WO2023098102A1 - Rotor de compresseur, corps de pompe de compresseur, compresseur et système de régulation de température - Google Patents

Rotor de compresseur, corps de pompe de compresseur, compresseur et système de régulation de température Download PDF

Info

Publication number
WO2023098102A1
WO2023098102A1 PCT/CN2022/107018 CN2022107018W WO2023098102A1 WO 2023098102 A1 WO2023098102 A1 WO 2023098102A1 CN 2022107018 W CN2022107018 W CN 2022107018W WO 2023098102 A1 WO2023098102 A1 WO 2023098102A1
Authority
WO
WIPO (PCT)
Prior art keywords
channel
compressor
cylinder
air guide
rotating shaft
Prior art date
Application number
PCT/CN2022/107018
Other languages
English (en)
Chinese (zh)
Inventor
雒应学
Original Assignee
广州市德善数控科技有限公司
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.)
Filing date
Publication date
Priority claimed from CN202122983169.1U external-priority patent/CN216381861U/zh
Priority claimed from CN202210622014.1A external-priority patent/CN115126697B/zh
Priority claimed from CN202210620465.1A external-priority patent/CN115126696B/zh
Application filed by 广州市德善数控科技有限公司 filed Critical 广州市德善数控科技有限公司
Publication of WO2023098102A1 publication Critical patent/WO2023098102A1/fr

