WO2012001966A1 - 回転式圧縮機 - Google Patents
回転式圧縮機 Download PDFInfo
- Publication number
- WO2012001966A1 WO2012001966A1 PCT/JP2011/003717 JP2011003717W WO2012001966A1 WO 2012001966 A1 WO2012001966 A1 WO 2012001966A1 JP 2011003717 W JP2011003717 W JP 2011003717W WO 2012001966 A1 WO2012001966 A1 WO 2012001966A1
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- WO
- WIPO (PCT)
- Prior art keywords
- shaft
- piston
- peripheral surface
- vane
- eccentric portion
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/04—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 of internal-axis type
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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
- F04C18/32—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
- F04C18/324—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 both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the inner member and reciprocating with respect to the outer member
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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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
- F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
- F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
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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
- F04C2240/00—Components
- F04C2240/60—Shafts
Definitions
- the present invention relates to a rotary compressor incorporated in a refrigerator, an air conditioner or the like.
- the rotary compressor includes a sealed container 1, an electric motor part (not shown), and a compression mechanism part A connected to the electric motor part via the shaft 4. It is stored and the bottom of the sealed container is an oil reservoir.
- the compression mechanism portion A is provided with a cylinder 5, a main bearing 7 and a sub-bearing 8 that are fastened to both end surfaces of the cylinder 5 to form a cylinder chamber 6, and an eccentric portion 41 between the main bearing 7 and the sub-bearing 8.
- the tip portion 11A of the vane 11 is swingably fitted and connected to a fitting portion 9A formed on the piston 9, so that the suction chamber 12 and the compression chamber 13 partitioned by the vane 11 in the cylinder chamber 6 are connected. To form.
- the volume of the suction chamber 12 and the compression chamber 13 is changed by the revolving motion of the piston 9 accompanying the rotation of the shaft 4 and the reciprocating motion of the vane 11, and the working refrigerant sucked into the suction chamber 12 from the suction port 17 by this volume change. It is compressed to a high temperature and high pressure, and is discharged from the compression chamber 13 through the discharge port 18 and the discharge muffler chamber 19 into the sealed container 1.
- the oil in the oil reservoir is sucked by the oil pump provided at the lower end of the shaft 4 and passes through the hollow hole provided in the shaft 4, so that the sliding surface in the compression mechanism portion, for example, the eccentric portion 41 of the shaft 4. And between the outer peripheral surface of the piston 9 and the inner peripheral surface of the cylinder 5 for lubrication (see, for example, Patent Document 1).
- the area of the sliding surface of the eccentric portion 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 is reduced.
- the viscous force of the oil acting between the eccentric portion 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 is reduced. It is desirable to keep it to a minimum.
- the piston 9 is inserted from the side of the auxiliary bearing 8 and fitted into the eccentric portion 41 of the shaft 4, so that the auxiliary shaft inserted into the auxiliary bearing 8 is inserted.
- the shaft diameter of the portion 43 is made smaller than the shaft diameter of the main shaft portion 42 fitted into the main bearing 7, and the outer peripheral surface of the eccentric portion 41 of the shaft 4 on the side opposite to the eccentric shaft is fitted into the sub-bearing 8. It is made to be the same as the outer peripheral surface of, or radially outward.
- the shaft diameter ⁇ D1 of the eccentric portion 41 of the shaft 4 is ⁇ D3 and the eccentric amount of the eccentric portion 41 is E
- the shaft diameter of the auxiliary shaft portion 43 fitted into the auxiliary bearing 8 is ⁇ D1 ⁇ ⁇ D3 + 2 ⁇ E
- the shaft diameter ⁇ D1 of the eccentric portion 41 must be set so as to satisfy the formula (1).
- the shaft diameter ⁇ D2 of the main shaft portion 42 is larger than the shaft diameter of the sub shaft portion 43, the outer peripheral surface of the eccentric portion 41 on the side opposite to the eccentric shaft is recessed from the outer peripheral surface of the main shaft portion 42. .
