EP2857688B1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
EP2857688B1
EP2857688B1 EP13797726.0A EP13797726A EP2857688B1 EP 2857688 B1 EP2857688 B1 EP 2857688B1 EP 13797726 A EP13797726 A EP 13797726A EP 2857688 B1 EP2857688 B1 EP 2857688B1
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EP
European Patent Office
Prior art keywords
piston
gap
peripheral surface
rotary compressor
crankshaft
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EP13797726.0A
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German (de)
English (en)
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EP2857688A1 (fr
EP2857688A4 (fr
Inventor
Daisuke Funakoshi
Hirofumi Yoshida
Takeshi Ogata
Yu Shiotani
Hiroaki Nakai
Tsuyoshi Karino
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Panasonic Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP2857688A4 publication Critical patent/EP2857688A4/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
    • F04C18/30—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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance
    • 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

Definitions

  • the present invention relates to a rotary compressor used for an air conditioner, a freezing machine, a blower, a water heater and the like.
  • a compressor is used in a freezing machine and an air conditioner.
  • the compressor sucks gas refrigerant which is evaporated by an evaporator, compresses the gas refrigerant to pressure which is required for condensation, and discharge high temperature and high pressure refrigerant into a refrigerant circuit.
  • a rotary compressor is known as one of such compressors.
  • Fig. 18 is a sectional view of essential portion of a conventional rotary compressor.
  • the compression mechanism 3 includes a compression chamber 39, a piston 32 and a vane (not shown) .
  • the compression chamber 39 is composed of a cylinder 30, and an upper bearing 34 and a lower bearing 35 which close both end surfaces of the cylinder 30.
  • the piston 32 exists in the compression chamber 39, and is fitted over an eccentric portion 31a of the crankshaft 31 supported by the upper bearing 34 and the lower bearing 35.
  • the vane abuts against a piston outer peripheral surface 32a of the piston 32, follows eccentric rotation of the piston 32 and reciprocates, and partitions an interior of the compression chamber 39 into a low pressure portion and a high pressure portion.
  • a suction port 40 opens in the cylinder 30, and gas is sucked through the suction port 40 toward the low pressure portion in the compression chamber 39.
  • a discharge port 38 opens in the upper bearing 34, and gas is discharged from the high pressure portion through the discharge port 38. The low pressure portion is turned and formed into the high pressure portion in the compression chamber 39.
  • the piston 32 is accommodated in the compression chamber 39 which is formed by the upper bearing 34, the lower bearing 35 and the cylinder 30. Upper and lower portions of the cylinder 30 are closed by the upper bearing 34 and the lower bearing 35.
  • the discharge port 38 is formed as a hole penetrating the upper bearing 34. This hole is circular as viewed from above.
  • the discharge port 38 is provided at its upper surface with a discharge valve 36 which opens when the discharge valve 36 receives pressure which is equal to or greater than predetermined pressure.
  • a cup muffler 37 is provided above the upper bearing 34 for canceling noise of discharged gas.
  • an operation-time minimum gap W is provided between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a. Magnitude of a leakage area S which is obtained by the operation-time minimum gap W and a height H of the compression chamber 39 exerts an influence on efficiency of the compressor.
  • the operation-time minimum gap W between the piston outer peripheral surface and the inner peripheral surface is set greater so that both the surfaces do not strongly come into contact with each other, the problem of seizing or wearing is eliminated and the sliding loss reduces.
  • Fig. 17 is a schematic diagram showing a shape of a cylinder having a non-circular (complex circular) cross section in the conventional rotary compressor described patent document 1.
  • a compression chamber has a non-circular cross section composed of a plurality of curvatures. According to this, even if an envelop locus of a piston outer peripheral surface becomes non-circular due to influence of an axial locus or the like, the operation-time minimum gap W while the piston rotates once can be maintained constant. As a result, the leakage loss and the sliding loss are reduced.
  • JP H01 138393 A discloses that a roller fitted into the eccentric revolution part of a crankshaft driven by a motor is housed into the bore of a cylinder, and the inside of the bore is divided into two chambers and by attaching and separating a blade onto the roller by the force of a spring.
  • the inner peripheral surface of the bore is formed into an elliptic having a major axis and minor axis, and said major axis is set at the position where the pressure in a compression side inner chamber becomes max. by the revolution of the crankshaft or the position set to the above-described position.