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet

Definitions

  • the invention relates to the field of compressors, in particular to a compressor rotor, a compressor pump body, a compressor and a temperature regulating system.
  • a rotary compressor includes a compressor housing 1', a motor 2' and a compressor pump body, and the motor 2' and the compressor pump body are all arranged in the compressor housing 1'.
  • Compressor pump body comprises cylinder 4 ', main bearing 5 ', auxiliary bearing 6 ' and compressor rotor 3.
  • the compressor rotor 3' includes a rotating shaft 31' and an eccentric rotor 32' connected to the rotating shaft 31', and a cylinder cavity is formed in the cylinder 4'.
  • the main bearing 5' and the auxiliary bearing 6' are respectively fixed on the upper and lower sides of the cylinder 4' to seal the cylinder cavity.
  • the rotating shaft 31' drives the eccentric rotor 32' to rotate in the inner chamber of the cylinder to compress the gas.
  • the gas in the cylinder cavity reaches the preset pressure, it will be discharged out of the compressor pump body from the exhaust valve 61' in the auxiliary bearing 6'.
  • the function of the eccentric rotor 32' of the compressor is very single, it is only used for compressing gas, and has no functions such as exhaust and intake, which makes the structure of the compressor more complicated, for example, it is necessary to install an exhaust valve 61 ' and the valve seat of the exhaust valve, etc., the cost of the compressor is relatively high, and the exhaust valve 61' is easily damaged and causes the compressor to fail.
  • the invention provides a multifunctional compressor rotor, a compressor pump body, a compressor and a temperature regulating system.
  • an embodiment of the present invention provides a compressor rotor, which includes a rotating shaft and an eccentric rotor connected to the rotating shaft, the rotating shaft is used to drive the eccentric rotor to rotate, and the eccentric rotor has The extended side surface and the end surface connecting the upper end and the lower end of the side surface, the eccentric rotor is provided with an air guide channel, and the air guide channel includes an air guide groove provided on the end surface and an air guide channel provided on the side surface An air guide port, the air guide port communicates with the air guide groove.
  • the eccentric rotor has an eccentric portion away from the rotating shaft, the end surface includes an upper end surface and a lower end surface, the rotating shaft protrudes relative to the upper end surface and the lower end surface, and the The protruding length of the rotating shaft relative to the upper end surface is greater than the protruding length relative to the lower end surface, the air guide groove is opened on the lower end surface of the eccentric rotor and has an opening at the top, and the air guide port is opened on the On the eccentric part of the eccentric rotor.
  • an oil guiding channel is opened in the rotating shaft, an oil outlet hole communicating with the oil guiding channel is opened on the side of the rotating shaft, and a top opening is opened on the upper end surface of the eccentric rotor
  • the oil guide groove includes an oil guide start section and an oil guide diffuser section, the first end of the oil guide start section faces the rotating shaft and communicates with the oil outlet hole, and the oil guide starts
  • the second end of the initial section is connected to the first end of the oil-guiding diffusion section, and the oil-guiding diffusion section is bent relative to the oil-guiding initial section and extends along the circumferential direction of the eccentric rotor.
  • the line connecting the center of the rotating shaft to the highest point of the eccentric part of the eccentric rotor is used as a bus bar, and two sides of the bus bar are respectively formed In the first cavity, a first reinforcing rib is formed between adjacent first cavities, and the oil guiding groove is opened on the first reinforcing rib.
  • the line connecting the center of the rotating shaft to the highest point of the eccentric part of the eccentric rotor is used as a bus line, and the center of the rotating shaft to the guide An included angle of 1-20 degrees is formed between the line connecting the center of the gas port and the bus bar.
  • the line connecting the center of the rotating shaft to the highest point of the eccentric part of the eccentric rotor is used as a bus bar
  • the air guide groove includes an air guide An initial section and an air guide connection section, the first end of the air guide initial section faces the rotating shaft, the second end of the air guide initial section is connected to the first end of the air guide connection section, the The second end of the air guide connection section communicates with the air guide port, the air guide start section extends along the bus bar, and the air guide connection section is bent relative to the air guide start section.
  • the line connecting the center of the rotating shaft to the highest point of the eccentric part of the eccentric rotor is used as a bus bar, and two sides of the bus bar are respectively formed In the second cavity, a second reinforcing rib extending along the generatrix is formed between the two second cavities, and the air guiding groove is opened on the second reinforcing rib.
  • the second cavities on both sides of the bus bar are connected through the auxiliary channel opened on the second reinforcing rib.
  • the auxiliary channel is a conduction groove opened on the end surface of the eccentric rotor, and the auxiliary channel is located on the same end surface as the air guide groove or located at the same end surface as the air guide groove. the other end surface of the back; or the auxiliary channel is a through hole penetrating through the second reinforcing rib.
  • the cross-section of the eccentric rotor is egg-shaped, which has an egg head end and an egg tail end, the radius of curvature of the egg tail end is smaller than that of the egg head end, and the egg tail end reaches the center of the rotating shaft The distance is greater than the distance from the head end of the egg to the center of the rotating shaft, and the air guide groove extends from the side of the rotating shaft to the tail end of the egg.
  • the egg tail end is in contact with the air cylinder
  • the air guide port is opened at the egg tail end
  • the egg head end and the egg tail end are both arc-shaped
  • the egg head end and the egg tail end They are connected by tangent lines or arcs
  • the ratio of the radius of curvature of the egg head end to the egg tail end is between 1.3-2.5
  • the ratio of the center-of-circle distance between the egg head end and the egg tail end to the radius of curvature of the egg tail end is 1.5- between 3.
  • the rotating shaft and the eccentric rotor are of an integrated structure
  • the air guide channel is an air supply channel
  • the air guide groove is a straight groove
  • the air guide groove is along the radial direction of the eccentric rotor. distribution, and one end extends to the side of the eccentric rotor to form the air guide port, the air guide groove and the air guide port form the air supplement channel
  • the protruding side of the eccentric rotor is provided with a plurality of The through hole in the axial direction of the rotating shaft.
  • a compressor pump body which includes a cylinder, a main bearing, an auxiliary bearing, a compressor rotor and a sliding vane, and a cylinder cavity and a cylinder communicating with the cylinder cavity are formed in the cylinder.
  • the suction port, the main bearing and the auxiliary bearing are respectively fixed on both sides of the cylinder to seal the inner cavity of the cylinder
  • the compressor rotor is the compressor rotor described in any of the above-mentioned embodiments
  • the eccentric The core rotor is accommodated in the inner cavity of the cylinder, the air guide port communicates with the inner cavity of the cylinder, the two ends of the rotating shaft protrude respectively relative to the end faces of the eccentric rotor, and are connected to the main bearing and the eccentric rotor respectively.
  • the auxiliary bearing rotates and cooperates.
  • the sliding plate is movably installed in the cylinder and is movably matched with the eccentric rotor to separate the inner cavity of the cylinder.
  • the eccentric rotor is driven by the rotating shaft to face each other Rotate on the cylinder, main bearing and auxiliary bearing.
  • the main bearing or the auxiliary bearing is provided with an exhaust channel.
  • the exhaust channel communicates with the air guide channel.
  • the compressed gas in the cavity is discharged out of the pump body of the compressor through the air guide channel and the exhaust channel.
  • the exhaust channel is not connected to the air guide channel.
  • the main bearing or the auxiliary bearing is also provided with an air supply channel.
  • the air supply channel communicates with the air guide channel.
  • the pump body of the compressor supplies air to the inner cavity of the cylinder through the air supply channel and the air guide channel.
  • the auxiliary bearing is provided with a first shaft hole, the rotating shaft is inserted into the first shaft hole, and rotates with the auxiliary bearing, and the exhaust channel and the air supply channel are both Set on the auxiliary bearing, the exhaust passage includes an exhaust groove and an exhaust pipeline connected with the exhaust groove, and the air supply passage includes an air supply groove and an air supply pipeline connected with the air supply groove.
  • the exhaust groove and the air supply groove are arc-shaped extending along the circumferential direction of the first shaft hole, and the exhaust groove and the air supply groove surround the first shaft hole and are arranged at opposite intervals,
  • the air guide channel is connected to the exhaust groove, but not connected to the air supply groove, and the compressed gas in the inner cavity of the cylinder passes through the air guide port, the air guide groove, and the exhaust groove in sequence.
  • the exhaust pipeline is discharged outwards.
  • the air guide channel communicates with the air supply groove and does not communicate with the exhaust groove.
  • the compressor pump body passes through the air supply pipe in turn. Road, air supply groove, air guide groove, and air guide port supply air to the inner cavity of the cylinder.
  • the cylinder includes an outer wall of the cylinder and an inner wall of the cylinder, the inner cavity of the cylinder is formed in the inner wall of the cylinder, and a gas-liquid separation chamber is formed between the outer wall of the cylinder and the inner wall of the cylinder , the exhaust passage communicates with the gas-liquid separation chamber, and the cylinder is also provided with a general exhaust port.
  • the compressor pump body When the compressor pump body is in a compressed state, the compressed gas in the inner cavity of the cylinder passes through the The air guide channel, the exhaust channel, the gas-liquid separation chamber and the total exhaust port are discharged out of the cylinder.
  • the gas-liquid separation chamber includes one or more sub-separation chambers, and adjacent sub-separation chambers are separated by separation ribs arranged between the outer wall of the cylinder and the inner wall of the cylinder, so The separation reinforcing rib forms the sub-separation cavity with the inner side of the outer wall of the cylinder and the outer side of the inner wall of the cylinder, and the separation reinforcing rib is provided with a separation channel that communicates with the adjacent sub-separation cavities.
  • the flow channel cross-sectional area of the channel is smaller than the flow channel cross-sectional area of the sub-separation chamber.
  • the separation channel includes an upper channel and a lower channel, the upper channel is set relatively close to or at the top of the separation rib, and the lower channel is set at There is a distance between the upper channel and the lower channel at the bottom end of the separating reinforcing rib.
  • the ratio of the flow channel cross-sectional area of the sub-separation chamber: the flow channel cross-sectional area of the separation channel: the flow channel cross-sectional area of the total exhaust port is: 3-30:1-1.8: 1.
  • a plurality of buffer cavities are formed between the outer wall of the cylinder and the inner wall of the cylinder, and adjacent buffer cavities are strengthened by the buffer provided between the outer wall of the cylinder and the inner wall of the cylinder.
  • the ribs are separated, and the buffer reinforcing rib is provided with a buffer channel that communicates with adjacent buffer chambers.
  • the flow channel cross-sectional area of the buffer channel is smaller than the flow channel cross-sectional area of the buffer chamber, and the cylinder is provided with a total air intake hole.
  • the inner wall of the cylinder is provided with the suction port, and the gas enters the inner cavity of the cylinder through the general air intake hole, the buffer cavity and the suction port in sequence.
  • the cylinder is also provided with a slide slot communicating with the inner cavity of the cylinder, the slide is movably installed in the slide slot, and can be extended or retracted.
  • the tail end of the slide is rolled or slidably fitted with the side of the eccentric rotor to separate the inner cavity of the cylinder.
  • the rotation angle corresponding to the initial conduction position of the air guide channel and the exhaust channel is between 220° and 250° or between 260° and 310°.
  • the eccentric rotor is provided with a second cavity
  • the main bearing and/or the auxiliary bearing is provided with a transition passage
  • the position of the transition passage is related to the position of the air guide passage and the second cavity.
  • the positions of the two cavities correspond to each other.
  • the transition channel includes a first transition channel and a second transition channel arranged at intervals, and when the eccentric rotor rotates to a preset position between the exhaust end position and the zero line, the The first transition channel communicates with the second cavity and the air guide channel at the same time, and when the eccentric rotor rotates between the zero line and the intake end position, neither the first transition channel nor the second transition channel Simultaneously communicate with the second cavity and the air guide channel, when the eccentric rotor rotates to a preset position between the intake end position and the exhaust start position, the second transition channel communicates with the air guide channel and the first air guide channel at the same time Two cavities.
  • An embodiment of the present invention also provides a compressor pump body assembly, which includes a cylinder, a first bearing, a second bearing, a rotating shaft, and an eccentric rotor connected to the rotating shaft.
  • the rotating shaft and the eccentric rotor are of an integrated structure.
  • An integrated rotating shaft is formed, and a compression chamber is formed between the outer peripheral wall of the eccentric rotor, the inner peripheral wall of the cylinder, the first bearing sealing end surface, and the second bearing sealing end surface;
  • the compressor pump body assembly also includes a combined air supply channel
  • the combined gas supply channel includes a gas introduction hole, a first gas supply channel and a second gas supply channel;
  • the gas introduction hole is opened on the first bearing or the second bearing;
  • the first air supply channel is opened on the sealing end surface of the first bearing or the sealing end surface of the second bearing;
  • the second air supply channel is opened on the end face of the eccentric rotor
  • an air guiding groove is opened on the end face of the eccentric rotor, the air guiding groove is a straight groove, the air guiding groove is distributed along the radial direction of the eccentric rotor, and one end extends to the
