WO2016157449A1 - Compresseur de gaz - Google Patents

Compresseur de gaz Download PDF

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Publication number
WO2016157449A1
WO2016157449A1 PCT/JP2015/060244 JP2015060244W WO2016157449A1 WO 2016157449 A1 WO2016157449 A1 WO 2016157449A1 JP 2015060244 W JP2015060244 W JP 2015060244W WO 2016157449 A1 WO2016157449 A1 WO 2016157449A1
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WO
WIPO (PCT)
Prior art keywords
discharge
flow path
gas compressor
screw rotors
port
Prior art date
Application number
PCT/JP2015/060244
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English (en)
Japanese (ja)
Inventor
大嗣 堀内
笠原　雅之
Original Assignee
株式会社日立産機システム
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 株式会社日立産機システム filed Critical 株式会社日立産機システム
Priority to PCT/JP2015/060244 priority Critical patent/WO2016157449A1/fr
Priority to JP2017508956A priority patent/JP6482649B2/ja
Publication of WO2016157449A1 publication Critical patent/WO2016157449A1/fr

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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

Definitions

  • the present invention relates to a gas compressor.
  • an oil-free screw compressor that is one of gas compressors (specifically, the compressor chamber is operated without oil supply) is capable of rotating two screw rotors that mesh with each other and two screw rotors.
  • a plurality of bearings for supporting each, a plurality of timing gears for rotating the two screw rotors in a non-contact manner, and a casing are provided.
  • the casing accommodates the tooth portions of the two screw rotors and forms a plurality of compression chambers in the tooth gaps, a suction passage for sucking gas into the compression chambers, and a compressed gas from the compression chambers.
  • a discharge channel for discharging.
  • the discharge flow path shown in FIG. 3 of Patent Document 1 is formed so as to be directed substantially in the rotor axial direction. Thereby, compared with the case where it forms so that it may go to a rotor radial direction, it is possible to suppress the change of the flow direction of compressed gas, and to aim at reduction of the pressure loss of a discharge flow path.
  • the discharge flow path shown in FIG. 3 of Patent Document 1 is formed so as not to interfere with the discharge-side timing gear and the bearing. That is, the discharge flow path is formed so that the discharge port which is the compression chamber side opening and the outlet port which is the outlet side opening do not overlap with the axial projection surfaces of the timing gear and the bearing. Therefore, there has been a limit to reducing the compression loss of the discharge flow path.
  • the present invention has been made in view of the above matters, and an object of the present invention is to improve the performance by reducing the pressure loss of the discharge flow path.
  • the gas compressor of the present invention includes a plurality of means for solving the above-described problems.
  • at least two screw rotors that mesh with each other and each of the at least two screw rotors can rotate.
  • At least a part of each of the discharge port that is a side opening and the outlet port that is an outlet side opening of the discharge flow path is the timing It is formed so as to overlap with the projected area in the axial direction of Ya.
  • the present invention compared with the case where the discharge port and the outlet port do not overlap with the axial projection surface of the timing gear, it is possible to reduce the pressure loss of the discharge flow path and improve the performance.
  • FIG. 2 is a vertical sectional view taken along section II-II in FIG.
  • FIG. 3 is a partial enlarged cross-sectional view of a part III in FIG. 2 and shows a structure of a discharge channel in the first embodiment of the present invention.
  • It is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing in the 1st Embodiment of this invention.
  • It is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing in the 1st Embodiment of this invention.
  • FIG. 20 is a vertical sectional view taken along section XX-XX in FIG. It is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing in the 3rd Embodiment of this invention. It is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing in the 3rd Embodiment of this invention. It is a horizontal sectional view showing the structure of the gas compressor in a 4th embodiment of the present invention.
  • FIG. 1 is a horizontal sectional view showing the structure of the gas compressor in the present embodiment.
  • 2 is a vertical cross-sectional view taken along a section II-II in FIG. 1
  • FIG. 3 is a partially enlarged cross-sectional view of a portion III in FIG. 4 and 5 are three-dimensional views showing the structure of the lower half of the compressor main body main casing in the present embodiment.
  • FIG. 6 is an axial projection showing the positional relationship among the discharge port, the outlet port, the storage chamber, the bearing, and the timing gear in the present embodiment.
  • the gas compressor of the present embodiment includes a compressor body 1 and a motor 2 that drives the compressor body 1, and the compressor body 1 and the motor 2 are integrated.
  • the compressor body 1 and the motor 2 are placed horizontally so that the rotation shaft of the compressor body 1 and the rotation shaft of the motor 2 described later extend in the horizontal direction, and the compressor body 1 and The motor 2 is connected in the horizontal direction.
