WO2020045068A1 - Liquid-cooled screw compressor - Google Patents

Liquid-cooled screw compressor Download PDF

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Publication number
WO2020045068A1
WO2020045068A1 PCT/JP2019/031728 JP2019031728W WO2020045068A1 WO 2020045068 A1 WO2020045068 A1 WO 2020045068A1 JP 2019031728 W JP2019031728 W JP 2019031728W WO 2020045068 A1 WO2020045068 A1 WO 2020045068A1
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WO
WIPO (PCT)
Prior art keywords
liquid
sectional area
rotor chamber
screw compressor
cross
Prior art date
Application number
PCT/JP2019/031728
Other languages
French (fr)
Japanese (ja)
Inventor
孝二 田中
透 野口
広宣 坂口
貴徳 今城
Original Assignee
株式会社神戸製鋼所
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
Priority claimed from JP2019077953A external-priority patent/JP7335089B2/en
Application filed by 株式会社神戸製鋼所 filed Critical 株式会社神戸製鋼所
Priority to KR1020217004176A priority Critical patent/KR102580244B1/en
Priority to SG11202100933SA priority patent/SG11202100933SA/en
Priority to CN201980056538.5A priority patent/CN112585358B/en
Publication of WO2020045068A1 publication Critical patent/WO2020045068A1/en

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    • 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
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • 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
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to a liquid-cooled screw compressor.
  • a liquid eg, oil
  • a liquid eg, oil
  • the oil supply port into the rotor chamber provided in the oil-cooled screw compressor disclosed in Patent Document 1 is a so-called drill hole, and has a straight pipe shape having a constant diameter between both ends.
  • a liquid-cooled screw compressor In a liquid-cooled screw compressor, power other than power for compressing air, such as power loss due to liquid agitation or power loss due to the viscosity of liquid in a narrow gap between the rotor chamber and the tooth portion of the screw rotor, is used. There is power loss. Due to these power losses, the use of a liquid-cooled type may rather reduce the efficiency.
  • the shape of the liquid supply port is a straight pipe shape as in the oil supply port of Patent Document 1
  • the screw rotor passes right above the liquid supply port during operation, the screw is supplied from the liquid supply port to the rotor chamber. Liquid flow is impeded and speed is reduced. Due to this speed reduction, the dispersibility of the liquid in the tooth space decreases, and the cooling efficiency of the compressed air may decrease.
  • the conventional liquid-cooled screw compressor has room for improvement in reducing the power required to compress air to a required pressure and improving cooling efficiency.
  • An object of the present invention is to reduce the power required for compressing air to a required pressure and improve cooling efficiency in a liquid-cooled screw compressor.
  • One embodiment of the present invention provides a rotor chamber provided in a casing and containing a pair of screw rotors, and a liquid supply provided in the casing to supply liquid supplied from a liquid supply line to the rotor chamber.
  • a liquid supply port an inlet portion fluidly communicating with the liquid supply line, an ejection portion fluidly communicating with the rotor chamber, and the inlet portion and the ejection portion.
  • An intermediate portion having a constant flow path cross-sectional area to be connected, wherein the flow path cross-sectional area of the opening of the injection portion with respect to the rotor chamber is larger than the flow path cross-sectional area of the intermediate portion, a liquid cooling type Provide a screw compressor.
  • the opening of the injection part of the liquid supply port with respect to the rotor chamber has a flow path cross-sectional area larger than the flow path cross-sectional area of the middle part of the liquid supply port.
  • the increase in the flow velocity promotes atomization when the liquid column collides with the tooth surface of the tooth portion of the screw rotor, increases the heat transfer area of the droplet, and improves the cooling efficiency for compressed air. Therefore, the power required to compress the air to the required pressure can be reduced.
  • the flow rate of the liquid injected into the rotor chamber can be increased while the volume flow rate of the liquid supplied to the liquid supply port remains the same, so that the power loss increases. Also does not occur.
  • the diameter of the injection section at the opening is larger than the width of the tooth section of the screw rotor perpendicular to the axis.
  • the “width perpendicular to the axis of the tooth portion” of the tooth portion of the screw rotor refers to the width of a smooth surface of the tip of the tooth portion in a cross section orthogonal to the rotor axis of the tooth portion.
  • the diameter of the intermediate portion may be 0.7 mm or more and 18 mm or less, and the diameter of the injection portion at the opening may be 4.0 times or less the diameter of the intermediate portion.
  • the diameter of the injection portion at the opening may be 1.5 times or more and 3.0 times or less the diameter of the intermediate portion.
  • the injection unit may have an inverse tapered shape in which the cross-sectional area of the flow path gradually increases from a portion connected to the intermediate portion toward the opening.
  • the injection section has a constant flow channel cross-sectional area from a portion connected to the intermediate portion to the opening, and the flow channel cross-sectional area is discontinuous at a portion connected to the intermediate portion of the injection portion. May be formed.
  • the liquid supply port is provided with a pipe member having both ends opened, which is inserted into a mounting hole penetrating from the liquid supply line provided in the casing to the rotor chamber, and the intermediate portion is defined by the pipe member.
  • An end face of the pipe member facing the rotor chamber may be located in the mounting hole, and the injection portion may be defined by the end face of the pipe member and a peripheral wall of the mounting hole.
  • the dimensional control during the processing of providing the liquid supply port in the casing is such that the casing itself is directly processed by excavation or the like, and the intermediate portion and the flow path cross-sectional area larger than the flow path cross-sectional area of the intermediate portion are processed. This is easier than in the case of forming an injection section provided at an opening to the rotor chamber. Higher quality stability can be ensured by easier dimensional control during processing. Also, by using different pipe members, the diameter of the middle part of the liquid supply port can be easily changed according to the product specifications.
  • processing of a step in which the flow path cross-sectional area increases discontinuously or processing of a taper shape in which the flow path cross-sectional area continuously increases is not required. Since only the formation of the mounting holes (through holes) is required, man-hours can be reduced.
  • the inlet may have a tapered shape in which a cross section of the flow path gradually decreases from a portion connected to the liquid supply line toward the intermediate portion.
  • the inlet portion has a constant flow path cross-sectional area larger than the flow path cross-sectional area of the intermediate portion, from a portion connected to the liquid supply line to a portion connected to the intermediate portion, and the inlet portion has A step where the cross-sectional area of the flow path is discontinuously reduced may be formed at a portion connected to the intermediate portion.
  • the cooling efficiency of the compressed air is improved, and the power required to compress the air to a required pressure can be reduced, that is, the efficiency can be improved.
  • FIG. 1 is a schematic plan view of an oil-cooled screw compressor according to a first embodiment of the present invention.
  • FIG. 2 is a sectional view taken along line II-II in FIG. 1.
  • FIG. 3 is a sectional view taken along line III-III in FIG. 1.
  • 1 is a schematic diagram of a compressor system including an oil-cooled screw compressor according to a first embodiment of the present invention. The enlarged view of the part V of FIG. Sectional drawing in the different cross section of the part V of FIG. The figure which looked at the filler port from the female rotor chamber. Sectional drawing similar to FIG. 5 of the conventional oil-cooled compressor.
  • FIG. 7 is a sectional view similar to FIG. 6 of a modified example of the first embodiment.
  • FIG. 7 is a sectional view similar to FIG.
  • FIG. 4 is a sectional view similar to FIG. 3 of an oil-cooled screw compressor according to a second embodiment of the present invention. Sectional drawing similar to FIG. 6 of 2nd Embodiment.
  • FIG. 7 is a sectional view similar to FIG. 6 of a modification of the second embodiment.
  • FIG. 7 is a sectional view similar to FIG. 6 of another modification of the second embodiment.
  • FIG. 4 is a sectional view similar to FIG. 3 of an oil-cooled screw compressor according to a third embodiment of the present invention.
  • FIG. 3 is a perspective view of an orifice tube. 4 is a graph showing a relationship between an oil amount and a sectional efficiency.
  • an oil-cooled screw compressor (liquid-cooled screw compressor) 1 according to a first embodiment of the present invention includes a male rotor chamber 2a and a female rotor chamber 2b spatially communicating with each other. And a casing 2 formed with the same.
  • the male rotor chamber 2a accommodates the male rotor 3
  • the female rotor chamber 2b accommodates the female rotor 4.
  • the casing 2 is provided with a suction port 2c and a discharge port 2d which are spatially communicated with the rotor chambers 2a and 2b.
  • the male rotor chamber 2a is defined by a cylindrical surface 2e and a pair of end surfaces 2g and 2h.
  • the female rotor chamber 2b is defined by a cylindrical surface 2f and a pair of end surfaces 2g and 2h common to the male rotor chamber 2a.
  • the male rotor (screw rotor) 3 includes a rotor shaft 3a and a plurality of spiral teeth 3b provided on the outer periphery of the rotor shaft 3a.
  • the female rotor 4 includes a rotor shaft 4a and a plurality of spiral teeth 4b provided on the outer periphery of the rotor shaft 4a.
  • a spiral tooth space 4c is defined between each pair of adjacent tooth portions 4b.
  • the rotor shaft 3a of the male rotor 3 is supported by bearings 5A and 5B so as to be rotatable around its own axis Lm.
  • the rotor shaft 4a of the female rotor 4 is also rotatably instructed about its own axis Lf by bearings 6A and 6B.
  • a drive mechanism 7 including a motor is mechanically connected to the rotor shaft 3a of the male rotor 3 on the suction port 2c side.
  • the teeth 3 b of the male rotor 3 mesh with the teeth 4 c of the female rotor 4 while meshing with each other, whereby the male rotor 3 and the female rotor 4 rotate synchronously.
  • the female rotor 4 may be rotationally driven by a drive mechanism.
  • the gas (air in the present embodiment) sucked from the suction port 2c is confined in a confined space defined by the tooth portions 3b of the male rotor 3 and the tooth grooves 4c of the female rotor 4, and the rotation of the rotors 3, 4 Accordingly, it is compressed while moving in the directions of the axes Lm and Lf, and is discharged from the discharge port 2d.
  • the casing 2 is provided with three oil supply ports (liquid supply ports) 11A, 11B, 11C for supplying oil (liquid) for cooling, lubrication, etc. to the female rotor chamber 2b.
  • These refueling ports 11A to 11C are open at the bottom of the female rotor chamber 2b, and are arranged on a straight line along the axis Lf of the female rotor 4 (also the axis of the female rotor chamber 2b).
  • the number of filler holes may be one or two, or four or more.
  • an oil supply port for the male rotor chamber 2a may be provided instead of or in addition to the oil supply port for the female rotor chamber 2b.
  • the filler ports 11A to 11C will be described later in detail.
  • the air discharged from the discharge port 2d contains oil.
  • the air discharged from the discharge port 2d is introduced into the separator 13 via the air pipe 12A.
  • the separator 13 air and oil are separated.
  • the air from which the oil has been separated is sent from the air pipe 12B to equipment or equipment that requires compressed air.
  • the oil separated from the air by the separator 13 is sent to an oil supply line (liquid supply line) 15 (a long hole formed in the casing 2 in the present embodiment) via the oil supply pipe 14. .
