CN218817170U

CN218817170U - Energy storage and heat management device of centrifugal compressor

Info

Publication number: CN218817170U
Application number: CN202223374990.4U
Authority: CN
Inventors: 宋云建; 刘学松; 舒涛; 冯福金
Original assignee: Sinobrook New Energy Technologies Shanghai Co Ltd
Current assignee: Sinobrook New Energy Technologies Shanghai Co Ltd
Priority date: 2022-12-15
Filing date: 2022-12-15
Publication date: 2023-04-07
Anticipated expiration: 2032-12-15

Abstract

The utility model provides a centrifugal compressor energy storage heat management device, include: a refrigeration circuit configured to circulate a refrigerant; a heat exchange medium circuit configured to circulate a heat exchange medium to cool or heat the target device; the heat exchange device is communicated with the refrigeration loop and the heat exchange medium loop respectively and exchanges heat, so that the refrigerant in the refrigeration loop can cool the heat exchange medium in the heat exchange medium loop; and a centrifugal compressor in communication with the refrigeration circuit.

Description

Energy storage and heat management device of centrifugal compressor

Technical Field

The utility model relates to a heat management technical field, in particular to centrifugal compressor energy storage heat management device.

Background

Thermal management is just needed for electrochemical energy storage, and has significant influence on the performance, service life and safety of an energy storage system. The liquid cooling heat management system has strong heat exchange capacity, can ensure the temperature difference of the battery core within 3 ℃, and can obviously prolong the service life of the energy storage system relative to the air cooling heat management system.

The refrigerating capacity required by the conventional liquid cooling heat management system for storing energy is usually 100kW or less, and a compressor adopted by the refrigerating cycle with low refrigerating capacity is mainly a scroll compressor. The scroll compressor requires oil circulation, which reduces the reliability of the compressor and the liquid cooling thermal management system; the bearing of the scroll compressor is usually a contact type ball bearing, is easy to wear, and the service life of the bearing is usually the bottleneck of the service life of the liquid cooling heat management system; the volume and the quality of the scroll compressor are large, the energy density of the energy storage system is not favorably improved, particularly, along with the increase of the power density of the energy storage system, the refrigerating capacity demand is remarkably increased, and the disadvantage of the scroll compressor in the aspect can be more remarkably realized.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a centrifugal compressor energy storage heat management device to the scroll compressor who adopts of the refrigeration cycle who solves current little cold volume is unfavorable for the problem that energy storage system energy density promoted.

In order to solve the technical problem, the utility model provides a centrifugal compressor energy storage heat management device, include:

the refrigeration system assembly is configured to be sequentially connected to form a refrigeration circuit which comprises a centrifugal compressor, wherein a refrigerant circulates in the refrigeration circuit;

the cooling liquid system assembly is configured to be sequentially connected to form a heat exchange medium loop, wherein a heat exchange medium flows through the heat exchange medium loop so as to cool or heat the target equipment; and

and the heat exchange device is communicated with the refrigeration loop and the heat exchange medium loop respectively and performs heat exchange so that the refrigerant in the refrigeration loop can cool the heat exchange medium in the heat exchange medium loop.

Optionally, in the centrifugal compressor energy storage and heat management apparatus, the apparatus further includes:

the refrigeration system assembly further includes a condenser, a fan, a bypass valve, a primary throttling element, a secondary throttling element, an economizer, a temperature sensor, and a pressure sensor;

the cooling liquid system component comprises a water pump, a temperature sensor and a pressure sensor;

wherein the heat exchange device is an evaporator; the target device is a battery pack heat source.

Optionally, in the centrifugal compressor energy-storage thermal management device, a first output end of the evaporator is connected to a first input end of the centrifugal compressor and an input end of the bypass valve respectively;

the output end of the centrifugal compressor is connected to the input end of the condenser, and the output end of the bypass valve is connected to the input end of the condenser;

the output end of the condenser is connected to the first input end of the economizer, the first output end of the economizer is connected to the input end of the main throttling element, and the output end of the main throttling element is connected to the first output end of the evaporator;

the first output end of the economizer is also connected to the input end of the auxiliary throttling element, the output end of the auxiliary throttling element is connected to the second input end of the economizer, and the second output end of the economizer is connected to the second input end of the centrifugal compressor;

the second output end of the evaporator is connected to the input end of the battery pack heat source, the output end of the battery pack heat source is connected to the input end of the water pump, and the output end of the water pump is connected to the second input end of the evaporator;

the fan is disposed on the condenser, and the temperature sensor and the pressure sensor are disposed at a first input end, a first output end and a second output end of the evaporator, and a first output end and a second input end of the centrifugal compressor, respectively.