  • the motor 2 includes a rotating shaft 3, a rotor core 4 attached to the rotating shaft 3, a stator core 5 disposed on the outer peripheral side of the rotor core 4, a motor casing 6 to which the stator core 5 is attached, and an axial direction of the motor casing 6 And a motor bracket 7 connected to one side (the right side in FIGS. 1 and 2).
  • a motor cooling jacket 8 is formed on the outer peripheral side of the stator core 5 in the motor casing 6.
  • the motor 2 is cooled by circulating a coolant (oil in this embodiment) through the motor cooling jacket 8.
  • a coolant oil in this embodiment
  • a part of the oil supplied to the motor cooling jacket 8 is supplied to a bearing and a timing gear described later.
  • Compressor body 1 is an oil-free screw compressor.
  • the compressor body 1 includes a pair of male and female screw rotors 10A and 10B that are engaged with each other, a compressor main body casing 12 that houses the tooth portions 11A of the male rotor 10A and the tooth portions 11B of the female rotor 10B, and the main body of the compressor.
  • a compressor main body suction side casing 13 connected to one axial side of the casing 12 (right side in FIGS. 1 and 2) is provided.
  • the portion on the other side in the axial direction of motor casing 6 (left side in FIGS. 1 and 2) is a portion corresponding to a gear casing, and stores compressor body suction side casing 13 and the like, and also includes a compressor body main casing. 12 is connected.
  • the shaft portion 14A (rotating shaft) of the male rotor 10A is provided only on one side in the axial direction (in other words, the suction side) with respect to the tooth portion 11A, and is integrally formed with the rotating shaft 3 of the motor 2.
  • the shaft portion 14A of the male rotor 10A is rotatably supported by a bearing 15A provided on the compressor body suction side casing 13, and the rotating shaft 3 of the motor 2 is rotatable by a bearing 16A provided on the motor bracket 7. It is supported. That is, the shaft portion 14A of the male rotor 10A is indirectly supported by the bearing 16A so as to be rotatable.
  • the bearing 15A supports a radial load
  • the bearing 16A supports a radial load and a thrust load.
  • the male rotor 10 ⁇ / b> A is rotated by driving the motor 2.
  • the shaft portion 14B (rotating shaft) of the female rotor 10B is provided only on one side in the axial direction (in other words, the suction side) with respect to the tooth portion 11B.
  • the shaft portion 14B of the female rotor 10B is rotatably supported by a bearing 15B provided in the compressor main body suction side casing 13 and a bearing 16B provided in the motor casing 6.
  • the bearing 15B supports a radial load
  • the bearing 16B supports a radial load and a thrust load.
  • Timing shafts 17A and 17B are provided on the shaft portion 14A of the male rotor 10A and the shaft portion 14B of the female rotor 10B, and the rotational force of the male rotor 10A is transmitted to the female rotor 10B by the engagement of the timing gears 17A and 17B. As a result, the male rotor 10A and the female rotor 10B rotate synchronously without contact.
  • the compressor body main casing 12 accommodates the tooth portion 11A of the male rotor 10A and the tooth portion 11B of the female rotor 10B, and forms a plurality of compression chambers S in the tooth gaps (in detail, a part of Two cylindrical bores), and a discharge passage 19 for discharging compressed gas from the compression chamber S.
  • the discharge port 20, which is the compression chamber side opening of the discharge flow channel 19, is formed only in the rotor axial direction with respect to the compression chamber S.
  • An outlet port 21 that is an outlet side opening of the discharge flow channel 19 is formed on a side surface of the casing 12.
  • the discharge flow path 19 is formed to extend linearly in the rotor axial direction. As shown in FIG. 6, a part of each of the discharge port 20 and the outlet port 21 is formed so as to overlap with the axial projection surfaces of the timing gears 17A and 17B or the bearings 15A and 15B.
  • the casings 12 and 13 of the compressor body 1 have suction passages 22A and 22B for sucking gas into the compression chamber S.
  • the suction port 23 that is the compression chamber side opening of the suction passage 22B is formed only in the rotor axial direction with respect to the compression chamber S.
  • An inlet port 24 that is an inlet side opening of the suction flow path 22 ⁇ / b> A is formed on the upper surface of the casing 12.
  • the compression chamber S moves in the rotor axial direction. At this time, the compression chamber S sucks gas (specifically, for example, air) from the suction flow paths 22A and 22B via the suction port 23, compresses the gas, and enters the discharge flow path 19 via the discharge port 20. Compressed gas is discharged.
  • gas specifically, for example, air
  • a compressor main body cooling jacket 25 is formed on the outer peripheral portion (except for the suction flow path 22 ⁇ / b> A) of the tooth portion 11 ⁇ / b> A of the male rotor 10 ⁇ / b> A and the tooth portion 11 ⁇ / b> B of the female rotor 10 ⁇ / b> B.
  • the compressor main body 1 is cooled by circulating a coolant (oil in this embodiment) through the compressor main body cooling jacket 25.
  • the shaft portion 14A of the male rotor 10A is only on the suction side with respect to the tooth portion 11A
  • the shaft portion 14B of the female rotor 10B is only on the suction side with respect to the tooth portion 11B