  • Oil is supplied from the oil supply line 15 to the female rotor chamber 2b via the oil supply ports 11A to 11C.
  • an oil pump 16 for feeding oil from the separator 13 to the oil-cooled screw compressor 1 is provided in the oil supply pipe 14.
  • the filler ports 11A to 11C will be described in detail.
  • the reference numeral 11 is used for one filler port unless it is necessary to particularly distinguish the three filler ports 11A to 11C.
  • the oil supply port 11 fluidly connects the oil supply line 15 to the female rotor chamber 2b.
  • the filler port 11 extends straight as a whole in a direction orthogonal to the axis Lm of the female rotor 4 (also the axis of the female rotor chamber 2b).
  • the refueling port 11 has an inlet 21 fluidly communicating with the refueling line 15, an ejection part 22 fluidly communicating with the female rotor chamber 2 b, and an intermediate part 23 fluidly connecting the inlet 21 and the ejection part 22. Is provided.
  • the shape of the cross section of the inlet 21 and the middle 23 orthogonal to the axis Li of the fuel filler 11 is circular.
  • This cross-sectional shape may be other than circular.
  • the inlet 21 has a constant diameter De
  • the intermediate part 23 also has a constant diameter Dm, and these diameters De and Dm are the same.
  • the flow channel cross-sectional areas Ae and Am are constant from the inlet 21 to the intermediate 23.
  • the injection unit 22 includes an opening 22a that opens into the female rotor chamber 2b, more specifically, the cylindrical surface 2f of the casing 2 that defines the female rotor chamber 2b.
  • the shape of the cross section of the injection unit 22 orthogonal to the axis Li of the fuel filler 11 is circular. This cross-sectional shape may be other than circular.
  • the injection portion 22 has a diameter Di that gradually increases from the portion 22b connected to the intermediate portion 23 toward the opening 22a.
  • the injection unit 22 has an inverse tapered shape in which the flow path cross-sectional area Ai gradually increases from the portion 22b where the injection unit 22 is connected to the intermediate portion 23 toward the opening 22a. Due to this inverted tapered shape, the flow path cross-sectional area Ai at the opening 22 a of the injection unit 22 is larger than the flow path cross-sectional area Am of the intermediate part 23.
  • the diameter Di of the opening 22a of the injection portion 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis.
  • the “shaft perpendicular tooth tip width” refers to the width of the smooth surface 4d of the tip of the tooth portion 4b in a cross section orthogonal to the axis Lf of the roach shaft 4a of the tooth portion 4b.
  • the diameter Dm of the intermediate portion 23 can be set to be 0.7 mm or more and 18 mm or less.
  • the diameter Di of the opening 22a of the injection unit 22 can be set to four times or less the diameter Dm of the intermediate part 23.
  • the diameter Di of the opening 22a of the injection unit 22 can be set to be 1.5 times or more and 3.0 times or less the diameter Dm of the intermediate part 23.
  • the oil supplied by the oil supply line 15 enters the oil supply port 11 through the oil supply port 11, flows into the intermediate part 23, and is injected from the end part 23a of the intermediate part 23 on the side of the female rotor chamber 2b.
  • the injected oil is supplied to the female rotor chamber 2b through the injection unit 22.
  • the diameter Di of the injection part 22 of the fuel filler port 11 with respect to the female rotor chamber 2b at the opening part 22a, that is, the flow path cross section Ai is larger than the diameter Dm of the intermediate part 23 of the fuel filler port 11, and thus the flow path cross sectional area Am.
  • the teeth 4 b of the female rotor 4 are connected to the oil supply port 11 during operation as compared with the case where the oil supply port 11 has a straight pipe shape (a so-called drill hole) in which the flow path cross section is constant between both ends.
  • the distance between the end 23a of the intermediate portion 23 on the female rotor chamber 2b side and the tip of the tooth portion 4b becomes long.
  • the flow rate of the oil injected into the female rotor chamber 2b can be increased without increasing the volume flow rate as compared with the case where the oil supply port 11 is a drilled hole. Due to this increase in flow velocity, atomization when the liquid column collides with the tooth surface of the tooth portion 4b of the female rotor 4 is promoted, the heat transfer area of oil droplets increases, and the cooling efficiency for compressed air improves. Therefore, the power required to compress the air to the required pressure can be reduced.
  • the flow rate of the oil injected into the female rotor chamber 2b can be increased while the volume flow rate of the oil supplied to the oil supply port 11 remains the same, so that the power loss does not increase.
  • the diameter Di of the opening 22a of the injection unit 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis. Therefore, when the tooth portion 4b of the female rotor 4 passes right above the oil filler port 11, the injection part 22 of the oil filler port 11 is not blocked by the smooth surface 4d of the tip of the tooth part 4b, and the female rotor 4 is more effectively Pressure loss during oil injection to the rotor chamber 2b can be reduced.
  • FIGS. 9 and 10 show a modification of the first embodiment.
  • the inlet 21 of the refueling port 11 has a taper shape in which the diameter De, and thus the flow path cross-sectional area Ae, gradually decreases from the portion 21 a connected to the refueling line 15 to the portion 21 b connected to the intermediate portion 23.
  • the diameter De and thus the flow path cross-sectional area Ae, gradually decreases from the portion 21 a connected to the refueling line 15 to the portion 21 b connected to the intermediate portion 23.
  • the inlet 21 of the fuel filler port 11 has a constant diameter De that is larger than the diameter Dm of the intermediate part 23 from the part 21 a connected to the fuel line 15 to the part 21 b connected to the intermediate part 23.
  • the inlet 21 has a constant flow cross-sectional area Ae that is larger than the flow cross-sectional area Am of the intermediate part 23 from the part 21a connected to the refueling line 15 to the part 21b connected to the intermediate part 23. Therefore, a step 25 is formed in a portion where the inlet 21 is connected to the intermediate part 23, where the cross-sectional area of the flow path decreases rapidly or discontinuously.
  • FIGS. 9 and 10 alleviates a sudden reduction in the flow path cross-sectional area when oil flows from the oil supply line 15 to the inlet 21 of the oil supply port 11, and reduces pressure loss. As a result, the flow rate of the oil injected into the female rotor chamber 2b can be increased more effectively without increasing the volume flow rate of the oil supplied to the oil supply port 11.
  • the injection part 22 of the oil supply port 11 includes the intermediate part from the part 22b connected to the intermediate part 23 to the opening part 22a. It has a constant diameter Di which is larger than the diameter Dm of 23.
  • the injection section 22 has a constant flow path cross-sectional area Ae that is larger than the flow path cross-sectional area Am of the intermediate section 23 from the portion 22b connected to the intermediate section 23 to the opening 22a. Therefore, a step 26 in which the cross-sectional area of the flow channel increases rapidly or discontinuously is formed at a portion of the injection unit 22 connected to the intermediate unit 23.
  • the opening 22a of the injection part 22 with respect to the female rotor chamber 2b has a flow path cross-sectional area Ae larger than the flow path cross-sectional area Am of the intermediate part 23, so that the injection part 22 is injected into the female rotor chamber 2b without increasing the volume flow rate.
  • Oil flow rate can be increased. This increase in speed improves the efficiency of cooling the compressed air and reduces the power required to compress the air to the required pressure. Further, since the flow rate of the liquid injected into the female rotor chamber can be increased while the volume flow rate of the oil supplied to the oil supply port 11 remains the same, the power loss does not increase.
  • the diameter Di of the opening 22a of the injection portion 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis, the smooth surface 4d of the tip end surface of the tooth portion 4b closes the injection portion 22. Therefore, the pressure loss at the time of oil injection into the female rotor chamber 2b can be reduced more effectively.
  • FIGS. 13 and 14 show a modification of the second embodiment.
  • the inlet 21 of the refueling port 11 has a constant flow larger than the flow path cross-sectional area Am of the intermediate part 23 from the part 21 a connected to the refueling line 15 to the part 21 b connected to the intermediate part 23. It has a road cross-sectional area Ae. For this reason, a step 25 where the flow path cross-sectional area is discontinuously reduced is formed at a portion of the inlet 21 connected to the intermediate portion 23.
  • the thickness THm of the intermediate portion 23 is larger than the sum of the thickness THe of the inlet portion 21 and the thickness THi of the injection portion 22.
  • the inlet 21 of the refueling port 11 has a tapered shape in which the diameter De, and thus the flow path cross-sectional area Ae, gradually decreases from the portion 21 a connected to the refueling line 15 to the portion 21 b connected to the intermediate portion 23.
  • the sudden reduction in the flow path cross-sectional area when oil flows from the oil supply line 15 to the inlet 21 of the oil supply port 11 is reduced, and the pressure loss is reduced.
  • the flow rate of the oil injected into the female rotor chamber 2b can be increased more effectively without increasing the volume flow rate of the oil supplied to the oil supply port 11.
  • the casing 2 is provided with a mounting hole 31 penetrating from the oil supply line 15 to the female rotor chamber 2b.
  • the mounting hole 31 is a circle having a constant diameter Da.
  • the end face 32b of the orifice tube 32 on the female rotor chamber 2b side is located in the mounting hole 31 and is depressed with respect to the cylindrical surface 2f defining the female rotor chamber 2b.
  • the end face 32 c of the orifice pipe 32 on the side of the oil supply line 15 is also located in the mounting hole 31.
  • the inlet 21 of the fuel filler port 11 is defined by the end face 32 c of the orifice pipe 32 and the hole peripheral wall 31 a of the mounting hole 31.
  • the shaft hole 32 a of the orifice pipe 32 constitutes an intermediate portion 23 of the fuel filler 11.
  • the injection portion 22 of the fuel filler 11 is defined by the end face 32 b of the orifice pipe 32 and the hole peripheral wall 31 a of the mounting hole 31.
  • the injection unit 22 in this embodiment has the same shape as that of the second embodiment.
  • a step 26 in which the cross-sectional area of the flow path increases discontinuously is formed at the intermediate portion 23, that is, at the portion where the shaft hole 32 a of the orifice tube 32 and the injection portion 22 are connected.
  • the inlet 21 in this embodiment has the same shape as that shown in FIG.
  • a step 25 where the flow path cross-sectional area is discontinuously reduced is formed at a portion where the inlet portion 21 is connected to the intermediate portion 23, that is, the shaft hole 32 a of the orifice tube 32.
  • the present embodiment has the following effects.
  • the dimension control at the time of forming the oil supply port 11 in the casing 2 is performed by directly processing the casing 2 itself by excavation or the like to cut the intermediate portion 23 and the flow path cross section larger than the flow path cross-sectional area of the intermediate portion 23. This is easier than forming the injection unit 22 having an area at the opening to the rotor chamber. Higher quality stability can be ensured by easier dimensional control during processing. Further, by using a different orifice pipe 32, the diameter Dm of the intermediate portion 23 of the fuel filler 11 can be easily changed according to the use of the product.
  • processing of a step where the cross-sectional area of the flow path increases discontinuously or processing of a tapered shape where the cross-sectional area of the flow path continuously increases is required.