- the shaft diameter of the eccentric portion 41 is reduced to reduce the area of the sliding surface of the eccentric portion 41.
- the shaft of the eccentric portion 41 is the same.
- the shaft diameter of the sub-shaft portion 43 is further reduced. As a result, the strength required particularly for the sub-shaft portion 43 cannot be obtained, and the reliability is lowered.
- the present invention solves the above-mentioned conventional problems, and by reducing the shaft diameter of the eccentric portion while ensuring the strength reliability of the shaft, the sliding loss caused by the reciprocating motion of the vane in the vane groove
- An object of the present invention is to provide a rotary compressor with a reduced input loss.
- a rotary compressor includes a cylinder, a main bearing and a sub-bearing that are fastened to both end surfaces of the cylinder to form a cylinder chamber, and a main bearing and a sub-bearing.
- a shaft provided with an eccentric portion therebetween, a piston fitted to the eccentric portion of the shaft, a vane dividing the cylinder chamber into a suction chamber and a compression chamber, and a vane groove formed in the cylinder for reciprocating movement of the vane.
- the outer peripheral surface of the eccentric portion of the shaft on the side of the eccentric shaft is recessed from the outer peripheral surface of the main shaft portion that is fitted into the main bearing and the outer peripheral surface of the sub shaft portion that is fitted into the sub bearing.
- escape means for assembling the piston to the shaft is provided in the eccentric part of the peripheral surface and the shaft.
- the shaft diameter of the eccentric portion can be reduced while ensuring the strength reliability of the shaft, the area of the sliding surface of the eccentric portion of the shaft and the inner peripheral surface of the piston can be reduced, and further the eccentric portion of the shaft Thus, the sliding speed of the inner peripheral surface of the piston can be reduced. That is, when the shaft rotates, it becomes possible to reduce the viscous force of oil acting between the eccentric part of the shaft and the inner peripheral surface of the piston, and this viscous force acts on the piston in the rotational direction of the shaft.
- the rotation moment around the center of the eccentric part of the shaft can be reduced, and when the vane reciprocates in the vane groove, the vane acts on the two contacts as a reaction force of the force that supports the rotation moment at the tip of the vane.
- the frictional resistance with the groove can be reduced. Therefore, it is possible to provide a rotary compressor in which the sliding loss generated by the reciprocating motion of the vane in the vane groove is reduced and the input loss is small.
- FIG. 1 is a longitudinal sectional view of a rotary compressor according to Embodiment 1 of the present invention.
- 2 is a cross-sectional view showing a compression mechanism of the rotary compressor of FIG. 3A to 3E are assembly process diagrams showing the assembly of the shaft and piston of the rotary compressor of FIG. 4 is an enlarged perspective view showing a piston of the rotary compressor of FIG.
- FIG. 5 is a surface development view showing the inner peripheral surface of the piston of the rotary compressor of FIG.
- FIGS. 6A to 6F are schematic diagrams for explaining the operation of the rotary compressor of FIG.
- FIG. 7 is a longitudinal sectional view showing a conventional rotary compressor.
- FIG. 8 is a cross-sectional view showing a compression mechanism of a conventional rotary compressor
- FIG. 9 is a schematic diagram for explaining the operation of the main part of a conventional rotary compressor.
- a first invention includes a cylinder, a main bearing and a sub-bearing that are fastened to both end surfaces of the cylinder to form a cylinder chamber, a shaft having an eccentric portion between the main bearing and the sub-bearing, and an eccentric portion of the shaft And a vane that divides the cylinder chamber into a suction chamber and a compression chamber, and a vane groove formed in the cylinder for reciprocating movement of the vane.
- a rotary compressor configured to be connected, wherein an outer peripheral surface of the eccentric portion of the shaft on the side opposite to the eccentric shaft is inserted into a main shaft portion and a sub shaft portion inserted into a sub bearing.
- escape means for assembling the piston to the shaft are provided on the inner peripheral surface of the piston and the eccentric portion of the shaft.
