WO2022111396A1 - 闭式叶轮和具有其的离心压缩机 - Google Patents

闭式叶轮和具有其的离心压缩机 Download PDF

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Publication number
WO2022111396A1
WO2022111396A1 PCT/CN2021/131830 CN2021131830W WO2022111396A1 WO 2022111396 A1 WO2022111396 A1 WO 2022111396A1 CN 2021131830 W CN2021131830 W CN 2021131830W WO 2022111396 A1 WO2022111396 A1 WO 2022111396A1
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WIPO (PCT)
Prior art keywords
blades
closed impeller
wheel
blade
wheel disc
Prior art date
Application number
PCT/CN2021/131830
Other languages
English (en)
French (fr)
Inventor
韩聪
殷纪强
李思茹
常云雪
朱万朋
俞国新
桂幸民
陈锦践
毛守博
宋强
李银银
劳春峰
Original Assignee
青岛海尔智能技术研发有限公司
海尔智家股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 青岛海尔智能技术研发有限公司, 海尔智家股份有限公司 filed Critical 青岛海尔智能技术研发有限公司
Publication of WO2022111396A1 publication Critical patent/WO2022111396A1/zh

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Classifications

    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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
    • F04D29/285—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors the compressor wheel comprising a pair of rotatable bladed hub portions axially aligned and clamped together
    • 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
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps

Definitions

  • the present invention relates to the technical field of compressors, in particular to a closed impeller and a centrifugal compressor having the same.
  • An object of the present invention is to overcome at least one defect in the prior art, and to provide a closed impeller and a centrifugal compressor having the same, which facilitates precision treatment of blades.
  • a further object of the present invention is to improve assembly efficiency.
  • Another further object of the present invention is to reduce the requirement on the strength of the connection between the wheel disc and the wheel cover.
  • the present invention provides a closed impeller for a centrifugal compressor, comprising:
  • a wheel disc a plurality of first blades arranged along the circumferential direction of the wheel disc are formed on one surface of the wheel disc;
  • the wheel cover is detachably connected to the wheel disc, and a side surface of the wheel cover facing the wheel disc is formed with a plurality of second blades, and the plurality of first blades and the plurality of second blades are butted one by one to form the blades of the closed impeller .
  • At least part of the first blade has a first positioning portion
  • At least part of the second blade has a second positioning portion
  • the first positioning portion and the second positioning portion are configured such that when the wheel cover is connected to the wheel disc, the first positioning portion and the second positioning portion are mutually restrained to position the wheel cover and the wheel disc.
  • the first positioning portion is a positioning recessed portion opened on the first blade
  • the second positioning portion is a positioning protrusion protruding from the surface of the second blade.
  • the inner peripheral wall of the positioning concave portion has an abutting section facing the rotation direction of the closed impeller, so as to exert a thrust on the positioning protrusion when the closed impeller rotates.
  • each first blade has a threaded hole
  • each second blade has a screw hole that communicates with the wheel cover, and the threaded hole and the screw hole are arranged in one-to-one correspondence, so that the wheel cover is fixed to the wheel with screws. on the plate.
  • each first blade has a first positioning portion
  • the threaded holes on each of the first blades are opened on the first positioning portion.
  • roulette wheel is circular;
  • the diameter of the roulette is not more than 80mm.
  • a first rounded corner is formed at the connection between the wheel disc and the first blade
  • a second fillet is formed at the connection between the wheel cover and the second blade.
  • each first fillet is between 1/8 and 1 of the height of the first blade
  • the radius of each second fillet is between 1/8 and 1 of the height of the second blade.
  • the present invention also provides a centrifugal compressor comprising the closed impeller of any one of the above.
  • the wheel cover is detachably connected to the wheel disk, and the side surface of the wheel cover facing the wheel disk is formed There are a plurality of second blades, and a plurality of first blades and a plurality of second blades are butted one by one to constitute the blades of the closed impeller.
  • the wheel disc and wheel cover are separated, so that when the wheel disc and wheel cover are formed separately, the overall height of the blades of the closed impeller can be shortened, which is convenient for the installer to further optimize the accuracy of the first blade and the second blade, so that the blades The surface roughness meets the requirements; and in this way, the tool can also extend into the adjacent first blades or the adjacent second blades, so as to facilitate the processing of rounded corners between the first and second blades, further making the closed
  • the air flow channel of the impeller is smoother, realizing a smooth transition and avoiding the angular vortex generated when the gas circulates in the air flow channel.
  • the first blade is provided with a first positioning portion
  • the second blade is provided with a second positioning portion.
  • the inner peripheral wall of the positioning recess has an abutting section facing the rotation direction of the closed impeller. Since the wheel disc is connected to the rotor of the motor, when the motor drives the closed impeller to rotate, the wheel disc is rotated. In fact, as the driving wheel, the wheel cover acts as the driven wheel.
  • the positioning protrusion When the wheel disk drives the wheel cover to rotate, at least a part of the positioning protrusion can abut on the abutting section, so that the abutting section can assist in transferring the torque of the wheel disk to the wheel cover, so that the positioning
  • the pre-positioning structure composed of the protruding part and the positioning concave part can not only realize the positioning, but also transmit the torque, which reduces the requirement on the connection strength of the wheel disc and the wheel cover.
  • FIG. 1 is a schematic diagram of a complete machine structure of a centrifugal compressor according to an embodiment of the present invention
  • Fig. 2 is a schematic cross-sectional view obtained by cutting the centrifugal compressor shown in Fig. 1 along the axial direction of the centrifugal impeller;
  • Fig. 3 is the enlarged view of A place of Fig. 2;
  • FIG. 4 is a schematic diagram of a closed impeller in a centrifugal compressor according to an embodiment of the present invention
  • Figure 5 is an exploded view of a closed impeller according to one embodiment of the present invention.
