WO2014192898A1 - スクリュー圧縮機及び冷凍サイクル装置 - Google Patents

スクリュー圧縮機及び冷凍サイクル装置 Download PDF

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Publication number
WO2014192898A1
WO2014192898A1 PCT/JP2014/064346 JP2014064346W WO2014192898A1 WO 2014192898 A1 WO2014192898 A1 WO 2014192898A1 JP 2014064346 W JP2014064346 W JP 2014064346W WO 2014192898 A1 WO2014192898 A1 WO 2014192898A1
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WIPO (PCT)
Prior art keywords
economizer
screw
slide valve
port
casing
Prior art date
Application number
PCT/JP2014/064346
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English (en)
French (fr)
Japanese (ja)
Inventor
下地　美保子
利秀 幸田
聡一 白石
和幸 塚本
雅章 上川
直人 上中居
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to EP14803724.5A priority Critical patent/EP3006740B1/de
Priority to CN201480030486.1A priority patent/CN105247217B/zh
Priority to JP2015519948A priority patent/JP6058133B2/ja
Publication of WO2014192898A1 publication Critical patent/WO2014192898A1/ja

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    • 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 present invention relates to a screw compressor and a refrigeration cycle apparatus that are used in a refrigeration cycle such as refrigeration and air conditioning, and that have an economizer function.
  • an intermediate cooler has been installed in the refrigeration cycle, and an economizer operation that sends economizer gas from the intermediate cooler to the compression chamber is performed.
  • a refrigeration cycle apparatus see, for example, Patent Document 1.
  • an example of an economizer cycle in which an economizer pipe connected to an economizer port provided in a casing of a screw compressor and economizer gas from an intermediate cooler is sent to a compression chamber is disclosed. .
  • the screw compressor of Patent Document 2 is provided with an economizer passage for injecting refrigerant gas from the intermediate cooler into the compression chamber.
  • an economizer port is provided on the inner surface side of the casing of the screw compressor, and an intermediate suction passage is provided on the outer surface side of the casing so as to communicate the outer surface of the casing and the slide groove in which the slide valve is accommodated.
  • a large diameter passage and a small diameter passage are provided in the slide valve.
  • JP-A-4-136663 page 3, FIG. 1
  • the coefficient of performance (capacity / power consumption) under rated conditions has been mainly used as an energy saving index of a refrigerator equipped with a screw compressor.
  • an index close to actual driving conditions, for example, a period performance coefficient IPLV (Integrated Part Load Value) determined in the United States has been attracting attention.
  • the operating time at rated conditions throughout the year is very short, and more than 90% of the operating time throughout the year is operated with partial load.
  • the partial load is mostly operated at 75 to 50% of the total load.
  • the refrigerant circulation flow rate and the operation compression ratio are different, and the coefficient of performance also changes.
  • the period performance coefficient has been attracting attention. That is, the period coefficient of performance is an index that emphasizes the coefficient of performance under partial load conditions.
  • the high and low differential pressure of the refrigeration cycle is large and large capacity operation
  • the high and low differential pressure of the refrigeration cycle is small and small capacity operation.
  • the coefficient of performance can be improved by performing economizer operation, but in partial load operation, the effect of the economizer operation decreases as the height differential pressure decreases, and the coefficient of performance deteriorates depending on the conditions. Therefore, the period coefficient of performance can be improved by switching driving / stopping of economizer operation in full load operation and partial load operation.
  • the economizer port diameter should be larger than the land width of the screw groove (groove crest width between adjacent screw grooves) so as not to be a leakage path between adjacent compression chambers when the economizer operation is stopped. It needs to be small. However, if the economizer port diameter is reduced, the flow rate cannot be secured this time during economizer operation. Therefore, based on these requirements for the economizer port, there has been a need for an improved economizer port design that is effective in achieving a high coefficient of performance over a wide operating range.
  • the present invention has been made to solve the above-described problems, and provides a screw compressor and a refrigeration cycle apparatus that can improve the position of the economizer port and achieve a high coefficient of performance over a wide operating range. With the goal.