  • the number of steps can be reduced.
  • test A test was performed to confirm the effects of the present invention.
  • the oil-cooled screw compressor 1 of the third embodiment (the oil supply port 11 is constituted by the orifice pipe 32 as shown in FIG. 15) and the oil-cooled screw compressor shown in FIG. 8 as a comparative example.
  • the machine 1 (the filler hole 11 was a drilled hole having a constant diameter) was used.
  • Each oil-cooled screw compressor 1 (75 KW) was actually operated with two kinds of circulating oil amounts, and the adiabatic efficiency (the ratio of the theoretical power consumption to the actual power consumption) was determined.
  • the discharge pressure of each oil-cooled screw compressor 1 was set to 0.7 MPa. Ambient temperature was 20 ° C.
  • the adiabatic efficiency when the circulating oil amount was operated at a predetermined oil amount Q 0 (L / min) and about 1.4 ⁇ Q 0 (L / min) was determined.
  • Fig. 18 shows the test results. As shown in FIG. 18, it was confirmed that the oil-cooled screw compressor 1 of the third embodiment improved the heat insulation efficiency by about 1% compared to the comparative example.
  • Oil-cooled screw compressor (liquid-cooled screw compressor) 2 Casing 2a Male rotor chamber 2b Female rotor chamber 2c Suction port 2d Discharge port 2e, 2f Cylindrical surface 2g, 2h End face 3 Male rotor 3a Rotor shaft 3b Teeth 4 Female rotor 4a Rotor shaft 4b Teeth 4c Tooth groove 4d Smooth surface 5A , 5B, 6A, 6B Bearing 7 Drive mechanism 11A, 11B, 11C Oil supply port (liquid supply port) 12A, 12B Air piping 13 Separator 14 Oil supply piping 15 Oil supply line (liquid supply line) Reference Signs List 16 Oil pump 21 Inlet 21a, 21b part 22 Injection part 22a Opening 22b part 23 Intermediate part 23a End part 25, 26 Step 31 Mounting hole 31a Hole peripheral wall 32 Orifice pipe 32a Shaft hole 32b, 32c End face

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

Abstract

A liquid-cooled screw compressor (1) is provided with a liquid supply port (11A) provided in a casing (2) in order to supply into a rotor chamber (2b) liquid supplied from a liquid supply line (15). The liquid supply port (11A) is provided with an inlet section (21) which fluidly communicates with the liquid supply line (15), an ejection section (22) which fluidly communicates with the rotor chamber (2b), and an intermediate section (23) which fluidly connects the inlet section (21) and the ejection section (22) and which has a certain flow passage cross-sectional area (Am). The flow passage cross-sectional area (Ai) of the opening (22a) of the ejection section (22), which is open to the rotor chamber (2b), is greater than the flow passage cross-sectional area (Am) of the intermediate section (23).

Description

液冷式スクリュー圧縮機Liquid-cooled screw compressor
　本発明は、液冷式スクリュー圧縮機に関する。 The present invention relates to a liquid-cooled screw compressor.
　油冷式スクリュー圧縮機のような液冷式スクリュー圧縮機では、潤滑と圧縮空気の冷却のために、ロータ室内に液体（例えば油）を供給し、雌雄ロータが噛み合いながら回転することにより構成される圧縮過程にある圧縮空気にその液体を混入させている。特許文献１に開示された油冷式スクリュー圧縮機が備えるロータ室内への給油口は、いわゆるキリ穴であり、両端間で直径が一定の直管形状である。 In a liquid-cooled screw compressor such as an oil-cooled screw compressor, a liquid (eg, oil) is supplied into a rotor chamber for lubrication and cooling of compressed air, and the male and female rotors rotate while meshing. The liquid is mixed with the compressed air in the compression process. The oil supply port into the rotor chamber provided in the oil-cooled screw compressor disclosed in Patent Document 1 is a so-called drill hole, and has a straight pipe shape having a constant diameter between both ends.
特開２０１４－２１４７４０号公報JP 2014-214740 A
　液冷式スクリュー圧縮機では、液体の撹拌による動力損失や、ロータ室とスクリューロータの歯部との間の狭小隙間における液体の粘性による動力損失のような、空気を圧縮するための動力以外の動力損失がある。これらの動力損失のために、液冷式とすることで、却って効率が低下し得る。 In a liquid-cooled screw compressor, power other than power for compressing air, such as power loss due to liquid agitation or power loss due to the viscosity of liquid in a narrow gap between the rotor chamber and the tooth portion of the screw rotor, is used. There is power loss. Due to these power losses, the use of a liquid-cooled type may rather reduce the efficiency.
　また、特許文献１の給油口のように、給液口の形状が直管形状であると、運転時にスクリューロータが給液口の真上を通り過ぎる際に、給液口からロータ室に供給される液体の流れが阻害され、速度が低下する。この速度低下により、歯溝内での液体の分散性が低下し、圧縮空気の冷却効率が低下し得る。 Further, when the shape of the liquid supply port is a straight pipe shape as in the oil supply port of Patent Document 1, when the screw rotor passes right above the liquid supply port during operation, the screw is supplied from the liquid supply port to the rotor chamber. Liquid flow is impeded and speed is reduced. Due to this speed reduction, the dispersibility of the liquid in the tooth space decreases, and the cooling efficiency of the compressed air may decrease.
　以上の理由より、従来の液冷式スクリュー圧縮機は、空気を所要圧力まで圧縮するために必要な動力の低減や、冷却効率の向上について、改善の余地がある。 For the above reasons, the conventional liquid-cooled screw compressor has room for improvement in reducing the power required to compress air to a required pressure and improving cooling efficiency.
　本発明は、液冷式スクリュー圧縮機において、空気を所要圧力まで圧縮するために必要な動力を低減することや、冷却効率を向上することを課題とする。 An object of the present invention is to reduce the power required for compressing air to a required pressure and improve cooling efficiency in a liquid-cooled screw compressor.
　本発明の一態様は、ケーシングに設けられ、一対のスクリューロータが収容されたロータ室と、給液ラインから供給される液体を前記ロータ室に供給するために、前記ケーシングに設けられた給液口とを備え、前記給液口は、前記給液ラインと流体的に連通する入口部と、前記ロータ室と流体的に連通する噴射部と、前記入口部と前記噴射部とを流体的に接続する、一定の流路断面積を有する中間部とを備え、前記噴射部の前記ロータ室に対する開口部の流路断面積は、前記中間部の前記流路断面積よりも大きい、液冷式スクリュー圧縮機を提供する。 One embodiment of the present invention provides a rotor chamber provided in a casing and containing a pair of screw rotors, and a liquid supply provided in the casing to supply liquid supplied from a liquid supply line to the rotor chamber. A liquid supply port, an inlet portion fluidly communicating with the liquid supply line, an ejection portion fluidly communicating with the rotor chamber, and the inlet portion and the ejection portion. An intermediate portion having a constant flow path cross-sectional area to be connected, wherein the flow path cross-sectional area of the opening of the injection portion with respect to the rotor chamber is larger than the flow path cross-sectional area of the intermediate portion, a liquid cooling type Provide a screw compressor.
　給液口の噴射部のロータ室に対する開口部は、給液口の中間部の流路断面積よりも大きい流路断面積を有する。この構成により、給液口が両端間で流路断面積が一定の直管形状（いわゆるキリ穴）である場合と比較して、運転時にスクリューロータの歯部が給液口の真上を通り過ぎる瞬間において、中間部のロータ室側の端部と歯先との距離が長くなる。言い換えれば、給液口から噴射された液体がスクリューロータの歯部（歯先）とケーシングの隙間を通過する際に、液体が通過し得る断面積が拡大する。従って、ロータ室への液噴射時の圧力損失が減少する。この圧力損失減少により、給液口へ供給される液体の体積流量を、給液口がキリ穴である場合と同一としたままで、ロータ室に噴射される液体の流速を増加できる。言い換えれば、体積流量を増加することなく、給液口がキリ穴である場合よりもロータ室に噴射される液体の流速を増加できる。この流速増加により、液柱がスクリューロータの歯部の歯面に衝突する際の微粒化が促進され、液滴の伝熱面積が増加し、圧縮空気に対する冷却効率が向上する。従って、空気を所要圧力まで圧縮するのに必要な動力を低減できる。 開口 The opening of the injection part of the liquid supply port with respect to the rotor chamber has a flow path cross-sectional area larger than the flow path cross-sectional area of the middle part of the liquid supply port. With this configuration, the teeth of the screw rotor pass right above the liquid supply port during operation, as compared with a case where the liquid supply port has a straight pipe shape (a so-called drilled hole) in which the flow path cross-sectional area is constant between both ends. At the moment, the distance between the end of the intermediate portion on the rotor chamber side and the tooth tip becomes long. In other words, when the liquid ejected from the liquid supply port passes through the gap between the tooth portion (tooth tip) of the screw rotor and the casing, the cross-sectional area through which the liquid can pass increases. Therefore, pressure loss at the time of liquid injection to the rotor chamber is reduced. Due to this pressure loss decrease, the flow rate of the liquid injected into the rotor chamber can be increased while keeping the volume flow rate of the liquid supplied to the liquid supply port the same as when the liquid supply port is a drilled hole. In other words, the flow velocity of the liquid injected into the rotor chamber can be increased as compared with the case where the liquid supply port is a drilled hole, without increasing the volume flow rate. The increase in the flow velocity promotes atomization when the liquid column collides with the tooth surface of the tooth portion of the screw rotor, increases the heat transfer area of the droplet, and improves the cooling efficiency for compressed air. Therefore, the power required to compress the air to the required pressure can be reduced.
　仮にロータ室へ噴射される液体の流速増加のために、給液口へ供給する液体の体積流量を増加すると、スクリューロータの歯部による液体の撹拌による動力損失や、スクリューロータの歯部（歯先）とケーシングとの間の狭小隙間における液体の粘性による動力損失を増加させてしまう。しかし、前述のように、本発明の一態様によれば、給液口へ供給する液体の体積流量は同一のままで、ロータ室に噴射される液体の流速を増加できるため、動力損失の増加も発生しない。 If the volume flow rate of the liquid supplied to the liquid supply port is increased in order to increase the flow velocity of the liquid injected into the rotor chamber, power loss due to agitation of the liquid by the tooth portion of the screw rotor and the tooth portion of the screw rotor (teeth) This increases the power loss due to the viscosity of the liquid in the narrow gap between (i) and the casing. However, as described above, according to one embodiment of the present invention, the flow rate of the liquid injected into the rotor chamber can be increased while the volume flow rate of the liquid supplied to the liquid supply port remains the same, so that the power loss increases. Also does not occur.
　好ましくは、前記噴射部の前記開口部における直径は、前記スクリューロータの歯部の軸直角歯先幅よりも大きい。 Preferably, the diameter of the injection section at the opening is larger than the width of the tooth section of the screw rotor perpendicular to the axis.
