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WO2014208398A1 - Vane compressor - Google Patents

Vane compressor Download PDF

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Publication number
WO2014208398A1
WO2014208398A1 PCT/JP2014/065988 JP2014065988W WO2014208398A1 WO 2014208398 A1 WO2014208398 A1 WO 2014208398A1 JP 2014065988 W JP2014065988 W JP 2014065988W WO 2014208398 A1 WO2014208398 A1 WO 2014208398A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive shaft
vane
rotor
side block
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2014/065988
Other languages
French (fr)
Japanese (ja)
Inventor
高橋　知靖
孝則 寺屋
大沢　仁
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Japan Co Ltd
Original Assignee
Valeo Japan Co Ltd
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 Valeo Japan Co Ltd filed Critical Valeo Japan Co Ltd
Priority to CN201480034059.0A priority Critical patent/CN105308323B/en
Priority to EP14818134.0A priority patent/EP3015711A1/en
Publication of WO2014208398A1 publication Critical patent/WO2014208398A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—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
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • 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
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/17—Tolerance; Play; Gap
    • F04C2270/175—Controlled or regulated

Definitions

  • the present invention relates to a vane type compressor, and more particularly to a vane type compressor having a structure useful for maintaining a proper distribution of clearances before and after a rotor.
  • Vane type compressors used in refrigeration cycles of vehicle air conditioners have various configurations (see the following patent publication).
  • the vane type compressor includes a cylinder 12 formed in the housing 5 and having a cam surface 11 formed on the inner peripheral surface, and both ends of the cylinder 12 in the axial direction are closed.
  • a pair of side blocks (a rear side block 13 and a front side block 21), a drive shaft 2 rotatably supported by the pair of side blocks, and a cylinder mounted in the drive shaft 2
  • the rotor 3 is rotatably accommodated
  • the vane groove 8 is formed from the outer peripheral surface of the rotor 3 toward the inside
  • the vane 4 is accommodated in the vane groove 8 so as to be able to appear and retract.
  • the vane 4 is contacted and supported on the inner peripheral surface (cam surface 11) of the cylinder 12 by the centrifugal force generated by the rotation of the rotor 3 and the back pressure from the back pressure chamber 8a provided at the bottom of the vane groove 8. Yes.
  • a compression chamber 31 is defined by the rotor 3 and the vane 4 in a space closed by the cylinder 12 and the pair of side blocks 13 and 21, and the fluid sucked into the compression chamber 31 is caused by the rotation of the rotor 3. To compress.
  • the dimensions of the rotor 3 are controlled so that an appropriate clearance is formed between the two.
  • one end (front end) of the drive shaft 2 on which the rotor 3 is fixed is required to be directly connected to the drive source, or a power transmission member (pulley, electromagnetic clutch, etc.) for transmitting the power of the drive source is fixed. Therefore, one side block (front side block 21) is made to penetrate.
  • the clearance on the rear side of the rotor 3 (the clearance between the rotor 3 and the rear side block 13) is the clearance on the front side of the rotor (the side block on the rotor 3 and the front side). (Clearance between the two) is not solved, and there still remains a disadvantage that the compression efficiency is lowered.
  • the present invention has been made in view of such circumstances, and can balance the distribution of clearances in the axial direction of the rotor in a proper state by balancing the forces acting on the front and rear of the drive shaft.
  • the main issue is to provide a mold compressor.
  • a vane compressor includes a housing, a cam surface formed therein, a cylinder provided in the housing, and both ends of the cylinder in the axial direction closed.
  • a pair of side blocks provided on the drive shaft, a drive shaft rotatably supported by the pair of side blocks, a rotor fixedly mounted on the drive shaft and rotatably accommodated in the cylinder, and the rotor
  • a vane type provided with a low pressure space that communicates with the suction chamber, and a shaft end space defined by a rear side block of the pair of side blocks and an end of the drive shaft.
  • the compressor is characterized in that a passage for communicating the low pressure space and the shaft end space is provided in the drive shaft.
  • the drive shaft is provided with a passage communicating the low pressure space and the shaft end space, the pressure in the shaft end space of the drive shaft becomes a pressure equivalent to the suction pressure, and the pressure difference acting on both ends of the drive shaft is reduced. Can be small. For this reason, by balancing the force acting in the axial direction of the rotor, the clearance before and after the axial direction of the rotor (the clearance between one end surface of the rotor and the side block facing it, and the other end surface in the axial direction of the rotor) And the clearance between the opposing side blocks) can be made appropriate.
  • the side block configuration described above is particularly advantageous in an electric compressor in which the drive shaft passes through the front side block and is directly connected to the shaft of the electric motor. In some cases, such as when the drive shaft passes through the front side block and protrudes to the outside of the housing, it is disposed in the low pressure space of the drive shaft or on the side protruding outward and in the compressor housing. This is an effective configuration for adjusting the deviation in the distribution of the clearance due to the pressure difference from the side.
  • the housing includes a first housing member integrally formed with the cylinder having an inner peripheral surface formed in a perfect circle, and a first side block that closes one end of the cylinder in the axial direction; A combination of a second housing member formed with a second side block that closes the other end side of the cylinder in the axial direction is formed, and the pair of side blocks is formed by the first side block and the second side block.
  • You may comprise with a block.
  • the first side block may correspond to the rear side block
  • the second side block may correspond to the front side block.
  • the passage that communicates the low pressure space that communicates with the suction chamber and the shaft end space defined by the rear side block and the end of the drive shaft is driven. Since it is provided on the shaft, it is possible to keep the distribution of the clearance in the axial direction of the rotor in an appropriate state by balancing the forces acting before and after the drive shaft. For this reason, the compression efficiency is not reduced while ensuring smooth rotation of the rotor.
  • FIG. 1 is a sectional view showing a vane type compressor according to the present invention.
  • FIG. 2A is a view of the vane compressor shown in FIG. 1 as viewed from the rear side along the line AA
  • FIG. 2B is a view of the vane compressor shown in FIG. It is the figure which looked at the front side from the B line.
  • FIG. 3 is a cross-sectional view showing a conventional vane compressor.
  • the vane compressor 1 and 2 show a vane type compressor suitable for a refrigeration cycle using a refrigerant as a working fluid.
  • the vane compressor 1 includes a drive shaft 2, a rotor 3 that is fixed to the drive shaft 2 and rotates as the drive shaft 2 rotates, a vane 4 attached to the rotor 3, and the drive shaft 2.
  • a housing 5 that supports the rotor 3 and the vanes 4 while supporting the rotor 3 and the vanes 4 is provided.
  • FIG. 1 when the compressor is viewed from the side, the left side is the front side and the right side is the rear side.
  • the housing 5 is configured by combining two members of the first housing member 10 and the second housing member 20.
  • the first housing member 10 accommodates the rotor 3 and is integrally formed so as to close the cylinder 12 having the cam surface 11 formed on the inner peripheral surface and one end side (rear side) of the cylinder 12 in the axial direction.
  • the rear side block 13 is formed.
  • the inner peripheral surface (cam surface 11) of the cylinder 12 is formed in a perfect circle in cross section, and the axial length of the cylinder 12 is substantially equal to the axial length of the rotor 3 described later.
  • the second housing member 20 is in contact with an end surface on the other end side (front side) in the axial direction of the cylinder 12 and closes the other end side, and a front side block 21 on the front side block 21.
  • a shell 22 that is integrally formed and extends in the axial direction of the drive shaft 2 and is formed so as to surround the cylinder 12 and the outer peripheral surface of the rear side block 13.
  • the first housing member 10 and the second housing member 20 are fastened in the axial direction via a connector 6 such as a bolt, and the side block 13 and the second side block 13 on the rear side of the first housing member 10 are connected.
  • a sealing member 7 such as an O-ring is interposed between the housing member 20 and the shell 22 so as to be airtightly sealed.
  • the second housing member 20 is integrally formed with a boss portion 23 extending from the front side block 21 to the front side.
  • a pulley 32 (shown by an alternate long and short dash line) that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23, and rotational power is transmitted from the pulley 32 to the drive shaft 2 via an electromagnetic clutch 33. It has come to be.
