EP3006740B1 - Schraubenverdichter und kühlkreisvorrichtung damit - Google Patents

Schraubenverdichter und kühlkreisvorrichtung damit Download PDF

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Publication number
EP3006740B1
EP3006740B1 EP14803724.5A EP14803724A EP3006740B1 EP 3006740 B1 EP3006740 B1 EP 3006740B1 EP 14803724 A EP14803724 A EP 14803724A EP 3006740 B1 EP3006740 B1 EP 3006740B1
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EP
European Patent Office
Prior art keywords
economizer
screw
slide valve
rotor
port
Prior art date
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Active
Application number
EP14803724.5A
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English (en)
French (fr)
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EP3006740A4 (de
EP3006740A1 (de
Inventor
Mihoko Shimoji
Toshihide Koda
Soichi SHIRAISHI
Kazuyuki Tsukamoto
Masaaki Kamikawa
Naoto UENAKAI
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3006740A1 publication Critical patent/EP3006740A1/de
Publication of EP3006740A4 publication Critical patent/EP3006740A4/de
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Publication of EP3006740B1 publication Critical patent/EP3006740B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • 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
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/50—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees
    • F04C18/52—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers

Definitions

  • the screw compressor according to Patent Literature 2 includes an economizer passage through which refrigerant gas from an intermediate cooling device is injected into the compression chamber.
  • an economizer port is provided in an inner-surface side of a casing of the screw compressor, and an intermediate suction passage is provided in an outer-surface side of the casing.
  • the intermediate suction passage allows the outer surface of the casing and a slide groove in which the slide valve is fitted to communicate with each other. Furthermore, the slide valve has a large-diameter passage and a small-diameter passage provided therein.
  • passages having different diameters are provided in the slide valve, and the resistance in the economizer passage is changed by utilizing the movement of the slide valve.
  • an intermediate pressure is raised in the small-capacity operation in which the pressure difference between the intermediate cooling device and the compression chamber is small, whereby a stable economizer operation is realized.
  • a hitherto mainstream energy-saving index for refrigerating machines including screw compressors is the coefficient of performance (capacity/power consumption) obtained under rated conditions (conditions at full load: 100 % load). Recently, however, an index obtained under conditions close to the actual operating conditions, for example, IPLV (integrated part load value) specified in the United States, has been attracting attention.
  • IPLV integrated part load value
  • FIG. 2 is a schematic cross-sectional view (sectional plan view) of the screw compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view taken along line A-A illustrated in FIG. 2 .
  • the casing 1 has a pair of gate-rotor-supporting chambers 6 provided across the housing portion 1A (i.e., the screw rotor 4) from each other.
  • the gate-rotor-supporting chambers 6 house the respective gate rotors 7, which each have a substantially disc-like shape.
  • the gate rotors 7 are provided on respective gate-rotor supports 5 housed in the respective gate-rotor-supporting chambers 6.
  • FIG. 4 includes perspective views illustrating a part around one of the discharge ports 15 (the housing portion) of the screw compressor 100 according to Embodiment 1 of the present invention.
  • the perspective views in FIG. 4 are seen in the direction of white arrow B illustrated in FIG. 3 .
  • FIG. 5 illustrates a configuration around the discharge port 15 of the screw compressor 100 according to Embodiment 1 of the present invention in a state where the slide valve 12 is positioned at the extreme end on the suction side.
  • the expression "extreme end on the suction side” used herein refers to “extreme end on the suction side” of the range within which the slide valve 12 moves for adjusting the timing of discharge, and does not necessarily coincide with “extreme end on the suction side” of the full slidable range of the slide valve 12.
  • the slide valve 12 is fitted in the slide groove 14 (see FIG. 5 ) in such a manner as to be movable parallel to the rotating shaft 9 (see FIG. 2 ).
  • the timing of starting discharge is adjusted by changing the position of a discharge-side end face 12d of the slide valve 12. That is, in a part-load operation and when the compression ratio is relatively low, the slide valve 12 slides toward the suction side, thereby advancing the timing of starting discharge.
  • the discharge port 15 is defined by the inner wall of an opening port 1B provided in the casing 1 (more specifically, an opening port provided in the housing portion 1A of the casing 1) and the discharge-side end face 12d of the slide valve 12.
  • the economizer port 12p extends through the slide valve 12 from the outer peripheral surface, which is a slide-contact surface with respect to the slide groove 14, to the inner peripheral surface, which is a slide-contact surface with respect to the screw rotor 4.
  • the refrigerant gas (1) discharged from the evaporator 105 and being at a pressure Ps is taken into the screw compressor 100, where the refrigerant gas is compressed to be at a pressure Pd and is discharged.
  • the thus discharged refrigerant gas (5) is subcooled to be in the state (6) by the condenser 102.
  • the high-pressure subcooled liquid (6) flows into the high-pressure section of the intermediate cooling device 103, where the subcooled liquid is further cooled to be in the state (8).
  • the refrigerant liquid (low-pressure-side refrigerant) (7) that has flowed into the low-pressure section of the intermediate cooling device 103 again evaporates by exchanging heat with the high-pressure-side refrigerant, thereby turning into refrigerant gas (7a).
  • the compressing power changes with the amount and the timing of the gas flowing into the screw compressor 100. Therefore, in terms of improving the coefficient of performance, it is important to increase the refrigeration capacity while suppressing the increase in compressing power as much as possible. Accordingly, there is an optimum intermediate pressure Pm.
