WO2020085752A1 - Compresseur - Google Patents

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Publication number
WO2020085752A1
WO2020085752A1 PCT/KR2019/013865 KR2019013865W WO2020085752A1 WO 2020085752 A1 WO2020085752 A1 WO 2020085752A1 KR 2019013865 W KR2019013865 W KR 2019013865W WO 2020085752 A1 WO2020085752 A1 WO 2020085752A1
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WO
WIPO (PCT)
Prior art keywords
flow path
compressor
oil
center housing
sealing portion
Prior art date
Application number
PCT/KR2019/013865
Other languages
English (en)
Korean (ko)
Inventor
김홍민
Original Assignee
한온시스템 주식회사
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 KR1020190130782A external-priority patent/KR102619911B1/ko
Application filed by 한온시스템 주식회사 filed Critical 한온시스템 주식회사
Priority to CN201980069216.4A priority Critical patent/CN112912627B/zh
Priority to JP2021519823A priority patent/JP7109666B2/ja
Publication of WO2020085752A1 publication Critical patent/WO2020085752A1/fr

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    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • 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
    • F04C29/06—Silencing

Definitions

  • the present invention relates to a compressor in which the movement path of the oil discharged from the discharge part is changed, and more particularly, to a compressor having improved oil residual amount by forming a flow path so that oil can be constantly supplied to the suction chamber and the back pressure chamber.
  • a compressor used in an air conditioning system sucks a refrigerant that has been evaporated from an evaporator, changes it to a high temperature and high pressure state that is easy to liquefy, and transfers it to a condenser, and the compressor is operated to compress the refrigerant that is moved through the evaporator.
  • the compressor has a reciprocating type in which a driving source for compressing refrigerant is reciprocating while performing compression, and a rotary type performing compression while rotating.
  • the reciprocating type includes a crank type that transmits a driving force of a driving source to a plurality of pistons using a crank, a swash plate type that transmits to a rotating shaft provided with a swash plate, and a wobble plate type that uses a wobble plate.
  • the rotary type includes a rotary rotary axis and a vane rotary type using vanes, and a scroll type using a rotary scroll and a fixed scroll.
  • the scroll compressor has advantages such as high efficiency, low noise, low vibration, and light weight compared to other types of compressors. In particular, it is possible to automatically prevent overpressure when a liquid refrigerant or a foreign material is injected into the compressor and suitability when an inverter is mounted. Has structural features.
  • scroll compressors Due to these advantages, the current use range of scroll compressors has been expanded to various cooling capabilities. For example, it has been widely used in residential air conditioners as well as room air conditioners and commercial air conditioners.
  • the scroll compressor is provided with two scrolls that are relatively pivotable by being engaged with each other.
  • the two scrolls are composed of a fixed scroll and an orbiting scroll.
  • the fixed scroll and the orbiting scroll have a circular end plate and a wrap or spiral element protruding from the circular end plate.
  • the fixed scroll and each helical element of the orbiting scroll are arranged in engagement with each other, and as the orbiting scroll pivots relative to the stationary scroll, the volume moves between the helical element of the orbiting scroll and the helical element of the orbiting scroll.
  • the above fluid pocket is formed.
  • the volume decreases as the fluid pocket moves to the discharge port of the housing, and the refrigerant fluid in the fluid pocket is compressed and discharged through the discharge port.
  • the scroll scroll of the scroll compressor is driven by a drive shaft, and the drive shaft is driven by an external power source.
  • the orbiting scroll is installed eccentrically with respect to the drive shaft via an eccentric bush, and when the drive mechanism is operated, the orbiting scroll is eccentrically turned about the center of the drive shaft.
  • the drive shaft, the eccentric bush, and the rotational contact portion of the orbiting scroll are supported by rotation through a bearing.
  • Compressors operated in this way should be provided with suitable lubrication to promote smooth operation and durability, and for this lubrication, the refrigerant fluid contains a trace amount of oil.
  • the refrigerant fluid containing the oil is configured to lubricate while moving to the drive shaft, eccentric bush, orbiting scroll.
  • the scroll compressor discharges the refrigerant compressed by the fluid pocket, and the compressed refrigerant thus discharged contains oil for lubrication.
  • the scroll compressor separates oil from a compressed refrigerant containing oil, and then increases the heat exchange efficiency of the compressed refrigerant discharged by returning the separated oil to the low pressure part in the housing, and separates oil to minimize waste of oil.
