WO2004010001A1 - Compresseur a volutes - Google Patents

Compresseur a volutes Download PDF

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Publication number
WO2004010001A1
WO2004010001A1 PCT/JP2003/008985 JP0308985W WO2004010001A1 WO 2004010001 A1 WO2004010001 A1 WO 2004010001A1 JP 0308985 W JP0308985 W JP 0308985W WO 2004010001 A1 WO2004010001 A1 WO 2004010001A1
Authority
WO
WIPO (PCT)
Prior art keywords
oil
scroll
pressure chamber
pressure
scroll compressor
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2003/008985
Other languages
English (en)
Japanese (ja)
Inventor
Masakuni Ishikawa
Ryosuke Tanishige
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Thermal Systems Japan Corp
Original Assignee
Zexel Valeo Climate Control Corp
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
Application filed by Zexel Valeo Climate Control Corp filed Critical Zexel Valeo Climate Control Corp
Priority to JP2004522734A priority Critical patent/JP4403074B2/ja
Publication of WO2004010001A1 publication Critical patent/WO2004010001A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F04C18/02—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
    • F04C18/0207—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 both members having co-operating elements in spiral form
    • F04C18/0215—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 both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C29/026—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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present invention relates to a scroll compressor, and more particularly to a scroll compressor suitable for a refrigeration cycle using carbon dioxide as a refrigerant.
  • a scroll compressor including an electric motor, a fixed scroll, and an orbiting scroll
  • an orbiting scroll is eccentrically connected to the tip of a rotating shaft driven by an electric motor with respect to the axis of the rotating shaft, and the oscillating scroll is eccentric with the rotation of the rotating shaft.
  • the refrigerant gas moves and compression of the refrigerant gas is performed in a plurality of compression chambers formed between the scroll and the fixed scroll.
  • a discharge gas is introduced into the back of the orbiting scroll, and the pressure of the discharge gas urges the orbiting scroll toward the fixed scroll.
  • the present invention has been made in view of the above-described problems, and has as its object to provide a scroll compressor that can prevent leakage of refrigerant gas from a compression chamber while maintaining a low pressure around an electric motor. Disclosure of the invention
  • the invention according to claim 1 of the present application is directed to a scroll compressor including an electric motor, a fixed scroll, an orbiting scroll, a low-pressure chamber into which suction gas is introduced, and a high-pressure chamber into which discharge gas is introduced.
  • the motor is housed in the low-pressure chamber, and oil separating means is provided in the high-pressure chamber for separating oil from discharge gas, and the oil separated by the oil separating means is supplied to each sliding portion by a differential pressure.
  • a back pressure chamber is formed on the back of the orbiting scroll so that the oil supply path passes through the back pressure chamber, and the pressure of the oil introduced into the back pressure chamber is reduced.
  • the scroll compressor is configured to bias the orbiting scroll toward the fixed scroll.
  • the motor since the motor is housed in the low-pressure chamber, the pressure resistance of the motor is sufficiently ensured.
  • the present invention is to supply oil to each sliding part rationally, This scroll compressor has achieved a remarkable effect of improving the compression efficiency of the scroll.
  • the invention described in claim 2 of the present application is the invention according to claim 1, wherein the oil supply path is provided with a throttle that sets the pressure of the oil at an intermediate value between the pressure of the low-pressure chamber and the pressure of the high-pressure chamber.
  • This is a scroll compressor with a different configuration.
  • the invention described in claim 3 of the present application is the scroll compressor according to claim 2, wherein the throttle uses a variable throttle.
  • the amount of oil throttle can be adjusted according to the pressure difference between the high pressure side and the low pressure side, and an extremely good biasing force can be obtained for the biasing of the orbiting scroll. Will be done.
  • the invention described in claim 4 of the present application is the invention according to claim 1, wherein the oil supply path includes an annular oil groove provided in a fixed scroll, and a portion of the annular oil groove and a portion of the orbiting scroll.
  • This is a scroll compressor having a configuration provided so as to slide.
  • the sliding portion is lubricated by the oil guided to the annular oil groove, so that the sliding is smoothly performed.
  • the invention described in claim 5 of the present application is directed to a scroll compressor including an electric motor, a fixed scroll, a moving scroll, a low-pressure chamber into which suction gas is introduced, and a high-pressure chamber into which discharge gas is introduced.
  • the low-pressure chamber houses the electric motor, and the high-pressure chamber is provided with oil separating means for separating oil from discharge gas.
  • the oil separated by the oil separating means is supplied to each sliding portion by a differential pressure.