  • the screw compressor according to the present invention has a discharge port formed therein, a casing having a cylindrical inner cylindrical surface portion, and rotatably accommodated in the inner cylindrical surface portion of the casing, and a plurality of screw grooves are provided in the outer peripheral portion.
  • An economizer channel formed in the casing and communicating between the outside of the casing and the slide groove; And an economizer port that communicates the economizer flow path to the compression chamber according to the position of the slide valve.
  • the slide valve advances the timing of the discharge start as it moves from the discharge side to the suction side.
  • the economizer port is provided at a position communicating with the suction pressure chamber when the slide valve is moved to the most suction side.
  • the slide valve in the state where the slide valve is at the most suction side, it is possible to make exactly the same state as a compressor not provided with an economizer port, and the re-expansion loss and economizer port generated at the economizer port can be reduced. There will be no increase in leakage. Therefore, the screw compressor which can implement
  • FIG. 3 is a cross-sectional view taken along line AA in FIG. 2. It is a perspective view which shows the discharge port 15 vicinity (accommodating part) of the screw compressor 100 which concerns on Embodiment 1 of this invention. It is explanatory drawing of the discharge port 15 vicinity of the screw compressor 100 which concerns on Embodiment 1 of this invention. It is explanatory drawing of the economizer port 12p vicinity which concerns on Embodiment 1 of this invention.
  • FIG. 6 is a pressure-specific enthalpy diagram when the high-low differential pressure is small in the partial load operation of the refrigeration cycle apparatus 200 according to Embodiment 1 of the present invention. It is explanatory drawing which shows the compression principle of the screw compressor 100 which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a refrigerant circuit diagram of a refrigeration cycle apparatus 200 including a screw compressor 100 according to Embodiment 1 of the present invention.
  • the same reference numerals are the same or equivalent, and this is common throughout the entire specification.
  • the forms of the constituent elements appearing in the entire specification are merely examples and are not limited to these descriptions.
  • the refrigeration cycle apparatus 200 includes a screw compressor 100 driven by an inverter 101, a condenser 102, a high-pressure unit of an intercooler 103, an expansion valve 104 that is a decompression device, and an evaporator 105 in order by refrigerant piping. It has a connected refrigerant circuit.
  • the refrigeration cycle apparatus 200 further branches from between the intermediate cooler 103 and the expansion valve 104 and is an economizer pipe connected to the screw compressor 100 via the intermediate cooler expansion valve 106 and the low pressure portion of the intermediate cooler 103. 107.
  • the condenser 102 cools and condenses the discharge gas from the screw compressor 100.
  • the expansion valve 104 squeezes and expands the liquid branched from the condenser 102.
  • the evaporator 105 evaporates the refrigerant that has flowed out of the expansion valve 104.
  • the intermediate cooler 103 exchanges heat between the high-pressure side refrigerant between the condenser 102 and the expansion valve 104 and the low-pressure side refrigerant obtained by decompressing part of the high-pressure side refrigerant with the expansion valve 106 for the intermediate cooler, to thereby exchange the high-pressure side refrigerant. Cool down.
  • the refrigeration cycle apparatus 200 further includes a control of the inverter 101, the expansion valve 104, the intercooler expansion valve 106, the control of the position of the slide valve 12 of the screw compressor 100, the driving and stopping of the economizer operation described later, and the like.
  • a control device 201 for controlling the entire device is provided.
  • FIG. 2 is a schematic cross-sectional view (planar cross-sectional view) of the screw compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a cross-sectional view taken along the line AA in FIG.
  • the screw compressor 100 includes a casing 1, a screw rotor 4, a gate rotor 7, an electric motor 8 that rotationally drives the screw rotor 4, a slide valve 12, and the like.
  • the casing 1 accommodates the screw rotor 4, the gate rotor 7, the electric motor 8, the slide valve 12, and the like.
  • the casing 1 is formed with a discharge port 15 (see FIG. 4 to be described later) that opens to the housing portion (inner cylinder surface portion) 1A. Details of the discharge port 15 will be described later.
  • a housing portion 1A which is a substantially cylindrical space, is formed inside the casing 1, and a substantially cylindrical screw rotor 4 is housed inside the housing portion 1A.
