An air conditioning system

Abstract

This invention provides an air conditioning system, relating to the field of air conditioning technology. This air conditioning system, through bearings and a controller, can detect and adjust the axial force of the compressor in real time, ensuring the safe and stable operation of the refrigeration system. The air conditioning system includes: a refrigeration system, which includes: a compressor and a controller. The compressor generates multiple axial forces, the sum of which is the total axial force. The compressor includes: an impeller and a bearing. The impeller is configured to generate a first axial force during compressor operation; the magnitude of the first axial force can be changed by altering the diameter of its rear end. The bearing is connected to the impeller. A second axial force is generated in the rear cavity of the bearing system. The controller is configured to adjust the second axial force, controlling the magnitude of the total axial force of the compressor to be within a preset range; wherein, the preset range is the range of axial force values ​​that the bearing can withstand.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more particularly to an air conditioning system. Background Technology

[0002] With the development of science and technology, the application of electrical appliances is becoming more and more common, and air conditioning has become an integral part of the daily lives of more and more people.

[0003] Currently, centrifugal compressors are generally used in air conditioning systems. Due to their high-speed characteristics, centrifugal compressors place high demands on bearings. Axial force is usually the main cause of excessive axial displacement in centrifugal compressor units. Excessive axial displacement will change the clearance between rotating and stationary parts, and cause a series of problems such as seal damage, bearing wear, excessive bearing temperature, casing wear, partition wear, and rotor wear, which seriously affect the life of centrifugal compressor units.

[0004] For oilless centrifugal compressors with ceramic bearings, since they do not use lubricating oil, they cannot use traditional thrust bearings. They generally use angular contact ceramic-coated ball bearings with a certain thrust resistance, but these bearings have poor axial force bearing capacity and cannot withstand large axial forces. Summary of the Invention

[0005] This invention provides an air conditioning system that can detect and control axial force in real time through bearings and a controller, thereby ensuring the safe and stable operation of the refrigeration system.

[0006] The air conditioning system includes a refrigeration system, which includes a compressor and a controller. The compressor generates multiple axial forces, the sum of which is a total axial force. The compressor includes an impeller and a bearing. The impeller is configured to generate a first axial force during compressor operation, and the magnitude of this first axial force can be changed by altering the diameter of its rear end. The bearing is connected to the impeller. The rear cavity of the bearing system generates a second axial force. The controller is configured to adjust the second axial force, controlling the magnitude of the total axial force of the compressor to be within a preset range. The preset range is the range of axial forces that the bearing can withstand.

[0007] Based on the above solutions, some embodiments of this application provide an air conditioning system. This air conditioning system can control the axial force of the compressor through a controller, which can prevent the compressor from having excessive total axial force, thus avoiding serious impact on the normal operation and safety performance of related devices. By controlling the magnitude of the total axial force, the service life of the bearings can be effectively extended, thereby ensuring the safety and reliability of the entire compressor and enabling the refrigeration system to operate safely and stably.

[0008] In some embodiments, the bearing system includes: a shaft, a bearing, a support frame, and two elastic rings; the bearing includes: an inner bearing ring, an outer bearing ring, and rolling elements; the shaft is connected to the impeller; the inner bearing ring is connected to the shaft; the rolling elements are disposed between the inner bearing ring and the outer bearing ring; the elastic rings are disposed between the support frame and the outer bearing ring, and the elastic rings are configured to detect the magnitude of the total axial force of the compressor.

[0009] In some embodiments, the two elastic rings are also connected to a controller; the two elastic rings are symmetrically distributed; the elastic rings are also configured to transmit the detected total axial force to the controller; the controller is also configured to adjust the magnitude of the second axial force according to the magnitude of the total axial force.

[0010] In some embodiments, the refrigeration system further includes: an economizer, a condenser, an evaporator, and a heat exchanger; the economizer is connected to the compressor; the condenser is connected to the compressor and also to the economizer; the evaporator is connected to the compressor, and also to the economizer and the condenser; the input end of the heat exchanger is connected to the condenser and the evaporator; and the output end of the heat exchanger is connected to the compressor.

[0011] In some embodiments, the refrigeration system further includes: a refrigeration cycle loop, a bearing lubrication loop, a first pump, and a first valve; the first pump is disposed between the first valve and the heat exchanger; the first valve is connected to the condenser and the evaporator.

[0012] The refrigeration cycle circuit includes: a suction line from the evaporator to the compressor; a gas supply line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator.

[0013] The bearing lubrication circuit includes: a second liquid supply line from the evaporator to the first valve; a third liquid supply line from the condenser to the first valve; a fourth liquid supply line from the first valve to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

[0014] In some embodiments, the refrigeration system further includes: a refrigeration cycle loop, a bearing lubrication loop, a first pump, a second valve, and a third valve; the second valve is connected to the evaporator, and the third valve is connected to the condenser; one end of the first pump is connected to the second valve and the third valve, and the other end of the pump is connected to the heat exchanger.

[0015] The refrigeration cycle circuit includes: a suction line from the evaporator to the compressor; a gas supply line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator.

[0016] The bearing lubrication circuit includes: a second liquid supply line from the evaporator to the second valve; a third liquid supply line from the condenser to the third valve; a fourth liquid supply line from the second valve or the third valve to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

[0017] In some embodiments, the refrigeration system further includes: a refrigeration cycle loop, a bearing lubrication loop, a first pump, a fifth valve, and a sixth valve; the fifth valve and the sixth valve are connected in parallel; one end of the first pump is connected to the fifth valve and the sixth valve, and the other end of the first pump is connected to the heat exchanger; the refrigeration cycle loop includes: a suction line from the evaporator to the compressor; a gas supply line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator.

[0018] The bearing lubrication circuit includes: a fourth liquid supply line from the condenser to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

[0019] In some embodiments, the control phase of the controller includes an axial force testing phase and an axial force control phase; in the axial force testing phase, the controller tests and acquires the total axial force of the compressor; in the axial force control phase, the controller determines in real time whether the axial force of the compressor is within a preset range; if yes, no action is taken; if no, the controller controls the input of a second axial force to make the axial force of the compressor within the preset range.

[0020] In some embodiments, the controller is further configured to set the preset range, wherein the minimum value of the preset range is a first preset axial force and the maximum value is a second preset axial force; the first preset axial force is the minimum value of the axial force borne by the bearing; and the second preset axial force is the maximum value of the axial force borne by the bearing.

[0021] In some embodiments, during the axial force control phase, when the controller determines in real time that the total axial force of the compressor is within a preset range; if the flow rate of the bearing fluid supply is greater than or equal to the first fluid supply flow rate, the controller does not take any action; if the flow rate of the bearing fluid supply is less than the first fluid supply flow rate, the controller turns on the first pump.

[0022] In some embodiments, during the axial force control phase, if the controller determines in real time that the total axial force of the compressor is not within a preset range; if the total axial force of the compressor is greater than or equal to the second preset axial force, and the duration is greater than or equal to a preset determination time, the controller reduces the second axial force; if the total axial force of the compressor is greater than or equal to the second preset axial force, and the duration is less than the preset determination time, the controller does not take any action.

[0023] If the total axial force of the compressor is less than or equal to the first preset axial force, and the duration is greater than or equal to the preset determination time, the controller increases the second axial force; if the total axial force of the compressor is less than or equal to the first preset axial force, and the duration is less than the preset determination time, the controller does not take any action. Attached Figure Description

[0024] The accompanying drawings are provided to further understand the technical solutions of the present invention and constitute a part of the specification. They are used together with the embodiments of the present invention to explain the technical solutions of the present invention, and do not constitute a limitation on the technical solutions of the present invention.

[0025] Figure 1 A schematic diagram of a conventional impeller provided for an embodiment of this application;

[0026] Figure 2 A structural block diagram of an air conditioning system provided in an embodiment of this application;

[0027] Figure 3 A schematic diagram of a compressor provided for an embodiment of this application;

[0028] Figure 4 A schematic diagram of the axial force distribution of a compressor provided in an embodiment of this application;

[0029] Figure 5 A schematic diagram of an impeller provided for an embodiment of this application;

[0030] Figure 6 A schematic diagram of a bearing system provided in an embodiment of this application;

[0031] Figure 7 A structural block diagram of a refrigeration system provided in an embodiment of this application;

[0032] Figure 8 This is a detailed schematic diagram of a first scheme of a refrigeration system provided in an embodiment of this application;

[0033] Figure 9 A schematic diagram of a bearing fluid supply provided in an embodiment of this application;

[0034] Figure 10 A detailed schematic diagram of another refrigeration system provided in this application embodiment;

[0035] Figure 11 A detailed schematic diagram of yet another refrigeration system provided in this application embodiment;

[0036] Figure 12 A detailed schematic diagram of another refrigeration system provided in the embodiments of this application;

[0037] Figure 13 This is an overall schematic diagram of a refrigeration system provided in an embodiment of this application;

[0038] Figure 14 This is a schematic diagram of a second embodiment of a refrigeration system provided in this application.

[0039] Figure 15 This is a schematic diagram of a third embodiment of a refrigeration system provided in this application.