  • the drive shaft 2 is rotatably supported by a rear side block 13 and a front side block 21 via bearings 14 and 24.
  • the distal end portion of the drive shaft 2 passes through the front side block 21 of the second housing member 20 and protrudes into the boss portion 23.
  • a space between the boss portion 23 and the drive shaft 2 is hermetically sealed by a seal member 25 provided between the boss portion 23 and the drive shaft 2.
  • a low-pressure space 26 is formed in the rear portion 25).
  • the rear side block 13 is formed with a bearing hole 13a into which the drive shaft 2 is inserted via a bearing 14, and the rear side block 13 and the drive shaft are formed at the end of the bearing hole 13a.
  • a shaft end space 15 defined by the two ends is provided.
  • the electromagnetic clutch 33 is known per se, and the clutch plate 35 is attached to a portion of the drive shaft 2 protruding from the housing member 20 (front side block 21) via a leaf spring 34 attached in the axial direction. Is fixed against the friction surface 32 a of the pulley 32.
  • the clutch plate 35 attracts the clutch plate 35 to the pulley 32 by energization of the excitation coil 36 included in the pulley 32, and the clutch plate 35 and the leaf spring 34 receive the rotational power from the traveling engine applied to the pulley 32. Via the drive shaft 2. Due to the adsorption of the clutch plate 35 to the pulley 32, the urging force toward the rear side block 13 (rear side) is urged to the drive shaft 2 by the spring force of the plate spring 34.
  • the rotor 3 has a circular cross section, and the drive shaft 2 is inserted through an insertion hole 3a provided at the center of the rotor 3, and the rotor 3 is fixed to the drive shaft 2 in a state where the centers of the shafts coincide with each other. Yes. Further, the axial center of the cylinder 12 and the axial center of the rotor 3 (drive shaft 2) are such that the outer peripheral surface of the rotor 3 and the inner peripheral surface (cam surface 11) of the cylinder 12 abut at one place in the circumferential direction. They are shifted (they are shifted by a half of the difference between the inner diameter of the cylinder 12 and the outer diameter of the rotor 3). A compression space 30 is defined between the inner peripheral surface of the cylinder 12 and the outer peripheral surface of the rotor 3 in the space closed by the cylinder 12, the rear side block 13, and the front side block 21. ing.
  • a plurality of vane grooves 8 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 8.
  • the vane groove 8 is opened not only on the outer peripheral surface of the rotor 3 but also on the end surface facing the side block 13 on the rear side and the side block 21 on the front side, and a back pressure chamber 8a is formed at the bottom.
  • a plurality of the vane grooves 8 are formed at equal intervals in the circumferential direction.
  • the vane groove is formed so as to be parallel to each other at two places different in phase by 180 degrees, and a plane including the vane 4 and a plane including the axis of the drive shaft 2 parallel to the vane 4. Are formed in a state (offset state) separated by a predetermined distance.
  • the vane 4 is formed such that the length along the axial direction of the drive shaft 2 is equal to the axial length of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 8 is The groove 8 is formed approximately equal to the length in the same direction.
  • the vane 4 is protruded from the vane groove 8 by oil, which will be described later, supplied to the back pressure chamber 8 a of the vane groove 8, and a tip portion thereof can come into contact with the inner peripheral surface (cam surface 11) of the cylinder 12. Yes.
  • the compression space 30 is partitioned into a plurality of compression chambers 31 by the vanes 4 slidably inserted into the vane grooves 8, and the volume of each compression chamber 31 changes as the rotor 3 rotates. ing.
  • the second housing member 20 is formed with a suction port 27 for sucking working fluid (refrigerant gas) from the outside and a discharge port 28 for discharging the working fluid (refrigerant gas) to the outside.
  • the front side block 21 is formed with a suction chamber 29 that is connected to the suction port 27 and is provided adjacent to the front side block and into which fluid before being compressed is introduced. .
  • the cylinder 12 of the first housing member 10 is formed with a suction port 16 that communicates with the suction chamber 29 and sucks fluid into the compression chamber 31.
  • the suction port 16 is formed in the vicinity of the front side in the rotational direction of the rotor 3 with respect to a portion (radial seal portion 40) where the outer peripheral surface of the rotor 3 comes into contact with the inner peripheral surface of the cylinder 12.
  • the first housing member 10 is provided with a discharge port 17 for discharging the fluid compressed in the compression chamber in the vicinity of the radial seal portion 40 on the rear side in the rotational direction of the rotor 3. Yes. Further, the first housing member 10 is formed with a discharge chamber 18 that guides the fluid discharged through the discharge port 17 to the discharge port 28.
  • An oil separator (not shown) is disposed between the discharge chamber 18 and the discharge port 28.
  • An oil chamber for storing high-pressure oil separated from the fluid by an oil separator is provided between the lower part of the rear side block 13 of the first housing member 10 and the lower part of the shell 22 of the second housing member 20. 19 is provided.
  • a rear-side oil introduction groove 41 is formed on the surface of the rear-side side block 13 that faces the end surface of the rotor 3 on the periphery of the bearing hole 13a into which the drive shaft 2 is inserted via the bearing 14. Yes.
  • the rear-side oil introduction groove 41 extends in the circumferential direction with the opening periphery of the bearing hole 13a being recessed, and the angle at which the discharge port 17 is provided from the angular position at which the radial seal portion 40 is provided. It is formed over a predetermined angle range (an angle range of about 270 degrees) from the position to the front.
  • the oil introduction groove 41 is connected to the oil chamber 19 via an oil communication path 42 having a throttle portion.
  • the high-pressure oil stored in the oil chamber 19 is supplied to the rear-side oil introduction groove 41 formed in the rear-side side block 13 via the oil communication path 42, and this rear From the oil introduction groove 41 on the side, the sliding portion such as the bearing 14 and the back pressure chamber 8 a of the rotor 3 are fed.
  • the vane 4 is pressed against the inner peripheral surface (cam surface 11) of the cylinder 12 by the oil fed into the back pressure chamber 8a, so that stable compression is ensured.
  • a front-side oil introduction groove 43 is formed on the opening periphery of the bearing hole 21 a into which the drive shaft 2 is inserted via the bearing 24 on the surface of the front-side side block 21 that faces the end surface of the rotor 3. Yes.
  • the front-side oil introduction groove 43 extends in the circumferential direction with the opening periphery of the bearing hole 21a being recessed, and the angle at which the discharge port 17 is provided from the angular position at which the radial seal portion 40 is provided. It is formed over a predetermined angle range (an angle range of about 270 degrees) from the position to the front.
  • the oil introduction groove 43 is formed between the bottom of the vane groove 8 (back pressure chamber 8a) when the tip of the vane 4 is in an angular range from a position where the vane 4 reaches the suction port 16 to just before the discharge port 17 is reached. It comes to communicate.
  • reference numeral 37 denotes a screw hole into which the connector 6 is screwed.
  • the front housing member is provided with a communication passage 51 that communicates the suction chamber 29 and the low pressure space 26, and the drive shaft 2 has a low pressure space 26 and a shaft end space. 15 is provided.
  • the communication passage 51 is configured by a passage that is formed substantially perpendicularly to the drive shaft 2 from the suction chamber 29 to the low pressure space 26.
  • a passage 52 provided in the drive shaft 2 is formed in the radial direction of the drive shaft 2, and has a radial hole 52 a having one end opened to the low-pressure space 26 and the other end extended to the center of the drive shaft 2.
  • the center of the drive shaft 2 is formed in the axial direction, and has an axial hole 52b having one end communicating with the radial hole 52a and the other end extending to the shaft end space 15.
  • the low-pressure space 26 communicates with the suction chamber 29 via the communication passage 51, and the shaft end space 15 communicates with the low-pressure space 26 via the passage 52.
  • the shaft end space 15 is maintained at a pressure corresponding to the suction pressure.
  • the compressor in the case where there are two vanes 4 has been described.
  • a similar configuration can be adopted in a three or more vane type compressor.
  • the vane groove 8 (vane 4) is offset in the two-vane configuration, but the plane including the vane 4 and the vane 4 are parallel to the drive shaft.
  • the same configuration is adopted to adjust the clearance distribution before and after the rotor 3 in the axial direction even when the plane including the axis 2 is made coincident (offset is set to 0) or when offset to the opposite side. You may make it do.

