CN220956100U - Vapor compressor and air conditioning unit - Google Patents

Abstract

The application discloses a vapor compressor and an air conditioning unit. The water vapor compressor includes a volute, a diffuser plate, and an impeller. The diffuser plate is connected to the volute and forms a rotor chamber. The impeller is rotatably disposed within the rotor cavity. The volute has a cooling chamber for containing a cooling medium. The cooling chamber is disposed adjacent to a side edge of the impeller. The impeller works on gas compression, so that the pressure, speed and temperature of the gas are improved, the energy consumption required by the gas compression at high temperature is higher under the condition of unchanged compression ratio, the compression power consumption of the vapor compressor is higher, the heat generated in the process of compressing the gas is absorbed by the cooling medium heat conduction in the cooling cavity, the temperature of the gas is timely reduced in the process of compression, the compression power consumption of the vapor compressor is further reduced, and the working efficiency of the compressor is improved.

Description

Vapor compressor and air conditioning unit

Technical Field

The application relates to the technical field of refrigeration equipment, in particular to a vapor compressor and an air conditioning unit.

Background

The gas pressure in the vapor compressor is increased by the centrifugal force acting on the gas by the rotation of the impeller when the gas flows through the impeller, and the gas obtains a velocity at the same time, and the gas flow velocity gradually decreases and the gas pressure is increased when the gas flows through the expansion passages such as the impeller and the diffuser. The pressure, speed and temperature of the gas are improved by the action of the impeller on the gas, and as the temperature of the gas is increased in the compression process and the gas is compressed at high temperature, the consumed work is increased, and the higher the end temperature of the gas is, the larger the compressed work is, so that in order to reduce the consumed work of compression, the scheme of interstage spray cooling is adopted in the compression process for the centrifugal compressor with higher pressure so as to reduce the power consumption of the compressor.

However, the water spray position of the centrifugal vapor compressor in the prior art is generally water spray on the suction pipe or the discharge pipe. The water spraying on the air suction pipeline needs to be very accurate to control the water spraying quantity, so that the gas and liquid can be mixed unevenly, the impeller is impacted by liquid, and potential safety hazards are caused; the water is sprayed on the exhaust pipe, so that the exhaust temperature can be reduced, but the compression work is reduced to a limited extent.

It should be noted that the statements in this background section merely provide background information related to the present disclosure and may not necessarily constitute prior art.

Disclosure of utility model

The application provides a vapor compressor and an air conditioning unit, which are used for reducing compression power consumption.

A first aspect of the present application provides a water vapor compressor comprising a volute, a diffuser plate, and an impeller. The diffuser plate is connected to the volute and forms a rotor chamber. The impeller is rotatably disposed within the rotor cavity. The volute has a cooling chamber for containing a cooling medium. The cooling chamber is disposed adjacent to a side edge of the impeller.

In some embodiments, the volute includes a volute body, an annular groove disposed on the volute body, and an annular plate covering an opening of the annular groove. The annular groove extends in a circumferential direction of the volute body. The annular groove and the annular plate enclose a cooling cavity.

In some embodiments, the water vapor compressor further comprises a seal. The sealing member is arranged at the joint of the annular plate and the volute body.

In some embodiments, the end surface of the volute body that engages the annular plate comprises a fluted end surface. The annular plate is arranged in the groove cavity of the groove end face. The seal is disposed between the circumferential edge of the annular plate and the sidewall of the slot cavity.

In some embodiments, the cooling cavity comprises an annular cavity. The annular cavity is coaxially arranged with the impeller.

In some embodiments, the ratio of the inner diameter of the annular cavity to the diameter of the inlet side of the impeller ranges from (1.2,1.6).

In some embodiments, the vapor compressor further comprises a spray flow passage. A diffuser flow passage is formed between the diffuser plate and the volute. The spray flow passage is arranged between the cooling cavity and the diffusion flow passage. The cooling medium includes cooling water. The spray flow passage is configured to spray cooling water through the spray flow passage into the diffuser flow passage.

In some embodiments, the volute has an exhaust port that discharges compressed gas. The vapor compressor further includes an adjustment member disposed within the spray flow path. The adjusting member is configured to adjust a flow rate of the sprayed cooling water according to a degree of superheat of the compressed gas discharged from the exhaust port.

