• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    BACKGROUND OF THE INVENTION The invention relates to volumetric compressors or blowers designed to pressurize or purge vehicle heat engines. The purpose of the invention is the increase in compressor capacity. The central portion 9 of the housing is located at the inlet aperture diametrically with the outlet 6 and separates two annular sectors 4 and 5. The opening angle of each sector is 160-200. Such an expansion of the compressor allows, with a compact design and with a large step, complete insulation between inlet and outlet due to buffer channels in which the pressure increases gradually as it rotates to the nominal pressure of compression at the output limit, thus creating a constant discharge pressure strongly weakened by pulsation f-ly. 3 il. § SP / SAE 00 cm
    公开号:SU1378790A3
    申请号:SU853866549
    申请日:1985-03-20
    公开日:1988-02-28
    发明作者:Карре Жан-Жак；Леврэ Ролан
    申请人:Сосьете Аноним Д.Б.А. (Фирма)；
    IPC主号:
    专利说明:

    FIG. 3
    The invention relates to screw komfsessorov, in particular to volumetric compressors or blowers, designed to pressurize or purge the heat engines of motor vehicles.
    The purpose of the invention is to increase productivity.
    Figure 1 shows a compressor with ring sectors forming an air inlet; figure 2 is the same, with the outlet, top view; on fig.Z - compressor, general view.15
    The screw compressor includes a housing 1 with a working cavity formed by two connected cylindrical chambers 2 and 3, an inlet opening containing two sections in the form of 20 coaxially chambers 2 and 3 ring sectors 4 and 5, an outlet radial opening 6 of V-shape, covering -1H1 rotor 7, imick diy four turns, and covering the rotor 8, having six 25 planar z-axis planes and
    corresponding to the radius of the hub corresponding to 7 and 8.
    The turns of the rotors 7 and 8 have a rough or slightly asymmetrical fil.
    The edges 13 and 14 of the sectors 4 move t radially to the respective axes of the m and z and form between an angle of less than 90, usually the 80 sector 4 of the rotor 7 has a cover of L / less than 180, usually 165. And the circular sector 5 of the rolling rotor B has an angle of more than 180 °, but less usually around 190.
    The outlet 6 has a triangular profile from the base perpendicular to the axis z and the distance from the end 7 and 8, and the converging edge 1 t in the projection plane
    It is suitable for the threads of the rotor (Figures 2 and 3). The sides are tivally opposed to the base and pairs to it. The base in the center has a site 18. Output 6 of Fig. 2 is centered on the intersection of chambers 2 and has some asymmetry accounting for different amounts of p0 and 8.
    thirty
    35
    40
    turns.
    The housing 1 is provided with a central portion 9 located at the inlet aperture diametrically with the outlet 6 and separating the ring sectors 4 and 5.
    The opening angle of each sector 4 and 5 is 160-200 °.
    The male rotor 7 and the female rotor 8 have a helicoidal thread, made so that the coils of the rotor 7 interact with a light mutual contact with the coils of the rotor 8 in two parallel cylindrical chambers 2 and 3, communicating longitudinally along a plane of movement parallel to the axes z and z, common for the male rotor 7 and the camera 2 on the one hand and for the female rotor 8 and the camera 3 on the other hand. d
    According to an embodiment of the compressor, the rotors 7 and 8 at one of the ends are connected to a pair of gears 10 and 11, interacting without a gap and leading the rotors 7 and 8 into synchronous motion. Gear P of the rotor 8 is connected via a shaft 12 with a compressor drive (not shown).
    Each annular sector 4 and 5 has an outer profile, centered along the corresponding axes z and z, with a radius corresponding to the radii of chambers 2 and 3, and an inner profile in the form of an arc of a circle, also centered
    z and
    on the corresponding axes, or with a radius corresponding to the radius of the hub of the corresponding rotor 7 and 8.
    The turns of the rotors 7 and 8 have a symmetrical or slightly asymmetrical profile.
    The edges 13 and 14 of sectors 4 and 5 run radially to the corresponding axes of the z and z, forming an angle of less than 90 between them, usually 80. The ring sector 4 of the rotor 7 has an opening angle L / less than 180, usually around 165. And the annular sector 5 of the surrounding rotor B has an opening angle of more than 180 ° but less than 200 °, typically about 190.
    The outlet 6 has a common triangular profile with a base perpendicular to the axes z and z, at some distance from the ends of the rotors 7 and 8, and the converging edges 15 and 16 are projected in a plane parallel to the plane of the axes z and
    0
    five
    0

    0
    parallel to the threads of the rotors 7 and 8 (Figures 2 and 3). The side 17 is opposite to the base and parallel to it. The base in the center has a protruding portion 18. The outlet 6 (FIG. 2) is centered. Plane. the intersection bones of chambers 2 and 3, but has some asymmetry to account for different numbers of rotors 7 and 8.
    The maximum axial height of the hole 6 between the base and the side 17 is less than twice the axial distance between the two turns of the adjacent rotors 7 and 8 and is about 1.25 times the axial distance between the turns of the adjacent rotors 7 and 8. The total length of the rotors 7 and 8 corresponds to half the pitch of the turns of each rotor 7 and 8 (FIG. 3). Ring sectors 4. and 5 inlets are made in the wall 19. The coils of the rotors 7 and 8 form the channels 20 - 22i and the channels 23 - 26, respectively.
    The compressor works as follows.
