Centrifugal heat pump unit and air conditioning unit

Abstract

The invention discloses a centrifugal heat pump unit and an air conditioning unit, and the centrifugal heat pump unit comprises an evaporator which is provided with a first air outlet and a second air outlet; the steam generator is provided with a third air outlet; the multi-stage compressor unit is connected between the first air outlet and the steam generator; the boosting device comprises a driving side and a compression side, the driving side is communicated with the third air outlet, and the compression side is connected with the first air outlet and the second air outlet. Water vapor discharged from the third air outlet of the steam generator flows to the pressure boosting device, and then the pressure boosting device absorbs a low-pressure gaseous refrigerant discharged from the second air outlet and compresses the low-pressure gaseous refrigerant to form a high-pressure gaseous refrigerant; and then the high-pressure gaseous refrigerant is sent back to the first air outlet and mixed with the low-pressure gaseous refrigerant discharged from the first air outlet to enter the multi-stage compressor unit, so that the air inlet pressure of the multi-stage compressor unit is improved, and the compression ratio of the multi-stage compressor unit is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of heat pump systems, and particularly to a centrifugal heat pump unit and an air conditioner unit. Background Art

[0002] With the development of centrifugal heat pump units, the demand for them in the industrial environment is no longer just to output high-temperature hot water. With the development of the food industry and industry, the demand for water vapor is becoming more and more prominent. Originally, water vapor was only obtained by burning boilers, but the efficiency of obtaining steam by burning boilers is low and the energy consumption is large. Obtaining steam through centrifugal heat pump units has become a new option.

[0003] It is extremely difficult to convert water into water vapor in a centrifugal heat pump unit and there are many problems to be solved. Because the steam to be generated often exceeds 100°C, the exhaust temperature and pressure of the unit are extremely high. This requires the compressor to boost the pressure of the gaseous refrigerant in the evaporator higher, that is, a larger compression ratio. A large compression ratio means that the compressor needs to operate at a high load. Long-term high-load operation will shorten the life of the compressor and increase the risk of failure. Moreover, as the system temperature continues to rise, the energy efficiency ratio of the unit will decrease, resulting in increased energy consumption and affecting the overall efficiency. In addition, a large compression ratio means large system pressure fluctuations, affecting the stability of the compressor operation. Summary of the Invention

[0004] The present invention provides a centrifugal heat pump unit and an air conditioner unit for solving the problems in the prior art that the pressure at the suction port of the compressor is low and the compression ratio of the compressor is large.

[0005] The technical solution of the present invention is a centrifugal heat pump unit, including:

[0006] An evaporator, which is respectively provided with a first air outlet and a second air outlet;

[0007] A steam generator, which is provided with a third air outlet;

[0008] A multi-stage compressor unit, which is connected between the first air outlet and the steam generator;

[0009] A boosting device, which includes a driving side and a compression side. The driving side communicates with the third air outlet, and the compression side is respectively connected to the first air outlet and the second air outlet.

[0010] Further, the centrifugal heat pump unit further includes a water storage device. The inlet side of the water storage device communicates with the compression side of the boosting device, and the outlet side of the water storage device communicates with the water replenishing port of the steam generator through a water pump.

[0011] Furthermore, the boosting device includes a housing, and the housing is axially provided with a sealed driving space and a compression space side by side, and the two spaces are separated by a partition board;

[0012] The intake side of the driving space communicates with the third air outlet, the intake side of the compression space communicates with the second air outlet, and the outlet side of the compression space communicates with the first air outlet;

[0013] A driving turbine impeller is arranged in the driving space, a gas compression turbine impeller is arranged in the compression space, the gas compression turbine impeller is linked with the driving turbine impeller through a coupling, and the coupling penetrates through the partition board in a matching manner.

[0014] Furthermore, sealing components are respectively and matchingly installed on both sides of the partition board penetrated by the coupling.

[0015] Furthermore, a first electric valve is arranged on the pipeline between the driving side of the boosting device and the third air outlet, and the first electric valve is used for controlling the steam flow rate entering the driving side;

[0016] A second electric valve is arranged on the pipeline between the compression side of the boosting device and the second air outlet, and the second electric valve is used for controlling the gaseous refrigerant flow rate entering the compression side.

[0017] Furthermore, the multi-stage compressor unit includes a first-stage compressor and a second-stage compressor;

[0018] The input end of the first-stage compressor communicates with the first air outlet, the output end of the first-stage compressor communicates with the input end of the second-stage compressor, and the output end of the second-stage compressor communicates with the refrigerant input side of the steam generator.

