flow therethrough and a second inlet and a second outlet for heat exchange medium flow therethrough;
the second heat exchange device comprises a first inlet and a first outlet for refrigerant to flow through, and a second inlet and a second outlet for air to flow through;
the third heat exchange device comprises a first inlet and a first outlet for air to flow through, and a second inlet and a second outlet for heat exchange medium to flow through;
the cold storage device comprises a first inlet and a first outlet for the flow of a refrigerant, and a second inlet and a second outlet for the flow of a heat exchange medium.
6. The air-floating centrifugal compressor-based thermal management apparatus for a storage-cooled automobile as recited in claim 2, further comprising an electric heater disposed on the heating branch for heating a heat exchange medium.
7. The air-floating centrifugal compressor-based cold storage type automotive thermal management device according to claim 2, further comprising:
the first three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the first three-way proportional valve is communicated with a second outlet of the first heat exchange device, a second path of the first three-way proportional valve is communicated with a first path of a third three-way proportional valve and the heating branch, and a third path of the first three-way proportional valve is communicated with the first heat exchange branch;
the second three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the second three-way proportional valve is communicated with a second inlet of the first heat exchange device and the first heat exchange branch, a second path of the second three-way proportional valve is communicated with a second outlet of the cold storage device and the second heat exchange branch, and a third path of the second three-way proportional valve is communicated with the heating branch;
the third three-way proportional valve is arranged on the heat exchange medium main loop, a first path of the third three-way proportional valve is communicated with the first path of the first three-way proportional valve and the heating branch, a second path of the third three-way proportional valve is communicated with a second outlet of the cold storage device, and a third path of the third three-way proportional valve is communicated with the second heat exchange branch.
8. The air-floating centrifugal compressor-based cold storage type automotive thermal management device according to claim 4, further comprising:
A first water pump disposed on the first heat exchange branch and a second water pump disposed on the second heat exchange branch, the first water pump and the second water pump configured to power a circulating flow of a heat exchange medium;
an electronic fan mounted on the condenser;
and a blower in communication with the second heat exchange device and the third heat exchange device.
9. The air-floating centrifugal compressor-based cold storage type automotive thermal management device according to claim 1, wherein the air-floating centrifugal compressor comprises:
an electric machine, comprising:
a first chamber and a second chamber are respectively arranged at two ends of the inner part of the shell; and
the rotor is provided with an air-floating radial bearing, the end part of the rotor is provided with a thrust disc, and one side or two sides of the thrust disc are provided with air-floating thrust bearings;
an impeller disposed at an end of the rotor and located within the first and/or second chambers;
an air inlet in communication with the air inlet of the first chamber;
an exhaust port in communication with the air outlet of the second chamber; and
and two ends of the connecting pipe are respectively communicated with the air outlet of the first chamber and the air inlet of the second chamber.
10. The air-floating centrifugal compressor-based cold storage type automotive thermal management device according to claim 9, wherein the air-floating centrifugal compressor further comprises:
a thrust plate provided at an end of the rotor;
the thrust bearings are arranged on one side or two sides of the thrust disc and are air bearing;
and the interstage air supplementing port is arranged on the connecting pipe.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320049876.XU CN219191867U (en) | 2023-01-09 | 2023-01-09 | Cold storage type automobile heat management device based on air floatation centrifugal compressor |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202320049876.XU CN219191867U (en) | 2023-01-09 | 2023-01-09 | Cold storage type automobile heat management device based on air floatation centrifugal compressor |
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| CN219191867U true CN219191867U (en) | 2023-06-16 |
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| CN202320049876.XU Active CN219191867U (en) | 2023-01-09 | 2023-01-09 | Cold storage type automobile heat management device based on air floatation centrifugal compressor |
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