  • the screw rotor 4 has one end on the fluid suction side and the other end on the discharge side.
  • a plurality of screw grooves 10 are spirally formed on the outer peripheral surface of the screw rotor 4.
  • a rotating shaft 9 serving as a driving shaft is provided at the center of the screw rotor 4 so as to rotate integrally.
  • the rotating shaft 9 is rotatably supported by a high pressure side bearing 2 and a low pressure side bearing 3 provided in the casing 1.
  • An electric motor 8 whose frequency is controlled by, for example, an inverter (not shown) is connected to the end of the rotary shaft 9 on the low-pressure side bearing 3 side.
  • a pair of gate rotor support chambers 6 are formed in the casing 1 so as to face each other with the accommodating portion 1A (that is, the screw rotor 4) as a center.
  • Each gate rotor support chamber 6 accommodates a substantially disc-shaped gate rotor 7.
  • the gate rotor 7 is provided in the gate rotor support 5 accommodated in the gate rotor support chamber 6.
  • the gate rotor support 5 is disposed such that a central axis (rotating shaft) 5b thereof is substantially perpendicular to the rotating shaft 9 of the screw rotor 4, and is freely rotatable by a bearing 5a that is disposed to face the central shaft 5b in a spaced manner. It is supported.
  • the gate rotor 7 forms the compression chamber 11 together with the accommodating portion 1A and the screw rotor 4, and a plurality of gate rotor teeth 7a to be engaged with the screw grooves 10 are formed on the outer peripheral portion thereof. More specifically, the casing 1 is formed with a gate rotor opening 1a extending in the direction of the rotating shaft 9 (see FIG. 2). The gate rotor opening 1a is formed so as to extend along the inclination of the screw groove 10 on the back surface, and is connected to the suction wall 1c of the housing portion 1A forming the compression chamber on the back surface.
  • the outer periphery of the gate rotor 7 is inserted into a gate rotor opening 1 a provided in the casing 1. That is, the gate rotor teeth 7 a of the gate rotor 7 are inserted into the accommodating portion 1 ⁇ / b> A through the gate rotor opening 1 a and meshed with the screw groove 10. Thereby, a space surrounded by the gate rotor 7, the inner wall surface of the accommodating portion 1A and the screw rotor 4 (in other words, the gate rotor teeth 7a of the gate rotor 7 and the screw groove 10 partitioned by the accommodating portion 1A) is formed. This space becomes the compression chamber 11.
  • two slide grooves 14 extending in the direction of the rotary shaft 9 of the screw rotor 4 are formed on the inner wall surface of the casing 1, and the slide valve 12 is slidably accommodated in the slide groove 14.
  • the two slide grooves 14 are formed in a substantially cylindrical shape, and a part of the inner peripheral surface communicates with the accommodating portion 1A. These two slide grooves 14 are arranged to be rotated by 180 ° about the rotation shaft 9 of the screw rotor 4.
  • the slide valve 12 provided in the slide groove 14 is formed in a substantially cylindrical shape like the slide groove 14.
  • the slide valve 12 has a shape in which a part of a cylinder is cut out so that the facing surface 1e facing the housing portion 1A has a shape along the outer peripheral wall of the housing portion 1A.
  • the slide valve 12 is connected to a linear motion actuator (not shown) via a connecting portion 12 c, and the slide valve 12 is driven in the slide groove 14 by driving the linear motion actuator. Move in the direction.
  • FIG. 4 is a perspective view showing the vicinity (container) of discharge port 15 of screw compressor 100 according to Embodiment 1 of the present invention.
  • 4 is a perspective view as seen from the white arrow B side in FIG. 4A shows a state where the slide valve 12 is moved to the discharge side, and
  • FIG. 4B shows a state where the slide valve 12 is moved to the suction side.
  • a guide portion and the like connected to the connecting portion 12 c are not shown.
  • FIG. 5 is an explanatory view of the vicinity of the discharge port 15 of the screw compressor 100 according to Embodiment 1 of the present invention, and shows a state when the slide valve 12 is located closest to the suction side.
