CN115217775B - Mixed flow-centrifugal combined centrifugal compressor with diffuser effect reflux device - Google Patents
Mixed flow-centrifugal combined centrifugal compressor with diffuser effect reflux device Download PDFInfo
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- CN115217775B CN115217775B CN202210780897.9A CN202210780897A CN115217775B CN 115217775 B CN115217775 B CN 115217775B CN 202210780897 A CN202210780897 A CN 202210780897A CN 115217775 B CN115217775 B CN 115217775B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
- F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
- F04D29/444—Bladed diffusers
Abstract
The invention discloses a mixed flow-centrifugal combined centrifugal compressor with a diffuser reflux device, which comprises a mixed flow stage, a centrifugal stage and a motor, wherein the outlet of a first-stage mixed flow impeller is connected with the inlet of a first-stage diffuser, the outlet of the first-stage diffuser is connected with one end of a first-stage curve, the other end of the first-stage curve is connected with the inlet of the first-stage reflux device, the outlet of the first-stage reflux device is connected with the inlet of a second-stage impeller, the outlet of the second-stage impeller is connected with the inlet of the second-stage diffuser, the outlet of the second-stage diffuser is connected with one end of a second-stage curve, and the other end of the second-stage curve is connected with the inlet of a second-stage gas collector. The invention can solve the problems of overlarge size, overhigh cost and low efficiency of the compressor in the field of refrigeration air conditioners using water as a refrigerant.
Description
Technical Field
The patent relates to a coaxial multistage centrifugal compressor, in particular to a mixed flow-centrifugal combined centrifugal compressor with a diffuser effect reflux device, and belongs to the technical field of centrifugal compressors.
Background
A coaxial multi-stage centrifugal compressor is used for conveying and increasing the pressure of gas, and the main components of the compressor are an impeller, a diffuser and a reflux device which are matched with the impeller. In the compressor, a medium is introduced into a next stage through a previous stage vane, a diffuser, a bend, and a return. At present, centrifugal impellers are adopted for each stage of the compressor, so that the radial size of the multistage centrifugal compressor is large, and the compressor is large in size, heavy in weight, high in manufacturing cost and large in occupied area. Problems with centrifugal impellers include that the impeller is not as efficient as a mixed flow impeller in terms of flow capacity.
In the refrigeration occasion using water as working medium, the working medium of the compressor is vapor with the temperature of 7-12 ℃, and the gas density is 0.0077566-0.01067kg/m 3 If a coaxial centrifugal compressor with a certain refrigerating capacity is manufactured, because each stage of the machine adopts a centrifugal impeller, the radial size of the steam refrigerating coaxial multistage centrifugal compressor is very large, taking 400kw refrigerating capacity as an example, the outer diameter of the compressor can reach 1400mm. Aiming at the problems, the first stage of the two-stage centrifugal compressor adopts the mixed flow impeller, so that the radial size can be reduced, the through-flow capacity is improved, the efficiency is improved, and the use occasions of large flow and small machine size are met.
The invention provides a backflow device with a pressure-expanding capacity, wherein the inlet flow area of the backflow device is smaller than the outlet flow area, so that the aerodynamic kinetic energy can be further converted into static pressure, and the radial size of the diffuser can be reduced.
Because the reflux device has a diffusion function, if the traditional binary blade reflux device is adopted, airflow is difficult to separate, and flow loss is increased.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a mixed flow-centrifugal combined centrifugal compressor with a diffuser effect reflux device and application thereof.