- the shaft diameter of the eccentric portion can be reduced while ensuring the strength reliability of the shaft, so that the area of the sliding surface between the eccentric portion of the shaft and the inner peripheral surface of the piston can be reduced, and further the eccentric portion of the shaft and the piston It becomes possible to reduce the sliding speed of the inner peripheral surface. That is, when the shaft rotates, it is possible to reduce the viscous force of the oil acting on the eccentric part of the shaft and the inner peripheral surface of the piston, and this viscous force acts on the piston in the direction of rotation of the shaft.
- the rotational moment around the center of the eccentric portion can be reduced, and when the vane reciprocates in the vane groove, the vane groove acting on the two contacts as a reaction force of the force that the tip of the vane supports this rotational moment Can reduce the frictional resistance.
- the thrust load acting on the shaft is supported by the end face of either the main bearing or the sub-bearing by sliding with the end face of the eccentric portion of the shaft. It is comprised so that it may do.
- either one of the end face of the main bearing or the sub-bearing is used as a reference plane for the revolving motion of the piston, and the outer peripheral surface of the piston and the cylinder that revolves while swinging in the cylinder chamber while minimizing the shaft swing. Since the gap formed between the inner circumferential surface and the inner circumferential surface of the refrigerant can be reduced, leakage of the refrigerant gas from the compression chamber to the suction chamber can be reduced, and the effect of the first invention can be obtained without reducing the volumetric efficiency. it can.
- the escape means is a suction surface of the cylinder chamber on the sliding surface facing the eccentric portion of the shaft, of the inner peripheral surface of the piston. It is formed in a mode in which the side is excised.
- the cut portion formed on the inner peripheral surface of the piston is configured on the suction chamber side of the cylinder chamber on the light load side, so that there is an influence such as seizure on the sliding surface facing the eccentric portion of the shaft. There is little, and reliability does not fall.
- the vane in the rotary compressor of the third aspect of the invention, is stored in the vane groove most on the sliding surface facing the eccentric part of the shaft among the inner peripheral surface of the piston.
- the side closer to the vane is used as a base point, and is formed in a form cut away from a position of 30 degrees in the rotation direction of the shaft.
- the start position of the excised part formed on the inner peripheral surface of the piston is shifted by 30 degrees from the base point of the light load part, so even if a load acts near the base point of the light load part during discharge operation, it is sufficient Durability can be secured.
- the piston is arranged so as to swing in a horizontal plane, and is opposed to the eccentric portion of the shaft on the inner peripheral surface of the piston. The upper portion of the sliding surface is cut away.
- the working refrigerant comprises a refrigerant having a base component of a hydrofluoroolefin having a double bond between carbon and carbon.
- a single refrigerant or a mixed refrigerant containing this refrigerant is used, and when such a refrigerant is used, it is more effective because the lubricity deteriorates with a decrease in chemical stability especially at high temperatures.
- the sliding loss caused by the reciprocating motion of the vane in the vane groove can be reduced.
- FIG. 1 is a longitudinal sectional view of a rotary compressor provided with one compression mechanism 101 as an embodiment of the rotary compressor of the present invention
- FIG. 2 is a transverse sectional view of the compression mechanism.
- the rotary compressor shown in FIG. 1 is disposed in a cylindrical sealed container 1, a motor unit 102 disposed on the upper side inside the sealed container 1, and a lower side of the motor unit 102, and is driven by the motor unit 102. And the bottom of the sealed container 1 is used as an oil reservoir.
- the electric motor unit 102 includes a stator 2 that is annularly attached along the inner peripheral surface of the upper side of the hermetic container 1, and a rotor 3 that is inserted with a slight gap inside the stator 2. Is fixed to the shaft 4 in the vertical direction at the center.