  • the “most suction side” here means the “most suction side” in the movement range of the slide valve 12 in adjusting the discharge timing, and the entire slide range of the slide valve 12 is defined. Does not necessarily match the “most inhalation side”. In other words, when the movement range of the slide valve 12 and the slide range of the slide valve 12 in adjusting the discharge timing are the same, they coincide, but otherwise, the “most suction side” here is the slide valve 12. In some cases, the position is closer to the discharge side than the “most suction side” of the slide range. In the following description, “most discharge side” has the same meaning.
  • the slide valve 12 is movably accommodated in the slide groove 14 (see FIG. 5) in parallel with the rotation shaft 9 (see FIG. 2), and changes the position of the discharge-side end surface 12 d of the slide valve 12.
  • the discharge start timing is adjusted. That is, the slide valve 12 slides to the suction side to accelerate the discharge start timing when the compression ratio is relatively small during partial load operation, and also when the compression ratio is relatively large during full load operation and partial load operation. In this case, the discharge start timing is delayed by sliding to the discharge side.
  • the discharge port 15 is formed by the inner wall surface of the opening 1B formed in the casing 1 (more specifically, the opening that opens in the housing 1A in the casing 1) and the discharge-side end surface 12d of the slide valve 12. Yes.
  • the discharge port 15 is defined as shown in FIG. That is, the discharge port 15 has a variable port 16 (thick hatched portion in the figure) and a fixed port 17 (thin hatched portion in the figure).
  • the variable port 16 is configured by a region of the discharge port 15 that opens to the same screw rotor central angle range ⁇ 1 as the slide valve 12. In other words, the variable port 16 is configured by a region portion of the discharge port 15 that overlaps with a region in which the facing surface 1e of the slide valve 12 is extended in the slide direction.
  • the variable port 16 varies the discharge start timing according to the position of the discharge side end of the slide valve 12.
  • the variable port 16 has a variable opening area according to the position of the discharge side end of the slide valve 12.
  • the fixed port 17 is an area other than the variable port 16 in the discharge port 15 and is a portion formed between the variable port 16 and the gate rotor 7 (see FIG. 4).
  • the mounting position of the slide valve 12 is defined as ⁇ 3,
  • the mounting position of the slide valve 12 is shown by an angle.
  • the lower limit of ⁇ 3 is set to a value larger than the conventional 30 ° which can increase the discharge area.
  • the upper limit of ⁇ 3 is an angle at which the slide valve 12 does not interfere with the gate rotor support component on the opposite surface. This changes depending on the size of the slide valve 12. For example, when the size of the slide valve 12 is the same as the conventional size (the central angle ⁇ 1 of the screw rotor 4 is about 40 ° in width), the upper limit of ⁇ 3 is 100 °.
  • the rotation side slide surface of the variable port 16 is defined as 16l
  • the counter-rotation side slide surface is defined as 16r
  • the suction side end surface of the fixed port 17 has a step, and hereinafter, it is defined as an inclined surface 17a and a vertical surface 17b from the variable port 16 side with the step portion as a boundary.
  • a portion including the inclined surface 17a is distinguished as a divided fixed port 17ax
  • a portion including the vertical surface 17b is distinguished as a divided fixed port 17bx.
  • the formation range of the divided fixed port 17bx is ⁇ 2 in the screw rotor central angle range, for example, about 10 °.
  • the screw compressor 100 further includes an economizer channel 50 (see FIG. 3) in the casing 1 for guiding the refrigerant gas from the intercooler 103 to the compression chamber 11 (screw groove 10 in the compression process).
  • the economizer channel 50 is provided in the casing 1 so as to communicate the outside of the casing 1 and the slide groove 14.
  • the economizer pipe 107 is connected to the economizer flow path 50, and the intermediate cooler 103 and the economizer flow path 50 are connected. Further, the screw compressor 100 is further provided with an economizer port 12 p in the cylindrical portion of the slide valve 12. As shown in the right diagram of FIG. 5, the economizer port 12 p has an inner peripheral surface that is a sliding contact surface with the screw rotor 4 in the slide valve 12 from an outer peripheral surface that is a sliding contact surface with the slide groove 14 in the slide valve 12. It is formed so as to penetrate through.
