• 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:
    In a meshing-screw compressor of the oil-injection type semi-rotary valve plates 2, 3 operated by a pair of servo-motors 4 (only one shown in Fig. 1) control the outlet port, the servo-motors in turn being controlled by a piston-actuated valve 5 in accordance with the pressure at the outlet end of the rotor chamber and the pressure in the delivery duct. The said pressures are applied to the valve's piston 6 through passages 18,19. Alternatively, there may be a single servo-motor operating one of the valve-plates. <IMAGE>
    公开号:SU1027430A1
    申请号:SU797770822
    申请日:1979-09-26
    公开日:1983-07-07
    发明作者:Моземанн Дитер
    申请人:Феб Кюльаутомат (Инопредприятие)；
    IPC主号:
    专利说明:

    2. A compressor according to claim 1, the servomotor of which comprises a working cylinder with a housing and a driving head, characterized in that the cylinder housing of the servomotor is arranged parallel to the plane of the end walls on the compression side.
    3. A compressor according to claim 1 with a control device and a valve device made as a multi-channel combination of valves and equipped with a control valve, characterized in that one cylinder chamber of the control device is connected to a compression chamber in the compressor.
    4. Compressor on PP. 1 and 3, characterized in that at least one wall of the control chamber has one channel that connects the compression chamber with a cross chamber, which is located in the compressor housing or in the end side of the flat distributor near the compressor housing, and the cross chamber through other channels connected to the corresponding chamber of the regulating piston cylinder.
    5. Compressor according to PP 1 and 2, characterized in that there is only one control device and the working cylinder chambers are connected in series.
    6. The compressor according to claim 6 with two working cylinders which work together with a flat distributor, characterized in that the piston space of one cylinder is connected to the piston space of the other cylinder, and both other cylinder chambers are connected to channels for supplying and discharging the working medium.
    7. The compressor on the PP. 1-7, characterized in that the cylinder chamber without a stem on the side of the main rotor and the cylinder chamber with a stem on the side of the auxiliary rotor are connected to the control device, and the other two cylinder chambers are connected by a pipeline.
    The invention relates to a power-controlled oil throughput screw compressor with at least one main rotor, which has convex concave teeth lying outside the pitch circle, and at least one secondary rotor, which has mainly concave teeth located inside the pitch circle, main and auxiliary rotors work in pairs. The body consists of side and end walls with inlets and outlets for the working medium controlled from the comb edges of the rotor, to which the suction chamber and the working chamber are attached. In known compressors, cavities and protrusions of the rotors form V-shaped suction and compression chambers. The working medium of the suction chamber, the base of which is directed to the end wall on the suction side, during rotation of the rotors flows through the entrances to the cavities of the gear wheel. During translational rotation, V-shaped working chambers (compression chambers) are reduced, the output of which is blocked by an end wall on the pressure side, so that an internal compression occurs. The vertices of the V-shaped chambers lie on the “contact line between the rotors. Depending on the position, shape and size of the outlet, the start of opening the V-shaped compression chamber in the direction of the working chamber is established. For such screw compressors, the pressure ratio achieved by internal compression and thus the final compression pressure for a specific working medium by internal compression depends on the volume ratio or on the position of the inlet or outlet edges. The operating conditions deviate from the calculated values, which leads to a loss of compression and a deterioration in efficiency. Although other known screw compressors are equipped with a device in which the internal pressure ratio to be achieved can be changed by moving the axial outer edges, they do not achieve complete agreement between the internal pressure and the external ratio and thus do not provide an optimal compression ratio. The purpose of the invention is to design the screw compressor so that at maximum performance, full internal pressure-to-external ratio between the pressure and suction nozzles is ensured, so that the screw compressor can operate continuously regardless of the operating state at the optimum compression ratio or almost the entire area with a high degree of compression.
    The technical task of the invention is to ensure that compressors with flat distributors, having parts of the edges of the outlet channel and located in the end wall of the working chamber on the discharge side, are displaced using an adaptation or device so that the final compression pressure P reached by internal compression is equal to or approximately equal to the pressure in the working chamber Pd, even in those cases when the operating conditions and partial load ratios in the compressors are changed.
    Distinctive features of the invention are that at least one flat valve on the drive side is connected to at least one servomotor and that this servomotor is driven by a working fluid in the machine for other purposes, and that at least one control device, preferably a valve, is provided , to control the servomotor, which, in turn, works through the final compression pressure or close to the final compression pressure chamber pressure and through the pressure difference (2i P) or Pol-P To from known working environments.