In some embodiments, the vapor compressor further comprises an atomizer. The atomizer is arranged at one end of the spray flow passage close to the diffusion flow passage. The atomizing nozzle is configured to convert cooling water in the cooling cavity into water mist and then spray the water mist to the diffusion flow channel.

In some embodiments, the vapor compressor includes a plurality of atomizer heads. The plurality of atomizing nozzles are circumferentially spaced relative to the axis of the impeller.

In some embodiments, the diameter of the atomizer is configured to satisfy the following calculation:

A= (4 q/u/n/3.14) ^1/2, where a is the diameter of the atomizer, u is the flow rate of droplets ejected from the atomizer, u=0.65 x (2 Δp/ρ) ^1/2, n is the number of atomizers, Δp is the pressure difference before and after the atomizer ejects the liquid, ρ is the density of the cooling water, and q is the amount of ejected water required to cool the compressed gas to a set superheat.

In some embodiments, the calculation formula for the diameter of the atomizer is configured to also satisfy:

n is 4 or 8, and ΔP is greater than or equal to 3bar.

In some embodiments, the volute has an exhaust port that discharges compressed gas. The discharge pressure of the cooling water is configured to be adjusted according to the degree of superheat of the compressed gas discharged from the exhaust port.

In some embodiments, the vapor compressor further comprises a perfusion channel. The pouring channel is arranged on the shell wall of the volute. The first end of the filling channel is connected with the cooling cavity, and the second end of the filling channel is externally connected with a cold source. The filling channel is used for filling cooling medium into the cooling cavity.

A second aspect of the application provides an air conditioning unit comprising a water vapour compressor as described above.

Based on the technical scheme provided by the application, the vapor compressor comprises a volute, a diffuser plate and an impeller. The diffuser plate is connected to the volute and forms a rotor chamber. The impeller is rotatably disposed within the rotor cavity. The volute has a cooling chamber for containing a cooling medium. The cooling chamber is disposed adjacent to a side edge of the impeller. The impeller works on gas compression, so that the pressure, speed and temperature of the gas are improved, the energy consumption required by the gas compression at high temperature is higher under the condition of unchanged compression ratio, the compression power consumption of the vapor compressor is higher, the heat generated in the process of compressing the gas is absorbed by the cooling medium heat conduction in the cooling cavity, the temperature of the gas is timely reduced in the process of compression, the compression power consumption of the vapor compressor is further reduced, and the working efficiency of the compressor is improved.

Other features of the present application and its advantages will become apparent from the following detailed description of exemplary embodiments of the application, which proceeds with reference to the accompanying drawings.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application and do not constitute a limitation on the application. In the drawings:

Fig. 1 is an overall schematic view of a water vapor compressor according to an embodiment of the present application.

Fig. 2 is a cross-sectional view of a water vapor compressor according to an embodiment of the present application.

Detailed Description

The following description of the embodiments of the present application will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present application, but not all embodiments. The following description of at least one exemplary embodiment is merely exemplary in nature and is in no way intended to limit the application, its application, or uses. All other embodiments, which can be made by those skilled in the art based on the embodiments of the application without making any inventive effort, are intended to be within the scope of the application.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present application unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but where appropriate, the techniques, methods, and apparatus should be considered part of the specification. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

Spatially relative terms, such as "above … …," "above … …," "upper surface on … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations "above … …" and "below … …". The device may also be positioned in other different ways and the spatially relative descriptions used herein are construed accordingly.

Referring to fig. 1 and 2, the present application provides a water vapor compressor comprising a volute 1, a diffuser plate 8, and an impeller 2. The diffuser plate 8 is connected to the volute 1 and forms a rotor chamber. The impeller 2 is rotatably arranged in the rotor chamber. The volute 1 has a cooling chamber B for accommodating a cooling medium. The cooling chamber B is arranged adjacent to the side edges of the impeller 2. Because the impeller 2 applies work to the gas compression, the pressure, speed and temperature of the gas are improved, and under the condition of unchanged compression ratio, the energy consumption required by the gas compression at high temperature is higher, so that the compression power consumption of the vapor compressor is larger, and the heat generated in the process of compressing the gas by the impeller 2 is absorbed through the heat conduction of the cooling medium in the cooling cavity B, so that the temperature of the gas is timely reduced in the compression process, the compression power consumption of the vapor compressor is further reduced, and the working efficiency of the compressor is improved.