  • FIG. 6 is an explanatory diagram of the vicinity of the economizer port 12p according to the first embodiment of the present invention.
  • the economizer flow path 50 has a pipe line 50a connected to the economizer pipe 107 and a long groove 50b connected to the slide groove 14 side.
  • the long groove 50b is configured to extend along the slide surface of the slide valve 12, and the length l of the long groove 50b is set to a length corresponding to the slide valve control position in the operation range in which the economizer operation is performed.
  • the expansion valve 106 for the intermediate cooler is opened to allow the economizer pipe 107 and the screw compressor 100 to communicate with each other, and the economizer gas that has passed through the low pressure portion of the intermediate cooler 103 is supplied to the screw compressor 100. It is the operation
  • the groove width (length in the circumferential direction of the screw rotor) of the long groove 50b is made larger than the diameter d of the economizer port 12p as shown in the right figure of FIG.
  • the economizer port diameter d is set to the maximum diameter (not more than the minimum tooth thickness) that does not allow the adjacent compression chambers 11 of the screw rotor 4 to communicate with each other.
  • FIG. 7 is an explanatory diagram of the refrigeration cycle during the economizer operation of the refrigeration cycle apparatus 200 according to Embodiment 1 of the present invention.
  • FIG. 8 is a pressure-specific enthalpy diagram during full load operation of the refrigeration cycle apparatus 200 according to Embodiment 1 of the present invention.
  • the arrows in FIG. 7 indicate the flow of the refrigerant, the solid line is the refrigerant liquid, and the broken line is the refrigerant gas.
  • the refrigerant state at each numerical position in parentheses in FIG. 8 corresponds to the refrigerant state at each corresponding pipe position in FIG.
  • the refrigerant gas (1) having the pressure Ps exiting the evaporator 105 is sucked into the screw compressor 100, compressed to the pressure Pd, and then discharged.
  • the discharged refrigerant gas (5) is supercooled to the state (6) by the condenser 102.
  • the high-pressure supercooled liquid (6) enters the high-pressure part of the intercooler 103 and is further cooled to the state (8).
  • a part of the high-pressure liquid (8) discharged from the intermediate cooler 103 is branched and expanded by the intermediate cooler expansion valve 106 to the intermediate pressure Pm, and again in the state (7), the low-pressure portion of the intermediate cooler 103 is expanded. Flow into.
  • the refrigerant liquid (low-pressure side refrigerant) (7) that has flowed again into the low-pressure part of the intercooler 103 evaporates into a refrigerant gas (7a) by heat exchange with the high-pressure side refrigerant.
  • the refrigerant gas (7a) is injected into the screw groove 10 during compression from the economizer port 12p provided in the slide valve 12 via the economizer pipe 107 and the economizer flow path 50, and mixed with the compressed gas. ((2)-(3)).
  • FIG. 9 is a pressure-specific enthalpy diagram when the differential pressure difference is small in the partial load operation of the refrigeration cycle apparatus 200 according to Embodiment 1 of the present invention.
  • the intermediate pressure intermediate cooler outlet
  • the compression chamber is small as shown in FIG. The operation becomes unstable.
  • the effect of expanding the refrigerating capacity is small, and the power increase due to the economizer gas flowing in the middle of compression becomes larger and the coefficient of performance decreases. Therefore, under the condition where the high / low differential pressure is small, the intermediate cooler expansion valve 106 of FIG. 7 is closed so that the economizer operation is not performed.
  • FIG. 10 is an explanatory diagram showing the compression principle of the screw compressor 100 according to Embodiment 1 of the present invention.
  • the screw rotor 4 is rotated by a motor 8 (see FIG. 2) via a rotating shaft 9 (see FIG. 2), so that the gate rotor teeth 7a of the gate rotor 7 pass through the screw groove 10. Move relatively.
  • the suction stroke, the compression stroke, and the discharge stroke are set as one cycle, and this cycle is repeated.
  • each stroke will be described focusing on the compression chamber 11 shown in gray in FIG.
  • FIG. 10A shows the state of the compression chamber 11 during the suction stroke.
  • the lower gate rotor 7 shown in FIG. 10 rotates in the direction of the white arrow as the screw rotor 4 rotates.