[0040] Figure label:

[0041] 1-Compressor; 2-Controller; 3-Economizer; 4-Condenser; 5-Evaporator; 6-Heat Exchanger; 7-First Pump; 8-First Valve; 9-Second Valve; 10-Third Valve; 11-Impeller; 12-Bearing; 121-Shaft; 122-Bearing Inner Ring; 123-Bearing Outer Ring; 124-Rolling Element; 125-Support Frame; 126-Elastic Ring; 13-First Stage Impeller; 14-Second Stage Impeller; 15-Motor; 16-Diffuser; 17-Return Fluid; 18-Suction Guide Vane; 19-First Ball Valve ; 20-Fourth valve; 21-First check valve; 22-First filter; 23-Second filter; 24-Fifth valve; 25-Sixth valve; 26-Mechanical pressure relief valve; 27-Electronic expansion valve; 28-Seventh valve; 29-Second ball valve; 30-Second pump; 31-Level sensor; 32-Third ball valve; 33-Eighth valve; 34-First orifice plate; 35-Second orifice plate; 36-First sensor; 37-Precision filter; 38-Second sensor; 39-Third sensor; 40-Fourth Sensor; 41-First sight glass; 42-Second sight glass; 100-Refrigeration system; 101-Refrigeration cycle circuit; 102-Bearing lubrication circuit; 103-Suction pipe; 104-Maintenance pipe; 105-Exhaust pipe; 106-First liquid supply pipe; 107-Return pipe; 108-Second liquid supply pipe; 109-Third liquid supply pipe; 110-Fourth liquid supply pipe; 111-Fifth liquid supply pipe; 112-Return gas pipe; 113-Connecting pipe; 114-First branch pipe; 115- Second branch pipeline; 116-Third branch pipeline; 117-Fourth branch pipeline; 118-Fifth branch pipeline; 119-Sixth branch pipeline; 130-Seventh branch pipeline; 131-Eighth branch pipeline; 132-Sixth liquid supply pipeline; 133-Ninth branch pipeline; 134-Tenth branch pipeline; 135-Low-pressure return pipeline; 136-Eleventh branch pipeline; 1000-Air conditioning system; HV-Hot gas valve; GV-Make-up gas valve; EV1-First electric valve; EV2-Second electric valve. Detailed Implementation

[0042] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0043] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0044] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0045] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances. Furthermore, when describing pipelines, the terms "connected" and "linked" as used in this invention have the meaning of enabling conduction. The specific meaning needs to be understood in conjunction with the context.

[0046] In embodiments of the present invention, the terms "exemplary" or "for example" are used to indicate that something is an example, illustration, or description. Any embodiment or design described as "exemplary" or "for example" in embodiments of the present invention should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of the terms "exemplary" or "for example" is intended to present the relevant concepts in a specific manner.

[0047] As described in the background section, with the development of science and technology, the application of electrical appliances is becoming more and more widespread, and the daily lives of more and more people are closely related to air conditioning.

[0048] Currently, centrifugal compressors are generally used in air conditioning systems. Due to their high-speed characteristics, centrifugal compressors place high demands on bearings. Axial force in centrifugal compressors is often the main cause of excessive axial displacement. Excessive axial displacement can alter the clearance between rotating and stationary parts, leading to a series of problems such as seal damage, bearing wear, excessive bearing temperature, casing wear, partition wear, and rotor wear, which seriously affect the lifespan of the centrifugal compressor.

[0049] like Figure 1As shown, one development trend in controlling axial force in centrifugal compressors is the horizontally opposed impeller arrangement, i.e., a "back-to-back" impeller configuration. This impeller arrangement allows the axial forces generated in two or more impeller stages to cancel each other out, thus balancing the axial force. Currently, many companies have adopted this "back-to-back" impeller arrangement. However, this configuration requires two volutes, significantly increasing the compressor's cost, weight, and size.

[0050] In addition, by setting a shaft seal structure on the back of the impeller, a low-pressure area is generated outside the shaft seal, while the high-pressure area outside the shaft seal is relatively small. This can effectively reduce the axial force on the bearing during unit operation, but it cannot adjust the axial force appropriately according to the real-time axial force under different operating conditions. Opening a hole structure on the impeller hub can balance the pressure between the impeller cover surface and the disc surface, which can also reduce the axial force to a certain extent, but it will reduce the compressor efficiency.

[0051] For oilless centrifugal compressors with ceramic bearings, since they do not use lubricating oil, they cannot use traditional thrust bearings. They generally use angular contact ceramic-coated ball bearings with a certain thrust resistance, but these bearings have poor axial force bearing capacity and cannot withstand large axial forces.

[0052] Based on this, embodiments of the present invention provide an air conditioning system. For example... Figure 2 As shown, the air conditioning system 1000 includes a refrigeration system 100. The refrigeration system is generally used in central air conditioning or multi-split air conditioning systems. The air conditioning system in this application can be directly connected to various terminal products such as fan coil units and can be considered as a single main unit.

[0053] like Figure 2 As shown, the refrigeration system 100 includes a compressor 1 and a controller 2.

[0054] During operation, compressor 1 generates multiple axial forces, the sum of which is the total axial force.

[0055] like Figure 3 As shown, compressor 1 includes: impeller 11 and bearing system 12.

[0056] Impeller 11 is configured to generate a first axial force during compressor operation. The magnitude of the first axial force can be changed by changing the diameter of the rear end of impeller 11. Bearing system 12 is connected to impeller 11.

[0057] The function of the bearing system 12 is to support the components (impeller) mounted on it and to transmit torque.

[0058] In some embodiments, the impeller 11 includes a primary impeller 13 and a secondary impeller 14.

[0059] The first-stage impeller 13 and the second-stage impeller 14 include: a disc, a cover, and blades. Under the action of the impeller blades, the gas rotates at high speed with the impeller. The gas is subjected to centrifugal force and diffusion flow within the impeller, which increases the pressure after it passes through the impeller.

[0060] Among them, reference Figure 4 It can be seen that, regarding the pressure and axial force distribution during the operation of compressor 1, each impeller stage can be specifically divided into:

[0061] 1. Impeller inlet gas pressure P X1 The axial force F acting on the impeller cover surface and the inner impeller disk surface X1 .

[0062] 2. The axial force F generated by the change in momentum of the gas at the impeller inlet from axial to radial flow. X2 .

[0063] 3. Gas pressure P leaking from the impeller outlet into the impeller cover side clearance X3 The resulting axial force F X3 .

[0064] 4. Gas pressure P leaking from the impeller outlet into the gap above the labyrinth seal on the impeller disc side. X4 The resulting axial force F X4 .

[0065] 5. Gas pressure P remaining below the labyrinth seal on the back of the impeller X5 The resulting axial force F X5 .

[0066] 6. Axial force F3 generated by gas pressure P3 in the end cap cavity of the shaft system.

[0067] It should be noted that in the subscript X, X represents the Xth stage in the impeller stage number. For example, for a two-stage impeller, the impeller inlet gas pressure P X1 Including: the inlet gas pressure P of the first-stage impeller 11 and secondary inlet gas pressure P 21 .at the same time Figure 4 P in 11 (F 11 This represents the inlet gas pressure P of the first-stage impeller. 11 The axial force F generated 11 Other similar reference numerals appearing in the attached figures also follow the above explanation.

[0068] The distribution of axial force generated by pressure in various parts of the compressor during operation is as follows:

[0069] (1) Impeller inlet gas pressure P 11 P21 The axial force F acting on the impeller cover surface and the inner impeller disk surface 11 F 21 .

[0070] Axial force F 11 The direction is from left to right, axial force F 21 The direction is from left to right.

[0071] (2) The axial force F generated by the momentum change caused by the change of the inlet gas from axial flow to radial flow at the impeller. 12 F 22 .

[0072] Axial force F 12 The direction is from left to right, axial force F 22 The direction is from left to right.

[0073] (3) Gas leakage pressure P from the impeller outlet to the impeller cover side clearance 13 P 23 The resulting axial force F 13 F 23 .

[0074] Axial force F 13 The direction is from left to right, axial force F 23 The direction is from left to right.

[0075] (4) Gas leakage pressure P on the first-stage impeller disk side 14 The resulting axial force F 14 .

[0076] Axial force F 14 The direction is from right to left.

[0077] (5) Gas pressure P leaking from the secondary impeller outlet into the gap above the labyrinth seal on the impeller disk side. 24 The resulting axial force F 24 .

[0078] Axial force F 24 The direction is from right to left.

[0079] (6) Pressure P of gas remaining below the labyrinth seal on the back of the secondary impeller 25 The resulting axial force F 25 .

[0080] Axial force F 25 The direction is from right to left.

[0081] (7) Axial force F3 generated by the gas environment pressure P3 in the cavity of the end cap of the shaft system.

[0082] The direction of the axial force F3 is from right to left.

[0083] The direction of the total axial force is defined as positive from the high-pressure side to the low-pressure side. If the direction of the axial force is opposite to the definition, it is multiplied by -1. For example, if right-to-left is positive, then left-to-right is negative. The first axial force is F. 25 The second axial force is F3; the total axial force is the sum of the above axial forces.