    According to this scheme, an optimum degree of compression is provided during operation at full load and at operation at partial load.
    The proposed device has a particularly advantageous design when the servomotor is designed as a hydraulic working cylinder, which is controlled through a multi-channel combination of valves, through which the working cylinder chambers can be filled with working fluid coming from a source of compression, or can be unloaded at a lower pressure point. . The combination of multi-channel valves contains a control piston that performs the appropriate control functions. The control piston with the transmission elements is in interaction with at least one regulating piston, on the end surfaces of which the pressure Pd and PX or PX act so that the resultant forces act against each other. A drive head is attached to the piston rod of the working cylinder, which is rigidly connected to the rod through the elements from the drive side and works together with the flat valve, and the working cylinder body is located in the pressure chamber parallel to the front wall plane on the pressure side.
    This drive connection scheme between the drive head and the flat distributor is implemented mainly through a pin, one end of which enters the 5 flat distributor and the other end holds the rotating transmission element, such as a roller, which enters the drive head, and, depending on the servomotor version, makes one-way or two-way transmission of effort. With this kind of compressor, the connecting channels between the working cylinders and the combination of multichannel valves have such an arrangement that, when the control piston is displaced due to
    5 of a low degree of internal compression, and thus a low pressure 1 or P connection channels open and flat valves are adjusted so that the internal compression increases, as a result of which the pressure P or P approaches the pressure in the discharge chamber PC {I provides maximum degree of compression is possible.
    The drop in pressure RK or Rsch in the injection chambers occurs predominantly
    5 through a channel in a flat distributor, which connects a compression chamber, i.e., a working chamber of a compressor, and a cross chamber, which is located in the compressor housing or in a flat fuse, the cross chamber connected to the corresponding cylinder cavity of the control piston. The device provides for a one-way servomotor, which adjusts the flat distribution, the divider only in higher pressure directions. The control discs are adjusted in the opposite direction when the servomotor is free from the load through the pressure difference between the suction pressure and the lower pressure in the compression chamber and the final compression pressure acting on the radial ends of the flat distributors.
    In another device according to the invention with at least two working cylinders each connected to the drive side with one control disk and a control device, the working cylinder chambers are arranged in such a way that one cylinder chamber is connected to the sub piston space of another cylinder. Both other cylinder chambers are connected to a control device. For adjustment, the working fluid from the control device is injected into the chamber of one cylinder, while from the chamber
    5 of another cylinder, the working fluid is directed to the control device.
    The sub-piston space of the working cylinder on the side of the main rotor and the sub-piston space of the working cylinder on the side of the auxiliary rotor is connected to the control device, and the other two chambers of the cylinder are connected via a pipeline. Due to the difference in piston surfaces, the distributor on the side of the auxiliary rotor turns at a smaller angle than that located on the side of the main rotor, and the edges of the outlet channel synchronously mix together according to the desired angle of rotation.
    FIG. 1 shows the proposed oil throughput screw compressor with power control, cross section; in fig. 2 is a section A-A in FIG. one; in fig. 3 shows the position of the working cylinders relative to the flow for synchronizing flat distributors.
    FIG. 1 and 2 shows the housing 1 (a partial view) in which the flat fuse 2 is placed on the side of the main rotor and the flat distributor 3 on the side of the auxiliary rotor, the radial ends 29 and 30 of which form parts of the edges 31 of the outlet channel.
    Through the drive elements 16 and 17, the working cylinder 4, used here as a servomotor, is connected on the drive side with a flat distributor 2. On the side of the auxiliary rotor, a similar servo drive is made. For controlling both working cylinders 4, a combination of multi-channel valves 5 is provided, through which the working cylinder 4 is moved. Channels 13, 22 and 24 or 35, 21 and 23 are connected to each other as well as channels 14 and 19. In view of the channel 18 is introduced into the chamber of the cylinder 42 of the adjusting piston b, and the channel 19 is inserted into the chamber of the cylinder 43 of the adjusting piston 6, in the chamber of the cylinder 43 there is a pressure close to and in the chamber of the cylinder 42 there is a pressure close to Pd. . Both pressures counteract each other. With too little internal compression, i. E; a low pressure P creates a resultant force acting to the right, so that the control piston 32 also shifts to the right and opens the channel 23, while the working medium in channel 26 flows through the channels 23 and 35 into the chamber 12 of the working cylinder 4 and moves the pores the working cylinder shaft, which causes the rotation of the flat distributor 2, and the control edge 28 are displaced in the direction of rotation of the main rotor, as a result of which the internal compression is increased. From cylinder 11, the working medium enters the channels 13, 24 and 27.