　本明細書において、スクリューロータの歯部の「軸直角歯先幅」とは、歯部のロータ軸と直交する断面における、歯部の先端が有する平滑面の幅をいう。開口部の直径を軸直角歯先幅よりも大きく設定したことにより、スクリューロータの歯部が給液口の真上を通り過ぎる際に、平滑面が給液口の噴射部を塞ぐことがないので、より効果的にロータ室への液噴射時の圧力損失を減少できる。 に お い て In the present specification, the “width perpendicular to the axis of the tooth portion” of the tooth portion of the screw rotor refers to the width of a smooth surface of the tip of the tooth portion in a cross section orthogonal to the rotor axis of the tooth portion. By setting the diameter of the opening to be larger than the width of the tooth tip perpendicular to the axis, the smooth surface does not block the injection part of the liquid supply port when the tooth part of the screw rotor passes right above the liquid supply port. Thus, the pressure loss at the time of liquid injection into the rotor chamber can be reduced more effectively.
　前記中間部の直径は０．７mm以上１８mm以下であり、前記噴射部の前記開口部における直径は、前記中間部の直径の４．０倍以下であってもよい。 The diameter of the intermediate portion may be 0.7 mm or more and 18 mm or less, and the diameter of the injection portion at the opening may be 4.0 times or less the diameter of the intermediate portion.
　特に、前記噴射部の前記開口部における直径は、前記中間部の直径の１．５倍以上３．０倍以下であってもよい。 Particularly, the diameter of the injection portion at the opening may be 1.5 times or more and 3.0 times or less the diameter of the intermediate portion.
　前記噴射部は、前記中間部と接続する部分から前記開口部に向けて前記流路断面積が漸増する、逆テーパ形状を有してもよい。 The injection unit may have an inverse tapered shape in which the cross-sectional area of the flow path gradually increases from a portion connected to the intermediate portion toward the opening.
　前記噴射部は、前記中間部と接続する部分から前記開口部までの前記流路断面積が一定であり、前記噴射部の前記中間部と接続する部分に、前記流路断面積が非連続的に増加する段差が形成されてもよい。 The injection section has a constant flow channel cross-sectional area from a portion connected to the intermediate portion to the opening, and the flow channel cross-sectional area is discontinuous at a portion connected to the intermediate portion of the injection portion. May be formed.
　前記給液口は、前記ケーシングに設けられた前記給液ラインから前記ロータ室まで貫通する取付穴に挿入された、両端開口の管部材を備え、前記管部材によって前記中間部が画定され、前記管部材の前記ロータ室に臨む端面は、前記取付穴内に位置し、前記管部材の前記端面と、前記取付穴の穴周壁によって前記噴射部が画定されてもよい。 The liquid supply port is provided with a pipe member having both ends opened, which is inserted into a mounting hole penetrating from the liquid supply line provided in the casing to the rotor chamber, and the intermediate portion is defined by the pipe member. An end face of the pipe member facing the rotor chamber may be located in the mounting hole, and the injection portion may be defined by the end face of the pipe member and a peripheral wall of the mounting hole.
　この構成により、給液口をケーシングに設ける加工時の寸法管理が、ケーシングそのものを直接、掘削等にて加工して、中間部と、その中間部の流路断面積より大きい流路断面積をロータ室に対する開口部に備えた噴射部を形成する場合に比べ、容易となる。加工時の寸法管理が容易になることで、より高度な品質安定性を確保できる。また、異なる管部材を使用することで、給液口の中間部の直径を、製品仕様に合わせて容易に変更できる。さらに、注液口を設けるためにケーシングに施す加工としては、流路断面積が非連続的に増加する段差の加工や、流路断面積が連続的に拡大するテーパ形状の加工を必要とせず、取付穴（貫通穴）の形成のみが要求されるため、工数削減を図ることができる。 With this configuration, the dimensional control during the processing of providing the liquid supply port in the casing is such that the casing itself is directly processed by excavation or the like, and the intermediate portion and the flow path cross-sectional area larger than the flow path cross-sectional area of the intermediate portion are processed. This is easier than in the case of forming an injection section provided at an opening to the rotor chamber. Higher quality stability can be ensured by easier dimensional control during processing. Also, by using different pipe members, the diameter of the middle part of the liquid supply port can be easily changed according to the product specifications. Further, as the processing to be performed on the casing to provide the liquid inlet, processing of a step in which the flow path cross-sectional area increases discontinuously or processing of a taper shape in which the flow path cross-sectional area continuously increases is not required. Since only the formation of the mounting holes (through holes) is required, man-hours can be reduced.
　前記入口部は、前記給液ラインと接続する部分から前記中間部に向けて流路断面が漸減する、テーパ形状を有してもよい。 入口 The inlet may have a tapered shape in which a cross section of the flow path gradually decreases from a portion connected to the liquid supply line toward the intermediate portion.
　前記入口部は、前記給液ラインと接続する部分から前記中間部と接続する部分まで、前記中間部の前記流路断面積よりも大きい一定の流路断面積を有し、前記入口部の前記中間部と接続する部分に、前記流路断面積が非連続的に減少する段差が形成されてもよい。 The inlet portion has a constant flow path cross-sectional area larger than the flow path cross-sectional area of the intermediate portion, from a portion connected to the liquid supply line to a portion connected to the intermediate portion, and the inlet portion has A step where the cross-sectional area of the flow path is discontinuously reduced may be formed at a portion connected to the intermediate portion.
　これらの構成により、給液ラインから給液口の入口部に液体が流入する際の流路断面積の急激な縮小が緩和され、圧力損失が低減される。その結果、より効果的に、給液口へ供給する液体の体積流量を増加することなく、ロータ室に噴射される液体の流速を増加できる。 に よ り With these configurations, the rapid reduction of the flow path cross-sectional area when the liquid flows from the liquid supply line to the inlet of the liquid supply port is reduced, and the pressure loss is reduced. As a result, the flow velocity of the liquid injected into the rotor chamber can be increased more effectively without increasing the volume flow rate of the liquid supplied to the liquid supply port.
　本発明に係る液冷式スクリュー圧縮機によれば、圧縮空気の冷却効率が向上し、空気を所要圧力まで圧縮するために必要な動力の低減、つまり効率改善を実現し得る。 According to the liquid-cooled screw compressor of the present invention, the cooling efficiency of the compressed air is improved, and the power required to compress the air to a required pressure can be reduced, that is, the efficiency can be improved.
本発明の第１実施形態に係る油冷式スクリュー圧縮機の模式的な平面図。FIG. 1 is a schematic plan view of an oil-cooled screw compressor according to a first embodiment of the present invention. 図１の線II－IIでの断面図。FIG. 2 is a sectional view taken along line II-II in FIG. 1. 図１の線III－IIIでの断面図。FIG. 3 is a sectional view taken along line III-III in FIG. 1. 本発明の第１実施形態に係る油冷式スクリュー圧縮機を含む圧縮機システムの模式図。1 is a schematic diagram of a compressor system including an oil-cooled screw compressor according to a first embodiment of the present invention. 図３の部分Ｖの拡大図。The enlarged view of the part V of FIG. 図３の部分Ｖの異なる断面での断面図。Sectional drawing in the different cross section of the part V of FIG. 給油口を雌ロータ室から見た図。The figure which looked at the filler port from the female rotor chamber. 従来の油冷式圧縮機の図５と同様の断面図。Sectional drawing similar to FIG. 5 of the conventional oil-cooled compressor. 第１実施形態の変形例の図６と同様の断面図。FIG. 7 is a sectional view similar to FIG. 6 of a modified example of the first embodiment. 第１実施形態の他の変形例の図６と同様の断面図。FIG. 7 is a sectional view similar to FIG. 6 of another modification of the first embodiment. 本発明の第２実施形態に係る油冷式スクリュー圧縮機の図３と同様の断面図。FIG. 4 is a sectional view similar to FIG. 3 of an oil-cooled screw compressor according to a second embodiment of the present invention. 第２実施形態の図６と同様の断面図。Sectional drawing similar to FIG. 6 of 2nd Embodiment. 第２実施形態の変形例の図６と同様の断面図。FIG. 7 is a sectional view similar to FIG. 6 of a modification of the second embodiment. 第２実施形態の他の変形例の図６と同様の断面図。FIG. 7 is a sectional view similar to FIG. 6 of another modification of the second embodiment. 本発明の第３実施形態に係る油冷式スクリュー圧縮機の図３と同様の断面図。FIG. 4 is a sectional view similar to FIG. 3 of an oil-cooled screw compressor according to a third embodiment of the present invention. 第３実施形態の図６と同様の断面図。Sectional drawing similar to FIG. 6 of 3rd Embodiment. オリフィス管の斜視図。FIG. 3 is a perspective view of an orifice tube. 油量と断面効率の関係を示すグラフ。4 is a graph showing a relationship between an oil amount and a sectional efficiency.
　（第１実施形態）
　図１から図３を参照すると、本発明の第１実施形態に係る油冷式スクリュー圧縮機（液冷式スクリュー圧縮機）１は、空間的に互いに連通する雄ロータ室２ａと雌ロータ室２ｂとが形成されたケーシング２を備える。雄ロータ室２ａには雄ロータ３が収容され、雌ロータ室２ｂには雌ロータ４が収容されている。また、ケーシング２には、ロータ室２ａ，２ｂに空間的に連通している吸込口２ｃと吐出口２ｄとが設けられている。 (1st Embodiment)
Referring to FIG. 1 to FIG. 3, an oil-cooled screw compressor (liquid-cooled screw compressor) 1 according to a first embodiment of the present invention includes a male rotor chamber 2a and a female rotor chamber 2b spatially communicating with each other. And a casing 2 formed with the same. The male rotor chamber 2a accommodates the male rotor 3, and the female rotor chamber 2b accommodates the female rotor 4. Further, the casing 2 is provided with a suction port 2c and a discharge port 2d which are spatially communicated with the rotor chambers 2a and 2b.
　雄ロータ室２ａは、円筒面２ｅと、一対の端面２ｇ，２ｈによって画定されている。また、雌ロータ室２ｂは、円筒面２ｆと、雄ロータ室２ａと共通の一対の端面２ｇ，２ｈによって画定されている。 The male rotor chamber 2a is defined by a cylindrical surface 2e and a pair of end surfaces 2g and 2h. The female rotor chamber 2b is defined by a cylindrical surface 2f and a pair of end surfaces 2g and 2h common to the male rotor chamber 2a.
　雄ロータ（スクリューロータ）３は、ロータ軸３ａと、ロータ軸３ａの外周に設けられた複数の螺旋状の歯部３ｂを備える。同様に、雌ロータ４は、ロータ軸４ａと、ロータ軸４ａの外周に設けられた複数の螺旋状の歯部４ｂを備える。互いに隣接する歯部４ｂの対の間には、螺旋状の歯溝４ｃがそれぞれ画定されている。雄ロータ３のロータ軸３ａは、軸受５Ａ，５Ｂによって、それ自体の軸線Ｌｍ回りに回転自在に支持されている。雌ロータ４のロータ軸４ａも、軸受６Ａ，６Ｂによって、それ自体の軸線Ｌｆ回りに回転自在に指示されている。 The male rotor (screw rotor) 3 includes a rotor shaft 3a and a plurality of spiral teeth 3b provided on the outer periphery of the rotor shaft 3a. Similarly, the female rotor 4 includes a rotor shaft 4a and a plurality of spiral teeth 4b provided on the outer periphery of the rotor shaft 4a. A spiral tooth space 4c is defined between each pair of adjacent tooth portions 4b. The rotor shaft 3a of the male rotor 3 is supported by bearings 5A and 5B so as to be rotatable around its own axis Lm. The rotor shaft 4a of the female rotor 4 is also rotatably instructed about its own axis Lf by bearings 6A and 6B.