Optionally, in the centrifugal compressor energy storage and thermal management apparatus, the centrifugal compressor includes:

an electric machine, comprising:

the device comprises a shell, a first cavity and a second cavity are respectively arranged at two ends of the interior of the shell; and

a rotor on which a radial bearing is provided, the radial bearing including a high-pressure side radial bearing and a low-pressure side radial bearing, being an air bearing and configured to support the rotor in a radial direction;

a high pressure impeller and a low pressure impeller disposed at an end of the rotor and located within the first chamber and/or the second chamber;

a compressor suction port communicating with a suction port of the first chamber;

a compressor discharge port in communication with the gas outlet of the second chamber;

and two ends of the high-low pressure connecting pipe are respectively communicated with the air outlet of the first chamber and the air inlet of the second chamber.

Optionally, in the centrifugal compressor energy storage thermal management apparatus, the centrifugal compressor further includes: the device comprises a low-pressure shell, an interstage gas supplementing port, a high-pressure shell, a low-pressure locking nut, a low-pressure wheel cover seal, a low-pressure end cover, a high-pressure wheel cover seal and a high-pressure locking nut;

a thrust disk provided at an end of the rotor; and

and the high-pressure side thrust bearing and the low-pressure side thrust bearing are arranged on one side or two sides of the thrust disc and are air-float bearings.

Optionally, in the centrifugal compressor energy storage and heat management device, low-temperature and low-pressure refrigerant gas from the evaporator enters the centrifugal compressor through the suction port;

in the centrifugal compressor, refrigerant gas compressed by a low-pressure impeller and acting enters a low-pressure shell, refrigerant gas enters a high-pressure impeller through a high-low pressure connecting pipe and is further compressed and enters a high-pressure shell, and finally high-temperature high-pressure refrigerant gas is discharged into a condenser through an exhaust port;

an interstage air supplement hole is formed in the high-pressure and low-pressure connecting pipe, exhaust from the economizer is connected, the exhaust of the low-pressure impeller is cooled, compression power consumption of the high-pressure impeller is reduced, and system efficiency is improved;

the high-pressure impeller and the low-pressure impeller are both closed impellers, secondary flow from a pressure surface to a suction surface of each blade caused by blade tip gaps is eliminated, the pneumatic efficiency of the compressor is improved, and the wheel cover sides of the high-pressure impeller and the low-pressure impeller are both provided with sealing structures, so that the backflow effect from an outlet to an inlet of the impellers is reduced, and the efficiency of the compressor is improved;

the high-pressure impeller and the low-pressure impeller adopt a back-to-back design mode, the axial thrust directions of the impellers at the high-pressure side and the low-pressure side are opposite and mutually offset, and the axial thrust borne by the thrust bearing is reduced;

two sides of the thrust disc are respectively provided with a thrust bearing so as to bear axial thrust directed to a low-pressure side or a high-pressure side;

when the motor rotating shaft rotates, the low-pressure side radial bearing and the high-pressure side radial bearing suck refrigerant gas to form a gas film to support the rotor to rotate at a high speed, and the thrust rotating shaft is not in contact with the thrust bearing;

meanwhile, the thrust bearing forms an air film to bear axial thrust.

Optionally, in the energy storage and heat management device of the centrifugal compressor, the thrust bearing and the radial bearing are dynamic pressure type air bearing, exhaust gas of the high-pressure impeller passes through a gap between the high-pressure impeller and the high-pressure end cover, then enters the high-pressure side radial bearing through a gap between the high-pressure end cover and the rotating shaft, then enters the low-pressure side radial bearing through an air gap between the motor stator and the rotor, then sequentially passes through the two thrust bearings through a gap between the thrust disc and the motor housing and a gap between the thrust disc and the low-pressure end cover, and finally sequentially passes through a gap between the low-pressure end cover and the rotating shaft and a gap between the low-pressure impeller and the low-pressure end cover, enters the exhaust port of the low-pressure impeller, returns to the main gas path, and sequentially passes through the low-pressure housing, the high-low-pressure connecting pipe and the high-pressure impeller, thereby achieving internal circulation; the motor is a high-speed permanent magnet synchronous motor.