  • Figure 6 is a front view of a wheel disc in a closed impeller according to an embodiment of the present invention, wherein the arrows show the direction of rotation of the wheel disc;
  • FIG. 7 is a schematic diagram of a wheel cover in a closed impeller according to an embodiment of the present invention, wherein the arrows show the rotation direction of the wheel cover;
  • FIG. 8 is a front view of a wheel disc in a closed impeller according to another embodiment of the present invention, wherein the threaded hole is shown in the positioning recess;
  • Fig. 9 is a positional relationship diagram of the vanes, the wheel cover and the disc of the closed impeller according to an embodiment of the present invention, wherein H1 represents the height of the first vane, H2 represents the height of the second vane, and R1 represents the height of the first rounded corner Radius, R2 represents the radius of the second fillet.
  • FIG. 1 is a schematic diagram of the whole machine structure of a centrifugal compressor according to an embodiment of the present invention
  • FIG. 2 is a schematic diagram obtained by cutting the centrifugal compressor shown in FIG. 1 along the axial direction of the centrifugal impeller
  • Figure 3 is an enlarged view of part A of Figure 2.
  • the centrifugal compressor 1 may generally comprise a casing 10 , a motor 40 and at least one compression unit 20 , 30 .
  • the casing 10 defines an accommodating space, and the motor 40 is installed in the casing 10 .
  • the motor 40 includes a stator 41 and a rotor 42 , the stator 41 is fixed to the casing 10 , and the rotor 42 is rotatable relative to the stator 41 .
  • the number of compression units 20, 30 may be one or more.
  • the centrifugal compressor 1 may be a single-stage compression type, and only one compression unit may be provided.
  • the centrifugal compressor 1 may also be of a multi-stage compression type in which a plurality of compression units 20, 30 are provided.
  • Each compression unit 20 , 30 includes a volute 100 mounted to the casing 10 and a closed impeller 200 disposed within the volute 100 .
  • the closed impeller 200 is configured to rotate under the driving of the motor 40 to compress the airflow entering the volute 100 and discharge it through the outlet of the volute 100 .
  • the centrifugal compressor 1 can be a two-stage compression type, and the number of compression units is two. It can be seen that one of the two compression units 20 and 30 must be a low pressure stage and the other is a high pressure stage. As shown in FIG. 1 and FIG. 2 , the compression unit 20 on the left side of the drawing is the low pressure stage, and the compression unit 30 on the right side is the low pressure stage. for the high pressure level.
  • the outlet of the volute 100 of the compression unit 20 of the low pressure stage communicates with the inlet of the volute 100 of the compression unit 30 of the high pressure stage through the connecting pipe 50 .
  • connection pipe 50 is provided with a flange 51 to connect with the flange 60 of the outlet of the volute 100 of the compression unit 20 of the low pressure stage, and the outlet end of the connection pipe 50 is provided with a flange 52 to be connected to the outlet of the compression unit 30 of the high pressure stage.
  • the volute 100 is connected.
  • the compression unit 20 of the low pressure stage and the compression unit 20 of the high pressure stage are located on both sides of the motor 40 in the axial direction, so that the closed impellers 200 of the two compression units 20 and 30 are directly connected to the motor 40, and it is convenient for the two The axial force of the closed impeller 200 is partially offset.
  • the volute 100 defines an inlet flow channel 101, a scroll-shaped flow channel 102 and an outlet flow channel 103 which are connected in sequence along the airflow direction, that is, the flow channel of the volute 100 is divided into three sections.
  • the inlet of the intake runner 101 constitutes the inlet of the volute 100 described herein, and the outlet of the outlet runner 103 constitutes the outlet of the volute 100 .
  • the intake flow passage 101 extends in the axial direction (x-axis direction) of the closed impeller 200 .
  • FIG. 4 is a schematic diagram of a closed impeller in a centrifugal compressor according to an embodiment of the present invention
  • FIG. 5 is an exploded view of a closed impeller according to an embodiment of the present invention
  • FIG. Figure 7 is a schematic diagram of a wheel cover in a closed impeller according to an embodiment of the present invention, wherein the arrows show the rotation direction of the wheel cover.
  • the closed impeller 200 has an inlet 201 facing the intake runner 101 and an outlet 202 facing the volute runner 102.
  • the airflow entering from the intake runner 101 first enters the closed impeller 200 from the inlet 201 of the closed impeller 200, and passes through the closed impeller 200. After being compressed, the impeller 200 discharges it to the outlet 202 , enters the spiral flow channel 102 , and finally discharges the centrifugal compressor 1 from the outlet flow channel 103 .
  • the closed impeller 200 may further include a wheel disc 210 and a wheel cover 220 , wherein a plurality of first blades 212 are formed on one side surface of the wheel disc 210 and arranged along the circumferential direction thereof, and the wheel cover 220 is detachably connected to the wheel disc 210 , and a plurality of second blades 222 are formed on the side surface of the wheel cover 220 facing the wheel disc 210, and the plurality of first blades 212 and the plurality of second blades 222 are butted one by one to constitute the blades of the closed impeller 200 (as shown in FIG. 4 shown).
  • the blades of the closed impeller 200 are divided into two parts, namely the first blade 212 formed on the wheel disc 210 and the second blade 222 formed on the wheel cover 220 , and the wheel disc 210 and the wheel cover 220
  • the first blade 212 and the second blade 222 may be directly formed on the wheel disc 210 and the wheel cover 220 by means of separate processing (eg casting, etc.).
