WO2013080519A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
WO2013080519A1
WO2013080519A1 PCT/JP2012/007594 JP2012007594W WO2013080519A1 WO 2013080519 A1 WO2013080519 A1 WO 2013080519A1 JP 2012007594 W JP2012007594 W JP 2012007594W WO 2013080519 A1 WO2013080519 A1 WO 2013080519A1
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WO
WIPO (PCT)
Prior art keywords
vane
chamber side
contact surface
compression chamber
suction chamber
Prior art date
Application number
PCT/JP2012/007594
Other languages
English (en)
Japanese (ja)
Inventor
大輔 船越
健 苅野
裕文 吉田
鶸田　晃
信吾 大八木
啓晶 中井
竜一 大野
飯田　登
Original Assignee
パナソニック株式会社
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 パナソニック株式会社 filed Critical パナソニック株式会社
Priority to CN201280042991.9A priority Critical patent/CN103765012A/zh
Publication of WO2013080519A1 publication Critical patent/WO2013080519A1/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
    • 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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • 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
    • F04C27/008—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids for other than working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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

Definitions

  • the present invention relates to a rotary compressor used for an air conditioner, a refrigerator, a blower, a water heater, and the like.
  • a compressor which sucks in gas refrigerant evaporated in an evaporator, compresses the sucked gas refrigerant to a pressure necessary for condensing, and sends out high temperature / high pressure gas refrigerant. It is done.
  • a rotary compressor is known as one of such compressors.
  • a motor and a compression mechanism are connected by a crankshaft and housed in a closed container.
  • the compression mechanism portion is composed of a cylinder, an upper bearing, a lower bearing, and a piston. Both end faces of the cylinder are closed by the end plate of the upper bearing and the end plate of the lower bearing.
  • the crankshaft is supported by the upper bearing and the lower bearing.
  • the eccentric part of the crankshaft is disposed between the upper bearing and the lower bearing.
  • the piston is fitted to the eccentric part of the crankshaft.
  • a compression space is formed by the cylinder, the upper bearing, the lower bearing, and the piston.
  • a vane groove is formed in the cylinder, and a vane is disposed in the vane groove.
  • the vane reciprocates following the eccentric rotation of the piston and divides the compression space into a suction chamber and a compression chamber.
  • the crankshaft is provided with an oil hole in the axial portion, and a wall portion of the crankshaft with respect to the upper bearing and the lower bearing is provided with an oil supply hole communicating with the oil hole. Further, the wall portion of the eccentric portion is provided with a feed hole communicating with the oil hole, and an oil groove is formed on the outer peripheral surface of the eccentric portion.
  • the cylinder is provided with a suction port for sucking the refrigerant gas into the suction chamber.
  • the upper bearing is provided with a discharge port for discharging the refrigerant gas from the compression chamber.
  • the discharge port is formed as a circular hole in a plan view penetrating the upper bearing, and the top surface of the discharge port is provided with a discharge valve which is released when a predetermined pressure is received.
  • the discharge valve is covered by a cup muffler.
  • the suction chamber sucks the refrigerant gas from the suction port by the expansion of the space, and the compression chamber compresses the refrigerant gas to a predetermined pressure or more by the contraction of the space.
  • the compressed refrigerant gas opens the discharge valve, flows out from the discharge port, and is discharged into the closed container via the cup muffler.
  • the vane groove has a spring hole for housing a spring which presses the vane against the piston at the start of the compressor, and the spring hole is filled with lubricating oil or high pressure refrigerant gas. Lubricant oil and high-pressure gas leak into the suction chamber and the compression chamber from the spring hole through the gap between the vane and the vane groove, and the efficiency is lowered.
  • FIG. 11 is a plan view of relevant parts showing a cylinder of a conventional rotary compressor. In FIG. 11, a portion of the cylinder 130 and a portion of the piston 132 disposed in the cylinder 130 are shown. In the cylinder 130, a vane groove 130b is formed.
  • the vanes 133 are disposed in the vane groove 130b.
  • An oil reservoir groove 133 a is formed in the vane 133.
  • a plurality of oil reservoir grooves 133 a are formed at arbitrary intervals in the direction intersecting with the sliding direction of the vanes 133.
  • An oil film is sufficiently formed between the vanes 133 and the vane groove 130b by the oil reservoir groove 133a. The oil film exerts a labyrinth sealing effect, and can prevent leakage of lubricating oil, refrigerant gas and the like (see, for example, Patent Document 1).
  • Patent Document 1 Although the suppression of leakage of lubricating oil, refrigerant gas and the like can be expected by the labyrinth seal effect, when the suction chamber and the compression chamber have the same pressure, the gap between the vane 133 and the vane groove 130b is completely I can not seal.