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

Abstract

[Problem] To provide a vane compressor which is configured so that the distribution of clearances at the front and rear of a rotor in the axial direction is maintained in an appropriate state by balancing forces acting on the front and rear of a drive shaft. [Solution] A passage (52) for connecting a low-pressure space (26), which connects to a suction chamber (29), and a shaft-end space (15), which is defined by a side block (13) on the rear side and by an end of a drive shaft (2), is provided in the drive shaft (2) to thereby balance forces acting on the front and rear of the drive shaft (2). As a result, the distribution of clearances at the front and rear of a rotor (3) in the axial direction is maintained in an appropriate state. Consequently, the smooth rotation of the rotor (3) is ensured and the compression efficiency does not degrade.

Description

ベーン型圧縮機Vane type compressor

　本発明は、ベーン型圧縮機に関し、特にロータ前後のクリアランスの配分を適正な状態に保つために有用な構造を備えたベーン型圧縮機に関する。 The present invention relates to a vane type compressor, and more particularly to a vane type compressor having a structure useful for maintaining a proper distribution of clearances before and after a rotor.

　車両用空調装置の冷凍サイクル等で用いられるベーン型圧縮機は、各種構成が存在する（下記の特許公報参照）。例えば、図３の構成で代表されるように、ベーン型圧縮機は、ハウジング５内に形成されてカム面１１が内周面に形成されたシリンダ１２と、シリンダ１２の軸方向の両端を閉塞する一対のサイドブロック（リア側のサイドブロック１３、フロント側のサイドブロック２１）と、この一対のサイドブロックに回転自在に支持された駆動軸２と、この駆動軸２に固装されてシリンダ内に回転可能に収容されたロータ３と、このロータ３の外周面から内部に向けて形成されたベーン溝８と、このベーン溝８に出没可能に収容されたベーン４とを有する。ベーン４は、ロータ３の回転による遠心力およびベーン溝８の底部に設けられた背圧室８ａからの背圧によってシリンダ１２の内周面（カム面１１）に接触支持されるようになっている。そして、シリンダ１２と一対のサイドブロック１３，２１とにより閉塞された空間にロータ３とベーン４とによって圧縮室３１が画成され、この圧縮室３１に吸入される流体をロータ３の回転に伴って圧縮させるようにしている。 Vane type compressors used in refrigeration cycles of vehicle air conditioners have various configurations (see the following patent publication). For example, as represented by the configuration of FIG. 3, the vane type compressor includes a cylinder 12 formed in the housing 5 and having a cam surface 11 formed on the inner peripheral surface, and both ends of the cylinder 12 in the axial direction are closed. A pair of side blocks (a rear side block 13 and a front side block 21), a drive shaft 2 rotatably supported by the pair of side blocks, and a cylinder mounted in the drive shaft 2 The rotor 3 is rotatably accommodated, the vane groove 8 is formed from the outer peripheral surface of the rotor 3 toward the inside, and the vane 4 is accommodated in the vane groove 8 so as to be able to appear and retract. The vane 4 is contacted and supported on the inner peripheral surface (cam surface 11) of the cylinder 12 by the centrifugal force generated by the rotation of the rotor 3 and the back pressure from the back pressure chamber 8a provided at the bottom of the vane groove 8. Yes. A compression chamber 31 is defined by the rotor 3 and the vane 4 in a space closed by the cylinder 12 and the pair of side blocks 13 and 21, and the fluid sucked into the compression chamber 31 is caused by the rotation of the rotor 3. To compress.

　このようなベーン型圧縮機においては、ロータ３のスムーズな回転を確保するために、また、圧縮効率の低下を防ぐために、ロータ３の軸方向の前後の端面とそれぞれのサイドブロック１３．２１との間に適切なクリアランスが形成されるよう、ロータ３の寸法が管理されている。 In such a vane compressor, in order to ensure smooth rotation of the rotor 3 and to prevent a reduction in compression efficiency, the front and rear end faces in the axial direction of the rotor 3 and the respective side blocks 13.21 The dimensions of the rotor 3 are controlled so that an appropriate clearance is formed between the two.

特開２０１３－０５００３８号公報JP 2013-050038 A 特開２００７－０６４１６３号公報JP 2007-064163 A

　しかしながら、ロータ３が固装されている駆動軸２の一端（前端）は、駆動源に直結させる必要から、或いは、駆動源の動力を伝達する動力伝達部材（プーリ、電磁クラッチ等）を固装する必要から、一方のサイドブロック（フロント側のサイドブロック２１）を貫通させるようにしている。 However, one end (front end) of the drive shaft 2 on which the rotor 3 is fixed is required to be directly connected to the drive source, or a power transmission member (pulley, electromagnetic clutch, etc.) for transmitting the power of the drive source is fixed. Therefore, one side block (front side block 21) is made to penetrate.

　このため、駆動軸２の一端が一方のサイドブロック（フロント側のサイドブロック２１）を貫通してハウジングの外部に突出している場合には、駆動軸２の一端側に大気圧が作用し、これに対して、駆動軸２の他端側（リア側のサイドブロック１３に支持される側）に圧縮機内部の相対的に高い圧力が作用する。したがって、駆動軸２は、軸方向の前後両側に作用する圧力差により、サイドブロックから突出している一端側（前側）へ付勢された状態となり、ロータ３の軸方向の位置は、駆動軸２が貫通しているサイドブロック側（フロント側のサイドブロック２１側）へ接近し、ロータ３の前端と前側のフロント側のサイドブロック２１との間のクリアランスは相対的に小さくなる。逆に、ロータ３の後端と後側のリア側のサイドブロック１３との間のクリアランスは相対的に大きくなる。このため、クリアランスが大きくなる後側（リア側のサイドブロック１３側）で、隣り合う圧縮室間でクリアランスを介して流体が漏流し（オイルシールが悪くなり）、圧縮効率が低下する不都合が生じる。 For this reason, when one end of the drive shaft 2 passes through one side block (front side block 21) and protrudes outside the housing, atmospheric pressure acts on one end side of the drive shaft 2, On the other hand, a relatively high pressure inside the compressor acts on the other end side of the drive shaft 2 (side supported by the rear side block 13). Therefore, the drive shaft 2 is biased to one end side (front side) protruding from the side block by the pressure difference acting on both the front and rear sides in the axial direction, and the axial position of the rotor 3 is , The clearance between the front end of the rotor 3 and the front side block 21 on the front side becomes relatively small. On the contrary, the clearance between the rear end of the rotor 3 and the rear side block 13 on the rear side becomes relatively large. For this reason, on the rear side (the side block 13 side on the rear side) where the clearance becomes larger, fluid leaks through the clearance between adjacent compression chambers (oil seal becomes worse), resulting in a disadvantage that the compression efficiency is lowered. .

　図３の一点鎖線で示されるように、動力伝達部材として電磁クラッチ３３が駆動軸２に設けられる場合には、ロータ３に動力が伝達される電磁クラッチ３３の吸着時には、クラッチを構成する板バネのバネ力が駆動軸２を介してロータ３を後方（リア側のサイドブロック１３側）へ付勢するように作用する。このため、ロータ３の軸方向の位置は、駆動軸２の軸方向の前後両側に作用する圧力差と電磁クラッチ３３のバネ力とによって決まることになる。
　しかしながら、ベーン型圧縮機は、小型のものが多く、電磁クラッチのバネ力も駆動軸２の前後両端の圧力差を相殺するほど大きくない。したがって、電磁クラッチ３３が設けられていても、ロータ３の後側のクリアランス（ロータ３とリア側のサイドブロック１３との間のクリアランス）がロータの前側のクリアランス（ロータ３とフロント側のサイドブロック２１との間のクリアランス）よりも大きくなる状態を解消することができず、圧縮効率が低下する不都合は依然として生じている。 As shown by the one-dot chain line in FIG. 3, when the electromagnetic clutch 33 is provided on the drive shaft 2 as a power transmission member, a leaf spring constituting the clutch is attracted when the electromagnetic clutch 33 is transmitted to the rotor 3. The spring force acts to urge the rotor 3 rearward (rear side block 13 side) via the drive shaft 2. For this reason, the position of the rotor 3 in the axial direction is determined by the pressure difference acting on both the front and rear sides in the axial direction of the drive shaft 2 and the spring force of the electromagnetic clutch 33.
However, many vane compressors are small, and the spring force of the electromagnetic clutch is not so large as to cancel the pressure difference between the front and rear ends of the drive shaft 2. Therefore, even if the electromagnetic clutch 33 is provided, the clearance on the rear side of the rotor 3 (the clearance between the rotor 3 and the rear side block 13) is the clearance on the front side of the rotor (the side block on the rotor 3 and the front side). (Clearance between the two) is not solved, and there still remains a disadvantage that the compression efficiency is lowered.