- the compression mechanism 101 includes a cylinder 5, a main bearing 7 and a sub-bearing 8 that are fastened to both end surfaces of the cylinder 5 to form a cylinder chamber 6, and a main bearing 7 and a sub-bearing. 8, a shaft 4 provided with an eccentric portion 41, a piston 9 fitted to the eccentric portion 41 of the shaft 4, and a vane 11 that reciprocates in a vane groove 10 formed in the cylinder 5 in a radial direction.
- the tip end portion 11A of the vane 11 has an arc shape, and is fitted and connected to a fitting portion 9A formed on the piston 9 so as to be swingable.
- the suction chamber 12 partitioned by the vane 11 in the cylinder chamber 6 A compression chamber 13 is formed. Further, the main bearing 7 is fastened to the upper end surface of the cylinder 5 and the sub-bearing 8 is fastened to the lower end surface of the cylinder 5 with bolts, and the main bearing 7 is welded to the hermetic container 1 so that the compression mechanism 101 is sealed. 1 is fixed.
- the shaft 4 is generally constituted by a main shaft portion 42 fitted into the main bearing 7, an eccentric portion 41 fitted into the piston 9, and a sub shaft portion 43 fitted into the sub bearing 8. Is done.
- the shaft diameter ⁇ D3 of the subshaft portion 43 fitted into the subbearing 8 is smaller than the shaft diameter ⁇ D2 of the main shaft portion 42 fitted into the main bearing 7.
- the required strength may be smaller than the strength required by the main shaft portion 42, and the required strength is ensured for the entire shaft 4.
- the shaft diameter of the eccentric portion 41 is ⁇ D1, and the outer peripheral surface of the eccentric portion 41 on the side opposite to the eccentric shaft is recessed from the outer peripheral surface of the main shaft portion 42 and the outer peripheral surface of the sub shaft portion 43.
- the amount of dent from the outer peripheral surface is the dimension ⁇ .
- the side of the eccentric part 41 on the auxiliary bearing 8 side is cut away from the outer peripheral surface of the eccentric part 41 radially inward by a height L1 concentric with the auxiliary shaft part 43 to form a relief part 301.
- Relief means for assembling the piston 9 to the shaft 4 is configured, and the end surface of the eccentric portion 41 slides with the end surface of the sub-bearing 8 to support the thrust load acting on the shaft 4.
- the main bearing 7 side of the eccentric portion 41 is also cut in an arc shape concentric with the main shaft portion 42 radially inward from the outer peripheral surface of the eccentric portion 41, and the cut-out space communicates with the hollow hole provided in the shaft 4. A hole is provided.
- the connecting portion between the eccentric portion 41 and the main shaft portion 42 and the sub shaft portion 43 is made smaller in diameter than the respective shaft diameters of the main shaft portion 42 and the sub shaft portion 43 in consideration of the manufacturing process of the shaft 4.
- the piston 9 is arranged so as to revolve while swinging in a horizontal plane, and has a dimension H in the height direction as shown in FIGS.
- the side surface of the secondary bearing 8 is cut into a circular shape concentric with the inner peripheral surface 9B of the piston 9 by a height L2 to form a relief portion 302, and the main bearing of the sliding surface facing the eccentric portion 41 of the shaft 4 is further formed. 7 is cut off by a height L3 in the shape of an arc around a position shifted by a necessary amount from the center of the inner peripheral surface 9B of the piston 9 to the eccentric shaft side, thereby forming the escape portion 303.
- the escape means when assembling to 4 is configured.
- a concave portion 304 is formed by cutting the same or slightly smaller circular shape by a height L.
- the excision height L1 of the escape portion 301, the excision height L2 of the escape portion 302, and the excision height L3 of the escape portion 303 are set so as to satisfy the following expression (2).
- FIG. 5 is based on the point closer to the vane 11 out of the intersection of the inner peripheral surface 9B of the piston 9 and the center line in the thickness direction of the vane 11 when the vane 11 is most housed in the vane groove 10. It is a surface development view in which the inner peripheral surface 9B is developed in the rotation direction of the shaft 4, and a sliding surface that is sandwiched between two two-dot chain lines in the figure and that faces the eccentric portion 41 of the shaft 4 is an escape portion 303.