  • the structure is provided.
  • the conventional scroll compressor configured as described above has a problem in that oil is not sufficiently supplied to the driving mechanism as it is located on the side of gravity (top of the driving shaft) based on the driving shaft.
  • Embodiments of the present invention is to provide a compressor capable of maintaining a constant oil residual amount by stably supplying the oil necessary for lubrication of the suction chamber and the back pressure chamber of the scroll compressor.
  • the compressor according to the first embodiment of the present invention includes a front housing 10 in which a suction chamber 12 is formed and a driving unit 2 generating driving force therein is provided; A center housing 20 facing the front housing 10 and having a back pressure chamber 22 formed therein; A rear housing 50 coupled to the center housing 20 and having a discharge chamber 52 formed therein; A fixed scroll 40 provided between the center housing 20 and the rear housing 50; A turning scroll (30) in which a turning motion is made with respect to the fixed scroll (40); And a flow path 100 is formed such that some of the oil contained in the refrigerant discharged to the discharge chamber 52 is supplied to the suction chamber 12 and the back pressure chamber 22 at different flow rates.
  • the flow path 100 includes a first flow path 110 communicating with the discharge chamber 32; A second flow path 120 communicating with the first flow path 110, one end opening in the center housing 20, and the other end opening toward the back pressure chamber 22; A third flow path 130 communicating with the second flow path 120 and extending upward along a circumferential direction of the center housing 20; The third flow path 130 and one end is connected, the other end includes a fourth flow path 140 opened toward the suction chamber 12, the second flow path 120 and the fourth flow path 140 Is formed on the relative surface of the center housing 20 facing the fixed scroll 40.
  • the third flow path 130 is formed with a cross-sectional area smaller than that of the second flow path 120 and the fourth flow path 140.
  • the sealing member 200 for sealing of oil moving along the fourth flow path 140 in the first flow path 110, the sealing The member 200 includes a first sealing portion 210 in close contact with the center housing 20; The first sealing portion 210 is in close contact with one side, the other side is in close contact with the orbiting scroll 30 and includes a second sealing portion 220 made of a different material from the first sealing portion 210.
  • the first sealing portion 210 is formed with an insertion protrusion 212 that is inserted into the opened inside of the second to fourth flow paths 120, 130, and 140.
  • a first decompression unit 112 for decompressing the pressure of oil moving to the second flow channel 120 is inserted into the first flow channel 110, and the third flow channel 130 is inserted into the fourth flow channel 140. ), The second decompression unit 142 for decompressing the pressure of the moving oil is inserted.
  • the third flow path 130 is branched and extended symmetrically from the second flow path 120 when looking at the center housing 20 from the outside.
  • the third flow path 130 extends from the second flow path 120 toward the fourth flow path 140 in a direction opposite to gravity.
  • the third flow path 130 extends longer than the first flow path 110.
  • the first sealing portion comprises a first body portion 214 made of a metallic or non-metallic material having an overall appearance; A first shape-retaining portion 216 formed at a predetermined thickness on the front surface of the first body portion 214 and maintaining a predetermined elastic restoring force; It includes a second shape-retaining portion 218 formed on a rear surface of the first body portion 214 and having a predetermined elastic restoring force.
  • the compressor according to the second embodiment of the present invention includes a front housing 10 in which a suction chamber 12 is formed and a driving unit 2 generating driving force therein is provided; A center housing 20 facing the front housing 10 and having a back pressure chamber 22 formed therein; A rear housing 50 coupled to the center housing 20 and having a discharge chamber 52 formed therein; A fixed scroll 40 provided between the center housing 20 and the rear housing 50; A turning scroll (30) in which a turning motion is made with respect to the fixed scroll (40); And a flow path 1000 is formed so that some of the oil contained in the refrigerant discharged to the discharge chamber 52 is supplied to the suction chamber 12 and the back pressure chamber 22 at different flow rates.
  • the main flow path 1300 formed in a section extending toward a direction opposite to gravity based on the center housing 20;
  • the main flow path 1300 includes an auxiliary flow path 1350 formed in a smaller size than the main flow path 1300.
  • the auxiliary flow path 1350 is formed in a groove shape so that the oil supplied through the main flow path 1300 remains, either one of the bottom surface 1310 or side surface 1320 of the main flow channel 1300 or the bottom. It is composed of any one formed on both the surface 1310 and the side surface 1320.