  • the first blade 212 is abutted with the second blade 222, so that the wheel disc 210 and the wheel cover 220 form the blades of the closed impeller 200, so that two adjacent blades
  • the airflow channel 2102 of the closed impeller 200 is formed therebetween.
  • the first blades 212 and the second blades 222 can be evenly arranged along the circumference of the wheel disc 210 and the wheel cover 220 , and are respectively located outside the wheel disc 210 and the wheel cover 220 , and in the middle of the wheel disc 210 .
  • Mounting holes 218 may be formed into which fasteners (eg, rivets, screws 300 , etc.) can be inserted to mount the disc 210 on the rotor 42 of the motor 40 , thereby enabling the rotor 42 to drive the disc 210 to rotate.
  • the wheel cover 220 can be arranged in a ring shape, and the inner ring of the wheel cover 220 extends in a direction away from the second blade 222 to form a connecting section 228 , and the interior of the connecting section 228 can also define the inlet 201 of the closed impeller 200 .
  • the direction away from the second blade 222 may extend in the direction of the central axis of the wheel cover 220 and extend in the direction away from the second blade 222 .
  • the processing of impellers for high-speed centrifuges with low cooling capacity has become an industry problem, especially for micro-miniature closed impellers.
  • the casting can be integrally formed, the surface roughness of the small impeller has high requirements, and the casting process is difficult to directly meet the precision requirements, and the small impeller is too small to use other measures to accurately treat its interior.
  • the blades are respectively arranged on the wheel disc 210 and the wheel cover 220, and the wheel disc 210 and the wheel cover 220 are of a split type, so that the After the disc 210 and the wheel cover 220 are respectively formed, the overall height of the blades of the closed impeller 200 is shortened, so that the installer can further optimize the precision of the first blade 212 and the second blade 222, so that the surface roughness of the blades meets the requirements; and this The method can also make the tool etc.
  • the air flow channel 2102 is smoother, so that a smooth transition is realized, and angular vortices are avoided when the gas circulates in the air flow channel 2102 .
  • the closed impeller 200 of the present embodiment can also add a pre-positioning structure on the basis of the split type.
  • the pre-positioning structure can be used in the process of assembling the wheel disc 210 and the wheel cover 220 pre-positioning.
  • first blades 212 have a first positioning portion 214
  • second blades 222 have a second positioning portion 224 .
  • the first positioning portion 214 and the second positioning portion 224 are configured to be connected to the wheel cover 220 .
  • the first positioning portion 214 and the second positioning portion 224 are mutually restrained to position the roulette 210 and the wheel cover 220 .
  • the number of the first blades 212 may be multiple, and a first positioning portion 214 may be provided on some or all of the first blades 212 of the multiple first blades 212 .
  • a first positioning portion 214 may be provided on some or all of the first blades 212 of the multiple first blades 212 .
  • each first positioning portion 214 can be correspondingly disposed on one first blade 212, or several first positioning portions 214 of the plurality of first positioning portions 214 are jointly disposed on one first blade 212; for another example, when there are three first positioning portions 214, the three first positioning portions 214 may be They are respectively arranged on three different first blades 212, or can be arranged on two first blades 212 (one of the first blades 212 is arranged with one, and the other first blade 212 is arranged with two pieces), or three first blades 212 are arranged.
  • the two positioning portions 224 are all centrally disposed on one of the first blades 212 .
  • the first positioning portion 214 is a positioning concave portion formed on the first blade 212
  • the second positioning portion 224 is a positioning protrusion protruding from the surface of the second blade 222 . department.
  • the first blade 212 is recessed inward to form a positioning concave portion, and correspondingly, the top end of the second blade 222 protrudes outward to form a positioning protrusion that cooperates with the positioning concave portion.
  • the positioning protrusions may extend into the corresponding positioning recesses to position the wheel cover 220 and the wheel disc 210 .
  • the positioning protrusions and the positioning recesses when the positioning protrusions and the positioning recesses are a group (one positioning protrusion and one positioning recess are a group), the positioning protrusions and the positioning recesses may also be respectively set to be non-circular shape, such as a triangle, a quadrilateral or other special shapes, so that the positioning protrusions and the positioning recesses are shaped to match, so that when the positioning protrusions and positioning recesses are only one set, the wheel cover 220 and the wheel disc 210 can be aligned. position.
  • the positioning protrusions and positioning recesses may be in any shape, such as polygonal, cylindrical, etc.
  • each positioning protrusion correspondingly extends into the positioning recess, the The positioning of the wheel cover 220 and the wheel disc 210 can be achieved.
  • the inner peripheral wall of the positioning recess has an abutment section 214 a facing the rotation direction of the closed impeller 200 , so as to exert a thrust on the positioning protrusion when the closed impeller 200 rotates.
  • the wheel disc 210 Since the wheel disc 210 is connected with the rotor 42 of the motor 40, when the motor 40 drives the closed impeller 200 to rotate, the wheel disc 210 actually acts as a driving wheel, and the wheel cover 220 acts as a driven wheel.
  • the wheel disc 210 drives the wheel cover 220 to rotate, at least a part of the positioning protrusion can abut against the abutting section 214a, so that the abutting section 214a can assist in transferring the torque of the wheel disc 210 to the wheel
  • the pre-positioning structure composed of the positioning protrusions and the positioning recesses can not only achieve positioning, but also transmit torque, which reduces the requirement on the connection strength of the wheel disc 210 and the wheel cover 220 .
  • the wheel disc 210 and the wheel cover 220 may be fastened by means of screw connection.