[0084] like Figure 5 It can be seen that, Figure 5 This refers to the structure of the impeller. The direction of the total axial force is generally from the high-pressure side to the low-pressure side, that is, from right to left. In order to balance the axial force and to better adjust the axial force by changing a certain force, it is necessary to minimize the absolute value of the axial force, that is, to reduce the axial force from right to left.

[0085] Therefore, the diameter D of the rear end ring plate of the second-stage impeller can be increased. For example, the outer side of the rear end ring plate of the second-stage impeller is matched with a labyrinth seal. By increasing the diameter D, the pressure inside the rear end ring plate of the impeller can be significantly reduced, thereby greatly reducing the force on the impeller from the high-pressure side to the low-pressure side. This reduces the axial force from right to left to a minimum, and may even reduce the total axial force from the low-pressure side to the high-pressure side.

[0086] like Figure 3 As shown, Figure 3 The compressor 1 is a basic structure comprising: suction guide vanes 18, bearing system 12, first-stage impeller 13, second-stage impeller 14, motor 15, diffuser 16, and return fluid 17.

[0087] The function of the intake guide vane 18 is to change the absolute velocity direction of the airflow entering the impeller by changing the vane angle. At the same time, the flow rate of the gas entering the impeller can be changed by changing the flow channel area.

[0088] The primary impeller 13 and the secondary impeller 14 each include a disc, a cover, and blades. Under the action of the impeller blades, the gas rotates at high speed with the impeller. The gas is subjected to centrifugal force and diffusion flow within the impeller, resulting in increased pressure after passing through the impeller. For example, the primary impeller 13 and the secondary impeller 14 are sequentially mounted on the main shaft of the motor 15 and rotate with the main shaft of the motor 15.

[0089] The main function of the diffuser 16 is to convert the kinetic energy of the airflow at the impeller outlet into pressure energy.

[0090] The function of bearing system 12 is to support the components (impeller) mounted on it and to transmit torque. The rear cavity of bearing system 12 generates a second axial force.

[0091] The controller 2 is configured to adjust the second axial force, and control the magnitude of the total axial force of the compressor to be within a preset range; wherein, the preset range is the range of axial force values ​​that the bearing can withstand.

[0092] In other words, increasing the diameter D of the rear end ring plate of the second-stage impeller can reduce the first axial force, i.e., the axial force F. 25 Decreasing this will also reduce the absolute value of the total axial force. (Refer to...) Figure 9 Meanwhile, the refrigerant in the refrigeration system provides a pressure during the lubrication process when supplying fluid to the rear bearing cavity; this pressure is the axial force F3. Pressure is essentially the driving force for fluid flow.

[0093] Controller 2 alters the fluid flow rate by controlling the opening of certain valves, thereby changing the axial force F3. Alternatively, controller 2 can change the fluid source, for example, from high pressure to low pressure, which reduces the axial force F3. If the total axial force is within a preset range, the controller does not act; if the total axial force is greater than the preset range, the controller can reduce the axial force F3 from right to left; if the total axial force is less than the preset range, the controller can increase the axial force F3 from right to left. This ensures that the total axial force remains within the preset range, better protecting the bearings and extending the compressor's lifespan.

[0094] Some embodiments of this application provide an air conditioning system that can control the axial force of the compressor through a controller, thereby preventing the compressor from experiencing excessive total axial force and avoiding serious impact on the normal operation and safety performance of related devices. By controlling the magnitude of the total axial force, the service life of the bearings can be effectively extended, thus ensuring the safety and reliability of the entire compressor and enabling the refrigeration system to operate safely and stably.

[0095] The above solution mentions that the controller can change the total axial force, but to accurately control the total axial force, it is necessary to detect the magnitude of the total axial force in real time.

[0096] like Figure 6 As shown, the bearing system 12 includes: a shaft 121, a bearing 120, a support frame 125, and two elastic rings 126; the bearing 120 includes: an inner bearing ring 122, an outer bearing ring 123, and rolling elements 124.

[0097] Shaft 121 is connected to impeller 11 (see reference) Figure 3 and Figure 6 The bearing inner ring 122 is connected to the shaft 121; the rolling element 124 is disposed between the bearing inner ring 122 and the bearing outer ring 123; the elastic ring 126 is disposed between the support frame and the bearing outer ring, and the elastic ring is configured to detect the magnitude of the total axial force of the compressor.

[0098] In other words, the elastic ring 126 can convert the axial force on the bearing into a strain output, which is equivalent to a force sensor.

[0099] In some embodiments, the bearing system 12 is a ceramic bearing, and the ceramic bearing is an angular contact bearing.

[0100] The axial force of the ceramic bearing is transmitted to the outer ring 123 of the bearing through the rolling elements 124 of the bearing system 12. Angular contact ball bearings are generally arranged in pairs, and two elastic rings 126 can be added between the two outer rings 123 and the support frame 125. When the shaft 121 is subjected to axial force, the outer rings 123 of the bearing compress the elastic rings 126. The magnitude of the axial force of the bearing system 12 can be obtained by measuring the strain output of the elastic rings 126.

[0101] This method enables continuous measurement and recording of the axial force of angular contact ball bearings. When designing the elastic ring, the structural dimensions and maximum axial force requirements of the angular contact ball bearing on the rotor under test are mainly considered to ensure that the elastic ring has high measurement sensitivity and small deformation, so as not to cause rubbing failure between the rotor and stator of the shaft system.

[0102] In some embodiments, the two elastic rings 126 are also connected to the controller 2; the two elastic rings 126 are symmetrically distributed.

[0103] The elastic ring 126 is also configured to transmit the detected total axial force to the controller 2; the controller 2 is also configured to adjust the magnitude of the second axial force according to the magnitude of the total axial force.

[0104] After the elastic ring is designed and manufactured, it requires multiple processes including strain gauge bonding, wiring, curing, insulation, and oil resistance. To reduce measurement errors, high-temperature resistant strain gauges and strain adhesives with low heat output are selected. The strain gauges are circumferentially symmetrically distributed and connected in a full-bridge configuration to eliminate the influence of temperature and lead length on the measurement results. Finally, the measurement results need to be acquired and displayed in real time in the controller for adjustment purposes when adjusting the axial force.

[0105] In other words, increasing the diameter D of the rear end ring plate of the second-stage impeller can reduce the first axial force, i.e., the axial force F. 25 This decreases the absolute value of the total axial force. Controller 2 provides an axial force F3 from right to left to the compressor at the bearing end.

[0106] The controller detects and adjusts the total axial force in real time through the bearing. If the total axial force is within the preset range, the controller does not take any action; if the total axial force is greater than the preset range, the controller can reduce the axial force F3 from right to left; if the total axial force is less than the preset range, the controller can increase the axial force F3 from right to left. In this way, the total axial force is always within the preset range, which can better protect the bearing and thus extend the service life of the compressor.

[0107] like Figure 7 As shown, the refrigeration system 100 also includes: an economizer 3, a condenser 4, an evaporator 5, and a heat exchanger 6.

[0108] Economizer 3 is connected to compressor 1; condenser 4 is connected to compressor 1 and also to economizer 3; evaporator 5 is connected to compressor 1, and also to economizer 3 and condenser 4; the input end of heat exchanger 6 is connected to condenser 4 and evaporator 5; the output end of heat exchanger 6 is connected to compressor 1.

[0109] In some embodiments, the inlet of heat exchanger 6 is connected only to condenser 4.

[0110] It should be noted that the refrigeration system 100 mainly applies energy to the refrigerant vapor through the compressor 1, causing its pressure and temperature to rise. After condensation and throttling, it becomes a low-pressure medium. The low-temperature refrigerant liquid evaporates in the evaporator 5, and at the same time absorbs heat from the surrounding environment (refrigerant) to lower the refrigerant temperature, thereby achieving the purpose of refrigeration.

[0111] In some embodiments, the heat exchanger described above is a plate heat exchanger. The working principle of a plate heat exchanger is primarily based on the principle of heat transfer. During operation, high-temperature and low-temperature fluids pass through opposite sides of the plate heat exchanger, exchanging heat through the space between the plates. This heat exchange is achieved through wall conduction and convection formed by the fluids on the wall surface, thereby promoting effective heat exchange between the two fluids at different temperatures. Specifically, the airflow during operation flows through the channel between two plates, with the intermediate partition plate separating the hot and cold fluids, and heat exchange taking place on this plate. The plate material has good thermal conductivity, allowing heat to be conducted quickly through the plates. By utilizing the space between the plates for heat exchange, combined with good thermal conductivity and an effective fluid distribution system, the plate heat exchanger achieves a highly efficient and compact heat exchange process.

[0112] Option 1: In some embodiments, such as Figure 8 As shown, the refrigeration system 100 also includes: a refrigeration circulation loop 101, a bearing lubrication loop 102, a first pump 7, and a first valve 8.

[0113] The first pump 7 is located between the first valve 8 and the heat exchanger 6; the first valve 8 is connected to the condenser 4 and the evaporator 5.