  • An oil supply path is formed, and a back pressure chamber is formed on the back surface of the orbiting scroll.
  • the oil supply path passes through the back pressure chamber, and a pressure of the oil introduced into the back pressure chamber.
  • the orbiting scroll is urged toward the fixed scroll by means of: a block located on the back of the orbiting scroll.
  • a scroll compressor in which a spring is provided between the orbiting scroll and the orbiting scroll to bias the fixed scroll toward the fixed scroll.
  • the motor since the motor is housed in the low-pressure chamber, the pressure resistance of the motor is sufficiently ensured.
  • the oil is brought to the oil supply path by a differential pressure between the high pressure side and the low pressure side.
  • the spring for biasing the orbiting scroll toward the fixed scroll is provided, even at the time of starting or the like in which the oil in the back pressure chamber cannot obtain a sufficient pressure, the orbiting scroll is fixed by the spring. And the leakage of the refrigerant gas from the compression chamber is prevented.
  • the present invention is a scroll compressor that achieves a remarkable effect of rationally supplying oil to each sliding portion and improving compression efficiency of refrigerant gas.
  • the invention described in claim 6 of the present application is the scroll compressor according to claim 1, wherein a baffle plate having a hole is provided above an oil reservoir of the high-pressure chamber.
  • baffle plate has a hole, oil can flow into the baffle plate from above through this hole.
  • the invention described in claim 7 of the present application is the invention according to claim 1, wherein the high pressure
  • the scroll compressor has a configuration in which a shroud having a hole is provided in the chamber, and the shroud surrounds the oil passage of the oil reservoir.
  • FIG. 1 is a sectional view of a scroll compressor according to a first embodiment of the present invention.
  • FIG. 3 is an enlarged view of a main part of FIG. 2 according to a first specific example of the present invention.
  • FIG. 4 is a plan view of a fixed scroll according to the first example of the present invention.
  • FIG. 5 is a plan view of an oil mixing section according to a first specific example of the present invention.
  • FIG. 6 is a sectional view of a scroll compressor according to a second specific example of the present invention.
  • FIG. 6 is an enlarged view of a main part of FIG. 5, according to a second specific example of the present invention.
  • FIG. 8 is a sectional view of a scroll compressor according to a third specific example of the present invention.
  • FIG. 8 is an enlarged view of a main part of FIG. 7, according to a third specific example of the present invention.
  • FIG. 10 is a cross-sectional view of a scroll compressor according to a fourth specific example of the present invention.
  • FIG. 10 is an enlarged view of a main part of FIG. 9, according to a fourth example of the present invention.
  • FIG. 12 is a cross-sectional view of a main part of a scroll compressor according to a fifth specific example of the present invention.
  • FIG. 15 is a right side view of a fixed scroll according to a fifth example of the present invention.
  • FIG. 14 is a sectional view of a main part of a scroll compressor according to a sixth embodiment of the present invention.
  • FIG. 15 is a sectional view of a main part of a scroll compressor according to a seventh embodiment of the present invention.
  • FIG. 25 is a right side view of a fixed scroll according to a seventh example of the present invention.
  • FIG. 17 is a sectional view of a main part of a scroll compressor according to an eighth embodiment of the present invention.
  • FIG. 16 is a cross-sectional view taken along line AA of FIG.
  • FIG. 19 is a sectional view of a main part of a scroll compressor according to a ninth embodiment of the present invention.
  • FIG. 9 is a cross-sectional view taken along the line AA of FIG. 18.
  • FIG. 20 ′ is a cross-sectional view of a main part of a scroll compressor according to a tenth example of the present invention.
  • FIG. 3 is a block diagram showing an oil supply path according to a tenth example of the present invention.
  • FIG. 4 is a cross-sectional view showing a variable stop according to a tenth example of the present invention.
  • Fig. 2 3 is a cross-sectional view showing a variable stop according to a tenth example of the present invention.
  • FIG. 9 is a graph showing an intermediate pressure characteristic according to the tenth example of the present invention.
  • Fig. 24
  • FIG. 6 is a cross-sectional view of a main part of a scroll compressor according to a eleventh embodiment of the present invention.
  • FIG. 4 is a block diagram showing an oil supply path according to the eleventh embodiment of the present invention.
  • FIG. 4 is a cross-sectional view of a main part of a scroll compressor according to a 12th embodiment of the present invention.
  • FIG. 4 is a block diagram showing an oil supply path according to a 12th specific example of the present invention.
  • FIG. 29 is a cross-sectional view showing a variable aperture stop according to the first and second specific examples of the present invention.
  • FIG. 3 is a cross-sectional view showing a variable aperture stop according to a first and second embodiment of the present invention.
  • FIG. 1 shows a vertical scroll compressor 1
  • FIG. 2 is an enlarged view of a main part of FIG.
  • an electric motor 2 is provided in an upper part and a scroll part is provided in a lower part of the cylindrical closed container 10, and the electric motor 2 and the scroll part are connected by a rotating shaft 11.