The utility model provides a mixed flow-centrifugal combination formula centrifugal compressor with diffusion effect backward flow ware which characterized in that: the device comprises a mixed flow stage, a centrifugal stage and a motor, wherein the mixed flow stage is a first stage, and the centrifugal stage is a second stage; the mixed flow stage comprises a first-stage mixed flow impeller, a first-stage diffuser, a first-stage bend and a first-stage return channel; the centrifugal stage comprises a secondary impeller, a secondary diffuser, a secondary bend and a secondary gas collector;
the outlet of the first-stage mixed flow impeller is connected with the inlet of a first-stage diffuser, the outlet of the first-stage diffuser is connected with one end of a first-stage curve channel, the other end of the first-stage curve channel is connected with the inlet of a first-stage reflux device, the outlet of the first-stage reflux device is connected with the inlet of a second-stage impeller, the outlet of the second-stage impeller is connected with the inlet of a second-stage diffuser, the outlet of the second-stage diffuser is connected with one end of a second-stage curve channel, and the other end of the second-stage curve channel is connected with the inlet of a second-stage gas collector;
the first-stage mixed flow impeller and the second-stage impeller are connected with the motor through a compressor main shaft;
the first-stage mixed flow impeller and the second-stage impeller are both open impellers containing splitter blades, and the first-stage mixed flow impeller and the second-stage impeller are coaxial and have the same inlet direction.
Furthermore, the outlet area of the first-stage reflux device is larger than the inlet area of the first-stage reflux device, the outlet area of the second-stage gas collector is larger than the inlet area of the second-stage gas collector, and the blades of the first-stage reflux device and the blades of the second-stage gas collector are all three-dimensional random space twisted blades.
Furthermore, the included angle between the side fixed wall of the outlet disc of the first-stage mixed flow impeller and the axis is 60-85 degrees.
Furthermore, the first-stage diffuser is inclined, the inlet and the outlet of the first-stage diffuser are consistent in width, and the included angle between the center line of the first-stage diffuser and the axis of the compressor is 60-85 degrees.
Furthermore, the inlet of the first-stage bend is inclined, the included angle between the inlet of the first-stage bend and the axis is 5-30 degrees, and the outlet of the first-stage bend is parallel to the axis.
Further, the outlet width of the first-stage mixed flow impeller is b2, the outlet diameter of the first-stage mixed flow impeller is D2, and the ratio of b2 to D2 is 0.08-0.1.
Furthermore, the first-stage mixed flow impeller adopts three-dimensional arbitrary space blades.
Furthermore, the first-stage mixed flow impeller is a splitter blade, the splitter blade on the disk side is located at 10% -20% of the length of the total flow passage, and the splitter blade on the cover side is located at 15% -25% of the length of the total flow passage.
Furthermore, the rotor of the motor, the first-stage mixed-flow impeller and the second-stage impeller jointly form a rotor of the compressor, the motor is provided with no bearing, the motor is supported by a single cantilever, and the rotor of the compressor is supported by magnetic suspension bearings distributed at two ends of the motor and a composite bearing with a bidirectional thrust bearing.
The mixed flow-centrifugal combined centrifugal compressor with the pressure-expanding reflux device is applied to a refrigeration air conditioner using water as a refrigerant.
The working method of the centrifugal compressor comprises the following steps: the air flow firstly flows through the motor to take away partial heat of the motor, the rotor and the stator of the motor are subjected to erosion-resistant treatment and then flow through the front bearing to take away the heat of the front bearing, and then the air flow enters the first-stage mixed-flow impeller, enters the inclined first-stage diffuser after being pressurized and accelerated in the first-stage mixed-flow impeller, enters the first-stage reflux device after being decelerated and pressurized in the first-stage reflux device, further is decelerated and pressurized in the first-stage reflux device, then sequentially enters the second-stage impeller, the second-stage diffuser, the second-stage bend and the second-stage gas collector, and is decelerated and pressurized in the second-stage gas collector and then discharged.
Compared with the prior art, the invention can obtain the following beneficial effects:
1. the compressor of the invention can meet the requirement of large flow with small size, taking water refrigeration as an example, when the refrigeration capacity is 400kw and the inlet of the compressor is 12 ℃, the capacity flow is 909m 3 The invention can meet the requirements with a very small machine size, namely the diameter of an impeller is only 420mm, and the maximum outer diameter of a compressor is only 650mm. For the same flow rate, if a centrifugal impeller is used, the maximum compressor diameter will be 1.15 times that of the compressor of the present invention when the ratio of the diffuser exit diameter D4 to the impeller outer diameter D2 is the same.