[0114] The refrigeration cycle circuit 101 includes: a suction line 103 from the evaporator 5 to the compressor 1; a make-up gas line 104 from the economizer 3 to the compressor 1; a discharge line 105 from the compressor 1 to the condenser 4; a first liquid supply line 106 from the condenser 4 to the economizer 3; a liquid return line 107 from the economizer 3 to the evaporator 5; and a connecting line 113 from the condenser 4 to the evaporator 5.

[0115] The bearing lubrication circuit 102 includes: a second liquid supply line 108 from the evaporator 5 to the first valve 8; a third liquid supply line 109 from the condenser 4 to the first valve 8; a fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6; a fifth liquid supply line 111 from the heat exchanger 6 to the compressor 1; and a return gas line 112 from the heat exchanger 6 to the evaporator 5.

[0116] In some embodiments, the first valve 8 is an electrically operated three-way valve. The first pump 7 is a refrigerant pump.

[0117] The aforementioned refrigeration cycle circuit 101 refers to the following: a low-temperature, low-pressure gaseous refrigerant is obtained by evaporation from the evaporator 5, and the low-temperature, low-pressure gaseous refrigerant is transferred to the compressor 1 through the suction pipe 103 from the evaporator 5 to the compressor 1, and the first-stage impeller 13 in the compressor 1 compresses the low-temperature, low-pressure gaseous refrigerant.

[0118] The medium-temperature, medium-pressure saturated gas obtained from the economizer is transferred to the compressor 1 through the gas supply line 104 from the economizer 3 to the compressor 1. The compressor 1 mixes the low-temperature, low-pressure gaseous refrigerant compressed from the first-stage impeller 13 with the medium-temperature, medium-pressure saturated gas, and then compresses it through the second-stage impeller 14 to finally obtain a high-temperature, high-pressure gaseous refrigerant.

[0119] The compressor 1 transfers the high-temperature, high-pressure gaseous refrigerant to the condenser 4 through the exhaust pipe 105 from the compressor 1 to the condenser 4; the high-temperature, high-pressure gaseous refrigerant is cooled by the cooling water in the condenser 4 and transformed into a high-temperature, high-pressure liquid refrigerant.

[0120] High-temperature, high-pressure liquid refrigerant is transferred to the economizer 3 via the first liquid supply line 106 from the condenser 4 to the economizer 3; the high-temperature, high-pressure liquid refrigerant is separated into liquid refrigerant and flashing gaseous refrigerant in the economizer 3; the gaseous refrigerant is transferred to the compressor 1 via the gas supply line 104 from the economizer 3 to the compressor 1, and the liquid refrigerant is transferred to the evaporator 5 via the liquid return line 107 from the economizer 3 to the evaporator 5; the liquid refrigerant is evaporated in the evaporator 5 to obtain low-temperature, low-pressure gaseous refrigerant, and then the low-temperature, low-pressure gaseous refrigerant is transferred to the compressor 1 via the suction line 103 from the evaporator 5 to the compressor 1, finally forming the refrigeration cycle loop 101.

[0121] The bearing lubrication circuit 102 refers to: a second liquid supply line 108 from the evaporator 5 to the first valve 8 and a third liquid supply line 109 from the condenser 4 to the first valve 8; both lines are connected to the first valve 8. Liquid refrigerant in the condenser 4 or evaporator 5 flows through the first valve 8 and is transferred to the heat exchanger 6 through a fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6.

[0122] The condenser 4 is equipped with a liquid level sensor. Before the start-up phase, the controller will use the liquid level sensor to determine the liquid level in the condenser.

[0123] If the liquid level in condenser 4 is greater than or equal to the safe liquid level, the first valve 8 opens the third liquid supply line 109, and after an appropriate time, the first pump 7 is opened to supply liquid to the bearing, that is, the fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6 is opened.

[0124] If the liquid level in condenser 4 is lower than the safe liquid level, the first valve 8 opens the second liquid supply line 108, and after an appropriate time, the first pump 7 is turned on to supply liquid to the bearing, that is, the fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6 is turned on.

[0125] A fourth sensor 40 is installed on the fifth liquid supply line 111 from the heat exchanger 6 to the compressor 1. The fourth sensor 40 is a flow sensor and is configured to monitor the flow rate of the bearing lubrication liquid supply.

[0126] When the liquid supply flow rate exceeds the minimum lubrication flow rate of the compressor bearing and remains so for a certain period of time, compressor 1 starts. After compressor 1 starts:

[0127] If the state of the first valve 8 is open and the third liquid supply line 109 is open, then the state of the first valve 8 remains unchanged.

[0128] If the state of the first valve 8 is that the second liquid supply line 108 is open, then the state of the first valve 8 remains unchanged; when the liquid level of the condenser 4 is greater than or equal to the safe liquid level, then the first valve 8 is switched to open the third liquid supply line 109.

[0129] Among them, the pipeline leading out of the evaporator 5 is the second liquid supply pipeline 108 from the evaporator 5 to the first valve 8; a first one-way valve 21 needs to be installed on the second liquid supply pipeline 108 to prevent the refrigerant of the condenser 4 from flowing directly into the evaporator 5 during the switching process of the first valve 8.

[0130] The fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6 includes: a first branch line 114 passing through the first pump 7 and a second branch line 115 not passing through the first pump 7.

[0131] The first branch pipe 114 passing through the first pump 7 is equivalent to the main line for supplying bearing lubricating fluid, while the second branch pipe 115 not passing through the first pump 7 is equivalent to the auxiliary line used for heat exchange to maintain the subcooling of the main line's fluid supply.

[0132] The first branch pipe 114 includes: a third branch pipe 116, a fourth branch pipe 117, a fifth branch pipe 118, and a sixth branch pipe 119; the third branch pipe 116 is equipped with a first ball valve 19, a first pump 7, and a fourth valve 20. The fourth branch pipe 117 is equipped with a second ball valve 29, a second pump 30, and a seventh valve 28. The fifth branch pipe 118 is equipped with a mechanical pressure relief valve 26. The sixth branch pipe 119 is equipped with a third ball valve 32 and an eighth valve 33, with the eighth valve 33 being closer to the first valve 8.

[0133] The first branch line 114 also includes an eleventh branch line 136, which can be considered as the main line of the differential pressure supply line.

[0134] In some embodiments, the eighth valve 33 is a one-way valve.

[0135] Under normal circumstances, the third branch pipeline 116 is in working condition. In case of an abnormality in the third branch pipeline, the liquid supply is switched to the fourth branch pipeline 117.

[0136] The second liquid supply line 108 and the third liquid supply line 109 converge at the first valve 8 and then split into two lines. One line is the main line supplying liquid for bearing lubrication, namely the first branch line 114; the other line is the auxiliary line cooling the main line to ensure that the refrigerant entering the motor is in a liquid state, namely the second branch line 115. After heat exchange in the heat exchanger 6, the refrigerant in the first branch line 114 enters the motor 15 to lubricate the front and rear bearings of the motor 15. After lubrication, the refrigerant returns to the evaporator 5 from the return pipe of the motor 15, and the refrigerant in the auxiliary line returns to the evaporator 5 after heat exchange. The main line for bearing lubrication liquid supply is equipped with a first pump liquid supply line and a differential pressure liquid supply line connected in parallel, namely the third branch line 116 and the fourth branch line 117 connected in parallel.

[0137] In some embodiments, the first pump supply pipeline is equipped with dual pumps, one for use and one for standby, which can be switched online. The first pump 7 is a variable frequency pump that can adjust the supply head and flow rate. At the same time, a mechanical pressure relief valve 26 is provided to connect the inlet and outlet of the first pump to prevent the first pump from being overloaded and burned out due to dirt and blockage of the first filter and the second filter of the main pipeline.

[0138] The opening pressure of the mechanical pressure relief valve 26 must be greater than the maximum pressure difference between the pump inlet and outlet under normal operating conditions. A fourth valve 20 must be installed before the junction of the outlet pipeline of the first pump 7 and the differential pressure supply pipeline to prevent backflow and self-circulation. A seventh valve 28 must be installed before the junction of the outlet pipeline of the second pump 30 and the differential pressure supply pipeline to prevent backflow and self-circulation. An electronic expansion valve 27 is installed in the auxiliary circuit, specifically in the second branch pipeline 115; this throttles the refrigerant in the auxiliary circuit while controlling the subcooling of the refrigerant in the main circuit.

[0139] In some embodiments, the fourth valve 20 and the seventh valve 28 are one-way valves. The first pump 7 and the second pump 30 are both refrigerant pumps.

[0140] The main functions of a ball valve include cutting off flow, distributing flow rate, and changing flow direction. It opens and closes by rotating a ball, typically by 90 degrees, but 180 or 360 degrees are also possible, thus controlling the flow of media (such as water, air, or gas). The design of ball valves makes them simple in structure, small in size, and lightweight, while also providing good sealing, easy operation, and rapid opening and closing. Furthermore, ball valves have the advantage of low fluid resistance; full-bore ball valves have virtually no flow resistance, making them suitable for applications requiring precise flow regulation and control.