  • each first blade 212 has a threaded hole 216
  • each second blade 222 has a screw hole 226 that communicates with the wheel cover 220.
  • the screw holes 216 and the screw holes 226 are arranged in a one-to-one correspondence, so as to use the
  • the screw 230 fixes the wheel cover 220 on the wheel disc 210 .
  • the installer can first use the first positioning portion 214 and the second positioning portion 224 to pre-position the wheel disc 210 and the wheel cover 220 , and then insert the screw 230 through the screw hole 226 and into the first blade 212 The screw 230 is finally connected with the screw hole 216 to realize the fast connection between the wheel disc 210 and the wheel cover 220 .
  • a plurality of threaded holes 216 can be arranged on the circumference that is concentric with the wheel disc 210, so as to avoid the eccentricity of the closed impeller 200, thereby avoiding the occurrence of eccentricity in the closed impeller. Abnormal phenomena such as vibration and noise occurred during the high rotation of the impeller 200.
  • FIG. 8 is a front view of a wheel disc in a closed impeller according to another embodiment of the present invention, wherein the threaded hole is shown in the positioning recess.
  • each first blade 212 has a first positioning portion 214
  • the threaded hole 216 on each first blade 212 is opened on the first positioning portion 214 . Since each first vane 212 has a threaded hole 216 and each first vane 212 has a first positioning portion 214, the threaded hole 216 can be disposed on the first positioning portion 214, that is, in the positioning concave portion, Makes the tightening effect better.
  • the roulette 210 may be configured in a circular shape, and its diameter may be configured to be no greater than 80mm, such as 80mm, 70mm, 60mm, and the like.
  • the existing casting process cannot meet the precision requirements of the inner blades, especially when the diameter of the wheel disc 210 is not greater than 80 mm, because the overall size is too small, the processing personnel cannot perform the precision treatment process on the inner blades .
  • the split assembly method of this embodiment is used, that is, the wheel disc 210 and the wheel cover 220 are cast separately, the first blade 212 or the second blade 222 is exposed to the outside, and then the precision treatment process is performed on them. Qualified blades can be processed on the basis of realizing the miniaturization of the closed impeller 200 .
  • FIG. 9 is a schematic diagram of the positional relationship between the wheel disc, the wheel cover and the blades in the closed impeller according to an embodiment of the present invention.
  • a first fillet 242 is formed at the connection between the wheel disc 210 and the first blade 212
  • a second fillet 244 is formed at the connection between the wheel cover 220 and the second blade 222 .