    If the pressure P in the chamber rises to the desired value, the resultant force on the adjustable pressure is
    zero, and the compressor is operating at optimum efficiency. With a high pressure Pj in the chamber, i.e., over-compression, the control operation proceeds similarly, but results in a decrease in pressure
    in the chamber. In order to determine the distance Rc in the chamber between the compression chambers and the channel 14, which is connected to the chamber of the cylinder 43 of the control valve 6, the channel 15 and the cross chamber 20 are made.
    The casing 8 of the working cylinder 4 is attached to the casing 1 by means of the thread 9. Gas tightness is provided by the sealing ring 10 between the casing 8 of the cylinder 4 and the casing 1. The drive head 7, in which the pin 33 captures the angular movable transmission element 34, simultaneously performs the function of a seal between the discharge camera 44 in which
    0, pressure P is set, and a cross-chamber 20 in which there is a pressure close to the pressure in chamber Pj. The control edge 28 of the outlet channel, which is the radial end of the flat distributor 2, is matched with the profile of the main rotor's not shown tooth, while the radial end 29 of the flat distributor 3 of the non-illustrated secondary rotor agrees more closely with the circumference
    0 45 with outer diameter of the rotor. The spring member 41 keeps the control piston 32 permanently in the plane of the connector 46 between the control piston 32 and the rod of the adjusting piston 47, so that between these two parts in both Directions there is a connection with the drive.
    To ensure favorable start-up conditions, a spring element is provided in the chamber of the cylinder 43. The item is designed so
    that when the machine is stopped, the adjusting piston 6 and the control piston 32 move to the end position, so that the channels 26, 22 and 13 are connected to supply the working fluid with the cylinder 11, and the flat valve 2 is brought to the end position against the direction of rotation of the rotor, since low power is required to start the compressor.
    FIG. 1 shows two control devices that operate respectively on a single flat dispenser; in fig. 3 is only one control device which, due to the series connection of the working cylinder chambers, controls both working cylinders.
    It is recognized as an invention according to the results of the examination carried out by the Office for the Invention of the German Democratic Republic.
    if 91013 f 20

    FIG. 2 1516
    权利要求:
    Claims (7)
    [1]
    1. ADJUSTABLE OIL-BYPASS SCREW COMPRESSOR with at least two screw rotors pairwise engaged with one another, equipped with protrusions and troughs, with a housing consisting of side and end walls with channels for the inlet and outlet of the working medium, which are adjoined by a suction and pressure head chamber, with flat distributors containing part of the exhaust channel and located on the housing of the discharge chamber, characterized in that at least one of the flat distributors is connected to the working link of the servomotor, rvodvigatel through the pressure line is connected to a device controlling the direction of movement of the working unit of the servo motor to a pressure source, wherein the one cylinder chamber control device is connected via a control line with the discharge port of the compressor or elsewhere with the level counterpressure P A, and the other chamber through the control line - with a camera compression.
    FIG. /
    [2]
    2. The compressor according to π. 1, the servomotor of which contains a working cylinder with a housing and a drive head, characterized in that the housing of the cylinder of the servomotor is placed parallel to the plane of the end walls from the compression side.
    [3]
    3. The compressor according to π. 1 with a control device and a valve device made as a multi-channel combination of valves and equipped with a control piston, characterized in that one cylinder chamber of the control device is connected to a compression chamber in the compressor.
    [4]
    4. The compressor according to paragraphs. 1 and 3, characterized in that at least one wall of the control chamber has one channel that connects the compression chamber to the cross chamber, which is located in the compressor housing or in the end side of the flat distributor located near the compressor housing, and the cross chamber is connected to other channels the corresponding cylinder chamber of the control piston.
    [5]
    5. Compressor 1 and 2, characterized in that there is only one control device and the chambers of the working cylinders are connected in series.
    [6]
    6. The compressor according to claim 6 with two working cylinders, which work together with a flat distributor, characterized in that the supra-piston space of one cylinder is connected to the sub-piston space of the other cylinder, and both other cylinder chambers are connected to channels for supplying and discharging the working medium.