  • the present invention solves the above-mentioned conventional problems, and in a state where the pressure difference between the suction chamber and the compression chamber is less than a predetermined pressure, the refrigerant gas and the lubricating oil pass through the gap between the vane and the vane groove to form the suction chamber. And a rotary compressor that suppresses leakage into the compression chamber.
  • the present invention provides a cylinder, an eccentric portion of a shaft disposed in the cylinder, a piston fitted to the eccentric portion, and the cylinder following an eccentric rotation of the piston. And reciprocate in a vane groove provided in the cylinder to divide the inside of the cylinder into a suction chamber and a compression chamber, and the vane has a suction chamber side contacting the vane groove on the suction chamber side.
  • a rotary having a contact surface and a compression chamber side contact surface in contact with the vane groove on the compression chamber side, wherein lubricating oil is supplied from an oil reservoir to the suction chamber side contact surface and the compression chamber side contact surface.
  • a differential pressure generating mechanism which is a compressor, wherein a pressure applied to the contact surface on the compression chamber side is larger than that on the contact surface on the suction chamber side when the pressure difference between the suction chamber and the compression chamber is less than a predetermined pressure.
  • Row characterized by being formed It is a re-compressor.
  • the vane is inclined toward the suction chamber
  • the vanes and the vane grooves are brought into contact with each other to suppress the refrigerant gas and the lubricating oil leaking into the suction chamber and the compression chamber, thereby improving the efficiency.
  • the oil can be easily held between the vanes and the vane grooves to improve the sliding condition, and the vanes can be prevented from fluttering in the vane grooves, thereby improving the reliability.
  • the principal part top view which shows the relationship of a cylinder and a vane when the piston of a comparative example is the vane top dead center vicinity
  • Top view showing the relationship of Graph for explaining the efficiency of the contact area ratio difference between the vanes and the vane grooves of the rotary compressor in the embodiment of the present invention
  • A) Principal part top view which shows cylinder of rotary compressor in other embodiment of this invention (b) Principal part side view seen from A direction and B direction shown to the figure
  • the motor and the compression mechanism are connected by a crankshaft and accommodated in the closed container, and the compression mechanism is fitted to the cylinder, the eccentric portion of the shaft disposed in the cylinder, and the eccentric portion Provided on the suction chamber side of the cylinder, which reciprocates in the vane groove provided in the cylinder following the eccentric rotation of the piston, and which divides the inside of the cylinder into a suction chamber and a compression chamber, and And the suction chamber side contact surface contacting the vane groove on the suction chamber side and the compression chamber side contact surface contacting the vane groove on the compression chamber side.
  • a rotary compressor in which lubricating oil is supplied from an oil reservoir to the suction chamber side contact surface and the compression chamber side contact surface, and a pressure difference between the suction chamber and the compression chamber is less than a predetermined pressure.
  • the suction chamber side contact surface A rotary compressor, wherein a pressure applied to the reduced chamber side contact surface to form a larger differential pressure generating mechanism.
  • the vane and the vane groove can be brought into contact to improve the sealing performance, and the refrigerant gas and the lubricating oil can suppress the leakage into the suction chamber and the compression chamber through the gap between the vane and the vane groove. Further, since the differential pressure generating mechanism is in communication with the oil reservoir, the lubricating oil is easily held between the vanes and the vane grooves, and the reliability is also improved.
  • the differential pressure generating mechanism is configured such that the contact area of the suction chamber side contact surface with the vane groove is the vane on the compression chamber side contact surface. It is a rotary compressor characterized in that it is larger than the contact area with the groove.
  • the differential pressure generating mechanism is characterized in that a counterbore in communication with the vane groove is provided in a direction orthogonal to the vane groove. Machine. By this configuration, it can be easily processed by a drill hole, an end mill or the like.
  • a suction chamber side counterbore in communication with the vane groove in the suction chamber side and a vane groove in communication with the compression chamber side
  • a compression chamber side counterbore is provided.
  • the height of the cylinder is about 4 to 6 times the width of the vane groove.
  • the pressure balance in the thickness direction (the contact surface on the suction chamber side and the contact surface on the compression chamber side) on the upper shaft side and the lower shaft side of the vane is lost, leading to a reduction in efficiency.
  • the diameter of the drill hole can be made larger than the vane groove width, so it becomes easy to penetrate in the axial direction in one drilling.