  • connection between the wheel disc 210 and the first blade 212 or the connection between the wheel cover 220 and the second blade 222 may be provided with the first rounded corner 242 or the second rounded corner 244, or may be a wheel
  • a first fillet 242 and a second fillet 244 are respectively provided at the connection between the disk 210 and the first blade 212 and the connection between the wheel cover 220 and the second blade 222 .
  • the first rounded corners 242 and the second rounded corners 244 can not only improve the strength of the roots of the first blade 212 and the second blade 222 and relieve the local stress concentration, but also make each airflow channel 2102 smoother and eliminate the corners of the airflow.
  • the vortex phenomenon ensures the uniformity of the flow field.
  • H1 represents the height of the first blade 212
  • H2 represents the height of the second blade 222
  • R1 represents the radius of the first fillet 242
  • R2 represents the radius of the second fillet 244
  • the radius R1 of a rounded corner 242 can also be configured to be between 1/8 and 1 of the height H1 of the first blade
  • the radius R2 of the second rounded corner 244 can also be configured to be between 1/8 and 1 of the height H2 of the second blade. , for example, 1/8, 1/5, or 1, etc.
  • the inventor has found through many experiments that the above-mentioned limitation can ensure that a better airflow field can be obtained without affecting the area of the airflow channel 2102, so as to further improve the compression effect.
  • the ratio of the radius R1 of the first rounded corner 242 to the height H1 of the first blade is 1, and when the ratio of the radius R2 of the second rounded corner 244 to the height H2 of the second blade is 1, that is, the first rounded corner 242
  • the radius R1 is equal to the height H1 of the first blade
  • the radius R2 of the second rounded corner 244 is equal to the height H2 of the second blade 222
  • the inner wall of the airflow channel 2102 is composed of the first rounded corner 242 and the second rounded corner 244 as a whole
  • the entire inner wall of the airflow channel 2102 is in a circular arc shape.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种闭式叶轮和具有其的离心压缩机，该闭式叶轮（200）包括轮盘（210）和轮盖（220），轮盘（210）一侧表面上形成有沿其周向排列的多个第一叶片（212），轮盖（220）与轮盘（210）可拆卸连接，并且轮盖（220）朝向轮盘（210）的一侧表面形成有多个第二叶片（222），多个第一叶片（212）与多个第二叶片（222）一一对接，以构成闭式叶轮（200）的叶片。该闭式叶轮（200）中轮盘（210）和轮盖（220）采用分体式，当轮盘（210）和轮盖（220）各自成型后，缩短了闭式叶轮（200）的叶片整体高度，便于安装人员进一步对第一叶片（212）和第二叶片（222）进行精度优化处理。

Description

闭式叶轮和具有其的离心压缩机 技术领域
本发明涉及压缩机技术领域，特别是涉及一种闭式叶轮和具有其的离心压缩机。
背景技术
近年来，随着高速电机及控制技术的成熟，磁悬浮和气悬浮等高速压缩机快速发展，用户所需要的离心机的冷量范围也越来越广，小冷量高速离心机的需求日渐增多。而小冷量高速离心机的叶轮加工成为行业难题，尤其是微小型的闭式叶轮。虽然铸造可以一体成型，但小型叶轮表面粗糙度等要求较高，铸造工艺难以直接满足精度要求，并且小型叶轮由于尺寸过小，也难以使用其他措施对其内部进行精度处理。
发明内容
本发明的一个目的旨在克服现有技术中的至少一个缺陷，提供一种便于对叶片进行精度处理的闭式叶轮和具有其的离心压缩机。
本发明一个进一步的目的是提高组装效率。