  • the auxiliary flow path 1350 is formed in a groove shape so that the oil supplied through the main flow path 1300 remains, and the main flow path 1350 decreases the area open toward the main flow path 1300.
  • the inclined portion 1352 having an inclined relative surface facing toward the flow path 1300 is formed.
  • First sealing portion 210 in close contact;
  • the first sealing portion 210 is in close contact with one side, the other side is in close contact with the orbiting scroll 30 and includes a second sealing portion 220 made of a different material from the first sealing portion 210.
  • the auxiliary flow path 1350 maintains a predetermined amount of oil remaining even when the compressor is stopped.
  • the first sealing portion comprises a first body portion (214a) forming an overall appearance and made of a metal or non-metal material; A first shape holding part 216a formed on a front surface of the first body part 214a and having a predetermined elastic restoring force; It includes a second shape holding portion 218a formed at a predetermined thickness on the rear surface of the first body portion 214a and maintaining a predetermined elastic restoring force.
  • Embodiments of the present invention can improve the overall performance of the compressor by improving the wear resistance by supplying the oil necessary for lubrication to the back pressure chamber of the compressor and the driving unit, and also improving the lubrication performance of the driving unit at the same time.
  • Embodiments of the present invention can minimize the occurrence of vibration and noise during the operation of the compressor by improving the amount of oil circulation supplied to the driving unit.
  • deformation of the first sealing portion is prevented, and tolerance generated between the orbiting scroll and the fixed scroll can be absorbed through the shape retaining portion, so that stable operation can be achieved even when a long-term compressor is used.
  • FIG. 1 is a cross-sectional view showing a compressor according to a first embodiment of the present invention.
  • FIG. 2 is a perspective view showing a center housing and a sealing member according to a first embodiment of the present invention.
  • FIG 3 is a perspective view showing a center housing according to a first embodiment of the present invention.
  • Figure 4 is a cross-sectional view showing a flow path according to the first embodiment of the present invention.
  • FIG. 5 is a cross-sectional view showing a compressor according to a second embodiment of the present invention.
  • FIG. 6 is a perspective view showing a center housing and a sealing member according to a second embodiment of the present invention.
  • FIG. 7 to 8 are views showing the main flow path and the auxiliary flow path according to the second embodiment of the present invention.
  • FIG. 1 is a sectional view showing a compressor according to a first embodiment of the present invention
  • FIG. 2 is a perspective view showing a center housing and a sealing member according to a first embodiment of the present invention
  • FIG. 3 is a view of the present invention It is a perspective view showing the center housing according to the first embodiment.
  • the compressor 1 uses the oil contained in the refrigerant discharged from the discharge chamber 52 to the suction chamber 12 and the back pressure chamber 22. It relates to a compressor that improves the wear resistance of components that generate friction and wear by supplying.
  • the compressor 1 of the present invention is formed with a suction chamber 12, a front housing 10 provided with a driving unit 2 for generating driving force therein, and facing the front housing 10 and being coupled , Forming a compression chamber 42 together with a center housing 20 having a back pressure chamber 22 formed therein, a pivoting scroll 30 inserted inside the center housing 20, and the pivoting scroll 30
  • the fixed scroll 40 and the rear housing 50 coupled to the center housing 20 and having a discharge chamber 52 formed therein, and some of the oil contained in the refrigerant discharged to the discharge chamber 52 are
  • the flow path 100 is formed so as to be supplied at different flow rates toward the suction chamber 12 and the back pressure chamber 22.
  • the compressor 1 forms an overall appearance and is composed of a front housing 10, a center housing 20, and a rear housing 50 from right to left based on the drawing.
  • a suction chamber 12 is formed in a predetermined volume therein, and a driving part 2 is provided in the axial direction at an inner center of the front housing 10.
  • the driving part 2 is a stator 2a positioned in the inner circumferential direction of the front housing 10, and a rotor 2b rotated in interaction with the stator 2a inside the stator 2a and the It is fastened to the rotor (2b), and includes a rotating shaft (2c) extending through the center of the front housing (10).
  • the stator 2a and the rotor 2b are accommodated in the suction chamber 12, and the rotating shaft 2c is the orbiting scroll 30 in the suction chamber 12 via a center housing 20. And extending end is connected to the orbiting scroll 30.
  • the center housing 20 is coupled facing the front housing 10, a back pressure chamber 22 is formed inside, and oil for lubrication is supplied to the back pressure chamber 22.