  • the rotating shaft 11 is supported by an upper part by a sub-bearing 12 and a lower part by a main bearing 13.
  • the bearing 1 2 1 3 may be a plain bearing or a rolling bearing.
  • the motor 2 is composed of ⁇ —evening 14 and staying overnight 15.
  • the mouth 14 is fixed to the rotating shaft 11, and the stay 15 is fixed to the closed container 10.
  • reference numeral 16 denotes a power supply terminal. 7 is connected.
  • the scroll part includes a fixed scroll 3 and a swinging scroll 4.
  • the fixed scroll 3 is provided with a disk-shaped end plate 18 and an impulse curved wrap 19 erected on this end plate, and a discharge port 20 at the center of the end plate 18. Is provided.
  • the orbiting scroll 4 has a disk-shaped end plate 21, an upright standing wrap 22 formed in the same shape as the fixed scroll wrap, and an anti-wrap of the end plate 21. And a boss 23 formed on the front surface.
  • the block 24 forms a bearing at the center, and the rotating shaft 11 is supported on the bearing.
  • the eccentric shaft 25 at the tip of the rotating shaft is inserted into the boss 23, the boss 23
  • the bearing may be a sliding bearing or a rolling bearing.
  • a balance weight 26 for balancing with the eccentric shaft 25 is provided at the tip of the rotating shaft.
  • the orbiting scroll 4 is supported by the block 24 by an old ring 27 so that the orbiting scroll 4 orbits with respect to the fixed scroll 3 without rotating.
  • the block 24 forms a back pressure chamber 9 on the back of the orbiting scroll 4.
  • a plurality of closed spaces are formed by eccentrically moving the fixed scroll 3 and the orbiting scroll 4 by a predetermined distance and shifting the wrap by 180 degrees.
  • Fig. 2 the thin arrows indicate the flow of oil, the thick white arrows indicate the flow of gas, and the thick black arrows indicate the flow of gas mixed with oil (the same applies to other figures).
  • the low-temperature and low-pressure refrigerant gas is guided from the suction port 28 into the closed container 10 and flows into the low-pressure chamber 5 in which the motor 2 is stored.
  • the refrigerant gas that has flowed into the low-pressure chamber 5 is mixed with oil by the oil mixing section 29, and reaches the scroll section through a gas passage 30 formed in the block 24. Due to the orbiting movement of the orbiting scroll 4, the enclosed space formed by both scrolls gradually shrinks. While moving to the center of the scroll, the refrigerant gas is increased in pressure and temperature and discharged from the central discharge port 20 to the high-pressure chamber 6.
  • the high-pressure chamber 6 is provided with oil separating means 7 for separating oil from the refrigerant gas.
  • the oil separating means 7 separates the refrigerant gas and the oil by causing the discharge gas to collide with the radial wall of the high-pressure chamber 6.
  • the separated oil accumulates in the lower oil sump 31.
  • the refrigerant gas separated from the oil passes through a gas passage 32 provided in the fixed scroll 3 and exits from the discharge port 33.
  • the high-pressure oil separated by the oil separating means 7 and stored in the oil reservoir 31 of the high-pressure chamber 6 is supplied to each sliding portion by an oil supply path 8.
  • This oil supply is performed by differential pressure oil supply.
  • the oil supply path 8 passes through a back pressure chamber 9 and urges the orbiting scroll 4 toward the fixed scroll 3 by the pressure of the oil introduced into the back pressure chamber 9. .
  • FIG. 3 is a plan view of the fixed scroll 3.
  • the high-pressure oil collected in the oil sump 31 passes through the oil suction pipe 34 and is introduced into the oil passage 35 formed in the fixed scroll 3, and the high-pressure oil introduced into the oil passage 35 is filled with oil. Filtered at 36, the first stage pressure is reduced by the throttle 37, and the pressure becomes an intermediate pressure between the discharge pressure and the suction pressure.
  • the oil having the intermediate pressure is introduced into an annular oil groove 38 provided in the fixed scroll 3.
  • the sliding of the fixed scroll 3 and the orbiting scroll 4 is such that the periphery of the end plate 21 of the orbiting scroll 4 on the wrap 2 2 side slides with the annular oil groove 38 of the fixed scroll 3.
  • the sliding portion is lubricated by the intermediate pressure oil guided to the annular oil groove 38.
  • the intermediate-pressure oil that lubricates the sliding parts of both scrolls passes through the vertical grooves 90 formed at the key points of the block 24 and the back of the orbiting scroll 4 Guided to the pressure chamber 9, the intermediate scroll urges the orbiting scroll 4 toward the fixed scroll 3 and lubricates the Oldham ring 27 and the seal bearing 39.
  • the intermediate-pressure oil lubricating the old ring 27 and the seal bearing 39 passes through the gap between the orbiting scroll 4 and the eccentric shaft 25, and is formed inside the eccentric shaft 25 and the rotating shaft 11. Is introduced into the oil passage 40 in the direction.
  • the intermediate-pressure oil introduced into the oil passage 40 is reduced in the second stage by the throttle 41 and becomes the suction pressure (low pressure).
  • the seal bearing 39 provided therebetween prevents oil from leaking from the intermediate pressure section to the low pressure section.
  • An elastic body (not shown) is provided between the sub bearing 12 and the rotating shaft 11 to urge the rotating shaft 11 upward.
  • FIG. 4 is a plan view of the oil mixing section 29.