　雄ロータ３の吸込口２ｃ側のロータ軸３ａには、モータを含む駆動機構７が機械的に接続されている。駆動機構７によって雄ロータ３が回転されると、雄ロータ３の歯部３ｂが雌ロータ４の歯溝４ｃに入り込んだ状態で噛み合い、それによって雄ロータ３と雌ロータ４が同期回転する。雄ロータ３に代えて、雌ロータ４を駆動機構によって回転駆動してもよい。 駆 動 A drive mechanism 7 including a motor is mechanically connected to the rotor shaft 3a of the male rotor 3 on the suction port 2c side. When the male rotor 3 is rotated by the driving mechanism 7, the teeth 3 b of the male rotor 3 mesh with the teeth 4 c of the female rotor 4 while meshing with each other, whereby the male rotor 3 and the female rotor 4 rotate synchronously. Instead of the male rotor 3, the female rotor 4 may be rotationally driven by a drive mechanism.
　吸込口２ｃから吸い込まれた気体（本実施形態では空気）は、雄ロータ３の歯部３ｂと雌ロータ４の歯溝４ｃによって画定される閉じ込み空間内に閉じ込められ、ロータ３，４の回転に伴って軸線Ｌｍ，Ｌｆ方向に移動しつつ圧縮され、吐出口２ｄから吐出される。 The gas (air in the present embodiment) sucked from the suction port 2c is confined in a confined space defined by the tooth portions 3b of the male rotor 3 and the tooth grooves 4c of the female rotor 4, and the rotation of the rotors 3, 4 Accordingly, it is compressed while moving in the directions of the axes Lm and Lf, and is discharged from the discharge port 2d.
　ケーシング２には、雌ロータ室２ｂに冷却、潤滑等のための油（液体）を供給するために３個の給油口（給液口）１１Ａ，１１Ｂ，１１Ｃが設けられている。これらの給油口１１Ａ～１１Ｃは、雌ロータ室２ｂの底部に開口しており、雌ロータ４の軸線Ｌｆ（雌ロータ室２ｂの軸線でもある。）に沿った直線上に配置されている。給油口の個数は１個又は２個でもよく、４個以上でもよい。また、雌ロータ室２ｂのための給油口に代えて、又はそれと併せて、雄ロータ室２ａのための給油口を設けてもよい。給油口１１Ａ～Ｃについては、後に詳述する。 The casing 2 is provided with three oil supply ports (liquid supply ports) 11A, 11B, 11C for supplying oil (liquid) for cooling, lubrication, etc. to the female rotor chamber 2b. These refueling ports 11A to 11C are open at the bottom of the female rotor chamber 2b, and are arranged on a straight line along the axis Lf of the female rotor 4 (also the axis of the female rotor chamber 2b). The number of filler holes may be one or two, or four or more. Further, instead of or in addition to the oil supply port for the female rotor chamber 2b, an oil supply port for the male rotor chamber 2a may be provided. The filler ports 11A to 11C will be described later in detail.
　給油口１１Ａ～１１Ｃから油を雌ロータ室２ｂに供給しているので、吐出口２ｄから吐出される空気には油が含まれている。図４を併せて参照すると、吐出口２ｄから吐出された空気は、空気配管１２Ａを介してセパレータ１３に導入される。セパレータ１３では、空気と油が分離される。油が分離された空気は、空気配管１２Ｂから圧縮空気を必要とする機器ないし設備へ送られる。セパレータ１３で空気から分離された油は、油供給配管１４を介して、ケーシング２に設けられた給油ライン（給液ライン）１５（本実施形態ではケーシング２に穿設した長孔）へ送られる。給油ライン１５から給油口１１Ａ～１１Ｃを経て、雌ロータ室２ｂに油が供給される。このように、油冷式スクリュー圧縮機１とセパレータ１３との間を油が循環する。本実施形態では、セパレータ１３から油冷式スクリュー圧縮機１へ送油するための油ポンプ１６が、油供給配管１４に設けられている。 Since oil is supplied to the female rotor chamber 2b from the oil supply ports 11A to 11C, the air discharged from the discharge port 2d contains oil. Referring also to FIG. 4, the air discharged from the discharge port 2d is introduced into the separator 13 via the air pipe 12A. In the separator 13, air and oil are separated. The air from which the oil has been separated is sent from the air pipe 12B to equipment or equipment that requires compressed air. The oil separated from the air by the separator 13 is sent to an oil supply line (liquid supply line) 15 (a long hole formed in the casing 2 in the present embodiment) via the oil supply pipe 14. . Oil is supplied from the oil supply line 15 to the female rotor chamber 2b via the oil supply ports 11A to 11C. Thus, oil circulates between the oil-cooled screw compressor 1 and the separator 13. In the present embodiment, an oil pump 16 for feeding oil from the separator 13 to the oil-cooled screw compressor 1 is provided in the oil supply pipe 14.
　次に、給油口１１Ａ～１１Ｃについて詳細に説明する。以下の説明では、３個の給油口１１Ａ～１１Ｃについて特に区別する必要がない場合、１個の給油口について参照番号１１を使用する。 Next, the filler ports 11A to 11C will be described in detail. In the following description, the reference numeral 11 is used for one filler port unless it is necessary to particularly distinguish the three filler ports 11A to 11C.
　図５から図７を参照すると、給油口１１よって給油ライン１５と雌ロータ室２ｂとが流体的に連通されている。給油口１１は、全体として、雌ロータ４の軸線Ｌｍ（雌ロータ室２ｂの軸線でもある。）に対して直交する方向に真直に延びている。 か ら Referring to FIGS. 5 to 7, the oil supply port 11 fluidly connects the oil supply line 15 to the female rotor chamber 2b. The filler port 11 extends straight as a whole in a direction orthogonal to the axis Lm of the female rotor 4 (also the axis of the female rotor chamber 2b).
　給油口１１は、給油ライン１５と流体的に連通する入口部２１、雌ロータ室２ｂと流体的に連通する噴射部２２、及び入口部２１と噴射部２２とを流体的に接続する中間部２３を備える。 The refueling port 11 has an inlet 21 fluidly communicating with the refueling line 15, an ejection part 22 fluidly communicating with the female rotor chamber 2 b, and an intermediate part 23 fluidly connecting the inlet 21 and the ejection part 22. Is provided.
　本実施形態では、入口部２１と中間部２３の、給油口１１の軸線Ｌｉに直交する断面の形状は円形である。この断面形状は、円形以外であってもよい。また、入口部２１は一定の直径Ｄｅを有し、中間部２３も一定の直径Ｄｍを有し、これらの直径Ｄｅ，Ｄｍは同一である。言い換えれば、入口部２１から中間部２３までの全体にわたって流路断面積Ａｅ，Ａｍが一定である。 で は In the present embodiment, the shape of the cross section of the inlet 21 and the middle 23 orthogonal to the axis Li of the fuel filler 11 is circular. This cross-sectional shape may be other than circular. In addition, the inlet 21 has a constant diameter De, and the intermediate part 23 also has a constant diameter Dm, and these diameters De and Dm are the same. In other words, the flow channel cross-sectional areas Ae and Am are constant from the inlet 21 to the intermediate 23.
　噴射部２２は雌ロータ室２ｂ、より具体的には雌ロータ室２ｂを画定するケーシング２の円筒面２ｆに開口する開口部２２ａを備える。本実施形態では、噴射部２２の、給油口１１の軸線Ｌｉに直交する断面の形状は円形である。この断面形状は、円形以外であってもよい。本実施形態では、噴射部２２は、中間部２３と接続する部分２２ｂから開口部２２ａに向けて漸増する直径Ｄｉを有する。言い換えれば、噴射部２２は、噴射部２２が中間部２３と接続する部分２２ｂから開口部２２ａに向けて流路断面積Ａｉが漸増する逆テーパ形状を有する。この逆テーパ形状により、噴射部２２の開口部２２ａにおける流路断面積Ａｉは、中間部２３の流路断面積Ａｍよりも大きい。 The injection unit 22 includes an opening 22a that opens into the female rotor chamber 2b, more specifically, the cylindrical surface 2f of the casing 2 that defines the female rotor chamber 2b. In the present embodiment, the shape of the cross section of the injection unit 22 orthogonal to the axis Li of the fuel filler 11 is circular. This cross-sectional shape may be other than circular. In the present embodiment, the injection portion 22 has a diameter Di that gradually increases from the portion 22b connected to the intermediate portion 23 toward the opening 22a. In other words, the injection unit 22 has an inverse tapered shape in which the flow path cross-sectional area Ai gradually increases from the portion 22b where the injection unit 22 is connected to the intermediate portion 23 toward the opening 22a. Due to this inverted tapered shape, the flow path cross-sectional area Ai at the opening 22 a of the injection unit 22 is larger than the flow path cross-sectional area Am of the intermediate part 23.
　噴射部２２の開口部２２ａにおける直径Ｄｉは、雌ロータ４の歯部４ｂの軸直角歯先幅Ｗｔよりも大きい。「軸直角歯先幅」とは、歯部４ｂのローチ軸４ａの軸線Ｌｆと直交する断面における、歯部４ｂの先端が有する平滑面４ｄの幅をいう。 直径 The diameter Di of the opening 22a of the injection portion 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis. The “shaft perpendicular tooth tip width” refers to the width of the smooth surface 4d of the tip of the tooth portion 4b in a cross section orthogonal to the axis Lf of the roach shaft 4a of the tooth portion 4b.
　中間部２３の直径Ｄｍは０．７mm以上１８mm以下に設定できる。噴射部２２の開口部２２ａにおける直径Ｄｉは、中間部２３の直径Ｄｍの４倍以下に設定できる。特に、噴射部２２の開口部２２ａにおける直径Ｄｉは、中間部２３の直径Ｄｍの１．５倍以上３．０倍以下に設定できる。 直径 The diameter Dm of the intermediate portion 23 can be set to be 0.7 mm or more and 18 mm or less. The diameter Di of the opening 22a of the injection unit 22 can be set to four times or less the diameter Dm of the intermediate part 23. In particular, the diameter Di of the opening 22a of the injection unit 22 can be set to be 1.5 times or more and 3.0 times or less the diameter Dm of the intermediate part 23.