[0019] Furthermore, a first pressure sensor is arranged on the pipeline between the output end of the first-stage compressor and the input end of the second-stage compressor, and the first pressure sensor is used for detecting the refrigerant pressure output by the first-stage compressor;

[0020] A second pressure sensor is arranged on the pipeline between the output end of the second-stage compressor and the input end of the steam generator, and the second pressure sensor is used for detecting the refrigerant pressure output by the second-stage compressor.

[0021] Furthermore, a gas-liquid filtering component is horizontally covered along the length direction of the upper part of the evaporator, and the gas-liquid filtering component divides the evaporator into a gas storage cavity and a liquid storage cavity;

[0022] The two ends of the gas storage cavity along its length direction are respectively provided with a first air outlet and a second air outlet.

[0023] Further, the refrigerant output side of the steam generator communicates with the liquid storage cavity through a throttling device.

[0024] The present invention also provides an air conditioning unit, which includes the above-mentioned centrifugal heat pump unit.

[0025] Compared with the prior art, the present invention has at least the following beneficial effects:

[0026] In the present invention, the water vapor discharged from the third air outlet of the steam generator flows to the compression side of the boosting device, and then the compression side drives the driving side to absorb the low-pressure gaseous refrigerant discharged from the second air outlet. Then, the driving side compresses the low-pressure gaseous refrigerant to form a high-pressure gaseous refrigerant. Then, the driving side sends the high-pressure gaseous refrigerant back to the first air outlet so that the high-pressure gaseous refrigerant and the low-pressure gaseous refrigerant discharged from the first air outlet are mixed and then enter the multi-stage compressor unit. Since the pressure of the mixed gaseous refrigerant is higher than the pressure of the gaseous refrigerant discharged from the first air outlet, the intake pressure of the multi-stage compressor unit is increased, thereby reducing the compression ratio of the multi-stage compressor unit, improving the operating stability of the multi-stage compressor unit, reducing the load of the multi-stage compressor unit, and extending the service life of the multi-stage compressor unit; and increasing the intake pressure can also increase the flow rate of the refrigerant flowing into the multi-stage compressor unit, thereby improving the heating effect of the centrifugal heat pump unit. Description of the Drawings

[0027] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the technical field to which this invention belongs; the terms used in the description of the present application in the specification are only for the purpose of describing specific embodiments and are not intended to limit the present invention; the terms "including" and "having" and any variations thereof in the specification and claims of the present invention and the above description of the drawings are intended to cover non-exclusive inclusion. The terms "first", "second", etc. in the specification and claims of the present invention or the above drawings are used to distinguish different objects and are not used to describe a specific order.

[0028] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following will briefly introduce the drawings required for use in the embodiments or the description of the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0029] Figure 1 Schematic diagram of the first centrifugal heat pump unit proposed by the present invention;

[0030] Figure 2 Schematic diagram of the flow of refrigerant and water vapor in the first centrifugal heat pump unit proposed by the present invention;

[0031] Figure 3 Partial internal schematic diagram of the boosting device proposed by the present invention;

[0032] Figure 4 Schematic diagram of the second centrifugal heat pump unit proposed by the present invention;

[0033] Figure 5 Schematic diagram of the flow of refrigerant and water vapor in the second centrifugal heat pump unit proposed by the present invention;

[0034] Figure 6 Schematic diagram of the third centrifugal heat pump unit proposed by the present invention;

[0035] Figure 7 Schematic diagram of the flow of refrigerant and water vapor in the third centrifugal heat pump unit proposed by the present invention.

[0036] Reference numerals:

[0037] 10. Evaporator; 101. First air outlet; 102. Second air outlet; 103. Gas-liquid filtration assembly; 104. Gas storage cavity; 105. Liquid storage cavity;

[0038] 20. Steam generator; 201. Third air outlet; 202. Water replenishing port;

[0039] 30. Multi-stage compressor unit; 301. First-stage compressor; 302. Second-stage compressor;

[0040] 40. Boosting device; 401. Housing; 402. Driving space; 403. Compression space; 404. Partition; 405. Driving turbine impeller; 406. Compressing turbine impeller; 407. Coupling; 408. Sealing assembly;

[0041] 50. Water storage device;

[0042] 60. First electric valve;

[0043] 70. Second electric valve;

[0044] 80. First pressure sensor;

[0045] 90. Second pressure sensor;

[0046] 100. Throttling device. Detailed implementation manners

[0047] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clearly understood, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention. Thus, a feature pointed out in this specification will be used to illustrate one of the features of one embodiment of the present invention, rather than implying that each embodiment of the present invention must have the feature described. In addition, it should be noted that this specification describes many features. Although certain features may be combined together to show a possible system design, these features may also be used in other combinations not explicitly described. Thus, unless otherwise stated, the described combinations are not intended to be limiting.