  • FIG. 9 is a pressure-specific enthalpy diagram obtained when the refrigeration cycle apparatus 200 according to Embodiment 1 of the present invention is in part-load operation with a small difference between the high pressure and the low pressure.
  • the effect of increasing the refrigeration capacity becomes smaller than the increase in the power generated by the injection of the economizer gas during the compression. Consequently, the coefficient of performance is lowered.
  • the intermediate-cooling-device expansion valve 106 illustrated in FIG. 7 is closed so that the economizer operation is not performed.
  • the gate rotor 7 on the upper side in FIG. 10 rotates in the direction opposite to the direction of rotation of the gate rotor 7 on the lower side, as indicated by the white arrow.
  • the capacity of the compression chamber 11 is largest, the compression chamber 11 communicates with a low-pressure space of the casing 1 (see FIG. 2 ), and the compression chamber 11 is filled with a low-pressure refrigerant gas.
  • each of the variable ports 16 is closed by a corresponding one of the slide valves 12, and the capacity of the compression chamber 11 is smaller than in the state illustrated in FIG. 10(a) .
  • the refrigerant gas in the compression chamber 11 is compressed.
  • FIGS. 11 and 12 each illustrate the relationship between the angle of screw rotation and the economizer port 12p in the screw compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 11 includes diagrams illustrating a state where the slide valve 12 is positioned on the discharge side (an operating state in which the compression ratio is high, such as a case of the full-load operation).
  • FIG. 12 includes diagrams illustrating a state where the slide valve 12 is positioned on the suction side (an operating state in the part-load operation and in which the compression ratio is relatively low).
  • FIG. 11(a) to 11(c) and FIG. 12(a) to 12(c) are each a development of the outer peripheral surface of the screw rotor 4.
  • FIG. 11(d) and FIG. 12(d) are cross-sectional views taken along lines C-C illustrated in FIG. 11(a) and FIG. 12(a) , respectively.
  • screw grooves B1 and B2 that are hatched with oblique lines are each a screw groove 10 that is in the suction step. That is, the screw grooves B1 and B2 are each at a position that is not completely closed by the gate rotor 7 and the inner wall of the housing portion 1A.
  • screw grooves A1, A2, A3, and B3 that are shaded are each a screw groove 10 that is in the compression step.
  • Screw grooves A4 to A9 and B4 to B11 that are not shaded are each a screw groove 10 that is in the discharge step.
  • the substantial discharge areas in the discharge step correspond to the areas where the discharge port 15 faces the screw grooves 10, and are each hatched with a grid pattern in FIGS. 11 and 12 .
  • the economizer port 12p starts to communicate with the screw groove A1 that is in a state immediately after the completion of suction and is at a low pressure.
  • the economizer port 12p moves over the screw groove A2 and then the screw groove A3 that are in the compression step. While the economizer port 12p moves over the screw grooves A2 and A3, economizer gas is injected into each of these screw grooves 10 from the economizer port 12p because of the pressure difference between the intermediate pressure Pm and the screw groove 10.
  • the economizer operation is performed by allowing the economizer passage 50 provided in the casing 1 and the economizer port 12p to communicate with each other.
  • the slide valve 12 is moved further toward the suction side than in the full-load operation or to the same slide position as in the full-load operation.
  • Embodiment 1 produces the following advantageous effects.
  • the economizer port 12p is provided at a position where the economizer port 12p communicates with one of the compression chambers 11 and the economizer passage 50 when the slide valve 12 is positioned at the extreme end on the discharge side.
  • the economizer port 12p is provided at a position where the economizer port 12p communicates with the suction-pressure chamber 1C when the slide valve 12 is positioned at the extreme end on the suction side.
  • the coefficient of performance can be improved by performing the economizer operation.
  • a fixed port 170 according to Embodiment 2 includes only the sectioned fixed port 17bx described in Embodiment 1 and does not include the sectioned fixed port 17ax.
  • the variable port 16 is closed by the slide valve 120.
  • the slide valve 12 opens the variable port 16 so that a satisfactory discharge area is secured.
  • the economizer ports 120p start to communicate with the screw groove A1 that is in a state a little before the completion of suction and is at a low pressure.
  • the economizer ports 120p move over the screw groove A2 and then the screw groove A3 that are in the compression step, and economizer gas is injected into each of these screw grooves 10 from the economizer ports 120p because of the pressure difference between the intermediate pressure Pm and the screw groove 10.
  • the economizer ports 120p each need to have a diameter that does not allow adjacent ones of the compression chambers 11 to communicate with each other, the diameter becomes small. In that case, the intermediate pressure is raised, and the effect of increasing the capacity by performing the economizer operation (the degree of subcooling at point (8) in FIG. 8 ) is reduced.
  • the plurality of economizer ports 120p are provided, whereby a satisfactory amount of flow is secured.
  • Embodiment 1 and Embodiment 2 when the economizer operation is not performed, the economizer passage 50 and the economizer port 12p or the economizer ports 120p are not allowed to communicate with each other.
  • FIG. 15A when the slide valve is positioned on the suction side, if the economizer pipe 107 is closed by the intermediate-cooling-device expansion valve 106 or the like, there is no chance that the economizer gas may leak toward the suction side and prevent the suction gas from flowing into the compression chambers 11.
  • FIG. 16 includes diagrams illustrating a modification of the economizer port 12p or the economizer ports 120p in terms of the diameter thereof.
  • Part (a) is a development illustrating the inner wall of the housing portion 1A and the outer peripheral surface of the screw rotor 4.
  • Part (b) is a cross-sectional view taken along line d-d illustrated in part (a).
  • the economizer port 12p or the economizer ports 120p may be wider than the land width as illustrated in FIG. 16(a) .
  • Such a case also produces the advantageous effects produced in Embodiment 1 and Embodiment 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (6)