  • the axis center of the crankshaft is set into eccentric to the compression side along the major axis from the center of the bore, and assembly is performed so that the gap between the outer peripheral surface of the roller and the inner peripheral surface of the bore becomes min. on the compression side on the major axis.
  • WO 2010/013375 A1 discloses a rotary compressor wherein the ratio of a first bearing gap between the inner circumferential surface of a roller and the outer circumferential surface at the eccentric portion of a crankshaft and the diameter at the eccentric portion of a crankshaft is set in the range of 11/10000-20/10000, the roller can be pressed lightly against the inner circumferential surface of a cylinder by the differential pressure between a high pressure portion and a low pressure portion, and since the minimum gap during operation is minimized and the inner circumferential surface of a cylinder can be touched only with the differential pressure, big sliding loss is not generated.
  • JP 2010 116782 A discloses a fluid machine in which a through-hole is formed on a straight line of the cylinder. With such structure, in the smallest gap position on the straight line, wherein foreign matters are easy to be caught, the cylinder can be easily and elastically deformed to restrict a stop of the fluid machine due to the caught foreign matters.
  • the cross section shape of the cylinder inner peripheral surface is non-circular composed of the plurality of curvatures, precision on the order of several ⁇ m is required, and its machining operation is extremely difficult. Further, machining errors such as surface roughness and undulation of the cylinder inner peripheral surface exert large influence on the efficiency of the compressor, and this causes variation in performance.
  • the present invention has been accomplished in view of the above circumstances, and it is an object of the invention to reduce a leakage loss from an operation-time minimum gap W from the ground up without deteriorating reliability, and to further enhance efficiency of a compressor without increasing a sliding loss.
  • a first aspect of the invention provides a rotary compressor comprising a motor and a compression mechanism both accommodated in a hermetic container, in which the compression mechanism connected to the motor through a crankshaft comprises a cylinder, an upper bearing and a lower bearing which close, from above and below, both end surfaces of the cylinder to form a compression chamber, a piston fitted over an eccentric portion of the crankshaft provided in the cylinder, a vane which follows eccentric rotation of the piston, which is provided in the cylinder, which reciprocates in a slot, and which partitions the compression chamber into a low pressure portion and a high pressure portion, a suction port which is in communication with the low pressure portion, and a discharge port which is in communication with the high pressure portion, wherein if a gap formed between an outer peripheral surface of the piston and an inner peripheral surface of the cylinder in a state where the eccentric portion is disposed at a position of a predetermined crank angle from a position of the vane and the piston is made to abut against a most eccentric position of the eccentric
  • the first bearing gap is formed between the piston and the eccentric portion
  • the second bearing gap is formed between the upper bearing and the main shaft
  • the crankshaft is moved by the first bearing gap in a load direction at a time of operation
  • the piston is moved by the second bearing gap in the load direction at the time of operation
  • a minimum gap formed between an outer periphery of the piston and a phantom line of an inner periphery of the cylinder is defined as ⁇
  • a direction of the minimum value ⁇ min is set such that a minimum gap ⁇ near a crank angle 45° and a minimum gap ⁇ near a crank angle 225° are substantially equal to each other.
  • the rotary compressor in the rotary compressor of the first or second aspect, further includes one more compression chamber.
  • the minimum value ⁇ min is about 5 ⁇ m to 10 ⁇ m.
  • a rotary compressor of a first aspect of the present invention if a gap formed between an outer peripheral surface of a piston and an inner peripheral surface of a cylinder in a state where an eccentric portion of a crankshaft is disposed at a position of a predetermined crank angle from a position of a vane and the piston is made to abut against a most eccentric position of the eccentric portion of the crankshaft and an inner peripheral surface of an upper bearing is made to abut against an outer peripheral surface of the crankshaft when the rotary compressor is assembled is defined as ⁇ , a minimum value ⁇ min of the gap ⁇ is set at a crank angle substantially opposite from a maximum load direction of the crankshaft during operation of the rotary compressor.
  • the operation-time minimum gap W becomes large at a crank angle opposite from the maximum load direction.