[0048] The principle and structure of the present invention will be described in detail below with reference to the accompanying drawings and embodiments.

[0049] In some embodiments, as Figure 1 - Figure 2 shown, the present invention provides a centrifugal heat pump unit, including:

[0050] An evaporator 10, with a first air outlet 101 and a second air outlet 102 respectively provided at both ends of the top of the evaporator 10 along its length direction;

[0051] A steam generator 20, with a third air outlet 201 provided at its top;

[0052] A multi-stage compressor unit 30, which is connected between the first air outlet 101 and the refrigerant inlet of the steam generator 20;

[0053] A boosting device 40, which includes a driving side and a compression side. The steam inlet of the driving side is communicated with the third air outlet 201 through a pipeline, and the compression side is respectively connected to the first air outlet 101 and the second air outlet 102 through pipelines.

[0054] It should be noted that the refrigerant inlet of the compression side is communicated with the second air outlet 102 through a pipeline, and the refrigerant outlet of the compression side is communicated with the first air outlet 101 through a pipeline. And the centrifugal heat pump unit also includes a main control unit (not shown, the same throughout the text). And the third air outlet 201 of the steam generator 20 is also connected to the user end through a pipeline to deliver high-temperature and high-pressure water vapor to the user end.

[0055] When the centrifugal heat pump unit starts, the main control unit starts the multi-stage compressor unit 30. The multi-stage compressor unit 30 sucks the low-pressure gaseous refrigerant discharged from the first air outlet 101 of the evaporator 10, compresses the low-pressure gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant, and then transports it to the refrigerant inlet of the steam generator 20. Then, the high-temperature and high-pressure gaseous refrigerant exchanges heat with water through the heat exchange tubes in the steam generator 20 and condenses into a high-temperature liquid refrigerant. At this time, the high-temperature liquid refrigerant will flow back into the evaporator 10 for the next round of heating cycle. At the same time, the water in the steam generator 20 continuously absorbs heat and is continuously converted into high-temperature and high-pressure water vapor after reaching saturation. Then, the high-temperature and high-pressure water vapor flows through the third air outlet 201 to the compression side of the booster device 40. Then, the compression side drives the drive side to suck the low-pressure gaseous refrigerant discharged from the second air outlet 102. Then, the drive side will compress the low-pressure gaseous refrigerant to form a high-pressure gaseous refrigerant. Then, the drive side sends the high-pressure gaseous refrigerant back to the first air outlet 101 so that the high-pressure gaseous refrigerant and the low-pressure gaseous refrigerant discharged from the first air outlet 101 are mixed and then enter the multi-stage compressor unit 30. Since the pressure of the mixed gaseous refrigerant is higher than the pressure of the gaseous refrigerant discharged from the first air outlet 101, the intake pressure of the multi-stage compressor unit 30 is increased, thereby reducing the compression ratio of the multi-stage compressor unit 30, improving the operating stability of the multi-stage compressor unit 30, reducing the load of the multi-stage compressor unit 30, and extending the service life of the multi-stage compressor unit 30. And increasing the intake pressure can also increase the flow rate of the refrigerant flowing into the multi-stage compressor unit 30, thereby improving the heating effect of the centrifugal heat pump unit. And increasing the intake pressure can also reduce the energy efficiency of the centrifugal heat pump unit because the multi-stage compressor unit 30 operates more efficiently at a smaller compression ratio. In addition, a higher intake pressure can effectively reduce pressure fluctuations and improve the stability of the centrifugal heat pump unit.

[0056] In some embodiments, as Figure 1 shown, the centrifugal heat pump unit further includes a water storage device 50. The inlet side of the water storage device 50 is communicated with the steam outlet of the drive side of the booster device 40 through a pipeline. The outlet side of the water storage device 50 is communicated with the water replenishing port 202 of the steam generator 20 through a pipeline, and a water pump 501 is provided on the pipeline between the outlet side of the water storage device 50 and the water replenishing port 202 of the steam generator 20.