  • the center housing 20 may communicate with a refrigerant suction pipe (not shown) that guides refrigerant from the outside of the compressor 1 to the suction chamber 12.
  • the rear housing 50 is in close contact with the left side of the center housing 20 based on the drawing, and is selectively detachably mounted to the center housing 20. Then, the refrigerant discharged through the orbiting scroll (30) and the fixed scroll (40) is discharged at a predetermined pressure toward the discharge chamber (52) via a back pressure chamber (22).
  • the rear housing 50 is formed in a structure partially protruding toward the outside with a predetermined length because the refrigerant is discharged at a predetermined pressure when discharged to the discharge chamber 52.
  • the fixed scroll 40 is disposed facing the orbiting scroll 30, and the orbiting scroll 30 rotates at a predetermined speed with respect to the fixed scroll 40 to compress the refrigerant.
  • the fixed scroll 40 forms a compression chamber 42 together with the orbiting scroll 30.
  • the flow path 100 maintains stable lubrication for components requiring lubrication by supplying oil at different flow rates to the suction chamber 12 and the back pressure chamber 22.
  • the flow path 100 is in communication with the discharge chamber 52, the first flow path 110, the first flow path 110, and the center housing 20, one end is opened, the other end is the back pressure
  • the third flow path 130 and one end is connected, the other end includes a fourth flow path 140 opened toward the suction chamber (12).
  • the first flow path 110 is opened in the axial direction of the discharge chamber 52 based on the drawing.
  • a first decompression unit 112 for depressurizing the pressure of the oil moving to the second flow path 120 is inserted into the first flow path 110.
  • the first pressure reducing unit 112 is formed along the axial direction as shown in the drawing, the pressure of the discharge chamber 52 and the second flow path 120 corresponding to the outlet of the first flow path 110 It may be formed of a nozzle-type orifice using a difference in pressure.
  • the first pressure reducing part 112 is formed in a cylindrical shape, and a spiral oil transfer groove G is formed on an inner circumferential surface.
  • the oil transfer groove (G) provides an oil transfer path and simultaneously moves the oil in the direction in which the second flow path 120 is formed by reducing the pressure of the refrigerant discharged at high pressure toward the discharge chamber 52 to an intermediate pressure. The oil is moved to the back pressure chamber (22).
  • the back pressure chamber 22 When the oil is supplied through the second flow path 120 as described above, the back pressure chamber 22 is maintained in a state that is constantly stored at a predetermined height below the rotating shaft 2c. In addition, since the back pressure chamber 22 is supplied with oil to components necessary for lubrication, the occurrence of wear due to friction is reduced, and it is possible to prevent the compressor from being stopped due to damage along with preventing noise and vibration.
  • the refrigerant contains oil, when the pressure is reduced, it can be stably moved from the first flow path 110 toward the second flow path 120.
  • the second flow path 120 and the third to fourth flow paths 130 and 140 are formed on the center housing 20 on the opposite surface facing the fixed scroll 40.
  • the second to fourth flow paths 120, 130, and 140 may be formed in a groove shape as illustrated in the drawing, but may be changed to other shapes.
  • the third flow path 130 is formed with a cross-sectional area smaller than that of the second flow path 120 and the fourth flow path 140.
  • the oil decreases the pressure in the third flow path 130 rather than the pressure at the position passing through the first flow path 110 and the second flow path 120, but the speed increases, so the fourth flow path 140 Is moving fast and reliably towards.
  • the third flow path 130 causes an orifice effect, so that the moving speed of the oil due to the pressure difference is increased.
  • the oil is self-viscous, and friction is inevitably generated while moving along the first to fourth flow paths 110, 120, 130, and 140, so that it is configured with the above-described structure for stable movement to minimize resistance. It is advantageous to move.
  • the oil does not remain only inside the lower portion of the compressor 1 and is lubricated according to sliding and friction. Oil is stably supplied toward the intake chamber 12 and the back pressure chamber 22 that are required.
  • the third flow path 130 extends to the left as an example when the center housing 20 is viewed from the outside.
  • the third flow path 130 extends to the place where the driving unit 2 is positioned based on the drawing in consideration of the layout in which the extension path is in close contact with the center housing 20 and the rear housing 50 during assembly.