　そこで、従来においては、ロータの後側のクリアランスが許容範囲に収まるようにするために、ロータの軸方向前後のトータルのクリアランス（ロータ前後のクリアランスの和）が大きくなり過ぎないように管理する方法を採用しているが、このような管理方法では、管理工程の複雑化を招き、また、生産性が低下する等の不都合がある。 Therefore, conventionally, in order to keep the clearance on the rear side of the rotor within an allowable range, the total clearance before and after the rotor in the axial direction (the sum of clearances before and after the rotor) is managed so as not to become too large. However, in such a management method, there are disadvantages such as a complicated management process and a decrease in productivity.

　本発明は、係る事情に鑑みてなされたものであり、駆動軸の前後に作用する力をバランスさせることで、ロータの軸方向前後のクリアランスの配分を適正な状態に保持することが可能なベーン型圧縮機を提供することを主たる課題としている。 SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and can balance the distribution of clearances in the axial direction of the rotor in a proper state by balancing the forces acting on the front and rear of the drive shaft. The main issue is to provide a mold compressor.

　上記課題を達成するために、本発明に係るベーン型圧縮機は、ハウジングと、カム面が形成され、前記ハウジング内に設けられたシリンダと、前記シリンダの軸方向の両端を閉塞し、前記ハウジングに設けられた一対のサイドブロックと、前記一対のサイドブロックに回転自在に支持された駆動軸と、前記駆動軸に固装されて前記シリンダ内に回転可能に収容されるロータと、前記ロータに形成された複数のベーン溝と、前記ベーン溝に摺動自在に挿入され、先端が前記ベーン溝から出没して前記カム面を摺動する複数のベーンと、前記シリンダと前記一対のサイドブロックとにより閉塞された空間に、前記ロータと前記ベーンとによって形成される圧縮室と、前記一対のサイドブロックのうちのフロント側のサイドブロックに隣接して設けられ圧縮される前の流体が導入される吸入室と、前記フロント側のサイドブロックと前記駆動軸との間に設けられたシール部材と、前記シール部材よりも前記駆動軸の軸方向リア側に設けられ、前記吸入室と連通する低圧空間と、前記一対のサイドブロックのうちのリア側のサイドブロックと前記駆動軸の端部とによって画成された軸端部空間と、を備えたベーン型圧縮機において、前記駆動軸に、前記低圧空間と前記軸端部空間とを連通する通路を設けたことを特徴としている。 In order to achieve the above object, a vane compressor according to the present invention includes a housing, a cam surface formed therein, a cylinder provided in the housing, and both ends of the cylinder in the axial direction closed. A pair of side blocks provided on the drive shaft, a drive shaft rotatably supported by the pair of side blocks, a rotor fixedly mounted on the drive shaft and rotatably accommodated in the cylinder, and the rotor A plurality of formed vane grooves; a plurality of vanes that are slidably inserted into the vane grooves; and tips that protrude and retract from the vane grooves and slide on the cam surface; the cylinder and the pair of side blocks; In the space closed by the rotor and the vane and adjacent to the front side block of the pair of side blocks. A suction chamber into which the fluid before being compressed is introduced, a seal member provided between the side block on the front side and the drive shaft, and closer to the axial rear side of the drive shaft than the seal member A vane type provided with a low pressure space that communicates with the suction chamber, and a shaft end space defined by a rear side block of the pair of side blocks and an end of the drive shaft. The compressor is characterized in that a passage for communicating the low pressure space and the shaft end space is provided in the drive shaft.

　したがって、駆動軸に低圧空間と軸端部空間とを連通する通路を設けたので、駆動軸の軸端部空間の圧力は吸入圧相当の圧力となり、駆動軸の両端部に作用する圧力差を小さくすることができる。このため、ロータの軸方向に作用する力をバランスさせることで、ロータの軸方向前後のクリアランス（ロータの一端面とこれに対峙するサイドブロックとの間のクリアランスと、ロータの軸方向の他端面とこれに対峙するサイドブロックとの間のクリアランス）の配分を適正なものとすることが可能となる。 Accordingly, since the drive shaft is provided with a passage communicating the low pressure space and the shaft end space, the pressure in the shaft end space of the drive shaft becomes a pressure equivalent to the suction pressure, and the pressure difference acting on both ends of the drive shaft is reduced. Can be small. For this reason, by balancing the force acting in the axial direction of the rotor, the clearance before and after the axial direction of the rotor (the clearance between one end surface of the rotor and the side block facing it, and the other end surface in the axial direction of the rotor) And the clearance between the opposing side blocks) can be made appropriate.

　なお、上述したサイドブロックの構成は、特に、駆動軸がフロント側のサイドブロックを貫通して電動モータの軸に直結している電動圧縮機において、電動モータを収容する空間が相対的に低圧である場合や、駆動軸がフロント側のサイドブロックを貫通してハウジングの外部へ突出しているような場合において、駆動軸の低圧空間または外部に突出している側と圧縮機のハウジング内に配置される側との圧力差に起因するクリアランスの配分の偏りを調整するために有効な構成である。 The side block configuration described above is particularly advantageous in an electric compressor in which the drive shaft passes through the front side block and is directly connected to the shaft of the electric motor. In some cases, such as when the drive shaft passes through the front side block and protrudes to the outside of the housing, it is disposed in the low pressure space of the drive shaft or on the side protruding outward and in the compressor housing. This is an effective configuration for adjusting the deviation in the distribution of the clearance due to the pressure difference from the side.

　また、前記ハウジングは、内周面が真円に形成された前記シリンダ、及び、前記シリンダの軸方向の一端側を閉塞する第1のサイドブロックが一体に形成された第１のハウジング部材と、前記シリンダの軸方向の他端側を閉塞する第２のサイドブロックが形成された第２のハウジング部材とを組み合わせて構成し、前記一対のサイドブロックを、第１のサイドブロックと第２のサイドブロックとにより構成してもよい。
　このような構成においては、例えば、第１のサイドブロックを前記リア側のサイドブロックに対応させ、第２のサイドブロックをフロント側のサイドブロックに対応させるようにするとよい。 The housing includes a first housing member integrally formed with the cylinder having an inner peripheral surface formed in a perfect circle, and a first side block that closes one end of the cylinder in the axial direction; A combination of a second housing member formed with a second side block that closes the other end side of the cylinder in the axial direction is formed, and the pair of side blocks is formed by the first side block and the second side block. You may comprise with a block.
In such a configuration, for example, the first side block may correspond to the rear side block, and the second side block may correspond to the front side block.

　以上述べたように、本発明によれば、吸入室と連通する低圧空間と、リア側のサイドブロックと駆動軸の端部とによって画成された軸端部空間と、を連通する通路を駆動軸に設けたので、駆動軸の前後に作用する力をバランスさせることで、ロータの軸方向前後のクリアランスの配分を適正な状態に保持することが可能となる。このため、ロータのスムーズな回転を確保しつつ、圧縮効率の低下を招くことがなくなる。 As described above, according to the present invention, the passage that communicates the low pressure space that communicates with the suction chamber and the shaft end space defined by the rear side block and the end of the drive shaft is driven. Since it is provided on the shaft, it is possible to keep the distribution of the clearance in the axial direction of the rotor in an appropriate state by balancing the forces acting before and after the drive shaft. For this reason, the compression efficiency is not reduced while ensuring smooth rotation of the rotor.