　給油ライン１５により供給される油は、入口部２１は給油口１１に入り、中間部２３に流入し、中間部２３の雌ロータ室２ｂ側の端部２３ａから噴射される。噴射された油は噴射部２２を通って雌ロータ室２ｂに供給される。 油 The oil supplied by the oil supply line 15 enters the oil supply port 11 through the oil supply port 11, flows into the intermediate part 23, and is injected from the end part 23a of the intermediate part 23 on the side of the female rotor chamber 2b. The injected oil is supplied to the female rotor chamber 2b through the injection unit 22.
　給油口１１の噴射部２２の雌ロータ室２ｂに対する開口部２２ａにおける直径Ｄｉ、従って流路断面Ａｉは、給油口１１の中間部２３の直径Ｄｍ、従って流路断面積Ａｍよりも大きい。そのため、図８に示すように給油口１１が両端間で流路断面積が一定の直管形状（いわゆるキリ穴）である場合と比較して、運転時に雌ロータ４の歯部４ｂが給油口１１の真上を通り過ぎる瞬間において、中間部２３の雌ロータ室２ｂ側の端部２３ａと歯部４ｂの歯先との距離が長くなる。言い換えれば、給油口１１から噴射された油が雌ロータ４の歯部４ｂの歯先とケーシング２の円筒面２ｆとの隙間を通過する際に、油が通過し得る断面積が拡大する。従って、雌ロータ室２ｂへの油噴射時の圧力損失が減少する。この圧力損失減少により、給油口１１へ供給される油の体積流量を、図８のように給油口１１がキリ穴である場合と同一としたままで、雌ロータ室２ｂに噴射される油の流速を増加できる。言い換えれば、体積流量を増加することなく、給油口１１がキリ穴である場合よりも雌ロータ室２ｂに噴射される油の流速を増加できる。この流速増加により、液柱が雌ロータ４の歯部４ｂの歯面に衝突する際の微粒化が促進され、油滴の伝熱面積が増加し、圧縮空気に対する冷却効率が向上する。従って、空気を所要圧力まで圧縮するのに必要な動力を低減できる。 直径 The diameter Di of the injection part 22 of the fuel filler port 11 with respect to the female rotor chamber 2b at the opening part 22a, that is, the flow path cross section Ai is larger than the diameter Dm of the intermediate part 23 of the fuel filler port 11, and thus the flow path cross sectional area Am. For this reason, as shown in FIG. 8, the teeth 4 b of the female rotor 4 are connected to the oil supply port 11 during operation as compared with the case where the oil supply port 11 has a straight pipe shape (a so-called drill hole) in which the flow path cross section is constant between both ends. At the moment of passing just above 11, the distance between the end 23a of the intermediate portion 23 on the female rotor chamber 2b side and the tip of the tooth portion 4b becomes long. In other words, when the oil injected from the oil supply port 11 passes through the gap between the tooth tip of the tooth portion 4b of the female rotor 4 and the cylindrical surface 2f of the casing 2, the cross-sectional area through which the oil can pass increases. Therefore, the pressure loss at the time of oil injection to the female rotor chamber 2b is reduced. Due to this decrease in pressure loss, the oil volume injected into the female rotor chamber 2b is maintained while the volume flow rate of the oil supplied to the oil supply port 11 remains the same as when the oil supply port 11 is a drilled hole as shown in FIG. The flow rate can be increased. In other words, the flow rate of the oil injected into the female rotor chamber 2b can be increased without increasing the volume flow rate as compared with the case where the oil supply port 11 is a drilled hole. Due to this increase in flow velocity, atomization when the liquid column collides with the tooth surface of the tooth portion 4b of the female rotor 4 is promoted, the heat transfer area of oil droplets increases, and the cooling efficiency for compressed air improves. Therefore, the power required to compress the air to the required pressure can be reduced.
　仮に雌ロータ室２ｂへ噴射される油の流速増加のために、給油口１１へ供給する液体の体積流量を増加すると、雌ロータ４の歯部４ｂによる油の撹拌による動力損失や、雌ロータ４の歯部４ｂ（歯先）とケーシング２の円筒面２ｆとの間の狭小隙間における油の粘性による動力損失を増加させてしまう。しかし、本実施形態では、給油口１１へ供給する油の体積流量は同一のままで、雌ロータ室２ｂに噴射される油の流速を増加できるため、動力損失の増加も発生しない。 If the volume flow rate of the liquid supplied to the oil supply port 11 is increased to increase the flow rate of the oil injected into the female rotor chamber 2b, power loss due to oil agitation by the teeth 4b of the female rotor 4, The power loss due to the viscosity of the oil in the narrow gap between the toothed portion 4b (tooth tip) and the cylindrical surface 2f of the casing 2 increases. However, in the present embodiment, the flow rate of the oil injected into the female rotor chamber 2b can be increased while the volume flow rate of the oil supplied to the oil supply port 11 remains the same, so that the power loss does not increase.
　前述のように、噴射部２２の開口部２２ａにおける直径Ｄｉは、雌ロータ４の歯部４ｂの軸直角歯先幅Ｗｔよりも大きい。そのため、雌ロータ４の歯部４ｂが給油口１１の真上を通り過ぎる際に、歯部４ｂの先端が有する平滑面４ｄによって給油口１１の噴射部２２が塞がることがなく、より効果的に雌ロータ室２ｂへの油噴射時の圧力損失を減少できる。 As described above, the diameter Di of the opening 22a of the injection unit 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis. Therefore, when the tooth portion 4b of the female rotor 4 passes right above the oil filler port 11, the injection part 22 of the oil filler port 11 is not blocked by the smooth surface 4d of the tip of the tooth part 4b, and the female rotor 4 is more effectively Pressure loss during oil injection to the rotor chamber 2b can be reduced.
　図９及び図１０は、第１実施形態の変形例を示す。 FIGS. 9 and 10 show a modification of the first embodiment.
　図９の変形例では、給油口１１の入口部２１は給油ライン１５と接続する部分２１ａから中間部２３と接続する部分２１ｂに向けて直径Ｄｅ、従って流路断面積Ａｅが漸減するテーパ形状を有する。 In the modification of FIG. 9, the inlet 21 of the refueling port 11 has a taper shape in which the diameter De, and thus the flow path cross-sectional area Ae, gradually decreases from the portion 21 a connected to the refueling line 15 to the portion 21 b connected to the intermediate portion 23. Have.
　図１０の変形例では、給油口１１の入口部２１は、給油ライン１５と接続する部分２１ａから中間部２３と接続する部分２１ｂまで、中間部２３の直径Ｄｍよりも大きい一定の直径Ｄｅを有する。言い換えれば、入口部２１は、給油ライン１５と接続する部分２１ａから中間部２３と接続する部分２１ｂまで、中間部２３の流路断面積Ａｍよりも大きい一定の流路断面積Ａｅを有する。そのため、入口部２１が中間部２３と接続する部分に、流路断面積が急激ないしは非連続的に減少する段差２５が形成されている。 In the modification of FIG. 10, the inlet 21 of the fuel filler port 11 has a constant diameter De that is larger than the diameter Dm of the intermediate part 23 from the part 21 a connected to the fuel line 15 to the part 21 b connected to the intermediate part 23. . In other words, the inlet 21 has a constant flow cross-sectional area Ae that is larger than the flow cross-sectional area Am of the intermediate part 23 from the part 21a connected to the refueling line 15 to the part 21b connected to the intermediate part 23. Therefore, a step 25 is formed in a portion where the inlet 21 is connected to the intermediate part 23, where the cross-sectional area of the flow path decreases rapidly or discontinuously.
　図９及び図１０に示す構成により、給油ライン１５から給油口１１の入口部２１に油が流入する際の流路断面積の急激な縮小が緩和され、圧力損失が低減される。その結果、より効果的に、給油口１１へ供給する油の体積流量を増加することなく、雌ロータ室２ｂに噴射される油の流速を増加できる。 及 び The configuration shown in FIGS. 9 and 10 alleviates a sudden reduction in the flow path cross-sectional area when oil flows from the oil supply line 15 to the inlet 21 of the oil supply port 11, and reduces pressure loss. As a result, the flow rate of the oil injected into the female rotor chamber 2b can be increased more effectively without increasing the volume flow rate of the oil supplied to the oil supply port 11.
　以下の第２及び第３実施形態については、第１実施形態と異なる点を説明する。これらの実施形態に関して特に言及しない構造、機能等は、第１実施形態と同様である。また、これらの実施形態に関する図面において、第１実施形態のものと同一又は同様の要素には同一の符号を付している。さらに、図１、図２、及び図４に示される第１実施形態に係る油冷式圧縮機の全体的な構成は、これらの実施形態についても同様である。 Regarding the following second and third embodiments, differences from the first embodiment will be described. Structures, functions, and the like that are not particularly described in these embodiments are the same as those in the first embodiment. In the drawings relating to these embodiments, the same or similar elements as those of the first embodiment are denoted by the same reference numerals. Further, the overall configuration of the oil-cooled compressor according to the first embodiment shown in FIGS. 1, 2 and 4 is the same for these embodiments.
　（第２実施形態）
　図１１及び図１２に示す本発明の第２実施形態に係る油冷式スクリュー圧縮機１では、給油口１１の噴射部２２は、中間部２３と接続する部分２２ｂから開口部２２ａまで、中間部２３の直径Ｄｍよりも大きい一定の直径Ｄｉを有する。言い換えれば、噴射部２２は、中間部２３と接続する部分２２ｂから開口部２２ａまで、中間部２３の流路断面積Ａｍよりも大きい一定の流路断面積Ａｅを有する。そのため、噴射部２２の中間部２３と接続する部分に、流路断面積が急激ないし非連続的に増加する段差２６が形成されている。 (2nd Embodiment)
In the oil-cooled screw compressor 1 according to the second embodiment of the present invention shown in FIGS. 11 and 12, the injection part 22 of the oil supply port 11 includes the intermediate part from the part 22b connected to the intermediate part 23 to the opening part 22a. It has a constant diameter Di which is larger than the diameter Dm of 23. In other words, the injection section 22 has a constant flow path cross-sectional area Ae that is larger than the flow path cross-sectional area Am of the intermediate section 23 from the portion 22b connected to the intermediate section 23 to the opening 22a. Therefore, a step 26 in which the cross-sectional area of the flow channel increases rapidly or discontinuously is formed at a portion of the injection unit 22 connected to the intermediate unit 23.