[0141] Mechanical pressure relief valves are typically set with a set pressure threshold. When the system pressure exceeds this threshold, the valve automatically opens to release excess pressure until it drops to a safe level. These valves are normally closed and only open when needed. For example, in a gas extinguishing system, when the pressure in the protected area reaches or exceeds a preset value (e.g., 1000 Pa or 1100 Pa ± 50 Pa), the mechanical pressure relief valve automatically opens to ensure effective release and impregnation time of the extinguishing agent.

[0142] In some embodiments, a liquid level sensor 31 is provided in the condenser 4. During the start-up phase, the controller uses the liquid level sensor to determine the liquid level in the condenser in real time.

[0143] When the liquid level in condenser 4 is greater than or equal to the safe liquid level, the first valve opens the condenser liquid supply channel, i.e. the third liquid supply line 109. After an appropriate time, the refrigerant pump control is started, and the refrigerant pump supplies liquid to the bearing.

[0144] When the liquid level in condenser 4 is lower than the safe liquid level, the evaporator liquid supply channel, i.e. the second liquid supply line 108, is opened. After a certain period of time, the first pump control is started, and the first pump is opened to supply liquid to the bearing.

[0145] When the fluid supply flow rate exceeds the minimum lubrication flow rate of the compressor bearing and remains so for a certain period of time, compressor 1 starts. After compressor 1 starts:

[0146] If the state of the first valve 8 at this time is that the liquid supply channel of the condenser 4 is open, that is, the third liquid supply pipeline 109 from the condenser 4 to the first valve 8 is open, then the state of the first valve 8 remains unchanged.

[0147] If the state of the first valve 8 at this time is that the liquid supply channel of the evaporator 5 is open, that is, the second liquid supply pipeline 108 from the evaporator 5 to the first valve 8 is open, then when the compressor runs and the liquid level of the condenser is greater than or equal to the safe liquid level, the liquid supply will be switched to the liquid supply channel of the condenser.

[0148] In other words, the liquid supply channel of condenser 4 refers to the third liquid supply line 109 from condenser 4 to first valve 8; the liquid supply channel of evaporator 5 refers to the second liquid supply line 108 from evaporator 5 to first valve 8.

[0149] After compressor 1 starts running: the first valve 8 keeps the third liquid supply line 109 open.

[0150] After compressor 1 starts, when the pressure difference between evaporator 5 and condenser 4 is greater than or equal to the set pressure difference, the first pump 7 stops running and switches to the pressure difference supply line, i.e., the eleventh branch line 136. At this time, lubrication liquid is supplied through the pressure difference between condenser 4 and evaporator 5.

[0151] The second branch pipeline 115 is equipped with an electronic expansion valve 27. The electronic expansion valve 27 controls the refrigerant flow and throttling of the auxiliary pipeline to ensure that the refrigerant entering the motor bearing from the main pipeline is a subcooled liquid to prevent the refrigerant gas from causing cavitation on the bearing.

[0152] When the pressure difference supply flow rate is less than the minimum required flow rate under low pressure ratio operating conditions, the first pump 7 is turned on to assist in liquid supply. When the liquid level in the condenser 4 is detected to be insufficient during operation, the liquid supply is switched to the evaporator 5 through the first valve 8. At this time, the first pump 7 continues to be turned on to maintain the liquid supply state. When the liquid level in the condenser 4 is detected to be higher than the safe liquid level and remains stable for a certain period of time, the liquid supply is switched back to the condenser 4 through the first valve 8.

[0153] In some embodiments, a first filter 22 is provided in the second liquid supply line 108 from the evaporator 5 to the second valve 9; a second filter 23 is provided in the third liquid supply line 109 from the condenser 4 to the third valve 10. The input end of the first filter 22 is connected to the evaporator 5, and the output end of the first filter 22 is connected to the second valve 9.

[0154] Among them, such as Figure 8 and Figure 9 As shown, the bearing lubrication supply line is divided into two lines entering the motor. One line lubricates the front bearing of the motor, and the other lubricates the rear bearing. The lubrication line for the rear bearing is further divided into two lines: one directly connects to the bearing for lubrication, and the other connects to the rear bearing cavity. Because the pressure in the bearing cavity exerts a thrust towards the front of the motor shaft at the rear end, the pressure of the bearing lubricant supply significantly affects the axial force of the entire bearing. Therefore, by changing the magnitude of this lubricant supply pressure, the pressure in the rear bearing cavity can be altered, thereby regulating and controlling the axial force of the compressor. The specific control logic is as follows:

[0155] The axial force F of the compressor under operating conditions can be measured in real time. After obtaining the axial force F under these operating conditions, it is compared with a preset range. At the same time, the axial force from the motor to the impeller side is defined as the positive axial force, and the first fluid supply flow rate Q required for bearing fluid supply is determined. min Minimum flow rate.

[0156] The controller is configured to set a preset range, the minimum value of which is a first preset axial force Fa. min (A negative value indicates a negative axial force), the maximum value is the second preset axial force Fa. max (A positive value indicates a positive axial force); First preset axial force Fa min The minimum axial force that the bearing can withstand; the second preset axial force Fa max This represents the maximum axial force that the bearing can withstand. If the axial force from the motor to the impeller is set as positive, then the axial force in the opposite direction is negative. Here, the first preset axial force is negative, so it can be considered the minimum value, not necessarily the smallest absolute value.

[0157] During the axial force control phase, assuming the controller determines in real time that the total axial force F of the compressor is within the preset range:

[0158] If the flow rate of the bearing fluid supply is greater than or equal to the first fluid supply flow rate Q min The controller does not operate; if the flow rate of the bearing fluid supply is less than the first fluid supply flow rate Q. min The controller turns on the first pump.

[0159] During the axial force control phase, if the controller determines in real time that the total axial force of the compressor is not within the preset range:

[0160] If the total axial force F of compressor 1 is greater than or equal to the second preset axial force Fa max If the duration T is greater than or equal to the preset judgment time Tt, the controller 2 reduces the second axial force.

[0161] If the total axial force F of compressor 1 is greater than or equal to the second preset axial force Fa max If the duration T is less than the preset judgment time Tt, the controller 2 will not take any action.

[0162] If the total axial force F of compressor 1 is less than or equal to the first preset axial force Fa min If the duration T is greater than or equal to the preset judgment time Tt, the controller 2 increases the second axial force.

[0163] If the total axial force F of compressor 1 is less than or equal to the first preset axial force Fa min If the duration T is less than the preset judgment time Tt, the controller 2 will not take any action.

[0164] In summary, the following further explains how the controller 2 monitors and controls the axial force of the compressor 1 during the operation of the refrigeration system 100.

[0165] S1. If the controller detects that the total axial force F of the compressor is greater than the first preset axial force Fa... min Less than the second preset axial force Fa max In the case of Fa min <F<Fa max And the flow rate Q of the bearing fluid supply is greater than or equal to the first fluid supply flow rate Q. min That is, Q≥Q min When the axial force under the current operating condition is within the preset range, and the axial force and the flow rate Q of the bearing fluid supply meet the operating requirements, the controller maintains the current state and does not take any action.

[0166] S2. If the controller detects that the total axial force F of the compressor is greater than the first preset axial force Fa... min Less than the second preset axial force Fa max In the case of Fa min <F<Fa max Furthermore, the flow rate Q of the bearing fluid supply is less than the first fluid supply flow rate Q. min Q min When the axial force under the current operating condition is within the preset range, but the flow rate Q of the bearing fluid supply does not meet the operating requirements, if the first pump is not turned on, then turn on the first pump; if the first pump is turned on, then increase the operating frequency of the first pump to increase the fluid supply flow rate.​

[0167] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and specifically includes:

[0168] S31. If the controller detects that the total axial force F of the compressor is greater than or equal to the second preset axial force Fa... max Furthermore, the duration T is greater than or equal to the preset judgment time Tt, and the flow rate Q of the bearing fluid supply is greater than or equal to the first fluid supply flow rate Q. min That is, F≥Fa max And T≥T t Q≥Q min If the positive axial force is excessive and this excessive axial force persists for a certain period of time, then to reduce the positive axial force in the compressor, it is necessary to reduce the pressure in the rear bearing chamber of the compressor. Therefore, the controller will detect the bearing fluid supply status and perform the following actions in sequence:

[0169] S311. If the liquid is supplied by the first pump and the liquid drawer is a high-pressure liquid from the condenser, then first reduce the frequency of the first pump to reduce the supply pressure. If the supply flow rate reaches the first supply flow rate Q... min Presatisfied Fa min <F<Fa max If the condition is met, the operation stops; if not, the first valve 8 is controlled to switch the liquid intake point to the evaporator, thereby reducing the liquid supply pressure. If the total axial force of the compressor at this time meets Fa... min <F<Fa max If the compressor fails to complete its operation, it will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control in order to reduce the total axial force.

[0170] Unloading the compressor load means reducing the compressor speed, reducing the unit's cooling capacity, and reducing the refrigerant circulation to reduce the total axial force.