  • the minimum gap ⁇ min is previously set at the crank angle opposite from the maximum load direction, the operation-time minimum gap W becomes small. Therefore, leakage can be reduced and efficiency can be enhanced.
  • a first bearing gap is formed between the piston and the eccentric portion of the crankshaft
  • a second bearing gap is formed between the upper bearing and the main shaft of the crankshaft
  • the crankshaft is moved by the first bearing gap in a load direction at a time of operation
  • the piston is moved by the second bearing gap in the load direction at the time of operation
  • a minimum gap formed between an outer periphery of the piston and a phantom line of an inner periphery of the cylinder is defined as ⁇
  • a direction of the minimum value ⁇ min is set such that a minimum gap ⁇ near a crank angle 45° and a minimum gap ⁇ near a crank angle 225° are substantially equal to each other.
  • the operation-time minimum gap W in the vicinity of the crank angle 45° and the operation-time minimum gap W in the vicinity of the crank angle 225° becomes substantially equal to each other, phantom lines in the load direction of the crankshaft become symmetric, the gaps are balanced and thus, a large sliding loss is generated. Therefore, leakage from the operation-time minimum gap W is reduced and efficiency can be enhanced while suppressing deterioration of reliability such as wearing and seizing.
  • the rotary compressor in the rotary compressor of the first or second aspect, further includes one more compression chamber.
  • a load direction in the case of a two-piston rotary, a load direction is substantially constant and a load becomes greater as compared with a one-piston rotary. Therefore, it is possible to reduce leakage from the operation-time minimum gap W and to enhance the efficiency while further suppressing deterioration of reliability such as wearing and seizing.
  • the minimum value ⁇ min is about 5 ⁇ m to 10 ⁇ m.
  • the phantom lines in the load direction of the crankshaft become symmetric, and the gaps are balanced. Therefore, even if the minimum gap ⁇ min is excessively reduced, a large sliding loss is not generated in the vicinity of the crank angle 45° and the crank angle 225° when the rotary compressor is operated. Therefore, it is possible to reduce leakage from the operation-time minimum gap W and to enhance the efficiency while suppressing deterioration of reliability such as wearing and seizing.
  • Fig. 1 is a vertical sectional view of a rotary compressor according to an embodiment of the invention
  • Fig. 6 is a plan view of essential portions showing a compression chamber of the rotary compressor when the rotary compressor is operated.
  • a motor 2 and a compression mechanism 3 are accommodated in a hermetic container 1.
  • the motor 2 and the compression mechanism 3 are connected to each other through a crankshaft 31.
  • the motor 2 is composed of a stator 22 and a rotor 24.
  • the compression mechanism 3 is composed of a cylinder 30, a piston 32, a vane 33, an upper bearing 34 and a lower bearing 35.
  • the compression chamber 39 is formed by the cylinder 30, and an upper bearing 34 and a lower bearing 35 which close both end surfaces of the cylinder 30.
  • the piston 32 is accommodated in the compression chamber 39, and the piston 32 is fitted over an eccentric portion 31a of the crankshaft 31 which is supported by the upper bearing 34 and the lower bearing 35.
  • the vane 33 reciprocates in a slot 33a provided in the cylinder 30 and always abuts against an outer peripheral surface 32a, thereby partitioning an interior of the compression chamber 39 into a low pressure portion 39a and a high pressure portion 39b. Two spaces are formed in the compression chamber 39 by the vane 33 and an operation-time minimum gap W.
  • a space connected to a suction port 40 is the low pressure portion 39a, and a space connected to the discharge port 38 is the high pressure portion 39b.
  • the operation-time minimum gap W is an operation-time gap generated at a position where the piston 32 most approaches the cylinder 30.
  • the suction port 40 opens in the cylinder 30, and the suction port 40 sucks (supplies) refrigerant gas to the low pressure portion 39a in the compression chamber 39.
  • the discharge port 38 opens in the upper bearing 34, and discharges gas from the high pressure portion 39b.
  • the discharge port 38 is formed as a circular hole which penetrates the upper bearing 34.
  • An upper surface of the discharge port 38 is provided with a discharge valve 36, and when the discharge valve 36 receives pressure which is equal to or greater than a predetermined value, the discharge valve 36 is opened.
  • the discharge valve 36 is covered with a cup muffler 37.
  • a volume of the low pressure portion 39a of the compression mechanism 3 gradually increases.
  • refrigerant gas flows in from the suction port 40.
  • the low pressure portion 39a moves while changing its volume by eccentric rotation of the piston 32, and if change in volume is turned from increase to reduction, the low pressure portion 39a becomes the high pressure portion 39b.