  • the shaft portion on the discharge side is eliminated.
  • the structure on the discharge side of the casing 12 can be simplified, and the degree of freedom in design can be increased. Therefore, the discharge channel 19 is formed so that a part of each of the discharge port 20 and the outlet port 21 overlaps with the timing gears 17A and 17B or the axial projection surfaces of the bearings 15A and 15B.
  • the pressure loss of the discharge passage 19 is reduced and the performance is improved. Can do. Moreover, discharge noise can also be reduced.
  • the discharge path 19 extends in a straight line shape in the rotor axial direction, and each radial cross section from the discharge port 20 to the outlet port 21 (however, the discharge port 20 And the outlet port 21 are formed in the same shape and size, and the radial positions thereof are the same.
  • the present invention is not limited to this, and the gist and technology of the present invention Modifications can be made without departing from the concept. That is, it is sufficient that at least a part of each of the discharge port 20 and the outlet port 21 is formed so as to overlap with the axial projection surfaces of the timing gears 17A and 17B or the bearings 15A and 15B, and various modifications are possible. is there.
  • the discharge flow path 19 is formed so that the radial cross section gradually increases from the discharge port 20 toward the outlet port 21 as a whole. May be.
  • the discharge flow path 19 has a partial radial cross section from the discharge port 20 toward the outlet port 21 (in this modification, the lower portion is). You may form so that it may expand gradually.
  • the outlet port 21 when the outlet port 21 is projected in the axial direction, it overlaps with most of 80% or more of the discharge port 20.
  • the discharge flow path 19 may be formed to be slightly inclined with respect to the rotor axial direction.
  • the discharge channel 19 is formed so as to incline radially outward (downward in FIG. 9) from the discharge port 20 toward the outlet port 21. Therefore, the overlapping area between the outlet port 21 and the axial projection surfaces of the timing gears 17A and 17B is smaller than the overlapping area between the discharge port 20 and the axial projection surfaces of the timing gears 17A and 17B. Further, the overlapping area between the outlet port 21 and the axial projection surfaces of the bearings 15A and 15B is smaller than the overlapping area between the discharge port 20 and the axial projection surfaces of the bearings 15A and 15B.
  • the discharge flow path 19 may be formed so that the shapes of the discharge port 20 and the outlet port 21 are different and the shape of the radial cross section gradually changes. Good.
  • the pressure loss of the discharge flow path 19 can be reduced and the performance can be improved.
  • FIG. 11 is a partially enlarged sectional view showing the structure of the discharge flow path 19 in the present embodiment, and corresponds to FIG. 3 described above.
  • FIG.12 and FIG.13 is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing 12 in this embodiment.
  • FIG. 14 is an axial projection showing the positional relationship among the discharge port, the outlet port, the storage chamber, the bearing, and the timing gear in the present embodiment.
  • an axial discharge port 20A that opens in the axial direction with respect to the compression chamber S and a radial discharge port 20B that opens in the radial direction with respect to the compression chamber S are provided.
  • the discharge flow path 19 includes a discharge pocket 26 formed outside the radial discharge port 20B, and is formed to extend linearly from the axial discharge port 20A and the discharge pocket 26 in the rotor axial direction.
  • each of discharge port 20A and exit port 21 is formed so that it may overlap with the axial direction projection surface of timing gear 17A, 17B or bearing 15A, 15B.
  • the discharge port 20A and the outlet port 21 are compared with the case where the timing gears 17A, 17B or the axial projection surfaces of the bearings 15A, 15B do not overlap.
  • the pressure loss of the discharge channel 19 can be reduced and the performance can be improved.
  • the discharge flow path 19 is, in detail, each radial cross section from the discharge port 20A to the outlet port 21 (however, the discharge port 19) so as to extend linearly in the rotor axial direction. 20A is included and the outlet port 21 is included), and the shape and size thereof are the same and the radial positions thereof are the same.
  • the present invention is not limited thereto, and the present invention is not limited thereto. Modifications are possible without departing from the spirit and technical idea of the present invention.
  • each of the discharge port 20A and the outlet port 21 is formed so as to overlap the axial projection surface of the timing gears 17A and 17B or the bearings 15A and 15B, and various modifications are possible. is there.
  • the discharge flow path 19 gradually increases in overall radial cross section from the discharge port 20A toward the outlet port 21. May be formed.
  • the discharge flow path 19 has a partial radial cross section from the discharge port 20 ⁇ / b> A toward the outlet port 21 (in this modification, the lower portion is). You may form so that it may expand gradually.
  • most of the discharge port 20A is 80% or more. It is supposed to overlap.
  • the discharge flow path 19 may be formed to be slightly inclined with respect to the rotor axial direction.