　噴射部２２の雌ロータ室２ｂに対する開口部２２ａは、中間部２３の流路断面積Ａｍよりも大きい流路断面積Ａｅを有するので、体積流量を増加することなく雌ロータ室２ｂに噴射される油の流速を増加できる。この速度増加により、圧縮空気に対する冷却効率が向上し、空気を所要圧力まで圧縮するのに必要な動力を低減できる。また、給油口１１へ供給する油の体積流量は同一のままで、雌ロータ室に噴射される液体の流速を増加できるため、動力損失の増加も発生しない。さらに、噴射部２２の開口部２２ａにおける直径Ｄｉは、雌ロータ４の歯部４ｂの軸直角歯先幅Ｗｔよりも大きいので、歯部４ｂの先端面が有する平滑面４ｄが噴射部２２を塞ぐことがなく、より効果的に雌ロータ室２ｂへの油噴射時の圧力損失を減少できる。 The opening 22a of the injection part 22 with respect to the female rotor chamber 2b has a flow path cross-sectional area Ae larger than the flow path cross-sectional area Am of the intermediate part 23, so that the injection part 22 is injected into the female rotor chamber 2b without increasing the volume flow rate. Oil flow rate can be increased. This increase in speed improves the efficiency of cooling the compressed air and reduces the power required to compress the air to the required pressure. Further, since the flow rate of the liquid injected into the female rotor chamber can be increased while the volume flow rate of the oil supplied to the oil supply port 11 remains the same, the power loss does not increase. Further, since the diameter Di of the opening 22a of the injection portion 22 is larger than the width Wt of the tooth portion 4b of the female rotor 4 at right angles to the axis, the smooth surface 4d of the tip end surface of the tooth portion 4b closes the injection portion 22. Therefore, the pressure loss at the time of oil injection into the female rotor chamber 2b can be reduced more effectively.
　図１３及び図１４は、第２実施形態の変形例を示す。 FIGS. 13 and 14 show a modification of the second embodiment.
　図１３の変形例では、給油口１１の入口部２１は、給油ライン１５と接続する部分２１ａから中間部２３と接続する部分２１ｂまで、中間部２３の流路断面積Ａｍよりも大きい一定の流路断面積Ａｅを有する。そのため、入口部２１の中間部２３と接続する部分に、流路断面積が非連続的に減少する段差２５が形成されている。中間部２３の厚みＴＨｍは、入口部２１の厚みＴＨｅと噴射部２２の厚みＴＨｉとの和よりも大きい。 In the modification of FIG. 13, the inlet 21 of the refueling port 11 has a constant flow larger than the flow path cross-sectional area Am of the intermediate part 23 from the part 21 a connected to the refueling line 15 to the part 21 b connected to the intermediate part 23. It has a road cross-sectional area Ae. For this reason, a step 25 where the flow path cross-sectional area is discontinuously reduced is formed at a portion of the inlet 21 connected to the intermediate portion 23. The thickness THm of the intermediate portion 23 is larger than the sum of the thickness THe of the inlet portion 21 and the thickness THi of the injection portion 22.
　図１４の変形例では、給油口１１の入口部２１は給油ライン１５と接続する部分２１ａから中間部２３と接続する部分２１ｂに向けて直径Ｄｅ、従って流路断面積Ａｅが漸減するテーパ形状を有する。図１３及び図１４の構成により、給油ライン１５から給油口１１の入口部２１に油が流入する際の流路断面積の急激な縮小が緩和され、圧力損失が低減される。その結果、より効果的に、給油口１１へ供給する油の体積流量を増加することなく、雌ロータ室２ｂに噴射される油の流速を増加できる。 In the modification of FIG. 14, the inlet 21 of the refueling port 11 has a tapered shape in which the diameter De, and thus the flow path cross-sectional area Ae, gradually decreases from the portion 21 a connected to the refueling line 15 to the portion 21 b connected to the intermediate portion 23. Have. 13 and 14, the sudden reduction in the flow path cross-sectional area when oil flows from the oil supply line 15 to the inlet 21 of the oil supply port 11 is reduced, and the pressure loss is reduced. As a result, the flow rate of the oil injected into the female rotor chamber 2b can be increased more effectively without increasing the volume flow rate of the oil supplied to the oil supply port 11.
　（第３実施形態）
　図１５及び図１６に示す本発明の第３実施形態に係る油冷式スクリュー圧縮機１では、ケーシング２に、別部材を取り付けることで、給油口１１を設けている。 (Third embodiment)
In the oil-cooled screw compressor 1 according to the third embodiment of the present invention shown in FIGS. 15 and 16, the casing 2 is provided with another member so that the oil supply port 11 is provided.
　ケーシング２には、給油ライン１５から雌ロータ室２ｂまで貫通する取付穴３１が設けられている。本実施形態では、取付穴３１は一定の直径Ｄａを有する円形である。図１７に示す、両端開口、つまり中央に軸穴３２ａを有するオリフィス管（管部材）３２が、取付穴３１に挿入ないし嵌入され、ケーシング２に対して固定されている。 The casing 2 is provided with a mounting hole 31 penetrating from the oil supply line 15 to the female rotor chamber 2b. In the present embodiment, the mounting hole 31 is a circle having a constant diameter Da. An orifice tube (pipe member) 32 having openings at both ends, that is, a shaft hole 32 a at the center, shown in FIG. 17, is inserted or fitted into the mounting hole 31 and fixed to the casing 2.
　オリフィス管３２の雌ロータ室２ｂ側の端面３２ｂは、取付穴３１内に位置しており、雌ロータ室２ｂを画定する円筒面２ｆに対して窪んでいる。また、オリフィス管３２の給油ライン１５側の端面３２ｃも取付穴３１内に位置している。オリフィス管３２の端面３２ｃと、取付穴３１の穴周壁３１ａとによって、給油口１１の入口部２１が画定されている。また、オリフィス管３２の軸穴３２ａが給油口１１の中間部２３を構成している。さらに、オリフィス管３２の端面３２ｂと、取付穴３１の穴周壁３１ａとによって、給油口１１の噴射部２２が画定されている。 The end face 32b of the orifice tube 32 on the female rotor chamber 2b side is located in the mounting hole 31 and is depressed with respect to the cylindrical surface 2f defining the female rotor chamber 2b. The end face 32 c of the orifice pipe 32 on the side of the oil supply line 15 is also located in the mounting hole 31. The inlet 21 of the fuel filler port 11 is defined by the end face 32 c of the orifice pipe 32 and the hole peripheral wall 31 a of the mounting hole 31. Further, the shaft hole 32 a of the orifice pipe 32 constitutes an intermediate portion 23 of the fuel filler 11. Further, the injection portion 22 of the fuel filler 11 is defined by the end face 32 b of the orifice pipe 32 and the hole peripheral wall 31 a of the mounting hole 31.
　本実施形態における噴射部２２は、第２実施形態のものと同様の形状を有している。特に、中間部２３、つまりオリフィス管３２の軸穴３２ａと噴射部２２とが接続する部分に、流路断面積が非連続的に増加する段差２６が形成されている。 噴射 The injection unit 22 in this embodiment has the same shape as that of the second embodiment. In particular, a step 26 in which the cross-sectional area of the flow path increases discontinuously is formed at the intermediate portion 23, that is, at the portion where the shaft hole 32 a of the orifice tube 32 and the injection portion 22 are connected.
　本実施形態における入口部２１は、図１３に示すものと同様の形状を有している。特に、入口部２１が中間部２３、つまりオリフィス管３２の軸穴３２ａと接続する部分に、流路断面積が非連続的に減少する段差２５が形成されている。 入口 The inlet 21 in this embodiment has the same shape as that shown in FIG. In particular, a step 25 where the flow path cross-sectional area is discontinuously reduced is formed at a portion where the inlet portion 21 is connected to the intermediate portion 23, that is, the shaft hole 32 a of the orifice tube 32.
　第１及び第２実施形態並びにそれらの変形例と同様の効果に加え、本実施形態には以下の効果がある。まず、給油口１１をケーシング２に設ける加工時の寸法管理が、ケーシング２そのものを直接、掘削等にて加工して、中間部２３と、その中間部２３の流路断面積より大きい流路断面積をロータ室に対する開口部に備えた噴射部２２を形成する場合に比べ、容易となる。加工時の寸法管理が容易になることで、より高度な品質安定性を確保できる。また、異なるオリフィス管３２を使用することで、給油口１１の中間部２３の直径Ｄｍを、製品使用に合わせて容易に変更できる。さらに、給油口１１を設けるためにケーシング２に施す加工としては、流路断面積が非連続的に増加する段差の加工や、流路断面積が連続的に拡大するテーパ形状の加工を必要とせず、取付穴３１の形成のみが要求されるため、工数削減を図ることができる。 に In addition to the same effects as the first and second embodiments and their modifications, the present embodiment has the following effects. First, the dimension control at the time of forming the oil supply port 11 in the casing 2 is performed by directly processing the casing 2 itself by excavation or the like to cut the intermediate portion 23 and the flow path cross section larger than the flow path cross-sectional area of the intermediate portion 23. This is easier than forming the injection unit 22 having an area at the opening to the rotor chamber. Higher quality stability can be ensured by easier dimensional control during processing. Further, by using a different orifice pipe 32, the diameter Dm of the intermediate portion 23 of the fuel filler 11 can be easily changed according to the use of the product. Further, as the processing to be performed on the casing 2 in order to provide the oil supply port 11, processing of a step where the cross-sectional area of the flow path increases discontinuously or processing of a tapered shape where the cross-sectional area of the flow path continuously increases is required. However, since only the formation of the mounting hole 31 is required, the number of steps can be reduced.
　（試験）
　本発明の効果を確認するための試験を行った。この試験では、第３実施形態の油冷式スクリュー圧縮機１（図１５に示すようにオリフィス管３２で給油口１１を構成している）と、比較例として図８に示す油冷式スクリュー圧縮機１（給油口１１が一定直径のキリ穴）を使用した。個々の油冷式スクリュー圧縮機１（７５KW）について、２種類の循環油量で実際に運転し、断熱効率（実際の消費動力に対する理論消費動力の割合）を求めた。個々の油冷式スクリュー圧縮機１の吐出圧力は０．７MPaに設定した。周囲温度は２０℃であった。 (test)
A test was performed to confirm the effects of the present invention. In this test, the oil-cooled screw compressor 1 of the third embodiment (the oil supply port 11 is constituted by the orifice pipe 32 as shown in FIG. 15) and the oil-cooled screw compressor shown in FIG. 8 as a comparative example. The machine 1 (the filler hole 11 was a drilled hole having a constant diameter) was used. Each oil-cooled screw compressor 1 (75 KW) was actually operated with two kinds of circulating oil amounts, and the adiabatic efficiency (the ratio of the theoretical power consumption to the actual power consumption) was determined. The discharge pressure of each oil-cooled screw compressor 1 was set to 0.7 MPa. Ambient temperature was 20 ° C.
　第３実施形態と比較例のいずれにおいても、３個の給油口１１Ａ～１１Ｃの中間部２３の直径Ｄｍは、雌ロータ４の歯部４ｂの軸直角歯先幅Ｗｔの４．４倍であった（Ｄｍ＝４．４×Ｗｔ）。 In each of the third embodiment and the comparative example, the diameter Dm of the intermediate portion 23 of the three oil fillers 11A to 11C is 4.4 times the axial perpendicular tooth tip width Wt of the tooth portion 4b of the female rotor 4. (Dm = 4.4 × Wt).