[0171] S312. If the first pump is supplying liquid to the evaporator at this time, adjust the liquid supply pressure of the first pump to ensure the liquid supply flow rate, i.e., Q ≥ Q. min To reduce the axial force to within the allowable range, if the total axial force of the compressor at this time satisfies Fa... min <F<Fa max If the axial force is too high, the operation will stop; if the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0172] S313. If the liquid supply is based on the differential pressure of the condenser, switch the liquid intake point to the evaporator and supply liquid through the first pump. Adjust the liquid supply pressure of the first pump to reduce the axial force to within the allowable range while ensuring the liquid supply flow rate. If the total axial force of the compressor satisfies Fa at this time... min <F<Fa max If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0173] It should be noted that PID control is a classic control theory that achieves precise control of the controlled object through a combination of proportional (P), integral (I), and derivative (D) components. This control method is widely used in various automatic control systems due to its simplicity, effectiveness, and good versatility.

[0174] The proportional (P) terminator changes the control input proportionally to the magnitude of the error signal to quickly respond to changes in the system. The integral (I) terminator accumulates the error to eliminate steady-state error. The derivative (D) terminator predicts the future state of the system by controlling the rate of change of the error, thus making adjustments in advance. The combined use of these three control methods enables PID control to effectively control various dynamically changing systems.

[0175] PID control, as a fundamental control strategy, is one of the most commonly used control methods in automatic control systems due to its simplicity and effectiveness. By rationally configuring and adjusting the proportional, integral, and derivative components, effective control of various complex systems can be achieved.

[0176] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0177] S32. If the controller detects that the total axial force F of the compressor is greater than or equal to the second preset axial force Fa... max And the duration T is greater than or equal to the preset judgment time Tt, and the flow rate Q of the bearing fluid supply is less than the first fluid supply flow rate Q. min That is, F≥Fa max And T≥T t Q min If the flow rate Q of the bearing fluid supply does not meet the operating requirements, and if the first pump is not turned on, then turn on the first pump; if the first pump is already turned on, then increase the operating frequency of the first pump to increase the fluid supply flow rate until Q ≥ Q. min ​The current operating condition shows excessive positive axial force, which has persisted for a certain period. To reduce the positive axial force in the compressor, it is necessary to reduce the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform the following actions in sequence:

[0178] S311. If the liquid is supplied by the first pump and the liquid drawer is a high-pressure liquid from the condenser, then first reduce the frequency of the first pump to reduce the supply pressure. If the supply flow rate reaches the first supply flow rate Q... min Presatisfied Fa min <F<Fa max If the condition is met, the operation stops; if not, the first valve 8 is controlled to switch the liquid intake point to the evaporator, thereby reducing the liquid supply pressure. If the total axial force of the compressor at this time meets Fa... min <F<Fa max If the compressor fails to operate, the operation will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0179] S312. If the first pump is supplying liquid to the evaporator at this time, adjust the liquid supply pressure of the first pump to reduce the axial force to within the allowable range while ensuring the liquid supply flow rate. If the total axial force of the compressor at this time satisfies Fa... min <F<Fa max If the axial force is too high, the operation will stop; if the total axial force of the compressor is still too high, the total axial force of the compressor will be appropriately unloaded according to PID control.

[0180] S313. If the liquid supply is based on the differential pressure of the condenser, switch the liquid intake point to the evaporator and supply liquid through the first pump. Adjust the liquid supply pressure of the first pump to reduce the axial force to within the allowable range while ensuring the liquid supply flow rate. If the total axial force of the compressor satisfies Fa at this time... min <F<Fa max If the axial force is too high, the operation will stop; if the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0181] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0182] S33. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min And the duration T is greater than or equal to the preset judgment time Tt, i.e., F≤Fa min And the duration of this state is T≥Tt Bearing fluid supply flow rate Q≥Q min The current operating condition shows an excessive negative axial force that has persisted for a period of time. To reduce the negative axial force in the compressor, it is necessary to increase the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform actions in the following sequence:

[0183] S331. If the first pump is supplying liquid and the liquid sampling point is the high-pressure liquid of the condenser, then first increase the frequency of the first pump to increase the liquid supply pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0184] S332. If the first pump is supplying liquid to the evaporator at this time, adjust and increase the liquid supply pressure of the first pump to reduce the axial force to within the allowable range. If the axial force returns to the allowable range at this time, stop the operation. If F ≤ Fa min The system detects whether the liquid level in the condenser is higher than the minimum set liquid level. If it is, the liquid sampling point will be changed to the condenser by adjusting the first valve, and the liquid supply pressure of the first pump will be adjusted to adjust the axial force to the allowable range. If the liquid level in the condenser is lower than the minimum set liquid level, the total axial force of the compressor will be appropriately unloaded according to the PID control.

[0185] S333. If the liquid supply is based on the differential pressure at which the condenser draws liquid, then the first pump is turned on to increase the liquid supply volume and pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0186] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0187] S34. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min And the duration T is greater than or equal to the preset judgment time Tt, i.e., F≤Fa min And the duration of this state is T≥T t Bearing fluid supply flow rate Q min ​If the flow rate Q of the bearing fluid supply does not meet the operating requirements, turn on the first pump if it is not turned on, or increase the operating frequency of the first pump to increase the fluid supply flow rate until Q ≥ Q. min At this point, F ≤ Fa min Furthermore, the duration of this state is T≥Tt, and the bearing fluid supply flow rate is Q≥Q min The current operating condition shows an excessive negative axial force that has persisted for a period of time. To reduce the negative axial force in the compressor, it is necessary to increase the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform actions in the following sequence:

[0188] S331. If the first pump is supplying liquid and the liquid sampling point is the high-pressure liquid of the condenser, then first increase the frequency of the first pump to increase the liquid supply pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0189] S332. If the first pump is supplying liquid to the evaporator at this time, adjust and increase the liquid supply pressure of the first pump to reduce the axial force to within the allowable range. If the axial force returns to the allowable range at this time, stop the operation. If F ≤ Fa min The system detects whether the liquid level in the condenser is higher than the minimum set liquid level. If it is, the liquid sampling point will be changed to the condenser by adjusting the first valve, and the liquid supply pressure of the first pump will be adjusted to adjust the axial force to the allowable range. If the liquid level in the condenser is lower than the minimum set liquid level, the compressor load will be appropriately unloaded according to PID control.

[0190] S333. If the liquid supply is based on the differential pressure at which the condenser draws liquid, then the first pump is turned on to increase the liquid supply volume and pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0191] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0192] S35. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min Or the total axial force F of the compressor is greater than or equal to the first preset axial force Fa. minAnd the duration T is less than the preset judgment time Tt, that is, F≤Fa min or F≥Fa max However, the duration of this state is T < Tt. The excessive positive or negative axial force under the current operating condition is only a short-term fluctuation. In order to avoid frequent adjustment, over-adjustment, and erroneous adjustment of the first pump and the first valve in the system, the refrigeration system will maintain the current state and not take any action in this situation.

[0193] In some embodiments, such as Figure 10 As shown, there is a connecting pipe 113 from the condenser 4 to the evaporator 5. A hot gas valve HV is installed on the connecting pipe 113. The hot gas valve HV is used to balance the pressure and can also be used to balance the refrigerant.

[0194] A gas supply valve GV is installed in the gas supply line 104 from the economizer 3 to the compressor 1; a first electric valve EV1 is installed in the first liquid supply line 106 from the condenser 4 to the economizer 3; and a second electric valve EV2 is installed in the liquid return line 107 from the economizer 3 to the evaporator 5.

[0195] In some embodiments, such as Figure 11 As shown, the first liquid supply line 106 from the condenser 4 to the economizer 3 is also provided with a first orifice plate 34, and the return liquid line 107 from the economizer 3 to the evaporator 5 is also provided with a second orifice plate 35.

[0196] In some embodiments, such as Figure 12 As shown, the fifth liquid supply line 111 from the heat exchanger 6 to the compressor 1 includes: a seventh branch line 130, an eighth branch line 131 and a sixth liquid supply line 132.

[0197] The seventh branch line 130 is equipped with a first sensor 36, the eighth branch line 131 is equipped with a precision filter 37, and the sixth liquid supply line 132 is equipped with a second sensor 38 and a third sensor 39.

[0198] The fourth sensor 40 is installed on the sixth liquid supply line 132.

[0199] In some embodiments, the first sensor 36 is a differential pressure sensor, the second sensor 38 is a pressure sensor, and the third sensor 39 is a temperature sensor.

[0200] The sixth liquid supply line 132 includes: a ninth branch line 133 and a tenth branch line 134. The ninth branch line 133 corresponds to... Figure 9 One of the lubrication lines is the front bearing of the motor, and the tenth branch pipe 134 corresponds to it. Figure 9 One of the lubricating motor's rear bearings.

[0201] In some embodiments, such as Figure 13As shown, the sixth liquid supply line 132 is also equipped with a first sight glass 41, and the fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6 is also equipped with a second sight glass 42.

[0202] In some embodiments, the bearing lubrication circuit 102 in the refrigeration system further includes a low-pressure return line 135 from the compressor 1 to the evaporator 5.