本发明另一个进一步的目的是降低轮盘和轮盖连接强度的要求。
特别地，本发明提供了一种用于离心压缩机的闭式叶轮，包括：
轮盘，其一侧表面上形成有沿轮盘的周向排列的多个第一叶片；
轮盖，与轮盘可拆卸连接，并且轮盖朝向轮盘的一侧表面形成有多个第二叶片，多个第一叶片与多个第二叶片一一对接，以构成闭式叶轮的叶片。
进一步地，至少部分第一叶片上具有第一定位部；且
至少部分第二叶片上具有第二定位部；
第一定位部与第二定位部配置成在轮盖连接于轮盘时，第一定位部与第二定位部相互约束，以对轮盖和轮盘的位置定位。
进一步地，第一定位部为开设于第一叶片上的定位凹陷部；且
第二定位部为凸出于第二叶片表面的定位凸出部。
进一步地，定位凹陷部的内周壁具有朝向闭式叶轮转动方向的抵接区段，以便在闭式叶轮转动时对定位凸出部施加推力。
进一步地，每个第一叶片上具有一螺纹孔，每个第二叶片上具有一与轮 盖相贯通的螺钉孔，螺纹孔与螺钉孔一一对应设置，以便利用螺钉将轮盖固定于轮盘上。
进一步地，每个第一叶片上具有一第一定位部；且
各第一叶片上的螺纹孔开设于第一定位部上。
进一步地，轮盘为圆形；且
轮盘的直径不大于80mm。
进一步地，轮盘与第一叶片的连接处形成有第一圆角；且/或
轮盖与第二叶片的连接处形成有第二圆角。
进一步地，每个第一圆角的半径为第一叶片高度的1/8至1之间；
每个第二圆角的半径为第二叶片高度的1/8至1之间。
特别地，本发明还提供了一种离心压缩机，该离心压缩机包括上述任一项中的闭式叶轮。
本发明的闭式叶轮中，由于轮盘的一侧表面上形成有沿其周向排列的多个第一叶片，轮盖与轮盘可拆卸连接，并且轮盖朝向轮盘的一侧表面形成有多个第二叶片，多个第一叶片与多个第二叶片一一对接，构成了闭式叶轮的叶片。轮盘和轮盖采用分体式，这样可以实现当轮盘和轮盖各自成型后，缩短闭式叶轮的叶片整体高度，便于安装人员进一步对第一叶片和第二叶片进行精度优化处理，使得叶片表面粗糙度满足要求；并且这种方式还能够使得刀具等伸入相邻的第一叶片或者相邻的第二叶片之间，便于在第一叶片和第二叶片加工出圆角，进一步使得闭式叶轮的气流流道更加光滑，实现圆滑过渡，避免气体在气流流道内流通时产生角涡。
进一步地，本发明的闭式叶轮中，第一叶片上具有第一定位部，第二叶片上具有第二定位部，在轮盖连接于轮盘时，第一定位部与第二定位部相互约束，以对轮盘和轮盖的位置定位，提高了组装效率。
进一步地，本发明的闭式叶轮中，定位凹陷部的内周壁具有朝向闭式叶轮转动方向的抵接区段，由于轮盘与电机的转子相连，当电机驱动闭式叶轮转动时，轮盘实际上作为主动轮，轮盖作为从动轮。当轮盘驱动轮盖转动时，定位凸出部的至少一部分可以抵靠于该抵接区段上，这样抵接区段可以辅助地将轮盘的转矩转递至轮盖上，使得定位凸出部和定位凹陷部组成的预定位结构不仅能够实现定位，而且可以传递转矩，降低了轮盘和轮盖连接强度的要求。
根据下文结合附图对本发明具体实施例的详细描述，本领域技术人员将会更加明了本发明的上述以及其他目的、优点和特征。
附图说明
后文将参照附图以示例性而非限制性的方式详细描述本发明的一些具体实施例。附图中相同的附图标记标示了相同或类似的部件或部分。本领域技术人员应该理解，这些附图未必是按比例绘制的。附图中：
图1是根据本发明一个实施例的离心压缩机的整机结构示意图；
图2是对图1所示离心压缩机沿离心叶轮的轴线方向剖切后得到的示意性剖视图；
图3是图2的A处放大图；
图4是根据本发明一个实施例的离心压缩机中闭式叶轮的示意图；
图5是根据本发明一个实施例的闭式叶轮的分解图；
图6是根据本发明一个实施例的闭式叶轮中轮盘的正视图，其中箭头示出了轮盘的转动方向；
图7是根据本发明一个实施例的闭式叶轮中轮盖的示意图，其中箭头示出了轮盖的转动方向；
图8是根据本发明另外一个实施例的闭式叶轮中轮盘的正视图，其中示出了螺纹孔处于定位凹陷部；
图9是根据本发明一个实施例的闭式叶轮的叶片、轮盖和轮盘的位置关系图，其中H1表示第一叶片的高度，H2表示第二叶片的高度，R1表示第一圆角的半径，R2表示第二圆角的半径。
具体实施方式
请参见图1至图3，图1是根据本发明一个实施例的离心压缩机的整机结构示意图，图2是对图1所示离心压缩机沿离心叶轮的轴线方向剖切后得到的示意性剖视图，图3是图2的A处放大图。本实施例提出一种离心压缩机1。该离心压缩机1一般性地可以包括机壳10、电机40和至少一个压缩单元20,30。
机壳10限定有容纳空间，电机40安装于机壳10内。电机40包括定子41和转子42，定子41固定于机壳10，转子42可相对定子41转动。压缩单元20,30的数量可为一个或多个。例如，可使离心压缩机1为单级压缩式， 仅设置一个压缩单元。也可使离心压缩机1为多级压缩式，其设置多个压缩单元20,30。每个压缩单元20,30包括安装于机壳10的蜗壳100和设置在蜗壳100内的闭式叶轮200。闭式叶轮200配置成在电机40驱动下转动，以对进入蜗壳100的气流进行压缩并将其经蜗壳100的出口排出。
在一些具体的实施例中，例如图1和图2所示，离心压缩机1可为双级压缩式，压缩单元的数量为两个。可知，两个压缩单元20,30中必然有一个为低压级，另一个为高压级，如图1和图2中，位于图面左侧的压缩单元20为低压级，右侧的压缩单元30为高压级。低压级的压缩单元20的蜗壳100的出口通过连接管50与高压级的压缩单元30的蜗壳100的进口连通。具体地，连接管50的进口端设置法兰51以与低压级的压缩单元20的蜗壳100出口的法兰60相接，连接管50出口端设置法兰52以与高压级压缩单元30的蜗壳100连接。优选使低压级的压缩单元20与高压级的压缩单元20分别位于电机40的轴向两侧，以便两个压缩单元20,30的闭式叶轮200分别直接连接于电机40，且利于使两个闭式叶轮200的轴向力进行部分抵消。
蜗壳100内限定有沿气流方向依次相连的进气流道101、蜗形流道102和出气流道103，即蜗壳100流道分为三个区段。进气流道101的进口即构成本文所述的蜗壳100的进口，出气流道103的出口构成蜗壳100的出口。进气流道101沿闭式叶轮200的轴线方向(x轴方向)延伸。
请参见图4至图7，图4是根据本发明一个实施例的离心压缩机中闭式叶轮的示意图，图5是根据本发明一个实施例的闭式叶轮的分解图，图6是根据本发明一个实施例的闭式叶轮中轮盘的正视图，图7是根据本发明一个实施例的闭式叶轮中轮盖的示意图，其中箭头示出了轮盖的转动方向。闭式叶轮200具有朝向进气流道101的进口201和朝向蜗形流道102的出口202，从进气流道101进入的气流首先从闭式叶轮200的进口201进入闭式叶轮200，经闭式叶轮200压缩后将其排向出口202，进入蜗形流道102，最终从出气流道103排出离心压缩机1。
该闭式叶轮200还可以包括轮盘210和轮盖220，其中轮盘210的一侧表面上形成有沿其周向排列的多个第一叶片212，轮盖220与轮盘210可拆卸连接，并且轮盖220朝向轮盘210的一侧表面形成有多个第二叶片222，多个第一叶片212与多个第二叶片222一一对接，以构成闭式叶轮200的叶片(如图4所示)。