  • the low-pressure refrigerant gas in the low-pressure chamber 5 is sucked from the gas inlet 46 into the C-shaped passage 47.
  • the C-shaped passage 47 communicates with a portion where the oil passage 48 intersects, where the refrigerant gas and the oil are mixed. Mixed with oil
  • the gas exits from the oil mixed gas outlet 49 and passes through the gas passage 30 of the block 24 to the scroll section.
  • the second-stage throttle was provided in the oil passage 40 inside the eccentric shaft.
  • the bearing of the boss 23 of the oscillating scroll is a sliding bearing
  • the oscillating scroll 4 and the eccentric shaft 2 are used. It may be squeezed by a gap with 5.
  • the scroll compressor of this example can be used as a horizontal type as long as it is placed horizontally with the right side of Fig. 1 facing down.
  • the electric motor is housed in the low-pressure chamber, so even if the refrigeration cycle uses carbon dioxide as the refrigerant gas, a special motor or power supply that can withstand high temperature and high pressure There is no need to use terminals, and conventional ones can be used, and cost increases can be suppressed.
  • the thickness of the closed container in the storage unit can be reduced, the size and weight can be reduced.
  • FIG. 5 shows a horizontal scroll compressor
  • FIG. 6 is an enlarged view of a main part of FIG.
  • portions having the same structure and operation as those of the first specific example are denoted by the same reference numerals, and the description thereof will be omitted.
  • This example is basically a horizontal version of the first specific example. The following points are different.
  • the oil suction pipe 34 of the first specific example is not provided because it is not necessary in the case of horizontal installation. Similarly, the gas inlet 46 of the oil mixing section 29 does not protrude as in the first specific example because there is no risk of oil flowing in.
  • the oil separating means 50 transfers the discharged gas in the radial direction of the high-pressure chamber 6. Instead, it collides with the axial wall to separate the refrigerant gas and oil.
  • the oil separating means may be such as to collide with a radial wall as in the first specific example.
  • discharge port 51 is provided on the axial wall of the high-pressure chamber 6, but may be provided on the radial wall.
  • FIG. 7 shows a vertical scroll compressor
  • FIG. 8 is an enlarged view of a main part of FIG.
  • This example differs from the first specific example in the following points.
  • the first specific example has a structure in which the motor 2, the fixed scroll 3, the block 24, and the like are housed inside the closed container 10, whereas in this example, a cup-shaped housing for housing the motor 2 is provided.
  • the closed container 52 is connected to the fixed scroll 3, the first block 53, and the second block 54 by bolts (not shown).
  • the lower part is larger in diameter than the upper part, and the peripheral wall is thicker.
  • a high-pressure chamber 56 provided with oil separating means 55 is provided above the scroll portion.
  • This high-pressure chamber 56 is formed by a first block 53 and a second block 54.
  • the high-pressure chamber 56 communicates with a wheel storage chamber 57 provided at a lower portion of the scroll section by an oil passage 58.
  • the low-temperature and low-pressure refrigerant gas is guided into the closed container 52 from the suction port 28 and flows into the low-pressure chamber 5 in which the motor 2 is stored.
  • the refrigerant gas that has flowed into the low-pressure chamber 5 is mixed with oil by the oil mixing section 29, and reaches the scroll section through a gas passage 30 formed in the first block 53 and the second block 54.
  • the discharged refrigerant gas reaches a high-pressure chamber 56 through a gas passage 59 formed in the fixed scroll 3 and the second block 54.
  • the high-pressure chamber 56 is provided with oil separating means 55, which separates refrigerant gas and oil.
  • the oil separating means 55 separates the refrigerant gas and the oil by causing the discharge gas to collide with the wall of the high-pressure chamber 56.
  • the separated oil collects in the lower oil sump 60.
  • the refrigerant gas separated from the oil exits from the outlet 61.
  • the high-pressure oil separated by the oil separating means 55 and accumulated in the oil sump 60 of the high-pressure chamber 56 is introduced into the oil sump 57 through the oil passage 58, and from there, the oil supply path 8 It is supplied to the sliding part.
  • This oil supply is performed by differential pressure oil supply.
  • the oil supply path 8 passes through the back pressure chamber 9 and urges the orbiting scroll 4 toward the fixed scroll 3 by the pressure of the oil introduced into the back pressure chamber 9.
  • the details of the oil supply path 8 are the same as those in the first specific example, and thus description thereof is omitted.
  • FIG. 9 shows a horizontal scroll compressor
  • FIG. 10 is an enlarged view of a main part of FIG.
  • This example is basically a horizontal version of the third example, but differs in the following points.
  • gas inlet 46 of the oil mixing section 29 does not protrude as in the third specific example because there is no danger of oil flowing in.
  • FIG. 11 is a sectional view of a main part of a horizontal scroll compressor.
  • This example is basically the same as that of the second specific example, except for the following points.
  • the pressure of the oil introduced into the back pressure chamber 9 is a discharge pressure (high pressure) in the present example, while it is an intermediate pressure in the second specific example.