  1. Schraubenkompressor (100), der Folgendes aufweist:
    - ein Gehäuse (1), das eine Auslassöffnung (15) und einen zylindrischen inneren Zylinderflächenbereich aufweist;
    - einen Schraubenrotor (4), der in dem inneren Zylinderflächenbereich des Gehäuses (1) untergebracht ist, drehbar ist und eine Vielzahl von Schraubennuten (10) an einem äußeren Umfang hiervon aufweist;
    - einen Gate-Rotor (7), der Zahnbereiche aufweist, die an einem Außenumfang angeordnet sind und mit den Schraubennuten (10) in Eingriff kommen, wobei der Gate-Rotor (7) zusammen mit den Schraubennuten (10) und dem inneren Zylinderflächenbereich Kompressionskammern (11) definiert;
    - eine in dem Gehäuse (1) angeordnete Saugdruckkammer (1C), die eine erste Saugdruckatmosphäre aufweist;
    - eine Gleitnut (14) die an dem inneren Zylinderflächenbereich des Gehäuses (1) angeordnet ist und sich in Richtung einer rotierenden Welle (9) des Schraubenrotors (4) erstreckt;
    - ein Schiebeventil (12, 120), das in der Gleitnut (14) angeordnet ist und in Richtung der rotierenden Welle (9) des Schraubenrotors (4) verschiebbar ist, und wobei das Schiebeventil (12, 120) dazu ausgebildet ist, einen Zeitpunkt des Auslass-Beginns anzupassen;
    - einen Economiser-Durchgang (50), der in dem Gehäuse (1) angeordnet ist und es einem Äußeren von dem Gehäuse (1) und der Gleitnut (14) ermöglicht, miteinander in Verbindung zu stehen; und
    - einen Economiser-Anschluss (12p, 120p), der in dem Schiebeventil (12, 120) angeordnet ist und es dem Economiser-Durchgang (50) ermöglicht, mit einer der Kompressionskammern (11) gemäß einer Position des Schieberventils (12, 120) in Verbindung zu stehen,
    - wobei das Schieberventil (12, 120) den Zeitpunkt des Auslass-Beginns graduell vorantreibt, wenn das Schieberventil (12, 120) von einer Auslassseite in Richtung einer Saugseite verläuft, und
    - dadurch gekennzeichnet, dass der Economiser-Anschluss (12p, 120p) an einer Position angeordnet ist, an der der Economiser-Anschluss (12p, 120p) mit der Saugdruckkammer (1C) in Verbindung steht, wenn das Schieberventil (12, 120) an einem Extremende auf der Ansaugseite positioniert ist.
  2. Schraubenkompressor (100) gemäß Anspruch 1,
    wobei der Economiser-Anschluss (12p, 120p) an einer Position angeordnet ist, an der der Economiser-Anschluss (12p, 120p) mit einer der Kompressionskammer (11) und dem Economiser-Durchgang (50) in Verbindung steht, wenn das Schieberventil (12, 120) an einem Extremende auf der Auslassseite positioniert ist.
  3. Schraubenkompressor (100) gemäß Anspruch 1 oder 2,
    wobei Paare des Gate-Rotors (7) und des Schiebeventils (12, 120) ausgebildet sind, und eine Position eines Zentrums jedes Schiebeventils (12, 120) innerhalb eines Bereichs zwischen 30 Grad und 100 Grad eines Mittelwinkels des Schraubenrotors (4) fällt,
    wobei der Bereich durch die Position des Zentrums jedes Schiebeventils (12, 120) und die Position einer Endfläche einer Gate-Rotor-Öffnungsanschluss (1a) definiert ist, die eine von den in dem Gehäuse (1) angeordneten Öffnungen ist und in der einige der Zahnbereiche eines entsprechenden der Gate-Rotoren (7) positioniert sind.
  4. Schraubenkompressor (100) gemäß einem der Ansprüche 1 bis 3,
    wobei der Economiser-Anschluss (120p) einer von einer Vielzahl von Economiser-Anschlüssen (120p) ist, die entlang einer Neigung der Schraubennuten (10) angeordnet sind.
  5. Schraubenkompressor (100) gemäß einem der Ansprüche 1 bis 4,
    der ferner einen Motor (8) aufweist, der über eine Antriebswelle mit dem Schraubenrotor (4) verbunden ist und den Schraubenrotor (4) dreht,
    wobei der Motor (8) von einem Wechselrichter (101) angetrieben wird.
  6. Kältemittelkreislaufvorrichtung (200), die Folgendes aufweist:
    - einen Kältemittelkreislauf, in dem der Schraubenkompressor (100) gemäß einem der Ansprüche 1 bis 5, ein Kondensator (102), ein Hochdruckbereich einer Zwischenkühleinrichtung (103), eine Dekompressionseinrichtung (104) und ein Verdampfer (105) in der Reihenfolge ihres Auftretens mit Kältemittelleitungen miteinander verbunden sind; und
    - ein Economiser-Rohr (107), das von einem Punkt zwischen der Zwischenkühleinrichtung (103) und der Dekompressionseinrichtung (104) abgezweigt ist und über ein Zwischenkühleinrichtungs-Expansionsventil (106) und einen Niederdruckbereich der Zwischenkühleinrichtung (103) mit dem Economiser-Durchgang (50) des Schraubenkompressors (100) verbunden ist.
EP14803724.5A 2013-05-30 2014-05-29 Schraubenverdichter und kühlkreisvorrichtung damit Active EP3006740B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013113748 2013-05-30
PCT/JP2014/064346 WO2014192898A1 (ja) 2013-05-30 2014-05-29 スクリュー圧縮機及び冷凍サイクル装置