[0057] In this way, the high-temperature and high-pressure steam that drives the drive side of the booster device 40 will enter the water storage device 50 through the pipeline, thereby increasing the temperature of the water in the water storage device 50. So that when the water storage device 50 continuously replenishes water to the steam generator 20 through the water pump 501, the water replenished into the steam generator 20 is more likely to reach the evaporation temperature and is more likely to be converted into water vapor, thereby improving the steam conversion efficiency of the steam generator 20, and the water vapor can also be reused, avoiding energy waste and reducing energy consumption.

[0058] In some embodiments, as Figure 1 shown, a gas-liquid filtration component 103 horizontally covers the upper part of the evaporator 10 along its length direction, and the gas-liquid filtration component 103 divides the evaporator 10 into a gas storage cavity 104 and a liquid storage cavity 105;

[0059] Both ends of the top wall of the gas storage cavity 104 along its length direction are respectively provided with a first air outlet 101 and a second air outlet 102.

[0060] It should be noted that the gas-liquid filtration component 103 proposed in this embodiment is preferably a gas-liquid filter mesh, which is a wire mesh structure made by a special weaving process and is mainly used to separate liquid droplets, mist or solid particles in a gas-liquid mixture; its core function is to achieve efficient gas-liquid separation through physical interception or inertial collision.

[0061] In this way, the liquid refrigerant is intercepted by the gas-liquid filtration component 103 to ensure that only the gaseous refrigerant enters the multi-stage compressor unit 30, and to prevent the liquid refrigerant from entering the multi-stage compressor unit 30 and affecting the operation status of the multi-stage compressor unit 30.

[0062] In some embodiments, as Figure 1 shown, the refrigerant output side of the steam generator 20 is communicated with the inlet of the throttling device 100 through a pipeline, and the outlet of the throttling device 100 is communicated with the liquid storage cavity 105 through a pipeline.

[0063] In this way, the high-temperature and high-pressure gas-liquid two-phase refrigerant in the steam generator 20 is converted into a low-temperature and low-pressure gas-liquid two-phase refrigerant through the throttling device 100, and then enters the liquid storage cavity 105, and the gas-liquid two-phase refrigerant is separated into gaseous refrigerant by the gas-liquid filtration component 103 and enters the gas storage cavity 104.

[0064] In some embodiments, to ensure that the boosting device 40 can boost the low-pressure gaseous refrigerant output by the evaporator 10, as Figure 1 and Figure 3 shown, the present invention proposes a structure of a boosting device 40:

[0065] The boosting device 40 includes a housing 401, and a sealed driving space 402 and a compression space 403 are arranged side by side along the axial direction of the housing 401, and the two spaces are separated by a partition 404;

[0066] The intake side of the driving space 402 is communicated with the third air outlet 201 through a pipeline, the intake side of the compression space 403 is communicated with the second air outlet 102 through a pipeline, and the outlet side of the compression space 403 is communicated with the first air outlet 101 through a pipeline;

[0067] A driving turbine impeller 405 is provided in the driving space 402, a gas compression turbine impeller 406 is provided in the compression space 403, the gas compression turbine impeller 406 is linked with the driving turbine impeller 405 through a coupling 407, and the coupling 407 penetrates through the partition plate 404 in a matching manner.

[0068] It should be noted that the driving space 402 and the driving turbine impeller 405 proposed in this embodiment form a driving side. The intake side of the driving space 402 is equivalent to the steam inlet of the driving side, and the outlet side of the driving space 402 is equivalent to the steam outlet of the driving side; the compression space 403 and the gas compression turbine impeller 406 proposed in this embodiment form a compression side. The intake side of the compression space 403 is equivalent to the refrigerant inlet of the compression side, and the outlet side of the compression space 403 is equivalent to the refrigerant outlet of the compression side. The driving turbine impeller 405, the gas compression turbine impeller 406 and the coupling 407 can form a shaft-connected turbine structure.

[0069] In this way, when the high-temperature and high-pressure water vapor flows from the third outlet 201 into the driving space 402, the high-temperature and high-pressure water vapor will drive the driving turbine impeller 405 to rotate. Then, the driving turbine impeller 405 drives the gas compression turbine impeller 406 to rotate through the coupling 407. The rotating gas compression turbine impeller 406 will suck the low-pressure gaseous refrigerant discharged from the second outlet 102 into the compression space 403. Then, the gas compression turbine impeller 406 compresses the low-pressure gaseous refrigerant in the compression space 403 to form a high-pressure gaseous refrigerant, and then sends the high-pressure gaseous refrigerant back to the first outlet 101 through a pipeline, so as to mix the high-pressure gaseous refrigerant and the low-pressure gaseous refrigerant discharged from the first outlet 101 and then enter the multi-stage compressor unit 30. Since the pressure of the mixed gaseous refrigerant is higher than the pressure of the low-pressure gaseous refrigerant discharged from the first outlet 101, the intake pressure of the multi-stage compressor unit 30 is increased, thereby reducing the compression ratio of the multi-stage compressor unit 30, improving the operating stability of the multi-stage compressor unit 30, reducing the load of the multi-stage compressor unit 30, and extending the service life of the multi-stage compressor unit 30; and increasing the intake pressure can also increase the flow rate of the refrigerant flowing into the multi-stage compressor unit 30, thereby improving the heating effect of the centrifugal heat pump unit; and increasing the intake pressure can also reduce the energy efficiency of the centrifugal heat pump unit because the multi-stage compressor unit 30 operates more efficiently at a smaller compression ratio; in addition, the higher intake pressure can effectively reduce the pressure fluctuation and improve the stability of the centrifugal heat pump unit.