  • the oil communicates with the Oldham ring 27 and the back pressure chamber 9, whereas in this example, the Oldham ring 27 and the back pressure chamber 9 are isolated by the block 24. . Further, the oil supply path 62 is also different.
  • FIG. 12 is a right side view of the fixed scroll 3.
  • the high-pressure oil accumulated in the oil sump 31 is introduced into an oil passage 63 formed in the fixed scroll 3 and the block 24.
  • the high-pressure oil introduced into the oil passage 63 is filtered by the filter 36, and is introduced at a high pressure into the back pressure chamber 9 behind the automatic scroll 4.
  • the oil introduced into the back pressure chamber 9 urges the orbiting scroll 4 toward the fixed scroll 3 at a high pressure and lubricates the seal bearing 39.
  • the high-pressure oil that has lubricated the seal bearings 39 passes through the gap between the orbiting scroll 4 and the eccentric shaft 25 and enters the oil passage 40 in the axial direction formed inside the eccentric shaft 25 and the rotating shaft 11. be introduced.
  • the high-pressure oil is reduced to the suction pressure (low pressure) by the throttle 41 or the clearance between the orbiting scroll 4 and the eccentric shaft 25 (in this case, the throttle 41 is unnecessary).
  • the low-pressure oil flows out of the oil passage 42 formed in the radial direction of the rotating shaft 11 to the surface of the rotating shaft 11, and passes through the spiral groove 43 on the rotating shaft surface to form the main bearing.
  • Lubricate 1 3 The low-pressure oil that has lubricated the main bearings 13 flows into the oil mixing section 29 and is mixed with the suction refrigerant gas.
  • the low-pressure oil that lubricates the Oldham ring 27 is introduced into the annular oil groove 38 provided in the fixed scroll 3, and the low-pressure oil flows into the fixed scroll 3. Lubricate the sliding part of Crawl 4. Then, the oil in the annular oil groove 38 flows into the scroll suction chamber 65 through the small hole 66.
  • the subsequent path of the low-pressure oil flowing through the oil passage 40 in the axial direction in the rotary shaft is the same as in the second specific example, and the description is omitted.
  • the seal bearing 39 provided between the high-pressure section and the low-pressure section prevents oil from leaking from the high-pressure section to the low-pressure section.
  • FIG. 13 is a cross-sectional view of a main part of a horizontal scroll compressor.
  • the urging means for urging the rear surface of the orbiting scroll 4 toward the fixed scroll 3 via the plate 67 by the elastic force of the spring 68 in the scroll compressor of the second specific example is described. It is provided.
  • the orbiting scroll 4 is reliably pressed against the fixed scroll 3 even at the time of start-up or the like in which the oil in the back pressure chamber 9 cannot obtain sufficient pressure. Leakage of refrigerant gas from the chamber is prevented.
  • FIG. 14 is a sectional view of a main part of a horizontal scroll compressor.
  • This example is basically the same as that of the second specific example, except for the oil supply to the Oldham ring 27 in the following points.
  • the oil communicates between the upper portion of the Oldham ring 27 and the back pressure chamber 9, while the lower portion of the Oldham ring 27 and the back pressure chamber 9 are isolated by the work 24. Also, the oil supply route 69 is different.
  • FIG. Fig. 15 is a right side view of the fixed scroll 3.
  • the oil introduced from the oil sump 31 into the oil passage 70 passes through the lower part of the Oldham ring 27 before going to the annular oil groove 38 provided in the fixed scroll 3. Lubricate the Oldham ring 27. O In the upper part of the dam ring 27, as in the second embodiment, the oil guided from the annular oil groove 38 to the back pressure chamber 9 through the longitudinal groove 90 lubricates the oil ring 27. .
  • FIG. 16 is a cross-sectional view of a main part of the horizontal scroll compressor
  • FIG. 17 is a cross-sectional view taken along line AA of FIG.
  • a baffle plate 71 is provided in a high-pressure chamber 6 to partition an oil reservoir 31.
  • a hole 72 serving as a communication passage between the oil and the refrigerant gas is provided in the kaffle plate 71.
  • the scroll compressor of this example even when the vehicle body vibrates when mounted on an automobile, the vibration of the oil accumulated in the oil sump 31 is restricted by the baffle plate 71, so that the oil passage 3 A situation in which oil does not flow into 5 is prevented, and oil can be supplied stably.
  • FIG. 18 is a cross-sectional view of a main part of the horizontal scroll compressor
  • FIG. 19 is a cross-sectional view taken along line AA of FIG.
  • shroud plates 73 and 74 are provided in the high-pressure chamber 6 so as to surround the inlet of the oil passage 35 and the oil reservoir 31 is partitioned. Things. Enclosures 73, 74 are provided with holes 75, 76, respectively, which serve as communication paths for oil and coolant gas.
  • the vibration of the oil accumulated in the oil sump 31 is regulated by the shroud 7 3 7 4. A situation in which oil does not flow into 5 is prevented, and oil can be supplied stably.
  • FIG. 21 is a cross-sectional view showing a main part of a horizontal scroll compressor
  • FIG. 21 is a block diagram showing an oil supply path
  • FIG. 22 is a cross-sectional view showing a variable throttle
  • FIG. 23 is a graph showing intermediate pressure characteristics.