  • the side surface of the core rotor forms an air guide port, and the air guide groove communicates with the air guide port and constitutes the second air supply channel.
  • the first gas supply channel is an arc-shaped air guide groove
  • the gas introduction hole communicates with the arc-shaped air guide groove inside the first bearing or the second bearing
  • the second air supply channel is an air guide straight groove; only when the integrated rotating shaft rotates within the first preset range, the air guide straight groove communicates with the arc-shaped air guide groove.
  • An embodiment of the present invention further provides a compressor, including a compressor casing, a drive assembly, and the compressor pump body described in any of the above-mentioned embodiments, and the drive assembly and the compressor pump body are both arranged on the compressor casing
  • the driving assembly is located on the side of the main bearing away from the cylinder, and is connected with the rotating shaft for driving the rotating shaft to rotate.
  • An embodiment of the present invention further provides a compressor, which is characterized in that it includes a compressor casing, a drive assembly, and the compressor pump body described in any of the above-mentioned embodiments, and the drive assembly and the compressor pump body are both arranged on the In the compressor housing, the driving assembly is located on the side of the main bearing away from the cylinder and is connected to the rotating shaft for driving the rotating shaft to rotate; the compressor also includes an oil discharge assembly, the The oil discharge assembly is connected with the gas-liquid separation chamber, and is used for draining the liquid in the gas-liquid separation chamber out of the compressor pump body.
  • an oil pool is also provided in the compressor casing, the oil pool is located under the auxiliary bearing, the oil discharge assembly includes a gap oil discharge structure, and the gap oil discharge structure includes a core shaft and the mandrel mounting seat matched with the mandrel, a gap channel is formed between the mandrel and the mandrel mounting seat, and the liquid in the gas-liquid separation chamber passes through the gap channel and is discharged to the in the oil pool.
  • the oil discharge assembly further includes oil passage one and oil passage two, the oil passage one is opened on the auxiliary bearing, the inlet of the oil passage one is connected to the The gas-liquid separation chamber is connected, and the oil is guided from the gas-liquid separation chamber to the entrance of the gap channel; the second oil passage connects the outlet of the gap channel with the oil pool, and the oil is introduced from the outlet of the gap channel to the The oil pool; the oil in the gas-liquid separation chamber sequentially passes through the first oil passage, the gap passage, and the second oil passage, and is discharged to the oil pool.
  • the width of the gap channel is 0.001mm-0.020mm
  • the mandrel mounting seat is provided with an inner hole
  • the mandrel is assembled in the inner hole of the mandrel mounting seat, so The oil passage 1 and/or the oil passage 2 are misaligned with the mandrel so as to limit the mandrel in the inner hole.
  • the oil discharge assembly also includes a filter structure, an oil discharge hole is provided in the gas-liquid separation chamber, the oil passage is provided on the auxiliary bearing, and the filter structure is provided In the oil discharge hole or arranged between the oil discharge hole and the oil passage one, the inlet of the oil passage one communicates with the outlet of the filter structure, and the filter structure is provided with a magnetic block, the filtering pores of the filtering structure are less than 0.005mm.
  • An embodiment of the present invention also provides a temperature adjustment system, which includes the compressor described in any of the above embodiments, and also includes an evaporator and a condenser, and a refrigerant circulates between the compressor, the evaporator, and the condenser .
  • the compressed gas in the inner chamber of the cylinder can be discharged out of the cylinder through the compressor rotor by providing an air guide channel on the compressor rotor. Make the structure of the compressor simpler and more reliable.
  • Fig. 1 is a structural schematic diagram of a compressor in the prior art.
  • Fig. 2 is a schematic structural diagram of a compressor according to an embodiment of the present invention.
  • Fig. 3 and Fig. 4 are partial exploded view and assembly view of the pump body of the compressor according to the embodiment of the present invention.
  • 5 to 10 are structural schematic diagrams of a compressor rotor according to an embodiment of the present invention.
  • Fig. 11 is a schematic structural diagram of the auxiliary bearing in Fig. 3 .
  • Fig. 12 and Fig. 13 are partial exploded view and assembly view of the pump body of the compressor according to another embodiment of the present invention.
  • 14 to 16 are structural schematic diagrams of a compressor rotor according to another embodiment of the present invention.
  • 17 to 19 are schematic structural views of the cylinder in FIG. 3 .
  • Fig. 20 is a schematic structural diagram of a compressor according to another embodiment of the present invention.
  • FIG. 21 is a partially enlarged view of FIG. 20 .
  • Fig. 22 is a schematic structural view of a compressor rotor in another embodiment.
  • FIG. 23 is a partially enlarged view of FIG. 22 .
  • FIG. 24 is a partial schematic view of a compressor pump body with the compressor rotor of FIG. 22 .
  • Fig. 25 is a structural schematic diagram of an auxiliary bearing corresponding to the compressor rotor in Fig. 22 .
  • 26 to 30 are schematic views of various states of the pump body of the compressor shown in FIG. 24 .
  • FIG. 31 is a schematic diagram showing the relationship between the compression ratio and the bus angle of the pump body of the compressor in FIG. 24 .
  • Fig. 32 is a schematic diagram of the dimensions of a compressor rotor according to an embodiment.
  • Fig. 33 to Fig. 38 are structural schematic diagrams of another embodiment of a pump body assembly of a compressor.
  • an embodiment of the present invention provides a compressor, which may be a rotary compressor, also known as a rotary compressor.
  • the compressor includes a compressor casing 1 , a drive assembly 2 and a compressor pump body, and the drive assembly 2 and the compressor pump body are both arranged in the compressor casing 1 .
  • the pump body of the compressor includes a cylinder 4, a main bearing 5, an auxiliary bearing 6, a compressor rotor 3 and a sliding vane 7.
  • the cylinder 4 is formed with a cylinder cavity 41 and an intake port 48 communicating with the cylinder cavity 41 .
  • the main bearing 5 and the auxiliary bearing 6 are respectively fixed on the upper and lower sides of the cylinder 4 to seal the cylinder cavity 41 .
  • the main bearing 5 is integrally formed with a part of the compressor housing 1 .
  • the compressor rotor 3 includes a rotating shaft 31 and an eccentric rotor 32 connected to the rotating shaft 31 , the rotating shaft 31 is used to drive the eccentric rotor 32 to rotate.
  • the eccentric rotor 32 is accommodated in the cylinder cavity 41 , and the two ends of the rotating shaft 31 respectively protrude relative to the end faces of the eccentric rotor 32 , and are rotatably matched with the main bearing 5 and the auxiliary bearing 6 respectively.
  • the eccentric rotor 32 rotates relative to the cylinder 4 , the main bearing 5 and the auxiliary bearing 6 driven by the rotating shaft 31 .
  • the sliding plate 7 is movably installed in the cylinder 4 and is movably matched with the eccentric rotor 32 to separate the inner cavity 41 of the cylinder.
  • the driving assembly 2 is located on the side of the main bearing 5 facing away from the cylinder 4 (that is, the upper side in FIG. 2 ), and is connected with the rotating shaft 31 for driving the rotating shaft 31 to rotate.
  • the driving assembly 2 may be a motor, which includes a stator and a rotor, etc. Since the structure of the motor is a known structure, it will not be repeated here.
  • the eccentric rotor 32 is cylindrical, and may be cylindrical, elliptical, and the like.
  • the eccentric rotor 32 has a side surface 3202 extending circumferentially around the rotating shaft 31 and an end surface connecting the upper end and the lower end of the side surface 3202.
  • the end surface includes an upper end surface 3204 (that is, a reverse thrust surface) and a lower end surface 3203 (that is, a thrust surface). surface), the upper end surface 3204 and the lower end surface 3203 are arranged in parallel.
  • An air guide channel is provided on the eccentric rotor 32 , the air guide channel includes an air guide groove 321 provided on the end surface and an air guide port 322 provided on the side surface 3202 , the air guide port 322 communicates with the air guide groove 321 .
  • the air guiding groove 321 can be arranged on the upper end surface 3204 or on the lower end surface 3203 .
  • the gas guide port 322 communicates with the cylinder cavity 41, so that the cylinder cavity 41 can communicate with the outside through the gas guide channel.
  • the eccentric rotor 32 has an eccentric portion away from the rotating shaft 31 . Since the rotating shaft 31 is arranged eccentrically on the eccentric rotor 32 , the distance between a part of the side 3202 of the eccentric rotor 32 and the center of the rotating shaft 31 is greater than that of other parts of the side 3202 from the center of the rotating shaft 31 , and this part is the eccentric part.
  • the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 (that is, the farthest from the center of the rotating shaft 31 on the cross section of the eccentric rotor 32
  • the connecting line between the corresponding points on the side surface 3202 and the center of the rotating shaft 31 and the generatrix 3201 form an angle within 20 degrees is defined as the eccentric part.
  • the rotating shaft 31 protrudes relative to the upper end surface 3204 and the lower end surface 3203 to form a main shaft 311 and a sub shaft 312 respectively.
  • the main shaft 311 passes through the main bearing 5 and is connected with the drive assembly 2, and the main shaft 311 is rotatably matched with the main bearing.
  • the secondary shaft 312 is rotatably matched with the secondary bearing 6 .
  • the protruding length of the rotating shaft 31 relative to the upper end surface 3204 ie, the length of the main shaft 311
  • the air guide groove 321 is opened on the lower end surface 3203 of the eccentric rotor 32 and has an open top
  • the air guide port 322 is opened on the eccentric portion of the eccentric rotor 32 .
  • an oil guide channel 313 is opened in the rotating shaft 31 , and an oil outlet hole 3111 communicating with the oil guide channel 313 is opened on the side of the rotating shaft 31 .
  • the oil guide channel 313 can be opened from the bottom of the auxiliary shaft 312 to the top of the main shaft 311, and the oil outlet hole 3111 can be opened on the main shaft 311 and the auxiliary shaft 312, which is used to pass lubricating oil through the bottom of the auxiliary shaft 312, the oil guide channel 313 ,
  • the oil outlet hole 3111 is introduced into the pump body of the compressor to lubricate between the rotating shaft 31 and the main bearing 5, the auxiliary bearing 6 and between the eccentric rotor 32 and the cylinder 4.
  • the upper end surface 3204 of the eccentric rotor 32 is provided with an oil guiding groove 325 with an open top for delivering lubricating oil flowing out from the oil outlet hole 3111 to between the upper end surface 3204 of the eccentric rotor and the inner surface of the main bearing 5 .
  • the oil guide groove 325 includes an oil guide initial section 3251 and an oil guide diffuser section 3252 .
  • the first end of the oil guide initial section 3251 faces the rotating shaft 31 (that is, faces the main shaft 311 ) and communicates with the oil outlet hole 3111 .
  • the upper end surface 3204 of the eccentric rotor 32 is provided with an annular oil collection groove 328 surrounding the main shaft 311, and the lubricating oil flowing out from the oil outlet hole 3111 falls into the oil collection groove 328, and the first oil guide section 3251 The end communicates with the oil collection groove 328, so that the lubricating oil flowing out of the oil outlet hole 3111 flows into the oil guide groove 325 through the oil collection groove 328.
  • the second end of the oil-guiding initial section 3251 is connected to the first end of the oil-guiding diffusion section 3252 , and the oil-guiding diffusion section 3252 is bent relative to the oil-guiding initial section 3251 and extends along the circumferential direction of the eccentric rotor 32 .
  • the connecting line from the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 is used as the bus bar 3201, and the two sides of the bus bar 3201 are respectively
  • One or more first cavities 326 are formed, and a first reinforcing rib 327 extending along the bus bar 3201 is formed between the two first cavities 326 closest to the bus bar 3201 , and the oil guiding groove 325 is opened on the first reinforcing rib 327 .
  • the first cavity 326 can also slightly deform the side surface 3202 of the eccentric rotor 32 when a large force is applied to prevent the eccentric rotor 32 from being stuck in the cylinder 4 .
  • the line connecting the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 is used as the bus 3201, and the connecting line of the rotating shaft 31
  • the line connecting the center to the center of the air guiding port 322 and the bus bar 3201 has an included angle of 1-20 degrees, preferably 1-5 degrees.
  • the line connecting the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 is used as the bus 3201 .
  • the air guiding groove 321 includes an air guiding initial section 3211 and an air guiding connecting section 3212.
  • the first end of the air guiding initial section 3211 faces the rotating shaft 31, and the second end of the air guiding initial section 3211 is connected to the second end of the air guiding connecting section 3212.
  • One end is connected, and the second end of the gas guiding connection section 3212 communicates with the gas guiding port 322 .
  • a connection hole 3213 is opened at the bottom of the second end of the air guiding connection section 3212 , and the connecting hole 3213 communicates with the air guiding connecting section 3212 and the air guiding port 322 .
  • the gas guiding starting section 3211 extends along the busbar, and the gas guiding connecting section 3212 is bent relative to the gas guiding starting section 3211 .
  • the bending direction of the air guide connecting section 3212 is away from the suction port 48 .
  • the air guide port 322 By connecting the air guide connecting section 3212, the air guide port 322 can be deviated from the highest point of the eccentric part, so that the strength of the eccentric rotor 32 will not be greatly affected, and the service life of the eccentric rotor 32 can be ensured.
  • the air guiding groove 321 may directly extend to the side surface 3202 of the eccentric rotor 32 , and the air guiding port 322 is formed on the side surface 3202 of the eccentric rotor 32 .
  • the connecting line from the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 is used as the bus bar 3201, and the two sides of the bus bar 3201 Second cavities 323 are respectively formed, and second reinforcing ribs 324 extending along the busbar 3201 are formed between the two second cavities 323 , and the air guiding groove 321 is opened on the second reinforcing ribs 324 .
  • the second cavity 323 can be integrated with the aforementioned first cavity 326 (that is, the same cavity), or can be separated from the first cavity 326, which can also reduce the weight of the eccentric rotor 32, And the side surface 3202 of the eccentric rotor 32 is slightly deformed when a large force is applied to prevent the eccentric rotor 32 from being stuck in the cylinder 4 .