Optionally, in the centrifugal compressor energy storage and heat management device,

when the unit works, a refrigerant in the fluorine system is discharged from the compressor by high-temperature and high-pressure gas, is condensed into high-temperature and high-pressure liquid by the condenser, passes through the main throttling element to form low-temperature and low-pressure liquid, passes through the evaporator to form low-temperature and low-pressure gas and returns to the compressor;

the gas supplementing circuit enables the low-temperature low-pressure liquid passing through the economizer to pass through the evaporation side of the economizer and then to be low-temperature low-pressure gas which is discharged into the gas supplementing side of the compressor;

and cooling liquid in the cooling liquid system exchanges heat with a refrigerant through the evaporator and flows to the battery pack for cooling and heat dissipation, and flows to the evaporator for heat exchange and temperature reduction after heat dissipation is finished.

Optionally, in the centrifugal compressor energy storage and heat management device, the system is controlled and operated according to the surge characteristic of the centrifugal compressor;

detecting the pressure ratio/flow of the compressor to obtain a current operation state point, judging whether a surge protection area is reached or not according to the current operation state point, if so, judging whether a gear of the fan is in an intervention state or not, and if not, continuously detecting the pressure ratio/flow of the compressor to obtain the current operation state point;

when judging whether the gear of the fan is in an interference state, if so, judging whether the opening of the main throttling element is in interference regulation; otherwise, adjusting the gear of the fan according to the surge curve;

when the opening of the main throttling element is judged to be adjusted in an intervention manner, if so, judging whether the intervention control of the auxiliary throttling element is adjusted in an intervention manner, otherwise, adjusting the main throttling element according to a surge curve;

when judging whether the intervention control of the auxiliary throttling element is adjusted in advance, if so, judging whether a bypass valve is opened, otherwise, adjusting the auxiliary throttling element according to a surge curve;

when judging whether the bypass valve is opened, if so, judging whether the current operation state point reaches a surge alarm point, and otherwise, opening the bypass valve and adjusting;

and when judging whether the current operation state point reaches a surge alarm point, if so, stopping the compressor to alarm, and otherwise, returning to detect the pressure ratio/flow of the compressor to obtain the current operation state point.

when judging whether the gear of the fan is in an intervention state, judging whether the current unit pressure is smaller than a first threshold value, if so, judging that the fan gear is in an intervention regulation state, otherwise, stopping the unit and giving an alarm;

when the fan gear is in the interference adjustment state, the fan gear is increased or decreased, whether the fan interference time is greater than a second threshold value or not is judged, and if yes, the opening of the main throttling element is subjected to interference adjustment;

when the opening degree of the main throttling element is judged to be in an intervention state, judging whether the current unit pressure is smaller than a third threshold value, if so, judging that the main throttling element is in an intervention regulation state, otherwise, stopping the unit and giving an alarm;

when the main throttling element is in the intervention adjusting state, judging whether the superheat degree of returned air is smaller than a fourth threshold value, if so, operating the main throttling element, otherwise, exiting the intervention state of the main throttling element;

judging whether the intervention time of the main throttling element is greater than a fifth threshold value, and if so, carrying out intervention regulation on the opening of the auxiliary throttling element;

when the opening degree of the auxiliary throttling element is judged to be in an intervention state, selecting a control strategy of the auxiliary throttling element according to the main path supercooling degree, judging whether the exhaust superheat degree is smaller than a sixth threshold value, if so, judging whether the intervention time of the auxiliary throttling element is larger than a seventh threshold value, and if not, exiting the intervention state of the auxiliary throttling element;

judging whether the intervention time of the auxiliary throttling element is greater than a seventh threshold value, and if so, carrying out intervention regulation on a bypass valve;

and when judging whether the bypass valve intervenes, judging whether the bypass valve is opened, if so, exiting the bypass valve stem pre-adjustment, and otherwise, opening the bypass valve.