  • the diameter of the drill hole can be increased, the tool life can be extended and the workability can be improved.
  • a ratio of a contact area of the contact surface on the compression chamber side with the vane groove on a contact area of the suction chamber side contact surface with the vane groove. Is 70% or more.
  • the gap between the vane and the compression chamber side of the vane groove is substantially filled with high pressure, and the differential pressure generating mechanism does not function, so the pressure distribution becomes equivalent to that of a common rotary compressor, and the vane and vane groove There is no strong sliding and the reliability does not deteriorate.
  • a single refrigerant comprising a refrigerant based on a hydrofluoroolefin having carbon and carbon-carbon double bond as a working fluid, or A mixed refrigerant containing the refrigerant is used.
  • This refrigerant has a low suction density, for example, it needs about 1.7 times the amount of circulation to achieve the same capacity as R410A, the difference between high and low pressure becomes large, and the influence of leakage of lubricating oil and refrigerant gas is large It is possible to more effectively improve the efficiency of the compressor.
  • this refrigerant since this refrigerant has no ozone destruction and a low global warming potential, it can contribute to the configuration of a climate-friendly air conditioning cycle.
  • FIG. 1 is a longitudinal sectional view of a rotary compressor according to an embodiment of the present invention.
  • FIG. 2 is an enlarged view of the compression mechanism portion in the embodiment of the present invention.
  • the motor 2 and the compression mechanism 3 are connected by a crankshaft 31 and accommodated in the sealed container 1.
  • a discharge pipe 5 is provided at the upper part of the closed container 1.
  • An oil reservoir 6 is formed in the lower part of the closed container 1. Since the compressed refrigerant gas is discharged in the closed container 1, the discharge pressure acts on the oil reservoir 6.
  • the motor 2 is composed of a stator 22 and a rotor 24.
  • the compression mechanism portion 3 includes a cylinder 30, an upper bearing 34, a lower bearing 35, and a piston 32. Both end surfaces of the cylinder 30 are closed by the end plate of the upper bearing 34 and the end plate of the lower bearing 35.
  • the crankshaft 31 is supported by the upper bearing 34 and the lower bearing 35.
  • the eccentric portion 31 a of the crankshaft 31 is disposed between the upper bearing 34 and the lower bearing 35.
  • the piston 32 is fitted to the eccentric portion 31 a of the crankshaft 31.
  • a compression space 39 is formed by the cylinder 30, the upper bearing 34, the lower bearing 35, and the piston 32.
  • a suction port 40 is formed in the cylinder 30.
  • An oil hole 41 is provided in the crankshaft 31 in the axial direction.
  • oil supply holes 42 and 43 respectively communicating with the oil hole 41 are provided.
  • the oil supply hole 44 communicating with the oil hole 41 is provided in the wall portion of the eccentric portion 31a, and the oil groove 45 is formed on the outer peripheral surface of the eccentric portion 31a. Lubricating oil is supplied to the oil hole 41 from the oil reservoir 6.
  • the discharge port 38 is formed as a circular hole in a plan view penetrating the upper bearing 34, and the top surface of the discharge port 38 is provided with a discharge valve 36 which is released when receiving a predetermined pressure.
  • the discharge valve 36 is covered by a cup muffler 37.
  • the suction chamber 39a sucks the refrigerant gas from the suction port 40 by the expansion of the space, and the compression chamber 39b compresses the refrigerant gas to a predetermined pressure or more by the contraction of the space.
  • the compressed refrigerant gas opens the discharge valve 36, flows out from the discharge port 38, and is discharged into the closed container 1 via the cup muffler 37.
  • the space 46 is surrounded by the eccentric portion 31 a, the upper bearing 34, and the inner peripheral surface of the piston 32.
  • the space 47 is surrounded by the eccentric portion 31 a, the lower bearing 35, and the inner peripheral surface of the piston 32.
  • the lubricating oil leaks into the space 46 from the oil hole 41 through the oil supply hole 42.
  • the lubricating oil leaks into the space 47 from the oil hole 41 through the oil supply hole 43. Therefore, since the discharge pressure is applied to the spaces 46 and 47, the spaces 46 and 47 are higher than the pressure in the compression space 39.
  • the height of the cylinder 30 is set to be slightly higher than the height of the piston 32 so that the piston 32 can slide therein. As a result, there are gaps between the end face of the piston 32 and the upper bearing 34 and between the end face of the piston 32 and the lower bearing 35. Therefore, the lubricating oil leaks from the spaces 46 and 47 to the compression space 39 through the gap.
  • FIG. 3A is a plan view of relevant parts showing a cylinder of the rotary compressor according to the present embodiment.
  • FIG.3 (b) is the principal part side view seen from the A direction and B direction which are shown to the figure (a).
  • a vane groove 30b is formed in the cylinder 30, a vane groove 30b is formed.
  • the vane 33 shown in FIG. 1 and FIG. 2 is disposed in the vane groove 30b.
  • the inside of the cylinder 30, ie, the compression space 39 forms a suction chamber 39a and a compression chamber 39b with the vane groove 30b interposed therebetween.