図１は、本発明にかかるベーン型圧縮機を示す断面図である。FIG. 1 is a sectional view showing a vane type compressor according to the present invention. 図２（ａ）は、図１で示すベーン型圧縮機のＡ－Ａ線からリア側を見た図であり、また、図２（ｂ）は、図１で示すベーン型圧縮機のＢ－Ｂ線からフロント側を見た図である。FIG. 2A is a view of the vane compressor shown in FIG. 1 as viewed from the rear side along the line AA, and FIG. 2B is a view of the vane compressor shown in FIG. It is the figure which looked at the front side from the B line. 図３は、従来のベーン型圧縮機を示す断面図である。FIG. 3 is a cross-sectional view showing a conventional vane compressor.

　以下、本発明のベーン型圧縮機について図面を参照しながら説明する。 Hereinafter, the vane type compressor of the present invention will be described with reference to the drawings.

　図１及び図２において、冷媒を作動流体とする冷凍サイクルに適したベーン型圧縮機が示されている。このベーン型圧縮機１は、駆動軸２と、駆動軸２に固定されて当該駆動軸２の回動に伴い回転するロータ３と、このロータ３に取り付けられるベーン４と、駆動軸２を回転自在に支持すると共にロータ３及びベーン４を収容するハウジング５とを有して構成されている。なお、圧縮機を側方から見た図１において、左側をフロント側、右側をリア側とする。 1 and 2 show a vane type compressor suitable for a refrigeration cycle using a refrigerant as a working fluid. The vane compressor 1 includes a drive shaft 2, a rotor 3 that is fixed to the drive shaft 2 and rotates as the drive shaft 2 rotates, a vane 4 attached to the rotor 3, and the drive shaft 2. A housing 5 that supports the rotor 3 and the vanes 4 while supporting the rotor 3 and the vanes 4 is provided. In FIG. 1 when the compressor is viewed from the side, the left side is the front side and the right side is the rear side.

　ハウジング５は、第１のハウジング部材１０と第２のハウジング部材２０との２つの部材を組み合わせて構成されている。
　第１のハウジング部材１０は、ロータ３を収納すると共にカム面１１が内周面に形成されたシリンダ１２と、このシリンダ１２の軸方向の一端側（リア側）を閉塞するように一体に形成されたリア側のサイドブロック１３と、から構成されている。シリンダ１２の内周面（カム面１１）は、断面が真円に形成され、シリンダ１２の軸方向の長さは、後述するロータ３の軸方向の長さにほぼ等しく形成されている。 The housing 5 is configured by combining two members of the first housing member 10 and the second housing member 20.
The first housing member 10 accommodates the rotor 3 and is integrally formed so as to close the cylinder 12 having the cam surface 11 formed on the inner peripheral surface and one end side (rear side) of the cylinder 12 in the axial direction. The rear side block 13 is formed. The inner peripheral surface (cam surface 11) of the cylinder 12 is formed in a perfect circle in cross section, and the axial length of the cylinder 12 is substantially equal to the axial length of the rotor 3 described later.

　第２のハウジング部材２０は、シリンダ１２の軸方向の他端側（フロント側）の端面に当接してこの他端側を閉塞するフロント側のサイドブロック２１と、このフロント側のサイドブロック２１に一体に形成されて駆動軸２の軸方向に延設され、前記シリンダ１２及びリア側のサイドブロック１３の外周面を包囲するように形成されたシェル２２と、を有して構成されている。 The second housing member 20 is in contact with an end surface on the other end side (front side) in the axial direction of the cylinder 12 and closes the other end side, and a front side block 21 on the front side block 21. And a shell 22 that is integrally formed and extends in the axial direction of the drive shaft 2 and is formed so as to surround the cylinder 12 and the outer peripheral surface of the rear side block 13.

　そして、これら第１のハウジング部材１０と第２のハウジング部材２０とは、ボルト等の連結具６を介して軸方向に締結され、第１のハウジング部材１０のリア側のサイドブロック１３と第２のハウジング部材２０のシェル２２との間は、Ｏリング等のシール部材７が介在されて気密よくシールされている。 The first housing member 10 and the second housing member 20 are fastened in the axial direction via a connector 6 such as a bolt, and the side block 13 and the second side block 13 on the rear side of the first housing member 10 are connected. A sealing member 7 such as an O-ring is interposed between the housing member 20 and the shell 22 so as to be airtightly sealed.

　また、第２のハウジング部材２０には、フロント側のサイドブロック２１からフロント側に延設されたボス部２３が一体に形成されている。このボス部２３には、駆動軸２に回転動力を伝えるプーリ３２（一点鎖線で示す）が回転自在に外装され、駆動軸２には、このプーリ３２から電磁クラッチ３３を介して回転動力が伝達されるようになっている。 Also, the second housing member 20 is integrally formed with a boss portion 23 extending from the front side block 21 to the front side. A pulley 32 (shown by an alternate long and short dash line) that transmits rotational power to the drive shaft 2 is rotatably mounted on the boss portion 23, and rotational power is transmitted from the pulley 32 to the drive shaft 2 via an electromagnetic clutch 33. It has come to be.

　前記駆動軸２は、リア側のサイドブロック１３とフロント側のサイドブロック２１とにベアリング１４，２４を介して回転自在に支持されている。駆動軸２の先端部は、第２のハウジング部材２０のフロント側のサイドブロック２１を貫通してボス部２３内に突出している。このボス部２３と駆動軸２との間に設けられたシール部材２５によって該ボス部２３と駆動軸２との間が気密よくシールされている。 The drive shaft 2 is rotatably supported by a rear side block 13 and a front side block 21 via bearings 14 and 24. The distal end portion of the drive shaft 2 passes through the front side block 21 of the second housing member 20 and protrudes into the boss portion 23. A space between the boss portion 23 and the drive shaft 2 is hermetically sealed by a seal member 25 provided between the boss portion 23 and the drive shaft 2.

　このシール部材２５よりも駆動軸２の軸方向リア側、この例では、シール部材２５とベアリング２４との間の駆動軸２の周囲（ボス部２３内の駆動軸２が突出する空間のシール部材２５よりリア側の部分）には、低圧空間２６が形成されている。
　また、リア側のサイドブロック１３には、駆動軸２がベアリング１４を介して挿入される軸受け孔１３ａが形成され、この軸受け孔１３ａの終端部には、このリア側のサイドブロック１３と駆動軸２の端部とによって画成された軸端部空間１５が設けられている。 The axial rear side of the drive shaft 2 from the seal member 25, in this example, the periphery of the drive shaft 2 between the seal member 25 and the bearing 24 (the seal member in the space in which the drive shaft 2 in the boss portion 23 protrudes) A low-pressure space 26 is formed in the rear portion 25).
The rear side block 13 is formed with a bearing hole 13a into which the drive shaft 2 is inserted via a bearing 14, and the rear side block 13 and the drive shaft are formed at the end of the bearing hole 13a. A shaft end space 15 defined by the two ends is provided.

　なお、電磁クラッチ３３は、それ自体公知のもので、駆動軸２のハウジング部材２０（フロント側のサイドブロック２１）から突出した部分に、軸方向に取り付けられた板バネ３４を介してクラッチ板３５がプーリ３２の摩擦面３２ａに対峙して固定されている。クラッチ板３５は、プーリ３２に内包された励磁コイル３６への通電によりクラッチ板３５をプーリ３２に吸着し、このプーリ３２に与えられる走行用エンジンからの回転動力をクラッチ板３５及び板バネ３４を介して駆動軸２に伝達するようになっている。
　このクラッチ板３５のプーリ３２への吸着により、駆動軸２には、板バネ３４のバネ力によってリア側のサイドブロック１３側（リア側）へ向かう付勢力が付勢される。 The electromagnetic clutch 33 is known per se, and the clutch plate 35 is attached to a portion of the drive shaft 2 protruding from the housing member 20 (front side block 21) via a leaf spring 34 attached in the axial direction. Is fixed against the friction surface 32 a of the pulley 32. The clutch plate 35 attracts the clutch plate 35 to the pulley 32 by energization of the excitation coil 36 included in the pulley 32, and the clutch plate 35 and the leaf spring 34 receive the rotational power from the traveling engine applied to the pulley 32. Via the drive shaft 2.
Due to the adsorption of the clutch plate 35 to the pulley 32, the urging force toward the rear side block 13 (rear side) is urged to the drive shaft 2 by the spring force of the plate spring 34.