[0070] To facilitate understanding of the specific difference between the high-pressure gaseous refrigerant formed by the compression of the gas compression turbine impeller 406 through the pressure boosting device 40 and the low-pressure gaseous refrigerant discharged from the first outlet 101, this embodiment gives a specific value for the pressure values of the high-pressure gaseous refrigerant and the low-pressure gaseous refrigerant as follows:

[0071] The pressure value of the low-pressure gaseous refrigerant discharged from the first air outlet 101 is preferably 0.4 MPa, while the pressure value of the high-pressure gaseous refrigerant compressed by the compressor turbine impeller 406 is preferably 1.0 MPa. Moreover, the boosting device 40 can compress 10%-30% of the low-pressure gaseous refrigerant in the evaporator 10 and then send it back to the first air outlet 101 for the multi-stage compressor unit 30 to absorb. Therefore, at this time, the pressure value of the mixed gaseous refrigerant absorbed by the multi-stage compressor unit 30 can reach 0.5 MPa. Of course, in this embodiment, the pressure values of the low-pressure gaseous refrigerant, the high-pressure gaseous refrigerant, and the mixed gaseous refrigerant can also be selected as other values according to the actual situation, which is not limited herein.

[0072] Specifically, to ensure that the high-pressure steam in the driving space 402 does not mix with the low-pressure gaseous refrigerant in the compression space 403, thereby affecting the normal operation of the boosting device 40 or the stable operation of the centrifugal heat pump unit, as Figure 3 shown, sealing components 408 are respectively and correspondingly installed on both sides of the partition plate 404 along the two sides penetrated by the coupling 407.

[0073] It should be noted that the sealing component 408 proposed in this embodiment is preferably a sealing ring resistant to high temperature and high pressure. The sealing ring is sleeved on the coupling 407 and is hermetically installed on both sides corresponding to the partition plate 404.

[0074] In some embodiments, to ensure that the multi-stage compressor unit 30 can stably boost the mixed gaseous refrigerant to a high-pressure gaseous refrigerant, as Figure 1 shown, the multi-stage compressor unit 30 includes a first-stage compressor 301 and a second-stage compressor 302;

[0075] The input end of the first-stage compressor 301 is communicated with the first air outlet 101 through a pipeline, the output end of the first-stage compressor 301 is communicated with the input end of the second-stage compressor 302 through a pipeline, and the output end of the second-stage compressor 302 is communicated with the refrigerant input side of the steam generator 20 through a pipeline.

[0076] It should be noted that the input end of the compressor proposed in this embodiment is the suction port, and the output end of the compressor is the exhaust port.

[0077] For easy understanding, this embodiment gives a specific value as follows:

[0078] When the boosting device 40 is not used, the pressure value of the low-pressure gaseous refrigerant discharged from the first air outlet 101 is preferably 0.4 MPa. The first-stage compressor 301 can boost the gaseous refrigerant of 0.4 MPa to 1.2 MPa, and the second-stage compressor 302 can boost the gaseous refrigerant of 1.2 MPa to 1.8 MPa and then input it into the steam generator 20.

[0079] After using the booster device 40, the gas compression turbine impeller 406 of the booster device 40 can compress and boost the gaseous refrigerant at 0.4 MPa to 1.0 MPa and then send it back to the first air outlet 101, so that the pressure of the mixed gaseous refrigerant output from the first air outlet 101 reaches 0.5 MPa. Then, the first-stage compressor 301 can boost the gaseous refrigerant at 0.5 MPa to 1.5 MPa, and the second-stage compressor 302 can boost the gaseous refrigerant at 1.5 MPa to 2.0 MPa and then input it into the steam generator 20. Of course, the above values can also be changed according to the actual situation and are not limited here.