  • the third flow path 130 extends in the opposite direction of gravity, and by supplying oil to the driving unit 2, it is possible to achieve stable lubrication at various bearing or sliding locations.
  • a sealing member 200 for sealing of oil moving along the fourth flow path 140 in the first flow path 110 is interposed between the center housing 20 and the orbiting scroll 30. .
  • the sealing member 200 has a first sealing portion 210 in close contact with the center housing 20, one surface is in close contact with the first sealing portion 210, the other side is in close contact with the orbiting scroll 30, It includes a second sealing portion 220 made of a different material from the first sealing portion 210.
  • first sealing part 210 and the second sealing part 220 are used for the first sealing part 210 and the second sealing part 220, and is not limited to a specific material.
  • the first sealing portion 210 has an overall appearance and is formed of a first body portion 214 made of a metal or non-metal material and a predetermined thickness on the front surface of the first body portion 214 and has a predetermined elastic restoring force. It includes a first shape-retaining portion 216 that is retained, and a second shape-retaining portion 218 that is formed at a predetermined thickness on the rear surface of the first body portion 214 and maintains a predetermined elastic restoring force.
  • the first body part 214 is formed of a metal material such as steel or a non-metal material to stably maintain the overall shape of the first sealing part 210 and is not particularly limited to a specific material.
  • the first body portion 214 is formed of a metal material, deformation due to warping can be minimized, so it can be stably used even when used for a long time.
  • the first and second shape-retaining parts 216 and 218 may be made of rubber, for example, but may be changed to other materials that maintain elastic resilience.
  • the first and second shape holding parts 216 and 218 can absorb axial tolerances generated between the orbiting scroll 30 and the fixed scroll 40 with its own elastic restoring force, thereby absorbing vibration in the axial direction during operation. And stable operation through absorption of tolerances.
  • the first and second sealing portions 210 and 220 protrude in the outer circumferential direction and protrude pieces 211 and 222 spaced apart at predetermined intervals.
  • Mounting holes 211a and 222a are not formed on the protruding pieces 211 and 222, but are formed on the protruding pieces 211 and 222a located at some positions, rather than being formed on the protruding pieces 211 and 222a. In an example shown in FIG. 2, mounting holes 211a and 222a are formed at 2 o'clock, 6 o'clock, and 9 o'clock based on the clockwise direction.
  • the protruding pieces 211 and 222a are inserted into a positioning pin (not shown) to a position in which mounting holes 211a and 222a are formed, so that an operator is in close contact with the center housing 20 when assembling the compressor 1. , 2 It is possible to install the sealing portion (210, 220) in place.
  • a first pin groove 21 in which the positioning pin is coupled is formed in the center housing 20.
  • Center holes 210a and 220a into which the rotation shaft 2c or the eccentric bush is inserted are formed in the first and second sealing portions 210 and 220 in the center position, and the radially outer circumference of the center holes 210a and 220a In the direction, a plurality of side holes 210b and 220b are formed at predetermined intervals.
  • the side holes 210b and 220b are center holes 20 in which the first and second sealing parts 210 and 220 are installed as holes in which pins (not shown) are coupled in a pin-and-ring structure that is an anti-rotation structure.
  • the pin is coupled to the second pin groove 21 formed on the relative surface of the.
  • the second sealing part 220 is formed in a relatively thicker thickness than the first sealing part 210 since it is in contact with the orbiting scroll 30 while being rotated. In this case, the second sealing portion 220 maintains a constant stiffness even when continuous contact is maintained and minimizes occurrence of deformation.
  • the first sealing portion 210 may prevent oil leakage when it is in close contact with the first to fourth flow paths 110, 120, 130, and 140, thereby maintaining stable operation of the compressor 1.
  • the second sealing portion 220 is made of a material having a wear resistance similar to that of steel or steel so that wear does not occur due to continuous contact and friction with the orbiting scroll 30, so even when in close contact with the orbiting scroll 30 1 Does not affect the stable sealing of the sealing portion 210.
  • the hardness of the side of the second sealing portion 220 that slides while being in contact with the orbiting scroll 30 may be formed relatively larger than the first sealing portion 210 in contact with the center housing 20.
  • the first sealing portion 210 is formed in a size that is located outside the radial reverberation than the position where the third flow path 130 is located, the part corresponding to the outer rim of the outer diameter does not cause problems due to leakage It can be used stably.
  • the second sealing part 220 has a circumference of the outer diameter greater than or equal to the radius of the orbiting scroll 30, so that a problem due to leakage does not occur and can be stably used.