2. The reflux device of the compressor has a diffusion effect, and part of the kinetic energy of gas is converted into static pressure rise in the reflux device, so that the diameters of the impeller and the diffuser can be further reduced, if the reflux device does not have the diffusion effect and obtains the same pressure, the size of the compressor needs to be further increased, the size of the compressor can reach about 1.389 times of the size of the compressor with the same design parameters, meanwhile, the weight and the volume of the compressor are correspondingly increased, the cost of the compressor is further increased, and the compressor cannot be installed and used in occasions with load bearing of buildings or limited installation space.
3. In the prior art, the air flow passes through the S-shaped bent pipe after coming out of the diffuser, so that great local resistance loss is caused, and the S-shaped bent pipe is eliminated. When the compressor is applied to an air-conditioning system taking water as a working medium, the medium density is very low, and the density of a primary inlet is 0.0077566-0.01067kg/m 3 At this time, because the number of Re is small, the friction loss is dominant in the loss of the compressor, the efficiency of the compressor is low, and the compressor efficiency is further reduced after passing through the S curve, so that the COP of the whole refrigeration system is reduced, compared with the refrigeration system using Freon, carbon dioxide and the like as working media, the COP of the refrigeration air-conditioning system using water as a refrigerant is smaller, and the centrifugal compressor with the S curve is not suitable for the parameter.
4. The mixed flow impeller blade and the reflux device blade are designed in a unified mode, the aerodynamic coupling of the mixed flow impeller blade and the reflux device blade is considered, and the internal flow loss of a mixed flow stage, including the impeller flow loss, the impact loss of an inlet of the reflux device and the separation loss inside the reflux device, is reduced.
5. Compared with a centrifugal compressor, the compressor with a large flow coefficient is sometimes an axial flow compressor or a compressor combining axial flow and centrifugation, and the manufacture of the compressor is complex and has high cost, taking the axial flow stage as an example, the number of first-stage moving blades is more than 30, and the number of static blades can reach more than 100, and compared with the centrifugal compressor, the manufacture cost is sharply increased; compared with a centrifugal compressor, the performance curve of the axial flow compressor is narrow in flow range and easy to stall, and the narrow flow range is not suitable for application scenarios of an air conditioning system.
Drawings
Fig. 1 is a structural view of a centrifugal compressor according to embodiment 1 of the present invention.
FIG. 2 shows a three-dimensional arbitrary space curved blade with diffuser effect flow-back device according to example 1 of the present invention.
FIG. 3 is a pressure distribution diagram of the suction side and the pressure side of the middle part of the blade of the reflux device blade with diffusion effect in the flow direction of the embodiment 1 of the invention. (the upper curve in the figure is the pressure distribution line of the pressure surface, and the lower curve is the pressure distribution line of the suction surface).
Fig. 4a is a mixed flow impeller with three-dimensional arbitrary space twisted blades according to embodiment 1 of the present invention.
Fig. 4b is a side view of the mixed flow impeller with three-dimensional arbitrarily spatially twisted blades of embodiment 1 of the present invention.
Fig. 5 is a centrifugal compressor stage of comparative example 1 of the present invention (where Z is the axial length and R is the radial length).
Fig. 6 is a mixed flow compressor stage of embodiment 2 of the present invention (where Z is the axial length and R is the radial length).
FIG. 7 is a graph comparing the centrifugal compressor stage efficiency of example 2 of the present invention and the compressor stage efficiency of comparative example 1.
Wherein, 1 is the motor, 2 is the front bearing, 3 is first order mixed flow impeller, 4 is first order diffuser, 5 is the first order bend, 6 is the first order backward flow ware, 7 is the second order impeller, 8 is the second order diffuser, 9 is the second order bend, 10 is the second order gas collector, 11 is composite bearing, 12 is the compressor main shaft, 13 is the back bearing support, 14 is the front bearing support, 15 is the motor support.