  • the setting of the second reinforcing rib 324 can not only ensure that the eccentric rotor 32 has sufficient strength, but also make it possible to reasonably set the position of the air guide groove 321 .
  • each second cavity 323 formed on both sides of the bus bar 3201 does not mean that each second cavity 323 is strictly located on one side of the bus bar 3201 and will not cross the bus bar 3201, but means Both sides of the bus bar 3201 have second cavities 323 .
  • the cross-sectional areas of the second cavities 323 on both sides of the reinforcing rib 324 are different, wherein a part of the second cavity 323 with a larger cross-sectional area crosses the busbar 3201, That is to say, the main part of the second cavity 323 is located on one side of the busbar 3201, while the other side of the busbar 3201 has a small part of the second cavity 323 and another second cavity with a smaller cross-sectional area. 323.
  • the second cavities 323 on both sides of the bus bar 3201 are connected through the auxiliary channel 3241 opened on the second rib 324, so that the two second cavities 323 Formed as a transition air cavity.
  • the cross-section of the eccentric rotor 32 is egg-shaped.
  • the auxiliary channel 3241 is a conducting groove opened on the end surface of the eccentric rotor 32, and the auxiliary channel 3241 is located on the same end surface as the air guiding groove 321 or on the side opposite to the air guiding groove 321. on the other end.
  • the auxiliary channel 3241 can be opened on the upper end surface 3204 of the eccentric rotor 32 , and can also be opened on the lower end surface 3203 .
  • both the auxiliary channel 3241 and the air guiding groove 321 are located on the lower end surface 3203 of the eccentric rotor 32 .
  • the auxiliary channel 3241 can also be a through hole passing through the second rib 324 .
  • the cross-section of the eccentric rotor 32 is egg-shaped, which has an egg head end (that is, the upper end in Fig. 16 ) and an egg tail end (that is, the upper end in Fig. 16 The lower end of the center), the radius of curvature of the egg tail end is smaller than the curvature radius of the egg head end, the distance from the egg tail end to the center of the rotating shaft 31 is greater than the distance from the egg head end to the center of the rotating shaft 31, and the air guide groove 321 rotates around the rotation axis 31 to the side of the egg tail end extend.
  • the outline of the shaded area A is the side projection of the circular eccentric rotor 32
  • the inner outline of the shaded area A is the side projection of the egg-shaped eccentric rotor 32 of the present embodiment
  • the eccentric rotor 32 has the same
  • the cross-sectional area occupied by the egg-shaped eccentric rotor 32 that is, the overall volume
  • the cross-sectional area occupied by the circular eccentric rotor 32 is smaller than the cross-sectional area occupied by the circular eccentric rotor 32, so the effective volume of the cylinder cavity 41 is larger .
  • both the egg head end and the egg tail end are arc-shaped, and the egg head end and the egg tail end are connected by a tangent line or an arc.
  • a tangent line can be connected to both sides of the egg head end and the egg tail end, and the tangent line is tangent to the arcs of the egg head end and the egg tail end.
  • both sides of the egg head end and the egg tail end are connected by an outer arc, and the radius of curvature of the two outer arcs is much larger than the radius of curvature of the egg head end and the egg tail end, for example, it may be the egg head end. 5-10 times the radius of curvature.
  • the ratio of the radius of curvature of the egg head end to the egg tail end is between 1.3-2.5, and the ratio of the center distance between the egg head end and the egg tail end to the curvature radius of the egg tail end is between 1.5-3.
  • the radius of curvature of the egg head end is 14 mm
  • the curvature radius of the egg tail end is 7.5 mm
  • the distance between the egg head end and the egg tail end is 15.5 mm.
  • an exhaust channel 62 is opened on the auxiliary bearing 6.
  • the exhaust channel 62 communicates with the air guide channel on the eccentric rotor 32, and the inner chamber of the cylinder
  • the compressed gas in 41 is discharged out of the compressor pump body through the air guide channel and the exhaust channel 62.
  • the exhaust channel 62 is not connected with the air guide channel.
  • the exhaust channel 62 is opened on the inner surface of the auxiliary bearing 6 opposite to the lower end surface 3203 of the eccentric rotor 32, and the air guiding groove 321 is opened on the lower end surface 3203 of the eccentric rotor 32.
  • the pump body of the compressor When turning to the compression position, the pump body of the compressor is in a compressed state, and the air guide groove 321 is rotated to the position communicating with the exhaust passage 62.
  • the channel 62 discharges out of the inner cavity 41 of the cylinder.
  • the air guide groove 321 is not connected to the exhaust passage 62, and the pump body of the compressor is in an air suction state.
  • the exhaust channel can be opened on the inner surface of the main bearing 5 opposite to the eccentric rotor 32, and correspondingly, the air guide channel is opened on the upper end surface 3202 of the eccentric rotor 32, and the working principle is the same as that of the above-mentioned embodiment. Example is similar.
  • the main bearing 5 or the auxiliary bearing 6 is also provided with an air supply passage 63.
  • the air supply passage 63 communicates with the air guide passage, and the compressor pump body passes through the air supply passage.
  • the air channel 63 and the air guide channel supply air to the inner cavity 41 of the cylinder.
  • the supplementary air passage 63 communicates with the refrigerant pipeline outside the compressor, and is used to introduce the medium-pressure gaseous refrigerant compressed by the compressor and passed through the condenser or flash evaporator into the compressor through the supplementary air passage 63.
  • the compression is completed in the inner cavity 41 of the cylinder along with the rotation of the eccentric rotor 32, so as to increase the pressure of the compressed refrigerant Enthalpy difference, thereby improving the efficiency of the compressor, especially making the compressor with the structure of supplementing air to increase the enthalpy more suitable for operation in severe cold environments.
  • the air guide channel is opened on the lower end surface 3203 of the eccentric rotor 32, the air supply channel 63 is opened on the auxiliary bearing 6; when the air guide channel is opened on the upper end surface 3202 of the eccentric rotor 32, the air supply channel 63 is opened on the main bearing 5.
  • the auxiliary bearing 6 is provided with a first shaft hole 61 , the first shaft hole 61 is a through hole, and the auxiliary shaft 312 of the rotating shaft 31 is inserted into the first shaft hole 61 to rotatably cooperate with the auxiliary bearing 6 .
  • Both the exhaust passage 62 and the air supply passage 63 are provided on the auxiliary bearing 6 .
  • the exhaust passage 62 includes an exhaust groove 621 and an exhaust pipeline 624 communicating with the exhaust groove 621 .
  • the air supply channel 63 includes an air supply tank 631 and an air supply pipeline 632 communicating with the air supply tank 631 .
  • the exhaust groove 621 and the air supply groove 631 are arc-shaped extending along the circumferential direction of the first shaft hole 61.
  • the exhaust groove 621 and the air supply groove 631 surround the first shaft hole 61 and are arranged at opposite intervals, that is, the exhaust groove
  • the inner arc surfaces of the 621 and the air supply groove 631 are opposite to each other, and the exhaust groove 621 and the air supply groove 631 are separated by a certain distance.
  • the air guide passage communicates with the exhaust groove 621 and does not communicate with the air supply groove 631, and the compressed gas in the cylinder cavity 41 passes through the air guide port 322, the air guide groove 321, and the exhaust groove in sequence. 621.
  • the exhaust pipeline 624 is discharged to the outside. Specifically, a first exhaust hole 622 is opened on the inner surface of the auxiliary bearing 6, and the exhaust hole 622 communicates with the exhaust path in the cylinder 4. The exhaust path is isolated from the cylinder cavity 41, and the compressed gas flows from the exhaust The gas pipeline 624 and the first exhaust hole 622 then flow into the exhaust path in the cylinder 4, and finally discharge out of the pump body of the compressor from the total exhaust port 45 of the cylinder 4.
  • a second exhaust hole 623 is opened on the side surface of the auxiliary bearing 6, and the compressed gas is directly discharged from the pump body of the compressor through the exhaust pipeline 624 and the second exhaust hole 623, for example, through a pipeline It is connected with the total discharge pipe 92 of the compressor.
  • the first exhaust hole 622 and the second exhaust hole 623 may not be open at the same time.
  • the cylinder 4 includes a cylinder outer wall 421 and a cylinder inner wall 422, the cylinder inner wall 200 is arranged in the cylinder outer wall 100, and the cylinder inner wall 422 forms the cylinder inner cavity 41, A gas-liquid separation chamber 43 is formed between the cylinder outer wall 421 and the cylinder inner wall 422 , and the exhaust channel 62 communicates with the gas-liquid separation chamber 43 .
  • the exhaust channel 62 can communicate with the gas-liquid separation chamber 43 through the first exhaust hole 622 opened on the inner surface of the auxiliary bearing 6 .
  • the cylinder 4 is also provided with a total exhaust port 45.
  • the compressed gas in the cylinder cavity 41 passes through the air guide channel, the exhaust channel 62, the gas-liquid separation chamber 43 and the total exhaust port 45. out of the cylinder. Due to the existence of the gas-liquid separation chamber 43, the inner wall 422 of the cylinder realizes a slight force-following deformation under the force of the eccentric rotor 32, which ensures the tightness between the eccentric rotor 32 and the inner wall 422 of the cylinder, and reduces friction during compression. Leakage can also reduce the occurrence of the eccentric rotor 32 stuck by the inner wall 422 of the cylinder.
  • the compressed gas discharged from the cylinder cavity 41 will carry lubricating oil droplets, so the compressed gas is first introduced into the gas-liquid separation chamber 43, and the gaseous refrigerant can be Separated from lubricating oil, so as to facilitate the recovery of lubricating oil and prevent lubricating oil from entering the refrigeration pipeline.
  • the gas-liquid separation chamber 43 can also have effects such as muffler and flow disturbance on the suction and exhaust actions of the compressor pump body, so as to reduce the noise of the compressor pump body during operation.
  • the gas-liquid separation chamber 43 includes a plurality of sub-separation chambers 431 , and adjacent sub-separation chambers 431 are separated by separation reinforcing ribs 432 arranged between the cylinder outer wall 421 and the cylinder inner wall 422 .
  • the separation reinforcing rib 432 forms a sub-separation cavity 431 with the inner side of the cylinder outer wall 421 and the outer side of the cylinder inner wall 422 .
  • the separation reinforcing rib 432 is provided with a separation channel 49 that communicates with adjacent sub-separation chambers 431 , and the cross-sectional area of the flow passage of the separation passage 49 is smaller than that of the sub-separation chambers 431 . Since the flow channel cross-sectional area of the separation channel 49 is smaller than the flow channel cross-sectional area of the sub-separation chamber 431, the flow rate of the compressed gas in the sub-separation chamber 431 will decrease, so that the lubricating oil contained in the compressed gas will settle in the sub-separation chamber 431 , so as to achieve gas-liquid separation.
  • the compressed gas flows through the plurality of sub-separation chambers 431 and the separation passages 49 therebetween, and is finally discharged from the main exhaust port 45, which can not only improve the noise reduction effect, but also improve the gas-liquid separation effect.
  • the separation channel 49 includes an upper channel 491 and a lower channel 492, the upper channel 491 is relatively close to the top of the separation rib 432 or is arranged on the top of the separation rib 432, and the lower channel 492 There is a space between the upper channel 491 and the lower channel 492 disposed at the bottom of the separating reinforcing rib 432 . Due to the distance between the upper channel 491 and the lower channel 492, when the gas-liquid mixture passes through the separation channel 49, the gas mainly flows through the upper channel 491, and the liquid mainly flows through the lower channel 492, so the effect of gas-liquid separation can be improved.
  • the ratio of the flow channel cross-sectional area of the sub-separation cavity 431: the flow channel cross-sectional area of the separation channel 49: the flow channel cross-sectional area of the total exhaust port 45 is: 3-30:1-1.8:1 .
  • the flow channel cross-sectional area of separation channel 49 the ratio of the flow channel cross-sectional area of total exhaust port 45 is 1-1.8:1, can make the gas flow velocity of separation channel 49 approach with the flow velocity of total exhaust port 45 like this, sub-separation cavity If the ratio of the flow channel cross-sectional area of 431 to the flow channel cross-sectional area of the separation channel 49 is too small, the gas-liquid separation effect will not be good, and if it is too large, the strength of the cylinder 4 will be easily affected.
  • a plurality of buffer cavities 441 are also formed between the outer wall 421 of the cylinder and the inner wall 422 of the cylinder, and adjacent buffer cavities 441 are strengthened by the buffer provided between the outer wall 421 of the cylinder and the inner wall 422 of the cylinder.
  • the ribs 442 are separated, and the buffer reinforcement ribs 442 are provided with a buffer channel that communicates with adjacent buffer chambers 441 .
  • the cylinder 4 is provided with a total intake hole 46, and the inner wall 422 of the cylinder is provided with a suction port 48, and the low-pressure gas enters the cylinder cavity 41 through the total gas intake hole 46, a plurality of buffer chambers 441, and the suction port 48 successively.
  • Air intake channel can be set on the secondary bearing 6, and be connected with total intake pipe 91, total air intake hole 46 can be communicated with the intake channel on the secondary bearing 6, the low-pressure gas that enters from total intake pipe 91 passes through on the secondary bearing 6
  • the intake passage and the total intake hole 46 enter the cylinder 4 .
  • the low-pressure gas that enters from the total intake hole 46 often also contains incompletely vaporized liquid refrigerant. In the cylinder of the prior art, its low-pressure gas and liquid refrigerant directly enter the cylinder cavity 41 from the suction port.
  • the liquid refrigerant since the liquid refrigerant cannot be compressed, it will reduce the compression efficiency of the compressor, and if it is discharged from the discharge valve, it may damage the discharge valve due to its high velocity.
  • a plurality of buffer chambers 441 and buffer passages are provided, so that the liquid refrigerant needs to pass through a plurality of buffer chambers 441 between the outer wall 421 and the inner wall 422 of the cylinder, and then enter the inner chamber 41 of the cylinder from the suction port 48 . Because the cylinder 4 will generate a certain temperature during the operation of the compressor, when the liquid refrigerant passes through multiple buffer chambers 441, it will be heated and vaporized, and enter into the cylinder cavity 41 in a gaseous state. There is no such liquid refrigerant Access to cylinder bore 41 creates problems.