  • the volume of the high pressure portion 39b gradually reduces, and pressure therein is increased by the reduction in volume.
  • the discharge valve 36 opens and high pressure refrigerant gas flows out from the discharge port 38.
  • Refrigerant gas is discharged into the hermetic container 1 by the cup muffler 37.
  • the refrigerant gas passes through a notch 28 formed by the stator 22 and an inner periphery of the hermetic container 1 and through an air gap 26 of the motor 2, and the refrigerant gas is sent into an upper shell 4 of an upper portion of the motor 2.
  • the refrigerant gas is discharged from the refrigerant discharge pipe 5 to outside of the hermetic container 1. Arrows in Fig. 1 show a flow of refrigerant.
  • a height of the cylinder 30 must be set slightly higher than a height of the piston 32 so that the piston 32 can slide in the cylinder 30.
  • oil leaks from the spaces 46 and 47 into the compression chamber 39 through this gap.
  • Fig. 2 is a sectional view of essential portions showing a relation between the piston of the rotary compressor of the embodiment and a gap of the crankshaft when the rotary compressor is assembled
  • Fig. 3 is a plan view of essential portions showing the compression chamber of the rotary compressor when the rotary compressor is assembled
  • Fig. 4 is a plan view of essential portions showing disposition of the upper bearing in Fig. 3
  • Fig. 5 is a sectional view taken along line V-V in Fig. 4 .
  • a gap between the piston inner peripheral surface 32b of the piston 32 and an eccentric portion outer peripheral surface 31b of the eccentric portion 31a of the crankshaft 31 is defined as a first bearing gap c1 as shown in Figs. 2 and 3 .
  • the crankshaft 31 is disposed such that the eccentric portion 31a becomes equal to an angle ⁇ from the vane 33 as shown in Fig. 3 .
  • the angle ⁇ is an angle on a side substantially opposite from the maximum load direction of the crankshaft 31.
  • crankshaft 31 is disposed such that a later-described minimum gap ⁇ min is disposed such that the minimum gap ⁇ min is closer to the discharge port 38 than a phantom line connecting the vane 33 and a center of the crankshaft 31 to each other.
  • the piston 32 is brought into abutment against a most eccentric position of the eccentric portion 31a.
  • a minimum gap ⁇ min is formed between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a at the position of the angle ⁇ .
  • the first bearing gap c1 is formed between the piston inner peripheral surface 32b and the eccentric portion outer peripheral surface 31b at the position of the angle ⁇ .
  • a second bearing gap c2 is formed between an inner peripheral surface 34a of the upper bearing 34 and the main shaft 31c of the crankshaft 31.
  • the minimum gap ⁇ min, the first bearing gap c1 and the second bearing gap c2 are disposed on a phantom line separated away from the vane 33 by the angle ⁇ .
  • Fig. 5 shows a state where the minimum gap ⁇ min, the first bearing gap c1 and the second bearing gap c2 are disposed.
  • the operation-time minimum gap W is provided between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a as shown in Fig. 16 .
  • Magnitude of a leakage area S obtained by the operation-time minimum gap W and a height H of the compression chamber 39 exerts influence on efficiency of the compressor.
  • the minimum gap ⁇ min is formed between the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a.
  • a pressure difference X is added to the piston 32 as shown by an arrow in Fig. 6 . Since the low pressure portion 39a and the high pressure portion 39b are formed in the compression chamber 39, the pressure difference X is applied from the high pressure portion 39b toward the low pressure portion 39a. The piston 32 is pushed toward the low pressure portion 39a by the pressure difference X and the piston 32 is displaced.
  • the operation-time minimum gap W is not formed at a position of the minimum gap ⁇ min which is set when the compression mechanism is assembled, a position of an angle ( ⁇ + ⁇ ) becomes the operation-time minimum gap W where the piston outer peripheral surface 32a and the cylinder inner peripheral surface 30a most approach each other.
  • the operation-time minimum gap W becomes a gap which is narrower than the minimum gap ⁇ min ( ⁇ is a minute angle which is varied depending upon an operation state).
  • the minimum gap ⁇ min which is set when the compression mechanism is assembled becomes narrow by 1/2 of the first bearing gap c1 and by 1/2 of the second bearing gap c2 when the compression mechanism is operated. According to this, the operation-time minimum gap W which is theoretically close to zero is formed, and the compression mechanism is operated with a gap size of only oil film size in practice.
  • the operation-time minimum gap W becomes large at a crank angle on the opposite side from the maximum load direction.
  • the minimum gap ⁇ min is previously set at the crank angle on the opposite side from the maximum load direction, it is possible to keep the operation-time minimum gap W small at the crank angle on the opposite side from the maximum load direction, and leakage is reduced. Further, the operation-time minimum gap W does not become small also at other crank angles, input is not increased and efficiency can be enhanced.