Referring to fig. 2, in some embodiments, the volute 1 includes a volute body 11, an annular groove 12 provided on the volute body 11, and an annular plate 13 covering an opening of the annular groove 12. The annular groove 12 extends in the circumferential direction of the volute body 11. The annular groove 12 and the annular plate 13 enclose a cooling chamber B. Specifically, the annular plate 13 is located between the circumferential side of the impeller 2 and the volute body 11, in the gas compression process, generated heat at the impeller 2 is conducted and radiated to the cooling medium in the cooling cavity B through the annular plate 13, the annular groove 12 and the annular plate 13 cooperate to enable the cavity of the cooling cavity B to be annular, the containing amount of the cooling medium is guaranteed, the radiating effect is improved, and in the circumferential direction of the annular cooling cavity B, the inner ring of the cooling cavity B is always attached to the annular plate 13, the heat exchange area is increased, the heat conduction and radiating capacity is further enhanced in the gas compression process, the cooling effect is improved, and the compression work is further reduced.

In other embodiments, the volute body and the annular plate are integrally formed, and the cooling cavity is a cavity formed in the volute 1.

Referring to fig. 2, in some embodiments, the inner wall of the annular plate 13 transitions through an arc, and the inner wall of the annular plate 13 and the side edges of the impeller 2 are adapted to increase the heat exchange area between the annular plate 13 and the impeller 2, enhancing the heat dissipation capacity.

Referring to fig. 2, in some embodiments, the water vapor compressor further comprises a seal 5. The seal 5 is provided at the junction of the annular plate 13 and the volute body 11. The sealing member 5 is used for sealing the annular plate 13 and the volute body 11, so that the tightness of the cooling cavity B is improved, and the risk of leakage of cooling medium is reduced.

Referring to fig. 2, in some embodiments, the end face of the volute body 11 that engages the annular plate 13 comprises a fluted end face. The annular plate 13 is disposed in the groove cavity of the groove-shaped end face. The seal 5 is arranged between the circumferential edge of the annular plate 13 and the side wall of the groove cavity. Specifically, the seal 5 includes a seal ring that is snappingly provided at a circumferential edge of the annular plate 13 to enhance a sealing effect between the annular plate 13 and the volute body 11.

Referring to fig. 2, in some embodiments, the inner side of the annular plate 13 is bent towards the inlet of the impeller 2, and the end surface of the bent portion of the annular plate 13 is flush with the end surface where the inlet of the impeller 2 is located, so that the heat exchange area can be further increased, and a sealing ring can be sleeved on the circumferential edge of the bent portion of the annular plate 13, so as to further improve the sealing effect.

In some embodiments, the seal ring is an O-ring.

In some embodiments, cooling cavity B comprises an annular cavity. The annular chamber is arranged coaxially with the impeller 2. The arrangement is convenient for processing the annular groove 12, and the distances between the annular cavity and the side edges of the impeller 2 are equal in the circumferential direction, so that the balance of heat dissipation performance is ensured.

On the basis of the above embodiment, the ratio of the inner diameter of the annular chamber to the diameter of the inlet side of the impeller 2 is in the range of (1.2,1.6). Specifically, the inside diameter of the annular chamber is D0, the diameter of the inlet side of the impeller is D0, and if D0/D0 is less than 1.2, it means that the annular chamber is too close to the side edge of the impeller 2, and the gas sucked by the impeller 2 may be saturated gas, so that the gas is cooled without being compressed, and water vapor in the impeller 2 may be condensed, resulting in liquid impact. If D0/D0 is greater than 1.6, it means that the annular chamber is too far from the side edge of the impeller 2, resulting in a decrease in heat dissipation performance and a limited reduction in compression power consumption.