[0080] Therefore, the pressure of the gaseous refrigerant discharged from the first air outlet 101 is increased from 0.4 MPa to 0.5 MPa. Since the intake pressure of the first-stage compressor 301 becomes larger, the compression ratio of the first-stage compressor 301 is reduced, the operating stability of the first-stage compressor 301 is improved, the load of the first-stage compressor 301 is reduced, and the service life of the first-stage compressor 301 is extended; moreover, increasing the intake pressure can also increase the flow rate of the refrigerant flowing into the first-stage compressor 301, thereby improving the heating effect of the centrifugal heat pump unit; and increasing the intake pressure can also reduce the energy efficiency of the centrifugal heat pump unit because the first-stage compressor 301 operates more efficiently at a smaller compression ratio; in addition, the higher intake pressure can effectively reduce the pressure fluctuation and improve the stability of the centrifugal heat pump unit.

[0081] In some embodiments, as Figure 4 - Figure 5 shown, a first pressure sensor 80 is provided on the pipeline communicating between the output end of the first-stage compressor 301 and the input end of the second-stage compressor 302. The first pressure sensor 80 is used to detect the refrigerant pressure output by the first-stage compressor 301.

[0082] A second pressure sensor 90 is provided on the pipeline communicating between the output end of the second-stage compressor 302 and the input end of the steam generator 20. The second pressure sensor 90 is used to detect the refrigerant pressure output by the second-stage compressor 302.

[0083] Among them, the first pressure sensor 80 is used to detect the output refrigerant pressure of the first-stage compressor 301 before and after the action of the booster device 40 and detect it multiple times within the same time period. The average value of the refrigerant pressure is obtained through multiple detections. Therefore, the average value of the refrigerant pressure measured by the first pressure sensor 80 is used to directly feedback the influence of changing the intake pressure on the first-stage compressor 301.

[0084] Moreover, the refrigerant pressure detected by the second pressure sensor 90 is the final exhaust pressure of the current operating condition of the current centrifugal heat pump unit, which is used to determine whether the intake pressure of the first-stage compressor 301 meets the requirements of the current operating condition. If the intake pressure of the first-stage compressor 301 meets the requirements of the current operating condition, the current boosting device 40 is maintained in operation, and the intake pressure of the first-stage compressor 301 remains unchanged. If the intake pressure of the first-stage compressor 301 does not meet the requirements of the current operating condition, the flow rate of the high-temperature and high-pressure water vapor flowing into the driving space 402 is increased, so as to increase the flow rate of the low-pressure gaseous refrigerant inhaled by the compression turbine impeller 406 into the compression space 403, thereby increasing the intake pressure of the first-stage compressor 301, and increasing the exhaust pressure of the second-stage compressor 302 to meet the requirements of the current operating condition.

[0085] In some embodiments, as Figure 6 - Figure 7 shown, a first electric valve 60 is provided on the pipeline communicating between the intake side of the driving space 402 of the boosting device 40 and the third air outlet 201. The first electric valve 60 is used to control the steam flow rate entering the driving space 402;

[0086] A second electric valve 70 is provided on the pipeline communicating between the intake side of the compression space 403 of the boosting device 40 and the second air outlet 102. The second electric valve 70 is used to control the flow rate of the gaseous refrigerant entering the compression space 403.

[0087] In this way, when the centrifugal heat pump unit is operating normally, the refrigerant pressure detected by the second pressure sensor 90 is lower than the preset value, that is, the intake pressure of the first-stage compressor 301 does not meet the requirements of the current operating condition. At this time, the main control unit will control the second electric valve 70 to be fully opened, and gradually increase the opening degree of the first electric valve 60, so as to increase the flow rate of the high-temperature and high-pressure water vapor flowing into the driving space 402, and increase the flow rate of the low-pressure gaseous refrigerant inhaled by the compression turbine impeller 406 into the compression space 403, thereby increasing the intake pressure of the first-stage compressor 301, and the exhaust pressure of the second-stage compressor 302 increases accordingly to meet the requirements of the current operating condition. Moreover, increasing the intake pressure of the first-stage compressor 301 can reduce the compression ratio of the first-stage compressor 301, improve the operating stability of the first-stage compressor 301, reduce the load of the first-stage compressor 301, and extend the service life of the first-stage compressor 301; moreover, increasing the intake pressure of the first-stage compressor 301 can also increase the flow rate of the refrigerant flowing into the first-stage compressor 301, thereby improving the heating effect of the centrifugal heat pump unit; moreover, increasing the intake pressure can also reduce the energy efficiency of the centrifugal heat pump unit, because the first-stage compressor 301 operates more efficiently at a smaller compression ratio; in addition, a higher intake pressure can effectively reduce pressure fluctuations and improve the stability of the centrifugal heat pump unit.