[0203] Option 2: In some embodiments, such as Figure 14 As shown, the refrigeration system 100 also includes: a refrigeration cycle circuit 101, a bearing lubrication circuit 102, a first pump 7, a second valve 9, and a third valve 10; the second valve 9 is connected to the evaporator 5, and the third valve 10 is connected to the condenser 4; one end of the first pump 7 is connected to the second valve 9 and the third valve 10, and the other end of the first pump 7 is connected to the heat exchanger 6.

[0204] The refrigeration cycle circuit 101 includes: a suction line 103 from the evaporator 5 to the compressor 1; a make-up gas line 104 from the economizer 3 to the compressor 1; a discharge line 105 from the compressor 1 to the condenser 4; a first liquid supply line 106 from the condenser 4 to the economizer 3; a liquid return line 107 from the economizer 3 to the evaporator 5; and a connecting line 113 from the condenser 4 to the evaporator 5.

[0205] The bearing lubrication circuit 102 includes: a second liquid supply line 108 from the evaporator 5 to the second valve 9; a third liquid supply line 109 from the condenser 4 to the third valve 10; a fourth liquid supply line 110 from the second valve 9 or the third valve 10 to the heat exchanger 6; a fifth liquid supply line 111 from the heat exchanger 6 to the compressor 1; and a return gas line 112 from the heat exchanger 6 to the evaporator 5.

[0206] The refrigeration cycle circuit 101 is the same as that in Scheme 1 above, and will not be described again here.

[0207] The bearing lubrication circuit 102 refers to: a second liquid supply line 108 from the evaporator 5 to the first valve 8 and a third liquid supply line 109 from the condenser 4 to the first valve 8; both lines are connected to the first valve 8. Liquid refrigerant in the condenser 4 or evaporator 5 flows through the first valve 8 and is transferred to the heat exchanger 6 through a fourth liquid supply line 110 from the first valve 8 to the heat exchanger 6.

[0208] In some embodiments, a first filter 22 is provided in the second liquid supply line 108 from the evaporator 5 to the second valve 9; a second filter 23 is provided in the third liquid supply line 109 from the condenser 4 to the third valve 10. The input end of the first filter 22 is connected to the evaporator 5, and the output end of the first filter 22 is connected to the second valve 9.

[0209] In other words, compared with Scheme 1, the first valve 8 is changed to the second valve 9 and the third valve 10; the first valve 8 is a three-way valve, and the second valve 9 and the third valve 10 are two-way valves.

[0210] Option 3: In some embodiments, such as Figure 15 As shown, the refrigeration system 100 also includes: a refrigeration cycle circuit 101, a bearing lubrication circuit 102, a first pump 7, a fifth valve 24, and a sixth valve 25; the fifth valve 24 and the sixth valve 25 are connected in parallel; one end of the first pump 7 is connected to the fifth valve 24 and the sixth valve 25, and the other end of the first pump 7 is connected to the heat exchanger 6.

[0211] In some embodiments, the fifth valve 24 is an electronic expansion valve, and the sixth valve 25 is an electronic shut-off valve.

[0212] The refrigeration cycle circuit 101 includes: a suction line 103 from the evaporator 5 to the compressor 1; a make-up gas line 104 from the economizer 3 to the compressor 1; a discharge line 105 from the compressor 1 to the condenser 4; a first liquid supply line 106 from the condenser 4 to the economizer 3; a liquid return line 107 from the economizer 3 to the evaporator 5; and a connecting line 113 from the condenser 4 to the evaporator 5.

[0213] The bearing lubrication circuit 102 includes: a fourth liquid supply line 110 from the condenser 4 to the heat exchanger 6; a fifth liquid supply line 111 from the heat exchanger 6 to the compressor 1; and a return gas line 112 from the heat exchanger 6 to the evaporator 5.

[0214] The refrigeration cycle circuit 101 is the same as that in Scheme 1 above, and will not be described again here.

[0215] In some embodiments, a second filter 23 is provided in the third liquid supply line 109 from the condenser 4 to the third valve 10.

[0216] In other words, an electronic expansion valve, i.e., the fifth valve 24, is added to the main bearing liquid supply line, specifically the fourth liquid supply line 110 from condenser 4 to heat exchanger 6; simultaneously, an electric shut-off valve, i.e., the sixth valve 25, is connected in parallel. The electronic expansion valve reduces the liquid supply pressure, thus replacing the low-pressure function of the evaporator. By default, the electric shut-off valve is open, and the electronic expansion valve is closed. The specific control method is as follows:

[0217] S1. If the controller detects that the total axial force F of the compressor is greater than the first preset axial force Fa... min Less than the second preset axial force Fa max In the case of Fa min <F<Fa max And the flow rate Q of the bearing fluid supply is greater than or equal to the first fluid supply flow rate Q. min That is, Q≥Q minWhen the axial force under the current operating condition is within the preset range, and the axial force and the flow rate Q of the bearing fluid supply meet the operating requirements, the controller maintains the current state and does not take any action.

[0218] S2. If the controller detects that the total axial force F of the compressor is greater than the first preset axial force Fa... min Less than the second preset axial force Fa max In the case of Fa min <F<Fa max Furthermore, the flow rate Q of the bearing fluid supply is less than the first fluid supply flow rate Q. min Q min When the axial force under the current operating condition is within the preset range, but the flow rate Q of the bearing fluid supply does not meet the operating requirements, if the first pump is not turned on, then turn on the first pump; if the first pump is turned on, then increase the operating frequency of the first pump to increase the fluid supply flow rate.

[0219] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and specifically includes:

[0220] S31. If the controller detects that the total axial force F of the compressor is greater than or equal to the second preset axial force Fa... max Furthermore, the duration T is greater than or equal to the preset judgment time Tt, and the flow rate Q of the bearing fluid supply is greater than or equal to the first fluid supply flow rate Q. min That is, F≥Fa max And T≥T t Q≥Q min If the positive axial force is excessive and this excessive axial force persists for a certain period of time, then to reduce the positive axial force in the compressor, it is necessary to reduce the pressure in the rear bearing chamber of the compressor. Therefore, the controller will detect the bearing fluid supply status and perform the following actions in sequence:

[0221] S314. If the liquid is supplied by the first pump and the liquid sampling point is a high-pressure liquid from the condenser, then first reduce the frequency of the first pump to reduce the supply pressure. If the supply flow rate reaches the first supply flow rate Q... min Presatisfied Fa min <F<Fa max If the condition is met, the operation stops; if not, the fifth valve 24 is opened and the sixth valve 25 is closed. The liquid supply pressure is reduced by adjusting the opening of the fifth valve 24. If the total axial force of the compressor meets Fa at this time... min <F<Fa max ​If the compressor fails to operate, the operation will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0222] S315. If the liquid supply is based on the differential pressure of the condenser, open the fifth valve 24 and close the sixth valve 25. Reduce the supply pressure by adjusting the opening of the fifth valve 24. If the supply flow rate reaches the first supply flow rate Q... min The total axial force Fa of the compressor is satisfied. min <F<Fa max If the compressor fails to operate, the operation will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0223] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0224] S32. If the controller detects that the total axial force F of the compressor is greater than or equal to the second preset axial force Fa... max And the duration T is greater than or equal to the preset judgment time Tt, and the flow rate Q of the bearing fluid supply is less than the first fluid supply flow rate Q. min That is, F≥Fa max And T≥T t Q min If the flow rate Q of the bearing fluid supply does not meet the operating requirements, and if the first pump is not turned on, then turn on the first pump; if the first pump is already turned on, then increase the operating frequency of the first pump to increase the fluid supply flow rate until Q ≥ Q. min The current operating condition shows excessive positive axial force, which has persisted for a certain period. To reduce the positive axial force in the compressor, it is necessary to reduce the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform the following actions in sequence:

[0225] S314. If the liquid is supplied by the first pump and the liquid sampling point is a high-pressure liquid from the condenser, then first reduce the frequency of the first pump to reduce the supply pressure. If the supply flow rate reaches the first supply flow rate Q... min Presatisfied Fa min <F<Fa max If the condition is met, the operation stops; if not, the fifth valve 24 is opened and the sixth valve 25 is closed. The liquid supply pressure is reduced by adjusting the opening of the fifth valve 24. If the total axial force of the compressor meets Fa at this time... min <F<Fa max If the compressor fails to operate, the operation will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.​

[0226] S315. If the liquid supply is based on the differential pressure of the condenser, open the fifth valve 24 and close the sixth valve 25. Reduce the supply pressure by adjusting the opening of the fifth valve 24. If the supply flow rate reaches the first supply flow rate Q... min The total axial force Fa of the compressor is satisfied. min <F<Fa max If the compressor fails to operate, the operation will stop. If the total axial force of the compressor is still too high, the compressor load will be appropriately unloaded according to PID control.

[0227] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0228] S33. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min And the duration T is greater than or equal to the preset judgment time Tt, i.e., F≤Fa min And the duration of this state is T≥T t Bearing fluid supply flow rate Q≥Q min The current operating condition shows an excessive negative axial force that has persisted for a period of time. To reduce the negative axial force in the compressor, it is necessary to increase the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform actions in the following sequence:

[0229] S334. If the sixth valve 25 is closed and the fifth valve 24 is open at this time, then open the sixth valve 25 and close the fifth valve 24, if Fa is satisfied. min <F<Fa max If so, then the action will stop.