  • the upper gate rotor 7 shown in FIG. 10 rotates in the opposite direction to the lower gate rotor 7 as indicated by a hollow arrow.
  • the compression chamber 11 has the largest volume, communicates with the low pressure space of the casing 1 (see FIG. 2), and is filled with low pressure refrigerant gas.
  • the gate rotor teeth 7a of the two gate rotors 7 sequentially rotate toward the discharge port 15 in conjunction with the rotation.
  • the volume (volume) of the compression chamber 11 is reduced as shown in FIG.
  • the slide valve 12 is not shown in FIG. 10 (b)
  • the variable port 16 is closed by the slide valve 12 in FIG. 10 (b)
  • the compression chamber 11 is more closed than in FIG. 10 (a). The volume is reduced and the refrigerant gas in the compression chamber 11 is compressed.
  • the compression chamber 11 communicates with the discharge port 15 as shown in FIG. As a result, the high-pressure refrigerant gas compressed in the compression chamber 11 is discharged from the discharge port 15 to the outside. Then, the same compression is performed again on the back surface of the screw rotor 4.
  • the gate rotor 7 and the gate rotor support chamber 6 on the opposite side (see FIG. 4). It communicates with the gate rotor 7 and the gate rotor support chamber 6), which are not shown, and has an intake pressure atmosphere.
  • a space (including the gate rotor support chamber 6) in the casing 1 that is not covered by the inner wall surface of the accommodating portion 1A and is in the suction pressure atmosphere is defined as a suction pressure chamber 1C.
  • FIGS. 11 and 12 are explanatory diagrams for explaining the relationship between the screw rotation angle and the economizer port 12p in the screw compressor 100 according to Embodiment 1 of the present invention.
  • FIG. 11 shows a state when the slide valve 12 is arranged on the discharge side (an operation state where the compression ratio is large such as full load operation).
  • FIG. 12 shows a state when the slide valve 12 is arranged on the suction side (an operation state in which the compression ratio is relatively small even in partial load operation).
  • FIGS. 11A to 11C and FIGS. 12A to 12C are development views of the outer peripheral surface of the screw rotor 4.
  • FIGS. 11D and 12D are CC cross-sectional views of FIGS. 11A and 12A.
  • FIG. 11 shows that the screw groove 10 has a rotation angle ⁇ A (1) ⁇ ⁇ A (2) ⁇ ⁇ A (3) ⁇ ⁇ A (4) ⁇ ⁇ A (5) ⁇ ⁇ A (6) ⁇ ⁇ A (7) ⁇ ⁇ A (8 ) ⁇ ⁇ A (9) in this order, and the volume of the screw groove 10 is reduced.
  • the screw groove 10 has a rotation angle ⁇ B (1) ⁇ ⁇ B (2) ⁇ ⁇ B (3) ⁇ ⁇ B (4) ⁇ ⁇ B (5) ⁇ ⁇ B (6) ⁇ ⁇ B (7) ⁇ ⁇ B (8 ) ⁇ ⁇ B (9) ⁇ ⁇ B (10) ⁇ ⁇ B (11), and the volume of the screw groove 10 is reduced.
  • the screw grooves B1 and B2 hatched with diagonal lines are the screw grooves 10 in the suction process. That is, the screw grooves B1 and B2 are in positions that are not completely closed by the gate rotor 7 and the inner wall surface of the accommodating portion 1A. Also, the screw grooves A1, A2, A3, and B3 filled in FIGS. 11 and 12 are screw grooves 10 in the compression process. Further, unfilled screw grooves A4 to A9 and B4 to B11 are screw grooves 10 in the discharging process. The substantial discharge area in the discharge process is the area of the area where the discharge port 15 and the screw groove 10 face each other, and is indicated by the grid lines in FIGS.
  • the economizer port 12p starts to communicate with the low-pressure screw groove A1 immediately after completing the suction.
  • the economizer port 12p travels on the screw grooves A2 ⁇ A3 during the compression stroke. While the economizer port 12p travels on the screw grooves A2 ⁇ A3, the economizer gas is injected from the economizer port 12p into the screw groove 10 due to the differential pressure between the intermediate pressure Pm and the screw groove 10.