  • the third flow path 130 is branched and extended symmetrically from the second flow path 120 when the center housing 20 is viewed from the outside.
  • the third flow path 130 is branched and extended to the left and right from the second flow path 120 formed in the center housing 20 toward the driving unit 2, respectively.
  • the oil is more stably moved because a plurality of paths are moved toward the suction chamber 12 or the driving unit 2 along the movement path extending to the right or left. .
  • the third flow path 130 stably moves oil along another extended movement path even when one movement path extending to the left or right of the center housing 20 is blocked or closed. It can improve the mobility stability.
  • the third flow path 130 can stably supply oil to the suction chamber 12 and the back pressure chamber 22, so that a predetermined oil is always retained and the circulation rate of the oil is improved.
  • the first sealing portion 210 is formed with an insertion protrusion 212 that is inserted into the opened inner side of the second to fourth flow paths 120, 130, and 140.
  • the first sealing portion 210 is maintained in a state where the opposite surfaces facing the second to fourth flow paths 120, 130, and 140 are face-to-face, and the insertion protrusion 212 is predetermined on the inner surface. Since it is inserted in length, there is no external leakage of oil.
  • the insertion protrusion 212 is inserted into the second to fourth flow paths 120, 130, and 140 with a predetermined thickness t and length L, and is not limited to the thickness and length shown in the drawing.
  • the oil may move to the fourth flow path 140 along the third flow path 130 opposite to the gravity direction.
  • a second decompression unit 142 for depressurizing the pressure of the oil moving in the third flow path 130 is inserted into the fourth flow path 140.
  • the second pressure reducing part 142 is formed in a cylindrical shape, and a spiral oil transfer groove G is formed on an inner peripheral surface.
  • the oil transport groove (G) provides a transport path of oil and simultaneously reduces the pressure of the refrigerant to guide the movement of the oil to the suction chamber (12).
  • this embodiment can improve the stability of oil movement through the auxiliary flow path and the problems due to lack of oil to promote stable lubrication of the compressor. .
  • the present embodiment is a front housing 10 having a suction chamber 12 formed thereon, and facing the front housing 10, the center housing 20 having a back pressure chamber 22 formed therein, and the center A rear housing 50 coupled to the housing 20 and having a discharge chamber 52 formed therein;
  • a fixed scroll 40 provided between the center housing 20 and the rear housing 50;
  • the flow path 1000 is formed such that some of the oil contained in the refrigerant discharged to the discharge chamber 52 is supplied to the suction chamber 12 and the back pressure chamber 22 at different flow rates.
  • the fixed scroll 40 forms a compression chamber 42 together with the orbiting scroll 30.
  • the flow path 1000 includes a main flow path 1300 formed in a section extending toward a direction opposite to gravity based on the center housing 20 and a size smaller than the main flow path 1300 inside the main flow path 1300. It includes an auxiliary flow path 1350 formed of.
  • the flow path 1000 communicates with the first flow path 1100 communicating with the discharge chamber 52, with the first flow path 1100, one end opening in the center housing 20, and the other end having the back pressure.
  • the second flow path 1200 opened toward the seal 22 and the main flow path 1300 communicating with the second flow path 1200 and extending upward along the circumferential direction of the center housing 20 are one end It is connected, the other end includes a fourth flow path (1400) opened toward the suction chamber (12).
  • first to second flow paths 1100 and 1200 and the fourth flow path 1400 are similar to the first and second flow paths 110 and 120 described in the above-described first embodiment, detailed descriptions are omitted and the auxiliary flow path 1350 is omitted. ).
  • a sealing member 200 for sealing the oil moving along the flow path 1000 is interposed between the center housing 20 and the orbiting scroll 30.
  • the sealing member 200 is in close contact with the center housing 20, the first sealing portion 210 made of an elastic material, and one surface is in close contact with the first sealing portion 210, the other side of the orbiting scroll 30 ) And a second sealing part 220 made of a different material from the first sealing part 210.
  • first sealing part 210 and the second sealing part 220 are used for the first sealing part 210 and the second sealing part 220, and is not limited to a specific material.
  • the first sealing portion 210 forms an overall shape and is formed of a first body portion 214a made of a metal or non-metal material, and a predetermined thickness on the front surface of the first body portion 214a, and has a predetermined elastic restoring force. It includes a first shape-retaining portion 216a to be retained, and a second shape-retaining portion 218a formed at a predetermined thickness on the rear surface of the first body portion 214a and maintaining a predetermined elastic restoring force.