在本实施例中，闭式叶轮200的叶片分为两部分，即形成于轮盘210上的第一叶片212和形成于轮盖220上的第二叶片222，并且轮盘210和轮盖220可以采用分体加工的方式(例如铸造等)，以将第一叶片212和第二叶片222分别直接形成在轮盘210和轮盖220。当将轮盘210和轮盖220连接在一起时，第一叶片212与第二叶片222对接，使得轮盘210和轮盖220形成该闭式叶轮200的叶片，进而使得相邻的两个叶片之间形成闭式叶轮200的气流流道2102。
请参见图5至图7，第一叶片212和第二叶片222可以分别沿轮盘210和轮盖220周向均匀地排列，并分别位于轮盘210和轮盖220外侧，轮盘210的中部可以形成安装孔218可以利用紧固件(例如铆钉、螺钉300等)伸入该安装孔218以将轮盘210安装在电机40的转子42上，从而实现转子42驱动轮盘210旋转。轮盖220可以设置成圆环状，并且轮盖220的内圈向背离第二叶片222的方向延伸以形成连接区段228，连接区段228的内部还可以限定出闭式叶轮200的进口201。背离第二叶片222的方向可以沿轮盖220的中心轴线方向延伸，且朝远离第二叶片222的方向延伸。
如背景技术部分所述，目前小冷量高速离心机的叶轮加工成为行业难题，尤其对于微小型的闭式叶轮。虽然铸造可以一体成型，但小型叶轮表面粗糙度等要求较高，铸造工艺难以直接满足精度要求，并且小型叶轮由于尺寸过小，也难以使用其他措施对其内部进行精度处理。
为了克服上述现有技术中的缺陷，本实施例中的闭式叶轮200将叶片分别设置在轮盘210和轮盖220上，并且轮盘210和轮盖220采用分体式，这样可以实现当轮盘210和轮盖220各自成型后，缩短闭式叶轮200的叶片整体高度，便于安装人员进一步对第一叶片212和第二叶片222进行精度优化处理，使得叶片表面粗糙度满足要求；并且这种方式还能够使得刀具等伸入相邻的第一叶片212或者相邻的第二叶片222之间，便于在第一叶片212和第二叶片222加工出圆角240，进一步使得闭式叶轮200的气流流道2102更加光滑，实现圆滑过渡，避免气体在气流流道2102内流通时产生角涡。
请参见图6和图7，为了进一步提高加工效率，本实施例的闭式叶轮200在分体式的基础上还可以增加预定位结构，预定位结构可以在组装轮盘210和轮盖220的过程中进行预定位。
具体地，至少部分第一叶片212上具有第一定位部214，至少部分第二 叶片222上具有第二定位部224，第一定位部214和第二定位部224配置成在轮盖220连接于轮盘210时，第一定位部214与第二定位部224相互约束，以对轮盘210和轮盖220的位置定位。
在本实施例中，第一叶片212的数量可以为多个，并且在这多个第一叶片212中的一部分或者全部第一叶片212上均可以设置有第一定位部214。例如，当第一定位部214为一个时，其可以设置在任意一个第一叶片212上；当第一定位部214为多个时，每个第一定位部214可以对应设置在一个第一叶片212上，或者多个第一定位部214中几个第一定位部214共同设置在一个第一叶片212；又例如，当第一定位部214为3个时，3个第一定位部214可以分别设置在3个不同的第一叶片212上，也可以设置在2个第一叶片212上(其中一个第一叶片212设置1个，另一个第一叶片212设置2个)，或者3个第二定位部224全部集中设置于其中一个第一叶片212上。
上述方案均能够实现对轮盘210和轮盖220的位置定位，但是需要说明的是，上述举例说明仅是为了更加清楚地描述本实施例的技术方案，不应理解为对本申请的限制。本领域技术人员可以根据上述描述进行简单的变形进而形成更多替换方案，在此不一一阐述。
请参见图6和图7，在一些实施例中，第一定位部214为开设于第一叶片212上的定位凹陷部，第二定位部224为凸出于第二叶片222表面的定位凸出部。
第一叶片212向内凹进形成定位凹陷部，对应地，第二叶片222的顶端向外凸出形成与定位凹陷部进行配合的定位凸出部。在组装轮盖220和轮盘210时，定位凸出部可以伸入至与其对应的定位凹陷部，以对轮盖220和轮盘210进行定位。
在一些实施例中，当定位凸出部和定位凹陷部为一组(一个定位凸出部和一个定位凹陷部为一组)时，定位凸出部和定位凹陷部还可以分别设置成非圆形，例如三角形、四边形或其他异形，以使得定位凸出部和定位凹陷部的形状配合，进而在定位凸出部和定位凹陷部仅为一组时就能够实现对轮盖220和轮盘210定位。
当定位凸出部和定位凹陷部为多组时，定位凸出部和定位凹陷部可以为任意形状，例如多边形、圆柱状等，当每个定位凸出部对应地伸入定位凹陷部后就可以实现对轮盖220和轮盘210定位。
请参见图6，在一些实施例中，定位凹陷部的内周壁具有朝向闭式叶轮200转动方向的抵接区段214a，以便在闭式叶轮200转动时对定位凸出部施加推力。
由于轮盘210与电机40的转子42相连，当电机40驱动闭式叶轮200转动时，轮盘210实际上作为主动轮，轮盖220作为从动轮。当轮盘210驱动轮盖220转动时，定位凸出部的至少一部分可以抵靠于该抵接区段214a上，这样抵接区段214a可以辅助地将轮盘210的转矩转递至轮盖220上，使得定位凸出部和定位凹陷部组成的预定位结构不仅能够实现定位，而且可以传递转矩，降低了轮盘210和轮盖220连接强度的要求。
请参见图5至图7，在一些实施例中，轮盘210和轮盖220可以采用螺钉连接的方式实现紧固。具体地，每个第一叶片212上具有一螺纹孔216，每个第二叶片222上具有一与轮盖220相贯通的螺钉孔226，螺纹孔216与螺钉孔226一一对应设置，以便利用螺钉230将轮盖220固定于轮盘210上。
在组装时，安装人员可以首先利用第一定位部214和第二定位部224对轮盘210和轮盖220进行预定位，然后将螺钉230从螺钉孔226穿入，并且伸入第一叶片212上的螺纹孔216，最终使螺钉230与螺纹孔216连接，实现轮盘210和轮盖220的紧固连接。
在一些具体的实施例中，为了使闭式叶轮的整体更加平衡，多个螺纹孔216可以设置在与轮盘210同心的圆周上，这样可以避免闭式叶轮200出现偏心，进而避免在闭式叶轮200高度转动中出现振动、噪音等异常现象。
请参见图8，图8是根据本发明另外一个实施例的闭式叶轮中轮盘的正视图，其中示出了螺纹孔处于定位凹陷部。在一些实施例中，每个第一叶片212上具有一个第一定位部214，各第一叶片212上的螺纹孔216开设于第一定位部214上。由于每个第一叶片212上具有一个螺纹孔216，每个第一叶片212上具有一个第一定位部214，螺纹孔216可以设置于第一定位部214上，也即设置于定位凹陷部内，使得紧固效果更佳。