  • the oil supply path 62 is provided with a variable throttle 77 that adjusts the amount of oil throttle according to the pressure difference between the high pressure side and the low pressure side. Oil is supplied from the back pressure chamber 9 to the old ring 27 via a predetermined oil passage 78.
  • the other basic configuration is the same as that of the fifth specific example.
  • high-pressure (P d) oil in the oil sump 31 is supplied to an oil flow passage 63 communicating the oil sump 31 and the back pressure chamber 9 with a throttle 3 7.
  • the oil in the back pressure chamber 9 passes through the seal bearing 39, the main bearing 13, and the oil mixing section 29, and is returned to the scroll suction chamber 65.
  • a restrictor 41 is provided between the seal bearing 39 and the main bearing 13, and the oil becomes low pressure (P s) by passing through the restrictor 41.
  • the oil supplied from the back pressure chamber 9 to the Oldham ring 27 through a predetermined oil passage 78 is introduced into the scroll suction chamber 65 after passing through the annular oil groove 38.
  • a variable throttle 77 is provided between the annular oil groove 38 and the scroll suction chamber 65, and the oil is reduced in pressure (P s) by passing through the variable throttle 77.
  • the variable throttle ⁇ 7 reciprocates between a piston body 7 7 a and a piston body 7 7 a, which can be separated from a small hole 6 6 that guides the oil in the annular oil groove 38 to the scroll suction chamber 65.
  • the cylinder part 77 b that holds the cylinder movably, the elastic body 77 c that urges the piston body 77 b toward the small hole 66 side, and the low-pressure (P s) gas It has a communication passage 77d for introducing into one of the insides and a communication passage 77e for introducing a high-pressure (Pd) gas into the other inside of the cylinder section 77b (FIG. 22). See).
  • the communication passage 77 d for introducing the gas is formed in the piston body 77 a. That is, the variable throttle 77 has a pressure difference between the low-pressure (P s) gas and the high-pressure (P d) gas. If the pressure is small, move the piston body 77a closer to the small hole 66 to increase the amount of oil squeezing.If the pressure difference is large, separate the piston body 77a from the small hole 66. It is designed to reduce the amount of oil throttle.
  • variable throttle 77 By using such a variable throttle 77, it is possible to adjust the amount of oil throttle according to the differential pressure between the high pressure side and the low pressure side, and the oil in the oil supply path 62 is extremely good.
  • the intermediate pressure (Pm) is set. That is, the urging force for urging the orbiting scroll 4 can be obtained more rationally. The concept is described below.
  • FIG. 25 is a cross-sectional view of a main part of a horizontal-type D-screw compressor
  • FIG. 25 is a block diagram illustrating an oil supply path.
  • the pressure of the oil in the back pressure chamber 9 may be set to the high pressure (Pd), and the pressure of the oil supplied to the Oldham ring 29 may be set to the intermediate pressure (Pm).
  • the center of the orbiting scroll 4 is urged by high-pressure (Pd) oil, and the surrounding area is urged by intermediate-pressure (Pm) oil. According to such a configuration, the urging force on the orbiting scroll 4 can be set in a more balanced manner.
  • FIG. 26 is a sectional view of a main part of a horizontal scroll compressor
  • FIG. 27 is a block diagram showing an oil supply path
  • FIGS. 28 and 29 are sectional views showing a variable throttle.
  • a variable throttle 80 is provided in an oil passage 63 communicating the oil sump 31 and the back pressure chamber 9, and between the annular oil groove 38 and the scroll suction chamber 65 ( Specifically, a non-variable aperture 81 is provided in the small hole 6 6).
  • the other basic configuration is the same as that of the above-described tenth example.
  • the variable throttle 80 is provided with a biston body 80 a and a biston body 80 a provided so as to be able to protrude and retract inside an oil flow passage 63 communicating the oil reservoir 31 and the back pressure chamber 9.
  • a communication passage 80d for introducing one inside of the cylinder portion 80b and a communication passage 80e for introducing a high-pressure (Pd) gas into the other inside of the cylinder portion 80b are provided. (See Figure 28).
  • the communication passage 80 e for introducing high-pressure (P d) gas is a piston body 80 a Is formed.
  • the tip of the piston body 80a has an appropriate shape corresponding to the oil passage 63 and the communication passage 80e.
  • the communication passage 80e can be formed outside the piston body 80a (see FIG. 29). That is, when the pressure difference between the low-pressure (P s) gas and the high-pressure (P d) gas is small, the variable restrictor 80 stores the piston body 80 a in the cylinder and restricts the amount of oil restricted. When the pressure difference is large, the piston body 80a is protruded into the oil flow passage 63 to increase the amount of restricted oil.
  • variable throttle 80 that adjusts the amount of oil throttle according to the differential pressure between the high-pressure side and the low-pressure side
  • a variable throttle 80 can be employed.
  • the position and structure of the variable throttle are as follows. The present invention is not limited to this example and the specific examples described above. Industrial applicability
  • the present invention is a scroll compressor particularly suitable for a refrigeration cycle using carbon dioxide as a refrigerant, and is suitable for an air conditioner mounted on an automobile or for home use.