The utility model provides an among the centrifugal compressor energy storage heat management device, adopt high-speed air supporting centrifugal compressor to replace scroll compressor for the refrigeration cycle of energy storage liquid cooling system has avoided the multiple drawback that scroll compressor brought.

The utility model adopts the air bearing, so that oil lubrication is not needed, an oil return pipeline is omitted, and the reliability of the compressor and the system is improved; when the air bearing works, the rotating shaft is not contacted with the bearing, but the motor rotor is suspended by an air film, so that the service life of the bearing can be prolonged by at least 1 time; under the same cold volume, the size and the weight of the centrifugal compressor based on the high-speed permanent magnet synchronous motor can be about 40% less than that of the scroll compressor, the volume of the liquid cooling system can be reduced, in other words, more batteries can be arranged in the container with the same size, the energy density of the energy storage system can be improved, and along with the increase of the refrigeration power demand of the energy storage system, the advantage of the high-speed centrifugal compressor in the aspect can be more remarkable.

Drawings

FIG. 1 is a schematic diagram of an energy storage and thermal management apparatus for a centrifugal compressor according to an embodiment of the present invention;

fig. 2 is a schematic view illustrating a control method of an energy storage and thermal management apparatus of a centrifugal compressor according to an embodiment of the present invention;

FIG. 3 is a schematic diagram illustrating a fan shift control method of an energy storage and thermal management apparatus of a centrifugal compressor according to an embodiment of the present invention;

FIG. 4 is a schematic diagram illustrating a control method of a main throttling element of the thermal management device for storing energy of the centrifugal compressor according to an embodiment of the present invention;

fig. 5 is a schematic view illustrating a control method of an auxiliary throttling element of the energy storage and thermal management device of the centrifugal compressor according to an embodiment of the present invention;

fig. 6 is a schematic view illustrating a bypass valve control method of an energy storage thermal management device of a centrifugal compressor according to an embodiment of the present invention;

FIG. 7 is a schematic view of a characteristic curve of a centrifugal compressor according to an embodiment of the present invention;

fig. 8 is a schematic structural view of a centrifugal compressor according to an embodiment of the present invention;

fig. 9 is a schematic structural view of a centrifugal compressor according to an embodiment of the present invention;

fig. 10 is a schematic structural view of a centrifugal compressor according to an embodiment of the present invention.

Detailed Description

The invention will be further elucidated with reference to the drawings in conjunction with the detailed description.

It should be noted that the components in the figures may be exaggerated and not necessarily to scale for illustrative purposes. In the figures, identical or functionally identical components are provided with the same reference symbols.

In the present invention, "disposed on" \ 8230 "", "disposed above" \8230and "disposed above" \8230 "", do not exclude the presence of an intermediate therebetween, unless otherwise specified. Furthermore, "arranged above or 8230that" on "merely indicates the relative positional relationship between the two components, but in certain cases, for example after reversing the product direction, can also be switched to" arranged below or below "8230, and vice versa.

In the present invention, the embodiments are only intended to illustrate the aspects of the present invention, and should not be construed as limiting.

In the present application, the terms "a" and "an" do not exclude the presence of a plurality of elements, unless otherwise indicated.

It is further noted herein that in embodiments of the present invention, only a portion of the components or assemblies may be shown for clarity and simplicity, but those skilled in the art will appreciate that the components or assemblies may be added as needed for specific scenarios, given the teachings of the present invention. Furthermore, features in different embodiments of the invention may be combined with each other, unless otherwise specified. For example, a feature of the second embodiment may be substituted for a corresponding or functionally equivalent or similar feature of the first embodiment, and the resulting embodiments are likewise within the scope of the disclosure or recitation of the present application.

It is also to be noted that, within the scope of the present invention, the expressions "identical", "equal", etc., do not mean that the two values are absolutely equal, but allow a certain reasonable error, that is, the expressions also cover "substantially identical", "substantially equal". By analogy, in the present disclosure, the terms "perpendicular to", "parallel to", and the like in the table direction also cover the meaning of "substantially perpendicular to", "substantially parallel to".

In addition, the numbering of the steps of the methods of the present invention does not limit the order of execution of the steps of the methods. Unless specifically stated, the method steps may be performed in a different order.