[0230] S331. If the first pump is supplying liquid and the liquid sampling point is the high-pressure liquid of the condenser, then first increase the frequency of the first pump to increase the liquid supply pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0231] S333. If the liquid supply is based on the differential pressure at which the condenser draws liquid, then the first pump is turned on to increase the liquid supply volume and pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0232] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa... min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0233] S34. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min And the duration T is greater than or equal to the preset judgment time Tt, i.e., F≤Fa min And the duration of this state is T≥T t Bearing fluid supply flow rate Q min If the flow rate Q of the bearing fluid supply does not meet the operating requirements, turn on the first pump if it is not turned on, or increase the operating frequency of the first pump to increase the fluid supply flow rate until Q ≥ Q. min At this point, F ≤ Fa min Furthermore, the duration of this state is T≥Tt, and the bearing fluid supply flow rate is Q≥Q min The current operating condition shows an excessive negative axial force that has persisted for a period of time. To reduce the negative axial force in the compressor, it is necessary to increase the pressure in the rear bearing chamber. Therefore, the controller will detect the bearing fluid supply status and perform actions in the following sequence:

[0234] S334. If the sixth valve 25 is closed and the fifth valve 24 is open at this time, then open the sixth valve 25 and close the fifth valve 24, if Fa is satisfied. min <F<Fa max If so, then the action will stop.

[0235] S331. If the first pump is supplying liquid and the liquid sampling point is the high-pressure liquid of the condenser, then first increase the frequency of the first pump to increase the liquid supply pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0236] S333. If the liquid supply is based on the differential pressure at which the condenser draws liquid, then the first pump is turned on to increase the liquid supply volume and pressure. If Fa is satisfied before the first pump reaches its maximum frequency... min <F<Fa max If the condition is met, the operation will stop; if not, the compressor load will be appropriately unloaded according to PID control.

[0237] S3. If the controller detects that the total axial force F of the compressor does not meet the preset range, i.e., Fa...​min <F<Fa max When the conditions are not met, meaning the axial force under the current operating conditions is not within the preset range, the controller needs to take action. The action varies depending on the situation, and may include:

[0238] S35. If the controller detects that the total axial force F of the compressor is less than or equal to the first preset axial force Fa... min Or the total axial force F of the compressor is greater than or equal to the second preset axial force Fa. max And the duration T is less than the preset judgment time Tt, that is, F≤Fa min or F≥Fa max However, the duration of this state is T < Tt. The excessive positive or negative axial force under the current operating condition is only a short-term fluctuation. In order to avoid frequent adjustment, over-adjustment, and erroneous adjustment of the first pump and the first valve in the system, the refrigeration system will maintain the current state and not take any action in this situation.

[0239] Reference Figures 13-15 It should be noted that Scheme 1 is the basic scheme. Scheme 2 is based on Scheme 1, but the first valve 8 is removed and replaced with the second valve 9 and the third valve 10. Scheme 3 is based on Scheme 2, but the second liquid supply line 108 from the evaporator 5 to the second valve 9 is removed, and the second valve 9 and the third valve 10 are not needed. An electronic expansion valve, i.e., the fifth valve 24, is added to the fourth liquid supply line 110 from the condenser 4 to the heat exchanger 6. At the same time, an electric shut-off valve, i.e., the sixth valve 25, is connected in parallel.

[0240] It should be noted that the above actions of opening the valve, closing the valve, and adjusting the valve can all be controlled and adjusted using controller 2.

[0241] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. An air conditioning system, characterized in that, The air conditioning system includes: Refrigeration system, the refrigeration system comprising: A compressor, wherein multiple axial forces are generated internally, and the sum of these multiple axial forces constitutes a total axial force; the compressor includes: An impeller configured to generate a first axial force during operation of the compressor, the magnitude of which can be changed by altering the diameter of the rear end of the impeller; A bearing system connected to the impeller; the rear cavity of the bearing system generates a second axial force. A controller configured to adjust a second axial force, ensuring that the magnitude of the total axial force of the compressor is within a preset range; The preset range refers to the range of axial forces that the bearing system can withstand.

2. The air conditioning system according to claim 1, characterized in that, The bearing system includes: Shaft, which is connected to the impeller; The bearing comprises: The bearing inner ring is connected to the shaft. Bearing outer ring; A rolling element, wherein the rolling element is disposed between the inner ring and the outer ring of the bearing; support frame Two elastic rings are disposed between the support frame and the outer ring of the bearing, and the elastic rings are configured to detect the magnitude of the total axial force of the compressor.

3. The air conditioning system according to claim 2, characterized in that, The two elastic rings are also connected to the controller; the two elastic rings are symmetrically distributed. The elastic ring is also configured to transmit the detected total axial force to the controller; The controller is also configured to adjust the magnitude of the second axial force according to the magnitude of the total axial force.

4. The air conditioning system according to claim 1, characterized in that, The refrigeration system also includes: An economizer, which is connected to the compressor; A condenser, which is connected to the compressor and also to the economizer; An evaporator, which is connected to the compressor, as well as to the economizer and the condenser; A heat exchanger, the input end of which is connected to the condenser and the evaporator; the output end of which is connected to the compressor.

5. The air conditioning system according to claim 4, characterized in that, The refrigeration system further includes: a refrigeration circulation loop, a bearing lubrication loop, a first pump, and a first valve; the first pump is disposed between the first valve and the heat exchanger; the first valve is connected to the condenser and the evaporator; The refrigeration cycle circuit includes: a suction line from the evaporator to the compressor; a make-up line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator. The bearing lubrication circuit includes: a second liquid supply line from the evaporator to the first valve; a third liquid supply line from the condenser to the first valve; a fourth liquid supply line from the first valve to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

6. The air conditioning system according to claim 4, characterized in that, The refrigeration system further includes: a refrigeration cycle loop, a bearing lubrication loop, a first pump, a second valve, and a third valve; the second valve is connected to the evaporator, and the third valve is connected to the condenser; one end of the first pump is connected to the second valve and the third valve, and the other end of the first pump is connected to the heat exchanger; The refrigeration cycle circuit includes: a suction line from the evaporator to the compressor; a make-up line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator. The bearing lubrication circuit includes: a second liquid supply line from the evaporator to the second valve; a third liquid supply line from the condenser to the third valve; a fourth liquid supply line from the second valve or the third valve to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

7. The air conditioning system according to claim 4, characterized in that, The refrigeration system further includes: a refrigeration cycle loop, a bearing lubrication loop, a first pump, a fifth valve, and a sixth valve; the fifth valve and the sixth valve are connected in parallel; one end of the first pump is connected to the fifth valve and the sixth valve, and the other end of the first pump is connected to the heat exchanger. The refrigeration cycle circuit includes: a suction line from the evaporator to the compressor; a make-up line from the economizer to the compressor; a discharge line from the compressor to the condenser; a first liquid supply line from the condenser to the economizer; a liquid return line from the economizer to the evaporator; and a connecting line from the condenser to the evaporator. The bearing lubrication circuit includes: a fourth liquid supply line from the condenser to the heat exchanger; a fifth liquid supply line from the heat exchanger to the compressor; and a return gas line from the heat exchanger to the evaporator.

8. The air conditioning system according to any one of claims 5 to 7, characterized in that, The controller's control phases include: an axial force testing phase and an axial force control phase; During the axial force test phase, the controller tests and acquires the total axial force of the compressor; During the axial force control phase, the controller determines in real time whether the total axial force of the compressor is within a preset range; if so, no action is taken; if not, the controller controls the input of the magnitude of the second axial force to ensure that the total axial force of the compressor is within the preset range.

9. The air conditioning system according to claim 8, characterized in that, The controller is also configured to set the preset range, wherein the minimum value of the preset range is a first preset axial force and the maximum value is a second preset axial force; The first preset axial force is the minimum value of the axial force borne by the bearing system; The second preset axial force is the maximum value of the axial force borne by the bearing system.

10. The air conditioning system according to claim 9, characterized in that, During the axial force control phase, when the controller determines in real time that the total axial force of the compressor is within a preset range; If the flow rate of the fluid supplied to the bearing system is greater than or equal to the first fluid supply flow rate, the controller will not take any action; If the flow rate of the fluid supplied to the bearing system is less than the first fluid supply flow rate, the controller turns on the first pump; During the axial force control phase, when the controller determines in real time that the total axial force of the compressor is not within the preset range; If the total axial force of the compressor is greater than or equal to the second preset axial force, and the duration is greater than or equal to the preset determination time, the controller reduces the second axial force; If the total axial force of the compressor is greater than or equal to the second preset axial force, and the duration is less than the preset determination time, the controller will not take any action. If the total axial force of the compressor is less than or equal to the first preset axial force, and the duration is greater than or equal to the preset determination time, the controller increases the second axial force; if the total axial force of the compressor is less than or equal to the first preset axial force, and the duration is less than the preset determination time, the controller does not take any action.

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