Detailed Description
The invention will be described in further detail with reference to the following figures and specific examples, which are given by way of illustration only and are not intended to limit the scope of the invention.
Example 1
A mixed flow-centrifugal combined centrifugal compressor with a diffuser effect reflux device comprises a mixed flow stage, a centrifugal stage, a motor 1, a front bearing 2, a composite bearing 11 and a compressor main shaft 12, wherein the mixed flow stage is a first stage, and the centrifugal stage is a second stage; the mixed flow stage comprises a first-stage mixed flow impeller 3, a first-stage diffuser 4, a first-stage bend 5 and a first-stage reflux device 6; the centrifugal stage comprises a secondary impeller 7, a secondary diffuser 8, a secondary bend 9 and a secondary gas collector 10;
the motor support 15 is arranged outside the motor 1, the compressor main shaft 12 which is common with the compressor is arranged in the center, the front bearing 2 is provided with the front bearing support 14, the composite bearing 11 at the rear end is provided with the rear bearing support 13, the composite bearing 11 at the rear end is a support and thrust composite bearing and is provided with a left thrust surface and a right thrust surface, the axial thrust of the compressor impeller is balanced, the compressor main shaft 12 is supported by the front bearing 2 and the composite bearing 11 together, and the first-stage mixed-flow impeller 3 and the second-stage impeller 7 are arranged on the compressor main shaft 12.
The outlet of the first-stage mixed flow impeller is connected with the inlet of the first-stage diffuser, the outlet of the first-stage diffuser is connected with one end of the first-stage bend, the other end of the first-stage bend is connected with the inlet of the first-stage reflux device, the outlet of the first-stage reflux device is connected with the inlet of the second-stage impeller, the outlet of the second-stage impeller is connected with the inlet of the second-stage diffuser, the outlet of the second-stage diffuser is connected with one end of the second-stage bend, and the other end of the second-stage bend is connected with the inlet of the second-stage gas collector;
the first-stage mixed flow impeller and the second-stage impeller are both open impellers containing splitter blades, and the first-stage mixed flow impeller and the second-stage impeller are coaxial and have the same inlet direction.
The outlet area of the first-stage reflux device is larger than the inlet area of the first-stage reflux device, the outlet area of the second-stage gas collector is larger than the inlet area of the second-stage gas collector, and the blades of the first-stage reflux device and the blades of the second-stage gas collector are all three-dimensional randomly-twisted blades.
The angle between the side fixed wall of the outlet disc of the first-stage mixed flow impeller and the axis is 60-85 degrees.
The first stage diffuser is inclined, the inlet and outlet widths of the first stage diffuser are consistent, and the included angle between the center line of the first stage diffuser and the axis of the compressor is 60-85 degrees.
The inlet of the first-stage bend is inclined and forms an angle of 5-30 degrees with the axis, and the outlet of the first-stage bend is parallel to the axis.
The outlet width of the first-stage mixed flow impeller is b2, the outlet diameter of the first-stage mixed flow impeller is D2, and the ratio of b2 to D2 is 0.08-0.1.
The first-stage mixed flow impeller adopts three-dimensional arbitrary space blades.
The first-stage mixed flow impeller is a splitter blade, the splitter blade on the disk side is positioned at 10% -20% of the length of the total flow channel, and the splitter blade on the cover side is positioned at 15% -25% of the length of the total flow channel.
The rotor of the motor, the first-stage mixed flow impeller and the second-stage impeller jointly form the rotor of the compressor, the motor has no bearing, the support of the motor is a single cantilever support, and the support of the rotor of the compressor is a magnetic suspension bearing and a composite bearing with a bidirectional thrust bearing, which are distributed at two ends of the rotor.
In the invention, after the airflow comes out of the first-stage mixed flow impeller, the airflow passes through the inclined first-stage diffuser and is not forced to turn into a radial direction any more, so that the flow loss can be reduced, and the radial size is reduced.