The centrifugal compressor energy storage and heat management device provided by the invention is further described in detail with reference to the accompanying drawings and specific embodiments. The advantages and features of the present invention will become more apparent from the following description. It should be noted that the drawings are in simplified form and are not to precise scale, and are provided for convenience and clarity in order to facilitate the description of the embodiments of the present invention.

An object of the utility model is to provide a centrifugal compressor energy storage heat management device to the scroll compressor that the refrigeration cycle who solves current little cold volume adopted is unfavorable for the problem that energy storage system energy density promoted.

In order to achieve the above object, the utility model provides a centrifugal compressor energy storage heat management device, include: a refrigeration circuit configured to circulate a refrigerant; a heat exchange medium circuit configured to circulate a heat exchange medium to cool or heat the target device; the heat exchange device is communicated with the refrigeration loop and the heat exchange medium loop respectively and exchanges heat, so that the refrigerant in the refrigeration loop can cool the heat exchange medium in the heat exchange medium loop; and a centrifugal compressor in communication with the refrigeration circuit.

Fig. 1-10 provide an embodiment of the present invention, and as shown in fig. 1, the centrifugal compressor energy storage and heat management apparatus of the present embodiment includes: a refrigeration circuit configured to circulate a refrigerant; a heat exchange medium circuit configured to circulate a heat exchange medium to cool or heat the target device; the heat exchange device is communicated with the refrigeration loop and the heat exchange medium loop respectively and exchanges heat, so that the refrigerant in the refrigeration loop can cool the heat exchange medium in the heat exchange medium loop; and a centrifugal compressor 1 communicating with the refrigeration circuit.

Specifically, the centrifugal compressor energy storage heat management device further comprises: a refrigeration system assembly configured to be disposed in a refrigeration circuit, including a condenser 4, a fan 5, a bypass valve 16, a primary throttling element 8, a secondary throttling element 7, an economizer 6, a temperature sensor (2, 11, 13, 14), and a pressure sensor (3, 10, 12, 15); a coolant system component configured to be disposed in the heat exchange medium loop, including a water pump 17, a temperature sensor 19, and a pressure sensor 20; wherein the heat exchange device is an evaporator 9; the target device is a battery pack heat source 18. The throttling element comprises an electronic expansion valve, a thermal expansion valve, a capillary tube and the like.

As shown in fig. 1, the first output of the evaporator is connected to the first input of the centrifugal compressor and the input of the bypass valve, respectively; the output end of the centrifugal compressor is connected to the input end of the condenser, and the output end of the bypass valve is connected to the input end of the condenser; the output end of the condenser is connected to the first input end of the economizer, the first output end of the economizer is connected to the input end of the main throttling element, and the output end of the main throttling element is connected to the first output end of the evaporator; the first output end of the economizer is also connected to the input end of the auxiliary throttling element, the output end of the auxiliary throttling element is connected to the second input end of the economizer, and the second output end of the economizer is connected to the second input end of the centrifugal compressor; the second output end of the evaporator is connected to the input end of the battery pack heat source, the output end of the battery pack heat source is connected to the input end of the water pump, and the output end of the water pump is connected to the second input end of the evaporator; the fan is arranged on the condenser, and the temperature sensor and the pressure sensor are respectively arranged at the first input end, the first output end and the second output end of the evaporator and the first output end and the second input end of the centrifugal compressor.

As shown in fig. 8 to 10, the high-speed air flotation centrifugal compressor is composed of the following components: the compressor comprises a compressor suction port 21, a low-pressure shell 22, an inter-stage air supplementing port 23, a high-low pressure connecting pipe 24, a high-pressure shell 25, a compressor exhaust port 26, a low-pressure impeller 27, a low-pressure locknut 28, a low-pressure impeller cover seal 29, a low-pressure end cover 30, a motor shell 31, an electronic stator 32, a motor rotor 33, a high-pressure end cover 34, a high-pressure impeller cover seal 35, a high-pressure impeller 36, a high-pressure locknut 37, a high-pressure side radial bearing 38, a low-pressure side radial bearing 39, a high-pressure side thrust bearing 40, a thrust disc 41 and a low-pressure side thrust bearing 42.