  • the economizer port 12p is opened in the screw groove 10 which becomes high pressure, the intermediate pressure rises, and the capacity expansion effect (supercooling degree in (8) of FIG. 8) by the economizer operation becomes small. Therefore, here, the economizer gas is injected into the screw groove 10 as low as possible.
  • the economizer port 12p communicates with the screw groove 10 at the timing when the suction is almost completed. That is, as shown in FIG. 11A, the economizer port 12p starts to communicate with the screw groove A1 at the start of compression, passes through the screw grooves A2 and A3 during the compression process, and is completely screwed with the screw groove A4. This is repeated.
  • the economizer operation is performed by connecting the economizer flow path 50 provided in the casing 1 and the economizer port 12p under the condition that the differential pressure is relatively large even in the partial load operation and the economizer effect is obtained. .
  • the slide valve 12 is moved from the full load operation to the suction side or is positioned at the same slide position as the full load operation.
  • the economizer port 12p is always in communication with the suction pressure chamber 1C. Therefore, when the differential pressure is small in the partial load operation, the operation is performed in a state where the economizer port 12p is not involved in the screw groove 10 from the suction process to the discharge process.
  • Patent Document 2 as described above, re-expansion loss occurs when the economizer port passes over the screw groove in a state where the economizer operation is stopped.
  • the economizer port 12p since the economizer port 12p is not involved at all in the operation of stopping the economizer operation, it is possible to prevent the performance degradation due to the re-expansion loss. Further, the partial load operation has a small capacity, and the influence of leakage between adjacent compression chambers becomes remarkable.
  • the economizer port 12p is completely involved when the economizer operation is stopped. By eliminating, leakage between the screw grooves 10 due to passing through the economizer port 12p can be eliminated.
  • the economizer port 12p is provided at a position communicating with the compression chamber 11 and the economizer flow path 50 in a state where the slide valve 12 is located on the most discharge side.
  • an economizer port 12p is provided at a position communicating with the suction pressure chamber 1C in a state where the slide valve 12 is located on the most suction side.
  • FIG. 13 is an explanatory diagram in the vicinity of the slide valve 120 of the screw compressor 100 according to Embodiment 2 of the present invention.
  • differences from the first embodiment will be described, and configurations not described in the second embodiment are the same as those in the first embodiment.
  • FIG. 14 is a view showing a state in which the slide valve 120 according to Embodiment 2 of the present invention is arranged on the discharge side.
  • FIG. 15 is a diagram showing a state in which the slide valve 12 according to Embodiment 2 of the present invention is arranged on the suction side. Description of hatching and the like in FIGS. 14 and 15 is omitted because they are the same as those in FIGS.
  • the land width of the screw groove 10 in the angular range in which the variable port 16, that is, the slide valve 120 is provided Small compared to 1. Therefore, in the second embodiment, a plurality of economizer ports 120p are provided along the inclination of the screw groove 10 so as to secure the flow path area.
  • the economizer port 120p is provided at a position communicating with the compression chamber 11 and the economizer flow path 50 in a state where the slide valve 120 is located on the most discharge side. Further, as in the first embodiment, the economizer port 120p is provided at a position communicating with the suction pressure chamber 1C when the slide valve 120 is located on the most suction side.
  • variable port 16 is closed by the slide valve 120 as shown in FIG. 11, but in the second embodiment, the slide valve 120 opens the variable port 16 in order to secure the discharge area.
  • the economizer port 120p starts to communicate with the low-pressure screw groove A1 slightly before the completion of suction.
  • the economizer port 120p travels on the screw groove A2 ⁇ A3 during the compression stroke, and the economizer gas is injected from the economizer port 120p into the screw groove 10 with a differential pressure between the intermediate pressure Pm and the screw groove 10. .
  • the economizer port 120p has a diameter that does not allow the adjacent compression chambers 11 to communicate with each other, the diameter of the economizer port 120p can only be small, and the intermediate pressure increases to increase the capacity by the economizer operation ((8) in FIG. 8). The degree of supercooling) is reduced. Therefore, in the second embodiment, a plurality of economizer ports 120p are provided so that the inflow amount can be secured.