  • Fig. 8 shows magnitude and a direction of a load at each of crank angles which is applied to the crankshaft 31 of a one-piston rotary compressor during one rotation (a direction of the vane is a plus side of y axis, and a direction of suction is a minus side of x axis and a plus side of y axis).
  • a load becomes the maximum in the vicinity of a crank angle 225°.
  • Figs. 9 and 10 show, at each of crank angles, a relation between a locus of the piston outer peripheral surface 32a and a position of the cylinder inner peripheral surface 30a when the crankshaft 31 moves by the second bearing gap c2 in the load direction at the time of operation and the piston 32 moves by the first bearing gap c1 in the load direction at the time of operation assuming that the cylinder 30 does not exist (at each of crank angles, a minimum gap formed between the piston outer peripheral surface 32a and a phantom line of the cylinder inner peripheral surface 30a is defined as ⁇ .
  • a gap when the piston outer peripheral surface 32a spreads outward more than the cylinder inner peripheral surface 30a is defined as substantially zero (oil film holding)
  • the minimum gap ⁇ becomes substantially equal to the operation-time minimum gap W).
  • a direction of the minimum gap ⁇ min is set to a general direction.
  • a direction of the minimum gap ⁇ min is set such that the minimum gap ⁇ in the vicinity of a crank angle 45° and the minimum gap ⁇ in the vicinity of a crank angle 225° becomes substantially equal to each other.
  • Fig. 11 shows magnitude and a direction of a load in each of the crank angles which is applied to the crankshaft 31 of a two-piston rotary compressor (not shown) during one rotation.
  • the load is the maximum in the vicinity of a crank angle 225°.
  • Figs. 12 and 13 show, at each of crank angles, positional relations between a locus of the piston outer peripheral surface 32a and a phantom line of the cylinder inner peripheral surface 30a when the crankshaft 31 moves by the second bearing gap c2 in the load direction at the time of operation and the piston 32 moves by the first bearing gap c1 in the load direction at the time of operation assuming that the cylinder 30 does not exist (only cylinder 30 on one side is shown).
  • a direction of the minimum gap ⁇ min is set to a general direction.
  • a direction of the minimum gap ⁇ min is set such that the minimum gap ⁇ in the vicinity of a crank angle 45° and the minimum gap ⁇ in the vicinity of a crank angle 225° become substantially equal to each other.
  • Figs. 12 and 13 are compared with each other, a portion of the piston outer peripheral surface 32a which spreads outward more than the cylinder inner peripheral surface 30a is held by an oil film, operation is actually carried out along the cylinder inner peripheral surface 30a.
  • a length of the sliding portion in Fig. 13 is apparently shorter, and increase in a sliding loss can be suppressed as small as possible.
  • the minimum gap ⁇ can be uniformed in a wide range of the crank angle, the leakage loss can be reduced and the efficiency can be enhanced.
  • a direction of a bearing load is substantially constant, the minimum gap ⁇ in the vicinity of a crank angle 45° and the minimum gap ⁇ in the vicinity of a crank angle 225° can be uniformed while keeping excellent balance and thus, efficiency can further be enhanced.
  • Fig. 14 shows a state where a direction of the minimum gap ⁇ min is set to a general direction and the minimum gap ⁇ min is extremely reduced as small as 5 to 10 ⁇ m.
  • Fig. 15 shows a state where a direction of the minimum gap ⁇ min is set such that the minimum gap ⁇ in the vicinity of a crank angle 45° and the minimum gap ⁇ in the vicinity of a crank angle 225° become substantially equal to each other and the minimum gap ⁇ min is extremely reduced as small as 5 to 10 ⁇ m. If Figs. 14 and 15 are compared with each other, a length of the sliding portion in Fig. 14 is largely increased, but the minimum gap ⁇ is more uniform in Fig. 15 over its entire circumference. In Fig.
  • Fig. 15 input does not increase so much and volume efficiency is largely enhanced. Generally, it is considered that if the minimum gap ⁇ min is made small, volume efficiency is enhanced, but its limit value is about 10 ⁇ m. If the minimum gap ⁇ min is set to a direction opposite from the maximum load direction of the crankshaft 31 as in this embodiment, efficiency can further be enhanced even if the minimum gap ⁇ min is set to 10 ⁇ m or less (compare Fig. 13 and 15 ).
  • the rotary compressor of the present invention it is possible to suppress deterioration of reliability such as wearing and seizing, to reduce both leakage loss and sliding loss, and to enhance the efficiency of the compressor.
  • the invention can also be applied to a compressor for an air conditioner using HFC-based refrigerant and HCFC-based refrigerant, and to an air conditioner and a heat pump water heater using carbon dioxide which is natural refrigerant.