Based on the small-sized high-speed air flotation centrifugal compressor, a system design based on the centrifugal compressor is designed. And aiming at the surge characteristic of the centrifugal compressor, a control method for preventing the compressor from entering a surge area is introduced based on the design of the system. The low-temperature low-pressure refrigerant gas from the evaporator enters the compressor through the air suction port, enters the low-pressure shell through the low-pressure impeller for compression work, then enters the high-pressure impeller through the high-low pressure connecting pipe for further compression and enters the high-pressure shell, and finally the high-temperature high-pressure refrigerant gas is discharged into the condenser through the air exhaust port. Be equipped with interstage tonifying qi hole on the high-low pressure connecting pipe, can insert the exhaust that comes from the economic ware, cool off the exhaust of low pressure impeller, reduce the compression consumption of high pressure impeller, and then the efficiency of lift system.

The high-low pressure impeller adopts the closed impeller, and compared with the open impeller, the secondary flow from the pressure surface to the suction surface of the blade caused by the blade tip clearance is eliminated, and the pneumatic efficiency of the compressor is effectively improved. And the wheel cap sides of the high-pressure and low-pressure impellers are provided with sealing structures, so that the backflow effect from the outlets of the impellers to the inlets of the impellers can be obviously reduced, and the efficiency of the compressor can be further improved.

The high-pressure impeller and the low-pressure impeller adopt a back-to-back design mode, the axial thrust directions of the impellers at the high-pressure side and the low-pressure side are opposite and mutually offset, and the axial thrust received by the thrust bearing can be effectively reduced. The thrust bearings are positioned as shown in fig. 10, and each thrust bearing is positioned on both sides of the thrust disk so as to receive axial thrust directed to the low pressure side or the high pressure side.

When the motor rotating shaft rotates, the low-pressure side radial bearing and the high-pressure side radial bearing suck refrigerant gas to form a gas film to support the rotor to rotate at a high speed, the thrust rotating shaft is not in contact with the bearings, the bearings are almost free of abrasion, and mechanical loss and noise are small. Meanwhile, the thrust bearing also forms an air film to bear axial thrust. The utility model discloses a thrust and journal bearing are dynamic pressure formula air supporting bearing, realize the bearing air feed through the inner loop: the exhaust of high pressure impeller passes through the space between high pressure impeller and the high pressure end cover, then get into high pressure side journal bearing through the clearance between high pressure end cover and the pivot, then get into low pressure side journal bearing through the air gap between motor stator and the rotor, pass through two thrust bearings in proper order through the clearance between thrust disc and the motor casing and the clearance between thrust disc and the low pressure end cover afterwards, pass through the clearance between low pressure end cover and the pivot in proper order at last, the clearance between low pressure impeller and the low pressure end cover gets into the low pressure impeller gas vent, get back to in the main gas circuit, pass through the low pressure shell in proper order, high low pressure connecting pipe, high pressure impeller, realize the inner loop. For static pressure air supporting bearing, the utility model discloses leave out external tonifying qi passageway, simplify system architecture, improve the reliability.

The utility model discloses the compressor adopts the motor to be high-speed PMSM, because air bearing during operation is non-contact bearing, can bear the rotational speed higher than general ball bearing, according to compressor Euler formula delta h = U2Cu2-U1Cu1 can know, the compressor of same working capacity, the rotational speed is big more, and radial dimension is little, therefore PMSM has promoted the power density of compressor.

As shown in fig. 1, when the unit is in operation, refrigerant in the fluorine system is discharged from the compressor as high-temperature high-pressure gas, condensed into high-temperature high-pressure liquid through the condenser, then passed through the main throttling element to become low-temperature low-pressure liquid, then passed through the evaporator to become low-temperature low-pressure gas, and returned to the compressor. The gas supplementing circuit enables the low-temperature low-pressure liquid passing through the economizer to pass through the evaporation side of the economizer to form low-temperature low-pressure gas, and then the low-temperature low-pressure gas is discharged to the gas supplementing side of the compressor. The bypass valve directly connects the inlet and discharge sides of the compressor. And cooling liquid in the cooling liquid system exchanges heat with a refrigerant through the evaporator and flows to the battery pack for cooling and heat dissipation, and flows to the evaporator for heat exchange and temperature reduction after heat dissipation is finished.