  • the first body portion 214a is formed of a metal material such as steel or a non-metal material to stably maintain the overall shape of the first sealing portion 210, and is not particularly limited to a specific material.
  • the first body portion 214a is formed of a metal material, deformation due to warping can be minimized, so it can be stably used even when used for a long time.
  • the first and second shape-retaining parts 216a and 218a may be made of rubber, for example, but may be changed to other materials that maintain elastic resilience.
  • the first and second shape retaining portions 216a and 218a can absorb axial tolerances generated between the orbiting scroll 30 and the fixed scroll 40 with its own elastic restoring force, thereby absorbing vibration in the axial direction during operation. And stable operation through absorption of tolerances.
  • the first and second sealing portions 210 and 220 protrude in the outer circumferential direction and protrude pieces 211 and 222 spaced apart at predetermined intervals.
  • Mounting holes 211a and 222a are not formed on the protruding pieces 211 and 222, but are formed on the protruding pieces 211 and 222a located at some positions, rather than being formed on the protruding pieces 211 and 222a.
  • mounting holes 211a and 222a are formed at 2 o'clock, 6 o'clock, and 9 o'clock based on the clockwise direction.
  • the protruding pieces 211 and 222a are inserted into a positioning pin (not shown) to a position in which mounting holes 211a and 222a are formed, so that an operator is in close contact with the center housing 20 when assembling the compressor 1. , 2 It is possible to install the sealing portion (210, 220) in place.
  • a first pin groove 21 in which the positioning pin is coupled is formed in the center housing 20.
  • Center holes 210a and 220a into which the rotation shaft 2c or the eccentric bush is inserted are formed in the first and second sealing portions 210 and 220 in the center position, and the radially outer circumference of the center holes 210a and 220a In the direction, a plurality of side holes 210b and 220b are formed at predetermined intervals.
  • the side holes 210b and 220b are center holes 20 in which the first and second sealing parts 210 and 220 are installed as holes in which pins (not shown) are coupled in a pin-and-ring structure that is an anti-rotation structure.
  • the pin is coupled to the second pin groove 21 formed on the relative surface of the.
  • the second sealing part 220 is formed in a relatively thicker thickness than the first sealing part 210 since it is in contact with the orbiting scroll 30 while being rotated. In this case, the second sealing portion 220 maintains a constant stiffness even when continuous contact is maintained and minimizes occurrence of deformation.
  • the second sealing portion 220 is made of a material having a wear resistance similar to that of steel or steel so that wear does not occur due to continuous contact and friction with the orbiting scroll 30, so even when in close contact with the orbiting scroll 30 1 Does not affect the stable sealing of the sealing portion 210.
  • the hardness of the side of the second sealing portion 220 that slides while being in contact with the orbiting scroll 30 may be formed relatively larger than the first sealing portion 210 in contact with the center housing 20.
  • the first sealing part 210 is formed in a size that is located outside the radial reflection of the main flow path 1300 where the portion corresponding to the outer rim is located, so that a problem due to leakage does not occur and is stable. Can be used as
  • the second sealing part 220 has a circumference of the outer diameter greater than or equal to the radius of the orbiting scroll 30, so that a problem due to leakage does not occur and can be stably used.
  • the auxiliary flow path 1350 is formed in a groove shape so that oil supplied through the main flow path 1300 remains, and a bottom surface 1310 or side surface 1320 of the main flow path 1300 is provided. ), Or any one formed on both the bottom surface 1310 and the side surface 1320.
  • this embodiment shows that the auxiliary flow path 1350 is formed on the bottom surface 1310.
  • the oil is supplied to the fourth flow path 1400 along the main flow path 1300 and then to the back pressure chamber 22.
  • the auxiliary flow path 1350 is formed in a groove shape so that oil supplied through the main flow path 1300 remains.
  • the auxiliary flow path 1350 is stored in a predetermined oil, and supply is performed at the same time.
  • auxiliary flow path 1350 when the auxiliary flow path 1350 is formed together with the main flow path 1300 rather than the configuration in which only the main flow path 1300 is formed, a predetermined oil always remains inside the auxiliary flow path 1350. In this case, since the oil supply continues to the suction chamber 12 and the back pressure chamber 22, stable lubrication for the components that generate continuous contact and friction is maintained.