  • the cylinder 4 is also provided with a slide slot 47 communicating with the cylinder cavity 41, the slide 7 is movably installed in the slide slot 47, and can be stretched out or When retracted into the slide groove 47 , the tail end of the slide 7 is rolled or slidably fitted with the side surface 3202 of the eccentric rotor 32 to separate the cylinder cavity 41 .
  • the compressor provided by the preferred embodiment of the present invention also includes an oil discharge assembly 94, and the oil discharge assembly 94 is connected to the above-mentioned gas-liquid separation chamber 43 for separating the liquid in the gas-liquid separation chamber 43 ( Specifically, lubricating oil) is discharged from the compressor pump body.
  • an oil pool 8 is also provided in the compressor housing 1, and the oil pool 8 is located below the auxiliary bearing 6, and the oil discharge assembly 94 can discharge the liquid in the gas-liquid separation chamber 43 to the oil pool 8 middle.
  • the oil discharge assembly 9 includes a gap oil discharge structure 941.
  • the gap oil discharge structure 941 includes a mandrel 9411 and a mandrel mounting seat 9412 matched with the mandrel 9411.
  • An inner hole is formed in the mandrel mounting seat 9412, and the mandrel 9411 is inserted into the inner hole. In the hole, and fit with the clearance of the inner hole.
  • a gap channel is formed between the mandrel 9411 and the inner wall of the installation through hole of the mandrel mounting seat 9412 , and the liquid in the gas-liquid separation chamber 43 passes through the gap channel and is discharged into the oil pool 8 .
  • the top of the inner hole is conical and flared (as shown in FIG. 21 ), which also facilitates the installation of the mandrel 9411 into the mandrel mounting seat 9412 .
  • the lubricating oil separated from the gas-liquid separation chamber 43 passes between the mandrel 9411 and the mandrel mounting seat 9412 under the action of the air pressure difference.
  • the gap channel is discharged into the oil pool 8 to realize the real separation of gas and liquid.
  • the width of the gap channel is 0.001mm-0.020mm, that is, in the radial direction of the mandrel 9411, the width of the gap between the mandrel 9411 and the inner wall of the inner hole is 0.001mm-0.020mm mm.
  • different refrigerants such as common R22, R134a, etc., will be selected according to the different working conditions of the temperature regulation system. Different refrigerants need to be equipped with different lubricating oils and pre-packaged in the compressor In the casing, different lubricating oils have great differences in viscosity, density, mutual solubility with refrigerant, and fluidity.
  • the oil discharge assembly 94 also includes a first oil passage 942 and a second oil passage 943 .
  • the first oil passage 942 is opened on the auxiliary bearing 6, the inlet of the first oil passage 942 communicates with the gas-liquid separation chamber 43, and guides oil from the gas-liquid separation chamber 43 to the entrance of the gap passage.
  • the second oil passage 943 can be opened on the sound-absorbing cover 93, and is used to communicate with the outlet of the gap passage and the oil pool 8, and oil is imported to the oil pool 8 from the outlet of the gap passage.
  • the oil in the gas-liquid separation chamber 43 sequentially passes through the first oil passage 942 , the gap passage, and the second oil passage 943 , and is discharged to the oil pool 8 .
  • the oil passage 1 942 and/or the oil passage 2 943 are misaligned with the mandrel 9411 so as to limit the mandrel 9411 in the inner hole.
  • one or both of the first oil passage 942 and the second oil passage 943 are misaligned with the mandrel 9411 to form a resistance Position, that is, the first oil passage 942 and the second oil passage 943 are not coaxial with the mandrel 9411.
  • the oil discharge assembly 9 also includes a filter structure 944, an oil discharge hole is arranged in the gas-liquid separation chamber 43, an oil passage 1 942 is arranged on the auxiliary bearing 6, and the filter structure 944 is arranged on the oil discharge hole
  • the inlet of the first oil passage 942 communicates with the outlet of the filter structure 944 or between the oil discharge hole and the first oil passage 942 .
  • the filter structure 944 is provided with a magnetic block, and the filter pores of the filter structure 944 are less than 0.005mm. When the compressor is working, metal wear will occur and some metal debris will be formed. These metal debris will block the gap oil discharge structure 941.
  • a magnetic block is added to the filter structure 944 to absorb and lubricate. The metal impurities in the oil prevent the metal impurities from clogging the filter structure 944.
  • an oil pool 8 is also provided in the compressor housing 1, and the oil pool 8 is located below the secondary bearing 6.
  • the compressor also includes an oil supply device (not shown), and the oil supply device is connected to the oil pool 8.
  • the oil supply device is also arranged in the compressor housing 1 and located below the auxiliary bearing 6 .
  • the oil supply device can be an oil pump, which can be connected with the rotating shaft 31, and the oil can be delivered to the oil guide channel 313 in the rotating shaft 31, and then enter the cylinder cavity 41 and the cylinder 4 and the main bearing 5, auxiliary Between the bearings 6, the circulating supply of lubricating oil is realized.
  • the gas-liquid separation chamber 43 can settle the lubricating oil and separate the gas and liquid, then the lubricating oil in the gas-liquid separation chamber 43 is truly separated from the gaseous refrigerant through the oil discharge assembly 94, and enters the oil pool 8 , and then from the oil pool 8 to the cylinder cavity 41 of the cylinder 4 and between the cylinder 4 and the main bearing 5 and the auxiliary bearing 6 through the oil supply device.
  • the structure of the oil supply system is very simple and compact. The cycle is completed within.
  • the line connecting the center of the rotating shaft 31 to the highest point of the eccentric part of the eccentric rotor 32 is used as the busbar 3201 , second cavities 323 are respectively formed on both sides of the busbar 3201 , and the adjacent second cavities 323 are separated by second reinforcing ribs 324 .
  • the second cavity 323 can be integrated with the aforementioned first cavity 326 (that is, the same cavity), or can be separated from the first cavity 326 .
  • the second cavities 323 on both sides of the second rib 324 are connected through the auxiliary channel 3241 provided on the second rib 324 , so that the two second cavities 323 together form a transition air cavity.
  • the cross-section of the eccentric rotor 32 is egg-shaped.
  • the second reinforcing rib 324 extends along the busbar 3201 , and the air guiding groove 321 is opened on the second reinforcing rib 324 .
  • the auxiliary channel 3241 is a conductive groove opened on the end surface of the eccentric rotor 32 , and the auxiliary channel 3241 is located on the same end surface as the air guiding groove 321 or on the other end surface opposite to the air guiding groove 321 .
  • the auxiliary channel 3241 can be opened on the upper end surface 3204 of the eccentric rotor 32 , and can also be opened on the lower end surface 3203 .
  • both the auxiliary channel 3241 and the air guiding groove 321 are located on the lower end surface 3203 of the eccentric rotor 32 .
  • the auxiliary channel 3241 can also be a through hole passing through the second rib 324 .
  • the eccentric rotor 32 is provided with a second cavity 323
  • the auxiliary bearing 6 is provided with a transition channel 65 ( FIG. 25 ), and the transition channel 65 is located in the auxiliary bearing 6 On the surface, its position corresponds to the position of the air guiding groove 321 of the air guiding channel.
  • the position of the transition channel 65 corresponds to the positions of the air guiding channel and the second cavity 323 .
  • the transition channel 65 When the eccentric rotor 32 rotates to between the zero line 3205 and the intake end position, the transition channel 65 does not communicate with the second cavity 323 and the air guide channel at the same time, and at this time there is no gap between the cylinder cavity 41 and the second cavity 323 Circulate gas.
  • the transition channel 65 When the eccentric rotor 32 rotates to a preset position between the intake end position and the exhaust start position, the transition channel 65 communicates with the air guide channel and the second cavity 323 at the same time, and the gas in the second cavity 323 passes through the transition channel 65 , The air guiding channel enters the inner cavity 41 of the cylinder.
  • the transition channel 65 includes a first transition channel 651 and a second transition channel 652 arranged at intervals.
  • the first transition passage 651 is located between the exhaust slot 62 and the second transition passage 652 .
  • the pump body of the compressor starts to exhaust air through the air guiding passage and the exhaust passage 62 .
  • Fig. 27 when the eccentric rotor 32 rotates to 335 degrees, the air guide groove 321 does not overlap with the exhaust groove 621 (this position is marked as the exhaust end position), and the exhaust ends.
  • the gas in the second cavity 423 is formed by mixing the compressed gas in the clearance and the gas in the original second cavity 423 , and its air pressure is higher than the air pressure in the original second cavity 423 and also higher than the intake air pressure.
  • the eccentric rotor 32 continues to rotate between the exhaust end position and the zero line 3205 , at this time the first transition channel 651 communicates with the air guide groove 321 , and the first transition channel 651 communicates with the second cavity 323 No communication, the second transition channel 652 is not connected with the air guide groove 321 , but communicated with the second cavity 323 , the second cavity 323 neither intakes nor exhausts, and there is no gas communication with the cylinder cavity 41 .
  • the eccentric rotor 32 continues to rotate and crosses the zero line 3205, and when it rotates between the intake start position (that is, the front edge of the suction port 48) and the intake end position (that is, the trailing edge of the suction port 48), Cylinder cavity 41 begins to take in air through air intake port 48, and first transition passage 651 and second transition passage 652 communicate with two second cavities 323 respectively, but are not connected with air guide groove 321, and at this moment the second cavities The 323 also has neither intake nor exhaust.
  • the second transition passage 652 communicates with the air guide groove 421 at the same time.
  • the gas in the second cavity 423 passes through the second transition channel 652, the air guide groove 421, and the air guide port 422 in sequence at this time, and enters the To the cylinder cavity 41, that is, the second cavity 423 exhaust.
  • FIG. 29 Please refer to FIG.
  • the eccentric rotor 32 continues to rotate (for example, rotated to a position of 52 degrees), at this time the second transition passage 652 is not connected to the air guide groove 421, and the second cavity 423 is no longer exhausted to the cylinder cavity 41, That is, the exhaust process of the second cavity 423 ends. Then the eccentric rotor 32 continues to rotate, forming a cycle process of air intake and exhaust in the second cavity 423 .
  • the second cavity 423 not only reduces the weight mentioned above and allows the eccentric rotor 32 to be slightly deformed, but also acts as a transitional air cavity, so that the clearance gas will not affect the performance of the compressor. air intake, thereby increasing the volumetric efficiency of the compressor.
  • the transition channel can also be provided on the inner surface of the main bearing 5 , and correspondingly, the air guide groove 321 is provided on the upper end surface 3204 of the eccentric rotor 32 .
  • the inner surfaces of the main bearing 5 and the auxiliary bearing 6 can be provided with transition channels, and the upper end surface 3204 and the lower end surface 3203 of the eccentric rotor 32 are respectively provided with air guide grooves 321 .
  • the air guide groove 321 is arc-shaped and extends around the circumference of the secondary shaft 322
  • the exhaust groove 621 is also arc-shaped and extends along the circumference of the first shaft hole 61
  • the distance from the air guide groove 321 to the center of the secondary shaft 322 is substantially equal to the distance from the exhaust groove 621 to the center of the first shaft hole 61 .
  • the air guiding groove 321 is also provided with an auxiliary air guiding groove 3215 extending toward the eccentric portion along the second reinforcing rib 324, and the two sides of the auxiliary air guiding groove 3215 are spaced from both sides of the second reinforcing rib 324.
  • the distances between the second cavities 323 are not equal.
  • the auxiliary air guide groove 3215 is used to communicate with the first transition channel 652 and the second transition channel 652 , so that the first transition channel 652 , the second transition channel 652 communicate with the air guide groove 321 . Since the distances between the two sides of the auxiliary air guide groove 3215 and the second cavities 323 on both sides of the second reinforcing rib 324 are not equal, when the first transition channel 652 is located on one side of the auxiliary air guide groove 3215, it can communicate with the auxiliary air guide groove 3215. When the air groove 3215 and the second cavity are located on the other side of the auxiliary air guide groove 3215, the auxiliary air guide groove 3215 and the second cavity cannot be connected.
  • the line connecting the center of the rotating shaft 3 to the center of the slide plate 7 is the zero line 3205
  • the angle between the bus bar 3201 and the zero line 3205 along the rotation direction of the eccentric rotor 32 is the rotation angle of the eccentric rotor 32 .
  • the compressor pump body is in a compressed state, and the air guide groove 321 and the exhaust groove
  • the position of 621 begins to overlap, which is recorded as the initial conduction position of the air guide channel and the exhaust channel (that is, the initial position of exhaust), so that the air guide groove 321 and the exhaust groove 621 are connected.
  • the air in the cylinder The compressed gas in the cavity 41 enters the gas-liquid separation cavity 43 through the gas guide port 322 , the gas guide groove 321 , and the exhaust channel 62 .
  • the pump body of the compressor continues to exhaust gas. Please refer to Fig. 27.
  • the eccentric rotor 32 rotates to 335 degrees, the pump body of the compressor is still in a compressed state.
  • the air guide groove 321 and the exhaust groove 621 do not overlap (that is, the exhaust end position), that is, the guide The air groove 321 is not connected to the exhaust groove 621, and the exhaust is finished at this moment.
  • the size of the rotation angle corresponding to the starting position of exhaust gas is directly related to the compression ratio of the compressor.
  • Fig. 31 shows the simulated curve relationship between the generatrix angle (that is, the rotation angle) and the compression ratio in one embodiment.
  • the rotation angle of the exhaust starting position is preferably between 220 degrees and 250 degrees.
  • the compression ratio is generally about 5-10, so the rotation angle of the exhaust starting position is preferably between 260 degrees and 310 degrees.
  • the exhaust end position of the compressor is generally set between 330° and 340°.
  • Embodiments of the present invention also provide a temperature regulating system, which can be used for cooling or heating, and specifically can be applied to electrical appliances such as air conditioners and refrigerators.