Comparative example 1
Design parameters of the compressor: the working medium is steam, the inlet temperature is 12 ℃, the inlet pressure is 1.402KPaA, the outlet static pressure is 3.033KPaA, the mass flow is 582kg/h, and the inlet volume flow is 909m 3 Min, design rotation speed n =21600rpm, impeller blade outlet installation angle beta 2A =65 °. The centrifugal impeller in the prior art is adopted, the reflux device has no diffusion effect, the design result is that the diameter D2 of the impeller is =444mm, and at the moment, the maximum outer diameter D of the compressor stage bend is 42 815mm as shown in fig. 5.
Example two
The mixed-flow centrifugal combined centrifugal compressor with the diffuser-effect reflux device in the embodiment 1 is applied to a refrigeration air conditioner using water as a refrigerant. The embodiment and the comparative example have the same aerodynamic design parameters, the same design rotating speed n =21600rpm and the same impeller blade outlet installation angle beta 2A =65 °. With the compressor of embodiment 1 of the present invention, as shown in fig. 1, the included angle between the side fixed wall of the outlet disk of the first-stage mixed-flow impeller and the axis of the compressor is 60 degrees, and the inlet end of the first-stage mixed-flow impeller maintains the characteristics of a centrifugal impeller, so that the axial size of the impeller is shortened. The airflow directly enters the first-stage return device from the first-stage bend, so that the through-flow distance is shortened to the maximum extent, and the on-way friction loss and the local resistance loss caused by multiple turns are reduced, wherein the loss can cause the compressor to be applied to the refrigeration and air-conditioning field which takes water as the refrigerantThe domain is failed. The airflow is continuously diffused in the first-stage reflux device, the first-stage reflux device plays a part of the function of the diffuser, the static-static pressure ratio of the outlet of the first-stage reflux device relative to the inlet of the first-stage reflux device is 1.1, and the maximum outer diameter D of the compressor-stage bend at the moment 42 590mm, as shown in fig. 6, the outer diameter is only about 72% thereof, which greatly reduces the radial size of the compressor, compared to the comparative example. The results of the CFD calculations show that the stage efficiency of the compressor of the present invention (mixed flow compressor) is slightly higher than the stage efficiency of the comparative example compressor (centrifugal compressor), as shown in fig. 7.
The invention greatly reduces the radial dimension of the machine and improves the efficiency of the machine. In the field of refrigeration and air conditioning, when the refrigerant is pure water, the compressor disclosed by the invention is small in size, and can meet the requirement of reducing the manufacturing cost; meanwhile, the compressor keeps higher efficiency and ensures the COP of the whole refrigeration system.
The above description is only a preferred embodiment of the present invention, and any person skilled in the art can apply the equivalent structural changes made by the present invention, or apply the equivalent structural changes directly or indirectly to other related products, especially to the air-conditioning field using water as refrigerant, and the same shall be included in the protection scope of the present invention.