　第３実施形態については、循環油量は所定の油量Ｑ０（L/min）と約１．４×Ｑ０（L/min）で運転した際の断熱効率を求めた。循環油量はＱ０（L/min）のときの給油口１１Ａ，１１Ｂ，１１Ｃの噴射部２２の直径Ｄｉは、それぞれ２．２Ｄｍ（Ｄｉ＝２．２×Ｄｍ）、２．９Ｄｍ（Ｄｉ＝２．９×Ｄｍ）、及び２．９Ｄｍ（Ｄｉ＝２．９×Ｄｍ）であった。一方、潤滑油量が１．４×Ｑ０（L/min）のときの給油口１１Ａ，１１Ｂ，１１Ｃの噴射部２２の直径Ｄｉは、それぞれ１．７Ｄｍ（Ｄｉ＝１．７×Ｄｍ）、２．２Ｄｍ（Ｄｉ＝２．２×Ｄｍ）、及び２．２Ｄｍ（Ｄｉ＝２．２×Ｄｍ）。 Regarding the third embodiment, the adiabatic efficiency when the circulating oil amount was operated at a predetermined oil amount Q 0 (L / min) and about 1.4 × Q 0 (L / min) was determined. When the circulating oil amount is Q 0 (L / min), the diameter Di of the injection portion 22 of each of the oil supply ports 11A, 11B, and 11C is 2.2 Dm (Di = 2.2 × Dm) and 2.9 Dm (Di = 2.9 × Dm) and 2.9 Dm (Di = 2.9 × Dm). On the other hand, when the lubricating oil amount is 1.4 × Q 0 (L / min), the diameters Di of the injection portions 22 of the oil supply ports 11A, 11B, and 11C are 1.7 Dm (Di = 1.7 × Dm), respectively. 2.2Dm (Di = 2.2 × Dm) and 2.2Dm (Di = 2.2 × Dm).
　図１８に試験結果を示す。この図１８に示されているように、第３実施形態の油冷式スクリュー圧縮機１は、比較例よりも約１％程度断熱効率が向上することが確認できた。 Fig. 18 shows the test results. As shown in FIG. 18, it was confirmed that the oil-cooled screw compressor 1 of the third embodiment improved the heat insulation efficiency by about 1% compared to the comparative example.
　１　油冷式スクリュー圧縮機（液冷式スクリュー圧縮機）
　２　ケーシング
　２ａ　雄ロータ室
　２ｂ　雌ロータ室
　２ｃ　吸込口
　２ｄ　吐出口
　２ｅ，２ｆ　円筒面
　２ｇ，２ｈ　端面
　３　雄ロータ
　３ａ　ロータ軸
　３ｂ　歯部
　４　雌ロータ
　４ａ　ロータ軸
　４ｂ　歯部
　４ｃ　歯溝
　４ｄ　平滑面
　５Ａ，５Ｂ，６Ａ，６Ｂ　軸受
　７　駆動機構
　１１Ａ，１１Ｂ，１１Ｃ　給油口（給液口）
　１２Ａ，１２Ｂ　空気配管
　１３　セパレータ
　１４　油供給配管
　１５　給油ライン（給液ライン）
　１６　油ポンプ
　２１　入口部
　２１ａ，２１ｂ　部分
　２２　噴射部
　２２ａ　開口部
　２２ｂ　部分
　２３　中間部
　２３ａ　端部
　２５，２６　段差
　３１　取付穴
　３１ａ　穴周壁
　３２　オリフィス管
　３２ａ　軸穴
　３２ｂ，３２ｃ　端面 1 Oil-cooled screw compressor (liquid-cooled screw compressor)
2 Casing 2a Male rotor chamber 2b Female rotor chamber 2c Suction port 2d Discharge port 2e, 2f Cylindrical surface 2g, 2h End face 3 Male rotor 3a Rotor shaft 3b Teeth 4 Female rotor 4a Rotor shaft 4b Teeth 4c Tooth groove 4d Smooth surface 5A , 5B, 6A, 6B Bearing 7 Drive mechanism 11A, 11B, 11C Oil supply port (liquid supply port)
12A, 12B Air piping 13 Separator 14 Oil supply piping 15 Oil supply line (liquid supply line)
Reference Signs List 16 Oil pump 21 Inlet 21a, 21b part 22 Injection part 22a Opening 22b part 23 Intermediate part 23a End part 25, 26 Step 31 Mounting hole 31a Hole peripheral wall 32 Orifice pipe 32a Shaft hole 32b, 32c End face

Claims (9)

  1. 　ケーシングに設けられ、一対のスクリューロータが収容されたロータ室と、
    　給液ラインから供給される液体を前記ロータ室に供給するために、前記ケーシングに設けられた給液口と
    　を備え、
    　前記給液口は、
    　前記給液ラインと流体的に連通する入口部と、
    　前記ロータ室と流体的に連通する噴射部と、
    　前記入口部と前記噴射部とを流体的に接続する、一定の流路断面積を有する中間部とを備え、
    　前記噴射部の前記ロータ室に対する開口部の流路断面積は、前記中間部の前記流路断面積よりも大きい、液冷式スクリュー圧縮機。     A rotor chamber provided in the casing and containing a pair of screw rotors,
    A liquid supply port provided in the casing for supplying a liquid supplied from a liquid supply line to the rotor chamber;
    The liquid supply port is
    An inlet portion in fluid communication with the liquid supply line;
    An injection unit in fluid communication with the rotor chamber;
    An intermediate part having a constant flow path cross-sectional area that fluidly connects the inlet part and the injection part,
    A liquid-cooled screw compressor, wherein a flow passage cross-sectional area of an opening of the injection unit with respect to the rotor chamber is larger than the flow passage cross-sectional area of the intermediate portion.
  2. 　前記噴射部の前記開口部における直径は、前記スクリューロータの歯部の軸直角歯先幅よりも大きい、請求項１に記載の液冷式スクリュー圧縮機。 2. The liquid-cooled screw compressor according to claim 1, wherein the diameter of the injection section at the opening is larger than the width of the tooth section of the screw rotor at a right angle to the axis.
  3. 　前記中間部の直径は０．７mm以上１８mm以下であり、
    　前記噴射部の前記開口部における直径は、前記中間部の直径の４．０倍以下である、請求項１又は２に記載の液冷式スクリュー圧縮機。     The diameter of the intermediate portion is not less than 0.7 mm and not more than 18 mm,
    3. The liquid-cooled screw compressor according to claim 1, wherein a diameter of the injection portion at the opening is 4.0 times or less a diameter of the intermediate portion. 4.
  4. 　前記噴射部の前記開口部における直径は、前記中間部の直径の１．５倍以上３．０倍以下である、請求項３に記載の液冷式スクリュー圧縮機。 The liquid-cooled screw compressor according to claim 3, wherein a diameter of the injection section at the opening is 1.5 times or more and 3.0 times or less of a diameter of the intermediate section.
  5. 　前記噴射部は、前記中間部と接続する部分から前記開口部に向けて前記流路断面積が漸増する、逆テーパ形状を有する、請求項１又は２に記載の液冷式スクリュー圧縮機。 3. The liquid-cooled screw compressor according to claim 1, wherein the injection unit has an inversely tapered shape in which the cross-sectional area of the flow passage gradually increases from a portion connected to the intermediate portion toward the opening. 4.
  6. 　前記噴射部は、前記中間部と接続する部分から前記開口部までの前記流路断面積が一定であり、
    　前記噴射部の前記中間部と接続する部分に、前記流路断面積が非連続的に増加する段差が形成されている、請求項１又は２に記載の液冷式スクリュー圧縮機。     The injection section has a constant cross-sectional area of the flow passage from a portion connected to the intermediate portion to the opening,
    3. The liquid-cooled screw compressor according to claim 1, wherein a step in which the cross-sectional area of the flow path increases discontinuously is formed at a portion of the injection unit connected to the intermediate unit. 4.
  7. 　前記給液口は、前記ケーシングに設けられた前記給液ラインから前記ロータ室まで貫通する取付穴に挿入された、両端開口の管部材を備え、
    　前記管部材によって前記中間部が画定され、
    　前記管部材の前記ロータ室に臨む端面は、前記取付穴内に位置し、
    　前記管部材の前記端面と、前記取付穴の穴周壁によって前記噴射部が画定されている、請求項６に記載の液冷式スクリュー圧縮機。     The liquid supply port is provided with a pipe member having both ends opened, which is inserted into a mounting hole penetrating from the liquid supply line provided in the casing to the rotor chamber.
    The intermediate portion is defined by the tube member;
    An end face of the pipe member facing the rotor chamber is located in the mounting hole,
    The liquid-cooled screw compressor according to claim 6, wherein the injection portion is defined by the end surface of the pipe member and a peripheral wall of the mounting hole.
  8. 　前記入口部は、前記給液ラインと接続する部分から前記中間部に向けて流路断面が漸減する、テーパ形状を有する、請求項１又は２に記載の液冷式スクリュー圧縮機。 3. The liquid-cooled screw compressor according to claim 1, wherein the inlet has a tapered shape in which a cross section of the flow path gradually decreases from a portion connected to the liquid supply line toward the intermediate portion. 4.
  9. 　前記入口部は、前記給液ラインと接続する部分から前記中間部と接続する部分まで、前記中間部の前記流路断面積よりも大きい一定の流路断面積を有し、
    　前記入口部の前記中間部と接続する部分に、前記流路断面積が非連続的に減少する段差が形成されている、請求項１又は２に記載の液冷式スクリュー圧縮機。     The inlet portion has a constant flow path cross-sectional area larger than the flow path cross-sectional area of the intermediate portion, from a portion connected to the liquid supply line to a portion connected to the intermediate portion,
    3. The liquid-cooled screw compressor according to claim 1, wherein a step where the cross-sectional area of the flow path is discontinuously reduced is formed at a portion of the inlet portion connected to the intermediate portion. 4.
PCT/JP2019/031728 2018-08-27 2019-08-09 Liquid-cooled screw compressor WO2020045068A1 (en)

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Application Number Priority Date Filing Date Title
KR1020217004176A KR102580244B1 (en) 2018-08-27 2019-08-09 Liquid-cooled screw compressor
SG11202100933SA SG11202100933SA (en) 2018-08-27 2019-08-09 Liquid-cooled screw compressor
CN201980056538.5A CN112585358B (en) 2018-08-27 2019-08-09 Liquid-cooled screw compressor

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Application Number Priority Date Filing Date Title
JP2018-158544 2018-08-27
JP2018158544 2018-08-27
JP2019077953A JP7335089B2 (en) 2018-08-27 2019-04-16 Liquid-cooled screw compressor
JP2019-077953 2019-04-16

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20030034806A (en) * 2001-10-27 2003-05-09 엘지전선 주식회사 An equipped restrictor at supplied oil line of screw compressor
CN201858157U (en) * 2010-10-22 2011-06-08 武汉新世界制冷工业有限公司 Screw compressor refrigerator oil injection device
WO2018038070A1 (en) * 2016-08-23 2018-03-01 株式会社日立産機システム Fluid machine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20030034806A (en) * 2001-10-27 2003-05-09 엘지전선 주식회사 An equipped restrictor at supplied oil line of screw compressor
CN201858157U (en) * 2010-10-22 2011-06-08 武汉新世界制冷工业有限公司 Screw compressor refrigerator oil injection device
WO2018038070A1 (en) * 2016-08-23 2018-03-01 株式会社日立産機システム Fluid machine

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