  • the suction port 40 communicates with the suction chamber 39a.
  • the spring hole 30c is a hole formed from the outer peripheral surface of the cylinder 30, and is formed in the same direction as the vane groove 30b.
  • a spring 30d shown in FIG. 1 and FIG. 2 is disposed in the spring hole 30c.
  • the spring 30 d presses the vanes 33 in the direction of the piston 32.
  • the spring hole 30c is filled with high pressure refrigerant gas and lubricating oil. Accordingly, the discharge pressure of the refrigerant is applied to the spring hole 30c.
  • FIG. 4A is a plan view of relevant parts showing the relationship between the cylinder 30 and the vane 33 when the piston 32 is located near the top dead center of the vane 33.
  • FIG. 4B is a plan view of relevant parts showing the relationship between the cylinder 30 and the vanes 33 when the compression chamber 39 b has reached a predetermined pressure.
  • the vane 33 has a suction chamber side contact surface 33a in contact with the vane groove 30c on the suction chamber 39a side and a compression chamber side contact surface 33b in contact with the vane groove 30c on the compression chamber 39b side. It is formed.
  • the lubricating oil from the oil reservoir 6 is supplied to the suction chamber side contact surface 33a and the compression chamber side contact surface 33b.
  • FIG.5 (a) is a principal part top view which shows the cylinder of the rotary compressor in a comparative example.
  • FIG.5 (b) is the principal part side view seen from the A direction and B direction which are shown to the figure (a).
  • symbol is attached
  • FIG. 6A is a plan view of relevant parts showing the relationship between the cylinder 130 and the vane 33 when the piston 32 is located near the top dead center of the vane 33.
  • 6B is a plan view of relevant parts showing the relationship between the cylinder 130 and the vanes 33 when the compression chamber 39 b has reached a predetermined pressure.
  • the spring holes 130c in the comparative example have the same length on the suction chamber 39a side and the compression chamber 39b side. Accordingly, the contact area of the suction chamber side contact surface 33 a of the vane 33 with the vane groove 30 b and the contact area of the compression chamber side contact surface 33 b of the vane 33 with the vane groove 30 b become equal.
  • the differential pressure generation mechanism in the present embodiment will be described below.
  • the compression chamber side spring hole 30e located on the compression chamber 39b side is made longer than the suction chamber side spring hole 30f located on the suction chamber 39a side. ing.
  • the contact area of the suction chamber side contact surface 33 a of the vane 33 with the vane groove 30 b is larger than the contact area of the compression chamber side contact surface 33 b of the vane 33 with the vane groove 30 b.
  • the hatched area in FIG. 3B is the contact surface between the vanes 33 and the vane grooves 30b.
  • the spring hole 30c is subjected to a discharge pressure. ing. Therefore, by making the contact area with the vane groove 30b in the suction chamber side contact surface 33a larger than the contact area with the vane groove 30b in the compression chamber side contact surface 33b, the compression chamber side than the suction chamber side contact surface 33a The pressure applied to the contact surface 33b is increased, and the pressure difference can tilt the vanes 33.
  • vanes 33 and the vane grooves 30b are brought into contact with each other to improve the sealing performance, and the refrigerant gas and the lubricating oil are prevented from leaking to the compression space 39 from the suction chamber side contact surface 33a and the compression chamber side contact surface 33b of the vane 33 it can.
  • the lubricating oil is easily held between the vanes 33 and the vane grooves 30b, and the reliability is also improved.
  • the compression chamber 39b has reached a predetermined pressure. Therefore, the oil reservoir 6 and the compression chamber 39b have substantially the same pressure. Therefore, the gap between the compression chamber side contact surface 33b of the vane 33 and the surface of the vane groove 30b on the compression chamber 39b side is substantially filled with high pressure. This is equivalent to the pressure distribution (see FIG. 6) of the vanes 33 and the vane grooves 30b of a general rotary compressor, so the vanes 33 and the vane grooves 30b do not slide strongly, and the reliability is deteriorated. do not do.
  • the ratio of the contact area of the compression chamber side contact surface 33b with the vane groove 30b to the contact area of the suction chamber side contact surface 33a with the vane groove 30b is preferably 70% or more.
  • FIG. 8 is a cylinder of a rotary compressor according to another embodiment of the present invention. Only the difference from the above embodiment will be described, and the description of the same configuration as the above embodiment will be omitted.
  • FIG. 8 (a) is a plan view of relevant parts showing a cylinder of a rotary compressor according to another embodiment of the present invention
  • FIG. 8 (b) is a view from directions A and B shown in FIG. It is a principal part side view.
  • a counterbore 60 communicating with the vane groove 30 b may be provided in the direction orthogonal to the vane groove 30 b as a differential pressure generation mechanism.