    [7]
    7. The compressor according to paragraphs. 1-7, characterized in that the cylinder chamber without a rod on the side of the main rotor and the cylinder chamber with the rod on the side of the auxiliary rotor are connected to the control device, and both other cylinder chambers are connected by a pipeline.
    12
    类似技术:
    公开号 | 公开日 | 专利标题
    US5722815A|1998-03-03|Three stage self regulating gerotor pump
    US4042310A|1977-08-16|Screw compressor control means
    CA2649551C|2014-07-08|Air driven pump with performance control
    US4498852A|1985-02-12|Scroll type fluid displacement apparatus with improved end plate fluid passage means
    US5490770A|1996-02-13|Vane pump having vane pressurizing grooves
    US4065229A|1977-12-27|Variable capacity radial-4 compressor
    US4453900A|1984-06-12|Valve system for capacity control of screw compressors
    EP0977933B1|2003-07-02|Fluid machine
    US4222716A|1980-09-16|Combined pressure matching and capacity control slide valve assembly for helical screw rotary machine
    US4261691A|1981-04-14|Rotary screw machine with two intermeshing gate rotors and two independently controlled gate regulating valves
    US4611976A|1986-09-16|Capacity and internal compression control device in a screw compressor
    SU1027430A1|1983-07-07|Controlled oil-crossing-over screw compressor
    US8834140B2|2014-09-16|Leakage loss flow control and associated media flow delivery assembly
    US7963754B2|2011-06-21|Hydraulic machine
    GB2122687A|1984-01-18|Meshing-screw gas- compressor
    EP0154856B1|1989-08-23|Vane type compressor
    KR101789899B1|2017-10-25|Vane pump with multiple control chambers
    US4316707A|1982-02-23|Gerotor with valve plate attached to rotor
    USRE31379E|1983-09-13|Combined pressure matching and capacity control slide valve assembly for helical screw rotary machine
    EP0845080B1|2000-11-22|Outlet pressure control for internal gear pump
    US5052901A|1991-10-01|Lift valve in a rotary screw machine
    GB2221258A|1990-01-31|Rotary-piston machine
    SU962673A1|1982-09-30|Screw compressor
    US4813858A|1989-03-21|Gerotor pump with pressure valve and suction opening for each pressure chamber
    US6672850B2|2004-01-06|Torque control oil pump with low parasitic loss and rapid pressure transient response
    同族专利:
    公开号 | 公开日
    SE7908892L|1980-04-28|
    JPS5591793A|1980-07-11|
    DE2935954A1|1980-05-08|
    DD139280A1|1979-12-19|
    GB2035458A|1980-06-18|
    BG33240A1|1983-01-14|
    FR2439887A1|1980-05-23|
    PL219173A2|1980-06-02|
    DD139280B1|1981-05-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR951626A|1941-04-22|1949-10-31|Improvements in rotary screw pumps, motors and the like for fluids|
    US3286635A|1964-11-13|1966-11-22|Borg Warner|Reversible pressure hydraulic system|
    US3936239A|1974-07-26|1976-02-03|Dunham-Bush, Inc.|Undercompression and overcompression free helical screw rotary compressor|
    US4076461A|1974-12-09|1978-02-28|Dunham-Bush, Inc.|Feedback control system for helical screw rotary compressors|
    US4060343A|1976-02-19|1977-11-29|Borg-Warner Corporation|Capacity control for rotary compressor|SE464657B|1987-03-04|1991-05-27|Stal Refrigeration Ab|CONTROL SYSTEM FOR REGULATING A ROTATE COMPRESSOR'S INTERNAL VOLUME CONTAINER|
    SE469437B|1987-10-28|1993-07-05|Stal Refrigeration Ab|CONTROL SYSTEM FOR REGULATING A ROTATE COMPRESSOR'S INTERNAL VOLUME CONTAINER|
    DE102004009639A1|2004-02-27|2005-09-15|Rietschle Thomas Gmbh + Co. Kg|Rotary gear compressor, includes control device for altering cross section of additional outlet opening between outlet chamber and work region|
    DK1963678T3|2005-12-12|2011-10-31|Johnson Controls Denmark Aps|Screw Compressor|
    JP2019019671A|2015-03-16|2019-02-07|ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド|Screw compressor|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DD20871678A|DD139280B1|1978-10-27|1978-10-27|POWER-CONTROLLED OIL-REFLECTED SCREW COMPRESSOR WITH ADJUSTABLE BUILT-IN VOLUME RATIO|
    [返回顶部]