Publications (3)

Publication Number Publication Date
EP3006740A1 EP3006740A1 (de) 2016-04-13
EP3006740A4 EP3006740A4 (de) 2017-01-04
EP3006740B1 true EP3006740B1 (de) 2018-11-14

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EP (1) EP3006740B1 (de)
JP (1) JP6058133B2 (de)
CN (1) CN105247217B (de)
WO (1) WO2014192898A1 (de)

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CN106605069B (zh) * 2014-09-24 2019-07-12 三菱电机株式会社 螺杆压缩机以及制冷循环装置
JP6234611B2 (ja) * 2014-11-26 2017-11-22 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置
RU2690543C2 (ru) * 2014-12-11 2019-06-04 АНГЕЛАНТОНИ ТЕСТ ТЕКНОЛОДЖИЗ С.Р.Л., сокращённо АТТ С.Р.Л. Поршневой компрессор для охлаждающего устройства
JP6685379B2 (ja) * 2016-03-01 2020-04-22 三菱電機株式会社 スクリュー圧縮機および冷凍サイクル装置
DE102017115623A1 (de) * 2016-07-13 2018-01-18 Trane International Inc. Variable Economizereinspritzposition
CN106762633A (zh) * 2017-01-10 2017-05-31 麦克维尔空调制冷(苏州)有限公司 一种多螺杆式定频制冷压缩机
CN107461222A (zh) * 2017-09-13 2017-12-12 北京工业大学 一种集成滑阀的单螺杆膨胀机
DK3660314T3 (da) 2018-10-09 2022-03-28 Maekawa Seisakusho Kk Skruekompressor og køleindretning

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Publication number Publication date
EP3006740A4 (de) 2017-01-04
CN105247217B (zh) 2017-03-15
WO2014192898A1 (ja) 2014-12-04
JPWO2014192898A1 (ja) 2017-02-23
EP3006740A1 (de) 2016-04-13
JP6058133B2 (ja) 2017-01-11
CN105247217A (zh) 2016-01-13

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