  • the temperature adjustment system includes the compressor described in any one of the above embodiments, and also includes an evaporator and a condenser, and refrigerant circulates between the compressor, the evaporator, and the condenser.
  • the refrigeration and heating principles of the temperature regulation system are common knowledge in the field, and will not be repeated here.
  • the refrigerant is carbon dioxide refrigerant.
  • the compressed gas in the inner cavity of the cylinder can be discharged out of the cylinder through the compressor rotor by providing an air guide channel on the compressor rotor, Make the structure of the compressor simpler and more reliable.
  • FIG 33 shows a schematic structural view of the compressor pump body assembly.
  • the rotating shaft and the eccentric rotor are integrally formed as an integrated rotating shaft 200 .
  • the integrated rotating shaft 200 includes an eccentric part 220 (that is, the eccentric rotor in the above embodiment), a main shaft 210 and a secondary shaft 230.
  • the main shaft 210 and the secondary shaft 230 form a rotating shaft.
  • the eccentric part 220 is assembled inside the cylinder 100.
  • the main shaft 210 and the The auxiliary shaft 230 is respectively equipped with a first bearing and a second bearing at a position close to the eccentric part 220.
  • the bearing assembled with the main shaft 210 will be described as the upper bearing 300 (that is, the main bearing in the above embodiment), and the bearing assembled with the auxiliary shaft 230.
  • the bearing is described as the lower bearing 400 (ie, the secondary bearing of the above embodiment).
  • the upper bearing 300 and the lower bearing 400 may be any one of the first bearing and the second bearing.
  • a suction port 110 and an exhaust port 120 are provided on the cylinder 100, which are respectively located on both sides of the slide groove 130.
  • the position of the center line of the slide groove 130 is set to 0°, and the direction from the slide groove 130 to the suction port 110 The direction of rotation is set as the positive direction.
  • the sliding vanes 600 When the highest point of the eccentric part 220 of the integrated rotating shaft contacts the sliding vane groove 130 , the sliding vanes 600 all enter into the sliding vane groove 130 , and the rotation angle of the integrated rotating shaft 200 is set to 0°.
  • the highest point of the eccentric portion 220 of the integrated rotating shaft rotates through the angle ⁇ , the suction ends and the compression chamber starts to compress.
  • the volume of the compression chamber decreases continuously, and the pressure of the refrigerant gas in the compression chamber continues to rise.
  • the exhaust valve opens, and the compressed high-pressure gaseous refrigerant is discharged
  • the air port 120 is discharged to complete a cycle of suction, compression and exhaust.
  • the first air supply channel is an arc-shaped air guide groove 520 , which is opened on the sealing end surface of the upper bearing 300 , and the gas introduction hole 510 is opened on the circumferential surface of the upper bearing 300 superior.
  • the arc-shaped air guide grooves 520 are centered on the rotation axis of the integrated rotating shaft 200 in the cylinder 100 and distributed along the circumference with a certain radius and angle. Inside the upper bearing 300 , the arc-shaped air guide groove 520 communicates with the air introduction hole 510 .
  • the second air supply groove is an air guiding straight groove 530 , which is opened on the end surface of the integrated rotating shaft eccentric part 220 and the sealing end surface of the upper bearing 300 .
  • the air guide straight groove 530 is distributed along the radial direction of the eccentric part 220 of the integrated rotating shaft, and one end extends to the outer circumferential surface of the eccentric part 220 of the integrated rotating shaft to form an air guide port, and the air guide straight groove 530 and the air guide port form the second air supply aisle.
  • the distance from the other end to the rotation axis of the integrated shaft is the same as the radial distance from the arc-shaped air guide groove 520 to the rotation axis of the integrated shaft.
  • the straight gas guide groove 530 communicates with the arc-shaped air guide groove 520.
  • the straight groove 530 reaches the compression chamber and mixes with the original low-pressure gaseous refrigerant in the compression chamber.
  • the volume of the compression chamber decreases continuously, and the pressure of the mixed gas increases continuously.
  • the first preset range ends.
  • the straight air guide groove 530 is disconnected from the arc-shaped air guide groove 520, and the medium-pressure gaseous refrigerant in the gas introduction hole 510 cannot continue to enter the compression chamber.
  • the gas in the compression chamber continues to be compressed with the rotation of the integrated rotating shaft 200 , and is finally discharged from the exhaust port 120 to complete a compression process.
  • the arc-shaped air guide groove 520 can also be opened on the sealing end surface of the lower bearing 400, and the corresponding second air supply channel should be opened on the eccentric part 220 of the integrated shaft that contacts the sealing end surface of the lower bearing 400. end face.
  • the air guiding straight groove 530 provided above in the eccentric portion 220 of the integrated rotating shaft may also be provided in a position corresponding to the rotor component in the split structure.
  • the starting angle of the arc-shaped air guide groove 520 in the circumferential direction must be greater than ⁇ .
  • the angle ⁇ distributed along the circumferential direction of the arc-shaped air-guiding groove 520 determines the size of the first preset range, that is, determines the communication time of the combined air supply channel, and further determines the amount of air supply.
  • the value of the angle ⁇ is set according to the pressure of the compressor and the amount of air supply, so as to realize the timely cut-off of the air supply channel and prevent the compression chamber from continuing to compress.
  • the arc ⁇ and the supplementary compression can be calculated under the premise that the arc-shaped air guide groove 520 has a certain cross-sectional area.
  • the volume of medium-pressure gaseous refrigerant in the chamber is correlated to realize precise control of the amount of medium-pressure gaseous refrigerant added.
  • ⁇ is about 31°
  • the starting angle of the arc-shaped air guiding groove 520 is ⁇ +5°, that is, 36°
  • the arc angle ⁇ distributed by the arc-shaped air guiding groove 520 is about 144°.
  • the setting of each angle can also select other angles under the condition of meeting the design requirements, and this application does not list them one by one here.
  • the angle from the center of the slide slot 130 to the exhaust end position is ⁇ .
  • the direction in which the integrated shaft eccentric part 220 rotates along the suction port 110 is the positive direction, and the radial angle of the air guiding straight groove 530 is ⁇ .
  • the angle ⁇ should be designed to ensure that the high-pressure refrigerant will not pass through the air supply straight groove provided on the eccentric part 220 of the integrated rotating shaft into the suction low-pressure chamber on the side of the suction port 110 . Further, the design of the angle ⁇ should be controlled to be smaller than the angle ⁇ , so as to ensure that the clearance of the high-pressure chamber will not enter the suction chamber from the joint gap between the slide plate 600 and the air supply straight groove 530 .
  • the first gas supply channel is a straight gas guide groove 530, which is opened on the sealing end surface of the upper bearing 300, and the gas introduction hole 510 is a through hole opened in the axial direction of the upper bearing 300, which is connected with the guide
  • the gas straight grooves 530 are not connected and are set independently of each other.
  • the second air supply channel is an arc-shaped air guide groove 520, which is set on the end surface of the eccentric part 220 of the integrated rotating shaft in contact with the upper bearing 300.
  • the center of the arc-shaped air guide groove 520 is located on the rotation axis of the integrated rotating shaft 200, Distributed along the circumferential direction with a certain radius and angle.
  • the upper bearing 300 and the air guide straight groove 530 and the gas introduction hole 510 opened on it are fixed, and the eccentric part 220 of the integrated rotating shaft and the arc-shaped air guide groove 520 opened on the end face surround the integrated shaft.
  • the rotation center of the eccentric portion 220 of the rotating shaft performs a circular motion.
  • the integrated rotating shaft 200 does not enter the first preset range, and the arc-shaped air guide groove 520 opened on the end surface of the eccentric part 220 of the integrated rotating shaft It is only communicated with the air guide straight groove 530 opened on the sealing end surface of the upper bearing 300, and the communication of the combined air supplement channel cannot be realized.
  • the integrated rotating shaft 200 rotates through the angle ⁇ , the suction ends, the volume of the compression chamber is the largest, and the compression chamber starts to compress.
  • the integrated rotating shaft 200 continues to rotate and reaches the first preset range, that is, one end of the arc-shaped air guiding groove 520 opened on the upper end surface of the eccentric part 220 of the integrated rotating shaft communicates with the air guiding straight groove 530 opened on the sealing end surface of the upper bearing 300, and the other end One end communicates with the axial gas introduction hole 510 opened in the upper bearing 300, and at this time, the combined air supply channel communicates.
  • the medium-pressure gaseous refrigerant is input from the gas introduction hole 510 into the combined air supply channel, and reaches the compression chamber through the arc-shaped air guide groove 520 and the straight air guide groove 530, where it mixes with the original low-pressure gaseous refrigerant in the compression chamber.
  • the volume of the compression chamber decreases continuously, and the pressure of the mixed gas increases continuously.
  • the integrated rotating shaft 200 After the integrated rotating shaft 200 continues to rotate through a certain angle, it rotates out of the first preset range, and the arc-shaped air guide groove 520 on the eccentric part 220 of the integrated rotating shaft is disconnected from the gas supply straight groove, and is only connected to the gas introduction hole 510 If it is not connected, the connection of the combined air supply channel cannot be realized, and the air supply is over.
  • the gas in the compression chamber continues to be compressed with the rotation of the integrated rotating shaft 200 , and is finally discharged from the exhaust port 120 , completing a suction, compression and exhaust process.
  • the air guide straight groove 530 and the gas introduction hole 510 can also be provided on the lower bearing 400, and the corresponding arc-shaped air guide groove 520 should be provided on the integrated rotating shaft eccentric part 220 in contact with the sealing end surface of the lower bearing 400 on the end face.
  • the above arc-shaped air guide groove 520 provided in the eccentric part 220 of the integrated rotating shaft may also be provided in a position corresponding to the rotor component in the split structure.
  • the rotation angle must be greater than ⁇ .
  • the arc-shaped air guide groove 520 is only connected to any one of the air guide straight groove 530 or the gas introduction hole 510 .
  • the integrated rotating shaft 200 is neither connected to the arc-shaped air guide groove 520 nor connected to the gas when it is not within the first preset range.
  • the introduction hole 510 communicates.
  • the integrated rotating shaft 200 is designed with a plurality of axial through holes on the eccentric portion 220 , and the holes are located on the protruding side of the eccentric portion 220 .
  • the weight of the protruding side of the eccentric part 220 of the integrated rotating shaft is reduced, so that the weight of the integrated rotating shaft 200 (self-weight) can be raised along the eccentricity based on the rotating shaft core of the integrated rotating shaft 200
  • the direction is evenly distributed front and rear, left and right, which effectively solves the problem of dynamic balance vibration caused by unequal weight in the radial direction of the integrated shaft 200, and effectively realizes its own self-balancing.
  • the integrated rotating shaft 200 is designed with a counterweight adjustment hole 221 in the opposite direction of the protruding side of the eccentric part 220 , and a plurality of openings on the protruding side of the eccentric part 220
  • the axial through holes are matched, and the refrigerating machine oil is filled according to the actual working conditions, which is used to finely adjust the self-static balance of the integrated rotating shaft 200 . Eliminate the vibration generated by the integrated rotating shaft 200 at high speed from the root cause, and because the root cause of the vibration is solved, there is no need to install a counterweight and balance weight on the eccentric part 220 of the integrated motor rotating shaft, which directly reduces production and assembly costs.
  • a through hole or counterweight adjustment hole 221 along its own axial direction can also be opened on the eccentric part 220 of the crankshaft or the position corresponding to the rotor to realize the above-mentioned self-balancing function .
  • the integrated shaft design omits the integrated shaft and rotor parts set on the original crankshaft structure.
  • the outer peripheral surface of the eccentric part 220 of the integrated shaft 200 directly contacts and rubs against the inner wall of the cylinder 100 and the sliding plate 600 .
  • a roller mounting groove is provided at the end of the sliding plate 600 in contact with the integrated rotating shaft 200 , and roller 700 is installed.
  • the cylindrical surface of the roller 700 cooperates with the outer cylindrical surface of the eccentric part 220 of the integrated rotating shaft to form rolling friction during the operation of the compressor, and the wear rate of the integrated rotating shaft 200 and the sliding plate 600 is minimized to ensure the sliding
  • the effective sealing between the plate 600 and the eccentric part 220 of the integrated rotating shaft prolongs the effective service life of the compressor.
  • the outer diameter of the roller and the inner diameter of the roller installation groove on the sliding plate can be matched first and assembled into one component. Afterwards, the two end faces in the height direction of the part are formed by a double-end surface grinder for one-time fine grinding. This can ensure that the height of both ends of the roller 700 is consistent with the height of the slider 600, which not only reduces the grouping process of the height dimensions of the roller 700 and the slider 600 when they are assembled, but also can well avoid the uneven height of the roller 700 and the slider 600 This causes the sliding vane 600 to run stuck, ensuring the smooth and effective operation of the compressor;
  • the roller mounting groove at the end of the sliding plate 600 is used to install the roller 700, and its section is a V-shaped mounting surface or a curved or U-shaped mounting surface.
  • This structural design makes the contact between the roller 700 and the sliding plate 600 relatively moving. The surface is maximized, which can not only ensure the relative stability of the position of the roller 700 during high-speed rotation without deviation, ensure the effective sealing between the high and low pressure chambers without air leakage, but also reduce the pressure of the friction between the roller 700 and the sliding plate 600, Reduce wear and tear.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