- the narrow portion 9D having a small width in the height direction and the large portion 9C having a relatively large width, which are excised by the above, are particularly located on the suction chamber 12 side of the cylinder chamber 6.
- the direction closer to the vane 11 is the base point, and 30 in the rotational direction of the shaft 4
- the height direction of the piston 9 from the position of degrees It is formed in a manner to ablate side.
- FIG. 6 shows the positional relationship between the piston 9 and the vane 11 when the piston 9 is revolved by 60 degrees in the order of (a), (b), (c), (d), (e), (f). ing. 3 (a), (b), (c), (d), (e), and (f), the working refrigerant is sucked into the suction chamber 12 from the suction port 17 in the order shown in FIG.
- the volume of the suction chamber 12 and the compression chamber 13 is changed by the swinging motion and the reciprocating motion of the vane 11, and due to this volume change, the working refrigerant is gradually compressed to high temperature and high pressure, and the compression chamber is processed at the timing shown in FIG.
- the shaft diameter of the auxiliary shaft portion 43 is made smaller than the shaft diameter of the main shaft portion 42, and the outer peripheral surface of the eccentric portion 41 on the side opposite to the eccentric shaft is the outer peripheral surface of the main shaft portion 42 and the auxiliary shaft portion 43.
- the sub-bearing 8 side of the eccentric portion 41 is concentric with the sub-shaft portion 43 radially inward from the outer peripheral surface of the eccentric portion 41 so that the shaft 4 and the piston 9 can be assembled while being recessed from the outer peripheral surface.
- the relief portion 301 is formed by cutting away the height L1 in a circular arc shape, and the auxiliary bearing 8 side is formed on the inner peripheral surface 9B of the piston 9 in a circular shape concentric with the inner peripheral surface 9B of the piston 9 by the height L2.
- a position where the escape portion 302 is formed by cutting, and the main bearing 7 side of the sliding surface facing the eccentric portion 41 of the shaft 4 is shifted from the center of the inner peripheral surface 9B of the piston 9 to the eccentric shaft side by a necessary amount. Since the escape portion 303 is formed by cutting away the height L3 in an arc shape around the center, While ensuring the strength reliability of Yafuto 4, it is possible to reduce the shaft diameter of the eccentric portion 41.
- the area of the sliding surface of the eccentric part 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 can be reduced, and the sliding speed of the eccentric part 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 can be reduced. It becomes possible. That is, when the shaft 4 rotates, the viscous force of oil acting between the eccentric portion 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 can be reduced, and the rotational direction of the shaft 4 is reduced by this viscous force. The rotational moment around the center of the eccentric portion 41 of the shaft 4 acting on the piston 9 can be reduced, so that when the vane 11 reciprocates in the vane groove 10, the tip portion 11A of the vane 11 has this rotational moment. It is possible to reduce the frictional resistance force with the vane groove 10 acting on the two contact points as a reaction force of the force for supporting the.
- the end surface of the eccentric portion 41 of the shaft 4 slides with the end surface of the sub-bearing 8 and supports the thrust load acting on the shaft 4, the end surface of the sub-bearing 8 is used as a reference surface for the revolving motion of the piston 9.
- the gap formed between the outer peripheral surface of the piston 9 and the inner peripheral surface of the cylinder 5 that revolves while swinging in the cylinder chamber 6 while minimizing the swing of the shaft 4 can be reduced. Therefore, leakage of the refrigerant gas from the compression chamber 13 to the suction chamber 12 is reduced, and volume efficiency is not reduced.
- the narrow portion 9D of the sliding surface facing the eccentric portion 41 of the shaft 4 is located on the suction chamber 12 side of the cylinder chamber 6 serving as a light load portion, so seizure occurs.
- the viscous force of oil acting between the eccentric portion 41 of the shaft 4 and the inner peripheral surface 9B of the piston 9 can be reduced.
- the sliding surface on the 12th side is a light load portion, and the load is very light.