  • the shape and size of each radial section from the discharge port 20A to the outlet port 21 are the same, their radial positions are It may be formed to change.
  • the discharge channel 19 is formed so as to incline radially outward (downward in FIG. 18) from the discharge port 20A toward the outlet port 21.
  • the overlapping area between the outlet port 21 and the axial projection surfaces of the timing gears 17A and 17B is smaller than the overlapping area between the discharge port 20A and the axial projection surfaces of the timing gears 17A and 17B. Further, the overlapping area between the outlet port 21 and the axial projection surfaces of the bearings 15A and 15B is smaller than the overlapping area between the discharge port 20A and the axial projection surfaces of the bearings 15A and 15B.
  • the pressure loss of the discharge flow path 19 can be reduced and the performance can be improved.
  • a third embodiment of the present invention will be described with reference to FIGS. In the present embodiment, the description of the same parts as in the first embodiment will be omitted as appropriate.
  • FIG. 19 is a horizontal sectional view showing the structure of the gas compressor in the present embodiment.
  • 20 is a vertical sectional view taken along a section XX-XX in FIG. FIG.21 and FIG.22 is a three-dimensional figure showing the structure of the lower half of the compressor main body main casing in this embodiment.
  • the structure on the discharge side of the casing 12 can be simplified, and the degree of freedom in design can be increased, so the cooling jacket 25A is enlarged. That is, the cooling jacket 25A includes not only the outer peripheral portion of the tooth portion 11A of the male rotor 10A and the tooth portion 11B of the female rotor 10B (however, the portion excluding the suction flow path 22A), as well as the tooth portion 11A of the male rotor 10A.
  • the upper end surface and the upper end surface of the tooth portion 11B of the female rotor 10B are also formed in a portion (however, a portion excluding the discharge passage 19).
  • the discharge side portion can be efficiently cooled, and the discharge side gap caused by thermal expansion can be reduced. Therefore, the gas leakage from the compression chamber S on the discharge side can be suppressed and the performance can be improved.
  • a fourth embodiment of the present invention will be described with reference to FIG. In the present embodiment, the description of the same parts as in the first embodiment will be omitted as appropriate.
  • FIG. 23 is a horizontal sectional view showing the structure of the gas compressor in the present embodiment.
  • the gas compressor of the present embodiment includes a flat motor 2A having a shaft dimension smaller than the diameter dimension.
  • the motor 2A is, for example, an axial gap type, and includes two rotor cores 4A attached to the rotation shaft 3A and a stator core 5A disposed between the two rotor cores 4A.
  • This flat motor 2A it is possible to reduce the axial dimension of the entire compressor.
  • the distance between the bearings 15B and 16B that support the female rotor 10B can be increased, and thereby the swing of the female rotor 10B may be suppressed.
  • the case where the structure of the discharge channel 19 of the first embodiment is adopted is illustrated as an example, but the present invention is not limited to this, and the second embodiment and the first to first embodiments are illustrated. You may employ
  • the case where the compressor body 1 is an oil-free type and the male rotor 10A and the female rotor 10B are rotated in a non-contact manner by the timing gears 17A and 17B has been described as an example. Not limited to this. That is, for example, the compressor body 1 is an oil supply type or a water supply type (specifically, the compressor chamber S is operated in an oil supply state or a water supply state), and the male rotor 10A and the female rotor are not provided without the timing gears 17A and 17B. 10B may be contacted and rotated. In this case as well, the discharge channel 19 is formed so that at least a part of each of the discharge port 20 (or 20A) and the outlet port 21 overlaps the axial projection surface of the bearings 15A and 15B. An effect can be obtained.
  • the shaft portion 14A of the male rotor 10A is integrally formed with the rotating shaft 3 of the motor 2
  • the present invention is not limited to this. That is, although the shaft portion 14A of the male rotor 10A and the rotating shaft 3 of the motor 2 are molded separately, they may be connected coaxially. Further, instead of the shaft portion 14A of the male rotor 10A, the shaft portion 14B of the female rotor 10B may be integrally formed with the rotating shaft 3 of the motor 2 or connected coaxially.
  • the compressor body 1 and the shaft portion 14A of the male rotor 10A, the shaft portion 14B of the female rotor 10B, and the rotating shaft 3 of the motor 2 extend in the horizontal direction.
  • the case where the motor 2 is placed horizontally has been described as an example, but is not limited thereto. That is, the compressor body 1 and the motor 2 are placed vertically so that the shaft portion 14A of the male rotor 10A, the shaft portion 14B of the female rotor 10B, and the rotating shaft 3 of the motor 2 extend in the vertical direction, and the compressor The main body 1 may be disposed on the upper side of the motor 2. In this case, the same effect as described above can be obtained.