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

Claims (4)

  1. Compresseur rotatif comprenant un moteur (2) et un mécanisme de compression (3) tous deux logés dans un récipient hermétique (1), dans lequel
    le mécanisme de compression (3) relié au moteur (2) par l'intermédiaire d'un vilebrequin (31) comprend
    un cylindre (30),
    un palier supérieur (34) et un palier inférieur (35) qui ferment, à partir du dessus et du dessous, les deux surfaces d'extrémité du cylindre (30) pour former une chambre de compression (39),
    un piston (32) monté sur une partie excentrique (31a) du vilebrequin (31) disposé dans le cylindre (30),
    une aube (33) qui suit la rotation excentrique du piston (32), qui est disposée dans le cylindre (30), qui effectue un mouvement de va-et-vient dans une fente et qui divise la chambre de compression (39) en une partie basse pression et en une partie haute pression,
    un orifice d'aspiration (40) qui est en communication avec la partie basse pression et
    un orifice de refoulement (38) qui est en communication avec la partie haute pression,
    un espace entre une surface périphérique interne (32b) du piston (32) et une surface périphérique externe (31b) de la partie excentrique (31a) du vilebrequin (31) étant défini comme un premier espace de palier (c1) et
    un deuxième espace de palier (c2) étant formé entre la surface périphérique interne (34a) du palier supérieur (34) et l'arbre principal (31c) du vilebrequin (31) par le fait d'amener le palier supérieur (34) en butée contre l'arbre principal (31c) du vilebrequin (31) dans une direction s'écartant de l'aube (33) de l'angle θ,
    caractérisé en ce que
    si un espace, formé entre une surface périphérique externe du piston (32a) et une surface périphérique interne du cylindre (30a) dans un état dans lequel la partie excentrique (31a) est disposée en une position d'un angle de vilebrequin prédéterminé par rapport à une position de l'aube (33) et le piston (32) est amené à venir en butée contre une position la plus excentrique de la partie excentrique (31a) et une surface périphérique interne (34a) du palier supérieur (34) est amenée à venir en butée contre une surface périphérique externe d'arbre principal (31c) du vilebrequin (31) lorsque le compresseur rotatif est assemblé, est défini comme δ,
    une valeur minimale δmin de l'espace δ est définie à un angle de vilebrequin sur un côté opposé à une direction de charge maximale qui agit sur le piston (32) dans l'angle de vilebrequin lorsqu'une différence de pression entre le côté de partie haute pression et le côté de partie basse pression est maximale pendant le fonctionnement du compresseur rotatif, lorsque le compresseur rotatif est assemblé et
    l'espace minimal δmin, le premier espace de palier (c1) et le deuxième espace de palier (c2) sont disposés sur une ligne de fantôme s'écartant de l'aube (33) par l'angle θ.
  2. Compresseur rotatif selon la revendication 1, où
    lorsque le compresseur rotatif est assemblé,
    le premier espace de palier (c1) est formé entre le piston (32) et la partie excentrique (31a),
    le deuxième espace de palier (c2) est formé entre le palier supérieur (34) et l'arbre principal (31c),
    dans chacun des angles de vilebrequin,
    le vilebrequin (31) est déplacé par le premier espace de palier (c1) dans une direction de charge au moment du fonctionnement,
    le piston (32) est déplacé par le deuxième espace de palier (c2) dans la direction de charge au moment du fonctionnement, lorsqu'un espace minimal formé entre une périphérie externe du piston (32) et une ligne fantôme d'une périphérie interne du cylindre (30) est défini comme β,
    une direction de la valeur minimale δmin est définie de telle sorte qu'un espace minimal β à un angle de vilebrequin 45° et un espace minimal β à un angle de vilebrequin 225° sont sensiblement égaux l'un à l'autre.
  3. Compresseur rotatif selon la revendication 1 ou 2, comprenant en outre une chambre de compression (39) supplémentaire.
  4. Compresseur rotatif selon l'une quelconque des revendications 1 à 3, la valeur minimale δmin étant de 5 µm à 10 µm.
EP13797726.0A 2012-06-01 2013-05-31 Compresseur rotatif Active EP2857688B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012125719 2012-06-01
PCT/JP2013/003446 WO2013179677A1 (fr) 2012-06-01 2013-05-31 Compresseur rotatif