- the sliding surface on the suction chamber 12 side facing the eccentric portion 41 of the shaft 4 in the inner peripheral surface 9B of the piston 9 is a light load portion.
- the start angle of the narrow portion 9D is set to the time when the vane 11 is stored most in the vane groove 10 so that sufficient durability can be secured even if a load is applied in the vicinity of the base point of the lightly loaded portion during the discharge operation.
- the intersecting points of the inner peripheral surface 9B of the piston 9 and the center line in the thickness direction of the vane 11 it is shifted by 30 degrees from the base point O which is closer to the vane 11, so that the reliability is not lowered.
- the narrow portion 9D is formed in such a manner that the upper side in the height direction of 9 is cut, and the cut portion formed on the sliding surface facing the eccentric portion 41 of the shaft 4 functions as an oil reservoir, so that the oil is insufficient. Lubrication can be prevented and reliability is improved.
- a single refrigerant composed of a refrigerant composed of carbon and a hydrofluoroolefin having a double bond between carbons as a base component or a mixed refrigerant containing this refrigerant is used.
- the lubricity deteriorates with a decrease in chemical stability at a high temperature, the sliding loss caused by the reciprocating motion of the vane in the vane groove is more effectively reduced. be able to.
- the rotary compressor according to the present invention can reduce input loss, it can be applied to a hot water compressor and air compression.
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- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
φD1 ≧ φD3 + 2×E ・・・(1)
で表され、偏心部41の軸径φD1は式(1)を満足するように設定しなければならない。また、この時、主軸部42の軸径φD2は副軸部43の軸径よりも大きくしているので、偏心部41における反偏心軸側の外周面は主軸部42の外周面よりへこんでいる。
図1は本発明の回転式圧縮機の実施例として、一つの圧縮機構部101を備えた回転式圧縮機の縦断面図、図2は圧縮機構部の横断面図を示している。
L1 > H - L - L2 -L3 ・・・(2)
2 ステータ
3 ロータ
4 シャフト
5 シリンダー
6 シリンダー室
7 主軸受け
8 副軸受け
9 ピストン
9A 嵌合部
9B 内周面
9C 幅大部
9D 狭小部
10 ベーン溝
11 ベーン
11A 先端部
12 吸入室
13 圧縮室
17 吸入ポート
18 吐出ポート
19 吐出マフラー室
41 偏心部
42 主軸部
43 副軸部
101 圧縮機構部
102 電動機部
201 接点
202 接点
301 逃げ部
302 逃げ部
303 逃げ部
304 凹部
Claims (6)
- シリンダーと、該シリンダーの両端面に締結されてシリンダー室を形成する主軸受け及び副軸受けと、前記主軸受けと前記副軸受けとの間に偏心部を設けたシャフトと、前記シャフトの偏心部に嵌合されるピストンと、前記シリンダー室内を吸入室と圧縮室に仕切るベーンと、前記シリンダーに形成され、前記ベーンが往復運動するベーン溝を有し、前記ベーンの先端部を前記ピストンと揺動自在に嵌合接続して構成される回転式圧縮機であって、前記シャフトの偏心部における反偏心軸側の外周面を前記主軸受けに嵌入される主軸部の外周面及び前記副軸受けに嵌入される副軸部の外周面よりへこませると共に、前記ピストンの内周面と前記シャフトの偏心部に、前記ピストンを前記シャフトに組み付ける際の逃げ手段を設けたことを特徴とする回転式圧縮機。
- 前記シャフトの偏心部の端面と摺動して、前記主軸受けと前記副軸受けのいずれか一方の端面で前記シャフトに作用するスラスト荷重を支持することを特徴とする請求項1に記載の回転式圧縮機。