La présente invention concerne un rotor de compresseur, un corps de pompe de compresseur, un compresseur et un système de régulation de température. Le rotor de compresseur comprend un arbre de rotation, et un rotor excentrique raccordé à l'arbre de rotation, l'arbre de rotation étant utilisé pour entraîner le rotor excentrique en rotation ; le rotor excentrique est pourvu d'une surface latérale s'étendant de manière circonférentielle autour de l'arbre de rotation, et d'une face d'extrémité raccordant l'extrémité supérieure et l'extrémité inférieure de la surface latérale ; le rotor excentrique est pourvu d'un canal de guidage d'air ; le canal de guidage d'air comprend une rainure de guidage d'air disposée sur la face d'extrémité et un orifice de guidage d'air disposé sur la surface latérale ; et l'orifice de guidage d'air est en communication avec la rainure de guidage d'air. Dans le rotor de compresseur, le corps de pompe de compresseur, le compresseur et le système de régulation de température qui sont prévus dans les modes de réalisation de la présente invention, le rotor de compresseur est pourvu du canal de guidage d'air, de telle sorte que le gaz comprimé dans une cavité interne d'un cylindre peut être évacué hors du cylindre au moyen du rotor de compresseur, et ainsi la structure du compresseur est plus simple et plus fiable.
PCT/CN2022/107018 2021-11-30 2022-07-21 Rotor de compresseur, corps de pompe de compresseur, compresseur et système de régulation de température WO2023098102A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CN202122983169.1U CN216381861U (zh) 2021-11-30 2021-11-30 泵体组件及增焓转子压缩机
CN202122983169.1 2021-11-30
CN202210622014.1A CN115126697B (zh) 2022-06-02 2022-06-02 压缩机泵体、压缩机及温度调节系统
CN202210620465.1A CN115126696B (zh) 2022-06-02 2022-06-02 压缩机泵体、压缩机及温度调节系统
CN202210620465.1 2022-06-02
CN202210622014.1 2022-06-02