  • the remaining oil is moved through the pressure difference between the discharge chamber 52 and the suction chamber 12 and the back pressure chamber 22, so that the oil is not depleted or not supplied.
  • the auxiliary flow path 1350 may be changed to other shapes in addition to the shapes illustrated in the drawings, and is not particularly limited.
  • the auxiliary flow path 1350 is formed with an inclined portion 1352 having an inclined relative surface facing toward the main flow path 1300 from the auxiliary flow path 1350 so that the area opened toward the main flow path 1300 is reduced. .
  • the inclined portion 1352 serves to prevent the oil stored in the auxiliary flow path 1350 from being moved to the opened area of the main flow path 1300, and of the oil moving through the auxiliary flow path 1350. It is formed to further improve the stability of movement through the pressure difference.
  • the inclined portion 1352 reduces the internal space of the auxiliary flow path 1350 so that oil remains in most of the opened areas of the auxiliary flow path 1350, so that a constant amount is always constant regardless of whether or not there is oil remaining in the main flow path 1300. Oil may remain.
  • the oil is supplied to the above-described suction chamber 12 and the back pressure chamber 22, but the amount of oil supplied according to the pressure varies depending on the number of revolutions per minute of the compressor 1 or the load condition.
  • the present embodiment shows the oil state of the main flow path 1300 in a condition in which the compressor 1 is stopped for a certain period of time, and the oil remaining in the main flow path 1300 than when it is normally operated. This may be lacking. It is advantageous for the main passage 1300 to retain oil to provide stable oil in the suction chamber 12 and the back pressure chamber 22, but when the use of the compressor 1 is stopped, such as in winter, the remaining oil is retained. It is minimized.
  • auxiliary oil passage 1350 retains excess oil necessary for lubrication, oil for minimal lubrication is supplied through the auxiliary oil passage 1350 when the unused compressor 1 is restarted in the off state, thereby improving lubrication performance You can plan.
  • the suction chamber 12 and the back pressure chamber 22 are stably lubricated to the sliding surface even when they are stopped for a long time and then suddenly operated. .
  • oil used for lubrication in a compressor can be used by stably remaining in a sealing member.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un compresseur. Un compresseur selon un mode de réalisation de la présente invention peut fournir de l'huile à une région d'une chambre d'aspiration ou d'une chambre de contre-pression et permettre à l'huile de rester stable à l'intérieur de celle-ci.
PCT/KR2019/013865 2018-10-22 2019-10-22 Compresseur WO2020085752A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201980069216.4A CN112912627B (zh) 2018-10-22 2019-10-22 压缩机
JP2021519823A JP7109666B2 (ja) 2018-10-22 2019-10-22 コンプレッサー

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR20180125893 2018-10-22
KR10-2018-0125893 2018-10-22
KR10-2019-0130782 2019-10-21
KR1020190130782A KR102619911B1 (ko) 2018-10-22 2019-10-21 압축기

Publications (1)

Publication Number Publication Date
WO2020085752A1 true WO2020085752A1 (fr) 2020-04-30

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PCT/KR2019/013865 WO2020085752A1 (fr) 2018-10-22 2019-10-22 Compresseur

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Country Link
WO (1) WO2020085752A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010096059A (ja) * 2008-10-15 2010-04-30 Toyota Industries Corp スクロール型圧縮機
US20110243777A1 (en) * 2008-12-03 2011-10-06 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor
KR20150047688A (ko) * 2013-10-24 2015-05-06 학교법인 두원학원 스크롤 압축기
KR20160138750A (ko) * 2015-05-26 2016-12-06 한온시스템 주식회사 오일회수 수단을 구비한 압축기
KR20180091507A (ko) * 2017-02-07 2018-08-16 한온시스템 주식회사 압축기

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010096059A (ja) * 2008-10-15 2010-04-30 Toyota Industries Corp スクロール型圧縮機
US20110243777A1 (en) * 2008-12-03 2011-10-06 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor
KR20150047688A (ko) * 2013-10-24 2015-05-06 학교법인 두원학원 스크롤 압축기
KR20160138750A (ko) * 2015-05-26 2016-12-06 한온시스템 주식회사 오일회수 수단을 구비한 압축기
KR20180091507A (ko) * 2017-02-07 2018-08-16 한온시스템 주식회사 압축기

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