Referring to fig. 2, in some embodiments, the water vapor compressor further includes a spray flow passage. A diffuser flow passage 3 is formed between the diffuser plate 8 and the scroll 1. The spray flow passage is arranged between the cooling cavity B and the diffusion flow passage 3. The cooling medium includes cooling water. The spray flow passage is configured to spray cooling water through the spray flow passage into the diffuser flow passage 3. The temperature of the cooling water is normal temperature, for example, about 30 ℃, and the cooling water is further sprayed into the diffusion flow passage 3 after being cooled in the process of compressing the gas by the impeller 2, so that the gas in the diffusion flow passage 3 is cooled, and the superheat degree of the gas output by the vapor compressor is reduced. Not only cooling down to impeller 2's compression process, still spray liquid cooling down on diffusion runner 3, abundant reduction exhaust superheat degree, on this basis, if make spiral case 1 with compressed gas delivery to second grade impeller in order further to compress, can also reduce second grade impeller's intake superheat degree, and then make second grade impeller's compression work also correspondingly reduce, promote holistic efficiency.

In actual use, the heat insulation efficiency may deviate from the expected value, and the compressed gas in the diffusion flow passage 3 also dissipates heat to the outside through heat conduction of the casing wall of the volute body 11, so that the actual exhaust superheat degree may deviate from the expected exhaust superheat degree, and the water spraying flow and/or water spraying pressure may be adjusted by detecting the actual exhaust superheat degree, so as to regulate and control the exhaust superheat degree. For example, in some embodiments, the volute 1 has an exhaust port that discharges compressed gas. The vapor compressor further includes an adjustment member disposed within the spray flow path. The adjusting member is configured to adjust a flow rate of the sprayed cooling water according to a degree of superheat of the compressed gas discharged from the exhaust port. Specifically, the adjusting part comprises a flow adjusting valve, the actual superheat degree of the exhaust gas is obtained by detecting the temperature and the pressure of the discharged compressed gas, and the valve core opening of the flow adjusting valve is adjusted according to the actual superheat degree, so that the flow of the sprayed cooling water is adjusted. For example, the measured actual superheat of the discharged compressed gas is greater than the desired superheat, indicating a need to increase the water spray flow; the actual superheat degree of the discharged compressed gas is measured to be smaller than the expected superheat degree, and the water spray flow rate can be appropriately reduced. In conclusion, the superheat degree of the discharged compressed gas can be adjusted by adaptively adjusting the water spraying flow according to the actual working condition, and the applicability is improved.

Referring to fig. 1, in some embodiments, the water vapor compressor further comprises a sensor 7. The volute is provided with an air collection cavity C for collecting compressed gas, the air collection cavity C is communicated with a diffusion flow passage 3, and the diffusion flow passage 3 guides the compressed gas output by the impeller 2 to the air collection cavity C. The gas collection cavity C is connected with the exhaust port of the volute 1, when the exhaust port is opened, compressed gas collected in the gas collection cavity C is discharged, the sensor 7 is arranged at the exhaust port of the volute 1 to detect the pressure and the temperature of the exhaust gas so as to obtain the actual superheat degree of the exhaust gas, and the valve core opening of the flow regulating valve is regulated according to the data of the sensor 7 to regulate the superheat degree of the exhaust gas.

Specifically, the sensor 7 includes a pressure sensor and a temperature sensor, and after the pressure sensor detects the actual pressure of the exhaust gas, the actual temperature detected by the temperature sensor is compared with the saturation temperature under the pressure, if the actual temperature is higher than the saturation temperature, the exhaust compressed gas is indicated to have a superheat degree, and then the exhaust compressed gas is regulated by spraying liquid.

In some embodiments, the water vapor compressor further comprises an exhaust flange provided at the exhaust port of the scroll case 1 for controlling whether the exhaust port is opened or not, and a sensor 7 is provided at the exhaust flange.

In some embodiments, the discharge pressure of the cooling water is configured to be adjusted according to the degree of superheat of the compressed gas discharged from the discharge port. For example, the measured actual superheat of the discharged compressed gas is greater than the desired superheat, indicating a need to increase the water spray pressure; the actual superheat degree of the discharged compressed gas is measured to be smaller than the desired superheat degree, and the water spray pressure can be appropriately reduced.