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

Abstract

La présente invention concerne un compresseur de gaz qui peut réaliser une performance améliorée par la réduction de perte de pression dans un passage de décharge. Le compresseur de gaz comporte: des rotors en forme de vis (10A, 10B) qui s'enclenchent mutuellement; une pluralité de paliers (15A, 15B, 16A, 16B) qui assurent le support rotatif respectif des rotors en forme de vis (10A, 10B); des engrenages de synchronisation (17A, 17B) qui servent à entraîner en rotation les rotors en forme de vis (10A, 10B) sans contact mutuel; et un carter (12, 13). Le carter (12, 13) comporte: une chambre de boîtier (18) qui renferme une partie dentée (11A) du rotor mâle (10A) et une partie dentée (11B) du rotor femelle (10B) et forme une pluralité de chambres de compression (S); des passages d'admission (22A, 22B) qui servent à introduire un gaz dans les chambres de compression (S); et un passage de décharge (19) qui sert à décharger un gaz comprimé depuis les chambres de compression (S). Le passage de décharge (19) est formé de sorte qu'au moins une partie d'un orifice de décharge (20) et une partie d'un orifice de sortie (21) chevauchent des plans de projection des engrenages de synchronisation (17A, 17B) dans une direction axiale.
PCT/JP2015/060244 2015-03-31 2015-03-31 Compresseur de gaz WO2016157449A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2015/060244 WO2016157449A1 (fr) 2015-03-31 2015-03-31 Compresseur de gaz
JP2017508956A JP6482649B2 (ja) 2015-03-31 2015-03-31 ガス圧縮機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2015/060244 WO2016157449A1 (fr) 2015-03-31 2015-03-31 Compresseur de gaz

Publications (1)

Publication Number Publication Date
WO2016157449A1 true WO2016157449A1 (fr) 2016-10-06

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PCT/JP2015/060244 WO2016157449A1 (fr) 2015-03-31 2015-03-31 Compresseur de gaz

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WO (1) WO2016157449A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51106918U (fr) * 1975-02-26 1976-08-26
JPS5918288A (ja) * 1982-07-21 1984-01-30 Hitachi Ltd スクリユ−圧縮機
JPS62247193A (ja) * 1986-04-18 1987-10-28 Tokico Ltd 真空ポンプ
JPH01237383A (ja) * 1988-03-18 1989-09-21 Hitachi Ltd スクリュー真空ポンプ

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51106918U (fr) * 1975-02-26 1976-08-26
JPS5918288A (ja) * 1982-07-21 1984-01-30 Hitachi Ltd スクリユ−圧縮機
JPS62247193A (ja) * 1986-04-18 1987-10-28 Tokico Ltd 真空ポンプ
JPH01237383A (ja) * 1988-03-18 1989-09-21 Hitachi Ltd スクリュー真空ポンプ

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JPWO2016157449A1 (ja) 2017-12-14
JP6482649B2 (ja) 2019-03-13

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