Publications (1)

Publication Number Publication Date
WO2023098102A1 true WO2023098102A1 (fr) 2023-06-08

Family

ID=86611472

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2022/107018 WO2023098102A1 (fr) 2021-11-30 2022-07-21 Rotor de compresseur, corps de pompe de compresseur, compresseur et système de régulation de température

Country Status (1)

Country Link
WO (1) WO2023098102A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006132348A (ja) * 2004-11-02 2006-05-25 Sanyo Electric Co Ltd 圧縮機
CN104929934A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机
CN105090026A (zh) * 2015-07-20 2015-11-25 广东美芝制冷设备有限公司 旋转式压缩机
CN106968947A (zh) * 2016-11-10 2017-07-21 桂林航天工业学院 摆动转子式压缩机
CN109611337A (zh) * 2017-10-05 2019-04-12 桂林航天工业学院 一种滚动转子式压缩机
CN209067472U (zh) * 2018-10-23 2019-07-05 珠海凌达压缩机有限公司 泵体组件、压缩机及具有压缩机的装置
CN112502974A (zh) * 2020-11-18 2021-03-16 珠海格力节能环保制冷技术研究中心有限公司 补气通道、压缩机及空调器
CN216381861U (zh) * 2021-11-30 2022-04-26 广州市德善数控科技有限公司 泵体组件及增焓转子压缩机

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006132348A (ja) * 2004-11-02 2006-05-25 Sanyo Electric Co Ltd 圧縮機
CN104929934A (zh) * 2015-05-27 2015-09-23 广东美芝制冷设备有限公司 旋转式压缩机
CN105090026A (zh) * 2015-07-20 2015-11-25 广东美芝制冷设备有限公司 旋转式压缩机
CN106968947A (zh) * 2016-11-10 2017-07-21 桂林航天工业学院 摆动转子式压缩机
CN109611337A (zh) * 2017-10-05 2019-04-12 桂林航天工业学院 一种滚动转子式压缩机
CN209067472U (zh) * 2018-10-23 2019-07-05 珠海凌达压缩机有限公司 泵体组件、压缩机及具有压缩机的装置
CN112502974A (zh) * 2020-11-18 2021-03-16 珠海格力节能环保制冷技术研究中心有限公司 补气通道、压缩机及空调器
CN216381861U (zh) * 2021-11-30 2022-04-26 广州市德善数控科技有限公司 泵体组件及增焓转子压缩机

Similar Documents

Publication Publication Date Title
CN102465878B (zh) 变排量式涡旋压缩机
US8602755B2 (en) Rotary compressor with improved suction portion location
WO2020042432A1 (fr) Ensemble pompe et compresseur
CN106795881A (zh) 涡旋压缩机及使用了该涡旋压缩机的冷冻循环装置
US20110064596A1 (en) Scroll compressor
CN1971050A (zh) 涡旋式压缩机
KR20120007337A (ko) 압축기
CN115126696B (zh) 压缩机泵体、压缩机及温度调节系统
WO2014192114A1 (fr) Compresseur à vis et dispositif à cycle frigorifique
WO2018049992A1 (fr) Vilebrequin, composant de corps de pompe et compresseur
WO2023098102A1 (fr) Rotor de compresseur, corps de pompe de compresseur, compresseur et système de régulation de température
CN110617222B (zh) 一种电动汽车空调用卧式旋转压缩机及工作方法
US20200018311A1 (en) Scroll compressor and refrigeration cycle apparatus
WO2023097898A1 (fr) Ensemble pompe et compresseur à rotor augmentant l'enthalpie
CN115126697B (zh) 压缩机泵体、压缩机及温度调节系统
CN216381861U (zh) 泵体组件及增焓转子压缩机
CN102889209B (zh) 压缩泵体、旋转式压缩机和制冷循环装置
KR20200054784A (ko) 스크롤 압축기
US11746783B2 (en) Rotary compressor
CN217898187U (zh) 压缩机转子、压缩机泵体、压缩机及温度调节系统
CN217898186U (zh) 压缩机泵体、压缩机及温度调节系统
KR100312366B1 (ko) 용적형 유체기계
JP5727348B2 (ja) 気体圧縮機
KR102004090B1 (ko) 누설 저감 구조가 적용된 로터리 압축기
CN219754799U (zh) 涡旋压缩机以及制冷设备

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 22899922

Country of ref document: EP

Kind code of ref document: A1