For example, referring to fig. 2, in some embodiments, the water vapor compressor further comprises a perfusion channel 6. The filling channel 6 is provided on the housing wall of the volute 1. The first end of the filling channel 6 is connected with the cooling cavity B, and the second end of the filling channel 6 is externally connected with a cold source. The filling channel 6 is used for filling the cooling medium into the cooling cavity B. Specifically, external cold source includes external cooling water source, is provided with the water pump in external cooling water source department, in the course of the work, because the cooling water in the cooling chamber B continuously spouts to diffusion runner 3, so external cooling water source continuously to cooling chamber B in pour into cooling water to guarantee cooling chamber B in the cooling water volume sufficient, and then guarantee the radiating effect in the compression process. And the pressure of cooling water input into the cooling cavity B is regulated by the water pump, so that the regulation of spray pressure is realized.

Referring to fig. 2, in some embodiments, the water vapor compressor further comprises an atomizer 4. The atomizing nozzle 4 is arranged at one end of the spray flow channel, which is close to the diffusion flow channel 3. The atomizer 4 is configured to convert the cooling water in the cooling chamber B into water mist and spray the water mist toward the diffuser flow passage 3. The injected water is in a droplet shape and is mixed with the compressed gas, the extremely large heat exchange surface rapidly absorbs the compression heat of the gas, the compressed gas is cooled, the exhaust temperature is greatly reduced, the characteristics of the vapor compressor are greatly changed due to the injection of water mist, the adaptable pressure and pressure ratio are improved, the structural design is simplified, the exhaust temperature is effectively controlled, and the noise is reduced. On the other hand, as the exhaust temperature is not affected by the pressure ratio, the working range of the compressor is only determined by the compression efficiency, and is not limited by the highest exhaust temperature, so that the applicability of the compressor to different working scenes is improved.

In some embodiments, the water vapor compressor includes a plurality of atomizer heads 4. The plurality of atomizer heads 4 are circumferentially spaced relative to the axis of the impeller 2. The plurality of atomizing nozzles 4 can enable atomized liquid drops to be dispersed and distributed in the diffusion flow channel 3, and the cooling effect on compressed gas is enhanced.

In some embodiments, the diameter of the atomizer head 4 is configured to satisfy the following calculation: a= (4 q/u/n/3.14) ^1/2, where a is the diameter of the atomizer 4, u is the flow rate of droplets ejected from the atomizer 4, u=0.65 x (2 Δp/ρ) ^1/2, n is the number of atomizers 4, Δp is the pressure difference between before and after the ejection of the atomizer 4 (i.e., the ejection pressure of the cooling water), ρ is the density of the cooling water, and q is the amount of ejection water required to cool the compressed gas to a set superheat degree. Specifically, under the nominal working condition, according to the set parameters such as adiabatic efficiency (e.g., 0.7), suction pressure, suction temperature, pressure ratio and the like, the temperature and pressure of the gas discharged from the vapor compressor under the nominal working condition can be calculated, the superheat degree of the exhaust gas can be obtained according to the temperature and pressure, and then the water spray amount required for reducing the superheat degree of the exhaust gas to the desired superheat degree (e.g., 5 degrees) is calculated, so that q can be obtained. Further, the diameter of the atomizer head 4 refers to the pipe diameter of the spray pipe in the nozzle head, in other words, the pipe diameter is determined by the number of atomizer heads 4 and the spray pressure together.

In some embodiments, the calculation formula for the diameter of the atomizer head 4 is configured to also satisfy: n is 4 or 8, and ΔP is greater than or equal to 3bar.

The application also provides an air conditioning unit comprising the water vapor compressor. By radiating heat in the compression process of the impeller 2, the compression power consumption is reduced, and the energy consumption of the air conditioning unit is further reduced.

Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present application and not for limiting the same; while the application has been described in detail with reference to the preferred embodiments, those skilled in the art will appreciate that: modifications may be made to the specific embodiments of the present application or equivalents may be substituted for part of the technical features thereof; without departing from the spirit of the application, it is intended to cover the scope of the application as claimed.