[0088] When the centrifugal heat pump unit is operating normally, when the refrigerant pressure detected by the second pressure sensor 90 is much higher than the preset value, the main control unit will control the opening degrees of the first electric valve 60 and the second electric valve 70 to gradually decrease (and the opening degree of the first electric valve 60 will be decreased to at most 50%), so as to reduce the flow rate of the high-temperature and high-pressure water vapor flowing into the driving space 402, and reduce the flow rate of the low-pressure gaseous refrigerant inhaled by the compression air turbine impeller 406 into the compression space 403, thereby reducing the intake pressure of the first-stage compressor 301, and the exhaust pressure of the second-stage compressor 302 will decrease accordingly to meet the requirements of the current working condition.

[0089] When the centrifugal heat pump unit is operating normally, when the refrigerant pressure detected by the second pressure sensor 90 is within the preset value, the main control unit will close the first electric valve 60 and the second electric valve 70, so that the first electric valve 60 and the second electric valve 70 maintain the current opening degree, and there is no need to change the intake pressure of the first-stage compressor 301.

[0090] It should be noted that the opening degree of the first electric valve 60 is decreased to at most 50% because the driving turbine impeller 405 needs sufficient steam flow to start. The decrease in the opening degree of the first electric valve 60 can reduce the speed and torque of the coaxial turbine structure, and then reduce the pressure of the compressed gas by the compression air turbine impeller 406; while the opening degree of the second electric valve 70 can be decreased from 100% to 0, controlling the flow rate of the gaseous refrigerant compressed by the compression air turbine impeller 406, and the two synchronously adjust the intake pressure of the first-stage compressor 301.

[0091] In some embodiments, based on the same inventive concept, the present invention also provides an air-conditioning unit, and the air-conditioning unit includes the centrifugal heat pump unit described above.

[0092] It should be noted that when the air-conditioning unit is in the heating working condition, the centrifugal heat pump unit is started.

[0093] When the air conditioning unit is in the heating mode and the centrifugal heat pump unit is started for the first time, the boosting device 40 is not operating. It is necessary to wait for the low-pressure gaseous refrigerant discharged from the first air outlet 101 of the evaporator 10 to be compressed and boosted in sequence through the first-stage compressor 301 and the second-stage compressor 302, and finally output to the steam generator 20 for heat exchange. At the same time, the water in the steam generator 20 continuously absorbs heat and is continuously converted into high-temperature and high-pressure water vapor after reaching saturation. Then, the high-temperature and high-pressure water vapor flows into the driving space 402 through the third air outlet 201. Then, the high-temperature and high-pressure water vapor drives the driving turbine impeller 405 to rotate. Then, the driving turbine impeller 405 drives the compression turbine impeller 406 to rotate through the coupling 407. In this way, the rotating compression turbine impeller 406 sucks the low-pressure gaseous refrigerant discharged from the second air outlet 102 into the compression space 403, and then the compression turbine impeller 406 compresses the low-pressure gaseous refrigerant in the compression space 403 to form a high-pressure gaseous refrigerant. Then, the high-pressure gaseous refrigerant is sent back to the first air outlet 101 through the pipeline, so that the high-pressure gaseous refrigerant and the low-pressure gaseous refrigerant discharged from the first air outlet 101 are mixed and then enter the first-stage compressor 301 and the second-stage compressor 302 in sequence for compression and boosting, and finally output to the steam generator 20 for heat exchange and generate high-temperature and high-pressure water vapor, thus forming a heating cycle. Since the pressure of the mixed gaseous refrigerant is higher than the pressure of the low-pressure gaseous refrigerant discharged from the first air outlet 101, the intake pressure of the first-stage compressor 301 is increased, thereby reducing the compression ratio of the first-stage compressor 301, improving the operating stability of the first-stage compressor 301, reducing the load of the first-stage compressor 301, and extending the service life of the first-stage compressor 301; and increasing the intake pressure can also increase the flow rate of the refrigerant flowing into the first-stage compressor 301, thereby improving the heating effect of the centrifugal heat pump unit; and increasing the intake pressure can also reduce the energy efficiency of the air conditioning unit because the first-stage compressor 301 operates more efficiently at a smaller compression ratio; in addition, the higher intake pressure can effectively reduce pressure fluctuations and improve the stability of the air conditioning unit.