    When the shaft 12 rotates in the direction indicated by the arrow with regard to the described arrangement, the channel 21 of the rotor 7 and the channel 25 of the rotor 8 communicate or enter one into the other, being isolated from their inlet ring sectors 4 and 5. The same applies to channels 22 and 26, which cease to be combined and begin to communicate with the corresponding sectors 4 and 5. In addition, the channel 20 is also locked by a wall 19, communicating with the channel 23 of the rotor 8, which, for its part, communicates with the inlet sector 5, and the channel 24 is completely closed. Therefore, the channels 21 and 25 remain closed half a turn of each rotor 7 and 8, thus fulfilling the role of buffer channels between sectors 4 and 5 and the outlet 6, while the air pressure in the channels 21 and 25 increases from the value equal to the atmospheric pressure, up to a nominal compression pressure of about 1.6 abs. bar at the limit of release. Thus, in a very compact arrangement and with a large pitch, complete isolation between inlet and outlet is achieved through buffer channels in which the pressure builds up gradually as it rotates to the nominal compression pressure at the release limit, thus creating a constant discharge pressure with very weak ripple.
    权利要求:
    Claims (7)
    [1]
    1. Screw volumetric compressor, comprising a housing with a working cavity formed by two interconnected cylindrical chambers, a frontal inlet, containing two sections in the form of coaxially chambers of annular sectors, and an outlet V-shaped radial outlet, which interact with the covered and cool 5 0 5
    0
    five
    „
    a roll-in rotor, having four and six turns, respectively, characterized in that, in order to increase productivity, the housing is provided with a central section located in the inlet opening diametrically with the opening opening separating two annular sectors, the opening angle of each of which is 160-200.
    [2]
    2. The compressor according to Clause I., of which is due to the fact that the converging edges of the outlet opening in the projection are made parallel to the turns of the rotors.
    [3]
    3. The compressor according to claim 1, wherein the maximum axial size of the outlet opening is 1-2 corresponding distances between two turns of the rotors.
    [4]
    4. The compressor according to Clause 3, of length, with the fact that said size is 1.25 of the specified distance.
    [5]
    5. The compressor according to claim 1, about T and - due to the fact that the angle of opening of the sector of the inlet from the side of the male rotor is no more than 180.
    [6]
    6. The compressor according to claim 1, wherein the opening angle of the inlet sector from the enclosing rotor is not less than 180.
    [7]
    7. The compressor according to claim 1, about t l and - due to the fact that the radial edges of the ring sectors opposite to the central section form an angle of 80 between them.
    1
    FIG. 2
    I GB 8
    one
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    同族专利:
    公开号 | 公开日
    DE3561761D1|1988-04-07|
    US4588363A|1986-05-13|
    AU566579B2|1987-10-22|
    EP0161130B1|1988-03-02|
    ES295665Y|1987-11-01|
    FR2562166B1|1986-07-18|
    FR2562166A1|1985-10-04|
    MX158277A|1989-01-18|
    AU4005085A|1985-10-03|
    EP0161130A1|1985-11-13|
    JP2589972B2|1997-03-12|
    ES295665U|1987-03-16|
    JPS60219486A|1985-11-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US2287716A|1941-04-22|1942-06-23|Joseph E Whitfield|Fluid device|
    US2410172A|1941-05-31|1946-10-29|Jarvis C Marble|Rotary screw wheel apparatus|
    CH325597A|1953-04-06|1957-11-15|Dresser Ind|Volumetric rotary machine|
    US3073514A|1956-11-14|1963-01-15|Svenska Rotor Maskiner Ab|Rotary compressors|
    GB959833A|1959-06-04|1964-06-03|Svenska Rotor Maskiner Ab|Improvements in or relating to screw rotor machines|
    US3108740A|1960-06-17|1963-10-29|Svenska Rotor Maskiner Ab|Regulating means for rotary piston compressors|
    US3414189A|1966-06-22|1968-12-03|Atlas Copco Ab|Screw rotor machines and profiles|
    GB1248031A|1967-09-21|1971-09-29|Edwards High Vacuum Int Ltd|Two-stage rotary vacuum pumps|
    DE1949175C3|1969-09-29|1973-10-11|Alexandr I. Borisoglebskij|
    GB1548663A|1975-06-24|1979-07-18|Maekawa Seisakusho Kk|Refrigerating apparatus|
    JPS5430520A|1977-08-12|1979-03-07|Hitachi Ltd|Screw compressor|
    JPS6340280B2|1982-11-25|1988-08-10|Hitachi Ltd|JP2501966Y2|1989-09-14|1996-06-19|小川精機株式会社|Supercharger|
    US6599112B2|2001-10-19|2003-07-29|Imperial Research Llc|Offset thread screw rotor device|
    US6786710B2|2002-08-27|2004-09-07|Carrier Corporation|Discharge porting for screw compressor with tangential flow guide cusp|
    JP2005315149A|2004-04-28|2005-11-10|Toyota Industries Corp|Screw type fluid machine|
    CN100417816C|2005-09-30|2008-09-10|浙江大学|Screw profile for high-flow high-pressure three-screw pump|
    CN100360808C|2005-09-30|2008-01-09|陈行|Unequal-tooth-number screw profile for high-flow high-pressure three-screw pump|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    FR8404841A|FR2562166B1|1984-03-28|1984-03-28|VOLUMETRIC SCREW COMPRESSOR|
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