Publications (3)

Publication Number Publication Date
EP2857688A1 EP2857688A1 (fr) 2015-04-08
EP2857688A4 EP2857688A4 (fr) 2015-05-27
EP2857688B1 true EP2857688B1 (fr) 2020-04-29

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EP (1) EP2857688B1 (fr)
JP (1) JP6350916B2 (fr)
CN (1) CN103782037B (fr)
WO (1) WO2013179677A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107061273B (zh) * 2016-12-01 2019-09-06 广东美芝制冷设备有限公司 旋转式压缩机

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010116782A (ja) * 2008-11-11 2010-05-27 Daikin Ind Ltd 流体機械

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
JPS5514278B2 (fr) * 1972-07-26 1980-04-15
JPS61142389A (ja) * 1984-12-14 1986-06-30 Daikin Ind Ltd ロ−タリ−圧縮機におけるクランク軸の芯出し方法
JPH0751951B2 (ja) * 1987-11-24 1995-06-05 ダイキン工業株式会社 回転式圧縮機
JP3490950B2 (ja) * 2000-03-15 2004-01-26 三洋電機株式会社 ２シリンダ型２段圧縮式ロータリーコンプレッサ
JP4019620B2 (ja) * 2000-09-22 2007-12-12 松下電器産業株式会社 密閉型圧縮機
JP3616056B2 (ja) * 2002-01-23 2005-02-02 三菱重工業株式会社 ロータリ圧縮機
JP2005240564A (ja) * 2004-02-24 2005-09-08 Mitsubishi Electric Corp ロータリ圧縮機
JP2006152950A (ja) * 2004-11-30 2006-06-15 Sanyo Electric Co Ltd 多段圧縮式ロータリコンプレッサ
WO2010013375A1 (fr) * 2008-07-28 2010-02-04 パナソニック株式会社 Compresseur rotatif

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010116782A (ja) * 2008-11-11 2010-05-27 Daikin Ind Ltd 流体機械

Also Published As

Publication number Publication date
CN103782037A (zh) 2014-05-07
WO2013179677A1 (fr) 2013-12-05
CN103782037B (zh) 2016-01-20
EP2857688A1 (fr) 2015-04-08
JP6350916B2 (ja) 2018-07-04
EP2857688A4 (fr) 2015-05-27
JPWO2013179677A1 (ja) 2016-01-18

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