[0094] Obviously, the embodiments described above are only a part of the embodiments of the present invention, rather than all the embodiments. The preferred embodiments of the present invention are given in the drawings, but do not limit the patent scope of the present invention. The present invention can be implemented in many different forms. On the contrary, the purpose of providing these embodiments is to make the understanding of the disclosed content of the present invention more thorough and comprehensive. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art can still modify the technical solutions recorded in the foregoing specific embodiments, or perform equivalent replacements on some of the technical features. Any equivalent structure made by using the specification and drawings of the present invention, directly or indirectly applied to other related technical fields, is equally within the scope of the patent protection of the present invention.

Claims

1. A centrifugal heat pump unit, characterized in that, Comprising: An evaporator (10) which is respectively provided with a first air outlet (101) and a second air outlet (102); A steam generator (20) which is provided with a third air outlet (201); A multi-stage compressor unit (30) which is connected between the first air outlet (101) and the steam generator (20); A boosting device (40) which includes a driving side and a compression side, the driving side communicates with the third air outlet (201), and the compression side is respectively connected to the first air outlet (101) and the second air outlet (102).

2. The centrifugal heat pump unit according to claim 1, characterized in that, The centrifugal heat pump unit further includes a water storage device (50), the inlet side of the water storage device (50) communicates with the compression side of the boosting device (40), and the outlet side of the water storage device (50) communicates with the water replenishing port (202) of the steam generator (20) through a water pump (501).

3. The centrifugal heat pump unit according to claim 1, characterized in that The boosting device (40) includes a housing (401), and an axially side-by-side sealed driving space (402) and compression space (403) are provided in the housing (401), and the two spaces are separated by a partition plate (404); The air inlet side of the driving space (402) communicates with the third air outlet (201), the air inlet side of the compression space (403) communicates with the second air outlet (102), and the air outlet side of the compression space (403) communicates with the first air outlet (101); A driving turbine impeller (405) is provided in the driving space (402), a gas compression turbine impeller (406) is provided in the compression space (403), the gas compression turbine impeller (406) is linked with the driving turbine impeller (405) through a coupling (407), and the coupling (407) penetrates through the partition plate (404) in a matching manner.

4. The centrifugal heat pump unit according to claim 3, characterized in that, Sealing assemblies (408) are respectively and matchingly installed on both sides of the partition plate (404) through which the coupling (407) penetrates.

5. The centrifugal heat pump unit according to claim 1, characterized in that, A first electric valve (60) is provided on the pipeline between the driving side of the boosting device (40) and the third air outlet (201), and the first electric valve (60) is used to control the steam flow rate entering the driving side; A second electric valve (70) is provided on the pipeline between the compression side of the boosting device (40) and the second air outlet (102), and the second electric valve (70) is used to control the gaseous refrigerant flow rate entering the compression side.

6. The centrifugal heat pump unit according to claim 1, characterized in that, The multi-stage compressor unit (30) includes a first-stage compressor (301) and a second-stage compressor (302); The input end of the first-stage compressor (301) communicates with the first air outlet (101), the output end of the first-stage compressor (301) communicates with the input end of the second-stage compressor (302), and the output end of the second-stage compressor (302) communicates with the refrigerant input side of the steam generator (20).

7. The centrifugal heat pump unit according to claim 6, characterized in that, A first pressure sensor (80) is provided on the pipeline between the output end of the first-stage compressor (301) and the input end of the second-stage compressor (302), and the first pressure sensor (80) is used to detect the refrigerant pressure output by the first-stage compressor (301); A second pressure sensor (90) is provided on the pipeline between the output end of the secondary compressor (302) and the input end of the steam generator (20), and the second pressure sensor (90) is used to detect the refrigerant pressure output by the secondary compressor (302).

8. The centrifugal heat pump unit according to claim 1, characterized in that, An air-liquid filtration component (103) is horizontally covered along the length direction on the upper part of the evaporator (10), and the air-liquid filtration component (103) divides the evaporator (10) into an air storage cavity (104) and a liquid storage cavity (105); A first air outlet (101) and a second air outlet (102) are respectively provided at both ends of the air storage cavity (104) along its length direction.

9. The centrifugal heat pump unit according to claim 8, wherein, The refrigerant output side of the steam generator (20) communicates with the liquid storage cavity (105) through a throttling device (100).

10. An air conditioning unit, characterized in that, The air conditioner unit includes the centrifugal heat pump unit according to any one of claims 1-9.

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