  • the economizer port 120p passes over the screw groove B1 and the screw groove B2 in the suction process, and slightly passes through the screw groove B3 at the start of compression.
  • the pressure increase amount of the screw groove 10 during this period is small, and the influence on the recompression loss and leakage loss is small.
  • the same effects as those of the first embodiment can be obtained, and the following effects can be obtained. That is, in the second embodiment (although the slide amount is smaller than in the first embodiment, the corresponding compression ratio width is reduced), the position of the slide valve 120 is closer to the gate rotor 7 side than in the first embodiment. It is possible to secure a space for creating another structural component or structure near the screw center angle of 90 °.
  • the land width of the screw groove 10 in the angular range in which the slide valve 120 is provided is the same as in the first embodiment. Smaller than that. In this case, in the design in which the economizer port diameter is smaller than the land width, the flow passage area cannot be secured if there is only one economizer port 120p. However, in the second embodiment, since a plurality of economizer ports 120p are provided along the inclination of the screw groove 10, a flow path area can be ensured.
  • the economizer flow path 50 and the economizer ports 12p and 120p are prevented from communicating with each other.
  • FIG. 15A when the slide valve is on the suction side, if the economizer pipe 107 is closed by the intercooler expansion valve 106 or the like, the economizer gas leaks to the suction side and the compression chamber of the suction gas 11 is not hindered. For this reason, the economizer flow path 50 and the economizer port 12p may be communicated with each other from the viewpoint of common parts and the like.
  • FIG. 16 is an explanatory view of a modified example of the diameters of the economizer ports 12p and 120p.
  • FIG. 16A is a development view of the inner wall surface of the accommodating portion 1A and the outer peripheral surface of the screw rotor 4, and FIG. A cross section is shown.
  • the economizer ports 12p and 120p have a diameter that does not allow the adjacent compression chambers 11 to communicate with each other.
  • the economizer ports 12p and 120p may be made larger than the land width as shown in FIG. 16 (a). In this case, the same effects as those of the first and second embodiments are obtained.
  • the screw compressor 100 that can achieve a high coefficient of performance in a wide operating range from a high compression ratio to a low compression ratio and that enables highly efficient operation throughout the year.
  • 1 casing 1A housing (inner cylinder surface), 1B opening, 1C suction pressure chamber, 1a gate rotor opening, 1aa gate rotor opening, 1c suction wall, 1e facing surface, 2 high pressure side bearing, 3 low pressure side Bearing, 4 screw rotor, 5 gate rotor support, 5a bearing, 5b central axis, 6 gate rotor support chamber, 7 gate rotor, 7a gate rotor teeth, 8 electric motor, 9 rotating shaft, 10 screw groove, 11 compression chamber, 12 slides Valve, 12c connecting part, 12d inclined surface (discharge side end surface), 12p economizer port, 14 slide groove, 15 discharge port, 16 variable port, 16l slide surface (rotation side slide surface), 16r anti-rotation side slide surface, 17 Fixed port, 17a inclined surface, 17ax split fixed port , 17b vertical surface, 17bx split fixed port, 50 economizer flow path, 50a conduit, 50b long groove, 100 screw compressor, 101 inverter, 102 condenser, 103 intermediate

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
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  • Fluid Mechanics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
PCT/JP2014/064346 2013-05-30 2014-05-29 スクリュー圧縮機及び冷凍サイクル装置 WO2014192898A1 (ja)

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JP2017538070A (ja) * 2014-12-11 2017-12-21 アンジェラントーニ テスト テクノロジーズ ソチエタ レスポンサビリタ リミタータ イン ショート エイティーティー ソチエタ レスポンサビリタ リミタータ 冷却装置用往復圧縮機
WO2020075220A1 (ja) * 2018-10-09 2020-04-16 株式会社前川製作所 スクリュ圧縮機及び冷凍装置

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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
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

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CN105247217A (zh) 2016-01-13
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CN105247217B (zh) 2017-03-15
EP3006740B1 (de) 2018-11-14
EP3006740A4 (de) 2017-01-04

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