　前記ロータ３は、断面が真円状に形成され、その軸中心に設けられた挿通孔３ａに前記駆動軸２が挿通され、互いの軸中心を一致させた状態で駆動軸２に固定されている。また、シリンダ１２の軸中心とロータ３（駆動軸２）の軸中心とは、ロータ３の外周面とシリンダ１２の内周面（カム面１１）とが周方向の一箇所で当接するようにずらして設けられている（シリンダ１２の内径とロータ３の外径との差の１／２だけずらして設けられている）。そして、シリンダ１２とリア側のサイドブロック１３及びフロント側のサイドブロック２１とにより閉塞された空間には、シリンダ１２の内周面とロータ３の外周面との間に圧縮空間３０が画成されている。 The rotor 3 has a circular cross section, and the drive shaft 2 is inserted through an insertion hole 3a provided at the center of the rotor 3, and the rotor 3 is fixed to the drive shaft 2 in a state where the centers of the shafts coincide with each other. Yes. Further, the axial center of the cylinder 12 and the axial center of the rotor 3 (drive shaft 2) are such that the outer peripheral surface of the rotor 3 and the inner peripheral surface (cam surface 11) of the cylinder 12 abut at one place in the circumferential direction. They are shifted (they are shifted by a half of the difference between the inner diameter of the cylinder 12 and the outer diameter of the rotor 3). A compression space 30 is defined between the inner peripheral surface of the cylinder 12 and the outer peripheral surface of the rotor 3 in the space closed by the cylinder 12, the rear side block 13, and the front side block 21. ing.

　前記ロータ３の外周面には、複数のベーン溝８が形成され、それぞれのベーン溝８には、ベーン４が摺動自在に挿入されている。ベーン溝８は、ロータ３の外周面のみならずリア側のサイドブロック１３及びフロント側のサイドブロック２１と対峙する端面にも開口されており、底部には背圧室８ａが形成されている。このベーン溝８は、周方向に等間隔に複数形成されている。この例では、ベーン溝は、１８０度位相が異なる２箇所に互いに平行となるように形成されており、ベーン４を含む平面と、ベーン４と平行をなし駆動軸２の軸心を含む平面とが所定の距離だけ離れた状態（オフセットされた状態）で形成されている。 A plurality of vane grooves 8 are formed on the outer peripheral surface of the rotor 3, and the vanes 4 are slidably inserted into the respective vane grooves 8. The vane groove 8 is opened not only on the outer peripheral surface of the rotor 3 but also on the end surface facing the side block 13 on the rear side and the side block 21 on the front side, and a back pressure chamber 8a is formed at the bottom. A plurality of the vane grooves 8 are formed at equal intervals in the circumferential direction. In this example, the vane groove is formed so as to be parallel to each other at two places different in phase by 180 degrees, and a plane including the vane 4 and a plane including the axis of the drive shaft 2 parallel to the vane 4. Are formed in a state (offset state) separated by a predetermined distance.

　ベーン４は、駆動軸２の軸方向に沿った長さが前記ロータ３の軸方向の長さに等しく形成され、また、ベーン溝８への挿入方向（摺動方向）の長さは、ベーン溝８の同方向の長さに略等しく形成されている。このベーン４は、ベーン溝８の背圧室８ａに供給される後述するオイルにより、ベーン溝８から突出されて先端部がシリンダ１２の内周面（カム面１１）に当接可能となっている。 The vane 4 is formed such that the length along the axial direction of the drive shaft 2 is equal to the axial length of the rotor 3, and the length in the insertion direction (sliding direction) into the vane groove 8 is The groove 8 is formed approximately equal to the length in the same direction. The vane 4 is protruded from the vane groove 8 by oil, which will be described later, supplied to the back pressure chamber 8 a of the vane groove 8, and a tip portion thereof can come into contact with the inner peripheral surface (cam surface 11) of the cylinder 12. Yes.

　したがって、前記圧縮空間３０は、ベーン溝８に摺動自在に挿入されたベーン４によって複数の圧縮室３１に仕切られ、それぞれの圧縮室３１の容積は、ロータ３の回転によって変化するようになっている。 Therefore, the compression space 30 is partitioned into a plurality of compression chambers 31 by the vanes 4 slidably inserted into the vane grooves 8, and the volume of each compression chamber 31 changes as the rotor 3 rotates. ing.

　ところで、第２のハウジング部材２０には、作動流体（冷媒ガス）を外部から吸入する吸入口２７および外部へ吐出する吐出口２８が形成されている。また、フロント側のサイドブロック２１には、前記吸入口２７と連通し、フロント側のサイドブロックに隣接して設けられて圧縮される前の流体が導入される吸入室２９とが形成されている。 Incidentally, the second housing member 20 is formed with a suction port 27 for sucking working fluid (refrigerant gas) from the outside and a discharge port 28 for discharging the working fluid (refrigerant gas) to the outside. Further, the front side block 21 is formed with a suction chamber 29 that is connected to the suction port 27 and is provided adjacent to the front side block and into which fluid before being compressed is introduced. .

　また、第１のハウジング部材１０のシリンダ１２には、前記吸入室２９に連通して前記圧縮室３１に流体を吸入するための吸入ポート１６が形成されている。この吸入ポート１６は、ロータ３の外周面がシリンダ１２の内周面と当接する部位（ラジアルシール部４０）に対してロータ３の回転方向の前方側の近傍に形成されている。 Also, the cylinder 12 of the first housing member 10 is formed with a suction port 16 that communicates with the suction chamber 29 and sucks fluid into the compression chamber 31. The suction port 16 is formed in the vicinity of the front side in the rotational direction of the rotor 3 with respect to a portion (radial seal portion 40) where the outer peripheral surface of the rotor 3 comes into contact with the inner peripheral surface of the cylinder 12.

　さらに、第１のハウジング部材１０には、ラジアルシール部４０に対してロータ３の回転方向の後方側の近傍に、前記圧縮室で圧縮された流体を吐出するための吐出ポート１７が設けられている。また、第１のハウジング部材１０には、この吐出ポート１７を介して吐出された流体を吐出口２８に導く吐出室１８が形成されている。 Further, the first housing member 10 is provided with a discharge port 17 for discharging the fluid compressed in the compression chamber in the vicinity of the radial seal portion 40 on the rear side in the rotational direction of the rotor 3. Yes. Further, the first housing member 10 is formed with a discharge chamber 18 that guides the fluid discharged through the discharge port 17 to the discharge port 28.

　吐出室１８と吐出口２８との間には図示しないオイル分離器が配置されている。また、第１のハウジング部材１０のリア側のサイドブロック１３の下部と第２のハウジング部材２０のシェル２２の下部との間には、オイル分離器によって流体から分離された高圧オイルを溜めるオイル室１９が設けられている。 An oil separator (not shown) is disposed between the discharge chamber 18 and the discharge port 28. An oil chamber for storing high-pressure oil separated from the fluid by an oil separator is provided between the lower part of the rear side block 13 of the first housing member 10 and the lower part of the shell 22 of the second housing member 20. 19 is provided.