  • the contact area between the suction chamber side contact surface 33a of the vane 33 and the suction chamber 39a side surface of the vane groove 30b, and the compression chamber side contact surface 33b of the vane 33 and the compression chamber 39b side surface of the vane groove 30b Contact area can be changed. That is, as shown in FIG. 8B, by providing the counterbore 60 as a differential pressure generation mechanism, the contact area of the vane 33 on the suction chamber side contact surface 33a with the vane groove 30b is the contact on the compression chamber side of the vane 33. It becomes larger than the contact area with the vane groove
  • the shaded area in FIG. 8B is the contact surface between the vanes 33 and the vane grooves 30b.
  • a differential pressure generating mechanism that makes the compression chamber side spring hole 30 e located on the compression chamber 39 b side longer than the suction chamber side spring hole 30 f located on the suction chamber 39 a side.
  • a differential pressure generating mechanism by the counterbore 60 was provided.
  • a differential pressure generating mechanism by the counterbore 60 is provided together with a differential pressure generating mechanism for making the compression chamber side spring hole 30e located on the compression chamber 39b longer than the suction chamber side spring hole 30f located on the suction chamber 39a. It is also good.
  • the counterbore 60 can be easily processed using a drill or an end mill.
  • FIG. 9 shows a cylinder of a rotary compressor according to still another embodiment of the present invention. Only the difference from the above embodiment will be described, and the description of the same configuration as the above embodiment will be omitted.
  • the intersecting portion (edge portion) of the counterbore 60 and the vane groove 30b has an acute angle, and the oil lubricity deteriorates. Therefore, it is preferable to position the center of the counterbore 60 in the vane groove 30b and to make the intersection of the counterbore 60 and the vane groove 30b an obtuse angle (see FIG. 8).
  • FIG. 10 shows a cylinder of a rotary compressor according to still another embodiment of the present invention. Only the difference from the above embodiment will be described, and the description of the same configuration as the above embodiment will be omitted.
  • 10A is a plan view of relevant parts showing a cylinder of a rotary compressor according to still another embodiment of the present invention
  • FIG. 10B is viewed from directions A and B shown in FIG. It is a principal part side view.
  • a suction chamber side counterbore 60a communicating with the vane groove 30b on the suction chamber 39a side and a compression chamber side counterbore 60b communicating with the vane groove 30b on the compression chamber 39b side may be provided. .
  • the height of the cylinder 30 is about 4 to 6 times the width of the vane groove 30b.
  • the pressure balance in the thickness direction on the upper shaft side 34a and the lower shaft side 35a of the vane 33 is broken, leading to a reduction in efficiency.
  • the diameter of the drill hole can be made larger than the width of the vane groove 30b. Become.
  • the diameter of the drill hole can be increased, the tool life can be extended and the workability can be improved.
  • the rotary compressor includes a vane coupled to the outer periphery of the piston in a protruding manner to divide the compression chamber into a low pressure side and a high pressure side, and a swinging bush that swingably supports the vane.
  • a vane coupled to the outer periphery of the piston in a protruding manner to divide the compression chamber into a low pressure side and a high pressure side
  • a swinging bush that swingably supports the vane.
  • a single refrigerant composed of a refrigerant having a hydrofluoroolefin having a double bond between carbon and carbon as a base component or a mixed refrigerant containing the refrigerant is used.
  • This refrigerant has a low suction density, and, for example, requires about 1.7 times the amount of circulation to achieve the same capacity as R410A. Therefore, the difference between the high pressure and the low pressure in the compression becomes large, and the influence of the leakage of the lubricating oil and the refrigerant gas becomes large, so that the efficiency of the compressor can be more effectively improved.
  • this refrigerant since this refrigerant has no ozone destruction and a low global warming potential, it can contribute to the configuration of a climate-friendly air conditioning cycle.
  • a mixed refrigerant may be used as the working refrigerant, in which the hydrofluoroolefin is tetrafluoropropene (HFO 1234yf) and the hydrofluorocarbon is difluoromethane (HFC 32).
  • a mixed refrigerant may be used as the working refrigerant, in which the hydrofluoroolefin is tetrafluoropropene (HFO 1234 yf) and the hydrofluorocarbon is pentafluoroethane (HFC 125).
  • a mixed refrigerant consisting of three components, in which the hydrofluoroolefin is tetrafluoropropene (HFO 1234yf) and the hydrofluorocarbon is pentafluoroethane (HFC 125) or difluoromethane (HFC 32), may be used as the working refrigerant.
  • HFO 1234yf tetrafluoropropene
  • HFC 125 pentafluoroethane
  • difluoromethane HFC 32
  • the rotary compressor of the present invention is provided with a differential pressure generating mechanism that presses the vanes in the direction of the suction chamber side of the vane groove and communicates with the oil reservoir.
  • a differential pressure generating mechanism that presses the vanes in the direction of the suction chamber side of the vane groove and communicates with the oil reservoir.