在一些实施例中，轮盘210可以设置成圆形，并且其直径可以设置成不大于80mm，例如80mm、70mm、60mm等。当闭式叶轮200小型化时，现有铸造工艺无法满足内部叶片精度要求，尤其是当轮盘210的直径不大于80mm时，由于整体尺寸过小，加工人员无法对内的叶片进行精度处理工序。而利用本实施例的分体式组装方式，即，将轮盘210和轮盖220分别铸造， 将第一叶片212或者第二叶片222暴露在外部，然后再对其进行精度处理工序，这种方式能够在实现闭式叶轮200小型化的基础上加工出合格的叶片。
请参见图9，图9是根据本实用新型一个实施例的闭式叶轮中轮盘、轮盖与叶片的位置关系示意图。在一些实施例中，轮盘210与第一叶片212的连接处形成有第一圆角242，且/或轮盖220与第二叶片222的连接处形成有第二圆角244。也即是，轮盘210与第一叶片212的连接处或者轮盖220与第二叶片222的连接处两者其一可以设置有第一圆角242或第二圆角244，也可以是轮盘210与第一叶片212的连接处和轮盖220与第二叶片222的连接处分别设置有第一圆角242和第二圆角244。
第一圆角242和第二圆角244不仅可以提高第一叶片212和第二叶片222根部的强度，缓解该局部应力集中，而且可以使得每个气流流道2102更加光滑、消除了气流的角涡现象，保证了流场的均匀性。
请参见图9，图9中H1表示第一叶片212的高度，H2表示第二叶片222的高度，R1表示第一圆角242的半径，R2表示第二圆角244的半径；进一步地，第一圆角242的半径R1还可以配置成为第一叶片高度H1的1/8至1之间，第二圆角244的半径R2还可以配置成第二叶片高度H2的1/8至1之间，例如，1/8、1/5或者1等等。发明人通过多次试验发现，通过上述限定可以保证在不影响气流流道2102面积的前提下获得更佳的气流场，以进一步提高压缩效果。
特别地，当第一圆角242的半径R1与第一叶片高度H1比值为1，且当第二圆角244的半径R2与第二叶片高度H2比值为1时，也即第一圆角242的半径R1与第一叶片的高度H1相等，第二圆角244的半径R2与第二叶片222高度H2相等，气流流道2102的内壁整体由第一圆角242和第二圆角244组成，使得气流流道2102的内壁整体呈圆弧状。
至此，本领域技术人员应认识到，虽然本文已详尽示出和描述了本发明的多个示例性实施例，但是，在不脱离本发明精神和范围的情况下，仍可根据本发明公开的内容直接确定或推导出符合本发明原理的许多其他变型或修改。因此，本发明的范围应被理解和认定为覆盖了所有这些其他变型或修改。

Claims (10)

  1. 一种用于离心压缩机的闭式叶轮，其特征在于包括：
    轮盘，其一侧表面上形成有沿所述轮盘的周向排列的多个第一叶片；
    轮盖，与所述轮盘可拆卸连接，并且所述轮盖朝向所述轮盘的一侧表面形成有多个第二叶片，多个所述第一叶片与多个所述第二叶片一一对接，以构成所述闭式叶轮的叶片。
  2. 根据权利要求1所述的闭式叶轮，其特征在于，
    至少部分所述第一叶片上具有第一定位部；且
    至少部分所述第二叶片上具有第二定位部；
    所述第一定位部与所述第二定位部配置成在所述轮盖连接于所述轮盘时，所述第一定位部与所述第二定位部相互约束，以对所述轮盖和所述轮盘的位置定位。
  3. 根据权利要求2所述的闭式叶轮，其特征在于，
    所述第一定位部为开设于所述第一叶片上的定位凹陷部；且
    所述第二定位部为凸出于所述第二叶片表面的定位凸出部。
  4. 根据权利要求3所述的闭式叶轮，其特征在于，
    所述定位凹陷部的内周壁具有朝向所述闭式叶轮转动方向的抵接区段，以便在所述闭式叶轮转动时对所述定位凸出部施加推力。
  5. 根据权利要求3所述的闭式叶轮，其特征在于，
    每个所述第一叶片上具有一螺纹孔，每个所述第二叶片上具有一与所述轮盖相贯通的螺钉孔，所述螺纹孔与所述螺钉孔一一对应设置，以便利用螺钉将所述轮盖固定于所述轮盘上。
  6. 根据权利要求5所述的闭式叶轮，其特征在于，
    每个所述第一叶片上具有一所述第一定位部；且
    各所述第一叶片上的所述螺纹孔开设于所述第一定位部上。
  7. 根据权利要求1所述的闭式叶轮，其特征在于，
    所述轮盘为圆形；且
    所述轮盘的直径不大于80mm。
  8. 根据权利要求1所述的闭式叶轮，其特征在于，
    所述轮盘与所述第一叶片的连接处形成有第一圆角；且/或
    所述轮盖与所述第二叶片的连接处形成有第二圆角。
  9. 根据权利要求8所述的闭式叶轮，其特征在于，
    每个所述第一圆角的半径为所述第一叶片高度的1/8至1之间；
    每个所述第二圆角的半径为所述第二叶片高度的1/8至1之间。
  10. 一种离心压缩机，其特征在于，包括根据权利要求1至9中任一项所述的闭式叶轮。
PCT/CN2021/131830 2020-11-24 2021-11-19 闭式叶轮和具有其的离心压缩机 WO2022111396A1 (zh)

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* Cited by examiner, † Cited by third party
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CN111486110A (zh) * 2019-01-29 2020-08-04 青岛海尔智能技术研发有限公司 离心压缩机、热泵系统
CN214887905U (zh) * 2020-11-24 2021-11-26 青岛海尔智能技术研发有限公司 闭式叶轮和具有其的离心压缩机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20040179947A1 (en) * 2002-12-19 2004-09-16 R & D Dynamics Corporation Motor driven two-stage centrifugal air-conditioning compressor
CN102817869A (zh) * 2012-08-13 2012-12-12 势加透博（北京）科技有限公司 大型离心压缩机叶轮及其加工成形方法
WO2015062802A1 (de) * 2013-10-29 2015-05-07 Continental Automotive Gmbh Aus mehreren bauteilen zusammengesetztes verdichterrad
CN111486110A (zh) * 2019-01-29 2020-08-04 青岛海尔智能技术研发有限公司 离心压缩机、热泵系统
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