　なお、リア側のサイドブロック１３のロータ３の端面と対峙する面には、駆動軸２がベアリング１４を介して挿入される軸受け孔１３ａの開口周縁にリア側のオイル導入溝４１が形成されている。このリア側のオイル導入溝４１は、軸受け孔１３ａの開口周縁を凹ませて周方向に延設されているもので、ラジアルシール部４０が設けられた角度位置から吐出ポート１７が設けられた角度位置より手前までの所定の角度範囲（約２７０度の角度範囲）にかけて形成されている。また、このオイル導入溝４１は、絞り部を有するオイル連通路４２を介して前記オイル室１９と接続されている。 A rear-side oil introduction groove 41 is formed on the surface of the rear-side side block 13 that faces the end surface of the rotor 3 on the periphery of the bearing hole 13a into which the drive shaft 2 is inserted via the bearing 14. Yes. The rear-side oil introduction groove 41 extends in the circumferential direction with the opening periphery of the bearing hole 13a being recessed, and the angle at which the discharge port 17 is provided from the angular position at which the radial seal portion 40 is provided. It is formed over a predetermined angle range (an angle range of about 270 degrees) from the position to the front. The oil introduction groove 41 is connected to the oil chamber 19 via an oil communication path 42 having a throttle portion.

　したがって、吐出圧が高くなると、オイル室１９に貯留されている高圧オイルは、オイル連通路４２を介してリア側のサイドブロック１３に形成されたリア側のオイル導入溝４１に供給され、このリア側のオイル導入溝４１からベアリング１４等の摺動部分やロータ３の背圧室８ａに送り込まれるようになっている。前記ベーン４は、この背圧室８ａに送り込まれたオイルにより、シリンダ１２の内周面（カム面１１）に押し付けられ、したがって、安定した圧縮が確保されるようになっている。 Therefore, when the discharge pressure increases, the high-pressure oil stored in the oil chamber 19 is supplied to the rear-side oil introduction groove 41 formed in the rear-side side block 13 via the oil communication path 42, and this rear From the oil introduction groove 41 on the side, the sliding portion such as the bearing 14 and the back pressure chamber 8 a of the rotor 3 are fed. The vane 4 is pressed against the inner peripheral surface (cam surface 11) of the cylinder 12 by the oil fed into the back pressure chamber 8a, so that stable compression is ensured.

　さらに、フロント側のサイドブロック２１のロータ３の端面と対峙する面には、駆動軸２がベアリング２４を介して挿入される軸受け孔２１ａの開口周縁にフロント側のオイル導入溝４３が形成されている。このフロント側のオイル導入溝４３は、軸受け孔２１ａの開口周縁を凹ませて周方向に延設されているもので、ラジアルシール部４０が設けられた角度位置から吐出ポート１７が設けられた角度位置より手前までの所定の角度範囲（約２７０度の角度範囲）にかけて形成されている。また、このオイル導入溝４３は、ベーン４の先端部が吸入ポート１６に差し掛かる位置から吐出ポート１７に差し掛かる直前までの角度範囲にある場合にベーン溝８の底部（背圧室８ａ）と連通するようになっている。 Further, a front-side oil introduction groove 43 is formed on the opening periphery of the bearing hole 21 a into which the drive shaft 2 is inserted via the bearing 24 on the surface of the front-side side block 21 that faces the end surface of the rotor 3. Yes. The front-side oil introduction groove 43 extends in the circumferential direction with the opening periphery of the bearing hole 21a being recessed, and the angle at which the discharge port 17 is provided from the angular position at which the radial seal portion 40 is provided. It is formed over a predetermined angle range (an angle range of about 270 degrees) from the position to the front. Further, the oil introduction groove 43 is formed between the bottom of the vane groove 8 (back pressure chamber 8a) when the tip of the vane 4 is in an angular range from a position where the vane 4 reaches the suction port 16 to just before the discharge port 17 is reached. It comes to communicate.

　したがって、背圧室８ａに送り込まれたオイルは、この背圧室８ａがフロント側のオイル導入溝４３と連通する行程でフロント側のオイル導入溝４３に供給され、このフロント側のオイル導入溝４３を介してベアリング等の摺動部分に送り込まれるようになっている。
　なお、図２において、３７は、連結具６を螺合するねじ穴である。 Therefore, the oil fed into the back pressure chamber 8a is supplied to the front oil introduction groove 43 in a process in which the back pressure chamber 8a communicates with the front oil introduction groove 43. It is sent to sliding parts, such as a bearing, via.
In FIG. 2, reference numeral 37 denotes a screw hole into which the connector 6 is screwed.

　そして、このような構成において、フロント側のハウジング部材には、吸入室２９と低圧空間２６とを連通する連通路５１が設けられ、また、駆動軸２には、低圧空間２６と軸端部空間１５とを連通する通路５２が設けられている。具体的には、連通路５１は、吸入室２９から低圧空間２６にかけて駆動軸２に対して略垂直に穿設された通路によって構成されている。また、駆動軸２に設けられた通路５２は、駆動軸２の径方向に形成されて、一端が低圧空間２６に開口し他端が駆動軸２の中心まで延設された径方向穴５２ａと、駆動軸２の中央を軸方向に形成されて、一端が径方向穴５２ａに連通し他端が軸端部空間１５まで延設された軸方向穴５２ｂとを有して構成されている。 In such a configuration, the front housing member is provided with a communication passage 51 that communicates the suction chamber 29 and the low pressure space 26, and the drive shaft 2 has a low pressure space 26 and a shaft end space. 15 is provided. Specifically, the communication passage 51 is configured by a passage that is formed substantially perpendicularly to the drive shaft 2 from the suction chamber 29 to the low pressure space 26. A passage 52 provided in the drive shaft 2 is formed in the radial direction of the drive shaft 2, and has a radial hole 52 a having one end opened to the low-pressure space 26 and the other end extended to the center of the drive shaft 2. The center of the drive shaft 2 is formed in the axial direction, and has an axial hole 52b having one end communicating with the radial hole 52a and the other end extending to the shaft end space 15.

　したがって、低圧空間２６は、連通路５１を介して吸入室２９と連通しており、また、軸端部空間１５は、低圧空間２６と通路５２を介して連通しているので、低圧空間２６および軸端部空間１５は、吸入圧相当の圧力に保たれている。
　このため、電磁クラッチ３３が設けられている場合において、駆動軸２に動力が伝達される電磁クラッチ３３の吸着時には、ロータ３の軸方向の位置は、駆動軸２の前後両側に作用する圧力差と、電磁クラッチ３３の板バネ３４のバネ力と、が釣り合った位置となる。 Therefore, the low-pressure space 26 communicates with the suction chamber 29 via the communication passage 51, and the shaft end space 15 communicates with the low-pressure space 26 via the passage 52. The shaft end space 15 is maintained at a pressure corresponding to the suction pressure.
For this reason, in the case where the electromagnetic clutch 33 is provided, the position of the rotor 3 in the axial direction is the pressure difference acting on both the front and rear sides of the drive shaft 2 when the electromagnetic clutch 33 to which power is transmitted to the drive shaft 2 is attracted. And the spring force of the leaf spring 34 of the electromagnetic clutch 33 is in a balanced position.

　駆動軸２のフロント側は、フロント側のサイドブロック２１を介してハウジング５の外部（大気中）に突出しているので、駆動軸２のフロント端には、板バネ３４を介して大気圧が作用すると共に電磁クラッチ３３の板バネ３４のバネ力が作用している。これに対して、駆動軸２のリア端には吸入圧相当の圧力が作用するので、フロント側のサイドブロック２１側への付勢力は小さくなっており、したがって、軸方向の前後に作用する圧力差を小さくすることが可能となる。このため、駆動軸２の前後に作用する力をバランスさせ、ロータ３の軸方向前後のクリアランスの配分を適正な状態に保持することが可能となる。 Since the front side of the drive shaft 2 protrudes to the outside (in the atmosphere) of the housing 5 via the side block 21 on the front side, atmospheric pressure acts on the front end of the drive shaft 2 via the leaf spring 34. In addition, the spring force of the leaf spring 34 of the electromagnetic clutch 33 is acting. On the other hand, since a pressure corresponding to the suction pressure acts on the rear end of the drive shaft 2, the urging force to the side block 21 on the front side is small, and therefore the pressure acting in the axial direction front and rear. The difference can be reduced. For this reason, it is possible to balance the force acting on the front and rear of the drive shaft 2 and maintain the distribution of the clearance on the front and rear of the rotor 3 in the proper state.