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

Abstract

L'invention porte sur un compresseur rotatif qui comprend un cylindre (30), une partie excentrique (31a) d'un arbre, un piston (32) et une palette (33), la surface de contact côté chambre d'entrée (33a) et une surface de contact côté chambre de compression (33b) sont formées dans la palette (33), de l'huile lubrifiante est acheminée à la surface de contact côté chambre d'entrée (33a) et à la surface de contact côté chambre de compression (33b), en arrivant d'un accumulateur d'huile (6), et un mécanisme de création de différence de pression, qui a pour effet que la pression ajoutée à la surface de contact côté chambre de compression (33b) est plus grande que celle de la surface de contact côté chambre d'entrée (33a), est formé dans un état dans lequel la différence de pression entre une chambre d'entrée (39a) et une chambre de compression (39b) est égale ou inférieure à une pression prédéterminée, de sorte que le gaz frigorigène et l'huile de lubrification sont empêchés de s'échapper dans la chambre d'entrée (39a) et dans la chambre de compression (39b) à travers une fente entre la palette (33) et une rainure de palette (30b).
PCT/JP2012/007594 2011-11-28 2012-11-27 Compresseur rotatif WO2013080519A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201280042991.9A CN103765012A (zh) 2011-11-28 2012-11-27 回转式压缩机

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JP2011258967 2011-11-28
JP2011-258967 2011-11-28

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WO2013080519A1 true WO2013080519A1 (fr) 2013-06-06

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WO (1) WO2013080519A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015105574A (ja) * 2013-11-28 2015-06-08 三菱電機株式会社 ロータリー圧縮機
CN106930943A (zh) * 2015-12-29 2017-07-07 珠海凌达压缩机有限公司 压缩机、泵体组件及其气缸

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Publication number Priority date Publication date Assignee Title
JPS56147388U (fr) * 1980-04-03 1981-11-06
JPS6186590U (fr) * 1984-11-13 1986-06-06
JPS63201390A (ja) * 1987-02-18 1988-08-19 Matsushita Refrig Co 回転型圧縮機
JP2003307191A (ja) * 2002-04-12 2003-10-31 Toshiba Kyaria Kk ロータリコンプレッサ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS56147388U (fr) * 1980-04-03 1981-11-06
JPS6186590U (fr) * 1984-11-13 1986-06-06
JPS63201390A (ja) * 1987-02-18 1988-08-19 Matsushita Refrig Co 回転型圧縮機
JP2003307191A (ja) * 2002-04-12 2003-10-31 Toshiba Kyaria Kk ロータリコンプレッサ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015105574A (ja) * 2013-11-28 2015-06-08 三菱電機株式会社 ロータリー圧縮機
CN106930943A (zh) * 2015-12-29 2017-07-07 珠海凌达压缩机有限公司 压缩机、泵体组件及其气缸

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JPWO2013080519A1 (ja) 2015-04-27

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