Claims (5)
1. The utility model provides a mixed flow-centrifugal combination formula centrifugal compressor with diffusion effect backward flow ware which characterized in that: the device comprises a mixed flow stage, a centrifugal stage and a motor, wherein the mixed flow stage is a first stage, and the centrifugal stage is a second stage; the mixed flow stage comprises a first-stage mixed flow impeller, a first-stage diffuser, a first-stage bend and a first-stage return channel; the centrifugal stage comprises a secondary impeller, a secondary diffuser, a secondary bend and a secondary gas collector;
the outlet of the first-stage mixed flow impeller is connected with the inlet of a first-stage diffuser, the outlet of the first-stage diffuser is connected with one end of a first-stage curve channel, the other end of the first-stage curve channel is connected with the inlet of a first-stage reflux device, the outlet of the first-stage reflux device is connected with the inlet of a second-stage impeller, the outlet of the second-stage impeller is connected with the inlet of a second-stage diffuser, the outlet of the second-stage diffuser is connected with one end of a second-stage curve channel, and the other end of the second-stage curve channel is connected with the inlet of a second-stage gas collector;
the first-stage mixed-flow impeller and the second-stage impeller are connected with the motor through a compressor main shaft;
the first-stage mixed flow impeller and the second-stage impeller are both open impellers containing splitter blades, and the first-stage mixed flow impeller and the second-stage impeller are coaxial and have the same inlet direction;
the included angle between the side fixed wall of the outlet disc of the first-stage mixed flow impeller and the axis is 60-85 degrees;
the first stage diffuser is inclined, the width of an inlet and the width of an outlet of the first stage diffuser are consistent, and the included angle between the center line of the first stage diffuser and the axis of the compressor is 60-85 degrees;
the outlet width of the first-stage mixed flow impeller is b2, the outlet diameter of the first-stage mixed flow impeller is D2, and the ratio of b2 to D2 is 0.08-0.1;
the rotor of the motor, the first-stage mixed flow impeller and the second-stage impeller jointly form a rotor of the compressor, the motor is not provided with a bearing, the support of the motor is a single cantilever support, and the support of the rotor of the compressor is a magnetic suspension bearing distributed at two ends of the rotor and a composite bearing with a bidirectional thrust bearing;
there is no S-bend behind the diffuser of the compressor;
the outlet area of the first-stage reflux device is larger than the inlet area of the first-stage reflux device, the outlet area of the second-stage gas collector is larger than the inlet area of the second-stage gas collector, and the blades of the first-stage reflux device and the blades of the second-stage gas collector are all three-dimensional randomly-twisted blades.
2. A combined mixed-flow and centrifugal compressor with diffuser effect return as claimed in claim 1, wherein: the inlet of the first-stage bend is inclined, the included angle between the inlet of the first-stage bend and the axis is 5-30 degrees, and the outlet of the first-stage bend is parallel to the axis.
3. A combined mixed-flow and centrifugal compressor with diffuser effect return as claimed in claim 1, wherein: the first-stage mixed flow impeller adopts three-dimensional random space blades.
4. A combined mixed-flow and centrifugal compressor with diffuser effect return as claimed in claim 1, wherein: the first-stage mixed flow impeller is a splitter blade, the splitter blade on the disk side is positioned at 10% -20% of the length of the total flow channel, and the splitter blade on the cover side is positioned at 15% -25% of the length of the total flow channel.
5. Use of a combined centrifugal compressor with diffuser reflux as claimed in any one of claims 1 to 4 in refrigeration air conditioning with water as refrigerant.
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0949498A (en) * | 1995-06-01 | 1997-02-18 | Ishikawajima Harima Heavy Ind Co Ltd | Multistage compressor |
| CN104653496A (en) * | 2015-01-27 | 2015-05-27 | 浙江理工大学 | Single-double-suction adjustable centrifugal ventilator |
| WO2022013069A1 (en) * | 2020-07-15 | 2022-01-20 | Ventilatorenfabrik Oelde Gmbh | Radial fan |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3759627A (en) * | 1972-02-14 | 1973-09-18 | Allis Chalmers | Compressor assembly |
| CN101105346B (en) * | 2007-08-23 | 2011-06-22 | 广东西屋康达空调有限公司 | Frequency conversion magnetic levitation compression expansion engine set |
| EP3121450B1 (en) * | 2015-07-23 | 2020-09-02 | Sulzer Management AG | Pump for conveying a fluid with varying viscosity |
| BE1024644B1 (en) * | 2017-03-07 | 2018-05-14 | Atlas Copco Airpower Naamloze Vennootschap | Compressor module for compressing gas and compressor equipped with it |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0949498A (en) * | 1995-06-01 | 1997-02-18 | Ishikawajima Harima Heavy Ind Co Ltd | Multistage compressor |
| CN104653496A (en) * | 2015-01-27 | 2015-05-27 | 浙江理工大学 | Single-double-suction adjustable centrifugal ventilator |
| WO2022013069A1 (en) * | 2020-07-15 | 2022-01-20 | Ventilatorenfabrik Oelde Gmbh | Radial fan |
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| CN115217775A (en) | 2022-10-21 |
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