Claims (15)

1. A water vapor compressor, comprising:

A volute (1);

A diffuser plate (8) connected to the volute (1) and forming a rotor chamber; and

The impeller (2) is rotationally arranged in the rotor cavity;

wherein the volute (1) has a cooling chamber (B) for receiving a cooling medium, the cooling chamber (B) being arranged adjacent to a side edge of the impeller (2).

2. The water vapor compressor as recited in claim 1, characterized in that the scroll (1) comprises a scroll body (11), an annular groove (12) provided on the scroll body (11), and an annular plate (13) provided covering an opening of the annular groove (12), the annular groove (12) extending in a circumferential direction of the scroll body (11), the annular groove (12) and the annular plate (13) enclosing to form the cooling chamber (B).

3. A water vapour compressor according to claim 2, further comprising a seal (5), the seal (5) being provided at the junction of the annular plate (13) and the volute body (11).

4. A water vapour compressor according to claim 3, characterized in that the end face of the volute body (11) engaging the annular plate (13) comprises a groove-shaped end face, the annular plate (13) being arranged in a groove cavity of the groove-shaped end face, the seal (5) being arranged between a circumferential edge of the annular plate (13) and a side wall of the groove cavity.

5. A water vapor compressor as claimed in claim 1, characterized in that the cooling chamber (B) comprises an annular chamber, which is arranged coaxially with the impeller (2).

6. A water vapour compressor according to claim 5, characterized in that the ratio of the inner diameter of the annular cavity to the diameter of the inlet side of the impeller (2) is in the range (1.2,1.6).

7. The water vapor compressor of claim 1, further comprising a spray flow passage forming a diffusion flow passage (3) between the diffuser plate (8) and the scroll (1), the spray flow passage being disposed between the cooling chamber (B) and the diffusion flow passage (3), the cooling medium comprising cooling water, the spray flow passage being configured to spray the cooling water into the diffusion flow passage (3) through the spray flow passage.

8. The water vapor compressor as recited in claim 7, characterized in that the scroll casing (1) has an exhaust port that discharges compressed gas, the water vapor compressor further comprising an adjusting member provided in the liquid spray flow passage, the adjusting member being configured to adjust the flow rate of the cooling water discharged according to the superheat degree of the compressed gas discharged from the exhaust port.

9. The water vapor compressor as recited in claim 7, further comprising an atomizer (4), the atomizer (4) being disposed at an end of the spray flow path near the diffuser flow path (3), the atomizer (4) being configured to convert cooling water in the cooling chamber (B) into water mist and spray the water mist toward the diffuser flow path (3).

10. A water vapour compressor according to claim 9, comprising a plurality of said atomizer heads (4), the plurality of atomizer heads (4) being circumferentially spaced relative to the axis of the impeller (2).

11. A water vapor compressor according to claim 9, characterized in that the diameter of the atomizer (4) is configured to satisfy the following calculation formula:

A= (4 q/u/n/3.14) ^1/2, where a is the diameter of the atomizer (4), u is the flow rate of droplets ejected from the atomizer (4), u=0.65 x (2 Δp/ρ) ^1/2, n is the number of atomizers (4), Δp is the pressure difference between before and after spraying the liquid by the atomizer (4), ρ is the density of the cooling water, and q is the amount of water to be sprayed when cooling the compressed gas to a set superheat degree.

12. The water vapor compressor as recited in claim 11, characterized in that a calculation formula of the diameter of the atomizer (4) is configured to further satisfy:

n is 4 or 8, and ΔP is greater than or equal to 3bar.

13. The water vapor compressor as recited in claim 7, characterized in that the scroll (1) has an exhaust port that discharges compressed gas, and the discharge pressure of the cooling water is configured to be adjusted according to the superheat degree of the compressed gas discharged from the exhaust port.

14. The water vapor compressor as recited in any one of claims 1 to 13, further comprising a filling channel (6), said filling channel (6) being provided on a housing wall of said volute (1), and a first end of said filling channel (6) being connected to said cooling chamber (B), a second end of said filling channel (6) being externally connected to a cold source, said filling channel (6) being adapted to fill cooling medium into said cooling chamber (B).

15. An air conditioning unit comprising a water vapour compressor as claimed in any one of claims 1 to 14.