The centrifugal compressor has surge phenomenon, it refers to the abnormal vibration of the compressor that takes place when the flow of the centrifugal compressor is reduced to a certain extent, this kind of vibration threatens the safe use of the compressor, need avoid entering, the centrifugal compressor in the production operation process, sometimes will produce the strong vibration suddenly, the flow and the pressure of the gas medium also appear and pulsate by a wide margin, and accompany the "call" sound of periodic stuffiness, and the air current fluctuation arouses the strong noise of "call gouge" in the pipe network, this kind of phenomenon is called the surge operating mode of the centrifugal compressor, because of the surge characteristic of the centrifugal compressor as shown in figure 7, the utility model designs a control method for avoiding the compressor to enter the surge area.

As shown in fig. 2, the control operation of the system is performed according to the surge characteristics of the centrifugal compressor; detecting the pressure ratio/flow of the compressor to obtain a current operation state point, judging whether a surge protection area is reached or not according to the current operation state point, if so, judging whether a gear of the fan is in an intervention state or not, and if not, continuously detecting the pressure ratio/flow of the compressor to obtain the current operation state point; when judging whether the gear of the fan is in an interference state, if so, judging whether the opening of the main throttling element is in interference regulation; otherwise, adjusting the gear of the fan according to the surge curve; when the opening of the main throttling element is judged to be adjusted in advance, if so, judging whether the intervention control of the auxiliary throttling element is adjusted in advance, and otherwise, adjusting the main throttling element according to a surge curve; when judging whether the interference control of the auxiliary throttling element is adjusted in advance, if so, judging whether the bypass valve is opened, otherwise, adjusting the auxiliary throttling element according to a surge curve; when judging whether the bypass valve is opened, if so, judging whether the current operation state point reaches a surge alarm point, and otherwise, opening the bypass valve and adjusting; and when judging whether the current operation state point reaches the surge alarm point, if so, stopping the compressor to alarm, and otherwise, returning to detect the pressure ratio/flow of the compressor to obtain the current operation state point. FAN refers to the gear of a FAN, the gear of the FAN corresponds to HP (system high pressure/exhaust pressure) in a one-to-one mode during normal control, namely the gear of the FAN required when the HP is high is higher, the gear of the FAN control is assumed to be A, and can be any one of 0-30bar, the value of B is set to be 36bar, and the gear of the FAN can be determined to be a normal value under the condition that the A does not exceed the value of B.

As shown in fig. 3, when it is determined whether the gear of the fan is in the intervention state, it is determined whether the current unit pressure is less than a first threshold, if so, the fan gear is in the intervention regulation state, otherwise, the unit is stopped to alarm; when the fan gear is in the intervention and adjustment state, the fan gear is increased or decreased, whether the fan intervention time is greater than a second threshold value or not is judged, and if yes, the opening of the main throttling element is subjected to intervention and adjustment; as shown in fig. 4, when judging whether the opening of the main throttling element is in the intervention state, judging whether the current unit pressure is smaller than a third threshold, if so, the main throttling element is in the intervention regulation state, otherwise, the unit is stopped to alarm; when the main throttling element is in the intervention adjusting state, judging whether the return air superheat degree is smaller than a fourth threshold value, if so, operating the main throttling element, otherwise, exiting the intervention state of the main throttling element; judging whether the intervention time of the main throttling element is greater than a fifth threshold value, and if so, carrying out intervention regulation on the opening of the auxiliary throttling element; as shown in fig. 5, when the opening degree of the auxiliary throttling element is judged to be in the intervention state, the control strategy of the auxiliary throttling element is selected according to the main supercooling degree, whether the exhaust superheat degree is smaller than a sixth threshold value is judged, if yes, whether the intervention time of the auxiliary throttling element is larger than a seventh threshold value is judged, and if not, the intervention state of the auxiliary throttling element is exited; judging whether the intervention time of the auxiliary throttling element is greater than a seventh threshold value, and if so, carrying out intervention regulation on a bypass valve; as shown in fig. 6, when judging whether the bypass valve intervenes, judging whether the bypass valve is opened, if so, exiting the bypass valve pre-adjustment, otherwise, opening the bypass valve.