　なお、以上の構成においては、ベーン４が２枚の場合の圧縮機について説明したが、３枚以上のベーン型圧縮機においても、同様の構成を採用することが可能である。また、２枚ベーンの構成においても、上述の例では、ベーン溝８（ベーン４）がオフセットして設けられた例を示したが、ベーン４を含む平面と、ベーン４と平行をなし駆動軸２の軸心を含む平面とを一致させる（オフセットを０にする）場合や、逆側にオフセットしている場合においても、同様の構成を採用してロータ３の軸方向前後のクリアランス配分を調整するようにしてもよい。 In the above configuration, the compressor in the case where there are two vanes 4 has been described. However, a similar configuration can be adopted in a three or more vane type compressor. In the above-described example, the vane groove 8 (vane 4) is offset in the two-vane configuration, but the plane including the vane 4 and the vane 4 are parallel to the drive shaft. The same configuration is adopted to adjust the clearance distribution before and after the rotor 3 in the axial direction even when the plane including the axis 2 is made coincident (offset is set to 0) or when offset to the opposite side. You may make it do.

　１　ベーン型圧縮機
　２　駆動軸
　３　ロータ
　４　ベーン
　５　ハウジング
　８　ベーン溝
　８ａ　背圧室　
　１０　第１のハウジング部材
　１１　カム面
　１２　シリンダ
　１３　リア側のサイドブロック
　１８　吐出室
　２０　第２のハウジング部材
　２１　フロント側のサイドブロック
　２９　吸入室
　３１　圧縮室 DESCRIPTION OF SYMBOLS 1 Vane type compressor 2 Drive shaft 3 Rotor 4 Vane 5 Housing 8 Vane groove 8a Back pressure chamber
DESCRIPTION OF SYMBOLS 10 1st housing member 11 Cam surface 12 Cylinder 13 Rear side block 18 Discharge chamber 20 Second housing member 21 Front side side block 29 Suction chamber 31 Compression chamber

Claims (3)

　ハウジングと、カム面が形成され、前記ハウジング内に設けられたシリンダと、前記シリンダの軸方向の両端を閉塞し、前記ハウジングに設けられた一対のサイドブロックと、前記一対のサイドブロックに回転自在に支持された駆動軸と、前記駆動軸に固装されて前記シリンダ内に回転可能に収容されるロータと、前記ロータに形成された複数のベーン溝と、前記ベーン溝に摺動自在に挿入され、先端が前記ベーン溝から出没して前記カム面を摺動する複数のベーンと、前記シリンダと前記一対のサイドブロックとにより閉塞された空間に、前記ロータと前記ベーンとによって形成される圧縮室と、前記一対のサイドブロックのうちのフロント側のサイドブロックに隣接して設けられ圧縮される前の流体が導入される吸入室と、前記フロント側のサイドブロックと前記駆動軸との間に設けられたシール部材と、前記シール部材よりも前記駆動軸の軸方向リア側に設けられ、前記吸入室と連通する低圧空間と、前記一対のサイドブロックのうちのリア側のサイドブロックと前記駆動軸の端部とによって画成された軸端部空間と、を備えたベーン型圧縮機において、
　前記駆動軸に、前記低圧空間と前記軸端部空間とを連通する通路を設けたことを特徴とするベーン型圧縮機。 A housing, a cam surface is formed, the cylinder provided in the housing, the both ends of the cylinder in the axial direction are closed, the pair of side blocks provided in the housing, and the pair of side blocks are rotatable. A drive shaft supported by the rotor, a rotor fixed to the drive shaft and rotatably accommodated in the cylinder, a plurality of vane grooves formed in the rotor, and a slidably inserted into the vane groove And a compression formed by the rotor and the vane in a space closed by the plurality of vanes whose front ends protrude from the vane grooves and slide on the cam surface, the cylinder, and the pair of side blocks. A suction chamber provided adjacent to a front side block of the pair of side blocks and into which fluid before being compressed is introduced; and the front A seal member provided between the side block and the drive shaft, a low-pressure space provided on an axial rear side of the drive shaft with respect to the seal member and communicating with the suction chamber, and the pair of side blocks A vane-type compressor comprising a rear end side block and a shaft end space defined by the end of the drive shaft,
A vane type compressor characterized in that a passage communicating the low pressure space and the shaft end space is provided in the drive shaft. 　前記駆動軸は、前記フロント側のサイドブロックを貫通して前記ハウジングの外部へ突出していることを特徴とする請求項１に記載のベーン型圧縮機。 2. The vane type compressor according to claim 1, wherein the drive shaft passes through the front side block and protrudes to the outside of the housing. 　前記ベーン型圧縮機は、内周面が真円に形成された前記シリンダ、及び、前記シリンダの軸方向の一端側を閉塞するリア側のサイドブロックが一体に形成された第１のハウジング部材と、前記シリンダの軸方向の他端側を閉塞するフロント側のサイドブロックが形成された第２のハウジング部材とを組み合わせてハウジングが構成され、
　前記一対のサイドブロックは、前記リア側のサイドブロックと前記フロント側のサイドブロックであることを特徴とする請求項１又は２のいずれかに記載のベーン型圧縮機。 The vane type compressor includes a first housing member integrally formed with the cylinder having an inner peripheral surface formed into a perfect circle and a rear side block that closes one end side in the axial direction of the cylinder. A housing is configured by combining with a second housing member formed with a front side block that closes the other axial end of the cylinder.
3. The vane compressor according to claim 1, wherein the pair of side blocks are a rear side block and a front side block. 4.
PCT/JP2014/065988 2013-06-27 2014-06-17 Vane compressor Ceased WO2014208398A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480034059.0A CN105308323B (en) 2013-06-27 2014-06-17 vane compressor
EP14818134.0A EP3015711A1 (en) 2013-06-27 2014-06-17 Vane compressor

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Application Number Priority Date Filing Date Title
JP2013134474A JP6242606B2 (en) 2013-06-27 2013-06-27 Vane type compressor
JP2013-134474 2013-06-27

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JP6510864B2 (en) * 2015-04-07 2019-05-08 株式会社Ｓｏｋｅｎ Cylinder rotary compressor

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JPS57110790A (en) * 1980-12-29 1982-07-09 Toyoda Autom Loom Works Ltd Vane compressor
JPS58163694U (en) * 1982-04-28 1983-10-31 日産自動車株式会社 Lubrication mechanism in rotary vane compressor
JPS60164684A (en) * 1984-02-08 1985-08-27 Hitachi Ltd Compressor for car air-conditioner
JPH051663A (en) * 1991-06-24 1993-01-08 Toshiba Corp Fluid compressor
JP2003184770A (en) * 2001-12-14 2003-07-03 Seiko Instruments Inc Gas compressor
JP2007064163A (en) 2005-09-02 2007-03-15 Valeo Thermal Systems Japan Corp Vane type compressor
JP2011137426A (en) * 2009-12-29 2011-07-14 Valeo Japan Co Ltd Vane type compressor
JP2013050038A (en) 2011-08-30 2013-03-14 Valeo Japan Co Ltd Vane-type compressor

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JPS57110790A (en) * 1980-12-29 1982-07-09 Toyoda Autom Loom Works Ltd Vane compressor
JPS58163694U (en) * 1982-04-28 1983-10-31 日産自動車株式会社 Lubrication mechanism in rotary vane compressor
JPS60164684A (en) * 1984-02-08 1985-08-27 Hitachi Ltd Compressor for car air-conditioner
JPH051663A (en) * 1991-06-24 1993-01-08 Toshiba Corp Fluid compressor
JP2003184770A (en) * 2001-12-14 2003-07-03 Seiko Instruments Inc Gas compressor
JP2007064163A (en) 2005-09-02 2007-03-15 Valeo Thermal Systems Japan Corp Vane type compressor
JP2011137426A (en) * 2009-12-29 2011-07-14 Valeo Japan Co Ltd Vane type compressor
JP2013050038A (en) 2011-08-30 2013-03-14 Valeo Japan Co Ltd Vane-type compressor

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JP6242606B2 (en) 2017-12-06
CN105308323B (en) 2017-05-31

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