- 前記逃げ手段は、前記ピストンの内周面のうち、前記シャフトの偏心部と対向する摺動面において、前記シリンダー室の吸入室側を切除した態様で形成されていることを特徴とする請求項1または請求項2に記載の回転式圧縮機。
- 前記逃げ手段は、前記ピストンの内周面のうち、前記シャフトの偏心部と対向する摺動面において、前記ベーンが前記ベーン溝に最も収納された時点の前記ピストンの内周面と前記ベーンの厚み方向中心線の交点のうち、前記ベーンに近い方を基点とし、前記シャフトの回転方向に30度の位置から切除した態様で形成されていることを特徴とする請求項3に記載の回転式圧縮機。
- 前記ピストンが水平面内を揺動しながら公転運動するように配置し、前記ピストンの内周面のうち、前記シャフトの偏心部と対向する摺動面の上側部分を切除した態様で形成されていることを特徴とする請求項3または請求項4に記載の回転式圧縮機。
- 作動冷媒として、炭素と炭素間に2重結合を有するハイドロフルオロオレフィンをベース成分とした冷媒からなる単一冷媒または前記冷媒を含む混合冷媒を用いたことを特徴とする請求項1から5のいずれか1項に記載の回転式圧縮機。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US13/808,030 US9074600B2 (en) | 2010-07-02 | 2011-06-29 | Rotary compressor |
EP11800436.5A EP2589809B1 (en) | 2010-07-02 | 2011-06-29 | Rotary compressor |
CN201180032823.7A CN102971537B (zh) | 2010-07-02 | 2011-06-29 | 旋转式压缩机 |
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JP2010-151805 | 2010-07-02 | ||
JP2010151805A JP5556450B2 (ja) | 2010-07-02 | 2010-07-02 | 回転式圧縮機 |
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US (1) | US9074600B2 (ja) |
EP (1) | EP2589809B1 (ja) |
JP (1) | JP5556450B2 (ja) |
CN (1) | CN102971537B (ja) |
WO (1) | WO2012001966A1 (ja) |
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JP6194465B2 (ja) * | 2013-03-12 | 2017-09-13 | パナソニックIpマネジメント株式会社 | 密閉型ロータリー圧縮機 |
KR102249115B1 (ko) * | 2014-09-19 | 2021-05-07 | 엘지전자 주식회사 | 압축기 |
JP7002033B2 (ja) * | 2016-02-26 | 2022-01-20 | パナソニックIpマネジメント株式会社 | 2シリンダ型密閉圧縮機 |
JP6489173B2 (ja) | 2017-08-09 | 2019-03-27 | ダイキン工業株式会社 | ロータリ圧縮機 |
KR102163622B1 (ko) | 2018-11-06 | 2020-10-08 | 엘지전자 주식회사 | 마찰 손실을 저감한 로터리 압축기 |
KR102310348B1 (ko) * | 2019-07-24 | 2021-10-07 | 엘지전자 주식회사 | 로터리 압축기 |
JP6881558B1 (ja) * | 2019-12-17 | 2021-06-02 | ダイキン工業株式会社 | 圧縮機 |
JP6930576B2 (ja) * | 2019-12-17 | 2021-09-01 | ダイキン工業株式会社 | 圧縮機 |
MX2021013733A (es) * | 2020-05-12 | 2021-12-10 | Energy Exploration Tech Inc | Sistemas y metodos para recuperar litio de salmueras. |
KR102372174B1 (ko) * | 2020-06-05 | 2022-03-08 | 엘지전자 주식회사 | 로터리 압축기 |
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- 2011-06-29 CN CN201180032823.7A patent/CN102971537B/zh active Active
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Also Published As
Publication number | Publication date |
---|---|
EP2589809A4 (en) | 2016-03-23 |
JP5556450B2 (ja) | 2014-07-23 |
CN102971537B (zh) | 2015-09-09 |
US20130101454A1 (en) | 2013-04-25 |
EP2589809A1 (en) | 2013-05-08 |
US9074600B2 (en) | 2015-07-07 |
JP2012013034A (ja) | 2012-01-19 |
EP2589809B1 (en) | 2017-01-04 |
CN102971537A (zh) | 2013-03-13 |
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