The utility model provides a centrifugal compressor does not have oil return system, and compressor and system reliability are high. When in operation, the bearing is not in contact with a motor shaft, the bearing is small in abrasion and long in service life. The intermediate pipe is provided with an air supplementing hole, so that interstage cooling is conveniently realized, and the power consumption of the compressor is reduced. The closed impeller and the wheel cover are sealed on the side, leakage and backflow losses are reduced, and the pneumatic efficiency of the compressor is improved. The back-to-back impeller design reduces axial thrust. The internal circulation dynamic pressure air bearing does not need an additional air supplement pipeline, and has simple and reliable structure. The high-speed permanent magnet synchronous motor is adopted, so that the power density of the compressor is high, and the volume and the mass are small.

For the system carrying the present centrifugal compressor: the system can make full use of all parts of the system, prevent the compressor from entering a surge area, protect the compressor, and perform sequential control and adjustment according to the state point of the compressor and the set priority sequence of the system.

In summary, the above embodiments have described the different configurations of the energy storage and thermal management device of the centrifugal compressor in detail, and of course, the present invention includes but is not limited to the configurations listed in the above embodiments, and any modifications based on the configurations provided by the above embodiments are within the scope of the present invention. One skilled in the art can take the content of the above embodiments to take the inverse three.

In the present specification, the embodiments are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other. For the system disclosed by the embodiment, the description is relatively simple because the system corresponds to the method disclosed by the embodiment, and the relevant points can be referred to the method part for description.

The above description is only for the preferred embodiment of the present invention and is not intended to limit the scope of the present invention, and any modification and modification made by those skilled in the art according to the above disclosure are all within the scope of the claims.

Claims

1. A centrifugal compressor energy storage thermal management device, comprising:

the cooling liquid system assembly is configured to be sequentially connected to form a heat exchange medium loop, wherein a heat exchange medium flows through the heat exchange medium loop to cool or heat the target equipment; and

2. The centrifugal compressor energy storage thermal management apparatus of claim 1, further comprising:

3. The centrifugal compressor energy storage thermal management apparatus of claim 2, wherein the first output of the evaporator is connected to the first input of the centrifugal compressor and the input of the bypass valve, respectively;

4. The centrifugal compressor energy storage thermal management apparatus of claim 3, wherein the centrifugal compressor comprises:

an electric machine, comprising:

the two ends of the interior of the shell are respectively provided with a first cavity and a second cavity; and

5. The centrifugal compressor energy storage thermal management apparatus of claim 4, wherein the centrifugal compressor further comprises: the device comprises a low-pressure shell, an interstage gas supplementing port, a high-pressure shell, a low-pressure locking nut, a low-pressure wheel cover seal, a low-pressure end cover, a high-pressure wheel cover seal and a high-pressure locking nut;

a thrust disk provided at an end of the rotor; and

and the high-pressure side thrust bearing and the low-pressure side thrust bearing are arranged on one side or two sides of the thrust disc and are air bearing.

6. The centrifugal compressor energy storage thermal management apparatus of claim 5, wherein low temperature, low pressure refrigerant gas from the evaporator enters the centrifugal compressor through a suction port;

in the centrifugal compressor, a low-pressure impeller compresses working refrigerant gas to enter a low-pressure shell, the refrigerant gas enters a high-pressure impeller through a high-low pressure connecting pipe to be further compressed and enters a high-pressure shell, and high-temperature high-pressure refrigerant gas is discharged into a condenser through an exhaust port;

an interstage air supplement hole is formed in the high-pressure and low-pressure connecting pipe, exhaust from the economizer is connected, and exhaust of the low-pressure impeller is cooled;

the high-pressure impeller and the low-pressure impeller are closed impellers, and the wheel cover sides of the high-pressure impeller and the low-pressure impeller are provided with sealing structures;

the high-pressure impeller and the low-pressure impeller are back to back mutually, and the axial thrust directions of the impellers at the high-pressure side and the low-pressure side are opposite and mutually offset;

the rotating shaft of the motor rotates to enable the low-pressure side radial bearing and the high-pressure side radial bearing to suck refrigerant gas, a gas film is formed to support the rotor to rotate at a high speed, and the thrust rotating shaft is not in contact with the thrust bearing;

the thrust bearing forms an air film to bear axial thrust.

7. The centrifugal compressor energy storage and heat management device according to claim 6, wherein the thrust bearing and the radial bearing are dynamic pressure type air bearings;

the motor is a high-speed permanent magnet synchronous motor.