Landscapes

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

Abstract

L'invention concerne un compresseur à volute (1) comprenant un moteur électrique (2), une volute fixe (3), une volute oscillante (4), une chambre à basse pression (5) dans laquelle est introduit un gaz de succion, et une chambre à haute pression (6) dans laquelle est introduite un gaz de distribution. Ledit moteur électrique (2) est logé dans la chambre à basse pression (5), la chambre à haute pression (6) qui renferme un dispositif de séparation d'huile (7) sert à séparer l'huile du gaz de distribution, ce qui permet de former une voie d'alimentation en huile (8) élaborée pour alimenter en l'huile séparée par le dispositif de séparation d'huile (7) chaque partie coulissante au moyen d'une différence de pression. La volute oscillante (4) comprend une chambre de contre-pression (9) formée dans la partie arrière correspondante, de telle façon que la voie d'alimentation en huile (8) s'étend à travers la chambre de contre-pression (9), à condition que la pression d'huile introduite dans la chambre de contre-pression (9) pousse la volute oscillante (4) vers la volute fixe (3).
PCT/JP2003/008985 2002-07-18 2003-07-15 Compresseur a volutes Ceased WO2004010001A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004522734A JP4403074B2 (ja) 2002-07-18 2003-07-15 スクロール圧縮機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2002-209280 2002-07-18
JP2002209280 2002-07-18

Publications (1)

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WO2004010001A1 true WO2004010001A1 (fr) 2004-01-29

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PCT/JP2003/008985 Ceased WO2004010001A1 (fr) 2002-07-18 2003-07-15 Compresseur a volutes

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JP (1) JP4403074B2 (fr)
WO (1) WO2004010001A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006316677A (ja) * 2005-05-11 2006-11-24 Denso Corp スクロール型圧縮機
US7195470B2 (en) * 2003-12-19 2007-03-27 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor having a supply passage connecting the back pressure chamber to discharge pressure region and passing a clearance at a sliding portion
JP2007100589A (ja) * 2005-10-04 2007-04-19 Denso Corp 密閉型電動圧縮機
US8096794B2 (en) 2007-03-15 2012-01-17 Denso Corporation Compressor with oil separation and storage
US8226387B2 (en) * 2005-10-26 2012-07-24 Emerson Climate Technologies, Inc. Scroll compressor including lubrication features
CN105370576A (zh) * 2014-08-07 2016-03-02 Lg电子株式会社 压缩机
EP3690246A1 (fr) * 2019-02-01 2020-08-05 LG Electronics Inc. Compresseur à spirales
CN111648962A (zh) * 2020-07-07 2020-09-11 苏州英华特涡旋技术股份有限公司 一种卧式涡旋压缩机的油循环结构
CN117823409A (zh) * 2022-09-27 2024-04-05 比亚迪股份有限公司 压缩机

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102589771B1 (ko) * 2021-11-30 2023-10-17 엘지전자 주식회사 스크롤 압축기

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Publication number Priority date Publication date Assignee Title
JPS61205386A (ja) * 1985-03-08 1986-09-11 Hitachi Ltd 密閉形スクロ−ル圧縮機

Patent Citations (1)

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Publication number Priority date Publication date Assignee Title
JPS61205386A (ja) * 1985-03-08 1986-09-11 Hitachi Ltd 密閉形スクロ−ル圧縮機

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7195470B2 (en) * 2003-12-19 2007-03-27 Kabushiki Kaisha Toyota Jidoshokki Scroll compressor having a supply passage connecting the back pressure chamber to discharge pressure region and passing a clearance at a sliding portion
JP2006316677A (ja) * 2005-05-11 2006-11-24 Denso Corp スクロール型圧縮機
JP2007100589A (ja) * 2005-10-04 2007-04-19 Denso Corp 密閉型電動圧縮機
US9458847B2 (en) 2005-10-26 2016-10-04 Emerson Climate Technologies, Inc. Scroll compressor having biasing system
US8226387B2 (en) * 2005-10-26 2012-07-24 Emerson Climate Technologies, Inc. Scroll compressor including lubrication features
US8764423B2 (en) 2005-10-26 2014-07-01 Emerson Climate Technologies, Inc. Scroll compressor with fluid injection feature
US8096794B2 (en) 2007-03-15 2012-01-17 Denso Corporation Compressor with oil separation and storage
DE102008013784B4 (de) * 2007-03-15 2017-03-23 Denso Corporation Kompressor
CN105370576A (zh) * 2014-08-07 2016-03-02 Lg电子株式会社 压缩机
EP2995817A1 (fr) * 2014-08-07 2016-03-16 LG Electronics Inc. Compresseur
US9945381B2 (en) 2014-08-07 2018-04-17 Lg Electronics Inc. Compressor
USRE48456E1 (en) 2014-08-07 2021-03-02 Lg Electronics Inc. Compressor
USRE48826E1 (en) 2014-08-07 2021-11-23 Lg Electronics Inc. Compressor
EP3690246A1 (fr) * 2019-02-01 2020-08-05 LG Electronics Inc. Compresseur à spirales
CN111648962A (zh) * 2020-07-07 2020-09-11 苏州英华特涡旋技术股份有限公司 一种卧式涡旋压缩机的油循环结构
CN117823409A (zh) * 2022-09-27 2024-04-05 比亚迪股份有限公司 压缩机

Also Published As

Publication number Publication date
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JPWO2004010001A1 (ja) 2005-11-17

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